EP3674038B1 - Machine-outil manuelle - Google Patents

Machine-outil manuelle Download PDF

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Publication number
EP3674038B1
EP3674038B1 EP19219478.5A EP19219478A EP3674038B1 EP 3674038 B1 EP3674038 B1 EP 3674038B1 EP 19219478 A EP19219478 A EP 19219478A EP 3674038 B1 EP3674038 B1 EP 3674038B1
Authority
EP
European Patent Office
Prior art keywords
gear
locking
locking mechanism
rotation
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.)
Active
Application number
EP19219478.5A
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German (de)
English (en)
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EP3674038A1 (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
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Filing date
Publication date
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Publication of EP3674038A1 publication Critical patent/EP3674038A1/fr
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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 invention relates to a hand machine tool, in particular a screwdriving device and / or drilling device, with a drive motor for driving a gear drive of a transmission which has a gear output for driving a tool holder of the hand machine tool and a first gear stage and a second gear stage , according to the preamble of claim 1.
  • a hand machine tool of this type in the form of a screwdriver is for example in DE 35 29 992 A1 explained.
  • the blocking devices are freewheels, one of which blocks depending on a respective direction of rotation of the drive motor and thus activates the assigned gear stage.
  • the screwdriver is not practical.
  • a conventional hand machine tool is off DE 33 29 295 A1 known.
  • the gear ensures that, despite the shift from one gear stage to the other gear stage, the gear output always rotates in the same direction of rotation, so that there is no reversal of the direction of rotation on the output side. It is therefore expediently provided that the first gear stage and the second Gear stage drive the output in opposite directions of rotation of the drive motor in the same direction of rotation.
  • the first gear stage can be a so-called plus gear, for example, and the second gear stage a so-called minus gear.
  • a minus gear causes, for example, a reversal of the direction of rotation from its drive side to its output side, a plus gear maintains the direction of rotation.
  • a screw can always be screwed into a workpiece with the same direction of rotation, although the transmission is shifting.
  • both gear stages there is a change in torque and speed between the drive side and the output side, which means that, for example, a high speed of the drive motor can be converted into a comparatively low speed at the gear 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 the drive and the output.
  • first gear stage and the second gear stage there is a change in speed between the input and output of the transmission.
  • the output and the drive are therefore not directly coupled with the same speed.
  • a gear stage should therefore advantageously be understood to mean that a torque and a speed between the drive side and the output side of the gear stage are changed in the gear stage.
  • the transmission is preferably a toothed transmission, an at least partial configuration as a friction wheel transmission or roller transmission is also possible.
  • the transmission preferably comprises a planetary gear or an epicyclic gear or is designed as a planetary gear or an epicyclic gear.
  • the first gear stage and the second gear stage expediently form components of a planetary gear or epicyclic gear.
  • first gear stage and the second gear stage can form components of a planetary gear, for example, while an upstream or downstream further gear stage, in particular a non-switchable or non-switched gear stage, can also be configured as a similar gear, for example a planetary gear .
  • this further gear stage it is also possible for this further gear stage to have a different type of gear, for example a toothed gear, in which the drive and output are not coaxial.
  • a preferred embodiment of the invention provides that the transmission or the hand machine tool as a whole has at least one gear wheel which meshes with both locking gear elements that can be locked by the first locking device and the second locking device.
  • This design is particularly compact.
  • the locking gear elements can, for example, actively drive the gear wheel, so to speak, so that it can transmit a torque to the gear output.
  • the locking gear elements form a support for the gear wheel or support the gear wheel so that the gear wheel can roll on the respective locking gear element when it assumes its locking position. This can be implemented particularly easily in the case of a planetary gear, for example.
  • An advantageous embodiment of the transmission according to the invention provides that it has a planetary stage.
  • Planet gears of the planetary stage are rotatably mounted on a planet carrier which has an output.
  • the planet gears are driven by a drive gear.
  • the drive wheel is arranged, for example, directly on an output shaft of the drive motor or is rotatably connected to it.
  • the drive wheel for the planetary wheels is in turn coupled to an output of a gear stage.
  • the drive wheel can be arranged on an output of a planetary stage.
  • the output of the planet carrier in turn is rotationally connected, rotationally coupled or the like to the gear output, for example.
  • the output of the planet carrier can be connected directly to the tool holder and drive it directly.
  • the output of the planet carrier drives the tool holder via at least one further gear stage, for example a planetary gear stage.
  • a particularly preferred embodiment of the invention provides that the planet gears have a first pitch circle diameter assigned to the drive gear and a second pitch circle diameter different from the first pitch circle diameter.
  • This second pitch circle diameter is, for example, smaller or larger than the first pitch circle diameter, so that it effects a gear ratio.
  • the planet gears can thus already contribute to bringing about a change in speed from the drive side to the output side, in particular that the first gear stage and the second gear stage are each designed as real gear stages, so to speak.
  • the planetary gears are designed as so-called stepped planets or stepped planetary gears.
  • the planet gears can also have at least one further, for example at least a third, pitch circle diameter.
  • the drive gear for the planetary gears can be, for example, 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 the planetary gears are accommodated.
  • the drive wheel is, for example, as mentioned, rotatably coupled or firmly connected to the output shaft of the drive motor.
  • the planet gears can therefore be driven from the radial outside by the ring gear or from the radial inside by the sun gear.
  • gear wheels of the first gear stage and of the second gear stage meshing with the planetary gears at least partially mesh with one another with respect to the axis of rotation of the planetary gears.
  • the gear wheels can comprise, 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 detail below.
  • gear wheels arranged next to one another can of course also mesh with the planet wheels with regard to the axes of rotation of the planet wheels.
  • the gear wheels that mesh with the planetary gears are preferably gear wheels that are rotatably coupled to the locking devices and can each be locked by the locking devices.
  • the gears can form, so to speak, support elements for the planetary gears.
  • a preferred embodiment of the invention provides that the planetary gears mesh with a ratchet sun gear that can be locked by the first locking device and a ratchet ring gear that can be locked by the second locking device, so that by locking the ratchet sun gear or the ratchet ring gear, the first or the second gear stage can be activated.
  • the ratchet sun gear is, for example, radially on the inside, the ratchet ring gear radially on the outside with respect to a central axis of rotation of the transmission.
  • the sun ratchet and the ring gear can have the same or at least approximately the same longitudinal positions with respect to an axis of rotation of the planetary gears or an axis of rotation of the transmission or an axis of rotation of the sun ratchet have or at least partially intervene. This makes the transmission particularly compact.
  • the ratchet sun gear is coupled to a support wheel or has a support wheel which is arranged next to the ratchet ring gear with respect to an axis of rotation of the ratchet sun gear and / or has the same or approximately the same outer circumference as the ratchet ring gear.
  • the support wheel and the ratchet ring gear are each connected or rotationally coupled to the associated locking device, for example, radially on the outside.
  • a locking device can, so to speak, reach through to the ratchet sun gear radially inward via the support wheel.
  • the support wheel and the ratchet sun gear can be made in one piece.
  • the support wheel and the ratchet sun wheel are two wheels that are, for example, firmly connected to one another or rotationally coupled to one another via further wheels, for example at least one gear wheel, in particular a planetary gear or several planetary gears, or the like.
  • the ratchet sun gear and the ratchet ring gear have the same or approximately the same longitudinal position with respect to an axis of rotation of the ratchet sun gear.
  • a step-like arrangement can be made in which the ratchet sun gear, so to speak, protrudes in front of the support wheel and engages in an interior of the ratchet ring gear.
  • the sun ratchet and the ring gear can have exactly the same longitudinal position with respect to the axis of rotation of the sun ratchet, or they can have a somewhat longitudinally offset position.
  • the locking gear element of the first gear stage that can be locked by the first locking device or the locking gear element of the second gear stage that can be locked by the second locking device or both are preferably designed as a support wheel, in particular as a ring gear or sun gear, on which at least one gear wheel, in particular a planetary gear, of the first or the second gear stage.
  • a locking device it is advantageously provided that when the associated locking gear element of a gear stage is locked, it turns the ratchet gear element into a support element or support wheel, so to speak, on which a further gear element of the respective gear stage can be supported or rolled.
  • the locking device activates the respectively assigned gear stage by locking a locking gear element.
  • the respective gear stage then transmits a torque from the gear drive to the gear output. If, however, the locking gear element is released by the locking device, the gear stage assigned to this locking gear element expediently runs freely or is not supported with respect to the housing of the gearbox or the hand machine tool, so that it does not transmit any torque from the gearbox drive to the gearbox output.
  • At least one locking gear element that can be locked by a respective locking device is designed as a ring gear or has a ring gear. It is thus possible for this ring gear to be coupled or connected to a locking device, so to speak, radially on the outside, so that this locking device ensures optimal support. A torque that acts on the locking device from the ring gear is comparatively small.
  • an active blocking device for example, to be provided as the blocking device, which can be blocked, for example, by means of an electromagnet or some other actuator.
  • the hand machine tool advantageously has a controller which is designed to switch such active blocking devices or blocking devices provided with an actuator.
  • the control can for example be designed in such a way that it actively switches the locking devices so that one locking device locks its assigned locking gear element, while the other locking device releases the locking gear element assigned to it 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, however, that the first locking device and / or the second locking device comprises a freewheel or is designed as a freewheel.
  • a freewheel has the advantage that it allows the locking gear element of the respective gear stage coupled to it to rotate freely in one direction of rotation, but blocks or supports or locks it in the opposite direction of rotation. The advantage here is that the gear stages are activated by themselves, so to speak, when the direction of rotation of the drive motor is switched. Active control of the locking devices is not necessary.
  • a freewheel also has a self-reinforcing locking effect.
  • At least one of the freewheels forms a radially outermost component or a 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 locking gear element of the first gear stage or the second gear stage.
  • first locking device have a first freewheel and the second locking device have a second freewheel, the freewheels having a locking direction in the same direction and a releasing direction of rotation in the same direction.
  • both freewheels can be switched over very easily with regard to their blocking 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 releases a rotational movement of the lockable locking gear element of the first or second gear stage in a second direction of rotation, and these directions of rotation can be switched so that the locking device or the freewheel after switching in the first direction of rotation allows a rotational movement of the lockable locking gear element, but locks or blocks in the second direction of rotation.
  • such a freewheel has a locking element loaded by a spring element in the direction of its locking position.
  • 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 locking element in the direction of its locking position or clamping position.
  • a spring element or, more generally speaking, such a spring arrangement ensure, for example, that the locking element already assumes the locking position, that is, it ensures that the locking device is locked before the drive train or the transmission starts up.
  • the locking gear element can thus be supported with respect to the locking direction on the freewheel starting from the standstill of the gearbox.
  • the locking gear element for example the aforementioned support wheel, ring gear or the like, then starts running in the direction of the locking position, it intensifies the locking effect or clamping effect in addition to the resilience by the spring element.
  • a spring element can serve to guide a respective locking element.
  • a preferred embodiment provides that a blocking element or the already mentioned blocking element of the freewheel is loaded by a spring element with respect to one revolution or direction of rotation in mutually opposite blocking positions.
  • a locking device and a free-wheeling device of at least one locking device can be switched over.
  • the directions of rotation in which the locking device or the freewheel locks or blocks or supports the locking gear element or releases the locking gear element can be switched over on the locking device.
  • a switching device is provided for simultaneous switching of the locking direction of the first locking device and the second locking device for reversing the direction of rotation of the gear output in the hand machine tool, in particular its gear. In this way, the operator can use a single switching operation to cause the gear output and thus the tool holder to 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 locking elements of the locking devices and hold them in a release position in one locking device and actuate them in the direction of a clamping position or fixing position in the other locking device.
  • 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 controls actuators that are assigned to a respective blocking device or are arranged on the blocking device.
  • an actuating element which acts mechanically directly on the two locking devices or actuates them 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 the direction of rotation of the drive motor when the locking direction of the first locking device and the second locking device is switched. For example, after switching the direction of rotation of the output, the gear unit starts up again in the previously set gear stage, for example the first gear stage or the second gear stage.
  • Another embodiment provides that the locking gear elements rotate in opposite directions have when the first locking device and the second locking device release the respective locking gear element.
  • the locking gear elements can be locked or released by the associated locking devices with the same direction of rotation.
  • first locking device and the second locking device are rotatably connected to a housing of the hand machine tool or the transmission and / or each locking device is connected to the housing of the machine tool or the Gear housing is rotatably connected. Then these locking devices are easily accessible, for example, for the aforementioned switching device for switching the direction of rotation of the transmission output.
  • a manual operating element can act on the locking devices, so to speak, directly or with the aid of a few components, in order to switch them over with regard to their locking direction and release direction of rotation.
  • an alternative embodiment can also provide that at least one or more locking devices or all locking devices are arranged on a shaft or a rotating element.
  • his advantageous embodiment of the invention or an independent invention in itself is when at least one locking device is arranged between the radially outer circumference of the locking gear element or an end face of the locking gear element and the housing of the hand machine tool or the gearbox and is supported on the housing.
  • Such a locking device is easily accessible, for example, for switching and / or enables optimal torque support.
  • At least one third gear stage for example a reduction gear, is connected downstream or upstream of the first and second gear stages.
  • the first and the second gear stage preferably form an input gear stage of the transmission, and the one another Downstream reduction stage.
  • the at least one further gear stage can be a switchable or a non-switchable gear stage.
  • first and the second gear stage work at their output higher speed, but lower torque when operating the hand machine tool or the gearbox, while at least a third downstream gear stage, for example an arrangement of several, in particular switchable gear stages, a have a lower speed, but a higher torque at the output. It is therefore advantageous if the first and second gear stages, viewed from the drive of the hand machine tool, are the first gear stages, which are followed by at least one, preferably further gear stages, which implement a speed reduction compared to the first two gear stages.
  • the hand-held machine tool advantageously has a gear arrangement upstream or downstream of the first gear stage and the second gear stage and having at least two gear stages. These gear stages can be switched manually or by motor or both. It is therefore preferably provided that the hand machine tool has a switching device that can be manually operated and / or operated by a motorized actuator for switching between the at least two gear stages of the gear arrangement.
  • the first and second gear stages can have a different type of gear than the third and further gear stages, 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 is or are a gear stage that can be switched manually or by a motor.
  • the at least one third stage can have, for example, two or more, in particular three or four, shiftable gears or gear ratios.
  • the at least one third, expediently third and fourth, gear stage can be switched, for example, by an electrical or pneumatic actuator.
  • the electrical actuator can, for example, have an electromagnetic drive, for example a coil or the like.
  • a control of the hand machine tool for controlling a motorized actuator for switching the at least one third gear stage between a first transmission ratio and at least one second transmission ratio is preferably designed and provided.
  • the controller has a corresponding output stage or control outputs.
  • the hand machine tool according to the invention has an impact mechanism.
  • this hammer mechanism is connected between the tool holder and the gear with the switchable gear stages.
  • the hand machine tool has a spindle stop, in particular in the area of the transmission.
  • the spindle stop it is possible, for example, for the gear output to be fixed in a torque-proof manner 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 therefore be switched quickly and effectively. It is possible that the switching process of the direction of rotation is almost imperceptible, so to speak, that is to say that no interruption in rotation, at most a slight reduction or increase in speed, is noticeable at the gear output.
  • a brushless motor is advantageous.
  • a brushless motor is understood to mean a motor without brushes or sliding contacts, ie a motor without electrical contact between the movable rotor and the stationary stator.
  • the drive motor is a three-phase motor or a brushless direct current motor or synchronous motor
  • the brushless motor still has no preferred direction of rotation, so that it has an optimal degree of efficiency or provides optimal performance in mutually opposite directions of rotation.
  • the brushless motor has no fixed distortion between the collector and the brush apparatus. Such a so-called distortion can be implemented on the software side in the brushless motor.
  • the hand machine tool according to the invention is preferably a screwdriver, drill or a combination thereof.
  • the hand machine tool according to the invention it is also possible for the hand machine tool according to the invention to be, for example, a router, a grinding device, a polishing device, a saw or the like or to include such a thing.
  • other configurations of a hand machine tool are also advantageous in which an automatic shifting of the transmission is advantageous.
  • the hand machine tool has a control for switching the direction of rotation of the drive motor depending on a speed of the gearbox output or the drive motor and / or a torque of the drive motor or a torque on the gearbox output.
  • the control can detect a torque and / or a speed of the drive motor and change the direction of rotation of the drive motor as a function thereof in order to switch between the first gear stage and the second gear stage in this way. If a torque in the drive motor rises or falls above a predetermined limit, the control switches the direction of rotation.
  • a speed-dependent switchover is also advantageous, for example, when the drive motor changes its direction of rotation when it exceeds or falls below a predetermined speed and is thus switched between the gear stages.
  • control can also switch the direction of rotation of the drive motor depending on a speed and / or a torque at the output of the transmission or an output shaft and thus switch between the gear stages of the transmission.
  • An output shaft can be coupled to the output of the transmission.
  • corresponding speed sensors and / or torque sensors are arranged on the output or on the output shaft, the signals of which are evaluated by the controller and used to control the drive motor and / or to control the transmission, which will be explained in detail below.
  • the controller uses one or more sensors on the drive motor and / or an output stage that controls the drive motor to detect the speed and / or torque and, depending on this, controls and / or controls the drive motor with regard to speed and / or torque and / or direction of rotation
  • another gear stage of the transmission shifts or controls for shifting.
  • this control not only shifts the first and second gear stages, but can also switch further gear stages, for example gear stages of a gear arrangement downstream or upstream of the first and second gear stages.
  • a control concept can expediently provide that the control switches the first and second gear stages as well as the further gear stages of the gear arrangement depending on the torque and / or speed of the drive motor and / or the tool shaft or the output of the transmission.
  • the control can switch the direction of rotation of the drive motor, switch between the first and second gear stages and also the downstream or upstream gear arrangement also switch between their gear stages or switching stages.
  • a torque measurement can be implemented by means of a current measurement without any special effort.
  • a speed detection and / or torque detection in the drive motor can take place, for example, via the output stage or power electronics that control the drive motor.
  • the controller is used to activate and / or regulate the drive motor and / or to shift the transmission as a function of a predefined as a function of a predefined or predefinable setpoint speed and / or setpoint speed and / or a predefined one or specifiable target torque and / or maximum torque is configured.
  • the hand machine 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 regulation module for example appropriate software, is advantageously provided in order to set the speed and / or torque output and / or direction of rotation of the drive motor.
  • the controller in particular the regulating module or control module, is expediently also designed to switch, for example, the switching actuator or switching device already explained as a function of speed, torque or direction of rotation.
  • the regulation conventional regulation methods with feedback of an actual variable (speed, torque or the like), observer principles or the like, which are known per se, can be used.
  • the control works, for example, on the basis of software or a program module suitable for regulation and / or control.
  • the control is designed to set a maximum torque and / or maximum speed at the output of the transmission or the output shaft.
  • Corresponding setting elements are preferably provided on the hand machine tool.
  • a maximum Torque of 25 Nm soft screwing, e.g. for screwing in wood up to 45 Nm (hard screwing, e.g. for screwing in metal) can be specified.
  • the control can also implement a speed limitation and / or torque limitation, for example.
  • the control controls the drive motor and / or the gearbox accordingly.
  • a hand machine tool 10 has a housing 11, in the interior of which a drive train 20 is arranged.
  • the hand machine tool 10 is, for example, a screwdriver, drill or both.
  • the housing 11 can be conveniently gripped at a handle portion 12 by an operator.
  • the drive train 20 is received in an upper housing section 13, which runs at an angle to the grip section 12 like a pistol.
  • a front housing section 14 extends in front of the handle section 12, which can be grasped with one hand, for example, the handle section 12 and the housing section 14 being connected to one another by a lower housing section.
  • this lower housing section there is, for example, a connection for a power cord 17. Furthermore, it is possible to provide a rechargeable battery or some other mobile energy storage device on this housing section or, as shown in the exemplary embodiment, in the area of the front housing section 14.
  • a hand machine tool according to the invention is network-connected, that is to say, for example, can be connected to an electrical supply network or is a battery-powered machine, that is to say represents a mobile device.
  • a switch 15 is provided on the handle section 12, with which a drive motor 16 of the hand machine tool 10 can be switched on or off. It is also conceivable to set a speed of the hand machine tool 10 with the switch 12.
  • the tool 19 is, for example, a drill, a screwdriver bit or the like.
  • another tool is of course expedient, 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.
  • An impact mechanism 21 can be connected between the gear 30 and the tool holder 18, so that the hand machine tool 10 can even be used to perform an impact operation, for example for drilling holes.
  • the drive motor 16 drives the transmission 30 with the aid of its motor shaft 22.
  • the transmission 30 has a shift stage 31 with shiftable first and second gear stages 41 and 42.
  • the switching stage 31 is followed by a transmission stage 32 which, for example, further reduces an output speed of the switching stage 31.
  • the translation stage 32 can be a reduction stage, for example.
  • the gear 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 gear drive 25.
  • the drive gear 33 is a sun gear 34 that drives transmission gears 35.
  • the transmission gears 35 are, for example, planet gears 36 which are rotatably mounted on a planet carrier 37 on planet axles 40.
  • the planet axles 40 are rotatably mounted on the planet carrier 37, for example, or the planet gears 36 are rotatably mounted on the planet axles 40.
  • plain bearings, ball bearings or even needle bearings or other roller bearings can be provided between the planetary gears 36 and the planetary axles 40 or the planetary axles 40 and the planetary carrier 37.
  • the planet gears 36 mesh with the drive gear 33 with a first pitch circle diameter 38.
  • a further, second pitch circle diameter 39 of the planetary 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 arranged radially on the outside with respect to the planet gears 36 and surrounds them in an annular manner.
  • 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 is assigned to the second gear stage 42.
  • the ring gear 45 forms a locking gear element 43, the sun gear 46 a locking gear element 44.
  • a respective locking gear element 43 or 44 When a respective locking gear element 43 or 44 is locked by locking devices 61 or 62 of a shifting arrangement 60, it forms a support element for the transmission gears 35, in this case the planet gears 36.
  • the locked locking gear element 43 or 44 shifts the respective first and second gear stages 41, 42, so to speak active. However, if a locking gear element 43, 44 is not locked by the associated locking device 61, 62, it can rotate freely so that it does not provide any support for the transmission wheels 35.
  • An unlocked locking gear element 43, 44 switches the assigned first and second gear stages 41, 42 inactive. Active and inactive should be understood to mean that a torque can be transmitted from the drive side to the output side.
  • the locking gear element 43 is arranged with its radially outer circumference, so to speak, directly on or next to the locking device 61. This is not possible with the sun gear 46, which is arranged centrally on the inside, so to speak. However, this also has a radially outer support area, namely in the form of a support wheel 47, which is connected to the sun wheel 46 or in one piece. For example, the support gear 47 is connected to the sun gear 46 by a connecting disc and / or spokes 47A.
  • the support wheel 46 and the ratchet gear element 43, that is to say the ring gear 45, have the same radial outer circumference.
  • a passage opening 48 is provided in the sun gear 46 or the locking gear element 44, through which the motor shaft 22 is connected to the drive gear 33.
  • the switching stage 31 drives the transmission stage 32 via an output gear 49.
  • the transmission stage 32 is designed as a planetary stage 50.
  • the output gear 49 is driven by the planet carrier 37 or is integral therewith.
  • the output gear 49 projects in front of the planet carrier 37.
  • Planetary gears 51 which are rotatably supported on a planetary carrier 52 by means of planetary axles 53, mesh with the output gear 49.
  • the output gear 49 forms a sun gear for the planet gears 51.
  • the planet gears 51 are arranged in the interior of a ring gear 54 which is fixed in place with respect to the housing 11 of the hand machine tool 10 or a gear housing 90 of the gear 30.
  • the ring gear 54 is fixed in place, for example, on a housing section 93 of the gear housing 90.
  • the planet gears 51 therefore roll on the inner circumference of the ring gear 54.
  • the planet gears 51 are rotatably mounted on the planet axles 53, for example.
  • the planetary axles 53 have an additional function, namely that they couple the planetary carrier 52 to an output shaft 54 of the transmission 30 in a rotationally fixed manner.
  • the planetary axles 53 protrude on opposite sides in front of the planet carrier 52, on the one hand supporting the planet gears 51 in a rotatable manner and on the other hand coupling a transmission element 56 for the output shaft 55 in a rotationally fixed manner or being firmly connected to it.
  • the transmission element 56 receives, for example, a shaft section 57 of the output shaft 55 or is firmly connected to this shaft section 57.
  • the output shaft 55 is rotatably supported, for example, on bearings 59 on a section 91 of the transmission housing 90.
  • a tool section 58 which has the tool holder 58 on its front side, protrudes in front of a front side 92 of the gear housing 90.
  • the gear housing 90 On a side opposite to the front side 92, the gear housing 90 is closed by a cover 95.
  • the cover 95 has a passage opening for the motor shaft 22 or some other drive shaft.
  • the transmission 30 can advantageously be encapsulated, can have seals or the like, for example at an opening on the front side 92, where the output shaft 55 penetrates the transmission housing 90.
  • the two locking devices 61, 62 are each designed as freewheels.
  • the power flow or the torque transmission from the gear drive 25, for example from the drive wheel 33 or the motor shaft 22, to a gear output 25, for example the output gear 49 or the output shaft 58 of the gear 30, can be achieved by simply reversing the direction of rotation of the drive motor 16 the gear stage 41 and the gear stage 42 are shifted.
  • the direction of rotation of the drive motor 16 can be quickly switched, in particular because the drive motor 16 in an advantageous embodiment of the invention is a so-called brushless motor, for example an electronically commutated motor.
  • the planet gears 36 and therefore the transmission gears 35 are not supported by the locking gear element 43 with respect to the gear housing 90, but can rotate freely.
  • the gear stage 41 is therefore inactive.
  • the other gear stage 42 is then active, namely in that its locking gear element 44 is supported by the locking device 62 with respect to the housing 90 so that the planet gears 36 can roll on the outer circumference of the sun gear 46 and thereby the power flow or the torque transmission from the gear drive 25 to the Gear output 26 runs over gear stage 42.
  • the locking device 62 releases the locking gear element 44, so that no power flow via the second gear stage 44 is possible.
  • the sun gear 46 rotates freely.
  • the other locking device 61 is then active, ie it locks the supporting element or locking gear element 43 assigned to it, namely the ring gear 45.
  • the transmission gears 35 in this case the planet gears 36, can roll on the ring gear 45, which is stationary with respect to the gear housing 90, and thus one Enable power flow or torque transmission from the gear drive 25 to the gear output 26.
  • the gear stages 41, 42 each provide a torque ratio and speed change between the gear drive 25 on the one hand and the gear output 26 on the other hand. By simply reversing the direction of rotation of the drive motor 16, a different speed of the tool holder 18 and / or a different torque output on the tool holder 18 can thus be achieved.
  • the operator can actively switch the direction of rotation of the drive motor 16 for this purpose. It is advantageously also possible for a controller 80 of the hand machine tool 10 to automatically reverse the direction of rotation, for example as a function of the torque and / or speed of the drive motor 16.
  • the controller 80 could be an analog controller which, with simple current monitoring, for example, of the drive current that leads to the drive motor 16, monitors its torque output and thus switches the direction of rotation accordingly.
  • a digital control is preferred, for example by means of corresponding digital circuits, in particular a microprocessor 81.
  • This 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 can, for example, control an output stage 83 for controlling the drive motor 16.
  • the output stage 83 contains, for example, power electronics.
  • the controller 80 receives signals via an input interface 84, for example from the switch 15 or a speed setting element 23 with which a speed of the drive motor 16 can be specified by the operator.
  • the controller 80 changes, for example, the direction of rotation of the drive motor 16, so that the transmission 30 switches back, for example, from the second gear stage to the first gear stage. However, if a speed of the drive motor 16 exceeds a predetermined amount, the controller 80 changes the direction of rotation of the drive motor 16 reversed, so that the gear 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 supported, so to speak, like a sandwich between the locking gear elements 43 and 44 on the one hand and a housing section 94 of the gear housing 90.
  • the locking devices 61, 62 therefore form, so to speak, radially outer components of the transmission 30. Because the locking devices 61, 62 are arranged radially on the outside, they are also easily accessible for interventions from the outside, for example for switching the respective blocking direction.
  • the two blocking devices 61, 62 switched off as freewheels can be switched with respect to their blocking direction and freewheeling direction.
  • the locking devices 61, 62 comprise a common support ring 63, which could be referred to as a freewheel ring.
  • each locking device 61, 62 it would also be possible for each locking device 61, 62 to be designed as a separate free-wheeling device, i.e. that there are no common components.
  • the support ring 63 is fixed in place with respect to the transmission housing 90.
  • support bodies 64 in particular bolts or the like, are inserted in a form-fitting manner between the inner circumference of the gear housing 90, that is to say the housing section 94, and the outer circumference of the support ring 63 and hold the two components together in a form-fitting manner.
  • the support ring 63 On its inner circumference, the support ring 63 has several, for example three, free-wheeling recesses 65, offset in rotation, in each of which a locking element 68 or 69, in particular a roller or a pin, of a respective locking device 61 is guided below 62.
  • the locking devices 61 have locking elements 68, 69 that are separate from one another, so that they can have opposite freewheeling directions in and locking directions.
  • the locking elements 68, 69 are mounted between the outer circumferences of the locking gear elements 43, 44 and the inner circumference of the support ring 63 in the area of the respective freewheel recesses 65.
  • the locking elements 68, 69 with respect to an axis of rotation D, about which the locking gear elements 45, 46, namely the ring gear 45 and the combination of sun gear 46 and support gear 47 rotate are moved on the outer circumference of the respective locking gear element 43, 44, namely into the area of the freewheel recesses 65 or out of these, in clamping bevels or constrictions 66, 67.
  • the respective locking device 61 or 62 is in freewheeling mode. If, however, 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 locking gear element 43, 44 is then blocked with respect to rotation about the axis of rotation D by the locking elements 68, 69 arranged on its outer circumference, which are located in one of the clamping bevels 66 or 67 and are supported on the support ring 63, so that the locking gear element 43, 44 can serve to support the planet gears 36 and thus the respective gear stage 41 or 42 is active.
  • a switching device 70 which can be conveniently actuated by a single, manual actuating element 71 by an operator.
  • the actuating element 71 is configured, for example, as a projection in front of a switching element 72 configured, for example, as a ring, which is rotatable about the axis of rotation D.
  • pin-like guide elements 73 which are also referred to below as 73a and 73b, protrude in the direction of the locking elements 68, 69, a respective locking element 68, 69 being arranged between guide elements 73 lying opposite one another in pairs.
  • the locking elements 69 are adjusted in the direction of the clamping bevels 66, so that the locking device 61 locks or blocks the support element or locking gear element 44 in a direction of rotation D1.
  • the guide elements 73b hold the locking elements 69 in the freewheel recesses 65.
  • the direction of rotation D2 therefore corresponds a freewheeling direction F1, the direction of rotation D1 a blocking direction S1 of the blocking device 62 in the position according to Figures 3 or 4 .
  • a spring element 75 is provided between the guide elements 73 and the locking elements 68, 69.
  • the spring elements 75 load the locking elements 68, 69 in the direction of the locking position, i.e. in the direction of the clamping bevels 66, 67.
  • the blocking elements 68, 69 are already loaded in the direction of the blocking position, so that the blocking function or, as of the supporting function, the blocking transmission elements 43, 44 is available as immediately as possible.
  • the locking elements 68, 69 are expediently mounted so as to be movable, decoupled from one another.
  • a decoupling ring 74 is arranged between the locking elements 68, 69.
  • the blocking direction and the freewheeling direction of the blocking devices 61, 62 can be switched in opposite directions, namely by the switching device 70.
  • the actuating element 71 is actuated about the axis of rotation D
  • the guide elements 73 make this rotary movement so that, starting from a central position, they approximately correspond Figure 2 can be adjusted in a position offset in relation to the rotational axis D, for example a position for clockwise rotation or a position for counter-clockwise rotation of the tool holder 18.
  • the blocking direction S1 and the freewheeling direction F1 can be switched in opposite directions.
  • the controller 80 adjusts the direction of rotation of the drive motor 16 depending on the position of the switching device 70 for clockwise or counterclockwise rotation, so that it is in the gear stage assumed before switching the direction of rotation after switching from clockwise to counterclockwise rotation or vice versa 41 or 42 starts up.
  • a sensor 85 is arranged on the switching device 70 in order to detect its 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 can be provided as a sensor, but also an electrical contact switch or the like.
  • the first gear stage 41 represents a minus gear
  • the second gear stage 42 a plus gear, so that the gear stages 41 and 42 can be switched by simply reversing the direction of rotation of the drive motor 16 in the gear unit 30, but no reversal of the direction of rotation is connected to the gear output 26.
  • This concept can also be used with types of gears that are not designed as planetary gears, which is based on the Figures 8 and 9 still becomes clear.
  • 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 gear drive 125.
  • Both switching stages 141 and 142 cause a change in speed and torque between the gear drive 125 on the one hand and the gear output 126 on the other hand, on which the tool holder 18 can be arranged directly, for example.
  • a further gear stage is arranged on the gear output 126 or that 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 in the area of the gearbox 120 could easily be referred to as a gearbox shaft. In the simplest case, these could be freewheels, but also switchable locking devices whose locking direction and release direction of rotation or freewheeling direction can be switched, for example by an electrical actuator that can be controlled by the controller 80.
  • the locking devices 161 and 162 are provided between locking gear elements 143 and 144. When a respective locking device 161 or 162 is locked, it takes its assigned locking gear element 143, 144. In a direction of rotation opposite thereto, however, the locking gear element 143 or 144 on the locking device 161 or 162 is rotatable, so it is not blocked or locked.
  • the ratchet gear element 143 is, for example, a gear 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 which drives it via a gear unit (not shown).
  • the gear stage 141 represents a so-called minus gear.
  • the locking gear element 144 is, for example, a ring gear 145 , with the inner circumference of the transmission wheel 135 meshes.
  • a plus gear is realized.
  • the ring gear 145 has spokes 146 or other connecting elements radially inward, which are connected to the locking device 162 or have a radially inner support wheel 147 which can be locked by the locking device 162.
  • the gear mechanism 130 is also very compact because, namely, both ratchet gear elements 143, 144 act directly on one and the same drive wheel 135.
  • a switching device 170 is shown as an example of a manually or electrically operated switching device for switching over the blocking directions or freewheeling direction in the blocking devices 161 and 161.
  • Their actuating element 171 acts, for example, on locking elements 168 and 169 of locking devices 161, 162 in a similar way to guide elements 73 of switching device 70.
  • switching device 171 must switch in opposite directions, since locking gear elements 143, 144 must have an opposite freewheeling direction so that gear stages 141 and the other time the gear stage 142 is inactive.
  • One possibility for such an actuation is, for example, that 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 gear 230 is provided, which is also designed so that no reversal of the direction of rotation occurs between its gear drive 225 and its gear output 226 when the drive motor 16 rotates in mutually opposite directions.
  • locking devices 261, 262 which are assigned to gear stages 241 and 242, are arranged coaxially and next to one another on a motor shaft 222, which can also represent a gear shaft.
  • the locking devices 261 and 262 carry locking gear elements 243, 244 on their outer circumference, of which a locking gear element 243 is entrained when the motor shaft 222 rotates in one direction of rotation, the other locking gear element 244 rotates freely, while the locking gear element 243 is freely rotatable in the opposite direction of rotation while the ratchet gear member 244 is driven by the motor shaft 222.
  • the locking gear elements 243, 244 are, for example, gears.
  • the locking gear elements 243, 244 are designed as drive wheels 245, 246, for example.
  • the drive wheel 245 drives a transmission wheel 235, which is provided for driving the tool holder 18, via a transmission wheel 248.
  • the transmission wheel 235 is arranged non-rotatably on an output shaft 255.
  • the tool holder 18 is provided directly on the output shaft 255.
  • the output shaft 255 could, however, also be designed to drive a further gear stage and / or an impact mechanism.
  • Another transmission wheel 247 is also connected non-rotatably to the output shaft 255 and is used to drive it.
  • a first gear stage 241 is active, which implements a so-called plus gear as a whole.
  • the transmission wheel 248 realizes a minus gear with the locking gear element 243 and the drive gear 235, so that a plus gear is present overall.
  • the second gear stage 242 is designed as a minus gear.
  • a powertrain 320 according to Figures 10 and 11 comprises a transmission 330, which is constructed similarly to the transmission 30 or its switching stage 31 with regard to a switching stage 331.
  • the actuation concept (with a switching device 370) in a switching arrangement 360, which functionally corresponds 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 exemplary embodiment according to FIG Figures 5 and 6 a switchable gear arrangement 350 is provided.
  • a switchable gear arrangement 350 is provided.
  • the gear stage 331 drives a gear stage 332 with its transmission output 25, which can work as a reduction stage in the sense of a speed reduction, but does not have to.
  • the drive motor 16 drives a drive wheel 333 via the motor shaft 22.
  • a receptacle 333a is on the drive wheel 333 or a shaft element connected to this is provided for receiving and non-rotatably coupling the motor shaft 22.
  • the drive gear 333 forms a sun gear 334 which meshes with planet gears 336.
  • the planet gears 336 advantageously form transmission gears 35.
  • the planet gears 336 are rotatably mounted on a planet carrier 337.
  • planet axles 40 are rotatably mounted on planet carrier 37 or planet carriers 336 are rotatably mounted on planet axles 40.
  • the planet gears 336 have different pitch circle diameters 38, 39 as the planet 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 is provided so that the planet gears 336 mesh with a ring gear 345, i.e. with it comb or can take the ring gear 345 with you.
  • 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 can be switched by reversing the direction of rotation of the drive motor 16.
  • the planet gears 336 are also supported radially on the inside, so to speak, namely can roll on a sun gear 346 which forms part of a locking gear element 344.
  • the locking gear element 344 corresponds to the locking gear element 44 and has a passage opening 48 for the motor shaft 22.
  • the switching arrangement 360 comprises a locking device 361 for locking or releasing the locking gear element 343 and a locking device 362 for locking or releasing the locking gear element 344.
  • Blocking elements 368, 369 shown schematically are supported on a support ring or freewheel ring 363 (similar to components 68, 69 and 63) and are preferably through in Figure 10 visible spring elements 375 (corresponding to the spring elements 75) loaded.
  • the actuating element 371 protrudes radially outward in front of a gear housing 390 of the gear 330, so it can be comfortably gripped by the operator.
  • the actuating element 371 is preferably rotatably mounted on the support ring or freewheel ring 363 or extends through it.
  • the actuating element 371 is provided on a housing section 394 of the transmission housing 390, in which the switching stage 331 is accommodated.
  • the actuating element 371 is connected to the switching element 372 in a rotationally fixed manner.
  • a section 374 of the rod-shaped or ring-shaped actuating element 371, for example, is coupled to the switching element 372.
  • the switching element 372 is, for example, similar to the switching element 72, ring-shaped. In contrast to the shift element 72, however, the shift element 372 is arranged between the gear stages 341, 342 and between the locking gear elements 343, 344. For example, a projection 372a engages in an intermediate section between the ring gear 345 and the support gear 347 of the ratchet gear element 344.
  • the gear 390 is also closed on its side facing the drive motor 16 by a cover, here a cover 395.
  • a cover 395 On a side facing away from the cover 395, next to the housing section 394, there is a further housing section 393, which accommodates the gear arrangement 350, that is to say the switching stage 332.
  • the housing section 393 is closed by a cover 391, on the end face or front face 392 of which the output shaft 55 is coupled to the tool holder 18.
  • the tool shaft 18 is driven by the gear stage or switching stage 332, which in turn is coupled to the gear output 26 of the switching stage 31.
  • the gear output 26 comprises an output gear 349, which is, for example, firmly connected to the planet carrier 337, for example is in one piece with it.
  • the output gear 349 forms a sun gear with which planet gears 351 of the gear arrangement 350 mesh.
  • the planet gears 351 can be rotated with respect to a planet carrier 352, for example in that they are rotatably mounted on planetary axles 353 or in that the planetary axles 353 are rotatably mounted on planetary carriers 352.
  • the switching position of the gear arrangement 350 shown here couples a switching gear 354, for example a ring gear, of the gear arrangement 350 the planet gears 351 in a rotationally fixed manner with the planet carrier 337.
  • the planet carrier 337 has, for example, on its outer circumference a toothing 337a, which can mesh with an internal toothing of the switching wheel 354.
  • a respective planet gear 351 is likewise in engagement with this toothing or a toothing lying next to it.
  • the planet gears 351 mesh with the internal toothing of the ratchet wheel 354, that is to say roll on this.
  • the indexing wheel 354, for its part, is fixed in a rotationally fixed manner with respect to the transmission housing, for example by means of an external toothing 354a of the indexing wheel 354 which meshes with an internal toothing 354b on the housing 390, for example the cover 391.
  • the internal toothing 354b is radially inside, the external toothing 354a is radially outside.
  • Figure 10 By shifting the ratchet wheel 354, a switching position can accordingly be achieved Figure 10 be set, in which the output shaft 55 and thus the tool on the tool holder 18 rotates at the speed of the planetary carrier 337 or the transmission output 26, and a switching position accordingly Figure 11 , in which a reduction stage is implemented.
  • the sun gear or drive gear 349 drives the planet gears 351, which in turn roll on the ring gear or ratchet gear 354 and thus cause a speed reduction and, at the same time, an increase in torque at the output.
  • the shiftable gear arrangement 350 can be shifted manually, for example by an actuating element 310 which is displaceably mounted in a receptacle 311 of the gear housing 390.
  • the actuation element 310 is coupled in terms of movement to the indexing wheel 354 by means of a coupling element 312, but could also be arranged fixedly on the indexing wheel 354.
  • the coupling element 312 comprises, for example, pins, brackets or other similar components which enable a power transmission from an outside of the gear housing 390 into its interior, where the ratchet wheel 354 is arranged.
  • the receptacle 311 forms a sliding bearing or a sliding receptacle in which the actuating element 310 is accommodated in a linearly displaceable manner.
  • actuation element 310 is motion-coupled or in one piece with a manually graspable actuation handle 313, for example a ring or slide.
  • the actuating handle 313 protrudes, for example, in front of the housing 11 of the hand machine tool 10, so it is easy to grasp.
  • An alternative or supplementary drive concept or setting concept for the ratchet wheel 354, hence a concept for switching the gear arrangement 350, is represented by an actuator 387, for example an electromagnet, an electric motor or the like (a pneumatic drive is also possible).
  • the actuator 387 is designed and provided to adjust the switching wheel 354, that is to say a switching element of the transmission arrangement 350, between at least two switching positions.
  • the actuator 387 can switch the switching wheel 354 between the switching positions according to FIG Figures 10 and 11 adjust back and forth.
  • the actuator 387 is controlled, for example, via an electrical switch 24a on the housing 11 of the hand-held machine tool 10.
  • the actuator 387 can be accommodated in a protected manner 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 actuator 387. For example, it has a switching output 388 for switching the actuator 387. In Figure 7 is that indicated.
  • the controller 80 can, for example, automatically shift the gear stage or shift stage 331, advantageously also the shiftable gear arrangement 350 or the shift stage 332 is working.
  • sensors can also be provided on the output area which interacts with the controller 80.
  • a sensor 87 for detecting speed and / or torque and / or direction of rotation or the like, for example a tachometer, torque detection, can be provided on the tool shaft or output shaft 55.
  • a sensor 88 for example an optical sensor, a Hall sensor or the like, in the drive motor 16 can for example detect its torque and / or direction of rotation and / or speed.
  • a sensor 89 in particular for detecting rotational speed and / or detecting torque and / or detecting the direction of rotation, can also 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 to the controller 80, which uses its software program 86, for example, to set the speed and / or direction of rotation of the drive motor 16 in order to shift the transmission 30, 330 in this way.
  • the controller 80 can control the actuator 387.
  • the sensor signals of the sensors 87, 89, 88 can also be used to regulate and / or control the drive motor 16 and in particular also to shift the transmission 330, in particular its shift stage 332.
  • 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 revolutions / min for a drilling operation and a maximum speed of 500 to 2000 revolutions / min for a screwdriving operation.
  • an optionally available torque setting element 24 for example a rotatable setting 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 can be advantageous for a milling cutter or saw, for example.
  • a touch-sensitive display can also be provided, for example, which displays the set values SM and / or SD.
  • a control module 86a of the software program 86 can, for example, on the basis of the maximum values or setpoint values SM and / or SD as well as the feedback of the set values, namely the actual values that the sensors 87, 88, 89 deliver, the drive motor 16 and / or control the output stage 83 and / or regulate. Furthermore, the control module 86a can also control the actuator 387 via the switching output 388 to switch the gear stage 332 as a function of these values.
  • the controller 80 controls the actuator 387 to shift the gear stage 332 from the shift position in which the gear stage 332 does not reduce the speed relative to the gearbox output 26 ( Figure 10 ), into the shift position in which gear stage 332 acts as a reduction gear ( Figure 11 ), ie the position in which the planet gears 351 roll in the ring gear 354.
  • the planetary axles 353 or 53 can be components of a spindle stop, i.e. that a rotation lock on the output side of the gears 30, 330 can easily be implemented at this point.

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Claims (15)

  1. Machine-outil portative, en particulier visseuse et/ou perceuse, avec un moteur d'entraînement (16) pour entraîner un entraînement de transmission (25) d'une transmission (30), qui présente une sortie de transmission (26) pour entraîner un porte-outil (18) de la machine-outil portative (10) et un premier étage de transmission (41) et un deuxième étage de transmission (42), dans laquelle la transmission présente un premier dispositif de verrouillage (61) pour verrouiller un élément de transmission formant un élément de transmission à verrouillage (43) du premier étage de transmission (41) et un deuxième dispositif de verrouillage (62) pour verrouiller un élément de transmission formant un élément de transmission à verrouillage (46) du deuxième étage de transmission (42), dans laquelle l'étage de transmission avec l'élément de transmission à verrouillage (43, 44) respectivement verrouillé transmet un couple de l'entraînement de transmission (25) à la sortie de transmission (26), dans laquelle un sens de rotation du moteur d'entraînement (16) peut être commuté et en fonction du sens de rotation du moteur d'entraînement (16) le premier étage de transmission (41) ou le deuxième étage de transmission (42) transmet un couple de l'entraînement de transmission (25) à la sortie de transmission (26), caractérisée en ce qu'un sens de verrouillage et un sens de roue libre d'au moins un dispositif de verrouillage, en particulier d'une roue libre, peut être commuté.
  2. Machine-outil portative (10) selon la revendication 1, caractérisée en ce que les deux étages de transmission provoquent une modification de vitesse de rotation entre l'entraînement de transmission (25) et la sortie de transmission (26) et un des deux étages de transmission provoque une inversion de sens de rotation entre l'entraînement de transmission (25) et la sortie de transmission (26).
  3. Machine-outil portative selon la revendication 1 ou 2, caractérisée en ce qu'elle présente au moins une roue de transmission, qui s'engrène avec les deux éléments de transmission à verrouillage (43, 44) pouvant être verrouillés par le premier dispositif de verrouillage (61) et le deuxième dispositif de verrouillage (62).
  4. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que la transmission (30) présente un étage planétaire, dans laquelle les satellites (36) de l'étage planétaire sont montés en rotation sur un porte-satellite (37) présentant une sortie, dans laquelle les satellites (36) sont entraînés par une roue motrice.
  5. Machine-outil portative selon la revendication 4, caractérisée en ce que les satellites (36) présentent un premier diamètre de cercle de roulement (38) associé à la roue motrice et un deuxième diamètre de cercle de roulement (39) différent du premier diamètre de cercle de roulement (38) et/ou que la roue motrice pour les satellites (36) est un solaire (46) s'insérant entre les satellites (36) ou une couronne (45) recevant les satellites (36) et/ou les roues de transmission s'engrenant avec les satellites (36) du premier étage de transmission (41) et du deuxième étage de transmission (42) par rapport à l'axe de rotation des satellites (36) sont insérées au moins en partie les unes dans les autres et/ou que les satellites (36) s'engrènent avec un solaire à verrouillage (46) pouvant être verrouillé par le premier dispositif de verrouillage (61) et une couronne à verrouillage (45) pouvant être verrouillée par le deuxième dispositif de verrouillage (62), de sorte que du fait du verrouillage du solaire à verrouillage (46) ou de la couronne à verrouillage (45) le premier ou deuxième étage de transmission (42) peut être activé, dans lequel il est prévu de manière avantageuse que le solaire à verrouillage (46) soit accouplé à une roue d'appui ou présente une roue d'appui, qui est disposée par rapport à un axe de rotation du solaire à verrouillage (46) à côté de la couronne à verrouillage (45) et/ou présente la même ou sensiblement la même périphérie extérieure que la couronne à verrouillage (45) et/ou que le solaire à verrouillage (46) et la couronne à verrouillage (45) présentent par rapport à un axe de rotation du solaire à verrouillage (46) la même ou sensiblement la même position longitudinale.
  6. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément de transmission à verrouillage du premier étage de transmission (41) pouvant être verrouillé par le premier dispositif de verrouillage (61) et/ou l'élément de transmission à verrouillage (46) du deuxième étage de transmission (42) pouvant être verrouillé par le deuxième dispositif de verrouillage (62) est conçu en tant que roue d'appui, sur lesquelles au moins une roue de transmission du premier étage ou deuxième étage de transmission (42) roule, et/ou qu'au moins un élément de transmission à verrouillage (43, 44) pouvant être verrouillé par un dispositif de verrouillage respectif est conçu en tant que couronne (45) ou présente une couronne (45) et/ou que le premier dispositif de verrouillage (61) et/ou le deuxième dispositif de verrouillage (62) est une roue libre ou comprend une roue libre, dans lequel la roue libre forme avantageusement un composant radialement extérieur ou radialement le plus extérieur de la transmission.
  7. Machine-outil portative selon la revendication 6, caractérisée en ce que le premier dispositif de verrouillage (61) présente une première roue libre et le deuxième dispositif de verrouillage (62) une deuxième roue libre, dans laquelle les roues libres présentent un sens de verrouillage de même sens et un sens de rotation de libération de même sens, dans laquelle il est prévu de manière avantageuse que la première et la deuxième roue libre soient disposées l'une à côté de l'autre de manière coaxiale et/ou les deux roues libres forment un composant radialement extérieur ou le plus extérieur de la transmission.
  8. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins un dispositif de verrouillage présente une roue libre pouvant être commutée en ce qui concerne son sens de verrouillage, dans laquelle il est prévu de manière avantageuse que la roue libre présente un élément de verrouillage sollicité par un élément ressort (75) en direction de sa position de verrouillage et/ou qu'un élément de verrouillage de la roue libre soit sollicité dans des positions de verrouillage opposées les unes aux autres par rapport à un sens de révolution par respectivement un élément ressort (75).
  9. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'elle présente un dispositif de commutation (70) pour la commutation simultanée du sens de verrouillage du premier dispositif de verrouillage (61) et du deuxième dispositif de verrouillage (62) pour une inversion de sens de rotation de la sortie de transmission (26), dans laquelle il est prévu de manière avantageuse que les sens de verrouillage du premier dispositif de verrouillage (61) et du deuxième dispositif de verrouillage (62) puissent être commutés simultanément par un seul élément d'actionnement (71, 171) et/ou que le dispositif de commutation (70) soit accouplé à une commande (80) du moteur d'entraînement (16), de sorte que la commande (80) commute le sens de rotation du moteur d'entraînement (16) lors de la commutation du sens de verrouillage du premier dispositif de verrouillage (61) et du deuxième dispositif de verrouillage (62).
  10. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que les éléments de transmission à verrouillage (43, 44) présentent des sens de rotation opposés les uns aux autres, lorsque le premier dispositif de verrouillage (61) et le deuxième dispositif de verrouillage (62) libèrent l'élément de transmission à verrouillage (43, 44) respectif.
  11. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le premier dispositif de verrouillage (61) et le deuxième dispositif de verrouillage (62) sont reliés de manière solidaire en rotation à un boîtier (11, 90) de la machine-outil portative ou de la transmission (30) et/ou chaque dispositif de verrouillage est relié de manière solidaire en rotation au boîtier (11, 90) de la machine-outil ou de la transmission (30).
  12. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins un dispositif de verrouillage est disposé entre la périphérie radialement extérieure de l'élément de transmission à verrouillage (43, 44) ou une face frontale de l'élément de transmission à verrouillage (43, 44) et le boîtier (11, 90) de la machine-outil portative ou de la transmission (30) et en appui sur le boîtier (11, 90).
  13. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'elle présente au moins un troisième étage de transmission monté en amont ou monté en aval du premier étage de transmission (41) et deuxième étage de transmission (42) et/ou présente un mécanisme de percussion et/ou qu'elle présente un ensemble de transmission monté en amont ou monté en aval du premier étage de transmission (41) et deuxième étage de transmission (42) avec au moins deux étages de transmission, et qu'elle présente un dispositif de commutation pouvant être actionné manuellement et/ou par un actionneur motorisé pour la commutation entre les au moins deux étages de transmission.
  14. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce que le moteur d'entraînement (16) est un moteur sans balais.
  15. Machine-outil portative selon l'une quelconque des revendications précédentes, caractérisée en ce qu'elle présente une commande (80) pour la commutation du sens de rotation du moteur d'entraînement (16) en fonction d'une vitesse de rotation du moteur d'entraînement (16) et/ou d'un couple du moteur d'entraînement (16) et/ou d'une vitesse de rotation et/ou d'un couple d'une sortie de la transmission (30) et/ou d'un arbre de sortie (55) pouvant être entraîné par l'intermédiaire de la transmission (30) ou accouplé à la transmission (30), dans laquelle il est prévu de manière avantageuse que la commande (80) soit conçue pour commander un actionneur (387) d'un dispositif de commutation pour la commutation entre au moins deux étages de transmission d'un ensemble de transmission monté en amont ou monté en aval du premier étage de transmission (41) et deuxième étage de transmission (42) et/ou que la commande (80) soit conçue pour commander et/ou régler le moteur d'entraînement (16) et/ou pour commuter la transmission (30 ; 330) en fonction d'une vitesse de rotation maximale et/ou vitesse de rotation théorique prédéfinie ou pouvant être prédéfinie et/ou d'un couple maximal et/ou couple théorique prédéfini ou pouvant être prédéfini.
EP19219478.5A 2015-06-30 2016-06-28 Machine-outil manuelle Active EP3674038B1 (fr)

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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
EP16733490.3A EP3317051B1 (fr) 2015-06-30 2016-06-28 Machine-outil portative

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EP16733490.3A Division EP3317051B1 (fr) 2015-06-30 2016-06-28 Machine-outil portative
EP16733490.3A Division-Into EP3317051B1 (fr) 2015-06-30 2016-06-28 Machine-outil portative
PCT/EP2016/065048 Previously-Filed-Application WO2017001423A1 (fr) 2015-06-30 2016-06-28 Machine-outil portative

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DE102017129988A1 (de) 2016-12-16 2018-06-21 Festool Gmbh Hand-Werkzeugmaschine
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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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
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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
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DE102015110504A1 (de) 2017-01-19
EP3674038A1 (fr) 2020-07-01
WO2017001423A1 (fr) 2017-01-05
CN107980019B (zh) 2021-10-15
CN107980019A (zh) 2018-05-01
EP3317051A1 (fr) 2018-05-09
EP3317051B1 (fr) 2020-02-12

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