EP2803447B1 - Dispositif d'outil manuel - Google Patents

Dispositif d'outil manuel Download PDF

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Publication number
EP2803447B1
EP2803447B1 EP14161634.2A EP14161634A EP2803447B1 EP 2803447 B1 EP2803447 B1 EP 2803447B1 EP 14161634 A EP14161634 A EP 14161634A EP 2803447 B1 EP2803447 B1 EP 2803447B1
Authority
EP
European Patent Office
Prior art keywords
impact
spindle
hammer
tool
hand tool
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
EP14161634.2A
Other languages
German (de)
English (en)
Other versions
EP2803447A1 (fr
Inventor
Tobias Herr
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 EP2803447A1 publication Critical patent/EP2803447A1/fr
Application granted granted Critical
Publication of EP2803447B1 publication Critical patent/EP2803447B1/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
    • B25D11/10—Means for driving the impulse member comprising a cam mechanism
    • B25D11/102—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool
    • B25D11/104—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool with rollers or balls as cam 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
    • 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
    • B25D11/02—Portable percussive tools with electromotor or other motor drive in which the tool is connected to an impulse member
    • 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
    • B25D16/003—Clutches specially adapted therefor
    • 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
    • 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
    • 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
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • 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
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0038—Tools having a rotation-only mode
    • 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
    • B25D2250/165—Overload clutches, torque limiters
    • 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

Definitions

  • a hand tool device with a tool spindle and a percussion mechanism that has a percussion and at least one cam guide that drives the percussion at least during percussion drilling has already been proposed.
  • EP 2 612 731 A1 discloses a hand tool device with a tool spindle, an impact mechanism and a planetary gear, which has at least a first planetary gear stage that drives the impact mechanism and a second planetary gear stage that drives at least one tool spindle.
  • U.S. 2 160 150 A describes an impact driver having an anvil and a hammer to strike the anvil, a clutch member on the hammer and the anvil, a spring to hold the clutch member in engagement with a drive unit of the hammer, and a link member to to keep the hammer and the drive unit connected.
  • the invention is based on a hand tool device with a tool spindle and a hammer mechanism which has a hammer and at least one cam guide which drives the hammer at least during percussion drilling operation.
  • the hand tool device according to the invention comprises the features of claim 1.
  • the tool spindle has at least one bearing surface which supports the hammer so that it can move in at least one operating state.
  • a “tool spindle” is to be understood in particular as a shaft which transmits a rotational movement from a transmission of the hand tool device to an insert tool attachment of the hand tool device.
  • the bearing surface provides a radially oriented bearing force on the racquet.
  • the hammer is preferably moved essentially in a translatory manner in the impact direction during the hammer drilling operation, while the tool spindle is driven in rotation during the hammer drilling operation.
  • the tool spindle is preferably designed as a solid shaft. Alternatively, the tool spindle could be designed as a hollow shaft.
  • a "percussion mechanism” is to be understood in particular as a device which is intended to generate an impact impulse and in particular to emit it in the direction of an application tool.
  • the percussion mechanism advantageously transfers the percussion pulse via the tool spindle and/or in particular, at least during percussion drilling operation the insert tool attachment of the hand tool device to the insert tool.
  • the percussion mechanism is preferably provided to convert a rotational movement into an in particular translational percussion movement.
  • the percussion mechanism is not designed as a notched percussion mechanism. “Provided” should be understood to mean, in particular, specially programmed, designed and/or equipped.
  • the term "beater” should be understood to mean a means that is accelerated at least essentially in a translatory manner, at least during percussion drilling operation, and emits an impulse picked up during the acceleration as an impact impulse in the direction of the insert tool.
  • the racquet is preferably designed in one piece. Alternatively, the racquet could be constructed in several pieces.
  • a "curve guide” is to be understood as a device that translates rotational energy for generating an impact into linear kinetic energy of the impactor, at least by means of a specially shaped guide surface along which a connecting means runs, at least during percussion drilling.
  • the hammer mechanism preferably has a hammer mechanism spring, which stores the linear kinetic energy of the hammer to generate an impact.
  • the specially shaped surface is a surface that delimits a guide curve of the curve guide.
  • the cam guide is preferably provided to move the hammer once to make an impact during one revolution of a hammer mechanism spindle of the hand tool device.
  • the cam guide could be provided to move the hammer to at least two or advantageously three hammers during one revolution of the hammer mechanism spindle.
  • a percussion gear stage could be dispensed with.
  • the cam guide applies a force to the racquet directed away from the bit attachment.
  • a “connecting means” is to be understood in particular as meaning a means that creates a mechanical coupling between at least one part of the impact mechanism that rotates during percussion drilling operation, in particular a percussion mechanism spindle, and the in particular linearly moving hammer.
  • the connecting means is spherical.
  • the connecting means could have a different form that appears sensible to a person skilled in the art.
  • the connecting means preferably has a diameter greater than 4 mm, advantageously greater than 5 mm, particularly advantageously greater than 6 mm.
  • the connecting means preferably has a diameter of less than 14 mm, advantageously less than 10 mm, particularly advantageously less than 8 mm.
  • a “percussion operation” is to be understood in particular as an operation of the hand tool device in which the insert tool rotates and during machining of a workpiece is driven percussively.
  • a “bearing surface” should be understood to mean a surface which, during operation, exerts a bearing force on the racquet perpendicular to the surface and allows the racquet to move parallel to the surface.
  • the bearing surface is provided for the hammer to slide on the surface during hammer drilling operation.
  • the surface preferably has a low level of roughness.
  • the bearing surface is preferably aligned completely parallel to a direction of impact of the racket.
  • the bearing surface is advantageously designed in the shape of a cylinder jacket.
  • the bearing surface preferably touches the racquet in at least one operating state. Due to the configuration of the hand tool device according to the invention, a particularly low-friction and low-wear mounting of the bat can be achieved.
  • the hammer at least essentially encloses the tool spindle on at least one level, as a result of which a large hammer mass can be achieved with a small overall size.
  • the expression "at least substantially encloses on at least one plane” is to be understood as meaning that rays emanating from an axis of the tool spindle, which are arranged on the plane, intersect the hammer over an angular range of at least 180 degrees, advantageously at least 270 degrees .
  • the bat encloses the striking mechanism spindle by 360 degrees, which is particularly advantageous.
  • the plane is preferably aligned perpendicularly to an axis of rotation of the tool spindle.
  • the hammer mechanism has an hammer mechanism spindle with a bearing surface which supports the hammer movably in at least one operating state, as a result of which a small overall size is possible.
  • a "percussion mechanism spindle” is to be understood in particular as a shaft which transmits a rotational movement directly to the cam guide.
  • the percussion mechanism spindle transmits the rotational movement separately from a rotational movement driving the attachment tool attachment to the cam guide.
  • the percussion mechanism spindle is designed separately from the tool spindle.
  • the percussion mechanism spindle is preferably designed as a hollow shaft.
  • the hammer at least essentially encloses the hammer mechanism spindle on at least one level, as a result of which a large hammer mass can be achieved with a small overall size.
  • an "interior” should be understood to mean a space which is arranged on a straight line between at least two points where the straight line intersects the racquet.
  • the racket preferably completely encloses the interior space on at least one level.
  • a "direction of impact” is to be understood in particular as a direction which runs parallel to an axis of rotation of the tool chuck and which is directed from the beater in the direction of the tool chuck.
  • the phrase “limiting inwardly narrowing” should be understood to mean that a diameter of the interior space decreases perpendicular to the direction of impact in the direction of impact.
  • the racquet has an at least substantially U-shaped cut surface parallel to the direction of impact.
  • the tool spindle has at least one striking surface on which the hammer strikes in an axial striking direction at least during percussion drilling operation, as a result of which a particularly simple construction can be achieved.
  • a "impact surface” is to be understood in particular as a surface of the tool spindle through which the hammer transmits the impact impulse to the tool spindle in at least one operating state.
  • the hammer preferably hits the tool spindle directly. Alternatively, the hammer could hit the tool spindle via a die.
  • the racquet has at least part of the curved guide, as a result of which a particularly small, light and yet powerful hammer mechanism can be provided.
  • the expression that "the racquet has at least part of the curve guide” should be understood in particular to mean that the racquet has a surface to which a connecting means of the curve guide directly transmits the energy for generating the striking movement.
  • the part of the curve guide which the racquet has is formed as a surface which fixes the connecting means in place relative to the racquet.
  • the part of the curved guide that the racquet has comprises a fastening recess delimited by the surface, which fastens the connecting means in a stationary manner relative to the racquet.
  • the racket is provided to attach a connecting means that during operation the part the curve guide and another part of the curve guide, in particular the guide curve, connects.
  • the connecting means and the racquet are connected in an unsprung manner. This means in particular that no spring is arranged between the connecting means and the racquet in terms of effect.
  • the connecting means could be formed at least partially in one piece with the racquet.
  • the part of the curve guide that the racquet has could be designed as a guide curve. “Stationary” is to be understood in particular as meaning that an axis of symmetry and/or a center point of the connecting means is at least essentially stationary relative to the racquet during a striking operation.
  • the hammer mechanism has at least one hammer mechanism spring, which stores at least part of an impact energy in at least one operating state, as a result of which an efficient hammer mechanism can be provided in a structurally simple manner.
  • a "hammer mechanism spring” is to be understood in particular as a spring which, in at least one operating state, causes a force in the direction of impact on the hammer.
  • impact energy should be understood to mean energy that accelerates the racquet in the direction of impact before it is struck.
  • “store” is to be understood in particular as meaning that the impact mechanism spring absorbs the impact energy at a point in time and delivers it to the striker at a later point in time, in particular by accelerating the striker.
  • the curve guide preferably tensions the hammer mechanism spring.
  • the hammer mechanism spring fastens the hammer in the circumferential direction in at least one operating state, as a result of which a particularly cost-effective, lightweight and space-saving design can be achieved.
  • a separate attachment of the racket can be dispensed with.
  • the phrase "fixed in the circumferential direction" should be understood to mean that the hammer mechanism spring causes a force on the hammer in at least one operating state, which counteracts a force acting on the hammer in the circumferential direction, which in particular causes the curve guidance.
  • the attachment of the hammer by the hammer mechanism spring preferably prevents the hammer from moving more than 360 degrees about a rotational axis of the hammer mechanism spindle, advantageously a movement by more than 180 degrees, particularly advantageously a movement by more than 90 degrees.
  • a "force acting in the circumferential direction” is to be understood in particular as a force which has at least one component which is aligned perpendicularly to an axis of rotation of an impact mechanism spindle of the impact mechanism and causes a torque relative to the circumferential direction of the impact mechanism spindle.
  • FIG. 1 shows a hand tool 10.
  • the hand tool 10 is designed as a percussion drill.
  • the hand tool 10 has a hand tool device 12 according to the invention, a hand tool housing 14 and a battery interface 16 .
  • the battery interface 16 is intended to supply the hand tool device 12 with electrical energy from a hand tool battery not shown in detail here.
  • the hand tool housing 14 is essentially pistol-shaped. It includes a handle 18, by means of which an operator holds the hand tool 10 during a work process.
  • the hand tool device 12 comprises a tool guide unit 20, an impact mechanism 22, an impact shut-off device 24, a gear 26, an impact mechanism gear 28, a drive unit 30, an operating device 32, a torque limiting unit 34 and a spindle blocking device 36.
  • the drive unit 30 is designed as an electric motor.
  • the gear 26 is provided to a speed of the drive unit 30 to to reduce.
  • the transmission 26 is provided to provide at least two different translations.
  • a gripping surface of the handle 18 is formed essentially perpendicularly to an axis of rotation of the tool guide unit 20 .
  • the hand tool housing 14 has an overhang on a side facing away from the tool guide unit 20 relative to the handle 18 .
  • a basic shape of the hand tool housing 14 is therefore T-shaped.
  • the tool guide unit 20 includes an insert tool attachment 38 and a tool spindle 40.
  • the insert tool attachment 38 and the tool spindle 40 are screwed together.
  • the insertion tool attachment 38 and the tool spindle 40 could be releasably connected without tools in a way that appears sensible to a person skilled in the art.
  • the insert tool attachment 38 attaches an insert tool (not shown here), for example a drill or a screw bit.
  • the application tool fastening 38 fastens the application tool in a non-positive manner.
  • an application tool attachment could attach the application tool in a form-fitting manner, for example with an SDS tool chuck or a hexagonal holder.
  • the insert tool attachment 38 has three clamping jaws which are movably attached by an operator and which attach the insert tool during a work process.
  • the insert tool attachment 38 fastens the insert tool in an axially immovable manner in relation to the insert tool attachment 38 and in particular in relation to the tool spindle 40.
  • a part of the insert tool attachment 38 and the tool spindle 40 are connected to one another in an immovable manner relative to one another.
  • the insertion tool attachment 38 and the tool spindle 40 are screwed together.
  • the hand tool device 12 has a bearing means 42 which supports the tool spindle 40 on a side facing the insertion tool attachment 38 .
  • the bearing means 42 supports the tool spindle 40 in an axially displaceable manner.
  • the bearing means 42 is axially firmly connected to the tool spindle 40 .
  • the bearing means 42 is mounted in the hand tool housing 14 so that it can move axially.
  • the hand tool device 12 has a further bearing means 44 which bears the tool spindle 40 on a side facing the gear 26 .
  • the bearing means 44 is designed as a slide bearing.
  • the bearing means 44 supports the tool spindle 40 in an axially displaceable manner.
  • the tool spindle 40 includes an impact surface 46 on which impact mechanism 22 impacts in a percussion drilling operation shown.
  • the hand tool housing 14 is designed in several parts.
  • the hand tool housing 14 comprises a two-shell handle and drive housing 48, a two-shell outer housing 50, a gear housing 52, an impact mechanism gear housing 54 and an impact mechanism housing 56. These parts of the hand tool housing 14 are manufactured separately from one another.
  • the handle and drive housing 48 forms the handle 18 and encloses the drive unit 30.
  • the outer housing 50 encloses the gear housing 52 and the impact mechanism gear housing 54.
  • the outer housing 50 fastens the gear housing 52, the impact mechanism gear housing 54 and the impact mechanism housing 56 to the handle and Drive housing 48.
  • Gear housing 52 encloses gear 26. It is tubular.
  • Impact mechanism gear housing 54 encloses impact mechanism gear 28.
  • Impact mechanism housing 56 encloses impact mechanism 22. It is also tubular.
  • the percussion mechanism 22 can be switched into an activated and a deactivated operating state.
  • the striking mechanism 22 has a striking mechanism 58 , a striking mechanism spindle 60 , a striking mechanism spring 62 and a striking mechanism drive device 64 .
  • Impact mechanism spindle 60 encloses bearing means 44 which mounts tool spindle 40 on a side facing gear 26 .
  • the bearing means 44 is functionally arranged between the tool spindle 40 and the percussion mechanism spindle 60 .
  • the beater 58 is mounted so that it can move in a translational manner in a direction of impact 66 .
  • Impact direction 66 is aligned parallel to an axial direction of impact mechanism spindle 60 .
  • the tool spindle 40 and the hammer mechanism spindle 60 each have a bearing surface 68, 70 on which the hammer 58 is movably mounted.
  • the bearing surfaces 68, 70 act directly on the hammer 58.
  • the bearing surfaces 68, 70 are lateral surfaces of the tool spindle 40 or the hammer mechanism spindle 60.
  • the hammer 58 could only be on the tool spindle 40 or on the hammer mechanism spindle 60 and possibly on an outside of the Racquet 58 be stored.
  • An inner side of the bat 58 delimits an interior space that narrows inward in the direction of impact 66 .
  • the Bearing surface 68 of the tool spindle 40 acts on a narrowed area of the inside of the hammer 58.
  • the bearing surface 70 of the hammer mechanism spindle 60 acts on an unnarrowed area of the inside of the hammer 58 facing the gear 26.
  • the hammer 58 has a pot-shaped basic shape, with the bottom A recess is arranged in the pot-shaped basic shape, through which the tool spindle 40 runs. During operation, hammer 58 strikes tool spindle 40 with a bottom outside of the pot-shaped basic shape.
  • a hammer mechanism could have a hammer and an hammer mechanism spindle, with the hammer mechanism spindle enclosing the hammer.
  • a curved guide of the hammer mechanism would be arranged on an outside of the racquet.
  • either the hammer or the percussion mechanism spindle could have a guide curve of the curve guide. Due to a larger radius of the curve guide, it would be advantageous in this case if the curve guide were intended to move the racquet several times to make a hit during one revolution.
  • Figures 3 and 4 show the impact mechanism spindle 60 in two different side views by 180 degrees.
  • figure 5 shows a sectional area A of the racquet drive device 64.
  • the racquet drive device 64 has exactly one cam guide 72.
  • the curve guide 72 comprises a guide curve 76, a connecting means 78 and a fastening means 80.
  • the curve guide 72 is arranged on the percussion mechanism spindle 60.
  • at least one curved guide could be arranged on a racquet.
  • the fastener 80 is arranged on the racquet 58 .
  • the beater 58 thus has part of the curved guide 72 .
  • at least one fastening means could be arranged on an impact mechanism spindle.
  • Fastening means 80 is designed as a fastening recess for connecting means 78 .
  • the fastener 80 is arranged on an inside of the racquet 58 .
  • the fastening means 80 is introduced into the inside of the hammer 58 by means of a bore through a side of the hammer 58 facing away from the fastening means.
  • the connecting means 78 is designed as a sphere.
  • the connecting means 78 has a diameter of 7 mm.
  • the fastener 80 supports the connecting means 78 in a stationary manner relative to the racquet 58 .
  • the connecting means 78 slides in the guide curve 76 during percussion drilling operation
  • Impact mechanism spindle 60 delimits a space in which the connecting means 78 moves during the impact drilling operation.
  • Impact mechanism spindle 60 is designed as a hollow shaft. Impact mechanism spindle 60 is rotatably mounted in hand tool housing 14 on a side facing away from insertion tool attachment 38 . Impact mechanism gear 28 drives impact mechanism spindle 60 .
  • the percussion mechanism spindle 60 has teeth 82 on a side facing away from the insertion tool attachment 38 .
  • the guide curve 76 has an impact free running area 84 , an impact winding area 86 and a mounting recess 88 .
  • the fastener 78 is inserted through the assembly recess 88 into the fastener 80 of the racquet 58 .
  • the hammer mechanism spindle 60 rotates clockwise when viewed in the direction of impact 66 during the hammer drill operation.
  • the impact elevator area 86 is formed in a spiral shape. It extends approximately 180 degrees around an axis of rotation 90 of the hammer mechanism spindle 60. The hammer elevator area 86 moves the connecting means 78 and thus the hammer 58 during the hammer drilling operation against the direction of impact 66.
  • the impact freewheel area 84 connects two ends 92, 94 of the impact winding area 86.
  • the impact freewheel area 84 extends approximately 180 degrees around the axis of rotation 90 of the impact mechanism spindle 60.
  • the impact freewheel area 84 has an impact flank 96 which, from the end 92 of the gear 26 facing the Impact elevator area 86 starting, runs approximately parallel to the impact direction 66.
  • the connecting means 78 After the connecting means 78 has penetrated the impact-free running area 84, the impact mechanism spring 62 accelerates the hammer 58 and the connecting means 78 in the direction of impact 66.
  • the connecting means 78 moves through the impact-free running area 84 without experiencing an axial force until the hammer 58 hits the Face 46 hits.
  • the impact mechanism spring 62 stores at least part of an impact energy that the impactor 58 transmits to the tool spindle 40 in the event of an impact.
  • FIGS. 6 and 7 show the hammer 58.
  • the hammer mechanism spring 62 accelerates the hammer 58 in the direction of impact 66 before an impact.
  • the hammer mechanism spring 62 presses directly against the hammer 58 .
  • the percussion spring 62 encloses part of the hammer 58.
  • the hammer mechanism spring 62 secures the hammer 58 in the circumferential direction during the hammer drilling operation.
  • the hammer 58 has a catch means 102 on which the hammer mechanism spring 62 acts in the circumferential direction when the insert tool attachment 38 rotates clockwise during percussion drilling operation.
  • the impact mechanism spindle 60 also rotates clockwise in this exemplary embodiment, viewed in the direction of impact 66 . It is obvious to a person skilled in the art to adapt the catch means 102 to a percussion mechanism spindle 60 rotating counterclockwise in the opposite direction to the right.
  • the catch means 102 has a latching surface 104 which is aligned at least essentially perpendicular to the surface 100 of the projection 98 on which the percussion mechanism spring 62 presses to accelerate the striker 58 .
  • the surface 100 on which the impact mechanism spring 62 presses to accelerate the impactor 58 is ramp-shaped and inclined relative to the impact direction 66 .
  • the hammer 58 and the hammer mechanism spring 62 therefore have a freewheel relative to one another in the circumferential direction when the insert tool attachment 38 rotates counter-clockwise.
  • the hammer mechanism spring 62 could always be connected in a torque-proof manner to the hammer 58 and the hammer mechanism spring 62 could have a freewheel relative to the hand tool housing 14 when rotating to the left.
  • the surface 106 is interrupted by a latching surface 107 which is oriented substantially perpendicular to the surface 106 of the component.
  • the latching surface 107 is intended to cause a force in the circumferential direction on the hammer mechanism spring 62 when the insert tool attachment 38 rotates to the right, which counteracts a movement of the hammer 58 .
  • the locking surface 107 thus connects the hand tool housing 14 and the hammer mechanism spring 62 in a form-fitting manner in the circumferential direction when the insert tool attachment 38 rotates to the right.
  • the striking mechanism spring 62 could dem on a Racquet 58 may be non-rotatably connected to the hand tool housing 14 on the side facing away, for example by one end of a wire forming the impact mechanism spring 62 being bent protruding in the direction of the drive unit 30 .
  • another component that appears useful to a person skilled in the art could have the latching surface 107, for example a housing part of the hand tool housing 14.
  • the hammer 58 has a ventilation opening 108 through which air can escape from a space delimited by the tool spindle 40, the hammer mechanism spindle 60 and the hammer 58 and/or can flow into the space when the hammer 58 moves.
  • Impact mechanism gear 28 is arranged between gear 26 and impact mechanism 22 .
  • Impact mechanism gear 28 has a first planetary gear stage 110 .
  • the transmission 26 has a second planetary gear stage 112 , a third planetary gear stage 114 and a fourth planetary gear stage 116 .
  • figure 9 shows a sectional area B of the first planetary gear stage 110.
  • the first planetary gear stage 110 increases a first rotational speed of the second planetary gear stage 112 to drive the impact mechanism 22.
  • the second planetary gear stage 114 drives the tool spindle 40 at this first rotational speed.
  • the toothing 82 of the impact mechanism spindle 60 forms a sun wheel of the first planetary gear stage 110.
  • the toothing 82 meshes with planet wheels 118 of the first planetary gear stage 110, which are guided by a planet carrier 120 of the first planetary gear stage 110.
  • Ring gear 122 of first planetary gear stage 110 meshes with planet gears 118 of first planetary gear stage 110.
  • Ring gear 122 is connected to hand tool housing 14 in a torque-proof manner.
  • the impact shut-off device 24 is provided to switch off the impact mechanism 22 during a screwing operation, during a drilling operation and in the impact drilling mode when the insert tool is unloaded.
  • Impact shut-off device 24 has three transmission means 128 , a control element 130 and an impact shut-off clutch 132 .
  • figure 10 shows an isolated side view of the impact shut-off device 24.
  • figure 11 shows a section C through the control element 130 of the impact shut-off device 24.
  • the figure 11 a connecting means 124 which non-rotatably connects the tool spindle 40 and a planet carrier 126 of the second planetary gear stage 112 .
  • the connecting means 124 connects the tool spindle 40 and the planet carrier 126 of the second planetary gear stage 112 in an axially displaceable manner.
  • the impact cut-off clutch 132 is arranged between the first planetary gear stage 110 and the second planetary gear stage 112 .
  • Impact shut-off clutch 132 has a first clutch element 134 which is always rotationally coupled to part of impact mechanism 22 .
  • the first clutch element 134 is non-rotatably connected to the planet carrier 120 of the first planetary gear stage 110 .
  • the first clutch element 134 is formed in one piece with the planet carrier 120 of the first planetary gear stage 110 .
  • the impact shut-off clutch 132 has a second clutch element 136 which is always rotationally coupled to a part of the transmission 26 .
  • the second coupling element 136 is connected to the connecting means 124 in a torque-proof manner.
  • the second coupling element 136 is formed in one piece with the connecting means 124 .
  • the planetary carrier 126 of the second planetary gear stage 112 is connected to the second clutch element 136 in a torque-proof manner. In the hammer drilling operation shown, the hammer shut-off clutch 132 is closed.
  • the tool spindle 40 transmits an axial clutch force to the hammer shut-off clutch 132 when the operator presses the bit against a workpiece.
  • the clutch force closes the impact shut-off clutch 132.
  • an impact switching spring 140 of the impact shut-off device 24 opens the impact shut-off clutch 132.
  • the transmission means 128 are designed as rods.
  • the control element 130 supports the tool guide unit 20 in a screwing and drilling mode in a direction opposite to the impact direction 66 .
  • a force applied to the tool guide unit 20 acts via the bearing means 44, a further transmission means 142 of the impact shut-off device 24 and the transmission means 128 designed as rods on support surfaces 144 of the control element 130.
  • the further transmission means 142 is essentially star-shaped with a central region in the shape of an annular disk.
  • the control element 130 has three recesses 146 . In the percussion drilling operation shown, the transmission means 128 are pushed into the recesses 146, as a result of which the tool guide unit 20 can be moved axially in the percussion drilling mode.
  • the connecting means 128 is functionally arranged between the planet carrier 126 of the second planetary gear stage 112 and the tool spindle 40 .
  • the connecting means 128 has the second clutch element 136 of the impact shut-off clutch 132 .
  • the connecting means 128 is mounted so that it can be displaced axially against the impact switch spring 140 .
  • the impact shut-off clutch 132 is opened by an axial displacement of the connecting means 128 in the direction of the insertion tool attachment 38 .
  • the connecting means 128 is always connected to the tool spindle 40 in a rotationally fixed and axially displaceable manner. As a result, the planetary carrier 126 of the second planetary gear stage 112 remains rotationally coupled to the tool spindle 40 even in the event of an impact.
  • the planet carrier 126 of the second planetary gear stage 112 is connected to the connecting means 128 in a torque-proof manner.
  • the planetary carrier 126 of the second planetary gear stage 112 and the connecting means 128 are connected in an axially displaceable manner relative to one another.
  • FIG 12 shows a sectional area D of the spindle blocking device 36.
  • the spindle blocking device 36 is intended to connect the tool spindle 40 in a torque-proof manner to the hand tool housing 14 when a tool torque is applied to the insert tool attachment 38, for example when an insert tool is clamped into the insert tool attachment 38.
  • the spindle blocking device 36 is partially formed in one piece with the connecting means 128 and the planetary carrier 126 of the second planetary gear stage 112 .
  • the spindle locking device 36 has locking means 150, first clamping surfaces 152, a second clamping surface 154 and freewheel surfaces 156.
  • the blocking means 150 are designed in the form of rollers.
  • the first clamping surfaces 152 are designed as areas of a surface of the connecting means 128 .
  • the first clamping surfaces 152 are flat.
  • the second clamping surface 154 is designed as an inside of a clamping means 158 of the spindle blocking device 36 .
  • the clamping means 158 is designed as a clamping ring.
  • Clamping means 158 is non-rotatably connected to hand tool housing 14 via a component of spindle blocking device 36, specifically to impact mechanism housing 56 of hand tool housing 14.
  • clamping means 158 is non-rotatably connected to hand tool housing 14 via stop means 160 of spindle blocking device 36.
  • the freewheeling surfaces 156 are designed as areas of a surface of the planetary carrier 126 of the second planetary gear stage 112 .
  • the locking means binds 150 between the first clamping surfaces 152 and the second clamping surface 154.
  • the free-wheeling surfaces 156 guide the blocking means 150 on a circular path and prevent jamming.
  • the planetary carrier 126 of the second planetary gear stage 112 and the connecting means 128 are meshed with one another with play.
  • the spindle blocking device 36 is arranged outside of the transmission housing 52 .
  • the spindle blocking device 36 is arranged inside the hammer mechanism housing 56 .
  • the torque limiting unit 34 is provided to limit a maximum tool torque delivered by the insertion tool attachment 38 in a screwing mode.
  • Torque limiting unit 34 includes stop means 160, an operating element 162, adjustment elements 164, limiting springs 166, transmission means 168, first stop surfaces 170, a second stop surface 172 and limiting means 174.
  • Transmission means 168, first stop surfaces 170 and second stop surfaces 172 form a clutch of the torque limiting unit 34.
  • a maximum torque that can be transmitted to the insertion tool attachment 38 can be limited by means of the operating element 162.
  • the operating element 162 is ring-shaped.
  • the operating element 162 is designed with two shells. In the direction of the transmission 26, it adjoins the insertion tool attachment 38.
  • the operating element 162 has inclined adjusting surfaces 176 which act on the adjusting elements 164 in the axial direction.
  • the adjustment elements 164 are non-rotatable and are mounted in an axially displaceable manner by the operating element 162 . A rotation of the operating element 162 displaces the adjustment elements 164 in the axial direction.
  • the limiting springs 166 are supported on the adjustment element 164 on one side. On another side, the limiting springs 166 are supported on the stop means 160 of the torque limiting unit 34 via the transmission means 168 .
  • the transmission means 168 are mounted so that they can be displaced in the axial direction.
  • a surface of the stop means 160 has the first stop faces 170 .
  • the stop means 160 is mounted so that it can move in the axial direction against the limiting springs 166 in the screwing mode.
  • the second stop surface 172 is designed as a region of a surface of a ring gear 178 of the second planetary gear stage 112 .
  • the second stop surface 172 delimits trough-shaped depressions 180.
  • the delimiting means 174 are of spherical design.
  • the torque limiter unit 34 has a limiter guide means 182, which is intended to support the limiting means 174 in an axially displaceable manner.
  • figure 13 shows a sectional area E of the limiting means guide means 182.
  • the limiting means guide means 182 delimits recesses 184 in which the limiting means 174 are mounted so that they can be displaced in the impact direction 66.
  • the recesses 184 are tubular.
  • Impact mechanism gear housing 54 fastens limiting means guide means 182 in a rotationally fixed manner.
  • the delimiting means 174 are arranged in the trough-shaped depressions 180 .
  • the limiting means 174 fasten the ring gear 178 of the second planetary gear stage 112 in a rotationally fixed manner.
  • the limiting means 174 push the stop means 160 away against the limiting springs 166 .
  • the limiting means 174 then each jump into a next one of the trough-shaped depressions 180.
  • the ring gear 178 of the second planetary gear stage 112 rotates, as a result of which the screwing process is interrupted.
  • the torque limiting unit 34 has switch-off means 186, 188 which are provided to switch off a torque limiter of the torque limiting unit 34, as a result of which a maximum torque is dependent on a maximum torque of the drive unit 30.
  • the adjusting element 164 and the transmission means 168 each have a part of the switch-off means 186, 188.
  • the shut-off means 186, 188 prevent an axial movement of the stop means 160, at least in a drilling mode.
  • the switch-off means 186, 188 extend towards one another.
  • the switch-off means 186, 188 are functionally aligned parallel to the limiting springs 166.
  • figure 14 shows a sectional area F of the second planetary gear stage 112.
  • the ring gear 178 of the second planetary gear stage 112 is mounted in the hand tool housing 14 secured against complete rotation at least during drilling operation.
  • Planet gears 190 of the second planetary gear stage 112 mesh with the ring gear 178 and a sun gear 192 of the second planetary gear stage 112.
  • figure 15 shows a sectional area G through a planet carrier 194 of the third planetary gear stage 114.
  • figure 16 shows a sectional area H through planet gears 196 of the third planetary gear stage 114.
  • the sun gear 192 of the second planetary gear stage 112 is non-rotatably connected to the planet carrier 194 of the third planetary gear stage 114.
  • Planet gears 196 of the third planetary gear stage 114 mesh with a sun gear 198 and a ring gear 200 of the third planetary gear stage 114.
  • Ring gear 200 of third planetary gear stage 114 has teeth 202 that connect ring gear 200 of third planetary gear stage 114 to hand tool housing 14 in a rotationally fixed manner in a first gear ratio.
  • the toothing 202 of the ring gear 200 of the third planetary gear stage 114 engages in the first gear ratio in an internal toothing of a ring 204, which in turn is non-rotatably connected to the hand tool housing 14.
  • a support means 206 which is provided to divert a force acting axially on the ring gear 200 of the third planetary gear stage 114, in particular by the torque limiting unit 34, to the hand tool housing 14.
  • the support means 206 is designed in the form of an annular disk.
  • the support means 206 is positively connected to the hand tool housing 14 via the ring 204 in an axial direction pointing away from the insertion tool attachment 38 .
  • a snap ring 208 secures the support means 206 in an axial direction toward the insert tool mount 38 .
  • figure 17 shows a sectional area I through a planet carrier 210 of the fourth planetary gear stage 116.
  • figure 18 shows a sectional area J through planet gears 212 of the fourth planetary gear stage 116.
  • the sun gear 198 of the third planetary gear stage 114 is non-rotatably connected to the planet carrier 210 of the fourth planetary gear stage 116.
  • the planet gears 212 of the fourth planetary gear stage 116 mesh with a sun gear 214 and a ring gear 216 of the fourth planetary gear stage 116.
  • the ring gear 216 of the fourth planetary gear stage 116 is connected to the hand tool housing 14 in a torque-proof manner.
  • Ring gear 216 of fourth planetary gear stage 116 is formed in one piece with a gear housing cover 218 facing away from insertion tool attachment 38 .
  • the transmission housing cover 218 can be formed in one piece with the transmission housing 52, but is formed separately here.
  • the gear housing cover 218 is removed before the gear housing is equipped 52 connected to the transmission 26 with the transmission housing 52.
  • the sun gear 214 of the fourth planetary gear stage 116 is connected in a torque-proof manner to a rotor 220 of the drive unit 30 .
  • the ring gear 200 of the third planetary gear stage 114 is as in figure 2 shown slidably mounted in the axial direction.
  • ring gear 200 of third planetary gear stage 114 is connected to hand tool housing 14 in a torque-proof manner.
  • ring gear 200 of third planetary gear stage 114 is non-rotatably connected to planet carrier 210 of fourth planetary gear stage 116 and is rotatably mounted relative to hand tool housing 14 .
  • the planetary carrier 210 of the fourth planetary gear stage 116 has external teeth. This results in a reduction ratio of the first translation between the rotor 220 of the drive unit 30 and the planet carrier 194 of the third planetary gear stage 114, which is greater than a reduction ratio of the second translation.
  • the application tool attachment 38 rotates more slowly in the first gear than in the second gear.
  • a maximum torque that can be effected by the drive unit 30 on the insertion tool attachment 38 is greater in the first gear ratio than in the second gear ratio.
  • a maximum torque that can be effected by the drive unit 30 on the insertion tool attachment 38 in the first gear ratio is 40 Nm.
  • a maximum torque that can be effected by the drive unit 30 on the insertion tool attachment 38 in the second gear ratio is 14 Nm.
  • the transmission housing cover 218 is formed from a plastic.
  • the gear housing cover 218 closes the gear housing 52 on the side facing away from the insertion tool attachment 38 .
  • the torque limiting unit 34 is provided to close the side of the transmission housing 52 facing the insertion tool attachment 38 in a ready-to-operate state.
  • Impact mechanism gear housing 54 fastens the component of torque limiting unit 34 to gear housing 52, which closes the side of gear housing 52 facing insertion tool attachment 38 when it is ready for operation.
  • the limiting means guide means 182 of the torque limiting unit 34 closes the side of the transmission housing 52 facing the insertion tool attachment 38 in an operational state.
  • the restricting means guide means 182 is formed of a metallic material.
  • the gear housing 52 is of a the side facing the insertion tool attachment 38 is equipped with at least the second, the third and the fourth planetary gear stage 112, 114, 116 of the gear 26.
  • the operating device 32 has a first operating element 222 and a second operating element 224 .
  • the first operating element 222 is arranged on a side of the hand tool housing 14 facing away from the handle 18 . It is movably mounted parallel to the axial direction of the transmission 26 .
  • the first operating element 222 is connected in the axial direction to the ring gear 200 of the third planetary gear stage 114 via an adjusting means 226 of the operating device 32 .
  • Ring gear 200 of third planetary gear stage 114 has a groove 228 in which adjusting means 226 engages. Ring gear 200 of third planetary gear stage 114 is thus connected to adjusting means 226 so that it can rotate axially in the axial direction relative to adjusting means 226 .
  • the adjusting means 226 is designed to be resilient, as a result of which the translation can be adjusted independently of a rotational position of the ring gear 200 of the third planetary gear stage 114 .
  • the first gear ratio is set.
  • the second gear ratio is set.
  • the second operating element 224 is arranged on a side of the hand tool housing 14 facing away from the handle 18 .
  • the second operating element 224 is arranged such that it can be displaced about an axis which is aligned parallel to the axial direction of the transmission 26 .
  • the second operating element 224 mechanically activates or deactivates the hammer drill mode when actuated.
  • the second operating element 224 is connected in a rotationally fixed manner to the control element 130 of the hand tool device 12 .
  • the screwing and drilling mode and the percussion drilling mode can be set using the second operating element 224 . When the second operating element 224 is pushed to the left, viewed in the impact direction 66, the percussion drilling mode is set. When the second operating element 224 is pushed to the right, viewed in the direction of impact 66, the screwing and drilling mode is set.
  • the impact switching spring 140 of the hand tool device 12 opens the impact shut-off clutch 132 during an impact drilling operation when the operator places the application tool away from the workpiece.
  • the impact switch spring 140 is arranged coaxially to the planetary gear stages 110, 112, 114, 116 of the gear 26.
  • the second planetary gear stage 112 and the third planetary gear stage 114 enclose the impact switching spring 140 each on at least one plane that is perpendicular to the axial direction of the transmission 26.
  • the connecting means 128 supports the impact switch spring 140 on a side facing the insertion tool attachment 38 .
  • a bearing means 230 supports the impact switch spring 140 on a side facing away from the insertion tool attachment 38 .
  • the bearing means 230 is designed as a ball.
  • the bearing means 230 is arranged between the impact switch spring 140 and the rotor 220 of the drive unit 30 .
  • the hand tool device 12 has a first detection unit 232 and a second detection unit 234 .
  • the first detection unit 232 is provided for the purpose of electrically outputting a parameter that depends on whether the striking mechanism 22 is activated, ie in the percussion drilling mode, or deactivated, ie in the drilling and screwing mode.
  • First detection unit 232 is embodied as a switch that detects a movement of second operating element 224 relative to hand-held tool housing 14 .
  • the detection unit 232 could detect a movement of another part of the percussion mechanism 22 that appears reasonable to a person skilled in the art.
  • the second detection unit 234 is provided for the purpose of electrically outputting a second parameter which is dependent on which of the transmission ratios of the transmission 26 is set using the first operating element 222 .
  • First detection unit 234 is embodied as a switch that detects a movement of first operating element 222 relative to hand-held tool housing 14 .
  • the detection unit 232 could detect a movement of another part of the transmission 26 that appears reasonable to a person skilled in the art.
  • the hand tool device 12 has a control unit 236 which is intended to control the drive unit 30 during operation.
  • the control unit 236 includes a microcontroller and power electronics.
  • the power electronics are provided to supply the drive unit 30 with energy for different speeds and/or different torques.
  • the microcontroller is provided to control the drive unit 30 via the power electronics as a function of the first parameter and the second parameter.
  • the control unit 236 includes a protection function intended to limit a maximum torque delivered by the drive unit 30 in the operating mode when the hammer drilling mode is activated and the first gear ratio, ie a small maximum Speed and a large maximum torque is set. Then the control unit 236 limits a maximum electric current delivered to the drive unit 30 .
  • the hand tool device 12 has an impact mechanism spindle bearing means 238 which rotatably supports the impact mechanism spindle 60 on the side facing away from the insertion tool attachment 38 .
  • Impact mechanism spindle bearing means 238 is firmly connected to impact mechanism spindle 60 in the axial direction, namely impact mechanism spindle bearing means 238 is pressed with impact mechanism spindle 60 .
  • the impact mechanism spindle bearing means 238 could be firmly connected to the hand tool housing 14 in the axial direction.
  • the hand tool device 12 has an impact mechanism spindle fastening means 242 which is provided for fastening the impact mechanism spindle 60 in the axial direction.
  • Impact mechanism spindle attachment means 242 is designed as a snap ring.
  • Impact mechanism spindle fastening means 242 engages in a groove 240 of impact mechanism spindle 60.
  • Groove 240 of impact mechanism spindle 60 is arranged on the side of impact mechanism spindle 60 facing away from insert tool attachment 38.
  • the impact mechanism spindle fastening means 242 is arranged in the axial direction between the impact mechanism spindle bearing means 238 and the first planetary gear stage 110 .
  • the striking mechanism spindle fastening means 242 fastens the striking mechanism spindle 60 in a form-fitting manner in the axial direction.
  • the percussion mechanism spindle 60 could be fastened in the axial direction in a different way that appears sensible to a person skilled in the art.
  • the hammer mechanism spindle bearing means 238 could be connected to the hammer mechanism spindle 60 in a materially bonded or non-positive manner in the axial direction.

Landscapes

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

Claims (10)

  1. Dispositif d'outil à main, comprenant une broche d'outil (40) et un mécanisme de percussion (22) qui présente un percuteur (58) et au moins un guide curviligne (72) qui entraîne le percuteur (58) au moins en mode perçage à percussion, la broche d'outil (40) présentant au moins une surface de palier (68) qui loge le percuteur (58) de façon mobile dans au moins un état de fonctionnement, la broche d'outil (40) présentant au moins une surface de percussion (46) que frappe le percuteur (58) au moins en mode perçage à percussion dans une direction de percussion axiale (66),
    caractérisé en ce que le mécanisme de percussion (22) présente une broche de mécanisme de percussion (60) pourvue d'une surface de palier (70) qui loge le percuteur (58) de façon mobile dans au moins un état de fonctionnement.
  2. Dispositif d'outil à main selon la revendication 1, caractérisé en ce que le percuteur (58) enferme au moins substantiellement la broche d'outil (40) sur au moins un plan.
  3. Dispositif d'outil à main selon l'une quelconque des revendications précédentes, caractérisé en ce que le percuteur (58) enferme au moins substantiellement la broche de mécanisme de percussion (60) sur au moins un plan.
  4. Dispositif d'outil à main selon l'une quelconque des revendications précédentes, caractérisé en ce que le percuteur (58) limite un espace intérieur du percuteur (58) dans la direction de percussion (66) avec un rétrécissement vers l'intérieur.
  5. Dispositif d'outil à main selon la revendication 4, caractérisé en ce qu'une surface de palier (68) de la broche d'outil (40) agit sur la zone rétrécie d'une face intérieure du percuteur (58), et la surface de palier (70) de la broche de mécanisme de percussion (60) agit sur une zone non rétrécie du percuteur (58), tournée vers un réducteur (26).
  6. Dispositif d'outil à main selon l'une quelconque des revendications précédentes, caractérisé en ce que le percuteur (58) présente une forme de base en forme de pot, un évidement étant disposé dans le fond de la forme de base en forme de pot, à travers lequel s'étend la broche d'outil (40), et le percuteur (58) percute la broche d'outil (40) par une face extérieure de fond de la forme de base en forme de pot.
  7. Dispositif d'outil à main selon l'une quelconque des revendications précédentes, caractérisé en ce que le percuteur (58) présente au moins une partie du guide curviligne (72).
  8. Dispositif d'outil à main selon l'une quelconque des revendications précédentes, caractérisé en ce que le mécanisme de percussion (22) présente au moins un ressort de mécanisme de percussion (62) qui accumule au moins une partie d'une énergie de percussion dans au moins un état de fonctionnement.
  9. Dispositif d'outil à main selon la revendication 8, caractérisé en ce que le ressort de mécanisme de percussion (62) fixe le percuteur (58) dans la direction circonférentielle dans au moins un état de fonctionnement.
  10. Outil à main, en particulier perceuse à percussion, comprenant un dispositif d'outil à main (12) selon l'une quelconque des revendications précédentes.
EP14161634.2A 2013-05-14 2014-03-26 Dispositif d'outil manuel Active EP2803447B1 (fr)

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DE201310208882 DE102013208882A1 (de) 2013-05-14 2013-05-14 Handwerkzeugvorrichtung

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EP (1) EP2803447B1 (fr)
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CN104755209B (zh) * 2012-10-26 2016-12-14 阿特拉斯·科普柯工业技术公司 具有柔性主轴进给的钻孔工具
DE102014207713A1 (de) 2014-04-24 2015-10-29 Robert Bosch Gmbh Werkzeugvorsatz für eine Handwerkzeugmaschine
DE102013208900A1 (de) * 2013-05-14 2014-11-20 Robert Bosch Gmbh Handwerkzeugvorrichtung
DE202013008724U1 (de) 2013-09-30 2015-01-05 Robert Bosch Gmbh Werkzeugvorsatz für eine Handwerkzeugmaschine
DE102015201921A1 (de) * 2015-02-04 2016-08-04 Robert Bosch Gmbh Zubehörvorrichtung
DE102015206634A1 (de) 2015-04-14 2016-10-20 Robert Bosch Gmbh Werkzeugvorsatz für eine Handwerkzeugmaschine
DE102015206622B4 (de) 2015-04-14 2024-05-23 Robert Bosch Gmbh Werkzeugvorsatz für eine Handwerkzeugmaschine
CN104942762A (zh) * 2015-06-05 2015-09-30 吴志明 电锤
JP2022188996A (ja) * 2021-06-10 2022-12-22 株式会社マキタ 回転打撃工具

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Also Published As

Publication number Publication date
CN104148702B (zh) 2020-03-03
CN104148702A (zh) 2014-11-19
DE102013208882A1 (de) 2014-11-20
EP2803447A1 (fr) 2014-11-19
US20180318997A1 (en) 2018-11-08
US20140338944A1 (en) 2014-11-20
US10780562B2 (en) 2020-09-22
US10046449B2 (en) 2018-08-14

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