EP2140978B1 - Vis autotaraudeuse à frapper - Google Patents

Vis autotaraudeuse à frapper Download PDF

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Publication number
EP2140978B1
EP2140978B1 EP20080011818 EP08011818A EP2140978B1 EP 2140978 B1 EP2140978 B1 EP 2140978B1 EP 20080011818 EP20080011818 EP 20080011818 EP 08011818 A EP08011818 A EP 08011818A EP 2140978 B1 EP2140978 B1 EP 2140978B1
Authority
EP
European Patent Office
Prior art keywords
impact
hammer
impact screwdriver
stepped
spring
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.)
Not-in-force
Application number
EP20080011818
Other languages
German (de)
English (en)
Other versions
EP2140978A1 (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 EP20080011818 priority Critical patent/EP2140978B1/fr
Publication of EP2140978A1 publication Critical patent/EP2140978A1/fr
Application granted granted Critical
Publication of EP2140978B1 publication Critical patent/EP2140978B1/fr
Not-in-force 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
    • B25B21/026—Impact clutches
    • 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

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 As a function of the pulse duration, periodically emitted rotational pulses produce a significantly higher resultant drive torque than would be possible given 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 striking 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 temporary delivery of energy to the anvil.
  • 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 released to the downforce in a shorter time, the stroke duration is shorter, the resulting torque peak is higher than a longer stroke duration.
  • 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.
  • An impact wrench according to the preamble of claim 1 is in the EP 1 714 745 A2 contain.
  • a speed reduction mechanism for transmitting a rotational force in an impact wrench for example, from DE 102 09 101 A1 previously known, wherein the mechanism is designed here as a planetary gear.
  • the invention is achieved by an impact wrench with the features of claim 1.
  • the adjustment device according to the invention for adjusting the spring preload a purely mechanical solution for the torque adjustment is achieved without the speed of the drive shaft, which interacts with the hammer, must be varied. In this way, a torque adjustment can be achieved without the impact rate is adversely affected by the reduction of the speed.
  • the spring is in particular a compression spring and is arranged for example between the hammer and the drive shaft.
  • the compression spring is mounted so that it rotates in particular together with the hammer.
  • Stepping disks may in particular be provided as adjusting means, whereby a stepped disk is understood to mean disks in which a step or a stair segment comprising several steps rises on at least one end face over the base surface of the end face. It should be understood under stepped discs and such a disc having only a single run-on slope, which rises above the base of the face.
  • the steps may have step surfaces which run parallel to the base surface of the end face or extend at an angle, ie form a bevel.
  • the steps, stair segments or the run-up slope may extend over the entire circumference or even over a partial circumference of the stepped disk.
  • a plurality of staircase segments comprising one or more steps can be provided, which can be spaced apart in the circumferential direction or can be provided immediately adjacent to one another. If at least two staircase segments with one or more steps are provided on one end face, there is the advantage that the power flow can be made more uniform.
  • two or more stepped disks with end faces having their steps can be arranged in such a way that the end surfaces having the steps are arranged towards one another.
  • the stepped disc acts together with a counter-stop in the form of a second stepped disc so that the distance between the discs is changed by turning the stepped discs to each other.
  • the two stepped disks with their stepped end faces lie against one another in such a way that complement the two stepped discs by the stages are fitted into each other.
  • An axial distance between the stepped disks is then given essentially at no point on the stepped disks.
  • the stepped discs are preferably against each other over their entire faces.
  • run-on slope on the end faces of the step disc or step surface (including surfaces) of the steps are preferably provided at an angle to the end face of the step discs that the spring force to be overcome during switching is not too large. It is therefore preferred if the slopes are not designed too steep.
  • At least two stair segments comprising one or more stages, are provided on the stepped disks, wherein the stair segment can extend in particular over 180 ° of the end face and in particular may have three or more stages.
  • the provision of several stair segments enables the most uniform flow of force possible, with the greater number of stages making several switching stages feasible.
  • one of the discs is fixed against rotation on a housing of the impact wrench and with respect to the housing also not axially displaceable.
  • the other disc is relative to the Housing both rotationally and axially displaceable and thereby performs the adjustment to change the spring preload.
  • a switching element which may be articulated, for example via a lever to the movable step disc, perform an axial and a rotational movement when switching.
  • a switching element which may be articulated, for example via a lever to the movable step disc, perform an axial and a rotational movement when switching.
  • a toothed or a wave washer may be provided, in particular wave troughs and wave crests are alternately provided or has the teeth on the front side, so then depending on whether a mountain with a Wellental the second disc is in contact, the two discs abut against each other or a modified bias of the spring can be achieved when the discs come to rest with two wave crests against each other.
  • the axial distance of the discs is adjusted to each other by rotating the discs against each other.
  • a component for example in the form of a disk, or a ring or a sleeve
  • the sleeve can be displaced axially, wherein an end face of the disk, the sleeve or ., the ring cooperates with the spring and so realizes an adjustment of the biasing force of the spring.
  • a ring or sleeve in the housing via a toothing of the ring which cooperates with a toothing of the housing, be guided axially displaceable.
  • the adjustment can be made by a corresponding sliding guide, which is a movement of the ring caused in the housing to be achieved.
  • On the housing can be provided for this purpose a sliding but also a rotary switch.
  • the percussion mechanism is designed as a V-groove arrangement, wherein the hammer performs an axial-rotational oscillation with respect to the drive shaft in the case of impact.
  • the hammer in case of impact performs both an axial relative movement, the hammer on the drive shaft alternately axially towards the drive end of the drive shaft and the output side end of the drive shaft in a groove back and is moved while experiencing a relative rotation to the drive shaft.
  • the groove is in particular V-shaped and arranged the tip of the V in the direction of the output side of the shaft, wherein the axial movement due to the V-shape of the grooves at the same time causes a relative rotational movement of the hammer to the drive shaft with an axial movement, the is coupled with this.
  • the hammer can be guided over a ball guide in the V-grooves, wherein preferably two grooves are arranged diametrically opposite to the drive shaft. To guide the grooves on the hammer corresponding treads can be arranged on the hammer.
  • An impact wrench and in particular an impact wrench with a V-groove impact works as follows: In a first non-impact case, the hammer, which rotates with the drive shaft, abut against the impact jaws of the anvil over its impact jaws, which overlap in the axial direction and thus in the Engage and drive over this anvil and thus the output shaft and the tool. A corresponding drive takes place until the maximum torque of the screwdriver is achieved without causing a shock case is reached. In this state, there is no relative movement between the hammer and the anvil or between the hammer and the drive shaft.
  • the impact jaws of the hammer and anvil are arranged on mutually facing end faces of the hammer and anvil and lie in the case of impact no longer permanently against each other, as is the case in pure screwing.
  • the hammer By releasing the hammer from the anvil, the hammer is free to move in a rotational direction and is accelerated by the stored energy stored in the spring by the axial movement of the hammer in the drive direction until at the end of its relative rotational and axial movement impinges against 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 screw to be machined. After the impact, the tensioning of the percussion mechanism takes place again by the axial and radial movement of the hammer.
  • the hammer comprises a control part and a flywheel
  • the flywheel of the hammer performs no oscillating axial movement and the control part is guided axially movable in grooves in the flywheel, but is rotatably coupled to the flywheel.
  • the rotary drive of the flywheel takes place via the control part, wherein the control part interacts with the spring for energy storage and the control part carries the impact jaws of the hammer, which cooperate with the impact jaws of the anvil.
  • the spring can be provided between the control part and flywheel and the device can act on the flywheel.
  • 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 done so that higher torques are achieved, so that you can possibly work without an additional impact function.
  • FIG. 1 shows a striking mechanism of a striking screwdriver 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 which has two impact jaws 16 which are formed diametrically opposite each other in the radial direction are, wherein the striking surfaces are substantially radially extending surfaces which extend in the radial and axial planes.
  • the impact jaws 16 can as well as impact jaws 18 of a hammer 20 both curved and flat against each other, with curved impact jaws only a linear contact between the impact jaws 16 and 18 may be given.
  • the hammer 20 forms on the one hand a flywheel and serves on the other hand as a control means for the control of the impact process.
  • the striking mechanism comprises a drive shaft 22 which is coupled via a gear 24 to a drive motor 26.
  • a spring 28 is provided which serves to store energy, which is then released to produce a rotary impact.
  • the spring is a compression spring and designed in particular as a spiral spring.
  • the transmission 24 may be configured in particular as a planetary gear to translate the speed of the drive motor 26 and to vary.
  • the spring 28 acts together with its output side end 12 with the hammer 20 and lies with its drive end against a first step plate 30 of the device 32 for adjusting the spring preload. It can be provided between the stepped disc 30 and the spring 28, a bearing 34 to a Allow relative rotation of the spring 28 relative to the device 32.
  • the device 32 comprises a second stepped disc 36 which cooperates with the first stepped disc 30, wherein the stepped discs 30 and 36 are aligned with two of their end faces and are formed on the two end faces 38 and 40 stages, each with a plurality of steps a stair segment form and the steps are designed so that by rotation of the step plates 30 and 36 relative to each other there is a varying axial extent of the device 32, depending on which steps abut against each other.
  • the steps rise differently far over the base surfaces of the end faces 38 and 40, wherein the staircase segments continuously increase or decrease.
  • FIG. 1 can be taken that the impact jaws 16 of the anvil 14 overlap in the axial direction with the impact jaws of the hammer 20.
  • FIG. 2 now shows a representation of a section through a striking mechanism according to the invention FIG. 1 ,
  • the spring 28 is rotatably fixed with the hammer 20 in this, wherein the hammer 20 is guided over balls 52 in V-grooves 42 of the drive shaft 22.
  • the tip of the V of the grooves 42 faces toward the output side end 44 of the drive shaft 22.
  • the V-shaped grooves 42 serve to control the axial-rotational oscillation of the hammer 20 with respect to the drive shaft 22 in impact.
  • There are two V-grooves 42 are provided in the drive shaft 22, which are arranged diametrically opposite one another, whereby a uniform guidance and a favorable force distribution is achieved.
  • the impact jaws 18 While in the case of a screw, or in non-impact, the impact jaws 18 abut against the striking jaws 16 of the anvil 14 and drive it, it comes in case of impact at a first blockage and thereby holding the tool with the anvil 14 and a simultaneous further rotation of the drive shaft 22, the is further driven by the motor 26, by the anvil of the anvil 14 to a migration of the hammer 20 in the V-grooves 42 by being guided over the balls 52 and thus to a movement in the direction of the arrow 46 and to a relative rotation of the hammer 20 to the drive shaft 22. It then comes to a latching of the impact jaws 18 with the impact jaws 16, if they separate axially from each other.
  • the device 32 already described is provided, which is formed of two stepped discs 30, 36, each with their stepped faces 38, 40 abut against each other.
  • the stepped disk 30 has a Actuator 48, which in FIG. 1 is shown, whereas the stepped pulley 36 is fixed against rotation on the gear of the impact wrench and can not be moved in the axial direction.
  • FIG. 3 shows the stepped pulley 36, which is fixed with attachment means, here via a screw 50, the transmission housing and thus with respect to the housing of the electric hand tool device rotationally fixed and axially immovable.
  • attachment means here via a screw 50
  • the transmission housing On an end face 40 of the stepped disk 36, there are provided here two stairways 54 'and 54 "which each comprise five steps 56, each stair segment 54' and 54" extending over approximately 180 ° of the end face 40.
  • the steps 46 are in this case inclined with respect to their step surfaces or surfaces 58 to the end face 40 of the stepped disk 36 and rise within a stair segment 54 on or off depending on the consideration.
  • FIG. 4 now shows the second stepped disc 30, which has an actuating element 48 which is attached via a lever 60 to the step disc 30 has.
  • the stepped pulley 30 also has two staircase segments 62 'and 62''which also extend over approximately 180 ° of the stepped pulley 30 and also have five steps 64 which also have an inclined step surface and rising from the base of the end face 38, depending on which of the stages 54 cooperates with a corresponding step 64, this leads to a different axial extent of the device 32 with the step plates 30, 36th
  • the stepped discs 30, 36 with their stair segments 54 and 62 against each other so that it is approximately full-surface contact of the stepped discs 30 and 36 against each other.
  • Rotational movement via the adjusting element 48 of the stepped disk 30 then causes the steps 56 and 64 to move relative to one another, so that, due to the step-like design, overcoming the spring force of the spring 28 results in an axial movement of the stepped disk 30 with respect to the stepped disk 36.
  • FIG. 5 shows an alternative embodiment of the impact mechanism, in which case the same components are provided with the same reference numerals.
  • a drive shaft 22 via a drive motor 26 which is coupled to the drive shaft via a gearbox 24, driven and it is a device 32, as shown in the FIGS. 1-4 has been described.
  • a two-piece hammer 20 is provided, comprising a flywheel 70 and a control part 72, wherein the control part 72 carries the impact jaws 18 of the hammer 20.
  • the spring 28 is arranged, which serves the energy storage to enable the impact of the control part 72 against the impact jaws 16 of the anvil 14.
  • a bearing 74 is located between the stepped disc 30 and the flywheel 70, wherein the flywheel mass includes the essential mass of the hammer 20 and the control part 72 may have a comparatively lower mass.
  • the control part 72 is now guided in the axial direction in grooves of the flywheel 70, in which the Control part 72 engages with corresponding ribs.
  • the control part 72 is rotatably connected to the flywheel 70 and drives these rotationally.
  • the flywheel 70 has no oscillating axial movement component and thus causes no vibration excitation of the machine in this direction. Due to the much smaller mass of the control part 72 lower vibrations are caused, so that the machine is generally more pleasant to lead. However, the flywheel 70 is still the necessary mass for the rotary blow available.
  • the control part 72 is further guided in the V-grooves 42 of the drive shaft 22 and therefore make a movement corresponding to the hammer in the FIGS.
  • the impact jaws 18 of the control part can protrude in the direction of the anvil 14 in the axial direction over the end face 76 of the flywheel 70 in the case of a rotary drive and thus a covering with the impact jaws 16 of the anvil 14.
  • a design may be provided in which the end face 78 of the impact jaws 18 of the control part 72 is flush with the end face 76 of the flywheel 70 and immerse the impact jaws 16 of the anvil 14 in the flywheel 70.
  • FIG. 6 now shows a design of a corresponding impact mechanism according to FIG. 5 in a non-sectional view, wherein the means 32 for presetting the torque of in FIG. 1 and 2 shown corresponds.
  • the flywheel 70 may be formed as a substantially cylindrical sleeve, wherein on its inner side, the spring 28 is supported against a drive-side end face 80 of the flywheel 70.
  • the device then interacts in particular with the flywheel 70 and moves it axially, whereby the change in bias is transmitted to the spring 28.
  • the advantage is achieved that without sacrificing speed in a torque adjustment can be realized in a purely mechanical way, so that a total of one screw can be completed faster due to the lack of speed reduction.
  • a speed control can be done via a gearbox regardless of the torque setting.
  • a corresponding embodiment is structurally simple and includes only compared to a conventional design only a few other components.
  • the vibrations in the axial direction can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (13)

  1. Visseuse frappeuse comportant un moteur d'entraînement (26) pour actionner un arbre d'entraînement (22) et un arbre de sortie (10) accouplé et agencé pour recevoir un outil ainsi qu'un mécanisme frappeur, dans laquelle le mécanisme frappeur comporte une enclume (14) couplée à l'arbre de sortie (10) ayant des premières joues frappeuses (16) ainsi qu'un marteau (20) qui est guidé sur l'arbre d'entraînement (22) et qui est entraîné en rotation avec lui lorsqu'il n'est pas en fonction de frappe et qui effectue un déplacement en translation, lorsqu'il est en fonction de frappe relativement à l'arbre d'entraînement (22), dans laquelle le marteau (20) comporte des secondes joues frappeuses (18) qui sont couplées aux premières joues frappeuses (16) de l'enclume (14) pour la transmission du mouvement de rotation, dans laquelle un ressort (28) est prévu pour générer l'énergie de frappe, alternativement mis en contrainte et relâché, en fonction de frappe, par le déplacement axial du marteau (20), dans laquelle, la contrainte du ressort (28) peut être réglée en continu ou en discontinu au moyen d'un dispositif de réglage (32), ce dispositif (32) étant monté entre le ressort (28) et l'arbre d'entraînement, caractérisée en ce qu'un roulement est prévu entre le dispositif (32) et l'arbre de transmission (22) et entre le dispositif (32) et le ressort (28).
  2. Visseuse frappeuse selon la revendication 1, caractérisée en ce que le ressort (28) est un ressort de compression.
  3. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que le dispositif de réglage (32) comprend au moins deux couronnes à gradins (30, 36) qui sont disposées en regard par les surfaces frontales (38, 40) de leurs gradins (56, 64), dans laquelle le décalage axial des couronnes (30, 36), l'une par rapport à l'autre est réglable par une rotation relative desdites couronnes (30, 36).
  4. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que le mécanisme frappeur est configuré sous la forme d'un mécanisme frappeur à rainure, dans laquelle le marteau (20) en fonction de frappe effectue un mouvement axial et rotatif oscillant par rapport à l'arbre d'entraînement (22).
  5. Visseuse frappeuse selon la revendication 3, caractérisée en ce que l'arbre d'entraînement (22) comporte au moins une gorge en V (42) et en ce que le marteau (20) est guidé dans les gorges en V (42) de l'arbre d'entraînement (22).
  6. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que le marteau (20) et l'enclume (14) comportent deux ergots de frappe (16, 18) respectifs, diamétralement opposés.
  7. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que les couronnes à gradins (30, 36) comportent deux ou plus de gradins (56, 64).
  8. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que les gradins (56, 64) forment un angle par rapport à la surface frontale (38, 40) des couronnes à gradins (30, 36).
  9. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que chaque couronne à gradins (30, 36) comporte au moins deux segments décalés (54, 62) englobant un ou plusieurs gradins (56, 64).
  10. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que l'une des couronnes (36) est fixe axialement par rapport à un logement de la visseuse frappeuse et en ce que l'autre couronne (30) est mobile axialement par rapport à ce logement.
  11. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que la couronne mobile (30) est couplée avec un élément de commande (48, 60).
  12. Visseuse frappeuse selon la revendication 11, caractérisée en ce que l'élément de commande (48, 60) enclenche un composant mobile en rotation et en translation axiale à l'enclenchement.
  13. Visseuse frappeuse selon l'une quelconque des revendications précédentes, caractérisée en ce que la visseuse frappeuse est un appareil équipé d'un accumulateur.
EP20080011818 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper Not-in-force EP2140978B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20080011818 EP2140978B1 (fr) 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20080011818 EP2140978B1 (fr) 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper

Publications (2)

Publication Number Publication Date
EP2140978A1 EP2140978A1 (fr) 2010-01-06
EP2140978B1 true EP2140978B1 (fr) 2012-11-28

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EP20080011818 Not-in-force EP2140978B1 (fr) 2008-07-01 2008-07-01 Vis autotaraudeuse à frapper

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Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102011005079A1 (de) * 2011-03-04 2012-09-06 Hilti Aktiengesellschaft Setzverfahren für einen Spreizanker und Schlagschrauber zum Setzen eines Spreizankers
JP2013208682A (ja) * 2012-03-30 2013-10-10 Hitachi Koki Co Ltd 動力工具
DK3356636T3 (da) * 2015-09-30 2020-05-11 Jaron Lyell Mcmillan Slagindretning
DE102021214868A1 (de) 2021-12-22 2023-06-22 Robert Bosch Gesellschaft mit beschränkter Haftung Handwerkzeugmaschine
DE102021214864A1 (de) 2021-12-22 2023-06-22 Robert Bosch Gesellschaft mit beschränkter Haftung Handwerkzeugmaschine
CN117072595B (zh) * 2023-10-17 2024-02-06 盐城大丰盛源机械有限责任公司 一种电动车后减震器

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
GB1180771A (en) * 1967-07-21 1970-02-11 Desoutter Brothers Ltd Improved power-operated impact wrench or screwdriver.
GB1282300A (en) * 1969-12-08 1972-07-19 Desoutter Brothers Ltd Improved impact wrench or screwdriver
DE4301610C2 (de) 1993-01-22 1996-08-14 Bosch Gmbh Robert Schlagschrauber
JP2002254336A (ja) 2001-03-02 2002-09-10 Hitachi Koki Co Ltd 電動工具
DE10341697B3 (de) * 2003-09-10 2004-10-07 Felo-Werkzeugfabrik Holland-Letz Gmbh Schraubwerkzeug mit einer Vorrichtung zur Begrenzung des übertragenen Drehmomentes
US7013769B2 (en) * 2004-03-19 2006-03-21 Chang-Ying Chen Torque adjustable screw driver
US20060237205A1 (en) * 2005-04-21 2006-10-26 Eastway Fair Company Limited Mode selector mechanism for an impact driver
US7168503B1 (en) * 2006-01-03 2007-01-30 Mobiletron Electronics Co., Ltd. Power hand tool

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