JPH1128383A - Self-traveling crushing machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a self-traveling crushing machine in which the overload state of a crusher is returned to a normal state by making carrier capacity small without lowering capacity of a sieve. SOLUTION: In the self-traveling crushing machine fitted with a raw material feeder 14 which carries material to be crushed in a hopper 13 to a crusher 1 and has a sieve function, a plate and grizzly bars are fitted to a frame body 19 and also an exciter 22 is freely vertically swingingly fitted to the frame body 19. The exciter 22 is swung in the vertical direction and thereby the vertical component of excitation force is made large and the horizontal component thereof is made small. Accordingly, carrier capacity is made small without lowering capacity of the sieve.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a self-propelled crushing machine that supplies crushed materials to a crusher provided on an airframe by a vibrating material supply device.

[0002]

2. Description of the Related Art As a self-propelled crushing machine, a crusher, a hopper, a raw material supply device having a sieve function, a conveyor, and the like are known. This self-propelled crushing machine puts only large rocks and the like into a crusher while sieving the material to be crushed in the hopper with a raw material supply device into earth and sand, small stones and the like, and large rocks and the like. The pebbles are discharged by the conveyor.

[0003] The above-mentioned raw material supply device having a sieve function is a device in which a flat plate, a grizzly river, and a vibrator are attached to a frame, and the hopper dropped onto the flat plate by vibrating the frame with the vibrator. The crushed material is transported to a grizzly river, and while being transported along the grizzly river, sediment, small stones and the like are sieved, and only large rocks and the like are transported to the crusher.

Further, a flat plate and a vibrator are attached to the frame in place of the raw material supply device having a sieve function, and the crushed material dropped on the flat plate is conveyed to the crusher by vibrating the frame with the vibrator. A self-propelled crushing machine using a raw material supply device without a sieve function is known.

As shown in FIG. 1, the vibrator rotates a pair of rotating shafts 1 and 1 in opposite directions, and attaches eccentric weights 2 and 2 to the pair of rotating shafts 1 and 1 in the same direction. ,
By rotating the pair of rotating shafts 1 and 1, the inward and outward forces are canceled to generate one-way vibration, and the magnitude of the vibration (excitation force F) is determined by the rotating shaft. It changes depending on the number of rotations (frequency).

[0006]

Since the raw material supply device having a sieve function has the above-described configuration, the horizontal component of the vibrating force is large if the direction of the vibrating force of the vibrator is close to horizontal. Since the vertical component becomes small, the conveying capacity is large and the sieving capacity is small. Further, when the direction of the exciting force of the vibrator is close to the vertical direction, the horizontal component of the exciting force is small and the vertical component of the exciting force is large, so that the carrying capacity is small and the sieve capacity is large.

In a self-propelled crushing machine, it is necessary to supply a certain amount of crushed material to the crusher in order to improve the processing capacity of the crusher, etc. It must be sufficiently sieved and not supplied to the crusher.

For this reason, in the self-propelled crushing machine, the direction of the vibrating force of the vibrator is set to 40 to 50 degrees with respect to the horizontal, and the horizontal and vertical components of the vibrating force are made substantially equal to each other, so that the conveying force and the sieve are changed. The abilities are almost equal.

If an excessive amount of crushed material is supplied to the crusher, or if crushable material that is difficult to crush is supplied, the crusher is overloaded. In this case, the crushed material supplied to the crusher is overloaded. It is necessary to return to the normal load state by reducing the amount of the load.

For this reason, conventionally, when the crusher is overloaded, the rotational speed (vibration frequency) of the vibrator is reduced to reduce the vibrating force, thereby reducing the horizontal component and the transport force. doing.

However, the rotational speed (vibration frequency) of the vibrator
When the vibrating force is reduced by reducing the oscillating force, the vertical component is also reduced, so that the sieving ability is also reduced, so that the earth and sand, pebbles, etc. mixed in the crushed material cannot be sufficiently sieved and supplied to the crusher. When earth and sand, pebbles, and the like are supplied to the crusher, the processing capacity is reduced and the teeth are damaged. In addition, earth and sand, pebbles, and the like may adhere to the sieve.

Further, when the sieving capacity is reduced, earth and sand, small stones and the like are deposited on the grizzly river, and large rocks are spilled and supplied to the crusher irrespective of the conveying force. The time required for the crusher to return from the overload state to the steady-state load state becomes longer without reducing the supply amount of the crushed material.

When a raw material supply device having no sieve function is used, the flat plate vibrates up and down due to the vertical component of the vibrating force of the vibrator, and it is possible to reduce the adhesion of earth and sand to the flat plate. As described above, when the crusher is overloaded, the rotational speed of the vibrator is reduced to reduce the vibrating force, thereby reducing the horizontal component and reducing the conveying force.
As described above, since the vertical component of the excitation force is also small, the flat plate does not sufficiently vibrate up and down and adheres to the flat plate in the case of the crushed material having a large adhesiveness, thereby lowering the transport efficiency.

As disclosed in Japanese Utility Model Laid-Open Publication No. Sho 57-119781, a vibration sieve has been proposed in which the direction of the vibrating force of a vibrator is variable, but this vibrator is a rotary sieve having an eccentric weight. The direction of the exciting force is made variable by changing the meshing state of the gear attached to the shaft and the gear attached to the drive shaft, and it is very troublesome to make the direction of the exciting force variable.

Therefore, an object of the present invention is to provide a self-propelled crushing machine capable of solving the above-mentioned problems.

[0016]

A first aspect of the present invention is to provide an airframe 11 having a traveling body 10 with a crusher 1.
2. In a self-propelled crushing machine equipped with a hopper 13, and a raw material supply device 14 for conveying the material to be crushed in the hopper 13 to the crusher 12, the raw material supply device 14 is attached to a frame 19 with a sieve member, This is a self-propelled crushing machine in which a vibrator 22 is attached to a body 19 so as to be able to swing up and down around the vicinity of a point where a vibrating force acts.

According to the first aspect of the present invention, when the vibrator 22 is swung in the vertical direction, the vertical component of the vibrating force is large and the horizontal component is small, so that the sieve capacity of the raw material supply device 14 is not reduced. The transfer capacity can be reduced.

As a result, the amount of transportation to the crusher 12 can be reduced while sufficiently sieving earth and sand, pebbles, etc., so that the crusher 12 can return to the normal load state in a short time when the crusher 12 is overloaded.

Further, since the vibrator 22 swings up and down around the vicinity of the point of application of the vibrating force, no excessive force acts on the mounting portion of the vibrator 22 or the like.

According to a second aspect of the present invention, there is provided a cylinder 36 for swinging the vibrator connected to the vibrator 22 and the frame 19 in the first aspect of the invention, and a first cylinder for supplying fluid pressure to the cylinder 36. Means for detecting overload of the crusher 12
This is a self-propelled crushing machine provided with a third means for oscillating the vibrator 22 in the vertical direction with the cylinder 36 by operating the first means by detecting the overload of the crusher 12.

According to the second aspect of the present invention, when the crusher 12 is overloaded, the vibrator 22 swings in the vertical direction by the cylinder 36, so that the sieve capacity of the raw material supply device 14 is not reduced and the transfer capacity is reduced. Become.

Thus, the overload state of the crusher 12 can be automatically returned to the normal load state.

Further, since the vibrator 22 swings up and down around the vicinity of the point of application of the exciting force, the force for expanding and contracting the cylinder 36 by the exciting force acts only minutely. Does not work). As a result, the fluid pressure does not become high in the cylinder 36, so that fluid leakage does not occur.

According to a third aspect of the invention, a conveyor 15 for transporting a sieved material and a crushed material is attached to the machine body 11 of the first invention, and a vibrator 22 is connected to the vibrator 22 and the frame body 19. A cylinder 36 for swinging the machine, and the cylinder 36
Means for supplying fluid pressure to the conveyor, fourth means for detecting an overload of the conveyor 15, and operation of the first means by the detection of the overload of the conveyor 15 to vertically move the vibrator 22 with the cylinder 36. This is a self-propelled crushing machine provided with fifth means for swinging in the direction.

According to the third aspect of the present invention, when the conveyor 15 is overloaded, the vibrator 22 swings in the vertical direction by the cylinder 36, so that the sieve capacity of the raw material supply device 14 is not reduced and the transfer capacity is reduced. Become.

Thus, the overload state of the conveyor 15 can be automatically returned to the normal load state.

According to a fourth aspect of the present invention, there is provided a cylinder 36 for swinging the vibrator connected to the vibrator 22 and the frame 19 in the first aspect of the invention, and a first cylinder for supplying fluid pressure to the cylinder 36. Means for detecting the actual angle of the shaker 22
Means, and seventh means for setting the angle of the vibrator 22,
A self-propelled crushing machine provided with eighth means for operating the first means so that the deviation between the target angle by the seventh means and the actual angle by the sixth means is within a specified value.

According to the fourth aspect, since the angle of the vibrator 22 can be set arbitrarily, the ratio between the sieving capacity and the transfer capacity can be arbitrarily changed and set.

According to a fifth aspect of the present invention, an airframe 1 having a traveling body 10 is provided.
1, a self-propelled crushing machine equipped with a crusher 12, a hopper 13, and a raw material supply device 14 for transporting the material to be crushed in the hopper 13 to the crusher 12.
4, a screen member is attached to the frame 19, and a vibrator 22 is attached to the frame 19 so that the vibrator 22 can swing up and down around the vibrating force application point. And a cylinder 36 for swinging the shaker,
6, a second means for detecting an overload of the crusher 12, and a first means for detecting the overload of the crusher 12 to operate the vibrator 22 with the cylinder 36. Third means for swinging in the vertical direction, ninth means for detecting the actual angle of the shaker 22,
The tenth means for detecting the actual rotation of the motor, the eleventh means for calculating the vertical component of the excitation force based on the detection values of the ninth means and the tenth means, and the eleventh means This is a self-propelled crushing machine provided with twelfth means for reducing the rotation of the vibrator 22 so that the vertical component of the vibrating force falls within a specified value.

According to the fifth aspect, when the crusher 12 is overloaded, the vibrator 22 swings vertically, and
The rotation of the vibrator 22 is reduced, and the vertical component of the excitation force is the same as in the normal case, and the horizontal component is reduced.

This makes it possible to keep the sieving capacity constant and reduce the carrying capacity, to return the overloaded crusher 12 to the normal load in a short time, and to keep the size of the sieved material constant.

According to a sixth aspect of the present invention, an airframe 1 having a traveling body 10 is provided.
1, a self-propelled crushing machine equipped with a crusher 12, a hopper 13, and a raw material supply device 14 for transporting the material to be crushed in the hopper 13 to the crusher 12.
4, a screen member is attached to the frame body 19, and a vibrator 22 is attached to the frame body 19 so as to be able to swing up and down around the vicinity of the point where the vibrating force acts, and the screen body 11 is sieved and crushed. And a first means for supplying fluid pressure to the cylinder 36, and a first means for supplying fluid pressure to the cylinder 36; A fourth means for detecting an overload of the vibrator, a fifth means for operating the first means by the overload detection of the conveyor 15 to swing the vibrator 22 in the vertical direction by the cylinder 36, Ninth means for detecting the actual angle of 22;
Tenth means for detecting the actual rotation of the vibrator 22, eleventh means for calculating a vertical component of the vibrating force based on the detected values of the ninth means and the tenth means, This is a self-propelled crushing machine provided with twelfth means for reducing the rotation of the vibrator 22 so that the vertical component of the vibrating force calculated by the means falls within a specified value.

According to the sixth aspect, when the conveyor 15 is overloaded, the vibrator 22 swings in the vertical direction, and the rotation of the vibrator 22 is reduced. And the horizontal component becomes smaller.

Thus, the conveying capacity can be reduced while the sieving capacity is always constant, and the conveyor 15 in the overloaded state can be returned to the normal load in a short time, and the size of the sieved material can be always fixed.

According to a seventh aspect of the present invention, an airframe 1 having a traveling body 10 is provided.
1, a self-propelled crushing machine equipped with a crusher 12, a hopper 13, and a raw material supply device 14 for transporting the material to be crushed in the hopper 13 to the crusher 12.
4 is a self-propelled crushing machine in which a flat plate 20 is attached to a frame 19, and a vibrator 22 is attached to the frame 19 so as to be able to swing up and down around the vicinity of the point where the exciting force acts.

According to the seventh aspect of the present invention, when the vibrator 22 is vertically swung, the vertical component of the vibrating force is large and the horizontal component is small, so that the vertical vibration of the raw material supply device 14 is reduced. Transport capacity can be reduced without using

By this, the amount of conveyance to the crusher 12 can be reduced while preventing the sticky crushed material from adhering, so that when the crusher 12 is overloaded, it can be returned to the normal load state in a short time, The crushed material does not adhere to the frame, the flat plate or the like, and the transport efficiency does not decrease.

Further, since the vibrator 22 swings up and down around the vicinity of the point where the vibrating force acts, no excessive force acts on the mounting portion of the vibrator 22 or the like.

[0039]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in FIGS. 2 and 3, a crusher 12, a hopper 1
3. A self-propelled crushing machine is provided with a raw material supply device 14, a conveyor 15 and the like.

The crusher 12 is attached to the middle part of the body 11 in the running direction, and the moving teeth 1
This is a jaw-type crusher in which an inlet and an outlet are formed by attaching 6a and fixed teeth 16b in a V-shape. By oscillating the moving teeth 16a toward the fixed teeth 16b with the eccentric shaft, the crushed material input from the input port is crushed, and the crushed pieces fall onto the conveyor 15 from the output port.

The hopper 13 is mounted on a support column 17 near the front end of the body 11. A raw material supply device 14 is provided below the bottom discharge port 18 of the hopper 13.
The raw material supply device 14 has a frame 19 to which a flat plate 20 and a sieve member, for example, a grizzly river 21 are attached.
2 is attached. A frame 19 is mounted near the front end of the body 11 via an elastic member 23, and its flat plate 20 is located below the bottom outlet 18 of the hopper 13.

The grizzly bar 21 is divided into two parts in the conveying direction.
0 overlaps, and the grizzly river 21 on the carry-out side overlaps the oblique loading plate 24. The sieved material such as earth and sand, pebbles, etc., which has fallen from between the grizzly rivers 21 falls on the conveyor 15 by the chute 25.

As shown in FIGS. 4 and 5, the vibrator 22 has a pair of rotating shafts 31, 31 rotatably provided in a casing 30, and an eccentric weight 32 is opposed to the rotating shafts 31 in the same direction. And a conventionally known structure for rotating the rotation shaft 31 thereof. The casing 30 serves as the raw material supply device 14.
The bracket 19 is attached to the frame 19 with a bracket 34 and pins 35 so as to be vertically swingable. A cylinder 36 is connected between the casing 30 and the frame 19, and the cylinder 3
When the piston rod 37 of No. 6 expands and contracts, the casing 30 swings up and down with respect to the frame 19.

The swing center of the casing 30 (pin 3
5) is near the bisecting position of a straight line connecting the centers of the pair of rotating shafts 31, 31, that is, near the action point of the excitation force. In FIG. 4, the oscillation center and the excitation force are the same.

Thus, in the state shown in the figure, the direction of the vibrating force of the vibrator 22 is the A direction,
When the piston rod 37 of the cylinder 36 extends and operates, the direction of the exciting force changes in the direction B (horizontal), and when the piston rod 37 of the cylinder 36 contracts and operates, the direction of the exciting force changes in the direction C (vertical). Change).

As described above, at normal times, the direction of the vibrating force of the vibrator 23 is set to 40 to 50 degrees, and the conveying capacity and the sieving capacity of the raw material supply device 14 are made substantially equal.

When the crusher 12 is overloaded,
By contracting the piston rod 37 of the cylinder 36 and setting the direction of the exciting force of the exciter 23 to 45 degrees or more in the vertical direction, the conveying capacity of the raw material supply device 14 is reduced and the sieve capacity is increased.

Next, the control device will be described. As shown in FIG. 6, the pressure oil discharged from the hydraulic pump 40 is supplied to a crusher hydraulic motor 45 by a crusher directional control valve 41, a directional control valve 42 for a conveyor, a directional control valve 43 for a raw material supply device, and a directional control valve 44 for a cylinder. , The hydraulic motor 46 for the conveyor, the hydraulic motor 47 for the raw material supply device, and the cylinder 36 that swings the vibrator 23.

The crusher hydraulic motor 45 swings the moving teeth of the crusher 12. The conveyor hydraulic motor 46 rotates a drive pulley of the conveyor 15. The material supply device hydraulic motor 47 rotates a pair of rotating shafts 31 of the vibrator 23.

The directional control valves 41, 42, 43 are held at a neutral position a by springs, and pressure receiving portions 41a, 42a,
It is pushed toward the supply position b in proportion to the pressure of the pressure oil supplied to 43a. The pressure receiving portions 41a, 42a, 43a have first, second, and third electromagnetic proportional pressure control valves 48, 49, 50, respectively.
Supplies the discharge pressure oil of the hydraulic pump 51.

The cylinder direction control valve 44 is held at the neutral position a by a spring, and is pushed toward the first supply position b in proportion to the pressure of the pressure oil supplied to the first pressure receiving portion 44a. It is pushed toward the second supply position c in proportion to the pressure of the pressure oil supplied to the portion 44b. The first pressure receiving section 44
The pressure oil of the hydraulic pump 51 is supplied to a by the fourth electromagnetic proportional pressure control valve 52, and the pressure oil of the hydraulic pump 51 is supplied to the second pressure receiving portion 44 b by the sixth electromagnetic proportional pressure control valve 53.

The first, second, third, fourth, and fifth electromagnetic proportional pressure control valves 48, 49, 50, 52, and 53 are proportional to the amounts of electricity supplied to the solenoids 48a, 49a, 50a, 52a, and 53a. Output pressure. Each of the solenoids 48a,
49a, 50a, 52a and 53a have a controller 54
Is controlled.

The controller 54 includes an operation panel 55
A start / stop signal is input from the controller. The crusher overload signal is input to the controller 54 from the crusher overload detecting means 56. The controller 54 receives a supply speed signal from a supply speed dial 57. The controller 54 receives a conveyor overload signal from the conveyor overload detecting means 58. A crusher overrun signal is input from the crusher overrun detection means 59 to the controller 54. The angle of the vibrator 22 (casing 30) with respect to the horizontal is input from the angle sensor 60 to the controller 54. The controller 54 includes a cleaning unit 6
1, a cleaning signal is input. Controller 5
4 receives a sieve overload signal from the sieve overload detecting means 62.

Next, the operation will be described. When a start signal is input from the operation panel 55 to the controller 54, the controller 54 applies a predetermined current to each of the solenoids 48a, 49a, and 50a. Each electromagnetic proportional control valve 48, 4
Reference numerals 9 and 50 output predetermined pressures, and the respective directional control valves 41 and 4
Reference numerals 2 and 43 indicate the supply position b, and the respective hydraulic motors 45 and 4
6, 47 are driven at a predetermined speed. At this time, the cylinder direction control valve 44 is at the neutral position a, and the angle of the vibrator 22 (the direction of the vibrating force) is a value corresponding to the supply speed dial 57.

As a result, the crusher 12, the raw material supply device 14, and the conveyor 15 are driven in the set normal state.
As described above, the material to be crushed charged into the hopper 13 is crushed by the crusher 12 and the sieved material and crushed pieces are discharged by the conveyor 15.

The change of the angle of the vibrator 22 by the supply speed dial 57 will be described. The magnitude (excitation force) F of the vibration of the exciter 22 is F = 2 × w × e × (2πf)
² = k × f ² = K ′ × Q ² (f is proportional to θ). Here, w is the weight of the eccentric weight, e is the turning radius of the eccentric weight,
k = 8 × w × e × π ² , Q is the supply flow rate of the hydraulic motor for the vibrator, and f is the frequency (rotation speed).

The magnitude of horizontal vibration FH is (FH = F
× cos θ), and the magnitude Fv of the vertical vibration is (Fv = F × sin θ).

From the supply speed dial 57 to the vibrator 22
Is input to the controller 54. The fourth or fifth electromagnetic proportional pressure control valve 5 is determined by the difference between the input target angle θt and the actual angle θ detected by the angle sensor 60.
The solenoids 52a and 53a are energized to set the cylinder direction control valve 44 to the first supply position b or the second supply position c, and the piston rod 37 of the cylinder 36 is extended or contracted to operate the vibrator 22. Rocks.

When the actual angle θ of the vibrator 22 matches the target angle θt, the fourth or fifth electromagnetic proportional pressure control valve 5
The energization of the solenoids 52a and 53a is stopped to set the cylinder direction control valve 44 to the neutral position a, the piston rod 37 of the cylinder 36 is stopped, and the vibrator 22 is fixed.

As described above, if the relationship between the operation angle θd of the supply speed dial 57 and the target angle θt of the vibrator 22 is shown by a solid line in FIG. It can be changed by the supply speed dial 57. In addition, you may change as shown by the virtual line in FIG.

For example, (target angle θt of vibrator 22) −
(Substantial angle θ of the vibrator 22) = When the angular deviation of the vibrator 22 is (+), the solenoid 53a of the fifth electromagnetic proportional pressure control valve 53 is energized and hydraulic oil is supplied to the second pressure receiving portion 44b. Is supplied, the cylinder direction control valve 44 is set to the second supply position c, and the piston rod 37 of the cylinder 36 is contracted and operated to swing the vibrator 22 in the vertical direction. When the actual angle θ = the target angle θt (the angle deviation becomes zero), the direction control valve 44 for the cylinder is set to the neutral position a.

When the angular deviation of the vibrator 22 is (-), the solenoid 52a of the fourth electromagnetic proportional pressure control valve 52 is energized to supply pressure oil to the first pressure receiving portion 44a, The use direction control valve 44 is set to the first supply position b, and the piston rod 37 of the cylinder 36 is extended and operated to swing the vibrator 22 in the horizontal direction. When the actual angle θ is equal to the target angle θt (the angle deviation is zero), the direction control valve 44 for the cylinder is set to the neutral position a.

When a stop signal is input from the operation panel 55 to the controller 54, the controller 54 stops energizing each of the solenoids 48a, 49a and 50a. Since each electromagnetic proportional pressure control valve 48, 49, 50 does not output pressure,
Each of the directional control valves 41, 42, 43 is in the neutral position a, and each of the hydraulic motors 45, 46, 47 is stopped.

As a result, the crusher 12, the raw material supply device 14, and the conveyor 15 are stopped.

In the above-mentioned normal driving state, the crusher overload signal is output from the crusher overload detecting means 56 to the controller 5.
4, the controller 54 energizes the solenoid 53a so that the target angle of the vibrator 22 becomes a preset θtk, and outputs the output pressure of the fifth electromagnetic proportional pressure control valve 53 to the second pressure receiving portion 44b. Supply. The cylinder direction control valve 44 is set to the second supply position c, and the piston rod 37 of the cylinder 36 contracts and operates.

As a result, the vibrator 22 of the raw material supply device 14 oscillates in the vertical direction, and the vertical component of the vibrating force is large as shown in FIG. 8A, and the horizontal component as shown in FIG. Becomes smaller, and the transfer capacity becomes smaller, so that the amount of the crusher 12 charged into the crusher 12 is reduced, and the crusher 12 is placed in the normal load state.

At this time, since the vertical component of the vibrator 22 is increased, the sieve capacity is increased without decreasing, and the sediment, small stones and the like are sufficiently sieved, and large rocks and the like are charged into the crusher 12. Sediment, pebbles, and the like are not thrown into the crusher 12.

When the vibrator 22 reaches the preset first target angle θtk in the above-described operation, the energization to the solenoid 53a of the fifth electromagnetic proportional pressure control valve 53 is stopped, and the cylinder direction control valve 44 is set to the neutral position. Cylinder 3 as a
The piston rod 37 of No. 6 is stopped, and the vibrator 22 is fixed at the first target angle θtk.

When a conveyor overload signal is input from the conveyor overload detecting means 58 to the controller 54 in the normal driving state, the controller 54 reduces the transport capacity of the raw material supply device 14 to zero or lower in the same manner as described above. I do.

As a result, the amount of the crushed material to be thrown into the crusher 3 is reduced, so that the amount of crushed pieces dropped on the conveyor 15 is reduced, and the conveyor 15 is put in the normal load state.

When the vibrator 22 reaches the preset second target angle θtc in the above-described operation, the energization of the solenoid 53a of the fifth electromagnetic proportional pressure control valve 53 is stopped, and the cylinder direction control valve 44 is set to the neutral position. a and cylinder 36
Is stopped, and the vibrator 22 is fixed at the second target angle θtc.

The first target angle θtk and the second target angle θtc are angles at which the crushed object is not conveyed to the crusher. Further, in the above-described normal driving state, the excessive input signal from the crusher
, The controller 54 lowers the transport capacity of the raw material supply device 14 in the same manner as described above. Also in this case, the vibrator 22 is fixed at the second target angle θtc.

As a result, the crusher 1
Crusher 1
2 is in a normal input state.

When a sieve overload signal is input from the sieve overload detecting means 62 to the controller 54 in the normal driving state, for example, a crushed material in which a large amount of soil with high viscosity is mixed is conveyed, and When the sediment cannot be sufficiently separated by the vertical vibration (large sieve capacity), the controller 54 swings the vibrator 22 in the vertical direction in the same manner as described above, and increases the vertical component of the vibrating force to increase the sieve capacity. Since it increases, the earth and sand, pebbles, and the like on the grease river 21 are sufficiently sieved, and a normal load state is set. An alarm is issued when the sieve overload signal is continuously input for a predetermined time or more.

When the vibrator 22 reaches the third target angle θtv set in advance in the above-described operation, the energization to the solenoid 53a of the fifth electromagnetic proportional pressure control valve 53 is stopped, and the cylinder direction control valve 44 is set to the neutral position. Then, the piston rod 37 of the cylinder 36 is stopped, and the vibrator 22 is fixed at the third target angle θtv.

FIG. 9 is a flowchart showing the above operation.
It becomes as shown in.

The cleaning means 61 is provided to the controller 54.
When a cleaning signal is input from the controller 5,
Reference numeral 4 denotes a power supply to the solenoids 50a and 53a of the third and fifth electromagnetic proportional pressure control valves 50 and 53 to set the directional control valve 43 for the raw material supply device to the supply position b and the directional control valve 44 for the cylinder.
Is set to the second supply position c to vertically swing the vibrator 22 to maximize the vertical component of the swing, maximize the sieve capacity of the raw material supply device 14, and significantly reduce the conveying force.

As a result, the grizzly river 21 can be cleaned by the sediment, small stones, etc. which adhere to the grizzly river 21 or clog between the grizzly rivers 21.

The crusher overload detecting means 56 is shown in FIG.
The pressure sensor 70 detects the pressure supplied to the crusher hydraulic motor 45 as shown in FIG.
When the detected pressure of 0 is equal to or higher than the set pressure, it is determined that an overload has occurred. In the case of an impact type crusher, the rotational speed of the crusher is detected, and when the rotational speed is equal to or less than a certain rotational speed, it is determined that an overload is present.

The crusher overload detecting means 59 is provided in FIG.
0, the inlet 1 of the body 16 of the crusher 12
An optical sensor 73 in which a light emitter 71 and a light receiver 72 are mounted to face each other near 6c. If the object to be crushed is thrown up to the height of the light emitter 71 and the light receiver 72 and the light receiver 72 does not receive light for a predetermined time or more, it is determined that the light is over thrown.

As shown in FIG. 6, the conveyor overload detecting means 58 is a pressure sensor 74 for detecting the driving oil pressure of the conveyor hydraulic motor 46. When the pressure detected by the pressure sensor 74 is higher than the installation pressure, the overload detecting means 58 is overloaded. Judge.

Further, the speed of the conveyor 15 may be detected, and it may be determined that an overload occurs when the speed is lower than a predetermined speed. Alternatively, the height of the conveyed material on the conveyor 15 and the conveyor speed may be detected, and the conveyor speed may be determined from the values. May be calculated, and when the volume is equal to or larger than a predetermined volume, it may be determined that an overload is present.

As shown in FIGS. 11 and 12, the sieve overload detecting means 62 is provided with an optical sensor 77 comprising a light emitting section 75 and a light receiving section 76 on the left and right sides of the frame 19,
If the object to be crushed accumulates at a predetermined height or more on the light receiving unit 1, the light receiving unit 76 may not receive light and may determine that the load is overloaded.

The crusher overload detecting means 56 may be configured as follows. As shown in FIG. 13, the rotation detection plate 80 is attached to the hydraulic motor 45 for crusher,
The rotation speed of the crusher hydraulic motor 45 is detected by the rotation sensor 81 facing the rotation detection plate 80, and when the rotation speed detected by the rotation sensor 81 is equal to or less than the set rotation speed, it is determined that an overload has occurred.

The crusher overload detecting means 56 may be configured as follows. As shown in FIG. 14, a rotation detection plate 83 is attached to a crusher flywheel 82 which is rotated by a crusher hydraulic motor 45 and swings the moving teeth 21, and a crusher flywheel is mounted by a rotation sensor 84 facing the rotation detection plate 83. The rotation speed of the rotation sensor 82 is detected, and when the rotation speed detected by the rotation sensor 84 is equal to or less than the set rotation speed, it is determined that an overload has occurred.

Next, a second embodiment of the control device of the present invention will be described. When the crusher overload signal, the conveyor overload signal, and the overload signal are input to the controller 54 and the shaker 22 is vertically swung, the rotation speed (frequency) of the shaker 22 is reduced to reduce the exciting force. FIG. 15 shows the vertical component FV.
The horizontal component FH is reduced as shown in FIG. 15B, with the same as in the normal driving as shown in FIG.

For example, when the crusher overload signal is input to the controller 54 and the angle of the vibrator 22 is set to the first target angle θtk, the vertical component Fv of the vibrating force F becomes Fx
(Sinθtk−sinθts)
The number of rotations of the rotating shaft 31 of the vibrator 22 is reduced to reduce the vibrating force F, and the vertical component FH is made the same as in the normal driving. θ
ts is the shaker angle before crusher overload.

More specifically, when a crusher overload signal, a conveyor overload signal, or an overload signal is input to the controller 54, the amount of electricity supplied to the solenoid 50a of the third electromagnetic proportional pressure control valve 50 is reduced to reduce the output pressure. Then, the pressure of the pressure receiving portion 43a of the raw material supply device directional control valve 43 is reduced to reduce the meter-in opening area, thereby reducing the supply flow rate to the raw material supply device hydraulic motor 47.

As a result, the number of rotations (frequency) of the rotating shaft 31 of the vibrator 22 decreases, and the vibrating force F decreases. As a result, even when the angle θ of the vibrator 22 increases, the vertical component FH is reduced. It does not increase and becomes the same as the normal driving state.

The rotation speed of the vibrator 22 is (Fv =
According to the equation of K′Q ² sin θ, Q = square root (Fvo /
k'sinθtk) is calculated and the meter-in opening area of the directional control valve 43 for the raw material supply device is controlled so that the supply flow rate of the hydraulic motor 47 for the raw material supply device becomes the calculated Q. Fvo is a vertical component of the excitation force F before each signal is input. The above operation will be described with reference to FIG. 15. When the angle of the vibrator 22 is changed from θts to θtk, the operating point of the vertical component becomes AV, but when the rotation speed of the vibrator 22 is changed as described above, the operating point becomes Becomes BV. The horizontal component changes from AH to BH.

Next, a third embodiment of the present invention (a method in which the vertical component can be accurately controlled and the horizontal component is controlled moderately) will be described. As shown in FIG.
4, a sieve capacity signal is input from the sieve capacity setting dial 90. Alternatively, the controller sets a vibrator rotation speed corresponding to a predetermined sieve capacity (vertical component). The controller 54 controls the amount of electricity supplied to the solenoid 50a of the third electromagnetic proportional pressure control valve 50 according to the input and preset sieve capacity in the same manner as described above, and meter-in the directional control valve 43 for the raw material supply device. The sieve capacity is increased or decreased by controlling the opening area to increase or decrease the supply flow rate of the hydraulic motor 47 for the material supply device, thereby changing the magnitude of the excitation force and thereby changing the magnitude of the vertical component.

FIG. 17 is a flowchart showing this operation.
It becomes as shown in. The portion D in FIG. 17 is the same as FIG.

Although the sieve member is the grizzly bar 21 in each of the above embodiments, it may be a trough or a screen.
Also, as shown in FIG. 18, the vibration exciter 22 may be vertically swung by inserting a bolt 93 into one of a plurality of holes 92 of a fixing bracket 91 and fixing the same.

In the above embodiment, the raw material supply device 14 has the flat plate 20 and the grizzly river 21.
As shown in FIG. 20, only the grizzly river 21 may be used, or only the flat plate 20 may have no sieve ability as shown in FIG.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram of a conventional vibrator.

FIG. 2 is a front view of the self-propelled crushing machine showing the embodiment of the present invention.

FIG. 3 is a plan view of FIG. 2;

FIG. 4 is a front view of a vibration exciter mounting portion.

FIG. 5 is a side view of FIG. 4;

FIG. 6 is an explanatory diagram of a configuration of a control device.

FIG. 7 is a chart showing a relationship between a supply speed dial operation angle and a shaker target angle.

FIG. 8 is a table showing changes in a vertical component and a horizontal component of an excitation force.

FIG. 9 is an operation flowchart.

FIG. 10 is a perspective view showing an example of detection of excessive crusher injection.

FIG. 11 is a front view showing an example of sieve overload detection.

FIG. 12 is a longitudinal sectional view of FIG.

FIG. 13 is an explanatory diagram showing an example of crusher overload detection.

FIG. 14 is an explanatory diagram showing another example of crusher overload detection.

FIG. 15 is a table showing changes in a vertical component and a horizontal component of an excitation force. .

FIG. 16 is an explanatory diagram of a control device showing a third embodiment of the present invention.

FIG. 17 is an operation flowchart.

FIG. 18 is a front view showing another example of mounting the shaker.

FIG. 19 is a plan view showing another example of the raw material supply device.

FIG. 20 is a plan view showing another example of the raw material supply device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Rotating shaft 2 ... Eccentric weight 10 ... Running body 11 ... Machine body 12 ... Crusher 13 ... Hopper 14 ... Raw material supply device 15 ... Conveyor 16 ... Main body 17 ... Column 18 ... Bottom discharge port 19 ... Frame 20 ... Flat plate 21 ... Grizz River 22 ... Exciter 23 ... Elastic member 24 ... Putting plate 25 ... Chute 30 ... Casing 31 ... Rotating shaft 32 ... Eccentric weight 34 ... Bracket 35 ... Pin 36 ... Cylinder 37 ... Piston rod 40 ... Hydraulic pump 41 ... Crusher direction Control valve 41a ... Pressure receiving part 42 ... Conveyor direction control valve 42a ... Pressure receiving part 43 ... Raw material supply device directional control valve 43a ... Pressure receiving part 44 ... Cylinder direction control valve 44a ... First pressure receiving part 44b ... Second pressure receiving part 45 ... Hydraulic motor for crusher 46 ... Hydraulic motor for conveyor 47 ... Hydraulic motor for raw material supply device 48 ... No. Solenoid proportional pressure control valve 48a solenoid 49 second solenoid proportional pressure control valve 49a solenoid 50 third solenoid proportional pressure control valve 50a solenoid 51 hydraulic pump 52 fourth solenoid proportional pressure control valve 42a solenoid 53 Fifth electromagnetic proportional pressure control valve 53a Solenoid 54 Controller 55 Operation panel 56 Crusher overload detection means 57 Supply speed dial 58 Conveyor overload detection means 59 Crusher overload detection means 60 Angle sensor 61 Cleaning Means 62: Sieve overload detecting means 70: Pressure sensor 71: Light emitter 72: Light receiver 73: Optical sensor 74: Pressure sensor 75: Light emitting unit 76: Light receiving unit 77: Optical sensor 80: Rotation detecting plate 81: Rotation sensor 82 ... Crusher flywheel 83 ... rotation detection plate 8 ... rotation sensor 90 ... sieve capacity setting dial 91 ... fixing bracket 92 ... hole 93 ... bolt

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Satoru Koyanagi 3-20-1 Nakase, Kawasaki-ku, Kawasaki-shi, Kanagawa Prefecture Inside the Construction Robot Division of Komatsu Ltd. (72) Inventor Katsuhiro Ikegami 3 Nakase, Kawasaki-ku, Kawasaki-shi, Kanagawa-ken -20-1 Inside the Construction Robot Division of Komatsu Ltd.

Claims (7)

[Claims] 1. A self-propelled crushing machine in which a crusher 12, a hopper 13, and a raw material supply device 14 for transporting a crushed object in the hopper 13 to a crusher 12 are attached to an airframe 11 having a traveling body 10. The supply device 14 is attached with a sieve member on the frame 19,
A self-propelled crushing machine in which a vibrator 22 is mounted on the frame 19 so as to be able to swing up and down around the vicinity of a point where a vibrating force acts. 2. A cylinder 36 for swinging the shaker connected to the shaker 22 and the frame 19, a first means for supplying fluid pressure to the cylinder 36, and a crusher 1
The second means for detecting the overload of the cylinder 2 and the first means for detecting the overload of the crusher 12 actuate the cylinder 3
The self-propelled crushing machine according to claim 1, further comprising a third means for swinging the vibrator 22 in the vertical direction in (6). 3. A conveyer 15 for conveying a sieved material and a crushed material is attached to the machine body 11, and the vibrator 22 and the frame 1
Cylinder 36 for rocking the shaker connected to 9
First means for supplying fluid pressure to the cylinder 36, fourth means for detecting an overload of the conveyor 15, and operation of the first means by the overload detection of the conveyor 15 to apply a pressure to the cylinder 36. Fifth swinging of the shaker 22 in the vertical direction
2. The self-propelled crushing machine according to claim 1, further comprising: 4. A vibrator shaker cylinder 36 connected between the vibrator 22 and the frame 19, first means for supplying fluid pressure to the cylinder 36, Sixth means for detecting the actual angle, seventh means for setting the angle of the vibrator 22, and the deviation between the target angle by the seventh means and the actual angle by the sixth means within a specified value. And means for activating said first means so as to perform said operation.
Self-propelled crushing machine as described. 5. A self-propelled crushing machine in which a crusher 12, a hopper 13, and a raw material supply device 14 for transporting a crushed object in the hopper 13 to a crusher 12 are attached to an airframe 11 having a traveling body 10. The supply device 14 is attached with a sieve member on the frame 19,
The vibrator 22 is mounted on the frame 19 so as to be vertically swingable around the vicinity of the point where the vibrating force acts, and a cylinder 36 for rocking the vibrator connected to the vibrator 22 and the frame 19 is provided. First means for supplying fluid pressure to the cylinder 36, second means for detecting an overload of the crusher 12, and operation of the first means by the overload of the crusher 12 Shaker 22
, A ninth means for detecting the actual angle of the vibrator 22, a tenth means for detecting the actual rotation of the vibrator 22, and a ninth means. And calculating the vertical component of the excitation force based on the detection value of the tenth means.
A self-propelled crushing machine comprising: means for reducing the rotation of the vibrator 22 such that the vertical component of the vibrating force calculated by the eleventh means falls within a specified value. 6. A self-propelled crushing machine in which a crusher 12, a hopper 13, and a raw material supply device 14 for transporting crushed materials in the hopper 13 to a crusher 12 are attached to an airframe 11 having a traveling body 10. The supply device 14 is attached with a sieve member on the frame 19,
A vibrator 22 is mounted on the frame 19 so as to be able to swing up and down around the vicinity of the point of application of the vibrating force, and a conveyor 15 for transporting the sieved material and the crushed material is mounted on the body 11. A vibrator swing cylinder 36 connected across the frame 22 and the frame 19, first means for supplying fluid pressure to the cylinder 36, fourth means for detecting overload of the conveyor 15, Fifth means for operating the first means by the overload detection of the conveyor 15 to swing the vibrator 22 in the vertical direction by the cylinder 36, and ninth means for detecting the actual angle of the vibrator 22 A tenth means for detecting the actual rotation of the vibrator 22, an eleventh means for calculating a vertical component of the vibrating force based on the detected values of the ninth means and the tenth means, Excitation so that the vertical component of the excitation force calculated by the means of 11 is within the specified value Self-propelled crushing machine provided with twelfth means for reducing the rotation of the machine 22. 7. A self-propelled crushing machine in which a crusher 12, a hopper 13, and a raw material supply device 14 for transporting a crushed object in the hopper 13 to a crusher 12 are attached to an airframe 11 having a traveling body 10. A self-propelled crushing machine in which the supply device 14 has a flat plate 20 mounted on a frame 19 and a vibrator 22 mounted on the frame 19 so as to be able to swing up and down around the vicinity of a point where a vibrating force acts.