EP1607187B1 - Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion - Google Patents

Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion Download PDF

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Publication number
EP1607187B1
EP1607187B1 EP04102799A EP04102799A EP1607187B1 EP 1607187 B1 EP1607187 B1 EP 1607187B1 EP 04102799 A EP04102799 A EP 04102799A EP 04102799 A EP04102799 A EP 04102799A EP 1607187 B1 EP1607187 B1 EP 1607187B1
Authority
EP
European Patent Office
Prior art keywords
breaker device
control sleeve
valve
piston
guide tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP04102799A
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German (de)
English (en)
Other versions
EP1607187A1 (fr
Inventor
Harald Schmitzer
Christoph Würsch
Alexander John
Hans Böni
Alexander Grosser
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
Priority to EP04102799A priority Critical patent/EP1607187B1/fr
Priority to DE502004011101T priority patent/DE502004011101D1/de
Publication of EP1607187A1 publication Critical patent/EP1607187A1/fr
Application granted granted Critical
Publication of EP1607187B1 publication Critical patent/EP1607187B1/fr
Not-in-force 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
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0019—Guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/035—Bleeding holes, e.g. in piston guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/131—Idling mode of tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/141—Magnetic parts used in percussive tools
    • B25D2250/145—Electro-magnetic parts

Definitions

  • the invention relates to degradation devices with electropneumatic drive, in particular to electropneumatic drill and / or chisel hammers.
  • it relates to a device for improving the shutdown behavior of such mining equipment (see, eg US-A-5,975,217 ).
  • an exciter piston is driven by an electric motor which periodically excites a reciprocating piston, which is coupled via a pressure impact pad (hereinafter “air spring”), to and fro.
  • air spring a pressure impact pad
  • the electro-pneumatic impact mechanism should be deactivated as quickly as possible, since after lifting the shock wave generated by the flying piston and running along the tool can no longer be absorbed by the substrate; it is completely reflected.
  • the total shock wave energy in this case must be taken up by the structure of the excavator and the user. Not only the returning shaft, but above all the first shock wave after lifting must be absorbed by the re-storage of the tool holder.
  • special damping elements ensure that no damage to the structure occurs due to repeated reference of the flying piston.
  • the method (a) is realized in practice so that when lifting the device from the ground, the tool and the striker move forward by a few millimeters to centimeters from the user. This axial movement is transmitted to a control sleeve, which
  • Air outlet openings on the guide tube opens. This causes a large leakage in the air spring and thus a pressure equalization to the atmospheric pressure.
  • the excitation piston is now no longer able to generate a negative pressure during the return stroke and to suck in the flying piston again.
  • the hammer mechanism is deactivated.
  • the path of the bonnet or tool when lifting the device from the ground is exploited, but not to control a sleeve, but to extend the percussion or its air spring.
  • the extension of the effective percussion length to the striker path causes the air spring is so soft that the flying piston is not sucked in during the return stroke of the exciter piston.
  • Method (c) requires a dynamic drive.
  • the most common type of drive in power tools of the type mentioned today is the universal motor.
  • This type of engine can not be actively braked - except by a very complex arrangement by turning the current direction in the stator. As soon as the excavator is lifted off the ground, the engine is switched off. When re-pressing the tool to the ground, the speed is increased again.
  • the invention has for its object to improve the shutdown and in particular Nachschlag of electropneumatically operated mining equipment, in particular of drilling and / or chipping hammers.
  • a mining device with electro-pneumatic percussion in particular a drill and / or chisel hammer whose percussion has an electrically driven within a guide tube back and forth driven exciter piston which accelerates a piston of this compressed air spring, which in turn held in a tool holder Powered striking tool, characterized by an activatable when lifting the excavator from the degraded surface valve means over which the pressure acting between the flying and the excitation piston pressure in the percussion is increased.
  • the valve device has a check valve, via which, when the tool is lifted off the ground, the negative pressure arising during the return stroke of the excitation piston between the latter and the flying piston is raised to a higher pressure, in particular ambient pressure.
  • the guide tube has at least one bore in the area of the air spring, here also referred to as "puff hole", and the check valve is displaceable relative to the guide tube and arranged so that that it is aligned when lifting the excavator from the ground by an adjustment on the hole.
  • the check valve is integrated in a control sleeve surrounding the control sleeve, which is displaceable by the adjusting device.
  • the air piston operated via the air spring striking acts on a tool holder associated with the beatpiece
  • the adjusting device for the check valve is preferably actuated by the lifting device when moving forward anvil.
  • the control sleeve can be formed by the adjusting device relative to the guide tube either axially displaceable or rotatable relative to the guide tube.
  • a flap valve integrated into the control sleeve can be formed, for example, by a leaf spring which is clamped on one side and extends transversely to a passage channel in the control sleeve.
  • the solution with integrated in the control sleeve ball valve has the advantage that the bias and thus the trigger pressure of the check valve can be adjusted well via an acting on a compression spring screw.
  • Another basic embodiment variant of the invention for preventing the refueling of the flyer provides for the use of an accumulator device, which increases the pressure in the percussion mechanism upon activation of the valve device at the time of interruption of work and lifting of the tool.
  • the pressure accumulator may be an actuatable via the exciter piston pump, for example, be actuated by the connecting rod of the exciter piston reciprocating pump.
  • a further basic embodiment variant of the invention provides to realize the valve means by means of at least one actively switched valve, such as an electromagnetically actuated valve, such as in the form of a dynamic valve sleeve valve.
  • the valve is formed in particular by an electromagnetically actuated control sleeve, which closes at least one guide tube passing through the through hole to the air spring in a switching position and releases in a different switching position.
  • Another proven and advantageous solution for a dynamic pusher sleeve valve is to move the control sleeve relative to the guide tube of the percussion axially by a voice coil actuator whose displaceable core is formed by the control sleeve.
  • the Fig. 1 shows a schematic side sectional view of a mining device with features of the invention, in the example shown a drill and / or chisel hammer 1, the housing is formed by two parts, namely a handle shell 2 and a motor housing shell 3. This division of the housing is not mandatory; There are other one-, two- or multi-part housing enclosures for devices of this kind.
  • a push button 4 for the ON / OFF circuit, which at certain operating modes via a potentiometer switch at the same time to Motorfaniere- or Torque adjustment can serve.
  • the power is supplied via a connection cable 6.
  • the drive motor is of conventional design and is not shown for reasons of clarity.
  • the excavator has an electropneumatic hammer mechanism 10 with a guide tube 11, in whose rear area an exciter piston 12 by a connecting rod 13 back and forth and is driven back and forth.
  • the excitation piston 12 acts via an air spring 19 on a flying mass 14, which passes on its kinetic energy via a pressure pad 21 to an anvil 15, which in turn axially striking a held in a tool holder 9 tool, in particular a chisel (not shown), acts.
  • the pressure pad 21 is not mandatory. In principle, it is also possible for the flying mass 14 to act directly on the tool or directly on the striker 15.
  • Essential to the invention is a pneumatic air piston brake generally indicated by reference 30 for generating an overpressure between the excitation piston 12 and the flying mass 14, which causes the flying mass 14 is pressed against the striker 15 when depositing the excavation device from the ground.
  • a negative pressure in the air spring 19 and thus a lookup of the flying piston 14 is avoided during the return stroke of the exciter piston 12.
  • a control sleeve 17, also referred to as "pump-up sleeve" the hammer or chisel operation of the mining equipment in the in Fig. 2A illustrated position in which Schnauflöcher 18 are closed by an annular closed portion of the control sleeve 17. If the excavator is set down from the ground, then the striker 15 slips forward by a length ⁇ x of a few millimeters to a centimeter by 2.5 cm in the direction of the tool.
  • FIG. 3A shows an enlarged view of a proven embodiment of the axially displaceable control sleeve 17.
  • This control sleeve 17, which is preferably produced as a plastic molded part consists - like the Fig. 3B can recognize - from a sleeve ring 21 with a number of the Schnauflöcher 18 corresponding plurality of recessed axial chambers 24, in which the flap valves 20 are inserted, and are held by a screw 26 sealingly.
  • the axial chambers 24 are connected via an opening 25 whose number corresponds to the number of Schnauflöcher 18, with the interior of the control sleeve in conjunction.
  • the flap valves 20 essentially consist in each case of a cantilevered leaf spring element 22 which releases or closes an inlet / outlet opening 27 depending on the pressure conditions on one or the other side of the leaf spring element 22.
  • the hardness of the leaf spring element 22 determines the response of the flapper valve 20.
  • the Fig. 4 shows another proven embodiment of the control sleeve 17.
  • ball valves 28 are here provided which release the openings 25 or close.
  • the response of this type of valve can be adjusted sensitively via a set screw 31, via which the bias of a pressure acting on the ball valve spring 29 is determined.
  • the advantage of this design with ball valves is a simpler manufacturing process, since the control sleeve 17 can be made largely completely as an injection molded part, and a good adjustability of the valve bias and thus the response of the check valves.
  • the Fig. 5 shows an embodiment of the electro-pneumatic impact mechanism 10, equipped with the ball valve sleeve according to Fig. 4 as a control sleeve 17.
  • the embodiment corresponds to Fig. 5 that of the Fig. 2A or 2B, so that further explanation is unnecessary.
  • Fig. 6 which in turn shows the already explained electro-pneumatic striking mechanism, but in this case only schematically indicated Control sleeve 17, serves to explain a mathematical estimate of the maximum achievable pressure and the effective forces, in Fig. 6 the term l eff used in the following is registered and illustrated as the "effective percussion length".
  • the mean pressure is to be estimated, which is generated in the percussion mechanism in order to illustrate that the forces are sufficient to accelerate the flying mass 14 forward in the direction of the tool within a short time.
  • A is the end face of the excitation piston and T is the period of an excitation piston cycle.
  • E denotes the complete elliptic integral of the second kind.
  • ⁇ denotes a general argument for the definition of the complete elliptic integral of the second kind (Eq. It is the integration variable to be integrated after.
  • E (x) can be evolved around zero into a Taylor series.
  • e x ⁇ 2 - ⁇ ⁇ x 2 - 3 ⁇ ⁇ ⁇ x 2 128 - 5 ⁇ ⁇ ⁇ x 3 512 + O x 4
  • a mining device of the type mentioned, in particular a drill and / or chisel, is all the more user-friendly, the lower the contact pressure, which must apply the user, so that the device after a business interruption z. B. when settling of underground, starts again quickly and works stably. By generating a higher pressure between the exciter piston 12 and the flying piston 14 when the device is discontinued, the pressing force expended for the restart is increased somewhat.
  • the flap valve 20, equipped axially displaceable control sleeve 17 has at a certain axial distance from the flapper valve 20 at least one bore as a discharge opening 32, but preferably a number of Schnauflöcher 18 corresponding plurality of discharge openings 32.
  • the Fig. 7A shows the working position of the excavation device, in which the Schnauflöcher 18 are closed by the front portion of the control sleeve 17. If the excavation device is set down from the ground, the control sleeve 17 is displaced by the striker 15 slipping forward by the path section ⁇ x 2 , so that the check valves, for example the flap valve 20, as in FIG Fig. 7C shown aligned with the Schnauflöcher 18. This is the same as in Fig. 2B shown pump-up position in which the flying mass 14 is temporarily stopped. If the operator begins a further degradation process, an intermediate position of the striker 6 or of the control sleeve 17 is achieved when the device is attached, the opposite of the in Fig.
  • FIG. 8 illustrated time-correlated partial diagrams (a) to (c) illustrate simulation results, with the striking mechanism according to Fig. 2 A / B were carried out.
  • the abscissa of the three diagrams shows the time in seconds (s). On the ordinates of the three diagrams are in the upper diagram (a) in its upper part diagram 33, the instantaneous position or the path-time curve of the exciter piston 12 and in the lower part of the graph 34, the instantaneous position and the path-time course of the flying piston 14 reproduced.
  • the middle diagram (b) shows on the one hand in a solid line 35 the total energy consumption and in the lower part of the energy of the individual beats, which are plotted as peaks 36.
  • the lowest partial diagram (c) shows the time course of the air mass present in the percussion mechanism during a stopping and starting operation for a striking mechanism according to the invention.
  • the pump-up or control sleeve 17 is activated, ie when placing the device in the in Fig. 2B moved position shown.
  • the percussion comes to a halt within two strokes, which is well from the subdiagram (b) of the Fig. 8 is apparent.
  • the percussion mechanism is reactivated, it takes, as shown in the partial diagram (c) of the Fig. 8 it can be seen, about 400 ms, until the excess air is broken down in the percussion over the Schnaufloch or the Schnauflöcher 32, and the percussion again starts to work fully.
  • Fig. 9 show a time-prolonged partial excerpt of the simulation results Fig. 8 , It can clearly be seen from this that the flying massile has already reached a rest position after only two individual beats (partial diagram (a)).
  • the exciter piston 12 continues to run and changed accordingly the existing air mass in the percussion pulsating, which is well from the partial diagrams (c) of Fig. 8 and 9 can be seen.
  • the FiG. 11 and 12 show the already explained FIGS. 8 or 10 corresponding graphics or diagrams for a striking mechanism with a pump-up or control sleeve 17 according to Fig. 7 with additional (additional) discharge opening (discharge openings) 32.
  • Fig. 8 shows Fig. 11 an overview of a stop and start operation of a percussion mechanism by means of a pump-up or control sleeve 17 according to the invention
  • Fig. 7 has additional discharge openings 32.
  • the percussion comes to a halt within two shots.
  • At t 1.2 s the hammer mechanism is reactivated.
  • Fig. 10 is from the Fig. 11 and 12 It is obvious that the striking mechanism begins to hammer almost immediately, which in both cases Fig. 11 and 12 the partial diagrams (b) and (c) can be recognized well.
  • This favorable start-up behavior of the percussion mechanism is achieved by the additional blow-off via the discharge opening 32. Excess air is rapidly reduced by briefly bleeding the impact mechanism.
  • FIGS. 13 and 14 Another basic embodiment of the invention using a pump with pressure accumulator is described below with reference to the FIGS. 13 and 14 described.
  • the electropneumatic percussion mechanism itself is used to fill an intermediate pressure accumulator 45, which is emptied via a preferably controllable valve 46 into the percussion mechanism, in particular into the air spring 19, as soon as the contact pressure decreases or the extraction unit declines lifted off the ground.
  • the Fig. 13 shows an embodiment with a driven by the exciter piston additional piston pump 40, which is connected via check valves 41, 42 with the intermediate pressure accumulator 45.
  • the suction sides of the reciprocating pump 40 also have check valves 43, 44.
  • a pressure relief valve 47 may be provided at the accumulator 45.
  • Fig. 14 shows, it is also possible to use the volume 50 of the eccentric drive 42 for the excitation piston 12 directly as the pump volume, wherein the crankcase serves as a pump housing 51.
  • the check valves 53 and 54 correspond in function to the check valves 41, 42 and 43, 44 at Fig. 13 ,
  • a third embodiment variant of the invention is based on the use of fast-switching valves with a sub-variant of a dynamically rapidly displaceable sliding sleeve. Two embodiments are in the FIGS. 15 and 16 shown.
  • Fig. 15 is the function of a check valve compared with the basis of the Fig. 1 to 12 described embodiments replaced by a fast-switching valve 60, which may be a magnetically actuated 2/2-way valve.
  • a fast-switching valve 60 which may be a magnetically actuated 2/2-way valve.
  • the valve 60 is closed as soon as the exciter piston 12 changes its direction of movement at the rear dead center. The air is compressed during the flow of the excitation piston 12 and generates an overpressure. The valve 60 is then opened again each time shortly after the exciter piston 12 has reached the front dead center or reversal point.
  • This embodiment of the invention has the advantage that after switching off the impact mechanism before the next start by a short opening of the valve 60, the pressure equalization can be made immediately.
  • the requirements for the valve 60 are relatively high; Switching frequencies of more than 50 Hz are necessary.
  • the nominal widths of a feedthrough bore on the guide tube 11 (in FiG. 15 not shown) or on the valve itself, must be sized relatively large for rapid gas exchange, z. B. diameters of 3 to 4 mm are required.
  • electrically operated slide valves or rotary slide valves come into question for this embodiment.
  • FIG. 16 An embodiment of the invention in which a control sleeve itself is used directly as a slide valve, is in Fig. 16 shown.
  • a control sleeve 61 which closes the Schnauflöcher 18 in an end position and releases in a second end position, at the same time forms a bobbin and forms the armature of a voice coil actuator 62, which is placed centrally around the guide tube 11.

Claims (10)

  1. Outil d'enlèvement, en particulier marteau perforateur et/ou burineur, dont le mécanisme de percussion électropneumatique comporte un piston excitateur (12) qui est apte à être entraîné vers l'avant et vers l'arrière à l'intérieur d'un tube de guidage (11) et qui, par l'intermédiaire d'un ressort pneumatique comprimé (19), accélère un piston volant (14) qui, pour sa part, entraîne en percussion un outil d'enlèvement mainteru dans un raccord d'outil (9), le tube de guidage étant pourvu d'au moins un perçage (18) dans la zone du ressort pneumatique, et un manchon de commande (17) entourant le tube de guidage étant prévu pour coulisser sous l'action d'un dispositif de déplacement (16) qui est actionné lorsque l'outil d'enlèvement est décollé du support, caractérisé en ce qu'au manchon de commande (17) est intégrée une soupape anti-retour (20 ; 28) qui, lorsque l'outil d'enlèvement est décollé du support, augmente la dépression négative créée, lors de la course de retour du piston excitateur (12), entre celui-ci et le piston volant (14), et qui est disposée de façon à être alignée avec le perçage (18) par le dispositif de déplacement (16) lorsque l'outil d'enlèvement est décollé du support.
  2. Outil d'enlèvement selon la revendicatior 1, dans lequel le piston volant entraîne par l'intermédiaire du ressort pneumatique agit par percussion sur une bouterolle (15) associée au porte-outil, caractérisé en ce que le dispositif de soupape (16) de la soupape anti-retour peut être actionné par l'intermédiaire de la bouterolle.
  3. Outil d'enlèvement selon la revendication 2, caractérisé en ce que le manchon de commande peut coulisser axialement par rapport au tube de guidage par l'intermédiaire du dispositif de déplacement.
  4. Outil d'enlèvement selon la revendication 2, caractérisé en ce que le manchon de commande peut tourner par rapport au tube de guidage par l'intermédiaire du dispositif de déplacement.
  5. Outil d'enlèvement selon la revendication 1, caractérisé en ce que la soupape anti-retour est une soupape à clapet (20).
  6. Outil d'enlèvement selon la revendication 5, caractérisé en ce que la soupape à clapet (20) est intégrée dans la paroi périphérique du manchon le commande (17).
  7. Outil d'enlèvement selon la revendication 6, caractérisé en ce que la soupape à clapet (20) est formée par un ressort à lame (22) bloqué d'un coté et s'étendant transversalement à un canal de passage.
  8. Outil d'enlèvement selon la revendication 1, caractérisé en ce que la soupape anti-retour est une soupape à bille (28) intégrée dans le manchon ce commande (17).
  9. Outil d'enlèvement selon la revendication 8, caractérisé en ce que la précontrainte de la soupape à bille est réglable par l'intermédiaire d'une vis de réglage (31) agissant sur un ressort de compression (29).
  10. Outil d'enlèvement selon la revendication 1, caractérisé par au moins une ouverture de sortie (32) qui traverse le manchon de commande (17) peur réduire rapidement une surpression dans le mécanisme de percussion lorsque le marteau ou le burin commence/recommence à fonctionner.
EP04102799A 2004-06-18 2004-06-18 Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion Not-in-force EP1607187B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP04102799A EP1607187B1 (fr) 2004-06-18 2004-06-18 Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion
DE502004011101T DE502004011101D1 (de) 2004-06-18 2004-06-18 Einrichtung zur Verbesserung des Abschaltverhaltens eines elektropneumatischen Abbaugeräts

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04102799A EP1607187B1 (fr) 2004-06-18 2004-06-18 Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion

Publications (2)

Publication Number Publication Date
EP1607187A1 EP1607187A1 (fr) 2005-12-21
EP1607187B1 true EP1607187B1 (fr) 2010-04-28

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EP04102799A Not-in-force EP1607187B1 (fr) 2004-06-18 2004-06-18 Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion

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EP (1) EP1607187B1 (fr)
DE (1) DE502004011101D1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112009001141T5 (de) * 2008-05-07 2011-06-09 Milwaukee Electric Tool Corp., Brookfield Antriebsanordnung für ein Kraftwerkzeug
JP2012196728A (ja) * 2011-03-18 2012-10-18 Makita Corp 打撃工具
DE102012206452A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Handwerkzeugmaschine und Steuerungsverfahren
GB201216905D0 (en) * 2012-09-21 2012-11-07 Black & Decker Inc A hammer drill
EP3181301A1 (fr) 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil portative a percussion
EP3181300A1 (fr) * 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil portative a percussion
EP3181298A1 (fr) * 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil a percussion
EP3181299A1 (fr) * 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil portative a percussion
CN116352658A (zh) * 2021-12-20 2023-06-30 南京泉峰科技有限公司 电动工具及锤钻
US11833652B2 (en) * 2022-01-25 2023-12-05 Hilti Aktiengesellschaft Power tool

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3932134A1 (de) * 1989-09-27 1991-04-04 Bosch Gmbh Robert Hammer mit luftfederschlagwerk
DE19714287A1 (de) * 1997-04-07 1998-10-08 Hilti Ag Bohr- und/oder Meisselgerät
DE19714288A1 (de) * 1997-04-07 1998-10-08 Hilti Ag Bohr- und/oder Meisselgerät
DE10121088A1 (de) * 2001-04-28 2002-11-07 Bosch Gmbh Robert Bohr- und/oder Meißelhammer
DE10156388A1 (de) * 2001-11-16 2003-06-05 Bosch Gmbh Robert Handwerkzeugmaschine mit einem pneumatischen Schlagwerk

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DE502004011101D1 (de) 2010-06-10

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