EP0329852B1 - Kraftschrauber - Google Patents

Kraftschrauber Download PDF

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Publication number
EP0329852B1
EP0329852B1 EP88121554A EP88121554A EP0329852B1 EP 0329852 B1 EP0329852 B1 EP 0329852B1 EP 88121554 A EP88121554 A EP 88121554A EP 88121554 A EP88121554 A EP 88121554A EP 0329852 B1 EP0329852 B1 EP 0329852B1
Authority
EP
European Patent Office
Prior art keywords
coupling
output shaft
power wrench
wrench according
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.)
Expired - Lifetime
Application number
EP88121554A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0329852A3 (en
EP0329852A2 (de
Inventor
Wolfgang Koppatsch
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.)
Wagner Paul-Heinz
Original Assignee
Wagner Paul-Heinz
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 Wagner Paul-Heinz filed Critical Wagner Paul-Heinz
Publication of EP0329852A2 publication Critical patent/EP0329852A2/de
Publication of EP0329852A3 publication Critical patent/EP0329852A3/de
Application granted granted Critical
Publication of EP0329852B1 publication Critical patent/EP0329852B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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

Definitions

  • the invention relates to a power wrench according to the preamble of patent claim 1.
  • Motor-driven power wrenches are known in which the speed, and thus also the torque, are switched as a function of the tightening torque can. This switchover can be carried out automatically. For example, it is known to measure the supply pressure in a power wrench driven by a hydraulic motor and to switch the power wrench to a higher torque if the supply pressure exceeds a certain limit value. In the case of an electrically driven power wrench, the tightening torque can be determined by the current consumed.
  • the preamble of claim 1 is based on a power wrench according to GB-A-794 045.
  • This power wrench has a first drive wheel which is connected via a slip clutch to an overrunning clutch which drives the output shaft.
  • a second drive wheel driven via a distributor shaft is also connected to the overrunning clutch.
  • the overrunning clutch allows the one of its two drives that has the higher speed. If the load torque exceeds a limit value, the slip clutch slips so that the force is transmitted to the output shaft via the second drive wheel. During this time, however, the slip clutch continues to slip, so that it is subject to considerable wear.
  • a slip clutch does not normally trigger exactly at a given load torque. The trigger torque depends on wear and the environmental conditions.
  • GB-A-2 025 290 describes a power wrench in which the input shaft is constantly coupled to the sun gear of a planetary gear.
  • the ring gear of the planetary gear can be coupled to the drive shaft via a snap-in coupling if the load torque exceeds a limit value.
  • the ring gear is additionally provided with a one-way clutch, which allows this ring gear to rotate in one direction only.
  • the load torque is low, the output shaft rotates via the planetary gear, the ring gear of which is stationary. If the load torque exceeds the limit value, the ring gear is coupled to the drive shaft and rotates with it, which reduces the output speed of the planetary gear. As long as the high load torque persists, the locking clutch remains disengaged.
  • the invention has for its object to provide a power wrench that performs an automatic switch from low torque to high torque in a purely mechanical manner, without a conversion to another physical parameter, and which works reliably and with little wear.
  • the force of the drive shaft is transmitted from a distributor shaft to the locking coupling in two different ways with different transmission ratios.
  • a low screwing torque load torque
  • the coupling part of the locking clutch engages with the first drive wheel, so that the output shaft is driven at a relatively high first speed, while the power transmission path from the second drive wheel to the locking clutch is interrupted.
  • the coupling part engages either with the first drive wheel or with the second drive wheel.
  • the coupling part is adjusted in that a force generated by the load torque counteracts the pretension of the coupling part.
  • the coupling part can engage either only with the first or only with the second drive wheel, but never with both drive wheels at the same time.
  • the preload of the coupling part can be applied by a spring device or also hydraulically. This preload can preferably be changed by external adjustment in order to be able to adjust the level of the load torque at which the switchover takes place.
  • the coupling part is arranged to be longitudinally displaceable on the output shaft and it is pressed by the pretensioning device in the direction in which it is non-positively connected to the first drive wheel. If the load torque exceeds the limit value, the pretensioning device yields and the action of a guide curve results in an axial displacement of the coupling part in the direction of the second drive wheel. The frictional connection between the coupling part and the first drive wheel is released, while the frictional connection of the coupling part to the second drive wheel is established.
  • One of the two locking couplings is preferably a claw coupling, while the other locking coupling is a ball coupling.
  • the ball coupling In the ball coupling, entrainment takes place between a coupling body which is firmly connected to the first drive wheel and the coupling part by spring-loaded balls which are pressed against a non-circular path.
  • Such a ball coupling forms a slip clutch in which the coupling body and the coupling part can move relative to one another.
  • a free orbit is provided adjacent to a path of the coupling body which contains the recesses of the locking coupling and which receives the balls when the other locking coupling is engaged .
  • the locking clutch provided with balls therefore has two tracks arranged side by side, one of which represents a driving track and the other an idling track.
  • the locking coupling is engaged; while the detent clutch is released when the balls are idling.
  • the power wrench according to the invention enables a smooth and shock-free changeover from low torque to high torque or vice versa.
  • the guide curve which, in conjunction with the preload, brings about the axial movement of the coupling part with respect to the output shaft as a function of the load torque, has the shape of an isosceles triangle. This results in a torque-dependent changeover of the gear ratio of the power wrench in both directions of rotation.
  • the power wrench is designed like a hand drill. It has a drive device 10 which contains a (not shown) rotary motor which can be switched on by actuating a trigger lever 11. The direction of rotation can be set on the direction selector 12.
  • the drive device 10 is accommodated in a separate housing to which the housing 13 containing the torque-dependent clutch 14 is fastened. At the opposite end of the housing 13, a housing 15 is attached, which contains a planetary gear 16.
  • the output shaft 17th of the planetary gear has a head 18 to which a key nut for turning a screw can be attached.
  • the shaft 19 of the motor projects into the interior of the housing 13 from the end wall of the housing of the drive device 10.
  • the shaft 19 is supported by a ball bearing 21.
  • the shaft 19 drives a gear 22, which is firmly seated on the distributor shaft 23.
  • the distributor shaft 23 is supported at both ends in the housing 13 and there are two further gear wheels 24, 25 of different diameters.
  • the larger gear 24 meshes with the teeth of the first drive wheel 26 and the gear 25 meshes with the teeth of the second drive wheel 27.
  • Both drive wheels 26 and 27 are arranged coaxially with the output shaft 28 of the torque-dependent clutch 14. They are driven by the distributor shaft 23 at different speeds, the speed of the drive wheel 26 being greater than that of the second drive wheel 27.
  • the first drive wheel 26 is mounted on the output shaft 28 with a ball bearing 29 and the second drive wheel 27 is with a roller bearing 30 mounted on a cylindrical projection 31 of the coupling body 32.
  • a cup-shaped coupling body 33 extends from the first drive wheel 26 in the direction of the second drive wheel 27.
  • the ball housing 34 of the coupling part 32 projects into the opening of the coupling body 33.
  • a ring of claws 35 projects from the ball housing 34 in the direction of the second drive wheel 27. These claws 35 can engage claws 36, which are provided on the end face of the second drive wheel 27, when the clutch body 32 is displaced in the direction of the second drive wheel 27.
  • the output end of the output shaft 28 is supported by a ball bearing 37 in the housing 13. On the rotating ring of the ball bearing 37, a spring 38 is supported, which presses the coupling part 32 in the direction of the first gear 26.
  • each of the openings 39 has the shape of an isosceles triangle, the tip of which is directed parallel to the axis of the output shaft 28 against the bias applied by the spring 38.
  • each guide curve 39 forms two inclined flanks 39a, 39b with opposite bevels (FIG. 3), along which the guide element 40 can slide. If the load torque occurring on the output shaft 28 exceeds the limit value, the guide element 40 disengages from the tips of the triangular guide curves 39 and slides along the flanks 39a or 39b, as a result of which the coupling part 32 disengages from and engages with the coupling body 33 Claws 35 come into engagement with the second drive wheel 27.
  • Fig. 4 shows a cross section of the first locking clutch, which is formed from the coupling body 33 and the ball housing 34.
  • the ball housing 34 contains a plurality of ball catches, each of which has a spring 43 contained in a radial blind bore 42 of the ball housing 34 and a ball 44 pressed outwards by the spring 43.
  • the balls 44 run in a driving path 45, which is provided on the inside of the coupling body 33.
  • This driving path 45 has a circumferentially varying diameter, i.e. it has recesses into which the balls 44 can penetrate.
  • an idling path 46 Adjacent to the driving path 45, an idling path 46 is provided in the clutch body 33, the peripheral surface of which has no recesses but a constant diameter (FIG. 5).
  • the coupling part 32 which is normally pressed in the direction of the drive wheel 26 by the spring 38, moves in the direction of the drive wheel 27 with compression of the spring 38, the balls 44 pass from the driving path 45 into the idle path 46.
  • the coupling part 32 is uncoupled rotationally from the coupling body 33.
  • the claws 35 and 36 engage in one another, so that the coupling part 32 is coupled to the drive wheel 27 and is rotated by the latter.
  • This first gear stage has planet gears 48 which engage with the sun gear 47 with their toothings and roll on an internal toothing 49 of the housing 15.
  • the planet gears 48 are supported on axles 50 which protrude from a bearing body 51 in which the end 52 of the output shaft 28 is also supported.
  • the bearing body 51 also forms the sun gear 53 of the second gear stage 16b, the planet gears 54 of which also engage with the internal toothing 49 of the housing 15.
  • the planet gears 54 are mounted on axles 55 which protrude from the bearing body 56.
  • the bearing body 56 is connected in one piece to the output shaft 17, which is mounted in a bearing 57 at the end of the housing 15.
  • the bearing 57 is accommodated in a head piece 58, which has an outer profile 59 for attaching an external (not shown) support element in order to divert the reaction force that arises when a screw is turned onto a stationary replacement bearing.
  • a nut is placed on the head 18 of the output shaft 17, which is connected to the screw to be rotated.
  • the drive device 10 rotates the distributor shaft 23, as a result of which the drive wheels 26 and 27 are rotated simultaneously, but at different speeds.
  • the spring 38 presses the coupling part 32 against the drive wheel 26, so that the balls 44 are in the driving path and the drive wheel 26 takes the coupling part 32 along via the coupling body 33. Since the claws 35.36 in this State are disengaged, the drive wheel 27 rotates empty on the coupling part 32.
  • the output shaft 28 is therefore driven at the high speed and correspondingly low torque.
  • the rotation of the output shaft 28 is reduced by the planetary gear 16 and transmitted to the screw via the output shaft 17.
  • the load-dependent clutch 14 is located between the drive device 10 and the planetary gear 16, where the torques to be transmitted are relatively low, so that the clutch 14 can be made small.
  • the coupling part 32 moves with the guide element 40 along the flanks 39a of the guide curve 39, so that the coupling part 32 moves against the drive wheel 27.
  • the balls 44 move from the carrier track 45 into the idle track 46 and at the same time the claws 35 and 36 come into mutual engagement.
  • the output shaft 28 is driven via the gears 25 and 27 at a lower speed and higher torque. This drive with higher torque and lower speed continues until the screw is tightened. So there is no constant switching back and forth between high and low speed.
  • the axis of the planetary gear 16 runs coaxially to that of the output shaft 28.
  • the shaft 19 of the rotary drive 10, in contrast, is laterally offset.
  • the snap coupling according to FIGS. 2 to 5 also have a blocking device 60, which makes it possible to hold the movable coupling part 32 in the load position after the limit speed has been exceeded against the bias of the spring 38.
  • a blocking device 60 which makes it possible to hold the movable coupling part 32 in the load position after the limit speed has been exceeded against the bias of the spring 38.
  • the blocking device 60 is used. This has a rotatable hand lever 61 which is fastened to a shaft 62 mounted in the housing 13.
  • a cam section 63 is provided on the shaft 62, against which a pin 64 abuts, which is arranged to be longitudinally displaceable in a bore of the output shaft 28.
  • This pin 64 abuts a cross pin 65, the ends of which protrude from the output shaft 28 and engage in a sleeve 66 surrounding the output shaft.
  • the clutch body 32 is pressed against this sleeve 66 by the spring 38.
  • the pin 64 is advanced as a result of the cam part 63, as a result of which the sleeve 66 presses the coupling part 32 into the position which corresponds to the high load torque and in which the claws 35, 36 are in mutual engagement, while the first latching clutch 33 , 34 is solved.
  • the hand lever 61 can be rotated without overcoming a greater counterforce, so that the sleeve 66 follows the coupling part 32. Since the power transmission via the shaft 62, the cam part 63 and the pin 64 is self-locking, the pressure of the spring 38 cannot move the coupling part 32 back into the overdrive position unless the hand lever 61 has been manually rotated into a position beforehand in which the sleeve 66 has been moved by the spring 38. If necessary, a locking device 67 can be provided with which the hand lever 61 is held in the effective position and in the ineffective position.
  • Fig. 6 shows another embodiment which is the same as that of the first embodiment, except that the blocking device 60 is omitted and is replaced by a locking device.
  • This latching device consists of a latching recess 39c in the guide curve 39. In the load position, the guide element 40 latches in the latching recess 39c according to FIG. 6. The latching in the latching recess 39c requires less force than the latching out of this latching recess. In this way, the switching behavior of the clutch receives a hysteresis. This means that when the load torque increases, the switchover to a lower speed of the output shaft takes place at a low torque than when the load torque decreases, the switchover to the higher output speed occurs. In this way, a constant switching of the clutch is avoided in the limit range of the critical load torque.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
EP88121554A 1988-01-23 1988-12-23 Kraftschrauber Expired - Lifetime EP0329852B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3801972 1988-01-23
DE3801972A DE3801972A1 (de) 1988-01-23 1988-01-23 Kraftschrauber

Publications (3)

Publication Number Publication Date
EP0329852A2 EP0329852A2 (de) 1989-08-30
EP0329852A3 EP0329852A3 (en) 1990-09-05
EP0329852B1 true EP0329852B1 (de) 1993-08-11

Family

ID=6345877

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88121554A Expired - Lifetime EP0329852B1 (de) 1988-01-23 1988-12-23 Kraftschrauber

Country Status (5)

Country Link
US (1) US4966057A (ja)
EP (1) EP0329852B1 (ja)
JP (1) JP2867031B2 (ja)
DE (2) DE3801972A1 (ja)
ES (1) ES2042703T3 (ja)

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3920471C1 (ja) * 1989-06-22 1990-09-27 Wagner, Paul-Heinz, 5203 Much, De
SE464747B (sv) * 1990-02-23 1991-06-10 Atlas Copco Tools Ab Tvaahastigheters kraftoeverfoering foer ett motordrivet verktyg
US5361853A (en) * 1991-11-29 1994-11-08 Ryobi Limited Power tool
US5236434A (en) * 1991-12-16 1993-08-17 Callicrate Michael P Method and apparatus for ligating a body part
US5681329A (en) 1991-12-16 1997-10-28 Callicrate; Michael P. Method and apparatus for castration using an endless elastic loop
US5372206A (en) * 1992-10-01 1994-12-13 Makita Corporation Tightening tool
DE9312303U1 (de) * 1993-08-18 1994-12-15 Robert Bosch Gmbh, 70469 Stuttgart Vorrichtung zum Anziehen von Schraubverbindungen
US5897454A (en) * 1996-01-31 1999-04-27 Black & Decker Inc. Automatic variable transmission for power tool
JP2756245B2 (ja) * 1996-05-30 1998-05-25 前田金属工業株式会社 ボルト・ナット締付機
DE69720557T2 (de) * 1996-09-05 2004-01-29 Black & Decker Inc Automatikgetriebe für Handwerkzeug
DE19845024C2 (de) * 1998-09-30 2000-08-03 Fein C & E Kraftgetriebener Schrauber
US6093128A (en) * 1999-03-12 2000-07-25 Ingersoll-Rand Company Ratchet wrench having self-shifting transmission apparatus
US6165096A (en) * 1999-03-12 2000-12-26 Ingersoll-Rand Company Self-shifting transmission apparatus
DE10161356B4 (de) * 2001-12-13 2013-03-07 Hilti Aktiengesellschaft Schraubgerät
JP2005299883A (ja) * 2004-04-15 2005-10-27 Omi Kogyo Co Ltd 歯車伝動機構及び電動工具
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver
ES2334081B2 (es) * 2006-04-28 2011-12-12 Unex Corporation Intensificador de par de torsion motorizado.
US8303449B2 (en) * 2006-08-01 2012-11-06 Techtronic Power Tools Technology Limited Automatic transmission for a power tool
SE0700264L (sv) * 2007-02-05 2008-05-13 Atlas Copco Tools Ab Mutterdragare med svivlat växelhus
JP5117258B2 (ja) * 2008-04-01 2013-01-16 株式会社マキタ 自動変速式動力工具
EP2471634B1 (en) 2009-08-28 2015-10-21 Makita Corporation Power tool
EP2471632B1 (en) * 2009-08-28 2015-12-16 Makita Corporation Power tool
US20120080285A1 (en) * 2010-10-01 2012-04-05 Ho-Tien Chen Clutch device for a screw driver
WO2012061176A2 (en) 2010-11-04 2012-05-10 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
FR2996484B1 (fr) * 2012-10-05 2014-12-19 Renault Georges Ets Dispositif de vissage comprenant au moins une roue-libre solidaire du carter
DE102017211772A1 (de) * 2016-07-11 2018-01-11 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
DE102016124694B4 (de) * 2016-12-16 2020-06-10 Peter Müller Fügeelemente-Bereitstellungsvorrichtung sowie zugehörige Robotervorrichtung

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DE3342880A1 (de) * 1983-11-26 1985-06-05 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Kupplung fuer elektrowerkzeuge
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SE450354B (sv) * 1986-06-24 1987-06-22 Atlas Copco Ab Motordrivet tvahastighetsverktyg
JPH0639899Y2 (ja) * 1986-08-08 1994-10-19 株式会社マキタ 回転電動工具におけるトルク調整装置

Also Published As

Publication number Publication date
EP0329852A3 (en) 1990-09-05
DE3801972A1 (de) 1989-08-03
ES2042703T3 (es) 1993-12-16
JP2867031B2 (ja) 1999-03-08
DE3883205D1 (de) 1993-09-16
EP0329852A2 (de) 1989-08-30
JPH01234175A (ja) 1989-09-19
US4966057A (en) 1990-10-30

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