EP3426442B1 - Hand-held power tool comprising a torque clutch - Google Patents

Hand-held power tool comprising a torque clutch Download PDF

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Publication number
EP3426442B1
EP3426442B1 EP17709619.5A EP17709619A EP3426442B1 EP 3426442 B1 EP3426442 B1 EP 3426442B1 EP 17709619 A EP17709619 A EP 17709619A EP 3426442 B1 EP3426442 B1 EP 3426442B1
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EP
European Patent Office
Prior art keywords
power tool
latching body
transmission element
handheld power
torque
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EP17709619.5A
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German (de)
French (fr)
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EP3426442A1 (en
Inventor
Heiko Roehm
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP3426442A1 publication Critical patent/EP3426442A1/en
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    • 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

Definitions

  • the present invention relates to a hand tool with a gear and a torque clutch, which has a limiting unit assigned to the gear, which is assigned a transmission element acted upon by at least one spring element axially in the direction of the motor, wherein a torque clutch at least has a torque level that can be actuated by a user is adjustable within specified limits.
  • a hand tool is known with a gear designed in the manner of a planetary gear and a torque clutch, which has a limiting unit assigned to the gear for setting a maximum torque level that can be transmitted from the gear to a tool holder of the hand tool.
  • the torque level is set with the help of an assigned adjusting sleeve within specified limits.
  • the torque clutch has a transmission element which is acted upon by a spring element with a predetermined spring force axially in the direction of spherical locking bodies which are assigned to the limiting unit. The spherical locking body is acted upon by the transmission element against a ring gear of the planetary gear.
  • the present invention relates to a hand machine tool with a gear and a torque clutch, which has a limiting unit assigned to the gear and which is assigned a transmission element acted upon by at least one spring element, in particular axially in the direction of the motor, alternatively in the direction of the tool holder, a torque level of the torque clutch being adjustable at least within predefined limits via an operating element which can be actuated by a user.
  • the limiting unit has at least one latching body which engages in the transmission element at least in sections in the axial direction of the torque clutch.
  • the invention thus makes it possible to provide a hand-held power tool in which reliable guidance of the transmission element is ensured.
  • the transmission element which is preferably designed in the manner of a pressure plate, is reliably positioned by the latching bodies both in the radial and in the axial direction, so that the friction and the associated wear are reduced. Furthermore, there is a reduced axial length of the torque clutch with a reduced weight. Due to the reduced weight, less vibrations are generated when the torque clutch is active. Furthermore, there is at least one line contact instead of one point contact between the latching bodies and the pressure plate, as in conventional torque couplings. In addition, the clutch forces are harmonized with an active torque clutch to maximize the service life.
  • the transmission element has at least one recess for axially receiving the at least one latching body at least in sections.
  • the at least one recess is designed in the manner of an opening and the at least one latching body is spherical, the at least one spherical latching body engaging at least in sections in the opening.
  • the spherical locking bodies commonly used as locking bodies can be used, while the openings e.g. can be designed as easy to manufacture, cylindrical bores.
  • a diameter of the at least one recess is smaller than a diameter of the at least one spherical locking body.
  • a diameter of the recess is preferably less than 0.9 times the diameter of the locking body. If necessary. a circumferential edge of the recess can be prismatically chamfered.
  • the at least one recess has a polygonal base area and the at least one latching body is cylindrical, the at least one cylindrical latching body engaging at least in sections in the at least one recess.
  • roller-shaped or roller-shaped locking bodies which, in comparison with spherical locking bodies, permit rectilinear contact with the ring gear.
  • a circumferential width of the at least one recess is smaller than a diameter of the at least one cylindrical locking body.
  • the transmission preferably has at least one ring gear, the limiting unit has at least three latching bodies and a coupling geometry formed on the end face of the ring gear, and the transmission element has at least three cutouts.
  • the coupling geometry is preferred realized with a number of trapezoidal starting ramps corresponding to the number of latching bodies or the cutouts.
  • the transmission element is preferably disc-shaped and has at least three radially inward projections, in each of which one of the at least three recesses is formed.
  • the invention thus enables the torque clutch to be simply switched off.
  • the at least one spring element preferably has at least one compression spring.
  • the transmission is preferably designed in the manner of a planetary transmission and has at least one ring gear, the at least one latching body being axially loaded against the ring gear by means of the transmission element.
  • the at least one latching body is designed to roll on the ring gear.
  • the operating element which can be actuated by the user is preferably designed to enable adjustment of a spring force exerted by the at least one spring element.
  • the control element is preferably designed as a torque adjusting sleeve that can be rotated by the user in relation to the tool housing.
  • Fig. 1 shows an example of a handheld power tool 100 provided with a torque clutch 160.
  • the handheld power tool 100 illustratively has a tool housing 105 with a handle 115.
  • the handheld power tool 100 can be mechanically and electrically connected to a battery pack 210 for the mains-independent power supply.
  • the handheld power tool 100 is designed, for example, as an Acku drill screwdriver, and the battery pack 210 can be permanently installed or exchangeable. It is pointed out, however, that the present invention is not limited to cordless drills, but rather can be used with different hand-held power tools that have a torque clutch corresponding to the torque coupling 160, regardless of whether the hand-held power tool is electrical, that is to say independent of the mains, with the battery pack 210 or network-dependent, and / or non-electrically operable.
  • an electric drive motor 200 which is supplied with current by the battery pack 210, and a transmission 170 are arranged, for example.
  • the drive motor 200 is connected to a drive shaft 120, e.g. a drive spindle.
  • the drive motor 200 is illustratively arranged in a motor housing 202 and the transmission 170 is accommodated in a transmission housing 110, the transmission housing 110 and the motor housing 202 being arranged, for example, in the tool housing 105.
  • the gear 170 is designed to transmit a torque generated by the drive motor 200 to the drive spindle 120 and, according to one embodiment, is a planetary gear 171 which is designed with different gear or planetary stages and which is driven by the drive motor 200 in rotation when the handheld power tool 100 is in operation.
  • the drive motor 200 is e.g. Can be operated via a manual switch 212, i.e. can be switched on and off and can be any type of motor, e.g. an electronically commutated motor or a DC motor.
  • the drive motor 200 is preferably electronically controllable or regulatable in such a way that a reversing operation as well as specifications regarding a desired rotational speed can be implemented.
  • the mode of operation and the construction of a suitable drive motor are sufficiently known from the prior art, so that a detailed description is omitted here for the sake of conciseness of the description.
  • the drive spindle 120 is rotatably mounted in the tool housing 105 via a bearing arrangement 130.
  • the drive spindle 120 is assigned a tool holder 140 which is arranged in the region of an end face 112 of the tool housing 105 and illustratively has a drill chuck 145.
  • the bearing arrangement 130 has at least two bearing points 132, 134 for the rotatable mounting of the drive spindle 120.
  • the tool holder 140 serves to hold an insert tool 150 and can be integrally formed on the drive spindle 120 or connected to it in the form of an attachment.
  • the tool holder 140 is designed as an example and attached to it by means of a fastening device 122 provided on the drive shaft 120 or the drive spindle.
  • the fastening device 122 is designed here as an example as an external thread.
  • the handheld power tool 100 has the torque clutch 160 as described above.
  • This is illustratively equipped with a control element 165 that can be actuated, in particular rotated, by a user of handheld power tool 100.
  • the operating element 165 which can be actuated by the user, is designed to set a torque limitation 160, for example work-specific, desired by the user, or to set a respective torque level of the torque clutch 160, at least within predetermined limits.
  • the operating element 165 of the torque clutch 160 is, for example, sleeve-shaped and is therefore also referred to below as the “torque adjusting sleeve” 165.
  • the torque clutch 160 is described below with respect to that in FIG Fig. 2 Enlarged view of section 220 of handheld power tool 100 explained in more detail.
  • Fig. 2 shows section 220 of handheld power tool 100 from FIG Fig. 1 , wherein, for the sake of simplicity and clarity of the drawing, a representation of the tool holder 140 and the insert tool 150 from FIG Fig. 1 was waived.
  • This section 220 shows, among other things, the gear 170 integrated into the gear housing 110, which is designed here only as an example as a planetary gear 171.
  • the cutout 220 shows the torque clutch 160 arranged at least in sections in the clutch housing 161 and a limiting unit 230 assigned to the planetary gear 171.
  • the planetary gear 171 includes, as an example, a rear drive motor 200 from Fig. 1 facing planetary stage 172 with a sun gear (not shown) which can be driven by the drive motor and three planet gears, of which only two planet gears 174, 175 are visible here.
  • the planet gears 174, 175 of the rear planetary stage 172 are connected to a planet carrier 176.
  • a middle planetary stage 177 comprises three planet wheels connected to a planet carrier 178, of which only one planet wheel 179 is visible here.
  • the planet gears of the middle planetary stage 177 can be driven in rotation by a sun gear 180 formed on the planet carrier 176 of the rear planetary stage 172.
  • a sun wheel 181 formed on the planet carrier 178 of the middle planetary stage 177 in turn drives three planet wheels of a front planetary stage 182, which are connected to a planet carrier 183, of the three planet wheels of the front planetary stage 182 only one planet gear 184 is visible.
  • the planet gears of the front planetary stage 182 are illustratively engaged with an internal toothing 185 of a ring gear 190.
  • the planet carrier 183 of the front planetary stage 182 is connected to the drive shaft 120 or the drive spindle, for example, in a rotationally fixed manner, for example by means of a positive connection.
  • the fastening device 122 for the tool holder 140 of FIG Fig. 1 intended.
  • the drive shaft 120 or the drive spindle is by means of the first and the second bearing 132, 134 as components of the bearing arrangement 130 of Fig. 1 rotatably received in the clutch housing 161, the first bearing 132 being exemplarily designed as a slide bearing 136 and the second bearing 134 as a ball bearing 138.
  • the limiting unit 230 is assigned one of at least one and preferably six spring elements - of which only a single spring element 234 embodied with a compression spring 232 is visible here - in the direction of the planetary gear 171 or in the direction of the drive motor 200 or transmission element 240 or pressure plate.
  • the six spring elements or the compression springs are preferably arranged circumferentially evenly spaced from one another.
  • the preferably at least approximately disk-shaped transmission element 240 and an end face 236 of the ring gear 190 facing the free end 123 of the drive shaft 120 there are likewise at least two, preferably three and preferably six locking bodies - of which only a single spherical locking body 250 is visible. Because of the spring force exerted by the compression springs on the transmission element 240 in the axial direction, the latching body 250 and all the other latching bodies are acted upon against a coupling geometry 252 formed on the end face 236 of the ring gear 190.
  • the compression spring 232 and all other compression springs are clamped on both sides between the transmission element 240 and a spring element holder 238, the compression spring 232 being at least slightly axially preloaded in the axial position of the spring element holder 238 shown here.
  • the operating element 165 assigned to the torque clutch 160 or the torque adjusting sleeve from Fig. 1 is rotatable, but is preferably arranged at least essentially axially immovably on the clutch housing 161.
  • the user can set a maximum torque that can be transmitted by the torque clutch 160 by rotating the operating element 165 or the torque adjusting sleeve, as a result of which the spring element holder 238 can be axially displaced in the direction of a double arrow 300 to vary the axial spring force of the at least one spring element 234.
  • the operating element 165 or the torque adjusting sleeve is preferably coupled in a rotationally fixed manner to an inner, nut-like adjusting ring 242, on which at least one radially inwardly directed engaging element 244 is formed, which engages in an external thread 246 provided on the outside of the clutch housing 161.
  • the thread-like connection between the at least one engagement element 244 and the external thread 246 of the clutch housing 161 preferably serves to guide the adjusting ring 242 on the external thread 246 by rotating the operating element 165 or the torque adjusting sleeve and thus displacing the adjusting ring 242 parallel to the longitudinal direction of the drive shaft 120 or the drive spindle - as indicated by the double arrow 300 - and thereby to vary the spring force of the spring elements or the compression springs within predetermined limits.
  • the transmission element 240 preferably has six recesses, each of which is axially continuous, which are circumferentially evenly spaced from one another and of which only one recess 260 is shown, into which the detent body 250 preferably dips at least in sections.
  • the cutout 260 is designed here only as an example as a circular opening 262 or a cylindrical bore, the diameter D A of which is smaller than a diameter D K of the latching body 250, which is likewise merely an example here.
  • the diameter D A of the cutout 260 is preferably smaller than 0.9 times the diameter of the latching body 250.
  • the latching bodies which axially immerse at least in sections in the transmission element 240, a shorter axial overall length of the torque clutch 160 and a lower weight thereof can be realized. Furthermore there is in particular a reliable radial guidance of the transmission element 240, which is accompanied by a reduction in friction and wear and contributes to an extension of the service life of the hand tool.
  • the circular recesses between the latching bodies and the transmission element 240 each result in a circular contact line or contact zone.
  • the limiting unit 230 is formed with the at least one spring element 234, the transmission element 240, the latching bodies 250 and the coupling geometry 252 on the end face 236 of the ring gear 190.
  • the torque clutch 160 essentially comprises the clutch housing 161, the operating element 165 or the torque adjusting sleeve and the adjusting ring 242 with the at least one engaging element 244 as well as the external thread 246 of the clutch housing interacting with this for transforming the rotary movement of the operating element 165 into a translatory movement of the spring element holder 238 161.
  • a support torque occurs within the planetary gear 171 due to the torque and speed conversion, which is transmitted from the planet gears of the front planetary stage 182 to the ring gear 190.
  • the torque clutch 160 responds when the support torque becomes greater than the holding torque applied by the limiting unit 230, so that the ring gear 190 slips or rotates in the final analysis. In this case, the transmission of speed between the front planetary stage 181 of the planetary gear 171 and the drive shaft 120 is interrupted or disabled and the transmission of torque is limited.
  • the respective holding torque of the limiting unit 230 acting on the ring gear 190 is dependent on the axial position of the spring element holder 238 and thus on the rotational position of the operating element 165.
  • the at least one spring element 234 is largely relaxed, so that the at least one latching body 250 is acted upon by the transmission element 240 with a comparatively small axial spring force against the coupling geometry 252 of the end face 236 of the ring gear 190 of the planetary gear mechanism 171 .
  • the ring gear 190 slips or rotates even at relatively small torques acting on the drive shaft 120 or the drive spindle, and the hand-held power tool is in a "screwing mode".
  • the at least one spring element 234 is more tensioned or compressed, which can be achieved by axially displacing the spring element holder 238 in the direction of the planetary gear 171 or in the direction of the drive motor 200 by turning the control element 165 on the user side, the at least one latching body 250 becomes the transmission element 240 is subjected to a higher spring force against the ring gear 190, which results in a higher holding torque and this begins to slip or spin only at higher torques acting on the drive shaft 120.
  • the at least one latching body 250 is acted upon by the transmission element 240 with such a high axial spring force against the coupling geometry 252 of the end face 236 of the ring gear 190 that it practically no longer slips can and a "drilling mode" of the hand tool is activated, in which a maximum working torque can be tapped on the drive shaft 120.
  • an axial distance between the spring element holder 238 and the transmission element 240 can also be made smaller than corresponding elevations (254 in Fig. 3 ) of the coupling geometry 252.
  • FIG. 12 shows an exploded view of part of section 220 of FIG Fig. 1 or. Fig. 2 . Accordingly, this is essentially hollow cylindrical Ring gear 190 of the limiting unit 230 of the torque clutch 160 via an internal toothing 185 and on the end face 236 of the ring gear 190, the coupling geometry 252 is formed.
  • the coupling geometry 252 here has only six protrusions of the same type, the cross-sectional geometry of which roughly corresponds to that of an isosceles trapezoid and of which two protrusions 254, 256 are designated by way of example.
  • the six elevations which are equally spaced on the circumferential side, face the spherical latching bodies in the axial direction, of which only the latching body 250 and a latching body 251 adjacent to the periphery thereof are also designated for the sake of a better graphic overview.
  • the preferably at least substantially disk-shaped transmission element 240 has a central recess 264, on the inner edge 266 of which six radially inwardly directed and approximately V-shaped projections are formed, of which only two projections 270, 272 are designated for the sake of a better overview of the drawing.
  • the number of projections preferably corresponds to the number of compression springs used. As an alternative to this, for example when using a single drive shaft 120 corresponds to Fig. 1 Concentrically arranged compression spring, the number of projections, the number of locking bodies.
  • Each of the six projections has a recess 260 which completely penetrates the respective projection in the axial direction, the recesses here being designed as circular openings or bores. Of the total of six openings here, only two openings 262, 263 are designated.
  • Each projection serves as a first support or abutment for one compression spring, of which only the compression springs 232 and a further compression spring 233 adjoining the circumference are designated here.
  • the spring element holder 238 represents a second support or abutment for the compression springs.
  • the spring element holder 238 has an approximately circular base body 239, on the inner edge of which is not designated here, for example, six holding webs are formed, of which only two holding webs run parallel to a longitudinal central axis 302 of the torque clutch 160 280, 282 are designated.
  • the retaining webs of the spring element holder 238 are arranged circumferentially evenly spaced from one another on the inner edge of the spring element holder 238.
  • each holding web has a radially inwardly directed, approximately semicircular tab, of which two tabs 284, 286 are designated and which act as a second support or abutment for each of the compression springs.
  • the number of tabs preferably corresponds to the number of compression springs used.
  • the adjusting ring 242 is used to set the axial position of the spring element holder 238 and thus the maximum torque that can be transmitted from the torque clutch 160 until it responds.
  • the setting ring 242 preferably has an approximately hollow cylindrical base body 248 with the engagement element 244 formed on the inside, which is designed here as an internal thread 249. On its outer circumference is a radially outward, cuboid driver 290 for the rotationally fixed coupling of the operating element 165 or the torque adjusting sleeve.
  • Fig. 4 shows section 220 of handheld power tool 100 from FIG Fig. 1 acc. Fig. 2 .
  • the at least one recess 260 now preferably has a polygonal base area 268 and the at least one latching body 250 is preferably cylindrical or roller-shaped and engages at least in sections in the at least one recess 260.
  • a circumferential width of the at least one cutout 260 is preferably smaller than a diameter Dz of the at least one cylindrical or roller-shaped locking body 250, preferably smaller than 0.9 times D z .
  • the circumferential width of the at least one recess 260 defines an expansion of the recess 260 in a possible direction of rotation of the drive spindle 120.
  • the radial extent of the at least one recess 260 is preferably greater than a corresponding cylinder height of the at least one cylindrical or cylindrical locking body 250.

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Description

Stand der TechnikState of the art

Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine mit einem Getriebe und einer Drehmomentkupplung, die eine dem Getriebe zugeordnete Begrenzungseinheit aufweist, der ein von mindestens einem Federelement axial in Richtung des Motors beaufschlagtes Übertragungselement zugeordnet ist, wobei eine Momentenhöhe der Drehmomentkupplung über ein von einem Benutzer betätigbares Bedienelement zumindest innerhalb vorgegebener Grenzen einstellbar ist.The present invention relates to a hand tool with a gear and a torque clutch, which has a limiting unit assigned to the gear, which is assigned a transmission element acted upon by at least one spring element axially in the direction of the motor, wherein a torque clutch at least has a torque level that can be actuated by a user is adjustable within specified limits.

Aus der DE 10 2009 046 663 A1 ist eine Handwerkzeugmaschine mit einem nach Art eines Planetengetriebes ausgebildeten Getriebe und einer Drehmomentkupplung bekannt, die eine dem Getriebe zugeordnete Begrenzungseinheit zum Einstellen einer maximalen, vom Getriebe auf eine Werkzeugaufnahme der Handwerkzeugmaschine übertragbaren Momentenhöhe aufweist. Die Einstellung der Momentenhöhe erfolgt mit Hilfe einer zugeordneten Einstellhülse innerhalb von vorgegebenen Grenzen. Die Drehmomentkupplung weist ein Übertragungselement auf, das von einem Federelement mit einer vorgegebenen Federkraft axial in Richtung von kugelförmigen Rastkörpern beaufschlagt wird, die der Begrenzungseinheit zugeordnet sind. Die kugelförmigen Rastkörper werden von dem Übertragungselement gegen ein Hohlrad des Planetengetriebes beaufschlagt.From the DE 10 2009 046 663 A1 A hand tool is known with a gear designed in the manner of a planetary gear and a torque clutch, which has a limiting unit assigned to the gear for setting a maximum torque level that can be transmitted from the gear to a tool holder of the hand tool. The torque level is set with the help of an assigned adjusting sleeve within specified limits. The torque clutch has a transmission element which is acted upon by a spring element with a predetermined spring force axially in the direction of spherical locking bodies which are assigned to the limiting unit. The spherical locking body is acted upon by the transmission element against a ring gear of the planetary gear.

In der EP 2 777 891 A1 wird eine Kupplung für eine Handwerkzeugmaschine mit einem Einstellring offenbart.In the EP 2 777 891 A1 discloses a clutch for a hand tool with an adjusting ring.

Aus der US 2011/127059 A1 ist eine Handwerkzeugmaschine mit einem Kupplungsmechanismus bekannt.From the US 2011/127059 A1 a hand tool with a clutch mechanism is known.

Offenbarung der ErfindungDisclosure of the invention

Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine mit einem Getriebe und einer Drehmomentkupplung, die eine dem Getriebe zugeordnete Begrenzungseinheit aufweist und der ein von mindestens einem Federelement, insbesondere axial in Richtung des Motors, alternativ in Richtung der Werkzeugaufnahme, beaufschlagtes Übertragungselement zugeordnet ist, wobei eine Momentenhöhe der Drehmomentkupplung über ein von einem Benutzer betätigbares Bedienelement zumindest innerhalb vorgegebener Grenzen einstellbar ist. Die Begrenzungseinheit weist mindestens einen Rastkörper auf, der in axialer Richtung der Drehmomentkupplung zumindest abschnittsweise in das Übertragungselement eingreift.The present invention relates to a hand machine tool with a gear and a torque clutch, which has a limiting unit assigned to the gear and which is assigned a transmission element acted upon by at least one spring element, in particular axially in the direction of the motor, alternatively in the direction of the tool holder, a torque level of the torque clutch being adjustable at least within predefined limits via an operating element which can be actuated by a user. The limiting unit has at least one latching body which engages in the transmission element at least in sections in the axial direction of the torque clutch.

Die Erfindung ermöglicht somit die Bereitstellung einer Handwerkzeugmaschine, bei der eine zuverlässige Führung des Übertragungselements gewährleistet ist. Das bevorzugt nach Art eines Druckblechs ausgebildete Übertragungselement ist durch die Rastkörper sowohl in radialer als auch in axialer Richtung zuverlässig positioniert, so dass sich die Reibung und damit einhergehend der Verschleiß verringern. Ferner ergibt sich eine reduzierte axiale Baulänge der Drehmomentkupplung bei einem zugleich reduzierten Gewicht. Aufgrund des verminderten Gewichts werden bei aktiver Drehmomentkupplung weniger Vibrationen hervorgerufen. Weiterhin besteht zwischen den Rastkörpern und dem Druckblech jeweils mindestens ein Linienkontakt anstelle eines Punktkontaktes, wie bei herkömmlichen Drehmomentkupplungen. Darüber hinaus werden die Kupplungskräfte bei aktiver Drehmomentkupplung zur Maximierung der Lebensdauer harmonisiert.The invention thus makes it possible to provide a hand-held power tool in which reliable guidance of the transmission element is ensured. The transmission element, which is preferably designed in the manner of a pressure plate, is reliably positioned by the latching bodies both in the radial and in the axial direction, so that the friction and the associated wear are reduced. Furthermore, there is a reduced axial length of the torque clutch with a reduced weight. Due to the reduced weight, less vibrations are generated when the torque clutch is active. Furthermore, there is at least one line contact instead of one point contact between the latching bodies and the pressure plate, as in conventional torque couplings. In addition, the clutch forces are harmonized with an active torque clutch to maximize the service life.

Das Übertragungselement weist mindestens eine Aussparung zur zumindest abschnittsweise axialen Aufnahme des mindestens einen Rastkörpers auf.The transmission element has at least one recess for axially receiving the at least one latching body at least in sections.

Hierdurch ergibt sich eine verlässliche Lagesicherung des Übertragungselements mittels der Rastkörper.This results in a reliable position securing of the transmission element by means of the locking body.

Gemäß einer Ausführungsform ist die mindestens eine Aussparung nach Art einer Öffnung ausgebildet und der mindestens eine Rastkörper ist kugelförmig ausgebildet, wobei der mindestens eine kugelförmige Rastkörper zumindest abschnittsweise in die Öffnung eingreift.According to one embodiment, the at least one recess is designed in the manner of an opening and the at least one latching body is spherical, the at least one spherical latching body engaging at least in sections in the opening.

Hierdurch können die gebräuchlicherweise als Rastkörper verwendeten, kugelförmigen Rastkörper Anwendung finden, während die Öffnungen z.B. als leicht zu fertigende, zylindrische Bohrungen ausgeführt sein können.As a result, the spherical locking bodies commonly used as locking bodies can be used, while the openings e.g. can be designed as easy to manufacture, cylindrical bores.

Erfindungsgemäß ist ein Durchmesser der mindestens einen Aussparung kleiner als ein Durchmesser des mindestens einen kugelförmigen Rastkörpers.According to the invention, a diameter of the at least one recess is smaller than a diameter of the at least one spherical locking body.

Infolgedessen kann sich der mindestens eine Rastkörper in axialer Richtung nicht durch das Übertragungselement hindurchdrücken. Ein Durchmesser der Aussparung ist vorzugsweise kleiner als das 0,9-fache des Durchmessers des Rastkörpers. Ggfls. kann ein umlaufender Rand der Aussparung prismatisch angefast sein.As a result, the at least one latching body cannot push through the transmission element in the axial direction. A diameter of the recess is preferably less than 0.9 times the diameter of the locking body. If necessary. a circumferential edge of the recess can be prismatically chamfered.

Gemäß einer weiteren Ausführungsform weist die mindestens eine Aussparung eine mehreckige Grundfläche auf und der mindestens eine Rastkörper ist zylinderförmig ausgebildet, wobei der mindestens eine zylinderförmige Rastkörper zumindest abschnittsweise in die mindestens eine Aussparung eingreift.According to a further embodiment, the at least one recess has a polygonal base area and the at least one latching body is cylindrical, the at least one cylindrical latching body engaging at least in sections in the at least one recess.

Hierdurch können auch walzenförmige bzw. rollenförmige Rastkörper zum Einsatz kommen, die im Vergleich zu kugelförmigen Rastkörpern einen geradlinigen Kontakt mit dem Hohlrad ermöglichen.As a result, it is also possible to use roller-shaped or roller-shaped locking bodies which, in comparison with spherical locking bodies, permit rectilinear contact with the ring gear.

Erfindungsgemäß ist eine umfangsseitige Breite der mindestens einen Aussparung kleiner als ein Durchmesser des mindestens einen zylinderförmigen Rastkörpers.According to the invention, a circumferential width of the at least one recess is smaller than a diameter of the at least one cylindrical locking body.

Hierdurch wird ein etwaiges Hindurchdrücken und damit unter Umständen einhergehendes Verklemmen des mindestens einen Rastkörpers innerhalb des Übertragungselements verhindert.This prevents any pushing through and possibly jamming of the at least one latching body within the transmission element.

Bevorzugt weist das Getriebe mindestens ein Hohlrad auf, die Begrenzungseinheit weist mindestens drei Rastkörper sowie eine stirnseitig an dem Hohlrad ausgebildete Kopplungsgeometrie auf und das Übertragungselement weist mindestens drei Aussparungen auf.The transmission preferably has at least one ring gear, the limiting unit has at least three latching bodies and a coupling geometry formed on the end face of the ring gear, and the transmission element has at least three cutouts.

Infolgedessen wird eine umfangsseitig gleichmäßige Abstützung des Übertragungselements in axialer Richtung erzielt. Die Kopplungsgeometrie ist bevorzugt mit einer der Anzahl der Rastkörper bzw. der Aussparungen entsprechenden Anzahl von trapezförmigen Anlauframpen realisiert.As a result, uniform support on the circumference of the transmission element is achieved in the axial direction. The coupling geometry is preferred realized with a number of trapezoidal starting ramps corresponding to the number of latching bodies or the cutouts.

Vorzugsweise ist das Übertragungselement scheibenförmig ausgebildet und weist mindestens drei radial einwärts gerichtete Vorsprünge auf, in denen jeweils eine der mindestens drei Aussparungen ausgebildet ist.The transmission element is preferably disc-shaped and has at least three radially inward projections, in each of which one of the at least three recesses is formed.

Die Erfindung ermöglicht somit ein einfaches Abschalten der Drehmomentkupplung.The invention thus enables the torque clutch to be simply switched off.

Bevorzugt weist das mindestens eine Federelement mindestens eine Druckfeder auf.The at least one spring element preferably has at least one compression spring.

Hierdurch ist eine umfangsseitig gleichmäßige Kraftbeaufschlagung gegeben.This results in a uniform application of force on the circumference.

Vorzugsweise ist das Getriebe nach Art eines Planetengetriebes ausgebildet und weist mindestens ein Hohlrad auf, wobei der mindestens eine Rastkörper mittels des Übertragungselements gegen das Hohlrad axial kraftbeaufschlagt ist.The transmission is preferably designed in the manner of a planetary transmission and has at least one ring gear, the at least one latching body being axially loaded against the ring gear by means of the transmission element.

Hierdurch ist eine konstruktiv einfache Realisierung der Drehmomentkupplung möglich.This enables a structurally simple implementation of the torque clutch.

Nach Maßgabe einer Weiterbildung ist der mindestens eine Rastkörper zum Abrollen an dem Hohlrad ausgebildet.According to a further development, the at least one latching body is designed to roll on the ring gear.

Hierdurch ergibt sich ein weitgehend geräusch- und verschleißarmer Betrieb der aktiven Drehmomentkupplung.This results in a largely low-noise and low-wear operation of the active torque clutch.

Vorzugsweise ist das von dem Benutzer betätigbare Bedienelement dazu ausgebildet, eine Einstellung einer von dem mindestens einen Federelement ausgeübten Federkraft zu ermöglichen.The operating element which can be actuated by the user is preferably designed to enable adjustment of a spring force exerted by the at least one spring element.

Infolgedessen kann die Momenthöhe einem jeweiligen Anwendungsszenario angepasst werden. Das Bedienelement ist bevorzugt als eine in Bezug zum Werkzeuggehäuse benutzerseitig verdrehbare Momenteneinstellhülse ausgeführt.As a result, the moment height can be adapted to a respective application scenario. The control element is preferably designed as a torque adjusting sleeve that can be rotated by the user in relation to the tool housing.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Die Erfindung ist anhand von in den Zeichnungen dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
eine schematische Ansicht einer Handwerkzeugmaschine mit einer Drehmomentkupplung gemäß einer Ausführungsform,
Fig. 2
eine Schnittansicht eines Ausschnitts 220 der Handwerkzeugmaschine von Fig. 1 mit einem Übertragungselement gemäß einer ersten Ausführungsform,
Fig. 3
eine Explosionsansicht eines Teils des Ausschnitts 220 von Fig. 1, und
Fig. 4
die Schnittansicht von Fig. 2 mit einem Übertragungselement gemäß einer zweiten Ausführungsform.
The invention is explained in more detail in the following description with reference to exemplary embodiments shown in the drawings. Show it:
Fig. 1
1 shows a schematic view of a hand tool with a torque clutch according to one embodiment,
Fig. 2
a sectional view of a section 220 of the hand tool of FIG Fig. 1 with a transmission element according to a first embodiment,
Fig. 3
an exploded view of a portion of section 220 of FIG Fig. 1 , and
Fig. 4
the sectional view of Fig. 2 with a transmission element according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Fig. 1 zeigt beispielhaft eine mit einer Drehmomentkupplung 160 versehene Handwerkzeugmaschine 100. Die Handwerkzeugmaschine 100 weist illustrativ ein Werkzeuggehäuse 105 mit einem Handgriff 115 auf. Fig. 1 shows an example of a handheld power tool 100 provided with a torque clutch 160. The handheld power tool 100 illustratively has a tool housing 105 with a handle 115.

Gemäß einer Ausführungsform ist die Handwerkzeugmaschine 100 zur netzunabhängigen Stromversorgung mechanisch und elektrisch mit einem Akkupack 210 verbindbar. In Fig. 1 ist die Handwerkzeugmaschine 100 beispielhaft als Acku-Bohrschrauber ausgebildet, wobei der Akkupack 210 festverbaut oder austauschbar sein kann. Es wird jedoch darauf hingewiesen, dass die vorliegende Erfindung nicht auf Akku-Bohrschrauber beschränkt ist, sondern vielmehr bei unterschiedlichen Handwerkzeugmaschinen Anwendung finden kann, die eine der Drehmomentkupplung 160 entsprechende Drehmomentkupplung aufweisen, unabhängig davon, ob die Handwerkzeugmaschine elektrisch, d.h. netzunabhängig mit dem Akkupack 210 oder netzabhängig, und/oder nicht-elektrisch betreibbar ist.According to one embodiment, the handheld power tool 100 can be mechanically and electrically connected to a battery pack 210 for the mains-independent power supply. In Fig. 1 The handheld power tool 100 is designed, for example, as an Acku drill screwdriver, and the battery pack 210 can be permanently installed or exchangeable. It is pointed out, however, that the present invention is not limited to cordless drills, but rather can be used with different hand-held power tools that have a torque clutch corresponding to the torque coupling 160, regardless of whether the hand-held power tool is electrical, that is to say independent of the mains, with the battery pack 210 or network-dependent, and / or non-electrically operable.

In dem Werkzeuggehäuse 105 sind beispielhaft ein von dem Akkupack 210 mit Strom versorgter, elektrischer Antriebsmotor 200 und ein Getriebe 170 angeordnet. Der Antriebsmotor 200 ist über das Getriebe 170 mit einer Antriebswelle 120, z.B. einer Antriebsspindel, verbunden. Der Antriebsmotor 200 ist illustrativ in einem Motorgehäuse 202 angeordnet und das Getriebe 170 ist in einem Getriebegehäuse 110 untergebracht, wobei das Getriebegehäuse 110 und das Motorgehäuse 202 beispielhaft in dem Werkzeuggehäuse 105 angeordnet sind.In the tool housing 105, an electric drive motor 200, which is supplied with current by the battery pack 210, and a transmission 170 are arranged, for example. The drive motor 200 is connected to a drive shaft 120, e.g. a drive spindle. The drive motor 200 is illustratively arranged in a motor housing 202 and the transmission 170 is accommodated in a transmission housing 110, the transmission housing 110 and the motor housing 202 being arranged, for example, in the tool housing 105.

Das Getriebe 170 ist zur Übertragung eines von dem Antriebsmotor 200 erzeugten Drehmoments auf die Antriebsspindel 120 ausgebildet und gemäß einer Ausführungsform ein mit verschiedenen Gang- bzw. Planetenstufen ausgebildetes Planetengetriebe 171, das im Betrieb der Handwerkzeugmaschine 100 vom Antriebsmotor 200 drehend angetrieben wird. Der Antriebsmotor 200 ist z.B. über einen Handschalter 212 betätigbar, d.h. ein- und ausschaltbar, und kann ein beliebiger Motortyp sein, z.B. ein elektronisch kommutierter Motor oder ein Gleichstrommotor. Vorzugsweise ist der Antriebsmotor 200 derart elektronisch steuer- bzw. regelbar, dass sowohl ein Reversierbetrieb, als auch Vorgaben hinsichtlich einer gewünschten Drehgeschwindigkeit realisierbar sind. Die Funktionsweise und der Aufbau eines geeigneten Antriebsmotors sind aus dem Stand der Technik hinreichend bekannt, sodass hier zwecks Knappheit der Beschreibung auf eine eingehende Beschreibung verzichtet wird.The gear 170 is designed to transmit a torque generated by the drive motor 200 to the drive spindle 120 and, according to one embodiment, is a planetary gear 171 which is designed with different gear or planetary stages and which is driven by the drive motor 200 in rotation when the handheld power tool 100 is in operation. The drive motor 200 is e.g. Can be operated via a manual switch 212, i.e. can be switched on and off and can be any type of motor, e.g. an electronically commutated motor or a DC motor. The drive motor 200 is preferably electronically controllable or regulatable in such a way that a reversing operation as well as specifications regarding a desired rotational speed can be implemented. The mode of operation and the construction of a suitable drive motor are sufficiently known from the prior art, so that a detailed description is omitted here for the sake of conciseness of the description.

Die Antriebsspindel 120 ist über eine Lageranordnung 130 drehbar im Werkzeuggehäuse 105 gelagert. Der Antriebsspindel 120 ist eine Werkzeugaufnahme 140 zugeordnet, die im Bereich einer Stirnseite 112 des Werkzeuggehäuses 105 angeordnet ist und illustrativ ein Bohrfutter 145 aufweist. Die Lageranordnung 130 weist gemäß einer Ausführungsform mindestens zwei Lagerstellen 132, 134 zur drehbeweglichen Lagerung der Antriebsspindel 120 auf.The drive spindle 120 is rotatably mounted in the tool housing 105 via a bearing arrangement 130. The drive spindle 120 is assigned a tool holder 140 which is arranged in the region of an end face 112 of the tool housing 105 and illustratively has a drill chuck 145. According to one embodiment, the bearing arrangement 130 has at least two bearing points 132, 134 for the rotatable mounting of the drive spindle 120.

Die Werkzeugaufnahme 140 dient zur Aufnahme eines Einsatzwerkzeugs 150 und kann an die Antriebsspindel 120 angeformt sein oder aufsatzförmig mit dieser verbunden sein. In Fig. 1 ist die Werkzeugaufnahme 140 beispielhaft aufsatzartig ausgebildet und mittels einer an der Antriebswelle 120 bzw. der Antriebsspindel vorgesehenen Befestigungsvorrichtung 122 an dieser befestigt. Die Befestigungsvorrichtung 122 ist hier exemplarisch als Außengewinde ausgeführt.The tool holder 140 serves to hold an insert tool 150 and can be integrally formed on the drive spindle 120 or connected to it in the form of an attachment. In Fig. 1 The tool holder 140 is designed as an example and attached to it by means of a fastening device 122 provided on the drive shaft 120 or the drive spindle. The fastening device 122 is designed here as an example as an external thread.

Gemäß einer Ausführungsform weist die Handwerkzeugmaschine 100 wie oben beschrieben die Drehmomentkupplung 160 auf. Diese ist illustrativ mit einem von einem Benutzer der Handwerkzeugmaschine 100 betätigbaren, insbesondere verdrehbaren Bedienelement 165 ausgestattet. Das von dem Benutzer betätigbare Bedienelement 165 ist zur Einstellung einer von dem Benutzer jeweils gewünschten, z.B. arbeitsspezifischen Drehmomentbegrenzung durch die Drehmomentkupplung 160 bzw. zur Einstellung einer jeweiligen Momentenhöhe der Drehmomentkupplung 160, zumindest innerhalb vorgegebener Grenzen, ausgebildet. Hierbei ist das Bedienelement 165 der Drehmomentkupplung 160 beispielhaft hülsenförmig ausgebildet und wird deshalb nachfolgend auch als die "Momenteneinstellhülse" 165 bezeichnet. Die Drehmomentkupplung 160 wird nachfolgend in Bezug auf die in Fig. 2 vergrößert dargestellte Ansicht des Ausschnitts 220 der Handwerkzeugmaschine 100 eingehender erläutert.According to one embodiment, the handheld power tool 100 has the torque clutch 160 as described above. This is illustratively equipped with a control element 165 that can be actuated, in particular rotated, by a user of handheld power tool 100. The operating element 165, which can be actuated by the user, is designed to set a torque limitation 160, for example work-specific, desired by the user, or to set a respective torque level of the torque clutch 160, at least within predetermined limits. Here, the operating element 165 of the torque clutch 160 is, for example, sleeve-shaped and is therefore also referred to below as the “torque adjusting sleeve” 165. The torque clutch 160 is described below with respect to that in FIG Fig. 2 Enlarged view of section 220 of handheld power tool 100 explained in more detail.

Fig. 2 zeigt den Ausschnitt 220 der Handwerkzeugmaschine 100 von Fig. 1, wobei zwecks Einfachheit und Übersichtlichkeit der Zeichnung auf eine Darstellung der Werkzeugaufnahme 140 und des Einsatzwerkzeugs 150 von Fig. 1 verzichtet wurde. Dieser Ausschnitt 220 zeigt unter anderem das in das Getriebegehäuse 110 integrierte Getriebe 170, das hier lediglich exemplarisch als ein Planetengetriebe 171 ausgeführt ist. Darüber hinaus zeigt der Ausschnitt 220 die zumindest abschnittsweise im Kupplungsgehäuse 161 angeordnete Drehmomentkupplung 160 sowie eine dem Planetengetriebe 171 zugeordnete Begrenzungseinheit 230. Fig. 2 shows section 220 of handheld power tool 100 from FIG Fig. 1 , wherein, for the sake of simplicity and clarity of the drawing, a representation of the tool holder 140 and the insert tool 150 from FIG Fig. 1 was waived. This section 220 shows, among other things, the gear 170 integrated into the gear housing 110, which is designed here only as an example as a planetary gear 171. In addition, the cutout 220 shows the torque clutch 160 arranged at least in sections in the clutch housing 161 and a limiting unit 230 assigned to the planetary gear 171.

Das Planetengetriebe 171 umfasst exemplarisch eine hintere, dem Antriebsmotor 200 von Fig. 1 zugewandte Planetenstufe 172 mit einem nicht dargestellten, vom Antriebsmotor drehend antreibbaren Sonnenrad und drei Planetenrädern, von denen hier lediglich zwei Planetenräder 174, 175 sichtbar sind. Die Planetenräder 174, 175 der hinteren Planetenstufe 172 sind mit einem Planetenträger 176 verbunden. Eine mittlere Planetenstufe 177 umfasst drei mit einem Planetenträger 178 verbundene Planetenräder, von denen hier lediglich ein Planetenrad 179 sichtbar ist. Die Planetenräder der mittleren Planetenstufe 177 sind von einem an dem Planetenträger 176 der hinteren Planetenstufe 172 ausgebildeten Sonnenrad 180 drehend antreibbar. Ein an dem Planetenträger 178 der mittleren Planetenstufe 177 ausgebildetes Sonnenrad 181 treibt seinerseits wiederum drei Planetenräder einer vorderen Planetenstufe 182 an, die mit einem Planetenträger 183 verbunden sind, wobei von den drei Planetenrädern der vorderen Planetenstufe 182 lediglich ein Planetenrad 184 sichtbar ist. Die Planetenräder der vorderen Planetenstufe 182 stehen illustrativ im Eingriff mit einer Innenverzahnung 185 eines Hohlrads 190. Der Planetenträger 183 der vorderen Planetenstufe 182 ist exemplarisch drehfest, beispielsweise mittels einer Formschlussverbindung, mit der Antriebswelle 120 bzw. der Antriebsspindel verbunden.The planetary gear 171 includes, as an example, a rear drive motor 200 from Fig. 1 facing planetary stage 172 with a sun gear (not shown) which can be driven by the drive motor and three planet gears, of which only two planet gears 174, 175 are visible here. The planet gears 174, 175 of the rear planetary stage 172 are connected to a planet carrier 176. A middle planetary stage 177 comprises three planet wheels connected to a planet carrier 178, of which only one planet wheel 179 is visible here. The planet gears of the middle planetary stage 177 can be driven in rotation by a sun gear 180 formed on the planet carrier 176 of the rear planetary stage 172. A sun wheel 181 formed on the planet carrier 178 of the middle planetary stage 177 in turn drives three planet wheels of a front planetary stage 182, which are connected to a planet carrier 183, of the three planet wheels of the front planetary stage 182 only one planet gear 184 is visible. The planet gears of the front planetary stage 182 are illustratively engaged with an internal toothing 185 of a ring gear 190. The planet carrier 183 of the front planetary stage 182 is connected to the drive shaft 120 or the drive spindle, for example, in a rotationally fixed manner, for example by means of a positive connection.

An einem freien Ende 123 der Antriebswelle 120 ist beispielhaft die Befestigungsvorrichtung 122 für die Werkzeugaufnahme 140 von Fig. 1 vorgesehen. Die Antriebswelle 120 bzw. die Antriebsspindel ist mittels der ersten und der zweiten Lagerstelle 132, 134 als Bestandteile der Lageranordnung 130 von Fig. 1 drehbar im Kupplungsgehäuse 161 aufgenommen, wobei die erste Lagerstelle 132 exemplarisch als ein Gleitlager 136 und die zweite Lagerstelle 134 als ein Kugellager 138 ausgebildet ist.At a free end 123 of the drive shaft 120, the fastening device 122 for the tool holder 140 of FIG Fig. 1 intended. The drive shaft 120 or the drive spindle is by means of the first and the second bearing 132, 134 as components of the bearing arrangement 130 of Fig. 1 rotatably received in the clutch housing 161, the first bearing 132 being exemplarily designed as a slide bearing 136 and the second bearing 134 as a ball bearing 138.

Der Begrenzungseinheit 230 ist ein von mindestens einem und bevorzugt sechs Federelementen - von denen hier lediglich exemplarisch ein einzelnes mit einer Druckfeder 232 ausgeführtes Federelement 234 sichtbar ist - in Richtung des Planetengetriebes 171 bzw. in Richtung des Antriebsmotors 200 beaufschlagtes Übertragungselement 240 bzw. Druckblech zugeordnet. Vorzugsweise sind die sechs Federelemente bzw. die Druckfedern umfangsseitig gleichmäßig zueinander beabstandet angeordnet.The limiting unit 230 is assigned one of at least one and preferably six spring elements - of which only a single spring element 234 embodied with a compression spring 232 is visible here - in the direction of the planetary gear 171 or in the direction of the drive motor 200 or transmission element 240 or pressure plate. The six spring elements or the compression springs are preferably arranged circumferentially evenly spaced from one another.

Zwischen dem vorzugsweise zumindest näherungsweise scheibenförmigen Übertragungselement 240 und einer dem freien Ende 123 der Antriebswelle 120 zugewandten Stirnseite 236 des Hohlrads 190 sind gleichfalls mindestens zwei, vorzugsweise drei und bevorzugt sechs Rastkörper - von denen hier lediglich ein einzelner kugelförmiger Rastkörper 250 sichtbar ist - angeordnet. Aufgrund der von den Druckfedern auf das Übertragungselement 240 in axialer Richtung ausgeübten Federkraft, werden der Rastkörper 250 sowie alle übrigen Rastkörper gegen eine an der Stirnseite 236 des Hohlrads 190 ausgeformte Kopplungsgeometrie 252 beaufschlagt. Die Druckfeder 232 sowie alle weiteren Druckfedern sind zwischen dem Übertragungselement 240 und einem Federelementhalter 238 beidseitig eingespannt, wobei die Druckfeder 232 in der hier gezeigten axialen Position des Federelementhalters 238 unter einer zumindest geringfügigen axialen Vorspannung steht.Between the preferably at least approximately disk-shaped transmission element 240 and an end face 236 of the ring gear 190 facing the free end 123 of the drive shaft 120 there are likewise at least two, preferably three and preferably six locking bodies - of which only a single spherical locking body 250 is visible. Because of the spring force exerted by the compression springs on the transmission element 240 in the axial direction, the latching body 250 and all the other latching bodies are acted upon against a coupling geometry 252 formed on the end face 236 of the ring gear 190. The compression spring 232 and all other compression springs are clamped on both sides between the transmission element 240 and a spring element holder 238, the compression spring 232 being at least slightly axially preloaded in the axial position of the spring element holder 238 shown here.

Das der Drehmomentkupplung 160 zugeordnete Bedienelement 165 bzw. die Drehmomenteinstellhülse von Fig. 1 ist verdrehbar, bevorzugt jedoch zumindest im Wesentlichen axial unbeweglich am Kupplungsgehäuse 161 angeordnet. Das Einstellen eines von der Drehmomentkupplung 160 maximal übertragbaren Drehmoments erfolgt durch das Verdrehen des Bedienelements 165 bzw. der Drehmomenteinstellhülse seitens des Benutzers, wodurch der Federelementhalter 238 zur Variation der axialen Federkraft des mindestens einen Federelements 234 in Richtung eines Doppelpfeils 300 axial verschiebbar ist.The operating element 165 assigned to the torque clutch 160 or the torque adjusting sleeve from Fig. 1 is rotatable, but is preferably arranged at least essentially axially immovably on the clutch housing 161. The user can set a maximum torque that can be transmitted by the torque clutch 160 by rotating the operating element 165 or the torque adjusting sleeve, as a result of which the spring element holder 238 can be axially displaced in the direction of a double arrow 300 to vary the axial spring force of the at least one spring element 234.

Das Bedienelement 165 bzw. die Drehmomenteinstellhülse ist bevorzugt drehfest mit einem innenliegenden, mutterartigen Einstellring 242 gekoppelt, an dem mindestens ein radial einwärts gerichtetes Eingreifelement 244 ausgebildet ist, das in ein außenumfänglich am Kupplungsgehäuse 161 vorgesehenes Außengewinde 246 eingreift. Die gewindeartige Verbindung zwischen dem mindestens einen Eingreifelement 244 und dem Außengewinde 246 des Kupplungsgehäuses 161 dient vorzugsweise dazu, durch eine Verdrehung des Bedienelements 165 bzw. der Drehmomenteinstellhülse den Einstellring 242 am Außengewinde 246 zu führen und somit eine Verschiebung des Einstellrings 242 parallel zur Längsrichtung der Antriebswelle 120 bzw. der Antriebsspindel - wie mit dem Doppelpfeil 300 angedeutet - zu bewirken und hierdurch die Federkraft der Federelemente bzw. der Druckfedern in vorgegebenen Grenzen zu variieren.The operating element 165 or the torque adjusting sleeve is preferably coupled in a rotationally fixed manner to an inner, nut-like adjusting ring 242, on which at least one radially inwardly directed engaging element 244 is formed, which engages in an external thread 246 provided on the outside of the clutch housing 161. The thread-like connection between the at least one engagement element 244 and the external thread 246 of the clutch housing 161 preferably serves to guide the adjusting ring 242 on the external thread 246 by rotating the operating element 165 or the torque adjusting sleeve and thus displacing the adjusting ring 242 parallel to the longitudinal direction of the drive shaft 120 or the drive spindle - as indicated by the double arrow 300 - and thereby to vary the spring force of the spring elements or the compression springs within predetermined limits.

Das Übertragungselement 240 weist in der hier illustrierten ersten Ausführungsform vorzugsweise sechs, jeweils axial durchgehend ausgeführte Aussparungen auf, die umfangsseitig gleichmäßig zueinander beabstandet angeordnet sind und von denen hier lediglich eine Aussparung 260 dargestellt ist, in die der Rastkörper 250 bevorzugt zumindest abschnittsweise eintaucht. Die Aussparung 260 ist hier lediglich exemplarisch als eine kreisrunde Öffnung 262 bzw. eine zylindrische Bohrung ausgeführt, deren Durchmesser DA kleiner als ein Durchmesser DK des hier gleichfalls lediglich exemplarisch kugelförmigen Rastkörpers 250 ist. Bevorzugt ist der Durchmesser DA der Aussparung 260 kleiner als das 0,9-fache des Durchmessers des Rastkörpers 250.In the first embodiment illustrated here, the transmission element 240 preferably has six recesses, each of which is axially continuous, which are circumferentially evenly spaced from one another and of which only one recess 260 is shown, into which the detent body 250 preferably dips at least in sections. The cutout 260 is designed here only as an example as a circular opening 262 or a cylindrical bore, the diameter D A of which is smaller than a diameter D K of the latching body 250, which is likewise merely an example here. The diameter D A of the cutout 260 is preferably smaller than 0.9 times the diameter of the latching body 250.

Aufgrund der axial zumindest abschnittsweise in das Übertragungselement 240 eintauchenden Rastkörper ist eine kürzere axiale Baulänge der Drehmomentkupplung 160 sowie ein geringeres Gewicht derselben realisierbar. Darüber hinaus ist insbesondere eine verlässliche radiale Führung des Übertragungselements 240 gegeben, was mit einer Reibungs- und Verschleißminderung einhergeht und zu einer Lebensdauerverlängerung der Handwerkzeugmaschine beiträgt. Daneben ergibt sich durch die runden Aussparungen zwischen den Rastkörpern und dem Übertragungselement 240 jeweils eine kreisförmige Kontaktlinie bzw. Berührzone. Es sei nochmals darauf hingewiesen, dass abweichend von den hier lediglich exemplarisch angeführten sechs Federelementen, den sechs Rastkörpern sowie den hiermit korrespondierend sechs Aussparungen als Teile der Begrenzungseinheit 230 eine hiervon abweichende Anzahl von Federelementen, Rastkörpern und Aussparungen vorgesehen sein kann, wobei die Anzahl der Rastkörper und Aussparungen jedoch jeweils gleich groß gewählt sein sollte.On account of the latching bodies which axially immerse at least in sections in the transmission element 240, a shorter axial overall length of the torque clutch 160 and a lower weight thereof can be realized. Furthermore there is in particular a reliable radial guidance of the transmission element 240, which is accompanied by a reduction in friction and wear and contributes to an extension of the service life of the hand tool. In addition, the circular recesses between the latching bodies and the transmission element 240 each result in a circular contact line or contact zone. It should be pointed out again that, deviating from the six spring elements, the six latching bodies as well as the corresponding six recesses as parts of the delimiting unit 230, a number of spring elements, latching bodies and recesses which differ from this can be provided, the number of latching bodies and cutouts should be chosen the same size.

Im Kontext der vorliegenden Erfindung ist die Begrenzungseinheit 230 mit dem mindestens einen Federelement 234, dem Übertragungselement 240, den Rastkörpern 250 sowie der Kopplungsgeometrie 252 an der Stirnseite 236 des Hohlrads 190 gebildet. Die Drehmomentkupplung 160 umfasst im Wesentlichen das Kupplungsgehäuse 161, das Bedienelement 165 bzw. die Drehmomenteinstellhülse sowie den Einstellring 242 mit dem mindestens einen Eingreifelement 244 sowie das mit diesem zur Transformation der Drehbewegung des Bedienelements 165 in eine translatorische Bewegung des Federelementhalters 238 zusammenwirkende Außengewinde 246 des Kupplungsgehäuses 161.In the context of the present invention, the limiting unit 230 is formed with the at least one spring element 234, the transmission element 240, the latching bodies 250 and the coupling geometry 252 on the end face 236 of the ring gear 190. The torque clutch 160 essentially comprises the clutch housing 161, the operating element 165 or the torque adjusting sleeve and the adjusting ring 242 with the at least one engaging element 244 as well as the external thread 246 of the clutch housing interacting with this for transforming the rotary movement of the operating element 165 into a translatory movement of the spring element holder 238 161.

Innerhalb des Planetengetriebes 171 fällt durch die Drehmoment- und Drehzahlwandlung ein Abstützdrehmoment an, das von den Planetenrädern der vorderen Planetenstufe 182 auf das Hohlrad 190 übertragen wird. Die Drehmomentkupplung 160 spricht an, wenn das Abstützdrehmoment größer wird, als das von der Begrenzungseinheit 230 aufgebrachte Haltedrehmoment, so dass das Hohlrad 190 in letzter Konsequenz durchrutscht bzw. durchdreht. In diesem Fall ist die Übertragung von Drehzahl zwischen der vorderen Planetenstufe 181 des Planetengetriebes 171 und der Antriebswelle 120 unterbrochen bzw. außer Kraft gesetzt und die Übertragung von Drehmoment begrenzt. Das jeweilige auf das Hohlrad 190 einwirkende Haltedrehmoment der Begrenzungseinheit 230 ist hierbei abhängig von der axialen Position des Federelementhalters 238 und damit von der Drehstellung des Bedienelements 165.A support torque occurs within the planetary gear 171 due to the torque and speed conversion, which is transmitted from the planet gears of the front planetary stage 182 to the ring gear 190. The torque clutch 160 responds when the support torque becomes greater than the holding torque applied by the limiting unit 230, so that the ring gear 190 slips or rotates in the final analysis. In this case, the transmission of speed between the front planetary stage 181 of the planetary gear 171 and the drive shaft 120 is interrupted or disabled and the transmission of torque is limited. The respective holding torque of the limiting unit 230 acting on the ring gear 190 is dependent on the axial position of the spring element holder 238 and thus on the rotational position of the operating element 165.

In der hier illustrierten axialen Stellung des Federelementhalters 238 ist das mindestens eine Federelement 234 weitgehend entspannt, so dass der mindestens eine Rastkörper 250 von dem Übertragungselement 240 mit einer vergleichsweise geringen axialen Federkraft gegen die Kopplungsgeometrie 252 der Stirnseite 236 des Hohlrads 190 des Planetengetriebes 171 beaufschlagt ist. Hierdurch rutscht bzw. dreht das Hohlrad 190 bereits bei verhältnismäßig kleinen auf die Antriebswelle 120 bzw. die Antriebsspindel einwirkenden Drehmomenten durch und die Handwerkzeugmaschine befindet sich in einem "Schraubmodus".In the axial position of the spring element holder 238 illustrated here, the at least one spring element 234 is largely relaxed, so that the at least one latching body 250 is acted upon by the transmission element 240 with a comparatively small axial spring force against the coupling geometry 252 of the end face 236 of the ring gear 190 of the planetary gear mechanism 171 . As a result, the ring gear 190 slips or rotates even at relatively small torques acting on the drive shaft 120 or the drive spindle, and the hand-held power tool is in a "screwing mode".

Ist das mindestens eine Federelement 234 hingegen stärker gespannt bzw. komprimiert, was durch das axiale Verschieben des Federelementhalters 238 in Richtung des Planetengetriebes 171 bzw. in Richtung des Antriebsmotors 200 durch benutzerseitiges Verdrehen des Bedienelements 165 erreichbar ist, so wird der mindestens eine Rastkörper 250 durch das Übertragungselement 240 mit einer höheren Federkraft gegen das Hohlrad 190 beaufschlagt, woraus ein höheres Haltedrehmoment resultiert und dieses erst bei höheren an der Antriebswelle 120 angreifenden Drehmomenten anfängt durchzurutschen bzw. durchzudrehen. Ist das mindestens eine Federelement 234 bzw. die Druckfeder 232 nahezu vollständig komprimiert, so wird der mindestens eine Rastkörper 250 durch das Übertragungselement 240 mit einer so hohen axialen Federkraft gegen die Kopplungsgeometrie 252 der Stirnseite 236 des Hohlrads 190 beaufschlagt, dass dieses praktisch nicht mehr durchrutschen kann und ein "Bohrmodus" der Handwerkzeugmaschine aktiviert ist, in dem an der Antriebswelle 120 ein maximales Arbeitsdrehmoment abgreifbar ist. Alternativ hierzu kann auch ein axialer Abstand zwischen dem Federelementhalter 238 und dem Übertragungselement 240 kleiner ausgebildet sein, als entsprechende Erhebungen (254 in Fig. 3) der Kopplungsgeometrie 252.If, on the other hand, the at least one spring element 234 is more tensioned or compressed, which can be achieved by axially displacing the spring element holder 238 in the direction of the planetary gear 171 or in the direction of the drive motor 200 by turning the control element 165 on the user side, the at least one latching body 250 becomes the transmission element 240 is subjected to a higher spring force against the ring gear 190, which results in a higher holding torque and this begins to slip or spin only at higher torques acting on the drive shaft 120. If the at least one spring element 234 or the compression spring 232 is almost completely compressed, the at least one latching body 250 is acted upon by the transmission element 240 with such a high axial spring force against the coupling geometry 252 of the end face 236 of the ring gear 190 that it practically no longer slips can and a "drilling mode" of the hand tool is activated, in which a maximum working torque can be tapped on the drive shaft 120. As an alternative to this, an axial distance between the spring element holder 238 and the transmission element 240 can also be made smaller than corresponding elevations (254 in Fig. 3 ) of the coupling geometry 252.

Es sei darauf hingewiesen, dass dem auf dem Gebiet von Bohrschraubern tätigen Fachmann die Funktionsweise einer Drehmomentkupplung im Übrigen aus dem Stand der Technik hinlänglich bekannt ist, sodass hier zwecks Knappheit der Beschreibung auf eine eingehendere Beschreibung der Funktionsweise der Drehmomentkupplung 160 verzichtet werden kann.It should be pointed out that the person skilled in the field of drill drivers is also well aware of the way in which a torque clutch works from the prior art, so that for the sake of conciseness of the description, a more detailed description of the way in which the torque clutch 160 works can be dispensed with here.

Fig. 3 zeigt eine Explosionsansicht eines Teils des Ausschnitts 220 von Fig. 1 bzw. Fig. 2. Dementsprechend verfügt das im Wesentlichen hohlzylindrische Hohlrad 190 der Begrenzungseinheit 230 der Drehmomentkupplung 160 über eine Innenverzahnung 185 und an der Stirnseite 236 des Hohlrads 190 ist die Kopplungsgeometrie 252 ausgeformt. Die Kopplungsgeometrie 252 weist hier lediglich exemplarisch sechs gleichartige Erhebungen auf, deren Querschnittsgeometrie exemplarisch in etwa der eines gleichschenkligen Trapezes entspricht und von denen beispielhaft zwei Erhebungen 254, 256 bezeichnet sind. Die sechs umfangsseitig gleichmäßig zueinander beabstandet ausgebildeten Erhebungen sind in axialer Richtung den kugelförmigen Rastkörpern zugewandt, von denen aus Gründen der besseren zeichnerischen Übersicht halber ebenfalls nur der Rastkörper 250 und ein zu diesem umfangsseitig benachbarter Rastkörper 251 bezeichnet sind. Fig. 3 FIG. 12 shows an exploded view of part of section 220 of FIG Fig. 1 or. Fig. 2 . Accordingly, this is essentially hollow cylindrical Ring gear 190 of the limiting unit 230 of the torque clutch 160 via an internal toothing 185 and on the end face 236 of the ring gear 190, the coupling geometry 252 is formed. The coupling geometry 252 here has only six protrusions of the same type, the cross-sectional geometry of which roughly corresponds to that of an isosceles trapezoid and of which two protrusions 254, 256 are designated by way of example. The six elevations, which are equally spaced on the circumferential side, face the spherical latching bodies in the axial direction, of which only the latching body 250 and a latching body 251 adjacent to the periphery thereof are also designated for the sake of a better graphic overview.

Das bevorzugt zumindest im Wesentlichen scheibenförmige Übertragungselement 240 verfügt über eine zentrische Ausnehmung 264, an deren Innenrand 266 sechs radial einwärts gerichtete sowie jeweils ungefähr V-förmige Vorsprünge ausgebildet sind, von denen lediglich zwei Vorsprünge 270, 272 der besseren zeichnerischen Übersicht halber bezeichnet sind. Die Anzahl der Vorsprünge entspricht bevorzugt der Anzahl der verwendeten Druckfedern. Alternativ hierzu entspricht z.B. bei Verwendung einer einzelnen, zur Antriebswelle 120 von Fig. 1 konzentrisch angeordneten Druckfeder die Anzahl der Vorsprünge der Anzahl der Rastkörper.The preferably at least substantially disk-shaped transmission element 240 has a central recess 264, on the inner edge 266 of which six radially inwardly directed and approximately V-shaped projections are formed, of which only two projections 270, 272 are designated for the sake of a better overview of the drawing. The number of projections preferably corresponds to the number of compression springs used. As an alternative to this, for example when using a single drive shaft 120 corresponds to Fig. 1 Concentrically arranged compression spring, the number of projections, the number of locking bodies.

Jeder der sechs Vorsprünge weist eine Aussparung 260 auf, die den jeweiligen Vorsprung in axialer Richtung vollständig durchsetzt, wobei die Aussparungen hier jeweils als kreisrunde Öffnungen bzw. Bohrungen ausgeführt sind. Von den hier insgesamt sechs Öffnungen sind lediglich zwei Öffnungen 262, 263 bezeichnet. Jeder Vorsprung dient dabei als ein erstes Auf- bzw. Widerlager für jeweils eine Druckfeder, von denen hier lediglich die Druckfedern 232 sowie eine weitere, umfangsseitige an diese anschließende Druckfeder 233 bezeichnet ist. Der Federelementhalter 238 stellt ein zweites Auf- bzw. Widerlager für die Druckfedern dar.Each of the six projections has a recess 260 which completely penetrates the respective projection in the axial direction, the recesses here being designed as circular openings or bores. Of the total of six openings here, only two openings 262, 263 are designated. Each projection serves as a first support or abutment for one compression spring, of which only the compression springs 232 and a further compression spring 233 adjoining the circumference are designated here. The spring element holder 238 represents a second support or abutment for the compression springs.

Der Federelementhalter 238 verfügt zu diesem Zweck über einen in etwa kreisringförmigen Grundkörper 239, an dessen nicht bezeichneten Innenrand hier beispielhaft sechs parallel zu einer Längsmittelachse 302 der Drehmomentkupplung 160 verlaufende Haltestege ausgebildet sind, von denen nur zwei Haltestege 280, 282 bezeichnet sind. Die Haltestege des Federelementhalters 238 sind umfangsseitig gleichmäßig zueinander beabstandet an dem Innenrand des Federelementhalters 238 angeordnet. Jeder Haltesteg verfügt an seinem in Richtung des Einstellrings 242 weisenden freien Ende über eine radial einwärts gerichtete, näherungsweise halbkreisförmige Lasche, von denen zwei Laschen 284, 286 bezeichnet sind und die als ein zweites Auf- bzw. Widerlager für jeweils eine der Druckfedern fungieren. Die Anzahl der Laschen entspricht bevorzugt der Anzahl der verwendeten Druckfedern.For this purpose, the spring element holder 238 has an approximately circular base body 239, on the inner edge of which is not designated here, for example, six holding webs are formed, of which only two holding webs run parallel to a longitudinal central axis 302 of the torque clutch 160 280, 282 are designated. The retaining webs of the spring element holder 238 are arranged circumferentially evenly spaced from one another on the inner edge of the spring element holder 238. At its free end pointing in the direction of the adjusting ring 242, each holding web has a radially inwardly directed, approximately semicircular tab, of which two tabs 284, 286 are designated and which act as a second support or abutment for each of the compression springs. The number of tabs preferably corresponds to the number of compression springs used.

Mit Hilfe des Einstellrings 242 wird die axiale Position des Federelementhalters 238 und damit das von der Drehmomentkupplung 160 bis zum Ansprechen maximal übertragbare Drehmoment eingestellt. Der Einstellring 242 verfügt bevorzugt über einen näherungsweise hohlzylindrischen Grundkörper 248 mit dem innenumfänglich ausgebildeten Eingreifelement 244, das hier als ein Innengewinde 249 ausgeführt ist. An seinem Außenumfang befindet sich ein radial auswärts gerichteter, quaderförmiger Mitnehmer 290 zur drehfesten Ankopplung des Bedienelements 165 bzw. der Drehmomenteinstellhülse.The adjusting ring 242 is used to set the axial position of the spring element holder 238 and thus the maximum torque that can be transmitted from the torque clutch 160 until it responds. The setting ring 242 preferably has an approximately hollow cylindrical base body 248 with the engagement element 244 formed on the inside, which is designed here as an internal thread 249. On its outer circumference is a radially outward, cuboid driver 290 for the rotationally fixed coupling of the operating element 165 or the torque adjusting sleeve.

Abweichend von den hier lediglich dargestellten sechs Erhebungen der Kopplungsgeometrie 252 des Hohlrads 190, den sechs kugelförmigen Rastkörpern, den sechs radial einwärts gerichteten Laschen des Übertragungselements 240, den sechs Druckfedern sowie den sechs Vorsprüngen bzw. Haltestegen des Federelementhalters 238 kann eine von 6 abweichende Anzahl vorgesehen sein.Deviating from the six elevations of the coupling geometry 252 of the ring gear 190, the six spherical latching bodies, the six radially inwardly directed tabs of the transmission element 240, the six compression springs and the six projections or retaining webs of the spring element holder 238, a number different from 6 can be provided be.

Fig. 4 zeigt den Ausschnitt 220 der Handwerkzeugmaschine 100 von Fig. 1 gem. Fig. 2. Im Gegensatz zu Fig. 2 weist die mindestens eine Aussparung 260 nun jedoch bevorzugt eine mehreckige Grundfläche 268 auf und der mindestens eine Rastkörper 250 ist bevorzugt zylinder- bzw. walzenförmig ausgebildet und greift zumindest abschnittsweise in die mindestens eine Aussparung 260 ein. Hierbei ist eine umfangsseitige Breite der mindestens einen Aussparung 260 bevorzugt kleiner als ein Durchmesser Dz des mindestens einen zylinder- bzw. walzenförmigen Rastkörpers 250, bevorzugt kleiner als das 0,9-fache von Dz. Die umfangsseitige Breite der mindestens einen Aussparung 260 definiert hierbei eine Ausdehnung der Aussparung 260 in eine mögliche Drehrichtung der Antriebsspindel 120 gesehen. Darüber hinaus ist die radiale Ausdehnung der mindestens einen Aussparung 260 bevorzugt größer als eine entsprechende Zylinderhöhe des mindestens einen zylinder- bzw. walzenförmigen Rastkörpers 250. Fig. 4 shows section 220 of handheld power tool 100 from FIG Fig. 1 acc. Fig. 2 . In contrast to Fig. 2 However, the at least one recess 260 now preferably has a polygonal base area 268 and the at least one latching body 250 is preferably cylindrical or roller-shaped and engages at least in sections in the at least one recess 260. Here, a circumferential width of the at least one cutout 260 is preferably smaller than a diameter Dz of the at least one cylindrical or roller-shaped locking body 250, preferably smaller than 0.9 times D z . The circumferential width of the at least one recess 260 defines an expansion of the recess 260 in a possible direction of rotation of the drive spindle 120. In addition, the radial extent of the at least one recess 260 is preferably greater than a corresponding cylinder height of the at least one cylindrical or cylindrical locking body 250.

Claims (8)

  1. Handheld power tool (100) having a gear mechanism (170) and a torque clutch (160) which has a limiting unit (230) which is assigned to the gear mechanism (170) and which is assigned a transmission element (240) which is acted on by at least one spring element (234), wherein a torque level of the torque clutch (160) can be set at least within predetermined limits via an operating element (165) actuated by a user, wherein the limiting unit (230) has at least one latching body (250, 251) which engages in the transmission element (240) at least in certain portions in the axial direction of the torque clutch (160), wherein the transmission element (240) has at least one cutout (260) for axially receiving at least one latching body (250, 251) at least in certain portions, and the at least one cutout (260) is formed in the manner of an opening (262, 263), and the at least one latching body (250, 251) is ball-shaped, wherein the at least one ball-shaped latching body (250, 251) engages in the opening (262, 263) at least in certain portions, or the at least one cutout (260) has a polygonal basic surface area (268), and the at least one latching body (250) is cylindrical in form, wherein the at least one cylindrical latching body (250) engages in the at least one cutout (260) at least in certain portions, characterized in that a diameter (DA) of the at least one cutout (260) is less than a diameter (DK) of the at least one ball-shaped latching body (250, 251), or a circumferential width of the at least one cutout (260) is less than a diameter (DZ) of the at least one cylindrical latching body (250).
  2. Handheld power tool according to one of the preceding claims, characterized in that the gear mechanism (170) has at least one annulus (190), the limiting unit (230) has at least three latching bodies (250, 251) and a coupling geometry (252) formed on the end side of the annulus (190), and the transmission element (240) has at least three cutouts (260).
  3. Handheld power tool according to Claim 2, characterized in that the transmission element (240) is disc-shaped and has at least three radially inwardly directed projections (270, 272) in each of which one of the at least three cutouts (260) is formed.
  4. Handheld power tool according to one of the preceding claims, characterized in that the at least one spring element (234) has at least one compression spring (232, 233).
  5. Handheld power tool according to one of the preceding claims, characterized in that the gear mechanism (170) is designed in the manner of a planetary gear mechanism (171) and has at least one annulus (190), wherein the at least one latching body (250, 251) is axially force-loaded against the annulus (190) by means of the transmission element (240) .
  6. Handheld power tool according to Claim 5, characterized in that the at least one latching body (250, 251) is designed to roll on the annulus (190).
  7. Handheld power tool according to one of the preceding claims, characterized in that the operating element (165) which can be actuated by the user is designed to allow a spring force exerted by the at least one spring element (234) to be set.
  8. Handheld power tool according to one of the preceding claims, characterized in that the transmission element (240) takes the form of a pressure plate.
EP17709619.5A 2016-03-09 2017-03-02 Hand-held power tool comprising a torque clutch Active EP3426442B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016203886.9A DE102016203886A1 (en) 2016-03-09 2016-03-09 Hand tool with a torque coupling
PCT/EP2017/054898 WO2017153245A1 (en) 2016-03-09 2017-03-02 Hand-held power tool comprising a torque clutch

Publications (2)

Publication Number Publication Date
EP3426442A1 EP3426442A1 (en) 2019-01-16
EP3426442B1 true EP3426442B1 (en) 2020-06-24

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EP17709619.5A Active EP3426442B1 (en) 2016-03-09 2017-03-02 Hand-held power tool comprising a torque clutch

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EP (1) EP3426442B1 (en)
CN (1) CN109219502B (en)
DE (1) DE102016203886A1 (en)
WO (1) WO2017153245A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102020206936A1 (en) * 2020-02-17 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hand machine tool with a torque adjustment device
DE102022210260A1 (en) 2022-09-28 2024-03-28 Robert Bosch Gesellschaft mit beschränkter Haftung Hand tool with a torque clutch

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5738469A (en) * 1996-02-08 1998-04-14 Regitar Power Tools Co., Ltd. Torque adjustment control mechanism of a hand drill
EP1468208B1 (en) * 2002-01-25 2011-06-22 Black & Decker Inc. Power drill / driver
DE102006057283A1 (en) * 2006-12-05 2008-06-12 Robert Bosch Gmbh hand tool
EP3346087B1 (en) * 2008-08-06 2021-05-26 Milwaukee Electric Tool Corporation Precision torque tool
DE102009046663A1 (en) * 2009-01-16 2010-07-22 Robert Bosch Gmbh Machine tool, in particular hand-held machine tool
DE102009054923B4 (en) * 2009-12-18 2018-01-18 Robert Bosch Gmbh Hand tool
DE102012221906B4 (en) * 2012-11-29 2021-12-30 Robert Bosch Gmbh Hand machine tool with a torque clutch
US9494200B2 (en) * 2013-03-14 2016-11-15 Black & Decker Inc. Clutch for power tool
CN105291032A (en) * 2014-06-03 2016-02-03 美之岚机械工业有限公司 Two-segment locking and attaching electric screw driver

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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CN109219502A (en) 2019-01-15
EP3426442A1 (en) 2019-01-16
CN109219502B (en) 2023-03-14
WO2017153245A1 (en) 2017-09-14
DE102016203886A1 (en) 2017-09-14

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