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EP1360041A1 - Marteau-foreur et/ou burineur - Google Patents

Marteau-foreur et/ou burineur

Info

Publication number
EP1360041A1
EP1360041A1 EP02704590A EP02704590A EP1360041A1 EP 1360041 A1 EP1360041 A1 EP 1360041A1 EP 02704590 A EP02704590 A EP 02704590A EP 02704590 A EP02704590 A EP 02704590A EP 1360041 A1 EP1360041 A1 EP 1360041A1
Authority
EP
European Patent Office
Prior art keywords
locking
hand tool
tool according
spring
designed
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.)
Granted
Application number
EP02704590A
Other languages
German (de)
English (en)
Other versions
EP1360041B1 (fr
Inventor
Otto Baumann
Dietmar Saur
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 EP1360041A1 publication Critical patent/EP1360041A1/fr
Application granted granted Critical
Publication of EP1360041B1 publication Critical patent/EP1360041B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/003—Clutches specially adapted therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/061—Swash-plate actuated impulse-driving mechanisms

Definitions

  • the invention relates to a hammer drill and / or chisel hammer according to the preamble of claim 1.
  • Drill and / or chisel hammers with pneumatic striking mechanisms which can be activated or deactivated via a mechanical friction clutch. If the drill and / or chisel hammer is pressed against a machining surface with a tool, a tool holder holding the tool is guided in the direction of an operator into a housing of the drill and / or chisel hammer. Conical friction surfaces of the friction clutch come into contact and the pneumatic hammer mechanism is driven by a frictional connection.
  • the striking mechanism During operation, the striking mechanism generates a compressed air cushion with a piston guided in a cylinder and movable in the axial direction, which accelerates a club in the axial direction onto a firing pin.
  • the racket strikes the firing pin, which receives an impulse. The impulse is forwarded to the tool in the tool holder.
  • the invention is based on a hand-held power tool with a striking mechanism and a coupling device which can be engaged and disengaged to produce and interrupt a drive connection of the striking mechanism.
  • the coupling device has a synchronizing device with a latching mechanism that transmits a drive torque and that has at least two corresponding latching elements during a synchronizing operation, wherein at least one of the latching elements can be moved out of its latching position against a spring force of a spring element in the event of a latching torque ,
  • the latching mechanism an advantageous synchronizing device can be created by means of a form-fit which can be disengaged and which can transmit a relatively large torque even with a low coupling force. Due to the low coupling force required, a particularly comfortable hand-held power tool can be achieved, which can be guided into its working position with only a small operating force.
  • a synchronization that is largely independent of the viscosity of a lubricant used in the coupling device can advantageously be achieved by the disengageable positive engagement over a short distance. Damped engagement can also be achieved with the synchronizing device, and a coupling device with little wear can be achieved.
  • the locking element which can be moved against a spring force is advantageously formed by a rolling element and the locking element corresponding to the locking element designed as a rolling element is formed by a recess.
  • the rolling element can be formed, for example, by a ball, a roller, a barrel, etc.
  • the locking elements can roll off when they are snapped on, and wear can be reduced.
  • the recess can be particularly adapted to the rolling of the rolling element, and a uniform and low-wear synchronization can be achieved.
  • rolling elements designed as rollers large transmission surfaces can be achieved and, compared to balls, larger torques can be transmitted, whereas with balls a rolling movement in more than two directions can advantageously be achieved and jamming can be avoided.
  • other latching elements that appear sensible to a person skilled in the art can also be used, such as Sliding blocks etc.
  • the locking element designed as a rolling element can be moved out of its locking position against an annular spring.
  • a simple and space-saving construction can be achieved with only one spring element.
  • the ring spring can be be designed in different ways, for example as a single spring with an anti-rotation device, as a single spring without an anti-rotation device and with an appropriately designed slot that prevents the locking elements designed as rolling elements from escaping despite the tensioned spring, or as a spring assembly, which advantageously means a large spring force with a small one Spring tension can be achieved.
  • the conical surface and / or the latching element can be designed to be axially movable with the annular spring. With the conical surface, a translation of the axial force can be achieved, namely by converting a larger axial movement with a smaller axial force into a smaller radial movement with a larger radial force.
  • the locking element designed as a rolling element can be guided with a continuous movement into the locking element designed as a recess, and uniform acceleration and an advantageous engagement can be achieved.
  • the recess formed as a latching element has a dome-shaped ⁇ cross-sectional area.
  • the conical surface is advantageously formed on one end of a component that is non-rotatable and axially displaceable on a drivable shaft, and a latching element designed as a recess extends into the conical surface.
  • the synchronization device can be implemented in a space-saving, structurally simple manner and with a few additional components.
  • the locking element can be guided radially outwards along the conical surface.
  • An available space in the radial direction to the outside can be used advantageously and a large, low-tolerance spring can be used. In principle, however, it is also conceivable to arrange the locking elements radially outside of an annular spring and to make them movable radially inward against the annular spring.
  • a component transmitting an impulse of the striking mechanism is connected to the displaceable component via a connection which transmits at least one force in the direction of the impulse, the impulse can be used to reach the idle position and a return spring or an idle spring can be supported in its effect.
  • the return spring can advantageously be made smaller than in a conventional engagement clutch, and a small operating force and a high level of comfort can be achieved.
  • an inner foot circle of at least two locking elements designed as recesses has the same diameter as an inner foot circle of the locking elements designed as rolling elements in an idling position.
  • the rolling elements can be guided into the recesses unhindered without loading the spring and simple coupling and uncoupling can be achieved.
  • the ring spring is unloaded during a working position.
  • the locking element is formed by a ball which is supported on a conical ring which is axially displaceable against a spring on a drivable shaft.
  • the spring can take over the function of a synchronizing spring and an idling spring, and additional components, installation space, weight and costs can be saved.
  • a ratio can be achieved with the conical ring, with which a small axial force can be translated into a large radial force and a large synchronizing force.
  • the locking element can be used to produce a positive connection and additional positive locking elements can be saved.
  • the locking element designed as a ball is supported radially inward on the displaceable conical ring and can be brought into operative connection radially outward with the corresponding locking element designed as a recess.
  • An available installation space in the radial direction to the outside can be used advantageously.
  • the locking elements are supported radially outwards on an axially displaceable cone ring.
  • the locking element is mounted in part of a drive element, in particular a drive bearing of the striking mechanism, existing components can be used and additional components, installation space and costs can be saved. If positive locking elements are molded onto the coupling device, which come into engagement next to the locking mechanism after the synchronization process, the locking mechanism can be relieved during operation and the wear of the locking elements can be reduced.
  • FIG. 1 a partial section through a rotary hammer
  • Fig. 2 a coupling device of the drilling and opinion ßelha mers' of Fig. 1 in a neutral position
  • Fig. 3 shows the coupling device of FIG. 2 during a sync
  • 5 shows a coupling element of the coupling device from FIG. 2 obliquely from above
  • FIG. 6 shows a partial section through a hammer drill and chisel hammer with an alternative coupling device
  • FIG. 7 shows the coupling device from FIG. 6 in an idling division
  • FIG. 8 shows the coupling device from FIG. 6 during synchronization
  • FIG. 9 shows the coupling device from FIG. 6 in a
  • FIG. 10 shows a coupling element of the coupling device from FIG. 6 in the axial direction
  • FIG. 11 shows an alternative to FIG. 6 coupling device with additional positive locking elements.
  • FIG. 1 shows a partial section through a hammer drill and chisel hammer with an electric motor, not shown, which is arranged in a housing 10 and has a drive shaft 52.
  • a pinion is formed on the drive shaft 52 and meshes with a fixed gear 118 arranged on a shaft 30 running parallel to the drive shaft 52.
  • the shaft 30 has a molded gear 56 on a side facing a tool holder 54, via which the shaft 30 meshes with a gear 58 arranged on a hammer tube 60.
  • the gearwheel 58 is rotatably mounted on the hammer tube 60 and is connected via a rolling element of a snap-in clutch 62 to a locking disk 64 arranged in a rotationally fixed manner on the hammer tube 60 prevented.
  • the hammer tube 60 is in turn non-rotatably connected to the tool holder 54.
  • An impact mechanism 14 with a drive bearing 74 is rotatably mounted on the shaft 30. There is also a shaft 30
  • Coupling device 12 mounted, which can be engaged and disengaged to establish and interrupt a drive connection 16 of the striking mechanism 14.
  • the coupling device 12 has, on the side of the gear 56 facing away from the tool holder 54, a first which is axially displaceable and non-rotatably mounted on the shaft 30.
  • Coupling element 32 The first coupling element 32 has at its end facing the tool holder 54 an internal toothing with which the first coupling element 32 is guided on the gear 56 in a rotationally fixed and axially displaceable manner.
  • part of a synchronizing device 18 is formed on an outer circumference of the first coupling element 32, specifically a conical surface 28, the diameter of which increases in the direction of the tool holder 54 (FIGS.
  • a conical surface instead of a conical surface, other surfaces which appear useful to the person skilled in the art can also be molded on. be, for example convex and / or concave surfaces, the diameter of which preferably increase in the direction of the tool holder.
  • the synchronization behavior can advantageously be influenced by the configuration of the surface.
  • locking elements 24 of a locking mechanism 20 of the synchronizing device 18 (FIGS. 1 and 5) extending in the direction of the tool holder 54 and designed as recesses begin.
  • the locking elements 24 designed as recesses have a dome-shaped transverse sectional area. In order to achieve a smooth engagement, the transitions in the circumferential direction into the recesses in the area of the conical surface 28 are rounded (FIG. 5).
  • the first coupling element 32 projects with its end facing away from the tool holder 54 into a second, corresponding coupling element 44, which also forms part of the drive bearing 74 of the striking mechanism 14.
  • latching elements 22 of the latching mechanism 20 designed as balls are mounted in a plurality of radially extending bores distributed over the circumference.
  • the locking elements 22, which are designed as balls project radially inward over part of an inner circumference of the second coupling element 44 and are each supported radially inward on a collar formed in the bores.
  • the locking elements 22 designed as balls form an inner circle 36 which has the same diameter as an inner circle 34 of the locking elements 24 designed as recesses (FIGS. 1 to 4). Furthermore, the number of balls coincides with the number of recesses, so that the first and second coupling elements 32, 44 can be joined without force when the hammer drill and chisel hammer are at a standstill.
  • the locking elements 22 designed as balls are surrounded radially outwards by an annular spring 26.
  • the synchronization behavior can be set via the design of the latching elements 24 designed as recesses and via the ring spring 26. 2 to 4, a coupling process of the coupling device 12 is shown. If the hammer and chisel hammer is used with a tool, not shown pressed against a machining surface, a reaction force is transmitted from the tool holder 54 via a locking ring 38, via the hammer tube 60, via a locking ring 40 to the locking disk 64 and from the locking disk 64 via a positive connection 76 to the first coupling element 32, and in particular, the components 32, 54, 60, 64 are pushed further into the housing 10.
  • An annular groove 70 is formed on an outer circumference of the locking disk 64, into which a collar 72 formed on the first coupling element 32 engages.
  • the annular groove 70 and the collar 72 form the positive connection 76 in the axial direction between the locking disk 64 and the first coupling element 32 (FIG. 1).
  • the first coupling element 32 is inserted into the second coupling element 44 against an idling spring 68 via the locking disk 64 and via the connection 76.
  • the idle spring 68 designed as a helical compression spring is arranged on the shaft 30 and is supported on the shaft 30 by its end facing away from the tool holder 54 via a support ring 78 and a securing ring 42 fastened in an annular groove in the shaft 30. With its end facing the tool holder 54, the idle spring 68 projects axially into an annular recess between the first coupling element 32 and the shaft 30 and acts on a stop molded onto the first coupling element 32 with a compressive force in the direction of the tool holder 54.
  • the locking elements 22 designed as balls are displaced radially outward against the annular spring 26 along the conical surface 28 at the beginning of the synchronization process (FIGS. 2 and 3).
  • the locking elements 22 designed as balls come along the locking elements 24 designed as recesses in operative connection.
  • a disengageable form fit is achieved by the latching elements 22, which are designed as balls, being able to disengage radially outward from their latching positions, namely from the latching elements 24, which are designed as recesses, against the annular spring 26 during a synchronizing process (FIG. 3).
  • the first coupling element 32 accelerates the second coupling element 44 via the form fit which can be disengaged, a maximum torque of the locking mechanism 20 being achieved after the conical surface 28.
  • claw-like form-locking elements 48 are formed on the first coupling element 32, axially extending in the direction of the second coupling element 44, with correspondingly designed, molded on the second coupling element 44, axially in the direction claw-like form-locking elements 50 extending to the first coupling element 32.
  • the locking mechanism 20 is bridged and the striking mechanism 14 is driven via the form-locking elements 48, 50 (FIG. 4). If the drive torque exceeds a permissible value during operation, the toothed wheel 58 is deflected in the axial direction toward the tool holder 54 against a latching spring 66 and the drive connection of the tool to the electric motor is interrupted.
  • 1 and 4 show the hammer drill and chisel hammer or the coupling device 12 in a percussion drilling position.
  • the idle spring 68, the first coupling element 32 via the connection 76, the locking disc 64, on the. Circlip 40, the hammer tube 60 and, via the locking ring 38, the tool holder 54 are axially displaced into their starting position in the direction of the machining surface.
  • the idle spring 68 is supported in its mode of operation by an idle stroke of a racket 80 guided in the hammer tube 60, namely by an impulse from the racket 80 via a striker 46, via the tool holder 54, the hammer tube 60, the locking disk 64 and via the connection 76 is transmitted to the first coupling element 32.
  • FIGS. 6 to 10 show a further exemplary embodiment with an alternative coupling device 100.
  • Components that remain essentially the same are fundamentally numbered with the same reference numerals.
  • a striking mechanism 14 with a drive bearing 74 is rotatably mounted on a shaft 30. Furthermore, a coupling device 100 is mounted on the shaft 30, which is used for the production and
  • the coupling device 100 On the side of a gear 56 facing away from a tool holder 54, the coupling device 100 has a first coupling element 104, which is axially displaceable and non-rotatably mounted on the shaft 30.
  • the first coupling element 104 has internal teeth on its end facing the tool holder 54, with which the first coupling element 104 is fixed in terms of rotation and is axially displaceably guided on the gear 56 (Fig. 6).
  • a sleeve 106 is molded onto the first coupling element 104 on its side facing away from the tool holder 54 and engages over a second, corresponding coupling element 122.
  • the second coupling element 122 forms part of the drive bearing 74 of the striking mechanism 14.
  • the sleeve 106 On its inner circumference, the sleeve 106 has latching elements 108 of a latching mechanism 110 of a synchronizing device 112 which are formed as recesses.
  • the locking elements 108 run obliquely radially outwards to an end facing away from the tool holder 54 or have a decreasing depth, and in a last area before the end facing away from the tool holder 54, the sleeve 106 has an inner diameter corresponding to a root circle 126 of the locking elements 108 (FIG 10).
  • the locking elements 108 have a spherical cross-sectional area.
  • a conical ring 114 is mounted on the shaft 30 so that it cannot rotate and can be moved in the axial direction.
  • the conical ring 114 can be displaced against a spring 116 on a side facing the tool holder 54.
  • the conical ring 114 is supported on the shaft 30 via a securing ring 120 fastened in an annular groove of the shaft 30.
  • the spring 116 is formed by a helical compression spring that has an increasing diameter in the direction of the tool holder 54 and is arranged between the first coupling element 104 and the conical ring 114.
  • the spring 116 is supported with its end facing the tool holder 54 in an annular recess on a collar of the first coupling element 104. On her the tool holder 54 facing away from the end, the spring 166 is supported on the cone ring 114 (FIGS. 6 to 10).
  • the synchronization behavior can be set via the choice of the spring 116, a cone angle of the cone ring 114 and via the locking elements 108 designed as recesses, in particular via a transition into the recesses.
  • latching elements 22 of the latching mechanism 110 designed as balls are mounted in a plurality of radially extending bores distributed over the circumference.
  • FIG. 7 shows the coupling device 100 in the disengaged state. If the rotary and chisel hammer is pressed against a machining surface with a tool (not shown in more detail), a reaction force is exerted by the tool holder 54 via a locking ring 38, via the hammer tube 60 and via a locking ring 40 onto the locking disk 64 and from the locking disk 64 transfer a positive connection 76 to the first coupling element 104, and in particular the components 54, 60, 64 and 104 are pushed further into the housing 10.
  • An annular groove 70 is formed on an outer circumference of the locking disk 64, into which a collar 72 formed on the first coupling element 104 engages.
  • the annular groove 70 and the collar 72 form the positive connection 76 in the axial direction between the locking disk 64 and the first coupling element 104.
  • the first coupling element 104 is pushed against the spring 116 over the second coupling element 122.
  • the spring 116 is pretensioned and transmits the axial movement of the first coupling element 104 to the cone ring 114 with a compressive force.
  • the locking elements 22, which are designed as balls, are pushed radially outward against the sleeve 106 of the first coupling element 104 by the cone ring 114 (FIG. 8). ,
  • the locking elements 22 designed as balls come into operative connection with the locking elements 108 of the first coupling element 104 designed as recesses.
  • a disengageable form fit is achieved in that the locking elements 22 designed as balls can disengage radially inward from their locking positions during the synchronization process, specifically from the locking elements 108 designed as recesses against the cone ring 114 at an overlap torque, and the cone ring 114 against the spring 116 can be moved in the direction of the tool holder 54.
  • the first coupling element 104 accelerates the second coupling element 122 (FIG. 8) via the form fit which can be disengaged.
  • the conical ring 114 is axially fixed in the direction of the tool holder 54 by a stop 124 of the first coupling element 104 (FIGS. 6 and 9).
  • the locking elements 22 designed as balls are supported radially inward on the axially fixed cone ring 114 and are securely chambered in the corresponding locking elements 108 designed as recesses.
  • the stop 124 prevents the latching elements 22 from disengaging. the, and the locking elements 22, 108 form a positive connection between the first and the second coupling element 104, 122. If the drive torque exceeds a permissible value during operation, the gear 58 is deflected against a locking spring 66 in the axial direction to the tool holder 54 and the Drive connection interrupted.
  • FIGS. 6 and 9 show the hammer drill and chisel hammer or the coupling device 12 in a percussion drilling position. If the hammer drill and chisel hammer is lifted from the machining surface, the first coupling element 104 is moved by the spring 116, the locking disk 64 via the connection 76, the hammer tube 60 via the locking ring 40 and the tool holder 54 via the locking ring 38 into its starting position axially in the direction shifted to the editing surface.
  • the spring 116 is supported in its mode of operation by an idling stroke of a striker 80 guided in the hammer tube 60, namely by an impulse from the striker 80 via a striker 46, via the tool holder 54, the hammer tube 60, the locking disk 64 and via the Connection 76 is transmitted to the first coupling element 104.
  • FIG. 11 shows a variant of the coupling device 100 from FIG. 7.
  • claw-like form-locking elements 128 are formed on the first coupling element 104 and extend axially in the direction of the second coupling element 122 appropriately designed, claw-like form-locking elements 130, which are molded onto the second coupling element 122 and extend axially in the direction of the first coupling element 104.
  • the locking mechanism 110 will bridged, and the striking mechanism 14 is driven via the form-locking elements 128, 130.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Boring (AREA)

Abstract

L'invention concerne une machine-outil à main comportant un mécanisme de percussion (14) et un dispositif d'accouplement (12, 100) qui peut être accouplée ou désaccouplée pour, respectivement, établir ou interrompre une liaison d'entraînement (16, 102) du mécanisme de percussion (14). Selon l'invention, ce dispositif d'accouplement (12, 100) comporte un dispositif de synchronisation (18, 112) pourvu d'un mécanisme d'enclenchement (20, 110) qui transmet un couple d'entraînement et comporte au moins deux éléments d'enclenchement (22, 24, 108) qui correspondent lors d'un processus de synchronisation. Au moins un (22) desdits éléments d'enclenchement peut, en cas de couple de surenclenchement, être déplacé de sa position d'enclenchement à l'encontre de la force élastique d'un ressort (26, 116).
EP02704590A 2001-02-09 2002-01-17 Marteau-foreur et/ou burineur Expired - Lifetime EP1360041B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10106034 2001-02-09
DE10106034A DE10106034B4 (de) 2001-02-09 2001-02-09 Handwerkzeugmaschine
PCT/DE2002/000113 WO2002064321A1 (fr) 2001-02-09 2002-01-17 Marteau-foreur et/ou burineur

Publications (2)

Publication Number Publication Date
EP1360041A1 true EP1360041A1 (fr) 2003-11-12
EP1360041B1 EP1360041B1 (fr) 2008-07-23

Family

ID=7673480

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02704590A Expired - Lifetime EP1360041B1 (fr) 2001-02-09 2002-01-17 Marteau-foreur et/ou burineur

Country Status (6)

Country Link
US (1) US7070008B2 (fr)
EP (1) EP1360041B1 (fr)
JP (1) JP2004517750A (fr)
CN (1) CN1298512C (fr)
DE (2) DE10106034B4 (fr)
WO (1) WO2002064321A1 (fr)

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Also Published As

Publication number Publication date
WO2002064321A1 (fr) 2002-08-22
US7070008B2 (en) 2006-07-04
EP1360041B1 (fr) 2008-07-23
DE10106034A1 (de) 2002-08-29
JP2004517750A (ja) 2004-06-17
DE50212532D1 (de) 2008-09-04
US20040020668A1 (en) 2004-02-05
DE10106034B4 (de) 2009-11-26
CN1298512C (zh) 2007-02-07
CN1457286A (zh) 2003-11-19

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