EP3363595B1 - Dispositif de transmission pour une machine-outil - Google Patents

Dispositif de transmission pour une machine-outil 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)
English (en)
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EP3363595A1 (fr
Inventor
Heiko Roehm
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP3363595A1 publication Critical patent/EP3363595A1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • 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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Claims (13)

  1. Dispositif de transmission de machine-outil, comprenant au moins un premier et un deuxième étage de transmission (12, 14 ; 12a, 14a) et un élément de commutation (16 ; 16a) qui peut être déplacé par un utilisateur au moyen d'un élément d'actionnement (18 ; 18a), l'élément de commutation (16 ; 16a), dans au moins une position fonctionnelle, entourant au moins en partie au moins un étage de transmission (12, 14 ; 12, 14a) le long d'une direction périphérique (20 ; 20a) et étant prévu pour commuter entre une première et une deuxième position fonctionnelle, l'élément de commutation (16 ; 16a) comprenant au moins un premier composant (22 ; 22a) et un deuxième composant (24 ; 24a), et l'élément de commutation (16 ; 16a) présentant au moins un composant supplémentaire (38 ; 38a) qui est formé au moins en partie par un élément de ressort (40 ; 40a), caractérisé en ce le premier composant (22 ; 22a) est en liaison fonctionnelle avec le deuxième composant (24, 24a) au moins au moyen de l'élément de ressort (40 ; 40a).
  2. Dispositif de transmission de machine-outil selon la revendication 1, caractérisé en ce que l'élément de commutation (16 ; 16a) est réalisé sous forme de couronne dentée de commutation (26 ; 26a).
  3. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier composant (22 ; 22a) est formé au moins en partie par un premier élément annulaire (28 ; 28a) et le deuxième composant (24 ; 24a) est formé au moins en partie par un deuxième élément annulaire (30 ; 30a).
  4. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier composant (22 ; 22a), au moins dans une position fonctionnelle, recouvre au moins en partie le deuxième composant (24 ; 24a) le long d'une direction radiale (32 ; 32a) .
  5. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier composant (22 ; 22a) et le deuxième composant (24 ; 24a) englobent essentiellement une région de réception (34 ; 34a).
  6. Dispositif de transmission de machine-outil au moins selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier composant (22 ; 22a) est supporté de manière déplaçable par rapport au deuxième composant (24 ; 24a) .
  7. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier composant (22 ; 22a) comprend au moins un élément de verrouillage (36 ; 36a).
  8. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément de ressort (40 ; 40a) est disposé le long d'au moins une direction (32, 42 ; 32a, 42a) entre le premier composant (22 ; 22a) et le deuxième composant (24 ; 24a).
  9. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier composant (22) présente au moins un élément d'engagement par correspondance de formes (44) qui est prévu pour venir en prise au moins en partie par l'arrière avec le deuxième composant (24) dans une direction axiale (42) .
  10. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier composant (22, 22a) présente au moins un élément de support (46 ; 46a) s'étendant dans une direction radiale (32 ; 32a), l'élément de support (46, 46a) étant orienté dans la direction du deuxième composant (24 ; 24a).
  11. Dispositif de transmission de machine-outil selon l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième composant (24 ; 24a) présente au moins un élément de support (48 ; 48a) s'étendant dans une direction radiale (32 ; 32a), l'élément de support (48 ; 48a) étant orienté dans la direction du premier composant (22 ; 22a).
  12. Dispositif de transmission de machine-outil selon les revendications 10 et 11, caractérisé en ce que les éléments de support (46, 48 ; 46a, 48a) sont prévus pour transférer au moins en partie une force du premier composant (22, 22a) au deuxième composant (24 ; 24a).
  13. Machine-outil manuelle comprenant un dispositif de transmission de machine-outil (10) selon l'une quelconque des revendications précédentes.
EP18160401.8A 2008-08-29 2009-07-15 Dispositif de transmission pour une machine-outil Active EP3363595B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008041718A DE102008041718A1 (de) 2008-08-29 2008-08-29 Werkzeugmaschinengetriebevorrichtung
EP09780610.3A EP2331296B1 (fr) 2008-08-29 2009-07-15 Dispositif d'engrenage de machine-outil
PCT/EP2009/059038 WO2010023027A1 (fr) 2008-08-29 2009-07-15 Dispositif d’engrenage de machine-outil

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP09780610.3A Division-Into EP2331296B1 (fr) 2008-08-29 2009-07-15 Dispositif d'engrenage de machine-outil
EP09780610.3A Division EP2331296B1 (fr) 2008-08-29 2009-07-15 Dispositif d'engrenage de machine-outil

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EP3363595A1 EP3363595A1 (fr) 2018-08-22
EP3363595B1 true EP3363595B1 (fr) 2021-09-08

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EP09780610.3A Active EP2331296B1 (fr) 2008-08-29 2009-07-15 Dispositif d'engrenage de machine-outil
EP18160401.8A Active EP3363595B1 (fr) 2008-08-29 2009-07-15 Dispositif de transmission pour une machine-outil

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US (1) US10300584B2 (fr)
EP (2) EP2331296B1 (fr)
CN (1) CN102137737B (fr)
DE (1) DE102008041718A1 (fr)
WO (1) WO2010023027A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008042354A1 (de) * 2008-09-25 2010-04-01 Robert Bosch Gmbh Handwerkzeugmaschine mit einem schaltbaren Getriebe
DE102009054931A1 (de) * 2009-12-18 2011-06-22 Robert Bosch GmbH, 70469 Handgeführtes Elektrowerkzeug mit einer Drehmomentkupplung
DE102011004126A1 (de) * 2011-02-15 2012-08-16 Robert Bosch Gmbh Handwerkzeugmaschine mit einem Untersetzungsgetriebe
US9233461B2 (en) 2012-02-27 2016-01-12 Black & Decker Inc. Tool having multi-speed compound planetary transmission
CN202779907U (zh) * 2012-08-01 2013-03-13 创科电动工具科技有限公司 电动工具
US9108312B2 (en) 2012-09-11 2015-08-18 Milwaukee Electric Tool Corporation Multi-stage transmission for a power tool
US9908228B2 (en) 2012-10-19 2018-03-06 Milwaukee Electric Tool Corporation Hammer drill
DE102014210344A1 (de) * 2013-06-03 2014-12-04 Robert Bosch Gmbh Handwerkzeugmaschine mit einem schaltbaren Getriebe
DE102013222550A1 (de) * 2013-11-06 2015-05-07 Robert Bosch Gmbh Handwerkzeugmaschine
USD928841S1 (en) * 2019-04-10 2021-08-24 Signode Industrial Group Llc Inflator
USD917575S1 (en) * 2020-08-28 2021-04-27 Shenzhen Chenguo Technology Co., Ltd. Handheld tire inflator
TWI810970B (zh) * 2022-06-14 2023-08-01 鑽全實業股份有限公司 電動工具的傳動裝置
USD1007548S1 (en) * 2023-09-29 2023-12-12 Haili Jin Cordless plastic welder

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5339908A (en) * 1990-10-02 1994-08-23 Ryobi Limited Power tool
US5550416A (en) * 1995-02-09 1996-08-27 Fanchang; We C. Control mechanism of revolving speed of an electric tool
US7044882B2 (en) 2003-04-03 2006-05-16 Atlas Copco Electric Tools Gmbh Switchable gearbox of a handheld power tool
DE10315138A1 (de) 2003-04-03 2004-10-21 Atlas Copco Electric Tools Gmbh Schaltbares Getriebe einer handgeführten Werkzeugmaschine
DE102004058686A1 (de) * 2004-09-03 2006-03-09 Robert Bosch Gmbh Elektrowerkzeug mit einem zwischen den Betriebsarten Bohren, Schlagbohren, Meißeln umschaltbaren Antrieb
DE102004058175B4 (de) * 2004-12-02 2019-10-31 Robert Bosch Gmbh Handwerkzeugmaschine mit anatomisch verbessertem Schaltelement
JP4609489B2 (ja) * 2007-12-25 2011-01-12 パナソニック電工株式会社 電動工具

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Publication number Publication date
CN102137737A (zh) 2011-07-27
EP2331296A1 (fr) 2011-06-15
EP2331296B1 (fr) 2018-05-23
DE102008041718A1 (de) 2010-03-04
WO2010023027A1 (fr) 2010-03-04
EP3363595A1 (fr) 2018-08-22
CN102137737B (zh) 2013-08-07
US20110220377A1 (en) 2011-09-15
US10300584B2 (en) 2019-05-28

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