EP2517835B1 - Outil à moteur - Google Patents

Outil à moteur Download PDF

Info

Publication number
EP2517835B1
EP2517835B1 EP12157411.5A EP12157411A EP2517835B1 EP 2517835 B1 EP2517835 B1 EP 2517835B1 EP 12157411 A EP12157411 A EP 12157411A EP 2517835 B1 EP2517835 B1 EP 2517835B1
Authority
EP
European Patent Office
Prior art keywords
hammer
anvil
section
control contour
pitch
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP12157411.5A
Other languages
German (de)
English (en)
Other versions
EP2517835A2 (fr
EP2517835A3 (fr
Inventor
Laurent Wahl
Dieter Profunser
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 EP2517835A2 publication Critical patent/EP2517835A2/fr
Publication of EP2517835A3 publication Critical patent/EP2517835A3/fr
Application granted granted Critical
Publication of EP2517835B1 publication Critical patent/EP2517835B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B25B21/026—Impact clutches

Definitions

  • the invention relates to a hand tool.
  • the hand tool can be realized for example in the form of a hammer drill or impact wrench.
  • the Tangentialtschwerk produce a Schlagschraubterrorism the output shaft.
  • the tool may be in the form of a screwdriver which can carry out a striking screw movement in the tool holder via the rotating and partially striking movement of the output shaft.
  • the Tangentialtschtechnik is usually powered by a motor, possibly with the interposition of a transmission.
  • the main components of a clutch-like tangential impactor are a hammer associated with a drive shaft of the clutch and an anvil associated with an output shaft of the clutch.
  • the hammer can be axially against the force of a spring while twisting the same from the anvil and then again while twisting the same-accelerated by the force of the spring-striking against the anvil to be moved.
  • the impact movement is practically tangential to the rotational movement.
  • the rotational movement and axial reciprocating motion for the execution of a rotary impact are coupled by a slotted guide, so that the hammer ultimately positively moves under specification of the slotted guide.
  • the hammer is triggered by the anvil.
  • the hammer makes a pivotal strike against the anvil.
  • the hammer can strike, for example, every half revolution practically tangential to the rotational movement of the anvil and transmit relatively high torque peaks during the rotary impact.
  • Such high torque peaks would usually not be achievable by a continuous rotary drive of the output shaft.
  • the hammer decouples from the anvil in the release position - ie the release torque when performing a separation of an engagement of the anvil and the hammer.
  • the operating point is characterized by the torque transmittable at impact. Decisive for this are, inter alia, the moment of inertia of the hammer, the spring stiffness of the spring and the transfer function of the slotted guide, which is ultimately predetermined by a control contour of the slotted guide.
  • a tangential screwdriver according to the preamble of claim 1 is made JP 2003 181774 A known.
  • a tangential striking device has a comparatively low release torque, which is achieved by means of a comparatively low spring rigidity.
  • a high torque requiring drilling of z. B. deep holes with large diameters is only partially possible using such a conventional Tangentialschlagwerks.
  • a first pitch angle ⁇ of the first pitch measured with respect to an axis of a cylindrical body for the link guide is smaller than a second pitch angle ⁇ of the second pitch measured with respect to the axis.
  • the slopes have in particular the same sign, ie the sections are part of a single thread-like course of the control contour.
  • the first section forms an anvil-proximal section and the second section forms an anvil-distant section of the control contour, wherein the first gradient is greater than the second gradient.
  • the first and the second pitch may be only significantly different slopes of the control contour. That except for a transitional area that is as continuous as possible, there are practically only the first and second sections with significantly different gradients.
  • the first and second portions directly adjoin one another.
  • the invention is based on the consideration that a Tangential Farbwerk for a user-friendly and comparatively low-weight hand tool machine should have a spring system with relatively low spring stiffness. On the basis of this, it has additionally been recognized that nevertheless a comparatively high release torque can be achieved if a slotted guide, in particular in an impact associated with, here e.g. first, section is preferably designed steeply. It has also been recognized that in order to transmit a comparatively high torque peak in a hammer to anvil stroke, a slotted guide, particularly in one of the hammer and anvil firing, here e.g. second, section preferably suitably flat. In principle, the invention has recognized that a first portion assigned to the impact and a second portion assigned to the triggering can be provided with a different first and second pitch of a thread-like control contour.
  • the concept of the invention therefore provides a slotted guide with a thread-like control contour which has a slope that is varied in an adapted manner.
  • This control contour adapted in the above-mentioned manner has a different pitch in a first section assigned to the torque transmission than in a second section assigned to triggering of the hammer and anvil.
  • the slide guide can also have a basically V-like - even double-threaded - executed control contour.
  • the anvil is integral with the output shaft and the spindle integrally connected to the drive shaft.
  • the slotted guide is on a cylindrical body, such as a shaft - e.g. Spindle or a hollow body formed; for example, on an outside or inside of the cylindrical body.
  • the slotted guide on a first control contour on a spindle between the drive shaft and output shaft has a second control contour on a shell inside of the hammer.
  • first and second control contour in a preferred slotted guide can be an axial and rotary movement of hammer against anvil for performing a rotary-striking movement realize with advantage.
  • first control contour or only the second control contour of the slotted guide each having a first portion with the first slope and a second portion with the second different pitch.
  • the first control contour and the second control contour of the sliding guide each to have a first section with the first gradient and a second segment with the second differential gradient.
  • the first section forms an anvil-proximal section and the second section forms an anvil-distant section of the control contour.
  • the first slope is greater than the second slope.
  • a first helix angle ⁇ of the first pitch measured with respect to an axis of a cylindrical body for the slotted guide is smaller than a one measured with respect to the axis second pitch angle ⁇ of the second pitch.
  • first and second pitches are substantially single pitches of the control contour and the first and second portions are directly adjacent to each other. This leads to a comparatively simple design of the control contour.
  • a further section may be provided, which is provided as a transition section with a gradual slope adjustment or has a constant value lying between the first and second pitch.
  • control contour-preferably a first control contour- is formed by a closed link of the slotted guide.
  • a closed slot is formed in the form of a groove (eg, with a U-shaped cross-section), wherein a sliding block positively connected to the hammer can be moved in the slot.
  • control contour is formed by an open link of the slide guide.
  • second control contour is formed by an open link of the slotted guide.
  • an open slide in the form of a running surface (with a flat cross-section) is formed, wherein on the running surface a forcibly guided connected to the hammer sliding block is movable.
  • the link guide is formed by an interaction of a closed gate on a spindle between the drive shaft and output shaft and an open gate on a shell inside of the hammer. It can alternatively also the slide guide by an interaction of a closed gate on a shell inside of the hammer and an open gate on a spindle between the drive shaft and Be formed output shaft.
  • control contour is formed in the form of a groove of the tread, wherein a force-guided on the control contour sliding block is movable.
  • control contour can also be formed inversely thereto, for. B. with a web on or on which a sliding block is forced.
  • a control contour of a slotted guide for realizing a suitable transfer function with two different gradients can be realized in a manner adapted to the design requirements.
  • the first section forms an anvil-proximal section and the second section forms an anvil-distant section of the control contour, the first slope being greater than the second slope.
  • the first pitch assigned to the transmission of the torque peak during impact is greater than the second pitch of the control contour assigned to the triggering of the hammer and anvil, in particular in the case of a first control contour located on the spindle.
  • the first slope increases in the first region near the anvil.
  • the increase can be implemented gradually.
  • the first section of greater pitch may also be in the form of a first anvil-proximal section of constant pitch greater than the second pitch in the second anvil-distal section.
  • the second slope of the control contour is comparatively small.
  • the pitch curve in the second section may gradually decrease.
  • the second section can also be designed relatively simply as a section of constant second pitch, which is less than one first climb in the first section.
  • a gradient curve in the transition from the first to the second section can be made gradual or graduated or as a simple step between the first and second gradient.
  • the anvil and the hammer is preferably in fully engaged position.
  • the anvil and the hammer have an engaging portion which may be predetermined by the length of stopper means, for example.
  • the first section in particular of a larger pitch, has an axial extent which makes up at least 20% of the axial extent of the engagement area. This ensures that at least on the remaining 20% of the axial extent of the engagement region an advantageously larger first slope is present, which allows a transmission of particularly high torque peaks. The result tends to be improved in the impact, the greater the axial extent of the first section.
  • the axial extension of the section makes up at least 20% of the axial extent of the engagement region or approximately corresponds to the extent of the engagement region without, however, exceeding it.
  • a stop means is formed in the anvil and / or hammer, preferably in the form of at least one cam.
  • Particularly advantageous two cams have proven.
  • the cams are advantageous on a ring circumference of the anvil or the Hammer formed.
  • the ring circumference can be arranged on the head side or laterally of the anvil and / or hammer.
  • the development with two cams allows with appropriate adaptation of the control contour a triggering or tangential striking of the hammer and anvil at every half turn.
  • more than two cams may be provided, for example in the form of a ring gear. In particular, this may limit a rotational movement to a fraction of a full revolution of the hammer.
  • a hand tool machine in the form of a rotary hammer can be formed.
  • the Tangentialtschtechnik is designed to perform the function of a slip clutch.
  • the tangential impactor may also preferably be operated out of resonance of the corresponding spring-mass system.
  • the second slope in the second anvil distant portion of the control contour is preferably designed such that the tangential impactor has a particularly high release torque to allow the normal drilling operation of the hammer drill, d. H. in normal drilling operation just do not trigger.
  • the Tangentialtschtechnik is designed to perform the function of a Schlagschraubzi.
  • the first slope in the first anvil-proximal portion is designed with a comparatively high value in order to achieve a particularly high torque peak transfer during the rotary impact between the hammer and the anvil.
  • An adaptation of the control contour according to the concept of the invention is especially advantageous for the two aforementioned cases of use.
  • the aforementioned cases of use can also be combined with one another by an optimized adaptation of both the first section with a comparatively larger pitch and the second section with a comparatively smaller pitch.
  • Fig. 1 shows a hand tool 100, which can be kept - for example in the form of an impact wrench - on a handle 102 formed by the housing 101 and the drive 104 can be activated here via a trigger 103 in the form of a lever or push button.
  • the drive 104 is formed here with a motor 105 in the form of an electric motor having an in Fig. 2 indicated rotational movement 1 via a gear 106 and a drive shaft 50 transmits to a spindle 20.
  • the spindle 20 is disposed between the drive shaft 50 and an output shaft 30 and in this case integrally connected to the drive shaft 50.
  • the rotational movement 1 of the spindle 20 is about the in Fig.
  • the on the same axis 2 as the spindle 20 and the output shaft 30 mounted in the tool holder 40 tool - for example, a screwdriver or the like- is capable of higher torques than with the continuous torque output of the motor 105 achievable, for example, a screw to transfer.
  • the tangential impactor 10 can be modeled as part of a spring-mass system. It is operated in the present case in the resonant range, which optimizes the torque peak transfer to the tool and the screw. A preferred application of an impact wrench shown is z. As the screwing of screws, setting anchors in concrete or the like hard ground.
  • the tangential impact mechanism 10 has an anvil 60 assigned to the output shaft 30 and a hammer 70 assigned to the drive shaft 50. Under the action of force of a spring 80 and a slotted guide 90, the hammer 70 can here be moved axially while twisting the same-practically tangentially to the direction of rotation-striking the anvil 60.
  • the axial movement 4 is presently indicated by an arrow as a reciprocating motion and the rotational movement 3 is indicated by a further arrow.
  • a forward turning point of the axial movement 4 follows the abutment of the hammer 70 on the anvil 60 by a rotary stroke (also called a tangential stroke) in which the torque peak is transmitted between the hammer 70 and the anvil 60.
  • a rear reversal point of the axial movement 4 is beyond a triggering location of hammer 70 and anvil 60.
  • the trip location is approximately in the region of the transition between the first and second sections 93, 94 of the control contour 91 explained below; ie approximately in the region of the kinking of the control contour 91.
  • the hammer 70 is shown far beyond the trip location to more clearly show the course of the slotted guide 90.
  • the anvil 60 has stop means in the form of two anvil cams 64 - of which only an anvil cam 64 lying on one side of the anvil is shown.
  • the bottom surface of the anvil cam 64 shown serves as the anvil striking surface 62.
  • a corresponding impulse mediated by abutment of the hammer 70 is imparted to the anvil striking surface 62 so that a torque peak is transmitted from the hammer 70 to the anvil 60.
  • the hammer 70 has two hammer cam 74, wherein the in Fig. 2 recognizable front of the lower hammer cam 74 serves as a hammered surface 72. This provided with abutment against the anvil striking surface 62 for transmission of said pulse.
  • a torque peak is transmitted to the anvil 60 during each half revolution of the spindle 20.
  • the two anvil cams 64 and two hammer cams 74 are designed accordingly and placed in coordination with the slotted guide 90.
  • the slide guide 90 here has a closed slot in the form of a groove 96 which is formed in the spindle 20 and the single continuous course of a thread-like control contour 91 follows.
  • the groove 96 is a here executed as a ball sliding block 92, via which the hammer 70 with a degree of freedom movable-forcibly guided by the slide guide 90 sits on the spindle 20 and is connected to this form-fitting manner; namely movable under execution of the reciprocating movement in the axial direction 4 and the rotational movement in the tangential direction 3.
  • the anvil abutment surfaces 62 and hammer abutment surfaces 72 are aligned perpendicular to the circumferential direction of the anvil 70 and hammer 60 here.
  • a perpendicular to the anvil striking surface 62 or hammer striking surface 72 thus points in a tangent direction to the annular circumference of the anvil 60 that surrounds the anvil cam 64 and the annular circumference of the hammer 70 that surrounds the hammer cam 74.
  • the slotted guide 90 has a first anvil-proximal portion 93 and a second anvil-distal portion 94, the first portion having a smaller axial extent than the second portion 94.
  • the second portion 94 directly adjoins the first portion 93.
  • the control contour 91 has a single thread-like course with a first, comparatively steep slope.
  • the control contour 90 has a single thread-like progression which continues in the same direction in the same direction in the first section 93 and has a second, flatter slope. The second, a smaller pitch angle ⁇ against the axis 2 having slope is thus greater than the first slope with a larger pitch angle a.
  • the first portion 93 has an axial extent that is slightly smaller than the axial extent of an engagement portion 95 of anvil 60 and hammer 70.
  • the engagement region 95 is determined by the axial extent of the stop means-namely here the anvil cam 64 and the hammer cam 74-.
  • the first slope -with a smaller pitch angle ⁇ - ensures that a rotary motion of the hammer 70 shortly before the tangential impact between the hammer 70 and the anvil 60 occurs in the region of the first, steeper slope of the first portion 93 in the tangential direction to the one is sufficiently accelerated and on the other hand, the rotational energy can be transmitted as a torque peak.
  • the spindle 20 is positively driven by the hammer 70 via the slide guide 90- through.
  • the hammer 70 remains in engagement with the anvil 60 via the hammer cam 74 and the anvil cam 64 until the head sides 63, 73 of the anvil cam 64 or hammer cam 74 can rotate past one another. This is done practically as soon as the anvil 60 and hammer 70 have moved farther apart than the axial extent of the engagement region 95.
  • the firing moment of hammer 70 and anvil 60 is determined by the first slope of the control contour 91 according to the first pitch angle ⁇ .
  • the release position of the anvil 60 and the hammer 70 is in the release position of the anvil 60 and the hammer 70 to perform the Separation of the engagement of the same with the hammer 70 forcibly connected sliding block 92 in the second section 94 of the control contour 90 and goes into this over.
  • the comparatively high release torque is also achieved without having to increase the total mass of the tangential impactor 10.
  • the tangential impactor 10 thus allows the operation of the hand tool 100 in the form of a impact wrench in applications with comparatively large torques in an improved manner. Also, this allows the use of the tangential impactor 10 in a hammer drill under stress with comparatively large torques occurring, for example, when drilling deep holes and / or large diameter.
  • the presently designated Tangentialtschtechnik 10 is also suitable as a slip clutch for example, a hammer drill or impact wrench.
  • the first slope with pitch angle ⁇ is chosen to be so small that a separation of an engagement between the hammer 70 and anvil 60 at normal torque load of the output shaft 30 practically does not occur.
  • FIG. 3A as a side view and in Fig. 3B as an end view of another Tangentialtschtechnik 11 is shown, which for a particularly preferred embodiment of a schematically in Fig. 1 Hand tool 100 shown is suitable.
  • Fig. 3A and Fig. 3B show to a drive shaft 51 which is connected in a manner not shown, for example via a gear 106 with a motor 105 of a power tool 100 rotationally driven.
  • a tool holder 40 or the like for receiving a tool, not shown, of the power tool 100 can be mounted in a manner not shown. Recognizable off Fig.
  • 3A and 3B is the output shaft 31 by means of the drive shaft 51 and a Tangentialtschwerk 11 in a rotating and partially beating movement displaceable - this basically analogous to the above with reference to Fig. 2 explained principle.
  • the tangential striking mechanism 11 has an anvil 61 assigned to the output shaft 31 and a hammer 71 assigned to the drive shaft 51.
  • the hammer 71 and the anvil 61 act in principle in the already principle with reference to Fig. 2 explained way together.
  • FIG. 3A and Fig. 3B shown constructive realization of the hammer 71 under the action of a spring 81 and one of the views (A) and (B) of Fig. 3A as well as the Fig. 4 apparent slide guide 190 axially movable and twisting of the hammer 71 this is against the anvil 61 beatable.
  • the anvil 61 is integrally connected to the output shaft 31.
  • a spindle 21 is presently integrally connected to the drive shaft 51.
  • the spring 81 is concentric with the spindle 21.
  • the drive shaft 51, the spindle 21, the anvil 61 and the output shaft 31 are each arranged concentrically to the axis 2 to form the tangential impact mechanism 11.
  • the spring 81 and the hammer 71 sit to move also concentric to the axis 2 on the spindle 21.
  • the spring 81 is supported on the side of the drive shaft 31 from an annular stop 22, which sits at a shoulder between the spindle 21 and drive shaft 51.
  • the spring 81 is supported on an end face 75 of the hammer 71 and biases it, or is able to move it in the direction of the axis 2 under positive guidance of the guide link 190. Both the end face 75 and the annular stop 22 for the spring 80 are shown schematically in FIG Fig. 2 shown.
  • the slotted guide 190 for the preferred constructive realization of the tangential impactor 11 is further referred to the views (A) and (B) to illustrate the sections A - A and B - B of the Fig. 3A and referring to the Fig. 4 described.
  • the slotted guide 190 has a first control contour 91.1 and a second control contour 91.2.
  • the first control contour 91.1 indicates the course of a closed slide in the form of a groove 180 in the spindle 21.
  • the groove 180 is threadedly introduced into the spindle 21 and has a basically V-shaped course, the -wie in view (B) of Fig. 3A evident- in plan symmetrical to the axis 2 extends.
  • a first branch 181 of the V-shaped groove 180 and a second branch 182 of the V-shaped groove 180 are so far mirror-symmetrical and formed in principle gleichver signed.
  • Each of the branches 181, 182 of the V-shaped groove 180 has a first portion 193 with a first pitch and a second portion 194 with a second pitch.
  • the first thread-like control contour 91.1 is assigned to the outer shell surface of the spindle 21 in the tangential impact mechanism 11, a second in Fig. 4 apparent control contour 91.2, which is introduced in a shell inside of the hammer 71.
  • the second control contour 91.2 specifies the course of an open backdrop in the form of a tread.
  • the second control contour 91.2 also has a first section 193 and a second section 194 provided with the same reference numerals for the sake of simplicity. Again, in the first section 193, a slope of the second control contour 91.2 measured with respect to the axis 2 is greater than a slope of the control contour 91.2 in the second section 194.
  • first slope of the control contours 91.1, 91.2 is so large that approach the control contours 91.1, 91.2 in the course of a virtually paraxial course to the axis 2.
  • the smallest first pitch angle ⁇ in the first section 193 thus results at the top of the overall V-shaped course of the control contour 190 where the first branch 181 and the second branch 182 collide in plan view at the level of the axis 2--.
  • the first slope of the control contour 91.1, 91.2 of the first section 193 asymptotically merges into the second slope of the second section 194.
  • the first and second pitches - as exemplified by the pitch angles ⁇ , ⁇ - are the substantially single different pitches of the control contour 190.
  • first control contour 91.1 and the second control contour 91.2 are best obtained from view (A) of Fig. 3A .
  • a sliding block 192 resting in the groove 180 of the spindle 21 as well as on the running surface 170 of the hammer 71 is forcibly guided.
  • Similar to the already with reference to Fig. 2 explained principle is the hammer 71 while rotating the same axially along the axis 2 of the spindle 21 according to the specification of the slotted guide 190 movable.
  • the bias of the spring 81 is thereby converted into kinetic energy of the hammer 71, which emits this as a torque peak when striking against the anvil 61. Beat it Hammer cam 74 and anvil cam 64 in the view (B) of Fig. 3A and Fig. 3B shown manner to each other.
  • the positively driven sliding block 192 merges into the second section 194 of the slotted guide 190, ie into the region of the shallower second gradient with a gradient angle ⁇ .
  • the sliding block 192 further passes through the groove 180 of the slotted guide 190 circumferentially of the spindle 21 and thus passes into the first portion 194 of the first branch 181 of the groove 180.
  • the movement of the sliding block 192 then continues on the other side of the spindle 21 in basically the same way. In total, one stroke of the hammer 61 and the anvil 71 is thus carried out per half revolution of the spindle 21.
  • a relatively high release torque of the hammer 71 against the anvil 61 is achieved by the steeper slope with first pitch angle ⁇ in the first section 193 of the slide guide 190.
  • this comparatively high release torque can be achieved with comparatively low spring stiffness of the spring 81 and at comparatively low mass of the tangential impact device 11.
  • the first section 193 of the slotted guide 190 primarily supports the formation of a comparatively high triggering torque.
  • the second portion of the slotted guide 190 is primarily designed to build and transmit a comparatively high torque peak between the hammer 71 and the anvil 61.
  • the transition between the second section 194 is comparatively narrow.
  • an extension of the transitional area between the first pitch angle ⁇ and the second pitch angle ⁇ is held comparatively small against the extension of the sections 194, 193.
  • This turns out - from views (B) of Fig. 3A and Fig. 4 apparent - in an approximately kink-like transition between the first portion 193 and the second portion 194 of the control contour 91.1 and the second control contour 91.2.
  • At the transition of the hammer 71 is due to the shallower pitch of the control contour 91.1, 91.2 comparatively high speeds.

Landscapes

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

Claims (10)

  1. Machine-outil manuelle (100), en particulier sous la forme d'un marteau perforateur ou d'une visseuse à percussion, comportant :
    - un porte-outil (40) monté sur un arbre entraîné (30, 31) pour recevoir un outil,
    - dans laquelle un mouvement de rotation et de percussion partielle peut être appliqué à l'arbre entraîné (30, 31) au moyen d'un arbre moteur (50, 51) et d'un mécanisme de percussion tangentielle (10, 11), et
    - dans laquelle le mécanisme de percussion tangentielle (10, 11) comporte une enclume (60, 61) couplée à l'arbre entraîné (30, 31) et un marteau (70, 71) couplé à l'arbre moteur (50, 51), dans laquelle le marteau (70, 71) est axialement mobile sous l'application d'une force par un ressort (80, 81) et d'un guide à coulisse (90, 190) et peut percuter l'enclume (60, 61) par rotation du marteau (70, 71) autour de l'arbre moteur (50, 51),
    dans laquelle le guide à coulisse (90, 190) comporte un contour de commande analogue à filetage (91, 91.1, 91.2) qui a, dans une première partie proche de l'enclume (93, 193), une première inclinaison et, dans une seconde partie éloignée de l'enclume (94, 194), une seconde inclinaison, dans laquelle les première et seconde inclinaisons sont différentes, caractérisée en ce que la première inclinaison est supérieure à la seconde inclinaison.
  2. Machine-outil manuelle (100) selon la revendication 1, caractérisée en ce que le guide à coulisse (90, 190) comporte un premier contour de commande (91.1) sur l'arbre moteur (20, 21 ; 50, 51) et/ou un second contour de commande (91.2) sur un côté intérieur d'enveloppe du marteau (70, 71).
  3. Machine-outil manuelle (100) selon la revendication 2, caractérisée en ce que le premier contour de commande (91.1) et le second contour de commande (91.2) du guide à coulisse (90, 190) comportent respectivement une première partie (93, 193) ayant la première inclinaison et une seconde partie (94, 194) ayant la seconde inclinaison différente de la première.
  4. Machine-outil manuelle (100) selon l'une des revendications 1 à 3, caractérisée en ce qu'un premier angle d'inclinaison (α) de la première inclinaison, mesuré par rapport à un axe (2) d'un corps cylindrique pour le guide à coulisse (90, 190), est inférieur à un second angle d'inclinaison (β) de la seconde inclinaison, mesuré par rapport à l'axe (2).
  5. Machine-outil manuelle (100) selon l'une des revendications 1 à 4, caractérisée en ce qu'une coulisse fermée du guide à coulisse (90, 190) est formée sous la forme d'une rainure (96), dans laquelle un coulisseau (92) relié au marteau (70) à guidage forcé peut se déplacer dans la rainure (96) et/ou une coulisse ouverte du guide à coulisse (90, 190) est formée sous la forme d'une surface de glissement, dans laquelle un coulisseau (92) à guidage forcé relié au marteau (70) peut se déplacer sur la surface de glissement.
  6. Machine-outil manuelle (100) selon l'une des revendications 1 à 5, caractérisée en ce que les première et seconde inclinaisons sont des inclinaisons individuelles sensiblement différentes du contour de commande (91, 91.1, 91.2) et la première partie (93, 193) et la seconde partie (94, 194) sont directement adjacentes l'une à l'autre.
  7. Machine-outil manuelle (100) selon l'une des revendications 1 à 6, caractérisée en ce que dans la position d'engagement de l'enclume (60, 61) et du marteau (70, 71), un coulisseau (92, 192) à guidage forcé relié au marteau (70, 71) est agencé dans la première partie (93, 193) du contour de commande (91, 91.1, 91.2) pour effectuer une roto-percussion.
  8. Machine-outil manuelle (100) selon l'une des revendications 1 à 7, caractérisée en ce que dans une position de déclenchement de l'enclume (60, 61) et du marteau (70, 71), un coulisseau (92, 192) à guidage forcé relié au marteau (70, 71) est agencé dans la seconde partie (94, 194) du contour de commande (91, 91.1, 91.2) pour effectuer un désengagement.
  9. Machine-outil manuelle (100) selon l'une des revendications 1 à 8, caractérisée en ce que l'enclume (60, 61) et le marteau (70, 71) comportent chacun une zone d'engagement (95) mutuellement opposée avec des moyens d'impact pour effectuer une roto-percussion, et des moyens d'impact sous la forme d'au moins une, de préférence deux, cames (64, 74) sont formés sur une circonférence annulaire de l'enclume (60, 61) et/ou du marteau (70, 71), qui comporte une surface d'impact (62, 72) transversale à la direction circonférentielle.
  10. Machine-outil manuelle (100) selon l'une des revendications 1 à 9, caractérisée en ce que la première partie (93) comporte une extension axiale qui se situe dans un intervalle entre 0,1 fois et 1,0 fois, en particulier supérieur à 0,2 fois, l'extension axiale de la zone d'engagement (95).
EP12157411.5A 2011-04-28 2012-02-29 Outil à moteur Active EP2517835B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011017671A DE102011017671A1 (de) 2011-04-28 2011-04-28 Handwerkzeugmaschine

Publications (3)

Publication Number Publication Date
EP2517835A2 EP2517835A2 (fr) 2012-10-31
EP2517835A3 EP2517835A3 (fr) 2018-03-14
EP2517835B1 true EP2517835B1 (fr) 2019-07-31

Family

ID=45833140

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12157411.5A Active EP2517835B1 (fr) 2011-04-28 2012-02-29 Outil à moteur

Country Status (4)

Country Link
US (1) US9381626B2 (fr)
EP (1) EP2517835B1 (fr)
CN (1) CN102756352B (fr)
DE (1) DE102011017671A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2815850B1 (fr) * 2007-02-23 2016-02-03 Robert Bosch Gmbh Outil d'alimentation rotatif qui fonctionne en mode d'impact ou en mode de forage
US10427277B2 (en) 2011-04-05 2019-10-01 Ingersoll-Rand Company Impact wrench having dynamically tuned drive components and method thereof
US9566692B2 (en) * 2011-04-05 2017-02-14 Ingersoll-Rand Company Rotary impact device
DE102012209446A1 (de) * 2012-06-05 2013-12-05 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
US9701001B2 (en) * 2014-04-30 2017-07-11 Arrow Fastener Co., Llc Motor-driven fastening tool
EP3175954B1 (fr) * 2014-07-31 2020-12-02 Koki Holdings Co., Ltd. Outil à percussion
GB201421577D0 (en) * 2014-12-04 2015-01-21 Black & Decker Inc Drill
GB201421576D0 (en) 2014-12-04 2015-01-21 Black & Decker Inc Drill
CN105424283A (zh) * 2015-11-21 2016-03-23 重庆市山城燃气设备有限公司 一种气表密封性检测用双联快速夹紧装置
CN105258860A (zh) * 2015-11-21 2016-01-20 重庆市山城燃气设备有限公司 一种具有双联快速夹紧装置的气表密封性检测设备
US10471573B2 (en) * 2016-01-05 2019-11-12 Milwaukee Electric Tool Corporation Impact tool
CN107500113B (zh) * 2017-09-18 2019-04-12 胡予飞 一种旋转吊钩
EP3501750A1 (fr) * 2017-12-19 2019-06-26 Hilti Aktiengesellschaft Machine-outil portative à vibrations amorties
EP3789162A1 (fr) * 2019-09-04 2021-03-10 Hilti Aktiengesellschaft Entraînement rotatif pour une machine-outil mainuelle
CN211805940U (zh) 2019-09-20 2020-10-30 米沃奇电动工具公司 冲击工具和锤头
JP6718007B1 (ja) * 2019-10-23 2020-07-08 ▲浜▼元 陽一郎 回転アシスト具及びアシスト付き回転工具

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1505493A (en) * 1920-08-13 1924-08-19 C S Somervell Impact tool
GB693415A (en) * 1951-01-26 1953-07-01 Chicago Pneumatic Tool Co Impact wrench torque control
DE1087538B (de) * 1953-01-05 1960-08-18 Chicago Pneumatic Tool Co Drehschlagwerkzeug
US3709306A (en) * 1971-02-16 1973-01-09 Baker Oil Tools Inc Threaded connector for impact devices
US5667283A (en) * 1996-04-15 1997-09-16 General Motors Corporation Variable screw-driven system
US5836403A (en) * 1996-10-31 1998-11-17 Snap-On Technologies, Inc. Reversible high impact mechanism
ATE231663T1 (de) 1999-09-01 2003-02-15 Ramachandran Ramarathnam Elektrohandwerkzeug
US7743847B2 (en) * 2000-08-15 2010-06-29 Wave Craft Limited Cam operated devices
DE10137159A1 (de) 2001-07-30 2003-02-20 Hilti Ag Schlagendes Elektrohandwerkzeuggerät
JP3767475B2 (ja) * 2001-12-14 2006-04-19 日立工機株式会社 インパクト工具
US7136271B2 (en) * 2003-03-17 2006-11-14 Illinois Tool Works Inc Static charge neutralizing assembly for use on rollers and shafts
JP4405900B2 (ja) * 2004-03-10 2010-01-27 株式会社マキタ インパクトドライバ
GB2423048A (en) * 2005-02-10 2006-08-16 Black & Decker Inc Hammer with two reciprocating strikers
GB2423047A (en) * 2005-02-10 2006-08-16 Black & Decker Inc Hammer with rotating striker
GB2423046A (en) * 2005-02-10 2006-08-16 Black & Decker Inc Hammer with cam mechanism and barrel surrounded by sleeve
EP1690640B1 (fr) * 2005-02-10 2013-03-06 Black & Decker Inc. Machine portative à percussion
GB2423044A (en) * 2005-02-10 2006-08-16 Black & Decker Inc Hammer with cam-actuated driven member
JP4400519B2 (ja) 2005-06-30 2010-01-20 パナソニック電工株式会社 インパクト回転工具
JP2008173716A (ja) 2007-01-18 2008-07-31 Max Co Ltd ブラシレスモータを備えた電動工具
DE102008000677A1 (de) * 2008-03-14 2009-09-17 Robert Bosch Gmbh Handwerkzeugmaschine für schlagend angetriebene Einsatzwerkzeuge
EP2140976B1 (fr) * 2008-07-01 2011-11-16 Metabowerke GmbH Vis autotaraudeuse à frapper
DE102009002479B4 (de) * 2009-04-20 2015-02-19 Hilti Aktiengesellschaft Schlagschrauber und Steuerungsverfahren für einen Schlagschrauber
US8631880B2 (en) * 2009-04-30 2014-01-21 Black & Decker Inc. Power tool with impact mechanism
DE102009002982A1 (de) 2009-05-11 2010-11-18 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Elektrohandwerkzeugmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN102756352A (zh) 2012-10-31
CN102756352B (zh) 2015-09-09
EP2517835A2 (fr) 2012-10-31
US9381626B2 (en) 2016-07-05
EP2517835A3 (fr) 2018-03-14
DE102011017671A1 (de) 2012-10-31
US20130112448A1 (en) 2013-05-09

Similar Documents

Publication Publication Date Title
EP2517835B1 (fr) Outil à moteur
EP2140976B1 (fr) Vis autotaraudeuse à frapper
EP2457694B1 (fr) Outil électrique
EP0108411B1 (fr) Machine à percer
EP2140977B1 (fr) Vis autotaraudeuse à frapper
EP2265420B1 (fr) Machine-outil portative pour outils entraînés en frappe
DE102009054930B4 (de) Bohrmaschine
EP2803447B1 (fr) Dispositif d'outil manuel
EP1862265A2 (fr) Machine-outil manuelle dotée d'un dispositif d'accouplement à patinage
EP2140978B1 (fr) Vis autotaraudeuse à frapper
WO2012110453A1 (fr) Dispositif de transfert de couple sous forme de mandrin pour mèches
DE3235544A1 (de) Bohrhammer
WO2012049078A1 (fr) Dispositif de transmission de couple de rotation à utiliser avec une clé à chocs
EP2612731B1 (fr) Dispositif d'outil manuel
EP0663270B1 (fr) Marteau à percussion rotative et/ou rectiligne
EP2132005B1 (fr) Mécanisme rotopercutant
DE102013208890B4 (de) Handwerkzeugvorrichtung
EP2495078A1 (fr) Carré conducteur
WO2009092366A2 (fr) Mécanisme de percussion pour une machine-outil, notamment pour une machine-outil manuelle telle qu'un marteau perforateur électrique ou une visseuse à percussion
DE102004017940A1 (de) Schlagwerk für eine Handwerkzeugmaschine
EP3341158A1 (fr) Outil de pose
DE3402728C2 (de) Antrieb für das Schlagwerk eines Bohr- oder Schlaghammers
DE2526511B2 (de) Zwei-Kolben-Bohrhammer mit einer eine Drallnutenverbindung aufweisenden Vorrichtung zum Umsetzen eines Bohrers
WO2019042869A1 (fr) Dispositif de marteau, de préférence dispositif de marteau à guidage manuel
WO2012084346A1 (fr) Système de transmission pour un outil électrique et outil électrique

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

AK Designated contracting states

Kind code of ref document: A2

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

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

RIC1 Information provided on ipc code assigned before grant

Ipc: B25B 21/02 20060101AFI20180207BHEP

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20180914

RBV Designated contracting states (corrected)

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

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20190502

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1160416

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190815

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: 502012015078

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190731

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: 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: 20190731

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: 20191202

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: 20191031

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: 20190731

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: 20190731

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: 20191031

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: 20190731

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: 20190731

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

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: 20191130

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: 20190731

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: 20190731

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: 20190731

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: 20190731

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: 20191101

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: 20190731

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

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: 20190731

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: 20190731

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: 20190731

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: 20190731

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

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: 20190731

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: 20190731

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: 20200224

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: 20190731

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502012015078

Country of ref document: DE

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

PG2D Information on lapse in contracting state deleted

Ref country code: IS

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

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: 20191030

26N No opposition filed

Effective date: 20200603

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

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: 20190731

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20200229

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200229

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

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: 20190731

Ref country code: LU

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

Effective date: 20200229

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

Ref country code: LI

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

Effective date: 20200229

Ref country code: CH

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

Effective date: 20200229

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: 20200229

Ref country code: GB

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

Effective date: 20200229

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

Ref country code: BE

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

Effective date: 20200229

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1160416

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200229

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: 20200229

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: 20190731

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: 20190731

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

Ref country code: MK

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: 20190731

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

Ref country code: FR

Payment date: 20230221

Year of fee payment: 12

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

Ref country code: IT

Payment date: 20230223

Year of fee payment: 12

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

Ref country code: DE

Payment date: 20240219

Year of fee payment: 13