EP3389934B1 - Machine-outil portative a percussion - Google Patents

Machine-outil portative a percussion Download PDF

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Publication number
EP3389934B1
EP3389934B1 EP16809722.8A EP16809722A EP3389934B1 EP 3389934 B1 EP3389934 B1 EP 3389934B1 EP 16809722 A EP16809722 A EP 16809722A EP 3389934 B1 EP3389934 B1 EP 3389934B1
Authority
EP
European Patent Office
Prior art keywords
striker
channel opening
channel
pneumatic chamber
machine tool
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.)
Active
Application number
EP16809722.8A
Other languages
German (de)
English (en)
Other versions
EP3389934A1 (fr
Inventor
Markus Hartmann
Rory Britz
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.)
Hilti AG
Original Assignee
Hilti AG
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 EP3389934A1 publication Critical patent/EP3389934A1/fr
Application granted granted Critical
Publication of EP3389934B1 publication Critical patent/EP3389934B1/fr
Active legal-status Critical Current
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • 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
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0019—Guide-sleeves
    • 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
    • B25D2250/035—Bleeding holes, e.g. in piston guide-sleeves
    • 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
    • B25D2250/131—Idling mode of tools
    • 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
    • B25D2250/185—Pressure equalising means between sealed chambers
    • 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
    • B25D2250/231—Sleeve details
    • 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
    • B25D2250/345—Use of o-rings
    • 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
    • B25D2250/365—Use of seals

Definitions

  • the present invention relates to a striking machine tool, in particular a hand-held pneumatic hammer drill and a hand-held pneumatic electric chisel according to the preamble of claim 1 and as from US 2002/108766 known.
  • a hand-held pneumatic hammer drill has a pneumatic percussion driven by a motor.
  • a pneumatic chamber forms an air spring which couples a racket to an exciter moved by the motor.
  • the hammer mechanism is deactivated if the user does not apply pressure to the tool to protect the hammer from excessive loading. As soon as the user presses the hammer to the tool, the hammer mechanism starts to work again. In high-performance machines, the guiding of the hammer when re-pressing proves to be difficult to control.
  • a beating hand tool has a tool holder for holding a striking tool on a work axis, an electric motor and a striking mechanism.
  • the striking mechanism has a pathogen in succession, a pneumatic chamber, a racket, an intermediate chamber and an anvil.
  • a closed channel connects a first channel opening in the pneumatic chamber and a second channel opening in the intermediate chamber.
  • a check valve which blocks at an air flow from the first channel opening to the second channel opening and opens at an air flow from the second channel opening to the first channel opening, is arranged in the channel.
  • a check valve is arranged, which is forced into a position closing the second channel opening when the striker is in the working position.
  • the exciter can increase the amount of air in the pneumatic chamber.
  • the larger air volume reduces the impact power and increases the stiffness of the air spring, which facilitates the attachment of the tool to the ground.
  • the striker disables the increase in the amount of air via the check valve upstream of the check valve.
  • the increased amount of air is selectively reduced in chiseling operation or reduced via loss channels, which increases the impact power to the setpoint.
  • the check valve is controlled by the striker, and thus indirectly by the user and the pressing of the tool to the ground.
  • the stationary arrangement of the check valve favors a short response time and robustness to the forces during chiseling operation.
  • One embodiment provides a slide valve formed by a radial opening of the pneumatic chamber and the racket.
  • the slide valve is closed in the racket adjacent to lying in the working position striker relative to the pneumatic chamber.
  • the slide valve is open at the racket adjacent to the striker in front of the working position striker against the pneumatic chamber.
  • the slide valve allows a complete shutdown of the impact mechanism, again indirectly by the user and a lack of pressing the tool to the ground.
  • the check valve has an elastic locking body, which is spaced in a non-tensioned basic shape of a valve seat, the check valve and elastically braced by the lying in the working position striker on the valve seat, fitting is deformed.
  • An embodiment provides that the first channel opening is arranged at a rack-side reversal point of the exciter. An embodiment provides that the channel is closed between the first channel opening and the second channel opening.
  • the pneumatic chamber has a throttle opening for exchanging air between the pneumatic chamber and the surroundings of the portable power tool.
  • the throttle opening may be arranged at a beater-side reversal point of the exciter.
  • a ratio of the cross-sectional area of the throttle opening to the cross-sectional area of the channel opening is less than one to twelve.
  • About the throttle opening can be adjusted specifically the outflow of the increased amount of air.
  • the throttle opening is very small, whereby the outflow preferably takes up to one second.
  • An embodiment provides that the check valve is arranged stationarily at the first channel opening.
  • Fig. 1 shows a hammer drill 1 as an example of a beating hand-held machine tool.
  • the hammer drill 1 has a tool holder 2 in which coaxial with a working axis 3, a drill, chisel or other beating tool 4 can be used and locked.
  • the hammer drill 1 has a pneumatic impact mechanism 5, which can exert periodic punches in a direction of impact 6 on the tool 4 .
  • a rotary drive 7 can rotate the tool holder 2 continuously about the working axis 3 .
  • the pneumatic impact mechanism 5 and the rotary drive are of an electric motor. 8 driven, which is fed from a battery 9 or a power line with electric current.
  • the striking mechanism 5 and the rotary drive 7 are arranged in a machine housing 10 .
  • a handle 11 is typically arranged on a side facing away from the tool holder 2 of the machine housing 10 .
  • the user can hold the hammer drill 1 by means of the handle 11 in operation and lead.
  • An additional auxiliary handle can be attached near the tool holder 2 .
  • an operating button 12 is arranged, which the user can operate preferably with the holding hand.
  • the electric motor 8 is turned on by operating the operating button 12 . Typically, the electric motor 8 rotates as long as the operation button 12 is kept depressed.
  • the tool 4 is movable in the tool holder 2 along the working axis 3 .
  • the tool 4 has an elongated groove into which a ball or other locking body of the tool holder 2 engages.
  • the user holds the tool 4 in a working position in that the user presses the tool 4 indirectly through the hammer drill 1 to a substrate ( Fig. 2 ).
  • the pressing is associated with a chiseling phase.
  • the tool 4 is moved by the impact of the striking mechanism 5 in the direction of impact 6 from the working position.
  • the tool 4 can remain in the advanced position if the user does not continue to press the hammer drill 1 ( Fig. 3 ).
  • the lack of pressing is associated with a rest phase and leads to an automatic shutdown of the striking mechanism 5.
  • the user can start the striking mechanism 5 by re-pressing, ie transfer from the resting phase in the chiseling phase (start phase; Fig. 4 ).
  • the pneumatic percussion 5 has along the direction of impact 6 a pathogen 13, a bat 14 and an anvil 15.
  • the exciter 13 is forced by means of the electric motor 8 to a periodic movement along the working axis 3 .
  • the bat 14 is coupled via an air spring to the movement of the exciter 13 .
  • the air spring is formed by a closed between the exciter 13 and the bat 14 pneumatic chamber 16 .
  • the bat 14 moves in the direction of impact 6 until the bat 14 strikes the striker 15 .
  • the striker 15 abuts the tool 4 in the direction of impact 6 and transmits the impact to the tool 4.
  • the exemplary impact mechanism 5 has a piston-shaped exciter 13 and a piston-shaped racket 14, which are guided by a guide tube 17 along the working axis 3 are.
  • the exciter 13 and the bat 14 abut with their lateral surfaces on the inner surface of the guide tube 17 .
  • the pneumatic chamber 16 is closed by the exciter 13 and the bat 14 along the working axis 3 and by the guide tube 17 in the radial direction. Sealing rings in the outer surfaces of exciter 13 and bat 14 can improve the airtight completion of the pneumatic chamber 16 .
  • the exciter 13 is connected via a gear component with the electric motor 8 .
  • the transmission component transmits the rotational movement of the electric motor 8 in a periodic translational movement along the working axis 3.
  • An exemplary transmission component based on an eccentric 18, which is connected to the electric motor 8 .
  • a connecting rod 19 connects a pin 20 of the Eccentric 18 with a pin in the exciter 13.
  • the exciter 13 moves in synchronism with the electric motor 8.
  • the electric motor 8 typically rotates in response to actuation of the operating button 12 and rotates as long as the user the operating button 12 is pressed holds.
  • the periodic forward and backward movement of the exciter 13 also begins and ends with the actuation or release of the operating button 12.
  • Another example of such a transmission component is a wobble drive.
  • the racket 14 is coupled via the air spring to the exciter 13 .
  • the air spring is based on a pressure difference between the pressure in the pneumatic chamber 16 and the pressure in the environment.
  • the forced-motion exciter 13 increases or decreases the pressure in the pneumatic chamber 16 by means of its periodic axial movement.
  • the racket 14 is accelerated by the pressure difference in or against the direction of impact 6 .
  • Fig. 2 shows in a split representation of the exciter 13 and racket 14 whose position in the compression point (upper half) and in the impact point (lower half). At the compression point, the pneumatic chamber 16 is maximally compressed, the pressure difference is therefore greatest.
  • the racket 14 has the smallest distance to the exciter 13.
  • the compression point coincides approximately with the reversal point of the oscillatory movement of the racket 14 .
  • the bat 14 induces a shock wave in the striker 15, which passes through this and is transmitted to the voltage applied to the striker 15 tool 4 .
  • the striker 15 is movably guided in a percussion tube 21 along the working axis 3 .
  • the impact tube 21 may be formed by the exciter 13 and racket 14 leading guide tube 17 or a separate tube.
  • the striker 15 is in the impact tube 21 between a working position ( Fig. 2 ), Rest positions ( Fig. 3 ) and a starting position ( Fig. 4 ) movable.
  • the striker 15 is in the working position against the direction of impact 6 on the stop 22 .
  • the working position of the tool 4 is characterized in that the striker 15 is in its working position and the tool 4 rests against the striker 15 .
  • the shock wave induced by the racket 14 can pass from the striker 15 to the tool 4 .
  • the user lifts the hammer drill 1 from the ground in a resting phase.
  • the tool 4 and the striker 15 can leave the working position in the direction of impact 6 in the rest position due to a shock or gravity ( Fig. 3 ).
  • the impact mechanism 5 is preferably deactivated when the striker 15 is in the rest position.
  • the striking mechanism 5 can have exactly one defined rest position, for example when the striker 15 abuts a stop 23 in the direction of impact 6 .
  • the exemplary striking mechanism 5 has a plurality of rest position, all within a contiguous, adjacent to the stop 23 area.
  • the striking mechanism 5 can be deactivated by reducing the rotational speed of the electric motor 8 .
  • the striking mechanism 5 is designed for an optimal number of beats, ie beats per second, at which a synchronous movement of the beater 14 and the exciter 13 occurs.
  • the optimum number of strokes is determined inter alia by the mass of the racket 14, the end face of the racket 14 and the distance from the compression point to the impact point. If the periodicity of the forced-motion exciter 13 is significantly different from the optimal stroke rate, the bat 14 can no longer follow the excitation by the exciter 13 and stops.
  • the speed can be lowered, for example, by 20% or more compared to the speed for the optimum number of strokes.
  • a sensor may detect accelerations of the machine housing 10, impact sounds, or a position of the striker 14 or the striker 15 to detect the rest position. The speed is reduced in response to the sensor.
  • the striking mechanism 5 can be deactivated by decoupling the racket 14 from the exciter 13 .
  • the pneumatic chamber 16 is vented to provide pressure equalization between the pneumatic chamber 16 and the environment.
  • the air exchange prevents the moving exciter 13 from building up a sufficient pressure difference to move the racquet 14 .
  • the venting is carried out by one or preferably a plurality of radial ventilation openings 24 of the pneumatic Chamber 16, which connects the cavity of the pneumatic chamber 16 with the environment.
  • the radial vents 24 are, for example, holes or punched holes in the guide tube 17.
  • the environment is typically the interior of the machine housing 10, which in turn may be in continuous air exchange through openings with an environment outside the machine housing 10 .
  • the volume of the environment is so great that the amount of air moved by the exciter 13 causes no appreciable pressure fluctuation.
  • the volume of the environment is at least ten times as large as the maximum volume of the pneumatic chamber 16.
  • the radial ventilation openings 24 can be closed and opened by a slide valve 25 .
  • the slide valve 25 is composed of the radial ventilation openings 24 and the bat 14 together.
  • the slide valve 25 is closed relative to the pneumatic chamber 16 when the lateral surface of the racket 14 covers the ventilation openings 24 or the racket 14 lies in the direction of impact 6 in front of the ventilation openings 24 ( Fig. 2 ).
  • the slide valve 25 is opened relative to the pneumatic chamber 16 when the racket 14 lies in the direction of impact 6 behind the ventilation openings 24 ( Fig. 3 ).
  • the pneumatic chamber 16 then extends along the working axis 3 to the ventilation openings 24.
  • the position of the racket 14, in which the slide valve 25 changes from open to closed and vice versa hereinafter referred to as switching point of the slide valve 25 ( Fig. 4 , lower half of the picture).
  • the slide valve 25, ie the ventilation openings 24, is arranged along the working axis 3 in such a way that the slide valve 25 is moved during the chiselling phase (FIG. Fig. 2 ), ergo in the working position, is closed continuously and only during the resting phase ( Fig. 3 ), ergo at rest, may be open.
  • the ventilation openings 24 are arranged along the working axis 3 in the direction of impact 6 behind the impact point.
  • the bat 14 is viewed in the direction of impact 6 in the point of impact before the switching point.
  • the racket 14 obscured during its movement between the compression point and the point of impact throughout the ventilation opening 24 from the pneumatic chamber 16.
  • the racquet 14 can also slide in the striking direction 6 via the percussion point when the anvil 15 is displaced sufficiently towards the working position in the impact direction 6 is.
  • the beater 14 no longer covers the vent opening 24 , ie, the pneumatic chamber 16 overlaps with the vent opening 24.
  • a cross-section of the vent openings is selected so that an air flow between the pneumatic chamber 16 and the environment is the rate of change of the volume of the pneumatic chamber 16 of the moving exciter 13.
  • the pressure in the pneumatic chamber 16 differs only slightly from the environment, so no appreciable force is exerted on the bat 14 .
  • the percussion mechanism 5 is deactivated despite the still moving exciter 13.
  • An accumulated cross-sectional area of the ventilation openings 24 is in the range between 2% and 6% of the cross-sectional area of the pneumatic chamber 16, ie the end face of the exciter 13.
  • the racket 14 and the striker 15 can complete an (intermediate) chamber 26 along the working axis 3 .
  • the guide tube 17 and the impact tube 21 enclose the intermediate chamber 26.
  • a channel 27 connects the pneumatic chamber 16 and the intermediate chamber 26.
  • the channel 27 allows a controlled exchange of air between the pneumatic chamber 16 and the intermediate chamber 26.
  • the channel 27 is provided with a check valve 28 and a check valve 29 .
  • the check valve 28 and the check valve 29 allow only an influx of air into the pneumatic chamber 16 and the inflow only when the striker 15 is displaced from the working position. Otherwise locks at least one of the two valves.
  • the channel 27 has a preferably a plurality of extending into the pneumatic chamber 16 passage openings 30.
  • the passage openings 30 are preferably radial openings in the pneumatic chamber 16, for example a bore or a punched hole in the guide tube 17.
  • the (first) channel opening 30 is preferably located at or near the beater-side reversal point of the exciter 13.
  • the channel opening 30 is not covered by the exciter 13 or for a long time by the racket 14 .
  • the channel opening 30 may be located at a different location along the guide tube 17 as long as the pneumatic chamber 16 at least temporarily overlaps the channel opening 30 in the chiseling phase.
  • the other (second) channel opening 31 extends, for example, into the intermediate chamber 26.
  • the channel 27 or the channel openings 30 have a cross-sectional area of 0.5% to 4% of the cross-sectional area of the pneumatic chamber 16, ie the end face of the exciter 13.
  • the check valve 28 is actuated by the striker 15 .
  • the check valve 28 is closed when the striker 15 is in the working position ( Fig. 2 ).
  • the check valve 28 is opened when the striker 15 is displaced from the working position ( Fig. 3 ).
  • the position of the striker 15, in which the check valve 28 changes from open to closed and vice versa, is hereinafter referred to as the switching point of the check valve 28 ( Fig. 4 , upper half of the picture).
  • the striker 15 is considered in the direction of impact 6 in the switching point behind the working position.
  • the switching point of the slide valve 25 and the switching point of the check valve 28 are preferably matched.
  • the striker 15 indicates by its position, whether the racket 14 can open the slide valve 25 . If the striker 15 is in the switching point of the check valve 28, the slide valve 25 is closed ( Fig. 4 , upper half of the picture).
  • the striker 15 protrudes in the switching point of the check valve 28 lying as far as against the direction of impact 6 before, that the bat 14 is adjacent to the striker 15 in the direction of impact 6 before the switching point of the spool valve 25 , ie the ventilation opening 24 covers.
  • the Schlagtechnik 5 has a starting position ( Fig.
  • the check valve 29 is connected on the input side to the intermediate chamber 26 and the output side to the pneumatic chamber 16 . Accordingly, the check valve 29 allows air flow from the intermediate chamber 26 into the pneumatic chamber 16 and blocks against air flow from the pneumatic chamber 16 into the intermediate chamber 26.
  • the amount of air (air mass) in the pneumatic chamber 16 increases when the striker 15 is in the starting area.
  • the increased amount of air leads to a higher average pressure in the pneumatic chamber 16.
  • the amount of air is reduced both when the striker 15 changes to the rest position or to the working position.
  • the Schlagtechnik 5 goes during a start phase continuously from the rest phase in the chiseling phase with full impact performance. The user feels when pressing the hammer drill 1 when the pressure in the pneumatic chamber 16 increases when the striker 15 reaches the starting area. The user must apply a minimum force to to overcome the pressure. Otherwise, the racket 14 moves the striker 15 to above the starting position and switches off the percussion mechanism 5 by the slide valve 25 .
  • the channel 27 with the check valve 28 and the check valve 29 leads to an overpressure in the pneumatic chamber 16 when the striker 15 is in the start region.
  • the check valve 29 allows only an inflow of air into the pneumatic chamber 16.
  • the exciter 13 sucks in its movement against the direction of impact 6 through the opening check valve 29 air.
  • the amount of air in the pneumatic chamber 16 increases because no air can escape. Leaks limit an increase in the amount of air.
  • the pressure in the pneumatic chamber 16 is greater than in the intermediate chamber 26, corresponding to a result in the direction of impact 6 force on the racket 14 and indirectly on the applied to the racket 14 striker 15. The user feels the counter to the direction of impact 6 acting Counterforce on the exciter 13 and the handle 11.
  • the throttle opening 33 is preferably arranged at or near the beater-side reversal point of the exciter 13 .
  • a cross-sectional area of the throttle opening 33 is very small.
  • the cross section limits air exchange with the environment to less than 1/10 of the air volume of the pneumatic chamber 16 within a period of the exciter 13.
  • the cross sectional area of the throttle opening 33 is in the range of 0.05% to 0.20% of the end face of the exciter 13.
  • the amount of air in the pneumatic chamber 16 equalizes within ten to fifty cycles of the exciter 13 to the environment. Depending on the size of the impact mechanism 5 , for example, 500 milliseconds (ms) to 800 ms pass by.
  • the preferably single throttle opening 33 is in particular significantly smaller than the ventilation openings 24 and the channel opening 30.
  • the cross-sectional area of the throttle opening 33 is preferably less than 6% of the cross-sectional area of the ventilation opening 24 and preferably less than 8% of the cross-sectional area of the channel opening 30.
  • the channel 27, four first channel openings 30 with a cross-sectional area of 2 mm 2 each, and the cross-sectional area of the throttle opening 33 is 0.5 mm 2 .
  • the racket 14 may inadvertently shut down the gate valve 25 after shutdown, eg, by shock. If the striker 15 is not accidentally in the working position, the pumping effect causes an average force in the direction of impact 6 on the bat 14. Der Bat 14 is moved to the rest position, the slide valve 25 is opened and the striking mechanism 5 is turned off.
  • the exemplary check valve 28 has a stationary valve seat 34 and a resilient lock body 35 in a valve passage 36 (FIGS. Fig. 5 ).
  • the valve channel 36 opens into the second channel opening 31.
  • the check valve 28 is closed when the blocking body 35 completely abuts against the valve seat 34 and thereby strangles the valve channel 36 .
  • the locking body 35 is elastically braced when the locking body 35 completely rests against the valve seat 34 .
  • the check valve 28 is self-opening. Without external force of the locking body 35 relaxes from the strained shape in a basic shape, which is not or only partially applied to the valve seat 34 .
  • the check valve 28 is switched by means of the striker 15 .
  • the striker 15 has an active surface 37 which actuates the blocking body 35 .
  • the active surface 37 forces the locking body 35 against the valve seat 34 when the striker 15 is in the working position. If the striker 15 is located in the direction of impact 6 behind the switching point, the active surface 37 is force-free or non-
  • the exemplary locking body 35 is an elastic ring, for example made of rubber.
  • the blocking body 35 is arranged inside the impact tube 21 coaxially with the working axis 3 .
  • the exemplary valve seat 34 has in the radial direction to the working axis 3 and lies with the locking body 35 in a plane.
  • the distance of the valve seat 34 to the working axis 3 is slightly larger than the outer radius of the elastic ring.
  • the active surface 37 of the striker 15 is a section of the cylindrical lateral surface.
  • the radius of the lateral surface is greater by at least the gap than an inner radius of the ring.
  • the active surface 37 is within the plane when the striker 15 is in the working position.
  • the active surface 37 spreads the ring so far that the ring completely touches the valve seat 34 . If the striker 15 is outside the working position, the ring contracts in the radial direction into its basic shape and separates from the valve seat 34.
  • the check valve 29 is stationarily arranged at or near the first passage opening 30 .
  • the channel portion from the first channel opening 30 to the check valve 29 is as short as possible.
  • a dead volume formed by the channel portion is constant and less than 5% of the mean volume of the pneumatic chamber 16.
  • the exemplary check valve 29 is based on a movable locking body 38 and an inclined guide surface 39 (FIG. Fig. 6 ).
  • the check valve 29 has a passage 40 in which an air flow can flow through the check valve 29 .
  • the check valve 29 locks automatically in an air flow against the passage direction 40.
  • the check valve 28 On the input side, ie in the forward direction 40 before the check valve 29, the check valve 28 is arranged on the output side, ie in the forward direction 40 after the check valve 29, the pneumatic chamber 16 is arranged.
  • the movable blocking body 35 lies in a bulge 41 of the channel 27.
  • the bulge 41 has a dimension along the passage direction 40, which allows a movement of the blocking body 38 along the passage 40 .
  • the inclined guide surface 39 is provided on the input side of the bulge 41 .
  • the guide surface 39 approaches the channel 27 counter to the passage direction 40 , whereby the blocking body 35 pressed against the guide surface 39 by a flow of air flowing against the passage direction 40 is pressed into the channel 27 .
  • the movable blocking body 35 may be a ball or an elastic ring spanning the guide tube 17 .
  • FIGS. 7, 8 and 9 An embodiment of the check valve 42 is in FIGS. 7, 8 and 9 shown.
  • the check valve 28 is actuated by the striker 15 .
  • the striker 15 closes the check valve 28 when the striker 15 is in the working position ( Fig. 7 upper half of the picture; Fig. 8 ).
  • the check valve 28 is opened when the striker 15 is displaced from the working position ( Fig. 8 lower half of the picture; Fig. 9 ).
  • the check valve 42 has a valve seat 43 and an elastic lock body 44.
  • the valve seat 45 and the lock body 46 are formed of a monolithic elastic ring 46 .
  • the ring 46 is arranged coaxially with the striker 15 .
  • the ring 46 is placed on the guide tube 17 .
  • the ring 46 may be disposed within the guide tube 17 between the beater 14 and the striker 15 .
  • the ring 46 is clamped along the working axis 3 between the striker 15 and a seat 45 .
  • the anvil 15 presses in the operating position lying against the impact direction 6 to the ring 46. In the exemplary embodiment, transmits a control ring 47, the force from the anvil 15 to the ring 46.
  • the seat 45 is immovable relative to the guide tube 17, whereby the pressing force of the beatpiece 15 can compress the ring 46 axially.
  • the seat 45 forms with the ring 46 the stop to which the striker 15 is pressed against the direction of impact 6 for the working position.
  • the ring 46 has a circumferential notch 48 which divides the ring 46 along the axis into the valve seat 43 and the lock body 44 .
  • the locking body 44 may be configured in the form of a thin lip.
  • the blocking body 44 can be pivoted into the notch 48 to such an extent that the blocking body 44 touches the valve seat 43 and closes the notch 48 (FIG. Fig. 8 ).
  • the ring 46 in particular the lip-shaped locking body 44 and a Block body 35 with the valve seat 43 connecting web 49, are elastically clamped when the locking body 44 abuts against the valve seat 43 .
  • the notch 48 is opened, that is, the blocking body 44 is at a distance from the valve seat 43 (FIG. Fig. 9 ).
  • the ring 46 has one or more radial punctures 50 in the valve seat 43 and an axial puncture 51 in the locking body 44.
  • the air can from the intermediate chamber 26 through the radial puncture 50 on the side with the notch 48, in the notch 48 and through the axial puncture 51 from the check valve 42 flow into the channel 27 .
  • the notch 48 is compressed, that is, the lip-shaped locking body 44 abuts against the valve seat 43 , the air flow is interrupted.
  • the ring 46 lies with its radially inner surface airtight on the guide tube 17 , the notch 48 is on the radial outer side.
  • the ring 46 may alternatively be arranged with the lip-shaped locking body in the direction of impact 6 and the valve seat against the seat.
  • the ring 46 is formed of, for example, rubber or a synthetic rubber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (8)

  1. Machine-outil manuelle à percussion (1) comportant :
    un porte-outil (2) pour maintenir un outil à percussion (4) sur un axe de travail (3),
    un moteur électrique (8),
    un mécanisme de percussion (5) comportant, agencés les uns à la suite des autres dans une direction de percussion (6), un piston excitateur (13), une chambre pneumatique (16), un percuteur (14), une chambre intermédiaire (26) et une enclume (15),
    un canal fermé (27) reliant un premier orifice de canal (30) dans la chambre pneumatique (16) et un second orifice de canal (31) dans la chambre intermédiaire (26),
    un clapet de blocage (28, 42) agencé sur le second orifice de canal (31) qui est forcé dans une position obturant le second orifice de canal (31) lorsque l'enclume (15) est dans la position de travail,
    caractérisée par
    un clapet anti-retour (29) agencé dans le canal (27) qui bloque un écoulement d'air depuis le premier orifice de canal (30) vers le second orifice de canal (31) et qui s'ouvre pour permettre un écoulement d'air depuis le second orifice de canal (31) vers le premier orifice de canal (30), et dans laquelle la chambre pneumatique (16) comporte un orifice d'étranglement (33) pour l'échange d'air entre la chambre pneumatique (16) et l'environnement de la machine-outil manuelle (1).
  2. Machine-outil manuelle (1) selon la revendication 1, caractérisée par un distributeur à tiroir (25) formé par un orifice radial (24) de la chambre pneumatique (16) et le percuteur (14), dans laquelle le distributeur à tiroir (25) est fermé par rapport à la chambre pneumatique (16) par le percuteur (14) en appui sur l'enclume (15) qui est dans la position de travail, et dans laquelle le distributeur à tiroir (25) est ouvert sur la chambre pneumatique (16) par le percuteur (14) en appui sur l'enclume (15) qui est avant la position de travail dans la direction de percussion (6).
  3. Machine-outil manuelle (1) selon la revendication 1 ou 2, caractérisée en ce que le clapet de blocage (28) comporte un corps de blocage élastique (35, 44) qui, dans une forme de base relâchée, est distant d'un siège de clapet (34, 43) du clapet de blocage (42) et qui est élastiquement déformé par l'enclume (15) qui est dans la position de travail et en appui sur le siège de clapet (34, 43).
  4. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que le premier orifice de canal (30) est agencé sur un point d'inversion côté percuteur du piston excitateur (13).
  5. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que l'orifice d'étranglement (33) est agencé sur un point d'inversion côté percuteur du piston excitateur (13).
  6. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce qu'un rapport de la surface de section transversale de l'orifice d'étranglement (33) sur la surface de section transversale de l'orifice de canal (30) est inférieur à un sur douze.
  7. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que le clapet anti-retour (29) est agencé de manière fixe sur le premier orifice de canal (30).
  8. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que le canal (27) est fermé entre le premier orifice de canal (30) et le second orifice de canal (31).
EP16809722.8A 2015-12-15 2016-12-06 Machine-outil portative a percussion Active EP3389934B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP15200146.7A EP3181299A1 (fr) 2015-12-15 2015-12-15 Machine-outil portative a percussion
PCT/EP2016/079894 WO2017102437A1 (fr) 2015-12-15 2016-12-06 Machine-outil portative à percussion

Publications (2)

Publication Number Publication Date
EP3389934A1 EP3389934A1 (fr) 2018-10-24
EP3389934B1 true EP3389934B1 (fr) 2019-09-11

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EP15200146.7A Withdrawn EP3181299A1 (fr) 2015-12-15 2015-12-15 Machine-outil portative a percussion
EP16809722.8A Active EP3389934B1 (fr) 2015-12-15 2016-12-06 Machine-outil portative a percussion

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Application Number Title Priority Date Filing Date
EP15200146.7A Withdrawn EP3181299A1 (fr) 2015-12-15 2015-12-15 Machine-outil portative a percussion

Country Status (3)

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US (1) US10675742B2 (fr)
EP (2) EP3181299A1 (fr)
WO (1) WO2017102437A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3181301A1 (fr) 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil portative a percussion
EP3181298A1 (fr) 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil a percussion
US11833652B2 (en) * 2022-01-25 2023-12-05 Hilti Aktiengesellschaft Power tool

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2641070A1 (de) * 1976-09-11 1978-03-16 Bosch Gmbh Robert Motorisch angetriebener schlaghammer mit luftfederung
JPS5930607A (ja) 1982-08-12 1984-02-18 Hitachi Koki Co Ltd 電気ハンマドリル
DE3826213A1 (de) 1988-08-02 1990-02-15 Bosch Gmbh Robert Bohr- oder schlaghammer
DE19810088C1 (de) 1998-03-10 1999-08-26 Bosch Gmbh Robert Bohr- und/oder Schlaghammer mit in Abhängigkeit von der Einstecktiefe eines Werkzeuges aktivierbarem Schlagwerk
DE10103141A1 (de) * 2001-01-24 2002-07-25 Hilti Ag Elektrohandwerkzeuggerät mit Leerschlagabschaltung
EP1607187B1 (fr) * 2004-06-18 2010-04-28 HILTI Aktiengesellschaft Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion
JP5154995B2 (ja) * 2008-03-28 2013-02-27 株式会社マキタ 打撃工具
JP5518617B2 (ja) * 2010-08-02 2014-06-11 株式会社マキタ 打撃工具
DE102012206452A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Handwerkzeugmaschine und Steuerungsverfahren
EP2871028A1 (fr) * 2013-11-11 2015-05-13 HILTI Aktiengesellschaft Machine-outil manuelle
EP3181301A1 (fr) 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil portative a percussion
EP3181300A1 (fr) 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil portative a percussion
EP3181298A1 (fr) 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil a percussion

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US20190039225A1 (en) 2019-02-07
US10675742B2 (en) 2020-06-09
WO2017102437A1 (fr) 2017-06-22
EP3389934A1 (fr) 2018-10-24
EP3181299A1 (fr) 2017-06-21

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