JP2001121023A - Hydraulic drive device of self-traveling type crusher - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance work efficiency by shortening a reversal operation. SOLUTION: A changeover valve 32 changed over corresponding to the normal rotation control signal Sa or reversal control signal Sb form a controller 33 and using the pressure from a pilot pump 19 to form normal rotation pilot pressure or reversal pilot pressure to output the same, first normal rotation pilot pipelines 35a, 35b and second normal rotation pilot pipelines 35a, 35c for guiding normal pilot pressure, reversal pressure pilot pipelines 36a, 36b, 36c for guiding reversal pilot pressure, a hydraulic drive cylinder device 23 for adjusting the angle of inclination of the inclined plate 12a of a variable capacity type crushing hydraulic motor 12 for driving a crusher 3 and a capacity adjusting pilot pipeline 37 for guiding the reversal pilot pressure to the cylinder device 23 are provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic drive device for a self-propelled crusher having a crushing device for crushing an object to be crushed, such as a roll crusher or a shredder.
The present invention relates to a hydraulic drive device for a self-propelled crusher capable of improving work efficiency.

[0002]

2. Description of the Related Art Crushers are used for various types of large and small rocks, construction wastes, industrial wastes, and natural stones generated at construction sites, such as concrete lumps carried out when dismantling buildings and asphalt lumps discharged during road repairs. Etc. are crushed to a predetermined size at the work site before transportation. In such a crusher, a self-propelled crusher has been already proposed in which the crusher can be driven by itself and has mobility based on the background of difficulty in securing land for the crushing plant or decentralization of the land. .

This self-propelled crusher includes a traveling body having left and right crawler tracks, a crushing device provided above the traveling body, and a conveyor provided below the traveling body. The crushed material placed in the hopper at the top of the machine is crushed to a predetermined size by the crushing device, and the crushed material falls from the space below the crushing device onto the conveyor and is conveyed. The crusher is delivered from the front or rear of the crusher.

At this time, the endless track, the crushing device, and the conveyor are driven by corresponding hydraulically driven actuators. That is, the hydraulic driving device of the self-propelled crusher including these hydraulic actuators is driven by, for example, at least one variable displacement hydraulic pump driven by one prime mover and pressure oil discharged from the hydraulic pump. And the traveling hydraulic motor, the crushing hydraulic motor, and the conveyor hydraulic motor that respectively drive the endless track, crushing device, and conveyor, and the direction and flow rate of hydraulic oil supplied to the hydraulic motors from the hydraulic pump. , And the hydraulic oil discharged from the hydraulic pump is supplied to each hydraulic motor via each control valve.

[0005] By the way, several types of crushing devices have already been proposed. For example, a cutter is fixed to each of a plurality of rotating shafts arranged substantially in parallel so as to bite the crushed material. A shear-type crushing device that shears finely (a biaxial shearing machine including a so-called shredder, etc.) or a roll-shaped rotating body with a crushing blade (bit) attached as a pair, and rotating the pair in opposite directions, A rotary crushing device (e.g., a 6-axis crusher including a so-called roll crusher) for crushing an object to be crushed between the rotating bodies, and a crushing object between the fixed teeth by oscillating moving teeth. A crushing device equipped with a jaw crusher for crushing by sandwiching the plate, a striking plate with a plurality of blades is rotated at a high speed, and the striking from the striking plate and the collision with the repelling plate are used. There is a crushing device equipped with a so-called impact crusher that crushes crushed materials impactfully, and a wood crushing device that turns wood such as wood, branch wood, construction waste wood, etc. into a rotor equipped with a cutter to make it into small pieces. is there.

[0006] In these various crushing apparatuses, the optimum object to be crushed is different from the viewpoint of their performance. Therefore, which crushing apparatus is used is appropriately selected according to the type of crushed object to be crushed. Is usually the case. Here, during the crushing operation as described above, if a crushed object or a non-crushable foreign substance having a size or amount exceeding the crushing ability of the crushing device is input, the crushed device is clogged with the crushing device. This may cause the crusher to stop or break.

To cope with such a problem, for example, as disclosed in JP-A-8-24704, a variable displacement type in which the crushing device is driven by pressurized oil discharged from at least one hydraulic pump. In a hydraulic drive device of a self-propelled crusher having a crushing hydraulic motor, a forward rotation load detecting means for detecting a load at the time of the forward rotation operation of the crushing hydraulic motor is provided. If it does, the tilting angle of the hydraulic motor for crushing is increased to increase the crushing force by low-speed high-pressure operation to increase the crushing force, enabling crushing of crushable objects that are difficult to crush. A configuration has been proposed in which when the predetermined value or more is exceeded, it is regarded as an overload state in which an uncrushable object or foreign matter has been introduced, and the hydraulic motor for crushing is reversely rotated (reversely rotated).

As described above, in a shearing crusher or a rotary crusher, by rotating a cutter or a blade around a rotation axis, an object to be crushed is sheared or co-operated with an adjacent cutter or a blade. This is a method of crushing, and when an uncrushable object or foreign matter gets caught between the adjacent cutter and blade, it can be escaped immediately by reversing it.
Therefore, although not particularly clearly shown in the above-mentioned known examples, the above configuration is considered to be particularly suitable for a self-propelled crusher equipped with a shear crusher or a rotary crusher. .

[0009]

In the above prior art, when a non-crushable material or foreign matter is input, the non-crushable material or foreign material is caused to escape from a biting state by reversing the crushing hydraulic motor. , To prevent the crushing device from being stopped or damaged.

However, this conventional technique has the following problems. That is, when the tilting angle of the crushing hydraulic motor during the forward rotation operation and the reverse rotation operation is the same, and the crushing hydraulic motor is rotated in the reverse direction from the state where the tilting angle of the crushing hydraulic motor is increased at the time of normal rotation high load. Because
The crushing hydraulic motor rotates in the reverse direction with the large tilt angle (= low speed and high pressure state). However, crushing work is not normally performed during reverse rotation, except for a special crushing device that is configured to perform crushing at another location even during reverse rotation. That is,
Although almost no crushing force is required at the time of reverse rotation, in the above-mentioned conventional technology, low-speed high-pressure operation is wastefully performed, and a long reverse rotation time is required. For this reason, the time required for the entire crushing operation is increased, and the work efficiency is reduced.

The present invention has been made in view of the above problems, and has as its object to provide a hydraulic drive device for a self-propelled crusher capable of improving work efficiency by shortening a reverse operation time. It is in.

[0012]

Means for Solving the Problems (1) In order to achieve the above object, the present invention is provided in a self-propelled crusher for crushing an object to be crushed by a crushing device, and discharges from at least one hydraulic pump. In a hydraulic drive device of a self-propelled crusher having a variable displacement type crushing hydraulic motor that drives the crushing device with the pressure oil to be applied, depending on whether the crushing hydraulic motor performs forward rotation operation or reverse rotation operation, A control means for switching and controlling the capacity of the crushing hydraulic motor is provided.

Thus, the capacity of the crushing hydraulic motor can be reduced during a reverse rotation operation requiring almost no crushing force, for example, as compared with a forward rotation operation. Accordingly, the crushing hydraulic motor can be rotated at a higher speed during the reverse rotation operation than when the capacity of the crushing hydraulic motor during the reverse rotation operation is the same as that during the forward rotation operation.
Therefore, the time required for the reverse rotation operation can be reduced, and the time required for the entire crushing operation can be shortened, so that the operation efficiency can be improved.

(2) In the above (1), preferably,
The control means reduces the capacity of the crushing hydraulic motor during the reverse rotation operation as compared with the normal rotation operation.

(3) In the above (1), preferably, the control means includes a motor capacity adjusting means for changing a capacity of the crushing hydraulic motor, and a forward rotation operation or a reverse rotation operation of the crushing hydraulic motor. Adjusting operation control means for controlling the adjusting operation by the motor capacity adjusting means.

(4) In the above (3), more preferably, the adjusting operation control means outputs a control signal corresponding to whether the crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation. Signal output means, pilot pressure generation means for generating and outputting a pilot pressure according to the control signal, and a capacity adjustment pilot conduit for guiding the pilot pressure to the motor capacity adjustment means, wherein the motor capacity adjustment means Changes the capacity of the hydraulic motor for crushing in accordance with the pilot pressure guided through the pilot pipe for capacity adjustment.

(5) In the above (1) or (2), preferably, the apparatus further comprises a normal rotation load detecting means for detecting a load during the normal rotation operation of the crushing hydraulic motor, and the control means includes: The capacity of the crushing hydraulic motor is controlled according to the detected load of the forward rotation load means.

Thus, for example, when the load at the time of forward rotation of the crushing hydraulic motor detected by the forward rotation load detecting means becomes large, the crushing hydraulic motor is automatically rotated in the reverse direction. However, the capacity of the crushing hydraulic motor can be immediately reduced correspondingly.

(6) In the above (1) or (2), preferably, the apparatus further comprises a reverse rotation instruction means for inputting an instruction by the operator to perform the reverse rotation operation of the crushing hydraulic motor, and the control means comprises: The capacity of the crushing hydraulic motor is controlled according to an instruction input from the reverse rotation instruction means.

Accordingly, even when the crushing hydraulic motor is operated in reverse by manual operation of the operator, the capacity of the crushing hydraulic motor can be immediately reduced, for example.

(7) In the above (1) or (2), preferably, at least two hydraulic pumps are provided, and when the crushing hydraulic motor rotates forward, two hydraulic pumps are used. The hydraulic oil supply path is such that the hydraulic oil is combined and supplied to the crushing hydraulic motor, and that only the hydraulic oil from one hydraulic pump is supplied to the crushing hydraulic motor during the reverse rotation operation of the crushing hydraulic motor. Is provided.

Normally, an energy saving effect can be obtained by reducing the number of pressure oil supply pumps at the time of the reverse operation without performing the crushing operation to half of the number of pressure oil supply pumps at the time of the forward operation.

(8) In any one of the above (1) to (7), preferably, the crushing device fixes a cutter to each of a plurality of rotating shafts arranged substantially in parallel,
A shearing type crushing device that bites the object to be crushed and shears, or a pair of crushing blades attached to a substantially roll-shaped rotating body, and rotates the pair in opposite directions to each other, between the rotating bodies. A rotary crusher that crushes the crushed object so as to bite it.

(9) In order to achieve the above object, the present invention also provides a self-propelled crusher provided in a self-propelled crusher for crushing an object to be crushed introduced from a hopper by a crusher, and driven by a prime mover. A second hydraulic pump, a variable displacement crushing hydraulic motor that includes a swash plate with a variable tilt angle, and drives the crushing device with pressure oil discharged from the first and second hydraulic pumps; Hydraulic pressure of a self-propelled crusher having a hydraulic pilot type first control valve and a second control valve for controlling the direction and flow rate of pressure oil supplied from the first and second hydraulic pumps to the crushing hydraulic motor, respectively. In the driving device, a pressure sensor connected to a pressure oil supply pipe on a side on which the crushing hydraulic motor performs a normal rotation operation, and the crushing hydraulic motor is operated in the normal rotation operation or in accordance with a detection pressure of the pressure sensor. A controller for outputting a normal rotation control signal or the reverse rotation control signal for reversing the operation is switched in response to said forward control signal or the reverse rotation control signal,
A switching valve for generating and outputting a forward rotation pilot pressure or a reverse rotation pilot pressure using a pressure from a hydraulic pressure source, and a first forward rotation guide pressure for guiding the forward rotation pilot pressure to the first control valve and the second control valve, respectively. Drive adjustment of a pilot line and a second forward rotation pilot line, a reverse rotation pilot line for guiding the reverse rotation pilot pressure to the first control valve, and a tilt angle of the swash plate of the crushing hydraulic motor. A hydraulic pressure driven cylinder device; and a capacity adjustment pilot line for guiding the reverse rotation pilot pressure to the cylinder device. The first control valve receives the forward rotation pilot pressure from the normal rotation pilot line. When this is done, the hydraulic oil from the first hydraulic pump is supplied to the hydraulic oil supply line on the side where the crushing hydraulic motor rotates forward. When switching to the forward rotation conducting position and when reverse rotation pilot pressure is introduced from the reverse rotation pilot line, the hydraulic oil from the first hydraulic pump is driven by the hydraulic oil on the side on which the crushing hydraulic motor rotates in the reverse direction. The second control valve is switched to the reverse rotation conducting position for supplying to the supply pipeline, and the second control valve supplies the hydraulic oil from the second hydraulic pump when the forward rotation pilot pressure is introduced from the forward rotation pilot pipeline. When the crushing hydraulic motor is switched to the conducting position for supplying to the pressure oil supply line on the side on which the crushing operation is performed, and when the forward rotation pilot pressure is not introduced, the crushing hydraulic pressure is supplied from the second hydraulic pump to the crushing hydraulic pressure. It is switched to the cutoff position where it is not supplied to the motor.

[0025]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a side view showing the entire structure of a self-propelled crusher to which the present invention is applied, and FIG.
It is a top view of the self-propelled crusher shown in FIG.

In FIGS. 1 and 2, the self-propelled crusher 1 uses a work implement such as a bucket of a hydraulic shovel, for example, to crush objects (for example, concrete blocks taken out when dismantling a building or asphalt discharged during road repair). A hopper 2 that receives rocks, construction wastes, etc., which are variously large and small rocks, construction wastes, industrial wastes, natural stones, etc. generated at the construction site such as lump, and which are referred to as rocks and construction wastes as appropriate. And a crusher main body 4 equipped with a crusher (in this example, a biaxial shredder) 3 for crushing rocks, construction waste materials, and the like received in the hopper 2 to a predetermined size and discharging the crushed rocks and construction waste materials downward. Traveling body 5 provided below
And a conveyor 6 for receiving the crushed material crushed by the crushing device 3 and discharged downward, transporting the crushed material to the rear side of the crusher 1 (the right side in FIGS. 1 and 2), and carrying out the conveyor.

The traveling body 5 includes a track frame 7
And left and right crawler tracks 8 as running means. The track frame 7 is formed of, for example, a substantially rectangular frame, and has a crusher mounting portion 7A on which the crushing device 3, the hopper 2, and a power unit 15 (described later) are mounted, and the crusher mounting portion 7A and the crusher mounting portion 7A. And a leg (not shown) connecting the left and right crawler tracks 8. The crawler track 8 includes a drive wheel 9 a and an idler 9.
b, and the crushing machine 1 is caused to travel by being provided with a driving force by left and right traveling hydraulic motors 10 provided on the driving wheel 9a side.

As shown in FIGS. 1 and 2, the crushing device 3 is mounted at the longitudinally forward end (left side in FIGS. 1 and 2) of the truck frame crusher mounting portion 7A. The hopper 2 is arranged further above the crushing device 3.

The crushing device 3 is a biaxial shearing machine (so-called shredder), and a cutter 3b is provided via a spacer 3a.
The two rotating shafts (not shown), which are attached at predetermined intervals in a comb-like shape, are arranged so as to be substantially parallel to each other and to allow the cutters 3b to alternately mesh with each other. By rotating the rotating shafts in opposite directions, the rock and construction waste supplied from the hopper 2 are caught between the cutters 3b and 3b and sheared into strips, and crushed to a predetermined size. It is supposed to. At this time, the driving force to the rotating shaft is generated in the drive device 11 provided on the rear side of the crushing device 3 on the track frame crusher attachment portion 7A (that is, in the longitudinal middle portion of the track frame crusher attachment portion 7A). Hydraulic motor 1
Given from 2.

The conveyor 6 has a support member (not shown) on the transport side (rear side of the crusher, right side in FIGS. 1 and 2).
And is supported by a power unit 15 to be described later. The portion on the opposite side to the transport side (the front side of the crusher, the left side in FIGS. 1 and 2) is located below the track frame crusher mounting portion 7A, and is supported by a support member (not shown). It is supported so as to be suspended from the mounting portion 7A. The conveyor 6 drives a belt 6a (the same) by a conveyor hydraulic motor 13 (see FIG. 2), and thereby transports the crushed material dropped from the crushing device 3 onto the belt 6a.

The above-mentioned truck frame crusher mounting section 7
A power unit 15 is mounted on the upper part of the rear end in the longitudinal direction of A (the right side in FIGS. 1 and 2) via a power unit stacking member 14 (see FIG. 1).

The power unit 15 includes the left and right traveling hydraulic motors 10, the crusher hydraulic motors 12,
And hydraulic pumps 17 and 18 (not shown, see FIG. 3 described later) for discharging pressure oil to hydraulic actuators such as a hydraulic motor 13 for a conveyor, and an engine 16 (the same) as a prime mover for driving the hydraulic pumps. A control valve device (not shown) including a plurality of control valves 20 and 21 (the same) for controlling the flow of the pressure oil supplied from the hydraulic pump to the hydraulic actuator is built in.

The front side of the power unit 15 (FIG. 1)
2 is provided with a driver's seat 16 on which an operator rides. The operator stands in the driver's seat 16 to monitor the crushing state of the crushing device 3 to some extent during the crushing operation. Is available.

Here, the crushing device 3, the conveyor 6, and the traveling body 5 constitute a driven member driven by a hydraulic drive device provided in the self-propelled crusher 1.
FIG. 3 is a hydraulic circuit diagram showing an essential configuration of the crushing hydraulic motor 12 in one embodiment of the hydraulic drive device for a self-propelled crusher of the present invention.

In FIG. 3, the hydraulic drive unit includes the engine 16 and the variable displacement type first hydraulic pump 17 and the second hydraulic pump 18 driven by the engine 16. Fixed-pump type pilot pump 19, the crushing hydraulic motor 12 to which pressure oil discharged from the first and second hydraulic pumps 17 and 18 is supplied, respectively, and the first and second hydraulic pumps 17 and 18 First and second control valves 20 and 21 for controlling the flow (direction and flow rate) of pressure oil supplied to the crushing hydraulic motor 12 from the crusher main body 4
(For example, in the above-mentioned driver's seat 16), and has an operation panel 22 for an operator to input and operate a start / stop of the crushing device 3, the conveyor 6, and the like.

The crushing hydraulic motor 12 generates a driving force for operating the crushing device 3 as described above.
This is a variable displacement motor whose displacement can be changed by changing the tilt angle of 2a. The tilt angle of the swash plate 12a is driven and adjusted by a hydraulically driven cylinder device 23. That is, the cylinder device 23 includes a rod portion 23a connected to the swash plate 12a, a spring member 23b for urging the rod portion 23a leftward in FIG.
When pressure oil is introduced into the bottom-side oil chamber 23c via a capacity adjusting pilot line 37, the tilt angle of the swash plate 12a is reduced against the urging force of the spring member 23b. When the pressure oil is no longer introduced into the bottom oil chamber 23c, the tilting angle of the swash plate 12a is increased by the urging force of the spring member 23b.

First and second control valves 20, 2
Reference numeral 1 denotes a three-position switching valve, and a first control valve 20 is provided in a discharge line 24 of the first hydraulic pump 17 and controls pressure oil supplied from the first hydraulic pump 17 to the crushing hydraulic motor 12. The second control valve 21 is provided in the discharge line 25 of the second hydraulic pump 18 so as to control the pressure oil supplied from the second hydraulic pump 18 to the crushing hydraulic motor 12. At this time, the forward hydraulic oil supply pipe 26 (or the reverse hydraulic oil supply pipe 27) connected to the first hydraulic pump discharge pipe 24 downstream of the first control valve 20, and the second hydraulic pump discharge pipe A forward-side pressure oil supply line 28 (or a reverse-side pressure oil supply line 29) connected to the line 25 downstream of the second control valve 21 merges on the downstream side to form one forward-side pressure oil supply. Conduit 30
(Or the reverse rotation side pressure oil supply pipe line 31) to guide the pressure oil to the crushing hydraulic motor 12.

The first and second control valves 2
0 and 21 respectively have pilot drive units 20a,
A center bypass type pilot operation valve that includes 20b, 21a, and 21b and is operated using pilot pressure, and is operated by the pilot pressure generated by the switching valve 32 using the pressure generated by the pilot pump 19. You. This switching valve 32 has a solenoid driving unit 32 at both ends.
a, 32b are electromagnetic switching valves. Drive control signals Sa (corresponding to the driving of the crushing hydraulic motor 12 in the forward rotation direction) and Sb (corresponding to the driving of the crushing hydraulic motor 12 in the reverse rotation direction) from the controller 33 are supplied to the solenoid drive units 32a and 32b. Are provided, and the switching valve 32 is switched according to the input of the forward rotation control signal Sa or the reverse rotation control signal Sb.

That is, when the forward rotation control signal Sa is output from the controller 33 to the switching valve solenoid drive section 32a, the switching valve 32 is switched to the switching position 32A on the right side in FIG. Thereby, the pressure oil from the pilot pump 19 is guided to the forward rotation pilot lines 35a to 35c on the downstream side of the switching valve 32 through the discharge pipe line 34 and the switching position 32A. The first control valve 20 is guided to the pilot drive section 20a and the second control valve 21 to the pilot drive section 21a. At the same time, the pilot line 36 for reverse rotation
The pressures in a to c (details will be described later) and in the capacity adjustment pilot line 37 (same as above) are all equal to the pressure (tank pressure) of the tank 39 via the tank line 38. Thereby, the first control valve 20 is switched to the switching position 20A on the right side in FIG. 3, and the pressure oil from the first hydraulic pump 17 is supplied to the discharge line 24, the first control valve switching position 2A.
0A, and is introduced into the forward rotation side pressure oil supply line 30 via the forward rotation side pressure oil supply line 26. At this time, the second control valve 21 is simultaneously switched to the switching position 21A on the right side in FIG. The pressure oil from the second hydraulic pump 18 is supplied to the forward rotation side pressure oil supply line 3 via the discharge line 25, the second control valve switching position 21A, and the forward rotation side pressure oil supply line 28.
9 and merges with the pressure oil from the first hydraulic pump 17 in the forward rotation side pressure oil supply line 30. The pressure oil for the two combined pumps is supplied to the crushing hydraulic motor 12, and the crushing hydraulic motor 12 is driven in the forward direction (forward direction).

On the other hand, when a reverse rotation control signal Sb is output from the controller 33 to the switching valve solenoid drive section 32b,
The switching valve 32 is switched to the left switching position 32B in FIG. As a result, the pressure oil from the pilot pump 19 flows through the discharge line 34 and the switching position 32B to the switching valve 32.
It is guided to the reverse rotation pilot lines 36a to 36c on the downstream side, through which the pilot drive unit 20b of the first control valve 20 and the second
The pilot lines 35a to 35c are guided to the pilot drive unit 21b of the control valve 21 and simultaneously the forward rotation pilot lines 35a to 35c.
The pressure inside is equal to the pressure in the tank 39 via the tank line 38. Thereby, the first control valve 20 is switched to the switching position 20B on the left side in FIG. 3, and the pressure oil from the first hydraulic pump 17 is supplied to the discharge line 24, the first control valve switching position 20B, and the reverse rotation side pressure oil supply pipe. The hydraulic oil is introduced into the reverse pressure oil supply line 31 via the passage 27, and at the same time, the pressure oil from the second hydraulic pump 18 is supplied via the discharge line 25, the second control valve switching position 21B, and the reverse rotation pressure oil supply line 29. It is introduced into the reverse rotation side pressure oil supply line 31 and merges with the pressure oil from the first hydraulic pump 17. This 2
The pressure oil for the pump is supplied to the crushing hydraulic motor 12 and driven in the reverse direction (reverse direction).

At this time, the capacity adjustment pilot line 37 branches off from the reverse rotation pilot line 36a, and the switching valve 32 is generated by switching to the switching position 32B on the left side in FIG. The reverse rotation pilot pressure is introduced from the reverse rotation pilot line 36a to the capacity adjustment pilot line 37, and is guided to the cylinder device bottom side oil chamber 23c. Thus, as described above, the cylinder device 23 reduces the tilt angle of the swash plate 12a of the hydraulic motor 12 for crushing, and reduces the capacity of the hydraulic motor 12 for crushing.

When neither of the drive signals Sa and Sb is output to the switching valve solenoid drive units 32a and 32b, the switching valve 32 returns to the neutral position 32C shown in FIG. 3 by the urging force of the springs 32c and 32d. The pressures in the forward rotation pilot lines 35a to 35c, the reverse rotation pilot lines 36a to 36c and the capacity adjustment pilot line 37 are all equal to the pressure (tank pressure) of the tank 39 via the tank line 38. As a result, the first control valve 20 is moved by the biasing force of the springs 20c and 20d to the neutral position 20C shown in FIG.
And the second control valve 21 is also moved to the neutral position 21 shown in FIG. 3 by the urging force of the springs 21c and 21d.
Returning to C, the oil discharged from the first and second hydraulic pumps 17, 18 returns to the tank via the tank lines 40, 41. That is, the forward rotation side pressure oil supply line 30 and the reverse rotation side pressure oil supply line 3
Since no pressure oil is supplied to any of the above, the crushing hydraulic motor 9 stops in the state at that time.

The first and second hydraulic pumps 17, 18
And the discharge pipes 24, 25,
Relief valves 45, 46, 47 are provided in pipes 42, 43, 44 branched from 34 respectively, and the first and second hydraulic pumps 17, 18 and pilot pump 19 are provided.
The values of the relief pressures that limit the maximum values of the discharge pressures of the respective springs 45a, 46a, 47a are respectively provided.
Is set by the urging force.

The first and second hydraulic pumps 17, 18
Although the detailed description is omitted, the maximum value of the discharge flow rate is limited to a small value as the discharge pressure increases by a regulator device (not shown), and the input horsepower (input torque) of the hydraulic pumps 17 and 18 is reduced. The hydraulic pump 1 is controlled so as to have an output horsepower (output torque) of the engine 16 or less.
The tilting of the swash plates 17a and 18a of the swash plates 7 and 18 is controlled (known input torque limiting control or horsepower control).

The forward pressure oil supply line 30 and the reverse pressure oil supply line 31 are provided with pressure sensors 48 and 49 for detecting their pressures, respectively. Are the corresponding detection signals P1, P2
Is output to the controller 33.

The operation panel 22 includes a start switch (not shown) for starting the crusher 3 in the forward direction,
A stop switch (the same) for stopping the crushing device 3 is provided. When an operator operates each switch of the operation panel 22, an operation signal is transmitted to the controller 3.
3 is input. The controller 33 generates the forward rotation control signal Sa or the reverse rotation control signal Sb to the switching valve 32 based on the operation signal from the operation panel 22, and outputs them to the corresponding switching valve solenoid drive units 32a and 32b. It is supposed to.

Here, the main part of this embodiment is that, when the crushing device 3 shifts from the normal rotation operation to the reverse rotation operation, the tilting angle of the crushing hydraulic motor 12 is reduced, so that the rotation of the crushing device 3 is more reverse than in the prior art. The purpose is to reduce the time required for operation. The control contents of the controller 33 relating to this function will be described with reference to FIG.

In FIG. 4, when the start switch of the operation panel 22 is pressed, the controller 33 starts this flow. First, in step 10, a flag for identifying whether the crushing device 3 is in an overload state, a calculator T for counting the duration of the overload state, and a calculator T for counting the duration of the reverse operation. 'To 0
To clear.

Next, at step 20, it is determined whether or not the stop of the shredding device (shredder) 3 is instructed. Specifically, it is determined whether the stop switch of the operation panel 22 has been pressed. If the stop switch has been pressed, this determination is satisfied, and the routine proceeds to step 130, which will be described later, and immediately stops the crushing device 3. If the stop switch has not been pressed, this determination is not satisfied, and the routine proceeds to step 30.

In step 30, it is determined whether or not the flag is 1 indicating the overload state of the crushing device 3. In the case of an overload state, the flag is set to 1 (described later) and the determination is satisfied, so that the process proceeds to step 110 described later and immediately drives the crushing device 3 in the reverse rotation direction (described later). If the state is not an overload state, the flag is 0, so that this determination is not satisfied, and the routine goes to Step 40.

In step 40, the crushing device 3 is driven in the normal rotation direction. That is, the forward rotation control signal Sa is output to the solenoid drive unit 32a of the switching valve 32, and if the reverse rotation control signal Sb is output to the solenoid drive unit 32b, it is stopped and the switching valve 32 is switched to the switching position 32A.
, Whereby the first and second control valves 20, 21 are switched to switching positions 20A, 21A,
The pressure oil from the first and second hydraulic pumps 17 and 18 is supplied to the crushing hydraulic motor 12 through the forward rotation side pressure oil supply pipe 30 to drive the crushing device 3 in the normal rotation direction.

Thereafter, the routine proceeds to step 50, where the detection signal P of the pressure sensor 48 provided in the forward rotation side pressure oil supply pipe 30 is provided.
1 is input, and P1 is a predetermined threshold value P10
(= Set and stored appropriately so as to prevent the crushing device 3 from being stopped or damaged). P
If 1 ≦ P10, the determination is not satisfied and the crushing device 3 is considered not to be in a high load state, and the time calculator T is cleared to 0 in step 60, and then the process returns to step 20. P1> P1
If 0, the determination is satisfied and the crushing device 3 is considered to be in a high load state, and after adding 1 to the time calculator T in step 70, the process proceeds to step 80.

In step 80, T is appropriately set and stored in order to determine whether T is a predetermined threshold value T1 (= transient / temporary high load state or continuous overload state). It is determined whether it is larger.
If T≤T1, the determination is not satisfied and the routine returns to step 20 to repeat steps 20 to 80. If the high load state disappears during this repetition and P1 ≦ P10, the process goes from step 50 to step 60, and the time calculator T is cleared again. If T> T1 finally continues, the determination in step 80 is satisfied, and the crushing apparatus 3 is considered to be in an overloaded state, and the routine proceeds to step 90.

At step 90, the time calculator T is cleared to T = 0. Thereafter, in step 100, the flag is set to 1 indicating that the vehicle is overloaded, and the routine proceeds to step 110.

In step 110, the crusher 3 is driven in the reverse direction. That is, while outputting the reverse rotation control signal Sb to the solenoid driving portion 32b of the switching valve 32,
If the reverse rotation control signal Sa has been output to the solenoid drive unit 32a, it is stopped, and the switching valve 32 is switched to the switching position 32.
Switch to B. As a result, the first and second control valves 20 and 21 are switched to the switching positions 20B and 21B, and the hydraulic oil from the first and second hydraulic pumps 17 and 18 is supplied to the crushing hydraulic motor 12 via the reverse-side hydraulic oil supply line 31. To drive the crushing device 3 in the reverse direction. At the same time, the cylinder device 23 is controlled via the capacity adjustment pilot line 37.
The reverse rotation pilot pressure acts on the hydraulic motor 12 to reduce the tilt angle of the swash plate 12a of the hydraulic motor 12.

Thereafter, the routine proceeds to step 120, where the detection signal P2 of the pressure sensor 49 provided in the reverse rotation side pressure oil supply line 30 is input, and P2 is set to a predetermined threshold value P20.
(= Set and stored appropriately so as to prevent the crushing device 3 from being stopped or damaged). P
If 2 ≦ P20, the determination is not satisfied, and further action is considered to be an unfavorable state that may cause damage to the crushing device 3 and the like, and the process proceeds to the step to stop the crushing device (shredder) 3. . That is, the control signals Sa and Sb of the solenoid drive unit 32a and the solenoid drive unit 32b of the switching valve 32 are both stopped to return to the neutral position shown in FIG. 3, the crushing hydraulic motor 12 is stopped, and this flow ends. .

If it is determined in step 120 that P2> P20, it is determined that the condition is satisfied and the crushing apparatus 3 is not in an unfavorable state in which the crushing apparatus 3 may be damaged.
After adding 1 to the time calculator T 'at step 150,
Move to

In step 150, T 'is appropriately set and stored so as to be sufficient for a predetermined threshold value T2 (= the clogged crushed object / foreign matter to escape from between the cutters 3b, 3b). ) Is determined.
If T'≤T2, the determination is not satisfied and the routine returns to step 20 to repeat steps 20 to 150. However, at this time, since the flag is 1 indicating the overload state,
Step 20 → step 30 → step 110 → steps 120 to 150 are repeated. If P2> P20 during this repetition, the process goes from step 120 to step 130 and the crushing device 3 is immediately stopped.
During the repetition, P2 ≦ P20 continues and finally T ′> T2
Is satisfied, the determination in step 150 is satisfied, and it is considered that the crushing apparatus 3 has been reversed for a sufficient time, and the process proceeds to step 160.

In step 160, the time calculator T '
= 0 is cleared. Thereafter, the process proceeds to step 170, where the flag is cleared to 0, which is not an overload state, and then returns to step 20. After that, the same procedure is repeated.

In the above, the first and second control valves 20 and 21 constitute the crushing control valve described in the claims, and the forward rotation side pressure oil supply line 2
6, 28, and 30 constitute a pressure oil supply line on the side on which the crushing hydraulic motor rotates forward, and the pressure sensor 48 constitutes a pressure sensor connected to the pressure oil supply line. It also constitutes a normal rotation load detecting means for detecting a load during a normal rotation operation of the hydraulic motor.

The pilot line 37 for capacity adjustment
Constitutes a capacity adjustment pilot line that guides the reverse rotation pilot pressure to the motor capacity adjustment means.

Further, the cylinder device 23 constitutes a motor capacity adjusting means for changing the capacity of the crushing hydraulic motor. Further, the controller 33 constitutes a control signal output means for outputting a corresponding control signal according to whether the crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation, and includes a pilot pump 19, a discharge pipe line 34, and a switching circuit. The valve 32 constitutes a pilot pressure generating means for generating and outputting a pilot pressure according to the control signal, and the controller 33, the pilot pump 19, the discharge line 34, the switching valve 32, and the pilot lines 36a, 37 The adjusting operation control means controls the adjusting operation by the motor capacity adjusting means depending on whether the hydraulic motor for normal operation or the reverse rotation operation is performed. The controller 33, the pilot pump 19, the discharge line 34, the switching valve 32, and the pilot lines 36a, 3
7 and the cylinder device 23 constitute control means for switching and controlling the capacity of the crushing hydraulic motor in accordance with whether the crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation.

Next, the operation and operation of this embodiment will be described below.

In the self-propelled crusher 1 having the above configuration, the operator presses a start switch (not shown) of the operation panel 22 during crushing work. As a result, the controller 33 outputs the normal rotation control signal Sa to the switching valve solenoid drive unit 32a in step 40 through steps 10, 20, and 30 of the flow shown in FIG.
The pressure oil from the second hydraulic pumps 17 and 18 is supplied to the crushing hydraulic motor 12 via the forward rotation supply pipes 26, 28 and 30, and the crushing device 3 is activated in the forward rotation direction.

When rocks and construction wastes are put into the hopper 2 by a bucket of a hydraulic shovel, for example, the rocks and construction wastes received by the hopper 2 are guided to the crushing device 3 and crushed by the crushing device 3. It will be crushed. The crushed crushed material falls from the space below the crushing device 3 onto the conveyor 6 and is conveyed, is almost uniform in size, and is finally carried out from the rear portion of the crusher 1 (the right end in FIG. 1). You.

At this time, if the rock or construction waste put into the hopper 2 contains foreign matter that is difficult to crush by the crushing device 3 or that cannot be crushed (hereinafter referred to as foreign material), they are crushed. The pressure of the crushing hydraulic motor 12 is increased when trying to be caught between the cutters 3b, 3b of the device 3, and the pressure sensor 4 for detecting the pressure of the forward rotation supply pipe 30 is provided.
The detection signal P1 of No. 8 becomes larger than P10. As a result, the determination in step 50 of the flow in FIG. 4 is satisfied, and the process proceeds from step 70 to step 80. If this state continues for a predetermined time, the determination in step 80 is satisfied, and steps 110 and 110 are performed through steps 90 and 100. The reverse rotation control signal Sb is output from the controller 33 to the switching valve solenoid drive unit 32b, and the pressure oil from the first and second hydraulic pumps 17, 18 is supplied to the reverse rotation side supply pipes 27, 29,
The crushing device 3 is supplied to the crushing hydraulic motor 12 via the crushing device 31 and the crushing device 3 is started in the reverse direction. Thereby, the crushing device 3
The blades 3b, 3b rotate in the opposite direction, and can push out the foreign matter or the like once caught up. In this embodiment, attention is paid to the fact that almost no crushing force is required during the reverse rotation operation,
By supplying the reverse rotation pilot pressure to the cylinder device 23 through the cylinder 7, the crushing hydraulic motor 12
Capacity is reduced. Accordingly, the crushing hydraulic motor 12 can be rotated at a higher speed during the reverse rotation operation than when the capacity of the crushing hydraulic motor 12 during the reverse rotation operation is the same as that during the forward rotation operation.

In the case where the foreign matter or the like that has been input is a foreign matter that cannot be crushed, the foreign matter is caught between the cutters 3b and 3b, and the load of the crushing hydraulic motor 12 becomes large even during the reverse rotation operation. The detection signal P2 of the pressure sensor 49 for detecting the pressure in the supply line 31 becomes larger than the signal P20, and the crushing device 3 stops at step 130.

If the input foreign matter is not crushable but happens to be a crushed object having a size or an amount exceeding the crushing ability, the input crushed object is loosened by the above-described reversing operation and crushed. Therefore, the load on the crushing hydraulic motor 12 does not increase during the reverse rotation operation.
As a result, the determination in step 120 is satisfied and the process proceeds from step 140 to step 150. If this state continues for a predetermined time, the determination in step 50 is satisfied and steps 160, 170, 20, and 30 are satisfied.
In step 40, the crushing hydraulic motor 12
Is driven forward.

In this manner, the crushing operation is performed while repeating the forward rotation operation and the operation of forward rotation → reverse rotation → forward rotation. When the crushing operation is completed, the operator operates the stop switch (see FIG. Step 2 by pressing (not shown)
From 0, the process proceeds to step 130, and the crushing device 3 stops.

As described above, according to the present embodiment, when the crushing device 3 performs the reverse rotation operation, compared to the case where the capacity of the crushing hydraulic motor 12 during the reverse rotation operation is the same as that during the forward rotation operation. The crushing hydraulic motor 12 can be rotated at a higher speed. Therefore, the time required for the reverse rotation operation can be reduced, and the time required for the entire crushing operation can be shortened, so that the operation efficiency can be improved.

In the embodiment of the present invention, as shown in FIG. 3, the hydraulic oil for crushing 12 is supplied with the hydraulic oil from the two pumps 17 and 18 during both the forward rotation operation and the reverse rotation operation. Although the supply is performed by merging, the present invention is not limited to this, and the pressure oil may be supplied from only one pump during the reverse rotation operation. Such a modification will be described below.

FIG. 5 is a hydraulic circuit diagram showing a main part of a modified example of the hydraulic drive device, and corresponds to FIG. 3 in the embodiment of the present invention. The same parts as those in FIG. 3 are denoted by the same reference numerals, and description thereof will be omitted.

Referring to FIG. 5, the hydraulic drive system uses the second control valve 21 of the three-position switching valve shown in FIG.
Instead of the second control valve 1 which is a two-position switching valve
21 are provided. This second control valve 121
Has a structure in which the switching position 21B on the left side in FIG. 3 of the control valve 21 is omitted.
3 sends a forward rotation control signal S to the switching valve solenoid drive unit 32a.
a is output and the switching valve 32 is switched to the switching position 32 on the right side in FIG.
5A, the forward pilot pressure via the forward pilot lines 35a and 35c is guided to the pilot drive unit 121a as in the case of the second control valve 21 of the embodiment of the present invention. The switching position is switched to the middle right switching position 121A, and the pressure oil from the second hydraulic pump 18 is supplied to the forward rotation side pressure oil supply line 39 via the discharge line 25, the switching position 121A, and the forward rotation side pressure oil supply line 28. The oil is introduced, merges with the above-mentioned pressure oil from the first hydraulic pump 17 in the forward rotation side pressure oil supply line 30, and the pressure oil for two pumps is supplied to the crushing hydraulic motor 12.

On the other hand, when the controller 33 outputs the reverse rotation control signal Sb to the switching valve solenoid drive unit 32b, the second control valve 121 returns to the shut-off position 121B shown in FIG. 5 by the biasing force of the spring 121b. , Second
The oil discharged from the hydraulic pump 18 returns to the tank 39 via the tank line 41. That is, in the reverse rotation side pressure oil supply line 31,
Only the pressure oil from the first hydraulic pump 17 via the switching position 20B of the first control valve 20 is supplied.

When neither of the drive signals Sa and Sb is output, the second control valve 121 is in the shut-off position 121B similar to the above, and the first control valve 20 is the same as the above-described embodiment of the present invention. Similarly, the spring returns to the neutral position 20C shown in FIG. 3 by the urging force of the springs 20c and 20d, and the pressure oil is not supplied to either the forward rotation side pressure oil supply pipe 30 or the reverse rotation side pressure oil supply pipe 31.

In the above description, the second control valve 121 constitutes a control valve for crushing, the controller 33, the switching valve 32, and the pilot line 3 for normal rotation.
5a-c, the reverse pilot lines 36a and 36b, the first control valve 20, and the second control valve 121 combine the hydraulic oil from the two hydraulic pumps during the forward rotation operation of the crushing hydraulic motor so that the crushing hydraulic pressure is reduced. Supply switching means for switching the pressure oil supply path so as to supply to the motor and to supply only the hydraulic oil from one hydraulic pump to the hydraulic motor for crushing during the reverse rotation operation of the hydraulic motor for crushing.

The forward rotation pilot lines 35a, 35
5b constitutes a first forward rotation pilot line for guiding the forward rotation pilot pressure to the first control valve, and the forward rotation pilot lines 35a, 35c reduce the forward rotation pilot pressure to a second rotation.
A second forward rotation pilot line leading to the control valve is formed. Pilot lines 36a and 36b for reverse rotation
Constitutes a reverse pilot line for guiding the reverse pilot pressure to the first control valve. Further, the capacity adjustment pilot line 37 constitutes a capacity adjustment pilot line for guiding the reverse rotation pilot pressure to the cylinder device.

The switching position 20A of the first control valve 20 constitutes a forward rotation conducting position for supplying the pressure oil from the first hydraulic pump to the pressure oil supply line on the side where the crushing hydraulic motor rotates forward. The switching position 20B constitutes a reverse rotation conducting position for supplying the pressure oil from the first hydraulic pump to the pressure oil supply pipe on the side where the crushing hydraulic motor performs the reverse rotation operation. The switching position 121A of the second control valve 121 is
When the forward rotation pilot pressure is introduced from the forward rotation pilot line, a conduction position for supplying the pressure oil from the second hydraulic pump to the pressure oil supply line on the side where the crushing hydraulic motor performs the forward rotation is configured. The neutral position 121B constitutes a shut-off position in which the hydraulic oil from the second hydraulic pump is not supplied to the crushing hydraulic motor when the forward rotation pilot pressure is not introduced.

In the above-described modified example, similarly to the above-described embodiment of the present invention, the case where the capacity of the crushing hydraulic motor 12 at the time of the reverse rotation operation is the same as that at the time of the forward rotation operation is performed at the time of the reverse rotation operation of the crushing device 3. , The crushing hydraulic motor 12 can be rotated at a higher speed. Further, in the circuit of FIG. 5, the amount of pressure oil supplied to the crushing hydraulic motor 12 is originally halved during the reverse rotation operation of the crushing device 3, so that the reverse rotation operation of the crushing hydraulic motor 12 is smaller than that during the forward rotation operation. The rotation speed of the crushing hydraulic motor 12 is increased by making the capacity of the crushing hydraulic motor 12 during the reverse rotation operation smaller than that during the forward rotation operation. It is also possible to reduce the difference from the above or to make the speed higher than the rotation speed during the forward rotation operation.

Normally, by reducing the number of pressure oil supply pumps at the time of reverse rotation without performing the crushing operation to half of the number of pressure oil supply pumps at the time of normal rotation, an energy saving effect can be obtained.

Further, in the embodiment of the present invention, the operator can operate only the normal rotation start and stop of the crushing device 3 from the operation panel 22, and when the overload state occurs during the normal rotation. Although the automatic reverse rotation is only performed, the present invention is not limited to this. The operation panel 22 may be provided with a reverse rotation switch as a reverse rotation instruction means so that the operator can manually perform the reverse rotation operation. Such a modification will be described with reference to FIG.

FIG. 6 shows a control flow executed by the controller 33 in this modification. The difference from FIG. 4 in the embodiment of the present invention is that a step between steps 20 and 30 is performed. 25 is provided. That is, in step 25, it is determined whether or not the reverse switch of the operation panel 22 has been pressed, and if the determination is satisfied, the process immediately proceeds to step 110 to drive the crushing device 3 in reverse. Thereby, the crushing device 3 can be reversed at any time during the operation of the crushing device 3 in the normal rotation direction by the operator's will. Needless to say, the reversing speed at that time can be increased as described in the embodiment of the present invention.

Further, in the above embodiment of the present invention, the cylinder device 23 is driven by guiding the reverse rotation pilot pressure from the switching valve 32 through the capacity adjustment pilot line 37. However, the present invention is not limited to this. It may be driven by another method. Such a modification will be described with reference to FIGS.

FIG. 7 is a hydraulic circuit diagram showing a main configuration of a hydraulic drive device according to the above-described modified example, and is a diagram corresponding to FIG. 3 of the embodiment of the present invention. In FIG.
Pilot lines 50a, 50b branching from the pilot pump discharge line 34 and reaching the cylinder device 23
Are provided, and the pilot lines 50a, 5
An electromagnetic switching valve 51 capable of communicating and blocking 0b is provided. When the reverse rotation control signal Sb is input from the controller 33 to the solenoid driving portion 51a, the electromagnetic switching valve 51 is switched to the communication position 51A on the right side in FIG. 7 to release the hydraulic oil from the pilot line 50a to the pilot pressure for reverse rotation. As a result, the swash plate 12a of the crushing hydraulic motor 12 is guided to the cylinder device 23 via the pilot line 50b to reduce the tilt angle. The controller 3
When the reverse rotation control signal Sb is no longer input from the control line 3, the spring 51 b returns to the cutoff position 51 B shown in FIG. 7 to cut off the pilot line 50 a and the pilot line 50 b, and disconnects the pilot line 50 b from the tank 3.
9 to increase the tilt angle of the crushing hydraulic motor swash plate 12a.

In the configuration of this modification, the pilot line 50b forms a capacity adjusting pilot conduit for guiding the reverse rotation pilot pressure to the motor capacity adjusting means (the cylinder device 23). Further, the controller 33 constitutes control signal output means for outputting a corresponding control signal according to whether the crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation, and includes a pilot pump 19, a discharge pipe line 34, a pilot line 50a and the electromagnetic switching valve 51 constitute a pilot pressure generating means for generating and outputting a pilot pressure according to the control signal. The controller 33, the pilot pump 19, the discharge pipe 34, the pilot line 50a, the electromagnetic switching valve 51 , And the pilot line 50b constitute an adjusting operation control means for controlling an adjusting operation by the motor capacity adjusting means depending on whether the crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation. The controller 33, the pilot pump 19, the discharge line 34, the pilot line 50
a, the electromagnetic switching valve 51, the pilot line 50b, and the cylinder device 23 constitute control means for switching and controlling the capacity of the crushing hydraulic motor in accordance with whether the crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation. .

According to this modification, the same effects as those of the above-described embodiment of the present invention can be obtained. In addition, as shown in FIG.
The configuration of the above modification may be applied to the configuration shown in FIG.

In the above description, the tilt angle of the crushing hydraulic motor 12 at the time of reverse rotation is always a fixed value.
It is needless to say that the present invention is not limited to this, and may be varied according to, for example, the load pressure immediately before the reverse rotation. Further, in the embodiment of the present invention, the operation can be stopped at the time of normal rotation and at the time of reverse rotation by pressing the stop switch. However, the operation may not be stopped at the time of reverse rotation.

Further, in the above description, a self-propelled crusher having a two-axis shearing machine as the crushing device has been described as an example. However, the present invention is not limited to this, and a self-propelled crushing machine having a plurality of shafts may be used. It is needless to say that the present invention can also be applied to a crusher. In short, a self-propelled crusher having a shear crusher that fixes a cutter to each of a plurality of rotating shafts arranged substantially in parallel and bites an object to be crushed and shears is sufficient. Furthermore, the present invention is not limited to such a shearing type crushing device, and other crushing devices, for example, a pair of roll-shaped rotating bodies having a crushing blade attached thereto are rotated in the opposite directions to each other, and the rotation is performed. A rotary crusher (such as a 6-axis crusher including a so-called roll crusher) that crushes rocks and construction waste materials between bodies, and a striking plate equipped with a plurality of blades is rotated at high speed. A crusher equipped with a so-called impact crusher that crushes rocks and construction waste materials by using impacts from impacts and collisions with repulsion plates, A crushing device equipped with a jaw crusher that crushes a crushed material by sandwiching it, and a wood crushing device that turns wood such as wood, branch wood, construction waste wood, etc. into a rotor with a cutter to make it into small pieces It is also applicable to self-propelled crushing machine having a. In these cases, similar effects can be obtained.

Further, in the above description, the case where the present invention is applied to a self-propelled crushing machine having only the conveyor 5 as an auxiliary machine for performing work related to crushing work by the crushing device has been described, but the present invention is not limited to this. . For example, a device having a feeder 4 that transports and guides rocks, construction waste materials, and the like received in the hopper 2 to the crushing device 3 according to work circumstances, and a crushed material provided above the conveyor 5 and being transported on the conveyor 5 May be applied to those provided with a magnetic separator 6 for magnetically attracting and removing magnetic substances contained in the magnetic material.

[0090]

According to the present invention, the control means switches and controls the capacity of the crushing hydraulic motor in accordance with whether the crushing hydraulic motor performs the forward rotation operation or the reverse rotation operation. The capacity of the crushing hydraulic motor can be reduced as compared with the time of the forward rotation operation. As a result, the crushing hydraulic motor can be rotated at a higher speed during the reverse rotation operation than the conventional structure, so that the time required for the reverse rotation operation can be reduced, and the time required for the entire crushing operation can be shortened. Improvement can be achieved.

[Brief description of the drawings]

FIG. 1 is a side view showing the overall structure of a self-propelled crusher to which the present invention is applied.

FIG. 2 is a top view of the self-propelled crusher shown in FIG.

FIG. 3 is a hydraulic circuit diagram showing a configuration of a main part related to a crushing hydraulic motor in one embodiment of the hydraulic drive device of the self-propelled crusher of the present invention.

FIG. 4 is a control flow executed by the controller shown in FIG. 3;

FIG. 5 is a hydraulic circuit diagram showing a main configuration of a modified example in which only one pump supplies pressure oil during a reverse rotation operation.

FIG. 6 is a control flow executed by a controller according to a modification in which a reverse rotation operation can be manually performed by an operator.

FIG. 7 is a hydraulic circuit diagram showing a modification in which a cylinder device is driven by guiding reverse rotation pilot pressure through an electromagnetic switching valve.

8 is a hydraulic circuit diagram showing a case where the configuration of FIG. 7 is applied to the configuration of FIG.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Self-propelled crusher 2 Hopper 3 Crusher 12 Crushing hydraulic motor 12a Swash plate 16 Engine (motor) 17 1st hydraulic pump 18 2nd hydraulic pump 19 Pilot pump (hydraulic power source, pilot pressure generation means, adjustment operation control means) , Control means) 20 1st control valve (control valve for crushing) 20A switching position (conduction position for forward rotation) 20B switching position (conduction position for reverse rotation) 21 second control valve (control valve for crushing) 23 cylinder device (motor capacity) Adjustment means,
Control means) 26 forward rotation side pressure oil supply line 28 forward rotation side pressure oil supply line 30 forward rotation side pressure oil supply line 32 switching valve (pilot pressure generation means, adjustment operation control means, control means) 33 controller (control signal output) Means, adjustment operation control means, control means) 34 Discharge pipeline (pilot pressure generation means, adjustment operation control means, control means) 35a pilot line (first and second forward rotation pilot pipelines) 35b pilot line (first positive Pilot line for diversion) 35c Pilot line (pilot line for second forward rotation) 36a Pilot line (pilot line for reverse rotation, adjustment operation control means, control means) 36b Pilot line (pilot line for reverse rotation) 37 Pilot line (capacity) Adjustment pilot pipeline, adjustment operation control means, control means) 48 Pressure sensor (forward rotation load detection) Stage) 50a pilot line (the pilot pressure generating means, adjusting operation control means, the control means) 50b pilot line (capacity adjusting pilot line, adjusting operation control means, the control means) 51 electromagnetic switching valve (pilot pressure generating means,
Adjusting operation control means, control means) 121 Second control valve (crushing control valve) 121A Switching position (conduction position) 121B Switching position (cutoff position)

 ────────────────────────────────────────────────── ─── Continuing from the front page (72) Yoshimi Shiba 650, Kandachi-cho, Tsuchiura-shi, Ibaraki F-term inside the Tsuchiura Plant of Hitachi Construction Machinery Co., Ltd. 3H089 AA61 AA65 BB15 CC09 DA03 DA06 DA13 DB03 DB46 DB49 EE04 EE22 EE36 FF07 GG02 JJ20 4D067 DD04 DD06 GA02 GA06 GA20 GB05

Claims (9)

[Claims] 1. A variable displacement type crushing hydraulic motor provided in a self-propelled crusher for crushing an object to be crushed by a crushing device and driving the crushing device by pressure oil discharged from at least one hydraulic pump. A hydraulic drive device for a self-propelled crusher, comprising: control means for switching and controlling the capacity of the crushing hydraulic motor according to whether the crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation. Hydraulic drive of self-propelled crusher. 2. The hydraulic drive system for a self-propelled crusher according to claim 1, wherein said control means reduces the capacity of said crushing hydraulic motor during said reverse rotation operation as compared with said forward rotation operation. Features a hydraulic drive for self-propelled crushers. 3. The hydraulic drive system for a self-propelled crusher according to claim 1, wherein said control means includes a motor capacity adjusting means for changing a capacity of said crushing hydraulic motor, and said crushing hydraulic motor rotates forward. A hydraulic drive device for a self-propelled crusher, comprising: an adjusting operation control means for controlling an adjusting operation by the motor capacity adjusting means depending on whether the motor operates or reversely operates. 4. The hydraulic drive device for a self-propelled crusher according to claim 3, wherein said adjusting operation control means performs a corresponding control depending on whether said crushing hydraulic motor performs a forward rotation operation or a reverse rotation operation. A control signal output unit that outputs a signal, a pilot pressure generation unit that generates and outputs a pilot pressure according to the control signal, and a capacity adjustment pilot pipeline that guides the pilot pressure to the motor capacity adjustment unit. The hydraulic drive device for a self-propelled crusher, wherein the motor capacity adjusting means changes the capacity of the crushing hydraulic motor in accordance with the pilot pressure guided through the capacity adjusting pilot pipe. 5. The hydraulic drive device for a self-propelled crusher according to claim 1, further comprising a normal rotation load detecting means for detecting a load during the normal rotation operation of the crushing hydraulic motor. The control means controls the capacity of the crushing hydraulic motor in accordance with the detected load of the forward rotation load means, and the hydraulic drive device for the self-propelled crusher is characterized in that 6. The hydraulic drive system for a self-propelled crusher according to claim 1, further comprising a reverse rotation instruction means for inputting an instruction by the operator to perform the reverse rotation operation of the crushing hydraulic motor,
The hydraulic drive device for a self-propelled crusher, wherein the control means controls a capacity of the crushing hydraulic motor in response to an instruction input from the reverse rotation instruction means. 7. The hydraulic drive device for a self-propelled crusher according to claim 1, wherein at least two hydraulic pumps are provided, and two hydraulic pumps are provided when the crushing hydraulic motor is in a normal rotation operation. The hydraulic oil from the pump is joined and supplied to the hydraulic motor for crushing, and the hydraulic oil from one hydraulic pump is supplied to the hydraulic motor for crushing during reverse rotation of the hydraulic motor for crushing. A hydraulic drive device for a self-propelled crusher, comprising a supply switching means for switching an oil supply path. 8. A hydraulic drive system for a self-propelled crusher according to claim 1, wherein said crusher fixes a cutter to each of a plurality of rotating shafts arranged substantially in parallel. A shearing type crushing device for biting and shearing the object to be crushed, or a pair of blades for crushing attached to a substantially roll-shaped rotating body, rotating these pairs in opposite directions to each other, and between the rotating bodies. A hydraulic crusher for a self-propelled crusher, which is a rotary crusher that crushes the object to be crushed into the crusher. 9. A self-propelled crusher for crushing an object to be crushed inputted from a hopper by a crushing device, a first and a second hydraulic pump driven by a prime mover, and a tilting angle variable tilting angle. A variable displacement type crushing hydraulic motor that includes a plate and drives the crushing device with pressure oil discharged from the first and second hydraulic pumps; and a crushing hydraulic motor from the first and second hydraulic pumps. In a hydraulic drive device of a self-propelled crusher having a first control valve and a second control valve of a hydraulic pilot system for controlling a direction and a flow rate of the supplied pressure oil, the crushing hydraulic motor performs a forward rotation operation. A pressure sensor connected to the pressure oil supply pipe on the side, and a forward rotation control signal or a reverse rotation control for causing the hydraulic motor for crushing to perform the forward rotation operation or the reverse rotation operation in accordance with the pressure detected by the pressure sensor. A controller that outputs a signal, a switching valve that is switched in response to the forward rotation control signal or the reverse rotation control signal, and generates and outputs a forward rotation pilot pressure or a reverse rotation pilot pressure by using a pressure from a hydraulic pressure source; A first forward rotation pilot line and a second forward rotation pilot line for guiding forward rotation pilot pressure to the first control valve and the second control valve, respectively, and a reverse rotation for guiding the reverse rotation pilot pressure to the first control valve. A pilot line, a hydraulically driven cylinder device for driving and adjusting the tilt angle of the swash plate of the crushing hydraulic motor, and a capacity adjusting pilot line for guiding the reverse rotation pilot pressure to the cylinder device. And the first control valve is configured to control when the forward rotation pilot pressure is introduced from the forward rotation pilot line. Is
The switch is switched to a forward rotation conducting position for supplying the pressure oil from the first hydraulic pump to the pressure oil supply line on the side on which the crushing hydraulic motor rotates forward, and the reverse rotation pilot pressure is switched from the reverse rotation pilot line. Is introduced, the pressure oil from the first hydraulic pump is switched to a reverse rotation conduction position for supplying the pressure oil supply pipe on the side on which the crushing hydraulic motor performs reverse rotation, and the second control valve is When the forward rotation pilot pressure is introduced from the forward rotation pilot line, the supply of the pressure oil from the second hydraulic pump to the pressure oil supply line on the side where the crushing hydraulic motor performs the forward rotation operation is performed. And switching to a shut-off position in which the hydraulic oil from the second hydraulic pump is not supplied to the crushing hydraulic motor when the forward rotation pilot pressure is not introduced. Hydraulic drive of self-propelled crusher.