JP2003343509A - Crasher, and its hydraulic circuit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic circuit of a crasher capable of smoothly performing gyrating, opening and shutting movements in a simple structure. <P>SOLUTION: The hydraulic circuit 1 is provided with an opening and closing oil pressure pipes 51 and 52 for supplying working oil to a hydraulic cylinder 37 provided for opening and closing of arms 38a and 38b of the crasher, and oil pressure pipes 53 and 55 for gyrating supplying working oil to a hydraulically-powered motor 18. A gyrating direction control means 67 comprising a pilot control valve 60 and a pilot pipes 68 and 70, and a shock pressure bypassing means 61 are arranged on a midway of the oil pressure pipes 53 and 55 for gyrating. When shocks are given to the hydraulically-powered motor 18 by smashing the crasher 2 onto a wall surface, the working oil flows through the pilot pipes 68 and 70, and a position of the pilot control valve 60 is switched. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic circuit for automatically turning a crushing arm in a crusher mounted on a self-propelled work cart by utilizing the pressure of hydraulic oil supplied to a hydraulic cylinder for opening and closing the arm. Is.

[0002]

2. Description of the Related Art Conventionally, a crusher used for demolition work of a building is often attached to a self-propelled work carriage such as a hydraulic excavator in order to improve work efficiency. Similar to the crusher 2 according to the embodiment of the present invention shown in FIG. 2, the crusher 200 generally used conventionally is roughly divided into a fixed portion 3 and a main body portion 5. Fixed part 3
Is a portion fixed to the tip side of the arm 6 such as a hydraulic excavator. The main body portion 5 includes a pair of crushing arms 38a and 38b for holding a crushing target such as a building, and the crushing arm 38.
and a hydraulic cylinder 37 for opening and closing a and 38b. Further, the main body portion 5 is rotatably supported with respect to the fixed portion 3.

In the conventional crusher 200, the main body 5 is swung by a so-called hit-and-turn method in which the main body 5 is swung by colliding it with a building or the like.
In some cases, the main body portion 5 is swung by hydraulic pressure in the same manner as the opening and closing of the crushing arms 38a and 38b.

[0004]

Since the crusher 200 of the type in which the main body 5 is rotated by turning it around has a simple structure, it can be easily installed on a hydraulic excavator or the like.
The cost required for installation is also low. However, the work of turning the main body portion 5 to the desired position by turning it around requires a certain amount of skill, and there is a problem in that the work efficiency greatly differs depending on the worker.

Further, the crusher 200 of the type in which the main body portion 5 is swung by hydraulic pressure is easier to operate than the above-described one in which the main body portion 5 is swung by turning around. However, the crusher 200 that turns the main body 5 by hydraulic pressure is used.
Has a problem that a hydraulic circuit for turning the main body 5 is required in addition to the hydraulic circuit required for opening and closing the crushing arms 38a, 38b, and the circuit configuration of the entire hydraulic circuit becomes complicated. It was Further, in this type of crusher, the turning operation of the main body 5 and the crushing arm 38a,
Since it is necessary to perform the opening / closing operation of 38b independently, there is a problem that the work efficiency is reduced accordingly.

In order to solve the above problems, it is an object of the present invention to provide a hydraulic circuit of a crusher which has a simple circuit structure and which can smoothly turn and open / close the crusher.

[0007]

Therefore, the invention according to claim 1 provided to solve the above-mentioned problems is an automatic system which is mounted on an arm of a self-propelled work carriage and which opens and closes a crushing arm with a hydraulic cylinder. In the hydraulic circuit of the rotating crusher,
A turning hydraulic actuator for turning, an opening / closing hydraulic actuator for opening / closing the arm, an opening / closing hydraulic line for supplying working oil to the opening / closing hydraulic actuator, and a branch from the opening / closing hydraulic line for turning A turning hydraulic line for supplying hydraulic oil to the hydraulic actuator; and a turning direction control means for controlling the flow of the working oil in the turning hydraulic line based on an external force acting on the turning hydraulic actuator. The hydraulic circuit of the crusher is characterized by

According to this structure, the turning direction regulating means is actuated by applying an external force to the turning hydraulic actuator, and the flow of hydraulic oil in the turning hydraulic pipe is controlled. Therefore, according to the hydraulic circuit of the present invention, the turning drive of the crusher can be accurately controlled by applying an external force to the turning hydraulic actuator.

Further, according to the above construction, it is not necessary to separately provide an independent hydraulic circuit for turning the crusher, which is required in the conventional hydraulic circuit. Therefore, according to the above configuration, the circuit configuration of the entire hydraulic circuit for opening / closing and turning the crusher can be simplified. Therefore,
According to the hydraulic circuit of the present invention, it is possible to reduce the manufacturing cost of the crusher and simplify the work of attaching and detaching the crusher to the self-propelled work cart.

According to a second aspect of the present invention, in a hydraulic circuit of a crusher which is mounted on an arm of a self-propelled work trolley and which opens and closes the crushing arm with a hydraulic actuator, a hydraulic actuator for turning and an opening and closing for opening and closing the arm. Hydraulic actuator, an opening / closing hydraulic line for supplying hydraulic oil to the opening / closing hydraulic actuator, a turning hydraulic line branched from the opening / closing hydraulic line, and a hydraulic pressure supplied to the pilot port. A hydraulic pilot type control valve, wherein the swing hydraulic line is connected to the swing hydraulic actuator via the hydraulic pilot type control valve, and the swing hydraulic actuator and the pilot of the hydraulic pilot type control valve are connected. It has a pilot line that connects the ports, and the pilot line is based on the external force that acts on the swing hydraulic actuator. In the hydraulic circuit of the crusher, which is characterized in that pressure is generated in the hydraulic oil in the pipe line and the flow of the hydraulic oil that operates the hydraulic actuator for turning is controlled by switching the hydraulic pilot type control valve by the pressure. is there.

According to this structure, the hydraulic pilot control valve can be switched by applying an external force to the turning actuator, and the operation of the turning actuator can be controlled with high accuracy.

Further, according to the above configuration, it is not necessary to separately provide an independent hydraulic circuit for turning the crusher. Therefore, according to the above configuration, the circuit configuration of the entire hydraulic circuit for opening / closing and turning the crusher can be simplified. Therefore, according to the above-described configuration, the manufacturing cost of the hydraulic circuit can be reduced, and the work of attaching / detaching the crusher to / from the self-propelled work carriage can be performed quickly.

Further, in the hydraulic circuit of the above-mentioned crusher, the hydraulic pilot type control valve is characterized in that it is possible to switch between disconnection and communication of a flow path reaching at least the turning hydraulic actuator. Is also good.
(Claim 3)

According to this structure, an external force is applied to the turning actuator to switch the hydraulic pilot control valve, so that the turning actuator can be turned or stopped accurately.

According to a fourth aspect of the present invention, the turning hydraulic actuator has two ports through which hydraulic oil flows in and out, and the hydraulic pilot type control valve causes the hydraulic oil to flow forward to the two ports. The hydraulic circuit of the crusher according to any one of claims 1 to 3, wherein the hydraulic circuit has a position and a position where hydraulic oil flows in the opposite direction.

The hydraulic pilot control valve provided in the hydraulic circuit of the present invention has a position where the hydraulic oil flows in the forward direction and a position where the hydraulic oil flows in the reverse direction. Therefore, if an external force is applied to the swing actuator and the hydraulic pilot control valve is switched, the flow direction of the hydraulic oil that flows into and out of the swing hydraulic actuator is changed, and the swing hydraulic actuator is swung in a desired direction. You can

According to a fifth aspect of the invention, the turning hydraulic actuator has two ports for the hydraulic oil to flow in and out, and the hydraulic pilot type control valve causes the hydraulic oil to flow in a forward direction to the two ports. It has a position, a position where the hydraulic oil flows in the reverse direction, and a neutral position, and it switches from the neutral position to the position where the hydraulic oil flows in the forward direction or the position where the hydraulic oil flows in the reverse direction depending on the pressure of the hydraulic oil in the pilot conduit. , Returning to the neutral position on condition that the pressure of the hydraulic oil in the pilot conduit has dropped below a certain level and the pressure of the hydraulic oil supplied to the turning hydraulic actuator has dropped below a certain level. A hydraulic circuit of the crusher according to any one of claims 2 to 4.

According to this structure, the position of the hydraulic pilot type control valve is adjusted by adjusting the pressure of the hydraulic oil in the pilot pipe and the pressure of the hydraulic oil supplied to the hydraulic actuator for turning, and the hydraulic pilot type control valve for turning is adjusted. The flow of hydraulic oil supplied to the hydraulic actuator can be accurately controlled. Therefore, according to the above configuration, the swing drive of the swing hydraulic actuator can be accurately controlled.

According to a sixth aspect of the present invention, the turning hydraulic actuator rotates in a direction in which an external force acting on the turning hydraulic actuator acts.
It is a hydraulic circuit of the crusher as described in any one of 1 to 5.

In the hydraulic circuit of the present invention, the crusher rotates in the acting direction of the external force acting on the hydraulic actuator. That is, in the hydraulic circuit of the present invention, since the acting direction of the external force acting on the hydraulic actuator and the rotating direction of the crusher are coincident with each other, the crusher can be turned intuitively and is excellent in operability. ing.

The invention according to claim 7 is characterized in that the pilot conduit is provided with a pressure control valve for adjusting the pressure of the working oil flowing in the pilot conduit. The hydraulic circuit of the crusher according to any one of 1.

According to this structure, even when an excessive external force is applied to the turning hydraulic actuator, the pressure acting on the hydraulic pilot type braking valve can be adjusted and relieved by the pressure control valve. Therefore, a larger pressure than necessary does not act on the hydraulic pilot type braking valve.
Therefore, according to the above configuration, it is possible to protect the hydraulic pilot type braking valve from excessive pressure, and prevent failure or damage to the components of the hydraulic circuit including the hydraulic pilot type braking valve.

The invention according to claim 8 is the invention according to claims 1 to 7.
A crusher comprising the hydraulic circuit according to any one of 1.

Since the crusher of the present invention comprises the hydraulic circuit according to any one of claims 1 to 7, if an external force is applied to the turning hydraulic actuator by colliding a crushing arm or the like. The crusher can be turned to a desired posture.

The crusher of the present invention comprises the hydraulic circuit according to any one of claims 1 to 7,
Unlike the conventional crusher, it is not necessary to separately provide an independent hydraulic circuit for turning drive. Therefore, the crusher of the present invention,
The circuit configuration of the hydraulic circuit that opens and closes and turns the crushing arm is extremely simple. Therefore, the crusher of the present invention,
The manufacturing cost is lower than that of the conventional crusher, and it can be easily attached to and detached from a self-propelled work cart.

[0026]

BEST MODE FOR CARRYING OUT THE INVENTION Next, an embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is a circuit diagram showing a hydraulic circuit of a crusher according to an embodiment of the present invention, and FIG. 2 is a front view showing the crusher according to an embodiment of the present invention. 3 and 4 are circuit diagrams of the throttle valve included in the hydraulic circuit shown in FIG. FIG. 5 is a circuit diagram showing a hydraulic circuit of a crusher which is another embodiment of the present invention. Figure 6
[Fig. 6] is a circuit diagram showing a hydraulic circuit of a crusher which is still another embodiment of the present invention.

In FIG. 1, reference numeral 1 is a hydraulic circuit of this embodiment. The hydraulic circuit 1 is a hydraulic circuit for driving the crusher 2 shown in FIG. The crusher 2 is a conventional crusher 2
Like 00, it is roughly composed of a fixed portion 3 and a main body portion 5.

As shown in FIG. 2, the fixed portion 3 is composed of a pair of side plates 8 and 8 and is a portion for connecting the arm 6 and the cylinder 7 such as a hydraulic excavator to the main body portion 5. The side plates 8 and 8 are supported by the arm 6 and the cylinder 7 by pins 10 and 10. Further, the hydraulic oil supply pipe 11 for supplying hydraulic oil to the hydraulic circuit 1 of the crusher 2 is
It is provided along the arm 6, and its tip side is connected to the crusher 2 side.

As shown in FIGS. 1 and 2, the main body part 5 is roughly divided into a swivel drive part 15 for swivel drive, and an open / close drive part for open / close drive of the crushing arms 38a, 38b and the crushing arms 38a, 38b which will be described later. 16 and 16. The turning drive unit 15 is a part that is continuous with the above-mentioned fixing unit 3 and that drives the main body unit 5 to turn. Turning drive unit 15
Is a horizontal plate 17 fixed vertically to the side plate 8 of the fixing portion 3, and a hydraulic motor 18 (hydraulic actuator for turning).
, A pinion 20 connected to the hydraulic motor 18, and a slewing bearing 21.

The horizontal portion 17 is fixed to the side plate 8 of the fixed portion 3 and covers the slewing bearing 21 from above. The hydraulic motor 18 is fixed to the upper side of the horizontal plate 17, and the rotation shaft 26 thereof protrudes to the lower side, that is, the slewing bearing 21 side, through a through hole 27 provided in the horizontal plate 17. The pinion 20 is connected to the tip end side of the rotating shaft 26.

As shown in FIG. 1, the slewing bearing 21 has an outer rim 30 and an inner rim 31, and a rack 32 is provided inside the inner rim 31 over the entire circumference. The pinion 20 meshes with a part of the inner rim 31 in the circumferential direction of the rack 32. Therefore, when the hydraulic motor 18 is rotationally driven, the rotational power of the rotary shaft 26 is transmitted to the inner rim 31 side via the pinion 20 and the rack 32, and the inner rim 31 is rotationally driven.

As shown in FIG. 2, the opening / closing drive section 16 has a main portion arranged below the slewing bearing 21.
The opening / closing drive unit 16 includes the side wall portion 35 and the swivel joint 3.
6. It comprises a hydraulic cylinder 37 and a crushing arm 38. The side wall portion 35 is fixed below the slewing bearing 21. Therefore, the opening / closing drive unit 16 is rotationally driven in conjunction with the inner rim 31 of the slewing bearing 21, and changes the posture of the crushing arm 38.

Further, as shown in FIG. 2, crushing arms 38a and 38b are rotatably supported on the side wall portion 35 by pins 40a and 40b. In addition, the crushing arm 38a,
A hydraulic cylinder 37 (a hydraulic actuator for opening and closing) for opening and closing the crushing arms 38a and 38b is provided on the upper end side of 38b.
Is fixed. Therefore, the crushing arms 38a, 38
b is opened and closed according to the expansion and contraction of the piston rod 37a of the hydraulic cylinder 37. More specifically, the piston rod 3
When 7a projects outward (direction of arrow A in FIGS. 1 and 2), crushing arms 38a and 38b move in a closing direction, and when piston rod 37a moves toward inside (direction of arrow B in FIGS. 1 and 2), crushing arm 38a. , 38b move in the opening direction. Hydraulic oil is supplied to the hydraulic cylinder 37 via opening / closing hydraulic pipes 51 and 52 described later. As described above, since the opening / closing drive unit 16 is rotationally driven in conjunction with the inner rim 31, the opening / closing hydraulic pipelines 51, 52 associated with this rotational drive.
A swivel joint 36 is provided on the rotary drive unit 16 in order to prevent the twisting. Swivel joint 36
Is for relaying the hydraulic lines 51, 52 for opening and closing,
It is inserted and fixed from above the horizontal plate 17.

Next, the hydraulic circuit 1 of this embodiment will be described in detail. As shown in FIG. 1, the hydraulic circuit 1 is branched from a series of opening / closing hydraulic pipelines 51 and 52 connecting the hydraulic power source 50 and the hydraulic cylinder 37, and is connected to the hydraulic motor 18 from the opening / closing hydraulic pipelines 51 and 52. Turning hydraulic lines 53, 55
Have and.

The opening / closing hydraulic pipes 51, 52 are connected to the head side port C and the rod side port R of the hydraulic cylinder 37 via swivel joints 36, respectively. The foot control valve 56 is provided in the opening and closing hydraulic lines 51 and 52.
Are connected. Further, the foot control valve 56 is connected to a hydraulic oil supply pipe 11 for supplying hydraulic oil from a hydraulic pressure source 50 and a return pipe 12 for returning the hydraulic oil circulating in the hydraulic circuit 1 to a storage tank TK. Has been done. The hydraulic oil 50 is supplied with the hydraulic oil stored in the storage tank TK. A control valve CV is provided in the middle of the hydraulic oil supply pipe 11.

The foot control valve 56 is operated by a pedal (not shown) installed in a driver's cab (not shown) of the crusher 2, and has a neutral position, a parallel position, and a cross position. Is a three-position four-way valve having three positions. More specifically, when the foot control valve 56 is in the parallel position, the hydraulic power source 5
The hydraulic fluid supplied from 0 is supplied to the port C on the head side of the hydraulic cylinder 37 via the opening / closing hydraulic pipeline 51,
The piston rod 37a of the hydraulic cylinder 37 is pushed outward (direction of arrow A in FIGS. 1 and 2). On the other hand, the foot control valve 5
When 6 is set to the cross position, the hydraulic oil supplied from the hydraulic power source 50 is supplied to the hydraulic cylinder 3 through the opening / closing hydraulic pipe 52.
7 is supplied to the rod side port R of the hydraulic cylinder 37.
Push the piston rod 37a of (3) inward (in the direction of arrow B in FIGS. 1 and 2). Further, when the foot control valve 56 is in the neutral position, the hydraulic source 50 opens and closes the hydraulic lines 51, 52 for opening and closing.
Supply of hydraulic oil to the side is shut off.

The opening / closing hydraulic lines 51, 52 are branched on the downstream side of the foot control valve 56, and turning hydraulic lines 53, 55 for supplying hydraulic oil to the hydraulic motor 18 side are provided. Swing hydraulic conduit 53 and 55 is connected to the port M _a and Port M _b of the hydraulic motor 18, respectively. A pilot control valve 60 is connected in the middle of the turning hydraulic pipes 53 and 55.

The pilot type control valve 60 has a neutral position,
3 positions having 3 positions of parallel position and cross position 4
It is a one-way valve. Further, the pilot control valve 60 has two pilot ports P _a and P _b , and is a hydraulic pilot type that can switch the valve position by applying pressure to the pilot port P _a or the pilot port P _b . It is a control valve. The pilot control valve 60 is
The pressure acting on the pilot ports P _a and P _b decreases,
Further, when the pressure of the hydraulic oil flowing through the pilot control valve 60 is lowered, the valve positions become parallel. In short, the pilot control valve 60, even if the reduced pressure acting pilot port P _a, the P _b, while the pilot control valve 60 the hydraulic oil continues to flow by way position of the valve is maintained is there. Furthermore, the pilot control valve 60 is controlled by a spring system and a position locking system in addition to the pilot system.

Pilot lines 68 and 70 are respectively connected to the pilot ports P _a and P _b of the pilot type control valve 60.
Are connected. Pilot lines 68 and 70 is a channel connecting the port M _a of the hydraulic motor 18, M _b and the pilot port P _a, and P _b, respectively. More specifically, the pilot line 68 is branched in the middle of the swing hydraulic conduit 53, a conduit leading to the pilot port P _a pilot control valve 60. Similarly, the pilot line 70 is a line that is branched in the middle of the turning hydraulic line 55 and is connected to the pilot port P _b of the pilot control valve 60. Pilot lines 68 and 70, the port M _a of the hydraulic motor 18 through the hydraulic oil flowing respective internal pilot port impact pressure acting on M _b P _a,
It is transmitted to P _b .

The pilot conduits 68 and 70, together with the pilot control valve 60 described above, constitute a turning direction control means 67. The turning direction control means 67 turns the crusher 2 in a predetermined direction by controlling the flow of hydraulic oil flowing through the turning hydraulic pipelines 53 and 55. More specifically, turning direction control means 67, the hydraulic motor 18 ports M _a, pilot impact pressure acting on M _b port P
Pilot control valve 6 by propagating to _a and P _b
By switching 0, the flow of the hydraulic oil flowing through the turning hydraulic pipelines 53 and 55 is controlled to control the turning drive of the crusher 2.

A check valve 54 is provided in the middle of the turning hydraulic line 53 and upstream of the pilot control valve 60, whereby the turning hydraulic line 51 is opened from the opening / closing hydraulic line 51 side. The flow of hydraulic oil to the 53 side is shut off. Further, a throttle valve 57 is provided on the upstream side of the pilot control valve 60 in the middle of the turning hydraulic pipe 55.
The throttle valve 57 is a circuit component having both a function of blocking passage of the hydraulic oil when the supply pressure of the hydraulic oil is equal to or lower than a predetermined pressure and a function of limiting the flow rate of the hydraulic oil. The throttle valve 57 has an adjustable throttle valve 58 as shown in FIG.
And an adjustable relief valve 59 are connected in series, or an adjustable throttle valve 58 and a check valve 64 capable of adjusting the cracking pressure are connected in series as shown in FIG. .

From the pilot type control valve 60 to the hydraulic motor 1
An impact pressure bypass means 61 is provided in the middle of the pipeline reaching 8. Impact pressure bypass means 61 is connected to the swing hydraulic conduit 53 that connects the port M _a of the hydraulic motor 18 from the pilot control valve 60, a port M _b of the hydraulic motor 18 from the pilot control valve 60 turning The hydraulic hydraulic line 55 is bypassed by the two bypass lines 62 and 63. A relief valve 65 from the turning hydraulic line 53 to the turning hydraulic line 55 is interposed in the bypass line 62. In addition, a relief valve 66 from the turning hydraulic line 55 to the turning hydraulic line 53 is provided in the bypass line 63.
Is intervening. Impact pressure bypass means 61 can escape excessive impact pressure acting on the port M _a or port M _b of the hydraulic motor 18 in the opposite port by the relief valve 65, 66. Therefore, according to the impact pressure bypass unit 61, the port M _a of the hydraulic motor 18, M _b and the pilot port P _a pilot control valve 60, P
_{It is possible} to prevent the action of excessive impact pressure on _b .

Next, the operation of the crusher 2 provided with the hydraulic circuit 1 will be described based on the operation method of the crusher 2. When the pedal in the driver's cab is operated to switch the foot control valve 56 from the neutral position to the parallel position, the hydraulic oil supplied from the hydraulic power source 50 flows through the opening / closing hydraulic pipe line 51 and the swivel joint 36. Is supplied from the port C into the hydraulic cylinder 37. The hydraulic oil supplied into the hydraulic cylinder 37 pushes the piston rod 37a toward the port R, and the end portion of the crushing arm 38b moves in the direction indicated by arrow A in FIGS. The crushing arm 38b has a pin 4
Rotating around 0b, the crushing arms 38a, 38b start to close.

When the crushing arms 38a, 38b start to close, the hydraulic oil stored on the port R side of the hydraulic cylinder 37 begins to flow into the opening / closing hydraulic pipe line 52. The hydraulic oil flowing in the opening / closing hydraulic pipe 52 flows to the foot control valve 56 side via the swivel joint 36, flows through the return pipe 12, and is returned to the storage tank TK.

On the other hand, when the pedal in the driver's cab is adjusted and the foot control valve 56 is switched to the cross side, the hydraulic oil supplied from the hydraulic power source 50 flows in the opening / closing hydraulic pipe line 52 and the swivel joint 36. It is supplied from the port R into the hydraulic cylinder 37 via. The hydraulic oil supplied from the port R pushes the piston rod 37a toward the port C side.
When the piston rod 37a moves into the hydraulic cylinder 37, the end portion of the crushing arm 38b is pushed and moved in the direction indicated by the arrow B in FIGS. 1 and 2, rotating about the pin 40b, and the crushing arms 38a and 38b are moved. Start opening.

When the crushing arms 38a, 38b start to open, the hydraulic oil stored on the port C side of the hydraulic cylinder 37 begins to flow into the opening / closing hydraulic pipe line 51. The hydraulic oil flowing in the opening / closing hydraulic pipeline 51 is swivel joint 36.
Flow toward the foot control valve 56 side through the return pipe 12 and return to the storage tank TK. Here, if the hydraulic oil is continuously supplied to the port R side of the hydraulic cylinder 37 while the crushing arms 38a and 38b are fully opened, the supply pressure of the hydraulic oil supplied to the opening / closing hydraulic pipeline 52 gradually rises. However, the pressure acting on the throttle valve 57 provided in the turning hydraulic pipe line 55 also rises. When the pressure acting on the throttle valve 57 reaches or exceeds a predetermined pressure, the adjustable relief valve 59 of the throttle valve 57 or the check valve 64 capable of adjusting the cracking pressure is opened, and the hydraulic oil flows to the pilot type control valve 60 side. .

When the pilot type control valve 60 is in the neutral position, the flow of hydraulic oil is blocked in the pilot type control valve 60, and the hydraulic motor 18 is not supplied with hydraulic oil. Therefore, when the pilot control valve 60 is in the neutral position, the hydraulic motor 18 does not rotate and the crusher 2 maintains a constant posture.

On the other hand, when the crushing arms 38a and 38b are fully opened and the pressure acting on the throttle valve 57 is equal to or higher than a predetermined pressure, when the crusher 2 is lightly collided with the wall surface or the like, the port M of the hydraulic motor 18 is made. _a or port M _b
Impact pressure is applied to. For example, the crusher 2 is allowed to act the impact pressure to port M _a by collisions, hydraulic oil hydraulic motor 18 of the pilot line 68 by the impact pressure
It flows from port M _a side pilot port P _a pilot control valve 60. Pilot control valve 60
The position of the valve by the pressure of the working oil that flows into the pilot port P _a side is switched to the parallel position from the neutral position. In the hydraulic circuit 1 of the present embodiment, the hydraulic motor 1
There is provided an impact pressure bypass means 61 for releasing an excessive impact pressure acting on one port of No. 8 to the other port.
Therefore, in the hydraulic circuit 1 of the present embodiment, even if the crusher 2 is made to collide more than necessary and an overload is applied,
The overload is absorbed and eliminated by the impact pressure bypass means 61.

When the pilot type control valve 60 is switched to the parallel position, the opening / closing hydraulic line 52 is turned to the turning hydraulic line 55.
The hydraulic oil that has flowed in and has been supplied up to immediately before the pilot type control valve 60 flows from the port M _b side of the hydraulic motor 18 beyond the pilot type control valve 60. At the same time, hydraulic fluid flows from port M _a of the hydraulic motor 18, flows to the opening and closing hydraulic conduit 51 side via the swing hydraulic conduit 53. That is, the flow of hydraulic oil into and out of the hydraulic motor 18 is started, and the hydraulic oil begins to circulate in the turning hydraulic pipe lines 53 and 55.

When the hydraulic oil flows in from the port M _b side and the hydraulic oil begins to circulate in the turning hydraulic pipe lines 53 and 55, the rotary shaft 26 of the hydraulic motor 18 starts to rotate (forward rotation).
The rotary power of the rotary shaft 26 is generated by the pinion 20 and the rack 3.
2 is transmitted to the slewing bearing 21 side, and the inner rim 31 of the slewing bearing 21 starts to rotate. When the inner rim 31 rotates, the crushing arms 38a,
The side wall portion 35 that supports 38b also rotates forward, and the main body portion 5
The attitude of is changed.

When the main body 5 turns and the crusher 2 takes a desired posture, the pedal in the operator's cab is operated to set the foot control valve 56 to the neutral position, and the turning hydraulic pipelines 53, 55 are provided. The flow of hydraulic oil inside stops and the pressure drops. Along with this, the pressure of the working oil in the pilot conduit 68, 70 is also lowered, the pressure acting on the pilot port P _a decrease.
Therefore, the valve position of the pilot control valve 60 is switched from the parallel position to the neutral position, and the turning hydraulic pipeline 53,
Inflow and outflow of hydraulic oil via 55 is blocked. Along with this, the rotation of the hydraulic motor 18 is stopped and the posture of the crusher 2 is fixed.

On the other hand, contrary to the case of rotating the crusher 2 in the forward direction, the main body 5 can be rotated in the reverse direction by applying an impact pressure to the port M _b of the hydraulic motor 18. More specifically, when the main body 5 of the crusher 2 is collided with a wall surface or the like and an impact pressure is applied to the port M _b , the hydraulic oil in the pilot conduit 70 is directed to the pilot port P _b of the pilot control valve 60. Flow, switching the pilot control valve 60 from the neutral position to the cross position. Also in this case, of the impact pressures acting on the hydraulic motor 18, an excessive impact pressure exceeding the impact pressure required for changing the position of the pilot control valve 60 is leaked in the impact pressure bypass means 61.

When the pilot type control valve 60 is in the cross position, the hydraulic oil flowing in the turning hydraulic line 55 on the upstream side of the pilot type control valve 60 exceeds the pilot type control valve 60 and turns. Flowing along the pipeline 53 side,
It flows to the port M _a side of the hydraulic motor 18. Port M _a
When the hydraulic oil flows into the hydraulic motor 18, circulation of the hydraulic oil in the hydraulic motor 18 starts, and the rotary shaft 26 of the hydraulic motor 18 starts reverse rotation. With the reverse rotation of the rotary shaft 26, the crushing arm 3
The side wall portion 35 supporting 8a and 38b also rotates in the reverse direction, and the posture of the main body portion 5 can be changed.

In the hydraulic circuit 1 of the present embodiment, the pilot type control valve 60 constituting the turning direction control means 67.
Has a function of returning the valve position to the parallel position when the pressure of the hydraulic oil in the pilot pipes 68, 70 drops below a certain level and the pressure of the hydraulic oil supplied to the hydraulic motor 18 also falls below a certain level. Was there. On the other hand, in the hydraulic circuit 1, when the foot control valve 56 is set to the neutral position by the pedal operation in the driver's cab, the pressure of the hydraulic oil in the pilot lines 68 and 70 drops below a certain level, and the hydraulic motor 18 is further operated. The pressure of the hydraulic oil supplied is also below a certain level. Therefore, the hydraulic circuit 1 of the present embodiment can easily and accurately stop the crusher 2 that is being driven to rotate by operating the foot control valve 56.

In this embodiment, the pilot-type control valve 60 has a parallel position and a cross position, which connect the turning hydraulic pipelines 53 and 55, and the hydraulic oil flowing to the hydraulic motor 18 is selected by selecting both of them. The flow direction of can be changed. Therefore, according to the hydraulic circuit 1 of the present embodiment, the crusher 2 can be turned in any direction.

As described above, the pilot type control valve 60
Was a control valve having both a spring system and a control system based on a position stop system in addition to the pilot system, but the present invention is not limited to this. For example, a combination of a pilot system and a spring system, or a pilot system A combination of the system and the position fixing system may be used. Further, the pilot control valve 60 described above has three positions of the neutral position, the parallel position, and the cross position, but for example, a four-way valve having two positions of communication and closing, a two-position two-way valve, etc. May be

Further, in the above embodiment, the pedal control valve 56 is set to the neutral position by the pedal operation in the driver's cab to switch the pilot control valve 60 to the neutral position, and the turning of the crusher 2 is stopped. Illustrated. However, in the above-described embodiment, the crusher 2 which is driven to rotate is collided with the wall surface or the like to apply a load to the rotation of the hydraulic motor 18 to switch the pilot control valve 60 to the neutral position. You can More specifically, for example, when applying a load to the crusher 2, which rotates forward by, for example, colliding body portion 5 to the wall or the like, the impact pressure is applied to the port M _a. As a result, the pilot pipeline 7
The hydraulic fluid in 0 flows from the port M _b side of the hydraulic motor 18 toward the pilot port P _b side of the pilot control valve 60. The pilot type control valve 60 is switched from the parallel position to the neutral position by the hydraulic oil flowing from the pilot port P _b side, and the turning of the crusher 2 is stopped. On the contrary, in the same manner as described above, by applying a load to the crusher 2 rotating in the reverse direction, the pilot control valve 60 can be set to the neutral position, and the turning of the crusher 2 can be stopped. . That is, by applying a load to the crusher 2 during turning, the pilot control valve 60 can be switched from the parallel position or the cross position to the neutral position, and the turning of the crusher 2 can be stopped.

In the hydraulic circuit 1 of the above embodiment, the impact pressure bypass means 61 is provided with relief valves 65 and 66 in bypass pipe lines 62 and 63 that bypass the turning hydraulic pipe line 53 and the turning hydraulic pipe line 55, respectively. It is equipped with. Therefore, even when an excessive impact pressure generates a crusher 2 upon colliding with the wall surface or the like, the port M _a of the hydraulic motor 18, M _b and the pilot port P _a pilot control valve 60, excessive in P _b Since no impact pressure is applied, the hydraulic motor 18 and the pilot control valve 60 can be prevented from malfunctioning.

In the above embodiment, the bypass line 6
Although the hydraulic circuit 1 provided with the impact pressure bypass means 61 in which the relief valves 65 and 66 are provided in the reference numerals 2 and 63 has been illustrated, the hydraulic circuit of the present invention is not limited to this, and for example, FIG.
It is also possible to adopt the configuration shown in. The hydraulic circuit 80 shown in FIG. 5 is almost the same as the hydraulic circuit 1 described above, except that the shock pressure bypass means 61 is provided in place of the shock pressure bypass means 61 included in the hydraulic circuit 1.

[0060] impact pressure bypass means 81, the swing hydraulic conduit 53 that connects the port M _a of the hydraulic motor 18 from the pilot control valve 60, a port M _b of the hydraulic motor 18 from the pilot control valve 60 The turning hydraulic pipeline 55 to be connected is bypassed by two pipelines, bypass pipelines 82 and 83. Further, a communication pipe 90 that bypasses the bypass pipes 82 and 83 is provided between the bypass pipes 82 and 83.

The bypass conduit 82 is provided with check valves 85 and 86 so that the flow directions of the hydraulic oil are opposite to each other, and the turning hydraulic conduit to which the bypass conduit 82 is connected. The hydraulic oil flowing in 53 and 55 can be introduced into the bypass line 82. Also, bypass line 8
3 is provided with check valves 87 and 88 so that the flow directions of the hydraulic oil are opposite to each other, and hydraulic oil for swirling the hydraulic oil between the check valves 87 and 88 is provided. Road 53,55
Can drain to the side. The communication conduit 90 communicates with the bypass conduits 82 and 83, and an adjustable relief valve 91 is provided in the middle thereof.

[0062] In the hydraulic circuit 80 of the present embodiment, when the excessive impact pressure to port M _a or M _b of the hydraulic motor 18 is applied, the port M _a or hydraulic oil flows out from the port M _b, impact pressure bypass means 81 Through to the port opposite to the above, and the impact pressure is absorbed and eliminated. More specifically, the hydraulic oil excessive impact pressure exits the ports M _a of the hydraulic motor 18 acts, flows into the bypass line 82 flows through the swing hydraulic conduit 53. The hydraulic oil flowing through the bypass conduit 82 flows into the bypass conduit 83 via the communication conduit 90. The hydraulic oil that has flowed into the bypass line 83 flows out to the port M _b side of the hydraulic motor 18. Similarly, the hydraulic oil exiting the port M _b of the hydraulic motor 18 due to the action of the excessive impact pressure flows through the turning hydraulic pipe line 55 and the bypass pipe line 82.
It flows into and out the port M _a side of the hydraulic motor 18 flows through the communication duct 90 and bypass line 83.

The above-mentioned hydraulic circuits 1 and 80 are provided for the port M of the hydraulic motor 18 by colliding the crusher 2 against a wall surface or the like.
By applying an impact pressure to _a and M _b , the position of the pilot-type control valve 60 can be switched to control the flow of hydraulic oil flowing in and out of the hydraulic motor 18. for that reason,
In the hydraulic circuits 1 and 80, the swinging drive of the crusher 2 can be accurately adjusted by causing the crusher 2 to collide with a wall surface or the like to exert an impact pressure on the hydraulic motor 18.

In the above-mentioned hydraulic circuits 1 and 80, the constitution provided with the impact pressure bypass means 61 and 81 in order to eliminate the excessively large external force acting on the hydraulic motor 18 is illustrated, but the present invention is not limited to this. The configuration is not limited to this, and may be, for example, the configuration shown in FIG. The hydraulic circuit 100 shown in FIG. 6 has substantially the same structure as the hydraulic circuit 1 described above, but the pressure reducing valve 1 is provided in the middle of the pilot lines 68 and 70.
The difference is that 01 and 102 (pressure control valves) are provided.
The pressure reducing valves 101 and 102 both reduce the primary pressure acting on the hydraulic oil in the pilot lines 68 and 70 on the hydraulic motor 18 side, and the pressures below a predetermined pressure are applied to the pilot ports P _a and P _b of the pilot control valve 60. The secondary pressure is applied.

The pressure reducing valve 101 is connected to the opening / closing hydraulic line 52 via the return line 103. Return line 103
A check valve 106 is provided midway along the line to prevent backflow of hydraulic oil from the opening / closing hydraulic pipeline 52 side to the pressure reducing valve 101 side. In addition, the return pipe 103 is branched upstream of the check valve 106, and the hydraulic line 5 for opening and closing is provided.
A return pipe line 105 that connects to 1 is formed. A check valve 107 is provided in the middle of the return pipe 105 to prevent backflow of the hydraulic oil from the opening / closing hydraulic pipe 51 side. Excessive pressure acting on the pressure reducing valve 101 is returned to the opening / closing hydraulic pipeline 51 or 52 through the return pipelines 103 and 105.

Like the pressure reducing valve 101, the pressure reducing valve 102 is connected to the opening / closing hydraulic pressure lines 51 and 52 via the return pipes 108 and 110, respectively. The return conduit 110 is branched in the middle of the return conduit 108. Check valves 111 and 1 are provided in the middle of the return lines 108 and 110, respectively.
12 is provided to prevent backflow of hydraulic oil from the opening / closing hydraulic pipelines 51, 52. The excess pressure acting on the pressure reducing valve 102 is returned to the opening / closing hydraulic pipeline 51 or 52 side through the hydraulic oil flowing in the return pipelines 108 and 110.

In the hydraulic circuit 100 described above, in addition to the impact pressure bypass means 61 provided in the hydraulic circuit 1, the pressure reducing valves 101 and 102 are provided in the pilot conduits 68 and 70 connected to the pilot type control valve 60. _a ,
No pressure above P _b acts on P _b . Therefore, according to the hydraulic circuit 100, even if an excessively large pressure acts on the hydraulic motor 18 due to an operator's operation error or the like, excessive pressure acts on the pilot ports P _a and P _b. Therefore, the failure of the pilot type braking valve 60 can be reliably prevented. Therefore, if the hydraulic circuit 100 is adopted, it is not necessary to consider the magnitude of the impact applied to the hydraulic motor 18 so much, and even if the crusher 2 is operated somewhat disorderly, the pilot type braking valve 60 or the like may fail. Absent.

The hydraulic circuit 100 described above includes the pressure reducing valve 10
1, 102 and the impact pressure bypass means 61 are both provided, but the impact pressure bypass means 61 may be replaced by the impact pressure bypass means 81. Further, the hydraulic circuit 100 includes the impact pressure bypass means 6
It is also possible to provide the pressure reducing valves 101 and 102 without providing the first and 81.

Further, the hydraulic circuit 100 described above is provided with the pressure reducing valves 101 and 102, but the present invention is not limited to this, and one or both of the pressure reducing valves 101 and 102 may be provided. Instead, an appropriate pressure control valve such as a relief valve or a safety valve may be used.

The hydraulic circuits 1, 80, 100 described above are integrated with a hydraulic circuit for opening and closing the crusher 2 and a hydraulic circuit for turning the crusher 2.
Can be operated only by the foot control valve 56. Therefore, compared with the conventional hydraulic circuit, which is provided with an independent hydraulic circuit for turning the crusher for opening and closing the crusher,
The hydraulic circuit has a simple circuit configuration, and the crusher 2 can be easily operated. Also, the hydraulic circuits 1, 80, 100 are
Since the circuit configuration is simple, it is possible to reduce the manufacturing cost of the crusher 2 as a whole and simplify the work of attaching and detaching the self-propelled work carriage such as a hydraulic excavator.

Further, the above hydraulic circuits 1, 80, 100
The hydraulic oil is supplied when the external force to act on the port M _a side of the hydraulic motor 18 to the port M _a side, the rotary shaft 26 of the hydraulic motor 18 rotates forward. Conversely, when an external force is applied to the port M _b side of the hydraulic motor 18, the rotary shaft 26 of the hydraulic motor 18 rotates in the reverse direction. That is, the hydraulic circuits 1, 80, 1
In 00, since the crusher 2 is driven to rotate in the same direction as the acting direction of the external force acting on the hydraulic actuator,
The crusher 2 can be rotated intuitively, and workability is high.

[0072]

According to the hydraulic circuit of the present invention, the turning drive of the crusher can be accurately controlled by applying an external force to the turning hydraulic actuator. Further, according to the present invention, since the opening and closing drive and the turning drive of the crusher can be performed by a single hydraulic circuit, the circuit configuration of the hydraulic circuit of the crusher can be simplified.

Since the hydraulic circuit of the crusher of the present invention has a simpler circuit structure than the conventional hydraulic circuit, the crusher can be easily attached and detached, and the cost for forming the hydraulic circuit can be reduced. it can.

Further, since the crusher of the present invention is provided with the above-mentioned hydraulic circuit, the crusher is swung to a desired posture by applying an external force to the turning hydraulic actuator by colliding the crushing arm or the like. Can be made.

The crusher of the present invention is equipped with the above-mentioned hydraulic circuit, and the circuit configuration of the hydraulic circuit for opening / closing and turning the crushing arm is extremely simple. Therefore, the crusher of the present invention has a low manufacturing cost and can be easily attached and detached.

[Brief description of drawings]

FIG. 1 is a circuit diagram showing a hydraulic circuit of a crusher according to an embodiment of the present invention.

FIG. 2 is a front view showing a crusher according to an embodiment of the present invention.

FIG. 3 is a circuit diagram of a throttle valve included in the hydraulic circuit shown in FIG.

FIG. 4 is a circuit diagram of a throttle valve included in the hydraulic circuit shown in FIG.

FIG. 5 is a circuit diagram showing a hydraulic circuit of a crusher which is another embodiment of the present invention.

FIG. 6 is a circuit diagram showing a hydraulic circuit of a crusher according to still another embodiment of the present invention.

[Explanation of symbols]

1,80,100 hydraulic circuit 2 crusher 6 arms 18 Hydraulic motor 37 hydraulic cylinder 38 Crushing arm 51,52 hydraulic line for opening and closing 53,55 Turning hydraulic line 60 Pilot type control valve 61,81 Impact pressure bypass means 62,63,82,83 Bypass line 65,66 relief valve 67 Turning direction control means 68,70 Pilot line 85,86,87,88 Check valve 90 communication lines 91 Adjustable relief valve 101,102 Pressure reducing valve

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[Procedure amendment]

[Submission date] May 30, 2002 (2002.5.3)
0)

[Procedure Amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0042

[Correction method] Change

[Correction content]

From the pilot type control valve 60 to the hydraulic motor 1
An impact pressure bypass means 61 is provided in the middle of the pipeline reaching 8. Impact pressure bypass means 61 is connected to the swing hydraulic conduit 53 that connects the port M _a of the hydraulic motor 18 from the pilot control valve 60, a port M _b of the hydraulic motor 18 from the pilot control valve 60 turning The hydraulic hydraulic line 55 is bypassed by the two bypass lines 62 and 63. A relief valve 66 from the turning hydraulic line 53 to the turning hydraulic line 55 is interposed in the bypass line 62. Further, in the bypass line 63, a relief valve 65 from the turning hydraulic line 55 to the turning hydraulic line 53.
Is intervening. Impact pressure bypass means 61 can escape excessive impact pressure acting on the port M _a or port M _b of the hydraulic motor 18 in the opposite port by the relief valve 65, 66. Therefore, according to the impact pressure bypass unit 61, the port M _a of the hydraulic motor 18, M _b and the pilot port P _a pilot control valve 60, P
_{It is possible} to prevent the action of excessive impact pressure on _b .

   ─────────────────────────────────────────────────── ─── Continued front page    F-term (reference) 2E176 AA01 DD06                 3H089 AA60 AA70 AA73 AA80 CC01                       CC08 CC13 DB03 DB04 DB13                       DB33 DB46 DB49 DB54 EE23                       GG02 JJ02

Claims (8)

[Claims] 1. In a hydraulic circuit of a crusher which is mounted on an arm of a self-propelled work cart and which opens and closes a crushing arm by a hydraulic actuator, a swing hydraulic actuator, an opening and closing hydraulic actuator for opening and closing the arm, and the opening and closing. A hydraulic line for opening and closing for supplying hydraulic oil to the hydraulic actuator for use, and a hydraulic line for swinging branched from the hydraulic line for opening and closing to supply hydraulic oil to the hydraulic actuator for turning.
A hydraulic circuit for a crusher, comprising: a turning direction control means for controlling a flow of hydraulic oil for operating the turning hydraulic actuator based on an external force acting on the turning hydraulic actuator. 2. In a hydraulic circuit of a crusher which is mounted on an arm of a self-propelled work cart and which opens and closes a crushing arm by a hydraulic actuator, a turning hydraulic actuator, an opening and closing hydraulic actuator for opening and closing the arm, and the opening and closing. It has a hydraulic line for opening and closing that supplies hydraulic oil to the hydraulic actuator, a hydraulic line for turning that branches from the hydraulic line for opening and closing, and a hydraulic pilot control valve that is switched by the hydraulic pressure supplied to the pilot port. The swing hydraulic line is connected to the swing hydraulic actuator via the hydraulic pilot control valve, and the pilot hydraulic line further connects the swing hydraulic actuator and the pilot port of the hydraulic pilot control valve. The hydraulic oil in the pilot line is compressed based on the external force that acts on the turning hydraulic actuator. A hydraulic circuit of a crusher, wherein force is generated and a hydraulic pilot type control valve is switched by the pressure to control a flow of hydraulic oil for operating a hydraulic actuator for turning. 3. The hydraulic circuit for a crusher according to claim 2, wherein the hydraulic pilot control valve is capable of switching between disconnection and communication of a flow path reaching at least the turning hydraulic actuator. 4. The turning hydraulic actuator has two ports for the hydraulic oil to flow in and out, and the hydraulic pilot control valve has a position where the hydraulic oil flows in the forward direction and a reverse direction for the two ports. The hydraulic circuit of the crusher according to any one of claims 1 to 3, wherein the hydraulic circuit has a position for flowing oil. 5. The turning hydraulic actuator has two ports for the hydraulic oil to flow in and out, and the hydraulic pilot control valve has a position where the hydraulic oil flows in a forward direction and a reverse direction in which the hydraulic oil flows. An oil flow position and a neutral position are provided, and the pressure in the pilot line causes the hydraulic oil to switch from the neutral position to a position where the hydraulic oil flows in the forward direction or a position where the hydraulic oil flows in the reverse direction, and the operation inside the pilot line 5. The neutral position is restored on condition that the pressure of the oil has dropped below a certain level and the pressure of the hydraulic oil supplied to the swing hydraulic actuator has dropped below a certain level.
The hydraulic circuit of the crusher according to any one of 1. 6. The hydraulic circuit for a crusher according to claim 1, wherein the turning hydraulic actuator rotates in a direction in which an external force acting on the turning hydraulic actuator is applied. 7. The crushing device according to claim 2, wherein the pilot pipe line is provided with a pressure control valve for adjusting the pressure of the hydraulic oil flowing in the pilot pipe line. Hydraulic circuit of the machine. 8. A crusher comprising the hydraulic circuit according to any one of claims 1 to 7.