JPS6142789Y2 - - Google Patents

Description

[Detailed explanation of the idea] [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 Unexamined Patent Publication No. 112782/1982.

The previously disclosed invention provides a holder on a civil engineering 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 thereof are fitted inside the 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 the hammering position rotated by the central rotating shaft of the impact generating mechanism in the main body casing and struck by the hammer is coaxially opposed to the intermediate shaft. The holder is movable from a hammering position to a non-hammering position on the side thereof, and there is a holder between the holder and the cylinder to resist movement of the cylinder towards the main body casing of the rock crushing device. This invention relates to a rock crusher having a structure equipped with a spring that

In this way, the previous invention presses the crushing blade inside the cylinder against the rock by compressing the spring between the holder and the cylinder, which is towed by a civil engineering vehicle, by the traction force. 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 via the intermediate shaft. That's what I do.

[Problems with background technology]

In such a rock crusher, the intermediary body may be moved manually to the hammering position, but a cam for moving the intermediary body is provided on the central rotating shaft of the impact generating mechanism, and this cam is used to move the intermediate body to the hammering position. Therefore, it is conceivable to move the intermediary body via an interlocking mechanism.

In this case, since it is not possible to install a large cam due to space constraints, the movement of the member directly driven by the cam is usually amplified by an interlocking mechanism and transmitted to the intermediary body. .

For this reason, if there is any play between the cam and the member directly driven by the cam, this play will appear as a large unnecessary runout at the intermediary body, for example when rotating a hammer. When an earthmoving vehicle makes a sharp turn while rotating, there is a risk that it will swing toward the hammering position and hit the hammer, causing sparks, even though there is no need for an intermediary body.

[Purpose of invention]

The present invention provides a concrete structure for a rock crusher that prevents play from occurring between a member directly operated by a cam for moving the intermediary body, and prevents malfunction of the intermediary body due to play. The purpose is to prevent.

[Summary of the idea]

The rock crusher of the present invention is provided with a holder on a civil engineering vehicle via a vertical movement mechanism, and this 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 provided with a spring to resist the above-mentioned central rotating shaft, and the cam body is interlocked with the central rotating shaft. The plate is integrally provided with a disc on the other side, which has an arcuate recess in a part of the inner surface on the opposite side facing the plate through a cam groove, and a cam base cylinder is provided inside the cam groove. The variable cam groove body, which has almost the same shape as the arc-shaped recess, is inserted into the hammering position of the intermediary body through a support member that is movably fitted only in the axial direction and moved by an external operating force. axially movable from the inner surface position of the flat disc on one side as a position corresponding to the non-hammering position of the intermediary body to the arcuate recess position of the other side disc as a position corresponding to the non-hammering position of the intermediary body. The cam is provided so as to be rotatable integrally with the cam body, and a guide means is provided on the side surface of the main body casing of the rock crushing device parallel to the rotating shaft via a support member, and a slide is slidably fitted into the kneading guide means, The structure is characterized in that a roller that fits into the cam groove is provided protruding from the slider, and the intermediate body is connected to the slider via an interlocking mechanism. The variable cam groove operates in parallel to the axial direction of the cam base fitted to the rotating shaft of the cam, and by the operation of this cam groove variable body, the roller in the cam groove and the slider integrated with the cam groove are moved parallel to the rotating shaft. The intermediary body is moved linearly along the guide means and via the interlocking mechanism.

[Example of idea]

Hereinafter, the present invention will be described 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 is usually equipped with an excavating device such as a ripper on a pair of left and right mounting boards 2 provided on the rear frame of a tracked tractor 1 as a civil engineering vehicle. A rectangular holder 4 for holding the rock crushing device is attached via 3. The vertical movement mechanism 3 has a pair of left and right lower arms 5, a pair of left and right tilt cylinders 6 for adjusting the working angle of the 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.

Moreover, as shown in FIG.
A cylindrical body 12 integral with the cylindrical body 12 is fitted so as to be movable forward and backward. This cylindrical body 12 includes a rectangular cylindrical portion 13, an outer cylindrical portion 15 integrally fixed to the rectangular cylindrical portion 13, and an inner cylindrical portion fitted into the outer cylindrical portion 15 and integrally fixed by a taper pin 16. It is integrally formed by the section 17 and a rectangular tube section 18 that is fitted into the tip of the rectangular tube section 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 bearings 11 are also arranged alternately with a large number of long rollers and corner members, and the corner members are held down by outer and inner plate members. The outer and inner parts of the roller are rotatably protruded from the 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 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 this 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 body 12. 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 cylindrical portion 18 so as to be able to move forward and backward _.
is loosely fitted in the elongated hole _30b of the crushing blade 26 in the axial direction, and the intermediate shaft 27 is fitted within the inner cylindrical portion 17, and the range where the convex portion 28 of the intermediate shaft 27 fits into the recess 29 of the inner cylindrical portion 17. It fits freely inside and out,
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, a bearing part 36 is provided on the inner surface of the front side of the main body casing 33.
The upper end of a support part 38 is pivotally attached to this bearing part 36 via a shaft 37 so as to be rotatable in the left-right direction, and the upper end of a support part 38 _b is attached to the lower end of this support part 38 through a shaft 38 _a in the front-rear direction. This support part 38 is rotatably attached to the shaft.
The intermediate body 41 is fixedly held by a holding part 39 integrally provided at the lower end of _b , and the lower end of a leaf spring 42 whose upper end is fixed to the supporting part 38 is used to hold the intermediate body 41 fixedly _. The support part 3 is urged in a direction away from the intermediate shaft 27, and is also
A holding part 39 integrated with _8b 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 shafts attached to this rotating shaft 44. A plate 45 is fixed, a hammer 47 is rotatably attached to the mounting shaft 46 on one side of the rotary plate 45, and a balancing weight 49 is rotatably attached to the attachment shaft 48 on the other side. A weight 50 is integrally provided on the side of the hammer 47. Furthermore, a plurality of large diameter pulleys 51 are integrally provided at one end of the rotating shaft 44, and a hydraulic motor 5 is mounted on the upper surface of the main body casing 33 via a mounting base 52.
3 and a bearing member 54, 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 56 and a flywheel 57 are integrally provided on the drive shaft 55. , a V-belt 58 is wound around the small diameter pulley 56 and the large diameter pulley 51.

The lift cylinder 7, tilt cylinder 6, and hydraulic motor 53 in FIG. 1 are supplied with 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 other side disk 77 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 above-mentioned arc-shaped plate 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 concave portion 84, which is moon-shaped and has an arcuate shape as shown in FIG. . The 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 and the pair of guide protrusions 87 This allows the cam groove variable body 93 to rotate integrally with the cam body 74. Also, the cylindrical support member 8
Flat disc 75 on one side from one end flange part 89 of 8
A coil spring 96 is fitted to the outer peripheral surface of the cylindrical support member 88 and the spring collar 95, and the coil spring 96 always urges the support members 88, 91, 92 to the right in FIG. The cam groove variable body 93 is elastically urged to fit into the arcuate 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 crimping force detection lever 103 is connected via the shaft 104.
The lower end of the holder 4 is rotatably supported, and a supporting member 106 integrally protrudes from the upper surface of the holder 4 is rotatably supported at the middle part of the crimping force detection lever 105 to detect the crimping force. A roller 107 serving as a lever pushing body that pushes the 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, an integral support member 109 is provided integrally projecting from one side of the main body casing 33, and a support member 109 on the upper side is provided in a slightly inclined shape 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 coil 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, an elongated hole 121 in the axial direction of the lever 114 is formed in the upper and lower shift forks 120 integrally provided at the tip of the lever 114.
A pin shaft 123 protruding from the upper and lower parts of the ring-shaped shift member 122 fitted to the rotating shaft 44 is fitted into the upper and lower elongated holes 121 so as to be slidable and rotatable along the elongated hole 121. The ring-shaped shift member 122 is rotatably and axially slidably fitted to the rotating shaft 44 together with the cylindrical member 124 that directly contacts the flange portion 89 of the cylindrical support member 88 . The cylindrical member 124 rotates together with the cylindrical support member 88 and the shift member 1 does not rotate.
A thrust bearing or the like is provided on the sliding surface with 22. 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 by four bolts 128.
09, the rotating shaft 44 is connected via the support plate 129.
Two guide rods 130 as guide means are fixedly supported in parallel with the guide rods 1.
30, both sides of a slider 131 as a movable member that supports the cam follower are slidably fitted,
A convex portion 13 is integrally formed from the center of this slider 131.
A roller shaft 133 is rotatably fitted via a bearing into a round hole passing through the convex portion 132 from the slider body, and is integrally formed with the roller shaft 133 and is formed on the upper surface of the convex portion 132. A roller 134 as a cam follower protruding from the cam groove 78 is fitted into the cam groove 78. This roller 134 has cam grooves 7 on both sides.
Line contact with 8. Further, the intermediate body 41 is connected to the slider 131 via an interlocking mechanism 135.
That is, as shown in FIGS. 6 and 7, a link 138 is attached to a protrusion piece 136 protruding from the side surface of the protrusion 132 of the slider 131 via a shaft 137.
One end of the link 138 is rotatably connected, and one end of a width increasing lever 140 is rotatably connected to the other end of the link 138 via a shaft 139. 141 is rotatably supported between the pair of support members 109 by a shaft 142, and one end of a rod 144 is rotatably connected to the other end of the width increasing lever 140 via a shaft 143.
As shown in FIG. 2, the holding portion 39 of the intermediary body 41 is connected to the other end of the rod 144 via a shaft 145. As shown in FIG. 6, the link 138 is formed by fixing two pieces in parallel via a support portion 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 use the crushing blade most effectively 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 2 passes through the cylindrical body 12.
6 to the above crack with strong force, or crushing blade 2
It is effective to press the gravel between 6 and the bedrock G into close contact with each other with a strong force, and then hammer the area that has been integrated into the crimped 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 beyond the play distance 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,
Ring-shaped shift member 122 and cylindrical member 124
When the cylindrical support member 88 of the cam groove variable body 93 is pushed linearly along the cam base cylinder portion 73 via As illustrated in FIG.
Move linearly to the inner surface position of 5. As a result, the cam groove 78 is connected to the arcuate surface 98 of the variable cam groove body 93.
and the arcuate recess 8 of the disc 77 on the other side of the cam body 74.
It passes through an arcuate path between 4 and 4. Therefore, each time the roller 134 passes between the arcuate surface 98 and the arcuate recess 84, the slider 131, which is formed by fitting the roller 134 into the cam groove 78, rotates in two directions parallel to the rotating shaft 44. Book guide rod 13
0 in the right direction in Figure 6,
Each time the slider 131 reciprocates in the right direction, the intermediary body 41 coaxially faces the rear end of the intermediate shaft 27 via the interlocking mechanism 135 and is positioned in the rotation locus of the hammer 47 so that the intermediary body 41
The rock G is moved to a hammering position where it is hit by the hammer 47, and the impact force is applied to the crushing blade 26 via the intermediate shaft 27 to crush the rock G. Note that the rotation of the rotating shaft 44 is reduced to 1/9 by the gears 66, 68, 70, and 71, and the rotation of the cam body 74 and the cam groove variable body 93 are reduced.
Therefore, every nine rotations of the hammer 47, the intermediary body 41 moves to the hammering position once, and hammering is performed.

This hammering is automatically continued 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.
The cylindrical body 12 is connected to the holder 4 by a coil spring 25.
slides in the direction of the crushing blade 26 due to the restoring force of
A lever 105 is pivotally supported by a support member 101 that projects from the main body casing 33 that is integral with the cylinder 12.
is separated from the roller 107 integral with the holder 4,
As shown in FIG. 2, the cam groove variable body 93 is returned to the original position by the coil spring 96 into the arcuate recess 84, the fluctuation of the roller 134 in the cam groove 78 is eliminated, and the interlocking mechanism 135 is activated. The intermediary body 41 is held in a non-hammering position. Therefore, when the rock mass G is cracked, hammering is automatically stopped, and dry hammering when the crushing blade 26 is not in close contact with the rock mass G is prevented. Note that the hydraulic motor 5
Unless 3 is stopped, the hammer 47 will continue to spin idly.

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 idea]

According to the present invention, the cam body, which is interlockably fitted to the central rotating shaft that rotates the hammer, has a flat disc on one side, and a cam base portion fitted to the outer peripheral surface of the central rotating shaft. A disk on the other side having an arc-shaped recess on a part of the inner surface on the opposite side facing this via the cam groove is integrally provided, and inside the cam groove,
A cam groove variable body having almost the same shape as the arc-shaped recess is inserted into the intermediary body through a support member that is fitted to the cam base cylinder so as to be movable only in the axial direction and is moved by an external operating force. axially from a position on the inner surface of the flat disc on one side as a position corresponding to the hammering position to a position inside the arcuate recess of the disc on the other side as a position corresponding to the non-hammering position of the intermediary body. Provided to be movable and rotatable integrally with the cam body, a guide means is provided on the side surface of the main body casing of the rock crushing device parallel to the rotation axis via a support member,
A slider is slidably fitted into this guide means,
A roller that fits into the cam groove is protruded from this slider, and the intermediate body is connected to the slider via an interlocking mechanism, so that a variable cam groove body is provided in the cam groove of the cam body for moving the intermediate body. can be operated linearly in the axial direction with respect to the cam base fitted to the central rotating shaft, and the cam groove can be changed by the cam groove variable body to move the roller in the cam groove and the The integral slider can be moved linearly along a guide means parallel to the axis of rotation, which is necessary if the variable cam groove body and roller are to be moved in an arc around a fulcrum at a fixed position. There is no need to take into account the extra gap that would result, and the roller is tightly fitted into the cam groove around the entire periphery of the cam body, and the clearance between the cam body and the roller is eliminated. It is possible to prevent the body from malfunctioning, and even when the earthmoving vehicle is maneuvered into a sharp curve while rotating the hammer, there is no risk that the intermediary body, which should be in the non-hammering position, swings to the hammering position, and the work can be performed safely. Further, in the case of circular arc motion, rollers cannot be used and spheres are used instead of rollers, but linear contact between rollers is more durable than point contact between spheres.

[Brief explanation of the drawing]

Fig. 1 is a front view showing an embodiment of the rock crushing machine 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 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, 73 ... Cam base cylinder part, 74 ... Cam body, 75 ... Flat disk, 77 ... Disk, 78
...Cam groove, 84...Circular recess, 88, 91,
92... Support member, 93... Cam groove variable body, 10
9... Support member, 130... Guide rod as guide means, 131... Slider, 134...
Roller, 135...Interlocking mechanism.

Claims (1)

[Scope of utility model registration request] A holder is installed on the earthmoving vehicle via a vertical movement mechanism,
This 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 casing, and 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. The cam body has a flat disc on one side and a part of the inner surface on the opposite side facing the cam base cylinder fitted on the outer peripheral surface of the central rotating shaft through a cam groove. It is integrally provided with a disc on the other side having an arcuate recess, and is fitted into the cam groove so as to be movable only in the axial direction with respect to the cam base barrel, so that it can be moved by external operating force. The variable cam groove body, which has almost the same shape as the arcuate recess, is moved from the inner surface of the flat disc on one side, which corresponds to the hammering position of the intermediate body, through the supporting member that moves along the intermediate body. A side surface of the main body casing of the rock crushing device, which is provided so as to be movable in the axial direction and rotatable integrally with the cam body within a position within the circular arc-shaped recess of the other side disc as a position corresponding to the hammering position. A guide means is provided in parallel to the rotating shaft via a support member, a slider is slidably fitted into the guide means, and a roller that fits into the cam groove is protruded from the slider to interlock with the slider. A rock crusher characterized in that the above-mentioned intermediary body is connected through a mechanism.