JPH11226446A - Feeder controller for crusher - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a feeder controller for a crusher by which the quantity of coarse coke fed to a crusher from a feeder can be normally kept proper irrespective of the compression strength of the coarse coke. SOLUTION: The feeder controller is formed of pressure sensors 85a, 85b for detecting load pressures of a crushing hydraulic motor 24, a level sensor 87 for detecting the quantity of coarse coke fed to a jaw crusher, and a feeder control part installed in a controller 90. The feeder control part starts a control function by an equipment control part 90b when a driving signal Sf of a solenoid control valve 41 is turned ON, and appropriately corrects/changes the driving signal Sf to the solenoid control valve 41 from the equipment control part 90b to control the action speed of a feeder hydraulic motor 23, based on load pressures PCL1 , PCL2 detected by the pressure sensors 85a, 85b and a coarse coke detection signal X detected by a photoelectric sensor 87.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a crusher for crushing rocks and construction waste, and more particularly to a crusher feeder control device for controlling a feeder provided in the crusher.

[0002]

2. Description of the Related Art Crushers are used to remove various large and small rocks and construction wastes (hereinafter referred to as "gara" as appropriate) generated at construction sites.
By crushing to a predetermined size at the site before transportation, the construction is facilitated and the cost is reduced. That is, the mower thrown into the hopper provided above the crusher by a hydraulic shovel or the like is guided to a crushing device such as a jaw crusher having a substantially V-shaped side cross-section by a feeder provided below the hopper, and a predetermined amount of water is supplied to the crusher. Crushed to size. The crushed gala falls from the space below the jaw crusher onto a conveyor arranged below the jaw crusher and is carried by the conveyor. During this transportation, a magnetic separator arranged above the conveyor adsorbs and removes, for example, reinforcing bar pieces mixed in the concrete garbage, and finally as a crushed material of almost uniform size, the front of the crusher It is carried out from.

[0003] During the above operation, it is important to control the feeder so as to perform appropriate supply in accordance with the crushing capacity and the crushing state of the crushing device, particularly when supplying waste from the feeder to the crushing device. Furthermore, at the operation site of the crusher,
In many cases, an operator of a hydraulic excavator that puts waste into a hopper without an operator dedicated to the crusher is also in charge. In such a case, the operator must operate not only the hydraulic excavator but also the crusher, so that the labor must be reduced as much as possible.

[0004] From the above point of view, an apparatus for automatically controlling the feeder supply operation has been conventionally proposed. Known techniques include, for example, Japanese Utility Model Publication No. 5-1315 and Japanese Patent Application Laid-Open No. Hei 7-116541. There is a gazette. Real fair 5-
In the feeder control device disclosed in Japanese Patent No. 1315, a photoelectric sensor is provided in a crushing chamber which is provided above the crushing device and introduces the waste from the feeder. If it is detected that the feeder has overflowed beyond a certain height, the operation of the feeder is stopped.

The feeder control device disclosed in Japanese Patent Application Laid-Open No. Hei 7-116541 detects the rotation speed of a hydraulic motor that drives a crushing device with a rotation sensor, and when the load of the hydraulic motor becomes excessive and the rotation speed falls below a predetermined value. Is to stop the operation of the feeder.

[0006]

The above-mentioned prior art has the following problems. In the feeder control device disclosed in Japanese Utility Model Publication No. 5-1315, when the gala (for example, rock) having a relatively high compressive strength is supplied, the total weight of the gala increases even with a small amount of supply, so that the photoelectric sensor does not operate. However, there is a possibility that the load on the hydraulic motor that drives the crushing device becomes excessive. If the load becomes excessive, the number of revolutions of the hydraulic motor decreases, and the crushing speed decreases. This will be described with reference to FIG. FIG. 10 is a PQ characteristic line showing general characteristics of a variable displacement hydraulic pump that supplies pressure oil for driving a hydraulic motor. The vertical axis indicates the flow rate Q of the pressure oil that can be discharged from the pump, and the horizontal axis indicates the discharge pressure P of the pressure oil discharged from the pump. As shown in the figure, in a region where the pump discharge pressure P ≦ PD (= the limit pressure at which the dischargeable flow rate Qo can flow), the discharge flow rate Q becomes the dischargeable flow rate Qo in terms of pump performance. If exceeded,
Since the discharge flow rate Q changes so that PQ = a constant value,
The discharge flow rate Q decreases as the discharge pressure P increases. At this time, when the pump tilt angle θ is the maximum tilt angle θmax, the flow rate Qo becomes the maximum flow rate. However, as shown in FIG. 10, as the pump tilt angle θ becomes smaller than θmax, the dischargeable flow rate Qo becomes smaller.
Becomes smaller and becomes Qo '. On the other hand, the dischargeable flow rate Qo '
Is increased to PD '.

During the crushing operation, when the load on the hydraulic motor driving the crushing device increases, the discharge pressure P of the pump also increases correspondingly. At this time, if the load becomes excessive, the pump discharge pressure P may exceed PD, and in this case, the pump discharge flow rate Q becomes lower than the dischargeable flow rate Qo due to the characteristics of the pump. As a result, the rotation speed of the hydraulic motor is reduced, the crushing speed is reduced, and the product particle size after crushing may be larger than the target particle size. Furthermore, if the load becomes excessively large, the pump discharge pressure P may reach the relief pressure PR set by the relief valve to ensure the safety of the hydraulic circuit, and the hydraulic motor may stop and the crushing may stop. There is.
In addition, when the load is extremely increased, the crushing device may be damaged.

On the other hand, according to the feeder control device disclosed in Japanese Patent Application Laid-Open No. Hei 7-116541, when supplying waste (eg, concrete) having relatively low compressive strength, the load of the hydraulic motor due to the waste is small even with a large supply amount. There is a possibility that an excessive amount of waste may overflow from the crusher into the crushing chamber above the crusher without reducing the rotation speed of the hydraulic motor that drives the feeder. In general, in a crushing apparatus, particularly a jaw crusher, it is considered that about 80% of the input amount of the crushing chamber is the best for controlling the product particle size after crushing. In such a case, the product particle size after crushing is targeted. May be larger than the particle size.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems of the prior art, and has as its object the purpose of crushing which can always properly maintain the amount of waste supplied from the feeder to the crushing device regardless of the magnitude of the compressive strength of the waste. An object of the present invention is to provide a control device for a machine feeder.

[0010]

Means for Solving the Problems (1) In order to achieve the above object, the present invention provides a crushing device for crushing at least rocks and construction waste materials input from a hopper, and a crushing device using the crushing device. A crusher that is provided in a crusher having a conveyor for transporting the supplied rocks and construction waste materials and the like and a feeder for supplying the crushers with the rocks and construction waste materials input to the hopper, and controls the operation of the feeder. In the feeder control device, load detecting means for detecting the load of the crushing device, supply amount detecting means for detecting the amount of the rock, construction waste, etc. supplied to the crushing device, the load detecting means and the supply amount Speed control means for controlling an operation speed of the feeder according to a detection signal of the detection means.
When supplying rocks and construction waste materials having relatively high compressive strength from the feeder to the crushing device, the load on the crushing device increases even with a small supply amount. According to the present invention, the feeder operation speed is controlled by the speed control means in accordance with the detection signal of the load detection means, so that when the load of the crushing device exceeds a predetermined value, the feeder operation is decelerated or stopped to stop the crushing device. Since the supply of rocks, construction waste materials, and the like to the crusher can be reduced, it is possible to prevent the load on the crusher from becoming excessive. On the other hand, when supplying rock or construction waste having relatively low compressive strength to the crushing device from the feeder, the load on the crushing device does not increase even if the supply amount is large. However, according to the present invention, the speed control means controls the feeder operation speed in accordance with the detection signal of the supply amount detection means, so that the feeder operation is decelerated or reduced when the supply amount to the crushing device exceeds a predetermined amount. Since the supply of the rock and the construction waste to the crushing device can be eased by stopping the operation, it is possible to prevent the crushing device from being supplied with an excessively large amount of the rock and the construction waste. As described above, it is possible to always properly maintain the amount of waste supplied from the feeder to the crushing device regardless of the magnitude of the compressive strength of the waste.

(2) In the above (1), preferably,
The speed control unit includes an overload determination unit configured to determine whether a load of the crushing device detected by the load detection unit is equal to or greater than a first predetermined value; The operation of the feeder is performed when at least one of the oversupply determination unit and the overload determination unit and the oversupply determination unit that determines whether the amount of the construction waste material or the like has reached a predetermined amount or more is satisfied. Deceleration / stop signal output means for outputting a signal for decelerating or stopping the motor.

(3) In the above (2), more preferably, the deceleration / stop signal output means is in a state where at least one of the overload judgment means and the oversupply judgment means is satisfied. When the predetermined time has elapsed, a signal for decelerating or stopping the operation of the feeder is output. If the feeder is decelerated or stopped as soon as the judgments of the overload judgment means and the oversupply judgment means are satisfied and the supply of rocks, construction waste materials, etc. is decelerated or stopped, the load will decrease again or the supply amount will decrease immediately after this deceleration or stoppage. As a result, the overload state or the oversupply state is reduced, the feeder operation is restored, and there is a possibility that an unstable control state in which feeder stop and operation start are repeated thereafter. In the present invention, after the overload state and the oversupply state continue for the first predetermined time, the deceleration / stop signal output means outputs a signal for decelerating or stopping the operation of the feeder, so that the overload state and the overload state are output. Only when the supply state continues to some extent, the supply of rocks, construction waste, etc. is decelerated or stopped. Thereby, control stability can be improved.

(4) In the above (2), preferably, further comprising a variable displacement hydraulic pump, and a hydraulic actuator operated by pressure oil supplied from the hydraulic pump to drive the crushing device, The means is pressure detection means for detecting a load pressure of the hydraulic actuator, and the overload determination means is capable of discharging the load pressure detected by the pressure detection means changing according to a tilt angle of the hydraulic pump. It is determined whether or not the pressure has become equal to or higher than a reference pressure set near the limit discharge pressure at which the flow rate can flow. If the discharge pressure exceeds the limit, the discharge flow rate from the pump will decrease and the crushing speed of the crusher will decrease.Therefore, by setting the pressure near this limit discharge pressure as the reference pressure, the feeder is stopped reliably when the crushing speed decreases. can do.

(5) In the above (4), more preferably, the reference pressure is equal to or lower than the limit discharge pressure.

(6) In (4) above, preferably, the speed control means determines whether or not the load pressure detected by the pressure detection means has become equal to or higher than a relief pressure for protecting a hydraulic circuit. Having a load determining means, and
When the determination of the overload determination unit is satisfied and the determination of the abnormal load determination unit is not satisfied, an overload alarm unit that issues a warning around the crusher, and the determination of the abnormal load determination unit is satisfied. Abnormal load alarm means for issuing an alarm to the periphery of the crusher when the crusher operates. Thereby, the operator can distinguish and recognize the occurrence of the abnormal load and the occurrence of the overload.

(7) In the above (2), preferably, the speed control means further comprises: after the operation of the feeder is decelerated or stopped by a signal from the deceleration / stop signal output means, the overload determination means and A first return signal for outputting a signal for decelerating or returning the operation of the feeder to a state before deceleration or stoppage when the state in which the determination by the oversupply determination means is no longer satisfied continues for a second predetermined time. It has output means. When both the judgments of the overload judgment means and the oversupply judgment means are not satisfied, the overload state and the oversupply state have been eliminated. However, if the feeder operation is immediately resumed and the supply of rocks, construction waste, etc. is resumed, immediately after this supply starts, the load will increase again or the supply amount will become excessive, and the feeder will be decelerated or stopped. There is a possibility that an unstable control state (so-called hunting) that repeats the operation and deceleration or stop will occur. According to the present invention, the first return signal output means outputs a signal for restoring the operation of the feeder after the overload state and the state in which the oversupply state has been eliminated continue for a predetermined period of time. Even if the supply state is canceled, the feeder operation is not immediately resumed, and the supply of rocks, construction waste materials, and the like is restarted after a certain period of time. Thereby, control stability can be improved.

(8) In the above (2), preferably, after the operation of the feeder is decelerated or stopped according to a signal from the deceleration / stop signal output means, the speed control means includes the overload determination means and the overload determination means. When none of the determinations by the oversupply determination unit is satisfied again, it is determined whether the load of the crushing device detected by the load detection unit has become less than a second predetermined value that is smaller than the first predetermined value. There is provided a return load determining means, and a second return signal output means for outputting a signal for returning the operation of the feeder to a state before deceleration or stop when the determination of the return load determination means is satisfied. When both the judgments of the overload judgment means and the oversupply judgment means are not satisfied, the overload state and the oversupply state have been eliminated. However, if the feeder operation is immediately resumed and the supply of rocks, construction waste, etc. is resumed, the load increases again immediately after the start of the supply, and the feeder is decelerated or stopped. The control state may be unstable (so-called hunting). In the present invention, even if the load of the crushing device is less than the first predetermined value and the overload state is resolved, the return load determining means and the second return signal output means are less than the second predetermined value smaller than the first predetermined value. And then resume the feeder operation. As a result, even if the overload state and the oversupply state are resolved, the feeder operation is not immediately restored, and after a certain time delay, the supply of rocks, construction waste, etc. is restarted, thus improving control stability. can do.

(9) In the above (1), preferably, the load detecting means is a rotational speed detecting means for detecting a rotational speed of the crushing device.

(10) In the above (9), more preferably, the rotation speed detecting means detects a rotation speed of an actuator for driving the crushing device.

(11) In the above (7), preferably, an adjusting means for adjusting the second predetermined time is provided.

[0021]

An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a hydraulic circuit diagram of a hydraulic drive device provided with a feeder control device according to the present embodiment, and FIG. 2 is a side view illustrating an entire structure of a self-propelled crusher to which the feeder control device is applied. , FIG. 3 is FIG.
It is the side view which showed the internal structure in the state which removed some side members in the inside, and FIG. 4 is a figure showing the operation state during crushing work.

In FIG. 2 to FIG. 4, the self-propelled crusher 1 generally includes rocks, construction waste materials, etc. (grass) to be crushed by a working tool such as a bucket of a hydraulic shovel.
The hopper 2 into which the 5A is inserted, the jaw crusher 3 as a crushing device for crushing the inserted gala 5A into a predetermined size having a substantially V-shaped cross-sectional shape, and the jaw crusher 3 as the crusher 3A input from the hopper 2. Feeder 4, leading to
A conveyor 6 for transporting the scraps 5B crushed and reduced by the jaw crusher 3 to the front of the crusher 1, and a scraper 5B provided above the conveyor 6 and transported on the conveyor 6.
And a left and right crawler belts 9L and 9R provided below the crusher main body 8 (but viewed from the driver's seat 17). (Only the left side is shown).

The jaw crusher 3 is connected to a lower traveling body 10 by a frame 11 provided on the crusher main body 8.
As shown in FIG. 4, the moving teeth 3a are swung back and forth with respect to the fixed teeth 3b by a driving force generated by a hydraulic motor 24 (described later), and the
Is crushed to a predetermined size. The feeder 4 is provided below the hopper 2 and has a base 12 on which the waste 5A put into the hopper 2 is mounted, and a known horizontal reciprocating movement of the base 12 by a driving force generated by a hydraulic motor 23 (described later). And a base drive mechanism 13. The conveyor 6 drives the belt 14 by a hydraulic motor 25 (same as above), and thereby transports the waste 5B that has fallen onto the belt 14 from the jaw crusher 3. The magnetic separator 7 drives the belt 15 disposed above the belt 14 of the conveyor 6 so as to be substantially orthogonal to the belt 14 around a magnetic force generating means (not shown) by a hydraulic motor 26 so that the magnetic force is generated from the magnetic force generating means. The magnetic force acts on the belt 15 through the
Then, the conveyor 6 is transported in a direction substantially perpendicular to the belt 14 and dropped to the side of the belt 14. The crawler tracks 9L and 9R are respectively provided on the lower traveling body 10
And between the drive wheels 16L and 16R (only the left side is shown) and the idlers 18L and 18R (the same), and the left and right hydraulic pressures for traveling provided on the drive wheels 16L and 16R are provided. Motors 28L, 28R (only shown in FIG. 1)
The crusher 1 is made to travel by applying a driving force to the crusher 1. An operator's driver's seat 17 is provided on the crusher main body 8.
An operation panel 38 (see FIG. 5, described later) is installed in the control panel.

At the time of the crushing operation, as shown in FIG. 4, after the waste 5A put into the hopper 2 is guided to the jaw crusher 3 by the feeder 4 below the hopper 2 and crushed to a predetermined size. The crushed pieces 5B fall from the space below the jaw crusher 3 onto the conveyor 6 and are conveyed. During the conveyance, the magnetic material mixed into the pieces 5B by the magnetic separator 7 (for example, a reinforcing steel mixed in the concrete pieces). Pieces) are removed, and are finally carried out from the front part of the crusher 1 as crushed materials of almost the same size.

The hydraulic drive device shown in FIG. 1 is provided in the above-mentioned self-propelled crusher 1, and includes an engine 19 as a prime mover and a variable displacement first hydraulic pump 20 driven by the engine 19. And the second hydraulic pump 21
And a fixed displacement pilot pump 22 also driven by the engine 19, and the first and second hydraulic pumps 2
Six hydraulic motors 23, 24, 25, 26, 28L, 28R to which pressure oil discharged from 0, 21 is respectively supplied.
And four control valves 29, 30, 31, 3 for controlling the direction and flow rate of the hydraulic oil supplied from the first and second hydraulic pumps 20, 21 to the hydraulic motors 23 to 28.
2, left and right running control lever devices 33, 34 for switching left and right running control valves 30, 31 (described later) using the pilot pressure generated by the pilot pump 22, and the pilot pump 22. The control pressure based on the pilot pressure obtained is derived, and the first and second
The operator instructs the regulators 104 and 105 for adjusting the discharge flow rates of the hydraulic pumps 20 and 21 and the start / stop of the jaw crusher 3, the feeder 4, the conveyor 6, and the magnetic separator 7 provided in the driver's seat 17 of the crusher main body. It has the operation panel 38 for inputting.

The six hydraulic motors 23 to 28 include the feeder hydraulic motor 23 for generating a driving force for operating the feeder 4, the crushing hydraulic motor 24 for generating a driving force for operating the jaw crusher 3, and the operation of the conveyor 6. Conveyor hydraulic motor 25 for generating a driving force for driving the magnetic separation machine 7, hydraulic motor 26 for generating a driving force for operating the magnetic separator 7, and the left motor for generating a driving force to the left and right crawler tracks 9L and 9R.・
The right running hydraulic motors 28L and 28R are formed.

Each of the control valves 29 to 32 is a center bypass type switching valve, and includes a crushing control valve 29 connected to the crushing hydraulic motor 24 and the left running hydraulic motor 28L connected to the left running hydraulic motor 28L. For a light load device connected to the control valve 30, the right traveling control valve 31 connected to the right traveling hydraulic motor 28R, the feeder hydraulic motor 23, the conveyor hydraulic motor 25, and the magnetic separator hydraulic motor 26. And a control valve 32. At this time, throttles 100 and 101 are provided on conduits 109 and 110 for connecting the control valve 30 and the control valve 32 to the tank 69, respectively. Pressure sensors 102 and 103 for detecting pressures (negative control pressures P1 'and P2') generated by the pressure sensors are provided. Here, as described above, the control valves 29 to 32 are center bypass type valves, and the flow rate flowing through the center bypass pipe changes depending on the operation amount of each of the control valves 29 to 32. When each of the control valves 29 to 32 is neutral, that is, when the required flow rate to the hydraulic pumps 20 and 21 is small, most of the hydraulic oil discharged from the first hydraulic pump 20 and the second hydraulic pump 21 ,
Since it flows to 110, the negative control pressures P1 'and P2' increase. Conversely, when each of the control valves 29 to 32 is operated to be opened, that is, when the hydraulic pumps 20 and 21 are opened.
When the required flow rate is large, the flow rate flowing through the pipelines 109 and 110 is reduced by the flow rate flowing toward the actuator side, so that the negative control pressures P1 'and P2' decrease. In the present embodiment, as described later, the pressure sensor 102,
The swash plate 20 of the first and second hydraulic pumps 20 and 21 based on the fluctuations of the negative control pressures P1 'and P2'
The tilt angles of A and 21A are controlled (details will be described later).

The first hydraulic pump 20 of the first and second hydraulic pumps 20 and 21 is a crushing control valve 2.
The pressure oil for supplying to the crushing hydraulic motor 24 and the left traveling motor 28L is discharged through the control valve 9 and the left traveling control valve 30. At this time, the crushing control valve 29 and the left traveling control valve 3
0 is connected in parallel with each other. On the other hand, the second hydraulic pump 21 supplies the right traveling motor 28R, the feeder hydraulic motor 23, the conveyor hydraulic motor 25, and the magnetic separator hydraulic motor 26 via the right traveling control valve 31 and the light load device control valve 32. Pressure oil is discharged. At this time, the control valve 32 for the light load device and the control valve 31 for the right running are connected in parallel with each other.

Here, regarding the supply of hydraulic oil from the second hydraulic pump 21 to the hydraulic motor 23 for the feeder, the hydraulic motor 25 for the conveyor, and the hydraulic motor 26 for the magnetic separator through the control valve 32 for the light load equipment, the hydraulic motors 2
Three solenoid control valves 39, 40, 41 are provided for controlling the flow rates of the pressure oil supplied to 3, 25, 26, respectively, and these are connected in parallel with each other.
Correspondingly, pressure compensating valves 42, 43, and 44 (described later) are provided, respectively. Solenoid control valve 3
9, 40 and 41 are driving signals S from the controller 90.
m, Sco, and Sf (described later).
Variable throttles 39A, 40A, 41A that control the flow rate of the pressure oil supplied to the hydraulic motors 23, 25, 26 according to the opening degree
Are provided respectively. These solenoid control valves 3
When the drive signals Sm, Sco, Sf are turned on, the switches 9, 40, 41 are respectively switched to the communicating position (the lower position in FIG. 1), from the second hydraulic pump 21 to the light load device control valve 32 and the introduction line 53. Pressure oil led through
It supplies to and drives the corresponding hydraulic motors 23, 25, 26, respectively. Further, the drive signals Sm, Sco, Sf are OF
When the pressure reaches F, the springs 39B, 40B, and 41B return to the shut-off positions (upper positions in FIG. 1) with the restoring force, and the supply of the hydraulic oil from the second hydraulic pump 21 to the corresponding hydraulic motors 23, 25, and 26 is interrupted. And these hydraulic motors 2
3, 25, and 26 are connected to the lead-out line 54 to connect the hydraulic motor 2
The drive of 3, 25, 26 is stopped. Also, the variable throttle 39 of the solenoid control valves 39, 40, 41
Hydraulic motors 23, 2 downstream of A, 40A, 41A
Load detection line 4 for detecting load pressure of 5, 26
5, 46 and 48 are respectively connected. Among these, the load detection lines 46 and 48 are further connected to a load detection line 50 via a shuttle valve 49, and the load pressure on the high pressure side selected via the shuttle valve 49 is guided to the load detection line 50. It has become. In addition, the load detection line 50
The load detection line 45 is connected to the maximum load detection line 52 via the shuttle valve 51, and the load pressure on the high pressure side selected by the shuttle valve 51 is guided to the maximum load detection line 52 as the maximum load pressure. It has become. On the other hand, the load pressure detected by the load detection lines 45, 46, 48 is transmitted to one side of the corresponding pressure compensating valves 42, 43, 44 as the outlet pressure of each of the solenoid control valves 39, 40, 41. The pressure upstream of the solenoid control valves 39, 40, 41 is led to the other side of the pressure compensating valves 42, 43, 44, whereby the pressure compensating valves 42, 43, 44 are controlled by the solenoid control valves 39, 40. , 41 variable aperture 39A, 4
It operates in response to the differential pressure between 0A and 41A, and operates from the light load device control valve 32 to the feeder hydraulic motor 2.
3. Variable throttles 39A, 40A regardless of changes in the pressure in the introduction pipe 53 for introducing pressure oil to the hydraulic motor 25 for the conveyor and the hydraulic motor 26 for the magnetic separator and the load pressure of the hydraulic motors 23, 25, 26. , 41A can be maintained constant, and a flow rate corresponding to the degree of opening of the solenoid control valves 39, 40, 41 can be supplied to the corresponding hydraulic motor. In addition, the above-described introduction pipe 53 and the hydraulic motor 2
A pressure control valve 56 is provided in a pipe 55 that directly connects the outlet pipe 54 that guides the pressure oil discharged from 3, 25, and 26 to the control valve 32 for light load equipment. The maximum load pressure is guided to one side of the pressure control valve 56 via the above-described maximum load detection pipe 52, and the pressure in the upstream pipe 55 is connected to the other side of the pressure control valve 56. Has been led. Thus, the pressure control valve 56 increases the pressure in the downstream pipe line 55 by the set pressure of the spring from the maximum load pressure.

The control valve 29 for crushing, left
Each of the right traveling control valves 30 and 31 and the light load device control valve 32 is a pilot operation valve that is operated using the pilot pressure generated by the pilot pump 22. Control valve for crushing 2
9 is connected to the pilot lines 5
Pilot pressures from the pilot pump 22 are guided through 8, 59, respectively. These pilot lines 58,
The 59 is provided with a solenoid control valve 60 driven by a drive signal Scr from a controller 90. The solenoid control valve 60 is switched in response to the input of the drive signal Scr, and changes the pilot pressure to the pilot lines 58 and 5.
Nine. That is, when the drive signal Scr is turned ON, the solenoid control valve 60 is switched to the communication position, that is, the right position (or the left position) in FIG. 1, and the pilot pressure from the pilot pump 22 is applied to the pilot line 58 (or 59). Drive unit 29a (or 29b)
The crushing control valve 29 is thereby switched to the upper position (or lower position) in FIG. 1, and the crushing hydraulic motor 24 is driven in the forward (or reverse) direction. When the drive signal Scr is turned off, the solenoid control valve 60 is in the neutral position, shuts off the pilot pressure from the control valve 22, and sets the pilot line 58
And 59 are connected to a tank 69 so that their pressure equals the tank pressure. Thereby, the crushing control valve 29 returns to the neutral position, and the crushing hydraulic motor 24 stops. The left and right traveling control valves 30 and 31 are operated by pilot pressure generated by the pilot pump 22 and reduced to a predetermined pressure by operation lever devices 33 and 34. That is, the operation lever device 3
Each of the control levers 3 and 34 includes operation levers 33a and 34a and pressure reducing valves 33b and 34b that output a pilot pressure according to the operation amounts of the operation levers 33a and 34a. When the operation lever 33a of the operation lever device 33 is operated in the direction a (or the opposite direction) in FIG. 1, the pilot pressure causes the driving portion 30a (or the driving unit 30a (or the driving unit 30a) of the control valve 30 for the left traveling to pass through the pilot line 61 (or 62). 30b), whereby the left traveling control valve 30 is switched to the upper position (or lower position) in FIG. 1, and the left traveling hydraulic motor 28L is driven in the forward (or reverse) direction. Similarly, the operation lever 34a of the operation lever device 34 is
When operated in the direction (or the opposite direction), the pilot pressure is guided to the drive unit 31a (or 31b) of the right travel control valve 31, and the pilot pressure is moved to the upper position (or lower position) in FIG.
And the right traveling hydraulic motor 28R is driven in the forward (or reverse) direction. The light-load device control valve 32 includes a drive unit 32a,
The pilot pressure from the pilot pump 22 is led to the pilot line 32b via the pilot lines 65 and 66, respectively.
As in the pilot lines 58 and 59 of the crushing control valve 29, the pilot lines 65 and 66 are provided with a solenoid control valve 68 that can be switched by a drive signal Sl (described later) from a controller 90. That is, when the drive signal Sl is turned on, the solenoid control valve 68 is switched to the communication position (the right position in FIG. 1), and the pilot pressure from the pilot pump 22 is changed to the pilot line 65.
To the drive unit 32a through which the control valve 32 for the light-load device is in the shut-off position (upper position in FIG. 1).
To supply hydraulic oil from the second hydraulic pump 21 to an introduction pipe 53 that introduces hydraulic oil to the feeder hydraulic motor 23, the conveyor hydraulic motor 25, and the magnetic separator hydraulic motor 26. When the drive signal Sl is turned off, the spring 6
With the restoring force of 8A, the solenoid control valve 68 returns to the left position in FIG. 1, shuts off the pilot pressure from the control valve 22, connects the pilot lines 65 and 66 to the tank 69, and reduces the pressure to the tank pressure. Equal to Thereby, the control valve 32 for the light load device is
Returns to the neutral position.

The regulators 104 and 105 have cylinders 35 and 36 for input torque limit control and cylinders 107 and 109 for negative control. These cylinders 35, 36, 107, and 109 have pistons 35A, 36A, 107A, and 109A, respectively. When the pistons 35A, 36A, 107A, and 109A move rightward in FIG. Hydraulic pumps 20, 20 so that the discharge flow from
The tilt angles (ie, pump displacement volumes) of the swash plates 20A, 21A of the piston 21 are changed, and the pistons 35A, 36A, 107
A and 109A move to the left in FIG.
The tilt angles of the swash plates 20A, 21A are changed so that the discharge flow rates from the hydraulic pumps 20, 21 increase. On the bottom side of the cylinders 35, 36, 107, 109, a control pressure based on the pilot pressure from the pilot pump 22 is applied to the pilot lines 70a, 71a, 70.
When the control pressure is high, the pistons 35A, 36A, 107A, and 109A move rightward in FIG. 1 to cause the first and second hydraulic pumps 20, 2 to move.
When the control flow is low and the control pressure is low, the pistons 35A, 36A, 107A and 109A move to the left in FIG. 1 to increase the discharge flow. At this time, the cylinders 35, 36, 1
07, 109 to pilot lines 70a, 71a, 70
b and 71b include the drive signal S from the controller 90.
Solenoid control valves 72, 73, 106, and 108 driven by 1, S2, S3, and S4 (described later) are provided, and these solenoid control valves 72, 73, 106, and
108 connects the pilot pipelines 70a, 71a, 70b, 71b in accordance with the output current values of the drive signals S1, S2, S3, S4. That is, the solenoid control valves 72, 73,
The control pressures supplied to the cylinders 35, 36, 107, 109 are increased by connecting the pilot pipelines 70a, 71a, 70b, 71b with a larger opening degree as the output current value increases, and the output current value increases. Becomes zero, the pilot lines 70a, 71a, 70b, 71b are shut off, and the control pressure supplied to the cylinders 35, 36, 107, 109 becomes zero.

For the solenoid control valves 72, 73 related to the input torque limiting control cylinders 35, 36, the controller 90 controls the discharge pressures P1, P1 of the first and second hydraulic pumps 20, 21 as described later. The output current value of the drive signals S1 and S2 increases as P2 increases. Thereby, the first and second hydraulic pumps 20, 2
When the first discharge pressures P1 and P2 exceed a predetermined pressure, the discharge flow rates of the first and second hydraulic pumps 20 and 21 are limited, and the load of the first and second hydraulic pumps 20 and 21 reduces the output torque of the engine 19. The tilting of the swash plates 20A and 21A is controlled so as not to exceed (the known input torque limiting control).

On the other hand, the negative control cylinder 106,
The following control is performed for the solenoid control valves 107 and 109 related to 108. That is, when the negative control pressures P1 and P2 detected by the pressure sensors 102 and 103 are high, the controller 90 decreases the output current values of the drive signals S3 and S4 for the solenoid control valves 106 and 108 as described later. On the other hand, when the negative control pressures P1 and P2 are low, the solenoid control valve 10
The output current value to 6,108 is increased. This allows
As the required flow rate to the first and second hydraulic pumps 20 and 21 decreases, the discharge flow rate of the first and second hydraulic pumps 20 and 21 decreases, and as the required flow rate to the first and second hydraulic pumps 20 and 21 increases, The so-called negative control for increasing the discharge flow rates of the first and second hydraulic pumps 20 and 21 is performed.

The three hydraulic pumps 20, 21, 22
Are provided with relief valves (not shown), respectively, and the first and second hydraulic pumps 20, 21
Is detected by pressure sensors 78 and 79 provided in a pipe branching from the discharge pipe, and a detection signal is input to the controller 90.

FIG. 5 shows a detailed structure of the operation panel 38. The "interlocking mode" for starting and stopping the jaw crusher 3, the feeder 4, the conveyor 6, and the magnetic separator 7 in association with each other, Dial-type mode selection switch 80 for selecting a “single-action mode” for starting and stopping the motor independently of each other, and a start / stop target when the single-action mode is selected with the mode selection switch 80 Dial-type device selection switch 81 for selecting a device to be set
Mode selection switch 80 and device selection switch 81
A start button 82 and a stop button 83 that can be used in common when any of the above items are selected, and an emergency stop button 84 for emergency stop of all devices are provided. The operation panel 38 has an adjustment switch 11 for adjusting a return time described later.
1 and an instruction switch 112 for instructing the maximum tilt angle.

FIG. 6 shows the function of the controller 90, which includes a pump control unit 90a, a device control unit 90b, a negative control unit 90c, and a feeder control unit 90d.

The pump control unit 90a includes a function generator 90a
1, 90a2, and these function generators 90a1,
90a2 is a pressure sensor 7 based on the illustrated table.
The first and second hydraulic pumps 20,2 detected at 8,79
Drive signals S1, S2 to the solenoid control valves 72, 73 for performing the input torque limiting control according to the discharge pressures P1, P2 and the maximum tilt angle instruction signal from the instruction switch 112.
Generates S2.

The negative control unit 90c includes a function generator 90
c1 and 90c2, and these function generators 90c
1, 90c2 is a pressure sensor 1 based on the illustrated table.
Drive signals S to the solenoid control valves 106 and 108 according to the negative control pressures P1 'and P2' detected at 02 and 103, respectively.
3. Generates S4.

The device control unit 90b generates the drive signals Sm, Sco, Sf, Scr, Sl based on the operation signals of the operation panel 38, and the corresponding solenoid control valves 39, 40, 41,
Output them to 60 and 68. That is, when the "running mode" is selected by the mode selection switch 80 of the operation panel, the drive signals Sf, Scr, Sco, and Sm of the solenoid control valves 41, 60, 40, and 39 are sequentially turned off, and the feeder 4, Jaw crusher 3, conveyor 6, and magnetic separator 7
Are sequentially stopped, the drive signal Sl of the solenoid control valve 68 is turned off, and the control valve 3 for the light load device is turned off.
2 to the neutral position, and the feeder hydraulic motor 23,
Conveyor hydraulic motor 25 and magnetic separator hydraulic motor 2
6 cannot be driven. Then, the drive signal St of the solenoid control valve 64 is turned on to switch to the communication position, and the operation of the control valves 30, 31 by the operation lever devices 33, 34 is enabled. When the “single-acting mode” is selected by the mode selection switch 80 on the operation panel, the drive signal St of the solenoid control valve 64 is turned off to return to the shut-off position, and the control valve for traveling by the operation lever devices 33 and 34 is used. Operation of 30, 30 is made impossible. Further, the control signal 32 for the light load device is switched by turning on the drive signal Sl of the solenoid control valve 68 to supply the pressure oil from the second hydraulic pump 21 to the introduction line 53. Thereafter, the device selection switch 81 of the operation panel 38
When any one of the jaw crusher, feeder, conveyor, and magnetic separator is selected and the start button 82 is turned on, the solenoid control valves 60, 41, 40, and 3 are correspondingly operated.
9, the drive signals Scr, Sf, Sco, Sm are turned ON, and the corresponding hydraulic motors 24, 23, 25, 26 are driven to start the respective devices. On the other hand, when the stop button 83 is turned on, the drive signals Scr, Sf, Sco, Sm of the solenoid control valves 60, 41, 40, 39 are turned off in accordance with the selection of the device selection switch 81 at that time, The corresponding hydraulic motors 24, 23, 25, 26 are stopped, and each device is stopped. "Interlocked mode" with the mode selection switch 80 on the operation panel
Is selected, as described above, the solenoid control valve 6
8 to turn on the drive signal Sl and supply the pressure oil from the second hydraulic pump 21 to the introduction pipe 53, and then drive the drive signals Sm, Sco, Scr, of the solenoid control valves 39, 40, 60, 41.
Sf is sequentially turned on in this order to turn on the hydraulic motor 2 for the magnetic separator.
6, hydraulic motor 25 for conveyor, hydraulic motor 2 for crushing
4. The feeder hydraulic motor 23 is sequentially driven to start all the devices in the order of the magnetic separator 7, the conveyor 6, the jaw crusher 3, and the feeder 4. On the other hand, when the stop button 83 is turned on, the solenoid control valves 41, 60,
These are sequentially turned OFF in the order of the drive signals Sf, Scr, Sco, Sm of 40, 39, and the feeder 4, the jaw crusher 3, the conveyor 6, and the magnetic separator 7 are sequentially stopped in this order.

The above-described hydraulic drive device is provided with the feeder control device according to the present embodiment. The feeder control device includes pressure sensors 85a and 85b (see FIG. 1) as pressure detecting means for detecting a load pressure of the crushing hydraulic motor 24, and a supply amount detecting means for detecting an amount of rattle supplied to the jaw crusher 3. A level sensor (photoelectric sensor) 87 (see FIG. 1 and FIG. 7 described later), the feeder control unit 90d provided in the controller 90 (see FIG. 6), and the adjustment switch 11 provided in the operation panel 38.
1 is formed.

The pressure sensors 85a and 85b are provided in pressure oil supply lines 86a and 86b to the crushing hydraulic motor 24, respectively, and the load pressures PCL1 and PCL2 of the crushing hydraulic motor 24 are provided.
Function as load detecting means for indirectly detecting the load on the jaw crusher 3. These detection signals are input to the feeder control unit 90d.

The installation position of the photoelectric sensor 87 will be described with reference to FIG. FIG. 7 is an enlarged view showing the structure in the vicinity of the jaw crusher 3, and the portion A in FIG.
It is a figure which substantially corresponds to the middle B part. In FIG. 7, a photoelectric sensor 87 is inserted and installed in a through hole formed in an upper chute 88 above the jaw crusher 3, and, like a known sensor of this type, for example, a light emitting device and a light receiving device are connected. It is provided so as to be substantially horizontally opposed, and when the amount of the glass supply becomes excessive and the glass 5A overflows from the jaw crusher 3 to the upper chute 88, the light from the light emitter is cut off and does not reach the light receiver. Thereby, it is detected that the supply amount of the waste 5A has reached the level of the installation position. This detection signal X is based on the load pressure PCL.
1. Like PCL, feeder control unit 90 of controller 90
d.

Returning to FIG. 6, the feeder control section 90d starts the control function when the drive signal Sf of the solenoid control valve 41 is turned on by the equipment control section 90b, and is controlled by the pressure sensors 85a and 85b. Based on the detected load pressures PCL1 and PCL and the detection signal X detected by the photoelectric sensor 87, the drive signal Sf from the device control unit 90b to the solenoid control valve 41 is appropriately corrected and changed, and the feeder hydraulic motor is adjusted. 23 is controlled. FIG. 8 is a flowchart showing the control contents. In FIG. 8, when the drive signal of the solenoid control valve 41 is turned ON by the device control unit 90b, this flow starts. First, in step S100, the flag is initialized to 0. This flag is used as an index indicating whether or not the feeder 4 is once decelerated or stopped by deceleration or stop control described later.

Next, in step S103, an instruction signal from an instruction switch 112 for appropriately setting the value of the maximum tilt angle of the first hydraulic pump 20 according to the work content and the like is input. Then, in step S105, step S10
Based on the instruction signal input in step 3, the first hydraulic pump 20 described with reference to FIG. 10 calculates the limit pressure PD at which the dischargeable flow rate Qo can flow.

Next, in step S110, the pressure sensor 8
The load pressures PCL1 and PCL2 detected at 5a and 85b and the mottle detection signal X detected by the photoelectric sensor 87 are input.
Then, in step S120, it is determined whether or not the jaw crusher 3 is in an overload state based on the load pressures PCL1 and PCL2 input in step S110. Specifically, it is determined whether one of PCL1 and PCL2 is equal to or greater than the pressure set near the limit pressure PD calculated in step S105, for example, 0.8PD. The reason for using this 0.8PD is as follows. That is, if the discharge pressure P1 of the first hydraulic pump 20 exceeds the limit discharge pressure PD, the discharge flow rate Q decreases and the crushing speed of the jaw crusher 3 decreases. By setting the pressure having a margin as the reference pressure and operating the feeder 4 only when the pressure is lower than the reference pressure, the feeder 4 can be reliably stopped when the crushing speed decreases. If PCL1, PCL2 <0.8PD, it is determined that the vehicle is not in an overload condition, and the routine goes to Step S130. In step S130, it is determined whether or not the jaw crusher 3 is in an oversupply state of the waste based on the waste detection signal X input in step S110. Gala detection signal X is OFF
If it is a signal (a signal indicating that the uppermost part of the glass does not reach the same level as the installation position of the photoelectric sensor 87), it is determined that the state is not the oversupply state, and the process proceeds to step S140. In step S140, it is determined whether the flag is 0. If the feeder 4 is not in the decelerating or stopping state, the flag is 0, so that this determination is satisfied, the process returns to step S110, and the same procedure is repeated until the jaw crusher 3 becomes overloaded or oversupplied.

(1) In the case of overload state As described above, steps S110 to S140
If the jaw crusher 3 is in an overload state while repeating (i.e., PCL1 or PCL2≥0.8PD), the determination in step S120 is satisfied, and the routine goes to step S150.

In step S150, step S110
It is determined whether or not the jaw crusher 3 is in an abnormal load state in which the jaw crusher 3 is higher than the overload state, based on the load pressures PCL1 and PCL2 input in the step (1). Specifically, based on the relief pressure PR described with reference to FIG. 10, it is determined whether any of PCL1 and PCL2 is equal to or higher than PR. PCL1,
If PCL2 <PR, it is determined that the vehicle is in the overload state but not in the abnormal load state, and step S1 is executed.
Go to 60.

In step S160, it is determined whether this overload state has continued for a first predetermined time. If it has not continued for the first predetermined time, the determination is not satisfied and the procedure returns to step S110 to repeat the same procedure. If it has continued for the first predetermined time, the procedure moves to step S170.

In step S170, an instruction signal is output to an unillustrated overload alarm means (for example, a patrol light) to generate an overload alarm. Thereby, it is possible to notify the operator of the overload state.

Thereafter, in step S180, feeder 4
Decrease or stop the operation speed of Specifically, the ON signal of the drive signal Sf input from the device control unit 90b is replaced with an OFF signal, the solenoid control valve 41 is switched to the shut-off position, and the feeder hydraulic motor 23 is stopped, or the drive signal Sf Is gradually reduced to gradually return the solenoid control valve 41 to the shut-off position, and the feeder hydraulic motor 23 is operated at an extremely low speed close to stop.

Then, in step S190, the flag is reset to 1 indicating that the feeder 4 has once decelerated or stopped, and the process returns to step S110.

(2) Case of Oversupply If the jaw crusher 3 is in an oversupply state while repeating steps S110 to S140 (that is, the detection signal X indicates that the uppermost part of the 8
7), the determination in step S130 is satisfied, and
Move to step S160.

Thereafter, similar to the above (1), step S
After step 170, the feeder hydraulic motor 23 is stopped or decelerated in step S180, and the flag is set to 1 in step S190.
Then, the process returns to step S110, and the same procedure is repeated.

(3) When the overload state and the oversupply state are resolved The jaw crusher 3 is operated while the steps S110 to S190 are repeated in the overload state or the oversupply state as described in (1) or (2). When both the over-supply state and the over-load state are eliminated (that is, PCL1, PCL2 <
If 0.8PD and X is an OFF signal), the determinations in steps S120 and S130 are not satisfied, and the routine goes to step S140.

Then, it is determined whether or not the flag is 0 in step S140. However, since the flag is set to 1 in step S190 after the feeder stops, this determination is not satisfied, and the process proceeds to step S200.

In step S200, it is determined whether this oversupply / overload elimination state has continued for a second predetermined time. If it has not continued for the second predetermined time, the determination is not satisfied and the procedure returns to step S110 to repeat the same procedure. If it has continued for the second predetermined time, the procedure moves to step S210.

In step S210, the operation speed of the feeder 4 is reduced or returned to the state before the stop. Specifically, the drive signal Sf input from the device control unit 90b
Is output to the solenoid control valve 41 as it is, and the solenoid control valve 41 is switched to the original position, and the feeder hydraulic motor 23 is returned to the original operation speed.

Then, in step S220, the flag is set to 0.
And returns to step S110.

Note that the second predetermined time set in step S200 is an adjustment switch 111 as an adjusting means for adjusting the return time provided on the operation panel 38 shown in FIG.
Can be arbitrarily adjusted according to the instruction signal from.

(4) Case of Abnormal Load State When the jaw crusher 3 enters an abnormal load state for some reason during the above-described procedure (ie, when PCL1 or PCL2 ≧ PR). Is the step S
If the determinations in step 120 and step S150 are satisfied, the process proceeds to step S230, in which an instruction signal is output to an abnormal load alarm unit (not shown, for example, a patrol light of a different color from the overload alarm unit) to generate an abnormal load alarm. With
Stop the feeder and crusher. Thus, the operator can be notified of the abnormal load state, and by separately providing the overload alarm means and the abnormal load alarm, the operator can distinguish the occurrence of the abnormal load from the occurrence of the overload. Can be recognized.

In the above, the feeder control section 90d of the controller 90 constitutes speed control means for controlling the operation speed of the feeder according to the detection signals of the load detecting means and the supply amount detecting means.

Further, regarding the control executed by the feeder control section 90d, 0.8PD used in step S120 forms a reference pressure near a limit discharge pressure at which a dischargeable flow rate can flow, and also forms a first predetermined value. . Step S120 constitutes means for determining whether or not the discharge pressure detected by the pressure detection means has become equal to or higher than the reference pressure,
Further, an overload judging means for judging whether or not the load of the crusher detected by the load detecting means is equal to or more than a first predetermined value is also configured. Further, step S130 constitutes oversupply determining means for determining whether or not the amount of rocks, construction wastes, and the like detected by the supply amount detecting means has exceeded a predetermined amount. Steps S160 and S180 include overload determination. When the determination by the means or the oversupply determining means is satisfied, a deceleration / stop signal output means for outputting a signal for decelerating or stopping the operation of the feeder is configured. Step S150 constitutes an abnormal load determining means for determining whether or not the discharge pressure detected by the pressure detecting means is equal to or higher than a relief pressure for protecting the hydraulic circuit. Further, in steps S200 and S210, after the operation of the feeder is decelerated or stopped by the signal from the deceleration / stop signal output unit, the state in which the determinations of the overload determination unit and the oversupply determination unit are no longer satisfied is satisfied. When the second predetermined time is continued, a first return signal output means for outputting a signal for returning the operation of the feeder to a state before deceleration or stop is configured.

The operation and operation of the present embodiment configured as described above will be described below.

At the time of the crushing operation, all devices are started in the interlock mode or the single action mode.

When starting all devices in the interlocking mode, the operator operates the mode selection switch 8 on the operation panel 38.
Set 0 to “interlock” and press the start button 82. Thereby, the magnetic separator 7, the conveyor 6, the jaw crusher 3, and the feeder 4 can be sequentially started in this order. When starting all devices in single-acting mode, the operator
The procedure of setting the mode selection switch 80 of the operation panel 38 to "single action" and then pressing the start button 82 in accordance with the device to be started by the device selection switch 81 is performed by the magnetic separator 7, the conveyor 6, the jaw crusher 3, and the feeder 4. The order is as follows.
Thus, as described above, the magnetic separator 7, the conveyor 6, the jaw crusher 3, and the feeder 4 can be started in this order.

In such a crushing operation, the waste 5A put into the hopper 2 is guided to the jaw crusher 3 by the feeder 4 and crushed to a predetermined size. Here, the feeder 4 generates a waste 5A having a relatively large compressive strength.
When supplying (for example, rock) to the jaw crusher 3, the load on the jaw crusher 3 increases. In this embodiment, the detection signals PCL1 and PCL1 of the pressure sensors 85a and 85b are used.
The operation speed of the feeder hydraulic motor 23 is controlled by the feeder control unit 90d according to PCL2, and when the load on the jaw crusher 3 exceeds a predetermined value, the hydraulic motor 23 is decelerated or stopped to stop the jaw crusher 3. Since the supply of the rag 5A can be reduced, it is possible to prevent the load on the jaw crusher 3 from becoming excessive. Here, in the case where the loose 5A (for example, concrete) having a relatively small compressive strength is supplied from the feeder 4 to the jaw crusher 3, the load on the jaw crusher 3 does not increase. However, in the present embodiment, the feeder control unit 90d controls the operation speed of the feeder hydraulic motor 23 according to the detection signal X of the photoelectric sensor 87, and when the supply amount to the jaw crusher 3 becomes equal to or more than a predetermined amount. Since the supply of the rattle 5A to the jaw crusher 3 can be reduced by decelerating or stopping the hydraulic motor 23, it is possible to prevent an excessive amount of the rattle 5A from being supplied to the jaw crusher 3.

On the other hand, when decelerating or stopping the feed of the waste 5A by the feeder 4 in such an overload state or oversupply state, the feeder 4 is decelerated or stopped immediately after the overload state or the oversupply state is reached. When the supply is decelerated or stopped, immediately after this deceleration or stop, the load is reduced again or the supply amount is reduced, the overload state or the oversupply state is eliminated, and the operation of the feeder 4 is restored. An unstable control state (so-called hunting) that repeats the operation start may occur. In the present embodiment, in steps S160 and S180, a signal for decelerating or stopping the operation of the feeder 4 is output after the overload state and the oversupply state continue for the first predetermined time, so that the overload state is output. Only when the oversupply state continues to some extent, the supply of the waste 5A is stopped. This allows
Control stability can be improved. Similarly, when the overload determining means and the oversupply determining means are both eliminated and the supply operation of the feeder 4 is restored, the feeder 4 is immediately returned and the supply of the waste 5A is restarted.
Immediately after that, the load increases again or the supply amount becomes excessive, so that the feeder 4 may be decelerated or stopped, and hunting may similarly occur. In the present embodiment, in steps S200 and S210, a signal for returning the operation of the feeder 4 after the overload and the oversupply have been eliminated for a second predetermined time set by the adjustment switch 111 is output. By outputting, even if the overload state and the oversupply state are resolved, the operation of the feeder 4 is not immediately resumed, but the supply of the waste 5A is restarted after a certain duration. This also improves control stability.

As described above, according to the present embodiment, it is possible to always properly maintain the amount of rattle supplied from the feeder 4 to the jaw crusher 3 regardless of the magnitude of the compressive strength of the rattle 5A.

In the above-described embodiment, in order to prevent hunting when the feeder 4 returns, as described above, it is determined in step S200 whether the overload / oversupply state has been eliminated for the second predetermined time. Although the determination is made, the determination is not limited to this, and another determination may be made regarding the elimination of the overload state. This modification will be described with reference to FIG. FIG.
FIG. 14 is a flowchart showing control contents of a feeder control unit 90d in this modification, and is a diagram corresponding to FIG. 8 of the embodiment. In FIG. 9, step S2 of FIG.
Step S201 is provided instead of 00, and Step S11
Based on the load pressures PCL1 and PCL2 input at 0, it is determined whether or not the jaw crusher 3 has become less than a certain return reference load. Specifically, a second predetermined value lower by 0.8P than 0.8PD used in step S120 is set as the return load, and it is determined whether any of PCL1 and PCL2 is less than the return load. If the determination is not satisfied, the process returns to step S110, and if the determination is satisfied, the process proceeds to step S210 and subsequent steps, as in the above embodiment.

In the above description, after the operation of the feeder 4 is decelerated or stopped by the signal from the deceleration / stop signal output means in step S201, both the judgments of the overload judgment means and the oversupply judgment means are no longer satisfied. In case,
The return load determining means determines whether the load of the crusher detected by the load detecting means is less than a second predetermined value that is smaller than the first predetermined value. Feeder 4
A second return signal output means for outputting a signal for returning the operation to the state before deceleration or stop. According to this modification as well, an effect of preventing hunting in returning the feeder 4 can be obtained.

In the above embodiment, the instruction switch 112 for instructing the maximum tilt angle of the first hydraulic pump 20 is used.
Is provided on the operation panel 38 and the limit pressure PD is calculated based on this signal. However, the maximum tilt angle may be set in advance to a predetermined angle so that the limit pressure PD is uniquely determined. In this case, it is not necessary to calculate the instruction switch 112 and the limit pressure PD.

In the above embodiment, the reference pressure for judging the overload condition is 0.8 times the limit pressure PD at which the first hydraulic pump 20 can flow the dischargeable flow rate Qo, that is, 0.8 PD. , But not limited to this, from PD to several M
The pressure Pa may be set lower. In this case, a similar effect is obtained.

Further, in the above embodiment, the photoelectric sensor 87 is connected to the upper chute 88 above the jaw crusher 3.
The jaw crusher 3 may be provided on the side plate 3c (see FIG. 7). In this case, a similar effect is obtained.

In the above embodiment, the pressure sensors 85a and 85b for detecting the load pressure of the crushing hydraulic motor 24 are used as the load detecting means. However, the present invention is not limited to this. That is, a rotation speed sensor for detecting the rotation speed of the hydraulic motor 24 may be provided, and when the rotation speed falls below a certain value, it may be determined that an overload has occurred. The rotation speed sensor may detect the rotation speed of a member rotated by the hydraulic motor 24, for example, the flywheel 89. Furthermore, although the hydraulic motor 24 is used as an actuator for driving the jaw crusher 3, the actuator is not limited to this, and may be an electric motor. In this case, as load detection means,
A rotation speed sensor for detecting the rotation speed of the electric motor may be used, or an ammeter for detecting the current value of the electric motor may be used. In the case of using an ammeter, it is sufficient to determine that an overload has occurred when the current value exceeds a certain value. In these cases, a similar effect is obtained.

Further, in the above-described embodiment, the crusher provided with the jaw crusher 3 for crushing the moving teeth 3a and the fixed teeth 3b as the crushing device has been described as an example. However, the crushing device is not limited to this. For example, a rotary crusher (a so-called roll) that crushes a roll-shaped rotating body having a crushing blade attached thereto as a pair, rotating the pair in opposite directions to each other, and sandwiching the lashes between the rotating bodies. It is also applicable to a crusher equipped with a crusher. In this case, the feeder 4 may be omitted. Further, in this case, the above-mentioned rotation speed sensor may detect the rotation speed of the rotary crushing device, and determine that an overload has occurred when the rotation speed falls below a certain value. In these cases, a similar effect is obtained.

In the above embodiment, the feeder 4, the jaw crusher 3, the conveyer 6, and the magnetic separator 7 are provided as devices related to the crushing operation. The magnetic separator 7 may be omitted as appropriate. In addition to these four, an auxiliary conveyor for extending the path of the conveyor 6 is provided on the downstream side (or upstream side) of the conveyor 6, and a vibrating screen for performing sorting according to the grain size of the jaw is provided with a jaw crusher. 3 may be provided on the downstream side. In these cases, a similar effect is obtained.

[0077]

According to the present invention, when the load of the crushing device exceeds a predetermined value, the feeder operation is decelerated or stopped to reduce the supply of rocks and construction waste materials to the crushing device, and the crushing is performed. When the supply amount to the apparatus becomes equal to or more than a predetermined amount, the feeder operation is decelerated or stopped, and the supply of rocks, construction waste materials, and the like to the crushing apparatus can be reduced. Irrespective of the magnitude of the compressive strength of the glass, the amount of the glass supplied from the feeder to the crusher can always be properly maintained.

[Brief description of the drawings]

FIG. 1 is a hydraulic circuit diagram of a hydraulic drive device provided with a feeder control device according to the present embodiment.

FIG. 2 is a side view illustrating the entire structure of a self-propelled crusher to which the feeder control device is applied.

FIG. 3 is a side view showing an internal structure in a state where a side member in FIG. 2 is partially removed.

FIG. 4 is a diagram illustrating an operation state during a crushing operation.

FIG. 5 is a diagram showing a detailed structure of an operation panel.

FIG. 6 is a block diagram illustrating functions of a controller.

FIG. 7 is an enlarged view showing a structure near a jaw crusher.

FIG. 8 is a flowchart illustrating control contents by a feeder control unit.

FIG. 9 is a flowchart illustrating control contents of a feeder control unit in a modified example.

FIG. 10 is a diagram showing general characteristics of a hydraulic pump that supplies pressure oil for driving a hydraulic motor.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Self-propelled crusher 2 Hopper 3 Jaw crusher (crushing device) 4 Feeder 5A, B Gala (rock, construction waste material, etc.) 6 Conveyor 85a, b Pressure sensor (pressure detection means, load detection means) 87 Photoelectric sensor (supply amount) Detection means) 90 controller 90d feeder control unit (speed control means)

Claims (11)

[Claims] Claims: 1. At least a rock introduced from a hopper.
It has a crushing device for crushing construction waste material, etc., a conveyor for transporting rock, construction waste material, and the like crushed by the crushing device, and a feeder for supplying the rock, construction waste material, and the like input to the hopper to the crushing device. In a feeder control device of the crusher provided in the crusher and controlling the operation of the feeder, load detection means for detecting a load of the crusher, and an amount of the rock, construction waste material, and the like supplied to the crusher. A feeder control device for a crusher, comprising: a supply amount detecting means for detecting; and a speed control means for controlling an operation speed of the feeder according to detection signals of the load detecting means and the supply amount detecting means. 2. A crusher feeder control device according to claim 1, wherein said speed control means determines whether or not the load of said crusher detected by said load detection means has become equal to or greater than a first predetermined value. Overload determination means, overload determination means for determining whether the amount of the rock, construction waste, etc. detected by the supply amount detection means has reached a predetermined amount or more, and overload determination means and oversupply determination means. A feeder control device for a crusher, comprising: a deceleration / stop signal output unit that outputs a signal for decelerating or stopping the operation of the feeder when at least one of the determinations is satisfied. 3. A feeder control device for a crusher according to claim 2, wherein said deceleration / stop signal output means is in a state in which at least one of said overload judgment means and said oversupply judgment means is satisfied. A feeder control device for a crusher, which outputs a signal for decelerating or stopping the operation of the feeder when the first predetermined time has elapsed. 4. The crusher feeder control device according to claim 2, further comprising: a variable displacement hydraulic pump; and a hydraulic actuator that is operated by pressure oil supplied from the hydraulic pump and drives the crusher. The load detecting means is:
Pressure detecting means for detecting a load pressure of the hydraulic actuator, wherein the overload determining means flows a dischargeable flow rate at which the load pressure detected by the pressure detecting means changes according to the tilt angle of the hydraulic pump. A feeder control device for a crusher, which determines whether or not a reference pressure set near a limit discharge pressure to be obtained is equal to or higher than a reference pressure. 5. The crusher feeder control device according to claim 4, wherein said reference pressure is equal to or lower than said limit discharge pressure. 6. The crusher feeder control device according to claim 4, wherein said speed control means determines whether or not the load pressure detected by said pressure detection means is equal to or higher than a relief pressure for protecting a hydraulic circuit. Abnormal load determination means,
And, when the judgment of the overload judging means is satisfied and the judgment of the abnormal load judging means is not satisfied, an overload alarming means for issuing an alarm around the crusher, and the judgment of the abnormal load judging means is An abnormal load alarm means for issuing an alarm to the periphery of the crusher when the condition is satisfied is provided. 7. The crusher feeder control device according to claim 2, wherein the speed control means determines the overload after the operation of the feeder is decelerated or stopped by a signal from the deceleration / stop signal output means. If the state in which the determination by the means and the oversupply determination means are no longer satisfied continues for a second predetermined time, a first signal for outputting a signal for decelerating or returning the operation of the feeder to a state before the stop is output. A feeder control device for a crusher, comprising a return signal output means. 8. The crusher feeder control device according to claim 2, wherein the speed control means determines the overload after the operation of the feeder is decelerated or stopped by a signal from the deceleration / stop signal output means. If the determination by the means and the oversupply determination means are no longer satisfied again, the load of the crushing device detected by the load detection means is reduced to the first load.
A return load determining means for determining whether or not the value is smaller than a second predetermined value which is smaller than a predetermined value; and if the return load determining means is satisfied, the operation of the feeder is returned to a state before deceleration or stop. And a second return signal output means for outputting a signal for causing the crusher to output a signal. 9. A feeder control device for a crusher according to claim 1, wherein said load detecting means is a rotational speed detecting means for detecting a rotational speed of said crushing device. . 10. The crusher feeder control device according to claim 9, wherein said rotation speed detecting means detects a rotation speed of an actuator for driving said crushing device. 11. A feeder control device for a crusher according to claim 7, further comprising an adjusting means for adjusting said second predetermined time.