EP4058251A1 - Ensemble mécanisme à percussion - Google Patents

Ensemble mécanisme à percussion

Info

Publication number
EP4058251A1
EP4058251A1 EP20797491.6A EP20797491A EP4058251A1 EP 4058251 A1 EP4058251 A1 EP 4058251A1 EP 20797491 A EP20797491 A EP 20797491A EP 4058251 A1 EP4058251 A1 EP 4058251A1
Authority
EP
European Patent Office
Prior art keywords
hammer
combi
impact
meissei
steamer
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.)
Granted
Application number
EP20797491.6A
Other languages
German (de)
English (en)
Other versions
EP4058251B1 (fr
Inventor
Uto Plank
Ulrich Mandel
Josef Fünfer
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 EP4058251A1 publication Critical patent/EP4058251A1/fr
Application granted granted Critical
Publication of EP4058251B1 publication Critical patent/EP4058251B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/54—Plastics
    • B25D2222/57—Elastomers, e.g. rubber
    • 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
    • B25D2250/351—Use of pins

Definitions

  • the present invention relates to a drilling and / or cutting hammer with a drive motor, an impact mechanism and a tool holder for receiving a tool.
  • the striking mechanism has a striker that is axially displaceable in a striker guide and that acts on the tool.
  • the hammer mechanism is equipped with an idle shock absorber element and a rebound shock absorber element, which are designed in one piece with one another and form a combination damper element.
  • Rotary hammers of the type mentioned are basically known from the prior art and are described, for example, in EP 1 479 485 A1.
  • Idle shock absorber elements and rebound shock absorber elements which are preferably designed as elastomer damping elements, are used to keep force peaks on downstream components and vibrations as low as possible.
  • the striker hits a typically provided impact disc after each impact and is intercepted by the impact shock absorption element.
  • a blank impact damping element is typically used to protect the downstream components from a peak force of the blank impact.
  • a blank impact damping of the idle impact absorber element influences the return speed of the anvil after a blank impact and thus also the shutdown behavior of the hammer.
  • the object is achieved in that the striker guide is arranged outside, preferably exclusively outside of the combi-steamer element.
  • the invention includes the knowledge that a striker guide implemented within the combi-steamer element, in particular if the combi-steamer element itself forms part of this striker guide as in the known prior art, significantly reduces the service life of the Combi-steamer element and thus the entire striking mechanism favors. Because the striker guide is arranged according to the invention outside, preferably exclusively outside of the combi-steamer element, this disadvantage is avoided.
  • the anvil is cylindrical.
  • the otherwise preferably cylindrical striker can have a radial bead which is arranged to strike the idle impact damper element on the one hand and to strike the rebound shock absorber element on the other hand.
  • the combi-steamer element can have a central recess which extends over the entire length of the combi-steamer element.
  • the anvil is preferably received at least in sections within the central recess and / or passed through it.
  • the combi-steamer element has a cylindrical inner surface which extends in the axial direction between a blank impact stop surface and a rebound impact stop surface.
  • a radial distance is provided between the cylindrical inner surface and the bead, preferably along the entire inner surface. The radial distance between the cylindrical inner surface and a thickest point of the bead, based on the radial direction, is preferably provided.
  • the combi-steamer element has a planar end stop surface via which the combi-steamer element is supported on a shoulder of the tool holder.
  • the end stop surface is annular and / or the end stop surface runs perpendicular to the axial direction of the anvil.
  • the combi-steamer element has a longitudinal slot. It has been found to be advantageous if the longitudinal slot extends axially along the combi-steamer element on the tool holder side.
  • the longitudinal slot is preferably used for air exchange. In this way, vacuum suction of the striker at the blank impact stop surface or at the set-down point that has been abandoned on the blank impact stop surface can be avoided. It has been found to be advantageous if, when the empty shock absorber element is compressed, a residual opening remains from the longitudinal slot.
  • the combi-steamer element consists of or has an elastomer material. This has the advantage that the combi-steamer element can be slipped comparatively easily over the anvil during assembly of the striking mechanism.
  • the Idle shock absorber element has a higher stop rigidity than the rebound shock absorber element.
  • the combi-steamer element is formed by two half-shells.
  • a parting plane between the half-shells is preferably oriented parallel to the axial direction of the anvil.
  • the striker guide has at least one slide bearing and / or at least one roller bearing.
  • the striker is preferably guided or supported on both sides outside the combi-steamer element by a sliding bearing and / or at least one roller bearing.
  • FIG. 1 shows a first preferred embodiment of a drill and / or Meissei hammer
  • FIG. 2 shows a first preferred exemplary embodiment of a combi-steamer element
  • FIG. 3 shows a second preferred exemplary embodiment of a combi-steamer element.
  • FIG. 1 A preferred exemplary embodiment of a drilling and / or chiselling hammer 100 according to the invention is shown in FIG. 1.
  • the hammer drill and / or Meisseihammer 100 is equipped with an electric drive motor 70, an impact mechanism 10 and a tool holder 50 for receiving a tool 110.
  • the impact mechanism 10, which is arranged in a housing 90, has an axial direction in an anvil guide 20 AR displaceable and acting on the tool 110 anvil 30.
  • the hammer mechanism 10 has a no-load shock absorber element 11 and a rebound shock absorber element 13.
  • the empty shock absorber element 11 and the rebound shock absorber element 13 are designed in one piece with one another and thus form a combination damper element 15.
  • the combination damper element 15 has a central recess 40 which extends over the entire length L ( see. Fig. 2B) of the combi-steamer element 15 extends.
  • the anvil 30 is received at least in sections within the central recess 40 and passed through it.
  • the striker guide 20 has two roller bearings 21, 23 which are arranged completely outside of the combi-steamer element 15.
  • the striker 30 is therefore not supported within the combi-steamer element 15 or by the combi-steamer element 15 itself.
  • the anvil 30 is cylindrical and has a radial bead 31 approximately in the middle.
  • the radial bead 31 is arranged to strike against the idle impact damper element 11 on the one hand (left in FIG. 1) and to strike against the rebound shock absorber element 13 on the other hand (right in FIG. 1).
  • the combination damper element 15 has a cylindrical inner surface 16 which extends in the axial direction AR between a blank impact stop surface 12 of the idle impact damper element 11 and a rebound impact stop surface 14 of the rebound impact damper element 13.
  • the cylindrical inner surface 16 is limited on the one hand by the beginning empty impact stop surface 12 and on the other hand by the beginning of a rebound impact stop surface 14, each seen in the axial direction AR.
  • a radial spacing 19 is provided between the cylindrical inner surface 16 and the bead 31, more precisely between the cylindrical inner surface 16 and the thickest point 32 of the bead 31 in the radial direction RR (can also be seen particularly well in FIG. 2B).
  • the radial distance 19 extends along the entire inner surface 16, ie at no point between the blank impact stop surface 12 and the rebound impact stop surface 14 does the thickest point 32 of the bead 31 touch cylindrical inner surface 16 of the combi-steamer element 15. Therefore, undesired abrasion of the combi-steamer element 15 is effectively avoided.
  • FIG. 2 now shows a first preferred exemplary embodiment of a combi-steamer element 15, as can be used, for example, in the drilling and / or chiselling hammer 100 of FIG. 1.
  • 2A shows the combi-steamer element 15 from the perspective of the tool holder 50. It can be clearly seen that the combi-steamer element 15 has a planar end stop surface 51, via which the combi-steamer element 15 is supported on a shoulder 52 (cf. also FIG. 1) of the tool holder 50.
  • the combi-damper element 15 of FIG. 2 consists, for example, of an elastomer material and is formed by two half-shells 15 15, 15 ′′, which facilitate assembly.
  • a parting plane 18 between the half-shells 15 ‘, 15 ′′ runs parallel to the axial direction AR.
  • FIG. 2B shows a section through the combi-steamer element 15 along the parting plane 18.
  • the central recess 40 which is delimited by the annular, planar end stop surface 51, can be clearly seen in FIG. 2A.
  • the central recess 40 extends over the entire length L of the combi-steamer element 15.
  • the anvil 30 (indicated schematically here) is received at least in sections within the central recess 40.
  • the radial distance 19 already described is provided between the cylindrical inner surface 16 and the bead 31, more precisely between the cylindrical inner surface 16 and the thickest point 32 of the bead 31 in the radial direction RR.
  • the idle impact damper element 11 has a higher stop stiffness than the rebound shock absorber element 13. This is achieved through structural design alone in such a way that - in relation to the axial direction AR - "more" of elastomer material is used in the idle shock absorber element 11 than in the rebound shock absorber element 13. If the idle shock absorber element 11 has a rather cylindrical cross-section Q11, it widens Cross section Q12 of the impact shock absorber element 13 in the manner of a diffuser (to the right in FIG. 2B).
  • FIG. 3 A second preferred exemplary embodiment of a combi-steamer element 15 is shown in FIG. 3.
  • a longitudinal slot 17 is provided in the combi-steamer element 15 in FIG. 3, which slot extends axially along the combi-steamer element 15 on the tool-receiving side (from the left in FIG. 3).
  • An exchange of air is ensured by the longitudinal slot 17, so that a vacuum suction of the anvil (not shown here) on the blank impact stop surface 12 is avoided.
  • Fig. 3A shows the combi-steamer element 15 in the relaxed state, ie the As can be seen, for example, in FIG. 2B, the striker is in a central position.
  • the combination damper element 15, more precisely the idle impact damper element 11, is shown in the compressed state.
  • a residual opening 17 ′ remains from the longitudinal slot 17, via which an exchange of air is possible even when the empty shock absorber element 11 is compressed.
  • shoulder 70 drive motor 90 housing 100 drill and / or Meissei hammer 110 tool

Landscapes

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

Abstract

L'invention concerne un marteau perforateur et/ou burineur (100) comprenant un moteur d'entraînement (70), un mécanisme à percussion et un porte-outil (50) conçu pour recevoir un outil (110), le mécanisme à percussion comportant une bouterolle (30) déplaçable axialement dans un élément de guidage de bouterolle (20) et agissant sur l'outil (110), le mécanisme à percussion comprenant un élément d'amortissement de percussion à vide (11) et un élément d'amortissement de frappe à vide (13) conçus de manière monobloc et formant ainsi un élément d'amortissement combiné (15), l'élément de guidage de bouterolle (20) étant agencé en dehors, de préférence exclusivement en dehors de l'élément d'amortissement combiné (15).
EP20797491.6A 2019-11-12 2020-11-02 Agencement de mécanisme de frappe Active EP4058251B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP19208476.2A EP3822036A1 (fr) 2019-11-12 2019-11-12 Agencement de mécanisme de frappe
PCT/EP2020/080640 WO2021094117A1 (fr) 2019-11-12 2020-11-02 Ensemble mécanisme à percussion

Publications (2)

Publication Number Publication Date
EP4058251A1 true EP4058251A1 (fr) 2022-09-21
EP4058251B1 EP4058251B1 (fr) 2023-09-13

Family

ID=68581193

Family Applications (2)

Application Number Title Priority Date Filing Date
EP19208476.2A Withdrawn EP3822036A1 (fr) 2019-11-12 2019-11-12 Agencement de mécanisme de frappe
EP20797491.6A Active EP4058251B1 (fr) 2019-11-12 2020-11-02 Agencement de mécanisme de frappe

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP19208476.2A Withdrawn EP3822036A1 (fr) 2019-11-12 2019-11-12 Agencement de mécanisme de frappe

Country Status (4)

Country Link
US (1) US20240123589A1 (fr)
EP (2) EP3822036A1 (fr)
CN (1) CN114555298A (fr)
WO (1) WO2021094117A1 (fr)

Family Cites Families (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2655899A1 (de) * 1976-12-09 1978-06-22 Bosch Gmbh Robert Handwerkzeugmaschine
DE3224176C2 (de) * 1982-06-29 1995-02-02 Bosch Gmbh Robert Motorisch angetriebene schlagende Handwerkzeugmaschine
DE4400779A1 (de) * 1994-01-13 1995-07-20 Duss Maschf Elektropneumatischer Schlag- oder Drehschlaghammer
EP1238759B1 (fr) * 2001-03-07 2003-12-17 Black & Decker Inc. Marteau
DE10157831B4 (de) * 2001-11-24 2004-06-24 Robert Bosch Gmbh Handwerkzeugmaschine mit einem ein Werkzeug aufnehmenden Döpper
DE10323606B4 (de) * 2003-05-20 2005-04-14 Robert Bosch Gmbh Elastische Döpperführung
DE10362025B4 (de) 2003-05-20 2006-02-09 Robert Bosch Gmbh Bohr- oder Schlaghammer
JP4525904B2 (ja) * 2004-06-08 2010-08-18 日立工機株式会社 打撃工具
DE102004044499B4 (de) * 2004-09-15 2021-02-18 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Bohr- und/oder Schlaghammer
DE102006000395A1 (de) * 2006-08-07 2008-02-14 Hilti Ag Handwerkzeugmaschine mit pneumatischem Schlagwerk
DE102007000131A1 (de) * 2007-03-07 2008-09-11 Hilti Ag Handwerkzeugmaschine mit pneumatischem Schlagwerk
DE102007048262A1 (de) * 2007-10-08 2009-04-09 Robert Bosch Gmbh Handwerkzeugmaschine
DE102008001957A1 (de) * 2008-05-26 2009-12-03 Robert Bosch Gmbh Bohr- und/oder Meißelhammer
DE102008040118A1 (de) * 2008-07-03 2010-01-07 Robert Bosch Gmbh Bohr- und/oder Meißelhammer
DE102010029917A1 (de) * 2010-06-10 2011-12-15 Hilti Aktiengesellschaft Werkzeugmaschine
DE102010044011A1 (de) * 2010-11-16 2012-05-16 Hilti Aktiengesellschaft Handwerkzeugmaschine
DE102011007660A1 (de) * 2011-04-19 2012-10-25 Hilti Aktiengesellschaft Handwerkzeugmaschine und Herstellungsverfahren
DE102011075765A1 (de) * 2011-05-12 2012-11-15 Hilti Aktiengesellschaft Handwerkzeugmaschine
DE102011079367A1 (de) * 2011-07-05 2013-01-10 Robert Bosch Gmbh Schlagwerkvorrichtung
US9079286B1 (en) * 2011-12-15 2015-07-14 Christian DeCamillis Pneumatic actuator for impact engraving tool
EP2848370A1 (fr) * 2013-09-12 2015-03-18 HILTI Aktiengesellschaft Machine-outil manuelle
EP2871030A1 (fr) * 2013-11-06 2015-05-13 HILTI Aktiengesellschaft Machine-outil manuelle
EP2918376A1 (fr) * 2014-03-12 2015-09-16 HILTI Aktiengesellschaft Machine-outil portative de burinage
CN104101422B (zh) * 2014-07-31 2016-08-24 苏州科技学院 超声振动刀具刃口振幅测量装置
EP3231560A1 (fr) * 2016-04-13 2017-10-18 HILTI Aktiengesellschaft Machine-outil portative
FR3058664B1 (fr) * 2016-11-17 2019-07-05 Montabert Appareil a percussions
EP3822037A1 (fr) * 2019-11-15 2021-05-19 Hilti Aktiengesellschaft Agencement de mécanisme de percussion
EP3822030A1 (fr) * 2019-11-15 2021-05-19 Hilti Aktiengesellschaft Marteau perforateur et/ou burin avec agencement de mécanisme de percussion

Also Published As

Publication number Publication date
WO2021094117A1 (fr) 2021-05-20
EP4058251B1 (fr) 2023-09-13
CN114555298A (zh) 2022-05-27
EP3822036A1 (fr) 2021-05-19
US20240123589A1 (en) 2024-04-18

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