JP2002266671A - Engine speed control device for soil improving machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an engine speed control device for soil improving machine minimized in the noise and vibration of an engine and excellent in fuel economy. SOLUTION: This engine speed control device for a soil improving machine equipped with a mixing machine for mixing the soil to be improved and at least one working machine provided on the periphery of the mixing machine for mixing comprises an operating means for outputting operation signals for starting and stopping the mixing machine and the respective peripheral working machines; a plurality of hydraulic actuators for driving the mixing machine and the peripheral working machines, respectively, which is divided into a plurality of groups; a pump having a plurality of hydraulic pumps for supplying pressure oil to each of the groups and driven by an engine; a governor control means for controlling the engine speed on the basis of an inputted command value; and a controller for integrating, on the basis of the operation signal outputted from the operation means, the pressure oil flow rate necessary for the hydraulic actuators operated by the operation signal according to the groups, calculating the command value corresponding to the engine speed according to the necessary flow rate of the group having the larger integrated value and outputting it to the governor control means.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine speed control device for a soil improvement machine.

[0002]

2. Description of the Related Art In recent years, soil improvement machines for improving soil quality on site have been often used for recycling construction-generated soil.
FIG. 6 shows a self-propelled soil improvement machine 1 as an example. The soil put into the raw material soil hopper 16 by a loading machine such as a hydraulic shovel (not shown) is conveyed on the supply belt conveyor 30 to a predetermined thickness by the scraping rotor 49, and the solidified material hopper 2 Pass below. Supply belt conveyor 30
When soil is present, the solidified material feeder 48 opens and the solidified material falls from the solidified material hopper 2 onto the soil. The soil and the solidified material are dropped on a discharge belt conveyor 50 while being cut and mixed by a soil cutter 47 provided near a transport outlet of the supply belt conveyor 30. When falling, the impact of the rotary hammers 27, 28, 29 further reduces the particle size of the soil covered with the solidifying material. Then, the soil mixed with the solidified material is transported outside the machine body by the discharge belt conveyor 50. The crane 31 is used when replenishing the solidified material to the solidified material hopper 2. The soil conditioner 1 is moved between sites by the traveling device 3. The soil cutter 47 and the rotary hammers 27, 28 and 29 are collectively referred to as a mixer, and the supply belt conveyor 30, the crane 31, the solidified material feeder 48, the scraping rotor 49, and the discharge belt conveyor 50 are collectively referred to as a standard working machine. As optional working machines, an air compressor 53 used at the time of cleaning, secondary and tertiary belt conveyors 51 and 52 for transporting mixed soil to a location at a predetermined distance from the soil improvement machine 1, and finer soil from the mixed soil. A vibrating sieve 32 is provided for selection. The mixing machine, the standard working machine, the optional working machine, and the traveling device 3 are all driven by the engine 4.

[0003]

However, the above-described soil improvement machine 1 has the following problems. The operator selects a working machine to be used among the mixer, the standard working machine, and the optional working machine for each soil type and each work content, and finely operates the operating speed of the actuator of the working machine to be used. At this time, since it is troublesome for the operator to frequently operate the engine 4 in accordance with the type of working machine and the operating speed for operating the engine throttle, the operator always works with the engine 4 set to the full throttle. However, even when the number of working machines to be operated is small and the required power is small, such as when the operating speed is low, the engine rotation speed is high, so that there is a problem that noise and vibration are large.
There is also a problem that fuel efficiency is poor.

An object of the present invention is to provide an engine rotation speed control apparatus for a soil improvement machine which reduces noise and vibration of an engine and has excellent fuel efficiency, focusing on the above-mentioned problems of the prior art.

[0005]

SUMMARY OF THE INVENTION In order to achieve the above object, a first invention is directed to an engine of a soil improvement machine provided with a mixer for mixing the soil to be improved and a working machine other than the mixer. In the rotation speed control device, an operation means for outputting an operation signal for starting / stopping at least the mixer of the soil conditioner, an engine for supplying at least the driving power of the mixer of the soil conditioner, and an input command value A governor control means for controlling the engine speed and a controller for outputting to the governor control means for controlling the engine speed based on an operation signal output from the operation means are provided.

According to the first invention, the governor control means is controlled based on the operation signal output from the operation means for starting and stopping the working machine of the soil improvement machine. Thus, for example, when the mixer of the soil conditioner is stopped, the engine speed is set to be low, so that the engine speed control device of the soil conditioner with reduced noise and vibration and good fuel efficiency can be obtained.

A second aspect of the present invention relates to an engine speed control apparatus for a soil improvement machine having a mixer for mixing the soil to be improved and one or more working machines around the mixer for the mixing. Operating means for outputting an operation signal for starting and stopping each peripheral work machine, and a plurality of hydraulic actuators for driving the mixer and the peripheral work machine, respectively, are divided into a plurality of groups, and hydraulic oil is supplied to each of the plurality of groups. A plurality of hydraulic pumps to be supplied, a pump driven by the engine, governor control means for controlling the engine rotational speed based on an input command value, and operation of the pump based on an operation signal output from the operation means. The hydraulic oil flow required for the hydraulic actuator operated by the signal is integrated for each of the plurality of groups, and the engine speed corresponding to the larger required flow is calculated. And calculates the command value corresponding to the time has a configuration that includes a controller that outputs to the governor control means.

[0008] According to the second invention, the required flow rate of each group is integrated based on the operation signal output from the operation means,
The rotational speed of an engine that drives a plurality of hydraulic pumps that drive each group is controlled according to the maximum value of the plurality of integrated values. Thereby, each hydraulic pump can secure the flow rate required for each group, so that the mixer to be operated and the peripheral working machine can be reliably operated. Further, since the engine speed is controlled according to the type of the mixer and the working machine to be operated, noise and vibration are reduced, and an engine speed control device for a soil improvement machine with good fuel efficiency can be obtained.

A third invention is based on the first or second invention, and further comprises a work mode setting means for outputting a work mode signal for setting the type of the soil to be improved, and the controller includes the work mode signal and the operating means. A command value to the governor control means is calculated in accordance with the operation signal of (i).

According to the third aspect, the operation speeds of the mixer and the working machine are set by the working mode signal and the operating signal set by the operator. As a result, the operating speed according to the type of the soil to be improved of the mixing machine and the working machine to be operated can be obtained, so that the soil after the improvement can always have predetermined constant specifications.

In a fourth aspect based on the third aspect, the controller stores in advance an engine control curve representing a relationship between a discharge amount of all hydraulic pumps and an engine rotation speed, and sets a work set by the work mode setting means. A hydraulic oil flow rate required for the hydraulic actuators of the mixer and the peripheral working machine is determined according to the mode and the operation signal of the operating means, and according to the engine rotation speed determined by the engine control curve based on the determined required flow rate. The command value is output to the governor control means.

According to the fourth aspect of the present invention, the engine speed to be set is determined from the required flow rate determined according to the work mode signal and the operation signal, based on the engine control curve stored in advance. Since the engine control curve is a curve whose performance has been confirmed in an actual vehicle test, it is possible to reliably obtain an engine rotation speed that ensures a required flow rate.

In a fifth aspect based on the third or fourth aspect, the work mode setting means has a plurality of selection switches for setting the type of soil to be improved, and the controller has a function corresponding to each selection switch in advance. Then, the necessary hydraulic oil flow rate is stored for each hydraulic actuator of the mixer and the peripheral working machine, and the stored required flow rates for each hydraulic actuator are integrated according to the set selection switch to obtain all necessary hydraulic oil flow rates. The flow rate is determined, and a command value to the governor control means is calculated based on the determined total required flow rate.

According to the fifth aspect, since the work mode setting means has a plurality of selection switches, the type of the soil to be improved can be finely set. Therefore, the required flow rate can be set finely, and the engine outputs only the required rotational speed, so that noise and vibration are reduced, and an engine rotational speed control device for a soil improvement machine with good fuel efficiency can be obtained.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment according to the present invention will be described below with reference to the drawings. Note that the same elements as those described with reference to FIG. FIG. 1 shows a configuration diagram of an embodiment of an engine speed control device 19 according to the present invention. The engine speed control device 19 has an operation panel 5 and a controller 6. The operation panel 5 has a mixer button 7 s, a supply belt conveyor button 30 s, a scraping rotor button 49 s, a discharge belt conveyor button 50 s, and a vibrating sieve button 32.
s, a secondary belt conveyor button 51s, a tertiary belt conveyor button 52s, and an air compressor button 53s. Each button has an ON button and an OFF button, and operation signals Sm, Sg, Sk, and S for instructing start and stop of the corresponding working machine.
h, Sv, S2, S3, and Sa are output to the controller 6.

The operation panel 5 is provided with a work mode setting means 8, a fuel adjustment dial 9, and an automatic control button 10. The work mode setting means 8 is a switch operated in accordance with a desired particle size of the improved soil, a high mode H selected when the desired particle size is small, and a middle mode as the desired particle size increases. Selection switches 8a and 8 for mode M, low mode L, and sand mode S which are selected when the material soil is soil with low viscosity such as sand.
b, 8c and 8d. The work mode signals H, M, L, S are input to the controller 6 in the order of each mode.
The fuel adjustment dial 9 is a governor control means 11 for adjusting a fuel amount to a throttle command value Thm corresponding to the dial position.
Output to When the automatic control button 10 is turned on, the engine speed is automatically controlled in accordance with the type of work machine that is activated and the work mode signals H, M, L, S. When the automatic control button 10 is turned off, the engine speed is reduced to the throttle command value Thm. The rotation speed is adjusted accordingly.

A material soil presence / absence switch 17 for detecting whether or not the supply belt conveyor 30 is carrying soil is mounted immediately after the scraping rotor 49, and is turned on when the soil has a predetermined thickness or more, and when there is no soil. Is input to the controller 6. In addition, an operation signal Sc for turning on at the time of starting and turning off at the time of stopping is input to the controller 6 from the crane button 31 for instructing starting and stopping of the crane 31.

Mixer button 7s, supply belt conveyor button 30
s, scraping rotor button 49s, discharge belt conveyor button 5
0s, vibrating sieve button 32s, secondary belt conveyor button 51s,
52s tertiary belt conveyor button, air compressor button 53
s and the crane button 31 are collectively referred to as operation means 18.

The mixers 27, 28, 29, 47 and all the working machines 30, 31, 32, 48, 49, 50, 51, 5
Reference numerals 2 and 53 are driven by respective hydraulic actuators. A configuration of a hydraulic circuit driven by the engine 4 and controlling a hydraulic actuator will be described with reference to FIG. The tandem pump 61 driven by the engine 4 has a first pump 21 and a second pump 41 of a hydraulic pump. The first circuit 20 into which the pressure oil of the first pump 21 flows,
2, 3 rotary hammer valves 27v, 28v, 29v, supply conveyor valve 30v, crane valve 31v, vibrating sieve valve 32
This is a circuit whose main element is v. The second circuit 40 into which the pressure oil of the second pump 41 flows is provided with a soil cutter valve 47.
v, solidified material feeder valve 48v, scraping rotor valve 49
v, a discharge belt conveyor valve 50v, a secondary belt conveyor valve 51v, a tertiary belt conveyor valve 52v, and an air compressor valve 53v. The first pump 21 and the second pump 41 may be individually driven by the engine 4 instead of the tandem.

The first pump 21 and the second pump 41 are variable displacement pumps whose discharge flow rate changes according to the angle of the swash plate. Each swash plate angle corresponds to the first servo valve 22 and the second servo valve 42.
, Respectively. Further, the first servo valve 22 and the second servo valve 42 are respectively configured to output the first pilot oil pressure P1 and the first pilot oil pressure P1 output from the first pressure valve 23 and the second pressure valve 43 that generate the pilot oil pressure according to the input electric signal. It is controlled by the second pilot oil pressure P2.

First, the configuration of the first circuit 20 will be described. First, second, third rotary hammer valves 27v, 28v, 29
v, the supply conveyer valve 30v, the crane valve 31v, and the vibrating sieve valve 32v, each valve has a valve opening to facilitate the description, and each valve 27v, 28v, 29v, 30v, 3
Each actuator 27 corresponding to 1v and 32v
The state when b, 28b, 29b, 30b, 31b, 32b is moving in a certain direction is shown. The first rotary hammer valve 27v will be described as an example. The first rotary hammer valve hydraulic signal C commanded from an operation lever or the like (not shown)
27 is input to the first rotary hammer valve pressure receiving section 27p, and the first rotary hammer valve 27v moves to an opening position corresponding to the magnitude of the first rotary hammer valve oil pressure signal C27. The pipe from the first pump 21 is connected to the port A2 of the first rotary hammer valve 27v, and the port A2 is
It communicates with the port A5 via the aperture 27e. Aperture 2
7e is the area of the first rotary hammer valve hydraulic signal C27.
It changes according to the size of. When the magnitude of the first rotary hammer valve hydraulic signal C27 is zero, the throttle 2
The area of 7e also becomes zero, and the discharge oil of the first pump 21 cannot pass through the first rotary hammer valve 27v.

Next, the port A5 communicates with one port of the first rotary hammer motor 27b via a pressure compensating valve 27c whose size of the throttle changes based on the input hydraulic pressure. The load pressure P27 of the first rotary hammer motor 27b is input to the first pressure selection valve 26 via the ports A4 and A1 of the first rotary hammer valve 27v. The first pressure selection valve 26 has a load pressure P2 on the output side of the other second and third rotary hammer valves 28v and 29v, a supply conveyor valve 30v, a crane valve 31v, and a vibrating sieve valve 32v.
8, P29, P30, P31, and P32 are also input. The first pressure selection valve 26 is the first load pressure P20m of the largest hydraulic pressure among the plurality of hydraulic pressures to be input.
Is selected, and the selected first load pressure P20m is set to the pressure compensating valve 2
7c, 28c, 29c, 30c, 31c, 32c. The other port of the first rotary hammer motor 27b is connected to the ports A6, A of the first rotary hammer valve 27v.
3 and communicate with the tank 60.

Next, the configuration of the second circuit 40 will be described. Internal circuits of the soil cutter valve 47v, the solidified material feeder valve 48v, the scraping rotor valve 49v, the discharge belt conveyor valve 50v, the secondary belt conveyor valve 51v, the tertiary belt conveyor valve 52v, and the air compressor valve 53v of the second circuit 40 Actuators 47b, 48b, 49b, 50
The circuit for connecting b, 51b, 52b, and 53b is the same as that of the first rotary hammer valve 27v, and a description thereof will be omitted. Load pressure P47, P4 of each actuator
8, P49, P50, P51, P52, P53
It is input to the pressure selection valve 46. Second pressure selection valve 46
Is the second of the largest hydraulic pressures among the plurality of hydraulic pressures to be input.
The load pressure P40m is selected, and the selected second load pressure P40m is selected.
Is output to each pressure compensating valve (not shown) of each valve.

Next, input / output signals of the pump controller 62 for controlling the discharge flow rate of the tandem pump 61 will be described. The first discharge pressure P20p detected by the first discharge pressure detector 24 attached to the discharge port of the first pump 21 and the first load pressure P20 detected by the first load pressure detector 25
m is input to the pump controller 62, respectively. Also, the second discharge pressure P40 detected by the second discharge pressure detector 44 attached to the discharge port of the second pump 41
p and the second load pressure P40m detected by the second load pressure detector 45 are also input to the pump controller 62, respectively. Further, an engine rotation speed Ne and a throttle command value Th detected by a detector (not shown) are input. Then, the first signal S from the pump controller 62 is output.
The first and second signals S2 are output to the first pressure valve 23 and the second pressure valve 43.

Here, the operation of the pump controller 62 will be described. The differential pressure between them is calculated from the first discharge pressure P20p and the first load pressure P20m. Then, a first signal S1 is output to the first pressure valve 23 so that the calculated differential pressure becomes a predetermined value set in advance. This is referred to as differential pressure control means in the pump controller 62. By the differential pressure control means, the load pressures P27, P28, P
The first pressure is set so that the differential pressure between the maximum value among the pressures 29, P30, P31, and P32 and the first discharge pressure P20p is substantially constant at a predetermined value.
The swash plate angle of the pump 21 is controlled. Further, a differential pressure between them is calculated from the second discharge pressure P40p and the second load pressure P40m, and the second signal S is calculated so that the calculated differential pressure becomes substantially constant.
2 is output to the second pressure valve 43. Then, the swash plate angle of the second pump 41 is controlled similarly to the first pump 21.

As shown in FIG. 3, when the vertical axis indicates the hydraulic pump discharge flow rate Qp and the horizontal axis indicates the load pressure Pp to the hydraulic pump, the pump output horsepower is obtained when the load pressure Pp is larger than the predetermined pressure Pc. The swash plate angle is controlled by the pump controller 62 so that is constant. When the load pressure Pp is equal to or lower than the predetermined pressure Pc, the maximum value of the swash plate angle of the hydraulic pump is regulated to a constant value, and the maximum value of the hydraulic pump discharge flow rate Qp is a constant value corresponding to the engine speed Ne. I have. Since the relief pressure of each circuit is set so that the load pressure of the first circuit 20 and the second circuit 40 is always equal to or lower than the predetermined pressure Pc, the maximum value of the discharge flow rate of each of the first and second pumps 21 and 41 is set. Is always a value corresponding to the engine rotation speed Ne.

Here, the operation of the first circuit 20 will be described as a representative. The crane 31 and the vibrating sieve 32 are stopped operating, and the first, second, third rotary hammers 27, 28, 29
And a case where the supply belt conveyor 30 is operated. The first, second and third rotary hammers 27, 28,
It is assumed that the same load is applied to all 29, and the first rotary hammer 27 will be described as a representative. First pump 21
Discharge oil flows into the first rotary hammer valve 27v and the supply belt conveyor valve 30v to rotate the first rotary hammer motor 27b and the supply belt conveyor motor 30b. When the area of the throttle 27e and the area of the throttle 30e are the same and the first rotary hammer load pressure P27 is equal to the supply belt conveyor load pressure P30, the same flow rate is supplied to the first rotary hammer valve 27v and the supply belt conveyor valve 30v. Flowing. At this time, the first load pressure P
20m is the first rotary hammer load pressure P27 or the supply belt conveyor load pressure P30, and the first discharge pressure P20p
Is controlled such that the swash plate angle becomes larger by a predetermined value than the first load pressure P20m.

When the load on the first rotary hammer 27 becomes large and the first rotary hammer load pressure P27 becomes larger than the supply belt conveyor load pressure P30, the first discharge pressure P20p becomes large and the throttle 30e of the supply belt conveyor valve 30 becomes smaller. The flow rate passing through is trying to increase. At this time, the first pressure selection valve 26 selects the first rotary hammer load pressure P27 as the first load pressure P20m, and supplies it to the pressure compensating valve 30c. Then, since the opening area of the pressure compensating valve 30c is reduced and narrowed, the flow rate passing through the throttle 30e does not increase, and the same flow rate as the flow rate passing through the throttle 27e is maintained. Further, since the first load pressure P20m increases, the predetermined differential pressure held between the first discharge pressure P20p and the first load pressure P20m decreases. The pump controller 62 again outputs the first signal S such that the predetermined differential pressure is obtained.
1 is output to the first pressure valve 23 and the first servo valve 22
, The discharge flow rate of the first pump 21 is increased. As described above, when one hydraulic pump drives a plurality of actuators via a plurality of valves, even if the loads of the individual hydraulic actuators are different, the operation of the other valves is not affected and the individual valves are always affected. Secure the control flow rate according to the opening.

Now, description will return to the configuration of the engine speed control device 19 shown in FIG. The required flow rate calculation unit 12 stores a required flow rate calculation table shown in FIG. 4 in advance. FIG. 4A or FIG. 4B shows the first circuit 20 or the second circuit 20.
The required flow rate of each actuator of the circuit 40 is shown for each of the operation mode signals H, M, L, and S from the operation mode setting means 8. Also, the buttons 31s, 7s, 3
0s, 49s, 50s, 32s, 51s, 52s, 53
S, Sm, Sg, Sk, Sh, S
The required flow rates when v, S2, S3, and Sa are ON signals are shown. In addition, the first, second and third rotary hammers 27,
28, 29, the soil cutter 47, and the required flow rate of the fixing material feeder 48 are determined by the presence / absence signal S
When u is on, the value in the column of raw material soil is taken, and when u is off, the value in the column of raw material soil is taken. The required flow rates of the first, second, third rotary hammers 27, 28, 29 and the soil cutter 47 are maximum values when the operation mode signal H is H, and decrease in the order of M, L, and S. The operation signals Sc, Sm, Sg,
When Sk, Sh, Sv, S2, S3, and Sa are off signals, the required flow rate of each actuator is zero, but is not shown in FIG.

The required flow rate calculator 12 calculates the first flow rate Q1 and the second flow rate Q2 required for the first circuit 20 and the second circuit 40 based on the table of FIG. The larger of the two flow rates Q1 and Q2 is selected as the large flow rate Q. The engine rotation calculator 14 calculates an engine rotation speed Ne at which the flow rate Q can be sufficiently discharged based on an engine control curve Ce shown in FIG. As shown in FIG. 5, when the engine speed Ne is a predetermined first speed N1, the hydraulic pump discharge flow rate Qp is from zero to Q1, and when the engine speed Ne is a predetermined second speed N2, the hydraulic pump discharge flow rate Qp is Changes from Q2 to Q3. When the engine speed Ne is between the first and second speeds, the hydraulic pump discharge flow rate Qp takes a value between Q1 and Q2. The first speed N1 and the second speed are, for example, 1400 rpm and a high idle rotation speed. In the throttle command value calculation unit 15, the engine control curve C
e, a throttle command value Thp corresponding to the engine speed Ne calculated by the e is calculated, and the calculated throttle command value T
The hp is input to the governor control unit 11.

The operation and effect of the engine speed control device 19 having the above configuration will be described. When the automatic control button 10 is turned on, the crane button 31s attached to the crane 31, the vibration sieve button 32s on the operation panel 5, the second and third belt conveyor buttons 51s and 52s, the air compressor button 53
It is assumed that s is turned off and the work mode signal M is selected by the work mode setting means 8. Further, it is assumed that soil is flowing on the supply belt conveyor 30, and the presence / absence signal Su of the material soil presence / absence switch 17 outputs an ON signal. In the required flow rate calculating section 12, the required flow rate b of the first, second, and third rotary hammers 27, 28, and 29 in the column of M of the first circuit 20 group shown in FIG.
The first flow rate Q1 is integrated, for example, to 150 liters / minute by combining 1, b3, and b5 with the required flow rate b7 of the supply belt conveyor 30. Also, the first circuit 4 shown in FIG.
The required flow rates f1 and f3 of the soil cutter 47 and the solidified material feeder 48 in the column M of the group 0 when the raw material is soiled, the required flow rate f5 of the scraping rotor 49, and the required flow rate f6 of the discharge belt conveyor 50 are combined. The two flow rates Q2 are integrated, for example, to 91 liters / minute. The large flow rate selection unit 13 selects the larger flow rate of 150 liter / min between the first and second flow rates Q1 and Q2 as the large flow rate Q. Next, the engine rotation speed calculation unit 14 calculates the engine rotation speed Ne corresponding to the large flow rate Q of 150 liters / minute as Xrpm based on the engine control curve Ce shown in FIG. The throttle command value calculation unit 15 calculates a throttle command value Thp corresponding to Xrpm, outputs the calculated throttle command value Thp to the governor control unit 11, holds the engine rotation speed Ne at Xrpm, and discharges the first and second pumps 21 and 41 respectively. At 150 l / min.

When no soil is flowing on the supply belt conveyor 30 and the presence / absence signal Su of the material soil presence / absence switch 17 is off, the necessary flow rate calculation unit 12 causes the first circuit 20 group shown in FIG. And the required flow rates b2, b4, b6 of the first, second, third rotary hammers 27, 28, 29 in the column of M when there is no raw material soil and the required flow rate b7 of the supply belt conveyor 30 are combined into a first flow rate Q1. Is integrated with, for example, 105 liters / minute. Also, the first type shown in FIG.
Required flow rates f2 and f4 of the soil cutter 47 and the solidified material feeder 48 in the column of M of the circuit 40 group when there is no raw material soil.
And the required flow rate f5 of the scraping rotor 49 and the required flow rate f6 of the discharge belt conveyor 50 together with the second flow rate Q2.
Is integrated with, for example, 51 liter / minute. In the large flow rate selection unit 13, the larger flow rate 1 of the first and second flow rates Q1 and Q2
Select 05 liters / min as the large flow rate Q. Next, the engine speed calculation unit 14 calculates the engine speed corresponding to the large flow rate Q of 105 L / min as N1 rpm, based on the engine control curve Ce shown in FIG. The throttle command value calculation unit 15 calculates a throttle command value Thp corresponding to N1 rpm, outputs the calculated throttle command value Thp to the governor control means 11, holds the engine rotation speed Ne at N1 rpm, and discharges the first and second pumps 21 and 41 respectively. To 105
Hold at liter / min

The automatic control button 10 is turned on and the operation panel 5
The upper vibrating sieve button 32s, the air compressor button 53s, and the crane button 31s are turned off, but the second and third belt conveyor buttons 51s and 52s are turned on. Is selected. Further, it is assumed that soil is flowing on the supply belt conveyor 30, and the presence / absence signal Su of the material soil presence / absence switch 17 outputs an ON signal. In the required flow rate calculation unit 12,
4A, the required flow rate of the first circuit 20 group is, for example, 105.5 liters / minute, and FIG.
The required flow rate of the 0 group is integrated, for example, to 120.5 liter / min. In the large flow rate selection unit 13, the first
2 The larger flow rate of 120.5 l / min of the flow rates Q1 and Q2 is selected as the large flow rate Q, and the engine speed corresponding to the flow rate of 120.5 l / min is calculated as Yrpm by the engine control curve Ce shown in FIG. I do. Then, the throttle command value calculation unit 15 calculates a throttle command value Thp according to Yrpm and outputs the calculated throttle command value Thp to the governor control means 11 to hold the engine rotation speed Ne at Yrpm.
2 The discharge flow rate of each of the pumps 21 and 41 is set to 120.5
Hold at liter / min.

When soil is not flowing on the supply belt conveyor 30 and the presence / absence signal Su of the material soil presence / absence switch 17 is an off signal, the necessary flow rate calculation unit 12 performs the operation shown in FIG.
The required flow rate of the first circuit 20 group is, for example, 77 liter / minute, and the required flow rate of the second circuit 40 group is, for example, 95.5 liter / minute from FIG. 4B. The large flow rate selection unit 13 selects the larger flow rate 95.5 l / min of the first and second flow rates Q1 and Q2 as the large flow rate Q, and sets the flow rate 95.5 l / min according to the engine control curve Ce shown in FIG. Engine speed Ne corresponding to
Is calculated as N1 rpm. Then, the throttle command value calculator 15 calculates the throttle command value Th according to N1 rpm.
is calculated and output to the governor control means 11 to maintain the engine rotation speed Ne at N1 rpm.
The discharge flow rate of each of Nos. 1 and 41 is maintained at 95.5 L / min.

When the automatic control button 10 is turned on, the buttons 31s, 7s, 30s, 49s, 50s, 32
When s, 51s, 52s, and 53s are turned off, the engine rotation speed Ne is controlled to the deceleration rotation speed (for example, a low idle rotation speed of 600 rpm).

As described above, the buttons 31s, 7s, 30s, 49s, and 50 for instructing the start and stop of each actuator are provided.
operation signal S from s, 32s, 51s, 52, 53s
c, Sm, Sg, Sk, Sh, Sv, S2, S3, Sa
And a work mode signal H,
Based on M, L, S and the presence / absence signal Su from the material soil presence / absence switch 17, the required pump flow rate is calculated. Then, the engine speed Ne is controlled to a speed corresponding to the required flow rate of the pump. Accordingly, when the required flow rate of the pump is small, the engine rotation speed Ne is automatically and finely controlled so as to be small, so that the engine noise and vibration of the engine are reduced and the engine rotation speed control device of the soil improvement machine having excellent fuel efficiency is provided. 19 is obtained.

Although the present embodiment has been described by taking a mobile type soil improvement machine as an example, it is apparent that a stationary type soil improvement machine instead of a mobile type can exert the same effect. . In this embodiment, the buttons 31s, 7s, 30s, 49s, 50s, 32
Although the engine rotation speed Ne is controlled to be the deceleration rotation speed when the s, 51s, 52s, and 53s are being turned off, the present invention is not limited to this. For example, only the mixer button 7s is turned off. The engine rotation speed Ne may be set to the deceleration rotation speed when the engine is in operation.

As described above, according to the present invention, the operation means for outputting the operation signals for starting and stopping the mixer and the respective peripheral working machines, and the plurality of hydraulic actuators for driving the mixing machine and the peripheral working machines, respectively, are provided. Dividing into groups, having a plurality of hydraulic pumps for supplying pressure oil to each of the plurality of groups, a tandem pump driven by the engine, and a governor control means for controlling the engine speed based on an input command value, Based on the operation signal output from the operation means, the hydraulic oil flow required for the hydraulic actuator operated by the operation signal is integrated for each of the plurality of groups, and the engine speed corresponding to the larger required integrated flow is calculated. And a controller for calculating a command value corresponding to the control value and outputting the command value to the governor control means. This allows
Since each hydraulic pump can secure the required flow rate in each group, the mixer and the peripheral working machine to be operated can be reliably operated. Further, since the engine speed is controlled according to the type of the mixer and the working machine to be operated, noise and vibration are reduced, and an engine speed control device for a soil improvement machine with good fuel efficiency can be obtained. Further, since the engine speed is automatically controlled to be large or small depending on the number of working machines in operation, the operation of the operator is easy and a soil improvement machine having an excellent driving feeling can be obtained.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of an engine rotation speed control device according to the present invention.

FIG. 2 is a hydraulic circuit diagram of a mixer and a working machine.

FIG. 3 is an explanatory diagram of a relationship between a hydraulic pump discharge flow rate and a hydraulic pump load pressure.

FIG. 4 is an explanatory diagram of a required flow rate calculation table.

FIG. 5 is an explanatory diagram of an engine control curve.

FIG. 6 is an explanatory view of a soil improvement machine.

[Explanation of symbols]

DESCRIPTION OF REFERENCE NUMERALS 1: soil improvement machine, 2: solidified material hopper, 3: traveling device, 4
... Engine, 5 ... Operation panel, 6 ... Controller, 8 ... Work mode setting means, 9 ... Fuel adjustment dial, 10 ... Automatic control button, 11 ... Governor control means, 12 ... Necessary flow rate calculation unit,
13 large flow rate selection unit, 14 engine speed calculation unit
15: Throttle command value calculation unit, 16: Raw material soil hopper,
Reference numeral 17: material soil presence / absence switch, 18: operating means, 19: engine rotation speed control device, 20: first circuit, 21: first
Pump, 22 first servo valve, 23 first pressure valve, 24
... First discharge pressure detector, 25 ... First load pressure detector, 26 ...
1st pressure selection valve, 27 ... 1st rotary hammer, 28 ...
2nd rotary hammer, 29 ... 3rd rotary hammer,
Reference numeral 30: supply belt conveyor, 31: crane, 32: vibrating sieve, 40: second circuit, 41: second pump, 42: second
Servo valve, 43 second pressure valve, 44 second discharge pressure detector, 45 second load pressure detector, 46 second pressure selection valve
47: soil cutter, 48: solidified material feeder, 49: scraping rotor, 50: discharge belt conveyor, 51: secondary belt conveyor, 52: tertiary belt conveyor, 53: air compressor, 60: tank, 61: tandem pump, 62 ... Pump controller, 7s ... Mixer button, 30
s: supply conveyor button, 31s: crane button, 32s: vibrating sieve button, 49s: scraping rotor button, 50s: discharge belt conveyor button, 51s: secondary belt conveyor button, 52s
... Third belt conveyor button, 53s ... Air compressor button, C27 ... First rotary hammer valve hydraulic signal, 27p
… First rotary hammer valve pressure receiving part, P27… Load pressure, 2
7e: throttle, 27c: pressure compensation valve, S1: first signal, S
2: second signal, P20m: first load pressure, P40m: second
Load pressure, P20p: first discharge pressure, P40p: second discharge pressure, P1: first pilot oil pressure, P2: second pilot oil pressure, Ne: engine rotation speed, Th, Thm, Thp
... Throttle command value, Q1 ... First flow rate, Q2 ... Second flow rate, Q ... High flow rate, Sc, Sm, Sg, Sk, Sh, S
v, S2, S3, Sa: operation signal, H, M, L, S: work mode signal, Su: presence / absence signal, Ce: engine control curve.

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Claims (5)

[Claims] An engine rotation speed control device for a soil improvement machine having a mixer for mixing the soil to be improved and a working machine other than the mixer, comprising: an operation signal (Sc) for starting / stopping at least the mixer of the soil improvement machine. , Sm, Sg, Sk, Sh, Sv, S2, S3, Sa), and an engine (4) that supplies at least the driving power of the mixer of the soil conditioner, Governor control means (11) for controlling the engine rotation speed based on the value, and operation signals (Sc, Sm, Sg, S
(k, Sh, Sv, S2, S3, Sa) based on the governor control means (11) for controlling the engine speed based on the controller (6) to output the engine speed control of the soil improvement machine apparatus. 2. An engine rotation speed control device for a soil improvement machine, comprising: a mixer for mixing the soil to be improved, and one or more working machines around the mixer for the mixing. Operation means (18) for outputting operation signals (Sc, Sm, Sg, Sk, Sh, Sv, S2, S3, Sa) for starting and stopping peripheral work machines, and a plurality of driving means for driving the mixing machine and the peripheral work machines respectively Hydraulic actuators (27b, 28b, 29b, 30b, 31b, 32b, 47b, 48b, 49b, 5
0b, 51b, 52b, 53b) into a plurality of groups, and a plurality of hydraulic pumps (21,
A pump (61) having an (41) and driven by an engine (4)
Governor control means (11) for controlling the engine speed based on the input command value, and operation signals (Sc, Sm, Sg, Sk, Sh, Sh,
Sv, S2, S3, Sa), the operation signals (Sc, Sm, Sg, Sk, S
h, Sv, S2, S3, Sa)
(b, 28b, 29b, 30b, 31b, 32b, 47b, 48b, 49b, 50b, 51b, 52b, 53b)
Controller that integrates the required pressure oil flow rate for each of the plurality of groups, calculates a command value corresponding to the engine speed corresponding to the required flow rate of the larger integrated value, and outputs the command value to the governor control means (11). 6) An engine speed control device for a soil improvement machine, comprising: 3. The work mode setting means for outputting a work mode signal (H, M, L, S) for setting the type of soil to be improved in the engine speed control device for a soil improvement machine according to claim 1 or 2. (8) attached, the controller (6), the work mode signal (H, M, L, S)
And the operation signal of the operation means (18) (Sc, Sm, Sg, Sk, Sh, Sv, S2,
S3, Sa), wherein an instruction value to the governor control means (11) is calculated. 4. The engine rotation speed control device for a soil conditioner according to claim 3, wherein the controller (6) has an engine control curve representing a relationship between a discharge amount of all hydraulic pumps and an engine rotation speed in advance.
(Ce), and the work mode set by the work mode setting means (8) and the operation signals (Sc, Sm, S
g, Sk, Sh, Sv, S2, S3, Sa) and the mixer (27,28,29,47)
And the hydraulic actuators (27b, 28b, 29b, 47b, 30b, 31b, 32b, 48) of the peripheral work machines (30, 31, 32, 48, 49, 50, 51, 52, 53).
b, 49b, 50b, 51b, 52b, 53b) to determine the required hydraulic oil flow rate, and based on the determined required flow rate, the engine control curve (Ce)
And outputting a command value corresponding to the engine rotation speed obtained by the above to the governor control means (11). 5. The engine speed control device for a soil improvement machine according to claim 3, wherein said work mode setting means (8) includes a plurality of selection switches (8a, 8b, 8c, 8d), and the controller (6) has a selection switch (8a, 8b, 8
c, 8d), the hydraulic actuators (27b, 27) of the mixer (27, 28, 29, 47) and the peripheral work machine (30, 31, 32, 48, 49, 50, 51, 52, 53). 28b, 29b, 47b, 30b, 31b, 32b, 48b, 49b, 50b, 51b, 52
b, 53b) separately stores the required hydraulic oil flow rate, and according to the set selection switch (8a, 8b, 8c, 8d), the stored hydraulic actuators (27b, 28b, 29b, 47b, 47b, 30
(b, 31b, 32b, 48b, 49b, 50b, 51b, 52b, 53b) Another required flow is integrated to obtain the total required flow, and a command to the governor control means (11) is issued based on the obtained total required flow. An engine speed control device for a soil improvement machine, which calculates a value.