EP1239087B1 - Quick coupling - Google Patents

Description

The present invention relates to a quick coupling for coupling a tool to the boom of a hydraulic excavator and the like, according to claim 1.

Swivel-type quick-release couplings are widely used in hydraulic excavators because they allow a simple and quick change of various tools such as hydraulic gripper, grave bucket, grapple and the like. For coupling, at first only one of the two locking axes needs to be positioned and engaged to be brought. This can advantageously be a transverse bolt, which is hooked into a hook-shaped eyelet on the opposite coupling part. Then, the cantilever-side coupling part can be pivoted relative to the tool about the already engaged locking axis, to thereby find the locking position in which the second locking axis can be locked. The latter is usually formed by a pair of locking bolts that can move apart and into corresponding locking holes on the opposite quick coupling part.

From the WO 91/01414 is such a swivel type quick coupling is known in which an automatic hydraulic coupling is provided which automatically couples a boom-side power circuit with a tool-side power circuit when pivoting the two quick coupling parts. There are two power coupling parts are provided, one of which is attached to the jib-side quick coupling part and the other on the tool-side quick coupling part, in such a way that the two power coupling parts are driven together and brought into engagement when pivoting the two quick coupling parts to the first already locked locking axis. One of the two power coupling parts is movably mounted on the corresponding quick coupling part to compensate for the circular motion of the quick coupling parts when pivoting together.

However, this known quick coupling is insufficient in several respects. The energy coupling parts do not couple cleanly when moving the quick coupling parts, so that oil leakage and thus contamination of the soil can take place. By tilting the power coupling parts subject to great wear and can even be damaged.

The DE-U1-29810118 discloses a quick coupling for coupling a tool to the boom of a hydraulic excavator with a boom side quick coupling part and a tool side quick coupling part. Furthermore, the quick coupling comprises a power circuit coupling for automatically coupling a tool-side power terminal to a jib-side power terminal comprising a jib-side power coupling part and a tool-side power coupling part. The document discloses a two-stage coupling process, in which in a first stage, the two quick coupling parts are mechanically locked together, then to be able to move together the two power coupling parts in a second step accurately and in alignment.

The present invention is therefore an object of the invention to provide an improved quick coupling of the type mentioned above, which avoids the disadvantages of the prior art and the latter further develops in an advantageous manner. In particular, an improved arrangement of the energy coupling is to be created, which allows a leak-free and trouble-free coupling of the boom and tool side power circuits.

According to the invention this object is achieved by a quick coupling according to claim 1. Preferred embodiments of the invention are the subject of the dependent claims.

According to the invention the energy coupling parts are driven exactly linear to each other. It is provided a linear guide for the power coupling parts, which forces the power coupling parts against the circular path pivotal movement to a relative movement to each other along a straight line. In order to enable the compensation of the pivoting movement, at least one of the two power coupling parts is mounted on the corresponding quick coupling part movable relative to this. In a further development of the prior art, however, it is provided that the movably mounted energy coupling part compensates for the pivoting movement when the quick coupling parts move together and moves exactly so that an exactly linear movement takes place between the two energy coupling parts.

In a further development of the invention, the linear guide has at least one armature-side guide element and at least one tool-side guide element, which engage with each other when closing the power circuit coupling, before the two power circuit coupling parts, in particular their connection conectors, engage each other. The linear guide thus arrives at the pivotal movement of the two quick coupling parts to the already locked first locking axis as the power coupling parts in and out of engagement. The engagement of the guide elements of the linear guide, however, takes place before the engagement of the connection conectors of the power coupling parts, so that the linear guidance of the energy coupling parts is ensured from the beginning. There can be no jamming and a precise linear movement over the entire coupling path of the power coupling parts is ensured. In particular, ie the guide elements of the linear guide of the actual power coupling elements ie the connector pieces separately formed components. However, they are preferably fixedly arranged on the power coupling parts or they may be integrally formed thereon.

The linear guide can basically be designed differently. Optionally, a slotted guide for the movably mounted power coupling part or for the movably mounted power coupling parts may be provided. It may also be provided a cam-like control of the movement of the or the movable power coupling parts. In a further development of the invention, however, at least one guide pin is preferably provided as guide elements on one of the energy coupling parts and at least one guide bore is provided on the other energy coupling part. When the energy coupling parts travel toward one another, the guide pin slides precisely into the complementary guide bore, whereby a linear movement is ensured. Preferably, a pair of spaced-apart guide pins and associated guide holes are provided, wherein the terminal connectors may be disposed between the guide pins and guide holes. The guide pins extend with their longitudinal axis parallel to the direction in which the connector connectors can be pushed together. As connector connectors, the power coupling parts may have known female and male connector pieces which can be slid into one another.

The one or more guide pins of the linear guide preferably have a special shape that prevents tilting when inserted into the complementary guide bore. In particular, each of the guide pins may have a rounded head, a cylindrical guide portion and a constriction provided between the head and the cylindrical guide portion. In the area of the constriction, the guide pin has a reduced diameter relative to the head or to the guide section. The rounded head can also be inserted with slight angular misalignment in the guide bore. An alignment or compensation of the angular offset occurs when the axially spaced from the bolt head cylindrical guide surface also comes into engagement with the guide bore.

At least one of the two power coupling parts is movably mounted relative to the associated quick coupling part. Preferably, only one is movably mounted, while the other is rigidly secured to the other quick coupling part. As a result, a simple arrangement is achieved, which nevertheless allows the necessary compensation of the pivoting movement.

The mobility of the storage of the corresponding power coupling part is preferably multi-axially formed. In particular, the bearing of the energy coupling part can at least allow a tilting movement about an axis parallel to the first locking axis and a movement in a direction perpendicular to the first locking axis. Preferably, it also permits a sliding movement parallel to the first locking axis and / or a tilting movement about a tilting axis perpendicular to the first locking axis. In such a comprehensive movable storage and lateral offset z. B. due to inaccuracies in the assembly can be compensated. In addition, the arrangement of the power coupling parts can be made cheaper due to coarser tolerances.

In a further development of the invention, one of the two power coupling parts is mounted on a spring device, in particular on a pair of compression springs. The compression springs can be rigidly attached to the corresponding quick coupling part and jointly carry the corresponding power coupling part. By deformation of the spring means of the compensation of the pivoting movement relative to the corresponding quick coupling part takes place.

In order to achieve a safe collapse of the power coupling parts, a limitation of the spring travel in the direction of the coupling movement may be provided. In a further development of the invention, a pressure ram can be provided, on which the movable energy coupling part is tiltably and / or slidably seated.

Preferably, the plunger has a rounded head which can engage approximately centrally between the spring elements of the spring device on the power coupling part. The plunger pushes the two power coupling parts safely and firmly in the final stage of the coupling movement. Advantageously, the pressure ram can be variable in length. In particular, the plunger may be resilient to avoid damage and to allow compensation of tolerances, wherein the spring constant of the plunger may be much harder than the resilient mounting of the power coupling part. The push rod may be formed in a further development of the invention as a hydraulic ram, d. H. he is by pressure medium in its extended position extendable or prestressed. As a result, greater pressure can be exerted on the movably mounted energy coupling part, preferably towards the end of the coupling movement or after complete collapse of the energy coupling parts, so that the energy coupling parts are reliably held in their contracted position.

In a particularly advantageous manner, the hydraulic pressure with which the pressure ram holds the two energy coupling parts, adapted to the respective operating conditions. The force holding together the power coupling parts is always chosen so large that the parts are held together completely free of play at all times. On the other hand, it is not constantly driven with a maximum force that would be sufficient under all operating conditions to hold the parts together. The latter is disadvantageous in a solution by means of a spring. If the plunger alone with spring force hold the power coupling parts, the spring must be sized so large that it holds the power coupling parts together under all conditions, so over long distances much too large forces would act. Advantageously, the pressure force can be varied in a hydraulic ram.

In particular, the pressure ram can be supplied with pressure medium from one of the pressure medium circuits to be coupled, ie the pressure tappet is acted upon by the pressure fluid, which is coupled via the energy coupling to the tool becomes. As a result, depending on the respective working pressure of the tool and the cohesion force increases. In an advantageous embodiment of the invention, the area ratio between the effective effective cylinder surface of the plunger, which is acted upon by the pressure medium, to the effective connector surface, ie the effective through the coupling passing flow cross-section, which is acted upon in the region of the connectors with pressure medium perpendicular to the coupling direction, greater chosen as 1. An advantageous embodiment may be that the area ratio is about _^5/4. The force applied by the push rod cohesion force is always greater than the maximum force that tries to squeeze the power clutch by this area ratio. If the operating pressure in the pressure medium lines to be coupled increases, the force acting on the pressure ram and thus the holding force increase as well. Usually, several pressure medium connectors are provided. Likewise, a plurality of pressure rams may be provided. In this case, the ratio of the sum of the effective cylinder effective areas and the sum of the connector areas is selected in the manner described above.

In a further development of the invention, the cylinder of the pressure ram or the cylinders of the pressure ram can be brought into fluid communication with a plurality, in particular all, of the pressure medium lines of the pressure medium circuit to be coupled. Preferably, a valve arrangement is connected between the pressure medium lines and the cylinder or cylinders, which ensures that always that of the pressure medium lines, which has the highest pressure, is in communication with the pressure plunger. This ensures that the pressure ram is always acted upon by the sufficiently large pressure. As a valve arrangement, the pressure medium lines can be interconnected in pairs via shuttle valves, so that, so to speak, always passes through the greater pressure.

The plunger can be fed from different sections of the pressure medium circuit ago. It is possible to connect the boom-side pressure medium circuit with the plunger. The fluid connectors are usually provided with leakage protection, so that the plunger can already be operated, if the connectors are not yet connected, whereby the connectors are connected by the extension of the plunger. In a preferred embodiment of the invention, however, the cylinder or cylinders are fed by the tool-side pressure medium circuit forth, ie they are only then pressurized when the power circuit clutch and in particular their fluid connectors are moved together and have coupled the connectors.

In a further development of the invention can also be provided, together retract the power circuit coupling parts with respect to the Zusammenschwenkbewegung the quick coupling delayed. This can be achieved simply by performing the hydraulic loading of the plunger with a time delay.

There may be provided a separate hydraulic circuit for actuating the plunger.

The movably mounted energy coupling part and thus the pressure ram can in principle be arranged on the boom side. In a further development of the invention, however, they are provided on the tool side.

It must be ensured between the pressure ram and the energy coupling part acted upon by it that relative movements can take place, both tilting movements and displacement movements perpendicular to the longitudinal axis of the pressure ram. On the one hand, the movably mounted power coupling half compensates for the pivotal movement of the quick coupler halves insofar as a linear movement is made from the circular path movement. In addition, occur due to game and the like relative movements. In order to allow this offset, the push rod and the power coupling half acted upon by it are movable relative to each other. To be able to transmit large forces, it can be provided that the pressure ram is frontally provided with a pressure cap which has a flat end face, so that it can sit on the substantially flat energy coupling part full and flat. In order to allow tilting movements, it is preferably provided that the pressure cap and plunger complement each other have arched surfaces, with which they sit on, so that the pressure cap on the plunger itself can tilt and yet provided a surface connection.

In order to securely hold the two power coupling parts even in rough operation, a positive locking of the two power coupling parts may be provided alternatively or in addition to the hydraulic pressure ram. In a further development of the invention can be provided to lock the guide pin of the linear guide, when this is retracted in the complementary guide bore. In particular, a movable transverse pin can be provided, which is mounted in the energy coupling part, which has the said guide bore. Preferably, the locking cross bolt can be hydraulically acted upon. Advantageously, the transverse pin can cooperate with the constriction of the guide pin, d. H. when the guide pin is fully retracted into the guide bore, the locking cross pin is retracted tangentially to the guide bore so that it projects into the guide bore, in the region in which the constriction of the guide pin is located.

In a further advantageous embodiment of the invention, a separate bolt for the positive locking of the two power coupling parts may be provided in the coupled position. Preferably, a latch flap is provided. For actuating the bolt, a preferably hydraulically operable actuating cylinder can be provided. The latch may be spring loaded so that it is biased to its latching position. As a result, the actuating means need only be actuated for unlocking.

In a further development of the invention, in addition to the linear guide, a pre-centering for the two power coupling parts when pivoting the quick coupling parts is provided. The pre-centering aligns the two energy coupling parts before engaging the linear guide to each other so far that the corresponding guide elements of the linear guide can intermesh as intended. This has particular advantages when in careless operation when pivoting together the two quick coupling parts the first locking axis is not exactly adjusted or completely retracted. In this case, misalignment of the power coupling parts may occur, which could cause damage to the power circuit clutch when moving together. The pre-centering also corrects for excessive misalignment of the power coupling parts relative to the corresponding quick coupling part, the z. B. due to the movable storage of at least one of the power coupling parts can occur.

The pre-centering can be designed differently. Preferably, it has a pair on pivoting together of the quick coupling parts successive sliding centering surfaces, one of which is provided on the movably mounted power coupling part. The other of the cooperating centering surfaces may be provided on the other power coupling part. In a further development of the invention, it can be arranged on the opposite quick coupling part. In particular, they are arranged such that they engage in front of the linear guide.

In a further development of the invention, in addition to the pre-centering, a pivoting guide can be provided, which ensures that the two quick-coupling parts can be pivoted together only in their desired alignment with one another, ie when the first locking axis is properly aligned. The pivot guide prevents damage to the hydraulic coupling by moving the quick coupling parts with offset. In the latter case, the connecting pieces or the guide pins of the power coupling parts would also drive each other with offset and cause damage. The pivoting guide preferably has guide surfaces provided on the solid pivoting coupling parts themselves, which, when the quick coupling parts are properly aligned when sliding together, slide past one another about the first locking axis or also slide on one another. They can be designed centering, so that they press together when pivoting the two quick coupling parts in their desired orientation to each other, in which the first locking axis is properly aligned. Advantageously, prevent the guide surfaces In particular, when the power coupling parts have already come into engagement with each other, a displacement of the two quick coupling halves to each other before the second locking axis is locked. Such an offset would inevitably result in damage to the power coupling. In particular, the guide surfaces may be designed such that, as soon as they are pushed over one another, they interact with the first, hook-shaped locking axis, so that an offset or a slippage of the quick coupling halves relative to each other is prevented.

According to a particularly advantageous embodiment of the invention, the power circuit clutch is a later mountable to the two quick coupling parts mounting unit. It is not an integral part of the quick coupler. The energy circuit coupling is preferably designed such that even existing quick couplers can be retrofitted.

In order to ensure good accessibility of the power circuit coupling, the power circuit coupling can be arranged outside the locking axes of the two quick coupling parts in the invention. The power circuit clutch is not difficult to access in this case between the two locking axes, but z. B. be easily reached for cleaning. Moreover, it is not in the vulnerable for the collection of dirt and dirt gap between the two locking axes.

In a further development of the invention, the power circuit clutch is disposed within abutting surfaces of the tool-side quick coupling part and / or the boom-side quick coupling part, in particular such that in the separated state of the two coupling parts, the energy circuit coupling parts do not hit the ground when the corresponding quick coupling part is deposited on the ground. Preferably, the two quick coupling parts each have two spaced, substantially perpendicular to the locking axes support pieces and the power coupling parts are each arranged between two associated support pieces transverse to these. They are in the protected Area between the vertical support pieces of the quick coupling parts. The support pieces of the quick coupling parts slide into each other or one above the other in the region of the locking axes. In particular, in contrast to the prior art, the boom-side quick-coupling part can be free of a base plate extending parallel to the locking axes, on which the energy-coupling part would be arranged. This avoids that when placing the boom-side coupling part with its base plate on the ground, the energy coupling part arranged thereon is pressed into the ground.

In a further development of the invention, the two power coupling parts are each formed substantially plate-shaped. On the plate-shaped carrier of the power coupling parts, the already mentioned male or female connector pieces, which form the power terminals, are arranged. Spaced apart from this, the guide pins or guide bores can be rigidly fastened or incorporated.

Fig. 1

eine perspektivische Ansicht einer Schnellkupplung nach einer bevorzugten Ausführung der Erfindung, die ein Paar mechanische Schnellkupplungsteile sowie eine Hydraulikkupplung aufweist, wobei die mechanischen Schnellkupplungsteile nur mit einer von zwei Verriegelungsachsen in Eingriff sind und die Hydraulikkupplung noch nicht gekuppelt ist,

Fig. 2

eine perspektivische Ansicht der Schnellkupplung aus Fig. 1, wobei die Schnellkupplungsteile im zusammengeschwenkten Zustand mit gekuppelter Hydraulikkupplung dargestellt sind,

Fig. 3

eine Seitenansicht der Schnellkupplung aus Fig. 1, wobei die Schnellkupplungsteile nur mit einer von zwei Verriegelungsachsen in Eingriff sind,

Fig. 4

eine vergrößerte Teilschnittansicht der Schnellkupplung, die die Hydraulikkupplung zeigt, kurz bevor deren zwei Energiekupplungsteile miteinander in Eingriff geraten,

Fig. 5

eine Teilschnittansicht ähnlich Fig. 4, wobei die Hydraulikkupplung in einer anderen Schnittebene gezeigt ist, in der die weiblichen und männlichen Konnektorstücke der Kupplung zu sehen sind,

Fig. 6

eine vergrößerte Schnittansicht der Hydraulikkupplung, die den Eingriff der Linearführung der Hydraulikkupplung zeigt, kurz bevor die Hydraulikkupplung vollständig gekuppelt ist,

Fig. 7

eine Frontansicht der Hydraulikkupplung in Schnittdarstellung, die die Hydraulikkupplung im vollständig verriegelten Zustand zeigt,

Fig. 8

eine Schnellkupplung nach einer weiteren bevorzugten Ausführung der Erfindung, bei der beide Energiekupplungsteile der Hydraulikkupplung beweglich gelagert sind,

Fig. 9

eine Detailansicht eines an einer schwenkbaren Lasche schwenkbar gelagerten Energiekupplungsteiles nach einer weiteren bevorzugten Ausführungsform der Erfindung, und

Fig. 10

eine Seitenansicht einer Schnellkupplung nach einer weiteren Ausführung der Erfindung, bei der eine Vorzentrierung des beweglich gelagerten Energiekupplungsteiles über eine nockenartige Vorzentrierungsfläche beim Zusammenschwenken der Schnellkupplungsteile vorgesehen ist,

Fig. 11

eine vergrößerte Teilschnittansicht einer Schnellkupplung ähnlich Figur 4, die die Hydraulikkupplung zeigt, kurz bevor deren zwei Energiekupplungsteile miteinander in Eingriff geraten,

Fig. 12

eine ausschnittsweise Frontansicht einer Hydraulikkupplung in Schnittdarstellung ähnlich Figur 7, die die Hydraulikkupplung in vollständig verriegeltem Zustand zeigt, wobei der Führungsbolzen des einen Energiekupplungsteiles durch einen Querbolzen im anderen Energiekupplungsteil gesichert ist,

Fig. 13

eine ausschnittsweise Schnittansicht entlang der Linie A-A in Figur 12,

Fig. 14

eine perspektivische Ansicht der Hydraulikkupplung im verriegelten Zustand, wobei mittels eines schwenkbar gelagerten Riegels die beiden Energiekupplungsteile formschlüssig verriegelt sind,

Fig. 15

eine Teilschnittansicht ähnlich Figur 4 einer weiteren Ausführung der Schnellkupplung, die die Hydraulikkupplung mit einem hydraulisch betätigbaren Druckstößel zeigt, kurz bevor die Kupplung kuppelt,

Fig. 16

eine Teilschnittansicht ähnlich Figur 15, wobei die Hydraulikkupplung in vollständig zusammengefahrenem Zustand gezeigt ist,

Fig. 17

eine vergrößerte Teilschnittansicht des hydraulischen Druckstößels aus den beiden vorhergehenden Figuren,

Fig. 18

eine schematische Darstellung des Schaltkreises zur Betätigung zweier hydraulischer Druckstößel gemäß der Ausführung der drei vorhergehenden Figuren,

Fig. 19

eine perspektivische Ansicht auf den unteren, beweglich gelagerten Teil der Hydraulikkupplung aus den vorhergehenden Figuren, und

Fig. 20

einen Halbschnitt durch einen Führungsbolzen der Energiekupplung, der ein lineares Zusammenschieben der beiden Energiekupplungsteile erzwingt.

The invention will be explained in more detail below with reference to preferred embodiments and associated drawings. In the drawings show:

Fig. 1

a perspective view of a quick coupling according to a preferred embodiment of the invention, comprising a pair of mechanical quick coupling parts and a hydraulic coupling, wherein the mechanical quick coupling parts are engaged with only one of two locking axes and the hydraulic clutch is not yet coupled,

Fig. 2

a perspective view of the quick coupling Fig. 1 , wherein the quick coupling parts are shown in the swung-together state with coupled hydraulic coupling,

Fig. 3

a side view of the quick coupling Fig. 1 wherein the quick coupling parts engage only one of two locking axes,

Fig. 4

an enlarged partial sectional view of the quick coupling, showing the hydraulic coupling, just before their two power coupling parts engage with each other,

Fig. 5

a partial sectional view similar Fig. 4 wherein the hydraulic coupling is shown in a different sectional plane, in which the female and male connector pieces of the coupling can be seen,

Fig. 6

an enlarged sectional view of the hydraulic clutch, which shows the engagement of the linear guide of the hydraulic clutch, just before the hydraulic clutch is fully coupled,

Fig. 7

3 is a front view of the hydraulic coupling in a sectional view, showing the hydraulic coupling in the fully locked state,

Fig. 8

a quick coupling according to another preferred embodiment of the invention, in which both power coupling parts of the hydraulic coupling are movably mounted,

Fig. 9

a detailed view of a pivotably mounted on a pivotable tab energy coupling part according to a further preferred embodiment of the invention, and

Fig. 10

a side view of a quick coupling according to a further embodiment of the invention, in which a pre-centering of the movably mounted power coupling part is provided via a cam-like Vorzentrierungsfläche when pivoting the quick coupling parts,

Fig. 11

an enlarged partial sectional view of a quick coupling similar FIG. 4 showing the hydraulic clutch just before its two power coupling parts engage each other,

Fig. 12

a fragmentary front view of a hydraulic coupling in a sectional view similar FIG. 7 showing the hydraulic clutch in the fully locked state, wherein the guide pin of the one power coupling part is secured by a cross pin in the other power coupling part,

Fig. 13

a partial sectional view taken along the line AA in FIG. 12 .

Fig. 14

a perspective view of the hydraulic coupling in the locked state, wherein by means of a pivotally mounted bolt, the two power coupling parts are positively locked,

Fig. 15

a partial sectional view similar FIG. 4 Another embodiment of the quick coupling, which shows the hydraulic coupling with a hydraulically actuated push rod just before the clutch couples,

Fig. 16

a partial sectional view similar FIG. 15 with the hydraulic clutch shown in fully collapsed condition,

Fig. 17

an enlarged partial sectional view of the hydraulic pressure ram from the two preceding figures,

Fig. 18

1 is a schematic representation of the circuit for actuating two hydraulic pressure rams according to the embodiment of the three preceding figures,

Fig. 19

a perspective view of the lower, movably mounted part of the hydraulic coupling of the preceding figures, and

Fig. 20

a half section through a guide pin of the power coupling, which forces a linear collapse of the two power coupling parts.

The quick coupling 1 shown in the figures has a boom-side quick coupling part 2, which is pivotally mounted on the stem 3 of a boom of a hydraulic excavator and can be pivoted about a pivot not shown in a conventional manner to the longitudinal axis of the stem 3 vertical pivot axis 4. The quick coupling 1 further has a tool-side quick coupling part 5, which is connected to a hydraulic excavator tool. This can be z. B. a gripping tool with a rotating mechanism 6, which is hydraulically actuated.

The two parts 2 and 5 of the quick coupling 1 are connected to each other via two parallel, spaced apart locking axes 7 and 8 locked together. The locking shafts 7 and 8 extend as FIG. 1 shows, parallel to the pivot axis 4, by which the quick coupling 1 can be pivoted relative to the stem 3.

The first of the two locking axes 7 is formed on the one hand by a provided on the tool-side quick coupling part 5 transverse pin 9 and a pair on the jib-side quick coupling part 2 provided locking hook 10. The locking hooks 10 can be hooked on the cross bolt 9 so that it can be gripped by the locking hooks 10 and the tool-side quick coupling part 5 can be raised. As FIG. 2 shows, the locking hooks 10 are open to one side, hook-shaped recesses which surround the cross bolt 9 halbschalenfömrig. The Hakenausnehmungen are open to the side of the quick coupling part 2, which is remote from the second locking axis 8.

The second locking axis 8 is formed on the one hand by a divisible locking bolt pair 11 and an associated pair of locking holes 12. As FIG. 3 shows, the locking pin pair 11 is arranged on the boom-side quick coupling part 2 and can by a known drive mechanism, preferably hydraulically, retracted and extended. The locking holes 12 are formed in the tool-side quick coupling part 5. As FIG. 1 can recognize both the cantilever-side quick coupling part 2 and the tool-side quick coupling part 5 spaced from each other, substantially vertical support pieces which are spaced differently from each other, so that the support plates of the boom-side quick coupling part 2 can retract between the support plates of the tool-side quick coupling part 5.

For coupling the two quick coupling parts 2 and 5 is first retracted with the boom-side quick coupling part 2 in the tool-side quick coupling part 5 and gripped with the hook-shaped locking recesses 10 of the transverse pin of the opposite quick coupling part (see. FIG. 3 ). By slightly raising the boom-side quick coupling part 2, it can be ensured that the tool-side quick-coupling part 5 falls securely into the hook-shaped locking recess 10. To lock the second locking axle 8, the boom-side quick coupling part 2 is then pivoted about the pivot axis 4, so that as a result the two quick coupling parts 2 and 5 are pivoted together about the first locking axis 7. The two quick coupling parts 2 and 5 are pivoted together so far that the locking pin pair 11 and the associated locking holes 12 are aligned. Then, the locking bolts 11 are preferably moved apart by hydraulic loading, so that they retract into the locking holes 12. By the two locking axes 7 and 8, the two quick coupling parts 2 and 5 are firmly locked together.

In order to prevent an offset of the two quick coupling halves and thus damage to the sensitive hydraulic coupling described below when pivoting the two quick coupling parts 2 and 5 about the first locking axle 7, the two quick coupling parts 2 and 5 may be provided with a pivoting guide 44 (see. FIG. 11 ). The two solid quick coupling parts 2 and 5 each have a guide surface 46 and 47 (see. FIG. 11 ), which can only be pushed over each other or past each other when the first locking shaft 7 is properly aligned. Drives z. B. an excavator with the hook-shaped recesses 10 is not correct, prevents the pivot guide pivoting together with offset. The guide surfaces 46 and 47 may be formed so that they act centering, ie press the two quick coupling parts 2 and 5 in the properly aligned position when they are pivoted together.

To supply tool-side drive elements with energy, the quick coupling 1 is associated with a hydraulic clutch 13, which connects a boom-side hydraulic circuit with a tool-side hydraulic circuit. For example, the rotary mechanism 1 according to FIG. 1 hydraulically operated. It can be provided and coupled further drive elements and accordingly more hydraulic circuits.

The hydraulic clutch 13 comprises two power coupling parts 14 and 15, which are mounted on the one hand on the boom-side quick coupling part 2 and on the other hand on the tool-side quick coupling part 5. They are arranged on the first locking axis 7 and 8 opposite sides of the quick coupling parts 2 and 5, in each case at the same distance from the first locking axis 7, so that they drive on each other when pivoting the two quick coupling parts 2 and 5. In principle, they could also be arranged between the two locking axes 7 and 8. Preferably, however, they are outside the limited by the two locking axes 7 and 8 area, since the latter tends to experience dirt and is difficult to access. By the arrangement of the power coupling parts 14 and 15 outside Locking axes 7 and 8 make them less susceptible and better to maintain. As the FIGS. 1 and 7 show, the power coupling parts 14 and 15 respectively between the vertical support pieces 16 of the boom-side quick coupling part 2 and the vertical support pieces 17 of the tool-side quick coupling part 5 are arranged. They are protected by this. In particular, they are not on the quick coupling parts 2 and 5 over such that the power coupling parts 14 and 15 would be pressed into the ground when the corresponding quick coupling parts 2 are sold at the bottom.

Both power coupling parts 14 and 15 combine a plurality of power line clutches. They are each designed as a connector block, in which a plurality of connector pieces 18 are combined. As FIG. 4 shows, each of the two power coupling parts 14 and 15 has a plate-shaped support piece 19 and 20, respectively, which extends transversely to the respective quick coupling part 2 and 5 respectively. Perpendicular to the support pieces 19 and 20 sit the connector pieces 18, which can be pushed together and cause the hydraulic fluid connection. The connector pieces 18 may be female and male type connector pieces known in the art.

According to the in the FIGS. 1 to 7 1, the energy coupling part 14 arranged on the cantilever-side quick coupling part 2 is fixedly mounted, ie it is rigid relative to the quick coupling part 2. The power coupling part 15 attached to the tool-side quick coupling part 5 is movably mounted on this. As FIG. 4 and FIG. 7 show, the entire power coupling part 15 is seated on a spring assembly 21, which consists of four arranged in the rectangle compression springs in the embodiment shown. The compression springs 22 are on the one hand attached to angle plates which are arranged on the vertical support pieces 17 of the tool-side quick coupling part 5 (see. FIG. 7 ). On the other hand, the cylindrical spring elements 22 are connected to the support piece 20 of the power coupling part 15, preferably screwed. The springs 22 have a sufficient height and elasticity, so that the power coupling part 15 can be multiaxially displaced or tilted. The spring assembly 21 forms a multi-axially movable mounting for the power coupling part 15 so that it can compensate for an offset to the opposite power coupling part 14, in particular due to the pivoting movement of the quick coupling parts 2 and 5.

Like from the FIGS. 3 to 6 shows, drive the two power coupling parts 14 and 15 automatically by the Zusammenschwenkbewegung the quick coupling parts 2 and 5 in synchronism with these. The power coupling parts 14 and 15 experience a circular path movement about the first locking axis 7. Since the connector pieces 18 on the two power coupling parts 14 and 15, however, must be moved together linearly, the pivotal movement of the power coupling parts 14 and 15 is compensated by the spring assembly 21. In order to ensure an exactly linear movement, the hydraulic coupling 13 is associated with a linear guide 23, which ensures that the energy coupling parts 14 and 15 are driven together in spite of the pivotal movement of the quick coupling parts 2 and 5 exactly along a straight line. The linear guide 23 consists in the illustrated embodiment of a pair of guide pins 24 and associated guide holes 25, in which the said guide pin 24 retract when moving the two power coupling parts 14 and 15. They force the springs 22 to a deflection in order to compensate for the pivoting movement component. In addition, offset due to tolerances during assembly are also compensated.

The guide pins 24 are rigidly connected to the support piece 19 of the power coupling part 15 and projecting vertically therefrom towards the opposite power coupling part 14. Each guide pin 24 is formed substantially cylindrical. In particular, however, each guide pin 24 has a rounded head 26, a cylindrical guide portion 27 and an intermediate constriction 28 which separates the bolt head 26 from the cylindrical guide portion 27. Due to the special design of the guide pin 24 tilting during insertion into the guide holes 25 is prevented. As FIG. 20 shows, the lateral surface of the guide pin 24 in the region of Kopfs 26 be spherically rounded. The spherical rounding passes into the constriction 28. In addition, it may be provided that the cylindrical shaft portion or guide portion 27 has a conical slope, which may be in the range of 5 to 15 degrees, preferably about 10 degrees. The special shape of the guide pin, in particular the spherical shape of the head allows a tilt-free insertion of the guide pin in the opposite guide holes. The guide bores 25 may have in the region of their opening cross section a cross-sectional widening in the form of a phase, a rounding or the like in order to facilitate the threading (see. FIG. 4 ). Preferably, the guide holes 25 and guide bushes 28 are formed of suitable material, which are inserted into the boom-side power coupling part 14.

In order to prevent the guide pins 24 from striking the guide bores 25 by excessive misalignment when the quick coupling parts 2 and 5 are moved together, a pre-centering 29 for pre-centering the two power coupling parts 14 and 15 relative to each other may be provided. FIG. 10 shows an example of such pre-centering 29. On the one hand, the movably mounted energy coupling part 15 may have a centering surface 30. On the other hand, a cam-shaped centering surface 31 may be provided on the opposite quick coupling part, on which the centering surface 30 of the power coupling part 15 slides off when the two quick coupling parts 2 and 5 are moved together. The pre-centering causes the two power coupling parts 14 and 15 to be in an at least roughly aligned position with each other as they are driven toward each other.

In order to achieve a safe and complete collapse of the connector pieces 18, an actuator is preferably provided, which is active on the last stretch of Zusammenschwenktbewegung the quick coupling parts 2 and 5 and the two power coupling parts 14 and 15 presses each other completely. In particular, a pressure ram 32 may be provided on which the spring-mounted power coupling part 15 is seated (see. FIG. 6 ). Because the springs are sufficiently elastic must be to compensate for the pivotal movement or offset, they could yield and be compressed, so that there is no complete coupling of the hydraulic clutch. The plunger 32 acts as a limiter for the spring travel of the spring bearing. As FIG. 6 shows, the head of the plunger 32 is preferably slightly rounded, so that even with slight inclination of the movably mounted power coupling part 15 as centric as possible sitting on the plunger 32 is achieved. The plunger 32 may also be resilient. As FIG. 6 shows, the plunger 32 may be a longitudinally displaceable bolt, which is biased by a compression spring 43 which may be in the form of a plate spring package. The spring rate of the plunger 32 is suitably much larger than that of the spring assembly 21 for the movable mounting of the one power coupling part 15. Wie FIG. 6 shows, the power coupling part 15 sits on the plunger 32 towards the end of the collapsing movement. This then presses during the remaining pivoting together of the quick coupling parts 2 and 5, the movably mounted power coupling part 15 completely on the opposite power coupling part 14. This ensures that a complete coupling of the hydraulic clutch is achieved. The plunger 32 may be a hydraulically actuated plunger according to an alternative embodiment of the invention. For this purpose, the arrangement can be reversed, ie the movably mounted energy coupling part is preferably arranged on the boom-side quick coupling part 2, so that the pressure ram can be supplied by the boom-side hydraulic system. In the hydraulically extendable plunger an increased force can be applied in particular towards the end of the coupling movement.

The FIGS. 15 to 18 show an advantageous embodiment of the hydraulic coupling with hydraulically actuated plunger. The energy coupling parts are basically movable or resiliently mounted in the manner described above, so that reference is made to the preceding description. As FIG. 15 shows, the plunger is retracted so far in its initial position that between the plate-shaped support piece 19 and the end face of the plunger 32 is air. The energy coupling thus threads first with the help of the springs 22 and the applied thereof Power. The linear guide ensures that the two power coupling parts are perpendicular to each other. This creates an elastic deformation of the stored springs, as this FIG. 16 shows.

In order to securely hold together the two power coupling parts even at high forces during operation, the hydraulic pressure ram 32 is provided which presses centrally against the support piece 19 so that it is pressed against the boom-side support piece 20. It can also be provided 32 two or more hydraulic pressure pieces. As FIG. 17 shows, the plunger 32 comprises a piston-cylinder unit, which consists of a plunger 60 and a plunger 60 displaceably leading cylinder liner 61. The cylinder liner 61 is screwed fluid-tight into the tool-fixed support piece 62 of the power coupling. As FIG. 17 shows the plunger 60 is biased with a spring assembly 63, in its extended position in which he drives by means of a shoulder 64 against a cylinder sleeve side paragraph. As a spring pack 63 disc springs can be provided of suitable strength. The disc springs are sized so that they can yield when moving the power coupling parts. The play-free, firm holding under all operating conditions is achieved by the hydraulic loading of the plunger 60. For this purpose, via a pressure fluid bore 65 of the plunger 60 and a pressure chamber 66 is connected to the hydraulic lines of the tool. As FIG. 18 shows, in the illustrated embodiment, four pressure medium lines 67, 68, 69, 70 are guided by means of the connectors 71 of the power coupling from the boom side to the tool side of the quick coupler. The tool-side pressure medium lines 67 to 70 are all connected to the pressure chamber 66 of the pressure plunger 32. The pressure medium lines 67 to 70 are combined in pairs by means of shuttle valves 72, 73 and 74. The change-over valves in the form of double check valves ensure that the pressure medium line, which has the highest pressure, always penetrates from the pressure medium lines 67 to 70. In the pressure chamber 66 of the plunger 32 so is always the pressure, which is the largest of the pressures prevailing in the pressure medium lines 67 to 70 pressures.

The effective area of the plunger, which causes its force is greater than the sum of the cross-sectional areas of the connectors 71. In conjunction with the circuit, which always gives the greatest pressure to the plunger, this ensures that the holding force is always greater than the forces caused by the pressures in the connectors, which try to force the energy coupling apart.

As FIG. 17 shows sits frontally on the plunger 60, a pressure cap 75, which has a substantially flat end face. This ensures that it always rests flat against the support piece plate 19 and excessive surface pressure, as would occur in a punctiform contact, are avoided. In order nevertheless to allow a tilting movement, the connecting surfaces 76, with which the end face of the plunger 60 and the pressure cap 75 touch each other, are rotationally symmetric rounded surfaces, so that a tilting movement between the pressure cap and the plunger 60 is possible. Nevertheless, the contact between the plunger 60 and the pressure cap 75 is also flat.

In operation, as already mentioned, sometimes large forces occur that could force the energy coupling parts apart. To remedy this situation, optionally a positive locking of the power coupling parts 14 and 15 may be provided.

As the Figures 12 and 13 show, in the power coupling part 14, a displaceably mounted cross pin 48 may be provided. The cross pin 48 is arranged so that it can retract tangentially into the guide bore 25, in the region in which the constriction 28 of the guide pin 24 comes to rest when the guide pin is fully inserted. As FIG. 13 shows, the cross pin 48 may have sections of different diameters. If the bolt is inserted with a large diameter portion in the guide bore 25, the guide pin 24 is locked. If the transverse pin 48 with a section of tapered diameter in the guide bore Inserted 25, the guide pin 24 can be inserted and ejected. The transverse pin 48 is preferably hydraulically actuated. If necessary, it can be biased by a spring in its locking position, so that a hydraulic actuation must be made only for unlocking.

Furthermore, a latch 49 may be provided which locks the power coupling parts 14 and 15 with each other in a form-fitting manner (cf. FIG. 14 ). In development of the invention, the latch 49 may be formed as a rocker arm, which is mounted pivotably about a pivot axis 51 on the power coupling part 14. At one end it has a cranked hook, with which it can engage behind a locking projection 52 on the opposite power coupling part 15. The latch 49 is preferably biased by a spring 50 in its locking position. In addition, a hydraulic cylinder 53 is articulated on the latch 49 in order to pivot it in its unlocking position (cf. FIG. 14 ). Preferably, the hydraulic cylinder 53 is arranged on the boom side in order to be permanently connected to the local hydraulic system.

FIG. 8 shows an alternative storage of the power coupling parts 14 and 15. Here, both power coupling parts are movably mounted. The power coupling part 14 attached to the jib-side quick coupling part 2 is pivotally mounted on a pivoting lug 34 about a transverse axis 33. The pivoting lug is in turn pivotally mounted on the quick coupling part 2 about a pivot axis 35 parallel to the transverse axis 33 and spaced therefrom. Optionally, a neutral position of the power coupling part 14 can be ensured by means of a spring device.

The second power coupling part 15, which is attached to the tool-side quick coupling part 5, is also movably mounted. In the illustrated embodiment, it is mounted longitudinally displaceable, in a plane which is parallel to the first locking axis 7 of the quick coupler 1 FIG. 8 the second power coupling part 15 is movable from left to right. It is held by the springs 35 in its neutral position.

FIG. 9 shows an alternative movable mounting of the tool side provided energy coupling part 15. It sits on a pivoting plate 36 which is pivotable about a transverse axis 37 to the first locking axis 7 and away from it. The energy coupling part 15 itself is also pivotally mounted on the pivoting lug 36 about the tilting axis 38. The tilting axis 38 extends parallel to the axis 37, as FIG. 9 shows. By means of springs 39, the power coupling part 15 is held in its neutral position on the pivoting lug 36.

FIG. 10 shows a further alternative storage of the power coupling part 14, which is attached to the boom-side quick coupling part 2. It sits tiltably on a transverse pin 40, which extends parallel to the first locking axis 7. In addition, the power coupling part 14 is slidably mounted on the bolt 40. It has a slot 41 so that it is displaceable transversely to the bolt 40. By means of a spring 42, the power coupling part 14 is held in its neutral position. In addition, the previously described pre-centering 29 is provided, which pre-centers the energy coupling part 14 when it is driven onto the opposite energy coupling part 15, when the two quick coupling parts 2 and 5 are pivoted together.

The upwardly projecting at the lower quick coupling part tines, on which the pre-centering cam surface 31 is provided, has a double function. At the same time, it forms the pivoting guide 44, which forces the two quick-action coupling parts in relation to one another in their properly aligned position. The reference numerals 46 and 47 also designate the corresponding guide surfaces.

Other types of storage of or the movable power coupling parts are possible without this being specifically shown. So z. B. a resilient storage can be achieved when the springs in the FIGS. 1 to 7 shown spring assembly 21 by elastic elements, for. B. rubber elements are replaced. Furthermore, it would be possible, instead of a self-aligning storage a To provide positive control for at least one of the power coupling parts, so that this compensates for the pivotal movement of the quick coupling parts 2 and 5 and between the two power coupling parts an exactly linear movement is achieved.

With the quick coupler shown considerable advantages can be achieved. In particular, the locking of the hydraulic clutch is ensured simultaneously with the quick coupler lock. In addition, the hydraulic clutch 13, in particular due to their arrangement and positioning shown, also retrofittable to existing quick coupler, since it is not integrated, but adapted. The positioning of the hydraulic clutch 13 allows good accessibility for maintenance and repair. In addition, by adapting the couplings to the quick coupler whose size is variable and adaptable to the conditions. In particular, a plurality of hydraulic lines can be combined into a single coupling block.

In order to prevent when moving apart of the quick coupling that the resilient mounting of an energy coupling part is excessively pulled apart, a stop 80 may be provided. As FIG. 19 shows, the stopper 80 may be formed by two projections against which the spring-mounted support piece plate 19 moves when pulling apart. The stops 80 are preferably arranged centrally, ie the line defined by them passes centrally through the guide pin 24 of the power coupling.

Claims (25)

1. A quick coupling for coupling a tool to the boom (3) of a hydraulic excavator and the like with a quick coupling part (2) at the boom side and a quick coupling part (5) at the tool side which can be latched together via a pair of spaced latching axles (7, 8) such that, after the gripping of only a first of the two latching axles (7), the two quick coupling parts (2, 5) can be pivoted together about the named first latching axle (7) up to the latching position and the second latching axle (8) can then be latched, and with a power circuit coupling (13), in particular a hydraulic coupling, for the automatic coupling of a power connector at the tool side to a power connector at the boom side, wherein the power circuit coupling has a power coupling part (14) at the boom side and a power coupling part (15) at the tool side which are arranged at the quick coupling part (2) at the boom side or at the quick coupling part (5) at the tool side spaced apart from the first latching axle (7) such that they move together on a circular orbit about the first latching axle by the pivoting together of the two quick coupling parts (2, 5) about the first latching axle (7) and thus automatically couple with one another,
   characterised in that
   at least one of the two power coupling parts (14, 15) can be tilted about an axis parallel to the first latching axle (7) and is movably supported perpendicular to the first latching axle (7); and in that a linear guide (23) which is separate from the power connectors is associated with the power circuit coupling (13), said linear guide, in cooperation with the movable support, compensating the tilting movement of the two power coupling parts (14, 15) on the pivoting together on the circular orbit about the first latching axle (7) and forcing the two power coupling parts (14, 15) to make an exact linear movement relative to one another along a straight line on the coupling.
2. A quick coupling in accordance with the preceding claim, wherein the linear guide (23) has at least one guide element (25) at the boom side and at least one guide element (24) at the tool side which enter into engagement with one another on the closing of the power circuit coupling (13), in particular before the two power coupling parts (14, 15) enter into engagement with one another.
3. A quick coupling in accordance with any of the preceding claims, wherein there are provided as guide elements at least one guide bolt (24) at one of the power coupling parts (15) and at least one guide bore (25) at the other power coupling part (14) to receive the at least one guide bolt, with the guide bolt (24) preferably having a rounded head (26), a cylindrical guide section (27) and a constriction (28) between the head and the guide section.
4. A quick coupling in accordance with the preceding claim, wherein the guide bolt (24) can be secured in its position pushed into the guide bore (25) by means of a movable, in particular hydraulically actuable transverse bolt (48), which is mounted in the power coupling part (14) having the guide bore (25).
5. A quick coupling in accordance with any of the preceding claims, wherein only one of the two power coupling parts is movably mounted relative to the corresponding quick coupling part.
6. A quick coupling in accordance with any of claims 1 to 3, wherein both power coupling parts are movably mounted relative to the quick coupling parts (2, 5).
7. A quick coupling in accordance with any of the preceding claims, wherein one of the two power coupling parts (15) is movably mounted, preferably on a spring device (21), in particular on an arrangement of a plurality of compression springs (22).
8. A quick coupling in accordance with any of the preceding claims, wherein a pressure ram (32) is provided on which the one of the two power coupling parts (15) is tiltably and/or displaceably seated.
9. A quick coupling in accordance with the preceding claim, wherein the pressure ram (32) has a bolt mounted in a longitudinally displaceable manner which is biased by means of a spring (43).
10. A quick coupling in accordance with claim 8, wherein the pressure ram (32) has a displaceably mounted cylinder (60) which can be acted on by a pressure medium.
11. A quick coupling in accordance with the preceding claim, wherein the cylinder (60) is acted on by a pressure medium from a pressure medium circuit to be coupled, with an areal ratio of the effective cylinder surface, which is acted on by the pressure medium, relative to the effective connector surface, which is acted on in the region of the connectors (71) by the pressure medium perpendicular to the coupling direction, being larger than 1.
12. A quick coupling in accordance with claim 10, wherein the cylinder (60) can be put into flow connection with a plurality of, in particular all pressure medium lines (67, 68, 69, 70) of the pressure medium circuit to be coupled, with a valve arrangement (72, 73, 74) preferably being provided between the pressure medium lines and the cylinder which connects the cylinder (60) to the pressure medium line standing under the highest pressure.
13. A quick coupling in accordance with either of the two preceding claims, wherein the cylinder (60) is fed from the pressure medium circuit on the tool side.
14. A quick coupling in accordance with claim 10, wherein the cylinder (60) is fed by a pressure medium circuit separate from the pressure medium circuit to be coupled.
15. A quick coupling in accordance with any of the claims 8 to 14, wherein the power circuit coupling can be travelled together with a time delay relative to the pivoting together movement of the quick coupling by means of the pressure ram (32).
16. A quick coupling in accordance with any of the claims 8 to 15, wherein the pressure ram (32) is provided on the end face with a pressure cap (75), with a tiltable connection, in particular surfaces rounded in complementary fashion with respect to one another, being provided between the pressure ram and the pressure cap.
17. A quick coupling in accordance with any of the preceding claims, wherein a pre-centring means (29) is provided for pre-centring the two power coupling parts (14, 15) on the pivoting together of the quick coupling parts (2, 5), preferably has a pair of centring surfaces (30, 31) which slide off one another on pivoting together and of which one is arranged at the movably mounted power coupling part (15) and the other at the other power coupling part (14) or the corresponding quick coupling part (2).
18. A quick coupling in accordance with any of the preceding claims, wherein a pivot guide is provided for the two quick coupling parts (2, 5) which forces the two quick coupling parts (2, 5) towards one another on the pivoting together into their desired alignment or which prevents a pivoting together with a misalignment of the two quick coupling parts.
19. A quick coupling in accordance with the preceding claim, wherein the pivot guide (44) has guide surfaces (46, 47) spaced from the first latching axle (7) which are provided at the quick coupling part (2) at the boom side or at the quick coupling part (5) at the tool side and which slide off on one another or slide past one another on the pivoting together of the two quick coupling parts (2, 5) about the first latching axle (7).
20. A quick coupling in accordance with any of the preceding claims, wherein the power circuit coupling (13) is an assembly unit which can be subsequently mounted on the two quick coupling parts (2, 5).
21. A quick coupling in accordance with any of the preceding claims, wherein the power circuit coupling (13) is arranged outside the area bounded by the two latching axles (7, 8).
22. A quick coupling in accordance with any of the preceding claims, wherein the two quick coupling parts (2, 5) each have two spaced carrier members (16; 17) substantially perpendicular to the latching axles (7, 8) and the power coupling parts (14, 15) are each arranged between two associated carrier members (16; 17) transversely to these.
23. A quick coupling in accordance with any of the preceding claims, wherein the power coupling parts (14, 15) each have substantially plate-like carrier members (19, 20) and male or female connector members (18) arranged perpendicular to the plate-like carrier members, with guide bolts (24) and guide bores (25) preferably being rigidly connected to the carrier members (19, 20) or formed in these for the linear guide of the two power coupling parts.
24. A quick coupling in accordance with any of the preceding claims, wherein the power coupling parts (14, 15) are each designed as a connector block which has a plurality of connector members (18) for a plurality of power lines.
25. A quick coupling in accordance with any of the preceding claims, wherein a bar (49) is provided for the form-locking latching of the two power coupling parts (14, 15) in their coupled position, with the bar (49) being preferably biased in its latching position by means of a spring and/or hydraulically actuable.

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