EP2101953A1 - Outil à main - Google Patents

Outil à main

Info

Publication number
EP2101953A1
EP2101953A1 EP07821412A EP07821412A EP2101953A1 EP 2101953 A1 EP2101953 A1 EP 2101953A1 EP 07821412 A EP07821412 A EP 07821412A EP 07821412 A EP07821412 A EP 07821412A EP 2101953 A1 EP2101953 A1 EP 2101953A1
Authority
EP
European Patent Office
Prior art keywords
overload
countershaft
hand tool
clutch
overload clutch
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.)
Withdrawn
Application number
EP07821412A
Other languages
German (de)
English (en)
Inventor
Robert Simm
Aldo Di Nicolantonio
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
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2101953A1 publication Critical patent/EP2101953A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B45/00—Hand-held or like portable drilling machines, e.g. drill guns; Equipment therefor
    • B23B45/008—Gear boxes, clutches, bearings, feeding mechanisms or like equipment
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2260/00—Details of constructional elements
    • B23B2260/044—Clutches
    • B23B2260/0445—Overload clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2270/00—Details of turning, boring or drilling machines, processes or tools not otherwise provided for
    • B23B2270/16—Constructions comprising three or more similar components

Definitions

  • the invention relates to a hand tool, in particular a
  • Electric hand tool in particular a drill or a cordless screwdriver, according to the preamble of claim 1.
  • Hand tools with a, in particular designed as an electric motor drive motor are well known.
  • an overload clutch as a torque limiting device in the power transmission train between the drive motor and tool shaft in order to limit the maximum transferable to the tool shaft torque.
  • a maximum torque is exceeded, the frictional connection between the motor and the tool shaft rotationally driven tool as soon as possible interrupted to protect the operator and the machined workpiece or product.
  • hand tools with an adjustable overload clutch are known in order to adjust the maximum torque to be transmitted to the task to be done.
  • the spring force of a closing spring acting on a coupling part of the overload clutch in particular a positive locking detent clutch, is varied. It has been observed that in known hand tools with adjustable overload clutch the adjuster does not always work perfectly.
  • the invention has for its object to provide an alternative design of a hand tool in which can be reliably selected between at least two different, maximum transferable torques.
  • the invention is based on the idea of providing, in addition to the first overload clutch, a second overload clutch which, alternatively and / or jointly, can be operated to transmit torque in the drive train of the hand tool.
  • the two overload clutches are preferably non-adjustable clutches, so that an adjusting device for varying the maximum torque of each individual, separate clutch can advantageously be dispensed with.
  • the provision of two separate overload clutches can be easily achieved by switching between the overload clutches or by closing switching the second overload clutch vary the maximum torque to be transmitted.
  • the two overload clutches are dimensioned differently, so that in an alternative operation, two different sized torques are transferable.
  • a common switch for switching the transmission gear and for closing and / or switching off the first and / or the second overload clutch is in an embodiment of the invention in a hand tool with a shiftable transmission for switching between at least two operating speeds intended.
  • the common switch is coupled to at least two transmission links, wherein a first transmission linkage for switching the transmission gear and a second transmission linkage for switching the overload clutches is used.
  • the at least two overload clutches are different types of coupling.
  • one of the overload clutches is designed as a frictionally engaging clutch and the other overload clutch as a positive locking detent clutch (detent clutch).
  • detent clutch positive locking detent clutch
  • the overload clutches can be arranged or switched as an alternative or together for torque transmission from the drive motor to the countershaft. From the countershaft turn the torque is then transmitted, in particular with the interposition of a transmission gear, to the tool driving tool shaft or initially to one or more intermediate shafts.
  • the weaker coupling (lower maximum torque) is permanently arranged so as to transmit torque, i. can not be switched on or off.
  • the weaker coupling is designed as a friction clutch.
  • a stronger clutch (greater maximum torque) can be connected to the weaker clutch.
  • the stronger overload clutch is preferably designed as a form-locking latching coupling.
  • an axially arranged within the countershaft shift rod is provided in an embodiment of the invention.
  • a shift rod which can be displaced on the countershaft and which is coupled to the countershaft so as to transmit torque, in particular via a meshing engagement.
  • the switching rod can preferably be designed as a switching sleeve, the surrounds the countershaft in sections completely.
  • the shift rod can be adjusted between at least two shift positions in which either the first or the second overload clutch is connected to the countershaft so as to transmit torque. It is also conceivable that in a switching position both overload clutches are coupled together to transmit torque with the countershaft.
  • the countershaft is mounted axially immovable in a hand tool housing and that the entire clutch assembly, consisting of the at least two overload clutches is relatively axially adjustable to the countershaft, wherein the coupling of the coupling components preferably takes place on the outer periphery.
  • the stronger overload clutch is permanently arranged to transmit torque, and that a weaker overload clutch can be engaged for this, wherein in the designed state only the lower maximum torque of the weaker overload clutch is transferable.
  • the connection and disconnection of the weaker overload Coupling can be done for example by an axially displaceably arranged on the countershaft shift rod.
  • Fig. 3 a possible arrangement of two separate overload clutches, wherein for connection and disconnection of the stronger overload clutch slidably disposed within a countershaft
  • FIG. 7 shows an alternative arrangement of two overload clutches which can be operated as an alternative, wherein a wedge gear is provided for switching the overload clutches, and
  • Fig. 8 an alternative arrangement of two overload clutches, wherein the weaker overload clutch is switched on and off.
  • an electric hand tool 1 is shown with a housing 2.
  • a power switch 3 is arranged, with which a designed as an electric motor drive motor 4 on and off.
  • the clutch housing 8 belongs to two overload clutches to be explained later.
  • the clutch housing 8 is arranged coaxially with a countershaft 9, which is rotatably mounted within the housing 2. On the countershaft 9 sit axially adjacent two output pinion 10, 11 with different diameters. Each of the output pinions 10, 11 meshes with a drive pinion 12, 13, wherein the drive pinions 12, 13 can be coupled in a manner known per se as an alternative to transmitting torque with a tool shaft 14 passing through them, such that a torque from the drive motor 4 via the motor shaft 5 , the output pinion 6, the drive pinion 7 and the clutch housing 8 with the two overload clutches on the countershaft 9 is transferable, from where the torque on the output pinion 10, 11 and the drive pinion 12 or the drive pinion 13 to the tool shaft 14 is transferable.
  • the tool shaft 14 in turn rotatably drives a tool 15, in this case a screwdriver bit.
  • a first switch 16 and a second switch 17 are shown.
  • the two switches 16, 17 are usually arranged on the housing 2 according to FIG.
  • the switch 16 the two drive pinions 12, 13 can alternatively be connected to the tool shaft 14 in a form-fitting manner in order to transmit torque.
  • Switch 17 is used for switching between two maximum torque to be transmitted, ie for switching the two overload clutches.
  • Fig. 2b shows a preferred embodiment.
  • a common rotary switch 18 is provided for switching the transmission (drive pinion 12 / drive pinion 13) and for switching between two maximum transmittable torques.
  • the common rotary switch 18 allows the changeover between two maximum transmissible torques in both gear shift stages.
  • the common switch 18 is coupled to two transmission linkages, not shown, one of which acts as an adjusting to the transmission and a further adjusting the yet to be explained overload clutches.
  • Fig. 3 an arrangement of two separate overload clutches 19, 20 is shown, wherein the overload clutch 19 is formed as a friction clutch and the overload clutch 20 as a positive locking coupling, in this embodiment, the second overload clutch 20 is used to transmit a larger maximum torque.
  • the clutch housing 8 is driven in rotation by a drive motor 4.
  • the sleeve-shaped coupling housing 8 has a radially inwardly projecting ring 21, against which a coupling component 22 penetrated by the countershaft 9 is pressed on the end side in the axial direction.
  • a plate spring element 23 is provided for axial application of force to the coupling component 22, a plate spring element 23 is provided.
  • the coupling member 22 is positively connected via an internal toothing 24 with the countershaft 9, so that the first overload clutch 19 is arranged permanently transmitting torque. If a maximum torque is exceeded, then the static friction between coupling component 22 and ring 21 is no longer sufficient to transmit the torque to the countershaft so that the clutch housing 8 with ring 21 can rotate in the circumferential direction. moved relative to the coupling member 22, the ring 21 so guided past the coupling member 22. If a larger maximum torque to be transmitted, the second overload clutch 20 is connected.
  • a switching rod 25 is provided, which is arranged displaceably in the axial direction within the countershaft 9.
  • switching balls 26 are pressed by means of a conical shoulder 27 outwardly in circumferentially spaced pockets 28 of a second coupling member 29 of the second overload clutch 20, whereby this form-fitting is coupled with the countershaft 9.
  • the second coupling component 29 in turn is axially pressed by a disc spring element 30 against the ring 21 of the clutch housing 8, whereby circumferentially distributed coupling balls 31 are axially pressed into corresponding receiving pockets 32 of the ring 21, whereby a torque from the clutch housing 8, or the ring 21 is transmitted to the second coupling member 29 and from there via the switching balls 26 on the countershaft 9.
  • the two coupling components 22, 29 are provided on their inner circumference, each with a toothing 34, 35.
  • pinion 36 is a shift rod 25 torque transmitting coupled to the countershaft 9.
  • an external toothing 37 formed as a sleeve switching rod 25 is connected to the toothing 34 of the first overload clutch 19 or with the toothing 35 of the second overload clutch 20 (shown) torque transmitting connectable.
  • the countershaft 9 is adjustable relative to the two overload clutches 19, 20 in the axial direction, wherein the pinion 36 arranged rotatably on the countershaft 9 can either be engaged with the internal gearing 34 of the first overload clutch 19 (in FIG 5) or with the internal teeth 35 of the second coupling component 29 of the second overload coupling 20.
  • FIG. 6 another embodiment is shown.
  • the countershaft 9 is arranged immovably.
  • a the countershaft 9 encompassing carriage 38 is axially displaceable relative to the countershaft 9 arranged.
  • the carriage 38 is coupled with the countershaft so as to transmit torque via a web 39 (see right half of the drawing).
  • a component 40 is provided, which serves for the rear grip of a transmission linkage, not shown.
  • the load coupling 20 has an annular coupling component 29 which is spring-loaded axially by a spring element 41 in the direction of an annular component 42, which in turn is connected in a rotationally fixed manner to the carriage 38.
  • the first overload clutch 19 has a coupling component 22, which is pressed by a plate spring element 23 via a further coupling component 43 in the axial direction against the annular member 42, which is non-rotatably coupled to the carriage 38 and thus torque transmitting with the countershaft 9.
  • the two coupling components 22, 29 are each provided with an outer toothing 44, 45, which are alternatively engageable with an internal toothing 46 of the sleeve-shaped coupling housing 8 by axially displacing the carriage 38, so that either the first overload clutch 19 or the second overload clutch 20 torque transmitting can be used.
  • the two overload clutches 19, 20 are alternatively operated via a double wedge switching rod 25 to transmit torque
  • the switching rod 25 with two separate switching ball assemblies 26, 47 cooperates, via a positive connection between countershaft 9 and the two overload clutches 19, 20, can be produced.
  • the shift rod 25 is against the spring force of a coil spring 33 adjustable. It is also conceivable that the switching rod 25 can be directly coupled in both directions of operation without a coil spring. It is also conceivable that the switching rod 25 can be directly coupled in both directions of operation without a coil spring.
  • FIG. 8 shows an alternative exemplary embodiment, in which the second, stronger overload clutch 20 configured as a lock-up clutch is permanently arranged to transmit torque.
  • an annular component 48 is permanently connected via a pinion 49 to transmit torque to the output pinion 6 of the motor shaft 5.
  • the component 48 is seated against rotation on the outside of the clutch housing 8.
  • a set of circumferentially spaced coupling ball 31 is arranged.
  • the component 29 is spring-loaded by a disk spring element 30 in the axial direction, so that the coupling balls 31 engage axially in receiving pockets 32 of the component 48 and thus a torque in the circumferential direction can be transmitted via the positive connection produced with it.
  • the component 29 is moved in the axial direction against the spring force of the plate spring member 30, so that the second overload clutch 20 disengages, ie engages.
  • the first overload clutch 19 can be connected.
  • the second overload clutch 20 serves for this purpose is an axially displaceable on the countershaft 9 shift rod 25 with an outer toothing 37 which is engageable with an internal toothing 34 of the first coupling member 22 of the first overload clutch 19 in engagement.
  • the switching rod 25 is coupled in the circumferential direction torque transmitting with the countershaft 9.
  • An annular, axially displaceable Coupling member 53 is spring-loaded by a plate spring member 23 in the direction of the first coupling member 22, whereby this between two to both sides of the coupling member 22 arranged friction jaws 50, 51 is received by clamping.
  • the friction pad 51 is supported on a radial wall 52 of the clutch housing 8. If a maximum torque is exceeded, the friction jaws 50, 51 slide past the first coupling component 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Mechanical Operated Clutches (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

L'invention concerne un outil à main (1), en particulier un outil électrique à main, avec un moteur d'entraînement (4), avec un arbre d'outil (14) et avec un premier accouplement de surcharge (19) pour limiter le couple maximal agissant sur l'arbre d'outil (14). Selon l'invention, il est prévu au moins un deuxième accouplement de surcharge (20).
EP07821412A 2006-12-05 2007-10-17 Outil à main Withdrawn EP2101953A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006057283A DE102006057283A1 (de) 2006-12-05 2006-12-05 Handwerkzeug
PCT/EP2007/061047 WO2008068103A1 (fr) 2006-12-05 2007-10-17 Outil à main

Publications (1)

Publication Number Publication Date
EP2101953A1 true EP2101953A1 (fr) 2009-09-23

Family

ID=38772298

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07821412A Withdrawn EP2101953A1 (fr) 2006-12-05 2007-10-17 Outil à main

Country Status (6)

Country Link
US (1) US8083006B2 (fr)
EP (1) EP2101953A1 (fr)
CN (1) CN101547771B (fr)
DE (1) DE102006057283A1 (fr)
RU (1) RU2458780C2 (fr)
WO (1) WO2008068103A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008033270A1 (de) * 2008-07-15 2010-01-21 Schaeffler Kg Elektromechanischer Aktuator, insbesondere für einen Wankstabilisator eines Kraftfahrzeugs
DE102009027951A1 (de) 2009-07-23 2011-01-27 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere akkubetriebene Elektrohandwerkzeugmaschine
DE102010042981A1 (de) * 2010-10-27 2012-05-03 Robert Bosch Gmbh Werkzeugmaschinenvorrichtung
DE102010063729A1 (de) 2010-12-21 2012-09-27 Robert Bosch Gmbh Getriebeanordnung für ein Elektrowerkzeug und Elektrowerkzeug
DE102011014357B3 (de) * 2011-03-17 2012-07-26 Lösomat Schraubtechnik Neef Gmbh Kraftschrauber-Überlastsicherung
CN102319910A (zh) * 2011-08-05 2012-01-18 沈阳机床（集团）设计研究院有限公司 伺服刀架用同步型过载保护结构
TWI408030B (zh) * 2012-01-17 2013-09-11 Vajra Power Ind Inc 扭力限制接頭
US9630307B2 (en) 2012-08-22 2017-04-25 Milwaukee Electric Tool Corporation Rotary hammer
DE102013212548A1 (de) * 2013-06-28 2014-12-31 Robert Bosch Gmbh Handwerkzeugmaschinengetriebevorrichtung
DE102015111878A1 (de) 2015-07-22 2017-01-26 Aesculap Ag Platzsparende Ratscheinheit mit Freilauf
DE102015111877A1 (de) 2015-07-22 2017-01-26 Aesculap Ag Werkzeugaufnahmeaufsatz für chirurgische Bohrmaschine mit zusätzlicher manueller Antriebseinheit und chirurgische Bohrmaschine
DE102016203886A1 (de) * 2016-03-09 2017-09-14 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Drehmomentkupplung
CN109565218B (zh) * 2016-08-02 2020-09-15 三菱电机株式会社 扭矩限制机构、驱动装置及机器人装置

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Also Published As

Publication number Publication date
US20100163264A1 (en) 2010-07-01
CN101547771A (zh) 2009-09-30
US8083006B2 (en) 2011-12-27
RU2009125609A (ru) 2011-01-20
RU2458780C2 (ru) 2012-08-20
WO2008068103A1 (fr) 2008-06-12
DE102006057283A1 (de) 2008-06-12
CN101547771B (zh) 2012-09-05

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