EP2140976A1 - Vis autotaraudeuse à frapper - Google Patents

Vis autotaraudeuse à frapper Download PDF

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Publication number
EP2140976A1
EP2140976A1 EP08011816A EP08011816A EP2140976A1 EP 2140976 A1 EP2140976 A1 EP 2140976A1 EP 08011816 A EP08011816 A EP 08011816A EP 08011816 A EP08011816 A EP 08011816A EP 2140976 A1 EP2140976 A1 EP 2140976A1
Authority
EP
European Patent Office
Prior art keywords
impact
hammer
drive shaft
actuating means
impact wrench
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.)
Granted
Application number
EP08011816A
Other languages
German (de)
English (en)
Other versions
EP2140976B1 (fr
Inventor
Benjamin Andel
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.)
Metabowerke GmbH and Co
Original Assignee
Metabowerke GmbH and Co
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 Metabowerke GmbH and Co filed Critical Metabowerke GmbH and Co
Priority to EP08011816A priority Critical patent/EP2140976B1/fr
Priority to US12/489,652 priority patent/US20100000750A1/en
Priority to CN200910151845A priority patent/CN101618536A/zh
Publication of EP2140976A1 publication Critical patent/EP2140976A1/fr
Application granted granted Critical
Publication of EP2140976B1 publication Critical patent/EP2140976B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • 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
    • 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
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B25B21/026—Impact clutches

Definitions

  • the invention relates to an impact wrench for screwing and drilling with a rotary impact mechanism wherein such impact wrench are used inter alia to produce or solve high-strength threaded connections.
  • Impact wrenches have been known in the art for many years, the function of the rotary impact mechanism being based on the idea of temporarily storing the drive energy of an engine and periodically applying it to an output shaft within a very short working phase. These periodically emitted angular momentum produce a significantly higher resulting depending on the pulse duration Drive torque as possible with a constant torque curve. From the drive side, the system receives kinetic energy in the form of torque and speed, which is cached in an assembly, for example in a spring or a rotating mass.
  • the storage process takes each time until a control mechanism ensures that the stored energy is delivered via a hammer on an anvil.
  • a control mechanism ensures that the stored energy is delivered via a hammer on an anvil.
  • both the anvil and the hammer of the impact mechanism on impact jaws wherein the hammer comprises a flywheel, which is formed by the massive part of the hammer, which is accelerated by this mass, the kinetic energy is transferred to the anvil.
  • the anvil is in a rotationally fixed connection to the output, so also for screwing.
  • the control mechanism provides for the time-limited delivery of energy to the anvil, so that the compound dissolves again when the stored energy is released.
  • phase 1 the energy is collected and stored and in phase 2 the stored energy is released again.
  • the energy stored in phase 1 is determined by the input quantities of torque, speed and stroke rate. The higher the stroke rate, the shorter Phase 1 is in terms of time and the less energy can be stored, because the engine can only apply a given torque and thus the duration of the storage process is crucial.
  • the second phase also decides the duration of the energy tax. If the stored energy is delivered to the output in a shorter time, ie the duration of the stroke is shorter, the resulting torque peak will be higher than with a longer duration of the stroke.
  • the typical torque curve of an impact wrench is created by temporarily storing energy over a longer period of time, which is delivered abruptly to the output in a very short period of time.
  • An impact wrench is for example in the DE 43 01 610 A1 described above.
  • the object of the invention is therefore to provide an actuating means for switching on and off of the impact mechanism, which has an alternative constructive solution and at the same time enables a particularly simple switching between an operating mode with and a mode with the impact mechanism switched off.
  • an impact wrench with the features of claim 1, namely a Impact wrench with a drive motor for driving a drive shaft and a coupled with a tool holder output shaft and a percussion mechanism, wherein the percussion includes an output shaft coupled to the anvil and a hammer which is guided on the drive shaft and rotates with this non-stop rotation and relative to the drive shaft in the case of impact performs at least a limited rotational movement, wherein an actuating means is provided for switching the percussion between a mode with and a mode with switched-off percussion, wherein the actuating means with activated percussion in a first position in a rotationally fixed engagement with the drive shaft or the hammer or without engagement with one of the two components, hammer or drive shaft, is and with the impact mechanism switched off in a second position in a rotationally fixed engagement with the hammer and drive shaft, wherein the actuating means for scarf th is axially movable.
  • Such an impact wrench is suitable in addition to the screws for drilling.
  • a transition to impact mode then takes place automatically when the percussion mechanism is activated, with the anvil and the hammer, with their percussion jaws, being arranged on hammer and anvil faces facing one another in percussive operation, against one another no longer permanently, as in the screw, abut, but are separated from each other during energy storage, and then in the energy discharge and thus the impact in the circumferential direction collide against each other and so to provide a momentarily greater torque.
  • the hammer can perform an axial movement relative to the drive shaft in case of impact in addition to the relative rotation to the drive shaft.
  • the axial movement can be oscillating.
  • the drive shaft connected by axial displacement of the actuating means with the hammer.
  • the actuating means is coupled in a first position only with the drive shaft or the hammer or is engaged with the two and in a second position hammer and drive shaft are coupled together so that there is no relative rotation between them and thus also in the axial direction oscillatory motion is prevented. In this way, no energy storage and no overlapping of the impact jaws.
  • the actuating means with the hammer and the drive shaft If the actuating means with the hammer and the drive shaft is engaged, it blocks the rotational relative movement between the hammer and the drive shaft, which allows the impact function in addition to the axial relative movement.
  • Such a configuration with an axially displaceable actuating means, in a first position and mode either without engagement or in engagement is only with drive shaft or hammer and is in a second mode with switched Schlagwerk in engagement with the hammer and drive shaft, manufacturing technology is particularly easy to implement, being particularly preferred that the switching operation can be done independently of the relative angle of the components hammer and drive shaft to each other.
  • This switching independently of the relative arrangement of the two components to one another can be achieved by the design of the impact mechanism, for example as V-Nutenschlagwerk that always has the same position of hammer and drive shaft to each other at a standstill, but it can also be achieved by the actuating means is designed accordingly.
  • an axially displaceable adjusting ring or an axially displaceable pin wherein the adjusting ring may in particular have one or more grooves or ribs, which are engageable with grooves or ribs in the drive shaft and / or the hammer and along the Nutlnaturesraum, which runs in the axial direction, can be moved.
  • spirally arranged grooves via which a rotationally-axially displaceable actuating means in engagement with one or both of the components can be brought.
  • the actuating means can be actuated via a slide switch but also via a rotational movement on a ring in an axial-rotational movement.
  • a rotary handle may be provided which allows a corresponding guide a translational movement or a coupled translationally rotational movement of the actuating element.
  • actuating the actuating means a protruding through a housing opening slide switch is provided, which is connected to the adjusting ring, wherein the slide switch is guided in particular in a circumferential groove around the adjusting ring and rotates in the groove around the adjusting ring, if the adjusting ring rotates with the drive shaft.
  • the impact mechanism is designed as a V-groove impact mechanism, wherein the hammer performs an axially oscillatory rotational movement with respect to the drive shaft in case of impact.
  • an axial oscillatory movement is to be understood here that the hammer in case of impact, both an axial relative movement, wherein the hammer on the drive shaft alternately axially toward the drive-side end of the drive shaft and the output side end of the drive shaft is reciprocated in a groove , wherein the groove is V-shaped and performs the tip of the V in the direction of the output side of the shaft, wherein caused by the axial movement due to the V-shape of the grooves at the same time also a relative rotational movement of the hammer to the drive shaft.
  • the hammer can be guided over a ball guide in the V-grooves, wherein preferably two V-grooves are arranged diametrically opposite to the drive shaft.
  • a V-groove striking mechanism works as follows: Before an impact event occurs, the anvil turns over its impact jaws which abut against the hammer's jaws, together with the hammer and the drive shaft without any relative movement between the individual components. When concerns a larger torque, it now comes from the fact that this torque is not due to the normal torque of the impact wrench can be applied between anvil and hammer to decouple the impact jaws. The rotation of the drive shaft, which is transferred to the hammer and the counter-support of the anvil, causes the hammer to move on the drive shaft in the V-grooves.
  • the hammer By providing the V-grooves, the hammer is moved away from the anvil at the same time as the rotation relative to the drive shaft in the axial direction, and it comes to a catch in the axial direction of the impact jaws of the hammer and the anvil.
  • the hammer By releasing the hammer from the anvil, the hammer can move freely in a rotational direction and is accelerated by the stored energy, which is stored in a spring by the axial movement of the hammer in the drive direction until it is at the end of its rotational movement and axial movement against striking the impact jaws of the anvil with its impact jaws and so performs a blow in the circumferential direction, which leads to a further tightening or loosening of the machined bfalls. After impact the tensioning of the percussion mechanism takes place by axial and radial movement of the hammer again.
  • a groove or a rib are provided, wherein generally also a plurality of circumferentially distributed grooves or ribs may be provided, which cooperate with a corresponding rib or groove of the actuating means.
  • actuating means if it is a sleeve or a ring, a toothing be mounted, which cooperates with a corresponding toothing on the outer circumference of the drive shaft and hammer.
  • the hammer consists of a separate flywheel and a separate control part, wherein the control part interacts with the anvil in case of impact and the flywheel and the control part rotatably, but are axially connected to each other movable.
  • the control part In Providence of a V-groove impacting particular only the control part is axially movable relative to the drive shaft.
  • a torque adjustment is realized, which takes place in particular via variations of the biasing force of the spring of the V-groove impaction.
  • the impact wrench is a cordless wrench, with cordless tools generally having the advantage of being easier to use at any location and even in difficult applications.
  • the impact function is particularly advantageous in cordless tools, since in devices with direct electrical connection, the torque design can be such that higher Torques can be achieved so that, if necessary, can be worked without an additional impact function.
  • FIG. 1 shows a striking mechanism of an impact wrench comprising an output shaft 10 which is connectable at its output end 12 with a tool, in particular a screwdriver and at its drive end has an anvil 14 having two impact jaws 16 which are formed diametrically opposite each other in the radial direction wherein the striking surfaces are substantially radially extending surfaces.
  • the rectangular impact jaws 16 of the anvil 14 cooperate with cake-piece-like impact jaws 18 of a hammer 20, wherein the impact jaws 18 of the hammer 20 have striking surfaces which face the striking surfaces of the striking jaws 16 of the anvil 14 against each other issue.
  • the hammer 20 forms on the one hand a flywheel and serves as another control means for the control of a beating process.
  • the percussion includes a collar 22 as an actuating means 23 having a circumferential groove 24 in which a slide switch 26 is guided, which passes through an opening in a housing of the impact wrench, wherein by movement of the slide switch 26 in the axial direction 28 there is a shift the adjusting ring 22 comes in the axial direction, wherein the adjusting ring 22 is coaxial with the output shaft 10 and the drive shaft 30 and the drive shaft 30 and the hammer 20 at least partially and at least partially surrounds.
  • a groove 32 is formed in the hammer 20, in which a rib 34 of the adjusting ring 22 engages, and so ensures a positive connection between the adjusting ring 22 and hammer 20.
  • FIG. 2 now shows an exploded view of the striking mechanism, in which case the adjusting ring 22 has been removed.
  • the adjusting ring 22 has two diametrically opposed ribs 34, each engaging in a groove 32 of the hammer 20, wherein also in the drive shaft 30 in an integrally connected to the drive shaft 30 flange 36 grooves 38 are provided, in which also the ribs 34 can intervene.
  • the drive shaft 30 is in this case coupled with its drive-side end 40 with a drive motor, in particular a planetary gear (not shown) between the drive motor and the drive shaft 30 can be interposed to translate the speed of the drive motor and to vary.
  • a spring 42 is provided, which cooperates with its output end with the hammer 20 and with its drive-side end 44 bears against the flange 36 of the drive shaft 30.
  • FIG. 3 now shows the drive shaft 30 with the flange 36 and the grooves 38 and another flange 46 for connection to a transmission or the drive motor, wherein in the drive shaft 30, two V-shaped grooves 48 are provided at the output end 50 of the drive shaft 30 and the V -shaped groove for controlling the axial oscillatory rotational movement of the hammer 20 relative to the drive shaft 30 is used.
  • the two V-grooves 48 are arranged opposite one another. In the grooves 48 of the hammer 20 via ball guides (not shown) out.
  • the hammer 20 alone is here in FIG. 4 shown.
  • FIG. 5 now shows the adjusting ring 22 with the ribs 34 for axial guidance and positive connection, in particular with the drive shaft 30 and the hammer 20 or both the drive shaft 30 and the hammer 20th
  • FIG. 6 represents a section through the percussion, in which case the adjusting ring 22 engages with its ribs 34 both in the groove 32 of the hammer 20 and in the groove of the flange 36 of the drive shaft 30 and so the drive shaft 30 rotatably and positively connected to the hammer 20 ,
  • the relative rotational movement of the hammer 20 to the drive shaft 30 to enable the impact process is prevented and the hammer 20 always rotates together with the drive shaft and thus remains constantly with its impact jaws 18 with the impact jaws 16 of the anvil 10 in Contact. In this way, a pure screwing or drilling function can be made possible.
  • FIG. 6 also shows the ball guide 50 in the V-grooves 48 of the drive shaft 30 and the spring 42, which serves to store the energy that discharges later in the blow.
  • a bearing 52 is arranged in the interior of the hammer 20, so that only an axial load on the spring 42 takes place, but no rotational load is applied to the spring 42.
  • FIG. 7 shows an operating mode in which the impact wrench is in an operating state with activated Schlagtechnik, in which case the adjusting ring 22 engages with its rib 34 only in the groove 32 of the hammer 20, but not in the groove 38 of the flange 36 of the drive shaft 30.
  • the hammer 20 can move in the direction of the drive shaft 30 both in the predetermined by the V-grooves dimensions rotationally and axially in the direction 44, so that it comes to a separation of the striking jaws 16 and 18 of the anvil 10 and hammer 20 and thus to a latching of the impact jaws 16 and 18 and to a subsequent relaxation of the spring 42 and to an acceleration of the hammer 20 in the axial direction, which is here designated by the arrow 56.
  • FIG. 8 shows a further embodiment, in which case the adjusting ring 22 is only in contact with the groove 38 of the flange 36 of the drive shaft 30 and thus also a relative movement in rotational terms between the hammer 20 and drive shaft 30 and an axial movement coupled thereto is made possible.
  • the adjusting ring 22 is neither in engagement with the drive shaft 30 still engaged with the anvil 14 and in this way a striking position is made possible.
  • connection and disconnection of an impact mechanism of a striking screwdriver can be achieved particularly easily in terms of production technology.
  • the force on the adjusting ring 22 are distributed over a relatively large area and over the circumference, so that the life of the device can be increased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP08011816A 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper Active EP2140976B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP08011816A EP2140976B1 (fr) 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper
US12/489,652 US20100000750A1 (en) 2008-07-01 2009-06-23 Impact Wrench
CN200910151845A CN101618536A (zh) 2008-07-01 2009-07-01 冲击扳手

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08011816A EP2140976B1 (fr) 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper

Publications (2)

Publication Number Publication Date
EP2140976A1 true EP2140976A1 (fr) 2010-01-06
EP2140976B1 EP2140976B1 (fr) 2011-11-16

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Family Applications (1)

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EP08011816A Active EP2140976B1 (fr) 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper

Country Status (3)

Country Link
US (1) US20100000750A1 (fr)
EP (1) EP2140976B1 (fr)
CN (1) CN101618536A (fr)

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WO2012049078A1 (fr) 2010-10-15 2012-04-19 Wera - Werk Hermann Werner Gmbh & Co. Kg Dispositif de transmission de couple de rotation à utiliser avec une clé à chocs
EP2476519A1 (fr) * 2009-09-10 2012-07-18 Positec Power Tools (Suzhou) Co., Ltd Outil motorisé
DE102011000710A1 (de) 2011-02-14 2012-08-16 Wera-Werk Hermann Werner Gmbh & Co. Kg Drehmomentübertragungseinrichtung in Form eines Bitfutters
EP2777882A3 (fr) * 2013-03-12 2017-10-25 Ingersoll-Rand Company Outil d'impact d'angle
EP2777881A3 (fr) * 2013-03-12 2017-11-01 Ingersoll-Rand Company Outil d'impact d'angle
WO2023117498A1 (fr) * 2021-12-22 2023-06-29 Robert Bosch Gmbh Machine-outil portative
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JP7258886B2 (ja) * 2017-12-11 2023-04-17 アトラス・コプコ・インダストリアル・テクニーク・アクチボラグ 電気パルス工具
CN109909938B (zh) * 2019-03-25 2024-06-21 北京弘益鼎视科技发展有限公司 冲击扳手
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CN211805940U (zh) * 2019-09-20 2020-10-30 米沃奇电动工具公司 冲击工具和锤头
US11351663B2 (en) * 2019-12-24 2022-06-07 Ingersoll-Rand Industrial U.S., Inc. Latching hammer impact wrench
EP4214388A1 (fr) 2020-09-17 2023-07-26 Assa Abloy Limited Capteur magnétique pour position de verrou
KR20230093244A (ko) 2020-09-25 2023-06-27 아싸 아블로이 오스트레일리아 피티와이 리미티드 자력계를 갖는 도어 로크
JP2023025360A (ja) * 2021-08-10 2023-02-22 パナソニックＩｐマネジメント株式会社 インパクト回転工具
JP2023179279A (ja) 2022-06-07 2023-12-19 株式会社マキタ インパクト工具
JP2023181600A (ja) * 2022-06-13 2023-12-25 株式会社マキタ インパクト工具

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Publication number Priority date Publication date Assignee Title
EP2476519A1 (fr) * 2009-09-10 2012-07-18 Positec Power Tools (Suzhou) Co., Ltd Outil motorisé
EP2476519A4 (fr) * 2009-09-10 2013-10-23 Positec Power Tools Suzhou Co Outil motorisé
WO2011151145A1 (fr) * 2010-06-01 2011-12-08 Robert Bosch Gmbh Machine-outil portative équipée d'un organe de percussion mécanique
WO2012049078A1 (fr) 2010-10-15 2012-04-19 Wera - Werk Hermann Werner Gmbh & Co. Kg Dispositif de transmission de couple de rotation à utiliser avec une clé à chocs
DE102010038210A1 (de) 2010-10-15 2012-04-19 Wera-Werk Hermann Werner Gmbh & Co. Kg Drehmomentübertragungsvorrichtung zur Verwendung mit einem Drehschlagschrauber
DE102011000710A1 (de) 2011-02-14 2012-08-16 Wera-Werk Hermann Werner Gmbh & Co. Kg Drehmomentübertragungseinrichtung in Form eines Bitfutters
WO2012110453A1 (fr) 2011-02-14 2012-08-23 Wera - Werk Hermann Werner Gmbh & Co. Kg Dispositif de transfert de couple sous forme de mandrin pour mèches
EP2777882A3 (fr) * 2013-03-12 2017-10-25 Ingersoll-Rand Company Outil d'impact d'angle
EP2777881A3 (fr) * 2013-03-12 2017-11-01 Ingersoll-Rand Company Outil d'impact d'angle
EP3505302A1 (fr) * 2013-03-12 2019-07-03 Ingersoll-Rand Company Outil d'impact d'angle
WO2023117498A1 (fr) * 2021-12-22 2023-06-29 Robert Bosch Gmbh Machine-outil portative
WO2023117486A1 (fr) * 2021-12-22 2023-06-29 Robert Bosch Gmbh Machine-outil portative

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US20100000750A1 (en) 2010-01-07
EP2140976B1 (fr) 2011-11-16
CN101618536A (zh) 2010-01-06

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