EP2241409B1 - Handwerkzeugmaschine mit Schwingungsdämpfer - Google Patents

Handwerkzeugmaschine mit Schwingungsdämpfer Download PDF

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Publication number
EP2241409B1
EP2241409B1 EP09158130A EP09158130A EP2241409B1 EP 2241409 B1 EP2241409 B1 EP 2241409B1 EP 09158130 A EP09158130 A EP 09158130A EP 09158130 A EP09158130 A EP 09158130A EP 2241409 B1 EP2241409 B1 EP 2241409B1
Authority
EP
European Patent Office
Prior art keywords
centre
hand
power tool
held power
gravity
Prior art date
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Active
Application number
EP09158130A
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English (en)
French (fr)
Other versions
EP2241409A1 (de
Inventor
Axel Fischer
Michael Weber
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
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Publication date
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Priority to EP09158130A priority Critical patent/EP2241409B1/de
Publication of EP2241409A1 publication Critical patent/EP2241409A1/de
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Publication of EP2241409B1 publication Critical patent/EP2241409B1/de
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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
    • B25D17/24—Damping the reaction force
    • 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
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted
    • 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
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the present invention relates to a hand-held power tool with a vibration-compensating mass as known of EP 1 767 315 and the features in the preamble of claim 1
  • European Publication EP 1 736 283 discloses a hand-held hammer drill.
  • a hammer mechanism repetitively strikes on a tool bit end in a tool bit holder. Vibrations of the hammer mechanism are damped by a tuned mass damper which is placed adjacent and above the hammer mechanism.
  • the tuned mass damper comprises a counter mass slideably supported on rods above the hammer mechanism. Springs are biasing the counter mass to a position of rest. The counter mass moves in forward and rearward direction, parallel to the striking movement of the hammer mechanism against the springs such to counteract vibrations generated by the operation of the hammer mechanism.
  • An object of the present invention is to realize improved ergonomic hand-held power tools.
  • the main handle is usually arranged opposite to a tool chuck.
  • the main handle may have a grip bar for one or two hands.
  • the percussion mechanism may be at least one of a pneumatic percussion mechanism, a motor-driven pneumatic percussion mechanism and a clutch mechanism.
  • a first distance from the handle to the position of rest of counter mass may be at the most 75 percent of a second distance from a handle of the hand-held power tool to the centre of gravity.
  • the distance may be measured projected on the percussion axis.
  • a reference point on the handle may be chosen by the grip surface which shows in forward direction, i.e. in direction of the centre of gravity.
  • the first distance is at the most 50 percent of the second distance.
  • a first imaginary lever and a second imaginary lever may define an angle of at least 10 degrees and at the most 80 degrees, the first imaginary lever connecting the centre of gravity with the position of rest and the second imaginary lever connecting the centre of gravity with a centre of the percussion mechanism.
  • a first imaginary lever and a second imaginary lever may define defining a first angle, the first imaginary lever connecting the centre of gravity with the position of rest and the second imaginary lever connecting the centre of gravity with a centre of the percussion mechanism, and the oscillation axis and the percussion axis may define a second angle, wherein the second angle is in a range of 20 percent to 90 percent of the first angle.
  • the relation of the first and second angle showed best overall damping results for both longitudinal and rotational vibration motions. In particular, values of at least 40 percent and at the most of 75 percent gave best results.
  • the first angle may be at least five degrees.
  • the centre of the motor-driven pneumatic percussion mechanism can be identified to be a centre position of an excitation piston or cylinder.
  • the centre of a clutch mechanism can be the identified to be the contact surface of the axially stationary part.
  • An imaginary lever and the oscillation axis may define an angle of at least 30 degrees and at the most 80 degrees, the imaginary lever connecting the centre of gravity with the position of rest.
  • the oscillation axis and the percussion axis may define an angle which is in a range of at least 5 degrees and at the most of 60 degrees.
  • the position of rest and the centre of gravity may be on opposite sides of the percussion axis.
  • a handling of the hand-held power tool is assumed to be better when the centre of gravity is close to the percussion axis.
  • the weighty tuned mass damper balances the heavy driving mechanism, e.g. an electric motor, so improved handling is obtained.
  • a long imaginary first lever ensures a high torsional momentum of the counter mass acting around the centre of gravity.
  • the hand-held power tool may be a hand-held power drill.
  • Fig. 1 illustrates an embodiment of a hand-held power tool 10.
  • the power tool 10 may be a rotary impact drill or a chipping hammer, for instance.
  • the power tool 10 has a machine housing 11 and a handle 12 attached to a rear side 13 of the machine housing 11.
  • the handle 12 has a grip surface 71 for the fingers.
  • the handle 12 may be decoupled from the machine housing 11 by damping, elastic elements 14.
  • the damping elements 14 are designed to have a low-pass characteristic.
  • a tool chuck 15 may be part of the machine housing 11 or detachably fixed to a front side 16 of the machine housing 11.
  • a percussion mechanism 17 is arranged inside the machine housing 11.
  • An exemplary percussion mechanism 17 may be a motor-driven pneumatic percussion mechanism.
  • a pneumatic chamber 18 is enclosed along a percussion axis 19 on one side by a flying piston 20 and on an opposite side by an excitation piston 21.
  • Other walls of the pneumatic chamber 18 which are parallel to the percussion axis 19 may be formed by at least one of a guiding cylinder 22, the flying piston 20 and the excitation piston 21.
  • the pneumatic chamber 18 is sealed such that a pressure inside the pneumatic chamber 18 depends on the relative position of the flying piston 20 and the excitation piston 21.
  • the excitation piston 21 is driven along the percussion axis 19 by a drive mechanism 23.
  • the drive mechanism 23 may comprise an electric motor 24.
  • the electric motor 24 may be powered by a rechargeable battery pack 25 or by a power grid.
  • An eccentric tappet 26 translates the rotational motion of the electric motor 24 to an axial motion along the percussion axis 19.
  • the excitation piston 21 is coupled to the drive mechanism 23 and, thus, moves periodically forward and backward along the percussion axis 19.
  • the pneumatic chamber 18 periodically increases and decreases its volume.
  • a centre 27 of the pneumatic chamber 18 may be defined to be on half the way between turning points of an inner side of the excitation piston 21.
  • the periodic movement of the excitation piston 21 excites a periodic movement the flying piston 20 via the pneumatic chamber 18.
  • the flying piston 20 transfers its impulse to a tool bit 28 when the flying piston 20 hits directly on the tool bit 28 or by means of an intermediate striker.
  • a striking frequency corresponds to the periodicity of the movement of the flying piston 20 and, hence, to the speed of the motor 24.
  • the location of the centre of gravity 34 may be dominated by heavy parts which are the percussion mechanism 17, the drive mechanism 23, the rechargeable battery pack 25 and a tool engaged to the tool chuck 15.
  • An ergonomic design of the hand-held power tool 10 may request for an arrangement of the drive mechanism 23 and the rechargeable battery pack 25 displaced from the percussion axis 19. Therefore, the centre of gravity 34 does not lye on the percussion axis 19, but may be in an area below the percussion axis 19, in particular below the pneumatic chamber 18.
  • a tuned mass damper 35 is arranged within the machine housing 11.
  • the tuned mass damper 35 is a near-resonant damping mechanism.
  • the tuned mass damper 35 comprises a counter mass 36 which may oscillate along an oscillation axis 37.
  • a restoring element 38 forces the counter mass 36 back to a position of rest 39 on the oscillation axis 37.
  • the tuned mass damper 35 is preferably a linear tuned mass damper 35 whom counter mass 36 moves along a straight line, i.e. the tuned mass damper 35 has predominantly a linear motion.
  • the linear tuned mass damper 35 can be constructed by simple elements.
  • Rods 40 may be guiding the counter mass 36 and spiral springs 41 are acting as restoring elements 38 which are seated on the rods 40 on both sides of the counter mass 36.
  • the tuned mass damper 35 may be housed by an encapsulating housing. The housing may guide the counter mass 36 instead of guiding rods 40.
  • the mass of the counter mass 36 and the restoring forces of the restoring element 38 define a resonance frequency of the tuned mass damper 35.
  • the resonance frequency is chosen to be equal to the striking frequency such that the tuned mass damper 35 becomes resonantly excited by the periodic counterforces 31.
  • An efficient energy transfer from the vibration to the tuned mass damper 35 is enabled because of the resonant excitation.
  • the tuned mass damper 35 swings with the striking frequency but by approximately 90 degrees out of phase with respect to the percussion mechanism 17.
  • the coupled system of tuned mass damper 35 and percussion mechanism 17 transfers energy of vibrations at the striking frequency to higher harmonics of the striking frequency. The amplitude of the vibrational motion is thus lowered compared to a percussion mechanism 17 without a tuned mass damper 35.
  • a location of the weighty tuned mass damper 35 close to the handle 12 is to be preferred.
  • a static torque a user has to maintain at the handle 12 for holding the power tool 10 is lowered.
  • the tuned mass damper 35 is arranged closer, in direction of the percussion axis 19, to the handle 12 than the percussion mechanism 17 or the pneumatic chamber 18.
  • Satisfactory ergonomic results have been obtained for tuned mass dampers 35 whom position of rest 39 is arranged in a distance 60 to the handle 12 being shorter than 75 percent, preferably less 50 percent, the distance 61 of the handle 12 to the centre of gravity 34.
  • the distances 60, 61 are to be measured in projection on the axis of percussion 19.
  • the reference on the handle 12 may be grip surface 71 which shows in direction to the tool chuck 15.
  • a first imaginary lever 42 connects the position of rest 39 with the centre of gravity 34 and a second imaginary lever 43 connects the centre 27 of the pneumatic chamber 18 and the centre of gravity 34.
  • the first imaginary lever 42 and the second imaginary lever 43 are inclined by a first angle 44.
  • the first angle 44 may be larger than 5 degrees and/or less than 80 degrees.
  • the oscillation axis 37 of the tuned mass damper 35 is inclined with respect to the percussion axis 19 by a second angle 45.
  • the second angle 45 may be chosen depending on the first angle 44.
  • the second angle 45 may be at least 20 percent and at the most 90 percent of the first angle 44, e.g. at least 30 percent, at least 50 percent, at the most 75 percent.
  • the damping of the linear vibrational motion and the rotational vibrational motion by the tuned mass damper 35 are partially decoupled.
  • a collinear arrangement i.e. a second angle 45 of zero degrees, reduces best the linear vibrational motion, however, gives poor results for the rotational vibrational motion.
  • An optimal damping of the rotational vibrational motion leads to an insufficient damping of the linear vibrational motion.
  • Ergonomic studies revealed a good overall performance of the tuned mass damper 35 for damping all vibrational motion can be achieved for the range of the second angle 45 mentioned above.
  • the second angle 45 may be chosen to provide a higher damping of the linear vibrational motion along the percussion axis 19 compared to the rotational vibrational motion.
  • a ratio of the damping quality may be specified by accelerations along the percussion axis 19 and a vertical direction 46 perpendicular to the percussion axis 19.
  • a ratio of the acceleration along the percussion axis 19 to the vertical acceleration is in a range of 25 percent to 80 percent with the installed tuned mass damper 35 at the second angle 45 chosen.
  • the first imaginary lever 42 and the oscillation axis 37 may, therefore, define an angle 70 in the range of at least 30 degrees and at the most of 80 degrees, for instance.
  • the tuned mass damper 35 may be arranged such that its position of rest 39 is above the percussion axis 19.
  • the long first imaginary lever 42 ensures a high torque of the tuned mass damper 35 with respect to the centre of gravity 34.
  • an efficient damping of the rotational vibration motion can be achieved even with a low mass of the counter mass 36.

Landscapes

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

Claims (11)

  1. Handwerkzeugmaschine (10) mit
    einem Hauptgriff (12),
    einem Schlagwerk (17), das entlang einer Schlagachse (19) schlägt,
    einem Schwerpunkt (34) der Handwerkzeugmaschine (10),
    einer Tilgermasse (36), die entlang einer Oszillationsachse (37) auslenkbar ist,
    einer Vorspanneinrichtung, die die Tilgermasse (36) in eine Ruhelage (39) auf der Oszillationsachse (37) vorspannt,
    wobei die Ruhelage (39) näher an dem Hauptgriff (12) als der Schwerpunkt (34) an dem Hauptgriff (12) ist, dadurch gekennzeichnet, dass
    die Oszillationsachse (37) gegenüber der Schlagachse (19) geneigt ist.
  2. Handwerkzeugmaschine (10) nach Anspruch 1, wobei ein erster Abstand (60) von dem Hauptgriff (12) zu der Ruhelage (39) der Tilgermasse (36) höchstens 75 Prozent der zweiten Distanz (61) von dem Hauptgriff (12) der Handwerkzeugmaschine (10) zu dem Schwerpunkt (34) ist.
  3. Handwerkzeugmaschine (10) nach Anspruch 2, wobei der erste Abstand (60) und der zweite Abstand (61) in einer Projektion auf die Schlagachse (19) gemessen sind.
  4. Handwerkzeugmaschine (10) nach Anspruch 2 oder 3, wobei der erste und zweite Abstand (60, 61) zu einer des Hauptgriffs (12) Grifffläche (71), welche zu dem Schwerpunkt (34) zeigt, gemessen ist.
  5. Handwerkzeugmaschine (10) nach einem der vorhergehenden Ansprüche, wobei ein erster virtueller Schenkel (42) und ein zweiter virtueller Schenkel (43) einen Winkel (44) von wenigstens 10 Grad und höchstens 80 Grad definieren, wobei der erste virtuelle Schenkel (42) den Schwerpunkt (34) mit der Ruhelage (39) verbindet und der zweite virtuelle Schenkel (43) den Schwerpunkt (34) mit einem Zentrum (27) des Schlagwerks (17) verbindet.
  6. Handwerkzeugmaschine (10) nach einem der vorhergehenden Ansprüche, wobei ein erster virtueller Schenkel (42) und ein zweiter virtueller Schenkel (43) einen ersten Winkel (44) definieren, wobei der erste virtuelle Schenkel (42) den Schwerpunkt (34) mit der Ruhelage (39) verbindet und der zweite virtuelle Schenkel (43) den Schwerpunkt (34) mit einem Zentrum des Schlagwerks (17) verbindet, und wobei die Oszillationsachse (37) und die Schlagachse (19) einen zweiten Winkel (45) definieren, wobei der zweite Winkel (45) im Bereich von 20 Prozent bis 90 Prozent des ersten Winkels (44) liegt.
  7. Handwerkzeugmaschine (10) nach Anspruch 6, wobei der erste Winkel (44) größer als fünf Grad ist.
  8. Handwerkzeugmaschine (10) nach einem der vorhergehenden Ansprüche, wobei ein virtueller Schenkel (42) und die Oszillationsachse (37) einen Winkel (70) von wenigstens 30 Grad und höchstens 80 Grad definieren, wobei der virtuelle Schenkel (42) den Schwerpunkt (34) mit der Ruheposition (39) verbindet.
  9. Handwerkzeugmaschine (10) nach einem der vorhergehenden Ansprüche, wobei die Oszillationsachse (37) und die Schlagachse (19) einen Winkel (45) definieren, der in einem Bereich von wenigstens 5 Grad und höchstens 60 Grad liegt.
  10. Handwerkzeugmaschine (10) nach einem der vorhergehenden Ansprüche, wobei die Ruhelage (39) und der Schwerpunkt (34) auf gegenüberliegenden Seiten der Schlagachse (19) liegen.
  11. Handwerkzeugmaschine (10) nach einem der vorhergehenden Ansprüche, wobei das Schlagwerk (17) einen motor-getriebenes pneumatisches Schlagwerk (17) beinhaltet.
EP09158130A 2009-04-17 2009-04-17 Handwerkzeugmaschine mit Schwingungsdämpfer Active EP2241409B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09158130A EP2241409B1 (de) 2009-04-17 2009-04-17 Handwerkzeugmaschine mit Schwingungsdämpfer

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09158130A EP2241409B1 (de) 2009-04-17 2009-04-17 Handwerkzeugmaschine mit Schwingungsdämpfer

Publications (2)

Publication Number Publication Date
EP2241409A1 EP2241409A1 (de) 2010-10-20
EP2241409B1 true EP2241409B1 (de) 2012-11-07

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024087576A1 (zh) * 2022-10-29 2024-05-02 江苏东成工具科技有限公司 冲击电动工具

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1882558A1 (de) * 2006-07-27 2008-01-30 HILTI Aktiengesellschaft Handwerkzeuggerät mit Entkopplungsanordnung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4647957B2 (ja) * 2004-08-27 2011-03-09 株式会社マキタ 作業工具
JP4815119B2 (ja) * 2004-10-15 2011-11-16 株式会社マキタ 往復作動式作業工具
GB2429675A (en) 2005-06-23 2007-03-07 Black & Decker Inc Vibration dampening mechanism
DE102007060636A1 (de) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Elektrohandwerkzeug, insbesondere ein Bohr- und/oder Meißelhammer, mit einer Tilgereinheit
DE102008000625A1 (de) * 2008-03-12 2009-09-17 Robert Bosch Gmbh Handwerkzeugmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1882558A1 (de) * 2006-07-27 2008-01-30 HILTI Aktiengesellschaft Handwerkzeuggerät mit Entkopplungsanordnung

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Publication number Publication date
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