EP2394793A1 - Machine-outil manuelle dotée d'une sonnette pneumatique et son procédé de contrôle - Google Patents

Machine-outil manuelle dotée d'une sonnette pneumatique et son procédé de contrôle Download PDF

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Publication number
EP2394793A1
EP2394793A1 EP11164392A EP11164392A EP2394793A1 EP 2394793 A1 EP2394793 A1 EP 2394793A1 EP 11164392 A EP11164392 A EP 11164392A EP 11164392 A EP11164392 A EP 11164392A EP 2394793 A1 EP2394793 A1 EP 2394793A1
Authority
EP
European Patent Office
Prior art keywords
striker
pneumatic chamber
valve
impact
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.)
Granted
Application number
EP11164392A
Other languages
German (de)
English (en)
Other versions
EP2394793B1 (fr
Inventor
Markus Hartmann
Frank Kohlschmied
Christian Daubner
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
Application filed by Hilti AG filed Critical Hilti AG
Publication of EP2394793A1 publication Critical patent/EP2394793A1/fr
Application granted granted Critical
Publication of EP2394793B1 publication Critical patent/EP2394793B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • 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
    • B25D2217/0015—Anvils
    • 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
    • B25D2250/365—Use of seals

Definitions

  • the present invention relates to a machine tool, in particular a hand-held chiseling machine tool and a control method for the machine tool.
  • a chisel action should be set when a chisel is lifted from a workpiece.
  • an air spring can be deactivated by means of additional ventilation openings, which are only opened when the bit is disengaged.
  • An anvil also known as an intermediate beater or anvil, should be kept away from the vents after a space. However, this is partly due to the rebound of the anus on a front stop is not given.
  • a machine tool has an anvil, which is guided along an axis parallel to a direction of impact.
  • a pneumatic chamber has a volume that varies with movement of the anvil along the axis.
  • a dependent of the direction of movement of the striker valve device operatively connects the pneumatic chamber with an air reservoir.
  • the valve device is actuated open in the direction of impact during a movement of the striker and, in the event of a movement of the striker, is throttled or closed against the direction of impact.
  • the throttled or closed valve device limits an air flow flowing through it to at most one tenth of the value relative to the air flow in an open position.
  • the striker is a longitudinally movable striker or anvil which is disposed between a striker of a pneumatic percussion mechanism and a tool inserted in a tool holder.
  • the striker undergoes a braking action by the closed pneumatic chamber as it slides back into the tool holder.
  • the valve means a pressure equalization in the pneumatic chamber, which is why no braking effect occurs.
  • the volume of the pneumatic chamber during a movement of the striker in the direction of impact is preferably monotonically increasing and the valve device is open for an air flow into the pneumatic chamber and throttling or blocking for an air flow from the pneumatic chamber.
  • the volume of the pneumatic chamber during a movement of the anvil in the direction of impact e.g. monotonically decreasing and the valve means is throttling or blocking for airflow into the pneumatic chamber and open to air flow out of the pneumatic chamber.
  • the air reservoir may be a further pneumatic chamber, the volume of which, when the striker is moved in the direction of impact, e.g. monotonically decreasing and the valve device connects the pneumatic chamber with the further pneumatic chamber.
  • the open actuated valve device can connect the pneumatic chamber with the further pneumatic chamber such that an air quantity escaping from the further pneumatic chamber flows into the pneumatic chamber.
  • One or two pneumatic chambers may be provided which, depending on their relative disposition with respect to the beatpiece, are compressed or stretched during a movement in the direction of impact.
  • a valve device may be provided or even in the case of two chambers, these may be connected via a common valve device.
  • An embodiment provides that the pneumatic chamber is guided by a guide for guiding the striker along the axis of the striker and two along the axis offset from each other arranged seals, e.g. in the radial direction, is completed between the striker and the guide, wherein in a projection on a plane perpendicular to the axis, the two seals at least partially overlap not.
  • An embodiment provides that the pneumatic chamber and the further pneumatic chamber are closed by a guide for guiding the striker along the axis, the striker and three along the axis staggered seals between the striker and the guide, wherein the respective adjacent seals in a projection on a plane perpendicular to the axis at least partially overlap not.
  • At least one of the seals may be formed by the valve means. Between two adjacent seals, an opening in the guide is arranged, and the valve means connects the opening with the air reservoir or another air reservoir.
  • the valve device can be arranged outside the guide.
  • valve device is a self-medium-actuated valve device which is actuated by an air flow in or out of the pneumatic chamber.
  • An air flow keeps the valve device open when the air flow flows in the direction of flow.
  • An air pressure acting counter to the direction of flow on the valve device closes it.
  • the valve device may include a check valve.
  • One embodiment has a throttle that connects the pneumatic chamber to an air reservoir.
  • An effective cross-sectional area of the pneumatic chamber defined by the differential of the volume of the pneumatic chamber in the direction of impact is greater than one hundred times a cross-sectional area of the throttle.
  • the striker is moved parallel to the axis, resulting in a volume change of the pneumatic chamber proportional to the displacement along the axis and the effective cross-sectional area.
  • the effective cross-sectional area can be determined by the mathematical operation of differentiating according to the direction of movement or impact. With a cylindrical guide and a cylindrical striker, the effective cross-sectional area corresponds to the largest cross-sectional area perpendicular to the axis.
  • the ratio of the effective cross-sectional area of the pneumatic chamber to the cross-sectional area of the throttle determines a relative flow rate of the air in the throttle relative to the velocity of the striker. From this relative flow rate, the air can escape quickly enough from the pneumatic chamber, without a pressure gradient builds up to the environment. It was recognized that an absolute speed of air in the throttle can not be exceeded. However, the throttle seems to lock a limit of absolute speed.
  • the ratio of one hundred times, preferably three hundred times, is chosen so that in a driven by the percussion striker, the absolute velocity of the air is achieved in the throttle, with a manually moving striker, the absolute speed is clearly below. As a result, the throttle locks in the beaten doubler and opens when manually moving anvil.
  • the machine tool has a pneumatic percussion mechanism, which is arranged with its percussion piston in striking direction on the striker.
  • valve device is opened when the striker moves in the direction of impact, and the valve device is closed when the striker moves counter to the direction of impact.
  • Fig. 1 shows a hammer drill 1 as an embodiment of a chiseling machine tool.
  • the hammer drill 1 has a machine housing 2 , in which a motor 3 and a driven by the motor 3 pneumatic percussion 4 are arranged and a tool holder 5 is preferably releasably attached.
  • the motor 3 is, for example, an electric motor which is supplied with power via a wired mains connection 6 or a rechargeable battery system.
  • the pneumatic impact mechanism 4 drives a tool 7 inserted into the tool holder 5 , for example a drill bit or a chisel, away from the hammer drill 1 , along an axis 8 in the direction of impact 9 into a workpiece.
  • the hammer drill 1 optionally has a rotary drive 10 , which can rotate the tool 7 in addition to the striking movement about the axis 8 .
  • a rotary drive 10 which can rotate the tool 7 in addition to the striking movement about the axis 8 .
  • On the machine housing 2 one or two handles 11 are attached, which allow a user to guide the hammer drill 1 .
  • the pneumatic impact mechanism 4 shown by way of example has a percussion piston 12 , which is excited by an excited air spring 13 to move forward, ie in the direction of impact 9 , along the axis 8 .
  • the percussion piston 12 strikes an anvil 20 and thereby releases a portion of its kinetic energy to the striker 20 . Due to the recoil and excited by the air spring 13 , the percussion piston 12 moves to the rear, ie counter to the direction of impact 9 until the compressed air spring 13, the percussion piston 12 drives back to the front.
  • the air spring 13 is formed by a pneumatic chamber which is closed axially, forward by a rear end face 21 of the percussion piston 12 and axially, to the rear by a field piston 22 .
  • the pneumatic chamber can be circumferentially closed by a hammer tube 23 , in which the percussion piston 12 and the exciter piston 22 are guided along the axis 8 .
  • the percussion piston 12 can slide in a cup-shaped excitation piston, wherein the excitation piston closes the cavity of the pneumatic chamber in the radial direction, ie circumferentially.
  • the air spring 13 is energized by a forced, oscillating movement along the axis 8 of the exciter piston 22 .
  • An eccentric 24 , a wobble drive, etc., can convert the rotational movement of the motor 3 in the linear oscillating motion.
  • a period of forced movement of the exciter piston 22 is tuned to the interaction of the system of percussion piston 12 , air spring 13 and striker 20 and their relative axial distances, in particular a predetermined impact point 25 of the percussion piston 12 with the striker 20 to the system resonant and thus optimal for an energy transfer from the motor 3 to the percussion piston 12 to stimulate.
  • the striker 20 is a body, preferably a body of revolution, with a front impact surface 26 exposed in the direction of impact 9 and a rear impact surface 27 exposed against the direction of impact 9 .
  • a shock on his rear striking surface 27 transmits the striker 20 on the voltage applied to his front striking surface 26 tool.
  • the striker 20 may also be referred to as an intermediate bat according to its function.
  • a guide 28 guides the striker 20 along the axis 8 .
  • the striker 20 partially dips with a rear end into a rear guide section 29 .
  • the rear end rests with its radial outer surface on the guide portion 29 in the radial direction.
  • a front guide portion 30 may equally surround a front end of the striker 20 and restrict its radial movement.
  • the rear and the front guide portion 29 , 30 at the same time form two stops, the axial movement of the striker 20 to a distance between the rear Stop 29 and the front, lying in the direction of impact 9 stop (striker) 30 limit.
  • the striker 20 has a thickened central portion 33 , which abuts with its end faces on the guide portions 29 , 30 .
  • the example illustrated guide 28 has a, for example, cylindrical, circumferentially closed guide tube 31 , in which the striker 20th
  • the thicker portion 33 of the striker 20 is radially spaced with its lateral surface 34 , ie radial outer surface, at least in sections or along its entire circumference by an inner wall 32 of the guide tube 31 .
  • a groove-shaped or cylindrical gap 35 extends between the striker 20 and the guide tube 31st
  • the gap 35 may have a radial dimension of between 0.5 mm and 4 mm.
  • the tool 7 When chiselling, the tool 7 is supported on the front striking surface 26 of the striker 20 , whereby the striker 20 is held in engagement with the rear stop 29 ( Fig. 2 ).
  • the impact mechanism 4 is designed for the engaged position of the striker 20 .
  • the predetermined impact point 25 ( Fig. 2 ) of the percussion piston 12 and reversal point in the movement of the percussion piston 12 is determined by the rear impact surface 27 of the engaged striker 20 .
  • the beating function of the pneumatic percussion mechanism 4 should be interrupted, otherwise the hammer drill 1 hits empty.
  • An impact of the percussion piston 12 on the striker 20 causes the striker 20 to slide to the front stop 30 and preferably stops in its vicinity.
  • the percussion piston 12 can move beyond the predetermined impact point 25 to the front, in the direction of impact 9 up to the preferably damping stop 30 .
  • the effect of the air spring 13 is reduced or canceled, which is why the percussion piston 12 stops due to the weakened or lacking coupling to the excitation piston 22 .
  • the impact mechanism 4 is activated again when the striker 20 is engaged to the rear stop 29 and the percussion piston 12, the vent opening 36 closes.
  • the striker 20 remains lying 30 for an empty blow preferably in the vicinity of the front stopper, the anvil 20 can move substantially unrestrained in the impact direction 9 to the front stop 30, the rear in the opposite direction to the Stop 29 is the movement, however, against a spring force of at least one air spring 40th
  • the spring force of the air spring 40 is controlled in dependence on the direction of movement of the striker 20 , based on the guide 28 .
  • An at least partially radially extending surface of the striker 20 and an at least partially radially extending surface of the guide 28 form inner surfaces of the pneumatic chamber 40 , which are oriented perpendicular or inclined to the axis 8 .
  • An axial distance of the two radially extending surfaces changes with the movement of the striker 20 and thus the volume of the pneumatic chamber 40 .
  • the volume change causes a change in the pressure within the pneumatic chamber 40 .
  • a rear bounce surface 41 of the thicker section 33 facing the direction of impact 9 can form the first radially extending inner surface of the pneumatic chamber 40 .
  • a rear bounce surface 42 of the guide 28 which points in the direction of impact 9 and defines the rear stop 29 with the rear bounce surface 41 of the thicker section 33 , may be the second radially extending inner surface of the pneumatic chamber 40 .
  • the pneumatic chamber 40 is closed on one side by the guide 28 and on the other side by the striker 22 .
  • a hermetic, airtight seal between the striker 20 and the guide 28 is effected by a first sealing element 43 and a second sealing element 44 .
  • the sealing elements 43 , 44 are arranged offset from one another along the axis 8 .
  • the first sealing element 43 for example, between the two stops 29 , 30, the second sealing element 44 axially outside the two stops 29 , 30 , that is, the respective bouncing surfaces 42 are arranged.
  • the sealing elements 43 , 44 are the radially extending inner surfaces of the pneumatic chamber 40th
  • the sealing elements 43 , 44 are arranged on portions of the striker 20 with different cross-section, whereby the distance of the sealing elements 43 , 44 to the axis 8 is different in size. In other embodiments, at least portions of the sealing elements 43 , 44 are at different distances from the axis 8 . In a projection on a plane perpendicular to the axis 8 , the two seals do not overlap or at least partially do not overlap.
  • the dependence of the air spring 40 on the direction of movement of the striker 20 is achieved in that at least one of the sealing elements 43 , 44 is designed as a valve 50 .
  • An air channel 45 connects the pneumatic chamber 40 to an air reservoir in the environment, eg the machine housing 2 .
  • the valve 50 is arranged, which controls an air flow through the channel 45 .
  • the control takes place in dependence of the movement of the head 20 .
  • the valve 50 opens and air can flow from the reservoir through the channel 45 into the increasing volume of the pneumatic chamber 40 ; the air spring is thereby deactivated.
  • the valve 50 locks the channel 45 when the striker 20 moves against the direction of impact 9 .
  • the pressure in the pneumatic chamber 40 increases with the decreasing volume of the pneumatic chamber 40 , whereby the air spring 40 counteracts the movement of the striker 20 .
  • the valve 50 is designed as an automatic or self-medium-actuated valve 50 , for example a check valve or a throttle check valve.
  • the valve 50 is actuated by an air flow which flows into the valve 50 .
  • the air flow is the result of a pressure difference between the pneumatic chamber 40 and the space 51 connected to it via the valve 50 .
  • the connected space 51 may be a very large air reservoir, eg, the environment, the interior of the machine housing 51 , or any other enclosed, limited volume pneumatic chamber.
  • the air spring 40 pushes a sealing closure body 52 of the valve 50 against a valve port 53 or valve seat of the valve 50 , whereby the valve port 53 is hermetically closed.
  • the closure body 52 is pushed away from the valve opening 53 . Air can flow through the valve opening 53 along the air channel 45 into the pneumatic chamber 40 .
  • a throttle opening 54 may ventilate the pneumatic chamber 40 .
  • the throttle opening 54 may be, for example, a bore through the wall of the guide tube 31 .
  • the area of a flow cross-section (hydraulic cross-section) of the throttle opening 54 is at least two orders of magnitude smaller than the annular cross-sectional area of the pneumatic chamber 40 , eg less than 0.5 percent.
  • the throttle opening 54 is greater than 1/2000 or 1/1500 of the annular cross-sectional area to allow manual insertion of the striker 20 .
  • the flow cross-section or the cross-sectional area of the throttle opening 54 is determined at its narrowest point perpendicular to the flow direction.
  • the volume of the pneumatic chamber 40 changes in proportion to the velocity of the striker 20 and to the annular cross-sectional area of the volume enclosed by the pneumatic chamber 40 . If the throttle 54 to compensate for the change in volume without pressure change, the displaced air must be at least one hundred times the speed of the striker pass the throttle 20 .
  • the flow properties of air set the flow velocity an upper limit, which is why a pressure equalization is possible with a slow but not a fast moving striker 20 .
  • the speed of the striker 20 in the direction of impact 9 is approximately in the range of 1 m / s to 10 m / s at a blank. Accordingly, the volume of the pneumatic chamber 40 increases rapidly.
  • the valve 50 releases in its open position a flow-through surface (hydraulic surface) which is at least 1/30, preferably at least 1/20, or at least 10% of the annular, effective cross-sectional area of the volume of the pneumatic chamber 40 .
  • the hydraulic surface is defined perpendicular to the flow direction in the valve 50 .
  • the effective cross-sectional area is the differential of the volume after the direction of movement, ie the change in volume is determined by the product of the effective cross-sectional area and the longitudinal displacement of the beatpiece 20 .
  • the valve 50 closes and the compression of the closed pneumatic chamber 40 brakes the striker 20 .
  • the throttle opening 54 leaves only a small air flow, whereby the overpressure in the pneumatic chamber 40 is maintained.
  • the air may exit through the orifice 54 at a rate sufficient to allow pressure equalization.
  • the valve 50 may be designed as a throttle valve which leaves a corresponding throttle opening open in a closed / throttled position.
  • FIG. 3 and FIG. 4 show an exemplary embodiment with a valve 60 in the closed or open state.
  • Fig. 5 and Fig. 6 are cross sections through the valve 60 in the planes VV and VI-VI.
  • the valve 60 has a sealing ring 52 as a sealing ring 61 , that is, an annular sealing element which is inserted in a circumferentially extending groove 62 in the thicker portion 33 of the striker 20 .
  • the gap 35 between striker 20 and guide tube 31 is divided by the sealing ring 61 and the groove 62 in two sections along the axis 8 , which corresponds to the subdivided by the valve 50 air passage 45 .
  • air can flow along the gap 35 .
  • the lockable Valve opening is defined by a seat of the sealing ring 61 in the region of a front, ie lying in the direction of impact 9 , groove wall 63 of the groove 62 .
  • the sealing ring 61 is for example an elastic O-ring made of natural or synthetic rubber.
  • a radially outwardly facing surface, radial below outer surface 64 of the sealing ring 61 lies along the entire circumference of the sealing ring 61 positively against the inner wall 32 of the guide tube 31, so that the sealing ring 61 and the guide tube 31 to complete hermetically together.
  • the sealing ring 61 may be radially biased in the guide tube 31 to assist the airtight seal.
  • a thickness 65 of the sealing ring 61 ie a difference from outer radius to inner radius, is preferably less than a depth 66 of the groove 62 .
  • a radially inwardly facing surface, subsequently radial inner surface 67 of the sealing ring 61 is spaced in the radial direction from a groove bottom 68 of the groove 62 at least in a portion along the circumference of the thicker portion 33 .
  • a gap 69 Between the groove bottom 68 and the sealing ring 61 is a gap 69 , can flow through the air along the axis 8 .
  • the sealing ring 61 bears against the front groove wall 63 of the groove 62 with a front end 70 , that is, in the direction of impact 9. Fig. 3 ).
  • the front groove wall 63 and the front end face 70 touch each other at least along an annular closed line around the axis 8 .
  • the front end face 70 may be flattened, for example, to terminate at a surface of the groove wall 63 with the same inclination, for example perpendicular, to the axis 8 .
  • a hermetic seal of the valve 60 results from the pairwise hermetic sealing of the sealing ring 61 with the groove wall 63 , ie the striker 20 , or the guide tube 31 , ie the guide 28 .
  • the movement of the striker 20 against the direction of impact 9 stabilizes the valve 60 in the closed state.
  • the pressure increases to the environment, whereby the sealing ring 61 is pressed against the front groove wall 63 .
  • the sealing ring 61 For the open state of the sealing ring 61 is located with a rear, ie opposite to the direction of impact 9 facing end face 71 on the rear groove wall 72 of the groove 62 at ( Fig. 4 ).
  • a distance of the front groove wall 63 to the rear groove wall 72 is dimensioned such that the sealing ring 61 of the front groove wall 63 at least partially dissolves along the circumference when the sealing ring 61 rests against the rear groove wall 72 .
  • the distance between the groove walls is greater than a dimension of the sealing ring 61 along the axis. 8
  • the sealing ring 61 shifts along the axis 8 of the front groove wall 63 to the rear groove wall 72nd
  • the rear groove wall 72 and / or the rear end face 70 of the sealing ring 61 are structured such that a contact surface along which they contact is interrupted by at least one lying in the contact surface, continuous channel from the groove bottom 68 to the guide tube 31 .
  • one or more radially extending grooves 73 are provided in the rear end face 71 .
  • the sealing ring 61 contacts the rear groove wall 724 only partially along the circumference and air can flow through the grooves 73 .
  • a channel through the open valve 60 thus extends along the front face 72 , the inner radial face 67 and the grooves 73 . The movement of the striker 20 in the direction of impact 9 stabilizes the valve 60 in the open state.
  • the pressure falls below the ambient pressure, for example in the space 51 , the pressure gradient causes an influx of air and a pressing of the sealing ring 61 to the rear groove wall 72nd
  • radially extending grooves can be embedded in the rear groove wall 72 . The air can flow along these grooves, webs between the grooves prevent closing of the grooves by the sealing ring 61 .
  • the rear end face 71 may have other structures instead of grooves 73 defining channels from the radially inner surface 67 to the radially outer surface 64 .
  • the channels can run strictly radially or additionally partially along the circumference of the sealing ring 61 .
  • stiff nubs may be provided which, contrary to the forces occurring during a forward movement of the striker 20 maintain the channels.
  • the sealing ring 61 may have grooves 74 on one of its radial inner surfaces ( Fig. 7 ). This allows a voltage applied to the groove bottom sealing ring 61 to use.
  • the sealing ring 61 throttles when the front end face 70 rests against the front groove wall 63 .
  • a small air flow can flow through between the end face 70 and the front groove wall 63 .
  • thin radial channels can be introduced in the front end face 70 .
  • the effective total cross-sectional area of the channels is less than the effective total cross-sectional area of the channels 73 in the rear face 71 .
  • a cross-sectional area perpendicular to the air flow of the thin channels is limited to at most one-hundredth of the cross-sectional areas of the grooves 73 that are summed over all the grooves 73 and that are perpendicular to the air flow.
  • the first sealing element 43 is realized in the embodiment by the valve 60 moved between the stops 29 , 30 .
  • the second sealing element 44 is axially offset from the rear stop 29 , counter to the direction of impact 9 , and is mounted in an exemplary manner in the guide 28 in a stationary manner.
  • the second sealing element 44 is preferably annular, for example as an O-ring made of rubber.
  • the striker 20 has a cylindrical, rear portion 75 , which is guided by the second sealing element 44 conclusively with its inner radial surface.
  • the length 76 of the rear cylindrical portion 75 is preferably such that at least a portion of the rear portion 75 in the second sealing member 44 is inserted when the striker 20 abuts the front stop 30 to the pneumatic chamber 40 in each position of the striker 20th hermetically seal.
  • the length 76 of the rear portion 75 is at least longer than the distance of the striker 20 between the front stop 30 and the rear stop 29th
  • the second sealing element 44 may be used, for example, in a cylindrical sleeve 77 , which is inserted into the guide tube 31 .
  • the front end sides of the sleeve 77 may form the abutment surfaces 42 for the rear stop 29 .
  • the cross-sectional area of the sleeve 77 may substantially define the cross-sectional area of the pneumatic chamber 40 .
  • the second sealing element 44 may alternatively be mounted on the rear portion 75 of the striker 20 , for example in an annular groove.
  • the sleeve 79 is provided with a preferably smooth cylindrical inner wall, on which the second sealing element 44 slides along.
  • a diameter of the rear portion 75 is smaller than a diameter of the thicker portion 33 , whereby the valve device 60 is arranged at a greater distance from the axis 8 than the second sealing element 44 .
  • the front groove wall 70 may be inclined relative to the axis 8 , for example between 45 degrees and 70 degrees.
  • the inclined groove wall 70 may spread the sealing ring 61 to assist a tight fit on the front groove wall 70 .
  • FIGS. 8 and 9 show an exemplary embodiment with a valve 80 in the closed or open state.
  • 10 and FIG. 11 are cross sections through the valve 80 in the planes XX and XI-XI.
  • the valve 80 has as a closure body a sealing ring 81 which is inserted in a circumferentially extending groove 82 in the thicker portion 33 of the striker 20 .
  • the gap 35 between striker 20 and guide tube 31 forms the channel 45 , which is divided by the groove 81 and the sealing ring 82 along the axis 8.
  • the sealing ring 82 can close the channel 45 .
  • the groove 82 can receive the sealing ring 81 such that the sealing ring 81 is spaced from the inner wall 32 of the guide tube 31 ( Fig. 8 ), ie an air gap 84 between sealing ring 81 and guide tube 31 is.
  • a depth 85 of the groove 82 may be at least as large as a thickness 86 of the sealing ring 81 .
  • a length 87 of a groove bottom 88 may be at least as long as a length 89 of the sealing ring 81 along the axis 8 may be selected.
  • the groove bottom 88 is substantially parallel to the axis 8 and is cylindrical. Air can flow into the pneumatic chamber 40 along the gap 35 .
  • a front groove wall 90 is inclined relative to the axis 8 and preferably defines a conical surface whose radius increases in the direction of impact 9 .
  • the sealing ring 81 is pushed onto the conical, front groove wall 90 .
  • the sealing ring 81 is radially spread apart and its outer diameter is increased, at least to the extent that the radial outer surface 91 of the sealing ring 81 contacts the inner wall 32 of the guide tube 31 (FIG. Fig. 9 ). This results in a hermetic seal between the striker 20 and the guide 28 by their pairs, hermetically sealing contact with the sealing ring 81st
  • the pressure conditions in a backward movement of the striker 20 push the sealing ring 81 on the conical front groove wall 90 and thus cause an automatic closure of the valve 80th During a forward movement, the sealing ring 81 detaches from the conical front groove wall 90 , relaxed in its basic form with a smaller outer diameter and releases the air gap 84 to open the valve 80 .
  • the sealing ring 81 is for example an elastic O-ring made of natural or synthetic rubber.
  • the sealing ring 81 may be formed symmetrically to a plane perpendicular to the axis 8 , ie with identical end faces.
  • the second sealing element 44 can be offset axially relative to the rear stop 29 , counter to the direction of impact 9 , and can be, for example, a sealing ring mounted in a stationary manner in the guide 28 .
  • the second sealing element 44 may be mounted on the rear portion 75 of the striker 20 .
  • FIGS. 12 and 13 show an exemplary embodiment with a valve 100 in longitudinal section and in cross-section in the plane XIII-XIII.
  • a sealing element 101 of the valve 100 has a pivotable lip 102 , which rests against an inner wall 32 of the guide tube 31 .
  • a fixing portion 103 of the sealing member 101 fastens the lip 102 the thicker portion 33 of the striker 20th
  • the lip 102 is preferably resiliently biased to be pressed against the inner wall 32 to close the valve 100 .
  • the illustrated lip 102 is inclined relative to the axis 8 and extends counter to the direction of impact 8 of the striker 20 to the inner wall 32nd
  • the lip 102 encloses with the anvil 20 a space 104 only open towards the rear pneumatic chamber.
  • Air flowing out of the rear pneumatic chamber accumulates in the half-open space 104 and presses the lip 102 against the guide tube 31 .
  • the valve 100 stabilizes in its closed position.
  • An air flow flowing counter to the direction of impact 9 pivots the lip 102 into the half-open space 104 , as a result of which it is detached from the guide tube 31 .
  • the airflow may pass through the open valve 100.
  • the exemplary seal member 101 may be, for example, a pneumatic piston seal or lip seal made of a natural or synthetic rubber.
  • a tubular cylindrical portion of the sealing member 101 serves as a fixing portion 103 to fix the sealing member 101 to the thicker portion 33 .
  • an annular groove is introduced into the anvil 20 , at the groove bottom 88 of the mounting portion 103 rests.
  • the lip 102 is formed by a hollow cone-shaped portion, which adjoins in the radial direction of the attachment portion 103 and widens against the direction of impact 9 . The lip 102 moves away in the direction of impact 9 in the radial direction from the attachment portion 103 and thus also the striker 20 , whereby an air gap 104 is formed.
  • An end face 106 directed counter to the direction of impact 9 is structured with an annular depression 105 , which is delimited in the radial direction by the lip 102 or the attachment section 103 .
  • the recess 105 may have a trapezoidal, rectangular or other depth profile.
  • the sealing element 101 has a V or U-shaped profile, which is closed in the direction of impact 9 .
  • the dimensions and elastic modulus of the lip 102 are adjusted so that the lip 102 can be deformed by an applied air pressure.
  • a wall thickness of the hollow cone is significantly smaller than a dimension of the lip 102 along the axis 8 .
  • a pivoting or folding movement of the lip 102 can take place in the direction of impact 9 away from the striker 20 or counter to the direction of impact 9 toward the striker 20 .
  • An area in which the lip 102 is fixed to the striker 20 , that is immovable in the radial direction, is offset in the impact direction 9 to a region in which the lip 102 rests against the guide tube 31 .
  • the lip 102 may have an area of reduced wall thickness which serves as a solid-state joint.
  • the attachment portion 103 may further include a hinge in which the lip 102 is rotatably supported about an axis.
  • the lip 102 is made of an elastic material and such a small wall thickness that a pressure gradient between the pneumatic chamber 40 bend the lip and thus can detach from the inner wall 32 .
  • the sealing element 101 is anchored in the inner wall and the lip 102 touches the striker 20th
  • the second sealing element 44 can be offset axially relative to the rear stop 29 , counter to the direction of impact 9 , and can be, for example, a sealing ring mounted in a stationary manner in the guide 28 .
  • Fig. 14 shows an exemplary embodiment with a valve 110 in longitudinal section.
  • the valve 110 has no physical closure body, but uses the flow behavior of the air to obtain a blocking effect for an air flow in the direction of impact 9 and a passage effect for an air flow against the direction of impact 9 .
  • the lateral surface 34 of the thicker portion 33 of the striker 20 is structured with a plurality of mutually axially offset, circumferential grooves 111 .
  • the grooves 111 each have a front groove wall 112 and a rear groove wall 113 .
  • the rear groove wall 113 is inclined relative to the axis 8 , and extends counter to the direction of impact 9 radially outward.
  • the rear inclination angle 114 with respect to the axis 8 may be, for example, between 10 degrees and 60 degrees.
  • the front groove wall 112, however, is substantially perpendicular to the axis 8 or may be inclined between 80 degrees and 100 degrees to the axis 8 .
  • a radial depth of the grooves 111 is small, for example in the range of 0.5 mm to 2 mm.
  • incoming air bounces off the steep, front groove walls 112 and forms vortices in the grooves 111th
  • the flow rate is reduced by several orders of magnitude.
  • inflowing air is gently deflected by the flat, rear groove walls 113, whereby the flow speed is influenced only slightly.
  • the second sealing element 44 can be offset axially relative to the rear stop 29 , counter to the direction of impact 9 , and can be, for example, a sealing ring mounted in a stationary manner in the guide 28 .
  • Fig. 15 shows in longitudinal section a further embodiment with a rear air spring 40 , a front air spring 120 and at least one valve 130 for controlling the behavior of the striker 20th
  • the spring force of the rear air spring 40 and the front air spring 120 is controlled depending on the direction of movement of the striker 20 . While in a forward movement, ie in the direction of impact 9 , the striker 20, the air springs 40 , 120 are deactivated or weak, the air springs 40 , 120 together brake a backward movement of the striker 20th
  • the spring force of the air springs 40 , 120 may be different, the pressure-loaded rear air spring 40 may exhibit a greater braking effect than the front air spring 120 .
  • the front pneumatic spring 120 of the front air spring has an at least partially radially extending front inner wall 131 formed by the guide 28 and an at least partially radially extending rear inner wall 132 formed by the striker 20 .
  • the rear pneumatic chamber 40 of the rear air spring has an at least partially radially extending front inner wall 41 , which is formed by the striker 20 , and an at least partially radially extending, rear inner wall 42 , which is formed by the guide 28 .
  • the pneumatic chambers 40 , 120 are closed by the inner wall 32 of the cylindrical or prismatic guide tube 31 .
  • the pneumatic chambers 40 , 120 are closed by the striker 20 .
  • a first sealing element 43 and a second sealing element 44 arranged to seal the rear pneumatic chamber 40 airtight.
  • the front and rear inner walls 41 , 42 of the rear pneumatic chamber 40 are disposed along the axis 8 between the first seal member 43 and the second seal member 44 .
  • a third sealing element 133 is arranged in the direction of impact 9 in front of the front inner wall 131 of the front pneumatic chamber 120 .
  • the front and rear inner walls 131 , 132 of the front pneumatic chamber 120 are located along the axis 8 within the first seal member 43 and the third seal member 133 .
  • the two pneumatic chambers 40 , 120 are connected to each other via an air passage 134 , in which a valve 140 is arranged.
  • the valve 140 is for airflow from the rear pneumatic chamber 40 into the front pneumatic chamber 120 blocking and for an air flow from the front pneumatic chamber 120 in the rear pneumatic chamber 40 can be flowed through.
  • An obturator 52 may be forced into a valve port 53 by airflow from the rear pneumatic chamber 40 closing the valve 140 , an opposing air flow lifting the obturator 52 away from the valve port 53 and opening the valve 140 .
  • the volume of the rear pneumatic chamber 40 is increased and the volume of the front pneumatic chamber 120 is reduced.
  • the volume of air displaced in the front pneumatic chamber 120 may flow through the valve 140 into the rear pneumatic chamber 40 .
  • the volume of the front pneumatic chamber 120 increases and the volume of the rear pneumatic chamber 40 decreases.
  • the valve 140 prevents air flow which would equalize the increased pressure in the rear pneumatic chamber 40 and the reduced pressure in the front pneumatic chamber 120 . The backward movement therefore takes place against the spring force of the two air springs 40 and 120 and is braked.
  • the air passage 134 may extend completely within the guide 28 .
  • the air passage 134 is closed so that all of the air displaced from the front pneumatic chamber 120 is introduced into the rear pneumatic chamber 40 .
  • the coupled via the air duct 134 front and rear pneumatic chamber 40 , 120 have a constant relative to the environment closed air volume, wherein a distribution of the air volume to the two chambers 40 , 120 varies depending on the current position of the striker 20 .
  • FIG. 12 shows an embodiment with the valve 60 pneumatically coupling the front pneumatic chamber 120 and the rear pneumatic chamber 40 .
  • the valve 60 pneumatically coupling the front pneumatic chamber 120 and the rear pneumatic chamber 40 .
  • the air channel 134 between the two pneumatic chambers 40 , 120 is disposed completely within the guide 28 .
  • a front bumper surface of the thicker portion 33 of the striker 20 forms the rear inner wall 132 of the front pneumatic chamber 120 and the rear bounce surface of the thicker portion 33, the front inner wall 41 of the rear pneumatic chamber 40.
  • the front inner wall 131 of the front pneumatic chamber 120 can by a the front stop 30 defining region of the guide 28 may be formed.
  • In the front pneumatic chamber 120 may also be an elastic damping member 30 made of rubber, such as an O-ring, arranged, which mitigates a shock of the striker 20 in the front stop 30 . Projections of the two inner walls 131 , 132 of the front pneumatic chamber 120 on a plane perpendicular to the axis 8 are substantially equal.
  • the rear inner wall 42 of the rear pneumatic chamber 40 may be formed by a surface defining the rear stop 29 of the guide 28 . Projections of the two inner walls 41 , 42 of the rear pneumatic chamber 40 on a plane perpendicular to the axis 8 are substantially equal. Upon movement of the striker 20 , the axial distances between the inner walls of each of the pneumatic chambers 40 , 120 and thus their volumes change. The sum of the two volumes can be constant, for which the areas of the front inner walls projected onto the plane perpendicular to the axis 8 and the correspondingly projected areas of the rear inner walls are the same.
  • the air passage 134 between the pneumatic chambers 40 , 120 forms the gap 35 between the striker 20 and the guide tube 31st Along the axis 8 extending grooves in the lateral surface 34 of the thicker portion 33 may form additional air channels.
  • valve 60 on the thicker section 33 locks against air flow from the rear to the front pneumatic chamber 120 and opens for air flow from the front pneumatic chamber into the rear pneumatic chamber 40 .
  • the construction of the valve 60 can be seen from the previous descriptions.
  • the third sealing element may be a sealing ring 142 made of rubber, which is arranged offset to the front stop 30 axially, opposite to the direction of impact 9 .
  • the third sealing element 133 may for example be inserted in a groove in the guide tube 31 .
  • the striker 20 has a cylindrical, front portion 143 , which is guided by the third sealing element 133 conclusively with its inner radial surface 144 .
  • the length 145 of the front cylindrical portion 143 is preferably such that at least a portion of the front portion 143 in the third sealing element 133 is plugged when the striker 20 abuts the rear stop 29 to the front pneumatic chamber 120 in each position of the striker 20 hermetically seal.
  • the front portion 143 projects beyond the third sealing element 133 in the direction of impact 9 by at least a length corresponding to the path of the striker 20 between the front stop 30 and the rear stop 29 .
  • One Diameter of the front portion 143 is smaller than the diameter of the thicker portion 33 .
  • a sealing ring 146 is mounted on the front portion 143 of the striker 20 , for example in an annular groove (FIG. Fig. 17 ).
  • the sealing ring 146 slides within a cylindrical sleeve 147 in the guide 28 and seals with it in any position of the striker 20 from.
  • An outer radial surface 148 of the sealing ring 146 contacts the sleeve 147 .
  • one-way valve 60 with an axially floating sealing ring 61
  • other one-way valve systems such as those described can be arranged with a conical gate for a sealing ring 80 , a flap valve 100 , a gap sealing valve 110 on the thicker portion 33 .
  • FIGS. 18 and 19 show in longitudinal section or cross-section in the plane XVIII-XVIII another embodiment with a valve 150th
  • the valve 150 is stationarily mounted in the guide 28 and forms the second sealing element 44 .
  • the orientation of the valve 150 is changed with respect to the direction of impact 9 , since the valve 150 is arranged behind the pneumatic chamber 40 as viewed from the tool.
  • valve 150 The structure of the valve 150 largely corresponds to the structure of the explained in connection with valve 50 embodiment. The only significant difference is the opposite orientation of the valve 150 with respect to the direction of impact 9 compared to the valve 50 . Both valves 50 allow air to flow into the pneumatic chamber 40 and prevent leakage of air.
  • the valve 150 has a sealing ring 151 , which is mounted in a circumferential groove 152 in the guide 28 .
  • the sealing ring 151 encloses flush and airtight the rear portion 75 of the striker 20th Between a groove bottom 153 of the groove 152 and the sealing ring 151 is a gap 154 through which air can flow along the axis 8 .
  • the groove 152 is wider than the sealing ring 151 to allow the sealing ring 151 to move along the axis 8 .
  • a front groove wall 155 and a front end face 156 of the sealing ring are structured such that upon contact of the sealing ring 151 on the front groove wall 155, radial channels 157 remain free between the sealing ring 151 and the front groove wall 155 .
  • the channels 157 may be imprinted , for example, as grooves in the front end face 156 of the sealing ring 151 .
  • the rear groove wall 158 of the groove 152 and the rear end face 159 of the sealing ring 151 can hermetically seal with each other along a closed ring line about the axis 8 .
  • the sealing ring 151 against the front Groove wall 155 is pressed, in addition supported by the along the rear portion 75 of the striker 20 in the pneumatic chamber 40 incoming air, whereby the valve 150 is opened or kept open.
  • the sealing ring 151 is pressed against the rear groove wall 158 , in addition supported by the building up pressure in the pneumatic chamber 40 , whereby the valve 150 is closed or kept closed.
  • the first sealing element 43 between the stops can for example be realized by a sealing ring made of rubber, for example an O-ring, which is used immovably in an annular groove 160 in the thicker section 33 .
  • a valve for example, the valve 60 of the previous embodiment, the first sealing element 43 form.
  • Fig. 20 shows in longitudinal section a further embodiment with a stationary valve 170 arranged.
  • the first sealing element 43 may be a permanently sealing sealing element or a valve.
  • the valve 170 forms the second sealing element 44 by means of a groove 171 , which is embedded in an inner wall 172 of the guide 28 , and an annular sealing element 173 , which is inserted into the groove 171 and surrounds the rear portion 75 of the striker 20 .
  • the groove 171 is arranged axially, counter to the direction of impact 9 to the rear stop 29 .
  • a front groove wall 174 of the groove 171 is substantially perpendicular to the axis 8 while the rear groove wall 175 of the groove 171 is inclined relative to the axis 8 .
  • the rear groove wall 175 extends counter to the direction of impact 9 radially inwards.
  • the valve 170 locks when air flows out of the pneumatic chamber 40 by the sealing ring 173 radially compressed by the oblique, rear groove wall 175 and pressed against the striker 20 .
  • Fig. 21 shows an embodiment in which a valve 180 is mounted in the guide 28 .
  • the construction of the valve 180 may correspond to the valve 100 .
  • the valve 180 is arranged axially offset relative to the direction of impact 9 to the rear stop 29 of the striker 20.
  • a sealing ring 181 of the valve 180 has an annular lip 182 , which extends in the direction of impact 9 radially inwardly up to the rear portion 75 of the striker 20 and contacts it.
  • the lip 182 is pivotally supported by a solid-state joint in the guide 28 .
  • the solid state joint is further away from the pneumatic chamber 40 along the axis 8 than the area where the lip 182 contacts the striker 20 .
  • the lip 182 locks against leakage of air from the pneumatic chamber 40 allows air to flow into the pneumatic chamber 40th
  • the first sealing element 43 may be a permanently sealing sealing element or a valve, which is inserted, for example, in an annular groove 160 in the guide section 77 .
  • the lip may be pivotally mounted on the rear portion 75 of the striker 20 , wherein the lip in the direction of impact 9 extends radially outward.
  • the lip contacts a sleeve within the guide tube 31 .
  • the axial position of the lip and the length of the rear portion 75 of the striker 20 are selected such that the lip contacts the sleeve in any position of the striker 20 .
  • Fig. 22 shows an exemplary embodiment with a valve 190 in longitudinal section.
  • the valve 190 may be formed analogously to the valve 110 .
  • the sawtooth-shaped profile formed from a plurality of grooves 191 arranged along the axis 8 is formed into a sleeve 192 which is inserted into the guide tube 31 .
  • Front groove walls 193 of the grooves 191 are inclined with respect to the axis 8
  • rear groove walls 194 extend substantially perpendicular to the axis 8 . Air flowing out of the pneumatic chamber 40 bounces off the steep, rear groove walls 194 , and the turbulent flow reduces the flow velocity.
  • An air flowing into the pneumatic chamber 40 from the rear portion 75 of the striker 20 is prevented only slightly by the inclined front groove walls 193 .
  • the grooves are introduced with an oblique, front groove wall and a vertical, rear groove wall in the rear portion 75 of the striker 20 .
  • the rear portion 75 slides in a cylindrical sleeve.
  • Fig. 23 shows a further embodiment with a differently designed striker 200 and an associated guide 201th
  • the guide 201 has an example cylindrical guide tube 202 in which the striker 200 slides.
  • a sleeve 203 is inserted, which locally reduces the inner cross section of the guide tube 202 .
  • the striker 200 has a tapered central portion 206 along the axis 8 between a front portion 204 and a rear portion 205 .
  • the front portion 204 and the rear portion 205 may form the striking surfaces 26 , 27 .
  • the diameter of the central portion 206 is adapted to the sleeve 203 .
  • The, preferably equal, diameter of the front and rear portions 204 , 205 are adapted to the largest inner diameter of the guide tube 201 .
  • the front portion 204 is in the direction of impact 9 and the rear portion 205 in the direction of impact 9 in front of the sleeve 203rd A directed against the direction of impact 9 radially extending surface 207 of the front portion 204 forms together with a direction of impact 9 facing surface 208 of the sleeve 203 the rear stop.
  • the front stop is through the rear section 205 and its pointing in the direction of impact 9 radially extending surface 209 and facing the direction of impact surface 210 of the sleeve 203 is formed.
  • the guide 201 is airtightly connected in the radial direction by a front sealing ring 211 and a rear sealing ring 212 with the front portion 204 and the rear portion 205 of the striker 200 .
  • a one-way valve 213 is arranged, which can seal the sleeve 203 relative to the central portion 206 of the striker 200 depending on the direction of movement of the striker 200 .
  • This defines a front pneumatic chamber 214 and a rear pneumatic chamber 215 which are coupled via the valve 213 .
  • the valve 213 opens when the striker 200 moves in the direction of impact 9 and closes or throttles against the direction of impact 9 when the striker 200 moves.
  • the one-way valve 213 may be, for example, the valve 60 with a slotted, axially floating sealing ring 61 , the valve 80 with a conical gate for a sealing ring, the valve 100 with a flap valve, the valve 110 with a gap sealing valve.
  • only one pneumatic chamber is provided, for which, for example, the front 211 or the rear sealing ring 212 is omitted or not arranged hermetically sealing.
  • Fig. 24 shows an exemplary embodiment with a valve 220 in longitudinal section.
  • the valve 220 is disposed outside the guide 28 .
  • One or more radial bores 221 through the wall of the guide tube 31 are arranged between the rear, second sealing element 44 and the first sealing element 43 on the thicker section 33 of the striker 20 .
  • the valve 220 is designed, for example, as a flap valve or check valve with a spring-mounted flap 222 in front of a first valve opening 223 .
  • the flap 222 is located in front of the first valve opening 223 , viewed from the pneumatic chamber 40 , whereby the valve 220 blocks in the pneumatic chamber 40 at an overpressure.
  • Fig. 25 shows an exemplary embodiment with a valve 230 in longitudinal section and Fig. 26 an associated section in the plane XXV-XXV.
  • the valve openings form one or more radial bores 231 through the wall of the guide tube 31 .
  • the bores 231 are arranged between the rear sealing element 44 and the front sealing element 43 on the thicker portion 33 of the striker 20, regardless of its position.
  • the pneumatic chamber 40 can be vented through the bores 231 .
  • the closure body is formed by a sealing ring 232 , which on the inner wall 32 of the Guide tube 31 abuts the axial height of the bores 231 .
  • the sealing ring 232 may have radially protruding dome-shaped dimples 233 , which engage in conical openings 234 of the bores 231 and can hermetically seal them.
  • the sealing ring 232 is pressed against the holes 231 and closes them.
  • the sealing ring 232 is radially compressed and air can flow into the pneumatic chamber 40 .
  • Fig . 27 shows a further embodiment in which two pneumatic chambers 40 , 120 are connected by one or two valves 240 outside the guide 28 .
  • Both pneumatic chambers 40 , 120 each have an opening, for example a radial bore 241 in the guide tube 31 .
  • An outside of the guide 28 extending, preferably closed, channel 242 connects the two pneumatic chambers 40 , 120th In the channel 242 , the valve 240 is switched.
  • the valve 240 may be, for example, a check valve or a throttle check valve, which can be flowed through in the direction of the rear pneumatic chamber 40 . The amount of air flowing out of the front chamber 120 is completely absorbed by the rear chamber.
  • Fig. 28 shows a further embodiment with two pneumatic chambers 40 , 120 and a valve 250 through which the two chambers are coupled.
  • an air channel 251 is arranged outside the guide 28 .
  • the front pneumatic chamber 120 and the rear pneumatic chamber 40 are each connected via a front opening 252 and a rear opening 253 , for example in the radially closing guide tube 31 , with the air channel 252 .
  • the rear opening 253 is preferably permanently open.
  • On the guide tube 31 is located on a blade 254 , which covers the front opening 252 airtight.
  • the blade 254 is elastically or pivotally mounted via a hinge 255 . Airflow from the front pneumatic chamber 120 may lift the fin 254 in the area of the front opening 252 and flow through the air passage 251 into the rear pneumatic chamber 40 .
  • a sleeve 256 can cover the front opening 252 and rear opening 253 at the same time and laterally flush with the guide 28 .
  • the air channel 251 extends within the sleeve 256 .
  • the fin 254 may be formed, for example, by a tube of rubber which is extended over the front opening 252 and the rear opening 253 . In the region of the rear opening 253 , an opening may be provided in the hose.
  • Fig. 29 shows a further embodiment with two pneumatic chambers 40 , 120 and a valve 260 via which the two chambers are coupled.
  • An air channel 261 extends outside of the guide tube 28 and is connected via a front opening 262 with the front pneumatic chamber 120 and via a rear opening 263 with the rear pneumatic chamber 40 .
  • the air channel 261 has a plurality of constrictions arranged one behind the other in the longitudinal direction.
  • the constrictions have a vertical facet 264 toward the rear pneumatic chamber 40 and an inclined facet 265 toward the front pneumatic chamber 266 .
  • the inclined facets 265 have an angle between 20 degrees and 60 degrees to the longitudinal direction of the air channel 261 .
  • the air channel 261 has a preferred flow direction from the front pneumatic chamber 120 to the rear pneumatic chamber 40 and blocks in the opposite direction.
  • the air duct 261 may be formed by a tube 266 which is fitted over the guide pipe 31 and introduced into the guide pipe 31 front and rear opening 262, the 263rd
  • the constrictions may be defined by a profile on the guide tube 31 and / or a profile in the tube 266 .
  • Fig. 30 shows a further embodiment in which two independent valves for two pneumatic chambers 40 , 120 are provided.
  • the pneumatic chambers 40 , 120 are not coupled.
  • the front pneumatic chamber 120 is coupled to the environment via a first valve 270 .
  • the first valve 270 is against the ingress of air into the front pneumatic chamber 120 .
  • a second valve 271 couples the rear pneumatic chamber 40 to the atmosphere and blocks leakage of air from the rear pneumatic chamber 40 .
  • the two pneumatic chambers 40 , 120 are separated by the first sealing element in the exemplary embodiment of a sealing ring 272 , which is arranged axially between the two valves 270 , 272 .
  • the two valves 270 , 271 may be formed, for example, by the illustrated one-way valve 60 or other one-way valves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP11164392.0A 2010-06-10 2011-05-02 Machine-outil manuelle dotée d'une sonnette pneumatiqueet et son procédé de contrôle Active EP2394793B1 (fr)

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DE102010029915A DE102010029915A1 (de) 2010-06-10 2010-06-10 Werkzeugmaschine und Steuerungsverfahren

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EP2394793A1 true EP2394793A1 (fr) 2011-12-14
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US (1) US9044847B2 (fr)
EP (1) EP2394793B1 (fr)
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EP2684646A1 (fr) * 2012-07-12 2014-01-15 HILTI Aktiengesellschaft Machine-outil manuelle
EP2857150A1 (fr) * 2013-10-03 2015-04-08 HILTI Aktiengesellschaft Machine-outil manuelle
EP2653269A3 (fr) * 2012-04-19 2017-01-04 HILTI Aktiengesellschaft Machine-outil
EP2551062B1 (fr) * 2011-07-26 2019-04-17 Black & Decker Inc. Marteau

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DE102009026542A1 (de) * 2009-05-28 2010-12-09 Hilti Aktiengesellschaft Werkzeugmaschine
DE102012206452A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Handwerkzeugmaschine und Steuerungsverfahren
DE102012208986A1 (de) * 2012-05-29 2013-12-05 Hilti Aktiengesellschaft Meißelnde Werkzeugmaschine
DE102012220886A1 (de) * 2012-11-15 2014-05-15 Hilti Aktiengesellschaft Werkzeugmaschine
US10131042B2 (en) 2013-10-21 2018-11-20 Milwaukee Electric Tool Corporation Adapter for power tool devices
EP2871028A1 (fr) * 2013-11-11 2015-05-13 HILTI Aktiengesellschaft Machine-outil manuelle
EP2886261A1 (fr) * 2013-12-18 2015-06-24 HILTI Aktiengesellschaft Machine-outil manuelle
EP3028821A1 (fr) * 2014-12-03 2016-06-08 HILTI Aktiengesellschaft Procédé de contrôle pour une machine-outils portative
EP3028820A1 (fr) * 2014-12-03 2016-06-08 HILTI Aktiengesellschaft Machine-outils portative et procédé de commande associé
EP3359747B1 (fr) * 2015-10-05 2021-04-14 Angus Robson Marteau à impact et à va-et-vient
US11613869B2 (en) * 2015-10-05 2023-03-28 Terminator Ip Limited Reciprocating impact hammer
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
EP3281747A1 (fr) * 2016-08-09 2018-02-14 HILTI Aktiengesellschaft Machine-outil portative
TWI606900B (zh) * 2017-08-16 2017-12-01 Jian Xiu Liao Carbon fiber seat for pneumatic hammer
WO2019079560A1 (fr) 2017-10-20 2019-04-25 Milwaukee Electric Tool Corporation Outil à percussion
EP3743245B1 (fr) 2018-01-26 2024-04-10 Milwaukee Electric Tool Corporation Outil à percussion
EP3627132B1 (fr) * 2018-09-18 2022-06-08 GF Machining Solutions AG Dispositif inducteur de chocs automatique
EP3670096A1 (fr) * 2018-12-21 2020-06-24 Hilti Aktiengesellschaft Machine-outil portative
WO2020150622A1 (fr) * 2019-01-17 2020-07-23 Carlson Donald W Système de marteau de sécurité motorisé à plusieurs courses
US11945087B2 (en) 2019-03-29 2024-04-02 Tien-I Industrial Co., Ltd. Impact tool head
EP4382254A1 (fr) 2022-12-07 2024-06-12 Hilti Aktiengesellschaft Mécanisme de percussion pour un outil électrique portatif et outil électrique portatif

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EP0759341A2 (fr) * 1995-08-18 1997-02-26 Makita Corporation Marteau perforateur avec mécanisme de prévention des frappes à vide
EP1967328A2 (fr) * 2007-03-08 2008-09-10 HILTI Aktiengesellschaft Machine-outil manuelle dotée d'une sonnette pneumatique
GB2458523A (en) * 2008-03-18 2009-09-23 Bosch Gmbh Robert Portable machine tool with device for holding striker in idling position

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2551062B1 (fr) * 2011-07-26 2019-04-17 Black & Decker Inc. Marteau
EP2653269A3 (fr) * 2012-04-19 2017-01-04 HILTI Aktiengesellschaft Machine-outil
EP2684646A1 (fr) * 2012-07-12 2014-01-15 HILTI Aktiengesellschaft Machine-outil manuelle
CN103538032A (zh) * 2012-07-12 2014-01-29 喜利得股份公司 手持式工具机
US10058987B2 (en) 2012-07-12 2018-08-28 Hilti Aktiengesellschaft Hand-held power tool
EP2857150A1 (fr) * 2013-10-03 2015-04-08 HILTI Aktiengesellschaft Machine-outil manuelle
WO2015049133A1 (fr) * 2013-10-03 2015-04-09 Hilti Aktiengesellschaft Machine-outil manuelle
US10814467B2 (en) 2013-10-03 2020-10-27 Hilti Aktiengesellschaft Handheld power tool
US11878401B2 (en) 2013-10-03 2024-01-23 Hilti Aktiengesellschaft Handheld power tool

Also Published As

Publication number Publication date
CN102275151A (zh) 2011-12-14
US9044847B2 (en) 2015-06-02
DE102010029915A1 (de) 2011-12-15
EP2394793B1 (fr) 2019-11-20
US20110303429A1 (en) 2011-12-15
CN102275151B (zh) 2015-08-05

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