JP2002331253A - Hydraulic driving apparatus of self-propelled crusher and self-propelled crusher - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic driving apparatus of a self-propelled crusher which retains a prescribed crushing capability of a crushing apparatus while miniaturizing a running means and to provide a self-propelled crusher. SOLUTION: The hydraulic driving apparatus of a self-propelled crusher provided with right and left hydraulic motors 6R, 6L for driving by hydraulic power from hydraulic pumps 44A, 44B driven by an engine 43 and a hydraulic motor 15 for the self-propelled crusher comprises right and left control valves for driving and a control valve for the crusher for introducing the hydraulic power from the hydraulic pumps 44A, 44B into the right and left hydraulic motors 6R, 6L for driving and the hydraulic motor 15 for the self-propelled crusher, operation lever apparatuses 41R, 41L and an operation board 42 for switching and operating them, respectively, and a relief valve 57 for setting the relief pressure of the hydraulic pumps 44A, 44B. The relief pressure is increased by adding pilot pressure to the control valve for the crusher to a driving unit 85 through the pipe 86 at the time of crushing work.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic drive unit and a self-propelled crusher of a self-propelled crusher provided with a crushing device for crushing an object to be crushed as a recycled material.

[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), for example, concrete lumps carried out at the time of building dismantling and emission during road repairs. Large and small rocks and construction waste generated at construction sites such as asphalt blocks
Alternatively, the use of self-propelled crushers, which use industrial waste (= crushed material) as a recycled material and crush the crushed material to produce crushed material as a recycled product, is expanding.

In this self-propelled crusher, a crushed object input by, for example, a hydraulic shovel or the like is received by a hopper as a receiving means provided at an upper portion, and the crushed object received by the hopper is subjected to a predetermined process by a crushing device. The crushed product is crushed to a size to produce a crushed product as a recycled product, and the generated crushed product is dropped on a conveyor provided below the crushing device and transported. Then, the crushed material being transported is removed by, for example, adsorbing reinforcing bar pieces mixed in the concrete mass by a magnetic separator arranged above the conveyor, and finally carried out of the self-propelled crusher. It has become.

This self-propelled crusher includes a self-propelled traveling means (for example, an endless track), in addition to the above-described crushing apparatus for performing crushing work, and auxiliary machines for performing operations related to crushing work such as a conveyor and a magnetic separator. Crawler belt), and the crushing device, the auxiliary machine, and the traveling means are driven and driven by a hydraulic drive device having a corresponding hydraulic actuator.

As such a hydraulic drive device, as described in, for example, Japanese Utility Model Application Laid-Open No. 6-81641, a left and right traveling hydraulic pump and pressure oil from these left and right traveling hydraulic pumps are used. A left / right traveling means (traveling section), a left / right traveling control valve (hydraulic control valve) for controlling the flow of pressure oil to the left / right traveling means, a crusher hydraulic motor (crusher), There is one having a crusher control valve means (a crusher hydraulic control valve) for controlling the flow of pressure oil to the crusher hydraulic motor.

In this prior art, during the crushing operation, the hydraulic oil from the left and right traveling hydraulic pumps passing through the neutral port of the left and right traveling control valves is combined and supplied to the hydraulic motor for the crushing device. The number of hydraulic pumps is reduced by also using hydraulic pumps for supplying hydraulic oil to the left and right running means and the crushing device.

[0007]

However, the above prior art has the following problems. That is, the traveling means is usually used for changing the crushing work position in the site of the operation site or adjusting the position of the self-propelled crusher itself,
I don't often travel long distances. Even if it travels a long distance, it is often transported by, for example, a trailer. In this case, too, the traveling means is driven only when the trailer gets on and off the platform. In addition, the frequency of driving such a traveling means is generally lower than the frequency of driving other devices such as the crusher and the auxiliary machine.

[0008] Therefore, in order to prevent the self-propelled crusher from being enlarged, the traveling means must be of a rating sufficient to ensure a predetermined traveling force, climbing power, stability and the like.
It is desirable to attach a device as small as possible within a range satisfying this condition. When such a relatively small traveling means is provided, it is desirable to use a relatively small capacity hydraulic motor for driving the traveling means.

On the other hand, it is desirable that the crushing device can be driven at a high output in order to ensure a reliable crushing capacity of crushed materials to be supplied as recycled materials which have been diversified in recent years. That is, the maximum pressure of the pressure oil supplied to the crusher hydraulic motor that drives the crusher needs to be set to a value sufficient to ensure the reliability of the crusher in the crushing processing capacity.

[0010] As described above, the above-mentioned prior art has a structure in which a hydraulic motor for the crushing device and a hydraulic pump for supplying pressure oil to the left and right running means are also used. If means is provided, that is, if a hydraulic pump having a sufficient capacity to secure the required crushing capacity of the crushing device using a relatively small capacity hydraulic motor for traveling is provided, for example, traveling by excessive supply of pressure oil Troubles such as breakage of the hydraulic motor may occur. In order to prevent such a problem, for example, when the maximum pressure of the hydraulic oil from the hydraulic pump is set low by a relief valve or the like, the pressure of the hydraulic oil supplied to the hydraulic motor for the crusher is sufficiently obtained. Therefore, it is difficult to ensure the reliability of the crushing capacity of the crusher.

The present invention has been made on the basis of the above-mentioned objects, and has as its object to reduce the size of the traveling means and to secure the required crushing capacity of the crushing device. And a self-propelled crusher.

[0012]

(1) In order to achieve the above object, the present invention provides a self-propelled type having self-propelled left and right running means and a crushing device for crushing an object to be crushed. A hydraulic pump provided in the crusher and driven by a prime mover, and a left / right traveling hydraulic motor and a crushing device for driving the left / right traveling means and the crushing device by hydraulic oil discharged from the hydraulic pump, respectively. A hydraulic drive device for a self-propelled crusher having a hydraulic motor and a left / right travel control valve for guiding hydraulic oil from the hydraulic pump to the left / right travel hydraulic motor and the crusher hydraulic motor, respectively; Control valve means for the crushing device, operating means for switching between the left / right traveling control valve and the control valve means for the crushing device, and a relief pressure for limiting the maximum value of the discharge pressure of the hydraulic pump. Comprising a relief valve for setting, according to the operation state of the operation means, and a relief pressure changing means for changing the relief pressure of the relief valve.

[0013] In the present invention, the provision of the relief pressure changing means for changing the value of the relief pressure for limiting the maximum value of the discharge pressure of the hydraulic pump in accordance with the operation of the operating means, thereby reducing the size of the traveling means. The required crushing capacity of the crushing device can be ensured while achieving the crushing.

For example, a first and a second hydraulic pump for supplying pressure oil to the left and right traveling hydraulic motors are provided as pressure oil supply sources. For the discharge pipelines of the first and second hydraulic pumps,
It is assumed that hydraulic drive devices connected via the left and right traveling control valves are configured. In such a hydraulic drive device, first, when the control valve for left / right traveling is switched by the operating means, the first
And the hydraulic oil from the second hydraulic pump is switched and supplied to the left and right traveling hydraulic motors, respectively, to drive the traveling means.
On the other hand, when the left / right traveling control valve is switched to the neutral position by the operating means, the hydraulic oil from the first and second hydraulic pumps passes through, for example, the neutral port of the left / right traveling control valve and merges. Then, it is supplied to the control valve means for the crushing device. At this time, by switching the control valve means for the crushing device, the first and second confluent first and second crushing devices are combined.
The pressure oil from the hydraulic pump is switched and supplied to the hydraulic motor for the crushing device to drive the crushing device.

In such a hydraulic drive device, for example, the control valve means for the crushing device includes at least one pilot control type control valve for the crushing device driven by a pilot pressure from the operating means,
The above-mentioned relief pressure changing means performs the above-mentioned first and second operations in accordance with the pilot pressure applied to the crushing device control valve.
The relief pressure that limits the maximum value of the discharge pressure of the hydraulic pump is changed. Specifically, for example, the pilot pressure from the operating means is reduced to the relief pressure set by the relief valve only when the control means for the crushing apparatus is switched by the operating means so that the hydraulic motor for the crushing apparatus is driven forward. It is configured to be energized.

Thus, for example, when the control valve means for the crushing device is operated by the operating means, the maximum value of the pressure oil from the combined first and second hydraulic pumps is compared with the maximum value set by the relief valve alone. Since the pressure can be set to a relatively high value higher than the relatively low relief pressure, a sufficient crushing capacity of the crusher can be secured. On the other hand, in other cases, for example, when the left and right traveling control valves are operated, the pilot pressure is not urged to the relief pressure changing means. It will be a low value.

Thus, even when a hydraulic pump having a sufficient capacity to secure the required crushing capacity of the crushing device is provided, the left and right traveling means and the left and right traveling hydraulic motors for driving these are relatively used. Small ones can be used. Therefore, the required crushing capacity of the crusher can be ensured while reducing the size of the traveling means.

(2) In order to achieve the above object, the present invention is also provided for a self-propelled crusher having left and right running means for self-propelling and a crushing device for crushing an object to be crushed. First and second hydraulic pumps driven by a prime mover, and left and right traveling hydraulic pressures for driving the left and right traveling means and the crushing device by pressure oil discharged from the first and second hydraulic pumps, respectively. A hydraulic drive device for a self-propelled crusher, comprising a motor and a hydraulic motor for the crusher;
A left travel control valve that is connected to a discharge pipe of a hydraulic pump and supplies pressure oil from a first hydraulic pump to the left travel hydraulic motor during traveling operation of the self-propelled crusher;
A right travel control valve that is connected to a discharge pipe of the second hydraulic pump and supplies pressure oil from the second hydraulic pump to the right travel hydraulic motor during travel of the self-propelled crusher; A crushing device connected to the discharge pipes of the first and second hydraulic pumps and joining the pressurized oil from the first and second hydraulic pumps during the crushing operation of the self-propelled crusher and supplying it to the hydraulic motor for the crushing device Control valve means, operating means for switching between the left / right traveling control valve and the crushing device control valve means, and a relief pressure for limiting the maximum value of the discharge pressure of the first and second hydraulic pumps. And a relief pressure changing means for changing the relief pressure of the relief valve according to the operation state of the operating means.

(3) In the above (1) or (2), preferably, the relief pressure changing means sets the relief pressure to a relatively high value when the control valve means for the crushing device is operated, When the left / right traveling control valve is operated, the relief pressure is set to a relatively low value.

(4) Any one of the above (1) to (3)
In one, preferably, the crushing device control valve means includes at least one pilot operation type crushing device control valve driven by pilot pressure from the operating means, and the relief pressure changing means, The relief pressure is changed according to a pilot pressure supplied to the control valve for the crushing device.

(5) In order to achieve the above object, the present invention provides a self-propelled left / right traveling means, a crushing device for crushing an object to be crushed, a hydraulic pump driven by a motor,
In a self-propelled crusher including a left / right traveling hydraulic motor and a crushing device hydraulic motor that respectively drive the left / right traveling means and the crushing device with pressure oil discharged from the hydraulic pump, Left and right traveling control valve and crushing device control valve means for guiding hydraulic oil from a pump to the left and right traveling hydraulic motor and crushing device hydraulic motor, respectively, and the left and right traveling control valve and crushing device Operating means for switching the control valve means for;
A relief valve for setting a relief pressure for limiting a maximum value of the discharge pressure of the hydraulic pump;

[0022]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the self-propelled crusher of the present invention will be described below with reference to the drawings. FIG. 1 is a side view showing the entire structure of the self-propelled crusher of the present embodiment, FIG. 2 is a top view thereof, and FIG. 3 is a front view of the self-propelled crusher viewed from the left side in FIG. 1 to 3, reference numeral 1 denotes a traveling body. The traveling body 1 includes a traveling body frame 2, track frames 3 provided on both sides of the traveling body frame 2, and one side of the track frame 3 ( (Left side in Fig. 1)
, A driving wheel 5 provided on the other side (right side in FIG. 1) of the track frame 3, and a left and right traveling hydraulic pressure directly connected to a rotating shaft (not shown) of the driving wheel 5. Motor 6
L, 6R (FIG. 1 shows only the left traveling hydraulic motor 6L,
The idler wheel 4 and the drive wheel 5 will be described later.
And crawler tracks (crawler tracks) 7.

Reference numeral 8 denotes a main body frame provided above the traveling body frame 2, and 9 denotes another side of the main body frame 8 (FIG. 1).
A power unit (details will be described later) provided on the middle right side via the support member 10.

Reference numeral 11 denotes an upper-diameter hopper that receives crushed materials (eg, construction waste materials, home appliances, plastic waste materials, old tires, etc.) as recycle raw materials supplied by a loading heavy machine such as a hydraulic excavator. A shear-type crusher (biaxial) provided on the front end (left side in FIG. 1) of the main body frame 8 for crushing the crushed material received by the hopper 11 into a predetermined size and discharging the crushed material downward. In the shredder, the hopper 11 is detachably attached to an upper portion of the housing 13 of the shearing crusher 12 by, for example, bolts or the like.

A driving device 14 is provided on the main frame 8 at a position rearward of the shearing type crushing device 12 (right side in FIG. 1) and has a hydraulic motor 15 for driving the shearing type crushing device 12 therein. As shown in FIG. 1, the end of the shearing type crushing device 12 on the side opposite to the driving device 14 (that is, the left side in FIG. 1) is the front end in the longitudinal direction of the main body frame 8 (the left side in FIG. 1). It is located at approximately the same position as above and faces outward on the front side of the self-propelled crusher.

FIG. 4 is a partially exploded top view showing the detailed structure of the above-mentioned shearing crusher 12, and FIG. 5 is a sectional view taken along the line VV in FIG. In these FIGS. 4 and 5,
Reference numerals 16 denote substantially regular polygonal cross sections (substantially square shapes in this example) disposed on the housing 13 in a substantially horizontal direction.
The rotary shaft 17 is an integral rotary tooth having a plurality of (five in this example) hook portions 19 in the circumferential direction of the substantially disk-shaped disk portion 18, and 20 is slightly thicker than the rotary tooth 17 in diameter. A small disk-shaped spacer,
The rotating members 21 and 21 are constituted by alternately inserting and fixing the rotating teeth 17 and the spacers 20 respectively to the rotating members 6 and 6.
As shown in FIGS. 4 and 5, the rotating bodies 21 and 21 are disposed such that the rotating shafts 16 and 16 are substantially along the longitudinal direction of the main body frame 8 (that is, the longitudinal direction of the self-propelled crusher). And the rotating teeth 17, 1 of each other
7 are partially overlapped in the radial direction, and are arranged so as to mesh with each other.

Reference numerals 22 and 23 denote driven gears and drive gears fixed to the ends of the upper and lower rotating shafts 16 and 16 of the rotating bodies 21 and 21 on the drive device 14 side (right side in FIG. 4), respectively. Reference numeral 24 denotes an input shaft connected to the driving device 14 side (right side in FIG. 4) of the driving gear 23.
Is connected to the output shaft 25 (see FIG. 1) of the hydraulic motor 15 of the driving device 14 so that the driving force is input.

As a result, the driving force (torque) input from the hydraulic motor 15 to the input shaft 24 is transmitted to the rotating body 21 shown in the lower part of FIG. Also transmitted to the body 21 via the drive gear 23 and the driven gear 22 described above, these rotating bodies 21 and 21 are rotated forward in the direction of the arrow in FIG.
They rotate in opposite directions. As a result, the objects to be crushed introduced from the hopper 11 (see FIG.
9 and the spacers 20), are sheared into strips, and are crushed to a predetermined size. At this time, the gear ratio of the driving gear 23 and the driven gear 22 is set so that the rotation speeds of the two rotating bodies 21 and 21 are different, and the crushed material introduced from the hopper 11 is transferred to the hook portions 19 of the rotating teeth 17. It is more preferable to carry out push-shear crushing. Reference numeral 26 denotes a bearing that rotatably supports the rotating shafts 16, 16 of the rotating bodies 21, 21 with respect to the housing 13.

As shown in FIGS. 4 and 5, the housing 13 has a substantially box shape, of which the side wall on the side opposite to the drive unit 14 (ie, the front side of the self-propelled crusher). The end bracket 27 as shown in FIG. 4 has a structure that can be freely attached and detached with bolts or the like (or an open / close structure using a hinge or the like) (FIG. 4 shows a state where the end bracket 27 is detached, see a broken arrow). When removed (or opened), the ends of the rotating shafts 16, 16 in the housing 13 on the side opposite to the drive device 14 are exposed outside the shearing crusher 12, and face the front of the self-propelled crusher. Has become.

Numerals 28, 28 are provided inside a cleaning fin support member 29 as side walls on both sides in the width direction of the housing 13, and have substantially the same number as the spacers 20 so as to face the spacers 20 of the rotating bodies 21, 21. As shown in FIG. 5, the base portion 30 of the cleaning fin is inserted into the slot 29 a of the cleaning fin support member 29. The cleaning fin support member 29 is detachably attached to one side (lower side in FIG. 4 and right side in FIG. 5) 31 of the housing 13 via, for example, a bolt (see a dashed line in FIG. 5). By removing this, the cleaning fin support member 29 and the cleaning fin 28 can be collectively pulled out from the housing side portion 31 to the outside.

Referring back to FIGS. 1 to 3, reference numeral 32 is provided below the shearing type crushing device 12, and a crushed material as a recycled product generated by crushing the input crushed material by the shearing type crushing device 12 is shown. A chute 33, which is guided downward, is a conveyor that conveys and discharges the crushed material derived from the chute 32. The conveyor 33 is suspended and supported from the power unit 9 and the main body frame 8 by a connecting portion 34, the upstream side in the transport direction (the left side in FIG. 1) is located below the chute 32, and the downstream side in the transport direction (in FIG. 1). The right side) is inclined upward from the lower part of the power unit 9 toward the right side in FIG. Reference numeral 35 denotes a drive motor of the conveyor 33 (see FIG. 2).

A magnetic separator 36 is provided above the conveyor 33 and adsorbs and removes, for example, foreign matter such as rebar pieces contained in the crushed material conveyed by the conveyor 33. It is supported by the power unit 9 via an arm 37 so as to be substantially orthogonal. 3
Numeral 8 denotes a magnetic separator belt of the magnetic separator 36, which is driven around a magnetic force generating means (not shown) by a hydraulic motor 39 for the magnetic separator so that the magnetic force from the magnetic force generating means acts on the magnetic separator belt 38. After the magnetic substance is attracted to the magnetic separator belt 38, the magnetic substance is conveyed and removed in a direction substantially perpendicular to the conveyor 33.

Reference numeral 40 denotes a front side of the power unit 9 (left side in FIG. 1).
The left and right traveling hydraulic motors 6L,
Left / right running operation lever device 41 for driving and controlling 6R
L, 41R, and start up the crusher hydraulic motor 15, the conveyor hydraulic motor 35, and the magnetic separator hydraulic motor 39.
An operation panel 42 (see FIG. 6 to be described later) having switches to be stopped (to be described later) is provided.

Here, the shearing type crushing device 12, the conveyor 33, the magnetic separator 36, and the traveling body 1 constitute driven members driven by a hydraulic driving device built in the power unit 9. Hereinafter, the detailed configuration of the hydraulic drive device will be described step by step.

FIG. 6 is a hydraulic circuit diagram showing an overall schematic configuration of a hydraulic drive device provided in an embodiment of the self-propelled crusher of the present invention. In FIG. 6, reference numeral 43 denotes an engine,
Reference numerals 44A, 44B and 44C denote first and second variable displacement type hydraulic pumps driven by the engine 43 and a third fixed displacement type hydraulic pump. At this time, the hydraulic oil from the first and second hydraulic pumps 44A and 44B is supplied to the left and right traveling hydraulic motors 6L and 6R, respectively. The hydraulic oil from the second hydraulic pump is combined and supplied, and the hydraulic oil from the third hydraulic pump 44C is supplied to the hydraulic motor 35 for the conveyor and the hydraulic motor 39 for the magnetic separator. ing. 45 is engine 4
3 is a fixed displacement pilot pump driven by the pump 3.

The flow (direction and flow rate) of the hydraulic oil supplied from the first and second hydraulic pumps 44A and 44B to the left and right traveling hydraulic motors 6L and 6R and the crushing device hydraulic motor 15 from the first and second hydraulic pumps 44A and 44B, respectively. , Or only the flow rate), the left travel control valve 47L and the first crusher control valve 48, the right travel control valve 47R, and the second crusher control valve 49.
First and second control valve devices each having a built-in (for details,
7 and 9 described later) and 46C indicate the flow (direction and flow rate, or only flow rate) of the pressure oil supplied from the third hydraulic pump 44C to the conveyor hydraulic motor 35 and the magnetic separator hydraulic motor 39, respectively. Conveyor control valve 50 to be controlled, magnetic separator control valve 51
And a third control valve device incorporating a flow dividing valve 52 (details will be described later) (see FIG. 11 described later for details).

The reference numerals 53L and 53R are provided in the driver's seat 40 (see FIG. 1), and are provided in the left control valve 47L (see FIG. 7) and the second control valve 46B in the first control valve 46A. Right running control valve 4
7R (see FIG. 9 described later), the left / right running control levers of the left / right running control lever devices 41L and 41R for switching operation, respectively, and 54 is the discharge of the first and second hydraulic pumps 44A and 44B. It is a regulator device as a pump control means for adjusting a flow rate.

55Aa, 55Ba, 55Ca and 56a
Are respectively the first, second, and third hydraulic pumps 44A,
44B, 44C and discharge line 5 of pilot pump 45
5A, 55B, 55C, and 56. The branch pipes branch from the branch pipes 55Aa, 55Ca, and 56a.
The first and second hydraulic pumps 44A, 44A
4B, relief valves 57, 58, 59 for limiting the maximum values of the discharge pressures P1, P2 of the third hydraulic pump 44C and the discharge pressure Pp of the pilot pump 45 are provided. Value is relief valve 57,5
8, 57 provided with springs 57a, 58a, respectively.
The setting is made with the urging force of 59a.

FIG. 7 is a hydraulic circuit diagram showing a detailed configuration of the first control valve device 46A. In FIG. 7, the left traveling control valve 47L and the first crusher control valve 48 both control the direction and flow rate of hydraulic oil to the corresponding left traveling hydraulic motor 6L and crusher hydraulic motor 15. Possible hydraulic pilot method 3
It is a position switching valve. These control valves 4
7L and 48 are discharge pipes 55A of the first hydraulic pump 44A.
In the first valve group 60A having the center bypass line 60Aa connected to the control valve 47A, the control valve 47L for the left running and the control valve 48 for the first crusher are arranged in this order from the upstream side. And this first
The valve group 60A includes two control valves 4
It is configured as one valve block including 7L and 48. 61L is the center bypass line 60Aa
Is a pump control valve (details will be described later) provided at the most downstream side of.

The left traveling control valve 47L is generated by the pilot pump 45 and is provided with the aforementioned operating lever 53L.
Is operated by a pilot pressure reduced to a predetermined pressure by an operation lever device 41L provided with. That is, the operating lever device 41L includes the operating lever 53L and a pair of pressure reducing valves 62La and 62 that output a pilot pressure corresponding to the operation amount.
2Lb. When the operating lever 53L of the operating lever device 41L is operated in the direction a in FIG. 7 (or in the opposite direction, the same applies hereinafter), the pilot pressure is controlled through the pilot line 63a (or the pilot line 63b) to the left traveling control. The driving unit 47La (or the driving unit 47Lb) of the valve 47L guides the left traveling control valve 47L to the upper switching position 47LA in FIG.
(Or the lower switching position 47LB). Then, the pressure oil from the first hydraulic pump 44 </ b> A
A, is supplied to the left traveling hydraulic motor 6L through the center bypass line 60Aa and the switching position 47LA (or the lower switching position 47LB) of the left traveling control valve 47L, and the left traveling hydraulic motor 6L is rotated in the forward direction ( Or in the reverse direction).

When the operating lever 53L is set at the neutral position shown in FIG. 7, the left traveling control valve 47L returns to the neutral position shown in FIG. Stop.

FIG. 8 is a hydraulic circuit diagram showing a detailed configuration of the operation valve device 64 provided in the hydraulic drive device. In FIG. 8, as described above, reference numeral 56 denotes a discharge line of the pilot pump 45. The discharge line 56 is connected to the traveling lock solenoid control valve 65, the crusher forward rotation solenoid control valve 66 F, and the crusher reverse rotation. Solenoid control valve 66R for traveling, solenoid control valve 67 for traveling speed switching (described later)
Are connected in parallel with each other.

The traveling lock solenoid control valve 65
Are provided in pilot introduction lines 68a, 68b for guiding the pilot pressure from the pilot pump 45 to the operation lever device 41L, and are provided with a drive signal St from the controller 70 (see FIG. 3). Can be switched with.

When the drive signal St input to the solenoid 65a is turned on, the traveling lock solenoid control valve 65 is switched to the communication position 65A on the right side in FIG. 8, and the pilot pressure from the pilot pump 45 is supplied to the introduction conduit 68a,
The control lever 47L is guided to the control lever device 41L via the control lever 68b to enable the above operation of the control valve 47L for left traveling by the control lever 53L. On the other hand, when the drive signal St is turned off, the traveling lock solenoid control valve 65 returns to the shut-off position 65B on the left side in FIG. The operation of the left traveling control valve 47L by the operation lever device 41L is locked by connecting the introduction pipe 68b to the tank line 69a to the tank 69 and setting the pressure in the introduction pipe 68b to the tank pressure. Has become.

Returning to FIG. 7, the first crushing device control valve 48 is generated by the pilot pump 45 and includes the crushing device normal rotation solenoid control valve 66F and the crushing device reverse rotation solenoid control valve 66R in the operation valve device 64.
Is operated by the pilot pressure reduced to a predetermined pressure. That is, the solenoid control valve 66F for crushing device normal rotation and the solenoid control valve 66R for crushing device reverse rotation shown in FIG.
Is a drive signal Scr from the controller 70 (see FIG. 6).
Solenoids 66Fa, 6 driven by 1 and Scr2, respectively
6Ra is provided, and the control valve 48 for the first crusher is switched according to the input of the drive signals Scr1 and Scr2.

That is, when the drive signal Scr1 is ON and the drive signal Scr2 is OFF, the crusher forward rotation solenoid control valve 66F is switched to the communication position 66FA on the right side in FIG.
R is the restoring force of the spring 66Rb, and is the blocking position 66 on the left side in FIG.
Return to RB. As a result, the pilot pressure from the pilot pump 45 flows through the introduction pipes 71a and 71b to the first
It is led to the driving portion 48a of the crushing device control valve 48, and the introduction lines 72a and 72b are connected to the tank line 69.
a to the tank pressure, whereby the first crusher control valve 48 is switched to the upper switching position 48A in FIG. Thereby, the pressure oil from the first hydraulic pump 44A is supplied to the crusher hydraulic motor 15 via the discharge pipe 55A, the center bypass line 60Aa, and the switching position 48A of the first crusher control valve 48, and crushed. The device hydraulic motor 15 is driven in the normal rotation direction.

Similarly, when the drive signal Scr1 is turned off and the drive signal Scr2 is turned on, the crushing device forward rotation solenoid control valve 66F returns to the shut-off position 66FB on the left side in FIG. The reverse solenoid control valve 66R is switched to the communication position 66RA on the right side in FIG. As a result, the pilot pressure is guided to the driving portion 48b of the control valve 48 for the first crushing device via the introduction lines 72a and 72b, and the introduction line 71
The tank pressures a and 71b become the tank pressure, and the control valve 48 for the first crushing device is switched to the lower switching position 48B in FIG. Thus, the pressure oil from the first hydraulic pump 44A is supplied to the crusher hydraulic motor 15 via the switching position 48B, and the crusher hydraulic motor 15 is driven in the reverse direction.

The drive signals Scr1 and Scr2 are both OFF.
, The crusher forward rotation solenoid control valve 66F and the crusher reverse rotation solenoid control valve 66R are both spring 6
With the restoring force of 6Fb and 66Rb, the blocking position 66 on the left side in FIG.
FB and 66RB, the first crushing device control valve 48 returns to the neutral position 48C shown in FIG. 7 by the restoring force of the springs 48c and 48d, and the pressure oil to the crushing device hydraulic motor 15 is cut off and crushed. The device hydraulic motor 15 stops. The details of the traveling speed switching solenoid control valve 67 will be described later.

The above pump control valve 61L
Has a function of converting a flow rate into a pressure, and the center bypass line 60Aa and the tank line 6
9b via a throttle portion 61Laa, a piston 61La for urging both ends of the piston 61La, and a pilot introduction line 73a to the discharge line 56 of the pilot pump 45.
(See FIG. 8), the traveling speed switching solenoid control valve 6
7, and the pilot pressure is guided through the upstream side through a pilot introduction pipe 73b (see FIG. 8), the downstream side is connected to the tank line 69c, and the spring 61L
and a variable relief valve 61Ld in which the relief pressure is variably set by b.

With such a configuration, the pump control valve 61L functions as follows. That is, as described above, the left traveling control valve 47L and the first crushing device control valve 48 are center bypass type valves, and the center bypass line 60A
The flow rate flowing through each control valve 47L, 48
(I.e., the switching stroke of the spool). When the control valves 47L, 48 are neutral, that is, the required flow rate of the control valves 47L, 48 (in other words, the required flow rate of the left traveling hydraulic motor 6L and the crushing apparatus hydraulic motor 15) required for the first hydraulic pump 44A is small. In this case, most of the pressure oil discharged from the first hydraulic pump 44A is introduced into the pump control valve 61L through the center bypass line 60Aa as a surplus flow rate, and a relatively large flow rate of the pressure oil flows into the throttle portion of the piston 61La. It is led to the tank line 69b via 61Laa. Thereby, the piston 61
Since La moves to the right side in FIG. 7, the set relief pressure of the relief valve 61Ld by the spring 61Lb is reduced, and the pipe is branched from the pipe line 73b to reach a first servo valve 74 for negative tilt control described later. A relatively low control pressure (negative control pressure) Pc1 is generated in the passage 75a.

Conversely, each control valve 47L, 48
Is operated to be in the open state, that is, when the required flow rate required for the first hydraulic pump 44A is large, the surplus flow rate flowing through the center bypass line 60Aa becomes the left traveling hydraulic motor 6L and the crushing apparatus hydraulic pressure. Since the pressure oil is reduced by the flow rate flowing to the motor 15 side, the flow rate of the pressure oil led out to the tank line 69b through the piston throttle portion 61Laa becomes relatively small, and the piston 61La moves to the left in FIG. 7 to set the relief valve 61Ld. Since the relief pressure increases, the control pressure Pc1 of the conduit 75a increases.

In the present embodiment, as will be described later, the tilt angle of the oblique shaft 44Aa of the first hydraulic pump 44A is controlled based on the fluctuation of the control pressure (negative control pressure) Pc1 (details). Will be described later).

FIG. 9 is a hydraulic circuit diagram showing a detailed configuration of the second control valve device 46B. In FIG. 9, the second
The control valve device 46B has substantially the same structure as the first control valve device 46A, 47R is a control valve for right running, 49 is a control valve for a second crushing device, and is discharged from the second hydraulic pump 44B. Hydraulic motor 6R for right running and hydraulic motor 1 for crusher
5. These control valves 47R and 49 are a control valve 47R for right running from the upstream side in the second valve group 60B having the center bypass line 60Ba connected to the discharge pipe 55B of the second hydraulic pump 44B, and a control valve for the second crusher. The control valves 49 are arranged in this order.

The second valve group 60B is configured as one valve block, similarly to the first valve group 60A of the first control valve device 46A. In addition, at this time, the right traveling control valve 47R is a valve having the same flow control characteristic (for example, a valve having the same structure) as the left traveling control valve 47L of the first valve group 60A, and further for the second crushing device. The control valve 49 is
The control valve 48 for the first crushing device of the first valve group 60A is a valve having the same flow control characteristic (for example, a valve having the same structure). As a result, the valve blocks forming the second valve group 60B and the valve blocks forming the first valve group 60A have the same structure. A pump control valve 61R having the same structure and function as the pump control valve 61L is provided at the most downstream side of the center bypass line 60Ba.

The right running control valve 47R is operated by the pilot pressure of the operating lever device 41R in the same manner as the left running control valve 47L.
When the 3R is operated in the direction b in FIG.
The drive valve 47R (or the drive unit 47Rb) of the right travel control valve 47R is guided via the 6a (or the pilot line 76b), whereby the right travel control valve 47R is switched to the upper switching position 47RA (or the upper position in FIG. 9). The switch is switched to the lower switching position 47RB), and the hydraulic oil from the second hydraulic pump 44B is supplied to the right traveling hydraulic motor 6R via the switching position 47RA (or the switching position 47RB) to rotate in the forward direction (or the reverse direction). ) Is driven. When the operating lever 53R is set to the neutral position shown in FIG. 9, the right traveling control valve 47R returns to the neutral position shown in FIG. 9 by the urging force of the springs 47Rc and 47Rd, and the right traveling hydraulic motor 6R stops.

The pilot pressure to the operation lever device 41R is supplied from the pilot pump 45 via the traveling lock solenoid control valve 65, similarly to the operation lever device 41L. Therefore, similarly to the operation lever device 41L, the solenoid 6 of the traveling lock solenoid control valve 65 is used.
When the drive signal St input to 5a is turned on, the above operation of the right traveling control valve 47R by the operation lever 53R becomes possible, and when the drive signal St is turned off,
The above operation of the right traveling control valve 47R by the operation lever device 41R becomes impossible.

Control valve 49 for second crusher
Is generated by the pilot pump 45 similarly to the control valve 48 for the first crushing device, and is generated by the operation valve device 6.
4 is operated by the pilot pressure reduced to a predetermined pressure by the crushing device normal rotation solenoid control valve 66F and the crushing device reverse rotation solenoid control valve 66R.

That is, when the drive signal Scr1 from the controller 70 is ON and the drive signal Scr2 is OFF, the pilot pressure from the pilot pump 45 is applied to the introduction line 71.
a, control valve 4 for the second crusher via 71b
9 and is guided to the driving section 49a, and the introduction pipes 72a, 72
b is communicated with the tank line 69a and becomes the tank pressure,
The control valve 49 for the second crusher is switched to the upper switching position 49A in FIG. As a result, the pressure oil from the second hydraulic pump 44B is supplied to the crusher hydraulic motor 15 via the switching position 49A, and the crusher hydraulic motor 15 is driven in the forward direction.

Similarly, when the drive signal Scr1 is turned off and the drive signal Scr2 is turned on, the pilot pressure becomes
a, control valve 4 for the second crusher via 72b
9 and is guided to the driving section 49b, and the introduction pipes 71a, 71
b becomes the tank pressure, the control valve 49 for the second crushing device is switched to the lower switching position 49B in FIG.
The pressure oil from the second hydraulic pump 44B is switched to its switching position 49B.
Is supplied to the hydraulic motor 15 for the crushing device, and the hydraulic motor 15 for the crushing device is driven in the reverse direction.

The drive signals Scr1 and Scr2 are both OF signals.
At F, the control valve 49 for the second crushing device is operated by the restoring force of the springs 49c and 49d to reach the neutral position 49 shown in FIG.
After returning to C, the hydraulic motor 15 for the crusher is stopped.

As described above, the first valve group 60
The control valve 48 for the first crusher and the control valve 49 for the second crusher A perform the same operation according to the drive signals Scr1 and Scr2 to the solenoid control valves 66F and 66R, and the drive signal Scr1 is turned on. When the drive signal Scr2 is OFF, the hydraulic oil from the first hydraulic pump 44A and the second hydraulic pump 44B are combined and supplied to the crusher hydraulic motor 15.

The aforementioned pump control valve 61R
When the required flow rates of the control valves 47R and 49 required for the second hydraulic pump 44B (in other words, the required flow rates of the right traveling hydraulic motor 6R and the crushing apparatus hydraulic motor 15) are small, a relatively large flow rate is required. The pressure oil is guided to the tank line 69b through the throttle portion 61Raa of the piston 61Ra, and the piston 61Ra moves to the left in FIG. A relatively low control pressure (negative control pressure) P is provided in a pipe 75b which is provided to reach a second servo valve 77 for negative tilt control described later.
Generates c2. When each of the control valves 47R and 49 is operated and the required flow rate to the second hydraulic pump 44B is large, the piston 61Ra moves to the right in FIG. 9 and the set relief pressure of the relief valve 61Rd increases, and the pipe 75b is closed. The control pressure Pc2 increases. Then, the first hydraulic pump 44
Similarly to A, the tilt angle of the inclined shaft 44Ba of the second hydraulic pump 44B is controlled based on the fluctuation of the control pressure (negative control pressure) Pc2 (details will be described later).

FIG. 10 is a hydraulic circuit diagram showing a detailed configuration of the regulator device 54. In FIG. 10, reference numerals 78 and 79 denote tilt actuators, and reference numerals 74 and 77 denote the first servo valve and the second servo valve.
And the second servo valve 74, 77 and the pilot pump 4
5 controls the pressure of the hydraulic oil acting on the tilting actuators 78, 79, and controls the first and second hydraulic pumps 44A, 44B.
Of the oblique shafts 44Aa and 44Ba (i.e., displacement).

The tilt actuators 78, 79 have large-diameter pressure receiving portions 78a, 79a and small-diameter pressure receiving portions 78b, 78b at both ends.
Working pistons 78c, 79c having a pressure receiving portion 79a, and pressure receiving chambers 78d, 78e and 79d, 79e in which the pressure receiving portions 78a, 78b and 79a, 79b are respectively located.
And When the pressures in the two pressure receiving chambers 78d, 78e and 79d, 79e are equal to each other, the working pistons 78c, 79c move rightward in FIG. And the respective pump discharge flow rates increase. When the pressure in the large-diameter pressure receiving chambers 78d, 79d decreases, the working pistons 78c, 79c move to the left in FIG. Has been reduced. The large-diameter pressure receiving chambers 78d and 79d are connected to a pipe 80 communicating with the discharge pipe 56 of the pilot pump 45 via the first and second servo valves 74 and 77, and the small-diameter pressure receiving chamber is provided. 78e and 79e are direct conduits 80
It is connected to the.

The first and second servo valves 74 and 77 are both servo valves for negative tilt control, and the first servo valve 74 of the first hydraulic pump 44A is controlled by the pump control valve 61L as described above. The second servo valve 77 related to the second hydraulic pump 44B is driven by the control pressure (negative control pressure) Pc2 from the pump control valve 61R as described above, and these are equivalent to each other. It has a structure.

That is, when the control pressures Pc1 and Pc2 are high, the valve bodies 74a and 77a move rightward in FIG. Rooms 78d, 79d
, Whereby the tilting of the oblique shafts 44Aa, 44Ba increases, and the first and second hydraulic pumps 44A, 44B
Are respectively increased. And the control pressure Pc
As Pc2 decreases, the valve bodies 74a and 77a move leftward in FIG. 10 by the forces of the springs 74b and 77b, reduce the pilot pressure Pp from the pilot pump 45, and transmit it to the pressure receiving chambers 78d and 79d. , The discharge flow rate of the first and second hydraulic pumps 44A, 44B is reduced.

As described above, in the two first and second servo valves 74 and 77 of the regulator device 54, the functions of the control valves 47L and 48 or the control valves 47R and 49 are required in addition to the functions of the pump control valves 61L and 61R. More specifically, the center bypass lines 60Aa, 60A
Pump control valves 61L, 61 flowing from Ba
A so-called negative control is realized in which the tilts (discharge flow rates) of the oblique axes 44Aa, 44Ba of the first and second hydraulic pumps 44A, 44B are controlled so that the flow rate passing through the R is minimized.

Next, the above-mentioned traveling speed switching solenoid control valve 67 will be described. In FIG. 8, when the drive signal Sv input from the controller 70 to the solenoid 67a is turned on, the traveling speed switching solenoid control valve 67 is switched to the communication position 67A on the right side in FIG. The pressure is led to the variable relief valves 61Ld and 61Rd (see FIGS. 7 and 9) via the pilot introduction line 73a and the pilot introduction lines 73b and 73c. As a result, the control pressures Pc1 and Pc2 according to the magnitude of the required flow rate of each control valve described above.
Can be generated, and as a result, as described above,
The oblique shaft 44 of the first hydraulic pump 44A can obtain a discharge flow rate according to the required flow rates of the control valves 47L and 48.
The oblique shaft 44Ba of the second hydraulic pump 44B so as to obtain a negative control for controlling the tilt of Aa and a discharge flow rate corresponding to the required flow rate of the control valves 47R and 49.
Negative control for controlling the tilt of the vehicle can be realized.

On the other hand, when the drive signal Sv is turned off, the traveling speed switching solenoid control valve 67 returns to the shut-off position 67B on the left side in FIG. 73b, 73c and the pilot introduction lines 73b, 73c.
Is communicated with the tank line 69a, and the pressure in the pilot introduction pipes 73b and 73c is used as the tank pressure.
Thus, the control pressures Pc1 and Pc2 are always equal to the tank pressure 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 described above becomes invalid.

As a result of the function of the running speed switching solenoid control valve 67 as described above, the following running speed switching control is realized. That is, when the traveling speed switching solenoid control valve 67 is at the communication position 67A, as described above, the oblique axes 44 of the first and second hydraulic pumps 44A and 44B are used.
Since the tilting of Aa and 44Ba is controlled by the negative control, the left and right traveling hydraulic motors 6L and 6L are controlled.
When the vehicle is not operating except for R, the discharge flow rate corresponding to the required flow rate of the left travel control valve 47L is discharged from the negatively controlled first hydraulic pump 44A and the right travel control valve 47R.
Is discharged from the negatively controlled second hydraulic pump 44B. At this time, as described above, the required flow rates of the left and right traveling control valves 47L and 47R and the left / right traveling operation lever 5
Since the operation amounts of 3L and 53R correspond to each other, the relationship between the operation amounts of the left and right traveling operation levers 53L and 53R and the supply flow rates to the left and right traveling hydraulic motors 6L and 6R is a linear relationship. Becomes That is, the motor supply flow rate is substantially zero when the operation amounts of the left and right traveling operation levers 53L and 53R are zero.
The supply flow rate increases almost linearly as the operation amount increases, and when the operation amount reaches the maximum value, the motor supply flow rate reaches the maximum value of the pump discharge flow rate.

On the other hand, the traveling speed switching solenoid control valve 6
When 7 is at the shut-off position 67B, the pressure in the pilot introduction pipes 73b and 73c is used as the tank pressure as described above. It becomes the tank pressure (in other words, the maximum value of the control pressure is reduced as compared with the maximum value of the control pressure in the case of the communication position 67A). As a result, the discharge flow rate of the first and second hydraulic pumps 44A and 44B always becomes the minimum value (in other words, the communication position 6).
The maximum discharge flow rate of the pump is reduced as compared with the case of 7A). 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 described above is released.

Therefore, the left and right traveling hydraulic motor 6
When the vehicle does not operate other than L and 6R, the first and the second control valves 47L and 47R do not operate irrespective of the required flow rates (ie, the operation amounts of the left and right operation levers 53L and 53R). Hydraulic pumps 44A, 44
A minimum flow rate is discharged from B, and only a portion of the flow rate corresponding to the degree of opening of the left / right running control valves 47L, 47R becomes the supply flow rate to the left / right running hydraulic motors 6L, 6R. That is, the left / right traveling operation lever 53
L, 53R and the left and right traveling hydraulic motors 6L, 6L
The relationship with the supply flow rate to R is a straight line having a smaller inclination than that in the case of the communication position 67A. When the operation amount is 0, the motor supply flow rate is 0, and as the operation amount increases, the supply flow rate becomes approximately When the operation amount increases linearly and reaches the maximum value (the valve is fully opened), the motor supply flow rate becomes the minimum value of the pump discharge flow rate.

FIG. 11 is a hydraulic circuit diagram showing a detailed configuration of the third control valve device 46C. In FIG. 11,
As described above, 50 is a conveyor control valve connected to the conveyor hydraulic motor 35, 51 is a magnetic separator control valve connected to the magnetic separator hydraulic motor 39, and 52 is a flow dividing valve.

Although a detailed description of the structure of the flow dividing valve 52 is omitted, the flow dividing valve 52 is a known flow dividing valve having a built-in pressure compensating function. Irrespective of the pressure, the third hydraulic pump 44C is set such that (the amount of pressure oil supplied to the hydraulic motor 35 for the conveyor) :( the amount of pressure oil supplied to the hydraulic motor 39 for the magnetic separator) = 2: 1. From the pressure oil.

The conveyor control valve 50
Is an electromagnetic switching valve provided with a solenoid driving unit 50a. The solenoid drive section 50a is provided with a solenoid driven by a drive signal Scon from the controller 70, and the conveyor control valve 50 is switched according to the input of the drive signal Scon. That is, when the drive signal Scon becomes an ON signal for operating the conveyor 33, the conveyor control valve 50 is switched to the switching position 50A on the right side in FIG. As a result, the pressure oil from the third hydraulic pump 44C guided through the discharge pipe 55C and the flow dividing valve 52 is supplied from the switching position 50A to the conveyor hydraulic motor 35 via the supply pipe 81a. 11 is driven.
The return oil at this time is supplied to the tank 69 via the discharge line 81b.
Return to. The drive signal Scon is transmitted from the conveyor 33 (FIG. 1).
11), the conveyor control valve 50 returns to the shut-off position 50B shown in FIG. 11 by the urging force of the spring 50b, and the conveyor hydraulic motor 35 stops.

The control valve 51 for the magnetic separator, like the control valve 50 for the conveyor, has its solenoid driving section 51a receiving a drive signal Sm from the controller 70.
And a solenoid that is driven by the solenoid. When the drive signal Sm becomes an ON signal for operating the magnetic separator 36, the magnetic separator control valve 51 is switched to the communication position 51A on the right side in FIG. 11, and the pressure oil from the third hydraulic pump 44C is supplied to the flow dividing valve 52. The oil is supplied to and driven by the hydraulic motor 39 for the magnetic separator through the switching position 51A of the control valve 51 for the magnetic separator and the supply line 82a, and the return oil returns to the tank 69 via the discharge line 82b. When the drive signal Sm becomes an OFF signal corresponding to the stop of the magnetic separator 36, the magnetic separator control valve 51 returns to the shut-off position 51B shown in FIG.
Stops.

The conveyor hydraulic motor 35
And supply of pressurized oil to the magnetic separator hydraulic motor 39, from the viewpoint of circuit protection and the like, pipes 83a, 84a connecting the supply pipes 81a, 82a and the discharge pipes 81b, 82b.
Are provided with relief valves 83b and 84b, respectively.

Returning to FIG. 6, reference numeral 85 denotes a drive unit provided in the relief valve 57 for limiting the discharge pressure of the first and second hydraulic pumps 44A and 44B. It is connected to a pipe 71b (see FIG. 8) via a pipe 86. Thereby, the shear type crusher 1
2, when the drive signal Scr1 from the controller 70 is turned on and the crusher forward rotation solenoid control valve 66F is switched to the communication position 66FA, the pilot pressure from the pilot pump 45 is applied to the introduction line 71a. , Through the communication position 66FA, the introduction pipe 71b, and the pipe 86, and is urged by the drive unit 85, and the maximum value of the discharge pressure of the first and second hydraulic pumps 44A, 44B by the relief valve 57 (ie, the relief pressure). Pressure) is set to a relatively large value which is substantially the sum of the urging force of the spring 57a and the pilot pressure to the drive unit 85. On the other hand, when the drive signal Scr1 from the controller 70 is O
FF, and when the crusher forward rotation solenoid control valve 66F is switched to the shut-off position 66FB, as described above,
While the introduction pipes 71a and 71b are shut off, the pipes 8
6 is connected to the tank line 69a via the introduction line 71b, the internal pressure of the tank line 69a becomes the tank pressure, the urging force of the pilot pressure to the drive unit 85 becomes zero, and the relief pressure of the relief valve 57 is reduced by the spring 57a. The biasing force is set to a relatively low value substantially equal to the biasing force of only the biasing force.

Further, the operation panel 42 includes a shredder start / stop for starting / stopping the shearing type crusher 12.
A stop switch 42a, a shredder forward / reverse selection dial 42b for selecting either forward or reverse operation direction of the shearing crusher 12, and a conveyor 33
Conveyor start / stop switch 42c for starting / stopping the magnetic separator, a magnetic separator start / stop switch 42d for starting / stopping the magnetic separator 36, and either a traveling mode for performing a traveling operation or a crushing mode for performing a crushing operation. A mode selection switch 42e for selecting one of them and a traveling mode selection switch 42f for selecting a normal mode or a slow mode of the traveling speed are provided.

When the operator operates various switches and dials of the operation panel 42, operation signals are input to the controller 70. The controller 70 controls the conveyor control valve 50 and the magnetic separator control valve 5 based on an operation signal from the operation panel 42.
1. Solenoid drive units 50a, 51a and solenoid 65a provided in a traveling lock solenoid control valve 65, a crusher forward rotation solenoid control valve 66F, a crusher reverse rotation solenoid control valve 66R, and a traveling speed switching solenoid control valve 67, respectively. , 66Fa, 66Ra, 67a to generate the aforementioned drive signals Scon, Sm, St, Scr1, Scr2, Sv and output them to the corresponding solenoids.

That is, when the "travel mode" is selected by the mode selection switch 42e of the operation panel 42, the drive signal St of the travel lock solenoid control valve 65 is turned on, and the travel lock solenoid control valve 65 is turned on. 8, switch to the communication position 65A on the right side, and operate the operation levers 53L, 53R.
Allows the operation of the traveling control valves 47L and 47R. Mode selection switch 42e of operation panel 42
When the "crushing mode" is selected, the drive signal St of the traveling lock solenoid control valve 65 is turned off to return to the shut-off position 65B on the left side in FIG.
L, 53R for traveling control valve 47L, 4
Operation of 7R is disabled.

Further, "forward rotation" (or "reverse rotation", hereinafter referred to as "forward rotation" or "reverse rotation") using the shredder forward / reverse selection dial 42b of the operation panel 42.
When the shredder start / stop switch 42a is pressed to the "start" side in a state where the same relationship is selected, the solenoid 66Fa of the crusher forward rotation solenoid control valve 66F is pressed.
(Or drive signal Scr1 (or drive signal Scr) to the solenoid 66Ra of the crushing device reverse rotation solenoid control valve 66R.
2) is turned on, and the drive signal Scr2 (or drive signal Scr1) to the solenoid 66Ra of the crusher reverse rotation solenoid control valve 66R (or the solenoid 66Fa of the crusher forward rotation solenoid control valve 66F) is turned off.
And the second crusher control valves 48, 49 are switched to the upper switching positions 48A, 49A (or the lower switching positions 48B, 49B) in FIGS.
The pressurized oils from the hydraulic pumps 44A and 44B are combined and supplied to and driven by the hydraulic motor 15 for the crusher, and the shear crusher 12 is activated in the normal rotation direction (or the reverse rotation direction).

As described above, when the drive signal Scr1 to the solenoid 66Fa of the crushing device normal rotation solenoid control valve 66F is ON, the crushing device reverse rotation solenoid control valve 66 is turned on.
When the drive signal Scr2 to the R solenoid 66Ra is OFF, the pilot pressure is applied to the drive unit 85 of the relief valve 57, and the maximum pressure of the hydraulic oil joined from the first and second hydraulic pumps 44A and 44B is compared. The crushing torque is set high enough to obtain sufficient crushing torque.

Thereafter, the shredder start / stop switch 4
When 2a is pushed to the "stop" side, the drive signal Scr
1 and Scr2 are both turned off, the control valves 48 and 49 for the first and second crushing devices are returned to the neutral positions 48C and 49C shown in FIGS. 7 and 9, the hydraulic motor 15 for the crushing device is stopped, and the The crushing device 12 is stopped.

When the conveyor start / stop switch 42c of the operation panel 42 is pushed to the "start" side, the drive signal Scon to the solenoid drive unit 50a of the control valve 50 for the conveyor is turned on, and the right side of FIG. Communication position 5
0A, and supplies the hydraulic oil from the third hydraulic pump 44C to the conveyor hydraulic motor 35 to drive it.
Start 3 Thereafter, when the conveyor start / stop switch 42c of the operation panel 42 is pushed to the "stop" side, the drive signal Scon to the solenoid drive unit 50a of the control valve 50 for the conveyor is turned off and the control returns to the shut-off position 50B shown in FIG. Then, the conveyor hydraulic motor 35 is stopped, and the conveyor 33 is stopped.

Similarly, the magnetic separator start / stop switch 42d
Is pushed to the “start” side, the control valve 51 for the magnetic separator is switched to the communication position 51A on the right side in FIG.
When the magnetic separator 36 is started by driving the magnetic separator hydraulic motor 39 and the magnetic separator start / stop switch 42d is pushed to the "stop" side, the magnetic separator control valve 51 is returned to the shut-off position 51B, and the magnetic separator 36 is stopped.

When the "normal mode" is selected by the drive mode selection switch 42f, the drive signal Sv of the drive speed switching solenoid control valve 67 is turned on, and the drive speed switching solenoid control valve 67 is turned on in FIG. Switching to the middle right communication position 67A, control of the pump discharge flow rate according to the required flow rate of the left / right travel control valves 47L, 47R (the amount of operation of the left / right travel operation levers 53L, 53R) as described above. Make it possible. Driving mode selection switch 4
When the "slow speed mode" is selected at 2f, the drive signal Sv of the traveling speed switching solenoid control valve 67 is turned off to return to the shut-off position 67B on the left side in FIG. Control of the pump discharge flow rate in accordance with the required flow rate of the control valves 47L and 47R for
The pump discharge flow rates of the second hydraulic pumps 44A and 44B are set to a constant value.

In the above, the crawler belt 7 constitutes self-propelled left / right traveling means as described in the claims, and the shearing type crushing device 12 crushes the crushed material and crushes the crushed material. Constituting a crushing device, wherein the engine 43 comprises:
Configure the prime mover.

The control valve 4 for the crusher
8, 49, the crushing device forward rotation solenoid control valve 66F and the crushing device reverse rotation solenoid control valve 66R constitute crushing device control valve means for guiding pressure oil from the hydraulic pump to the crushing device hydraulic motor, and And a control for the crushing device, which is connected to a discharge line of the second hydraulic pump and joins the pressure oils from the first and second hydraulic pumps during the crushing operation of the self-propelled crusher and supplies it to the hydraulic motor for the crushing device. The valve means is constituted by operating lever devices 41L and 41R and operating panel 42.
Constitutes operating means for switching between the left and right traveling control valves and the crushing device control valve means.

Further, the relief valve 57 constitutes a relief valve for setting a relief pressure for limiting the maximum value of the discharge pressure of the first and second hydraulic pumps. The forward rotation solenoid control valve 66F is
Relief pressure changing means for changing the relief pressure of the relief valve according to the operation state of the operating means is constituted.

Next, the operation of the self-propelled crusher of 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 configuration, at the time of crushing operation, after the operator selects “crushing mode” with the mode selection switch 42e of the operation panel 42 to disable the traveling operation, "Forward" is selected with the shredder forward / reverse selection dial 42b, and the magnetic separator start / stop switch 42d, the conveyor start / stop
Stop switch 42c, Shredder start / stop switch 4
2a is sequentially pushed to the "start" side.

By the above operation, the controller 70 controls the solenoid drive unit 5 of the control valve 51 for the magnetic separator.
When the drive signal Sm to the control valve 1a is turned ON, the control valve 51 for the magnetic separator is switched to the communication position 51A on the right side in FIG. When turned ON, the control valve 50 for the conveyor is switched to the communication position 50A on the right side in FIG.
Further, the controller 70 controls the solenoid control valve 66F for the crushing device normal rotation and the solenoid control valve 6 for the crushing device reverse rotation.
The drive signals Scr1 and Scr1 to the 6R solenoid drive units 66Fa and 66Ra turn ON and OFF, respectively, and the first
And the control valves 48, 49 for the second crushing device are switched to the upper switching positions 48A, 49A in FIGS.

Thus, the hydraulic oil from the third hydraulic pump 44C is supplied to the magnetic separator hydraulic motor 39 and the conveyor hydraulic motor 35, and the magnetic separator 36 and the conveyor 33 are activated, while the first and second hydraulic pumps are activated. The pressure oils from the pumps 44A and 44B join and are supplied to the hydraulic motor 15 for the crushing device, and the shearing crushing device 12 is started in the normal rotation direction.

At this time, the pilot pressure guided from the pilot pump 45 to the driving portions 48a, 49a of the first and second crushing device control valves 48, 49 via the introduction line 71b is branched off from the introduction line 71b. Conduit 86
Through the drive unit 85 provided in the relief valve 57. Thereby, the maximum value of the discharge pressure of the first and second hydraulic pumps 44A, 44B by the relief valve 57 is set high, and the maximum value of the discharge pressure from the first and second hydraulic pumps 44A, 44B supplied to the crusher hydraulic motor 35 is increased. The pressure of the combined pressure oil increases.

When the hydraulic drive unit in the power unit 9 operates as described above, the crushed object put into the hopper 1 by, for example, a hydraulic shovel or the like is guided to the shearing type crushing unit 12, and Crushed to a predetermined size. The crushed crushed material falls from the shear crushing device 12 via the chute 32 onto the conveyor 33 and is conveyed. The transported crushed material is transferred to the magnetic separator 36 during transport.
Foreign matter (for example, magnetic substances such as rebar pieces mixed in concrete construction waste) is removed by the process, the size is almost uniform, and finally from the rear of the self-propelled crusher (right end in FIG. 1). It is carried out.

(II) Self-traveling 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 42e of the operation panel 42 and the traveling mode. The "normal mode" is selected by the selection switch 42f, and the operator gets on the driver's seat 40 and operates the operation levers 53L and 53R forward. As a result, the left and right traveling control valves 47L, 47R are moved to the upper switching position 47L in FIGS.
A, 47RA and the hydraulic oil from the first and second hydraulic pumps 44A, 44B is supplied to the left / right traveling hydraulic motor 6
L and 6R, the left and right traveling hydraulic motors 6L and 6R are driven in the normal rotation direction, and the crawler belt 7 causes the self-propelled crusher to travel forward (to the left in FIG. 1).

At this time, the driving mode selection switch 42f
Since the "normal mode" is selected in the above, the traveling speed switching solenoid control valve 67 becomes the communication position 67A, and as described above, the discharge flow rate according to the operation amount of the left / right traveling operation levers 53L and 53R is reduced. First and second hydraulic pumps 44
A and 44B are discharged, and the degree of opening of the left and right traveling control valves 47L and 47R increases according to the operation amount. Accordingly, the operator can operate the traveling operation levers 53L and 53R with a relatively large operation amount to perform high-speed traveling, so that the operator can quickly move to a desired position in a movable site, and the operating rate can be reduced. Improvement can be achieved.

[0098] For example, when the operator runs on the trailer carrier to load the trailer to the operation site, the operator selects the "running mode" with the mode selection switch 42e of the operation panel 42. At the same time, select the "slow speed mode" with the driving mode selection switch 42f,
The operator gets on the driver's seat 40 and operates the operation levers 53L and 53R forward. At this time, the driving mode selection switch 42
Since the "slow speed mode" is selected in e, the traveling speed switching solenoid control valve 67 is in the shut-off position 67B, and as described above, the left and right traveling operation levers 53L and 53R.
Irrespective of the operation amount of, the pump minimum discharge flow rate is constantly discharged from the first and second hydraulic pumps 44A and 44B. Accordingly, the operator can operate the traveling operation levers 53L and 53R with a relatively small amount of operation, thereby performing ultra-low speed traveling (slow traveling).

The left and right traveling operation levers 53L, 5L
Since the supply flow rates of the left and right traveling hydraulic motors 6L and 6R are increased at a relatively low rate with respect to the increase in the operation amount of the 3R,
The speed change with respect to the change amount of the operation amount can be reduced, and precise control of the self-running speed can be performed.

According to the hydraulic drive system for a self-propelled crusher according to one embodiment of the present invention having the above-described configuration and operation, the following effects can be obtained. (1) Reducing the size of the traveling means and ensuring the required crushing capacity of the crushing device In the present embodiment, the first and second hydraulic pumps 44 are used.
The values of the relief pressures for limiting the maximum values of the discharge pressures of the A and 44B are determined during the crushing operation, that is, as described above.
After selecting the "crushing mode" with the mode selection switch 42e of No. 2 and disabling the traveling operation, when selecting "forward" with the shredder forward / reverse selection dial 42b, the drive unit 85 of the relief valve 57 When the pilot pressure is urged and increased, the required crushing capacity of the shearing type crushing device 12 can be ensured while the crawler belt 7 is downsized.

That is, as described above, in the hydraulic drive device of the present embodiment, first, "running mode" is selected by the mode selection switch 42e of the operation panel 42, and left and right are operated by the operation lever devices 41L and 41R. When the traveling control valves 47L and 47R are switched, the hydraulic oil from the first and second hydraulic pumps 44A and 44B is switched and supplied to the left and right traveling hydraulic motors 6L and 6R, respectively, and the operating lever devices 41L and 41R. The crawler belt 7 is driven in response to the operation.

On the other hand, the mode selection switch 4 on the operation panel 42
When the "crushing mode" is selected in 2e, the drive units 47La, 47R of the left and right traveling control valves 47L, 47R are operated.
Lb, 47Ra, pilot line 63a to 47Rb,
63b is the tank pressure, and the left and right traveling control valves 47L, 47R are springs 47Lc, 47L, respectively.
d and the biasing forces of the springs 47Rc, 47Rd are switched to the neutral positions 47LC, 47RC. As a result, the first
The hydraulic oil from the second hydraulic pumps 44A and 444B passes through the center bypass lines 60Aa and 60Ba, and passes through the neutral positions 47LC and 47RC of the left and right traveling control valves 47L and 47R, respectively. , 49.

In this state, when "forward" is selected by the shredder forward / reverse selection dial 42b and the shredder start / stop switch 42a is set to the start side, the switching positions 48A, 49A of the crushing device control valves 48, 49 are switched. Are combined and supplied to the crusher hydraulic motor 15, and the shear crusher 12 is driven forward.

At this time, since the control valves 48, 49 for the crushing device are switched to the switching positions 48A, 49A, the pilot pressure guided to the driving portions 48a, 49a is:
As described above, the relief pressure of the relief valve 57 is also introduced to the drive unit 85 provided in the relief valve 57 for limiting the maximum value of the discharge pressure of the first and second hydraulic pumps 44A and 44B via the pipe line 86. Can be changed to a relatively large value obtained by adding the pilot pressure to the urging force of the spring 57a (relatively low relief pressure set by the relief valve alone). For this reason, sufficient crushing capacity of the shear crusher 12 can be ensured.

On the other hand, for example, when the left and right traveling control valves 47L and 47R are operated (that is, at the time of traveling) as described above, the pilot pressure is applied to the driving portion 85 of the relief valve 57. Without being biased, the relief pressure of the relief valve 57 has a relatively low value set only by the biasing force of the spring 57a.

As described above, the hydraulic pumps of sufficient capacity (in this example, the first and second hydraulic pumps 44A, 44A,
4B), it is possible to use relatively small crawler belts 7 and the left and right traveling hydraulic motors 6L and 6R for driving them. Therefore, the required crushing ability of the shear crusher 12 can be ensured while the crawler belt 7 is downsized.

(2) Effect of Improving Work Efficiency In the hydraulic drive system of the self-propelled crusher according to the present embodiment, as described above, during the crushing operation, the water is discharged from the first and second hydraulic pumps 44A and 44B. The pressurized oil is merged from the respective discharge pipe lines 55A and 55B via the first and second crushing device control valves 47L and 47R and supplied to the crushing device hydraulic motor 15 to be driven. In the traveling operation, the hydraulic oil discharged from the first hydraulic pump 44A is supplied from the discharge pipeline 55A to the left traveling hydraulic motor 6L via the left traveling control valve 47L to be driven, and the second hydraulic pump is driven. The pressure oil discharged from 44B is supplied from the discharge pipeline 55B to the right traveling hydraulic motor 6R via the right traveling control valve 47R to be driven.

As described above, the hydraulic circuit on the side of the shearing crusher 12 having a very large load compared to the auxiliary machine such as the conveyor 33 and the magnetic separator 36 is similarly shared with the traveling side having a relatively large load to be independent. By supplying pressure oil to the conveyor 33 and the magnetic separator 36 side separately from the third hydraulic pump 44C, the shear-type crusher 12 and the conveyor 33 and the magnetic separator 36 are completely separated from each other. Hydraulic circuit. As a result, as compared with a structure in which pressure oil is distributed and supplied from the common hydraulic source to both the crushing device side and the auxiliary machine side, the shear type crushing device 12 side and the auxiliary Sufficient pressure oil can be supplied to each of the machines (that is, the conveyor 33 and the magnetic separator 36). Therefore, the auxiliary machine 3
Since the power loss on the 3, 36 side can be reduced, the energy efficiency can be improved, the horsepower input to the shear crusher 12 can be increased, and the crushing operation efficiency can be improved.
In addition, fuel efficiency can be improved.

[0109] Unlike a construction machine such as a hydraulic excavator, a self-propelled crusher basically does not perform work while traveling, and requires a very low traveling speed. Thus, in a normal use mode, the total horsepower input to the left and right traveling hydraulic motors and the horsepower input to the crusher hydraulic motor are relatively similar. Therefore, as in the present embodiment, the hydraulic oil from the first and second hydraulic pumps 44A, 44B is supplied to the left and right traveling hydraulic motors 6L, 6R during the traveling operation, respectively, and merged during the crushing operation to be crushed. The supply to the device hydraulic motor 15 is the most effective and less wasteful circuit configuration in view of the characteristics of the self-propelled crusher, which also has the effect of improving energy efficiency.

(3) Meandering Prevention Effect In the present embodiment, the first hydraulic pump 44A
Is supplied to the left traveling hydraulic motor 6L, and the pressure oil from the second hydraulic pump 44B is supplied to the right traveling hydraulic motor 6R.
Compared to a structure in which pressure oil is distributed and supplied to both the L and the right traveling hydraulic motor 6R, the left and right circuits are independent, the meandering during traveling can be prevented, and the straight traveling performance can be improved.

(4) Set two control valves for the crushing device.
Effect of Dividing into Two In this embodiment, when the hydraulic oil from first and second hydraulic pumps 44A and 44B is combined and supplied to hydraulic motor 15 for the crushing device during the crushing operation, the first and second hydraulic pumps are used. The pressure oils of the hydraulic pumps 44A and 44B are joined after passing through the first and second crusher control valves 48 and 49, respectively, and supplied to the crusher hydraulic motor 15. That is,
Before the merge, the flow of the pressure oil is controlled using two valves. Thereby, for example, the first and second hydraulic pumps 4
After combining the pressure oils from 4A and 44B, one control valve for the crusher is provided and controlled.
Since the flow rate per control valve can be reduced, the pressure loss at the control valve can be further reduced. In addition, it is not necessary to use a large control valve, and the cost can be reduced. Moreover, at this time, the first and second crusher control valves 48,
By using a control valve having the same characteristics as 49, the cost can be further reduced. At this time,
A valve block 60A composed of a control valve 48 for the first crushing device and a control valve 47L for left running.
And a valve block 6 comprising a second crushing device control valve 49 and a right traveling control valve 47R.
The cost can be further reduced by configuring the OB to be common to the left and right.

(5) Pressure Loss Reduction Effect at Very Low Speed Running According to the present embodiment, as described above, the first and second
By increasing / decreasing the pump discharge flow rate of the hydraulic pumps 44A, 44B and increasing / decreasing the supply flow rate to the left / right traveling hydraulic motors 6L, 6R, both high-speed traveling and very low-speed traveling are enabled. As a result, the flow rate of a series of pressure oil supply paths from the first and second hydraulic pumps 44A and 44B to the left and right traveling control valves 47L and 47R to the left and right traveling hydraulic motors 6L and 6R is reduced during the slow traveling. So left
The flow rate through the right traveling control valves 47L and 47R can also be reduced. This, at least,
The pressure loss generated in the left and right traveling control valves 47L and 47R can be reduced as compared with the case where the same large flow rate is supplied even at the time of low-speed traveling as at the time of high-speed traveling. Second hydraulic pumps 44A, 44B
Required for the engine 43 for driving the vehicle. As a result, the fuel consumption of the engine 43 can be reduced.
This has the effect of extending operating time and improving productivity.

(6) Energy saving effect by negative control of the crusher-side pump In this embodiment, the pump control valve 6
1L, 61R and first and second of the regulator device 54
Negative control is performed via the servo valves 74, 77, etc., whereby the center bypass line 60A
a, the discharge flow rate of the first and second hydraulic pumps 44A, 44B increases as the flow rate of the pressure oil flowing downstream of the 60Ba decreases, and during the crushing operation, the flow rates from the first and second hydraulic pumps 44A, 44B increase. The discharge flow rate is controlled so as to be a minimum flow rate necessary for driving the crusher hydraulic motor 15. Therefore, the discharge flow rates of the first and second hydraulic pumps 44A and 44B are not unnecessarily increased and the horsepower of the engine 43 is not wasted, so that further energy saving can be achieved.

In the embodiment of the present invention, the oblique axes 44A of the first and second hydraulic pumps 44A, 44B are controlled by using the pump control valves 61L, 61R.
a, 44Ba tilt control (negative control) was performed, but the above-mentioned effect (1), which is an essential effect of the present invention,
Is not always necessary as long as the first hydraulic pump 44A,
4B may be a fixed displacement pump.

Further, in the present embodiment, the pressure oils of the first and second hydraulic pumps 44A and 44B are merged after passing through the first and second crushing device control valves 48 and 49, and the crushing device hydraulic pressure is reduced. Although supplied to the motor 15, the arrangement is not necessarily required as long as the above-mentioned effect (1), which is an essential effect of the present invention, is obtained. The right traveling control valve 4 in the downstream side of the valve 47L and the center bypass line 60Ba.
The downstream side of the 7R may be joined to each other, and after the joining, one control valve for the crushing device may be provided to control the flow of the pressure oil to the hydraulic motor 15 for the crushing device.

Further, in the present embodiment, both high-speed traveling and very low-speed traveling are enabled by using the traveling speed switching solenoid control valve 67. Needless to say, as long as is obtained, it is not necessary to provide such a function, and it is not necessary to be able to switch between high speed and fine speed.

During the traveling operation, the first hydraulic pump 44A
The hydraulic oil is supplied to the left traveling hydraulic motor 6L and the hydraulic oil from the second hydraulic pump 44B is supplied to the right traveling hydraulic motor 6R. As long as 1) is obtained, the present invention is not limited to this.
It is good also as a structure which supplies pressure oil to L and 6R. In short, any structure may be used as long as the maximum value of the discharge pressure of the hydraulic pump during traveling and crushing can be changed.

Another embodiment of the self-propelled crusher of the present invention will be described with reference to FIGS. FIG. 12 is a hydraulic circuit diagram showing an overall schematic configuration of a hydraulic drive device provided in another embodiment of the self-propelled crusher of the present invention, and FIG. 13 is a hydraulic circuit diagram provided in the hydraulic drive device of the present embodiment. 1 control valve device 46
FIG. 14 is a hydraulic circuit diagram illustrating a detailed configuration of a second control valve device 46B ′ provided in the present embodiment, and FIG. 15 is a hydraulic circuit diagram illustrating a detailed configuration of a second control valve device 46B ′ provided in the present embodiment. FIG. 9 is a hydraulic circuit diagram illustrating a detailed configuration of an operating valve device 64 ′ provided, and corresponds to FIGS. 6, 7, 9, and 8, respectively. Note that the same parts as those in each of the preceding drawings are denoted by the same reference numerals, and description thereof will be omitted. First, in FIG. 12, reference numeral 87 denotes a pipeline which serves as a pipeline for supplying pressure oil to the hydraulic motor 15 for the crushing device at the time of normal rotation, and
A pressure reducing valve 87a provided in a pipe 88 connecting the valve 5 is a spring of the pressure reducing valve 87 for setting the pressure of the pipe 88 after the pressure reduction (that is, the pressure on the downstream side of the pressure reducing valve 87). This pressure reducing valve 8
Reference numeral 7 denotes a known pressure reducing valve, which controls the pressure of the pressure oil on the downstream side and a spring 87a.
Are made to be equal. That is, when the pressure on the downstream side is lower than the urging force of the spring 87a, the valve body is moved upward in FIG. 12 by the urging force of the spring 87a, and the passing flow rate is reduced by reducing the opening area. On the other hand, when the pressure on the downstream side is higher than the urging force of the spring 87a, the spring 87a is pressed and contracted by the pressure on the downstream side, the valve element moves to the lower side in FIG. 12, and the passage flow rate is reduced by reducing the opening area. Decrease. This allows
The downstream pressure and the biasing force of the spring 87a are offset, and the downstream pressure is set by the biasing force of the spring 87a.

Further, in FIGS. 13 and 14, 46
A ′ and 46B ′ correspond to the first and second control valve devices 46.
The first and second control valve devices 46A and 46B are substantially the same as the first and second control valve devices 46A and 46B. , 49 are constituted by electromagnetically driven control valves. That is, in the present embodiment, the control valve 48 for the first crusher (or the control valve 49 for the second crusher,
The same applies to the following.) The driving signals Scr1 and Scr2 output from the controller 70 by the above-described operation are the driving units 48a and 48b each formed by a solenoid.
(Or drive units 49a, 49b).

Thus, at the time of normal rotation, the driving portion 48a (or the driving portion 49a) of the first crushing device control valve 48 (or the second crushing device control valve 49).
The drive signal Scr1 to the drive unit is turned ON, and the drive unit 48
b (or the drive unit 49b) is turned off, so that the switching position 48A (or the switching position 49b) is turned off.
Switch to A). On the other hand, at the time of reverse rotation, the drive unit 48a (or the drive unit 49) of the first crusher control valve 48 (or the second crusher control valve 49).
The drive signal Scr1 to a) is turned off, and the drive signal Scr2 to the drive unit 48b (or the drive unit 49b) becomes O.
N, the switching position 48B (or the switching position 4
9B). Further, the drive signals Scr1, Sc
When both r2 are turned OFF, the springs 48c, 48 are controlled similarly to the control valves 48, 49 for the first and second crushing devices.
and the neutral position 48C,
It returns to 49C.

As described above, in the present embodiment, the control valves 48 and 49 for the first and second crushing devices are constituted by electromagnetically driven control valves, and as a result, FIG.
As shown in FIG. 5, the operation valve device 64 'omits the crusher forward rotation solenoid control valve 66F and the crusher reverse rotation solenoid control valve 66R.

As described above, in the present embodiment, as in the above-described embodiment, the first and the second
Drive unit 48 of control valves 48, 49 for the crushing device
a, 49a (see FIGS. 7 and 9) is supplied to the crushing device hydraulic motor 15 when the crushing device hydraulic motor 15 rotates forward instead of introducing the pilot pressure supplied to the drive unit 85 of the relief valve 57. Pressure oil to reduce pressure
7 is supplied to the drive unit 85.

Thus, during the crushing operation, the pressure of the reduced pressure oil is applied to the urging force of the spring 57a of the relief valve 57, so that the maximum value of the discharge pressure of the first and second hydraulic pumps 44A and 44B increases. It has become. On the other hand, during other operations such as running, for example, during the above-described forward rotation, the pressure of the pipeline supplying the pressurized oil to the crusher hydraulic motor 15 becomes the tank pressure and is urged by the drive unit 85 of the relief valve 57. Therefore, the maximum value of the discharge pressure of the first and second hydraulic pumps 44A and 44B limited at that time is set to a relatively low value only by the urging force of the spring 57a of the relief valve 57. Will be. Therefore, also in the present embodiment, the same effect as in the above-described one embodiment is obtained.

In the present embodiment, the driving unit 8
5. The pressure reducing valve 87 and the pipeline 88 constitute relief pressure changing means for changing the relief pressure of the relief valve according to the operation state of the operating means.

A still another embodiment of the self-propelled crusher of the present invention will be described with reference to FIG. FIG. 16 is a hydraulic circuit diagram showing an overall schematic configuration of a hydraulic drive device provided in still another embodiment of the self-propelled crusher of the present invention.
FIG. Note that the same parts as those in each of the preceding drawings are denoted by the same reference numerals, and description thereof will be omitted. In FIG. 16, 89
Is a solenoid provided on the drive unit 85 of the relief valve 57. As described above, the "forward" is selected by the shredder forward / reverse selection dial 42b of the operation panel 42, and the shredder start / stop switch 42a is turned on. When the drive signal Scr1 output from the controller 70 is turned ON, a predetermined force is applied to the drive unit 57a of the relief valve 57. Thus, the relief pressure for limiting the maximum value of the discharge pressure of the first and second hydraulic pumps 44A and 44B can be set higher than the case where the relief pressure is limited only by the urging force of the spring 57a of the relief valve 57. ing. On the other hand, when the drive signal Scr1 is turned off,
The solenoid 89 is in a neutral state, so that no force acts on the driving portion 57a of the relief valve 57.

The other structure is the same as that of the above-mentioned other embodiments described with reference to FIGS. 12 to 15, but in this embodiment, The pressure reducing valve 87 and the pipeline 88 are omitted because the structure is configured to be energized by the solenoid 89.

With the above-described configuration, in the present embodiment, the driving portions 48a, 49a of the first and second crushing device control valves 48, 49 (FIGS. 7 and 9)
Instead of introducing the pilot pressure supplied to the drive unit 85 of the relief valve 57 into the drive unit Sfa1 of the crusher forward rotation solenoid control valve 66F, the drive signal Scr1 is input to the solenoid 89 to output the relief valve. An urging force is applied to the drive unit 85 of the 57.

Thus, during the crushing operation, the urging force of the solenoid 89 is applied to the urging force of the spring 57a of the relief valve 57, and the first and second hydraulic pumps 44A, 44A are operated.
The maximum value of the discharge pressure of B increases. On the other hand, during other operations such as running, for example, the drive signal Scr1 is turned off, and the drive unit 8 of the relief valve 57 is turned off.
The urging force for 5 becomes 0. Thereby, the maximum value of the discharge pressure of the first and second hydraulic pumps 44A and 44B limited at that time is set to a relatively low value only by the urging force of the spring 57a of the relief valve 57. Therefore, also in the present embodiment, the same effect as in the above-described one embodiment is obtained.

In this embodiment, the solenoid 89 constitutes a relief pressure changing means for changing the relief pressure of the relief valve in accordance with the operating state of the operating means.

The structure for changing the set value of the relief pressure of the relief valve 57 does not need to be limited to the structure described in each of the embodiments described above, but may be another structure. For example, in the above-described embodiment, as described above, the control valves 48 and 49 for the first and second crushing devices of the pilot operation type are provided, and the control valves 48 and 49 for the first and second crushing devices are provided. The relief pressure by the relief valve 57 is changed by applying pilot pressure to the drive units 48a and 49a to the drive unit 85 of the relief valve 57. In this structure, the embodiment described with reference to FIG. Similarly to the above, a solenoid 89 may be provided in the drive unit 85 of the relief valve 57, and the drive signal Scr1 that is turned on during the forward rotation operation may be input to the solenoid 89. In short, the first and second
The relief pressure for limiting the maximum value of the discharge pressure of the hydraulic pumps 44A, 44B is increased by operating lever devices 41L, 41R,
What is necessary is just to set it as the structure which can be changed by operation of operation means, such as the operation panel 42.

In the above description, the shearing type crushing device 12 is provided with a cutter on a shaft arranged in parallel, and crushes construction waste materials, home electric appliances, plastic waste materials, old tires and the like by rotating them in opposite directions. Although a self-propelled crusher provided with (a two-axis shearing machine including a so-called shredder) has been described as an example, the present invention is not limited to this, and other crushing devices, for example, jaw crushers that crush with moving teeth and fixed teeth Also, a rotary crusher that rotates a pair of rotating bodies with a crushing blade attached to a crushing blade in the opposite direction to each other, and crushes rocks and construction waste materials between these rotating bodies. (A six-axis crusher including a so-called roll crusher) or a striking plate equipped with a plurality of blades is rotated at a high speed. A self-propelled crusher equipped with a crushing device (so-called impact crusher) that crushes construction waste materials and the like, as well as wood, branch timber, construction waste wood, etc., into a rotor equipped with a cutter. It is also applicable to a self-propelled wood crusher that shreds pieces. Similar effects are obtained in these cases.

In the above, the shear crusher 1
As the rotary teeth 17 provided in the second embodiment, a so-called mono-cutter integrally formed has been described as an example, but the present invention is not limited to this. For example, a cutter piece as a cutting tooth is detachably provided on a substantially circular disk portion. A so-called piece cutter may be used. In addition, the shearing type crushing device 12 is a two-axis shearing device, but is not limited to this, and each of the above embodiments can be applied to a self-propelled crushing device having a shearing device having a larger number of shafts. Needless to say. In this case, a similar effect is obtained.

In the above description, the cleaning fins 2 are provided on the outer peripheral side of the rotating bodies 21 and 21 of the shearing type crushing apparatus 12.
Although the cleaning fins 28 and 28 are provided, the cleaning fins 28 and 28 need not always be provided. Further, the cleaning fin support members 29, 29 may be omitted, and a housing in which the width direction side wall is fixed may be used. further,
Although a two-shaft shearing machine has been described as an example of the shearing-type crushing apparatus 12, the present invention is not limited to this, and a self-propelled crushing machine including a shearing machine having a larger number of shafts may be used. In these cases, a similar effect is obtained.

Further, in the above, in order to receive the torque from the rotating shaft 16, the section of the rotating shaft 16 is polygonal. However, the present invention is not limited to this. The shape may be substantially circular, and the torque from the rotating shaft 16 may be supported using a key or the like. In these cases, a similar effect can be obtained.

[0135]

According to the present invention, travel is provided by providing relief pressure changing means for changing the value of the relief pressure for limiting the maximum value of the discharge pressure of the hydraulic pump in accordance with the operation of the operating means. The required crushing capacity of the crushing device can be ensured while reducing the size of the means.

[Brief description of the drawings]

FIG. 1 is a side view showing the overall structure of an embodiment of a self-propelled crusher according to the present embodiment.

FIG. 2 is a top view illustrating the entire structure of the embodiment of the self-propelled crusher according to the present embodiment.

FIG. 3 is a front view showing the entire structure of the embodiment of the self-propelled crusher according to the present embodiment, as viewed from the left side in FIG.

FIG. 4 is a partially exploded top view showing a detailed structure of a shear crusher provided in one embodiment of the self-propelled crusher of the present embodiment.

FIG. 5 is a sectional view taken along a line VV in FIG. 4;

FIG. 6 is a hydraulic circuit diagram showing an overall schematic configuration of a hydraulic drive device provided in an embodiment of the self-propelled crusher of the present invention.

FIG. 7 is a hydraulic circuit diagram showing a detailed configuration of a first control valve device constituting a hydraulic drive device provided in one embodiment of the self-propelled crusher of the present invention.

FIG. 8 is a hydraulic circuit diagram showing a detailed configuration of an operation valve device constituting a hydraulic drive device provided in one embodiment of the self-propelled crusher of the present invention.

FIG. 9 is a hydraulic circuit diagram showing a detailed configuration of a second control valve device constituting a hydraulic drive device provided in one embodiment of the self-propelled crusher of the present invention.

FIG. 10 is a hydraulic circuit diagram showing a detailed configuration of a regulator device constituting a hydraulic drive device provided in an embodiment of the self-propelled crusher of the present invention.

FIG. 11 is a hydraulic circuit diagram showing a detailed configuration of a third control valve device constituting a hydraulic drive device provided in one embodiment of the self-propelled crusher of the present invention.

FIG. 12 is a hydraulic circuit diagram showing an overall schematic configuration of a hydraulic drive device provided in another embodiment of the self-propelled crusher of the present invention, and is a diagram corresponding to FIG.

FIG. 13 is a hydraulic circuit diagram showing a detailed configuration of a first control valve device constituting a hydraulic drive device provided in another embodiment of the self-propelled crusher of the present invention, and is a diagram corresponding to FIG. .

FIG. 14 is a hydraulic circuit diagram showing a detailed configuration of a second control valve device constituting a hydraulic drive device provided in another embodiment of the self-propelled crusher of the present invention, and is a diagram corresponding to FIG. .

FIG. 15 is a hydraulic circuit diagram showing a detailed configuration of an operation valve device constituting a hydraulic drive device provided in another embodiment of the self-propelled crusher of the present invention, and is a diagram corresponding to FIG.

FIG. 16 is a hydraulic circuit diagram showing an overall schematic configuration of a hydraulic drive device provided in still another embodiment of the self-propelled crusher of the present invention, and is a diagram corresponding to FIG.

[Explanation of symbols]

6L, R Hydraulic motor for left / right running 7 Crawler belt (left / right running means) 12 Shear type crushing device (crushing device) 15 Hydraulic motor for crushing device 41L, R Operating lever device (operating device) 42 Operating panel (operating device) 43 engine (motor) 44A first hydraulic pump 44B second hydraulic pump 44C third hydraulic pump 47L, R left / right traveling control valve 48 first crushing device control valve (crushing device control valve means) 49 second Crusher control valve (Crusher control valve means) 57-59 Relief valve 66F Crusher forward rotation solenoid control valve (Crusher control valve means) 66R Crusher reverse rotation solenoid control valve (Crusher control valve means) 85 Drive unit (relief pressure changing means) 86 Pipe line (relief pressure changing means) 87 Pressure reducing valve (relief pressure changing means) ) 88 Pipe line (Relief pressure changing means) 89 Solenoid (Relief pressure changing means)

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Jun Ikeda 650, Kandate-cho, Tsuchiura-shi, Ibaraki Hitachi Construction Machinery Co., Ltd. F-term in Tsuchiura Plant (reference) 4D067 DD04 DD06 EE48 GA02 GA06 GA20

Claims (5)

[Claims] 1. A hydraulic pump provided in a self-propelled crusher having left and right running means for self-propelling and a crushing device for crushing an object to be crushed, and driven by a motor, A hydraulic drive device for a self-propelled crusher comprising a left / right traveling hydraulic motor and a crushing device hydraulic motor that respectively drive the left / right traveling means and the crushing device by the discharged pressure oil, A left / right traveling control valve and a crushing device control valve means for guiding pressure oil from a pump to the left / right traveling hydraulic motor and the crushing device hydraulic motor, respectively; and the left / right traveling control valve and the crushing device. Operating means for switching operation control valve means, a relief valve for setting a relief pressure for limiting the maximum value of the discharge pressure of the hydraulic pump, and according to the operating state of the operating means, Serial hydraulic drive system of the self-propelled crushing machine, characterized in that a relief pressure changing means for changing the relief pressure of the relief valve. 2. A first and second hydraulic pumps provided on a self-propelled crusher having self-propelled left and right running means and a crushing device for crushing an object to be crushed, and driven by a motor. A self-propelled type equipped with a left / right traveling hydraulic motor and a crushing device hydraulic motor that respectively drive the left / right traveling means and the crushing device with pressure oil discharged from the first and second hydraulic pumps; A hydraulic drive device for the crusher, which is connected to a discharge line of the first hydraulic pump and supplies hydraulic oil from the first hydraulic pump to the left traveling hydraulic motor during a traveling operation of the self-propelled crusher. A right control hydraulic valve connected to a discharge control line of the second hydraulic pump and supplying hydraulic oil from the second hydraulic pump to the right hydraulic motor during a traveling operation of the self-propelled crusher; A control valve, The self-propelled crusher is connected to the discharge pipes of the first and second hydraulic pumps, and when the crushing operation of the self-propelled crusher is performed, the hydraulic oil from the first and second hydraulic pumps is combined and supplied to the hydraulic motor for the crushing device. Crushing device control valve means; operating means for switching between the left / right traveling control valve and crushing device control valve means; and limiting the maximum value of the discharge pressure of the first and second hydraulic pumps. A hydraulic drive device for a self-propelled crusher, comprising: a relief valve for setting a relief pressure; and a relief pressure changing means for changing the relief pressure of the relief valve according to an operation state of the operating means. . 3. The hydraulic drive system for a self-propelled crusher according to claim 1, wherein said relief pressure changing means relatively reduces said relief pressure when said crusher control valve means is operated. A hydraulic drive device for a self-propelled crusher, wherein the relief pressure is set to a relatively high value when the left and right traveling control valves are operated. 4. The hydraulic drive system for a self-propelled crusher according to claim 1, wherein the control valve means for the crusher is operated by a pilot pressure driven by a pilot pressure from the operating means. A self-propelled vehicle comprising at least one control valve for a crushing device, wherein the relief pressure changing means changes the relief pressure in accordance with a pilot pressure supplied to the control valve for the crushing device. Hydraulic drive of the crusher. 5. A left / right traveling means for self-propelling, a crushing device for crushing an object to be crushed, a hydraulic pump driven by a motor, and the left / right by hydraulic oil discharged from the hydraulic pump. A self-propelled crusher including a traveling unit and a left / right traveling hydraulic motor and a crushing device hydraulic motor that respectively drive the crushing device, wherein the hydraulic oil from the hydraulic pump is supplied to the left / right traveling hydraulic motor. A control valve for the left and right running and a control valve means for the crushing device, respectively leading to the hydraulic motor for the crushing device, and an operating means for switching the control valve for the left and right running and the control valve means for the crushing device; A relief valve for setting a relief pressure for limiting a maximum value of a discharge pressure of a pump; and a relief for changing the relief pressure of the relief valve in accordance with an operation state of the operation means. A self-propelled crusher, comprising: