EP3638457A1 - Handwerkzeugmaschine - Google Patents
HandwerkzeugmaschineInfo
- Publication number
- EP3638457A1 EP3638457A1 EP18729382.4A EP18729382A EP3638457A1 EP 3638457 A1 EP3638457 A1 EP 3638457A1 EP 18729382 A EP18729382 A EP 18729382A EP 3638457 A1 EP3638457 A1 EP 3638457A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hand tool
- tool
- housing
- guide tube
- eccentric
- 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.)
- Granted
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 37
- 230000005540 biological transmission Effects 0.000 claims abstract description 34
- 230000033001 locomotion Effects 0.000 claims abstract description 29
- 238000009527 percussion Methods 0.000 claims abstract description 27
- 238000013016 damping Methods 0.000 claims description 20
- 230000008878 coupling Effects 0.000 description 70
- 238000010168 coupling process Methods 0.000 description 70
- 238000005859 coupling reaction Methods 0.000 description 70
- 238000013519 translation Methods 0.000 description 9
- 238000003780 insertion Methods 0.000 description 5
- 230000037431 insertion Effects 0.000 description 5
- 230000000903 blocking effect Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 4
- 238000012545 processing Methods 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000001174 ascending effect Effects 0.000 description 2
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 230000035559 beat frequency Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000005553 drilling Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000000284 resting effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
-
- 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
- B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- 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
- the invention relates to a system comprising a first hand tool machine and a second hand tool machine, each with a percussion mechanism, each with a motor, each having a percussion comprehensive gear, which is adapted to transmit a drive movement of the motor to a recorded in a tool holder insert tool, wherein the respective gear have a partially along a working axis identical guide tube, in which a racket is mounted axially movable, wherein the guide tube is rotatably coupled via a first gear unit to the motor and wherein the racket is driven via a piston of a second gear unit linearly oscillating.
- the hand tool is in particular designed to drive an insert tool rotating around and / or striking along a working axis.
- the working axis extends substantially along the longitudinal extent of the first and the second hand tool machine.
- the insert tool may be formed by way of example as a drill or chisel.
- the insert tool is a wearing part which can be detachably fastened in the tool holder.
- the insert tool has an insertion end, which is received in the tool holder of the power tool.
- the insertion ends of insert tools usually have a standardized shaft diameter which 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 comprises an exchangeable drill chuck or a fixed drill chuck.
- a "guide tube identical in regions along a working axis" should be understood to mean in particular a guide tube which is at least 33%, preferably at least 50%, in particular at least 66%, of the length of the guide tube along the longitudinal extension of the hand tool machine identical to another guide tube.
- the inner and / or outer diameter of the guide tube of the first hand tool and of the second hand tool is identical at least partially along the working axis
- the second hand tool machine is identical in a region between the rear end facing away from the tool holder and a control opening or the B-impact damping system and a diameter of the guide tube in the first hand tool by 1.8 times larger than in the second hand tool.
- a “diameter of the tool holder” is to be understood in particular to mean an inner diameter of the tool holder which is adapted to the shank size of the insertion tool. It is proposed that a single impact energy of the second hand tool is mechanically reduced in comparison to a single impact energy of the first hand tool. Advantageously, the second hand tool machine can thereby be easily adapted to a different field of application.
- a “single impact energy” is to be understood as meaning, in particular, the energy which is transferred to the racket during operation of the handheld power tool or which is transferred from the racket to the insertion tool. is preferably reduced by the second gear unit of the transmission.
- the single impact energy of the second hand tool is reduced by at least 10%, in particular at least 17.5%, preferably by at least 25%. In absolute terms, this corresponds to a reduction of the single impact energy with a diameter of the guide tube of about 30 mm of over 0.5 Joule, in particular 1.5 to 2.0 Joule.
- the percussion power of the second hand tool machine is mechanically reduced in comparison to a percussion power of the first hand tool machine.
- the impact frequency of the percussion mechanism of the first hand tool is substantially identical to the beat frequency of the second hand tool.
- crank stroke of the second gear unit of the second hand tool machine is reduced, in particular reduced by 10%, preferably reduced by 15%, preferably reduced by 20%, compared with a crank stroke of the second gear unit of the first hand tool.
- a crank stroke is to be understood in particular 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 the second hand power tool are each driven via an eccentric unit, wherein an eccentricity of the eccentric unit of the second hand tool is smaller than an eccentricity of the eccentric unit of the first portable power tool.
- the eccentric unit is assigned to the second gear unit.
- the eccentric unit is driven about an axis of rotation by the motor.
- the eccentric unit has a transmission element designed as an eccentric pin, which is connected to the piston via a crank element.
- the translation element moves about the axis of rotation on a particular circular path.
- the eccentricity of the eccentric unit results from the distance between the axis of rotation of the eccentric unit and the track on which the transmission element moves.
- an air spring length of the percussion mechanism of the first hand-held power tool differ from an air spring length of the percussion mechanism of the second hand-held power tool, in particular is greater.
- the single impact energy can be reduced to a structurally simple manner by a smaller air spring length of the striking mechanism.
- An air spring length of the percussion mechanism should in particular be understood as meaning a minimum distance between the club and the piston or a distance between the club and the piston at the front, the tool holder facing, reversal point.
- the air spring length can be adjusted by way of example of the shape of the racket, the shape of the piston or the shape of the crank member.
- a bearing distance of the percussion mechanism of the first hand tool machine is equal to a bearing distance of the percussion mechanism of the second hand tool machine.
- a bearing spacing is to be understood in particular as meaning a distance between two regions over which the guide tube of the percussion mechanism is mounted.
- the bearing distance as a distance between an axial or radial bearing and another axial or radial bearing, each supporting the guide tube.
- the bearing distance is formed as a distance between two radial bearings.
- a point of impact of the first hand tool machine is equal to a point of impact of the second hand tool.
- the position of the bat, in particular the rear of the tool holder facing away from, the end of the racket, in the guide tube, while the insert tool is pressed against the processing surface understood.
- both the impact point and the air spring length of the first hand tool machine is identical to the impact point and the air spring length of the second hand tool.
- the first and the second hand tool machine each have a B-impact damping system, which are identical to each other.
- a B-impact damping system is intended in particular to be understood to mean an arrangement of components in the striking mechanism which are designed to damp the recoil of the insertion tool against the impact direction.
- the racket transmits its energy via a bolt element on the insert tool.
- the B-impact damping system is at least partially arranged in the guide tube and comprises at least one damping element, which may be arranged inside and / or outside of the guide tube.
- the mass ratio between the bolt element and the racket in the first hand tool machine is identical to the second hand tool machine, so that the same B-impact damping system can advantageously be optimized both on the first and the second hand tool.
- the first and the second hand tool machine each have a gear housing, wherein the mechanical components within the gear housing to at least 80%, in particular at least 90%, are identical.
- the transmission housing may be formed as an outer housing and / or as an internal housing.
- a diameter of the tool holder of the second hand tool is below 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 tool in a range between 2.8 and 3.4 , in particular in a range between 2.9 and 3.1.
- a particularly powerful hand tool machine can be realized.
- the invention relates to a hand tool with a percussion mechanism, with a motor, comprising a percussion gear, which is adapted to transmit a driving movement of the motor to a recorded in a tool holder insert tool, wherein the transmission comprises a guide tube, in which a racket is mounted axially movable, wherein the guide tube is rotatably coupled via a first gear unit with the motor and wherein the racket is driven to oscillate linearly via a piston of a second gear unit.
- the ratio between a diameter of the guide tube and a diameter of the tool holder is in a range between 2.8 and 3.4, in particular in a range between 2.9 and 3.1.
- a particularly powerful hand tool machine can be realized thereby.
- the diameter of the tool holder is less than 18 mm, in particular 10 mm.
- the invention relates to a hand tool with a percussion mechanism, with a motor, comprising a percussion gear, which is adapted to transmit a drive movement of the motor to a tool holder, wherein the transmission has a guide tube in which a racket mounted axially movable is, wherein the guide tube is rotatably coupled via a first gear unit with the motor and wherein the racket is coupled via a second eccentric unit comprising a comprehensive gear unit with the engine and driven by a piston linearly oscillating.
- an eccentricity of the eccentric unit is adjustable in at least two different positions such that a crank stroke of the second gear unit is changed.
- the single impact energy of the impact mechanism can be adjusted.
- the eccentricity of the eccentric unit is adjustable so that the hammer mechanism is switched off.
- a mode change of the power tool from a chisel mode or a hammer drill mode can be realized in a drilling mode.
- the eccentricity is adjustable such that in the position with the lowest eccentricity of the crank stroke of the second gear unit is reduced such that the racket of the striking mechanism performs no impact movement.
- the eccentricity of the eccentric unit is manually adjustable.
- the adjustment of the eccentricity can be realized mechanically in a simple manner.
- a manual setting is to be understood in particular as meaning that the eccentric unit is coupled to an actuating element, via which the eccentricity can be adjusted by means of a force exerted by a user of the hand-held power tool.
- the eccentricity of the eccentric unit is semiautomatically adjustable.
- the eccentricity can be easily adjusted.
- a semi-automatic setting should in particular be understood as meaning that the eccentricity can be selected by the user of the handheld power tool, but the changeover is controlled by an electronic system of the handheld power tool.
- the eccentricity of the eccentric unit is automatically adjustable.
- a particularly comfortable adjustment of the eccentric unit can be realized thereby.
- An automatic setting is to be understood in particular as meaning that the eccentricity can not be selected or set by the user, but is completely controlled or regulated by an electronic system.
- the eccentric unit has a first eccentric element, which is mounted rotatably about the axis of rotation of the eccentric unit, and a second eccentric element, which is mounted rotatably about the axis of rotation and an adjustment axis.
- the adjustment axis is arranged parallel to the axis of rotation.
- the first and the second eccentric element are driven about the axis of rotation during operation of the power tool.
- the second eccentric element is rotatably connected to the first eccentric element, in particular rotatably mounted on the second eccentric element.
- the distance between the axis of rotation and the adjustment axis is fixed, and thus not changeable.
- the eccentric unit comprises an adjustment unit, which is designed, the second eccentric element about the adjustment axis to turn.
- the eccentricity can be adjusted thereby targeted.
- the adjusting unit is in particular designed to adjust and / or fix the second eccentric element in at least two different positions.
- the setting unit has at least two mutually corresponding adjusting elements, which are designed to produce a non-positive and / or positive connection between the second eccentric element and one of the adjusting elements.
- at least one of the adjusting elements, in particular both adjusting elements, is rotatably mounted about the adjusting axis.
- one of the adjusting elements is designed as an external toothing of the second eccentric element.
- the adjusting element is formed integrally with the second eccentric element.
- the external toothing can be arranged partially or completely on an outer circumference of the second eccentric element.
- one of the adjusting elements is designed as an actuator element which is pivotably and / or linearly movably mounted, wherein the actuator element is connected to the actuator element corresponding to the adjusting element only during a setting process.
- the actuator element is in particular so controllable via an electronic system that an electrical signal of the electronics is converted into a mechanical movement of the actuator element.
- one of the adjusting elements is designed as a ring gear.
- the ring gear is rotatably mounted about the rotation axis.
- the hollow wheel can be driven and / or braked via a drive element.
- the ring gear may be formed as part of a planetary gear.
- the piston is coupled via a crank element with an eccentric pin of the eccentric unit.
- the crank element can be designed, for example, as a connecting rod or as a connecting rod element.
- the eccentric pin is preferably non-rotatably connected to the second eccentric element, and thus rotatable about the axis of rotation and the adjustment axis.
- the invention relates to an overload device for a hand tool, which is adapted to limit a torque transmitted from a motor of the power tool to a tool holder of the power tool, with a first coupling element and a second coupling element, the rotationally fixed to each other via a Overload unit can be coupled, wherein the overload unit is arranged linearly movable between the first and the second coupling element. It is proposed that the overload unit is tiltably mounted in the overload device.
- the wear of the overload device can be significantly reduced thereby.
- the overload device is in particular designed as a coupling, via which a motor shaft of the motor is releasably connected to the guide tube such that a torque of the motor is no longer transmitted to the guide tube above a threshold value.
- the first coupling element is coupled to the motor shaft and the second coupling element to the guide tube.
- the coupling can be done by way of example via a spur gear or a bevel gear.
- the overload device is rotatably mounted about a coupling axis.
- the coupling axis is preferably formed parallel to a drive axis of the motor shaft.
- the second coupling element is in particular rotationally fixedly mounted on a coupling shaft.
- the overload unit is in particular mounted linearly movable relative to the first and the second coupling element.
- the overload unit is preferably mounted linearly movable radially to the coupling axis. Alternatively or additionally, it is also conceivable that the overload unit is mounted to be movable parallel to the coupling axis or obliquely to the coupling axis.
- the overload unit may be formed completely or partially tiltable. In particular, a tilt axis of the overload unit is formed substantially parallel to the coupling axis of the overload device.
- the overload unit comprise an overload element. points, which is acted upon by a spring element with a force.
- the overload element acts on an inner surface of the first coupling element with a force.
- the overload device preferably has a plurality of overload units, in particular six to eight, preferably seven, on.
- the overload units are in particular arranged symmetrically around the coupling axis.
- the overload element is tiltably received in a recess of the second coupling element.
- the overload element is received in the recess of the second coupling element with play.
- the overload element is tiltably received in the recess such that the spring element is guided only axially movable in the overload element.
- the distance between the recess and the overload element varies.
- angles by which the overload unit can be tilted can be predetermined in a structurally simple manner.
- the distance between the recess and the overload element in the direction of the coupling axis in particular increases steadily.
- the recess and / or the overload element are cone-shaped.
- the outer surface and / or the inner surface of the overload element is cone-shaped.
- the term "cone-shaped" should be understood in particular to mean that the inner surface of the recess, or the inner or outer surface of the overload element, extends at least partially at a slight angular offset relative to the linear direction of movement of the overload unit.
- the angular offset may in particular be less than 10 °, preferably less than 6 °, preferably less than 3 °.
- the spring element is tiltably received in the overload element.
- this can tilt both the overload element and the spring element relative to the second coupling element.
- the spring element tilts at a different angle than the overload element during operation of the power tool.
- the spring element is guided exclusively by the overload element.
- the spring element is overturned by at most 95% of the overload element.
- the spring element comprises five resilient windings.
- a particularly compact overload device which at the same time has a high transmissible transmission power, can be realized.
- the spring element has a total number of turns of seven.
- the invention relates to a hand tool machine with an overload device as described above, with a striking mechanism, with a motor, comprising a striking mechanism comprehensive gear, which is adapted to transmit a drive movement of the motor to a tool holder, wherein the transmission is a guide tube in which a racket is mounted axially movable, wherein the guide tube is rotatably coupled via a first gear unit to the motor and wherein the racket is coupled via a second eccentric unit comprising a gear unit coupled to the motor via a piston linearly oscillating drivable.
- the first gear unit has a ratio between height and length in a range between 1.3 and 1.5, in particular in a range between 1.35 to 1.45.
- a compact hand tool with an optimized center of gravity can be realized thereby.
- a diameter of the tool holder is more than 10 mm, in particular 18 mm, and that a ratio between a diameter of the guide tube and the diameter of the tool holder in a range between 1.35 and 2.00, in particular in one area between 1.6 and 1.8, lies.
- a particularly compact and powerful hand tool machine can be realized.
- the invention relates to a hand tool, in particular a hammer drill, with a housing which has at least three housing parts, which are interconnected via housing interfaces, wherein the first housing part via a first housing interface to the second housing part and a second housing interface to the third Housing part is attached. It is proposed that the second housing part is fastened to the third housing part via the first housing interface.
- a cost-effective and compact housing structure can be realized.
- the housing interfaces are in particular designed to fasten at least two housing parts relative to one another in a movable, immovable or rotatable manner to one another.
- the housing interfaces preferably have damping elements which are designed to damp vibrations that occur during operation of the handheld power tool.
- the damping elements may be configured, for example, as elastic or resilient elements, for example a spring element or a rubber ring.
- the housing interfaces each have at least two mutually corresponding connecting elements, which are each assigned to one of the two interconnected housing parts.
- Connecting elements may be formed integrally with the housing parts or as separate components.
- the connecting elements are in particular designed for non-positive and / or positive connection of the housing parts.
- a connecting element of the first housing part is in particular positively connected to a connecting element of the second housing part and with a connecting element of the third housing part.
- one of the connecting elements is separated from the other two connecting elements. menten positively embraced.
- the second housing part is immovably fixed to the first housing part and the third housing part is movably mounted on the first housing part.
- a motor is arranged in the first housing part, arranged in the third housing part electronics and formed the second housing part as a handle.
- the electronics of the power tool is in particular designed to control the power tool.
- the third housing part has a network interface or a battery interface.
- the housing has an outer housing and an inner housing in which a transmission is arranged, wherein at least one of the housing parts is designed as an outer housing.
- the gear can be safely stored by an arrangement of the transmission in an inner housing.
- An inner housing should in particular be understood to mean a housing part which is enclosed at least partially, in particular completely, by a housing part formed as an outer housing.
- At least one of the housing parts is formed from two housing half-shells.
- the housing half-shells can be connected to one another, for example, via a screw connection.
- the hand tool machine is designed as a cordless power tool. Alternatively or additionally, it is proposed that the hand tool machine is designed as a mesh power tool.
- the invention relates to a system comprising a hand tool, in particular a rotary hammer, with a housing having at least three housing parts which are interconnected via housing interfaces, wherein the first housing part via a first housing interface to the second housing part and via a second housing interface the third Housing part is attached, and another hand tool, in particular a hammer drill, with a housing having at least three housing parts which are interconnected via housing interfaces, wherein the first housing part via a first housing interface to the second housing part and a second housing interface to the third Housing part is fixed, wherein the hand tool is designed as a battery hand tool and the other hand tool as a net power tool.
- the first housing part of the hand tool machine is formed identically to the first housing part of the further hand tool machine.
- the same housing part for handheld power tools with different power supplies can be used by the modular housing structure.
- the system be an additional hand tool, in particular a hammer drill, with a housing having at least three housing parts which are interconnected via housing interfaces, wherein the first housing part via a first housing interface to the second housing part and a second housing interface the third housing part is attached, wherein a diameter of a tool holder of the power tool differs from a diameter of a tool holder of the additional hand tool and the first housing part of the additional hand tool is identical to the first housing part of the power tool and the other hand tool.
- the same housing part for handheld power tools with different performance classes can be used by the modular housing structure.
- FIG. 1 shows a longitudinal section of a first hand tool
- 3a shows a longitudinal section of a transmission of the first hand tool
- 3b shows a cross section of an eccentric unit of the transmission of the first
- FIG. 5b shows a perspective view of the eccentric unit according to FIG. 5a
- 6a is a perspective view of a third embodiment of the eccentric unit
- FIG. 6b shows a further perspective view of the eccentric unit according to FIG. 6a;
- FIG. 6c shows a cross section of the eccentric unit according to FIG. 6a
- FIG. 6d shows a further cross section of the eccentric unit according to FIG. 6a;
- FIG. Fig. 7 is an enlarged view of the transmission of Fig. 3;
- FIG. 8b is an enlarged view of an overload unit of the overload device according to FIG. 8a;
- FIG. 8c shows a further enlarged view of an overload unit of the overload device according to FIG. 8a;
- 9a is a side view of a housing of the first hand tool
- 9b is a side view of a housing of the second hand tool
- 9c is a side view of a housing of a third hand tool
- 9d is a side view of a housing of a fourth hand tool
- FIG. 10a shows a longitudinal section through the housing according to FIG. 9a;
- FIG. 10b shows a side view of a housing half shell of the first housing part
- 10c shows a perspective view of a housing half shell of the second housing part
- FIG. 10D shows a side view of a housing half-shell of the third housing part
- FIG. Fig. 10E is a perspective view of the fourth housing part
- Fig. IIa is a schematic view of an alternative second housing part
- 11b shows a further schematic view of an alternative second housing part
- Fig. 11c is a schematic view of another alternative second housing part.
- the first hand tool 10 (see FIG. 1) and the second hand tool 10 ' (see FIG. 2) are designed as cordless hand tool machines.
- the two handheld power tools 10, 10 ' each have a tool holder 12, 12 ' , which differ in their diameter 14, 14 ' from each other.
- the tool holder 12 is designed as a fixed drill chuck and the tool holder 12 ' as an exchangeable drill chuck.
- the first hand tool 10 with an SDS-max tool holder 12 and the second hand tool 10 ' with an SDS-plus tool holder 12 ' is formed.
- the diameter 14 of the SDS-max tool holder 12 is substantially 18 mm and the diameter 14 'of the SDS-plus tool holder 12 ' is substantially 10 mm, resulting in a ratio between the diameter 14 of the tool holder 12 of the first hand tool 10 and the diameter 14 'of the tool holder 12 ' of the second hand tool 10 ' of 1.8 results.
- the third handheld power tool 10 " (see FIG. 9c) and the fourth handheld power tool 10 "' (see FIG. 9d) are in each case designed as power-net machine tools with an SDS-max tool holder 12 and an SDS-plus tool holder 12 ' .
- Fig. 1 is a longitudinal section through the first hand tool 10 is shown.
- the hand tool 10 is designed as a hammer drill.
- the hand tool 10 has a housing 16, which is formed from a plurality of housing parts 18, 20, 22, 24.
- the housing parts 18, 20, 22, 24 are formed as outer housing. It is alternatively or additionally also conceivable that at least one of the housing parts 18, 20, 22, 24 is partially or completely formed as an inner housing.
- a motor 26 is arranged within the first housing part 18.
- the motor 26 is in the variants of the power tool 10, 10 ' as a cordless power tool as a particular brushless DC motor and in the variants of the power tool 10 " , 10 "' as a power hand tool as AC motor, for example as a synchronous motor, asynchronous or universal motor trained.
- the motors 26 of the handheld power tools 10, 10 ' , 10 " , 10 “” are optimized for equal characteristics so that the relationship between speed and torque is substantially identical at relevant operating points
- 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 formed as an inner housing, in particular made of metal Alternatively, it is also conceivable that the transmission housing 38 is at least partially designed as an outer housing.
- the first gear unit 32 is configured to rotatably couple the motor 26 with a guide tube 40 of the hammer mechanism 36.
- the first gear unit 32 comprises an overload device 42, which is designed to limit the maximum torque that can be transmitted by the motor 26 to the guide tube 40.
- the second gear unit 34 is configured to translate the rotational drive movement of the motor 26 into a linear movement of a racket 44, which is mounted and guided linearly movable in the guide tube 40.
- the second gear unit 34 comprises an eccentric unit 46, which has a transmission element 48 designed as an eccentric pin, which has a crank element 50 a piston 52 is connected.
- the piston 52 is guided linearly movable in the guide tube 40.
- the percussion mechanism 36 comprises the guide tube 40, the racket 44 and a bolt element 54, which is likewise guided linearly movably in the guide tube 40 and via which the energy of the racket 44 is transmitted to the insert tool 30.
- the guide tube 40 has a diameter, in particular an inner diameter of 30 mm, whereby a high single impact energy can be realized. This results in the first hand tool 10, a ratio between the diameter of the guide tube 40 and the diameter 14 of the tool holder 12 of about 1.7.
- the handheld power tool 10 comprises a plurality of operating modes which can be set via an operating mode switching element 56.
- the operating mode changeover element 56 has at least three switching positions, one switching position corresponding to a drilling mode, another switching position to a hammer drill mode and yet another switching position to a chisel mode.
- the insert tool 30 is rotationally and translationally movable with the gear 28, in particular with the guide tube 40 and the bolt member 54 is coupled. During operation of the power tool 10, the insert tool 30 rotates about a working axis 58 and / or oscillates along the working axis 58.
- the hand tool 10 extends in its length along the working axis 58.
- the tool holder 12 and at the rear end of the power tool 10 which is designed as a handle 60 third housing part 22 is arranged.
- the handle 60 is pivotally mounted on the first housing part 18 and 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, which is designed as an operating switch for switching on and off of the power tool 10.
- the handheld power tool 10 In its height, the handheld power tool 10 extends essentially flat. parallel to a longitudinal extent of the handle 60 and / or parallel to the longitudinal extent, in particular a motor shaft 66, the motor 26. Above the motor 26, the transmission 28 is arranged. Below the motor 26, an electronics 68 is arranged, which is designed to control the hand tool 10, in particular the motor 26 of the power tool 10, or control. The electronics 68 is arranged in the second housing part 20. At the lower end of the handle 60, a battery interface 70 is arranged, via which a hand tool machine battery bag 72 can be detachably fastened to the second housing part 22 designed as a handle 60.
- the handheld power tool battery pack 72 comprises 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 tool 10 ' is shown.
- the majority of the components installed in the handheld power tool 10 ' are identical to the components of the handheld power tool 10.
- a guide tube 40 'of the second hand tool 10 ' is formed in regions identical to the guide tube 40 of the first hand tool 10.
- the diameter of the guide tube 40 'of the second hand tool 10 ' is identical to the diameter of the guide tube 40 of the first hand tool 10.
- the diameter of the guide tube 40 ' is also 30 mm. This results in the second hand tool 10, a ratio between the diameter of the guide tube 40 ' and the diameter 14 ' of the tool holder 12 ' of 3.0.
- the gear 28 ' of the second hand tool 10 ' differs from the gear 28 of the first hand tool 10 in a few components.
- the percussion mechanism 36 'of the second handheld power tool 10 ' has a different Ches bolt element 54 ' on.
- the second gear unit 34 'of the second hand tool 10 ' has a different crank element 50 ' and an eccentric eccentric unit 46 " .
- the gear 28 and the tool holder 12 of the first hand tool 10 is shown.
- the gear housing 38 has on the underside an opening formed as a drive interface 39, in which the motor shaft 66 of the motor 26 is rotatably mounted.
- the drive interface 39 comprises bearing elements and sealing elements and is standardized for the different variants of the handheld power tools 10, 10 ' , 10 " and 10 " , so that for example both DC motors, in particular brushless DC motors, and AC 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 the second gear unit 32, 34 are coupled to one another with the motor shaft 66.
- the first gear unit 32 is coupled to the motor shaft 66 via a first spur gear 78.
- the first spur gear 78 is associated with the overload device 42, via which the torque from the motor shaft 66 to the clutch shaft 80 is transferable.
- the overload device 42 is in particular pressed onto the coupling shaft 80.
- the coupling shaft 80 is rotatably supported about a coupling axis 81, wherein the coupling axis 81 is arranged substantially parallel to a drive axis 67 of the motor shaft 66.
- a pinion element 82 is pressed, which is assigned to a bevel gear 84.
- the bevel gear 84 also includes a ring gear 86 which is rotatably connected to the guide tube 40.
- the guide tube 40 is rotatably mounted in the housing 16, in particular in the transmission housing 38, via a first and a second bearing arrangement 88, 90.
- the insert tool 30 is rotatable with the guide tube 40 coupled so that the insert tool 30 is rotationally driven.
- the second gear unit 34 is coupled to the motor shaft 66 via a second spur gear 79. Via the second spur gear 79, the torque of the motor shaft 66 is transmitted to an eccentric shaft 92.
- the eccentric shaft 92 is rotatably supported about a rotation axis 93 in the transmission housing 38.
- On the top of the eccentric shaft 92 designed as an eccentric cam eccentric 94 is arranged, wherein the eccentric shaft 92 and the eccentric 94 are preferably formed integrally.
- the eccentric 94 designed as Exzenterpin translation element 48 is firmly connected. For better illustration, the transmission of the rotational movement into a linear movement through the eccentric unit 46 in FIG. 3b is shown from above.
- the crank member 50 is formed as a connecting rod rotatably connected to the transmission member 48 and rotatably connected to the piston 52.
- the translation element 48 is spaced from the axis of rotation 93 of the eccentric unit 46 and rotates about the axis of rotation 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 axis of rotation 93, or the distance between the circular path 100 and the rotation axis 93rd
- the striking mechanism 36 is designed as a pneumatic percussion mechanism.
- the hammer mechanism 36 has a percussion control 104, by means of which it can be put from an idle mode into a working mode. Below the working axis 58, the impact mechanism 36 is shown in the idle mode and above the working axis 58 in the working mode.
- the guide tube 40 has in the area between the racket 44 and the piston 52 control openings 106, via which a pressure equalization between the interior and the outer space of the guide tube 40 can be made.
- 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 acted upon by means of a spiral spring designed as a spring element 110 with a force in the direction of the idle position.
- the power tool 10 To move the power tool 10 from idle mode to work mode To put it, it is pressed with inserted insert tool 30 against a processing surface. Due to the force acting thereon, the insert tool 30, the bolt element 54 resting on the insert tool 30 and the striker 44 resting against the bolt element 54 are displaced axially in the direction of the rear end of the guide tube 40. The position of the racket 44 when the insert tool 30 is pressed is the impact point 112 of the percussion mechanism 36. The axial mobility of the insert tool 30 or of the bolt element 54 is limited by a B-impact damping system 114. The B-Impact damping system 114 is axially movably coupled to the percussion control 104.
- the B-Impact damping system 114 is configured to damp 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 movably mounted in a recess of the guide tube 40.
- a damping element 118 of the B-impact damping system 114 designed as a rubber ring is arranged and connected to the pin element 116.
- the damping element 118 abuts on the control sleeve 108 of the hammer mechanism control 104 and shifts it in the working mode such 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.
- the gear 28 ' and the tool holder 12 ' of the second hand tool 10 ' are shown.
- the single impact energy of the racket 44 is reduced by about 20% reduced crank stroke of the piston 52 by 1.5 to 2.0 Joule.
- the ratio between the diameter of the guide tube 40, 40 ' and the piston stroke in the first hand tool 10 is 1.8, in particular 1.77, and in the second hand tool 10 ' 1.4, in particular 1.44.
- the reduction of the crank stroke of the piston Bens 52 is realized over a reduction of the eccentricity 102 'of the eccentric unit 46 ' relative to the eccentric unit 46 of the first hand tool 10. This is realized in that the translation element 48 is arranged closer to the rotation axis 93 of the eccentric unit 46 ' than in the first hand tool 10.
- the transmission 28 of the first hand tool 10 and the gear 28 'of the second hand tool 10 ' are received in identical gear boxes 38. This is realized in particular by the fact that the gears 28, 28 'are similar to a large extent. In particular, the bearing distance between the two bearing assemblies 88, 90 in both hand tool 10, 10 'is identical.
- the guide tube 40 of the first hand tool 10 along the working axis 58 is partially identical to the guide tube 40 'of the second hand tool 10 ' formed.
- the guide tubes 40, 40 ' are formed identically at least between their rear ends and the control openings 106, preferably at least between their rear ends and the percussion controls 104, preferably between their rear ends and the B-impact damping systems 114.
- the diameter of the guide tubes 40, 40 ' in the region of the piston 52 and in the region of the racket 44 is identical.
- first gear unit 32 of the second hand tool 10 is formed identical to the first gear unit 32 of the first hand tool 10.
- the impact point 112 of the second hand tool 10 ' is identical to the impact point 112 of the first hand tool 10. This is realized in particular by the extended shape of the bolt element 54 'of the second hand tool 10 ' in comparison to the bolt element 54 of the first hand tool 10.
- the mass ratio between the bolt member 54 and the racket 44 is the first Hand tool 10 essentially equal to the mass ratio between the bolt member 54 ' and the racket 44 of the second hand tool 10 ' .
- the same B-impact damping system 114 can be optimized on both hand tool 10, 10 ' .
- the air spring length 120 of the second hand tool 10 ' is identical to the air spring length 120 of the first hand tool 10. This is realized by compensating for the shorter crank stroke by an extended crank element 50 ' such that the distance between the impact point 112 and the front reversal point of the piston 52 is the same.
- FIGS. 5a and 5b show an alternative embodiment of the eccentric unit 46a, wherein the eccentricity 102a of the eccentric unit 46a, unlike the previous eccentric units 46, 46 ', is not fixed but adjustable.
- FIG. 5a shows the eccentric unit 46a in a cross section and in FIG. 5b 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 a rotation axis 93a.
- the eccentric unit 46a also comprises 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 rotatable about the rotation axis 93a and rotatably supported about an adjustment axis 123a.
- the second eccentric element 122a is partially taken up, for example, by the first eccentric element 94a, but alternatively it is also conceivable that the second eccentric element 122a is formed on the first eccentric element 94a.
- a trained as Exzenterpin translation element 48a is rotatably connected to the second eccentric 122a.
- 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 adjust the second eccentric element 122a, in particular the translation element 48a, about the adjustment axis 123a and to set it in at least two different positions, each having a different eccentricity 102a.
- the adjusting unit 124a comprises two mutually corresponding adjusting elements 126a, 128a, which are formed into a positive connection with each other.
- the first adjusting element 126a is formed integrally with the second eccentric element 122a as an external toothing.
- the second adjusting element 128a is designed as an actuator element 130a, which is accommodated by way of example in a linearly movable manner in the housing of the handheld power tool.
- the actuator element 130a has a toothing corresponding to the external toothing of the first adjustment element 126a.
- the toothings of the adjusting elements 126a, 128a are engaged with each other in such a way that a linear movement of the actuator element 130a is transferred into a rotational movement of the second eccentric element 122a about the setting axis 123a.
- the rotational movement of the second eccentric element 122a is limited by a stop 131a between the two adjustable positions.
- the eccentric unit 46a has different eccentricities 102a, as a result of which the crank stroke can advantageously be varied.
- the actuator element 130a can be controlled or regulated automatically or semi-automatically via an electronic system of the handheld power tool.
- the actuator element 130a is mechanically coupled to an operating element, not shown, in order to enable manual actuation of the actuator element 130a.
- FIGS. 6a to 6d show an alternative embodiment of an adjustable eccentric unit 46b.
- 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 rotatable about the rotation axis 93b and the adjustment axis 123b.
- a translation element 48b is rotatably connected to the second eccentric 94b.
- the adjusting unit 124b of the eccentric unit 46b is designed to adjust the eccentric to set 102b in a plurality of different positions between a maximum and a minimum eccentricity 102b.
- the adjustment unit 124b comprises two mutually corresponding adjustment elements 126b, 128b.
- the first adjusting member 126b is formed as an external toothing of the second eccentric member 122b.
- the second eccentric element 122b is designed in particular as a toothed wheel which is rotatably arranged on the first eccentric element 94b.
- the second adjusting member 128b is rotatably supported around the rotation axis 93b in the housing.
- the second adjusting element 128b is in engagement with the first adjusting element 126b via a toothing corresponding to the external toothing.
- the second adjusting member 128b is formed as a ring gear 132b.
- the ring gear 132b encloses both the first and second eccentric elements 94b, 122b. Above the first eccentric element 94b, the ring gear 132 is engaged with the second eccentric element 122b designed as a gear wheel, 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 via a front-side pinion with the ring gear 132b.
- the drive element 134b can be driven and / or braked via a drive unit (not shown), which for example comprises a motor.
- the ring gear 132b is independently drivable by the first eccentric element 94b via the drive element 134b.
- the eccentricity 102b can be adjusted via a relative movement of the ring gear 132b to the first eccentric element 94b.
- the ring gear 132b moves during the hammering operation of the power tool at the same rotational speed as the first cam member 94b so that the eccentricity 102b of the cam unit 46b is constant during the hammering operation.
- the eccentricity 102b is varied during impact operation.
- the drive element 134b may be controlled such that the eccentricity 102b preferably changes periodically to produce a variable percussion 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 in which the second eccentric element 94b can be adjusted between the positions 136b, 138b can be determined by the number of teeth of the toothings of the adjusting elements 126b, 128b be determined.
- the transmission element 48b is arranged substantially centrally on the rotation axis 93b, so that the eccentricity 102b is essentially zero and no crank stroke is generated by the eccentric unit 46b in this position.
- the adjustment unit 124b can thereby be designed to switch off a percussion mechanism of the handheld power tool.
- the eccentric unit can be designed in another way, by way of example as described in US Pat. No. 6,055,582.
- the overload device 42 is designed such that a high transmissible transmission power can be realized with a small size and weight.
- the overload device 42 comprises a first coupling element 140 and a second coupling element 142, which are non-rotatably coupled to one another 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 decoupled from the second coupling element 142 if the maximum torque is exceeded.
- the first and the second coupling element 140, 142 In the coupled state, the first and the second coupling element 140, 142 have the same speed, whereas in the decoupled state, the rotational speed of the first coupling element 140 differs from the rotational speed of the second coupling element 142.
- the first coupling element 140 is formed as a part of the spur gear 78.
- the first coupling element 140 has on its circumferential outer surface a spur gear toothing, which meshes with the motor shaft 66.
- the second coupling element 142 is rotatably connected to the coupling shaft 80.
- the second coupling element 142 has recesses 145, which extend substantially radially and in each of which an overload unit 144 is arranged to be linearly movable.
- the overload unit 144 comprises an overload element 146 and a spring element 148, which act on the overload element 146 with a force.
- 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 height 150 and length 152 of the overload device 42 is in a range between 0.18 and 0.22.
- Embodiment about 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 not more than 10%.
- the diameter of the ring gear 86 exceeds the length 152 of the overload device 42 by approximately 5%.
- the short length 152 of the overload device 42 and a very compact first gear unit 32 can be realized.
- 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 about 1.45.
- Fig. 8a is 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, that the second coupling element 142 and the overload unit 144 rotatably coupled to each other 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 acted upon by the spring element 148 radially to the coupling axis 81 with a force.
- 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 includes seven locking segments corresponding to the number of recesses, each having an ascending and a descending ramp.
- the locking segments are formed symmetrical, so that the slope of the ascending ramp is identical to the slope of the descending ramp.
- the rotational movement of the first clutch element 140 is associated with the rotational movement of the second clutch element 142. pelt.
- this can ensure that the hand tool 10 does not rotate about the working axis 58 in the event of blocking of the insert tool 30.
- very high forces act on the overload device 42, which can lead to a very high wear and thus a short life of the overload device 42.
- FIG. 8b the area marked in FIG. 8a is shown in an enlarged view.
- the compact design is realized 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, wherein five turns are resilient.
- the spring element has a spring stiffness of at least 50 N / mm with a dynamic stroke of up to 1.5 mm.
- the spring element 148 bears axially against a flat stop surface 164 of the second coupling element 142 and against the overload element 146, in particular 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 both in the coupled and in the decoupled state in the recesses 145, while the head 160 only is partially disposed in the recess 145 in the decoupled state.
- the guide ratio between the length of the spring element 148 and the length of the region in which the spring element 148 is guided by the overload element 146 is about 1.13 in the coupled state.
- the spring element 148 is guided exclusively by the overload element 146.
- a guide of the spring element 148 through the second coupling element 142 does not take place.
- 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 disposed in this groove 166.
- the spring element 148 abuts against the second coupling element 142 in the region of the groove 166.
- the spring element 148 has a constant diameter, in particular outer diameter.
- the overload element 146 is tilted linearly movable in the recess 145 added.
- the distance between the recess 145 and the overload element 146 along a longitudinal extent 168 of the overload element 146, which extends in particular in the coupled state of the overload device 42 coaxial with a radial extent 83 of the coupling axis 81 not constant.
- the distance between the recess 145 and the overload element 146 in the direction of the coupling axis 81 increases steadily, whereby tilting is possible.
- the recess 145 is straight and the overload element 146 is formed obliquely or conically.
- the surface of the recess 145, against which the overload element 146 rests is formed essentially parallel to the longitudinal extent 168 of the overload element 146.
- the term oblique is to be understood here as meaning that the outer surface of the overload element 146 has a slight angular offset from the longitudinal extension 168, which is approximately 5 ° by way of example.
- the recess 145 is formed obliquely or that the recess 145 is oblique and the overload element 146 are straight.
- the overload element 146 is also formed obliquely or conically on its inner surface.
- the spring element 148 is conical.
- the guide arms 147 are formed obliquely or conically both on their inner side facing the spring element 148 and on their outer side facing the recess 145.
- the overload device 42 is shown in the decoupled state.
- the overload element 146 experiences a force against the force of the spring element 148 via the latching profile 162.
- the overload element 146 moves into the recess 145 in such a way that the head 160 also partially moves in the recess 145 is arranged, and on the other hand, the overload element 146 is tilted.
- the overload element 146 is tilted such that the radial extent 83 and the longitudinal extent 168 of the overload element 146 have an angular offset of approximately 4 °.
- the handheld power tools 10, 10 ' , 10 " and 10 “' are each shown in a side view.
- the housings 16, 16 ' , 16 “ , 16 “' of the handheld power tools 10, 10 ' , 10 “ , 10 “' are based on a common housing concept, so that the first housing part 18 of the handheld power tools 10, 10 ' , 10 " , 10 "'. is identical.
- 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 gearbox 28.
- the motor 26 and the gearbox 28 are arranged substantially completely within the space defined by the housing half-shells of the first housing part 18.
- the first housing part 18 comprises air openings 170, which are designed to supply the engine 26 and / or the transmission 28 with cooling air.
- an operating mode switching element 56 can be arranged in an opening 172 on the top of the first housing part 18.
- the gear housing 38 is mounted via bearings 174. In particular, the gear housing 38 is supported exclusively by the first housing part 18.
- the first housing part 18 is connected via three housing interfaces 178, 180, 182 to the second housing part 20, the third housing part 22 and the fourth housing part 24.
- the second housing part 20 is immovably fixed to the first housing part 18 via the first housing interface 178.
- the second housing part 20 is formed as an electronics housing, in which the electronics 68 is arranged.
- the second housing part 20 also includes air openings 183, which are designed to cool the electronics 68.
- the second housing part 20 comprises two housing half-shells, which are connected to one another via a screw connection.
- the third housing part 22 designed as a handle 60 is movably fastened to the first housing part 18 via the second housing interface 180.
- the third housing part 22 has two housing half-shells, which are connected to one another via a screw connection.
- the fourth housing part 24 is fixed immovably 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.
- the housing 16 'of the second hand tool 10 ' is shown. Since the first handheld power tool 10 and the second handheld power tool 10 ' essentially differ from one another by the tool receivers 12, 12 ' , the first, second and third housing parts 18, 20, 22 of the two the hand tool 10, 10 'formed identical to each other.
- the fourth housing part 24 'of the second hand tool 10 ' differs from the fourth housing part 24 of the first hand tool 10 in particular by its compactness and length.
- the housing 16 'of the second hand tool 10 ' on the fourth housing part 24 ' to the shape of the tool holder 12 ' can be adjusted.
- the housing interface 182 are formed in the hand tool 10, 10 ' identical to each other.
- the third hand tool 10 " and in Fig. 9d, the fourth hand tool 10 '' is shown.
- the third hand tool 10 " is designed as a network variant of the first hand tool 10 and the fourth hand tool 10 "' as a network variant of the second hand tool 10 ' .
- the third and fourth hand tool 10 " , 10 “' each have a different second housing part 20 " and a different third housing part 22 " on.
- the hand tools comprise 10 ", 10"'are each a network interface 188, which is arranged at the lower end of the handle 60 "formed the third housing part 22".
- a power cable 189 emerges from the housing 16 " , 16 “' via an opening in the third housing part 22 " , via which the handheld power tools 10 " , 10 “' can be supplied with energy. 180, 182 in the hand tool 10, 10 ' , 10 “ , 10 “' identical to each other.
- another hand tool machine has identical housing parts 18, 20, 24 and only the third housing part 22 by an alternative battery interface 70 for receiving an alternative handheld power tool battery pack, which for example has a different number of battery cells differs.
- FIG. 10a-e the housing interfaces 178, 180, 182 are shown on the basis of the housing 16 of the first hand tool 10.
- Fig. 10a shows a A longitudinal section through the housing 16 and FIGS. 10b to 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 are positively connected to one another.
- 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 few connecting elements 184, which are formed as a circular receptacle.
- the connecting elements 184 are formed integrally 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 formed as a pin-shaped extension which extends from the inner surface of the second housing part 20 perpendicular.
- the connecting element 186 extends substantially perpendicular to the longitudinal and vertical extension of the hand 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 positively enclosed by the connecting elements 184, or received.
- the second housing interface 180 pivotally secures the third housing part 22 to the first housing part 18.
- the handle is pivotably attached to the first housing part 18 via three axes of rotation 190, 192, 194.
- the corresponding connecting elements 196, 198 are designed as rotary bearing elements which support the damping unit 62.
- the connecting elements 196, 198 are integrally formed with the housing parts 18, 22.
- the damping unit 62 is designed as a spring-loaded connecting rod element.
- the third housing part 22 has a further formed as a circular receptacle connecting element 200 which is form-fitting connectable with the connecting element 186 of the second housing interface 178 is formed.
- the connecting element 186 of the second Housing part 20 positively received 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 engage in one another in a form-fitting manner.
- the connecting element 202 is associated with the first housing part 18 and formed as an extension, which extends from the inner surface of the first housing part 18 inwardly.
- the fourth housing part 24 at a front side
- End portion 206 of the two housing halves of the first housing part 18 is enclosed in such a way that the extensions 202 engage in the formed as openings corresponding connecting elements 204 of the fourth housing part 24.
- the fourth housing part 24 is thus radially fixed by the first housing part 18 and axially fixed by the connecting elements 202 of the first housing part 18 and around the working axis 58 in the direction of rotation.
- the handheld power tools 10, 10 ' , 10 " , 10 “” which are constructed essentially as described above, to have an alternative second housing part 20c
- the alternative second housing part 20c comprises, in particular, electronics 68 and a Additional functional units 208c are shown in Figures 11a to 11c.
- the second housing part 20c can be connected to a further housing part of the handheld power tool via a housing interface (not shown)
- the second housing part 20c can be of one-piece pot construction 11a
- the additional functional unit 208c is embodied as a light-emitting element 210c
- the light-emitting elements 210c can, for example, be a bright light for illuminating a processing surface or a colored light for displaying a status the hand Send out a machine tool.
- the lighting elements 210c are arranged forward, in particular in the machining direction. Alternatively or additionally, it is also conceivable that at least one luminous element 212c is arranged laterally. Preferably, the side luminous element 212c is configured to display a status. It is conceivable, for example, that the triggering of a safety function, caused by blocking of the tool, a low battery level, too high an operating temperature, etc. can be displayed via the light-emitting elements 210c and / or the light-emitting element 212c.
- the additional functional unit 208c is formed as a coupling means 214c for an accessory device (not shown).
- the coupling means 214c is formed as a pair of guide rails for a dust extractor for a hammer drill.
- the hand tool in particular the second housing part 20c, can be connected to an accessory device via the coupling means 214c.
- the additional functional unit 208c is formed as a rangefinder 216c, which measures the distance to the processing surface by means of laser distance measurement.
- further additional functional units 208c such as, for example, a projection unit for projecting information, patterns, a water balance or a running time counter or an anti-theft module, are conceivable.
- the invention relates to a system of two hand power tools, each having a housing having at least two housing parts which are fastened together via a housing interface, wherein the first housing part is fastened via a first housing interface to the second housing part.
- the second housing part of the first portable power tool differ from the second housing part of the further portable power tool by an additional functional unit.
- the first housing part is designed in each case as a motor housing and the second housing part in each case designed as an electronics housing.
- this can be equipped with a new and additional function by means of minor interference with the housing design of the power tool.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017209829.5A DE102017209829A1 (de) | 2017-06-12 | 2017-06-12 | Handwerkzeugmaschine |
PCT/EP2018/064459 WO2018228829A1 (de) | 2017-06-12 | 2018-06-01 | Handwerkzeugmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3638457A1 true EP3638457A1 (de) | 2020-04-22 |
EP3638457B1 EP3638457B1 (de) | 2024-01-10 |
Family
ID=62530211
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18729382.4A Active EP3638457B1 (de) | 2017-06-12 | 2018-06-01 | Handwerkzeugmaschine |
Country Status (5)
Country | Link |
---|---|
US (1) | US11279016B2 (de) |
EP (1) | EP3638457B1 (de) |
CN (1) | CN110785264B (de) |
DE (1) | DE102017209829A1 (de) |
WO (1) | WO2018228829A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11059155B2 (en) | 2018-01-26 | 2021-07-13 | Milwaukee Electric Tool Corporation | Percussion tool |
WO2021202968A1 (en) * | 2020-04-02 | 2021-10-07 | Milwaukee Electric Tool Corporation | Power tool |
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 |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 (de) * | 2004-04-07 | 2008-10-29 | HILTI Aktiengesellschaft | Verfahren und Einrichtung zur Reduktion von Druckspitzen in einer Handwerkzeugmaschine mit elektropneumatischem Schlagwerk |
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系统、电动工具 |
EP3285966A4 (de) | 2015-04-22 | 2019-05-01 | Milwaukee Electric Tool Corporation | Bohrhammer |
-
2017
- 2017-06-12 DE DE102017209829.5A patent/DE102017209829A1/de active Pending
-
2018
- 2018-06-01 US US16/613,789 patent/US11279016B2/en active Active
- 2018-06-01 CN CN201880038954.8A patent/CN110785264B/zh active Active
- 2018-06-01 EP EP18729382.4A patent/EP3638457B1/de active Active
- 2018-06-01 WO PCT/EP2018/064459 patent/WO2018228829A1/de unknown
Also Published As
Publication number | Publication date |
---|---|
DE102017209829A1 (de) | 2018-12-13 |
EP3638457B1 (de) | 2024-01-10 |
CN110785264A (zh) | 2020-02-11 |
CN110785264B (zh) | 2023-05-19 |
US20210170560A1 (en) | 2021-06-10 |
US11279016B2 (en) | 2022-03-22 |
WO2018228829A1 (de) | 2018-12-20 |
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