EP3317051A1 - Machine-outil portative - Google Patents

Machine-outil portative

Info

Publication number
EP3317051A1
EP3317051A1 EP16733490.3A EP16733490A EP3317051A1 EP 3317051 A1 EP3317051 A1 EP 3317051A1 EP 16733490 A EP16733490 A EP 16733490A EP 3317051 A1 EP3317051 A1 EP 3317051A1
Authority
EP
European Patent Office
Prior art keywords
gear
transmission
locking
locking device
stage
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
Application number
EP16733490.3A
Other languages
German (de)
English (en)
Other versions
EP3317051B1 (fr
Inventor
Peter Seiler
Johannes Steimel
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.)
Festool GmbH
Original Assignee
Festool GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Festool GmbH filed Critical Festool GmbH
Priority to EP19219478.5A priority Critical patent/EP3674038B1/fr
Publication of EP3317051A1 publication Critical patent/EP3317051A1/fr
Application granted granted Critical
Publication of EP3317051B1 publication Critical patent/EP3317051B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/008—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with automatic change-over from high speed-low torque mode to low speed-high torque mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket

Definitions

  • the handheld machine tool The handheld machine tool
  • the invention relates to a hand-held power tool, in particular a screwdriver and / or drill, with a drive motor for driving a transmission drive of a transmission having a transmission output for driving a tool holder of the hand-held machine tool and a first gear stage and a second gear stage wherein the transmission comprises a first locking device for locking a transmission element forming a blocking transmission element of the first transmission step and a second locking device for locking a transmission element of the second transmission step forming a blocking transmission element, wherein the transmission step with the respectively locked blocking transmission element generates a torque from the transmission drive to the transmission Output transmits, wherein a direction of rotation of the drive motor is switchable and depending on the direction of rotation of the drive motor, the first gear stage or the second gear stage, a torque from the transmission drive to the transmission output via wearing.
  • a hand-held machine tool of this type in the form of a screwdriver is explained for example in DE 35 29 992 A1.
  • the locking devices are freewheels, one of which locks in response to a respective direction of rotation of the drive motor and thus activates the associated gear stage.
  • the screwdriver is not practical.
  • both gear stages a speed change cause between gearbox drive and gearbox output and one of the two gear stages causes a reversal of direction between the gearbox drive and the gearbox output.
  • the transmission ensures that despite the shifting of the one gear stage in the other gear stage of the transmission output always rotates in the same direction, so there is no reversal of direction of rotation on the side of the output. It is thus expediently provided that the first gear stage and the second gear stage drive the output in mutually opposite directions of rotation of the drive motor in the same direction of rotation.
  • the first gear stage may, for example, be a so-called plus gear, in the second gear stage a so-called minus gear.
  • a negative gear causes, for example, a reversal of direction from its drive side to its output side, a plus gear keeps the direction of rotation.
  • a screw with always the same direction of rotation can be screwed into a workpiece, although the transmission switches.
  • there is a change in torque and speed between the drive side and the driven side that is, for example, a high speed of the drive motor can be converted into a relatively low speed at the transmission output in each of the gear stages.
  • the first gear stage expediently has a first gear ratio and the second gear stage has a second gear ratio, which differs from the first gear ratio, between drive and output.
  • the first gear stage and the second gear stage each have a speed change between the drive and output of the transmission is present. Of the The output and the drive are therefore not directly coupled with the same speed.
  • a gear stage should thus advantageously be understood to mean that in the gear stage, a torque and a rotational speed between the drive side and output side of the gear stage are changed.
  • the transmission is a toothed gear, wherein at least a partial embodiment as a friction gear or roller gear is possible.
  • the transmission preferably comprises a planetary gear or a planetary gear or is designed as a planetary gear or a planetary gear.
  • the first gear stage and the second gear stage expediently form components of a planetary gear or epicyclic gearbox.
  • first gear stage and the second gear stage can form components of a planetary gear, while an upstream or downstream further gear stage, in particular a
  • Non-switchable or non-switched gear stage although also as a similar transmission, such as planetary gear, can be configured. But it is also possible that this further gear stage has a different type of transmission, such as a gear transmission, in which the drive and output are not coaxial.
  • a preferred embodiment of the invention provides that the transmission or the hand-held power tool as a whole has at least one gear wheel which meshes with both lockable by the first locking means and the second locking means lock gear elements.
  • This design is particularly compact.
  • the blocking gear elements for example, actively drive the gear, so to speak, so that it can transmit a torque to the transmission output.
  • the locking gear elements form a support for the gear or support the gear, so that the gear can roll on each locking gear element when it assumes its blocking position. This is particularly easy to implement, for example, in a planetary gear.
  • An advantageous embodiment of the transmission according to the invention provides that it has a planetary stage.
  • Planet wheels of the planetary stage are rotatably mounted on a planet carrier, which has an output.
  • the planet gears are driven by a drive wheel.
  • the drive wheel is for example arranged directly on an output shaft of the drive motor or rotatably connected thereto.
  • the drive wheel for the planetary gears in turn is coupled to a driven gear stage.
  • the drive wheel may be arranged on an output of a planetary stage.
  • the output of the planet carrier in turn, for example, rotatably connected to the transmission output, rotationally coupled or the like.
  • the output of the planet carrier can be connected directly to the tool holder and drive it directly. But it is also possible that the output of the planet carrier via at least one further gear stage, such as a planetary gear stage, drives the tool holder.
  • a particularly preferred embodiment of the invention provides that the planetary gears have a first, the drive wheel associated Wälz Vietnamese bemesser and a second, different from the first pitch circle diameter Wälz Vietnamese bemesser.
  • This second Wälz Vietnamese bemesser example is smaller or larger than the first Wälz Vietnamese bemesser so that it causes a gear ratio.
  • the planet gears can already help to cause a speed change from the drive side to the driven side, in particular that the first gear stage and the second gear stage are each designed as a kind of genuine gear stages.
  • the planetary gears are designed as so-called stepped planets or stepped planet wheels.
  • the planetary gears can also have at least one further, for example at least a third, pitch circle diameter.
  • the drive wheel for the planetary gears may for example be a sun gear engaging between the planetary gears. It is also possible that the drive wheel for the planetary gears is a ring gear, in which the planetary gears are arranged or that receives the planetary gears.
  • the drive wheel is for example, as mentioned, rotatably coupled or fixedly connected to the output shaft of the drive motor. The planetary gears can therefore be driven from radially outward by the ring gear or from radially inward by the sun gear.
  • An advantageous embodiment of the invention provides that intermesh with the planet gears meshing gears of the first gear stage and the second gear stage with respect to the axis of rotation of the planetary gears at least partially.
  • the gears may include, for example, a sun gear and a ring gear, which have the same longitudinal position with respect to the axis of rotation, which will be explained in more detail below. It should be noted, however, that of course also in relation to the axes of rotation of the planetary gears arranged side by side gears can mesh with the planetary gears.
  • the gear wheels that mesh with the planetary gears it is preferably rotatably coupled with the locking devices gears, which are each blocked by the locking devices.
  • the gears can form so to speak supporting elements for the planetary gears.
  • a preferred embodiment of the invention provides that the planetary gears with a lockable by the first locking device locking sun gear and a lockable by the second locking device locking ring gear, so that by locking the locking sun gear or the ring gear, the first or the second gear stage is activated.
  • the locking sun gear is, for example, radially inward, the locking ring gear radially outward with respect to a central axis of rotation of the transmission.
  • the ratchet sun gear and the ratchet ring gear may have the same or at least about the same longitudinal positions with respect to an axis of rotation of the planet gears or a rotation axis of the transmission or a rotation axis of the ratchet sun gear have or at least partially interlock. This makes the transmission particularly compact.
  • the blocking sun gear is coupled to a support wheel or has a support wheel, which is arranged with respect to a rotational axis of the locking sun gear next to the blocking ring gear and / or the same or about the same outer circumference as the locking ring gear has.
  • the Abstützrad and the ring gear are, for example, radially outwardly connected to the associated locking device or rotationally coupled. A locking device can thus pass through the support wheel radially inward to the locking sun so to speak.
  • the support wheel and the ratchet sun gear may be in one piece. But it is also possible that the Abstützrad and the
  • Block sun gear are two wheels that are for example firmly connected to each other or via other wheels, for example, at least one gear, in particular a planet or more planetary gears, or the like are rotationally coupled together.
  • a further advantageous embodiment provides that the locking sun gear and the blocking ring gear with respect to a rotational axis of the locking sun gear have the same or approximately the same longitudinal position.
  • a step-like arrangement can be made, in which the blocking sun gear protrudes, so to speak, before the support wheel and engages in an interior of the locking ring gear.
  • the blocking sun gear and the blocking ring gear can have exactly the same longitudinal position with respect to the axis of rotation of the blocking sun gear or can also have a somewhat longitudinal offset position.
  • the lockable by the first locking device locking gear element of the first gear stage or the lockable by the second locking device locking gear element of the second gear or both are preferably designed as a support wheel, in particular as a ring gear or sun gear on which at least one gear, especially a planetary gear, the first or the second gear stage rolls. It should be noted that it is advantageously provided in the case of a blocking device that it makes the blocking transmission element, so to speak, into a support element or support wheel upon a blocking of the associated blocking gear element of a gear stage, against which a further gear element of the respective gear stage can be supported or displaced.
  • the locking device activated by the locking of a locking gear element, the respective associated gear stage.
  • the respective gear stage then transmits a torque from the transmission drive to the transmission output.
  • the gear unit assigned to this locking gear expediently runs freely with or is not supported with respect to the housing of the transmission or the hand-held power tool, so that it does not transmit torque from the gear drive to the gearbox output.
  • At least one lockable by a respective locking device blocking gear element is designed as a ring gear or has a ring gear.
  • this ring gear is virtually coupled or connected radially outside with a locking device, so that this locking device ensures optimal support.
  • a torque acting on the locking device from the ring gear is comparatively small.
  • an active locking device is provided as a locking device, which can be blocked, for example, by means of an electromagnet or other actuator.
  • the hand-held power tool advantageously has a controller that is designed to switch such active or actuator-provided locking devices.
  • the controller may for example be designed so that it actively switches the locking devices, so that the one locking device associated with her blocking gear member locks while the other locking device releases the associated locking gear element and vice versa.
  • the control can, so to speak, alternately deactivate one gear stage and activate the other gear stage.
  • a preferred embodiment of the invention provides that the first locking device and / or the second locking device comprises a freewheel or is configured as a freewheel.
  • a freewheel has the advantage that it can rotate freely coupled with him locking gear element of the respective gear in the one direction of rotation, but blocked in the opposite direction of rotation o- supports or blocks.
  • the advantage here is that the gear stages are activated so to speak by itself when the direction of rotation of the drive motor is switched. An active control of the locking devices is not necessary.
  • a freewheel also has a self-reinforcing barrier action.
  • At least one of the freewheels forms a radially outermost component or radially outer component of the transmission. But it is also possible that one or both of the freewheels forms a radially inner component of the transmission.
  • a freewheel it is possible for a freewheel to be arranged between an output shaft of the drive motor and a respective blocking gear element of the first gear stage or the second gear stage.
  • the first locking device has a first freewheel and the second locking device has a second freewheel, wherein the freewheels have a reverse direction in the same direction and a direction of freewheeling in the same direction.
  • both freewheels can be switched over very comfortably with regard to their locking direction and release direction of rotation.
  • a blocking direction of at least one blocking device in particular a freewheel
  • the locking device or the freewheel locks in the first direction of rotation and in a second rotational direction releases a rotational movement of the lockable locking gear member of the first or second gear stage, and these directions of rotation are reversible, so that the locking device o- the freewheel after switching in the first direction of rotation allows a rotational movement of the lockable locking gear member, but blocks or blocks in the second direction of rotation.
  • a freewheel it is provided in such a freewheel that it has a loaded by a spring element in the direction of its locking position blocking element.
  • the spring element for example an elastic buffer, a rubber element or an element made of elastic plastic, a spring, in particular a helical spring or leaf spring, thus loads the blocking element in the direction of its blocking position or clamping position.
  • a spring element or, more generally, such a spring arrangement ensure, for example, that the blocking element already occupies the blocking position, ie provides for blocking of the blocking device, before the drive train or the transmission starts up.
  • the blocking gear element can thus already be supported starting from the standstill of the transmission with respect to the locking direction on the freewheel.
  • a spring element can serve to guide a respective blocking element.
  • a preferred embodiment provides that a blocking element or the aforementioned locking element of the freewheel is loaded with respect to a revolution or rotation direction in opposite locking positions in each case by a spring element.
  • a locking device and a freewheeling at least one locking device such as a freewheel or other locking device
  • the directions of rotation, in which the locking device or the freewheel blocks the blocking gear element or blocks or supports or releases the blocking transmission element can be switched to the locking device.
  • Hand machine tool in particular the transmission, is provided.
  • the operator can cause by means of a single switching operation that the transmission output and thus the tool holder have a different direction of rotation.
  • the locking devices of the first locking device and the second locking device can be switched simultaneously by a single actuating element.
  • the actuating element can act, for example, on blocking elements of the locking devices and hold them in one locking device in a release position and actuate in the other locking device in the direction of a clamping position or fixing position.
  • the actuating element is for example an operating element or switching element, with which an electrical switching device can be switched.
  • the switching device then acts, for example, on actuators or actuators, which are assigned to a respective locking device or arranged on the locking device.
  • an actuating element which acts directly on the two locking devices or actuates them directly is advantageous.
  • An advantageous embodiment of the invention provides in connection with the switching device for switching the locking devices that it is coupled to a control of the drive motor, so that the control switches when switching the reverse direction of the first locking device and the second locking device, the direction of rotation of the drive motor. For example, can be realized that after switching the direction of rotation of the output, the transmission again in the previously set gear stage, for example, the first gear stage or the second gear stage, starts.
  • An expedient embodiment of the invention which can also represent an independent invention in connection with the preamble of claim 1, provides that the blocking gear elements are provided with mutually opposite rotary mechanisms. have directions when the first locking device and the second locking device release the respective Sperrget ebe element. Thus, the locking gear elements can be locked or released by the associated locking devices with the same direction of rotation.
  • a manual control element can, so to speak, act on the locking devices directly or on the basis of fewer components in order to switch them with regard to their locking direction and release direction of rotation.
  • An alternative embodiment may also provide that at least one or more locking devices or all locking devices are arranged on a shaft or a rotating element.
  • the first and second gear stage at least a third gear stage, for example, a reduction gear, downstream or upstream.
  • the first and the second gear stage forms an input gear stage of the transmission, which is another Reduction stage is downstream.
  • the at least one further gear stage may be a shiftable or a non-shiftable gear stage.
  • first and second gear stage from the drive of the hand-held machine tool ago are the first gear stages, which at least one, preferably further gear stages are followed, realize a speed reduction compared to the first two gear stages.
  • the hand-held power tool has a first gear stage and second gear stage upstream or downstream gear arrangement with at least two gear stages.
  • These gear stages can be manual or motorized or both switchable.
  • the manual power tool has a manually operable and / or operable by a motor actuator switching device for switching between the at least two gear stages of the gear assembly.
  • gear arrangement is advantageously provided that it forms a reduction gear or a reduction stage.
  • the first and the second gear stage may have a different gear type than the third and further gear stage, so that, for example, a combination of planetary gear and bevel gear is possible.
  • first and the second gear stage comprise or form a planetary gear. It is also expedient if the third and / or at least one optional further gear stage, in particular switchable gear stage, are also part of a planetary gear.
  • the at least one third gear stage, optionally further gear stages is a manual or motor-operated gear stage or are.
  • the at least one third stage may have, for example, two or more, in particular three or four, shiftable gears or gear ratios.
  • the at least one third, suitably third and fourth, gear stage can be switched, for example, by an electric or pneumatic actuator.
  • the electrical actuator may, for example, an electromagnetic drive, for example, a coil or the like having.
  • a control of the manual power tool for driving a motor actuator for switching the at least one third gear stage between a first gear ratio and at least one second gear ratio is configured and provided.
  • the controller has a corresponding output stage or control outputs.
  • the hand-held machine tool according to the invention has a striking mechanism.
  • this striking mechanism is connected between the tool holder and the gearbox with the switchable gear stages.
  • the manual power tool has a spindle stop, in particular in the region of the gear.
  • the spindle stop it is possible, for example, that the gear output is fixed against rotation in order to change a tool.
  • the drive motor is preferably a brushless motor.
  • the drive motor is an electronically commutated motor.
  • the brushless motor has the advantage that it has a low mass. The direction of rotation can thus be switched quickly and effectively. It is possible that the switching of the direction of rotation is almost unnoticeable, so to speak, ie that at the transmission output no rotational interruption, at most a slight reduction in speed or increase, is noticeable.
  • a brushless motor is understood to mean a motor without brushes or sliding contacts, ie a motor without electrical contact between the moving rotor and the fixed stator.
  • the drive motor is a three-phase motor or a brushless DC motor or synchronous motor
  • the brushless motor also has no preferred direction of rotation, so that he has in opposite directions of rotation optimal efficiency or optimal performance. Unlike so-called commutator motors, the brushless motor has no fixed distortion between the collector and the brushing apparatus. Such a so-called distortion is realized on the software side in the brushless motor.
  • the hand-held machine tool preferably a screwdriver, drill or a combination thereof.
  • the inventive hand-machine tool for example, a router, a grinder, a polishing device, a saw or the like or includes such.
  • other embodiments of a hand-held machine tool are advantageous in which an automatic shift of the transmission is advantageous.
  • Hand machine tool has a control for switching the direction of rotation of the drive motor in response to a speed of the transmission output or the drive motor and / or a torque of the drive motor or a torque at the transmission output.
  • the controller can detect a torque and / or a rotational speed of the drive motor and, depending on this, change the direction of rotation of the drive motor in order to switch in this way between the first gear stage and the second gear stage.
  • the controller reverses the direction of rotation.
  • a speed-dependent switching is advantageous, ie that the drive motor, for example, when its exceeding or falling below a predetermined speed changes its direction of rotation and is thus switched between the gear stages.
  • the controller can also switch the direction of rotation of the drive motor as a function of a rotational speed and / or a torque at the output of the transmission or an output shaft and thus switch between the transmission stages of the transmission.
  • an output shaft can be coupled.
  • corresponding speed sensors and / or torque sensors are arranged on the output or on the output shaft, the signals of which evaluates the control and used to control the drive motor and / or for controlling the transmission, which will be explained in more detail below.
  • the controller detects rotational speed and / or torque on the basis of one or more sensors on the drive motor and / or an output stage driving the drive motor and drives the drive motor with respect to rotational speed and / or torque and / or rotational direction as a function of this and / or as explained in more detail below, another transmission stage of the transmission switches or controls for switching.
  • this control not only switches the first and second gear stage, but can also switch other gear stages, for example gear stages of one of the first and second gear stage downstream or upstream gear assembly.
  • a control concept can expediently provide for the controller to switch the first and second gear stage as well as the further gear stages of the gear arrangement as a function of torque and / or rotational speed of the drive motor and / or the tool shaft or the output of the gearbox.
  • the controller can switch the direction of rotation of the drive motor, thus switching between the first and second gear stage and also the downstream or upstream gear assembly additionally switch between the gear stages or switching stages.
  • a Drehmonnenter upset is in a drive motor, for example via a current detection without special effort feasible.
  • a speed detection and / or torque detection in the drive motor can be done for example via the drive motor driving output stage or power electronics.
  • the controller for controlling and / or regulating the drive motor and / or for switching the transmission in dependence on a predetermined as a function of a predetermined or predetermined target speed and / or target speed and / or by a predetermined or predefinable setpoint torque and / or maximum torque is configured.
  • the hand-held power tool expediently has corresponding input devices, for example a speed setting element or a torque setting element or both, via which an operator can make inputs.
  • a control module or control module for example, a corresponding software provided to adjust the speed and / or torque output and / or direction of rotation of the drive motor.
  • the controller in particular the control module or control module, is expediently also configured to switch, for example, the already explained switching actuator or the switching device as a function of speed, torque or direction of rotation.
  • Conventional control methods with feedback of an actual variable (rotational speed, torque or the like), observer principles or the like which are known per se can be used for the control.
  • the controller operates, for example, based on a suitable software for control and / or control or a program module.
  • the control for setting a maximum torque and / or maximum speed at the output of the transmission or the output shaft is configured.
  • Corresponding adjusting elements are preferably provided on the hand-held machine tool.
  • a maximum Torque of 25 Nm soft screwing, eg with a screw in wood up to 45 Nm (hard screwing, eg with a screw in metal) be specifiable.
  • the control can realize for example also a speed limitation and / or torque limitation The control steers the drive motor and / or the gearbox accordingly.
  • FIG. 1 shows a side view of a hand-held machine tool
  • Figure 2 is a front view of a transmission of
  • FIG. 3 shows the view corresponding to FIG. 2, wherein a front locking device of the transmission assumes a blocking position
  • Figure 4 shows the view corresponding to Figure 3, wherein the locking device a
  • FIG. 5 shows a cross section along a section line A-A through the transmission according to FIG. 2, FIG.
  • FIG. 6 shows a cross section along a section line B-B through the transmission according to FIG. 2,
  • FIG. 7 shows a circuit diagram of a control of the hand-held machine tool according to FIGS. 1 to 6,
  • Figure 8 is a schematic side view of a transmission variant of a
  • FIG. 9 shows a schematic side view of a further transmission variant of a hand-held machine tool
  • Figure 10 shows another transmission with a gear part similar to that shown in Figure 5, additionally with a switchable gear arrangement in a sectional view similar to Figure 5 in a first switching position of the switchable gear assembly, and
  • Figure 1 the transmission of Figure 10 in a second switching position of the gear assembly.
  • a hand-held power tool 10 has a housing 1 1, in the interior of which a drive train 20 is arranged.
  • the hand-held power tool 10 is, for example, a screwdriver, drill or both.
  • the housing 1 1 can be comfortably grasped at a handle portion 12 by an operator. In an upper housing portion 13, the gun-like angle to the handle portion 12 extends, the drive train 20 is received.
  • a front housing section 14 extends in front of the handle section 12, which can be gripped by one hand, for example, wherein the handle section 12 and the housing section 14 are connected to one another by a lower housing section.
  • a hand-held power tool according to the invention is network-connected, ie, for example, can be connected to an electrical supply network or is a battery-powered machine, ie represents a mobile device.
  • a switch 15 is provided, with which a drive motor 16 of the hand-held power tool 10 can be turned on or off.
  • a speed of the hand-held power tool 10 can be turned on or off.
  • a tool holder 18 for receiving a tool 19 is provided, for example, a plug-in receptacle, a chuck or the like.
  • the tool 19 is, for example, a drill, a screwdriver bit or the like.
  • grinding or polishing machine is of course another tool appropriate, for example, a polishing tool, grinding tool or milling tool or the like.
  • the drive motor 16 drives the tool holder 18 via a gear 30. Between the gear 30 and the tool holder 18, a striking mechanism 21 may be connected, so that with the hand-held power tool 10 even a
  • Impact operation for example, for drilling holes, is possible.
  • the drive motor 16 drives the transmission 30 on the basis of its motor shaft 22.
  • the transmission 30 has a switching stage 31 with switchable first and second gear stages 41 and 42.
  • the switching stage 31 is followed by a translation stage 32, which further reduces, for example, an output speed of the switching stage 31.
  • the translation stage 32 may be, for example, a reduction stage.
  • the transmission 30 is designed, for example, as a planetary gear.
  • the transmission 30 can be driven via a drive shaft, for example the motor shaft 22.
  • a drive wheel 33 is arranged on the motor shaft 22.
  • the drive wheel 33 drives the switching stage 31.
  • the drive wheel 33 forms a transmission drive 25.
  • the drive wheel 33 is a sun gear 34 that drives transfer wheels 35.
  • the transmission wheels 35 are, for example, planet wheels 36, which are rotatably mounted on a planetary carrier 37 on planetary axles 40.
  • the planetary axles 40 are for example rotatably mounted on the planetary carrier 37 or the planetary gears 36 are rotatably mounted on the planetary axles 40. It can, for example, sliding bearings, ball bearings or needle roller bearings or other bearings between the planetary gears 36 and the planetary axles 40 or the planetary axles 40 and the planet carrier 37 may be provided.
  • the planet gears 36 mesh with a first pitch circle diameter 38 with the drive wheel 33rd
  • another, second pitch circle diameter 39 of the planet gears 36 is smaller than the pitch circle diameter 38, which contributes to a gear ratio.
  • the planet gears 36 mesh with a ring gear 45 and a sun gear 46.
  • the ring gear 45 is disposed radially outwardly with respect to the planetary gears 36 and surrounds them annularly.
  • the sun gear 46 is provided in the center of the planet gears 36, so to speak.
  • the ring gear 45 is assigned to the first gear stage 41 and the sun gear 46 to the second gear stage 42.
  • the ring gear 45 forms a blocking gear element 43, the sun gear 46 a blocking gear element 44.
  • a respective blocking gear element 43 or 44 is blocked by locking devices 61 or 62 of a switching arrangement 60, it forms a support element for the transmission wheels 35, in the present case the planetary gears 36.
  • the respectively locked blocking transmission element 43 or 44 switches, as it were, the respective first and second gear stages 41, 42 active.
  • a ratchet gear member 43, 44 is not locked by the associated locking means 61, 62, it can rotate freely so that it does not provide support for the transmission wheels 35.
  • An unlocked blocking gear element 43, 44 switches the associated first and second gear stage 41, 42 inactive. Under active and inactive should be understood That a torque can be transmitted from the drive side to the output side.
  • the blocking gear element 43 is arranged with its radially outer circumference, so to speak, directly on or next to the blocking device 61.
  • This also has a radially outer support region, namely in the form of a Abstützrads 47 which is connected to the sun gear 46 or in one piece.
  • the support wheel 47 is connected to the sun gear 46 through a connecting disc and / or spokes 47A.
  • the Abstützrad 46 and the lock gear member 43, so the ring gear 45, have the same radial outer circumferences.
  • a passage opening 48 is provided, through which the motor shaft 22 is connected to the drive wheel 33.
  • the switching stage 31 drives via a driven gear 49 to the translation stage 32.
  • the translation stage 32 is configured as a planetary stage 50.
  • the output gear 49 is driven by the planet carrier 37 or in one piece with this.
  • the output gear 49 protrudes in front of the planet carrier 37.
  • the planetary gears 51 are arranged in the interior of a ring gear 54 which is fixed relative to the housing 1 1 of the hand-held power tool 10 or a transmission housing 90 of the transmission 30.
  • the ring gear 54 is fixed in place, for example, on a housing portion 93 of the gear housing 90. Consequently, therefore, the planet gears 51 roll on the inner circumference of the ring gear 54 from.
  • the planetary gears 51 are rotatably supported, for example, on the planetary axles 53.
  • the planetary axles 53 have an additional function, namely by coupling the planetary carrier 52 with an output shaft 54 of the transmission 30 in a torque-proof manner.
  • the planetary axles 53 protrude on opposite sides in front of the planet carrier 52, wherein on the one hand the planetary gears 51 rotatably support, on the other hand a transmission element 56 for the output shaft 55 rotatably couple or are firmly connected thereto.
  • the transmission element 56 receives, for example, a shaft portion 57 of the output shaft 55 or is fixedly connected to this shaft portion 57.
  • the output shaft 55 is rotatably supported, for example, on bearings 59 on a portion 91 of the transmission housing 90.
  • a tool section 58 which has the tool holder 58 on its end face, protrudes in front of a front side 92 of the gear housing 90.
  • the transmission housing 90 is closed by a cover 95.
  • the lid 95 has a passage opening for the motor shaft 22 or other drive shaft.
  • the transmission 30 can be advantageously encapsulated, may have seals or the like, for example, at an opening on the front side 92, where the output shaft 55, the transmission housing 90 penetrates.
  • the two locking devices 61, 62 are each designed as freewheels.
  • the power flow or the torque transmission from the transmission drive 25, for example, from the drive wheel 33 or the motor shaft 22, to a transmission output 25, for example, the output gear 49 or the output shaft 58 of the transmission 30 can by a simple reversal of the direction of rotation of the drive motor 16 between see the gear stage 41 and the gear stage 42 are switched.
  • the direction of rotation of the Ant ebsmotors 16 is quickly switchable, especially because the drive motor 16 in an advantageous embodiment of the invention, a so-called brushless motor, such as electronically commutated motor is.
  • the locking device 62 releases the lock gear member 44, so that no power flow is possible through the second gear 44.
  • the sun gear 46 turns free.
  • the other inhibitor 61 then operates, i. It locks the associated support member or blocking gear element 43, namely the ring gear 45.
  • the transmission wheels 35 in this case the planetary gears 36, at the stationary with respect to the gear housing 90 ring gear 45 roll and thus a power flow or torque transmission from the transmission drive 25 for Gearbox output 26 allow.
  • the gear stages 41, 42 each provide a torque ratio and speed change between on the one hand the transmission drive 25 and on the other hand the transmission output 26 ready.
  • a simple reversal of rotation of the drive motor 16 is thus a different speed of the tool holder 18 and / or a different torque output to the tool holder 18 can be realized.
  • the operator can actively switch the direction of rotation of the drive motor 16 for this purpose.
  • a controller 80 of the hand-held power tool 10 to automatically effect the reversal of the direction of rotation, for example as a function of the torque and / or rotational speed of the drive motor 16.
  • the controller 80 could be an analog controller that monitors its torque output with a simple current monitoring, for example, of the drive current leading to the drive motor 16, thus switching the direction of rotation accordingly.
  • a digital control is preferred, for example by means of corresponding digital circuits, in particular a microprocessor 81.
  • the latter works on the basis of a software program 86, which is stored in a memory 82 which the processor 81 can read out.
  • the processor 81 for example, an output stage 83 to drive the drive motor 16 to control.
  • the output stage 83 contains, for example, power electronics.
  • the controller 80 receives signals, for example, from the switch 15 or a Drehbaumeinstellelement 23, with which a speed of the drive motor 16 can be predetermined by the operator.
  • the controller 80 changes the direction of rotation of the drive motor 16, for example, so that the transmission 30 switches back, for example, from the second gear stage to the first gear stage.
  • the controller 80 reversely changes the rotational direction of the drive motor 16, so that the transmission 30 shifts from the first gear stage to the second gear stage, so that the drive motor 16 can rotate at a lower speed.
  • the locking devices 61, 62 are, so to speak, sandwiched between the blocking gear elements 43 and 44 on the one hand and a housing section 94 of the gear housing 90.
  • the blocking devices 61, 62 thus form, as it were, radially outer components of the transmission 30.
  • tions 61, 62 are arranged radially outward, they are also easily accessible to external intervention, such as for switching the respective reverse direction, accessible.
  • the two shut-off devices 61, 62 which are switched off as freewheels, can be shifted in relation to their blocking direction and freewheeling direction.
  • the locking devices 61, 62 include a common support ring 63, which could be described as a freewheel ring.
  • each locking device 61, 62 it would also be readily possible for each locking device 61, 62 to be designed as a separate freewheel device, i. that there are no common components.
  • the support ring 63 is fixed relative to the transmission housing 90.
  • support body 64 in particular bolts or the like, between the inner circumference of the gear housing 90, so the housing portion 94, and the outer periphery of the support ring 63 is positively inserted and hold the two components form-fitting together.
  • the support ring 63 has at its inner circumference rotationally offset a plurality, for example three, freewheel recesses 65, in each of which a locking element 68 or 69, in particular a roller or a pin, a respective locking device 61 is 62 out.
  • the locking devices 61 have mutually separate locking elements 68, 69, so that they can have opposite direction of freewheeling in and locking directions.
  • the blocking elements 68, 69 are mounted between the outer peripheries of the locking gear elements 43, 44 and the inner circumference of the support ring 63 in the region of the respective freewheel recesses 65.
  • the blocking elements 68, 69 of a locking device 61 or 62 are in the freewheel recesses 65, the respective locking device 61 or 62 is in free-running. However, if the locking elements 68, 69 are moved in the direction of the clamping slope in or constrictions 66 or 67, the locking device 61, 62 is locked. The associated blocking gear element 43, 44 is then blocked by the arranged on its outer circumference locking elements 68, 69, which are located in one of the clamping bevels 66 or 67 and supported on the support ring 63, with respect to a rotation about the rotation axis D, so that the blocking gear member 43, 44 can serve to support the planet gears 36 and thus the respective gear stage 41 or 42 is active.
  • the blocking direction or free-wheeling direction of a respective locking device 61, 62 is switchable.
  • a switching device 70 is provided, which is easily actuated by a single, manual actuator 71 by an operator.
  • the actuating element 71 is configured, for example, as a projection in front of a switching element 72 designed as a ring, for example, which is rotatable about the axis of rotation D.
  • pin-like guide elements 73 which are also referred to below with 73a and 73b, in the direction of the locking elements 68, 69 before, with a respective locking element 68, 69 is arranged between pairs opposite guide elements 73.
  • the blocking elements 69 are adjusted in the direction of the clamping bevels 66, so that the blocking device 61 blocks or blocks the supporting element or blocking gear element 44 in a direction of rotation D1.
  • the guide elements 73b hold the blocking elements 69 in the freewheel recesses 65.
  • the direction of rotation D2 thus corresponds a freewheeling direction F1, the direction of rotation D1 a blocking direction S1 of the locking device 62 in the position according to Figures 3 or 4.
  • each have a spring element 75 is provided between the guide elements 73 and the locking elements 68, 69 each have a spring element 75 is provided.
  • the spring elements 75 bias the blocking elements 68, 69 in the direction of the blocking position, i. in the direction of the clamping bevels 66, 67 into it.
  • the locking elements 68, 69 are already loaded in the direction of the locking position, so that the blocking function or from supporting function of the locking gear elements 43, 44 is available as directly as possible.
  • the locking elements 68, 69 expediently decoupled from each other movably mounted.
  • a decoupling ring 74 between the locking elements 68, 69 is arranged.
  • the locking direction and the freewheeling direction of the locking devices 61, 62 can be reversed in opposite directions, namely by the switching device 70. Namely, if the actuating element 71 is actuated about the axis of rotation D, make the guide elements 73 with this rotational movement, so that starting from a central position approximately corresponding figure 2 in relation to the rotational axis D rotationally offset position, for example, a position for clockwise or a position for counterclockwise rotation of the tool holder 18 are adjustable.
  • the blocking direction S1 and the freewheeling direction F1 can be reversed in opposite directions.
  • the guide elements 73a hold the locking elements 69 in the freewheeling position, which then corresponds to the direction of rotation D1.
  • the locking gear member 44 then rotate freely in the direction of rotation D1, opposite thereto, in the direction of rotation D1, however, it is prevented by the locking device 62 at its rotation, so locked.
  • one of the locking elements 69 is shown in a blocking position in dashed lines, in which is applied to the clamping slope 67, which is a reverse direction S2 equivalent.
  • the position of the guide elements 73a according to FIG. 4 in dashed lines corresponds to a freewheeling position FIG. 2.
  • the controller 80 adjusts the direction of rotation of the drive motor 16 as a function of the position of the switching device 70 for clockwise or anti-clockwise rotation so that it switches to clockwise rotation or vice versa in a gear stage occupied before switching the direction of rotation 41 or 42 starts.
  • a sensor 85 is arranged on the switching device 70 in order to detect their respective switching position.
  • the sensor 85 is, for example, an electrical contact, a non-contact contact or the like.
  • an inductive, optical or capacitive measuring element may be provided as a sensor, but also an electrical contact switch or the like.
  • the first gear stage 41 is a negative gear
  • the second gear 42 is a plus gear, so that by a simple reversal of the drive motor 16 in the transmission 30, the gear stages 41 and 42 are switchable, but so that no reversal of rotation is connected to the transmission output 26.
  • This concept can also be used in transmission types that are not designed as a planetary gear, which is still clear from Figures 8 and 9.
  • the drive motor 16 drives a first shift stage 141 and a second shift stage 142 of a transmission 130, for example via a motor shaft 122, which at the same time represents a transmission drive 125.
  • Both switching stages 141 and 142 cause a speed change and torque change between on the one hand the gear drive 125 and on the other hand, the transmission output 126, on which, for example, directly the tool holder 18 can be arranged.
  • the transmission output 126 yet another gear stage is arranged or this gear output 126 is arranged on a gear stage, not shown, for example, a reduction stage.
  • Locking devices 161, 162 are arranged on the motor shaft 122, which could easily also be referred to as a transmission shaft in the region of the gearbox 120. These could be in the simplest case freewheels, but also switchable locking devices, the reverse direction and release direction of rotation or freewheeling direction can be switched, so for example by an electric actuator, which is controlled by the controller 80.
  • the locking means 161 and 162 are provided between blocking gear members 143 and 144. When a respective locking device 161 or 162 is locked, it takes its associated locking gear member 143, 144. In a direction opposite thereto, however, the rotation is opposite direction locking mechanism 143 or
  • the blocking gear element 143 is, for example, a toothed wheel or drive wheel 146, which meshes with a transmission wheel 135.
  • the transmission wheel 135 is non-rotatably connected to an output shaft 155, which has the tool holder 18 at its free end or drives it via an unillustrated transmission.
  • the gear stage 141 represents a so-called negative gear.
  • the blocking gear member 144 is, for example, a ring gear 145th , with the inner circumference of the transmission wheel 135 meshes.
  • a plus gear is realized.
  • the ring gear has
  • the transmission 130 is very compact, because on one and the same drive wheel 135 both locking gear elements 143, 144 act directly.
  • a switching device 170 is shown as an example of a manually or electrically operable switching device for switching the locking directions or freewheeling direction in the locking devices 161 and 161.
  • Their actuating element 171 acts, for example, on locking elements 168 and 169 of the locking devices 161, 162 similar to the guide elements 73 of the switching device 70.
  • the switching device 171 must turn in opposite directions, since the locking gear elements 143, 144 must have an opposite direction of freewheeling, so once the gear stage 141 and the other time the gear stage 142 is inactive.
  • the actuating element 171 is rotatably mounted about an axis of rotation 176, so that it can act in opposite directions on the locking elements 168, 169.
  • a transmission 230 is provided, which is likewise designed such that no reversal of the direction of rotation takes place between its transmission drive 225 and its transmission output 226 when the drive motor 16 rotates in opposite directions.
  • a motor shaft 222 which may also constitute a transmission shaft
  • coaxial and juxtaposed locking means 261, 262 are arranged, the gear stages 241 and 242 are assigned.
  • the locking means 261 and 262 carry on its outer periphery locking gear elements 243, 244, of which upon rotation of the motor shaft 222 in one direction, a blocking gear member 243 is taken, the other locking gear member 244 freely rotates, while in the opposite direction of rotation, the locking gear member 243 freely rotatable is while the blocking gear member 244 is driven by the motor shaft 222.
  • the blocking gear elements 243, 244 are, for example, gears.
  • the blocking gear elements 243, 244 are designed, for example, as drive wheels 245, 246.
  • the drive wheel 245 drives via a transmission wheel 248 to a transmission wheel 235, which is provided for driving the tool holder 18.
  • the transmission wheel 235 is rotatably mounted on an output shaft 255.
  • the tool holder 18 is provided directly on the output shaft 255.
  • the output shaft 255 could also be designed to drive a further gear stage and / or an impact mechanism.
  • Another transmission wheel 247 is also rotatably connected to the output shaft 255 and serves to drive.
  • a first gear stage 241 is active, which realizes a total of a so-called plus gear.
  • the transmission wheel 248 realized with the locking gear member 243 and the drive wheel 235 each have a minus gear, so that a total of a plus gear is available.
  • the second gear stage 242 is designed as a minus gear.
  • a powertrain 320 according to FIGS. 10 and 11 comprises a transmission 330, which is constructed in a similar manner to the transmission 30 or its gear stage 31 with respect to a shift stage 331.
  • actuation concept (with a switching device 370) in a switching arrangement 360, which corresponds functionally to the switching arrangement 60, and the output side of the transmission 330, where instead of a simple planetary stage or a simple reduction gear as in the embodiment of FIGS 5 and 6, a switchable Gear assembly 350 is provided.
  • a switchable Gear assembly 350 is provided.
  • the switching stage 331 drives with its transmission output 25 to a switching stage 332, which can work as a reduction stage in terms of speed reduction, but does not have to.
  • the drive motor 16 drives a drive wheel 333 via the motor shaft 22.
  • a receptacle 333a on the drive wheel 333 or a shaft member connected to this for receiving and rotationally fixed coupling of the motor shaft 22 is provided.
  • the drive wheel 333 forms a sun gear 334 which meshes with planet gears 336.
  • the planetary gears 336 advantageously form transmission wheels 35.
  • the planet gears 336 are rotatably mounted on a planet carrier 337.
  • planetary axes 40 are rotatably mounted on the planet carrier 37 or the planet carrier 336 are rotatably mounted on the planetary axles 40.
  • the planet gears 336 have different pitch circle diameters 38, 39 as the planetary gears 36. With the pitch circle diameter 38, the planet gears 336 mesh with the sun gear 334, while the smaller pitch circle diameter 39 provides that the planet gears 336 engage a ring gear 345, thus comb or the ring gear 345 can take-along.
  • the switching stage 331 has a first gear stage 341 (corresponding to the gear stage 41) and a second gear stage 342 (corresponding to the gear stage 42), between which the switching stage 331 is switchable based on a reversal of the direction of rotation of the drive motor 16.
  • the planetary gears 336 are also supported so to speak radially inward, namely can roll on a sun gear 346, which forms part of a blocking gear member 344.
  • the blocking gear element 344 corresponds to the blocking gear element 44 and has a passage opening 48 for the motor shaft 22.
  • the switching arrangement 360 comprises a blocking device 361 for blocking or releasing the blocking transmission element 343 and a blocking device 362 for blocking or releasing the blocking transmission element 344.
  • Locking elements 368, 369 shown schematically in FIG. 11 are based on a supporting ring or freewheel ring 363 (similar to the components 68 , 69 and 63) and are preferably loaded by spring elements 375 visible in FIG. 10 (corresponding to the spring elements 75).
  • the respective direction of rotation, in which the blocking devices 361, 362 block or release can be switched over.
  • the actuator 371 protrudes radially outward in front of a transmission housing 390 of the transmission 330, so it can be easily grasped by the operator.
  • the actuator 371 is rotatably mounted on the support ring or freewheel ring 363 or passes through this.
  • the actuator 371 is provided on a housing portion 394 of the gear housing 390, in which the switching stage 331 is received.
  • the actuator 371 is rotatably connected to the switching element 372.
  • a portion 374 of the example rod-shaped or annular actuator 371 is coupled to the switching element 372.
  • the switching element 372 is, for example similar to the switching element 72 annular. In contrast to the switching element 72, however, the switching element 372 is arranged between the gear stages 341, 342 and between the blocking gear elements 343, 344. For example, a protrusion 372a engages an intermediate portion between the ring gear 345 and the support gear 347 of the ratchet gear member 344. Similar to the Getnebegehause 90 and the gear 390 on its side facing the drive motor 16 side by a lid, here a lid 395, closed. On a side facing away from the cover 395, next to the housing portion 394, there is a further housing portion 393, which receives the gear assembly 350, that is, the switching stage 332. The housing section 393 is closed by a cover 391, on whose front side or front side 392 the output shaft 55 is coupled to the tool holder 18.
  • the tool shaft 18 is driven by the gear stage or shift stage 332, which in turn is in turn coupled to the transmission output 26 of the switching stage 31.
  • the gear output 26 includes a driven gear 349, which is for example fixedly connected to the planet carrier 337, for example, is integral therewith.
  • the output gear 349 forms a sun gear with which planet gears 351 of the gear assembly 350 mesh.
  • the planet gears 351 are rotatable with respect to a planetary carrier 352, for example, by being rotatably supported on planetary axles 353 or by the planetary axles 353 being rotatably supported on planetary carriers 352.
  • a ratchet wheel 354, for example a ring gear, of the gear arrangement 350 rotatably couples the planet wheels 351 to the planet carrier 337.
  • the planet carrier 337 has a toothing 337a on its outer circumference, which engages with an internal toothing of the planetary gear Ratchet 354 can get. Also in engagement with this gearing or lying next to this gearing is a respective planetary gear 351st
  • the switching position is adjusted according to Figure 1 1, comb the planetary gears 351 with the internal teeth of the ratchet wheel 354, so roll at this from.
  • the ratchet wheel 354 in turn is rotationally fixed with respect to the transmission housing, for example by means of an external toothing 354a of the ratchet wheel 354, which engages with an internal toothing 354b on the housing 390, for example, the lid 391.
  • the internal toothing 354b is radially inward, the external toothing 354a radially outward.
  • the switchable gear arrangement 350 can be switched manually, for example by an actuating element 310, which is displaceably mounted in a receptacle 31 1 of the gear housing 390.
  • the actuating element 310 is coupled in terms of movement by means of a coupling element 312 to the switching wheel 354, but could also be fixedly arranged on the switching wheel 354.
  • the coupling element 312 includes, for example, pins, brackets or the like other components, which allows a power transmission from an outside of the transmission case 390 in the interior thereof, where the switching wheel 354 is arranged.
  • the receptacle 31 1 forms a sliding bearing or a sliding receptacle, in which the actuating element 310 is received linearly displaceable.
  • the actuating element 310 is coupled in motion or in one piece with a manually engageable actuating handle 313, for example a ring or slider.
  • the actuating handle 313 projects, for example, in front of the housing 1 1 of the hand-held machine tool 10, so it is easy to grasp.
  • An alternative or supplementary drive concept or setting concept for the switching wheel 354, that is to say a concept for switching the gear arrangement 350, represents an actuator 387, for example an electromagnet, an electric motor or the like (a pneumatic drive is also possible).
  • the actuator 387 is configured and provided for an adjustment of the switching wheel 354, that is to say a switching element of the gear arrangement 350, between at least two switching positions.
  • the actuator 387 can shift the indexing wheel 354 back and forth between the switching positions according to FIGS. 10 and 11.
  • the actuator 387 is driven, for example via an electrical switch 24a on the housing 1 1 of the hand-held power tool 10.
  • the actuator 387 is housed protected in the interior of the transmission housing 390.
  • the representation of the actuator 387 is to be understood as an example.
  • the controller 80 is preferably designed to control the activation of the actuator 387. For example, it has a switching output 388 for switching the actuator 387. In Figure 7 is indicated.
  • the controller 80 can thus automatically switch the gear stage or shift stage 331, for example, and advantageously also the shiftable gear arrangement 350 or the shift stage 332.
  • the gear stage or shift stage 331 for example, and advantageously also the shiftable gear arrangement 350 or the shift stage 332.
  • sensors can also be provided on the output area, which interacts with the controller 80.
  • a sensor 87 for detecting rotational speed and / or torque and / or rotational direction or the like, for example a tachometer, a torque detection, may be provided on the tool shaft or output shaft 55.
  • a sensor 88 for example, an optical sensor, a Hall sensor or the like, the drive motor 16, for example, detect its torque and / or direction and / or speed.
  • a sensor 89 in particular for speed detection and / or torque detection and / or rotational direction detection, may be provided at the input of the transmission 30, 330, for example on the motor shaft 22.
  • the sensors 87, 88, 89 report their respective sensor signals via the input interface 84 of the controller 80, which adjusts, for example, the speed and / or direction of rotation of the drive motor 16 by means of its software program 86 in order to switch the transmission 30, 330 in this way. Based on the signals of the sensors 87,1888, 89, the controller 80 but the actuator 387 control.
  • the sensor signals of the sensors 87, 89, 88 can also be used to control the drive motor 16 and / or to control and in particular also the transmission 330, in particular its switching stage 332, to switch.
  • an operator can, for example, specify a desired maximum speed or setpoint speed SD of the output shaft 55.
  • a desired maximum speed or setpoint speed SD of the output shaft 55 For example, the operator can specify a maximum speed of 2000 to 4000 rpm for a drilling operation, and a maximum speed of 500 to 2000 rpm for a screwing operation.
  • an optional torque setting element 24 for example a rotatable adjusting element, a slide or the like
  • the operator can, for example, specify a desired maximum torque or setpoint torque SM on the output shaft 55.
  • a desired maximum torque or setpoint torque SM on the output shaft 55.
  • a speed control or torque control may be advantageous, for example, in a milling cutter or saw.
  • a touch-sensitive display can be provided, which displays the set values SM and / or SD.
  • a control module 86a of the software program 86 can, for example, based on the maximum values or target values SM and / or SD and the feedback of the set values, namely the actual values, the sensors 87, 88, 89 supply, the drive motor 16 and / or drive the power amplifier 83 and / or rules. Furthermore, the control module 86a can also control the actuator 387 in accordance with these values via the switching output 388 in accordance with the switching of the gear stage 332.
  • the controller 80 controls the actuator 387 to shift the transmission 332 from the shift position in which the shift 332 does not realize speed reduction relative to the transmission output 26 (FIG ), in the switching position in which the gear stage 332 acts as a reduction gear ( Figure 1 1), ie the position at which the planet gears 351 roll in the ring gear 354.
  • the planetary axes 353 or 53 may be part of a spindle stop, i. that a rotational blocking on the output side of the gear 30, 330 readily at this point is feasible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Toys (AREA)

Abstract

L'invention concerne une machine-outil portative (10), en particulier une visseuse et/ou une perceuse, comportant un moteur d'entraînement (16) entraînant une entrée (25) d'une transmission (30) qui présente une sortie (26) entraînant un porte-outil (18) de la machine-outil portative (10), et un premier étage de transmission (41) et un second étage de transmission (42). La transmission présente un premier dispositif de verrouillage (61) servant à verrouiller un élément de transmission du premier étage de transmission (41) formant un élément de transmission à verrouillage (43), et un second dispositif de verrouillage (62) servant à verrouiller un élément de transmission du second étage de transmission (42) formant un élément de transmission à verrouillage. L'étage de transmission muni de l'élément de transmission à verrouillage respectivement verrouillé transmet un couple de rotation de l'entrée (25) à la sortie (26) de la transmission, le sens de rotation du moteur d'entraînement pouvant être commuté et, selon le sens de rotation du moteur d'entraînement (16), soit le premier étage de transmission (41), soit le second étage de transmission (42) transmet un couple de rotation de l'entrée (25) à la sortie (26) de la transmission. Selon l'invention, un des deux étages de transmission provoque une inversion du sens de rotation entre l'entrée (25) et la sortie (26) de la transmission.
EP16733490.3A 2015-06-30 2016-06-28 Machine-outil portative Active EP3317051B1 (fr)

Priority Applications (1)

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EP19219478.5A EP3674038B1 (fr) 2015-06-30 2016-06-28 Machine-outil manuelle

Applications Claiming Priority (2)

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DE102015110504.7A DE102015110504A1 (de) 2015-06-30 2015-06-30 Hand-Werkzeugmaschine
PCT/EP2016/065048 WO2017001423A1 (fr) 2015-06-30 2016-06-28 Machine-outil portative

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EP19219478.5A Division EP3674038B1 (fr) 2015-06-30 2016-06-28 Machine-outil manuelle
EP19219478.5A Division-Into EP3674038B1 (fr) 2015-06-30 2016-06-28 Machine-outil manuelle

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Publication number Priority date Publication date Assignee Title
EP3335839B1 (fr) * 2016-12-16 2019-05-01 Festool GmbH Machine-outil portative
CN109849177A (zh) * 2019-04-10 2019-06-07 陈晓清 一种混凝土管抹光增强装置
US20220314415A1 (en) * 2019-05-02 2022-10-06 Festool Gmbh Attachment for a hand-held power tool
SE2130369A1 (en) * 2021-12-17 2023-06-18 Atlas Copco Ind Technique Ab Power tool and load-responsive power transmission for a power tool

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Publication number Priority date Publication date Assignee Title
FR2542655B1 (fr) * 1983-03-18 1985-07-12 Renault Broche de vissage
DE3329295A1 (de) * 1983-08-12 1985-02-28 Alfing Montagetechnik GmbH, 7080 Aalen Motorisch angetriebenes schraubwerkzeug
DE3529992A1 (de) 1985-08-22 1987-02-26 Volkswagen Ag Antrieb fuer schrauber
DE19625850B4 (de) * 1995-06-27 2008-01-31 Matsushita Electric Works, Ltd., Kadoma Planetengetriebe
DE19619428B4 (de) * 1996-05-14 2005-11-10 Eduard Gasinski Handgeführte Kombinationswerkzeugmaschine mit Bohrmaschinen- und Stichsägenfunktion
DE10356006A1 (de) * 2003-11-27 2005-06-23 Robert Bosch Gmbh Handbohrschraubmaschine
DE102004018025B4 (de) * 2004-04-14 2008-01-31 Metabowerke Gmbh Elektrohandwerkzeug mit einer Mitnahme-/Blockiereinrichtung
DE102008043795A1 (de) * 2008-11-17 2010-05-20 Robert Bosch Gmbh Schaltbares Planetengetriebe in einer Handwerkzeugmaschine
WO2011089766A1 (fr) * 2010-01-25 2011-07-28 株式会社マキタ Outil motorisé
DE102012212032A1 (de) * 2012-07-10 2014-01-16 Metabowerke Gmbh Getriebeanordnung
CN103846879B (zh) * 2012-12-07 2016-03-16 苏州宝时得电动工具有限公司 动力工具
DE102013212196A1 (de) * 2013-06-26 2014-12-31 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Spindellockvorrichtung

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CN107980019A (zh) 2018-05-01
WO2017001423A1 (fr) 2017-01-05
EP3674038B1 (fr) 2021-06-30
EP3674038A1 (fr) 2020-07-01
EP3317051B1 (fr) 2020-02-12
CN107980019B (zh) 2021-10-15
DE102015110504A1 (de) 2017-01-19

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