EP3426442B1 - Machine-outil manuelle avec un limiteur de couple - Google Patents

Machine-outil manuelle avec un limiteur de couple 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
Authority
EP
European Patent Office
Prior art keywords
power tool
latching body
transmission element
handheld power
torque
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
EP17709619.5A
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German (de)
English (en)
Other versions
EP3426442A1 (fr
Inventor
Heiko Roehm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3426442A1 publication Critical patent/EP3426442A1/fr
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Publication of EP3426442B1 publication Critical patent/EP3426442B1/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

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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Claims (8)

  1. Machine-outil à main (100) comprenant une boîte de vitesses (170) et un embrayage de transmission de couple (160) qui présente une unité de limitation (230) associée à la boîte de vitesses (170), à laquelle est associé un élément de transfert (240) sollicité par au moins un élément de ressort (234), un niveau de couple de l'embrayage de transmission de couple (160) pouvant être ajusté au moins à l'intérieur de limites prédéfinies par le biais d'un élément de commande (165) pouvant être actionné par un utilisateur, l'unité de limitation (230) présentant au moins un corps d'encliquetage (250, 251) qui s'engage dans la direction axiale de l'embrayage de transmission de couple (160) au moins en partie dans l'élément de transfert (240), l'élément de transfert (240) présentant au moins un évidement (260) pour recevoir axialement au moins en partie l'au moins un corps d'encliquetage (250, 251) et l'au moins un évidement (260) étant réalisé à la manière d'une ouverture (262, 263) et l'au moins un corps d'encliquetage (250, 251) étant réalisé sous forme sphérique, l'au moins un corps d'encliquetage sphérique (250, 251) s'engageant au moins en partie dans l'ouverture (262, 263), ou l'au moins un évidement (260) présentant une surface de base polygonale (268) et l'au moins un corps d'encliquetage (250) étant réalisé sous forme cylindrique, l'au moins un corps d'encliquetage cylindrique (250) s'engageant au moins en partie dans l'au moins un évidement (260), caractérisée en ce qu'un diamètre (DA) de l'au moins un évidement (260) est inférieur à un diamètre (DK) de l'au moins un corps d'encliquetage sphérique (250, 251) ou une largeur du côté périphérique de l'au moins un évidement (260) est inférieure à un diamètre (DZ) de l'au moins un corps d'encliquetage cylindrique (250).
  2. Machine-outil à main selon l'une quelconque des revendications précédentes, caractérisée en ce que la boîte de vitesses (170) présente au moins une couronne dentée (190), l'unité de limitation (230) présente au moins trois corps d'encliquetage (250, 251) ainsi qu'une géométrie d'accouplement (252) réalisée du côté frontal au niveau de la couronne dentée (190), et l'élément de transfert (240) présente au moins trois évidements (260).
  3. Machine-outil à main selon la revendication 2, caractérisée en ce que l'élément de transfert (240) est réalisé en forme de disque et présente au moins trois saillies (270, 272) orientées radialement vers l'intérieur, dans lesquelles est à chaque fois réalisé l'un des au moins trois évidements (260).
  4. Machine-outil à main selon l'une quelconque des revendications précédentes, caractérisée en ce que l'au moins un élément de ressort (234) présente au moins un ressort de compression (232, 233).
  5. Machine-outil à main selon l'une quelconque des revendications précédentes, caractérisée en ce que la boîte de vitesses (170) est réalisée à la manière d'un engrenage planétaire (171) et présente au moins une couronne dentée (190), l'au moins un corps d'encliquetage (250, 251) étant sollicité axialement par force au moyen de l'élément de transfert (240) contre la couronne dentée (190).
  6. Machine-outil à main selon la revendication 5, caractérisée en ce que l'au moins un corps d'encliquetage (250, 251) est réalisé de manière à rouler sur la couronne dentée (190).
  7. Machine-outil à main selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément de commande (165) pouvant être actionné par l'utilisateur est réalisé de manière à permettre un ajustement d'une force de ressort exercée par l'au moins un élément de ressort (234).
  8. Machine-outil à main selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément de transfert (240) est réalisé sous forme de tôle de pression.
EP17709619.5A 2016-03-09 2017-03-02 Machine-outil manuelle avec un limiteur de couple Active EP3426442B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016203886.9A DE102016203886A1 (de) 2016-03-09 2016-03-09 Handwerkzeugmaschine mit einer Drehmomentkupplung
PCT/EP2017/054898 WO2017153245A1 (fr) 2016-03-09 2017-03-02 Machine-outil manuelle avec un limiteur de couple

Publications (2)

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

Family

ID=58264489

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17709619.5A Active EP3426442B1 (fr) 2016-03-09 2017-03-02 Machine-outil manuelle avec un limiteur de couple

Country Status (4)

Country Link
EP (1) EP3426442B1 (fr)
CN (1) CN109219502B (fr)
DE (1) DE102016203886A1 (fr)
WO (1) WO2017153245A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020206936A1 (de) * 2020-02-17 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Handwerkzeugmaschine mit einer Drehmomenteinstellvorrichtung
DE102022210260A1 (de) 2022-09-28 2024-03-28 Robert Bosch Gesellschaft mit beschränkter Haftung Handwerkzeugmaschine mit einer Drehmomentkupplung

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
BR0307083A (pt) * 2002-01-25 2004-12-28 Black & Decker Inc Furadeira/chave de fenda elétrica
DE102006057283A1 (de) * 2006-12-05 2008-06-12 Robert Bosch Gmbh Handwerkzeug
WO2010017371A1 (fr) * 2008-08-06 2010-02-11 Milwaukee Electric Tool Corporation Outil de couple précis
DE102009046663A1 (de) 2009-01-16 2010-07-22 Robert Bosch Gmbh Werkzeugmaschine, insbesondere handgehaltene Werkzeugmaschine
DE102009054923B4 (de) * 2009-12-18 2018-01-18 Robert Bosch Gmbh Handwerkzeugmaschine
DE102012221906B4 (de) * 2012-11-29 2021-12-30 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Drehmomentkupplung
US9494200B2 (en) * 2013-03-14 2016-11-15 Black & Decker Inc. Clutch for power tool
CN105291032A (zh) * 2014-06-03 2016-02-03 美之岚机械工业有限公司 二段锁附电动起子

Non-Patent Citations (1)

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

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Publication number Publication date
CN109219502A (zh) 2019-01-15
EP3426442A1 (fr) 2019-01-16
CN109219502B (zh) 2023-03-14
DE102016203886A1 (de) 2017-09-14
WO2017153245A1 (fr) 2017-09-14

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