EP3638457B1 - Machine-outil portative - Google Patents

Machine-outil portative Download PDF

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Publication number
EP3638457B1
EP3638457B1 EP18729382.4A EP18729382A EP3638457B1 EP 3638457 B1 EP3638457 B1 EP 3638457B1 EP 18729382 A EP18729382 A EP 18729382A EP 3638457 B1 EP3638457 B1 EP 3638457B1
Authority
EP
European Patent Office
Prior art keywords
hand
held power
power tool
tool
designed
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
EP18729382.4A
Other languages
German (de)
English (en)
Other versions
EP3638457A1 (fr
Inventor
Andre Kurz
Thomas Brinkmann
Lars Schmid
Pascal Schmitz
Hardy Schmid
Patrick Heinen
Jan Koalick
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
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Filing date
Publication date
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Publication of EP3638457A1 publication Critical patent/EP3638457A1/fr
Application granted granted Critical
Publication of EP3638457B1 publication Critical patent/EP3638457B1/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
    • B25D11/005—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
    • 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
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • 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
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
    • B25D17/084—Rotating chucks or sockets
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • 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
    • B25D2216/0084—Mode-changing mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0019—Guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/131—Idling mode of tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/165—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
    • B25D2250/275—Tools having at least two similar components

Definitions

  • Rotary hammers with eccentric impact mechanisms of different performance classes are already known both as cordless devices and as mains devices.
  • the invention relates to a system consisting of a first hand-held power tool and a second hand-held power tool, each with a percussion mechanism, each with a motor, each with a gearbox comprising the percussion mechanism, which is designed to transmit a drive movement of the motor to an insert tool held in a tool holder, wherein the respective gears have a guide tube that is identical in some areas along a working axis, in which a beater is mounted in an axially movable manner, the guide tube being rotatably coupled to the motor via a first gear unit and the beater being able to be driven in a linear oscillating manner via a piston of a second gear unit.
  • the hand-held power tool is designed in particular to drive an insert tool rotating and/or striking along a working axis.
  • the working axis extends essentially along the longitudinal extent of the first or second hand-held power tool.
  • the insert tool can be designed, for example, as a drill or chisel.
  • the insert tool is a wearing part that can be detachably fastened in the tool holder.
  • the insert tool has an insertion end that is received in the tool holder of the hand-held power tool.
  • the insertion ends of insert tools usually have a standardized shaft diameter that is designed for different device classes or device sizes, for example a 10 mm shaft diameter for SDS-plus tool holders and an 18 mm shaft diameter for SDS-Max tool holders.
  • the tool holder preferably includes an interchangeable drill chuck or a fixed drill chuck.
  • a “guide tube that is identical in some areas along a working axis” is to be understood in particular as meaning a guide tube which is identical to another guide tube at least to 33%, preferably at least 50%, in particular at least 66% of the length of the guide tube along the longitudinal extent of the hand-held power tool.
  • the inside and/or outside diameter of the guide tube of the first hand-held power tool and the second hand-held power tool is identical at least in regions along the working axis.
  • the guide tube of the first and/or the second hand-held power tool can be designed in one piece or in several parts.
  • the guide tube of the first hand-held power tool and the second hand-held power tool is identical in a region between the rear end, which faces away from the tool holder, and a control opening or the B-impact damping system.
  • a ratio between a diameter of the tool holder and a diameter of the guide tube is 1.8 times larger in the first hand-held power tool than in the second hand-held power tool.
  • a “diameter of the tool holder” is intended to mean, in particular, an inner diameter of the tool holder that is adapted to the shaft size of the insert tool.
  • a “diameter of the guide tube” should be understood to mean in particular the inner diameter of the guide tube.
  • a single impact energy of the second hand-held power tool is mechanically reduced in comparison to a single impact energy of the first hand-held power tool. This advantageously allows the second hand-held power tool to be easily adapted to a different area of application.
  • Single impact energy is to be understood in particular as meaning the energy that is transferred to the striker during operation of the hand-held power tool or that is transferred from the striker to the insert tool.
  • Mechanismically reduced should be understood in particular to mean that the individual impact energy is reduced by the transmission, preferably by the second transmission unit of the transmission.
  • the individual impact energy of the second hand-held power tool is preferably reduced by at least 10%, in particular at least 17.5%, preferably by at least 25%.
  • the impact power of the second hand-held power tool is mechanically reduced in comparison to an impact power of the first hand-held power tool.
  • the impact frequency of the impact mechanism of the first hand-held power tool is essentially identical to the impact frequency of the second hand-held power tool.
  • crank stroke of the second gear unit of the second hand-held power tool is reduced, in particular reduced by 10%, preferably reduced by 15%, preferably reduced by 20%, in comparison to a crank stroke of the second gear unit of the first hand-held power tool.
  • a crank stroke is to be understood in particular as the axial distance between the two reversal points of the piston in the guide tube. In particular, no axial force acts on the piston at the two reversal points.
  • the pistons of the first and second hand-held power tools are each driven via an eccentric unit, with an eccentricity of the eccentric unit of the second hand-held power tool is smaller than an eccentricity of the eccentric unit of the first hand tool.
  • the eccentric unit is assigned to the second gear unit.
  • the eccentric unit is driven around an axis of rotation by the motor.
  • the eccentric unit has a translation element designed as an eccentric pin, which is connected to the piston via a crank element.
  • the translation element moves around the axis of rotation on a particularly circular path.
  • the eccentricity of the eccentric unit results from the distance between the axis of rotation of the eccentric unit and the path on which the translation element moves.
  • an air spring length of the impact mechanism of the first hand-held power tool differs from an air spring length of the impact mechanism of the second hand-held power tool, and is in particular larger.
  • the individual impact energy can be reduced in a structurally simple manner by reducing the air spring length of the striking mechanism.
  • An air spring length of the striking mechanism should be understood in particular as a minimum distance between the striker and the piston or a distance between the striker and the piston at the front reversal point facing the tool holder.
  • the air spring length can be adjusted, for example, via the shape of the racket, the shape of the piston or the shape of the crank element.
  • a bearing distance of the striking mechanism of the first hand-held power tool is equal to a bearing clearance of the striking mechanism of the second hand-held power tool.
  • a bearing distance is to be understood in particular as a distance between two areas over which the guide tube of the impact mechanism is mounted.
  • the bearing distance is a distance between an axial or radial bearing and another axial or radial bearing, each of which supports the guide tube.
  • the bearing distance is preferably designed as a distance between two radial bearings.
  • a striking point of the first hand-held power tool is equal to a striking point of the second hand-held power tool.
  • a hitting point should in particular be the position of the bat, in particular of the rear end of the striker, facing away from the tool holder, in the guide tube, while the insert tool is pressed against the processing surface.
  • both the impact point and the air spring length of the first hand-held power tool are identical to the impact point and the air spring length of the second hand-held power tool.
  • the first and second hand-held power tools each have a B-impact damping system, which are designed identically to one another.
  • a B-impact damping system is intended to mean, in particular, an arrangement of components in the striking mechanism that are designed to dampen the recoil of the insert tool against the direction of impact.
  • the bat transfers its energy to the insert tool via a bolt element.
  • the B-impact damping system is at least partially arranged in the guide tube and comprises at least one damping element, which can be arranged inside and/or outside the guide tube.
  • the mass ratio between the bolt element and the striker in the first hand-held power tool is identical to the second hand-held power tool, so that the same B-impact damping system can advantageously be optimized for both the first and the second hand-held power tool.
  • the first and the second hand-held power tool each have a gear housing, with the mechanical components within the gear housing being at least 80%, in particular at least 90%, identical.
  • the transmission housing can be designed as an outer housing and/or as an internal housing.
  • a diameter of the tool holder of the second hand-held power tool is less than 18 mm, in particular 10 mm, and that the ratio between a diameter of the guide tube and the diameter of the tool holder of the second hand-held power tool is in a range between 2.8 and 3.4 , in particular in a range between 2.9 and 3.1. This can advantageously be used to realize a particularly powerful hand-held power tool.
  • the hand-held machine tools are designed to include as many of the same components as possible in order to cost-effectively cover different areas of application.
  • the same components and the same structural units are given the same reference numbers below.
  • the different variants of the hand-held power tool are identified by the number of apostrophes after the reference number.
  • Different embodiments of components or units that are assigned to one or more specific variants of the hand-held power tool are also marked with the same number of apostrophes.
  • Alternative embodiments of the components or structural units, which are fundamentally suitable for at least two variants, are identified with a letter after the reference number.
  • the first hand tool 10 (see Fig. 1 ) and the second hand tool 10 '(see Fig. 2 ) are designed as cordless handheld power tools.
  • the two hand-held power tools 10, 10' each have a tool holder 12, 12' which differ from one another in their diameter 14, 14'.
  • the tool holder 12 is designed as a fixed drill chuck and the tool holder 12 'is designed as an interchangeable drill chuck.
  • the first hand-held power tool 10 is designed with an SDS-max tool holder 12 and the second hand-held power tool 10' is designed with an SDS-plus tool holder 12'.
  • the diameter 14 of the SDS-max tool holder 12 is essentially 18 mm and the diameter 14 'of the SDS-plus tool holder 12' is essentially 10 mm, which results in a ratio between the diameter 14 of the tool holder 12 of the first hand-held power tool 10 and the diameter 14 'of the tool holder 12' of the second hand tool 10' of 1.8 results.
  • the third hand tool 10" (see Fig. 9c ) and the fourth hand tool 10′′′ (see Fig. 9d ) are each designed as network handheld machine tools with an SDS-max tool holder 12 and an SDS-plus tool holder 12 '.
  • Fig. 1 a longitudinal section through the first hand-held power tool 10 is shown.
  • the hand tool 10 is designed as a hammer drill.
  • the hand-held power tool 10 has a housing 16 which is formed from several housing parts 18, 20, 22, 24.
  • the housing parts 18, 20, 22, 24 are designed as external housings. Alternatively or additionally, it is also conceivable that at least one of the housing parts 18, 20, 22, 24 is partially or completely designed as an inner housing.
  • a motor 26 is arranged within the first housing part 18.
  • the motor 26 is designed in the variants of the hand-held power tool 10, 10' as a cordless hand-held power tool, in particular as a brushless direct current motor, and in the variants of the hand-held power tool 10", 10" as a mains hand-held power tool as an alternating current motor, for example as a synchronous motor, asynchronous motor or universal motor.
  • the motors 26 of the hand-held power tools 10, 10', 10", 10 ⁇ are optimized to the same characteristics, so that the relationship between speed and torque at relevant operating points is essentially identical.
  • a drive movement of the motor 26 is transmitted via a gear 28 to the tool holder 12, in which an insert tool 30 is detachably received.
  • the gear 28 has a first gear unit 32, a second gear unit 34 and a striking mechanism 36.
  • the gear 28 is accommodated in a gear housing 38, which is designed as an inner housing, in particular made of metal.
  • the gear housing 38 is at least partially designed as an outer housing.
  • the first gear unit 32 is designed to rotatably couple the motor 26 to a guide tube 40 of the impact mechanism 36.
  • the first gear unit 32 includes an overload device 42, which is designed to limit the maximum torque that can be transmitted from the motor 26 to the guide tube 40.
  • the second gear unit 34 is designed to translate the rotary drive movement of the motor 26 into a linear movement of a racket 44, which is mounted and guided in a linearly movable manner in the guide tube 40.
  • the second gear unit 34 includes an eccentric unit 46, which has a translation element 48 designed as an eccentric pin, which has a crank element 50 a piston 52 is connected. The piston 52 is guided in a linearly movable manner in the guide tube 40.
  • the striking mechanism 36 includes the guide tube 40, the beater 44 and a bolt element 54, which is also guided in a linearly movable manner in the guide tube 40 and via which the energy of the beater 44 is transmitted to the insert tool 30.
  • the guide tube 40 has a diameter, in particular an inner diameter, of 30 mm, which means that high individual impact energy can be achieved. This results in a ratio between the diameter of the guide tube 40 and the diameter 14 of the tool holder 12 of approximately 1.7 in the first hand-held power tool 10.
  • the hand-held power tool 10 includes several operating modes that can be set via an operating mode switching element 56.
  • the operating mode switching element 56 has at least three switching positions, with one switching position corresponding to a drilling mode, another switching position corresponding to a hammer drill mode and yet another switching position corresponding to a chiseling mode.
  • the insert tool 30 is coupled to the gear 28, in particular to the guide tube 40 and the bolt element 54, in a rotationally and translationally movable manner via the tool holder 12.
  • the insert tool 30 rotates about a working axis 58 and/or oscillates along the working axis 58.
  • the hand-held power tool 10 extends in length along the working axis 58.
  • the tool holder 12 is arranged at the front end of the hand-held power tool 10 and the third housing part 22, designed as a handle 60, is arranged at the rear end of the hand-held power tool 10.
  • the handle 60 is pivotally attached to the first housing part 18 and to the second housing part 20.
  • the handle 60 is attached to the first housing part 18 via a damping unit 62.
  • An operating element 64 is arranged on the handle 60 and is designed as an operating switch for switching the hand-held power tool 10 on and off.
  • the height of the hand-held power tool 10 extends essentially parallel to a longitudinal extent of the handle 60 and/or parallel to the longitudinal extent, in particular of a motor shaft 66, of the motor 26.
  • the gear 28 is arranged above the motor 26.
  • Electronics 68 are arranged below the motor 26 and are designed to regulate or control the hand-held power tool 10, in particular the motor 26 of the hand-held power tool 10.
  • the electronics 68 is arranged in the second housing part 20.
  • a battery interface 70 arranged, via which a hand-held power tool battery pack 72 can be detachably attached to the second housing part 22 designed as a handle 60.
  • the handheld power tool battery pack 72 includes a battery pack housing 74, in which at least one battery cell 76, advantageously five or ten battery cells 76, are accommodated.
  • a longitudinal section of the second hand-held power tool 10' is shown.
  • the majority of the components installed in the hand-held power tool 10' are designed identically to the components of the hand-held power tool 10.
  • a guide tube 40′ of the second hand-held power tool 10′ is partially identical to the guide tube 40 of the first hand-held power tool 10.
  • the diameter of the guide tube 40' of the second hand-held power tool 10' is identical to the diameter of the guide tube 40 of the first hand-held power tool 10.
  • the diameter of the guide tube 40' is therefore also 30 mm. This results in a ratio between the diameter of the guide tube 40' and the diameter 14' of the tool holder 12' of 3.0 in the second hand-held power tool 10.
  • the tool holder 12' of the second hand-held power tool 10' is designed for smaller insert tools 30', or for insert tools 30' with smaller shaft diameters, a lower single impact energy is required to drive the insert tool 30' with the second hand-held power tool 10' than to drive the Insertion tool 30 with the first handheld power tool 10.
  • the gearbox 28' of the second handheld power tool 10' differs from the gearbox 28 of the first handheld power tool 10 in a few components.
  • the striking mechanism 36' of the second hand-held power tool 10' has a different one Bolt element 54 '.
  • the second gear unit 34' of the second hand-held power tool 10' has a different crank element 50' and an eccentric unit 46' that differs in eccentricity.
  • Fig. 3a the gearbox 28 and the tool holder 12 of the first hand-held power tool 10 are shown.
  • the gear housing 38 has an opening on the underside designed as a drive interface 39, in which the motor shaft 66 of the motor 26 is rotatably mounted.
  • the drive interface 39 includes bearing elements and sealing elements and is standardized for the different variants of the hand-held power tools 10, 10', 10" and 10", so that, for example, both direct current motors, in particular brushless direct current motors, as well as alternating current motors can be accommodated.
  • the first gear unit 32 and the second Gear unit 34 are rotatably coupled to the motor shaft 66. In particular, both the first gear unit 32 and the second gear unit 34 are coupled directly to the motor shaft. Alternatively, it is also conceivable that the first and second gear units 32, 34 are coupled one above the other to the motor shaft 66 are.
  • the first gear unit 32 is coupled to the motor shaft 66 via a first spur gear 78.
  • the first spur gear 78 is assigned to the overload device 42, via which the torque can be transferred from the motor shaft 66 to the clutch shaft 80.
  • the overload device 42 is in particular pressed onto the clutch shaft 80.
  • the coupling shaft 80 is rotatably mounted about a coupling axis 81, the coupling axis 81 being arranged essentially parallel to a drive axis 67 of the motor shaft 66.
  • a pinion element 82 which is assigned to a bevel gear 84, is pressed onto the upper end of the clutch shaft 80.
  • the bevel gear 84 also includes a ring gear 86, which is connected to the guide tube 40 in a rotationally fixed manner.
  • the guide tube 40 is rotatably mounted in the housing 16, in particular in the gear housing 38, via a first and a second bearing arrangement 88, 90.
  • the insert tool 30 rotates with the guide tube 40 coupled so that the insert tool 30 can be driven in rotation.
  • the second gear unit 34 is coupled to the motor shaft 66 via a second spur gear 79.
  • the torque of the motor shaft 66 is transmitted to an eccentric shaft 92 via the second spur gear 79.
  • the eccentric shaft 92 is rotatably mounted about an axis of rotation 93 in the gear housing 38.
  • An eccentric element 94 designed as an eccentric disk is arranged on the top of the eccentric shaft 92, the eccentric shaft 92 and the eccentric element 94 preferably being designed in one piece.
  • the translation element 48 designed as an eccentric pin, is firmly connected to the eccentric element 94. For better illustration, the transfer of the rotary movement into a linear movement is shown by the eccentric unit 46 in Fig. 3b shown from above.
  • the crank element 50 is designed as a connecting rod which is rotatably connected to the translation element 48 and rotatably connected to the piston 52.
  • the translation element 48 is arranged at a distance from the rotation axis 93 of the eccentric unit 46 and rotates about the rotation axis 93 along a circular path 100.
  • the eccentricity 102 of the eccentric unit 46 results from the distance between the translation element 48 and the rotation axis 93, or the distance between the circular path 100 and the axis of rotation 93.
  • the percussion mechanism 36 is designed as a pneumatic percussion mechanism.
  • the striking mechanism 36 has a striking mechanism control 104, via which it can be switched from an idle mode to a working mode. Below the working axis 58, the percussion mechanism 36 is shown in idle mode and above the working axis 58 in working mode.
  • the guide tube 40 has control openings 106 in the area between the racket 44 and the piston 52, via which a pressure equalization between the interior and the exterior of the guide tube 40 can be established.
  • the control openings 106 are designed to be closable via a control sleeve 108, which is arranged outside the guide tube 40.
  • the control sleeve 108 is subjected to a force in the direction of the idle position by means of a spring element 110 designed as a spiral spring.
  • the handheld power tool 10 To move the handheld power tool 10 from idle mode to working mode To move it, it is pressed against a processing surface with the insert tool 30 inserted. Due to the force acting as a result, the insert tool 30, the bolt element 54 resting on the insert tool 30 and the striker 44 resting on the bolt element 54 are displaced axially in the direction of the rear end of the guide tube 40. The position of the striker 44 when the insert tool 30 is pressed is the impact point 112 of the impact mechanism 36.
  • the axial mobility of the insert tool 30 or the bolt element 54 is limited via a B-impact damping system 114.
  • the B impact damping system 114 is axially movably coupled to the impact mechanism control 104.
  • the B-shock absorption system 114 is designed to dampen the kickback of the insert tool 30.
  • the movement of the insert tool 30 is transmitted from the bolt element 54 to a pin element 116 which is movably mounted in a recess in the guide tube 40.
  • a damping element 118 of the B-impact damping system 114 designed as a rubber ring is arranged outside the guide tube and connected to the pin element 116.
  • the damping element 118 rests on the control sleeve 108 of the impact mechanism control 104 and moves it in the working mode in such a way that the control openings 106 of the guide tube 40 are closed by the control sleeve 108 against the spring force of the spring element 110.
  • Fig. 4 the gearbox 28' and the tool holder 12' of the second hand-held power tool 10' are shown.
  • the individual impact energy of the racket 44 is reduced by 1.5 to 2.0 joules via a crank stroke of the piston 52 that is reduced by approximately 20%.
  • the ratio between the diameter of the guide tube 40, 40' and the piston stroke is 1.8, in particular 1.77, in the first hand-held power tool 10, and 1.4, in particular 1.44, in the second hand-held power tool 10'.
  • the reduction in the crank stroke of the piston 52 is realized by reducing the eccentricity 102 'of the eccentric unit 46' compared to the eccentric unit 46 of the first hand-held power tool 10.
  • the gearbox 28 of the first hand-held power tool 10 and the gearbox 28' of the second hand-held power tool 10' are accommodated in identical gearbox housings 38. This is achieved in particular by the fact that the gears 28, 28 'are largely similar. In particular, the bearing distance between the two bearing arrangements 88, 90 is identical in both hand-held power tools 10, 10'.
  • the guide tube 40 of the first hand-held power tool 10 along the working axis 58 is designed in areas identical to the guide tube 40' of the second hand-held power tool 10'.
  • the guide tubes 40, 40 ' are identically designed at least between their rear ends and the control openings 106, preferably at least between their rear ends and the impact mechanism controls 104, preferably between their rear ends and the B-impact damping systems 114.
  • the diameter of the guide tubes 40, 40 ' is identical in the area of the piston 52 and in the area of the beater 44.
  • first gear unit 32 of the second hand-held power tool 10' is designed identically to the first gear unit 32 of the first hand-held power tool 10.
  • the impact point 112 of the second hand-held power tool 10' is identical to the impact point 112 of the first hand-held power tool 10. This is realized in particular by the elongated shape of the bolt element 54 'of the second hand-held power tool 10' compared to the bolt element 54 of the first hand-held power tool 10.
  • the mass ratio between the bolt element 54 and the striker 44 is the first Hand-held power tool 10 substantially equal to the mass ratio between the bolt element 54' and the striker 44 of the second hand-held power tool 10'.
  • the same B-impact damping system 114 can advantageously be optimized for both hand-held power tools 10, 10'.
  • the air spring length 120 of the second hand-held power tool 10' is identical to the air spring length 120 of the first hand-held power tool 10. This is achieved in that the shorter crank stroke is compensated for by an extended crank element 50 ', so that the distance between the impact point 112 and the front reversal point of the piston 52 is the same.
  • FIG. 5a and Fig. 5b an alternative embodiment of the eccentric unit 46a is shown, wherein the eccentricity 102a of the eccentric unit 46a, in contrast to the previous eccentric units 46, 46 ', is not fixed but adjustable.
  • Fig. 5a is the eccentric unit 46a in a cross section and in Fig. 5b shown in a perspective view.
  • the eccentric unit 46a is designed to transmit a rotary drive movement into a linear movement.
  • the eccentric unit 46a has a first eccentric element 94a designed as an eccentric disk, which is rotatably mounted about an axis of rotation 93a.
  • the eccentric unit 46a also includes a second eccentric element 122a designed as an eccentric disk, which is designed to be movable relative to the first eccentric element 94a.
  • the second eccentric element 122a is rotatably mounted about the rotation axis 93a and rotatable about an adjustment axis 123a.
  • the second eccentric element 122a is, for example, partially accommodated by the first eccentric element 94a; alternatively, however, it is also conceivable that the second eccentric element 122a is designed to be placed on the first eccentric element 94a.
  • a translation element 48a designed as an eccentric pin is connected to the second eccentric element 122a in a rotationally fixed manner.
  • the eccentricity 102a of the adjustable eccentric unit 46a results from the distance between the circular path on which the translation element 48a moves about the rotation axis 93a and the rotation axis 93a.
  • the eccentric unit 46a comprises an adjustment unit 124a, which is designed to rotate the second eccentric element 122a, in particular the translation element 48a, about the adjustment axis 123a and to adjust it into at least two different positions, each of which has a different eccentricity 102a.
  • the adjustment unit 124a comprises two mutually corresponding adjustment elements 126a, 128a, which are designed to form a positive connection with one another.
  • the first adjusting element 126a is formed in one piece with the second eccentric element 122a as an external toothing.
  • the second adjustment element 128a is designed as an actuator element 130a, which is accommodated in the housing of the hand-held power tool in a linearly movable manner, for example.
  • the actuator element 130a has a toothing that corresponds to the external toothing of the first adjusting element 126a.
  • the teeth of the adjusting elements 126a, 128a engage with one another in such a way that a linear movement of the actuator element 130a is transferred into a rotary movement of the second eccentric element 122a about the adjusting axis 123a.
  • the rotational movement of the second eccentric element 122a is limited between the two adjustable positions via a stop 131a.
  • the eccentric unit 46a has different eccentricities 102a, which allows the crank stroke to be advantageously varied.
  • the actuator element 130a can advantageously be controlled or regulated automatically or semi-automatically via electronics of the hand-held power tool. Alternatively or additionally, it is also conceivable that the actuator element 130a is mechanically coupled to an operating element, not shown, in order to enable manual actuation of the actuator element 130a.
  • FIG. 6a to Fig. 6d an alternative embodiment of an adjustable eccentric unit 46b is shown.
  • the eccentric unit 46b comprises an eccentric shaft 92b, a first and a second eccentric element 94b, 122b, wherein the first eccentric element 94b is rotatably mounted about a rotation axis 93b and the second eccentric element 122b is rotatably mounted about the rotation axis 93b and the adjustment axis 123b.
  • a translation element 48b is connected to the second eccentric element 94b in a rotationally fixed manner.
  • the setting unit 124b of the eccentric unit 46b is designed to adjust the eccentricity 102b in several different positions between a maximum and a minimum eccentricity 102b.
  • the setting unit 124b comprises two corresponding setting elements 126b, 128b.
  • the first adjusting element 126b is designed as an external toothing of the second eccentric element 122b.
  • the second eccentric element 122b is in particular designed as a gear that is rotatably arranged on the first eccentric element 94b.
  • the second adjusting element 128b is rotatably mounted in the housing about the axis of rotation 93b.
  • the second adjusting element 128b is in engagement with the first adjusting element 126b via a toothing that corresponds to the external toothing.
  • the second adjusting element 128b is designed as a ring gear 132b.
  • the ring gear 132b encloses both the first and the second eccentric elements 94b, 122b. Above the first eccentric element 94b, the ring gear 132 is in engagement with the second eccentric element 122b, which is designed as a gear, and below the first eccentric element 94b, the ring gear 132b is in engagement with a drive element 134b.
  • the drive element 134b is coupled to the ring gear 132b via a front pinion.
  • the drive element 134b can be driven and/or braked via a drive unit, not shown, which comprises, for example, a motor.
  • the ring gear 132b is designed to be drivable independently of the first eccentric element 94b via the drive element 134b.
  • the eccentricity 102b can advantageously be adjusted via a relative movement of the ring gear 132b to the first eccentric element 94b.
  • the ring gear 132b moves at the same rotational speed as the first eccentric element 94b during the impact operation of the hand-held power tool, so that the eccentricity 102b of the eccentric unit 46b is constant during the impact operation.
  • the eccentricity 102b is varied during the impact operation.
  • the drive element 134b can be controlled such that the eccentricity 102b preferably changes periodically in order to generate a variable impact mechanism pressure.
  • the eccentric unit 46b is shown in a position 136b with a maximum eccentricity 102b and in a position 138b with a minimum eccentricity 102b.
  • the number of possible positions into which the second eccentric element 94b can be adjusted between the positions 136b, 138b can be determined via the number of teeth of the toothings of the adjusting elements 126b, 128b be determined.
  • the translation element 48b is arranged essentially centrally on the axis of rotation 93b, so that the eccentricity 102b is essentially zero and no crank stroke is generated by the eccentric unit 46b in this position.
  • the setting unit 124b can advantageously be designed to switch off a percussion mechanism of the hand-held power tool.
  • the eccentric unit is in a different way, for example as in US 6505582 described, can be designed.
  • the overload device 42 is advantageously designed in such a way that a high transferable transmission power can be achieved with a low size and weight.
  • the overload device 42 comprises a first coupling element 140 and a second coupling element 142, which can be coupled to one another in a rotationally fixed manner via an overload unit 144.
  • the first coupling element 140 is coupled to the second coupling element 142 for torque transmission as long as a maximum torque is not exceeded.
  • the first coupling element 140 is advantageously decoupled from the second coupling element 142 if the maximum torque is exceeded.
  • the first and second coupling elements 140, 142 In the coupled state, the first and second coupling elements 140, 142 have the same speed, whereas in the decoupled state, the speed of the first coupling element 140 differs from the speed of the second coupling element 142.
  • the first coupling element 140 is designed as a part of the spur gear 78.
  • the first coupling element 140 has spur gear teeth on its circumferential outer surface, which meshes with the motor shaft 66.
  • the second coupling element 142 is connected to the coupling shaft 80 in a rotationally fixed manner.
  • the second coupling element 142 has recesses 145 which extend essentially radially and in each of which an overload unit 144 is arranged to be linearly movable.
  • the overload unit 144 includes an overload element 146 and a spring element 148, which apply a force to the overload element 146.
  • the compactness of the overload device 42 results in particular from the low height 150 and length 152 of the overload device 42.
  • the ratio between the height 150 and length 152 of the overload device 42 is advantageous in a range between 0.18 and 0.22.
  • the ratio between height 150 and length 152 of the overload device 42 in the exemplary embodiment shown is approximately 0.20.
  • the length 152 of the overload device 42 does not exceed the diameter of the ring gear 86 by more than 20%, preferably by not more than 10%.
  • the diameter of the ring gear 86 exceeds the length 152 of the overload device 42 by approximately 5%.
  • a very compact first gear unit 32 can also be realized due to the short length 152 of the overload device 42.
  • the ratio of the height 154 of the first gear unit 32 to the length 156 of the first gear unit 32, which corresponds to the length 152 of the overload device 42, is in a range between 1.3 and 1.5. In the embodiment shown the ratio is approximately 1.45.
  • Fig. 8a a section through the overload device 42 is shown in a cross section.
  • the overload device 42 is in the coupled state.
  • the first coupling element 140 encloses the second coupling element 142.
  • the overload unit 144 is arranged in the recesses 145 of the second coupling element 142 in such a way that the second coupling element 142 and the overload unit 144 are coupled to one another in a rotationally fixed manner about the coupling axis 81.
  • the overload device 42 comprises seven recesses 145 in each of which an overload unit 144 is arranged.
  • the overload element 146 is subjected to a force radially to the coupling axis 81 by the spring element 148.
  • the head 160 of the overload element 146 acts on the first coupling element 140, in particular a latching profile 162 on the inner circumferential surface of the first coupling element 140.
  • the latching profile 162 comprises seven latching segments, each of which has an ascending and a descending ramp.
  • the locking segments are designed symmetrically, so that the gradient of the ascending ramp is identical to the gradient of the descending ramp.
  • the overload unit 144 thus couples the rotational movement of the first coupling element 140 with the rotational movement of the second coupling element 142.
  • the torque to be transmitted from the motor shaft 66 to the insert tool 30 via the first coupling element 140 can no longer be transmitted, since the coupling shaft 80 coupled to the insert tool is also blocked.
  • a locking process takes place in which the overload elements 146 slide from one pocket of the locking profile 162 to the next until the blocking is released or the hand-held power tool 10 is switched off.
  • Fig. 8b is the one in Fig. 8a marked area shown in an enlarged view.
  • the compact design is achieved by a particularly compact spring element 148.
  • the spring element 148 is designed as a helical compression spring.
  • the spring element 148 comprises a total number of turns of seven, with five turns being designed to be resilient.
  • the spring element has a spring stiffness of at least 50N/mm with a dynamic stroke of up to 1.5 mm.
  • the spring element 148 rests axially on a flat stop surface 164 of the second coupling element 142 and on the overload element 146, in particular on an inner surface of the overload element 146 opposite the head 160.
  • the spring element 148 is guided by the overload element 146.
  • the overload element 146 has two guide arms 147, which are arranged opposite one another and which guide the spring element 148.
  • the guide arms 147 are arranged in the recesses 145 both in the coupled and in the decoupled state, while the head 160 only in the decoupled state is partially arranged in the recess 145.
  • the guiding ratio between the length of the spring element 148 and the length of the area in which the spring element 148 is guided by the overload element 146 is approximately 1.13 in the coupled state.
  • the spring element 148 is guided exclusively by the overload element 146.
  • the spring element 148 is not guided by the second coupling element 142.
  • the recesses 145 of the second coupling element 142 are connected to one another via a circumferential groove 166 which extends around the coupling axis 81.
  • the spring element 148 is partially arranged in this groove 166.
  • the spring element 148 lies against the second coupling element 142 in the area of the groove 166.
  • the spring element 148 has a constant diameter, in particular the outside diameter.
  • the overload element 146 is accommodated in the recess 145 in a linearly movable, tiltable manner.
  • the distance between the recess 145 and the overload element 146 along a longitudinal extension 168 of the overload element 146, which extends coaxially to a radial extension 83 of the coupling axis 81, in particular in the coupled state of the overload device 42 is not constant.
  • the distance between the recess 145 and the overload element 146 increases steadily in the direction of the coupling axis 81, which enables tilting.
  • the recess 145 is straight and the overload element 146 is oblique or conical.
  • the term straight should be understood in particular to mean that the surface of the recess 145, against which the overload element 146 rests, is designed essentially parallel to the longitudinal extent 168 of the overload element 146.
  • the term oblique is intended to mean in particular that the outer surface of the overload element 146 has a slight angular offset from the longitudinal extension 168, which is, for example, approximately 5°.
  • the recess 145 is designed obliquely or that the recess 145 is designed obliquely and the overload element 146 is straight.
  • the overload element 146 is also obliquely or conically shaped on its inner surface. So the distance between is also the spring element 148 and the overload element 146 steadily increasing in the direction of the coupling axis 81.
  • the spring element 148 is conical.
  • the guide arms 147 are obliquely or conically shaped both on their inner side facing the spring element 148 and on their outer side facing the recess 145.
  • Fig. 8c the overload device 42 is shown in the decoupled state. Due to a relative movement of the first coupling element 140 to the second coupling element 142, the overload element 146 experiences a force via the locking profile 162 against the force of the spring element 148. As a result, the overload element 146 moves into the recess 145 in such a way that the head 160 is also partially is arranged in the recess 145, and on the other hand the overload element 146 is tilted. In particular, the overload element 146 is tilted in such a way that the radial extent 83 and the longitudinal extent 168 of the overload element 146 have an angular offset of approximately 4°.
  • Fig. 9a to Fig. 9d the hand power tools 10, 10', 10" and 10" are each shown in a side view.
  • the housings 16, 16', 16", 16" of the hand power tools 10, 10', 10", 10" are based on a common housing concept, so that the first housing part 18 of the hand-held power tools 10, 10', 10", 10" is designed identically.
  • Fig. 9a the housing 16 of the first hand-held power tool 10 is shown.
  • the first housing part 18 has two housing half-shells connected to one another via screw connections.
  • the first housing part 18 encloses the motor 26 and the transmission 28.
  • the motor 26 and the transmission 28 are arranged essentially completely within the space spanned by the housing half-shells of the first housing part 18.
  • the first housing part 18 includes air openings 170 which are designed to supply the motor 26 and/or the transmission 28 with cooling air.
  • An operating mode switching element 56 can be arranged on the top of the first housing part 18.
  • the gear housing 38 is mounted via bearing points 174.
  • the gearbox 38 is supported exclusively by the first housing part 18.
  • the first housing part 18 is connected to the second housing part 20, the third housing part 22 and the fourth housing part 24 via three housing interfaces 178, 180, 182.
  • the second housing part 20 is immovably attached to the first housing part 18 via the first housing interface 178.
  • the second housing part 20 is designed as an electronics housing in which the electronics 68 is arranged.
  • the second housing part 20 preferably also includes air openings 183 which are designed to cool the electronics 68.
  • the second housing part 20 comprises two housing half-shells that are connected to one another via a screw connection.
  • the third housing part 22 designed as a handle 60, is movably attached to the first housing part 18 via the second housing interface 180.
  • the control element 64, designed as an operating switch, and the battery interface 70 are arranged on the third housing part 22.
  • the third housing part 22 has two housing half-shells that are connected to one another via a screw connection.
  • the fourth housing part 24 is immovably attached to the first housing part 18 via the third housing interface 182.
  • the fourth housing part 24 partially encloses the tool holder 12 and has air openings 185 for cooling.
  • the fourth housing part 24 is formed in one piece.
  • the fourth housing part 24 has a tubular shape.
  • Fig. 9b the housing 16' of the second hand-held power tool 10' is shown. Since the first hand-held power tool 10 and the second hand-held power tool 10' differ from each other essentially by the tool holders 12, 12', the first, second and third housing parts are 18, 20, 22 of the two Hand tool tools 10, 10 'are identical to one another.
  • the fourth housing part 24 'of the second hand-held power tool 10' differs from the fourth housing part 24 of the first hand-held power tool 10 in particular in its compactness and length. Due to the more compact tool holder 12' of the second hand tool 10' compared to the tool holder 12 of the first hand tool 10, the housing 16' of the second hand tool 10' can be adapted to the shape of the tool holder 12' via the fourth housing part 24'.
  • the housing interface 182 is designed identically to one another in the hand-held power tools 10, 10'.
  • Fig. 9c is the third hand tool 10" and in Fig. 9d the fourth hand tool 10′′′ is shown.
  • the third hand-held power tool 10′′ is designed as a network variant of the first hand-held power tool 10 and the fourth hand-held power tool 10′′′ as a network-based variant of the second hand-held power tool 10′.
  • the third and fourth hand-held power tools 10′′, 10′′′ each have a different second Housing part 20" and a different third housing part 22".
  • the hand-held power tools 10", 10" each have a network interface 188, which is arranged at the lower end of the third housing part 22" designed as a handle 60". In the area of the network interface 188, entry occurs via an opening in the third housing part 22".
  • the housing interfaces 178, 180, 182 in the handheld power tools 10, 10', 10", 10" are advantageously designed to be identical to one another.
  • another hand-held power tool has identical housing parts 18, 20, 24 and only the third housing part 22 differs by an alternative battery interface 70 for receiving an alternative hand-held power tool battery pack, which, for example, has a different number of battery cells.
  • Fig. 10a-e the housing interfaces 178, 180, 182 are shown using the housing 16 of the first hand-held power tool 10.
  • Fig. 10a shows one Longitudinal section through the housing 16 and Fig. 10b to Fig. 10e each show a housing part 18, 20, 22, 24, or a housing half-shell of the housing parts 18, 20, 22, 24.
  • the first housing interface 178 has mutually corresponding connecting elements 184, 186, which can be connected to one another in a form-fitting manner.
  • the connecting elements 184 are assigned to the first housing part 18, the connecting elements 186 are assigned to the second housing part 20.
  • the first housing part 18 has a pair of connecting elements 184 which are designed as a circular receptacle.
  • the connecting elements 184 are formed in one piece with the first housing part 18.
  • the two connecting elements 184 form the lower end of the first housing part 18.
  • the second housing part 20 also has a few connecting elements 186, which are designed as a pin-shaped extension which extends vertically starting from the inner surface of the second housing part 20.
  • the connecting element 186 extends essentially perpendicular to the longitudinal and vertical extent of the hand-held power tool 10.
  • the connecting element 186 is advantageously designed as a screw dome 187, via which the two housing half-shells of the second housing part 20 can be connected by means of a screw connection. In the connected state, the connecting elements 186 are enclosed or received in a form-fitting manner by the connecting elements 184.
  • the second housing interface 180 pivotally attaches the third housing part 22 to the first housing part 18.
  • the handle is pivotally attached to the first housing part 18 via three axes of rotation 190, 192, 194.
  • the axes of rotation 190, 192 are arranged at the upper end of the housing 16.
  • the corresponding connecting elements 196, 198 are designed as pivot bearing elements that support the damping unit 62.
  • the connecting elements 196, 198 are formed in one piece with the housing parts 18, 22.
  • the damping unit 62 is designed as a sprung connecting rod element.
  • the third housing part 22 has a further connecting element 200 designed as a circular receptacle, which is designed to be positively connectable to the connecting element 186 of the second housing interface 178.
  • the connecting element 186 of the second is in the connected state Housing part 20 is received in a form-fitting manner by the connecting element 184 of the first housing part 18 and the connecting element 200 of the third housing part 22.
  • the third housing interface 182 has two corresponding connecting elements 202, 204, which interlock with one another in a form-fitting manner.
  • the connecting element 202 is assigned to the first housing part 18 and is designed as an extension which extends inwards from the inner surface of the first housing part 18.
  • the fourth housing part 24 is enclosed at a front end region 206 by the two housing half-shells of the first housing part 18 in such a way that the extensions 202 engage in the corresponding connecting elements 204 of the fourth housing part 24, which are designed as openings.
  • the fourth housing part 24 is thus fixed radially by the first housing part 18 and axially and in the direction of rotation about the working axis 58 by the connecting elements 202 of the first housing part 18.
  • the hand-held power tools 10, 10', 10", 10"", which are constructed essentially as described above have an alternative second housing part 20c.
  • the alternative second housing part 20c in particular includes electronics 68 and an additional functional unit 208c.
  • the second housing part 20c can be connected to another housing part of the hand-held power tool via a housing interface (not shown).
  • the second housing part 20c can be formed in one piece in a pot design or, as already described above, in a half-shell housing design.
  • the additional functional unit 208c is designed as a lighting element 210c.
  • the lighting elements 210c can, for example, emit a bright light to illuminate a processing surface or a colored light to display a status of the hand-held power tool.
  • the lighting elements 210c are arranged to the front, in particular in the processing direction. Alternatively or additionally, it is also conceivable that at least one lighting element 212c is arranged laterally.
  • the side lighting element 212c is preferably designed to display a status. It is conceivable, for example, that a safety function could be triggered due to a blocking of the tool, a low battery level, an operating temperature that is too high, etc. can be displayed via the lighting elements 210c and/or the lighting element 212c. In the Fig.
  • the additional functional unit 208c is designed as a coupling means 214c for an accessory device (not shown).
  • the coupling means 214c is designed as a pair of guide rails for a dust extraction device for a hammer drill.
  • the hand-held power tool, in particular the second housing part 20c, can advantageously be connected to an accessory device via the coupling means 214c.
  • the additional functional unit 208c is designed as a distance meter 216c, which measures the distance to the processing surface using laser distance measurement.
  • further additional functional units 208c such as a projection unit for projecting information, patterns, a spirit level or a running time counter or an anti-theft module, are conceivable.

Landscapes

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

Claims (9)

  1. Système composé d'une première machine-outil portative (10) et d'une deuxième machine-outil portative (10') avec chacune un mécanisme de frappe (36, 36'), avec chacune un moteur (26), avec chacune une transmission (28, 28') comprenant le mécanisme de frappe (36, 36'), qui est configurée pour transmettre un mouvement d'entraînement du moteur (26) à un outil d'insertion logé dans un logement d'outil (12, 12'), les transmissions respectives (28, 28') présentant un tube de guidage (40, 40') identique par sections le long d'un axe de travail (58), dans lequel un frappeur (44) est monté de manière mobile axialement, le tube de guidage (40, 40') étant couplé de manière rotative au moteur (26) par l'intermédiaire d'une première unité de transmission (32) et le frappeur (44) pouvant être entraîné en oscillation linéaire par l'intermédiaire d'un piston (52) d'une deuxième unité de transmission (34),
    un rapport entre un diamètre (14, 14') du logement d'outil (12, 12') et un diamètre du tube de guidage (40, 40') étant 1,8 fois plus grand pour la première machine-outil portative (10) que pour la deuxième machine-outil portative (10'),
    caractérisé en ce
    qu'une énergie de frappe individuelle de la deuxième machine-outil portative (10') est mécaniquement réduite en comparaison d'une énergie de frappe individuelle de la première machine-outil portative (10).
  2. Système selon la revendication 1, caractérisé en ce qu'une course de manivelle de la deuxième unité de transmission (34') de la deuxième machine-outil portative (10') est réduite, notamment réduite de 10 %, de préférence réduite de 15 %, préférentiellement réduite de 20 %, en comparaison d'une course de manivelle de la deuxième unité de transmission (34) de la première machine-outil portative (10).
  3. Système selon la revendication 1 ou 2, caractérisé en ce que les pistons (52) de la première et de la deuxième machine-outil portative (10, 10') sont entraînés chacun par une unité excentrique (46, 46'), une excentricité (102') de l'unité excentrique (46') de la deuxième machine-outil portative (10') étant inférieure à une excentricité (102) de l'unité excentrique (46) de la première machine-outil portative (10).
  4. Système selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une longueur de ressort pneumatique (120) du mécanisme de frappe (36) de la première machine-outil portative (10) diffère d'une longueur de ressort pneumatique (120') du mécanisme de frappe (36') de la deuxième machine-outil portative (10'), notamment est supérieure à celle-ci.
  5. Système selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une distance de palier du mécanisme de frappe (36) de la première machine-outil portative (10) est égale à une distance de palier du mécanisme de frappe (36') de la deuxième machine-outil portative (10').
  6. Système selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un point de frappe (112) de la première machine-outil portative (10) est égal à un point de frappe (112) de la deuxième machine-outil portative (10').
  7. Système selon l'une quelconque des revendications précédentes, caractérisé en ce que la première et la deuxième machine-outil portative (10, 10') présentent chacune un système d'amortissement de frappe (114), qui est configuré de manière identique à l'autre.
  8. Système selon l'une quelconque des revendications précédentes, caractérisé en ce que la première et la deuxième machine-outil portative (10, 10') présentent chacune un carter de transmission (38), les composants mécaniques à l'intérieur du carter de transmission (38) étant identiques à au moins 80 %, notamment à au moins 90 %.
  9. Système selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un diamètre (14') du logement d'outil (12') de la deuxième machine-outil portative (10') est inférieur à 18 mm, notamment à 10 mm, et en ce que le rapport entre un diamètre du tube de guidage (40') et le diamètre du logement d'outil (12') de la deuxième machine-outil portative (10') se situe dans une plage comprise entre 2,8 et 3,4, notamment dans une plage comprise entre 2,9 et 3,1.
EP18729382.4A 2017-06-12 2018-06-01 Machine-outil portative Active EP3638457B1 (fr)

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DE102017209829.5A DE102017209829A1 (de) 2017-06-12 2017-06-12 Handwerkzeugmaschine
PCT/EP2018/064459 WO2018228829A1 (fr) 2017-06-12 2018-06-01 Machine-outil portative

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CN (1) CN110785264B (fr)
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US11059155B2 (en) 2018-01-26 2021-07-13 Milwaukee Electric Tool Corporation Percussion tool
WO2021202968A1 (fr) * 2020-04-02 2021-10-07 Milwaukee Electric Tool Corporation Outil électrique
CN112296393B (zh) * 2020-10-16 2021-05-11 武义县亚太电器有限公司 一种高安全性电钻
JP2022119301A (ja) * 2021-02-04 2022-08-17 株式会社マキタ 打撃工具
JP2022128006A (ja) * 2021-02-22 2022-09-01 株式会社マキタ 打撃工具

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DE19717712A1 (de) * 1997-04-18 1998-10-22 Black & Decker Inc Bohrhammer
GB9910599D0 (en) 1999-05-08 1999-07-07 Black & Decker Inc Rotary hammer
DE10002748B4 (de) * 2000-01-22 2006-05-18 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Sicherheitskupplung
JP3968967B2 (ja) 2000-07-07 2007-08-29 日産自動車株式会社 レシプロ式内燃機関の可変圧縮比機構
EP1584422B1 (fr) * 2004-04-07 2008-10-29 HILTI Aktiengesellschaft Procédé et appareil pour réduire les pointes de pression dans une machine-outil munie d'un système de percussion électromagnétique
DE102004025951A1 (de) * 2004-05-27 2005-12-22 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Bohr- und/oder Schlaghammer
CN1939660B (zh) * 2005-09-30 2011-08-03 苏州宝时得电动工具有限公司 电动工具
DE102007035699A1 (de) * 2007-07-30 2009-02-05 Robert Bosch Gmbh Handwerkzeugmaschine
CN101444909B (zh) * 2007-11-27 2013-03-27 希尔蒂股份公司 具有气动冲击装置的手持式工具机
DE102011075765A1 (de) * 2011-05-12 2012-11-15 Hilti Aktiengesellschaft Handwerkzeugmaschine
CN105856140A (zh) * 2014-09-02 2016-08-17 苏州宝时得电动工具有限公司 电动工具的控制方法及***、电动工具
EP3285966A4 (fr) 2015-04-22 2019-05-01 Milwaukee Electric Tool Corporation Perceuse à percussion

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DE102017209829A1 (de) 2018-12-13
CN110785264A (zh) 2020-02-11
EP3638457A1 (fr) 2020-04-22
CN110785264B (zh) 2023-05-19
US20210170560A1 (en) 2021-06-10
US11279016B2 (en) 2022-03-22
WO2018228829A1 (fr) 2018-12-20

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