EP3363595A1 - Dispositif de transmission pour une machine-outil - Google Patents

Dispositif de transmission pour une machine-outil Download PDF

Info

Publication number: EP3363595A1
Authority: EP; European Patent Office
Prior art keywords: component; gear; ring; switching; machine tool
Prior art date: 2008-08-29
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.): Granted

Application number

EP18160401.8A

Other languages

German (de)

English (en)

Other versions

EP3363595B1 (fr

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

Original Assignee

Robert Bosch GmbH

Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)

2008-08-29

Filing date

2009-07-15

Publication date

2018-08-22

2009-07-15 Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH

2018-08-22 Publication of EP3363595A1 publication Critical patent/EP3363595A1/fr

2021-09-08 Application granted granted Critical

2021-09-08 Publication of EP3363595B1 publication Critical patent/EP3363595B1/fr

Status Active legal-status Critical Current

2029-07-15 Anticipated expiration legal-status Critical

Images

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 relates to a power tool gear device according to the preamble of claim 1.
Machine tool transmission devices having a first and a second gear stage and a switching element are already known, wherein the switching element is movable by an operator by means of an actuating element, in an operating position surrounds the first gear stage along a circumferential direction and is provided between a first and a second Switch operating position.
the invention relates to a power tool gear device having at least a first and a second gear stage and a switching element which is movable by an operator by means of an actuating element, the switching element at least partially surrounds at least one operating position at least one gear stage along a circumferential direction and is provided to switch between a first and a second operating position.
the switching element comprises at least a first component and a second component.
"intended” 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 of planet carriers, ring gears, planet gears and sun gears, in a transmission, in particular a planetary gear understood, which is intended to transmit predetermined torques and / or speeds and / or set torques and / or speeds and / or translate.
the torque and / or the rotational speed and / or a reduction and / or translation of the torque and / or the rotational speed can 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 is an operative connection and which is intended to transfer the further element and / or component from one state to another state.
the actuating element is formed by a component separate from the switching element.
the actuator is by means of an outer geometry of the switching element with this in operative connection, 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 switching position, of the switching element within a transmission, in particular a planetary gear in which transmit a specific torque and / or speed via the transmission to a shaft and / or gears of the transmission can be.
the term "circumferential direction” is to be understood here in particular as meaning a direction perpendicular to a rotational axis of an output shaft of the power tool transmission device, the circumferential direction running circumferentially about the rotational axis of the power take-off shaft of the power tool gear device.
the expression "surrounds along a circumferential direction" should in particular define 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 is perpendicular to the axis of rotation of the output shaft of the power tool gear device.
an arrangement of gears, in particular of a planet carrier, a ring gear, planetary gears and / or a sun gear to be covered radially by at least one component of the switching element.
the power tool gear device for hand-held power tools such as screwdrivers, drills and impact drills and especially for cordless screwdrivers, cordless drills and cordless drills, provided to a motor speed of about 20 000 U / min in one for a work spindle of the hand-held power tool reasonable speed range from approx. 150 rpm to 2000 rpm.
the inventive design of the horrmaschinengertiebevoriques an operator can switch particularly comfortable between a first and a second operating position, switched from a first gear of the power tool gear device with a low speed and high torque in a second gear of the power tool gear device with a high speed and low torque can be. In this case, it is particularly advantageous to achieve a switching operation during operation of the power tool gear device under load.
the switching element is designed as a switching ring gear. Particularly advantageous is the switching ring gear provided for a planetary gear. Such a configuration, the switching element can be structurally easily integrated into existing machine tool gear devices and it can be advantageously saved costs and installation costs.
the first component is 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 extent, which extends along the entire circumferential direction, so that the first ring element is closed in itself and the second ring element is also closed in itself.
the inventive design of the components as a ring element, a compact machine tool gear device can be achieved.
the first component at least partially covers the second component along a radial direction.
an existing space can be used advantageously and it can be achieved a simple combination of components function.
a high operating comfort of the power tool gear device can be achieved.
the first component and the second component substantially enclose a receiving region.
the receiving area extends like an annular segment along the circumferential direction.
the receiving area along the circumferential direction can be divided into several independent sections.
the receiving area in an axial direction and in the radial direction substantially of the first component and the second Component to be covered.
the axial direction is substantially parallel to the axis of rotation of the output shaft of the power tool gear device.
the term "essentially parallel” is to be understood here in particular as meaning a direction which, relative to a reference direction, has a deviation, in particular less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 °.
a protective function for an element and / or a component arranged in the receiving region can be achieved by means of the receiving region, and wear of the element and / or of the component can advantageously be reduced.
the first component is movably mounted relative to the second component.
the first component can move along the circumferential direction relative to the second component, in order to be able to compensate advantageously torque and / or speed differences during a switching operation between the first and the second operating position.
the first component can move along the axial direction relative to the second component. This allows a structurally simple design switching element can be achieved.
the first component comprises at least one locking element.
a “locking element” is to be understood here in particular as an element and / or component which is intended to prevent a movement of the element and / or component relative to a further element and / or component by means of positive locking and / or frictional connection.
the locking element is intended to form a positive connection.
the locking element is formed integrally with the first component.
one piece is intended to be understood in particular to be formed in one piece and / or from a cast and / or formed as a component.
the locking element is 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.
the first component can advantageously be held in a desired position by means of the locking element.
the locking geometry can be advantageously provided as a rotation of the first component relative to a housing in which the power 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 defined in this context a spring-elastic element and / or component, such as a plate spring, an elastomer and / or other, the expert appears to be useful resilient elements.
the spring element is particularly advantageously designed as a helical spring.
the spring element preferably has a function of a damping means, whereby an advantageous protection of components can be achieved and wear can be reduced.
the first component is in operative connection with the second component at least by means of the spring element.
the spring element is intended to ensure a relative movement between the components.
the spring element is arranged along at least one direction between the first component and the second component.
between is meant in particular an arrangement spatially along the radial direction and / or the axial direction.
the spring element is preferably arranged in the receiving region surrounded by the first component and the second component. It can thereby be achieved a protective function of the spring element and further, a compact arrangement of the components can be achieved in the power tool gear device.
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-fitting element" is to be understood here in particular as an element and / or a component which is intended to form a positive connection with a further element and / or component.
the positive-locking element is formed integrally with the first component, whereby advantageous space and components can be saved.
the first component has at least one support element extending in a radial direction, wherein the support element is aligned in the direction of the second component.
a "support element” is to be understood here in particular an element and / or component, the is designed as a system and / or a stop of a further element and / or component, in particular of the spring element, in particular to absorb and / or transmit forces and / or to introduce into the further element and / or component.
the support element is formed integrally with the first component, whereby an advantageous and structurally simple introduction of force into the component can be achieved.
the second component has at least one support element extending in a radial direction, wherein the support element is aligned in the direction of the first component.
the support element is formed integrally with the second component. This allows a structurally simple functional coupling of the components can be achieved, in particular a relative movement between the components, wherein the relative movement can be damped by the spring element to prevent torque surges. Furthermore, advantageous space, components, assembly costs and costs can 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.
FIG. 1 shows a designed as a cordless screwdriver 50, hand-held power tool 52 with a power 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 power 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 FIG. 2 ) of the power tool gear device 10, which is in operative connection with the tool holder 60, can be driven in rotation.
the cordless screwdriver 50 comprises a positioning ring 66 which is arranged on the tool holder 60 and which is provided to set a torque that can be transmitted to the tool holder 60.
a main extension direction 68 of the cordless screwdriver 50 extends from one side 70 of the housing 54, are arranged on the cooling holes 72, in the direction of the tool holder 60.
a handle 74 On the housing 54 is disposed substantially perpendicular to the main extension direction 68, a handle 74, which for guiding the Cordless screwdriver 50 is provided by an operator.
the handle 74 is formed integrally with the housing 54.
a battery pack 76 is attached.
the handle 74 further includes an actuation switch 78 having electrical contacts that are provided upon actuation of the actuation switch 78 by the operator to make or break an electrical supply to the motor unit 56 through 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 axially displaceable along the main extension direction 68 of the cordless screwdriver 50.
a switching element 16 (see FIG. 2 ) of the power tool gear device 10 is movable by the operator along an axial direction 42.
the axial direction 42 extends substantially parallel to the main extension direction 68 of the cordless screwdriver 50.
FIG. 2 shows a detailed view of the power tool gear device 10 according to the invention in a schematic representation.
the power tool gear device 10 includes a Planetary gear 84 having 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 planetary carrier 88, 120, 124 and a plurality of planetary gears 90, 100, 122, which are arranged on the planet carrier 88, 120, 124.
the power tool gear device 10 includes the switching element 16, which is movable 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 in a first operating position the ring gear 94 of the second gear stage 14 along a radial direction 32 which is perpendicular to a rotational axis 96 of the output shaft 64.
the ring gear 94 of the second gear stage 14 includes 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 is 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 power tool gear device 10.
the first operating position forms a first gear of the planetary gear 84.
first gear during operation of the planetary gear 84, low rotational speeds and high torque are transmitted to the output shaft 64 and thus to the tool 62 in the tool holder 60.
the second operating position forms a second gear of the planetary gear 84.
high speeds and low torque are transmitted to the output shaft 64 during operation of the planetary gear.
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 in this case runs parallel to the axis of rotation 96 of the output shaft 64 of the power 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 against rotation with the housing 54 of the cordless screwdriver 50.
the first locking element 36 is formed in the form of a first external toothing 102.
the first external toothing 102 extends 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 comprises a receiving region 34, which is essentially enclosed by the switching ring 92 and the ring gear 94 of the second gear stage 14.
the switching ring 92 and the ring gear 94 of the second gear stage 14 in this case cover the receiving area 34 along the radial direction 32 and the axial direction 42.
the receiving area 34 is provided to accommodate at least one further component 38 of the switching ring gear 26.
the further component 38 is designed as a spring element 40.
two spring elements 40 which are formed as coil springs 108, arranged in the receiving region 34.
the receiving region 34 is divided along the circumferential direction 20 into two spatially separated sections 110, wherein one of the coil springs 108 is arranged in each section 110.
the receiving area 34 is subdivided into more than two sections 110 and a corresponding number of coil springs 108 are arranged in the sections 110.
the switching ring 92 in this case has a support element 46 extending in the radial direction 32, which is aligned in the direction of the ring gear 94 of the second gear stage 14.
the switching ring 92 depending on the number of sections 110 has a plurality of support members 46 for subdivision.
the ring gear 94 of the second gear stage 14 a support member 48 which is aligned in the direction of the switching ring 92.
the person skilled in the art will likewise 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 ringenfedem 108 are each supported with one end 112 on the support member 46 of the switching ring 92 and with a respective opposite end 114, the coil springs 108 are supported on the support member 48 of the ring gear 94 of the second gear 14 from.
the switching ring 92 is in operative connection with the ring gear 94 of the second gear stage 14 by means of the coil 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 coil springs 108.
the switching ring 92 is in this case 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 coil springs 108 in the receiving area 34 movably mounted (see FIG. 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. Further, the coil springs 108 are disposed along the radial direction 32 between the switching ring 92 and the ring gear 94 of the second gear stage 14.
the power tool gear device 10 is driven by a shaft of the motor unit 56, on which a drive pinion 116 of the power tool gear device 10 is arranged.
the drive pinion 116 engages in the planetary gears 90 of the first gear 12 a.
the planet gears 90 of the first gear 12 mesh with an internal toothing 118, which is arranged along the circumferential direction 20 in a non-rotatably arranged to the housing 54 ring gear 86 of the first gear 12, and drive the planetary carrier 88 of the first gear 12 at.
An arbitrary point of the planetary gears 90 of the first gear stage 12 in this case carries out a movement superimposed by two rotational movements.
a first of the two superimposed rotational movements is a self-rotation of the planet gears 90 of the first gear stage 12 and the second rotational movement is a rotation of the planetary gears 90 of the first gear stage 12 about an axis of rotation of the drive pinion 116 of the power tool gear device 10.
the planetary carrier 88 of the first gear 12 drives the planetary gears 100 of the second gear 14, wherein any point of the planetary gears 100 of the second gear 14 carries out a movement superimposed by two rotational movements.
a first of the two superimposed rotational movements is a self-rotation of the planetary gears 100 of the second gear stage 14 and the second rotational movement is a rotation of the planetary gears 100 of the second gear stage 14 about an axis of rotation of the planetary carrier 88 of the first gear stage 12.
the second gear stage 14 is made possible by a rotationally secure arrangement of the switching ring 92 and thus of 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 coil springs 108 and the support elements 46, 48 after a slight relative movement to the switching ring 92 and / or housing 54 substantially against rotation to the housing 54.
the movement of the planetary gears 100 of the second gear stage 14 drives a planet carrier 120 of the second gear stage 14.
the torque clutch 126 is adjustable by means of the adjusting ring 66 to a maximum torque which is desired by the operator.
the mode of operation of the torque coupling 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 circumferential groove 20 in the circumferential direction 130 of the switching ring 92.
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-fitting element 44 is formed as a separate component which is firmly connected to the switching ring 92.
the connection of the form-fitting element 44 takes place here in a manner which appears appropriate to the person skilled in the art, such as, for example, a screw connection, an adhesive bond, etc.
the switching ring 92 comprises a second locking element 132 in the form of a second external toothing 134, which extends in the circumferential direction 20 on one of the first gear stage 12 facing side 136 of the switching ring 92 and along the axial direction 42 in the direction of the first gear 12 is aligned.
the second external toothing 134 has steep flanks, which are intended to mesh with flanks of an external toothing 138 of the planetary carrier 88 of the first gear stage 12, in order thus to rotatably couple the switching ring 92 to the ring gear 86 of the first gear stage 12.
the outer toothing 138 of the planetary carrier 88 of the first gear stage 12 extends for this purpose 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 extends in the circumferential direction 20 on an inner side 142 of the switching ring 92 and along the radial direction 32 in the direction of the ring gear 94 of the second gear stage 14 is aligned.
the internal toothing 150 would mesh with an outer toothing 138 of the planet carrier 88 of the first gear stage 12, which extends 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 14 is also coupled by means of coil springs 108 substantially rotationally with the ring gear 86 of the first gear stage 12.
the switching ring gear 26 is coupled to the planetary 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 toward the third gear stage 82.
the second external toothing 134 of the switching ring 92 is thereby disengaged from the external teeth 138 of the planetary carrier 88 of the first gear 12, whereby a coupling of the planetary gears 100 of the second gear 14 is canceled with the planet carrier 88 of the first gear 12.
the switching ring gear 26 By the movement of 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, wherein the engagement of the external toothing 102 of the switching ring 92 in the internal toothing 106 of the housing 54 a torque surge between the switching ring 92 and the ring gear 94 of the second gear 14 is formed.
This torque shock is attenuated by means of the coil 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 after the switching operation substantially against rotation with the housing 54.
FIG. 4 an alternative embodiment is shown. Substantially identical components, features and functions are basically numbered by the same reference numerals. In order to distinguish the embodiments, however, the letter a is added to the reference numerals of the alternative embodiment. The following description is essentially limited to the differences from the embodiment in the Figures 2 and 3 , in which with respect to the same components, features and functions on the description of the embodiment in the Figures 2 and 3 can be referenced.
FIG. 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 power tool gear device 10a is in a position as in FIG FIG. 1 shown hand-held power tool 52 arranged.
the machine tool transmission device 10a comprises a planetary gear 84a with a first, a second and a third gear stage 12a, 14a, 82a, wherein an operation of the planetary gear 84a of the operation of the planetary gear 84 of the FIG. 2 equivalent.
the power tool transmission device 10a further comprises the shifting 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, wherein the spring element 40a is designed as a helical spring 108a.
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 FIG.
the support element 46a of the switching ring 92a is designed such that the coil springs 108a can be supported on the support element 46a in any operating position of the switching ring 92a.
the support element 46a extends along the axial direction 42a over a substantially entire width of the switching ring 92a.
the coil springs 108a may additionally be guided in a groove disposed in an outer side of the ring gear 94a of the second gear stage 14a.
the switching ring 92a is movable along a circumferential direction 20a relative to the ring gear 94a of the second gear stage 14a. Further, 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 In a switching operation of the planetary gear 84a from a first gear of the planetary gear 84a in 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, wherein a locking element 36a of the switching ring 92a out of engagement a locking geometry 146a of with a housing 54 of the cordless screwdriver 50 rotatably arranged component 148a passes.
the locking element 36a is integrally formed with the support member 46a of the switching ring 92a.
the ring gear 94a of the second gear stage 14a maintains its position in the axial direction 42a throughout the shifting operation.
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 aligned in the direction of the ring gear 94a of the second gear stage 14a.
the internal toothing 150a extends substantially along the entire circumferential direction 20a and at least partially comprises the support element 46a of the switching ring 92a.
the internal toothing 150a engages during the switching operation in an external toothing 138a of the planetary carrier 88a of the first gear stage 12a, thereby coupling the ring gear 94a of the second gear stage 14a to the planet carrier 88a of the first gear stage 12a.
a torque shock caused by different rotational speeds between the switching ring 92a and the ring gear 94a of the second gear stage 14a during the engagement of the internal teeth 150a of the switching ring 92a in the external teeth 138a of the planetary carrier 88a of the first gear stage 12a is damped by the coil springs 108a.
the shift ring gear 26a is moved along the axial direction 42a in the direction of the third gear stage 82a.
the internal teeth 150a of the switching ring 92a are disengaged from the external teeth 138a of the planetary carrier 88a of the first gear stage 12a.
a coupling of the planet gears 100a of the second gear stage 14a with the planet carrier 88a of the first gear stage 12a is hereby canceled.
the switching ring gear 26a is substantially non-rotatably connected to the housing 54 after the switching operation.
the ring gear 94a of the second gear stage 14a retains during the entire shift from the second gear of the planetary gear 84a in the first gear of the planetary gear 84a in its position in the axial direction 42a.

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Engineering & Computer Science (AREA)
Mechanical Engineering (AREA)
Structure Of Transmissions (AREA)
Retarders (AREA)

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
PCT/EP2009/059038 WO2010023027A1 (fr)	2008-08-29	2009-07-15	Dispositif d’engrenage de machine-outil
EP09780610.3A EP2331296B1 (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

Publications (2)

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

Family

ID=41119422

Family Applications (2)

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

Family Applications After (1)

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

Country Status (5)

Country	Link
US (1)	US10300584B2 (fr)
EP (2)	EP3363595B1 (fr)
CN (1)	CN102137737B (fr)
DE (1)	DE102008041718A1 (fr)
WO (1)	WO2010023027A1 (fr)

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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
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DE102014210343A1 (de) *	2013-06-03	2014-12-04	Robert Bosch Gmbh	Handwerkzeugmaschine mit einem schaltbaren Getriebe
DE102013222550B4 (de) *	2013-11-06	2024-12-19	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

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EP1464427A2 (fr) *	2003-04-03	2004-10-06	Atlas Copco Electric Tools GmbH	Entraínement commutable d'un outil électrique portable
EP2077177A1 (fr) *	2007-12-25	2009-07-08	Panasonic Electric Works Co., Ltd.	Outil d'alimentation électrique

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DE102004058686A1 (de) *	2004-09-03	2006-03-09	Robert Bosch Gmbh	Elektrowerkzeug mit einem zwischen den Betriebsarten Bohren, Schlagbohren, Meißeln umschaltbaren Antrieb
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2008
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2009
- 2009-07-15 WO PCT/EP2009/059038 patent/WO2010023027A1/fr not_active Ceased
- 2009-07-15 EP EP18160401.8A patent/EP3363595B1/fr active Active
- 2009-07-15 CN CN2009801333127A patent/CN102137737B/zh active Active
- 2009-07-15 EP EP09780610.3A patent/EP2331296B1/fr active Active
- 2009-07-15 US US12/737,849 patent/US10300584B2/en active Active

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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
EP1464427A2 (fr) *	2003-04-03	2004-10-06	Atlas Copco Electric Tools GmbH	Entraínement commutable d'un outil électrique portable
EP2077177A1 (fr) *	2007-12-25	2009-07-08	Panasonic Electric Works Co., Ltd.	Outil d'alimentation électrique

Also Published As

Publication number	Publication date
US20110220377A1 (en)	2011-09-15
CN102137737A (zh)	2011-07-27
CN102137737B (zh)	2013-08-07
EP2331296A1 (fr)	2011-06-15
EP2331296B1 (fr)	2018-05-23
EP3363595B1 (fr)	2021-09-08
US10300584B2 (en)	2019-05-28
DE102008041718A1 (de)	2010-03-04
WO2010023027A1 (fr)	2010-03-04

Publication	Publication Date	Title
EP2331296B1 (fr)	2018-05-23	Dispositif d'engrenage de machine-outil
EP2318184B1 (fr)	2017-09-20	Transmission débrayable pour une machine-outil manuelle
EP0566926B1 (fr)	1995-12-13	Dispositif d'engrenage pour outil à main
EP2675597B1 (fr)	2018-01-03	Machine-outil portative à démultiplicateur
EP2334472B1 (fr)	2018-10-10	Machine-outil manuelle équipée d un mécanisme commutable
EP2726252B1 (fr)	2015-08-12	Tournevis pour construction à paroi sèche
CH697940B1 (de)	2009-03-31	Handwerkzeugmaschine, insbesondere Bohr- und/oder Schlaghammer.
EP2342050B1 (fr)	2018-05-09	Machine-outil manuelle équipée d'une transmission débrayable
DE102009027951A1 (de)	2011-01-27	Handwerkzeugmaschine, insbesondere akkubetriebene Elektrohandwerkzeugmaschine
DE102004058809A1 (de)	2006-06-08	Handwerkzeugmaschine mit einer Drehmomentbegrenzungseinheit
DE19809133A1 (de)	1999-09-09	Handwerkzeugmaschine, insbesondere Bohrschrauber
EP2132453B1 (fr)	2011-11-02	Systeme d'engrenage
DE102013200867A1 (de)	2014-07-24	Werkzeugmaschinenbremsvorrichtung
WO2008068103A1 (fr)	2008-06-12	Outil à main
DE102012213724B4 (de)	2023-11-30	Planetengetriebe für eine Handwerkzeugmaschine
DE102012212404B4 (de)	2017-09-28	Handwerkzeugmaschinenvorrichtung
EP2134512B1 (fr)	2013-10-09	Système d'engrenage
DE102010013102A1 (de)	2011-09-29	Ablaufsicherungsvorrichtung
DE102007062248A1 (de)	2009-06-25	Handwerkzeugmaschine mit einer, mindestens eine drehbar gelagerte Zwischenwelle umfassenden Getriebevorrichtung
EP1652631B1 (fr)	2007-02-14	Machine outil motorisé
EP2104594B1 (fr)	2016-01-06	Machine-outil portative
EP3895846B1 (fr)	2025-08-06	Tournevis de construction à sec
DE102018001858A1 (de)	2019-09-12	Drehmomentübertragungsanordnung, Antriebsstrang mit einer solchen Drehmomentübertragungsanordnung und Fliehkraftpendeleinrichtung für eine solche Drehmomentübertragungsanordnung
DE102013212548A1 (de)	2014-12-31	Handwerkzeugmaschinengetriebevorrichtung
DE102012212399A1 (de)	2014-01-16	Handwerkzeugmaschinenvorrichtung

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