EP3116688B1 - Chiselling hand-held machine tool - Google Patents

Chiselling hand-held machine tool Download PDF

Info

Publication number
EP3116688B1
EP3116688B1 EP15709154.7A EP15709154A EP3116688B1 EP 3116688 B1 EP3116688 B1 EP 3116688B1 EP 15709154 A EP15709154 A EP 15709154A EP 3116688 B1 EP3116688 B1 EP 3116688B1
Authority
EP
European Patent Office
Prior art keywords
chiselling
striker
plunger
hand
held
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
EP15709154.7A
Other languages
German (de)
French (fr)
Other versions
EP3116688A1 (en
Inventor
Udo Hauptmann
Aaron Wiedner
Markus Hartmann
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 EP3116688A1 publication Critical patent/EP3116688A1/en
Application granted granted Critical
Publication of EP3116688B1 publication Critical patent/EP3116688B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • B25D2217/0015—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
    • B25D2250/131—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
    • B25D2250/225—Serrations

Definitions

  • the present invention relates to a chiselling hand tool with Leertschabsciens according to the preamble of claim 1 and as from US 2004/194987 A1 known.
  • US 2002/0050191 A describes a generic hand tool with a coupled via an air spring to a pathogen racquet.
  • the striking mechanism has an anvil, which can move from a working position to a position that is advanced in the direction of impact when there is no clearance.
  • the racket can now also continue to advance in the direction of impact, thereby releasing the ventilation opening of the air spring.
  • the air spring remains deactivated until the striker is pushed back into the working position by a drill or chisel pressed against the ground. The case also shifted racket closes the vent and the air spring is activated again.
  • the hand tool has a tool holder for receiving a chiseling tool coaxial with a working axis.
  • a striking mechanism has a pathogen, a pneumatic chamber, a club and a striker on the working axis one after the other.
  • the pathogen is periodically forced by an engine.
  • the racket is guided coaxially to the working axis movable.
  • the pneumatic chamber is adapted for coupling movement of the racket to movement of the pathogen between the pathogen and the racket.
  • the striker is disposed in the direction of impact after the racket for indirectly transmitting a shock from the racket to a tool received in the tool holder.
  • the striker is arranged in a warehouse.
  • the striker has a lateral surface and a stop direction facing stop surface.
  • the bearing has a coaxially arranged to the working axis sleeve and a catcher.
  • the lateral surface of the striker is slidably guided on the inside of the sleeve.
  • the catcher is in the direction of impact from the stopper surface of the striker to limit movement of the striker Döppers arranged in the direction of impact.
  • a backdrop is for displacing the striker in a relative rotation with respect to the bearing when the striker moves in the direction of impact.
  • the gate has a flank on the striker and a flank on the bearing, the two flanks abutting one another in the direction of impact rising in the direction of impact in the same circumferential direction.
  • the striker turns at the blank over the camp.
  • the conversion of the axial movement in the rotational movement proves to be very lossy, whereby advantageously the striker comes to a halt in the vicinity of the catcher.
  • the scenery may have a spur gear teeth on the end face of the striker and a spur gear teeth on the catcher.
  • the spur gears are preferably formed complementary to each other. When the striker hits the catcher, the serrations align with each other, causing the striker or catcher to rotate.
  • the bearing can be freely rotatably mounted in the machine housing about the working axis.
  • the bearing is decoupled from a drive shaft.
  • the freely rotatable catcher can rest in the direction of impact on an elastic damping element.
  • the friction between the damping element and the catcher stops the striker.
  • the damping element ensures that the catcher is always in its rear stop at the operating point and thus can perform an idle stroke axial movement direction tool, which is limited by the stop in the guide tube. By this additional impact process the striker is deprived of more energy.
  • the scenery may have a flank forming spiral groove in a cylindrical surface, the striker and engaging in the groove from the bearing runners.
  • the gate may equally comprise a flank forming helical groove in a cylindrical inner surface of the bearing and engaging in the groove from the striker rotor.
  • Fig. 1 schematically shows a hammer drill 1 as an example of a chiseling hand tool .
  • the hammer drill 1 has a tool holder 2, in which a shank end 3 of a tool, for example one of the drill 4, can be used.
  • a primary drive of the hammer drill 1 is a motor 5, which drives a pneumatic impact mechanism 3 and an output shaft 6 .
  • a battery pack 7 or a power line provide the motor 5 with power.
  • a user can guide the hammer drill 1 by means of a handle 8 and take means of a system switch 9, the hammer drill 1 is in operation.
  • the hammer drill 1 rotates the drill 4 continuously about a working axis 10 and can beat the drill 4 in the direction of impact 11 along the working axis 10 in a substrate.
  • the striking mechanism 3 and preferably the further drive components are arranged within a machine housing 12 .
  • the pneumatic impact mechanism 3 has a piston-shaped exciter 13, a pneumatic chamber 14, a piston-shaped racket 15 and an anvil 16, which are successively arranged in the direction of impact 11 on the working axis 10 and guided along the working axis 10 .
  • the exciter 13 and the racket 15 are arranged for example in a stationary guide tube 17 .
  • the racket may also be arranged in a cup-shaped exciter whose tubular wall forms the guide tube for the racket; analogously, the racket can be designed cup-shaped.
  • the exciter 13 is connected to the motor 5 via a gear unit, which converts the rotational movement of the motor 5 into a periodic linear forward and backward movement of the exciter 13 along the working axis 10 .
  • the gear unit includes an eccentric 18 driven by the motor 5 , which is connected to the exciter 13 by a connecting rod 19 .
  • the gear unit may also contain a wobble drive.
  • the pneumatic chamber 14 is closed by the exciter 13 and the racket 15 .
  • the motor-driven periodic movement of the exciter 13 increases the air pressure in the pneumatic chamber 14 from the ambient pressure.
  • the freely movable racket 15 is accelerated away from the exciter 13 by the increased air pressure, accelerated in the direction of impact 11 or accelerated towards the exciter 13 at reduced air pressure.
  • the movement of the racket 15 is coupled to the movement of the exciter 13 through the pneumatic chamber 14, also referred to as an air spring.
  • the racket 15 oscillates in operation between a front inflection point, in which the exciter 13 and the racket 15 compress the pneumatic chamber 14 maximum, and a rear inflection point (impact point) in which the racket 15 strikes the striker 16 .
  • the striker 16 is held in operation by a pressed-on the substrate tool 4 in a working position, which tunes the distance between the turning points such that the periodicity of the movement of the racket 15 with the periodicity of movement of the exciter 13 matches. Missing the contact pressure of the tool 4, for example, because the user lifts the hammer drill 1 from the ground, the striker 16 leaves the working position in the direction of impact 11. The bat 15 flies over the impact point in the direction of impact 11 addition. In this case, a ventilation opening 20 is released, which allows an exchange of air of the pneumatic chamber 14 with the environment and thus deactivates the air spring. The racket 15 is no longer coupled to the exciter 13 and the striking mechanism 3 switches off automatically. The striker 16 preferably remains outside the working position. Once the user presses the tool 4 back to the ground, the striker 16 is moved to the working position and the vent opening 20 is closed. The Schlagtechnik 3 turns itself on again.
  • the exemplary ventilation openings 20 are in radial openings in the guide tube 17, which seals the racket 15 with respect to the pneumatic chamber 14 in operation.
  • the ventilation openings 20 are offset in the direction of impact 11 to the pneumatic chamber 14 when the racket 15 is in the direction of impact 11 before the impact point.
  • the pneumatic chamber 14 extends to the ventilation openings 20 and is ventilated.
  • the ventilation openings 20 can also be opened or closed by sleeves which actuate the racket 15 or the striker 16 .
  • the striker 16 has a substantially cylindrical core 21 and a collar 22 surrounding a central portion of the core 21 .
  • the core 21 is along the working axis 10 through in Essentially to the working axis 10 vertical end faces 23, 24 completed.
  • the end faces 23, 24 form the impact-absorbing face 23 on which the racket 15 strikes w. the impact-releasing face 24, which strikes the drill 4 .
  • the striking surfaces 23, 24 may be slightly convex.
  • the collar 22 has a cylindrical lateral surface 25 and is closed along the working axis 10 by end faces 26, 27 , which are inclined relative to the working axis 10 .
  • the racket 15 facing, front end face 26 is conical.
  • the racket 15 facing away from the rear end face 27 has a cone-shaped envelope.
  • the mean inclination 28 of the end faces 26, 27 is in the range between 30 degrees and 70 degrees.
  • the striker 16 is guided in a bearing 29 on the working axis 10 .
  • the exemplary bearing 29 includes a sleeve 30 against which the cylindrical surface 25 of the collar 22 of the striker 23 abuts.
  • the cylindrical jacket surface 31 of the core 21 for axially guiding the beatpiece 23 can rest on the sleeve 30 .
  • the bearing 29 limits the axial movement in the direction of impact 11 by a catcher 32 and counter to the direction of impact 11 by a base 33.
  • the example annular socket 33 is in the direction of impact 11 in front of the collar 22 of the striker 23.
  • the core 21 may be in the opening of the Moving pedestal 33 freely, the inner diameter of the base 33 is designed to be a game greater than the diameter of the impact-absorbing face 24 .
  • the diameter of the collar 22 is greater than the inner diameter of the base 33, consequently, the collar 22 may rest against the base 33 against impact direction 11 .
  • the pressed drill 4 presses the collar 22, that is, the racket 15 facing end face 26, against the base 33, which corresponds to the working position of the striker 23 during operation.
  • the impact-absorbing face 24 defines in the working position the point of impact of the striking mechanism 3.
  • the catcher 32 is located in the direction of impact 11 in front of the collar 22 .
  • the catcher 32 is annularly formed with an inner diameter which is larger than the diameter of the impact-releasing impact surface 24 and less than the diameter of the collar 22 .
  • the pointing in the direction of impact 11 end face 27 of the collar 22 may rest in the direction of impact 11 on the catcher 32 , since they overlap in the radial direction.
  • the striker 16 is stopped by the catcher 32 after the racket 15 strikes the striker 16 in the absence of contact pressure of the tool 4 .
  • the catcher 32 may be formed as a constriction of the sleeve 30 as shown or like the example socket 33 may be formed as a separate component.
  • the catcher 32 preferably has an axial play in the machine housing 12.
  • the catcher 32 is supported on the machine housing 12 in the direction of impact 11 by means of a damping element 34 .
  • the catcher 32 preferably absorbs the kinetic energy of the striker 23 to prevent the striker 16 from sliding back to the operative position by itself due to the recoil.
  • the striker 16 and its bearings 29 are provided with a link 35 which causes the striker 16 in its movement in the direction of impact 11 in a rotational movement.
  • the rotational movement proves to be an effective measure, the striker 16 to escape its kinetic energy during impact with the catcher 32 .
  • the striker 16 thus remains close to the catcher 32 and does not accidentally slip back into the working position.
  • the link 35 includes, for example the catcher 32 facing spur gear teeth 36 on the rear end surface 27 of the collar 22 and the collar 22 facing the spur gear toothing 37 at the catcher 32.
  • the two end teeth 36, 37 are complementary to each other.
  • the spur toothing 36 of the collar 22 may be formed as a bevel gear 36
  • the complementary spur toothing 37 of the catcher 32 is concave.
  • the striker 16 is freely rotatable about the working axis 10 in the bearing 29 . The angular orientation of the two end faces 26, 27 is therefore largely random. As soon as the striker 16 strikes the catcher 32 , the two end faces 26 are oriented towards one another.
  • the striker 16 rotates by a quarter of the width of the teeth 38 of the spur gear 36 with respect to the catcher 32 until the two spur gears 36, 37 are aligned with each other.
  • the gate 35 proves to be highly attenuating. Presumably results in the strong damping due to a dynamic inhibition, which arises after the two serrations 36, 37 are aligned.
  • the spur gears 36, 37 now move apart due to the rotational movement of the striker 23 along the working axis 10 , against the pulse of the striker 16 in the direction of impact 11th
  • the spur toothing 36 of the collar 22 has a plurality of identical teeth 38, which are arranged in the circumferential direction 39 successively distributed equidistant.
  • the number of teeth 38 depends on the size of the striker 16, for example, the number is between 15 and 40.
  • the head line 40 of the tooth 38 is rectilinear and lies with the working axis 10 in a plane. When formed as a bevel gear spur gear 36 of the collar 22 , the head line 40 between 30 degrees and 70 degrees with respect to the working axis 10 is inclined.
  • the head line may be skewed in another embodiment with the working axis 10, wherein the head line monotonically from one end to the other end of the working axis 10 degrees. Alternatively, the head line may be formed spirally.
  • the tooth 38 has a flank 42 pointing only in the right-handed circumferential direction 41 and an edge pointing only in the left-handed circumferential direction 39 43.
  • the two flanks 42, 43 run in the direction of impact 11 towards each other and in the head line 40 together.
  • the tooth 38 tapers in the direction of impact 11.
  • An inclination 44 of the right-hand flank 42 is determined relative to a reference plane 45.
  • the reference plane 45 is spanned by the working axis 10 and the point on the flank 42 at which the slope 44 is to be determined.
  • the slope 44 is preferably in the range between 30 degrees and 60 degrees.
  • the inclination 46 of the left-handed flank 43 with respect to the reference plane 45 is preferably equal to the inclination 44 of the right-hand flank 42.
  • the two flanks 42, 43 can converge toward one another in the direction of the working axis 10 .
  • the tooth 38 is thus wider on its outside than closer to the working axis 10.
  • the width of the tooth 38 preferably increases in proportion to the distance from the working axis 10.
  • the angular width of the tooth 38 is thus constant along the radial direction.
  • a height 47 of the teeth 38, ie the dimension of the flanks 42, 43 along the working axis 10, is in the range between 2 mm and 5 mm.
  • the spur toothing 37 of the catcher 32 is constructed to be complementary to the spur toothing 36 of the collar 22 .
  • the spaces between the teeth 48 of the catcher 32 correspond in shape and number to the teeth 38 of the collar 22.
  • a left-hand flank 49 of the tooth 48 on the catcher 32 is largely congruent with the right-hand flank 42 of the tooth 38 on the collar 22;
  • a right-hand flank of the tooth 48 on the catcher 32 is largely congruent with the left-hand flank 43 of the tooth 38 on the collar 22nd
  • the catcher 32 may be freely rotatable about the working axis 10 in the machine housing 12. In particular, the catcher 32 is decoupled from the output shaft 6. Upon impact of the striker 23 in the catcher 32 , both rotate relative to each other. The rotational energy transmitted by the striker 16 into the catcher 32 is removed from the striking mechanism 3 .
  • the damping element 34 is preferably rotationally fixed in the machine housing 12, whereby the catcher 32 moves relative to the damping element 34 . The friction between the rubber-containing damping element 34 and the catcher 32 extracts the kinetic energy from the striker 16 .
  • a link 50 on a lateral surface 25, 31 of the striker 23 engage to convert the striker 16 in a rotational movement.
  • the exemplary gate 50 has a groove 51 extending spirally in the lateral surface 31.
  • the bearing 29 is provided with a rotor 52 , which engages in the groove 51 .
  • the rotor 52 is connected in the bearing 29 such that the rotor 52 relative to the bearing 29 along the working axis 10 and in the circumferential direction 41 is immovable.
  • the rotor 52 may be, for example, a ball that is enclosed in the bearing 29 .
  • the ball can rotate in the socket about its center.
  • the rotor 52 is located with a flank on an obliquely to the working axis 10 extending edge 53 of the groove 51 at.
  • the movement of the striker 23 along the working axis 10 forces a relative rotational movement of striker 16 and bearing 29.
  • the groove 51 may have a constant pitch 54 along the working axis 10 .
  • the length of the entire groove 51 corresponds to the free path of the striker 23 between the base 33 and the catcher 32, typically in the range between 20 mm and 50 mm.
  • the groove 51 is parallel to the working axis 10 at an end facing the racket 15 and the pitch 54 increases in the direction of impact 11.
  • the parallel section may be between 4 mm and 10 mm in length.
  • the slope 54 at the tool-side end of the groove 51 is between 30 degrees and 60 degrees.
  • the ball can equally be caught in the lateral surface 31 of the striker 23 and the groove 30 may be arranged in the inner surface of the sleeve.
  • a plurality of identical grooves 51 may be provided around the working axis 10 .

Landscapes

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

Description

GEBIET DER ERFINDUNGFIELD OF THE INVENTION

Die vorliegende Erfindung betrifft eine meißelnde Handwerkzeugmaschine mit Leerschlagabschaltung gemäß dem Oberbegriff von Anspruch 1 und wie aus US 2004/194987 A1 bekannt.The present invention relates to a chiselling hand tool with Leerschlagabschaltung according to the preamble of claim 1 and as from US 2004/194987 A1 known.

US 2002/0050191 A beschreibt eine gattungsgemäße Handwerkzeugmaschine mit einem über eine Luftfeder an einen Erreger gekoppelten Schläger. Das Schlagwerk hat einen Döpper, welcher sich bei einem Leerschlag aus der Arbeitsstellung in eine in Schlagrichtung vorgerückte Stellung bewegen kann. Der Schläger kann nun ebenfalls weiter in Schlagrichtung vorrücken und gibt dabei Belüftungsöffnung der Luftfeder frei. Die Luftfeder bleibt solange deaktiviert, bis der Döpper durch einen an den Untergrund anpressten Bohrer oder Meißel in die Arbeitsstellung zurückgeschoben wird. Der dabei gleichfalls verschobene Schläger verschließt die Belüftungsöffnung und die Luftfeder ist wieder aktiviert. US 2002/0050191 A describes a generic hand tool with a coupled via an air spring to a pathogen racquet. The striking mechanism has an anvil, which can move from a working position to a position that is advanced in the direction of impact when there is no clearance. The racket can now also continue to advance in the direction of impact, thereby releasing the ventilation opening of the air spring. The air spring remains deactivated until the striker is pushed back into the working position by a drill or chisel pressed against the ground. The case also shifted racket closes the vent and the air spring is activated again.

Das Deaktivieren der Luftfeder ist davon abhängig, dass der Döpper in der vorgerückten Stellung verbleibt.Disabling the air spring is dependent on the striker remaining in the advanced position.

OFFENBARUNG DER ERFINDUNGDISCLOSURE OF THE INVENTION

Die erfindungsgemäße Handwerkzeugmaschine hat eine Werkzeugaufnahme zum Aufnehmen eines meißelnden Werkzeugs koaxial zu einer Arbeitsachse. Ein Schlagwerk hat auf der Arbeitsachse nacheinander einen Erreger, eine pneumatische Kammer, einen Schläger und einen Döpper. Der Erreger ist periodisch von einem Motor zwangserregt. Der Schläger ist koaxial zu der Arbeitsachse beweglich geführt. Die pneumatische Kammer ist zum Ankoppeln einer Bewegung des Schlägers an die Bewegung des Erregers zwischen Erreger und Schläger ausgebildet. Der Döpper ist in Schlagrichtung nach dem Schläger zum mittelbaren Übertragen eines Stoßes von dem Schläger auf ein in der Werkzeugaufnahme aufgenommenes Werkzeug angeordnet. Der Döpper ist in einem Lager angeordnet. Der Döpper hat eine Mantelfläche und eine in Schlagrichtung weisende Stoppfläche. Das Lager hat eine zu der Arbeitsachse koaxial angeordnete Hülse und einen Fänger. Die Mantelfläche des Döppers ist an der Innenseite der Hülse gleitend geführt. Der Fänger ist in Schlagrichtung von der Stoppfläche des Döppers zum Begrenzen einer Bewegung des Döppers in der Schlagrichtung angeordnet. Eine Kulisse ist zum Versetzen des Döppers in eine Relativdrehung gegenüber dem Lager, wenn der Döpper sich in Schlagrichtung bewegt. Die Kulisse hat an dem Döpper eine Flanke und an dem Lager eine Flanke, wobei die beiden bei der Bewegung aneinander anliegenden Flanken in Schlagrichtung in die gleiche Umfangsrichtung ansteigen.The hand tool according to the invention has a tool holder for receiving a chiseling tool coaxial with a working axis. A striking mechanism has a pathogen, a pneumatic chamber, a club and a striker on the working axis one after the other. The pathogen is periodically forced by an engine. The racket is guided coaxially to the working axis movable. The pneumatic chamber is adapted for coupling movement of the racket to movement of the pathogen between the pathogen and the racket. The striker is disposed in the direction of impact after the racket for indirectly transmitting a shock from the racket to a tool received in the tool holder. The striker is arranged in a warehouse. The striker has a lateral surface and a stop direction facing stop surface. The bearing has a coaxially arranged to the working axis sleeve and a catcher. The lateral surface of the striker is slidably guided on the inside of the sleeve. The catcher is in the direction of impact from the stopper surface of the striker to limit movement of the striker Döppers arranged in the direction of impact. A backdrop is for displacing the striker in a relative rotation with respect to the bearing when the striker moves in the direction of impact. The gate has a flank on the striker and a flank on the bearing, the two flanks abutting one another in the direction of impact rising in the direction of impact in the same circumferential direction.

Der Döpper dreht sich beim Leerschlag gegenüber dem Lager. Die Konversion der axialen Bewegung in die Drehbewegung erweist sich als stark verlustbehaftet, wodurch vorteilhafterweise der Döpper in der Nähe des Fängers zum Stehen kommt.The striker turns at the blank over the camp. The conversion of the axial movement in the rotational movement proves to be very lossy, whereby advantageously the striker comes to a halt in the vicinity of the catcher.

Die Kulisse kann eine Stirnverzahnung an der Stirnfläche des Döppers und eine Stirnverzahnung an dem Fänger aufweisen. Die Stirnverzahnungen sind vorzugsweise zueinander komplementär ausgebildet. Wenn der Döpper in den Fänger einschlägt, richten sich die Stirnverzahnungen zueinander aus, wodurch der Döpper oder der Fänger in eine Drehbewegung versetzt werden.The scenery may have a spur gear teeth on the end face of the striker and a spur gear teeth on the catcher. The spur gears are preferably formed complementary to each other. When the striker hits the catcher, the serrations align with each other, causing the striker or catcher to rotate.

Das Lager kann in dem Maschinengehäuse um die Arbeitsachse frei drehbar gelagert sein. Insbesondere ist das Lager von einer Antriebswelle entkoppelt. Der frei drehbare Fänger kann in Schlagrichtung an einem elastischen Dämpfelement anliegen. Die Reibung zwischen dem Dämpfelement und dem Fänger stoppt den Döpper. Darüber hinaus stellt das Dämpfelement sicher, dass sich der Fänger im Arbeitspunkt immer in seinem hinteren Anschlag befindet und somit im Leerschlag einen axiale Bewegung Richtung Werkzeug durchführen kann, welche durch den Anschlag im Führungsrohr begrenzt wird. Durch diesen zusätzlichen Stoßvorgang wird dem Döpper weitere Energie entzogen.The bearing can be freely rotatably mounted in the machine housing about the working axis. In particular, the bearing is decoupled from a drive shaft. The freely rotatable catcher can rest in the direction of impact on an elastic damping element. The friction between the damping element and the catcher stops the striker. In addition, the damping element ensures that the catcher is always in its rear stop at the operating point and thus can perform an idle stroke axial movement direction tool, which is limited by the stop in the guide tube. By this additional impact process the striker is deprived of more energy.

Die Kulisse kann eine die Flanke bildende spiralförmige Nut in einer zylindrischen Mantelfläche, des Döppers und eine von dem Lager in die Nut eingreifenden Läufer aufweisen. Die Kulisse kann gleichermaßen eine die Flanke bildende spiralförmige Nut in einer zylindrischen Innenfläche des Lagers und einen von dem Döpper in die Nut eingreifenden Läufer aufweisen.The scenery may have a flank forming spiral groove in a cylindrical surface, the striker and engaging in the groove from the bearing runners. The gate may equally comprise a flank forming helical groove in a cylindrical inner surface of the bearing and engaging in the groove from the striker rotor.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Die nachfolgende Beschreibung erläutert die Erfindung anhand von exemplarischen Ausführungsformen und Figuren. In den Figuren zeigen:

Fig. 1
einen Bohrhammer
Fig. 2
ein Schlagwerk des Bohrhammers
Fig. 3
einen Döpper und Führung des Schlagwerks
Fig. 4
ein Schlagwerk des Bohrhammers
The following description explains the invention with reference to exemplary embodiments and figures. In the figures show:
Fig. 1
a hammer drill
Fig. 2
a striking mechanism of the hammer drill
Fig. 3
a striker and leadership of the percussion
Fig. 4
a striking mechanism of the hammer drill

Gleiche oder funktionsgleiche Elemente werden durch gleiche Bezugszeichen in den Figuren indiziert, soweit nicht anders angegeben. Die Anordnung der Elemente wird soweit nicht anders ausgeführt unter Bezug auf die Arbeitsachse und die Schlagrichtung beschrieben. Ein vorderes Element liegt in Schlagrichtung vor einem hinteren Element.Identical or functionally identical elements are indicated by the same reference numerals in the figures, unless stated otherwise. Unless otherwise stated, the arrangement of the elements will be described with reference to the working axis and direction of impact. A front element lies in the direction of impact in front of a rear element.

AUSFÜHRUNGSFORMEN DER ERFINDUNGEMBODIMENTS OF THE INVENTION

Fig. 1 zeigt als Beispiel einer meißelnden Handwerkzeugmaschine schematisch einen Bohrhammer 1. Der Bohrhammer 1 hat einen Werkzeughalter 2, in welchen ein Schaftende 3 eines Werkzeug, z.B. eines des Bohrers 4, eingesetzt werden kann. Einen primären Antrieb des Bohrhammers 1 bildet ein Motor 5, welcher ein pneumatisches Schlagwerk 3 und eine Abtriebswelle 6 antreibt. Ein Batteriepaket 7 oder eine Netzleitung versorgen den Motor 5 mit Strom. Ein Anwender kann den Bohrhammer 1 mittels eines Handgriffs 8 führen und mittels eines Systemschalters 9 den Bohrhammer 1 in Betrieb nehmen. Im Betrieb dreht der Bohrhammer 1 den Bohrer 4 kontinuierlich um eine Arbeitsachse 10 und kann dabei den Bohrer 4 in Schlagrichtung 11 längs der Arbeitsachse 10 in einen Untergrund schlagen. Das Schlagwerk 3 und vorzugsweise die weiteren Antriebskomponenten sind innerhalb eines Maschinengehäuses 12 angeordnet. Fig. 1 schematically shows a hammer drill 1 as an example of a chiseling hand tool . The hammer drill 1 has a tool holder 2, in which a shank end 3 of a tool, for example one of the drill 4, can be used. A primary drive of the hammer drill 1 is a motor 5, which drives a pneumatic impact mechanism 3 and an output shaft 6 . A battery pack 7 or a power line provide the motor 5 with power. A user can guide the hammer drill 1 by means of a handle 8 and take means of a system switch 9, the hammer drill 1 is in operation. In operation, the hammer drill 1 rotates the drill 4 continuously about a working axis 10 and can beat the drill 4 in the direction of impact 11 along the working axis 10 in a substrate. The striking mechanism 3 and preferably the further drive components are arranged within a machine housing 12 .

Das pneumatische Schlagwerk 3 hat einen kolbenförmigen Erreger 13, eine pneumatische Kammer 14, einen kolbenförmigen Schläger 15 und einen Döpper 16, die in Schlagrichtung 11 aufeinanderfolgend auf der Arbeitsachse 10 angeordnet und längs der Arbeitsachse 10 geführt sind. Der Erreger 13 und der Schläger 15 sind beispielsweise in einem stehenden Führungsrohr 17 angeordnet. Der Schläger kann auch in einem topfförmigen Erreger angeordnet sein, dessen rohrförmige Wandung das Führungsrohr für den Schläger bildet; analog kann auch der Schläger topfförmig ausgestaltet sein. Der Erreger 13 ist mit dem Motor 5 über eine Getriebeeinheit verbunden, welche die Drehbewegung des Motors 5 in eine periodische lineare Vor- und Rückbewegung des Erregers 13 längs der Arbeitsachse 10 umsetzt. Beispielsweise beinhaltet die Getriebeeinheit einen von dem Motor 5 angetriebenen Exzenter 18, der durch ein Pleuel 19 mit dem Erreger 13 verbunden ist. Die Getriebeeinheit kann auch einen Taumelantrieb enthalten. Die pneumatische Kammer 14 ist von dem Erreger 13 und dem Schläger 15 abgeschlossen. Die motorgetriebene periodische Bewegung des Erregers 13 erhöht den Luftdruck in der pneumatischen Kammer 14 gegenüber dem Umgebungsdruck. Der frei bewegliche Schläger 15 wird durch den erhöhten Luftdruck von dem Erreger 13 weg, in Schlagrichtung 11 beschleunigt oder bei verringertem Luftdruck zu dem Erreger 13 hin beschleunigt. Die Bewegung des Schlägers 15 ist an die Bewegung des Erregers 13 durch die pneumatische Kammer 14, auch als Luftfeder bezeichnet, angekoppelt. Der Schläger 15 pendelt im Betrieb zwischen einem vorderen Wendepunkt, in welchem der Erreger 13 und der Schläger 15 die pneumatische Kammer 14 maximal komprimieren, und einem hinteren Wendepunkt (Schlagpunkt), in welchem der Schläger 15 auf den Döpper 16 aufschlägt.The pneumatic impact mechanism 3 has a piston-shaped exciter 13, a pneumatic chamber 14, a piston-shaped racket 15 and an anvil 16, which are successively arranged in the direction of impact 11 on the working axis 10 and guided along the working axis 10 . The exciter 13 and the racket 15 are arranged for example in a stationary guide tube 17 . The racket may also be arranged in a cup-shaped exciter whose tubular wall forms the guide tube for the racket; analogously, the racket can be designed cup-shaped. The exciter 13 is connected to the motor 5 via a gear unit, which converts the rotational movement of the motor 5 into a periodic linear forward and backward movement of the exciter 13 along the working axis 10 . For example, the gear unit includes an eccentric 18 driven by the motor 5 , which is connected to the exciter 13 by a connecting rod 19 . The gear unit may also contain a wobble drive. The pneumatic chamber 14 is closed by the exciter 13 and the racket 15 . The motor-driven periodic movement of the exciter 13 increases the air pressure in the pneumatic chamber 14 from the ambient pressure. The freely movable racket 15 is accelerated away from the exciter 13 by the increased air pressure, accelerated in the direction of impact 11 or accelerated towards the exciter 13 at reduced air pressure. The movement of the racket 15 is coupled to the movement of the exciter 13 through the pneumatic chamber 14, also referred to as an air spring. The racket 15 oscillates in operation between a front inflection point, in which the exciter 13 and the racket 15 compress the pneumatic chamber 14 maximum, and a rear inflection point (impact point) in which the racket 15 strikes the striker 16 .

Der Döpper 16 ist im Betrieb durch ein an den Untergrund angepresstes Werkzeug 4 in einer Arbeitsstellung gehalten, welche die Wegstrecke zwischen den Wendepunkten derart abstimmt, dass die Periodizität der Bewegung des Schlägers 15 mit der Periodizität der Bewegung des Erregers 13 übereinstimmt. Fehlt der Anpressdruck des Werkzeugs 4, z.B. weil der Anwender den Bohrhammer 1 von dem Untergrund abhebt, verlässt der Döpper 16 die Arbeitsstellung in Schlagrichtung 11. Der Schläger 15 fliegt über den Schlagpunkt in Schlagrichtung 11 hinaus. Dabei wird eine Belüftungsöffnung 20 freigegeben, welche einen Luftaustausch der pneumatischen Kammer 14 mit der Umgebung ermöglicht und folglich die Luftfeder deaktiviert. Der Schläger 15 ist nicht mehr an den Erreger 13 angekoppelt und das Schlagwerk 3 schaltet sich selbsttätig ab. Der Döpper 16 bleibt vorzugsweise außerhalb der Arbeitsstellung liegen. Sobald der Anwender das Werkzeug 4 wieder an den Untergrund anpresst, wird der Döpper 16 in die Arbeitsstellung verschoben und die Belüftungsöffnung 20 verschlossen. Das Schlagwerk 3 schaltet sich selbsttätig wieder ein.The striker 16 is held in operation by a pressed-on the substrate tool 4 in a working position, which tunes the distance between the turning points such that the periodicity of the movement of the racket 15 with the periodicity of movement of the exciter 13 matches. Missing the contact pressure of the tool 4, for example, because the user lifts the hammer drill 1 from the ground, the striker 16 leaves the working position in the direction of impact 11. The bat 15 flies over the impact point in the direction of impact 11 addition. In this case, a ventilation opening 20 is released, which allows an exchange of air of the pneumatic chamber 14 with the environment and thus deactivates the air spring. The racket 15 is no longer coupled to the exciter 13 and the striking mechanism 3 switches off automatically. The striker 16 preferably remains outside the working position. Once the user presses the tool 4 back to the ground, the striker 16 is moved to the working position and the vent opening 20 is closed. The Schlagwerk 3 turns itself on again.

Die beispielhaften Belüftungsöffnungen 20 sind in radiale Öffnungen in dem Führungsrohr 17, welche der Schläger 15 gegenüber der pneumatischen Kammer 14 im Betrieb abdichtet. Die Belüftungsöffnungen 20 sind in Schlagrichtung 11 zu der pneumatischen Kammer 14 versetzt, wenn der Schläger 15 in Schlagrichtung 11 vor dem Schlagpunkt ist. Wenn der Schläger 15 in Schlagrichtung 11 teilweise oder vollständig nach dem Schlagpunkt ist, reicht die pneumatische Kammer 14 bis zu den Belüftungsöffnungen 20 und ist belüftet. Die Belüftungsöffnungen 20 können auch durch Hülsen geöffnet oder verschlossen werden, welche der Schläger 15 oder der Döpper 16 betätigen.The exemplary ventilation openings 20 are in radial openings in the guide tube 17, which seals the racket 15 with respect to the pneumatic chamber 14 in operation. The ventilation openings 20 are offset in the direction of impact 11 to the pneumatic chamber 14 when the racket 15 is in the direction of impact 11 before the impact point. When the racket 15 in the direction of impact 11 is partially or completely after the impact point, the pneumatic chamber 14 extends to the ventilation openings 20 and is ventilated. The ventilation openings 20 can also be opened or closed by sleeves which actuate the racket 15 or the striker 16 .

Der Döpper 16 hat einen weitgehend zylindrischen Kern 21 und einen Bund 22, der einen mittleren Abschnitt des Kerns 21 umgibt. Der Kern 21 ist längs der Arbeitsachse 10 durch im Wesentlichen zur Arbeitsachse 10 senkrechte Stirnflächen 23, 24 abgeschlossen. Die Stirnflächen 23, 24 bilden die schlagaufnehmende Schlagfläche 23, auf welche der Schläger 15 aufschlägt w. die schlagabgebende Schlagfläche 24, welche auf den Bohrer 4 aufschlägt. Die Schlagflächen 23, 24 können leicht konvex gewölbt sein. Der Bund 22 hat eine zylindrische Mantelfläche 25 und ist längs der Arbeitsachse 10 durch Stirnflächen 26, 27 abgeschlossen, welche gegen über der Arbeitsachse 10 geneigt sind. Die dem Schläger 15 zugewandte, vordere Stirnfläche 26 ist kegelförmig. Die dem Schläger 15 abgewandte, hintere Stirnfläche 27 hat eine kegelförmige Hüllkurve. Die mittlere Neigung 28 der Stirnflächen 26, 27 liegt im Bereich zwischen 30 Grad und 70 Grad.The striker 16 has a substantially cylindrical core 21 and a collar 22 surrounding a central portion of the core 21 . The core 21 is along the working axis 10 through in Essentially to the working axis 10 vertical end faces 23, 24 completed. The end faces 23, 24 form the impact-absorbing face 23 on which the racket 15 strikes w. the impact-releasing face 24, which strikes the drill 4 . The striking surfaces 23, 24 may be slightly convex. The collar 22 has a cylindrical lateral surface 25 and is closed along the working axis 10 by end faces 26, 27 , which are inclined relative to the working axis 10 . The racket 15 facing, front end face 26 is conical. The racket 15 facing away from the rear end face 27 has a cone-shaped envelope. The mean inclination 28 of the end faces 26, 27 is in the range between 30 degrees and 70 degrees.

Der Döpper 16 ist in einem Lager 29 auf der Arbeitsachse 10 geführt. Das beispielhafte Lager 29 beinhaltet eine Hülse 30, an der die zylindrische Mantelfläche 25 des Bunds 22 des Döppers 23 anliegt. An der Hülse 30 kann zudem die zylindrischen Mantelfläche 31 des Kerns 21 zum axialen Führen des Döppers 23 anliegen. Das Lager 29 begrenzt die axiale Bewegung in Schlagrichtung 11 durch einen Fänger 32 und entgegen der Schlagrichtung 11 durch einen Sockel 33. Der beispielsweise ringförmige Sockel 33 liegt in Schlagrichtung 11 vor dem Bund 22 des Döppers 23. Der Kern 21 kann sich in der Öffnung des Sockels 33 frei bewegen, der Innendurchmesser des Sockels 33 ist um ein Spiel größer als der Durchmesser der schlagaufnehmenden Schlagfläche 24 ausgelegt. Der Durchmesser des Bunds 22 ist größer als der Innendurchmesser des Sockels 33, demzufolge kann der Bund 22 an dem Sockel 33 entgegen Schlagrichtung 11 anliegen. Der angepresste Bohrer 4 drückt den Bund 22, d.h. dessen dem Schläger 15 zugewandte Stirnfläche 26, gegen den Sockel 33, was der Arbeitsstellung des Döppers 23 im Betrieb entspricht. Die schlagaufnehmende Schlagfläche 24 definiert in der Arbeitsstellung den Schlagpunkt des Schlagwerks 3. Der Fänger 32 liegt in Schlagrichtung 11 vor dem Bund 22 angeordnet. Der Fänger 32 ist ringförmig mit einem Innendurchmesser ausgebildet, der größer als der Durchmesser der schlagabgebenden Schlagfläche 24 und geringer als der Durchmesser des Bunds 22 ist. Die in Schlagrichtung 11 weisende Stirnfläche 27 des Bunds 22 kann in Schlagrichtung 11 an dem Fänger 32 anliegen, da sie in radialer Richtung überlappen. Der Döpper 16 wird von dem Fänger 32 gestoppt, nachdem der Schläger 15 auf den Döpper 16 bei fehlendem Anpressdruck des Werkzeugs 4 aufschlägt. Der Fänger 32 kann wie dargestellt als eine Einschnürung der Hülse 30 ausgebildet oder wie der beispielhafte Sockel 33 als getrenntes Bauteil ausgebildet sein. Der Fänger 32 hat vorzugsweise ein axiales Spiel in dem Maschinengehäuse 12. Der Fänger 32 ist mittels eines Dämpfelements 34 an dem Maschinengehäuse 12 in Schlagrichtung 11 abgestützt. Der Fänger 32 absorbiert vorzugsweise die kinetische Energie des Döppers 23, damit der Döpper 16 nicht aufgrund des Rückstoßes von selbst zurück in die Arbeitsstellung gleitet.The striker 16 is guided in a bearing 29 on the working axis 10 . The exemplary bearing 29 includes a sleeve 30 against which the cylindrical surface 25 of the collar 22 of the striker 23 abuts. In addition, the cylindrical jacket surface 31 of the core 21 for axially guiding the beatpiece 23 can rest on the sleeve 30 . The bearing 29 limits the axial movement in the direction of impact 11 by a catcher 32 and counter to the direction of impact 11 by a base 33. The example annular socket 33 is in the direction of impact 11 in front of the collar 22 of the striker 23. The core 21 may be in the opening of the Moving pedestal 33 freely, the inner diameter of the base 33 is designed to be a game greater than the diameter of the impact-absorbing face 24 . The diameter of the collar 22 is greater than the inner diameter of the base 33, consequently, the collar 22 may rest against the base 33 against impact direction 11 . The pressed drill 4 presses the collar 22, that is, the racket 15 facing end face 26, against the base 33, which corresponds to the working position of the striker 23 during operation. The impact-absorbing face 24 defines in the working position the point of impact of the striking mechanism 3. The catcher 32 is located in the direction of impact 11 in front of the collar 22 . The catcher 32 is annularly formed with an inner diameter which is larger than the diameter of the impact-releasing impact surface 24 and less than the diameter of the collar 22 . The pointing in the direction of impact 11 end face 27 of the collar 22 may rest in the direction of impact 11 on the catcher 32 , since they overlap in the radial direction. The striker 16 is stopped by the catcher 32 after the racket 15 strikes the striker 16 in the absence of contact pressure of the tool 4 . The catcher 32 may be formed as a constriction of the sleeve 30 as shown or like the example socket 33 may be formed as a separate component. The catcher 32 preferably has an axial play in the machine housing 12. The catcher 32 is supported on the machine housing 12 in the direction of impact 11 by means of a damping element 34 . The catcher 32 preferably absorbs the kinetic energy of the striker 23 to prevent the striker 16 from sliding back to the operative position by itself due to the recoil.

Der Döpper 16 und seine Lager 29 sind mit einer Kulisse 35 versehen, welche den Döpper 16 bei seiner Bewegung in Schlagrichtung 11 in eine Drehbewegung versetzt. Die Drehbewegung erweist sich als effektive Maßnahme, dem Döpper 16 während des Aufprallens in den Fänger 32 seine Bewegungsenergie zu entziehen. Der Döpper 16 bleibt dadurch nahe des Fängers 32 liegen und rutscht nicht unbeabsichtigt zurück in die Arbeitsstellung.The striker 16 and its bearings 29 are provided with a link 35 which causes the striker 16 in its movement in the direction of impact 11 in a rotational movement. The rotational movement proves to be an effective measure, the striker 16 to escape its kinetic energy during impact with the catcher 32 . The striker 16 thus remains close to the catcher 32 and does not accidentally slip back into the working position.

Die Kulisse 35 beinhaltet beispielsweise eine dem Fänger 32 zugewandte Stirnverzahnung 36 an der hinteren Stirnfläche 27 des Bunds 22 und eine dem Bund 22 zugewandte Stirnverzahnung 37 an dem Fänger 32. Die beiden Stirnverzahnungen 36, 37 sind zueinander komplementär. Die Stirnverzahnung 36 des Bunds 22 kann als Kegelzahnrad 36 ausgebildet sein, die komplementäre Stirnverzahnung 37 des Fängers 32 ist konkav eingewölbt. Der Döpper 16 ist in dem Lager 29 frei um die Arbeitsachse 10 drehbar. Die Winkelorientierung der beiden Stirnflächen 26, 27 ist daher weitgehend zufällig. Sobald der Döpper 16 auf den Fänger 32 aufschlägt, orientieren sich die beiden Stirnflächen 26 zueinander aus. Im Mittel dreht sich dabei der Döpper 16 um ein Viertel der Breite der Zähne 38 der Stirnverzahnung 36 gegenüber dem Fänger 32 bis die beiden Stirnverzahnungen 36, 37 zueinander ausgerichtet sind. Obwohl nur ein geringer Anteil der translatorischen kinetischen Energie in Rotationsenergie gewandelt wird, erweist sich die Kulisse 35 als stark dämpfend. Vermutlich ergibt sich die starke Dämpfung aufgrund einer dynamischen Hemmung, welche entsteht nachdem die beiden Stirnverzahnungen 36, 37 ausgerichtet sind. Die Stirnverzahnungen 36, 37 rücken nun aufgrund der Drehbewegung des Döppers 23 längs der Arbeitsachse 10 auseinander, gegen den Impuls des Döpper 16 in Schlagrichtung 11. The link 35 includes, for example the catcher 32 facing spur gear teeth 36 on the rear end surface 27 of the collar 22 and the collar 22 facing the spur gear toothing 37 at the catcher 32. The two end teeth 36, 37 are complementary to each other. The spur toothing 36 of the collar 22 may be formed as a bevel gear 36 , the complementary spur toothing 37 of the catcher 32 is concave. The striker 16 is freely rotatable about the working axis 10 in the bearing 29 . The angular orientation of the two end faces 26, 27 is therefore largely random. As soon as the striker 16 strikes the catcher 32 , the two end faces 26 are oriented towards one another. On average, the striker 16 rotates by a quarter of the width of the teeth 38 of the spur gear 36 with respect to the catcher 32 until the two spur gears 36, 37 are aligned with each other. Although only a small portion of the translational kinetic energy is converted into rotational energy, the gate 35 proves to be highly attenuating. Presumably results in the strong damping due to a dynamic inhibition, which arises after the two serrations 36, 37 are aligned. The spur gears 36, 37 now move apart due to the rotational movement of the striker 23 along the working axis 10 , against the pulse of the striker 16 in the direction of impact 11th

Die Stirnverzahnung 36 des Bunds 22 hat mehrere identische Zähne 38, die in Umfangsrichtung 39 aufeinanderfolgend äquidistant verteilt angeordnet sind. Die Zahl der Zähne 38 richtet sich nach der Größe des Döppers 16, beispielsweise liegt die Zahl zwischen 15 und 40. Die Kopflinie 40 des Zahns 38 ist geradlinig und liegt mit der Arbeitsachse 10 in einer Ebene. Bei der als Kegelzahnrad ausgebildeten Stirnverzahnung 36 des Bunds 22 ist die Kopflinie 40 zwischen 30 Grad und 70 Grad gegenüber der Arbeitsachse 10 geneigt. Die Kopflinie kann in einer anderen Ausgestaltung zu der Arbeitsachse 10 windschief sein, wobei sich die Kopflinie von einem Ende zu dem anderen Ende hin monoton von der Arbeitsachse 10 entfernt. Alternativ kann die Kopflinie spiralförmig ausgebildet sein. Der Zahn 38 hat eine nur in die rechtshändige Umfangsrichtung 41 weisende Flanke 42 und eine nur in die linkshändige Umfangsrichtung 39 weisende Flanke 43. Die beiden Flanken 42, 43 laufen in Schlagrichtung 11 aufeinander zu und in der Kopflinie 40 zusammen. Der Zahn 38 verjüngt sich in Schlagrichtung 11. Eine Neigung 44 der rechtshändigen Flanke 42 wird gegenüber einer Referenzebene 45 bestimmt. Die Referenzebene 45 wird von der Arbeitsachse 10 und dem Punkt auf der Flanke 42 aufgespannt, an dem die Neigung 44 zu bestimmen ist. Die Neigung 44 liegt vorzugsweise im Bereich zwischen 30 Grad und 60 Grad. Die Neigung 46 der linkshändigen Flanke 43 gegenüber der Referenzebene 45 ist vorzugsweise gleich der Neigung 44 der rechtshändigen Flanke 42. Die beiden Flanken 42, 43 können in Richtung zu der Arbeitsachse 10 aufeinander zulaufen. Der Zahn 38 ist somit an seiner Außenseite breiter als näher an der Arbeitsachse 10. Die Breite des Zahns 38 erhöht sich vorzugsweise proportional zu dem Abstand von der Arbeitsachse 10. Die Winkelbreite des Zahns 38 ist somit längs der radialen Richtung konstant. Eine Höhe 47 der Zähne 38, d.h. die Abmessung der Flanken 42, 43 längs der Arbeitsachse 10, liegt im Bereich zwischen 2 mm und 5 mm.The spur toothing 36 of the collar 22 has a plurality of identical teeth 38, which are arranged in the circumferential direction 39 successively distributed equidistant. The number of teeth 38 depends on the size of the striker 16, for example, the number is between 15 and 40. The head line 40 of the tooth 38 is rectilinear and lies with the working axis 10 in a plane. When formed as a bevel gear spur gear 36 of the collar 22 , the head line 40 between 30 degrees and 70 degrees with respect to the working axis 10 is inclined. The head line may be skewed in another embodiment with the working axis 10, wherein the head line monotonically from one end to the other end of the working axis 10 degrees. Alternatively, the head line may be formed spirally. The tooth 38 has a flank 42 pointing only in the right-handed circumferential direction 41 and an edge pointing only in the left-handed circumferential direction 39 43. The two flanks 42, 43 run in the direction of impact 11 towards each other and in the head line 40 together. The tooth 38 tapers in the direction of impact 11. An inclination 44 of the right-hand flank 42 is determined relative to a reference plane 45. The reference plane 45 is spanned by the working axis 10 and the point on the flank 42 at which the slope 44 is to be determined. The slope 44 is preferably in the range between 30 degrees and 60 degrees. The inclination 46 of the left-handed flank 43 with respect to the reference plane 45 is preferably equal to the inclination 44 of the right-hand flank 42. The two flanks 42, 43 can converge toward one another in the direction of the working axis 10 . The tooth 38 is thus wider on its outside than closer to the working axis 10. The width of the tooth 38 preferably increases in proportion to the distance from the working axis 10. The angular width of the tooth 38 is thus constant along the radial direction. A height 47 of the teeth 38, ie the dimension of the flanks 42, 43 along the working axis 10, is in the range between 2 mm and 5 mm.

Die Stirnverzahnung 37 des Fängers 32 ist komplementär zu der Stirnverzahnung 36 des Bunds 22 aufgebaut. Die Zwischenräume zwischen den Zähnen 48 des Fängers 32 entsprechen in Form und Zahl den Zähnen 38 des Bunds 22. Eine linksseitige Flanke 49 des Zahns 48 am Fänger 32 ist weitgehend deckungsgleich zu der rechtsseitigen Flanke 42 des Zahns 38 am Bund 22; analog ist eine rechtsseitige Flanke des Zahns 48 am Fänger 32 ist weitgehend deckungsgleich zu der linksseitigen Flanke 43 des Zahns 38 am Bund 22. The spur toothing 37 of the catcher 32 is constructed to be complementary to the spur toothing 36 of the collar 22 . The spaces between the teeth 48 of the catcher 32 correspond in shape and number to the teeth 38 of the collar 22. A left-hand flank 49 of the tooth 48 on the catcher 32 is largely congruent with the right-hand flank 42 of the tooth 38 on the collar 22; Similarly, a right-hand flank of the tooth 48 on the catcher 32 is largely congruent with the left-hand flank 43 of the tooth 38 on the collar 22nd

Der Fänger 32 kann in dem Maschinengehäuse 12 frei drehbar um die Arbeitsachse 10 gelagert sein. Insbesondere ist der Fänger 32 von der Abtriebswelle 6 entkoppelt. Bei einem Aufprall des Döppers 23 in den Fänger 32 drehen sich beide relativ zueinander. Die von dem Döpper 16 in den Fänger 32 übertragene Rotationsenergie wird dem Schlagwerk 3 entzogen. Das Dämpfelement 34 ist vorzugsweise drehfest in dem Maschinengehäuse 12, wodurch der Fänger 32 sich relativ zu dem Dämpfelement 34 bewegt. Die Reibung zwischen dem gummihaltigen Dämpfelement 34 und dem Fänger 32 entzieht dem Döpper 16 die Bewegungsenergie.The catcher 32 may be freely rotatable about the working axis 10 in the machine housing 12. In particular, the catcher 32 is decoupled from the output shaft 6. Upon impact of the striker 23 in the catcher 32 , both rotate relative to each other. The rotational energy transmitted by the striker 16 into the catcher 32 is removed from the striking mechanism 3 . The damping element 34 is preferably rotationally fixed in the machine housing 12, whereby the catcher 32 moves relative to the damping element 34 . The friction between the rubber-containing damping element 34 and the catcher 32 extracts the kinetic energy from the striker 16 .

Alternativ oder zusätzlich zu der Kulisse 35 mit der Stirnverzahnung 36, 37 kann eine Kulisse 50 an einer Mantelfläche 25, 31 des Döppers 23 angreifen, um den Döpper 16 in eine Drehbewegung zu überführen. Die beispielhafte Kulisse 50 hat eine in der Mantelfläche 31 spiralförmig verlaufende Nut 51. Das Lager 29 ist mit einem Läufer 52 versehen, der in die Nut 51 eingreift. Der Läufer 52 ist in dem Lager 29 derart verbunden, dass der Läufer 52 gegenüber dem Lager 29 längs der Arbeitsachse 10 und in Umfangsrichtung 41 unbeweglich ist. Der Läufer 52 kann beispielsweise eine Kugel sein, die in dem Lager 29 eingefasst ist.Alternatively, or in addition to the slide 35 with the spur toothing 36, 37 , a link 50 on a lateral surface 25, 31 of the striker 23 engage to convert the striker 16 in a rotational movement. The exemplary gate 50 has a groove 51 extending spirally in the lateral surface 31. The bearing 29 is provided with a rotor 52 , which engages in the groove 51 . The rotor 52 is connected in the bearing 29 such that the rotor 52 relative to the bearing 29 along the working axis 10 and in the circumferential direction 41 is immovable. The rotor 52 may be, for example, a ball that is enclosed in the bearing 29 .

Vorzugsweise kann die Kugel sich in der Fassung um ihr Zentrum drehen. Der Läufer 52 liegt mit einer Flanke an einer schräg zur Arbeitsachse 10 verlaufenden Flanke 53 der Nut 51 an. Die Bewegung des Döppers 23 längs der Arbeitsachse 10 erzwingt eine relative Drehbewegung von Döpper 16 und Lager 29. Die Nut 51 kann eine konstante Steigung 54 längs der Arbeitsachse 10 aufweisen. Die Länge der gesamten Nut 51 entspricht dem freien Weg des Döppers 23 zwischen dem Sockel 33 und dem Fänger 32, typischerweise im Bereich zwischen 20 mm und 50 mm. Vorteilhafterweise ist die Nut 51 an einem dem Schläger 15 zugewandten Ende parallel zu der Arbeitsachse 10 und die Steigung 54 erhöht sich in Schlagrichtung 11. Der parallele Abschnitt kann zwischen 4 mm und 10 mm lang sein. Die Steigung 54 am werkzeugseitigen Ende der Nut 51 liegt zwischen 30 Grad und 60 Grad. Die Kugel kann gleichermaßen in der Mantelfläche 31 des Döppers 23 gefangen und die Nut in der Innenfläche der Hülse 30 angeordnet sein. Ferner können mehrere identische Nuten 51 um die Arbeitsachse 10 vorgesehen sein.Preferably, the ball can rotate in the socket about its center. The rotor 52 is located with a flank on an obliquely to the working axis 10 extending edge 53 of the groove 51 at. The movement of the striker 23 along the working axis 10 forces a relative rotational movement of striker 16 and bearing 29. The groove 51 may have a constant pitch 54 along the working axis 10 . The length of the entire groove 51 corresponds to the free path of the striker 23 between the base 33 and the catcher 32, typically in the range between 20 mm and 50 mm. Advantageously, the groove 51 is parallel to the working axis 10 at an end facing the racket 15 and the pitch 54 increases in the direction of impact 11. The parallel section may be between 4 mm and 10 mm in length. The slope 54 at the tool-side end of the groove 51 is between 30 degrees and 60 degrees. The ball can equally be caught in the lateral surface 31 of the striker 23 and the groove 30 may be arranged in the inner surface of the sleeve. Furthermore, a plurality of identical grooves 51 may be provided around the working axis 10 .

Claims (10)

  1. Hand-held chiselling power tool comprising:
    a tool holder (2) for holding a chiselling tool coaxially with a working axis (10),
    a motor (5),
    a striking mechanism (3) having an exciter (13) forcibly excited periodically by the motor (5), a striker (15) movably guided coaxially with the working axis (10), a pneumatic chamber (14) provided between the exciter (13) and the striker (15) for coupling the movement of the striker (15) to the movement of the exciter (13) and a plunger (16) arranged downstream of the striker (15) in the impact direction (11) for indirectly transmitting an impact from the striker (15) to a tool (4) held in the tool holder (2), the plunger (16) having a circumferential surface (25) and an end surface (27) pointing in the impact direction (11),
    a bearing (29) including a sleeve (30) arranged coaxially with the working axis (10) and a catcher (32), the circumferential surface (25) of the plunger (16) being slidably guided on the sleeve (30) and the catcher (32) being arranged in the impact direction (11) of the end surface (27) of the plunger (16) in order to limit the movement of the plunger (16) in the impact direction (11),
    characterised by
    a link (35; 50) that forces the plunger (16) and the bearing (29) to rotate relative to one another when the plunger (23) moves in the impact direction (11), the link (35) having one flank (42; 53) on the plunger (16) and one flank (49; 52) on the bearing (29), wherein the two flanks (42; 53, 49; 52) bearing against one another during the movement rise in the same circumferential direction (39) in the impact direction (11).
  2. Hand-held chiselling power tool according to claim 1, characterised in that the link (35) has one end tooth system (36) on the end surface (27) of the plunger (23) and one end tooth system (37) on the catcher (32).
  3. Hand-held chiselling power tool according to claim 2, characterised in that the end tooth systems (36, 37) are designed to be complementary to one another.
  4. Hand-held chiselling power tool according to claim 3, characterised in that the end tooth system (36) of the plunger (23) has several identical teeth (38) and the flanks (42, 43) of each tooth (38) converge in the impact direction (11).
  5. Hand-held chiselling power tool according to claim 4, characterised in that the inclination (44) of the flanks (42) is between 30 degrees and 60 degrees.
  6. Hand-held chiselling power tool according to claim 4 or 5, characterised in that the dimension (47) of the flanks (42, 43) in the impact direction (11) is between 2 mm and 5 mm.
  7. Hand-held chiselling power tool according to one of the preceding claims, characterised in that the bearing (29) is mounted in the machine housing (12) in such a manner that it can rotate about the working axis (10).
  8. Hand-held chiselling power tool according to one of the preceding claims, characterised in that the catcher (32) can rotate about the working axis (10) and bears against a flexible damping element (34) in the impact direction (11).
  9. Hand-held chiselling power tool according to one of the preceding claims, characterised in that the link (50) has a helical groove (51) forming the flank (53) in a cylindrical circumferential surface (25, 31) of the plunger (23) and a runner (52) engaging in the groove (51) from the bearing (29) or the link has a helical groove forming the flank in a cylindrical inner surface of the bearing (29) and a runner engaging in the groove from the plunger (16).
  10. Hand-held chiselling power tool according to claim 9, characterised in that the groove (51) has a portion parallel to the working axis (10) at a front end as viewed in the impact direction (11) and the pitch (54) of the groove (51) increases in the impact direction (11).
EP15709154.7A 2014-03-12 2015-03-10 Chiselling hand-held machine tool Not-in-force EP3116688B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14159121.4A EP2918376A1 (en) 2014-03-12 2014-03-12 Chiselling hand-held machine tool
PCT/EP2015/054919 WO2015135916A1 (en) 2014-03-12 2015-03-10 Chiselling portable power tool

Publications (2)

Publication Number Publication Date
EP3116688A1 EP3116688A1 (en) 2017-01-18
EP3116688B1 true EP3116688B1 (en) 2018-01-31

Family

ID=50289393

Family Applications (2)

Application Number Title Priority Date Filing Date
EP14159121.4A Withdrawn EP2918376A1 (en) 2014-03-12 2014-03-12 Chiselling hand-held machine tool
EP15709154.7A Not-in-force EP3116688B1 (en) 2014-03-12 2015-03-10 Chiselling hand-held machine tool

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP14159121.4A Withdrawn EP2918376A1 (en) 2014-03-12 2014-03-12 Chiselling hand-held machine tool

Country Status (4)

Country Link
US (1) US20170014983A1 (en)
EP (2) EP2918376A1 (en)
CN (1) CN105939820B (en)
WO (1) WO2015135916A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11858104B2 (en) 2018-12-21 2024-01-02 Hilti Aktiengesellschaft Portable power tool

Family Cites Families (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1796371A (en) * 1928-12-04 1931-03-17 Nordiska Armaturfab Ab Arrangement in striking tool
US2831462A (en) * 1951-03-30 1958-04-22 Atlas Copco Ab Hammer pistons and percussion apparatuses provided with such hammer pistons
US2833173A (en) * 1957-01-08 1958-05-06 Reginald J Aspeek Rotary impact hand tool
GB1030136A (en) * 1963-10-23 1966-05-18 Kango Electric Hammers Ltd Improvements relating to power-operated percussive tools
US3768577A (en) * 1972-07-28 1973-10-30 Nuova Lapi Pneumatic screw-drivers
US4364440A (en) * 1980-05-08 1982-12-21 Milton Clar Hand held rotary impact tool
DE3304916A1 (en) * 1983-02-12 1984-08-16 Robert Bosch Gmbh, 7000 Stuttgart DRILLING HAMMER
US4561507A (en) * 1984-03-06 1985-12-31 Liou Mou T Tool adapter
US4745980A (en) * 1985-03-30 1988-05-24 Chung Te Shun Auto-hammer driver
NO300702B1 (en) * 1996-02-19 1997-07-07 Bakke Oil Tools As Orientation device, especially for drilling tools or well tools
DE19726383A1 (en) * 1997-06-21 1998-12-24 Bosch Gmbh Robert Power tool
DE10019071A1 (en) 2000-04-18 2001-10-25 Hilti Ag Electric hand tool device with blank stop
US6467547B2 (en) * 2000-12-11 2002-10-22 Weatherford/Lamb, Inc. Hydraulic running tool with torque dampener
DE60200127T2 (en) * 2001-03-07 2004-06-03 Black & Decker Inc., Newark hammer
US7032683B2 (en) * 2001-09-17 2006-04-25 Milwaukee Electric Tool Corporation Rotary hammer
DE10157831B4 (en) * 2001-11-24 2004-06-24 Robert Bosch Gmbh Hand-held machine tool with a die for receiving a tool
US6745836B2 (en) * 2002-05-08 2004-06-08 Jeff L. Taylor Down hole motor assembly and associated method for providing radial energy
DE10261030A1 (en) * 2002-12-24 2004-07-08 Robert Bosch Gmbh Rotary Hammer
DE10346534A1 (en) * 2003-10-07 2005-05-12 Bosch Gmbh Robert Hand tool with a striking mechanism and method for operating the power tool
GB2423044A (en) * 2005-02-10 2006-08-16 Black & Decker Inc Hammer with cam-actuated driven member
DE102005000042A1 (en) * 2005-04-25 2006-10-26 Hilti Ag Chisel or chisel
DE102006000168A1 (en) * 2006-04-10 2008-01-03 Hilti Ag tool holder
DE102006000209A1 (en) * 2006-05-05 2007-11-15 Hilti Ag Hand tool machine with impact tool holder
US7604640B2 (en) * 2007-06-14 2009-10-20 Zimmer Spine Austin, Inc. Device and system for applying rotary impact
DE102010029918A1 (en) * 2010-06-10 2011-12-15 Hilti Aktiengesellschaft machine tool
DE102010044011A1 (en) * 2010-11-16 2012-05-16 Hilti Aktiengesellschaft Hand tool
DE102011004985A1 (en) * 2011-03-02 2012-09-06 Hilti Aktiengesellschaft tool holder
DE102012212231A1 (en) * 2012-07-12 2014-01-16 Hilti Aktiengesellschaft Hand tool
JP6070826B2 (en) * 2013-03-26 2017-02-01 日立工機株式会社 Electric tool

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11858104B2 (en) 2018-12-21 2024-01-02 Hilti Aktiengesellschaft Portable power tool

Also Published As

Publication number Publication date
WO2015135916A1 (en) 2015-09-17
CN105939820A (en) 2016-09-14
EP3116688A1 (en) 2017-01-18
US20170014983A1 (en) 2017-01-19
CN105939820B (en) 2017-12-29
EP2918376A1 (en) 2015-09-16

Similar Documents

Publication Publication Date Title
DE60302283T2 (en) Hammer drill with overload clutch
DE3224176C2 (en) Motor-driven striking hand machine tool
EP2855099B1 (en) Apparatus of hand-held machine tool
CH637056A5 (en) DRILLING HAMMER.
DE2109239A1 (en) Power-driven device for drilling holes in or otherwise processing concrete, masonry and the like, in particular rotary hammer
DE102008000727A1 (en) Portable machine tool, in particular drilling or percussion hammer, with a club catching device and / or racket damping device
DE10105250A1 (en) Tool insert holding device in striking tools
DE102009027440A1 (en) Hand tool
EP2684646B1 (en) Manual tool machine
EP2612731B1 (en) Handheld tool apparatus
EP1910039B1 (en) Percussion mechanism for an at least percussively-operated hand-held tool
EP3233382B1 (en) Power tool
EP1621290B1 (en) Machine tool with intermittent angular momentum
EP2561962B1 (en) Hand-held tool machine
EP3116688B1 (en) Chiselling hand-held machine tool
EP2842696B1 (en) Power tool
EP1355764A1 (en) Pneumatic percussive tool with a short working drive piston
DE102011089917A1 (en) Hand tool device
EP3052274B1 (en) Manual tool machine
DE3120326A1 (en) DRILLING HAMMER
DE3039617A1 (en) DRILLING HAMMER
EP3898117B1 (en) Handheld chiselling machine tool
DE3024715C2 (en) Impact drill
DE1427747C3 (en) Tool for replaceable tools that can be driven by means of a striking and / or rotary movement and the use of such a tool
DE3040464A1 (en) Pneumatic impact drill with reciprocating piston - has striker in cylinder between piston and anvil holding bit

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20161012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20171020

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 966910

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180215

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502015002986

Country of ref document: DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180322

Year of fee payment: 4

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180131

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180430

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180430

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180501

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180531

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502015002986

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180331

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180310

26N No opposition filed

Effective date: 20181102

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180310

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180331

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180331

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180331

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180331

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502015002986

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190310

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191001

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190310

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20150310

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180131

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180131

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 966910

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200310

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200310