JP2006051453A - Crusher and grizzly feeder - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a crusher and a grizzly feeder highly accurately adjusting the feed amount of a crushing object to a jaw crusher corresponding to a load condition and preventing unexpected variation of carrying speed of the crushing object during operation. <P>SOLUTION: This crusher for crushing the crushing object by the jaw crusher is provided with a grizzly feeder 15, which comprises: a grizzly feeder body 15A; a vibrator casing 61 fixed to a lower part of the grizzly feeder body 15A; a pair of approximately parallel rotary shafts 62 provided in the casing 61; a pair of eccentric weights 63 respectively rotatably provided in relation to the shafts 62, a hydraulic motor 64 for the feeder rotating the shafts 62; and a phase adjusting jack 65 allowing rotation of the eccentric weights 63 around the shafts 62 and varying the phase of the eccentric weights 63 in relation to the shafts 62. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a crusher provided with a jaw crusher as a crushing device and a grizzly feeder used therefor.

  A crusher using a jaw crusher can be used for various types of construction waste and industrial waste generated at construction sites, such as concrete lumps delivered at the time of building demolition and asphalt lumps discharged at road repairs, or rock mining sites and working faces. The material to be crushed, such as rocks and natural stones mined in, is introduced between the fixed teeth and the moving teeth, and is crushed by the rocking movement of the moving teeth.

  Usually, such a crusher is equipped with a grizzly feeder for introducing a material to be crushed into a jaw crusher. The grizzly feeder is equipped with a plate with grizzly bars inside the frame-shaped main body, vibrates the main body to convey the material to be crushed, and sifts earth and sand and fine particles from between the grizzly rivers. While supplying a crushed object having a predetermined size or more to the jaw crusher.

  A vibration exciter that vibrates the grizzly feeder has a pair of rotating shafts, each having an eccentric weight attached to the rotating shaft, arranged in parallel in the casing, and a line connecting both rotating shafts of the exciting force applied by the rotating eccentric weight. In general, a configuration in which the grizzly feeder is reciprocally oscillated in a direction substantially perpendicular to a line connecting the two rotation axes by canceling out components parallel to the rotation axis. In such a shaker, when the jaw crusher is overloaded, the driving speed is usually lowered to reduce the conveyance amount of the object to be crushed. The sieving ability will be reduced more than necessary together with the ability. As a result, the earth and sand and fine particles are not sufficiently classified, and there is a possibility that, for example, the moving teeth and fixed teeth of the jaw crusher may be damaged.

  Therefore, the casing of the vibration exciter is supported rotatably about the center position of both rotation shafts, and the casing of the vibration exciter and the grizzly feeder main body are connected by a cylinder, and the cylinder is expanded and contracted to excite the vibration. There is one that changes the vibration direction of the shaker by rotating the casing of the machine and adjusts the conveyance capacity of the object to be crushed while maintaining the drive speed of the shaker (for example, see Patent Document 1).

JP-A-11-28383

  However, in the above prior art, since the casing of the vibration exciter is rotated by a cylinder connected to the grizzly feeder main body, the moment acting on the casing during operation interferes with the operation direction of the cylinder. Therefore, during operation, it is difficult to adjust the vibration direction of the shaker with high accuracy according to the load of the jaw crusher because the cylinder does not expand and contract smoothly due to the influence of the moment. In addition, if a moment exceeding the cylinder's holding force is applied during operation, the cylinder rod may be displaced and the vibration direction of the shaker changes regardless of the load condition of the jaw crusher. May fluctuate unexpectedly.

  The present invention has been made in view of the above, and an object of the present invention is to adjust the supply amount of the object to be crushed to the jaw crusher with high accuracy according to the load state during operation. An object of the present invention is to provide a crusher and a grizzly feeder that can prevent unexpected fluctuations.

  In order to achieve the above object, a first invention is a crusher for crushing an object to be crushed by a jaw crusher, a grizzly feeder main body, a vibrator casing fixed to the lower part of the grizzly feeder main body, and the vibration exciter. A pair of rotating shafts provided substantially in parallel in the machine casing, a pair of eccentric weights rotatably provided with respect to the rotating shafts, a drive means for excitation for rotating the rotating shaft, and the eccentricity A grizzly feeder is provided that includes a phase adjusting drive unit that rotates a weight around the rotation shaft and changes a phase of the eccentric weight with respect to the rotation shaft.

  According to a second invention, in the first invention, a guide groove that is inclined with respect to an axial direction of the rotary shaft is provided in a peripheral body portion of the rotary shaft, and the eccentric weight engages with the guide groove and It rotates with respect to the said rotating shaft by sliding to the axial direction of a rotating shaft, It is characterized by the above-mentioned.

  In a third aspect based on the second aspect, the eccentric weight includes a flange, and the phase adjusting driving means pushes and pulls the block engaged with the flange in the axial direction of the rotating shaft. An eccentric weight is slid in the guide groove.

  According to a fourth invention, in any one of the first to third inventions, a detecting means for detecting a load state of the jaw crusher and a driving means for adjusting the phase are driven in accordance with a detection signal of the detecting means. And a control means for controlling the phase of the eccentric weight.

  According to a fifth aspect of the present invention, there is provided a grizzly feeder that conveys and supplies the object to be crushed to the jaw crusher, a grizzly feeder main body, a vibrator casing fixed to the lower portion of the grizzly feeder main body, and substantially parallel to the vibrator casing. A pair of rotating shafts provided, a pair of eccentric weights provided so as to be rotatable with respect to the respective rotating shafts, a driving means for exciting the rotational shafts, and the eccentric weights around the rotating shafts And a phase adjusting driving means for rotating and changing the phase of the eccentric weight with respect to the rotating shaft.

  According to the present invention, the phase of the eccentric weight is easily adjusted by rotating the eccentric weight with respect to the rotation axis thereof using the phase adjusting drive means, and the crushing object conveying capacity of the grizzly feeder is controlled. Can do. At this time, the vibration direction of the vibration exciter is changed by rotating the eccentric weight with respect to the rotation axis, so the vibration direction of the vibration exciter and the operation direction of the driving means for phase adjustment are completely different, and the vibration exciter casing Like the structure that rotates itself, the moment of the vibrator during vibration does not interfere with the driving means that changes the vibration direction of the vibrator. Therefore, during operation, the amount of material to be crushed to the jaw crusher can be adjusted with high accuracy according to the load state, and the vibration direction of the shaker does not change regardless of the load state of the jaw crusher. Therefore, the unexpected fluctuation | variation of the to-be-crushed object conveyance speed can also be prevented.

Hereinafter, an embodiment of a crusher of the present invention will be described with reference to the drawings.
FIG. 1 is a side view showing the overall structure of an embodiment of the crusher of the present invention, FIG. 2 is a top view thereof, and FIG. 3 is a front view seen from the left side in FIG. In the following description, the left and right in FIG. 1 are the rear and front of the crusher or one side and the other side in the longitudinal direction of the main body frame, respectively.
The crusher in the present embodiment is, for example, a large or small construction waste, industrial waste, or a rock mining site or a face that is generated at a construction site such as a concrete block transported at the time of building demolition or an asphalt block discharged at the time of road repair. The rocks, natural stones, etc. mined at the site are treated as objects to be treated, and these are received as the above-mentioned objects to be crushed.

  In FIG. 1 to FIG. 3, reference numeral 1 denotes a traveling body, and the traveling body 1 is composed of a traveling device 2 and a main body frame 3 extending substantially horizontally above the traveling device 2. Reference numeral 4 denotes a track frame of the traveling device 2, and the track frame 4 is connected to the lower portion of the main body frame 3. Reference numerals 5 and 6 denote driven wheels and driving wheels provided at both ends of the track frame 4, 7 denotes a crawler belt wound around the driven wheels 5 and the driving wheels 6, and 8 denotes a traveling hydraulic motor directly connected to the driving wheels 6.

  Reference numerals 9 and 10 denote support posts erected on one side in the longitudinal direction of the main body frame 3, and reference numeral 11 denotes a support bar provided on the support posts 9 and 10. Reference numeral 12 denotes a hopper that receives an object to be crushed. The hopper 12 is formed to expand upward, and is supported on the support bar 11 via a plurality of support members 13. .

  15 is a grizzly feeder located below the hopper 12, and this grizzly feeder 15 is supported by the support bar 11 separately from the hopper 12, and sorts the object to be crushed received in the hopper 12 according to its particle size. However, it conveys to the crushing apparatus (jaw crusher) 20 mentioned later. Reference numeral 15 </ b> A denotes a main body of the grizzly feeder 15, and the grizzly feeder 15 </ b> A is provided on the support bar 11 via a plurality of springs 18 so as to vibrate. In the grizzly feeder 15A, a plurality of (two in the present embodiment) plates 17 having grizzly bars 16 arranged in parallel in the width direction of the main body frame 3 (vertical direction in FIG. 2) are stepped downward. It is fixed. Reference numeral 19 denotes a vibration exciter that vibrates the grizzly feeder 15, and the grizzly feeder 15 is vibrated by the vibration exciter 19, and the crushed material on the loaded plate 17 is conveyed forward.

  Reference numeral 14 denotes a chute provided below the grizzly river 16 of the plate 17, and this chute 14 is configured to be switchable between a discharge conveyor chute 14a and a side conveyor chute 14b. The discharge conveyor chute 14a guides fine particles (so-called slip) and the like contained in an object to be crushed that falls from the gaps between the grizzly bars 16 of the plate 17 onto a discharge conveyor 40 described later. On the other hand, the chute 14b for the side conveyor guides the fine particles onto a side conveyor (not shown) that is optionally provided. Reference numeral 23 denotes a space for installing the side conveyor (see FIG. 1).

  Reference numeral 20 denotes a crushing device (jaw crusher) for crushing an object to be crushed. This crushing device 20 is located in front of the hopper 12 and the grizzly feeder 15, and as shown in FIG. It is installed in the vicinity. Although not particularly illustrated, the crushing device 20 is provided with a pair of fixed teeth and moving teeth that are arranged so as to face each other so that the gap space of each crushing space decreases in the downward direction. Reference numeral 21 denotes a crusher hydraulic motor (see FIG. 2). The crusher hydraulic motor 21 rotates the flywheel 22. The rotational motion of the flywheel 22 is converted into a swinging motion of a moving tooth (not shown), so that the moving tooth swings in the front-rear direction with respect to the fixed tooth. In the present embodiment, the drive transmission structure from the crushing device hydraulic motor 21 to the flywheel 22 is configured via a belt (not shown), but is not limited thereto. Other configurations such as a configuration via a chain may be used.

  Reference numeral 25 denotes a power unit (power unit) having a built-in power source for each hydraulic actuator. The power unit 25 is located further forward than the crushing unit 20 and is connected to the longitudinal end of the main body frame 3 via the support member 26. It is supported by. Although not particularly illustrated, the power unit 25 is provided with an engine serving as a power source of the crusher, a hydraulic pump driven by the engine, and the like. Reference numerals 30 and 31 denote fuel tanks and hydraulic oil tanks (both not shown) built in the power unit 25, 32 a pre-cleaner, 35 a driver seat provided in a rear compartment of the power unit 25, and 36 A pair of left and right traveling operation levers for operating the traveling hydraulic motor 8.

  Reference numeral 40 denotes a discharge conveyor that conveys crushed materials and the like crushed by the crushing apparatus 20 and discharges them outside the apparatus. The discharge conveyor 40 rises diagonally from the lower position of the crushing apparatus 20 toward the downstream side (front side) in the conveying direction. As described above, the suspension is supported from the arm member 43 or the main body frame 3 attached to the power unit 25 via the support members 41 and 42. 45 is a conveyor frame of the discharge conveyor 40, 46 and 47 are driven wheels (idlers) and drive wheels provided at both ends of the conveyor frame 45, and 48 is a hydraulic motor for the discharge conveyor (see FIG. 2) directly connected to the drive wheels 47. . Reference numeral 50 denotes a conveyor belt wound around the driven wheel 46 and the drive wheel 47, and this conveyor belt 50 is driven to circulate when the drive wheel 47 is driven to rotate by a discharge conveyor hydraulic motor 48.

  Reference numeral 55 denotes a magnetic separator that removes foreign matters (magnetic substances) such as reinforcing bars in the crushed material to be discharged. The magnetic separator 55 is supported by being suspended from the arm member 43 via a support member 56. The magnetic separator 55 is arranged such that the magnetic separator belt 59 wound around the driving wheel 57 and the driven wheel 58 is substantially orthogonal to the discharge conveyor 40. Reference numeral 60 denotes a magnetic separator hydraulic motor directly connected to the drive wheel 57. Inside the circulation trajectory of the magnetic separator belt 59, magnetic force generating means (not shown) is provided, and foreign matters such as reinforcing bars on the transport belt 50 are separated by the magnetic force from the magnetic force generating means acting over the magnetic separator belt 59. It is adsorbed by the machine belt 59, conveyed to the side of the discharge conveyor 40, and dropped.

4 is a side view showing the detailed structure of the grizzly feeder 15, FIG. 5 is a cross-sectional view taken along the line VV in FIG. 4, FIG. 6 is a cross-sectional view taken along the line IV-IV in FIG. It is sectional drawing by the VII-VII cross section. In these drawings, the same parts as those in the previous drawings are denoted by the same reference numerals, and description thereof is omitted.
4 to 7, the above-described vibrator 19 includes a vibrator casing 61 fixed to the lower portion of the grizzly feeder main body 15A, and a pair of rotating shafts 62 provided substantially in parallel in the vibrator casing 61. A pair of eccentric weights 63 provided so as to be rotatable with respect to the rotary shaft 62, a feeder hydraulic motor 64 which is a driving means for exciting the rotary shaft 62, and the eccentric weight 63 are connected to the rotary shaft 62. A phase adjustment jack 65 is provided as a phase adjustment drive unit that rotates around and changes the phase of the eccentric weight 63 with respect to the rotation shaft 62.

  The vibrator casing 61 is formed in a container shape with a cylindrical body 66 and a side plate 67, and the rotating shaft 62 is housed in a space defined by the cylindrical body 66 and the side plate 67, and is parallel and horizontal to each other. At approximately the same height. Reference numeral 68 denotes four bearings provided on the side plate 67, and the rotary shaft 62 is rotatably supported by these bearings 68.

  A plurality of guide grooves 69 that are inclined with respect to the axial direction of the rotating shaft 62 (in this example, a total of six on one bearing 62) are provided on the peripheral body portion of the rotating shaft 62 so as to describe a part of the spiral track. (See FIGS. 6 and 7). The guide grooves 69 are engaged with the tips of a plurality of pins 70 provided on an eccentric weight 63 inserted through the rotation shaft 62, and the eccentric weight 63 rotates as the pins 70 slide in the guide grooves 69. It rotates with respect to the shaft 62 and changes its phase. Both eccentric weights 63 are provided with flanges 72, and blocks 74 engaged with the flanges 72 are attached to the tips of the rods 73 of the phase adjusting jack 65 described above. Thus, when the rod 73 is expanded and contracted, the eccentric weight 63 is pushed and pulled in the axial direction of the rotating shaft 62 and slides in the axial direction of the rotating shaft 62 along the guide groove 69.

  In the state shown in FIGS. 6 and 7, the horizontal component of the excitation force by the eccentric weights 63 cancels out, and the vibration direction becomes almost vertical as shown by the arrows in FIG. When sliding on the groove 69 and rotating with respect to the rotating shaft 62, the direction component in which the excitation force is canceled gradually inclines with respect to the horizontal direction (that is, the vibration direction gradually inclines with respect to the vertical direction). To go). Further, the gears 71 provided on the rotary shafts 63 are meshed so that the phase relationship between the eccentric weights 63 is always maintained, and the guide grooves 69 are located on the rotary shafts 62 that rotate reversely with each other. Inclined in the same direction. The state in which the phase adjusting jack 65 is extended is shown in FIGS. 8 and 9 corresponding to FIGS.

  Here, the power unit 25 described above controls the engine, a plurality of hydraulic pumps driven by the engine, and the flow of pressure oil discharged from the hydraulic pumps, and supplies them to each driving unit. A hydraulic drive device having a plurality of control valve devices is provided. Hereinafter, a detailed configuration of the hydraulic drive device will be described.

FIG. 10 is a hydraulic circuit diagram showing an overall schematic configuration of the hydraulic drive device.
In FIG. 10, reference numeral 100 denotes an engine, 101A to 101C are variable displacement type first and second hydraulic pumps driven by the engine 100, and a fixed displacement type third hydraulic pump, and 102 is similarly driven by the engine 100. This is a fixed displacement pilot pump. 103A and 103B are first and second control valve devices, and these control valve devices 103A and 103B control the direction and flow rate of the pressure oil discharged from the first and second hydraulic pumps 101A and 101B, for example, pilot operation type. A plurality of control valves (not shown) are provided. The left traveling hydraulic motor 8L is driven by the discharge hydraulic oil from the first hydraulic pump 101A, and the right traveling hydraulic motor 8R and the crushing device hydraulic motor 21 are driven by the discharge hydraulic oil from the second hydraulic pump 101B.

  Reference numeral 105 denotes an operation valve device that switches the operation state of the first and second control valve devices 103A and 103B. Although not particularly illustrated, the operation valve device 105 includes a plurality of solenoid-driven switching valves, for example. The switching valve in the operation valve device 105 is switched by an electric signal output via the controller 107 in accordance with the operation of the operation panel 106. By switching the plurality of switching valves, the direction of the pilot pressure from the pilot pump 102 is switched, and the control valve corresponding to the crushing device hydraulic motor 21 in the first and second control valve devices 103A and 103B is switched. The forward and reverse rotations of the hydraulic motor 21 are switched, and the pilot pressure is supplied to and cut off from the operation lever devices 36L and 36R respectively provided with the left and right traveling operation levers 36, and the left and right traveling hydraulic motors 8L and 8R. Or make it operable.

  103C controls the direction and flow rate of the pressure oil supplied from the third hydraulic pump 101C to each driving device (discharge conveyor hydraulic motor 48, magnetic separator hydraulic motor 60, feeder hydraulic motor 64, phase adjusting jack 65). These control valves are switched by an electrical signal output from the controller 107 in response to the operation of the operation panel 106.

  Reference numerals 110 to 112 are relief valves that limit the maximum discharge pressures of the first and second hydraulic pumps 101A and 101B, the third hydraulic pump 101C, and the pilot pump 102, respectively. To the branch pipes 113 of the discharge pipes 101Aa and 101Ba of the second hydraulic pumps 101A and 101B, the branch pipe 114 of the discharge pipe 101Ca of the third hydraulic pump 101C, and the branch pipe 115 of the discharge pipe 102a of the pilot pump 102 Is provided. A regulator device 116 adjusts the discharge flow rates of the first and second hydraulic pumps 101A and 101B so that the discharge flow rate according to the required flow rate of each control valve in the first and second control valve devices 103A and 103B can be obtained. The tilting of the first and second hydraulic pumps 101A and 101B is controlled.

  A pressure sensor 120 is a detecting means for detecting the load state of the jaw crusher 20, and this pressure sensor 120 is provided in a pressure oil supply line to the crushing device hydraulic motor 21. The load state of the jaw crusher 20 is detected by detecting the pressure of the pressure oil supplied to. The detection signal of the pressure sensor 120 is output to the controller 107, and the controller 107 corresponds to the phase adjustment jack 65, strictly speaking, to the phase adjustment jack 65 in the third control valve device 103C according to the detection signal from the pressure sensor 120. A command signal is output to the control valve. Thereby, the phase adjusting jack 65 is driven (expanded / contracted) according to the load state of the jaw crusher 20 to control the phase of the eccentric weight 63, and the vibration direction of the vibration exciter 19, that is, the object to be crushed by the grizzly feeder 15. The conveyance speed is controlled.

Next, the operation and action of the embodiment of the crusher of the present invention having the above-described configuration will be described.
For example, when an object to be crushed is introduced into the hopper 12 by a hydraulic excavator or the like, the introduced object to be crushed is introduced into the grizzly feeder 15 and conveyed toward the crushing device 20 by vibration. At that time, fine particles (slipping etc.) smaller than the gaps between the grizzly rivers 16 of the plate 17 are guided from the gaps to the discharge conveyor 40 via the discharge conveyor chute 14a, and larger objects to be crushed (larger) Lump) is conveyed to the crushing device 20. The material to be crushed introduced into the crushing device 20 is crushed into a predetermined particle size in the crushing chamber 73 by fixed teeth and moving teeth, and introduced onto the lower discharge conveyor 40. The crushed material guided onto the discharge conveyor 40 is combined with the fine particles selected by the grizzly feeder 15 and guided through the discharge conveyor chute 14a and conveyed forward (right side in FIG. 1). The machine 55 adsorbs and removes foreign matter such as reinforcing bars and then discharges it outside the machine.

  When the fine particles selected by the grizzly feeder 15 are separated and discharged without joining the crushed material crushed by the crushing device 20, a side conveyor is optionally installed in the installation space 23 and the chute 14 is attached. Switch to side conveyor chute 14b. Thereby, the fine particles selected by the grizzly feeder 15 are dropped onto the side conveyor and carried out to the side of the machine body.

  During the operation as described above, when the amount of the material to be crushed into the jaw crusher 20 is excessive and the jaw crusher 20 falls into an overload state, the pressurized oil supplied to the crushing device hydraulic motor 21 rises as the load increases. Is detected by the pressure sensor 120 and output to the controller 107. Then, the controller 107 calculates a predetermined command signal according to a program stored in advance according to the detection signal from the pressure sensor 120, and the generated command signal corresponds to the phase adjustment jack 65 in the third control valve device 103C. Output to the control valve.

  Accordingly, for example, the phase adjustment jack 65 is contracted from the state shown in FIGS. 8 and 9 where the conveyance speed is high to bring the vibration direction of the vibration exciter 19 close to the vertical direction, and the object conveyance speed of the grizzly feeder 15 is reduced. As a result, the amount of material to be crushed into the jaw crusher 20 is reduced, and an overload state of the jaw crusher 20 is avoided. When the detection signal of the pressure sensor 120 returns to the normal range after the predetermined time has elapsed, the controller 107 extends the phase adjustment jack 65 to return the crushed object transport speed of the grizzly feeder 15 to the original state.

  According to the present embodiment, as described above, the eccentric weight 63 is rotated with respect to the rotation shaft 62 by using the phase adjustment jack 65, thereby easily adjusting the phase of the eccentric weight 63 and the grizzly feeder 15. The to-be-crushed object conveyance capability of can be controlled. At that time, since the eccentric weight 63 is rotated with respect to the rotating shaft 62 to change the vibration direction, the vibration direction of the vibration exciter 19 and the operation direction of the phase adjustment jack 65 are completely different, and the vibration exciter casing itself is rotated. As in the configuration, the driving unit that changes the vibration direction of the vibration exciter is not affected by the moment of the vibration exciter, and the vibration direction of the vibration exciter 19 is accurately adjusted according to the load of the jaw crusher 20. Can do. Of course, the phase adjusting jack 65 does not move due to the moment acting on the vibrator 19 during operation. Therefore, during operation, the supply amount of the object to be crushed to the jaw crusher 20 can be adjusted with high accuracy according to the load state, and the vibration direction of the vibrator 19 changes regardless of the load state of the jaw crusher 20. Therefore, it is possible to prevent unexpected fluctuations in the conveyance speed of the object to be crushed.

  In the present embodiment described above, the pressure sensor 120 is exemplified as the detecting means for detecting the load state of the jaw crusher 20, but the rotation state of the crushing device hydraulic motor 21 is detected and the load state of the jaw crusher 20 is detected. It is also conceivable that a rotation speed sensor is provided in the crushing device hydraulic motor 21 in order to detect. Further, when detecting the load of the jaw crusher 20 by detecting the amount of the object to be crushed between the moving teeth and the fixed teeth, the object to be crushed between the moving teeth and the fixed teeth in the jaw crusher 20 is detected. It is also possible to use a level sensor that detects the height of the. In these cases, similar effects can be obtained.

  Further, the phase adjustment jack 65 has been described as being automatically controlled according to the load state of the jaw crusher 20, but may not be necessarily automatically controlled, for example, manually operated by the control panel 106. . Of course, as a configuration that is automatically controlled, a configuration that can be switched to manual operation as necessary may be used. In these cases, the same effect is obtained.

  Furthermore, in the above, the example which applied this invention to the crusher which mounted the grizzly feeder 15 provided with the plate 17 provided with the grizzly river 16 was demonstrated, but not only this but the plate 17 is provided only with one step. The present invention may be applied to a grinder equipped with a grizzly feeder or a grizzly feeder provided with three or more grizzly bars. Moreover, although the case where this invention was applied to the self-propelled crusher which has the traveling body 1 was illustrated and demonstrated, it is not restricted to this, This invention is applicable also to a stationary crusher. In these cases, similar effects can be obtained.

It is a side view showing the whole structure of one embodiment of the crusher of the present invention. It is a top view showing the whole structure of one embodiment of the crusher of the present invention. It is the front view seen from the left side in FIG. 1 showing the whole structure of one Embodiment of the crusher of this invention. It is a side view showing the detailed structure of the grizzly feeder with which one embodiment of the crusher of the present invention was equipped. It is sectional drawing by the VV cross section in FIG. 4 showing the detailed structure of the grizzly feeder with which one Embodiment of the crusher of this invention was equipped. It is sectional drawing by the IV-IV cross section in FIG. 4 showing the detailed structure of the vibrator of the grizzly feeder with which one Embodiment of the crusher of this invention was equipped. It is sectional drawing by the VII-VII cross section in FIG. 6 showing the detailed structure of the vibrator of the grizzly feeder with which one Embodiment of the crusher of this invention was equipped. FIG. 7 is a diagram showing a detailed structure of a vibrator of a grizzly feeder provided in an embodiment of a crusher of the present invention in a state where a driving means for phase adjustment is extended, corresponding to FIG. 6. FIG. 8 is a view showing the detailed structure of the vibrator of the grizzly feeder provided in the embodiment of the crusher of the present invention in a state where the driving means for phase adjustment is extended, corresponding to FIG. 7. It is a hydraulic circuit figure showing the whole schematic structure of the hydraulic drive unit with which one embodiment of the crusher of the present invention was equipped.

Explanation of symbols

15 Grizzly feeder 15A Grizzly feeder main body 19 Exciter 20 Jaw crusher 61 Exciter casing 62 Rotating shaft 63 Eccentric weight 64 Feeder hydraulic motor 65 Phase adjusting jack 69 Guide groove 72 Flange 74 Block 107 Controller 120 Pressure sensor

Claims (5)

In a crusher that crushes objects to be crushed by a jaw crusher,
Grizzly feeder body,
A vibrator casing fixed to the lower part of the grizzly feeder main body,
A pair of rotating shafts provided substantially parallel in the shaker casing;
A pair of eccentric weights rotatably provided with respect to each of the rotation shafts;
Drive means for excitation for rotating the rotary shaft;
A crusher comprising a grizzly feeder having a phase adjusting driving means for rotating the eccentric weight around the rotation shaft and changing a phase of the eccentric weight with respect to the rotation shaft.   A guide groove that is inclined with respect to the axial direction of the rotary shaft is provided in a peripheral body portion of the rotary shaft, and the eccentric weight engages with the guide groove and slides in the axial direction of the rotary shaft. The crusher according to claim 1, wherein the crusher rotates with respect to a rotating shaft.   The eccentric weight includes a flange, and the phase adjusting drive means pushes and pulls the block engaged with the flange in the axial direction of the rotating shaft to slide the eccentric weight in the guide groove. The crusher according to claim 2, which is characterized.   And a detecting means for detecting a load state of the jaw crusher, and a control means for controlling the phase of the eccentric weight by driving the phase adjusting driving means in accordance with a detection signal of the detecting means. The crusher according to any one of claims 1 to 3. In the grizzly feeder that feeds the material to be crushed to the jaw crusher,
Grizzly feeder body,
A vibrator casing fixed to the lower part of the grizzly feeder main body,
A pair of rotating shafts provided substantially parallel in the shaker casing;
A pair of eccentric weights rotatably provided with respect to each of the rotation shafts;
Drive means for excitation for rotating the rotary shaft;
A grizzly feeder comprising phase adjusting drive means for rotating the eccentric weight around the rotation axis and changing a phase of the eccentric weight with respect to the rotation axis.

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