Classifications

• • 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 present invention relates to a power tool with a gear and a torque coupling, which has a transmission associated with the limiting unit, which is assigned by at least one spring element axially acted upon in the direction of the engine transmission element, wherein a torque level of the torque coupling via a user-operable control element at least is adjustable within predetermined limits.
• a hand tool with a trained in the manner of a planetary gear and a torque clutch which has a transmission associated with the limiting unit for setting a maximum, transferable from the transmission to a tool holder of the power tool torque level.
• the adjustment of the torque height takes place with the aid of an associated adjusting sleeve within predetermined limits.
• the torque coupling has a transmission element, which is acted upon by a spring element with a predetermined spring force axially in the direction of spherical detents, which are associated with the limiting unit.
• the spherical detent body are acted upon by the transmission element against a ring gear of the planetary gear.
• the present invention relates to a handheld power tool having a gearbox and a torque coupling, which has a gearbox associated with the gearbox.
• the limiting unit has at least one locking body, which engages in the axial direction of the torque coupling at least partially into the transmission element.
• the invention thus enables the provision of a hand tool machine, in which a reliable guidance of the transmission element is ensured.
• the preferably designed in the manner of a pressure plate transmission element is reliably positioned by the locking body both in the radial and in the axial direction, so that reduce the friction and concomitantly the wear. Furthermore, there is a reduced axial length of the torque coupling with a reduced weight at the same time. Due to the reduced weight, less vibration is produced when the torque clutch is active. Furthermore, there is at least one line contact between the locking bodies and the pressure plate instead of a point contact, as in conventional torque clutches. In addition, the coupling forces are harmonized with active torque clutch to maximize the life.
• the transmission element has at least one recess for at least partially axial reception of the at least one detent body.
• the at least one recess is designed in the manner of an opening and the at least one latching body is spherical, wherein the at least one spherical latching body engages at least in sections in the opening.
• the spherical detent body commonly used as a detent body can be used, while the openings can be designed, for example, as easy-to-manufacture cylindrical bores.
• a diameter of the at least one recess is smaller than a diameter of the at least one spherical detent body.
• a diameter of the recess is preferably smaller than 0.9 times the diameter of the detent body.
• a peripheral edge of the recess can be prismatically chamfered.
• the at least one recess has a polygonal base surface and the at least one latching body is cylindrical, wherein the at least one cylindrical latching body engages at least in sections in the at least one recess.
• roller-shaped or roller-shaped ratchet bodies can be used, which enable a linear contact with the ring gear in comparison to spherical ratchet bodies.
• a circumferential width of the at least one recess is smaller than a diameter of the at least one cylindrical detent body.
• the transmission has at least one ring gear
• the limiting unit has at least three locking body and a front side formed on the ring gear coupling geometry
• the transmission element has at least three recesses.
• the coupling geometry is preferred realized with one of the number of locking body or the recesses corresponding number of trapezoidal starting ramps.
• the transmission element is disc-shaped and has at least three radially inwardly directed projections, in each of which one of the at least three recesses is formed.
• the invention thus enables a simple shutdown of the torque coupling.
• the at least one spring element has at least one compression spring.
• the transmission is designed in the manner of a planetary gear and has at least one ring gear, wherein the at least one locking body is subjected to axial force by means of the transmission element against the ring gear.
• the at least one locking body is subjected to axial force by means of the transmission element against the ring gear.
• the at least one locking body is designed for rolling on the ring gear.
• the user-operable control element is designed to allow adjustment of a spring force exerted by the at least one spring element.
• the operating element is preferably designed as a torque setting sleeve which can be rotated by the user in relation to the tool housing.
• FIG. 1 is a schematic view of a hand tool with a torque coupling according to an embodiment
• FIG. 2 shows a sectional view of a detail 220 of the handheld power tool of FIG. 1 with a transmission element according to a first embodiment
• Fig. 3 is an exploded view of a portion of the cutout 220 of Fig. 1, and
• Fig. 4 is the sectional view of Fig. 2 with a transmission element according to a second embodiment.
• the hand tool 100 shows by way of example a hand tool 100 provided with a torque coupling 160.
• the hand tool 100 illustratively has a tool housing 105 with a handle 15.
• the handheld power tool 100 for mains-independent power supply can be mechanically and electrically connected to a battery pack 210.
• the power tool 100 is exemplified as a cordless drill driver, the battery pack 210 can be permanently installed or interchangeable.
• the present invention is not limited to cordless drill, but rather can be applied to various hand tool having a torque coupling 160 corresponding torque coupling, regardless of whether the power tool electrically, ie independent of the battery with the battery pack 210th or network-dependent, and / or non-electrically operable.
• the tool housing 105 for example, one of the battery pack 210 supplied with power, electric drive motor 200 and a transmission 170 are arranged.
• the drive motor 200 is connected via the gear 170 with a drive shaft 120, for example a drive spindle.
• the drive motor 200 is illustratively arranged in a motor housing 202 and the gear 170 is housed in a gear housing 1 10, wherein the gear housing 1 10 and the motor housing 202 are arranged for example in the tool housing 105.
• the transmission 170 is designed for transmitting a torque generated by the drive motor 200 to the drive spindle 120 and, according to one embodiment, a planetary gear 171 designed with different gear or planetary stages, which is rotationally driven by the drive motor 200 during operation of the power tool 100.
• the drive motor 200 is e.g. via a hand switch 212 actuated, i. on and off, and may be any type of motor, e.g. an electronically commutated motor or a DC motor.
• the drive motor 200 can be electronically controlled or regulated in such a way that both a reversing operation and specifications regarding a desired rotational speed can be realized.
• the mode of operation and the design of a suitable drive motor are sufficiently known from the prior art, so that a detailed description of the description is omitted here for the purpose of conciseness of the description.
• the drive spindle 120 is rotatably mounted in the tool housing 105 via a bearing arrangement 130.
• the drive spindle 120 is associated with a tool holder 140, which is arranged in the region of an end face 1 12 of the tool housing 105 and illustratively has a drill chuck 145.
• the bearing arrangement 130 has at least two bearing points 132, 134 for rotatably supporting the drive spindle 120.
• the tool holder 140 serves to receive an insert tool 150 and may be integrally formed with the drive spindle 120 or be connected to it in a tower-shaped manner.
• the tool holder 140 is exemplified tower-like and secured by means provided on the drive shaft 120 and the drive spindle fastening device 122 thereto.
• the fastening device 122 is embodied here as an external thread.
• the hand tool 100 has the torque coupling 160 as described above. This is illustratively equipped with a user of the power tool 100 actuated, in particular rotatable control element 165.
• the user-operable control element 165 is configured to set a respectively desired, eg, work-specific torque limitation by the torque coupling 160 or to set a respective torque height of the torque coupling 160, at least within predetermined limits.
• the operating element 165 of the torque coupling 160 is designed as an example sleeve-shaped and is therefore hereinafter also referred to as the
• FIG. 2 shows the detail 220 of the hand tool 100 of FIG. 1, wherein a representation of the tool holder 140 and the insert tool 150 of FIG. 1 has been dispensed with for the sake of simplicity and clarity of the drawing.
• This cutout 220 shows, inter alia, the transmission 170 integrated in the gearbox housing 1 10, which is merely exemplified here as a planetary gear 171.
• the cutout 220 shows the torque coupling 160 arranged at least in sections in the clutch housing 161 and a limiting unit 230 assigned to the planetary gear 171.
• the planetary gear 171 includes by way of example a rear, the drive motor 200 of FIG. 1 facing planetary stage 172 with a, not shown, from
• a Drive motor rotatably driven sun gear and three planetary gears, of which only two planet gears 174, 175 are visible here.
• the planet gears 174, 175 of the rear planetary stage 172 are connected to a planet carrier 176.
• a central planetary stage 177 comprises three planetary gears connected to a planetary carrier 178, of which only one planetary gear 179 is visible here.
• the planet gears of the central planetary stage 177 are rotationally driven by a sun gear 180 formed on the planet carrier 176 of the rear planetary stage 172.
• a sun gear 181 formed on the planet carrier 178 of the middle planetary stage 177 in turn, in turn drives three planet wheels of a front planetary stage 182 which are connected to a planet carrier
• the planet gears of the front planetary stage 182 are illustratively in engagement with an internal toothing 185 of a ring gear 190.
• the planet carrier 183 of the front planetary stage 182 is exemplary rotationally fixed, for example by means of a positive connection, with the drive shaft 120 and the drive spindle connected.
• the fastening device 122 for the tool holder 140 of FIG. 1 is provided by way of example.
• the drive shaft 120 and the drive spindle is rotatably received in the clutch housing 161 by means of the first and the second bearing 132, 134 as components of the bearing assembly 130 of FIG. 1, wherein the first bearing 132 exemplified as a sliding bearing 136 and the second bearing 134 as a Ball bearing 138 is formed.
• the limiting unit 230 is one of at least one and preferably six
• Spring elements - of which only a single spring element 234 designed with a compression spring 232 is visible here by way of example - are assigned in the direction of the planetary gear 171 or in the direction of the drive motor 200 acted upon transmission element 240 or pressure plate.
• the six spring elements or the compression springs circumferentially uniformly spaced from each other.
• the detent body 250 and all other detent bodies are acted upon by a coupling geometry 252 formed on the end face 236 of the ring gear 190.
• the compression spring 232 and all other compression springs are clamped on both sides between the transmission element 240 and a spring element holder 238, wherein the compression spring 232 is in the axial position of the spring element holder 238 shown here under an at least slight axial bias.
• the torque adjustment 160 associated control element 165 and the Drehmomenteinstellhülse of FIG. 1 is rotatable, but preferably at least substantially axially immovably arranged on the clutch housing 161. The setting of a maximum of the torque coupling 160 torque transmissible by the rotation of the operating element 165 and the
• the spring element holder 238 for varying the axial spring force of the at least one spring element 234 in the direction of a double arrow 300 is axially displaceable.
• the operating element 165 or the torque setting sleeve is preferably non-rotatably coupled to an internal, nut-like adjusting ring 242 on which at least one radially inwardly directed engagement element 244 is formed, which engages in an outer circumference provided on the clutch housing 161 external thread 246.
• the thread-like connection between the at least one engaging element 244 and the external thread 246 of the coupling housing 161 preferably serves to guide the adjusting ring 242 on the external thread 246 by a rotation of the operating element 165 or the torque setting sleeve and thus a displacement of the adjusting ring 242 parallel to the longitudinal direction of the drive shaft 120 or the drive spindle - as indicated by the double arrow 300 - to effect and thereby to vary the spring force of the spring elements and the compression springs within predetermined limits.
• the transmission element 240 preferably has six recesses which are axially continuous in each case and which are circumferentially arranged uniformly spaced from one another and of which only one recess 260 is shown, into which the detent body 250 preferably dips at least in sections.
• the recess 260 is embodied here merely by way of example as a circular opening 262 or a cylindrical bore, the diameter DA of which is smaller than a diameter DK of the detent body 250, which here too is merely an exemplary spherical body.
• the diameter DA of the recess 260 is smaller than 0.9 times the diameter of the detent body 250.
• Due to the axially at least partially immersed in the transmission element 240 detent body is a shorter axial length of the torque coupling 160 and a lower weight of the same can be realized.
• a reliable radial guidance of the transmission element 240 is given, which is associated with a reduction in friction and wear and contributes to an extension of the service life of the power tool.
• the round recesses between the locking bodies and the transmission element 240 each result in a circular contact line or contact zone.
• the six latching bodies and the six corresponding recesses may be provided as parts of the delimiting unit 230 a different number of spring elements, latching bodies and recesses
• the locking body and recesses should be the same size.
• the limiting unit 230 with the at least one spring element 234, the transmission element 240, the detent bodies 250 and the coupling geometry 252 is formed on the end face 236 of the ring gear 190.
• the torque coupling 160 essentially comprises the clutch housing 161, the operating element 165 or the torque setting sleeve and the adjusting ring 242 with the at least one engaging element 244 and the external thread 246 of the clutch housing interacting therewith to transform the rotational movement of the operating element 165 into a translatory movement of the spring element holder 238 161.
• the torque coupling 160 responds when the supporting torque becomes greater than the holding torque applied by the limiting unit 230, so that the ring gear 190 ultimately slips or slips.
• the transmission of rotational speed between the front planetary stage 181 of the planetary gear 171 and the drive shaft 120 is suspended and limits the transmission of torque.
• the respective holding torque of the limiting unit 230 acting on the ring gear 190 is dependent on the axial position of the spring element holder 238 and thus on the rotational position of the operating element 165.
• the at least one spring element 234 is largely relaxed, so that the at least one detent body 250 is acted upon by the transmission element 240 with a comparatively small axial spring force against the coupling geometry 252 of the end face 236 of the ring gear 190 of the planetary gear 171 , As a result, the ring gear 190 slips or rotates even at relatively small torques acting on the drive shaft 120 or the drive spindle, and the power tool is in a "screwing mode".
• the at least one spring element 234 is more strongly tensioned or compressed, which can be achieved by the axial displacement of the spring element holder 238 in the direction of the planetary gear 171 or in the direction of the drive motor 200 by user-side rotation of the operating element 165, then the at least one latching body 250 passes through the transmission element 240 is acted upon by a higher spring force against the ring gear 190, resulting in a higher holding torque results and this only begins to slip or turn at higher torque acting on the drive shaft 120.
• the at least one spring element 234 or the compression spring 232 is compressed almost completely, the at least one detent body 250 is acted upon by the transmission element 240 with such a high axial spring force against the coupling geometry 252 of the end face 236 of the ring gear 190 that it is practically no longer slipping can and a "drilling mode" of the power tool is activated, in which on the drive shaft 120, a maximum working torque can be tapped.
• an axial distance between the spring element holder 238 and the transmission element 240 may be smaller than corresponding elevations (254 in FIG. 3) of the coupling geometry 252.
• FIG. 3 shows an exploded view of part of the cutout 220 of FIG. 1 and FIG. 2. Accordingly, the substantially hollow cylindrical one has Ring gear 190 of the limiting unit 230 of the torque coupling 160 via an internal toothing 185 and on the end face 236 of the ring gear 190, the coupling geometry 252 is formed.
• the coupling geometry 252 has here only by way of example six similar elevations whose cross-sectional geometry corresponds to an isosceles trapezoid in an exemplary manner and by way of example two elevations 254, 256 are designated.
• the six circumferentially evenly spaced trained surveys are facing the spherical detent bodies in the axial direction, of which for reasons of better graphical overview also half only the detent body 250 and a circumferentially adjacent detent body
• the preferably at least substantially disc-shaped transmission element 240 has a central recess 264, on the inner edge 266 six radially inwardly directed and each approximately V-shaped projections are formed, of which only two projections 270, 272 of the better diagrammed overview half are designated.
• the number of projections preferably corresponds to the number of compression springs used. Alternatively, e.g. when using a single, to the drive shaft 120 of FIG. 1 concentrically arranged compression spring, the number of projections of the number of locking body.
• Each of the six projections has a recess 260, which passes completely through the respective projection in the axial direction, wherein the recesses are each designed here as a circular openings or holes. Of the total of six openings here only two openings 262, 263 are designated.
• Each projection serves as a first abutment or abutment for each compression spring, of which only the compression springs 232 and a further, peripheral thereto adjacent compression spring 233 is designated.
• the spring element holder 238 represents a second abutment or abutment for the compression springs.
• the spring element holder 238 has, for example, an approximately circular base body 239, at its inner edge, not designated, six parallel to a longitudinal central axis 302 of the torque coupling
• each holding web 160 extending holding webs are formed, of which only two holding webs 280, 282 are designated.
• the holding webs of the spring element holder 238 are circumferentially equally spaced from each other on the inner edge of the spring element holder 238 arranged.
• Each holding web has, at its free end pointing in the direction of the adjusting ring 242, a radially inwardly directed, approximately semicircular tab, of which two tabs 284,
• the adjusting ring 242 preferably has an approximately hollow-cylindrical basic body 248 with the inner circumference formed engaging element 244, which is designed here as an internal thread 249. On its outer circumference is a radially outwardly directed, cuboid driver 290 for the rotationally fixed coupling of the control element 165 and the Drehmomenteinstellhülse.
• FIG. 4 shows the detail 220 of the hand tool 100 of FIG. 1 according to FIG.
• the at least one recess 260 now preferably has a polygonal base surface 268 and the at least one latching body 250 is preferably cylindrical or roller-shaped and at least partially engages in the at least one recess 260.
• a circumferential width of the at least one recess 260 is preferably smaller than a diameter Dz of the at least one cylindrical or roller-like latching body 250, preferably less than 0.9 times of D z.
• the circumferential width of the at least one recess 260 defines an extension of the recess 260 in a possible direction of rotation of the drive spindle 120.
• the radial extent of the at least one recess 260 is preferably greater than a corresponding cylinder height of the at least one cylinder-shaped or roller-shaped latching body 250.

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

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• 2016
  • 2016-03-09 DE DE102016203886.9A patent/DE102016203886A1/de not_active Withdrawn
• 2017
  • 2017-03-02 WO PCT/EP2017/054898 patent/WO2017153245A1/de active Application Filing
  • 2017-03-02 EP EP17709619.5A patent/EP3426442B1/de active Active
  • 2017-03-02 CN CN201780015845.XA patent/CN109219502B/zh active Active

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