EP3770330A1 - Quick changer - Google Patents

Abstract

The invention relates to a quick coupler (2) for coupling and uncoupling attachments (4) to or from a dipperstick (1) of an earth-moving machine (5). The quick coupler (2) has a quick coupler frame (17) which on its front side has a number of claw-shaped catch hooks (20) for engaging a shaft (9a, 9b, 9c) on the attachment (4) and on which one can be retracted and extended The quick coupler frame (17) carries a first single- or double-acting hydraulic linear actuator system (18a, 40a, 45a, 18b, 40b, 45b; 48a, 45a, 48b, 45b) via which the number of locking elements (38a, 38b; 50a, 50b) can be moved linearly between a locking position and an unlocking position for locking or unlocking the attachment (4). A safety device is provided to prevent the number of locking elements (38a, 38b; 50a, 50b) from being locked if the number of locking elements is insufficient To prevent the attachment (4) falling off the quick coupler (2), as well as its own, hydraulically driven actuating device (19, 33; 69; 79, 73; 83) for actuating the safety device. The invention zei It works out that the safety device has at least one safety claw (30; 60; 70; 80) which is arranged on the front side of the quick coupler frame (17) so as to be pivotable about an axis (37) axially parallel to the shaft (9a, 9b, 9c), the securing claw (30; 60; 70; 80) via the actuating device (19 , 33; 69; 79, 73; 83) at least from its release position, in which it lets go of the shaft (9a, 9b, 9c), into its access position in which it grips the shaft (9a, 9b, 9c) is.

Description

The invention relates to a quick coupler according to the preamble of claim 1.

Such quick couplers are used in order to be able to couple attachments such as excavator buckets to a dipperstick of an earth-moving machine such as an excavator and also to be able to decouple them again, in contrast to attachments permanently installed on it. With such quick couplers, the attachments to be used with the excavator can thus be exchanged quickly.

There are different types of locking with which the quick coupler can be locked on the attachment or on an adapter frame attached to the attachment. According to the ISO 13031 standard, there are positive and non-positive locking systems, as well as frictional locking systems and wedge-like locking systems. The invention can be used with all types of locking, but preferably with a quick changer with a wedge-like locking system.

It is common to all of these types of locking that there are movable locking elements on the quick changer, which can be moved between a locking position and an unlocking position for locking or unlocking on the attachment.

In contrast to mechanically movable locking elements, hydraulically movable locking elements and thus so-called hydraulic quick couplers are used today, which allow the quick coupler to be actuated from the driver's cab of the earth-moving machine. To this end, generic quick changers have a hydraulic linear actuator system with which the locking element (s) can or is usually linearly displaceable between the locking position and the unlocking position.

Often a number of catch hooks are provided on one side of a quick coupler frame, which is usually designed as a closed housing, the opening of which is placed against a shaft on the adapter frame on the attachment, whereupon the quick coupler is moved into position in the adapter frame by the excavator driver using the dipper stick can be pivoted around the shaft on the attachment and then locked there by actuating the hydraulic linear actuator system. To uncouple the attachment, proceed in the opposite order. By actuating the hydraulic linear actuator system, the quick coupler is unlocked from the adapter frame on the attachment, then swiveled around the shaft on which its catch hooks lie and finally moved upwards with the dipperstick.

The German patent specification DE 10 2005 037 105 C5 shows such a quick coupler with the special feature that the adapter frame has two identically constructed shafts, the quick coupler can be placed either on one or the other shaft with its catch hook and can be locked or unlocked with its locking bolt below the other shaft .

Like in the DE 10 2005 037 105 C5 shown, such quick couplers mostly have double-acting hydraulic linear actuators, especially in the large excavator area, for example in the form of a piston guided in a pressure chamber, which can be subjected to hydraulic pressure from both sides, with the locking element either in one or in the one via a piston rod attached to the piston other direction can be moved in order to reach its locked or unlocked position. In use on smaller earth-moving machines, however, single-acting hydraulic linear actuator systems have also proven themselves, in which the piston can only be acted upon by hydraulic pressure from one side, usually in the direction of the unlocking position, whereas on the other side one or more preload springs press the piston with the locking element attached to it Preload into the other position, usually the locking position, which it only leaves when the preload is overcome by hydraulic pressure.

However, it can happen that the quick coupler is inadvertently not swiveled completely into the adapter frame, but is still locked. In this case, the locking elements, for example the locking bolts, move according to DE 10 2005 037 105 C5 into the void or against one of the shafts of the adapter frame and do not reach into the latch receptacles provided on the adapter frame. This means that the attachment only hangs on the quick coupler without a secure locking being guaranteed. However, the operator assumes that the quick coupler is properly connected to the attachment and secured and begins to work. The attachment hanging loosely on the quick coupler can thus be swiveled with the The excavator boom kinematics can easily fall off the quick coupler, which has resulted in serious injuries to people in the immediate vicinity.

Acoustic alarms are already known that emit a warning tone in the driver's cab of the earth-moving machine in response to corresponding sensors on the quick coupler or visual displays on the quick coupler itself, which are intended to indicate when the quick coupler is in its unlocked position. However, these measures do not work reliably under all circumstances and are often deliberately disregarded, for example if an operator just wants to lift an attachment using the quick coupler and move it to another location and simply attach the quick coupler to the attachment or adapter frame, but not lock it. This so-called crane operation is risky and forbidden, but is still often done in practice.

Further measures to better safeguard the quick coupler operation are pawls that are provided on the side of the immovable catch hook of the quick coupler and can be brought into attack on the shaft on the adapter frame to be gripped by the immovable catch hook via the movable locking elements or their hydraulic linear actuators, for additional security to prevent the attachment falling off the quick coupler.

An example of such a quick coupler with a pawl is the European patent EP 1 318 242 B1 or the DE 602 15 289 T2 refer to. The quick coupler disclosed there has movable claws on the one hand and fixed claws on the other hand, which grip two parallel, spaced-apart locking axes on the attachment. A pawl is also provided there, which serves as an additional safeguard for the bolt axis on the fixed claws. The pawl is biased into its locked position via a tension spring, with a hydraulic cylinder serving as a drive device for moving the movable claws to actuate the pawl from the locked state to the unlocked state against the spring force of the spring with its rear side actuating the pawl.

The shows something similar DE 11 2015 001 153 T5 . When extending the cylinder there to grasp a bolt axis on the attachment with the movable claws of the quick coupler is at the other end of the hydraulic cylinder with which the movable Claws are moved, a locking bolt is pressed down, which then additionally secures the bolt axis of the attachment, which is otherwise only hooked into a fork. For this purpose, the hydraulic cylinder has a pawl that presses against an inclined surface on the locking bolt and rotates it about the axis into the locking position. The hydraulic cylinder can retract against the pretensioning force of a spring damper or be designed as a double-acting hydraulic cylinder.

While such additional pawls provide a high level of security against accidental falling of the attachment from the quick coupler, the result is a relatively complex structure of the quick coupler with many moving parts and the corresponding maintenance effort.

On the other hand, a quick coupler structure like the one in the European patent application is simpler and less bulky EP 3 312 350 A1 can be found. Here, in addition to the two hydraulic linear actuators, which are provided for extending and retracting the locking bolts shown there, a further hydraulic linear actuator is provided, which can retract or extend an additional safety locking element on the front of the quick changer opposite the two locking bolts, which the quick changer against the otherwise only clamped by the two catch hooks shaft of the attachment.

However, due to the fact that the two safety elements are pressed in between the shaft of the adapter and a cover plate of the quick changer in bracing contact, severe signs of wear can occur. In addition, it requires a corresponding support surface on the shaft of the adapter frame on the attachment in order to prevent the shaft of the adapter frame held in the two catch hooks from rotating via the additional locking element.

Starting from this, the object of the present invention is to create a quick coupler that fits common adapter frames, in which additional security against undesired falling of the attachment from the quick coupler is provided in a structurally simple and low-maintenance manner.

This object is achieved with the features of claim 1.

Quick changers of the generic type have a quick changer frame, preferably designed as a housing, which as a rule has an approximately cuboid shape and is hollow in order to be able to accommodate the mechanical and hydraulic components of the quick changer. A number, preferably two laterally spaced apart, claw-shaped catch hooks are molded or welded onto the front of the quick coupler frame, the catch hooks each having a mostly forward-facing opening for engaging a shaft on the attachment. Furthermore, a number of locking elements that can be retracted and extended, which are preferably retractable and extendable at the rear, that is to say on the side opposite the openings of the catch hooks, are received in the quick coupler frame.

Furthermore, the quick coupler frame carries a first single or double-acting hydraulic linear actuator system, which is advantageously accommodated in the quick coupler frame designed as a housing. Via the first hydraulic linear actuator system, the number of locking elements for locking or unlocking on the attachment, i.e. on corresponding receptacles for the locking elements, for example on the adapter frame attached to the attachment, can be moved linearly between a locking position and an unlocking position. In this case, the locking position is advantageously shifted towards the rear compared to the unlocking position.

Furthermore, the quick coupler has a hydraulically driven or actuatable safety device which can advantageously also be accommodated in the quick coupler frame or housing in order to prevent the attachment from falling off the quick coupler in the event that the number of locking elements is insufficiently locked.

According to the invention, the quick coupler is characterized in that the securing device comprises at least one securing claw which is arranged on the front side of the quick coupler frame so as to be pivotable about an axis parallel to the shaft on the implement on which the number of catch hooks have to engage and between an access position in which it grips the shaft, and a release position in which it lets go of the shaft is pivotable.

Like the quick changer of the generic type, the quick changer according to the invention has its own hydraulic actuating device for actuating the Safety device, but the design of the safety device with safety claw ensures that round shafts, as they are standard on most attachments or adapter frames for gripping by the catch hook of the quick coupler, can be securely gripped without causing greater frictional forces and with it signs of wear and tear.

Advantageous further developments are the subject of the subclaims.

Thus, a pretensioning device can be provided with which the securing claw is pretensioned into its release position. This ensures that when the hydraulic force is not applied to the actuating device, an open position of the catch hook and the securing claw suitable for receiving the shaft of the attachment is reached.

With the pretensioning device, it can be sufficient if the actuating device for the securing claw is designed such that the securing claw can be pivoted via the actuating device from its release position, in which it releases the shaft, into its access position, in which it grips the shaft.

Advantageously, however, the actuating device has a further, single or double-acting hydraulic linear actuator system, via which one (or more) actuating bolts, which are accommodated in the quick coupler frame and can be moved towards and away from it, can be moved linearly between an actuating position extended to the front and a release position retracted to the rear , whereby the actuation of the securing claw via the actuating device advantageously only takes place in the direction of the access position, but the retraction of the actuating device can under certain circumstances also take place without coupling to the securing claw and the securing claw can also be moved back into the release position solely via the pretensioning device.

The pretensioning device can be designed, for example, as one or more leg springs or the like wound around the axis or axle suspension of the securing claw and engaging the securing claw, in particular if this axis is formed according to a further aspect of the invention by an axle bolt which engages through the securing claw and which is in the area of the catch hook, i.e. the The front side is supported on the quick coupler frame, preferably extending between the two catch hooks.

On the other hand, the actuating device could also comprise a hydraulic rotary motor, about whose axis the securing claw can be pivoted not only from its released position into its access position but also back by means of the rotary motor engaging the securing claw.

In particular in connection with the further development of the invention with a securing claw penetrated by an axle bolt, the actuating device can advantageously comprise at least one actuating bolt which is received in the quick coupler frame so that it can be moved towards and away from it, as well as a further single or double-acting hydraulic linear actuator system via which the at least one Actuating bolt can be moved linearly between a forwardly extended operating position and a rearwardly retracted release position, so that the securing claw can be operated via the actuating bolt.

In a single-acting hydraulic linear actuator system, the safety claw is pressed into its access position by the spring force of a spring, preferably a compression spring. When hydraulic pressure is applied to the hydraulic linear actuator system, the actuating bolt moves back and thus allows the safety claw to move from its access position to its release position, for example by means of a pretensioning device. If the safety claw is in the release position, the hydraulic linear actuator system can be hydraulically driven by releasing hydraulic pressure, so that the safety claw is pivoted from its release position into the access position by the spring of the single-acting hydraulic linear actuator system.

In a double-acting hydraulic linear actuator system, the actuating bolt is shifted in both directions by hydraulic pressure, so that the safety claw is pivoted from its release position into its access position by hydraulic pressure and the safety claw can also be released again via hydraulic pressure, for example to be pivoted back into its release position via the pretensioning device will.

The further single or double-acting hydraulic linear actuator system can then be coupled to the hydraulic supply or discharge lines of the first hydraulic linear actuator system, which results in a simple controllability of the actuating device for the safety claw. The coupling can be done either in series or in parallel. This means that the further hydraulic linear actuator system is only switched in response to the unlocking position of the locking bolts being reached by means of the first hydraulic linear actuator system for moving the actuating bolt from its actuating position into its release position (series connection) or at the same time as the movement of the locking bolts or locking elements begins Hydraulic linear actuator system in the direction of the unlocking position, the further hydraulic linear actuator system for moving the actuating bolt from its actuating position extended to the front into its release position retracted to the rear is switched on (parallel connection).

The parallel connection can be achieved, for example, by hydraulic oil supply channels running from a central control valve parallel to the first hydraulic linear actuator system and to the further hydraulic linear actuator system, the series connection, for example, via a valve in the hydraulic oil supply channel to the further hydraulic linear actuator system, which is only activated when the unlocked position of the first hydraulic linear actuator system or the locking elements for the flow release are reached is unlocked. With a series connection designed in this way, even greater security against undesired falling of the incorrectly coupled attachment from the quick coupler can be achieved by the fact that the securing claw only releases the shaft on the attachment or adapter frame when the regular locking elements are already in their unlocked position.

The actuating bolt and the securing claw are advantageously coupled via a gear, via which the securing claw can be moved at least from its release position into its access position, the return movement to the release position being able to take place solely via the pretensioning device and / or via a suitable design of the gear, which the securing claw is then pivoted in response to the movement of the actuation bolt not only from its release position into its actuation position from the release position into the access position, but also in response to the movement of the actuation bolt from its actuation position into the

Release position pivoted from its access position into its release position.

There are several advantageous options for forming the transmission.

For example, a circumferential section of the securing claw can be designed as a pinion and mesh with an end section designed as a rack on the end of the actuating bolt facing the securing claw or a plunger attached to it, in response to the movement of the actuating bolt between its release position and its actuating position, the securing claw between its To pivot the release position and their access position.

On the other hand, the transmission could also have a pivot rod articulated to the actuating bolt or a plunger attached to it on the one hand and the securing claw on the other hand, via which the securing claw pivots between its release position and its access position in response to the movement of the actuating bolt between its release position and its actuation position.

Furthermore, the gear could also be designed as a wedge gear coupling the actuating bolt with the securing claw, via which the securing claw can be pivoted at least from its release position into its access position in response to the actuation bolt being moved from its release position to its actuating position.

It is sufficient if the actuating bolt pivots the securing claw into its access position when it is pushed out into its actuating position, because the securing claw can be pivoted back into the release position either solely by the opening movement when the shaft of the adapter frame or the attachment is released or with the help of the pretensioning device. However, it would also be conceivable to provide appropriate traction means between the actuating bolt and the securing claw, such as tension springs or a driving pin on the actuating bolt that engages in a link guide on the securing claw or the like in order to also perform or support the pivoting of the securing claw back into the release position by actuating bolts.

However, a simple wedge / counter-wedge arrangement on the actuation bolt or on the safety claw is particularly suitable as a wedge gear coupling the actuating bolt to the securing claw. For this purpose, the actuating bolt can taper in a wedge shape at its end facing the securing claw or have a wedge-shaped plunger which runs into the actuating position on an oppositely inclined or curved counter-wedge surface on the securing claw during the extension movement of the actuating bolt and thereby pivoting the securing claw into the access position.

For this purpose, the securing claw can advantageously be formed on a rocker which is suspended on the axle or the axle bolt or the axially centric mounting of the securing claw, the rocker having a rear rocker leg extending from the axis in the direction of the actuating bolt. The contact surface of the securing claw swept over by the actuating bolt or the tappet attached to its end facing the securing claw can then be formed on the rear rocker leg, so that a favorable lever ratio for pivoting the rocker or the securing claw around the axis or the axis bolt or an axially centric suspension of the same is achieved results. The securing claw itself can then be formed on a front-side rocker leg of the rocker that extends forward from the axis.

On the actuating bolt side, the wedge gear can have an actuating surface that is inclined to the direction of displacement of the actuating bolt, in particular on the wedge-shaped plunger, and the securing claw, preferably on the rear rocker leg, can have an oppositely inclined contact surface facing the actuating surface so that the actuating surface can run off the contact surface. It is advantageous in terms of the swiveling movement of the securing claw to be carried out, however, if only the actuating surface has a slope inclined to the direction of displacement of the actuating bolt, but the contact surface on the securing claw running on it has a curved profile. However, it would also be conceivable to design the plunger or wedge without inclination in such a way that it presses frontally on an inclined contact surface on the rocker or the securing claw, thereby causing the rocker to pivot. Theoretically, it would also be conceivable, both the actuating surface on the plunger and the contact surface on the securing claw in the Execute the normal plane for the direction of displacement of the actuating bolt as long as the lever is large enough that the safety claw swings out.

It is particularly advantageous if the actuating surface has a first actuating surface section on the end of the plunger attached to the actuating bolt facing the securing claw and a second actuating surface section following it in the direction away from the securing claw, the first actuating surface section being stronger than the second actuating surface section for the displacement direction of the actuating bolt Has inclination. As a result, a relatively strong pivoting movement of the securing claw by a large angle of rotation can then initially be brought about in a relatively short time as long as the first actuation surface section runs off the contact surface. Subsequently, the slight inclination of the second actuation surface section causes a high closing force and advantageously a self-locking of the wedge gear, which then serves as the lock of the shaft system, the securing claw resting on it and the actuating bolt pushed in.

Because the securing claw is pressed against the receiving axis of the adapter frame and this in turn into the two catch hook openings, the generated clamping force almost excludes the attachment tool from swinging and swinging if it is incorrectly locked in the catch hook opening, which is particularly important when the safety claw comes to rest on the shaft with a different opening direction than the catch hook. In the case of forwardly directed openings of the catch hooks, the securing claw can advantageously be moved against the shaft from below, that is to say with the opening direction upwards, or else from the front, that is to say with the opening direction to the rear.

In order to design the structure of the entire actuation line from the actuation bolt via the attached plunger, the rear rocker leg of the rocker, on which the securing claw is formed at the same time, with the rocker suspended on a rotary axis in the area between the two catch hooks in the sense of good force and torque transmission It is advantageous if the contact surface formed on the rear rocker leg points at least with a directional component upwards, whereas the actuation surface formed on the plunger points at least with a directional component downwards. When extending the Actuating bolt in its actuating position thus the rear rocker leg of the rocker suspended above it is pressed down by the plunger and correspondingly the locking claw is pivoted upward into its access position on the shaft of the attachment or its adapter frame.

In terms of a structure that is generally less susceptible to failure, the first hydraulic linear actuator system with the number of locking elements, preferably designed as two locking bolts, and the further hydraulic linear actuator system with the actuating bolt are combined in a common and advantageously closed locking housing, which is either formed in one piece with the quick hitch frame or connected to the quick hitch frame, preferably screwed, can be. In particular, the locking housing can be pushed into the interior of the quick coupler frame, advantageously from the rear of the quick coupler frame facing away from the shaft on the adapter frame on which the catch hooks engage. Furthermore, advantageously, the locking housing preferably has an opening on the underside which allows assembly access that is necessary for fastening the plunger to the securing bolt, it being possible for the opening to be closed with a cover or the like.

As a number for the locking elements, a number of two locking elements arranged next to one another, preferably in the form of locking bolts which can be pushed out by hydraulic pressure, has proven successful. The first hydraulic linear actuator system advantageously has a separate pressure chamber for each locking bolt with a piston received therein such that it can be displaced towards the rear and away from it. The respective locking bolt can then be formed in one piece on the piston or preferably fastened to the piston. For this purpose, a piston rod attached to the piston can be provided, which carries the locking bolt. The locking bolt can, however, also be attached directly to the piston.

The pressure chambers assigned to the locking bolts advantageously each extend with their longitudinal axis along the quick coupler frame towards the rear of the quick coupler frame, so that each locking bolt can be displaced at least from its locking position into its unlocking position towards the front of the quick coupler frame by applying hydraulic pressure to the associated pressure chamber and the piston. In the case of a single-acting Hydraulic linear actuator system, the opposite movement of the locking bolts from their unlocking position into their locking position towards the rear of the quick coupler frame can then be carried out by applying spring force or another suitable pretensioning device that biases the respective locking bolt into its locked or locking position. In the case of a double-acting hydraulic linear actuator system, the shift from the unlocking position into the locking position also takes place by hydraulic pressure, with hydraulic pressure then being able to be applied to the piston from both sides. Each of the number of locking bolts can advantageously taper off in a wedge shape at its end in order to form a quick coupler with a wedge-like locking system together with the catch hook.

On each of the number of locking bolts, at least one driver projecting circumferentially in the radial direction can be attached, which is guided in an assigned slot guide or the like running parallel to the respective locking bolt in the locking housing or the quick coupler frame, so that an anti-twist device is formed for the locking bolt . Furthermore, at least one of the driver pins can preferably be connected to a locking indicator pin which extends along the quick coupler frame to its front side so far that it protrudes there in the unlocked position of the locking bolt and does not protrude in the locked position. This creates an additional display in order to be able to check the correct locking status of the quick coupler on the adapter frame or on the attachment and thus to further increase safety.

The further hydraulic linear actuator system for the preferably one actuating bolt for actuating the securing claw can then comprise a pressure chamber with a piston received therein such that it can be displaced towards the front and away from it. The actuating pin can be formed integrally on the piston or attached to the piston, wherein the plunger can be formed integrally on the actuating pin or can be attached to the actuating pin. In terms of a compact design of the quick changer, it is advantageous if the pressure chamber of the further hydraulic linear actuator system extends along the quick changer frame towards the front, so that the actuating bolt at least from its actuating position into its release position by applying the pressure chamber and of the piston can be moved backwards with hydraulic pressure.

In the case of a single-acting, further hydraulic linear actuator system, the opposite movement of the actuating bolt from its retracted release position towards the rear into its actuated position extended towards the front can be brought about by the biasing force of a compression spring pressing on the piston or another suitable biasing device. The further hydraulic linear actuator system can, however, also be designed to be double-acting, so that the piston can be acted upon by hydraulic pressure from both sides and can be displaced both from its actuation position into its release position and from its release position into its actuation position by applying hydraulic pressure to the pressure chamber and the piston.

In the hydraulic supply line to the pressure chamber, a 2/2-way plunger valve can furthermore preferably be arranged, the valve plunger of which protrudes into this pressure chamber on the side facing the front of one of the pressure chambers of the first hydraulic linear actuator system. The piston there can then be provided with a piston rod that presses on the valve tappet when the unlocking position is approached from the locking position, so that only then is the hydraulic line to the other hydraulic linear actuator system released, which leads to the side of the piston there that is used to move the piston and so that the actuating bolt is to be acted upon in the release position with hydraulic pressure. This series connection brings additional security to the quick coupler, since the quick coupler can only be swiveled out of the adapter frame with the catch hook when it is completely unlocked.

Figur 1

zeigt einen Bagger mit einem Löffelstiel und einem daran angebrachten Schnellwechsler gemäß einer ersten Ausführungsform der Erfindung, sowie ein aufzunehmendes Anbaugerät mit einem daran angebrachten, für den Schnellwechsler passenden Adapterrahmen;

Figur 2a

einen Adapterrahmen zum Anbau an ein Anbaugerät, passend für einen erfindungsgemäßen Schnellwechsler;

Figur 2b

einen Adapterrahmen zum Anbau an ein Anbaugerät, passend für einen erfindungsgemäßen Schnellwechsler;

Figur 3a

einen Adapterrahmen zum Anbau an ein Anbaugerät, passend für einen erfindungsgemäßen Schnellwechsler;

Figur 3b

einen Schnellwechsler gemäß einer ersten Ausführungsform der Erfindung im an dem in Figur 3a gezeigten Adapterrahmen in einer ersten Stellung verriegelten Zustand;

Figur 3c

den in der Figur 3b gezeigten Schnellwechsler im in einer zweiten Stellung an den Adapterrahmen aus Figur 3a verriegelten Zustand;

Figuren 4a

den in den Figuren 3b und 3c gezeigten Schnellwechsler an dem in

und 4b

der Figur 2b gezeigten Adapterrahmen im unverriegelten Zustand in unterschiedlichen Längsschnitten;

Figuren 5a

den Figuren 4a und 4b entsprechende Ansichten, wobei der

und 5b

Schnellwechsler am Adapterrahmen verriegelt ist;

Figuren 6a

Schnittansichten des in den Figuren 4a bis 5b gezeigten

und 6b

Schnellwechslers in fehlerhaft verriegelter Stellung am Adapterrahmen;

Figur 7

eine Schnittansicht des in den Figuren 4a bis 6b gezeigten Schnellwechslers, der nach einem fehlerhaften Verriegeln den Adapterrahmen mit seiner Sicherungsklaue hält;

Figur 8a

eine Seitenansicht des Schnellwechslers gemäß der bereits in den vorhergehenden Figuren gezeigten Ausführungsform;

Figur 8b

eine Draufsicht auf den in Figur 8a gezeigten Schnellwechsler;

Figur 8c

eine Schnittansicht entlang Linie C-C in Figur 8a;

Figur 9a

einen Hydraulikschaltplan für den in den vorhergehenden Figuren gezeigten Schnellwechsler mit Parallelschaltung seiner Hydrauliklinearaktuatoren;

Figur 9b

einen Hydraulikschaltplan für den in den vorhergehenden Figuren gezeigten Schnellwechsler gemäß einer Variante mit Reihenschaltung des mittleren Hydrauliklinearaktuators nach den beiden äußeren Hydrauliklinearaktuatoren;

Figur 10a

eine Längsschnittansicht in einer durch einen Riegelbolzen verlaufenden Ebene durch einen Schnellwechsler gemäß einer zweiten Ausführungsform der Erfindung mit einem doppeltwirkenden Hydrauliklinearaktuatorsystem für die Riegelbolzen;

Figur 10b

eine weitere Längsschnittansicht durch den in Figur 10a gezeigten Schnellwechsler in einer durch seinen Betätigungsbolzen verlaufenden Ebene;

Figur 10c

eine der Figur 8c entsprechende Schnittansicht durch den in den Figuren 10a und 10b gezeigten Schnellwechsler;

Figur 11a

einen Hydraulikschaltplan für den in den Figuren 10a bis 10c gezeigten Schnellwechsler mit parallel geschaltenen Hydrauliklinearaktuatorsystemen;

Figur 11b

einen Hydraulikschaltplan für den in den Figuren 10a bis 10c gezeigten Schnellwechsler gemäß einer alternativen Variante mit Reihenschaltung des mittleren Hydrauliklinearaktuatorsystems nach den beiden äußeren Hydrauliklinearaktuatorsystemen;

Figuren 11c und 11d

weitere Varianten eines Hydraulikschaltplans für den in den Figuren 10a bis 10c gezeigten Schnellwechsler;

Figur 11e

einen Hydraulikschaltplan für einen Schnellwechsler gemäß einer weiteren Ausführungsform der Erfindung, welcher neben einem doppeltwirkenden ersten Hydrauliklinearaktuatorsystem für die Riegelbolzen auch ein doppeltwirkendes weiteres Hydrauliklinearaktuatorsystem für den Betätigungsbolzen aufweist;

Figuren 11f bis 11j

Abwandlungen des Hydraulikschaltplans für den Schnellwechsler gemäß der dritten Ausführungsform der Erfindung;

Figuren 12a und 12b

perspektivische Ansichten einer Verriegelungseinheit für den in den Figuren 4a bis 8c gezeigten Schnellwechsler;

Figuren 13 bis 16

verschiedene Varianten eines Keilgetriebes zwischen Betätigungsbolzen und Sicherungsklaue für einen Schnellwechsler gemäß einer der zuvor gezeigten Ausführungsformen der Erfindung;

Figur 17

einen Schnellwechsler gemäß einer vierten Ausführungsform der Erfindung mit Zahnstangen-Ritzel-Getriebe zwischen Sicherungsklaue und Betätigungsbolzen;

Figur 18

einen Schnellwechsler gemäß einer fünften Ausführungsform der Erfindung mit Schwenkstangengetriebe zwischen Sicherungsklaue und Betätigungsbolzen;

Figur 19

einen Schnellwechsler gemäß einer sechsten Ausführungsform der Erfindung mit einem die Sicherungsklaue betätigenden Schwenkmotor; und

Figur 20

eine Hydraulikschnellwechsler-Baggerlöfelschwenkmotor-Kombination, in der ein Schnellwechsler gemäß einer Ausführungsform der Erfindung verbaut ist.

Further advantageous developments of the invention are explained in more detail with reference to the embodiments of the invention shown in the accompanying drawings.

Figure 1

shows an excavator with a dipper stick and a quick coupler attached to it according to a first embodiment of the invention, as well as an attachment to be picked up with an adapter frame attached to it that fits the quick coupler;

Figure 2a

an adapter frame for attachment to an attachment, suitable for a quick coupler according to the invention;

Figure 2b

an adapter frame for attachment to an attachment, suitable for a quick coupler according to the invention;

Figure 3a

an adapter frame for attachment to an attachment, suitable for a quick coupler according to the invention;

Figure 3b

a quick changer according to a first embodiment of the invention in the in Figure 3a adapter frame shown in a first locked position;

Figure 3c

in the Figure 3b shown quick coupler in a second position on the adapter frame Figure 3a locked state;

Figures 4a

the in the Figures 3b and 3c quick coupler shown on the in

and 4b

the Figure 2b adapter frame shown in the unlocked state in different longitudinal sections;

Figures 5a

the Figures 4a and 4b corresponding views, with the

and 5b

Quick coupler is locked on the adapter frame;

Figures 6a

Sectional views of the Figures 4a to 5b shown

and 6b

Quick coupler in incorrectly locked position on the adapter frame;

Figure 7

a sectional view of the in the Figures 4a to 6b shown quick coupler, which holds the adapter frame with its securing claw after an incorrect locking;

Figure 8a

a side view of the quick changer according to the embodiment already shown in the previous figures;

Figure 8b

a top view of the in Figure 8a shown quick coupler;

Figure 8c

a sectional view along line CC in Figure 8a ;

Figure 9a

a hydraulic circuit diagram for the quick coupler shown in the previous figures with parallel connection of its hydraulic linear actuators;

Figure 9b

a hydraulic circuit diagram for the quick changer shown in the preceding figures according to a variant with series connection of the middle hydraulic linear actuator after the two outer hydraulic linear actuators;

Figure 10a

a longitudinal sectional view in a plane running through a locking bolt through a quick coupler according to a second embodiment of the invention with a double-acting hydraulic linear actuator system for the locking bolt;

Figure 10b

a further longitudinal sectional view through the in Figure 10a quick coupler shown in a plane extending through its actuating bolt;

Figure 10c

one of the Figure 8c corresponding sectional view through the in the Figures 10a and 10b shown quick coupler;

Figure 11a

a hydraulic circuit diagram for the Figures 10a to 10c shown quick coupler with hydraulic linear actuator systems connected in parallel;

Figure 11b

a hydraulic circuit diagram for the Figures 10a to 10c shown quick coupler according to an alternative variant with series connection of the middle hydraulic linear actuator system after the two outer hydraulic linear actuator systems;

Figures 11c and 11d

further variants of a hydraulic circuit diagram for the Figures 10a to 10c shown quick coupler;

Figure 11e

a hydraulic circuit diagram for a quick coupler according to a Another embodiment of the invention, which in addition to a double-acting first hydraulic linear actuator system for the locking bolt also has a double-acting further hydraulic linear actuator system for the actuating bolt;

Figures 11f to 11j

Modifications of the hydraulic circuit diagram for the quick changer according to the third embodiment of the invention;

Figures 12a and 12b

perspective views of a locking unit for the Figures 4a to 8c shown quick coupler;

Figures 13 to 16

different variants of a wedge gear between the actuating bolt and the securing claw for a quick coupler according to one of the embodiments of the invention shown above;

Figure 17

a quick coupler according to a fourth embodiment of the invention with rack and pinion gear between the securing claw and actuating bolt;

Figure 18

a quick coupler according to a fifth embodiment of the invention with a swivel rod gear between the securing claw and the actuating bolt;

Figure 19

a quick changer according to a sixth embodiment of the invention with a swivel motor which actuates the safety claw; and

Figure 20

a hydraulic quick coupler-excavator swivel motor combination in which a quick coupler according to an embodiment of the invention is installed.

The quick-change system presented in the invention comprises a quick-change system 2 and an adapter frame 3. As in FIG Figure 1 shown, the quick coupler 2 is attached to an excavator boom kinematics 1 on an earth-moving machine 5. The adapter frame 3 is attached to an attachment tool 4. There are several in principle Compatible variants for forming the adapter frame 3:
The first variant ( Fig. 2a ) consists of a base plate 8, two suspension brackets 10a connected by an adapter shaft 9a and an inclined rear plate 7a. The base plate 8 is a sheet of metal approximately the size of the quick changer, on which the other components are aligned and fastened and through which the attachment tool 4 and the adapter frame 3 are firmly connected to one another. The inclined rear plate 7a has two conical bores 6 for large quick couplers on the flat side. The rear plate 7a is attached to the rear side of the base plate 8. On the opposite side, the adapter shaft 9a is attached to two lateral suspension lugs 10a on the base plate 8. This adapter shaft 9a must have a suitable diameter for the catch hook opening 47 (see Figure 8a ) of the quick coupler 2.

As Figure 2b shows, instead of the base plate 8 with the suspension tabs 10a on the sides of the rear panel 7b, a side panel 10b can also be attached to the right and left, parallel and at the same height to one another. The two side plates 10b are connected at their other end by the adapter shaft 9b. This adapter shaft 9b must have a suitable diameter for the catch hook opening 47 (see Figure 8a ) of the quick coupler 2. Instead of the base plate 8, the side plates 10b and the rear plate 7b are attached directly to the attachment tool 4. In this way, the top of the attachment 4 assumes the function of the base plate 8. The inclined rear plate 7b here has two identical semicircular cutouts 11 which are particularly suitable for small quick couplers. The semicircular cutouts are aligned with the flat side up and at the same height to each other. The center points of the semicircular cutouts 11 have an identical center point to openings for locking bolts 38a and 38b in a rear housing 22 of the quick coupler 2, see Figures 4a, 4b , 5a, 5b . Another circular opening 13 is arranged centrally between the other two openings 11.

In the in the Figure 3a In the variant shown, the adapter frame 3 has a further adapter shaft 9c at its position instead of the inclined rear plate 7a or 7b. This is to ensure that the attachment tool 4 is also used rotated and z. B. a backhoe ( Figure 3b ) with a 180 ° turn as a shovel ( Figure 3c ) can be used. Both adapter shafts 9c have an inclined contour 14 on their inside congruent with the slope of the rear panel. They also have cutouts 15 on the underside that are congruent with the cutouts in the rear panel so that the locking bolts in the rear panel or the adapter shaft 9c properly engage within the required tolerance and ensure secure locking.

In the following, the embodiments of the quick changer 2 according to the invention are primarily described in combination with the in Figure 2b shown variant of the adapter frame 3 described.

The quick coupler 2 consists, such as the Figures 8a to 8c can be seen from an approximately cuboid quick coupler frame or housing 17 with three hydraulic linear actuators 18a, 18b, 19 inside. On the front underside of the quick coupler housing 17 are immovable, parallel to each other aligned catch hooks 20 with the opening 47 to the front. These catch hooks 20 are intended to accommodate the adapter shaft 9a, 9b or 9c (see FIG Figure 4a ). At the rear of the housing 22, two locking bolts 38a, 38b are extended to lock the quick coupler 2 firmly in the adapter frame 3. An excavator suspension plate 16 is attached to the right and left on the top of the housing 17. The quick coupler 2 is attached to the dipper stick 25 and pressure support 26 of the excavator boom kinematics 1 in a manner similar to a conventional backhoe or comparable attachment tool 4.

With the aid of the excavator boom kinematics 1, the quick coupler 2 is pivoted into the immediate vicinity of the adapter frame 3 on the attachment tool 4. The quick coupler 2 is unlocked hydraulically: the locking bolts 38a, 38b retract. After the catch hook 20 has latched into the adapter shaft 9a, 9b or 9c, the quick coupler 2 together with the attachment tool 4 latched onto the adapter frame 3 is raised slightly until the attachment tool 4 hangs freely above the ground. The unlocked quick coupler 2 is then pivoted further into the adapter frame 3 of the attachment 4 by extending the bucket cylinder 24 of the earth-moving machine 5 until the quick coupler 2 with its rear housing 22 rests on the rear panel 7a or 7b or the adapter shaft 9c of the adapter frame 3 ( Figure 4a ).

The quick coupler 2 is then locked from the driver's cab 23: The two locking bolts 38a, 38b move into the two openings 6, 11 or 15 of the rear panel 7a or 7b or the adapter shaft 9c of the adapter frame 3 ( Figure 5a ). As a result, they clamp the rear housing 22 against the rear plate 7a or 7b or the inclined adapter shaft contour 14 and the catch hook 20 against the adapter shaft 9a, 9b or 9c of the adapter frame 3.

With quick couplers known from the prior art, it could happen that the quick coupler is inadvertently not pivoted completely into the adapter frame, but is still locked. In this case the locking bolts move to the block ( Figure 6a ) or into the void ( Figure 6b ) and do not intervene in the rear panel or the second adapter shaft and the contact surfaces provided for it. The result is that the attachment tool with the adapter shaft only hangs in the two catch hook openings and the locking indicator is still retracted into the quick coupler housing. The operator assumes that the quick coupler is properly connected to the attachment and secured and begins to work. Since the attachment hangs loosely on the quick coupler, the attachment tool will most likely fall off the quick coupler when pivoting with the excavator boom kinematics. In this case, people in the immediate vicinity can be seriously or even fatally injured by the attachment tool falling.

Another forbidden but frequent use of a quick-change system is crane operation. The operator drives a locked quick coupler with both catch hook openings into the adapter shaft and lifts the attachment tool in order to transport it or move it to another location. The attachment is not firmly connected to the quick coupler and can fall: People standing in the vicinity can be seriously or fatally injured if the attachment falls. The risky crane operation and thus the picking up of an attachment or load attachment device with only one or both catch hooks of the quick coupler without locking it properly is prohibited. An attachment may only be moved if it is locked with the quick coupler and is therefore firmly connected. A load attachment device may only be picked up using load hooks attached to the quick coupler.

According to the present invention, the quick coupler 2 has a securing claw 30 to prevent accidents of this type, see Figure 7 :
The attachment 4 cannot fall off even if the locking bolt 38a, 38b is incorrectly locked, but is held on the shaft 9b of the adapter by the securing claw 30. As the Figures 4b and 5b show, the securing claw 30 is formed on a rocker 27 which is pivotably suspended on an axle bolt 37 forming a pivot axis. The rocker 27 has a rear rocker leg 29 extending from the axis 37 in the direction of the actuating bolt 33, with a contact surface 32 on which a wedge-shaped plunger 31 attached to the actuating bolt 33 can engage with its actuating surface 35, 36 the securing claw 30, which forms a front rocker leg of the rocker 27, from its release position ( Figure 4b ) in their access position ( Figure 5b ) to pivot.

The securing claw 30 is attached between the catch hooks 20 of the quick coupler 2 and has a shape similar to that of the catch hooks 20. The rear end or the rear rocker leg 29 has a rounded contact surface 32. The securing claw 30 is rotatably mounted either directly between the two catch hooks 20 of the quick coupler 2 or on a suitable receptacle in the quick coupler frame or housing 17 between the catch hooks 20 and is, like Figure 8c shows, for example prestressed via torsion springs 28. The springs 28 are designed in such a way that they bring about a pretensioning of the securing claw 30 in the "open claw" direction. Instead of the torsion springs 28, any other device that generates such a pretension can also be used.

The pretensioning prevents the securing claw 30 from swinging loose and the rear end 29 of the rocker 27 can swing out to the highest possible point. At this rear end 29 of the rocker 27 there is a contact surface 32 which, by being pivoted upward, is in engagement with a wedge-shaped plunger 31 placed there. In this variant, the plunger 31 has a cuboid shape with two different slopes on the underside, and the contact surface 32 has an arc which rests tangentially on the plunger or wedge 31. The plunger 31 and the rear rocker arm 29 on the securing claw 30, or its contact surface 32, can differ in their illustrated form, provided that they continue to fulfill the purpose set out below (see Fig. 13 , Fig. 14 , Fig. 15 and Fig. 16 ).

The wedge or plunger 31 is used to actuate the rocker 27 via a contact surface 32 at the rear end 29 of the rocker 27. The wedge 31 is connected to the piston rod 33 of a single-acting linear actuator 19: The middle piston rod 33 is extended via a compression spring 34, which The piston rod 33 is retracted by means of hydraulic fluid. If the piston rod 33 with the wedge 31 attached to it moves in or out, the securing claw 30 is pivoted on its axis 37 and thus opened or closed. The steep slope 35 of the wedge 31 serves to ensure that the securing claw 30 moves in a large angle of rotation in a short time. The smaller slope 36 of the wedge or tappet 31 is used to ensure that the securing claw 30 receives a high closing force and great self-locking.

When closing (see Figure 5b ) of the securing claw 30, this is pressed against the adapter shaft 9b of the adapter frame 3. This ensures that when the quick changer 2 is locked, the adapter shaft 9b is firmly pressed into the two catch hook openings. If the quick coupler 2 is locked even though it has not been swiveled completely into the adapter frame 3 and the two locking bolts move onto the block or into space ( Fig. 6a or 6b ), the attachment 4 can no longer fall off the quick coupler ( Fig. 7 ). The fact that the securing claw is pressed against the receiving axis of the adapter frame and this in turn into the two catch hook openings means that the generated clamping force almost prevents the attachment tool from swinging and swinging if it is incorrectly locked in the catch hook openings.

The present invention also makes crane operation more difficult or even prevented by the securing claw 30 arranged between the two catch hooks 20.

If the quick changer 2 is locked with the locking bolts 38a, 38b in the locking position, without the locking bolts 38a, 38b engaging the adapter frame 3, the securing claw 30 is also closed. No attachment tool 4 or load attachment means can be picked up with the catch hook 20, since the securing claw 30 blocks the way into the catch hook opening 47. An attachment tool 4 or a load attachment means can now only be picked up when the quick coupler 2 is unlocked. While the quick coupler is unlocked, a warning signal can sound in the driver's cab 23. The displays 21 can from the Quick coupler housing extended ( Fig. 12 ) and the safety claw 30 is open. These three features then signal to the operator the unlocked position of the quick coupler 2 and thus a safety-critical state. If the operator carries out crane operation in spite of the unlocked quick coupler 2 and the opened safety claw 30, he deliberately opposes the ban on crane operation. If the operator now locks the quick coupler 2 after picking up the load 4 in order to switch off the warning signal, the securing claw 30 secures the load.

The quick changer 2 has, like in particular the Figures 8a to 8c show a cuboid housing 17. The housing 17 is open on at least one side in order to insert one into the Figures 12a, 12b Locking unit shown in detail with its three hydraulic linear actuators 18a, 18b, 19 to be received. The locking unit is inserted into the housing 17 and fixed to the quick coupler frame or housing 17 or screwed directly onto the quick coupler housing 17.

On the front underside of the quick coupler housing 17 are the two immovable, parallel to each other aligned catch hooks 20 with the opening 47 to the front. These openings 47 are intended to accommodate the adapter shaft 9a, 9b or 9c. On the rear side or on the rear of the housing 22 of the quick changer 2, the two locking bolts 38a, 38b, the right locking bolt 38a are to be moved and extended by the right linear actuator 18a, 40a, 45a and the left locking bolt 38b by the left linear actuator 18b, 40b, 45b, in order to firmly clamp the quick coupler 2 in the adapter frame 3.

The right and left linear actuators together form a first hydraulic linear actuator system 18a, 40a, 45a, 18b, 40b, 45b for actuating the locking elements 38a, 38b formed by the two locking bolts 38a, 38b.

Another hydraulic linear actuator system 19, 34, 46, which is used to move the actuating bolt or the central piston rod 33, is accommodated in the locking unit or the housing 58 of the locking unit 58, called the locking housing, between the two outer linear actuators. The further hydraulic linear actuator system 19, 34, 46 together with the central piston rod 33 forms a hydraulically drivable actuating device 19, 33, 34, 46 for actuating the securing claw 30, which is in turn part of a safety device which is intended to prevent the attachment 4 from falling off the quick coupler 2 in the event of an inadequate locking of the locking bolts 38a, 38b.

The locking housing 58 consists, for example, of a milled block with cutouts which are connected to one another by bores: the linear actuators are integrated in the cutouts. On the outside on the left and right side of the locking housing 58, two holders with bores or bores can be arranged. The locking unit 58 is fastened to the quick coupler housing 17 by means of screws and dowel pins with these bores. However, the locking housing 58 can also be implemented directly as part of the quick coupler housing or inserted and fixed by other devices. The locking unit can, however, also consist of individual linear actuators in any form, which are connected to one another by tubing or pipes or fluid channels in the quick coupler housing and thus form a unit.

The two outer piston rods 38a, 38b are connected in parallel and connected in the locking housing 58 by channel bores. The supply line for the two outer piston rods 38a, 38b to the third, central piston rod 33 is released via channel bores in the locking housing 58. The openings of the duct bores are closed with screw plugs or expanders.

Depending on the design, one or more hydraulic connections 53 are located on the upper side of the locking housing 58. The hydraulic connection 53 is designed as a screw-in thread 54 and a counterbore 55. A screw connection can be screwed into the locking unit 58 and the linear actuators can be connected to the hydraulic system or a seal is inserted into the countersink of the locking housing 58 and screwed against a milled sealing surface of the quick changer housing and thus sealed. For example, this is solved in this way for quick couplers with a swivel motor structure Fig. 20 ).

On one or both sides, a locking visual indicator rod 21 is attached to the respective locking bolt 38a, 38b by the respective screwed-in driver 41. This locking indicator 21, which can be designed both flat and as a round rod can is mounted and guided on the cylinder housing or in the quick coupler housing 17 either on the top when the driver 41 points upwards, or laterally when the driver 41 points outwards. The visual indicator rod 21 protrudes longitudinally up to the front to the front end of the quick changer housing 17. The length of the locking visual indicator rod 21 is designed in such a way that when the quick changer 2 is locked, the locking indicator 21 in the quick changer housing 17 has disappeared and can no longer be seen by the operator. If the quick coupler is unlocked, the two locking bolts 38a, 38b retract and the corresponding locking indicators 21 move out of the quick coupler housing 17 at the front. The locking display 21 visible to the operator signals the safety-critical state of the quick coupler 2.

In addition to the variant of a quick coupler consisting of several components, this can also be designed as a complete unit, whereby the cuboid housing 17 with its catch hook 20 and the housing of the locking unit 58 form an inseparable unit and the hydraulic linear actuators 18a, 40a, 45a, 18b, 40b, 45b and 19, 34, 46 can be integrated directly.

The housing 17 is constructed in such a way that all three linear actuators 18a, 40a, 45a and 18b, 40b, 45b and 19, 34, 46, as well as the locking bolts 38a, 38b are mounted from the rear. It goes without saying that the housing 17 can also be constructed in such a way that assembly takes place completely or partially from the front.

The quick changer 2 is controlled via the three linear actuators, each with a piston rod 38a, 38b, 33. The two outer piston rods 38a, 38b function as the locking bolts or - if the locking bolts consist of several components - as the rear section of the locking bolt unit. The middle piston rod 33 functions as an actuating bolt which is used to move the wedge 31 and which in turn is used to move the rocker 27 with the securing claw 30. The linear actuators either share the same housing or they are individual linear actuators that are connected to one another by their respective housings by hose or pipelines or fluid channels in the quick coupler housing and are thus built into the quick coupler housing.

While in the quick changer 2 according to the first embodiment, the middle Piston rod 33 is moved by a single-acting linear actuator 19, double-acting linear actuators can also be installed, in particular for the locking, which results in two possible variants of the quick coupler and its load capacity: the single-acting, which can be used for smaller earth-moving machines, or the double-acting control, which can accommodate higher locking restoring forces and thus heavier attachment tools. In general, it is also possible to move the middle piston rod 33 with a double-acting linear actuator so that the securing claw 30 can absorb higher forces and thus hold heavier attachments.

With the single-acting control, a compression spring 40a, 40b and 34 is installed in the locking housing 58 of the linear actuators 18a, 18b and 19 behind each piston 45a, 45b and 46 in order to lock the quick coupler 2 or to close the safety claw 30. Due to the pretensioned compression springs 40a, 40b, 34 and the piston rods 38a, 38b, 33 extended as a result, this is the basic position of the three pistons 45a, 45b, 46 when no hydraulic pressure is acting. The compression springs 40a, 40b of the outer piston rods 38a, 38b are designed in such a way that they withstand the forces that occur during proper operation and that the loads that occur do not overcome the locking force. In order to generate an even higher locking force, several compression springs can be built into one another. In addition, both locking bolts 38a, 38b are acted upon separately from one another by spring force by the compression springs 40a, 40b; H. if the compression spring 40a, 40b of a locking bolt 38a or 38b fails, the compression spring 40b, 40a of the other locking bolt still engages.

The middle compression spring 34 is designed so that it can hold the heaviest attachment 4 that can be picked up with the quick coupler 2 with the securing claw 30 securely in the catch hook openings 47 ( Fig. 7 ).

It is unlocked by applying hydraulic pressure. The two outer piston rods 38a, 38b are connected in parallel and retract in parallel when unlocking. A 2/2-way tappet valve 39 is positioned behind one of the two outer piston rods, here 38a. As soon as this locking bolt is almost completely retracted, the piston rod 38a moves onto a valve tappet 43 and thus actuates the 2/2-way valve 39. Only when the 2/2-way tappet valve 39 is actuated does it switch the fluid channel to the central linear actuator 19 free. Only then is hydraulic pressure applied to the central piston 46 and the central piston rod 33 with the wedge 31 mounted on it retracts. This series connection brings additional security to the quick coupler, since the quick coupler 2 can only be pivoted out of the adapter frame 3 with the catch hook 20 when it is completely unlocked.

On the locking bolts 38a, 38b are drivers 41 for moving the in the Figures 12a, 12b lock visual indicators 21 shown attached. The drivers 41 also serve as an anti-twist device for the locking bolts. In the event that no locking indicator is to be attached, a shorter anti-rotation device 42 can also be installed.

It should also be said that in addition to the single-acting variant ( Figure 9b ) with a 2/2-way slide valve 39 also a variant ( Figure 9a ) is possible without this. In this case ( Figure 9a ) there is no series connection, but a parallel connection of all three linear actuators when unlocking. If the locking bolts 38a, 38b are retracted, the securing claw 30 also opens at the same time. The securing claw 30 is not opened with a delay. However, this has no effect on the initial benefit of the invention - the immediate securing of the attachment 4, even in the event of incorrect positioning. If, however, a delayed opening of the securing claw 30 is to be generated, one can also resort to a throttling in the supply line of the central linear actuator 19. By this, the securing claw 30 is delayed or opened more slowly.

In an embodiment of the invention with double-acting control ( Figures 10a, 10b , 10c ) of the locking bolts, the two outer linear actuators 48a, 45a, 48b, 45b are double-acting and can be connected in parallel and each equipped with a hydraulically releasable check valve 44 ( Figures 11a, 11b ). A variant is also possible here in which the double-acting outer linear actuators 48a, 45a, 48b, 45b are equipped with a common releasable check valve 44 before the parallel connection ( Figures 11c, 11d ). The check valves used can be designed either unloaded or spring-loaded. The locking takes place by means of permanent hydraulic pressure.

The middle piston rod 33 is designed here to be single-acting and extends by means of spring pressure. The pistons 45a, 45b and the compression spring 34 of the three linear actuators are dimensioned so that they apply a correspondingly high force that they can withstand the forces that occur during proper operation and that the loads that occur do not overcome the locking force. In addition, hydraulic pressure is applied to both locking bolts 38a, 38b in parallel and separately from one another, ie if one of the two outer piston rods should fail, the second piston rod still engages. The middle compression spring 34 is dimensioned so that the middle piston rod 33 applies a correspondingly high force in order to be able to securely hold the heaviest attachment that can be picked up with the quick coupler 2 with the securing claw 30 in the catch hook openings 47. In order to generate an even higher locking force, several compression springs can be built into one another.

In the event that the two outer piston rods do not function as complete locking bolts 38a, 38b, a locking bolt attachment 50a, 50b is axially screwed onto the front end of the piston rods 49a, 49b via a thread. The locking bolts have a threaded transverse hole on the side or top on the outer jacket surface. A cylinder screw or a turned part with a collar is screwed into this hole. Another variant is a hole with a fixation by a dowel pin 42. The head of the cylinder screw or the collar of the rotating part or the dowel pin is guided in a milled longitudinal groove on the side or top of the locking bolt bearing and thus the locking bolt is secured against twisting.

In general, it is also possible to move the middle piston rod 33 with a double-acting linear actuator ( Figures 11e, 11f ) so that the safety claw 30 can absorb even higher forces and thus hold heavier attachments. The double-acting middle linear actuator can also be equipped with a pilot operated check valve ( Figures 11i, 11j ). A variant is also possible here in which all linear actuators are equipped with a common releasable non-return valve 44 upstream of the parallel connection ( Figures 11g, 11h ).

It is unlocked by applying hydraulic pressure. The two outer piston rods 38a, 38b are connected in parallel and retract in parallel when unlocking. According to the Figure 11b A 2/2-way slide valve 39 is positioned behind one of the two outer piston rods, here 38a, behind one of the two outer piston rods shown. As soon as this locking bolt is almost completely retracted, the piston rod moves onto the valve stem 43 and actuates the 2/2-way valve 39. Only when the valve is actuated does it switch the Fluid channel to central piston rod 33 of securing claw 30 is free. Only then is hydraulic pressure applied to the central piston rod 33 and the central piston rod 33 with the plug 31 mounted on it retracts.

The series connection brings additional security to the quick hitch. The quick coupler can only be pivoted out of the adapter frame 3 with the catch hook 20 when it is completely unlocked. On the locking bolts 38a, 38b drivers 41 for moving the locking visual indicators 21 are attached ( Fig. 12 ). The drivers 41 also serve as an anti-twist device for the locking bolts. In the event that no locking indicator is to be attached, a shorter anti-rotation device 42 can also be installed.

In addition to the double-acting variant with a 2/2-way slide valve ( Figure 11b ), a variant without this is also possible ( Figure 11a ). In this case there is no series connection, but a parallel connection of all three linear actuators 48a, 48b and 19 during unlocking. If the locking bolts are retracted, the securing claw 30 opens at the same time. The securing claw 30 is not opened with a delay. However, this has no effect on the initial benefit of the invention - the immediate securing of the lock, even in the event of incorrect positioning. If, however, a delayed opening of the safety claw is to be generated, one can resort to throttling in the supply line of the central linear actuator 19. This delays the safety claw or opens it more slowly.

In the rear of the lock housing, a piston rod or locking pin bearing is arranged on the left and right side. The optional sockets 56 are used to mount the locking bolts in the linear actuator housing and are secured against axial movement by a securing element such as a clamping ring 57. The plain bearing bushes have an opening so that the anti-rotation device 42 attached to the locking bolt can engage in the locking bolt bearing. The sockets are either designed with a lubricating nipple or a self-lubricating material.

The wedge or plunger 31 for actuating the securing claw 30 is mounted on the central piston rod 33. The connection is designed in such a way that the locking forces via the graduation attached to the piston rod 33 be transferred positively to the wedge 31. When unlocking, the force from the central piston rod 33 could be via a connecting element, such as. B. a dowel pin can be transferred to the wedge 31. In addition, the wedge is positively mounted in the linear actuator housing via the upper and side contact surfaces. Thus, transverse forces which are conducted from the securing claw 30 onto the piston rod are absorbed. It goes without saying that other fastening and force transmission variants can also be used, see in particular those in FIGS Figures 17 and 18th Shown embodiments of the quick changer according to the invention with a rack 71 - pinion 72 - gear between securing claw 70 and actuating bolt 73 or with a pivot rod 81, to which rocker 87 and actuating bolt 83 is articulated.

It must also be noted that the shape of the wedge and the rear end of the locking claw have an effect on the required direction of movement of the piston rod. Depending on the variant, the compression spring must retract the middle piston rod for the claw lock (e.g. Fig. 16 ) or extend (e.g. Fig. 13 ). The hydraulic line connections and routes within the quick coupler must therefore also be adapted for the corresponding variant. This means that only securing claws and wedges that fit with one another and with the direction of piston movement can be used. In order to be able to mount the wedge on the middle piston rod, the underside of the locking unit must be open. A cover is attached here to prevent foreign bodies from entering. In addition to the use of a gearbox and another hydraulic linear actuator system, a swivel motor 69 can also be used to swivel the safety claw. Fig. 19 ) can be used.

It is advantageous to have a thread 51 drilled on the front side of the piston rod 33 on the side of the piston. A cover 12 is then either screwed onto the rear housing of the quick changer or a hole with a screw plug is attached. When using a cover on the rear of the housing, a threaded hole with screw plug 52 is also provided in the center of the cover. In this way, an emergency release device can be attached in the event of a defect.

Variations and modifications of the embodiments shown are possible without departing from the scope of the invention.

Claims (15)

Quick coupler (2) for coupling and uncoupling attachments (4) to or from a dipperstick (1) of an earth-moving machine (5), wherein
the quick coupler (2) has a quick coupler frame (17), preferably designed as a housing, which on its front side has a number, preferably two laterally spaced apart, claw-shaped catch hooks (20) with a preferably forward facing opening for engaging a shaft (9a, 9b , 9c) on the attachment (4) and on which a number of locking elements are received, preferably retractable and extendable at the rear, and wherein
the quick coupler frame (17) carries a first single or double-acting hydraulic linear actuator system (18a, 40a, 45a, 18b, 40b, 45b; 48a, 45a, 48b, 45b) via which the number of locking elements (38a, 38b; 50a, 50b) to Locking or unlocking on the attachment (4) can be moved linearly between a locking position, in particular shifted to the rear, and an unlocking position, in particular shifted to the front, and wherein
a safety device is provided to prevent the attachment (4) from falling off the quick coupler (2) in the event of insufficient locking of the number of locking elements (38a, 38b; 50a, 50b), as well as a separate, hydraulically driven actuating device (19, 33, 34, 46; 69; 79, 73; 83) for actuating the safety device, characterized in that
the securing device comprises at least one securing claw (30; 60; 70; 80) which is arranged on the front side of the quick coupler frame (17) so as to be pivotable about an axis (37) which is axially parallel to the shaft (9a, 9b, 9c), the securing claw (30 ; 60; 70; 80) via the actuating device (19, 33, 34, 46; 69; 79, 73; 83) at least from its release position, in which it releases the shaft (9a, 9b, 9c), into its access position , in which it grips the shaft (9a, 9b, 9c), is pivotable. Quick coupler (2) according to Claim 1, characterized in that the securing claw (30) is pretensioned into its release position via a pretensioning device (28), the pretensioning device (28) preferably a number of which are wound around the axis (37) and attached to the securing claw ( 30) attacking leg springs (28) comprises. Quick coupler (2) according to claim 1 or 2, characterized in that the actuating device (69) comprises a hydraulic rotary motor (69), around the axis of which the securing claw (60) is positioned between their by means of the rotary motor (69) engaging the securing claw (60) Release position and its access position is pivotable. Quick coupler (2) according to claim 1 or 2, characterized in that the securing claw (30) is penetrated by an axle bolt (37) which preferably extends between the two catch hooks (20), in the area of the catch hooks (20) on the quick coupler frame (17) and forms the axis (37) on which the securing claw (30) is pivotably suspended. Quick coupler (2) according to claim 1, 2 or 3, characterized in that the actuating device (19, 33, 34, 46; 79, 73; 83) accommodated at least one in the quick coupler frame (17) such that it can be moved towards and away from it Includes actuating bolt (33; 73; 83), as well as a further single or double-acting hydraulic linear actuator system (19, 34, 46; 79), via which the at least one actuating bolt (33; 73; 83) moves between a forwardly extended operating position and a forward rear retracted release position is linearly movable, wherein
the at least one actuation bolt (33; 73) and the at least one securing claw (30; 70) are each coupled via a gear (31, 32; 71, 72; 81) via which the securing claw (30; 70; 80) at least its release position is pivotable into its access position, in response to the movement of the actuation bolt (33; 73; 83) from its release position into its actuation position. Quick changer (2) according to claim 4 or 5, characterized in that a circumferential section (72) of the securing claw (70) is designed as a pinion and with an end section designed as a rack of an end of the actuating bolt (73) facing the securing claw (27) attached plunger (71) combs in response to the movement of the actuating bolt (73) between its release position and its actuation position to pivot the securing claw (70) between its release position and its access position. Quick coupler (2) according to claim 4 or 5, characterized in that the Securing claw (30; 80) is formed on a rocker (27; 87) which is pivotably suspended on the axis (37), the rocker (27; 87) extending from the axis (37) in the direction of the actuating bolt (33 ; 83) having rear-side rocker limbs (29; 89) and wherein the securing claw (30; 80) forms a front-side rocker limb (30; 80) of the rocker (27; 87) extending forward from the axis. Quick coupler (2) according to claim 5 or 7, characterized in that the gear (81) has a pivot rod (81) articulated to the actuating bolt (83) on the one hand and the securing claw (80) on the other, via which, in response to the method of Actuating bolt (83) between its release position and its actuating position, the securing claw (80) is pivotable between its release position and its access position, the pivot rod (81) preferably being hinged to the rear rocker leg (89). Quick changer (2) according to claim 5 or 7, characterized in that the gear (29, 31) is designed as a wedge gear (29, 31) which couples the actuating bolt (33) with the securing claw (30) and via which in response to the method of the actuation bolt (33) from its release position into its actuation position, the securing claw (30) can be pivoted from its release position into its access position. Quick changer (2) according to one of claims 5 to 9, characterized in that the actuating bolt (33) has a preferably wedge-shaped plunger (31) at its end facing the securing claw (30), wherein
the tappet (31) has an actuation surface (35, 36; 95; 115) which is inclined or curved in relation to the direction of displacement of the actuating bolt (33), preferably facing the securing claw (30), and the securing claw (30) has one on the actuation surface (35, 36) ; 95; 115) running down and preferably facing the plunger (31) contact surface (32; 92; 112)
and or
the securing claw (30) has a contact surface which is inclined or curved in relation to the direction of displacement of the actuating bolt (33), preferably facing the plunger (31) (32; 92; 102; 112), and the plunger (31) has an actuation surface (35, 36; 95; 105; 115) running on the contact surface (32; 92; 112), preferably facing the securing claw (30). Quick changer (2) according to claim 10, characterized in that the contact surface (32) is formed on the rear rocker leg (29) and at least with a directional component points upwards, while the actuation surface (35, 36) on the plunger (31) at least with a directional component pointing downwards, so that when the actuating bolt (33) is extended into its actuating position, the rear rocker leg (29) is pressed down by the plunger (31) and the securing claw (30) is pivoted upwards into its access position. Quick changer according to claim 10 or 11, characterized in that the actuating surface (35, 36) has a first actuating surface section (35) on its end of the plunger (31) facing the securing claw (30) and one thereon in the direction away from the securing claw (30) the following, second actuating surface section (36), the first actuating surface section (35) having a greater inclination than the second actuating surface section (36) for the direction of displacement of the actuating bolt (33). Quick coupler according to one of claims 5 to 12, characterized in that the first hydraulic linear actuator system (18a, 40a, 45a, 18b, 40b, 45b; 48a, 45a, 48b, 45b) with the number of locking elements (38a, 38b; 50a, 50b) and the further hydraulic linear actuator system (19, 34, 46) with the actuating bolt (33) are arranged in a common locking housing (58) which is formed in one piece with the quick coupler frame or is connected, preferably screwed, to the quick coupler frame (17), the locking housing ( 58) is preferably inserted into the interior of the quick-change frame (17), and the locking housing (58) preferably has an opening on the underside which allows assembly access for fastening the plunger (31) to the securing bolt (33) and which can be closed with a cover. Quick coupler according to one of the preceding claims, characterized in that the number, preferably two, locking elements (38a, 38b; 50a, 50b) is formed as a number, preferably two, locking bolts (38a, 38b; 50a, 50b) and the first hydraulic linear actuator system (18a, 40a, 45a, 18b, 40b, 45b; 48a, 45a, 48b, 45b) for each locking bolt (38a, 38b; 50a, 50b) with a separate pressure chamber (18a, 18b; 48a, 48b) a piston (45a, 45b) received therein so as to be slidable towards the rear and away from it, the locking bolt (38a, 38b; 50a, 50b) being integrally formed on the piston or attached to the piston (45a, 45b), and wherein the pressure chamber (18a, 18b; 48a, 48b) extends with its longitudinal axis along the quick coupler frame (17) towards the rear of the quick coupler frame (17) so that each locking bolt (38a, 38b; 50a, 50b) is at least out of its locking position can be moved into its unlocked position towards the front of the quick coupler frame (17) by applying hydraulic pressure to the associated pressure chamber (18a, 18b; 48a, 48b) and the piston (45a, 45b), and the number of locking bolts (38a, 38b; 50a, 50b) preferably wedge-shaped at its end run out, and in an advantageous further development the number of locking bolts (38a, 38b; 50a, 50b) in each case at least one driver (41, 42) protruding circumferentially in the radial direction is fastened, which is located in an associated elongated hole guide in the locking housing (58) or the quick coupler frame (17) running parallel to the respective locking bolt (38a, 38b; 50a, 50b) ), wherein at least one of the driver pins (41) is preferably connected to a locking indicator pin (21) which extends along the quick coupler frame (17) to the front side so far that it is there in the unlocked position of the locking bolt (38a, 38b ; 50a, 50b) protrudes and does not protrude in the locked position. Quick coupler according to one of claims 5 to 14, characterized in that the further hydraulic linear actuator system (19, 34, 46; 79) for the preferably single actuating bolt (33; 73) has a pressure chamber (19) with a pressure chamber (19) therein towards the front and away from it comprises displaceably received pistons (46; 73), the actuating pin (33; 73) being formed in one piece on the piston (73) or attached to the piston (46) and the plunger (31; 71) being formed in one piece on the actuating pin or on the actuating bolt (33; 73) is attached, the pressure chamber (19; 79) each extending with its longitudinal axis along the quick coupler frame (17) to the front, so that the actuating bolt (33; 73) in each case at least from its actuating position into its release position by Loading of the pressure chamber (19; 79) and the piston (46; 73) with hydraulic pressure is displaceable to the rear, wherein in the hydraulic supply line to Pressure chamber (19) preferably a 2/2-way plunger valve (39) is provided, the valve plunger (43) of which on the side facing the front side of one of the pressure chambers (18a; 48a) of the first hydraulic linear actuator system (18a, 48a) into the pressure chamber ( 18a; 48a) protrudes, and the piston (45a, 45b) there is provided with a piston rod (49a) which presses on the valve stem (43) when the locking position is approached, so that the hydraulic supply line is released.

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