JPS5819247B2 - Combine harvester with traveling speed control mechanism - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a combine harvester configured to branch and transmit engine output to a threshing device and a traveling transmission.

In recent years, research has been carried out to control the vehicle speed of combine harvesters according to the threshing load.As a specific example, the threshing load detection result and the traveling speed are controlled so that the threshing load and traveling speed are kept in a preset inverse ratio relationship. A means has been developed to automatically control the traveling transmission based on the speed detection result to always perform harvest traveling while making maximum use of engine power.

In this case, since the running speed is detected using, for example, the rotational speed of the input shaft of the running transmission case, the engine rotational speed decreases due to an increase in load on parts of the device other than the threshing device, such as an increase in running load. Then, the traveling speed detection value decreases accordingly, and as a result, the inverse ratio balance between the threshing load and the traveling speed is disrupted, and the control to increase the traveling speed is activated, further increasing the traveling load and the threshing load. This would cause some inconvenience.

The present invention has been made to solve such problems.

Embodiments of the present invention will be described below based on the drawings.

Figure 1 shows the side view of the combine, and shows the crawler traveling device 1.
, 1 is equipped with a threshing device 3, an engine 4, and a driver's seat 5, and a hoisting device 6, a reaping device 7, and a reaped husk conveying device 8 are mounted on the front part of the platform 2. , etc. are connected to each other.

The threshing device 3 is also equipped with a feed chain 10, a straw removal conveyance chain 11, and a straw removal cutter 12.

FIG. 2 is a block diagram showing the transmission system from the engine 4 to each device. The power from the engine 4 is branched into m=systems, and one branched power is used to drive the threshing device 3, the feed chain 10, and the straw removal cutter. 12, Straw removal chain 1
1 is driven.

In addition, the other branched power is a variable displacement pump P and a hydraulic motor M.
It is input to the hydraulic continuously variable transmission H8T14 consisting of
A part of the output from this transmission 14 is transmitted to the crawler traveling devices 1, 1 via the traveling mission case 15, and another part of the output from the transmission 14 is transmitted to the pulling device 6 and the reaping device 7. , is transmitted to the cut culm conveying device 8.

Incidentally, since the transmission 14 is configured to be capable of forward and reverse movement (forward and backward movement), the reversal power is transmitted to the reaping and conveying devices 6,
A one-way rotation clutch 16 is interposed to prevent the transmission from being transmitted to 7.8.

The transmission device 14 can be operated manually or automatically based on the threshing load, and its schematic configuration is shown in FIG. 3.

The transmission device 14 is linked to the speed change lever 17 via a link mechanism 18, and the intermediate portion of the link mechanism 18 and a forward/reverse transmission motor 19 for automatic transmission are connected to a worm reduction device 20 and a friction plate type rotation transmission. They are interlocked and connected via a mechanism 21.

The threshing device 3 is also equipped with a threshing load detection mechanism 23 that detects the threshing load as a load torque acting on the handling cylinder 22.

This detection mechanism 23, as shown in FIG.
An input pulley 26 is supported for relative rotation within a certain range and is connected to the handling cylinder shaft 24 via a spring 25, and an iron gear-shaped rotating body 27° 28 of the same shape is connected to the handling cylinder shaft 24, respectively.
The output pulse P1 from both coils 2930 is fixed to the rotary bodies 27 and 28, and opposed resistance generating coils 29 and 30 are fixedly arranged on the teeth of each rotating body 27 and 28.
, R2 are input to the arithmetic circuit 31 to obtain the handling cylinder torque T.

In this circuit 31, as shown in FIG.
20 phase deviation pulse P3 is obtained, the delayed phase of the handling cylinder shaft 24 with respect to the input pulley 26 is determined from the length of this pulse P3, and the handling cylinder torque T is calculated from this.

On the other hand, the output pulse P1 of the no-pulse generating coil 29 is also input to the engine rotational speed detection circuit 32.

This circuit 32 calculates the engine rotation speed R by counting the number of pulses within a set unit time.

Further, the input section of the traveling mission case 15 is equipped with a mechanism 33 for calculating and detecting the traveling speed vo from the input shaft rotation speed per set unit time, and furthermore, this traveling speed detecting mechanism, 3
3 is input to a traveling speed correction circuit 34.

This correction circuit 34 includes the engine rotation speed detection circuit 3.
2 and the output from the reference engine rotational speed setting circuit 35 are input, the traveling speed is corrected as shown by the following equation, and the corrected traveling speed V is taken out as a small force.

However, when Ro-R<0, Ro-R>= 0Ro-R
When ≧0, Ro −R> = Ro−Rvo: Detected traveling speed Ro: Reference engine rotation speed (correction starting point) R: Detected engine rotation speed n: Constant f: Correction coefficient Also, the value obtained in this way The corrected traveling speed V and the detected handling cylinder torque T are input to an automatic control circuit 3.6 that controls the motor 19.

The gear shift lever 17 can be manually operated arbitrarily against the frictional force of the transmission mechanism 21, and the gear shift lever 17 can also be automatically operated by the motor 19. Does the handling cylinder torque T and the corrected traveling speed V maintain the predetermined inverse proportional relationship shown in FIG. 6? Furthermore, the motor 19 is configured to be driven in forward and reverse directions based on both T and V.

If reaping and harvesting work is carried out using the vehicle speed control mechanism with the above configuration, as is clear from Fig. 6, when the threshing load is large, the harvesting operation will be carried out at a low speed, and the harvest amount per unit time will be reduced. In addition, when the unloading is small, high-speed harvesting runs are carried out to increase the harvest amount per unit time,
Harvest driving is always carried out using sufficient engine power.

In this case, even if the engine rotation speed R decreases due to an increase in the running load and the running speed Vo decreases, the detected engine rotation speed R remains at or above the reference speed Ro for a short period of time when the engine rotation speed decreases. Time (Ro R(0* or R
o-R=0) is <Ro-R>-〇 or <Ro-
Since R:>-R8-R=0, V=Vo from the above correction calculation formula, and the detected traveling speed [Vo is input as is for control.

Then, the running load increases greatly and the engine rotational speed R
becomes lower than the reference speed Ro (Rn - R> O)
, <Ro-R>-Ro-R, and the denominator on the right side of the correction calculation formula is 0<1-(Ro-R)f/n(1 and V)V.

becomes.

The detection speed V is sent to the control circuit 36. A larger correction value is input.

As a result, if only the actual traveling speed Vo is significantly reduced due to a decrease in the engine rotational speed R without any fluctuation in the handling cylinder torque T, the increase-corrected traveling speed V is used as the moderation input. The balance of the inverse ratio relationship of control is maintained, and speed increase control is not performed.

Then, when the engine speed R decreases particularly greatly,
The traveling speed boosting pressure is sufficiently applied, and rather the balance of the inverse ratio relationship is disturbed in the direction that requires the reduction control, and troubles such as engine stop can be avoided by actively controlling the deceleration.

The timing of such control is determined by appropriately setting the positive coefficient f in the iMJ correction calculation formula.

Further, in the embodiment, the engine rotation speed R is indirectly detected using pulses in the handling barrel torque detection mechanism 23.
Of course, a speed meter may be separately attached directly to the engine output shaft or the rotating shaft linked thereto for detection.

As described above in the embodiments, according to the present invention, there is no problem in which improper speed increase/control is performed due to a decrease in travel speed due to a decrease in engine rotational speed, and stable speed control can be performed.

[Brief explanation of drawings]

The drawings illustrate an embodiment of the combine harvester with a traveling speed control mechanism according to the present invention, in which FIG. 1 is an overall side view, FIG. 2 is a block diagram schematically showing the power transmission system, and FIG. 3 is a diagram showing the control mechanism. 4 is a diagram showing the principle structure of the handling cylinder torque detection section, FIG. 5 is a pulse signal diagram for detecting the handling cylinder torque, and FIG. 6 is a control characteristic diagram. 3... Threshing device, 4... Engine, 1
5... Traveling transmission, 23... Threshing load detection device, 34... Traveling speed correction circuit, V
o...Detected running speed, ■...Corrected running speed value, R...Detected engine rotation speed,
Ro...Reference rotation speed.

Claims (1)

[Claims] 1. The output of the engine 4 is transmitted to the threshing device 3 and the traveling transmission device 1.
In addition, a mechanism 23 for detecting the load of the threshing device 3 and a mechanism 33 for detecting the actual running speed WVo are provided, and the threshing load and the running speed are set in a preset inverse ratio relationship. In a combine harvester having a control circuit for controlling the automatic transmission mechanism of the transmission device 15, a mechanism for detecting the engine 40 rotation speed is provided so that when the detected engine rotation speed R decreases, at this time A combine harvester with a traveling speed control mechanism, characterized in that it is equipped with a traveling speed correction circuit 34 which increases the detected traveling speed Vo and inputs this correction value V to the control circuit as a traveling speed for control. 2 In the K1 correction circuit 34, the detected engine rotation speed I
The combine harvester according to claim 1, wherein the combine harvester is configured such that the traveling speed value increase correction is performed in proportion to the difference Ro-H only when tR falls below a preset reference rotation speed Ro.