DE19537890C2 - Process for smashing concrete floors and a subsoiler suitable for carrying out the process - Google Patents

Description

The invention relates to a method according to the preamble of Claim 1 and a subsoiler to perform the procedure is suitable.

A well-known underground smashing machine, especially concrete slab debris, includes a chassis having a chassis and a smashing device carried by the smashing car direction with exactly one drop weight, at least in one Working position of the smashing device in a case weight management of the smashing device essentially in is slidably mounted in the vertical direction, and with a Falling weight assigned lifting and triggering device for Lifting the drop weight using at least one on the drop weight attacking drive elements in a maximum lifting position and Drop the falling weight from the maxixmal lifting position a surface, especially a concrete ceiling, in the work position of the smashing device.

In the known, also referred to only as a concrete shatter Concrete slab crushers almost cover the drop weight the entire width of the smash. It will be convenient operated in such a way at the concrete ceiling smashing that it falls position to drop position on the concrete surface, the Concrete floor shatter stopped at the respective drop position and the drop weight is dropped on the concrete surface. As the drop weight, as mentioned, essentially above the entire width of the concrete slab shatter essentially transverse extends to the direction of travel of the concrete ceiling shatter and the Curve radius that the concrete slab shatter can follow, is limited, in practice the case positions are approximate wise on a substantially straight or relatively gentle curved line. At the case positions are mainly Cracks across to the direction of travel or to the specified line expect. Accordingly, those at the smash  resulting clods across the specified line relative be greatly expanded; the extent parallel to the specified Line depends on the distance of the drop positions. Depending on the distance the drop positions give relatively large clods with very different dimensions in longitudinal and Transverse direction or there are clods with strong varying dimensions or areas due to uncontrollable Cracking in any direction if the distance is the case positions is reduced, in order to receive.

From CH 670 466 a subsoiler is known according to the preamble of claim 16 (and thus also according to the preamble of claim 7). The drop weights 3 , which are laterally offset from one another transversely to the straight-ahead direction of travel of the self-propelled ground breaker and are arranged at the same height in the direction of the straight-ahead direction of travel, can be lifted and dropped individually or together by means of their respectively associated lifting and triggering devices 5 , 6 in order to provide different working widths (see page 4, column 2, lines 27 to 43).

The lifting and triggering devices assigned to the drop weights each have two friction rollers 7 , 8 arranged one above the other on one side of the respective drop weight 3 and two pressure rollers 19 , 20 arranged on the other side of the respective drop weight, which can be pressed against the drop weight. To raise the respective drop weight, the pressure rollers are moved in the direction of the friction rollers until frictional engagement is established between the constantly rotating friction rollers and the respective drop weight. The drop weight is then raised until a release cam 38 provided on the lower end area of the drop weight engages a contact member 39 , whereupon the pressure rollers are moved away from the drop weight and the drop weight falls freely onto the ground.

Whether and to what extent a coordination between the ancestor of the Underground smashing and lifting and dropping the  Drop weights exist, is explicitly not in CH 670 466 specified. From the design features of the underground smashing machine can be concluded with a high degree of certainty that the Stop the ground breaker to drop the weights becomes as follows from the following.

The drop weights point at their spaced apart in the transverse direction Edge each a side slide rail, which in a associated recess extending in the vertical direction of a shatterproof guide frame slidably to grab. The recesses are in the straight-ahead direction of the Smashed wider than the engaging leadership rail, so that the falling weight falls into motion Straight direction of travel of the underground smasher. Out of this must be concluded that the drop weights with standing Smashers are dropped and the smashers first pulls up again when the drop weights are raised, because otherwise uncontrolled relative movements between the driving smashers and the dropped and not yet raised again, i.e. still in engagement with the subsurface falling weight could occur, resulting in tilting of the falling weight in his lead frame and the operation the destroyer seriously, if not even the destroyer could damage debris.

Otherwise, a coordination of dropping the drop weights would be among themselves and in relation to the ancestor of the underground debris due to the frictional coupling between the lifting and release device and the drop weights only in be limited possible. It always becomes a certain thing Spin the friction rollers until the frictional engagement with the respective drop weight is made. The one for lifting the Fall weights required time after actuation of the pressure rollers therefore from time to time and in particular from falling weight too Fall weight fluctuate to a certain extent. This must also be taken into account that the friction rollers and possibly also the opposite surface of the respective falling weight in the course of time change their friction properties due to wear  become, which leads to a change in the lifting time. Becomes repeatedly not worked with all drop weights, for example to just a footpath using just a single case to smash weight, it can be due to different Wear at different average lifting times for the Drop weights are coming.

From the foregoing it follows that the drop weights are due to the fluctuating and changing lifting times defined and during continuous operation of the assigned lifting and tripping device constant time interval can be dropped from each other on the ground, so that it is also regardless of the problem of canting the Drop weights in the event of dropping while the Zer is moving debris extremely difficult, if not impossible, that Drop weights with continuously moving smashers Locations spaced apart from one another in the working direction to drop the ground.

As the only one in CH 670 466, due to the simultaneous Use of the drop weights criterion to be optimized Efficiency or the yield is called, according to the Information on page 4, column 2, lines 27 to 43 apparently the pro Unit of time shattered underground surface is meant Underground smashers of the CH 670 466 most likely like this uses that at a stop position of the smash all drop weights used simultaneously are dropped, and is then advanced to the next stopping position. In this case you get a smash result like the one at the beginning described known concrete ceiling smashers, the Work area, however, in width and position relative to the smasher by selecting the drop weights used is variable.

In contrast, it is an object of the invention to provide a method for Smashing concrete ceilings into clods according to the generic term of claim 1 by which a more controlled Cracking in the processed concrete floor, in particular  in terms of achieving relatively small-area concrete clods with relatively uniform dimensions can be achieved can. To solve this problem, the invention proposes gene that in the drive direction next-adjacent drop positions are so offset from one another transversely to the working direction that the falling positions at the break points of at least one on average the zigzag line following the working direction, the Breakpoints are chosen so that clods with relative Similar dimensions arise, especially relatively small flat ceiling channels.

It was recognized by the inventors that small areas Concrete clods with relatively uniform dimensions due to controlled cracking can be achieved if successive case positions alternating in opposite set direction are laterally offset, as such Staggered sides to a largely controlled cracking leads, with a direction of tear extension, one to the Lateral direction orthogonal, essential direction components in Has working direction. On a conventionally necessary one Primary crusher for further clod crushing before feeding to the actual crusher can thus be dispensed with under certain circumstances become.

Small-area slabs with not too much of one another deviating longitudinal and transverse dimensions are particularly noticeable then when the distance in the working direction from in Working direction next-neighboring case positions about half up to twice the distance across the working direction of this Case positions.

In particular for carrying out the method according to the invention the invention provides an underground shatter as claimed 7 or claim 16 defined, ready.

The subsoiler according to claim 7 is characterized from that at least two of the laterally offset drop weights also are offset from each other in the working direction. According to this  preferred training of the underground smashers can at a Position of the ground breaker Weights on at least two both in the working direction and across the working direction spaced fall position to be dropped. To drop the drop weights at drop positions, which correspond to the inventions process according to the invention at the breakpoints of an average of Driving curve of the smasher are following the zigzag line, the ground breaker needs to be stopped less often become. At a respective position of the smashers, the at least two drop weights simultaneously or in succession be dropped. In both cases you get due to the Stopping the smasher less often reduces the cost reducing time advantage with underground destruction.

The subsoiler according to claim 16 is characterized that the at least two laterally offset and on Same drop weights arranged in the working direction assigned lifting and triggering devices designed in this way are that the drop weights with defined and with continuous Operation of the assigned lifting and triggering device constant remaining distance from each other and thus with one Ancestors of the smashers in the working direction from each other in Working direction defines spaced locations on the sub can be dropped. Even if the smasher follows a straight or slightly curved driving line the drop weights, especially when the vehicle is moving continuously Unbroken Smashers dropped at drop positions be to the according to the inventive method Breakpoints of at least one following the middle of the line Zigzag line, i.e. from case position to case position in are laterally offset in the opposite direction.

Advantageous further developments of the method and the underground smashers according to the invention are in the sub claims specified.

The following is proposed for the process:  

For small-area slabs with not too much of one another deviating longitudinal and transverse dimensions, the distance in Direction of work closest to neighboring in the direction of work Fall positions about half to twice the distance across Direction of work correspond to these drop positions.

Preferably two alternate approximately in the working direction same height in relation to the working direction, transverse to Working direction staggered case positions of the first kind and one transverse to the working direction approximately in the middle between case position of the second type lying on these case positions at the. This can be used to achieve clods that are rough have a rectangular or square shape. In this together it is suggested that at least for the most part the execution of the procedure a drop weight on a respective Fall position of the first kind is only dropped when the next to this drop position in opposite directions Beard case positions of the second kind already drop a drop weight has been left. This is a particularly reliable controlled crack formation at the first position in the case achieved essentially parallel to the working direction.

In the method according to the invention, a method according to the invention can be used Underground smashers or a smash according to the invention be used. But in principle it is too conceivable, a shatter not according to the invention, in particular with only one drop weight (in this case the smasher should to the individual case positions).

To the underground smasher according to claim 7 further education suggested:

At least two of the drop weights offset laterally can open the same height in the working direction, the latter Lifting and release devices assigned to drop weights in this way are formed that the drop weights with a time interval from each other and thus at an ancestor of the smasher in Working direction at a distance from each other in the working direction  Places on the ground can be dropped. Even if the smasher of a straight or slightly curved one Following the driving line, the drop weights can thus be at drop positions be dropped at least one at the break points are in the middle of the zigzag line following the driving line, i.e. from Fall position to fall position in the opposite direction are laterally offset. It follows from the above that the Underground smashers from case position to case position must drive up.

It is particularly advantageous if the smashing device has a total of three drop weights, which at the corners of an im essential isosceles triangle with the working direction are arranged substantially orthogonal triangular base. It has it has been shown that the use of three Drop weights, especially in the case of the specified triangle arrangement, a high smashing performance (machined sub floor space per unit of time) can be achieved by the Triangle arrangement the smashing device despite the three Weights can be made relatively compact. Through this Training can, as will become clear below, controlled cracking in a very reliable manner Working direction achieved in essentially parallel direction become.

Each drop weight of the three drop weights can be a separate one Be assigned to the drive element, said drive elements preferably by a common drive device, ins special at least one hydraulic motor, the smashing device direction can be driven. A simple mechanical structure without Gearboxes, couplings or the like for driving force distribution can be achieved if closed in a particular Loop guided drive elements are motion-coupled.

The drivers can be arranged on the drive elements in this way be that when the movement-coupled movement moves in the same direction, drive guided in a respective closed loop elements maximum two of the three drop weights lifted at the same time  become. This makes it possible in comparison to the alternative speed with simultaneous lifting of all three weights in certain Operating states of the smashing device the advantage achieved that a relatively uniform load or a uniform drive of the arrangement results, preferably with im substantially constant rotational speed of the drive elements. Because of the lower and more even load the drive device can be designed correspondingly weaker be, with the more even load having a positive impact has the life of the drive device.

The drivers are preferably on the drive elements in this way arranged that the two are arranged on the triangular base Drop weights simultaneously and with that at the top of the triangle arranged drop weight alternately raised and dropped become. The two drop weights arranged on the triangular base can be about half as heavy to about three quarters each heavy, preferably about two thirds as heavy as that on the Triangular tip drop weight arranged to be even Load and a correspondingly low maximum load for the Get drive device.

The drop weights on the triangular base preferably each have one for creating cracks in the working direction in the underground trained service head, in particular a service head with an impact channel extending in the working direction te. The falling weight at the tip of the triangle then preferably points one for creating cracks across the working direction in the Underground service head, especially one Extend the service head with a cross to the working direction the impact edge. The service heads can, as above mentioned, be interchangeable. The impact heads can, for example then be replaced when the edge of the has worn or if others have to adapt to the surface Head designs bring better results, for example heads with service areas instead of service edges.  

With the described design of the smashing device becomes a controlled with particularly high reliability Cracking reached, the small-scale clods with in allows substantially constant dimensions. This is It is particularly useful if the cracks in Drop weights at the triangular base that serve the direction of work between two using the drop weight at the top of the triangle generated cracks are dropped across the working direction.

For a subsoiler according to the invention is also Generally the following further training is proposed:

Between the drop weights and the one attacking them at least one drive element can be a detachable coupling device tion should be provided.

This brings significant advantages over the one mentioned at the beginning Concrete ceiling smashers with almost the entire width of the Shattering falling weight. This drop weight is with the known concrete ceiling smashers (concrete smashers) namely always with two, each acting as a drive element Tied ropes. The two pull ropes are each from theirs respective attachment point on the drop weight via an assigned, rotatably mounted on a cross member of the drop weight guide Deflection pulley led to an assigned winch. For lifting of the falling weight, the two ropes are placed on a rope drum assigned winch coiled over a jaw clutch is driven by an associated drive motor. The Couplings of the two winches will be used as soon as one of the desired maximum drop position is reached is decoupled to drop the weight onto the concrete surface pelt.

During the falling movement of the Falling weight pulls the two ropes with it. Around a rope Avoid tangling when dropping the case weight, the two cable drums are braked in doses. With regard to the metering of the braking of the cable drums, a must  Compromise can be found because on the one hand to avoid The two rope drums are not too weak may be braked and, on the other hand, the cable drums may not may be slowed down too much to avoid the impact restrict and avoid excessive friction wear. There Intertwined ropes seriously disrupt the smashing operation and would hinder and even damage the smash can lead to noticeable restrictions in practice the fall effect and noticeable frictional wear on the rope drum or accept the assigned braking devices have to.

By contrast, by means of the coupling device according to claim 17 Lifting the drop weight a coupling connection between the Drive element and the drop weight are produced, which for Drop the falling weight after reaching the maximum Lift position is releasable. After loosening the coupling connection, this can Weight can then fall freely without restricting the fall effect, because it does not involve a rope or the like as a drive element. Accordingly, as in the case of a rope or the like Drive element also no rope entanglements or the like occur, so that a possibly provided cable drum or the like Chen does not have to be braked when the weight is dropped. Accordingly, the rope drum, if provided, also occurs no friction wear on.

The drive element can be an elongated drive element, be designed in particular as a conveyor chain, the Kop peleinrichtung preferably a driver on the elongated Includes drive element (especially conveyor chain) with the Falling weight for establishing the coupling connection between the Drive element and the drop weight in particular over a Driving element, if necessary driving pins of the falling weight together works.

The driver can by moving back and forth of the Drive elements between a lower coupling position in which the Coupling connection, if necessary by latching with the driving element,  is producible, and an upper decoupling position in which the Coupling connection is releasable, movable, in the case of a Establish the coupling connection by latching the take-along lake element and / or the driver is preferably wedge-shaped are.

As a preferred alternative solution to the latter solution proposed that the driver by moving the same direction drive elements guided in a closed loop between a lower coupling position, in which the Koppelver binding, in particular by taking hold of the driver under the Driving element that can be produced, and an upper decoupling position tion, in which the coupling connection is detachable, is movable. Due to the same movement of the closed Loop-guided drive elements can be the drive element assigned drive device for a movement in only one Direction be formed without gear means for movement reversal is necessary. One when braking to the direction of movement reversal of the reciprocating drive element occurring increased wear is avoided in the preferred solution. If the coupling connection is under the grip of the driver manufactured the driver element, so the driver and Driving element can be designed simply, what cost advantages and results in high operational reliability.

The maximum lifting position of the drop weight can be determined by vertical Shift of the decoupling position of the driver and / or by vertical displacement of the driving element on the drop weight be adjustable. Since the coupling position of the driver of the Vertical position of the driving element depends on the drop weight, it occurs with a vertical displacement of the driving element Falling weight to a corresponding shift of the coupling position of the driver. About setting the maximum stroke position the impact weight of the drop weight on the surface can be set to the underground for optimal Set smashing result. For a concrete ceiling that too If you want to smash clods, you will hit the impact adjust so that there are reliable cracks in the  Adjust the concrete ceiling to form the ceiling clods without the Concrete ceiling too small in the impact area of the drop weight Pieces are "crushed".

It is suggested that the driver and / or take away Element-associated decoupling means are provided, which Coupling connection in the decoupling position of the driver forcibly solve. A separate manual operation of the Coupling device for dropping the falling weight from a maximum stroke position can thus be omitted.

The driving element of the drop weight can be between a Kop position in which the coupling connection can be established, and a release position in which the coupling connection is released or cannot be manufactured, be movably mounted on the drop weight. In In this case, the driving element is preferably by spring means biased into the coupling position, the possibly provided Decoupling means the driving element to solve the coupling Bring the binding into the release position.

In the described configuration of the driving element, the at least one driver on the elongated drive element be simple, for example as a one-piece and rigid attached to the drive element (especially conveyor chain), if necessary cuboid-like element. Towards a relative to Drive element movable driver or driver part is the solution described due to the drop weight available standing, relatively extensive space less expensive and therefore advantageous. In particular, the manufacturing costs for the coupling device must be reduced and a high one is obtained Operational safety.

The decoupling means can have at least one control curve with one Include trigger curve section on the drop weight guide, wherein the decoupling position, which can be shifted in the vertical direction tion of the driver-defining trigger curve section on the Driving element acts in the decoupling position of the driver and this to release the coupling connection in the release position  brings. The driving element preferably extends from one first drop weight side facing the carrier to one second drop weight side away from the driver through the Falling weight through and points at it from the driver distal end scanning means for scanning the control curve on. Is the driving element in the coupling position over the first drop weight side, the driving element is in the Release position over the coupling position preferably in Shifted towards the second drop weight side.

The fact that the driving element as described by the Drop weight extends through is a simple reliable positive engagement between the drop weight and the driving element. At the same time this will achieved that the smashing device is relatively compact can be carried out because an essential section of the taking element and the driving element associated storage means for sliding storage largely within the drop weight can be arranged. The arrangement described is a spatial separation of the driver or the driver end the driving element and the drive element on the one hand and the Scanning means and the control curve on the other hand reached so that the Smashing device can be relatively simple, because both for the driver and the drive element on the one hand also relative for the scanning means and the control curve much space can be made available.

The first drop weight side can be one (at work position arranged smashing device) in vertical Limit the longitudinal groove in the drop weight in the direction the driving element protrudes at least in the coupling position and in which the driver at least when lifting the drop weight is partially arranged. This training of the falling weight bears also help to make the smashing device relatively compact to be able to train.  

The scanning means can be at least one on the respective Control cam rolling roller. Due to the Scanning roll occurs minimal friction when dropping the Fall weight on, so that the fall effect is not limited and substantially no wear on the sensing means and the control curve occurs.

It is suggested that the drop weight be a replaceable one Has rash head. This training is special before partial, as this will result in an adjustment of the falling weight different underground characteristics is possible, e.g. B. by optionally providing an edge of impact or Impact area.

For reasons of convenience, the smashing car can be a self-driving car. In this case it is suggested that the smashing wagon is an excavator, which may be a preferred one as hydraulic auxiliary pump driven by the excavator motor Drive the at least one hydraulic motor of the smash tion device. The use of an excavator as Smashers are particularly advantageous because excavators with appropriate construction measures (e.g. lane renewal for road or track construction) at the respective construction site in general anyway are available, especially for processing the subsurface and to perform a variety of other tasks, in This case, if necessary, also to include the Zer rubble produced clods when the smashing completed or interrupted. Will be such, anyway available excavator used as smashing wagon, by a smashing device according to the invention on the excavator direction is mounted, the transport of a additional underground smashers or smashers, the otherwise take up additional space at the construction site would no longer be required.

The smashing device can be attached to a boom of the excavator be attached, especially to a hydraulically movable Excavator arm instead of an excavator bucket or the like. In the event of  A hydraulic moveable excavator arm can do the shattering device within the range of movement of the excavator arm (in Case weight) from case position to case position or (in the case of several case weights) from case position group to Case position group can be moved on the ground. It can also Shattering device when driving the excavator in such a way be raised that none of the drop weights on the ground grinds. Such a lifting of the smashing device is but generally not necessary; a grinding of one or more In most cases, weights on the surface do not interfere. So it is also conceivable that the smasher with appropriate Formation of the smashing device, in particular with two or three only perpendicular to the working direction, but not parallel to the Falling weights continuously shift the working direction moves up particularly in the working direction without dropping the Stop falling weights.

The excavator can do this especially as a crawler track trained undercarriage and one on the Undercarriage rotatably mounted superstructure with the boom include. According to this training of the excavator and thus the Smashers are different orientations of the working direction possible relative to the direction of travel of the excavator. For example the working direction coincide with the driving direction or be opposite, orthogonal or oblique to this his. An oblique orientation, especially in such a way that Longitudinal cracks at 45 ° to the direction of travel of the excavator result the advantage that the picking up of the clods by a subsequent wheel loader is facilitated because its loader bucket can easily attack the tips of the clods. Can also by Rotating the uppercarriage to match the working width Maximum boom length of the excavator can be widened.

The invention also relates to a smashing device for Installation on a driving device serving as a smashing car, if necessary a truck or preferably a construction machine such as a Excavator or the like. The smashing device can according to the description above (cf. the  Features of the smashing device relating to the smashing device) be trained.

The invention is described below with reference to the figures shown embodiments explained in more detail.

Fig. 1 shows an underground smashing device according to the invention with an excavator as a smashing wagon and a smashing device mounted on a boom of the excavator in a side view;

FIG. 2 shows in FIG. 2a the smashing device of the smashing device of FIG. 1 from the side opposite to the view of FIG. 1 (direction of view corresponding to the arrow IIA in FIG. 2b) and in FIG. 2b in a side view corresponding to the arrows IIB in FIG Figures 1 and 2a.

Fig. 3 shows the shattering device of the shatter in a partially sectioned plan view accordingly arrow III in Fig. 2b.

Fig. 4 shows three further top views of the shattering device corresponding to the illustration of Fig. 3, wherein Fig. 3 and Figs. 4a, 4b and 4c illustrate a sequence of operating states of the shattering device;

FIG. 5 shows a a driving element comprising carrying means of a falling weight of Zertrümmerungsvor direction of FIGS. 1 through 4, wherein Fig. 5a is a partially cutaway plan view corresponding to Fig. 3, Fig. 5b is a side view according to arrow VB in Fig. 5a and Fig. 5c is a partially sectioned side view corresponding to arrow VC in FIG. 5a;

. 1 Fig 6 shows schematically the crushing apparatus of Figure 1-4 in a lateral view corresponding to Fig for illustrating the operation of the Zertrümmerers, Figs 6a and 6b show two operating states of the un terschiedlichen Zertrümmerers correspond...;

Fig. 7 is an explanatory diagram of the operation of the smashing device and the underground smashing device;

Fig. 8, Fig. 9 and Fig. 10 show in plan views three different working positions of the underground smash according to the invention, wherein the smashing device is slightly modified compared to the embodiment of Fig. 3;

Fig. 11 shows a sequence of crack arrangements in a concrete ceiling, the debris with a Untergrundzer according to the invention according to Figures 1 to 7 (which has three falling weights) in a procedure accordingly Fig. 8 can be produced. and

Fig. 12 shows an alternative sequence of crack arrangements in a concrete ceiling, which can be produced with a subsoiler with two falling weights.

Fig. 1 shows an inventive, especially as Be tondeckenzertrümmerer 10 usable underground smashers with an excavator 12 as smashers. The excavator comprises an uppercarriage 14 and an undercarriage 16 , the uppercarriage 14 on the undercarriage 16 in a manner known per se, e.g. B. is rotatably mounted by means of a slewing ring. The undercarriage 16 includes a crawler track 18 . On the superstructure 14 of the excavator 12 , an excavator arm 20 is pivotally mounted about an essentially horizontal axis, a double-acting cylinder-piston unit 22 known per se being provided for pivoting the excavator arm 20 . At the end of the excavator arm 20 remote from the superstructure 14 , a shattering device 30 (to be described only schematically in FIG. 1), which is described in more detail below, is mounted (for example instead of an excavator shovel) and can be relative to a subsurface U, in particular relative to, using the excavator arm 20 a concrete ceiling, raised and lowered. By means of a further, double-acting Zylin the piston unit 24 , which is articulated on the excavator arm 20 near its upper end and on the shattering device 30 , the shattering device can be pivoted about a substantially horizontal axis on the excavator arm 20 such that a Longitudinal axis L of Zertrümmerungsvor direction 30 extends substantially in the vertical direction. (In the following it is assumed that the Zertrümmerungsvor device is arranged in a working position with a vertical longitudinal axis L and with a vertical distance suitable for shattering the ground by means of three falling weights above the ground U.) By rotating the superstructure 14 on the undercarriage 16 by means of a Known rotary drive, the smashing device 30 can be brought in various positions relative to the undercarriage, such as. B. shown in Figs. 8, 9 and 10.

As described in more detail below, the shattering device 30 is driven hydraulically. The hydraulic pressure required for this is supplied to the shattering device 30 by means of hydraulic pressure hoses, not shown, from a hydraulic pump of the excavator. The hydraulic pump can be the main hydraulic pump of the excavator, which drives the chassis via corresponding hydraulic motors, or a hydraulic auxiliary pump, which, like the main hydraulic pump, is preferably driven by the excavator motor.

The smashing device 30 comprises a framework composed essentially of double T-beams, in which three case weights G1, G2 and G3 can be displaced parallel to the longitudinal axis L in a respective drop weight guide formed by two double-T beams (in the case of FIG. 1 shown position of the smashing device are thus vertically displaceable). The drop weight guides of the three drop weights G1, G2 and G3 are formed by the double T-beam pairs 33 a, 33 b, 34 a, 34 b and 32 a, 32 b, which extend parallel to the longitudinal axis L, whose (hereinafter also called Double-T longitudinal beams) beams 33 a and 33 b, 34 a and 34 b or 32 a and 32 b are offset from one another transversely to a working direction A orthogonal to the longitudinal axis L. (The working direction A is a direction in the vectoral sense, which points away from the excavator 12 in the arrangement according to FIG. 1.) The drop weights are between the T longitudinal beam sections and (which extend parallel to the working direction A in cross section) the T-crossbar sections of the respective double T-beam pair (extending in cross section transversely to the working direction A).

The double-T beams 33 a, 33 b, 34 a and 34 b and thus the two drop weights G1 and G2 are at the same height with respect to the working direction A; are only offset from each other transversely to the working direction. The double-T beams 32 a and 32 b of the falling weight G2 are arranged in the working direction A in front of the double T-beams 33 a, 33 b, 34 a and 34 b that the falling weight G3 at the triangle tip of an isosceles Three corners is arranged, the drop weights G1 and G2 are arranged on the triangle base on a respective triangle corner. The double-T beams 32 a and 32 b are across transverse to the working direction A and transverse to the longitudinal axis L extending double-T cross beams 36 , 37 and 38 (whose T-longitudinal beam sections extend parallel to the working direction A in cross section) with connected to the double-T side members 33 a, 33 b, 34 a and 34 b.

The double-T longitudinal members 33 b and 34 a each carry a lower and an upper, plate-like articulation member 40 a and 40 b on their side corresponding to the outside of a T-cross bar section and located away from the cross members 36 , 37 and 38 . 41 a and 41 b with a respective bearing opening 42 for receiving a respective, extending orthogonally to the longitudinal axis L and the working direction A connecting bolt with which the two upper link members 40 a and 41 a with the shattering device-side end of the cylinder-piston unit 24 and the two lower articulation members 40 b and 41 b can be connected or are connected to the end of the excavator arm 20 on the smashing device side ( FIGS. 2 and 4 show the smashing device 30 alone, but not the excavator 12 or the excavator arm 20 and the cylinder Piston units 22 and 24 ).

The three drop weights G1, G2 and G3, of which the drop weight G3, for example, weigh 3 t (tons) and the drop weights G1 and G2, for example 2 t each, are each assigned a lifting and triggering device for lifting and dropping the drop weight, which is about a drive device common to all three drop weights is driven. The drive device comprises two hydraulic motors 52 a and 52 b acting on a common, rotatably mounted drive shaft 50 (so-called hydraulic brake motors with gears, for example with a lifting capacity of 60 kW each). The two, arranged on two transverse sides of the shattering hydraulic motors are attached to the double-T side members 33 a, 33 b, 34 a and 34 b, support elements including a further double-T cross member 39 and at the ends of the double-T -Cross member 39 attached carriers 39 a and 39 b carried such that the two hydraulic motors connecting, extending transversely to the longitudinal axis L and the working direction A extending drive shaft 50 , referring to the working direction A, is arranged behind the two falling weights G1 and G2. The two hydraulic motors 52 a and 52 b each carry on a rotor 55 a and 54 b coaxial with the drive shaft 50 and coaxial with the drive shaft 50 , a gear 56 a and 56 b coaxial with the rotor and thus with the drive shaft.

Parallel to and at the same height (in the vertical direction) as the drive shaft 50 arranged in an upper end region of the shattering device 30 , a rotatably mounted intermediate shaft 58 is arranged between the drop weights G1 and G2 on the one hand and the drop weight G3 on the other hand, each of which has one end at both ends with the gear 56 a or 56 b aligned gear 60 a or 60 b carries. A conveyor chain 62 a and 62 b rotates in a respective endless loop both around the gear wheels 56 a and 60 a and around the gear wheels 56 b and 60 b. As a result, the drive shaft 50 and the intermediate shaft 58 are motionally coupled, so that the intermediate shaft 58 is equally sensible and with the same rotational speed with the drive shaft 50 rotates.

The drive shaft 50 also carries two gears 64 and 65 , of which, based on a transverse direction orthogonal to the longitudinal axis L and to the working direction A, the gear 64 is arranged approximately in the middle of the falling weight G1 and the gear 65 is arranged approximately in the middle of the falling weight G2 is. Similarly, the intermediate shaft 58 carries a gear pair of two close to each other Benach disclosed gears 66 a and 66 b, which are arranged with respect to said transverse direction, approximately in the middle of the falling weight G3. The gears 64 and 65 and the gear pair 66 each have a gear 67 or 68 or a pair of gears 69 from two closely adjacent gears 69 a and 69 b assigned to the gear 64 , 65 or with the gear pair 66 tending are supported in a lower end region of the shattering device 30 by a respective end shaft 70 , 71 and 72, which is rotatably mounted and parallel to the shafts 50 and 58 . More precisely: the gear 64 is aligned with the gear 67 , the gear 65 with the gear 68 and the two gears of the gear pair 66 with a respective gear of the gear pair 69 . The gear shaft 67 carrying end shaft 70 and the gear wheel 68 carrying end shaft 72 are coaxial with one another and with their respective two shaft ends in two on the double-T longitudinal members 33 a and 33 b or 34 a and 34 b attached shaft bearings 74 a and 74 b or 75 a and 75 b rotatably mounted. In the same way, the end shaft 72 , which is arranged at the same height (in the vertical direction) as the end shafts 70 and 71 and carries the gear pair 69, is rotatably mounted with its two ends in two shaft bearings attached to the double-T longitudinal member 32 a and 32 b , of which only the shaft bearing 76 b can be seen in Fig. 2b.

With respect to the working direction A, the end shafts 70 and 71 are arranged at the same height as the drive shaft 50 and the end shaft 72 at the same height as the intermediate shaft 58 .

Both around the gears 64 and 72 , as well as around the gears 65 and 68 , as well as around the pairs of gears 66 and 69 , a conveyor chain 77 , 78 and 79 is guided in a closed endless loop, so that the end shafts 70 and 71 with the same rotational speed with the drive shaft 50 and the end shaft 72 with the same rotational speed with the intermediate shaft 58 rotate in the same direction (the gears 64 , 65 , 66 a, 66 b, 67 , 68 , 69 a and 69 b accordingly have the same diameter and same number of teeth).

According to the preceding description, the conveyor chains 77 , 78 and 79 are thus coupled in motion in such a way that they can be driven together by the two hydraulic motors 52 a and 52 b and then rotate with the same sense of rotation and the same speed of rotation.

The conveyor chains 77 , 78 and 79 serve as drive elements for lifting the drop weights G1, G2 and G3. For this purpose, the conveyor chains 77 , 78 and 79 each carry exactly one block-shaped driver 82 , 83 and 84 on their outer circumferential side facing away from the grinding. The catches 82 , 83 and 84 are each assigned a catch device with a catch element in the form of a catch bolt 85 , 86 and 87, which is displaceable in the falling weight G1, G2 and G3 parallel to the working direction A.

The three drop weights G1, G2 and G3 have, apart from a respective impact head at the lower end, parallel to the longitudinal axis L, a substantially constant cross section. The case weights give way from a pure rectangular cross section through a side facing the conveyor chain 77 , 78 or 79 and thus the driver 82 , 83 or 84 through a side running in the middle parallel to the longitudinal axis L to the respective conveyor chain 77 , 78 or 79 open longitudinal groove 90 , 91 and 92 respectively. The driving pins 85 , 86 , 87 are each slidably mounted in a guide sleeve 88 which is received in a through-opening 81 of the falling weight which is open to the groove, and is biased by a compression spring 89 into a coupling position in which the driving pin 85 , 86 and 87 maximum in the respective longitudinal groove 90 , 91 or 92 of the drop weight G1, G2 or G3 before. The driving bolts are at a relatively small distance parallel to the working direction A between their respective free ends and a respective drop weight close to the longitudinal groove 90 , 91 and 92 extending section of the conveyor chain 77 , 78 and 79 respectively. This section of the respective conveyor chain extends slightly into the longitudinal groove 90 , 91 and 92 , respectively.

If the driver 82 , 83 or 84 of the conveyor chain 77 , 78 or 79 is arranged on the chain section which is close to the falling weight G1, G2 or G3 and is parallel to the respective longitudinal groove 90 , 91 or 92 , this driver is completely in the longitudinal groove 90 , 91 and 92 respectively. The free end of the driving pin 85 , 86 or 87 and the respective driver 82 , 83 or 84 overlap in the direction parallel to the longitudinal axis L.

The conveyor chains are driven by the hydraulic motors 52 a and 52 b in such a direction of rotation that the respective carrier after rotation around the gear 67 , 68 or 69 coming from below enters the longitudinal groove 90 , 91 or 92 and the other Circulation of the conveyor chains relative to the falling weight G1, G2 or G3 in the respective longitudinal groove upwards until it reaches a coupling position in which it strikes the Mitnahmebol zen 85 , 86 or 87 , or engages under it, so that a coupling connection is produced between the conveyor chain 77 , 78 and 79 and the drop weight G1, G2 and G3 via the catches 82 , 83 and 84 and the catch bolts 85 , 86 and 87 , respectively.

As the conveyor chain continues to circulate, the respective case weight G1, G2 or G3 is raised due to the coupling connection through the conveyor chain 77 , 78 or 79 , until the driver 82 , 83 or 84 has reached a decoupling position in which the respective driving pin 85 , 86 and 87 is brought by a decoupling means to be written in more detail against the force of the spring 89 into a release position in which the driving pin 85 , 86 or 87 projects less far into the longitudinal groove 90 , 91 or 92 . In this release position, the driver 82 , 83 or 84 no longer engages under the driving pins 85 , 86 or 87 , so that the falling weight falls back into its original position from the maximum lifting position reached. If, as assumed, the smashing device is arranged at a suitable distance above the subsurface U, the drop weight falls from the maximum lifting position onto the subsurface; more precisely: The drop weight hits the ground with a head K1, K2 or K3 located at the lower end of the drop weight.

To adjust the drop height of the drop weights G1, G2 and G3, the driving bolts 85 , 86 and 87 together with their respective guide sleeve 88 on the drop weight G1, G2 or G3 are displaceable in the vertical direction; the drop weights have, as indicated in Fig. 6, three vertically spaced through openings 81 a, 81 b and 81 c for receiving the guide sleeve, in Fig. 6 the respective guide sleeve with the driving pin for all drop weights in the middle through opening 81 b is added. By shifting the driving pin in the vertical direction, the coupling position of the driver 82 , 83 or 84 is shifted in the vertical direction and there is a different maximum lifting height of the falling weight. A further variation of the drop height is possible via the decoupling means by vertical displacement of the decoupling position of the driver, as will be explained in more detail below.

In the following, the drive pins of the three drop weights, which comprise the respective drive pins, the respective guide sleeve and the respective spring, will be discussed in more detail. Here, reference is made in particular to FIG. 5, which shows the entrainment device of the drop weight G3 in three views (the drop weight G3 is indicated by dashed lines, the drop weight management is omitted). The explanations apply accordingly to the driving devices of the case weights G1 and G2.

As already mentioned, the guide sleeve 88 is received in a through-opening 81 opening towards the longitudinal groove 92 of the drop weight G3 and to the opposite drop weight side; it therefore extends between the case weight side 51 shown in FIG. 5a, delimiting the groove in the working direction A, and the opposite case weight side S2. As can be seen from FIG. 3, the drop weight side S1 faces the driver 84 or the conveyor chain 79 , whereas the drop weight side S2 faces away from the driver or from the conveyor chain 79 . The releasably festge placed in the through-guide sleeve 88 is closed on its projecting over the falling weight side S2 by a cover plate 88 a. The driving pin 87 comprises also on one side to a threaded hole closed bolt sleeve 87 a which is received within the guide sleeve 88 that the closed, the threaded hole having the end of the pin boot from the Füh approximately sleeve protrudes into the longitudinal groove 92 88th At the end opposite the closed-end end end 87, the pin boot on a has a radially protruding annular rim, the larger as shown in Fig. 5a position of the driving pin 87 at an annular shoulder between a sleeve interior diameter portion of the guide sleeve 88 and a sleeve interior portion small ren diameter of the guide sleeve 88 strikes so that the bolt sleeve 87 a can no longer be moved out of the guide sleeve 88 into the longitudinal groove 92 .

The cover plate 88 a has a through hole for a bolt rod 87 b of the driving pin 87 . The bolt rod 87 b extends through the opening of the cover plate 88 a through the interior of the guide sleeve 88 and the interior of the bolt sleeve 87 a to the closed end of the bolt sleeve 87 a and is fixed here in the threaded hole with its one rod end by screwing. Between the cover plate 88 a and the closed end of the bolt sleeve 87 a (this closed end corresponds to the free end of the driving bolt), the helical compression spring 89 carried by the bolt rod 87 b acts and expresses the bolt sleeve 89 a together with the bolt rod 87 b as far as possible the guide sleeve 88 in the direction of the groove 92 .

At the end of the bolt rod 87 b, which is remote from the bolt sleeve 87 a and on the other side of the cover plate 88 a, a rectangular frame-like cross element 102 is rigidly fastened (the cross elements of the entrainment devices of the drop weight G1 and G2 have the reference numbers 100 and 101 ). The cross member 102 extends substantially transversely to the working direction A and transversely to the longitudinal axis L and carries at its two, in the transverse direction spaced ends, a scanning roller 105 a and 105 b (the scanning rollers of the driving devices of the Fallge weight G1 and G2 have the reference numerals 103 a and 103 b or 104 a and 104 b). The scanning rollers, which can be rotated about an axis orthogonal to the working direction A and the longitudinal axis L, roll on the front and rear of the double-T beam 32 a and 32 b, respectively, in relation to the working direction A, during the lifting and falling movement of the falling weight. These front sides of the double-T girders 32 a and 32 b (and correspondingly the front sides of the double T-girders 33 a, 33 b, 34 a and 34 b) function as control curves and carry a wedge-shaped shape at an upper end region Ges trigger element 108 a and 108 b, whose front side in the working direction A represents a trigger curve section of the respective control curve (the double-T beams 33 a, 33 b, 34 a and 34 b carry a trigger element 106 in the same way on their front a, 106 b, 107 a and 107 b).

If the respective scanning roller now reaches the release element held on the corresponding double-T longitudinal member while the drop weight is being lifted, the roller becomes a curved section through the release together with the cross element 100 , 101 and 102 , the bolt rod ( 87 b) and the bolt sleeve ( 87 a) shifted in the direction A, so that the driving pin 85 , 86 or 87 is increasingly drawn into the guide sleeve 88 until the associated driver 82 , 83 or 84 no longer engages under the driving pin, the coupling connection between the with conveyor chain 77 , 78 or 79 and the falling weight G1, G2 or G3 is thus solved. The drop weight has reached its maximum stroke position at the moment the dome connection is released and falls out of it onto the underground U, which it hits with its impact head.

As indicated in Fig. 6 for the trigger elements 106 a and 108 a by a respective double arrow, the trigger elements are displaceable on the respective double-T side member. The vertical position of the trigger elements directly determines the decoupling position of the respective driver, so that the maximum lifting position of the drop weight can be adjusted in a certain range by appropriate displacement of the trigger elements. From the above it follows that the control cams, the triggering elements, the transverse elements and the scanning rollers are parts of the above-mentioned decoupling means, which remove the respective driving pin from the coupling position, in which the assigned driver can engage under the driving pin, into the release position, in the under grip of the driver is lifted under the driving pin.

As already mentioned above, the three conveyor chains 77 , 78 and 79 assigned to the drop weight G1, G2 and G3 are each provided with a driver 82 , 83 and 84 and rotate synchronously with one another at the same rotational speed and the same direction of rotation around their assigned gears. The sense of rotation is such that the section of the conveyor chain which is closer to the respective falling weight and runs in the vertical direction is moved vertically upward, as illustrated in FIG. 6. The drivers are attached at such positions along the closed loop of the respective conveyor chain, so that the drivers 82 and 83 , which are assigned to the drop weights G1 and G2, always move synchronously with one another at the same height. Are the entrainment devices of the drop weights G1 and G2 arranged at the same height relative to the respective drop weight and the triggering elements 106 a, 106 b, 107 a and 107 b are also at the same height relative to the destruction device 30 and the respective double-T side member 33 a, 33 b, 34 a and 34 b arranged, the drivers 82 and 83 simultaneously reach their coupling position arranged at the same height and then their decoupling position arranged at the same height, so that the two falling weights G1 and G2 are raised synchronously with each other and be dropped. The position of the driver 84 along the closed loop of the conveyor chain 79 is so matched to the position of the other two drivers on their respective conveyor chain that the falling weight G3 is never raised simultaneously with the two falling weights G1 and G2. With continuous circulation of the conveyor chains, there is a constant change of the two states shown in FIGS. 6a and 6b:

• a) The two drop weights G1 and G2 are simultaneously in raised their maximum stroke position and then to the Un dropped, the falling weight is G3 in its lowest position;
• b) the drop weight G3 is in its maximum lifting position raised and then dropped, here are the two Drop weights G1 and G2 in their lowest positions.

FIGS. 3 and 4 show a sequence of four Betriebszu stands during a complete revolution of the conveyor chains. In Fig. 3 the drop weight G3 is raised, as can be seen from the position of the dog 84 below the driving pin 87th The drivers 82 and 83 move along the section of the conveyor chain 87 and 78 that is distant from the respective falling weight G1 and G2. In Fig. 4a, the carrier element 84 has just reached the Entkoppelposition. Due to the interaction of the release elements 108 a and 108 b and the scanning rollers, the driving pin 87 has just slid from the driver 84 , so that the falling weight G3 falls on the ground in the next instant. In Fig. 4b, the two drop weights G1 and G2 are now raised, as can be seen from the position of the two drivers 82 and 83 below the driver bolts 85 and 86 . The drop weight G3 remains in its lowest position. (In this case, the driver 84 moves along the section of the conveyor chain 79 that is remote from the falling weight G3.) In FIG. 4c, the drivers 82 and 83 have both reached their decoupling position. The driving bolts 85 and 86 are accordingly just by the interaction of the trigger elements 106 a, 106 b, 107 a and 107 b with the scanning rollers 103 a, 103 b, 104 a and 104 b slid from the respective driver 82 and 83 , respectively that the two drop weights G1 and G2 fall onto the ground in the next moment.

The coordinated movement (lifting movement and falling movement) of the three falling weights G1, G2 and G3 is also clear from the diagram in FIG. 7. In the two upper slide diagrams of this diagram, the vertical position of the drop weight G3 and the common vertical position of the two drop weights G1 and G2 are plotted over a parameter B. The parameter 8 is a measure of the rotation of the conveyor chains and can be identified, for example, with a rotation angle of a fictitious drive gear that rotates exactly 360 ° during a complete rotation of the conveyor chain loops. To clarify the term "complete circulation of the conveyor chain loops", a complete circulation of the conveyor chains is characterized, for example, by the fact that the participants, starting from a respective starting position (for one of the carriers, for example, the coupling position or the decoupling position) after a complete circulation of the conveyor chain have just returned to their starting position.

As shown in the diagram of FIG. 7, the falling weight G3 is increased starting at θ ₁ until it falls onto the ground at θ ₂ . The drop weights G1 and G2 are then raised starting at θ ₃ and then falling at θ ₄ on the ground. This is then followed by the falling of the drop weight G3, starting at θ ₁ . The difference between θ ₂ and θ ₁ (Δθ ₂ ) and the difference between θ ₄ and θ ₃ (Δθ ₄ ) corresponds to the maximum lifting height of the falling weight G3 or falling weights G1 and G2. As described above, this maximum lifting height can be varied by vertically displacing the coupling position of the driver (by vertically displacing the driving bolt on the drop weight) and by vertically displacing the decoupling position of the driver (by vertically displacing the release elements). From θ ₂ to θ ₃ (difference Δθ ₃ ) and from θ ₄ to θ ₁ (difference Δθ ₁ ) all three case weights are in their lowest position, i.e. with their respective impact heads K1, K2 or K3 in accordance with Fig. 1 arranged smashing device on the ground, in particular a concrete ceiling. The differences Δθ ₁ and Δθ ₃ can also vary strongly in size from each other, as shown in Fig. 7.

The foregoing description has not yet gone into the forward movement of the concrete floor smasher 10 by appropriately advancing the excavator. To the ancestor, the entire smashing device 30 can be raised by means of the excavator arm 20 , so that the one or those drop weights, which are arranged in their lowest position, do not grind on the ground with their impact head K1, K2 or K3 (on the drop weights and stops are provided in the drop weight guides, which limit the vertical movement of the drop weights downwards relative to the respective drop weight guide). However, it has been found that letting one or more impact heads grind on the ground is mostly harmless, so that it is generally not necessary to lift the smashing device 30 in order to advance the smasher.

For reasons explained in more detail below, the drop weight G3 preferably has an impact head for generating cracks transverse to the working direction A in the subsurface, in particular the concrete ceiling. A design of the impact head K3 with an impact edge extending transversely to the working direction A is particularly suitable for this purpose, as indicated in FIGS. 2 and 6. The two drop weights G1 and G2 preferably have an impact head K1 or K2 for generating cracks in the subsurface, in particular in the concrete ceiling, essentially parallel to the working direction A. A design of the impact heads K1 and K2 with an impact edge extending essentially parallel to the working direction A is particularly suitable for this. The service heads are preferably interchangeable in order to provide other head shapes, for example, with service surfaces instead of service edges, or to be able to replace the heads if these, in particular the service edge, are worn.

If the impact heads of the drop weights are designed with impact edges, as indicated, it is at least useful if the excavator moves parallel to the working direction A, while lifting the drop weight with the impact edge extending transversely to the working direction (the drop weight G3 ) to raise. Based on the circulation dimension θ of the conveyor chains, the excavator would have to advance between θ ₁ and θ ₂ , as illustrated in the lower part of the diagram. In this sub-diagram with M for engine (excavator engine) marked y-axis, the intervals in which the excavator is preferably driven forward are indicated by solid lines. Depending on the subsurface, however, grinding of the drop weight G3 on the subsurface when the smashing machine is ancestor tolerated; In this case, the excavator could drive up during the intervals shown in dashed lines. In the latter case, it would be expedient to make the interval Δθ ₃ significantly smaller than the interval Δθ ₁ by arranging the drivers on the conveyor chains accordingly, so that, based on the circumferential dimension θ, larger intervals are available for driving the excavator forward. Of course, the circulation of the conveyor chains can also be stopped while the excavator is advancing, so that the time available for the ancestors is independent of the conveyor chain circulation.

In deviation from the preceding description, the shattering device can also be carried out without conveyor chains rotating in closed loops, but for example by means of reciprocating drive elements, in particular conveyor chains. In Fig. 5c such a design of the smashing device is indicated by a dashed double arrow instead of an upward, solid arrow. To produce the coupling connection between the driver 84 and the driving pin 87 in the coupling position of the driver, the driver can be wedge-like in deviation from the block-like shape, as just indicated by dashed lines in Fig. 5c, so that the driver when approaching the Driving pin presses this into the guide sleeve from above, so that the driver can move past the driving pin past at least to a position at which the driving pin is pressed out of the guide sleeve again due to the force of the spring 89 , so that now the Carrier with subsequent movement in the opposite direction ent up the driving pin and thus the drop weight can take. The coupling connection can be released in the decoupling position of the driver as explained in connection with the previously described embodiment.

In the preceding description of the concrete ceiling smasher 10 or the smashing device 30 it has already been indicated that the excavator preferably moves up to a position on the ground, in particular the concrete ceiling, and stops there for dropping the falling weights. The drop weights are arranged in a respective drop position in this excavator position and, as written, are dropped onto the ground one after the other (when the concrete floor shatter is at a standstill). The excavator then moves to the next position on the ground; the drop weights are thereby moved on to their next respective drop position. As explained in conjunction with Fig. 7, the orbital movement of the conveyor chains here on the forward movement of the excavator is preferentially coordinated such that the time required to raise the drop weight G3 is used to drive the excavator forward. Accordingly, at a standstill position of the excavator, the falling weight G3 is first dropped in its falling position depending on the position of the excavator, the rotational position of the superstructure on the undercarriage of the excavator and the position of the excavator arm. Then the two case weights G1 and G2 are raised at this excavator position (with the excavator stationary) and dropped onto the ground. The excavator then moves on to the next excavator position.

The procedure described offers several advantages. On the one hand, the hydraulic motors driving the conveyor chains need only be designed so strongly that they are sufficient to lift the heavier load of the two loads formed by the drop weight G3 alone and by the two drop weights G1 and G2 together. On the other hand, a particularly well-defined formation of clods is achieved by producing corresponding longitudinal and transverse cracks in the subsurface, in particular the concrete ceiling, as shown in FIG. 11. This figure shows in FIGS . 11a to 11j a sequence of drop positions of the drop weights G1, G2 and G3 and the cracks in the subsurface resulting from the dropping of the respective weight at the corresponding drop position. From a snapshot to the next snapshot of the sequence, the additionally added case positions at which a drop weight has been dropped are identified by an arrow.

As indicated above, the drop weights G1 and G2 are equipped with an impact head designed to form longitudinal cracks essentially parallel to the orientation A and the drop weight G3 is equipped with an impact head designed to form transverse cracks essentially orthogonal to the working direction A. The mode of operation is as indicated in FIG. 8. The excavator moves to a series of excavator positions spaced apart from one another in the working direction, at each of which the drop weights are dropped at the corresponding drop positions. The drop positions are accordingly also spaced apart from one another in the working direction A. If a series of excavator positions spaced apart in working direction A has been approached, the excavator turns and successively moves to a series of excavator positions parallel to the aforementioned series, which series is essentially parallel to the first-mentioned series. The excavator is therefore moved back and forth across the ground row by row.

Starting from a subsurface without cracks, the drop weight G3 is dropped onto the subsurface as the first weight according to FIG. 11a; this results in a transverse crack QR1 in the underground. Fig case the two weights G1 and G2 are subsequently laser-case according. 11b at the same digging position sen, this results in addition to the cross-sectional view QR1 the two longitudinal cracks LR1 and LR2, the überge at one end in the cross-sectional view QR1 hen. The two longitudinal cracks LR1 and LR2 end at a certain distance from the cross crack QR1. After the two drop weights G1 and G2 have been dropped, the excavator moves in working direction A and stops at the next excavator position in the series of excavator positions. At this position, the drop weight G3 is dropped again, which causes a transverse tear QR2 essentially parallel to the transverse tear QR1, as shown in FIG. 11c. Then the drop weights G1 and G2 are dropped at the same excavator position, whereby longitudinal cracks LR1 and LR2 are generated, which at one end merge into the transverse tear QR1 and at their other end into the transverse tear QR2. The cracks QR1, LR2, QR2 and LR4 thus delimit a flounder of the subsoil or the concrete ceiling, which is essentially rectangular.

When the procedure corresponding to FIG. 11, the excavator of backhoe digging position to position in front travels about a distance which corresponds to the distance of the drop weights G1 and G2 in the transverse direction to the working direction A substantially. Accordingly, the plaice shown in Fig. 11d is substantially quadratic. The two drop weights G1 and G2 can, for example, be spaced apart from one another by approximately 1.1 m transversely to the working direction and have a distance of approximately 0.7 m from the falling weight G3 parallel to the working direction A. If the excavator moves from excavator position to excavator position approximately 0.7 m, there are clods with a size of approximately 1.4 × 1.1 m, which should still be regarded as approximately square. By appropriate design of the smashing device or by moving the smashing device, for example with means of the excavator arm at a respective excavator position at an angle to the working direction such that the drop weight G3 is dropped exactly between two drop positions at which the drop weights G1 and G2 have already been dropped clods with an edge length of about 0.5 m (with a correspondingly smaller distance 12309 00070 552 001000280000000200012000285911219800040 0002019537890 00004 12190 of the falling weights of about 0.4 m from each other) are also produced.

To generate the next transverse crack QR3 in the working direction according to FIG. 11e, the excavator again moves to the next excavator position, stops there and the falling weight G3 is dropped at its corresponding falling position. The two falling weights G1 and G2 are then dropped at the same excavator position, so that two longitudinal cracks LR5 and LR6 form between the two transverse cracks QR2 and QR3, which delimit a further slab. As indicated in FIG. 11f, the falling positions closest to one another in the working direction are offset from one another transversely to the working direction in such a way that the falling positions lie at the break points of two zigzag lines 21 and 22 following the middle of the working direction A.

Referring to FIGS. 11g to 11j then 11 agrees with the number of event positions according to Fig. A parallel series of positions on the case, in which case the weights G1, G2 and G3 according to corresponding movement of the Zertrümmerers who dropped the. The drop positions of the drop weights G1, G2 and G3 are chosen such that on the one hand the drop positions of the drop weight G3 are each approximately at the same height as a drop position of this drop weight of the row according to FIG. 11f, so that the already existing transverse cracks QR1 and QR2 in be extended substantially transversely to the working direction, and on the other hand the falling positions of the falling weights G1 and G2 of the adjacent rows have a substantially constant distance transversely to the working direction, so that the longitudinal cracks LR9, LR10, LR3 and LR4 accordingly also have a substantially constant distance from one another. Approximately square clods with essentially the same dimensions are formed.

If the procedure illustrated in FIG. 11 is continued accordingly, a crack pattern as illustrated in FIG. 8 is finally achieved. Here the subsurface has a large area that is smashed into square clods with essentially constant dimensions. (Depending on the surface, the cracks may also be more straightforward than drawn in the figures for better differentiation from other figures.) FIGS . 8 and 11 give an example of a method for explaining how the preceding explanations make it clear Smashing concrete ceilings into clods by dropping three weights. The distance in the working direction from the nearest neighboring falling positions in the working direction corresponds approximately to the distance of these falling positions transverse to the working direction.

In deviation from the preceding description, the superstructure can also be rotated relative to the undercarriage of the excavator in such a way that the working direction A and the direction of travel F of the excavator are not parallel. According to FIG. 9, the angle between the working direction A and the driving direction F is approximately 45 °. This arrangement has the advantage that the cracks running at about 45 ° to the direction of travel F facilitate picking up the resulting clods by means of a loading shovel of a wheel loader following the excavator and also traveling in the direction of travel F, since the loading shovel at the tips of the loader facing it Can attack clods.

Another alternative procedure is shown in FIG. 10; here the angle between the working direction A and the direction of travel of the excavator F is about 90 °.

To that shown in Figs. 8, 9 and 10 destroyer 10 'is be added that carried by the excavator arm cerium trümmerungsvorrichtung 30' is slightly different design than the destruction apparatus 30 of the FIGS. 2 and 3. In the crushing device 30 'are Gears 56 a, 56 b, 60 a and 60 b transversely to the working direction A substantially in the middle of the shattering device, so that the gears 60 a and 60 b are the gear pair between them 66 immediately adjacent. This change compared to the smashing device 30 and the slightly different shape of the smashing device 30 'as a whole in plan view are of no importance for the functioning of the smashing device.

Compared to the preceding description of the underground smashing device according to the invention and the smashing method according to the invention according to FIGS . 1 to 11, many modifications are conceivable. For example, the smashing device may have only two instead of three falling weights. Such a design of the smashing device can be easily explained using the exemplary embodiment with the three falling weights. Compared to this embodiment, for example, with the three drop weights G1, G2 and G3, only the drop weight G3 together with the device parts associated with this drop weight G3, such as intermediate shaft 58 , gear wheels 62 a and 62 b, gear pair 66 , gear pair 69 , conveyor chain 79 , double T, Carrier 32 a and 32 b, etc. are omitted. The carriers 82 and 83 are then preferably attached to their respective conveyor chain 77 or 78 in such a way that only one of the two case weights is always lifted, the other case weight is thus arranged in its lowest position. For example, the drivers could be attached to the conveyor chains in such a way that the uppermost partial diagram of FIG. 7 describing the movement of the drop weight G3 is applicable to the drop weight G2 and the middle one, in itself the movement of the two drop weights G1 and G2 descriptive partial diagram of FIG. 7 applies only to the drop weight G1.

Are the two drop weights G1 and G2 corresponding to that ahead outgoing statements at the same level relative to the work Direction A arranged, the smashers, if the Fall positions of the fall weight G1 from the fall positions of the Falling weight G2 spaced apart in working direction A.  between the dropping of one and the fall Allow the other weight to move in one direction ren that a component parallel to the working direction A. points. Each drop position ent one of the two drop weights ent then speaks an excavator position. Alternatively, the Smashing device can also be modified such that the Drop weights G1 and G2 not only across the working direction, but also parallel to the working direction A from each other are spaced. For example, the drop weight G2 in Direction of work A shifted and for example at about height of the omitted falling weight G3. With a corresponds to such formation of the smashing device For each excavator position, a pair of fall positions of the fallge Weigh G1 and G2 in the direction of work and across the work direction are spaced from each other.

With a smashing device with two falling weights, which are spaced apart from one another transversely to the working direction and are either arranged at the same height relative to the working direction A or parallel to the working direction, a substrate, in particular a concrete ceiling, can be used in the manner shown in FIG. 12 and smashed into clods. Fig. 12 shows in Figs. 12a to 12g, a sequence of event positions of the two drop weights G1 and G2, a according to the foregoing abgewan punched bursting apparatus and the resulting in dropping of the respective drop weight cracks in the substrate. As in FIG. 11, the newly added drop position at which the drop weight G1 or G2 has been dropped is identified by an arrow. The two case weights each have an impact head, which is suitable for generating cracks transversely to the working direction.

In Fig. 12a, the first drop weight has fallen onto the ground and a cross crack QR1 has formed. Subsequently, the other drop weight is dropped according to FIG. 12b, possibly after ancesting the smashing device in the working direction. Accordingly, a transverse tear QR2 is formed, which is offset in the working direction A with respect to the first transverse tear QR1. The distance between the two transverse cracks is considerably smaller than the distance between adjacent transverse cracks according to FIG. 11, so that in addition a crack LR1, which runs slightly obliquely with respect to the working direction and is nevertheless referred to as a longitudinal tear, arises, which connects the two transverse cracks QR1 and QR2 with one another. The excavator then moves forward again, and the first drop weight is dropped again, so that a transverse tear QR2 and a longitudinal tear LR2 result. The procedure continues in the manner described, FIG. 12d showing a somewhat later snapshot. As indicated in Fig. 12d, the next adjacent falling positions in the working direction A of the two falling weights are so offset from one another transversely to the working direction that the falling positions lie at the break points of a zigzag line Z following the average of the working direction A.

As shown in FIGS . 12e to 12g, dropping the falling weights at falling positions of a second row, which is offset in relation to the first row according to FIG. 12d transversely to the working direction A, creates clods, each delimited by two transverse cracks and four longitudinal cracks are. The four longitudinal cracks can also be summarized as four longitudinal tear sections of two longitudinal cracks spaced apart from one another transversely to the working direction.

The foregoing makes it clear that Fig. 12 gives an explanation of an embodiment of a method for crushing concrete floors to clods by dropping two falling weights. The distance in the working direction from the next adjacent case positions in the working direction corresponds approximately to half the distance of these falling positions transverse to the working direction. In principle, however, the method can also be carried out with a smashing device with only one drop weight by corresponding movements of the smashing wagon or better by appropriate displacement of a smashing device with only one drop weight relative to the smashing wagon (e.g. by means of the excavator arm).

In summary, the present invention relates to a sub ground smashers, in particular concrete floor smashers with a chassis wreck and one Smashing device with at least one drop weight. According to one aspect, a detachable coupling device is between a drive element lifting the drop weight and the drop suggested weight. In another aspect, they are invented According to the invention, at least two against a working direction drop weights offset from each other. The Erfin dung also relates to a method for crushing concrete cover to clods by dropping at least one Falling weight that is on in one working direction from each other spaced fall positions dropped on the concrete surface becomes. According to the invention, they are next in the working direction neighboring case positions so transverse to the working direction offset from each other that the drop positions at the kink score at least one on average follow the direction of work the zigzag line.

Claims (34)

1. A method for smashing concrete ceilings into clods by dropping at least one falling weight, in particular at least two falling weights (G1, G2, G3; G1, G2), the at least one falling weight at falling positions on the concrete spaced apart in a working direction (A) blanket is dropped, characterized in that the next adjacent falling positions in the working direction are offset from one another transversely to the working direction (A) in such a way that the falling positions at the break points of at least one zigzag line (Z1, Z2; Z) following the working direction on average lie, the inflection points are chosen such that ceiling clods with relatively similar dimensions arise, in particular relatively small-area ceiling clods. 2. The method according to claim 1, characterized in that the Distance in working direction (A) from next in working direction neighboring case positions about half to double the Distance across the working direction (A) of these drop positions corresponds, preferably ver in these case positions different drop weights are dropped. 3. The method according to claim 2, characterized in that in Working direction alternating two be at approximately the same height moved to the work direction, across the work direction of mutually offset case positions of the first kind  and one transverse to the working direction approximately in the middle between case position of the second type lying on these case positions follow each other. 4. The method according to claim 3, characterized in that to at least during most of the process a drop weight (G1; G2) at a respective drop position is only dropped when this Fall position in opposite directions next bear drop positions of the second kind already a drop weight (G) has been dropped. 5. The method according to claim 3 or 4, characterized in that the two at about the same level based on the work direction of the case type of the first kind, one case each weight (G1; G2) of the first type is assigned and which is transverse to Working direction approximately in the middle between these case posi fall position of the second type a drop weight (G3) is assigned to the second type. 6. The method according to claim 5, characterized in that a Fall weight (G1; G2) of the first type about half as heavy to about Three quarters as heavy, preferably about two thirds as heavy heavy as a falling weight (G3) of the second kind. 7. Underground smashers, in particular for use in the method according to one of claims 1 to 6, in particular concrete ceiling smashers, comprising:

• 1. a smashing carriage ( 12 ) having a chassis ( 18 ),
• 2. A carried by Zertrümmererwagen (12) fragmenter device (30) having at least two case weights (G1, G2, G3), at least approximately device in a working position of the Zertrümme (30) in a drop-weight guide (33 a, b; 34 a, b ; 32 a, b) of the shattering device ( 30 ) are mounted so as to be displaceable essentially in the vertical direction, the drop weights (G1; G2; G3) each having a lifting and triggering device ( 77 , 82 , 106 ; 78 , 83 , 107 ; 79 , 84 , 108 ) is assigned for lifting the respective drop weight by means of at least one drive element ( 77 ; 78 ; 79 ) acting on the drop weight into a maximum lifting position and for dropping the drop weight from the maximum lifting position onto a surface (U), in particular one Concrete ceiling, in the working position of the shattering device ( 30 ),

wherein the smashing device ( 30 ) has at least two falling weights (G1; G2; G3) laterally offset relative to a working direction (A), in particular the direction of travel (F) of the smashing carriage ( 12 ),
characterized,
that at least two (G1, G3; G2, G3) of the laterally offset drop weights (G1, G2, G3) are also offset against each other in the working direction. 8. subsoiler according to claim 7, characterized records that at least two (G1, G2) of the ver put drop weights (G1, G2, G3) at the same height in Working direction are arranged, and that the this case weight assigned lifting and triggering devices are designed so that the drop weights with time Distance from each other and thus with an ancestor of the Zer debris in the working direction on each other in working Directionally spaced areas on the subsurface can be let. 9. subsoiler according to claim 7 or 8, characterized ge indicates that the smashing device as a whole has three drop weights (G1, G2, G3) at the corners an essentially isosceles triangle with Working direction (A) essentially orthogonal triangle base are arranged. 10. Underground smasher according to claim 9, characterized in that each drop weight (G1, G2, G3) is assigned a separate drive element ( 77 ; 78 ; 79 ), these drive elements to a common drive device, in particular at least one hydraulic motor ( 52 a , b), the destruction device ( 30 ) can be driven. 11. Underground smasher according to claim 10, characterized in that the drive elements guided in a respective closed loop ( 77 , 78 , 79 ) are coupled in motion and are preferably drivable at a substantially constant speed. 12. subsoiler according to claim 11, characterized in that the drivers ( 82 , 83 , 84 ) are arranged on the drive elements ( 77 , 78 , 79 ) in such a way that a maximum of two (G1, G2) of the three falling weights (G1, G2 , G3) can be raised simultaneously. 13. Untergrundzertrümmerer according to claim 12, characterized in that the drivers ( 82 , 83 , 84 ) are arranged on the drive elements such that the two falling weights arranged on the triangular base (G1, G2) simultaneously and with that at the triangle tip arranged drop weight (G3) alternately raised and dropped. 14. Underground smasher according to claim 13, characterized net that the two Fallge arranged at the triangle base weights (G1, G2) each about half as heavy to about three a quarter as heavy, preferably about two thirds as heavy, like the drop weight at the top of the triangle (G3) are. 15. Underground smasher according to one of claims 9 to 14, characterized in that the drop weights (G1, G2) on the Triangular base one for creating cracks in Ar in the underground direction of impact head (K1; K2), in particular an impact head with a impact edge extending in the working direction, and  that the falling weight at the top of the triangle (G3) one to Er generation of cracks across the working direction in the subsurface trained impact head (K3), in particular one Service head with a cross to the working direction stretching edge. 16. Underground smasher, in particular for use in the method according to one of claims 1 to 6, in particular concrete ceiling smashers, comprising:

• 1. a smashing carriage ( 12 ) having a chassis ( 18 ),
• 2. A carried by Zertrümmererwagen (12) fragmenter device (30) having at least two case weights (G1, G2, G3), at least approximately device in a working position of the Zertrümme (30) in a drop-weight guide (33 a, b; 34 a, b ; 32 a, b) of the shattering device ( 30 ) are mounted so as to be displaceable essentially in the vertical direction, the drop weights (G1; G2; G3) each having a lifting and triggering device ( 77 , 82 , 106 ; 78 , 83 , 107 ; 79 , 84 , 108 ) is assigned to lift the respective drop weight by means of at least one attack on the drop weight of the drive elements ( 77 ; 78 ; 79 ) in a maximum lifting position and to drop the drop weight from the maximum lifting position onto a surface (U) , in particular a concrete ceiling, in the working position of the shattering device ( 30 ),

wherein the smashing device ( 30 ) has at least two falling weights (G1; G2; G3) laterally offset relative to a working direction (A), in particular the direction of travel (F) of the smashing carriage ( 12 ),
at least two (G1, G2) of the laterally offset case weights (G1, G2, G3) are arranged at the same height in the working direction,
characterized,
that the this at the same height in the working direction NED falling weights (G1, G2) assigned lifting and triggering devices ( 77 , 82 , 106 ; 78 , 83 , 107 ) are formed out such that the falling weights (G1, G2) with defined and during continuous operation of the associated lifting and triggering device ( 77 , 82 , 106 ; 78 , 83 , 107 ) constant distance from each other and thus with an ancestor of the smashing device in the working direction can be dropped onto the ground at points defined in the working direction can. 17. Underground smashing device according to one of claims 7 to 16, characterized in that between the drop weights (G1, G2, G3) and the at least one drive element ( 77 ; 78 ; 79 ) engaging thereon a releasable coupling device ( 82 , 85 ; 83 , 86 ; 84 , 87 ) is provided. 18. Underground smasher according to claim 17, characterized in that the coupling device comprises at least one driver ( 82 ; 83 ; 84 ) on the elongated drive element, in particular conveyor chain ( 77 , 78 ; 79 ), which weights with the case (G1; G2; G3) for establishing the coupling connection between the drive element and the drop weight, in particular via a driving element, possibly driving pins ( 85 ; 86 ; 87 ) of the falling weight interacts. 19. Underground smasher according to claim 18, characterized net that the driver by appropriate back and forth tion of the drive element between a lower coupling position tion in which the coupling connection, if necessary by locking with the driving element, can be produced, and an upper one Decoupling position, in which the coupling connection can be released, is movable whereby in the case of establishing the coupling connection by Locking the driving element and / or the driver before are preferably wedge-shaped. 20. Underground smasher according to claim 18, characterized in that the driver ( 82 ; 83 ; 84 ) by moving in the same direction of the drive element guided in a closed loop ( 77 ; 78 ; 79 ) between a lower coupling position in which the coupling connection, in particular by gripping the driver under the driver element ( 85 ; 86 ; 87 ), and an upper decoupling position in which the coupling connection can be released can be moved. 21. Underground smasher according to claim 19 or 20, characterized in that the maximum stroke position of the falling weight (G1; G2; G3) is adjustable by vertical displacement of the decoupling position of the driver ( 82 ; 83 ; 84 ) and / or by vertical displacement of the driving element ( 85 ; 86 ; 87 ) on falling weight. 22. Underground smasher according to claim 19, 20 or 21, characterized in that the driver and / or the Mitnahmele element ( 85 ; 86 ; 87 ) associated decoupling means ( 106 a, b; 107 a, b; 108 a, b) are provided that forcibly loosen the coupling connection in the decoupling position of the driver ( 82 ; 83 ; 84 ). 23. Underground smasher according to one of claims 19 to 22, characterized in that the driving element ( 85 ; 86 ; 87 ) between a coupling position in which the coupling connection can be established, and a release position in which the coupling connection is released or cannot be produced , on the case weight (G1; G2; G3) is movably mounted. 24. The subsoiler according to claim 23, characterized in that the entrainment element ( 85 ; 86 ; 87 ) is prestressed into the coupling position by spring means ( 88 ), the decoupling means ( 106 a, b; 107 a, b; 108 ) which may be provided a, b) bring the driving element to the release position to release the coupling connection. 25. Underground smashers according to claim 22 and 24, characterized in that the decoupling means at least one control curve ( 33 a, b; 34 a, b; 32 a, b) with a release curve section ( 106 a, b; 107 a, b ; 108 a, b) on the drop weight guide ( 33 a, b; 34 a, b; 32 a, b), with the possibly relocable in the vertical direction, the decoupling position of the driver ( 82 ; 83 ; 84 ) defining the trigger curve section ( 106 a, b; 107 a, b; 108 a, b) acts on the driving element in the decoupling position of the driver and brings this to the release position to release the coupling connection. 26. Underground smasher according to claim 25, characterized in that the driving element ( 85 ; 86 ; 87 ) from a first, the driver ( 82 ; 83 ; 84 ) facing drop weight side ( 51 ) to a second case away from the driver Weight side ( 52 ) through the falling weight (G1; G2; G3) extends through and at its end lying away from the driver scanning means ( 103a , b; 104 a, b; 105 a, b) for scanning the control curve ( 33 a, b; 34 a, b; 35 a, b), the driving element in the release position relative to the coupling position, in which it projects beyond the first falling weight side, preferably being displaced in the direction of the second falling weight side. 27. The subsoiler according to claim 26, characterized in that the first drop weight side (S1) defines a longitudinal groove ( 90 ; 91 ; 92 ) extending in the vertical direction in the drop weight (G1; G2; G3) into which the driving element ( 85 ; 86 ; 87 ) protrudes at least in the coupling position and in which the driver ( 82 ; 83 ; 84 ) is at least partially arranged when the drop weight is raised. 28. Underground smasher according to claim 26 or 27, characterized in that the scanning means comprise at least one scanning roller rolling on the respective control cam ( 103 a, b; 104 a, b; 105 a, b). 29. Underground smasher according to one of claims 7 to 28, there characterized in that the falling weight (G1; G2; G3) a exchangeable service head (K1; K2; K3).   30. Underground smasher according to one of claims 7 to 29, characterized in that the smasher wagon is a self-propelled wagon ( 12 ). 31. Underground smasher according to claim 30, characterized in that the smasher wagon is an excavator ( 12 ), which optionally has a hydraulic pump, preferably driven by the excavator motor, for driving the at least one hydraulic motor ( 52 a, b) of the smashing device ( 30 ). 32. Underground smasher according to claim 31, characterized in that the smashing device is attached to a boom of the excavator, in particular on a hydraulically movable excavator arm ( 20 ) instead of an excavator shovel or the like. 33. Untergrundzertrümmerer according to claim 32, characterized net gekennzeich that the excavator (12) comprises the landing gear, in particular as a bead (18) formed chassis having chassis (16) and one on the undercarriage is rotatably mounted, the boom (20) having upper carriage (14 ) includes. 34. Shattering device with features according to at least one of claims 7 to 29, in particular for use in the method according to one of claims 1 to 6, for mounting on a driving device serving as a shattering vehicle, possibly a truck or preferably a construction machine such as an excavator ( 12 ) or the like.