EP2394795B1 - Machine-outil - Google Patents

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Publication number
EP2394795B1
EP2394795B1 EP20110166470 EP11166470A EP2394795B1 EP 2394795 B1 EP2394795 B1 EP 2394795B1 EP 20110166470 EP20110166470 EP 20110166470 EP 11166470 A EP11166470 A EP 11166470A EP 2394795 B1 EP2394795 B1 EP 2394795B1
Authority
EP
European Patent Office
Prior art keywords
pneumatic chamber
stop surface
axis
striker
cross
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
EP20110166470
Other languages
German (de)
English (en)
Other versions
EP2394795A1 (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 EP2394795A1 publication Critical patent/EP2394795A1/fr
Application granted granted Critical
Publication of EP2394795B1 publication Critical patent/EP2394795B1/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
    • 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
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B25D17/245—Damping the reaction force using a fluid
    • 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
    • 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
    • B25D2250/365—Use of seals

Definitions

  • the present invention relates to a machine tool, in particular a hand-held chiseling machine tool according to the preamble of claim 1 and as from EP 0 133 161 A1 and the EP 0 933 169 A2 known.
  • 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, cf. US 6116352 A .
  • 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 in a guide along an axis.
  • a pneumatic chamber has a volume that varies with movement of the anvil along the axis.
  • a pneumatic chamber is completed by the striker, the guide and a self-medium-actuated valve device. The volume of the pneumatic chamber varies with movement of the striker along the axis.
  • the self-medium-actuated valve device has in a flow channel between the striker and the guide in a bearing along the axis between two positions movable sealing element.
  • the flow channel has in a first of the two positions of the sealing element adjacent to a first abutment surface of the bearing a first cross-sectional area and the flow channel has in a second of the two position of the sealing element adjacent to the first abutment surface along the axis offset second abutment surface of the bearing has a second cross-sectional area ,
  • the second cross-sectional area is larger than the first cross-sectional area.
  • the self-medium-actuated valve device may, for example, have a groove embedded in the anvil or in the guide and a sealing element.
  • the sealing element is movable in the groove along the axis between a first and a second groove wall.
  • the flow channel of the valve device has in a first position of the sealing element adjacent to the first Nutwand the first cross-sectional area and in a second position of the sealing element adjacent to the second groove wall, the second cross-sectional area which is larger than the first cross-sectional area. Adjacent to the first groove wall, the sealing element closes or throttles an air flow into and out of the pneumatic chamber. The striker undergoes a braking action by the closed pneumatic chamber as it slides back into the tool holder. Adjacent to the second groove wall, a larger air flow through the second cross-sectional area of the flow channel is possible. When moving in the direction of impact, the valve device allows a pressure equalization in the pneumatic chamber, which is why no braking effect occurs.
  • a volume of the pneumatic chamber is increasing when the striker is moving in the direction of impact, and the first abutment surface of the bearing faces the pneumatic chamber, e.g. the groove is arranged with the second groove wall facing the pneumatic chamber.
  • the sealing element is pushed in an air flow from the pneumatic chamber in the direction of the pneumatic chamber facing abutment surface of the bearing.
  • air should be able to flow into the pneumatic chamber as the striker moves forward and the volume increases.
  • the second abutment surface of the bearing faces the pneumatic chamber, e.g. arranged the groove facing the first groove wall of the pneumatic chamber.
  • a further embodiment provides for the two pneumatic chambers, which are connected by the self-medium-actuated valve device.
  • the invention provides that the flow channel extends between the first abutment surface of the bearing and a first abutment surface of the sealing element facing the first abutment surface of the bearing and between the second abutment surface of the bearing and a second abutment surface of the sealing element facing the second abutment surface of the bearing.
  • the first gluer cut surface of the flow channel is determined by the space between the first abutment surfaces of bearing and sealing element, when they abut each other.
  • the second abutment surface of the bearing and / or a stop surface facing the second abutment surface of the bearing, that is to say the second abutment surface, of the sealing element can have grooves extending at least partially radially, ie perpendicular to the axis.
  • the grooves define the second cross-sectional area greater than zero and allow air exchange into and out of the pneumatic chamber, even when the sealing member abuts the second groove wall.
  • the two second stop surfaces of the bearing and Seal element close only partially flush, eg due to the grooves.
  • the second cross-sectional area is nonzero and an airflow may flow through the flow channel. If the two first abutment surfaces are flush with each other, the first cross-sectional area is equal to zero.
  • the groove and the sealing element can run in an annular manner about the axis and the sealing element in the first position, the guide and the striker each touching a closed line around the axis.
  • An embodiment provides that a channel extends from the first groove wall to the second groove wall between a groove bottom of the groove and the sealing element.
  • the flow channel of the valve extends between the sealing element and the body, in which the groove is introduced.
  • the first groove wall is inclined with respect to the axis by less than 60 degrees and the second groove wall with respect to the axis inclined by at least 80 degrees.
  • An embodiment provides that the first cross-sectional area of the flow channel is at most one tenth of the second cross-sectional area of the flow channel.
  • the striker has a prismatic first section and a second section with a cross-sectional area that is larger than the first section, wherein the valve device is arranged in the second section of the striker.
  • Prismatic are bodies having a constant cross-section along an axis, e.g. Cylinder.
  • One embodiment provides that a to the self-medium actuated valve means offset along the axis provided a seal between the striker and the guide for sealing the pneumatic chamber, wherein the self-medium-actuated valve means and the seal are arranged at different distances from the axis.
  • 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 be determined. 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 valve device may be formed as a throttle valve device.
  • 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 the first cross-sectional area of the flow channel.
  • the first abutment surface of the bearing and / or a stop surface of the sealing element facing the first abutment surface of the bearing may have grooves extending radially at least partially perpendicular to the axis. A sum over its cross-sectional area is less than one-hundredth of the effective cross-sectional area of the pneumatic chamber.
  • One embodiment has a pneumatic striking mechanism, which is arranged with its percussion piston in the direction of impact on the striker, and a tool holder for receiving a tool on which the striker is arranged strikingly in the direction of impact.
  • 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.
  • 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 an excitation 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 optimally for 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 which limit an 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 .
  • 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, but the movement is in the opposite direction toward the rear stop 29 against a spring force 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 .
  • Sealing 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.
  • Between the two 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.
  • At least portions of the sealing elements 43 , 44 are at different distances from 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 as a function of the movement of the beatpiece 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 may flow through the valve port 53 along the air passage 45 into the pneumatic chamber 40 .
  • 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 .
  • the valve 50 at its narrowest point perpendicular to the flow direction has an opening with a cross-sectional area (hydraulic cross-section) which preferably does not fall below 1/30, eg 1/20, 10% of the effective cross-sectional area of the pneumatic chamber 40 .
  • the displaced air flows through the open valve 50 at about 30 times, respectively 20 times, 10 times the speed of the striker 20 .
  • 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 displaced air must pass through the throttle 20 at least one hundred times the speed of the striker.
  • 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. Through the open valve 50 , air flows into the pneumatic chamber 40 at a high rate, so that pressure equalization rapidly occurs. When the striker 20 is reflected at the striker stop 30 , its velocity against the direction of impact 9 may be of the same order of magnitude. The valve 50 closes and the compression of the closed pneumatic chamber 40 brakes the striker 20 .
  • the throttle opening 54 allows only a small air flow leak, whereby the pressure 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 closable 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 of 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 in the radial direction of a groove bottom 68 of the groove 62 spaced at least in a portion along the circumference of the thicker portion 33. 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 is located with a front, ie in the direction of impact 9 facing, end face 70 on the front groove wall 63 of the groove 62 at ( 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 end surface 72 , the radially inner surface 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 surface 70 abuts 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 end 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 surfaces 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 on the be attached to 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 a non-inventive 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 80.
  • the sealing ring 81 detaches from the conical front groove wall 90, relaxed in its basic form 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 .
  • 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 channel 134 between the pneumatic chambers 40, 120 forms the gap 35 between the striker 20 and the guide tube 31.
  • the air channel 134 between the pneumatic chambers 40, 120 forms the gap 35 between the striker 20 and the guide tube 31.
  • Along the axis 8 extending grooves in the lateral surface 34 of the thicker portion 33 may form additional air channels.
  • the 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 understood from the foregoing descriptions.
  • the third sealing element may be a sealing ring 142 made of rubber, which is arranged offset to the front stop 30 axially, in 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 .
  • a 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. 13 ).
  • 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. 14 and 15 show in longitudinal section or cross-section in the plane XV-XV another embodiment with a valve 150.
  • the valve 150 is mounted stationary in the guide 28 and forms the second sealing element 44. Compared to the previous embodiments, the orientation of the valve 150 with respect to the direction of impact 9 , since the valve 150 is located behind the pneumatic chamber 40 when 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
  • 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 in such a way that when the sealing ring 151 abuts 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, for example, be impressed 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 With the forward movement of the striker 20 , the sealing ring 151 is pressed against the front groove wall 155 , in addition supported by the air flowing along the rear portion 75 of the striker 20 in the pneumatic chamber 40 , 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. 16 shows in longitudinal section a non-inventive 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. 17 shows a further embodiment with a differently designed striker 200 and an associated guide 201th
  • the guide 201 has a cylindrical, for example 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 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 formed by the rear portion 205 and its radially extending surface 209 pointing in the direction of impact 9 and the direction 210 facing the impact direction of the sleeve 203 .
  • 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. 18 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.
  • Fig. 19 shows a further embodiment with a valve 280 in a longitudinal section through the striking mechanism 4 , Fig. 20 in a cross section through the valve 280 in the plane XX-XX and Fig. 21 with an enlarged detail.
  • the thicker middle section 33 has a radially projecting rib 283 which, for example, runs closed around the circumference.
  • the rib 282 sealing ring 281 is slipped, which spans the central portion 33 .
  • the sealing ring 281 has a groove 282 in which the rib 283 engages.
  • the groove 282 is wider than the rib 283 and a groove bottom 287 is spaced from a roof surface 286 of the rib 283 .
  • the sealing ring 281 is preferably offset on a lateral surface 293 of the central portion 33 to the rib 283 .
  • a plurality of axially extending grooves 290 are introduced into a surface 291 facing the anvil 20 such that the surface 291 together with the groove 292 forms at least one continuous axially extending channel between the anvil 20 and the sealing ring 281 .
  • an air flow through the valve 280 can flow.
  • the striker 20 can move relative to the sealing ring 281 along the axis 8 .
  • a front end face 284 of the rib 283 may abut a front groove wall 288 of the groove 282 .
  • a plurality of radially extending grooves 292 are introduced in the groove wall 288 .
  • the radial grooves 292 form an air passage having a non-zero cross-sectional area.
  • the front end face 284 of the rib 283 and the front groove wall 289 are perpendicular to the axis 8 in the illustrated embodiment.
  • a rear end face 285 of the rib 283 abut against a rear groove wall 289 of the groove 282 .
  • the rear end face 285 and the rear groove wall 289 are preferably form-fitting, whereby an air flow between the two surfaces in the second position can be prevented.
  • the sealing ring 281 is axially movable in the guide 28 , ie the guide tube 31 . In a leading striker 20 of the sealing ring 281 is taken, the front 285 abuts the front groove wall 288 (first position).
  • air may flow along a flow channel defined by the axial grooves 290 , the radial grooves 292 along the front groove wall 288 and the front end surface 284 , the cavity between the groove bottom 287 and the roof surface 286 of the rib 283 , and FIGS spaced apart rear groove wall 289 and rear end face 285 of the rib 283 is formed.
  • a returning striker 20 of the sealing ring 281 is also taken, now the rear end face 284 rests against the rear groove wall 287 .
  • the sealing ring 281 is flush, hermetically sealed, against the inner wall 32 of the guide tube 31 , whereby the flow channel of the valve 280 is pinched off.
  • the cross section of the flow channel is now determined by the two adjoining rear surfaces.
  • the radially extending grooves 292 are alternatively or additionally arranged in the front end face 284 of the rib 283 .
  • the pneumatic chamber 40 may be closed by the second sealing element 44 , preferably a permanently sealing immovable sealing ring which encloses a rear end 75 of the striker 20 .
  • Fig. 22 shows in a detailed view of a stationary valve 300 on the sleeve 77th
  • the sleeve 77 has a projecting rib 303 , over which a movable sealing ring 301 is slipped with a groove 302 .
  • the arrangement of the sealing ring 301 is arranged mirrored to a plane perpendicular to the axis 8 .
  • a groove wall 308 with radially extending grooves 312 faces a rear end surface 304 of the rib 303 .
  • the rear end surface 304 faces away from the pneumatic chamber 40 .
  • a front groove wall 309 is preferably smooth and faces a flush front end face 305 of the rib 303 .
  • the sealing ring 301 is moved by the air streams in and out of the pneumatic chamber 40 .
  • Air flow into the pneumatic chamber 40 shifts the sealing ring toward the pneumatic chamber 40 , thereby abutting the rear surfaces with the radial grooves 312 .
  • the valve 300 is open. An airflow from the pneumatic chamber 40 displaces the sealing ring 301 away from the pneumatic chamber 40 , whereby the two flush front surfaces 305 , 309 abut each other.
  • the valve 300 is closed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Claims (12)

  1. Machine-outil comportant :
    un percuteur (20),
    un guide (28) dans lequel le percuteur (20) est guidé le long d'un axe (8),
    un dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300),
    une chambre pneumatique (40) qui est fermée par le percuteur (20), le guide (28) et le dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300), le volume de la chambre pneumatique (40) variant en fonction d'un mouvement du percuteur (20) le long de l'axe (8),
    dans laquelle le dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300) comporte un élément d'étanchéité (61, 151, 281, 301) mobile entre deux positions dans un palier (62, 160, 203, 283, 303) le long de l'axe (8) dans un canal d'écoulement entre le percuteur (20) et le guide (28),
    dans laquelle le canal d'écoulement présente une première aire de section transversale dans une première des deux positions de l'élément d'étanchéité en butée contre une première surface d'arrêt (63, 158, 285, 305) du palier (62, 160, 203, 283, 303), et le canal d'écoulement présente une seconde aire de section transversale dans une seconde des deux positions de l'élément d'étanchéité en butée contre une seconde surface d'arrêt (72, 155, 284, 304) du palier (62, 160, 203, 283, 303) décalée par rapport à la première surface d'arrêt le long de l'axe (8), et la seconde aire de section transversale est plus grande que la première aire de section transversale, caractérisée en ce que
    le canal d'écoulement entre la première surface d'arrêt (63, 158, 285, 305) du palier s'étend entre la première surface d'arrêt (63, 158, 285, 305) du palier et une première surface d'arrêt (70, 159, 289, 309) de l'élément d'étanchéité (61, 151, 281, 301) attribuée à la première surface d'arrêt du palier, et entre la seconde surface d'arrêt (72, 155, 284, 304) du palier et une seconde surface d'arrêt (71, 156, 288, 308) de l'élément d'étanchéité attribuée à la seconde surface d'arrêt du palier.
  2. Machine-outil selon la revendication 1, caractérisée en ce que si un volume de la chambre pneumatique (40) augmente lors d'un mouvement du percuteur (20) dans une direction de percussion (9), la première surface d'arrêt (63, 158, 285, 305) du palier est agencée dirigée vers la chambre pneumatique (40), et si un volume de la chambre pneumatique (120) diminue lors d'un mouvement du percuteur (20) dans la direction de percussion (9), la seconde surface d'arrêt (72, 155, 284, 304) du palier est agencée dirigée vers la chambre pneumatique (120).
  3. Machine-outil selon la revendication 1 ou 2, caractérisée par une chambre pneumatique supplémentaire (120) qui est fermée par le percuteur (20), le guide (28) et le dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300), dans laquelle le volume de la chambre pneumatique (40) augmente lors d'un mouvement du percuteur (20) dans une direction de percussion (9), et un volume de la chambre pneumatique supplémentaire (120) diminue lors d'un mouvement du percuteur (20) dans la direction de percussion (9), et la chambre pneumatique (40) et la chambre pneumatique supplémentaire (120) sont reliées par le dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300).
  4. Machine-outil selon l'une quelconque des revendications précédentes, caractérisée en ce que la seconde surface d'arrêt (72, 155, 284, 304) du palier et/ou une surface d'arrêt (71, 156, 288, 308) de l'élément d'étanchéité attribuée à la seconde surface d'arrêt du palier comporte des cannelures (73, 157, 292, 312) s'étendant radialement et au moins partiellement perpendiculairement à l'axe (8).
  5. Machine-outil selon l'une quelconque des revendications précédentes, caractérisée en ce que le palier est formé par une rainure (62) dans le percuteur ou une rainure (152) dans le guide, et l'élément d'étanchéité est axialement mobile dans la rainure inséré entre la première surface d'arrêt formée par une première paroi de rainure et la seconde surface d'arrêt formée par une seconde paroi de rainure.
  6. Machine-outil selon la revendication 5, caractérisée en ce que la rainure et l'élément d'étanchéité s'étendent de manière annulaire autour de l'axe (8) et dans la première position, l'élément d'étanchéité est respectivement en contact avec le guide et le percuteur le long d'une ligne fermée autour de l'axe (8).
  7. Machine-outil selon la revendication 5 ou 6, caractérisée en ce que la première paroi de rainure est inclinée par rapport à l'axe (8) de moins de 60 degrés, et la seconde paroi de rainure est inclinée par rapport à l'axe (8) de moins de 80 degrés.
  8. Machine-outil selon l'une quelconque des revendications précédentes, caractérisée en ce que le percuteur comporte une première partie prismatique (75) et une seconde partie prismatique (33) ayant une aire de section transversale plus grande que la première partie, dans laquelle le dispositif de clapet (60) est agencé sur la seconde partie (33) du percuteur (20).
  9. Machine-outil selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un joint entre le percuteur (20) et le guide (28), décalé par rapport au dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300) le long de l'axe (8), est prévu pour rendre la chambre pneumatique (40) étanche, dans laquelle le dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300) et le joint sont agencés à différentes distances par rapport à l'axe (8).
  10. Machine-outil selon l'une quelconque des revendications précédentes, caractérisée en ce que la première aire de section transversale du canal d'écoulement est au plus égale à un centième de la seconde aire de section transversale du canal d'écoulement.
  11. Machine-outil selon l'une quelconque des revendications précédentes, caractérisée par un étranglement (54) qui relie la chambre pneumatique (40) à un réservoir d'air, dans laquelle une aire de section transversale de l'étranglement correspond au plus à un centième de la seconde aire de section transversale du dispositif de clapet actionné par son propre fluide (60, 150, 200, 280, 300).
  12. Machine-outil selon la revendication 11, caractérisée en ce que la première surface d'arrêt (63, 285, 305) du palier et/ou une surface d'arrêt (70, 287, 308) de l'élément d'étanchéité attribuée à la première surface d'arrêt du palier comporte au moins en partie des cannelures s'étendant radialement et au moins partiellement perpendiculairement à l'axe (8), et une somme de leur aire de section transversale est inférieure à un centième de l'aire de section transversale de la chambre pneumatique (40, 120).
EP20110166470 2010-06-10 2011-05-18 Machine-outil Active EP2394795B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010029918 DE102010029918A1 (de) 2010-06-10 2010-06-10 Werkzeugmaschine

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EP2394795B1 true EP2394795B1 (fr) 2013-03-13

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EP (1) EP2394795B1 (fr)
CN (1) CN102275152B (fr)
DE (1) DE102010029918A1 (fr)

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EP2857150A1 (fr) * 2013-10-03 2015-04-08 HILTI Aktiengesellschaft Machine-outil manuelle
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WO2015143762A1 (fr) 2014-03-27 2015-10-01 Techtronic Power Tools Technology Limited Dispositif d'entraînement d'attache motorisé et son procédé de fonctionnement
ES2727934T3 (es) * 2014-09-30 2019-10-21 Cgm Spa Dispositivo para generar una fuerza impulsiva y una pistola de clavos para este
EP3181300A1 (fr) * 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil portative a percussion
WO2019079560A1 (fr) 2017-10-20 2019-04-25 Milwaukee Electric Tool Corporation Outil à percussion
US11059155B2 (en) 2018-01-26 2021-07-13 Milwaukee Electric Tool Corporation Percussion tool

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Also Published As

Publication number Publication date
US20110303430A1 (en) 2011-12-15
US8939229B2 (en) 2015-01-27
DE102010029918A1 (de) 2011-12-15
CN102275152B (zh) 2016-08-03
EP2394795A1 (fr) 2011-12-14
CN102275152A (zh) 2011-12-14

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