EP1258321B1 - Tournevis motorisé avec embrayage limitateur de couple - Google Patents

Tournevis motorisé avec embrayage limitateur de couple Download PDF

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Publication number
EP1258321B1
EP1258321B1 EP02010510A EP02010510A EP1258321B1 EP 1258321 B1 EP1258321 B1 EP 1258321B1 EP 02010510 A EP02010510 A EP 02010510A EP 02010510 A EP02010510 A EP 02010510A EP 1258321 B1 EP1258321 B1 EP 1258321B1
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EP
European Patent Office
Prior art keywords
screw driver
coupling part
coupling
rotation
torque
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
EP02010510A
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German (de)
English (en)
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EP1258321A3 (fr
EP1258321A2 (fr
Inventor
Holger Listl
Klaus Schmitz
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
Original Assignee
C&E Fein GmbH and Co
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Publication date
Application filed by C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP1258321A2 publication Critical patent/EP1258321A2/fr
Publication of EP1258321A3 publication Critical patent/EP1258321A3/fr
Application granted granted Critical
Publication of EP1258321B1 publication Critical patent/EP1258321B1/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
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings

Definitions

  • the invention relates to a power-driven screwdriver for screwing and loosening of screws, having a torque-dependent triggering torque limiting clutch having a first coupling part, a second coupling part, a spring element for axial clamping of the first coupling part against the second coupling part and at least one rolling element running between the two coupling parts , in which the two coupling parts are coupled together in a drive of the screwdriver in a first direction of rotation (working direction) until reaching a preset triggering torque.
  • Such a screwdriver is from the WO 99/16885 known.
  • Power-driven screwdrivers for screwing in and loosening screws have increasingly replaced conventional manual screwdrivers in the past.
  • power-driven screwdrivers are used with a torque-dependent triggering torque limiting clutch, since there screws are usually screwed with well-defined torques.
  • torque-dependent triggering torque limiting clutch since there screws are usually screwed with well-defined torques.
  • Under screws are understood in the broadest sense, all types of threaded fasteners, ie in particular also nuts.
  • Torque limiting clutches are placed in a drive train between a driver of the screwdriver and a tool holder.
  • the torque limiting clutch breaks the connection between the drive and the tool holder as soon as a screwed-in screw is clamped with the desired force in a screw-receiving thread.
  • the torque with which the drive of the screwdriver then acts on the stuck screw is called the tripping torque and can usually be set on the torque limiting clutch. So that the drive does not idle after loosening the torque limiting clutch, the torque limiting clutch usually acts on an additional switch, upon actuation of the drive is turned off.
  • a power screwdriver known whose torque limiting clutch comprises two with the aid of a compression spring against each other braced clutch discs.
  • the clutch discs have serrations whose teeth each have two differently inclined flanks. When the triggering torque is exceeded, the two serrations slide apart on the less inclined flanks against the action of the compression spring and finally disengage, whereby the torque limiting clutch opens. When loosening a screw is given by the spring tension and the edge slope release torque higher than when screwing, since the flanks are then steeper.
  • this known torque limiting clutch has a relatively short service life, as act on the teeth of the serrations when opening and closing the torque limiting clutch large shear forces that gradually lead to a removal of the tooth edges.
  • a screwdriver whose torque-dependent triggering torque limiting clutch is not arranged between two sections of a drive spindle, but between a housing of the screwdriver and a ring gear of a planetary gear.
  • the ring gear receives a reaction torque of the planetary gear relative to the drive spindle and is rotatably received in the housing.
  • the torque limiting clutch on an axially displaceable ring gear, which is braced against the ring gear by means of a compression spring.
  • On one of the ring gear facing end face of the ring gear three recesses are formed, in which balls are held captive.
  • On the ring gear itself is on the ring gear facing a tread formed on the three cams are arranged at equal angular intervals.
  • Torque limiting clutches in which the torque transmitting surfaces of coupling parts are coupled together via balls are subject to less wear than torque limiting clutches in which these surfaces slide directly on each other.
  • a disadvantage of torque limiting clutches with balls is that when loosening screws often either no sufficiently large torque is available or an increased wear of the torque limiting clutch must be taken into account. Indeed, if a different determination of the maximum transmittable torques using asymmetric trained cam coupling parts, this always leads to the fact that the balls when screwing a screw while "relatively slow” when loosening the torque limiting clutch on the run slightly inclined run-up edge of the cam, but then due to the steeper trailing edge of the cam more suddenly roll down again or, even worse, slide down. The resulting impact leads to signs of wear on the rolling elements and possibly also on the formed on the coupling parts cams.
  • latching here also means producing any positive connection understood between the two coupling parts.
  • the locking elements of the coupling parts surface in abutment, so that can be transferred without deformation and larger torques between the coupling parts.
  • the locking of the two coupling parts can be made so that they only manually, ie, for example by a caused by an operator relative movement between the two coupling parts, can be canceled again.
  • latching can be canceled by reversing the direction of rotation of the screwdriver.
  • the latch is so automatically canceled when the direction of rotation is reversed after loosening a screw to screw in a screw.
  • the locking is retained, so that as many screws in a row can be solved without additional coupling movements.
  • Such automatic release of the latching can be achieved, for example, that the locking elements come into contact only in one direction and can move away from each other when reversing the direction of rotation.
  • mutually associated sliding surfaces are formed at mutually facing end faces of the two coupling parts, via which the two coupling parts abut each other at predetermined relative angular positions.
  • the at least one rolling element is fully or at least partially relieved at certain angular positions, whereby the wear is further reduced.
  • These particular angular positions preferably comprise at least those in which the coupling between the two coupling parts does not take place via the at least one rolling body. The forces that then act between the coupling parts, then essentially only go back to the spring element, so that the at least one rolling element is little or possibly not charged at all.
  • this measure makes it possible to form the locking elements on the sliding surfaces.
  • the at least one rolling element and regions of the coupling parts on which the rolling body runs are thus not influenced by the design of the locking elements.
  • the sliding surface of a coupling part is formed by an end face and axially protruding projections thereof.
  • the sliding surface of the other coupling part is formed by steps, which are each limited by paragraphs on which the projections can strike in the second direction of rotation.
  • a circumferentially extending cam track is formed on the second coupling part, which is composed of a plurality, preferably three, identically designed track sections.
  • the coupling behavior of the torque limiting clutch can be influenced in a structurally simple manner by the formation of the cam track.
  • the cam track is arranged outside and concentric with the sliding surface of the second coupling part.
  • An outer cam track allows a relatively large radius of movement for the rolling elements and thus a favorable leverage for the torque transfer via the rolling elements.
  • each track section has a cam whose flanks form a casserole side and a discharge side for the at least one rolling element. It is particularly preferred if the run-up side is steeper than the discharge side.
  • the inclination of the discharge side becomes smaller with increasing distance from the casserole side.
  • the cam track between the cams in each case has a partial section which is not touched by the at least one rolling element.
  • the sliding surfaces are arranged to the cam track, that in a drive of the screwdriver in the first direction of rotation (working direction) and closed torque limiting clutch the at least one rolling element is in abutment with the casserole side of a cam and at the same time the first coupling part is supported on the second coupling part in the axial direction over the sliding surfaces.
  • the at least one rolling element can be, for example, a free-running ball or a ball received in a recess, as is known from the prior art.
  • the at least one rolling element is designed as a roller.
  • the roll may e.g. be guided in a hollow cylindrical recess which is formed on the end face of one of the two coupling parts.
  • the roller is rotatably mounted on an axis held on the first coupling part axis.
  • the bearing formed on the axle may be e.g. be designed as a needle bearing, which allows high loads with low friction values.
  • the axis of rotation defined by the axis of the roller is arranged at a distance from a longitudinal axis of the first coupling part.
  • the axis of rotation of the roller thus does not extend through a radius of the first coupling part, but at an angle thereto. Accordingly, the direction of the roller is not tangential, but set at an angle to the tangent. As a result, in one of the two possible directions of rotation, which is preferably the working direction, the roller carries out a self-centering movement. Therefore, the roller does not move when rolling outward and thus can not dig into surrounding housing parts.
  • roller is mounted on the axis flying.
  • This flying bearing which is made possible by the self-centering of the roller due to the not extending through the longitudinal axis of the first coupling part axis of rotation, simplifies the storage of the roller on the axis and reduces the size, since fasteners omitted.
  • the reaction part is a ring gear of a planetary gear which receives a plurality of planetary gears.
  • planetary gearboxes Due to their distribution of forces, planetary gearboxes are particularly reliable and long-lasting, making them particularly suitable for power-driven screwdrivers in the commercial sector.
  • the coupling part rotatably connected to the housing of the screwdriver is arranged to be displaceable in the axial direction.
  • a switch is provided for switching off the screwdriver, which is actuated by the axially displaceable arranged in the coupling part.
  • an inventive screwdriver is shown in a side view and generally designated 10.
  • the screwdriver 10 has a housing 11 with a main housing part 12 on which a handle portion 16 is formed. From there, a main switch 18 is conveniently operated by an operator.
  • a main switch 18 is conveniently operated by an operator.
  • an angle head housing 19 of an angle head 20 is rotatably mounted, from which a tool holder 22 protrudes at right angles to a longitudinal axis of the screwdriver 10.
  • Such screwdrivers are commonly referred to as rod angle screwdriver and have the advantage over conventional power screwdrivers that the torque absorbed by the screwdriver when screwing not to twist the screwdriver about its longitudinal axis, but to a pivoting of the screw to the right angle, through the Tool holder 22 fixed axis leads. Such pivotal movements can be more easily absorbed by an operator than rotations of the screwdriver about its longitudinal axis.
  • a rotary ring 28 is arranged rotatable relative to the main housing part 12. Slots 30 inserted therein, of which only the one facing the observer can be seen in FIG. 1, a tool can be introduced into the screwdriver 10, with which the tripping torque of the screwdriver 10 can be adjusted in a manner to be explained in more detail.
  • Fig. 2 shows a part of the screwdriver 10 shown in Fig. 1 with partially removed housing parts. The recognizable through the housing opening parts of the screwdriver 10 are indicated only schematically.
  • the screwdriver 10 has an example designed as an electric motor drive 32 which is rotatably attached to a fixed relative to the main housing part 12 support sleeve 34.
  • the drive 32 drives via an intermediate shaft 36 to a reduction gear in the form of a planetary gear 38, which on the output side, a spindle 40 is rotated.
  • the spindle 40 drives a tool spindle 44 via a bevel gear arrangement 46 arranged in the angle head 20, which tool holder carries the tool holder 22 at its free end.
  • a torque limiting clutch 50 is shown schematically in Fig. 2, which couples a reaction torque with respect to the spindle 40 receiving reaction part of the planetary gear 38 with a control sleeve 52.
  • the adjusting sleeve 52 is integrally formed with an angle head housing 19 or rotatably connected via one or more intermediate parts with this.
  • the entire angle head 20, i. the angle head housing 19 with bearings 55 and 56 accommodated therein for the spindles 40 and 44 and the adjusting sleeve 52, relative to the support sleeve 34 fixed to the housing are rotated along an adjusting device 58 designed here as a screw connection.
  • the torque limiting clutch 50 is closed, the reaction part of the planetary gear 38 is fixed against rotation relative to the angle head 20 and coupled to the drive 32 via the adjusting device 58.
  • the spindle 40 is blocked by a tightly tightened screw, so that the torque generated by the drive 32 must be completely absorbed by the housing parts of the angle wrench 10.
  • On the intermediate shaft 36 between the drive 32 and the planetary gear 38 then acts the torque generated by the drive 32.
  • a corresponding counter-torque of the same size is - taken from the housing parts, namely the carrier sleeve 34 and the adjusting sleeve 52 - when assumed as closed torque limiting clutch 50.
  • This torque is smaller by the reduction factor of the planetary gear 38 than the torque acting between the planetary gear 38 and the angle head housing 19.
  • the adjustment device 58 can therefore be designed as a simple screw connection, which may have an additional locking mechanism. For reasons of torque transmission, however, such a locking mechanism is not required. If, nevertheless, such a known locking mechanism is desired, it may also be very simple and easy to construct, since it only needs to absorb small torques.
  • FIG. 3 shows in an axial section details of parts shown only schematically in FIG. 2 in the interior of the screwdriver 10.
  • An intermediate shaft 62 which is formed integrally with a first sun gear 64 of the two-stage planetary gear 38, is pushed in a rotationally fixed manner onto a rotor socket 60 of the drive 32, which is hexagonal in cross-section, of the drive 32 only indicated in FIG.
  • the first sun gear 64 meshes with three first planetary gears 66 of a first planetary gear stage, of which only two can be seen in FIG.
  • the first planetary gears 66 are rotatably mounted on a first planet carrier 68 and mesh simultaneously with a ring gear 70 which extends over the entire axial length of the planetary gear 38.
  • the first planet carrier 68 is integrally formed with a second sun gear 72 or rotatably connected, which meshes with second planetary gears 74.
  • the second planet gears 74 are in turn rotatably mounted on a second planet carrier 76 and also mesh with the ring gear 70.
  • the stub 80 and the driving wheel 84 together form a further below with reference to FIG. 4 explained in more detail game coupling 86th
  • the ring gear 70 which takes over the intermediate shaft 62 and the spindle 40, a reaction torque and thus the reaction part represents the planetary gear 38 is rotatably received in the screwed to the drive 32 support sleeve 34 and the adjusting device 58 connected thereto adjusting sleeve 52 via a bearing 88.
  • the ring gear 70 is fixed to the adjusting sleeve 52 (or a part rotatably connected thereto) via the torque limiting clutch 50.
  • This comprises a rotatably screwed into the ring gear 70 cam ring 90, which projects beyond the ring gear 70 shoulder 92 is also supported on the bearing 88 on the adjusting sleeve 52, and a switching ring 96 which is clamped by a compression spring 94 against the cam ring 90.
  • the switching ring 96 is axially, ie in the longitudinal direction 95 of the spindle 40, slidably, but rotatably received in a connected to the adjusting sleeve 52 intermediate sleeve 98.
  • the rotationally fixed, but axially displaceable arrangement of the switching ring 96 is achieved by means of first and second longitudinal grooves 100 which are arranged on a peripheral surface of the switching ring 96 and the inside of the intermediate sleeve 98 and cooperate with guide balls 102.
  • first and second longitudinal grooves 100 which are arranged on a peripheral surface of the switching ring 96 and the inside of the intermediate sleeve 98 and cooperate with guide balls 102.
  • the switching ring 96 and the intermediate sleeve 98 can be moved to each other in the axial direction, wherein a snap ring inserted into the intermediate sleeve 98 105 prevents falling out of the guide balls 102.
  • rollers 104 are rotatably mounted on axles 106 circumferentially.
  • the rollers 104 can roll on a cam track 108, which is formed on a switching ring 96 facing the end face of the cam ring 90.
  • Projections 109 formed whose function will be explained in more detail with reference to FIGS. 5 to 10.
  • the compression spring 94 is supported on a clamping plate 110, which is accommodated in the intermediate sleeve 98 so as to be displaceable in the axial direction.
  • a clamping plate 110 On the clamping disk 110 four circumferentially uniformly distributed clamping bolts 112 act, which are guided in holes 114 which are mounted in a shoulder of the intermediate sleeve 98, and supported on a collar 116.
  • the adjusting ring 116 can be displaced by turning on a threaded portion 118 applied externally to the intermediate sleeve 98 in the longitudinal direction 95.
  • a longitudinal displacement of the adjusting ring 116 on the threaded portion 118 of the intermediate sleeve 98 is transmitted via the clamping bolt 112 and the clamping disk 110 to the compression spring 94, so that in this way the bias between the switching ring 96 and the cam ring 90 can be changed.
  • a tool e.g. a screwdriver
  • the collar 116 can be rotated together with the rotary ring 28 until the desired tension of the Compressive spring 94 and thus the triggering torque of the torque limiting clutch 50 is reached.
  • the rollers 104 are formed on the cam track 108 cams such that the force exerted on the ring gear 70 reaction torque on the cam, the rollers 104 and the switching ring 96 on the intermediate sleeve 98 and thereby on the rotatably associated adjusting sleeve 52 is transmitted, so that the ring gear 70 during the screwing a screw rests.
  • the torque acting on the cam ring 90 increases until, finally, the cam ring 90 begins to rotate, lifting the rollers 104 and thus the switching ring 96 counter to the force of the compression spring 94 with its cams.
  • this Upon further rotation of the cam ring this runs with its cams under the rollers 104 away, so that the rollers 104 with the switching ring 96 finally lower again under the pressure of the compression spring 94.
  • the planetary gear 38 is no longer fixed against rotation, so that the torque exerted by the drive 32 on the spindle 40 is reduced to virtually zero.
  • a switch 124 which protrudes through the intermediate sleeve 98 in a above the switching ring 96 remaining space 128.
  • the switch 124 interrupts the power supply for the drive 32 and thus ensures that after exceeding the triggering torque of the cam ring 90 does not turn away repeatedly under the switching ring 96.
  • the play clutch 86 between the output of the planetary gear 38 and the spindle 40 is shown in perspective.
  • the game clutch includes the three ports 80, the of the planetary gear axles 82 passing through the second planet carrier 76 are formed, and the follower wheel 84 is rotatably guided in a central recess of the second planet carrier 76.
  • the entrainment wheel 84 has a central, executed as a hexagon socket passage 130, in the assembled state, an end of the cross-sectionally also hexagonal spindle 40 is inserted. From the center of the entraining wheel 84, three wings 132 extend radially outward, and indeed so far that they can get into contact with the nozzle 80.
  • the connecting pieces 80 with the second planet carrier 76 receiving them rotate about the longitudinal axis 95 of the spindle 40 and act on the wings 132 of the carrier wheel 84. In this way, guided in the entrainment wheel 84 spindle 40 is coupled to the output of the planetary gear 38.
  • Fig. 5 shows the switching ring 96 in a perspective view.
  • the switching ring 96 is divided into three sections 136, 138 and 140 of different diameters. At first Section 136 with the largest diameter are distributed on the circumference of the longitudinal grooves 100 at equal angular intervals. About these longitudinal grooves 100 of the switching ring 96 is slidably held in the axial direction, but rotatably held by means of the guide balls 102 on the intermediate sleeve 98. The first section 136 is followed by the second section 138 and the third section 140 thereafter.
  • This third section 140 is peripherally provided with three holes 142 which serve to receive the axes 106 and of which in Fig. 5, only the viewer facing hole can be seen.
  • the mouth of the bores 142 surrounding portion of the second portion 138 and the third portion 140 is just milled to create a contact surface for the rollers 104.
  • end face 143 of the switching ring 96 On the mounted in the mounted state to the cam ring 90 end face 143 of the switching ring 96 is a flat end surface 144, which forms a sliding surface of the switching ring 96. From the end face 144 are the three projections 109, which also form sliding surfaces of the switching ring 96. Through the entire switching ring 96 extends centrally a bore 148 through which the spindle 40 rotates freely in the mounted state.
  • FIG. 6 shows a plan view of the end face 143 of the switching ring 96 shown in FIG. 5.
  • rollers 104 fastened to the switching ring 96 are also shown.
  • the longitudinal grooves 100 and the projections 109 can be seen.
  • Dashed lines indicate the axes of rotation 152 of the rollers 104 which are predetermined by the position of the axes 106.
  • the axes of rotation 152 extend at a distance from that perpendicular to the end surface 144 Longitudinal axis of the switching ring 96.
  • the axes of rotation 152 therefore do not meet at a common point on this longitudinal axis, but are each offset to a radius connecting the circumference and the longitudinal axis.
  • FIG. 7 shows a vectorial decomposition of the running direction 160 into a tangential movement component 163 and a radially inwardly directed movement component 164.
  • the tangential movement component 163 corresponds to the running direction of a roller whose axis is not at a distance from the longitudinal axis 154 but through it runs. In such a direction, therefore, no radial movement component would be present.
  • the distance 156 between the axis of rotation 152 and the longitudinal axis 154 and thus also the radially inward movement component 164 is different from zero, which leads to a self-centering of the rollers 104.
  • the inward movement component 164 effects with others Words that the rollers 104 when the cam ring 90 moves away from them, not or only slightly migrate radially outward and thus do not dig into the surrounding support sleeve 34. Therefore, the rollers 104 can be stored without additional means for fixing flying on the axles 106. At the same time, signs of wear on the rollers 104 and the surrounding carrier sleeve 34 are reduced and a reliable function ensured, since problems caused by friction are avoided.
  • the cam ring 90 is shown in a perspective view or in a plan view of an in the assembled state to the switching ring 96 facing front side 165.
  • an external thread 166 is first visible, with which the cam ring 90 is screwed into the ring gear 70.
  • On the outer cam track 108 three cams 168 are formed, each having a steeper casserole side 170 and a flatter running drain side 172.
  • the cam track 108 is thus composed of three identically formed track sections, the boundaries of which are naturally determined arbitrarily due to the periodic arrangement. In Fig. 9, these limits are set so that they coincide with the 168 facing away from the ends of the casserole sides 170 and thereby form a first, a second and a third track section 176, 178 and 180, respectively.
  • the cam track 108 encloses three spaced-apart steps 184 which are bounded on one side by shoulders 196 and on the opposite sides by the casserole sides 170 of the cams 168 extending there over the entire ring width.
  • the steps 184 are doing this in a radial plane extending sliding surfaces of the cam ring 90 on which the switching ring 96 with its end face 144 or its projections 109 come into contact and can slide along.
  • locking elements are further formed, on which, when the end face 144 rests on the steps 184, the projections 109 can strike at a relative rotation between the cam ring 90 and the switching ring 96. In this way, a locking between the cam ring 90 and the switching ring 96 is achieved, which prevents further relative movement in this direction of rotation.
  • FIGS. 10a to 10h a section of the switching ring 96 is shown in Figs. 10a to 10h, in which one of the rollers 104 and one of the projections 109 below the end face 144 can be seen. Since the arrangement of the rollers 104 and projections 109 repeats in the same way periodically as the contour of the cam track 108, only one of the rollers 104 and one of the projections 109 is reproduced on the switching ring 96.
  • the relative movement between the switching ring 96 and the cam track 108 shown in FIGS. 10a to 10h is shown such that the switching ring 96 moves over the fixed cam track 108 for reasons of clarity.
  • the cam ring 90 moves under the switching ring 96. So if in the following e.g. It will be understood that the rollers 104 move across the cams 168, in effect meaning that the cams 168 move beneath the fixed rollers 104.
  • Fig. 10a shows the mutual arrangement of the cam ring 90 and the switching ring 96 at a time when the Drehmomentbegrenzungskupplung 50 has just been solved so that the rollers 104 are already rolled over the cam 168 away.
  • the rollers 104 rest on the discharge sides 172 of the cams 168, while both the end surface 144 and the projections 109 move away from the underlying steps 184 over the cam ring 90.
  • Fig. 10d can be seen that the rollers 104 have already lifted from the cam track 108, so that the switching ring 96 rests only with the projections 109 on the steps 184 of the cam ring.
  • the projections 109 slip over the transition between the steps 184 and the depressions 192 forming paragraphs 196, whereby the switching ring 96 slightly lower than the cam ring 90, so that now the switching ring 96 relative to the cam ring 90 is supported on the steps 184 via its end face 144 (FIG. 10e).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Claims (20)

  1. Tournevis motorisé (10) pour visser et dévisser des vis, avec un embrayage limiteur de couple (50) se déclenchant en fonction du couple, qui présente une première partie d'embrayage (96), une deuxième partie d'embrayage (90), un élément à ressort (94) pour pousser axialement la première partie d'embrayage (96) contre la deuxième partie d'embrayage (90) et au moins un corps roulant (104) circulant entre les deux parties d'embrayage (90, 96), par l'intermédiaire duquel les deux parties d'embrayage (90, 96) sont couplées l'une à l'autre en cas d'entraînement du tournevis (10) dans une première direction de rotation jusqu'à atteindre un couple de déclenchement prédéfini, caractérisé en ce que sur les deux parties d'embrayage (90, 96) sont formés des éléments de crantage (109, 196) par l'intermédiaire desquels les deux parties d'embrayage (90, 96) se crantent directement l'une à l'autre en cas d'entraînement du tournevis (10) dans une deuxième direction de rotation.
  2. Tournevis selon la revendication 1, caractérisé en ce que le crantage peut être levé par une inversion de la direction de rotation du tournevis (10).
  3. Tournevis selon la revendication 1 ou 2, caractérisé en ce que sur des faces frontales (165, 143) mutuellement en vis-à-vis des deux parties d'embrayage (90, 96) sont formées des surfaces de glissement (144, 184) mutuellement associées, par l'intermédiaire desquelles les deux parties d'embrayage (90, 96) s'appuient l'une contre l'autre dans des positions angulaires relatives prédéfinies.
  4. Tournevis selon la revendication 3, caractérisé en ce que les éléments de crantage (109, 196) sont réalisés sur les surfaces de glissement (144, 184).
  5. Tournevis selon la revendication 4, caractérisé en ce que la surface de glissement de la première partie d'embrayage (96) est formée par une surface frontale (144) et par des saillies (109) dépassant axialement de celle-ci, et en ce que la surface de glissement (184) de l'autre partie d'embrayage est formée par des gradins (184) qui sont limités chacun par des talons (196), contre lesquels les saillies (109) peuvent buter dans la deuxième direction de rotation.
  6. Tournevis selon l'une des revendications précédentes, caractérisé en ce que sur la deuxième partie d'embrayage (90) est formée une piste de roulement de came (108) s'étendant dans la direction circonférentielle, qui se compose de plusieurs, de préférence trois, sections de piste (176, 178, 180) réalisées identiques.
  7. Tournevis selon l'une des revendications 3 à 5 et selon la revendication 6, caractérisé en ce que la piste de roulement de came (108) est placée à l'extérieur de la surface de glissement (184) de la deuxième partie d'embrayage (90) et de manière concentrique à elle.
  8. Tournevis selon la revendication 6 ou 7, caractérisé en ce que chaque section de piste (176, 178, 180) présente une came (168) dont les flancs forment une face de montée (170) et une face de descente (172) pour le corps roulant (104) au nombre d'au moins un.
  9. Tournevis selon la revendication 8, caractérisé en ce que la face de montée (170) est plus inclinée que la face de descente (172).
  10. Tournevis selon la revendication 8 ou 9, caractérisé en ce que l'inclinaison de la face de descente (172) diminue quand la distance depuis la face de montée (170) augmente.
  11. Tournevis selon la revendication 9 ou 10, caractérisé en ce que la piste de roulement de came (108) présente entre les cames (168) à chaque fois une sous-section (197) qui n'est pas touchée par le corps de roulement (104) au nombre d'au moins un.
  12. Tournevis selon la revendication 11, caractérisé en ce que les surfaces de glissement (144, 184) sont agencées de telle manière par rapport à la piste de roulement de came (108) qu'en cas d'entraînement du tournevis (10) dans la première direction de rotation et avec l'embrayage limiteur de couple (50) accouplé, le corps roulant (104) au nombre d'au moins un est en appui avec la face de montée (170) d'une came (168) et, dans le même temps, la première partie d'embrayage (96) s'appuie contre la deuxième partie d'embrayage (90) dans la direction axiale par l'intermédiaire des surfaces de glissement (144, 184).
  13. Tournevis selon l'une des revendications précédentes, caractérisé en ce que le corps roulant au nombre d'au moins un est conformé en galet (104).
  14. Tournevis selon la revendication 13, caractérisé en ce que le galet (104) est monté rotatif sur un axe (106) tenu sur la première partie d'embrayage (96).
  15. Tournevis selon la revendication 14, caractérisé en ce que l'axe de rotation (152) du rouleau (104) défini par l'axe (106) est placé à distance d'un axe longitudinal (154) de la première partie d'embrayage (96).
  16. Tournevis selon la revendication 15, caractérisé en ce que le galet (104) est monté en roue libre sur l'axe (106).
  17. Tournevis selon l'une des revendications précédentes, caractérisé en ce que l'une des deux parties d'embrayage (96) est reliée de manière fixe en rotation à un boîtier (11) du tournevis (10) et l'autre partie d'embrayage (90) est reliée de manière fixe en rotation à une partie de réaction (70)- d'un mécanisme (38) comprenant rotative par rapport au boîtier (11) et supportant un couple de rotation par rapport à une broche (40).
  18. Tournevis selon la revendication 17, caractérisé en ce que la partie de réaction est une roue creuse (70) d'un mécanisme à roues planétaires (38) comprenant plusieurs roues planétaires (66, 74).
  19. Tournevis selon la revendication 17 ou 18, caractérisé en ce que la partie d'embrayage (96) reliée de manière fixe en rotation au boîtier (11) du tournevis (10) est montée mobile dans la direction axiale (95).
  20. Tournevis selon la revendication 19, caractérisé par un commutateur (124) pour arrêter le tournevis (10), qui peut être actionné par la partie d'embrayage (96) montée mobile dans la direction axiale.
EP02010510A 2001-05-14 2002-05-10 Tournevis motorisé avec embrayage limitateur de couple Expired - Lifetime EP1258321B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10124569 2001-05-14
DE10124569A DE10124569A1 (de) 2001-05-14 2001-05-14 Kraftgetriebener Schrauber mit Drehmomentbegrenzungskupplung

Publications (3)

Publication Number Publication Date
EP1258321A2 EP1258321A2 (fr) 2002-11-20
EP1258321A3 EP1258321A3 (fr) 2005-02-09
EP1258321B1 true EP1258321B1 (fr) 2007-07-25

Family

ID=7685483

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02010510A Expired - Lifetime EP1258321B1 (fr) 2001-05-14 2002-05-10 Tournevis motorisé avec embrayage limitateur de couple

Country Status (4)

Country Link
EP (1) EP1258321B1 (fr)
AT (1) ATE367893T1 (fr)
DE (2) DE10124569A1 (fr)
ES (1) ES2290213T3 (fr)

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WO2023009733A1 (fr) * 2021-07-28 2023-02-02 Milwaukee Electric Tool Corporation Outil de pose d'écrou à rivet aveugle

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Publication number Priority date Publication date Assignee Title
DE102004038829A1 (de) * 2004-08-04 2006-03-16 C. & E. Fein Gmbh Schrauber
DE102006025703B4 (de) 2005-06-01 2019-11-14 Milwaukee Electric Tool Corp. Kraftwerkzeug, Antriebsanordnung und Betriebsverfahren davon
FR2895929B1 (fr) * 2006-01-06 2009-06-26 Georges Renault Soc Par Action Outil de vissage dant le corps presente un acces a des moyens de reglage du couple, une protection de la partie terminale de l'outil venant couvrir ledit acces.
US11673243B2 (en) * 2018-09-05 2023-06-13 Milwaukee Electric Tool Corporation Blind rivet nut-setting tool
DE202019106525U1 (de) * 2019-11-22 2021-02-26 C. & E. Fein Gmbh Handwerkzeugmaschine
DE102020130665B4 (de) 2020-11-19 2024-04-25 Herwig Herrmann 1 - 17Abschaltkupplung

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DE683190C (de) * 1933-10-05 1939-11-01 Bosch Gmbh Robert Kraftbetriebene Werkzeugmaschine
DE3432376A1 (de) * 1984-09-03 1986-03-13 Hilti Ag, Schaan Motorisch betriebenes schraubgeraet
DE4123349C1 (de) * 1991-07-15 1993-03-04 Fein C & E Schrauber mit variabler Drehmomenteinstellung
US5372206A (en) * 1992-10-01 1994-12-13 Makita Corporation Tightening tool
SE507908C2 (sv) * 1996-09-16 1998-07-27 Atlas Copco Tools Ab Kraftmutterdragare med avstängning
DE19833943C2 (de) * 1998-07-28 2000-07-13 Rodcraft Pneumatic Tools Gmbh Schlagschrauber

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Publication number Priority date Publication date Assignee Title
WO2023009733A1 (fr) * 2021-07-28 2023-02-02 Milwaukee Electric Tool Corporation Outil de pose d'écrou à rivet aveugle

Also Published As

Publication number Publication date
ATE367893T1 (de) 2007-08-15
ES2290213T3 (es) 2008-02-16
DE50210539D1 (de) 2007-09-06
DE10124569A1 (de) 2002-11-21
EP1258321A3 (fr) 2005-02-09
EP1258321A2 (fr) 2002-11-20

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