FR2808261A1 - Rapid changer for multi-grab gripper has grabs pivotably located on support and central support connectable at one end with gripper suspension, having adapter at its other end - Google Patents

Abstract

The rapid changer has grabs (5) pivotably located on a support (8), with a central support (2) connectable at one end with a gripper suspension (3) and having an adapter (6) at its other end. The adapter can be coupled with the grab support. Several pressure fluid piston cylinder units (4) are provided for opening and closing the grabs. The pressure fluid piston cylinder units with one of their ends are pivotably linked to the central support or the gripper suspension and with their other end with the grabs. The grabs have coupling units (17), to which the pressure fluid piston cylinder units can be coupled. A cylinder centering unit (32), on coupling the adapter in the grab support, automatically centers the pressure fluid piston cylinder units accurately in relation to the coupling units.

Description

The present invention relates to a fast changer for multihull grapples whose grapple hulls are pivotally housed to a hull support. The present invention further relates to a multihull grapple for such a fast changer, with a hull support which is housed in a pivotal manner the grapple hooks of the multihull grapple. Finally, the invention relates to a load crossbar for such a fast changer.

Fast changers for multihull grabs are known, for example, from EP 0 728 874A2 or DE 19643892A. grapple hulls of a multihull grapple usually have cross members which are connected to pivoting levers of a hull support such that the grapple hulls are pivotally accommodated to the hull support and can be brought in a manner corresponding in an open and closed state. In the known fast changers, the entire hull support can be uncoupled from the ties of the grapple hulls and be coupled thereto. As a result, only one shell support is required which can be coupled to different grapple hulls of different widths.

Fast changers can be perfected in many ways. It is thus desirable, for example in the case of narrow grapple hulls, to be able to use an ejector to eject sticky materials, which has not been satisfactorily solved so far in the known fast changers. In addition, it is necessary to seek to improve the rigidity of the overall arrangement since the current fast changers which must be configured according to the narrowest hull to use, do not confer the required rigidity large grapple hulls .

The present invention therefore relates to the creation of an improved fast changer for multihull grapples of the indicated, an improved multihull grapple for such a fast changer and an improved load crossbar for such a fast changer that avoid the known disadvantages of the prior art. These include creating a layout that can be operated in a simple and safe manner that gives the grapple hulls great rigidity and stability.

According to the invention, this object is achieved by a fast changer of the type indicated at the beginning with a central support which can be connected at one of its ends to a grapple suspension and which has at its other end an adapter which can to be coupled with the hull support, a plurality of pressurized fluid cylinder piston units for opening and closing the grapple hulls which are connected at one end to the central support or the grapple suspension and which may be coupled with their other end with the grapple hulls, which are associated with the grapple hulls coupling units in which can be coupled the piston units and pressurized fluid cylinder, and a centering cylinder installation which, when coupling the adapter into the hull support, automatically centers piston units and pressurized fluid cylinder in a manner is well adjusted for mating units.

Therefore, it is not the entire support hulls that is uncoupled from the grapple hulls and coupled to them. The point of separation is higher, in particular a central point of separation between the adapter and the hull support and other points of separation between the grapple hull end ends of the piston and cylinder units. pressurized fluid and the respective grapple hulls. Each multihull grapple has its individual hull support, and in particular for grapple hulls of a different width, also supports hulls of a different width can be provided. This makes it possible to achieve a greater rigidity of the entire construction, especially in large areas of cutting width since the support width of the shell support does not need to be oriented to the hull of narrowest grapple.

The fast changer according to the invention is particularly characterized in that. pre-positioning of the piston and pressurized fluid cylinder units during coupling is provided. Using the cylinder centering system, the piston and pressurized fluid cylinder units can be snugly fitted into the coupling units on the grapple hull side. They are positioned in particular so that the coupling units can be locked without further manipulation. This allows operation with an operator, since it is only necessary for one person to position the pressurized fluid piston and cylinder units and another person to depress the lock bolt or the like. In particular, the prepositioning of the piston and pressurized fluid cylinder units eliminates the need for manipulation inside the grapple hulls as well as a reciprocating movement with a fast changer, which eliminates the risk of corresponding accident and greatly enhances safety.

According to a further development of the invention, the prior positioning of the piston units and pressurized fluid cylinder can be achieved by stops against which the piston and pressurized fluid cylinder units can be applied when the fast changer is in the uncoupled state. The stops can be realized at the central support. As a result of the gravity, piston and pressurized-fluid cylinder units are pivotally hinged above the stops and pushed against the stops so that the pressurized fluid piston and cylinder units occupy a defined position relative to the central support. By exact prior positioning relative to the central support, piston and pressurized-fluid cylinder units also occupy relative to the desired defined-position grapple hulls as soon as the quick-change central carrier, with its adapter, is coupled with the hull carrier. Preferably, abutments are made so that they position the piston and pressurized-fluid cylinder units in two directions in advance, namely that they predetermine, on the one hand, the pivoting position of the piston and fluid cylinder units. under pressure in the circumferential direction about their axis of pivoting upper articulation and, secondly position the piston units and fluid cylinder under pressure transversely thereto. Thus, the pressurized fluid piston and cylinder units can be pivotally hinged at their upper ends in the manner of a spherical hinge to compensate for misalignment, and despite this exact exact positioning is reached.

According to a further development of the invention, the centering installation of the cylinders is made so that it yields elastically. This avoids kinematic collisions, which could occur during a rigid realization of the centering installation. The cylinder centering device maintains, when normal forces are exerted on the piston and pressurized fluid cylinder units, in the uncoupled state of the fast changer, the piston and pressurized fluid cylinder units. a precise way in the predetermined position, in the case of large forces, the centering installation of the cylinders can however yield so that damage to the centering installation of the cylinders or piston units and fluid cylinder under pressure is avoided. On the other hand, the elastic flexibility of the pre-positioning allows a fine adjustment of the piston and cylinder units to fluid under pressure by hand, for example to contribute to the coupling of the piston units and pressurized fluid cylinder in the grapple hulls. The prior positioning of the pressurized fluid cylinder piston units can be achieved in particular by means of rubber buffers attached to the central support of the fast changer.

Preferably, an adapter centering device is provided for the fast changer center support adapter for the well-fitting centering of the adapter relative to the shell support. 1 adapter and the shell support are provided in particular complementary adjustment faces to each other which, when coupling the adapter with support shells slip on each other.

In order to reliably enable the coupling of piston and pressurized fluid cylinder units with grapple hulls and to be able to do this in a substantially automatic manner, guide faces may be provided in accordance with a further development of the invention. to the coupling units provided at the side of the grapple hulls along which pressurized piston and cylinder units can slide in their respective locking positions. In particular, the coupling units can be arranged directly to the crosspieces of the grapple shells so that the crosspieces form guiding faces to improve coupling. Preferably, guide faces extending transversely to the crosspieces of the grapple shells are provided between which the pressurized fluid piston and cylinder units can slide with their grapple shell end ends in the coupling units. The aforesaid guide faces prevent the pressurized piston and cylinder units from pivoting transversely away from their main pivoting direction, i.e. along the crossties of the grapple shells.

To allow a defined return of the piston and cylinder units in coupling units provided on the side of the grapple shell, coupling stops are preferably associated therewith against which are movable the piston units and fluid cylinder pressure in their locking position. The coupling stops may suitably be formed by hollow-shaped guide plates which can be attached to corresponding cross-members of the grapple shells. With the aid of the coupling stops, uneven output of the piston and pressurized fluid cylinder units can be compensated. The coupling positions of the piston and pressurized fluid cylinder units can be hydraulically addressed even in the case where the different piston and pressurized fluid cylinder units would come out asynchronously. This allows the corresponding shovel operator to perform a single shifting tool grapple shells respectively. The fast changer, from the shovel's place, can be retracted into the corresponding grapple hull to be coupled, where all the parts to be coupled can be hydraulically brought into their coupling position. It is sufficient for the shovel to descend to lock the corresponding couplings.

According to a further development of the invention, the coupling units for piston and pressurized fluid cylinder units are each formed as integral units, free of loose or removable parts. This improves handling ability, and necessary mating parts such as bolts or the like can not be lost. The coupling of the piston and cylinder units to the grapple shells or, as the case may be, to corresponding pivoting levers of the shells support which are connected to the grapple shells, can take place in various ways. Preferably, the pressurized fluid piston and cylinder units are bolted together with the grapple hulls. According to a further development of the invention, bolt lock units are provided for locking the pressurized fluid piston and cylinder units each having a movable lock bolt and a bolt control for the entrance and exit of the locking bolt. The bolt lock units may be provided in principle to the piston and pressure fluid cylinder units themselves such that they engage in recesses corresponding to the grapple hulls. However, preferably, the bolt lock units are arranged at the side of the grapple shells. The locking bolts engage in complementary recesses at the ends of the piston and pressurized fluid cylinder units. As a result of the bolt control provided, it is not necessary to intervene with the hammer to drive the locking bolts, this is ensured by the corresponding bolt control. Preferably, the bolt lock units respectively have a locking bolt that can exit from a side that enters an eye at the end of the corresponding pressurized fluid piston and cylinder unit. Preferably, the corresponding eye of the piston and cylinder unit does not have a hinge bearing. A rigid socket for receiving the locking bolt may be provided. The absence of a hinge bearing facilitates the attainment of the recess in the eyelet of the piston and cylinder unit since rotation of such hinge bearing is excluded.

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According to a further development of the invention, the bolt lock units are arranged at the multihull grapple so that they are accessible from an outer side of the multihull grapple including through a recess in the grapple hulls. According to an embodiment of the invention, the recess can be provided or covered by a removable sheet. After removal of the sheet, the bolt lock unit can be struck through the outer wall of the multihull grapple to 1 outside, example to be able to pull it out as a whole, for example following a blocking bolt lock by rust. Thus, even a defect, clamping or rusting of the control can not permanently shut down the bolt lock unit.

According to a further development of the invention, there is also provided for the locking of an adapter to the hull support a bolt lock unit which comprises at least one bolt housed in a displaceable manner and a bolt control for the entry and the exit of the bolt. Preferably, two locking bolts arranged coaxially, movable in the opposite direction are provided. The bolt control may consist of a drive spindle which is threadingly engaged with its opposite ends with the two locking bolts so that upon rotation of the drive spindle, the locking bolts are moved in different directions. At least one of the locking bolts may have a through recess so that the drive pin is accessible through the bolt from the outside to be able to place, for example, or a crank on the drive pin.

According to a preferred embodiment of the invention, bolt lock unit is made asymmetrically so that the drive spindle is operable only from one side. In particular, the through recesses in the locking bolts can be closed by different closure screws so that the operator can actuate with his actuating tool only one of the two closure screws. In particular recess through one of the locking bolts can be closed with a hexagon socket screw, and the through recess of the other locking bolt with a closing screw with a male conductive hexagon. In a corresponding manner, the threaded spindle may have only on the side from which it is accessible, an actuating section may be coupled with a corresponding tool, such as for example a crank. This allows for a simpler configuration of the other threaded spindle.

Locking bolts that are axially displaceable can be provided in a variety of ways against rotation. A preferred embodiment of the invention consists in providing guide bolts, as security against rotation, which are fixed axially by closure screws. The guide bolts may have flattened guide faces to be able to receive greater force through these planar surfaces. Wear is thus reduced. The separate realization of the guide bolts of the safety and closing screws allows a more precise positioning of the guide bolts, which are preferably made as stepped bolts, through fitted holes and to fix them without play by the axial clamping of the bolts. these by means of the closing screws. Overall, by this embodiment, the locking bolt is adapted to receive much higher rotational torques.

The bolt lock unit for locking the adapter may be disposed at the shell support so that the locking bolts can engage in complementary locking recesses in the adapter. However, preferably, the bolt lock unit is provided to the adapter itself. In the shell support are provided corresponding bolt recesses in which the locking bolts can engage from the adapter. As a result, it is not necessary for each shell support to be provided with a clean bolt lock unit.

Preferably, it is also provided for the bolt lock unit, for the locking of the adapter, a bolt stop, in particular with a double security against an unplanned release of the locking unit to bolt, as described before.

In addition, the fast changer is advantageously characterized in that the hydraulic circuit for actuating the mechanics of the grapple hulls is provided only on the side of the fast changer so that when coupling and disconnecting the quick changer the multihull grapple, there is no coupling of hydraulic hoses or the like. This greatly facilitates and accelerates the coupling and uncoupling of the quick changer.

The invention also relates to a multihull grapple for a fast changer of the type described above, is characterized according to the invention in that it comprises a hull support which are housed in a pivotal manner the grapple hulls, in that that the hull support has a coupling part complementary to the adapter for coupling the adapter, that coupling units for coupling the piston and pressurized-fluid cylinder units are connected to the hulls of grapple, and that coupling units each have a bolt lock with a bolt loosely accommodated and a bolt drive for bolt entry and exit.

Preferably, the coupling portion for coupling the adapter may have an open centering recess to a side and a locking recess for receiving a locking bolt by which the adapter is locked with the locking portion. coupling. In particular, the centering recess and the locking recess can be arranged in a common straight line along which the adapter can be entered into the coupling portion.

The invention also relates to a load crossbar for a fast changer of the type described above which is characterized according to the invention in that it comprises a complementary coupling part to the adapter, for the coupling of 1 adapter, and recesses preferably in the form of cup or recess for receiving the shell ends of grapple piston and pressurized fluid cylinder units, which are constructed so that the pressurized piston and pressurized piston units are movable against them as a stop and are provided against a displacement transverse to their longitudinal axis.

The pressurized fluid piston and cylinder units can therefore preferably buttot end-to-end engagement without self-locking, in the manner of a compression member in the recesses corresponding to the load crossbar which prevents spacing or slippage. to the side of the piston and pressurized cylinder units. This makes it possible to exclude, on the one hand, an uncontrolled pendulum movement of the piston and pressurized fluid cylinder units during the actuation of the grapple rotation control, which considerably increases the safety. On the other hand, support similar to a compression member of the load beam by the piston and pressurized fluid cylinder units provides stability to the load beam. Conveniently, the recesses for supporting pressurized piston and fluid-press units are disposed at the load crossbar so that the cylinder centering device pre-positions the piston and fluid-cylinder units. Such pressure can be retracted automatically in a well-fitting manner into the recesses that the adapter to the central support of the fast changer has been retracted into the coupling portion of the load crossbar.

By providing a separate load crossbeam that can be quickly and easily coupled to the fast changer, inadmissible cables are prevented from being lifted and the like are mounted to the multihull grapple, especially when the multihull grapple is open, which has already caused serious accidents.

The invention will be better understood, and other objects, features, details and advantages thereof will appear more clearly in the following explanatory description made with reference to the accompanying schematic drawings given solely by way of example illustrating Embodiments of the invention and in which - Figure 1 is a perspective view of a two-hull grapple with a fast changer according to a preferred embodiment of the invention, wherein the fast changer is uncoupled from a hull support of the two-hull grapple; FIG. 2 is a perspective view of the double-hull grapple of FIG. 1, in which the fast changer is being inserted into the hull support; FIG. 3 is a perspective view of the double-hull grapple of FIG. 1, in which the fast changer is retracted with its central support in the hull support, however the piston-cylinder units are not yet coupled; - Figure 4 is a schematic front view of the two-shell grab according to the preceding figures, wherein the fast changer is coupled to the grapple hulls; - Figure 5 is a side view of the double-hook grab with the quick coupler coupled; - Figure 6 is a schematic front view of the double hull grapple similar to Figure 4, where the grapple hulls are open; FIG. 7 is a detailed perspective view of a coupling unit which is attached to the cross member of a grapple shell and which is intended for coupling of one of the piston and cylinder units into one partial cut; FIG. 8 is a detailed perspective view of the coupling unit of FIG. 7; FIG. 9 is a detailed perspective view of the fast changer of the preceding figures which shows a cylinder centering installation for prior positioning of the units; piston and cylinder; - Figure 10 is a sectional view, in perspective of the central support of the fast changer which shows the bolt lock unit for locking the central support of the fast changer to the shell support of the two-shell grapple; - Figure 11 is a schematic representation of a load crossbar which can be coupled to the fast changer according to the preceding figures; FIG. 12 is a diagrammatic perspective view of an adapter as well as of the complementary coupling part of the shell support according to another embodiment of the invention; FIG. 13 is a perspective view of a five-hull grab where the piston and crank units are not articulated to the grapple suspension, as in the previous embodiments, but to the central support of the fast changer; - Figure 14 is a sectional view, in perspective, of a bolt lock unit with a bolt stop according to an alternative embodiment of the invention; FIG. 15 is a schematic representation of a centering bolt of the fast changer according to an alternative embodiment of the invention; FIG. 16 is a partial view of a bolt lock unit for locking a piston and cylinder unit according to an alternative embodiment of the invention; Fig. 17 is a partial sectional view of a bolt lock unit similar to Fig. 16 according to an alternative embodiment of the invention; FIG. 18 is a diagrammatic representation of a bolt stop according to an alternative embodiment of the invention; 19 is a sectional view of a locking bolt with a stop screw for stopping the locking bolt according to a preferred embodiment of the invention, the stop screw being released; FIG. 20 is a sectional view of the locking bolt of FIG. 19, where the stop screw is shown in its position stopping the bolt; and Fig. 21 is a sectional view of a bolt lock unit for locking the central carrier of the fast changer to the hull support of the two-hull grapple according to another preferred embodiment of the invention. As shown in Figure 1, the fast changer comprises a central support 2 which has an oblong, beam-shaped extension and which, when in the intended orientation, extends substantially vertically. At its upper end, the central support 2 connected to a grapple suspension 3 where a not shown rotation drive device is disposed between the grapple suspension 3 and the central support 2 to rotate the central support 2 about its axis vertical. The grapple suspension 3 is hinged in the usual way in a pivoting manner with a boom of a shovel.

Laterally along the central support 2 on diametrically opposite sides thereof extend two piston and cylinder units 4 which are hinged at their upper end in a pivotal manner to the upper end of the central support 2 respectively at a rotating section of the grapple suspension 3. In the embodiment shown, the cylinder piston units 4 are articulated with their cylinders to the central support 2 respectively to rotating section of the grapple suspension 3, and piston rods are oriented towards the hull of grapple 5. This arrangement can be reversed if necessary. Preferably, however, the piston and cylinder units are mounted in the position shown such that the narrower piston rods, which are less cumbersome, are located in the vicinity of the grapple shell 5.

At the lower end, the central support has an adapter 6 which can be retracted and coupled into a coupling portion 7 formed in a complementary manner thereto of the hull support 8. The coupling portion 7 is formed by a the box-shaped head portion of the shell support 8, which has a recess complementary to the adapter 6 and which, in the embodiment shown, is made as a sheet steel construction. The adapter 6 and the corresponding recess in the head piece of the shell support 8 has complementary adjustment faces to each other along which the adapter 6 can slide in the shell support 8 and is centered relative to it.

The adapter 6 of the central support 2 has its lower end, as shown in FIGS. 9 and 10, a head piece 9 extending transversely to the longitudinal axis of the support 2 in which a bolt locking unit 10 is provided. for the locking of the adapter 6 to the shell support 8. I1 is formed in the head piece 9 a cylindrical through bore 11 extending transversely in which are housed in a longitudinally displaceable manner two locking bolts 12. The bolts 12 have themselves a tapping extending in their longitudinal direction with which they rest on opposite ends of a drive pin 13. By rotating the drive pin 13, the locking bolts 12 can be retracted and retracted to lock the adapter 6 to the head piece of the hull support 8. The head piece of the hinge support 8 has for this purpose on the opposite sides respectively a locking bore 14 in which can be retracted the locking bolts 12 (see Figure 1).

An alternative embodiment of the bolt lock unit 10 is shown in FIG. 21. The two locking bolts 12 arranged coaxially and axially displaceable in the cylindrical through bore 11, as in the embodiment described before, are threaded with opposite ends of the drive pin 13. By rotating the drive pin 13, the locking bolts 12 can be retracted and exit in the opposite direction. Unlike the embodiment described before, the drive pin 13 is operable only from one side, it has only one side a coupling section 59 to which a drive can be coupled, such as for example a crank (see Figure 21). The opposite side of the drive pin 13 may simply be cut. As a result, the bolt lock unit 10 can be operated only from one side, namely on the right side. This is also ensured by the fact that on the opposite side to the coupling section 59 of the drive pin 13, the through bore 11 is closed by a closure screw 60 for which the operator does not have a tool adapted. In particular, as a closure screw 60, a closure screw according to DIN 906 with hexagon socket may be provided. It suffices then to use a male-to-hexagon locking screw and a stop screw, respectively, formed by forming, as shown in FIG. 21 on the right-hand side.

The bolt lock unit 10 according to Fig. 21 is further characterized by axial guiding or safety against rotation of the locking bolts 12. As shown in the figure, two locking bolts 12 have on their peripheral side of the groove-shaped recesses 61 extending axially. In these are accommodated guide bolts 56 which have flattened guide faces 57 along which are guided the side walls of the grooves 61. The guide bolts 56 rest in fitted holes which are provided in the head piece 9 such that the guide bolts 56 protrude radially into the through bore 11. The adjusted bores have a step such that the guide bolts 56 which are formed as stepped bolts are applied therewith with a corresponding shoulder ( see Figure 21). The guide bolts 56 are provided with closure screws 62, in particular they are clamped axially against the corresponding shoulder of the bores adjusted so that they are fixed without play. The closure screws 62 are preferably made of a identical manner the closing screw 60 in one of the locking bolts 12. The closing of one of the locking bolts 12 by the special closing screw indicated as well as the security against a rotation respectively the axial guidance of the Each locking bolt by a guide bolt which is tightened by a separate closing screw of the type described, give particular advantages regardless of the remaining embodiment according to the invention of the fast changer. In particular, much higher rotational torques can be received which act on the locking bolt. In addition, cost savings can be made by using the described closure screw as well as by the simpler configuration of the threaded rod spindle and the locking bolt.

Above the locking bolts 12, there is provided at the central support 2 a rigid centering bolt 15 whose longitudinal axis extends parallel to the common longitudinal axis of the locking bolts 12 and projects from the opposite side of the bolt. central support 2 (see Figure 10). For receiving the centering bolt 15, the head piece of the shell support 8, in which the adapter 6 can be retracted, has centering recesses 16 open upwardly in the manner of an open oblong hole of a side. As shown in FIG. 1, the flanks of the centering recesses 16 widen in the shape of a hopper towards its open side so that the adapter 6, also in the case of misalignment, can be retracted into the The centering recesses 16 tapering towards their bottom center the centering bolt 16 during complete insertion, as shown in FIGS. 2 and 3. As soon as the adapter 6 is fully retracted into the room 8, the locking bolts 12 are released into the associated locking holes 14 so that the central support 2 is coupled and bolted with the shell support 8. To avoid excessive surface compression, the centering bolt 15 may have plates on its periphery with which it rests in the centering recesses 16 (see Figure 15).

In order to couple the piston and cylinder units 4 to the grapple shells 5, they have corresponding coupling units 17 (see FIG. 7) which are arranged at the ends of the grapple shells 5. Each of these coupling units 17 has a bolt lock unit 18, respectively with a lock bolt 19 which can be pulled out on one side which can be retracted and pulled out by a drive pin 20. The base of the bolt lock unit 18 is a tube 21 which has a continuous internal longitudinal groove. The tube 21 and therefore the bolt lock unit 18 extends parallel to the crossbar of the grapple shells 5 and is fixed to the outer side of the corresponding grapple shells 5 approximately in the lower third of the crossbar directly. to this one. In this tube 21, a spiral-shaped groove is provided at the inner side, which allows the locking bolt 19 to be lubricated. A radially axially locking pin 19 is inserted into the locking bolt 19 which serves as a protrusion on the periphery side and slides as a slider in the inner longitudinal groove of the tube 21 and prevents the rotation of the bolt 19 relative to the tube 21. The drive pin 20 is supported axially in both directions and causes by a rotational movement a return respectively out of the bolt. The axial support of the drive pin 20 is formed, on the one hand, by an annular application face corresponding to the tube 21 and, on the other hand, by a support disk 23 which is retained by a ring of safety 24 relative to the tube (see Figure 7). The drive pin 20 rests with a shoulder projecting radially between the application face and the support disc. If the locking bolt 19, for example due to corrosion due to insufficient lubrication, could no longer be actuated, it could be pulled out, by striking against it, after removing the safety ring 24. and the support disk 23, with the drive pin 20. For this purpose, there is provided in the wall of the grapple shell 5 a corresponding recess by which the support disk 23 is closed.

axial movement of the locking bolt 19 is limited firstly by a stop of the axis 22 to the bearing plate of the grapple shell 5 and, secondly, by an application to the front side with 1 side shoulder end of the drive pin 20.

As an additional safety against rotation, the locking bolt 19 may preferably have at its outlet end, on the periphery side, a planar face 25 which cooperates with a counterpart 26 corresponding to the bearing plate 27, in which can fit the locking bolt 19.

As shown in the figure, the coupling units 17 have two parallel spaced parallel bearing plates 27 which extend perpendicularly to the longitudinal axis of the respective cross member at a distance from each other. it. Between these two bearing plates 27 can be inserted the eyelet end of the piston rod of the piston unit and cylinder 4. The bearing plates 7 form in this case lateral guides that prevent a push off of the piston rod during coupling, for example by the outgoing bolt.

retraction of the ends of the piston rods of the piston unit and cylinder 4 in the coupling units 17, that is to say between the two bearing plates 27, is facilitated by the peripheral faces of the crosspieces 29 which form the guide faces 30 for piston and cylinder units 4.

Below each locking bolt 19 is provided respectively a stop plate 31 against which the end of the respective piston rod can be brought and which defines the coupling position of the corresponding piston rod (see FIG. 7). As a whole, the housing of the coupling units 17 for the ends of the piston rods is hollow-shaped so that the piston-and-cylinder unit 4, for coupling purposes, can be retracted from the piston. hydraulically in the coupling unit 17.

In order to be able to retract the piston and cylinder unit automatically in a well-targeted manner into the coupling unit 17 on the grapple hull side, there is provided to the central support 2 a cylinder centering unit As shown in FIG. 9 respectively, two rubber buffers 33 are fixed at a distance from each other to the central support 2 at its sides facing the piston and cylinder unit 4, against which the piston units and As a result, the piston and cylinder units 4 are pre-positioned so that the piston rods, on exit, come into precise contact with the coupling units 17.

The grapple hulls 5 are permanently interconnected by bolts which are pivotally housed in the hull support 8 and by a connecting rod which is not shown in more detail. The shell support 8 may advantageously be made in different shell widths to achieve, in a manner corresponding to the grapple shell width 5, greater rigidity. The coupling of the fast changer 1 to the grapple 5 can best be achieved when the grapple shells 5 are closed, if necessary also when the grapple shells 5 are open, preferably in the working position according to the planning. The adapter 6 is first, according to Figure 1, approximately 500 mm vertically above the shell support 8. The piston and cylinder units 4 and the locking bolts 12 to the adapter 6 as well as the locking bolts to the coupling units 17 are first fully retracted. The adapter 6 is now oriented so that a color marking 34 on the front side of the rigid centering bolt 15 is oriented towards the side of the grapple shells 5 from which will be used crank, ie are actuated the bolt locking units 10 and 18. This saves the worker later a lock on both sides. The adapter 6 is now inserted into the shell support 8 until the rigid upper centering bolt 15 is flush with the corresponding contour of the shell support 8. Now, by the grapple closing function, the two Piston and cylinder units 4 are out. By the rubber buffers 33 screwed laterally to a flange plate the piston and cylinder units 4 are positioned beforehand in a predetermined angular position for the eyelets of the piston rods first slide the bearing plate respectively the crosspiece 29 of the shells 5, so that they can be pulled out to the two abutment plates 31. They are then retracted in a suitable manner by a brief actuation of the grapple opening function 1 up to 2 mm and are made without pressure so that the bolt lock units can then be locked. For this purpose, the shovel actuates, by crank rotation, the drive pins 13 and 20 of the corresponding bolt lock units 10 and 18. Then, the lock bolts 12 and 19 are stopped to prevent unplanned release of the latches. interlocks.

Bolt stops 36 are provided for this purpose for each of the locking bolts. According to a preferred embodiment of the invention (see Figures 19 and 20), a stop screw 7 can be screwed into the end of the respective locking bolt 12 or 19 opposite to the drive spindle. The stop screw 37 prevents in the screwed state that drive pin is screwed into the respective locking bolt and therefore, that the locking bolt is retracted. As shown in Figure 19 it is provided as double security in addition to a fixture arrangement for matching the shapes for the stop screw 37 which is designed as a latching mechanism. a safety ring 38 which rests in a recess the through recess 40 of the respective locking bolt 12 or 19, the stop screw 37 is held in its end position. To this end, the stop screw 37 also has a notch on the periphery side 41 which, in the final position of the stop screw 37, comes to lie in front of the bolt-side cut 39 so that the ring Elastic safety device 38 can engage. The rotation torque required to rotate out the stop screw 37 is adjusted by the configuration of the shape of the notch 41 to the stop screw 37 and the prestressing force of the safety ring 38. The ring safety device 38 can be made not only as a ring, but also as a rectangular ring or other suitable elastic element for example in the form of a clamp.

In place of the safety ring 38, also an elastic pressure piece may be provided. As shown in Fig. 14, an axle 42 may be displaceably received in a radially extending bore 43. I1 is biased by a spring 44 and is prestressed towards the screw stop 37 for, at a corresponding position of the stop screw, snap into a groove on the periphery side (see Figure 14).

In the embodiment of the stop screw 37 shown in Fig. 19, the safety ring 38, when the stop screw 37 is unscrewed, can remain in the locking bolt 12 or 19. It is also possible that the safety ring 38 remains in the notch 41 formed as an annular groove of the stop screw 37.

As a stop security, according to a further embodiment of the invention, it is also possible to act directly on the drive pin 13 respectively 20 to prevent rotation thereof. As shown in FIG. 18, in particular a form-locking lock 46 may be engaged in locking engagement with the actuating portion 45 of the drive pin. The actuating portion 45 of the drive pin, in the embodiment shown, is in the form of hexagon and is used for the interlocking of a crank which rotates the drive pin. Blocking 46 is preferably made as a rocking lever which can be pushed with a locking section complementary to the actuating portion 45 thereon. It is intended for this purpose a solicitation by spring.

As shown in FIGS. 7 and 10, the actuating portion 45 of the drive pin 13 and is formed respectively at a front end of the drive pin which fits respectively in the corresponding locking bolt 12 or 19. The Actuating portion 45 is actuated through the locking bolt, i.e. through the through-holes formed therein. According to another embodiment of the invention, which is shown in Fig. 17, the driving portion 45 of the driving pin may also be provided at the remote ends of the locking bolt. This embodiment is particularly suitable in the case of locking bolts 19 coming out only one side which are mounted at the side of the grapple hulls. Thus, the actuating portion 45 of the drive pin 20, if necessary protruding through the bearing disc 23, can be actuated from the outside, ie through the side wall of the grapple shells. .

To ensure the locking bolts 12 and 19 against rotation, they may have at their outer periphery a longitudinal groove 47, as shown in the embodiment according to Figure 16. A projection 48 projecting from the radially inward receiving bore, in particular a screw, engages in the manner of a slider in the longitudinal groove 47 so that rotation of the locking bolt is prevented.

The longitudinal groove 47 is preferably made in both directions as a blind groove so that at the same time the maximum displacement path of the locking bolts is limited. It is particularly advantageous that the screw 48 can be simply unscrewed to release the locking bolts, for example during a jamming of the drive pin.

However, in particular for the bolt-hook bolt lock units 18, the embodiment shown in FIG. 17 with a longitudinal groove made in the tube 21 is advantageous since the locking bolts do not have

need <SEP> of <SEP> present <SEP> of <SEP> groove <SEP> to <SEP> their <SEP> perimeter, <SEP> which <SEP> is
<tb> would <SEP> quickly <SEP> precisely <SEP> in <SEP> the <SEP><SEP> area exposed <SEP> to
<tb> cracks <SEP> of <SEP> shells <SEP> of <SEP> grapple.
<tb> As <SEP> the <SEP> show <SEP> the <SEP> figures <SEP> 1 <SEP> to <SEP> in <SEP> the
<tb><SEP> described <SEP> realization of the <SEP> fast <SEP><SEP> changer 1, <SEP> a <SEP> ejector <SEP> 49
<tb> can <SEP> be <SEP> willing <SEP> of a <SEP> simple <SEP> way. <SEP> By <SEP> the
<tb> realization <SEP> special <SEP> of the <SEP> changer <SEP> fast <SEP> 1, <SEP> the ejector <SEP> 49 can be fixed to the support of shells 8. An ejector is particularly advantageous for smaller hulls, for example with a hull width of 400 to mm given these small hulls tend to accumulate sticky materials.

Furthermore, the fast changer 1 is characterized in that a separate load beam 50 can be coupled in place of the grapple shell to the central support 2. In particular, the load beam is locked only by the locking unit. bolt 10 in the head piece of the adapter 6 of the central support 2 with it. The load crossbar 50 has for this purpose a coupling portion 51 complementary to the adapter 6 which is made exactly as the coupling portion 7 shell support and wherein the adapter 6 can be retracted in a corresponding manner.

furthermore, the load beam 50 has two cup-shaped recesses 52 each symmetrically spaced from the coupling part 51 which are open upwards, that is to say to cylinder piston units 4 (see Figure 11). recesses 52 form a forced guide for the two piston and cylinder units 4 which, after coupling passes through load 50 to the central support 2, can enter the recesses 52 and come against them as a stop. The recesses 52 secure the lower ends of the piston and cylinder units 4 against pivoting to the side to exclude an uncontrolled pendulum movement upon actuation of the grapple rotation drive which greatly enhances safety. In addition, retraction in the manner of a compression member of the piston and cylinder units 4 in the recesses 52 gives the suspension of the load crossbar 50 additional stability.

Advantageously, it is to all of the remaining grapple mechanics of the fast changer 1 no load hook so that the worker is not trying to pass a stop or strike means to through the semi-open grapple hulls and to strike them at another location at the fast changer 1. The load beam 50 has a central load hook which is aligned with the longitudinal axis of the central support 2, as well as hooks of load 54 protruding towards the sides which are arranged preferably all four rectangle so that, for example, during pipe laying work, exact positioning of the pipes is possible. Through the various load hooks of the load crossbar 50, the abutment or striking stop means can be individually adapted to the case of respective load lifting (see Figure 11).

An alternative embodiment of the adapter 6 of the central support 2 of the fast changer 1 is shown in Fig. 12. The rigid upper bolt 15 is omitted in this embodiment. The lateral guidance between the adapter 6 and the shell support 8 is achieved by a four-sided adaptation. The adapter 6 has adjustment faces 55 opposed in pairs symmetrically to a plane across the longitudinal axis of the bolt lock unit 10 which, upon retraction of the adapter 6 into the coupling part 7 of the shell support 8 cooperate with complementary adjusting faces made therein and center the adapter 6 relative to the shell support 8. The bolt locking unit can be made as in the embodiment of the adapter 6 according to Figures 1 to 10.

Figure 13 shows another embodiment of the fast changer 1 where it is coupled with a four hooks grapple. In a corresponding manner, four piston and cylinder units are provided to open the different hulls. Unlike the embodiment described before the fast changer according to Figures 1 to 10, the piston and cylinder units 4 are pivotally articulated here directly to the central support 2 so that it can be separated with the piston and cylinder units 4 of the grapple suspension 3. The centering installation of the cylinders for the prior positioning of the piston and cylinder units 4 is not shown in more detail in FIG. 13.

Claims (1)

<U> CLAIMS </ U> 1. Fast changer for multihull grabs, characterized in that grapple shells (5) are pivotally housed to a hull support (8), with a central support (2) which can be connected at one of its ends to a grapple suspension (3) and which has at its other end an adapter (6) which can be coupled with the hull support (8), a plurality of piston and cylinder pressurized fluid (4) to open close the grapple shells which are connected at one end to the central support (2) or the grapple suspension (3) and which can be coupled with their other end with the grapple hulls (5) which are associated with the grapple hulls (5) coupling units (17) in which can be coupled the piston units and pressurized fluid cylinder (4), and an installation centering cylinder (3) which, when coupling the adapter (6) in the shell carrier (8), automatically centers the pressurized piston and cylinder units in a well-fitting manner relative to the coupling units (17). 2. Fast changer according to claim 1, characterized in that the cylinder centering device (32) has stops (33) against which the piston units and pressurized fluid cylinder (4) are pushed by the gravity , where the stops (33) are preferably fixed to the central support (2). 3. Fast changer according to one of claims 1 or 2, characterized in that the cylinder centering installation is performed to yield elastically. 4. Fast changer according to one of the preceding claims, characterized in that an adapter centering device (15, 16; 55) is provided for centering the adapter (6) in a closely fitting position relative to the shell support ( 8), which preferably consists of adjustment faces complementary to the adapter and the shell support. Fast changer according to one of the preceding claims, characterized in that associated with the coupling units (17) for the pressurized fluid piston and cylinder units (4) are guide faces (30) along which pressurized piston and cylinder units (4) can slide into their respective locking positions. Fast changer according to one of the preceding claims, characterized in that coupling stops (31) are associated with the coupling units (17) for the pressurized piston and cylinder units against which the units piston and pressurized fluid cylinder (4) can be moved to their locking position. Fast changer according to one of the preceding claims, characterized in that the coupling units (17) for pressurized-fluid piston and cylinder units (4) are each formed as an integral unit free from loose parts, which can to be removed. Fast changer according to one of the preceding claims, characterized in that bolt locking units (for locking the piston and pressurized fluid cylinder units (4) are provided which each have a locking bolt (19). ) movably accommodated and a bolt control (20) for the entry and exit of the locking bolt (19) 9. Fast changer according to the preceding claim, characterized in that the bolt control has a pin of drive (20) which is screwingly engaged with the respective locking bolt (19) and which is rotatably housed axially fixed 10. Fast changer according to one of the preceding claims, characterized in that there is provided a bolt lock unit (10) for locking the adapter (6) to the shell carrier (8) which has at least one movable lock bolt (12) and a control gear e bolt (13) for the entry and exit of the locking bolt (12). . Fast changer according to one of the preceding claims, characterized in that two locking bolts (12) arranged coaxially, which are displaceable in the opposite direction, are provided, and that the bolt drive has a driving pin (13) which is engaged screwing with the two locking bolts (12) so that during a rotation of the drive pin (13), the locking bolts (12) are moved in the opposite direction. Fast changer according to the preceding claim, characterized in that the drive pin (13) is operable through a recess in one of the locking bolts (12), preferably only from one side of the unit bolt lock (10). 13. Fast changer according to one of claims 8 to 12, characterized in that a bolt stop (35) is provided for stopping the locking bolts (12; 19) in their respective locking positions, which can be preferably provided in a position blocking the bolt control (13; 20), wherein is provided in particular respectively a stop screw (37) screwable in the respective locking bolt (12;  19) and preferably a fixing device (38) in particular by matching shapes to fix

    the <SEP> stop of <SEP> <SEP> (36) <SEP> bolt in <SEP> its <SEP> <SEP> stopping position. <tb> 14. <SEP> Fast <SEP> Changer <SEP> According to <SEP> One <SEP> of <SEP> Claims <tb> 8 <SEP> to <SEP> 13, <SEP> characterized <SEP> in <SEP> this <SEP> only <SEP> <SEP> <SEP> bolts of <SEP> lock <tb> (12) <SEP> are <SEP> assured <SEP> to <SEP> against <SEP> of <SEP> rotation <SEP> by <SEP> a <tb> bolt <SEP> of <SEP> guidance <SEP> (56) <SEP> of <SEP> preference <SEP> with <SEP> of <SEP> faces <SEP> of <tb> guidance <SEP> flattened <SEP> (57), <SEP> where <SEP> of <SEP> preference <SEP> the <SEP> guide bolts <SEP> (56) are fixed axially again by screws separate closure (62). 15. Fast changer according to one of claims 14, characterized in that the bolt lock units (10; 18) including the bolt control; are made so that they can be removed. 16. Rapid changer according to one of claims 14, characterized in that the bolt locking units (10 18) are accessible from an outer side of the multihull grapple, in particular through a recess in the hull support (8). respectively grapple hulls (5). 17. Fast changer according to one of the preceding claims, characterized in that there is provided between the fast changer (1) and the multihull hook only a bolt lock (10) between 'adapter (6) and the hull support (8) and respectively a bolt lock (18) of each pressurized piston and cylinder units (4) relative to the grapple hulls (5). Fast changer according to one of the preceding claims, characterized in that a hydraulic circuit for the actuation of the grapple shells (5) is arranged only on the side of the central support (2) so that the quick changer ( 1), free of hydraulic couplings, can be coupled to the multihull grapple. Fast changer according to one of the preceding claims, characterized in that the pressurized fluid piston and cylinder units (4) at their shell ends are free of articulation bearings, and in particular rigid bushing for receiving locking bolts. 20. Fast changer according to one of the preceding claims, characterized in that a separate load cross member (50) can be coupled which has a coupling portion (51) complementary to the adapter (6), for the coupling the adapter (6) and preferably cup-shaped recesses (52) for receiving ends of the pressurized piston and cylinder units (4) such that the fluid cylinder piston units under pressure (4) engage with their ends in the housing (52) and rely on it in the manner of a workpiece compression. 21. A multi-hull grab for a fast changer according to one of the preceding claims, characterized in that it comprises a hull support (8) to which are pivotally housed the grapple hulls (5), which the support of shells (8) has a coupling part (7) complementary to the adapter (6) for coupling the adapter (6), in that coupling units (17) for coupling the piston and pressurized fluid cylinder (4) are attached to the grapple hulls (5) and in that the coupling units (17) each have a bolt lock (18) with a locking bolt (9) housed in a displaceable manner and a bolt control (20) for bolt entry and exit. 22. A multi-hull grab according to the preceding claim, characterized in that guide faces for introducing the pressurized fluid piston and cylinder units (4) into the coupling units are attached to the grapple hulls (5), being formed in particular by sleepers (29) of grapple hulls (5). 23. A multi-hull grapple according to one of the preceding claims, characterized in that stops (31) for the grapple hull ends of the piston and pressurized-fluid cylinder units (4) are arranged in such a way that they position the pressurized piston and cylinder units (4) in a well-fitting manner for coupling into the units

    mating <SEP> (17), <SEP> <SEP> being <SEP> arranged <SEP> in particular <SEP> to <SEP> la <tb> crosses <SEP> <B> (29) <SEP> of the <SEP> <SEP> shells of <SEP> grapple <SEP> (5). <tb> 24. <SEP> Grapple <SEP> multihull <SEP> according to <SEP> one <SEP> of <tb> previous <SEP> claims, <SEP> characterized <SEP> in <SEP> this <SEP> la <tb> part <SEP> of coupling <SEP> (7) <SEP> for <SEP> <SEP> coupling of <tb> adapter <SEP> (6) <SEP> presents <SEP> a <SEP> recess <SEP> of <SEP> centering <SEP> (16) <tb> open <SEP> to <SEP> a <SEP> side <SEP> and <SEP> a <SEP> recess <SEP> of <SEP> lock <SEP> (14) <tb> for <SEP> <SEP> receiving <SEP> of a <SEP> <SEP> bolt of <SEP> <SEP> locking (12). <tb> 25. <SEP> Traverse <SEP> of <SEP> Load <SEP> for <SEP> a <SEP> Fast <SEP> Changer <tb> according to <SEP> one <SEP> of <SEP> previous <SEP> claims, <SEP> characterized <tb> in <SEP> this <SEP> 'it <SEP> contains <SEP> a <SEP> part <SEP> of <SEP> mating (51) <tb> complementary <SEP> to <SEP> the adapter <SEP> (6), <SEP> for <SEP> the <SEP> coupling of <tb> the <SEP> (6) <SEP> and <SEP> <SEP> <SEP> (52) adapter <SEP> of <SEP> <SEP> <SEP> <tb> form <SEP> of <SEP> bucket <SEP> for <SEP> the <SEP> receipt <SEP> of <SEP> ends <SEP> side <tb> shell <SEP> grapple <SEP> of <SEP> units <SEP> to <SEP> piston <SEP> and <SEP> to <SEP> cylinder <SEP> to <tb> fluid <SEP> under <SEP> pressure <SEP> (4), <SEP> which <SEP> are <SEP> performed <SEP> of <SEP> way <SEP> that <tb> <SEP> units <SEP> to <SEP> piston <SEP> and <SEP> to <SEP> cylinder <SEP> to <SEP> fluid <SEP> under <SEP> pressure <tb> are <SEP> movable <SEP> against <SEP> <SEP> recesses <SEP> as <SEP> stop <SEP> and <tb> are <SEP> assured <SEP> to <SEP> against <SEP> of a <SEP> move <tb> crosswise <SEP> to <SEP> their <SEP> longitudinal <SEP> axis.