JPS6156072B2 - - Google Patents

Description

[Detailed description of the invention] [Technical field of invention] The present invention relates to a rock crusher.

[Technical background of the invention]

The inventor of the present invention disclosed the invention on which the present invention is based in Japanese Patent Application Laid-Open No. 112782/1982.

The previously disclosed invention provides a holder on an earthmoving vehicle via a vertical movement mechanism, and this holder fits and holds the cylindrical body of a rock crushing device so that it can move forward and backward, and this rock crushing device generates a blow inside the main body casing. In addition to having a built-in mechanism, the cylindrical body is integrally protruded from the main casing, and an intermediate shaft and a crushing blade located at the front of the cylindrical body are fitted inside the cylindrical body so that they can move forward and backward within a certain range. , an intermediary body coaxially opposed to the rear end of the intermediate shaft and selectively interposed at a hammering position where the hammer is struck by a hammer rotated by the central rotating shaft of the impact generating mechanism in the main body casing; The holder is movable from a hammering position coaxial with the holder to a non-hammering position on the side thereof, and between the holder and the cylindrical body there is a mechanism for moving the cylindrical body toward the main body casing side of the rock crushing device. This invention relates to a rock crusher having a structure equipped with a spring that resists.

In this way, the previous invention presses the crushing blade inside the cylinder against the rock by compressing the spring between the cylinder and the holder that is towed by an earthmoving vehicle. When the crimping becomes strong, that is, when the traction load increases, the intermediate body is moved from the non-hammering position to the hammering position, the intermediate body is struck by a rotating hammer, and the impact is transmitted to the crushing blade through the intermediate shaft. I have to.

[Problems with background technology]

However, in the earlier invention, the operation of moving the intermediary body to the hammering position is performed by the operator of the earthmoving vehicle who intuitively determines the magnitude of the traction load and moves a manual lever.
Such manual operation places a burden on the operator and poses a risk that the intermediary body may be struck by a hammer even though the traction load is low. In other words, it is necessary to judge whether the traction load is high enough to cause hammering.
It is often difficult to judge whether or not the rock has been fractured enough to stop hammering. Conventionally, hammering was started at a low traction load, or hammering was stopped after rock fragmentation. It is difficult to stop the crushing blade quickly, and the burden on the operator is also heavy, resulting in the crushing blade often making unnecessary idle strikes.

[Purpose of the invention]

The present invention automatically moves the intermediary body to the hammering position when the crushing blade is pressed against the rock with a certain strong force, performs continuous hammering until the rock is cracked, and automatically The intermediate member is then moved to a non-hammering position to prevent blank firing.

[Summary of the invention]

In the rock crusher of the present invention, a holder is provided on an earthwork vehicle via a vertical movement mechanism, and the holder fits and holds the cylindrical body of the rock crusher so that it can move forward and backward. In addition to having a built-in generating mechanism, the above-mentioned cylindrical body is integrally protruded from the main casing, and an intermediate shaft and a crushing blade located at the tip thereof are fitted inside this cylindrical body so as to be able to move forward and backward within a certain range. , an intermediary body coaxially opposed to the rear end of the intermediate shaft and selectively interposed at a hammering position where the hammer is struck by a hammer rotated by the central rotating shaft of the impact generating mechanism in the main casing; The holder is movable from a hammering position coaxial with the holder to a non-hammering position on the side thereof, and between the holder and the cylindrical body, there is a mechanism for moving the cylindrical body toward the main body casing side of the rock crushing device. A cam body is interlocked with the central rotating shaft, and a variable cam groove is provided inside the cam groove provided endlessly in the cam body to change a part of the path of the cam groove. Make your body move freely,
A support member is provided protruding from the main body casing of the rock crushing device onto the outer surface of the holder, a crimp force detector is movably provided on the support member, and the cam groove variable body is connected to the crimp force detector via an interlocking mechanism. The cam groove variable body is supported by a support member protruding from the holder and pushed against the return force to move the cam groove variable body to the non-hammering position of the intermediary body. The detection body pushing body, which moves from the corresponding position to the position corresponding to the hammering position of the intermediary body, is opposed to each other with a play interval, and a part of the path of the cam body is changed by the cam groove variable body. This configuration is characterized in that a cam follower is fitted into a cam groove, and the intermediary body is connected to a movable member that supports the cam follower via an interlocking mechanism, and the spring is then activated by the force of the earthmoving vehicle. When the crushing blade is compressed by a certain amount and presses against the rock with a certain strong force, the detection body pushing body integrated with the holder that compresses the spring pushes the pressure detection body, and this pressure detection body and The interlocking cam groove variable body is moved to a position corresponding to the hammering position, and the intermediary body is automatically moved to the hammering position via the interlocking mechanism by the cam follower that fits into the partially changed cam groove. Then, the rock is continuously pounded until it cracks, and at the moment when the rock breaks, a pressing force detector movably attached to a supporting member integral with the main casing of the rock crushing device is moved by a spring. The cam follower is released from the detector pusher on the holder side and returned to its original position, and the cam groove variable body interlocked with this detector is moved to a position corresponding to the non-hammering position, and the cam follower is fitted into the cam groove thus returned. The intermediate body is automatically returned to the non-hammering position via the interlocking mechanism, and the hammering is automatically stopped to prevent dry hammering.

[Embodiments of the invention]

Hereinafter, the present invention will be explained in detail with reference to embodiments shown in the drawings.

As shown in FIG. 1, a vertical movement mechanism of a parallel link mechanism type, which is usually equipped with an excavating device such as a ripper, is mounted on a pair of left and right mounting boards 2 provided on the rear frame of a tracked tractor 1 as an earthmoving vehicle. 3, a rectangular holder 4 for holding the rock crushing device is attached. The vertical movement mechanism 3 includes a pair of left and right lower arms 5, a pair of left and right tilt cylinders 6 for adjusting the working angle of a rock crushing device 31, which will be described later, and a pair of left and right lift cylinders 7 for vertical movement. Two sets of support plates 8 are pivotally supported, and the holder 4 is supported by these support plates 8.

Further, as shown in FIG. 2, the main body casing 33 of the rock crushing device 31 is connected to the central rectangular tube portion 9 of the holder 4 via a box-shaped slide bearing 11.
A cylindrical body 12 integral with the cylindrical body 12 is fitted so as to be movable forward and backward. The cylindrical body 12 includes a square cylindrical part 13, an outer cylindrical part 15 integrally fixed to the square cylindrical part 13, and an inner cylindrical part fitted into the outer cylindrical part 15 and integrally fixed by a taper pin 16. It is integrally formed by the square tube portion 17 and the square tube portion 18 that is fitted into the tip of the square tube portion 13 and fixed by welding or the like.

Further, a spring receiving member 21 is fitted and fixed to the rectangular tube portion 13 of the cylindrical body 12, and spring fitting tubes 22 are provided on both sides of the spring receiving member 21, and the opposite side is provided in the both side recesses 23 of the holder 4. A pair of large coil springs 25 are installed between the spring fitting tubes 22 and 24 on both sides of the spring fitting tube 24 (this is shown in FIG. 1). Therefore, the cylindrical body 12 of the rock crushing device 31 is urged diagonally downward.

The box-shaped slide bearing 11 has a large number of long rollers and corner members arranged alternately, the corner members are held down by outer and inner plate members, and holes are formed in the plate members on both sides. The outer and inner parts of the roller are rotatably protruded from the elongated hole,
Furthermore, a planar bearing assembly is formed by fixing the outer and inner plate members and each corner member with bolts and nuts,
And this flat bearing assembly is 4
Prepare 4 bearing assemblies for each bearing assembly.
It is formed into a square box shape with book connecting corner members interposed therebetween. Also, one end of a rod 61 is connected to one end face of each of the connecting corner members at the four corners, and the other end of the rod 61 can move freely into and out of a hole in a spring receiving piece 62 attached to the outer surface of the cylinder 12. In addition, one end surface of the slide bearing 11 and the spring receiving piece 62 are inserted into this rod 61.
A small coil spring 63 located between the two is installed. The small coil spring 63 elastically supports the box-shaped slide bearing 11 with a repulsive force that is balanced with the weight of the slide bearing 11, and functions to prevent the slide bearing 11 from falling off.

Further, as shown in FIG. 2, the cylindrical body 1
The crushing blade 26 is fitted into the lower part of the cylindrical tip 2, that is, inside the rectangular tube portion 18 so as to be able to move forward and backward, and the locking portion 30a of the rectangular tube portion 18
is loosely fitted in the elongated hole 30b of the crushing blade 26 in the axial direction, and the intermediate shaft 27 is inserted into the inner cylindrical portion 17 within a range where the protrusion 28 of the intermediate shaft 27 fits into the recess 29 of the inner cylindrical portion 17. It fits freely in the direction of movement.
Furthermore, the base 32 of the main body casing 33 of the rock crushing device 31 is attached to the upper part of the outer cylindrical part 15 of the cylinder 12.
Attach by welding etc.

Main body casing 33 of this rock crushing device 31
is the crushing blade 2 via the intermediate shaft 27.
As shown in FIG. 2, the main body casing 33
A bearing part 36 is provided on the inner surface of the front side part of the support part 38.
The upper end of a support part 38b is rotatably attached to the lower end of the support part 38b via a shaft 38a, and this support part 38b
The intermediate body 41 is fixedly held by the holding part 39 integrally provided at the lower end of the support part 38b. The supporting portion 38 is biased in a direction away from the shaft 27 and is also supported by a locking portion 43 fixed to the bottom of the casing 33.
A holding part 39 integrated with b is locked in a fixed position, and the impact generating mechanism inside the main body casing 33 has a rotating shaft 44 disposed in the center of the main casing 33, and a pair of rotating plates attached to this rotating shaft 44. 45, a hammer 47 is rotatably attached to the mounting shaft 46 on one side of the rotating plate 45, and a balancing weight 49 is rotatably attached to the mounting shaft 48 on the other side. A weight 50 is integrally provided on the side of the hammer 47. In addition, a plurality of large diameter pulleys 51 are integrally provided at one end of the rotating shaft 44, and a hydraulic motor 53 is mounted on the upper surface of the main body casing 33 via a mounting base 52.
A drive shaft 55 driven by a hydraulic motor 53 is rotatably provided on the bearing member 54, and a plurality of small diameter pulleys 5 are mounted on the drive shaft 55.
6 and a flywheel 57 are integrally provided, and a V-belt 58 is wound around the small diameter pulley 56 and the large diameter pulley 51.

The lift cylinder 7, the tilt cylinder 6, and the hydraulic motor 53 in FIG. 1 receive hydraulic pressure from a hydraulic power source built in the tractor 1 through valves.

Furthermore, as shown in FIG.
A central rotary shaft 44 of the impact generating mechanism is made to protrude to the outside, and a reduction gear mechanism and a cam mechanism are provided in this protruding portion.

That is, a first small-diameter gear 66 is integrally fitted to the rotating shaft 44, and a second large-diameter gear is rotatably supported on the small-diameter gear 66 by a gear casing 67 that is integrated with the main body casing 33. A third small-diameter gear 70 meshes with the large-diameter gear 68 and rotates integrally through the shaft 69, and a third small-diameter gear 70 is rotatably connected to the rotation shaft 44 through a cam base cylinder portion to be described next. The fitted fourth large diameter gear 71 is engaged. gear 66, 68
The gear ratio is 1/3, and the gear ratio of gears 70 and 71 is also 1/3, so the gear ratio of gears 66 and 71 is 1/9 reduction.

Further, as shown in FIGS. 3 and 4, the large-diameter gear 71 is connected to the outer circumferential surface of one end of a cam base cylinder portion 73 that is rotatably fitted to the outer circumferential surface of the central rotating shaft 44 via a bearing 72. Further, a cam body 74 is provided on the outer peripheral surface of this cam base cylinder portion 73.

The cam body 74 has a flat disc 75 on one side directly fixed to the outer peripheral surface of the cam base cylinder part 73 by welding or the like, and a large number of support rods 76 in an annular arrangement integrally protruding from the flat disc 75. The disk 77 on the other side is supported via the cam groove 78. The disk 77 on the other side is provided spaced apart on the outer circumferential surface of the cam base portion 73 via an annular gap 79, and as shown by the dotted line in FIG. A two-stage notch 80 is provided in a part of 77, and this notch 80
An arcuate plate 81 which is curved in the same shape as the outer circumference of the disc 77 and bulges outward is fitted into the upper part, and a mounting plate 82 welded to both ends of this arcuate plate 81 is fitted. It is fixed to the outer surface of this disc 77 with four bolts 83, and an arc-shaped recess 84 is provided on the inner surface of the arc plate 81.

Further, as shown in FIGS. 3 to 5, a pair of guide protrusions 87 are fitted onto the outer surface of the cam base cylinder part 73, and the guide protrusions 87 are fitted along the guide protrusions 87 into the gap 7.
A cylindrical support member 88 that slides in the axial direction within the cam base cylinder 73 is fitted onto the outer peripheral surface of the cam base cylinder part 73, and a bolt 90 is attached to a part of the flange part 89 at one end of the cylindrical support member 88.
The plate-shaped support member 91 is fixed by the plate-shaped support member 91, and the arc-shaped recess is placed on the end of the plate-shaped support member 91 in the cam groove 78 via the intermediate support member 92, as shown in FIG. A cam groove variable body 93 is welded to the cam groove variable body 93, which is moon-shaped and has approximately the same shape as 84 (more precisely, the radius of curvature of the circular arc surface is slightly smaller), and whose side surface is circular as shown in FIG. Intermediate support member 92
is slidably fitted between a pair of guide protrusions 94 protruding from the flat disc 75 on one side, and the guide protrusions 94, together with the pair of guide protrusions 87, are connected to the variable cam groove body. 93 can be rotated integrally with the cam main body 74. Further, a coil spring 96 is fitted to the outer peripheral surface of the cylindrical support member 88 and the spring collar 95 from the flange portion 89 at one end of the cylindrical support member 88 to the flat disk 75 on one side. The support members 88, 91, and 92 are biased rightward in FIG. 4, and the cam groove variable body 93 is resiliently biased so as to fit into the arc-shaped recess 84. 97 is Natsuto. 98 is an arcuate surface of the cam groove variable body 93.

In addition, as shown in FIG. 2, the rock crushing device 3
A support member 101 is integrally protruded from the front surface of the main body casing 33 of 1 onto the upper surface of the holder 4, and a large coil spring 2 is inserted into the elongated hole of this support member 101.
The shaft support plate 102 whose movement was adjusted on site according to the compression state of No. 5 is fixed with screws 103, and this shaft support plate 102 is
The lower end of a crimp force detection lever 105 as a crimp force detection body is rotatably supported via a shaft 104, and integrally projects from the upper surface of the holder 4 with respect to the intermediate portion of the crimp force detection lever 105. A roller 107 as a detection body pushing body which is rotatably supported by a supporting member 106 provided therein and which pushes the pressing force detection lever 105 to move the cam groove variable body 93 is opposed to the roller 107 with a play interval 100 interposed therebetween. .

The cam groove variable body 93 is placed between the upper end of the pressing force detection lever 105 and the cam groove variable body 93 on the inner surface of the flat disc 75 on one side at a position corresponding to the hammering position of the intermediary body 41. An interlocking mechanism 108 is provided that moves in the axial direction from a position within the arcuate recess 84 of the disk 77 on the other side as a position corresponding to the non-hammering position of the intermediary body 41.
That is, as shown in FIG. 2, a pair of support members 109 are integrally provided to protrude from one side of the main body casing 33, and a pair of support members 109 are provided in a slightly inclined shape from the upper support member 109 as shown in FIG. Protruding shaft 1
10, two L-shaped levers 111, 112
and one shift fork lever 114 are rotatably fitted and supported, and this shift fork lever 1
L-shaped levers 111, 11 are attached to the outer surface of the proximal end of 14.
Pressing portions 115 and 116 integrally protruding from 2 are respectively exposed in a detachable manner, and one end of a turnbuckle 118 for length adjustment is connected to the upper L-shaped lever 111 via a wheel spring 117. One end of a rod 119 is rotatably connected to the other end of the turnbuckle 118 via a shaft, the other end of this rod 119 is rotatably connected to the upper end of the crimping force detection lever 105 through a shaft, and the shift fork As shown in FIG. 3, the upper and lower shift forks 120 integrally provided at the tip of the lever 114 are provided with elongated holes 121 in the axial direction of the lever 114, and the rotation shaft 44 is fitted into the upper and lower elongated holes 121. A pin shaft 123 protruding from the upper and lower parts of the combined ring-shaped shift member 122 is fitted to be slidable and rotatable along the elongated hole 121, and this ring-shaped shift member 122 is attached to the rotating shaft 44. The cylindrical member 124 that directly contacts the flange portion 89 of the cylindrical support member 88 is rotatably and slidably fitted in the axial direction, and the cylindrical member 124 rotates together with the cylindrical support member 88 and the shift member that does not rotate. 122
A thrust bearing or the like is installed on the sliding surface. In this way, the interlocking mechanism 108 of the lever 105 is provided. The shift fork lever 114 is automatically returned to its original position by the coil spring 96, and the lever 111 is completely returned to its original position by a spring 125 provided between it and the gear casing 67. Further, the lower L-shaped lever 112 is a manual lever, and is rotated when the operator of the tractor 1 wants to arbitrarily move the intermediary body 41, such as when performing undermining.

Further, as shown in FIGS. 2, 6, and 7, the pair of support members 1 are fixed to one side of the main body casing 33 with four bolts 128.
09, two guide rods 1 as guide means are installed parallel to the rotation shaft 44 through the support plate 129.
30 is fixedly supported, and these two guide rods 13
0, both sides of a slider 131 as a movable member that supports the cam follower are slidably fitted, and a convex portion 132 is integrally inserted from the center of the slider 131.
A roller shaft 133 is rotatably fitted via a bearing into a round hole passing through the protrusion 132 from the slider body, and is formed integrally with the roller shaft 133 and protrudes from the upper surface of the protrusion 132. The roller 134 as a cam follower is fitted into the cam groove 78. This roller 134 is in line contact with the cam groove 78 on both sides. Also, the slider 131 has an interlocking mechanism 1.
The intermediary body 41 is connected via 35. That is, as shown in FIG. 6 and FIG.
One end of a link 138 is rotatably connected to 36 via a shaft 137, and the other end of this link 138 is connected to the shaft 1.
39, one end of a width increasing lever 140 is rotatably connected, and this width increasing lever 140 has a boss portion 141 located on the shaft 139 side rotatably connected between the pair of support members 109 by a shaft 142. One end of a rod 144 is rotatably connected to the other end of the width increasing lever 140 via a shaft 143, and as shown in FIG.
The holding portion 39 of the intermediary body 41 is connected via the link 5.
As shown in FIG. 6, the link 138 is formed by fixing two pieces in parallel via a support part 146.

Further, as shown in FIG. 2, a cam safety plate 151 is provided projecting from the lower support member 109 in parallel to the discs 75 and 77. This cam safety plate 151 is
It is provided in an arc shape along the lower surface of the cylindrical member 124 over a range of approximately 180° in the direction opposite to the rotational direction of the cam body 74 from a position approximately in the same phase as the roller 134 with respect to the rotating shaft 44. It becomes. Furthermore, as shown in FIGS. 2, 3, and 4, a mounting plate 152 is fixed to the outer end of the plate-shaped support member 91 of the variable cam groove body 93 with bolts 153, and A mounting plate 154 is fixed in the right angle direction with bolts 155, and a locking body 156 is fixed to the upper surface of the tip of the mounting plate 154. This locking body 156 is provided with sloped surface portions 157 on both sides on the advancing side, and locking surface portions 158 are provided on both sides of the rear thereof. The tip of the cam safety plate 151 is also provided with inclined surface portions 159 on both sides.

Next, the operation of this embodiment will be explained.

First, even if the hydraulic motor 53 is driven, the rotating shaft 44 is rotated, and the hammer 47 etc. are rotated, the crushing blade 2
When no load is applied to the tip of the roller 6 or the load is small, the roller 107 and the pressure detection lever 105 are separated by the clearance 100, so the pressure detection lever 105 has a rod 119, No force acts on the shift fork lever 114 connected via the L-shaped lever 111 etc.
Therefore, the cam groove variable body 93 is fitted by the coil spring 96 into a position within the arcuate recess 84 of the disc 77, which corresponds to the non-hammering position of the intermediary body 41, and the cam groove 78 is Cam body 7
4. There is no fluctuation in the axial direction over the entire circumference. Therefore, the roller 134 fitted in this cam groove 78 and the slider 131 supporting this roller 134 do not move in the axial direction, and the interlocking mechanism 1 is attached to the slider 131.
The intermediary body 41 connected through the intermediate shaft 27 is moved out of the coaxial position of the rear end of the intermediate shaft 27 and out of the rotation locus of the hammer 47, and is in a non-hammering position where it is not interfered with by the hammer 47 (see FIG. 2). ), the hammer 47 only rotates idly, and hammering is not performed automatically.

Next, in order to perform hammering automatically,
The tractor 1 is moved forward strongly, and the traction force causes the holder 4 to move against the crushing blade 26 that is locked to the rock G and the cylindrical body 12 that is locked to this crushing blade 26.
is strongly pulled diagonally downward, and the large coil spring 25 with a large repulsive force is sufficiently compressed. In order to exert the most effective crushing force during hammering, the crushing blade 26 must be inserted into a crack in the rock G, or pebbles, gravel, etc. may be caught between the rock G and the crushing blade 26. , even if the large coil spring 25 is sufficiently compressed by the strong traction force of the tractor 1, the crushing blade 26 passes through the cylindrical body 12.
Press the crack into the crack with a strong force, or use the crushing blade 26
It is effective to use a strong force to clamp the gravel between the rock G and the rock G, and to hammer this crimped and integrated area with a hammer. For this purpose, when the large coil spring 25 is sufficiently compressed with a strong traction force, the roller 107 moves sufficiently more than the play interval 100, and the pressing force detection lever 105 is moved as shown in FIG.
The interlocking mechanism 108 is pushed as shown by the dotted chain line.
Pull the L-shaped lever 111 inside, and
Shift fork lever 1 by pressing part 115 of 1
14 against the coil spring 96 and linearly push the cylindrical support member 88 of the cam groove variable body 93 along the cam base cylinder part 73 via the ring-shaped shift member 122 and the cylindrical member 124. The cam groove variable body 93 is inserted into the flat disc 75 at a position corresponding to the hammering position of the intermediary body 41, as shown by the two-dot chain line in FIG.
move linearly to the medial surface position. As a result, the cam groove 78 is formed between the arcuate surface 98 of the cam groove variable body 93 and the arcuate recess 84 of the disc 77 on the other side of the cam body 74.
It passes through an arcuate path between. Therefore,
Each time the roller 134 passes between the arcuate surface 98 and the arcuate recess 84, the slider 131 has a roller 134 fitted into the cam groove 78.
The slide 131 reciprocates linearly in the right direction in FIG. 41 is moved to a hammering position where it coaxially faces the rear end of the intermediate shaft 27 and is located in the rotation locus of the hammer 47 and receives the impact action of the hammer 47. The force is applied to the crushing blade 26 via the intermediate shaft 27,
Crush bedrock G. Note that the rotation of the rotating shaft 44 is as follows:
Since the rotation of the cam body 74 and the cam groove variable body 93 is reduced to 1/9 by the gears 66, 68, 70, and 71, the intermediate body 41 rotates once every nine rotations of the hammer 47. The hammer is moved to the above-mentioned hammering position and hammering is performed.

This hammering continues automatically until the rock G is cracked, and at the moment the rock G is cracked, the locking action on the tip of the crushing blade 26 is released, and the cylinder 12 is attached to the holder 4 using the coil spring. The lever 105 slides in the direction of the crushing blade 26 due to the restoring force of the lever 105 and is pivotally supported by a support member 101 that projects from the main body casing 33 that is integrated with the cylinder 12.
away from the roller 107 integral with the holder 4, and the second
As shown in the figure, the cam groove variable body 93 is returned to its original position by the coil spring 96 into the arcuate recess 84, and the roller 13 inside the cam groove 78 is returned to its original position.
4, and the intermediary body 41 is held in the non-hammering position via the interlocking mechanism 135. Therefore, when the rock G is cracked, hammering is automatically stopped, and empty hammering is prevented when the crushing blade 26 is not in close contact with the rock G. Note that the hammer 47 remains idle unless the hydraulic motor 53 is stopped.

In addition, the cam safety plate 151 and the locking body 156
is when the roller 13 is moved while the cam groove variable body 93 is switching.
This is to prevent the locking body 156 from colliding with the cam groove variable body 93, and as the cam groove variable body 93 rotates, the locking body 156 also rotates via the mounting plates 152, 154.
However, from the phase of the roller 134 with respect to the rotating shaft 44,
Approximately 180 degrees in front of you, on either side of the cam safety plate 151, there are inclined surface portions 157 at both tips.
The locking body 156 is forcibly prevented from moving in the axial direction until it reaches approximately the same phase as the roller 134, and the variable cam groove body rotates integrally with the locking body 156. 93 also cannot move in the axial direction,
When the cam groove variable body 93 rotates to the position of the roller 134, the cam groove variable body 93 is always in either a position inside the arc-shaped recess 84 or a position in close contact with the flat disc 75 on one side, It is not located in the middle, and there is no risk of collision with the roller 134.

For example, when the locking body 156 is engaged with the right side surface of the cam safety plate 151 in FIG. 3 and is sliding along this side surface, even if the lever 105 is pushed by the roller 107, the cam The variable groove body 93, the shift fork lever 114, and the L-shaped lever 111 do not operate, and the coil spring 117 only extends. This coil spring 117 is stronger than the coil spring 96 that returns the cam groove variable body 93, and is stronger than the coil spring 11 that returns the lever 111.
In the above case, the cam safety plate 151 is stronger than No.
Due to the elasticity accumulated in the coil spring 117, the moment the engaging body 156 comes off the cam safety plate 151, the cam groove variable body 93 moves into the arcuate recess 84.
From there, it is switched to the flat disc 75 side on the opposite side.

〔Effect of the invention〕

According to the present invention, the cam body is interlockably fitted to the central rotating shaft that rotates the hammer, and the cam changes a part of the path of the cam groove inside the cam groove provided endlessly in the cam body. A movable groove variable body is provided, a support member is provided protruding from the main body casing of the rock crushing device onto the outer surface of the holder, a pressure force detection body is movably provided on this support member, and an interlocking mechanism is attached to this pressure force detection body. The cam groove variable body is connected to the cam groove variable body through the cam groove variable body, and the cam groove variable body is supported by a support member protruding from the holder and pushes the crimping force detector against the return force. The detection body pushing body, which moves from a position corresponding to the non-hammering position of the intermediary body to a position corresponding to the hammering position of the intermediate body, is opposed to each other with a play interval, and the path is controlled by the cam groove variable body. The cam follower is fitted into the cam groove of the cam body, which is partially changed, and the intermediary body is connected to the movable member that supports the cam follower via an interlocking mechanism, so that it can be adjusted according to the increase or decrease of the load applied to the tip of the crushing blade. The cam groove variable body is automatically moved by the crimp force detection body that is automatically operated by the detection body pushing body.
The cam follower that fits into the cam groove changed by this cam groove variable body allows the intermediary body to be automatically selected and moved between the hammering position and the non-hammering position, and the crushing blade applies a constant strong force. When the rock is crimped, the intermediate body is automatically moved to the hammering position and continuous hammering is performed until the rock is cracked, and the moment the rock is cracked, the intermediate body is automatically moved to the non-hammering position. You can prevent blank firing.

[Brief explanation of the drawing]

Fig. 1 is a front view showing one embodiment of the rock crusher of the present invention, Fig. 2 is a cutaway perspective view of the rock crushing device, Fig. 3 is a plan view of the cam portion for moving the intermediary body, and Fig. 4 is a 3, FIG. 5 is a sectional view taken along the line --- in FIG. 3, FIG. 6 is a plan view of the slider portion, and FIG. 7 is a front view thereof. DESCRIPTION OF SYMBOLS 1... Tractor as an earthmoving vehicle, 3... Vertical movement mechanism, 4... Holder, 12... Cylindrical body, 25... Spring, 26... Crushing blade, 27... Intermediate shaft, 31... Rock crushing device , 33... Main body casing, 41... Intermediary body, 44... Rotating shaft, 47...
... Hammer, 74 ... Cam body, 78 ... Cam groove, 93 ... Cam groove variable body, 100 ... Play interval, 101 ... Support member, 105 ... Pressure force detection lever as a pressure force detection body, 106 ...Supporting member, 107...Roller as a detection body pushing body, 1
08... Interlocking mechanism, 131... Slider as a movable member, 134... Roller as a cam follower, 135... Interlocking mechanism.

Claims (1)

[Claims] 1. A holder is provided on the earthmoving vehicle via a vertical movement mechanism, and the holder fits and holds the cylindrical body of the rock crushing device so that it can move forward and backward, and this rock crushing device has a built-in impact generating mechanism in the main body casing,
The cylindrical body integrally protrudes from the main casing,
An intermediate shaft and a crushing blade located at the front end of the intermediate shaft are fitted inside this cylinder so that they can move forward and backward within a certain range. An intermediary body selectively interposed in a hammering position struck by a hammer rotated by a central rotating shaft is movable from a hammering position coaxial with the intermediate shaft to a non-hammering position lateral to the hammering position. A spring is provided between the holder and the cylindrical body to resist movement of the cylindrical body toward the main body casing of the rock crushing device, and the cam body is interlockably fitted to the central rotating shaft. A cam groove variable body that changes part of the path of the cam groove is movably provided inside the cam groove provided in an endless shape in the cam body, and a supporting member is attached from the main body casing of the rock crushing device to the outer surface of the holder. A crimp force detector is movably provided on the supporting member, and the cam groove variable body is linked to the crimp force detector via an interlocking mechanism, so that the crimp force detector protrudes from the holder. The cam groove variable body is moved from a position corresponding to the non-hammering position of the intermediary body to a position corresponding to the hammering position of the intermediary body by pushing the crimp force detection body supported by the provided support member against the restoring force. The detecting body and the pushing body that move are opposed to each other with a clearance between them,
A cam follower is fitted into a cam groove of a cam body whose path is partially changed by the cam groove variable body, and the intermediary body is connected to a movable member that supports the cam follower via an interlocking mechanism. Rock crusher.