WO2009003790A1 - Dispositif de traitement de pièces - Google Patents

Dispositif de traitement de pièces Download PDF

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Publication number
WO2009003790A1
WO2009003790A1 PCT/EP2008/057081 EP2008057081W WO2009003790A1 WO 2009003790 A1 WO2009003790 A1 WO 2009003790A1 EP 2008057081 W EP2008057081 W EP 2008057081W WO 2009003790 A1 WO2009003790 A1 WO 2009003790A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuator
tool
workpiece
movement
spring
Prior art date
Application number
PCT/EP2008/057081
Other languages
German (de)
English (en)
Inventor
Erwin Schmucker
Original Assignee
Erwin Schmucker
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 Erwin Schmucker filed Critical Erwin Schmucker
Priority to EP08760653.9A priority Critical patent/EP2162250B1/fr
Priority to CN2008900000739U priority patent/CN201921963U/zh
Publication of WO2009003790A1 publication Critical patent/WO2009003790A1/fr

Links

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 for machining workpieces, in particular for beating machining, such.
  • a device for machining workpieces in particular for beating machining, such.
  • for the post-processing of metallic surfaces in welded structures for the removal or penetration of surfaces of workpieces, etc., which can be understood in a wide sense Werkstük- in a floor area or a part of the building.
  • UIT Ultrasonic Impact Treatment
  • an ultrasonic 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, US 6289736, US 6338765 or US 6458225.
  • UIT Ultrasonic Impact Treatment
  • the strength of the welds can be significantly improved.
  • the device is unwieldy and expensive.
  • the present invention has for its object to provide an improved device for machining workpieces, in particular for beating processing of workpiece surfaces.
  • actuators with a pressurizable, compressed air, elongated hollow body, which between two in its longitudinal direction spaced stood end bodies laterally closed by the tubular flexible membrane and the supply of compressed air into the cavity with lateral expansion of the membrane shortens the mutual distance between the two end body, 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 the company Festo. The operating 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 process 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 durable without damage ,
  • 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.
  • 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 arrangement contains at least one tool part driven by the actuator, in particular its end body movable relative to the housing of the device, and movable relative to a housing main body.
  • the tool assembly additionally contains at least one stationary with respect to the housing part, which is advantageously for replacement of a tool releasably connected to 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 a plurality of working bodies relative to the housing Base 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 for the guidance of the working body known solutions, in particular from the aforementioned UIT method known solutions can be used.
  • 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-operated 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 a 2-way switching valves, which are switched periodically with a preferably variably predeterminable clock frequency and in a first switching state for a first switching duration (on) initiate compressed air from a compressed air source into the cavity of the actuator and in a second Switching state for a second switching duration (switch-off time) Divert air from the hollow space.
  • the duty cycle between the first and second switching time is advantageously variable. With the variation of the duty cycle advantageously the time-averaged pressure in the cavity and thus an operating point of the actuator can be adjusted variably.
  • 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 may also be adjustable depending on the pressure of the compressed air source or at the input of the valve arrangement and by its 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 base 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 of the actuator facing the workpiece is fixedly connected to the housing base body and the end body remote from the workpiece is movable relative to the housing body, advantageously one within the cavity or laterally of the flexible membrane of the movable End body provided in the direction of the workpiece surface continuous thrust element, which converts the movement of the movable end body in 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 arrangement can take place more quickly in the second movement section than in the first movement section, whereby the impact force of a striking action of the tool arrangement at the end of the second movement section can be stronger on a workpiece than on the direct action of the driving force of the actuator 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 disc spring is advantageously fixed with its outer edge in the housing main 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 can 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 means 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 Bethebszupartyn.
  • 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. In order to reduce the flow resistance in the valves, the parallel connection of several valves can be advantageously 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 control device is programmable and / or the control device contains 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. Preference is given to 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 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 is advantageously carried out cyclically with a typically dependent on the size and application of the working device 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 may be different lengths and turn-on and / or turn-off advantageously advantageous adjustable.
  • the clock frequency is advantageously so high or the switch-off time so short that the tool assembly does not return to its rest position during the switch-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.
  • 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 ⁇ 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 the inflow and outflow of compressed air are not constant over time, and advantageously an equilibrium state is established as the operating point, which can advantageously be changed by the user, inter alia, via the change of the switch-on time and / or switch-off time and / or clock frequency.
  • 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 striking working movement of the tool arrangement, 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. 3 shows the device according to FIG. 2 in working position
  • FIG. 5 is a tool head to Fig. 4 in an oblique view
  • FIG. 7 shows a tool head to FIG. 6, FIG.
  • FIG. 10 is an oblique view of parts of the apparatus of FIG. 8,
  • Fig. 11 is an illustration of a device with movable
  • the handle part The handle part,
  • FIG. 16 is a longitudinal section through the apparatus of FIG. 15,
  • Fig. 17 is an illustration of a clocked oscillating movement.
  • FIG. 1 shows a sectional view of a pneumatic actuator in which a cavity RH between two end bodies E1, E2 spaced apart in a longitudinal direction LR is closed laterally by a flexible membrane ME.
  • the flexible membrane is typically tubular and anchored in both end bodies, for example clamped.
  • the anchoring is indicated in FIG. 1, 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 into the cavity RH inserted or under overpressure 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.
  • 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 Fig. 1st a working position of the actuator is shown.
  • a rest position of the actuator with substantially parallel to the longitudinal direction LR membrane ME and in the right half of Fig. 1st a working position of the actuator is shown.
  • the flexible membrane ME bulges out laterally away from the central longitudinal axis SA.
  • a tension-resistant fabric with obliquely running crossed fibers embedded in the membrane ME 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 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.
  • the right half of FIG. arched diaphragm of the second end body E2 drawn on the first end body E1 out. With such a displacement, a drive force can be generated in the longitudinal direction by the actuator and the actuator can thus be used in a drive device.
  • a provision of the end body E2 in the rest position after elimination of the excess pressure in the cavity RH can be done for example by the own elasticity of the membrane, by an outgoing load 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 outlined in Fig. 1 are available in different versions, for example as Fluidic Muscle from Festo.
  • FIG. 2 shows a first advantageous embodiment of a device for producing a beating or knocking movement using a pneumatic actuator PA2 of the type outlined in FIG.
  • 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 Umschaltventilanowski note 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 and division of a clock period in switch-on and switch-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 Fl, which is designed as a compression spring and causes a spring force in the direction of the outlined in Fig. 2 elongated shape of the actuator.
  • the spring arrangement Fl 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 push 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 of the rod DS is arranged.
  • the rod DS is movably guided in sliding guides GF in the longitudinal direction LR and laterally removed. supports.
  • the rod DS passes through the compressed air channel LK.
  • a seal of the implementation 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 gasket or, since the movements are only a small stroke, by a membrane.
  • the tool head WK2 includes in the example shown a working body AK2, which 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 hupp after Fig. 2 causes, is secured by locking.
  • 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 of Fig. 2 fragmentary 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 can take place in the form of individual knocking movements between the rest position sketched in FIG. 2 and the impact position sketched in FIG. 3 with working body AK2 impinging on the workpiece surface WO and respective return to the rest position.
  • the valve arrangement is controlled by the control device such that in the working position according to FIG. 3 the tool head WK2 is constantly deflected from the rest position according to FIG. 2 and lifted off the end body E1 in the direction of the workpiece surface and with a small stroke around a center Position in the longitudinal direction LR oscillates and cyclically hits the workpiece surface WO in a short sequence with the clock frequency.
  • the spring assembly Fl presses the movable end body E2 again in the sketched in Fig. 2 rest position in which the tool head WK2 rests against the resting stop formed by the end body E1 in the example.
  • 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 body AK2 is fixedly coupled in its longitudinal movement with the movement of the movable end body E2
  • the working bodies AK in turn act with their workpiece surfaces facing the end faces on the workpiece surface.
  • the working bodies AK are displaceably movably mounted in a guide device AF of the tool head WK4 in the working direction AR4 and can be secured against failure from the tool head in a manner known per se in a holding part EH, which can be embodied for example as an elastomer block or membrane when 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 of AR4, and wherein at substantially longitudinally fixed body GK of the device and the associated tool head WK4 the working body AK between the face of the hammer head HV and the workpiece surface WO in the direction of AR4 out and fly her.
  • 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 clamped 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 plurality of working bodies AK in the tool arrangement according to FIG. 4 are preferably arranged in a line one behind the other. It is also possible to provide a tool arrangement with only one working body movably guided in the working direction AR4 relative to the hammer head.
  • the striking surface of the hammer head HV is effective for all working bodies in different surface areas.
  • the hammer head HV can be matched to the linear arrangement of a plurality of working bodies AK and for this purpose have an impact area that is elongated in one direction and narrow across it.
  • guides or alignment aids between tool head WK4 and hammer head HV and / or body GK are provided.
  • the area of action of the impact surface of the hammer head on the surfaces of the workpieces facing away from the workpiece surface WO can be viewed in order to quickly detect possible disturbances.
  • 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 in the view of 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 in dissolved from the device form without hammer head HV.
  • the recording room for the ham- mer head is designated AH.
  • the hammer head can be arranged at the workpiece facing the end of the rod DS in a drive device of the type shown in FIG. 2, wherein the drive force caused by the actuator by reducing the distance between the two end body directly as impact of the hammer head on the Working body acts.
  • the working direction AR4 of the working bodies 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 is an example of this in the form of a body attached to the base of the device tool head WK6 sketched in this case four arranged in a line working bodies AK.
  • FIG. 7 shows the tool head WK6 in the representation released by the device.
  • the working direction AR6 is inclined to the longitudinal direction LR.
  • the inclination against the longitudinal direction LR is preferably the same for all workpieces AK.
  • the plane in which the plurality of working body AK extend with the working direction AR6, inclined against the longitudinal direction LR In contrast, in the example of the working head WK8 shown in FIG. 8, the plane in which the plurality of working bodies AK arranged in a row lie with the working direction AR8 is 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 piece 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 in addition 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 that the actuator of the drive means a drive movement substantially opposite to the direction of the tool assembly exerts and in this case under tension of a spring assembly 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 in which the tool assembly includes a tool head of the type of Fig. 6 and Fig. 7. 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 disposed away in the longitudinal direction of the workpiece surface WO and, for example, connected via a retaining ring HR to the main body of the device housing and with respect to this considered to be stationary.
  • 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 disk springs can be tension-free or longitudinally biased away from the workpiece.
  • 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 plate springs TF1, TF2 deformed, in particular in the direction of the tool head bulging away against the spring tension of the plate springs, which increases rapidly with increasing deformation over short displacement distances.
  • the displacement of the second end body E2 with the movable part of the tool assembly takes 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 arrangement 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 return referred to by force of the disc spring assembly as the second movement section.
  • a sequence of a first movement section and a second movement section can return the actuator and the movable part of the tool arrangement back into the starting position sketched in FIG. 9.
  • the control device SE to have the valve arrangement VA in cyclically successive clock periods with a switch-on time during which the first movement section takes place and a switch-off time during which the second movement section takes place, drives, wherein the clock frequency is advantageously at least 50 Hz, in particular at least 100 Hz, preferably at least 200 Hz.
  • the clock frequency can be variable.
  • the movable part of the tool assembly reached during the second movement section only a lower reversal point, from which by initiating the next turn-on of the actuator with associated first movement section again a movement of the movable part of the WS Tool arrangement away from the workpiece surface up to an upper reversal point in the switching of the valve assembly to the output terminal for the duration of a turn-off takes place.
  • the movable part WS of the tool assembly then oscillates between two reversed points deflected to different degrees from the rest position sketched in FIG. 9.
  • FIG. 17 illustrates such an oscillating movement in a diagram in which a deflection SW of the movable part of the tool arrangement from the rest position sketched in FIG. 9 over time t is plotted.
  • 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 SO.
  • 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 SO.
  • the lower reversal point UL from the rest position SO 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 SO and the distance between the upper reversal point UH and the maximum permissible deflection SN which can be limited by a stop are advantageously at least 10% of the maximum displacement SM against the rest position SO in clock mode.
  • 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 the already mentioned air cooling via a channel KK are illustrated by the movable part WS of the tool assembly, which continues in the hammer head HS as further advantageous features of a device according to the invention.
  • the cooling air which may advantageously be at least partially out of the cavity of the actuator during its off-time flowing 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 of 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 away from the workpiece surface under the action of the driving force of a drive device and associated with the tension of a spring assembly and under with the movement of a movable part of the tool assembly in the direction of the workpiece surface the action of the previously tensioned 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 processing of the workpiece surface fast movement on 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 workpiece assembly coupled to the tool assembly and the second end body for example, as in Fig. 2 or Fig. 3, possible instead of the indirect loading of the workpiece surface on the movable between Ham- head HS and workpiece surface, especially 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.
  • FIG. 11 further features which are advantageous for devices according to the invention are described, which in some cases can already be taken from the sketch according to FIG. 9.
  • 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 handle position designated GR1 is provided on a housing sleeve GH of a handle part GG of the housing, this handle part GG of the housing being displaceable relative to the base body GK in the longitudinal direction against the return 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.
  • the rest position of the handle housing part GG is shown relative to the main body 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 at the side of the actuator facing away from the workpiece surface WO on the housing, with a gripping position GG of the housing which is displaceable relative to the main body on the housing handle part GG, which is designated GR2 in FIG.
  • a handle HG2 is provided on the housing lever GG.
  • FIG. 12 diagrammatically shows a further construction of a device according to the invention with regard to the relative arrangement of the various components, wherein here a handle position facing away from the workpiece is not provided as an extension of the actuator but as a grip position GQ extending laterally away.
  • FIG. 13 shows a further advantageous embodiment of a combination of a spring arrangement with an actuator of the type outlined in FIG. 1, FIG. 14 showing a section of the first end body E13 facing away from the tool arrangement with the spring arrangement F13 arranged thereon.
  • the end body E13 is connected to the housing body GK13 firmly connected.
  • a thrust element is guided by the end body E13 through the end body and the cavity of the actuator to the movable end body E23 facing the tool assembly 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 connected to the movable end body E23 similar to the embodiment of FIGS. 9 and 10.
  • the movable part of the tool arrangement can, as in the example according to FIGS. 2 and 3, be connected directly to a working body or, as in FIG. 13, to a striker HS13, which in turn is similar to the embodiments according to FIGS. 4 to 11 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 suggests.
  • a working body a kind of chisel is shown in Fig. 13.
  • 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 arrangement F13 is supported on the one hand against the housing base body and on the other hand against the thrust element, for which the thrust element is connected in the example outlined with a support body GLB, which can also form the second guide for the movement of the thrust element in the longitudinal direction at the same time.
  • the spring arrangement is shown in the example shown as in particular from Fig. 14 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 cup springs.
  • a support of the thrust element transversely to the longitudinal direction can also be provided as described for FIG. 9 and FIG. 10 by a centering function of the spring arrangement.
  • the spring arrangement is 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 is. 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 are also intended to illustrate that individual components are combined differently in different ways. can be and the invention is not limited to the example outlined.
  • Fig. 15 shows 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 grip head HK is arranged, on which two handles GP are fastened and which can contain various components, in particular a valve arrangement, a control device and operating elements.
  • 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 described type is arranged as the actuator element, which is fastened to a first end body E1 A fixed relative to the housing 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 E1 A to a valve arrangement arranged in the device head HK.
  • the actuation of the valve arrangement and the thereby determined loading 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, in particular with an optionally 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.
  • Compressive rods SH lead from the connecting element VS in the longitudinal direction of the device to a striking element HT and firmly couple a longitudinal movement of the connecting element VS to a longitudinal movement of the striking element HT.
  • the impactor HT is guided longitudinally displaceably in an end piece ES of the housing in a bearing HL.
  • the hammer head HT can have recesses or openings for the housing-fixed rods GS and can additionally be guided on these and / or on the inner wall of the tubular housing RG.
  • the connecting body VS have recesses or openings for the housing-fixed rods GS and guided on these and / or on the inner wall of the tubular housing RG slidable in the longitudinal direction 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 fastened fixedly with respect to the housing with a first end body E1Z, for which, in the example shown, a fastening body FS is arranged stationarily within the tubular housing RG and 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 end body E2Z of the second actuator AZ which is movable relative to the housing, is connected to the connecting body VS and coupled with its longitudinal movement.
  • the second actuator AZ is connected via a compressed air channel KZ in its first end body E1Z and a compressed air line hidden in FIG. 15 and FIG. 16 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 impact force depends inter alia on the pressure in the second actuator AZ and can be influenced by the adjustment of this pressure.
  • 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 carried out either in the device head HK or in a compressed-air source which is at a distance from it.
  • 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 drive 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 the supply of compressed air in the first actuator determined.
  • 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 typically not constant during the pulsed activation of the first actuator AA and varies with the displacement of the connecting body VS in the longitudinal direction, since the comparatively long compressed air supply line from the device head HK to the channel KZ in the first end body E1Z a pressure equalization does not take place completely.
  • the clocked actuator in the handle and serving as a pneumatic spring further hollow body AZ is arranged facing the tool, in other embodiments, the positions can also be reversed, in which case the clocked actuator the impact movement and the further actuator causes the return movement.
  • the working position of the tool on the workpiece can be illuminated, for example, by an LED in the Berich of 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)

Abstract

L'invention concerne un dispositif de traitement de la surface de pièces, en particulier la surface métallique de structures soudées, par exemple de cordons de soudure ou dans le domaine de la construction, avec une nouvelle structure dotée d'un actionneur pneumatique dans un dispositif d'entraînement et/ou d'un système de ressort (FI) tendu par un système d'entraînement, pour appliquer une force de travail.
PCT/EP2008/057081 2007-06-30 2008-06-06 Dispositif de traitement de pièces WO2009003790A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP08760653.9A EP2162250B1 (fr) 2007-06-30 2008-06-06 Dispositif de traitement de pièces
CN2008900000739U CN201921963U (zh) 2007-06-30 2008-06-06 用于加工工件的装置

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
DE102007030544.5 2007-06-30

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WO2009003790A1 true WO2009003790A1 (fr) 2009-01-08

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EP (1) EP2162250B1 (fr)
CN (1) CN201921963U (fr)
DE (1) DE102007030544A1 (fr)
WO (1) WO2009003790A1 (fr)

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CN105158895A (zh) * 2015-10-13 2015-12-16 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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DE102012005803A1 (de) * 2012-03-21 2013-09-26 Wacker Neuson Produktion GmbH & Co. KG Bohr-und/oder Schlaghammer mit belastungsabhängiger Anpassung der Schlagzahl

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US20070040476A1 (en) * 2005-08-19 2007-02-22 U.I.T., Llc Oscillating system and tool for ultrasonic impact treatment

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105158895A (zh) * 2015-10-13 2015-12-16 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
WO2019057746A1 (fr) 2017-09-19 2019-03-28 Pitec Deutschland Gmbh Outil à percussion servant à l'usinage de pièces

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

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