EP0092127A2 - Outil rotatif - Google Patents

Outil rotatif Download PDF

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Publication number
EP0092127A2
EP0092127A2 EP83103469A EP83103469A EP0092127A2 EP 0092127 A2 EP0092127 A2 EP 0092127A2 EP 83103469 A EP83103469 A EP 83103469A EP 83103469 A EP83103469 A EP 83103469A EP 0092127 A2 EP0092127 A2 EP 0092127A2
Authority
EP
European Patent Office
Prior art keywords
output shaft
input shaft
gear
turning tool
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Withdrawn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
EP83103469A
Other languages
German (de)
English (en)
Other versions
EP0092127A3 (fr
Inventor
Oswald Dubiel
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 EP0092127A2 publication Critical patent/EP0092127A2/fr
Publication of EP0092127A3 publication Critical patent/EP0092127A3/fr
Withdrawn legal-status Critical Current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
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/008—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with automatic change-over from high speed-low torque mode to low speed-high torque mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • 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

Definitions

  • the invention relates to a turning tool with a drive motor driving the input shaft of a reduction gear and an output shaft which can be driven via the reduction gear.
  • Such turning tools are used, for example, as power screwdrivers to tighten or loosen screws or nuts; but they are also suitable for other purposes in which a part must be rotated with a motor drive force against a resistance, for example for turning pipes.
  • Hydraulically or pneumatically driven turning tools are known in which a key nut is attached to the output shaft.
  • Such turning tools can be switched between different speeds, so that a screw to be tightened is first driven at a higher speed as long as it does not yet have a greater resistance to rotation.
  • the drive motor or the reduction gear connected downstream of it can be switched over in such a way that the output shaft produces a lower speed with higher torque.
  • this requires a manual speed changeover.
  • the invention has for its object to provide a turning tool of the type mentioned, in which the speed is automatically switched depending on the load, such that at low torque, the rotation at high speed and at high torque or torque resistance, the rotation at lower speed.
  • the invention provides that the input shaft is coupled to the output shaft via an overload clutch and that in the drive path leading from the input shaft via the reduction gear to the output shaft between a first part driven by the input shaft and one which can be driven by the output shaft via the overload clutch second part an overrunning clutch is provided, which couples the first and the second part only when the first part rotates faster than the second part.
  • the output shaft is driven in a ratio of 1: 1 to the motor shaft. Since the motor shaft rotates relatively quickly, this means one Fast rotation of the output shaft with a relatively low torque. If the load acting on the output shaft increases, the overload clutch disengages, as a result of which the direct flow of force from the input shaft to the output shaft is interrupted. The output shaft would therefore initially stop, ie no longer rotate at all. In any case, the part of the overrunning clutch connected to the output shaft rotates slower than the part of this overrunning clutch connected to the input shaft, so that these two parts of the overrunning clutch are rotatably coupled to one another in the state mentioned.
  • the power flow is now transmitted from the input shaft via the reduction gear and the overrunning clutch to the output shaft, while the direct path of the power flow from the input shaft to the output shaft is interrupted.
  • the output shaft is driven in the speed ratio to the input shaft specified by the reduction gear.
  • the output shaft rotates at high loads with a correspondingly low speed and high torque.
  • the switchover takes place automatically at a load which is predetermined by the disengagement point of the overload clutch.
  • the invention is therefore based on the principle of creating two parallel transmission paths, one of which is a direct coupling between the input shaft and the output shaft, while the other transmission path contains the reduction gear.
  • an overload clutch in the first transmission path, For example, a slip clutch that cancels the direct clutch between the input shaft and the output shaft when a certain load torque is exceeded.
  • the overrunning clutch is in the other transmission path, which leads via the reduction gear, which is ineffective if the output shaft rotates as fast as the input shaft or rotates faster than the input shaft. If, on the other hand, the overload clutch does not take the output shaft fully along, the overrunning clutch takes the second coupling part with it, so that the drive from the input shaft takes place via the overrunning clutch and the reduction gear to the output shaft.
  • the overrunning clutch can be designed as a "freewheel", similar to a bicycle freewheel, or in the manner of a ratchet.
  • the first part of the overrunning clutch has a polygonal profile and the second part has a coaxial round profile and that rollers or balls are arranged between the two profiles.
  • One of the two profiles of the overrunning clutch is a hollow profile or inner profile, while the other profile part has an outer profile.
  • the overload clutch consists of a slip clutch.
  • the overload clutch has at least one coupling part which is non-rotatably connected to the input shaft and is pressed against the output shaft by spring force and that a cylinder chamber is provided is, which is connected to a hydraulic line in the compressed state of the spring means and in this state holds the spring means compressed by the hydraulic pressure.
  • the cylinder chamber is connected to the hydraulic line and the pressure of this hydraulic line causes the cylinder chamber to be kept open, i.e. occupies its largest volume. This compresses the spring means hydraulically to relieve the overload clutch.
  • there is no longer any friction loss at the overload clutch as soon as the cylinder chamber is pressurized.
  • the hydraulic line is preferably connected to the pressure line of the drive motor designed as a hydraulic motor, such that when the pressure drops due to a low load of the hydraulic motor, the spring presses the coupling part again into engagement with the output shaft.
  • the hydraulic pressure to relieve the overload clutch is therefore derived from the flow pressure of the hydraulic motor and the overload clutch reacts as soon as the supply pressure is reduced again when the load falls below a certain load torque.
  • the reduction gear is preferably a multi-stage planetary gear, the overrunning clutch being arranged between the planetary gear cage of one gear stage and the sun gear of the subsequent gear stage.
  • the overrunning clutch When the overload clutch is engaged, the subsequent gear stage rotates empty, with its sun gear rotating faster than the planet gear cage of the first gear stage, so that the overrunning clutch cannot establish a positive connection.
  • the planetary gear cage of the subsequent gear stage is expediently non-rotatably connected to the output shaft.
  • This has the advantage that the speeds of the two parts of the overrunning clutch are relatively low, so that proper functioning of the overrunning clutch can be ensured.
  • the overrunning clutch could also be arranged on the input side of the reduction gear, but the speeds are considerably higher here.
  • the turning tool shown serves as a hydraulically driven power wrench for turning screws. It has a switching and control part 10 which is connected to a pump 12 via a pressure connection 11 and to a return line leading to a tank 14 via a tank connection 13.
  • the switching and control part 10 supplies a hydraulic motor 15 with hydraulic fluid.
  • the shaft of the hydraulic motor 15 drives the input shaft of the gear part 16.
  • the output shaft of the gear part 16 has a square 17, to which a key nut for unplugging can be attached to a screw.
  • the housing of the gear part 16 is rotatably connected to a support foot 18 which protrudes laterally and obliquely to the front in order to fixed abutment to be set so that rotations of the housing and the motor 15 due to the reaction force generated when screwing are avoided.
  • the pressure connection 11 is connected to the tank connection 13 via a throttle valve 19.
  • the opening position of the throttle valve 19 is manually adjusted by means of a lever 20 which is operated with the index finger and which is mounted in a pistol-like handle 21.
  • the throttle valve 19 When the throttle valve 19 is fully open, the pressure connection 11 is fully connected to the tank connection 13. This is the case when the lever 20 is released and is pressed into the rest position shown in FIG. 1 by a spring (not shown). However, if the lever 20 is pressed into the handle 21, the throttle valve 19 closes in a proportional manner.
  • the pressure connection 11 and the tank connection 13 are also connected to a switching valve 22, which connects these connections to the consumer connections 23 and 24 of the hydraulic motor 15.
  • the switching valve 22 is switchable, so that a reversal of the direction of rotation of the shaft of the hydraulic motor 15 is possible.
  • the switching valve 22 is switched over a lever 25 which is pivotally attached to the handle 21. If the lever 25 is pivoted out of the position shown, the consumer connection 24 is connected to the pressure connection 11 instead of the consumer connection 23 and the consumer connection 23 is connected to the tank connection 13 instead of the consumer connection 24.
  • the (not shown) shaft of the hydraulic motor 15 is rotatably connected to the input shaft 26 of the transmission part 16.
  • the input shaft 26 is formed over a substantial part of its length as a hollow shaft and its longitudinal bore 27 is connected to the pressure connection 11.
  • a square 28 which cooperates with a suitable inner square of a disk 29 which projects radially from the input shaft 26, so that the disk 29 is held on the input shaft 26 in a rotationally fixed but longitudinally displaceable manner.
  • the disk 29 is axially supported with a cylindrical bush 30 in an axial recess of the output shaft 31.
  • the output shaft 31, at the front end of which the square 17 is located, is mounted in a hollow cylindrical extension 32 of the housing of the gear part 16 with roller bearings 33.
  • the projection 32 has an external toothing 32 ', in which an internal toothing of the support arm 18 engages in order to be able to fasten the support arm 18 (FIG.
  • the output shaft 31 has a radially projecting flange 34 which is provided with blind bores 35 at its rear end.
  • the blind bores 35 lie on a circular ring and balls 26 are supported on the openings of these blind bores are held in through bores of the disk 29, but project in the axial direction forward and backward from the disk 29, respectively.
  • the disc 29 thus serves as a cage for guiding the balls 36, which snap into the blind holes 35.
  • the balls 36 are pressed by a pressure ring 37 in the direction of the blind bores 35.
  • a pressure cylinder 39 presses against the pressure ring 37, which is arranged coaxially to the input shaft 26, via radially aligned needles 38, which in turn is pressed axially forward by a pressure ring 41 via further radial needles 40.
  • a spring 42 which coaxially surrounds the input shaft 26 and which is axially supported on the planet gear cage 43 of the second gear stage II GS presses against the front of the pressure ring 41.
  • This planet gear cage 43 is fixedly connected to the flange 34 of the output shaft 31 by screws 44.
  • the second gear stage II GS has a sun gear 45 which is rotatably mounted on the input shaft 26 and a plurality of planet gears 46 which are in engagement with the toothing of the sun gear 45.
  • the planet gears 46 are mounted in a known manner on axes 47, which are part of the planet gear cage 43.
  • the first gear stage I GS is designed in a similar manner. It has a sun gear 48 fixedly connected to the input shaft 26, around which the planet gears 49 rotate. These planet gears are on the Axles 51 of the planetary gear cage 50 are mounted.
  • the overrunning clutch 52 which is shown in cross section in FIG. 3, is located between the first gear stage I GS and the second gear stage II GS.
  • the overrunning clutch 52 has a first part 53, which is fixedly connected to the planetary gear cage 50 of the first gear stage and has an outer contour in the form of a hexagon.
  • the first part 53 is surrounded by the second part 54 at a radial distance.
  • the second part 54 which is fixedly connected to the sun gear 45 of the second gear stage, has a cylindrical inner surface.
  • rollers 55 which are aligned axially parallel to the input shaft 26.
  • These rollers 55 are held in an annular cage 56 which has a corresponding recess for each roller 55.
  • the cage 56 has a radially projecting flange 57 with an outer inclined surface.
  • Spring-loaded balls 58 which are held on the housing, press against this inclined surface.
  • the second part 54 of the overrunning clutch 52 can rotate freely relative to the first part 53, the rollers 55 each moving to a point of greatest radial freedom, that is to say in the middle of a hexagonal flank of the part 53, to adjust. If, on the other hand, the first part 53 is rotated relative to the second part 54, the rollers 55 are taken along, leaving their central position relative to the hexagonal flanges and between the first Part 53 and the second part 54 are clamped. This clamping causes the second part 54 to be carried along with the first part 53.
  • the overrunning clutch 52 thus has the effect that the rollers 55 are always brought into the clamping position (driving position) when the first part 53 is in one of the two directions of rotation rotates faster than the second part 54. However, if the two parts 53 and 54 rotate at the same speed, or if the second part 54 rotates faster than the first part 53, the rollers 55 remain in the central position shown in FIG that no power flow takes place via the overrunning clutch 52.
  • a cylinder chamber 59 is formed between the hub 58 of the disk 29, which closely surrounds the front end of the input shaft 26, and the cylinder 39, which is sealed on all sides by seals 60. If the cylinder 39 is pushed back by the balls 36 against the action of the spring 42, the cylinder chamber 59 is expanded to the rear so that radial outlets 61 of the bore 27 reach the area of the cylinder chamber 59. In this way, pressure oil can flow into the cylinder chamber 59 in order to keep the cylinder chamber 59 open, as a result of which the spring 42 is now held hydraulically in the tensioned state. As a result, the balls 36 are relieved of axial pressure.
  • the components of the gear part 16 are in the state shown in FIG. 2, in which the balls 36 are pressed against the blind bores 35 of the output shaft 31 by the force of the spring 42.
  • the input shaft 26 When the input shaft 26 is rotated, it takes the output shaft 31 with it via the balls 36.
  • the balls 36 together with the blind bores 35 and the spring 42, form the overload clutch 35, 36, 42.
  • the second part 54 of the overrunning clutch 52 which is fixedly connected to the sun gear 45, rotates.
  • the rotational speed of the second part 54 is greater than that of the first part 53, which is driven by the first gear stage I GS, so? that the parts 53 and 54 of the overrunning clutch 52 do not take each other with them.
  • the output shaft 31 initially stops because the direct coupling to the input shaft 26 is eliminated.
  • the second gear stage II GS and the second part 54 of the overrunning clutch 52 stand still. Since the first part 53 of the overrunning clutch has a greater rotational speed than the second part 54, the rollers 55 are clamped between the first part 52 and the second part 54, so that the overrunning clutch 52 connects the second gear stage II GS to the first Gear stage I GS is done.
  • the input shaft 26 drives the output shaft 31 via the two gear stages I GS and II GS, with a significantly lower speed and a correspondingly higher torque. In this way, the screw is tightened more slowly and with greater force.
  • the pressure in the cylinder chamber 59 is maintained until the throttle valve 19 (FIG. 1) is opened to an extent which causes a corresponding pressure drop in the line 27. This is the case when the lever 20 is completely or partially released. Then the throttle valve 19 is opened and the hydraulic fluid supplied by the pump 12 through the pressure connection 11 is returned to the tank 14 without pressure. The hydraulic pressure is no longer sufficient to keep the pressure chamber 59 open, so that it closes under the action of the spring 42 and the balls 36 snap back into the blind bores 35.
  • the output shaft 31 is now directly coupled to the input shaft 26 again.
  • the spring 42 ′ which presses the pressure piece 39 in the direction of the flange 34 of the output shaft 31, is located in the interior of the housing 65 in the vicinity of the rear housing end.
  • the spring 42 ' is a radial leaf-shaped disk which has a forward-facing edge 66 at its inner end which presses against a rigid pressure disk 67.
  • the thrust washer 67 is supported on the first part 53 of the overrunning clutch 52 via an axial thrust bearing 68.
  • the second part 54 of the overrunning clutch is supported on the pressure piece 39 via a further axial thrust bearing 69, that forms the cage of the second gear stage II GS.
  • the axial force of the spring 42 is transmitted via the first gear stage I GS, the overrunning clutch 52 and the second gear stage II GS as well as via the needles 38 and the pressure ring 37 to the balls 36, which with a predetermined force into the recesses 35 of the Flange 34 are pressed.
  • the disk 29, which is non-rotatably connected to the input shaft 26, is coupled to the flange 34 of the output shaft 31 via the balls 36. If the load torque exceeds the set limit value, the balls 36 leave the recesses 35, the spring 42 'being pushed back (to the right).
  • the first gear stage I GS, the overrunning clutch 52 and the second gear stage II GS are shifted slightly within the housing 65.
  • the pressure piece 39 has axially projecting pins 70, which dip into corresponding recesses 71 of the flange 34, so that the pressure piece 39 is always coupled to the flange 34 in a rotationally fixed manner.
  • FIG. 6 is a hydraulic pressure chamber to relieve the pressure on the Balls 36 exerted axial pressure is not provided.
  • the balls 36 therefore snap into each of the recesses 35 of the flange for a short time.
  • a pressure ring 73 which is arranged in the housing 65, presses against the outer edge of the spring 42 ′.
  • Axial pins 74 abut against the outside of the pressure ring 73, their outer ends abutting a threaded ring 75 which is screwed onto an external thread of the housing 65. By turning the threaded ring 75, the preload of the spring 42 ′ can be changed in order to set the overload torque at which the balls 36 disengage.
  • the spring 42 or 42 'for the overload clutch can also be fitted between the two gear stages I GS and II GS or in the lower region of the second gear stage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
EP83103469A 1982-04-21 1983-04-09 Outil rotatif Withdrawn EP0092127A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3214842A DE3214842A1 (de) 1982-04-21 1982-04-21 Drehwerkzeug
DE3214842 1982-04-21

Publications (2)

Publication Number Publication Date
EP0092127A2 true EP0092127A2 (fr) 1983-10-26
EP0092127A3 EP0092127A3 (fr) 1986-01-08

Family

ID=6161554

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83103469A Withdrawn EP0092127A3 (fr) 1982-04-21 1983-04-09 Outil rotatif

Country Status (4)

Country Link
US (1) US4513827A (fr)
EP (1) EP0092127A3 (fr)
JP (1) JPS58223570A (fr)
DE (1) DE3214842A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0195851A2 (fr) * 1985-03-29 1986-10-01 MAG Aerospace Industries, Inc. Outil d'installation pour éléments de fixation par coincement
FR2607050A1 (fr) * 1986-06-24 1988-05-27 Atlas Copco Ab Outil a moteur a deux vitesses dont le passage d'une vitesse a l'autre est effectue automatiquement par un dispositif a came, tel que perceuses ou analogues
EP0277105A1 (fr) * 1987-01-27 1988-08-03 Atlas Copco Aktiebolag Outil de commande pour fixation en deux étapes de joints à vis
EP0281775A2 (fr) * 1987-03-09 1988-09-14 Olympic Co., Ltd. Engrenage à vitesse variable pour outil électrique rotatif
EP0404035A2 (fr) * 1989-06-22 1990-12-27 Wagner, Paul-Heinz Tournevis motorisé
GB2242487A (en) * 1990-02-23 1991-10-02 Atlas Copco Tools Ab A two-speed torque responsive planetary power transmission for a power tool
US6938526B2 (en) 2003-07-30 2005-09-06 Black & Decker Inc. Impact wrench having an improved anvil to square driver transition
US7036406B2 (en) 2003-07-30 2006-05-02 Black & Decker Inc. Impact wrench having an improved anvil to square driver transition
US7249638B2 (en) 2005-01-07 2007-07-31 Black & Decker Inc. Impact wrench anvil and method of forming an impact wrench anvil
WO2023110230A1 (fr) * 2021-12-17 2023-06-22 Atlas Copco Industrial Technique Ab Outil motorisé et transmission de puissance réagissant à la charge pour outil motorisé

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JPS6011769U (ja) * 1983-06-30 1985-01-26 前田金属工業株式会社 異常回転防止具付きボルト・ナツト締付具
SE439349B (sv) * 1983-10-04 1985-06-10 Per John Karlsson Reversibel momentomvandlare
EP0226426B1 (fr) * 1985-12-06 1990-05-16 Desoutter, Limited Transmission à deux vitesses
JPH0674829B2 (ja) * 1986-10-11 1994-09-21 本田技研工業株式会社 始動及び後退用減速装置
JPS6434678A (en) * 1987-07-30 1989-02-06 Olympic Co Ltd Speed change gear for rotary power tool
DE3801972A1 (de) * 1988-01-23 1989-08-03 Wagner Paul Heinz Kraftschrauber
DE3825711A1 (de) * 1988-07-28 1990-02-01 Weber Schraubautomaten Drehwerkzeug
US4883130A (en) * 1988-08-31 1989-11-28 Dixon Automatic Tool, Inc. Dual speed transmission for automatic assembly machine
US4913242A (en) * 1989-08-07 1990-04-03 Top Driver Enterprise Co., Ltd. Electric screw driver
WO1996019322A1 (fr) 1994-06-17 1996-06-27 Dale Francis Systeme de clef a couple ameliore
US5595251A (en) * 1994-08-10 1997-01-21 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Displaceable gear torque controlled driver
US5897454A (en) * 1996-01-31 1999-04-27 Black & Decker Inc. Automatic variable transmission for power tool
DE19843452A1 (de) * 1998-09-22 2000-03-23 Bihler Otto Handels Beteiligungs Gmbh Werkzeugmaschine mit Drehmomentkupplung
US6553873B2 (en) 2000-05-03 2003-04-29 Power Tork Hydraulics, Inc. Hydraulic wrench control valve systems
US20050130782A1 (en) * 2003-12-12 2005-06-16 Guenther Boehler Gmbh. Handheld power tool
US7146880B1 (en) 2004-12-06 2006-12-12 Francis Services, Inc. Torque wrench system
US7980324B2 (en) * 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver
DE102007020542B4 (de) * 2006-04-28 2015-10-22 Unex Corp. Werkzeug mit Drehmomentverstärkung
EP2030710B1 (fr) * 2007-08-29 2014-04-23 Positec Power Tools (Suzhou) Co., Ltd. Outil motorisé et système de commande pour un outil motorisé
US7798038B2 (en) * 2007-10-29 2010-09-21 Junkers John K Reaction arm for power-driven torque intensifier
US8042434B2 (en) * 2008-01-24 2011-10-25 Junkers John K Safety torque intensifying tool
JP5562540B2 (ja) * 2008-08-21 2014-07-30 株式会社マキタ 電動工具
JP5653820B2 (ja) * 2011-03-31 2015-01-14 株式会社マキタ 動力工具
JP5836621B2 (ja) * 2011-03-31 2015-12-24 株式会社マキタ 動力工具
US20150111692A1 (en) * 2013-10-17 2015-04-23 Torq Fusion LLC Planetary gear train for use with extended length sun in high torque applications

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SE388468C (sv) * 1975-06-04 1978-10-23 Skf Nova Ab Planetvexel med alternerande friktions- och kuggkraftoverforing
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Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH256607A (de) * 1946-12-09 1948-08-31 Prachar Cyril Spindelspannfutter mit Überlastungssicherung.
US2743804A (en) * 1950-05-10 1956-05-01 Albert O Roberts Clutch
US2951389A (en) * 1954-07-28 1960-09-06 Wille Eduard Control for motor driven nut tightener
GB889991A (en) * 1957-05-11 1962-02-21 Luciano Ceruti Improvements in or relating to a gradual mechanical automatic speed variator
US3718054A (en) * 1971-10-07 1973-02-27 Gen Motors Corp Load responsive torque transmission mechanism
US3942337A (en) * 1974-09-16 1976-03-09 Industrial Analytics Inc. Torque limiting device
US4296848A (en) * 1977-07-27 1981-10-27 Aisin Seiki Kabushiki Kaisha Free wheel hub mechanism
SE421084B (sv) * 1981-01-29 1981-11-23 Ffv Industriprodukter Ab Sekerhetsslirkoppling

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0195851A2 (fr) * 1985-03-29 1986-10-01 MAG Aerospace Industries, Inc. Outil d'installation pour éléments de fixation par coincement
EP0195851A3 (en) * 1985-03-29 1988-02-24 Monogram Industries, Inc. Installing tool for wedging-type fasteners
FR2607050A1 (fr) * 1986-06-24 1988-05-27 Atlas Copco Ab Outil a moteur a deux vitesses dont le passage d'une vitesse a l'autre est effectue automatiquement par un dispositif a came, tel que perceuses ou analogues
EP0277105A1 (fr) * 1987-01-27 1988-08-03 Atlas Copco Aktiebolag Outil de commande pour fixation en deux étapes de joints à vis
US4881435A (en) * 1987-01-27 1989-11-21 Atlas Copco Aktiebolag Power tool for two step tightening of screw joints
EP0281775A2 (fr) * 1987-03-09 1988-09-14 Olympic Co., Ltd. Engrenage à vitesse variable pour outil électrique rotatif
EP0281775A3 (fr) * 1987-03-09 1990-12-05 Olympic Co., Ltd. Engrenage à vitesse variable pour outil électrique rotatif
EP0404035A3 (fr) * 1989-06-22 1991-09-04 Wagner, Paul-Heinz Tournevis motorisé
EP0404035A2 (fr) * 1989-06-22 1990-12-27 Wagner, Paul-Heinz Tournevis motorisé
GB2242487A (en) * 1990-02-23 1991-10-02 Atlas Copco Tools Ab A two-speed torque responsive planetary power transmission for a power tool
GB2242487B (en) * 1990-02-23 1994-04-06 Atlas Copco Tools Ab A two-speed power transmission for a power tool
US6938526B2 (en) 2003-07-30 2005-09-06 Black & Decker Inc. Impact wrench having an improved anvil to square driver transition
US7036406B2 (en) 2003-07-30 2006-05-02 Black & Decker Inc. Impact wrench having an improved anvil to square driver transition
CN1829588B (zh) * 2003-07-30 2012-03-28 布莱克和戴克公司 具有改进方形驱动器过渡部的砧座的冲击扳手
US7249638B2 (en) 2005-01-07 2007-07-31 Black & Decker Inc. Impact wrench anvil and method of forming an impact wrench anvil
WO2023110230A1 (fr) * 2021-12-17 2023-06-22 Atlas Copco Industrial Technique Ab Outil motorisé et transmission de puissance réagissant à la charge pour outil motorisé

Also Published As

Publication number Publication date
JPS58223570A (ja) 1983-12-26
EP0092127A3 (fr) 1986-01-08
DE3214842A1 (de) 1983-10-27
US4513827A (en) 1985-04-30

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