EP2686136B1 - Werkzeugmaschinenbremsvorrichtung - Google Patents

Werkzeugmaschinenbremsvorrichtung Download PDF

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Publication number
EP2686136B1
EP2686136B1 EP12703280.3A EP12703280A EP2686136B1 EP 2686136 B1 EP2686136 B1 EP 2686136B1 EP 12703280 A EP12703280 A EP 12703280A EP 2686136 B1 EP2686136 B1 EP 2686136B1
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EP
European Patent Office
Prior art keywords
braking
brake
unit
tool
elements
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP12703280.3A
Other languages
German (de)
English (en)
French (fr)
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EP2686136A1 (de
Inventor
Florian Esenwein
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
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Publication of EP2686136A1 publication Critical patent/EP2686136A1/de
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Publication of EP2686136B1 publication Critical patent/EP2686136B1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B24B23/028—Angle tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B47/00—Drives or gearings; Equipment therefor
    • B24B47/26—Accessories, e.g. stops
    • 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

  • a machine tool braking device of a portable machine tool which has a brake unit which is provided to brake a movement of a machining tool, at least in one operating mode.
  • the invention relates to machine tool braking device, in particular portable power tool brake device, a portable machine tool, with at least one brake unit which is provided to brake, at least in one operating mode, a movement of a machining tool.
  • the brake unit has at least one rolling element which is provided to activate at least one braking mode of the brake unit.
  • a "portable machine tool” is to be understood here in particular as meaning a machine tool, in particular a hand tool machine, which can be transported without transport machine by an operator.
  • the portable power tool has a mass which is less than 50 kg, preferably less than 20 kg and particularly preferably less than 10 kg.
  • the brake unit is preferably provided to brake a rotational movement of the machining tool.
  • the brake unit is preferably provided by means of a direct contact of at least two components, a speed, in particular a rotational speed of the Machining tool due to a conversion of kinetic energy into heat energy to reduce.
  • the brake unit is preferably provided to brake the machining tool in a braking mode of the brake unit, in particular in a period greater than 0.1 s, preferably greater than 0.5 s and particularly preferably less than 3 s, starting from a working speed, in particular one Decelerate speed that is less than 50% of the working speed, preferably less than 20% of the working speed, and more preferably decelerating to a speed of 0 m / s.
  • a "rolling element” is to be understood here in particular an element which is rotationally symmetrical at least about an axis, in particular a rotation axis.
  • the rolling element is provided to roll on at least one operating state as a result of a rotational movement about the axis of rotation with at least one surface, in particular a lateral surface, on a surface of a component.
  • the rolling element is designed as a cylinder.
  • the rolling element is designed as a ball, as a cone, as a barrel or as another, a skilled worker appearing appropriate rotation body.
  • the term "braking mode" should in particular define an operating state of the brake unit in which a braking force is generated for reducing a speed of a moving component, in particular of the machining tool.
  • a brake mode of the brake unit can be structurally activated simply. It can be advantageously used a rolling movement, in particular a rolling movement due to a centrifugal force, the rolling element to activate the braking mode.
  • the brake unit has at least one driver element which is provided to move at least one friction element of the brake unit at least in the braking mode by means of cooperation with the rolling element.
  • the driver element is advantageously rotatably mounted.
  • the friction element is moved by means of the interaction of the driver element and the rolling element along a circumferential direction.
  • the friction element is annular.
  • the friction element extends along the circumferential direction in an angular range of 360 °.
  • the circumferential direction is preferably in a mounted state in a at least substantially perpendicular to a rotational axis of the driver element extending plane.
  • substantially perpendicular is intended here to define, in particular, an orientation of a direction relative to a reference direction, the direction and the reference direction, in particular in one plane, including an angle of 90 ° and the angle a maximum deviation of, in particular, less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 °.
  • the driver element has at least one clamping contour, which is provided to clamp the rolling element between the friction element and the driver element at least in the braking mode.
  • a "clamping contour” is to be understood here in particular as a contour of the driver element, which is arranged at least in a partial area of an outer contour of the driver element running along the circumferential direction and which is intended to generate a clamping force to pinch the rolling element at least in one state. by an interaction with the friction element.
  • the clamping contour is arranged on a radial extension of the driver element. The radial extension extends at least substantially perpendicular to the axis of rotation of the driver element in a direction away from the driver element direction.
  • the clamping contour is ramp-shaped.
  • "Ramp-shaped” is to be understood here in particular as meaning a geometrical shape of the clamping contour, which has a mathematically defined gradient along a path starting from a starting point in the direction of an end point, at least in a plane comprising the starting point and the end point.
  • the starting point particularly preferably has, viewed along a direction extending at least substantially perpendicular to the axis of rotation of the driver element, a smaller distance from the axis of rotation compared with a distance of the end point from the axis of rotation.
  • a direction along which the rolling element moves at least to an activation of the braking mode can be predetermined by the clamping contour.
  • can structurally simple pinching of the rolling element in the braking mode between the friction element and the driver element can be realized.
  • the friction element has a friction extension, which is arranged in an assembled state at least partially along an axial direction between at least two brake elements of the brake unit.
  • the friction extension extends at least substantially perpendicular to the axis of rotation of the driver element in a direction away from the friction element direction.
  • the friction extension extends along the circumferential direction along an entire circumference of the friction element.
  • the axial direction advantageously extends at least substantially parallel to the axis of rotation of the driver element.
  • substantially parallel is to be understood here in particular as an alignment of a direction relative to a reference direction, in particular in a plane, wherein the direction relative to the reference direction is a deviation, in particular less than 8 °, advantageously less than 5 ° and particularly advantageously less than 2 °.
  • the embodiment according to the invention can advantageously be a kinetic energy of the friction element and thus the driver element are converted into heat energy.
  • a deceleration of the driver element can advantageously be achieved, in particular when the portable machine tool is switched off.
  • the brake unit has at least one spring element which is provided to bias at least one brake element of the brake unit in the direction of the friction element.
  • a "spring element” is to be understood in particular as a macroscopic element which has at least one extension that is elastically changeable by at least 10%, in particular by at least 20%, preferably by at least 30% and particularly advantageously by at least 50% in a normal operating state , And in particular generates a dependent of a change in the extension and preferably proportional to the change of counterforce, which counteracts the change.
  • An “extension” of an element should, in particular, be understood to mean a maximum distance between two points of a vertical projection of the element onto a plane.
  • a “macroscopic element” is meant in particular an element with an extension of at least 1 mm, in particular of at least 5 mm and preferably of at least 10 mm.
  • the brake element has at least one brake pad, which is fixed to the brake element.
  • the brake pad can be fixed to the brake element by means of a positive, non-positive and / or material connection, such as an adhesive connection, a rivet connection, a screw connection or a connection, which was produced by means of a sintering process or by means of a spraying process.
  • the brake pad can hereby be designed as a sintered brake pad, as an organic brake pad, as a brake pad made of carbon, as a brake pad made of ceramic or as another, one skilled in the art seem appropriate brake pad.
  • the friction element in particular the friction extension, can be designed to achieve a suitable combination of materials for producing an advantageous braking force in a braking mode by means of interaction with the braking element made of sintered bronze, steel, nitrided steel, aluminum or another surface-treated steel and / or metal.
  • the spring element of the brake unit structurally simple, an effect of a frictional force between the friction element and the brake element can be adjusted.
  • the brake unit has at least one actuating element which is provided as a result of a relative movement between the actuating element and a driver element of the brake unit to move the rolling element at least in one operating mode.
  • the rolling element is moved to a release of the braking mode of the brake unit by means of the actuating element.
  • a release operation can be initiated due to a relative movement. It may be advantageous to dispense with additional electrical and / or electronic components to initiate a dissolution process.
  • the machine tool braking device comprises at least one output unit, which comprises at least one output element, with which the actuating element is rotatably connected.
  • An "output unit” is to be understood here in particular as a unit which can be driven by means of a drive unit of the portable power tool and transmits forces and / or torques generated by the drive unit to a machining tool.
  • the output unit is designed as an angle gear.
  • the output element is preferably designed as a ring gear.
  • the actuating element is preferably arranged on a side facing away from a toothing of the ring gear side of the ring gear. Particularly preferred is the actuating element rotatably connected to the ring gear.
  • the actuating element may be formed integrally with the ring gear.
  • one-piece should be understood here in particular at least materially connected, for example, by a welding process, an adhesive process, Anspritzrind and / or another, a person skilled in the appear reasonable process, and / or advantageously understood in one piece, such as by a production from a casting and / or by a production in a one-component or multi-component injection molding process and advantageously from a single blank.
  • the actuating element is positively and / or non-positively connected to the ring gear, such as by means of a screw etc.
  • the machine tool braking device is designed as an assembly module.
  • the term "assembly module" is intended here to define, in particular, a structure of a unit in which a plurality of components are preassembled and the unit as a whole is mounted in an overall system, in particular in the portable machine tool.
  • the mounting module preferably has at least one fastening element, which is intended to releasably connect the mounting module with the overall system.
  • the mounting module can be dismantled from the overall system, in particular with fewer than 10 fastening elements, preferably with fewer than 8 fastening elements and particularly preferably with fewer than 5 fastening elements.
  • the fastening elements are particularly preferably designed as screws.
  • the fastening elements are designed as other elements which appear meaningful to a person skilled in the art, such as, for example, quick-action clamping elements, fastening elements which can be actuated without tools.
  • at least one function of the mounting module can be ensured in a state disassembled from the overall system.
  • the mounting module can be particularly preferably dismantled by an end user.
  • the mounting module is designed as a replaceable unit, which by another mounting module can be replaced, such as in the case of a defect of the mounting module or a functional extension and / or functional change of the overall system.
  • the brake unit as a mounting module can advantageously be achieved a wide range of uses of the machine tool brake device.
  • An integration into existing portable machine tools can also be achieved structurally simple. Furthermore, production costs can thus advantageously be kept low.
  • the invention is also based on a portable machine tool, in particular a portable hand tool, with a machine tool brake device according to the invention, in particular with a portable power tool brake device.
  • the portable machine tool can be designed here as an angle grinder, as a drill, as a circular saw, as a chisel hammer and / or as a hammer drill and so on. It can be advantageously achieved a safety function for an operator of the portable power tool.
  • the machine tool braking device according to the invention and / or the portable power tool according to the invention should not be limited to the application and embodiment described above.
  • the machine tool braking device according to the invention and / or the portable power tool according to the invention may have a number deviating from a number of individual elements, components and units specified herein for fulfilling a mode of operation described herein.
  • FIG. 1 shows a designed as angle grinder 64a portable power tool 12a with a machine tool brake device 10a.
  • the angle grinder 64a comprises a protective hood unit 66a, a machine tool housing 68a and a main handle 174a.
  • the main handle 174a extends from the machine tool housing 68a on a side facing away from a machining tool 16a side 70a of the machine tool housing 68a in a direction away from the machine tool housing 68a direction, which extends at least substantially parallel to a main direction of extent 72a of the angle grinder 64a.
  • the machining tool 16a is designed here as a grinding wheel. However, it is also conceivable that the machining tool 16a is designed as a separating or polishing disc.
  • the machine tool housing 68a comprises a motor housing 74a for receiving a drive unit 76a of the angle grinder 64a and a gear housing 78a for receiving an output unit 60a of the machine tool brake device 10a.
  • the drive unit 76a is provided to drive the machining tool 16a in rotation via the output unit 60a.
  • the output unit 60a is connected via a rotationally drivable drive element 80a of the drive unit 76a in a manner already known to a person skilled in the art to the drive unit 76a.
  • the drive element 80a is designed as a pinion which is non-rotatably connected to an armature shaft 82a of the drive unit 76a ( FIG. 2 ).
  • an additional handle 84a is further arranged on the transmission housing 78a.
  • the auxiliary handle 84a extends transversely to the main extension direction 72a of the angle grinder 64a.
  • the machine tool brake device 10a is arranged on the gear housing 78a of the angle grinder 64a ( FIG. 2 ). A portion of the machine tool braking device 10a extends into the transmission housing 78a. Thus, a portion of the machine tool brake device 10a is enclosed by the gear housing 78a.
  • the machine tool brake device 10a comprises a brake unit 14a, which is provided to brake, in a braking mode of the brake unit 14a, a movement of the machining tool 16a fixed to a spindle 88a of the output unit 60a.
  • the brake unit 14a in this case has three rolling elements 18a, 20a, 22a, which are provided to activate the braking mode of the brake unit 14a.
  • the rolling elements 18a, 20a, 22a are cylindrical ( FIG. 8 ).
  • the brake unit 14a has the output unit 60a, which has an output element 62a.
  • the output element 62a is designed as a ring gear 86a.
  • the ring gear 86a is arranged by means of a clearance fit on a rotatably mounted output shaft of the output unit 60a.
  • the output shaft of the output unit 60a is formed here by the spindle 88a.
  • the output unit 60a further comprises a bearing flange 90a and a bearing element 92a arranged in the bearing flange 90a for rotatably supporting the spindle 88a.
  • the bearing flange 90a is detachably connected to the transmission housing 78a by means of fastening elements (not shown here in detail) of the output unit 60a.
  • the machine tool brake device 10a further comprises a flow control unit 46a, which is provided to prevent a running of the machining tool 16a and / or a drainage of the fastening element for fixing the machining tool 16a of the spindle 80a in the braking mode of the brake unit 14a of the machine tool brake device 10a.
  • the flow assurance unit 46a is in this case designed as a receiving flange, which by means of a Positive fit rotationally fixed to the spindle 88a is connected.
  • the process control unit 46a is non-rotatably connected to the spindle 88a by means of other types of connection that appear appropriate to a person skilled in the art.
  • the brake unit 14a has a driver element 26a, which is provided to move a friction element 28a of the brake unit 14a in braking mode by means of interaction with the rolling elements 18a, 20a, 22a ( Figures 3 and 4 ).
  • the driver element 26a is rotatably connected to the spindle 88a.
  • the driver element 26a has three clamping contours 40a, 42a, 44a which are provided, in the braking mode, the rolling elements 18a, 20a, 22a, viewed along a direction at least substantially perpendicular to a rotation axis 24a of the spindle 88a, between the friction element 28a and pinch the driver element 26a.
  • the rolling elements 18a, 20a, 22a are arranged in the region of the clamping contours 40a, 42a, 44a.
  • a rotational axis of the driver element 26a extends in a mounted state due to the rotationally fixed connection of the driver element 26a and the spindle 88a coaxial with the axis of rotation 24a of the spindle 88a.
  • the clamping contours 40a, 42a, 44a are each formed in a ramp shape. Furthermore, the clamping contours 40a, 42a, 44a are respectively arranged on a radial extension 94a, 96a, 98a of the driver element 26a ( FIG. 7 ).
  • the radial extensions 94a, 96a, 98a extend along the direction at least substantially perpendicular to the axis of rotation 24a of the spindle 88a, starting from the driver element 26a in the direction of the friction element 28a.
  • the radial extensions 94a, 96a, 98a are arranged spaced along the at least substantially perpendicular to the axis of rotation 24a extending to the friction element 28a.
  • the radial extensions 94a, 96a, 98a are formed integrally with the driver element 26a.
  • the radial extensions 94a, 96a, 98a are connected by means of a positive and / or a frictional connection with the driver element 26a.
  • the clamping contours 40a, 42a, 44a are each arranged on a side facing the friction element 28a of the radial extensions 94a, 96a, 98a.
  • the radial extensions 94a, 96a, 98a are distributed uniformly along the circumferential direction 30a on the driver element 26a.
  • the circumferential direction 30a extends in a plane extending at least substantially perpendicular to the axis of rotation 24a of the spindle 88a.
  • the friction element 28a is annular. Furthermore, the friction element 28a is at least partially surrounded along the circumferential direction 30a by four brake elements 32a, 34a, 36a, 38a of the brake unit 14a.
  • the brake elements 32a, 34a, 36a, 38a are arranged uniformly spaced along the circumferential direction 30a. In this case, in each case two brake elements 32a, 34a, 36a, 38a directly successive along the circumferential direction 30a are arranged offset from each other by 90 °.
  • the brake elements 32a, 34a, 36a, 38a each have a brake pad on a side of the respective brake element 32a, 34a, 36a, 38a facing the friction element 28a (not shown here in detail).
  • the friction element 28a has a guide projection 120a which extends along the direction at least substantially perpendicular to the rotation axis 24a of the spindle 88a, starting from the friction element 28a in the direction of the brake elements 32a, 34a, 36a, 38a ( FIG. 8 ).
  • the guide extension 120a is provided for an axial guidance of the friction element 28a in the bearing flange 90a of the output unit 60a.
  • the brake elements 32a, 34a, 36a, 38a each have a stepped shoulder 138a, 140a, 142a, 144a ( FIG. 8 ), on which the guide extension 120a can abut in the direction of the ring gear 86a during an axial movement of the friction element 28a.
  • the bearing flange 90a has a groove-shaped recess (not shown here in detail) in which the friction element 28a is arranged with play.
  • the friction member 28a is movably disposed along the circumferential direction 30a in the bearing flange 90a.
  • the brake unit 14a has a spring element 52a, which is provided to bias the brake elements 32a, 34a, 36a, 38a of the brake unit 14a in the direction of the friction element 28a.
  • the spring element 52a is designed as an annular spring.
  • the spring element 52a comprises holding regions 122a 124a, 126a, 128a.
  • the holding portions 122a, 124a, 126a, 128a each engage in a positioning recess 130a, 132a, 134a, 136a of the corresponding brake member 32a, 34a, 36a, 38a for positioning the brake members 32a, 34a, 36a, 38a.
  • the brake elements 32a, 34a, 36a, 38a bear against the friction element 28a on a side of the friction element 28a facing the brake elements 32a, 34a, 36a, 38a.
  • the brake unit 14a further comprises three actuating elements 54a, 56a, 58a, which are provided as a result of a relative movement between the actuating elements 54a, 56a, 58a and the driver element 26a of the brake unit 14a to move in a mode of operation, the rolling element 18a, 20a, 22a ( FIGS. 3 and 4 ).
  • the rolling elements 18a, 20a, 22a are moved in the braking mode and in a release mode in which an action of braking forces on the driver element 26a, the spindle 88a and thus on the machining tool 16a is prevented, by means of the actuating elements 54a, 56a, 58a.
  • the actuating elements 54a, 56a, 58a each have two actuating arms 146a, 148a, 150a, 152a, 154a, 156a.
  • one of the actuating arms 146a, 148a, 150a, 152a, 154a, 156a of the respective actuating element 54a, 56a, 58a extends along the circumferential direction 30a and in each case one of the actuating arms 146a, 148a, 150a, 152a, 154a, 156a of the respective actuating element 54a , 56a, 58a against the circumferential direction 30a.
  • the actuating elements 54a, 56a, 58a are non-rotatably connected to the output element 62a designed as a ring gear 86a.
  • the actuating elements 54a, 56a, 58a are arranged along the at least substantially perpendicular to the axis of rotation 24a extending direction spaced from the friction element 28a ( Figures 3 and 4 ).
  • the ring gear 86a has three formed as threaded holes recesses 102a, 104a (in FIG. 5 only two shown), which are intended to be formed as screws fasteners 106a, 108a of the brake unit 14a (in FIG. 5 only two shown) for mounting a support plate 110a of the brake unit 14a record.
  • the carrier plate 110a in this case has three recesses 112a, 114a, 116a, in which the fastening elements 106a, 108a are arranged in an assembled state.
  • the actuating elements 54a, 56a, 58a are formed integrally with the carrier plate 110a ( FIG. 6 ).
  • the operating members 54a, 56a, 58a in an assembled state, viewed along the circumferential direction 30a, are uniformly arranged along the circumferential direction 30a on the support plate 110a.
  • the carrier plate 110a is arranged in an assembled state on a side facing away from a toothing 118a of the ring gear 86a side of the ring gear 86a.
  • the ring gear 86a When the angle grinder 64a is put into operation, the ring gear 86a is driven by means of the pinion-shaped drive element 80a of the drive unit 76a. In this case, the ring gear 86a first moves relative to the rotationally fixed with the Spindle 88a connected driver element 26a, until the actuating elements 54a, 56a, 58a each come to rest on a respective actuating element 54a, 56a, 58a facing driving surface 158a, 160a, 162a of the driver element 26a.
  • the rolling elements 18a, 20a, 22a are respectively moved by means of an actuating arm 146a, 150a, 154a of the respective actuating element 54a, 56a, 58a from a clamping position between the friction element 28a and the driver element 28a along the clamping contours 40a, 42a, 44a. FIG. 3 ).
  • the brake unit 14a is thus transferred to the release mode.
  • the rolling elements 18a, 20a, 22a are moved away from the friction element 28a by the movement along the clamping contours 40a, 42a, 44a.
  • the brake unit 14a is in the release mode.
  • the rolling elements 18a, 20a, 22a are arranged at a smaller distance, along the direction substantially perpendicular to the rotation axis 24a, to the spindle 88a than a distance of the rolling elements 18a, 20a, 22a to the spindle 88a in the braking mode the brake unit 14a.
  • the rotatably connected to the spindle 88a machining tool 16a is driven in rotation due to the interaction of the ring gear 86a, the driver element 26a and the spindle 88a.
  • a workpiece can be machined by means of the machining tool 16a.
  • the drive element 80a embodied as a pinion is braked by the drive unit 76a.
  • the machining tool 16a mounted on the spindle 88a continues to rotate due to inertia.
  • the spindle 88a is thus also further rotated about the rotation axis 24a.
  • the drive element 80a brakes the ring gear 86a.
  • the ring gear 86a is thereby rotated relative to the driver element 26a about the rotation axis 24a until the actuating elements 54a, 56a, 58a abut against stop surfaces 164a, 166a, 168a of the radial extensions 96a, 98a as a result of the relative movement.
  • the abutment surfaces 164a, 166a, 168a are each arranged along the circumferential direction 30a on a side of the respective radial extension 96a, 98a facing away from the respective driving surface 158a, 160a, 162a ( FIG. 4 ).
  • the rolling elements 18a, 20a, 22a are moved in the direction of the friction element 28a as a result of centrifugal force and through the respective actuating arms 148a, 152a, 156a along the clamping contours 40a, 42a, 44a.
  • the rolling elements 18a, 20a, 22a move along the clamping contour 40a, 42a, 44a until the rolling elements 18a, 20a, 22a are clamped between the friction element 28a and the clamping contours 40a, 42a, 44a. This creates a frictional connection along the circumferential direction 30a between the driver element 26a and the friction element 28a.
  • the brake unit 14a is thus in the braking mode.
  • the friction element 28a is moved around the axis of rotation 24a due to the interaction of the driver element 26a, the friction element 28a and the rolling elements 18a, 20a, 22a together with the driver element 26a due to the inertia of the machining tool 16a. At this time, the friction member 28a moves relative to the brake members 32a, 34a, 36a, 38a. The brake elements 32a, 34a, 36a, 38a thus grind on the brake elements 32a, 34a, 36a, 38a facing side of the friction element 28a.
  • the brake unit 14a is designed together with the output unit 60a as an assembly module 100a ( FIG. 5 ).
  • the mounting module 100a forms the machine tool brake device 10a.
  • the mounting module 100a comprises four fasteners designed as screws (not shown here). The bolts are intended to releasably connect the mounting module 100a to the transmission housing 78a. An operator may disassemble the mounting module 100a from the transmission housing 78a as needed.
  • the angle grinder 64a and the machine tool brake device 10a thus form a machine tool system.
  • the machine tool system may include another mounting module.
  • the further assembly module can comprise, for example, a drive unit designed as an angle gear.
  • the further assembly module could, for example, be mounted on the transmission housing 78a by the operator as an alternative to the mounting module 100a.
  • an operator thus has the option of equipping the angle grinder 64a with the assembly module 100a with the brake unit 14a and the output unit 60a or with the further assembly module with an output unit.
  • the assembly module 100a can be replaced by the further assembly module of the machine tool system by an operator.
  • the operator merely disassembles the mounting module 100a from the gear housing 78a and mounts the further mounting module on the gear housing 78a.
  • FIGS. 9 to 12 Alternative embodiments are shown. Substantially identical components, features and functions are basically numbered by the same reference numerals. To distinguish the embodiments, the letters a to c are added to the reference numerals of the embodiments. The following description is limited essentially to the differences from the first embodiment in the FIGS. 1 to 8 , wherein with respect to the same components, features and functions on the description of the first embodiment in the FIGS. 1 to 8 can be referenced.
  • FIG. 9 shows an alternative machine tool brake device 10b to a transmission housing of an analogous to that in the description of FIGS. 1 to 8 described angle grinder 64a trained angle grinder (not shown here) can be mounted.
  • the machine tool brake device 10b includes a brake unit 14b, which is intended to brake in a mode of operation, a movement of a machining tool (not shown here). Furthermore, the machine tool brake device 10b comprises an output unit 60b.
  • the brake unit 14b and the output unit 60b have an at least substantially analogous structure to the brake unit 14a and the output unit 60a, which in the description of FIG FIGS. 1 to 8 was described on.
  • the brake unit 14b has three rolling elements 18b, 20b, 22b, and the output unit 60b has an output element 62b designed as a ring gear 86b.
  • the rolling elements 18b, 20b, 22b are provided to activate a braking mode of the brake unit 14b.
  • the brake unit 14b has three actuating elements 54b, 56b, 58b, which are formed integrally with the output element 62b designed as a ring gear 86b.
  • the actuating elements 54b, 56b, 58b each have an actuating arm 146b, 148b, 150b, which is provided in each case for preventing as far as possible movement of the respective rolling element 18b, 20b, 22b in the direction of a friction element 28b of the brake unit, and the rolling elements 18b, 20b , 22b to press against clamping contours 40b, 42b, 44b of a driver element 26b of the brake unit 14b.
  • the actuating arms 146b, 148b, 150b are each arranged on a respective clamping contour 40b, 42b, 44b side facing the actuating element 54b, 56b, 58b on the respective actuating element 54b, 56b, 58b.
  • FIG. 10 shows a further alternative machine tool brake device 10c which is mounted on a gear housing of an analogous to the described in the description of Figures 1 to 8 angle grinder 64a angle grinder (not shown here) mounted.
  • the machine tool brake device 10c comprises a brake unit 14c, which is provided to brake a movement of a machining tool (not shown here in detail) in an operating mode.
  • the machine tool brake device 10c has an output unit 60c.
  • the output unit 60c has an at least substantially analogous structure to the output unit 60a, which in the description of the FIGS. 1 to 8 was described on.
  • the output unit 60c has a driven element 62c designed as a ring gear 86c.
  • the output element 62c designed as a ring gear 86c is by means of a clearance fit arranged on a rotatably mounted and designed as a spindle 88c output shaft of the output unit 60c.
  • the brake unit 14c has three rolling elements 18c, 20c, 22c which are provided to activate a braking mode of the brake unit 14c ( FIG. 11 ).
  • the rolling elements 18c, 20c, 22c are formed as balls.
  • the brake unit 14c has three actuating elements 54c, 56c, 58c.
  • the actuators 54c, 56c, 58c are pin-shaped.
  • the actuating elements 54c, 56c, 58c viewed in a plane extending at least substantially to a rotational axis 24c of the spindle 88c, have a rectangular cross-section.
  • the actuating elements 54c, 56c, 58c are connected by means of a positive and / or non-positive connection with the ring gear 86c.
  • the actuating elements 54c, 56c, 58c are formed integrally with the ring gear 86c.
  • the brake unit 14c has a driver element 26c, which is provided to move a friction element 28c of the brake unit 14c in braking mode by means of cooperation with the rolling elements 18c, 20c, 22c.
  • the driver element 26c has three clamping contours 40c, 42c, 44c, which are provided in the braking mode to clamp the rolling elements 18c, 20c, 22c between the friction element 28c and the driver element 26c.
  • the rolling elements 18c, 20c, 22c are arranged in the region of the clamping contours 40c, 42c, 44c.
  • the rolling elements 18c, 20c, 22c by means of the actuators 54c, 56c, 58c along the clamping contours 40c, 42c, 44c away from the friction element 28c moves until the rolling elements 18c, 20c, 22c abut on driving surfaces 158c, 160c, 162c of radial projections 94c, 96c, 98c of the driver element 26c.
  • the actuating elements 54c, 56c, 58c thus transmit a torque via the rolling elements 18c, 20c, 22c to the driver element 26c.
  • the radial extensions 94c, 96c, 98c are arranged at a distance from the friction element 28c at least substantially perpendicular to the axis of rotation 24c.
  • the cam member 26c and the rolling elements 18c, 20c, 22c can move together with the cam members 86c arranged on the ring gear 86c, 56c, 58c in a release mode of the brake unit 14c relative to the friction member 28c.
  • the friction element 28c has a friction extension 48c, which is arranged in an assembled state at least partially along an axial direction 50c between two brake elements 32c, 34c of the brake unit 14c.
  • the axial direction 50c extends at least substantially parallel to the axis of rotation 24c of the spindle 88c.
  • the friction extension 48c extends starting from the friction element 28c along the direction at least substantially perpendicular to the rotation axis 24c in the direction of a bearing flange 90c of the output unit 60c.
  • the brake elements 32c, 34c are arranged fixed to the housing in the bearing flange 90c.
  • One of the brake elements 32c, 34c is biased by means of a spring element 52c of the brake unit 14c in the direction of the friction extension 48c formed integrally with the friction element 28c.
  • the brake unit 14c has three control springs 170c (in FIG FIG. 12 only one shown), which are intended to bias the rolling elements 18c, 20c, 22c in the direction of the friction element 28c.
  • the adjusting springs 170c are each arranged in a recess 172c in the radial extensions 94c, 96c, 98c (in FIG FIG. 12 only one shown).
  • the brake unit 14c on guide extensions 176c, 178c, 180c, which are arranged in an assembled state in the recesses 172c of the radial projections 94c, 96c, 98c.
  • the guide extensions 176c, 178c, 180c are bolt-shaped. It is conceivable that the guide extensions 176c, 178c, 180c are formed integrally with the rolling elements 18c, 20c, 22c. The rolling elements 18c, 20c, 22c are moved in the direction of the driving surfaces 158c, 160c, 162c against movement of the actuating elements 54c, 56c, 58c counter to a spring force of the adjusting springs 170c. With regard to a further mode of operation of the brake unit 14c and the output unit 60c, reference may be made to the description of FIGS. 1 to 8 to get expelled.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Portable Power Tools In General (AREA)
EP12703280.3A 2011-03-18 2012-02-02 Werkzeugmaschinenbremsvorrichtung Active EP2686136B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011005812A DE102011005812A1 (de) 2011-03-18 2011-03-18 Werkzeugmaschinenbremsvorrichtung
PCT/EP2012/051720 WO2012126660A1 (de) 2011-03-18 2012-02-02 Werkzeugmaschinenbremsvorrichtung

Publications (2)

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EP2686136A1 EP2686136A1 (de) 2014-01-22
EP2686136B1 true EP2686136B1 (de) 2015-10-07

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US (1) US20140124307A1 (zh)
EP (1) EP2686136B1 (zh)
CN (1) CN103429385B (zh)
DE (1) DE102011005812A1 (zh)
RU (1) RU2013146367A (zh)
WO (1) WO2012126660A1 (zh)

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DE102010043185A1 (de) * 2010-10-29 2012-05-03 Robert Bosch Gmbh Werkzeugmaschinenbremsvorrichtung
DE102013200867A1 (de) * 2013-01-21 2014-07-24 Robert Bosch Gmbh Werkzeugmaschinenbremsvorrichtung
DE102013212193A1 (de) * 2013-06-26 2014-12-31 Robert Bosch Gmbh Handwerkzeugmaschine mit einer Spindellockvorrichtung
CN105014541A (zh) * 2014-04-23 2015-11-04 电能有限公司 具有停机制动装置的手持电动砂轮机
DE102014211578A1 (de) * 2014-06-17 2015-12-17 Robert Bosch Gmbh Elektrowerkzeugmaschine

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CN2688041Y (zh) * 2004-03-16 2005-03-30 苏州宝时得电动工具有限公司 刹车装置
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Also Published As

Publication number Publication date
US20140124307A1 (en) 2014-05-08
EP2686136A1 (de) 2014-01-22
CN103429385B (zh) 2016-10-19
DE102011005812A1 (de) 2012-09-20
RU2013146367A (ru) 2015-04-27
WO2012126660A1 (de) 2012-09-27
CN103429385A (zh) 2013-12-04

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