EP0523477B1 - Outil de vissage avec réglage du couple variable - Google Patents

Outil de vissage avec réglage du couple variable Download PDF

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Publication number
EP0523477B1
EP0523477B1 EP92111307A EP92111307A EP0523477B1 EP 0523477 B1 EP0523477 B1 EP 0523477B1 EP 92111307 A EP92111307 A EP 92111307A EP 92111307 A EP92111307 A EP 92111307A EP 0523477 B1 EP0523477 B1 EP 0523477B1
Authority
EP
European Patent Office
Prior art keywords
screwdriver according
spring
ring
torque
screwdriver
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92111307A
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German (de)
English (en)
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EP0523477A1 (fr
Inventor
Wolfgang Schreiber
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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Filing date
Publication date
Application filed by C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP0523477A1 publication Critical patent/EP0523477A1/fr
Application granted granted Critical
Publication of EP0523477B1 publication Critical patent/EP0523477B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • 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

Definitions

  • the invention relates to a screwdriver with variable torque setting, in particular a screwdriver with torque switch-off, with a shaft driven by a motor via a transmission for driving a tool, with an actuating device for presetting a torque in which the motor is switched off.
  • Such a screwdriver is known from DE 37 42 952 A1.
  • a work spindle is driven by a motor via a two-stage planetary gear.
  • the first gear stage of the planetary gear has a motor pinion that drives planet gears held on a planet carrier, which are supported in a ring gear.
  • the second gear stage is coupled to the planet carrier with a second ring gear which is held in the housing in a rotationally fixed manner.
  • the first ring gear on the drive side is rotatably mounted and, when an adjustable limit torque is exceeded, it actuates a motor cut-out against the action of a torsion spring.
  • the tightening torque of a screw can be set very precisely in the case of soft screwdriving, since the counter-torque increases only slowly when the screw is tightened.
  • the counter-torque increases suddenly when the screw reaches the end position and the angular momentum that is still present in the entire transmission system leads to an additional tightening of the screw.
  • the actual tightening torque of the screw cannot be precisely determined in the case of hard screwdriving, since it is influenced to a considerable extent by the re-turning angle.
  • the object of the present invention is accordingly to improve a screwdriver of the type mentioned in such a way that, regardless of the size of the re-turning angle, there are approximately the same torque characteristics for hard and soft screwdriving depending on the setting of the screwdriver.
  • this object is achieved in a screwdriver with variable torque setting, in particular a screwdriver with torque switch-off, with a shaft driven by a motor via a transmission for driving a tool and with an adjusting device for presetting a torque at which the motor is switched off. that, independently of this, a separating clutch with variable triggering torque is additionally provided, and that a second adjusting device is provided for setting the second triggering torque, which can be adjusted together with the first adjusting device.
  • a screwdriver according to the invention therefore has, in addition to a first actuating device for presetting a torque, a second actuating device for a clutch with a variable triggering torque.
  • a second actuating device for a clutch By adjusting the second adjusting device together with the first adjusting device, the release torque of the clutch is adjusted depending on the desired torque.
  • the additional, dynamically determined tightening torque that occurs in a screwdriver according to the prior art during hard screwdriving is applied to this Caught by early release of the clutch.
  • the clutch triggers later than with a low torque.
  • the screwdriver can be designed so that approximately the same torque curves result for the hard and soft screwdriving.
  • the achievable tightening torque is predetermined by setting the triggering torque of the clutch with the second actuating device.
  • the drive is preferably switched off depending on the setting of the first actuating device.
  • the coupling has two coupling halves which can be positively connected to one another and which are urged against one another by a spring.
  • the form-fitting design of the coupling ensures reproducible triggering moments and wear-free operation.
  • the spring tension can be selected and the second actuating device can be matched to the spring tension in such a way that, for hard and soft screwdriving, largely identical torque profiles result.
  • a particularly space-saving design of the coupling is obtained when the shaft is coaxially penetrated by it.
  • the coupling halves have rolling bodies that engage in one another in a form-fitting manner.
  • a roller holder is preferably provided on the first coupling half, in which a plurality of rollers is rotatably held, and the second coupling half has a corresponding number of balls which engage in a positive manner in the spaces between the rollers.
  • the roller holder is preferably flange-shaped, and the rollers are arranged so that the axes of rotation of the rollers point radially outward. This also simplifies the construction of the clutch.
  • the gear of the screwdriver is preferably designed as a planetary gear, which enables a particularly space-saving construction.
  • a planetary gearbox enables additional use of the dynamics in hard conditions Screwdriving case to generate a higher torque when the screwdriver is adjusted accordingly. As mentioned above, this effect can be used to achieve a higher switch-off torque for a screwdriver that is not sufficiently dimensioned than for the basic setting in the case of hard screwdriving.
  • one of the two coupling halves is preferably connected in a rotationally fixed manner to a ring gear of the transmission, while the other of the two coupling halves is fixed to the housing.
  • the clutch can also be coupled to any other gearbox, provided that it only has one actuating device for presetting a torque, in which the engine is switched off and / or the shaft is separated from the gearbox drive.
  • the transmission is designed as a multi-stage planetary gear, the planetary gear having a first ring gear which is rotatably mounted and is limitedly rotatably fixed on the housing via the first actuating device, and wherein a second rotatably mounted ring gear of the planetary gear with the first coupling half is rotatably connected.
  • the second actuating device has an adjusting nut which is fixed with a thread in the housing so as to be adjustable in the axial direction in order to adjust the preload to change the spring.
  • the spring is preferably designed as a plate spring, since a plate spring enables a compact structure with high spring force.
  • the first adjusting device has a switching ring for the adjustment, which is rotatably connected to the adjusting nut for adjustment together with the second adjusting device.
  • a threaded sleeve is screwed into the housing, in which axial pins are held, which are axially displaceable for biasing the spring via an adjusting ring which is adjustably fixed on the threaded sleeve.
  • the adjusting ring can be adjusted in the axial direction without this leading to an axial movement of the shaft.
  • the adjusting ring is screwed onto a threaded connector of the threaded sleeve and is connected to the switching ring of the first adjusting device in a rotationally fixed manner.
  • the axial adjustment takes place through these measures the adjusting ring and thus the change in the preload of the spring, as well as the coupling with the first actuating device, are particularly simple.
  • the axial travel of the adjusting ring is limited on both sides, for which purpose a radial end face of the threaded sleeve is provided on the spring side and a stop ring is provided on the opposite side.
  • a radial end face of the threaded sleeve is provided on the spring side and a stop ring is provided on the opposite side.
  • the rotationally fixed connection between the adjusting ring and the switching ring can be achieved in a particularly simple manner by knurling.
  • the spring is preloaded together with an adjustment of the first actuating device and a change in the preload of the spring without adjustment of the first actuating device is only possible with additional effort (removal of the switching ring), in a further embodiment of the invention the Preload of the spring can be changed regardless of the position of the switching ring of the first actuating device.
  • This version is advantageous if a simple setting option for the screwdriver to increase the torque curve in the case of hard screwdriving is to be created for the user.
  • a spring-loaded sliding sleeve is axially displaceably arranged on the adjusting ring, which is connected in a rotationally fixed manner to the adjusting ring via driving teeth.
  • the sliding sleeve is in a rest position on the shift ring and is non-rotatably connected to it by knurling. In this position, an adjustment of the adjusting ring of the second adjusting device is only possible together with the switching ring of the first adjusting device.
  • the sliding sleeve can be retracted against the spring force from the switching ring into an adjustment position in which the knurling is not in engagement with the switching ring, so that the adjusting ring is rotated relative to the switching ring is possible.
  • a device for limiting the adjustment angle of the sliding sleeve relative to the switching ring.
  • a coding disk can be fixed to the switching ring, which has a slotted guide in the form of a segment into which a cam of the sliding sleeve engages to limit the adjustment angle.
  • the planetary gear 1 is designed as a hand tool, which is driven in a known manner by a drive motor via a two-stage planetary gear according to DE 37 42 952 A1.
  • the planetary gear has a first gear stage, the sun gear of which is formed by the motor pinion.
  • the motor pinion drives planet wheels arranged around it, which are rotatably mounted on a planet carrier which is arranged coaxially to the axis of rotation of the motor shaft.
  • the planet gears engage with their teeth on the one hand in the motor pinion and on the other hand are supported in the internal toothing of a first ring gear which is rotatably mounted.
  • the first gear stage is coupled via the planet carrier to the second gear stage, from the planet carrier of which the shaft 20 is driven.
  • the second gear stage has a ring gear 27 which, contrary to the previously known embodiment, is not fixed in terms of rotation on the housing 1, but is connected in a rotationally fixed manner to a first coupling half 48 of a coupling described below, designated as a whole as 29, the second coupling half 49 fixed to the housing 1 is.
  • the ring gear of the first stage of the gearbox is rotatably mounted and held by a swivel lever, the pretensioning of which can be adjusted via a torsion bar.
  • the prestressing of the torsion bar can be adjusted via a switching ring 18 in connection with an adjusting sleeve 46 and a link ring 44, which are indicated in FIG. 2.
  • there is a known bias of the torsion bar which leads to a shutdown of the engine via a rotation of the shift fork by the counter-torque acting on the first ring gear when a certain torque is reached.
  • the first actuating device designated as a whole by the number 28, by means of which the prestress acting on the shift fork via the torsion bar can be adjusted is only partially indicated in the drawings. Also, only the second ring gear 27 of the transmission 2 is shown, which is connected to the clutch 29 according to the invention.
  • the shaft 20 driven by the planet gear carrier of the second gear stage is provided for driving a screw head, which is indicated in FIGS. 2 and 3 by a bit receptacle 45, into which the screw head can be inserted with a correspondingly shaped insert part.
  • the second ring gear 27 is supported by an injected bearing bush 4 on the shaft 20, which in turn is slidably mounted in a flange-shaped roller holder 5.
  • the roller holder 5 is connected in a rotationally fixed manner to the ring gear 27 by means of an annular section 60 on the gearbox side via two axial pins 3 and is held in its central region in an annular web 59 of the housing 1.
  • the roller holder 5 has an end face on which, as can be seen from the view according to FIG. 1b, six radial grooves 26 are provided in the radial direction for receiving rollers 6, which are separated from one another by triangular webs 25 are separated.
  • the axes of rotation 47 of the rollers 6 point radially outwards and are each offset by 60 °.
  • the rollers 6 are guided in the grooves 26 on their side facing the shaft 20 and are supported on their outside on a support disk 7, which rests on the side of the ring web 59 of the housing 1 facing away from the gear 2.
  • a pressure disc 8 adjoins the roller holder 5, the shape of which can be seen from the view according to FIG. 1a.
  • the thrust washer 8 has three grooves 23, each offset by 120 ° from one another, into which grub screws 19 radially screwed into the housing 1 engage in order to lock the thrust washer 8 in a rotationally fixed manner.
  • six bores 22, each offset by 60 °, are provided, in which balls 9 are held, which engage in a positive manner in the spaces between the rollers 6.
  • the diameter of the rollers 6 is dimensioned so that the rollers act as a thrust bearing between the support disk 7 and the thrust washer 8.
  • the balls 9 are held on their side facing away from the roller holder 5 on an axial disk 10 which is acted upon by a spring 11 designed as a plate spring in the direction of the rollers 6.
  • the spring 11 rests on the transmission side against the axial disk 10 and rests with its other end against the end face of an adjusting nut 15 which is screwed into the housing 1 with a thread 14.
  • a bearing bush 16 is provided, which is fixed on the transmission side via a circlip 12, abuts on a shoulder 17 of the shaft 20 at its opposite end facing away from the transmission and is held in a central bore of the adjusting nut 15.
  • the switching ring 18 of the first actuating device which is indicated only as a whole by the number 28, surrounds the adjusting nut 15 at its end facing away from the transmission 2 and is connected to it via a Knurling 21 non-rotatably connected.
  • the preload of the spring 11 can be adjusted by turning the adjusting nut 15 in the housing 1. Depending on the set bias, the spring 11 is compressed so far when a certain limit torque M is reached that the balls 9 move out of their position between the rollers 6 into the next space.
  • the bias of the spring 11 is also increased when the switch-off torque of the first actuating device is increased, which leads to an approximately linear torque curve over the entire adjustment range of the actuating device 28 results. Likewise, there is an almost identical torque curve regardless of whether there is a hard or soft tightening case.
  • the pretension of the spring 11 can be adjusted independently of the angular position of the switching ring 18.
  • the coupling 29 only responds to a higher tightening torque in the case of hard screwdriving.
  • the angular momentum of the gearbox is used to increase the shutdown torque in the case of hard screwdriving.
  • the screwdriver can thus be set so that this undesired effect is specifically brought about in a screwdriver according to the prior art, in order to achieve a higher torque curve in the case of hard screwdriving. This can be useful in order to use a screwdriver that is not sufficiently dimensioned for a specific screwdriving in exceptional cases to achieve a higher torque in the hard screwdriving case.
  • Fig. 2 shows a slightly modified embodiment of a screwdriver according to the invention, in which the bias of the spring 11 is adjustable by displacement of axial pins 36.
  • the thrust washer 8 is connected to the housing 1 via two parallel keys 30.
  • the spring 11 bears on the transmission side against an axial disk 33 and on the opposite side against an axial disk 31.
  • the axial disk 31 is in turn supported on a threaded sleeve 34, which is screwed into the housing 1 and has longitudinal slots 32 at its end on the transmission side, in which the feather key 30 engages.
  • the threaded sleeve 34 is screwed into the housing 1 with its external thread 35 and can be locked in a rotationally fixed manner in the positions in which the longitudinal slots 32 are aligned with the feather key 30.
  • the preload of the spring 11 can be increased by advancing the axial disk 31 via a total of three axial pins 36 acting thereon.
  • the axial pins 36 are guided displaceably in the bores of the threaded sleeve 34 and lie on their side facing away from the spring against an adjusting ring 40 which is adjustable in the axial direction on a threaded connector 38 of the threaded sleeve 34.
  • the axial travel of the adjusting ring 40 is limited on the spring side by an end face 57 of the threaded sleeve 34 and on the opposite side by a stop ring 41 which is held on the threaded sleeve 34 at the end of the threaded connector 38.
  • the adjusting ring 40 is connected in a rotationally fixed manner to the switching ring 18 of the first adjusting device 28 via a knurling 39.
  • the pretension of the spring 11 is changed at the same time.
  • the bias of the spring 11 is set in the manner described above so that the coupling 29 does not respond in the case of soft screwing and the motor is switched off when the tightening torque is reached via the first actuating device.
  • the coupling 29 triggers in hard screwing when the preset torque is reached by giving in the spring 11, so that the balls 9 move back from the rollers 6 until they engage in the next space between the rollers.
  • the shaft 20 is supported on both sides similar to the embodiment according to FIG. 1.
  • the shaft On the transmission side, the shaft is held by the bearing bush 4, which is injected into the planet carrier of the second transmission stage.
  • a bearing bush 16 is provided, which is on the transmission side through a snap ring 12 is fixed and is held on its opposite side by balls 37 which abut a correspondingly shaped collar 42 of the shaft 20.
  • the bearing bush 16 is held in a central bore of the threaded sleeve 34.
  • an O-ring 43 is arranged in a correspondingly shaped annular groove of the shaft between the shaft 20 and the threaded sleeve 34.
  • the screwdriver which is otherwise the same as the embodiment according to FIG. 2 is modified in such a way that an additional sliding sleeve is provided in front of the switching ring 18, via which the preload of the spring 11 can be changed independently of the position of the switching ring 18 .
  • Such an arrangement is useful if the user is to be given the opportunity to achieve a later response of the clutch by a corresponding increase in the preload of the spring in the case of hard screwdriving, so that a switch-off only takes place at a higher tightening torque. wherein the angular momentum of the transmission is used and thus a higher torque results, which leads to a correspondingly increased torque curve (see curve C in FIG. 5).
  • the axial pins 36 can be displaced in a manner corresponding to the embodiment according to FIG. 2 by rotating the adjusting ring 50 on the threaded connector 38 of the threaded sleeve 34 in the direction of the spring 11 in order to increase its pretension.
  • the adjusting ring 50 is somewhat widened compared to the previously described embodiment and has on its outer surface a driving toothing 54 in which the sliding sleeve 52 engages, so that the latter can be displaced in the axial direction but at the same time a rotationally fixed connection between the sliding sleeve 52 and the adjusting ring 50 is ensured .
  • the sliding sleeve 52 is urged in the direction of the switching ring 18 by a spring 51, which is supported on its outer end facing away from the transmission on a snap ring 53.
  • the sliding sleeve 52 therefore bears against the switching ring 18 in the normal case.
  • the sliding sleeve 52 is positively connected to it via a knurling 39 which engages in a corresponding central knurling of the switching ring (18), so that a non-rotatable connection of the switching ring 18 with the adjusting ring 50 is produced.
  • the sliding sleeve 52 can slide back into the rest position under the action of the spring 51 until the knurling 39 is engaged again and the sliding sleeve bears against the switching ring 18.
  • a coding disk 55 is fixed on the switching ring 18, which according to FIG. 4 has a sliding block guide 58 in the form of a segment, into which a cam 56 of the sliding sleeve 52 engages.
  • the torque curves of a screwdriver according to the invention according to FIG. 1, 2 or 3 are shown schematically as a function of the scale setting of the first actuating device.
  • the tightening torque is given in Newton meters on the ordinate, while the scale setting of the first actuating device is plotted on the abscissa, which corresponds to a respective angular position of the link ring of the first actuating device and thus to a specific preload of the torsion bar for switching off the engine via the shift fork.
  • Curve A shows the torque curve for soft screwdriving.
  • Curve B shows the torque curve in the case of hard screwing and relatively low preload of the spring 11 (normal case). In the screwdriver according to the invention, therefore, an approximately identical torque curve results regardless of the size of the re-rotation angle for hard and soft screwdriving.
  • the torque curves of a screwdriver according to the prior art are represented by curves I for the soft screwing case and II for the hard screwing case.
  • the structure of the screwdriver corresponds entirely to the screwdriver according to the invention except for the coupling according to the invention.
  • the torque profiles for the soft screwdriving case of the screwdriver according to the invention curve A
  • the screwdriver according to the prior art curve I
  • the state of the art results overall in a strongly raised torque curve for hard screwdriving. It is not possible to adjust the conventional screwdriver to a torque curve that approximates the soft screwdriving case.
  • the screwdriver according to the invention results in the same tightening torque as the conventional screwdriver in the case of hard screwdriving, since in this case the switch-off is only specified by the first actuating device, with the angular momentum being fully utilized.

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

Claims (20)

  1. Visseuse à réglage variable du couple de rotation, en particulier visseuse avec arrêt par le couple de rotation, avec un arbre (20) entraîné par un moteur par l'intermédiaire d'un engrenage (2) pour l'entraînement d'un outil, avec un dispositif de réglage (28) pour le réglage préalable d'un couple de rotation auquel le moteur est arrêté, caractérisée en ce qu'indépendamment de ces éléments, il est prévu un accouplement de séparation (29) à couple de déclenchement variable, et en ce qu'il est prévu pour le réglage du deuxième couple de déclenchement un deuxième dispositif de réglage (13) qui est réglable en même temps que le premier dispositif de réglage (28).
  2. Visseuse selon la revendication 1, caractérisée en ce que l'accouplement (29) présente deux moitiés d'accouplement (48, 49) pouvant être liées entre elles par engagement positif, qui sont poussées l'une contre l'autre par un ressort (11).
  3. Visseuse selon la revendication 1 ou 2, caractérisée en ce que l'accouplement (29) est traversé de façon coaxiale par l'arbre (20).
  4. Visseuse selon l'une quelconque des revendications précédentes, caractérisée en ce que les moitiés d'accouplement (48, 49) présentent des roulements (6, 9) qui se mettent en prise l'un dans l'autre par engagement positif.
  5. Visseuse selon la revendication 4, caractérisée en ce que la première moitié d'accouplement (48) présente un logement de rouleaux (5), dans lequel une pluralité de rouleaux (6) sont maintenus avec possibilité de rotation, et la deuxième moitié d'accouplement (49) présente un nombre correspondant de billes (9), qui se mettent en prise par engagement positif dans les espaces compris entre les rouleaux (6).
  6. Visseuse selon la revendication 5, caractérisée en ce que le logement de rouleaux (5) est de préférence réalisé sous la forme d'une bride, et en ce que les axes de rotation (47) des rouleaux (6) sont orientés dans le sens radial vers l'extérieur.
  7. Visseuse selon l'une quelconque des revendications précédentes, caractérisée en ce que l'engrenage (2) est réalisé comme un engrenage à train planétaire.
  8. Visseuse selon la revendication 7, caractérisée en ce que l'une (48) des deux moitiés d'accouplement est liée de manière solidaire en rotation à une roue creuse de l'engrenage (2), et en ce que l'autre moitié d'accouplement (49) est fixée au carter (1).
  9. Visseuse selon la revendication 8, caractérisée en ce que l'engrenage (2) est réalisé comme un engrenage à train planétaire à plusieurs étages, en ce que l'engrenage à train planétaire présente une première roue creuse montée avec possibilité de rotation et liée au carter (1) avec possibilité de rotation limitée en fonction du couple de rotation par le premier dispositif de réglage (28), et en ce que l'engrenage à train planétaire présente une deuxième roue creuse (27) montée avec possibilité de rotation, qui est liée de manière solidaire en rotation à la première moitié d'accouplement.
  10. Visseuse selon l'une quelconque des revendications précédentes, caractérisée en ce que le deuxième dispositif de réglage (13) présente un écrou de réglage (15), qui est fixé par un filet (14) dans le carter (1) de façon réglable dans le sens axial, afin de modifier la précontrainte du ressort (11).
  11. Visseuse selon la revendication 10, caractérisée en ce que le premier dispositif de réglage (28) présente pour le réglage une bague de commande (18) qui est liée de manière solidaire en rotation à l'écrou de réglage (15), en vue du réglage commun avec le deuxième dispositif de réglage (13).
  12. Visseuse selon l'une quelconque des revendications 1 à 11, caractérisée en ce qu'il est prévu une douille filetée (34), qui est vissée dans le carter (1), en ce que des goupilles axiales (36) sont maintenues dans la douille filetée (34) et peuvent être déplacées dans le sens axial pour la précontrainte du ressort (11) par l'intermédiaire d'une bague de réglage (40, 50) fixée en position réglable sur la douille filetée (34).
  13. Visseuse selon la revendication 12, caractérisée en ce que la bague de réglage (40, 50) est vissée sur un manchon fileté (39) de la douille filetée (34) et liée de manière solidaire en rotation à la bague de commande (18) du premier dispositif de réglage (28).
  14. Visseuse selon la revendication 13, caractérisée en ce que la course de réglage axial de la bague de réglage (40, 50) est limitée des deux côtés.
  15. Visseuse selon la revendication 14, caractérisée en ce que la course de réglage axial de la bague de réglage (40, 50) est limitée du côté du ressort par une face (57) radiale de la douille filetée (34) et sur le côté opposé par une bague de butée (41, 53).
  16. Visseuse selon la revendication 15, caractérisée en ce que la bague de réglage (40) et la bague de commande (18) sont liées de manière solidaire en rotation par un moletage (39).
  17. Visseuse selon l'une quelconque des revendications 12 à 15, caractérisée en ce qu'une douille coulissante (52) chargée par ressort est disposée de façon coulissante dans le sens axial sur la bague de réglage (50) et liée de manière solidaire en rotation à la bague de réglage (50) par l'intermédiaire d'une denture d'entraînement (54), en ce que la douille coulissante (52) s'appuie dans une position de repos sur la bague de commande (18) et est liée de manière solidaire en rotation avec celle-ci par un moletage (39), et en ce que la douille coulissante (52) peut être retirée contre la force de ressort de la bague de commande (18) dans une position de réglage dans laquelle le moletage (39) n'est pas en prise avec la bague de commande (18), de sorte qu'une rotation de la bague de réglage (50) par rapport à la bague de commande (18) est possible.
  18. Visseuse selon la revendication 17, caractérisée en ce qu'il est prévu un dispositif (55, 56, 58) pour limiter l'angle de déplacement de la douille coulissante (52) par rapport à la bague de commande (18).
  19. Visseuse selon la revendication 18, caractérisée en ce qu'une rondelle de codage (55) présentant un guide à coulisse (58) en forme de segment de cercle, dans lequel une came (56) de la douille coulissante (52) se met en prise pour limiter l'angle de réglage, est fixée à la bague de commande (18).
  20. Visseuse selon l'une quelconque des revendications précédentes, caractérisée en ce que le ressort (11) est conformé en rondelle-ressort.
EP92111307A 1991-07-15 1992-07-03 Outil de vissage avec réglage du couple variable Expired - Lifetime EP0523477B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4123349A DE4123349C1 (de) 1991-07-15 1991-07-15 Schrauber mit variabler Drehmomenteinstellung
DE4123349 1991-07-15

Publications (2)

Publication Number Publication Date
EP0523477A1 EP0523477A1 (fr) 1993-01-20
EP0523477B1 true EP0523477B1 (fr) 1995-10-25

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EP92111307A Expired - Lifetime EP0523477B1 (fr) 1991-07-15 1992-07-03 Outil de vissage avec réglage du couple variable

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US (1) US5356350A (fr)
EP (1) EP0523477B1 (fr)
JP (1) JPH05208380A (fr)
DE (2) DE4123349C1 (fr)

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EP0523477A1 (fr) 1993-01-20
US5356350A (en) 1994-10-18
DE59204104D1 (de) 1995-11-30
JPH05208380A (ja) 1993-08-20
DE4123349C1 (de) 1993-03-04

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