JP2001263482A - Hydraulic driving device for mobile recycled product manufacturing machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To permit both high speed travel when traveling on the level land and crawling travel when unloading a trailer and to reduce pressure loss during crawling travel to improve productivity. SOLUTION: This hydraulic driving device for a mobile recycled product manufacturing machine has at least one variable displacement hydraulic pump 19 (20) driven by an engine 21 and provided at a mobile crusher self-advancing by a crawler belt 14 and leading a crushed material received by a hopper 1, into a crushing device 2 and applying specified treatment to form crushed material products; and traveling hydraulic motors 16, 17 for driving the crawler belt 14 by pressure oil discharged from the hydraulic pumps 19, 20. The discharge flow QP1, QP2 of the hydraulic pumps 19, 20 are controlled with a control characteristic corresponding to an instruction by a travel mode selecting switch 36g to which an instruction on the working speed of the crawler belt 14 is inputted in relation to the demand flow of the traveling hydraulic motors 16, 17.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a self-propelled crusher equipped with a crushing device for crushing crushed raw materials, and a self-propelled soil improver provided with a mixing device for adding a soil improving material to earth and sand and crushing and mixing. More specifically, self-propelled recycled product production machines, including those that can perform both high-speed traveling on flat terrain and low-speed traveling when unloading a trailer, and reduce pressure loss during low-speed traveling to improve productivity The present invention relates to a hydraulic drive device of a self-propelled recycle product production machine capable of improving the performance.

[0002]

2. Description of the Related Art In recent years, under the background of the promotion of waste recycling such as the enforcement of the Recycling Resources Promotion Law (so-called Recycling Law) (October 1991), self-propelled crushers and self-propelled soil improvement machines The place of activity of mobile recycling product production machines is expanding.

[0003] Self-propelled crushers are various types of large and small rocks, construction waste materials, industrial wastes, and the like generated at construction sites such as concrete lump taken out during building demolition and asphalt lump discharged during road repair. The crushed material) is used as a recycled material. For example, the recycled material (material to be crushed) which is put into a hopper as a receiving means at the upper part of the self-propelled crusher by a hydraulic shovel or the like is provided, for example, below the hopper. It is led to a crushing device as a processing device by a feeder, and crushed to a predetermined size by the crushing device. The crushed material is dropped from the space below the crushing device onto a conveyor below the crushing device and transported by this conveyor. During this transportation, the magnetic separator placed above the conveyor adsorbs and removes, for example, rebar pieces mixed in the concrete mass, and finally as a crushed product for recycling from the rear of the self-propelled crusher. It is designed to be carried out.

A self-propelled soil improvement machine uses excavated soil, which is not suitable for backfilling, among the excavated soil generated in burying of gas pipes, water and sewage works, and other road works and foundation works. The recycled material (soil and sand) charged into the earth and sand hopper as a receiving means at the upper part of the self-propelled soil improvement machine by a hydraulic shovel or the like, for example, is processed as a processing device by a conveyor (introduction conveyor) provided below the earth and sand hopper. To the mixing device
The mixture is subjected to a crushing and mixing process together with the soil improving material, and the mixture is dropped on a conveyor (conveyor for unloading), and finally conveyed from the rear part of the self-propelled soil improving machine as a soil product for recycling by the conveyor. It has become. These self-propelled recycled product production machines are equipped with a traveling body having crawler tracks at the lower part, and the crawler tracks are
It is driven by a hydraulically driven actuator (in this case, a traveling hydraulic motor) together with the crushing device, the mixing device, the feeder, the conveyor, and the magnetic separator. That is,
At least one variable displacement hydraulic pump is driven by the prime mover, and pressure oil discharged from the hydraulic pump is supplied to and driven by the traveling hydraulic motor. At this time, the direction and flow rate of the pressure oil supplied to the traveling hydraulic motor are controlled by traveling control valve means operated by traveling operation means (for example, traveling operation lever).

[0005] The self-propelled recyclable product production machine is capable of self-propelled operation as described above, so that it can be frequently moved at an operation site and effective use of space can be achieved. Also, when transporting to the operation site, it can be moved and loaded on the carrier of the transport trailer by its own driving, so that mobility is improved. It is possible to use it quickly and without waste (high operation rate).

[0006] As described above, when the self-propelled recycle product production machine runs on its own, the self-propelled recycle product production machine operates at an operation site (for example, a recycle processing plant) and at the time of transportation and unloading to a trailer. There are two. Normally, in the former case, the operator operates the traveling operation means with a relatively large operation amount and travels at a relatively high speed from the viewpoint of improving the operation rate. On the other hand, in the latter case, the operator travels on an inclined surface that extends from the ground to the trailer carrier loading surface, and requires sufficient consideration in terms of posture stability (prevention of falling). The operation means is operated with a relatively small operation amount, and the vehicle is traveling at a relatively low speed. By the way, since the 1990s, the amount of construction waste and industrial waste has been increasing year by year due to the promotion of recycling, such as the fact that recycling of construction by-products is obligated by the Recycling Law. Against this background, self-propelled recycled product production machines in recent years tend to become larger in size. The main factor is the lengthening of the conveyor (conveyance conveyor). That is, in general, the conveyor, if the height of the unloading side (rear side) end from the ground is low,
Within a short time after the start of the processing operation, the space below the rear end of the conveyor is filled with the recycled product, and the subsequent operation becomes impossible, and the operation must be temporarily suspended.
As a result, the continuous processability and smoothness of the entire recycle processing work are impaired, and the work efficiency is reduced. On the other hand, if the height position of the end of the conveyor on the unloading side is high, a large amount of recycled products to be unloaded and dropped can be reserved (stocked) in a piled state, so that the working efficiency can be improved. Further, if the height position is somewhat high, there is an advantage that the recycled product can be transported by another work machine, for example, a wheel loader.
As described above, as the length of the conveyor in the transport direction increases, the dimension of the entire self-propelled recycle product production machine in the front-rear direction tends to increase.

[0007] In the self-propelled recycled product production machine, which tends to become larger as described above, the stability of the entire self-propelled recycled product production machine during the unloading by the self-propelled traveling to the trailer carrier described above. More careful consideration is needed to ensure the safety (prevention of falling and flapping). For this reason, there is an increasing need to perform a low-speed traveling at a lower speed than before in self-powered traveling.

In order to meet such needs, for example, as disclosed in Japanese Patent Application Laid-Open No. Hei 8-299838, a variable displacement hydraulic pump driven by a prime mover and a hydraulic pump discharged from the hydraulic pump are disclosed. A traveling hydraulic motor for driving traveling means by oil, traveling control valve means for controlling a flow of pressure oil supplied from the hydraulic pump to the traveling hydraulic motor, and traveling for operating the traveling control valve means. There is a hydraulic drive device of a self-propelled recycle product production machine having operating means for a vehicle, wherein the traveling hydraulic motor is a variable displacement type hydraulic motor.

With this configuration, although there is no specific description in the above-mentioned prior art publication, the capacity of the variable displacement hydraulic motor for traveling is increased at the time of loading / unloading the trailer, so that the self-load per one supply flow rate is increased. The running speed can be reduced. This makes it possible to use the same amount of operation at low speeds with the same operation amount compared to the conventional low-speed operation with a small amount of operation of the traveling operation means when loading and unloading a trailer, improving the stability of a self-propelled recycled product production machine can do. On the other hand, when traveling flat on an operation site, the capacity of the variable displacement hydraulic motor can be returned to the original value and the conventional high-speed traveling can be performed.

[0010]

The above-mentioned prior art uses a variable displacement hydraulic motor for traveling so that the need for high-speed traveling when traveling on level ground in an operation site and the need for very low-speed traveling when loading and unloading a trailer are reduced. It satisfies both.

[0011] However, the above-mentioned prior art has the following problems. That is, generally, when the hydraulic oil discharged from the hydraulic pump is supplied to the traveling hydraulic motor through the traveling control valve means and driven, a series of pressures of the hydraulic pump → the traveling control valve means → the traveling hydraulic motor is used. Pressure loss mainly occurs in the travel control valve means in the oil supply path, and the pressure loss increases as the flow rate of the travel control valve means increases.

[0012] Here, in the above-mentioned prior art, a low-speed operation is performed by increasing the capacity of the hydraulic motor while supplying the same large flow rate at the time of high-speed running even at low-speed running. Therefore, even at a very low speed, a large pressure loss due to the large flow rate occurs at the traveling control valve means as in the high speed traveling. Therefore, in the prime mover that drives the hydraulic pump, the input horsepower required per unit traveling distance increases by the amount of the loss, and the fuel consumption increases. As a result, the operation time is shortened and the productivity is reduced.

SUMMARY OF THE INVENTION An object of the present invention is to provide a self-propelled recycle system that can perform both high-speed traveling on flat ground and low-speed traveling when unloading a trailer, and can reduce pressure loss during low-speed traveling and improve productivity. An object of the present invention is to provide a hydraulic drive for a product production machine.

[0014]

(1) In order to achieve the above object, according to the present invention, a self-propelled traveling means is used, and a recycle raw material received by a receiving means is introduced into a processing apparatus to perform predetermined processing. A self-propelled recycle product production machine that is used as a recycle product and is provided with at least one variable displacement hydraulic pump driven by a prime mover, and a travel unit that drives the travel unit with pressure oil discharged from the hydraulic pump. In a hydraulic drive device of a self-propelled recycle product production machine having a hydraulic motor, an input means for inputting an instruction regarding an operation speed of the traveling means, and a required flow rate of the traveling hydraulic motor, Control means for controlling the discharge flow rate of the hydraulic pump with control characteristics according to the instruction.

In the present invention, when an instruction relating to the operating speed of the traveling means is inputted by the input means, the control means has a control characteristic corresponding to the instruction and outputs the discharge flow rate of the hydraulic pump with respect to the required flow rate of the traveling hydraulic motor. Control. This makes it possible for the control means to change the characteristic of the required hydraulic motor flow rate-the pump discharge flow rate between when the vehicle is traveling at a very low speed and when the vehicle is traveling at a high speed.

Therefore, for example, when a relatively low speed instruction is input by the input means, the maximum pump discharge flow rate can be suppressed to a relatively low value, and the required flow rate of the traveling hydraulic motor increases. , It is possible to increase the supply flow rate of the traveling hydraulic motor at a relatively low rate. With this, for example, if the travel control valve means for controlling the supply pressure oil to the travel hydraulic motor is operated by the travel operating means and the operation amount corresponds to the required flow rate of the travel hydraulic motor, It becomes possible to increase the operating speed of the traveling means at a relatively low rate with respect to the increase in the amount.
With the above-described configuration, for example, the traveling speed when the traveling operation means is at the full lever (maximum operation amount) can be reduced, and the variation in the traveling speed per unit operation amount variation can be reduced. Therefore, the vehicle can run at a very low speed, and can perform precise speed control.

Conversely, for example, when a relatively high-speed instruction is input by the input means, the maximum pump discharge flow rate can be set to a relatively high value, and the required flow rate of the traveling hydraulic motor increases. , The supply flow rate of the traveling hydraulic motor can be increased at a relatively high rate. Thereby, in the above example, it becomes possible to increase the operation speed of the traveling means at a relatively high rate with respect to the increase in the operation amount of the traveling operation means. With the above configuration, for example, the full lever (maximum operation amount) of the traveling operation means
The traveling speed at the time can be increased, and high-speed traveling is possible.

In the present invention, as described above, both high-speed traveling and very low-speed traveling are enabled by increasing or decreasing the pump discharge flow rate and increasing or decreasing the supply flow rate itself to the traveling hydraulic motor. Therefore, when the vehicle is traveling at a very low speed, the flow rate of a series of hydraulic oil supply paths of the hydraulic pump, the travel control valve means, and the travel hydraulic motor is reduced, so that the flow rate of the travel control valve means can be reduced. This allows
At least, the pressure loss generated in the traveling control valve means can be reduced as compared with the related art in which the same large flow rate is supplied even at the time of low-speed traveling as at the time of high-speed traveling, and the hydraulic pump is accordingly driven. The horsepower required for the prime mover can be reduced. As a result, the fuel consumption can be reduced, so that the operation time can be lengthened and the productivity can be improved.

(2) In the above (1), preferably,
When a relatively high-speed instruction is input by the input unit, the control unit sets the maximum discharge flow rate of the hydraulic pump to a relatively high value, and inputs a relatively low-speed instruction by the input unit. In this case, the maximum discharge flow rate of the hydraulic pump is set to a relatively low value.

(3) In the above (1) or (2), preferably, a travel control valve means for controlling a flow of pressurized oil supplied from the hydraulic pump to the travel hydraulic motor; Traveling operation means for operating the control valve means.

Thus, the required flow rate of the traveling hydraulic motor becomes the required flow rate of the traveling control valve means, in other words, corresponds to the operation amount of the traveling operation means.
As a result, the control means controls the discharge flow rate of the hydraulic pump with a control characteristic corresponding to the operation amount of the traveling operation means in accordance with the instruction from the input means. Therefore, the amount of increase in the operating speed of the traveling means corresponding to the amount of increase in the operation amount can be changed (for example, the relationship between the operation lever operation position and the traveling speed) can be changed. It is possible to realize a low-speed traveling performance in which the traveling speed can be reduced and a subtle speed change can be easily performed.

(4) In any one of the above (1) to (3), preferably, the control means discharges the hydraulic pump with a predetermined adjusting characteristic to a required flow rate of the traveling hydraulic motor. A pump adjusting unit that adjusts a flow rate; and a characteristic control unit that changes the adjustment characteristic of the pump adjusting unit in response to the instruction from the input unit.

(5) In the above (4), more preferably, the pump adjusting means includes a control pressure generating means for generating a control pressure corresponding to a required flow rate of the traveling hydraulic motor, and a control pressure generating means. And a regulator means for controlling the discharge flow rate of the hydraulic pump in accordance with the control pressure. The characteristic control means changes the control pressure in accordance with the instruction from the input means.

(6) In the above (5), more preferably, the traveling control valve means is a center bypass type valve, and the control pressure generating means is a center bypass type traveling control valve means. Pressure conversion means for converting the flow rate of pressure oil flowing downstream of the center bypass line into pressure is included.

(7) In order to achieve the above object, according to the present invention, while traveling by self-traveling means, the recycled material received by the receiving means is introduced into a processing device and subjected to predetermined treatment to produce a recycled product. The self-propelled recycle product production machine includes at least one variable displacement hydraulic pump driven by a prime mover, and a traveling hydraulic motor that drives the traveling means with pressure oil discharged from the hydraulic pump. In a hydraulic drive device of a self-propelled recycle product production machine, a center bypass type travel control valve means for controlling a flow of hydraulic oil supplied from the hydraulic pump to the travel hydraulic motor, and the travel control valve means Operating means for operating the vehicle, selecting means for selectively inputting one of a first mode and a second mode of the running means, and controlling the running Pressure converting means for converting the flow rate of the pressure oil flowing downstream of the center bypass line of the means into pressure and generating a control pressure according to the operation amount of the travel operating means, and the control pressure from the pressure converting means Regulator means for controlling the discharge flow rate of the hydraulic pump to increase in accordance with the increase in
When the mode is selected, the maximum value of the control pressure is relatively increased to set the maximum discharge flow rate of the hydraulic pump to a relatively high value, and when the second mode is selected by the selection means, Has control pressure switching means for making the maximum value of the control pressure relatively small and making the maximum discharge flow rate of the hydraulic pump relatively low.

(8) In any one of the above (1) to (7), preferably, the self-propelled recycle product production machine crushes the material to be crushed as the recycle raw material to produce the recycle product. It is a self-propelled crusher equipped with a crushing device for producing crushed material as the processing device.

(9) In any one of the above (1) to (7), preferably, the self-propelled recycle product production machine crushes and mixes the earth and sand as the recycle raw material with a soil improvement material, and It is a self-propelled soil improvement machine equipped with a mixing device for producing improved soil as a recycled product as the treatment device.

[0028]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. This embodiment describes the present invention,
It is an embodiment when applied to a self-propelled crusher as a self-propelled recycle product production machine. FIG. 1 is a side view showing the entire structure of a self-propelled crusher provided with one embodiment of the hydraulic drive device of the present invention, and FIG. 2 is a top view of the self-propelled crusher shown in FIG. is there.

In FIG. 1 and FIG. 2, this self-propelled crusher is used as a material to be crushed (for example, a concrete block carried out at the time of dismantling a building or a road repair) by a working tool such as a bucket of a hydraulic shovel. Various types of large and small construction waste materials and industrial wastes generated at construction sites such as discharged asphalt lump, and rocks and natural stones mined at rock mining sites and face, etc .; The hopper 1 receives the rock / construction waste material and the like, and the rock / construction waste material received by the hopper 1 is crushed into a predetermined size and crushed to be discharged downward, for example, the jaw crusher 2 and the hopper 1. A crusher main body 4 equipped with a feeder 3 for transporting and guiding rocks, construction waste materials, and the like to the crushing device 2, and provided below the crusher main body 4. The row body 5 and the crushed material crushed by the crushing device 2 and discharged downward are received, and the rear side of the self-propelled crusher (the other side in the longitudinal direction of the track frame crusher mounting portion 8A described later, the right side in FIG. 1) ), And a magnetic material (reinforcing bar, etc.) contained in the crushed material provided above the conveyor 6 and being transported on the conveyor 6 is magnetically sucked and finally removed for recycling. And a magnetic separator 7 as a crushed product.

The traveling body 5 includes a track frame 8
And left and right crawler tracks 14 as running means. The track frame 8 is formed of, for example, a substantially rectangular frame, and has a crusher mounting portion 8A on which the crushing device 2, the hopper 1, a power unit 24 and the like described below are mounted, and the crusher mounting portion 8A and the left side. And a leg 8B for connecting to the right endless track crawler 14. The crawler track 14 extends between a drive wheel 12a and an idler 12b rotatably supported by the legs 8B. The left and right traveling hydraulic motors 16, 16 provided on the drive wheel 12a side. The driving force is given by 17 so that the crusher runs.

The hopper 1, together with the feeder 3, is located above one end of the track frame crusher mounting portion 8A in the longitudinal direction (left-right direction in FIG. 1) (front side of the crusher, ie, left side in FIG. 1). It is installed in.

The crushing device 2 is located on the rear side (right side in FIG. 1) of the crusher with respect to the hopper 1 and the feeder 3, and as shown in FIG. It is mounted on the middle part in the longitudinal direction. At this time, the driving force generated by the crushing hydraulic motor 9 (see FIG. 2) is transmitted to the flywheel 2a via a belt (not shown), and the driving force transmitted to the flywheel 2a is converted to a known conversion mechanism. To convert the rocking motion of the moving tooth (not shown) back and forth with respect to the fixed tooth (not shown). Is crushed to a predetermined size.

The feeder 3 is, as shown in FIG.
Feeder frame 15 provided near one end (left side in FIG. 1) of the track frame crusher mounting portion 8A in the longitudinal direction.
And the hopper 1 is located almost directly above the hopper. The feeder 3 is a so-called grizzly feeder. The driving force generated by the feeder hydraulic motor 10 causes the rock /
A bottom plate portion including a plurality (two in this example) of sawtooth plates 3a (see FIG. 2) on which construction waste materials and the like are placed is vibrated.
With such a structure, rocks and construction waste materials and the like put into the hopper 1 are sequentially conveyed and supplied to the crushing device 2 (= conveyance function), and fine particles and fine particles contained in the rocks and construction waste materials are conveyed during the conveyance. The earth and sand fall down through the gap between the saw teeth of the saw-toothed plate 3a via the chute 3b (see FIG. 1) and are introduced onto the conveyor 6. In other words, a screening function of selecting rocks, construction waste materials, and the like having a particle size larger than the size of the gap by sifting rocks, construction waste materials, and the like having a smaller particle size than the size of the gap between the saw teeth of the serrated plate 3a is also provided. Equipped. The conveyor 6 includes a conveyor hydraulic motor 11 (see FIG. 2).
This drives the belt 6a, thereby transporting the crushed material that has fallen onto the belt 6a from the crushing device 2 and the fine-grained falling material (not crushed) via the chute 3b.

The conveyor 6 has a support member 6 on the transport side (in other words, the rear side of the crusher, the right side in FIG. 1).
It is suspended and supported by an arm member 18 attached to a power unit 24 (details will be described later) via c and 6d. Also, the part on the non-transport side (the front side of the crusher, the left side in FIG. 1)
It is located below the track frame crusher attachment portion 8A, and is supported so as to be suspended from the track frame crusher attachment portion 8A via a support member (not shown). Thereby, as shown in FIG. 1, the conveyor 6 is disposed so as to rise obliquely in the carrying-out direction (rightward in FIG. 1) in the space below the outer edge (rear end) of the power unit 24. The support member 6c connects the conveyor 6 at a position closest to the power unit 24, that is, connects the intermediate portion 6b of the conveyor 6 in the transport direction and the outer edge (rear end) of the power unit 24 at almost the shortest distance. It is connected to.

The magnetic separator 7 is suspended from and supported by the arm member 18 via a support member 7b, and is disposed above the conveyor belt 6a so as to be substantially perpendicular to the conveyor belt 6a. The belt 7a is driven around the magnetic force generating means (not shown) by the magnetic separator hydraulic motor 13 so that the magnetic force from the magnetic force generating means acts on the magnetic separator belt 7a, and the magnetic material is applied to the magnetic separator belt 7a. After being sucked, it is transported in a direction substantially perpendicular to the conveyor belt 6a and dropped to the side of the conveyor belt 6a. The rear side in the longitudinal direction of the track frame crusher mounting portion 8A (the right side in FIGS. 1 and 2).
The power unit 24 is mounted on the upper part of the end via a power unit loading member 24b (see FIG. 1).
The power unit 24 includes an engine 2 as a prime mover.
1 (see FIG. 5 to be described later), a variable displacement first hydraulic pump 19 and a second hydraulic pump 20 (the same) driven by the engine 21, and a control valve 26 to be described later.
The control valve device provided with -31 is built in. Further, a driver's seat 24a on which an operator rides is provided in front of the power unit 24 (left side in FIGS. 1 and 2).

Here, the crushing device 2, feeder 3, running body 5, conveyor 6, and magnetic separator 7 constitute a driven member driven by a hydraulic drive device provided in the self-propelled crusher. I have. FIG. 3, FIG. 4, and FIG. 5 are hydraulic circuit diagrams showing an embodiment of the hydraulic drive device of the self-propelled crusher of the present invention.

In FIGS. 3 to 5, the hydraulic drive unit includes the engine 21 and the variable displacement type first hydraulic pump 19 and the second hydraulic pump 20 driven by the engine 21. The hydraulic motors 9, 10, 11, 13, which are supplied with hydraulic oil discharged from the first and second hydraulic pumps 19, 20, respectively.
16, 17 and the flow (direction and flow rate or only flow rate) of the pressure oil supplied from the first and second hydraulic pumps 19, 20 to the hydraulic motors 9, 10, 11, 13, 16, 16 and 17 are controlled. Six control valves 26, 27,
28, 29, 30, 31 and a control valve 2 for left / right running provided in the driver's seat 24a (see FIG. 1).
Left and right traveling operation levers 32a and 33a for switching operations of the first and second 7, 28 (described later);
Pump control means for adjusting the discharge flow rates QP1 and QP2 of the hydraulic pumps 19 and 20 (see FIG. 7 described later), for example, regulator devices 34 and 35, and the crusher main body 4 (for example, in the driver's seat 24a) are provided. An operation panel 36 is provided for the operator to input and operate the crushing device 2, feeder 3, conveyor 6, and start / stop of the magnetic separator 7 and the like.

The six hydraulic motors 9, 10, 11, 13,
The crushing hydraulic motor 9 for generating a driving force for operating the crushing device 2, the feeder hydraulic motor 10 for generating a driving force for operating the feeder 3, as described above,
The conveyor hydraulic motor 11 for generating a driving force for operating the conveyor 6, the magnetic separator hydraulic motor 13 for generating a driving force for operating the magnetic separator 7, and a left / right trackless track 14.
Left and right traveling hydraulic motor 1 that generates a driving force to
6 and 17.

The control valves 26 to 31 are two-position switching valves or three-position switching valves. The crushing control valve 26 connected to the crushing hydraulic motor 9 and the left running hydraulic motor 16 are connected to the left running hydraulic motor 16. Control valve 27 connected to the right travel hydraulic motor 17, the right travel control valve 28, and the feeder hydraulic motor 1
0, a feeder control valve 29 connected to
It comprises a conveyor control valve 30 connected to the conveyor hydraulic motor 11 and a magnetic separator control valve 31 connected to the magnetic separator hydraulic motor 13.

At this time, the first and second hydraulic pumps 19,
20, the first hydraulic pump 19 discharges hydraulic oil to be supplied to the left traveling hydraulic motor 16 and the crushing hydraulic motor 9 via the left traveling control valve 27 and the crushing control valve 26. Has become. Each of these control valves 27 and 26 is a three-position switching valve capable of controlling the direction and flow rate of hydraulic oil to the corresponding hydraulic motors 16 and 9, and is connected to the discharge line 37 of the first hydraulic pump 19. Center bypass line 22a
In the first valve group 22 provided with the above, the control valve 27 for left running and the control valve 26 for crushing are arranged in this order from the upstream side. In addition, a pump control valve 38 (details will be described later) is provided at the most downstream side of the center bypass line 22a.

On the other hand, the second hydraulic pump 20 is provided with a hydraulic motor 10 for feeder, a hydraulic valve 10 for conveyor, via a control valve 28 for right running, a control valve 29 for feeder, a control valve 30 for conveyor, and a control valve 31 for magnetic separator. Pressure oil to be supplied to the motor 11 and the hydraulic motor 13 for the magnetic separator is discharged. Of these, the right travel control valve 28
Is a three-position switching valve capable of controlling the flow of pressure oil to the corresponding right-travel hydraulic motor 17, and the other control valves 28, 29, 30, 31 are connected to the corresponding hydraulic motors 10, 11, 13. A two-position switching valve capable of controlling the flow rate of the pressure oil of the second hydraulic pump 20.
In the second valve group 23 having a center bypass line 23a connected to the control line 9 and a center line 23b further connected downstream of the center bypass line 23a, the right running control valve 28, the magnetic separator control valve 31 , A conveyer control valve 30 and a feeder control valve 29 in this order. The center line 23b is closed on the downstream side of the feeder control valve 29 on the most downstream side.

Among the control valves 26 to 31, the left and right traveling control valves 27 and 28 are center bypass type pilot operated valves which are operated using pilot pressure generated by the pilot pump 25. These left and right running control valves 2
7 and 28 are operating lever devices 32 generated by the pilot pump 25 and provided with the operating levers 32a and 33a described above.
It is operated by the pilot pressure reduced to a predetermined pressure at 33.

That is, the operating lever devices 32 and 33 are
Operation levers 32a and 33a and a pair of pressure reducing valves 32b, 32b and 3 for outputting a pilot pressure corresponding to the operation amount thereof
3b and 33b. When the operating lever 32a of the operating lever device 32 is operated in the direction a in FIG. 3 (or in the opposite direction, the same applies hereinafter), the pilot pressure is increased via the pilot line 40 (or 41). It is led to the driving unit 27a (or 27b),
As a result, the left traveling control valve 27 is switched to the upper switching position 27A (or the lower switching position 27B) in FIG. 1, and the hydraulic oil from the first hydraulic pump 19 receives the discharge oil line 37, the center bypass line 22a, The hydraulic pressure is supplied to the left traveling hydraulic motor 16 via the switching position 27A (or the lower switching position 27B) of the left traveling control valve 27, and the left traveling hydraulic motor 16 is driven in the forward (or reverse) direction. You.

When the operating lever 32a is set to the neutral position shown in FIG. 3, the left traveling control valve 27 returns to the neutral position shown in FIG. 3 by the urging forces of the springs 27c and 27d, and the left traveling hydraulic motor 16 Stop.

Similarly, when the operating lever 33a of the operating lever device 33 is operated in the direction b (or the opposite direction) in FIG. 3, the pilot pressure is increased via the pilot line 42 (or 43). Drive unit 28a
(Or 28b), and the upper switching position 28A in FIG.
(Or the lower switching position 28B), and the right traveling hydraulic motor 17 is driven in the forward direction (or the reverse direction). When the operating lever 33a is set to the neutral position, the right traveling control valve 28 returns to the neutral position by the urging force of the springs 28c and 28d, and the right traveling hydraulic motor 17
Stops.

Here, a solenoid control valve 46 which is switched by a drive signal St (described later) from a controller 45 is provided in the pilot introduction pipes 44a and 44b for guiding the pilot pressure from the pilot pump 25 to the operation lever devices 32 and 33. Is provided. This solenoid control valve 46
Means that the drive signal St input to the solenoid 46a is ON
, It is switched to the communication position 46A on the left side in FIG.
Pilot pressure from pilot pump 25
4a, 44b to the operating lever devices 32, 33,
The above operation of the left and right traveling control valves 27 and 28 by the operation levers 32a and 33a is enabled.

On the other hand, when the drive signal St is turned off, the solenoid control valve 46 returns to the shut-off position 46B on the right side in FIG. 5 by the restoring force of the spring 46b, and shuts off the introduction pipes 44a and 44b. The introduction pipe 44b is connected to the tank 47
To the tank line 47a.
The pressure in b is set to the tank pressure, and the operating lever devices 32 and 33
The above-mentioned operation of the left and right traveling control valves 27 and 28 is not possible.

The crushing control valve 26 is a center bypass type electromagnetic proportional valve having solenoid driving portions 26a and 26b at both ends. The solenoid drive unit 26a,
The solenoid 26b is provided with a solenoid driven by a drive signal Scr from the controller 45, and the crushing control valve 26 is switched according to the input of the drive signal Scr.

That is, the drive signal Scr is a signal corresponding to the forward rotation (or reverse rotation, hereinafter the same relationship is the same) of the crushing device 2,
For example, when the drive signals Scr to the solenoid drive units 26a and 26b are turned on and off, respectively (or the drive signals Scr to the solenoid drive units 26a and 26b are turned off and on, respectively), the crushing control valve 26 is turned to the upper side in FIG. The switching position 26A (or the lower switching position 26)
B). Thereby, the first hydraulic pump 1
9 is supplied to the crushing hydraulic motor 9 via the discharge pipe 37, the center bypass line 22a, and the switching position 26A (or the lower switching position 26B) of the crushing control valve 26, and the crushing hydraulic pressure is supplied. The motor 9 is driven in the forward (or reverse) direction.

When the drive signal Scr is a signal corresponding to the stop of the crushing device 2, for example, the drive signals Scr to the solenoid drive units 26a and 26b are both turned off, the control valve 26 is turned on by the urging force of the springs 26c and 26d as shown in FIG. The crushing hydraulic motor 9 returns to the neutral position shown in FIG.

The pump control valve 38 has a function of converting a flow rate into a pressure, and a piston 38a capable of connecting / disconnecting the center bypass line 22a and the tank line 47b via a throttle portion 38aa.
And a spring 38 for biasing both ends of the piston 38a.
b, 38c and a pilot introduction line 83a (described later), a solenoid control valve 110 (same), and a pilot introduction line 83c in the discharge line 79 of the pilot pump 25.
And a variable relief valve 38d whose upstream side is connected to guide pilot pressure, the downstream side is connected to the tank line 47c, and the relief pressure is variably set by the spring 38b.

With such a configuration, the pump control valve 38 functions as follows. That is, as described above, the left traveling control valve 27 and the crushing control valve 26 are center bypass type valves, and the flow rate flowing through the center bypass line 22a depends on the operation amount of each of the control valves 27 and 26 (that is, the spool). Changeover stroke amount). When the control valves 27 and 26 are in a neutral state, that is, when the control valves 27 and 2
6 (in other words, the required flow rates of the left traveling hydraulic motor 16 and the crushing hydraulic motor 9) are small.
Most of the pressure oil discharged from the first hydraulic pump 19 is supplied as an excess flow rate Qt1 (see FIG. 6 described later) via the center bypass line 22a.
8, a relatively large flow of hydraulic oil is
It is led to the tank line 47b through the throttle portion 38aa of a. As a result, the piston 38a moves to the right in FIG. 3, so that the set relief pressure of the relief valve 38d by the spring 38b becomes low, and the first servo valve for branching control, described later, for negative tilt control, which is provided from the pipe 83c. A comparatively low control pressure (negative control pressure) P
Generates c1.

Conversely, when each of the control valves 27 and 26 is operated to be opened, that is, when the required flow rate required for the first hydraulic pump 19 is large, the excess flow rate Qt1 flowing through the center bypass line 22a is provided. Is reduced by the flow rate flowing to the hydraulic motors 16 and 9,
The flow rate of the pressure oil led to the tank line 47b through the piston throttle portion 38aa is relatively small, and the piston 38
Since a moves to the left side in FIG. 3 and the set relief pressure of the relief valve 38d increases, the control pressure Pc1 of the pipeline 81 increases.

In the present embodiment, as will be described later, the tilt angle of the swash plate 19A of the first hydraulic pump 19 is controlled based on the fluctuation of the control pressure (negative control pressure) Pc1 (details). Will be described later).

The first and second hydraulic pumps 19, 20
A relief valve 89 and a relief valve 90 are provided in pipes 87 and 88 branched from the discharge pipes 37 and 39 of the first and second hydraulic pumps 19 and 20, respectively, so that the maximum discharge pressures P1 and P2 of the first and second hydraulic pumps 19 and 20 are provided. The value of the relief pressure for limiting the value is set by the biasing force of the springs 89a and 90a provided respectively.

The feeder control valve 29 is an electromagnetic switching valve having a solenoid drive section 29a. The solenoid drive section 29a is provided with a solenoid driven by a drive signal Sf from the controller 45, and the feeder control valve 29 is switched according to the input of the drive signal Sf. That is, when the drive signal Sf becomes an ON signal for operating the feeder 3, the feeder control valve 29 is switched to the upper switching position 29A in FIG. As a result, the pressure oil from the second hydraulic pump 20 guided through the discharge pipeline 39, the center bypass line 23a, and the center line 23b is supplied to the throttling means 29 provided at the switching position 29A.
From Aa, a pipeline 50 connected thereto, a pressure control valve 51 provided in this pipeline 50 (details will be described later), a switching position 29
A provided in port A, and this port 29A
The oil is supplied to the feeder hydraulic motor 10 through a supply pipe 52 connected to the feeder b, and the hydraulic motor 10 is driven.
When the drive signal Sf becomes an OFF signal corresponding to the stop of the feeder 3, the feeder control valve 29 turns on the spring 2.
With the urging force of 9b, it returns to the shut-off position shown in FIG. 4, and the feeder hydraulic motor 10 stops.

The control valve 30 for the conveyor, like the control valve 29 for the feeder, drives the solenoid drive unit 30a to the drive signal S from the controller 45.
A solenoid driven by com is provided. Drive signal Sc
When om becomes an ON signal for operating the conveyor 6, the control valve 30 for the conveyor moves to the upper communication position 3 in FIG.
0A, and the pressure oil from the center line 23b flows from the throttle means 30Aa at the switching position 30A to the pipeline 5A.
3. The pressure control valve 54 (details will be described later), the port 30Ab of the switching position 30A, and the supply pipe 55 connected to the port 30Ab are supplied to the conveyor hydraulic motor 11 to be driven. When the drive signal Scom becomes an OFF signal corresponding to the stop of the conveyor 6, the conveyor control valve 30 returns to the shut-off position shown in FIG. 4 by the urging force of the spring 30b, and the conveyor hydraulic motor 11 stops.

As with the control valve 29 for the feeder and the control valve 30 for the conveyor, the solenoid of the solenoid drive unit 31a of the magnetic separator control valve 31 is driven by a drive signal Sm from the controller 45. When the drive signal Sm becomes an ON signal, the control valve 31 for the magnetic separator is switched to the upper communication position 31A in FIG. 31Ab → supplied through the supply conduit 58 to the hydraulic motor 13 for the magnetic separator and driven. When the drive signal Sm becomes the OFF signal, the control valve 31 for the magnetic separator returns to the shut-off position by the urging force of the spring 31b.

The feeder hydraulic motor 1 described above
0, supply of pressurized oil to the conveyor hydraulic motor 11 and the magnetic separator hydraulic motor 13 from the viewpoint of circuit protection, etc.
Relief valves 62, 63, 64 are provided in pipes 59, 60, 61 connecting the supply pipes 52, 55, 58 and the tank line 47b, respectively. Here, the pressure control valves 51, 5 provided in the pipes 50, 53, 56 described above.
The functions related to 4, 57 will be described.

The port 29Ab at the switching position 29A of the control valve 29 for the feeder and the port 30A at the switching position 30A of the control valve 30 for the conveyor.
b, and the switching position 3 of the control valve 31 for the magnetic separator
The 1A port 31Ab has a load detection port 29Ac, a load detection port 30Ac for detecting the load pressure of the corresponding feeder hydraulic motor 10, conveyor hydraulic motor 11, and magnetic separator hydraulic motor 13, respectively.
The load detection port 31Ac is in communication. At this time,
The load detection port 29Ac is connected to the load detection line 65, the load detection port 30Ac is connected to the load detection line 66, and the load detection port 31Ac is connected to the load detection line 6
7 is connected.

Here, the load detection line 65 to which the load pressure of the feeder hydraulic motor 10 is guided and the load detection line 6 to which the load pressure of the conveyor hydraulic motor 11 is guided.
6 further includes a load detection line 6 via a shuttle valve 68.
9, and the load pressure on the high pressure side selected via the shuttle valve 68 is guided to the load detection line 69. The load detection line 69 and the load detection line 6 to which the load pressure of the magnetic separator hydraulic motor 13 is guided.
7 is the maximum load detection line 71 via the shuttle valve 70.
The load pressure on the high pressure side selected by the shuttle valve 70 is guided to the maximum load detection pipe 71 as the maximum load pressure.

The maximum load pressure guided to the maximum load detection line 71 is supplied to the corresponding pressure control valve 51 via lines 72, 73, 74, and 75 connected to the maximum load detection line 71. , 54, 57, respectively. At this time, the pressure in the pipes 50, 53, 56, that is, the downstream pressure of the throttle means 29Aa, 30Aa, 31Aa is guided to the other side of the pressure control valves 51, 54, 57.

As described above, the pressure control valves 51, 54, 57
Is the throttle means 2 of the control valves 29, 30, 31
Each hydraulic motor operates in response to the differential pressure between the downstream pressure of 9Aa, 30Aa, and 31Aa and the maximum load pressure of the feeder hydraulic motor 10, the conveyor hydraulic motor 11, and the magnetic separator hydraulic motor 13. The differential pressure is maintained at a constant value irrespective of changes in the load pressures 10, 11, and 13. That is, the throttle means 29Aa, 3
The downstream pressures of 0Aa and 31Aa are set higher than the maximum load pressure by the set pressures of the springs 51a, 54a and 57a.

On the other hand, the discharge line 39 of the second hydraulic pump 20
Bleed-off line 76 branched from center bypass line 23a and center line 23b connected to
A relief valve (unload valve) 77 having a spring 77a is provided. On one side of the relief valve 77, a maximum load pressure is guided through a maximum load detection pipe 71 and a pipe 78 connected thereto, and the other side of the relief valve 77 is bleed off through a port 77b. The pressure in line 76 is led. Thereby, the relief valve 77 is configured to increase the pressure in the pipeline 76 and the center line 23b by the pressure set by the spring 77a from the maximum load pressure. That is, when the pressure in the pipe 76 and the pressure in the center line 23b becomes a pressure obtained by adding the spring force of the spring 77a to the pressure in the pipe 78 to which the maximum load pressure is introduced, the relief valve 77 The pressure oil in the passage 76 is led to the tank 47 via the pump control valve 82, whereby the feeder control valve 29,
Control is performed so that the flow rates from the control valve 30 for the conveyor and the control valve 31 for the magnetic separator become constant.

At this time, the relief pressure set by the spring 77a is controlled by the relief valve 89 and the relief valve 90 described above.
Is set to a value smaller than the set relief pressure.

A pump control valve 82 having a flow-pressure conversion function similar to that of the pump control valve 38 is provided downstream of the relief valve 77 of the bleed-off pipe 76, and a tank line 47 is provided.
d and the tank line 47e connected to
a that can be connected / disconnected via a, and springs 82b and 82c that bias both ends of the piston 82a.
A pilot introduction line 83a (described later) and a solenoid control valve 11 are connected to the discharge line 79 of the pilot pump 25.
0 (same) and the pilot introduction pipeline 83b (same), the upstream side is connected to guide the pilot pressure, the downstream side is connected to the tank line 47e, and the spring 8
A variable relief valve 82d whose relief pressure is variably set by 2b.

With such a configuration, during the crushing operation, the pump control valve 82 functions as follows. That is, as described above, the center line 23b
Is closed at the most downstream end, and the right-running control valve 28 is not operated during the crushing operation, as described later. Valve 30, control valve 3 for magnetic separator
It changes according to the amount of operation (i.e., the amount of spool switching stroke). Each control valve 29, 30, 31
Is neutral, that is, when the required flow rates of the control valves 29, 30, and 31 (in other words, the required flow rates of the hydraulic motors 10, 11, and 13) required for the second hydraulic pump 20 are small, Is hardly introduced into the supply pipelines 52, 55, and 58, and thus is discharged from the relief valve 77 downstream as a surplus flow rate Qt2 (see FIG. 6 described later) and introduced into the pump control valve 82. . As a result, a relatively large amount of pressurized oil is led out to the tank line 47e through the throttle portion 82aa of the piston 82a.
Moving to the middle right side, the set relief pressure of the relief valve 82d by the spring 82b becomes low, and the pipe 84 is branched from the pipe 83 and is provided to a first servo valve 96 for load sensing tilt control described later. A relatively low control pressure (load sensing pressure) Pc2 is generated.

Conversely, when each control valve is operated to be in the open state, that is, when the required flow rate to the second hydraulic pump 20 is large, the excess flow rate Qt2 flowing through the bleed-off line 76 is Since it is reduced by the flow rate flowing to the 10, 11, and 13 sides, the piston throttle portion 8
The flow rate of the pressure oil led to the tank line 47e through the line 2aa becomes relatively small, and the piston 82a moves to the left in FIG. 3 to increase the set relief pressure of the relief valve 82d. Will be higher. In the present embodiment, as described later, the swash plate 2 of the second hydraulic pump 20 is controlled based on the fluctuation of the load sensing pressure Pc2.
The tilt angle of 0A is controlled (details will be described later).

The pressure control valves 51, 54, 5 described above
7, control between the downstream pressure of the throttle means 29Aa, 30Aa, 31Aa and the maximum load pressure, and the relief valve 7
7, the control between the pressure in the bleed-off line 76 and the maximum load pressure allows the throttling means 29Aa, 30Aa, 3
The pressure compensating function for keeping the differential pressure of 1 Aa constant is performed. Thereby, each hydraulic motor 10, 11, 13
Control valve 2 regardless of load pressure change
The pressure oil corresponding to the opening degree of 9, 30, 31 can be supplied to the corresponding hydraulic motor. The pressure compensation function and the tilt angle control of the swash plate 20A of the hydraulic pump 20 described later based on the output of the load sensing pressure Pc2 from the pump control valve 82 result in the discharge pressure of the second hydraulic pump 20 And aperture means 29Aa,
The difference from the downstream pressure of 30Aa, 31Aa is kept constant (details will be described later).

A relief valve 85 is provided between the pipe line 78 for introducing the maximum load pressure and the tank line 47e to limit the maximum pressure in the pipe line 78 to a set pressure of the spring 85a or less, thereby protecting the circuit. Is to be planned. That is,
The relief valve 85 and the relief valve 75 constitute a system relief valve. When the pressure in the pipe 78 becomes larger than the pressure set by the spring 85a, the action of the relief valve 85 causes the pressure in the pipe 78 to be reduced. The pressure is reduced to the tank pressure, whereby the above-described relief valve 77 is operated to be in a relief state.

In the above arrangement, the crushing control valve 26 and the left traveling control valve 27 of the first valve group 22, the right traveling control valve 28 of the second valve group, and the pump control valve 38 , The relief valves 89 and 90 are combined as a high-pressure side system, and are integrated into the main valve unit 91. On the other hand, the control valve 29 for the feeder, the control valve 30 for the conveyor, and the control valve 31 for the magnetic separator of the second valve group 23,
A relief valve 77, a pump control valve 82,
The relief valve 85 is integrated as a low-pressure side system, and is integrated into the sub-valve unit 92. Center bypass line 23 of main valve unit 91
The carry-over port 91a on the downstream side of a is connected to the pump port 92a of the sub-valve unit 92 communicating with the center line 23b.

At this time, although the detailed structure is not shown,
Control valve 29 for feeder, control valve 30 for conveyor, and control valve 3 for magnetic separator
The diameter of each of the spools 1 is smaller than the diameter of the spool of the crushing control valve 26, the left traveling control valve 27, and the right traveling control valve 28.

The regulator devices 34 and 35 include tilt actuators 93 and 94, first servo valves 95 and 96, and second servo valves 97 and 98. These servo valves 95
To 98, the pressure of the hydraulic oil acting on the tilt actuators 93, 94 from the pilot pump 25 or the first and second hydraulic pumps 19, 20 is controlled, and the swash plates 19A, 19A, The tilt (ie, displacement) of the 20A is controlled. The tilt actuators 93 and 94 have large-diameter pressure receiving portions 93a and 94 at both ends.
a and operating pistons 93c and 94c having small-diameter pressure receiving portions 93b and 94b, and pressure receiving portions 93a, 93b and 94, respectively.
a and 94b respectively have pressure receiving chambers 93d and 93e and 94d and 94e. And both pressure receiving chambers 93
When the pressures d, 93e and 94d, 94e are equal to each other, the working pistons 93c, 94c move rightward in FIG.
The displacement of 20A becomes large, and the pump discharge flow rates QP1, QP2
Increase. When the pressures in the large-diameter pressure receiving chambers 93d and 94d decrease, the working pistons 93c and 94c move to the left in FIG. QP2 is reduced. The large-diameter side pressure receiving chambers 93d, 94d
Is connected to a pipe 99 communicating with a discharge pipe 79 of the pilot pump 25 via first and second servo valves 95 to 98, and the pressure receiving chambers 93 e and 94 e on the small diameter side are directly connected to the pipe 99. Have been.

Of the first servo valves 95 and 96, the first servo valve 95 of the regulator device 34 is for negative tilt control which is driven by the control pressure (negative control pressure) Pc1 from the pump control valve 38 as described above. The first servo valve 96 of the regulator device 35 is a servo valve.
Are load sensing control servo valves driven by the control pressure (load sensing pressure) Pc2 from the pump control valve 82 as described above, and have the same structure.

That is, when the control pressures PC1 and PC2 are high, the valve bodies 95a and 96a move rightward in FIG. 5, and the pilot pressure PP from the pilot pump 25 is not reduced and the tilting actuators 93 and 94 receive the pressure. This is transmitted to the chambers 93d and 94d, thereby increasing the tilt of the swash plates 19A and 20A, and increasing the discharge flow rates QP1 and QP2 of the first and second hydraulic pumps 19 and 20. As the control pressures PC1 and PC2 decrease, the valve bodies 95a and 96a
5 and the pilot pressure PP from the pilot pump 25 is reduced to reduce the pressure in the pressure receiving chamber 93.
d, 94d, and the first and second hydraulic pumps 19, 2
The discharge flow rates QP1 and QP2 of 0 are reduced. As described above, in the first servo valve 95 of the regulator device 34, specifically, the center bypass is provided so that the discharge flow rate QP1 corresponding to the required flow rate of the control valves 26 and 27 can be obtained in addition to the function of the pump control valve 38 described above. A so-called negative control is realized in which the tilt (discharge flow rate) of the swash plate 19A of the first hydraulic pump 19 is controlled such that the flow rate flowing from the line 22a and passing through the pump control valve 38 is minimized. Further, in the first servo valve 96 of the regulator device 35, specifically, the discharge flow rate QP2 according to the required flow rate of the control valves 28, 29, 30, 31 is obtained in addition to the function of the pump control valve 82 described above. Is the discharge pressure P2 of the second hydraulic pump 20 and the throttle means 29Aa, 30A
The so-called load sensing control for controlling the tilt (discharge flow rate) of the swash plate 20A of the second hydraulic pump 20 so that the difference between the pressures a and 31Aa on the downstream side is kept constant is realized.

On the other hand, the second servo valves 97 and 98 are both servo valves for input torque limiting control, and have the same structure. That is, the second servo valves 97 and 98
Are the discharge pressures P1, P1 of the first and second hydraulic pumps 19, 20.
These valves are operated by P2, and their discharge pressures P1, P2
Is the discharge line 3 of the first and second hydraulic pumps 19 and 20.
A discharge pressure detection pipe 100 branched from 7, 39
The pressure receiving chambers 97b and 97c of the operation driving unit 97a and the pressure receiving chamber 98 of the operation driving unit 98a are transmitted through the ac and 101a to 101c.
b, 98c.

That is, the first and second hydraulic pumps 19,
The operation drive unit 97 is determined by the sum P1 + P2 of the discharge pressures of 20.
When the force acting on the valve bodies 97e and 98e is smaller than the force acting on the valve bodies 97e and 98e due to the spring force set by the springs 97d and 98d, the valve bodies 97e and 98e move rightward in FIG. 25 to the first servo valve 95,
The pilot pressure PP guided through the second 96 is transmitted to the pressure receiving chambers 93d and 94d of the tilt actuators 93 and 94 without reducing the pressure, whereby the first and second hydraulic pumps 19 and 20 are moved.
The inclination of the swash plates 19A and 20A is increased to increase the discharge flow rate. Then, the first and second hydraulic pumps 19, 20
The force due to the sum P1 + P2 of the discharge pressures of the springs 97d and 98d
The valve bodies 97e and 98e move to the left in FIG. 5 as the force becomes larger than the spring force set value, and the pilot pressure PP guided from the pilot pump 25 via the first servo valves 95 and 96 is reduced. To the pressure receiving chambers 93d and 94d, whereby the first and second hydraulic pumps 19 and 2
The discharge flow rate of 0 is reduced.

As described above, the first and second hydraulic pumps 1
As the discharge pressures P1 and P2 of the pumps 9 and 20 increase, the maximum values Q1max and Q2max of the discharge flow rates Q1 and Q2 of the first and second hydraulic pumps 19 and 20 are limited to a small value. So-called input torque limiting control (horsepower control) in which the tilt of the swash plates 19A and 20A of the first and second hydraulic pumps 19 and 20 is controlled so as to limit the total input torque of the engine 21 to the output torque of the engine 21 or less. Is achieved. At this time, in more detail, according to the sum of the discharge pressure P1 of the first hydraulic pump 19 and the discharge pressure P2 of the second hydraulic pump 20, the sum of the input torques of the first and second hydraulic pumps 19, 20 is calculated. The so-called total horsepower control for limiting the output torque to the engine 21 or less is realized.

In this embodiment, both the first hydraulic pump 19 and the second hydraulic pump 20 are controlled to have substantially the same characteristics. That is, the sum P1 of the discharge pressures of the first and second hydraulic pumps 19 and 20 when the first hydraulic pump 19 is controlled by the second servo valve 97 of the regulator device 34.
+ P2 and the maximum value Q1m of the discharge flow rate Q1 of the first hydraulic pump 19
ax and the second servo valve 9 of the regulator device 35
8, the sum P1 + of the discharge pressures of the first and second hydraulic pumps 19 and 20 when the second hydraulic pump 20 is controlled.
P2 and the maximum value Q2max of the discharge flow rate Q2 of the second hydraulic pump 20
And the maximum values Q1max and Q2max of the discharge flow rates Q1 and Q2 of the first and second hydraulic pumps 19 and 20 are substantially equal to each other (for example, with a width of about 10%).
Are restricted by substantially the same value (same).

The most significant feature of the present embodiment is that the pilot pressure from the pilot pump 25 is applied to the variable relief valve 3 of the pump control valves 38 and 82.
8d and 82d, the controller 4 is provided between the pilot introduction pipeline 83a and the pilot introduction pipelines 83b and 83c.
5 is provided with a solenoid control valve 110 which can be switched by a drive signal Sv (described later). When the drive signal Sv input to the solenoid 110a is turned ON, the solenoid control valve 110 turns to the communication position 110A on the left side in FIG.
And the pilot pressure from the pilot pump 25 is supplied to the variable relief valves 38d and 8 via the pilot introduction pipe 83a and the pilot introduction pipes 83c and 83b.
Lead to 2d. As a result, the control pressures Pc1 and Pc2 can be generated in accordance with the required flow rates of the control valves described above. As a result, the discharge flow rates corresponding to the required flow rates of the control valves 26 and 27 can be obtained as described above. Q
Negative control for controlling the tilt of the swash plate 19A of the first hydraulic pump 19 so as to obtain P1, and the second hydraulic pump so as to obtain the discharge flow rate QP2 corresponding to the required flow rate of the control valves 28, 29, 30, and 31. 20 swash plates 20
Load sensing control for controlling the tilt of A can be realized.

On the other hand, when the drive signal Sv is turned off, the solenoid control valve 110 returns to the shut-off position 110B on the right side in FIG. 4 by the restoring force of the spring 110b, and the pilot introduction pipe 83a and the pilot introduction pipes 83b and 83c And the pilot line 83b, 83c is branched from the tank line 47d to form a tank line 47f (FIG. 4).
), And the pressure in these introduction pipe lines 83b and 83c is set as the tank pressure PT. As a result, the control pressures Pc1 and Pc2 are always equal to the tank pressure PT, regardless of the required flow rate of each control valve. In other words, the pump tilt control for obtaining the discharge flow rate according to the required flow rate of the control valve using the negative control and the load sensing control described above becomes invalid. The pump control valve 38, which is realized as a result of the function of the solenoid control valve 110 as described above,
The control characteristics of the pump discharge flow rate and the traveling hydraulic motor supply flow rate by the regulator 82 and the regulator devices 34 and 35 will be described with reference to FIGS. FIG. 6 shows the first hydraulic pump 1
9 and the throttle portion 38 of the pump control valve 38 through the center bypass line 22a.
The excess flow rate Qt1 guided to the aa, or the excess flow rate Qt2 discharged from the second hydraulic pump 20 and guided to the piston throttle portion 82aa of the pump control valve 82 via the relief valve 77, and the pump control valve 38, 82, the variable relief valve 38d, 82
FIG. 9 is a diagram showing a relationship between the control pressures Pc1 and Pc2 generated by the function d.

FIG. 7 shows the control pressure Pc as described above.
FIG. 3 is a diagram showing a relationship between Pc2 and pump discharge flow rates QP1 and QP2 of first and second hydraulic pumps 19 and 20.

FIG. 8 shows the operation amounts of the left and right traveling operation levers 32a and 33a corresponding to the required flow rates of the left and right traveling control valves 27 and 28, and the left and right traveling hydraulic motors 16 and 17 respectively. FIG. 6 is a diagram showing a relationship between a supply flow rate QM and a supply flow rate QM.

(I) The solenoid control valve 110 is in the communication position 1
In the case of 10A In this case, since the pilot pressure from the pilot pump 25 is guided to the variable relief valves 38d and 82d, as described above, the required flow rate of each control valve is large or small (in other words, the excessive flow rate Qt1 or Qt2 is small or large). The control pressures Pc1 and Pc2 are generated according to. That is, in FIG.
Control valves 27, 26 (or 28, 31, 3)
0, 29, the same applies to the following), the control pressure Pc1 (or Pc2) is the maximum if there is no excess flow Qt1 (or Qt2) from the first hydraulic pump 19 to the pump control valve 38 (or 82). As a result, the pump discharge flow rate QP1 (or QP2) reaches the maximum value Qmax, as shown at point 'in FIG. Control valves 27, 26 (or 28, 31, 30, 2)
9) The required flow rate decreases and the excess flow rate Q from the first hydraulic pump 19 to the pump control valve 38 (or 82)
As t1 (or Qt2) increases, as shown by the solid line a in FIG. 6, the control pressure Pc1 (or Pc2) becomes the maximum value P1.
From the pump discharge flow rate QP1 (or QP2) as shown in FIG.
It decreases almost linearly from ax. And in FIG.
Control valves 27, 26 (or 28, 31, 3)
When the required flow rate (0, 29) further decreases and the surplus flow rate Qt1 (or Qt2) further increases and the control pressure Pc1 (or Pc2) decreases to the tank pressure PT (the point in FIG. 6), the point in FIG. ', The pump discharge flow rate QP1 (or QP
2) is the minimum value Qmin, but thereafter, the variable relief valves 38d and 82d are fully opened, and the control pressure Pc1 (or Pc2) remains at the tank pressure PT even if the surplus flow rate Qt1 (or Qt2) increases. And the pump discharge flow rate QP1 (or QP
2) also remains at the minimum value Qmin (point 'in FIG. 7).

As a result, as described above, the negative control for controlling the tilt of the swash plate 19A of the first hydraulic pump 19 so as to obtain the discharge flow rate QP1 corresponding to the required flow rate of the control valves 26 and 27, and the control valve Discharge flow rate Q according to required flow rates of 28, 29, 30, 31
Load sensing control for controlling the tilt of the swash plate 20A of the second hydraulic pump 20 so as to obtain P2 can be realized.

The left and right traveling hydraulic motors 16, 1
In the running state in which the control valve 27 does not operate other than 7, the discharge flow rate QP1 corresponding to the required flow rate of the left travel control valve 27 is discharged from the negatively controlled first hydraulic pump 19, and the discharge flow rate QP1 corresponds to the required flow rate of the right travel control valve 28. The discharge flow rate QP2 is controlled by load sensing.
Discharged from the hydraulic pump 20. At this time, as described above, the required flow rates of the left and right traveling control valves 27 and 28 correspond to the operation amounts of the left and right traveling operation levers 32a and 33a. 32
a, 33a and the left and right traveling hydraulic motors 16, 1
7 has a linear relationship with the supply flow rate QM. That is, when the operation amount X of the left / right traveling operation levers 32a and 33a is 0, the motor supply flow rate QM is 0, and as the operation amount X increases, as shown by a solid line d in FIG.
The supply flow rate QM increases substantially linearly, and when the operation amount X reaches the maximum value Xmax, the motor supply flow rate QM becomes the pump discharge flow rate maximum value Qmax.

(Ii) When the solenoid control valve 110 is in the shut-off position 1
In the case of 10B In this case, since the pressure in the pilot introduction pipes 83b and 83c is the tank pressure PT, as shown by a straight line A in FIG. Control pressures Pc1 and Pc2 are always equal to the tank pressure PT (in other words,
The maximum values Pc1 and Pc2 of the control pressure in the case of the above (i) =
The maximum value of the control pressure is reduced as compared with P1). As a result, as shown by a point 'in FIG.
1 (or QP2) is always the minimum value Qmin (in other words, the maximum pump discharge flow rate QP1 in case (i) above).
(Or QP2) = the maximum discharge flow rate is reduced compared to Qmax). In this way, the pump tilt control for obtaining the discharge flow rate according to the required flow rate of the control valve using the negative control and the load sensing control described above is released.

The left and right traveling hydraulic motors 16, 1
7, the required flow rate of the left / right traveling control valves 27, 28 (ie, the left / right traveling control valves 27, 28).
The minimum flow rate Qmin is discharged from the first and second hydraulic pumps 19, 20 irrespective of the operation amounts of the right traveling operation levers 32a, 33a, and the left and right traveling control valves 27, 28 of the flow rate Qmin are discharged. Only the portion corresponding to the opening degree is the supply flow rate QM to the left and right traveling hydraulic motors 16 and 17. That is, the left and right traveling operation levers 32a, 33
The relationship between the manipulated variable a and the supply flow rate QM to the left and right traveling hydraulic motors 16 and 17 is represented by a straight line having a smaller inclination than the straight line d in the case of the above (i) as shown by a straight line e in FIG. Becomes
When the operation amount X is 0, the motor supply flow rate QM is 0,
As the operation amount X increases, the supply flow rate QM increases almost linearly, and the operation amount X reaches the maximum value Xmax (when the valve is fully open).
, The motor supply flow rate QM becomes the pump discharge flow rate minimum value Qmin.

Returning to FIGS. 3 to 5, the operation panel 36 includes a crusher start / stop switch 36a for starting and stopping the crushing device 2, and an operation direction of the crushing device 2 in a forward or reverse direction. Crusher forward / reverse selection dial 36b for selecting one of them, and feeder 3 is activated.
Feeder start / stop switch 36c for stopping
A conveyor start / stop switch 36d for starting / stopping the conveyor 6, a magnetic separator start / stop switch 36e for starting / stopping the magnetic separator 7, a traveling mode for performing a traveling operation, and a crushing operation for performing a crushing operation. A mode selection switch 36f for selecting one of the modes,
A traveling mode selection switch 36g for selecting a traveling speed normal mode or a slow speed mode, which is a major feature of the present embodiment, is provided.

When an operator operates various switches and dials of the operation panel 36, operation signals are input to the controller 45. The controller 45 controls the crushing control valve 26 and the feeder control valve 2 based on an operation signal from the operation panel 36.
9. Conveyor control valve 30, magnetic separator control valve 31, solenoid control valve 46, and solenoid drive units 26a, 26 of solenoid control valve 110.
b, solenoid drive unit 29a, solenoid drive unit 30
a, the drive signals Scr, Sf, Sc to the solenoid drive unit 31a, the solenoid 46a, and the solenoid 110a.
om, Sm, St, Sv are generated and output to the corresponding solenoid. That is, the operation panel 3
When the "running mode" is selected by the mode selection switch 36f of No. 6, the drive signal St of the solenoid control valve 46 is
Is turned on, the solenoid control valve 46 is switched to the communication position on the left side in FIG.
When the "crushing mode" is selected by the mode selection switch 36f of the operation panel 36, the drive signal St of the solenoid control valve 46 is turned off to return to the shutoff position on the right side in FIG. 3, and the operation levers 32a and 33a are used. The operation of the traveling control valves 27 and 28 is disabled. Further, the crusher start / stop switch 36a is pushed to the "start" side in a state where "forward" (or "reverse" (hereinafter, the correspondence is the same)) is selected by the crusher forward / reverse selection dial 36b of the operation panel 36. In this case, the drive signal Scr to the solenoid drive unit 26a (or the solenoid drive unit 26b) of the crushing control valve 26 is turned ON, and the drive signal Scr to the solenoid drive unit 26b (or the solenoid drive unit 26a) is turned OFF. Then, the crushing control valve 26 is switched to the upper switching position 26A (or the lower switching position 26B) in FIG. 3, and the hydraulic oil from the first hydraulic pump 19 is supplied to the crushing hydraulic motor 9 to be driven, thereby crushing. The device 2 is started in the normal rotation direction (or the reverse rotation direction). Thereafter, when the crusher start / stop switch 36a is pushed to the "stop" side, the drive signals Scr of both the solenoid drive unit 26a and the solenoid drive unit 26b of the crushing control valve 26 are turned off to return to the neutral position shown in FIG. Then, the crushing hydraulic motor 9 is stopped, and the crushing device 2 is stopped.
Also, a feeder start / stop switch 36c of the operation panel 36
Is pushed to the "start" side, the drive signal Sf to the solenoid drive unit 29a of the feeder control valve 29 is
To ON to switch to the upper switching position 29A in FIG.
The pressure oil from the second hydraulic pump 20 is supplied to and driven by the feeder hydraulic motor 10 to start the feeder 3. Thereafter, when the feeder start / stop switch 36c of the operation panel 36 is pushed to the "stop" side, the drive signal Sf to the solenoid drive unit 29a of the feeder control valve 29 is turned off.
The FF is returned to the neutral position shown in FIG. 4, the feeder hydraulic motor 10 is stopped, and the feeder 3 is stopped. Similarly, when the conveyor start / stop switch 36d is pushed to the "start" side, the conveyor control valve 30 is switched to the upper switching position 30A in FIG. 4, and the conveyor hydraulic motor 11 is driven to start the conveyor 6. Then, when the conveyor start / stop switch 36d is pushed to the "stop" side,
The conveyor control valve 30 is returned to the neutral position, and the conveyor 6 is stopped. When the start / stop switch 36e of the magnetic separator is pushed to the "start" side, the control valve 31 for the magnetic separator is switched to the upper switching position 31A in FIG.
And the magnetic separator hydraulic motor 13 is driven to start the magnetic separator 7, and when the magnetic separator start / stop switch 36e is pushed to the "stop" side, the magnetic separator control valve 31
Is returned to the neutral position, and the magnetic separator 7 is stopped. Also,
When the “normal mode” is selected by the drive mode selection switch 36g, the drive signal S of the solenoid control valve 110 is
v is turned on, the solenoid control valve 110 is switched to the communication position 110A on the left side in FIG. 4, and the required flow rates of the left and right traveling control valves 26 and 27 (the left and right traveling operation levers 32a and 33a It is possible to control the pump discharge flow rate according to the manipulated variable X). When the "slow speed mode" is selected by the traveling mode selection switch 36g, the drive signal Sv of the solenoid control valve 110 is turned off to return to the shutoff position 110B on the right side in FIG. The control of the pump discharge flow according to the required flow rates of the control valves 26 and 27 is stopped, and the pump discharge flows QP1 and QP2 are set to a constant value Qmin.

In the above, the crawler track 14 constitutes the traveling means described in the claims, the hopper 1 constitutes the receiving means for receiving the recycled material, and the crushing device 2 performs a predetermined process on the recycled material. Construct a processing device. Also, the left and right traveling control valves 27,
28 constitutes travel control valve means for controlling the flow of hydraulic oil supplied to the travel hydraulic motor, and left and right travel operation lever devices 32, 33 operate travel travel valve means for operating the travel control valve means. Configure the operation means.

The traveling mode selection switch 36g of the operation panel 36 constitutes a selection means for selectively inputting either the first mode or the second mode of the traveling means.
It also constitutes input means for inputting an instruction regarding the operating speed of the traveling means. At this time, the normal mode corresponds to the first mode, and the slow mode corresponds to the second mode.

Further, the pump control valve 38,
The control pressure 82 generates pressure control means for converting the flow rate of the hydraulic oil flowing downstream of the center bypass line of the travel control valve means into pressure, and generates a control pressure corresponding to the required flow rate of the travel hydraulic motor. The generating means is also constituted. Further, the regulator devices 34 and 35 constitute regulator means for controlling the discharge flow rate of the hydraulic pump according to the control pressure from the control pressure generating means. The regulator devices 34 and 35 and the pump control valve 3
8 and 82 constitute pump adjusting means for adjusting the discharge flow rate of the hydraulic pump with a predetermined adjustment characteristic to the required flow rate of the traveling hydraulic motor, and the characteristic lines shown in FIGS. Is equivalent to Further, when the first mode is selected by the selecting means, the solenoid control valve 110 increases the maximum value of the control pressure relatively to make the maximum discharge flow rate of the hydraulic pump a relatively high value. Second
When the mode is selected, the control pressure switching means is configured to make the maximum value of the control pressure relatively small to make the maximum discharge flow rate of the hydraulic pump a relatively low value, and to respond to an instruction from the input means. Thus, it also constitutes a characteristic control means for changing the adjustment characteristic of the pump adjustment means or the control pressure. The regulator devices 34 and 35, the pump control valves 38 and 82, and the solenoid control valve 110
Constitutes a control means for controlling the discharge flow rate of the hydraulic pump with a control characteristic according to an instruction from the input means with respect to the required flow rate of the traveling hydraulic motor.

Next, the operation of the self-propelled crusher according to the present embodiment having the above configuration will be described below.

(I) At the time of crushing operation In the self-propelled crusher having the above-mentioned configuration, at the time of crushing operation, the operator selects the "crushing mode" with the mode selection switch 36f of the operation panel 36 to disable the traveling operation. Then, while selecting "forward" with the crusher forward / reverse selection dial 36b and turning the crusher speed setting dial 36c to a position where the desired speed is set, the magnetic separator start / stop switch 36f, the conveyor start / stop switch 36e, crusher start / stop switch 36a, feeder start / stop
The stop switch 36d is sequentially pushed to the "start" side.

With the above operation, the controller 45 controls the solenoid drive unit 3 of the control valve 31 for the magnetic separator.
When the drive signal Sm to 1a is turned ON, the control valve 31 for the magnetic separator is switched to the upper switching position 31A in FIG. Turned ON and conveyor control valve 3
0 is switched to the upper switching position 30A in FIG. Further, the drive signal Scr from the controller 45 to the solenoid drive section 26a of the crushing control valve 26 is turned on.
And the drive signal S to the solenoid drive section 26b.
The cr is turned off, the crushing control valve 26 is switched to the upper switching position 26A in FIG.
The drive signal Sf to ON is turned ON, and the feeder control valve 29 is switched to the upper switching position 29A in FIG.

Thus, the pressure oil from the second hydraulic pump 20 is introduced into the pump port 92a and the center line 23b of the sub-valve unit 92 via the center bypass line 23a and the carry-over port 91a of the main valve unit 91. Hydraulic motor for magnetic separator 13,
The magnetic separator 7, the conveyor 6, and the feeder 3 are supplied to the conveyor hydraulic motor 11 and the feeder hydraulic motor 10, and are started. On the other hand, the pressure oil from the first hydraulic pump 19 is supplied to the crushing hydraulic motor 9, and the crushing device 2 is started in the normal rotation direction.

When the crushed raw material is charged into the hopper 1 by, for example, a bucket of a hydraulic shovel, the input crushed raw material is guided to the crushing device 2 while only those having a predetermined particle size or more are sorted out in the feeder 3 and crushed. Crushed to a predetermined size by the device 2. The crushed crushed material falls from the space below the crushing device 2 onto the conveyor 6 and is conveyed. During the conveyance, the crushed crushed material is mixed with the crushed material by the magnetic separator 7 (for example, mixed with concrete construction waste material). The crusher is removed from the crusher (right end in FIG. 1).

(II) Self-Running As described above, usually, when a self-propelled recycle product production machine such as a self-propelled crusher performs self-propelled operation, it is arranged and moved in an operation site (for example, a recycling processing plant). There are two types: time (that is, when traveling on level ground) and loading and unloading on a trailer during transportation. Therefore, the operation during self-propelled driving will be described below separately for these two cases.

(II-1) Traveling on level ground For example, when the self-propelled crusher travels on level ground in the operation site, the operator selects the "traveling mode" with the mode selection switch 36f of the operation panel 36, "Normal mode" is selected by the driving mode selection switch 36g, and the operator enters the driver's seat 24a and operates the operation levers 32a and 33a forward. Thereby, the left / right traveling control valves 27, 28 are switched to the upper switching positions 27A, 28A in FIG. 3, and the hydraulic oil guided from the first hydraulic pump 19 via the center bypass line 22a travels left / right. Are supplied to the hydraulic motors 16 and 17, which are driven in the forward direction. The crawler tracks 14 on both sides of the crusher are driven in the forward direction, and the traveling body 5 travels forward.

At this time, the driving mode selection switch 36g
Selects the "normal mode", the solenoid control valve 110 becomes the communication position 110A, and as described above, the operation amount X of the left / right traveling operation levers 32a and 32b.
The discharge flow rate QP1 corresponding to the first and second hydraulic pumps 19,
20 and the degree of opening of the left and right traveling control valves 27 and 28 increases according to the manipulated variable X. As a result, the supply flow rate QM according to the operation amount X is supplied to the left and right traveling hydraulic motors 16 and 17.

At this time, the relationship between the operation amount X and the motor supply flow rate QM is such that the operation amount X of the left / right traveling operation levers 32a, 33a is 0, as shown by the solid line d in FIG. When the motor supply flow rate QM increases from 0 to the maximum value Xmax, the motor supply flow rate QM increases from 0 to the pump discharge flow rate maximum value Qmax. In this manner, the left and right traveling operation levers 32a,
When 32b is the maximum value Xmax (i.e., at the time of the full lever), the supply flow rate to the left / right traveling hydraulic motors 16 and 17 can be increased so that the vehicle can travel at a high speed.
The left and right traveling hydraulic motors 16 and 1 are operated at a relatively high rate with respect to an increase in the operation amount X of the right traveling operation levers 32a and 32b.
7, and the amount of increase in the traveling speed can be increased.

As a result, the operator can operate the operation lever 3 for traveling.
By operating the 2a and 32b with a relatively large operation amount, high-speed traveling is possible, so that the vehicle can be quickly moved to a desired position in a movable site, and an operation rate can be improved.

(II-2) Loading / unloading to / from a trailer For example, when the vehicle travels by itself onto a trailer carrier to load on a trailer in order to head to an operation site (or to descend from the trailer carrier after arriving at the operation site). If you run, the same applies to parentheses in this section)
The operator operates the mode selection switch 36f of the operation panel 36.
To select the "running mode", and to select the "slow speed mode" using the running mode selection switch 36g.
a, and operates the operation levers 32a and 33a forward (or backward). As a result, the left and right traveling control valves 27, 28 are switched to the upper switching positions 27A, 27A in FIG.
28A (or 27B, 28B), and the pressure oil guided from the first hydraulic pump 19 via the center bypass line 22a is supplied to the left and right traveling hydraulic motors 16, 17, which are forward (or reverse). Direction), and the crawler tracks 14 on both sides of the crusher are forward (or reverse).
And the traveling body 5 travels forward (or backward).

At this time, the traveling mode selection switch 36g
Selects the "slow speed mode", the solenoid control valve 110 is brought to the shut-off position 110B, and as described above, the operation amount X of the left / right traveling operation levers 32a, 32b.
The minimum pump flow Qmin is constantly discharged from the first and second hydraulic pumps 19 and 20 irrespective of the control amount of the left and right traveling control valves 27 and 2 according to the manipulated variable X.
The opening degree of No. 8 becomes large (the aperture becomes small). As a result, the supply flow rate QM according to the operation amount X is supplied to the left and right traveling hydraulic motors 16 and 17.

At this time, the relationship between the operation amount X and the motor supply flow rate QM is such that the operation amount X of the left and right traveling operation levers 32a and 33a is 0, as shown by the solid line e in FIG. , The motor supply flow rate QM increases only from 0 to the pump discharge flow rate minimum value Qmin. In this manner, the left and right traveling hydraulic motors 16 and 1 when the left and right traveling operation levers 32a and 32b are at the maximum value Xmax (ie, at the time of the full lever).
7 can be reduced (in other words, the relationship between the operation amount of the left / right traveling control lever and the traveling speed can be changed as compared with the above-described "normal mode"). This allows the operator to operate the traveling operation lever 32.
By operating a and 32b with a relatively small operation amount, it is possible to travel at an extremely low speed (slow traveling). Further, the supply flow rate of the left and right traveling hydraulic motors 16 and 17 is increased at a relatively low rate with respect to the increase in the operation amount X of the left and right traveling operation levers 32a and 32b. Speed change can be reduced, and precise control of self-propelled speed becomes possible. According to the hydraulic drive device of the self-propelled crusher according to the embodiment of the present invention having the configuration and operation described above, the following effects can be obtained.

(1) Productivity Improvement Effect by Reduction of Pressure Loss at Slow Traveling According to the present embodiment, as described above, the first and the second
The pump discharge flow rates QP1 and QP2 of the hydraulic pumps 19 and 20 are increased or decreased, and the supply flow rate Q to the left and right traveling hydraulic motors 16 and 17 is increased.
By increasing or decreasing M itself, both high-speed traveling and very low-speed traveling are enabled. Thereby, at the time of traveling at a very low speed, the first and second hydraulic pumps 19 and 20 → the control valves 27 and 28 for the left and right traveling → the hydraulic motors 16 and 17 for the left and right traveling.
Therefore, the flow rate of the series of pressure oil supply paths becomes smaller, so that the flow rate of the left and right travel control valves 27 and 28 can be reduced. As a result, the pressure loss generated in the left and right traveling control valves 27 and 28 is reduced at least as compared with the above-described conventional technology in which the same large flow rate is supplied even at the time of low-speed traveling as at the time of high-speed traveling. And the horsepower required for the engine 21 that drives the hydraulic pumps 19 and 20 can be reduced accordingly. As a result, the fuel consumption of the engine 21 can be reduced, so that the operation time can be extended and the productivity can be improved. (2) Effects of Fixed Capacity Left / Right Travel Hydraulic Motor According to the present embodiment, the left / right travel hydraulic motor 1
The fixed capacitance type 6 and 17 are sufficient, and there is no need to use a variable capacitance type as in the prior art. Accordingly, various mechanisms (for example, a swash plate driving mechanism) for changing the capacity can be omitted, so that the number of components can be reduced, the structure can be simplified, reliability can be improved, and cost can be reduced. .

In the embodiment of the present invention, the solenoid control valve 110 is an ON-OFF electromagnetic switching valve,
At the shut-off position 110B corresponding to the selection of the "slow speed mode", the pressures in the pilot introduction pipes 83b and 83c are reduced to the tank pressure to reduce the control pressures Pc1 and Pc2 to the tank pressure PT.
7 (see the solid line a in FIG. 6), and as a result, the characteristic shown by the point 'in FIG. 7 is obtained, whereby the characteristic shown by the solid line e in FIG. 8 is obtained. is not.

That is, the solenoid control valve 110 is an electromagnetic proportional valve, and a separate speed setting dial for appropriately setting the maximum speed when the fine speed mode is selected is provided on the operation panel 36. When the "fine speed mode" is selected, the speed setting dial is operated. A signal of a drive current value corresponding to the amount may be output from the controller 45 to the solenoid control valve 110 so that the opening degree is set according to the set value of the speed setting dial. In this case, the pressures in the pilot introduction pipes 83b and 83c are set to a desired P2 (where PT <P2 <P1) according to the set values, and the values of the control pressures Pc1 and Pc2 are also reduced to P2 (see FIG. 6). As a result, the characteristic between the points ′ and ′ in FIG. 7 is obtained, and as a result, the characteristic as shown by the two-dot chain line in FIG. 8 is obtained. In this case, there is an advantage that the operator can arbitrarily set how much low-speed traveling (or how precise speed control is to be performed) in the low-speed mode by setting the speed setting dial.

In the embodiment of the present invention, the maximum load pressure of the auxiliary machine hydraulic motors 10, 11, 13 is controlled by the pipes 65, 66, 67, 69, 71, 78 and the shuttle valves 68, 70. While detecting, the pressure control valves 51, 54,
At 57, the differential pressure between the downstream pressure of the throttle means 29Aa, 30Aa, 31Aa and the maximum load pressure is kept constant, and the unload valve 77 is used to control the discharge pressure P2 of the second hydraulic pump 20 and the maximum load pressure. Although the differential pressure is kept constant and the differential pressures before and after the throttling means 29Aa, 30Aa and 31Aa are kept constant to obtain a reliable distribution function, the present invention is not limited to this. For example, a pressure compensating valve may be provided simply to guide the differential pressure across the throttling means 29Aa, 30Aa, 31Aa to both ends, and the differential pressure may be kept constant by the set pressure of the spring. Further, in the above, the load sensing control is performed by using the unload valve 77 to keep the pressure difference between the discharge pressure P2 of the second hydraulic pump 20 and the maximum load pressure constant, but the present invention is not limited to this. Absent. That is, the second
For example, the discharge pressure P2 of the hydraulic pump 20 is detected by a pressure sensor or the like, and the maximum load pressure is also detected by a pressure sensor or the like. Is calculated, and the second differential pressure is kept constant according to the calculation result.
The tilt angle of the hydraulic pump 20 may be controlled.

In the embodiment of the present invention, of the left and right traveling control valves 27 and 28, the left traveling control valve 27 is included in the first valve group 22, and the right traveling control valve 28 is included. Although they are allocated to the second valve group 23, the above effects (1) and (2)
As long as is obtained, the arrangement is not necessarily required. For example, the right traveling control valve 28 may be arranged in the first valve group 22. However, in this case, from the viewpoint of ensuring straight traveling performance, some means for balancing the pressure oil supplied to the left and right traveling hydraulic motors 16 and 17 via the left and right traveling control valves 27 and 28 during traveling (for example, for example) Left / right running control valve 27,
28 pressure compensation means).

Further, in the above-described embodiment of the present invention, a self-propelled crusher provided with a jaw crusher for crushing moving teeth and fixed teeth as the crushing device 2 has been described as an example, but is not limited to this. Another crushing device, for example, a pair of roll-shaped rotating bodies having a crushing blade attached thereto is rotated in a direction opposite to each other, and crushing is performed by sandwiching rocks, construction waste materials, and the like between the rotating bodies. (A six-shaft crusher including a so-called roll crusher) that performs cutting, and a crusher (a so-called shredder) that shears rocks, construction waste, and the like by providing cutters on axes arranged in parallel and rotating them in opposite directions. Twin-shaft shearing machine including
And a crushing device (so-called impact crusher) for rotating a striking plate equipped with a plurality of blades at a high speed, and crushing rocks, construction waste materials, etc. using the impact from the striking plate and the collision with the repelling plate. The present invention can also be applied to a wood crushing machine in which wood, such as wood, branch wood, and construction waste wood, is put into a rotor provided with a cutter to turn the wood into small pieces. In these cases,
The feeder 3 may be omitted as appropriate. In these cases, a similar effect is obtained. In the embodiment of the present invention, as the feeder 3, a grizzly feeder that vibrates a bottom plate portion including a plurality of saw-tooth plates 3a on which objects to be crushed are placed by using the driving force of a hydraulic motor. Although the self-propelled crusher provided with is described as an example, the invention is not limited to this. That is, another type of feeder, for example, a crushed object input from a hopper is placed on a substantially flat bottom plate provided below the hopper, and the bottom plate is driven by a base driving mechanism based on a driving force generated by a hydraulic motor. Equipped with a so-called plate feeder that reciprocates in a substantially horizontal direction to sequentially extrude the preceding crushed object on the bottom plate by inputting the subsequent crushed object and sequentially supply the crushed object to the crushing device from the front end of the bottom plate. It is also applicable to shredders.

In the embodiment of the present invention, the feeder 3, the conveyor 6, and the magnetic separator 7 serve as auxiliary machines for performing operations related to the crushing operation by the crushing device 2.
Although the description has been made by taking as an example a case where the present invention is applied to a self-propelled crusher provided with a crusher, the present invention is not limited to this. That is, a self-propelled crusher in which some of the feeder 3, the conveyor 6, and the magnetic separator 7 are appropriately omitted, for example, the crushing raw material is directly supplied from the hopper 1 to the crushing device 2 via a duct or a chute without the feeder 3. The present invention may be applied to a device having no hopper 1 and the chute itself constituting the receiving means, or a device in which the magnetic separator 7 is omitted according to the working circumstances. vice versa,
In addition to the feeder 3, the conveyor 6, and the magnetic separator 7, additional auxiliary machines, for example, an auxiliary conveyor (a secondary conveyor, a secondary conveyor, which is located downstream (or upstream) of the conveyor 6 in order to lengthen the path of the conveyor 6). (A tertiary conveyor, a sub-conveyor, etc.) or a self-propelled crusher provided with a vibrating screen located downstream of the crushing device 2 for further sorting according to the particle size of the crushed material. When an auxiliary machine is added, the corresponding control valve must be
Needless to say, it is provided in the valve group 23 so that pressure oil from the second hydraulic pump 20 is supplied. In these cases, a similar effect is obtained. The above description is directed to a self-propelled recycle product production machine to which the hydraulic drive device according to the present invention is applied. For example, rock, construction waste, industrial waste, or the like (= crushed material) is used as a recycled material and crushed for recycling. The self-propelled crusher that produces a product is described as an example, but the present invention is not limited to this. That is, for example, excavated soil generated in gas pipes and other burial works, water and sewage works, and other road works and foundation works that are not suitable for backfilling are used as recycled materials.
The present invention may be applied to a self-propelled soil conditioner that produces improved soil as a product for recycling (including a self-propelled fluidization processor that makes excavated soil into a slurry state). A case where the hydraulic drive device according to the present invention is applied to a self-propelled soil improvement machine will be described below.

FIG. 9 shows this self-propelled soil improvement machine 200.
It is a side view showing the detailed structure of. In FIG. 9, a soil improvement machine 200 receives a recycled material (= earth and sand to be improved) by a working tool such as a bucket of a hydraulic shovel and sorts the injected earth and sand into a predetermined particle size (details will be described later). Unit 201, this sieve unit 20
A sediment hopper 202 as a receiving means for receiving and temporarily storing the sediment selected in step 1, and crushing and mixing the sediment introduced from the sediment hopper 202 with a predetermined soil improving material (solidified material). A mixing device (processing tank) 203 as a processing device for discharging downward, a carry-in conveyor (feeder) 204 for transporting and introducing the earth and sand received in the earth and sand hopper 202 to the mixing device 203, and supplying the soil improvement material. Soil improvement machine main body 206 equipped with soil improvement material supply device 205 for
And a rear side of the self-propelled soil improvement machine 200 which receives the mixture mixed by the mixing device 203 and discharged downward (in the longitudinal direction of a track frame soil improvement machine mounting portion 209A described later). Fig. 9
(The middle right side).

The traveling body 207 is composed of a track frame 209 and left and right endless track tracks 210 as traveling means.
And The track frame 209 is formed of, for example, a substantially rectangular frame, and the sieve unit 201,
A soil improvement device mounting portion (body frame) 209A that forms a chassis on which the earth and sand hopper 202, the mixing device 203, the soil improvement material supply device 205, and a power unit (machine room) 279 described below are mounted; It comprises a leg 209B for connecting the improved machine attachment part 209A and the above-mentioned left / right crawler track 210. The crawler track 210 is stretched between a drive wheel 211 and a driven wheel (idler) 212 rotatably supported by the legs 209B, and is provided on the drive wheel 211 for left and right running. The self-propelled soil improvement machine 200 is made to run by the application of driving force by the hydraulic motor 213.

The sieve unit 201 is a so-called vibrating sieve capable of vibrating in the vertical direction. The support post 21 is provided upright on the truck frame soil improvement machine mounting portion 209A.
4, a support frame 217 elastically supported by a support member 215 via a spring 216,
A vibration member (not shown) mounted on the rotating member 17 and a hydraulic motor for vibration (for generating a driving force for rotationally driving a rotating drum (the same) having a vibration axis (the same) inserted therein) are driven. The same). Then, the driving force of the vibration hydraulic motor is transmitted to the rotating drum and rotated, and the vibration axis of the lattice member is vibrated.
17 vibrates up and down.

The carry-in conveyor 204 rises obliquely at a predetermined angle from one side in the longitudinal direction of the truck frame soil improvement machine mounting portion 9A to the other side (toward the rear of the self-propelled soil improvement machine 200). It is provided so as to be inclined. And this loading conveyor 204
And a transport belt 225 wound and provided between a drive wheel 223 and a driven wheel (idler) 224 supported by the frame 222 and driven by a carry-in conveyor hydraulic motor (not shown). Belt 225
Roller 226 for supporting the transport surface at
And regulating plates 227 provided on the left and right sides in the width direction at the downstream end of the conveying surface of the conveying belt 225.

The earth and sand hopper 202 has an upper end fixed to the support member 215 and a lower end inclined at an angle corresponding to the inclination angle of the carry-in conveyor 204. The sand hopper 202 has a bottomless box shape (in other words, a substantially rectangular tube shape or a frame shape) whose diameter increases upward for convenience when the sand is smoothly fed from the sieve unit 201. And the upper and lower sides are open.

At this time, of the four peripheral side walls (not shown) constituting the frame of the earth and sand hopper 202, the side wall (the same) located on the downstream side in the feed direction of the carry-in conveyor 204 has a height. An unillustrated earth and sand supply opening (gate) having substantially the same height as the regulating plate 227 and a width dimension slightly smaller than the width of the conveyor belt 225 of the carry-in conveyor 204 is formed. And earth and sand hopper 2
02 is a conveyor belt 22 of a carry-in conveyor 204 which receives the earth and sand input from the sieve unit 201 through an upper opening.
5 and is conveyed to the downstream side. At this time, of the input sediment conveyed on the conveying belt 225, the one that has passed through the supply opening (= the height of the supply opening only). Only) is drawn out of the earth and sand hopper 202 (pulled out) and led to the mixing device 203. Thus, a predetermined amount of earth and sand determined by the conveyance speed of the conveyance belt 225 in the carry-in conveyor 204 and the opening area of the earth and sand supply opening is supplied from the earth and sand hopper 202 to the mixing device 203.

The above-mentioned soil improvement material supply device 205 is supported by, for example, a substantially rectangular base plate 233 provided on four (or three) columns 232 erected on the truck frame soil improvement machine mounting portion 209A. Have been. At this time, the downstream end of the carry-in conveyor 204 extends to a position between the columns 232 and 232, and in such a positional relationship, is directly above the downstream end of the carry-in conveyor 204. A predetermined amount of soil improvement material is added to the earth and sand supplied from the earth and sand hopper 202 on the carry-in conveyor 4 by the soil improvement material supply device 205.

The soil improving material supply device 205 includes a storage tank 234 for storing a predetermined amount of soil improving material, and a feeder 235 connected to a lower portion of the storage tank 234 and supplying the soil improving material by a predetermined amount. ing. The soil improvement material is mixed in order to improve and modify the earth and sand to produce the above-described high-quality hydraulic composite roadbed material particle size adjusting material (stabilizing material). For example, lime is used. You.

The storage tank 234 has a substantially cylindrical shape as a whole and has a space for storing the soil improving material therein, and has a variable height (details will be described later). That is, the lower side of the storage tank 234 is installed on the base plate 233,
36, a top plate part 237, and a bellows part 238 as an upper tank part provided between the lower tank part 236 and the top plate part 237 and having a variable upper volume.

A bottom plate (not shown) of the lower tank portion 236 is provided with a soil improving material supply opening having a predetermined opening diameter, and supplies the soil improving material to the feeder 235 from this opening. . And the lower tank part 23
In the lower part of 6, an in-tank agitator (not shown) is provided.

This tank agitating device is provided in the lower tank section 2.
36, a plurality of main stirring blades (not shown) attached to a rotating shaft 230 extending through the center of the bottom plate of
The main stirring blade is arranged at a position close to the bottom plate in the lower tank part 236. On the other hand, the lower tank portion 23 of the rotating shaft 230
The position outside 6 is connected to a stirring hydraulic motor (not shown) fixedly provided on the back side of the bottom plate. With such a configuration, the in-tank agitating device is used to
The soil improving material stored in the stirrer is stirred to improve the uniformity and fluidity so that the material can be smoothly and reliably supplied to the feeder 235.

The feeder 235 is a so-called rotary feeder, in which a rotor (not shown) rotatably driven by a feeder motor (not shown) is provided. The rotor is provided with a plurality of partitions (the same) radially, and every time the rotor rotates a predetermined angle, the soil improvement material corresponding to the space between adjacent partitions is separated, and the volume of the space is reduced. Of soil improvement materials are supplied in fixed quantities. Thus, by controlling the rotation speed of the feeder motor, the supply amount (addition rate) of the soil improving material can be controlled, and the mixing ratio between the earth and sand and the soil improving material can be accurately kept constant. . More specifically, for example, the amount of earth and sand transported by the carry-in conveyor 204 is detected by a detection unit (not shown) (or by detecting the amount of the earth / sand / soil improving material mixture by the carry-out conveyor 208, the amount of earth and sand transferred by the carry-in conveyor 204 is indirectly detected). The transport amount may be detected), and the drive of the feeder hydraulic motor is controlled in accordance with the detected amount. The storage tank 234 is divided into upper and lower parts, and the bellows 2
The reason why 38 is provided is to increase the storage capacity of the soil improvement material in the storage tank 2 and to reduce the height of the self-propelled soil improvement machine 200 when transporting the whole by a trailer or the like. .

That is, a support rod 258 is suspended from a mounting plate 257 provided on the top plate portion 237, and
A guide cylinder 259 is provided upright at a position corresponding to the vertical position of each of the 33 support rods 258. And the guide cylinder 259
When the stopper pin (not shown) is inserted with the insertion hole 260 provided below the support rod 258 aligned with the pin insertion hole 261 provided at (The state of FIG. 9), the pin insertion hole 260 provided above the support rod 258 is
When the stopper pin is inserted through the bellows portion 23
8 is held in a stored state.

The mixing device 203 is provided at a mixing device main body 262 composed of a rectangular container arranged in a longitudinal direction (= substantially horizontal direction) and an upper portion on the front side of the mixing device main body 262. An inlet (not shown) for introducing the soil improving material from the soil and soil improving material supply device 205, a discharge port (same) provided at the lower rear side of the mixing device main body 262, and a mixing device main body 262. An even number (for example, two) of paddle mixers provided in parallel with each other and a mixing hydraulic motor 27 for generating a driving force
And 2.

The paddle mixer has a rotating shaft (not shown)
A large number of blades (paddles, not shown) as stirring / transfer members are provided intermittently (for example, at every 90 ° in the circumferential direction and at a predetermined pitch in the axial direction). , A mixing hydraulic motor 27 via a transmission gear (not shown)
2 output shafts. Then, by driving the mixing hydraulic motor 272, the two rotating shafts of the paddle mixer are simultaneously and rotationally driven in opposite directions (so that the opposite sides of the two rotating shafts rotate upward), and both the rotating shafts are rotated through the introduction ports. The earth and sand introduced into the center between the paddle mixers and the soil reforming material are transferred to the discharge port while stirring, and during the transfer, the mixture is crushed (coarse crushed) and uniformly mixed. , To produce improved soil. The improved soil thus produced is discharged from the discharge port onto the carry-out conveyor 208 by the action of its own weight.

The unloading conveyor 208 drives the belt 75 by the unloading conveyor hydraulic motor 274, thereby transporting the mixture (improved soil) that has dropped onto the belt 275 from the mixing device 203, and The improved machine 200 is carried out from the rear. A power unit 279 is provided via a power unit loading member 278 on an upper portion of a longitudinally rear end (the right side in FIGS. 1 and 9) of the truck frame soil improvement device attaching portion 209A.
Is installed. On the front side (left side in FIG. 9) of the power unit 279, a driver's seat (not shown) on which an operator rides is provided.

The sieve unit 201, the mixing device 203, the carry-in conveyor 204, the traveling body 207, the carry-out conveyor 208, and the agitating device in the tank are driven by a hydraulic drive device provided in the self-propelled soil improvement machine. Driven member. The hydraulic drive of k has substantially the same configuration as the hydraulic drive described with reference to FIGS. That is, in FIGS.
The right and left traveling hydraulic motors 16 and 17 are used for the left and right traveling hydraulic motors 213, the crushing hydraulic motor 9 is used for the mixing hydraulic motor 272, the feeder hydraulic motor 10 is used for the carry-in conveyor hydraulic motor, and the conveyor The hydraulic motor 11 is replaced with the stirring hydraulic motor, the magnetic separator hydraulic motor 13 is replaced with the carry-out conveyor hydraulic motor 274, and
Control valve 2 for left and right running corresponding to them
7 and 28 are left and right traveling control valves for controlling hydraulic oil to the left and right traveling hydraulic motors 213, and the crushing control valves 26 are the mixing hydraulic motors 272.
The control valve for mixing to control the pressure oil to the feeder, the control valve for the feeder 29 to the control valve for the carry-in conveyor for controlling the pressurized oil to the hydraulic motor for the carry-in conveyor, and the control valve 30 for the conveyor to the hydraulic motor for agitation. The control valve for agitation for controlling the pressure oil to the conveyer and the control valve 31 for the magnetic separator are replaced with a control valve for the carry-out conveyor for controlling the pressure oil to the hydraulic motor 274 for the carry-out conveyor.
And the same structure on the downstream side of the feeder control valve 29 than the arrangement of the three control valves of the magnetic separation machine control valve 31, the conveyor control valve 30, and the feeder control valve 29 from the upstream side of the center line 23b. And a control valve for the vibrating hydraulic motor that vibrates the sieve unit 201 is controlled by the control valve.

The other structure is almost the same as the structure shown in FIGS.

At this time, a control valve device (not shown) containing the above-mentioned various control valves is mounted on the engine 2.
The first and second hydraulic pumps 19 and 20 are housed and arranged in the power unit 279.

In the hydraulic drive of the self-propelled soil improvement machine as described above, the same operation and effect can be obtained by the same principle as that of the hydraulic drive of the self-propelled crusher described above.

That is, during the soil improvement work, the pressure oil from the second hydraulic pump 20 is supplied to the center bypass line 23 a of the main valve unit 91 and the carry-over port 9.
1a, the pump port 9 of the sub-valve unit 92
2a and the center line 23b, and further supplied to the unloading conveyor hydraulic motor 274, the stirring hydraulic motor, the loading conveyor hydraulic motor, and the vibration hydraulic motor of the sieve unit 201, and the unloading conveyor 208, the tank stirring device. , The conveyer 204 and the sieve unit 201 are activated. On the other hand, the pressure oil from the first hydraulic pump 19 is supplied to the mixing hydraulic motor 272 and the mixing device 203 is started.

When the vehicle runs on its own, the operator gets on the driver's seat of the power unit 279 and operates the operation levers 32a and 33a (see FIG. 3) provided on the driver's seat. As a result, the left and right traveling control valves 27 and 28 are switched, and the pressure oil guided from the first hydraulic pump 19 via the center bypass line 22a is supplied to the left and right traveling hydraulic motors 213 and 213. Is driven to drive the crawler track 210 and the traveling body 207 travels. At this time, by selecting the "normal mode" or the "slow speed mode" with the traveling mode selection switch 36g, the relationship between the operation amount of the left / right traveling operation lever and the traveling speed can be changed, and the ultra-low speed traveling can be performed. (Slow speed running) becomes possible, and precise control of the self-running speed becomes possible. At this time, similarly to the hydraulic drive device of the self-propelled crusher, (1) the effect of improving the productivity by reducing the pressure loss at the time of low-speed traveling, and (2) the effect of the fixed displacement type left / right traveling hydraulic motor. Can be obtained.

As can be seen from the above description, the basic technical idea of the present invention is that the operation amounts of the left and right traveling operation levers 32a and 33a and the self-propelled recycle product production machine are controlled according to the instruction input by the operator. The first and second hydraulic pumps corresponding to the operation amounts of the left and right traveling operation levers 32a and 33a in response to the instruction input when changing the relationship between the self-propelled speed and the high-speed traveling and the very low-speed traveling. 19, 20 discharge flow rate Q
The purpose is to change the control characteristics of P1 and QP2, thereby reducing the pressure loss during very low-speed running,
It is intended to improve productivity.

[0137]

According to the present invention, when a relatively low speed instruction is input by the input means, the maximum pump discharge flow rate can be suppressed to a relatively low value. And precise speed control becomes possible. On the other hand, when a relatively high-speed instruction is input by the input means, the maximum pump discharge flow rate can be set to a relatively high value, and high-speed traveling on flat ground can be performed. As described above, the pump discharge flow rate is increased and decreased, and the supply flow rate itself to the travel hydraulic motor is increased / decreased, thereby enabling both high-speed travel and low-speed travel, thereby reducing pressure loss during low-speed travel and improving productivity. Can be improved.

Since the traveling hydraulic motor is of a fixed displacement type, various mechanisms (for example, a swash plate driving mechanism) for varying the displacement can be omitted. As a result, the number of parts can be reduced and the structure can be simplified, thereby improving reliability and reducing costs.

[Brief description of the drawings]

FIG. 1 is a side view showing the entire structure of a self-propelled recycled product production machine provided with an embodiment of a hydraulic drive device of the present invention.

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

FIG. 3 is a hydraulic circuit diagram illustrating an embodiment of the hydraulic drive device of the present invention.

FIG. 4 is a hydraulic circuit diagram showing an embodiment of the hydraulic drive device of the present invention.

FIG. 5 is a hydraulic circuit diagram illustrating an embodiment of the hydraulic drive device of the present invention.

FIG. 6 is a diagram showing a relationship between an excess flow introduced from a hydraulic pump to a pump control valve and a control pressure generated by a pump control valve in one embodiment of the hydraulic drive device of the present invention. It is.

FIG. 7 is a diagram showing a relationship between a control pressure and a hydraulic pump discharge flow rate in one embodiment of the hydraulic drive device of the present invention.

FIG. 8 is a diagram showing a relationship between an operation amount of a left / right traveling operation lever and a supply flow rate to a left / right traveling hydraulic motor in one embodiment of the hydraulic drive device of the present invention.

FIG. 9 is a side view showing the overall structure of a self-propelled recycled product production machine provided with one embodiment of the hydraulic drive device of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Hopper (accepting means) 2 Crushing apparatus (processing apparatus) 14 Endless track crawler (running means) 16, 17 Hydraulic motor for traveling 19 First hydraulic pump 20 Second hydraulic pump 21 Engine (motor) 27, 28 Control valve for traveling (Running control valve means) 32, 33 running operating lever device (running operating means) 38, 82 pump control valve (pressure conversion means, control pressure generating means, pump adjusting means, control means) 34, 35 regulator device ( Regulator means, pump adjustment means, control means) 36g traveling mode selection switch (selection means,
Input means) 110 Solenoid control valve (Control pressure switching means, characteristic control means, control means) 202 Sediment hopper (Receiving means) 203 Mixing device (Processing device) 210 Endless track crawler (Running means) 213 Hydraulic motor for running QP1, QP2 Pump discharge flow rate

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Tadashi Shiohata 650, Kandamachi, Tsuchiura City, Ibaraki Prefecture Inside the Tsuchiura Plant of Hitachi Construction Machinery Co., Ltd. (72) Masamichi Tanaka 650, Kandamachi, Tsuchiura City, Ibaraki Prefecture Inside the Tsuchiura Plant, Ltd. GA03 GB05

Claims (9)

[Claims] 1. A self-propelled recycle product production machine, which is self-propelled by a traveling means and is supplied to a processing device by introducing a recycled material received by a receiving means to perform a predetermined process to produce a recycled product, and is driven by a prime mover. A self-propelled recycle product production machine having at least one variable displacement type hydraulic pump and a traveling hydraulic motor that drives the traveling means with pressure oil discharged from the hydraulic pump. Input means for inputting an instruction relating to the operating speed of the traveling means, and control for controlling a discharge flow rate of the hydraulic pump with a control characteristic according to the instruction at the input means for a required flow rate of the traveling hydraulic motor. Means for a self-propelled recycle product production machine. 2. The hydraulic drive system for a self-propelled recycle product production machine according to claim 1, wherein said control means controls the hydraulic pump when a relatively high-speed instruction is input by said input means. When the maximum discharge flow rate is set to a relatively high value and a relatively low speed instruction is input by the input means,
A hydraulic drive device for a self-propelled recycle product production machine, wherein a maximum discharge flow rate of the hydraulic pump is set to a relatively low value. 3. A travel control valve means for controlling a flow of pressurized oil supplied from said hydraulic pump to said travel hydraulic motor, in the hydraulic drive system for a self-propelled recycle product production machine according to claim 1. And a traveling operation means for operating the traveling control valve means. A hydraulic drive device for a self-propelled recycle product production machine, further comprising: traveling operation means for operating the traveling control valve means. 4. A hydraulic drive system for a self-propelled recycle product producing machine according to claim 1, wherein said control means has a predetermined adjusting characteristic with respect to a required flow rate of said traveling hydraulic motor. A self-propelled vehicle comprising: a pump adjusting unit that adjusts a discharge flow rate of the hydraulic pump; and a characteristic control unit that changes the adjustment characteristic in the pump adjusting unit in accordance with the instruction from the input unit. Hydraulic drive unit for recycling-type product production machines. 5. A hydraulic drive device for a self-propelled recycle product producing machine according to claim 4, wherein said pump adjusting means includes control pressure generating means for generating a control pressure corresponding to a required flow rate of said traveling hydraulic motor. Regulator means for controlling the discharge flow rate of the hydraulic pump in accordance with the control pressure from the control pressure generating means, wherein the characteristic control means controls the control pressure in response to the instruction from the input means. The hydraulic drive of a self-propelled recycle product production machine characterized by changing 6. A hydraulic drive system for a self-propelled recycle product producing machine according to claim 5, wherein said traveling control valve means is a center bypass type valve, and said control pressure generating means is said center bypass type valve. A hydraulic drive device for a self-propelled recycle product production machine, comprising pressure conversion means for converting a flow rate of pressure oil flowing downstream of a center bypass line of the travel control valve means into pressure. 7. A self-propelled recycle product production machine, which is self-propelled by a traveling means and is introduced into a processing device by introducing a recycle raw material received by a receiving means to perform a predetermined process to produce a recycle product, and is driven by a prime mover. A self-propelled recycle product production machine having at least one variable displacement type hydraulic pump and a traveling hydraulic motor that drives the traveling means with pressure oil discharged from the hydraulic pump. A center bypass type control valve means for controlling the flow of hydraulic oil supplied from the hydraulic pump to the travel hydraulic motor; a travel operation means for operating the travel control valve means; Selecting means for selecting and inputting one of a first mode and a second mode; and a flow downstream of a center bypass line of the traveling control valve means. Pressure conversion means for converting the flow rate of pressure oil into pressure to generate a control pressure corresponding to the operation amount of the travel operation means, and controlling the hydraulic pump in response to an increase in the control pressure from the pressure conversion means. A regulator means for controlling so as to increase the discharge flow rate, and when the first mode is selected by the selection means,
When the maximum value of the control pressure is relatively large and the maximum discharge flow rate of the hydraulic pump is a relatively high value, and the second mode is selected by the selection means, the maximum value of the control pressure is Control pressure switching means for making the maximum discharge flow rate of the hydraulic pump relatively small so as to be relatively low, wherein the hydraulic drive device of the self-propelled recycle product production machine is provided. 8. The self-propelled recycle product production machine according to claim 1, wherein said self-propelled recycle product production machine crushes the material to be crushed as said recycled material. A hydraulic drive device for a self-propelled recycle product production machine, wherein the self-propelled crusher is provided with a crusher for producing a crushed material as the recycled product as the processing device. 9. The self-propelled recycle product producing machine according to claim 1, wherein said self-propelled recycle product production machine uses a soil improving material as a material for recycle. A hydraulic device for a self-propelled recycle product production machine, which is a self-propelled soil quality improvement machine provided as the treatment device with a mixing device for producing improved soil as the recycled product by crushing and mixing.