EP3227056B1 - Machine-outil à main - Google Patents

Machine-outil à main Download PDF

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Publication number
EP3227056B1
EP3227056B1 EP15802103.0A EP15802103A EP3227056B1 EP 3227056 B1 EP3227056 B1 EP 3227056B1 EP 15802103 A EP15802103 A EP 15802103A EP 3227056 B1 EP3227056 B1 EP 3227056B1
Authority
EP
European Patent Office
Prior art keywords
cam
bending spring
angular position
hand
degrees
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.)
Active
Application number
EP15802103.0A
Other languages
German (de)
English (en)
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EP3227056A1 (fr
Inventor
Oliver Ohlendorf
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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Filing date
Publication date
Application filed by Hilti AG filed Critical Hilti AG
Publication of EP3227056A1 publication Critical patent/EP3227056A1/fr
Application granted granted Critical
Publication of EP3227056B1 publication Critical patent/EP3227056B1/fr
Active 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
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—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
    • 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
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—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
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • 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
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • 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
    • B25D2250/045—Cams used in percussive 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
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other
    • 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
    • B25D2250/371—Use of springs
    • B25D2250/381—Leaf springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for

Definitions

  • the present invention relates to a chisel hand tool according to the preamble of claim 1, which includes a damper for reducing vibrations.
  • a hand tool is from the US 2011/0017483 A1 known.
  • the hand tool has a tool holder for holding a tool on a working axis, a pneumatic impact mechanism for applying shocks to the tool and a damper from a transverse to the working axis bending spring and a mass body.
  • a countershaft is driven by a rotation axis parallel to the working axis through the motor.
  • On the countershaft a wobble drive for driving the pneumatic impact mechanism is arranged.
  • a cam disc with a cam extending in a direction parallel to the working direction of the starting cam is arranged on the countershaft.
  • the spiral spring has provided counterpart to the cam. The cam biases adjacent to the counterpart of the spiral spring in the direction of advance.
  • the absorber is triggered by the rotating cam.
  • the abutment takes place at the resting position of the spiral spring when the absorber is at a standstill or when the absorber has not yet completely settled.
  • the cam periodically forces a minimum deflection of the absorber.
  • the absorber excited by the vibrations and the hand tool can deflect more.
  • the abutment is synchronized with the movement of the striking mechanism and thus the vibrations of the power tool.
  • the cam disc is non-contact with the bending spring when the cam and the counterpart are in diametrical angular position relative to the axis of rotation.
  • the cam disc dissolves with each revolution of the cam about the axis of rotation once by the spiral spring, so that the absorber can oscillate freely at least during this phase.
  • the absorber releases for at least 50% of an oscillation, ie, without contact with the cam and only driven by the inertia of the mass.
  • the mass body is guided by the spiral spring on a curved path.
  • the flexure spring may be attached to the machine housing at a first end and secured to a second end of the mass body, wherein the first end and the second end are diametrically disposed from the countershaft.
  • the projection may be at a distance from the first end which corresponds to between 30% and 50% of the distance of the first end to the second end.
  • An embodiment provides that a maximum deflection of the spiral spring from a rest position by the voltage applied to the counterpart cam is between 1 degree and 5 degrees.
  • the cam has a helical flank facing the spiral spring, which rises in the direction of feed via a central angle between 30 degrees and 90 degrees.
  • the counterpart may have a helical flank facing the cam, which rises in the opposite direction to the starting direction via a central angle between 30 degrees and 90 degrees.
  • the force applied to the absorber during abutment force is preferably kept low. This avoids suggestions of higher harmonic oscillations in the spiral spring.
  • the pneumatic chamber of the striking mechanism is maximally compressed when the countershaft angle is set.
  • the cam at the time assumes a specific position relative to the projection, which depends on the arrangement of the cam before or after the bending spring. If the cam is in front of the spiral spring, the cam and the projection are in the same angular position with respect to the axis of rotation, i. The cam can maximally deflect the projection. When the cam is positioned after the bending spring, the cam and projection are diametrically opposed to the axis of rotation, i. offset by 180 degrees.
  • the absorber is optimally tuned to the movement of the impact mechanism.
  • the wobble drive is at a first angular position of the countershaft in a dead center away from the tool.
  • the cam is at a second angular position in a bending spring maximally deflecting angular position. If the cam is arranged on the side facing away from the tool of the bending spring, the second angular position can advantageously follow between 95 degrees and 115 degrees to the first angular position. If the cam is arranged on the tool facing side of the spiral spring, the first angular position can advantageously follow between 65 degrees and 85 degrees to the second angular position.
  • Fig. 1 shows an exemplary hammer drill 1.
  • the hammer drill 1 has a tool holder 2, which along a working axis 3 a drill bit 4, a chisel or other tool can accommodate.
  • a motor 5 can drive the tool holder 2 in rotation about the working axis 3 .
  • a striking mechanism 6 can also exert on the lying in the tool holder 2 tool periodically blows in the direction of impact 7 along the working axis 3 for chiseling operation.
  • the striking mechanism 6 is driven by the motor 5 .
  • the user takes the motor 5 with a main switch 8 in operation.
  • the motor 5 and the striking mechanism 6 are arranged in a machine housing 9 .
  • a battery pack or a power line provide the motor 5 with electrical power.
  • the user can guide the hammer drill 1 with a handle 10 which is fixed to the machine housing 9 .
  • the hammer drill 1 has a shiftable transmission with a countershaft 11.
  • the countershaft 11 is rotatably mounted about an axis of rotation 12 .
  • the axis of rotation 12 is parallel to the working axis 3.
  • the motor 5 meshes with a drive pinion 13 on the countershaft 11 and drives the countershaft 11 permanently.
  • the countershaft 11 transmits the torque to a wobble drive 14 for the striking mechanism 6 and a rotary drive 15 for the tool holder 2.
  • the exemplary transmission allows the rotary drive of the tool holder 2 on and off.
  • a shift sleeve 16 is axially movable on the countershaft 11 between a first position and a second position.
  • the shift sleeve 16 In the first illustrated position engages an internal toothing of the shift sleeve 16 in a toothing 17 of the countershaft 11 , in a second position, the shift sleeve 16 is disengaged.
  • the shift sleeve 16 is in permanent engagement with a ring gear 18, which is coupled to the rotary drive 15 and the tool holder 2 .
  • a shift knob allows the user to move the shift sleeve 16 between the two positions.
  • An analog shift sleeve can be arranged on the countershaft 11 for connecting and disconnecting the wobble drive.
  • the wobble drive 14 converts the rotational movement of the countershaft 11 into a periodic, linear movement for the striking mechanism 6 .
  • the wobble drive 14 includes a swash plate 19 and a wobble finger 20.
  • the exemplary swash plate 19 includes a rolling bearing with an inner ring driven by the countershaft 11 and an outer ring connected to the wobble finger 20 .
  • the outer ring is rotatable relative to the inner ring about an axis inclined to the axis of rotation 12 , but inhibited by the applied to the percussion 6 tumble finger 20 against rotation about the axis of rotation 12 .
  • the driven inner ring forces the outer ring and the wobble finger 20 to a periodic pivotal movement in a plane E spanned by the axis of rotation 12 of the countershaft 11 and the working axis 3 about a pivot axis which passes through the axis of rotation 12 and perpendicular to the plane spanned E.
  • the pneumatic percussion 6 has an exciter piston 21 and a racket 22, both of which are guided in a guide tube 23 of the impact mechanism 6 coaxial with the working axis 3 .
  • the exciter piston 21 is connected to the wobble finger 20 .
  • the pivoting movement of the wobble finger 20 translates into a periodic linear movement of the excitation piston 21.
  • An air spring formed by a pneumatic chamber 24 between the excitation piston 21 and the racket 22 couples a movement of the racket 22 to the movement of the exciter piston 21 ( Fig. 8 ).
  • the racket 22 may strike directly on a rear end of the drill 4 or indirectly via a substantially resting intermediate racket 25 transmit a portion of its pulse to the drill 4 .
  • the impact rate of the hammer mechanism 6 is equal to the rotational speed of the countershaft. 11
  • the periodically striking mechanism 6 generates vibrations in the machine housing 9 , which the user perceives as vibrations of the handle 10 .
  • the vibrations lead to early fatigue of the user and can cause damage to health under excessive load.
  • the handle 10 may be connected to the vibration reduction via damping elements 26 to the machine housing 9 .
  • the damping elements 26 in particular reduce high-frequency components of the vibrations and convert them into heat.
  • the damping elements 26 are preferably made of open-cell polymer foams. The effectiveness of the damping elements 26 are limited.
  • the guiding of the power tool 1 requires a stable and rigid connection of the handle 10 to the machine housing 9, while for an ideal damping a loose and soft connection would be advantageous.
  • the exemplary hammer drill 1 has a damper 27 to reduce the vibration .
  • the damper 27 has a mass body 28 and a bending spring 29.
  • the mass body 28 is held only by the bending spring 29 and is preferably unguided otherwise.
  • the mass body 28 can move along the working axis 3 on a curved path, approximately a circular path, back and forth.
  • the curved path is preferably located in a plane spanned by the working axis 3 and the axis of rotation 12 of the countershaft 11 E (image plane of Fig. 2 ).
  • the absorber 27 has a rest position 30 (shown in FIG Fig. 2 ), in which the mass body 28 and the bending spring 29 return when no force is applied to the absorber 27 .
  • the mass body 28 can be deflected out of the rest position 30 on the curved path (cf. FIG. 3 and FIG. 4 ).
  • the bending spring 29 is elastically bent and exerts a force driving back into the rest position 30 on the mass body 28 .
  • the absorber 27 oscillates after a deflection 31 from the rest position 30 about the same with its natural frequency.
  • the natural frequency of the mass-spring system is determined by the rigidity of the spiral spring 29 and the mass of the mass body 28 .
  • the absorber 27 is tuned to the percussion 6 .
  • the natural frequency is approximately equal to the stroke rate of the striking mechanism 6 selected, for example, between 100% and 105% of the stroke rate.
  • inert mass body 28 dynamically counteracts the vibrations of the impact mechanism 6 , whereby the force acting on the handle 10 vibrations of the machine housing 9 are reduced.
  • the inertial mass body 28 begins to move due to its inertia by itself relative to the machine housing 9 , as soon as the impact mechanism. 6 is switched on and vibrations occur. Stimulated by the impact mechanism 6, the mass body 28 oscillates between two reversal points, which in 3 and 4 are shown.
  • the amplitude of the deflection 31 depends on the load of the hammer drill 1 .
  • the deflection is known for typical applications, eg when working with reinforced concrete, from test series.
  • the deflection 31 subsequently designates the angle of inclination of the bending spring 29 with respect to its rest position 30.
  • Fig. 2 shows the exemplary absorber 27 in its rest position 30.
  • the bending spring 29 is arranged in the rest position substantially perpendicular to the working axis 3 .
  • One end of the bending spring 29 is configured as the suspension 32 and fixed to the machine housing 9 .
  • the mass body 28 is attached to the distal end of the suspension 32 end 33 of the spiral spring 29 .
  • the distance of the distal end 33 to the suspension 32 is the largest dimension or length 34 of the bending spring 29.
  • a thickness 35 of the spiral spring 29, ie, its dimension along the working axis 3, is at least an order of magnitude smaller than the length 34.
  • the spiral spring 29 is elastically bendable along the working axis 3 .
  • the mass body 28 moves on the curved path around the suspension 32.
  • the length 34 of the spiral spring 29 provides the distance to the suspension 32 .
  • the curved path corresponds in good approximation to a circular arc with a radius equal to the length 34.
  • the bending spring 29 curves with increasing deflection, whereby the radius is shortened.
  • the spiral spring 29 is stiff in the third spatial direction.
  • the curved path runs in the plane defined by the working axis 3 and the axis of rotation 12 of the countershaft 11 plane E (image plane of Fig. 2 ).
  • the mass body 28 and the suspension 32 are arranged symmetrically to the plane E.
  • the absorber 27 is preferably arranged in a sufficiently large cavity in the machine housing 9 , so that the mass body 28 in typical vibrations, no element, except for the bending spring 29, in the machine housing 9 touches.
  • a cam 36 facilitates the settling of the damper 27, in particular when initially the striking mechanism 6 is still accelerated to the intended number of strokes.
  • the cam disc 36 deflects the absorber 27 in a direction of start 37 on one side of its rest position 30 ; the arranged for example in the direction of impact 7 in front of the absorber 27 cam 36 deflects the absorber 27 on the side facing away in the direction of impact 7 of the rest position 30 from.
  • the cam 36 does not touch the damper 27 when the damper 27 swings to the other side of the rest position 30 ( Fig. 4 ).
  • the typical deflection 30 of the damper 27 in the steady state and in an active hammer mechanism 6 is greater than the possible of the cam 36 possible forced deflection 38 of the damper 27.
  • the damper 27 vibrates freely according to its natural frequency, ie alone given by the inertia of the mass body 28 and stiffness of the spiral spring 29th
  • the cam plate 36 is disposed on the countershaft 11 adjacent to the bending spring 29 .
  • the cam 36 may be integrated in the drive sprocket 13, integrated in the swash plate 19 , or formed as a discrete disk.
  • the countershaft 11 drives the cam plate 36 at the same speed as the swash plate 19 , whereby the wobble of the swash plate 19 and the rotation cam 36 have a constant angular displacement.
  • the cam plate 36 can be coupled or decoupled from the countershaft 11 together with the swash plate 19 in order to activate or deactivate the impact mechanism 6 .
  • the cam disc 36 has a single cam 39, which projects in a direction parallel to the working axis 3 starting direction 37 to the bending spring 29 out.
  • the exemplary cam 39 has a vertex 40, a flank 42 rising in the circumferential direction 41 as far as the apex 40, and a flank 43 descending to the apex 40 (FIG. Fig. 6 ).
  • the helical flanks 42, 43 rise in the starting direction 37 or fall off in the starting direction 37 .
  • the flanks 42 can increase linearly with the angle of rotation about the axis of rotation 12 .
  • a center angle 44 of the rising flank 42 is for example in the range between 45 degrees and 90 degrees.
  • the falling edge 43 is preferably formed symmetrically to the rising edge 42 .
  • the entire cam 39 covers a maximum of a central angle of 180 degrees.
  • the exemplary cam disk 36 has a recess 45.
  • the cam disk 36 can touch the bending spring 29 with only one cam 39 .
  • the cam 39 passes over a coaxial to the rotational axis 12 , annular rotational volume.
  • the spiral spring 29 has a to the cam 36. against the start-up direction 37 extending projection 46 to which the cam can strike. 39
  • the projection 46 protrudes, when the bending spring 29 is in the rest position, into the rotational volume swept by the cam 39 .
  • the projection 46 may be formed the same as the cam 39 .
  • the exemplary projection 46 has a vertex 47 projecting toward the cam 36 .
  • the projection 46 has a flank 48 rising in the sense of rotation to the apex 47 and a flank 49 descending to the apex 47.
  • a center angle 50 of the rising flank 48 is, for example, in the range between 45 degrees and 90 degrees.
  • Of the Vertex 47 is preferably in the plane E and between the mass body 28 and the countershaft 11th
  • Fig. 7 illustrates the abutment of the damper 27 by the cam 36.
  • the ordinate shows the position of the cam 36 and the bending spring 29 along the working axis 3 in the plane E.
  • the position is plotted against the cyclic angular position 51 of the countershaft 11 .
  • the angular position 51 at 0 degrees lies in plane E and faces the mass body 28.
  • the movement of the damper 27 is represented by the projection 46 or its vertex 47 .
  • the movement of the damper 27 is shown for the following explanations without excitation by vibrations, with which typically sets a greater deflection.
  • the dashed line indicates the position of the apex 47 in the rest position 30 .
  • the cam 36 rotates driven by the countershaft 11 about the rotation axis 12.
  • the cam 39 approaches the projection 46 of the spiral spring 29.
  • the cam 39 exceeds in the direction of start 37 with the rising edge 42, the rest position 30 of the projection 46.
  • the cam exceeds 39, the rest position 30 at an angular position 52 of -45 degrees.
  • the angular position 52 is given by the axial distance of the cam plate 36 30 to the rest position, unless the damper 27 unmoved, and thus the projection 46 is in the rest position 30, the cam 39 begins to deflect in the start-up direction 37, 27 and to tension the vibration absorber.
  • the deflection 38 forced by the cam 39 is maximum when the apex 40 of the cam 39 has an angular position 53 which is aligned identically with the apex 47 of the projection 46 .
  • the equi-aligned peaks 40, 47 are both at 0 degrees.
  • the two vertices 40, 47 lie in the plane E with the mass body 28 and the vibration plane of the damper 27.
  • the maximum forced deflection 38 is in the range between 1 degree and 5 degrees.
  • the cam 39 moves away with the falling edge 43 of the projection 46.
  • the cam 39 no longer exerts force in the direction of start 37 on the bending spring 29 from.
  • the spiral spring 29 relaxes and accelerates the mass body 28 against the starting direction 37 in the direction of the rest position 30.
  • the projection 46 moves with increasing speed against the starting direction 37.
  • the rate of increase of the falling edge 48 at the speed of the countershaft 11 is greater than that Speed of the projection 46 is selected.
  • 36 opens a gap between the spiral spring 29 and the cam plate.
  • the movement of the damper 27 is now solely by the inertia of the mass body 28 and the Stiffness of the bending spring 29 predetermined.
  • the free movement lasts at least 75% of one revolution of the countershaft 11 (270 degrees).
  • the absorber 27 oscillates on the rest position 30 and reaches its greatest deflection 31 counter to the starting direction 37 when the cam 39 is at about 180 degrees.
  • the cam 39 is again in the plane E, but on the suspension 32 of the spiral spring 29 facing side of the countershaft 11.
  • the cam 39 and the projection 46 are relative to the axis of rotation 12 diametrically.
  • the cam 39 is preferably arranged along the axis of rotation 12 a recess 54 of the spiral spring 29 against the projection 46 is preferably along the axis of rotation 12, the recess 45 of the cam plate 36 against.
  • the cam 36 and the bending spring 29 do not touch each other in the diametrical angular position 55 , regardless of the amplitude of the deflection 31 of the spiral spring 29.
  • Die in Fig. 7 shown amplitude 38 includes only the excitation by the cam disc 36, in the chiseling rotary hammer 1 , the deflection 38 in the typical applications by at least 20% greater.
  • the maximum forced deflection 38 of the damper 27 is preferably carried out simultaneously with the maximum compression of the pneumatic chamber 24.
  • the countershaft 11 drives synchronously the wobble finger 20, thus indirectly the striking mechanism 6, and also the cam 36 at.
  • the wobble finger 20 periodically reaches its tool-remote dead center 56 at an angular position 57, for example at 255 degrees (-105 degrees).
  • the wobble finger 20 moves and the excitation piston 21 subsequently in the direction of impact 7.
  • the pneumatic chamber 24 of the striking mechanism 6 is compressed.
  • the maximum compression is achieved between 95 degrees and 115 degrees after dead center 56 .
  • the fixed angular offset of the wobble drive 14 to the cam 36 is selected so that the rectified angular position 53 of the cam 39 to the projection 46 between 95 degrees and 115 degrees to the tool away from the dead center 56 of the wobble drive 14 .
  • the angular offset shifts by 180 degrees when the cam plate 36 is arranged on the tool side of the bending spring 29 .
  • the already oscillating absorber 27 should be disturbed as little as possible by the cam 39 .
  • the projection 46 is designed to leave the area swept by the cam 39 quickly.
  • the apex 47 lies on a side facing away from the suspension 32 of the countershaft 11. The distance of the apex 47 to the suspension 32 is between 30% and 50% of the length 34 of the spiral spring 29th
  • the spiral spring 29 may be stiffened perpendicular to the plane.
  • the width 58 of the spiral spring 29 is preferably greater than its thickness 35 and less than its length 34.
  • the exemplary bending spring 29 is formed as a plate-shaped leaf spring ( Fig. 5 ).
  • the bending spring 29 surrounds the countershaft 11.
  • the suspension 32 of the spiral spring 29 and the distal end 33 with the mass body 28 are on diametrically opposite sides of the countershaft 11.
  • the spiral spring 29 has, for example, a recess 59 through which the countershaft 11 is guided.
  • the bending spring 29 may have a further recess 54 through which the impact mechanism 6 arranged parallel to the countershaft 11 is guided.
  • the recesses 54, 59 are sufficiently dimensioned so that the bending spring 29 does not abut against the countershaft 11 and the percussion mechanism 6 when it is deflected by the mass body 28 .
  • the bending spring 29 is for example made of spring steel or a fiber composite.

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

Claims (11)

  1. Machine-outil manuelle comportant :
    un porte-outil (2) pour maintenir un outil (4) sur un axe de travail (3),
    un moteur (5),
    un mécanisme de percussion pneumatique (6) pour appliquer des percussions à l'outil (4),
    un amortisseur (27) constitué d'un corps massif (28),
    un arbre de renvoi (11) entraîné par le moteur (5) autour d'un axe de rotation (12) parallèle à l'axe de travail (3),
    un entraînement oscillant (14) agencé sur l'arbre de renvoi (11) pour entraîner le mécanisme de percussion pneumatique (6),
    caractérisée en ce que l'amortisseur (27) est en outre constitué d'un ressort de flexion (29) agencé transversalement à l'axe de travail (3), et en ce que la machine-outil manuelle est munie d'un disque à came (36) agencé sur l'arbre de renvoi (11) avec une came (39) faisant saillie dans une direction de démarrage (37) parallèle à l'axe de travail (3), et d'une pièce complémentaire (46) de la came (39) prévue sur le ressort de flexion (29),
    dans laquelle la came (39) en contact avec la pièce complémentaire (46) précontraint le ressort de flexion (29) dans la direction de démarrage (37).
  2. Machine-outil manuelle (1) selon la revendication 1, caractérisée en ce que le disque à came (36) est sans contact par rapport au ressort de flexion (29) lorsque la came (39) et la pièce complémentaire (46) sont dans une position angulaire diamétralement opposée (55) par rapport à l'axe de rotation (12).
  3. Machine-outil manuelle (1) selon la revendication 1 ou 2, caractérisée en ce que le disque à came (36) est sans contact par rapport au ressort de flexion (29) pour au moins 75 % d'une rotation autour de l'axe de rotation (12).
  4. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que le corps massif (28) est guidé par le ressort de flexion (29) sur une trajectoire courbe.
  5. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que le ressort de flexion (29) est fixé sur le boîtier de machine (9) par une première extrémité (32) et est fixé sur une seconde extrémité (33) du corps massif, dans laquelle la première extrémité (32) et la seconde extrémité (33) sont agencées diamétralement opposées à l'arbre de renvoi (11) .
  6. Machine-outil manuelle (1) selon la revendication 5, caractérisée en ce que la pièce complémentaire (46) de la came (39) se situe à une distance de la première extrémité (32) qui correspond à entre 30 % et 50 % de la distance (34) entre la première extrémité (32) et la seconde extrémité (33).
  7. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce qu'une déviation forcée maximale (38) du ressort de flexion (29) à partir d'une position de repos (30) de la came (39) venant en butée contre la pièce complémentaire (46) est comprise entre 1 degré et 5 degrés.
  8. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que la came (39) comporte un flanc hélicoïdal (42) dirigé vers le ressort de flexion (29), qui est ascendant dans la direction de démarrage (37) sur un angle central (44) compris entre 30 degrés et 90 degrés.
  9. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que la pièce complémentaire (46) comporte un flanc hélicoïdal (48) dirigé vers la came (39), qui est ascendant à l'encontre de la direction de démarrage (37) sur un angle central (50) compris entre 30 degrés et 90 degrés.
  10. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce qu'une chambre pneumatique (24) du mécanisme de percussion (6) est comprimée au maximum dans une position angulaire (54) de l'arbre de renvoi (11) et dans laquelle la came (39) est dans la position angulaire (53) de l'arbre de renvoi (11) et, dans un agencement de la came (39) sur un côté du ressort de flexion (29) opposé à l'outil (4), est dans la même position angulaire (53) par rapport à l'axe de rotation (12) que la pièce complémentaire (46), ou dans laquelle la came (39) est dans la position angulaire (53) et, dans un agencement de la came (39) sur un côté du ressort de flexion (29) dirigé vers l'outil (4), est diamétralement opposée à la pièce complémentaire (46) par rapport à l'axe de rotation (12).
  11. Machine-outil manuelle (1) selon l'une des revendications précédentes, caractérisée en ce que l'entraînement oscillant (14) est à un point mort (56) opposé à l'outil (4) dans une première position angulaire (57) de l'arbre de renvoi (11), et la came (39) est dans une position angulaire de déviation maximale du ressort de flexion (29) dans une seconde position angulaire (53), et dans laquelle, dans un agencement de la came (39) sur le côté du ressort de flexion (29) opposé à l'outil (4), la seconde position angulaire (53) suit la première position angulaire (57) entre 95 degrés et 115 degrés, et dans laquelle, dans l'agencement de la came (39) sur le côté du ressort de flexion (29) dirigé vers l'outil (4), la première position angulaire (57) suit la seconde position angulaire (53) entre 65 degrés et 85 degrés.
EP15802103.0A 2014-12-03 2015-12-01 Machine-outil à main Active EP3227056B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14196018.7A EP3028818A1 (fr) 2014-12-03 2014-12-03 Machine-outil portative
PCT/EP2015/078122 WO2016087399A1 (fr) 2014-12-03 2015-12-01 Machine-outil à main

Publications (2)

Publication Number Publication Date
EP3227056A1 EP3227056A1 (fr) 2017-10-11
EP3227056B1 true EP3227056B1 (fr) 2018-08-15

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EP14196018.7A Withdrawn EP3028818A1 (fr) 2014-12-03 2014-12-03 Machine-outil portative
EP15802103.0A Active EP3227056B1 (fr) 2014-12-03 2015-12-01 Machine-outil à main

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Application Number Title Priority Date Filing Date
EP14196018.7A Withdrawn EP3028818A1 (fr) 2014-12-03 2014-12-03 Machine-outil portative

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US (1) US10414035B2 (fr)
EP (2) EP3028818A1 (fr)
CN (1) CN107000181B (fr)
WO (1) WO2016087399A1 (fr)

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Also Published As

Publication number Publication date
CN107000181A (zh) 2017-08-01
US10414035B2 (en) 2019-09-17
CN107000181B (zh) 2019-07-12
WO2016087399A1 (fr) 2016-06-09
EP3028818A1 (fr) 2016-06-08
US20170355070A1 (en) 2017-12-14
EP3227056A1 (fr) 2017-10-11

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