EP2162250B1 - Vorrichtung zur bearbeitung von werkstücken - Google Patents

Vorrichtung zur bearbeitung von werkstücken Download PDF

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Publication number
EP2162250B1
EP2162250B1 EP08760653.9A EP08760653A EP2162250B1 EP 2162250 B1 EP2162250 B1 EP 2162250B1 EP 08760653 A EP08760653 A EP 08760653A EP 2162250 B1 EP2162250 B1 EP 2162250B1
Authority
EP
European Patent Office
Prior art keywords
actuator
workpiece
tool
arrangement
spring
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
EP08760653.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2162250A1 (de
Inventor
Erwin Schmucker
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.)
Pitec Deutschland GmbH
Original Assignee
Individual
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
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Publication of EP2162250A1 publication Critical patent/EP2162250A1/de
Application granted granted Critical
Publication of EP2162250B1 publication Critical patent/EP2162250B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/24—Drives for hammers; Transmission means therefor for power hammers operated by steam, air, or other gaseous pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • 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
    • B25D9/08—Means for driving the impulse member comprising a built-in air compressor, i.e. the tool being driven by air 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
    • B25D9/16—Valve arrangements therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/085—Elastic behaviour of tool components
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/275—Tools having at least two similar components
    • B25D2250/285—Tools having three or more similar components, e.g. three motors
    • B25D2250/291—Tools having three or more parallel bits, e.g. needle guns
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/311—Ultrasonic percussion means

Definitions

  • the invention relates to a device according to the preamble of claim 1 for machining workpieces, in particular for beating machining, such.
  • a floor surface or a building part can be understood.
  • a device for the reworking of welds, a device is known under the name UIT (UItrasonic Impact Treatment), in which an ultrasound controller acts on one or more pins movably guided between the exciter and the workpiece surface. The device is moved manually along the welds. Methods and devices are for. In US 6171415 . US6289736 . US 6338765 or US 6458225 described. By reworking welds with such a device, the strength of the welds can be significantly improved. The device is unwieldy and expensive.
  • UIT Ultrasonic Impact Treatment
  • a pneumatic actuator is known.
  • the actuator includes an outer housing and a typically pneumatic fluid muscle mounted within the outer housing defining an annular space between the fluid muscle and the outer housing.
  • Fluid ports ie, generally air ports, are provided to pressurize the fluid muscle and annular space to above ambient pressure, thereby allowing the fluid muscle to produce an actuation motion in which pressure is released from the annular space.
  • the DE 3402010 A1 describes a work tool that should greatly facilitate the work of removing rust from iron plates and other iron structures. Rust is removed with the help of a few small hammers, which are parallel and the knock against the surface from which rust is to be removed.
  • the small hammers are driven by an electric motor, which is either integrated in the implement or in another implement, such as an electric hand drill, to which the device is attached to the small hammers.
  • the work implement conveniently includes a motorized control roller which periodically displaces alternately the small hammers or the respective guide rods connected to them, against the force of a spring, but then, so that the small hammers are urged by the force, releases this spring the surface from which rust should be removed.
  • the present invention has for its object to provide an improved device for machining workpieces, in particular for beating processing of workpiece surfaces.
  • the solution according to the invention is specified in claim 1.
  • the dependent claims contain advantageous refinements and developments of the invention.
  • actuators with an acted upon by compressed air, elongated hollow body, which spaced between two in its longitudinal direction End bodies is closed laterally through the tubular flexible membrane and shortens the mutual distance of the two end body with supply of compressed air into the cavity with lateral expansion of the membrane, in the drive device proves to be very advantageous from various aspects.
  • Such actuators are known per se and z. B. as so-called “Fluidic Muscles” from Festo available.
  • the functional principle is also referred to as membrane contraction.
  • Such an actuator is available at low cost and can be operated favorably by the operation with compressed air and easily controlled via conventional valve arrangements.
  • the actuator is particularly advantageous for small strokes of an oscillating motion by high achievable frequencies and extensive wear and high Aktuatorkraft.
  • in the beating processing is of particular advantage that the actuator due to the flexibility of the membrane and the compressibility of air as a fluid, the sudden delay when hitting the workpiece or a movable impact tool or the acceleration on setback of a percussion tool without damage survives permanently.
  • the elongated shape of the actuator proves to be advantageous in that in a preferred arrangement of acted upon by the actuator tool assembly this advantageously in the longitudinal direction of the actuator can be offset against this and thereby facing the workpiece results in a slim design of the device through which also surfaces in angles are usually within easy reach.
  • a gripping position for the hand of a user can be provided on a recaptable housing wall of the device surrounding the actuator.
  • compressed air By operating with compressed air as the drive medium, on the one hand, a low weight of the device results, so that it can be advantageously designed as a hand-held device in operation.
  • the compressed air derived from the actuator can easily be released into the environment and, in an advantageous embodiment, diverted to the tool arrangement and the workpiece surface being processed as the cooling medium.
  • compressed air can be passed as the cooling medium, bypassing the actuator, to the tool arrangement and workpiece surface.
  • one of the two end body is attached to a housing base body of the device and the other end body relative to the housing base body movable.
  • the tool assembly includes at least one by the actuator, in particular its relative to the housing of the device movable end body driven, relative to a housing base body movable tool part.
  • the tool assembly additionally contains at least one fixed relative to the housing part, which is advantageously releasably connected to exchange a tool with the housing base body and / or which can advantageously form a guide for at least one working body, in a workpiece facing the tool head is movably guided and acts on the surface of a workpiece.
  • the at least one working body can be made in one piece with the part driven by the actuator or connected to it in solid motion coupling.
  • one or preferably several working bodies are relative to the housing main body and movably mounted relative to the driven part and acted upon on their faces facing away from the workpiece by the driven part.
  • a working body is advantageously substantially rod-shaped and acts with the end face facing the workpiece on the workpiece, in particular the workpiece surface a striking.
  • rod-shaped working bodies can advantageously be arranged next to one another in a row.
  • the device is generally advantageous, in particular for producing a beating machining of a workpiece, in particular a workpiece surface, wherein the driven part of the tool acts directly or preferably via at least one movable working body on the workpiece surface.
  • the driven part of the device then strikes the workpiece facing away from the surface of the working body in the latter embodiment and the working body strikes with a workpiece facing surfaces on the workpiece, in particular the workpiece surface.
  • the distance of the striking surface of the driven part from the workpiece surface is greater than the length of the movable working body, so that it flies in its direction of movement between the workpiece surface and the driven part back and forth, wherein the working body guided in a guided tour is movable.
  • the working body may also be suspended from at least one membrane and supported transversely to its direction of movement. Several working bodies are preferably guided independently of each other movably.
  • the device can also be advantageously used to drive a tool part into a workpiece, it also being possible for a workpiece or wall to be a bottom surface.
  • Such tools can be used in particular as motor-driven hand-held chisels or hammers, in particular in structural engineering.
  • the device is a device or a part thereof for processing metallic surfaces, in particular for post-processing on or around welded structures, in particular welds, in order to improve their strength in near-surface areas.
  • the direction of movement of the working body advantageously extends substantially in the direction of the direction of movement of the driven element, but may also be inclined therewith, the direction deviation advantageously not exceeding 30 °.
  • a valve device for the controlled supply of compressed air into the cavity of the actuator and preferably also for the controlled removal of air from the cavity advantageously contains one or more electrically controllable valves.
  • the valves are designed in a preferred embodiment as 2-way switching valves, which are periodically switched with a variable predetermined frequency and initiate compressed air from a compressed air source in the cavity of the actuator in a first switching state for a first switching duration (switch-on) and in a second switching state derive air from the cavity for a second switching period (switch-off time).
  • the duty cycle between the first and second switching time is variable. With the variation of the duty cycle, the time-averaged pressure in the cavity and thus an operating point of the actuator can be variably adjusted.
  • Such an operating point adjustment is also in another embodiment of the valves and / or Variation only one switching period possible.
  • operating point is meant, for example, averaged over several clock periods deflection of the movable end body or a motion-coupled with this part against a rest position with the drive device off or a comparable average size.
  • an actuatable actuator by the user is provided on the device, by means of which a change in the operating point on the change of at least one switching period is possible.
  • such an actuating element can also influence a flow resistance for the supplied and / or derived compressed air.
  • the clock frequency is variably adjustable.
  • An operating point is further dependent on the pressure of the compressed air source or at the input of the valve assembly and adjustable by the change.
  • the actuator can also be actuated only for a single cycle, that is to say in particular a single stroke, for which advantageously a separate or separately operable control element can be present
  • the housing of the device advantageously has a housing base body and a relative to this in the direction of the workpiece to a limited extent displaceable second housing part, wherein the drive means is connected to the housing main body and the second part in a preferably hand-held device operable at least has a gripping position for a user's hand and the second housing part from a rest position against a restoring force, in particular a spring force relative to the housing base body in the direction of the workpiece is displaceable in a working position.
  • a good manual specification of a pressing force of the device in the direction of the workpiece is possible and Advantageously given via such a pressing force, a further parameter for influencing the processing result.
  • at least one position for attachment in the machine may be provided instead of the at least one gripping position.
  • the displacement between the rest position and the working position is advantageously limited in both directions by stops.
  • the shift from the rest position to the working position and / or the force applied thereby can be evaluated in a development for the derivation of an operating signal for the device by z. B. operation is possible only if there is a minimum shift or a minimum force and / or if a maximum force is not exceeded.
  • a displacement sensor or force sensor or limit switch are in communication with the control device.
  • the end body facing the workpiece of the actuator fixedly connected to the housing base body and the workpiece facing away from the end body is movable relative to the housing body is advantageously within the cavity or laterally of the flexible membrane of the movable end body in Direction of the workpiece surface continuous thrust element provided, which converts the movement of the movable end body into a working movement of the tool assembly, in particular at least one working body of the tool assembly.
  • the direction of the driving force of the actuator is directed toward the workpiece.
  • the pusher element is passed through the cavity and through the stationary end body.
  • a counter-movement of the movable end body and the pusher in the direction away from the workpiece after elimination or reduction of the working force of the actuator can by the elastic deformation of the flexible membrane, by the reaction force on the pressing force of the device and / or preferably predominantly by the spring force of a spring, which is tensioned in the motion caused by the driving force done.
  • the spring may in particular also be arranged within the cavity.
  • the driving force of an actuator moves the tool assembly or a movable part of the tool assembly in a first movement portion against the working direction of the tool assembly away from the workpiece, wherein such movement is against a spring force of a spring assembly.
  • the spring arrangement can advantageously already be preloaded at the beginning of the first movement section. At the end of the first movement section, the drive force is reduced or preferably completely switched off and the movable part of the tool arrangement is moved in the direction of the workpiece surface under the influence of the spring force in a second movement section.
  • the movement of the movable part of the tool assembly may advantageously take place faster in the second movement section than in the first movement section, whereby the impact force of an impact of the tool arrangement at the end of the second movement section on a workpiece can be stronger than if the drive force of the actuator is directly affected on the tool assembly in the direction of the workpiece.
  • the spring assembly advantageously contains at least one plate spring (including special designs, diaphragm spring o. ⁇ .) Which may have a particularly high spring constant with a simple structure and thereby at low movement stroke can cause high accelerations of the movable part of the tool assembly.
  • the diaphragm spring is advantageously fixed with its outer edge in the housing base body of the device and connected to the edge of its central opening with the movable part of the tool assembly.
  • the movable part of the tool assembly at the junction with the diaphragm spring is centered transversely to the direction of movement.
  • at least two disc springs are provided spaced apart in the direction of movement, wherein the distance is preferably at least equal to the outer radius of the disc springs.
  • a spring may also be formed by a pneumatic spring as a variable gas-filled cavity, wherein advantageously the spring properties are adjustable, in particular variable adjustment of the pressure in the pneumatic spring.
  • a pneumatic spring may in particular also be provided by a further hose contraction actuator.
  • a preferably electronic control device controls the actuator of the drive device time-varying and thereby varies its driving force, wherein such a variation is preferably carried out by switching between at least two, preferably exactly two operating states.
  • Particularly advantageous is the switching off between on and off state of the actuator, z. B. in an electrically operated actuator switching on and off of a current or voltage source or in a pneumatic actuator, the opening and closing of an input valve, via which compressed air from a compressed air source can be supplied, preferably with closing and opening an output valve, via which compressed air is discharged from the cavity of the actuator, in push-pull to the input valve.
  • Input valve and output valve are advantageously combined in a switching valve. To reduce the flow resistance in the valves, the parallel connection of several valves can advantageously be provided.
  • the control device can be arranged both integrated in the device, in particular in the housing as well as in a via a preferably flexible compressed air line connected to the device compressed air source or be filled on compressed air source and device. Electrical supply or control lines can be advantageously integrated into a flexible compressed air line.
  • the controller is programmable and / or the controller includes a program memory having at least one, preferably a plurality of selectably stored operating programs.
  • the device can be operated with individually triggered movements, which can be triggered by the user via a control element.
  • the device has a control device which is provided for a clocked operation with consecutively cyclically successive movements by continuous switching of the valve arrangement between a switch-on state and a switch-off state by the control device.
  • operating elements for switching on and off in particular spring-loaded, optionally lockable electrical or pneumatic switches can be provided.
  • the switching takes place cyclically with a typically dependent on the size and application of the implement clock frequency, which z. B. for a device for reworking welds advantageously at least 30 Hz, preferably at least 50 Hz, in particular at least 100 Hz, for a chisel device advantageously at least 10 Hz, in particular at least 20 Hz, preferably at least 40 Hz, wherein the sub-cycles of on-time and off can be different lengths and switch-on and / or switch-off are variable adjustable.
  • the clock frequency is advantageously so high or the off time so short that the tool assembly does not return to its rest position during the off time.
  • the switch-on time is limited so that the tool arrangement does not exceed a permissible maximum deflection from the rest position, which may also be limited by a stop.
  • a permissible maximum deflection from the rest position which may also be limited by a stop.
  • an oscillating movement of the tool arrangement is established between two reversing positions which are deflected to different degrees relative to a rest position.
  • the device with the movement of the movable part of the tool assembly under the action of the driving force against the working direction of the tool assembly under tension of a spring assembly and the provision of the force for movement in the working direction by the spring assembly is advantageously realized with various types of drive means, in particular magnetic actuators.
  • the device is particularly advantageous with the compressed air actuator described and known as Fluidic Muscle, resulting in a particularly advantageous construction with arranged between the actuator and the workpiece spring arrangement.
  • the use of disc springs corresponds particularly advantageous with the property of such an actuator to be able to exert a particularly high driving force per pressure difference at small movement strokes.
  • a small movement stroke is again advantageously compatible with short durations of the first and second movement section, so that a short cycle time of the first and second movement section is given and a high clock frequency is possible.
  • the movement stroke in cyclic clock mode with a clock frequency of at least 30 Hz, in particular at least 50 Hz, preferably at least 100 Hz is advantageously less than 1 mm.
  • the device is advantageously only slightly vibrating relatively quiet in the hand.
  • the flow rates during inflow and outflow of compressed air are not constant over time and it turns advantageously an equilibrium state as an operating point, which is changeable, inter alia, on the change of turn-on and / or turn-off and / or clock frequency by the user.
  • a valve arrangement which also has a blocking position in addition to a closed position and an off position, in which the state of the filled with compressed air actuator is maintained for a holding period, there are more advanced Control options.
  • a 2-way switching is advantageous because of the particularly simple construction of the controllable switching valves.
  • the invention is particularly advantageous as a tool with a beating working movement of the tool assembly, in particular as a hand-held device for machining metallic workpiece surfaces for reworking welded structures or as a construction hammer or chisel device.
  • Fig. 1 shows a sectional view of a pneumatic actuator in which a cavity RH between two spaced in a longitudinal direction LR end bodies E1, E2 is completed laterally by a flexible membrane ME.
  • the flexible membrane is typically tubular and anchored in both end bodies, for example clamped.
  • the anchorage is in Fig. 1 indicated, omitted in the following figures for the sake of clarity and replaced by a simplified representation of the actuator.
  • the two End bodies typically each have fastening structures BS1, BS2, which can be largely of any type and which are therefore not discussed in detail.
  • a compressed air channel LK is formed, via which compressed air from a compressed air source in the cavity RH inserted or under pressure against the ambient air from the cavity RH in a sink, in particular the environment can be derived.
  • the actuator has an elongated shape in a longitudinal direction LR and at least the cavity RH is typically rotationally symmetrical about a longitudinal axis SA pointing in the longitudinal direction LR.
  • the cavity may be partially filled by a packing to keep the fluid volume of the cavity small and increase the operating speed of the actuator.
  • the Fig. 1 is shown in two parts in a plane passing through the central longitudinal axis SA perpendicular to the plane of the drawing, wherein in the left half of Fig. 1 a rest position of the actuator with substantially parallel to the longitudinal direction LR membrane ME and in the right half of the Fig. 1 a working position of the actuator is shown. If compressed air is introduced into the cavity RH starting from the rest position of the actuator via the channel LK, the flexible membrane ME bulges out laterally away from the central longitudinal axis SA. By means of a tension-resistant fabric with obliquely running crossed fibers embedded in the membrane ME, a lateral bulge of the membrane ME is connected with a shortening of the mutual spacing of the two end bodies E1, E2 in the longitudinal direction LR.
  • one of the two end bodies is held in a position to be regarded as stationary for registration, and the second end body imparts a longitudinal driving force to a movable part.
  • the first end body E1 as stationary and the second end body E2 as movable, so that the second end body E2 performs a movement in the longitudinal direction LR on the first end body E1 out, which is indicated by the double arrow at the end body E2 when compressed air ( or another fluid) is introduced into the cavity RH.
  • compressed air or another fluid
  • a driving force can be generated in the longitudinal direction by the actuator and the actuator can be used in this way in a drive device.
  • a provision of the end body E2 in the rest position after elimination of the overpressure in the cavity RH can be done for example by the inherent elasticity of the membrane, by a restoring force from a load or in an advantageous embodiment by a return spring, which can also be integrated into the cavity.
  • Actuators of the type described above and in Fig. 1 sketched type are available in different versions, for example as Fluidic Muscle from Festo.
  • Fig. 2 shows a first advantageous embodiment of a device for generating a beating or knocking movement using a pneumatic actuator PA2 of Fig. 1 sketched kind.
  • the actuator PA2 is housed in a housing GE, which is only schematically indicated functionally and at the same time forms the housing main body GK without relatively movable housing parts, to which the actuator is attached to a first end body E1 and thus stationary with respect to the housing main body.
  • the fixed end body E1 in the longitudinal direction LR faces a workpiece WO surface and the end body E2 of the actuator PA2 faces away from the workpiece surface WO and is movable longitudinally relative to the housing.
  • a valve arrangement VA is arranged, via which the cavity RH of the actuator via a LK extending in the longitudinal direction LK and a transverse to the longitudinal direction of the connecting passage QK in Compressed air from an input terminal DE of a compressed air source can be fed to the first end body E1 and via which also compressed air can be diverted from the cavity RH to a compressed air sink, in particular into the environment via an outlet connection DA.
  • the valve arrangement is advantageously designed as a reversing valve arrangement, which alternatively connects the pneumatic actuator with either the input terminal DE or the output terminal DA.
  • the switching of the flow path is schematically indicated in the valve arrangement VA with arrows for the respective flow direction.
  • a switching rest position or switch-off position is shown, in which the pneumatic actuator is connected to the output terminal DA and a dashed line is a closed position drawn, in which the actuator to the input terminal DE and thus a compressed air source is connected.
  • the control device SE controls the valve arrangement and in the preferred embodiment as Umschaltventilan Aunt particular the change between one of the two alternative switching positions.
  • the control device can in particular make a control of the valve arrangement with a periodic clock signal which is subdivided into a switch-on time and a switch-off time within one clock period. Duration of the clock period or clock frequency is variable and the division of a clock period in on-time and off can be changed in an advantageous embodiment, for which GE GE controls BE1, BE2 can be provided on the housing, by means of which variable parameters are adjustable by the user.
  • An operating element can also generally be provided as an on-off switch or push-button.
  • control device SE and the valve assembly VA are fed via an electrical power supply, not shown, which may be provided by a connection cable as well as by an integrated battery or rechargeable battery unit. Electrical connections between controls, control device and Valve arrangement are indicated by simple lines. A connection to an external compressed air source is also not shown for clarity.
  • the control device can also be completely or partially displaced to a compressed air source, in particular a compressor, and connected via control lines to the preferably hand-held device.
  • the controller may include a programmable memory which preferably includes a plurality of operating programs having different parameter combinations (eg, frequency, on-off duty cycle, etc.) selectably.
  • the pneumatic actuator includes an inner spring assembly FI, which is designed as a compression spring and a spring force in the direction of Fig. 2 sketched elongated shape of the actuator causes.
  • the spring arrangement FI takes in the example, only a portion of the length of the actuator and acts between the two end bodies with the interposition of a body FZ, which can advantageously serve as a filler, which reduces the free volume within the cavity RH and thus the amount of for a certain internal pressure and a certain deformation of the membrane required compressed air advantageously significantly reduced.
  • the workpiece body surface facing away from the second end body E2 is, as indicated by a double arrow, movable in the longitudinal direction LR.
  • the movement of the end body E2 is transmitted via a thrust element, which is formed in the sketched embodiment on the filler FZ and a push rod DS, through the cavity RH and through the first end body E1 through to a tool head WK2, which on the workpiece surface WO facing the end the rod DS is arranged.
  • the rod DS is movably guided in sliding guides GF in the longitudinal direction LR and laterally supported.
  • the rod DS passes through the compressed air channel LK.
  • a sealing of the passage of the rod DS in the direction of the workpiece surface WO or the tool head WK2 can be formed by the sliding guide GF itself or by an additional sealing sleeve or, since the movements are only of small stroke, by a membrane.
  • the tool head WK2 contains in the example shown a working body AK2, which is screwed onto a mounting end of the push rod DS and by means of a lock nut KM, which also a support on the housing or on a guided through the housing portion of the first end body E1 in the rest position Fig. 2 causes is secured by countering.
  • the working body AK2 is tapered toward the workpiece surface WO in the example outlined, in order to apply a small surface element of the workpiece surface WO in a targeted manner.
  • Fig. 3 shows the device after Fig. 2 Sectionally with the area of the actuator in a working position with laterally bulged membrane ME and shortened distance between the two end body E1, E2.
  • the rest position of the movable end body E2 is indicated by a dashed line transverse to the longitudinal direction.
  • the tool head WK2 is lifted from the support on the first end body EK in the direction of the workpiece surface.
  • the movement of the tool head in the direction of the workpiece surface WO may be in the form of individual knocking movements between the in Fig. 2 sketched rest position and the in Fig. 3 sketched impact position with impinging on the workpiece surface WH working body AK2 and respective return to the rest position.
  • the valve arrangement is controlled via the control device so that in the working position Fig. 3 the tool head WK2 constantly from the rest position to Fig. 2 deflected and lifted from the end body E1 in the direction of the workpiece surface and with a small stroke around a center position oscillates in the longitudinal direction LR and thereby beats in a short sequence cyclically with the clock frequency on the workpiece surface WO.
  • the spring assembly FI pushes the movable end body E2 back into the in Fig. 2 sketched rest position in which the tool head WK2 rests against the resting stop formed by the end body E1 in the example outlined.
  • the longitudinal movement of the movable end body E2 to the tool head can also be carried out by the outside of the cavity and the first end body E1 guided thrust elements from the movable end body E2 towards the tool head, in which case a sealing of a passage is eliminated.
  • the arrangement of a thrust element within the cavity and the passage through the end body E1 is advantageous from the entire structure ago.
  • the working bodies AK in turn act with their workpiece surfaces facing the end faces on the workpiece surface.
  • the working body AK are movably mounted in a guide device AF of the tool head WK4 in the working direction AR4 and can be secured in a conventional manner in a holding part EH, which may be embodied for example as an elastomer block or membrane against failure from the tool head, even if the Working body AK are designed in an advantageous embodiment as pins.
  • the plurality of working bodies AK are movable independently of each other within the guides FK in the working direction AR4.
  • the guides can be designed in known per se for pen-shaped body designs.
  • the working bodies can also be used in openings of one or more membrane as guides.
  • a working position in which the impact surface of the hammer head HV of the tool surface WO maintains a distance which is larger by a small amount is as the length of the working body AK in the direction AR4, and wherein at substantially longitudinally fixed body GK of the device and the associated tool head WK4 the working body AK fly between the face of the hammer head HV and the workpiece surface WO in the direction of AR4 back and forth ,
  • the tool head WK4 is advantageously releasably attached to the body GK and interchangeable.
  • a clamping attachment in the form of a clamping device KE in particular a clamping sleeve may be provided, which is braced against the body and, for example, receives a clamping portion of the tool head WK4 radially clamped.
  • a clamping device KE for example screws KS can be provided.
  • the several working bodies AK in the tool arrangement according to Fig. 4 are preferably arranged in a line one behind the other. It can also be a tool assembly with only one relative to the hammer head in the working direction AR4 movably guided working body can be provided.
  • the striking surface of the hammer head HV is effective for all working bodies in different surface areas.
  • the hammer head HV can be tuned to the linear arrangement of several working body AK and for this purpose have an elongated in one direction and transverse thereto narrow striking surface.
  • guides or alignment aids between tool head WK4 and hammer head HV and / or body GK are provided.
  • the range of action of the impact surface of the hammer head on the workpiece surface WO facing away from the surfaces of the work body is visible to quickly detect any faults.
  • the tool head WK4 forms this in the example sketched a fork shape, which is bridged at the fork ends by the guide device FK.
  • the tool head is toward the workpiece surface as seen in the view Fig. 4 (B) clarified, screwed, whereby the machined surface area is particularly advantageous visible.
  • Fig. 5 shows an oblique view of the tool head WK4 dissolved in the device mold without hammer head HV.
  • the receiving space for the hammer head is designated AH.
  • the hammer head can in a drive device according to the type in Fig. 2 and Fig. 3 be arranged on the workpiece facing the end of the rod DS, wherein the actuator caused by the driving force acts by reducing the distance between the two end body directly as impact of the hammer head on the working body.
  • the working direction AR4 of the working body AK is directed parallel to the longitudinal direction LR of the actuator.
  • the working direction of the working body may be inclined against the longitudinal direction of the actuator, wherein the angle of inclination is advantageously not greater than 30 °.
  • Fig. 6 an example of this is sketched in the form of a tool head WK6 fastened to the main body of the device, with four working bodies AK arranged in a line in this case.
  • the Fig. 7 shows the tool head WK6 dissolved in the device representation. In particular from Fig. 7 It can be seen that the working direction AR6 is inclined relative to the longitudinal direction LR.
  • the inclination against the longitudinal direction LR is preferably the same for all workpieces AK.
  • the tool head WK6 after Fig. 6 and Fig. 7 is the plane in which the plurality of working body AK extend with the working direction AR6, inclined to the longitudinal direction LR.
  • working head WK8 the plane in which the plurality of arranged in a row working body AK with the working direction AR8, not inclined to the longitudinal direction LR, but includes the longitudinal direction. Within this plane, the working direction AR8 of the working body AK is inclined against the longitudinal direction.
  • the hammer heads are each tuned to different designs of tool heads. The hammer heads are this advantageously also easily replaceable attached.
  • Fig. 6 shows yet another, advantageous in a device according to the invention feature, according to which the compressed air required anyway for the operation of the actuator can also be used for cooling the tool assembly and the workpiece surface.
  • the exhaust air from the cavity of the actuator via the output port of the valve assembly and other flow-conducting devices can be supplied to the tool head and the work area on the workpiece surface.
  • cooling air channels KL are provided in the hammer head HS, which open advantageously next to acting as impact surfaces for the working body AK surface parts of the hammer head HS.
  • the drive movement of the actuator is directed in the direction of the workpiece surface and directly with the movement of a working head AK2 or acting on individually movable working body hammer head acts, the drive direction of the movable end body E2 is substantially equal to the working direction of the tool assembly, provides a preferred embodiment in that the actuator of the drive device exerts a drive movement substantially counter to the working direction of the tool arrangement and in this case under tension of a spring arrangement and against its spring force a movable part of the tool assembly against the working direction of the tool assembly shifts.
  • the spring assembly advantageously contains at least one, in a preferred embodiment, at least two in the direction of movement of the moving part of the tool assembly spaced disc springs (or special design diaphragm springs).
  • Fig. 9 shows an embodiment of such a preferred drive form, wherein the tool assembly a tool head in the manner of Fig. 6 and Fig. 7 contains. This is fastened, for example, in the manner described by means of a clamping device KE to the main body GK of the housing of the device.
  • a first plate spring TF1 and a second disc spring TF2 spaced apart in the longitudinal direction LR are arranged, which are held with their outer edges by a spacer sleeve DH stationary with respect to the base body.
  • the inner openings of the two disc springs are also held by a shank WS of the tool arrangement via a spacer sleeve or a corresponding device on the tool shank.
  • the tool shank is connected to the longitudinally movable second end body E2 of the actuator PA9.
  • the first end body E1 of the actuator is arranged away in the longitudinal direction of the workpiece surface WO and, for example, connected via a retaining ring HR to the base body of the device housing and with respect to this considered to be stationary.
  • a compressed air passage LK in which a compressed air passage LK is provided for supplying and discharging compressed air into the cavity of the actuator is a controllable valve arrangement VA and a control device SE arranged.
  • the cavity of the actuator is partially filled by a filler FZ.
  • the disc springs can be found in the Fig. 9 sketched initial state stress-free or biased away from the workpiece in the longitudinal direction.
  • a stop LA is provided on the base GK and / or on the movable part of the tool assembly, which prevents deformation of the disc springs TF from the outlined starting position in the direction of the workpiece.
  • the second end body E2 facing the workpiece in the longitudinal direction shifts away from the workpiece in the direction of the first end body E1 with simultaneous buckling of the flexible membrane ME of the actuator.
  • the displacement of the second end body E2 with the movable part of the tool assembly take place up to an upper reversal point at which the air supply from the compressed air source is broken off into the cavity and connected by switching the valve assembly of the cavity with the compressed air outlet of the valve assembly.
  • Compressed air flows out of the cavity of the actuator, thereby reducing the holding force of the actuator, and the movable part WS of the tool assembly, at the lower end of which the hammer head HS is disposed, and which is motion-coupled to the second end body E2 of the actuator, by the spring force of the actuator Disc springs is moved in the direction of the workpiece.
  • the return movement of the movable part WS of the tool assembly is usually fast and can in particular be faster than the movement of the movable part in tension of the spring assembly under the action of the driving force of the actuator during the supply of compressed air.
  • the movement of the movable part WS of the tool assembly under the action of the driving force of the actuator from the tool head WK6 or away from the workpiece surface is hereinafter also referred to as the first movement section, the movement of the movable part WS of the tool assembly in the direction of the tool head WK6 under the action of the restoring force Disc spring assembly referred to as the second movement section.
  • a sequence of a first movement section and a second movement section, the actuator and the movable part of the tool assembly back into the in Fig. 9 return the initial situation.
  • the control device SE, the valve assembly VA in cyclically successive clock periods with a switch-on, during which the first movement section takes place, and a switch-off, during which the second movement section, controls the clock frequency advantageously at least 50 Hz, in particular at least 100 Hz, preferably at least 200 Hz.
  • the clock frequency is variable.
  • Fig. 17 is such an oscillating movement in a diagram in which a deflection SW of the movable part of the tool arrangement of the in Fig. 9 sketched resting position plotted against the time t illustrated.
  • the oscillating movement with alternately successive first movement sections BE over a switch-on time TE and second movement sections BA over a switch-off time TA takes place between an upper reversal point UH and a lower reversal point UL, which are at different distances from the rest position designated S0.
  • the upper reversal point UH can reach a maximum deflection SM at most, the lower reversal point UL is in the extreme case at the rest position S0.
  • the lower reversal point UL from the rest position S0 and the upper reversal point UH is spaced from the maximum displacement SM and the stroke HU of the oscillating motion is advantageously at most 50% of the maximum permissible deflection SM.
  • the distance between the lower reversal point UL from the rest position S0 and the distance between the upper reversal point UH and the maximum permissible deflection SN which may be limited by a stop is advantageously at least 10% of the maximum displacement SM against the rest position S0 during cyclic operation.
  • the movement of the movable part WS of the tool arrangement typically does not run linearly over the time t and in the first movement sections BE as well as in the second movement sections BA
  • Time-dependence is typically different in first movement sections than in second movement sections.
  • an operating point of the movement which may be assumed, for example, as a mean deflection UM between UL and UH, by varying the duration of the switch-on time TE and / or the switch-off time TA.
  • the operating point is readily achieved starting from the rest position with the clocked mode without further action, especially if the movements during the switch-on and / or switch-off not linear, especially in monotonously curved diagram over time.
  • the operating point can also be varied by varying the pressure at the inlet of the valve arrangement, in particular by controlling a controllable compressed air source or by intervening in the cross sections of the flow paths.
  • Fig. 9 are as further advantageous features of a device according to the invention, the already mentioned air cooling via a channel KK illustrated by the movable part WS of the tool assembly, which continues in the hammer head HS.
  • the cooling air which may advantageously be at least partially out of the cavity of the actuator during its off-time air is passed through channels, not shown channels of recesses of the retaining ring HR in the space between the actuator and the housing wall of the housing body.
  • Fig. 10 are essential parts of the device after Fig. 9 , which are connected to the base body or are also movable relative to this in the longitudinal direction, shown without housing in an oblique view.
  • the first end body E1 of the actuator is connected via a retaining ring HR to the housing base body of the device, in particular screwed.
  • the movable end body E2 of the actuator is under clamping of the disc springs TF1, TF2 to the Edges of the inner recesses of the disc springs coupled to the movable part WS of the tool assembly, said movable part of the tool assembly can form in particular a compressive and tensile shank RA.
  • a valve arrangement VA is shown with a plurality of individual valves.
  • a drive device with a working direction of an actuator, which is directed under the action of the driving force of a drive device away from the workpiece surface and associated with the tension of a spring assembly and with the movement of a movable part of the tool assembly in the direction of the workpiece surface under the action the tensioned previously by the drive means spring arrangement after reduction or elimination of the driving force is also advantageously feasible with other types of drives.
  • a drive device can be used with a lower drive speed when tensioning the spring arrangement, as long as the driving force is sufficient for tensioning the spring arrangement. The favorable for the machining of the workpiece surface fast movement to the workpiece surface is then conveniently ensured by the spring arrangement.
  • the structure of the device with the spring arrangement is also fixed with a directly on the moving part of the tool assembly and thus firmly to the movement of the movable part the tool assembly and the second end body coupled working body assembly, for example, as in Fig. 2 or Fig. 3 , possible instead of the indirect loading of the workpiece surface on the movable between the hammer head HS and the workpiece surface, in particular also relative to the hammer head HS movable working body.
  • disc springs TF1, TF2 in the spring arrangement is of particular advantage for a self-centering guidance of the movable part of the tool assembly and the movable end body E2 of the actuator.
  • the disc springs are fitted with their outer edges in the inner cross section of the base body and thus not only fixed in the longitudinal direction with insertion of the spacer sleeve, but also directly or indirectly supported transversely to the longitudinal direction of the inner wall of the body GK.
  • the movable part of the tool assembly is fitted in the inner openings of the disc springs and thus centered transversely to the longitudinal direction.
  • the two longitudinally spaced disc springs TF1, TF2 results in a given by the distance base over which any occurring - tilting moments are safely intercepted on the shaft of the movable part of the tool assembly.
  • the hammer head HS or another type of hammer head to be used for another tool head is advantageously fastened detachably to the shank of the movable part of the tool arrangement with little effort.
  • the movable part WS of the tool arrangement can also be viewed in whole or in part as part of the drive device and associated with it.
  • the use of the pneumatic actuator described advantageously allows a slender, longitudinally elongated design of the body GK of the device, which allows in the longitudinal region of the actuator and / or the movable part of the tool assembly to provide a grip position GR1, where the housing is substantially tubular with circular cross-section is executed and due to the small transverse dimensions of the actuator has an outer diameter of typically between 40 and 80 mm, which usually allows embracing the tubular housing portion with a user's hand.
  • this gripping position designated GR1 is provided on a housing sleeve GH of a gripping part GG of the housing, wherein this gripping part GG of the housing is displaceable relative to the main body GK in the longitudinal direction counter to the restoring force of a spring arrangement FA preferably arranged in the interior of the housing.
  • a spring arrangement FA preferably arranged in the interior of the housing.
  • FIG. 11 (A) the rest position of the handle housing part GG is shown relative to the base GK of the housing.
  • the tubular housing section with the grip position GR1 is advantageously designed as a cladding tube around the main body GK of the housing.
  • a gripping position is provided on the side of the actuator facing away from the workpiece surface WO on the housing, on the housing handle part GG, a gripping position being provided in the gripping part GG of the housing which is displaceable relative to the main body Fig. 11 designated GR2.
  • a gripping position is provided on the side of the actuator facing away from the workpiece surface WO on the housing, on the housing handle part GG, a gripping position being provided in the gripping part GG of the housing which is displaceable relative to the main body Fig. 11 designated GR2.
  • Fig. 11 provided on the housing handle part GG a handle HG2.
  • the possibility of relative displacement of a handle housing part GG relative to a housing main body GK of the device against a restoring force of a spring assembly FA can be used in an advantageous development for a safety function in such a way that, for example, switching on the drive means, in the example of the pneumatic actuator so a Supplying compressed air in the actuator, only possible if a minimum displacement corresponding to a minimum force of the pressing of the device is given to the workpiece surface.
  • FIG. 12 schematically another structure of a device according to the invention is outlined with respect to the relative arrangement of the various components, in which case a handle position remote from the workpiece is not provided in extension of the actuator, but laterally projecting away as handle position GQ.
  • Fig. 13 is a further advantageous embodiment of a combination of a spring arrangement with an actuator of in Fig. 1 outlined manner, with in Fig. 14 a section of the tool assembly facing away from the first end body E13 is shown with the arranged in this spring assembly F13.
  • the end body E13 is connected to the housing body GK13 firmly connected. Similar to the execution of an actuator of the type FIGS. 2 and 3 is guided by the end body E13 a thrust element through the end body and the cavity of the actuator to the tool assembly facing movable end body E23 and connected thereto.
  • the pusher element advantageously again forms in the cavity a filling body FK13 which reduces the free gas volume of the cavity and in the region of the first end body E13 a push rod DS13.
  • the thrust element has a bore LK or the like in the longitudinal direction. This serves as a part of the channel for supplying and discharging compressed air into and out of the cavity of the actuator.
  • the longitudinal bore LK In the region of the filler cross channels are formed to the longitudinal bore LK, which form a connection in the cavity in the membrane ME with low flow resistance.
  • a movable part of a tool assembly is similar to the embodiment according to Fig. 9 and Fig. 10 connected to the movable end body E23.
  • the movable part of the tool assembly can as in Example after Fig. 2 and Fig. 3 directly with a working body or as in Fig. 13 be associated with a striker HS13, which in turn similar to the comments Fig. 4 to Fig. 11 strikes with a striking surface on a relative to the base body GK and to the striking body HS13 in a working direction AR13 movable working body AK13.
  • a working body is in Fig. 13 presented a kind of chisel.
  • the movable part of the tool assembly is supported in a tubular portion by means of a co-moving slider GLA transversely to the longitudinal direction LR and guided in its movement in the longitudinal direction.
  • the pressure element is at the same time at the passage through the first end body and / or in a region facing away from the cavity after the first end body transversely supported to the longitudinal direction in a second guide and guided, so that there is a good support against any tilting moments transverse to the longitudinal direction by the guides spaced far in the longitudinal direction.
  • the spring assembly F13 is supported on the one hand against the housing base body and the other against the thrust element, for which the thrust element is connected in the example shown with a support body GLB, which can also form the second guide for the movement of the thrust element in the longitudinal direction.
  • the spring arrangement is in the example outlined as in particular Fig. 14 is formed by a plate spring assembly, which is formed for a lower spring constant and / or in particular for a larger stroke of the oscillating motion during operation of the device by a column of a plurality of alternately oppositely oriented disc springs.
  • a support of the thrust element transversely to the longitudinal direction can also as Fig. 9 and Fig. 10 be described by a centering function of the spring arrangement.
  • the spring arrangement is located in the in FIGS. 13 and 14 sketched embodiment advantageously on the one hand outside the cavity of the actuator, on the other hand in a region which does not need to be sealed against the cavity of the actuator and is preferably substantially pressure-balanced with the cavity of the actuator. In this way, advantageously, a pressure-tight guide between longitudinally relative to each other moving parts can be avoided.
  • the space containing the spring assembly is statically sealed against the environment.
  • the arrangement of the spring arrangement outside the cavity of the actuator advantageously allows a simple variation of the spring arrangement when using the same actuators.
  • the channel LK in the thrust element can also be provided that the compressed air between the passage in the first end body E13 and the thrust element, which is then at least partially radially spaced from the passage in the end body done.
  • the handle assembly HG13 can again be displaceable relative to the housing base body against a spring force in the direction of the workpiece.
  • FIGS. 13 and 14 should also illustrate that individual components are put together differently in different ways can be and the invention is not limited to the example outlined.
  • Fig. 15 shows in an oblique view with partially cut tubular housing RG a device PH in the manner of a compressed air hammer used in the construction sector, in which a bit MK is arranged as a tool on a tool head WK15.
  • Fig. 16 shows a section in a plane through the longitudinal axis of the device.
  • a handle HK At the upper end of a handle HK is arranged, on which two handles GP are attached and which may contain various components, in particular a valve assembly, a control device and controls.
  • compressed air connections D1, D2 are provided at the head HK compressed air connections D1, D2 are provided.
  • the device head HK is connected to the tool head WK15 on the one hand via a stable, in particular tubular housing RG and advantageously additionally via a plurality of rods or rods GS arranged within the tubular housing.
  • a pneumatic actuator AA of the type described which is fixed with a first, fixed relative to the housing end body E1A in the region of the device head HK.
  • the cavity of the actuator AA surrounded by the flexible membrane ME is connected via a channel KA leading through the first end body E1A to a valve arrangement arranged in the device head HK.
  • the control of the valve arrangement and the thereby determined admission of the actuator AA with compressed air from a compressed air source via one of the compressed air input terminals D1 or D2 can be done in one of the ways already described, with a variable clock frequency.
  • the second, with respect to the device head HK and the housing in the longitudinal direction of the device displaceable second end body E2A of the actuator AA, which faces away from the head HK in the longitudinal direction of the device is connected to a connecting body VS.
  • pressure rods SH lead in the longitudinal direction of the device to a striking body HT and couple a longitudinal movement of the connecting body VS firmly to a longitudinal movement of the impactor HT.
  • the impactor HT is guided longitudinally displaceably in an end piece ES of the housing in a bearing HL.
  • the hammer head HT may have recesses or openings for the housing-fixed rods GS and additionally be guided on these and / or on the inner wall of the tubular housing RG.
  • the connecting body VS may have recesses or openings for the housing-fixed rods GS and guided displaceably in the longitudinal direction on these and / or on the inner wall of the tubular housing RG and be supported transversely to the longitudinal direction.
  • the various possible bearing guides for the connecting body VS and / or for the impactor HT can also be designed individually or as a plurality of compressed air bearings, which is advantageous due to the already given supply of compressed air to the device and keeps the bearing friction and bearing wear particularly low. Corresponding compressed air supply lines to the individual bearing points are not shown for clarity.
  • the further actuator AZ is fixedly mounted with respect to the housing with a first end body E1Z, for which in the example sketched a fixing body FS is fixedly arranged within the tubular housing RG and is stably supported against displacement in the longitudinal direction. Such support can be given in particular via the rods GS against the device head HK.
  • the second, relative to the housing movable end body E2Z of the second actuator AZ is connected to the connecting body VS and coupled with its longitudinal movement.
  • the second actuator AZ is via a compressed air channel KZ in its first end body E1Z and a in Fig. 15 and Fig. 16 concealed compressed air line connected to the device head HK and a compressed air source.
  • the second actuator AZ is advantageously acted upon by a constant, optionally variable adjustable pressure and therefore acts in the clocked variable loading of the first actuator AA as a spring. Depending on the choice of typically during a work process constant pressure in the supply line for the second actuator AZ this can act as a soft or a hard spring.
  • the rods or rods SH are from the connecting body VS through the fastening body or past this led to the impactor HAT.
  • the actuator lengths are matched to one another and the pressure in the second actuator AZ is selected so that the second actuator is always under a bias voltage which is changed with compressed air in time with the first actuator AA.
  • the striking body HT is moved away from the bit tool MK, thereby increasing the spring tension of the second actuator AZ.
  • the two actuators AA and AZ can be the same size or different.
  • the chisel tool MK which is guided longitudinally displaceable in the tool head WK15, perform an oscillating movement, without striking a limit in the longitudinal direction.
  • the impactor HT acts strikingly on the tool bit MK and is predominantly lifted from its face facing the impactor.
  • the compressed air for the second actuator AZ on the one hand and the first actuator AA on the other hand can be supplied via separate compressed air connections D1, D2.
  • the variable setting of a pressure for the second actuator AZ can be made either in the device head HK or at a compressed air source spaced therefrom.
  • only a compressed air connection can be provided, which is divided within the head HK in a supply for the second actuator AZ with a substantially constant, optionally variably specifiable pressure, and a supply line to the valve assembly in the device head for pulsed loading of the first actuator AA with compressed air.
  • the control of the valve arrangement can be effected both by a control device and operating elements in the device head HK and by arranging a control device and / or operating elements at a position spaced from the device, in particular in the case of a compressed air source.
  • operating elements B51, B52, B53 are shown on the device head HK, wherein, for example, the operating element B51 can be provided for a change in the clock frequency of the clocked activation of the first actuator AA via the valve arrangement and the operating element B52 the duty cycle of switch-on time to switch-off time of the supply determined by compressed air in the first actuator.
  • a third operating element B53 can predetermine the pressure for the second actuator AZ, which can be viewed as constant, compared to the clocked activation of the first actuator.
  • the pressure in the second actuator AZ is tpyically not constant in the pulsed control of the first actuator AA and varies with the displacement of the connecting body VS in the longitudinal direction, as by the relatively long compressed air supply from the head HK to the channel KZ in the first end body E1Z a pressure compensation is not complete takes place.
  • displaceable housing handle part shock and / or vibration damping between the two housing parts may be provided.
  • the disc springs including their special designs, in particular diaphragm springs, other spring arrangements can be provided with appropriate effect.
  • the working position of the tool on the workpiece can be illuminated, for example by an LED in the Berich the tool head.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Actuator (AREA)
EP08760653.9A 2007-06-30 2008-06-06 Vorrichtung zur bearbeitung von werkstücken Not-in-force EP2162250B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007030544A DE102007030544A1 (de) 2007-06-30 2007-06-30 Vorrichtung zur Bearbeitung von Werkstücken
PCT/EP2008/057081 WO2009003790A1 (de) 2007-06-30 2008-06-06 Vorrichtung zur bearbeitung von werkstücken

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EP2162250B1 true EP2162250B1 (de) 2018-08-29

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DE102009001284B4 (de) * 2008-03-04 2019-11-21 Peter Gerster Vorrichtung und Verfahren zur Behandlung von metallischen Oberflächen mittels eines motorisch angetriebenen Schlagwerkzeugs
DE102012005803A1 (de) * 2012-03-21 2013-09-26 Wacker Neuson Produktion GmbH & Co. KG Bohr-und/oder Schlaghammer mit belastungsabhängiger Anpassung der Schlagzahl
CN105158895B (zh) * 2015-10-13 2018-04-10 中国科学院国家天文台南京天文光学技术研究所 用于天文望远镜镜面位置调整的微位移促动器
DE102017121668A1 (de) 2017-09-19 2019-03-21 Erwin Schmucker Schlagwerkzeug zur Bearbeitung von Werkstücken

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CN201921963U (zh) 2011-08-10
EP2162250A1 (de) 2010-03-17
DE102007030544A1 (de) 2009-01-08
WO2009003790A1 (de) 2009-01-08

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