JP2010285825A - Hydraulic driving device of treating machine, and self-travelling treating machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic driving device of a treating machine and a self-travelling treating machine wherein excess conveying capacity of either one of a first conveyor or a second conveyor can be utilized to compensate shortage of the conveying capacity of the other conveyor. <P>SOLUTION: A ratio-changing circuit 50 (a hydraulic circuit) is arranged between a supply conduit 36 for the first conveyor, which guides pressure oil from a control valve 32 for the first conveyor to a hydraulic pressure motor 22 for the first conveyor, and a supply conduit 37 for the second conveyor, which guides the pressure oil from a control valve 33 for the second conveyor to a hydraulic pressure motor 23 for the second conveyor. The ratio changing circuit 50 guides a part of the pressure oil from the supply conduit 37 for the second conveyor to the supply conduit 36 for the first conveyor by a direction-control valve 52 and a flow-dividing valve 51. Thus, a ratio of the amount of flow of the pressure oil distributed to the hydraulic pressure motor 22 for the first conveyor and a ratio of the amount of flow of the pressure oil distributed to the hydraulic pressure motor 23 for the second conveyor are changed. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a sorting device that sorts objects to be sorted such as crushing, wood chips, earth and sand, etc., into larger and smaller particles, and small particles smaller than a predetermined particle size sorted by the sorting device. Processing such as a crusher or a sieve equipped with a first conveyor that transports the first conveyor and a second conveyor that transports crushed ones of large particles larger than a predetermined particle size sorted by the sorting device The present invention relates to a hydraulic drive device for a processing machine that drives the machine, and a self-propelled processing machine including the hydraulic drive device.

  Patent Document 1 discloses a self-propelled crusher. The self-propelled crusher includes a sorting device (grid feeder), a first conveyor (side conveyor) that transports a small granular material smaller than a predetermined particle size sorted by the sorting device, and a predetermined sorted by the sorting device. A crushing device (jaw crusher) for crushing large granular material larger than the particle size and a second conveyor (main conveyor) for conveying the crushed material generated by crushing by the crushing device are provided.

  The sorting device, the first conveyor, and the second conveyor are driven by a hydraulic drive device. This hydraulic drive device is provided with a hydraulic motor that is a hydraulic actuator separately for the sorting device, the first conveyor, and the second conveyor as a drive source for the sorting device, the first conveyor, and the second conveyor. Hereinafter, the hydraulic motors that are the drive sources of the sorting device, the first conveyor, and the second conveyor are referred to as a sorting device hydraulic motor, a first conveyor hydraulic motor, and a second conveyor hydraulic motor.

  Further, the hydraulic drive device is shared by the sorting device hydraulic motor, the first conveyor hydraulic motor, and the second conveyor hydraulic motor, and discharges the pressure oil supplied to these hydraulic motors, and this hydraulic pump And a hydraulic circuit that distributes the discharge flow rate to the sorting device hydraulic motor, the first conveyor hydraulic motor, and the second conveyor hydraulic motor at a predetermined constant ratio.

  The first ratio, which is the ratio of the flow rate distributed to the first conveyor hydraulic motor in the discharge flow rate of the hydraulic pump, and the ratio of the flow rate, which is distributed to the second conveyor hydraulic motor, in the discharge flow rate of the hydraulic pump. The ratio of 2 is the mixing ratio of the objects to be sorted handled by the self-propelled crusher at the work site, that is, the large granular material that is sorted as a granular material having a predetermined particle size or more by the sorting device and is crushed by the crushing device, It is determined on the assumption of a ratio with small granular materials smaller than the predetermined particle size. For example, when assuming a sorting object in which the proportion of small granular materials is larger than that of large granular materials, the first proportion is higher than the second proportion so that the conveying capability of the first conveyor is higher than the conveying capability of the second conveyor. It is set large. The types of objects to be sorted include concrete lumps produced by building demolition, construction waste and industrial waste such as asphalt lumps produced by road repair, and minerals such as rocks and earth and sand mined at the mining site. The mixing ratio of these selection objects varies.

  Patent Document 2 discloses a self-propelled sieving machine that is a different type of processing machine from a self-propelled crusher. This self-propelled sieving machine includes a sorting device (vibrating screen device), a first conveyor that conveys small granular materials smaller than a predetermined particle size sorted by the sorting device, and a predetermined particle size sorted by the sorting device. And a second conveyor for conveying large large granular materials. This type of self-propelled sieving machine is also driven by a hydraulic drive device having the same configuration as the hydraulic drive device described above.

JP 2001-259467 A JP 2005-296893 A

  As described above, in the conventional hydraulic drive device for a processing machine, the first and second ratios are constant. For this reason, when the processing machine handles a sorting object having a different mixing ratio than expected, for example, when the sorting object has a larger proportion of small granular materials than expected, the sorting object is Is put into the sorting device by the same amount as the case of the sorting object as expected, the conveying capacity of the second conveyor becomes excessive, and the conveying capacity of the first conveyor is insufficient. For this reason, it is necessary to reduce the input amount of the sorting object in comparison with the case where the sorting object is input as expected, in accordance with the transporting capability of the first conveyor that is insufficient in transporting capability. On the other hand, if the sorting object has a larger proportion of large granular materials than expected, the input amount of the sorting object is matched with the transport capacity of the second conveyor, which is short of transport capacity, as expected. It is necessary to make it smaller than the case where the selection object of the mixing ratio is input. In other words, when the processing machine handles sorting objects with various mixing ratios, the entire processing machine is not sufficiently transported due to insufficient transport capacity of one of the first and second conveyors. There is a problem that the work ability of the is limited.

  In addition, since this kind of self-propelled processing machine can be self-propelled and can be moved on the carrier bed of a trailer, it is much easier to carry than a processing machine that is not self-propelled. For this reason, a self-propelled processing machine is easy to be used as what handles the selection target object of various mixing ratios in many fields rather than a treatment machine which is not self-propelled, and the above-mentioned problem tends to arise.

  The present invention has been made in consideration of the above-mentioned circumstances, and the object thereof is to compensate for the excess of the transfer capability that occurs in one of the first and second conveyors, and the lack of transfer capability that occurs in the other conveyor. It is an object of the present invention to provide a hydraulic drive device for a processing machine and a self-propelled processing machine that can be used.

  In order to achieve the above-mentioned object, the hydraulic drive device of the processing machine of the present invention is “[1]” to “[6]”, and the self-propelled processing machine of the present invention is “[7]”. It is configured as follows.

[1] A hydraulic drive device for a processing machine according to the present invention includes a sorting device hydraulic actuator that drives a sorting device into which a sorting object is charged and sorts into a larger and smaller size than a predetermined particle size, and the sorting device. By a hydraulic actuator for a first conveyor that drives a first conveyor that transports a small granular material smaller than the selected predetermined particle size, and a large granular material larger than the predetermined particle size selected by the selecting device, or a crushing device It is shared by the hydraulic actuator for the second conveyor that drives the second conveyor that transports the crushed crushed material, and the hydraulic actuator for the first and second conveyors, and is supplied to the hydraulic actuator for the first and second conveyors. A hydraulic pump that discharges the pressure oil, the hydraulic oil discharged from the hydraulic pump, and the first actuator And a hydraulic control circuit that distributes the hydraulic actuator for the second conveyor to a hydraulic actuator for the second conveyor. Of the discharge flow rate of the hydraulic pump, the flow of the flow that is distributed to the hydraulic actuator for the first conveyor A first ratio that is a ratio and a second ratio that is a ratio of a flow rate that is distributed to the hydraulic actuator for the second conveyor out of the discharge flow rate of the hydraulic pump, and a total ratio of these first ratio and second ratio A ratio changing means for changing without increasing / decreasing is provided.

  In the hydraulic drive apparatus for a processor according to the present invention, the ratio changing means changes the first and second ratios without increasing or decreasing the total ratio of the first and second ratios. Thereby, the excess of the conveyance capability which arises in one conveyor of a 1st, 2nd conveyor can be utilized for supplementing the lack of conveyance capability which arises in the other conveyor.

[2] The present invention is the hydraulic drive device for a processing machine according to “[1]”, in which the pressure oil to the first conveyor hydraulic actuator is placed between the first conveyor hydraulic actuator and the hydraulic pump. A control valve for the first conveyor that can switch between supply and stoppage of the supply is interposed, and between the hydraulic actuator for the second conveyor and the hydraulic pump, the pressure oil to the hydraulic actuator for the second conveyor A second conveyor control valve capable of switching between supply and stoppage of the supply is interposed, and the ratio changing means directs pressure oil from the first conveyor control valve to the first conveyor hydraulic actuator. On at least one supply line of the supply line for the conveyor or the supply line for the second conveyor for guiding the pressure oil from the control valve for the second conveyor to the hydraulic actuator for the second conveyor Provided, wherein the guiding part of the flow rate of the hydraulic fluid to the other supply line from one feed line.

[3] The hydraulic drive device for a processing machine according to the present invention is the hydraulic drive device for a processing machine described in “[1]”, wherein the first conveyor is provided between the hydraulic actuator for the first conveyor and the hydraulic pump. A control valve for a first conveyor capable of switching between supply of pressure oil to the hydraulic actuator and stop of the supply is interposed, and the second conveyor is provided between the hydraulic actuator for the second conveyor and the hydraulic pump. There is a second conveyor control valve capable of switching between supply of pressure oil to the hydraulic actuator and stoppage of the supply, and the ratio changing means controls the opening degree of the first conveyor control valve steplessly. A first stepless control means capable of controlling the opening degree of the control valve for the second conveyor steplessly, and the first stepless control means for the first conveyor. Change in opening of control valve When, by the change of the opening degree of the second conveyor control valve according to the second stepless control means and to realize the first, change of the second fraction.

[4] The hydraulic drive device for a processing machine according to the present invention is the hydraulic drive device for a processing machine according to “[1]”, wherein the first conveyor is provided between the first conveyor hydraulic actuator and the hydraulic pump. A control valve for a first conveyor capable of switching between supply of pressure oil to the hydraulic actuator and stop of the supply is interposed, and the second conveyor is provided between the hydraulic actuator for the second conveyor and the hydraulic pump. When an auxiliary hydraulic actuator serving as a drive source for an auxiliary machine is provided with a control valve for a second conveyor that can switch between supply of pressure oil to the hydraulic actuator and stopping of the supply, the auxiliary actuator A spare control valve is provided, which is interposed between the hydraulic actuator and the hydraulic pump, and is capable of switching between supply of pressure oil to the auxiliary hydraulic actuator and stop of supply thereof. The changing means includes a first state in which pressure oil is guided from the preliminary control valve to the first conveyor hydraulic actuator, and a second state in which pressure oil is guided from the preliminary control valve to the second conveyor hydraulic actuator. The switching means is switchable.

[5] A hydraulic drive device for a processing machine according to the present invention is the hydraulic drive device for a processing machine according to “[1]”, wherein the first conveyor is provided between the first conveyor hydraulic actuator and the hydraulic pump. A control valve for a first conveyor capable of switching between supply of pressure oil to the hydraulic actuator and stop of the supply is interposed, and the second conveyor is provided between the hydraulic actuator for the second conveyor and the hydraulic pump. When an auxiliary hydraulic actuator serving as a drive source for an auxiliary machine is provided with a second conveyor control valve capable of switching between supply of hydraulic oil to the hydraulic actuator and stoppage of the supply, the auxiliary hydraulic actuator is provided. A spare control valve is provided, which is interposed between the hydraulic actuator for machine and the hydraulic pump, and is capable of switching between supply of pressure oil to the hydraulic actuator for auxiliary equipment and stoppage of this supply. The ratio changing means includes a first state in which pressure oil is guided from the preliminary control valve to the first conveyor hydraulic actuator, and a second state in which pressure oil is guided from the preliminary control valve to the second conveyor hydraulic actuator; And switching means provided on the downstream side of the switching means, and distributing means for distributing the pressure oil to the first and second conveyor hydraulic actuators.

[6] The hydraulic drive device for a processing machine according to the present invention is the hydraulic drive device for a processing machine described in “[1]”, wherein the first conveyor is provided between the hydraulic actuator for the first conveyor and the hydraulic pump. A control valve for a first conveyor capable of switching between supply of pressure oil to the hydraulic actuator and stop of the supply is interposed, and the second conveyor is provided between the hydraulic actuator for the second conveyor and the hydraulic pump. A second conveyor control valve capable of switching between supply of hydraulic oil to the hydraulic actuator and stoppage of the supply; an auxiliary hydraulic actuator serving as a drive source for the auxiliary; and an auxiliary hydraulic actuator; A backup control valve interposed between the hydraulic pumps and capable of switching between supply of pressure oil to the hydraulic actuator for auxiliary machinery and switching of the supply stop is provided; A first state in which pressure oil is guided from the control valve to the first conveyor hydraulic actuator; a second state in which pressure oil is guided from the spare control valve to the second conveyor hydraulic actuator; and Switching means capable of switching to a third state for guiding pressure oil to the auxiliary hydraulic actuator, and distribution for distributing the pressure oil to the first and second conveyor hydraulic actuators provided downstream of the switching means. Means.

[7] The self-propelled processing machine of the present invention is charged with a sorting object, a sorting device for sorting into a larger one and a smaller one with a predetermined particle size, and a smaller particle size than the predetermined particle size sorted with the sorting device. A first conveyor for conveying small granular materials, a second conveyor for conveying large granular materials larger than the predetermined particle size sorted by the sorting device, or crushed materials crushed by a crushing device, the sorting device, The self-propelled processing machine provided with the main body frame which supports the hydraulic drive which drives the 1st conveyor and the 2nd conveyor, and the running body provided in the main body frame, as the hydraulic drive device, The hydraulic drive device according to any one of -6 is provided.

  According to the hydraulic drive device and the self-propelled processing machine of the processing machine of the present invention, as described above, the excess of the conveying capacity generated in one of the first and second conveyors is insufficient for the conveying capacity generated in the other conveyor. Can be used to supplement Therefore, even though there is a margin in the transfer capacity of one of the first and second conveyors, the situation in which the work capacity of the entire processing machine is limited due to a shortage of the transfer capacity of the other conveyor occurs. Can be difficult.

It is a left view of the self-propelled sieving machine which is an example of the self-propelled processing machine to which the hydraulic drive device of the processor of the present invention is applied. It is a top view of the self-propelled sieving machine shown in FIG. 1-1. It is a front view of the self-propelled sieve shown in FIG. 1 is a hydraulic circuit diagram illustrating a hydraulic drive device according to a first embodiment of the present invention. It is a left view of the self-propelled crusher which is another example of the self-propelled processing machine to which the hydraulic drive device of the processing machine of this invention is applied. FIG. 3 is a top view of the self-propelled crusher shown in FIG. 3-1. It is a front view of the self-propelled crusher shown to FIGS. FIG. 3 is an enlarged perspective view of a sorting unit (grid feeder) provided in the self-propelled crusher shown in FIG. It is a hydraulic circuit diagram which shows the hydraulic drive device which concerns on 2nd Embodiment of this invention. It is a hydraulic circuit diagram which shows the hydraulic drive device which concerns on 3rd Embodiment of this invention. It is a hydraulic circuit diagram which shows the hydraulic drive device which concerns on 4th Embodiment of this invention. It is a hydraulic circuit diagram which shows the hydraulic drive device which concerns on 5th Embodiment of this invention.

[First Embodiment]
1st Embodiment of the hydraulic drive apparatus of the processing machine of this invention and a self-propelled processing machine is described using FIGS. 1-1 to 1-3 and FIG. FIG. 1-1 is a left side view of a self-propelled sieving machine as an example of a self-propelled processing machine to which a hydraulic drive device for a processing machine of the present invention is applied. FIG. 1-2 is a top view of the self-propelled sieve shown in FIG. 1-1. FIG. 1-3 is a front view of the self-propelled sieve shown in FIG. 1-1. FIG. 2 is a hydraulic circuit diagram showing the hydraulic drive apparatus according to the first embodiment of the present invention.

  A self-propelled sieving machine 1 shown in FIGS. 1-1 to 1-3 includes a traveling body 2. The traveling body 2 combines a pair of track frames 2a and 2b arranged in parallel in the left-right direction of the self-propelled sieving machine 1 and the pair of track frames 2a and 2b. The lower frame 3a forming the lower part of the main body frame 3 is used as a skeleton. A drive wheel 4 driven by a hydraulic motor (not shown) is provided at one end (rear end) of the left track frame 2a. A follower wheel 5 is provided at the other end (front end) of the track frame 2a. A crawler belt 6 </ b> A is wound around the driving wheel 4 and the driven wheel 5. The right track frame 2b is also provided with a driving wheel and a driven wheel (not shown), and a crawler belt 6B is wound around these wheels.

  The main body frame 3 is formed so as to protrude forward and rearward from the traveling body 2. In the approximate center of the main body frame 3 in the front-rear direction, a hopper 7 that forms an input port for the sorting object, a sorting object that has passed through the hopper 7 and a small granular material smaller than a predetermined grain size, A vibrating sieve device 10 is provided as a sorting device for sorting into large granular materials larger than a predetermined particle size. The vibration type sieve device 10 is provided below the hopper 7 and includes a screen box 11 that receives and sorts a selection object that has passed through the hopper 7 with a mesh floor 11a. A drive source of the vibration sieve device 10, that is, a drive source for vibrating the screen box 11 is a sorting device hydraulic motor 21. The screen box 11 is vibrated when the hydraulic motor 21 for the sorting device rotates the eccentric weight. Although not shown, the mesh floor 11a is provided in the screen box 11 so as to be inclined such that the front end portion is inclined obliquely downward.

  The main body frame 3 is provided with a first conveyor 12 in a posture that extends rearward and obliquely upward from below the mesh floor 11a. The first conveyor 12 receives small particles smaller than a predetermined particle size selected by the mesh floor 11a, that is, small particles that have passed through the mesh floor 11a, below the mesh floor 11a. Transport diagonally upward.

  A second conveyor 13 is provided at the front end portion of the main body frame 3 so as to extend obliquely upward and downward to the right from the lower front of the mesh floor 11a. The second conveyor 13 is a small granular material larger than a predetermined particle size selected by the mesh floor 11a, that is, a large granular material that does not pass through the mesh floor 11a and rolls down from the front end of the mesh floor 11a due to the inclination of the mesh floor 11a. It is received at the front diagonally lower side of the mesh floor 11a and conveyed to the upper right side of the self-propelled sieving machine 1.

  As shown in FIG. 2, the hydraulic drive device 20 according to the first embodiment conveys a small granular material smaller than a predetermined particle size sorted by the above-described sorting device hydraulic motor 21 and the vibrating sieve device 10. A first conveyor hydraulic motor 22 that drives the first conveyor, a second conveyor hydraulic motor 23 that drives a second conveyor 13 that conveys a large granular material larger than a predetermined particle size selected by the vibrating sieve device 10, and It has. The hydraulic drive unit 20 includes an engine 24, a main pump 25 (variable displacement hydraulic pump) and a pilot pump 26 (constant displacement hydraulic pump) driven by the engine 24, and the main pump 25 includes a sorting device hydraulic pressure. The oil discharged from the main pump 25 is used for the motor 21, the first conveyor hydraulic motor 22 and the second conveyor hydraulic motor 23, and the sorting apparatus hydraulic motor 21, the first conveyor hydraulic motor 22 and the second conveyor hydraulic pressure are used. And a hydraulic control circuit 30 that distributes to the motor 23.

  The hydraulic control circuit 30 includes a control valve 31 for the sorting device, a control valve 32 for the first conveyor, and a control valve 33 for the second conveyor. The sorter control valve 31 is interposed between the sorter hydraulic motor 21 and the main pump 25. Supply of pressure oil from the main pump 25 to the sorter hydraulic motor 21 is stopped, and the supply is stopped. Can be switched. The first conveyor control valve 32 is interposed between the first conveyor hydraulic motor 22 and the main pump, and can switch between supply of pressure oil to the first conveyor hydraulic motor 22 and stop of the supply. It is configured. The second conveyor control valve 33 is interposed between the second conveyor hydraulic motor 23 and the main pump 25, and switches between supply of pressure oil to the second conveyor hydraulic motor 23 and stop of the supply. It is configured to be possible.

  The sorting device control valve 31, the first conveyor control valve 32, and the second conveyor control valve 33 are all spring return type electromagnetic / hydraulic pilot type valves. The control valve 31 for the sorting device is primarily operated by supplying the electric power Ws to the solenoid 31a, and operates by introducing the discharge oil of the pilot pump 26, that is, the pilot pressure. The control valve 32 for the first conveyor is primarily operated by supplying the electric power Wc1 to the solenoid 32a and operates by introducing the discharge oil of the pilot pump 26, that is, the pilot pressure. The second conveyor control valve 33 is primarily operated by supplying electric power Wc2 to the solenoid 33a, and operates by introducing discharge oil of the pilot pump 26, that is, pilot pressure.

  When the valve position of the sorting device control valve 31 is the initial position (the lower valve position in FIG. 2), all the pressure oil from the main pump 25 to the sorting device control valve 31 is guided to the hydraulic oil tank 27. When the valve position of the sorting device control valve 31 is switched to the operating position (upper valve position), the pressure oil from the main pump 25 to the sorting device control valve 31 passes through the sorting device control valve 31 and is used for the sorting device. The sorting device return pipe 35 led to the sorting device supply line 34 for leading the pressure oil to the inlet 21a of the hydraulic motor 21 and led out from the outlet 21b of the sorting device hydraulic motor 21 is a control valve for the sorting device. The hydraulic oil tank 27 communicates with the hydraulic oil tank 31.

  When the valve position of the first conveyor control valve 32 is the initial position (the lower valve position in FIG. 2), all the pressure oil from the main pump 25 to the first conveyor control valve 32 is guided to the hydraulic oil tank 27. It is burned. When the valve position of the first conveyor control valve 32 is switched to the operating position (upper valve position), the pressure oil from the main pump 25 to the first conveyor control valve 32 passes through the first conveyor control valve 32. The first conveyor return pipe led to the first conveyor supply pipe 36 for guiding the pressure oil to the inlet 22a of the first conveyor hydraulic motor 22 and led out from the outlet 22b of the first conveyor hydraulic motor 22 The path 35 communicates with the hydraulic oil tank 27 via the first conveyor control valve 32.

  When the valve position of the second conveyor control valve 33 is the initial position (the lower valve position in FIG. 2), all the pressure oil from the main pump 25 to the second conveyor control valve 33 enters the hydraulic oil tank 27. Led. When the valve position of the second conveyor control valve 33 is switched to the operating position (upper valve position), the pressure oil from the main pump 25 to the second conveyor control valve 33 passes through the second conveyor control valve 33. The second conveyor return pipe led to the second conveyor supply pipe 37 leading the pressure oil to the inlet 23a of the second conveyor hydraulic motor 23 and led out from the outlet 23b of the second conveyor hydraulic motor 23. 35 communicates with the hydraulic oil tank 27 via the second conveyor control valve 33.

  The hydraulic control circuit 30 is configured to supply the sorting device supply pipe 34 in a state where all the valve positions of the sorting device control valve 31, the first conveyor control valve 32, and the second conveyor control valve 33 are switched to the operating positions. Pressure oil flow rate Fs guided to the first conveyor supply line 36, pressure oil flow rate Fc1 guided to the second conveyor supply line 37, pressure oil flow rate Fc2 guided to the second conveyor supply line 37, and these flow rates Fs, The relationship of the flow rate Fa obtained by adding Fc1 and Fc2 is set to be “Fs: Fc1: Fc2: Fa = 4: 3: 3: 10”.

  In particular, the hydraulic drive device 20 according to the first embodiment includes a first ratio R1 that is a ratio of a flow rate distributed to the first conveyor hydraulic motor 22 in a discharge flow rate of the main pump 25, and a discharge flow rate of the main pump 25. As a ratio changing means for changing the second ratio R2, which is the ratio of the flow rate distributed to the second conveyor hydraulic motor 23, without increasing or decreasing the total ratio R12 of the first ratio R1 and the second ratio R2. A ratio changing circuit 50 (hydraulic circuit) is provided.

  This ratio changing circuit 50 includes a diversion valve 51 and a direction control valve 52. The diversion valve 51 has a branch line 51 a that diverts the pressure oil flowing through the second conveyor supply line 37 and guides it to the direction control valve 52. The branch pipe 51a is set so that 1/3 of the flow rate of the pressure oil flowing into the second conveyor supply pipe 37 from the second conveyor control valve 33 is diverted. The direction control valve 52 has first and second outlets 52a and 52b. The first outlet 52 a communicates with the second conveyor supply pipe 37 via the return pipe 53 on the downstream side of the flow dividing valve 51. The second outlet 52 b communicates with the first conveyor supply pipe 36 via the merge pipe 54. The junction line 54 is provided with a check valve 55 that blocks the flow of pressure oil from the first conveyor supply line 36 toward the second outlet 52b.

  The direction control valve 52 is a spring return type electromagnetic pilot type valve, and operates by supplying electric power Wd to the solenoid 52c. When the valve position of the directional control valve 52 is the initial position (the valve position on the right side in FIG. 2), the branch pipe line 51a communicates with the first outlet 52a, whereby the pressure oil diverted by the diversion valve 51 is It returns to the second conveyor supply line 37 through the direction control valve 52 and the return line 53. When the valve position of the direction control valve 52 is switched to the operating position (the valve position on the left side), the branch pipe line 51a communicates with the second outlet 52b, so that the pressure oil branched by the branch valve 51 is The first control line 52 is led to the first conveyor supply line 36 through the direction control valve 52 and the merging line 54.

  The engine 24, the main pump 25, the pilot pump 26, the hydraulic control circuit 30 and the ratio changing circuit 50 are combined as a power unit 14 and attached to the rear part of the main body frame 3.

  A control panel (not shown) is provided on the right side surface of the power unit 14. The control panel is provided with an operation dial 56 as a command device for the first and second ratios, and a controller 60 for controlling the hydraulic drive device 20 by a command signal from the operation dial 56.

  The operation dial 56 can be rotated so that the pointer 56a faces the first mark 57A, the second mark 57B, and the third mark 57C, and the pointer 56a faces the first mark 57A. In the posture in which the second mark 57B is directed and the posture in which the pointer 56a is directed to the third mark 57C, if a rotational force of a predetermined value or more is not applied, the posture is stopped. The operation dial 56 outputs an auto mode command signal (electrical signal) when the pointer 56a is stationary with the posture toward the first mark 57A, and is stationary with the pointer 56a facing the second mark 57B. The first conveyor mode command signal (electrical signal) is output in a state where the pointer is in a posture in which the pointer 56a faces the third mark 57C, and the second conveyor mode command signal (electrical signal) is output. . All of these command signals are input to the controller 60.

  A first pressure sensor 61 that detects the load pressure of the first conveyor hydraulic motor 22 is provided on the inlet 22 a side of the first conveyor hydraulic motor 22. The first pressure sensor 61 outputs a first detection pressure signal S1 (electric signal) corresponding to the detected pressure value. The first detection pressure signal S1 is input to the controller 60. A second pressure sensor 62 that detects a load pressure of the second conveyor hydraulic motor 23 is provided on the inlet 23 a side of the second conveyor hydraulic motor 23. The second pressure sensor 62 outputs a second detection pressure signal S2 (electric signal) corresponding to the detected pressure value. The second detection pressure signal S2 is also input to the controller 60.

  The controller 60 has a CPU, a RAM, and a ROM, and operates according to a computer program stored in advance in the ROM. When the controller 60 receives any of the auto mode command signal, the first conveyor mode command signal and the second conveyor mode command signal from the operation dial 56, the solenoid 31a of the control valve 31 for the sorting device and the first conveyor Electric power Ws, Wc1, and Wc2 are supplied to the solenoid 32a of the control valve 32 and the solenoid 33a of the second conveyor control valve 33, respectively, and the sorting device control valve 31, the first conveyor control valve 32, and the second All the valve positions of the conveyor control valve 33 are set to be switched to the operating positions.

  The controller 60 is set to enter the auto mode when the auto mode command signal is input. In this auto mode, the controller 60 determines that the load pressure of the first conveyor hydraulic motor 22 obtained from the first detection pressure signal S1 is greater than the load pressure of the second conveyor hydraulic motor 23 obtained from the second detection pressure signal S2. Is also determined to be higher than a predetermined value, and the electric power Wd is supplied to the solenoid 52c of the direction control valve 52 only when the determination result is true.

  Further, the controller 60 is set to enter the first conveyor mode when the first conveyor mode command signal is input. In the first conveyor mode, the controller 60 applies the load pressure of the second conveyor hydraulic motor 23 obtained from the second detected pressure signal to the load pressure of the first conveyor hydraulic motor 22 obtained from the first detected pressure signal. Regardless, the power Wd is supplied to the solenoid 52c of the direction control valve 52.

  Furthermore, the controller 60 is set to enter the second conveyor mode when the second conveyor mode command signal is input. In the second conveyor mode, the controller 60 applies the load pressure of the second conveyor hydraulic motor 23 obtained from the second detected pressure signal to the load pressure of the first conveyor hydraulic motor 22 obtained from the first detected pressure signal. Regardless, the power Wd is not supplied to the solenoid 52c of the direction control valve 52.

  In the hydraulic drive device 20 configured as described above, the discharge oil of the main pump 25 is supplied to each of the first conveyor hydraulic motor 22 and the second conveyor hydraulic motor 23 as follows.

<Auto mode>
When the operation dial 56 is stationary with the pointer 56a facing the first mark 57A, the controller 60 continues to receive the auto mode command signal from the operation dial 56, and the controller 60 is now in the auto mode. Maintain state.

  In this auto mode, the controller 60 supplies power Ws, Wc1, and Wc2 to the solenoid 31a of the control valve 31 for the sorting device, the solenoid 32a of the control valve 32 for the first conveyor, and the solenoid 33a of the control valve 33 for the second conveyor, respectively. Each is supplied, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, and the control valve 33 for the second conveyor are switched to the operating positions. At this time, the flow rate Fs of pressure oil guided to the supply line 34 for the sorting device, the flow rate Fc1 of pressure oil guided to the supply line 36 for the first conveyor, and the pressure oil flowed to the supply line 37 for the second conveyor The relationship between the flow rate Fc2 and the total flow rate Fa of these flow rates Fs, Fc1, and Fc2 is “Fs: Fc1: Fc2: Fa = 4: 3: 3: 10”.

  While the controller 60 maintains the state of outputting the electric power Ws, Wc1, and Wc2, the first detection pressure signal S1 from the first pressure sensor 61 and the second detection pressure signal S2 from the second pressure sensor 62 Is periodically input at time intervals of milliseconds, and the load pressure of the first conveyor hydraulic motor 22 obtained from the first detection pressure signal S1 is obtained from the second detection pressure signal S2 each time it is input. It is determined whether or not the load pressure of the two-conveyor hydraulic motor 23 is higher than a predetermined value.

  When the determination result is negative, that is, when the load pressure of the first conveyor hydraulic motor 22 is not higher than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 60 controls the direction control valve 52. The power Wd is not supplied to the solenoid 52c. Therefore, the valve position of the direction control valve 52 is held at the initial position. As a result, the pressure oil that has been branched from the second conveyor supply line 37 by the branch line 51 a of the diversion valve 51 by a rate of 1/3 is supplied to the second conveyor supply line through the direction control valve 52 and the return line 53. Return to 37. That is, the flow rate fs of pressure oil supplied to the hydraulic motor 21 for the sorting device, the flow rate fc1 of pressure oil supplied to the hydraulic motor 22 for the first conveyor, and the flow rate of pressure oil supplied to the hydraulic motor 23 for the second conveyor. The relationship between fc2 and the flow rate fa obtained by adding these flow rates fs, fc1, and fc2 is the same as the relationship between the flow rates Fs, Fc1, Fc2, and Fa (Fs: Fc1: Fc2: Fa = 4: 3: 3: 10). “Fs: fc1: fc2: fa = 4: 3: 3: 10” is set. At this time, the first ratio R1, which is the ratio of the flow rate distributed to the first conveyor hydraulic motor 22 in the discharge flow rate of the main pump 25, is distributed to the second conveyor hydraulic motor 23 in the discharge flow rate of the main pump 25. The relationship between the second ratio R2 that is the ratio of the flow rate and the total ratio R12 of the first and second ratios R1 and R2 is “R1: R2: R12 = 3: 3: 6”.

  On the other hand, when the determination result by the controller 60 is true, that is, the determination result is that the load pressure of the first conveyor hydraulic motor 22 is higher than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 60 controls the direction. Electric power Wd is supplied to the solenoid 52c of the valve 52, and the valve position of the direction control valve 52 is switched to the operating position. As a result, the pressure oil that has been diverted from the second conveyor supply line 37 by the branch line 51 a of the diversion valve 51 by a rate of 1/3 passes through the directional control valve 52 and the merging pipe line 54. 36. As a result, the relationship between the flow rates fs, fc1, fc2, and fa is the same as the relationship between the flow rates Fs, Fc1, Fc2, and Fa (Fs: Fc1: Fc2: Fa = 4: 3: 3: 10). It is changed to a different “fs: fc1: fc2: fa = 4: 4: 2: 10”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is such that the total ratio R12 does not increase or decrease from “R1: R2: R12 = 3: 3: 6” to “R1: R2: R12 = 4: It is changed to “2: 6”.

<First conveyor mode>
In a state where the operation dial 56 is stationary with the pointer 56a facing the second mark 57B, the controller 60 continues to input the first conveyor mode command signal from the operation dial 56, whereby the controller 60 Keep the mode.

  In the first conveyor mode, the controller 60 supplies electric power Ws, Wc1, and power to the solenoid 31a of the sorting device control valve 31, the solenoid 32a of the first conveyor control valve 32, and the solenoid 33a of the second conveyor control valve 33, respectively. Each of Wc2 is supplied, and the valve positions of the sorting device control valve 31, the first conveyor control valve 32, and the second conveyor control valve 33 are switched to the operating positions. Furthermore, the controller 60 also supplies power Wd to the solenoid 52c of the direction control valve 52 regardless of whether or not the load pressure of the first conveyor hydraulic motor 22 is higher than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more. To switch the valve position of the direction control valve 52 to the operating position. As a result, the relationship between the flow rates fs, fc1, fc2, and fa is different from the relationship between the flow rates Fs, Fc1, and Fc2 (Fs: Fc1: Fc2: Fa = 4: 3: 3: 10): “fs: fc1: fc2: fa = 4: 4: 2: 10 ". That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is such that the total ratio R12 does not increase or decrease from “R1: R2: R12 = 3: 3: 6” to “R1: R2: R12 = 4: 2: 6 ".

<Second conveyor mode>
In a state where the operation dial 56 is stationary with the pointer 56a facing the third mark 57C, the second conveyor mode command signal from the operation dial 56 is continuously input to the controller 60, whereby the controller 60 Keep the mode.

  In this second conveyor mode, the controller 60 supplies power Ws, Wc1, and power to the solenoid 31a of the sorting device control valve 31, the solenoid 32a of the first conveyor control valve 32, and the solenoid 33a of the second conveyor control valve 33, respectively. Each of Wc2 is supplied, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, and the control valve 33 for the second conveyor are switched to the operating positions, and the load of the hydraulic motor 22 for the first conveyor Regardless of whether the pressure is higher than the load pressure of the hydraulic motor 23 for the second conveyor by a predetermined value or more, the power Wd is not supplied to the solenoid 52c of the direction control valve 52, and the valve position of the direction control valve 52 is set to the initial position. Hold on. Thereby, the relationship between the flow rates fs, fc1, fc2, and fa is set to “fs: fc1: fc2: fa = 4: 3: 3: 10”, which is the same as the relationship between the flow rates Fs, Fc1, Fc2, and Fa. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 3: 3: 6”.

  Thus, according to the hydraulic drive device 20 according to the first embodiment, the first ratio R1 that is the ratio of the flow rate distributed to the first conveyor hydraulic motor 22 in the discharge flow rate of the main pump 25, and the main pump 25. The setting of the relationship with the second ratio R2, which is the ratio of the flow rate distributed to the second conveyor hydraulic motor 23, is made without increasing or decreasing the total ratio R12 of the first ratio R1 and the second ratio R2. “R1: R2 = 3: 3” and “R1: R2 = 4: 2” can be selected. Thus, when the first conveyor 12 is insufficient in conveying capacity and the second conveyor 13 is excessive in conveying capacity, the excess of the conveying capacity generated in the second conveyor 13 can be compensated for the insufficient conveying capacity generated in the first conveyor 12. it can. Therefore, it is less likely to cause a situation where the working capacity of the entire self-propelled sieving machine 1 is limited due to the lack of the conveying capacity of the first conveyor 12 even though the conveying capacity of the second conveyor 13 is sufficient. can do.

  In the hydraulic drive device 20 according to the first embodiment described above, the hydraulic control circuit 30 is such that all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, and the control valve 33 for the second conveyor are in the operating position. In this state, the pressure oil flow rate Fs guided to the sorting device supply line 34, the pressure oil flow rate Fc1 guided to the first conveyor supply line 36, and the second conveyor supply line 37 are guided. The relationship between the flow rate Fc2 of the pressurized oil and the total flow rate Fa of these flow rates Fs, Fc1, and Fc2 is set to be “Fs: Fc1: Fc2: Fa = 4: 3: 3: 10”. However, this relationship is an example, and other relationships such as “Fs: Fc1: Fc2: Fa = 5: 3: 2: 10” may be used.

  In the hydraulic drive device 20 according to the first embodiment described above, the hydraulic circuit as the ratio changing means is the ratio changing circuit 50, and is supplied from the second conveyor supply pipe 37 by the diversion valve 51, the direction control valve 52, and the like. A part of the flow rate of the pressure oil is guided to the conveyor supply line 36. The hydraulic circuit as the ratio changing means in the present invention is not limited to the one that guides a part of the flow rate from the first conveyor supply pipe 36 to the second conveyor supply pipe 37, but the first conveyor supply. The hydraulic circuit may be provided with a diversion valve, a direction control valve, and the like so as to guide a part of the flow rate of the pressure oil from the pipeline 36 to the second conveyor supply pipeline 37. Further, a hydraulic circuit for guiding a part of the flow rate of the pressure oil from the second conveyor supply line 37 to the first conveyor supply line 36, and a second conveyor supply line 37 from the first conveyor supply line 36. Alternatively, a hydraulic circuit that guides a part of the flow rate of the pressure oil may be selectively used.

  The processing machine to which the hydraulic drive device 20 according to the first embodiment is applied is self-propelled. However, the processing machine to which the hydraulic drive device according to the present invention is applied is not a self-propelled type. What is necessary is just to provide the 1st conveyor and the 2nd conveyor.

  In the self-propelled sieving machine 1 to which the hydraulic drive device 20 according to the first embodiment described above is applied, the vibrating sieving device 10 as the sorting device is provided with the mesh floor 11a. It is not limited, The vibration type sieve apparatus provided with the finger type vibration floor may be sufficient.

  The self-propelled processing machine to which the hydraulic drive device 20 according to the first embodiment is applied is the self-propelled sieving machine 1, but the self-propelled processing machine to which the hydraulic drive device of the present invention is applied is self-propelled. The self-propelled crusher 70 described below with reference to FIGS. 3-1 to 3-4 may be used. FIG. 3-1 is a left side view of a self-propelled crusher that is another example of a self-propelled processing machine to which the hydraulic drive device for the processing machine of the present invention is applied. 3-2 is a top view of the self-propelled crusher shown in FIG. 3-1. 3-3 is a front view of the self-propelled crusher shown in FIG. 3-1. FIG. 3-4 is an enlarged perspective view of the sorting unit (grid feeder) provided in the self-propelled crusher shown in FIG. Among the components shown in FIGS. 3-1 to 3-3, the same reference numerals as those shown in FIGS. 1-1 to 1-3 are given to the components equivalent to those shown in FIGS. 1-1 to 1-3. It was used.

  In the self-propelled crusher 70 shown in FIGS. 3-1 to 3-3, a hopper 7 that forms an inlet for a sorting object is provided at the front of the main body frame 3. Below the hopper 7, there is provided a grizzly feeder 71 as a sorting device for sorting the sorting object passing through the hopper 7 into a small granular material smaller than a predetermined particle size and a large granular material larger than the predetermined particle size. ing.

  The grizzly feeder 71 includes a sorting unit 72 located below the hopper 7. As shown in FIG. 3-4, the selection unit 72 includes a casing 73. The casing 73 is coupled to the main body frame 3 through a plurality of elastic leg portions 74 (only one is shown) configured by two coil springs 74a and 74b arranged in parallel.

  In the casing 73, a flat plate portion 75 that receives the sorting object thrown into the hopper 7, and a plurality of first grizzly rivers that are located obliquely below the flat plate portion 75 and extend in the front-rear direction of the self-propelled crusher 70. The first grizzly river row 76 a is formed in parallel with a gap in the left-right direction of the self-propelled crusher 70, and is positioned obliquely below and rearward of the first grizzly river row 76. A plurality of second grizzly rivers 77a extending in the direction are fixed to a second grizzly river row 77 formed in parallel with a gap in the left-right direction of the self-propelled crusher 70. The flat plate portion 75, the first grizzly river row 76, and the second grizzly river row 77 as a whole form a downwardly inclined stepped shape. Moreover, the 1st, 2nd grizzly river row | line | column 77 inclines so that a rear-end part may become diagonally downward.

  The sorting unit 72 configured in this manner vibrates by rotating an eccentric weight by a hydraulic motor (not shown). Due to the vibration of the sorting unit 72, the sorting object in the casing 73 moves from the flat plate portion 75 to the first grizzly river row 76 and from the first grizzled river row 76 to the second grizzled river row 77. During this time, the small granular material in the sorting object passes through the first grizzly river row 76 or the second grizzly river row 77 and falls downward, and the large granular material falls from the second grizzly river row 77 obliquely downward and rearward. It will be.

  A crushing device 78 is arranged behind the second grizzly river row 77 and is supported by the main body frame 3. The crushing device 78 is a fixed plate (not shown) provided in a posture that rises obliquely upward in the forward direction, and is separated or close to the fixed plate in the front-rear direction of the self-propelled crusher 70. A jaw crusher having a movable plate (not shown) that swings so as to sway, the large granular material dropped from the rear end of the second grizzly river row 77 is received between the fixed plate and the movable plate, and the movable plate is shaken. It is made to move and bite between the movable plate and the fixed plate.

  As shown in FIGS. 3-2 and 3-3, in the self-propelled crusher 70, the first conveyor 12 is self-propelled crusher 70 from below the first and second grizzly river rows 76 and 77 of the sorting unit 72. Is supported by the main body frame 3 in a posture extending to the right side, and conveys small granular materials. The second conveyor 13 is supported by the main body frame 3 in a posture extending obliquely upward and backward from a discharge port (not shown) of the crushing device 78, and conveys the granular material crushed by the crushing device 78. To do.

[Second Embodiment]
A hydraulic drive device according to the second embodiment will be described with reference to FIG. FIG. 4 is a hydraulic circuit diagram showing a hydraulic drive apparatus according to the second embodiment of the present invention. Among those shown in FIG. 4, the same reference numerals as those in FIG. 2 are used for those equivalent to those shown in FIG. 2.

  The hydraulic drive device 20 according to the first embodiment described above includes the first conveyor control valve 32, the second conveyor control valve 33, the controller 60, and the operation dial 56, but the hydraulic drive device according to the second embodiment. 90 includes a first conveyor control valve 91, a second conveyor control valve 92, a controller 93, and an operation dial 94 instead.

  The first conveyor control valve 91 has a proportional solenoid 91a that makes the pilot pressure variable, and the opening degree can be changed steplessly by adjusting the magnitude of the electric power Wc1 to the proportional solenoid 91a. It can be done. The control valve 92 for the second conveyor also has a proportional solenoid 92a that makes the pilot pressure variable, and the opening degree can be changed steplessly by adjusting the magnitude of the electric power Wc2 to the proportional solenoid 92a. Is.

  The operation dial 94 functions as a variable resistor in a state where the pointer 56a faces a position within an angle range of about 120 ° between the second mark 57B and the third mark 57C, and the command value is set to a voltage according to the rotation angle. The ratio command signal indicated by the value is output.

  When the controller 93 receives the ratio command signal from the operation dial 94, the controller 93 enters the manual adjustment mode. In this manual adjustment mode, the controller 93 determines the value of the electric power Wc1 supplied to the proportional solenoid 91a of the first conveyor control valve 91 and the second conveyor control valve 92 based on the command value (voltage value) of the ratio command signal. The electric power Wc2 supplied to the proportional solenoid 92a is calculated, and the electric power Wc1 and Wc2 are supplied to the proportional solenoids 91a and 92a, respectively. That is, the proportional solenoid 91a and the controller 93 constitute a first stepless control means capable of controlling the opening degree of the first conveyor control valve 32 in a stepless manner. A second stepless control means that can control the opening degree of the two-conveyor control valve 92 steplessly is configured.

  Further, the controller 93 is set to calculate a larger power Wc1 as the position indicated by the pointer 56a is closer to the second mark 57B (away from the third mark 57C), and at this time, the power Wc1 is calculated to be smaller. Yes. That is, the opening degree of the second conveyor control valve 92 is decreased by the increase amount of the opening degree of the first conveyor control valve 91, or the second conveyor control amount is decreased by the decrease amount of the opening degree of the first conveyor control valve 91. The electric power Wc1 and Wc2 are determined so as to increase the opening of the valve 92, and the first ratio R1 and the second ratio R2 are not increased or decreased by the total ratio R12.

  In short, in the hydraulic drive device 90 according to the second embodiment, the ratio changing means includes a proportional solenoid 91a of the first conveyor control valve 91, a proportional solenoid c2 of the second conveyor control valve 92, and a controller 93. It is composed of

  It should be noted that when the ratio command signal is input in a state in which the pointer 56a of the operation dial 94 points to the second mark 57B, the controller 93 sets the flow rate Fs of the pressure oil guided to the sorting device supply pipe 34, the first conveyor. The relationship between the flow rate Fc1 of the pressure oil guided to the supply pipeline 36, the flow rate Fc2 of the pressure oil guided to the supply channel 37 for the second conveyor, and the total flow rate Fa is “Fs: Fc1: Fc2: Fa”. = 4: 5: 1: 10 "is set to calculate power Ws (constant value), Wc1, Wc2. When the ratio command signal is input while the pointer 56a points to the third mark 57C, the controller 93 determines that the relationship between the flow rates Fs, Fc1, Fc2, and Fa is “Fs: Fc1: Fc2: Fa = 4: 1”. : 5: 10 "is set to calculate the electric power Ws (constant value), Wc1, Wc2.

  In the auto mode, the controller 93 determines that the load pressure of the first conveyor hydraulic motor 22 obtained from the first detection pressure signal S1 is the load pressure of the second conveyor hydraulic motor 23 obtained from the second detection pressure signal S2. The first determination is made to determine whether or not the value is higher than the predetermined value. When the result of the first determination is true, the relationship between the flow rates Fs, Fc1, Fc2, and Fa is “Fs: Fc1: Fc2: Fa = 4”. : 4: 2: 10 "is supplied to the proportional solenoids 91a and 92a, respectively. Further, in the auto mode, the controller 93 performs a second determination to determine whether the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more. 2 When the determination result is true, the electric power Wc1 and Wc2 having values at which the relationship between the flow rates Fs, Fc1, Fc2, and Fa becomes “Fs: Fc1: Fc2: Fa = 4: 2: 4: 10” are proportional equations, respectively. The solenoids 91a and 92a are supplied.

  In the hydraulic drive device 90 configured as described above, the discharge oil of the main pump 25 is supplied to each of the first conveyor hydraulic motor 22 and the second conveyor hydraulic motor 23 as follows.

<Auto mode>
When the operation dial 94 is stationary with the pointer 56a facing the first mark 57A, an auto mode command signal from the operation dial 94 is continuously input to the controller 93, whereby the controller 93 enters the auto mode. Maintain state.

  In this auto mode, the controller 93 supplies the power Ws to the solenoid 31a of the control valve 31 for the sorting device, the proportional solenoid 91a of the control valve 91 for the first conveyor, and the proportional solenoid 92a of the control valve 92 for the second conveyor. Each of Wc1 and Wc2 is supplied. As a result, the valve position of the control valve 31 for the sorting device is switched to the operating position, and the valve positions of both the first conveyor control valve 91 and the second conveyor control valve 92 are between the initial position and the operating position. Switch. As a result, the flow rate Fs of pressure oil guided to the supply line 34 for the sorting device, the flow rate Fc1 of pressure oil guided to the supply line 36 for the first conveyor, and the pressure oil flow guided to the supply line 37 for the second conveyor The relationship between the flow rate Fc2 and the total flow rate Fs, Fc1, Fc2 is “Fs: Fc1: Fc2: Fa = 4: 3: 3: 10”. Accordingly, the flow rate fs of pressure oil supplied to the hydraulic motor 21 for the sorting device, the flow rate fc1 of pressure oil supplied to the hydraulic motor 22 for the first conveyor, and the flow rate of pressure oil supplied to the hydraulic motor 23 for the second conveyor. The relationship of fc2 and the flow rate fa obtained by adding these flow rates fs, fc1, and fc2 is similar to the relationship of the flow rates Fs, Fc1, Fc2, and Fa (Fs: Fc1: Fc2: Fa = 4: 3: 3: 10). : Fc1: fc2: fa = 4: 3: 3: 10 ”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 3: 3: 6”.

  In the auto mode, the controller 93 periodically sends the first detection pressure signal S1 from the first pressure sensor 61 and the second detection pressure signal S2 from the second pressure sensor 62 at time intervals of milliseconds. Each time it is input, the load pressure of the first conveyor hydraulic motor 22 obtained from the first detection pressure signal S1 is greater than the load pressure of the second conveyor hydraulic motor 23 obtained from the second detection pressure signal S2. A first determination is made as to whether or not the load pressure of the first conveyor hydraulic motor 22 is higher than a predetermined value, and a second determination is made as to whether or not the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23. The first determination can determine whether the first conveyor 12 is insufficient in conveying capacity and the second conveyor 13 is excessive in conveying capacity, and the second determination determines that the second conveyor 13 is insufficient in conveying capacity and the first conveyor 12 is excessive in conveying capacity. Can be determined.

  The determination result is negative, that is, the load pressure of the first conveyor hydraulic motor 22 is not higher or lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value. At some point, the controller 60 maintains the power Wc1, Wc2 supplied to each of the proportional solenoids 91a, 92a. Therefore, the relationship among the flow rates fa, fc1, fc2, and fa is maintained at “fa: fc1: fc2: fa = 4: 3: 3: 10”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is maintained at “R1: R2: R12 = 3: 3: 6”.

  When the result of the first determination is true, that is, when the determination result indicates that the load pressure of the first conveyor hydraulic motor 22 is higher than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 60 determines that the proportional solenoid 91a, Electric power Wc1 and Wc2 supplied to each of 92a is changed. That is, the power Wc1 is increased, and at the same time, the power Wc2 is decreased. As a result, the opening degree of the first conveyor control valve 32 is increased, and at the same time, the opening degree of the second conveyor control valve 33 is decreased, and the relationship between the flow rates fs, fc1, fc2, and fa is “fs: fc1”. : Fc2: fa = 4: 4: 2: 10 ”. The relationship between the first ratio R1, the second percentage, and the total ratio R12 is set to “R1: R2: R12 = 4: 2: 6” without increasing or decreasing the total ratio R12. As a result, the transport capability of the first conveyor 12 increases and the transport capability of the second conveyor 13 decreases.

  When the result of the second determination is true, that is, the determination result that the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 60 determines that the proportional solenoid 91a, Electric power Wc1 and Wc2 supplied to each of 92a is changed. That is, the power Wc1 is reduced, and at the same time, the power Wc2 is increased. Thereby, the opening degree of the control valve 32 for 1st conveyor becomes small, and the opening degree of the control valve 33 for 2nd conveyors becomes large simultaneously with this, and the relationship of flow volume fs, fc1, fc2, fa is "fs: fc1. : Fc2: fa = 4: 2: 4: 10 ”. The relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 2: 4: 6” without increasing or decreasing the total ratio R12. As a result, the conveyance capacity of the first conveyor 12 decreases and the conveyance capacity of the second conveyor 13 increases.

<Manual adjustment mode>
In a state where the operation dial 94 is stationary in a posture in which the pointer 56a is directed to an arbitrary position within the range of about 120 ° between the second mark 57B and the third mark 57C, it corresponds to the rotation angle of the operation dial 94. The ratio command signal of the voltage value (command value) continues to be input to the controller 93, whereby the controller 93 maintains the state in the manual adjustment mode.

  In this manual adjustment mode, the controller 60 calculates the values of the electric power Wc1 and Wc2 corresponding to the command value (voltage value) of the ratio command signal, and supplies the electric power Wc1 and Wc2 to the proportional solenoids 91a and 92a, respectively. Then, the valve positions of the first conveyor control valve 32 and the second conveyor control valve 33 are switched. The solenoid 31a of the sorting device control valve 31 is continuously supplied with a certain amount of electric power Ws regardless of the command value of the ratio command signal, and the valve position of the sorting device control valve 31 is held at the operating position.

  By controlling the valve positions of the first and second conveyor control valves 91 and 92 in this way, for example, the pointer 56a of the operation dial 94 is positioned 60 ° from the second mark 57B to the third mark 57C (120 ° In the case of facing the center of the range of °, the relationship between the flow rates fs, fc1, fc2, and fa is set to “Fs: Fc1: Fc2: Fa = 4: 3: 3: 10”. That is, the relationship between the first ratio R1, the second ratio R1, and the total ratio R12 is set to “R1: R2: R12 = 3: 3: 6” without increasing or decreasing the total ratio R12.

  When the pointer 56a points to the position of 30 ° from the second mark 57B to the third mark 57C, the relationship between the flow rates fs, fc1, fc2, and fa is “fs: fc1: fc2: fa = 4: 4: 2:10 ". That is, the relationship between the first ratio R1, the second ratio R1, and the total ratio R12 is set to “R1: R2: R12 = 4: 2: 6” without the total ratio R12 increasing or decreasing.

  When the pointer 56a points to the 90 ° position from the second mark 57B to the third mark 57C, the relationship between the flow rates fs, fc1, fc2, and fa is “fs: fc1: fc2: fa = 4: 2: 4:10 ". That is, the relationship between the first ratio R1, the second ratio R1, and the total ratio R12 is set to “R1: R2: R12 = 2: 4: 6” without increasing or decreasing the total ratio R12.

  When the pointer 56a points to the second mark 57B (0 °), the relationship between the flow rates fs, fc1, fc2, and fa is set to “fs: fc1: fc2: fa = 4: 5: 1: 10”. The That is, the relationship between the first ratio R1, the second ratio R1, and the total ratio R12 is set to “R1: R2: R12 = 5: 1: 6” without increasing or decreasing the total ratio R12.

  When the pointer 56a points to the third mark 57C (120 °), the relationship between the flow rates fs, fc1, fc2, and fa is set to “fs: fc1: fc2: fa = 4: 1: 5: 10”. The That is, the relationship between the first ratio R1, the second ratio R1, and the total ratio R12 is set to “R1: R2: R12 = 1: 5: 6” without increasing or decreasing the total ratio R12.

  As described above, according to the hydraulic drive device 90 according to the second embodiment, the first ratio R1 which is the ratio of the main pump 25 discharged to the first conveyor hydraulic motor 22 and the main pump 25 discharge flow rate. Of these, the relationship with the second ratio R2, which is the ratio to be distributed to the first conveyor hydraulic motor 22, is “R1: R2 = 5: 1 without increasing or decreasing the total ratio r12 of the first and second ratios R1, R2. To “R1: R2 = 1: 5” can be selected steplessly. As a result, the excess of the transfer capability that occurs in one of the first and second conveyors 12 and 13 can be used to compensate for the shortage of transfer capability that occurs in the other conveyor. Therefore, a situation in which the work capacity of the entire processing machine is limited due to a shortage of the transport capacity of the other conveyor, although there is a surplus in the transport capacity of one of the first and second conveyors 12 and 13 is conventionally known. It can be made less likely to occur.

  In addition, if the processing machine to which the hydraulic drive device 20 according to the above-described second embodiment is applied is also provided with a sorting device, a first conveyor, and a second conveyor, as in the first embodiment, it is self-propelled. But it doesn't have to be self-propelled.

  The self-propelled sieving machine to which the hydraulic drive device 20 according to the second embodiment described above is applied is similar to the first embodiment, even if the vibratory sieving apparatus provided with a mesh floor is mounted. It may be one equipped with a vibrating sieve device having a vibrating floor.

  The self-propelled processing machine to which the hydraulic drive device 20 according to the second embodiment is applied may be a self-propelled sieving machine or a self-propelled crusher as in the first embodiment.

[Third Embodiment]
A hydraulic drive device 100 according to a third embodiment will be described with reference to FIG. FIG. 5 is a hydraulic circuit diagram showing a hydraulic drive apparatus according to the third embodiment of the present invention. Among those shown in FIG. 5, the same reference numerals as those in FIG. 2 are used for those equivalent to those shown in FIG. 2.

  The hydraulic drive device 100 according to the third embodiment includes a ratio changing circuit 101 (hydraulic circuit) as ratio changing means. As a component of the ratio changing circuit 101, a spare control valve 102 already installed in the hydraulic control circuit 30 is used. The auxiliary control valve 102 is interposed between the auxiliary hydraulic actuator and the main pump 25 when an auxiliary hydraulic actuator (see FIG. 7) serving as a drive source for the auxiliary is provided. Switching between the supply of pressure oil to the hydraulic actuator and the stop of the supply is performed. This spare control valve 102 is also a spring return type electromagnetic / hydraulic pilot type valve, like the sorting device control valve 31, the first conveyor control valve 32, and the second conveyor control valve 33, and is connected to the solenoid 102r. It operates by supplying the electric power Wr.

  Further, the ratio changing circuit 101 includes a directional control valve 103. This directional control valve 103 is provided in the auxiliary supply pipe 104 that should be a pipe that leads pressure oil from the auxiliary control valve 102 to the auxiliary hydraulic actuator. This directional control valve 103 is a spring return type electromagnetic pilot type valve and has first and second outlets 103a and 103b. The first outlet 103 a communicates with the first conveyor supply pipe 36 via the first merge pipe 105. The second outlet 103 b communicates with the second conveyor supply pipe 37 via the second junction pipe 106. Accordingly, the ratio changing circuit 101 guides the pressure oil from the spare control valve 102 to the first conveyor hydraulic motor 22 when the valve position of the direction control valve 103 is the initial position (the valve position on the right side in FIG. 5). However, the hydraulic oil 23 for the second conveyor is in the first state where no pressure oil is guided. Further, when the electric power Wd is supplied to the solenoid 103c and the valve position of the direction control valve 103 is the operating position (the position on the left side in FIG. 5), pressure oil is supplied from the spare control valve 102 to the second conveyor hydraulic motor 23. The second state is such that no pressure oil is guided to the first conveyor hydraulic motor 22 while being guided.

  The hydraulic control circuit 30 performs sorting in a state where all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 are switched to the operating positions. The flow rate Fs of pressure oil led to the apparatus supply line 34, the flow rate Fc1 of pressure oil led to the supply line 36 for first conveyor, the flow rate Fc2 of pressure oil led to the supply line 37 for second conveyor, The relationship between the flow rate Fr of pressure oil guided to the machine supply conduit 104 and the total flow rate Fa of these flow rates Fs, Fc1, Fc2, Fr is “Fs: Fc1: Fc2: Fr: Fa = 4: 2: 3: 1: 10 ”.

  The hydraulic drive device 100 according to the third embodiment includes a controller 107 instead of the controller 60 in the first embodiment.

  In any of the auto mode, the first conveyor mode, and the second conveyor mode, the controller 107 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, and a second conveyor control valve 33. Electric power Ws, Wc1, Wc2, and Wr are supplied to the solenoid 33a and the solenoid 102a of the backup control valve 102, respectively, and the control valve 31 for the sorting device, the control valve 32 for the first conveyor, and the control for the second conveyor. Any valve position of the valve 33 and the auxiliary control valve 102 is set to be switched to the operating position.

  In the auto mode, the controller 107 determines that the load pressure of the first conveyor hydraulic motor 22 obtained from the first detection pressure signal S1 is the load pressure of the second conveyor hydraulic motor 23 obtained from the second detection pressure signal S2. It is determined whether or not it is lower than a predetermined value, and power Wd is supplied to the solenoid 103c of the directional control valve 103 only when the determination result is true.

  Further, in the first conveyor mode, the controller 107 loads the load of the second conveyor hydraulic motor 23 obtained from the second detected pressure signal to the load pressure of the first conveyor hydraulic motor 22 obtained from the first detected pressure signal. Regardless of the pressure, the power Wr is not supplied to the solenoid 103c of the direction control valve 103.

  Further, in the second conveyor mode, the controller 107 loads the load of the second conveyor hydraulic motor 23 obtained from the second detected pressure signal on the load pressure of the first conveyor hydraulic motor 22 obtained from the first detected pressure signal. Regardless of the pressure, electric power Wd is supplied to the solenoid 103c of the direction control valve 103.

  In the hydraulic drive device 100 configured as described above, the oil discharged from the main pump 25 is supplied to each of the first conveyor hydraulic motor 22 and the second conveyor hydraulic motor 23 as follows.

<Auto mode>
In the auto mode, the controller 107 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the spare control valve 102, respectively. Are supplied with electric power Ws, Wc1, Wc2, and Wr, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 are set. Switch to operating position.

  The controller 107 maintains the state of outputting the electric power Ws, Wc1, Wc2, and Wr, while the first detection pressure signal S1 from the first pressure sensor 61 and the second detection pressure signal from the second pressure sensor 62. S2 is periodically input at time intervals of milliseconds, and the load pressure of the first conveyor hydraulic motor 22 obtained from the first detection pressure signal S1 is obtained from the second detection pressure signal S2 each time it is input. It is determined whether or not the load pressure of the second conveyor hydraulic motor 23 is lower than a predetermined value.

  When the determination result is negative, that is, the determination result is that the load pressure of the first conveyor hydraulic motor 22 is not lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 107 detects the direction control valve. The power Wd is not supplied to the solenoid 103c of 103, whereby the direction control valve 103 is held at the initial position, and the ratio changing circuit 101 is held in the first state. As a result, the pressure oil guided from the auxiliary control valve 102 to the auxiliary machine supply pipe 104 is led to the first conveyor supply pipe 36 through the direction control valve 103 and the first merge pipe 105. Accordingly, the flow rate fs of pressure oil supplied to the hydraulic motor 21 for the sorting device, the flow rate fc1 of pressure oil supplied to the hydraulic motor 22 for the first conveyor, and the pressure oil supplied to the hydraulic motor 23 for the second conveyor. The relationship between the flow rate fc2 and the total flow rate fa of these flow rates fs, fc1, and fc2 is the same as the relationship between the flow rates Fs, Fc1 + Fr, Fc2, and Fa (Fs, Fc1 + Fr, Fc2, Fa = 4: 2 + 1: 3: 10). “Fs, fc1, fc2 = 4: 3: 3: 10” is set. At this time, the first ratio R1, which is the ratio of the flow rate distributed to the first conveyor hydraulic motor 22 in the discharge flow rate of the main pump 25, is distributed to the second conveyor hydraulic motor 23 in the discharge flow rate of the main pump 25. The relationship between the second ratio R2 that is the ratio of the flow rate and the total ratio R12 of the first and second ratios R1 and R2 is “R1: R2: R12 = 3: 3: 6”.

  On the other hand, when the determination result by the controller 107 is true, that is, the determination result is that the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 107 performs direction control. Electric power Wd is supplied to the solenoid 103c of the valve 103, whereby the valve position of the direction control valve 52 is switched to the operating position, and the ratio changing circuit 101 is changed to the second state. Therefore, the pressure oil introduced from the auxiliary control valve 102 to the auxiliary machine supply pipe 104 is led to the second conveyor supply pipe 37 through the direction control valve 103 and the second merge pipe 106. As a result, the relationship between the flow rates fs, fc1, fc2, and fa is the same as the relationship between the flow rates Fs, Fc1, Fc2 + Fr, and Fa (Fs: Fc1: Fc2 + Fr: Fa = 4: 2: 3 + 1: 10) (fs: fc1: fc2). : Fa = 4: 2: 4: 10). That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is such that the total ratio R12 does not increase or decrease from “R1: R2: R12 = 3: 3: 6” to “R1: R2: R12 = 2: 4: 6 ".

<First conveyor mode>
In the first conveyor mode, the controller 107 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the standby control valve 102. Are supplied with electric power Ws, Wc1, Wc2, and Wr, respectively, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 To the operating position. Further, regardless of whether or not the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the power Wd is not supplied to the solenoid 103c of the direction control valve 103, The valve position of the direction control valve 103 is held at the initial position. Thereby, the ratio changing circuit 101 is held in the first state. Therefore, the relationship between the flow rates fs, fc1, fc2, and fa is the same as the relationship between the flow rates Fs, Fc1 + Fr, Fc2, and Fa (Fs: Fc1 + Fr: Fc2: Fa = 4: 2 + 1: 3: 10), “fs: fc1: fc2: fa = 4: 3: 3: 10 ”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 3: 3: 6” without increasing or decreasing the total ratio R12.

<Second conveyor mode>
In the second conveyor mode, the controller 107 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the standby control valve 102. Are supplied with electric power Ws, Wc1, Wc2, and Wr, respectively, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 To the operating position. Further, the controller 107 supplies electric power Wd to the solenoid 103c of the direction control valve 103 regardless of whether or not the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more. Then, the valve position of the direction control valve 103 is switched to the operating position. As a result, the ratio changing circuit 101 changes to the second state. Therefore, the relationship between the flow rates fs, fc1, fc2, and fa is the same as the relationship between the flow rates Fs, Fc1, Fc2 + Fr, and Fa (Fs: Fc1: Fc2 + Fr: Fa = 4: 2: 3 + 1: 10), “fs: fc1: fc2 : Fa = 4: 2: 4: 10 ”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 2: 4: 6”.

  Thus, according to the hydraulic drive apparatus 100 according to the third embodiment, the first ratio R1 that is the ratio of the flow rate distributed to the first conveyor hydraulic motor 22 in the discharge flow rate of the main pump 25, and the main pump 25. The setting of the relationship with the second ratio R2, which is the ratio of the flow rate distributed to the second conveyor hydraulic motor 23, is made without increasing or decreasing the total ratio R12 of the first ratio R1 and the second ratio R2. “R1: R2 = 3: 3” and “R1: R2 = 4: 2” can be selected. As a result, an excess of the transport capacity generated in the first conveyor 12 can be used to make up for the shortage of transport capacity generated in the second conveyor 13. Accordingly, it is possible to make it less likely that the work capacity of the entire processing machine is limited due to a shortage of the transport capacity of the second conveyor 13 even though the transport capacity of the first conveyor 12 is sufficient. .

  In addition, if the processing machine to which the hydraulic drive device 100 according to the above-described third embodiment is applied is also provided with a sorting device, a first conveyor, and a second conveyor, as in the first embodiment, it is self-propelled. But it doesn't have to be self-propelled.

  As in the first embodiment, the self-propelled sieving machine to which the hydraulic drive device 100 according to the above-described third embodiment is applied is also a finger-type sieving machine equipped with a vibrating sieving apparatus having a mesh floor. It may be one equipped with a vibrating sieve device having a vibrating floor.

  The self-propelled processing machine to which the hydraulic drive device 100 according to the above-described third embodiment is applied may be a self-propelled sieving machine or a self-propelled crusher as in the first embodiment.

[Fourth Embodiment]
FIG. 6 is a hydraulic circuit diagram showing a hydraulic drive apparatus according to the fourth embodiment of the present invention. Among those shown in FIG. 6, the same reference numerals as those in FIG. 5 are used for those equivalent to those shown in FIG. 5.

  The hydraulic drive device 200 according to the fourth embodiment includes a ratio changing circuit 201 (hydraulic circuit) as ratio changing means. The ratio changing circuit 201 includes a first directional control valve 202, a second directional control valve 203, and a flow dividing valve 204. The first and second directional control valves 202 and 203 and the diversion valve 204 are provided in the auxiliary supply line 104. The first and second directional control valves 202 and 203 are spring return type electromagnetic pilot type valves.

  The diversion valve 204 is provided on the downstream side of the first directional control valve 202, and the first outlet 202 b of the first directional control valve 202 communicates with the inlet 204 a of the diversion valve 204 via the connection pipe 205. The diversion valve 204 is set to divert the pressure oil to 1: 1. The first outlet 204 b of the diversion valve 204 communicates with the first conveyor supply line 36 via the first merging pipe line 206. The second outlet 204 cB of the diversion valve 204 communicates with the second conveyor supply pipe 37 via the second merging pipe 207. A check valve 208 is provided in the first merge pipe 206 to prevent the flow of pressure oil from the first conveyor supply pipe 36 toward the first outlet 204 b of the diversion valve 204. A check valve 209 is also provided in the second merge pipe 207 to prevent the flow of pressure oil from the second conveyor supply pipe 37 toward the second outlet 204 c of the diversion valve 204.

  The second outlet 202 c of the first directional control valve 202 communicates with the first merging pipe line 206. The first outlet 203 a of the second directional control valve 203 communicates with the inlet 202 a of the first directional control valve 202. The second outlet 203 b of the second directional control valve 203 communicates with the second merging conduit 207.

  When the valve position of the second directional control valve 203 is the initial position and the valve position of the first directional control valve 202 is the operating position (the valve position on the left side in FIG. 6), the ratio changing circuit 201 is a spare control valve. The pressure oil is guided to the first conveyor hydraulic motor 22 from the second direction control valve 203, the first direction control valve 202 and the first merging pipe line 206, while the second conveyor hydraulic motor 23 receives the pressure oil. It will be in the 1st state which does not guide. Further, when the valve position of the second direction control valve 203 is the operating position (the position on the left side in FIG. 5), the second control valve 102 is connected to the second conveyor through the second direction control valve 203 and the second merging pipe line 207. While the pressure oil is guided to the hydraulic motor 23, the pressure oil is not guided to the first conveyor hydraulic motor 22. That is, the first and second directional switching valves 202 and 203 constitute switching means that can switch the ratio changing circuit 201 between the first state and the second state.

  Further, when both the valve positions of the first and second directional control valves 202 and 203 are the initial positions, the pressure oil from the first directional control valve 202 is supplied from the spare control valve 102 through the flow dividing valve 204 to the first and first directional valves. It will be in the 3rd state (state shown in Drawing 6) where pressure oil is distributed to hydraulic motors 22 and 23 for 2 conveyors. In other words, the diversion valve 204 is a distribution unit that distributes the pressure oil from the backup control valve 102 to the first and second conveyor hydraulic motors 22 and 23.

  The hydraulic control circuit 30 performs sorting in a state where all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 are switched to the operating positions. The flow rate Fs of pressure oil led to the apparatus supply line 34, the flow rate Fc1 of pressure oil led to the supply line 36 for first conveyor, the flow rate Fc2 of pressure oil led to the supply line 37 for second conveyor, The relationship between the flow rate Fr of the pressure oil guided to the machine supply conduit 104 and the total flow rate Fa of these flow rates Fs, Fc1, and Fc2 is “Fs: Fc1: Fc2: Fr: Fa = 4: 2: 2: 2:10 ".

  The hydraulic drive device 200 according to the fourth embodiment includes a controller 210. In any of the auto mode, the first conveyor mode, and the second conveyor mode, the controller 210 has a solenoid 31a of the control valve 31 for the sorting device, a solenoid 32a of the control valve 32 for the first conveyor, and a control valve 33 for the second conveyor. Electric power Ws, Wc1, Wc2, and Wr are supplied to the solenoid 33a and the solenoid 102a of the backup control valve 102, respectively, and the control valve 31 for the sorting device, the control valve 32 for the first conveyor, and the control for the second conveyor. Any valve position of the valve 33 and the auxiliary control valve 102 is set to be switched to the operating position.

  In the auto mode, the controller 210 determines that the load pressure of the first conveyor hydraulic motor 22 obtained from the first detection pressure signal S1 is greater than the load pressure of the second conveyor hydraulic motor 23 obtained from the second detection pressure signal S2. A first determination for determining whether the pressure is higher than a predetermined value; a second determination for determining whether the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23; Is supposed to do. The electric power Wd is supplied to the solenoid 202d of the first directional control valve 202 only when the result of the first determination is true. Further, the electric power Wd2 is supplied to the solenoid 203c of the second directional control valve 203 only when the result of the second determination is true.

  In the first conveyor mode, the controller 210 changes the load pressure of the first conveyor hydraulic motor 22 obtained from the first detected pressure signal to the load pressure of the second conveyor hydraulic motor 23 obtained from the second detected pressure signal. Regardless, the electric power Wd1 is supplied to the solenoid 202d of the first directional control valve 202.

  In the second conveyor mode, the controller 210 sets the load pressure of the first conveyor hydraulic motor 22 obtained from the first detected pressure signal to the load pressure of the second conveyor hydraulic motor 23 obtained from the second detected pressure signal. Regardless, the power Wd2 is supplied to the solenoid 203c of the second direction control valve 203.

  The hydraulic drive device 200 includes an operation dial 211 that is different from the operation dials of the other embodiments. The operation dial 211 has a fourth mark 212, and outputs a normal mode command signal (electric signal) in a state where the pointer 56 a points to the fourth mark 212.

  The controller 210 is set to enter the normal mode when the normal mode command signal from the operation dial 211 is input. In this normal mode, the controller 210 does not supply the power Wd1 to the solenoid 202d of the first directional control valve 202 or supply the power Wd2 to the solenoid 203c of the second directional control valve 203. In the normal mode as well as the other modes, the controller 210 performs the solenoid 31a of the sorting device control valve 31, the solenoid 32a of the first conveyor control valve 32, the solenoid 33a of the second conveyor control valve 33, and a spare. Electric power Ws, Wc1, Wc2, and Wr are supplied to the solenoids 102a of the control valve 102, respectively.

  In the hydraulic drive device 200 configured as described above, the oil discharged from the main pump 25 is supplied to each of the first conveyor hydraulic motor 22 and the second conveyor hydraulic motor 23 as follows.

<Auto mode>
In the auto mode, the controller 210 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the spare control valve 102, respectively. Are supplied with electric power Ws, Wc1, Wc2, and Wr, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 are set. Switch to operating position.

  The controller 210 maintains the state of outputting the electric power Ws, Wc1, Wc2, and Wr, while the first detection pressure signal S1 from the first pressure sensor 61 and the second detection pressure signal from the second pressure sensor 62. S2 is periodically input at time intervals of milliseconds, and the first and second determinations are performed each time the S2 is input.

  The determination result is negative, that is, the determination result is that the load pressure of the first conveyor hydraulic motor 22 is neither higher nor lower than the load pressure of the second conveyor hydraulic motor 23. At this time, the controller 210 neither supplies the power Wd1 to the solenoid 202d of the first directional control valve 202 nor supplies the power Wd2 to the solenoid 203c of the second directional control valve 203. As a result, the first and second directional control valves 202 and 203 are both held at the initial positions, and the ratio changing circuit 201 is held in the third state.

  In the third state, the pressure oil guided from the auxiliary control valve 102 to the auxiliary supply line 104 is guided to the flow dividing valve 204 through the second direction control valve 203, the first direction control valve 202 and the connection line 205. Then, the flow is divided into 1: 1 by the flow dividing valve 204. The pressure oil discharged from the first outlet 204b is guided to the first conveyor supply line 36 through the first merge pipe 206, and the pressure oil discharged from the second outlet 204c is passed through the second merge pipe 207. It is led to the supply line 37 for the second conveyor.

  Thereby, the relationship between the flow rates fs, fc1, fc2, and fa is the relationship between the flow rates Fs, Fc1 + Fr / 2, Fc2 + Fr / 2, and Fa (Fs, Fc1 + Fr / 2, Fc2 + Fr / 2, Fa = 4: 2 + 1: 2 + 1: 10). Is set to “fs, fc1, fc2 = 4: 3: 3: 10”. At this time, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 3: 3: 6”.

  When the result of the first determination is true, that is, the determination result is that the load pressure of the first conveyor hydraulic motor 22 is higher than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 210 performs the first direction control. Electric power Wd1 is supplied to the solenoid 202d of the valve 202, and electric power Wd2 is not supplied to the solenoid 203c of the second direction control valve 203. As a result, the valve position of the first directional control valve 202 is switched to the operating position, and the valve position of the second directional control valve 203 is held at the initial position. That is, the ratio changing circuit 201 changes to the first state.

  In the first state, the pressure oil guided from the auxiliary control valve 102 to the auxiliary supply line 104 passes through the second directional control valve 203, the first directional control valve 202, and the first merging pipe line 206. It is led to the supply pipeline 36 and not to the second conveyor feed pipeline 37.

  Accordingly, the relationship between the flow rates fs, fc1, fc2, and fa is the same as the relationship between the flow rates Fs, Fc1 + Fr, Fc2, and Fa (Fs: Fc1 + Fr: Fc2: Fa = 4: 2 + 2: 2: 10) (fs: fc1: fc2). : Fa = 4: 4: 2: 10). That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is different from “R1: R2: R12 = 3: 3: 6” without increasing or decreasing the total ratio R12 “R1: R2: R12 = 4: 2: 6 ”.

  When the result of the second determination is true, that is, the determination result that the load pressure of the first conveyor hydraulic motor 22 is lower than the load pressure of the second conveyor hydraulic motor 23 by a predetermined value or more, the controller 210 performs the first direction control. Electric power Wd1 is not supplied to the solenoid 202d of the valve 202, and electric power Wd2 is supplied to the solenoid 203c of the second direction control valve 203. As a result, the valve position of the first directional control valve 202 is held at the initial position, and the valve position of the second directional control valve 203 is switched to the operating position. That is, the ratio changing circuit 201 changes to the second state.

  In the second state, the pressure oil introduced from the auxiliary control valve 102 to the auxiliary supply line 104 is introduced to the second conveyor supply line 37 through the second directional control valve 203 and the second merge line 207. However, it is not led to the supply line 36 for the first conveyor.

  Accordingly, the relationship between the flow rates fs, fc1, fc2, and fa is the same as the relationship between the flow rates Fs, Fc1, Fc2 + Fr, and Fa (Fs: Fc1: Fc2 + Fr: Fa = 4: 2: 2 + 2: 10) (fs: fc1: fc2). : Fa = 4: 2: 4: 10). That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is “R1: R2: R12 = 3: 3: 6” and “R1: R2: R12 = 4: “R1: R2: R12 = 2: 4: 6”, which is different from “2: 6”.

<First conveyor mode>
In the first conveyor mode, the controller 210 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the spare control valve 102. Are supplied with electric power Ws, Wc1, Wc2, and Wr, respectively, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 To the operating position. Further, the power Wd1 is supplied to the solenoid 202d of the first directional control valve 202 regardless of the load pressure of the hydraulic motor 22 for the first conveyor and the load pressure of the hydraulic motor 23 for the second conveyor, and the second directional control valve The power Wd2 is not supplied to the solenoid 203c of 203. As a result, the valve position of the first directional control valve 202 is switched to the operating position, and the valve position of the second directional control valve 203 is held at the initial position. That is, the ratio changing circuit 201 enters the first state.

  In the first state, as described above, the pressure oil introduced from the auxiliary control valve 102 to the auxiliary machine supply line 104 is supplied to the second direction control valve 203, the first direction control valve 202, and the first merge line. It is guided to the first conveyor supply line 36 through 206 and is not guided to the second conveyor supply line 37. Accordingly, the relationship between the flow rates fs, fc1, fc2, and fa is set to “fs: fc1: fc2: fa = 4: 4: 2: 10”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 4: 2: 6”.

<Second conveyor mode>
In the second conveyor mode, the controller 210 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the standby control valve 102. Are supplied with electric power Ws, Wc1, Wc2, and Wr, respectively, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 To the operating position. The controller 210 does not supply the power Wd1 to the solenoid 202d of the first direction control valve 202 regardless of the load pressure of the first conveyor hydraulic motor 22 or the load pressure of the second conveyor hydraulic motor 23. The electric power Wd2 is supplied to the solenoid 203c of the second direction control valve 203. As a result, the valve position of the first directional control valve 202 is held at the initial position, and the valve position of the second directional control valve 203 is switched to the operating position. That is, the ratio changing circuit 201 enters the second state.

  In the second state, as described above, the pressure oil introduced from the auxiliary control valve 102 to the auxiliary supply pipe 104 is supplied to the second conveyor through the second directional control valve 203 and the second merge pipe 207. It is led to the pipe line 37 and is not led to the first conveyor supply pipe line 36. Accordingly, the relationship between the flow rates fs, fc1, fc2, and fa is set to “fs: fc1: fc2: fa = 4: 2: 4: 10”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set from “R1: R2: R12 = 3: 3: 6” to “R1: R2: R12 = 2: 4: 6”. become.

<Normal mode>
In the normal mode, the controller 210 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the spare control valve 102, respectively. Are supplied with electric power Ws, Wc1, Wc2, and Wr, and all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 are set. Switch to operating position.

  The controller 210 also supplies power Wd1 to the solenoid 202d of the first directional control valve 202 regardless of the load pressure of the first conveyor hydraulic motor 22 or the load pressure of the second conveyor hydraulic motor 23. The power Wd2 is not supplied to the solenoid 203c of the two-way control valve 203. Thus, both the first and second directional control valves 202 and 203 are held at the initial positions. That is, the ratio changing circuit 201 enters the third state.

  In the third state, as described above, the pressure oil introduced from the auxiliary control valve 102 to the auxiliary machine supply line 104 passes through the second direction control valve 203, the first direction control valve 202, and the connection line 205. The flow is guided to the diversion valve 204 and diverted 1: 1 by the diversion valve 204. The pressure oil discharged from the first outlet 204b is guided to the first conveyor supply line 36 through the first merge pipe 206, and the pressure oil discharged from the second outlet 204c is passed through the second merge pipe 207. It is led to the supply line 37 for the second conveyor. Thus, the relationship between the flow rates fs, fc1, fc2, and fa is set to “fs, fc1, fc2 = 4: 3: 3: 10”. That is, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 is set to “R1: R2: R12 = 3: 3: 6”.

  Thus, according to the hydraulic drive device 200 according to the fourth embodiment, the first ratio R1 that is the ratio of the flow rate distributed to the first conveyor hydraulic motor 22 in the discharge flow rate of the main pump 25, and the main pump 25. The setting of the relationship with the second ratio R2, which is the ratio of the flow rate distributed to the second conveyor hydraulic motor 23, is made without increasing or decreasing the total ratio R12 of the first ratio R1 and the second ratio R2. It can be selected from “R1: R2 = 3: 3”, “R1: R2 = 4: 2” and “R1: R2 = 2: 4”. As a result, the excess of the transfer capability that occurs in one of the first and second conveyors 12 and 13 can be used to compensate for the shortage of transfer capability that occurs in the other conveyor. Therefore, a situation in which the work capacity of the entire processing machine is limited due to a shortage of the transport capacity of the other conveyor, although there is a surplus in the transport capacity of one of the first and second conveyors 12 and 13 is conventionally known. It can be made less likely to occur.

  In addition, if the processing machine to which the hydraulic drive device 200 according to the above-described fourth embodiment is applied is also provided with a sorting device, a first conveyor, and a second conveyor, as in the first embodiment, it is self-propelled. But it doesn't have to be self-propelled.

  The self-propelled sieving machine to which the hydraulic drive device 200 according to the above-described fourth embodiment is applied is also a finger-type sieving machine equipped with a vibrating sieving apparatus having a mesh floor, as in the first embodiment. It may be one equipped with a vibrating sieve device having a vibrating floor.

  The self-propelled processing machine to which the hydraulic drive device 200 according to the above-described fourth embodiment is applied may be a self-propelled sieve or a self-propelled crusher as in the first embodiment.

[Fifth Embodiment]
FIG. 7 is a hydraulic circuit diagram showing a hydraulic drive apparatus according to the fifth embodiment of the present invention. Among those shown in FIG. 7, the same reference numerals as those in FIG. 6 are used for those equivalent to those shown in FIG. 6.

  The hydraulic drive apparatus 300 according to the fifth embodiment includes an auxiliary hydraulic motor 301 and a ratio changing circuit 302 (hydraulic circuit). The ratio changing circuit 302 is obtained by adding a third direction control valve 303 to the ratio changing circuit 201 in the fourth embodiment. The third direction control valve 303 is interposed between the auxiliary hydraulic motor 301 and the first direction control valve 202 and between the flow dividing valve 204 and the first direction control valve 202. The third direction control valve 303 is also a spring return type electromagnetic pilot type valve, and has a first outlet 303a and a second outlet 303b. The first outlet 303 a communicates with the inlet 204 a of the flow dividing valve 204 through the connection pipe line 205. The second outlet 303 b communicates with the inlet 301 a of the auxiliary hydraulic motor 301. When the valve position of the third directional control valve 303 is the initial position, the first outlet 202b of the first directional control valve 202 and the inlet of the diversion valve 204 communicate with each other via the third directional control valve 303. When the valve position of the third directional control valve 303 is the operating position, the first outlet 202 b of the first directional control valve 202 and the inlet 301 a of the auxiliary hydraulic motor 301 communicate with each other via the third directional control valve 303.

  The hydraulic drive device 300 includes an operation dial 304 that is different from the operation dials of the other embodiments. The operation dial 304 has a fifth mark 305, and outputs an accessory mode command signal (electrical signal) in a state where the pointer 56a points to the fifth mark 305.

  The controller 306 is also different from that of the other embodiments. The controller 306 is set to enter the auxiliary machine mode when the auxiliary machine mode command signal from the operation dial 304 is input. In this accessory mode, the controller 306 does not supply the power Wd1 to the solenoid 202d of the first directional control valve 202 or supply the power Wd2 to the solenoid 202c of the second directional control valve 203, but in the third direction. Electric power Wd3 is supplied to the solenoid 303c of the control valve 303. In addition, in the auxiliary mode as in the other modes, the solenoid 31a of the control valve 31 for the sorting device, the solenoid 32a of the control valve 32 for the first conveyor, the solenoid 33a of the control valve 33 for the second conveyor, and the spare control valve 102 Each of the solenoids 102a is supplied with electric power Ws, Wc1, Wc2, and Wr.

  In modes other than the accessory mode, the controller 306 does not supply the power Wd3 to the solenoid 303c of the third direction control valve 303.

  In the ratio changing circuit 302, the valve position of the third direction control valve 303 is the initial position, the valve position of the second direction control valve 203 is the initial position, and the valve position of the first direction control valve 202 is the operating position. The second conveyor hydraulic motor 23 is guided to the first conveyor hydraulic motor 22 from the spare control valve 102 through the second directional control valve 203, the first directional control valve 202, and the first merge pipe 206. In addition, the auxiliary oil hydraulic motor 301 is in a first state in which no pressure oil is guided. Further, when the valve position of the second directional control valve 203 is the operating position, pressure oil is guided from the spare control valve 102 to the second conveyor hydraulic motor 23 through the second directional control valve 203 and the second merge pipe 207. However, the second state is reached in which no pressure oil is guided to the first conveyor hydraulic motor 22 or the auxiliary hydraulic motor 301. In addition, when the valve position of the third direction control valve 303 is the operating position, the pressure oil is guided from the auxiliary control valve 102 to the auxiliary hydraulic motor 301 while the hydraulic motors 22 and 23 for the first and second conveyors are in operation. In any case, the pressure oil is not guided to the third state. That is, the first and second direction switching valves 201 and 202 and the third direction switching valve 303 constitute switching means capable of switching the ratio changing circuit 302 to the first to third states.

  Further, when the valve position of the third direction control valve 303 is the initial position and the valve positions of both the first and second direction control valves 202 and 203 are the initial positions, the pressure oil is divided from the spare control valve 102. While being distributed to the hydraulic motors 22 and 23 for the first and second conveyors through the valve 204, a fourth state (state shown in FIG. 7) in which no pressure oil is guided to the auxiliary hydraulic actuators. That is, the diversion valve 204 is a distributing unit that distributes the pressure oil from the preliminary control valve 102 to the first and second conveyor hydraulic motors 22 and 23 even in the fifth embodiment.

  In the hydraulic drive apparatus 300 configured as described above, the oil discharged from the main pump 25 is supplied to each of the first conveyor hydraulic motor 22 and the second conveyor hydraulic motor 23 as follows.

<Modes other than auxiliary mode>
In modes other than the accessory mode, that is, in the auto mode, the first conveyor mode, the second conveyor mode, and the normal conveyor mode, the controller 306 does not supply the power Wd3 to the solenoid 303c of the third direction control valve 303, and performs the third direction control. The valve position of the valve 303 is held at the initial position. In this state, the same thing as the case of 4th Embodiment is performed, and 1st, 2nd ratio R1, R2 is set.

<Auxiliary machine mode>
In the accessory mode, the controller 306 includes a solenoid 31a of the sorting device control valve 31, a solenoid 32a of the first conveyor control valve 32, a solenoid 33a of the second conveyor control valve 33, and a solenoid 102a of the spare control valve 102. Supplying electric power Ws, Wc1, Wc2, and Wr to each of them, all valve positions of the control valve 31 for the sorting device, the control valve 32 for the first conveyor, the control valve 33 for the second conveyor, and the spare control valve 102 To the operating position.

  The controller 306 supplies the power Wd3 to the solenoid 303c of the third direction control valve 303. The supply of the power Wd1 to the solenoid 202d of the first direction control valve 202 is also supplied to the solenoid 203c of the second direction control valve 203. The power Wd2 is not supplied. As a result, the first and second directional control valves 202 and 201 are both held at the initial position, and the ratio changing circuit 302 is held in the fourth state.

  In the fourth state, the pressure oil introduced from the auxiliary control valve 102 to the auxiliary supply line 104 passes through the second direction control valve 202, the first direction control valve 203, and the third direction control valve 303. Guided to the hydraulic motor 301.

  As a result, the relationship between the flow rates fs, fc1, fc2, and fa is similar to the relationship between the flow rates Fs, Fc1, Fc2, and Fa (Fs, Fc1, Fc2, Fa = 4: 2: 2: 8). fc2 = 4: 2: 2: 8 ”. That is, when an auxiliary machine is used, the relationship between the first ratio R1, the second ratio R2, and the total ratio R12 decreases by the ratio of the flow rate at which the total ratio R12 is distributed to the auxiliary hydraulic motor 301. Thus, “R1: R2: R12 = 2: 2: 4” is set.

  As described above, according to the hydraulic drive device 300 according to the fifth embodiment, similarly to the hydraulic drive device 300 according to the fourth embodiment, the setting of the relationship between the first ratio R1 and the second ratio R2 is increased or decreased. Without selection, it can be selected from “R1: R2 = 3: 3”, “R1: R2 = 4: 2” and “R1: R2 = 2: 4”. Thereby, the excess of the conveyance capability which arises in one conveyor of the 1st, 2nd conveyors 12 and 13 can be utilized for supplementing the lack of conveyance capability which arises in the other conveyor. Therefore, a situation in which the work capacity of the entire processing machine is limited due to a shortage of the transport capacity of the other conveyor, although there is a surplus in the transport capacity of one of the first and second conveyors 12 and 13 is conventionally known. It can be made less likely to occur.

  In addition, when the auxiliary machine is used, the first and second ratios can be fixed to stabilize the flow rate of the pressure oil supplied to the auxiliary machine hydraulic motor 301.

  In addition, if the processing machine to which the hydraulic drive device 300 according to the above-described fifth embodiment is applied is also provided with a sorting device, a first conveyor, and a second conveyor, as in the first embodiment, it is self-propelled. But it doesn't have to be self-propelled.

  The self-propelled sieving machine to which the hydraulic drive device 300 according to the above-described fifth embodiment is applied is also a finger-type sieving machine equipped with a vibrating sieving apparatus having a mesh floor, as in the first embodiment. It may be one equipped with a vibrating sieve device having a vibrating floor.

  The self-propelled processing machine to which the hydraulic drive device 300 according to the fifth embodiment is applied may be a self-propelled sieving machine or a self-propelled crusher as in the first embodiment.

DESCRIPTION OF SYMBOLS 1 Self-propelled sieving machine 2 Running body 2a, 2b Track frame 3 Main body frame 3a Lower frame 4 Drive wheel 5 Driven wheel 6A, 6B Crawler track 7 Hopper 10 Vibrating sieve device (sorting device)
DESCRIPTION OF SYMBOLS 11 Screen box 11a Mesh floor 12 1st conveyor 13 2nd conveyor 14 Power unit 20 Hydraulic drive device 21 Hydraulic motor for sorting devices (Hydraulic actuator for sorting devices)
21a Inlet 21b Outlet 22 First conveyor hydraulic motor (first conveyor hydraulic actuator)
22a Inlet 22b Outlet 23 Second conveyor hydraulic motor (second conveyor hydraulic actuator)
23a Inlet 23b Outlet 24 Engine 25 Main pump 26 Pilot pump 27 Hydraulic oil tank 30 Hydraulic control circuit 31 Control valve 31a for sorting device Solenoid 32 Control valve for first conveyor 32a Solenoid 33 Control valve for second conveyor 33a Solenoid 34 For sorting device Supply line 35 Sorting device return line 36 First conveyor supply line 37 First conveyor return line 38 Second conveyor supply line 39 Second conveyor return line 50 Ratio change circuit (ratio change means) )
51 Branch valve 51a Branch pipe 52 Direction control valve 52a First outlet 52b Second outlet 52c Solenoid 53 Return pipe 54 Junction pipe 55 Check valve 56 Operation dial 56a Pointer 57A First mark 57B Second mark 57C Third mark 60 controller 61 first pressure sensor 62 second pressure sensor

70 Self-propelled crusher 71 Grizzly feeder (sorting device)
72 Sorting Unit 73 Casing 74 Elastic Legs 74a, 74b Coil Spring 75 Flat Plate 76 First Grizzle River Row 76a First Grizzle River 77 Second Grizzle River Row 77a Second Grizzle River 78 Crushing Device

90 Hydraulic Drive Device 91 First Conveyor Control Valve 91a Proportional Solenoid (First Stepless Control Unit, Ratio Changing Unit)
92 Second conveyor control valve 92a Proportional solenoid (second stepless control means, ratio changing means)
93 controller (first and second stepless control means, ratio changing means)
94 Operation dial

100 Hydraulic Drive Device 101 Ratio Change Circuit (Ratio Change Means)
102 Preliminary control valve 102a Solenoid 103 Direction control valve 103a First outlet 103b Second outlet 103c Solenoid 104 Auxiliary supply line 105 First merge line 106 Second merge line 107 Controller

200 Hydraulic Drive Device 201 Ratio Change Circuit (Ratio Change Means)
202 First direction control valve 202a Inlet 202b First outlet 202c Second outlet 202d Solenoid 203 Second direction control valve 203a First outlet 203b Second outlet 203c Solenoid 204 Flow dividing valve 204a Inlet 204b First outlet 204c Second outlet 205 Connection pipe Path 206 first merging pipe line 207 second merging pipe line 208, 209 check valve 210 controller 211 operation dial 212 fourth mark

300 Hydraulic Drive Device 301 Auxiliary Hydraulic Motor 301a Inlet 302 Ratio Change Circuit (Ratio Change Means)
303 Third direction control valve 303a First outlet 303b Second outlet 303c Solenoid 304 Operation dial 305 Fifth mark 306 Controller

Claims (7)

A hydraulic actuator for a sorting device that drives a sorting device into which a sorting object is charged and sorts into a larger one and a smaller one than a predetermined particle size;
A hydraulic actuator for a first conveyor that drives a first conveyor that transports a small granular material smaller than the predetermined particle size sorted by the sorting device;
A hydraulic actuator for a second conveyor that drives a second conveyor that conveys a large granular material larger than the predetermined particle size selected by the sorting device or a crushed material crushed by the crushing device;
A hydraulic pump that is shared by the hydraulic actuators for the first and second conveyors and that discharges the pressure oil supplied to the hydraulic actuators for the first and second conveyors;
In a hydraulic drive device for a processing machine, comprising: a hydraulic control circuit that distributes oil discharged from the hydraulic pump to the hydraulic actuator for the sorting device, the hydraulic actuator for the first conveyor, and the hydraulic actuator for the second conveyor;
Of the discharge flow rate of the hydraulic pump, the first rate that is the rate of the flow rate distributed to the hydraulic actuator for the first conveyor, and the flow rate distributed to the hydraulic actuator for the second conveyor of the discharge flow rate of the hydraulic pump. A hydraulic drive device for a processing machine, characterized in that a ratio changing means for changing a second ratio, which is a ratio, without changing the total ratio of the first ratio and the second ratio is provided. In the hydraulic drive device of the processing machine according to claim 1,
Between the first conveyor hydraulic actuator and the hydraulic pump, there is a first conveyor control valve capable of switching between supply of pressure oil to the first conveyor hydraulic actuator and stop of the supply,
Between the second conveyor hydraulic actuator and the hydraulic pump, there is a second conveyor control valve capable of switching between supply of pressure oil to the second conveyor hydraulic actuator and stop of the supply,
The ratio changing means is
Lead oil is guided from the first conveyor control valve to the first conveyor hydraulic actuator, or from the first conveyor supply valve, or from the second conveyor control valve to the second conveyor hydraulic actuator. A hydraulic drive device for a processor, which is provided on at least one of the supply lines for the second conveyor and guides a part of the flow rate of the pressure oil from one supply line to the other supply line. . In the hydraulic drive device of the processing machine according to claim 1,
Between the first conveyor hydraulic actuator and the hydraulic pump, there is a first conveyor control valve capable of switching between supply of pressure oil to the first conveyor hydraulic actuator and stop of the supply,
Between the second conveyor hydraulic actuator and the hydraulic pump, there is a second conveyor control valve capable of switching between supply of pressure oil to the second conveyor hydraulic actuator and stop of the supply,
The ratio changing means is
First stepless control means capable of steplessly controlling the opening degree of the first conveyor control valve, and second stepless control means capable of steplessly controlling the opening degree of the second conveyor control valve. Prepared,
By changing the opening of the first conveyor control valve by the first stepless control means and changing the opening of the second conveyor control valve by the second stepless control means, 2. A hydraulic drive device for a processing machine, characterized in that a change of two ratios is realized. In the hydraulic drive device of the processing machine according to claim 1,
Between the first conveyor hydraulic actuator and the hydraulic pump, there is a first conveyor control valve capable of switching between supply of pressure oil to the first conveyor hydraulic actuator and stop of the supply,
Between the second conveyor hydraulic actuator and the hydraulic pump, there is a second conveyor control valve capable of switching between supply of pressure oil to the second conveyor hydraulic actuator and stop of the supply,
When an auxiliary hydraulic actuator serving as a drive source for the auxiliary is provided, the auxiliary hydraulic actuator is interposed between the hydraulic pump and the hydraulic pump for supplying the auxiliary hydraulic actuator, A spare control valve capable of switching between the supply stop and the stop is provided,
The ratio changing means is
Switchable switching between a first state in which pressure oil is guided from the preliminary control valve to the first conveyor hydraulic actuator and a second state in which pressure oil is guided from the preliminary control valve to the second conveyor hydraulic actuator A hydraulic drive apparatus for a processing machine, characterized in that the apparatus is a means. In the hydraulic drive device of the processing machine according to claim 1,
Between the first conveyor hydraulic actuator and the hydraulic pump, there is a first conveyor control valve capable of switching between supply of pressure oil to the first conveyor hydraulic actuator and stop of the supply,
Between the second conveyor hydraulic actuator and the hydraulic pump, there is a second conveyor control valve capable of switching between supply of pressure oil to the second conveyor hydraulic actuator and stop of the supply,
When an auxiliary hydraulic actuator serving as a drive source for the auxiliary is provided, the auxiliary hydraulic actuator is interposed between the auxiliary hydraulic actuator and the hydraulic pump, so that supply of pressure oil to the auxiliary hydraulic actuator is performed. And a preliminary control valve that can be switched between the supply stop and
The ratio changing means is
Switchable switching between a first state in which pressure oil is guided from the preliminary control valve to the first conveyor hydraulic actuator and a second state in which pressure oil is guided from the preliminary control valve to the second conveyor hydraulic actuator Means,
A hydraulic drive apparatus for a processor, comprising: a distribution unit that is provided downstream of the switching unit and distributes the pressure oil to the hydraulic actuators for the first and second conveyors. In the hydraulic drive device of the processing machine according to claim 1,
Between the first conveyor hydraulic actuator and the hydraulic pump, there is a first conveyor control valve capable of switching between supply of pressure oil to the first conveyor hydraulic actuator and stop of the supply,
Between the second conveyor hydraulic actuator and the hydraulic pump, there is a second conveyor control valve capable of switching between supply of pressure oil to the second conveyor hydraulic actuator and stop of the supply,
Auxiliary hydraulic actuator, which is a drive source of the auxiliary machine, is interposed between the auxiliary hydraulic actuator and the hydraulic pump, and supplies pressure oil to the auxiliary hydraulic actuator and stops the supply. A switchable spare control valve is provided,
The ratio changing means is
A first state in which pressure oil is guided from the preliminary control valve to the first conveyor hydraulic actuator; a second state in which pressure oil is guided from the preliminary control valve to the second conveyor hydraulic actuator; and the preliminary control Switching means switchable from a valve to a third state for guiding pressure oil to the auxiliary hydraulic actuator;
A hydraulic drive apparatus for a processor, comprising: a distribution unit that is provided downstream of the switching unit and distributes the pressure oil to the hydraulic actuators for the first and second conveyors. A sorting device into which an object to be sorted is input and sorts into a larger one and a smaller one than a predetermined particle size, a first conveyor that conveys a small granular material smaller than the predetermined particle size sorted by the sorting device, and the sorting A second conveyor for conveying a large granular material larger than the predetermined particle size selected by the apparatus or a crushed material crushed by the crushing apparatus, and a hydraulic drive for driving the sorting apparatus, the first conveyor and the second conveyor In a self-propelled processing machine comprising a main body frame that supports the apparatus and a traveling body provided in the main body frame
A self-propelled processing machine comprising the hydraulic drive device according to any one of claims 1 to 6 as the hydraulic drive device.

Images