EP4382254A1 - Mécanisme de percussion pour un outil électrique portatif et outil électrique portatif - Google Patents

Mécanisme de percussion pour un outil électrique portatif et outil électrique portatif Download PDF

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Publication number
EP4382254A1
EP4382254A1 EP22211885.3A EP22211885A EP4382254A1 EP 4382254 A1 EP4382254 A1 EP 4382254A1 EP 22211885 A EP22211885 A EP 22211885A EP 4382254 A1 EP4382254 A1 EP 4382254A1
Authority
EP
European Patent Office
Prior art keywords
impact
piston
striker
air spring
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.)
Pending
Application number
EP22211885.3A
Other languages
German (de)
English (en)
Inventor
Rory Britz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilti AG
Original Assignee
Hilti AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hilti AG filed Critical Hilti AG
Priority to EP22211885.3A priority Critical patent/EP4382254A1/fr
Publication of EP4382254A1 publication Critical patent/EP4382254A1/fr
Pending legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/005—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
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • 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

Definitions

  • the present invention relates to an electropneumatic impact mechanism for a hand-held power tool and to the hand-held power tool itself.
  • Impact mechanisms are used in hand-held power tools such as rotary hammers for chiseling or drilling concrete, stone and other hard materials.
  • fluid-driven impact mechanisms e.g. in pneumatic or hydraulic hammers
  • electro-pneumatic impact mechanisms While fluid-driven impact mechanisms require the supply of a pressurized fluid from outside the impact mechanism, electro-pneumatic impact mechanisms generate the necessary operating pressures within the impact mechanism itself.
  • a generic electropneumatic percussion mechanism is made of US7,926,586 B2 known.
  • the impact mechanism comprises an excitation piston and a percussion piston, each of which can be moved linearly and is sealed in a guide tube.
  • An air spring is formed between the excitation piston and the percussion piston.
  • the excitation piston is driven in a linear oscillation by an electric motor, with the drive energy being transferred to the percussion piston by the air spring.
  • the percussion piston in turn transfers the kinetic energy in the form of a pulse transfer to a tool insert or striker, which is coupled to a tool, for example a chisel.
  • the guide tube has large ventilation openings beyond the percussion piston in the direction of impact so that the movement of the percussion piston is not hindered by throttling losses.
  • the positioning of the ventilation openings in the axial direction is usually chosen so that they are as far forward as possible in the direction of impact so that they are not covered by the percussion piston when the percussion piston moves in the direction of impact.
  • valves for improved shutdown of a passive percussion mechanism are used and according to DE 30 24 715 A1 An opening is controlled by the impact piston itself in order to achieve an improved shutdown.
  • EN 10 2011 105 600 A1 An electro-pneumatic impact mechanism is known in which the excitation piston and impact piston are coupled via two air springs connected in series. This is intended to achieve a recoil-tolerant and soft energy transfer at high speed of the excitation piston.
  • an electropneumatic percussion mechanism which has a compensation piston which oscillates in the opposite direction to the percussion piston and which is housed in a cylinder which is fluidically coupled to a side of the percussion piston facing away from the excitation piston.
  • this is intended to achieve mass compensation to reduce the vibrations caused by the percussion mechanism and, on the other hand, the compensation piston supports the preload of the air spring between the excitation piston and the percussion piston during the return stroke (opposite the direction of impact) of the latter.
  • One object of the present invention is therefore to provide a particularly electropneumatic impact mechanism for a hand-held power tool, which is characterized by improved start-up and shutdown behavior.
  • the object is to provide an improved hand-held power tool that is more ergonomic to operate.
  • an electropneumatic impact mechanism for a hand-held power tool, in particular for an electropneumatic hammer drill, which comprises an excitation piston that can be driven in a linear oscillating manner in the axial direction by a drive device and an impact piston that can be displaced in the axial direction.
  • the excitation piston and the impact piston are accommodated in a guide tube and sealed off from it, so that a first air spring is formed between the excitation piston and the impact piston.
  • the impact mechanism also comprises an anvil that can be displaced in the axial direction between two end positions and can be coupled to a tool holder.
  • a first end position of the anvil is a rest position in which the anvil is disengaged in an impact direction pointing away from the impact piston, and a second end position of the anvil is a working position in which the anvil is engaged in a pressure direction pointing towards the impact piston.
  • the impact piston is designed to cause an impulse transfer to the anvil at least temporarily during operation of the impact mechanism.
  • a second air spring is designed to exert a restoring force on the striking piston that is directed counter to the direction of impact, so that when the striking mechanism is in operation and the striker is in the rest position, no impulse is transmitted from the striking piston to the striker.
  • the percussion mechanism according to the invention advantageously has a self-regulating mechanism that allows a continuous transition from an activated to an deactivated state of the percussion mechanism and vice versa.
  • the second air spring When the striker is in its rest position disengaged in the direction of impact, the second air spring generates such a large counterpressure and thus a restoring force acting on the percussion piston that movement of the percussion piston in the direction of impact is reversed and it does not reach the striker.
  • the percussion piston oscillates between the front and rear air springs. Only the comparatively weak pneumatic forces act on the striker. Because only very little energy leaves the system to the outside, the internal energy of the percussion mechanism increases, causing the percussion piston to oscillate increasingly in phase with the excitation piston and thus stopping further coupling of energy.
  • the percussion mechanism appears to be switched off to the outside, although the percussion piston continues to oscillate.
  • the impact piston hits the striker before the impact piston has been completely braked by the air spring. In this state, the impact mechanism begins to work under partial load. If the striker is pushed in completely in the direction of pressure, i.e. it is in its working position, the braking effect of the front air spring is negligible, so that the impact mechanism works at full load.
  • the impact mechanism according to the invention can be started gently and automatically returns to a state in which no energy is given off to the tool. Furthermore, the impact mechanism according to the invention can be operated continuously at partial load. In order to achieve this, only a minimal amount of equipment is required according to the invention, namely the provision of a front air spring in the direction of impact beyond the impact piston.
  • known electropneumatic impact mechanisms can be equipped with a second air spring, for example by adding a corresponding seal to the guide tube opposite the striker.
  • guide tube is understood here to mean in particular a cylinder in which the excitation piston and the impact piston are guided in a sealed manner.
  • axial direction is understood here to mean in particular a direction that coincides with a longitudinal extension of a tool that can be coupled to the impact mechanism, such as a chisel or drill.
  • radial direction is understood here to mean in particular a direction that runs perpendicular to the axial direction.
  • the striker can protrude into the guide tube with a pulse transmission end at an end of the impact piston facing away from the excitation piston and can be sealed against it. More precisely, the pulse transmission end of the striker can protrude into the second air spring.
  • the impulse transmission end of the striker is the end facing the impact piston, where the latter is hit by the impact piston to transmit an impact impulse when the impact mechanism is in operation.
  • the guide tube can have a reduced cross-section at its front end in the direction of impact compared to a cross-sectional area of the second air spring, with the striker protruding into the guide tube through this area of reduced cross-section. Since the end of the striker protruding into the guide tube forms a piston surface, this advantageously reduces the pneumatic forces acting on the striker.
  • a partial load impulse transfer can take place from the striking piston to the anvil.
  • the transition between the striking mechanism being switched off (anvil in the rest position) and any degree of partial load operation is infinitely variable and can be easily adjusted by the user by varying the contact pressure exerted on the tool held in the tool holder. The deeper the anvil is pushed into the guide tube or the second air spring in the direction of pressure, the less the striking piston is braked by the second air spring before it reaches the anvil.
  • the striking mechanism when the striking mechanism is in operation and the striker is in the working position, a full load impulse transfer from the striking piston to the striker can take place.
  • the working position of the striker ie when it is pushed into the guide tube or the second air spring as far as possible in the pressing direction, the restoring force of the second air spring acting on the striking piston is minimal or completely eliminated, so that the drive energy used to drive the excitation piston is converted into the The impact energy acting on the striker can be converted.
  • the second air spring can have at least one ventilation opening that breaks through a wall of the guide tube.
  • the ventilation opening serves, among other things, to prevent temperature and/or air pressure-related pressure gradients between the second air chamber and the environment, so that the impact mechanism does not become unduly tense.
  • the at least one ventilation opening of the second air spring is positioned in the axial direction such that it is located at or in the direction of impact beyond a position at which a front piston surface of the impact piston in the direction of impact is located when the impact piston hits the striker in the working position during operation of the impact mechanism.
  • This can ensure that the restoring force exerted on the impact piston by the second air spring during full-load operation of the impact mechanism is minimized or even eliminated entirely, which increases the efficiency of the impact mechanism and reduces dissipation losses.
  • this positioning of the at least one ventilation opening contributes to the lowest possible damping of the impact energy at full load.
  • the ventilation opening of the second air spring can be positioned in the axial direction such that it is located a maximum of 15%, in particular a maximum of 5%, of a diameter of the second air spring in the impact direction beyond the position at which a front piston surface of the impact piston in the impact direction is located when the impact piston hits the striker in the working position during operation of the impact mechanism.
  • the at least one ventilation opening of the second air spring can be positioned in the axial direction in such a way that, when the striking mechanism is in operation and the striker is in the rest position, it is completely closed by the striking piston when the striking piston moves in the direction of impact.
  • the air spring is thus only formed when the striking piston passes over the at least one ventilation opening, since pressure can only build up in the second air spring when the ventilation opening is closed. This ensures that the second air spring can optimally exert its braking effect on the striking piston when the striker is in its rest position - i.e. in its maximum end position in the direction of impact.
  • the at least one ventilation opening of the striking mechanism according to the invention is in Impact direction as far back as possible.
  • the second air spring has no further ventilation openings in the direction of impact beyond the at least one ventilation opening, which is advantageous for the most efficient operation of the second air spring, since this can prevent leaks from the second air spring, which are detrimental to the desired braking effect.
  • a cross-sectional area of the at least one ventilation opening can be at least 10%, in particular at least 25%, in particular at least 50%, of a cross-sectional area of the second air spring. This can ensure that the restoring force exerted by the second air spring on the impact piston during full load operation is minimized particularly effectively. If the cross-sectional area of the at least one ventilation opening is smaller, restoring forces acting on the impact piston during full load may not be completely avoided due to the throttling effect of the at least one ventilation opening.
  • the cross-sectional shape of the at least one ventilation opening can be circular, for example. In embodiments, however, the at least one ventilation opening can also have a slot-shaped cross-section and extend over a predetermined angular range of the guide tube.
  • the second air spring can have a plurality of ventilation openings, each of which penetrates a wall of the guide tube, wherein in particular the plurality of ventilation openings are distributed at equal angular intervals over a circumference of the guide tube and/or are present at a common axial position.
  • a larger number of ventilation openings makes it possible to realize the desired total cross-section of the ventilation openings with the smallest possible axial extension of the ventilation openings, which allows the opening and closing behavior of the ventilation openings to be precisely adjusted by the impact piston.
  • the impulse transmission end of the striker protruding into the guide tube has a cross-sectional area that is a maximum of 50%, in particular a maximum of 33%, in particular a maximum of 25%, of the cross-sectional area of the second air spring. It is generally advantageous if the cross-sectional area of the impulse transmission end of the striker protruding into the guide tube is as small as possible in relation to the cross-sectional area of the second air spring, as this results in the largest possible air volume of the second air spring, which contributes to lower and easier to control peak pressures in full load operation.
  • the impulse transmission end of the striker which projects into the guide tube, is sealed from the guide tube by a radial sealing device.
  • the radial sealing device can comprise at least one radial seal, which is accommodated in a circumferential sealing groove of the guide tube.
  • a jacket surface of the impulse transmission end of the striker has a surface that is as smooth as possible, in particular finely turned or ground.
  • the radial sealing device is arranged in particular at the front end of the guide tube in the direction of impact.
  • the guide tube can have a radially drawn-in collar at its front end in the direction of impact, on the inner jacket surface of which the radial sealing device is located.
  • the impact mechanism according to the invention can comprise a tool holder which has a guide device which is adjacent to the guide tube in the direction of impact and in which the striker is mounted so that it can be moved linearly.
  • the striker can be sealed from the guide device with a tool holder seal which acts in particular radially.
  • the tool holder seal prevents foreign bodies such as particulate contaminants or liquids from entering the impact mechanism and is therefore important for preventing premature wear of the impact mechanism.
  • the tool holder seal also prevents lubricants from escaping from the impact mechanism into the environment, which allows a hand-held power tool equipped with the impact mechanism according to the invention to operate cleanly.
  • a further aspect of the present invention relates to a hand-held power tool, in particular an electro-pneumatic hammer drill.
  • the hand-held power tool comprises a housing with an impact mechanism according to the invention arranged therein, a tool holder coupled to the impact mechanism and a drive device coupled to the impact mechanism, which is designed to drive the excitation piston of the impact mechanism in a linear oscillating manner in the axial direction.
  • the drive device can in particular comprise an electric motor that is coupled to a gear that is designed to convert a rotationally effective output of the electric motor into a linearly oscillating drive of the excitation piston in the axial direction.
  • the gear can in particular have an eccentric and/or a crankshaft.
  • the gear can be single-stage or multi-stage in order to achieve optimal adaptation to a given speed-torque characteristic curve of the electric motor.
  • the gear can also be designed to convert a rotationally effective output of the electric motor into a rotationally effective drive of the tool holder of the impact mechanism, whereby, for example, the guide tube of the impact mechanism is accommodated in a drive sleeve that is mounted so that it can rotate around the axial direction and can be coupled to it in a rotationally fixed manner, whereby the drive sleeve is coupled to the gear so that the impact mechanism can be a co-rotating impact mechanism.
  • the impact mechanism it is also possible for the impact mechanism not to rotate and for the rotational movement to only be initiated at the tool holder.
  • Fig.1 the percussion mechanism 10 according to the invention is shown in a longitudinal sectional view, wherein the left side of the figure shows the state of the percussion mechanism 10 during full load operation and the right side of the figure shows the state when the percussion mechanism 10 is switched off.
  • the direction designations impact direction S for a direction pointing away from the impact mechanism 10 in the axial direction L, pressure direction A for a direction pointing towards the impact mechanism 10 in the axial direction L and radial direction R for a direction normal to the axial direction L are used.
  • the impact mechanism 10 comprises an excitation piston 1 which can be driven in a linear oscillating manner in the axial direction L and which can be coupled to a drive device, for example an electric motor, via a connecting rod 501 indirectly via a gear.
  • the impact mechanism 10 also comprises an impact piston 2 which can be displaced in the axial direction L, the excitation piston 1 and the impact piston 2 being accommodated in a guide tube 4.
  • the excitation piston 1 is sealed from the guide tube 4 by a radially effective excitation piston seal 11 and the impact piston 2 by an impact piston seal 22.
  • a first air spring 5 is formed between the excitation piston 1 and the impact piston 2, which allows a contactless energy transfer of drive energy from the excitation piston 1 to the impact piston 2.
  • the first air spring 5 has a ventilation opening 51, via which temperature and/or air pressure-related pressure gradients between the interior of the first air spring 5 and the environment can be compensated when the impact mechanism 10 is not in operation. In the impact direction S beyond the ventilation opening 51, the first air spring 5 is free of further ventilation openings.
  • the guide tube 4 functions as a cylinder for the excitation piston 1 and the impact piston 2.
  • the striking mechanism 10 further comprises a striker 3 which can be displaced in the axial direction L between two end positions L R , L A and which is coupled to a tool holder 20.
  • the striker 3 On the right-hand side of the figure, the striker 3 is shown in its first end position L R , which is a rest position L R in which the striker 3 is disengaged in an impact direction S pointing away from the striking piston 2.
  • the striker 3 is shown in its second end position L A , which is a working position L A in which the striker 3 is engaged in a pressure direction A pointing towards the striking piston 2.
  • the percussion piston 2 is designed to cause a pulse transfer to the anvil 3 when the percussion mechanism 10 is in operation - i.e., for example, in the full-load operating state shown in the figure on the left.
  • the percussion piston 2 moving in the direction of impact S hits with its front piston surface 21 in the direction of impact S on a pulse transfer end 31 of the anvil 3 pointing towards the percussion piston 2 and transfers its kinetic energy in the form of a pulse to the anvil 3.
  • the percussion piston 2 cannot reach the impulse transmission end 31 of the striker 3 because the striker 2 has already been braked beforehand by a restoring force F R exerted on the striker piston 2 by a second air spring 6 and its movement is reversed.
  • the second air spring 6 is formed between the front piston surface 21 of the striker piston 2 in the impact direction S and a front end 41 of the guide tube 4 in the impact direction S. At the front end 41 of the guide tube 4 in the impact direction S, the striker 3 protrudes with its impulse transmission end 31 into the guide tube 4 or into the second air spring 6.
  • the impulse transmission end 31 of the striker 3 is sealed off from the front end 41 of the guide tube 4 in the impact direction S by a radial sealing device 7.
  • the radial sealing device 7 is located on a radially drawn-in collar at the front end 41 of the guide tube 4 in the impact direction S and comprises a sealing groove 72 provided on an inner surface of the collar and a radial seal 71 arranged therein.
  • the second air spring 6 also has ventilation openings 61, each of which penetrates a wall of the guide tube 4.
  • the ventilation openings 61 of the second air spring 6 are positioned in the axial direction in such a way that when the striking mechanism 10 is in operation and the striker 3 is in the rest position L R (right side of the illustration), they are completely closed by the striking piston 2 when the striking piston 2 moves in the striking direction S.
  • the air spring 6 is therefore only closed when the striking piston 2 passes over the ventilation openings 61.
  • the ventilation openings 61 are not passed over by the impact piston 2 and the second air spring 6 remains permanently open, ie no or only insignificant pressure can build up in it.
  • the ventilation openings 61 of the second air spring 6 is positioned in the axial direction such that it is located at or in the direction of impact beyond a position at which the front piston surface 21 of the impact piston 2 is located when the impact piston 2 hits the striker 3 in the working position L A during operation of the impact mechanism 10, which contributes to the lowest possible damping of the impact energy at full load.
  • a sum of the cross-sectional areas of the ventilation openings 61 can be at least 10%, in particular at least 25%, in particular at least 50%, of the diameter 62 of the second air spring 6.
  • the guide tube 4 can have a circular cross-section in the area of the second air spring 6.
  • the impulse transmission end 31 of the striker 3 can have a circular cross-section. It has proven to be particularly advantageous if a diameter 311 of the impulse transmission end 31 of the striker 3 is a maximum of 50%, in particular a maximum of 33%, in particular a maximum of 25%, of a diameter 62 of the second air spring 6, since this allows the largest possible volume of the second air spring 6 to be achieved, which contributes to lower and easier to control peak pressures in full load operation.
  • Partial load mode always occurs when the striker 3 is in an intermediate position between the rest position L R and the working position L A.
  • the striking piston 2 hits the striker 3 before the striking piston 2 can be completely braked by the second air spring 6.
  • a transition between the striking mechanism 10 being switched off (strikeper 3 in the rest position L R ) and any degree of partial load mode is stepless and can be varied by the respective insertion path of the striker 3 into the second air spring 6.
  • the impact mechanism 10 has a tool holder 20, which has a guide device 201 adjacent to the guide tube 4 in the direction of impact S, in which the anvil 3 is mounted so as to be linearly displaceable.
  • the tool holder 20 carries a tool 8, for example a chisel or drill.
  • the anvil 3 is coupled to the tool 8 via the tool holder 20 for transmitting the impulse to the tool 8.
  • the anvil 3 is sealed off from the guide device 201 with a radially acting tool holder seal 202, which on the one hand prevents foreign bodies from the outside into the striking mechanism 10 and, on the other hand, prevents lubricants from escaping from the striking mechanism 10 into the environment.
  • the impact mechanism 10 has an inner housing 40 in which the guide tube 4 and the tool holder 20 are held.
  • this inner housing 40 can be mounted in an outer housing 60 of a hand-held power tool 100 (see Fig.2 ) or form an outer casing themselves.
  • a side view of a hand-held power tool 100 according to the invention is shown, which has a percussion mechanism 10 according to the invention.
  • the illustration shows a cutout in the outer housing 60 of the hand-held power tool 100, so that its internal structure can be recognized.
  • the hand-held power tool 100 is in particular a hammer drill of a basically known design with a handle 601 and a switch or power regulator 602.
  • the tool holder 20 (see Fig.1 ) of the impact mechanism 10 is coupled to a chuck 70 in which a tool 8 is accommodated.
  • the chuck 70 can be a drill chuck of known design, such as a keyless drill chuck or SDS drill chuck.
  • the hand-held power tool 100 has a drive device 30 that includes an electric motor 30.
  • the electric motor 30 has a rotary output that, via a gear 50, on the one hand drives the excitation piston 1 of the impact mechanism 10 in a linear oscillating manner in the axial direction L and, on the other hand, drives the tool holder 20 of the impact mechanism 10 in a rotary manner.
  • An output shaft of the electric motor 30 is coupled to two intermediate shafts via a spur gear stage 504 of the gear 50.
  • a first intermediate shaft drives a bevel gear stage 503, via which a drive sleeve 80, in which the impact mechanism 10 is at least temporarily held in a rotationally fixed manner, can be set in rotation.
  • a second intermediate shaft drives an eccentric stage 502 which is coupled to the connecting rod 501 of the impact mechanism in order to finally cause the linear oscillating movement of the excitation piston 1 of the impact mechanism 10 in the axial direction L.
  • gear 50 The design of the gear 50 described here is expressly not to be understood as limiting the invention. Rather, the invention includes any gear design that appears suitable to a person skilled in the art, including the variant of completely dispensing with a drilling function in order to form a pure impact tool.
  • the percussion mechanism 10 is mounted in the outer housing 60 by means deemed suitable by a person skilled in the art in such a way that force and torque flows occurring during operation of the percussion mechanism 10 can be safely introduced and diverted.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP22211885.3A 2022-12-07 2022-12-07 Mécanisme de percussion pour un outil électrique portatif et outil électrique portatif Pending EP4382254A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP22211885.3A EP4382254A1 (fr) 2022-12-07 2022-12-07 Mécanisme de percussion pour un outil électrique portatif et outil électrique portatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP22211885.3A EP4382254A1 (fr) 2022-12-07 2022-12-07 Mécanisme de percussion pour un outil électrique portatif et outil électrique portatif

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EP4382254A1 true EP4382254A1 (fr) 2024-06-12

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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3024715A1 (de) 1980-06-30 1982-04-22 Hitachi Koki Co., Ltd., Tokyo Schlagbohrmaschine
DE3040464A1 (de) 1980-10-27 1982-05-13 Hitachi Koki Co., Ltd., Tokyo Schlagbohrmaschine mit pneumatischer schlageinrichtung
DE8708167U1 (de) 1987-06-10 1988-10-13 Robert Bosch Gmbh, 7000 Stuttgart Rückstoßunabhängiges Bohrhammerschlagwerk
DE19714288A1 (de) 1997-04-07 1998-10-08 Hilti Ag Bohr- und/oder Meisselgerät
WO2000016949A1 (fr) * 1998-09-23 2000-03-30 Wacker-Werke Gmbh & Co. Kg Appareil de percussion tubulaire a coussin d'air de rappel
EP1607187B1 (fr) * 2004-06-18 2010-04-28 HILTI Aktiengesellschaft Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion
US7926586B2 (en) 2007-11-27 2011-04-19 Hilti Aktiengesellschaft Hand-held power tool with a pneumatic percussion mechanism
DE102010029915A1 (de) 2010-06-10 2011-12-15 Hilti Aktiengesellschaft Werkzeugmaschine und Steuerungsverfahren
DE102011105600A1 (de) 2011-06-27 2012-12-27 Wacker Neuson Produktion GmbH & Co. KG Luftfederschlagwerk mit geteiltem Luftfedervolumen
EP1584420B1 (fr) * 2004-04-07 2014-06-11 HILTI Aktiengesellschaft Marteau perforateur et/ou burineur avec mécanisme de percussion électro-pneumatique et dispositif pour le réglage variable de l'énergie d'impact

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3024715A1 (de) 1980-06-30 1982-04-22 Hitachi Koki Co., Ltd., Tokyo Schlagbohrmaschine
DE3040464A1 (de) 1980-10-27 1982-05-13 Hitachi Koki Co., Ltd., Tokyo Schlagbohrmaschine mit pneumatischer schlageinrichtung
DE8708167U1 (de) 1987-06-10 1988-10-13 Robert Bosch Gmbh, 7000 Stuttgart Rückstoßunabhängiges Bohrhammerschlagwerk
DE19714288A1 (de) 1997-04-07 1998-10-08 Hilti Ag Bohr- und/oder Meisselgerät
WO2000016949A1 (fr) * 1998-09-23 2000-03-30 Wacker-Werke Gmbh & Co. Kg Appareil de percussion tubulaire a coussin d'air de rappel
EP1584420B1 (fr) * 2004-04-07 2014-06-11 HILTI Aktiengesellschaft Marteau perforateur et/ou burineur avec mécanisme de percussion électro-pneumatique et dispositif pour le réglage variable de l'énergie d'impact
EP1607187B1 (fr) * 2004-06-18 2010-04-28 HILTI Aktiengesellschaft Appareil pour l'amélioration de la réponse en coupure d'un outil électropneumatique à percussion
US7926586B2 (en) 2007-11-27 2011-04-19 Hilti Aktiengesellschaft Hand-held power tool with a pneumatic percussion mechanism
DE102010029915A1 (de) 2010-06-10 2011-12-15 Hilti Aktiengesellschaft Werkzeugmaschine und Steuerungsverfahren
DE102011105600A1 (de) 2011-06-27 2012-12-27 Wacker Neuson Produktion GmbH & Co. KG Luftfederschlagwerk mit geteiltem Luftfedervolumen

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