JP2005305360A - Hydraulic system in self-traveling crusher - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent main working devices and auxiliary working devices from being influenced by large load on a crushing device and to prevent working efficiency of the main working devices from falling even when load on any working device increases, in a self-traveling crusher which is provided with the crushing device, main working devices such as a feeding device and a carrying out device mounted in advance on a machine body and auxiliary working devices such as an externally attached optional device. <P>SOLUTION: While providing a first hydraulic pump 12 used as a pressurized oil supply source of a hydraulic motor 22 for the crushing device and a second hydraulic pump 13 used as a pressurized oil supply source of hydraulic motors 23 to 26 for main working devices and hydraulic motors 27 to 29 for auxiliary working devices, pressurized oil of the second hydraulic pump 13 is preferentially supplied to the hydraulic motors 23 to 26 for main working devices via a priority valve 59. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention belongs to the technical field of a hydraulic system in a self-propelled crusher equipped with a crushing device such as a jaw crusher.

In recent years, there is an increasing demand for self-propelled crushers equipped with a crushing device on a vehicle body equipped with a traveling body as a machine for finely crushing massive objects such as concrete generated at the site of building demolition etc. However, in such a self-propelled crusher, not only the crushing device, but also a feeder such as a feeder that supplies the crushing material to the crushing device, and a crushing material processed by the crushing device are carried out from the crushing device. Various work devices for carrying out work related to crushing work, such as carry-out devices such as conveyors, are mounted. These crushing devices and working devices are usually configured to be driven by a hydraulic actuator such as a hydraulic motor to which pressure oil is supplied from a hydraulic pump mounted on a self-propelled crusher.
By the way, the hydraulic actuator for the crushing apparatus has a larger load and the fluctuation is larger than the hydraulic actuator for the working apparatus. For this reason, if the hydraulic supply source is shared by the crushing device hydraulic actuator and the working device hydraulic actuator, the amount of pressure oil supplied to the working device hydraulic actuator is not stable due to the large load fluctuation of the crushing device hydraulic actuator. There's a problem.

Therefore, a first hydraulic pump that serves as a hydraulic supply source for the crushing device hydraulic actuator and a second hydraulic pump that serves as a hydraulic supply source for the working device hydraulic actuator are provided to reduce the influence of load fluctuations on the crushing device hydraulic actuator. A technique has been proposed in which a hydraulic actuator for a working device is difficult to receive (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 11-226444

  By the way, in the self-propelled crusher, not only the main work device such as the supply device and the carry-out device described above but also an external optional device such as an additional conveyor can be detachably attached as an auxiliary work device. There is what I did. In this configuration, when the hydraulic pump is separately provided for the crushing device hydraulic actuator and the working device hydraulic actuator as in Patent Document 1, the second hydraulic pump supplies pressure oil to the main working device and the auxiliary working device. Therefore, if these main work equipment and auxiliary work equipment are operated simultaneously, the supply flow rate of the second hydraulic pump will be in a state where there is no margin (the second hydraulic pump will be enlarged in order to make allowance for the supply flow rate) However, increasing the size of the pump hinders energy saving and cost reduction.) In such a state, if the load on one of the working devices increases and the pump flow rate decreases, there is a risk that the supply flow rate of the second pump will be insufficient. If there is a shortage of pressure oil supply to the main work device that performs the main work, such as a supply device to supply and a carry-out device to carry out the crushed material from the crushing device, there is a problem that the work efficiency is greatly reduced, There has been a problem to be solved by the present invention.

The present invention has been made in order to solve these problems in view of the above circumstances, and the invention of claim 1 provides a crushing device and a material to be crushed to the crushing device. A self-propelled crusher comprising a main work device such as a carry-out device for carrying out a crushed material from a supply device or a crushing device, and an auxiliary work device such as a detachable external optional device. In forming a hydraulic system for supplying hydraulic oil for operation to hydraulic actuators for the crushing device, the main working device, and the auxiliary working device for driving the working device and the auxiliary working device, the crushing device is provided in the hydraulic system. A first hydraulic pump that serves as a pressure oil supply source for the hydraulic actuator for the engine and a second hydraulic pump that serves as a pressure oil supply source for the hydraulic actuator for the main working device and the hydraulic actuator for the auxiliary device. Rutotomoni, pressure oil of the second hydraulic pump is characterized in that it has configured to be preferentially supplied to the main working device hydraulic actuator through a priority valve.
In this way, even if there is a large load fluctuation in the crushing device, the main work device and the auxiliary work device are not affected by the large load fluctuation of the hydraulic actuator for the crushing device, and stable pressure oil supply is possible. In addition, even when the supply flow rate of the second hydraulic pump serving as the pressure oil supply source of the hydraulic actuator for the main working device and the auxiliary working device is lowered, the pressure oil of the second hydraulic pump is Since it is preferentially supplied to the main work device, the work efficiency of the main work device is not reduced. Thus, the supply of the material to be crushed to the crushing device, the removal of the crushed material from the crushing device, etc. It is possible to avoid a problem that the main work is delayed and the work efficiency is greatly reduced.
According to a second aspect of the present invention, in the first aspect, the control valves for performing pressure oil supply / discharge control on the hydraulic actuator for the main working device and the hydraulic actuator for the auxiliary working device are the multiple control valve unit for the main working device, the auxiliary Each of the multiple control valve units for the work device is incorporated into the multiple control valve unit for the work device, and the multiple control valve unit for the main work device and the multiple control valve unit for the auxiliary work device are arranged downstream of the priority valve. Is.
And by doing in this way, the control valve for small flow rates corresponding to the hydraulic actuator for the main working device and the hydraulic actuator for the auxiliary working device is changed to the multiple control valve unit for the main working device and the multiple control for the auxiliary working device. It can be incorporated as a valve unit, and thus it is possible to perform highly accurate flow control to the main working device hydraulic actuator and the auxiliary working device hydraulic actuator.

  Next, embodiments of the present invention will be described with reference to the drawings. In FIG. 1, reference numeral 1 denotes a self-propelled crusher. The self-propelled crusher 1 is provided from a jaw crusher or the like at a substantially central portion in the front-rear direction of a machine body including crawler-type left and right traveling bodies 2 and 3. A crushing device 4 is placed. A hopper 5 into which a material to be crushed, such as a concrete lump, is placed is arranged at the upper rear side of the crushing device 4, and a material to be crushed in the hopper 5 is disposed below the hopper 5 in the crushing device 4. A vibration feeder 6 for introduction into the inlet 4a is arranged. The vibration feeder 6 is a so-called grizzly feeder, has a sawtooth plate 6a on the front half side of the bottom surface portion, and sequentially conveys the objects to be crushed put into the hopper 5 to the crushing device 4 side. At the same time, a small concrete lump, earth and sand, etc. that do not need to be crushed are dropped downward from the gap between the sawtooth plates 6a. And the fallen object is configured to be carried out to the left and right outside of the self-propelled crusher 1 by a side conveyor 7 arranged in a state of projecting left and right from the front half side of the vibration feeder 6. ing.

  On the other hand, a control unit 8, a fuel tank 9, an oil tank 10 and the like are arranged in front of the crushing device 4, and further, an engine 11 and first and second hydraulic pumps 12 and 13 to be described later are stored in front of the crushing device 4. A power chamber 14 is arranged. Moreover, the main conveyor 15 for carrying out the crushing processed material crushed by the crushing device 4 from the crushing device 4 to the outside of the machine reaches from the lower side of the crushing device 4 to the lower side of the power chamber 14, and further toward the upper front of the machine body. It is arranged in a protruding state. Further, 16 is a magnetic separator disposed above the middle part of the main conveyor 15, and the magnetic separator 16 magnetically attaches a metal material such as a reinforcing bar contained in the concrete block with a magnet and releases it to the outside. It is configured.

Further, the self-propelled crusher 1 is provided as an optional external device with a vibrating screen 17 that is arranged below the conveyance end of the main conveyor 15 and sieves the crushed material conveyed by the main conveyor 15, the vibration A secondary conveyor 18 and a tertiary conveyor 19 for conveying the crushed material falling from the screen 17 to a further distance can be detachably mounted.
In the present embodiment, the vibration feeder 6, the side conveyor 7, the main conveyor 15, and the magnetic separator 16 correspond to the main working device of the present invention, and the vibration screen 17, the secondary conveyor 18, and the tertiary conveyor 19 are the present invention. Of course, the main working device and the auxiliary working device are not limited to these.

  扨, left and right traveling bodies 2, 3, crushing device 4, vibration feeder 6, side conveyor 7, main conveyor 15, magnetic separator 16, vibration screen 17, secondary conveyor 18, and tertiary conveyor 19 are for left and right traveling, It is driven based on the rotation of hydraulic motors 20 to 29 for crusher, vibration feeder, main conveyor, side conveyor, magnetic separator, vibration screen, secondary conveyor and tertiary conveyor. 2 to 5 are circuit diagrams of the hydraulic system of the self-propelled crusher 1 provided with the motors 20 to 29. In the circuit diagrams, 10 is an oil tank, 12 is a first pump, and 13 is a second. The pump 30 is a pilot pump, and these pumps 12, 13, and 30 are configured to be driven by the power of the engine 11. In the above circuit diagram, circled numbers are connector symbols, and the corresponding circled numbers are connected to each other.

  In the circuit diagram, reference numeral 31 denotes a main control valve unit. The main control valve unit 31 includes left and right traveling control valves 32 and 33, a crushing device control valve 34, and a working device control valve 35. It has been incorporated.

  The left and right traveling control valves 32 and 33 are constituted by pilot-type three-position switching valves. These traveling control valves 32 and 33 are pilot pressures output from the left and right traveling pilot valves 34 and 35. Thus, the neutral position N where no pressure oil is supplied to the left and right traveling hydraulic motors 20, 21 is switched to the operating position X or Y where pressure oil is supplied. The left and right pilot valves 34 and 35 are connected to a pilot supply oil passage F, which will be described later, and the left and right traveling control valves are operated based on the operation of the left and right traveling levers 36 and 37 disposed in the control unit 8. Pilot pressure is output to 32 and 33.

  The crushing device control valve 34 is composed of a pilot-type three-position switching valve. The crushing device control valve 34 is a pilot pressure output from the crushing device first and second electromagnetic valves 38 and 39. Thus, the neutral position N where no pressure oil is supplied to the hydraulic motor 22 for crushing apparatus is switched to the operating position X or Y where pressure oil is supplied. The crushing device first and second solenoid valves 38 and 39 are connected to the pilot supply oil passage F, and the crushing device operation switches 41 (push button switches) on the operation panel board 40 arranged in the control unit 8 are used. The pilot pressure is supplied to the crushing device control valve 34 from the OFF position N where the pilot pressure is not supplied to the crushing device control valve 34 based on an operation signal input to the controller 42 described later from a changeover switch, a dial, etc. Switch to ON position X.

  The work device control valve 35 is a pilot-type three-position switching valve, but is used here as a two-position switching valve. The working device control valve 35 supplies pressure oil from a neutral position N where pressure oil is not supplied to the working device supply oil passage C, which will be described later, by the pilot pressure output from the mode switching electromagnetic valve 43. Switch to operating position X. The mode switching solenoid valve 43 does not supply pilot pressure to the work device control valve 35 based on a signal input to the controller 42 from the travel-work mode switch 44 disposed on the operation panel 40. The position N is switched to the ON position X where the pilot pressure is supplied to the work device control valve 35.

  45 is a multiple control valve unit for the main work device, and the multiple control valve unit 45 for the main work device includes a main work device, that is, a vibration feeder, a side conveyor, a main conveyor, and a magnetic separator. Each control valve 46-49 for machines is incorporated.

  The control valves 46 to 49 for the vibration feeder, the side conveyor, the main conveyor, and the magnetic separator are constituted by electromagnetic proportional three-position switching valves. The control valves 46 to 49 for the vibration feeder, the side conveyor, the main conveyor, and the magnetic separator are respectively used for the vibration feeder, the side conveyor, the main conveyor, and the magnetic separator on the operation panel panel 40. Based on the operation signals input to the controller 42 from the operation switches 50 to 53, the signals output from the controller 42 to the solenoids of the control valves 46 to 49 are used for vibration feeders, side conveyors, main conveyors, magnetic selection. The operation is switched from the neutral position N where no pressure oil is supplied to the machine hydraulic motors 23 to 26 to the operation position X or Y where the pressure oil is supplied.

  Further, 54 is a multiple control valve unit for the auxiliary work device, and the multiple control valve unit 54 for the auxiliary work device includes controls for the auxiliary work device, that is, for the vibrating screen, secondary and tertiary conveyors. Valves 55 and 56 are incorporated.

  The control valves 55 and 56 for the vibrating screen, secondary and tertiary conveyors are constituted by electromagnetic proportional two-position switching valves. The control valves 55 and 56 for the vibration screen, the secondary and the tertiary conveyor are connected to the controller 42 from the operation switches 57 and 58 for the vibration screen, the secondary and the tertiary conveyor on the operation panel 40. Based on the input operation signal, pressure oil is supplied to the hydraulic motors 27 to 29 for the vibration screen, the secondary conveyor, and the tertiary conveyor by a signal output from the controller 42 to the solenoids of the control valves 55 and 56. It switches from the neutral position N which is not supplied to the operating position X where pressure oil is supplied.

  Here, as described above, the main control valve unit 31 incorporates the control valves 32 to 35 for the left and right traveling, the crushing device, and the working device, and the multiple control valve unit 45 for the main working device. The control valves 46 to 49 for the main working device are incorporated, and the control valves 55 and 56 for the auxiliary working device are incorporated in the multiple control valve unit 54 for the auxiliary working device. As the control valves 32 to 35 incorporated in the main control valve unit 31, a flow control valve for a large flow rate is used. The traveling hydraulic motors 20 and 21 and the crushing device hydraulic motor 22 that require a large flow rate are used. The total flow rate of the main working device hydraulic motors 23 to 26 and the auxiliary working device hydraulic motors 27 to 29 (to the main working device hydraulic motors 23 to 26 and the auxiliary working device hydraulic motors 27 to 29 as will be described later). Pressure oil supply is adapted to accommodate.) To be made via the working device control valve 35. The control valves 46 to 49, 55, 56 incorporated in the main control unit multiple control valve unit 45 and the auxiliary control unit multiple control valve unit 54 are small flow rate control valves. Highly accurate flow rate control can be performed on the hydraulic motors 23 to 26 for the main working device and the hydraulic motors 27 to 29 for the auxiliary working device.

  Next, pressure oil supply to the control valves 32 to 35, 46 to 49, 55 and 56 described above will be described. Of the first and second hydraulic pumps 12 and 13, the discharge oil from the first hydraulic pump 12 is The supplied first supply oil passage A is connected to the left traveling control valve 32 and the crushing device control valve 34. Thus, the left traveling hydraulic motor 20 and the crushing device hydraulic motor 22 are connected to the first hydraulic pump 12 via the first supply oil passage A, the left traveling control valve 25 and the crushing device control valve 27. The oil discharged from is supplied. In this case, the left travel control valve 32 and the crushing device control valve 34 are connected in parallel.

  On the other hand, the second supply oil passage B to which the oil discharged from the second hydraulic pump 13 is supplied is connected to the right travel control valve 33 and the work device control valve 35. Thus, the second hydraulic pump is connected to the right traveling hydraulic motor 21 and the working device supply oil passage C via the second supply oil passage B, the right traveling control valve 33, and the working device control valve 35. The configuration is such that the discharged oil from 13 is supplied. In this case, the right travel control valve 33 and the work device control valve 35 are connected in parallel.

Further, the working device supply oil passage C is branched into a main working device supply oil passage D and an auxiliary work device supply oil passage E via a priority valve 59.
The priority valve 59 includes a throttle valve 59a that adjusts the priority flow rate, a pressure compensation valve 59i that keeps the differential pressure of the throttle valve 59a constant, and a pilot line orifice 59j. The pressure oil supplied from the second hydraulic pump 13 through the work device control valve 35 is supplied to the inlet of the throttle valve 59a of the priority valve 59, the non-priority side input port 59c of the pressure compensation valve 59i, and the non-priority side. It is led to the pilot port 59g. On the other hand, the outlet pressure of the throttle valve 59a is led to the priority pilot port 59f of the pressure compensation valve 59i through the priority input port 59b and the orifice 59j.
In the valve body of the priority valve 59, the inlet pressure of the throttle valve 59a is guided to the non-priority side pilot port 59g of the pressure compensation valve 59i, and the outlet of the throttle valve 59a is passed to the priority side pilot port 59f via the orifice 59j. The pressure is guided, and the pressure compensation valve 59i controls the pressure difference between the inlet pressure and the outlet pressure of the throttle valve 59a to be constant. Thus, regardless of the flow rate input from the second hydraulic pump 13 through the work device control valve 35, the priority side output port 59d of the priority valve 59 is preferentially fixed to the main work device supply oil path D. The remaining flow rate obtained by subtracting the priority flow rate from the discharge flow rate of the second hydraulic pump 13 is supplied from the non-priority side output port 59e to the auxiliary working device supply oil passage E. .

  The main working device supply oil passage D is connected to control valves 46 to 49 for a vibration feeder, a side conveyor, a main conveyor, and a magnetic separator incorporated in a multiple control valve unit 45 for the main working device. ing. Thus, the hydraulic oils 23 to 26 for the main working device, that is, for the vibration feeder, for the side conveyor, for the main conveyor, and for the magnetic separator are provided with the second supply oil passage B and the working device control valve 35. , Supply oil passage C for working device, priority valve 59, supply oil passage D for main working device, and control valves 46 to 49 for vibration feeder, side conveyor, main conveyor, and magnetic separator. The oil discharged from the two hydraulic pumps 13 is supplied. In this case, the control valves 46 to 49 for the vibration feeder, the side conveyor, the main conveyor, and the magnetic separator are connected in parallel to each other and correspond to the control valves 46 to 49, respectively. 60-63 are provided.

  On the other hand, the auxiliary working device supply oil passage E is connected to the control valves 55 and 56 for the vibrating screen, secondary and tertiary conveyors incorporated in the auxiliary working device multiple control valve unit 54. Thus, each of the hydraulic motors 27 to 29 for the auxiliary work device, that is, the vibrating screen, the secondary conveyor, and the tertiary conveyor has the second supply oil passage B, the work device control valve 35, and the work device. Oil discharged from the second hydraulic pump 13 via the supply oil passage C, the priority valve 59, the auxiliary oil supply passage E, and the control valves 55 and 56 for the vibrating screen, secondary and tertiary conveyors. Is configured to be supplied. In this case, the vibration screen control valve 55 and the secondary and tertiary conveyor control valves 56 are connected in parallel, and pressure compensation valves 64 and 65 are provided corresponding to the control valves 55 and 56, respectively. It has been.

  Further, F is a pilot supply oil passage to which oil discharged from the pilot pump 30 is supplied. The pilot supply oil passage F is connected to the left and right traveling pilot valves 34 via the traveling hydraulic lock electromagnetic switching valve 66. 35 and the crushing device first and second electromagnetic valves 38 and 39 and the mode switching electromagnetic valve 43.

  The travel hydraulic lock electromagnetic switching valve 66 opens and closes a supply oil path from the pilot supply oil path F to the left and right travel pilot valves 34, 35. When the lock command is output from the controller 42, the controller 42 is positioned at the closed position N for closing the supply path to the left and right traveling pilot valves 34, 35, and when the lock release command is output, It is set to be located at an open position X that opens the supply path. When the traveling hydraulic lock electromagnetic switching valve 66 is in the closed position N, the supply of pilot pressure from the pilot pump 30 to the traveling pilot valves 34 and 35 is cut off, so that the left and right traveling levers The pilot pressure is not output from the traveling pilot valves 34 and 35 even if the driving levers 36 and 37 are operated. However, when the traveling hydraulic lock electromagnetic switching valve 66 is switched to the open position X, the left and right traveling levers 36 and 37 are operated. The pilot pressure is output from the traveling pilot valves 34 and 35 based on the above.

  On the other hand, the controller 42 is configured by using a microcomputer or the like, and includes a CPU (Central Processing Unit), a memory, and the like. As shown in the block diagram of FIG. , Operation switches 41, 50, 51, 52, 53, 57, 58 for crushing devices, for vibration feeders, for side conveyors, for main conveyors, for magnetic separators, for vibration screens, for secondary and tertiary conveyors, A signal from the travel-work mode switch 44 or the like is input, and on the basis of the input signal, the crushing device first and second electromagnetic valves 38 and 39, the vibration feeder control valve 46, the side conveyor control valve 47, Main conveyor control valve 48, magnetic separator control valve 49, vibration screen control valve 55, secondary and tertiary conveyor control valve 56, mode switching solenoid valve 43, travel hydraulic pressure Tsu is configured to output a control command to the click selector valve 66 and the like.

  The travel-work mode switching switch 44 is a switch for switching to the “travel mode” when the operator travels the self-propelled crusher 1 and to the “work mode” when performing the shredding work. When the travel-work mode switch 44 is switched to the “travel mode” side, the controller 42 outputs a lock release command to the travel hydraulic lock electromagnetic switching valve 66. When the unlocking command is output to the travel hydraulic lock electromagnetic switching valve 66, pilot pressure is output from the left and right travel pilot valves 34, 35 based on the operation of the left and right travel levers 36, 37. Thus, the left and right traveling control valves 32, 33 are switched to the operating position X or Y, and pressure oil is supplied to the left and right traveling hydraulic motors 20, 21. In this case, the left traveling hydraulic motor 20 is supplied with the discharge oil from the first hydraulic pump 12 via the first supply oil passage A, and the right traveling hydraulic motor 21 is supplied with the second hydraulic pump 13. The discharged oil from is supplied through the second supply oil passage B.

  Further, when the travel-work mode switch 44 is switched to the “travel mode” side, the controller 42 controls the crushing device first and second solenoid valves 38 and 39 and the mode switching solenoid valve 43. The control command is output so as to be positioned at the OFF position N. Thus, the pilot pressure is not supplied to the crushing device control valve 34 and the working device control valve 35, and the crushing device control valve 27 and the working device control valve 35 are held at the neutral position N. Thus, even if the corresponding operation switches 41, 50 to 53, 57, 58 are operated, the crushing device, the vibration feeder, the side conveyor, the main conveyor, the magnetic separator, the vibration screen, and the secondary conveyor Therefore, the hydraulic oil is not supplied to the hydraulic motors 22 to 29 for the secondary conveyor and the tertiary conveyor, and is kept in an operation stopped state.

  On the other hand, when the travel-work mode switch 44 is switched to the “work mode” side, the controller 42 outputs a lock command to the travel hydraulic lock electromagnetic switching valve 66. When the lock command is output to the travel hydraulic lock electromagnetic switching valve 66, the pilot pressure is not output from the travel pilot valves 34, 35, and the left and right travel control valves 32, 33 are neutral. Held in position N. Thus, even if the left and right travel levers 36 and 37 are operated, no pressure oil is supplied to the left and right travel hydraulic motors 20 and 21 and the travel is stopped.

  Further, when the travel-work mode switch 44 is switched to the “work mode” side, the controller 42 controls the crushing device operation switches 41 for the crushing device first and second electromagnetic valves 38, 39. A control command is output so as to switch to the ON position X based on the above operation. As a result, the pilot pressure is output from the crushing device first and second electromagnetic valves 38 and 39, the crushing device control valve 34 is switched to the operating position X or Y, and pressure oil is supplied to the crushing device hydraulic motor 22. Supplied. In this case, the oil discharged from the first hydraulic pump 12 is supplied to the crushing device hydraulic motor 22 via the first supply oil passage A.

In addition, when the travel-work mode switch 44 is switched to the “work mode” side, the controller 42 outputs a control command so as to be positioned at the ON position X with respect to the mode switching solenoid valve 43 and vibrates. For the control valves 46 to 49, 55 and 56 for feeders, side conveyors, main conveyors, magnetic separators, vibrating screens, secondary and tertiary conveyors, corresponding operation switches 50 to 53, 57, Based on the operation of 58, a control command is output so as to switch to the operating position X or Y. Accordingly, the pressure oil is supplied to the hydraulic motors 23 to 29 for the vibration feeder, the side conveyor, the main conveyor, the magnetic separator, the vibration screen, the secondary conveyor, and the tertiary conveyor. In these hydraulic motors 23 to 29, the oil discharged from the second hydraulic pump 13 passes through the second supply oil passage B, the working device oil passage C, the main working device oil passage D, or the auxiliary working device oil passage E. In this case, the priority valve 59 for distributing the pressure oil in the working device oil passage C to the main working device oil passage D and the auxiliary working device oil passage E is as described above. In order to always supply a constant flow rate to the main working device oil passage D regardless of the pump flow rate, each hydraulic motor for the vibration feeder, side conveyor, main conveyor, and magnetic separator is the main working device. The pressure oil of the second hydraulic pump 13 is preferentially supplied to 23-26.
The second hydraulic pump 13 is used for each of the hydraulic motors 23 for a vibration feeder, a side conveyor, a main conveyor, a magnetic separator, a vibration screen, a secondary conveyor, and a tertiary conveyor during a normal crushing operation. In the case where the hydraulic fluid has a capacity enough to supply the pressure oil at a flow rate necessary to rotate the rotation speed to 29 at the set rotational speed, but the load increases and the supply flow rate of the second hydraulic pump 13 decreases. As described above, the pressure oil is preferentially supplied to the hydraulic motors 23 to 26 for the main working device by the priority valve 59.

  In the present embodiment configured as described, the self-propelled crusher 1 includes left and right traveling, crushing device, vibration feeder, side conveyor, main conveyor, magnetic separator, vibration screen, and secondary The first and second hydraulic pumps 12 and 13 for supplying pressure oil to the hydraulic motors 20 to 29 for the conveyor and the tertiary conveyor are provided, but the travel-work mode changeover switch 44 is “work mode”. In the crushing operation, the oil discharged from the first hydraulic pump 12 is exclusively supplied to the crushing device hydraulic motor 22, while the oil discharged from the second hydraulic pump 13 is used for the main working device. And hydraulic motors 23 to 29 for auxiliary work devices, that is, for vibration feeders, for side conveyors, for main conveyors, for magnetic separators, for vibration screens, for secondary conveyors, and for tertiary conveyors. It will be supplied. Thus, even if the crushing device 4 has a large load fluctuation, the hydraulic motors 23 to 29 for the main working device and the auxiliary working device are not affected by the large load fluctuation of the crushing device hydraulic motor 22. Thus, a stable pressure oil supply is made.

  Thus, in this embodiment, during the crushing operation, the first hydraulic pump 12 is used as a hydraulic supply source exclusively for the crushing device 4, while the second hydraulic pump 13 is used as a hydraulic supply source for the main working device and the auxiliary working device. Thus, the main working device and the auxiliary working device are not affected by the large load fluctuation of the crushing device 4, and in this case, pressure oil is supplied from the second hydraulic pump 13. When the load of the working device of either the main working device or the auxiliary working device increases and the supply flow rate of the second hydraulic pump 13 decreases, the discharge oil of the second hydraulic pump 13 is discharged from the priority valve. 59 is distributed preferentially to the hydraulic motors 23 to 26 for the vibration feeder, side conveyor, main conveyor, and magnetic separator, which are the main work devices. Is, vibrating screens external optional devices remaining pressure oil is an auxiliary working device, for the secondary conveyor, to be supplied to the hydraulic motors 27 to 29 for the tertiary conveyor.

  As a result, even if there are a large number of working devices supplied with pressure oil from the second hydraulic pump 13, pressure oil is preferentially supplied to the vibration feeder 6, the side conveyor 7, the main conveyor 15, and the magnetic separator 16 as the main working devices. Therefore, the work efficiency of these main work devices does not decrease, and even if the load on any of the work devices increases, It is possible to avoid a problem that the main work such as carrying out the crushed material from the crushing device 4 is delayed and the work efficiency is lowered.

  Further, in this configuration, the pressure oil is supplied to the hydraulic motors 23 to 29 for the main working device and the auxiliary working device by using the priority valve 59 to supply the pressure oil from the second hydraulic pump 13 to the main working device oil passage D. After being distributed to the auxiliary work device oil passage E, the control valves 46 to 49, 55, and 56 are incorporated into the main work device multiple control valve unit 45 and the auxiliary work device multiple control valve unit 54. In this case, the multiple control valve units 45, 54 have a working device hydraulic motor 23 that requires a smaller flow rate than the traveling hydraulic motors 20, 21 and the crushing device hydraulic motor 22. Since only the control valves 46 to 49, 55, and 56 that perform oil supply / discharge control to 29 are incorporated, the flow control valve for small flow rate corresponding to the work device is a multiple control valve unit 45, 5 Will be able to incorporate as can be Thus, performs highly accurate flow rate control to each working device hydraulic motor 23-29.

  Of course, the present invention is not limited to the above-described embodiment. In the above-described embodiment, the side conveyor and the magnetic separator are included in the main working device. However, the side conveyor and the magnetic separator are externally attached options. Although it is not detachably mounted at the work site like an apparatus, it is generally mounted arbitrarily as an option, and there is no need to prioritize the work of the side conveyor 7 and magnetic separator 16 If possible, it can also be configured to be included in an auxiliary work device. In this case, the control valve for the side conveyor and the control valve for the magnetic separator are incorporated in the multiple control valve unit for the auxiliary work device.

It is a top view of a self-propelled crusher. It is a circuit diagram which shows the hydraulic system of a self-propelled crusher. It is a circuit diagram which shows the hydraulic system of a self-propelled crusher. It is a circuit diagram which shows the hydraulic system of a self-propelled crusher. It is a circuit diagram which shows the hydraulic system of a self-propelled crusher. It is a block diagram which shows the input-output to a controller.

Explanation of symbols

DESCRIPTION OF SYMBOLS 12 First hydraulic pump 13 Second hydraulic pump 22 Hydraulic motor for crushing device 23 Hydraulic motor for vibration feeder 24 Hydraulic motor for main conveyor 25 Hydraulic motor for side conveyor 26 Hydraulic motor for magnetic separator 27 Hydraulic motor for vibration screen 28 Secondary conveyor Hydraulic motor for secondary conveyor 29 Hydraulic motor for tertiary conveyor 45 Multiple control valve unit for main work equipment 54 Multiple control valve unit for auxiliary work equipment 59 Priority valve

Claims (2)

  A crushing device, a main work device such as a supply device that supplies a material to be crushed to the crushing device, a carry-out device that carries out the crushed material from the crushing device, and an auxiliary work device such as a detachable external optional device In this self-propelled crusher, hydraulic oil for operation is supplied to hydraulic actuators for the crushing device, the main working device, and the auxiliary working device that drive the crushing device, the main working device, and the auxiliary working device, respectively. In forming the hydraulic system, the hydraulic system includes a first hydraulic pump serving as a pressure oil supply source for the crushing device hydraulic actuator, and a first hydraulic pump serving as a pressure oil supply source for the main working device hydraulic actuator and the auxiliary device hydraulic actuator. Two hydraulic pumps, and pressure oil from the second hydraulic pump is preferentially supplied to the hydraulic actuator for the main working device via the priority valve. Hydraulic systems in mobile crusher which is characterized by being configured to so that.   2. The control valve for controlling supply / discharge of pressure oil to / from the hydraulic actuator for the main working device and the hydraulic actuator for the auxiliary working device according to claim 1, wherein the control valve unit for the main working device and the multiple control valve for the auxiliary working device The hydraulic pressure in the self-propelled crusher is incorporated in each unit, and the multiple control valve unit for the main work device and the multiple control valve unit for the auxiliary work device are arranged downstream of the priority valve. system.

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