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
  • 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
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
  • B25D—PERCUSSIVE TOOLS
  • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
  • B25D2216/0069—Locking means
• • 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
  • B25D2217/0084—Arrangements for damping of the reaction force by use of counterweights being fluid-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
  • B25D2217/0088—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
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
  • B25D—PERCUSSIVE TOOLS
  • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
  • B25D2250/131—Idling mode of tools
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
  • B25D—PERCUSSIVE TOOLS
  • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
  • B25D2250/231—Sleeve details

Definitions

• the invention is based on a handheld power tool percussion device according to the preamble of claim 1.
• the proposal is for a hand tool machine impact device with a striking mechanism arrangement, with at least one unit which is intended to generate a counterforce to a force resulting from the striking mechanism arrangement.
• a hand tool machine impact device with a striking mechanism arrangement with at least one unit which is intended to generate a counterforce to a force resulting from the striking mechanism arrangement.
• the generated counterforce and the force resulting from the hammer mechanism are Preferably aligned in opposite directions, so that an advantageous and at least partial cancellation of the forces can be achieved in a vibration reduction and thus particularly advantageous almost vibration-free guidance for an operator of the power tool can be achieved.
• the unit is intended to generate the counterforce within a large rotational speed range of a drive unit or over a high impact frequency range of the percussion mechanism so that the generated counterforce is advantageously matched in direction and time to a compression force of the striking mechanism arrangement and achieves maximum vibration reduction can be.
• the unit can be designed as a mechanical, an electrical and / or a magnetic and / or a pneumatic unit and / or as a further unit that appears appropriate to a person skilled in the art and thereby has a mechanical, an electrical and / or a magnetic etc. Create counterforce to the resulting force of the percussion arrangement.
• the unit is formed by a mass vibration unit, whereby constructionally simply by means of a mechanical excitation, in particular if the unit formed by the mass vibration unit has a counter-vibration mass, a counterforce to the compression force of the striking mechanism arrangement generated by a counter-vibration can be achieved.
• the unit has at least one spring means which supports the countervibration mass, whereby, after excitation of the countervailing mass, an advantageous return of the countervailing mass into the ring is obtained. heposition or starting position can be achieved and thus a renewed and in particular periodic excitation of the countervailing mass can be achieved.
• acts by the spring means or by a spring force of the spring means an additional force on the countervailing mass against an acceleration direction of the countervailing mass, so that the counterforce of the unit can be advantageously increased.
• the spring means supports the mating mass on a housing of the power tool.
• the unit has at least one excitation means which can be driven by means of a drive means of the striking mechanism arrangement, whereby a structurally simple adaptation or a coupling of the generated countervibration or the counterforce generated to a rotational speed of the drive unit or to a beat frequency of the striking mechanism arrangement can be achieved.
• the excitation means can be formed by an electrical, a magnetic and / or a mechanical excitation means and / or further excitation means which appears expedient to the person skilled in the art.
• the countervibration mass can be excited by means of the excitation means counter to a drive direction of the striking mechanism arrangement, whereby an advantageous cancellation of the counterforce and the resulting force of the striking mechanism arrangement can be achieved.
• the excitation means is formed by an eccentric wheel, so that in particular a periodic excitation of the countervibration mass can be achieved can, wherein the eccentric wheel is preferably coupled to a beat frequency of the striking mechanism arrangement or a rotational speed of the drive unit.
• an advantageous excitation can be achieved at a time of maximum compression or a maximum compression force of the striking mechanism arrangement if the excitation means is formed by a pneumatic means.
• the excitation means formed by a pneumatic means is coupled to a pneumatic unit of the striking mechanism arrangement and thus coupled to a striking frequency of the striking mechanism arrangement.
• the counter-vibration mass is arranged in the region of a hammer tube, whereby an advantageous vibration reduction can be achieved at a location of the vibration generation by the striking mechanism arrangement.
• a rapid cancellation of the vibration force resulting from the impact mechanism arrangement can be achieved by means of the counterforce and a long transmission path with a concomitant vibration propagation can be avoided.
• a "region of a hammer tube” is to be understood as a region within the handheld power tool impacting device that is at least partially circumferentially disposed about the hammer tube and / or positioned in front of and / or behind the hammer tube along a drive direction of the impactor assembly and / or particularly
• the hammer tube is formed directly. Assembly costs, costs and in particular a weight of the handheld machine tool striking device can be advantageously saved.
• the unit has a locking unit which is provided for securing the counterweight mass in an idling position.
• a locking unit which is provided for securing the counterweight mass in an idling position.
• FIG. 1 shows a hand tool with a hand tool according to the invention Schlagtechnik- device in a schematic side view
• FIG. 3 shows an eccentric wheel of the portable power tool impacting device
• FIG. 4 is a schematic top view of a hand tool machine alternative to FIG. 2, FIG.
• FIG. 5 shows the hand tool machine impact device of FIG. 2 with a stop means in a schematic view from above, FIG.
• FIG. 6 shows the handheld power tool impact device of FIG. 2 with another spring means in a schematic view from above, FIG.
• FIG. 7 shows a further alternative hand-held power tool impact device with a locking unit in a schematic side view
• FIG. 8 shows the handheld power tool striking device of FIG. 7 with a direct arrangement of the locking unit on a hammer tube in a schematic side view
• FIG. 9 shows a further alternative hand-held power tool impact device in a schematic side view
• FIG. 10 shows the handheld power tool impact device of FIG. 9 with an alternative excitation in a schematic view from above, FIG.
• FIG. 11 shows a further alternative hand-held power tool impacting device with a counterweight mass formed by a hammer tube in a schematic side view
• FIG. 12 shows a further alternative hand-held power tool impact device with a pneumatic means as an excitation means in a schematic side view.
• FIG. 1 shows a handheld power tool 36a with a handheld power tool striking device 10a according to the invention.
• the portable power tool impact device 10a (FIG. 2) comprises a striking mechanism assembly 12a and a unit 14a formed by a mass vibration unit.
• the percussion arrangement 12a is provided for generating a percussion impulse for a tool 40a, which is located in a tool holder 42a of the hand tool 36a (FIG.
• the Schlagtechnikan order 12a includes a hammer tube 32a, in which the piston 44a and the racket 48a along a drive direction 26a of the impact werkan ever 12a are mounted axially movable. Between the piston 44a and the racket 48a, the pneumatic element 46a formed by an air cushion is arranged (FIG. 2).
• a drive torque is generated by a drive unit of the handheld power tool 36a (not shown here in detail and formed by an electric motor).
• the drive unit transmits a drive torque to a drive means 38a, which is formed by a drive shaft and is aligned perpendicular to the drive direction 26a of the impact mechanism arrangement 12a (FIG. 2).
• a drive means 38a which is formed by a drive shaft and is aligned perpendicular to the drive direction 26a of the impact mechanism arrangement 12a (FIG. 2).
• this has an eccentric drive unit 52a with a non-rotatably connected to the drive shaft eccentric 54a and a bolt-shaped eccentric pin 56a.
• the eccentric pin 56a is aligned perpendicular to a main extension surface 58a of the eccentric wheel 54a and perpendicular to the drive direction 26a of the hammer mechanism 12a and arranged in a region of the eccentric wheel 54a which is arranged outside a drive shaft 60a of the eccentric wheel 54a formed by a rotation axis.
• the eccentric pin 56a is connected to the piston 44a via a drive rod 62a of the striking mechanism assembly 12a.
• the mass vibration unit is disposed in a portion of the portable power tool 36a, that of the drive shaft From the perspective, the drive direction 26a of the hammer mechanism 12a is opposite.
• the mass vibration unit has a counterweight 20a, a spring means 22a and an excitation means 24a formed by an eccentric wheel 28a.
• the eccentric 28a is driven via the drive shaft of the drive unit, which is provided for driving the hammer mechanism assembly 12a, and is rotationally connected thereto.
• the eccentric wheel 28a has a cam-shaped, asymmetrical shape of a main extension surface 64a, which, relative to a circular shape, has in a center a recess 66a for rotationally fixed attachment to the drive shaft (FIG. 3).
• the eccentric wheel 28a or a drive cam 68a of the mass vibration unit and the eccentric 54a and the eccentric 56a of Schlagtechnikanord- tion 12a run in the direction of rotation 72a with a phase shift of 180 ° about the drive shaft, so that the drive cam 68a of the eccentric 28a of the mass vibration unit in one of the drive direction 26a opposite end position is located when the eccentric pin 56a of the Exzen- terrads 54a of the hammer mechanism assembly 12a in a direction of drive 26a facing end position ( Figure 2).
• the counterweight 20a is moved counter to a drive direction 26a of the hammer mechanism 12a.
• the counterweight 20a is moved counter to a spring force of a spring means 22a, wherein the spring means 22a, the counterweight 20a is supported on a housing 70a of the power tool 36a.
• a counter force 16a is generated which reaches a maximum, due to the arrangement of the mass vibration unit, almost simultaneously with the maximum resulting force 18a of the impact mechanism 12a.
• the opposing force 16a of the mass vibration unit is directed counter to the resultant force 18a of the percussion mechanism arrangement 12a, so that the resulting force 18a of the percussion unit 12a
• Impact mechanism 12a and the counterforce 16a in the area of the drive shaft cancel as possible and resulting oscillations of the power tool 36a at least reduced and / or avoided ( Figure 2).
• the spring means 22a of the mass vibration unit causes an automatic return of the counterweight 20a in the initial situation, the counterweight 20a after a periodic rotation about the axis of rotation of the drive shaft of the cam-shaped Exzenterrads 28a again against the spring force of the spring means 22a and against the drive direction 26a of the impact mechanism 12a to move.
• the counterforce 16a of the mass oscillation unit is adapted to a momentary impact frequency of the striking mechanism arrangement 12a or to a direction and time of the force 18a resulting from the striking mechanism arrangement 12a.
• the spring means 22a causes increased inertia when the counterweight 20a is accelerated, and the counterforce 16a thus counteracts the resultant force 18a of the hammer mechanism 12a over a relatively long period of time.
• the figures 4 to 12 alternative embodiments are shown. Substantially identical components, features and functions are basically numbered by the same reference numerals. In order to distinguish the exemplary embodiments, however, the letters a to f have been added to the reference symbols of the exemplary embodiments. The following description is essentially limited to the differences from the exemplary embodiment in FIGS. 1 to 3, wherein reference can be made to the description of the exemplary embodiment in FIGS. 1 to 3 with regard to components, features and functions remaining the same.
• FIGS. 4 to 6 show an alternative hand tool machine impact device 10b.
• An eccentric wheel 28b for exciting a counterweight 20b is also provided for driving a hammer mechanism 12b.
• the eccentric wheel 28b has two eccentric pins 56b, 74b which are arranged on mutually opposite edge regions 76b, 78b of the eccentric wheel 28b.
• the eccentric pin 74b extends for excitation of the counterweight mass 20b on a side of the eccentric wheel 28b facing away from the eccentric pin 56b for driving the striking mechanism arrangement 12b, perpendicular to a main extension surface 64b of the eccentric wheel 28b.
• another spring means 80b is arranged on a side facing in a drive direction 26b side.
• the spring means 80b allows a muted coupling of the eccentric pin 74b to the counterweight mass 20b, wherein the eccentric pin 74b has a direction of movement in a direction of rotation 72b of the eccentric 28b and a drive shaft.
• the eccentric pin 74b coupled to a Timing to the spring element 80b, in which a compression force is built up in the hammer mechanism assembly 12b.
• a compressive force or a resultant force 18b increases counter to the drive direction 26b in the striking mechanism arrangement 12b and at the same time the countervailing mass 20b is pressed counter to the drive direction 26b and thus a counterforce 16b is generated by an acceleration of the countervailing mass 20b , If the eccentric pin 56b is located in an end position facing the striking mechanism arrangement 12b or if the eccentric pin 74b is in an end position facing the counterweight 20b, a maximum force 18b results from the striking mechanism arrangement 12b Drive direction 26b and from the mass vibration unit results in a maximum counterforce 16b in the direction of the drive direction 26b, wherein the force 18b and the counterforce 16b cancel each other at least partially.
• the mass vibration unit has a stop means 82b, which is arranged in the drive direction 26b of the impact mechanism arrangement 12b after the further spring means 80b.
• the stop means 82b prevents excessive back movement of the counterweight 20b by means of a spring means 22b and positions the counterweight 20b in a starting position for a renewed excitation by means of the eccentric wheel 28b.
• the stop means 82b is additionally provided with a
• Spring element 84b is coupled to the counterweight 20b, to prevent undesirable abutment of the spring means 80b and / or the countermass 20b on the stop means 82b.
• the counterweight 20b is positioned by means of the spring means 22b for support on the housing 70b of the power tool and the spring element 84b in a starting position for a new excitation.
• FIGS. 7 and 8 show a hand-held power tool striking device 10c according to the invention with a locking unit 34c, which is provided for securing a counterweight 20c in an idling position.
• the locking unit 34c has a spring element 86c, a locking element 88c, a fixing element 90c and a retaining ring 92c arranged on a hammer tube 32c.
• the spring element 86c supports the locking element 88c on a housing 70c of a hand-held power tool and is arranged in a chiseling operation in a prestressed position.
• the fixing element 90c is fixedly connected to the retaining ring 92c with an end 94c pointing in a drive direction 26c and movably arranged with the other end 96c within the locking element 88c.
• the locking element 88c has a recess 98c, which tapers in a direction which extends counter to the drive direction 26c, in which the fixing element 90c is arranged to be axially movable.
• the spring element 86c causes displacement of the fixing element 90c in the drive direction 26c or displacement from the tapered recess 98c Moving the locking member 88c upward or a movement of the locking member 88c, which is directed away from the housing 70c of the power tool.
• the locking element 88c moves into a locking recess 102c, which is arranged inside the counterweight 20c, so that the counterweight 20c is secured in the axial direction 100c ,
• the idling position is coupled to an idling position of a hammer mechanism 12c.
• the locking unit 34c in Figure 8 differs from the locking unit 34c in Figure 7 by a direct arrangement of the fixing element 90c on the hammer tube 32c, which has a holding element 104c for this purpose.
• FIGS. 9 and 10 show a portable power tool impacting device 10d with a counterweight 20d, which is arranged like a cylinder around a hammer tube 32d of a striking mechanism arrangement 12d.
• the counterweight 20d is thereby excited counter to a drive direction 26d of the impact mechanism 12d to a counter vibration, which generates a counter force 16d to a resultant force 18d of the impact mechanism 12d.
• the counterweight 20d is supported by a spring means 22d on a housing 7Od of a portable power tool, wherein the spring means 22d is arranged on one of the drive direction 26d of the striking mechanism arrangement 12d opposite end 124d of the counterweight 20d.
• a stop means 126d is arranged on the housing 7Od of a hand tool that stops the counterweight 20d when it is swung back into an initial position for a renewed excitation and prevents undesired advancement of the counterweight 20d in the direction of the drive direction 26d.
• the counter oscillating mass 20d arranged around the hammer tube 32d is excited to counter oscillations via an eccentric wheel 28d, which is different from an eccentric wheel 54d for driving the striking mechanism arrangement 12d.
• the counterweight 20d is excited via an excitation rod 128d, which is set into an axial movement via the eccentric wheel 28d.
• the counterweight 20d arranged around the hammer tube 32d is driven via the eccentric wheel 28d to drive the striking mechanism arrangement 12d.
• the excitation rod 128d has an axial guide 130d aligned in the drive direction 26d for exciting the counterweight 20d.
• FIG. 11 shows a portable power tool impact device 10e with a counter vibration mass 20e of a mass vibration unit formed by a hammer tube 32e.
• An operation and an excitation of the counterweight 20e in this case correspond to the embodiment in FIG. 9.
• FIG. 12 shows a portable power tool impact device 10f with an excitation means 24f formed by a pneumatic means 30f.
• a counterweight 20f of a mass vibration unit in a housing 11Of of the mass vibration unit.
• the housing 11Of of the mass vibration unit has a cylindrical shape with two valves 132f, 134f.
• the counterweight 20f which is disk-shaped, is excited to counter vibrations of a hammer mechanism 12f, so that the counterweight 20f generates a counterforce 16f to a resultant force 18f of the hammer mechanism 12f.
• the counterweight 20f is supported on the housing 11Of by a spring means 22f thereon.
• the two valves 132f, 134f are disposed on opposite housing walls 136f, 138f of the housing 11Of, with one of the two valves 132f for supplying air and the other of the two valves 134f for discharging air.
• the valve 132f for supplying Air is connected to a pneumatic element 46f of the impact mechanism assembly 12f via an air line 14Of. Air is conducted via the air line 14Of or the valve 132f by means of an overpressure in the pneumatic element 46f of the impact mechanism arrangement 12f into the housing 11Of of the mass vibration unit and an overpressure is generated in the mass vibration unit.
• the positive air pressure in the housing 11Of of the mass vibration unit pushes the counterweight 20f against a driving direction 26f of the hammer mechanism 12f against a spring force of the spring means 22f against the housing
• the counterweight 20f is located at a minimum distance from the housing 11Of of the mass vibration unit by means of the overpressure in a drive direction 26f, or the valve 134f for discharging air from the counterweight 20f uncovered within a portion 142f of the housing 11Of with the overpressure , air can be discharged into the hand tool. This results in a backward movement of the counterweight 20f in the drive direction 26f, wherein the valve 134f for discharging air in a starting position for re-excitation of the counterweight 20f is covered, so that a removal of the air before reaching a maximum counterforce 16f to the striking mechanism assembly 12f avoided becomes.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Percussive Tools And Related Accessories (AREA)
• Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)

Applications Claiming Priority (2)

Publications (2)

Family

ID=38829021

Family Applications (1)

Country Status (6)

Cited By (1)

Families Citing this family (9)

Family Cites Families (6)

• 2006
  • 2006-11-10 DE DE102006053105A patent/DE102006053105A1/de not_active Withdrawn
• 2007
  • 2007-09-20 EP EP07803568A patent/EP2089192B1/fr not_active Not-in-force
  • 2007-09-20 WO PCT/EP2007/059988 patent/WO2008055743A1/fr not_active Ceased
  • 2007-09-20 CN CN200780041828XA patent/CN101535007B/zh not_active Expired - Fee Related
  • 2007-09-20 DE DE502007006800T patent/DE502007006800D1/de active Active
  • 2007-09-20 AT AT07803568T patent/ATE502732T1/de active
  • 2007-09-20 RU RU2009121814/02A patent/RU2466856C2/ru not_active IP Right Cessation

Non-Patent Citations (1)

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