EP2269781A2 - Dispositif de réduction et/ou de compensation de vibrations, notamment pour une machine-outil manuelle et pour l'utilisation dans des machines-outils manuelles - Google Patents

Dispositif de réduction et/ou de compensation de vibrations, notamment pour une machine-outil manuelle et pour l'utilisation dans des machines-outils manuelles Download PDF

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Publication number
EP2269781A2
EP2269781A2 EP10161761A EP10161761A EP2269781A2 EP 2269781 A2 EP2269781 A2 EP 2269781A2 EP 10161761 A EP10161761 A EP 10161761A EP 10161761 A EP10161761 A EP 10161761A EP 2269781 A2 EP2269781 A2 EP 2269781A2
Authority
EP
European Patent Office
Prior art keywords
additional mass
movement
tool
compensating
vibrations
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.)
Withdrawn
Application number
EP10161761A
Other languages
German (de)
English (en)
Other versions
EP2269781A3 (fr
Inventor
Kurt Sieber
Otto Baumann
Elisabeth Michl
Hardy Schmid
Holger Ruebsaamen
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 EP2269781A2 publication Critical patent/EP2269781A2/fr
Publication of EP2269781A3 publication Critical patent/EP2269781A3/fr
Withdrawn legal-status Critical Current

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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
    • B25D17/24—Damping the reaction force
    • B25D17/245—Damping the reaction force using a fluid
    • 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
    • B25D2211/061—Swash-plate 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
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven
    • 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

Definitions

  • the invention relates to a device for the reduction and / or compensation of vibrations according to the preamble of the independent claims.
  • DE 10 2008 000 677 is already a device for reducing and / or compensation of vibrations, especially for a hand tool known.
  • reduction and / or compensation of vibrations is meant in particular measures and / or means and / or their effects, which counteract especially occurring in hand tool machines, caused by internal and / or external forces vibrations.
  • DE 10 2008 000 677 is a hand tool, in particular a drill and / or chisel, with a repetitive percussion drive for striking drivable tools, in particular application tools, known in which a, about a Huber Wegungsvorraumered as drive mechanism, preferably repetitive driven compensation body is provided.
  • the impact drive has in the example of DE 10 2008 000 677 at least one predominantly axially repetitive driven lifting element and a well-known air spring impact mechanism on.
  • the repetitive movement of the lifting element and the periodically occurring force pulses of the air spring impact mechanism stimulate the power tool to vibrate.
  • a movement of the compensation body of the power tool according to DE 10 2008 000 677 is tuned in a phase relationship to the movement of the lifting element so that a periodic force is generated by the movement of the compensating body, which acts as a counterforce reducing and / or compensating for the forces causing the vibrations.
  • the repetitive movement of the compensation body follows in time substantially a sinusoidal shape, wherein the periodic forces are generated in particular in a reversal of the direction of movement and show a pulse-like individual course.
  • this effective force Due to the superposition of various occurring over a period of the impact drive, vibration-inducing forces resulting from the percussion drive and / or setbacks of the applied during operation on the insert tool impact pulses and / or other sources to a vibration-inducing effective force, this effective force has a complex time profile over a period. Depending on characteristic differences in the time profile of the vibration-exciting effective force and the counterforce caused by the balance body, the vibration-compensating effect of the balance body may be limited.
  • the device according to the invention with the features of the main claim has the advantage that at least one relative to the compensating body relatively movable, preferably limited relatively movable additional mass is provided which forms a time profile of the compensating body caused by the counterforce advantageous force or deformed, preferably at a periodic movement of the compensation body adjusts the vibration-inducing effective force.
  • a further advantage is to be considered that a lower peak load of the drive mechanism can be achieved by the inventive development of the compensation body.
  • relatively movable is meant in particular that move the additional mass relative to the balancing body, preferably move and / or rotate.
  • limited relatively movable is meant in particular that a movement limits the additional mass relative to the compensation body, in particular in an extension or amplitude is smaller than a spatial extension of the compensation body and / or as an extension or amplitude of movement of the compensation body.
  • provided is meant in particular “to be equipped”, “to be equipped” or “to be supplemented”.
  • adjusting the vibration-inducing effective force will be used understood that compensate for the vibration-stimulating effective force and the counterforce as much as possible or cancel.
  • the at least one additional mass is arranged within the compensating body.
  • the term "arranged inside” means, in particular, that the additional mass is essentially taken up by the compensating body or enclosed by the compensating body.
  • the at least one additional mass is guided in the compensating body, in particular guided guided on at least one guide surface on the compensating body.
  • the at least one additional mass is arranged on or on the compensating body, a particularly well tunable embodiment can thereby be achieved.
  • the additional mass is guided guided on the compensating body.
  • the additional mass is formed from a plurality of mass bodies, in particular a plurality of mass bodies.
  • the compensating body has at least one receiving space in which the mass bodies are accommodated.
  • the additional mass is formed from a granular medium.
  • the granular medium may in this case be formed, in principle, from mass bodies of one type and / or size or else from a mixture of different mass bodies. The mixture can be distributed homogeneously or heterogeneously in the receiving space.
  • a particularly effective embodiment of a device according to the invention for reducing and / or compensating vibrations is achieved in that the at least one additional mass has at least a first degree of freedom of movement relative to the balancing body, wherein the additional mass in both a forward direction and a backward direction of this first degree of freedom can move. Furthermore, a means for influencing the movement of the additional mass is provided, by which the movement in the forward direction has a relation to the backward direction changed movement behavior.
  • the "means for influencing the movement” can also be understood as a “means for direction-dependent influencing of the movement”. Under a "Degree of freedom of the movement” is understood here in particular, a mobility in a spatial axis and / or a rotational mobility about a spatial axis.
  • a “changed movement behavior” is understood in particular as meaning a directionally different movement speed of the additional mass relative to the compensation body and / or a time shift, for example a deceleration, of the course of movement and / or a movement amplitude.
  • the "means for influencing the movement” may be in particular mechanical and / or pneumatic and / or hydraulic and / or magnetic and / or electrical nature.
  • the means for influencing the movement can be used if the first degree of freedom of the movement of the additional mass is aligned substantially parallel to a degree of freedom of the movement of the compensating body.
  • the at least one additional mass of the device according to the invention has a rest position mediated by at least one return element.
  • the return element is connected at one end to the compensation body.
  • the return element is supported by a second end of the additional mass and / or connected to the additional mass.
  • the restoring element comprises a fluid, in particular the restoring element consists of the fluid.
  • the fluid may be gel-like, liquid, in particular oily, or gaseous.
  • the gaseous fluid is air.
  • the at least one additional mass of the device according to the invention interacts with an attenuator.
  • cooperating is meant in particular a damping of the movement of the additional mass by means of the attenuator.
  • the attenuator may have a granular or rubbery or elastomeric damping element.
  • the attenuator comprises a fluid, in particular it consists of the fluid.
  • means for influencing a phase position between the movement of the additional mass and the movement of the compensating body are provided, by means of which the phase position can be selected in a selectable manner.
  • an advantageous hand tool machine with a drive device for driving a tool, wherein vibrations are caused in the hand tool which comprises a device according to the invention for reducing and / or compensating for these vibrations.
  • the drive device is driven by a motor, in particular by an electric motor, and the drive mechanism of the device according to the invention for reducing and / or compensating for vibrations is operatively connected to the drive device.
  • the drive mechanism is coupled to the drive device.
  • the drive device for driving the tool comprises a percussion mechanism, in particular an air spring impact mechanism, by which the tool is pulse-like, in particular periodically impulsively driven in an axial direction.
  • the hand tool is designed as a drill and / or chisel hammer.
  • a device according to the invention for reducing and / or compensating vibrations in a hand tool in particular a hand tool with a motor, preferably electric motor driven tool for reduction and / or compensation of a drive device for driving the tool and / or or used or used by a use of the tool vibrations.
  • Fig. 1 shows a schematic side view of a first embodiment of a device 100 according to the invention for the reduction and / or compensation of vibrations.
  • the device 100 comprises a movably mounted compensation body 102 and a drive mechanism 104.
  • the drive mechanism 104 is of the kind on the compensation body 102 that this is drivable by the drive mechanism 104 drivable, preferably repetitive drivable.
  • the compensation body is geometrically simple, for example substantially cylindrical or cubic.
  • the drive mechanism 104 is configured as a swashplate drive 106.
  • the swashplate drive 106 has a swashplate 112 which can be driven via a swash-bearing 108 on a drive shaft 110 which can be driven in rotation and can be driven by the drive shaft 110.
  • a wobble finger 114 is provided at the swash plate 112, a wobble finger 114 is provided.
  • the drive shaft 110 extends along a rotation axis 116, about which it is rotatably driven.
  • the swash bearing 108 comprises bearing elements 118, which run on a bearing track, not shown here, inclined by an angle WT relative to the axis of rotation 116.
  • the wobble finger 114 extends in this example radially from the swash plate 112 substantially perpendicular to a normal direction 120 of a plane of the bearing race. However, other orientations of the wobble finger 114 may be advantageous without departing from the spirit of the invention. If the drive shaft 110 is now driven in rotation, a rotational movement 122 of the drive shaft 110 is converted into a substantially oscillating movement 124 of the wobble finger 114.
  • the angle WT covers an angle between two reversal points.
  • the wobble finger 114 engages with its free end in or by a compensation body 102 provided on the hinge seat 126.
  • the hinge seat 126 can, for example, as a hinge joint with a hinge pin, as it is known from among others DE 10 2008 041 890 is known, or designed as a ball joint.
  • means 128 for guiding and supporting the compensating body 102 are provided.
  • the balancing body 102 In the execution after Fig. 1 is the balancing body 102 on at least one Guiding element 130 arranged axially movably guided in at least one movement axis 132.
  • the movement axis 132 extends substantially parallel to the rotation axis 116. If the wobble finger 114 is excited to oscillate 124, then the compensation body 102 executes an axially oscillating pendulum motion 134 in the movement axis 132.
  • the compensating body 102 further has a receiving space 138.
  • an additional mass 140 is movably received.
  • the receiving space 138 and the additional mass 140 is formed substantially cylindrical or cubic.
  • the additional mass 140 has a first degree of freedom of the movement 142 relative to the compensation body 102. This first degree of freedom of the movement 142 is designed as an axial displacement 144, wherein the axial displacement 144 is oriented substantially parallel to the movement axis 132 of the compensation body 102.
  • the receiving space 138 has a preferably closed end 146 and an end 150 preferably closed by a closure element 148.
  • the additional mass 140 is therefore limited relative to the compensation body 102 substantially between the preferably closed end 146 and the closure element 148.
  • at least one inner lateral surface 152 of the receiving space 138 and a lateral surface 154 of the additional mass 140 are each designed as a guide surface, so that the additional mass 140 guided movably in the receiving space 138.
  • a venting means for venting the receiving space 138 is provided in at least one end 146, 150, which can preferably be realized by a vent hole, for example in the closure element 148 or a vent bypass.
  • at least one of the ends 146, 150 is at least partially open.
  • the additional mass 140 can also have at least one venting means, which essentially connects the two subspaces of the receiving space created by the additional mass 140 for the purpose of pressure equalization.
  • the additional mass 140 is further arranged between two return elements 156a, 156b.
  • the first return element 156a extends between the closed end 146 of the receiving space 138 and a first end face 158a of the additional mass 140, in particular the first return element 156a is supported on the closed end 146 and on the first end face 158a.
  • the second return element 156b extends between the closed end 150 and a second end face 158b of the additional mass 140, in particular the second return element 156b is supported on the closed end 150 and on the second end face 158b.
  • the return elements 156a, 156b are connected to the compensation body 102 with one end each.
  • the return elements 156a, 156b may be connected at their respective other end to the additional mass 140.
  • By “connected” is meant in particular "attached”.
  • the reset elements 156a, 156b are in the present example after Fig. 1 designed as coil springs, preferably helical compression springs.
  • return elements 156a, 156b known, such as other spring elements - eg leaf springs or disc springs - or elastic damping elements made of an elastomer or rubber-like material, which can be advantageously used in a device according to the invention.
  • the additional mass 140 is designed to be magnetic, preferably permanent magnetic, and that a magnet is also provided on at least one of the two ends 146, 150 of the receiving space 138.
  • the fields of the magnets of the additional mass 140 and at the at least one end 146, 150 are aligned so that the additional mass 140 experiences a repulsive force when approaching the at least one end 146, 150.
  • the two return elements 156a, 156b can be of the same type, in particular identically designed, or of different types and / or different. The skilled person will case by case select the most advantageous embodiment.
  • the reset elements 156a, 156b in the present example each exert a restoring force on the additional mass 140. Act no external forces on the additional mass 140, the additional mass 140 is moved by the restoring forces of the return elements 156a, 156b in a rest position S0 relative to the compensating body 102.
  • At least one damping member 160a, 160b cooperates with the additional mass 140.
  • compensating body 102 is excited in the operation of the device according to the invention via the wobble finger 114 to axially oscillating pendulum 134, the system of additional mass 140 and the return elements 156a, 156b reacts delayed on the movement of the compensation body 102.
  • the additional mass 140 forms together with the return elements 156a 156b a so-called mass-spring system whose properties, in particular resonance properties, are well known to the person skilled in the art.
  • an oscillating pendulum motion 162 with a variable amplitude AZ will likewise be set around the rest position S0 in the additional mass 140.
  • the closure element 148 is designed in particular axially adjustable relative to the compensation body. If, for example, the closure element 148 is designed as a screw-in element, the resonance properties of the mass-spring system can be made adjustable by selecting a screw-in depth. This may be advantageous in particular during assembly of the device according to the invention.
  • Fig. 2 shows a drill and / or chisel hammer 10 as an example of a hand tool with a drive device 12 for driving a tool 14 and a device according to the invention for reducing and / or compensation of vibrations 100.
  • the drill and / or chisel hammer 10 has at least one machine housing 16 , on whose one end face 18 a tool holder 20 with a tool holder, not shown, for receiving, in particular to exchangeable receiving of the tool 14 is provided.
  • the tool 14 is in the tool holder 20 rotationally and / or beating drivable and defined over a longitudinal extent an axial direction 15.
  • a Handle device 24 is provided at one of the end face 18 opposite end 22 is on the machine housing 16 .
  • the handle device 24 has a device switch 26 for commissioning the drill and / or chisel hammer 10.
  • a device switch 26 for commissioning the drill and / or chisel hammer 10.
  • the drive device 12 is arranged substantially within the machine housing 16 and shown only schematically.
  • the drive device 12 comprises a motor 30, in particular an electric motor 32, and a gear device 34 for transmitting and / or translating a movement of the motor 30, 32 in movement of the tool 14 relative to the machine housing 16.
  • the device 100 for reduction and / or compensation of vibrations is in the present example operatively connected to the transmission device 34, in particular coupled directly to this.
  • the gear device 34 comprises a hammer mechanism 36, in particular an air spring impact mechanism 38, as is well known to the person skilled in the art.
  • the hammer mechanism 36, 38 By the hammer mechanism 36, 38, the tool 14 is pulse-like, in particular in the axial direction 15 pulse-like, in particular periodically driven.
  • the percussion mechanism 36, 38 and / or the impulsively acted upon tool 14 in a reaction causes vibrations in the drill and / or chisel 10, in particular on the machine housing 16 and / or on the handle device 24 and / or on Additional handle 28.
  • the percussion mechanism 36, 38 comprises a piston unit 40, which is arranged axially displaceable in a hammer tube 42.
  • the piston unit 40 is driven via a drive unit 44, which is part of the transmission device 34, axially oscillating in the hammer tube 42.
  • the drive unit 44 is designed as a wobble unit 46.
  • Racket unit 48 arranged axially displaceable. Between the piston unit 40 and the racket unit 48, an air spring 50 is provided. By the axially oscillating movement of the piston unit 40, the air spring 50 is compressed or relaxed, whereby pressure forces arise, which can be transmitted via the piston unit 40 and / or the hammer tube 42 on the drilling and / or percussion hammer 10.
  • the pressure forces can also be understood as a source for excitation of vibrations in the hammer and / or percussion hammer 10.
  • the racket unit 48 is accelerated by the pressure forces alternately in the direction of the tool holder 20 to or from the tool holder 20 away.
  • the club unit 48 transmits a shock pulse to an unillustrated shank end of the tool 14.
  • This impact pulse prepares to a working tip via the tool 14 and is transferred there to a work surface.
  • a reverse pulse is prepared via the tool 14 on the tool holder 20 and / or the racket unit 48.
  • This reverse pulse is another source for excitation of vibrations in the hammer and / or percussion hammer 10.
  • FIG. 2 illustrated simple embodiment of a drill and / or chisel hammer 10
  • FIG. 2 illustrated simple embodiment of a drill and / or chisel hammer 10
  • alternative and / or further developed embodiments of air spring impact devices 38 can include, for example, a firing pin unit in addition to the piston unit 40 and the club unit 48, which receive the impact pulses of the club unit 48 and transmit it to the tool 14.
  • a firing pin unit in addition to the piston unit 40 and the club unit 48, which receive the impact pulses of the club unit 48 and transmit it to the tool 14.
  • it is off DE 10 2006 046 472 A1 an air spring percussion 38a with an additional firing pin unit known, the disclosure of which reference is made at this point.
  • the device 100 according to the invention for reduction and / or compensation of vibrations, one on the complex time course of the effective force to create a coordinated counterforce.
  • the opposing force is superimposed on the effective force in such a way that the residual force that stimulates the vibrations is as small as possible or only excites vibrations, which can be optimally damped by additional damping measures.
  • further development options for the device 100 according to the invention for reducing and / or compensating vibrations are presented, with which the person skilled in the art can be given further possibilities for achieving the described objective.
  • FIG. 3 a modified embodiment of the device 100 according to the invention Fig. 1 wherein the drive mechanism 104 is formed as an eccentric drive.
  • Such drives are well known to those skilled in the art and serve as the above described wobble drive the conversion of a rotary motion 122 in an oscillating axial movement 134.
  • the operation of the device 100 according to the invention corresponds to the operation of the first embodiment, so that reference is made to the preceding description.
  • DE 10 2008 000 677 are other alternative drive mechanisms such as cam, link or lever systems for generating an oscillating axial movement known, which can be advantageously used in a drive mechanism 104 of a device 100 according to the invention.
  • the operation of the device 100 according to the invention corresponds to the operation of the first embodiment, so that reference is made to the preceding description.
  • Regarding the description of the alternative drive mechanisms is on the DE 10 2008 000 677 which is hereby expressly included in the disclosure.
  • the drive mechanism 104 is an electromagnetic, electromotive, piezoelectric, Magnetostrictive or other kind of drive comprises, in particular consists of this.
  • Fig. 4 shows the schematic side view of a second embodiment of a device 100 according to the invention for the reduction and / or compensation of vibrations.
  • the second embodiment according to Fig. 4 differs from the first embodiment in the embodiment of the additional mass 140, which is movably arranged in the receiving space 138 of the compensation body 102, in particular along the movement axis 132 axially displaceable.
  • the drive mechanism 104 of the device 100 according to the invention corresponds to the form already known from the first embodiment, to the description of which reference is made at this point.
  • the receiving space 138 is at least partially filled with a fluid 164, wherein the fluid 164 can act as a return element 156, 156a, 156b and / or as an attenuator 160, 160a, 160b.
  • the fluid 164 may be gel-like, liquid or gaseous.
  • the fluid 164 is a gas 166 - e.g. Air, a liquid 168 - e.g. Water or an oil - or liquid-gas mixture 170.
  • the closing element 148 which closes the receiving space 138 is in this case embodied with a seal substantially close to the fluid 164.
  • "dense” means, in particular, "tightly over the service life of the handheld power tool with respect to an escape of the fluid 164 from the receiving space 138".
  • the additional mass 140 preferably has at least sealing element 172.
  • the sealing element 172 circumferentially around the additional mass 140 is formed circumferentially.
  • the sealing element 172 may be embodied in particular as an O-ring or a shape-sealing element.
  • the sealing element 172 subdivides the receiving space 138 with respect to a mobility of the fluid 164, 166, 168, 170 into two substantially separate segments 138 a, 138 b.
  • segments 138a, 138b are filled with a fluid 164, 166, 168 or both segments 138a, 138b are filled with different fluids 164a, 164b, 166a, 166b, 168a, 168b.
  • the fluid 164, 166, 168, 170 which lies in the direction of movement in front of the additional mass 140, segment 138a, 138b exists, compacted.
  • the fluid 164 is essentially a gas 166
  • the gas 166a, 166b in the relevant segment 138a, 138b acts as a compressed gas spring.
  • the fluid 164 is essentially a liquid 168
  • the movement of the additional mass is strongly damped by a rapidly increasing fluid pressure in the relevant segment 138a, 138b.
  • the spring and damping effect depends on the composition, that is to say in particular on the degree of filling of the segments with the liquid.
  • a fluid 164, 166, 168, 170 in a direction of movement of the additional mass 140 opposite segment 138a, 138b of the receiving space 138 is diluted analogously.
  • the second embodiment of the inventive device 100 according to Fig. 4 is similar in effect to the already described above effect of the first embodiment, so that reference is made to the description there.
  • a throttle device 174 preferably a direction-dependent throttle device 174, is provided in the additional mass 140.
  • the damping effect can be influenced in an adjustable manner via such a throttle device.
  • Fig. 5a shows a third embodiment of an inventive device 100 for reducing and / or compensation of vibrations in a schematic side view.
  • the drive mechanism 104 of the device 100 according to the invention corresponds to the form already known from the first embodiment, to the description of which reference is made at this point.
  • the receiving space 138 is at least partially filled with a fluid 164, in particular with a liquid 168 or a liquid-gas mixture 170, preferably with an oil, which serves as a return element 156, 156a, 156b and / or as an attenuator 160, 160a, 160b can act.
  • the receiving space 138 is formed substantially cylinder-like.
  • the at least one additional mass 140 to third embodiment has an ellipsoidal, preferably spherical shape.
  • a transverse extension, In particular, a diameter d of the additional mass is smaller than a diameter D of the receiving space 138.
  • a diameter difference ⁇ of the diameter D and the diameter d thereby determines a cross section of a slit throttle 176.
  • the gap choke 176 divides the receiving space 138 with respect to the fluid 164, 168, 170 into two segments 138a, 138b. If the additional mass 140 is caused by an external force from a rest position to move in the direction of the segment 138a, then volume fractions of the fluid 164, 168, 170 are displaced from the segment 138a via the gap throttle 176 into the segment 138b. An attenuation effect of the fluid of a 164, 168, 170 on the mobility of the additional mass 140 depends on the size of the gap throttle 176, in particular the diameter difference ⁇ .
  • the third exemplary embodiment substantially corresponds to the second exemplary embodiment, wherein a throttle device 174 is provided in the additional mass 140.
  • Fig. 5b shows a further development of the third embodiment according to Fig. 5a , wherein an over an axial extension T variable cross-section, in particular diameter D (T) of the receiving space 138 is provided.
  • the variable cross section has the consequence that the diameter difference ⁇ (T) and thus the cross section of the gap throttle 176 over the axial extent T is variable.
  • the damping effect of the gap choke 176 depends on the current position of the additional mass 140 in the receiving space 138.
  • the thus formed gap choke 176 forms a means for influencing the movement of the at least one additional mass 140, by which the movement in a forward direction of the additional mass relative to the movement in a backward direction has a changed movement behavior.
  • the inner circumferential surface 152 is executed substantially barrel-like arched. However, it may be advantageous for the inner circumferential surface 152 to have a conical, double conical or otherwise curved surface.
  • Fig. 6a shows a fourth embodiment of a device 100 according to the invention in a schematic side view.
  • the receiving space 138 of the compensation body 102 is in the fourth embodiment, at least partially executed with a plurality of mass bodies 180, for example, a granules such as steel shot filled.
  • the Mass body 180 thereby form the additional mass 140 of the device 100 according to the invention.
  • the mass body 180 by inertial forces for example by the drive mechanism 104 induced oscillating pendulum motion 134 of the compensating body 102 caused inertial forces from a relatively relative to the compensating body 102 rest position relative to this are moved.
  • the mass bodies 180 are embedded in a carrier medium 182, preferably in an elastic carrier medium 182.
  • the carrier medium 182 acts in particular as a restoring element 156 and / or damping member 160.
  • Each individual mass body 180 acts as a reduced version of the additional mass 140 to first embodiment.
  • the carrier medium 182 may be a rheological or an electromagnetic-sensitive fluid.
  • 100 devices for influencing the mechanical properties, in particular the viscous and / or elastic properties of the rheological or electromagnetic-sensitive fluid are provided in the apparatus 100 according to the invention. These means can be used in a particularly preferred embodiment as a means for direction-dependent influencing the movement of the at least one additional mass 140.
  • Fig. 6b shows a modification of the fourth embodiment in which the additional mass 140 consists of a mixture of a plurality of mass bodies 180a, 180b of at least two different types and / or size.
  • the additional mass 140 consists of a mixture of a plurality of mass bodies 180a, 180b of at least two different types and / or size.
  • mass bodies 180 may also be advantageous, without thereby departing from the inventive idea.
  • a grid of lamellas 184 directed at an angle of incidence relative to the movement axis 132 is also shown, which influences a mobility of the mass bodies 180 in a direction-dependent manner.
  • the lamellae 184 act counter to the angle of attack as greater resistance to movement of the mass body as a movement in the direction of the angle of attack.
  • These lamellae 184 thus represent a means for direction-dependent influencing of the movement of the at least one additional mass 140.
  • Fig. 7 shows a fifth embodiment of a device 100 according to the invention.
  • the additional mass 140 is movably arranged on an outer surface 186 of the compensating body 102.
  • the additional mass 140 is arranged guided on the outer surface 186.
  • the additional mass 140 can both be arranged on one side on the compensation body 102 and also have a shape which at least partially, preferably almost completely surrounds the compensation body 102. This by the disputed lines in Fig. 7 indicated.
  • two abutment elements 188a, 188b are provided on the compensating body 102, in particular connected to the compensating body 102.
  • the abutment elements 188a, 188b limit the axial relative mobility of the additional mass 140 relative to the compensating body 102.
  • a restoring element 156a, 156b and / or an attenuator 160a, 160b is provided between the end faces 158a, 158b and the corresponding abutment elements 188a, 188b.
  • a restoring element 156a, 156b and / or an attenuator 160a, 160b is provided between the end faces 158a, 158b and the corresponding abutment elements 188a, 188b.
  • at least one of the contact elements 158a, 158b is connected to the compensating body 102 in an axially lockable manner relative to the compensating body 102.
  • the fifth embodiment of the operation corresponds to the above-described first embodiment, the description of which reference is made here.
  • Fig. 8 shows a sixth embodiment of a device 100 according to the invention.
  • the compensation body 102 and the additional mass 140 are arranged substantially adjacent to one another along the movement axis 132.
  • the additional mass 140 essentially corresponds to an extended part of the compensating body 102.
  • the additional mass 140 is connected to the compensating body 102 via an elastic element 190.
  • the additional mass 140 is connected at its end face facing the compensating body 102 via the elastic element 190 to the corresponding end face of the compensating body 102.
  • the elastic element 190 may consist in particular of an elastomer or a rubber-like material. Alternatively or additionally, the elastic element 190 may also comprise a spring element.
  • this embodiment corresponds to the embodiments already described, to the description of which reference is made here.
  • this may also be very advantageous, e.g. in saber saws, jigsaws, drills, percussion drilling machine or other machine tools, in particular hand tool machines with preferably an axially oscillating acting drive of a tool for the reduction and / or compensation of vibrations are used.
EP10161761.1A 2009-07-02 2010-05-03 Dispositif de réduction et/ou de compensation de vibrations, notamment pour une machine-outil manuelle et pour l'utilisation dans des machines-outils manuelles Withdrawn EP2269781A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910027422 DE102009027422A1 (de) 2009-07-02 2009-07-02 Vorrichtung zur Reduktion und/oder Kompensation von Vibrationen, insbesondere für eine Handwerkzeugmaschine und zur Verwendung in Handwerkzeugmaschinen

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EP2269781A2 true EP2269781A2 (fr) 2011-01-05
EP2269781A3 EP2269781A3 (fr) 2014-01-29

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EP (1) EP2269781A3 (fr)
CN (1) CN101941199B (fr)
DE (1) DE102009027422A1 (fr)

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EP2269781A3 (fr) 2014-01-29
DE102009027422A1 (de) 2011-01-05
CN101941199B (zh) 2015-07-29
CN101941199A (zh) 2011-01-12

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