JP2006247603A - Self-propelled crusher and its overload-protection arrangement - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a self-propelled crusher which enables a stable overload-protection of a jaw crusher for a long period, and its overload-protection arrangement. <P>SOLUTION: The crusher has a crusher frame 61, a fixed tooth 71 fixed to the crusher frame 61, a moving tooth 72 slidably supported by the crusher frame 61, a supporting member 64 fixed at a front side of the moving tooth 72 in the crusher frame 61, a braking plate 67 and a sliding member 66 provided so as to enable a sliding in a predetermined direction within a space formed by the supporting member 64, a braking piston 69 giving a pressure via a friction plate 68 from a direction perpendicular to the sliding direction of the braking plate 67 so as to hold the braking plate 67, a toggle plate 70 held between the sliding member 66 and a lower end of the moving tooth 72, and a hydraulic cylinder 75 biasing to a direction where the moving tooth 72 and the supporting member 64 come close. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a self-propelled crusher provided with a crushing device that crushes an object to be crushed such as a jaw crusher and an overload protection device thereof.

  In general, crushers aim to reuse waste materials, facilitate construction, reduce costs, etc. by crushing objects to be crushed, such as various types of rocks and construction waste materials generated at construction sites, to a predetermined size. Used for.

  Among such crushers, for example, a self-propelled crusher is generally a main body frame, a traveling means provided in the main body frame, a hopper into which an object to be crushed is charged, and a load loaded into the hopper. Conveying means for conveying the crushed material to the crushing device, a crushing device for crushing the material to be crushed by the conveying means to a predetermined size, and a discharge conveyor for conveying the crushed material crushed by the crushing device to the outside of the machine It has.

  Among the crushing apparatuses, there is a so-called jaw crusher that swings a moving tooth with respect to a fixed tooth and introduces a material to be crushed between them to perform crushing. As conventional techniques of this jaw crusher, there are fixed teeth (fixed jaw plates), moving teeth (movable jaw plates) provided so as to be swingable with respect to the fixed teeth, and crushing that acts on the moving teeth from the object to be crushed. A lock cylinder (hydraulic mechanical lock device) that receives the reaction force by a frictional force acting between the cylinder and the rod, and a slide member (toggle block) that is provided at the rod end of the lock cylinder and that can slide in the axial direction of the cylinder ) And a toggle plate sandwiched between the slide member and the lower end of the moving tooth (for example, see Patent Document 1). In this jaw crusher, the crushing reaction force that acts on the moving teeth from the object to be crushed during normal crushing is transmitted to the lock cylinder through the toggle plate and the slide plate, and is received by the friction force of the lock cylinder. And when an overload is generated in the crushing device due to, for example, a foreign object biting in the crushing chamber between the fixed tooth and the moving tooth, the rod is connected to the cylinder by an excessive load acting on the lock cylinder at that time. The cylinder slides against the frictional force and the cylinder contracts, and the moving tooth retracts from the fixed tooth to eliminate the overload. Thereby, it can prevent that members, such as a toggle plate, are damaged by an excessive load at the time of an overload, and can protect the member at the time of an overload.

Japanese Utility Model Publication No. 63-141638

  In the above prior art, as described above, a lock cylinder is used to receive a load from the moving tooth side, but this lock cylinder has a structure that receives an axial load by a mechanical frictional force between the cylinder and the rod. As a result, the frictional force acting between the cylinder and the rod decreases as the rod slides against the frictional force with the cylinder when overloaded, and the frictional force can be kept constant over a long period of time. It was difficult. As a result, the magnitude of the load applied when the moving tooth is retracted from the fixed tooth varies, and the overload protection of the jaw crusher cannot be performed stably.

  The present invention has been made in view of the above-described problems of the prior art, and an object thereof is to provide a self-propelled crusher and its overload protection device capable of stably performing overload protection of a jaw crusher over a long period of time. It is to provide.

  (1) In order to achieve the above object, the first invention of the present application includes a main body frame, traveling means provided on the main body frame, a hopper provided on the main body frame for receiving an object to be crushed, and the main body frame. In the crushing device frame, a fixed tooth fixed to the crushing device frame, a moving tooth that is disposed to face the fixed tooth and is supported on the crushing device frame by an eccentric shaft so as to be swingable. A support member fixed to the front side of the moving tooth, a slide member provided so as to be slidable in a predetermined direction in a space formed by the support member, and a friction member at a tip, and the slide member A first pressing means for applying a pressing force from a direction perpendicular to the sliding direction of the slide member so as to hold it; a tong that is held between the slide member and a lower end portion of the moving tooth And a crushing device that crushes the object to be crushed received by the hopper, and crushing crushed by the crushing device. And a discharge conveyor for conveying the object outside the apparatus.

  In the present invention, at the time of crushing, the first pressing means applies a pressing force to the sliding member to brake (lock) the sliding of the sliding member. Thus, during normal load, the crushing reaction force transmitted from the object to be crushed through the moving teeth and the toggle plate can be received by the frictional force between the friction member of the first pressing means and the slide member. . On the other hand, when an overload occurs in the crushing device due to, for example, foreign matter biting in the crushing chamber between the fixed tooth and the moving tooth, an excessive load acting on the slide member from the moving tooth through the toggle plate The slide member slides forward (on the opposite side to the toggle plate) against the frictional force with the friction member of the first pressing means. As a result, the moving tooth moves backward from the fixed tooth and the overload is eliminated.

  According to the present invention, even when such an overload occurs repeatedly and the slide member slides against the frictional force many times, the first pressing means causes a substantially constant amount relative to the slide member. A pressing force can be applied. Thereby, the frictional force between the friction member of the first pressing means and the slide member can be kept substantially constant. As a result, since the load applied when the moving tooth is retracted from the fixed tooth can be made substantially constant without variation, the overload protection of the crushing device can be stably performed over a long period of time.

  (2) The second invention of the present application is characterized in that, in the first invention, the first pressing means includes a piston device that drives the piston by hydraulic pressure and applies a pressing force to the friction member.

  According to the present invention, by maintaining the pressure oil supplied to the piston device at a constant pressure, the friction member can be pressed against the slide member with a constant load by the piston device. Thereby, the frictional force between the friction member and the slide member can be kept substantially constant.

  (3) The third invention of the present application is characterized in that, in the second invention, there is provided control means for controlling the pressure oil for driving the piston device so as to be maintained at a substantially constant pressure.

  (4) According to a fourth invention of the present application, in the third invention, the slide member has a brake portion for stopping the slide, and the friction member and the piston device are arranged on both sides of the brake portion, respectively. It is characterized by that.

  Accordingly, the braking member can be pressed by being sandwiched from both sides by the friction member of the first pressing means, and a stable friction force can be generated between the friction member and the braking unit.

  (5) The fifth invention of the present application is characterized in that, in any one of the first to fourth inventions, the urging means is a hydraulic cylinder.

  In the present invention, at the time of crushing work, by supplying a constant pressure of oil to the hydraulic chamber on the rod side of the hydraulic cylinder, the hydraulic cylinder attempts to contract and the moving teeth and the support member are attached in a direction close to each other with a predetermined compression load. To force. When adjusting the gap between the fixed tooth and the moving tooth (set adjustment), the pressing of the first pressing means (or the piston device) against the slide member by the friction member is stopped to release the slide member, and in this state the hydraulic cylinder is By expanding and contracting, the gap between the fixed tooth and the moving tooth can be easily adjusted. In this way, a single hydraulic cylinder can serve as both the urging means and the set adjusting cylinder.

  (6) The sixth invention of the present application is characterized in that, in the fifth invention, there is provided a second pressing means for pressing the slide member and the toggle plate toward the moving tooth side.

  Thus, when the hydraulic cylinder is extended to adjust the set of the fixed tooth and the moving tooth to reduce the gap, the toggle plate and the slide member are moved so as to follow the movement of the moving tooth moving to the fixed tooth side. Can do. Therefore, the toggle plate can be prevented from falling off.

  (7) In order to achieve the above object, the seventh invention of the present application eliminates the overload of the crushing apparatus that rocks the moving teeth with respect to the fixed teeth and introduces the object to be crushed between them to crush. In the overload protection device for a self-propelled crusher that protects the member, a support member fixed to the front side of the moving tooth in the crushing device frame of the crushing device, and a space formed by the support member A sliding member provided so as to be slidable in a predetermined direction, and a friction member at the tip, and a pressing force is applied from a direction perpendicular to the sliding direction of the sliding member so as to sandwich the sliding member. It is characterized by comprising a first pressing means for giving, and a toggle plate sandwiched between the slide member and the lower end portion of the moving tooth.

  According to the present invention, overload protection of the jaw crusher can be performed stably over a long period of time.

Hereinafter, an embodiment of a self-propelled crusher and an overload protection device of the present invention will be described with reference to the drawings.
FIG. 1 is a side view showing the overall structure of an embodiment of the self-propelled crusher of the present invention, FIG. 2 is a top view thereof, and FIG. 3 is a front view as viewed from the left side in FIG. In the following description, the left and right in FIG. 1 are the rear and front of the crusher or the one side and the other side in the longitudinal direction of the main body frame, respectively.

  The self-propelled crusher in this embodiment is a large or small construction waste, industrial waste, or rock mining site that is generated at a construction site such as a concrete lump carried out at the time of building demolition or an asphalt lump discharged at road repair Rocks, natural stones, etc. mined with swords and working faces are treated, and these are received as the material to be crushed and crushed.

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

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

  Reference numeral 15 denotes a grizzly feeder located below the hopper 12. The grizzly feeder 15 is supported by the support bar 11 via a spring 18 separately from the hopper 12, and the object to be crushed received by the hopper 12 has its particle size. The material is conveyed to a crushing device 20 to be described later while sorting according to the conditions. 15A is a main body of the grizzly feeder 15, and a plurality of (two in this embodiment) comb teeth 16 arranged in the width direction of the main body frame 3 (vertical direction in FIG. 2) are provided in the grizzly feeder main body 15A. The grizzly river 17 is fixed in a staircase shape that descends forward. Reference numeral 19 denotes a feeder hydraulic motor that vibrates the grizzly feeder main body 15A. The grizzly feeder main body 15A is vibrated by the feeder hydraulic motor 19, and the object to be crushed on the loaded grizzly river 17 is conveyed forward.

  Reference numeral 14 denotes a chute provided below the comb teeth 16 of the grizzly river 17, and the chute 14 removes fine grains (so-called slip) contained in the object to be crushed from the gaps between the comb teeth 16 of the grizzly river 17. Then, it is guided onto a discharge conveyor 40 which will be described later. Reference numeral 23 denotes an installation space for an optional side conveyor (not shown) (see FIG. 1).

  Reference numeral 20 denotes a crushing device (jaw crusher) for crushing an object to be crushed. This crushing device 20 is located in front of the hopper 12 and the grizzly feeder 15, and as shown in FIG. It is installed in the vicinity. Although details are illustrated in FIG. 4 and the like later, this crushing device 20 is provided with a pair of fixed teeth 71 and moving teeth 72 which are arranged so as to face each other so that the gap space of each crushing space decreases in the downward direction. Reference numeral 21 denotes a crusher hydraulic motor (see FIG. 2). The crusher hydraulic motor 21 rotates a flywheel 22 (see FIG. 4 described later). As will be described later, the rotational motion of the flywheel 22 is converted into the swinging motion of the moving tooth 72, whereby the moving tooth 72 swings in the front-rear direction with respect to the fixed tooth 71. In the present embodiment, the drive transmission structure from the crushing device hydraulic motor 21 to the flywheel 22 is configured via a belt (not shown), but is not limited to this, and for example via a chain. Other configurations such as a configuration may be used.

  Reference numeral 25 denotes a power unit (power unit) having a built-in power source for each hydraulic actuator. The power unit 25 is located further forward than the crushing unit 20 and is connected to the longitudinal end of the main body frame 3 via the support member 26. It is supported by. Although not particularly illustrated, the power unit 25 is provided with an engine, hydraulic pumps 82 and 93 (see FIG. 5 to be described later), which are power sources of the crusher, and the like. Reference numerals 30 and 31 denote fuel tanks and hydraulic oil tanks (both not shown) built in the power unit 25, 32 a pre-cleaner, 35 a driver's seat provided in a rear compartment of the power unit 25, Reference numeral 36 denotes a travel operation lever for operating the travel hydraulic motor 8.

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

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

FIG. 4 is a side view showing the internal structure of the crushing device 20 in a partial cross section.
In FIG. 4, reference numeral 61 denotes a crushing device frame of the crushing device 20, and a pair of crushing device frames 61 are fixed or mounted on both sides in the width direction on the main body frame 3. A fixed tooth 71 is fixedly installed between the two crushing device frames 61, 61, and an eccentric drive shaft 62 in which a moving tooth 72 is rotatably provided on the crushing device frame 61 so as to face the fixed tooth 71. It is attached so that it can swing freely. At this time, the space formed by the fixed teeth 71 and the moving teeth 72 is the crushing chamber 63, and the object to be crushed is a predetermined defined by the gap between the fixed teeth 71 and the moving teeth 72 below the crushing chamber 63. It is crushed so that it is chewed to the size of.

  On the front side of the moving tooth 72 (right side in FIG. 4), for example, when a foreign substance is caught in the crushing chamber 63 and an overload occurs, members such as a toggle plate 70 described later are protected from an excessive load. An overload protection device 79 is installed. The overload protection device 79 includes a support member 64 fixed between the crushing device frames 61, 61, a guide member 65 provided on the rear side (left side in FIG. 4) of the support member 64, and the above-mentioned A sliding member (sliding member) 66 slidably provided along the guide direction of the guide member 65 in the space formed by the support member 64, and the front side (right side in FIG. 4) of the sliding member 66 And a substantially plate-like braking plate (sliding member, braking portion) 67 slidable with the sliding member 66 with respect to the support member 64, and braking so as to sandwich this braking plate 67. A friction plate (first pressing means, friction member) 68 that applies a pressing force from a direction substantially perpendicular to the sliding direction of the plate 67 (and the sliding member 66), and the friction plate 68 against the braking plate 67. Brake piston (first pressing means, piston) to be pressed with a predetermined load Ton device) 69, a toggle sheet 73 provided at both ends of the moving tooth 72 on the lower front side, and a toggle sheet 74 provided on the sliding member 66, and the moving tooth 72 receives from the object to be crushed during the crushing operation. A toggle plate 70 that transmits the crushing reaction force to the sliding member 66, and an air cylinder (second pressing means) 76 that presses the toggle plate 70, the sliding member 66, and the braking plate 67 toward the moving tooth 72 with an appropriate load. And. Here, the air cylinder 76 is used as a pressing means for pressing the brake plate 67 or the like toward the moving tooth 72, but it may be pressed using a spring or the like instead. Further, it is not always necessary to provide this pressing means, and it may be omitted.

  Reference numeral 75 denotes a hydraulic cylinder (biasing means) provided below the overload protection device 79 in order to prevent the toggle plate 70 from falling off. The hydraulic cylinder 75 causes the moving teeth 72 and the support member 64 to appropriately move during crushing work. It is urged in the approaching direction by the compression load (details will be described later). Further, during the set adjustment, the hydraulic cylinder 75 expands and contracts to adjust the gap between the fixed tooth 71 and the moving tooth 72 (details will be described later).

  The brake piston 69 presses the friction plate 68 against the brake plate 67 when pressure oil is supplied from the oil supply port 77 to the hydraulic chamber 78 to brake (lock) the sliding of the sliding member 66. The hydraulic drive device that drives the brake piston 69 will be described below together with the hydraulic drive device that drives the hydraulic cylinder 75.

  FIG. 5 is a hydraulic circuit diagram showing an extracted portion of the hydraulic drive device provided in the self-propelled crusher of this embodiment, which is related to driving of the brake piston 69 and the hydraulic cylinder 75.

  In FIG. 5, the first switching valve 80 is a switching valve that switches between locking and unlocking of the sliding operation of the sliding member 66. That is, when the first switching valve 80 is switched to the lock position 80A by a command signal from the controller 81, the pressure oil discharged from the first hydraulic pump 82 is connected to the lock position 80A of the first switching valve 80 and the pipe line. It is guided to a hydraulic chamber 78 provided in the support member 64 through 83. As a result, the brake piston 69 presses the friction plate 68 against the brake plate 67, and the sliding operation of the sliding member 66 is braked (that is, locked).

  On the other hand, when the first switching valve 80 is switched to the unlock position 80B by a command signal from the controller 81, the pipe 83 and the tank 84 are communicated so that the pressure in the hydraulic chamber 78 is equal to the tank pressure. Thus, the pressing force of the friction plate 68 against the brake plate 67 by the brake piston 69 is released, and the sliding operation of the sliding member 66 is allowed (that is, the unlocking state is established).

  On the other hand, when the command signal from the controller 81 is not output to the first switching valve 80, the first switching valve 80 is returned to the neutral position 80C by the biasing force of the springs at both ends, and the hydraulic chamber 78 and the pipe 83 Pressure oil is enclosed. Between the pipe 83 and the tank 84, there are an on-off valve 85 that can arbitrarily open the lock of the sliding member 66, and a relief valve 86 that sets a relief pressure in the hydraulic chamber 78 and the pipe 83. Is provided. The pipe 83 is provided with an accumulator 87, a hydraulic chamber 78, and a pressure sensor 88 for detecting the pressure in the pipe 83. The pressure value detected by the pressure sensor 88 is output to the controller 81, and the controller 81 outputs a command signal to the first motor 89 for driving the first hydraulic pump 82 in accordance with the detected value. The first hydraulic pump 82 is driven for an appropriate time so as to keep the pressure in the hydraulic chamber 78 and the pipe line 83 substantially constant.

  FIG. 6 is a flowchart showing the control contents related to the pressure constant holding control in the hydraulic chamber 78 and the pipe 83 performed by the controller 81.

  In FIG. 6, first, in step 10, the pressure P in the hydraulic chamber 78 and the pipe 83 detected by the pressure sensor 88 is input.

  In the next step 20, it is determined whether or not the pressure P input in step 10 is equal to or lower than Po-X. Here, Po is a set pressure of the hydraulic chamber 78, and X is a permissible value (allowable range of pressure drop) that can be regarded as substantially equal to the set pressure Po even if the pressure is reduced by this amount. The setting may be input by an appropriate external terminal). The set pressure Po is such that the frictional force generated between the brake plate 67 and the friction plate 68 is smaller than the buckling load of the toggle plate 70 when the pressure in the hydraulic chamber 78 is the set pressure Po. Is set to If the pressure P is greater than Po-X, the determination is not satisfied and the routine returns to step 10. On the other hand, if the pressure P is equal to or lower than Po-X, the determination is satisfied, and the routine goes to the next Step 30.

  In step 30, it is determined whether or not the state in which the pressure P is equal to or lower than Po-X continues for the time T. Here, the time T is a time determined so that the pressure in the hydraulic chamber 78 and the pipe line 83 can be regarded as lowered when the state where the pressure P is equal to or lower than Po-X continues for the time T or longer. For example, it is stored in advance in the controller 81 (or may be set and input by an appropriate external terminal). By this determination, it is possible to prevent the first hydraulic pump 82 from being erroneously driven due to an instantaneous pressure fluctuation due to an impact at the time of crushing, for example. If the determination is not satisfied, the process returns to step 10. On the other hand, if the determination is satisfied, the process proceeds to the next step 40.

  In step 40, a command signal is output to the first motor 89 to drive the first hydraulic pump 82, and a command signal is output to the first switching valve 80 to switch to the lock position 80 </ b> A and discharged from the first hydraulic pump 82. The pressurized oil thus introduced is introduced into the pipe 83 and the hydraulic chamber 78.

  In the next step 50, the pressure P in the hydraulic chamber 78 and the pipe 83 detected by the pressure sensor 88 is input again.

  In the next step 60, it is determined whether or not the pressure P input in step 50 is equal to or higher than the set pressure Po. If the pressure P has not reached the set pressure Po, the determination is not satisfied and the routine returns to step 50. If the pressure P reaches the set pressure Po, the determination is satisfied and the routine goes to the next step 70.

  In the next step 70, a command signal is output to the first motor 89 to stop the first hydraulic pump 82, and the command signal to the first switching valve 80 is turned OFF to return to the neutral position 80C. The pressure oil in the pipe 83 is sealed. Thereafter, the process returns to Step 10.

  The control flow as described above is executed by the controller 81, so that the pressure in the hydraulic chamber 78 and the pipe line 83 can be kept substantially constant.

Returning to FIG. 5, a hydraulic circuit for driving the hydraulic cylinder 75 will be described next.
The second switching valve 90 is a switching valve for controlling the expansion / contraction direction and expansion / contraction amount of the hydraulic cylinder 75. That is, in the set adjustment of the fixed teeth 71 and the moving teeth 72, for example, when the gap is reduced, the second switching valve 90 is switched to the extended position 90A by the command signal from the controller 81, and the third switching valve 91 is used. Is switched to the communication position 91A, the fourth switching valve 92 is switched to the cutoff position 92A, and the pressure oil discharged from the second hydraulic pump 93 is connected to the communication position 91A of the third switching valve 91 and the extended position 90A of the second switching valve 90. Through the pipe 95 and led to the head side hydraulic chamber (not shown) of the hydraulic cylinder 75. Thereby, the hydraulic cylinder 75 is extended, and the moving tooth 72 moves in the direction of the fixed tooth, so that the gap between the fixed tooth 71 and the moving tooth 72 is reduced.

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

  Further, at the time of crushing work, the command signal from the controller 81 to the second switching valve 90 is turned OFF, the second switching valve 90 is returned to the neutral position 90C by the biasing force of the spring, and the third switching valve 91 is moved to the cutoff position 91B. In addition, the fourth switching valve 92 is returned to the communication position 92B, and the pressure in the rod side hydraulic chamber, the pipe 96 and the pipe 97 connected to the pipe 96 via the communication position 92B of the fourth switching valve 92 is increased. Oil is enclosed (state shown in FIG. 5). Between the pipe 97 and the tank 84, there are provided an on-off valve 98 capable of arbitrarily releasing the sealed pressure, and a relief valve 99 for setting a relief pressure in the rod side hydraulic chamber and the pipes 96, 97. ing. Further, the accumulator 100, the rod side hydraulic chamber, and a pressure sensor 101 for detecting the pressure in the ducts 96 and 97 are provided in the duct 97. The pressure value detected by the pressure sensor 101 is output to the controller 81 in the same manner as the pressure sensor 88, and is the same as the pressure constant holding control in the hydraulic chamber 78 and the pipe 83 described above. Thus, the pressure in the rod side hydraulic chamber and the pipes 96 and 97 is also kept substantially constant by the controller 81. Since this control is the same as the flowchart shown in FIG.

  In the above, the slide member 66 and the brake plate 67 constitute a slide member provided on the support member described in the claims so as to be slidable in a predetermined direction, and the friction plate 68 and the brake piston 69 are provided. Constitutes a first pressing means for applying a pressing force from a direction perpendicular to the sliding direction of the sliding member described in the claims.

Next, operation | movement of one Embodiment of the self-propelled crusher of this invention of the said structure and its overload protection apparatus is demonstrated below.
Before the crushing operation is performed, in order to obtain a crushed material having a desired particle size, first, clearance adjustment (set adjustment) between the fixed tooth 71 and the moving tooth 72 is performed. First, as shown in FIG. 7, the first switching valve 80 is switched to the unlock position 80B by a command signal from the controller 81, and the pressing force of the friction plate 68 against the brake plate 67 by the brake piston 69 is released. As a result, the sliding member 66 is unlocked.

  In this state, set adjustment is performed. For example, when reducing the gap, as shown in FIG. 8, the second switching valve 90 is switched to the extended position 90A by the command signal from the controller 81, and the third switching valve 91 is moved to the communication position 91A. The switching valve 92 is switched to the cutoff position 92 </ b> A, and the pressure oil from the second hydraulic pump 93 is guided to the head side hydraulic chamber of the hydraulic cylinder 75 through the pipe line 95. As a result, the hydraulic cylinder 75 extends, the moving tooth 72 moves in the direction of the fixed tooth (the arrow direction in FIG. 8), and the gap between the fixed tooth 71 and the moving tooth 72 becomes smaller. At this time, since the toggle plate 70, the sliding member 66, and the brake plate 67 are urged toward the moving tooth 72 by the air cylinder 76 as described above, the moving tooth 72 is moved in the fixed tooth direction in this way. In this case, the toggle plate 70 is prevented from falling off.

  On the other hand, when the gap is increased, for example, as shown in FIG. 9, the second switching valve 90 is switched to the contracted position 90B by a command signal from the controller 81 (the third switching valve 91 and the fourth switching valve 92). Is a switching position similar to that described above), the pressure oil from the second hydraulic pump 93 is guided to the rod side hydraulic chamber (not shown) of the hydraulic cylinder 75 through the pipe 96. As a result, the hydraulic cylinder 75 is shortened, the moving tooth 72 is moved in the direction opposite to the fixed tooth (in the direction of the arrow in FIG. 9), and the gap between the fixed tooth 71 and the moving tooth 72 is increased.

  When the set adjustment is thus completed, the first switching valve 80 is then switched to the lock position 80A by a command signal from the controller 81, and the pressure oil from the first hydraulic pump 82 is hydraulically supplied via the pipe 83. Guided to chamber 78. Thereby, the brake piston 69 presses the friction plate 68 against the brake plate 67, and the sliding operation of the sliding member 66 is locked. Then, as shown in FIG. 5, the command signal from the controller 81 is turned OFF, the first switching valve 80 is returned to the neutral position 80 </ b> C, and the pressure oil in the hydraulic chamber 78 and the conduit 83 is moved to the sliding member 66. Is sealed with the pressure at the time of locking (that is, the set pressure Po).

  Further, as shown in FIG. 5, the command signal from the controller 81 to the second switching valve 90 is turned OFF, the second switching valve 90 is switched to the neutral position 90C, and the third switching valve 91 and the fourth switching valve 92 are switched. The command signal to is also turned OFF, and each is returned to the blocking position 91B and the communication position 92B, and the pressure oil in the rod side hydraulic chamber and the pipes 96 and 97 is sealed at an appropriate pressure. As a result, a force to shorten the hydraulic cylinder 75 acts, and the moving tooth 72 and the support member 64 are urged toward each other with an appropriate compressive load.

  In such a state, a crushing operation is performed. That is, when an object to be crushed is input to the hopper 12 by a hydraulic excavator or the like, the input object to be crushed is introduced into the grizzly feeder 15 and conveyed toward the crushing device 20 by vibration. At that time, fine particles (slipping etc.) smaller than the gaps between the comb teeth 16 of the grizzly river 17 are guided to the discharge conveyor 40 through the discharge conveyor chute 14 from the gaps, and a larger object ( Large block) is conveyed to the crushing device 20. The object to be crushed introduced into the crushing device 20 is crushed into a predetermined particle size corresponding to the exit gap between the fixed tooth 71 and the moving tooth 72 and introduced onto the lower discharge conveyor 40. The crushed material guided onto the discharge conveyor 40 is combined with the fine particles selected by the grizzly feeder 15 and guided through the discharge conveyor chute 14 and conveyed forward (right side in FIG. 1). The machine 55 adsorbs and removes foreign matter such as reinforcing bars and then discharges it outside the machine.

  During the crushing operation, the crushing reaction force that the moving tooth 72 receives from the object to be crushed is transmitted to the sliding member 66 via the toggle plate 70. At this time, in the case of a normal load, the transmitted reaction force is received by the sliding member 66 whose sliding operation is locked by the pressing force of the piston 69. On the other hand, when an overload occurs due to, for example, foreign matter biting in the crushing chamber 63 and an excessive load is applied to the sliding member 66, the braking plate 67 of the sliding member 66 is subjected to a frictional force with the friction plate 68. The sliding member 66 slides to the front side. Thereby, the moving tooth 72 moves to the front side via the toggle plate 70 and retracts from the fixed tooth 71, and the overload is eliminated. As described above, since the frictional force generated between the brake plate 67 and the friction plate 68 is set to a value smaller than the buckling load of the toggle plate 70, even if an overload occurs in this way, the toggle force is set. Members such as the plate 70 can be protected from damage.

  While the crushing operation is performed as described above, for example, when the pressure in the hydraulic chamber 78 and the pipe 83 is decreased due to leakage of the hydraulic oil sealed in the hydraulic chamber 78 and the pipe 83, for example, The pressure drop is detected by the pressure sensor 88, the first hydraulic pump 82 is driven by the control of the controller 81, the first switching valve 80 is switched to the lock position 80A, and the pressure in the hydraulic chamber 78 and the pipe 83 is changed. The pressure is increased to the set pressure Po. Then, the first switching valve 80 is returned to the neutral position 80C, and the pressure oil raised to the set pressure Po is sealed again.

  According to the present embodiment described above, the following various effects can be obtained. Hereinafter, each item will be described.

(1) Long-term stabilization of overload protection of the crushing device According to this embodiment, the pressure oil supplied to the hydraulic chamber 78 can be automatically controlled to a substantially constant pressure as described above. The pressing force of the friction plate 68 against the brake plate 67 by the brake piston 69 can be kept substantially constant for a long time. As a result, even if overload occurs repeatedly and the sliding member 66 slides against the frictional force many times, the frictional force acting between the braking plate 67 and the frictional plate 68 is reduced. It can be held almost constant. As a result, since the load applied when the moving tooth 72 is retracted from the fixed tooth 71 can be made substantially constant without variation, the overload protection of the crushing device 20 can be stably performed over a long period of time.

(2) Improvement in accuracy of set friction force In this embodiment, the pressure sensor 88 detects the pressure in the hydraulic chamber 78 and the pipe 83 as described above, and the controller 81 detects the pressure in the hydraulic chamber 78 and the pipe according to the detected pressure. Since the pressure in the passage 83 is controlled to be constant, the holding pressure can be set with high accuracy. As a result, it is possible to set the pressing force by the brake piston 69 with high accuracy, so that the frictional force acting between the brake plate 67 and the friction plate 68 can be set with high accuracy.

(3) Miniaturization of the overload protection device In the present embodiment, the brake plate 67 is pressed using the brake piston 69 with a small stroke, so that the brake plate 67 is pressed using a cylinder or the like, for example. Thus, the dimension in the stroke direction (the vertical dimension in this embodiment) can be greatly reduced. Therefore, the overload protection device 79 can be reduced in size.

(4) Reduction of maintenance work and cost reduction effect For example, the structure of the prior art that receives a load from the moving tooth side using a lock cylinder that receives a load in the axial direction by a mechanical frictional force. In the case of the jaw crusher, when the frictional force acting between the cylinder and the rod (or piston) decreases due to deterioration or the like, it is necessary to replace the lock cylinder together. Since this lock cylinder is generally large in size and high in cost, the replacement work takes time and cost.

  On the other hand, according to this embodiment, the brake plate 67 is sandwiched between the friction plates 69 to brake the sliding member 66. Therefore, the friction plate 69 is mainly deteriorated due to wear or the like. Sometimes it is mainly necessary to replace the friction plate 69. Therefore, the labor for the replacement work is reduced, and the cost can be greatly reduced.

(5) Increase effect of set adjustment allowance between fixed tooth and moving tooth In this embodiment, a hydraulic cylinder 75 is used as a biasing means for biasing the moving tooth 72 and the support member 64 in the approaching direction. The cylinder 75 is used to adjust the set. As a result, for example, a tension mechanism having a spring structure is used as the biasing means, and the crushing apparatus can be made smaller and smaller as compared with a structure in which a separate cylinder for setting adjustment is provided. Cost reduction can be achieved. Further, for example, in the structure of the present embodiment, the stroke of the hydraulic cylinder 75 becomes the set adjustment allowance between the fixed tooth 71 and the moving tooth 72 as compared with the structure in which the moving tooth is moved through the toggle plate by the set adjusting cylinder. Therefore, the set adjustment allowance can be expanded.

  In the above embodiment, the brake piston 69 driven by hydraulic pressure is used as the pressing means for pressing the friction plate 68 against the brake plate 67. However, the present invention is not limited to this, and a hydraulic cylinder may be used. A manual jack or the like that is manually operated may be used. That is, any material that can press the friction plate 68 with a substantially constant load over the long term may be used.

  Moreover, in the above embodiment, although the drive source of the hydraulic pumps 82 and 93 is a motor, it is not limited to this, and it may be configured to drive using the driving force of the engine of the self-propelled crusher.

It is a side view showing the whole structure of one embodiment of the self-propelled crusher of the present invention. It is a top view showing the whole structure of one Embodiment of the self-propelled crusher of this invention. It is a front view showing the whole structure of one embodiment of the self-propelled crusher of the present invention. It is a side view which shows the internal structure of the crushing apparatus mounted in one Embodiment of the self-propelled crusher of this invention in a partial cross section. It is a hydraulic circuit diagram which extracts and shows the part concerning the drive of a brake piston and a hydraulic cylinder among the hydraulic drive units with which one embodiment of the self-propelled crusher of the present invention is equipped. It is a flowchart showing the control content regarding the pressure chamber holding | maintenance control performed by the controller with which one embodiment of the self-propelled crusher of this invention is performed. FIG. 3 is a hydraulic circuit diagram of a portion related to driving of a brake piston and a hydraulic cylinder in a state in which the lock of the slide member is released. FIG. 5 is a hydraulic circuit diagram of a portion related to driving of a brake piston and a hydraulic cylinder when a gap between a fixed tooth and a moving tooth is reduced. FIG. 4 is a hydraulic circuit diagram of a portion related to driving of a brake piston and a hydraulic cylinder when a gap between a fixed tooth and a moving tooth is increased.

Explanation of symbols

1 Traveling body (traveling means)
3 Main body frame 12 Hopper 20 Crushing device 40 Discharge conveyor 61 Crushing device frame 62 Eccentric shaft 64 Support member 66 Slide member (slide member)
67 Brake plate (brake part, slide member)
68 Friction plate (friction member, first pressing means)
69 Brake piston (piston device, first pressing means)
70 Toggle plate 71 Fixed tooth 72 Moving tooth 75 Hydraulic cylinder (biasing means)
76 Air cylinder (second pressing means)
79 Overload protection device 81 Controller (control means)

Claims (7)

Body frame,
Traveling means provided on the main body frame;
A hopper provided on the main body frame for receiving an object to be crushed;
A crushing device frame provided on the main body frame, a fixed tooth fixed to the crushing device frame, a moving tooth which is disposed opposite to the fixed tooth and is supported by the crushing device frame so as to be swingable by an eccentric shaft; A support member fixed to the front side of the moving tooth in the crushing device frame, a slide member provided so as to be slidable in a predetermined direction in a space formed by the support member, and a friction member at the tip; First pressing means for applying a pressing force from a direction perpendicular to the sliding direction of the slide member so as to hold the slide member, and is sandwiched between the slide member and the lower end portion of the moving tooth A crushing device that crushes a to-be-crushed object received by the hopper, having a toggle plate, and a biasing means that biases the moving tooth and the support member in a proximity direction;
A self-propelled crusher comprising a discharge conveyor for conveying the crushed material crushed by the crushing apparatus to the outside of the apparatus.   2. The self-propelled crusher according to claim 1, wherein the first pressing unit includes a piston device that drives the piston by hydraulic pressure to apply a pressing force to the friction member.   The self-propelled crusher according to claim 2, further comprising control means for controlling the pressure oil for driving the piston device to be maintained at a substantially constant pressure.   4. The self-propelled crusher according to claim 3, wherein the slide member has a braking portion for stopping the sliding, and the friction member and the piston device are arranged on both sides of the braking portion, respectively. .   The self-propelled crusher according to any one of claims 1 to 4, wherein the biasing means is a hydraulic cylinder.   6. The self-propelled crusher according to claim 5, further comprising second pressing means for pressing the slide member and the toggle plate toward the moving tooth side. In an overload protection device for a self-propelled crusher that swings a moving tooth with respect to a fixed tooth and eliminates an overload of a crushing device that introduces a material to be crushed between them to protect the member. ,
A support member fixed to the front side of the moving tooth in the crushing device frame of the crushing device;
A slide member provided so as to be slidable in a predetermined direction in the space formed by the support member;
A first pressing means having a friction member at a tip, and applying a pressing force from a direction perpendicular to the sliding direction of the slide member so as to sandwich the slide member;
An overload protection device for a self-propelled crusher, comprising a toggle plate sandwiched between the slide member and a lower end portion of the moving tooth.

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