JP2005238038A - Wood crushing machine and wood treating method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wood crushing machine and a wood treating method capable of smoothly performing the continuous supply of material to be crushed for the crusher without stopping a feed conveyor even when a wooden chip is bitten into the feed conveyor. <P>SOLUTION: The wood crushing machine is provided with a crusher which crushes the introduced wood to be crushed, the feed conveyor which comprises a driving wheel and driven wheel disposed respectively on both end parts of the conveyance direction, a conveyance body wound around the driving wheel and driven wheel and an oil hydraulic motor 49 for feed conveyor rotatively driving the driving wheel and conveys the wood to be crushed to the crusher, and a torque changing means which is capable of changing an output torque of the oil hydraulic motor 49 for feed conveyor of the feed conveyor and comprises a regulator 170 and a control valve 171. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a wood crusher for crushing pruned branch materials / thinned wood, branch wood, waste wood, etc., for example, a wood crusher and a wood treatment method for crushing an object to be crushed by rotating a crushing rotor. is there.

  For example, pruned branches / thinned wood generated when pruning timber harvested in forests, branch timber generated in creation / green space maintenance management, or waste wood used in wooden houses is usually the final In general, it is treated as industrial waste. The wood crusher is used for the purpose of reducing the volume of crushed wood as waste in such a waste treatment process, or fermenting crushed timber (wood chips) after pulverization and reusing it as organic fertilizer. The crushed wood is crushed into a predetermined size.

  As this kind of wood crusher, generally, the wood to be crushed put into a bottomless hopper is introduced into a crushing device by a feed conveyor (guide conveyor) having an endless chain belt provided in the hopper, Some of the introduced wood to be crushed are crushed by a crushing rotor or the like provided inside the crushing apparatus (see, for example, Patent Document 1).

JP 2002-1159 A

  In the above-described prior art, the crushed wood to be crushed is conveyed by an endless chain belt and introduced into the crushing device. The chain belt moved on the conveying surface is moved downward by a drive wheel located in front of the crushing device. Go around and return to the driven wheel. At this time, some wood pieces (chips) conveyed on the conveying surface of the chain belt may not be introduced into the crushing device, but may wrap around the chain belt and return to the return surface side through the drive wheels. is there. In this case, if the piece of wood is detached from the chain belt on the way back to the driven wheel, the piece of wood spills down to the ground because the hopper has a bottomless shape. There is a risk of accumulation and scattering.

  In view of this point, the present inventors have invented a bottomed hopper configuration including a side wall provided on both sides of the feed conveyor in the width direction and a bottom wall provided below the feed conveyor. If this bottomed hopper is used, even if some pieces of wood caught on the chain belt during the crushing work go around to the return surface, they will be received by the bottom wall of the hopper. Etc. can be prevented from being scattered below the feed conveyor.

  However, if the bottom wall body is provided in the hopper, if the wood pieces or the like that have turned around to the return surface side accumulate on the bottom wall body and become compacted between the feed conveyor and the bottom wall body of the hopper, the feed conveyor Smooth operation may be hindered. In addition, for example, part of the crushed wood to be transported may be bitten between the chain belt and the drive wheel constituting the transport surface of the feed conveyor, or between the chain belt and the driven wheel, In severe cases, the feed conveyor could stop.

  The present invention has been made in view of the above-described problems, and its purpose is to continuously supply a material to be crushed smoothly to a crushing device without stopping the feed conveyor even if a piece of wood bites into the feed conveyor. An object of the present invention is to provide a wood crusher and a wood processing method that can be used.

  In order to achieve the above object, the first invention includes a crushing device for crushing introduced wood to be crushed, driving wheels and driven wheels respectively provided at both ends in the conveying direction, and these driving wheels and driven wheels. A feed conveyor having a wound conveyor and a drive device that rotationally drives the drive wheel, and a torque change capable of changing the output torque of the feed conveyor and the feed conveyor drive device for conveying the wood to be crushed to the crushing device Means.

  According to a second aspect, in the first aspect, the torque changing unit includes a regulator device that changes the tilt of the driving device and a control valve that controls a pilot pressure that drives the regulator device. Features.

  According to a third invention, in the first or second invention, the torque changing means is a variable relief valve that changes a relief pressure of a supply pipe that supplies pressure oil to the driving device. .

  According to a fourth invention, in any one of the first to third inventions, a control device is provided that outputs a torque change signal to the torque changing means and controls the output torque of the drive device when the drive device is overloaded. It is characterized by.

  According to a fifth invention, in the fourth invention, when the reverse rotation operation of the drive device is repeatedly performed, the control device correspondingly increases the torque change signal to the torque changing means stepwise. The output torque of the drive device is controlled to increase stepwise.

  In a sixth aspect of the invention, when the wood to be crushed is introduced into the crushing device by the feed conveyor and crushed, when the wood to be crushed bites into the feed conveyor, the output torque of the drive device that drives the feed conveyor is temporarily increased. The biting of the feed conveyor is released by increasing the speed.

  According to the present invention, even if a piece of wood is compacted on the bottom wall body of the hopper, the accumulated piece of wood is forced to the rear side by temporarily increasing the output torque of the drive device that drives the feed conveyor. For example, it can be returned to the conveyance surface of the feed conveyor. Further, even if a piece of wood is caught between the driving wheel or driven wheel of the feed conveyor and the transport body, the bited piece of wood can be forced to pass through the driving wheel or the driven wheel. Thereby, a to-be-crushed object can be continuously supplied smoothly with respect to a crushing apparatus, without stopping a feed conveyor.

Hereinafter, an embodiment of a wood crusher of the present invention will be described with reference to the drawings.
FIG. 1 is a side view showing the overall structure of an embodiment of a wood crusher of the present invention, FIG. 2 is a plan view of an embodiment of the wood crusher of the present invention shown in FIG. 1, and FIG. It is a side view showing the detailed structure inside the side cover near the crushing device 12. In the following, the directions corresponding to the left and right in FIG. 1 are the rear and front of the wood crusher, or one and the other.
1 to 3, reference numeral 1 denotes a traveling body that enables self-running, 2 denotes a crushing function constituent unit that crushes the wood to be shredded provided on the traveling body 1, and 3 denotes the crushing functional constituent unit 2. The discharge conveyor that transports the crushed material crushed in step 1 and discharges it outside the machine. 4 is a power unit (power unit) equipped with the power source (engine) of each mounted device. The body 1, the crushing function component 2, the discharge conveyor 3, the power unit 4, and the like are roughly configured.

  The traveling body 1 includes a track frame 5, drive wheels 6 and driven wheels 7 provided at both front and rear ends of the track frame 5, and a drive device (travel hydraulic motor) in which an output shaft is connected to the shaft of the drive wheel 6. 8 and a crawler belt (endless track crawler) 9 wound around the drive wheel 6 and the driven wheel 7. A main body frame 36 is provided on the track frame 5. The main body frame 36 supports the crushing function component 2, the discharge conveyor 3, the power unit 4, and the like.

  The crushing function component 2 is introduced by a hopper 10 that receives the crushed wood to be input, a feed conveyor 11 as a means for conveying the crushed wood accommodated in the hopper 10, and the feed conveyor 11. A crushing device 12 for crushing the wood to be crushed (see FIG. 3 and the like later), and a press conveyor device 13 for pressing the wood to be crushed introduced into the crushing device 12 in front of the crushing device 12 against the feed conveyor 11 (rear figure 3).

4 is a side view showing a detailed structure in the vicinity of the rear end of the hopper 10, FIG. 5 is a cross-sectional view taken along line VV in FIG. 4, and FIG. 6 is a front view of the hopper 10 viewed from the rear. In the figure, the same reference numerals are given to the same parts as those in the previous drawings, and the description will be omitted. However, in FIG. 4, the state which removed the outer wall body 15 mentioned later is shown in figure.
4 to 6, the hopper 10 is formed in a bottomed shape, is provided substantially horizontally on the rear side of the crushing rotor 61 (described later) on the main body frame 36, and is provided on the rear side of the feed conveyor 11. A plurality of members are provided on the rear wall body 14, the outer wall bodies 15 on the left and right sides in the width direction, and on both sides in the width direction of the feed conveyor 11 inside the outer wall body 15, so that a gap is secured between the outer wall bodies 15. An L-shaped side wall body 16, and a widening portion (tilting portion) 17 that is provided in an upwardly widened shape so as to hang over the outer wall body 15 and the upper portion of the side wall body 16, A bottom wall body 18 provided on the entire bottom surface so as to slightly interpose a gap below the feed conveyor 11 and a front wall body 19 at the front side end portion are provided. The upper end of the rear wall 14 is set to the same level as or slightly higher than the transport surface of the feed conveyor 11, and the upper end of the front wall 19 is set to a level slightly lower than the transport surface of the feed conveyor 11. .

FIG. 7 is a cross-sectional view taken along the arrow VII-VII in FIG. 6 showing the detailed structure of the rear end portion of the feed conveyor 11. In this figure, the same parts as those in the previous drawings are given the same reference numerals for explanation. Omitted.
In the present embodiment, the bottom wall 18 of the hopper 10 is divided into a fixed portion 20 and an opening / closing portion 21 located at the rear end. The fixing part 20 is fixed to the side wall body 16, whereas the opening / closing part 21 is fixed to the rear wall body 14. A pin 23 is provided on the upper end portion of the rear wall body 14 via a bracket 22, and the rear wall body 14 is attached to the side wall body 16 so as to be rotatable with the pin 23 as a fulcrum. As a result, the opening / closing part 21 fixed to the rear wall body 14 rotates together with the rear wall body 14 so that the rear end part of the bottom wall body 18 can be opened and closed. Note that a guide member 35 formed in an arc shape is provided on the opening / closing portion 21 so as to follow the trajectory of the rear end portion of the feed conveyor 11 with a slight gap, and the wood to be crushed is fed into the feed conveyor 11. Preventing entry into the space behind.

  Reference numerals 24 and 25 denote lock mechanisms for holding the opening / closing portion 21 in a closed state. The lock mechanism 24 is provided on the rear end surface of the beam 26 that is passed to the rear end portion of the bottom of the L-shaped side wall body 16. They are respectively provided on the upper surface of the bottom of the side wall body 16 at a position slightly ahead of the lock mechanism 24.

8 (a) and 8 (b) are detailed views of the locking mechanism 24 as seen from the same direction as FIG. 7. In these drawings, the same parts as those in the previous drawings are denoted by the same reference numerals. Description is omitted. Although detailed description is omitted, the configuration of the lock mechanism 25 is the same as that of the lock mechanism 24.
8A and 8B, the lock mechanism 24 includes a support plate 28 fixed to the beam 26 by a plurality of bolts 27, and two brackets provided on the support plate 28 at a predetermined interval. 29, a pin 30 inserted through the bracket 29, a handle 31 provided substantially perpendicular to the outer periphery of the pin 30, a locking member 32 for locking the handle 31, and a lower end portion of the rear wall body 14 And a bracket 33 fixed to.

  With this configuration, the pin 30 is inserted into the bracket 33 on the rear wall body 14 side and the handle 31 is locked between the bracket 29 and the locking member 32 as shown in FIG. The rear wall body 14 is fixed to the side wall body 16 via the pin 30 and the opening / closing part 21 of the bottom wall body 18 is held in a closed state. On the other hand, the pin 30 is rotated to a position where the handle 31 is substantially horizontal, the pin 30 is slid through the notch portion of the locking member 32, and the pin 30 is removed from the bracket 33 as shown in FIG. 8B. As a result, the restriction between the rear wall body 14 and the side wall body 16 is released. In this example, since another lock mechanism 25 is provided, similarly, the lock mechanism 25 side is completely unconstrained by removing the pin from the bracket provided on the open / close portion 21 side. The opening / closing part 21 can be opened and closed. The state in which the opening / closing part 21 is opened is shown in FIG. 9 corresponding to FIG. By setting it as this state, when the wood piece stays in the hopper 10, it can be easily discharged at the time of maintenance or the like.

  Reference numeral 34 denotes a snap ring that prevents the pin 30 from falling off. The snap ring 34 is provided on the outer periphery of the pin 30 so as to be positioned between the brackets 29 and 29. In this example, when the lock of FIG. 8A is locked and the lock is released of FIG. The length is limited.

  The feed conveyor 11 includes a sprocket-like drive wheel 40 (see FIG. 3) provided on the crushing rotor 61 (described later) side and a slave provided on the opposite side (the wood crusher front side and the rear wall body 14 side). A plurality of rows (4 rows in this example, see FIG. 2) arranged in the width direction are wound between the driving wheels 41 (see FIG. 7 and the like) and the driving wheels 40 and the driven wheels 41 provided at both ends in the conveying direction. Transported bodies (conveying belts, chain belts) 42 are provided. The transport body 42 is not shown in FIG. 3 and FIG. 11 and FIG.

  The driven wheel 41 is supported by a bearing 43 (see FIG. 4) provided on the outer wall surface of the rear portion of the side wall body 16 of the hopper 10, and the driving wheel 40 is positioned substantially on the same plane on the front side of the side wall body 16. It is supported by a bearing 46 (see FIG. 10 described later) provided on the outer wall surface of the side cover 45 (described later) of the crushing device 12 provided. As a result, the feed conveyor 11 extends from the lower part of the hopper 10, that is, from the inside of the side wall body 16 of the hopper 10 to the vicinity of the crushing rotor 61 (described later), and extends substantially horizontally to cover the side surfaces of the hopper 10 and the crushing device 12. 45 (described later).

FIG. 10 is a side view of the vicinity of the crushing device 12, and FIG. 11 is a cross-sectional view showing the internal structure in detail. In these drawings, the same parts as those in the previous drawings are denoted by the same reference numerals and description thereof is omitted. .
10 and 11, 45 is a side cover of the crushing device 12 provided in front of the hopper 10, and 46 is a bearing of the feed conveyor 11 provided on the outer wall surface of the side cover 45. The rotation shaft of the drive wheel 40 of the feed conveyor 11 is connected to the output shaft of a drive device (feed conveyor hydraulic motor, not shown) provided outside the bearing 46 in the width direction via a coupling or the like. The feed conveyor 11 circulates and drives the transport body 42 between the drive wheels 40 and the driven wheels 41 by rotationally driving the drive device 49 (not shown here, see FIG. 19 used in the following description). It has become. As shown in FIG. 11 (see also FIG. 3), the bottom wall body 18 of the hopper 10 described above extends to the lower side of the drive wheel 40, and its tip end faces the side cover 45. Yes.

  47 is a guide member that is bent so as to be close to the rotation trajectory of the drive wheel 40, and is connected to the bottom wall body 18 and the front wall body 19 of the hopper 10, and 48 is slightly lower than the rotation trajectory of the drive wheel 40 and The scraper is disposed on the upper portion of the front wall body 19 so that the end facing the drive wheel 40 is as close as possible to the rotation locus of the drive wheel 40. The end portions in the width direction of the guide member 47 and the scraper 48 are fixed to the side cover 45 of the crushing device 12.

  The aforementioned press conveyor device 13 is provided so as to face the transport surface (upper surface) of the feed conveyor 11 that transports the wood to be shredded so as to be close to the rear side of the crushing rotor 61 (described later). The pressing conveyor device 13 has a rotating shaft 51 (see FIG. 3) supported by a crusher side cover 45 by a bearing 50 (see FIG. 11) so that it can rotate in a vertical plane (in the vertical direction). A support member 52 supported so as to be swingable and a presser roller 53 provided so as to be rotatable with respect to the support member 52 are provided.

  The support member 52 includes an arm portion 54 that includes a rotation shaft 51 and a bracket portion 55 that is provided on the distal end side of the arm portion 54 and supports the pressing roller 53. The lower end surface of the arm portion 54 is formed to be curved in an arc shape, and a curved plate 68 constituting a part of a crushing chamber 60 described later is attached to the curved portion. On the other hand, the attachment portion of the pressing roller 53 in the bracket portion 55 is formed in an arc shape having a smaller diameter than the pressing roller 53, and the outer peripheral surface of the pressing roller 53 protrudes from the bracket portion 55. The dimension of the pressing roller 53 in the width direction (the direction orthogonal to the paper surface in FIG. 3) is set to be equal to or larger than the width of the conveying surface of the feed conveyor 11.

  3 and 11, 56 and 57 are stoppers for restricting the rotation operation of the presser conveyor device 13. When the presser roller 53 is lowered to the proximity position of the drive wheels 40 of the feed conveyor 11, It arrange | positions inside the crusher side cover 45 so that the bracket part 55 and the curved board 68 may each contact | abut. Although not specifically shown, the presser roller 53 has a drive device 58 (not shown here, see FIG. 19 described later) built in the body thereof, and the feed conveyor 11 is driven by this drive device (not shown). Rotate at a peripheral speed substantially the same as the conveying speed of the wood to be crushed in the direction of rolling to the conveying surface, and the wood to be crushed on the feed conveyor 11 that has been pressed is introduced into the crushing device 12 in cooperation with the feeding conveyor 11. It is like that.

  The crushing device 12 described above is mounted on a substantially central portion in the longitudinal direction of the main body frame 36, and as shown in FIGS. 3 and 11, a crushing rotor 61 that rotates at high speed in the crushing chamber 60, and the crushing rotor 61 The first anvil 62 and the second anvil 63 are arranged so as to face each other in the rotation direction (forward rotation direction, clockwise direction in FIG. 3). Although details will be described later, the first and second anvils 62 and 63 are configured to be rotatable so as to be retracted in a direction following the normal rotation direction of the crushing rotor 61 when, for example, excessive impact is applied. (See FIG. 11 and the like).

  The crushing rotor 61 is rotatably supported by a bearing (not shown) provided on, for example, a side cover 45 of the crushing device 12 (or a support member (not shown) provided separately on the main body frame 36). The part is provided with a plurality of support members 64 and crushing bits (impact plates or crushing blades) 65 attached to the support members 64, respectively. The crushing bit 65 is disposed such that the blade surface thereof precedes the support member 64 when the crushing rotor 61 rotates in the forward rotation direction. Further, each crushing bit 65 is fixed to the support member 64 with a bolt 66 or the like, and can be easily replaced even when worn. In FIG. 10, reference numeral 67 denotes a driving device (hydraulic motor for crushing rotor) that rotationally drives the crushing rotor 61, and this driving device 67 is not particularly shown but is bolted to the side cover 45 of the crushing device 12. The output shaft is connected to the rotation shaft of the crushing rotor 61 via a drive transmission mechanism using a belt or the like, for example.

  The crushing chamber 60 described above is provided with respect to the crushing rotor 61, respectively, on the curved plate 68 provided on the upper side, and on the front side and the lower side, respectively, and opened with a diameter that sets the particle size of the crushed wood (wood chips) The first screen (first sieving member) 69 and the second screen (second sieving member) 70 having a large number of holes are substantially defined, and the rear side thereof is released as a crushed wood introducing portion. The curved plate 68 is attached to the curved portion of the arm portion 54 of the presser conveyor device 13 as described above, and is configured to move with the up and down swinging motion of the presser conveyor device 13. Similar to the curved plate 68, the first and second screens 69, 70 are arcuate so as to substantially follow the rotation trajectory of the crushing rotor 61 with a predetermined gap between the first and second screens 69, 70, respectively, with the crushing bit 65. Each is formed and movable (details will be described later).

FIGS. 12 and 13 are diagrams illustrating the details of the movable mechanism by extracting the configuration in the vicinity of the first anvil 62 and the first screen 69, and FIG. 14 is a sectional view taken along arrow XIV-XIV in FIG. In the figure, the same reference numerals are given to the same parts as those in the previous drawings, and the description will be omitted.
12 to 14, reference numeral 71 denotes an arm to which the first anvil 62 is attached. The arm 71 is provided in a pair in the width direction (left and right direction in FIG. 14), and includes two rotating shafts 72 and 73 and a beam. 74. For example, one rotation shaft 72 is supported by a bearing 75 provided on the outer wall surface of the crusher side cover 45 (see FIG. 10), so that the rotation shaft 72 can be rotated as a fulcrum. It has become a structure. The directions of the rotation shafts 72 and 73 are substantially parallel to the rotation axis of the crushing rotor 61, respectively.

  The arm 71 is connected to a support member 76 whose front end is fixed to the crusher side cover 45 via a shear pin 77, so that the first anvil 62 is in a crushing operation (for example, in the state of FIG. 3). The curved plate 68 projects in the circumferential direction (the circumferential direction of the crushing rotor 61) on one side (the lower side in FIG. 12) and on the inner side of the curved plate 68 in the radial direction (the radial direction of the crushing rotor 61). It is fixed and held in such a posture. Therefore, when an impact load exceeding the allowable limit of the shear pin 77 is applied to the first anvil 62, the shear pin 77 is broken, the restraint of the arm 71 is released, and the arm 71 is retracted from the crushing chamber 60. And damage to each part is prevented.

  At this time, the rotation operation of the arm 71 is detected by, for example, a sensor that detects the rotation of the rotation shaft 72, and when the rotation of the arm 71 is detected by this sensor, the controller for driving the crushing rotor 61 is not illustrated. A command signal for stopping 67 is output.

  Reference numeral 78 denotes a stopper fixed to, for example, the crusher side cover 45 (or a support member (not shown) separately provided on the main body frame 36). The stopper 78 prevents interference between the arm 71 and other components. In order to prevent this, the rotation range of the arm 71 in the retracting direction of the first anvil 62 is limited.

  Reference numeral 80 denotes a frame-type screen support member (banana plate) that presses and holds the first screen 69 against the arm 71 from the outer peripheral side, and this screen support member 80 is arranged on one side (in the circumferential direction of the crushing rotor 61) ( The lower end in FIG. 12 is connected to the arm 71 via the previous rotation shaft 73. Further, the other end portion in the circumferential direction of the screen support member 80 is connected to the beam 74 through the hydraulic cylinder 81. Both ends of the hydraulic cylinder 81 are rotatably connected to the screen support member 80 and the beam 74 via pins, respectively, and the screen support member 80 rotates relative to the arm 71 as the hydraulic cylinder 81 expands and contracts. Move. That is, by contracting the hydraulic cylinder 81, the screen support member 80 is separated from the first screen 69, and the first screen 69 can be easily replaced. 10 and 11, reference numeral 82 denotes an opening for drawing out and inserting the first screen 69 provided on the crusher side cover 45 in consideration of the replacement work of the first screen 69. For example, a bolt detachable cover or the like is attached to the opening 82.

  In FIG. 14, reference numeral 85 denotes a lock mechanism for the screen support member 80. The lock mechanism 85 has a bracket 86 in a fixed relationship with the arm 71, and a bottom side end portion fixed to the bracket 86 in the width direction (left and right in FIG. 14). The lock cylinder 87 provided in the direction), taper blocks 88 and 89 having taper portions fixed to the rod side end of the lock cylinder 87 and the screen support member 80 and engaged with each other; And a guide member 90 that guides the sliding operation of the taper block 88.

  When the first screen 69 is sandwiched between the screen support member 80 and the arm 71, the taper block 88 in a fixed relationship with the arm 71 has a screen support member 80 from the outside in the radial direction (the radial direction of the crushing rotor 61). The taper block 89 is engaged with the taper block 89. That is, when the first screen 69 is held, the lock cylinder 87 is extended and the taper blocks 88 and 89 are engaged, so that the rotation of the screen support member 80 is restricted, and the first screen 69 is It is firmly fixed and held at a position (position shown in FIG. 3) where the crushing chamber 60 holding the crushing work is fixed. As described above, when the first screen 69 is replaced by rotating the screen support member 80 by retracting the hydraulic cylinder 81, the lock cylinder 87 is retracted and the engagement of the taper blocks 88 and 89 is released. The unlocked state is shown in FIG. 15 in correspondence with FIG. In the present embodiment, the lock mechanisms 85 are provided on both sides of the first screen 69 in the width direction (left and right direction in FIG. 14). However, if only one side is sufficient, either one may be omitted.

  Returning to FIGS. 3 and 10 to 11, reference numeral 91 denotes a frame-type arm to which the second anvil 63 is attached. The arm 91 is, for example, the outer wall surface (or the main body frame 36) of the crusher side cover 45 (see FIG. 10). A rotation shaft (not shown) is supported by a bearing 92 provided on a support member (not shown) provided separately above, and is configured to be rotatable about the rotation shaft. The direction of the rotation axis is substantially parallel to the rotation axis of the crushing rotor 61.

  The arm 91 is connected to a support member 93 whose front end is fixed to the crusher side cover 45 via a shear pin 94, so that the second anvil 63 is in a crushing operation (for example, in the state of FIG. 3). The first screen 69 projects in the circumferential direction (the circumferential direction of the crushing rotor 61) on one side (the lower side in FIG. 3) and inward in the radial direction (the radial direction of the crushing rotor) from the inner wall surface of the first screen 69. Fixed and held in posture. Therefore, when an impact load exceeding the allowable limit of the shear pin 94 is applied to the second anvil 63, the shear pin 94 is broken, the restraint of the arm 91 is released, and the arm 91 is retracted from the crushing chamber 60. And damage to each part is prevented.

  At this time, the rotation operation of the arm 91 is detected by, for example, a sensor that detects the rotation of the rotation shaft, and when the rotation of the arm 91 is detected by this sensor, the controller for driving the crushing rotor 61 is not illustrated. A command signal for stopping 67 is output.

  A stopper 95 is fixed to, for example, the crusher side cover 45 (or a support member (not shown) provided separately on the main body frame 36). The stopper 95 interferes with the arm 91 and other components. In order to prevent this, the rotation range of the arm 91 in the retracting direction of the second anvil 63 is limited.

FIG. 16A to FIG. 16C are diagrams showing the details of the movable mechanism extracted from the configuration around the second screen 70 described above. In this figure, the same parts as those in the previous drawings are the same. Reference numerals are assigned and description is omitted.
In FIG. 16, reference numeral 97 denotes a press plate for the second screen 70, and the press plate 97 is formed so that the outer peripheral portion thereof substantially coincides with the curvature of the inner wall surface of the second screen 70. 16A), for example, the inner wall surface of the second screen 70 is in contact with the inner wall surface of the crusher side cover 45 (or a support member (not shown) provided separately on the main body frame 36). It is fixed with bolts etc. so as to contact. A frame-type screen support member (banana plate) 98 holds the second screen 70 by pressing it against the presser plate 97 from the outer peripheral side. The screen support member 98 has a rotating shaft 99 provided at one end (left side in FIG. 16) in the circumferential direction (circumferential direction of the crushing rotor 61) provided separately on the crusher side cover 45 (or on the main body frame 36). It is supported by a bearing 100 fixed to a support member (not shown) and is configured to rotate in the vertical direction.

  The other end in the circumferential direction of the screen support member 98 is connected to a support member 102 fixed to the outer wall surface of the crusher side cover 45 with bolts or the like via a hydraulic cylinder 101. Both ends of the hydraulic cylinder 101 are rotatably connected to the screen support member 98 and the support member 102 via pins, respectively, and the screen support member 98 moves the rotation shaft 99 along with the expansion / contraction operation of the hydraulic cylinder 101. Rotates to a fulcrum. Thus, by extending the hydraulic cylinder 98, the screen support member 98 is separated from the second screen 70, and the second screen 70 can be easily replaced. 10 and 11, reference numeral 103 denotes a notch for drawing out and inserting the second screen 70 provided on the crusher side cover 45 in consideration of the replacement work of the second screen 70. For example, a bolt detachable cover or the like is attached to the notch 103.

  Reference numeral 105 denotes a lock mechanism for the screen support member 98. The lock mechanism 105 includes a bracket 106 fixed to the outer wall surface of the crusher side cover 45, and a bottom side end portion fixed to the bracket 106 in the front-rear direction (see FIG. 16 and the taper blocks 108 and 109 having taper portions fixed to the rod side end of the lock cylinder 107 and the screen support member 98 and engaged with each other, and a crusher side cover And a guide member 110 that is fixed to the outer wall surface of 45 by a bolt or the like and guides the sliding operation of the taper block 108 accompanying the expansion and contraction operation of the lock cylinder 107.

  When the second screen 70 is sandwiched between the screen support member 98 and the pressing plate 97, the taper block 108 is provided on the screen support member 98 from the outside in the radial direction (the radial direction of the crushing rotor 61). Engage with. As a result, when the second screen 70 is held, the lock cylinder 107 is extended and the taper blocks 108 and 109 are engaged, so that the rotational movement of the screen support member 98 is restricted, and the second screen 70 is It is firmly fixed and held at a position (position shown in FIG. 16 (a)) where the crushing chamber 60 having crushing work is fixed. Therefore, when replacing the first screen 69 by rotating the screen support member 98 by extending the hydraulic cylinder 101 as shown in FIG. 16C, first, as shown in FIG. The operation is performed after the taper blocks 108 and 109 are disengaged. The state around the crushing device 12 at the time of unlocking is shown in FIG. The lock mechanism 105 is preferably provided on both sides of the second screen 70 in the width direction (for example, the direction orthogonal to the inner surface of FIG. 16A), but either one may be omitted if only one side is sufficient.

  1 and 2, the discharge conveyor 3 is suspended and supported by a support member 112 provided at the discharge side (front side, right side in FIGS. 1 and 2) so as to protrude from the power unit 4. . The opposite side (rear side, left side in FIGS. 1 and 2) is supported by being suspended from the main body frame 36 via a support member 113. Thereby, the discharge conveyor 3 passes below the power unit 4 from the lower side of the crushing device 61, and is disposed in an upward inclination outward from the front side of the wood crusher. Reference numeral 114 denotes a frame of the discharge conveyor 3, and 115 denotes a conveyor belt wound between driving wheels (not shown) and driven wheels (not shown) provided at both ends of the frame 114 in the longitudinal direction. Reference numeral 116 denotes a drive device (hydraulic motor for the discharge conveyor) that rotationally drives the drive wheels 115. By rotating the drive device 116, the conveyor belt 115 is circulated between the drive wheels and the driven wheels. Yes.

  The power unit 4 is mounted on the other end in the longitudinal direction of the main body frame 36 (the right side in FIGS. 1 and 2) via a support member 117. A driver's seat 118 is provided in a compartment on the rear side of the power unit 4 and on one side in the width direction (lower side in FIG. 2). Reference numeral 119 denotes an operation lever for driving operation provided in the driver's seat 118, and 120 denotes an operation panel for performing other operations, settings, monitoring, and the like. In this example, the operation panel 120 is provided on the side of the machine body so that the operator can easily operate from the ground, but may be provided on the driver's seat 118.

  The operation panel 120 receives operation signals from the operation unit of the operation panel 120 and detection signals from sensors provided in each unit, and controls the flow of pressure oil to each hydraulic actuator according to these input signals. A control device 121 (see the next FIG. 18) that outputs a command signal to the solenoid valve, a display signal to the operation panel 120, and manages operation data and the like is incorporated.

FIG. 18 is a block diagram illustrating a schematic configuration of the control device 121.
In FIG. 3, reference numeral 122 denotes an A / D converter that is a signal input unit. Via this A / D converter 122, detection signals from sensors provided in various places and signals from the operation unit of the operation panel 120 are displayed. An operation signal is input and converted into a digital signal. 123 is a read-only memory (ROM) that stores a program of a predetermined control procedure and constants necessary for control, 124 is a timer that measures time, 125 is a command stored in the ROM 123, etc. This is a central processing unit (CPU) that calculates signals and display signals on the display unit of the operation panel 120. 126 is a random access memory (RAM) that temporarily stores the calculation results of the CPU 125 and numerical values during the calculation, and 127 is a D / A converter that converts the command signal calculated by the CPU 125 into an analog signal and outputs the analog signal to a corresponding device. It is.

  Although not specifically shown, the control device 121 is also provided with a memory and the like, in which the detection signals from various sensors or operation data calculated based on the signals are stored. Is done. The stored data can be output to a display unit or an external device in accordance with a predetermined operation on the operation unit of the operation panel 120.

  Here, the hydraulic actuators such as the traveling body 1, the discharge conveyor 3, the feed conveyor 11, the crushing device 12, the presser roller 53, the hydraulic cylinders 81 and 101, the lock cylinders 87 and 107, etc. A driven member is configured to be driven by a hydraulic drive device provided in the wood crusher.

FIG. 19 is a hydraulic circuit diagram showing the overall configuration of the hydraulic drive device provided in the embodiment of the wood crusher of the present invention. In this figure, the same parts as those in the previous figures are denoted by the same reference numerals. The description is omitted.
In FIG. 19, reference numerals 130 and 131 denote variable displacement first and second hydraulic pumps driven by an engine (not shown), and 132 denotes left and right traveling hydraulic motors 8L and 8R and a crusher hydraulic motor 67. 1 is a first control valve device that controls the flow of pressure oil from the first and second hydraulic pumps 130 and 131 (details will be described later).

  133 and 134 are fixed displacement type third hydraulic pumps and pilot pumps driven by an engine (not shown), 135 is a hydraulic actuator of an auxiliary machine other than the above (here, feed conveyor hydraulic motor 49, presser roller hydraulic motor 58) The second control valve device (details will be described later) for controlling the flow of pressure oil supplied to the discharge conveyor hydraulic motor 116 and the second screen hydraulic cylinder 101. 136 is an operation valve device, 137L and 137R are left and right travel operation lever devices provided with left and right travel operation levers 119L and 119R provided in the driver's seat 118, and 138 and 139 are first and second hydraulic pumps. It is the regulator apparatus which adjusts the discharge flow rates and output torque of 130 and 131, respectively. In this example, the hydraulic cylinders 81, 87, and 107 described above are omitted for the purpose of preventing congestion, but the hydraulic circuit is the same as that of the second screen hydraulic cylinder 101.

  The first control valve device 132 includes first and second crushing device control valves 140 and 141 connected to the crushing device hydraulic motor 67 and a left running control valve 142 connected to the left running hydraulic motor 8L. And a right travel control valve 143 connected to the right travel hydraulic motor 8R.

  The first and second crushing device control valves 140 and 141 and the left and right traveling control valves 142 and 143 are respectively connected to the crushing device hydraulic motor 67 and the left and right traveling hydraulic motors 8L and 8R. This is a three-position switching valve that can control the flow rate. Among these, the first crushing device control valve 140 and the left traveling control valve 142 are arranged in the center bypass line 145 connected to the discharge pipe 144 of the first hydraulic pump 130 from the upstream side to the left traveling control valve 142, The first crushing device control valves 140 are arranged in this order. A pump control valve 146 is provided on the most downstream side of the center bypass line 145. On the other hand, the second crushing device control valve 141 and the right traveling control valve 143 are connected to the right bypass control valve 143 from the upstream side in the center bypass line 148 connected to the discharge pipe 147 of the second hydraulic pump 131, The second crushing device control valves 141 are arranged in this order. A pump control valve 149 is provided on the most downstream side of the center bypass line 148.

  The left and right traveling control valves 142 and 143 are center bypass type pilot operation valves, which are operated by pilot pressure generated by the pilot pump 134 and reduced to a predetermined pressure by the left and right operation lever devices 137L and 137R. It has come to be. The operation lever devices 137L and 137R respectively include operation levers 119L and 119R and a pair of pressure reducing valves 150a and 150b and 151a and 151b that output pilot pressures corresponding to the operation amounts. The pilot pressure corresponding to the operation amount is guided to the left / right travel control valves 142, 143 via a pilot line (not shown), whereby the left / right travel control valves 142, 143 are switched to the left. The right traveling hydraulic motors 8L and 8R are driven.

  The control valves 140 and 141 for the first and second crushing devices are generated by the pilot pump 134 and reduced to a predetermined pressure by the crushing device normal rotation solenoid control valve 152 and the crushing device reverse rotation solenoid control valve 153 in the operation valve device 136. The pilot pressure is operated. When the forward drive signal is input from the control device 121 described above, the crushing device forward solenoid control valve 152 is switched to the communication position and the crushing device reverse solenoid control valve 153 is set to the shut-off position. The pressure is guided to the first and second crushing device control valves 140 and 141 through an introduction pipe (not shown), and the first and second crushing device control valves 140 and 141 are switched to the forward rotation switching position. . As a result, the crusher hydraulic motor 67 is driven in the forward direction. On the other hand, when a reverse drive signal is input from the control device 121, the crushing device reverse solenoid control valve 153 is switched to the communication position, and the crushing device normal rotation solenoid control valve 152 is set to the shut-off position. The crusher control valves 140 and 141 are switched to the reverse switching position, and the crusher hydraulic motor 67 is driven in the reverse direction.

  Here, the above-described operation valve device 136 is provided with a solenoid control valve 154 that shuts off the pilot pilot pressure from the pilot pump 134 to the operation lever devices 137L and 137R. This solenoid control valve 154 is switched to the shut-off position when the travel lock signal input from the control device 121 is turned on, shuts off the pilot original pressure from the pilot pump 134, and the left and right by the operation lever devices 137L and 137R. The above operation of the traveling control valves 142 and 143 is invalidated. On the other hand, when the travel lock signal input from the control device 121 is turned off, the operation position is switched to the communication position, and the operation of the left / right travel control valves 142, 143 by the operation levers 119L, 119R is validated. Therefore, a safe crushing operation can be performed by storing a program for turning on the traveling lock signal during the crushing operation.

  The pump control valves 146 and 149 have a function of converting the flow rate into pressure, and feed back the amounts of pressure oil flowing into the pump control valves 146 and 149 from the center bypass lines 145 and 148 to the regulator devices 138 and 139, respectively. To work.

  That is, when both the first crushing device control valve 140 and the left travel control valve 142 are in the neutral position, the required flow rate required for the first hydraulic pump 130 is reduced, and therefore, the first crushing device control valve 140 is discharged from the first hydraulic pump 130. Most of the pressure oil is introduced into the pump control valve 146 via the center bypass line 145 as an excessive flow rate, and the set relief pressure of the relief valve 146a of the pump control valve 146 is lowered. As a result, the pilot pressure guided to the regulator device 138 via the conduit 155 becomes relatively low, and the tilt of the first hydraulic pump 130 is reduced by the regulator device 138 and the discharge flow rate is reduced.

  On the other hand, when the control valves 140 and 142 are in the open state, the required flow rate required for the first hydraulic pump 130 increases, and the pressure oil flowing through the center bypass line 145 is reduced by the flow rate flowing toward the hydraulic motors 8L and 67. Therefore, the excessive flow rate becomes relatively small. As a result, the set relief pressure of the relief valve 146a increases, the pilot pressure guided to the regulator device 138 via the conduit 155 becomes relatively high, and the tilt of the first hydraulic pump 130 is increased by the regulator device 138. The discharge flow rate increases.

  Similarly, when both the second crushing device control valve 141 and the right traveling control valve 143 are in the neutral position, the set relief pressure of the relief valve 149a of the pump control valve 149 becomes low, and the regulator device is connected via the conduit 156. Since the pilot pressure guided to 139 becomes relatively low, the regulator device 139 reduces the tilt of the second hydraulic pump 131 and reduces the discharge flow rate. When the control valves 141 and 143 are in the open state, the set relief pressure of the relief valve 149a is increased, and the pilot pressure guided to the regulator device 139 via the conduit 156 is relatively increased. As a result, the tilt of the second hydraulic pump 131 is increased by the regulator device 139 and the discharge flow rate is increased.

  With such a circuit configuration, the first and second hydraulic pressures are obtained so that the discharge flow rates corresponding to the required flow rates of the first and second crushing device control valves 140 and 141 and the left and right traveling control valves 142 and 143 are obtained. So-called negative control is performed to control the discharge flow rate of the pumps 130 and 131.

  Here, the operation valve device 136 described above is provided with a solenoid control valve 157 that shuts off the pilot pilot pressure from the pilot pump 134 to the pump control valves 146 and 149. The solenoid control valve 157 is switched to the shut-off position when the input signal from the control device 121 is turned on, shuts off the pilot original pressure to the pump control valves 146 and 149, and invalidates the negative control. In this case, the pilot pressure acting on the regulator device 138 becomes the tank pressure, and the discharge flow rate of the first hydraulic pump 130 becomes the minimum value. On the other hand, the solenoid control valve 157 is switched to the communication position when the input signal from the control device 121 is turned OFF, guides the pilot pressure to the pump control valves 146 and 149, and validates the negative control.

  In addition, the operation valve device 136 is provided with solenoid control valves 158 and 159 that block a pipe line between the pump control valve 146 and the regulator device 138 of the first hydraulic pump 130. These solenoid control valves 158 and 159 are switched to the communication position and the cutoff position, respectively, when the input signal from the control device 121 is turned off. In this state, the pilot pressure from the pilot pump 134 is guided to the pump control valve 146, and the negative control is activated. On the other hand, when the input signal from the control device 121 is turned off, the solenoid control valves 158 and 159 are switched to the cutoff position and the communication position, respectively. In this case, the solenoid control valve 158 shuts off the pump control valve 146 and the regulator device 138, and the pilot pressure from the pilot pump 134 is directly guided to the regulator device 138 via the solenoid control valve 159, so that the first hydraulic pump The discharge flow rate 130 is a maximum value.

  With such a circuit configuration, the discharge flow rate of the first hydraulic pump 130 can be forcibly increased or decreased regardless of the operating state of the crushing device hydraulic motor 67 and the left and right traveling hydraulic motors 8L and 8R. ing.

  The second control valve device 135 includes a feed conveyor switching valve 160 connected to the feed conveyor hydraulic motor 49, a press roller switching valve 161 connected to the press roller hydraulic motor 58, and a discharge conveyor hydraulic motor 116. And a second screen switching valve 163 connected to the second screen hydraulic cylinder 101. As described above, in FIG. 19, the hydraulic circuit portions corresponding to the hydraulic cylinders 81, 87, 107, etc. are not shown.

  The switching valves 160 to 163 are appropriately constituted by two-position switching valves or three-position switching valves that can control the flow of pressure oil to the corresponding hydraulic actuators 49, 58, 116, 101 in response to command signals from the control device 121. Thus, pressure oil is supplied from the third hydraulic pump 133. These switching valves 160 to 163 are, from the upstream side in the center bypass line 165 connected to the discharge pipe 164 of the third hydraulic pump 133, the second screen switching valve 163, the discharge conveyor switching valve 162, and the presser roller. The switching valve 161 and the feed conveyor switching valve 160 are arranged in this order. A pressure compensation valve 166 is provided on the most downstream side of the center bypass line 165, and the maximum pressure of the center bypass line 165 is limited.

  When the command signal from the control device 121 is turned ON, the switching valves 160 to 163 are switched to the communication position corresponding to the operation. As a result, the corresponding hydraulic motor is switched and supplied from the direction corresponding to the operation, and is driven by the pressure oil not less than the predetermined pressure via the pressure compensation valve 167, respectively. At this time, in this example, since the discharge conveyor switching valve 162 is a two-position switching valve, pressure oil is supplied to the discharge conveyor hydraulic motor 116 from a single direction, and the discharge conveyor hydraulic motor 116 is single. Although it is driven in the direction, the discharge conveyor switching valve 162 may be a three-position switching valve, and the discharge conveyor hydraulic motor 116 may be configured to be reversely rotatable. On the other hand, when the command signal from the control device 121 is turned OFF, the switching valves 160 to 163 are switched to the cutoff position, and the corresponding hydraulic motor is stopped.

  In the wood crusher of the present invention configured as described above, the greatest feature of the present embodiment is that a torque changing means capable of changing the output torque of the drive device (feed conveyor hydraulic motor) 49 of the feed conveyor 11 is provided. is there. In the present embodiment, the torque changing means includes a regulator device 170 that changes the tilt of the feed conveyor hydraulic motor 49 and a control valve 171 that controls the pilot pressure that drives the regulator device 170.

  The control valve 171 is switched and driven by a torque change signal from the control device 121. When the torque change signal is turned ON, the control valve 171 is switched to the communication position. Then, the pilot original pressure from the pilot pump 134 is guided to the regulator device 170 via the pipe line 172, whereby the tilt of the feed conveyor hydraulic motor 49 increases, and the capacity of the feed conveyor hydraulic motor 49 increases. The output torque is controlled and increased.

  On the other hand, when the torque change signal from the control device 121 is turned OFF, the control valve 171 is switched to the cutoff position. Then, the pilot pump 134 and the pipe line 172 are blocked by the control valve 171, and the pipe line 172 communicates with the tank 173. As a result, the pilot pressure acting on the regulator device 170 becomes the tank pressure, so that the tilt of the feed conveyor hydraulic motor 49 is reduced, the capacity of the feed conveyor hydraulic motor 49 is reduced, and the normal output torque is restored. .

Here, typical examples of the ON / OFF switching timing of the torque change signal from the control device 121 to the control valve 171 include the following cases.
For example, when load detection means for detecting discharge pressure, output torque, etc. of the feed conveyor hydraulic motor 49 is provided, and the load on the feed conveyor hydraulic motor 49 calculated based on the detection signal from the load detection means is excessive. In addition, a command signal is output to the feed conveyor switching valve 160, and a program for switching the supply direction of the pressure oil to the feed conveyor hydraulic motor 49 to reversely drive the feed conveyor 11 for a predetermined time is stored in the ROM 123 of the control device 121 in advance. Keep it.

  In such a configuration, when the control device 121 instructs the reverse rotation of the feed conveyor 11, at the same time as (or slightly before or after) returning the feed conveyor 11 to the forward rotation operation after a predetermined time has elapsed, Turn on the torque change signal. By doing so, even if a piece of wood is still caught on the feed conveyor 11, the output torque of the feed conveyor hydraulic motor 49 is increased, so that the piece of wood is forcibly conveyed. Thereafter, when the load of the feed conveyor hydraulic motor by the load detection means returns to within the appropriate range, the control device 121 turns off the torque change signal and returns the output torque of the feed conveyor hydraulic motor 49 to the normal value.

  At this time, for example, if the load of the hydraulic motor 49 for the feed conveyor does not return within the proper range even after the torque is increased by setting the control valve 171 to be a proportional electromagnetic type, the increased output torque value is maintained, and again It is also conceivable that the torque change signal is increased when the feed conveyor 11 returns to the normal rotation operation through the reverse rotation operation and the output torque of the feed conveyor hydraulic motor 49 is further increased. In addition, when a program for automatically reversely rotating the feed conveyor 11 when the feed conveyor hydraulic motor 49 is overloaded is not stored in advance, the operator determines that it is overloaded by looking at the operating state of the feed conveyor 11. When the feed conveyor 11 is reversely rotated for a predetermined time by manual operation, the torque change signal is turned on (or increased) together with (or before and after) the operation signal from the operation panel 120 when switching to the normal rotation operation. It is also conceivable to store the program in the ROM 123 of the control device 121. Further, regardless of the reverse operation of the feed conveyor 11, the torque change signal is turned ON when an overload of the feed conveyor hydraulic motor 49 is detected, and the torque is changed when the load of the feed conveyor 11 returns to an appropriate range. It is also conceivable that a program for turning off the signal is stored in the ROM 123 and the control device 121 executes this program.

  As described above, in the present embodiment, the torque changing means including the regulator device 171 and the control valve 170 is driven by the torque change signal output from the control device 121, and automatically when the feed conveyor 11 is overloaded. The output torque of the feed conveyor hydraulic motor 49 can be controlled and changed. Of course, it is also possible to control and change the output torque of the feed conveyor hydraulic motor 49 by manual operation.

Next, operation | movement and an effect | action of the wood crusher which concern on this Embodiment of the said structure are demonstrated one by one.
For example, when wood to be crushed is introduced into the hopper 10 with an appropriate work tool such as a grapple of a hydraulic excavator, the wood to be crushed is guided by the expanding portion 17 of the hopper 10 and placed on the carrier 42 of the feed conveyor 11. Then, it is transported in a substantially horizontal direction toward the front side of the wood crusher by a transport body 42 that is circulated and driven while being guided by the side wall body 16 of the hopper 10.

  When the wood to be crushed on the feed conveyor 11 is conveyed to the vicinity of the press conveyor device 13, it enters the lower part of the press roller 53 of the press conveyor device 13 and pushes up the press conveyor device 13. Thereby, the wood to be crushed on the feed conveyor 11 is introduced into the crushing chamber 60 while being pressed and held between the feed conveyor 11 by the action of the weight of the press conveyor device 13. Thereby, at the time of crushing, the to-be-crushed wood protrudes into the crushing chamber 60 in a cantilevered manner with the portion sandwiched between the presser roller 54 and the feed conveyor 11 as a fulcrum, and this protruding portion of the crushing rotor 61 rotates. When the crushing bit 65 collides, the primary crushing is relatively roughly performed. The pieces of crushed wood that have been primarily crushed go around the space in the crushing chamber 60 on the outer periphery side of the crushing rotor 61 in the rotation direction of the crushing rotor 61, and sequentially collide with the first and second anvils 62 and 63. , The impact is further shattered.

  Of the pieces of wood that are being crushed as described above, those that are larger than the holes provided in the first and second screens 69 and 70 continue to circulate in the crushing chamber 60, By colliding with the first and second anvils 69 and 70 again, they are further crushed. Thus, when pulverized to a particle size that passes through the holes of the first and second screens 69, 70, crushed wood (wood chips) passes through the holes of the first or second screens 69, 70, It is discharged from the crushing device 12.

  The crushed wood (wood chips) discharged from the crushing device 12 falls on the conveyor belt 115 of the discharge conveyor 3 that is circulated and driven through a chute (not shown), and moves forward (right side in FIGS. 1 and 2). And are discharged as recycled products.

  Here, when the bottomed hopper 10 is used as in the present embodiment, when a part of the crushed wood to be transported is caught on the transport body 42, the crushed wood to be caught is the bottom of the hopper 10. It stays on the wall 18 and is compacted between the bottom wall 18 and the transport body 42, or is bitten between the transport body 42 and the drive wheel 40 or between the transport body 42 and the driven wheel 41. There is a possibility of sneaking. In such a case, the wood conveyor biting causes an overload on the driving device 49 of the feed conveyor 11, and the feed conveyor 11 may stop in a severe case.

  Therefore, in the present embodiment, when the wood to be crushed is introduced into the crushing device 12 by the feed conveyor 11 and crushed, when the wood to be crushed is caught in the feed conveyor 11, the torque changing means is used as described above. The output torque of the feed conveyor hydraulic motor 49 is temporarily increased. Thereby, the output of the feed conveyor 11 temporarily increases, the wood piece on the bottom wall 18 can be forcibly moved to the rear side, guided by the guide member 35, and returned to the conveying surface. If the opening / closing part 121 of the hopper 10 described above is opened, the piece of wood staying in the hopper 10 can be discharged from the rear end side. It is also possible to forcibly pass the piece of wood bitten between the driving wheel 40 and the transport body 42 or between the driven wheel 41 and the transport body 42 through the driving wheel 40 or the driven wheel 41. The biting of the crushed wood can be released. Therefore, the stop by the overload of the feed conveyor 11 can be avoided, and even if a piece of wood bites into the feed conveyor 11, the object to be crushed smoothly continuously to the crushing device 12 without stopping the feed conveyor 11. Can be supplied.

  Further, in general, a hydraulic motor for a feed conveyor is used on the small capacity side during normal operation. As a result, the required maximum flow rate is reduced compared to the large capacity side, and power consumption is reduced. If the feed conveyor hydraulic motor 49 is used on the large capacity side from the beginning, it is necessary to always secure the flow rate of the pressure oil in order to secure the number of rotations required according to the feed speed of the wood to be crushed. In general, if a large torque motor is used only on the large torque side, it will take time to recover once an overload condition occurs. In the first place, as mentioned above, the maximum torque is very rarely required to break down the state due to the biting of wood pieces, etc. The power becomes excessive, the horsepower to be distributed to the crushing device 12 is reduced, and the processing capacity is reduced.

  With respect to this point as well, in the present embodiment, the feed conveyor hydraulic motor 49 is normally used on the small capacity side, and only when an overload occurs, the feed conveyor hydraulic motor 49 is set to a large capacity by the torque changing means. By switching to the use on the side, wasteful power consumption is suppressed, and a reduction in processing capacity can be prevented.

Next, another embodiment of the wood crusher of the present invention will be described with reference to the drawings.
FIG. 20 is a hydraulic circuit diagram showing the overall configuration of a hydraulic drive device provided in another embodiment of the wood crusher of the present invention. In this figure, the same parts as those in the previous figures are denoted by the same reference numerals. The description is omitted.
This embodiment differs from the above-described embodiment of the wood crusher of the present invention in that it is supplied to the feed conveyor hydraulic motor 49 as torque changing means for changing the output torque of the feed conveyor hydraulic motor 49. This is a variable relief valve 180 for changing the relief pressure of the pressurized oil.

  The variable relief valve 180 is a pilot-operated proportional electromagnetic relief valve, and a branch line 182 that connects a supply line 181 that supplies pressure oil to the feed conveyor hydraulic motor 49 from the normal rotation direction and a tank 173. The supply line 183 for supplying pressure oil from the reverse direction and the branch line 184 connecting the tank 173 are provided respectively.

  The relief pressure of the supply lines 181 and 183 limited by the variable relief valve 180 (that is, the maximum pressure of the pressure oil to the feed conveyor hydraulic motor 49) is normally set by the spring 185, and the supply line 183 or The supply line 183 or 185 communicates with the tank 173 when the pressure oil pressure of 185 exceeds the biasing force of the spring 185.

  On the other hand, for example, when a piece of wood bites into the feed conveyor 11 and the hydraulic motor 49 falls into an overload state, the maximum pressure oil in the supply line 181 or 183 on the supply side to the hydraulic motor 49 at that time The torque change signal to the solenoid drive unit 186 of the variable relief valve 180 that limits the value is increased. This torque change signal is output from the control device 121 described above. As a result, the urging force from the solenoid drive unit 186 according to the magnitude of the torque change signal is applied, and the relief pressure of the supply lines 181 and 183 restricted by the variable relief valve 180 is pushed up, and the feed conveyor hydraulic motor 49 Output torque can be increased.

  Of course, when the overload state of the feed conveyor hydraulic motor 49 is released, the supply line 181 is turned off as described above by turning off (or reducing) the torque change signal from the control device 121 to the solenoid drive unit 186. , 183 can be restored (or reduced) to a normal state limited to the biasing force of the spring 185 only.

  Also in the present embodiment, the procedure for increasing the torque change signal to the variable relief valve 180 is executed in accordance with the reverse operation of the feed conveyor 11 and the return to the normal operation thereafter, as in the previous embodiment. The program is stored in the ROM 123 of the control device 121 described above. Further, particularly in the present embodiment, when the reverse operation of the feed conveyor hydraulic motor 49 is repeatedly performed, the torque change signal is increased stepwise correspondingly, and the output torque of the feed conveyor hydraulic motor 49 is stepped. It is programmed to control so that it grows larger.

21 is a flowchart showing a torque control procedure of the feed conveyor hydraulic motor 49 by the control device 121, and FIG.
As shown in FIGS. 21 and 22, the control device 121 calculates the load of the hydraulic motor 49 for the feed conveyor during the crushing operation in step 101, and determines whether or not it is equal to or greater than a threshold value. . When the load of the feed conveyor hydraulic motor 49 is greater than or equal to the threshold value, the control device 121 outputs a command signal for causing the feed conveyor 11 to perform reverse operation to the feed conveyor control valve 160 to cause the feed conveyor 11 to perform reverse operation. The procedure proceeds to step 102 at the same time (or slightly before or after) when the feed conveyor 11 is returned to the normal rotation operation after the predetermined time has elapsed. In this example, the timing of shifting the procedure to step 102 is set to the time of switching from the reverse operation to the normal operation (time T ₁ ) as shown in FIG. 22, but the present invention is not limited to this. It does not matter if it is between the time when the operation is performed and the forward operation is switched.

In the subsequent step 102, the control device 121 calculates a torque change signal by the CPU 125 according to the program stored in the ROM 123 and outputs the torque change signal to the variable relief valve 180. The magnitude of the torque change signal output with this first reverse rotation operation increases the relief pressure P of the supply pipeline 181 or 183 to a value P ₁ that is increased from the normal value P ₀ by a set value. It is the size to do.

Next, the process proceeds to step 103, and the control device 121 causes the CPU 125 to determine, based on the measurement time of the timer 124, before the elapsed time T ₀ after the torque change signal is output reaches a predetermined time Tf (set value). It is determined whether or not the reverse operation of the feed conveyor 11 has been performed again (in other words, whether or not the load of the feed conveyor hydraulic motor 49 is still greater than or equal to the threshold value). After the torque change signal is output, when the load on the feed conveyor hydraulic motor 49 does not fall below the threshold value, the feed conveyor 11 is reversely rotated again within the predetermined time Tf, and the determination of this step is satisfied. Returns the procedure to step 102, and further increases the output torque of the hydraulic motor 49 for the feed conveyor by one step (time T ₂ ). In this way, when the reverse rotation operation of the feed conveyor 11 is repeated before the predetermined time Tf has elapsed from the immediately preceding torque change signal output time, the steps 102 and 103 are repeatedly executed. Thus, for example, as illustrated in FIG. 22, the relief pressure P ₂ (> P ₁ ) at times T _{2 to} T _{3 and} the relief pressure P ₃ (> P ₂ ) at times T _{3 to} T _4. Then, the relief pressure is increased stepwise by a set amount.

If the reverse operation of the feed conveyor 11 is not performed even after the predetermined time Tf has elapsed after the output of the immediately preceding torque change signal, the control device 121 moves the procedure to step 104 to reduce the torque change signal (or to OFF), the relief pressure P of the supply line 181 or 183 to return to the normal value _{P 0} at, ends the procedure. If the reverse operation of the feed conveyor 11 is not performed in the previous step 101, the procedure is terminated as it is.

  Also in the present embodiment, by repeating the above procedure, when the hydraulic motor 49 falls into an overload state due to a piece of wood biting into the feed conveyor 11 or the like, temporarily as described above. The output torque of the feed conveyor hydraulic motor 49 can be increased, and the same effect as that of the embodiment of the wood crusher of the present invention described above can be obtained. In addition, according to the present embodiment, when the reverse operation of the feed conveyor 121 is repeated, wasteful power consumption is reduced by increasing the relief pressure step by step according to the set pressure. It is also suitable for ensuring energy efficiency.

  In the present embodiment, except for the portion related to the variable relief valve 180 as the torque changing means described above, the other configuration is the same as that of the embodiment of the wood crusher of the present invention described above. However, in FIG. 20, the control valve 170 and the regulator device 170 are also illustrated, and can be used together with the torque change in the above-described embodiment, but of course, these can be omitted.

  In this embodiment, in order to automatically change the output torque of the feed conveyor hydraulic motor 49, the torque change signal is output based on the signal resulting from the reverse rotation of the feed conveyor 11. Not limited to. For example, a pressure sensor is provided in the pressure oil supply line of the hydraulic motor 49 for the feed conveyor, the load of the feed conveyor 11 is calculated by the control device 121 based on the detection signal from the pressure sensor, and the calculation result is thresholded. A torque change signal may be output as necessary by comparing with the value. In addition, a torque sensor may be provided in the hydraulic motor 49 of the feed conveyor 11 and the output torque of the hydraulic motor 49 may be similarly changed according to the detection result. In these cases, similar effects can be obtained.

  Further, in this embodiment, the output torque of the feed conveyor hydraulic motor 49 is increased stepwise, but as long as the overload state of the feed conveyor hydraulic motor 49 is removed, it is not necessarily stepped. There is no need to increase the torque. When the increase in the output torque is simply turned ON / OFF, the solenoid drive unit 186 of the variable relief valve 180 may be a simple electromagnetic drive type instead of a proportional electromagnetic type. Further, although the output torque is automatically changed, for example, a torque change signal may be input to the solenoid drive unit 186 of the variable relief valve 180 via the control device 121 according to a command from the operation panel 120. .

  Moreover, in both embodiment demonstrated above, although the presser conveyor apparatus 13 mentioned above was employ | adopted as a press introduction means of to-be-crushed wood, it is not restricted to this, For example, it is an endless shape between a drive roller and a driven roller. You may use what wound a member (belt, a chain, etc.). Further, the operation at the time of pressing may be configured to move up and down instead of rotating. Further, although the bottomed hopper 10 is used, it may be replaced with a bottomless one. In these cases, the same effect is obtained.

  Moreover, although the wood crusher provided with what is called an impact crusher which attached the cutter (crushing bit 65) to the outer peripheral part of the crushing rotor 61 as an example was demonstrated as an example, it is not restricted to this, Other crushing apparatuses, for example, parallel A crushing device (such as a biaxial shearing machine including a so-called shredder) that has a cutter on a shaft arranged on the shaft and reversely rotates each other, and a roll-shaped rotating body (rotor) for crushing blades A rotary crushing apparatus (such as a six-axis crusher including a roll crusher) that rotates the pair in opposite directions and crushes the object to be crushed between the rotating bodies. Also, the present invention can be applied to a wood crusher equipped with a so-called wood chipper that makes the object to be crushed into chips. In these cases, the same effect as described above is obtained.

  Furthermore, although the case where the present invention is applied to a wood crusher capable of traveling on its own has been described as an example, the present invention is not limited thereto, and it can be lifted and transported by a mobile wood crusher that can be towed and run, for example, a crane. Needless to say, the present invention may be applied to a portable wood crusher, and further to a stationary wood crusher arranged as a fixed machine in a plant or the like.

It is a side view showing the whole structure of one embodiment of the wood crusher of the present invention. It is a top view showing the whole structure of one embodiment of the wood crusher of the present invention. It is a side view showing the detailed structure inside the side cover of the crushing device vicinity with which one Embodiment of the wood crusher of this invention was equipped. It is a side view showing the detailed structure of the rear end vicinity provided in one embodiment of the wood crusher of this invention. FIG. 5 is a cross-sectional view taken along line VV in FIG. 4 showing a detailed structure in the vicinity of a rear end of a hopper provided in an embodiment of the wood crusher of the present invention. It is the front view seen from the back of hopper 10 showing the detailed structure near the rear end of the hopper with which one embodiment of the wood crusher of the present invention was equipped. It is a VII-VII arrow sectional view in Drawing 6 showing the detailed structure of the rear end part of the feed conveyor with which one embodiment of the wood crusher of the present invention was equipped. It is detail drawing of the locking mechanism of the opening-and-closing part of the hopper with which one embodiment of the wood crusher of this invention was equipped. It is a figure showing the state by which the opening / closing part of the hopper with which one Embodiment of the wood crusher of this invention was equipped was open | released. It is a side view of the crushing device vicinity with which one Embodiment of the wood crusher of this invention was equipped. It is sectional drawing showing in detail the internal structure of the crushing device vicinity with which one Embodiment of the wood crusher of this invention was equipped. It is a figure showing the detail of those movable mechanisms which extracted the structure of the 1st anvil and 1st screen vicinity with which one Embodiment of the wood crusher of this invention was equipped. It is a figure showing the detail of those movable mechanisms which extracted the structure of the 1st anvil and 1st screen vicinity with which one Embodiment of the wood crusher of this invention was equipped. It is the XIV-XIV arrow directional cross-sectional view in FIG. 12 which extracts the structure of the 1st anvil and 1st screen vicinity with which one Embodiment of this invention was equipped, and shows the detail of those movable mechanisms. It is a figure showing the state at the time of lock release of the 1st screen with which one Embodiment of the wood crusher of this invention was equipped. It is a figure showing the detail of the movable mechanism which extracted the structure of the 2nd screen vicinity with which one Embodiment of the wood crusher of this invention was equipped. It is a figure showing the state of the crushing device periphery at the time of lock release of the 2nd screen with which one Embodiment of the wood crusher of this invention was equipped. It is a block diagram showing schematic structure of the control apparatus with which one Embodiment of the wood crusher of this invention was equipped. It is a hydraulic circuit diagram showing the whole structure of the hydraulic drive unit with which one embodiment of the wood crusher of this invention was equipped. It is a hydraulic circuit figure showing the whole structure of the hydraulic drive unit with which other embodiment of the wood crusher of this invention was equipped. It is a flowchart showing the torque control procedure of the drive device by the control apparatus with which other embodiment of the wood crusher of this invention was equipped. It is a timing chart at the time of torque control by the control apparatus with which other embodiment of the wood crusher of this invention was equipped.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Feed conveyor 12 Crushing device 40 Drive wheel 41 Driven wheel 42 Conveyance body 49 Hydraulic motor for feed conveyor (drive device)
120 Operation panel 121 Control device 170 Regulator device (torque changing means)
171 Control valve (torque changing means)
180 Variable relief valve (torque changing means)

Claims (6)

A crushing device for crushing the introduced shredded wood;
A driving wheel and a driven wheel provided at both ends in the conveying direction; a conveying body wound around the driving wheel and the driven wheel; and a driving device for driving the driving wheel to rotate; A feed conveyor that transports to
A wood crusher comprising: torque changing means capable of changing output torque of the driving device of the feed conveyor.   The wood crusher according to claim 1, wherein the torque changing means includes a regulator device that changes the tilt of the drive device and a control valve that controls a pilot pressure that drives the regulator device.   3. The wood crusher according to claim 1, wherein the torque changing unit is a variable relief valve that changes a relief pressure of a supply pipe that supplies pressure oil to the driving device.   4. The apparatus according to claim 1, further comprising a control device that outputs a torque change signal to the torque changing unit and controls an output torque of the drive device when the drive device is overloaded. 5. Wood crusher.   When the reverse rotation operation of the drive device is repeatedly performed, the control device increases the torque change signal to the torque changing means stepwise in response to this, and the output torque of the drive device increases stepwise. The wood crusher according to claim 4, which is controlled as follows.   When crushing wood to be crushed by introducing it into a crushing device with a feed conveyor and crushing the wood to be crushed, the output torque of the driving device that drives the feed conveyor is temporarily increased, The wood processing method characterized by canceling the biting of the feed conveyor.

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