EP3825063B1 - Machine-outil portative - Google Patents

Machine-outil portative Download PDF

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Publication number
EP3825063B1
EP3825063B1 EP20208763.1A EP20208763A EP3825063B1 EP 3825063 B1 EP3825063 B1 EP 3825063B1 EP 20208763 A EP20208763 A EP 20208763A EP 3825063 B1 EP3825063 B1 EP 3825063B1
Authority
EP
European Patent Office
Prior art keywords
switch
contour
torque
machine tool
hand
Prior art date
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Active
Application number
EP20208763.1A
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German (de)
English (en)
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EP3825063A1 (fr
Inventor
Frank Walz
Michael Mück
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.)
C&E Fein GmbH and Co
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C&E Fein GmbH and Co
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Publication of EP3825063A1 publication Critical patent/EP3825063A1/fr
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • 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
    • B25B23/147—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for electrically operated wrenches or screwdrivers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools

Definitions

  • the invention relates to an electric hand-held power tool, in particular a cordless screwdriver, with a preferably electric drive accommodated in a housing, which drives a drive shaft, with an output unit which can be non-positively connected to the drive by means of a mechanical shut-off clutch, in order to transfer torque from the drive to a to transfer the application tool connected to the output unit, wherein the mechanical shut-off clutch comprises a switching ring which is mounted axially against the force of a return spring and at least one switching element guided on a control cam, the control cam being limited at one end by a first switching contour for providing a release torque of the shut-off clutch and at the other end by a limiting contour is.
  • the document EP 0 476 999 A1 shows an electric hand tool according to the preamble of claim 1.
  • This shut-off clutch includes a switching ring, which is axially adjusted against the force of a return spring when the predefinable tightening torque is exceeded and thereby unlocks, or opens or releases, the shut-off clutch.
  • the torque of the drive train In order to open the shut-off clutch, the torque of the drive train must ultimately overcome the force of the return spring. With increasing torque that is introduced into the shut-off clutch, the introduced torque is transmitted to the shift ring until the force of the return spring, which counteracts the shift ring in the axial direction, is less than the force component that is due to the applied torque in the axial direction direction.
  • the switching ring is then deflected axially against the force of the restoring spring and relative rotation occurs between the first switching contour and the switching element.
  • This axial deflection of the switching ring and thus ultimately the opening of the shut-off clutch is usually used as a sensor signal in order to switch off the drive and, if necessary, brake it and thus bring it to a standstill.
  • a microswitch can be used here for switching or a magnetic field can also be changed by the axial deflection.
  • a switching slide with a magnet accommodated therein is also axially deflected during the axial deflection of the switching ring.
  • the induced by the axial deflection of the magnet Detect changes in the magnetic field, which can then be used as a sensor signal to switch off the drive.
  • the force of the return spring pushes the switching ring axially back in the direction of the drive and forces the switching element back onto the control cam.
  • the part of the shut-off clutch which is non-rotatably connected to the drive is then rotated further by the available rotational energy of the drive until the motor comes to a standstill. If the drive speed is low, the drive is switched off and braked so quickly that the shut-off clutch does not trip again. In order to ensure a defined screwing process, the drive is often continued to be operated at a very low speed after a short time until the first switching contour is again in contact with the switching element. The shut-off clutch is now in its starting position for the next screw connection.
  • shut-off clutch is associated with an acoustic effect that can usually be referred to as a clicking noise. If the shut-off clutch now releases several times, this is often irritating for the user, since he then assumes that the screw connection was incorrectly executed if he hears the clicking noise several times.
  • the object of the present invention is therefore to reduce the above-mentioned disadvantages, in particular to provide a hand-held power tool that provides improved process reliability at high screwing speeds.
  • the second switching contour ultimately provides a pre-shift torque, which also leads to an axial deflection of the switching ring, which is mounted axially against the force of the return spring.
  • This additional axial deflection is used to generate an upstream signal well before the actual triggering torque is reached, which ultimately corresponds to the tightening torque, in order to switch off or brake the drive at this early point in time, or at least to prepare for these steps.
  • it is also alternatively or additionally provided, in addition to detecting the axial adjustment of the switching ring, to also detect a relative rotation of the switching ring with respect to the part of the shut-off clutch non-rotatably connected to the drive shaft.
  • This relative rotation ultimately occurs when the pre-shift torque is exceeded and the shifting element over the second shifting contour slides away and then comes to rest at the first switching contour.
  • the second switching contour can therefore already detect an increasing torque before the actual triggering of the shut-off clutch, in order to initiate or prepare for shutting off or braking the drive.
  • the first shifting contour has a shifting point whose tangent slope defines the release torque of the shut-off clutch, and if the cam is assigned a second shifting contour with a pre-shift point whose tangent slope defines the pre-shift torque that is smaller than the release torque . Since the triggering torque or the pre-shifting torque can be determined on the basis of the slope of the tangent at the switching point or at the pre-shifting point, this provides a simple way of defining the triggering torque and the pre-shifting torque. In this context, it has also turned out to be advantageous if the gradient of the tangent at the switching point is greater than the gradient of the tangent at the upstream switching point. If the stroke of the second switching contour is the same as or less than that of the first switching contour, this ensures when the second switching contour is triggered that the pre-shift torque can be clearly distinguished from the triggering torque of the first switching contour.
  • the ratio between the gradient of the tangent of the switching point and the gradient of the tangent of the upstream switching point is preferably 1.2:1 or greater, preferably 1.5:1 or greater and particularly preferably 1.8:1 or greater and more preferably 4 :1 or less, preferably 3:1 or less and most preferably 2:1. This ensures that the value of the pre-shift torque is significantly lower than the value of the triggering torque in order to be able to make a reliable distinction between the pre-clamping torque and the triggering torque.
  • the angle between the slope of the tangent of the switching point and a plane that is oriented perpendicularly to the drive shaft is preferably 50° or greater, preferably 55° or greater and particularly preferably 60° or greater and greater preferably 80° or less, preferably 75° or less, and more preferably 70° or less. If this angle becomes too large, there is a risk that the shifting element can only slide over the first shifting contour with difficulty when the shut-off clutch is released, ie that the release torque in particular increases too much.
  • the angle between the slope of the tangent of the upstream switching point and a plane which is oriented perpendicularly to the drive shaft is preferably 20° or greater, preferably 25° or greater and particularly preferably 30° or is greater and more preferably 45° or less, preferably 40° or less and particularly preferably 35° or less. This also ensures that a suitable differentiation can be made between the pre-clutching torque and the triggering torque.
  • the cam has a constant slope in the area of the second switching contour. In particular, this can be implemented particularly easily in terms of manufacturing technology.
  • the resulting characteristic increase in torque can be used to detect that the shifting element is in the area of the second shifting contour, which then initiates or initiates the switching off and/or braking of the drive can be executed.
  • conclusions can be drawn about the torque rate. The faster the axial deflection occurs, the harder the screwdriving is. Ultimately, this makes it possible to control the switch-off or braking behavior of the drive depending on the hardness of the screwdriving application.
  • the control curve includes a first maximum, which defines the triggering torque, and a second maximum, which defines the pre-clutching torque.
  • the use of two maxima ultimately means that the deflection of the switching ring, which can be adjusted axially against the spring force of the restoring spring, can be shifted by the second switching contour significantly before the deflection by the first switching contour.
  • the first maximum is greater than the second maximum. This takes into account the fact that the switching signal is generated by the deflection of the axially adjustable switching ring, ie ultimately the axial deflection of the switching ring is to be detected.
  • a differentiation can then be made between the pre-clamping torque and the triggering torque.
  • a relative rotation can also be caused by the maxima between the adjusting ring and the part of the shut-off clutch which is non-rotatably connected to the drive shaft.
  • the ratio of the height of the first maximum to the height of the second maximum is preferably 1.5:1 or greater, preferably 3:1 or greater and particularly preferably 4:1 or greater and more preferably 10: 1 or less, preferably 8:1 or less and more preferably 6:1 or less and most preferably 5:1. This also ensures that a clear differentiation can be made between the pre-shift torque and the triggering torque, which ultimately reduces the risk that the axial deflection of the switching ring induced by the pre-shift torque is held for the movement induced by the triggering torque.
  • the amount of the derivation of the course of the control curve in the area of the first shifting contour and the second shifting contour is greater than 0. This ultimately provides a continuously rising control curve between the two shifting contours which, however, both the pre-shift torque and the release torque are delimited by a clearly defined shift contour. In addition, this ensures that after the release of the shut-off clutch and the shutting off and braking of the drive, the shifting element cannot permanently reach an intermediate position between the first shifting contour and the second shifting contour.
  • the boundary contour of an adjacent second control cam is formed on the first switching contour of a first cam. In this way, in particular, the production outlay is further reduced.
  • the edge of the delimiting contour is steeper than the first switching contour. This means that when the direction of travel of the drive is reversed—that is, to loosen an existing screw connection—the loosening torque is greater than the tightening torque of the screw connection.
  • the shut-off clutch includes a cam ring which is connected to the drive shaft in a torque-proof manner and on which the cam ring is formed.
  • a functional division is created in particular, the mechanical overload individual components.
  • the switching element is designed as a switching ball.
  • the shifting element is designed, for example, as a shifting cylinder that is guided on the cam.
  • the restoring spring is designed as a compression spring whose spring force is adjustable.
  • the spring force is adjustable.
  • due to the adjustability of the spring force it can be achieved that different screw connections can be carried out with the electric hand-held power tool.
  • FIG 1 shows a perspective view of an electric hand tool 1, which is formed in the embodiment shown as an industrial cordless screwdriver 2 with high precision, more precisely as a baton angle screwdriver 3, which is usually used in industrial series screw connections.
  • This baton angle screwdriver 3 has a drive 5 accommodated in a housing 4, the direction of rotation of which can be adjusted by means of a control switch 6 in order to give the user the opportunity to undo a screw connection again.
  • the electrical energy required to supply power to the drive 5 is provided by an accumulator 7 which is detachably attached to the baton angle screwdriver 3 .
  • Accumulator 7 pioneering end is formed on the rod angle wrench 3 a receptacle 8, with the various attachments or tools can be connected. In the embodiment shown, this is an example of an angle head 9.
  • the one in the figure 2 The section of a longitudinal section through the baton angle wrench 3 shown in the illustration shows that the drive 5 drives a drive shaft 11 via a gear 10 .
  • the drive shaft 11 is non-positively connected to an output unit 13 via a mechanical shut-off clutch 12 .
  • This output unit 13 ends in the receptacle 8 to which the various attachments or application tools can be attached.
  • FIG. 1 shows a first embodiment of the shut-off clutch 12, this comprises a switching ring 15 which is mounted axially against the force of a return spring 14 and which is designed to be essentially non-rotatable with a switching element 16 which is formed as a switching ball 17 in the exemplary embodiment shown .
  • the switching ball 17 runs on a control cam 18 which is formed on a cam ring 19 which is connected to the drive shaft 11 in a rotationally fixed manner.
  • the torque applied by the drive 5 is introduced from the transmission 10 at the cam ring 19 into the shut-off clutch 12 and is ultimately transmitted to the output unit 13 when the shut-off clutch 12 is closed.
  • the torque is transmitted from the control curve 18 formed on the cam ring 19 to the switching ring 15 via the switching element 16, which is provided in triplicate in the exemplary embodiment shown.
  • the switching elements 16 are each accommodated captively on the switching ring 15 in a ball pocket 20, but have certain degrees of freedom of movement here.
  • the Shift ring 15 is mounted on the output unit 13 axially against the force of the prestressed return spring 14 which is mounted between the shift ring 15 and a pressure ring 21 .
  • the axial position of the pressure ring 21 in the direction of the receptacle 8 is limited by means of an adjusting ring 22 which is adjustably mounted on the output unit 13 via a threaded connection 23 .
  • the cam ring 19 is rotatably mounted with respect to the output unit 13 in order to enable the relative rotation required for triggering the shut-off clutch 12 .
  • the cam 18 is delimited at one end by a first switching contour 24 and at the other end by a delimiting contour 25 .
  • the release torque of the shut-off clutch 12, which corresponds to the screwing torque is provided by the first shifting contour 24.
  • the control cam 18 also includes a second switching contour 26, the function of which is explained in particular below with reference to FIG Figures 4 to 8 is explained in more detail.
  • the second switching contour 26 becomes visible, which is formed between the delimiting contour 25 and the first switching contour 24 .
  • This second switching contour 26 provides a pre-switching torque that is smaller than the triggering torque.
  • the control curve 18 has a curve with a curvature or radius adapted to the switching element 16 in the area of the first switching contour 24, the control curve 18 has a constant gradient in the area of the second switching contour 26, i.e. it is ultimately a straight line educated.
  • the amount of the derivation of the course of the cam 18 in the area of the first shifting contour 24 and the second shifting contour 26 is constantly greater than 0 and the second derivative of the course of the cam 18 is greater than or equal in the area of the first shifting contour 24 and the second shifting contour 26 0.
  • the figure 4 can also be seen that on the first switching contour 24 of a first cam 18, the boundary contour 25 of an adjacent second cam 18 is formed.
  • the Figures 5 to 7 show the course of the triggering behavior of the handheld power tool 1 according to the invention, implemented by the cam 18.
  • the figure 5 shows the state of the shut-off clutch 12 during screwing.
  • the shifting element 16 rests against the second shifting contour 26 which defines the pre-shift torque, and the torque is transmitted from the drive 5 via the transmission 10 and the closed shut-off clutch 12 to the output unit 13 .
  • the torque of the drive 5 introduced at the cam ring 19 is transmitted to the switching ring 15 until the pre-shift torque is exceeded.
  • the switching element 16 then slides on the second switching contour 26, as in FIG figure 6 shown.
  • the switching ring 15 is adjusted axially against the force of the return spring 14 .
  • This axial displacement of the switching ring 15 can now be detected, for example by means of a magnet and a corresponding Hall sensor, and used to prepare for or already initiate the switching off and braking of the drive 5 at this early point in time by means of appropriate drive electronics.
  • the switching ring 15 moves further axially against the force of the return spring 14 misaligned. This is the particular figure 7 refer to.
  • This displacement is now also detected, for example by the magnets already mentioned and the Hall sensor, and the switching off and braking of the drive 5 is completed and the screwing is thus ended.
  • the force of the return spring 14 then presses the switching ring 15 with the switching element 16 back onto the control curve 18 of the cam ring 19.
  • the second switching contour 26 ensures that an earlier signal for braking the drive shaft 11 occurs in good time so that the repeated triggering of the shut-off clutch 12 is avoided.
  • the cam ring 19 continues to be rotated at a very low speed by the drive 5 until the second switching contour 26 reaches the switching element 16 . There it comes to a standstill.
  • the shut-off clutch 12 is now in its starting position for the next screw connection, in which the switching element 16 rests against the second switching contour 26 .
  • the first switching contour 24 has a switching point 31 whose tangent gradient defines the release torque of the shut-off clutch 12 .
  • the pre-shift torque is defined by the slope of the tangent of a pre-shift point 32 which is associated with the second shift contour 26 .
  • the tangent slope of the switching point 31 is greater than the tangent slope of the upstream switching point 32, which ultimately means that the upstream torque is smaller than the triggering moment, which is determined by the tangent slope in the switching point 31 of the first switching contour 24.
  • the ratio between the gradient of the tangent of the switching point 31 and the gradient of the tangent of the upstream switching point 32 is around 2:1.
  • the angle between the slope of the tangent of the switching point 31 and a plane 33 that is perpendicular to the drive shaft 11 is oriented between 60° and 70°.
  • the angle between the slope of the tangent of the upstream switching point 32 and the plane 33 is between 30° and 35°.
  • figure 9 shows a perspective view of a cam 18 of a second embodiment of the shut-off clutch 12.
  • the cam 18 has a first maximum 34, which forms the first shifting contour 24 and defines the triggering moment, and a second maximum 35, which forms the second shifting contour 26 and the Pre-torque defined.
  • the first maximum 34 is greater than the second maximum 35 and the ratio of the height of the first maximum 34 to the height of the second maximum 35 is 5:1.
  • the slope of the edge of the first maximum 34 is greater than the slope of the edge of the second maximum 35.
  • figure 10 and figure 11 show in a partially sectional view the axial adjustment of the switching ring 15 when the applied torque exceeds the pre-shift torque.
  • the switching element 16, which is formed as a switching ball 17 is adjusted by the level of the second maximum 35, which forms the pre-shift torque. Due to the lower height of the second maximum 35 compared to the first maximum 34, there is also less axial displacement of the switching ring 15 than when the switching element 16 is adjusted by the height of the first maximum 34, which occurs when the shut-off clutch 12 is released. This difference in the axial adjustment can thus be used again in order to be able to differentiate whether the axial adjustment of the switching ring 15 was effected by the pre-clutching torque or by the triggering torque.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Claims (15)

  1. Machine-outil manuelle électrique (1), en particulier visseuse sans fil (2), avec un entraînement électrique (5) de préférence logé dans un boîtier (4), qui entraîne un arbre d'entraînement (11), avec une unité de sortie (13), qui peut être reliée à force à l'entraînement (5) au moyen d'un embrayage de coupure mécanique (12) afin de transmettre le couple de rotation de l'entraînement (5) à un outil d'insertion relié à l'unité de sortie (13), dans laquelle l'embrayage de coupure mécanique (12) comprend une bague de commutation (15) montée axialement contre la force d'un ressort de rappel (14) et au moins un élément de commutation (16) guidé sur une came de commande (18), dans laquelle la came de commande (18) est limitée sur une extrémité par un premier contour de commutation (24), qui sert à la mise à disposition d'un couple de déclenchement de l'embrayage de coupure (12), lorsque l'élément de commutation (16) glisse au-delà du premier contour de commutation (24) et qu'un signal de capteur peut être de ce fait généré pour la coupure de l'entraînement (5), et dans laquelle la came de commande (18) est limitée sur une autre extrémité par un contour de limitation (25), caractérisée en ce qu'est associé à la came de commande (18) un deuxième contour de commutation (26), qui sert à la mise à disposition d'un couple de commutation en amont, lorsque l'élément de commutation (16) glisse au-delà du deuxième contour de commutation (26) et qu'un signal de commutation en amont du signal de capteur peut de ce fait être généré, dans laquelle le couple de commutation en amont est inférieur au couple de déclenchement.
  2. Machine-outil manuelle électrique (1) selon la revendication 1, caractérisée en ce que le premier contour de commutation (24) présente un point de commutation (31), dont la pente de tangente définit le couple de déclenchement de l'embrayage de coupure (12), et en ce qu'est associé à la came de commande (18) un deuxième contour de commutation (26) avec un point de commutation en amont (32), dont la pente de tangente définit le couple de commutation en amont, qui est inférieur au couple de déclenchement.
  3. Machine-outil manuelle (1) selon la revendication 2, caractérisée en ce que la pente de tangente du point de commutation (31) est supérieure à la pente de tangente du point de commutation en amont (32).
  4. Machine-outil manuelle (1) selon la revendication 2 ou 3, caractérisée en ce que le rapport entre la pente de tangente du point de commutation (31) et la pente de tangente du point de commutation amont (32) est de préférence supérieur ou égal à 1,2:1, de manière préférée supérieur ou égal à 1,5:1 et de manière particulièrement préférée supérieur ou égal à de 1,8:1 et de préférence par ailleurs inférieur ou égal à de 4:1, de manière préférée inférieur ou égal à de 3:1 et de manière très particulièrement préférée égal à 2:1.
  5. Machine-outil manuelle (1) selon l'une quelconque des revendications 2 à 4, caractérisée en ce que l'angle entre la pente de tangente du point de commutation (31) et un plan (33), qui est orienté perpendiculairement à l'arbre d'entraînement (11), est de préférence supérieur ou égal à 50°, de manière préférée supérieur ou égal à 55° et de manière particulièrement préférée supérieur ou égal à 60°et, de préférence par ailleurs inférieur ou égal à 80°, de manière préférée inférieur ou égal à 75° et de manière particulièrement préférée inférieur ou égal à 70°.
  6. Machine-outil manuelle (1) selon l'une quelconque des revendications 2 à 5, caractérisée en ce que l'angle entre la pente de tangente du point de commutation en amont (32) et le plan (33), qui est orienté perpendiculairement à l'arbre d'entraînement (11), est de préférence supérieur ou égal à 20°, de manière préférée supérieur ou égal à 25° et de manière particulièrement préférée supérieur ou égal à 30° et de préférence par ailleurs inférieur ou égal à 45°, de manière préférée inférieur ou égal à 40° et de manière particulièrement préférée inférieur ou égal à 35°.
  7. Machine-outil manuelle (1) selon l'une quelconque des revendications 1 à 6, caractérisée en ce que la came de commande (18) présente une pente constante dans la zone du deuxième contour de commutation (26).
  8. Machine-outil manuelle (1) selon l'une quelconque des revendications 1 à 7, caractérisée en ce que la came de commande (18) comprend un premier maximum (34), qui définit le couple de déclenchement, et un deuxième maximum (35), qui définit le couple de commutation en amont.
  9. Machine-outil manuelle (1) selon la revendication 8, caractérisée en ce que le premier maximum (34) est supérieur au deuxième maximum (35).
  10. Machine-outil manuelle (1) selon la revendication 8 ou 9, caractérisée en ce que le rapport entre la hauteur du premier maximum (34) et la hauteur du deuxième maximum (35) est de préférence de supérieur ou égal à 1,5:1, de manière préférée supérieur ou égal à 3:1 et de manière particulièrement préférée supérieur ou égal à 4:1 et de préférence par ailleurs inférieur ou égal à 10:1, de manière préférée inférieur ou égal à 8:1 et de manière particulièrement préférée inférieur ou égal à 6:1 et de manière très particulièrement préférée égal à 5:1.
  11. Machine-outil manuelle (1) selon l'une quelconque des revendications 1 à 10, caractérisée en ce que la valeur de la dérivée du tracé de la came de commande (18) dans la zone du premier contour de commutation (24) et du deuxième contour de commutation (26) est supérieure à 0.
  12. Machine-outil manuelle (1) selon l'une quelconque des revendications 1 à 11, caractérisée en ce que la deuxième dérivée du tracé de la came de commande (18) dans la zone du premier contour de commutation (24) et du deuxième contour de commutation (26) est supérieure ou égale à 0.
  13. Machine-outil manuelle (1) selon l'une quelconque des revendications 1 à 12, caractérisée en ce que l'élément de commutation (16) et la came de commande (18) sont prévus plusieurs fois, notamment trois fois.
  14. Machine-outil manuelle (1) selon l'une quelconque des revendications 1 à 13, caractérisée en ce que le contour de limitation (25) d'une deuxième came de commande (18) adjacente est réalisé sur le premier contour de commutation (24) d'une première came de commande (18).
  15. Machine-outil manuelle (1) selon l'une quelconque des revendications 1 à 14, caractérisée en ce que l'accouplement de coupure (12) comprend une bague à cames (19) reliée de manière solidaire en rotation à l'arbre d'entraînement (11), sur laquelle la came de commande (18) est réalisée.
EP20208763.1A 2019-11-22 2020-11-19 Machine-outil portative Active EP3825063B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202019106525.7U DE202019106525U1 (de) 2019-11-22 2019-11-22 Handwerkzeugmaschine

Publications (2)

Publication Number Publication Date
EP3825063A1 EP3825063A1 (fr) 2021-05-26
EP3825063B1 true EP3825063B1 (fr) 2023-08-09

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US (1) US11701758B2 (fr)
EP (1) EP3825063B1 (fr)
CN (1) CN112828817B (fr)
DE (1) DE202019106525U1 (fr)
ES (1) ES2964576T3 (fr)
HU (1) HUE063690T2 (fr)

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DE3510605A1 (de) * 1985-03-23 1986-10-02 C. & E. Fein Gmbh & Co, 7000 Stuttgart Kupplung fuer kraftgetriebene schraubwerkzeuge
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SE520916C2 (sv) * 1999-12-28 2003-09-09 Atlas Copco Tools Ab Mutterdragare med momentkoppling med utlösningssensor för kraftavstängning
DE10124569A1 (de) * 2001-05-14 2002-11-21 C & E Fein Gmbh & Co Kg Kraftgetriebener Schrauber mit Drehmomentbegrenzungskupplung
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JP4359716B2 (ja) * 2004-10-21 2009-11-04 株式会社マキタ 締付け工具
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DE102015201573A1 (de) * 2015-01-29 2016-08-04 Robert Bosch Gmbh Schlagwerkvorrichtung, insbesondere für einen Schlagschrauber
DE102016220001A1 (de) * 2015-10-15 2017-04-20 Robert Bosch Gmbh Handwerkzeugmaschine
DE102017102497A1 (de) * 2017-02-08 2018-08-09 C. & E. Fein Gmbh Drehmomentabhängig auslösbare Kupplung für ein Handwerkzeug
US10801552B2 (en) * 2018-07-26 2020-10-13 C&E Fein Gmbh Torque-dependant, releasable clutch for a hand-held power tool

Also Published As

Publication number Publication date
CN112828817A (zh) 2021-05-25
US20210154807A1 (en) 2021-05-27
US11701758B2 (en) 2023-07-18
EP3825063A1 (fr) 2021-05-26
HUE063690T2 (hu) 2024-02-28
ES2964576T3 (es) 2024-04-08
CN112828817B (zh) 2022-11-15
DE202019106525U1 (de) 2021-02-26

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