EP0663270B1 - Marteau à percussion rotative et/ou rectiligne - Google Patents

Marteau à percussion rotative et/ou rectiligne Download PDF

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Publication number
EP0663270B1
EP0663270B1 EP95100007A EP95100007A EP0663270B1 EP 0663270 B1 EP0663270 B1 EP 0663270B1 EP 95100007 A EP95100007 A EP 95100007A EP 95100007 A EP95100007 A EP 95100007A EP 0663270 B1 EP0663270 B1 EP 0663270B1
Authority
EP
European Patent Office
Prior art keywords
tool
catching
rotative
ring
impact hammer
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.)
Expired - Lifetime
Application number
EP95100007A
Other languages
German (de)
English (en)
Other versions
EP0663270A1 (fr
Inventor
Gerhard Schroth
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.)
Friedrich Duss Maschinenfabrik & Co GmbH
Original Assignee
Friedrich Duss Maschinenfabrik & Co GmbH
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 Friedrich Duss Maschinenfabrik & Co GmbH filed Critical Friedrich Duss Maschinenfabrik & Co GmbH
Publication of EP0663270A1 publication Critical patent/EP0663270A1/fr
Application granted granted Critical
Publication of EP0663270B1 publication Critical patent/EP0663270B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/226—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having elastic elements, e.g. springs, rubber pads

Definitions

  • the invention relates to an electropneumatic or electrical driven impact or rotary hammer according to the preamble of Claim 1.
  • Such devices are commonly used in the construction industry and Artisan area used as portable hammers.
  • the catching elements are two conical Sleeves, the outer of which is fixed to the housing, while the inner longitudinally slotted sleeve when hitting the percussion piston in is axially displaceable under radial deformation. Slowed down is not directly related to the tool here standing strikers, which therefore rebound when an empty stroke occurs can and brings the blows back into the blow position.
  • the inner displaceable ring becomes axial when empty blows occur driven into the other ring.
  • the multiple holding elements 5 includes.
  • the firing pin is also in the working position constantly in the holding element by springs acting radially inwards clamped so that friction forces occur even in the working position.
  • the striking element arrives by means of attached Projections in recesses of the holding elements and is fixed there.
  • the holding element is thus a large radial with each blank Interplay subject, which significantly reduces the lifespan.
  • the holding elements are only slightly axially displaceable, so that all the energy that occurs when emptying is destroyed is that there is a positive connection between the Projections of the firing pin and the recesses of the holding element is coming.
  • the firing pin cannot kick back be excluded.
  • the multi-part of the holding elements leads in addition to increased costs and assembly costs.
  • a pneumatic hammer drill is known from DE-A 33 35 553 which are provided as a rubber-elastic ring body, the one prepared accordingly when a blank stroke occurs Recesses are pressed.
  • the braking effect takes place in the essential about the deformation of these rubber-elastic elements. Residual energy can be destroyed via an O-ring that is loose in the Machine is inserted.
  • the O-ring relaxes again after the blank has occurred and can neither contribute to a soft braking of the striker, still pushing the percussion piston back into the working position influence.
  • CH-PS 590 716 proposes the percussion piston in the empty stroke position by a catch ring to shut down.
  • This longitudinally slotted catch ring is in one Area arranged in front of the percussion piston, which is usually in Working position is not reached. If there are empty blows, so the percussion piston reaches the area of the catch ring and spreads this catch ring radially outwards. Because of the axial direction The arrangement of the catch ring is only a short one Braking distance possible, so that it is due to the impact of the Percussion piston comes to rebound forces and the percussion piston again is thrown back so that several spaces are repeated, before the percussion piston stops.
  • a clamping device is provided as an interception device.
  • the Clamping device comprises an axially fixed inner clamping sleeve and a casing tube into which the shaft of the percussion piston is immersed. If there are blanks here, there is a limited one axial displacement of the casing tube with increasing distance from the working position due to inclined surfaces between the casing tube and clamping sleeve leads to jamming of the percussion piston. However, to To actually intercept the percussion piston, it must first get into a position that prevents the Percussion piston on the clamping sleeve. Because only at this time a full braking takes place, there are rebound effects and thus repeated blank blows.
  • the present invention is based on this prior art based on the task of a hammer or rotary hammer further developed in such a way that simple Way a lookup is reliably avoided.
  • the braking force can be changed by changing the excess of the catch element compared to its leadership and the size of the cross section of the Fangelements are influenced.
  • the braking force is preferably so set that it corresponds approximately to the machine weight, so that at Push the catch element back into the working position, no additional Force must be used. This is particularly true for larger ones Machines that are usually used vertically. There but at the same time acting on the tool or tool holder itself If the impact element itself is braked, a rebound is avoided.
  • the axial force is largely in a die Radial force increasing braking force converted. Should still be residual energy be present, this can be done by known elastic silencers be absorbed. If a cone angle of more than 5 ° is provided, a small contact pressure is enough to do that Bring the catch element back into the working position. A suffice for this only catch ring exposed to play no strong radial change is what increases its lifespan.
  • the striker can within the catch ring in the axial direction several millimeters free and move without braking so that no wear occurs on the catch ring and the impact performance is retained.
  • the catch ring is moved forward by the striker and the racket drawn. While now overcoming the by the Pre-deformation caused by friction forces, a braking effect occurs, If you run into the contact edges at the shortest possible distance, Deceleration. This short braking distance also contributes to a shorter one Overall length of the entire machine, which increases ease of use, there is only a short way between empty position and working position must be overcome.
  • the shift of the catch ring can also be against the force of a spring take place, which increases the braking effect and the resetting of Striking element supported in the working position.
  • the percussion or rotary hammer is a portable one Device that is commonly used in the construction and craft industries is used.
  • the percussion or rotary hammer 10 is driven electrically. in the a rear cylinder 24, a guide cylinder 14 is arranged. On Another housing part 22 encloses the so-called tool holder 21. A free-flying striking element is arranged in the guide cylinder, that rhythmically axially back and forth due to pressure fluctuations of an air cushion is moved here. The pressure fluctuations of the air cushion are in the Embodiment generated by a drive device 23, the an excitation piston 28 can swing back and forth in the guide cylinder.
  • the percussion piston vibrates on a striker 12, the in turn the tool 11 operated.
  • the percussion piston 13 ' has a shaft 13c' which extends up to Tool 11 is enough so that here the blows directly from the percussion piston 13 are transferred to the tool.
  • An interception device is provided in all exemplary embodiments, those of the striking element, regardless of whether percussion piston 13 itself or Crosspiece 12 is penetrated.
  • the interception device has a Catch element, the impact element when the tool is empty intercepts.
  • the catch element is a single one Catch ring 15, 15 ', however, the braking function in the guide area 14a also by several catch rings working together or one behind the other, Catch elements or catch ring parts can be achieved.
  • the catch element is in a guide area 14a clamped under elastic pre-deformation. It is only in the guide area 14a when the tool 11 strikes empty axially movable and produces a gradual braking effect while the Impact element otherwise free and unbraked, if necessary in the catch ring is mobile.
  • the guide area 14a can be part of the guide cylinder but can also be a separate part of the hammer.
  • the catch element is a catch ring provided with a longitudinal slot 15g 15.15 '.
  • the catch ring 15 has opposite its guide region 14a an excess. This has the consequence that the clamping ring during installation must be pre-deformed and in this respect due to its elastic Deformation in the guide area 14a coaxial to the tool axis a-a is clamped.
  • This clamping force results in an increased Frictional force between the guide area 14a and the catch ring 15, 15 ', which build up a braking force despite the axial displacement Increase of the contact pressure on the guide area when empty blows occur enables.
  • the possibility of axial displacement but also minimizes the radial load on the catch ring, since a Clamping is excluded and thus material fatigue.
  • a head 12a of the Döppers 12 movably mounted within the catch ring. In working position as long as there is no empty space, it is on one cylindrical portion 15b of the catch ring guided so that a free and unbraked movement is possible without wear of the catch ring 15.
  • the striker with a shaft 12d is on a guide 20 guided.
  • the head part 12a of the striker 12 has bevels 12b, 12c on that with appropriately shaped stops 15c and a cone 15a of the catch ring to limit the maximum path of the striker interact within the catch ring.
  • the tool stop is formed by the cone 15a.
  • This attack has in concrete embodiment an angle of 15 °. It can too any other angle can be selected.
  • the selection of the cone angle influences the conversion of the axial force into a reinforcing braking effect Radial force, i.e. a normal force on the guide area 14a.
  • Radial force i.e. a normal force on the guide area 14a.
  • the larger the angle the smaller the brake boost.
  • the smaller the angle the larger the Brake booster.
  • the catch ring On the tool side The cone 15a is provided at the end. On the opposite The end is the stop 15c. Between these two stops is the cylindrical section 15b.
  • the catch ring has on the outer surface 15 a finely machined sliding area 15d and a clearance 15e, on the one hand for mass reduction and on the other hand for contributes to easier manufacture. Beyond that there is another Bending 15f provided that in the working position a system on Stop 14b of the guide cylinder allowed.
  • the percussion piston 13 has a nose 13a, the length l of which is greater than the maximum possible path s of the striker within the catch ring. This will reliably avoided that the percussion piston 13 directly on the Catch ring can hit if the Döpper suddenly gives way to the front.
  • the striker 12 arrives in the Area of the cone 15a in contact with the catch ring and is through the Cone tension held at a distance from the percussion piston 13 so that it too no lookup comes. If the machine is started again, due to the movement of the tool, the strikers are also reset, the selected cone angle is easy to loosen from the Cone tension allows. When pushed back, the striker then comes in System against the stop 15c, so that the snap ring 15 also with the striker 12 is pushed back until the striker is in the area of the percussion piston.
  • the percussion piston acts directly onto the tool via a shaft 13c '. So far the percussion piston is not within the pre-deformed slotted catch ring are performed.
  • the catch ring 15 'therefore has a cone 15a 'with a bevel 13b' of the percussion piston cooperates.
  • the catch ring is now 15 'in a manner comparable to the first two Embodiments moved forward, but takes the Guide 26 of the shaft 13c 'of the percussion piston 13'. Both elements together form the interception device. The maximum way this The displacement unit is stopped by the stop 31a of the tool holder 31 limited.
  • the resetting is done in that bevels 11a of the Attack tool on bends 26a of the guide bush 26 and the Provision of both guide bush 26 and catch ring 15 ' accomplish.
  • the cone 15a ' is chosen such that there is a slight provision. It takes place in all exemplary embodiments a targeted reset of the interception device Contact of the striking element on the interception device.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (8)

  1. Marteau électropneumatique à percussion ou à rotopercussion (10) comportant un élément de frappe en porte-à-faux qui oscille dans un cylindre de guidage (14) sous l'influence des variations de pression d'un coussin d'air (27) et donne des coups rythmiques axiaux à un outil (11) ou à un porte-outil, et un dispositif d'arrêt qui présente un élément d'arrêt déformable élastiquement qui est serré avec prédéformation élastique dans le cylindre de guidage (14) et, lorsque l'outil frappe à vide, arrête l'élément de frappe en se déplaçant axialement dans la direction de l'axe (a-a) de l'outil, caractérisé par le fait que le dispositif d'arrêt est traversé par l'élément de frappe qui frappe l'outil (11) ou le porte-outil lui-même, et présente au moins un élément d'arrêt (bague d'arrêt 15, 15') qui, lorsque l'outil frappe à vide, freine l'élément de frappe sur une zone de guidage (14a) du marteau à percussion ou à rotopercussion ayant comme axe l'axe (a-a) de l'outil.
  2. Marteau à percussion ou à roto-percussion selon la revendication 1, caractérisé par le fait que comme élément unique d'arrêt, une bague d'arrêt fendue longitudinalement (15, 15'), pour augmenter la force de freinage à l'endroit où l'élément de frappe monte sur la bague d'arrêt lorsque l'outil frappe à vide, présente un cône (15a, 15a') qui a un angle de préférence supérieur à 5° et coopère avec des chanfreins (12b, 13b') de l'élément de frappe.
  3. Marteau à percussion ou à roto-percussion selon l'une des revendications 1 et 2, caractérisé par le fait que l'élément de frappe est une bouterolle (12) qui est frappée par un piston de frappe (13) et, en position de travail, est montée librement oscillante à l'intérieur d'une partie cylindrique (15b) de la bague d'arrêt (15), cette bouterolle (12) présentant sur sa partie de tête (12a) des chanfreins (12b, 12c) qui coopèrent avec des butées de forme correspondante (15c, cône 15a) de la bague d'arrêt pour limiter la course de la bouterolle (12) à l'intérieur de la bague d'arrêt (15).
  4. Marteau à percussion ou à roto-percussion selon l'une des revendications précédentes, caractérisé par le fait que la bague d'arrêt (15) s'appuie partiellement par une zone de glissement (15d) de sa surface latérale extérieure sur la zone de guidage (14a) du cylindre de guidage (14) et, dans la zone restante de sa surface latérale extérieure, présente du côté de l'outil une dépouille (15e).
  5. Marteau à percussion ou à roto-percussion selon l'une des revendications précédentes, caractérisé par le fait qu'un ressort (16) est monté du côté de l'outil devant la bague d'arrêt (15) pour supporter élastiquement celle-ci.
  6. Marteau à percussion ou à roto-percussion selon l'une des revendications 3 à 5, caractérisé par le fait que le piston de frappe (13) présente un nez (13a) dont la longueur (l) est supérieure à la course maximale possible (s) de la bouterolle (12) à l'intérieur de la bague d'arrêt (15).
  7. Marteau à percussion ou à roto-percussion selon l'une des revendications 1 et 2, caractérisé par le fait que le piston de frappe (13), constituant un élément de frappe, est guidé dans une douille de guidage (26) qui forme avec la bague d'arrêt (15') le dispositif d'arrêt et est également mobile axialement entre une butée (31a) du porte-outil (31) et la bague d'arrêt (15'), qui bute contre une butée (14b) du cylindre de guidage (14).
  8. Marteau à percussion ou à roto-percussion selon la revendication 7, caractérisé par le fait que la douille de guidage (26) a du côté de l'outil une butée (26a) qui coopère avec des chanfreins (11a) de l'outil (11) pour rappeler l'élément d'arrêt.
EP95100007A 1994-01-13 1995-01-02 Marteau à percussion rotative et/ou rectiligne Expired - Lifetime EP0663270B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4400779A DE4400779A1 (de) 1994-01-13 1994-01-13 Elektropneumatischer Schlag- oder Drehschlaghammer
DE4400779 1994-01-13

Publications (2)

Publication Number Publication Date
EP0663270A1 EP0663270A1 (fr) 1995-07-19
EP0663270B1 true EP0663270B1 (fr) 1999-05-12

Family

ID=6507827

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95100007A Expired - Lifetime EP0663270B1 (fr) 1994-01-13 1995-01-02 Marteau à percussion rotative et/ou rectiligne

Country Status (2)

Country Link
EP (1) EP0663270B1 (fr)
DE (2) DE4400779A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102039584A (zh) * 2009-10-14 2011-05-04 罗伯特.博世有限公司 工具装置

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29905322U1 (de) * 1999-03-23 1999-06-24 Heilmeier & Weinlein Hydraulisch entsperrbares Füllventil
ES2208623T3 (es) 2001-03-07 2004-06-16 Black & Decker Inc. Martillo.
DE10362025B4 (de) * 2003-05-20 2006-02-09 Robert Bosch Gmbh Bohr- oder Schlaghammer
DE102006000533A1 (de) 2006-12-18 2008-06-19 Hilti Ag Handwerkzeugmaschine mit pneumatischem Schlagwerk
DE102007000131A1 (de) 2007-03-07 2008-09-11 Hilti Ag Handwerkzeugmaschine mit pneumatischem Schlagwerk
DE102007000135A1 (de) * 2007-03-08 2008-09-11 Hilti Ag Handwerkzeugmaschine mit pneumatischem Schlagwerk
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
EP2842696B1 (fr) * 2013-08-30 2016-06-01 HILTI Aktiengesellschaft Outil électrique
US20240123589A1 (en) * 2019-11-12 2024-04-18 Hilti Aktiengesellschaft Impact mechanism arrangement
EP3822030A1 (fr) * 2019-11-15 2021-05-19 Hilti Aktiengesellschaft Marteau perforateur et/ou burin avec agencement de mécanisme de percussion

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2756993A1 (de) * 1977-12-21 1979-07-05 Duss Maschf Elektropneumatischer hammer mit fangring fuer den schlagkolben
DE3309187A1 (de) * 1983-03-15 1984-09-20 Robert Bosch Gmbh, 7000 Stuttgart Hammer, insbesondere bohrhammer
DE3335553C2 (de) * 1983-09-30 1994-02-24 Black & Decker Inc Bohrhammer mit Leerlauffangeinrichtung
DE3624153A1 (de) * 1986-07-17 1988-01-28 Bosch Gmbh Robert Motorbetriebener hammer

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102039584A (zh) * 2009-10-14 2011-05-04 罗伯特.博世有限公司 工具装置
CN102039584B (zh) * 2009-10-14 2015-07-01 罗伯特.博世有限公司 工具装置

Also Published As

Publication number Publication date
EP0663270A1 (fr) 1995-07-19
DE4400779A1 (de) 1995-07-20
DE59505872D1 (de) 1999-06-17

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