JP2008168267A - Crusher - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a crusher which aims an improvement of a fuel cost, and at the same time, can aim an increase in long life span of parts in a carrier device conveying a crushed material produced. <P>SOLUTION: The crusher comprises a crushing device 6 which compressively fractures a material to be crushed supplied from one side between two members 63, 64 by operating one or both of two members 63, 64 to discharge the crushed material from the other side, the carrier device conveying the crushed material discharged from between ends of the other side of two members 63, 64, a spacing adjusting means 12 adjusting the spacing D of the other side ends of two members 63, 64 by a displacement, a displacement amount detecting means 13 for detecting an amount of the displacement of the spacing adjusting means 12, and a conveying speed control means for controlling a conveying speed of the carrier device depending on the amount of the displacement detected by the displacement amount detecting means 13. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  TECHNICAL FIELD The present invention relates to a crusher that crushes objects to be crushed, such as concrete lumps, asphalt concrete lumps, and natural stones, to produce crushed materials such as crushed stones.

  Conventionally, there is a self-propelled crusher as a machine for producing a product such as crushed stone by crushing a raw material such as rock finely. This self-propelled crusher has a configuration in which a hopper, a vibration feeder, a jaw crusher (hereinafter referred to as a crusher), a main conveyor, a side conveyor, a magnetic separator, and a power unit are mounted on a crawler type traveling body. The jaw crusher has a configuration in which a fixed tooth receiving plate and a moving tooth plate arranged opposite to each other with a space between the tooth receiving plate are provided, and between the tooth receiving plate and the moving tooth plate. The raw material is compressed and crushed by rocking the moving tooth plate with the raw material interposed therebetween, and the crushed crushed material is discharged from the gap between the lower end of the tooth receiving plate and the lower end of the moving tooth plate. Some conventional self-propelled crushers are provided with an interval adjusting mechanism for adjusting the interval between the lower end of the tooth receiving plate and the lower end of the moving tooth plate by moving the moving tooth plate with a cylinder or the like. By adjusting the interval by this interval adjusting mechanism, the particle size of the crushed material to be produced can be adjusted.

When the raw material is crushed by the self-propelled crusher having the above-described configuration, first, the raw material is put into a hopper. The raw material thrown into the hopper is conveyed by the vibration feeder and supplied to the crusher. At this time, the dirt such as earth and sand adhering to the raw material is screened by the vibration of the vibration feeder, and the screened sand is discharged to the outside by the side conveyor. The raw material supplied to the crusher is compressed and crushed by the tooth receiving plate and the moving tooth plate, and the crushed crushed material is discharged from the gap between the lower end of the tooth receiving plate and the lower end of the moving tooth plate. The discharged crushed material is conveyed by the main conveyor and is carried out of the machine as a product. In addition, the iron scrap etc. which were mixed in the crushed material are removed by the magnetic separator on the main conveyor (for example, refer patent documents 1-5).
JP 2005-270847 A JP 2005-305277 A JP 2004-188251 A JP 2006-175393 A JP 2006-110421 A

  By the way, when the crushing operation is performed using the crusher having the above-described configuration, actually, there are few cases of producing a crushed material having a large particle size, and many cases producing a crushed material having a small particle size. When producing a crushed material with a small particle size, the gap between the lower end of the toothed plate and the lower end of the moving tooth plate will be narrowed. The amount of discharged crushed material is reduced. However, in the conventional crusher described above, when the discharge amount of crushed material from the crusher is the maximum, that is, when the interval between the lower end of the tooth receiving plate and the lower end of the moving tooth plate is expanded to the maximum, The speed of the main conveyor is set, and the main conveyor is always operated at the maximum speed corresponding to the maximum discharge amount of crushed material. For this reason, when the discharge amount of the crushed material from the crusher is small as described above, the conveyance speed of the main conveyor is too high with respect to the discharge amount of the crushed material. That is, the discharge amount of the crushed material and the conveyance speed of the main conveyor are not matched, and the main conveyor is operating unnecessarily fast. As described above, in the conventional crusher, the conveyance speed of the main conveyor often does not correspond to the discharge amount of the crushed material, so that not only fuel consumption is bad, but also the life of the main conveyor parts such as belts and bearings is shortened. There is a problem of becoming.

  The present invention takes the above-described conventional problems into consideration, and improves the fuel consumption and can increase the life of parts of a main conveyor (conveying device) that conveys the crushed material produced. The purpose is to provide a machine.

  In the crusher according to the present invention, one or both of the two members are moved to compress and crush the material to be crushed supplied from one side between the two members between the two members, and crush the material from the other side. A crushing device for discharging the crushing material, a conveying device for conveying crushed material discharged from between the other end portions of the two members, and an interval adjusting means for adjusting the distance between the other end portions of the two members by displacing And a displacement amount detecting means for detecting the displacement amount of the interval adjusting means, and a transport speed control means for controlling the transport speed of the transport device according to the displacement amount detected by the displacement amount detecting means. It is characterized by.

  Due to such a feature, the distance between the other end portions of the two members is adjusted by displacing the distance adjusting means. Further, the displacement amount of the interval adjusting means at this time is detected by the displacement amount detecting means. The displacement amount detected by the displacement amount detection means changes according to the interval between the other end portions of the two members. On the other hand, the transport speed control unit controls the transport speed of the transport device according to the displacement amount detected by the displacement amount detection unit. That is, the transport speed of the transport device is controlled according to the distance between the other end portions of the two members, and the transport speed of the transport device becomes a speed corresponding to the distance between the two members. Since the discharge amount of the crushed material changes in accordance with the interval between the other end portions of the two members, the transfer device is operated at a transfer speed corresponding to the discharge amount of the crushed material. Specifically, the larger the distance between the two members, the faster the conveying speed of the conveying device, and the smaller the distance between the two members, the slower the conveying speed of the conveying device.

  In the crusher according to the present invention, the conveyance speed control means includes a standard conveyance speed setting means for setting a standard conveyance speed of the conveyance device based on the number of rotations of the prime mover, and a displacement amount detected by the displacement amount detection means. Speed correction coefficient setting means for setting the speed correction coefficient based on the above, optimum transfer speed setting means for correcting the standard transfer speed by the correction coefficient to set the optimal transfer speed of the transfer apparatus, and operating the transfer apparatus at the optimal transfer speed Thus, it is preferable that a command value setting means for setting a command value to be sent to the transport device control valve for controlling driving of the transport device drive device is provided.

  As a result, the standard transport speed is set by the standard transport speed setting means based on the rotational speed of the prime mover, and the speed correction coefficient is set by the speed correction coefficient setting means based on the displacement amount of the interval adjusting means. Then, the standard transport speed is corrected by the speed correction coefficient by the optimal transport speed setting means, and the optimal transport speed is set. Based on this optimal transport speed, the command value to be sent to the control valve for the transport device is set by the command value setting means. Then, the transport device control valve is switched based on the command value, and the drive of the transport device drive device is controlled.

  Further, the crusher according to the present invention includes a crushing device driving device provided in the crushing device and a hydraulic driving means for driving the conveying device driving device provided in the conveying device by hydraulic pressure. Controls the hydraulic pump driven by the prime mover, the hydraulic circuit for transmitting the hydraulic pressure from the hydraulic pump to the crushing device driving device and the conveying device driving device, respectively, and the flow rate of the pressure oil sent to the conveying device driving device It is preferable that the transfer device control valve is capable of controlling the transfer speed of the transfer device by controlling the transfer device control valve.

  As a result, only the drive of the transport device drive device is adjusted without changing the drive of another device having the same drive source (prime mover) as the transport device.

  According to the crusher of claim 1 of the present invention, since the conveying device is operated at a conveying speed corresponding to the amount of crushed material discharged from the crushing device, fuel consumption can be improved and It is possible to extend the service life of the parts of the conveying device that conveys the crushed material.

  According to the crusher of claim 2 of the present invention, since the drive of the transport device drive device is controlled based on the amount of displacement of the interval adjusting means, the transport speed of the transport device is set to the other side of the two members. The speed can be adjusted according to the distance between the end portions.

  Moreover, according to the crusher of Claim 3 of this invention, since only the drive of the drive device for conveyance apparatuses is adjusted, a conveyance apparatus can be operated with the conveyance speed corresponding to the discharge amount of a crushed material.

  Hereinafter, the self-propelled crusher 1 which is one Example of the crusher which concerns on this invention is demonstrated based on drawing.

First, the configuration of the self-propelled crusher 1 will be described.
FIG. 1 is a side view showing the overall configuration of the self-propelled crusher 1, FIG. 2 is a plan view showing the overall configuration of the self-propelled crusher 1, and FIG. It is sectional drawing showing the whole structure. In this embodiment, the lower side in FIGS. 1, 2, and 3 is the forward direction, the upper side is the rear direction, the left side in FIG. 2 is the right direction, and the right side is the left direction.

  As shown in FIG. 1 to FIG. 3, the self-propelled crusher 1 carries in a crushed material X such as rock as a raw material, crushes the crushed material X that is carried in, and crushed crushed material such as crushed stone. A machine that carries Y out as a product. The self-propelled crusher 1 conveys the crawler-type traveling body 2, the hopper 3 for feeding the material to be crushed X, and the material to be crushed X fed from the hopper 3 to the crusher 6. The vibration feeder 4 for supplying the material to be crushed X, the side conveyor 5 for discharging the separated shear to the outside of the machine separately from the material to be crushed Y, the crusher 6 for compressing and crushing the material to be crushed X, and the crusher 6 The main conveyor 7 that conveys the crushed material Y discharged from the discharge port 67 and discharges the crushed material Y to the outside of the machine, and removes magnetic materials such as iron scrap contained in the crushed material Y conveyed by the main conveyor 7 A magnetic separator 8 and a power unit 9 are provided. The crusher 6 described above corresponds to a “crushing device”, the main conveyor 7 corresponds to a “conveying device”, and the power unit 9 corresponds to a “hydraulic drive unit”.

  The crusher 6 is a jaw crusher type crushing device. The crusher 6 is supported by a flywheel 60 that is rotated in the vertical direction by a hydraulic motor 106, a flywheel shaft 61 having a rotational axis that is eccentric with respect to the rotation center of the flywheel 60, and the flywheel shaft 61. A swing jaw 62, a moving tooth plate 63 attached to the swing jaw 62, and a tooth receiving plate 64 fixed in a standing state on the main body 24 of the traveling body 2 are provided. The moving tooth plate 63 and the tooth receiving plate 64 described above correspond to “two members” for compressing and crushing the object to be crushed.

  The moving tooth plate 63 and the tooth receiving plate 64 are arranged in the front-rear direction, and are arranged to face each other with a space therebetween. Further, the moving tooth plate 63 is disposed with a predetermined opening angle with respect to the tooth receiving plate 64 so that the distance between the moving tooth plate 63 and the tooth receiving plate 64 gradually decreases downward. Further, since the swing jaw 62 is supported by a flywheel shaft 61 having a rotation axis eccentric with respect to the rotation center of the flywheel 60 via a bearing, the swing jaw 62 swings in the front-rear direction as the flywheel 60 rotates. Be exercised. As the swing jaw 62 swings, the moving tooth plate 63 attached to the swing jaw 62 swings with respect to the fixed tooth receiving plate 64. Accordingly, a space between the moving tooth plate 63 and the tooth receiving plate 64 (hereinafter referred to as the crushing chamber 66) from the gap between the upper end of the moving tooth plate 63 and the upper end of the tooth receiving plate 64 (hereinafter referred to as a supply port 65). When the moving tooth plate 63 swings away from the tooth receiving plate 64, the object X to be crushed falls downward, and the moving tooth plate 63 swings in a direction approaching the tooth receiving plate 64. Then, when the moving tooth plate 63 swings again in a direction away from the tooth receiving plate 64, it further falls downward, and the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 are reduced. It is crushed to a size that can pass through a gap (hereinafter referred to as a discharge port 67). Then, the crushed material Y having a size that can pass through the discharge port 67 is discharged downward from the discharge port 67. Note that a cheek plate 68 that closes the side surface of the crushing chamber 66 is provided on both the left and right sides of the crushing chamber 66, and is gradually lowered downward by the cheek plate 68, the moving tooth plate 63, and the tooth receiving plate 64 on both sides. It is formed in a cylindrical shape that narrows.

  Also, the crusher 6 has a toggle block 15 disposed at a distance on the retreating side of the swing jaw 62 (the opposite side of the surface on which the moving tooth plate 63 is attached. In the present embodiment, the front side). A toggle plate 16 interposed between the lower end of the swing jaw 62 and the toggle block 15 is provided. The toggle block 15 is a reaction force receiving member that receives a crushing reaction force acting on the swing jaw 62 from the moving tooth plate 63 via the toggle plate 16 and is provided in a state of being fixed at a predetermined position. The toggle plate 16 is a plate-shaped reaction force transmission member sandwiched between the lower end portion of the swing jaw 62 and the toggle block 15. One end of the toggle plate 16 is brought into contact with a contact portion 62a provided on the back of the lower end portion of the swing jaw 62 (the surface on the retreating side of the swing jaw 62), and the other end of the toggle plate 16 is provided in the toggle block 15. The contact portion 15a is in contact with the contact portion 15a. By the toggle block 15 and the toggle plate 16 described above, the swing of the lower end portion of the moving tooth plate 63 is restricted, and the width of the discharge port 67 of the crusher 6 is determined.

  The crusher 6 is provided with a pulling mechanism 17 that pulls the swing jaw 62 backward. The tension mechanism 17 includes a tension rod 18 having one end attached to the lower end of the swing jaw 62 and extending to the retreat side of the swing jaw 62, and a tension spring 19 that urges the tension rod 18 to the retreat side. Yes. With the pulling mechanism 17 having the above-described configuration, the swing jaw 62 is always pulled backward, and the toggle plate 16 is prevented from coming off.

  The main conveyor 7 is a belt-conveyor-type conveying device that rotates a wide endless belt 71 in the form of a ring in the circumferential direction, and the crushed material Y or the like is conveyed by placing the crushed material Y or the like on the rotating endless belt 71. Is done. The main conveyor 7 extends in the front-rear direction of the self-propelled crusher 1, extends forward from a position directly below the undershoot 44, and a tip (front end) thereof projects forward. . By the main conveyor 7 having the above-described configuration, the crushed material Y and the like are discharged from the front end (front end) of the main conveyor 7 to the front of the self-propelled crusher 1.

FIG. 4 is a hydraulic circuit diagram showing the configuration of the power unit 9.
As shown in FIG. 4, the power unit 9 drives each of the above-described devices (the traveling body 2, the vibration feeder 4, the side conveyor 5, the crusher 6, the main conveyor 7, and the magnetic separator 8) with hydraulic pressure. It is the hydraulic drive means to make it. Specifically, the power unit 9 includes traveling body hydraulic motors 102 </ b> A and 102 </ b> B that respectively drive the traveling body 2, feeder hydraulic motor 104 that drives the vibration feeder 4, and side conveyor hydraulic pressure that drives the side conveyor 5. A motor 105, a crusher hydraulic motor 106 that rotates the flywheel 60 provided in the crusher 6, a main conveyor hydraulic motor 107 that drives the main conveyor 7, and a magnetic separator hydraulic motor 108 that drives the magnetic separator 8. Are driven respectively. The crusher hydraulic motor 106 described above corresponds to a “crushing device drive device”, and the main conveyor hydraulic motor 107 corresponds to a “conveyance device drive device”.

  The power unit 9 transmits the hydraulic pressure from the prime mover 100, the hydraulic pumps 101A and 101B driven by the prime mover 100, and the hydraulic motors 102A, 102B, 104, 105, 106, 107, and 108 from the hydraulic pumps 101A and 101B, respectively. The configuration includes a hydraulic circuit 103 and control valves 109A and 109B for distributing the pressure oil supplied from the hydraulic pumps 101A and 101B to the hydraulic motors 102A, 102B, 104, 105, 106, 107, and 108.

As the prime mover 100, an internal combustion engine (engine) such as a gasoline engine or a diesel engine can be used.
The hydraulic pumps 101A and 101B are pressure feeding devices that send pressure oil to the hydraulic circuit 103, and publicly known pumps can be used.
The prime mover 100 described above includes an accelerator dial (not shown) that adjusts the rotational speed of the prime mover 100. By adjusting the rotational speed of the prime mover 100 by this accelerator dial, the driving of the hydraulic pumps 101A and 101B is adjusted, and the hydraulic pressure sent to the hydraulic circuit 103 can be adjusted. Further, the information on the rotational speed of the prime mover 100 is output as a signal from the above-described accelerator dial.

  The pressure oil flowing in the hydraulic circuit 103 is sent from the hydraulic pumps 101A, 101B to the hydraulic motors 102A, 102B, 104, 105, 106, 107, 108, and further, the hydraulic motors 102A, 102B, 104, 105 , 106, 107, 108 are returned to the hydraulic pumps 101 A, 101 B and circulated in the hydraulic circuit 103. The hydraulic circuit 103 includes a first hydraulic circuit 103A that transmits hydraulic pressure to one traveling body hydraulic motor 102A, side conveyor hydraulic motor 105, main conveyor hydraulic motor 107, and magnetic separator hydraulic motor 108. There is a second hydraulic circuit 103B that transmits hydraulic pressure to the other traveling body hydraulic motor 102B, feeder hydraulic motor 104, and crusher hydraulic motor 106. The hydraulic circuit 103 includes a pilot circuit 103b in addition to the main circuit 103a represented by a solid line in FIG. 4, and a part of the pressure oil flowing through the main circuit 103a flows into the pilot circuit 103b. As a result, the pilot pressure is transmitted to the control valves 112A, 112B, 114, 115, 116, 117, and 118 described later.

  The control valves 109A and 109B include a first control valve 109A provided in the first hydraulic circuit 103A and a second control valve 109B provided in the second hydraulic circuit 103B. The first control valve 109A includes a traveling body control valve 112A for controlling the hydraulic pressure transmitted to one traveling body hydraulic motor 102A, and a side conveyor for controlling the hydraulic pressure transmitted to the side conveyor hydraulic motor 105. A control valve 115, a main conveyor control valve 117 for controlling the hydraulic pressure transmitted to the main conveyor hydraulic motor 107, and a magnetic separator control valve 118 for controlling the hydraulic pressure transmitted to the magnetic separator hydraulic motor 108 are provided. It has been. The second control valve 109B includes a traveling body control valve 112B that controls the hydraulic pressure transmitted to the other traveling body hydraulic motor 102B, and a vibration feeder that controls the hydraulic pressure transmitted to the feeder hydraulic motor 104. And a crusher control valve 116 for controlling the hydraulic pressure transmitted to the crusher hydraulic motor 106.

  Each of the control valves 112A, 112B, 114, 115, 116, 117, 118 described above is a valve capable of adjusting the flow rate of pressure oil and switching the direction (including opening / closing switching). Each of these control valves 112A, 112B, 114, 115, 116, 117, 118 is an electromagnetic proportional valve in which the spool is moved in proportion to the current to the solenoid, and the pilot valve spool is moved by electromagnetic force. Thus, it is possible to use an electromagnetic pilot switching valve that switches the pilot pressure flow path and moves the main spool with the pilot pressure. In the present embodiment, a three-position closed center type four-port valve, which is a double solenoid-spring centering type valve, is used. The control valves 112A, 112B, 114, 115, 116, 117, and 118 operate the operation panel 26 provided in the driver seat 25 shown in FIG. It is controlled by adjusting the current to 115, 116, 117 and 118.

  Further, in the hydraulic circuit 103 described above, a pressure control valve (sequence valve 110, pilot type sequence valve 111, pressure reducing valve 113), check valve (shuttle valve 119), filter 120, and the like are provided as appropriate. .

FIG. 5 is a partially enlarged view showing a detailed configuration near the crusher 6. In FIG. 5, the right side is the front side, and the left side is the rear side.
As shown in FIG. 5, the self-propelled crusher 1 having the above-described configuration includes a distance adjusting unit 12 that adjusts a distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 by being displaced. Displacement amount detection means 13 for detecting the displacement amount of the interval adjustment means 12 is provided. The “interval D” mentioned above refers to the exit clearance dimension of the crusher 6 when the swinging tooth plate 63 is most open. The exit gap dimension is the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64. Refers to the distance between the valleys.

  The distance adjusting means 12 moves the position of the moving tooth plate 63 in the advancing / retreating direction (front and rear direction), whereby the distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64, that is, the discharge port 67 of the crusher 6. Is to adjust the width. More specifically, the interval adjusting means 12 is fixed with a wedge block 121 provided on the backward side (right side in FIG. 5) of the toggle block 15 and a cylinder 122 for moving the wedge block 121 in the forward / backward direction. A plurality of shims 124 interposed between the frame 123 and the wedge block 121 are provided. The cylinder 122 is disposed on the backward side of the wedge block 121 and is disposed in a direction extending in the forward / backward direction. The cylinder body 122a is fixed to the frame 123, and a wedge block 121 is fixed to the tip of the piston 122b of the cylinder 122. The shim 124 is made of a thin plate-like member, and a plurality of shims 124 are stacked in the forward / backward direction. Each of the plurality of shims 124 can be removed, and the number of shims 124 can be increased or decreased.

  In the interval adjusting means 12 described above, the toggle block 15 is moved back and forth by operating the cylinder 122 and moving the wedge block 121 provided at the tip of the piston 122b back and forth. For example, when the toggle block 15 is moved to the forward side (left side in FIG. 5) by the cylinder 122, the lower end portion of the swing jaw 62 is pushed to the forward side via the toggle plate 16, and the moving teeth attached to the swing jaw 62 are moved. The lower end of the plate 63 moves to the forward side. As a result, the distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 is reduced. On the other hand, when the toggle block 15 is moved backward (the right side in FIG. 5) by the cylinder 122, the lower end portion of the swing jaw 62 is pulled backward by the pulling mechanism 17 and is attached to the swing jaw 62. The lower end of the is moved backward. As a result, the distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 is increased. Thus, the crushed material Y of a desired magnitude | size can be obtained by adjusting the space | interval D (width | variety of the discharge port 67 of the crusher 6).

  Further, as described above, when the interval D is adjusted by the interval adjusting unit 12, the number of shims 124 is increased or decreased in accordance with the movement of the wedge block 121. That is, when the piston 122b of the cylinder 122 is extended and the wedge block 121 is moved forward, there is a gap between the wedge block 121 and the frame 123, and the number of shims 124 is increased accordingly. On the other hand, when the piston 122b of the cylinder 122 is shortened and the wedge block 121 is moved backward, the number of shims 124 is reduced by the amount of the backward movement of the wedge block 121. The toggle block 15 described above is displaced according to the distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64, and corresponds to a “displacement portion”.

  The displacement amount detection means 13 detects the distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 by detecting the displacement amount of the toggle block 15. More specifically, the displacement amount detection means 13 includes a stroke sensor 130 that detects the position of the toggle block 15 in the forward / backward direction. As the stroke sensor 130, a wire drum winding type displacement meter whose output resistance value changes depending on the amount of wire drawn can be used. When using this displacement meter, the position of the toggle block 15 can be detected by fixing the main body of the stroke sensor 130 to the frame 123 and fixing the tip of the wire of the stroke sensor 130 to the toggle block 15. The distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 can be detected based on the detected displacement amount of the toggle block 15.

  Further, the self-propelled crusher 1 has a conveyance speed control means 14 (a figure to be described later) that controls the conveyance speed of the main conveyor 7 shown in FIGS. 1 to 3 according to the displacement detected by the displacement detection means 13. 6).

FIG. 6 is a diagram schematically showing the configuration of the conveyance speed control means 14.
As shown in FIG. 6, the conveyance speed control means 14 includes a standard conveyance speed setting means 141 for setting the standard conveyance speed V1 of the main conveyor 7 based on the rotational speed N of the prime mover 100 shown in FIG. 4, and a displacement amount detection means. 13 is a speed correction coefficient setting means 142 for setting a coefficient (hereinafter referred to as a speed correction coefficient k) for correcting the transport speed of the main conveyor 7 on the basis of the displacement detected by 13 and a standard transport speed by the speed correction coefficient k. An optimum conveyance speed setting means 143 that corrects V1 and sets an optimum conveyance speed V2 of the main conveyor 7, and a command value that is sent to the main conveyor control valve 117 so that the main conveyor 7 operates at the set optimum conveyance speed V2. And command value setting means 144 for setting.

  The standard transport speed setting means 141 tabulates the value of the standard transport speed V1 with respect to the rotational speed N of the prime mover 100, and uses this table in accordance with the value of the rotational speed N of the prime mover 100 set by the accelerator dial 100a. The value of the standard transport speed V1 is calculated and output. The above table is set so that the value of the standard transport speed V1 becomes faster (higher) stepwise as the value of the rotational speed N of the prime mover 100 increases. For example, when the distance D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 is widened to the maximum, the above-described standard conveying speed V1 is the maximum, and the discharge is made from the discharge port 67 widened to the maximum. It becomes the conveyance speed of the main conveyor 7 which can convey appropriately the crushed material Y to be performed, ie, the conveyance speed according to the maximum discharge amount.

  The speed correction coefficient setting unit 142 tabulates the value of the speed correction coefficient k with respect to the interval D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64, and is detected by the stroke sensor 130 using this table. The value of the speed correction coefficient k corresponding to the value of the interval D detected based on the displacement amount is calculated and output. The above table is set so that the value of the speed correction coefficient k increases stepwise as the value of the interval D increases. The speed correction coefficient k is a coefficient for correcting the standard transport speed V1 described above to a speed corresponding to the detected interval D.

  The optimum transport speed setting means 143 calculates the optimum transport speed V2 by multiplying the standard transport speed V1 output from the standard transport speed setting means 141 and the speed correction coefficient k output from the speed correction coefficient setting means 142. It consists of a multiplier that outputs.

  The command value setting means 144 converts the optimum transport speed V2 output from the optimum transport speed setting means 143 into a command value for the main conveyor control valve 117. The command value output from the command value setting means 144 is sent to the main conveyor control valve 117, and the current to the solenoid of the main conveyor control valve 117 is controlled. As a result, the flow rate of the pressure oil passing through the main conveyor control valve 117 is adjusted, and the drive of the main conveyor hydraulic motor 107 is controlled.

  Next, the effect | action of the self-propelled crusher 1 which consists of an above-described structure is demonstrated.

  First, the interval D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64 is adjusted by the interval adjusting means 12 shown in FIG. 5 so that the crushed material Y having a desired particle diameter is obtained. For example, when producing the small crushed material Y, the space | interval D is made small by the space | interval adjustment means 12. FIG. On the other hand, when producing a large crushed material Y, the interval D is increased by the interval adjusting means 12. Specifically, by operating the cylinder 122 and moving the wedge block 121 back and forth, the lower end portion of the swing jaw 62 is moved back and forth via the toggle block 15 and the toggle plate 16 to adjust the position of the moving tooth plate 63. To adjust the interval D.

  At this time, the displacement amount of the toggle block 15 that is displaced according to the interval D is detected by the displacement amount detection means 13, and the interval D is detected based on the detected displacement amount of the toggle block 15. The detected distance D is output from the displacement amount detection means 13 to the speed correction coefficient setting means 142. The speed correction coefficient setting unit 142 sets the speed correction coefficient k based on the input interval D. The set speed correction coefficient k is output from the speed correction coefficient setting means 142 to the optimum transport speed setting means 143.

  On the other hand, the prime mover 100 is operated to drive the vibration feeder 4, the side conveyor 5, the crusher 6, the main conveyor 7, and the magnetic separator 8. At this time, the speed N of the prime mover 100 is adjusted by switching the accelerator dial 100a shown in FIG. The rotational speed N of the prime mover 100 is output from the accelerator dial 100a to the standard transport speed setting means 141. In the standard transport speed setting means 141, the standard transport speed V1 is set based on the rotational speed N of the prime mover 100. The set standard transport speed V1 is output from the standard transport speed setting means 141 to the optimum transport speed setting means 143.

  When the standard transport speed V1 and the speed correction coefficient k are respectively input, the optimal transport speed setting means 143 corrects the standard transport speed V1 by the speed correction coefficient k and sets the optimal transport speed V2. The set optimum conveyance speed V2 is output from the optimum conveyance speed setting means 143 to the command value setting means 144. The command value setting means 144 sets and outputs a command value to be sent to the main conveyor control valve 117 based on the optimum transport speed V2. By this command value, the main conveyor control valve 117 is switched, and the hydraulic flow rate to the main conveyor hydraulic motor 107 is adjusted. As a result, the main conveyor 7 is operated at a speed (optimum transport speed V2) corresponding to the discharge amount of the crushed material Y that changes in accordance with the interval D between the lower end of the moving tooth plate 63 and the lower end of the tooth receiving plate 64.

  Next, the effect of the self-propelled crusher 1 having the above-described configuration will be described.

  According to the self-propelled crusher 1 having the above-described configuration, the main conveyor 7 is not operated unnecessarily fast, and fuel consumption can be improved. In addition, since the main conveyor 7 is operated at a low speed corresponding to the discharge amount of the crushed material Y, the service life of parts such as the endless belt 71 and the bearings constituting the main conveyor 7 can be extended. Can be reduced.

  By the way, even if it is the conventional crusher, hydraulic pump 101A, 101B driven by the motor 100 is controlled by adjusting the rotation speed of the motor 100 with the accelerator dial 100a, and the conveyance speed of the main conveyor 7 is controlled. Can do. However, when the rotational speed of the prime mover 100 is adjusted to lower the conveying speed of the main conveyor 7, the driving speed of the vibration feeder 4 and the crusher 6 also decreases, the processing capacity decreases, and the crushed material from the crusher 6 Y discharge is reduced. Therefore, when the interval D is small, even if the rotational speed of the prime mover 100 is adjusted to lower the conveyance speed of the main conveyor 7, the discharge amount of the crushed material Y from the crusher 6 is also reduced. However, the conveyance speed of the main conveyor 7 does not change.

  On the other hand, the self-propelled crusher 1 having the above-described configuration does not adjust the conveyance speed of the main conveyor 7 by adjusting the rotation speed of the prime mover 100, and does not change the rotation speed of the prime mover 100. It consists of the structure which changes conveyance speed. In other words, the hydraulic motors 102A, 102B, 104, 105, 106, 108 of the traveling body 2, the vibration feeder 4, the side conveyor 5, the crusher 6, and the magnetic separator 8 having the same drive source (primary motor 100) as the main conveyor 7 are driven. It is possible to adjust only the drive of the main conveyor hydraulic motor 107 without changing. Thereby, the main conveyor 7 can be operated at the conveyance speed corresponding to the discharge amount of the crushed material Y.

As mentioned above, although embodiment of the crusher which concerns on this invention was described, this invention is not limited to above-described embodiment, In the range which does not deviate from the meaning, it can change suitably.
In the above-described embodiment, as shown in FIG. 6, the table of the distance D and the speed correction coefficient k provided in the speed correction coefficient setting means 142 has a relatively fine number of steps. It is not limited. For example, as shown in FIG. 7 (a), the table of the interval D and the speed correction coefficient k may be a single stage, and as shown in FIG. 7 (b), the interval D and the speed correction coefficient k. The table may be a few steps. Furthermore, as shown in FIG. 7 (c), the present invention provides hysteresis for the speed correction coefficient k to prevent small fluctuations in the signal from the displacement amount detection means 13 due to slight vibration during driving of the crusher 6. It may be insensitive. That is, when the signal from the displacement detection means 13 reaches the switching value d0 for switching the correction coefficient, the correction coefficient does not immediately follow, and the correction coefficient is changed when the signal changes from the switching value d0 by a value exceeding the amplitude a of the minute vibration. To follow and change. For example, when the speed correction coefficient k is at the lower stage value k1, the speed correction coefficient k does not change even if the signal from the displacement amount detection means 13 rises to the switching value d0, and the amplitude of the minute vibration further from the switching value d0. When the speed rises beyond a, the speed correction coefficient k changes to the upper stage value k2 that is one stage higher. On the other hand, when the speed correction coefficient k is at the upper value k2, the speed correction coefficient k does not change even if the signal from the displacement detection means 13 falls to the switching value d0, and the amplitude of the minute vibration further from the switching value d0. When descending beyond a, the speed correction coefficient k changes to the lower value k1 one step lower.

  Moreover, although the above-described embodiment describes the self-propelled crusher 1 including the traveling body 2 that is self-propelled, the present invention does not include the traveling body 2 and is installed at an arbitrary place. It may be a fixed crusher, or it may be equipped with a traveling body composed of wheels or the like, but it is not equipped with a drive mechanism for self-propelling the traveling body, and is driven by pulling with a heavy machine etc. It may be a crusher.

  In the above-described embodiment, the hopper 3, the vibration feeder 4, the side conveyor 5, and the magnetic separator 8 are provided. However, the present invention may be configured without these members and devices. Therefore, the above-described members and devices can be selectively provided as appropriate.

In the above-described embodiment, the crusher 6 that crushes the object X to be crushed includes the crusher 6 in which the moving tooth plate 63 swings with respect to the fixed tooth plate 64. Can be configured to include a crushing device other than the crusher 6 described above.
For example, the present invention can use a jaw crusher type crusher in which one of two tooth plates is movable as a crushing device.

In the above-described embodiment, the belt conveyor type main conveyor 7 is provided as a conveying device for conveying the crushed crushed material Y. However, the present invention is not limited to the belt conveyor type main conveyor 7. It is also possible to adopt a configuration provided with.
For example, in the present invention, a chain conveyor, a roller conveyor, or the like can be used as the transport device.

In the above-described embodiment, the interval adjusting unit 12 using the wedge block 121, the cylinder 122, and the frame 123 is provided. However, the present invention includes an interval adjusting unit other than the above-described interval adjusting unit 12. It is also possible to adopt a configuration.
For example, according to the present invention, an interval adjusting unit using another drive mechanism such as a motor can be used as the interval adjusting unit, or an interval adjusting unit that is manually adjusted can be used.

In the above-described embodiment, the displacement amount detecting means 13 for detecting the displacement amount of the toggle block 15 by the stroke sensor 130 is provided. However, the present invention is not limited to the displacement amount detecting means 13 configured as described above. It is also possible to adopt a configuration provided with a quantity detection means.
For example, the present invention may use displacement amount detection means for detecting the displacement amount of the lower end portion of the swing jaw 62 and the lower end portion of the moving tooth plate 63 in the above-described embodiment as the displacement amount detection means. In addition to the stroke sensor 130, various sensors such as an optical sensor and an ultrasonic sensor can be used as the displacement amount detection unit according to the present invention.

  In the above-described embodiment, the main conveyor hydraulic motor 107 is controlled by adjusting the main conveyor control valve 117 by the conveyance speed control means 14, and the conveyance speed of the main conveyor 7 is controlled. The invention can also use an electric motor as the drive mechanism for the transfer device, and in this case, the transfer speed of the transfer device can be controlled by adjusting the current or voltage flowing through the electric motor.

  In the above-described embodiment, the main conveyor hydraulic motor 107 of the main conveyor 7 and the hydraulic motors 102A and 102B of other devices (the traveling body 2, the vibration feeder 4, the side conveyor 5, the crusher 6, and the magnetic separator 8). , 104, 105, 106, and 108 are driven by the same drive source (the prime mover 100). However, in the present invention, the drive mechanism of the transport device drives the drive mechanism of another device. It is good also as a structure driven by a different drive source. In this case, the control valve such as the main conveyor control valve 117 is not adjusted, and the drive source for driving the transport device is controlled, so that the drive of the other devices is not changed, and the distance D is changed. Thus, the transport speed of the transport device can be controlled.

  In the above-described embodiment, the hydraulic power unit 9 including the prime mover 100, the hydraulic pumps 101A and 101B, the hydraulic circuit 103, and the control valves 109A and 109B is provided. The crusher driven by driving means other than the power unit 9 may be used. For example, an electric crusher may be used, or a crusher driven by other power may be used.

In the above-described embodiment, the conveyance speed control unit 14 includes the standard conveyance speed setting unit 141, the speed correction coefficient setting unit 142, the optimum conveyance speed setting unit 143, and the command value setting unit 144. However, the present invention can also use transport speed control means having another configuration.
For example, when the rotational speed of the prime mover is always constant, a table of optimum transport speed values of the transport apparatus corresponding to the interval D is used, and the displacement detected by the displacement amount detection means using this table. A configuration may be adopted in which the optimum transport speed of the transport device is determined based on the interval D calculated based on the amount, and the drive mechanism of the transport device is controlled.

  In addition, in the range which does not deviate from the main point of this invention, it is possible to replace suitably the component in above-mentioned embodiment with a well-known component, and you may combine the above-mentioned modification suitably.

It is a side view of the self-propelled crusher for demonstrating embodiment of the crusher which concerns on this invention. It is a top view of the self-propelled crusher for demonstrating embodiment of the crusher which concerns on this invention. It is sectional drawing of the self-propelled crusher for demonstrating embodiment of the crusher which concerns on this invention. It is a hydraulic circuit figure showing a power unit for explaining an embodiment of a crusher concerning the present invention. It is the elements on larger scale which show the detail of the crusher vicinity for demonstrating embodiment of the crusher which concerns on this invention. It is a block diagram which shows the conveyance speed control means for demonstrating embodiment of the crusher which concerns on this invention. It is a graph which shows the table of the speed correction coefficient setting means for demonstrating other embodiment of the crusher which concerns on this invention.

Explanation of symbols

1 Self-propelled crusher 6 Crusher (crusher)
7 Main conveyor (conveyor)
9 Power unit (hydraulic drive means)
12 Interval adjusting means 13 Displacement amount detecting means 14 Conveying speed control means 63 Moving tooth plate (two members)
64 Tooth plate (two members)
100 prime movers 101A, 101B hydraulic pump 103 hydraulic circuit 106 hydraulic motor for crusher (driving device drive device)
107 Hydraulic motor for main conveyor (drive device for conveyor)
117 Control valve for main conveyor (Control valve for transfer device)
141 Standard transport speed setting means 142 Speed correction coefficient setting means 143 Optimal transport speed setting means 144 Command value setting means D Interval k Speed correction coefficient V1 Standard transport speed V2 Optimal transport speed X Object to be crushed Y Crushed object

Claims (3)

A crushing device that compresses and crushes the crushed material supplied from one side between the two members and discharges the crushed material from the other side by moving one or both of the two members,
A transport device for transporting crushed material discharged from between the other end portions of the two members;
An interval adjusting means for adjusting the interval between the other end portions of the two members by displacing;
A displacement amount detecting means for detecting a displacement amount of the interval adjusting means;
A transport speed control means for controlling the transport speed of the transport device in accordance with the displacement amount detected by the displacement amount detection means;
A crusher characterized by being provided with. The crusher according to claim 1,
The transport speed control means includes a standard transport speed setting means for setting the standard transport speed of the transport device based on the number of rotations of the prime mover, and a speed for setting a speed correction coefficient based on the displacement amount detected by the displacement amount detection means. Correction coefficient setting means, optimum conveyance speed setting means for setting the optimum conveyance speed of the conveyance apparatus by correcting the standard conveyance speed by the correction coefficient, and driving of the conveyance apparatus drive device so as to operate the conveyance apparatus at the optimum conveyance speed A crusher characterized by comprising command value setting means for setting a command value to be sent to a control valve for a conveying device that controls the control. The crusher according to claim 1 or 2,
Hydraulic driving means for driving the crushing device driving device provided in the crushing device and the conveying device driving device provided in the conveying device, respectively, by hydraulic pressure is provided,
The hydraulic driving means includes a hydraulic pump driven by a prime mover, a hydraulic circuit that transmits hydraulic pressure from the hydraulic pump to the crushing device driving device and the conveying device driving device, and a flow rate of pressure oil sent to the conveying device driving device. And a control valve for a transport device capable of controlling
A crusher characterized in that the conveyance speed control means controls a conveyance speed of the conveyance device by controlling a control valve for the conveyance device.

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