EP3363595B1 - Power tool gear device - Google Patents

Power tool gear device Download PDF

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Publication number
EP3363595B1
EP3363595B1 EP18160401.8A EP18160401A EP3363595B1 EP 3363595 B1 EP3363595 B1 EP 3363595B1 EP 18160401 A EP18160401 A EP 18160401A EP 3363595 B1 EP3363595 B1 EP 3363595B1
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EP
European Patent Office
Prior art keywords
component
gear
ring
gear stage
transmission device
Prior art date
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Active
Application number
EP18160401.8A
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German (de)
French (fr)
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EP3363595A1 (en
Inventor
Heiko Roehm
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3363595A1 publication Critical patent/EP3363595A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools

Definitions

  • the invention is based on a machine tool gear device according to the preamble of claim 1.
  • Machine tool transmission devices with a first and a second gear stage and with a switching element are already known, the switching element being movable by an operator by means of an actuating element, in an operating position surrounding the first gear stage along a circumferential direction and being provided between a first and a second To switch operating position.
  • Such machine tool gear devices are, for example, from EP 1 464 427 A , U.S. 5,339,908 A , EP 2 077 177 A and U.S. 5,550,416 A known.
  • the invention is based on a machine tool gear device with at least a first and a second gear stage and with a switching element that can be moved by an operator by means of an actuating element, the switching element at least partially surrounding at least one gear stage in at least one operating position along a circumferential direction and being provided for this purpose to switch between a first and a second operating position.
  • the switching element comprises at least a first component and a second component.
  • “provided” should be understood to mean in particular specially equipped and / or specially designed.
  • the term "gear stage" is intended here in particular an arrangement of gears, in particular planetary carriers, ring gears, planet gears and sun gears, in a transmission, in particular a planetary gear, which is intended to transmit predetermined torques and / or speeds and / or to reduce torques and / or speeds and / or translate.
  • the torque and / or the speed and / or a reduction and / or translation of the torque and / or the speed can preferably be changed by means of the switching element.
  • an “actuating element” is to be understood here in particular as an element and / or component, in particular an element and / or component, which can be actuated directly by an operator, which is connected to a further element and / or component, in particular the switching element, in an operative connection and which is provided to transfer the further element and / or component from one state to another state.
  • the actuating element is preferably formed by a component that is separate from the switching element.
  • the actuating element is in operative connection with the switching element by means of an external geometry, thus forces can be transmitted from the actuating element to the switching element.
  • An "operating position” here defines in particular a position, such as a shift position, of the shift element within a transmission, in particular a planetary gear, in which a specific torque and / or a specific speed is transmitted via the transmission to a shaft and / or to gears of the transmission can be.
  • the term "circumferential direction” is to be understood here in particular as a direction perpendicular to an axis of rotation of an output shaft of the machine tool transmission device, the circumferential direction running circumferentially around the axis of rotation of the output shaft of the machine tool transmission device.
  • the expression “surrounds along a circumferential direction” is intended to define, in particular, an overlap in a radial direction of at least one element and / or component by means of at least one further element and / or component.
  • the radial direction runs perpendicular to the axis of rotation of the output shaft of the machine tool gear device.
  • an arrangement of gears in particular a planet carrier, a ring gear, planet gears and / or a sun gear, should be radially covered by at least one component of the switching element.
  • the machine tool gear device for hand-held power tools such as screwdrivers, drill / drivers and hammer drills and especially for cordless screwdrivers, cordless drills and cordless hammer drills
  • a motor speed of about 20,000 rpm in a work spindle of the hand-held Power tool to reduce a reasonable speed range of approx. 150 rpm to 2000 rpm.
  • the inventive design of the machine tool gear device allows an operator to switch particularly comfortably between a first and a second operating position, switching from a first gear of the machine tool gear device with a low speed and a high torque to a second gear of the machine tool gear device with a high speed and a low torque can be. In this case, a switching process can be achieved in a particularly advantageous manner during operation of the machine tool transmission device under load.
  • the switching element is designed as a switching ring gear.
  • the switching ring gear is particularly advantageously provided for a planetary gear.
  • the first component is advantageously at least partially formed by a first ring element and the second component is at least partially formed by a second ring element.
  • the first ring element and the second ring element each have a longitudinal extension which runs along the entire circumferential direction, so that the first ring element is self-contained and the second ring element is also self-contained.
  • the inventive design of the components as a ring element makes it possible to achieve a compact machine tool transmission device.
  • the first component at least partially cover the second component along a radial direction, at least in an operating position.
  • an existing installation space can be used advantageously and a simple functional combination of the components can be achieved.
  • a high level of operating convenience of the machine tool gear device can be achieved.
  • the first component and the second component essentially enclose a receiving area.
  • the receiving area preferably runs in the manner of a ring segment along the circumferential direction.
  • the receiving area can be divided into several independent sections along the circumferential direction.
  • the receiving area in an axial direction and in the radial direction can be substantially of the first component and the second component be covered.
  • the axial direction runs essentially parallel to the axis of rotation of the output shaft of the machine tool gear device.
  • the term “essentially parallel” is to be understood here in particular as a direction which has a deviation from a reference direction, in particular less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 °.
  • the first component is preferably mounted so as to be movable relative to the second component.
  • the first component can particularly advantageously move along the circumferential direction relative to the second component in order to be able to advantageously compensate for torque and / or speed differences during a switching process between the first and the second operating position.
  • the first component can move relative to the second component along the axial direction. In this way, a structurally simple switching element can be achieved.
  • the first component advantageously comprises at least one locking element.
  • a “locking element” is to be understood here in particular as an element and / or component that is provided to prevent movement of the element and / or component relative to a further element and / or component by means of a form fit and / or force fit.
  • the locking element is preferably provided to form a form-fit connection.
  • the locking element is particularly advantageously designed in one piece with the first component.
  • “One-piece” is to be understood here in particular as one-piece and / or formed from a cast and / or formed as a component.
  • the locking element is preferably designed as a locking geometry in the form of a partial external toothing, in particular a spur gear toothing, and / or a partial internal toothing of the first component.
  • a one-piece design can advantageously save installation space, installation effort and costs.
  • the first component can advantageously be held in a desired position by means of the locking element.
  • the locking geometry can advantageously be provided to prevent rotation of the first component relative to a housing in which the machine tool gear device is arranged.
  • the switching element has at least one further component which is at least partially formed by a spring element.
  • a "spring element” is defined in this context a resilient element and / or component, such as a disc spring, an elastomer and / or other resilient elements that appear sensible to a person skilled in the art.
  • the spring element is particularly advantageously designed as a helical spring.
  • the spring element preferably has the function of a damping means, whereby an advantageous protection of components can be achieved and wear can be reduced.
  • the first component be in operative connection with the second component at least by means of the spring element.
  • the spring element is preferably provided to ensure relative movement between the components.
  • a switching process can be achieved particularly advantageously during operation of the machine tool transmission device, such as, in particular, during a load by a drive torque.
  • the spring element is preferably arranged along at least one direction between the first component and the second component. “Between” is to be understood here in particular as an arrangement spatially along the radial direction and / or the axial direction.
  • the spring element is preferably arranged in the receiving area surrounded by the first component and the second component. In this way, a protective function of the spring element can be achieved and, furthermore, a compact arrangement of the components in the machine tool gear device can be achieved.
  • the first component has at least one form-locking element which is provided to at least partially engage behind the second component in an axial direction.
  • a “form-fit element” is to be understood here in particular as an element and / or a component which is provided to form a form-fit connection with a further element and / or component.
  • the form-locking element is preferably designed in one piece with the first component, which advantageously allows savings in terms of installation space and components.
  • a secure coupling of the components can advantageously be achieved by the form-fit element and a machine tool gear device with a simple design can be achieved.
  • the first component advantageously has at least one support element running in a radial direction, the support element being oriented in the direction of the second component.
  • a “support element” is to be understood here in particular as an element and / or component that is designed as a system and / or a stop of a further element and / or component, in particular the spring element, in order to absorb and / or transmit forces in particular and / or to introduce them into the further element and / or component.
  • the support element is preferably formed in one piece with the first component, with which an advantageous and structurally simple introduction of force into the component can be achieved.
  • the second component has at least one support element running in a radial direction, the support element being oriented in the direction of the first component.
  • the support element is preferably designed in one piece with the second component.
  • FIG 1 shows a hand-operated electric machine tool 52 designed as a cordless screwdriver 50 with a machine tool gear device 10 according to the invention in a schematic representation.
  • the cordless screwdriver 50 comprises a multi-part housing 54, in which the machine tool gear device 10 and a motor unit 56 are arranged, and a tool holder 60 into which a tool 62 can be inserted.
  • the tool 62 is driven by an output shaft 64 (see in this regard Figure 2 ) the machine tool gear device 10, which is operatively connected to the tool holder 60, can be driven in rotation.
  • the Acku screwdriver 50 comprises an adjusting ring 66 which is arranged on the tool holder 60 and is provided to set a torque that can be transmitted to the tool holder 60.
  • a main direction of extent 68 of the cordless screwdriver 50 extends from a side 70 of the housing 54, on which cooling openings 72 are arranged, in the direction of the tool holder 60
  • Cordless screwdriver 50 is provided by an operator.
  • the handle 74 is formed in one piece with the housing 54.
  • a battery pack 76 is attached to the handle 74.
  • the handle 74 further comprises an actuation switch 78 with electrical contacts which, when the actuation switch 78 is actuated by the operator, are provided to establish or interrupt an electrical supply to the motor unit 56 by the battery pack 76.
  • an actuating element 18, which is designed as a switch 80, is arranged on a side of the housing 54 facing away from the handle 74.
  • the switch 80 is mounted so as to be axially displaceable along the main direction of extent 68 of the cordless screwdriver 50.
  • a switching element 16 (see in this regard Figure 2 ) of the machine tool transmission device 10 can be moved by the operator along an axial direction 42.
  • the axial direction 42 runs essentially parallel to the main direction of extent 68 of the cordless screwdriver 50.
  • FIG. 2 shows a detailed view of the machine tool transmission device 10 according to the invention in a schematic representation.
  • the machine tool gear device 10 includes a Planetary gear 84 with a first, a second and a third gear stage 12, 14, 82.
  • the gear stages 12, 14, 82 each include a ring gear 86, 94, 152, a planet carrier 88, 120, 124 and several planet gears 90, 100, 122, which are arranged on the planet carrier 88, 120, 124.
  • the machine tool transmission device 10 further comprises the switching element 16, which can be moved by the operator by means of the switch 80.
  • the switching element 16 is designed as a switching ring gear 26.
  • the switching ring gear 26 comprises a first component 22 and a second component 24.
  • the first component 22 is formed by a first ring element 28, which is designed as a switching ring 92.
  • the second component 24 is formed by a second ring element 30, which is designed as a ring gear 94 of the second gear stage 14.
  • the switching ring 92 covers the ring gear 94 of the second gear stage 14 along a radial direction 32 which runs perpendicular to an axis of rotation 96 of the output shaft 64.
  • the ring gear 94 of the second gear stage 14 comprises an internal toothing 98 with which the planet gears 100 of the second gear stage 14 mesh.
  • the switching ring 92 surrounds the second gear stage 14 of the planetary gear 84 along a circumferential direction 20 which runs perpendicular to the axis of rotation 96 of the output shaft 64 and extends circumferentially around the axis of rotation 96 of the output shaft 64.
  • the switching ring gear 26 is provided to switch between the first operating position and a second operating position of the machine tool transmission device 10.
  • the first operating position forms a first gear of the planetary gear 84.
  • low speeds and a high torque are transmitted to the output shaft 64 and thus to the tool 62 in the tool holder 60 when the planetary gear 84 is in operation.
  • the second operating position forms a second gear of the planetary gear 84.
  • high speeds and a low torque are transmitted to the output shaft 64 when the planetary gear 84 is in operation.
  • the switching ring gear 26 is moved by the operator by means of the switch 80 along the axial direction 42.
  • the axial direction 42 here runs parallel to the axis of rotation 96 of the output shaft 64 of the machine tool transmission device 10.
  • the switching ring gear 26 is connected in the first gear of the planetary gear 84 by means of a first locking element 36 of the switching ring 92 in a rotationally secure manner to the housing 54 of the cordless screwdriver 50.
  • the first locking element 36 is designed in the form of a first external toothing 102.
  • the first external toothing 102 runs along the circumferential direction 20 on an outer side 104 of the switching ring 92 and extends in the radial direction 32 in the direction of the housing 54.
  • the housing 54 accordingly comprises an internal toothing 106 in which the first external toothing 102 of the switching ring 92 engages.
  • the switching ring gear 26 further comprises a receiving area 34 which is essentially enclosed by the switching ring 92 and the ring gear 94 of the second gear stage 14.
  • the shift ring 92 and the ring gear 94 of the second gear stage 14 cover the receiving area 34 along the radial direction 32 and the axial direction 42.
  • the receiving area 34 is provided to receive at least one further component 38 of the shift ring gear 26.
  • the further component 38 is designed as a spring element 40.
  • a total of two spring elements 40, which are designed as helical springs 108, are arranged in the receiving area 34.
  • the receiving area 34 is divided into two spatially separate sections 110 along the circumferential direction 20, one of the helical springs 108 being arranged in each section 110.
  • the receiving area 34 is divided into more than two sections 110 and a corresponding number of helical springs 108 are arranged in the sections 110.
  • the switching ring 92 has a support element 46 running in the radial direction 32, which is oriented in the direction of the ring gear 94 of the second gear stage 14.
  • the switching ring 92 has several support elements 46 for subdivision, depending on the number of sections 110.
  • the ring gear 94 of the second gear stage 14 has a support element 48 which is oriented in the direction of the shift ring 92.
  • the person skilled in the art will also provide the ring gear 94 of the second gear stage 14 with a corresponding number of support elements 48 depending on the number of sections 110.
  • the coil springs 108 are each supported with one end 112 on the support element 46 of the switching ring 92, and with an opposite end 114 the coil springs 108 are supported on the support element 48 of the ring gear 94 of the second gear stage 14.
  • the switching ring 92 is therefore operatively connected to the ring gear 94 of the second gear stage 14 by means of the helical springs 108.
  • a force is transmitted from the switching ring 92 to the ring gear 94 of the second gear stage 14 by means of the support elements 46, 48 and the helical springs 108.
  • the switching ring 92 is movably supported here over an angular range with an angle ⁇ of at least 90 ° along the circumferential direction 20 relative to the ring gear 94 of the second gear stage 14 due to the arrangement of the helical springs 108 in the receiving area 34 (see also FIG Figure 3 ).
  • the coil springs 108 are arranged along the axial direction 42 between the switching ring 92 and the ring gear 94 of the second gear stage 14. Furthermore, the coil springs 108 are arranged along the radial direction 32 between the switching ring 92 and the ring gear 94 of the second gear stage 14.
  • the machine tool gear device 10 When the cordless screwdriver 50 is in operation, the machine tool gear device 10 is driven by a shaft of the motor unit 56 on which a drive pinion 116 of the machine tool gear device 10 is arranged.
  • the drive pinion 116 engages in the planet gears 90 of the first gear stage 12.
  • the planet gears 90 of the first gear stage 12 mesh with an internal toothing 118, which is arranged along the circumferential direction 20 in a ring gear 86 of the first gear stage 12 that is non-rotatable relative to the housing 54, and drive the planet carrier 88 of the first gear stage 12. Any point on the planetary gears 90 of the first gear stage 12 executes a movement superimposed by two rotary movements.
  • a first of the two superimposed rotary movements is a rotation of the planet gears 90 of the first gear stage 12 and the second rotary movement is a rotation of the planet gears 90 of the first gear stage 12 about an axis of rotation of the drive pinion 116 of the machine tool gear device 10.
  • the planet carrier 88 of the first gear stage 12 drives the planet gears 100 of the second gear stage 14, any point on the planet gears 100 of the second gear stage 14 executing a movement superimposed by two rotary movements.
  • a first of the two superimposed rotary movements is a natural rotation of the planet gears 100 of the second gear stage 14 and the second rotary movement is a rotation of the planet gears 100 of the second gear stage 14 about an axis of rotation of the planet carrier 88 of the first gear stage 12.
  • the movement of the planet gears 100 superimposed by two rotary movements the second gear stage 14 is made possible by a non-rotatable arrangement of the switching ring 92 and thus the ring gear 94 of the second gear stage 14 in the housing 54.
  • the ring gear 94 of the second gear stage 14 is positioned by means of the helical springs 108 and the support elements 46, 48 after a slight movement relative to the switching ring 92 and / or the housing 54 in an essentially non-rotatable manner with respect to the housing 54.
  • the movement of the planet gears 100 of the second gear stage 14 drives a planet carrier 120 of the second gear stage 14.
  • This in turn drives planetary gears 122 of the third gear stage 82, which drives a planet carrier 124 of the third gear stage 82 according to a principle that corresponds to a drive of the first gear stage 12.
  • This is connected to the output shaft 64 of the machine tool transmission device 10 by means of a torque coupling 126.
  • the torque coupling 126 can be adjusted by means of the adjusting ring 66 to a maximum transmittable torque desired by the operator.
  • the mode of operation of the torque clutch 126 takes place in a manner already known to the person skilled in the art.
  • the switching ring gear 26 is moved by the operator by means of the switch 80 along the axial direction 42 in the direction of the first gear stage 12.
  • the switch 80 has a bolt 128 which engages in a groove 130 of the switching ring 92 running around in the circumferential direction 20.
  • the switching ring 92 moves along the axial direction 42, the two helical springs 108 and the ring gear 86 of the first gear stage 12 are also moved along the axial direction 42.
  • the switching ring 92 has a form-locking element 44 which is provided to engage behind the ring gear 94 of the second gear stage 14.
  • the form-fit element 44 is designed as a separate component that is firmly connected to the switching ring 92.
  • the interlocking element 44 is connected in a manner that appears sensible to a person skilled in the art, such as a screw connection, an adhesive connection, etc. of the switching ring 92 out of engagement with the internal toothing 106 of the housing 54.
  • the ring gear 94 of the second gear stage 14 is then accelerated and set in rotation by the planet gears 100 of the second gear stage 14, the switching ring 92 by means of an interaction of the helical springs 108 and the support elements 46, 48 is also accelerated and set in rotation.
  • the switching ring 92 comprises a second locking element 132 in the form of a second external toothing 134, which runs in the circumferential direction 20 on a side 136 of the switching ring 92 facing the first gear stage 12 and is aligned along the axial direction 42 in the direction of the first gear stage 12.
  • the second external toothing 134 has steep flanks which are provided to mesh with the flanks of an external toothing 138 of the planetary carrier 88 of the first gear stage 12 in order to rotationally couple the switching ring 92 to the ring gear 86 of the first gear stage 12.
  • the external toothing 138 of the planet carrier 88 of the first gear stage 12 runs in the circumferential direction 20 on an outer side 140 of the planet carrier 88 of the first gear stage 12 and is aligned along the axial direction 42 in the direction of the second gear stage 14.
  • the switching ring gear 26 comprises a second locking element 132 in the form of internal teeth 150, which runs in the circumferential direction 20 on an inner side 142 of the switching ring 92 and is aligned along the radial direction 32 in the direction of the ring gear 94 of the second gear stage 14.
  • the internal toothing 150 would mesh with an external toothing 138 of the planetary carrier 88 of the first gear stage 12, which runs in the circumferential direction 20 on an end face 144 of the planetary carrier 88 of the first gear stage 12 and would be aligned along the radial direction 32 in the direction of the housing 54.
  • the ring gear 94 of the second gear stage 14 is also essentially rotationally coupled to the ring gear 86 of the first gear stage 12 by means of the coil springs 108.
  • the shift ring gear 26 is coupled to the planet gears 100 of the second gear stage 14 and to the planet carrier 88 of the first gear stage 12.
  • the switching ring gear 26 is moved by the operator by means of the switch 80 along the axial direction 42 in the direction of the third gear stage 82.
  • the second external toothing 134 of the switching ring 92 disengages the external toothing 138 of the planetary carrier 88 of the first gear stage 12, whereby a coupling of the planetary gears 100 of the second gear stage 14 with the planetary carrier 88 of the first gear stage 12 is canceled.
  • the switching ring gear 26 By moving the switching ring gear 26 along the axial direction 42 in the direction of the third gear stage 82, the first external toothing 102 of the switching ring 92 engages the internal toothing 106 of the housing 54, with the engagement of the external toothing 102 of the switching ring 92 in the internal toothing 106 of the housing 54, a torque surge occurs between the switching ring 92 and the ring gear 94 of the second gear stage 14. This torque surge is dampened by means of the helical springs 108 between the switching ring 92 and the ring gear 94 of the second gear stage 14.
  • the switching ring gear 26 is connected to the housing 54 in an essentially non-rotatable manner after the switching process.
  • FIG. 4 an alternative embodiment is shown. Components, features and functions that essentially remain the same are generally numbered with the same reference numerals. To distinguish the exemplary embodiments, however, the letter a is added to the reference symbols of the alternative exemplary embodiment. The following description is essentially limited to the differences from the exemplary embodiment in FIG Figures 2 and 3 , whereby with regard to components, features and functions that remain the same, refer to the description of the exemplary embodiment in FIG Figures 2 and 3 can be referenced.
  • FIG Figure 4 shows a detailed view of a machine tool transmission device 10a according to the invention with an alternative switching element 16a in a schematic representation.
  • the machine tool gear device 10a is in one as shown in FIG Figure 1 hand-held power tool 52 shown is arranged.
  • the machine tool gear device 10a comprises a planetary gear 84a with a first, a second and a third gear stage 12a, 14a, 82a, one mode of operation of the planetary gear 84a being the mode of operation of the planetary gear 84 of FIG Figure 2 is equivalent to.
  • the machine tool transmission device 10a further comprises the switching element 16a, which comprises a first, a second and a third component 22a, 24a, 38a.
  • the first component 22a is designed as a switching ring 92a.
  • the second component 24a is designed as a ring gear 94a of the second gear stage 14a and the third component 38a is designed as a spring element 40a, the spring element 40a being designed as a helical spring 108a.
  • a total of two coil springs 108a are arranged between the switching ring 92a and the ring gear 94a of the second gear stage 14a, which are analogous to Figure 3 on a support element 46a of the switching ring 92a and on a support element 48a of the ring gear 94a of the second gear stage 14a.
  • the support element 46a of the switching ring 92a is designed such that the helical springs 108a can be supported on the support element 46a in every operating position of the switching ring 92a.
  • the support element 46a extends along the axial direction 42a over an essentially entire width of the switching ring 92a.
  • the coil springs 108a can additionally be guided in a groove which is arranged in an outer side of the ring gear 94a of the second gear stage 14a.
  • the switching ring 92a can be moved along a circumferential direction 20a relative to the ring gear 94a of the second gear stage 14a.
  • the switching ring 92a is movably supported along an axial direction 42a relative to the ring gear 94a of the second gear stage 14a.
  • the switching ring 92a When the planetary gear 84a is shifted from a first gear of the planetary gear 84a to a second gear of the planetary gear 84a, the switching ring 92a is moved along the axial direction 42a in the direction of the first gear stage 12a, with a locking element 36a of the switching ring 92a disengaging a locking geometry 146a arrives with a housing 54 of the cordless screwdriver 50 rotatably arranged component 148a.
  • the locking element 36a is formed in one piece with the support element 46a of the switching ring 92a.
  • the ring gear 94a of the second gear stage 14a maintains its position in the axial direction 42a during the entire shifting process.
  • the ring gear 94a of the second gear stage 14a is arranged along the axial direction 42a between a planet carrier 88a of the first gear stage 12a and a planet carrier 120a of the second gear stage 14a.
  • the ring gear 94a of the second gear stage 14a is thus axially secured and maintains its position in the axial direction 42a.
  • the switching ring 92a has an internal toothing 150a which is formed by the support element 46a and is oriented in the direction of the ring gear 94a of the second gear stage 14a.
  • the internal toothing 150a runs essentially along the entire circumferential direction 20a and at least partially encompasses the support element 46a of the switching ring 92a.
  • the internal toothing 150a engages an external toothing 138a of the planetary carrier 88a of the first gear stage 12a and here couples the ring gear 94a of the second gear stage 14a to the planetary carrier 88a of the first gear stage 12a.
  • a torque shock caused by different speeds between the shift ring 92a and the ring gear 94a of the second gear stage 14a during the engagement of the internal toothing 150a of the shifting ring 92a with the external toothing 138a of the planetary carrier 88a of the first gear stage 12a is dampened by the helical springs 108a.
  • the switching ring gear 26a is switched from the second gear of the planetary gear 84a to the first gear of the planetary gear 84a, the switching ring gear 26a is moved along the axial direction 42a in the direction of the third gear stage 82a.
  • the internal toothing 150a of the switching ring 92a disengages from the external toothing 138a of the planetary carrier 88a of the first gear stage 12a.
  • a coupling of the planetary gears 100a of the second gear stage 14a with the planet carrier 88a of the first gear stage 12a is canceled.
  • the locking element 36a of the switching ring 92a engages the locking geometry 146a of the non-rotatable component 148a in the housing 54, with the engagement of the locking element 36a of the switching ring 92a in the Locking geometry 146a of the component 148a arranged in the housing 54 so that it cannot rotate, a torque surge occurs between the switching ring 92a and the ring gear 94a of the second gear stage 14a.
  • This torque shock is dampened by means of the helical springs 108a between the switching ring 92a and the ring gear 94a of the second gear stage 14a.
  • the switching ring gear 26a is connected to the housing 54 in an essentially non-rotatable manner after the switching process.
  • the ring gear 94a of the second gear stage 14a retains during the entire shift from the second gear of the planetary gear 84a to the first gear of the planetary gear 84a its position in the axial direction 42a.

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Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Werkzeugmaschinengetriebevorrichtung nach dem Oberbegriff des Anspruchs 1.The invention is based on a machine tool gear device according to the preamble of claim 1.

Es sind bereits Werkzeugmaschinengetriebevorrichtungen mit einer ersten und einer zweiten Getriebestufe und mit einem Schaltelement bekannt, wobei das Schaltelement von einem Bediener mittels eines Betätigungselements bewegbar ist, in einer Betriebsposition die erste Getriebestufe entlang einer Umfangsrichtung umgibt und dazu vorgesehen ist, zwischen einer ersten und einer zweiten Betriebsposition zu schalten. Derartige Werkzeugmaschinengetriebevorrichtungen sind z.B. aus EP 1 464 427 A , US 5 339 908 A , EP 2 077 177 A und US 5 550 416 A bekannt.Machine tool transmission devices with a first and a second gear stage and with a switching element are already known, the switching element being movable by an operator by means of an actuating element, in an operating position surrounding the first gear stage along a circumferential direction and being provided between a first and a second To switch operating position. Such machine tool gear devices are, for example, from EP 1 464 427 A , U.S. 5,339,908 A , EP 2 077 177 A and U.S. 5,550,416 A known.

Vorteile der ErfindungAdvantages of the invention

Die Erfindung geht aus von einer Werkzeugmaschinengetriebevorrichtung mit zumindest einer ersten und einer zweiten Getriebestufe und mit einem Schaltelement, das von einem Bediener mittels eines Betätigungselements bewegbar ist, wobei das Schaltelement zumindest teilweise in zumindest einer Betriebsposition zumindest eine Getriebestufe entlang einer Umfangsrichtung umgibt und dazu vorgesehen ist, zwischen einer ersten und einer zweiten Betriebsposition zu schalten.The invention is based on a machine tool gear device with at least a first and a second gear stage and with a switching element that can be moved by an operator by means of an actuating element, the switching element at least partially surrounding at least one gear stage in at least one operating position along a circumferential direction and being provided for this purpose to switch between a first and a second operating position.

Es wird vorgeschlagen, dass das Schaltelement zumindest ein erstes Bauteil und ein zweites Bauteil umfasst. In diesem Zusammenhang soll unter "vorgesehen" insbesondere speziell ausgestattet und/oder speziell ausgelegt verstanden werden. Unter dem Begriff "Getriebestufe" soll hier insbesondere eine Anordnung von Zahnrädern, insbesondere von Planetenträgern, Hohlrädern, Planetenrädern und Sonnenrädern, in einem Getriebe, insbesondere einem Planetengetriebe, verstanden werden, die dazu vorgesehen ist, vorbestimmte Drehmomente und/oder Drehzahlen zu übertragen und/oder Drehmomente und/oder Drehzahlen zu untersetzen und/oder zu übersetzen. Vorzugsweise kann das Drehmoment und/oder die Drehzahl und/oder eine Untersetzung und/oder Übersetzung des Drehmoments und/oder der Drehzahl mittels des Schaltelements geändert werden. Unter einem "Betätigungselement" soll hier insbesondere ein Element und/oder Bauteil, insbesondere ein Element und/oder Bauteil, welches direkt von einem Bediener betätigt werden kann, verstanden werden, das mit einem weiteren Element und/oder Bauteil, insbesondere dem Schaltelement, in einer Wirkverbindung steht und das dazu vorgesehen ist, das weitere Element und/oder Bauteil von einem Zustand in einen anderen Zustand zu überführen. Vorzugsweise ist das Betätigungselement von einem zum Schaltelement separaten Bauteil gebildet. Das Betätigungselement steht mittels einer Außengeometrie des Schaltelements mit diesem in Wirkverbindung, somit können Kräfte von dem Betätigungselement auf das Schaltelement übertragen werden.It is proposed that the switching element comprises at least a first component and a second component. In this context, “provided” should be understood to mean in particular specially equipped and / or specially designed. The term "gear stage" is intended here in particular an arrangement of gears, in particular planetary carriers, ring gears, planet gears and sun gears, in a transmission, in particular a planetary gear, which is intended to transmit predetermined torques and / or speeds and / or to reduce torques and / or speeds and / or translate. The torque and / or the speed and / or a reduction and / or translation of the torque and / or the speed can preferably be changed by means of the switching element. An “actuating element” is to be understood here in particular as an element and / or component, in particular an element and / or component, which can be actuated directly by an operator, which is connected to a further element and / or component, in particular the switching element, in an operative connection and which is provided to transfer the further element and / or component from one state to another state. The actuating element is preferably formed by a component that is separate from the switching element. The actuating element is in operative connection with the switching element by means of an external geometry, thus forces can be transmitted from the actuating element to the switching element.

Eine "Betriebsposition" definiert hier insbesondere eine Position, wie beispielsweise eine Schaltposition, des Schaltelements innerhalb eines Getriebes, insbesondere eines Planetengetriebes, in der ein bestimmtes Drehmoment und/oder eine bestimmte Drehzahl über das Getriebe an eine Welle und/oder an Zahnräder des Getriebes übertragen werden können. Unter dem Begriff "Umfangsrichtung" soll hier insbesondere eine Richtung senkrecht zu einer Drehachse einer Abtriebswelle der Werkzeugmaschinengetriebevorrichtung verstanden werden, wobei die Umfangsrichtung umlaufend um die Drehachse der Abtriebswelle der Werkzeugmaschinengetriebevorrichtung verläuft. Der Ausdruck "entlang einer Umfangsrichtung umgibt" soll hier insbesondere eine Überdeckung in einer radialen Richtung von zumindest einem Element und/oder Bauteil mittels zumindest eines weiteren Elements und/oder Bauteils definieren. Hierbei verläuft die radiale Richtung senkrecht zur Drehachse der Abtriebswelle der Werkzeugmaschinengetriebevorrichtung. Vorzugsweise soll eine Anordnung von Zahnrädern, insbesondere von einem Planetenträger, einem Hohlrad, Planetenrädem und/oder einem Sonnenrad, durch zumindest ein Bauteil des Schaltelements radial überdeckt werden.An "operating position" here defines in particular a position, such as a shift position, of the shift element within a transmission, in particular a planetary gear, in which a specific torque and / or a specific speed is transmitted via the transmission to a shaft and / or to gears of the transmission can be. The term "circumferential direction" is to be understood here in particular as a direction perpendicular to an axis of rotation of an output shaft of the machine tool transmission device, the circumferential direction running circumferentially around the axis of rotation of the output shaft of the machine tool transmission device. The expression “surrounds along a circumferential direction” is intended to define, in particular, an overlap in a radial direction of at least one element and / or component by means of at least one further element and / or component. Here, the radial direction runs perpendicular to the axis of rotation of the output shaft of the machine tool gear device. Preferably, an arrangement of gears, in particular a planet carrier, a ring gear, planet gears and / or a sun gear, should be radially covered by at least one component of the switching element.

Vorteilhafterweise ist die Werkzeugmaschinengetriebevorrichtung für handgeführte Elektrowerkzeuge, wie z.B. Schrauber, Bohrschrauber und Schlagbohrmaschinen und insbesondere für Akku-Schrauber, Akku-Bohrschrauber und Akku-Schlagbohrmaschinen, vorgesehen, um eine Motordrehzahl von ca. 20 000 U/min in einen für eine Arbeitsspindel des handgeführten Elektrowerkzeugs sinnvollen Drehzahlbereich von ca. 150 U/min bis 2000 U/min zu untersetzen. Durch die erfindungsgemäße Ausgestaltung der Werkzeugmaschinengertiebevorrichtung kann ein Bediener besonders komfortabel zwischen einer ersten und einer zweiten Betriebsposition schalten, wobei von einem ersten Gang der Werkzeugmaschinengetriebevorrichtung mit einer geringen Drehzahl und einem hohen Drehmoment in einen zweiten Gang der Werkzeugmaschinengetriebevorrichtung mit einer hohen Drehzahl und einem geringen Drehmoment geschalten werden kann. Es kann hierbei besonders vorteilhaft ein Schaltvorgang während eines Betriebs der Werkzeugmaschinengetriebevorrichtung unter Last erreicht werden.Advantageously, the machine tool gear device for hand-held power tools, such as screwdrivers, drill / drivers and hammer drills and especially for cordless screwdrivers, cordless drills and cordless hammer drills, is provided to a motor speed of about 20,000 rpm in a work spindle of the hand-held Power tool to reduce a reasonable speed range of approx. 150 rpm to 2000 rpm. The inventive design of the machine tool gear device allows an operator to switch particularly comfortably between a first and a second operating position, switching from a first gear of the machine tool gear device with a low speed and a high torque to a second gear of the machine tool gear device with a high speed and a low torque can be. In this case, a switching process can be achieved in a particularly advantageous manner during operation of the machine tool transmission device under load.

Des Weiteren wird vorgeschlagen, dass das Schaltelement als Schalthohlrad ausgebildet ist. Besonders vorteilhaft ist das Schalthohlrad für ein Planetengetriebe vorgesehen. Durch eine derartige Ausgestaltung kann das Schaltelement konstruktiv einfach in bereits bestehende Werkzeugmaschinengetriebevorrichtungen integriert werden und es können vorteilhaft Kosten und Montageaufwand eingespart werden.It is also proposed that the switching element is designed as a switching ring gear. The switching ring gear is particularly advantageously provided for a planetary gear. By means of such a configuration, the switching element can be integrated in a structurally simple manner in already existing machine tool transmission devices and costs and assembly effort can advantageously be saved.

Vorteilhafterweise sind das erste Bauteil zumindest teilweise von einem ersten Ringelement und das zweite Bauteil zumindest teilweise von einem zweiten Ringelement gebildet. Vorzugsweise weisen das erste Ringelement und das zweite Ringelement jeweils eine Längserstreckung auf, welche entlang der gesamten Umfangsrichtung verläuft, so dass das erste Ringelement in sich geschlossen ist und das zweite Ringelement ebenfalls in sich geschlossen ist. Durch die erfindungsgemäße Ausgestaltung der Bauteile als Ringelement kann eine kompakte Werkzeugmaschinengetriebevorrichtung erreicht werden.The first component is advantageously at least partially formed by a first ring element and the second component is at least partially formed by a second ring element. Preferably, the first ring element and the second ring element each have a longitudinal extension which runs along the entire circumferential direction, so that the first ring element is self-contained and the second ring element is also self-contained. The inventive design of the components as a ring element makes it possible to achieve a compact machine tool transmission device.

Ferner wird vorgeschlagen, dass das erste Bauteil zumindest in einer Betriebsposition zumindest teilweise das zweite Bauteil entlang einer radialen Richtung überdeckt. Hierdurch kann ein vorhandener Bauraum vorteilhaft genutzt werden und es kann eine einfache Funktionskombination der Bauteile erreicht werden. Ferner kann ein hoher Bedienkomfort der Werkzeugmaschinengetriebevorrichtung erreicht werden.It is also proposed that the first component at least partially cover the second component along a radial direction, at least in an operating position. As a result, an existing installation space can be used advantageously and a simple functional combination of the components can be achieved. Furthermore, a high level of operating convenience of the machine tool gear device can be achieved.

Des Weiteren wird vorgeschlagen, dass das erste Bauteil und das zweite Bauteil einen Aufnahmebereich im Wesentlichen umschließen. Vorzugsweise verläuft der Aufnahmebereich ringsegmentartig entlang der Umfangsrichtung. Hierbei kann der Aufnahmebereich entlang der Umfangsrichtung in mehrere unabhängige Abschnitte unterteilt sein. Ferner kann der Aufnahmebereich in einer axialen Richtung und in radialer Richtung im Wesentlichen von dem ersten Bauteil und dem zweiten Bauteil überdeckt sein. Hierbei verläuft die axiale Richtung im Wesentlichen parallel zur Drehachse der Abtriebswelle der Werkzeugmaschinengetriebevorrichtung. Unter dem Begriff "im Wesentlichen parallel" soll hier insbesondere eine Richtung verstanden werden, die gegenüber einer Bezugsrichtung eine Abweichung insbesondere kleiner als 8°, vorteilhaft kleiner als 5° und besonders vorteilhaft kleiner als 2° aufweist. Mittels des Aufnahmebereichs kann vorteilhaft eine Schutzfunktion für ein Element und/oder ein Bauteil, das im Aufnahmebereich angeordnet ist, erreicht werden und ein Verschleiß des Elements und/oder des Bauteils kann vorteilhaft reduziert werden.It is further proposed that the first component and the second component essentially enclose a receiving area. The receiving area preferably runs in the manner of a ring segment along the circumferential direction. Here, the receiving area can be divided into several independent sections along the circumferential direction. Furthermore, the receiving area in an axial direction and in the radial direction can be substantially of the first component and the second component be covered. Here, the axial direction runs essentially parallel to the axis of rotation of the output shaft of the machine tool gear device. The term “essentially parallel” is to be understood here in particular as a direction which has a deviation from a reference direction, in particular less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 °. By means of the receiving area, a protective function for an element and / or a component that is arranged in the receiving area can advantageously be achieved and wear of the element and / or the component can advantageously be reduced.

Vorzugsweise ist das erste Bauteil relativ zu dem zweiten Bauteil beweglich gelagert. Besonders vorteilhaft kann sich das erste Bauteil entlang der Umfangsrichtung relativ zum zweiten Bauteil bewegen, um hierdurch vorteilhaft Drehmoment- und/oder Drehzahlunterschiede während eines Schaltvorgangs zwischen der ersten und der zweiten Betriebsposition ausgleichen zu können. Es ist jedoch ebenfalls möglich, dass das erste Bauteil sich entlang der axialen Richtung relativ zum zweiten Bauteil bewegen kann. Hierdurch kann ein konstruktiv einfach gestaltetes Schaltelement erreicht werden.The first component is preferably mounted so as to be movable relative to the second component. The first component can particularly advantageously move along the circumferential direction relative to the second component in order to be able to advantageously compensate for torque and / or speed differences during a switching process between the first and the second operating position. However, it is also possible that the first component can move relative to the second component along the axial direction. In this way, a structurally simple switching element can be achieved.

Vorteilhafterweise umfasst das erste Bauteil zumindest ein Verriegelungselement. Unter einem "Verriegelungselement" soll hier insbesondere ein Element und/oder Bauteil verstanden werden, das dazu vorgesehen ist, mittels eines Formschlusses und/oder Kraftschlusses eine Bewegung des Elements und/oder Bauteils relativ zu einem weiteren Element und/oder Bauteil zu verhindern. Vorzugsweise ist das Verriegelungselement dazu vorgesehen, eine Formschlussverbindung zu bilden. Besonders vorteilhaft ist das Verriegelungselement einstückig mit dem ersten Bauteil ausgebildet. Unter "einstückig" soll hier insbesondere einteilig und/oder aus einem Guss gebildet und/oder als ein Bauteil ausgebildet verstanden werden. Vorzugsweise ist das Verriegelungselement als eine Verriegelungsgeometrie in Form einer teilweisen Außenverzahnung, insbesondere einer Stirnradverzahnung, und/oder einer teilweisen Innenverzahnung des ersten Bauteils ausgebildet. Durch eine einstückige Ausführung können vorteilhaft Bauraum, Montageaufwand und Kosten eingespart werden. Ferner kann das erste Bauteil mittels des Verriegelungselements vorteilhaft in einer gewünschten Position gehalten werden. Die Verriegelungsgeometrie kann vorteilhaft als Verdrehsicherung des ersten Bauteils relativ zu einem Gehäuse, in dem die Werkzeugmaschinengetriebevorrichtung angeordnet ist, vorgesehen sein.The first component advantageously comprises at least one locking element. A “locking element” is to be understood here in particular as an element and / or component that is provided to prevent movement of the element and / or component relative to a further element and / or component by means of a form fit and / or force fit. The locking element is preferably provided to form a form-fit connection. The locking element is particularly advantageously designed in one piece with the first component. "One-piece" is to be understood here in particular as one-piece and / or formed from a cast and / or formed as a component. The locking element is preferably designed as a locking geometry in the form of a partial external toothing, in particular a spur gear toothing, and / or a partial internal toothing of the first component. A one-piece design can advantageously save installation space, installation effort and costs. Furthermore, the first component can advantageously be held in a desired position by means of the locking element. The locking geometry can advantageously be provided to prevent rotation of the first component relative to a housing in which the machine tool gear device is arranged.

Das Schaltelement weist zumindest ein weiteres Bauteil auf, das zumindest teilweise von einem Federelement gebildet ist. Ein "Federelement" definiert in diesem Zusammenhang ein federelastisches Element und/oder Bauteil, wie etwa eine Tellerfeder, ein Elastomer und/oder andere, dem Fachmann als sinnvoll erscheinende federelastische Elemente. Besonders vorteilhaft ist das Federelement jedoch als Schraubenfeder ausgebildet. Das Federelement weist vorzugsweise eine Funktion eines Dämpfungsmittels auf, wodurch eine vorteilhafte Schonung von Bauteilen erreicht werden kann und ein Verschleiß reduziert werden kann.The switching element has at least one further component which is at least partially formed by a spring element. A "spring element" is defined in this context a resilient element and / or component, such as a disc spring, an elastomer and / or other resilient elements that appear sensible to a person skilled in the art. However, the spring element is particularly advantageously designed as a helical spring. The spring element preferably has the function of a damping means, whereby an advantageous protection of components can be achieved and wear can be reduced.

Erfindungsgemäß wird vorgeschlagen, dass das erste Bauteil zumindest mittels des Federelements mit dem zweiten Bauteil in einer Wirkverbindung steht. Vorzugsweise ist das Federelement dazu vorgesehen, eine relative Bewegung zwischen den Bauteilen zu gewährleisten. Durch eine derartige Ausgestaltung kann eine vorteilhafte Funktionskombination der Bauteile erreicht werden. Besonders vorteilhaft kann ein Schaltvorgang während eines Betriebs der Werkzeugmaschinengetriebevorrichtung, wie insbesondere während einer Belastung durch ein Antriebsmoment, erreicht werden.According to the invention, it is proposed that the first component be in operative connection with the second component at least by means of the spring element. The spring element is preferably provided to ensure relative movement between the components. Such a configuration can achieve an advantageous functional combination of the components. A switching process can be achieved particularly advantageously during operation of the machine tool transmission device, such as, in particular, during a load by a drive torque.

Vorzugsweise ist das Federelement entlang zumindest einer Richtung zwischen dem ersten Bauteil und dem zweiten Bauteil angeordnet. Unter "zwischen" soll hier insbesondere eine Anordnung räumlich entlang der radialen Richtung und/oder der axialen Richtung verstanden werden. Bevorzugt ist das Federelement in dem von dem ersten Bauteil und dem zweiten Bauteil umgebenen Aufnahmebereich angeordnet. Es kann hierdurch eine Schutzfunktion des Federelements erreicht werden und ferner kann eine kompakte Anordnung der Bauteile in der Werkzeugmaschinengetriebevorrichtung erreicht werden.The spring element is preferably arranged along at least one direction between the first component and the second component. “Between” is to be understood here in particular as an arrangement spatially along the radial direction and / or the axial direction. The spring element is preferably arranged in the receiving area surrounded by the first component and the second component. In this way, a protective function of the spring element can be achieved and, furthermore, a compact arrangement of the components in the machine tool gear device can be achieved.

Ferner wird vorgeschlagen, dass das erste Bauteil zumindest ein Formschlusselement aufweist, das dazu vorgesehen ist, das zweite Bauteil in einer axialen Richtung zumindest teilweise zu hintergreifen. Unter einem "Formschlusselement" soll hier insbesondere ein Element und/oder ein Bauteil verstanden werden, das dazu vorgesehen ist, einen Formschluss mit einem weiteren Element und/oder Bauteil zu bilden. Vorzugsweise ist das Formschlusselement einstückig mit dem ersten Bauteil ausgebildet, wodurch vorteilhaft Bauraum und Bauteile eingespart werden können. Durch das Formschlusselement kann vorteilhaft eine sichere Kopplung der Bauteile erreicht werden und es kann eine konstruktiv einfache Werkzeugmaschinengetriebevorrichtung erreicht werden.It is further proposed that the first component has at least one form-locking element which is provided to at least partially engage behind the second component in an axial direction. A “form-fit element” is to be understood here in particular as an element and / or a component which is provided to form a form-fit connection with a further element and / or component. The form-locking element is preferably designed in one piece with the first component, which advantageously allows savings in terms of installation space and components. A secure coupling of the components can advantageously be achieved by the form-fit element and a machine tool gear device with a simple design can be achieved.

Vorteilhafterweise weist das erste Bauteil zumindest ein in einer radialen Richtung verlaufendes Stützelement auf, wobei das Stützelement in Richtung des zweiten Bauteils ausgerichtet ist. Unter einem "Stützelement" soll hier insbesondere ein Element und/oder Bauteil verstanden werden, das als eine Anlage und/oder ein Anschlag eines weiteren Elements und/oder Bauteils, insbesondere des Federelements, ausgebildet ist, um insbesondere Kräfte aufzunehmen und/oder zu übertragen und/oder in das weitere Element und/oder Bauteil einzuleiten. Vorzugsweise ist das Stützelement einstückig mit dem ersten Bauteil ausgebildet, womit eine vorteilhafte und konstruktiv einfache Krafteinleitung in das Bauteil erreicht werden kann.The first component advantageously has at least one support element running in a radial direction, the support element being oriented in the direction of the second component. A “support element” is to be understood here in particular as an element and / or component that is designed as a system and / or a stop of a further element and / or component, in particular the spring element, in order to absorb and / or transmit forces in particular and / or to introduce them into the further element and / or component. The support element is preferably formed in one piece with the first component, with which an advantageous and structurally simple introduction of force into the component can be achieved.

Des Weiteren wird vorgeschlagen, dass das zweite Bauteil zumindest ein in einer radialen Richtung verlaufendes Stützelement aufweist, wobei das Stützelement in Richtung des ersten Bauteils ausgerichtet ist. Vorzugsweise ist das Stützelement einstückig mit dem zweiten Bauteil ausgebildet. Hierdurch kann eine konstruktiv einfache Funktionskopplung der Bauteile erreicht werden, wie insbesondere eine Relativbewegung zwischen den Bauteilen, wobei die Relativbewegung durch das Federelement zur Verhinderung von Drehmomentstößen gedämpft werden kann. Ferner können vorteilhaft Bauraum, Bauteile, Montageaufwand und Kosten eingespart werden. Besonders vorteilhaft kann dies erreicht werden, wenn die Stützelemente dazu vorgesehen sind, zumindest teilweise eine Kraft von dem ersten Bauteil auf das zweite Bauteil zu übertragen.It is further proposed that the second component has at least one support element running in a radial direction, the support element being oriented in the direction of the first component. The support element is preferably designed in one piece with the second component. In this way, a structurally simple functional coupling of the components can be achieved, such as, in particular, a relative movement between the components, the relative movement being able to be dampened by the spring element to prevent torque surges. Furthermore, installation space, components, assembly effort and costs can advantageously be saved. This can be achieved particularly advantageously if the support elements are provided to at least partially transmit a force from the first component to the second component.

Zeichnungdrawing

Weitere Vorteile ergeben sich aus der folgenden Zeichnungsbeschreibung. In der Zeichnung sind Ausführungsbeispiele der Erfindung dargestellt. Die Zeichnung, die Beschreibung und die Ansprüche enthalten zahlreiche Merkmale in Kombination.Further advantages emerge from the following description of the drawings. Exemplary embodiments of the invention are shown in the drawing. The drawing, the description and the claims contain numerous features in combination.

Es zeigen:

Fig. 1
eine handgeführte Elektrowerkzeugmaschine mit einer erfindungsgemäßen Werkzeugmaschinengetriebevorrichtung in einer schematischen Darstellung,
Fig. 2
eine Detailansicht der erfindungsgemäßen Werkzeugmaschinengetriebevorrichtung in einer schematischen Darstellung,
Fig. 3
eine Detailansicht eines Schaltelements der erfindungsgemäßen Werkzeugmaschinengetriebevorrichtung in einem Schnitt durch das Schaltelement entlang der Linie II-II aus Figur 2 in einer schematischen Darstellung und
Fig. 4
eine Detailansicht einer weiteren Werkzeugmaschinengetriebevorrichtung mit einem alternativen Schaltelement in einer schematischen Darstellung.
Show it:
Fig. 1
a hand-held electric machine tool with a machine tool gear device according to the invention in a schematic representation,
Fig. 2
a detailed view of the machine tool gear device according to the invention in a schematic representation,
Fig. 3
a detailed view of a switching element of the machine tool transmission device according to the invention in a section through the switching element along the line II-II Figure 2 in a schematic representation and
Fig. 4
a detailed view of a further machine tool transmission device with an alternative switching element in a schematic representation.

Beschreibung der AusführungsbeispieleDescription of the exemplary embodiments

Figur 1 zeigt eine als Akku-Schrauber 50 ausgebildete, handgeführte Elektrowerkzeugmaschine 52 mit einer erfindungsgemäßen Werkzeugmaschinengetriebevorrichtung 10 in einer schematischen Darstellung. Der Akku-Schrauber 50 umfasst ein mehrteiliges Gehäuse 54, in dem die Werkzeugmaschinengetriebevorrichtung 10 und eine Motoreinheit 56 angeordnet sind, und eine Werkzeugaufnahme 60, in die ein Werkzeug 62 einsetzbar ist. Das Werkzeug 62 ist durch eine Abtriebswelle 64 (siehe hierzu Figur 2) der Werkzeugmaschinengetriebevorrichtung 10, die mit der Werkzeugaufnahme 60 in einer Wirkverbindung steht, rotatorisch antreibbar. Des Weiteren umfasst der Acku-Schrauber 50 einen an der Werkzeugaufnahme 60 angeordneten Stellring 66, welcher dazu vorgesehen ist, ein auf die Werkzeugaufnahme 60 übertragbares Drehmoment einzustellen. Eine Haupterstreckungsrichtung 68 des Akku-Schraubers 50 erstreckt sich von einer Seite 70 des Gehäuses 54, an der Kühlöffnungen 72 angeordnet sind, in Richtung der Werkzeugaufnahme 60. Am Gehäuse 54 ist im Wesentlichen senkrecht zur Haupterstreckungsrichtung 68 ein Handgriff 74 angeordnet, welcher zur Führung des Akku-Schraubers 50 durch einen Bediener vorgesehen ist. Der Handgriff 74 ist einstückig mit dem Gehäuse 54 ausgebildet. Am Handgriff 74 ist ein Akku-Pack 76 befestigt. Der Handgriff 74 umfasst ferner einen Betätigungsschalter 78 mit elektrischen Kontakten, die bei einer Betätigung des Betätigungsschalters 78 durch den Bediener dazu vorgesehen sind, eine elektrische Versorgung der Motoreinheit 56 durch das Akku-Pack 76 herzustellen oder zu unterbrechen. Des Weiteren ist an einer dem Handgriff 74 abgewandten Seite des Gehäuses 54 ein Betätigungselement 18 angeordnet, das als Schalter 80 ausgebildet ist. Der Schalter 80 ist axial entlang der Haupterstreckungsrichtung 68 des Akku-Schraubers 50 verschiebbar gelagert. Mittels des Schalters 80 ist ein Schaltelement 16 (siehe hierzu Figur 2) der Werkzeugmaschinengetriebevorrichtung 10 von dem Bediener entlang einer axialen Richtung 42 bewegbar. Die axiale Richtung 42 verläuft im Wesentlichen parallel zur Haupterstreckungsrichtung 68 des Akku-Schraubers 50. Figure 1 shows a hand-operated electric machine tool 52 designed as a cordless screwdriver 50 with a machine tool gear device 10 according to the invention in a schematic representation. The cordless screwdriver 50 comprises a multi-part housing 54, in which the machine tool gear device 10 and a motor unit 56 are arranged, and a tool holder 60 into which a tool 62 can be inserted. The tool 62 is driven by an output shaft 64 (see in this regard Figure 2 ) the machine tool gear device 10, which is operatively connected to the tool holder 60, can be driven in rotation. Furthermore, the Acku screwdriver 50 comprises an adjusting ring 66 which is arranged on the tool holder 60 and is provided to set a torque that can be transmitted to the tool holder 60. A main direction of extent 68 of the cordless screwdriver 50 extends from a side 70 of the housing 54, on which cooling openings 72 are arranged, in the direction of the tool holder 60 Cordless screwdriver 50 is provided by an operator. The handle 74 is formed in one piece with the housing 54. A battery pack 76 is attached to the handle 74. The handle 74 further comprises an actuation switch 78 with electrical contacts which, when the actuation switch 78 is actuated by the operator, are provided to establish or interrupt an electrical supply to the motor unit 56 by the battery pack 76. Furthermore, an actuating element 18, which is designed as a switch 80, is arranged on a side of the housing 54 facing away from the handle 74. The switch 80 is mounted so as to be axially displaceable along the main direction of extent 68 of the cordless screwdriver 50. By means of the switch 80, a switching element 16 (see in this regard Figure 2 ) of the machine tool transmission device 10 can be moved by the operator along an axial direction 42. The axial direction 42 runs essentially parallel to the main direction of extent 68 of the cordless screwdriver 50.

Figur 2 zeigt eine Detailansicht der erfindungsgemäßen Werkzeugmaschinengetriebevorrichtung 10 in einer schematischen Darstellung. Die Werkzeugmaschinengetriebevorrichtung 10 umfasst ein Planetengetriebe 84 mit einer ersten, einer zweiten und einer dritten Getriebestufe 12, 14, 82. Die Getriebestufen 12, 14, 82 umfassen jeweils ein Hohlrad 86, 94, 152 einen Planetenträger 88, 120, 124 und mehrere Planetenräder 90, 100, 122, welche auf dem Planetenträger 88, 120, 124 angeordnet sind. Ferner umfasst die Werkzeugmaschinengetriebevorrichtung 10 das Schaltelement 16, das von dem Bediener mittels des Schalters 80 bewegbar ist. Das Schaltelement 16 ist als Schalthohlrad 26 ausgebildet. Das Schalthohlrad 26 umfasst ein erstes Bauteil 22 und ein zweites Bauteil 24. Das erste Bauteil 22 ist von einem ersten Ringelement 28 gebildet, das als Schaltring 92 ausgebildet ist. Das zweite Bauteil 24 ist von einem zweiten Ringelement 30 gebildet, das als Hohlrad 94 der zweiten Getriebestufe 14 ausgebildet ist. Der Schaltring 92 überdeckt in einer ersten Betriebsposition das Hohlrad 94 der zweiten Getriebestufe 14 entlang einer radialen Richtung 32, welche senkrecht zu einer Drehachse 96 der Abtriebswelle 64 verläuft. Das Hohlrad 94 der zweiten Getriebestufe 14 umfasst eine Innenverzahnung 98, mit der die Planetenräder 100 der zweiten Getriebestufe 14 kämmen. Ferner umgibt der Schaltring 92 in der ersten Betriebsposition der Werkzeugmaschinengetriebevorrichtung 10 die zweite Getriebestufe 14 des Planetengetriebes 84 entlang einer Umfangsrichtung 20, welche senkrecht zur Drehachse 96 der Abtriebswelle 64 verläuft und sich umlaufend um die Drehachse 96 der Abtriebswelle 64 erstreckt. Figure 2 shows a detailed view of the machine tool transmission device 10 according to the invention in a schematic representation. The machine tool gear device 10 includes a Planetary gear 84 with a first, a second and a third gear stage 12, 14, 82. The gear stages 12, 14, 82 each include a ring gear 86, 94, 152, a planet carrier 88, 120, 124 and several planet gears 90, 100, 122, which are arranged on the planet carrier 88, 120, 124. The machine tool transmission device 10 further comprises the switching element 16, which can be moved by the operator by means of the switch 80. The switching element 16 is designed as a switching ring gear 26. The switching ring gear 26 comprises a first component 22 and a second component 24. The first component 22 is formed by a first ring element 28, which is designed as a switching ring 92. The second component 24 is formed by a second ring element 30, which is designed as a ring gear 94 of the second gear stage 14. In a first operating position, the switching ring 92 covers the ring gear 94 of the second gear stage 14 along a radial direction 32 which runs perpendicular to an axis of rotation 96 of the output shaft 64. The ring gear 94 of the second gear stage 14 comprises an internal toothing 98 with which the planet gears 100 of the second gear stage 14 mesh. Furthermore, in the first operating position of the machine tool gear device 10, the switching ring 92 surrounds the second gear stage 14 of the planetary gear 84 along a circumferential direction 20 which runs perpendicular to the axis of rotation 96 of the output shaft 64 and extends circumferentially around the axis of rotation 96 of the output shaft 64.

Des Weiteren ist das Schalthohlrad 26 dazu vorgesehen, zwischen der ersten Betriebsposition und einer zweiten Betriebsposition der Werkzeugmaschinengetriebevorrichtung 10 zu schalten. Hierbei bildet die erste Betriebsposition einen ersten Gang des Planetengetriebes 84. Im ersten Gang werden im Betrieb des Planetengetriebes 84 geringe Drehzahlen und ein hohes Drehmoment an die Abtriebswelle 64 und somit an das Werkzeug 62 in der Werkzeugaufnahme 60 übertragen. Die zweite Betriebsposition bildet einen zweiten Gang des Planetengetriebes 84. Im zweiten Gang werden im Betrieb des Planetengetriebes 84 hohe Drehzahlen und ein geringes Drehmoment an die Abtriebswelle 64 übertragen. Während eines Schaltvorgangs in einem Betrieb des Akku-Schraubers 50 wird das Schalthohlrad 26 von dem Bediener mittels des Schalters 80 entlang der axialen Richtung 42 bewegt. Die axiale Richtung 42 verläuft hierbei parallel zur Drehachse 96 der Abtriebswelle 64 der Werkzeugmaschinengetriebevorrichtung 10.Furthermore, the switching ring gear 26 is provided to switch between the first operating position and a second operating position of the machine tool transmission device 10. Here, the first operating position forms a first gear of the planetary gear 84. In the first gear, low speeds and a high torque are transmitted to the output shaft 64 and thus to the tool 62 in the tool holder 60 when the planetary gear 84 is in operation. The second operating position forms a second gear of the planetary gear 84. In the second gear, high speeds and a low torque are transmitted to the output shaft 64 when the planetary gear 84 is in operation. During a switching process in an operation of the cordless screwdriver 50, the switching ring gear 26 is moved by the operator by means of the switch 80 along the axial direction 42. The axial direction 42 here runs parallel to the axis of rotation 96 of the output shaft 64 of the machine tool transmission device 10.

Das Schalthohlrad 26 ist im ersten Gang des Planetengetriebes 84 mittels eines ersten Verriegelungselements 36 des Schaltrings 92 verdrehsicher mit dem Gehäuse 54 des Akku-Schraubers 50 verbunden. Hierbei ist das erste Verriegelungselement 36 in Form einer ersten Außenverzahnung 102 ausgebildet. Die erste Außenverzahnung 102 verläuft entlang der Umfangsrichtung 20 an einer Außenseite 104 des Schaltrings 92 und erstreckt sich in radialer Richtung 32 in Richtung des Gehäuses 54. Das Gehäuse 54 umfasst dementsprechend eine Innenverzahnung 106, in welche die erste Außenverzahnung 102 des Schaltrings 92 eingreift.The switching ring gear 26 is connected in the first gear of the planetary gear 84 by means of a first locking element 36 of the switching ring 92 in a rotationally secure manner to the housing 54 of the cordless screwdriver 50. Here, the first locking element 36 is designed in the form of a first external toothing 102. The first external toothing 102 runs along the circumferential direction 20 on an outer side 104 of the switching ring 92 and extends in the radial direction 32 in the direction of the housing 54. The housing 54 accordingly comprises an internal toothing 106 in which the first external toothing 102 of the switching ring 92 engages.

Ferner umfasst das Schalthohlrad 26 einen Aufnahmebereich 34, der im Wesentlichen von dem Schaltring 92 und dem Hohlrad 94 der zweiten Getriebestufe 14 umschlossen ist. Der Schaltring 92 und das Hohlrad 94 der zweiten Getriebestufe 14 überdecken hierbei den Aufnahmebereich 34 entlang der radialen Richtung 32 und der axialen Richtung 42. Der Aufnahmebereich 34 ist dazu vorgesehen, zumindest ein weiteres Bauteil 38 des Schalthohlrads 26 aufzunehmen. Das weitere Bauteil 38 ist als Federelement 40 ausgebildet. Insgesamt sind zwei Federelemente 40, die als Schraubenfedern 108 ausgebildet sind, im Aufnahmebereich 34 angeordnet. Hierzu ist der Aufnahmebereich 34 entlang der Umfangsrichtung 20 in zwei räumlich getrennte Abschnitte 110 unterteilt, wobei in jedem Abschnitt 110 eine der Schraubenfedern 108 angeordnet ist. Es ist jedoch denkbar, dass der Aufnahmebereich 34 in mehr als zwei Abschnitte 110 unterteilt ist und eine entsprechende Anzahl an Schraubenfedern 108 in den Abschnitten 110 angeordnet sind. Zur Unterteilung des Aufnahmebereichs 34 weist der Schaltring 92 hierbei ein in radialer Richtung 32 verlaufendes Stützelement 46 auf, welches in Richtung des Hohlrads 94 der zweiten Getriebestufe 14 ausgerichtet ist. Es ist jedoch denkbar, dass der Schaltring 92 je nach Anzahl der Abschnitte 110 mehrere Stützelemente 46 zur Unterteilung aufweist. Ferner weist das Hohlrad 94 der zweiten Getriebestufe 14 ein Stützelement 48 auf, das in Richtung des Schaltrings 92 ausgerichtet ist. Der Fachmann wird das Hohlrad 94 der zweiten Getriebestufe 14 ebenfalls je nach Anzahl der Abschnitte 110 mit einer entsprechenden Anzahl von Stützelementen 48 versehen. Die Schraubenfedern 108 stützen sich jeweils mit einem Ende 112 an dem Stützelement 46 des Schaltrings 92 ab und mit einem jeweils gegenüberliegenden Ende 114 stützen sich die Schraubenfedern 108 an dem Stützelement 48 des Hohlrads 94 der zweiten Getriebestufe 14 ab. Somit steht der Schaltring 92 mittels der Schraubenfedern 108 in einer Wirkverbindung mit dem Hohlrad 94 der zweiten Getriebestufe 14. Mittels der Stützelemente 46, 48 und der Schraubenfedern 108 wird eine Kraft von dem Schaltring 92 auf das Hohlrad 94 der zweiten Getriebestufe 14 übertragen. Der Schaltring 92 ist hierbei über einen Winkelbereich mit einem Winkel α von zumindest 90° entlang der Umfangsrichtung 20 relativ zum Hohlrad 94 der zweiten Getriebestufe 14 aufgrund der Anordnung der Schraubenfedern 108 im Aufnahmebereich 34 beweglich gelagert (siehe hierzu Figur 3). Die Schraubenfedern 108 sind entlang der axialen Richtung 42 zwischen dem Schaltring 92 und dem Hohlrad 94 der zweiten Getriebestufe 14 angeordnet. Ferner sind die Schraubenfedern 108 entlang der radialen Richtung 32 zwischen dem Schaltring 92 und dem Hohlrad 94 der zweiten Getriebestufe 14 angeordnet.The switching ring gear 26 further comprises a receiving area 34 which is essentially enclosed by the switching ring 92 and the ring gear 94 of the second gear stage 14. The shift ring 92 and the ring gear 94 of the second gear stage 14 cover the receiving area 34 along the radial direction 32 and the axial direction 42. The receiving area 34 is provided to receive at least one further component 38 of the shift ring gear 26. The further component 38 is designed as a spring element 40. A total of two spring elements 40, which are designed as helical springs 108, are arranged in the receiving area 34. For this purpose, the receiving area 34 is divided into two spatially separate sections 110 along the circumferential direction 20, one of the helical springs 108 being arranged in each section 110. However, it is conceivable that the receiving area 34 is divided into more than two sections 110 and a corresponding number of helical springs 108 are arranged in the sections 110. To subdivide the receiving area 34, the switching ring 92 has a support element 46 running in the radial direction 32, which is oriented in the direction of the ring gear 94 of the second gear stage 14. However, it is conceivable that the switching ring 92 has several support elements 46 for subdivision, depending on the number of sections 110. Furthermore, the ring gear 94 of the second gear stage 14 has a support element 48 which is oriented in the direction of the shift ring 92. The person skilled in the art will also provide the ring gear 94 of the second gear stage 14 with a corresponding number of support elements 48 depending on the number of sections 110. The coil springs 108 are each supported with one end 112 on the support element 46 of the switching ring 92, and with an opposite end 114 the coil springs 108 are supported on the support element 48 of the ring gear 94 of the second gear stage 14. The switching ring 92 is therefore operatively connected to the ring gear 94 of the second gear stage 14 by means of the helical springs 108. A force is transmitted from the switching ring 92 to the ring gear 94 of the second gear stage 14 by means of the support elements 46, 48 and the helical springs 108. The switching ring 92 is movably supported here over an angular range with an angle α of at least 90 ° along the circumferential direction 20 relative to the ring gear 94 of the second gear stage 14 due to the arrangement of the helical springs 108 in the receiving area 34 (see also FIG Figure 3 ). The coil springs 108 are arranged along the axial direction 42 between the switching ring 92 and the ring gear 94 of the second gear stage 14. Furthermore, the coil springs 108 are arranged along the radial direction 32 between the switching ring 92 and the ring gear 94 of the second gear stage 14.

Im Betrieb des Akku-Schraubers 50 wird die Werkzeugmaschinengetriebevorrichtung 10 von einer Welle der Motoreinheit 56, auf der ein Antriebsritzel 116 der Werkzeugmaschinengetriebevorrichtung 10 angeordnet ist, angetrieben. Das Antriebsritzel 116 greift hierbei in die Planetenräder 90 der ersten Getriebestufe 12 ein. Die Planetenräder 90 der ersten Getriebestufe 12 kämmen mit einer Innenverzahnung 118, die entlang der Umfangsrichtung 20 in einem zum Gehäuse 54 verdrehsicher angeordneten Hohlrad 86 der ersten Getriebestufe 12 angeordnet ist, und treiben den Planetenträger 88 der ersten Getriebestufe 12 an. Ein beliebiger Punkt der Planetenräder 90 der ersten Getriebestufe 12 führt hierbei eine von zwei Drehbewegungen überlagerte Bewegung aus. Eine erste der zwei überlagerten Drehbewegungen ist eine Eigenrotation der Planetenräder 90 der ersten Getriebestufe 12 und die zweite Drehbewegung ist eine Rotation der Planetenräder 90 der ersten Getriebestufe 12 um eine Drehachse des Antriebsritzels 116 der Werkzeugmaschinengetriebevorrichtung 10.When the cordless screwdriver 50 is in operation, the machine tool gear device 10 is driven by a shaft of the motor unit 56 on which a drive pinion 116 of the machine tool gear device 10 is arranged. The drive pinion 116 engages in the planet gears 90 of the first gear stage 12. The planet gears 90 of the first gear stage 12 mesh with an internal toothing 118, which is arranged along the circumferential direction 20 in a ring gear 86 of the first gear stage 12 that is non-rotatable relative to the housing 54, and drive the planet carrier 88 of the first gear stage 12. Any point on the planetary gears 90 of the first gear stage 12 executes a movement superimposed by two rotary movements. A first of the two superimposed rotary movements is a rotation of the planet gears 90 of the first gear stage 12 and the second rotary movement is a rotation of the planet gears 90 of the first gear stage 12 about an axis of rotation of the drive pinion 116 of the machine tool gear device 10.

Im ersten Gang des Planetengetriebes 84 treibt der Planetenträger 88 der ersten Getriebestufe 12 die Planetenräder 100 der zweiten Getriebestufe 14 an, wobei ein beliebiger Punkt der Planetenräder 100 der zweiten Getriebestufe 14 eine von zwei Drehbewegungen überlagerte Bewegung ausführt. Eine erste der zwei überlagerten Drehbewegungen ist eine Eigenrotation der Planetenräder 100 der zweiten Getriebestufe 14 und die zweite Drehbewegung ist eine Rotation der Planetenräder 100 der zweiten Getriebestufe 14 um eine Drehachse des Planetenträgers 88 der ersten Getriebestufe 12. Die von zwei Drehbewegungen überlagerte Bewegung der Planetenräder 100 der zweiten Getriebestufe 14 wird durch eine verdrehsichere Anordnung des Schaltrings 92 und somit des Hohlrads 94 der zweiten Getriebestufe 14 im Gehäuse 54 ermöglicht. Das Hohlrad 94 der zweiten Getriebestufe 14 wird mittels der Schraubenfedern 108 und der Stützelemente 46, 48 nach einer geringen Relativbewegung zum Schaltring 92 und/oder Gehäuse 54 im Wesentlichen verdrehsicher zum Gehäuse 54 positioniert. Die Bewegung der Planetenräder 100 der zweiten Getriebestufe 14 treibt einen Planetenträger 120 der zweiten Getriebestufe 14 an. Dieser wiederum treibt Planetenräder 122 der dritten Getriebestufe 82 an, welche nach einem Prinzip, das einem Antrieb der ersten Getriebestufe 12 entspricht, einen Planetenträger 124 der dritten Getriebestufe 82 antreibt. Dieser steht mittels einer Drehmomentkupplung 126 mit der Abtriebswelle 64 der Werkzeugmaschinengetriebevorrichtung 10 in Verbindung. Die Drehmomentkupplung 126 ist hierbei mittels des Stellrings 66 auf ein vom Bediener gewünschtes, maximal übertragbares Drehmoment einstellbar. Die Funktionsweise der Drehmomentkupplung 126 erfolgt auf eine dem Fachmann bereits bekannte Art und Weise.In the first gear of the planetary gear 84, the planet carrier 88 of the first gear stage 12 drives the planet gears 100 of the second gear stage 14, any point on the planet gears 100 of the second gear stage 14 executing a movement superimposed by two rotary movements. A first of the two superimposed rotary movements is a natural rotation of the planet gears 100 of the second gear stage 14 and the second rotary movement is a rotation of the planet gears 100 of the second gear stage 14 about an axis of rotation of the planet carrier 88 of the first gear stage 12. The movement of the planet gears 100 superimposed by two rotary movements the second gear stage 14 is made possible by a non-rotatable arrangement of the switching ring 92 and thus the ring gear 94 of the second gear stage 14 in the housing 54. The ring gear 94 of the second gear stage 14 is positioned by means of the helical springs 108 and the support elements 46, 48 after a slight movement relative to the switching ring 92 and / or the housing 54 in an essentially non-rotatable manner with respect to the housing 54. The movement of the planet gears 100 of the second gear stage 14 drives a planet carrier 120 of the second gear stage 14. This in turn drives planetary gears 122 of the third gear stage 82, which drives a planet carrier 124 of the third gear stage 82 according to a principle that corresponds to a drive of the first gear stage 12. This is connected to the output shaft 64 of the machine tool transmission device 10 by means of a torque coupling 126. The torque coupling 126 can be adjusted by means of the adjusting ring 66 to a maximum transmittable torque desired by the operator. The mode of operation of the torque clutch 126 takes place in a manner already known to the person skilled in the art.

Während eines Schaltvorgangs der Werkzeugmaschinengetriebevorrichtung 10 von dem ersten Gang in den zweiten Gang des Planetengetriebes 84 wird das Schalthohlrad 26 von dem Bediener mittels des Schalters 80 entlang der axialen Richtung 42 in Richtung der ersten Getriebestufe 12 bewegt. Hierzu weist der Schalter 80 einen Bolzen 128 auf, der in eine in Umfangsrichtung 20 umlaufende Nut 130 des Schaltrings 92 eingreift. Bei einer Bewegung des Schaltrings 92 entlang der axialen Richtung 42 werden die zwei Schraubenfedern 108 und das Hohlrad 86 der ersten Getriebestufe 12 ebenfalls entlang der axialen Richtung 42 bewegt. Der Schaltring 92 weist hierzu ein Formschlusselement 44 auf, das dazu vorgesehen ist, das Hohlrad 94 der zweiten Getriebestufe 14 zu hintergreifen. Das Formschlusselement 44 ist als separates Bauteil ausgebildet, das mit dem Schaltring 92 fest verbunden ist. Die Verbindung des Formschlusselements 44 erfolgt hierbei auf eine, dem Fachmann als sinnvoll erscheinende Art und Weise, wie z.B. einer Schraubverbindung, einer Klebeverbindung usw. Bei der Bewegung des Schalthohlrads 26 entlang der axialen Richtung 42 in Richtung der ersten Getriebestufe 12 gelangt die erste Außenverzahnung 102 des Schaltrings 92 außer Eingriff der Innenverzahnung 106 des Gehäuses 54. Das Hohlrad 94 der zweiten Getriebestufe 14 wird daraufhin durch die Planetenräder 100 der zweiten Getriebestufe 14 beschleunigt und in Rotation versetzt, wobei der Schaltring 92 mittels eines Zusammenspiels der Schraubenfedern 108 und der Stützelemente 46, 48 ebenfalls beschleunigt und in Rotation versetzt wird.During a shift operation of the machine tool transmission device 10 from the first gear to the second gear of the planetary gear 84, the switching ring gear 26 is moved by the operator by means of the switch 80 along the axial direction 42 in the direction of the first gear stage 12. For this purpose, the switch 80 has a bolt 128 which engages in a groove 130 of the switching ring 92 running around in the circumferential direction 20. When the switching ring 92 moves along the axial direction 42, the two helical springs 108 and the ring gear 86 of the first gear stage 12 are also moved along the axial direction 42. For this purpose, the switching ring 92 has a form-locking element 44 which is provided to engage behind the ring gear 94 of the second gear stage 14. The form-fit element 44 is designed as a separate component that is firmly connected to the switching ring 92. The interlocking element 44 is connected in a manner that appears sensible to a person skilled in the art, such as a screw connection, an adhesive connection, etc. of the switching ring 92 out of engagement with the internal toothing 106 of the housing 54. The ring gear 94 of the second gear stage 14 is then accelerated and set in rotation by the planet gears 100 of the second gear stage 14, the switching ring 92 by means of an interaction of the helical springs 108 and the support elements 46, 48 is also accelerated and set in rotation.

Des Weiteren umfasst der Schaltring 92 ein zweites Verriegelungselement 132 in Form einer zweiten Außenverzahnung 134, die in Umfangsrichtung 20 an einer der ersten Getriebestufe 12 zugewandten Seite 136 des Schaltrings 92 verläuft und entlang der axialen Richtung 42 in Richtung der ersten Getriebestufe 12 ausgerichtet ist. Die zweite Außenverzahnung 134 weist steile Flanken auf, die dazu vorgesehen sind, mit Flanken einer Außenverzahnung 138 des Planetenträgers 88 der ersten Getriebestufe 12 zu kämmen, um somit den Schaltring 92 rotatorisch mit dem Hohlrad 86 der ersten Getriebestufe 12 zu koppeln. Die Außenverzahnung 138 des Planetenträgers 88 der ersten Getriebestufe 12 verläuft hierzu in Umfangsrichtung 20 an einer Außenseite 140 des Planetenträgers 88 der ersten Getriebestufe 12 und ist entlang der axialen Richtung 42 in Richtung der zweiten Getriebestufe 14 ausgerichtet. Es ist jedoch denkbar, dass das Schalthohlrad 26 ein zweites Verriegelungselement 132 in Form einer Innenverzahnung 150 umfasst, die in Umfangsrichtung 20 an einer Innenseite 142 des Schaltrings 92 verläuft und entlang der radialen Richtung 32 in Richtung des Hohlrads 94 der zweiten Getriebestufe 14 ausgerichtet ist. Hierbei würde die Innenverzahnung 150 mit einer Außenverzahnung 138 des Planetenträgers 88 der ersten Getriebestufe 12 kämmen, die in Umfangsrichtung 20 an einer Stirnseite 144 des Planetenträgers 88 der ersten Getriebestufe 12 verläuft und entlang der radialen Richtung 32 in Richtung des Gehäuses 54 ausgerichtet wäre.Furthermore, the switching ring 92 comprises a second locking element 132 in the form of a second external toothing 134, which runs in the circumferential direction 20 on a side 136 of the switching ring 92 facing the first gear stage 12 and is aligned along the axial direction 42 in the direction of the first gear stage 12. The second external toothing 134 has steep flanks which are provided to mesh with the flanks of an external toothing 138 of the planetary carrier 88 of the first gear stage 12 in order to rotationally couple the switching ring 92 to the ring gear 86 of the first gear stage 12. The external toothing 138 of the planet carrier 88 of the first gear stage 12 runs in the circumferential direction 20 on an outer side 140 of the planet carrier 88 of the first gear stage 12 and is aligned along the axial direction 42 in the direction of the second gear stage 14. However, it is conceivable that the switching ring gear 26 comprises a second locking element 132 in the form of internal teeth 150, which runs in the circumferential direction 20 on an inner side 142 of the switching ring 92 and is aligned along the radial direction 32 in the direction of the ring gear 94 of the second gear stage 14. The internal toothing 150 would mesh with an external toothing 138 of the planetary carrier 88 of the first gear stage 12, which runs in the circumferential direction 20 on an end face 144 of the planetary carrier 88 of the first gear stage 12 and would be aligned along the radial direction 32 in the direction of the housing 54.

Bei einem Eingriff der zweiten Außenverzahnung 134 und/oder Innenverzahnung 150 des Schaltrings 92 in die Außenverzahnung 138 des Planetenträgers 88 der ersten Getriebestufe 12 entsteht aufgrund unterschiedlicher Drehzahlen des Schaltrings 92 und des Planetenträgers 88 der ersten Getriebestufe 12 ein Drehmomentstoß zwischen dem Schaltring 92 und dem Hohlrad 94 der zweiten Getriebestufe 14. Dieser Drehmomentstoß wird mittels der Schraubenfedern 108 zwischen dem Schaltring 92 und dem Hohlrad 94 der zweiten Getriebestufe 14 gedämpft. Hierbei bewegt sich der Schaltring 92 rotatorisch relativ zum Hohlrad 94 der zweiten Getriebestufe 14 durch eine Verformung der Schraubenfedern 108. Ferner ist das Hohlrad 94 der zweiten Getriebestufe 14 ebenfalls mittels der Schraubenfedern 108 im Wesentlichen rotatorisch mit dem Hohlrad 86 der ersten Getriebestufe 12 gekoppelt. Somit ist im zweiten Gang des Planetengetriebes 84 das Schalthohlrad 26 mit den Planetenrädern 100 der zweiten Getriebestufe 14 und mit dem Planetenträger 88 der ersten Getriebestufe 12 gekoppelt.When the second external toothing 134 and / or internal toothing 150 of the switching ring 92 meshes with the external toothing 138 of the planetary carrier 88 of the first gear stage 12, a torque surge occurs between the switching ring 92 and the ring gear due to different speeds of the switching ring 92 and the planetary carrier 88 of the first gear stage 12 94 of the second gear stage 14. This torque surge is dampened by means of the helical springs 108 between the switching ring 92 and the ring gear 94 of the second gear stage 14. Here, the switching ring 92 moves rotationally relative to the ring gear 94 of the second gear stage 14 by deformation of the coil springs 108. Furthermore, the ring gear 94 of the second gear stage 14 is also essentially rotationally coupled to the ring gear 86 of the first gear stage 12 by means of the coil springs 108. Thus, in the second gear of the planetary gear 84, the shift ring gear 26 is coupled to the planet gears 100 of the second gear stage 14 and to the planet carrier 88 of the first gear stage 12.

Während eines Schaltvorgangs der Werkzeugmaschinengetriebevorrichtung 10 von dem zweiten Gang in den ersten Gang des Planetengetriebes 84 wird das Schalthohlrad 26 von dem Bediener mittels des Schalters 80 entlang der axialen Richtung 42 in Richtung der dritten Getriebestufe 82 bewegt. Die zweite Außenverzahnung 134 des Schaltrings 92 gelangt hierbei außer Eingriff der Außenverzahnung 138 des Planetenträgers 88 der ersten Getriebestufe 12, wodurch eine Kopplung der Planetenräder 100 der zweiten Getriebestufe 14 mit dem Planetenträger 88 der ersten Getriebestufe 12 aufgehoben wird. Durch die Bewegung des Schalthohlrads 26 entlang der axialen Richtung 42 in Richtung der dritten Getriebestufe 82 gelangt die erste Außenverzahnung 102 des Schaltrings 92 in Eingriff der Innenverzahnung 106 des Gehäuses 54, wobei durch den Eingriff der Außenverzahnung 102 des Schaltrings 92 in die Innenverzahnung 106 des Gehäuses 54 ein Drehmomentstoß zwischen dem Schaltring 92 und dem Hohlrad 94 der zweiten Getriebestufe 14 entsteht. Dieser Drehmomentstoß wird mittels der Schraubenfedern 108 zwischen dem Schaltring 92 und dem Hohlrad 94 der zweiten Getriebestufe 14 gedämpft. Das Schalthohlrad 26 ist nach dem Schaltvorgang im Wesentlichen verdrehsicher mit dem Gehäuse 54 verbunden.During a shift operation of the machine tool transmission device 10 from the second gear to the first gear of the planetary gear 84, the switching ring gear 26 is moved by the operator by means of the switch 80 along the axial direction 42 in the direction of the third gear stage 82. The second external toothing 134 of the switching ring 92 disengages the external toothing 138 of the planetary carrier 88 of the first gear stage 12, whereby a coupling of the planetary gears 100 of the second gear stage 14 with the planetary carrier 88 of the first gear stage 12 is canceled. By moving the switching ring gear 26 along the axial direction 42 in the direction of the third gear stage 82, the first external toothing 102 of the switching ring 92 engages the internal toothing 106 of the housing 54, with the engagement of the external toothing 102 of the switching ring 92 in the internal toothing 106 of the housing 54, a torque surge occurs between the switching ring 92 and the ring gear 94 of the second gear stage 14. This torque surge is dampened by means of the helical springs 108 between the switching ring 92 and the ring gear 94 of the second gear stage 14. The switching ring gear 26 is connected to the housing 54 in an essentially non-rotatable manner after the switching process.

In Figur 4 ist ein alternatives Ausführungsbeispiel dargestellt. Im Wesentlichen gleich bleibende Bauteile, Merkmale und Funktionen sind grundsätzlich mit den gleichen Bezugszeichen beziffert. Zur Unterscheidung der Ausführungsbeispiele ist jedoch den Bezugszeichen des alternativen Ausführungsbeispiels der Buchstabe a hinzugefügt. Die nachfolgende Beschreibung beschränkt sich im Wesentlichen auf die Unterschiede zu dem Ausführungsbeispiel in den Figuren 2 und 3, wobei bezüglich gleich bleibender Bauteile, Merkmale und Funktionen auf die Beschreibung des Ausführungsbeispiels in den Figuren 2 und 3 verwiesen werden kann.In Figure 4 an alternative embodiment is shown. Components, features and functions that essentially remain the same are generally numbered with the same reference numerals. To distinguish the exemplary embodiments, however, the letter a is added to the reference symbols of the alternative exemplary embodiment. The following description is essentially limited to the differences from the exemplary embodiment in FIG Figures 2 and 3 , whereby with regard to components, features and functions that remain the same, refer to the description of the exemplary embodiment in FIG Figures 2 and 3 can be referenced.

Figur 4 zeigt eine Detailansicht einer erfindungsgemäßen Werkzeugmaschinengetriebevorrichtung 10a mit einem alternativen Schaltelement 16a in einer schematischen Darstellung. Die Werkzeugmaschinengetriebevorrichtung 10a ist in einer wie in Figur 1 dargestellten handgeführten Elektrowerkzeugmaschine 52 angeordnet. Die Werkzeugmaschinengetriebevorrichtung 10a umfasst ein Planetengetriebe 84a mit einer ersten, einer zweiten und einer dritten Getriebestufe 12a, 14a, 82a, wobei eine Funktionsweise des Planetengetriebes 84a der Funktionsweise des Planetengetriebes 84 der Figur 2 entspricht. Figure 4 shows a detailed view of a machine tool transmission device 10a according to the invention with an alternative switching element 16a in a schematic representation. The machine tool gear device 10a is in one as shown in FIG Figure 1 hand-held power tool 52 shown is arranged. The machine tool gear device 10a comprises a planetary gear 84a with a first, a second and a third gear stage 12a, 14a, 82a, one mode of operation of the planetary gear 84a being the mode of operation of the planetary gear 84 of FIG Figure 2 is equivalent to.

Die Werkzeugmaschinengetriebevorrichtung 10a umfasst ferner das Schaltelement 16a, welches ein erstes, ein zweites und ein drittes Bauteil 22a, 24a, 38a umfasst. Das erste Bauteil 22a ist als Schaltring 92a ausgebildet. Das zweite Bauteil 24a ist als Hohlrad 94a der zweiten Getriebestufe 14a ausgebildet und das dritte Bauteil 38a ist als Federelement 40a ausgebildet, wobei das Federelement 40a als Schraubenfeder 108a ausgeführt ist. Insgesamt sind zwei Schraubenfedern 108a zwischen dem Schaltring 92a und dem Hohlrad 94a der zweiten Getriebestufe 14a angeordnet, die sich analog zu Figur 3 an einem Stützelement 46a des Schaltrings 92a und an einem Stützelement 48a des Hohlrads 94a der zweiten Getriebestufe 14a abstützen. Das Stützelement 46a des Schaltrings 92a ist derart ausgeführt, dass sich die Schraubenfedern 108a in jeder Betriebsposition des Schaltrings 92a an dem Stützelement 46a abstützen können. Hierzu erstreckt sich das Stützelement 46a entlang der axialen Richtung 42a über eine im Wesentlichen gesamte Breite des Schaltrings 92a. Die Schraubenfedern 108a können zusätzlich in einer Nut, die in einer Außenseite des Hohlrads 94a der zweiten Getriebestufe 14a angeordnet ist, geführt werden. Mittels einer derartigen Anordnung der Schraubenfedern 108a ist der Schaltring 92a entlang einer Umfangsrichtung 20a relativ zum Hohlrad 94a der zweiten Getriebestufe 14a bewegbar. Ferner ist der Schaltring 92a entlang einer axialen Richtung 42a relativ zum Hohlrad 94a der zweiten Getriebestufe 14a beweglich gelagert.The machine tool transmission device 10a further comprises the switching element 16a, which comprises a first, a second and a third component 22a, 24a, 38a. The first component 22a is designed as a switching ring 92a. The second component 24a is designed as a ring gear 94a of the second gear stage 14a and the third component 38a is designed as a spring element 40a, the spring element 40a being designed as a helical spring 108a. A total of two coil springs 108a are arranged between the switching ring 92a and the ring gear 94a of the second gear stage 14a, which are analogous to Figure 3 on a support element 46a of the switching ring 92a and on a support element 48a of the ring gear 94a of the second gear stage 14a. The support element 46a of the switching ring 92a is designed such that the helical springs 108a can be supported on the support element 46a in every operating position of the switching ring 92a. For this purpose, the support element 46a extends along the axial direction 42a over an essentially entire width of the switching ring 92a. The coil springs 108a can additionally be guided in a groove which is arranged in an outer side of the ring gear 94a of the second gear stage 14a. By means of such an arrangement of the helical springs 108a, the switching ring 92a can be moved along a circumferential direction 20a relative to the ring gear 94a of the second gear stage 14a. Furthermore, the switching ring 92a is movably supported along an axial direction 42a relative to the ring gear 94a of the second gear stage 14a.

Bei einem Schaltvorgang des Planetengetriebes 84a aus einem ersten Gang des Planetengetriebes 84a in einen zweiten Gang des Planetengetriebes 84a wird der Schaltring 92a entlang der axialen Richtung 42a in Richtung der ersten Getriebestufe 12a bewegt, wobei ein Verriegelungselement 36a des Schaltrings 92a außer Eingriff einer Verriegelungsgeometrie 146a eines mit einem Gehäuse 54 des Akku-Schraubers 50 verdrehsicher angeordneten Bauteils 148a gelangt. Das Verriegelungselement 36a ist einstückig mit dem Stützelement 46a des Schaltrings 92a ausgebildet. Das Hohlrad 94a der zweiten Getriebestufe 14a behält während des gesamten Schaltvorgangs seine Position in axialer Richtung 42a bei. Das Hohlrad 94a der zweiten Getriebestufe 14a ist entlang der axialen Richtung 42a zwischen einem Planetenträger 88a der ersten Getriebestufe 12a und einem Planetenträger 120a der zweiten Getriebestufe 14a angeordnet. Das Hohlrad 94a der zweiten Getriebestufe 14a wird somit axial gesichert und behält seine Position in axialer Richtung 42a bei.When the planetary gear 84a is shifted from a first gear of the planetary gear 84a to a second gear of the planetary gear 84a, the switching ring 92a is moved along the axial direction 42a in the direction of the first gear stage 12a, with a locking element 36a of the switching ring 92a disengaging a locking geometry 146a arrives with a housing 54 of the cordless screwdriver 50 rotatably arranged component 148a. The locking element 36a is formed in one piece with the support element 46a of the switching ring 92a. The ring gear 94a of the second gear stage 14a maintains its position in the axial direction 42a during the entire shifting process. The ring gear 94a of the second gear stage 14a is arranged along the axial direction 42a between a planet carrier 88a of the first gear stage 12a and a planet carrier 120a of the second gear stage 14a. The ring gear 94a of the second gear stage 14a is thus axially secured and maintains its position in the axial direction 42a.

Der Schaltring 92a weist eine Innenverzahnung 150a auf, welche von dem Stützelement 46a gebildet ist und in Richtung des Hohlrads 94a der zweiten Getriebestufe 14a ausgerichtet ist. Es ist jedoch auch denkbar, dass die Innenverzahnung 150a im Wesentlichen entlang der gesamten Umfangsrichtung 20a verläuft und zumindest teilweise das Stützelement 46a des Schaltrings 92a umfasst. Die Innenverzahnung 150a greift während des Schaltvorgangs in eine Außenverzahnung 138a des Planetenträgers 88a der ersten Getriebestufe 12a ein und koppelt hierbei das Hohlrad 94a der zweiten Getriebestufe 14a mit dem Planetenträger 88a der ersten Getriebestufe 12a. Ein durch unterschiedliche Drehzahlen hervorgerufener Drehmomentstoß zwischen dem Schaltring 92a und dem Hohlrad 94a der zweiten Getriebestufe 14a während des Eingriffs der Innenverzahnung 150a des Schaltrings 92a in die Außenverzahnung 138a des Planetenträgers 88a der ersten Getriebestufe 12a wird durch die Schraubenfedern 108a gedämpft.The switching ring 92a has an internal toothing 150a which is formed by the support element 46a and is oriented in the direction of the ring gear 94a of the second gear stage 14a. However, it is also conceivable that the internal toothing 150a runs essentially along the entire circumferential direction 20a and at least partially encompasses the support element 46a of the switching ring 92a. During the shifting process, the internal toothing 150a engages an external toothing 138a of the planetary carrier 88a of the first gear stage 12a and here couples the ring gear 94a of the second gear stage 14a to the planetary carrier 88a of the first gear stage 12a. A torque shock caused by different speeds between the shift ring 92a and the ring gear 94a of the second gear stage 14a during the engagement of the internal toothing 150a of the shifting ring 92a with the external toothing 138a of the planetary carrier 88a of the first gear stage 12a is dampened by the helical springs 108a.

Wird das Schalthohlrad 26a aus dem zweiten Gang des Planetengetriebes 84a in den ersten Gang des Planetengetriebes 84a geschalten, so wird das Schalthohlrad 26a entlang der axialen Richtung 42a in Richtung der dritten Getriebestufe 82a bewegt. Hierbei gelangt die Innenverzahnung 150a des Schaltrings 92a außer Eingriff der Außenverzahnung 138a des Planetenträgers 88a der ersten Getriebestufe 12a. Eine Kopplung der Planetenräder 100a der zweiten Getriebestufe 14a mit dem Planetenträger 88a der ersten Getriebestufe 12a wird hierbei aufgehoben. Durch die Bewegung des Schalthohlrads 26a entlang der axialen Richtung 42a in Richtung der dritten Getriebestufe 82a gelangt das Verriegelungselement 36a des Schaltrings 92a in Eingriff der Verriegelungsgeometrie 146a des im Gehäuse 54 verdrehsicher angeordneten Bauteils 148a, wobei durch den Eingriff des Verriegelungselements 36a des Schaltrings 92a in die Verriegelungsgeometrie 146a des im Gehäuse 54 verdrehsicher angeordneten Bauteils 148a ein Drehmomentstoß zwischen dem Schaltring 92a und dem Hohlrad 94a der zweiten Getriebestufe 14a entsteht. Dieser Drehmomentstoß wird mittels der Schraubenfedern 108a zwischen dem Schaltring 92a und dem Hohlrad 94a der zweiten Getriebestufe 14a gedämpft. Das Schalthohlrad 26a ist nach dem Schaltvorgang im Wesentlichen verdrehsicher mit dem Gehäuse 54 verbunden. Das Hohlrad 94a der zweiten Getriebestufe 14a behält während des gesamten Schaltvorgangs aus dem zweiten Gang des Planetengetriebes 84a in den ersten Gang des Planetengetriebes 84a seine Position in axialer Richtung 42a bei.If the switching ring gear 26a is switched from the second gear of the planetary gear 84a to the first gear of the planetary gear 84a, the switching ring gear 26a is moved along the axial direction 42a in the direction of the third gear stage 82a. Here, the internal toothing 150a of the switching ring 92a disengages from the external toothing 138a of the planetary carrier 88a of the first gear stage 12a. A coupling of the planetary gears 100a of the second gear stage 14a with the planet carrier 88a of the first gear stage 12a is canceled. As a result of the movement of the switching ring gear 26a along the axial direction 42a in the direction of the third gear stage 82a, the locking element 36a of the switching ring 92a engages the locking geometry 146a of the non-rotatable component 148a in the housing 54, with the engagement of the locking element 36a of the switching ring 92a in the Locking geometry 146a of the component 148a arranged in the housing 54 so that it cannot rotate, a torque surge occurs between the switching ring 92a and the ring gear 94a of the second gear stage 14a. This torque shock is dampened by means of the helical springs 108a between the switching ring 92a and the ring gear 94a of the second gear stage 14a. The switching ring gear 26a is connected to the housing 54 in an essentially non-rotatable manner after the switching process. The ring gear 94a of the second gear stage 14a retains during the entire shift from the second gear of the planetary gear 84a to the first gear of the planetary gear 84a its position in the axial direction 42a.

Claims (13)

  1. Power tool transmission device having at least one first and one second gear stage (12, 14; 12a, 14a) and having a shifting element (16; 16a) which is movable by a user by means of an actuating element (18; 18a), wherein the shifting element (16; 16a) at least partially surrounds at least one gear stage (12, 14; 12, 14a) in a circumferential direction (20, 20a) in at least one operating position and is intended to shift between a first and a second operating position, wherein the shifting element (16; 16a) comprises at least one first component (22; 22a) and one second component (24; 24a) and the shifting element (16; 16a) has at least one further component (38; 38a) which is formed at least partially by a spring element (40; 40a), characterized in that the first component (22; 22a) is operatively connected to the second component (24, 24a) at least by means of the spring element (40; 40a).
  2. Power tool transmission device according to Claim 1, characterized in that the shifting element (16; 16a) is configured as a shifting ring gear (26; 26a) .
  3. Power tool transmission device according to either of the preceding claims, characterized in that the first component (22; 22a) is formed at least partially by a first ring element (28; 28a) and the second component (24, 24a) is formed at least partially by a second ring element (30; 30a).
  4. Power tool transmission device according to one of the preceding claims, characterized in that the first component (22; 22a) at least partially covers the second component (24; 24a) in a radial direction (32; 32a) at least in one operating position.
  5. Power tool transmission device according to one of the preceding claims, characterized in that the first component (22; 22a) and the second component (24; 24a) substantially enclose a receiving region (34; 34a).
  6. Power tool transmission device according to at least one of the preceding claims, characterized in that the first component (22; 22a) is mounted so as to be movable relative to the second component (24; 24a) .
  7. Power tool transmission device according to one of the preceding claims, characterized in that the first component (22, 22a) comprises at least one locking element (36; 36a).
  8. Power tool transmission device according to one of the preceding claims, characterized in that the spring element (40; 40a) is arranged between the first component (22; 22a) and the second component (24; 24a) in at least one direction (32, 42; 32a, 42a) .
  9. Power tool transmission device according to one of the preceding claims, characterized in that the first component (22) has at least one form-fitting element (44) which is intended to at least partially engage behind the second component (24) in an axial direction (42).
  10. Power tool transmission device according to one of the preceding claims, characterized in that the first component (22, 22a) has at least one support element (46; 46a) extending in a radial direction (32; 32a), wherein the support element (46, 46a) is oriented in the direction of the second component (24; 24a).
  11. Power tool transmission device according to one of the preceding claims, characterized in that the second component (24; 24a) has at least one support element (48; 48a) extending in a radial direction (32; 32a), wherein the support element (48; 48a) is oriented in the direction of the first component (22; 22a).
  12. Power tool transmission device according to Claims 10 and 11, characterized in that the support elements (46, 48; 46a, 48a) are intended to at least partially transmit a force from the first component (22, 22a) to the second component (24; 24a).
  13. Portable power tool having a power tool transmission device (10) according to one of the preceding claims.
EP18160401.8A 2008-08-29 2009-07-15 Power tool gear device Active EP3363595B1 (en)

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DE102008041718A DE102008041718A1 (en) 2008-08-29 2008-08-29 Tool gear device
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PCT/EP2009/059038 WO2010023027A1 (en) 2008-08-29 2009-07-15 Power tool gear device

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EP3363595A1 (en) 2018-08-22
EP2331296A1 (en) 2011-06-15
US10300584B2 (en) 2019-05-28
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US20110220377A1 (en) 2011-09-15
DE102008041718A1 (en) 2010-03-04

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