EP1239087B2 - Attache rapide - Google Patents

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Publication number
EP1239087B2
EP1239087B2 EP02005070.4A EP02005070A EP1239087B2 EP 1239087 B2 EP1239087 B2 EP 1239087B2 EP 02005070 A EP02005070 A EP 02005070A EP 1239087 B2 EP1239087 B2 EP 1239087B2
Authority
EP
European Patent Office
Prior art keywords
quick coupling
power
coupling
quick
accordance
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02005070.4A
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German (de)
English (en)
Other versions
EP1239087B1 (fr
EP1239087A1 (fr
Inventor
Rolf Mieger
Thomas Zitterbart
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Liebherr Hydraulikbagger GmbH
Original Assignee
Liebherr Hydraulikbagger GmbH
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Priority claimed from DE10159417A external-priority patent/DE10159417C2/de
Application filed by Liebherr Hydraulikbagger GmbH filed Critical Liebherr Hydraulikbagger GmbH
Publication of EP1239087A1 publication Critical patent/EP1239087A1/fr
Publication of EP1239087B1 publication Critical patent/EP1239087B1/fr
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Anticipated expiration legal-status Critical
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3663—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat hydraulically-operated
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3654—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat with energy coupler, e.g. coupler for hydraulic or electric lines, to provide energy to drive(s) mounted on the tool
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2271—Actuators and supports therefor and protection therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2275—Hoses and supports therefor and protection therefor

Definitions

  • the present invention relates to a quick coupling for coupling a tool to the boom of a hydraulic excavator and the like, according to the preamble of claim 1.
  • Swivel-type quick-release couplings are widely used in hydraulic excavators because they allow a simple and quick change of various tools such as hydraulic gripper, grave bucket, grapple and the like.
  • This can advantageously be a transverse bolt, which is hooked into a hook-shaped eyelet on the opposite coupling part.
  • the cantilever-side coupling part can be pivoted relative to the tool about the already engaged locking axis, to thereby find the locking position in which the second locking axis can be locked.
  • the latter is usually formed by a pair of locking bolts that can move apart and into corresponding locking holes on the opposite quick coupling part.
  • a swivel type quick coupling in which an automatic hydraulic coupling is provided which automatically couples a boom-side power circuit with a tool-side power circuit when pivoting the two quick coupling parts.
  • There are two power coupling parts are provided, one of which is attached to the jib-side quick coupling part and the other on the tool-side quick coupling part, in such a way that the two power coupling parts are driven together and brought into engagement when pivoting the two quick coupling parts to the first already locked locking axis.
  • One of the two power coupling parts is movably mounted on the corresponding quick coupling part to compensate for the circular motion of the quick coupling parts when pivoting together.
  • the DE-U1-29810118 discloses a quick coupling for coupling a tool to the boom of a hydraulic excavator with a boom side quick coupling part and a tool side quick coupling part. Furthermore, the quick coupling comprises a power circuit coupling for automatically coupling a tool-side power terminal to a jib-side power terminal comprising a jib-side power coupling part and a tool-side power coupling part.
  • the document discloses a two-stage coupling process, in which in a first stage, the two quick coupling parts are mechanically locked together, then to be able to move together the two power coupling parts in a second step accurately and in alignment.
  • the present invention is therefore an object of the invention to provide an improved quick coupling of the type mentioned above, which avoids the disadvantages of the prior art and the latter further develops in an advantageous manner.
  • an improved arrangement of the power coupling is to be created, which allows a leak-free and trouble-free coupling of the boom and tool side power circuits.
  • this object is achieved by a quick coupling according to claim 1, wherein the preamble of the SE 468 320 B is known.
  • Preferred embodiments of the invention are the subject of the dependent claims.
  • the energy coupling parts are driven exactly linear to each other. It is provided a linear guide for the power coupling parts, which forces the power coupling parts against the circular path pivotal movement to a relative movement to each other along a straight line. In order to enable the compensation of the pivoting movement, at least one of the two power coupling parts is mounted on the corresponding quick coupling part movable relative to this. In a further development of the prior art, however, it is provided that the movably mounted energy coupling part compensates for the pivoting movement when the quick coupling parts move together and moves exactly so that an exactly linear movement takes place between the two energy coupling parts.
  • the linear guide comprises a pair of cantilever-side guide elements and a pair of tool-side guide elements which engage with each other upon closing of the power circuit coupling before the two power circuit coupling parts, in particular their terminal conectors, engage each other.
  • the linear guide thus arrives at the pivotal movement of the two quick coupling parts to the already locked first locking axis as the power coupling parts in and out of engagement.
  • the engagement of the guide elements of the linear guide takes place before the engagement of the connection conectors the power coupling parts, so that the linear guide of the power coupling parts is ensured from the beginning. There can be no jamming and a precise linear movement over the entire coupling path of the power coupling parts is ensured.
  • the guide elements of the linear guide are of the actual power coupling elements ie the connector pieces separately formed components. However, they are preferably fixedly arranged on the power coupling parts or they may be integrally formed thereon.
  • the linear guide can basically be designed differently.
  • a slotted guide for the movably mounted power coupling part or for the movably mounted power coupling parts may be provided. It may also be provided a cam-like control of the movement of the or the movable power coupling parts.
  • As guide elements a pair of guide pins are provided on one of the power coupling parts and a pair of guide holes are provided on the other power coupling part. When the energy coupling parts travel toward one another, the guide pins slide precisely into the complementary guide bores, which ensures linear movement.
  • the guide pins extend with their longitudinal axis parallel to the direction in which the connector connectors can be pushed together.
  • the power coupling parts may have known female and male connector pieces which can be slid into one another.
  • the one or more guide pins of the linear guide preferably have a special shape that prevents tilting when inserted into the complementary guide bore.
  • each of the guide pins may have a rounded head, a cylindrical guide portion and a constriction provided between the head and the cylindrical guide portion. In the area of the constriction, the guide pin has a reduced diameter relative to the head or to the guide section.
  • the rounded head can also be inserted with slight angular misalignment in the guide bore. An alignment or compensation of the angular offset occurs when the axially spaced from the bolt head cylindrical guide surface also comes into engagement with the guide bore.
  • At least one of the two power coupling parts is movably mounted relative to the associated quick coupling part.
  • a simple arrangement is achieved, which nevertheless allows the necessary compensation of the pivoting movement.
  • the mobility of the storage of the corresponding power coupling part is preferably multi-axially formed.
  • the bearing of the energy coupling part can at least allow a tilting movement about an axis parallel to the first locking axis and a movement in a direction perpendicular to the first locking axis.
  • it also permits a sliding movement parallel to the first locking axis and / or a tilting movement about a tilting axis perpendicular to the first locking axis.
  • the arrangement of the power coupling parts can be made cheaper due to coarser tolerances.
  • one of the two power coupling parts is mounted on a spring device, in particular on a pair of compression springs.
  • the compression springs can be rigidly attached to the corresponding quick coupling part and jointly carry the corresponding power coupling part.
  • a limitation of the spring travel in the direction of the coupling movement may be provided.
  • a pressure ram can be provided, on which the movable energy coupling part is tiltably and / or slidably seated.
  • the plunger has a rounded head which can engage approximately centrally between the spring elements of the spring device on the power coupling part.
  • the plunger pushes the two power coupling parts safely and firmly in the final stage of the coupling movement.
  • the pressure ram can be variable in length.
  • the plunger may be resilient to avoid damage and to allow compensation of tolerances, wherein the spring constant of the plunger may be much harder than the resilient mounting of the power coupling part.
  • the push rod may be formed in a further development of the invention as a hydraulic ram, d. H. he is by pressure medium in its extended position extendable or prestressed. As a result, greater pressure can be exerted on the movably mounted energy coupling part, preferably towards the end of the coupling movement or after complete collapse of the energy coupling parts, so that the energy coupling parts are reliably held in their contracted position.
  • the hydraulic pressure with which the pressure ram holds the two energy coupling parts adapted to the respective operating conditions.
  • the force holding together the power coupling parts is always chosen so large that the parts are held together completely free of play at all times.
  • it is not constantly driven with a maximum force that would be sufficient under all operating conditions to hold the parts together.
  • the latter is disadvantageous in a solution by means of a spring. If the plunger alone with spring force hold the power coupling parts, the spring must be sized so large that it holds the power coupling parts together under all conditions, so over long distances much too large forces would act.
  • the pressure force can be varied in a hydraulic ram.
  • the pressure plunger can be supplied with pressure medium from one of the pressure medium circuits to be coupled, ie the pressure tappet is acted upon by the pressure fluid, which is transmitted to the tool via the energy coupling coupled.
  • the area ratio between the effective effective cylinder surface of the plunger, which is acted upon by the pressure medium, to the effective connector surface, ie the effective through the coupling passing flow cross-section, which is acted upon in the region of the connectors with pressure medium perpendicular to the coupling direction greater chosen as 1.
  • An advantageous embodiment may be that the area ratio is about 5/4.
  • the force applied by the push rod cohesion force is always greater than the maximum force that tries to squeeze the power clutch by this area ratio. If the operating pressure in the pressure medium lines to be coupled increases, the force acting on the pressure ram and thus the holding force increase as well.
  • several pressure medium connectors are provided.
  • a plurality of pressure rams may be provided. In this case, the ratio of the sum of the effective cylinder effective areas and the sum of the connector areas is selected in the manner described above.
  • the cylinder of the pressure ram or the cylinders of the pressure ram can be brought into flow connection with a plurality of, in particular all, pressure medium lines of the pressure medium circuit to be coupled.
  • a valve arrangement is connected between the pressure medium lines and the cylinder or cylinders, which ensures that always that of the pressure medium lines, which has the highest pressure, is in communication with the pressure plunger. This ensures that the pressure ram is always acted upon by the sufficiently large pressure.
  • the pressure medium lines can be interconnected in pairs via shuttle valves, so that, so to speak, always passes through the greater pressure.
  • the plunger can be fed from different sections of the pressure medium circuit ago. It is possible to connect the boom-side pressure medium circuit with the plunger.
  • the fluid connectors are usually provided with leakage protection, so that the plunger can already be operated when the connectors are not yet connected, wherein by the extension of the Tappet the connectors are connected.
  • the cylinder or cylinders are fed by the tool-side pressure medium circuit forth, ie they are only then pressurized when the power circuit clutch and in particular their fluid connectors are moved together and have coupled the connectors.
  • the movably mounted energy coupling part and thus the pressure ram can in principle be arranged on the boom side. In a further development of the invention, however, they are provided on the tool side.
  • the movably mounted power coupling half compensates for the pivotal movement of the quick coupler halves insofar as a linear movement is made from the circular path movement. In addition, occur due to game and the like relative movements. In order to allow this offset, the push rod and the power coupling half acted upon by it are movable relative to each other.
  • the pressure ram is frontally provided with a pressure cap which has a flat end face, so that it can sit on the substantially flat energy coupling part full and flat.
  • pressure cap and plunger have mutually complementary curved surfaces, with which they sit on one another, so that the Can push cap on the plunger itself and yet a flat connection is provided.
  • a positive locking of the two power coupling parts may be provided alternatively or in addition to the hydraulic pressure ram.
  • a positive locking of the two power coupling parts may be provided alternatively or in addition to the hydraulic pressure ram.
  • a positive locking of the two power coupling parts may be provided alternatively or in addition to the hydraulic pressure ram.
  • a movable transverse pin can be provided, which is mounted in the energy coupling part, which has the said guide bore.
  • the locking cross bolt can be hydraulically acted upon.
  • the transverse pin can cooperate with the constriction of the guide pin, d. H. when the guide pin is fully retracted into the guide bore, the locking cross pin is retracted tangentially to the guide bore so that it projects into the guide bore, in the region in which the constriction of the guide pin is located.
  • a separate bolt for the positive locking of the two power coupling parts may be provided in the coupled position.
  • a latch flap is provided.
  • a preferably hydraulically operable actuating cylinder can be provided.
  • the latch may be spring loaded so that it is biased to its latching position. As a result, the actuating means need only be actuated for unlocking.
  • a pre-centering for the two power coupling parts when pivoting the quick coupling parts is provided.
  • the pre-centering aligns the two energy coupling parts before engaging the linear guide to each other so far that the corresponding guide elements of the linear guide can intermesh as intended.
  • This has particular advantages when in careless operation when pivoting the two quick coupling parts, the first locking axis not exactly adjusted or completely retracted. In this case, misalignment of the power coupling parts may occur, which could cause damage to the power circuit clutch when moving together.
  • the pre-centering also corrects for excessive misalignment of the power coupling parts relative to the corresponding quick coupling part, the z. B. due to the movable storage of at least one of the power coupling parts can occur.
  • the pre-centering can be designed differently. Preferably, it has a pair on pivoting together of the quick coupling parts successive sliding centering surfaces, one of which is provided on the movably mounted power coupling part. The other of the cooperating centering surfaces may be provided on the other power coupling part. In a further development of the invention, it can be arranged on the opposite quick coupling part. In particular, they are arranged such that they engage in front of the linear guide.
  • a pivoting guide in addition to the pre-centering, can be provided, which ensures that the two quick-coupling parts can be pivoted together only in their desired alignment with one another, ie when the first locking axis is properly aligned.
  • the pivot guide prevents damage to the hydraulic coupling by moving the quick coupling parts with offset. In the latter case, the connecting pieces or the guide pins of the power coupling parts would also drive each other with offset and cause damage.
  • the pivoting guide preferably has guide surfaces provided on the solid pivoting coupling parts themselves, which, when the quick coupling parts are properly aligned when sliding together, slide past one another about the first locking axis or also slide on one another.
  • the guide surfaces prevent in particular when the power coupling parts already in engagement with each other have come, a displacement of the two quick coupling halves to each other before the second locking axis is locked. Such an offset would inevitably result in damage to the power coupling.
  • the guide surfaces may be designed such that, as soon as they are pushed over one another, they interact with the first, hook-shaped locking axis, so that an offset or a slippage of the quick coupling halves relative to each other is prevented.
  • the power circuit clutch is a later mountable to the two quick coupling parts mounting unit. It is not an integral part of the quick coupler.
  • the energy circuit coupling is preferably designed such that even existing quick couplers can be retrofitted.
  • the power circuit coupling can be arranged outside the locking axes of the two quick coupling parts in the invention.
  • the power circuit clutch is not difficult to access in this case between the two locking axes, but z. B. be easily reached for cleaning. Moreover, it is not in the vulnerable for the collection of dirt and dirt gap between the two locking axes.
  • the power circuit clutch is disposed within abutting surfaces of the tool-side quick coupling part and / or the boom-side quick coupling part, in particular such that in the separated state of the two coupling parts, the energy circuit coupling parts do not hit the ground when the corresponding quick coupling part is deposited on the ground.
  • the two quick coupling parts each have two spaced, substantially perpendicular to the locking axes support pieces and the power coupling parts are each arranged between two associated support pieces transverse to these. They lie in the protected area between the vertical support pieces of the quick coupling parts. The support pieces of the quick coupling parts slide into each other or one above the other in the region of the locking axes.
  • the boom-side quick-coupling part can be free of a base plate extending parallel to the locking axes, on which the energy-coupling part would be arranged. This avoids that when placing the boom-side coupling part with its base plate on the ground, the energy coupling part arranged thereon is pressed into the ground.
  • the two power coupling parts are each formed substantially plate-shaped.
  • the already mentioned male or female connector pieces, which form the power terminals are arranged on the plate-shaped carrier of the power coupling parts. Spaced apart from this, the guide pins or guide bores can be rigidly fastened or incorporated.
  • the quick coupling 1 shown in the figures has a boom-side quick coupling part 2, which is pivotally mounted on the stem 3 of a boom of a hydraulic excavator and can be pivoted about a pivot not shown in a conventional manner to the longitudinal axis of the stem 3 vertical pivot axis 4.
  • the quick coupling 1 further has a tool-side quick coupling part 5, which is connected to a hydraulic excavator tool. This can be z.
  • the two parts 2 and 5 of the quick coupling 1 are connected to each other via two parallel, spaced apart locking axes 7 and 8 locked together.
  • the locking shafts 7 and 8 extend as FIG. 1 shows, parallel to the pivot axis 4, by which the quick coupling 1 can be pivoted relative to the stem 3.
  • the first of the two locking axes 7 is formed on the one hand by a provided on the tool-side quick coupling part 5 transverse pin 9 and a pair on the jib-side quick coupling part 2 provided locking hook 10.
  • the locking hooks 10 can be hooked on the cross bolt 9 so that it can be gripped by the locking hooks 10 and the tool-side quick coupling part 5 can be raised.
  • the locking hooks 10 are open to one side, hook-shaped recesses which surround the cross bolt 9 endeavourschalenfömrig.
  • the HakenausEnglishept are open to the side of the quick coupling part 2, which is remote from the second locking axis 8.
  • the second locking axis 8 is formed on the one hand by a divisible locking bolt pair 11 and an associated pair of locking holes 12.
  • the locking pin pair 11 is arranged on the boom-side quick coupling part 2 and can by a known drive mechanism, preferably hydraulically, retracted and extended.
  • the locking holes 12 are formed in the tool-side quick coupling part 5.
  • FIG. 1 can recognize both the cantilever-side quick coupling part 2 and the tool-side quick coupling part 5 spaced from each other, substantially vertical support pieces which are spaced differently from each other, so that the support plates of the boom-side quick coupling part 2 can retract between the support plates of the tool-side quick coupling part 5.
  • the boom-side quick coupling part 2 is first retracted with the boom-side quick coupling part 2 in the tool-side quick coupling part 5 and gripped with the hook-shaped locking recesses 10 of the transverse pin of the opposite quick coupling part (see. FIG. 3 ).
  • the boom-side quick coupling part 2 is then pivoted about the pivot axis 4, so that as a result the two quick coupling parts 2 and 5 are pivoted together about the first locking axis 7.
  • the two quick coupling parts 2 and 5 are pivoted together so far that the locking pin pair 11 and the associated locking holes 12 are aligned. Then, the locking bolts 11 are preferably moved apart by hydraulic loading, so that they retract into the locking holes 12. By the two locking axes 7 and 8, the two quick coupling parts 2 and 5 are firmly locked together.
  • the two quick coupling parts 2 and 5 may be provided with a pivot guide 44 (see. FIG. 11 ).
  • the two solid quick coupling parts 2 and 5 each have a guide surface 46 and 47 (see. FIG. 11 ), which can only be pushed over each other or past each other when the first locking shaft 7 is properly aligned.
  • the guide surfaces 46 and 47 may be formed so that they act centering, ie the two quick coupling parts 2 and 5 in the properly aligned position when they are pivoted together.
  • the quick coupling 1 is associated with a hydraulic clutch 13, which connects a boom-side hydraulic circuit with a tool-side hydraulic circuit.
  • a hydraulic clutch 13 which connects a boom-side hydraulic circuit with a tool-side hydraulic circuit.
  • the rotary mechanism 1 according to FIG. 1 hydraulically operated. It can be provided and coupled further drive elements and accordingly more hydraulic circuits.
  • the hydraulic clutch 13 comprises two power coupling parts 14 and 15, which are mounted on the one hand on the boom-side quick coupling part 2 and on the other hand on the tool-side quick coupling part 5. They are arranged on the first locking axis 7 and 8 opposite sides of the quick coupling parts 2 and 5, in each case at the same distance from the first locking axis 7, so that they drive on each other when pivoting the two quick coupling parts 2 and 5. In principle, they could also be arranged between the two locking axes 7 and 8. Preferably, however, they are outside the limited by the two locking axes 7 and 8 area, since the latter tends to experience dirt and is difficult to access. The arrangement of the power coupling parts 14 and 15 outside the locking shafts 7 and 8, these are less prone and better to maintain.
  • the power coupling parts 14 and 15 are respectively between the vertical support pieces 16 of the boom-side quick coupling part 2 and the vertical support pieces 17 of the tool-side quick coupling part 5 is arranged. They are protected by this. In particular, they are not on the quick coupling parts 2 and 5 over such that the power coupling parts 14 and 15 would be pressed into the ground when the corresponding quick coupling parts 2 are sold at the bottom.
  • Both power coupling parts 14 and 15 combine a plurality of power line clutches. They are each designed as a connector block, in which a plurality of connector pieces 18 are combined. As FIG. 4 shows, each of the two power coupling parts 14 and 15 has a plate-shaped support piece 19 and 20, respectively, which extends transversely to the respective quick coupling part 2 and 5 respectively. Perpendicular to the support pieces 19 and 20 sit the connector pieces 18, which can be pushed together and cause the hydraulic fluid connection.
  • the connector pieces 18 may be female and male type connector pieces known in the art.
  • the energy coupling part 14 arranged on the cantilever-side quick coupling part 2 is fixedly mounted, ie it is rigid relative to the quick coupling part 2.
  • the power coupling part 15 attached to the tool-side quick coupling part 5 is movably mounted on this.
  • the entire power coupling part 15 is seated on a spring assembly 21, which consists of four arranged in the rectangle compression springs in the embodiment shown.
  • the compression springs 22 are on the one hand attached to angle plates which are arranged on the vertical support pieces 17 of the tool-side quick coupling part 5 (see. FIG. 7 ).
  • the cylindrical spring elements 22 are connected to the support piece 20 of the power coupling part 15, preferably screwed.
  • the springs 22 have a sufficient height and elasticity, so that the power coupling part 15 can be multiaxially displaced or tilted.
  • the spring arrangement 21 forms a multi-axially movable mounting for the energy coupling part 15, so that this offset to the opposite power coupling part 14, in particular due to the pivotal movement of the quick coupling parts 2 and 5 can compensate.
  • the linear guide 23 consists in the illustrated embodiment of a pair of guide pins 24 and associated guide holes 25, in which the said guide pin 24 retract when moving the two power coupling parts 14 and 15. They force the springs 22 to a deflection in order to compensate for the pivoting movement component. In addition, offset due to tolerances during assembly are also compensated.
  • the guide pins 24 are rigidly connected to the support piece 19 of the power coupling part 15 and projecting vertically therefrom towards the opposite power coupling part 14.
  • Each guide pin 24 is formed substantially cylindrical.
  • each guide pin 24 has a rounded head 26, a cylindrical guide portion 27 and an intermediate constriction 28 which separates the bolt head 26 from the cylindrical guide portion 27. Due to the special design of the guide pin 24 tilting during insertion into the guide holes 25 is prevented.
  • the lateral surface of the guide pin 24 may be spherically rounded in the region of the head 26. The spherical rounding passes into the constriction 28.
  • the cylindrical Shank portion or guide portion 27 has a conical slope, which may be in the range of 5 to 15 degrees, preferably about 10 degrees.
  • the special shape of the guide pin, in particular the spherical shape of the head allows a tilt-free insertion of the guide pin in the opposite guide holes.
  • the guide bores 25 may have in the region of their opening cross section a cross-sectional widening in the form of a phase, a rounding or the like in order to facilitate the threading (see. FIG. 4 ).
  • the guide holes 25 and guide bushes 28 are formed of suitable material, which are inserted into the boom-side power coupling part 14.
  • a pre-centering 29 for pre-centering the two power coupling parts 14 and 15 relative to each other may be provided.
  • FIG. 10 shows an example of such pre-centering 29.
  • the movably mounted energy coupling part 15 may have a centering surface 30.
  • a cam-shaped centering surface 31 may be provided on the opposite quick coupling part, on which the centering surface 30 of the power coupling part 15 slides off when the two quick coupling parts 2 and 5 are moved together.
  • the pre-centering causes the two power coupling parts 14 and 15 to be in an at least roughly aligned position with each other as they are driven toward each other.
  • an actuator is preferably provided, which is active on the last stretch of Haitischwenktterrorism the quick coupling parts 2 and 5 and the two power coupling parts 14 and 15 presses each other completely.
  • a pressure ram 32 may be provided on which the spring-mounted power coupling part 15 is seated (see. FIG. 6 ). Since the springs must be sufficiently elastic to compensate for the pivotal movement or offset, they could yield and be compressed, so that it is not complete Clutch of the hydraulic clutch comes.
  • the plunger 32 acts as a limiter for the spring travel of the spring bearing. As FIG.
  • the head of the plunger 32 is preferably slightly rounded, so that even with slight inclination of the movably mounted power coupling part 15 as centric as possible sitting on the plunger 32 is achieved.
  • the plunger 32 may also be resilient.
  • the plunger 32 may be a longitudinally displaceable bolt, which is biased by a compression spring 43 which may be in the form of a plate spring package.
  • the spring rate of the plunger 32 is suitably much larger than that of the spring assembly 21 for the movable mounting of the one power coupling part 15.
  • Wie FIG. 6 shows, the power coupling part 15 sits on the plunger 32 towards the end of the collapsing movement.
  • the plunger 32 may be a hydraulically actuated plunger according to an alternative embodiment of the invention.
  • the arrangement can be reversed, ie the movably mounted energy coupling part is preferably arranged on the boom-side quick coupling part 2, so that the pressure ram can be supplied by the boom-side hydraulic system.
  • the hydraulically extendable plunger an increased force can be applied in particular towards the end of the coupling movement.
  • FIGS. 15 to 18 show an advantageous embodiment of the hydraulic coupling with hydraulically actuated plunger.
  • the energy coupling parts are basically movable or resiliently mounted in the manner described above, so that reference is made to the preceding description.
  • the plunger is retracted so far in its initial position that between the plate-shaped support piece 19 and the end face of the plunger 32 is air.
  • the energy coupling thus initially threads with the aid of the springs 22 or the force applied thereto.
  • the linear guide ensures that the two energy coupling parts perpendicular to each other. This creates an elastic deformation of the stored springs, as this FIG. 16 shows.
  • the hydraulic pressure ram 32 is provided which presses centrally against the support piece 19 so that it is pressed against the boom-side support piece 20. It can also be provided 32 two or more hydraulic pressure pieces.
  • the plunger 32 comprises a piston-cylinder unit, which consists of a plunger 60 and a plunger 60 displaceably leading cylinder liner 61.
  • the cylinder liner 61 is screwed fluid-tight into the tool-fixed support piece 62 of the power coupling.
  • the plunger 60 is biased with a spring assembly 63, in its extended position in which he drives by means of a shoulder 64 against a cylinder sleeve side paragraph.
  • a spring pack 63 disc springs can be provided of suitable strength.
  • the disc springs are sized so that they can yield when moving the power coupling parts.
  • the play-free, firm holding under all operating conditions is achieved by the hydraulic loading of the plunger 60.
  • via a pressure fluid bore 65 of the plunger 60 and a pressure chamber 66 is connected to the hydraulic lines of the tool.
  • FIG. 18 shows, in the illustrated embodiment, four pressure medium lines 67, 68, 69, 70 are guided by means of the connectors 71 of the power coupling from the boom side to the tool side of the quick coupler.
  • the tool-side pressure medium lines 67 to 70 are all connected to the pressure chamber 66 of the pressure plunger 32.
  • the pressure medium lines 67 to 70 are combined in pairs by means of shuttle valves 72, 73 and 74.
  • the change-over valves in the form of double check valves ensure that the pressure medium line, which has the highest pressure, always penetrates from the pressure medium lines 67 to 70. In the pressure chamber 66 of the plunger 32 so is always the pressure, which is the largest of the pressures prevailing in the pressure medium lines 67 to 70 pressures.
  • the effective area of the plunger, which causes its force is greater than the sum of the cross-sectional areas of the connectors 71. In conjunction with the circuit, which always gives the greatest pressure to the plunger, this ensures that the holding force is always greater than the forces caused by the pressures in the connectors, which try to force the energy coupling apart.
  • a pressure cap 75 which has a substantially flat end face. This ensures that it always rests flat against the support piece plate 19 and excessive surface pressure, as would occur in a punctiform contact, are avoided.
  • the connecting surfaces 76 with which the end face of the plunger 60 and the pressure cap 75 touch each other, are rotationally symmetric rounded surfaces, so that a tilting movement between the pressure cap and the plunger 60 is possible. Nevertheless, the contact between the plunger 60 and the pressure cap 75 is also flat.
  • a positive locking of the power coupling parts 14 and 15 may be provided.
  • a displaceably mounted cross pin 48 may be provided in the power coupling part 14.
  • the cross pin 48 is arranged so that it can retract tangentially into the guide bore 25, in the region in which the constriction 28 of the guide pin 24 comes to rest when the guide pin is fully inserted.
  • the cross pin 48 may have sections of different diameters. If the bolt is inserted with a large diameter portion in the guide bore 25, the guide pin 24 is locked. If the transverse pin 48 with a section of tapered diameter in the guide bore Inserted 25, the guide pin 24 can be inserted and ejected.
  • the transverse pin 48 is preferably hydraulically actuated. If necessary, it can be biased by a spring in its locking position, so that a hydraulic actuation must be made only for unlocking.
  • a latch 49 may be provided which locks the power coupling parts 14 and 15 with each other in a form-fitting manner (cf. FIG. 14 ).
  • the latch 49 may be formed as a rocker arm, which is mounted pivotably about a pivot axis 51 on the power coupling part 14. At one end it has a cranked hook, with which it can engage behind a locking projection 52 on the opposite power coupling part 15.
  • the latch 49 is preferably biased by a spring 50 in its locking position.
  • a hydraulic cylinder 53 is articulated on the latch 49 in order to pivot it in its unlocking position (cf. FIG. 14 ).
  • the hydraulic cylinder 53 is arranged on the boom side in order to be permanently connected to the local hydraulic system.
  • FIG. 8 shows an alternative storage of the power coupling parts 14 and 15.
  • both power coupling parts are movably mounted.
  • the power coupling part 14 attached to the jib-side quick coupling part 2 is pivotally mounted on a pivoting lug 34 about a transverse axis 33.
  • the pivoting lug is in turn pivotally mounted on the quick coupling part 2 about a pivot axis 35 parallel to the transverse axis 33 and spaced therefrom.
  • a neutral position of the power coupling part 14 can be ensured by means of a spring device.
  • the second power coupling part 15, which is attached to the tool-side quick coupling part 5, is also movably mounted. In the illustrated embodiment, it is mounted longitudinally displaceable, in a plane which is parallel to the first locking axis 7 of the quick coupler 1 FIG. 8 the second power coupling part 15 is movable from left to right. It is held by the springs 35 in its neutral position.
  • FIG. 9 shows an alternative movable mounting of the tool side provided energy coupling part 15. It sits on a pivoting plate 36 which is pivotable about a transverse axis 37 to the first locking axis 7 and away from it.
  • the energy coupling part 15 itself is also pivotally mounted on the pivoting lug 36 about the tilting axis 38.
  • the tilting axis 38 extends parallel to the axis 37, as FIG. 9 shows.
  • springs 39 By means of springs 39, the power coupling part 15 is held in its neutral position on the pivoting lug 36.
  • FIG. 10 shows a further alternative storage of the power coupling part 14, which is attached to the boom-side quick coupling part 2. It sits tiltably on a transverse pin 40, which extends parallel to the first locking axis 7.
  • the power coupling part 14 is slidably mounted on the bolt 40. It has a slot 41 so that it is displaceable transversely to the bolt 40.
  • the power coupling part 14 is held in its neutral position.
  • the previously described pre-centering 29 is provided, which pre-centers the energy coupling part 14 when it is driven onto the opposite energy coupling part 15, when the two quick coupling parts 2 and 5 are pivoted together.
  • the upwardly projecting at the lower quick coupling part tines, on which the pre-centering cam surface 31 is provided, has a double function. At the same time, it forms the pivoting guide 44, which forces the two quick-action coupling parts in relation to one another in their properly aligned position.
  • the reference numerals 46 and 47 also designate the corresponding guide surfaces.
  • the locking of the hydraulic clutch is ensured simultaneously with the quick coupler lock.
  • the hydraulic clutch 13 in particular due to their arrangement and positioning shown, also retrofittable to existing quick coupler, since it is not integrated, but adapted.
  • the positioning of the hydraulic clutch 13 allows good accessibility for maintenance and repair.
  • by adapting the couplings to the quick coupler whose size is variable and adaptable to the conditions.
  • a number of hydraulic lines can be combined into a single coupling block.
  • a stop 80 may be provided. As FIG. 19 shows, the stopper 80 may be formed by two projections against which the spring-mounted support piece plate 19 moves when pulling apart.
  • the stops 80 are preferably arranged centrally, ie the line defined by them passes centrally through the guide pin 24 of the power coupling.

Claims (24)

  1. Raccord rapide pour l'accouplement d'un outil à la flèche (3) d'une pelle hydraulique et analogue, avec une partie de raccord rapide (2) côté flèche et une partie de raccord rapide (5) côté outil qui peuvent être verrouillées l'une avec l'autre par une paire d'axes de verrouillage espacés (7, 8) de telle sorte qu'après le verrouillage seulement d'un premier des deux axes de verrouillage (7), les deux parties de raccord rapide (2, 5) peuvent être pivotées autour dudit premier axe de verrouillage (7) l'un vers l'autre, et ensuite le deuxième axe de verrouillage (8) peut être verrouillé, ainsi qu'un raccord de circuit d'énergie (13), en particulier un raccord hydraulique, pour le raccordement automatique d'un raccord d'énergie côté outil à un raccord d'énergie côté flèche, où le raccord de circuit d'énergie possède une partie de raccord d'énergie côté flèche (14) et une partie de raccord d'énergie côté outil (15), qui sont disposées sur la partie de raccord rapide (2) côté flèche et respectivement sur la partie de raccord rapide (5) côté outil d'une manière espacée du premier axe de verrouillage (7) de telle manière que par le pivotement l'une vers l'autre des deux parties de raccord rapide (2, 5) autour du premier axe de verrouillage (7) elles se rejoignent sur une voie circulaire autour du premier axe de verrouillage et, de ce fait, s'accouplent automatiquement l'une avec l'autre, caractérisé en ce qu'au moins une des deux parties de raccord d'énergie (14, 15) est logée d'une manière basculable autour d'un axe parallèle au premier axe de verrouillage (7) et mobile perpendiculairement au premier axe de verrouillage (7), et qu'il est associé au raccord de circuit d'énergie (13) un guidage linéaire (23) séparé des raccords d'énergie, constitué d'une paire de boulons de guidage (24) et de perçages de guidage (25) associés, dans lesquels lesdits boulons de guidage (24) s'introduisent lors de la rencontre des deux parties de raccord d'énergie (14, 15), et qui, en coopération avec le logement mobile, compense le mouvement de basculement des deux parties de raccord d'énergie (14, 15) lors du pivotement l'une vers l'autre sur la voie circulaire autour du premier axe de verrouillage (7) et contraint les deux parties de raccord d'énergie (14, 15) lors de l'accouplement à un mouvement linéaire exact l'une relativement à l'autre le long d'une droite.
  2. Raccord rapide selon la revendication 1, où le boulon de guidage (24) possède une tête arrondie (26), une section de guidage cylindrique (27) et entre la tête et la section de guidage, un rétrécissement (28).
  3. Raccord rapide selon la revendication précédente, où le boulon de guidage (24) peut être assuré au moyen d'un boulon transversal mobile (48), en particulier actionnable hydrauliquement, qui est logé dans la partie de raccord d'énergie (14) présentant le perçage de guidage (25), dans sa position insérée dans le perçage de guidage (25).
  4. Raccord rapide selon l'une des revendications précédentes, où seulement une des deux parties de raccord d'énergie est logée d'une manière mobile relativement à la partie de raccord rapide correspondante.
  5. Raccord rapide selon l'une des revendications 1 ou 2, où les deux parties de raccord d'énergie sont logées d'une manière mobile relativement aux parties de raccord rapide (2, 5).
  6. Raccord rapide selon l'une des revendications précédentes, où l'une des deux parties de raccord d'énergie (15) est logée d'une manière mobile, de préférence sur une installation à ressort (21), en particulier sur un agencement de plusieurs ressorts de pression (22).
  7. Raccord rapide selon l'une des revendications précédentes, où une tige de poussée (32) est prévue sur laquelle repose d'une manière basculable et/ou déplaçable l'une des deux parties de raccord d'énergie (15).
  8. Raccord rapide selon la revendication précédente, où la tige de poussée (32) présente un boulon logé d'une manière déplaçable longitudinalement qui est précontraint au moyen d'un ressort (43).
  9. Raccord rapide selon la revendication 7, où la tige de poussée (32) présente un cylindre logé d'une manière déplaçable et apte à être soumis à l'action d'un fluide de pression.
  10. Raccord rapide selon la revendication précédente, où le cylindre (60) est soumis à l'action de fluide de pression d'un circuit de fluide de pression à accoupler, où un rapport des surfaces de la face active de cylindre effective, qui est soumise à l'action du fluide de pression, à la face de connexion effective, qui est soumise dans la zone des connecteurs (71) à l'action du fluide de pression perpendiculairement à la direction d'accouplement, est supérieur à 1.
  11. Raccord rapide selon la revendication 9, où le cylindre (60) peut être amené en liaison d'écoulement avec plusieurs, en particulier tous les conduits de fluide de pression (67, 68, 69, 70) du circuit de fluide de pression à accoupler, où est prévu de préférence entre les conduits de fluide de pression et le cylindre un agencement de vannes (72, 73, 74) qui relie le cylindre (60) au conduit de fluide de pression soumis à la pression la plus élevée.
  12. Raccord rapide selon l'une des deux revendications précédentes, où le cylindre (60) est alimenté par le circuit de fluide de pression côté outil.
  13. Raccord rapide selon la revendication 9, où le cylindre (60) est alimenté par un circuit de fluide de pression séparé du circuit de fluide de pression à accoupler.
  14. Raccord rapide selon l'une des revendications 7 à 13, où le raccord de circuit d'énergie peut être réuni au moyen de la tige de poussée (32) d'une manière retardée dans le temps par rapport au mouvement de pivotement d'assemblage du raccord rapide.
  15. Raccord rapide selon l'une des revendications 7 à 14, où la tige de poussée (32) présente au côté frontal un capuchon de pression (75), où est prévu entre la tige de poussée et le capuchon de pression une liaison basculable, en particulier des faces arrondies d'une manière complémentaire l'une à l'autre.
  16. Raccord rapide selon l'une des revendications précédentes, où est prévu un précentrage (29) pour le précentrage des deux parties de raccord d'énergie (14, 15) lors du pivotement l'une vers l'autre des parties de raccord rapide (2, 5), de préférence présentant une paire de faces de centrage (30, 31) glissant l'une sur l'autre lors du pivotement l'une vers l'autre, dont une est disposée sur la partie de raccord d'énergie (15) logée d'une manière mobile et l'autre sur la partie de raccord d'énergie (14) respectivement sur la partie de raccord rapide correspondante (2).
  17. Raccord rapide selon l'une des revendications précédentes, où est prévu un guidage pivotant pour les deux parties de raccord rapide (2, 5) qui contraint les deux parties de raccord rapide (2, 5) lors du pivotement l'une vers l'autre dans leur orientation de consigne l'une par rapport à l'autre ou qui empêche un pivotement l'une vers l'autre lors d'une orientation erronée des deux parties de raccord rapide.
  18. Raccord rapide selon la revendication précédente, où le guidage pivotant (44) possède à distance du premier axe de verrouillage (7) des faces de guidage (46, 47) qui sont prévues sur la partie de raccord rapide (2) côté flèche, et respectivement sur la partie de raccord rapide côté outil (5) et qui, lors du pivotement l'une vers l'autre des deux parties de raccord rapide (2, 5) autour du premier axe de verrouillage (7), glissent l'une sur l'autre ou glissent l'une devant l'autre.
  19. Raccord rapide selon l'une des revendications précédentes, où le raccord de circuit d'énergie (13) est une unité de montage pouvant être montée ultérieurement sur les deux parties de raccord rapide (2, 5).
  20. Raccord rapide selon l'une des revendications précédentes, où le raccord de circuit d'énergie (13) est disposé à l'extérieur de la zone délimitée par les deux axes de verrouillage (7, 8).
  21. Raccord rapide selon l'une des revendications précédentes, où les deux parties de raccord rapide (2, 5) présentent chacune deux pièces de support (16 ; 17) espacées sensiblement perpendiculaires aux axes de verrouillage (7, 8), et les parties de raccord d'énergie (14, 15) sont disposées chacune entre deux pièces de support (16: 17) associées transversalement à celles-ci.
  22. Raccord rapide selon l'une des revendications précédentes, où les parties de raccord d'énergie (14, 15) possèdent chacune des pièces de support (19, 20) sensiblement en forme de plaque ainsi que des pièces de connexion mâle ou femelle (18) disposées perpendiculairement aux pièces de support en forme de plaque, où de préférence les boulons de guidage (24) et les perçages de guidage (25), pour le guidage linéaire des deux parties de raccord d'énergie, sont reliés rigidement aux pièces de support (19, 20) ou sont réalisés dans celles-ci.
  23. Raccord rapide selon l'une des revendications précédentes, où les parties de raccord d'énergie (14, 15) sont réalisées chacune comme bloc de connecteur, qui présente une pluralité de pièces de connecteur (18) pour une pluralité de lignes d'énergie.
  24. Raccord rapide selon l'une des revendications précédentes, où est prévu un verrou (49) pour le verrouillage par concordance des formes des deux parties de raccord d'énergie (14, 15) dans leur position accouplée, où le verrou (49) est précontraint de préférence dans sa position verrouillée au moyen d'un ressort et/ou est actionnable hydrauliquement.
EP02005070.4A 2001-03-09 2002-03-06 Attache rapide Expired - Lifetime EP1239087B2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10111485 2001-03-09
DE10111485 2001-03-09
DE10159417A DE10159417C2 (de) 2001-03-09 2001-12-04 Schnellkupplung
DE10159417 2001-12-04

Publications (3)

Publication Number Publication Date
EP1239087A1 EP1239087A1 (fr) 2002-09-11
EP1239087B1 EP1239087B1 (fr) 2012-01-18
EP1239087B2 true EP1239087B2 (fr) 2017-01-18

Family

ID=26008732

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02005070.4A Expired - Lifetime EP1239087B2 (fr) 2001-03-09 2002-03-06 Attache rapide

Country Status (8)

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US (1) US6813851B2 (fr)
EP (1) EP1239087B2 (fr)
JP (1) JP4102578B2 (fr)
CN (1) CN1246540C (fr)
CA (1) CA2374679C (fr)
CZ (1) CZ303239B6 (fr)
PL (1) PL200100B1 (fr)
RU (1) RU2235829C2 (fr)

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KR102360704B1 (ko) * 2021-08-25 2022-02-08 유제록 중장비용 회전링크 연결장치의 유압포트 구조
KR102368581B1 (ko) * 2021-08-25 2022-02-25 유제록 중장비용 회전링크 연결장치
DE102022126522A1 (de) 2022-10-12 2024-04-18 Liebherr-France Sas Arbeitsmaschine mit Kupplungsvorrichtung für fluidführende Leitungen
DE102022127836A1 (de) 2022-10-21 2024-05-02 Liebherr-Hydraulikbagger Gmbh Baggerlöffel

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FR2684120A1 (fr) † 1991-11-27 1993-05-28 Emily Ets Systeme d'accouplement et de desaccouplement d'un chargeur a commande hydraulique pour tracteurs agricoles ou autres.
GB2310472A (en) † 1996-02-23 1997-08-27 Dart Engineering Ag Hydraulic coupling
SE468320C (sv) † 1991-02-26 1997-10-21 Chrial Engineering Handelsbola Hydrauliskt kopplingsarrangemang
DE19881458T1 (de) † 1997-08-28 1999-11-25 Caterpillar Inc Verfahren und Vorrichtung zum Kuppeln eines mit Strömungsmittel betriebenen Werkzeugs mit einer Arbeitsmaschine

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FR2676765B1 (fr) * 1991-05-22 1994-05-13 Koehl Jean Marie Dispositif d'accouplement mecanique, hydraulique et electrique de maniere instantanee, automatique, commandee a distance.
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SE468320C (sv) † 1991-02-26 1997-10-21 Chrial Engineering Handelsbola Hydrauliskt kopplingsarrangemang
FR2684120A1 (fr) † 1991-11-27 1993-05-28 Emily Ets Systeme d'accouplement et de desaccouplement d'un chargeur a commande hydraulique pour tracteurs agricoles ou autres.
GB2310472A (en) † 1996-02-23 1997-08-27 Dart Engineering Ag Hydraulic coupling
DE19881458T1 (de) † 1997-08-28 1999-11-25 Caterpillar Inc Verfahren und Vorrichtung zum Kuppeln eines mit Strömungsmittel betriebenen Werkzeugs mit einer Arbeitsmaschine

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EP3901378A1 (fr) * 2020-04-17 2021-10-27 Liebherr-Hydraulikbagger GmbH Accouplement rapide pourvu de dispositif de centrage

Also Published As

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PL352565A1 (en) 2002-09-23
CN1246540C (zh) 2006-03-22
CZ303239B6 (cs) 2012-06-13
CA2374679C (fr) 2009-02-10
EP1239087B1 (fr) 2012-01-18
US20020157287A1 (en) 2002-10-31
EP1239087A1 (fr) 2002-09-11
CZ2002828A3 (cs) 2002-10-16
CA2374679A1 (fr) 2002-09-09
JP4102578B2 (ja) 2008-06-18
RU2235829C2 (ru) 2004-09-10
CN1375601A (zh) 2002-10-23
US6813851B2 (en) 2004-11-09
JP2002348905A (ja) 2002-12-04
PL200100B1 (pl) 2008-12-31

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