EP1578564B1 - Drill hammer - Google Patents

Drill hammer Download PDF

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Publication number
EP1578564B1
EP1578564B1 EP03814444A EP03814444A EP1578564B1 EP 1578564 B1 EP1578564 B1 EP 1578564B1 EP 03814444 A EP03814444 A EP 03814444A EP 03814444 A EP03814444 A EP 03814444A EP 1578564 B1 EP1578564 B1 EP 1578564B1
Authority
EP
European Patent Office
Prior art keywords
switch
hammer
ring
characterized
switch button
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.)
Expired - Fee Related
Application number
EP03814444A
Other languages
German (de)
French (fr)
Other versions
EP1578564A1 (en
Inventor
Axel Kuhnle
Willy Braun
Heinz Schnerring
Gerhard Meixner
Karl Frauhammer
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
Priority to DE2002161030 priority Critical patent/DE10261030A1/en
Priority to DE10261030 priority
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PCT/DE2003/002512 priority patent/WO2004060616A1/en
Publication of EP1578564A1 publication Critical patent/EP1578564A1/en
Application granted granted Critical
Publication of EP1578564B1 publication Critical patent/EP1578564B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D16/00Portable 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
    • B25D16/006Mode changers; Mechanisms connected thereto
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2211/00Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003Crossed drill and motor spindles
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2211/00Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06Means for driving the impulse member
    • B25D2211/068Crank-actuated impulse-driving mechanisms
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2216/00Details of 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
    • B25D2216/0007Details of percussion or rotation modes
    • B25D2216/0015Tools having a percussion-only mode
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2216/00Details of 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
    • B25D2216/0007Details of percussion or rotation modes
    • B25D2216/0023Tools having a percussion-and-rotation mode
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2216/00Details of 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
    • B25D2216/0007Details of percussion or rotation modes
    • B25D2216/0038Tools having a rotation-only mode

Abstract

The invention relates to a drill hammer comprising a hammer tube (13) which is rotationally drivable inside a housing (10), a striking train (14) which is arranged in the hammer tube (13) and is provided with a piston (15) which can be driven in a reciprocating movement, in addition to an operating mode commutator (35) for the operating modes 'impact drilling ' and 'chiselling '. The hammer tube (13) is decoupled from the rotary drive when in the 'impact drilling ' operating mode and is secured in a non-rotative manner in the housing (10) when in the 'chiselling' operating mode.

Description

    State of the art
  • The invention is based on a hammer drill according to the preamble of claim 1. An example of such a hammer drill is in the document US Pat. No. 6,176,321 B1 disclosed.
  • It is common today to equip rotary hammers certain performance so that with them both in the mode of "hammer or hammer drilling" in which the percussion hammer in the axial direction on the tool and at the same time the tool is rotated via the tool holder in rotation, as well can be used in the "chiseling" mode, in which only the impact mechanism is activated and the rotary drive for the tool holder is turned off. Since a single electric motor drives both a gear transmission rotatably connected to the tool holder hammer tube, as well as a crank mechanism drives the percussion whose piston performs a reciprocating stroke in the hammer tube and acts on a racket, which in turn via a striker the blows transmits to the tool end, a mode switch is provided, which separates the hammer tube from the gear train in the "chiseling" mode and fixed against rotation in the housing. Thereby the separation between the hammer ear becomes enclosing, rotatably mounted output gear of the gear transmission and the hammer ear made.
  • Advantages of the invention
  • The hammer drill according to the invention with the features of claim 1, has the advantage that the switching mechanism of the mode selector switch is very flat and the axial extent of the mode selector switch can be kept small in particular by a narrow running switching ring. Due to the flat design of the manually operable switch button receiving housing cover made low and the corner of the hammer drill, which is the distance between the hammer middle and upper edge of the housing to be kept small. For a non-rotatable connection between the rotatable on the hammer tube and axially displaceable fixed switching ring and the output gear of the transmission, a single locking cam is sufficient. Preferably, a plurality of distributed over the circumference of the switching ring locking cam are provided which are axially inserted into a corresponding plurality of Axialausnehmungen in the driven gear. Due to the large number of locking cams and axial recesses, the metal-made switching ring can transmit a higher torque and, if necessary, can also be made of plastic. In addition, a non-aligned alignment of locking cam and Axialausnehmungen a much smaller rotary travel of the hammer tube for engaging the switching ring in the drive wheel is required. If the guide cams provided for the rotationally fixed connection are arranged equidistantly on the switching ring and guide grooves in the hammer tube, then the switching ring can be pushed onto the hammer tube in any relative position, which facilitates assembly. The rear derailleur can be made very compact and stable despite Baukleinheit, so that it ensures a long service life.
  • The measures listed in the further claims advantageous refinements and improvements of the claim 1 rotary hammer are possible.
  • According to an advantageous embodiment of the invention, the switching ring is located on the side facing away from the switching knob side of the driven gear and is fixedly connected under the drive wheel with a pushed onto the other side of the driven gear on the hammer tube coupling ring, which is coupled to the switch knob so that a Switch button switching causes an axial displacement of the switching ring. By this structural design, the derailleur is placed on the hammer tube under the output gear of the transmission, so that the corner of the hammer drill is determined solely by the outer diameter of the usually designed as a crown gear driven gear and thereby minimized.
  • The connection to the preferably made of plastic coupling ring is realized according to an advantageous embodiment of the invention via two cantilevers, which protrude in one piece with the coupling ring axially from this and record the switching ring arranged near its ends recesses. By compressing the two elastically outwardly biased cantilevers of the switching ring can be easily mounted. The circumferential play of the cantilevers is kept larger than that of the switching ring on the hammer tube, so sat the cantilevers no torque must be transmitted.
  • According to an advantageous embodiment of the invention, the coupling ring is coupled via a shift fork, which is guided with a nose in an annular groove in the coupling ring on the switch button, wherein the coupling is made via a held on the shift fork synchronization spring and arranged on the switching knob eccentric pin, where the legs of the shift fork abut at diametrical locations non-positively. The large synchronization spring allows a smooth and safe switching of the Operating modes switch. The shift fork and the coupling ring can be inexpensively made of plastic. The size of the switch button facilitates operation and also allows handling with work gloves.
  • According to an advantageous embodiment of the invention, the switching knob is assigned a further setting position for the works council "drilling" in which the hammer mechanism is disconnected from its drive with a rotating hammer tube. This decoupling is not caused by the axial displacement of the switching ring on the hammer tube, but by a perpendicular thereto oriented displacement of a switching mechanism part that separates a arranged in the drive chain of the percussion clutch. For this purpose, a switching ramp extending over a rotation angle is formed on the switching knob, preferably on its underside, which rises in the direction of the axis of rotation of the switching knob. The switching mechanism part is advantageously designed as an axially displaceable separating slide, which bears non-positively on the one hand on the switching ramp and on the other hand on a displaceable coupling part of the clutch, by the axial displacement against the force of a clutch spring, the clutch can be solved. The low spring force of the clutch spring and provided on the isolation slide for non-positive application to the switching ramp spring allows a smooth, yet safe switching the mode selector switch.
  • drawing
  • The invention is explained in more detail in the following description with reference to an embodiment shown in the drawing. Show it:
  • Fig. 1
    a section of a longitudinal section of a hammer drill with a mode switch,
    Fig. 2
    1 is a perspective view of a switching element of the mode selector switch in FIG. 1,
    Fig. 3
    2 partially in perspective view of a hammer tube of the hammer drill in FIG. 1 switching element according to FIG.
    Fig. 4
    a top view of a switch button of the mode selector switch in Fig. 1,
    Fig. 5 to 8
    a top view of a switch button bottom and a coupled shift fork of the mode selector in Figure 1 in four different setting positions of the switch knob,
    Fig. 9
    a development of the switch button base with switching ramp for actuating a vertical isolating slide of the operating mode switch in Fig. 1st
    Description of the embodiment
  • The rotary hammer shown in FIG. 1 in fragmentary form with its rear region in longitudinal section has a housing 10 with a housing opening 11, which is closed by a housing cover 12. At its left end, not shown in FIG. 1, a tool holder projects from the housing 10 for the limited axial displacement of a tool. The tool holder is rotatably connected to a rotatably mounted in the housing 10 hammer tube 13. In the hammer tube 13, an air cushion impact mechanism 14 is arranged with a piston 15 axially displaceable in the hammer tube 13, which is offset by means of a lying in a drive chain between an electric motor 27 and the piston 15 crank mechanism 16 in a reciprocating stroke movement can be. To the air cushion impactor 14 also includes a driven by the piston 15 racket, which acts via an anvil on the end of the tool holder received in the tool. In that regard, the hammer drill described here agrees with that in the DE 38 26 213 A1 match described hammer drill, the local arrangement and training of tool holder, hammer tube 13 and air cushion impact mechanism 14 with piston 15 also applies to the hammer drill described here.
  • The crank mechanism 16 comprises a crank wheel 18 with a molded bearing socket 181 and a crank pin 19 arranged eccentrically to the rotation axis, on which a push rod 20 rotatably seated, which in turn is pivotally connected to the piston 15 of the air cushion impact mechanism 14. The crank wheel 18 is rotatably mounted with its bearing socket 181 on a housing-fixed axis 17. On the bearing sleeve 181 is rotatably and axially displaceably arranged a gear 21 with external teeth 22. Between the crank wheel 18 and the gear 21, a trained as a helical compression spring clutch spring 23 is supported, which presses the gear 21 frontally against a later described in detail separating slide 24. In this displacement position of the toothed wheel 21 shown in FIG. 1, a rotational connection between the crank wheel 18 and the toothed wheel 21 is produced via toothing 25 between toothed wheel 21 and bearing stub 181 of the crank wheel 18, which are lifted upward by displacement of the toothed wheel 21 in FIG can. In the drive chain so that a clutch is arranged, whose one coupling part of the crank wheel 18 with bearing stub 181 and the other, which can be actuated by the separating lever 24 coupling part of the gear 21 is formed. The clutch is held closed by the clutch spring 23. The gearwheel 21 meshes with its external teeth 22 in a drive pinion 28 formed on an output shaft 26 of the electric motor 27. It should be noted that in FIG. 1 the crank drive 16 is shown in a position in which the piston 15 has its front, in FIG left dead center position occupies. For the sake of clarity in the Drawn representation is the piston 15, however, shifted more to the left than it corresponds to the actual conditions.
  • The rotatably mounted in the housing 10, the hammer tube 13 is rotated by the electric motor 27 via a gear train 30 in rotation, so that the limited axially displaceable and non-rotatably received in the tool holder tool also rotates. The gear transmission 30 includes a seated on the hammer tube 13 ring gear 31 which is axially displaceable and rotatably supported on the hammer tube 13, a meshing with the ring gear 31 meshing bevel gear 32 and a bevel gear 32 rotatably connected gear 33 with external teeth 34th bevel gear 32nd and gear 33 are rotatably held in the housing 10, and the external teeth 34 meshes with the drive pinion 28 on the output shaft 26 of the electric motor 27th
  • The hammer drill thus described can be used in three modes. In the "percussion drilling" mode, both the hammer tube 13 is set in rotation by the switched-on electric motor 27, and the air cushion striking mechanism 14 is activated, for which purpose the coupling in the drive chain of the air cushion percussion mechanism 14 (as shown in FIG. 1) is closed and the ring gear 31 rotatably connected to the hammer tube 13 is connected. In the "chiseling" mode, only the air cushion impact mechanism 14 is activated, for which purpose the clutch in the drive chain of the air cushion impact mechanism 14 is closed and the ring gear 31 is decoupled from the hammer tube 13. In the "drilling" mode, the air cushion impact mechanism 14 is stopped and the hammer tube 13 is rotated, for which purpose the clutch in the drive chain of the air cushion impact mechanism 14 is opened and the ring gear 31 is non-rotatably connected to the hammer tube 13.
  • To set these three different operating modes of the hammer drill is a mode switch 35, which includes a single, manually operated switch button 36 and a stable and compact designed switching mechanism 37. The switch button 36 is protected and user friendly in the housing cover 12th
  • It has a switch button lower part 38 and a switch button cap 39, which engages over a housing 12 formed on the collar 12. The switch button lower part 38 is inserted in a collar 21 enclosed by the stepped bore and fixed to the underside of the switch button cap 39. The switch button base 38 has an eccentric pin 40 projecting at right angles from the underside of the switch button base 38, and a shift ramp 41 disposed on the underside of the shift button base 38 extending circumferentially of the shift button base 38 and thereby in the direction of the axis of rotation of the switch knob 36, in Fig. 1 so down, increases.
  • To the switching mechanism 37 also includes the aforementioned slide 24, which is guided vertically displaceably in the housing 10 and with a bent slider end 241 on the underside of the switch button base 38 and rests on the switching ramp 41 and with its other bent slider end 242 the displaceable coupling part of the clutch in the drive chain of the air cushion impact mechanism 14 forming gear 21 overlaps frontally. The upper slide end 241 is pressed by a in Fig. 1 only schematically indicated spring 42 to the underside of the switch button base 38 and the switching ramp 41, wherein the spring force of the spring 42 is sized larger than the spring force of the clutch spring 23, so that in that range of rotation of the switch button lower part 38, in which the upper slide end 241 leaves the switching ramp 41, via the spring 42 and the lower end of the lever 242, the gear 21 is moved under tensioning the clutch spring 23 in Fig. 1 upwards so far that the teeth 25 between crank wheel 18 and gear 21 is repealed, the clutch in the drive chain of the air cushion impact mechanism 14 thus opened and the striking mechanism 14 is turned off. As illustrated in the development of the switching ramp 41 shown in FIG. 9, the switching ramp extends over approximately 270 ° circumferential angle of the switching knob base 38, so that only in a range of rotation of about 90 ° of the switching knob 36 of the slide valve 24 for displacement is released by the spring 42.
  • To the rear derailleur 37 further includes a pushed onto the hammer tube 13 switching member 43, which is shown in perspective in FIGS. 2 and 3, and a switching member 43 to the switching knob 36 connecting shift fork 44. The switching element 43 is composed of a coupling ring 45 made of plastic , of which two with the coupling ring 45 integral, diametrically arranged cantilevers 46 protrude axially. The cantilevers 46 are each provided with a recess 47 at their ring-distal, free end and are biased in the radial direction of the coupling ring 45 to the outside. By compressing the two cantilevers 46 can be in the recesses 47, a switching ring 48 used, which is preferably made of metal. The switching ring 48 carries on its the hammer tube 13 facing the inside two diametrically arranged, radially projecting guide cam 49, the corresponding guide grooves 50 which are incorporated on the outside of the hammer tube 13, einliegen. In the hammer tube 13, two further guide grooves 50 are incorporated, each receiving one of the two cantilevers 46. Preferably, the dimensions of the cantilever arms 46 and the guide cam 49 are made equal, so that the total of four guide grooves 50 can be made the same. On its turned away from the hammer tube 13 outside of the switching ring 45 carries a plurality of equidistantly arranged, radially projecting locking cam 51 which are formed so that they can be axially inserted into corresponding Axialausnehmungen 52 on the hammer tube 13 facing bottom of the ring gear 31. The insertion openings of the Axialausnehmungen 52 in the ring gear 31 opposite a housing-fixed locking member 53 is arranged, the locking teeth are formed so that the locking cam 51 can be inserted axially into the locking member 53 and einliegen positively in the direction of rotation. The locking member 53 is disposed in such axial distance from the Axialausnehmungen 52 in the ring gear 31 that after pushing out the switching ring 48 from the ring gear 31 of the switching ring 48 is still able to take a position in which its locking cam 51 does not engage in the locking member 53. In this so-called neutral or zero position of the switching ring 48, the hammer tube 13 is neither on the ring gear 31 still fixed to the housing Locking part 53 coupled, so that the hammer tube 13 can rotate freely. The coupling ring 45 has a recess or an annular groove 54 into which a radially oriented nose 45 of the shift fork 44 engages.
  • The in Fig. 1 in section and in Figs. 5 - 8 in plan view to see flat shift fork 44, which is preferably made of plastic, extends with its nose-bearing, free end on the hammer tube 13 to the annular groove 54 in the coupling ring 45, is bent at the end of the hammer tube 13 and extends below the switch button base 38. The coupling of the shift fork 44 to the switch button 36 via a synchronization spring 56 and the eccentric pin 40 on the switch button base 38. The synchronization spring 56 is a helical spring with right angles bent to the spring axis, long legs 561, 562 is formed, which is pushed onto a right angle of the shift fork 44 upwardly projecting bolt 57 and with its two long legs 561 and 562 non-positively applied to diametrical positions of the eccentric pin 40, in the direction of the shift fork 44th approximately aligned with each other (Fig. 5 - 8). The eccentric pin 40 is arranged on the switch button lower part 38 at an angle α relative to the longitudinal axis of the shift fork 44 so that when turning the switch knob 36 by 90 ° four pivot positions of the eccentric pin 40 result, seen in the direction of shift fork 44 each a distance of a / 2 are offset from each other, as shown in Fig. 5. The total displacement of the shift fork 44 is a, after which the shift fork 44 abuts against a housing-fixed stop 59. In the illustration of FIGS. 5-8, the upper slide end 241 of the separating slide 24 can still be seen, which engages over the underside of the switching button lower part 38 and rests on the switching ramp 41 over a circumferential angle of approximately 270 °.
  • In Fig. 4, the switch button cap 39 is shown in plan view. It has a grip web 58 on which a marking tip 581 is formed. The marker tip 581 indicates the setting position of the switch button 36 and in order to set the mode of operation "chiseling" M, "impact drilling" S and "drilling" B, which is set by operating mode selector 35. In addition, a "neutral or zero position" 0 is provided, in which only the air cushion impact mechanism 14, but not the rotary drive for the Hammer tube 13 is effective and the hammer tube 13 is free and arbitrary to rotate in the housing 10.
  • The operation of mode switch 35 is as follows:
  • Is - as shown in Fig. 4 - the switching knob 36 is set so that the marker tip 581 points to the position M, it is - as shown in Fig. 5 - the shift fork 44 furthest in Fig. 1 to the left shifted by the maximum displacement a. Accordingly, the switching member 43 is displaced by the shift fork 44 to the maximum left, whereby the switching ring 48 has penetrated with its locking cam 51 in the housing-fixed locking part 53. By obtained via the guide cam 49, cantilevers 46 and grooves 50 rotatable connection of the switching ring 48 to the hammer tube 13, the hammer tube 13 rotatably fixed to the housing 10, and there is no connection between the hammer tube 13 and the ring gear 31. When the electric motor 27 is driven both via the gear transmission 30, the free-rotating ring gear 31 and the air cushion impact mechanism 14, since the slide 24 rests with its upper slider end 241 on the switching ramp 41 and - as shown in Fig. 1 - is shifted downwards, so that the clutch spring 23 keeps the clutch between the crank 18 and gear 21 closed. Since only the Lüftpolster impact mechanism 14 is activated, the tool is driven exclusively by the air cushion impact mechanism 14 in an axial striking motion.
  • If the switching knob 36 is rotated from the position M to the position 0 by 90 ° in Fig. 4 counterclockwise, it is - as shown in Fig. 6 - via the eccentric pin 40 and the synchronization spring 56, the shift fork 44 to the displacement a / 2 in Fig. 1 shifted to the right. About the coupling ring 45 the switching member 43 is shifted in Fig. 1 to the right by the same displacement, whereby the locking cam 51 on the switching ring 48 emerge from the locking member 53 and the switching ring 48 - as shown in Fig. 1 - a middle position between the locking member 53 and ring gear 21st occupies. The hammer tube 13 is released for free rotation, but is not offset by the electric motor 27 in rotation. The air cushion impact mechanism 14 remains activated because the separating slide 24 is held in this rotational position of the switch button 36 by the switching ramp 41 in the position shown in Fig. 1.
  • If the switching knob 36 is rotated into the switch button position SB, the shift fork 44 is again shifted to the right by the displacement a / 2 in Fig. 1 and abuts the stop 50 fixed to the housing at the half of the pivoting path of the eccentric pin. The further displacing eccentric pin 40 deflects the spring leg 561 of the synchronization spring 56 (FIG. 7). The shifter fork 44 displacing by a / 2 displaces the shift ring 48 in FIG. 1 to the right so that the locking cams 51 insert positively into the axial recesses 52 in the ring gear 31 and thus connect the hammer tube 13 to the ring gear 31 in a rotationally fixed manner. The electric motor 27 now puts the hammer tube 13 and thus the tool holder and the rotatably held in the tool holder tool in rotation. The air cushion impact mechanism 14 remains activated since the upper slide end 241 of the isolating slide 24 has not yet left the switching ramp 41 (see position SB in FIG.
  • If now the switching knob 36 is further rotated by 90 ° in the setting position B, so the eccentric pin 40 moves back to the pivoting a / 2 back. Since, however, previously the eccentric pin 40 in the setting position SB at a displacement of the shift fork 44 by a / 2 has moved under deflection of the spring leg 561 to the pivoting a (Fig. 7) is not displaced by this return displacement of the eccentric pin 40, a shift of the shift fork 44 causes (Fig. 8). The switching ring 48 therefore retains its engaged position in Tellerrad 31 at. As a result of the rotation of the switch button lower part 38 to this further 90 °, the switching ramp 41 has pushed out of the region of the upper end of the lever 241 of the isolating slide 24, so that the slide valve 24 by the spring 42 in Fig. 1 upwards to rest on the scarf ramp Area of the switch button lower part 38 is displaced while its lower end of the lever 242, the gear 21 is displaced by compressing the clutch spring 23 upwards, so that the external teeth between the gear 21 and bearing sleeve 181 of the crank wheel 18 is disengaged and thus the clutch in the drive chain of the Air cushion impact mechanism 14 is solved. Thus, the air cushion impact mechanism 14 is disconnected from the electric motor 27 and only the hammer tube 13 of the electric motor 27 is set in rotation. With the rotatably held in the tool holder tool now pure drilling can be performed.
  • Of course, it is possible to turn the switching knob 36 from a setting position M in the opposite direction of rotation directly in the setting position B and then from this further successively in the setting position SB and 0. On the operation of the rear derailleur 37 thereby changes nothing.

Claims (15)

  1. Hammer drill comprising a hammer tube (13) which is rotatably mounted in a housing (10) and can be rotationally driven via an output gear (31), sitting on the hammer tube (13), of a gear unit (30), comprising a percussion mechanism (14) which is arranged in the hammer tube (13) and has a piston (15) which can be driven with a reciprocating stroke movement, and comprising an operating-mode changeover switch (35) for the operating modes "percussion drilling" and "chiselling", said operating-mode changeover switch (35) having a manually operable switch button (36) and a switch mechanism (37) which is connected to the switch button (36) and couples the hammer tube (13) to the output gear (31) in the setting position of the switch button (36) "percussion drilling" and secures it in the housing (10) in a non-rotatable manner in the setting position "chiselling", characterized in that the switch mechanism (37) has a switch ring (48) which is fixed on the hammer tube (13) in a rotationally locked and axially displaceable manner and has on its outer side facing away from the hammer tube (13) at least one radially projecting locking lug (51) which is designed for sliding in a positive-locking manner in the circumferential direction into at least one axial recess (52), fixed with respect to the drive gear, on the one hand and into an axial tooth system (53), fixed with respect to the housing, on the other hand.
  2. Hammer drill according to Claim 1, characterized in that, to fix the switch ring (48) on the hammer tube (13) in a rotationally locked and axially displaceable manner, the switch ring (48) has at least one radially projecting guide lug (49), preferably two diametrically arranged guide lugs (49), on its inner side facing the hammer tube (13), and the hammer tube (13) has at least one axial guide groove (50), preferably two diametrically arranged guide grooves, on its outer side facing the switch ring (48), in which guide groove (50) the guide lug (49) rests in position in a positive-locking manner in the circumferential direction.
  3. Hammer drill according to Claim 1 or 2, characterized in that the switch ring (48) lies on the side of the output gear (31) facing away from the switch button (36) and is connected through beneath the output gear (31) to a coupling ring (45) which is pushed into place on the hammer tube (13) on the other side of the output gear (31) and is coupled to the switch button (36) in such a way that turning the switch button effects an axial displacement of the switch ring (48).
  4. Hammer drill according to Claim 3, characterized in that the connection between switch ring (48) and coupling ring (45) is produced by means of at least two cantilevers (46) projecting axially from the coupling ring (45).
  5. Hammer drill according to Claim 3 or 4, characterized in that the cantilevers (46) are integrally formed in one piece on the coupling ring (45), and in that the switch ring (48) is accommodated in recesses (47) which are integrally formed in the outer side, facing away from the hammer tube (13), of the cantilevers (46) close to the end of the cantilevers (46) which is remote from the coupling ring.
  6. Hammer drill according to Claim 4 or 5, characterized in that the cantilevers (46) are accommodated in axial grooves (50) in the hammer tube (13) in an axially displaceable manner and in a positive-locking manner in the circumferential direction of the hammer tube (13).
  7. Hammer drill according to one of Claims 3 to 6, characterized in that an annular groove (54) is incorporated in the outer side of the coupling ring (45), a radially oriented nose (55) of a switch fork (44) coupled to the switch button (36) being guided in said annular groove (54) in a sliding manner.
  8. Hammer drill according to Claim 7, characterized in that the switch button (36) is secured in the housing (10) in such a way as to be rotatable about an axis of rotation, and the switch fork (44) is coupled via a synchronization spring (56) to an eccentric pin (40) projecting from the switch button (36) and arranged at a radial distance from the axis of rotation.
  9. Hammer drill according to Claim 8, characterized in that the synchronization spring (56) is a helical spring having long legs (561, 562) bent at right angles to the spring axis, and in that the leg spring (56) is accommodated on a stud (57) formed on the switch fork (44) and bears frictionally with its two legs (561, 562) against diametrical points of the eccentric pin (40) facing away from one another in the displacement direction of the switch fork (44).
  10. Hammer drill according to one of Claims 1 to 9, characterized in that assigned to the switch button (36) is a setting position in which such a displacement position of the switch ring (48) of the switch mechanism (37) is set that the switch ring (48) is neither in rotationally locked engagement with the output gear (31) nor in rotationally locked engagement with the housing (10).
  11. Hammer drill according to one of Claims 1 to 10, characterized in that the switch button (36) has a setting position for the operating mode "drilling", in which the percussion mechanism (14) is uncoupled, and in that the percussion mechanism (14) is uncoupled by a displacement movement of a switch mechanism part (37) which is initiated by the switch button (36) and is at right angles to the displacement movement of the switch ring (48) on the hammer tube (13).
  12. Hammer drill according to Claim 11, characterized in that a clutch having two clutch parts held in engagement with one another by a clutch spring (23) is arranged in the drive chain for the percussion mechanism (14), of which clutch parts the one clutch part is designed to be displaceable against the force of the clutch spring (23) by the switch mechanism part actuated via the switch button (36).
  13. Hammer drill according to Claim 12, characterized in that a switch ramp (41) is formed on the switch button (36), said switch ramp (41) rising in the direction of rotation of the switch button (36) at right angles to the underside of the switch button (36), and in that the switch mechanism part has a separating slide (24) which is guided in an axially displaceable manner and which bears frictionally against the switch ramp (41) on the one hand and the displaceable clutch part on the other hand.
  14. Hammer drill according to Claim 13, characterized in that the friction grip between separating slide (24) and clutch part on the one hand and separating slide (24) and switch ramp (41) on the other hand is produced by a spring (42) which acts on the separating slide (24) and whose spring force is greater than that of the clutch spring (23) and is opposed to the clutch spring force.
  15. Hammer drill according to one of Claims 12 to 14, characterized in that the drive chain for the percussion mechanism (14) has a crank wheel (18) of a crank drive (16), acting on the piston (15) of the percussion mechanism (14), and a gear (21) which meshes with a drive pinion (28) driven by an electric motor (27), in that the crank wheel (18) and the gear (21) form the clutch parts, which are in engagement with one another via an axial tooth system (25), and in that the clutch spring (23) is designed as a compression spring which is supported axially between crank wheel (18) and gear (21).
EP03814444A 2002-12-24 2003-07-25 Drill hammer Expired - Fee Related EP1578564B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE2002161030 DE10261030A1 (en) 2002-12-24 2002-12-24 Rotary Hammer
DE10261030 2002-12-24
PCT/DE2003/002512 WO2004060616A1 (en) 2002-12-24 2003-07-25 Drill hammer

Publications (2)

Publication Number Publication Date
EP1578564A1 EP1578564A1 (en) 2005-09-28
EP1578564B1 true EP1578564B1 (en) 2007-10-10

Family

ID=32477999

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03814444A Expired - Fee Related EP1578564B1 (en) 2002-12-24 2003-07-25 Drill hammer

Country Status (6)

Country Link
US (1) US7121359B2 (en)
EP (1) EP1578564B1 (en)
JP (1) JP2006512216A (en)
CN (1) CN100519091C (en)
DE (2) DE10261030A1 (en)
WO (1) WO2004060616A1 (en)

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Also Published As

Publication number Publication date
DE50308372D1 (en) 2007-11-22
US20050269116A1 (en) 2005-12-08
DE10261030A1 (en) 2004-07-08
CN1717300A (en) 2006-01-04
US7121359B2 (en) 2006-10-17
CN100519091C (en) 2009-07-29
EP1578564A1 (en) 2005-09-28
JP2006512216A (en) 2006-04-13
WO2004060616A1 (en) 2004-07-22

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