EP1727945B1 - Quick-change device with a hydraulic coupling for media on a building implement - Google Patents

Abstract

The invention relates to a quick-change device with a hydraulic coupling for media on a building implement, comprised of a quick-changer (30), which is fastened to the implement and which can be locked together with an adapter plate (12) fastened to the tool, and comprised of a device for aligning interacting parts between the building implement and the tool. A respective coupling valve (1, 3) is mounted on the quick-changer (30) and on the adapter plate (12), at least one coupling valve (1, 3) being mounted in a floating manner. According to the invention, a device is provided for aligning for the locking motion between the quick-changer (30) and the adapter plate (12) (primary alignment), and a separate device is provided for aligning the hydraulic coupling with regard to the quick-changer (30) and/or to the adapter plate (12) during operation (secondary alignment).

Description

The invention relates to a quick-change device according to the preamble of patent claim 1.

Such quick-change devices have become known in various embodiments.

A first embodiment of a quick-change device is for example from the EP 0 483 232 B1 known, in which the quick-change device consists of a swivel and Verrieglungseinrichtung comprehensive quick coupler and an adapter plate. The quick coupler is the excavator-side stem and the opposite, with the quick coupler to be coupled adapter plate is a replaceable tool, eg. B. an excavator bucket assigned.

The swivel lock described in the cited document first provides a merger of a hydraulic coupling of the media before the production of the lock between the adapter plate and quick coupler. Such media couplings must be brought together over a relatively wide pivoting.

Since coupling valves of the hydraulic clutch are brought together before the pivoting of the quick coupler to the adapter plate and liquid-tight, there is the disadvantage that very large, dirt-contacting surfaces are present, which lead to a dirt entry into the oil circuit when connecting the media feedthrough.

The said hydraulic couplings are arranged completely free in the space between the adapter plate and the quick coupler and therefore not suitable to work properly in Schmutzbelasteter environment.

In addition, in play-related pivot axis between the adapter plate and quick coupler, the two associated with each other and to be coupled with each other media feedthroughs are no longer centered to each other, beat against each other and the associated seals wear very strong.

The immersion of the associated media clutches during the pivoting movement of the adapter plate relative to the quick coupler is connected to a very long pivoting path, which means that the two media clutches touch each other over a very long pivoting and immersion path and rub against each other. As a result, the wear is very high.

In such a quick-change device, there is the disadvantage that initially in the open, unlocked position of the Schenkverriegelung the hydraulic clutch is produced, which is associated with the risk of damage due to high forces occurring. Only after Production of the hydraulic clutch engages the lock between the adapter plate and the quick coupler and holds them in a predetermined position to each other.

From the DE 101 59 417 A1 a quick coupler according to the preamble of claim 1 is known, in which in the last pivoting of the pivoting movement between the adapter plate and quick coupler a linear guide is provided. This linear guide is intended to center the mutually associated hydraulic couplings and the quick coupler to the adapter plate for the coupling movement to each other before they are liquid-tight coupled and interconnected.

The disadvantage of the known longitudinal guide, however, is that over a very long immersion a longitudinal guide to align the associated clutch valves and the quick coupler to the adapter plate, resulting in large, dirt-contaminated surfaces corresponding wear, thereby resulting game and the resulting disturbance forces on the hydraulic Coupling is connected. Since this centering also serves the orientation of the quick coupler to the adapter plate, thereby acting great forces.

This document discloses, moreover, a hydraulic clutch of the form that the one clutch valve firmly and immovably to one part, z. B. the adapter plate is mounted, while the other opposing coupling valve floating and biased by springs on the other opposite and pivotable part of the quick-change device is attached.

It is already described so that a floating centering of the two associated coupling valves.

Disadvantage of this arrangement, however, is that the floating centering is done by spring packets that are completely free and open and are therefore exposed to a high risk of contamination. On the one hand, the function of the springs is endangered because they sit down full of dirt and their spring capacity no longer reach and on the other hand, a high wear, because all the parts of the hydraulic coupling must work in a highly aggressive and polluted atmosphere. As is known, construction equipment, in particular excavators, work under heavily loaded environmental conditions, in particular in civil engineering and canal construction.

The there incurred aggressive wastewater affect the floating storage and centering of the associated clutch valves, so that their centering function can not be ensured over a longer life.

This also applies to the still additionally used clamping cylinder, which should provide a pressing force between the mutually associated coupling valves in order to avoid that the coupled high-pressure oil blows the two coupling valves apart.

The invention has for its object to improve the alignment of the coupling valves for the equipment required on a construction equipment according to the preamble of claim 1, so as to provide a hydraulic coupling for much longer life and less wear and thus a cost-effective and reliable hydraulic coupling to achieve the media implementation.

This object is solved by the characterizing features of claim 1 in conjunction with its preamble features.

The invention is based on the finding that by separating the alignment / centering for the locking movement and the alignment / centering of the clutch valves during operation, the load corresponding to the different forces occurring during locking on the one hand and during operation between the clutch valves distributed on the other side and thus the wear can be reduced. Above all, this significantly increases the reliability of the connection of the hydraulic clutch.

There are therefore a means for aligning the locking movement between quick coupler and adapter plate - primary alignment - and a separate means for aligning the hydraulic coupling with respect to the quick coupler and / or the adapter plate during operation - secondary alignment - provided.

An essential feature of the invention is also that the device for the secondary alignment, the floating mounting of a coupling valve, z. B. the upper coupling valve, and is formed in the form of an elastomeric Abdrückelements which presses against a fixed part of the quick-change device and acts with at least two mutually parallel surfaces with central biasing force on the coupling valve.

In particular, a mutually associated coupling valve is provided in each case at the free, pivotable end of the quick coupler and the adapter plate.

The push-off element is preferably designed as elastomeric rubber, which is associated with the advantage that the push-off element now simultaneously assumes sealing and guiding / compensating functions.

The arrangement of a Abdrückelementes with at least two mutually parallel surfaces, the advantage of an accurate centric Abdrückkraft results on the top of the coupling valve, so that canting forces can no longer act.

A possibly acting dirt load can no longer be used in the space of now no longer used springs, but the elastomeric Abdrückelement is self-contained and preferably forms a spectacle-shaped receiving space, so that it is formed with ring encircling walls.

The encircling walls provide a self-contained Abdrückelement which is arranged with its upper end faces on the upper side of a yoke of the quick coupler, while the lower end faces press on the upper side of the upper coupling valve.

Thus, lateral jams on the floating upper coupling valve are collected, because not only the parallel, relatively long trained side walls of the Abdrückelementes take over a guiding and compensation function, but also the shorter end walls, which form a total of approximately circumferential, oval hollow part.

By forming this Abdrückelementes as an oval hollow part has the further advantage that now an inner receiving space between a fixed yoke of the quick coupler and the floating mounted below the clutch valve, which is arranged in particular in a valve block is formed, which is preferably filled with a flowable grease , In this way, the floating function of the upper coupling valve is always ensured because the trapped in the receiving space grease ensures a reliable seal the floating storage under all aggressive environmental conditions.

According to one embodiment of the invention, the Abdrückelement relatively large wall thicknesses of z. B. 5-50 mm, because these wall thicknesses form a very good tilt protection for lateral jounce joints.

The push-off element is pretensioned between the upper coupling valve and the lower coupling valve and the intended, thick wall thicknesses ensure that the push-off element does not buckle, but deforms in the direction of the axial pushing movement (plunging movement of the valve). A lateral buckling, bulging is indeed not prevented, but it is provided for an absolutely central deformation of this Abdrückelementes.

In a preferred embodiment of the shaping of the Abdrückelementes is provided that in the walls of the Abdrückelementes debilitating recesses are present, so as to control the Ausknick- or deformation behavior and the hardness of these walls.

An idea of the invention is thus also that an elastomeric pressure element is used both as a sealing element and as a pressure element itself, which is associated with a much higher reliability and reliability of the entire arrangement.

Dirt carried on the side of the upper coupling valve and aggressive sewage can no longer penetrate into the upper coupling valve.

The entire floating suspension of the upper coupling valve is hermetically sealed by the Abdrückelement invention and the purity of the closed interior is prepared by filling with fluid grease or graphite foam or other suitable medium and always maintained.

As far as aggressive wastewater and dirt loads could get into the contact surfaces between the mutually associated coupling valves, a water injection of the mutually associated and successive dipping contact surfaces of the coupling valves is also provided.

In a further development of the invention, it is otherwise provided that the push-off element biases the upper coupling valve against the housing-fixed yoke in the idle state with a certain bias.

This is important and advantageous when a swivel spoon is stored and the upper coupling valve remains only on the excavator handle or on the arranged on the excavator handle quick coupler.

If tumbling or swiveling movements with a high degree of acceleration are now carried out with the excavator handle, there is the risk that the floating bearing leads to tilting of the upper coupling valve. This is avoided according to the invention in that the elastomeric pressure element is arranged with a considerable biasing force between the quick coupler side yoke and the upper coupling valve, so as to bias the upper coupling valve with high biasing force and thereby avoid tilting of the floating bearing.

In a preferred embodiment of the invention, it is also provided that, in addition to the pressing force, which between the upper coupling valve and the lower Clutch valve acts and is provided only by the elastomeric Abdrückelement, in addition a hydraulic damper is turned on.

This hydraulic damper dampens load surges acting on the contact surface between the upper and lower coupling valves, especially when the excavator tool is a hammer drill, which penetrates into the ground with high acceleration forces and initiates corresponding acceleration shocks on the connection surface between the upper and lower coupling valves.

These additional acceleration forces, which act in particular in the axial direction on the two clutch valves, are absorbed by the hydraulic damper, which dampens the pressing force of the Abdrückelementes to prevent unacceptable vibration of the Abdrückelementes. It should be avoided resonant vibrations on Abdrückelement that could be introduced to the valve body in an unfavorable manner. For this purpose, the hydraulic damper according to the invention is provided.

The hydraulic damper can be realized either by a separate component above the elastomeric Abdrückelementes or by the elastomeric Abdrückelement itself.

Further advantages and possible applications of the present invention will become apparent from the following description in conjunction with the embodiment shown in the drawing.

Figur 1

eine schematisierte Darstellung einer Schnellwechselvorrichtung nach der Erfindung in geöffnetem Zustand;

Figur 2

die Schnellwechselvorrichtung von Figur 1 im geschlossenen Zustand mit Darstellung weite- rer Einzelheiten;

Figur 3

eine vergrößerte Schnittdarstellung der hyd- raulischen Kupplung der Schnellwechselvor- richtung von Figur 2 im noch nicht verbunde- nen Zustand;

Figur 4

eine vergrößerte Schnittdarstellung der hyd- raulischen Kupplung der Schnellwechselvor- richtung von Figur 2 im verbundenen und flüs- sigkeitsleitendem Zustand;

Figur 5

die Seitenansicht des elastomeren Abdrückele- mentes;

Figur 6

die Draufsicht auf das elastomere Abdrückele- ment;

Figur 7

die Draufsicht auf die Schnellwechselvorrich- tung in Richtung auf den Schnellwechsler.

In the description, in the claims, in the abstract and in the drawing, the terms and associated reference numerals used in the list of reference numerals recited below are used. Show it:

FIG. 1

a schematic representation of a quick-change device according to the invention in the open state;

FIG. 2

the quick-change device of FIG. 1 in the closed state with further details;

FIG. 3

an enlarged sectional view of the hydraulic coupling of Schnellwechselvor- direction of FIG. 2 not yet connected;

FIG. 4

an enlarged sectional view of the hydraulic coupling of Schnellwechselvor- direction of FIG. 2 in the connected and liquid-conducting state;

FIG. 5

the side view of the elastomeric Abdrückele- mentes;

FIG. 6

the top view of the elastomeric Abdrückele- ment;

FIG. 7

the top view of the quick-change device in the direction of the quick coupler.

The quick-change device after the FIGS. 1 and 2 essentially comprises a quick coupler 30 and an adapter plate 12, in front of which the quick coupler 30 is attached to a boom, not shown, an earthmoving machine, also not shown, and the adapter plate 12 associated with the work implement, also not shown, and is firmly connected thereto.

The adapter plate 12 comprises a base plate 14, on which at one end a latch plate 16 and at the opposite end by means of fastening tabs 17, a pivot axis / coupling axis 19 are welded. The locking plate 16 has on the side facing the coupling axis 19 a clamping surface 20 which is inclined to a vertical surface of the adapter plate 12 by 3 ° to 35 degrees, preferably by 5 to 15 degrees.

The locking plate 16 is further provided with two spaced-apart and conically shaped in longitudinal section, arranged parallel to each other cone openings 21. Each cone breakthrough 21 is associated with an associated latch bolt 36 which can be displaced into it.

The front end of the locking bolt 36 is formed in each case as a cone end 50.

The cone angle of the conical breakthroughs 21 delimited by the conical surface areas is dimensioned correspondingly and in the illustrated embodiment is 5 ° to 15 degrees.

The approximately rectangular quick coupler 30 has on its side surfaces depending on a receiving claw 31, which engage around the coupling axis 19 in the retracted state. The end face of the quick coupler 30 located between the receiving claws 31 merges into a cylindrical jacket-shaped abutment surface 32 which, in the retracted state, is supported on the cylinder jacket surface of the coupling axis 19.

The facing end face 34 is inclined by 3 to 35 degrees, preferably by 5 to 15 degrees, relative to the vertical - corresponding to the clamping surface 20 of the locking plate 16 - and also has two apertures 35, through each one in the quick coupler 30 longitudinally displaceable driven latch bolt 36th can pass through.

Each locking bolt 36 has a spring arranged in a blind bore, which is supported with its free end on a spring plate, which is associated with the end face of an angle lever. The angle lever is part of a toggle mechanism, which acts in the feed direction and in the opposite direction on the locking bolt 36.

The in the presentation of the FIGS. 1 and 2 Parts shown form a toggle mechanism, which is driven by a shift shaft.

For the purpose of lateral centering - first primary alignment - when lowering the quick coupler 30 on the adapter plate 12 of the implement Zentrierorgane are provided, of which the quick coupler 30 associated Zentrierorgane are designed as cylindrical pins 52 in the flat end face 34 on both sides the sliding latch bolt 36 are located. The centering pins 52 cooperate with surfaces of the latch plate 16.

In addition, the locking plate 16 Zentrierorgane for centering the quick coupler 30 and the adapter plate 12 to each other in the longitudinal direction inclined surfaces in cooperation with the coupling axis 19 on - second primary alignment. These are lying in the Absenkweg the quick coupler 30 surfaces. When lowering the quick coupler 30 on the adapter plate 12 are due to these inclined surfaces of the quick coupler and thus the sliding latch bolt 36 aligned with respect to the cone openings 21 in cooperation with the coupling axis 19 and thus centered. The coupling process between the locking bolt 36 and the openings 21 can be done without interference.

Incidentally, with respect to the function of the quick-change device based on the same applicant EP 0 569 026 A1 Reference is made, the disclosure of which is intended to be fully encompassed by the disclosure of the present invention.

At the rear free end of the adapter plate 12, a lower coupling valve, a lower valve part 1, by means of a Anschraubblockes 13 is attached. The further attachment takes place on the latch plate 16. The lower valve part 1 forms an upper connection surface 2 which cooperates with the lower connection surface 5 of an upper coupling valve, a valve upper part 3. In the area of these two pads 2, 5 is the to be described later media delivery of the hydraulic clutch.

The adapter plate 12 is clamped without play on the clamping surface 20 of a fastened to the adapter plate 12 latch plate 16.

In FIG. 2 is shown that the lock between the adapter plate 12 and the quick coupler 30 is already made in the direction of arrow 6, because the respective locking bolt 36 is already partially retracted into the cone-shaped recess - cone opening 21 -. In this state, the connecting surfaces 2, 5 of the two mutually associated coupling valves 1, 3 to each other, so that no dirt, even in this provisional locking position, in the space between the coupling valves 1, 3 can penetrate. The adapter plate 30 is connected to a suspension 7, which has four spaced-apart receivers 8, 9, through which engage the bolts of an excavator handle.

This is a significant advantage over the aforementioned EP 0 483 232 B1 in which the flow between the mutually associated coupling valves has been provided long before the interlock between the mutually associated parts.

Furthermore, it is off FIG. 2 to recognize that the valve upper part 3 is fixed in a floating manner on a yoke 4 of the quick coupler, which in turn is fastened via fastening screws 71 on the top of the quick coupler 30.

The withdrawal force for the floating bearing is achieved by an elastomeric push-off element 40, which is arranged between the yoke 4 and the valve upper part 3 sealing.

FIG. 2 shows further that with increasing impressions of the cone end 50 in the cone opening 21 an axial lifting movement takes place in the direction of arrow of the valve upper part 3 in the direction of the fixed lower part 1. This lifting movement is sufficient to bring the short-stroke designed two valve body of the two coupling valves 1, 3 in the open position and thus to connect liquid-conducting together.

There are no further drive means required to produce the liquid flow through the two coupling valves 1, 3. Only the overtravel movement of the closing device by engagement of the cone ends 50 of the locking bolt in the cone opening 21 is sufficient to achieve the opening of both coupling valves 1, 3.

The FIG. 3 shows more details in an enlarged view of FIG. 2 ,

There it can be seen that the lower part of the valve 1 has a Anschraubblock 13 which is screwed with the interposition of wear plates 15 on the latch plate 16.

Should there be wear in the region of the coupling shafts 19 in connection with the abutment surfaces 32 come the Aufnahmeklauen 31, wear plates 15 are removed and the lower valve part 1 is thus advanced.

This ensures that the actual valve opening triggering annular valve extension 56 of the valve upper part 3 meets the associated bearing surface of the floating valve housing 18 and actuates this in the opening direction.

For this purpose, the lower part of the valve 1 consists of the fixed screwed in Anschraubblock 13 Anschraubgehäuse 72, whose interior is spring-loaded slidably mounted in the valve housing 18.

In the Anschraubgehäuse 72 a valve body 23 is screwed firmly and immovably, which applies sealingly with its conical surface on an associated conical surface in the region of the floating spring-loaded valve housing 18.

The valve upper part 3 is - as äusgeführt - floatingly mounted and the yoke 4 is initially disposed in the region of a recess, an upper sealing washer 10, below which a number of parallel and mutually spaced guide screws 38 are arranged. Each coupling valve 1, 3 is associated with a guide screw 38. Here, a number of parallel juxtaposed coupling valves 1, 3 are provided, as in FIG. 7 is shown as an example. There, a total of five coupling valves 1, 3 are provided to allow five media flows.

Depending on the need for the number of media flows therefore more or less clutch valves 1, 3 are arranged in pairs, each coupling valve 1, 3 is preferably associated with a guide screw 38 for the floating suspension.

The bolt-side end of the respective guide screw 38 is screwed into an associated threaded bore 33 in a floating valve block 29 of the valve upper part 3.

The bolt passes through a guide piece 39 which is fixedly connected to the bolt and which is supported by a lower shoulder on the upper side of the valve block 29.

The guide piece 39 forms a radially encircling collar, which forms a radial clearance 42 in the direction of the recess in the yoke 4.

In the region of an upper enlarged diameter, the head of the guide piece 39 rests on a bearing surface 41 in the region of the recess in the yoke 4.

In the neutral position shown, the elastomeric push-off element 40 is already biased and thus presses the valve block 29 with high biasing force down, centering it at the same time and thus exerts a parallel centering force on the entire surface of the valve block 29. Here, the clearance 43 is over the entire length of the valve unit according to FIG. 7 maintained.

The elastomeric push-off element 40 supports the top and bottom in circumferential, self-contained and mutually parallel receiving grooves 44, wherein the upper receiving groove in the yoke 4 and the lower receiving groove in the valve block 29 is arranged.

After the elastomeric pressure element according to the FIGS. 5 and 6 a self-contained interior with associated recesses 67, see FIGS. 5 and 6 , defined, this interior receiving space 48 is according to FIG. 3 with a fluid grease 49 or other suitable flowable material, such. B. graphite foam, filled.

Thus, the push-off element 40 provides a centering push-off force on the valve block 29 and additionally a seal, because the entire receiving space 48 is hermetically sealed from the outside world. The floating support of the valve block 29 is thus protected against the ingress of dirt and corrosive waters.

The push-off element 40 also serves as a seal against suction. When the loaded, compressed push-off element 40 is relaxed again, a negative pressure is generated in the receiving space 48, which must not suck in dirt and waste water. For this reason, the seal of the push-off element 40 in the area of the mutually opposite receiving grooves 44 also serves to suck in dirt and waste water.

For the sake of completeness, it should also be mentioned that, in addition, the mating surfaces 2, 5 assigned to one another are also cleaned. For this purpose, a water supply 45 is provided, which opens into a longitudinal bore over the entire length of the valve block 29 extending longitudinal bore 46.

From this longitudinal bore 46 open at regular intervals from each other parallel transverse bores 47, which are each associated with a pair of valves 1, 3.

In FIG. 3 the retraction of the locking bolt 36 is not shown. It is only the recess 37 drawn for the locking bolt 36, as well as the cone opening 21. The water flow from the transverse bore 47 opens into a spray nozzle 51 which is directed with a plurality of openings against the pads 2, 5 of the valves 1, 3. It engages in each case a drain opening 22 on the valve base 1 a.

In this way, before the production of the media feedthrough and well before the collapse of the two coupling valves 1, 3, a steered water flow against the pads 2, 5 is passed to keep all surfaces touched by the hydraulic oil.

The actual hydraulic coupling between the mutually associated coupling valves 1, 3 takes place in the transition between FIG. 3 and 4 ,

In FIG. 3 It is shown that with the aid of the guide screws 38, the elastomeric push-off element 40 is biased. This bias ensures stable storage of the valve block 29 on the yoke 4, even if it is exposed to strong vibration shocks.

FIG. 4 shows the flow through the coupling valves 1, 3, when the cone end 50 of the locking bolt 36 is fully retracted into the cone opening 21 in the form of an overstroke.

It should be noted that the actual locking has already taken place and that the overtravel by retracting the cone end 50 into the cone opening 21 to a displacement movement in the direction of arrow, see FIG. 2 , between the valve upper part 3 and the valve lower part 1 results, so that the two coupling valves 1, 3 are pressed against each other.

Contrary to the bias of the elastomeric Abdrückelementes 40 thus the circumferential and annular valve extension 56 is pressed in the valve block 29 down against the spring-loaded upwardly depressed valve housing 18 in the valve base 1.

At the same time so comes the face seal 25 to the system, on the surface of the valve housing 18 and seals first, before a media flow takes place at all.

During this time, the upper valve body 27 seals with the sealing seat 28 assigned to its conical surface in the valve upper part 3. The valve body 27 is in this case pressed under the force of a spring in the closing direction of the sealing seat 28.

As soon as the described overstroke movement of the locking device takes place in the direction of arrow 11, the yoke 4 is pressed down and the valve lug 56th of the valve block 29 presses against the valve housing 18 in the valve base 1 and opens this against the force of the spring 24. Thus, the media flow is established, as in FIG. 4 is shown.

The displacement movement is so strong that in this case the push-off element 40 in accordance with FIG. 4 deformed while the guide piece 39 lifts from its support surface 41.

It should be noted that the valve upper part 3 is associated with the Einschraubgehäuse 26, which is screwed into the valve block 29.

FIG. 4 shows as a further embodiment, the addition of a hydraulic damper 57 in order to dampen any movement shocks on the floating valve upper part 3 effectively.

It should also be prevented that the elastomeric Abdrückelement 40 under the action of rhythmic beating, as z. B. arise in rotary hammers, comes to a resonance behavior of the Abdrückelementes 40. For this purpose, the hydraulic damper 57 is used, which consists as a housing-side conclusion of an upper, sealed, inserted in a recess in the yoke 4 cover 58, which is held fixed in position by means of circlips 59.

The cover 58 defines on its underside a pressure chamber 61 which communicates with an oil bore 60 in connection. About this oil hole 60, pressure oil is introduced.

The pressure oil leads to the displacement of a two-part piston 62, 63.

The oil hole 60 is incidentally on an external bladder accumulator, which calms the shocks, which act on the floating bearing of the valve upper part 3.

The two-part piston consists of the outer piston 63 which is slidably guided in the cylinder chamber and in which a piston of smaller diameter 62 is slidably guided.

The inner piston 62 rests on an abutment collar 64 of the outer piston 63. This forms a distance to a fixed stop 73 on the cylinder chamber.

When the two coupling valves 1, 3 are separated from each other, the elastomeric push-off element 40 relaxes and the outer piston 63 moves onto the outer stop 73. Thus, at the same time the guide piece 39 against its stationary support surface 41 according to FIG. 3 hazards.

The hydraulic damper therefore biases the elastomeric push-off element 40 in its direction of force.

In another variant, not shown in the drawing, it is provided to form the elastomeric pressure element 40 itself as a hydraulic damper.

For this purpose, the receiving space 48 is instead of a fluid grease 49 or other sealing liquid filled with a liquid and / or gaseous pressure medium.

This pressure medium fills the receiving space 48 with an arbitrary overpressure of 0.1 to 5 bar and on the one hand changes the Abdrückverhalten, but on the other hand also acts as a damping for transmitted there load surges.

In this case, the push-off element 40 can also form a closed pressure chamber. This is achieved by forming the Abdrückelementes as a closed tube, which is arranged in the intermediate space between the yoke 4 and the valve block 29.

FIG. 4 shows that the lower valve part 1 is connected to an oil connection 55 and the valve upper part 3 with an oil connection 54 in connection.

The Anschraubblock 13 of the valve base 1 is fixed by means of fastening screws 53 to the latch plate 16.

FIGS. 5 and 6 show more details of the elastomeric push-off element 40. It is approximately oval or spectacle-shaped, as shown in FIG FIG. 6 is shown. It has relatively strongly dimensioned side walls 66 and end walls 65, which have a great resilience due to their wall thickness.

The height of the walls as a whole is a measure of the required, elastomeric restoring force of Abdrückelementes 40. The push-off element 40 forms in its interior a series of semi-open and merging into one another Recesses 67, because in each recess 67 in each case a valve upper part 3 engages. It is therefore according to FIG. 7 a series of valve upper parts 3 in the push-off element 40 stored together.

Instead of the merging recesses 67, it can in another embodiment FIG. 6 Also be provided that the recesses are separated by elastomeric partitions 70 from each other. Again, thus, the elastomeric resilience is on each, there engaging in the respective recess 67 valve upper part 3, controlled.

Should only a single coupling valve be required for a single media feedthrough, the push-off element is designed only as a cup-shaped single part.

It can be used for this purpose a section of a rubber hose.

For the controlled weakening of the side walls in the region of the protruding arcuate edges, which define the recesses 67, recesses 68, 69 of different diameters are arranged in these side walls.

Thus, the elastomeric Abdrückelement forms relatively stiff side walls 66, which are connected to one another via arcuate end walls 65 material integrally.

Thus, a self-rigid and tilt-free mounted Abdrückelement is described, which due to its stable connection between the side walls 66 and the end walls 65 is protected against tilting and tilting. It is thus always guaranteed a parallel guidance of the respective valve upper part 3 with respect to its floating storage.

FIG. 7 shows the top view of the entire arrangement after the FIGS. 1 to 3 , where it can be seen that a number of parallel juxtaposed covers 58 are provided for sealing in the yoke 4. Under these covers the respective hydraulic damper 57 is arranged and in turn in each case a valve upper part 3, which is floatingly mounted.

Furthermore, the central water supply 45 can be seen, which in conjunction with the Figures 3 and 4 already described.

LIST OF REFERENCE NUMBERS

1

Valve lower part, lower coupling valve

2

Connection surface (below)

3

Valve upper part, upper coupling valve

4

yoke

5

Connection area (top)

6

arrow

7

suspension

8th

admission

9

admission

10

sealing washer

11

arrow

12

Adapter plate (tool side)

13

Anschraubblock

14

baseplate

15

wear plate

16

locking plate

17

mounting tab

18

valve housing

19

coupling axis

20

clamping surface

21

Conical opening

22

drain hole

23

valve body

24

feather

25

Face seal

26

screw-in

27

valve body

28

sealing seat

29

manifold

30

Quick coupler (excavator handle)

31

claw

32

Abutment surface

33

threaded hole

34

front

36

locking bolt

37

Recess for 36

38

lead screw

39

guide piece

40

Push-off element elastomeric

41

bearing surface

42

game

43

distance game

44

receiving groove

45

water supply

46

longitudinal bore

47

cross hole

48

accommodation space

49

fluid grease

50

cone end

51

nozzle

52

straight pin

53

fixing screw

54

Oil connection above

55

Oil connection below

56

valve approach

57

hydraulic damper

58

cover

59

Seeger ring

60

oil well

61

pressure chamber

62

Piston (inside)

63

Piston (outside)

64

contact collar

65

bulkhead

66

Side wall

67

recess

68

recess

69

recess

70

partition

71

fixing screw

72

screw-on housing

73

attack

Claims (14)

1. A quick change device (10) comprising a quick change element (30) mounted on a machine, and an adapter plate (12) mounted on a tool and which can be locked with said element (30) via a common coupling axis (19), means (20, 32) for aligning (primary alignment) the interacting parts of the construction machine and the tool with each other, a hydraulic coupling for media required in the construction machine, which coupling comprises coupling valves (1, 3) provided on said quick-change element (30) and on said adapter plate (12), at least one of which valves is mounted in a floating manner (secondary alignment), characterized in that said floating support (secondary alignment) of the one coupling valve (1, 3), for example the upper coupling valve (3), is in the form of an elastomeric pressing element (40) which presses up against a stationary portion of said quick-change device and exerts a centric preload force on said coupling valve (3) via at least two parallel surfaces (66) thereof.
2. The quick-change device of claim 1, characterized in that an excess travel movement of the locking means (16, 21, 36, 50) will overcome the counter-pressure exerted by the elastomeric pressing element (40), thus causing the two coupling valves (1, 3) to be pressed onto each other so as to allow passage of a fluid flow therethrough.
3. The quick-change device of claims 1 and 2, characterized in that the one pressing element (40) which performs sealing and guiding/compensating functions is made of an elastomeric rubber.
4. The quick-change device of one of claims 1 to 3, characterized in that said pressing element (40) has circumferential walls forming a self-contained receiving space (48) whose upper front faces abut on the top of the yoke (4) of the quick-change element (30) and whose lower front faces bear on the top of the coupling valve (3).
5. The quick-change device of claim 4, characterized in that said receiving space (48) is filled with flowable grease (49) or graphite foam.
6. The quick-change device one of the preceding claims, characterized in that said pressing element (30), in a rest position thereof, is preloaded between the top coupling valve (3) and the bottom coupling valve (1).
7. The quick-change device of one of claims 1 to 6, characterized in that the walls (65, 66, 70) of said pressing element (40) exhibit weakening recesses (68, 69) in order to determine the buckling or deformation behaviour and/or the hardness of the walls.
8. The quick-change device of one of claims 1 to 7, characterized in that assigned to said pressing element (30) is a hydraulic dampening means (57) which acts on the contact and connection surface (2, 5) between the top and bottom coupling valves (1, 3) so as to dampen load surges.
9. The quick-change device of claims 1 to 8, characterized in that the top and bottom parts of said elastomeric pressing element (40) are mounted in circumferential self-contained receiving grooves (44) which extend in parallel to each other, with the upper receiving groove being provided in a yoke (4) of said quick-change element (30) and the lower receiving groove being provided in a valve block (29) of said coupling valve (3).
10. The quick-change device of one of claims 1 to 9, characterized in that counteracting the preload exerted by the elastomeric pressing element (40), the circumferential and annular valve seat (56) in the valve block (29) presses down on the valve housing (18) in the bottom coupling valve (11) which housing is being pressed upward by the action of the spring.
11. The quick-change device of one of the preceding claims, characterized in that said pressing element (40) is in the form of a hydraulic damper.
12. The quick-change device of claim 11, characterized in that said receiving space (48) defined by said pressing element (40) is filled with a pressure medium.
13. The quick-change device of claims 11 or 12, characterized in that said pressing element (40) is in the form of a self-contained hose.
14. The quick-change device of claim 1, characterized in that the contact surfaces (2, 5) of the coupling valves (1, 3) provided on the quick-change element (30) and on the adapter plate (12) and assigned to each other are to be cleaned by means of a high-pressure fluid line (45, 47).

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