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EP2011605B1 - Outil manuel actionné hydrauliquement - Google Patents

Outil manuel actionné hydrauliquement Download PDF

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Publication number
EP2011605B1
EP2011605B1 EP08159378.2A EP08159378A EP2011605B1 EP 2011605 B1 EP2011605 B1 EP 2011605B1 EP 08159378 A EP08159378 A EP 08159378A EP 2011605 B1 EP2011605 B1 EP 2011605B1
Authority
EP
European Patent Office
Prior art keywords
piston
working head
hand tool
hydraulic
tool according
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.)
Not-in-force
Application number
EP08159378.2A
Other languages
German (de)
English (en)
Other versions
EP2011605A2 (fr
EP2011605A3 (fr
Inventor
Egbert Frenken
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.)
Gustav Klauke GmbH
Original Assignee
Gustav Klauke GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Gustav Klauke GmbH filed Critical Gustav Klauke GmbH
Priority to PL08159378T priority Critical patent/PL2011605T3/pl
Publication of EP2011605A2 publication Critical patent/EP2011605A2/fr
Publication of EP2011605A3 publication Critical patent/EP2011605A3/fr
Application granted granted Critical
Publication of EP2011605B1 publication Critical patent/EP2011605B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R43/00—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors
    • H01R43/04—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors for forming connections by deformation, e.g. crimping tool
    • H01R43/042—Hand tools for crimping
    • H01R43/0427—Hand tools for crimping fluid actuated hand crimping tools

Definitions

  • the invention relates to a preferably hydraulically actuated hand tool according to the features of the preamble of claim 1.
  • Such a hand tool is from the DE 102 16 213 A1 known.
  • Hand tools of the type in question are known, in addition to conventional, two-hand, further example, electro-hydraulically operating hand tools in lighter version for one-handed operation.
  • Such hand tools are used, for example, in the sanitary area for pressing pipe joints or in the electrical area for pressing cable lugs on electric wire ends.
  • hydraulic forces of, for example, 3 tons are achieved.
  • the working head is connected to the trunk device via a thread. But this only to make an exchange of a working head, if necessary, or to carry out maintenance.
  • the working part is a pivotable pressing jaw, which can be moved by hydraulic movement of a working head associated piston against an example fixed jaw.
  • a feed movement that is a force actuation of the working part by hydraulic pressure or, for example, a spindle adjustment by means of an electric motor causes.
  • a first switching operation with a switch button is required.
  • Another movement of the working part in particular a return movement after work, so for example after completion of a compression, often takes place automatically, namely on the triggering of a return valve out at a hydraulic device, or must by another lever or switch operation, the latter at about one electrical device, to be triggered.
  • the invention has the object, a hand tool of the type specified in such a way and further, that safe working is ensured by means of a clear and clear handling.
  • the workability of the handset as such, so in the case of a hydraulic device, the work of the pump can be started by a separate button.
  • the rotary connection area the already existing in the known devices threaded connection can be used. As explained in more detail below, precautions can be taken that it does not involuntarily come to a complete unscrewing of the working head.
  • a separate rotary connection region can also be provided independently of the threaded connection, in which case there is no axial distance change between the working head and the trunk device in the course of a rotation.
  • a preferred embodiment is given by the fact that a pivoting position between the working head and the trunk device can be fixed. For example, in order to be able to effortlessly maintain the same pivoting position over several work processes. Or also, in order to maintain a secure pivoting between the working head and the trunk device in the course of then taking place power operation of the working part.
  • the hull device has a first piston, which pivots in the course of the switching movement about its longitudinal axis extending in the direction of movement. This is usually achieved by a direct rotational coupling between the hull device and the first piston.
  • the pivot position of the first piston can be used to the desired switching. This then also in that influenced by the possible longitudinal movement of the piston, the circuit with, for example, only secured, is.
  • the aforementioned first piston can be coupled with the working head. It is an immediate coupling between the first piston and the working head achievable.
  • the coupling can thus be limited to the already longitudinally movable part, the first piston and the associated region of the working head.
  • a pivoting position between the first piston and the working head by direct contact between the first piston and the working head can be fixed.
  • the first piston can be moved against the working head and the case given plant on the working head also serves to fix the pivoting position.
  • the determination of the desired pivoting position is further preferably due to the hydraulic load of the first piston on the piston head facing away from the working head.
  • the surface of the first piston opposite this piston surface is consequently pressed under pressure against the working head, after which a further pivoting is possible only after the pressure on the piston has been reduced.
  • a sufficiently high frictional force of the superimposed portions for example. End faces, the cooperating portions of the piston and working head reached.
  • a positive interlocking Set the desired pivot position of piston and working head sections.
  • the fixing can also be achieved, for example, by the action of a spring force on the piston in the direction of the working head, moreover also by mechanical means, for example by a restraint of forceful release or the like.
  • a spring action in the direction of the setting position for example, a helical spring or the like can continue to act on the piston surface facing away from the working head.
  • Such a spring force can be designed to be triggered, which triggering takes place after reaching the desired pivoting position between the first piston and working head.
  • the first piston is pivotally limited relative to the working head, so on with respect to the piston longitudinal axis by an angle of preferably less than 360 °, for example in an angular range of 1 ° to 90 °, more preferably in a range of 10th ° to 300 °.
  • an angular adjustability of the first piston relative to the working head of about 15 ° to 25 °, so on, for example, about 20 ° predetermined.
  • Preferred is an angular position that can be easily reached for the user from the wrist.
  • at least two different action functions of the working head are preferably adjustable. These two functional positions more preferably correspond to the pivot end positions of the first piston relative to the working head.
  • intermediate positions of the first piston are possible, which may also be fixed, via which intermediate positions further functions can be triggered, whereby a further function, for example, can constitute a locking position of the working head in its working position.
  • first piston with a second piston received in a second cylinder is pivotably coupled.
  • the second cylinder is preferably formed in the working head.
  • the working head itself can form the cylinder. Due to the different pivot positions of the first piston different effects on the sliding in the second cylinder second piston can be achieved, so on, for example, a circuit of the second piston in the flow or return direction of the same.
  • the force acting on the second piston and, moreover, the displacement speed of the second piston can also be specifically controlled via the pivoting position of the first piston relative to the working head.
  • the longitudinal axes of the two pistons can be arranged rectified one after the other in one embodiment of the subject invention, further also forming a common, both pistons centrally in the longitudinal direction or in Direction of movement passing through axis.
  • the longitudinal axes of the two pistons run differently, that is to say enclose an angle of less than 180 ° with respect to one another, whereby these axes can certainly also be offset relative to one another in a plane directed transversely to the longitudinal axis extension.
  • the aforementioned inclusion angle relates correspondingly to a projection of the piston longitudinal axes into a projection plane considered perpendicular to the longitudinal axis transverse plane.
  • the included by the piston longitudinal axis angle may have a size of, for example 15 ° to 170 °, further example, from 45 ° to 135 °, more preferably, the first and the second cylinder T-shaped to each other.
  • the included angle is not necessarily right-angled. This may well have a value other than 90 °, such as a value of 60 ° to 120 °, further for example a value of 75 ° to 105 °.
  • the compression between the first piston and the working head for fixing the pivoting position of the first piston is achieved by the same also the second piston moving hydraulic means. Accordingly, the second piston as well as the first piston is acted upon by the stored in the hand tool hydraulic fluid, further, under construction of a built up by a provided in the hand tool hydraulic pressure. Accordingly, it does not require separate means for actuating the second piston provided in the working head (hydraulic fluid). The operation of the working head is dependent on an assignment to the hydraulically actuated hand tool. For hydraulic actuation of the second piston in the working head of the first piston is formed by the hydraulic fluid permeable.
  • first piston flow paths so on in particular inlet and outlet flow paths for the hydraulic fluid, which in a preferred embodiment, the channel-like manner, the first piston substantially aligned along the piston longitudinal axis.
  • These flow paths are preferably used only for the flow of the working head or its piston acting hydraulic fluid.
  • first piston serves primarily only as an actuating element to be fixed, its axial displaceability can be limited to a minimum dimension which makes it possible to set and release again. After overcoming this displacement path, the associated piston surface of the first piston frictionally engages a cylinder end surface formed by the working head.
  • the first piston in a preferred embodiment with different formed large effective areas, wherein on the upstream side, a larger effective area is provided as on the downstream side of the first piston.
  • the lower effective area on the downstream side is given in a further preferred embodiment by an area associated with the substantially pressure-free hydraulic return surface portion, which hydraulic return is achieved by a first piston passing through the flow path. This results in an effective area of the piston surface which can be brought into the operative position in relation to the cylinder bottom for the piston area to be pressurized.
  • a sliding displacement of the first piston for fixing the same in the desired pivot position is also possible if on the downstream piston surface hydraulic fluid from a previous outflow from the second cylinder or from the working head is present, which hydraulic medium also in a blocking position of the downstream flow paths second cylinder or to the second piston can escape over the provided in the first piston hydraulic return substantially free of pressure.
  • the displaceability of the thus designed differential piston in the Festsetzwolf is always given.
  • the first piston acts as a result of the proposed area ratios with a multiple of the value against the cylinder bottom, so for example with the 3- to 6-fold, further example. With 2 times the Value, that is about 80 N / mm 2 .
  • the metallically co-operating surfaces of the piston and cylinder base thus form an oil-tight transition.
  • a hydraulic flow for pressurizing the arranged in the working head second piston is also provided in the first piston at the same time.
  • an inflow opening is provided on the inflow side of the first piston for the entry of the same time also the first piston in the Festsetzwolf displaceable hydraulic fluid in the first piston.
  • the inflow opening has a prestressed valve, which only when a predetermined by the bias voltage is exceeded Threshold the inlet opening for the passage of the hydraulic fluid releases. This threshold value is only reached after the first piston has shifted to the fixed setting position to the working head.
  • the valve After exceeding the valve threshold value in the inflow opening and correspondingly after reaching the sealing position in the region of the interface between the first piston and the working head, the valve switches the hydraulic flow within the first piston free, for Hydraulikstoffschetzung arranged in the working head second piston.
  • the valve arranged in the inflow opening first closes.
  • Any contaminations, such as shavings or the like, located in the sealing region between the downstream piston surface of the first piston and the counter-sealing surface in the region of the cylinder end wall can be correspondingly flushed out by means of the hydraulic fluid.
  • the guided in the working head within the there formed second cylinder second piston is designed as a double-acting piston or differential piston and at least for movement in one direction at the same time in opposite directions with different effective surface sizes acted upon by the hydraulic fluid.
  • This loading of the second piston can be done in both directions of movement of the second piston. In this regard, such loading is preferred only in one direction of movement, more preferably in the case of a forward displacement of the second piston from a rearward basic position. In this case, the pressurization of the differently effective piston surfaces is carried out with the same pressure, resulting in a difference force for movement of the second piston as a result of the different surface sizes.
  • the second piston is preferably pressurized only on one side for the return displacement, while the rear side is depressurized.
  • Such a one-sided pressurization is also possible as an alternative with respect to the piston advancement.
  • the alternative pressure conditions can also be controlled via the various pivot positions.
  • the different piston surfaces result in a preferred embodiment by arranging a piston rod on one of the two piston surfaces, which end of the piston rod carries a preferably over the cylinder projecting functional head. The latter is moved in accordance with the second piston linearly in the direction of the axial extension of the second piston. In the course of forward displacement of the functional head is expressed with the piston rod via the second piston from the second cylinder, this preferably by applying double-sided action of the second piston.
  • the loading of the second piston preferably takes place only on one side, more preferably from the piston rod side piston surface and thus from the smaller piston surface, while the opposite, larger piston surface remains unpressurized.
  • the hydraulic means located in this cylinder section is forced into the hydraulic supply via the larger piston surface for the return flow through the first piston.
  • the piston surfaces of the second piston are dimensioned such that supply and return take place at the same speeds. This is preferably achieved by a reduced by 50% piston area on the piston rod side opposite the opposite piston surface.
  • equally large forces act on the second piston both in the forward and in the return direction.
  • the piston surfaces may be in relation to one another in such a way that the tensile force acting in the return direction is greater or smaller than the ejection force acting in the advance direction.
  • the second piston has a projecting spring element for cooperation with the associated cylinder bottom.
  • This is preferably an elastomeric part, which acts like a buffer. Accordingly, there is no hard impact against the associated cylinder bottom to complete the return movement.
  • the spring element may for example also be a latch spring.
  • the protruding spring element leaves in a retracted non-compressed starting position a clearance between the cylinder base and the facing piston surface, for the inflow of the hydraulic fluid.
  • the spring element in the non-pressurized position of the second piston one, albeit minimal relative displacement of the second piston in the second cylinder allows, so on in particular over a path of several Tenths of a millimeter, further example, about 0.5mm to 2mm.
  • the axial projection of the spring element corresponds, for example, about 1 to 5%, preferably about 2% of the axial Kolbenverlagerungswegs in the cylinder.
  • the attachment or removal of the working head can be facilitated by an admission part to be acted upon or to be entrained via the functional head.
  • an outlet opening and a drain opening are formed in the end face of the first piston, wherein the outlet opening is connected to the piston inlet-side inlet opening via a channel passing through the first piston.
  • the end surface side drain opening serves the hydraulic return from the second cylinder.
  • Outlet opening and drain opening are separated from each other in terms of flow.
  • the outlet and drain openings may each have a circular cross-section corresponding to the downstream flow paths in the first piston on the end surface side of the first piston. It is further possible in this regard that at least one of the openings, so far preferably the drain opening is enlarged in area over the downstream flow path in cross-section, which resulting cross-sectional area of the drain opening may also be formed deviating from a circular shape.
  • the drain opening may have a radially projecting from the flow channel connected to the drain port opening portion.
  • the drain opening associated with and formed in the first piston discharge line opens in a further preferred embodiment in one, in both directions - with respect to the extension direction of the piston longitudinal axis - sealed intermediate region, which intermediate region a between the piston outer surface and the cylinder inner surface in the region between two axially spaced-apart sealing regions adjusting annular space is assigned.
  • This intermediate region is hydraulically separated from the hydraulic inlet region assigned to the inflow side of the first piston and is connected in fluid communication with a hydraulic storage container.
  • two hydraulic paths are formed in a development of the subject invention, which form the end face, that is, the downstream end face of the first piston associated openings.
  • these hydraulic passages as well as the inlet and outlet lines formed in the first piston open into the press-fitted region sealed to the working head in the setting position of the first piston.
  • One of the second cylinder associated hydraulic paths is designed to act on the effective total cross section of the second piston, while the second hydraulic path is used to act on an annular space.
  • This annular space is assigned to the areal smaller piston surface of the second piston, resulting from a cylinder space portion passing through, connected to the piston piston rod.
  • the two piston surfaces of the second piston formed as a differential piston can be selectively actuated via the two hydraulic paths. At the same time serves at least one of the hydraulic paths as a drainage path for the hydraulic fluid.
  • the two openings of the hydraulic paths are arranged in the pivoting region of the outlet opening of the first piston, are accordingly both with the inflow side of the first piston, in particular switchable after displacement of the pressure relief valve in the open position, for selectively or combined action on the two piston surfaces of the second piston.
  • one of the openings of the hydraulic paths is hereby in Pivoting range of the drain opening of the first piston arranged, can accordingly form the return path for the hydraulic fluid to the storage container in dependence on the pivoting position of the first piston.
  • the latter are different from the outlet opening and the outlet opening of the first piston assignable, so as to achieve different effects on the second piston, so more preferred Flow and return movement of the piston.
  • both openings of the hydraulic paths with respect to the outlet opening of the first piston and the pivoting region are arranged so that they can be simultaneously flowed through by hydraulic means.
  • This configuration is preferably achieved in one of the pivoting end positions of the first piston. In the opposite pivot end position of the first piston, more preferably, only one of the openings of the hydraulic path is connected to the outlet opening of the first piston, while the opening of the other hydraulic path is associated with the discharge opening of the first piston.
  • latchable pivotal intermediate positions are possible, for example, a center position, in which although one of the hydraulic path openings of the outlet opening of the first piston is assigned, the opening of the second hydraulic path, however, neither the outlet nor the drain opening of the first piston is assigned blocked. In this position results in operation of the hand tool, that is, when building a hydraulic pressure no displacement of the second piston both in one direction and in the other direction. Further, a position may be provided, in which the hydraulic means, the second piston for advancement only on one side, namely on the piston rod acted on opposite piston surface.
  • the opening of the associated hydraulic path is assigned to the outlet opening of the first piston, while the opening of the hydraulic path associated with the piston area opposite the piston area engaged is connected to the outlet opening of the first piston.
  • the generally free rotatable in the second cylinder about its longitudinal axis second piston is circumferentially aligned during retraction from a forward displacement position by means of a formed on the second cylinder catching recess.
  • a wedge-shaped outwardly widening groove is provided on the front side of the second cylinder, which serves for the circumferentially aligned reception of a radial projection arranged, for example, in the region of the functional head. This ensures that, in particular, the functional head is always aligned in the initial position, that is, in the retracted piston position in a positionally correct starting position.
  • FIG. 1 Shown and described is first with reference to FIG. 1 a suitable for single-handed operation electro-hydraulic (trunk) hand tool 1 for actuating an arranged working head 2.
  • the latter is used for expelling or drawing a chisel 3 from or into a chisel holder. 4
  • the hand tool 1 is designed substantially elongate rod-shaped, which supports the one-handed operation of the tool.
  • This rod-shaped configuration is achieved in that the individual assemblies are positioned in the housing 5 in axial succession arrangement and further aligned substantially in alignment with a longitudinal axis y of a linearly displaceable in the hand tool 1 first piston 6.
  • the housing 5 forms a grip area 7, the housing diameter being selected to be ergonomically adapted in this grip area 7.
  • the electric motor is fed by a battery 8 which can be plugged in the axial direction of the electric motor.
  • the battery 8 can be plugged into and latched into a corresponding housing receptacle.
  • the device can also be formed directly with power plug operation, or be provided in addition to the accumulator 8 with a power plug.
  • the first piston 6 is moved in a known manner in the hand tool 1 via an oil pressure increase, this along its longitudinal axis y.
  • a transmission is arranged between the electric motor and a pump.
  • the implementation of the rotational movement is achieved by the electric motor in an oscillating pumping movement of a pump tappet 9. This reciprocating pumping movement takes place in the axial direction of the motor shaft and correspondingly further in the axial direction of the first piston 6.
  • the first piston 6 With the oscillating movement of the pump plunger 9, the first piston 6 is oil pressure-applied via a valve arrangement, not shown.
  • the first piston 6 is in this case in a first cylinder 10 of a tool-side head 11 a.
  • This head 11 is provided with an external thread for cooperation with a corresponding internal thread of the attachable working head 2.
  • a return valve 12 is provided in juxtaposition, that is offset parallel to the pump plunger 9, which at one end is conductively connected to the pressure chamber 13 in front of the first piston 6.
  • This return valve 12 opens automatically when a predefined pressure in the pressure chamber 13 is exceeded and opens a path to the pump or the pump tappet 9 and the return valve 12 annularly surrounding the hydraulic storage container 14.
  • the opening of the check valve 12 causes a resetting of the first piston 6 in the unloaded basic position via a on the pressure chamber 13 opposite piston surface of the first piston 6 acting force.
  • a pivotable actuating switch 15 is provided in the grip area 7.
  • the substantially circular cylindrical designed working head 2 forms a second cylinder 16, in which a second piston 17 is guided linearly.
  • the longitudinal axis x of the second piston 17 is aligned at right angles to the longitudinal axis y of the first piston 6, an extension of this longitudinal axis y cutting.
  • Mantelwandungsau built lake is formed on the second cylinder 16 a circular cross-section, aligned in the state of assignment to the hand tool 1 coaxial with the longitudinal axis y of the first piston 6 aligned flange 18.
  • This is the inside of the wall for fixing the working head 2 on the hand tool 1 in the region of a radial extension of the interior with the, provided with the external thread of the first cylinder 10 meshing internal thread.
  • the axially adjoining the internal thread, rooted in the cylinder wall flange portion forms on the inside wall a portion of the first cylinder 10, correspondingly forms an extension of the same.
  • the first piston 6 guided in the first cylinder 10 initially has an outer diameter reduced in relation to the inner diameter of the cylinder and is further designed substantially as a solid body, with a length considered in the axial direction which is approximately 0.9 to 0.98 times further about 0.97 times the considered in the same direction length of the first cylinder 10 including the cylinder 10 further forming this flange portion corresponds.
  • first piston 6 Distributed over the length of the first piston 6 is provided with radially expanded portions 19, 20, 21, whose outer diameter are adapted to the inner diameter embedded in these extended sections 19 to 21 of the first piston 6 carries in correspondingly positioned circumferential annular grooves 22 ring seals 23, which occur radially outwardly sealing against the cylinder wall.
  • the extended portion 19 is formed in the pressure chamber 13 facing the end portion of the first piston 6. At this opposite end of the second extended portion 20 is formed, for cooperation with the, the enlarged cylinder-forming flange portion of the working head 2. Between the end-side sections 19 and 20, the further extended portion 21 is positioned, with an axial distance to the pressure chamber side portion 19th , which corresponds approximately twice the distance to the frontal section 20. This results in between the sections 19 and 21 or 20 and 21, the first piston 6 comprising annular spaces 24 and 25, wherein the created between the pressure chamber side portion 19 and the central extended portion 21 annular space 24 via a transverse to the axis y radially to externally aligned bore 26 communicates with the storage container 14.
  • the first piston 6 is designed for the flow of hydraulic fluid.
  • this first has a substantially parallel to the piston axis y extending inflow 27, which extends over the entire length of the piston 6 and thus opens both on the inflow side A and on the outflow side B of the first piston 6 and there corresponding to an inflow 28 and an outflow opening 29 ausformt, wherein further in the immediate region of the outflow opening 29 of the inflow passage 27 has a radial offset to the outside.
  • the outflow opening 29 is formed in the pressure chamber 13 facing away from the end surface 30 as a circular opening.
  • the inflow opening 28 of the inflow channel 27 is formed in an axial extension 32 screwed into the inflow channel 27 from the end face 31 of the piston 6 facing the pressure chamber 13. This projects according to the arrangement of the inflow 27 in an eccentric assignment beyond the end face 31, wherein further the axial extension 32 rests positively in an associated axial slot 33 in the pressure chamber 13. As a result, a backup of the first piston 6 is given against rotation about its longitudinal axis y with further enabled linear displacement along the longitudinal axis y.
  • the inflow opening 28 is closed in the unloaded position by a prestressed valve 34.
  • this is a pressure controllable ball valve, with a ball 35 which is aligned within the axial extension 32 parallel to the longitudinal axis y against a rearwardly acting against the ball 35 compression spring 36 from its sealing seat position against the inflow opening 2 by pressurizing the inflow opening 28 is displaced.
  • the discharge channel 37 forms a discharge opening 39 that is initially circular in plan, and that merges further in the area of the end face 30 into an extension section 40 extending radially outward. This is formed out of the end face 30 recess-like and extends to the end edge edge edge such that a relative to the longitudinal axis y, the inflow opening 28 opening in the end face 30 traverses the extension section 40 in the center thereof in its extension, this continues with an adjacent allocation of the extension section 40 and inflow opening 28, including an angle of approximately 30 °.
  • the plan, aligned transversely to the piston axis y end face 30 is optionally spaced with the order of the displacement of the piston 6 a plane even directed, also flat cylinder head surface 41 foot side of the working head flange 18 opposite.
  • this cylinder head surface 41 two associated with the formed in the working head 2 second cylinder 16 associated hydraulic paths 42, 43.
  • Their openings 44 and 45 are arranged on an axis y relating to the circular line, which in a projection on the opposite end face 30 of the first piston 6 intersects the inflow opening 28 and the extension section 40.
  • the openings 44 and 45 are arranged offset by an angle of about 20 ° in the circular line direction to each other.
  • the second piston 17, which is displaceable linearly along the longitudinal axis x in the second cylinder 16, is designed as a differential cam.
  • this piston 17 has a first piston surface 47, which faces a cylinder bottom 46 and corresponds in terms of area substantially equal to the cross-sectional area of the cylinder interior.
  • This piston surface 47 is opposite to the piston 17 centrally coaxially to the axis x over the opposite end of the cylinder 16 extending beyond piston rod 48 is formed, which is diametrically selected so that radially outwardly, the piston rod 48 on the opposite piston surface 47 Side of the piston 17 results in an annular piston surface 49 which corresponds in terms of area in the illustrated embodiment 0.5 times the opposite piston surface 47.
  • the second piston 17 is provided with a piston ring seal 50, which cooperates sealingly with the inner wall of the second cylinder 16.
  • the effective cylinder space 16 has an extension length which corresponds approximately to 4 times the cylinder diameter.
  • the piston rod 48 passes through in the region of the cylinder bottom 46 facing away from the end of the cylinder 16 centrally a guide insert 51.
  • the latter is the cylinder end side wall inside screwed to the cylinder wall. Facing the cylinder chamber carries the guide insert 51 radially outward a circumferential seal 52 for sealing the cylinder chamber to the outside.
  • the guide insert 51 carries two further gaskets arranged at a distance from one another in the axial direction, an axially inner seal facing the cylinder chamber being a ring seal 53 and an axially outer seal in the form of a stripping element 54 ,
  • the functional head 55 is configured claw-like for mounting the free end of the chisel shaft 56, so as to engage in a shaft end-side annular groove of the chisel shaft 56.
  • the functional head 55 is in a basic tool position according to the FIGS. 13 to 15 taken in a functional head 55 at least partially comprehensive support portion 57. This is the same material, integrally formed from the cylinder wall pot-like shape.
  • radially engaging cam 58 is attached.
  • This is formed in the illustrated embodiment by a screw head of a fastened in a shell portion of the support portion 57 screw.
  • the screw head or the cam 58 cooperates with a wedge-shaped opening axially aligned groove 59 of the functional head 55. This groove 59 is open radially outward.
  • the second piston 17 receives centrally on the opposite side of the piston rod 48, a spring element 60.
  • this is an elastomer part, which is held in a central bore 61 opening into the piston surface 47 and projects beyond the associated piston surface 47 with an axial dimension of approximately 1 mm to 2 mm.
  • the second piston 17 is supported in an unloaded basic position while leaving a the free end portion of the spring element 60 surrounding annular space on the associated cylinder base 46 from.
  • the in the first piston 6 associated cylinder head surface 41 opening into the opening 45 hydraulic path 43 extends parallel to the piston axis y stitch-like straight to the mouth in which between the second piston 17 and the guide insert 51 and the piston rod 48 penetrated annular space 62, which is formed by the axially at both ends provided seal in the region of the second piston 17 and in the region of the guide insert 51 as a pressure chamber.
  • the second opening into the opening 44 hydraulic passage 42 passes through parallel to the axis of the second piston 17, the cylinder wall to expire end in the region of the cylinder bottom 46 via a radially inwardly facing transverse channel 63 in the pressure chamber 64 formed between the cylinder bottom 46 and the second piston 17 ,
  • the entire working head 2 and thus also guided in this piston 17 and the cylinder 26 are pivotally supported relative to the hand tool 1 and thus relative to the rotatably guided in the hand tool 1 first piston 6 about the piston axis y to the head 11, this in the illustrated embodiment over a limited pivot angle of about 17 ° to 18 °. Due to this pivotability, a relative pivotal displacement of the hydraulic-path-side openings 44 and 45 to the piston-side outflow opening 29 and the discharge opening 39 can also be achieved.
  • the angle-limited pivotal displacement is achieved by a flange 18 radially penetrating screw 65, which projects radially inwardly beyond the Flanschinnenwandung and there dips into a recessed recess 66 of the head wall.
  • This Ausappelungsokosterrorism 66 has a width considered in the circumferential direction of the head 11, which allows in cooperation with the screw end the relative pivoting of the flange 18 to the head 11 by the prescribed angular amount.
  • a pivot position between the tool 1 and working head 2 is set, in which both openings 44 and 45 of the two working-head-side hydraulic passages 42 and 43 are in fluid communication with the outflow opening 29 of the inlet formed in the first piston 6 inlet passage 27.
  • a pressure constructed which acts with respect to the second piston 17 in opposite directions.
  • the hand tool 1 is pivotally displaced about the axis y relative to the working head 2 such that thereafter the opening 45 of the hydraulic path 43 in register with the discharge opening 29 of the piston-side inflow passage 27 and the opening 44 of the hydraulic path 42 overlap with the extension portion 40 of the drain port 39.
  • the hydraulic fluid acts under pressure correspondingly in the annular space 62 on the smaller piston surface 49 of the second piston 17, while the rear, larger piston surface 47 can escape pressure-free.
  • the hydraulic means located in the associated pressure space 64 is forced back into the storage container 14 via the hydraulic path 42, the opening 44 and further via the extension section 40 and the discharge opening 39.
  • the second piston with its projecting spring element 60 strikes against the cylinder bottom 46, which initially causes a compression of the spring element 60 upon further pressurization of the smaller piston surface 49.
  • the hand tool 1 is switched off, for example triggered by the automatic return valve 12, which opens as a function of a pressure threshold value, the pressure acting on the smaller piston surface 49 is reduced, which triggers the subsequent decompression of the spring element 60.
  • the pressure limiting valve 34 in the first piston 6 is optionally loaded in the closing direction by the hydraulic fluid flowing back.
  • the valve 34 may be formed in a development that this opens in the closing direction even at a low pressure, thus representing a corresponding acting in both directions pressure relief valve.
  • an additional conventional check valve may be arranged in the first piston 6, which allows the return flow of the hydraulic medium.
  • first and the second cylinder (10, 16) are T-shaped to each other.
  • an inflow opening (28) of the first piston (6) prefferably has a prestressed valve (34).
  • the second piston (17) has an end over the cylinder (16) projecting functional head (55).
  • the second piston (17) has at its end facing away from the functional head (55) a protruding spring element (60), for cooperation with the associated cylinder bottom (46).
  • the intermediate region is fluidly connected to a hydraulic storage container (14)
  • both openings (44, 45) can be arranged with respect to the outflow opening of the first piston (6) and its pivoting region such that they can simultaneously flow through hydraulic means.
  • the second piston (17) is also possible for the second piston (17) to be aligned circumferentially during retraction by means of a catching recess formed on the second cylinder (16).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Automation & Control Theory (AREA)
  • Actuator (AREA)
  • Shearing Machines (AREA)
  • Shovels (AREA)
  • Gripping On Spindles (AREA)

Claims (15)

  1. Outil manuel (1) de préférence à actionnement hydraulique, comprenant une tête de travail (2) et un corps qui reste en place par rapport à ce dernier, dans lequel des éléments d'actionnement de la tête de travail sont prévus dans le corps, par exemple une pompe hydraulique et un réservoir hydraulique, dans lequel en outre un déplacement sous effort d'une ou plusieurs pièces de travail de la tête de travail (2) est déclenché par un déplacement commutatif et la tête de travail (2) est en liaison pivotante avec le corps dans une région d'accouplement pivotant, caractérisé en ce qu'une inversion concernant le déplacement sous effort de la pièce de travail qui est destinée à influer sur la direction de déplacement de la pièce de travail ou inverser celle-ci est susceptible d'être opérée grâce au pivotement du corps par rapport à la tête de travail (2) autour d'un axe de rotation dans la région d'accouplement pivotant de la tête de travail au corps.
  2. Outil manuel selon la revendication 1, caractérisé en ce qu'il est possible de bloquer une position de pivotement entre la tête de travail (2) et le corps.
  3. Outil manuel selon l'une des revendications précédentes, caractérisé en ce que le corps présente un premier piston (6) lequel pivote, au cours du mouvement d'inversion, autour de son axe longitudinal (y) qui s'étend suivant sa direction de déplacement.
  4. Outil manuel selon la revendication 3, caractérisé en ce que le premier piston est susceptible d'être couplé avec la tête de travail (2).
  5. Outil manuel selon l'une des revendications 3 ou 4, caractérisé en ce que le premier piston (6) est susceptible de pivoter par rapport à la tête de travail (2).
  6. Outil manuel selon l'une des revendications précédentes, caractérisé en ce que le pivotement entre la tête de travail (2) et le corps, en particulier entre la tête de travail (2) et le premier piston (6), est limité angulairement.
  7. Outil manuel selon l'une des revendications 3 à 6, caractérisé en ce qu'une position de pivotement entre le premier piston (6) et la tête de travail (2) est susceptible d'être bloquée par appui direct entre le premier piston (6) et la tête de travail (2).
  8. Outil manuel selon l'une des revendications 3 à 7, caractérisé en ce que le premier piston (6) est couplé de manière pivotante avec un deuxième piston (17) reçu dans un deuxième cylindre (16).
  9. Outil manuel selon l'une des revendications 3 à 8, caractérisé en ce que le premier piston (6) est traversé par le fluide hydraulique.
  10. Outil manuel selon l'une des revendications 3 à 9, caractérisé en ce que la premier piston (6) a une surface efficace plus grande du côté écoulement amont (A) que du côté écoulement aval (B), dans lequel la surface efficace plus petite du côté écoulement aval (B) est procurée par une portion de surface qui est en communication avec un retour hydraulique sensiblement libre de pression.
  11. Outil manuel selon l'une des revendications 8 à 10, caractérisé en ce que le deuxième piston (17) est réalisé sous forme de piston à double effet et est susceptible d'être sollicité simultanément par le fluide hydraulique dans des directions opposées avec des surfaces efficaces de taille différente pour le déplacer au moins dans une direction.
  12. Outil manuel selon l'une des revendications 3 à 11, caractérisé en ce qu'une ouverture de sortie d'écoulement (29) et une ouverture d'évacuation (39) sont formées dans la surface frontale (30) du premier piston (6).
  13. Outil manuel selon l'une des revendications 3 à 12, caractérisé en ce qu'un conduit d'évacuation (37) réalisé dans le premier piston et associé à l'ouverture d'évacuation (39), aboutit dans une région intermédiaire du premier piston (6) qui est étanche dans les deux directions.
  14. Outil manuel selon l'une des revendications 8 à 13, caractérisé en ce que sont réalisés dans le deuxième piston (16) au moins deux chemins hydrauliques (42, 43) formant ouvertures (44, 45) qui sont associés à la surface frontale (30) du premier piston (6), l'un d'eux étant prévu pour agir sur la section transversale efficace totale du deuxième piston et le deuxième pour alimenter un espace annulaire (62).
  15. Outil manuel selon la revendication 14, caractérisé en ce que les deux ouvertures (44, 45) des chemins hydrauliques (42, 43) sont agencées dans la région de pivotement de l'ouverture de sortie d'écoulement (29) et en ce qu'au moins l'une des ouvertures (44, 45) est agencé dans la région de pivotement de l'ouverture d'évacuation (39) du premier piston (6).
EP08159378.2A 2007-07-02 2008-07-01 Outil manuel actionné hydrauliquement Not-in-force EP2011605B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL08159378T PL2011605T3 (pl) 2007-07-02 2008-07-01 Narzędzie ręczne z napędem hydraulicznym

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007030644A DE102007030644A1 (de) 2007-07-02 2007-07-02 Hydraulisch betätigbares Handwerkzeug

Publications (3)

Publication Number Publication Date
EP2011605A2 EP2011605A2 (fr) 2009-01-07
EP2011605A3 EP2011605A3 (fr) 2014-04-30
EP2011605B1 true EP2011605B1 (fr) 2016-12-21

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EP08159378.2A Not-in-force EP2011605B1 (fr) 2007-07-02 2008-07-01 Outil manuel actionné hydrauliquement

Country Status (8)

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US (1) US8672054B2 (fr)
EP (1) EP2011605B1 (fr)
CN (1) CN101337349B (fr)
AU (1) AU2008202895B2 (fr)
CA (1) CA2635703C (fr)
DE (1) DE102007030644A1 (fr)
ES (1) ES2615536T3 (fr)
PL (1) PL2011605T3 (fr)

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Also Published As

Publication number Publication date
CA2635703C (fr) 2016-11-08
DE102007030644A1 (de) 2009-01-08
PL2011605T3 (pl) 2017-05-31
CA2635703A1 (fr) 2009-01-02
AU2008202895A1 (en) 2009-01-22
ES2615536T3 (es) 2017-06-07
EP2011605A2 (fr) 2009-01-07
US20090008118A1 (en) 2009-01-08
CN101337349B (zh) 2012-09-26
US8672054B2 (en) 2014-03-18
CN101337349A (zh) 2009-01-07
EP2011605A3 (fr) 2014-04-30
AU2008202895B2 (en) 2014-04-03

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