JP2010069414A - Jaw crusher - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a jaw crusher capable of easily returning to a crushing work even if a moving blade moves in occurrence of an overload, and capable of suppressing affect on the service life of the member of a device. <P>SOLUTION: The jaw crusher includes a toggle cylinder 66 attached to the moving blade 72 at the end of a rod part side, an accumulator 67 holding the toggle cylinder 66 with the rod part 78 maximally extended, a relief valve 105 releasing pressure of a bottom side hydraulic chamber when the pressure exceeds a first set pressure P1, a sliding member 68 attached with the end of the bottom part side of a first hydraulic cylinder, a brake device 70 restraining movement of the sliding member, and a return cylinder 75 urging the moving blade during crushing work in the direction separating from a fixed blade 71. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a jaw crusher for crushing an object to be crushed such as rock.

  In crushers that crush stone-based materials such as rocks and wood-based materials such as construction waste (objects to be crushed), there are fixed teeth and moving teeth that swing with respect to these fixed teeth as crushing devices. There is a jaw crusher to prepare.

  Jaw crusher introduces and crushes rocks and other objects to be crushed between fixed teeth and moving teeth, but if the objects to be crushed contain foreign objects such as metal lumps, the crusher is overloaded. Sometimes. In such a case, as an apparatus for protecting the crushing device and its peripheral members from overload, an overload protection device that releases the moving tooth from the fixed tooth by releasing the restraint of the moving tooth fulcrum is used.

  Further, the particle size of the crushed material produced by the jaw crusher is controlled by the size of the gap (discharge gap) formed at the tips of the fixed teeth and the moving teeth. In order to produce a crushed product having a uniform particle size, it is desirable that the crushing device has a mechanism that keeps the discharge gap constant while resisting a crushing load (crushing reaction force) that acts during crushing operations.

  As an overload protection device having such a function, a member for holding the toggle plate sandwiched between the moving teeth and a sliding member for moving the moving teeth away from the fixed teeth when an overload occurs is provided. There is a thing (refer patent documents 1 grade). This overload protection device presses and restrains the sliding member via a friction plate with a braking device during crushing work, but if an overload exceeding the restraining force is applied, the sliding member slides. Thus, the moving tooth is separated from the fixed tooth, so that the member is protected from overload.

JP 2006-247603 A

  However, if the jaw crusher of the above technique is overloaded and the sliding member slides, the sliding member remains displaced from the set position. For this reason, the discharge gap must be readjusted by releasing the restraint of the sliding member, and the crushing operation must be interrupted during the adjustment operation. In the above technique, since the sliding member and the friction plate slide each time an overload is applied, the replacement operation may be forced when the life of these members is exhausted by repeating this sliding operation.

  An object of the present invention is to provide a jaw crusher that can easily return to a crushing operation even if a moving tooth moves when an overload occurs, and that can suppress the influence on the life of members of the apparatus. It is in.

  (1) In order to achieve the above object, the present invention provides a crushing device frame, a fixed tooth fixed to the crushing device frame, and opposed to the fixed tooth, and is swingable via an eccentric shaft. In a jaw crusher provided with a moving tooth provided on the first hydraulic cylinder, the rod portion side end of the first hydraulic cylinder is rotatably attached to the moving tooth, and the rod portion of the first hydraulic cylinder is most extended. Pressure holding means for holding the pressure of the bottom hydraulic chamber of the first hydraulic cylinder, and when the pressure of the bottom hydraulic chamber exceeds a first set pressure set for machine protection, A pressure release means for releasing the pressure of the bottom side hydraulic chamber, a guide member attached to the crushing device frame, and an end on the bottom side of the first hydraulic cylinder are rotatably attached; A sliding member provided so as to be capable of advancing and retreating along, a braking device that presses the sliding member and restrains the movement of the sliding member with respect to the guide member, and the moving tooth below the first hydraulic cylinder The end of the rod portion is rotatably attached to the first hydraulic cylinder and is positioned below the first hydraulic cylinder, and the moving teeth are fixed in a state where the braking device restrains the movement of the sliding member during the crushing operation. A second hydraulic cylinder biased in a direction away from the teeth.

  (2) In the braking device of (1), preferably, the second setting that allows the sliding member to slide when a load is applied that causes the pressure in the bottom side hydraulic chamber to reach the first set pressure or higher. It is assumed that the sliding member is pressed with pressure.

  (3) In the above (1) or (2), preferably, the pressure holding means is an accumulator connected to the bottom side hydraulic chamber, and the pressure release means is connected to the bottom side hydraulic chamber. It shall be a relief valve.

(4) Moreover, in order to achieve the above object, the present invention provides a crusher frame,
In a jaw crusher comprising a fixed tooth fixed to the crushing device frame and a moving tooth disposed opposite to the fixed tooth and swingably provided via an eccentric shaft, a rod portion is provided on the moving tooth. A first hydraulic cylinder rotatably mounted at its end and the pressure of the bottom hydraulic chamber of the first hydraulic cylinder to hold the first hydraulic cylinder with the rod portion extended most An accumulator, a guide member attached to the crushing device frame, and a sliding member provided such that an end of the first hydraulic cylinder on the bottom side is rotatably attached, and can be moved back and forth along the guide member A braking device that presses the sliding member through a friction member and restrains the movement of the sliding member relative to the guide member, and the moving tooth below the first hydraulic cylinder. A pressure oil enclosed in the bottom side hydraulic chamber, the rod side end being rotatably attached, and a second hydraulic cylinder for urging the moving teeth away from the fixed teeth during crushing work Is opened when the pressure in the bottom hydraulic chamber exceeds a first set pressure set for machine protection, and the braking device causes the pressure in the bottom hydraulic chamber to reach the first set pressure or higher. The sliding member is pressed with a second set pressure that allows sliding of the sliding member when a tightening load is applied, and the discharge gap formed at the tip of the moving tooth and the fixed tooth is It is adjusted by the second hydraulic cylinder when it is stopped and the restraint of the sliding member by the braking device is released.

  According to the present invention, since it is not necessary to readjust the discharge gap even if the moving tooth moves when an overload occurs, it is possible to easily return to the crushing operation and to reduce the chance that the members slide. Therefore, the life of the member can be extended.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  1 is a side view of a self-propelled jaw crusher according to an embodiment of the present invention, FIG. 2 is a top view thereof, and FIG. 3 is a front view thereof.

  The jaw crusher shown in these drawings includes a traveling body 1, a hopper 12, a grizzly feeder 15, a crushing device 20, a power device 25, and a discharge conveyor 40. The jaw crusher in the present embodiment is, for example, a large or small construction waste, industrial waste, or a rock mining site generated at a construction site such as a concrete block carried out at the time of building demolition or an asphalt block discharged during road repair. Rocks, natural stones, etc. mined at the face are to be treated, and these are received as crushed objects and crushed. Hereinafter, the discharge conveyor 40 side may be referred to as the front, and the hopper 12 side may be referred to as the rear.

  The traveling body 1 includes a traveling device 2 and a main body frame 3 provided substantially horizontally above the traveling device 2. The traveling device 2 includes a track frame 4 attached to a lower portion of the main body frame 3, driven wheels 5 and drive wheels 6 provided at both ends of the track frame 4, and crawler belts wound around the driven wheels 5 and the drive wheels 6. 7 and a traveling hydraulic motor 8 directly connected to the drive wheel 6.

  The hopper 12 accepts an object to be crushed and expands upward. The hopper 12 is provided on the support bar 11 via the support member 13. The support bar 11 is supported by support posts 9 and 10 attached to the upper part of the main body frame 3.

  The grizzly feeder 15 sorts the material to be crushed received by the hopper 12 according to the particle size and conveys it to the crushing device 20, and is provided below the hopper 12. The grizzly feeder 15 is supported by the support bar 11 via a spring 18. The grizzly feeder 15 includes a grizzly feeder main body 15A and a feeder hydraulic motor 19 that vibrates the grizzly feeder main body 15A.

  A plurality (two in the present embodiment) of grizzly bars 17 (see FIG. 2) are housed in the grizzly feeder main body 15A. The grizzly river 17 uses vibration applied to the feeder hydraulic motor 19 to convey the object to be crushed into the hopper 12 toward the crushing device 20, and forms a stair that goes down toward the crushing device 20. Are arranged as follows. Further, the grizzly bar 17 has comb teeth 16 (see FIG. 2) in which a plurality of combs are arranged in the width direction of the main body frame 3, and an object to be crushed (fine grain (so-called slipper) smaller than the interval between the comb teeth 16. )). A chute 14 (see FIG. 1) is provided below the grizzly river 17, and fine particles and the like dropped from the comb teeth 16 are guided onto the discharge conveyor 40 through the chute 14.

  The crushing device (jaw crusher) 20 is for crushing the material to be crushed into the hopper 12, and is located in front of the hopper 12 and the grizzly feeder 15, and as shown in FIG. It is mounted near the center. Although details will be described later, the crushing device 20 is provided with a pair of fixed teeth 71 and moving teeth 72 (see FIG. 4) arranged to face each other.

  The power unit (power unit) 25 incorporates an engine and a hydraulic pump as a power source of each hydraulic actuator, and is located further forward than the crushing device 20 and is disposed on the discharge conveyor 40 side of the main body frame 3 on the support member 26. Is provided. A driver's seat 35 is provided in a compartment on the rear side of the power unit 25. The driver's seat 35 is provided with a travel operation lever 36 for operating the travel device 2.

  The discharge conveyor 40 conveys the crushed material and the like crushed by the crushing device 20 and discharges them outside the apparatus. The discharge conveyor 40 forms an upward slope from between the crawler belt 7 of the traveling device 1 through the crushing device 20 and the power unit 4 toward the front of the machine body, and via the support members 41, 42, etc. It is supported by being suspended from the main body frame 3. Further, the discharge conveyor 40 includes a driven wheel (idler) 46 and a driving wheel 47 provided at both ends of the conveyor frame 45, and a conveyance belt 50 wound around the driven wheel 46 and the driving wheel 47. The conveyor belt 50 is circulated and driven by drive wheels 47 that are driven to rotate by a discharge conveyor hydraulic motor 48 (see FIG. 2).

  The magnetic separator 55 removes foreign matter (magnetic material) such as reinforcing bars from the crushed material conveyed on the discharge conveyor 40, and is supported by being suspended from the arm member 43 via a support member 56. In the magnetic separator 55, the magnetic separator belt 59 wound around the drive wheel 57 (see FIG. 2) and the driven wheel 58 (see FIG. 2) is disposed so as to face the discharge conveyor 40. A magnetic separator 60 is directly connected to the drive wheel 57. A magnetic force generating means (not shown) is provided inside the circulation trajectory of the magnetic separator belt 59. Foreign matters such as reinforcing bars on the conveyor belt 50 are attracted to the magnetic separator belt 59 by the magnetic force acting through the magnetic separator belt 59, and are conveyed to the side of the discharge conveyor 40 and dropped.

  FIG. 4 is a side view showing the internal structure of the crushing device 20, and FIG. 5 is a hydraulic circuit diagram relating to the moving tooth moving mechanism 65.

  The crushing device 20 shown in these drawings includes a crushing device frame 61 fixed on the main body frame 3 (see FIG. 1 and the like), a fixed tooth 71 fixed to the crushing device frame 61, and a fixed tooth 71. A moving tooth 72 that is arranged and swingably provided via the eccentric shaft 62 of the flywheel 22, a moving tooth moving mechanism 65 that separates the moving tooth 72 from the fixed tooth 71 when an overload occurs, and a moving tooth 72 during crushing work. Is provided with a return cylinder (second hydraulic cylinder) 75 that attracts the moving tooth moving mechanism 65 toward (forward).

  The fixed teeth 71 and the moving teeth 72 are arranged to face each other so that their tooth plates face each other, and form a crushing chamber 63 that shrinks downward. The object to be crushed introduced into the crushing chamber 63 is crushed so as to be bitten by the fixed teeth 71 and the swinging moving teeth 72. The particle size of the crushed material discharged from the crushing device 20 is defined by the exit width of the crushing chamber 63, that is, the gap formed by the lower ends of the fixed teeth 71 and the moving teeth 72 (discharge gap).

  The flywheel 22 is rotationally driven via a belt (not shown) by a crushing device hydraulic motor 21 (see FIG. 2). The rotational movement of the flywheel 22 is converted into a swinging movement of the moving tooth 72 via the eccentric shaft 62. In the present embodiment, a structure using a belt as a drive transmission structure from the crushing device hydraulic motor 21 to the flywheel 22 has been described. However, a configuration using a chain, for example, may be used.

  The moving tooth moving mechanism 65 is for protecting peripheral members from an excessive load when an overload occurs due to, for example, a foreign matter being caught in the crushing chamber 63. It is provided on the opposite side of 63. The moving tooth moving mechanism 65 includes a toggle cylinder (first hydraulic cylinder) 66, an accumulator (pressure holding means) 67, a relief valve (pressure release means) 105 (see FIG. 5), a sliding member 68, and a guide member. 69 and a braking device 70.

  The toggle cylinder (first hydraulic cylinder) 66 supports the moving tooth 72 against the crushing reaction force, and its rod side end is rotatably attached to the moving tooth 72 via a fulcrum pin 76. ing. That is, the fulcrum pin 76 is a swing fulcrum of the moving tooth 72. As will be described later, in the normal state, the pressure in the bottom hydraulic chamber 77 of the toggle cylinder 66 is held, and the toggle cylinder 66 is held in a state where the rod portion 78 is most extended (that is, the stroke end on the extension side). Yes.

  The accumulator (pressure holding means) 67 pressurizes the inside of the bottom side hydraulic chamber 77 of the toggle cylinder 66 and holds the pressure, and is connected to the bottom side hydraulic chamber 77. Note that the pressurization of the bottom side hydraulic chamber 77 by the accumulator 67 may be performed automatically, or may be manually performed by a maintenance worker using a pressurizing pump.

Next, a hydraulic circuit diagram relating to the toggle cylinder 66 will be described with reference to FIG.
In FIG. 5, the switching valve 110 controls the supply of pressure oil to the bottom side hydraulic chamber 77 of the toggle cylinder 66. When the switching valve 110 is switched to the supply position 110 </ b> A by a command signal from the controller 81, the pressure oil discharged from the hydraulic pump 112 is supplied to the bottom side hydraulic chamber via the supply position 110 </ b> A of the switching valve 110 and the pipeline 106. 77. Thereby, since the bottom side hydraulic chamber 77 is filled with the pressure oil, the rod portion 78 can be extended.

  On the other hand, when the command signal from the controller 81 is not output to the switching valve 110, the switching valve 110 is returned to the neutral position 110C by the biasing force of the springs at both ends, and the pressure oil in the bottom side hydraulic chamber 77 and the pipe line 106 is returned. Is enclosed. Thereby, the rod part 78 is hold | maintained in the state extended most. Here, when the bottom side hydraulic chamber 77 is pressurized by the accumulator 67, the pressure in the bottom side hydraulic chamber 77 can be maintained at a predetermined value or more. Thereby, the rod part 78 can be hold | maintained in the most extended state also at the time of a crushing operation | work. In addition, a relief valve 105 and an opening / closing valve 115 that can arbitrarily release the pressure oil in the bottom side hydraulic chamber 77 are provided between the pipe line 106 and the tank 84.

  The relief valve (pressure release means) 105 releases the pressure when the pressure in the bottom side hydraulic chamber 77 exceeds the first set pressure P1 (relief pressure). The first set pressure P1 is a value set for protecting the machine around the crushing chamber 63, and is set to a value commensurate with the maximum allowable load Fm that can be supported by the toggle cylinder 66. Here, the crushing reaction force that brings the pressure in the bottom side hydraulic chamber 77 to the first set pressure P1 is defined as the first load F1 (where F1 <Fm).

  When the switching valve 110 is switched to the discharge position 110B by a command signal from the controller 81, the conduit 106 and the tank 84 are communicated with each other, and the pressure in the bottom side hydraulic chamber 77 becomes equal to the tank pressure. The extension / contraction operation of the toggle cylinder 66 is allowed.

  Returning to FIG. 4, the sliding member 68 is a plate-like member, and is rotatably attached to an end portion on the bottom portion side of the toggle cylinder 66 via a toggle pin 79. The sliding reaction force acting on the toggle cylinder 66 is transmitted to the sliding member 68 via the toggle pin 79. Further, guide members 69 that define the advancing and retreating directions of the sliding member 68 are attached to the positions of the upper surface side and the lower surface side of the sliding member 68 in the crusher frame 61. That is, the sliding member 68 is provided so as to be able to advance and retract along the guide member 69 toward the moving tooth 72.

  The braking device 70 presses the sliding member 68 and restrains the movement of the sliding member 68 relative to the guide member 69. The braking device 70 includes a pair of braking pistons 74 that press the sliding member 68 with pressure oil. The brake piston 74 is disposed so as to sandwich the sliding member 68 from a direction perpendicular to the sliding direction of the sliding member 68. Further, it is preferable to attach a friction member 73 to the surface of the brake piston 74 on the sliding member 68 side and press the sliding member 68 via the friction member 73. When the pressing is performed through the friction member 73 as described above, the sliding member 68 can be firmly restrained.

  A hydraulic chamber 110 is formed on the back surface of the brake piston 74, and the hydraulic chamber 110 is held at the second set pressure P2 during the crushing operation. The hydraulic chamber 110 is connected to a hydraulic pump 82 (see FIG. 5), and the pressure oil is sealed when the pressure in the hydraulic chamber 110 reaches the second set pressure P2 by the pressure oil supplied from the hydraulic pump. It is like that. The pressure in the hydraulic chamber 110 is monitored by the pressure sensor 88, and when the pressure in the hydraulic chamber 110 fluctuates, the pressure oil corresponding to the deviation is appropriately supplied and discharged, and the hydraulic chamber 110 has the second pressure. It is held near the set pressure P2.

  The second set pressure P2 determines the pressing force of the brake piston 74 and defines the magnitude of the crushing reaction force (second load F2) at which the sliding member 68 on the friction member 73 starts to slide. . The second load F2 is set to a value that is greater than or equal to the first load F1 and less than the maximum allowable load Fm (F1 ≦ F2 <Fm). That is, the sliding member 68 is restrained by the braking device 70 so as to slide for the first time when the second load F2 is applied.

  Note that one braking piston 74 of the present embodiment is provided above and below the sliding member 68, and is disposed to face each other with the sliding member 68 interposed therebetween. Further, the friction member 73 is attached to the brake piston 74 so as to be replaceable on the assumption that the service life is exhausted by repeated sliding operations.

Next, a hydraulic circuit diagram relating to the braking device 70 will be described with reference to FIG.
In FIG. 5, a switching valve 80 is a switching valve that switches between locking and unlocking of the sliding operation of the sliding member 68. That is, when the switching valve 80 is switched to the lock position 80 A by a command signal from the controller 81, the pressure oil discharged from the hydraulic pump 82 is supplied to the hydraulic chamber via the lock position 80 A of the switching valve 80 and the pipe 83. 110. As a result, the brake piston 74 presses the friction member 73 against the sliding member 68, and the sliding operation of the sliding member 68 is braked (ie, locked).

  On the other hand, when the switching valve 80 is switched to the unlock position 80B by a command signal from the controller 81, the conduit 83 and the tank 84 are communicated with each other, and the pressure in the hydraulic chamber 110 becomes equal to the tank pressure. As a result, the pressing force of the brake piston 74 against the sliding member 68 is released, and the sliding operation of the sliding member 68 is allowed (that is, the unlocking state is established).

  On the other hand, when the command signal from the controller 81 is not output to the switching valve 80, the switching valve 80 is returned to the neutral position 80C by the biasing force of the springs at both ends, and the pressure oil in the hydraulic chamber 110 and the pipe 83 is enclosed. Is done. Between the pipe 83 and the tank 84, there is an on-off valve 85 that can arbitrarily open the lock of the sliding member 68, and a relief valve 86 that sets the relief pressure in the hydraulic chamber 110 and the pipe 83. Is provided. The pipe 83 is provided with an accumulator 87, a hydraulic chamber 110, and a pressure sensor 88 for detecting the pressure in the pipe 83. The pressure value detected by the pressure sensor 88 is output to the controller 81. The controller 81 outputs a command signal to the motor 89 for driving the hydraulic pump 82 in accordance with the detected value, and appropriately drives the hydraulic pump 82 so that the pressure in the hydraulic chamber 110 and the pipe line 83 is substantially equal to the second set pressure P2. It is supposed to hold on.

  By the way, as a technique related to the moving tooth moving mechanism, unlike the present embodiment, there is a technique in which the toggle plate is supported only by a hydraulic cylinder filled with pressure oil of a predetermined pressure from the front side of the machine body. In this type of technology, the hydraulic cylinder expands and contracts in conjunction with fluctuations in the crushing reaction force during the crushing operation, so that the discharge gap between the fixed teeth and the moving teeth fluctuates, resulting in variations in the particle size of the crushed material. There was a problem. However, in the present embodiment, the toggle cylinder 66 is firmly supported by using the frictional force generated on the sliding surfaces of the sliding member 68 and the friction member 73, so that the crushing reaction force that fluctuates during the crushing operation is reduced. Even if it acts, the discharge gap does not fluctuate. Therefore, according to this Embodiment, the crushed material of a fixed particle size can always be produced.

  Returning to FIG. 4, the return cylinder (second hydraulic cylinder) 75 is positioned below the toggle cylinder 66, and the end portion on the rod portion side is rotatably attached to the moving tooth 72. Similar to the hydraulic chamber 110 of the brake piston 74, pressure oil of a constant pressure is enclosed in the head side hydraulic chamber (not shown) of the return cylinder 75 during the crushing operation. In other words, the return cylinder 75 during the crushing operation is urged in a direction in which the moving tooth 72 is separated from the fixed tooth 71 by the pressure oil in the head side hydraulic chamber. In this way, when an urging force is applied to the lower portion of the moving tooth 72 via the return cylinder 75, the eccentric rotation locus of the moving tooth 72 can be stabilized.

  The return cylinder 75 is used when adjusting (setting adjustment) the discharge gap between the fixed tooth 71 and the moving tooth 72. That is, if the return cylinder 75 is appropriately expanded and contracted to change the position of the moving tooth 72, the desired discharge gap can be set.

Next, a hydraulic circuit for driving the hydraulic cylinder 75 will be described with reference to FIG.
In FIG. 5, the switching valve 90 is a switching valve for controlling the expansion / contraction direction and expansion / contraction amount of the hydraulic cylinder 75. In the adjustment (set adjustment) of the discharge gap between the fixed tooth 71 and the moving tooth 72, when the gap is reduced, the switching valve 90 is switched to the extended position 90A by the command signal from the controller 81, and the switching valve 91 is communicated. At the position 91A, the switching valve 92 is switched to the cutoff position 92A. Thus, the pressure oil discharged from the hydraulic pump 93 is guided to the bottom hydraulic chamber of the hydraulic cylinder 75 through the pipe line 95 via the communication position 91A of the switching valve 91 and the extended position 90A of the switching valve 90. Thereby, the hydraulic cylinder 75 is extended, and the moving tooth 72 moves in the direction of the fixed tooth, so that the gap between the fixed tooth 71 and the moving tooth 72 is reduced.

  On the other hand, when the gap is increased, the switching valve 90 is switched to the contracted position 90B by a command signal from the controller 81 (the switching valve 91 and the switching valve 92 are the same switching positions as described above). As a result, the pressure oil from the hydraulic pump 93 is guided to the head side hydraulic chamber (not shown) of the hydraulic cylinder 75 via the conduit 96 through the contracted position 90B of the switching valve 90. As a result, the hydraulic cylinder 75 is shortened, and the moving tooth 72 moves in the direction opposite to the fixed tooth, so that the gap between the fixed tooth 71 and the moving tooth 72 is increased. The expansion and contraction operation of the hydraulic cylinder 75 is performed after the sliding member 66 is unlocked.

  At the time of crushing work, the command signal from the controller 81 to the switching valve 90 is turned OFF, the switching valve 90 is returned to the neutral position 90C by the biasing force of the spring, the switching valve 91 is set to the cutoff position 91B, and the switching valve 92 is set to Returning to the communication position 92B, pressure oil is sealed in the head side hydraulic chamber, the pipe 96, and the pipe 97 connected via the communication position 92B of the pipe 96 and the switching valve 92 (see FIG. 5). State shown). Between the pipe 97 and the tank 84, there are provided an opening / closing valve 98 capable of arbitrarily releasing the sealed pressure, and a relief valve 99 for setting a relief pressure in the head side hydraulic chamber and the pipes 96, 97. . The pipe 97 is provided with a pressure sensor 101 for detecting the pressure in the accumulator 100, the head side hydraulic chamber, and the pipes 96 and 97. The pressure value detected by the pressure sensor 101 is output to the controller 81 in the same manner as the pressure sensor 88, and is the same as the pressure constant holding control in the hydraulic chamber 78 and the pipe 83 described above. Thus, the pressure in the head side hydraulic chamber and the pipes 96 and 97 is also kept substantially constant by the controller 81.

  Next, the operation of the jaw crusher of the present embodiment configured as described above will be described.

  Before the crushing operation is performed, the clearance between the fixed tooth 71 and the moving tooth 72 is first adjusted in order to obtain a crushed material having a desired particle size. First, pressure oil is sealed in the bottom side hydraulic chamber 77 of the toggle cylinder 66 and the pressure is held by the accumulator 67, and the toggle cylinder 66 is held in a state where the rod portion 78 is most extended. Next, the switching valve 80 is switched to the unlock position 80B by a command signal from the controller 81, and the pressing force against the sliding member 68 by the brake piston 74 is released. As a result, the sliding member 68 is unlocked.

  In this state, set adjustment is performed using the return cylinder 75. For example, in order to reduce the discharge gap, the switching valve 90 is switched to the extended position 90A by a command signal from the controller 81, the switching valve 91 is switched to the communication position 91A, and the switching valve 92 is switched to the cutoff position 92A. The pressure oil from the pump 93 is guided to the bottom hydraulic chamber of the hydraulic cylinder 75 through the pipe line 95. As a result, the hydraulic cylinder 75 is extended, and the moving tooth 72 moves in the direction of the fixed tooth 71, so that the discharge gap can be reduced.

  On the other hand, when the clearance is increased, the switching valve 90 is switched to the contracted position 90B by a command signal from the controller 81 (the switching positions similar to those described above for the switching valve 91 and the switching valve 92). The pressure oil is guided to the rod side hydraulic chamber (not shown) of the hydraulic cylinder 75 through the pipe 96. As a result, the hydraulic cylinder 75 is shortened, the moving tooth 72 is moved in the opposite direction to the fixed tooth 71, and the discharge gap is increased.

  When the set adjustment is thus completed, the switching valve 80 is then switched to the lock position 80A by a command signal from the controller 81, and the pressure oil from the hydraulic pump 82 is guided to the hydraulic chamber 110 via the conduit 83. It is burned. Thereby, the braking piston 74 presses the friction member 73 against the sliding member 68, and the sliding operation of the sliding member 68 is locked. Then, the command signal from the controller 81 is turned OFF, the switching valve 80 is returned to the neutral position 80C, and the pressure when the hydraulic oil in the hydraulic chamber 110 and the pipe 83 locks the sliding member 66 (second setting). Sealed with pressure P2).

  In addition, the command signal from the controller 81 to the switching valve 90 is turned OFF, the switching valve 90 is switched to the neutral position 90C, and the command signals to the switching valve 91 and the switching valve 92 are also turned OFF, so that the cutoff position 91B and Returning to the communication position 92B, the pressure oil in the head side hydraulic chamber and the pipes 96 and 97 is sealed with an appropriate pressure. As a result, a force to shorten the hydraulic cylinder 75 acts, and the moving tooth 72 is urged toward the braking device 70 in an approaching direction with an appropriate compressive load.

  In the jaw crusher set and adjusted as described above, the object to be crushed introduced into the hopper 12 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 interval between the comb teeth 16 of the grizzly bar 17 fall from the gap and are guided onto the discharge conveyor 40 via the chute 14. On the other hand, an object to be crushed (large lump) larger than the gap between the comb teeth 16 is conveyed to the crushing device 20.

  The object to be crushed introduced into the crushing device 20 is crushed to a predetermined particle size according to the discharge gap between the fixed tooth 71 and the moving tooth 72. During the crushing operation, the moving tooth 72 according to the present embodiment is firmly supported by the toggle cylinder 66 held at the stroke end on the extension side and the braking device 70 that restrains the movement of the toggle cylinder 66. The discharge gap formed between the two and 71 is kept constant even when the crushing reaction force fluctuates. Thereby, the to-be-crushed object which has a fixed particle size is discharged | emitted on the discharge conveyor 40 from a discharge gap. The crushed material guided onto the discharge conveyor 40 merges with the fine particles guided through the chute 14, and after the foreign matter such as rebar is adsorbed and removed by the magnetic separator 55, it is discharged outside the machine.

  By the way, during the crushing operation, the crushing reaction force received by the moving tooth 72 from the object to be crushed is first transmitted to the toggle cylinder 66 and further to the sliding member 68 via the toggle pin 79. At this time, in the case of a normal load, the reaction force transmitted from the moving tooth 72 is received by the toggle cylinder 66 that holds the pressure in the bottom hydraulic chamber 77.

  However, when an overload occurs due to foreign object biting or the like and a crushing reaction force exceeding the first load F1 acts on the toggle cylinder 66, the pressure in the bottom side hydraulic chamber 77 exceeds the first set pressure P1. As a result, the pressure in the bottom hydraulic chamber 77 is released by the relief valve 105, so that the toggle cylinder 66 is shortened. As a result, the moving tooth 72 can be separated from the fixed tooth 71, so that overload can be eliminated. Since the first load F1 is set to a value smaller than the maximum allowable load Fm as described above, members such as the toggle cylinder 66 can be protected from damage even if an overload occurs.

  On the other hand, in order to re-extend the toggle cylinder 66 once shortened in order to restart the crushing operation, the switching valve 110 is switched to the supply position 110A, and the oil is filled into the bottom hydraulic chamber 77 by the hydraulic pump 112. When the bottom side hydraulic chamber 77 is filled with oil, the accumulator 67 pressurizes the bottom side hydraulic chamber 77 to hold the pressure again. Thus, if the pressure in the bottom side hydraulic chamber 77 is restored again, the toggle cylinder 66 can be extended again to the stroke end on the extension side, so that the crushing operation can be resumed early. In particular, when only the toggle cylinder 66 is contracted without sliding the sliding member 68 as described above, the crushing operation can be resumed without adjusting the discharge gap again, so that the crushing efficiency can be improved. .

  On the other hand, when a crushing reaction force exceeding the second load F2 acts on the sliding member 68 via the toggle cylinder 66 due to an overload during the crushing operation, the toggle cylinder 66 contracts and the sliding member 68 moves backward. Then, the moving tooth 72 moves away from the fixed tooth 71. Thereby, even if a sudden and huge load acts, the toggle cylinder 66, the braking device 70, etc. can be protected from damage. That is, the braking device 70 and the sliding member 68 of the present embodiment function as a second moving tooth moving device different from the toggle cylinder 66.

  Next, the effect of this embodiment will be described.

  If the technique described in Patent Document 1 is a comparative example of the present embodiment, in the comparative example, the movement of the toggle plate is directly restrained by the sliding member. When moved, the sliding member remains displaced from the initial setting position. For this reason, the discharge gap must be readjusted by releasing the restraint of the sliding member, and the crushing operation must be interrupted during the adjustment operation. Further, in the comparative example, since the sliding member and the friction plate slide each time an overload is applied, the replacement work may be forced when the life of these members is exhausted by repeating this sliding operation. .

  On the other hand, in this embodiment, the crushing operation is performed with the toggle cylinder 66 held at the stroke end on the extension side by the accumulator 67. When an overload occurs, the toggle cylinder 66 is shortened and moved. The tooth 72 is moved. If the moving tooth moving mechanism 65 is configured in this way, the position of the sliding member 68 remains the initial setting even when the toggle cylinder 66 is contracted, so that the clearance adjustment can be performed simply by refilling the bottom hydraulic chamber 77 with pressure oil. It is possible to return to the crushing work early without performing it. In addition, according to the present embodiment, except when a load greater than or equal to the second load F2 is applied, overload can be avoided by extending and retracting only the toggle cylinder 66, so that the sliding member 68 slides. The opportunity to do so can be reduced. Thereby, the lifetime of the sliding member 68 and the friction member 73 can be prolonged from the said comparative example. As described above, according to the present embodiment, it is not necessary to readjust the discharge gap even if the moving tooth 72 moves in the event of an overload. Since the sliding opportunity is reduced, the life of the member can be extended.

  In the present embodiment, as described above, the toggle cylinder 66 is supported by the sliding member 68 that is pressed by the brake piston 74 at the second set pressure P2. If comprised in this way, when the sudden and huge crushing reaction force (2nd load F2) exceeding the 1st load F1 will act, the crushing apparatus 20 and its peripheral device can be protected from damage.

  In the above description, the example in which oil is supplied to the bottom side hydraulic chamber 77 using the hydraulic pump 112 has been described. However, when an overload occurs, a configuration in which a maintenance worker supplies supplementary oil manually is employed. May be. In this case, it is preferable to connect the bottom side hydraulic chamber 77 and a tank (unlike the tank 84, dedicated to the oil discharged from the hydraulic chamber 77) through a pipeline, and provide the relief valve 105 in the pipeline. This is because the configuration related to the toggle cylinder 66 can be simplified.

  In the above description, the example using the relief valve 105 as the pressure release means of the bottom side hydraulic chamber 77 has been described. However, other configurations may be used. As an example, when the pressure sensor 104 provided in the pipe line 106 is used and the inside of the pipe line 106 exceeds the first set pressure P1, the switching valve 110 is switched to the position 110B and the inside of the bottom side hydraulic chamber 77 is moved. There are methods such as tank pressure.

  Furthermore, although the example which applied this invention to the self-propelled jaw crusher was demonstrated above, it cannot be overemphasized that it can utilize for a stationary type.

The side view of the self-propelled jaw crusher which is an embodiment of the invention. The top view of the self-propelled jaw crusher which is an embodiment of the invention. The front view of the self-propelled jaw crusher which is an embodiment of the invention. The side view which shows the internal structure of the crushing apparatus of the self-propelled jaw crusher which is embodiment of this invention. The hydraulic circuit diagram regarding the moving tooth moving mechanism of the self-propelled jaw crusher which is embodiment of this invention.

Explanation of symbols

65 Moving tooth moving mechanism 66 Toggle cylinder (first hydraulic cylinder)
67 accumulator 68 sliding member 69 guide member 70 braking device 71 fixed tooth 72 moving tooth 73 friction member 74 braking piston 75 return cylinder (second hydraulic cylinder)
77 Bottom side hydraulic chamber 78 Rod portion 105 Relief valve F2 First load F2 Second load P1 First set pressure P2 Second set pressure

Claims (4)

A crusher frame;
Fixed teeth fixed to the crusher frame;
In a jaw crusher provided with a moving tooth that is arranged to face this fixed tooth and swingably provided via an eccentric shaft,
A first hydraulic cylinder in which an end on the rod side is rotatably attached to the moving tooth;
Pressure holding means for holding the pressure of the bottom side hydraulic chamber of the first hydraulic cylinder in order to hold the first hydraulic cylinder in a state where the rod portion is most extended;
Pressure release means for releasing the pressure of the bottom side hydraulic chamber when the pressure of the bottom side hydraulic chamber exceeds a first set pressure set for machine protection;
A guide member attached to the crusher frame;
A sliding member that is rotatably attached to an end of the first hydraulic cylinder on the bottom side, and is provided so as to advance and retreat along the guide member;
A braking device that presses the sliding member and restrains the movement of the sliding member relative to the guide member;
The end of the rod side is rotatably attached to the moving tooth and is positioned below the first hydraulic cylinder, and the moving tooth is in a state in which the brake device restrains the movement of the sliding member during crushing work. A jaw crusher comprising: a second hydraulic cylinder biased in a direction away from the fixed teeth. The jaw crusher according to claim 1, wherein
The braking device presses the sliding member with a second set pressure that allows the sliding member to slide when a load is applied to bring the pressure in the bottom side hydraulic chamber to the first set pressure or higher. Jaw crusher characterized by being. The jaw crusher according to claim 1 or 2,
The pressure holding means is an accumulator connected to the bottom hydraulic chamber;
The jaw crusher, wherein the pressure release means is a relief valve connected to the bottom hydraulic chamber. A crusher frame;
Fixed teeth fixed to the crusher frame;
In a jaw crusher provided with a moving tooth that is arranged to face this fixed tooth and swingably provided via an eccentric shaft,
A first hydraulic cylinder in which an end on the rod side is rotatably attached to the moving tooth;
An accumulator for holding the pressure of the bottom hydraulic chamber of the first hydraulic cylinder in order to hold the first hydraulic cylinder in a state where the rod portion is most extended;
A guide member attached to the crusher frame;
A sliding member that is rotatably attached to an end of the first hydraulic cylinder on the bottom side, and is provided so as to advance and retreat along the guide member;
A braking device that presses the sliding member via a friction member and restrains the movement of the sliding member relative to the guide member;
Below the first hydraulic cylinder, a second hydraulic cylinder is attached to the moving tooth so that the end on the rod portion side is rotatable, and the moving tooth is urged away from the fixed tooth during crushing work Prepared,
The pressure oil sealed in the bottom side hydraulic chamber is released when the pressure in the bottom side hydraulic chamber exceeds a first set pressure set for machine protection,
The braking device presses the sliding member with a second set pressure that allows the sliding member to slide when a load is applied to bring the pressure of the bottom side hydraulic chamber to the first set pressure or higher.
The discharge gap formed at the tip of the moving tooth and the fixed tooth is adjusted by the second hydraulic cylinder when the moving tooth is stopped and the restraint of the sliding member by the braking device is released. Jaw crusher characterized by that.

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