JP2000136739A - Engine control device for crushing machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce energy loss, noise and the amount of exhaust gas by reducing the rotating speed of an engine in a standby state where the operation of equipments including a crushing device is stopped. SOLUTION: An engine control device for a crushing machine is provided on the self-travelling crushing machine 1 having a jaw crusher 4 for crushing rubbish, a feeder 5, a conveyor 6, an electromagnetic selector 7 and a traveller 11, hydraulic pumps 16, 18 driven by an engine 15 and operating lever devices 29, 30 for operating hydraulic motors 19-23 for controlling the rotating speed of the engine 15. When all equipments 4-7, 11 are in stopped condition or the feeder 5 and the jaw crusher 4 are in idling condition, the engine control part 45d of the controller 45 limits the amount of fuel to be injected via a fuel injection control device 103 from a fuel injector 102 to be a first preset value for controlling the rotating speed of the engine 15 to be a preset idling speed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine control device for a crusher for crushing rocks, construction waste, and the like, and more particularly, to reducing the engine speed in a standby state in which each device such as a crusher stops operating. Reduces energy loss,
The present invention relates to an engine control device for a crusher capable of reducing noise and exhaust gas amount.

[0002]

2. Description of the Related Art A crusher crushes various crushed rocks, construction waste materials and the like (hereinafter appropriately referred to as garbage) generated at a construction site to a predetermined size before transporting the crushed material. In this way, the construction is facilitated and costs are reduced. For example, in the crusher described in Japanese Patent Application Laid-Open No. Hei 8-196933, the waste put into the hopper above the crusher by a hydraulic shovel or the like is guided to a crushing device such as a jaw crusher by a feeder below the hopper. Crushed to a predetermined size. The crushed gala,
It falls from the space below the jaw crusher onto the conveyor below the jaw crusher and is conveyed by this conveyor. During this transportation, the magnetic separator placed above the conveyor adsorbs and removes, for example, rebar pieces mixed into the concrete garbage, and finally as a crushed product of almost uniform size from the rear of the crusher. It is carried out. Each of the above-mentioned devices such as the feeder, the crushing device, the conveyor, and the magnetic separator is a corresponding hydraulic actuator, that is, a hydraulic motor for the feeder, a crushing hydraulic motor, a hydraulic motor for the conveyor, a hydraulic motor for the magnetic separator, and the like. It operates by being driven by the pressure oil discharged from the. The hydraulic pump is driven by an engine mounted on the crusher, and the discharge amount of the pressure oil changes according to the rotation speed of the engine.

[0003] Further, although not specifically described in the above-mentioned known art, usually, for example, a fuel injection device for injecting fuel into the engine and a fuel injection amount of the fuel injection device are controlled in the engine. A fuel injection control device and a throttle device 91 for setting and inputting a fuel injection amount to the fuel injection control device as shown in FIG. 25 are provided side by side. When the operator operates the dial 92 of the throttle device 91, a signal corresponding to the operation amount is input to the fuel injection control device, and the fuel injection control device determines the fuel injection amount from the fuel injection device in accordance with the signal. Under the control, the engine rotates at a rotational speed corresponding to the fuel injection amount. Thus, the rotation speed of the engine is set to a value corresponding to the operation amount of the dial 92 of the throttle device.

[0004]

The above prior art has the following problems. During the crushing operation by the crusher, the hydraulic oil from the hydraulic pump is supplied to the feeder hydraulic motor, the crushing hydraulic motor, the conveyor hydraulic motor, the magnetic separator hydraulic motor, etc., and the feeder, the crusher,
Each device such as a conveyor and a magnetic separator operates. At this time, a load is applied to each of the hydraulic actuators. In particular, a crushing hydraulic motor that drives the crushing device includes:
The largest load is applied. In the related art, the engine speed is uniquely set according to the dial operation amount of the throttle device 91. Therefore, the engine speed is set relatively high so that the hydraulic pump can discharge hydraulic oil according to the maximum load applied to the crushing hydraulic motor during the crushing operation, and set to a higher speed during the crushing operation. You have to use fixed value.

[0005] On the other hand, the crushing operation by the crusher is usually not continuous, and a certain amount of standby time is required between the time when a predetermined amount of looseness is input by a hydraulic shovel and crushing is performed and the next time when the next emptying is input. May be present. During this time, there is no load in which there is almost no rattle in each device. At this time, unlike a hydraulic shovel, a crusher is often operated only by simple operations such as switching between driving and non-driving as shown in FIG. 6 described later. Since the devices are not always arranged at all times, during the standby time, each device usually stands by in an idling state while maintaining the same drive as in the previous crushing. Therefore, when the engine speed is set to a relatively high value as described above, the engine is uselessly rotated at a high speed even during the idling state where no load is applied to each device, resulting in energy loss. There is. During the standby time, the feeder, the crusher, the conveyor, and the magnetic separator are not loaded, so that noise from them is reduced. Noise is not reduced. In particular, in recent years, there has been an attempt to use a crusher to recycle even in an urban area. However, if the noise during the standby time is large, it is difficult to install and operate the crusher in an urban area, especially in a residential area. Furthermore, the amount of exhaust gas from the engine is particularly large when the engine speed is high, and the noise also increases.

The present invention has been made in view of the above-mentioned problems of the prior art, and an object of the present invention is to reduce the number of revolutions of an engine during a standby time during which no load is applied to devices such as a crushing device. An object of the present invention is to provide an engine control device of a crusher capable of reducing energy loss, noise, and exhaust gas amount.

[0007]

Means for Solving the Problems (1) In order to achieve the above object, the present invention relates to a crushing device for crushing rocks, construction wastes, and the like put into a hopper, and an operation related to crushing work by the crushing device. A plurality of devices, including auxiliary machines for performing
A plurality of hydraulic actuators for driving the plurality of devices, at least one hydraulic pump for discharging hydraulic oil to the plurality of hydraulic actuators, an engine for driving the hydraulic pump, and operation of the plurality of hydraulic actuators, respectively The engine control device of the crusher provided in the crusher having a plurality of operating means for controlling the number of revolutions of the engine, wherein all predetermined devices including the crusher among the plurality of devices are in a stopped state. Or a first detection means for detecting that all of the predetermined devices in the operating state are in an idle state in which the crushing or the work related to the crushing operation is not performed on rocks, construction waste materials, etc. The engine speed is controlled to a preset idling speed based on the value detected by the first detecting means. And a first control means.

[0008] The waste put into the hopper is crushed to a predetermined size by a crushing device and then subjected to a predetermined operation by an auxiliary machine. This series of operations is not usually continuous, and there is a certain amount of waiting time between the time when a predetermined amount of waste is thrown into the hopper and crushing is performed and the time when the next waste is thrown. When such a standby time is reached, a plurality of devices such as a crushing device and an auxiliary machine are in an operation state and are in an idle operation state in which there is no looseness in the devices. It is detected by the first detection means that all of them are in the idling state. This allows
The first control means limits the fuel injection amount from the fuel injection means to a first predetermined value by, for example, the first limiting means,
Since the engine speed is controlled to a preset idling speed, the engine speed can be kept low. In addition, even when all of the predetermined devices are stopped by the operator, the stopped states are detected by the first detection means, and thus the engine speed can be similarly reduced. Therefore, the energy loss, the noise, and the exhaust gas amount can be reduced as compared with the related art in which the engine speed is maintained at a value corresponding to the setting of the speed setting means.

(2) In order to achieve the above object, the present invention also relates to a crushing device for crushing rocks and construction waste materials input from a hopper, and a crushing device for rocks and construction waste materials input to the hopper. Feeder, and a plurality of devices including a conveyor for transporting rocks, construction waste, and the like crushed by the crushing device, a plurality of hydraulic actuators respectively driving the plurality of devices, and a plurality of hydraulic actuators A crusher having at least one hydraulic pump that discharges hydraulic oil, an engine that drives the hydraulic pump, and a plurality of operating units that respectively operate the plurality of hydraulic actuators, controls a rotation speed of the engine. In the engine control device of the crusher, all the predetermined devices including the crusher among the plurality of devices are stopped Or first detection means for detecting that all of the predetermined devices in the operating state are in an idle state in which the crushing or work related to the crushing work is not performed on rocks, construction waste materials, and the like, First control means for controlling the engine speed to a preset idling speed based on the value detected by the first detecting means.

(3) In the above (1) or (2), preferably, the apparatus further comprises a rotation speed setting means for setting a rotation speed of the engine, and the first control means comprises a first detection means. In the first case, when it is detected that all of the predetermined devices are in a stopped state or all of the predetermined devices that are in an operation state are in the idle operation state, Regardless of the setting, the engine speed is limited to the idling speed, and in the second case instead of the first case, the engine speed is set to a speed according to the setting of the speed setting means. First
It has limiting means.

(4) In the above (3), further preferably, there is further provided a fuel injection means for injecting fuel to the engine, and wherein the first restricting means, in the first case, is provided with the rotary engine. Regardless of the setting of the number setting means, the fuel injection amount from the fuel injection means is limited to a first predetermined value corresponding to the idling speed, and in the second case, the fuel injection amount from the fuel injection means is reduced. There is provided first fuel injection control means for setting a value according to the setting of the rotation speed setting means.

(5) In the above (1) or (2), preferably, the first detecting means is configured such that a predetermined device including the crushing device among the plurality of devices is in an operating state or a stopped state. A first operating state detecting means for detecting whether or not the predetermined equipment is operating, and when the operating state of the predetermined equipment is detected by the first operating state detecting means, First operating state detecting means for detecting whether the apparatus is in an actual operating state in which crushing or work related to the crushing operation is performed or in the idle operating state.

(6) In order to achieve the above-mentioned object, the present invention provides a crushing device for crushing rocks, construction waste materials and the like put into a hopper, and an auxiliary machine for performing work related to crushing work by the crushing device. A plurality of devices, a traveling body having traveling means, a plurality of hydraulic actuators respectively driving the plurality of devices and the traveling body, and at least one hydraulic pump for discharging hydraulic oil to the plurality of hydraulic actuators An engine for driving the hydraulic pump, and a crusher having a plurality of operating means for respectively operating the plurality of hydraulic actuators, wherein the engine control device of the crusher for controlling the rotation speed of the engine, The traveling means is in a stopped state, and whether or not all the predetermined devices including the crushing device among the plurality of devices are in a stopped state. The second detection means for detecting that all of the predetermined devices in the operating state are in an idle state in which the crushing or work related to the crushing work is not performed on rocks, construction waste materials, and the like, and Second control means for controlling the engine speed to a preset idling speed based on a value detected by the second detecting means.

When the crusher is of a self-propelled type equipped with a traveling means, the crushing machine may travel on its own in the crushing site. In this case, even if all of the plurality of devices provided in the crusher are in a stopped state, it is preferable to reduce the engine speed in order to obtain a predetermined traveling speed because the traveling means is in an operating state. Absent. Therefore, in the present invention, the second detecting means detects that the traveling means is in the stopped state and all the predetermined devices are in the stopped state or in the idling state, and the second control is performed in accordance with the detection result. The engine speed is controlled to the idling speed by means. Thereby, a favorable traveling speed during traveling can be secured.

(7) In the above (6), preferably,
The apparatus further includes a rotation speed setting unit that sets a rotation speed of the engine, and wherein the second control unit is the second detection unit, wherein the traveling unit is in a stopped state, and among the plurality of devices, In a third case where it is detected that all of the predetermined devices including the crushing device are in a stopped state or all of the predetermined devices that are in an operation state are in the idle operation state, The engine speed is limited to the idling speed irrespective of the setting of the setting means, and in the fourth case instead of the third case, the engine speed is adjusted according to the setting of the speed setting means. There is provided second limiting means for setting the number of rotations.

(8) In the above (7), further preferably, there is further provided a fuel injection means for injecting fuel to the engine, and the second restricting means, in the third case, the rotation Regardless of the setting of the number setting means, the fuel injection amount from the fuel injection means is limited to a first predetermined value corresponding to the idling speed, and in the fourth case, the fuel injection amount from the fuel injection means is reduced. There is provided second fuel injection control means for setting a value according to the setting of the rotation speed setting means.

(9) In the above (6), preferably, the second detection means is configured such that predetermined equipment including the crushing device and the traveling means among the plurality of equipment are in an operating state or a stopped state. A second operating state detecting means for detecting whether or not the predetermined equipment is located in the rock. If the operating state of the predetermined equipment is detected by the second operating state detecting means,
A second operating state detecting means for detecting whether the crushing operation or the crushing operation is being performed on construction waste or the like in the actual operation state or the idle operation state.

(10) In the above (3) or (7),
Also preferably, there is provided a first or second selecting means for selecting whether or not to perform the restriction by the first or second restricting means.

(11) In the above (4) or (8),
Preferably, the first or second limiting means sets the fuel injection amount from the fuel injection means to a value according to the setting of the rotation speed setting means in the second case or the fourth case. In the first case or the third case, the fuel injection amount from the fuel injection means is reduced to the first predetermined value with a substantially rectangular wave-like response characteristic. As a result, the engine speed can be reduced with good responsiveness.

(12) In the above (4) or (8),
Preferably, the first or second limiting means sets the fuel injection amount from the fuel injection means to a value according to the setting of the rotation speed setting means in the second case or the fourth case. In the first case or the third case, the fuel injection amount from the fuel injection means is reduced to the first predetermined value with asymptotic response characteristics.

Accordingly, when the standby state is relatively short, the fuel injection amount returns to the original value before decreasing to the first predetermined value, and the engine speed can be relatively quickly increased. Can be returned to the set rotation speed. Therefore, fluctuations in the engine speed can be reduced, so that the load on the engine can be reduced and fuel efficiency can be improved. In addition, it is possible to prevent the exhaust gas properties from deteriorating due to a rapid change in the engine speed.

(13) In the above (4) or (8),
Preferably, the first or second limiting means sets the fuel injection amount from the fuel injection means to a value according to the setting of the rotation speed setting means in the second case or the fourth case. In the first case or the third case, the fuel injection amount from the fuel injection means is reduced to the first predetermined value with a predetermined delay time.

By providing a delay time, when the standby time is relatively short and the operation returns to the second or fourth case before the delay time elapses after the first or third case has elapsed. Is maintained without decreasing the fuel injection amount from the fuel injection means, so that the engine speed is maintained at the speed set by the speed setting means without lowering. As a result, a decrease in the discharge flow rate of the hydraulic pump can be prevented, and energy loss due to an unnecessary increase or decrease in the engine speed can be prevented.

(14) In the above (4) or (8),
Preferably, the first or second limiting means sets the fuel injection amount from the fuel injection means to a value according to the setting of the rotation speed setting means in the second case or the fourth case. In the first case or the third case, the fuel injection amount from the fuel injection means is changed to the first case.
After limiting to a second predetermined value larger than the predetermined value and maintaining the second predetermined value for a predetermined time, the response characteristic is reduced to the first predetermined value with a substantially rectangular wave-like response characteristic.

(15) In the above (4) or (8),
Preferably, the first or second limiting means sets the fuel injection amount from the fuel injection means to a value according to the setting of the rotation speed setting means in the second case or the fourth case. In the first case or the third case, the fuel injection amount from the fuel injection means is changed to the first case.
After limiting to a second predetermined value larger than a predetermined value and maintaining the second predetermined value for a predetermined time, the first predetermined value is obtained with an asymptotic response characteristic.
Decrease to a predetermined value. Accordingly, when the standby state is relatively short, it is possible to return to the original value before the fuel injection amount is limited to only the second predetermined value.

(16) In the above (4) or (8),
More preferably, the first or second limiting means is configured to limit the fuel injection amount from the fuel injection means to the first predetermined value in the first case or the third case. In the second case or the fourth case, the fuel injection amount from the fuel injection means is increased to a value according to the setting of the rotation speed setting means with a substantially rectangular wave response characteristic. As a result, the engine speed can be restored with good responsiveness.

(17) In the above (4) or (8),
More preferably, the first or second limiting means is configured to limit the fuel injection amount from the fuel injection means to the first predetermined value in the first case or the third case. In the second case or the fourth case, the fuel injection amount from the fuel injection means is increased with an asymptotic response characteristic to a value according to the setting of the rotation speed setting means.

Thus, when the operation time after the return is relatively short and the operation immediately enters the standby state, the fuel injection amount can be reduced to the first predetermined value again before the fuel injection amount completely returns.
Therefore, fluctuations in the engine speed can be reduced, so that the load on the engine can be reduced and fuel efficiency can be improved. In addition, it is possible to prevent the exhaust gas properties from deteriorating due to a rapid change in the engine speed.

(18) In the above (4) or (8),
Also preferably, the first or second limiting means is configured to limit the fuel injection amount from the fuel injection means to the first predetermined value in the first case or the third case. In the second case or the fourth case, the fuel injection amount from the fuel injection unit is increased with a predetermined delay time to a value according to the setting of the rotation speed setting unit.

Accordingly, if the operation time after the return is relatively short and the vehicle enters the standby state immediately before the delay time elapses after returning to the second case or the fourth case, the fuel injection amount is reduced. Since the first predetermined value is maintained without being restored, it is possible to prevent energy loss due to unnecessary increase and decrease of the engine speed.

(19) In the above (4) or (8),
More preferably, the first or second limiting means is configured to limit the fuel injection amount from the fuel injection means to the first predetermined value in the first case or the third case. In the second case or the fourth case, the fuel injection amount from the fuel injection means is set to a third predetermined value larger than the first predetermined value, and after maintaining the third predetermined value for a predetermined time, The response characteristic is increased to a value corresponding to the setting of the rotation speed setting means with a substantially rectangular wave-like response characteristic.

(20) In the above (4) or (8),
More preferably, the first or second limiting means is configured to limit the fuel injection amount from the fuel injection means to the first predetermined value in the first case or the third case. In the second case or the fourth case, the fuel injection amount from the fuel injection means is set to a third predetermined value larger than the first predetermined value, and after maintaining the third predetermined value for a predetermined time, The asymptotic response characteristic is increased to a value according to the setting of the rotation speed setting means.

Thus, when the operation time after the return is relatively short and the system immediately enters the standby state, it is possible to return to the first predetermined value before the fuel injection amount increases only to the third predetermined value. it can.

(21) In the above (4) or (8),
Also preferably, the first or second restricting means is provided with the first or second restricting means.
In the third case or the third case, when the fuel injection amount from the fuel injection means is limited to the first predetermined value,
There is provided a forced restriction canceling unit for forcibly increasing the fuel injection amount from the fuel injection unit to a value according to the setting of the rotation speed setting unit regardless of the detection result of the first or second detection unit.

When the injection of rocks, construction waste, etc. into the hopper is restarted during the auto-idle state in which the fuel injection amount from the fuel injection means is limited to the first predetermined value by the first or second restriction means, Even if the input amount to the hopper is small, for example, rocks and construction waste may spill into the feeder or the crusher and be introduced. May be preferable in terms of production efficiency. However, when the charging amount is small as described above, the first or second detecting means may continue to detect the idle state, and in this case, the fuel injection amount is limited as it is. Since the engine speed remains at the idling speed, each device including the crushing device remains at a low operation speed corresponding to the idling speed of the engine, and the production efficiency is reduced.

Therefore, in the present invention, by providing the forced limitation releasing means, in such a case, the fuel injection amount is set to the setting of the rotation speed setting means regardless of the detection result of the first or second detecting means. Since the value can be forcibly increased to a corresponding value, the above-described decrease in production efficiency can be prevented. In addition, since the restriction on the fuel injection amount can be released at any time in accordance with the intention of the operator, there is an effect that the degree of security of the operator can be increased.

(22) In (4) above, preferably, the first restricting means sets the fuel injection amount from the fuel injection means in the second case to a value corresponding to the setting of the rotation speed setting means. If the first case occurs while the fuel injection is being performed, the fuel injection amount from the fuel injection means is changed to the first amount.
The feeder is stopped or decelerated while decreasing to a predetermined value.

For example, when a grizzly feeder is used as a feeder, the vibration when the engine reaches the idling speed matches the natural frequency of the feeder,
The feeder may resonate and cause abnormal vibration. Therefore, in the present invention, the abnormal vibration can be reliably prevented by stopping or reducing the speed of the feeder in the first case where the engine speed is the idling speed.

(23) In the above (5) or (9),
Also preferably, the first or second operation state detection means includes an operation state detection means for detecting an operation state of the plurality of operation means corresponding to the predetermined device. This makes it possible to detect whether the predetermined device is in the operating state or the stopped state with good responsiveness.

(24) In the above (5) or (9),
Preferably, the first or second operating state detecting means includes a load pressure detecting means for detecting a load pressure of the plurality of hydraulic actuators corresponding to the predetermined device. As a result, it is possible to accurately detect and determine the actual operation state and the idle operation state of the predetermined device.

(25) In any one of the above (1), (2) and (6), preferably, the first or second detecting means detects the situation of the rock / construction waste material with a light beam, It includes a wave dynamic detection unit that detects using at least one of an electromagnetic wave and an ultrasonic wave.

(26) In the above (25), more preferably, the wave dynamic detecting means detects a stagnation state or a flow state of the rock / construction waste material in at least one of the hopper, the feeder and the crushing device. To detect.

As a result, even when the state of stay of rocks, construction wastes, and the like in the grizzly feeder is detected, the actual operation state and the idle operation state can be detected with high accuracy.

(27) In the above (25), preferably, the wave dynamic detecting means detects an operation state of a working tool for putting the rock, construction waste material, and the like into the hopper.

(28) In order to achieve the above object, the present invention also relates to a crushing device for crushing rocks and construction waste materials input from a hopper, and a crushing device for rocks and construction waste materials input to the hoppers. Equipment including a feeder to be supplied to the crusher and a conveyor for transporting rocks, construction wastes, and the like crushed by the crusher, a traveling body including traveling means, and a plurality of hydraulic actuators for driving the plurality of apparatuses, respectively. And a crushing machine having at least one hydraulic pump for discharging hydraulic oil to the plurality of hydraulic actuators, an engine for driving the hydraulic pump, and a plurality of operating means for operating the plurality of hydraulic actuators, respectively. In the engine control device of the crusher for controlling the number of revolutions of the engine, a method for setting the number of revolutions for setting the number of revolutions of the engine is provided. Detecting the operating state of the operating means corresponding to a predetermined device including the crushing device and the traveling device, respectively, among the plurality of devices, and fuel operating means for injecting fuel into the engine; Operating state detecting means for detecting whether the device and the traveling means are in an operating state or in a stopped state, and when the operating state of the predetermined device is detected by the operating state detecting means, By detecting the load pressure of the corresponding hydraulic actuator, the predetermined device is in an actual operation state in which the crushing or the work related to the crushing operation is performed on rocks, construction waste materials, or the like, or such an operation is performed. A load pressure detecting means for detecting whether the apparatus is in an idle state in which the operation is not performed, and whether or not the operation state detecting means detects that all the predetermined devices are in a stopped state. When the operation state detecting means detects that at least one of the predetermined devices is in the operating state and the load pressure detecting means detects that all of the devices in the operating state are in the idle state; And, in a fifth case in which the operation state detecting means detects that the traveling means is in the stopped state, the fuel injection amount from the fuel injection means is changed regardless of the setting of the rotational speed setting means. In a sixth case other than the fifth case, the fuel injection amount from the fuel injection means is set to a first predetermined value set in advance so as to correspond to the idling speed of the engine. And third selection means for selecting whether or not the third fuel injection control means limits the first predetermined value.

[0046]

Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 1 to 16 show a first embodiment of the present invention.
This will be described below. FIG. 1 is a hydraulic circuit diagram of a hydraulic drive device provided with an engine control device according to the present embodiment. FIG. 2 is an overall structure of a self-propelled crusher to which the engine control device according to the present embodiment is applied. FIG. 3 is a top view showing the entire structure of the self-propelled crusher shown in FIG. 2, FIG. 4 is a front view seen from the direction A in FIG. FIG. 3 is a rear view as viewed from a direction B in FIG. 2.

In FIG. 2 to FIG. 5, the self-propelled crusher 1
Roughly speaking, a hopper 3 into which crushed materials such as rocks and construction waste materials (hereinafter, referred to as galls, not shown) are charged by a working tool such as a bucket of a hydraulic shovel, and has a substantially V-shaped cross section. Jaw crusher 4 and a hopper 3 as a crushing device for crushing the input waste into a predetermined size
Crusher body 8 equipped with a feeder 5 for guiding the waste put into the jaw crusher 4 and a jaw crusher 4
A conveyor 6 for transporting the crushed and reduced pieces of waste to the rear of the crusher 1, and a magnetic separator provided above the conveyor 6 for magnetically sucking and removing magnetic substances contained in the pieces of waste being transported on the conveyor 6. And a traveling body 11 provided below the crusher main body 8 and provided with left and right crawler belts 9L and 9R as traveling means (only the left side as viewed from the driver's seat 10 of the operator is shown).

The jaw crusher 4 is installed on a track frame 12 provided on the traveling body 11, and drives the moving teeth 4a (see FIG. 18 described later) by a driving force generated by a crushing hydraulic motor 20 (described later). By swinging back and forth with respect to the fixed teeth 4b (same as above), the supplied looseness is crushed to a predetermined size. The feeder 5 is a so-called grizzly feeder, and is driven by a driving force generated by a feeder hydraulic motor 19 (details will be described later). (See FIG. 3). As a result, the crushed raw material supplied to the hopper 3 is sequentially conveyed and supplied to the jaw crusher 4, and fine sediment or the like attached to the crushed raw material is dropped downward from the gap between the saw teeth of the sawtooth plate 5a during the conveyance. ing.

The conveyor 6 includes a hydraulic motor 21 for the conveyor.
The belt 6a is driven in accordance with the above (d), and thereby the waste falling from the jaw crusher 4 onto the belt 6a is carried. The magnetic separator 7 drives a belt 7a, which is disposed above the belt 6a of the conveyor 6 so as to be substantially orthogonal to the belt 6a, around a magnetic force generating means (not shown) by a hydraulic motor 22 for magnetic separator (same as above). Then, the magnetic force from the magnetic force generating means is applied through the belt 7a to attract the magnetic material to the belt 7a.
Is transported in a direction substantially perpendicular to the belt 6a and dropped to the side of the belt 6a. The crawler tracks 9L and 9R are respectively provided with drive wheels 13L and 13R provided on the traveling body 11.
R (however, only the left side is shown) and idlers 14L, 14R
And the drive wheels 13L and 13L.
Left and right hydraulic motors 23L, 2 for traveling provided on the R side
The crusher 1 is caused to travel by applying a driving force by 3R (illustrated only in FIG. 1 and described in detail later). The driver's seat 10 is provided on the crusher main body 8, and an operation panel 33 (see FIG. 6, details will be described later) is installed in the driver's seat 10.

During the crushing operation, the waste put into the hopper 3 is guided to the jaw crusher 4 by the feeder 5 below the hopper 3 and crushed to a predetermined size. 4 Drops from the space underneath onto the conveyor 6 and is conveyed. During the conveyance, the magnetic material (for example, rebar pieces mixed in the concrete galley) mixed into the gala by the magnetic separator 7 is removed. It is finally carried out from the rear part (the right end in FIG. 2) of the crusher 1 as substantially uniform crushed materials.

The hydraulic drive device shown in FIG. 1 is provided in the self-propelled crusher 1 described above, and includes a so-called electronic governor type engine 15 and a variable displacement type engine 15 driven by the engine 15. The first hydraulic pump 16 and the second hydraulic pump 18, the fixed displacement pilot pump 19 similarly driven by the engine 15, and the pressure oil discharged from the first and second hydraulic pumps 16 and 18 are supplied, respectively. Six hydraulic motors 19, 20, 21, 2
2, 23L, 23R, the first and second hydraulic pumps 16,
Four control valves 2 for controlling the direction and flow rate of hydraulic oil supplied from the hydraulic motors 18 to the hydraulic motors 19 to 23
4, 25, 26, 28, and are provided in the driver's seat 10,
Left and right traveling control lever devices 29 and 30 for switching left and right traveling control valves 25 and 26 (described later) using pilot pressure generated by pilot pump 19, respectively, and pilot pressure generated by pilot pump 19. 31 and 32 for adjusting the discharge flow rate from the first and second hydraulic pumps 16 and 18, the jaw crusher 4, the feeder 5 and the conveyor provided in the driver's seat 10 of the crusher body. 6 and the operation panel 33 for the operator to input instructions to start / stop the magnetic separator 7.

The six hydraulic motors 19 to 23 include the feeder hydraulic motor 19 for generating a driving force for operating the feeder 5, the crushing hydraulic motor 20 for generating a driving force for operating the jaw crusher 4, and the operation of the conveyor 6. Conveyor hydraulic motor 21 for generating a driving force for driving, the magnetic motor 22 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 traveling hydraulic motors 23L and 23R are formed.

Each of the control valves 24 to 28 is a center bypass type switching valve, and includes a crushing control valve 24 connected to the crushing hydraulic motor 20 and the left running hydraulic motor 23L connected to the left running hydraulic motor 23L. A control valve 25, the right traveling control valve 26 connected to the right traveling hydraulic motor 23R, and an auxiliary machine control connected to the feeder hydraulic motor 19, the conveyor hydraulic motor 21, and the magnetic separator hydraulic motor 22. And a valve 28. At this time, the control valve 25, the control valve 28 and the tank 3
The throttles 38, 39 are provided on conduits 35, 36 connecting
Pressure sensors 40, 41 for detecting pressures (negative control pressures P1 ', P2') generated upstream of the throttles 38, 39, respectively.
Is provided. Here, as described above, the control valves 24 to 28 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 24 to 28. When the control valves 24 to 28 are neutral, that is, when the required flow rate to the hydraulic pumps 16 and 18 is small, most of the hydraulic oil discharged from the first hydraulic pump 16 and the second hydraulic pump 18 is connected to the pipelines 35 and 36. , The negative control pressures P1 'and P2' increase. Conversely, when each of the control valves 24 to 28 is operated to be opened, that is, when the required flow rate to the hydraulic pumps 16 and 18 is large, the pipeline 3
Since the flow rates flowing to the actuators 5 and 36 are reduced by the flow rates flowing to the actuator side, the negative control pressures P1 'and P2' decrease. In the present embodiment, as described later, the negative control pressures P1 'and P2' detected by the pressure sensors 40 and 41 are used.
The tilt angles of the swash plates 16A and 18A of the first and second hydraulic pumps 16 and 18 are controlled on the basis of the fluctuations (described later).

The first hydraulic pump 16 of the first and second hydraulic pumps 16 and 18 is a crushing control valve 2.
The pressure oil for supplying to the crushing hydraulic motor 20 and the left traveling motor 23L is discharged through the control valve 4 and the left traveling control valve 25. At this time, the crushing control valve 24 and the left traveling control valve 2
5 are connected in parallel with each other. On the other hand, the second hydraulic pump 18 is driven by a right traveling motor 23R via a right traveling control valve 26 and an auxiliary machine control valve 28.
Also, pressure oil to be supplied to the feeder hydraulic motor 19, the conveyor hydraulic motor 21, and the magnetic separator hydraulic motor 22 is discharged. At this time, the accessory control valve 28 and the right traveling control valve 26 are connected in parallel with each other.

Here, the feeder hydraulic motor 1 is supplied from the second hydraulic pump 18 via the auxiliary control valve 28.
9, regarding the supply of pressure oil to the hydraulic motor 21 for the conveyor and the hydraulic motor 22 for the magnetic separator, the hydraulic motors 19,
Three solenoid control valves 42, 43, and 44 for controlling the flow rates of the pressure oil supplied to the pumps 21 and 22 are provided, and these are connected in parallel with each other. Correspondingly, pressure compensating valves 56, 58, 59 (details will be described later) are provided, respectively. Solenoid control valve 4
2, 43 and 44 are driving signals S from the controller 45.
m, Sco, and Sf (described later).
Variable throttles 42A, 43A, 44A for controlling the flow rate of the pressure oil supplied to the hydraulic motors 22, 21, 19 according to the opening degree
Are provided respectively. Solenoid control valves 42, 4
When the drive signals Sm, Sco, Sf are turned on, the switches 3 and 44 are respectively switched to the communicating position (the lower position in FIG. 1),
The hydraulic oil guided from the hydraulic pump 18 via the accessory control valve 28 and the introduction conduit 46 is supplied to the corresponding hydraulic motors 22, 21 and 19, respectively, to drive them. When the drive signals Sm, Sco, and Sf are turned off, the springs 42B, 43B, and 44B return to the shut-off positions (upper positions in FIG. 1) by the restoring force, and the corresponding hydraulic motors 22,
The supply of the hydraulic oil from the second hydraulic pump 18 to the hydraulic pumps 21 and 19 is cut off, and the hydraulic motors 22, 21 and 19 are connected to the lead-out line 48 to stop the driving of the hydraulic motors 22, 21 and 19. Has become.

The solenoid control valves 42, 43, 44
Downstream of the variable throttles 42A, 43A, 44A, load detection lines 49, 50, 51 for detecting the load pressures of the hydraulic motors 22, 21, 19 are respectively connected.
Among these, the load detection lines 50 and 51 are further connected to a load detection line 53 via a shuttle valve 52, and the load pressure on the high pressure side selected via the shuttle valve 52 is led to the load detection line 53. It has become. The load detection pipe 53 and the load detection pipe 49 are connected to a maximum load detection pipe 55 via a shuttle valve 54, and the shuttle valve 54
The load pressure on the high pressure side selected in (1) is led to the maximum load detection pipe 55 as the maximum load pressure. On the other hand, the load pressure detected by the load detection lines 49, 50, 51 is transmitted to one side of the corresponding pressure compensating valves 56, 58, 59 as the outlet pressure of each of the solenoid control valves 42, 43, 44. The pressure upstream of the solenoid control valves 42, 43, 44 is guided to the other side of the pressure compensating valves 56, 58, 59.
59 operates in response to the differential pressure across the variable throttles 42A, 43A, 44A of the solenoid control valves 42, 43, 44,
The pressure in the introduction line 46 for introducing pressure oil from the auxiliary control valve 28 to the feeder hydraulic motor 19, the conveyor hydraulic motor 21, and the magnetic separator hydraulic motor 22, and the load of each hydraulic motor 19, 20, 21 The differential pressure across the variable throttles 42A, 43A, 44A is kept constant irrespective of the change in pressure, and a flow rate corresponding to the degree of opening of the solenoid control valves 42, 43, 44 can be supplied to the corresponding hydraulic motor. I have. In addition, a pressure control valve is provided in a pipe 60 that directly connects the above-described introduction pipe 46 and a lead-out pipe 48 that guides the pressure oil discharged from the hydraulic motors 19, 20, and 21 to the auxiliary control valve 28. 61 are provided. The maximum load pressure is guided to one side of the pressure control valve 61 via the maximum load detection pipe 55 described above, and the pressure in the upstream pipe 60 is connected to the other side of the pressure control valve 61. Is led. Thus, the pressure control valve 61 increases the pressure in the downstream pipeline 60 by the set pressure of the spring from the maximum load pressure.

The control valve 24 for crushing,
The right traveling control valves 25 and 26 and the auxiliary control valve 28 are respectively connected to the pilot pump 1.
9 is a pilot operation valve operated using the pilot pressure generated in 9.

The pilot pressure from the pilot pump 19 is guided to the drive units 24a and 24b of the crushing control valve 24 via pilot lines 62 and 63, respectively. A solenoid control valve 64 driven by a drive signal Scr from the controller 45 is provided in the pilot lines 62 and 63. This solenoid control valve 64
Are switched in response to the input of the drive signal Scr, and the pilot pressure is guided to the pilot lines 62 and 63. That is, when the drive signal Scr is turned on, the solenoid control valve 64 is switched to the right position (or the left position) in FIG. 2
4a (or 24b), whereby the crushing control valve 24 is switched to the upper position (or the lower position) in FIG. 1, and the crushing hydraulic motor 20 is driven in the forward (or reverse) direction. When the drive signal Scr is turned off,
The solenoid control valve 64 is in the neutral position, shuts off the pilot pressure from the pilot pump 19, connects the pilot lines 62 and 63 to the tank 34, and makes those pressures equal to the tank pressure. Thereby, the crushing control valve 24 returns to the neutral position, and the crushing hydraulic motor 20 stops.

Control valves 25, 2 for left and right running
6 is operated by the pilot pressure generated by the pilot pump 19 and reduced to a predetermined pressure by the operation lever devices 29 and 30. That is, the operation lever devices 29, 30
Operation levers 29a and 30a and operation levers 29a and 30a
Pressure reducing valve 29 that outputs a pilot pressure according to the operation amount of
b, 30b. When the operating lever 29a of the operating lever device 29 is operated in the direction a (or the opposite direction) in FIG. 1, the pilot pressure is changed to the pilot line 65 (or 6).
6) to the drive unit 25a (or 25b) of the left traveling control valve 25, whereby the left traveling control valve 25 is switched to the upper position (or lower position) in FIG. The hydraulic motor 23L is driven in the forward (or reverse) direction. Similarly, when the operation lever 30a of the operation lever device 30 is operated in the direction b (or the opposite direction) in FIG. It is switched to the middle upper position (or lower position),
The right traveling hydraulic motor 23R is driven in the forward (or reverse) direction. The pilot pump 1
A solenoid control valve 67 that is switched by a drive signal St (described later) from a controller 45 is provided in a pilot introduction pipe line 57 that guides the pilot pressure from the controller 9 to the operation lever devices 29 and 30. That is, when the drive signal St is turned on, the solenoid control valve 67 is switched to the communication position (the right position in FIG. 1), and the pilot pressure from the pilot pump 19 is supplied to the operating lever device 2 via the introduction pipe 57.
9 and 30 to enable the operation of the traveling control valves 25 and 26 by the operation lever devices 29 and 30. On the other hand, when the drive signal St is turned off, the spring 67A
The solenoid control valve 67 returns to the shut-off position (the left position in FIG. 1) by the restoring force, shuts off the pilot pressure from the pilot pump 19, and operates the traveling control valves 25, 26 by the operating lever devices 29, 30. Is made impossible.

The pilot pressure of the pilot pump 19 is guided to the drive parts 28a and 28b of the auxiliary control valve 28 via pilot pipes 68 and 69, respectively. Similarly to the pilot lines 62 and 63 of the crushing control valve 24, the pilot lines 68 and 69 are provided with a solenoid control valve 70 that can be switched by a drive signal Sl (described later) from the controller 45.
That is, the solenoid control valve 70 turns on the drive signal Sl.
When it becomes, it is switched to the communication position (right position in FIG. 1),
The pilot pressure from the pilot pump 19 is guided to the drive unit 28a via the pilot line 68, whereby the auxiliary control valve 28 is switched to the upper position in FIG. 1, and the feeder hydraulic motor 19, the conveyor hydraulic motor 21, And, the pressure oil from the second hydraulic pump 18 is supplied to the introduction pipe 46 for introducing the pressure oil to the hydraulic motor 22 for the magnetic separator. When the drive signal Sl is turned off, the solenoid control valve 70 returns to the shut-off position (the left position in FIG. 1) by the restoring force of the spring 70A, shuts off the pilot pressure from the pilot pump 19, and simultaneously operates the pilot lines 68 and 69. Are connected to tanks 34 so that their pressure equals the tank pressure. As a result, the auxiliary control valve 28 returns to the neutral position.

The regulators 31 and 32 include cylinders 71 and 72 for input torque limit control and cylinders 73 and 74 for negative control. Cylinders 71, 7
2, 73, 74 are pistons 71A, 72A, respectively.
73A, 74A, and pistons 71A, 72A.
When A, 73A and 74A move to the right in FIG. 1, the swash plates 16A and 18 of the first and second hydraulic pumps 16 and 18 decrease so that the discharge flow rates thereof decrease.
When the piston 71A, 72A, 73A, 74A moves to the left in FIG. 1 by changing the tilt angle of A (that is, the displacement of the pump), the discharge flow rate from the first and second hydraulic pumps 16, 18 increases. The tilt angles of the swash plates 16A and 18A are changed. The cylinders 71, 72,
A control pressure based on the pilot pressure from the pilot pump 19 is provided on the bottom side of the pilot lines 73 and 74.
a, 76a, 75b, and 76b, and when the control pressure is high, the pistons 71A, 72A, 73
A and 74A move rightward in FIG. 1 and the discharge flow rates from the first and second hydraulic pumps 16 and 18 decrease. When the control pressure is low, the pistons 71A, 72A, 73A and 74A move to the left in FIG. To increase the discharge flow rate. At this time, the cylinder 7
Pilot lines 75a, 76 to 1, 72, 73, 74
a, 75b and 76b are provided with solenoid control valves 78, 79, 80 and 81 respectively driven by drive signals S1, S2, S3 and S4 (described later) from the controller 45. 79, 80, and 81 connect the pilot lines 75a, 76a, 75b, and 76b in accordance with the output current values of the drive signals S1, S2, S3, and S4. In other words, the solenoid control valves 78, 79 have the pilot lines 75a,
The control pressure supplied to the cylinders 71 and 72 is increased by communicating the valve 76a, and when the output current value becomes zero, the pilot lines 75a and 76a are cut off to reduce the control pressure supplied to the cylinders 71 and 72 to zero. It has become. Also, the solenoid control valves 80, 81 increase the control pressure supplied to the cylinders 73, 74 by communicating the pilot lines 75b, 76b with a larger opening degree as the output current value is smaller,
When the output current value becomes 0, the pilot lines 75b, 76b
And the control pressure supplied to the cylinders 73 and 74 is reduced to zero.

For the solenoid control valves 78 and 79 related to the input torque limiting control cylinders 71 and 72, the controller 45 controls the discharge pressure P1 from the first and second hydraulic pumps 16 and 18 as described later. , P2, the output current value of the drive signals S1, S2 is increased. Thereby, the first and second hydraulic pumps 1
When the discharge pressures P1 and P2 from 6, 18 exceed a predetermined pressure,
The discharge flow rates from the first and second hydraulic pumps 16 and 18 are limited, and the swash plates 16A and 16A are so controlled that the load on the first and second hydraulic pumps 16 and 18 does not exceed the output torque of the engine 15.
The tilt of 18A is controlled (known input torque limiting control).

On the other hand, negative control cylinders 73 and 7
The following control is performed for the solenoid control valves 80 and 81 related to No. 4. That is, the negative control pressures P1 ', P1 detected by the pressure sensors 40, 41 described above.
When 2 ′ is high, the controller 45 outputs drive signals S3 and S3 to the solenoid control valves 80 and 81 as described later.
The output current value of S4 is reduced, and negative control pressures P1 'and P
When 2 ′ is low, the output current value to the solenoid control valves 80 and 81 is increased. Thereby, the smaller the required flow rate to the first and second hydraulic pumps 16 and 18 is, the more the first and second hydraulic pumps
The discharge flow rate from the hydraulic pumps 16 and 18 is reduced, and the larger the required flow rate to the first and second hydraulic pumps 16 and 18,
Also, so-called negative control for increasing the discharge flow rate from the second hydraulic pumps 16 and 18 is performed.

The relief pipes of the three hydraulic pumps 16 and 18 are provided with relief valves 91 and 92, respectively, and the discharge pipe of the hydraulic pump 19 is also provided with a relief valve (not shown). The discharge pressures from the first and second hydraulic pumps 16 and 18 are detected by pressure sensors 82 and 83 provided in pipes branched from the discharge pipes, respectively, and the detection signals are input to the controller 45. It has become.

FIG. 6 shows a detailed structure of the operation panel 33, which includes a "conveyor", a "magnetic separator", a "crusher", and a "feeder".
"ON" and "OFF" operation buttons for operating the respective devices are provided, and the operator operates each of the devices separately and independently by pressing each button.

FIG. 7 shows the function of the controller 45, which includes a pump control unit 45a, a device control unit 45b, a negative control unit 45c, and an engine control unit 45d.

The pump control unit 45a includes a function generator 45a
1, 45a2, and function generators 45a1, 45a2
Is a solenoid control valve 78 for performing the input torque limiting control in accordance with the discharge pressures P1, P2 from the first and second hydraulic pumps 16, 18 detected by the pressure sensors 78, 79 based on the illustrated table. , 79 to the drive signals S1, S2
Occurs.

The device control unit 45b generates the drive signals Sm, Sco, Sf, Scr, and Sl based on the operation signals of the operation panel 33, and outputs the corresponding solenoid control valves 42, 43, 70,
Output them to 64,44. That is, the "conveyor", "magnetic separator", and "feeder" of the operation panel 33 for operating the auxiliary machine
Is turned on, the drive signal St of the solenoid control valve 67 is turned off to return to the shut-off position, and the drive signal Sl of the solenoid control valve 70 is turned off.
Is turned on to switch the control valve 28 for auxiliary equipment to supply the pressure oil from the second hydraulic pump 18 to the introduction line 46, and to control the corresponding solenoid control valves 43, 4
The drive signals Sco, Sm, and Sf of the control units 2, 44 are turned ON, and the corresponding hydraulic motors 21, 22, 19 are driven to start the respective auxiliary machines. Thereafter, when the switch is turned off, the drive signal S of the corresponding solenoid control valve 43, 42, 44 is output.
co, Sm, and Sf are turned off, and the corresponding hydraulic motors 21 and
22 and 19 are stopped, and each auxiliary machine is stopped. Then, the drive signal St of the solenoid control valve 67 is turned on to switch to the communication position, and the operation of the traveling control valves 25 and 26 by the operation lever devices 29 and 30 is enabled. When the switch of the "crushing device" on the operation panel 33 is turned on, the drive signal St of the solenoid control valve 67 is operated as described above.
Is turned off to return to the shut-off position, the drive signal Scr of the solenoid control valve 64 is turned on in accordance with the selection of a forward rotation or reverse rotation selection switch (not shown), the crushing control valve 24 is switched, and the first hydraulic pump 16 Is supplied to the crushing hydraulic motor 20 and driven to start the jaw crusher 4. After that, the switch
When the FF is set, the drive signal S of the solenoid control valve 64 is
The cr is turned off, the crushing hydraulic motor 20 is stopped, and the jaw crusher 4 is stopped. Then, similarly to the above, the drive signal St of the solenoid control valve 67 is turned ON to switch to the communication position.

The negative control unit 45c includes a function generator 45
c1 and 45c2, and function generators 45c1 and 45c2
c2 is a pressure sensor 40, 4 based on the illustrated table.
Drive signals S3 and S4 for the solenoid control valves 80 and 81 are generated in accordance with the negative control pressures P1 'and P2' detected in step 1.

The above-described hydraulic drive device is provided with the engine control device according to the present embodiment. The engine control device includes a rotation speed setting unit for manually setting and inputting the rotation speed of the engine 15 by the operator, for example, a throttle device 101 similar to that of FIG. Device 102;
A fuel injection control device 103 that controls the fuel injection amount of the fuel injection device 102, a rotation speed detector 104 that detects the rotation speed of the engine 15, and pilot lines 65 and 66 related to the left traveling control valve 25 are connected. A pressure sensor 106 for detecting the maximum pilot pressure of the pilot lines 65 and 66 via the shuttle valve 105, and a pilot line 108 via a shuttle valve 108 connected to the pilot lines 84 and 85 related to the right travel control valve 26. 8
Pressure sensor 10 for detecting the maximum pilot pressure of 4,85
9, a pressure sensor 111 for detecting the maximum pilot pressure of the pilot lines 62, 63 via a shuttle valve 110 connected to the pilot lines 62, 63 related to the crushing control valve 24, and a control valve 28 for auxiliary equipment.
Between a pressure sensor 113 for detecting the maximum pilot pressure of the pilot lines 68 and 69 via a shuttle valve 112 connected to the pilot lines 68 and 69, and the crushing control valve 24 and the crushing hydraulic motor 20. Pressure sensors 201 and 202 for detecting the load pressure in the pressure oil supply lines 86a and 86b, and a pressure for detecting the load pressure in the pressure oil supply line 88 between the solenoid control valve 44 and the feeder hydraulic motor 19. Sensor 203 and controller 45
The engine control unit 45d provided in (see FIG. 7)
And the automatic idle function (the jaw crusher 4, the feeder 5, the conveyor 6, the magnetic separator 7, and the traveling body 11 are all stopped, or the traveling body 11 is stopped and the jaw crusher 4 and the feeder 5 are idle. Selection switch 114 for the operator to manually select whether or not to execute the function of lowering the engine speed when the state is reached.
And formed from

Pressure sensors 106, 109, 111, 11
3, 201, 202, and 203, the detection signals are input to the engine control unit 45d as shown in FIG.
Based on these detection signals, the operation state of each device (the jaw crusher 4, the feeder 5, the conveyor 6, the magnetic separator 7, and the traveling body 11) and the operation state of the jaw crusher 4 and the feeder 5 are determined by the engine control unit 45d. (Details will be described later).

In FIG. 1, the fuel injection control device 103
The control signal (to be described later) is input from the engine control unit 45d, and the fuel injection amount of, for example, a known fuel injection pump provided in the fuel injection device 102 is controlled based on the control signal. The rotation speed of the engine 15 is determined according to the fuel injection amount, and the rotation speed is detected by the rotation speed detector 104 and fed back to the engine control unit 45d. As a result, the rotation speed of the engine 15 is eventually controlled by the control signal from the engine control unit 45d.

Returning to FIG. 7, the engine control unit 45d operates the pressure sensors 106, 109, 111, 113, 20
1, 202, and 203, and the throttle device 10
1 and the current rotational speed of the engine 15 detected by the rotational speed detector 104, and the selection switch 1
14, the fuel injection control device 103
The control signal is output to the controller. FIG. 8 is a flowchart showing the control contents. In FIG.
First, in step 100, it is determined whether or not the selection by the selection switch 114 is the ON position for performing the auto idle function.

When the selection by the selection switch 114 is at the OFF position where the auto idle function is not performed,
In step 140, a control signal for controlling the fuel injection amount from the fuel injection device 102 is output to the fuel injection control device 103 so that the rotation speed of the engine 15 becomes the set rotation speed of the throttle device 101. Return.

If the selection switch 114 is in the ON position, the process proceeds to step 110, where the pressure sensors 106, 10
9 (see FIG. 1), it is determined whether the crusher 1 is in a running state or in a non-running state. Specifically, for example, if the pressures detected by the pressure sensors 106 and 109 are both less than a predetermined threshold value near 0, none of the operation levers 29a and 30a of the operation lever devices 29 and 30 are operated. Therefore, it is determined that the crusher 1 is in the non-traveling state, and if at least one of the detected pressures is equal to or more than the threshold value, it is determined that the crusher 1 is in the traveling state.

If the crusher 1 is in the running state, the routine proceeds to step 140, where the engine speed is set to the set speed. If the crusher 1 is in a non-running state, step 12
Moving to 0, it is determined whether at least one device (feeder 5, jaw crusher 4, conveyor 6, and magnetic separator 7) is operating based on the detection signals of the pressure sensors 111 and 113. Specifically, for example, the pressure sensor 111,
If the detected pressure at 113 is less than a predetermined threshold value near 0, the “conveyor” and “magnetic separator” of the operation panel 33
The operation buttons of the “crusher” and “feeder” are both “O”
N ", the control valve 24 for crushing and the control valve 28 for auxiliary equipment are not operated, so that it is determined that all the devices are in the stopped state, and at least one of the detected pressures is in the stopped state. If not less than the threshold value, it is determined that at least one device is operating.

If at least one device is operating, the process proceeds to step 121, where it is determined whether the feeder 5 is operating. The determination at this time may be based on whether the drive signal Sf is equal to or greater than a predetermined threshold value near zero. If it is in the operating state, the determination is satisfied and the routine goes to step 122, where the feeder 5 is in the actual operating state (= the feeder 5 is sending the waste to the jaw crusher 4) or the idle operating state (= the feeder 5 is in the idle state). It is determined that there is no backlash and no-load operation is being performed). This is based on whether the pressure detected by the pressure sensor 203 is equal to or higher than a predetermined threshold. If it is the actual operation state, the determination is satisfied and the routine goes to step 140, where the engine speed is set as the set speed. Step 12
If the determination in step 1 or step 122 is not satisfied, the process proceeds to step 123. In step 123, it is determined whether or not the jaw crusher 4 is operating.
This may be based on whether the pressure detected by the pressure sensor 111 is equal to or higher than a predetermined threshold value near zero. If it is in the operating state, the determination is satisfied and step 124 is performed.
And the jaw crusher 4 is in the actual operation state (= the state in which the jaw crusher 4 is crushing the waste) or the idle operation state (= the state in which the jaw crusher 4 has no waste in the no-load operation). Is determined. This is based on whether one of the detected pressures of the pressure sensors 201 and 202 is equal to or higher than a predetermined threshold value. If it is in the actual driving state, the determination is satisfied and
Move to 0, and set the engine speed as the set speed.

When all the devices are stopped in step 120, when the jaw crusher 4 is stopped in step 123, or when the jaw crusher 4 is idle in step 124, the determination is made. Is not satisfied, and the routine goes to Step 130. In this step 130, regardless of the rotation speed setting in the throttle device 101,
The fuel injection amount from the fuel injection device 102 is
Is a relatively small predetermined value (first predetermined value) for restricting the rotation speed to a low rotation speed (= a predetermined idle rotation speed, for example, a rotation speed lower than the lowest rotation speed that can be set by the throttle device 101). Is output to the fuel injection control device 103, and the process returns to the beginning.

In the above, the feeder 5, the conveyor 6, and the magnetic separator 7 constitute an auxiliary machine for performing work related to the crushing operation by the crushing device. The devices are configured, and among them, the feeder 5 and the jaw crusher 4 configure predetermined devices including a crushing device among a plurality of devices. Also, the hydraulic motors 19 to 22 and the hydraulic motors 23L and 23L
R constitutes a plurality of hydraulic actuators respectively driving the plurality of devices, and includes operating lever devices 29, 30, pilot lines 65, 66, 84, 85, solenoid control valves 64, 70, and pilot lines 62, 63. , 68,
69 constitutes a plurality of operating means for respectively operating the plurality of hydraulic actuators.

The shuttle valves 110 and 112 and the pressure sensors 111 and 113 constitute operating state detecting means for detecting the operating states of a plurality of operating means corresponding to the predetermined equipment. ) Is in the operating state or the stopped state (first (or second))
The operating state detecting means is also constituted. The pressure sensor 20
1, 202 and the pressure sensor 203 constitute load pressure detecting means for detecting the load pressure of a plurality of hydraulic actuators corresponding to a predetermined device, and the first or second operation state detecting means detects the operating state of the predetermined device. Is detected, a first device (or a first device that detects whether the predetermined device is in an actual operation state or an idle operation state in which crushing or work related to crushing work is performed on rocks and construction waste materials, etc. Second, the operating state detecting means is also configured. All of the above devices are in a state where all predetermined devices including a crushing device among a plurality of devices are in a stopped state, or all of the above devices which are in an operating state are crushed or crushed for rocks, construction waste materials, etc. The first detecting means for detecting that the vehicle is in an idle state in which no work is performed, the traveling means is in a stopped state, and all of the predetermined devices including the crushing device among the plurality of devices are included. A second detection means for detecting that all of the stationary equipment or the predetermined equipment in the operating state are in an idle state in which rocks, construction wastes, etc. are not crushed or work related to crushing work is performed. Is also configured.

The engine control unit 45d and the fuel injection control device 103 of the controller 45 determine whether the first detection means is in a state where all of the predetermined devices are stopped or all of the predetermined devices which are in operation are empty. In the first case where it is detected that the vehicle is in the operating state, the amount of fuel injection from the fuel injection means is limited to a first predetermined value corresponding to the idling speed regardless of the setting of the speed setting means. In the second case, which is not the case, the first fuel injection control means for setting the fuel injection amount from the fuel injection means to a value corresponding to the setting of the rotation speed setting means, and in the first case, the rotation speed A first limiting means is also provided which limits the engine speed to the idling speed regardless of the setting of the setting device, and sets the engine speed to the speed according to the setting of the speed setting device in the second case. Then , Also constitutes a first control means for controlling the idling speed set the speed of the engine in advance based on the value detected by the first detecting means.

The engine control unit 45d and the fuel injection control device 103 of the controller 45
The traveling means is in a stopped state, and all predetermined devices including the crushing device among the plurality of devices are in a stopped state, or all of the predetermined devices in an operating state are in an idle state. In the detected third case, the fuel injection amount from the fuel injection unit is limited to the first predetermined value corresponding to the idling rotation speed regardless of the setting of the rotation speed setting unit, and the fourth case other than the third case is set. In the case, the second fuel injection control means is configured to set the fuel injection amount from the fuel injection means to a value corresponding to the setting of the rotation speed setting means. In the fourth case, the engine speed is limited to the idling speed, and in the fourth case, the engine speed is adjusted to a speed in accordance with the setting of the speed setting device. Based on the detection value of the detection means. Also it constitutes the second control means for controlling the idling speed set the rotational speed of the down beforehand.

Further, similarly, the engine control unit 45d and the fuel injection control unit 103 of the controller 45 determine whether the operation state detecting means detects that all of the predetermined devices are in the stopped state, or whether the operation state detecting means detects the predetermined state. When at least one of the predetermined devices is detected to be in the operating state and the load pressure detecting means detects that all of the devices in the operating state are in the idling state, and In the fifth case where it is detected that the traveling means is in the stop state, the fuel injection amount from the fuel injection means is set in advance so as to correspond to the idling speed of the engine regardless of the setting of the speed setting means. The third predetermined value is limited to the first predetermined value, and in the “sixth case” which is not the fifth case, the fuel injection amount from the fuel injection means is set to a value corresponding to the setting of the rotation speed setting means. Also constitutes the control means.

Further, the selection switch 114 constitutes first or second selection means for selecting whether or not to perform restriction by the first or second restriction means, and the first switch by third fuel injection control means. A third selection means for selecting whether or not to restrict to a predetermined value is also configured.

The operation and operation of the present embodiment configured as described above will be described below. When the crusher 1 is allowed to travel on its own, the operator operates the operating levers 29a and 30a of the operating lever devices 29 and 30 to switch the traveling control valves 25 and 26, and the traveling left and right hydraulic motors 23
L and 23R are driven to travel. Upon arrival at the crushing site, the operating levers 29a and 30a are returned to the neutral position,
The crusher 1 is stopped.

At the time of the crushing operation, the operator operates the dial (not shown) of the throttle device 101 to appropriately set the rotation speed of the engine 15. For example, the rotation speed is set relatively high so that the first hydraulic pump 16 can discharge pressure oil according to the maximum load applied to the crushing hydraulic motor 20 during the crushing operation. Then, when executing the auto-idle function, the operator sets the selection switch 114 to the ON position where the auto-idle function is performed. In this state, the operation buttons of the devices 7, 6, 5, and 4 of the operation panel 33 are sequentially turned on to be in an operation state, and the crushing operation is started. That is, when throwing into the hopper 3 by a hydraulic shovel (not shown) or the like,
It is guided to the jaw crusher 4 by the feeder 5 and crushed to a predetermined size. The crushed waste falls onto a conveyor 6 and is conveyed. The magnetic separator 7 removes rebar pieces and the like, and is finally carried out from the rear part of the crusher 1. This series of operations is usually not continuous, and the hopper 3
After a certain amount of waste is thrown in and crushed and carried out, work may be interrupted and put into a standby state until the next waste is thrown in. During this time, there is no load in which almost no rattle is present in each device. However, in general, unlike a hydraulic shovel, in a crusher, the operation of each device is often a simple operation such as switching between driving and non-driving ( Since the operator dedicated to the crusher is not always arranged at all times, the devices 4, 5, 6, and 7 are operated in the same manner as during the crushing during this standby time. Standby in the idling state while maintaining. Then, it is detected through the pressure sensors 201, 202, and 203 that the feeder 5 and the jaw crusher 4 are in idle operation with no load, and the shuttle valves 105 and 108 and the pressure sensors 106 and 109 are in a running stopped state. , The engine control unit 45d of the controller 45 executes step 12 through step 100 and step 110.
The determination at 0 is satisfied, and steps 122 and 12
The judgment of 4 is not satisfied. Thus, step 1
In 30, the fuel injection amount from the fuel injection device 102 is immediately limited to the first predetermined value with a substantially rectangular wave-like response characteristic, and the rotation speed of the engine 15 is limited to the low-speed auto idle rotation speed. FIG. 9 shows a time chart of the fuel injection amount at this time. Thereafter, when the work is resumed and the waste is put into the hopper 3 again, the feeder 5 and the jaw crusher 4 return to the actual operation state, so that the determination of step 122 of the engine control unit 145d is satisfied, and The injection amount immediately returns with a substantially rectangular wave-like response characteristic (see FIG. 9), whereby the rotation speed of the engine 15 also returns to the set rotation speed in the throttle device 101. Note that the above is a case where each device is in the no-load idle operation state during the standby state. However, when the operator sequentially turns off the operation buttons of each device on the operation panel 33 to stop each device, the operation is stopped. ,
This is detected via the shuttle valves 110 and 112 and the pressure sensors 111 and 113, and the fact that the vehicle is in the running stop state is determined by the shuttle valves 105 and 108 and the pressure sensor 1
06 and 109, the engine control unit 45d of the controller 45 executes step 100
Then, the determination in step 120 is not satisfied through step 110. This also results in step 130
Thus, the rotation speed of the engine 15 is limited to the low-speed auto idle rotation speed.

As described above, according to the present embodiment, during the standby time when each device enters the no-load idle operation state (or enters the stop state), the rotation speed of the engine 15 is automatically reduced to the low speed. Since the engine speed is limited to the auto idle speed, the engine speed is reduced to a value corresponding to the setting of the speed setting means.
In addition, the amount of exhaust gas can be reduced. Moreover, since the self-propelled crusher is not a machine that repeatedly lowers and raises the engine rotation like a hydraulic excavator, it is particularly effective to reduce the rotation speed of the engine 15 when each device is not operating. . In addition, since the operation state and the stop state of each device and the traveling body 11 are detected by the pressure sensors 106, 109, 111, and 113 in the form of pilot pressure, the response can be detected with good responsiveness. Furthermore, since the idle state of the feeder 5 and the jaw crusher 4 is detected by the pressure sensors 201, 202, and 203 in the form of the load pressure, it is possible to accurately determine whether the operation is the actual operation or the idle operation. Further, in a self-propelled crusher, the traveling body 11 may be self-propelled in a crushing site. In this case, even if all the devices 4 to 7 in the crusher main body 8 are in a stopped state, since the traveling body 1 is in an operating state, the rotational speed of the engine 15 is also reduced to obtain a predetermined traveling speed. It is not preferable to lower it. Therefore, in the present embodiment, in the flow of FIG. 8, only when all of the devices 4 to 7 are in the stopped state or the feeder 5 and the jaw crusher 4 are in the idle running state and are in the non-running state. , So as to suppress the engine speed. Thereby, a favorable traveling speed during traveling can be secured.

In the first embodiment, the feeder 5 and the jaw crusher 4 among the devices 4, 5, 6, and 7 are arranged.
Attention was paid only to these two, and it was detected whether these two were the actual operation or the idle operation. This is because these two devices among the four devices 4, 5, 6, 7 have a large load, and energy loss in driving by the engine 15 This is a major factor. At this time, when the work is interrupted and the waiting time is reached, if the feeder 5 and the jaw crusher 4 on the upstream side lose the rattle, the rattle remains on the conveyor 6 and the magnetic separator 7 is still functioning, and the automatic idle state is established. As a result, the engine speed is reduced. However, since the load of these two is originally small, the transport speed of the conveyor 6 and the operation speed of the magnetic separator 7 are slightly reduced, but there is no problem in operation. When resuming work,
When the feeder is supplied to the feeder 5 and the jaw crusher 4 on the upstream side, the engine speed returns to the normal speed although the feeder has not yet reached the conveyor 6 and the magnetic separator 7 is not functioning. This is because, even when these motors having a small load are operated idle, the energy loss is extremely small and there is substantially no adverse effect. Therefore, in order to more completely prevent energy loss, it may be possible to detect whether the conveyor 6 is in actual operation or idle operation by detecting the load pressure of the conveyor motor 21. Conversely, only the jaw crusher 4 having the largest load may be focused on, and only the actual operation or the idle operation of the jaw crusher 4 may be detected.

Further, in the first embodiment, the fuel injection amount from the fuel injection device 102 is controlled as shown in FIG. 9, but the invention is not limited to this. Various modifications are possible. These modified examples,
This will be described sequentially below.

(1) The case where the engine speed is gradually reduced / returned. That is, as shown in FIG. 10, when the operation is interrupted and a standby state is reached, the fuel injection amount from the fuel injection device 102 is asymptotically responded. It is a characteristic that is reduced. This allows
The rotation speed of the engine 15 can be gradually reduced to the auto idle rotation speed. Also, at the time of return when the work is resumed, the fuel injection amount from the fuel injection device 102 is similarly increased with asymptotic response characteristics. Thereby, the engine 1
5 can be gradually increased to the set rotation speed. In this case, if the standby state is relatively short, FIG.
As indicated by a dashed line in FIG. 0, the fuel injection amount returns to the original injection amount before the fuel injection amount has not completely decreased to the first predetermined value. There is an effect that can be returned to the number. Also, although not specifically shown for the purpose of preventing complication, when the operation time after the return is relatively short and the operation immediately enters the standby state, the first predetermined time before the fuel injection amount does not increase to the original value is reached. As a result, the engine speed can be relatively quickly reduced to the auto idle speed again. As described above, since the fluctuation of the engine speed can be reduced, the load on the engine 15 can be reduced and the fuel efficiency can be improved. In addition, there is an effect that deterioration of exhaust gas properties (such as generation of black smoke) due to a sudden change in the engine speed can be prevented.

(2) In the case of changing in multiple stages. That is, as shown in FIG. 11, when the operation is interrupted and the operation enters the standby state, the fuel injection amount from the fuel injection device 102 is limited to the second predetermined value slightly smaller. Then, after maintaining the state for a predetermined time, the response characteristic is immediately reduced to the first predetermined value with a substantially rectangular wave-like response characteristic. At the time of return, similarly, immediately after the operation state of at least one device is detected, the fuel injection device 10
The fuel injection amount from Step 2 is set to a third predetermined value which is slightly larger than the first predetermined value, and after maintaining the state for a predetermined time, the injection amount immediately before the auto-idle is immediately performed with the substantially rectangular wave response characteristic. It is to return. In this case, when the standby state is relatively short, as shown by the dashed line in FIG. 11, the fuel injection amount returns to the original injection amount while decreasing only to the second predetermined value, and the engine There is an effect that the rotation speed can be relatively quickly returned to the original setting rotation speed. Although not particularly shown for the purpose of preventing complexity,
Conversely, if the operation time after the return is relatively short and the vehicle immediately enters the standby state, the fuel injection amount returns to the original first predetermined value while increasing only to the third predetermined value, and the engine speed is reduced. Is relatively quickly reduced to the auto idle speed. Thus, similarly to the above (1), the load on the engine 15 can be reduced, the fuel efficiency can be improved, and the deterioration of the exhaust gas properties can be prevented.

Further, in combination with the control of the above (1), as shown in FIG. 12, the fuel injection amount can be changed asymptotically rather than in a substantially rectangular waveform, and the engine speed can be gradually increased / decreased. In this case, the above effects can be further improved. The above description is for the case where the fuel injection amount is changed in two stages, but it goes without saying that the fuel injection amount may be changed in three or more stages.

(3) Providing a Delay Time That is, a case where a predetermined delay time is provided between the time when the operation is interrupted and the standby state is established and the time when the fuel injection amount is reduced. Also in this case, as in the above (1) and (2), there is a great merit when the standby state is relatively short. This will be described with reference to FIGS. 13 and 14A and 14B.

FIG. 13 is a flowchart showing the control contents of the engine control unit 45d in this modification. The same steps as those in FIG. 8 are denoted by the same reference numerals, and description thereof will not be repeated. The flow of FIG.
8 is different from the flow of FIG. 8 in that steps 125 and S126 are provided between the steps 30 and 30 and that a step 127 is provided between steps 110 and 140. That is, if the determination in step 123 or S124 is not satisfied in the actual operation of the feeder 5 and the jaw crusher 4 or the determination in step 120 is satisfied with all the devices stopped, first, in step 125, the current low-speed operation is commanded. Is determined (whether a control signal for performing auto-idling is output to the fuel injection control device 103). Immediately after entering the standby state, since the low-speed rotation operation has not been commanded yet, the determination is not satisfied,
Move to step 126. In step 126, counting of a predetermined delay time is started, and it is determined whether the delay time has elapsed. Until the delay time has elapsed, the determination is not satisfied, and the routine proceeds to step 140, where the throttle device 1
The operation at the set number of revolutions at 01 is continuously commanded, and the process returns to the beginning. When the delay time has elapsed, the routine proceeds to step 130, in which an operation at a low speed (auto idle speed) is commanded, and the process returns to the beginning. Thereafter, while the standby state continues, Step 100 → Step 110 → Step 1
20 → (Steps 121 to S124, etc.) → Step 12
5 → The flow of step 130 is repeated. Here, when at least one of the feeder 5 and the jaw crusher 4 is in the actual operation, the process proceeds from step 120 to step 127, where the counting of the delay time is stopped and cleared, and
At 40, a command for the set number of revolutions is issued, and the process returns to the beginning.

FIG. 14A is similar to FIG.
It is a time chart of a fuel injection amount. FIG. 14 (b)
Is a time chart of the discharge flow rate of the corresponding hydraulic pump. In FIG. 14A, when the delay time is not provided (indicated by a dashed line), as described in the first embodiment, the operation is interrupted and the fuel injection device 102 immediately returns from the standby state. The fuel injection amount of the engine 15 decreases to the first predetermined value, and the rotation speed of the engine 15 decreases accordingly to the automatic idle rotation speed. Thus, the discharge flow rates of the hydraulic pumps 16 and 18 also decrease rapidly as shown in FIG. On the other hand, when work is resumed from this state,
Immediately, the fuel injection amount from the fuel injection device 102 returns to the original injection amount (see FIG. 14A), and the discharge flow rate from the hydraulic pumps 16 and 18 increases as shown in FIG. 14B. On the other hand, when the delay time is provided, if the standby time is relatively short and the operation is resumed before the delay time has elapsed, the fuel injection amount remains unchanged as shown by the solid line in FIG. Therefore, the discharge flow rate from the hydraulic pumps 16 and 18 can be maintained without decreasing as shown by the solid line in FIG. In the above description, a delay time is provided when the fuel injection amount is reduced to reduce the engine speed, but similarly, when the work is resumed, the fuel injection amount returns to the original value. A delay time may be provided. Also, after the delay time
As in the first embodiment, the fuel injection amount from the fuel injection device 102 is reduced / returned with a substantially rectangular wave response characteristic, but is changed with an asymptotic response characteristic as in the above (1). You may.

In FIGS. 9, 10, 11, and 12, the time when the engine speed is reduced and the time when the engine speed is restored are changed with the same characteristics. However, the present invention is not limited to this. Needless to say, the characteristics may be changed with different characteristics. That is, they may be appropriately combined, for example, the characteristic shown in FIG. 9 may be changed when the engine speed is reduced, and the characteristic shown in FIG.

Further, in the first embodiment, the differential pressure across the solenoid control valves 42, 43, 44 is maintained at a predetermined value by the pressure compensating valves 56, 58, 59 as pressure compensating means. The solenoid control valve 4 is not limited to
Instead of 2, 43, 44, a flow control valve with a pressure compensation function may be used. In this case, a similar effect is obtained.

In the first embodiment, as shown in the flow chart of FIG. 8, after selecting the auto-idle function ON with the selection switch 114 in step 100, selecting the auto-idle OFF with this selection switch. Unless otherwise, the auto-idle function continued, but is not limited to this. That is, for example, in addition to the selection switch 114, a forced release switch (not shown, which can manually release the auto idle function) may be arranged on the operation panel 33,
Alternatively, a pendant switch provided separately from the operation panel 33 may be provided, or a switch which can be remotely operated from a driver's seat of a hydraulic shovel by radio may be provided. Engine control unit 45 in this case
The control flow of d may be, for example, as shown in FIG. That is, Step 105 is provided between Step 100 and Step 110, and if ON is selected by the selection switch 114 and Step 100 is satisfied, Step 1 is executed.
At 05, it is determined whether or not the auto-idle function is turned off by the forcible release switch.
If it has not been operated, the flow proceeds to the procedure after step 110. If it has been turned off, the flow proceeds to step 140, and a fuel injection amount control signal is output such that the rotation speed of the engine 15 becomes the rotation speed set in the throttle device 101. Output to the control device 103.

The above-mentioned forced release switch is used when the first or second limiting means limits the fuel injection amount from the fuel injection means to the first predetermined value in the first case or the third case. A compulsory restriction canceling means for forcibly increasing the fuel injection amount from the fuel injection means to a value according to the setting of the rotational speed setting means irrespective of the detection result of the first or second detecting means.

The present modification has the following effects. That is, when the injection of the waste into the hopper 3 is restarted in the auto-idle state in which the fuel injection amount from the fuel injection device 102 is limited and the engine 15 is reduced to the idle speed, the injection amount into the hopper 3 Even if the amount is small, the hopper 3 may spill into the feeder 5 and the jaw crusher 4 and may be introduced. To the normal speed may be preferable in terms of production efficiency. However, when the input amount is small as described above, since the load pressure of the feeder 5 and the jaw crusher 4 detected by the pressure sensors 201 to 203 does not increase so much, the determination in steps 122 and 124 of the flow of FIG. May not be satisfied (that is, it is determined that the vehicle is in the idling operation state). In this case, the fuel injection amount is continuously limited, and the engine 15 remains at the idling speed. Therefore, each device remains at a low operating speed according to the idling speed of the engine 15, and the production efficiency is reduced.

Therefore, in this modified example, by operating the above-mentioned forced release switch to auto idle OFF,
Even in such a case, the pressure sensors 201 to 203
Regardless of the detection result of the throttle device 10
Since the value can be forcibly increased to a value corresponding to the setting of 1, the above-described decrease in production efficiency can be prevented. Further, by enabling the automatic idle function to be released at any time in accordance with the intention of the operator, there is an effect that the psychological level of security of the operator can be increased.

As can be seen from the flow of FIG.
Selection switch 11 even during execution of auto idle function
If the switch 4 is operable, it is needless to say that the same effect can be obtained by giving the same function to the selection switch 114 without separately providing the above configuration release switch. In this case, the selection switch 114 constitutes not only the above-described first to third selection means but also the above-mentioned forced restriction release means.

Further, in the first embodiment, when the automatic idle function is executed, the discharge flow rate from the hydraulic pumps 16 and 18 decreases due to the engine 15 decreasing to the above-mentioned idle speed. , The operating speeds of the jaw crusher 4, the conveyor 6, and the magnetic separator 7 are simply reduced correspondingly. However, for example, when a grizzly feeder is used as the feeder 5 as in the first embodiment, the vibration when the engine 15 reaches the idling speed matches the natural frequency of the feeder 5 and the feeder 5 5 may resonate and cause abnormal vibration. In such a case, the feeder 5 may be stopped at the time of the automatic idle. Engine control unit 45d in this modified example
FIG. 16 is a flowchart showing the control contents.

FIG. 16 differs from FIG. 8 in the first embodiment in that steps 135 and 145 are provided after steps 130 and 140, respectively. That is, step 130
The fuel injection amount from the fuel injection device 102 is
After outputting a control signal of a relatively small predetermined value (first predetermined value) corresponding to the idle speed of 5 to the fuel injection control device 103, the process proceeds to step 135, where the device control unit 45
The drive signal Sf to the solenoid control valve for feeder 44 is turned off via b (see the broken arrow in FIG. 7). As a result, the feeder solenoid control valve 44 returns to the shut-off position (upper position in FIG. 1) by the restoring force of the spring 44B as described above, and supplies the hydraulic oil from the second hydraulic pump 18 to the feeder hydraulic motor 19. , The driving of the feeder hydraulic motor 19 is stopped, and the operation of the feeder 5 is stopped. By stopping the feeder 5 in this manner, the abnormal vibration described above can be reliably prevented.

Similarly, at the time of return from the auto-idle, at step 140, after outputting a fuel injection control signal to the fuel injection control device 103 such that the rotation speed of the engine 15 becomes the rotation speed set by the throttle device 101, In step 145, the drive signal Sf to the feeder solenoid control valve 44 via the device control unit 45b is turned ON. As a result, the feeder solenoid control valve 44 is switched to the communication position (the lower position in FIG. 1), and supplies hydraulic oil from the second hydraulic pump 18 to the feeder hydraulic motor 19,
The feeder hydraulic motor 19 is driven, and the feeder 5 operates.

It is needless to say that at the time of the above-mentioned auto idling, the feeder 5 should not be completely stopped, but should be decelerated to the extent that abnormal vibration due to the resonance does not occur.
In this case, as shown in FIG. 1, the feeder solenoid control valve 44 is set as an electromagnetic proportional valve that can be switched at an opening corresponding to the drive current value of the drive signal Sf. Sf
Is set to a predetermined low value, the pressure oil supply from the second hydraulic pump 18 to the feeder hydraulic motor 19 is throttled, and the operation of the feeder 5 is decelerated. It is also conceivable to control the drive signal Sl instead of the feeder solenoid control valve 44 to return the accessory control valve 28 to the neutral position or to narrow the opening.

Further, from the viewpoint of preventing abnormal vibration due to the resonance in the feeder 5, the supply of the hydraulic oil to the feeder hydraulic motor 19 is not necessarily controlled by controlling the feeder solenoid control valve 44 and the accessory control valve 28. It is not limited to reduction. That is, the above-mentioned set value of the idle speed of the engine 15 is
If the pressure oil supply amount to the feeder hydraulic motor 19 is set so that the feeder 5 does not vibrate abnormally, the control of the valves 44 and 28 as described above is not required. A similar effect is obtained.

Note that, in the first embodiment,
A grizzly-type feeder is used as the feeder 5, and is not a so-called plate type. Usually, in a plate type feeder, the feeder hydraulic motor 1
Since the load of the feeder 9 fluctuates in close relation to the amount of the raw material in the hopper 3, the pressure sensor 203 for detecting the load pressure in the pressure oil supply pipe 88 is used as the operation state detecting means of the feeder 5.
Is particularly effective. However, in the case of a grizzly-type feeder, the load of the hydraulic motor for the feeder has little relation with the amount of the raw material in the hopper 3 and does not fluctuate so much. There is. Therefore, in such a case, an optical detection unit, for example, a level sensor may be provided in the hopper 3 to detect the amount of the backlash. Such an embodiment will now be described.

FIG. 1 is a hydraulic circuit diagram of a hydraulic drive device provided with an engine control device according to a second embodiment of the present invention.
FIG. The same members as those in the first embodiment are denoted by the same reference numerals, and description thereof will not be repeated. In the present embodiment, as means for detecting the operating state of the feeder 5 (that is, the above-described first or second operating state detecting means), instead of the pressure sensor 203 of the first embodiment, a garage in the hopper 3 is used. A wave detecting means for detecting the quantity using a light beam, for example, a level sensor 204 is provided. This level sensor 204
Although a detailed structure is not shown in the drawing, is known as a so-called photoelectric sensor. That is, the level sensor 20
For example, the light emitting device 4 and the light receiving device 4 are provided so as to be substantially horizontally opposed in the hopper 3, and the amount of waste supplied to the hopper 3 becomes excessive, so that the feeder 5 overflows the inside of the hopper 3. When the light comes, the light from the light emitting device is cut off and does not reach the light receiving device, whereby it is detected that the supply amount of the glass has reached the level of the installation position (for example, the lowermost portion of the hopper).

The detection signal of the level sensor 204 is input to the engine control unit 45d of the controller 45.
Then, in step 122 (see FIG. 8) described above, it is determined whether the feeder 5 is in the actual operation state or the idle operation state based on the detection signal of the level sensor 204. That is, the hopper 3 is detected by the level sensor 204.
It is determined that the feeder 5 is in the idle operation state if it is detected that there is no rattle in the inside. If the level sensor 204 detects the presence of looseness in the hopper 3, it is determined that the vehicle is in the actual operation state. Other structures and control procedures are almost the same as those of the first embodiment. According to the present embodiment, even in the case of the grizzly-type feeder 5, the operating state can be detected and determined more accurately, and the same effect as that of the first embodiment can be obtained.

Note that such a wave detection means is not limited to the detection of the staying state of the waste in the hopper 3 by the above-mentioned level sensor 204, and other configurations and uses are also possible. Hereinafter, such modified examples will be sequentially described.

(A) When Using Ultrasonic Waves or Electromagnetic Waves In other words, as shown in FIG. A known ultrasonic sensor (or an electromagnetic wave sensor) 1 is provided near the tip of the arm 118.
Means 15 for detecting the operating state of the feeder 5 by detecting the staying state and flow state of the waste 2 in the hopper 3 located below (that is, the first or second operating state detecting means described above). ).
It also constitutes a part of the above-mentioned first detecting means and second detecting means. At this time, as shown in an enlarged perspective view of a portion C in FIG.
Bracket 120 welded and fixed to the lower part near the tip of 18
Is fixed by bolts 119. The detection signal of the ultrasonic sensor 115 is input to the engine control unit 45d of the controller 45 via a cable (not shown) extending through the arm 118, for example. Then, as in the second embodiment, step 122
In this case, if the ultrasonic sensor 115 detects that the waste 2 has disappeared in the hopper 3, it is determined that the feeder 5 is in an idle operation state.
If the presence of the waste 2 is detected, it is determined that the vehicle is in the actual operation state.

(B) In the case of detecting the state of looseness in the jaw crusher That is, as shown in FIG. 19, an ultrasonic sensor (or an electromagnetic wave sensor) 1 supported by the same structure as in the above (A)
15A, means for detecting the operating state of the jaw crusher 4 by detecting the staying state and flow state of the mower 2 in the jaw crusher 4 located thereunder (that is, the first or second operating state detecting means described above). ). It also constitutes a part of the above-mentioned first detecting means and second detecting means.

The detection signal of the ultrasonic sensor 115A is input to the engine control unit 45d of the controller 45 in the same manner as in the above (A), and in step 124 shown in FIG.
Is detected, it is determined that the jaw crusher 4 is in the idle operation state, and if the presence of the rattle 2 in the jaw crusher 4 is detected, it is determined that the actual operation state is in effect.

(C) A case where the position of a bucket or the like of a hydraulic excavator is detected and a return operation is performed in response to the detected position. That is, as shown in FIG. 20, the excavator was supported by the same structure as (A) and (B). The ultrasonic sensor (or an electromagnetic wave sensor) 115 </ b> B detects that the position of the work tool (in the example of the drawing, the bucket 121 or the arm 122 of the hydraulic shovel) that puts the waste 2 into the hopper 3 has come below it. Then, the operation state of the work implement is detected. In this case, unlike the above (A) and (B), the ultrasonic sensor 11
5B does not constitute the first or second operating state detecting means, but constitutes a part of the above-mentioned first detecting means and second detecting means. The detection signal of the ultrasonic sensor 115B is input to the engine control unit 45d of the controller 45, and is used for determining whether to return from the auto idle. FIG. 21 shows a control flow of the engine control unit 45d at this time.

FIG. 21 differs from FIG. 8 in the first embodiment in that step 125 is provided between step 121 and step 122 and step 123. That is, it is determined whether or not the feeder is operating in step 121 (the drive signal Sf).
Is greater than or equal to a predetermined threshold value near 0) or the determination in step 122 (whether or not the pressure detected by the pressure sensor 203 is greater than or equal to a predetermined threshold value) is not satisfied. Move on to 125.

In this step 125, based on the detection signal of the ultrasonic sensor 115B, a work tool (a bucket 121 and an arm 122 of a hydraulic shovel, etc., or a manual work tool such as a scoop, etc.) for throwing looseness into the hopper 3 may be used. )
Is located above the hopper 3 (ie, below the sensor 115B). If the determination is satisfied, the process proceeds to step 123 to determine whether or not the jaw crusher 4 is in the operating state. If the determination in step 125 is not satisfied, the process proceeds to step 140 to set the engine 15 to the set rotation speed.

According to such a flow, in steps 121, 122, 123, 124 and 125, when shifting to the auto-idle state, "the feeder 5 is stopped or idling", and "the bucket or the like is on the hopper. , And the jaw crusher 4 is in a stopped state or in an idling state, and the transition is made only when all three conditions are satisfied. Conversely, when returning from the auto-idle to the normal state, the feeder 5 is switched to the normal state. "Actual operation state", "bucket or the like is on the hopper", or "jaw crusher 4".
Is restored if any one of the conditions is satisfied.

This modification has the same effect as the modification of the first embodiment described above with reference to FIG. That is, as described above, in the flow of FIG. 8, when resuming the feeding of the waste to the hopper 3 during the auto-idle state, if the feeding amount is small, it is determined that the idle operation state is established. Although the engine 15 remains at the idling speed, each device may have a low operation speed and the production efficiency may be reduced. However, in this modified example, the working tool at the time of inputting is moved above the hopper 3. By detecting the fact and returning from the auto-idle state to the normal state, it is possible to prevent the above-described decrease in production efficiency.

FIGS. 22 to 2 show a third embodiment of the present invention.
4 will be described. This embodiment is an embodiment in which so-called load sensing control is performed on the second hydraulic pump instead of the negative control. The same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof will not be repeated.

FIG. 22 is a hydraulic circuit diagram of a hydraulic drive device of a self-propelled crusher according to the present embodiment, FIG. 23 is a block diagram showing functions of a controller 45A of the present embodiment, and FIG. Pump control unit 45aA in 23 (described later)
FIG. 4 is a block diagram showing functions of a load sensing control unit 45a3 provided in the system. 22, 23, and 24, in the present embodiment, the maximum load detection pipeline 5
The pressure sensor 87 detects the maximum load pressure PL of the hydraulic motor 22 for the magnetic separator, the hydraulic motor 21 for the conveyor, and the hydraulic motor 19 for the feeder, which is led to 5, and based on the detection signal, the load control of the pump controller 45aA is performed. A drive signal S5 (described later) is output from the control unit 45a3. The drive signal S5 drives a solenoid control valve 89 provided in place of the solenoid control valve 81 for negative control in the regulator 32A, and a load sensing cylinder 90 provided in place of the cylinder 74 for negative control. The driving of the cylinder 90 is controlled by controlling the control pressure on the cylinder 90.

The cylinder 90 is provided with a piston 90A similarly to the cylinders 78 and 79. When the piston 90A moves to the right (or left) in FIG.
The tilt angle of the swash plate 18A of the hydraulic pump 18 is changed so that the discharge flow from the nozzle 8 decreases (increases).
A pilot pump 1 is provided on the bottom side of the cylinder 90.
9 is led via pilot line 76b. The solenoid control valve 89 communicates the pilot line 76b according to the output current value of the drive signal S5 from the load sensing control unit 45a3. In the load sensing control unit 45a3, first, the second hydraulic pump discharge pressure P2 by the pressure sensor 83 and the pressure sensor 87
The actual differential pressure ΔPLS from the maximum load pressure PL is
a31, and the differential pressure Δ between the actual differential pressure ΔPLS and the target differential pressure ΔPo previously set in the target differential pressure setting section 45a32.
(ΔPLS) is calculated by the subtractor 45a33. After that, the control gain setting section 45a34 compares this differential pressure Δ (ΔPLS) with FIG.
The target tilt change Δθ is obtained from the control gain K shown in FIG. 4 and the target tilt change Δθ is calculated by the integration element 45a.
The target pump tilt angle θ for load sensing control is obtained by integration at 35. And the function generator 45a36
The solenoid drive signal S5 is generated from this table based on the illustrated table in which the output current value increases as the target tilt angle θ increases. Thus, load sensing control for controlling the discharge flow rate of the second hydraulic pump 18 is executed so that the pump discharge pressure P2 is maintained at a pressure higher than the maximum load pressure PL by a predetermined value.

The negative control unit 45cA has only one function generator 45c1 corresponding to the above functions.

The other structure is almost the same as that of the first embodiment.

According to the present embodiment, the second hydraulic pump 1
8 is maintained at a pressure higher than the maximum load pressure PL by a predetermined value, and the corresponding hydraulic motors 22, 21, 1
9 is controlled so as to have a minimum pressure necessary for driving the actuator 9. Therefore, the discharge flow rate of the second hydraulic pump 18 is not increased unnecessarily and the horsepower of the engine 15 is not wasted, so that the energy loss is further reduced.
Noise and exhaust gas volume can be reduced.

In the first to third embodiments,
Although three feeders 5, a conveyor 6, and a magnetic separator 7 are provided as auxiliary machines for performing work related to the crushing operation, the present invention is not limited to this, and the magnetic separator 7 may be omitted as appropriate according to the work circumstances. . In addition to these three, 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. 4 may be provided on the downstream side. In these cases, a similar effect is obtained.

In the first to third embodiments, the crusher provided with the jaw crusher 4 for crushing the moving teeth 4a and the fixed teeth 4b as a crushing device has been described as an example. Not limited to, other crushing devices, for example, a pair of roll-shaped rotating body with a crushing blade attached, and rotating the pair in the opposite direction to each other, crushing by sandwiching the looseness between these rotating bodies Rotary crusher (six-shaft crusher including so-called roll crusher),
Equipped with a cutter on the axis arranged in parallel, a crushing device that shears the gala by rotating in opposite directions (such as a biaxial shearing machine including a so-called shredder), and a high-speed rotation of a striking plate equipped with a plurality of blades, A crusher that is equipped with a so-called impact crusher, which crushes rocks and construction waste materials by using the impact from the impact plate and the collision with the rebound plate, and wood such as wood, branch timber, and construction waste wood Is applied to a rotor equipped with a cutter, and is also applicable to a wood crushing machine that turns the pieces into small pieces. In these cases, feeder 5
May be omitted. In these cases, a similar effect is obtained.

Further, in the first to third embodiments, the bottom plate portion including the plurality of saw-toothed plates 5a on which the crushed material is placed is added as the feeder 5 by using the driving force of the hydraulic motor. Although the self-propelled crusher 1 provided with the shaking grizzly feeder has been described as an example, the invention is not limited to this.
That is, another type of feeder, for example, a crushed raw material supplied from a hopper is placed on a substantially flat bottom plate provided below the hopper, and the bottom plate is substantially driven by a base drive mechanism based on a driving force generated by a hydraulic motor. By reciprocating in the horizontal direction, the subsequent crushed material is input, the preceding crushed material is sequentially extruded on the bottom plate, and the crusher equipped with a so-called plate feeder that sequentially supplies the crushed material from the front end of the bottom plate to the crusher. Is also applicable.

In the first to third embodiments, a crusher equipped with crawler tracks 9L and 9R is described as an example. However, the present invention is not limited to this. Is also applicable. In this case, in the control flows of FIGS. 8 and 13, step 110 may be omitted, and if the determination of step 100 is satisfied, the process may proceed to step 120. In this case, a similar effect is obtained.

[0131]

According to the present invention, in the waiting time,
The rotation speed of the engine is suppressed to a low idling rotation speed by the first or second limiting means. Therefore, as compared with the related art in which the engine speed is maintained at a value corresponding to the setting of the speed setting means, reduction of energy loss, reduction of noise,
In addition, the amount of exhaust gas can be reduced.

[Brief description of the drawings]

FIG. 1 is a hydraulic circuit diagram of a hydraulic drive device provided with an engine control device according to a first embodiment of the present invention.

FIG. 2 is a side view showing the entire structure of a self-propelled crusher to which the engine control device according to the first embodiment of the present invention is applied.

FIG. 3 is a top view showing the entire structure of the self-propelled crusher shown in FIG.

FIG. 4 is a front view as viewed from a direction A in FIG. 2;

FIG. 5 is a rear view as viewed from a direction B in FIG. 2;

FIG. 6 is a diagram showing a detailed structure of the operation panel shown in FIG.

FIG. 7 is a diagram illustrating functions of a controller illustrated in FIG. 1;

FIG. 8 is a flowchart illustrating control contents of an engine control unit illustrated in FIG. 7;

FIG. 9 is an example of a time chart of a fuel injection amount when an auto idle function is executed by control based on the flow of FIG. 8;

FIG. 10 is a time chart of a fuel injection amount in a modified example in which the engine speed is gradually reduced / returned.

FIG. 11 is a time chart of a fuel injection amount in a modification in which the engine speed is changed in multiple stages.

FIG. 12 is a time chart of a fuel injection amount in a modification in which the engine speed is changed in multiple stages and gradually reduced / returned.

FIG. 13 is a flowchart illustrating control contents of an engine control unit in a modification in which a delay time is provided.

FIG. 14 is a time chart of a fuel injection amount and a discharge amount of a hydraulic pump in a modification in which a delay time is provided.

FIG. 15 is a flowchart illustrating control contents of an engine control unit in a modification in which a forced release switch capable of manually releasing an auto idle function is provided.

FIG. 16 is a flowchart illustrating control contents of an engine control unit in a modified example in which a feeder is stopped or decelerated at the time of auto idling.

FIG. 17 is a hydraulic circuit diagram of a hydraulic drive device provided with an engine control device according to a second embodiment of the present invention.

FIG. 18 is a partial perspective side view showing a modified example in which the state of the backlash in the hopper is detected using an ultrasonic sensor or an electromagnetic wave sensor.

FIG. 19 is a partial perspective side view showing a modification in which the state of the lash in the jaw crusher is detected using an ultrasonic sensor or an electromagnetic wave sensor.

FIG. 20 is a partial perspective side view illustrating a modification in which the position of a bucket, an arm, or the like of a hydraulic shovel is detected using an ultrasonic sensor or an electromagnetic wave sensor to perform a return operation.

FIG. 21 is a flowchart showing control contents of an engine control unit in the modification shown in FIG.

FIG. 22 is a hydraulic circuit diagram of a hydraulic drive device for a self-propelled crusher according to a third embodiment of the present invention.

FIG. 23 is a block diagram showing functions of the controller shown in FIG.

24 is a block diagram showing functions of a load sensing control unit provided in the pump control unit shown in FIG.

FIG. 25 is a diagram illustrating an example of a structure of a throttle device.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Self-propelled crusher 3 Hopper 4 Jaw crusher (crushing device, predetermined device, multiple devices) 5 Feeder (auxiliary machine, predetermined device, multiple devices) 6 Conveyor (auxiliary machine, multiple devices) 7 Magnetic separator (Auxiliary machine, multiple devices) 9L, 9R Crawler belt (traveling means) 11 Traveling body 15 Engine 16 First hydraulic pump 18 Second hydraulic pump 19 Hydraulic motor for feeder (hydraulic actuator) 20 Hydraulic motor for crushing (hydraulic actuator) 21 Conveyor hydraulic motor (hydraulic actuator) 22 Magnetic separator hydraulic motor (hydraulic actuator) 23L, R Traveling hydraulic motor (hydraulic actuator) 29, 30 Operating lever device (operating means) 45 Controller 45d Engine control unit (first to first) (3 fuel injection control means, first to third restriction means, first to third control means) 2, 63 Pilot line (operation means) 64 Solenoid control valve (operation means) 65, 66 Pilot line (operation means) 68, 69 Pilot line (operation means) 70 Solenoid control valve (operation means) 84, 85 Pilot Pipe line (operating means) 101 Throttle device (rotation speed setting means) 102 Fuel injection device (fuel injection means) 103 Fuel injection control device (first to third fuel injection control means, first to third limiting means, first To third control means) 105 shuttle valve 106 pressure sensor 108 shuttle valve 109 pressure sensor 110 shuttle valve (operating state detecting means, first or second operating state detecting means, first or second detecting means) 111 pressure sensor (operating State detection means, first or second operation state detection means, first or second detection means) 112 shuttle valve (operation state detection means) First or second operating state detecting means, first or second detecting means) 113 Pressure sensor (operating state detecting means, first or second operating state detecting means, first or second detecting means) 114 Selection switch (first or second operating state detecting means) 1st to 3rd selecting means; forced restriction releasing means) 115 Ultrasonic sensor (wave dynamic detecting means, first or second operating state detecting means, first or second detecting means) 115A ultrasonic sensor (wave dynamic detecting means, 115B Ultrasonic sensor (wave dynamic detecting means, first or second detecting means) 201 Pressure sensor (load pressure detecting means, first or second detecting means) Operating state detecting means, first or second detecting means) 202 Pressure sensor (load pressure detecting means, first or second operating state detecting means, first or second detecting means) 203 Pressure sensor (load pressure detecting means, first or second detecting means) 1st or 2nd Rolling state detecting means, the first or second detection means) 204 level sensor (wave detection means, the first or second operation state detection means, the first or second detecting means)

Claims (28)

[Claims] 1. A plurality of devices including a crushing device for crushing rocks, construction waste materials and the like put into a hopper, and auxiliary machines for performing work related to crushing work by the crushing device, and each of the plurality of devices is driven. It has a plurality of hydraulic actuators, at least one hydraulic pump that discharges hydraulic oil to the plurality of hydraulic actuators, an engine that drives the hydraulic pump, and a plurality of operating units that respectively operate the hydraulic actuators. In the engine control device of the crusher provided in the crusher and controlling the number of revolutions of the engine, all the predetermined devices including the crusher among the plurality of devices are in a stopped state, or the predetermined device Among them, all those in the operating state have not performed the above-mentioned crushing or crushing work on rocks, construction waste materials, etc. A first detecting means for detecting that the engine is idling, and a first controlling means for controlling the engine speed to a preset idling speed based on a value detected by the first detecting means.
An engine control device for a crusher, comprising: a control unit. 2. A crushing device for crushing rocks and construction waste materials input from a hopper, a feeder for supplying the rocks and construction waste materials input to the hopper to the crushing device, and a rock crushed by the crushing device. A plurality of devices including a conveyor for transporting construction waste, etc., a plurality of hydraulic actuators each for driving the plurality of devices, at least one hydraulic pump for discharging hydraulic oil to the plurality of hydraulic actuators, An engine control device for a crusher that is provided in a crusher having an engine that drives a pump and a plurality of operation units that respectively operate the plurality of hydraulic actuators, and controls a rotation speed of the engine, Among them, all the predetermined devices including the crushing device are in a stopped state, or are in operation state among the predetermined devices. First detecting means for detecting that all of the objects are in an idle state in which the work related to the crushing or crushing work is not performed on rocks, construction waste materials, and the like, and based on a detection value of the first detecting means, 1st control for controlling the engine speed to a preset idling speed
An engine control device for a crusher, comprising: a control unit. 3. An engine control device for a crusher according to claim 1, further comprising a rotation speed setting means for setting a rotation speed of said engine, and wherein said first control means comprises:
The first detecting means detects that all of the predetermined devices are in a stopped state or all of the predetermined devices in an operating state are in the idle operation state.
In the case of, the engine speed is limited to the idling speed regardless of the setting of the speed setting means,
In a second case other than the first case, the engine of the crushing machine is provided with first limiting means for setting the number of revolutions of the engine to the number of revolutions according to the setting of the number of revolutions setting means. Control device. 4. The engine control device for a crusher according to claim 3, further comprising fuel injection means for injecting fuel into said engine, and wherein said first restricting means comprises: The fuel injection amount from the fuel injection means is limited to a first predetermined value corresponding to the idling rotation speed regardless of the setting of the rotation speed setting means, and in the second case, the fuel injection from the fuel injection means is restricted. An engine control device for a crusher, comprising: first fuel injection control means for setting an amount to a value according to the setting of the rotation speed setting means. 5. The engine control device for a crusher according to claim 1, wherein the first detecting means is configured to determine whether a predetermined device including the crushing device among the plurality of devices is in an operating state or a stopped state. A first operating state detecting means for detecting whether or not the predetermined equipment is operating, and when the operating state of the predetermined equipment is detected by the first operating state detecting means, An engine control device for a crusher, comprising: first operation state detection means for detecting whether the apparatus is in an actual operation state in which crushing or work related to the crushing operation is performed or in the idle operation state. . 6. A traveling body having traveling means, comprising: a plurality of devices including a crushing device for crushing rocks, construction waste materials and the like put into a hopper, and auxiliary machines for performing operations related to crushing work by the crushing device. A plurality of hydraulic actuators that respectively drive the plurality of devices and the traveling body, at least one hydraulic pump that discharges pressure oil to the plurality of hydraulic actuators, an engine that drives the hydraulic pump, An engine control device for a crusher, which is provided in a crusher having a plurality of operation means for respectively operating hydraulic actuators and controls a rotation speed of the engine, wherein the traveling means is in a stopped state, and the plurality of devices are Out of all the predetermined devices including the crushing device are in a stopped state, or some of the predetermined devices are in an operating state. A second detecting means for detecting that the crushing or the work related to the crushing operation is not performed on all the rocks, construction waste materials, etc., and that the engine is in an idle state; and the engine based on a detection value of the second detecting means. To control the number of revolutions to a preset idling number of revolutions.
An engine control device for a crusher, comprising: a control unit. 7. An engine control device for a crusher according to claim 6, further comprising a rotation speed setting means for setting a rotation speed of said engine, and wherein said second control means is provided by said second detection means. The traveling means is in a stopped state, and
A third case in which it is detected that all of the predetermined devices including the crushing device among the plurality of devices are in a stopped state or all of the predetermined devices that are in an operation state are in the idle operation state. The engine speed is limited to the idling speed regardless of the setting of the speed setting means. In the fourth case, not the third case, the engine speed is set to the speed setting. An engine control device for a crusher, comprising: second limiting means for setting the number of revolutions according to the setting of the means. 8. The engine control device for a crusher according to claim 7, further comprising a fuel injection means for injecting fuel into said engine, and wherein said second restriction means comprises: The fuel injection amount from the fuel injection means is limited to a first predetermined value corresponding to the idling rotation speed regardless of the setting of the rotation speed setting means, and in the fourth case, the fuel injection from the fuel injection means is restricted. An engine control device for a crusher, comprising: second fuel injection control means for setting an amount to a value according to the setting of the rotation speed setting means. 9. The engine control device for a crusher according to claim 6, wherein said second detecting means is configured to determine whether predetermined equipment including said crushing apparatus and said traveling means among said plurality of equipment are in operation. A second operating state detecting means for detecting whether the apparatus is in a stop state, and when the operating state of the predetermined apparatus is detected by the second operating state detecting means,
A second operating state detecting means for detecting whether the crushing or the crushing operation is performed on the rock or the construction waste material in the actual operation state or the idle operation state. The crusher engine control device. 10. An engine control device for a crusher according to claim 3, wherein said first or second restricting means selects whether or not to perform restriction.
An engine control device for a crusher, comprising a selection unit. 11. An engine control device for a crusher according to claim 4, wherein said first or second restricting means comprises a fuel injection amount from said fuel injection means in said second or fourth case. Is set to a value according to the setting of the rotation speed setting means, and in the first case or the third case, the fuel injection amount from the fuel injection means is changed by a substantially rectangular wave-like response characteristic. An engine control device for a crusher, wherein the engine control device reduces the value to the first predetermined value. 12. An engine control device for a crusher according to claim 4, wherein said first or second restricting means is configured to control the amount of fuel injected from said fuel injection means in said second or fourth case. Is set to a value corresponding to the setting of the rotation speed setting means, and in the first case or the third case, the fuel injection amount from the fuel injection means is reduced by an asymptotic response characteristic. An engine control device for a crusher, wherein the engine control device reduces the value to a first predetermined value. 13. The engine control device for a crusher according to claim 4, wherein said first or second restricting means is configured to control a fuel injection amount from said fuel injection means in said second or fourth case. Is set to a value corresponding to the setting of the rotation speed setting means, and in the first case or the third case, the fuel injection amount from the fuel injection means is reduced by a predetermined delay time. (1) An engine control device for a crusher, wherein the engine control device reduces the value to a predetermined value. 14. The engine control device for a crusher according to claim 4 or 8, wherein said first or second restricting means is configured to control the fuel injection amount from said fuel injection means in said second or fourth case. Is set to a value corresponding to the setting of the rotation speed setting means, and in the first case or the third case, the fuel injection amount from the fuel injection means is set to be smaller than the first predetermined value. An engine control device for a crushing machine, wherein the engine control device is configured to limit to a large second predetermined value, maintain the second predetermined value for a predetermined time, and then reduce the response to the first predetermined value with a substantially rectangular wave-like response characteristic. 15. The engine control device for a crusher according to claim 4, wherein said first or second restricting means is configured to control an amount of fuel injected from said fuel injection means in said second or fourth case. Is set to a value corresponding to the setting of the rotation speed setting means, and in the first case or the third case, the fuel injection amount from the fuel injection means is set to be smaller than the first predetermined value. An engine control device for a crushing machine, wherein the engine control device is limited to a large second predetermined value, maintained at the second predetermined value for a predetermined time, and then reduced to the first predetermined value with asymptotic response characteristics. 16. The engine control device for a crusher according to claim 4, wherein said first or second restricting means is configured to control the fuel injection amount from said fuel injection means in said first or third case. Is limited to the first predetermined value, and in the second case or the fourth case, the fuel injection amount from the fuel injection means is reduced by the rotational speed with a substantially rectangular wave-like response characteristic. An engine control device for a crusher, wherein the value is increased to a value according to a setting of a setting means. 17. The engine control device for a crusher according to claim 4, wherein said first or second restricting means is configured to control an amount of fuel injected from said fuel injection means in said first or third case. Is limited to the first predetermined value, and in the second case or the fourth case, the fuel injection amount from the fuel injection means is set to the rotational speed setting with asymptotic response characteristics. An engine control device for a crusher, wherein the value is increased to a value according to the setting of the means. 18. The engine control apparatus for a crusher according to claim 4, wherein said first or second restricting means is configured to control the fuel injection amount from said fuel injection means in said first or third case. Is limited to the first predetermined value, and in the second case or the fourth case, the fuel injection amount from the fuel injection means is reduced by a predetermined delay time to the rotational speed setting means. The engine control device of the crusher, wherein the value is increased to a value according to the setting of (1). 19. The engine control device for a crusher according to claim 4, wherein said first or second restricting means is configured to control an amount of fuel injected from said fuel injection means in said first or third case. Is limited to the first predetermined value, and in the second case or the fourth case, the fuel injection amount from the fuel injection means is set to a third value larger than the first predetermined value. An engine control device for a crushing machine, wherein a predetermined value is set, and after maintaining the third predetermined value for a predetermined time, the response is increased to a value corresponding to the setting of the rotation speed setting means with a substantially rectangular wave response characteristic. 20. The engine control device for a crusher according to claim 4, wherein the first or second restricting means is configured to control the amount of fuel injected from the fuel injection means in the first or third case. Is limited to the first predetermined value, and in the second case or the fourth case, the fuel injection amount from the fuel injection means is set to a third value larger than the first predetermined value. An engine control device for a crushing machine, wherein a predetermined value is set, and after maintaining the third predetermined value for a predetermined time, the asymptotic response characteristic is increased to a value according to the setting of the rotation speed setting means. 21. The engine control device for a crusher according to claim 4, wherein said first or second restricting means determines a fuel injection amount from said fuel injection means in said first or third case. When limiting to the first predetermined value, the fuel injection amount from the fuel injection unit is reduced to a value according to the setting of the rotation speed setting unit regardless of the detection result of the first or second detection unit. An engine control device for a crusher, comprising a forced restriction canceling means for forcibly increasing the number. 22. An engine control device for a crusher according to claim 4, wherein said first restricting means changes a fuel injection amount from said fuel injection means in accordance with a setting of said rotation speed setting means in said second case. Crushing machine, wherein, if the first case occurs while the fuel injection amount is set to a predetermined value, the fuel injection amount from the fuel injection means is reduced to the first predetermined value, and the feeder is stopped or decelerated. Engine control device. 23. The engine control device for a crusher according to claim 5, wherein said first or second operating state detecting means detects operating states of said plurality of operating means corresponding to said predetermined device. An engine control device for a crusher, comprising an operation state detecting means. 24. The engine control device for a crusher according to claim 5, wherein the first or second operating state detecting means detects a load pressure of the plurality of hydraulic actuators corresponding to the predetermined device. An engine control device for a crusher, comprising a load pressure detecting means. 25. The engine control device for a crusher according to claim 1, wherein said first or second engine is provided.
An engine control device for a crusher, wherein the detecting means includes a wave dynamic detecting means for detecting a state of the rock, the construction waste material, and the like using at least one of a light beam, an electromagnetic wave, and an ultrasonic wave. 26. The engine control device for a crusher according to claim 25, wherein said wave detection means includes a stagnant state or a flow of said rock / construction waste material in at least one of said hopper, feeder and crusher. An engine control device for a crusher, which detects a situation. 27. The crusher engine control device according to claim 25, wherein said wave dynamic detecting means detects an operation state of a working tool for putting said rocks, construction waste materials, etc. into said hopper. Crusher engine control device. 28. A crushing device for crushing rocks and construction waste materials input from a hopper, a feeder for supplying the rocks and construction waste materials input to the hopper to the crushing device, and a rock crushed by the crushing device. A plurality of devices including a conveyor for transporting construction waste and the like, and a traveling body equipped with traveling means,
A plurality of hydraulic actuators for driving the plurality of devices, at least one hydraulic pump for discharging pressure oil to the plurality of hydraulic actuators, an engine for driving the hydraulic pump, and operation of the plurality of hydraulic actuators, respectively An engine control device for a crusher provided in a crusher having a plurality of operating means for controlling the number of rotations of the engine, wherein a number of rotations setting means for setting the number of rotations of the engine; and injecting fuel to the engine. Detecting the operating states of the operating means corresponding to the predetermined equipment including the crushing device and the traveling means, respectively, of the plurality of equipment, so that the predetermined equipment and the traveling means operate. Operating state detecting means for detecting whether the operating state is in the stop state or the operating state detecting means. When the operating state of a certain device is detected, by detecting the load pressure of the hydraulic actuator corresponding to the predetermined device, the predetermined device can perform the crushing or crushing operation on rocks, construction waste, and the like. Load pressure detecting means for detecting whether the apparatus is in an actual operation state in which work related to the operation is performed or in an idle state in which such work is not performed, and all of the predetermined devices are stopped by the operation state detection means Or the operating state detecting means detects that at least one of the predetermined devices is in an operating state, and the load pressure detecting means detects that all of the operating devices are in the idle state. In a fifth case in which it is detected that the driving state is the driving state, and in a fifth case in which the operation state detecting means detects that the traveling means is in the stopped state, the setting of the rotation speed setting means is performed. Regardless of the fifth case, the fuel injection amount from the fuel injection means is limited to a first predetermined value corresponding to the idling speed of the engine, Third fuel injection control means for setting the fuel injection amount from the engine to a value corresponding to the setting of the rotational speed setting means; and determining whether to limit the third fuel injection control means to the first predetermined value. An engine control device for a crusher, comprising: third selection means for selecting.