EP1677950B1 - Outil de percussion pour une machine-outil a main - Google Patents

Outil de percussion pour une machine-outil a main Download PDF

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Publication number
EP1677950B1
EP1677950B1 EP04762744A EP04762744A EP1677950B1 EP 1677950 B1 EP1677950 B1 EP 1677950B1 EP 04762744 A EP04762744 A EP 04762744A EP 04762744 A EP04762744 A EP 04762744A EP 1677950 B1 EP1677950 B1 EP 1677950B1
Authority
EP
European Patent Office
Prior art keywords
drive piston
round
percussion
gearwheel
percussion mechanism
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 - Fee Related
Application number
EP04762744A
Other languages
German (de)
English (en)
Other versions
EP1677950A1 (fr
Inventor
Friedmar Dresig
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1677950A1 publication Critical patent/EP1677950A1/fr
Application granted granted Critical
Publication of EP1677950B1 publication Critical patent/EP1677950B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B25D11/06—Means for driving the impulse member
    • B25D11/10—Means for driving the impulse member comprising a cam mechanism
    • 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
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body

Definitions

  • the invention relates to a striking mechanism for a hand tool, in particular for a hammer drill, percussion hammer or a percussion drill, according to the preamble of claim 1.
  • axially displaceable drive piston is connected by a connecting rod with a crank pin of a crankshaft, which is driven by a pinion gear from the drive shaft of an electric motor.
  • the crank drive puts the drive piston in a reciprocating motion.
  • the stroke of the drive piston over time shows a nearly sinusoidal course.
  • the stroke movement of the drive piston arises in the compression space between the drive piston and racket alternately an over- and under-pressure, whereby the racket is accelerated in the direction of the tool.
  • the time course of the pressure in the compression chamber results from the relative displacement between the drive piston and racket and is determined by the sinusoidal profile of the stroke of the drive piston.
  • the pressure curve is characterized by a short high peak value and a relatively long period of time at low pressure.
  • the principal pressure curve is shown in Fig. 3 curve a.
  • the high peak pressure in the compression chamber leads to a high load on the compression space and to a relatively high cost for the sealing of the compression space in the guide tube, which increases disproportionately with increasing pressure.
  • the conditional by the sinusoidal stroke of the drive piston pressure curve in the compression chamber also leads to the fact that provided by the drive piston drive energy is not effectively used to uniform pressurization of the racket and thus the optimal club speed is not achieved for a rapid Bohrfort Kunststoff.
  • the hammer mechanism according to the invention for a hand tool with the features of claim 1 has the advantage that by means of the non-circular gear pair a virtually arbitrary course of the stroke of the drive piston can be adjusted, depending on how the rolling curves of the two gears are designed.
  • the design of the rolling curves depends exclusively on the optimization goal.
  • the Wälzkurven can z. B. calculated so that the racket receives a maximum speed at a minimum pressure load of the compression space. They can also be calculated so that at a minimum pressure load in the compression chamber at the same time high speed of the racket only a minimum drive torque for the drive piston is required.
  • further optimization goals are possible through the rolling curve design.
  • the principal aim of the design of the rolling curves is the delivery of high energy to the tool at a low power consumption, so a significant increase in efficiency.
  • the percussion shown in Fig. 1 as a schematic sketch partially cut for a hand tool for example for a hammer drill, a percussion hammer or a percussion drill, has a drive piston 11 and a racket 12, which are axially successively received in a guide tube 13 and guided axially displaceable therein ,
  • the mutually facing end faces of drive piston 11 and racket 12 define a compression space 14 in the guide tube 13, in which an air cushion is enclosed.
  • the guide tube 13 is arranged in a housing, not shown here, of the power tool.
  • the axis of the guide tube 13 is aligned with the axis of a Tool holder in which a tool, such as a percussion drill, is partially held.
  • the tool either projects into the guide tube 13 with its tool shank or, as in this case, is aligned axially in alignment with a firing pin 15, which is guided axially displaceably in the guide tube 13.
  • an electric motor 16 is arranged, which puts the drive piston 11 in a reciprocating, axial stroke movement in the guide tube 13 via a gear 17.
  • the gear 17 has two intermeshing non-circular gears 18, 19, of which one non-circular gear 18 is a driving and the other non-circular gear 19 is a driven non-circular gear.
  • Each non-circular gear 18, 19 has a rotation axis 20 and 21.
  • the two axes of rotation 20, 21 are arranged at a fixed distance a from each other.
  • the driving non-circular gear 18 is non-rotatably mounted on a countershaft 25 mounted in the housing and between the output shaft 22 of the electric motor 16 and the countershaft 25, an intermediate gear 26 is arranged.
  • the driven non-circular gear 19 is rotatably mounted in the housing about its axis of rotation 21.
  • On the driven non-circular gear 19 eccentrically to the rotation axis 21 acting as a crank or connecting rod piston rod 23 is articulated, which is pivotally connected to the drive piston 11.
  • the piston-side end of the piston rod 23 acts on a pivot pin 24, which is received transversely to the axis of the guide tube 13 in the drive piston 11 at its end facing away from the compression space 14 end.
  • the drive piston 11 is shown in its one stroke end position, in Fig. 2 in its other stroke end position.
  • the drive piston 11 When the electric motor 16 is switched on, the drive piston 11 is set in a reciprocating, axial stroke movement via the gear 17, wherein the air cushion in the compression space 14 is alternately compressed and relaxed.
  • the temporal Course of the pressure in the compression chamber 14 depends on the relative distance between the drive piston 11 and racket 12 and is determined essentially by the time course of the stroke of the drive piston 11.
  • novel gear can be achieved by appropriate design of the Wälzkurven 181, 191 of the non-circular gears 18, 19 depending on the optimization goal a good Bohr progress or chisel removal, lower power consumption and a more uniform power consumption.
  • the hand tool machine shows a lower vibration overall.

Landscapes

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

Claims (5)

  1. Mécanisme de percussion pour machine-outil à main, notamment pour un marteau de démolition ou une perceuse à percussion, comportant un piston d'entraînement (11) coulissant axialement dans un tube de guidage (13), en étant entraîné en va-et-vient par un moteur par l'intermédiaire d'un engrenage (17), un percuteur (12) coulissant axialement dans le tube de guidage (13), une chambre de compression (14) délimitée par le piston d'entraînement (11) et par le percuteur (12) et enfermant un coussin pneumatique,
    caractérisé en ce que
    l'engrenage (17) présente deux pignons non circulaires (18, 19) engrenant entre eux avec leurs axes de rotation (20, 21) présentant entre eux un espace fixe (a), le pignon (18) pouvant être entraîné par un moteur, tandis que sur l'autre pignon (19) entraîné par le pignon moteur (18), est articulée excentriquement par rapport à l'axe de rotation (21) de celui-ci une tige de piston (22) reliée au piston d'entraînement (11).
  2. Mécanisme de percussion selon la revendication 1,
    caractérisé en ce que
    les profils de roulement (181, 191) des deux pignons non circulaires (18, 19) sont configurés de manière que la course du piston d'entraînement (11) présente une variation souhaitée dans le temps.
  3. Mécanisme selon la revendication 2,
    caractérisé en ce que
    la variation dans le temps de la course du piston d'entraînement (11) est déterminée pour obtenir une vitesse de percussion élevée quand la pression est minimale dans la chambre de compression (14).
  4. Mécanisme de percussion selon la revendication 2,
    caractérisé en ce que
    la variation dans le temps de la course du piston d'entraînement (11) est déterminée pour obtenir une vitesse élevée du percuteur avec une énergie électrique consommée minimale.
  5. Mécanisme de percussion selon une des revendications 1 à 4,
    caractérisé en ce que
    les deux pignons non circulaires (18, 19) ont le même nombre de dents.
EP04762744A 2003-10-17 2004-09-03 Outil de percussion pour une machine-outil a main Expired - Fee Related EP1677950B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10348397A DE10348397A1 (de) 2003-10-17 2003-10-17 Schlagwerk für eine Handwerkzeugmaschine
PCT/DE2004/001957 WO2005044521A1 (fr) 2003-10-17 2004-09-03 Outil de percussion pour une machine-outil a main

Publications (2)

Publication Number Publication Date
EP1677950A1 EP1677950A1 (fr) 2006-07-12
EP1677950B1 true EP1677950B1 (fr) 2007-03-07

Family

ID=34442058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04762744A Expired - Fee Related EP1677950B1 (fr) 2003-10-17 2004-09-03 Outil de percussion pour une machine-outil a main

Country Status (6)

Country Link
US (1) US20060260830A1 (fr)
EP (1) EP1677950B1 (fr)
CN (1) CN1867429A (fr)
DE (2) DE10348397A1 (fr)
ES (1) ES2281819T3 (fr)
WO (1) WO2005044521A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005021734A1 (de) * 2005-05-11 2006-11-16 Robert Bosch Gmbh Elektrowerkzeugmaschine
DE102006059076A1 (de) * 2006-12-14 2008-06-19 Robert Bosch Gmbh Schlagwerk einer Elektrohandwerkzeugmaschine
DE102008044219A1 (de) * 2008-12-01 2010-06-02 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
CN107397233A (zh) * 2017-08-07 2017-11-28 宁德职业技术学院 一种鲜魔芋打浆成泥机
EP3697574A1 (fr) 2017-10-20 2020-08-26 Milwaukee Electric Tool Corporation Outil à percussion
EP3743245B1 (fr) 2018-01-26 2024-04-10 Milwaukee Electric Tool Corporation Outil à percussion
CN108677629B (zh) * 2018-07-14 2023-11-03 徐瀛 一种电动捣固机
CN113482529A (zh) * 2021-08-20 2021-10-08 湖北万众通达机械设备有限公司 一种煤矿高效节能乳化液钻机

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AUPO519497A0 (en) * 1997-02-20 1997-04-11 Stokes, Nigel Cameron Multiple shaft engine
US3301244A (en) * 1964-11-09 1967-01-31 John P Renshaw Piston stroke control mechanism
US3382767A (en) * 1966-04-19 1968-05-14 Fellows Gear Shaper Co Gear shaper driving means
DE3511437A1 (de) * 1985-03-29 1986-10-02 Hilti Ag, Schaan Motorisch betriebenes handwerkzeug
US4793171A (en) * 1985-07-31 1988-12-27 Sleeper & Hartley Corp. Multi-slide wire and strip forming machine
DE19601300C2 (de) * 1996-01-16 2003-04-17 Ver Deutscher Werkzeugmaschine Antriebseinrichtung für eine Umformmaschine
DE10034359A1 (de) * 2000-07-14 2002-01-24 Hilti Ag Schlagendes Elektrohandwerkzeuggerät
DE10142569A1 (de) * 2001-08-30 2003-03-27 Bosch Gmbh Robert Handwerkzeugmaschine
US6644947B2 (en) * 2002-03-14 2003-11-11 Tuthill Corporation Wave tooth gears using identical non-circular conjugating pitch curves

Also Published As

Publication number Publication date
WO2005044521A1 (fr) 2005-05-19
EP1677950A1 (fr) 2006-07-12
CN1867429A (zh) 2006-11-22
DE10348397A1 (de) 2005-05-19
ES2281819T3 (es) 2007-10-01
US20060260830A1 (en) 2006-11-23
DE502004003181D1 (de) 2007-04-19

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