EP2632632B1 - Tragbare werkzeugmaschine - Google Patents

Tragbare werkzeugmaschine Download PDF

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Publication number
EP2632632B1
EP2632632B1 EP11760476.9A EP11760476A EP2632632B1 EP 2632632 B1 EP2632632 B1 EP 2632632B1 EP 11760476 A EP11760476 A EP 11760476A EP 2632632 B1 EP2632632 B1 EP 2632632B1
Authority
EP
European Patent Office
Prior art keywords
unit
spindle
coding
brake
angle grinder
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.)
Not-in-force
Application number
EP11760476.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2632632A1 (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
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.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2632632A1 publication Critical patent/EP2632632A1/de
Application granted granted Critical
Publication of EP2632632B1 publication Critical patent/EP2632632B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B24B45/00—Means for securing grinding wheels on rotary arbors
    • 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
    • B24B45/00—Means for securing grinding wheels on rotary arbors
    • B24B45/006—Quick mount and release means for disc-like wheels, e.g. on power 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
    • B24B55/00—Safety devices for grinding or polishing machines; Accessories fitted to grinding or polishing machines for keeping tools or parts of the machine in good working condition
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
    • B27B—SAWS FOR WOOD OR SIMILAR MATERIAL; COMPONENTS OR ACCESSORIES THEREFOR
    • B27B5/00—Sawing machines working with circular or cylindrical saw blades; Components or equipment therefor
    • B27B5/29—Details; Component parts; Accessories
    • B27B5/30—Details; Component parts; Accessories for mounting or securing saw blades or saw spindles
    • B27B5/32—Devices for securing circular saw blades to the saw spindle

Definitions

  • a portable power tool known with a spindle for receiving and driving a machining tool with at least one brake unit, which is intended to brake at least in an operating mode, the spindle and / or the machining tool, and with a safety device, which is provided at least in the braking mode thereto to avoid drainage of the machining tool from the spindle.
  • a portable machine tool in particular a hand tool, with at least one spindle for receiving and driving a machining tool, with at least one brake unit, which is intended to brake at least in a braking mode, the spindle and / or the machining tool, and with at least one flow assurance unit , which is provided at least in the braking mode to avoid running of the machining tool from the spindle proposed.
  • 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.
  • a “braking unit” is to be understood here as meaning, in particular, a unit which is intended to at least substantially reduce a speed, in particular a rotational speed, of a moving component, in particular of a rotating component, compared to an operating speed of the component, and / or or limit.
  • the braking unit reduces and / or limits the speed in addition to a purely friction-related Reducing and / or limiting the speed due to storage of the component.
  • a “braking mode” is to be understood here as meaning, in particular, a mode of the portable power tool, in which the spindle is braked by means of the braking unit, so that tracking of the spindle, such as, for example, when a power supply to an electric motor is interrupted, is advantageous at least largely prevented.
  • moments of inertia of the machining tool may result in relative movement between the machining tool mounted on the spindle, the run-down safety unit and a clamping nut provided on the spindle for clamping the machining tool.
  • the relative movement between the machining tool and the clamping nut can cause the clamping nut is released and thus can run off the spindle.
  • substantially parallel is to be understood here as meaning, in particular, 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 process control unit is detachably coupled to the spindle.
  • Decorable is to be understood here in particular as a decoupling of the operational safety device from the spindle, wherein at least one function of the safety device, in particular a relative movement between at least two safety elements of the safety device, remains in a decoupled state.
  • the flow safety unit is designed as a receiving flange.
  • the portable power tool comprises an encoding unit which is provided to generate an encoding at least between the spindle and the operation safety unit.
  • a "coding unit” is to be understood here as meaning, in particular, a unit which is intended to encrypt an interface of the portable power tool between at least two components, in particular between the spindle and the execution assurance unit, in particular according to a key-keyhole principle.
  • the interface between the spindle and the anti-drainage unit is in particular intended to fix an axial position of the anti-skid unit relative to a dimension of the spindle along the axial direction on the spindle and to define a concentric position of the anti-skid unit with respect to an axis of rotation of the spindle.
  • the coding unit is designed as an electronic, electrical, optical, magnetic and / or electromagnetic coding unit.
  • the coding unit is in this case preferably coupled to a control and / or regulating unit which controls and / or regulates the starting of an electric motor unit of a drive unit of the portable power tool.
  • a "control and / or regulating unit” is to be understood here in particular as a unit having at least one control unit.
  • a “control unit” is to be understood in particular as meaning a unit having a processor unit and a memory unit as well as an operating program stored in the memory unit.
  • the brake unit is designed as a mechanical brake.
  • the brake unit has at least one friction lining, which is intended to brake the spindle in a braking mode. It can be achieved structurally simple brake unit for braking the spindle.
  • the brake unit is designed as an electromagnetic brake.
  • the brake unit is preferably designed as an eddy-current brake and / or as a hysteresis brake.
  • the brake unit is designed as another, an expert appear appropriate sense electromagnetic brake.
  • the electromagnetic brake preferably has at least one permanent magnet which, in at least one operating mode, generates a magnetic field acting on an eddy current element and / or a hysteresis element. It can be achieved advantageously a friction-acting brake unit.
  • the brake unit is designed as a mounting 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 can be 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 in one of the entire system disassembled state be guaranteed.
  • the mounting module can be particularly preferably assembled and / or disassembled by an end user.
  • the mounting module is designed as a replaceable unit that can be replaced by another mounting module, such as in the case of a defect of the mounting module or a functional extension and / or a functional change of the overall system.
  • the brake unit as an assembly module, structurally simple integration into already existing portable machine tools can be achieved. Furthermore, thus advantageous production costs can be kept low.
  • the invention is further based on a machine tool system, in particular a hand-held power tool system, with a portable power tool according to the invention and with at least one mounting module. It is proposed that the mounting module can be mounted on the portable machine tool as an alternative to the brake unit, which is designed as a mounting module. It can be advantageously achieved a wide range of uses of the portable power tool.
  • FIG. 1 shows a designed as angle grinder 44a portable power tool 10a.
  • the angle grinder 44a comprises a protective hood unit 46a, a machine tool housing 48a and a main handle 50a, which on a side facing away from a machining tool 14a side 52a of the machine tool housing 48a in the direction of a main extension direction 54a of the Angle grinder 44a extends.
  • the machining tool 14a is designed here as a grinding wheel. However, it is also conceivable that the machining tool 14a is formed as a separating or polishing wheel.
  • the machine tool housing 48a comprises a motor housing 56a for receiving a drive unit 58a of the angle grinder 44a and a gear housing 60a for receiving an output unit 62a of the angle grinder 44a.
  • the drive unit 58a is provided for rotating the machining tool 14a via the output unit 62a.
  • the angle grinder 44a has a spindle 12a for receiving and driving the machining tool 14a (FIG. FIG. 2 ).
  • the output unit 62a is connected to the drive unit 58a via a drive element 66a of the drive unit 58a that is rotationally driven about a rotation axis 64a.
  • the drive element 66a is designed as an armature shaft 68a (FIG. 2).
  • On the gear housing 60a an auxiliary handle 70a is arranged on the gear housing 60a.
  • the auxiliary handle 70a extends transversely to the main extension direction 54a of the angle grinder 44a.
  • FIG. 2 shows an arrangement of a brake unit 16a of the angle grinder 44a in the transmission housing 60a.
  • the brake unit 16a is designed as an electromagnetic brake.
  • the brake unit 16a is provided to brake the spindle 12a and / or the machining tool 14a in a braking mode.
  • the angle grinder 44a has a down-flow securing unit 18a, which in the braking mode is provided to prevent the machining tool 14a from running away from the spindle 12a.
  • the flow assurance unit 18a has a movement change unit (not shown here in detail), which is provided to transfer in the braking mode, a first relative movement between two flow protection elements (not shown here) in a second relative movement.
  • the flow assurance unit 18a is formed as a receiving flange, which is rotatably connected by means of a positive connection with the spindle 12a.
  • the receiving flange is rotatably connected to the spindle 12a by means of other types of connection that appear appropriate to a person skilled in the art.
  • the brake unit 16a further comprises a mechanical activation unit 72a.
  • the activation unit 72a is provided to change a characteristic of a magnetic field of the electromagnetic brake as a result of a relative movement.
  • the output unit 62a of the angle grinder 44a comprises an output element 74a on which at least one braking element 78a of the brake unit 16a designed as the first permanent magnet 76a is arranged.
  • the output unit 62a is designed as an angle gear 80a, which is coupled for torque transmission with the drive unit 58a of the angle grinder 44a.
  • the brake unit 16a is arranged behind a transmission input gear 82a of the angle gear 80a along a power flow originating from the drive unit 58a.
  • the output element 74a is formed here as a crown wheel 84a.
  • the ring gear 84a is in a mounted state of the output unit 62a in engagement with a pinion 86a of the drive unit 58a.
  • the transmission input gear 82a is thus formed by the ring gear 84a.
  • FIG. 3 shows a detailed view of the ring gear 84a of the output unit 62a.
  • the ring gear 84a is formed of a magnetically conductive material such as a ferromagnetic material. As a result, a magnetic field in the region of the ring gear 84a can be compressed and leakage fluxes can be kept low.
  • the ring gear 84a has three rotational drive elements 100a, 102a, 104a on a side 98a of the ring gear 84a facing away from a toothing 96a of the ring gear 84a.
  • the ring gear 84a has one of three different number of rotational drive elements 100a, 102a, 104a.
  • a person skilled in the art will provide a suitable number of rotary drive elements 100a, 102a, 104a on the ring gear 84a.
  • the rotational drive elements 100a, 102a, 104a are distributed uniformly along a circumferential direction 106a on the side 98a of the ring gear 84a facing away from the toothing 96a.
  • the circumferential direction 106a extends in this case in a direction perpendicular to a rotation axis 108a of the Tellerrads 84a extending level.
  • the ring gear 84a rotates in an operation for transmitting torques to the machining tool 14a about the rotation axis 108a.
  • rotational drive elements 100a, 102a, 104a extend perpendicular to the side 98a of the ring gear 84a facing away from the toothing 96a.
  • the rotational drive elements 100a, 102a, 104a extend in the direction of the entrainment element 94a (FIG. FIG. 2 ).
  • the brake unit 16a has a further brake element 126a, which is designed as an eddy current element 128a.
  • the brake unit 16a is formed as an eddy current brake.
  • the brake line 16a has, as an alternative to the eddy current element 128a, a braking element designed as a hysteresis element and is thus designed as a hysteresis brake.
  • the eddy current element 128a is formed of an electrically conductive material, such as aluminum and / or copper. Further, the eddy current element 128a is disposed axially along the rotational axis 108a of the ring gear 84a between the first permanent magnet 76a and the second permanent magnet 120a.
  • the eddy current element 128a is fixedly connected to the bearing flange 88a.
  • the first permanent magnet 76a and the second permanent magnet 120a are moved by means of the spindle 12a relative to the eddy current element 128a.
  • the driving element 94a and the spindle 12a are formed of a non-magnetizable material, such as stainless steel, etc.
  • FIG. 4 shows a detailed view of the driving element 94a.
  • the driving element 94a has three rotational driving recesses 110a, 112a, 114a for receiving the rotary driving elements 100a, 102a, 104a.
  • the rotational drive elements 100a, 102a, 104a thus extend in an assembled state along the rotational axis 108a of the ring gear 84a into the rotational engagement recesses 110a, 112a, 114a.
  • the Drehitddlingaus Principle 110a, 112a, 114a are arranged along the circumferential direction 106a evenly distributed on the driving element 94a.
  • the rotational driving recesses 110a, 112a, 114a along the circumferential direction 106a have a greater extent compared to the rotational drive elements 100a, 102a, 104a. It is achieved a rotational play between the ring gear 84a and the driving element 94a along the circumferential direction 106a.
  • the rotational play is formed by an angular range around which the ring gear 84a can be rotated relative to the driving element 94a.
  • the angular range is hereby formed by a circumference of 360 °, divided by the number of poles of the permanent magnets 76a, 120a.
  • the rotary driving elements 100a, 102a, 104a on the driving element 94a and the Drehit Vietnameseaus Principle 110a, 112a, 114a are arranged on the ring gear 84a.
  • the rotational engagement elements 100a, 102a, 104a of the ring gear 84a and the rotational engagement recesses 110a, 112a, 114a of the carrier element 94a form the mechanical activation unit 72a.
  • the brake unit 16a is in a rest state of the angle grinder 44a in a braking mode.
  • a braking mode opposite polarities of the angular segments 116a, 118a of the first permanent magnet 76a and of the angular segments of the second permanent magnet 120a, respectively, follow each other Viewed rotation axis 108 of the ring gear 84a, opposite.
  • the angle grinder 44a is put into operation by energizing an electric motor unit of the drive unit 58a, the ring gear 84a is driven by the pinion 86a.
  • the permanent magnets 76a, 120a in addition to the rotation relative to each other by means of the activation unit 72a along the rotation axis 108a are moved in translation relative to each other.
  • a distance between the permanent magnets 76a, 120a can be changed.
  • a groove may be provided on the spindle 12a, which has a mathematically defined pitch along the axis of rotation 108a.
  • a lifting element could engage in the groove.
  • the first permanent magnet 76a could be moved in a direction away from the carrier element 94a relative to the second permanent magnet 120a.
  • the first permanent magnet 76a is rotated relative to the second permanent magnet 120a due to the relative movement between the ring gear 84a and the follower 94a. As a result, the brake unit 16a is switched to an operating mode in which small magnetic forces of the brake unit 16a act on the eddy current element 128a.
  • the activation unit 72a changes a pole position of the first permanent magnet 76a relative to the second permanent magnet 120a of the brake unit 16a when changing from a braking mode to an operating mode.
  • the pinion 86a is braked by the electric motor unit.
  • the machining tool 14a mounted on the spindle 12a further rotates due to inertia.
  • the spindle 12a is thus also further rotated about the rotation axis 108a.
  • the machining tool 14a has larger mass moments of inertia compared to the pinion 86a.
  • the pinion 86a thus brakes the ring gear 84a.
  • the ring gear 84a is rotated relative to the driving element 94a about the rotation axis 108a until the rotary driving elements 100a, 102a, 104a abut against edge regions of the rotational driving recesses 110a, 112a, 114a.
  • the brake unit 16a is hereby switched to a braking mode.
  • the two permanent magnets 76a, 120a are rotated relative to each other.
  • the first permanent magnet 76a is in this case rotated relative to the second permanent magnet 120a until oppositely directed polarities of the angular segments 116a, 118a of the first permanent magnet 76a and the angular segments of the second permanent magnet 120a, viewed along the rotational axis 108a of the ring gear 84a, face each other.
  • a voltage is induced in the eddy current element 128a.
  • the induced voltage causes a current flow perpendicular and vortex-shaped to a magnetic flux of the brake unit 16a. In this case, eddy currents are formed.
  • the eddy currents generate in the eddy current element 128a a magnetic field which counteracts a magnetic field of the permanent magnets 76a, 120a.
  • a braking torque is generated, which decelerates the with the spindle 12a relative to the eddy current element 128a rotating permanent magnets 76a, 120a.
  • the spindle 12a and the machining tool 14a are also braked.
  • a strength of the magnetic field of the brake unit 16a and thus a propagation of a magnetic flux of the brake unit 16a for generating the braking torque is dependent on a distance along the rotation axis 108a between the first permanent magnet 76a and the second permanent magnet 120a and a pole position along the circumferential direction 106a of first permanent magnet 76a and second permanent magnet 120a relative to each other.
  • the brake unit 16a is designed together with the output unit 62a as an assembly module 40a ( FIG. 6 ).
  • the mounting module 40a comprises four fasteners designed as screws (not shown here). The screws are intended to releasably connect the mounting module 40a to the transmission housing 60a. An operator may disassemble the mounting module 40a from the transmission housing 60a as needed.
  • the angle grinder 44a and the mounting module 40a thus form a machine tool system.
  • the machine tool system comprises a further mounting module 42a (FIG. FIG. 7 ).
  • the further assembly module 42a comprises a drive unit 130a configured as an angle gear and decoupled from a brake unit.
  • the further assembly module 42a may be mounted on the transmission housing 60a by the operator as an alternative to the mounting module 40a.
  • an operator thus has the option of equipping the angle grinder 44a with a mounting module 40a with a brake unit 16a and an output unit 62a or with an assembly module 42a with an output unit 130a.
  • the mounting module 40a can be replaced by the further mounting module 42 of the machine tool system by an operator.
  • the operator merely disassembles the mounting module 40a from the gear housing 60a and mounts the further mounting module 42a on the gear housing 60a.
  • the machine tool 10a has, in addition to the brake unit 16a, a further brake unit which is arranged in the motor housing 56a of the angle grinder 44a.
  • the angle grinder 44a comprises a cooling unit which is provided to dissipate heat generated by the brake unit 16a in the braking mode as a result of internal friction of the eddy current element 128a.
  • the brake unit 16a has an electromagnet. The solenoid may be provided to allow additional torque during start-up of the drive unit 58a to achieve a working speed of the electric motor unit in a short period of time, such as preferably to achieve a boost operation.
  • the electromagnet is intended to amplify a magnetic field of the permanent magnets 76a, 120a. As a result, a strong braking torque for braking the rotating permanent magnet 76a, 120a can be achieved.
  • the electromagnet can in this case be coupled, for example, with a safety unit which activates the electromagnet, for example, when the machining tool 14a bursts, in order to prevent further rotation of the spindle 12a of the angle grinder 44a.
  • the portable power tool 10a embodied as an angle grinder 44a has an encoding unit 20a which is provided to generate an encoding between the spindle 12a and the run-down protection unit 18a that can be mounted on the spindle 12a ( FIG. 2 ).
  • the coding unit 20a is designed as a mechanical coding unit 20a.
  • the coding unit 20a has a first coding element 22a, which is formed integrally with the spindle 12a.
  • the first coding element 22a is, in one plane viewed perpendicular to a rotation axis 132a of the spindle 12a, formed as a circular segment 134a.
  • the rotation axis 132a of the spindle 12a extends in a mounted state of the spindle 12a coaxially with the rotation axis 108a of the ring gear 84a.
  • the code-turning unit 20a further has a second coding element 24a, which is formed integrally with the sequence-securing unit 18a ( FIG. 8 ).
  • the second coding element 24a is designed as an edge 136a delimiting a recess of the drainage sealing unit 18a.
  • the recess of the flow assurance unit 18a viewed in a mounted state of the flow assurance unit 18a in the plane perpendicular to the rotation axis 132a of the spindle 12a, has a shape corresponding to the circle segment 134a.
  • limiting edge 136a is located on an outer periphery 168a of the circular segment 134a.
  • the outer periphery 168a of the circle segment 134a extends along the circumferential direction 106a, which extends in a plane perpendicular to the rotation axis 132a of the spindle.
  • FIGS. 9 to 20 Alternative embodiments are shown. Substantially identical components, features and functions are basically numbered by the same reference numerals. To distinguish the embodiments, the reference numerals of the embodiments, the letters a to k are added. 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.
  • the coding unit 20b has an RFID reader 140b, which is arranged in a gear housing 60b of the angle grinder 44b.
  • the RFID reader 140b is provided to read a key and / or an identifier from the RFID coding element 38b.
  • the coding unit 20b is connected to a control and / or regulating unit 142b of the angle grinder 44b.
  • the angle grinder 44b has a display unit 138b ( FIG. 9 ).
  • the display unit 138b is provided to indicate an operational readiness of the angle grinder 44b to an operator as a result of the anti-dropping unit 18b mounted on the spindle 12b. If a receiving unit that is decoupled from an RFID coding element and / or has an RFID coding element that has a key that is not permitted for the coding unit 20b is mounted on the spindle 12b, the display unit 138b indicates to an operator that a startup of the Angle grinder 44b is prevented by means of the control and / or regulating unit.
  • the display unit 138b may be formed by analog display means such as a pointer or the like, and / or electronic display means such as LEDs or a LC display, etc.
  • the angle grinder 44b further comprises a brake unit 16b, one for the brake unit 16a FIG. 2 has analog structure. Thus, with respect to an operation of the brake unit 16b to the description of FIGS. 2 to 8 to get expelled.
  • the brake unit 16b is formed together with the output unit 62b as a mounting module 40b.
  • the mounting module 40b includes four as Screw trained fasteners (not shown here). The screws are intended to releasably connect the mounting module 40b to the transmission housing 60b. An operator may disassemble the mounting module 40b from the transmission housing 60b as needed.
  • the angle grinder 44b and the mounting module 40b thus form a machine tool system.
  • the machine tool system comprises a further mounting module (not shown here).
  • the further mounting module can be mounted on the transmission housing 60b by the operator as an alternative to the mounting module 40b.
  • FIG. 11 shows an alternative coding unit 20c, which is intended to generate an encoding between a spindle 12c and a flow assurance unit 18c of an angle grinder (not shown here).
  • the coding unit 20c is designed as a mechanical coding unit 20c.
  • the coding unit 20c has a first coding element 22c, which is formed integrally with the spindle 12c.
  • the first coding element 22c has a geometric shape which has a base circle 26c and an encoding structure 28c projecting beyond the base circle 26c.
  • the coding structure 28c extends along a radial direction of the base circle 26c.
  • the coding structure 28c is arranged in a region of the spindle 12c, which is intended to receive the run-off securing unit 18c and / or to form a contact surface of the spindle 12c for the axial support of the run-off securing unit 18c.
  • the coding structure 28c is arranged in a plane parallel to a surface enclosed by the base circle 26c.
  • a radial extent of the coding structure 28c is greater than a radial extent of the area enclosed by the base circle 26c.
  • the coding structure 28c and the base circle 26c viewed along a rotation axis 132c of the spindle 12c, are connected to one another by means of a lateral surface 144c of the coding element 22c.
  • the coding structure 28c, the base circle 26c and the lateral surface 144c form a truncated cone, which is formed integrally with the spindle 12c.
  • the coding unit 20c furthermore has a second coding element 24c, which is formed by an edge 136c which delimits a recess of the sequence-securing unit 18c.
  • the edge 136c has a conical shape with respect to the rotation axis 132c.
  • the first coding element 22c designed as a truncated cone rests against the edge 136c.
  • the societysicheurngstechnik 18c is in this case rotatably connected to the spindle 12c.
  • FIG. 12 shows a sectional view of an alternative coding element 22d of an alternative coding unit 20d.
  • the coding element 22d is integrally formed with a spindle 12d of an angle grinder (not shown in detail here).
  • the coding element 22d has a geometric shape which has a base circle 26d and an encoding structure 28d projecting beyond the base circle 26d.
  • the coding structure 28d extends along a radial direction of the base circle 26d.
  • the coding structure 28d includes a plurality of rectangular shaped drivers 146d, 148d, 150d, 152d, 154d, 156d.
  • the drivers 146d, 148d, 150d, 152d, 154d, 156d are distributed uniformly along the circumference sight 106d on the base circle 26d.
  • the spindle 12d thus has a splined shaft profile for encoding an interface.
  • a monitorable on the spindle 12d flow assurance unit (not shown here) has a for the encryption of the encrypted interface with the coding structure 28d korresspondierende embodiment.
  • FIG. 13 shows a sectional view of an alternative coding element 22e of an alternative coding unit 20e.
  • the coding element 22e is integrally formed with a spindle 12e of an angle grinder (not shown in detail here).
  • the coding element 22e has a geometric shape which has a base circle 26e and an encoding structure 28e projecting beyond the base circle 26e.
  • the coding structure 28e extends along a radial direction of the base circle 26e.
  • the coding structure 28e comprises a toothing 158e.
  • the toothing 158e extends along a circumferential direction 106e on an outer surface of the spindle 12e.
  • the spindle 12e thus has a serration profile for encoding an interface.
  • a on the spindle 12e monitierbare flow assurance unit (not shown here) has a for decrypting the encrypted interface with the coding structure 28e korresspond Schlettide embodiment.
  • FIG. 14 shows a sectional view of an alternative coding element 22f of an alternative coding unit 20f.
  • the coding element 22f is integrally formed with a spindle 12f of an angle grinder (not shown in detail here).
  • the coding element 22f has a geometric shape which has a base circle 26f and an encoding structure 28f projecting beyond the base circle 26f.
  • the coding structure 28f extends along a radial direction of the base circle 26f.
  • the coding structure 28e comprises a A plurality of drivers 146f, 148f, 150f, 152f, 154f, 156f, wherein the flanks of the drivers 146f, 148f, 150f, 152f, 154f, 156f are formed by involutes.
  • FIG. 15 shows a sectional view of an alternative coding element 22g of an alternative coding unit 20g.
  • the coding element 22g is formed integrally with a spindle 12g of an angle grinder (not shown here in detail).
  • the coding element 22g has a geometric shape which has a base circle 26g and an encoding structure 28g projecting beyond the base circle 26g.
  • the coding structure 28g extends along a radial direction of the base circle 26g.
  • the coding structure 28g is formed as a polygon with rounded corners.
  • the spindle 12g thus has a polygonal profile for encryption of an interface.
  • One on the spindle 12g monitierbare flow assurance unit (not shown here) has a for the decryption of the encrypted interface with the coding structure 28g korresspond Schlettide embodiment.
  • FIG. 16 shows a sectional view of an alternative coding element 22h of an alternative coding unit 20h.
  • the coding element 22h is integrally formed with a spindle 12h of an angle grinder (not shown in detail here).
  • the coding element 22h comprises a longitudinal recess 30h for receiving a positive-locking element 32h of the coding unit 20h.
  • the positive locking element 32h is formed as a key 160h.
  • the key 160h extends in an assembled state parallel to a rotational axis 132h of the spindle 12h.
  • the spindle 12h thus has a feather key connection for encrypting an interface.
  • One on the spindle 12h monitierbare flow assurance unit (not shown here) has an axial groove for decrypting the encrypted interface, which is formed corresponding to the key 160h.
  • FIG. 17 shows a sectional view of an alternative coding element 22i of an alternative coding unit 20i.
  • the coding element 22i is integrally formed with a spindle 12i of an angle grinder (not shown in detail here).
  • the coding element 22i comprises a longitudinal recess 30i for receiving a positive-locking element 32i of the coding unit 20h.
  • the form-fitting element 32i is designed as a longitudinal pin 162i.
  • the longitudinal pin 162i extends in an assembled state parallel to a rotational axis 132i of the spindle 12i.
  • a monitorable on the spindle 12i flow assurance unit (not shown here) has an axial groove for decrypting the encrypted interface, which is formed corresponding to the longitudinal pin 162i.
  • FIG. 18 shows a sectional view of an alternative coding element 22j of an alternative coding unit 20j.
  • the coding element 22j is integrally formed with a spindle 12j of an angle grinder (not shown in detail here).
  • the coding element 22j comprises a transverse recess 34j for receiving a positive-locking element 36j of the coding unit 20j.
  • the positive connection element 36j is designed as a transverse pin 164j.
  • the cross pin 164j extends in an assembled state perpendicular to a rotational axis 132j of the spindle 12j.
  • the cross pin extends along a direction perpendicular to the axis of rotation 132j on two sides beyond an outer surface 166j of the spindle 12j.
  • a run-down protection unit 18j (merely indicated) which can be mounted on the spindle 12j has two grooves for decrypting the encrypted interface which are formed corresponding to regions of the transverse pin 164j which project beyond the outer surface 166j of the spindle on two sides.
  • the sequence assurance unit 18k has a movement change unit (not shown here in detail) which is provided to transfer a first relative movement between two flow control elements (not shown in detail here) into a second relative movement in the braking mode.
  • the brake unit 16k is designed as a mechanical brake. With regard to a structure and an operation of the brake unit 16k of Hand tool may in particular to the publication DE 195 10 291 C2 be referenced, the content, in particular with regard to the structure and operation of the brake unit 16k is to be regarded as part of the disclosure of the present document.
  • the rotation axis 132k of the spindle 12k is coaxial with a rotation axis 108k of the ring gear 84k in a mounted state of the spindle 12k.
  • the code-turning unit 20k further has a second coding element 24k, which is formed integrally with the process-control unit 18k.
  • the second coding element 24k is designed as an edge 136k delimiting a recess of the process control unit 18k.
  • the recess of theticianêtrudsgnac 18k has, in a mounted state of the flow assurance unit 18k viewed in the plane perpendicular to the rotation axis 132k of the spindle 12k, a corresponding to the circular segment 134k shape.
  • limiting edge 136k is located on an outer periphery 168k of the circle segment 134k.
  • the circular segment 134k and the edge 136k which delimits the recess of the discharge-securing unit 18k form a positive connection in an assembled state.
  • the outer circumference 168k of the circle segment 134k extends along the circumferential direction 106k, which extends in a plane perpendicular to the rotational axis 132k of the spindle.
  • FIG. 20 shows an exploded view of together with an output unit 62k of the angle grinder 44k designed as a mounting module 40k brake unit 62k.
  • the mounting module 40k comprises four fastening elements designed as screws (not shown here). The screws are designed to releasably secure the mounting module 40k to a gear housing 60k of the angle grinder 44k to connect. An operator may disassemble the mounting module 40k from the transmission housing 60k as needed.
  • the angle grinder 44k and the mounting module 40k thus form a machine tool system.
  • the machine tool system comprises a further mounting module (not shown here).
  • the further assembly module comprises a trained as an angle gear and decoupled from a brake unit output unit.
  • the further mounting module can be mounted on the transmission housing 60k by the operator as an alternative to the mounting module 40k.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Wood Science & Technology (AREA)
  • Forests & Forestry (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Braking Arrangements (AREA)
EP11760476.9A 2010-10-29 2011-09-21 Tragbare werkzeugmaschine Not-in-force EP2632632B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010043182A DE102010043182A1 (de) 2010-10-29 2010-10-29 Tragbare Werkzeugmaschine
PCT/EP2011/066403 WO2012055643A1 (de) 2010-10-29 2011-09-21 Tragbare werkzeugmaschine

Publications (2)

Publication Number Publication Date
EP2632632A1 EP2632632A1 (de) 2013-09-04
EP2632632B1 true EP2632632B1 (de) 2014-08-20

Family

ID=44674795

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11760476.9A Not-in-force EP2632632B1 (de) 2010-10-29 2011-09-21 Tragbare werkzeugmaschine

Country Status (6)

Country Link
US (1) US9079290B2 (zh)
EP (1) EP2632632B1 (zh)
CN (1) CN103189161B (zh)
DE (1) DE102010043182A1 (zh)
RU (1) RU2590427C2 (zh)
WO (1) WO2012055643A1 (zh)

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DE102012211087A1 (de) 2012-06-28 2014-01-02 Robert Bosch Gmbh Werkzeugmaschinentrennvorrichtung
US9314896B2 (en) * 2012-07-03 2016-04-19 Atlas Copco Industrial Technique Ab Power tool
DE102012217803A1 (de) * 2012-09-28 2014-04-03 Hilti Aktiengesellschaft Werkzeuggerät mit einer Spanneinrichtung zum Festspannen eines scheibenförmigen Bearbeitungswerkzeuges
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Also Published As

Publication number Publication date
US9079290B2 (en) 2015-07-14
US20130288581A1 (en) 2013-10-31
EP2632632A1 (de) 2013-09-04
CN103189161A (zh) 2013-07-03
DE102010043182A1 (de) 2012-05-03
WO2012055643A1 (de) 2012-05-03
CN103189161B (zh) 2016-07-06
RU2590427C2 (ru) 2016-07-10
RU2013124406A (ru) 2014-12-10

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