JP2011011193A - Crusher - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a crusher suppressing damage of bits when biting foreign matter.SOLUTION: The crusher is provided with: crushing apparatus frames 20; a crushing rotor 15 having the bits 36 on an outer periphery of a plate integrated body 101 rotatably provided in relation to the crushing apparatus frames 20; a crushing chamber 27 housing the crushing rotor 15; an anvil 34 set in the crushing chamber 27 so as to face an outermost diameter part of a rotary trajectory of the crushing rotor 15 via a space; anvil frames 40 supporting the anvil 34 and supported turnably in relation to the crushing apparatus frames 20; and a shear pin 43 allowing the turning of the anvil frames 40 when an impact force exceeding a set value is applied to the anvil 34 and separating the anvil 34 from the crushing chamber 27 to open the crushing chamber 27. The bits 36 are turnably mounted in the direction along a face orthogonal to a rotary shaft 100 of the crushing rotor 15.

Description

  The present invention occurs due to the use of declining branches, thinned timber, remaining wood from felled wood, demolition of wooden buildings, etc., due to the creation and maintenance of forests, for the reuse and volume reduction of waste. The present invention relates to a crusher that mainly crushes waste wood and the like.

  In the crushing apparatus of Patent Document 1, a crushing rotor provided with a bit on the outer peripheral surface is rotated at high speed in a crushing chamber provided with an anvil (fixed blade) and a screen, and a crushing object introduced by a feed conveyor is first hit and crushed with a bit. To do. The crushed pieces hit by the bit collide with the anvil on the front side in the direction of rotation of the crushing rotor, or are crushed by being hit by the subsequent bit while staying around the anvil, and then cross the anvil. Further crushing action due to collision and rubbing with the screen. As the crushing rotor circulates along the rotation of the crushing rotor, the crushing pieces are subjected to a series of crushing operations and are finely divided, and those having a size that passes through the screen are discharged through the screen.

JP 2005-319349 A

  In the crusher of the above-mentioned patent document 1, the anvil frame to which the anvil is fixed is configured to be rotatable with respect to the frame of the crushing device, and the anvil frame and the crushing device frame are separately connected via a shear pin (rotation permitting member). ing. With this mechanism, when a non-crushable foreign matter such as a metal lump mixed in the object to be crushed is caught between the bit and the anvil, the shear pin breaks due to the impact force acting on the anvil, and the anvil frame rotates. As a result, the crushing chamber is opened and foreign matter is discharged from the crushing chamber, so that the main structure of the crushing device is prevented from being damaged.

  However, it has become clear from the knowledge of the present inventors that when a foreign object actually bites between the bit and the anvil and the shear pin breaks, the bit of the crushing rotor is often damaged even if the anvil frame rotates. It was. The main cause of bit damage is thought to be the impact force caused by the crushing reaction force from the anvil transmitted when the foreign object is caught.

  For example, if the anvil frame rotates at a speed commensurate with the peripheral speed of the crushing rotor at the moment when the foreign object is caught, the crushing reaction force from the anvil is greatly reduced. However, because there is an inertia in practice, the anvil frame does not immediately rotate at high speed when a foreign object is caught. That is, at the moment when the shear pin breaks, the speed difference between the escape operation of the anvil frame and the rotation operation of the crushing rotor is large, and a large crushing reaction force acts on the crushing rotor from the anvil through the foreign matter. The impact force at this time is considered to be the cause of damaging the most fragile bit in the crushing rotor. If the bit is damaged, it takes a long time to repair the bit, resulting in downtime.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a crusher capable of suppressing damage to a bit when a foreign object is caught.

  (1) In order to achieve the above object, the present invention includes a crushing device frame, a plate integrated body provided rotatably with respect to the crushing device frame, and a bit provided on an outer peripheral portion of the plate integrated body. A crushing rotor, a crushing chamber containing the crushing rotor, an anvil provided in the crushing chamber so as to face the outermost diameter portion of the rotation trajectory of the crushing rotor via a gap, and a frame that supports the anvil An anvil frame supported rotatably with respect to the crushing device frame, and when an impact force exceeding a set value is applied to the anvil, the anvil frame is allowed to rotate, and the anvil is crushed. Rotation permitting means for opening the crushing chamber away from the chamber, and a direction along a plane perpendicular to the rotation axis of the crushing rotor on the outer peripheral portion of the plate assembly Wherein the bit rotatably is mounted.

  (2) In the above (1), preferably, the rotation permission means is a shear pin that connects the anvil frame to the crushing device frame.

  (3) In the above (1), preferably, the rotation permitting means includes a stopper member capable of moving back and forth in a direction intersecting a rotation tangent of the anvil frame, and biasing the stopper member with a set biasing force. And a mechanism for holding the posture of the anvil frame by restraining the anvil frame with the stopper member.

(4) In any one of the above (1) to (3), preferably, Ir: moment of inertia of the crushing rotor, Δωr: deviation in rotation speed of the crushing rotor before and after operation of the rotation permitting means, Ic: the bit Moment of inertia of the rotation component, Δωc: deviation of the rotation component of the bit before and after operation of the rotation permission means, If: moment of inertia of the anvil frame, Δωf: deviation of rotation speed of the anvil frame before and after operation of the rotation permission means , M: mass of the anvil frame, g: gravitational acceleration, h: height deviation of the center of gravity of the anvil frame, Ep: (Ir × Δωr ² ) / 2 + (Ic) XΔωc ² ) / 2 = (If × Δωf ² ) / 2 + mgh + Ep is satisfied.

  (5) In any one of the above (1) to (4), preferably, the anvil is disposed on a surface including a rotation shaft of the anvil frame and a rotation shaft of the crushing rotor when the rotation permission unit is not operated. And the anvil frame is configured not to interfere with an extension line extending from the position of the anvil to the rotation tangent of the crushing rotor after the rotation permission means is actuated. .

  According to the present invention, the excessive crushing reaction force from the anvil to the bit is converted into the rotational motion of the bit, so that the bit can be prevented from being damaged when the foreign object is caught.

It is a side view showing the whole crusher structure concerning a 1st embodiment of the present invention. It is a top view which shows the whole structure of the crusher which concerns on the 1st Embodiment of this invention. It is a see-through | perspective side view which shows the principal part structure of the crushing function structure part with which the crusher which concerns on the 1st Embodiment of this invention was equipped. It is an arrow line view by the IV-IV line in FIG. In the crusher which concerns on the 1st Embodiment of this invention, it is explanatory drawing showing operation | movement of the crushing apparatus when a foreign material bites between a bit and an anvil, and represents the mode before foreign material biting. In the crusher which concerns on the 1st Embodiment of this invention, it is explanatory drawing showing operation | movement of the crushing apparatus when a foreign material bites between a bit and an anvil, and represents the mode of the moment of foreign material biting. . In the crusher which concerns on the 1st Embodiment of this invention, it is explanatory drawing showing operation | movement of the crushing apparatus when a foreign material bites between a bit and an anvil, and represents the mode of the moment of a shear pin fracture | rupture. In the crusher which concerns on the 1st Embodiment of this invention, it is explanatory drawing showing operation | movement of the crushing apparatus when a foreign material bites between a bit and an anvil, and represents the mode after anvil frame rotation. . It is a fragmentary top view which shows the principal part of the crusher which concerns on 2nd Embodiment of this invention. It is arrow sectional drawing of the anvil frame 20 grade | etc., By the XX line in FIG.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 is a side view showing the overall structure of a crusher according to a first embodiment of the present invention, and FIG. 2 is a plan view thereof. The directions corresponding to the right and left in FIGS. 1 and 2 are the front and rear of the crusher.

  The crusher illustrated in FIG. 1 and FIG. 2 is crushed by a traveling body 1 for traveling on its own, a crushing function component 2 that crushes an object to be crushed provided on the traveling body 1, and a crushing function component 2. It includes a discharge conveyor 3 that transports the crushed material (wood chips) and discharges it to the outside of the machine, a power unit (power unit) 4 that includes an engine that is a power source of each mounted device, and the like. The crushing object of the crusher according to the present embodiment includes, for example, pruned branches and thinned wood generated in the forest, wood such as waste wood generated when the building is demolished, waste plastic material, waste Tatami and bamboo are also included. The wood is not limited to relatively dry and hard wood, but also includes soft wood with a large amount of water such as roadside branches and roadside weeds that have just been pruned. In the present embodiment, these objects to be crushed are collectively referred to as objects to be crushed.

  The traveling body 1 includes a track frame 5, driving wheels 6 and driven wheels 7 provided at both front and rear ends of the track frame 5, a driving device (traveling hydraulic motor) 8 having an output shaft connected to the shaft of the driving wheel 6, and driving A crawler belt (endless track crawler belt) 9 is provided around the wheel 6 and the driven wheel 7. A main body frame 10 is provided on the track frame 5, and the main body frame 10 supports the crushing function component 2, the discharge conveyor 3, the power unit 4, and the like.

  The crushing function component 2 was introduced by a hopper 11 that receives the material to be crushed, a feed conveyor 12 (see FIG. 2) that is a means for conveying the material to be crushed arranged in the hopper 11, and the feed conveyor 12. A crushing device 13 for crushing the material to be crushed (see FIG. 3), and a crushing device 13 that presses the material to be crushed before the crushing device 13 and introduces the material to be crushed into the crushing device 13 in cooperation with the feed conveyor 12. The press feeder apparatus 14 (refer FIG. 3) sent in is provided. The configuration of the crusher delivery component 2 will be described later.

  The discharge conveyor 3 discharges the crushed material discharged from the crushing device 13 to the outside of the machine, and includes a conveyor frame 50, driving wheels and driven wheels (not shown) provided at both front and rear ends of the conveyor frame 50, and driving wheels. And a driven belt (not shown) wound around the conveyor belt, a conveyor cover 51 attached to the conveyor frame 50 so as to cover the upper surface of the conveyor belt, and a drive device for rotating the drive wheel (for the discharge conveyor) Hydraulic motor) 52 and the like. A portion on the discharge side (front side) of the discharge conveyor 3 is suspended and supported by a support member 53 that protrudes from a support portion of the power unit 4, and an end portion on the opposite side (rear side) is interposed via a support member 54. The main body frame 10 is suspended and supported. The discharge conveyor 3 extends forward from the lower side of the crushing device 13 in the space between the left and right endless track crawlers 9 and is inclined upward from the lower side of the power unit 4 to the front side. However, a straight first conveyor that extends forward from below the crushing device 13 in the lower region of the main body frame 10 and forward from below the discharge end of the first conveyor without using the bent conveyor in this way. In some cases, a transfer type discharge conveyor may be configured with a straight second conveyor that is inclined upward.

  The power unit 4 is mounted on the front end of the main body frame 10 via a support member 55. A driver's seat 56 is provided in the rear right side (lower side in FIG. 2) of the power unit 4. The driver's seat 56 is provided with an operation lever 57 for operating the crusher. Below the driver's seat 56 is provided an operation panel 58 for performing other operations, settings, monitoring, and the like. In this example, the operation panel 58 is provided on the side of the machine body so that an operator can operate on the ground, but it may be provided in the driver's seat 56.

  3 is a see-through side view showing the main structure of the crushing function component 2, and FIG. 4 is an arrow view taken along line IV-IV in FIG. However, in FIG. 4, the pressing feeder device 14 is omitted and omitted.

  As shown in FIG. 3 and FIG. 4, the feed conveyor 12 functions as a feeder together with the pressure feeder device 14 to convey and supply the object to be crushed toward the crushing rotor 15. The feed conveyor 12 includes a sprocket-like drive wheel 16 disposed to face the rear side of the crushing rotor 15, a driven wheel (not shown) provided on the opposite side (near the rear end of the machine body), and these drive wheels. 16 and a driven belt (chain belt) 17 (see FIG. 2) wound between a driven wheel and a plurality of rows (four rows in this example) in the width direction. It extends almost horizontally toward the rear. The driven wheels are supported by bearings 19 (see FIG. 1) provided at the rear portions of the left and right side wall bodies 18 (see FIG. 1) of the hopper 11, and the drive wheels 16 are supported at the front portions of the side wall bodies 18 (or the left and right sides of the crushing device 13). It is supported by a bearing (see FIG. 1) provided on the crushing device frame 20) constituting the side wall. The rotating shaft 21 of the driving wheel 16 of the feed conveyor 12 is connected to an output shaft of a driving device (not shown) provided outside the bearing in the body width direction via a coupling or the like. By rotating the driving device (not shown), the conveyor belt 17 is circulated between the driving wheel 16 and the driven wheel, and the object to be crushed is supplied to the crushing device 13.

  The pressing feeder device 14 includes a rotating shaft 22 extending in the body width direction above the crushing rotor 15, a support member 23 supported so as to be rotatable in the vertical direction about the rotating shaft 22, and a supporting member 23. The presser roller 24 is rotatably supported on the rear side of the crushing rotor 15 and faces the conveying surface of the feed conveyor 12, and a hydraulic cylinder 29 that rotates the presser roller 24 up and down.

  The rotating shaft 22 is rotatably supported by a bearing (not shown) provided on the crushing device frame 20.

  The support member 23 includes an arm portion 25 that rotates about a rotation shaft 22 and a bracket portion 26 that is attached to the distal end side of the arm portion 25 and that is attached to a press roller. The lower surface of the arm portion 25 is curved in a substantially arc shape, and a curved plate 28 is attached to the lower portion of the curved portion.

  The presser roller 24 corresponds to the width of the conveying surface of the feed conveyor 12 in the machine body width direction (the direction perpendicular to the paper surface in FIG. 3), and is set equal to or slightly larger than the conveying surface of the feed conveyor 12. ing. The presser roller 24 rides on the object to be crushed on the feed conveyor 12, presses the object to be crushed by its own weight, and corresponds to the conveyance speed of the feed conveyor 12 by a driving device (not shown) built in the body. The object to be crushed is supplied to a crushing chamber 27 (described later) accommodating the crushing rotor 15 in cooperation with the feed conveyor 12 by rotating at the peripheral speed.

  The hydraulic cylinder 29 is forcibly moved up and down during maintenance or the like, and is attached to a bracket 30 fixed to the crushing device frame 20 via a beam provided at an upper position near the front end of the arm 25. However, the rod side end portion is rotatably connected to a bracket 32 provided at the rear end portion of the upper surface of the arm portion 25.

  The crushing device 13 is located on a substantially central portion in the longitudinal direction of the main body frame 10 (see FIG. 1), and as shown in FIG. 3, the crushing rotor 15 that rotates at high speed in the crushing chamber 27 and the rotation of the crushing rotor 15. An anvil (repulsion plate) 34 provided in the crushing chamber 27 is provided so as to face the outermost diameter portion of the locus via a gap.

  The crushing rotor 15 has a configuration in which a plurality of bits 36 are provided on the outer peripheral portion of the plate assembly 101 that is rotatably provided with respect to the crushing device frame 20.

  The rotating shaft 100 of the plate assembly 101 is rotatably supported by bearings 102 provided on the outer wall surfaces of the left and right crushing device frames 20 of the crushing device 13, and a driving device (hydraulic motor, FIG. (Not shown). The plate assembly 101 includes a plurality of plate-like (for example, disc-like) plates 35 arranged with a gap in the extending direction of the rotating shaft 100. The rotation shaft 100 of the crushing rotor 15 passes through the center of these plates 35, and each plate 35 is fixed to the outer peripheral portion of the rotation shaft 100 and rotates integrally with the rotation shaft 100. In the vicinity of the outer peripheral portion of the plate 35, a shaft 37 penetrates in the extending direction of the rotary shaft 100. A plurality of shafts 37 are provided in the rotational direction of the crushing rotor 15 with respect to the plate assembly 101 (in this example, four diameters at a pitch of 90 degrees), and each of the shafts 37 penetrates through each plate 35.

  By passing the shaft 37 together with the plate 35, the bit 36 is connected to the outer peripheral portion of the plate assembly 101 so as to be rotatable in a direction along a plane orthogonal to the rotation shaft 100 of the crushing rotor 15. That is, the bit 36 is interposed in each gap between the adjacent plates 35, 35 and is connected to the plate assembly 101 via each shaft 37. The center of gravity of each bit 36 is deviated from the position through the shaft 37, and in the following description, a portion on the center of gravity side of the insertion position of the shaft 37 of the bit 36 is appropriately described as a “striking portion” of the bit 36. In the case of the present embodiment, the rotating shaft 100 is rotated about the rotation shaft 100 in a posture (in the state of FIG. 3) in which the striking portion is directed radially outward of the crushing rotor 15 with respect to the shaft 37 due to the centrifugal force due to the rotation of the crushing rotor 15. A slight gap is secured between the outermost diameter portion of the locus of the bit 36 and the anvil 34. The radius of the trajectory of the bit 36 becomes maximum when the striking portion is in a posture in which it is directed radially outward.

  There is no particular limitation on the shape of the bit 36 except that the center of gravity is eccentric to the striking portion side and the tip of the striking portion constitutes the outermost diameter portion of the trajectory of the crushing rotor 15, but the operation of the crushing rotor 15 is not limited. In the present embodiment, the bit 36 has a thickness (axial dimension) equivalent to several 35 plates so that a suitable striking force is secured as a bit by the peripheral speed inside.

  The anvil 34 is supported by the anvil frame 40 in a posture in which the collision surface 39 is opposed to the crushing pieces that circulate in the crushing chamber 27 as the crushing rotor 15 rotates. The anvil 34 is attached to the upstream side in the forward rotation direction of the crushing rotor 15 with respect to the curved plate 41 constituting a part of the inner wall of the crushing chamber 27 in the anvil frame 40. Further, as shown in FIG. 4, the anvil 34 extends in the width direction of the machine body, and there is a slight gap between the left and right crushing device frames 20, but it extends almost the full width of the crushing chamber 27 and crushes. It has the same length as the rotor 15.

  The anvil frame 40 that holds the anvil 39 is supported so as to be pivotable in the front-rear direction about the pivot shaft 31 supported by the crusher frame 20 above the pivot shaft 22 of the above-described pressing feeder device 14. In normal times, the support block 42 fixed to the inner wall surface of the crushing device frame 20 is supported via a shear pin 43 to restrain the rotation operation.

  The shear pin 43 serves as a rotation permission means for the anvil frame 40, and connects the anvil frame 40 to the crushing device frame 20 via the support block 42, while allowing the anvil 34 to permit the shear pin 43 during operation. When an impact load exceeding the shear stress is applied, the anvil frame 40 is allowed to rotate by breaking and the anvil 34 is moved away from the crushing chamber 27 and the crushing chamber 27 is opened. The shear pin 43 is installed in a posture that extends in the front-rear direction, and can be inserted and removed from the front during replacement. In the present embodiment, one shear pin 43 is provided at a substantially middle position between the left and right crushing device frames 20, but the number and position are not particularly limited.

  Here, the crushing chamber 27 is a space that accommodates the crushing rotor 15 and crushes the material to be crushed. On the outer peripheral surface of the crushing rotor 15, the curved plate 28, the anvil 34, the curved plate 41, and the screen (sieving member) 38 in the normal rotation direction (clockwise direction in FIG. 3) of the crushing rotor 15 in order from the feed conveyor 12. The inner wall of the crushing chamber 27 around the crushing rotor 15 is formed by the curved plate 28, the anvil 34, the screen 38, and the like.

  The screen 38 is a plate-shaped sieve member bent in an arc shape and has a number of discharge holes (not shown). The lower half of the outer peripheral surface of the crushing rotor 15 (with respect to the anvil 34). It is detachably held on a screen holder 44 formed in an arc shape so as to face the crushing rotor 15 in the forward rotation direction). A plurality of the screens 38 are arranged in the rotation direction of the crushing rotor 15 (four in this embodiment), and a gap is secured between the screen 38 and the outermost diameter portion of the rotation locus of the crushing rotor 15. Further, when the shear pin 43 is not in operation (before breakage), the anvil 39 is positioned on a plane including the rotation shaft 31 (center line) of the anvil frame 40 and the rotation shaft 100 (center line) of the crushing rotor 15. Yes. Further, when the rotation tangent of the crushing rotor 15 is extended rearward from the position of the anvil 34, when the anvil frame 40 is rotated rearward and the crushing chamber 27 is opened (see FIG. 8 later), the extension of the previous rotation tangent is performed. The anvil frame 40 is retracted from the line (the extension line and the anvil frame 40 do not interfere with each other).

  The screen holder 44 that supports the screen 38 is configured to rotate in the vertical direction as the cylinder 47 expands and contracts with a shaft 45 extending in the machine body width direction as a fulcrum, and from the state shown in FIG. When lowered, the screen 38 descends to a position lower than the lower end of the crushing device frame 20, and the screen 38 can be inserted and removed from the body width direction.

  The cylinders 47 are, for example, hydraulic cylinders (or electric cylinders), and one cylinder 47 is installed on each of the left and right main body frames 10 (not shown in FIG. 3). Each cylinder 47 is located on the front side of the crushing device 13, and the bottom side is connected to a bracket 49 (see FIG. 3) fixed on the main body frame 10. Extending in the longitudinal direction of the main body frame 10. The rod tip of each cylinder 47 is connected to a slider 48 that slides along the main body frame 10, and the slider 48 is connected to the vicinity of the front end of the screen holder 44 via an arm 46. Both ends of the arm 46 are rotatably connected to the slider 48 and the screen holder 44. As can be seen from FIG. 3, the slider 48 and the arm 46 constitute a link mechanism, and the expansion and contraction operation of the cylinder 47 is converted into the vertical movement of the screen holder 44 by the slider 48 and the arm 46.

  Note that the length of the screen holder 44 and the arm 46, the front and rear positions of the cylinder 47, and the like are substantially along the tangential direction of the crushing chamber 27 when the screen holder 44 is raised (the state shown in FIG. 3). Thus, the angle is set so as to rise up to a right angle with respect to the main body frame 10, and consideration is given so that the push-up force and the posture holding force of the screen holder 44 by the link mechanism can be obtained effectively.

  Among the crushed pieces being crushed in the crushing chamber 27, those having a particle size passing through the discharge hole pass through the screen 38 and are discharged from the crushing device 13, and the crushed pieces circulating around the crushing chamber 27 without passing through the screen 38 are The screen 38, the crushing rotor 15, and the anvil 34 are made fine by the action of collision, shearing, grinding, and the like, and eventually discharged through the screen 38. Thereby, the particle size of the crushed material discharged from the crushing device 13 is adjusted according to the size of the discharge hole of the screen 38, and the crushed material discharged from the crushing device 13 is guided onto the discharge conveyor 3.

  At this time, in this embodiment, the mass of the crushing rotor 15, the radius of rotation, the number of revolutions, the mass of the bit 36, the offset amount of the center of gravity from the shaft 37, the mass of the anvil frame 40, the offset amount of the center of gravity from the rotating shaft 31. The shear fracture stress of the shear pin 43 is set so as to satisfy the following relational expression (1).

(Ir × Δωr ² ) / 2 + (Ic × Δωc ² ) / 2 = (If × Δωf ² ) / 2 + mgh + Ep (1)
Where Ir: moment of inertia of the crushing rotor 15; Δωr: deviation in rotational speed of the crushing rotor 15 before and after the shear pin 43 breaks; Ic: moment of inertia of the rotation component of the bit 36; Number (spinning component) deviation, If: moment of inertia of the anvil frame 40, Δωf: rotational speed deviation of the anvil frame 40 before and after the shear pin 43 breaks, m: mass of the anvil frame 40, g: gravitational acceleration, h: anvil frame 40 The height deviation of the center of gravity, and Ep: set value of the shear breaking stress of the shear pin 43.

  In addition, the “spinning component” of the bit 36 described in the previous paragraph is not the rotational motion of the bit 36 relative to the plate assembly 101 having the axis 37 as the rotation center, but from the operation of the bit 36 as viewed from the stationary side, for example. Refers to the extracted rotation component. For example, when the relative speed with respect to the plate assembly 101 is 0 and the bit 36 is rotated integrally with the plate assembly 101, when the viewpoint is aligned with the axis 37 while keeping the field of view horizontal from the stationary side, the bit is The rotation component 36 has the same value as the rotational speed of the plate assembly 101 (ωr = ωc).

  For example, assumed values of the rotational speeds of the respective elements before and after the shear pin 43 are broken are, for example, 135 [rad / s] and 125 [rad / s], respectively. The rotation speed of the bit 36 before and after the break is 135 [rad / s] and 0 [rad / s], respectively, and the rotation speed of the anvil frame 40 before and after the shear pin 43 is broken is 0 [rad / s] and 60 [rad / s, respectively. ], Δωr = 10 [rad / s], Δωc = 135 [rad / s], and Δωf = 60 [rad / s].

  Next, the operation of the crusher of the present embodiment having the above configuration will be described.

(1) Normal time When a material to be crushed is put into the hopper 11 by a heavy machine (such as a hydraulic excavator) equipped with an appropriate work tool such as a grapple, the material to be crushed is placed on the transport belt 17 of the feed conveyor 12. Then, it is conveyed toward the crushing device 13 by a conveying belt 17 that is driven to circulate. When the object to be crushed is conveyed to the vicinity of the pressure feeder device 14, the press roller 24 rides on the object to be crushed, and the object to be crushed is pressed against the conveying surface of the feed conveyor 12 by the weight of the pressing roller 24. In this way, the presser roller 24 introduces the material to be crushed into the crushing chamber 27 in cooperation with the feed conveyor 12 in a state where the material to be crushed is sandwiched between the pressure roller 24 and the feed conveyor 12. At that time, the object to be crushed protrudes into the crushing chamber 27 in a cantilever shape with a portion sandwiched between the pressing roller 24 and the feed conveyor 12 as a fulcrum.

  The bit 36 of the crushing rotor 15 that rotates at high speed collides with the object to be crushed protruding into the crushing chamber 27 from below, whereby the object to be crushed is roughly crushed (primary crushing). The fragments to be crushed and thus splashed into the crushing chamber 27 collide with the anvil 34 and are further crushed by the impact force (secondary crushing). Of the crushed pieces that have been secondarily crushed, those that are already small enough to pass through the screen 38 are discharged through the screen 38, and those that do not pass are circulated in the crushing chamber 27 as the crushing rotor 15 rotates. Then, it is further crushed by receiving a collision action, a shearing action, a crushing action, and the like with the inner wall surface of the crushing chamber 27 such as the anvil 34, the bit 36, and the screen 38 (third crushing). Then, the crushed pieces that have been refined to a size that passes through the discharge holes of the screen 38 by a series of crushing actions are sequentially discharged from the crushing chamber 27 through the screen 38. The crushed material discharged from the crushing chamber 27 falls on the discharge conveyor 3, is transported by the discharge conveyor 3, and is discharged outside the machine.

(2) When Overload Occurred FIGS. 5 to 8 are diagrams showing the operation of the crushing device 13 in a time series when a foreign object is caught between the bit 36 and the anvil 34. 5 to 8, the crushing rotor 15 is represented by a VV cross section in FIG. 4 in order to represent the movement of the bit 36.

  When the crushing operation is normally performed as shown in FIG. 5, each bit 36 receives the centrifugal force given by the high-speed rotation of the crushing rotor 15, and each bit 36 is in the radial direction of the crushing rotor 15. Take a posture with the striking part protruding outward. At this time, each bit 36 is basically stationary with respect to the plate assembly 101.

  When foreign matter such as a metal lump enters the crushing chamber 27 and enters between the anvil 34 and the bit 36 as shown in FIG. 6, the normal crushing material is crushed. A larger impact force acts on the anvil 34 as compared to the case.

  During the crushing operation, the impact force acting on the anvil 34 is transmitted to the shear pin 43 via the anvil frame 40, and if the excessive impact force due to foreign matter biting exceeds the allowable shear stress of the shear pin 43, the shear pin 43 breaks. Then, the restraint of the anvil frame 43 is released. FIG. 7 schematically shows the moment, that is, the moment when the anvil frame 40 starts to rotate due to the impact force acting on the anvil 34 via the foreign object.

  In addition, since the bit 36 is rotatably attached to the plate assembly 101 via the shaft 37, when an excessive impact force is generated due to the biting of foreign matter, as shown in FIG. It rotates in the direction opposite to the rotation direction of the crushing rotor 15 with respect to the body 101. At this time, assuming that the rotation component immediately after the breakage of the shear pin 43 of the bit 36 that collided with the anvil 34 via a foreign object is 0 (error is allowed), the kinetic energy of the bit 36 is calculated from the relational expression (1) described above. It can be seen that most of the energy is converted to the breaking energy of the shear pin 43 and the rotational force of the anvil 34 and the anvil frame 40 and lost. At the moment of the collision, the rotational movement of the plate assembly 101 does not stop suddenly and continues due to inertia, but for example, when another pendulum collides with a stationary pendulum in a model of a hard ball collision of the pendulum movement, 36 loses most of the above-mentioned rotation component, and as a result, a relative speed is generated between the plate assembly 101 and the bit 36, and the bit 36 is opposite to the plate assembly 101 in the direction opposite to the plate assembly 101. It will have a rotational speed (refer FIG.7 and FIG.8).

  In other words, in this embodiment, when a foreign object is caught between the bit 36 and the anvil 34 and the shear pin 43 breaks, the impact force caused by the crushing reaction force from the anvil 34 to the bit 36 is applied to the rotation of the bit 36 relative to the plate assembly 101. It can be converted into motion, which can prevent the bit 36 from being damaged. Therefore, it is possible to suppress the occurrence of downtime due to the repair of the bit 36.

  As described above, when the above-described rotation component of the bit 36 immediately after the shear pin 43 is broken is assumed to be 0 (error is allowed), another pendulum collides with a stationary pendulum in a hard ball collision model of pendulum motion. A similar movement can be realized. Therefore, the kinetic energy of the bit 36 is converted into the kinetic energy of the anvil frame 40 through the foreign matter, and the foreign matter that has become the energy transmission medium at that time has a certain degree of velocity vector immediately before biting between the anvil 34 and the bit 36. In this state, it is discharged from the opening (upper part of the screen 38) of the crushing chamber 27 opened by the rotating operation of the anvil frame 40. At this time, in this embodiment, since the anvil 34 is provided between the anvil frame 40 and the rotating shafts 31 and 100 of the crushing rotor 15, the rotation of the crushing rotor 15 at the position of the anvil 34 when the anvil frame 40 is retracted. Since the tangential direction is opened and the foreign matter travels along the rotational tangential direction, the smoothness of the foreign matter discharge is also expected (see FIG. 8).

  As described above, according to the present embodiment, the combination of the swing hammer type bit 36 and the retracting mechanism of the anvil 34 maintains the crushing ability at the time of normal crushing, and may damage the crushing device 13 at the time of contamination. Can be greatly reduced. Thereby, since it can recover rapidly even if a foreign material mixes and the crushing operation is interrupted while reliably crushing the object to be crushed, the crushing operation efficiency can be greatly improved.

  A second embodiment of the present invention will be described.

  FIG. 9 is a partial plan view showing the main part of the crusher according to the second embodiment of the present invention, and FIG. 10 is a cross-sectional view of the anvil frame 20 and the like along the line XX in FIG. FIG. 10 corresponds to FIG. 4 of the first embodiment.

  The difference between the present embodiment and the first embodiment is the configuration of the rotation permission means of the anvil frame 40, and the shear pin 43 is applied as the rotation permission means of the anvil frame 40 in the first embodiment. In the embodiment, when the stopper member is elastically engaged with the anvil frame 40 and the excessive impact force acts on the anvil 34 and the stopper member is disengaged, the restriction of the anvil frame 40 is released. is there. Specifically, the rotation permission means 414 of the present embodiment includes a roller 495 as a stopper member that can advance and retreat in a direction intersecting the rotational tangent of the anvil frame 40, and a biasing force that biases the roller 495 with a set biasing force. The anvil frame 40 is restrained by a roller 495 and the posture of the anvil frame 40 is held. In the present embodiment, one rotation permission means 414 is provided at a substantially intermediate position between the left and right crushing device frames 20, but the number and position are not particularly limited. The detailed configuration of the rotation permission means 414 will be described later again.

  The anvil frame 40 includes an engagement portion 446 (described later) at a position in front of the rotation shaft 31 when the anvil 34 is in the normal posture in the crushing chamber 27. The anvil frame 40 is formed such that the distance from the pivot shaft 31 that is the fulcrum to the anvil 34 that is the power point and the length (distance) to the engaging portion 446 that is the action point are approximately the same. A load having the same magnitude as the load applied to the anvil 34 acts on the engaging portion 446. In addition, the magnitude relationship between the length from the rotating shaft 31 to the anvil 34 of the anvil frame 40 and the length from the rotating shaft 31 to the engaging portion 446 is not particularly limited in obtaining the essential effect of the present invention.

  The above-described rotation permission means 414 includes upper and lower beams 448 and 494 passed between the left and right crushing device frames 20 in front of the anvil frame 40, a bracket 496 provided at the rear of the lower beam 494, and an upper stage. A rod 91 penetrating the beam 448 in the front-rear direction, a lever 490 having both ends connected to the rod 91 and the bracket 496 via 490a and 490b, a roller 495 rotatably provided to the lever 490 via a pin 490c, A biasing means (an elastic member such as rubber or a spring) 93 interposed between the lever 490 and the beam 448 through the rod 91 is provided therein, and a shim 92 inserted between the beam 448 and the biasing means 93. .

  The roller 495 is disposed at a position near the pin 490b between the upper and lower pins 490a, 490b, and the outer peripheral surface protrudes rearward from the lever 490. When the rod 91 slides back and forth with respect to the beam 448, the lever 490 rotates with the lower pin 490b as a fulcrum, and the roller 495 also moves in the front-rear direction. In this embodiment, the roller 495 is configured to move in the front-rear direction. However, the direction of movement of the roller 495 is not particularly limited as long as the roller 495 intersects the rotational tangent of the anvil frame 40 at the contact position with the roller 495. In this embodiment, the roller 495 is urged toward the anvil frame 40 by the urging force of the urging means 93, and the engaging portion 446 of the anvil frame 40 is restrained on the lower half side. The anvil frame 40 is restrained by the roller 495 by the urging force of the urging means 93 and is held in a posture in which the anvil 34 faces the crushing chamber 27. When an excessive impact force acts on the anvil 34 due to foreign matter biting or the like, a strong rotational force is applied to the anvil frame 40, and the engaging portion 446 of the anvil frame 40 resists the elastic force of the urging means 93. When the roller 495 is pushed forward and the engaging portion 446 gets over the roller 495, the restraint of the anvil frame 40 is released as in the case where the shear pin 43 is broken in the first embodiment.

  Note that the engaging portion 446 of the anvil frame 40 includes a latch 447 that contacts the roller 495 of the rotation allowing means 414, a case 452 that holds the latch 447, and a base portion 449 that fixes the case 452 to the anvil frame 40. And. The contact surface of the latch 447 with the roller 495 is formed as a curved surface that protrudes toward the roller 495 when viewed from the axial direction of the roller 495, and the outer surface of the roller 495 is moved forward and backward with respect to the case 452. The contact position with the latch 447 moves up. If the latch 447 further protrudes from the state of FIG. 10, the contact position between the latch 447 and the roller 495 moves downward. In this case, the radius of rotation of the latch 447 around the rotation shaft 31 of the anvil frame 40 is increased, and in order to get over the roller 495, the roller 495 must be moved further forward, and the anvil frame 40 is moved accordingly. The impact force required for rotation is increased. If the latch 447 is retracted toward the case 452, the rotating operation of the anvil frame 40 is allowed with a small impact force.

  A bolt 450 is screwed into the latch 447 in the sliding direction of the latch 447 from the side opposite to the roller 495. The bolt 450 passes through a through hole provided in the end surface of the case 452, and the head portion 450 a is outside the end surface of the case 452. The bolt 450 is also passed through a spring 451 interposed between the end surface of the case 452 and the latch 447. When the anvil frame 40 is opened, the latch 447 is not subjected to the force of pushing and compressing the spring 451 from the roller 495. However, when the anvil frame 40 is opened, if the anvil frame 40 is rotated and pushed clockwise in FIG. Since the latch 447 contacts the roller 495 from the tip, the spring 451 is temporarily contracted, the latch 447 is retracted, and the normal posture is restored. That is, it is possible to return to the original state without disassembling the engaging portion 446 or the rotation permitting means 414 or exchanging any parts.

  Other configurations are the same as those of the first embodiment.

  Also in the present embodiment, the combination of the swing hammer type bit 36 and the retracting mechanism of the anvil 34 maintains the crushing capability at the time of normal crushing as in the first embodiment, while the crushing device 13 at the time of contamination is mixed. The possibility of damage can be greatly reduced. Thereby, since it can recover rapidly even if a foreign material mixes and the crushing operation is interrupted while reliably crushing the object to be crushed, the crushing operation efficiency can be greatly improved.

  In each of the above embodiments, the case where the present invention is applied to a crusher capable of traveling on its own has been described as an example. However, the present invention is not limited to this, and a mobile crusher that can travel by towing, for example, a crane. The present invention can also be applied to a portable crusher that can be lifted and transported by, for example, a stationary crusher arranged as a fixed machine in a plant or the like. Moreover, although the case where this invention was applied to the crushing machine which supplies a to-be-crushed object from a horizontal direction with respect to the crushing rotor rotated with a horizontal axis | shaft was mentioned as an example, crushing by providing a hopper on a crushing apparatus The present invention can also be applied to a type of crusher that supplies an object to be crushed from above to a rotor. In these cases, similar effects can be obtained.

15 crushing rotor 20 crushing device frame 27 crushing chamber 34 anvil 36 bit 40 anvil frame 43 sheer pin (rotation permitting means)
93 Biasing means 101 Plate assembly 414 Rotation permitting means 495 Roller (stopper member)
Ep Setting value g of rotation allowance means g Gravity acceleration h Height deviation of center of gravity of anvil frame mc Mass of anvil frame Inc moment of inertia of bit rotation If inertial moment of anvil frame Ir Inertia moment of crushing rotor Δωc Rotational component deviation Δωf of the bit before and after the operation Anvil frame rotational speed deviation Δωr before and after the operation of the rotation permission means Rotational speed deviation of the crushing rotor before and after the operation of the rotation permission means

Claims (5)

A crusher frame;
A plate assembly provided rotatably with respect to the crushing device frame, and a crushing rotor having a bit provided on an outer peripheral portion of the plate assembly,
A crushing chamber containing the crushing rotor;
An anvil provided in the crushing chamber so as to face the outermost diameter portion of the rotation trajectory of the crushing rotor via a gap;
An anvil frame that supports the anvil and is rotatably supported with respect to the crushing device frame;
A rotation allowing means for allowing the anvil frame to rotate when an impact force exceeding a set value is applied to the anvil, and opening the crushing chamber by moving the anvil away from the crushing chamber;
The crusher, wherein the bit is attached to an outer peripheral portion of the plate assembly so as to be rotatable in a direction along a plane orthogonal to the rotation axis of the crushing rotor.   2. The crusher according to claim 1, wherein the rotation permission means is a shear pin that connects the anvil frame to the crusher frame.   2. The crusher according to claim 1, wherein the rotation permission means includes a stopper member capable of moving back and forth in a direction intersecting a rotation tangent of the anvil frame, and a biasing means for biasing the stopper member with a set biasing force. And a crusher characterized in that the anvil frame is restrained by the stopper member and holds the posture of the anvil frame. In the crusher in any one of Claims 1-3,
Ir: moment of inertia of the crushing rotor,
Δωr: rotational speed deviation of the crushing rotor before and after operation of the rotation permission means,
Ic: moment of inertia of the rotation component of the bit,
Δωc: rotation component deviation of the bit before and after operation of the rotation permission unit,
If: moment of inertia of the anvil frame,
Δωf: rotational speed deviation of the anvil frame before and after operation of the rotation permission means,
m: mass of the anvil frame,
g: acceleration of gravity,
h: height deviation of the center of gravity of the anvil frame,
Ep: When the set value of the rotation permission means is used,
(Ir × Δωr ² ) / 2 + (Ic × Δωc ² ) / 2 = (If × Δωf ² ) / 2 + mgh + Ep
A crusher characterized in that the relational expression represented by In the crusher in any one of Claims 1-4,
The anvil is located on a surface including the rotation axis of the anvil frame and the rotation axis of the crushing rotor when the rotation permission means is inoperative; and
A crusher configured to prevent the anvil frame from interfering with an extended line extending from a position of the anvil to a rotation tangent of the crushing rotor after the rotation permission means is actuated.

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