ROTARY HAMMER

Abstract: In a rotary hammer with an electric motor which is arranged with its longitudinal axis perpendicular to the axis of the hammer spindle (8) and the tool holder (2) there is a single switching element (25) for the activation and deactivation of the hammer mechanism and for the activation and deactivation of the rotary drive for the tool holder. The switching element (25) acts, with an eccentric actuating section (29) which extends parallel to the main axis (27) of the switching element, on a coupling part for the activation and deactivation of the hammer drive and with a cam section on a slider part, with the help of which a coupling sleeve (17) sitting non-rotatable on the hammer spindle can selectively be brought into positive engagement with a driven drive sleeve (16) or brought out of engagement with the latter.

Description: ROTARY HAMMER The invention relates to a rotary hammer with a hammer housing, an electric motor provided in the hammer housing, a tool holder which is provided at the front end of the hammer housing and which can be rotatingly driven by the electric motor about the spindle axis of the hammer spindle, a hammer mechanism provided in the hammer housing for generating impacts acting on the rear end of a hammer bit or chisel bit inserted into the tool holder, and a switching element which is rotatable from the outside about its main axis and which has a cam section for switching between at least three operating modes, of which the first is pure drilling, the second hammer drilling and the third chiselling. Known rotary hammers of this type (German Patent Application P 40 13 512) with switching between more than two operating modes by means of a single switching element are known. In these, there is a parallel arrangement of the axis of the hammer spindle, of the armature shaft of the electric motor and of the intermediate shaft which is driven by this and, in the activated case, drives the hammer mechanism and brings about the rotation of the tool holder. All the coupling and uncoupling processes for the activation and deactivation of the rotary drive and of the hammer mechanism therefore take place in one direction, namely parallel to the axis of the hammer spindle, so that the operating mode in question can be set by successive actuation of different coupling arrangements. In the case of larger rotary hammers in which the drive motor is arranged with its armature shaft at right angles to the axis of the hammer spindle, it is not at present possible to carry out switching between more than two operating modes, i.e. in addition to switching between activated and deactivated rotary drive or to switching between activated and deactivated hammer mechanism, with a single switching element. Rather, separate switching elements are used, one of which moves the coupling arrangement for the rotary drive in a direction parallel to the axis of the hammer spindle, this parallel movement generally being directed coaxially relative to the axis of the hammer spindle, while the other switching element displaces the coupling arrangement for the activation and deactivation of the hammer mechanism parallel or coaxially relative to the armature shaft. The object of the invention is to simplify the structure of a rotary hammer in which the armature shaft of the electric motor is arranged perpendicular to the axis of the rotary hammer spindle by making it possible for switching between at least three operating modes to be effected with a single switching element. To achieve this object, a rotary hammer of the type mentioned at the beginning, in which the armature shaft of the electric motor is arranged perpendicular to the axis of the hammer spindle and the armature shaft can selectively be coupled with a drive shaft for the hammer mechanism, is designed in such a way that the armature shaft drives a drive sleeve which is rotatably arranged on the hammer spindle and which can be coupled with the hammer spindle via a coupling sleeve which sits non-rotatable but axially displaceable on the hammer spindle, that the cam section of the switching element acts on the coupling sleeve via a slider part which can be moved parallel to the axis of the hammer spindle, so that the coupling sleeve can be moved between a position of engagement with the drive sleeve and a release position separated from the drive sleeve, and that an actuating section which is eccentric relative to the main axis and which cooperates with a coupling part which can be moved coaxially relative to the drive shaft, is provided at the switching element in order to move the coupling part between a position coupling the drive shaft with the armature shaft and a position in which the drive connection between the armature shaft and the drive shaft is broken ' . In the case of the rotary hammer according to the invention, the activation and deactivation of the rotary drive thus takes place by means of a slider part which is arranged between the coupling sleeve and the switching element, so that switching is made possible through action on the slider part at a distance from the actual coupling arrangement for the rotary drive, to which end the slider part can be displaced parallel to the axis of the hammer spindle by the cam section provided at the switching element. In this way, the movement of the coupling sleeve is brought about in the manner that is usual per se parallel or coaxially relative to the axis of the hammer spindle. The activation and deactivation of the rotary drive of a rotary hammer through displacement of a coupling sleeve sitting on the hammer spindle is customary in rotary hammers of the type concerned (U.S. Patent No. 4 236 588) . However, the associated switching element is situated in the immediate vicinity of the coupling sleeve and engages with an eccentric pin or the like with an annular groove of the coupling sleeve, so that the latter is axially displaced upon rotation of the switching element. The activation and deactivation of the hammer mechanism of the rotary hammer according to the invention is achieved by the provision, at the switching element, of an actuating section lying eccentrically relative to its main axis, so that, upon rotation of the switching element arranged LO LO to to H H LΠ σ LΠ o ( l o LΠ j 0 ft ) P μ- a LQ 0 Hi rr tr CD Ω O a TJ μ- a LQ en H J CD CD <! CD C tr μ- Ω tr μ- CΓJ a a μ- Hi O ϋ 3 O a tr o rr tr sides and by means of which tipping movements can be avoided. The slider part may be spring-loaded in the direction of the advanced position of the coupling sleeve, in order, in the case of the misalignment of the engagement sections of the coupling sleeve and housing-fixed zone during the switching process, to then bring about an engagement at once when a twisting of the coupling sleeve occurs in relation to the housing-fixed zone. The coupling part serving for activation and deactivation of the hammer mechanism may be spring-loaded in the direction of the coupling with the drive shaft. It may consist of a sleeve which sits non-rotatable but axially displaceable on the drive shaft and which has a radially outwardly directed flange. In order to bring about a displacement of such a sleeve-shaped coupling part, the actuating section which is arranged eccentrically relative to the main axis of the switching element can be brought, by rotation of the switching element, into engagement with the flange which displaces the coupling part. The invention is explained in more detail below with reference to the drawings which show an embodiment. Figure 1 shows, partly broken open and in section, a rotary hammer . Figure 2 shows, partly in section, partly as a view, a portion of the rotary hammer from Figure 1. Figure 3 shows, partly in section and partially as a view, the portion of the rotary hammer from Figures 1 and 2 around the hammer spindle in an operating position for pure drilling. Figure 4 shows a section along the line IV- IV from Figure 3 , a part of the rotary hammer being represented as a view . Figure 5 shows, in a representation corresponding to Figure 3, the rotary hammer in the operating position for hammer drilling. Figure 6 shows, in a representation corresponding to Figure 4, a section along the line VI -VI from Figure 5. Figure 7 shows, in a representation corresponding to Figures 3 and 5, the rotary hammer in the chiselling position with the hammer spindle unlocked. Figure 8 shows a section along the line VI I I -VI I I from Figure 7 in a representation corresponding to Figures 4 and 6. Figure 9 shows, in a representation corresponding to Figures 3, 5 and 7, the rotary hammer in the chiselling position with the hammer spindle locked. Figure 10 shows a section along the line X-X from Figure 9 in a representation corresponding to Figures 4, 6 and 8. The represented rotary hammer has a hammer housing 1, made up in the usual way of several components, which forms a gripping portion 3 at its rear end, so that a customary switch actuator 5 for switching the electric motor 6 on and off projects into a grip opening 4 which is defined at its rear side by the gripping portion 3. In the rear lower portion of the hammer housing 1, a mains lead which serves to connect the rotary hammer to a power source, is led out. Located in the upper portion of the rotary hammer in Figure 1 is an inner housing 1', formed of half -shells and made from cast aluminium or the like, which extends forwards out of the rotary hammer housing 1 and in which the hammer spindle 8 is rotatably housed. The rear end of the latter forms the guide tube 8 ' , provided in known manner with vent apertures, for a pneumatic hammer mechanism, and at the front end of which the customary tool holder 2 is held. The hammer mechanism contains a piston 9 which is coupled, via a trunnion 11 housed in it and a crank arm 12, with a crank pin 15 which sits eccentrically on the upper plate-shaped end 14 of a drive shaf 13. A reciprocating movement of the piston 9 is carried out to alternately create a vacuum and an over-pressure in front of it, in order to move the ram 10 situated in the guide tube 8 ' correspondingly, so that this transmits impacts onto the beat piece 11, which passes them on to the rear end of a hammer bit or chisel bit, not represented, which is inserted into the tool holder 2. This mode of operation and the structure of a pneumatic hammer mechanism are, as already mentioned, known and will therefore not be explained in more detail. The electric motor 6 is arranged in the hammer housing 1 in such a way that its armature shaft 7 extends perpendicular to the longitudinal axis of the hammer spindle 8 and the tool holder 2, the longitudinal axis of the armature shaft 7 preferably lying in a plane with the longitudinal axis of the hammer spindle 8 and tool holder 2. At the upper end of the armature shaft 7 in Figure 1 a pinion 7' is formed which meshes with a gear wheel 18 which sits rotatable on the drive shaft 13 for the hammer mechanism. The pinion 7 1 also meshes with a gear wheel 21 which is arranged on the side of the armature shaft 7 lying opposite the drive shaft 13 and is non-rotatably secured on a shaft 22 rotatably housed in the housing 1 ' . At the upper end of the shaft 22 a bevel gear is formed, which meshes with the bevel toothing 16' of a drive sleeve 16 which sits rotatable via a schematically indicated friction bearing, but axially non-displaceable on the hammer spindle 8 or on its rear part forming the guide tube 8 ' for the hammer mechanism. A coupling sleeve 17 is arranged, axially displaceable but non-rotatable as a result of engagement with a splined section on the outer surface of the hammer spindle 8, on the hammer spindle 8 in front of the drive sleeve 16. This coupling sleeve 17 can be displaced between a position in which it is in positive engagement, via teeth or projections formed at its rear end, with corresponding teeth or projections at the front end of the drive sleeve 17, and a forwardly displaced position in which there is no engagement between it and the drive sleeve 16. A helical spring 30' loads the coupling sleeve 17 in the direction of the drive sleeve 16. The result of this spring loading is that, upon movement of the coupling sleeve 17 in the direction of the positive engagement with the drive sleeve 16 and a concomitant blocking of the positive engagement by abutment of the end faces of the projections or teeth of the coupling sleeve 17 against the end face of the projections or teeth of the drive sleeve 16, a positive engagement is then automatically established when there is a relative twisting of the coupling sleeve 17 and the drive sleeve 16, say because the shaft 22 rotates the drive sleeve 16. As is to be seen, a rotation of the armature shaft 7 via the gear wheel 21 and the bevel toothing 23 of the shaft 22 causes a rotation of the drive sleeve 16 and, when there is a positive engagement between this and the coupling sleeve 17, also a rotation of the hammer spindle 8 and thus of the tool holder 2. Accordingly, in the absence of a positive engagement between the drive sleeve 16 and the coupling sleeve 17, the hammer spindle 8 is not rotated despite rotation of the drive sleeve 16. If, rather, the coupling sleeve 17 with its protrusions which are provided at the front end-area and project radially outwards enter into a positive engagement with corresponding recesses in the housing-fixed zone 24, the result is a position of the coupling sleeve 17, and thus of the hammer spindle 8 including the tool holder 2, which is locked against rotation. This mode of operation of the coupling sleeve 17 is known. To drive the hammer mechanism, the gear wheel 18 driven by the pinion 7 ' of the armature shaft 7 is coupled with the drive shaft 13 in a manner yet to be described, so that the crank pin 15 performs a circular movement which creates, via the crank arm 12, the reciprocating movement of the piston 9 in the guide tube 8 ' of the hammer mechanism. This type of drive is also known in rotary hammers in which the armature shaft 7 of the drive motor 6 lies perpendicular to the longitudinal axis of the hammer spindle 8 and the tool holder 2. To switch between the individual operating modes of the rotary hammer, the latter has a single switching element 25 which is rotatable about its main axis 26. From the outside an actuation button, not represented, is secured to the switching element 25 and is accessible to the user. On its inside the switching element 25 has a cam section 27, which has a cam surface 28 which runs spirally around the main axis 26. It extends over an angle range of roughly 210 and the ends of the cam surface are connected by a rectilinear section. Projecting from the inner end of the switching element 25 is a rod- or pin-shaped actuating section 29 which extends parallel to the main axis 26 and at a lateral distance from the latter. A sleeve 19 sits on the drive shaft 13, non-rotatable through engagement with a splined section but axially displaceable, and has an annular flange 20 at its upper end in Figures 1 to 3. A spring 21, which lies with its upper end against the inner race of a ball bearing rotatably housing the drive shaft 13, supports itself on the annular flange 20, so that a force which is directed downwards, i.e. in the direction of the gear wheel 18, acts permanently on the sleeve 19. At the lower end, the sleeve 19 has projections or teeth, not represented, which, in the lower position of the sleeve 19 which is shown in Figures 2, 5 " , 7 and 9, are in positive engagement with corresponding recesses in the body of the gear wheel 18, so that in this position a rotation of the gear wheel 18 also brings about rotation of the drive shaft 13 which is in positive engagement with the sleeve 19. The rod- or pin- shaped actuating section 29 which is provided at the switching element 25 extends into the area below the flange 20 of the sleeve 19 and, upon rotation of the switching element 25 about its main axis 26, in the positions according to Figures 5, 7 and 9, is moved about same on a semi-circle which, when the sleeve 19 is situated in the lower position, lies below the flange 20. In all these positions, the sleeve 19 is therefore in positive engagement with the gear wheel 18, so that, upon rotation of the armature shaft 7, the hammer mechanism is driven as a result of the circular movement of the crank pin 15. How-ever, if the switching element 25 is twisted clockwise out of the position according to Figure 5 or counter-clockwise out of the position according to Figure 9, the result is an engagement of the rod- or pin- shaped actuating section 29 with the lower surface of the flange 20 and thereby a raising of the sleeve 19, against the force of the spring 21 acting on it, out of the engagement position with the gear wheel 18. In this position, shown in Figure 3, the hammer mechanism is not driven when the gear wheel 18 is driven, i.e. the rotary hammer operates in pure drilling mode . To change the aforementioned position of the coupling sleeve 17 which is arranged non-rotatable, but axially displaceable on the hammer spindle 8, a slider part is provided which consists of a connection section 30 and an engagement section 35, which are guided in projections of the housing 1 which are not shown. At one end, the connection section " 30 has an bent part 31 which, as represented, supports itself against the cam surface 28 of the cam section 27 of the switching element 25. Supporting itself against the opposite bent end 32 is one end of a spring 41 which sits on a pin of the engagement section 35 and, with its other end, rests against a side wall of the engagement section 35. This spring is stiffer than the spring 30' acting on the coupling sleeve 17 and thus creates, between connection section 30 and engagement section 35, a force which loads the connection section 30 in the direction of engagement with the cam surface 28 and the engagement section 35 in the forward direction, i.e. in the direction of the front end of the spindle 8, if the sections 30, 35 are displaced relative to each other. At the engagement section 35, legs extending on both sides of the hammer spindle 8, of which only the leg 37 is represented in the drawings, are formed at lateral projections 36, 38, so that the engagement section 35 has an essentially U-shaped cross-section in this area. The legs 37 extend upwards from the essentially level engagement section 35 above the level of the longitudinal axis of the hammer spindle 8, as is shown in Figures 2, 3, 5, 7 and 9. As is to be seen at once, a rotation of the switching element 25 causes, in addition to the movement explained above of the rod- or pin- shaped actuating section 9, a displacement of the slider part 30, 35 as a result of the changing distance of the cam surface 28 from the main axis 26 of the switching element 25. If the operating mode according to Figures 3 and 4 is considered first, it will be to t H LΠ o LΠ o LΠ o LΠ tn μ- Ω TJ ft ) P TJ Ω rt 3 J 3 rt rt ft ) ft ) rt 3 rt o TJ ftJ rr μ- μ 1 P ft ) 03 a O i LQ o μ- 0 0 rr φ LΠ O O tr tr Ω tr o tr μ- ii ft ) 3 1 μ- LQ Φ Φ rr a O ft ) ~ tn hi 03 O ft ) Ω 03 rr Φ φ Ω Φ P Φ a 3 3 rt 03 ft ) Φ Φ O TJ rt μ- TJ μ- Ω rt rr hi μ- o O Φ TJ ft ) 3 O μ- rt μ- a <: hi a μ j rt rt r PJ Φ rt Ω tr LQ s: hi TJ rr o CQ rt Φ 03 ft ) ti Φ ft ) μ- a tn LΠ ft ) tr μ- ≤ M rr a 3 μ- rr ft ) φ Φ P 0 ft ) 03 rr a hi TJ a 03 rt a P rt • Ω φ O μ- tr μ- ft ) O ft ) 3 ft ) hi μ- 03 O 3 μ- ftj ii o J Ω rt tr I- 1 TJ LQ μ- φ a 03 Φ cn μ- a a 3 ϋ μ- a μ- hi 3 rt TJ φ 03 en hi Φ ft ) Ch 0 a rt •-_ 3 tr Φ rt 3 a LQ Φ a LQ rt rt Φ μ- Φ TJ μ- φ ftJ rt ~ CQ en LQ rr rr φ ft ft ) tr o 03 O μ- ii £ LQ μ- rr TJ ii <! en μ- rt 03 μ- h- 1 φ Φ a 3 Ω O φ TJ μ- a tr rt O Φ a φ tr a μ- 03 ϋ N rt tn rt φ hi rt 3 Ω a Φ 03 a LQ 3 Φ o O a hi 3 ftj ft j P < Φ 0 0 tr o μ- Φ ft ) hi Φ o rt en ϋ a rr φ Φ 03 φ φ φ Ω Φ P 3 3 φ O < P φ Φ 0 hi hi £. ft ) P Ω tr μ- Ω •x] ft ) Ω a r rt φ Φ rt a φ μ- ft ) LQ P O μ- rr ii tr Φ rr rr rt μ- Ω μ- P rr LQ a Φ rt σ tr ft ) ii en 3 μ- rt μ- μ- ft ) tn ft ) M rr LQ Ω rt hi ft ) ft ) PJ - . ∞ a ft j rr O Φ ft μ- μ> h- 1 rt φ t- Ω 3 < a tr 3 Φ a O Ω μ- a LQ r • LQ 03 Φ r j rt a -0 en ^ Ω LQ rt tr LQ φ LQ Φ P μ- h hi rr - 1 μ- Φ μ- μ- ft ) rt ^ a Φ rr rr μ- a Φ a μ- 03 ft ) 03 Φ P μ- - 1 03 3 a CO LQ ft ) 3 rt rt s: ft ) ii rt Φ 3 3 P rr 03 3 a - 1 μ- 3 μ- 3 φ LQ μ- Φ ft ) tr TJ rr tr a O O tr ft ) O LQ o • rt Φ a LQ a a a P 3 ϋ μ- φ ftJ φ μ- P a ft ) Φ a TJ P. a TJ ft ) Φ ~ LQ LQ μ- rt Ω ii φ φ a i Ω rr Ω a μ- ^i o Φ φ P ft ) a ≤ rt < φ • 03 Φ φ μ- a 03 Ω rt P tr rt φ rt rt 03 μ- en a ii Ω rr tr Φ rt rt Ω ^ <! rt a ftj ft ) ii tr ft ) 03 tr 3 LQ μ- φ rt rr φ Φ Φ rr O Φ a μ- rt φ X 3 μ- μ- Φ hi Φ TJ a rt 3 o rr O ii i H Φ 3 o rt μ- μ- a € rt μ- < r hi P O ft ) i μ- φ hi φ TJ Φ φ ^ φ rt tr o a μ- 03 03 φ φ tQ Φ ii tr φ O 3 Φ H ii ft ) ii μ- a a hi rt 0 a o μ- tr a rr a a rt ii rr ϋ O 03 O μ- Φ LQ rt P rt rt o rr to hi ^ ft ) rr LQ rt o ft ) PJ ft j 3 - ϋ a 03 a ii rr to tr rt O rt tr ft ) - ft ) t rt 3 rt a Φ rt a hi to μ- φ u. μ- PJ rr rt ~ ft ) rt h a P φ LQ H r Ω LΠ ft! 3 μ- P rt tr o - 1 φ LΠ 03 rr rr a j Ω tr o μ- rt Φ tr rt Ω ii φ O rr Φ μ- rt φ LQ rr μ- Φ φ ≤ Φ φ rt rt ω tr rt ft ) Φ rr O μ- ^ hi 3 rr φ Ω a TJ - μ- a φ ft ) o 3 rr tr TJ φ φ 3 a hi Φ ii 03 ^ rr ft ) o 03 - ft! 03 TJ LQ P ft ) φ t Ω Φ Φ h- 1 φ φ P Φ P tr 03 a 3 a ft j 03 PJ μ- hi φ ii o hi O a ft ) rt 3 P μ- i ft ) TJ rt en ft ) 03 μ- tn a rt rt ii ii ^ μ- rr φ a hi LQ Ω ii rr rt rt μ- ii 3 O 3 μ- rr μ- Φ TJ rt rt s: tr s: ft ) ft ) < μ- tr a o ft ) φ O tr 03 μ- LQ rt 3 a Φ O a O μ- ft ) O μ- μ- tr μ- rt a Φ O ^ tr Φ rt LQ a 0 en a < PJ Φ P hi rt en <; 03 03 Φ 03 μ- J 3 μ- Ω ft ) Φ rt rt hi Φ tn ft ) Φ rt rt i Φ ft ) tr μ- Φ ϋ rt rt Φ Φ r j 0 tn rt Ω rt rt P tr Ω O Φ μ- φ rt X φ rt φ tr φ μ- t- 1 P LQ a h- 1 0 rr tr μ- μ- μ- Φ TJ r O hi P 3 rr μ- H- Φ ft j Φ P 03 Φ Φ O o ≤ tQ a hi μ- O φ LQ O Φ 03 Ω O a H rt 3 ϋ Φ μ- a a μ- P 0 0 hi 3 μ- hi HJ 3 LQ ; TJ Ω rt rr 0 0 < r Ω 03 rt Ω a rt ft ) LQ a μ- μ- φ 03 t 3 ft ) O tr Φ rr Φ rr o 03 o rr O 0 Φ tr ft ) μ- a ii en 03 - h- 1 σ> LQ P tn O φ ft ) φ ft ) Φ a ft ) Φ £ Ω > Φ hi a hi rt μ- - 03 O Φ Φ μ- Ω 3 03 - rt H TJ rt Ω rr TJ rt LΠ P 03 φ tr 03 hi rt P a ϋ 3 03 rr rV 0 P μ- T 03 - 1 rr rt tr rt μ- tn φ φ o rr Φ rt ii φ Ω μ- ≤ TJ Φ rt O - TJ μ- ftj μ- tr Φ μ- tr O ii h- 1 ft ) LΠ hi rr rt Φ ii tr 3 hi O μ- φ rt Φ tr a ii a O Φ a Φ a Φ μ- Ω • ft ) Φ ft ) ii rt μ- a cn ii tr <! Φ ft j μ- LQ 3 3 P LQ en CQ P rt μ- rt rr TJ Ω μ- tr φ ft j Φ φ o a 3 μ- tr H rt φ μ- 3 Φ ft j ft j Φ < Φ rt ϋ hi P LQ en 3 ft ) μ- tQ hi < rt P 3 hi μ- μ- P O H- φ to 0 μ- 1 μ- o 3 < μ- 1 ft ) O 3 rt to a rr a a p. rt rt Φ 3 3 φ φ TJ rt Φ LQ rr rt LQ o tr tr φ a Φ φ ft j Φ rt 03 hi μ- hi O Φ Φ - < 3 μ- ii < ii P rr O o μ- O 03 O φ a O φ φ φ rt Φ en hti hti rt hi 03 spindle 8 is broken. However, since there is still no positive engagement between the recesses in the housing-fixed zone 24 and the pro-jections or teeth at the front end of the coupling sleeve 17, the hammer spindle 8 is not yet secured against non-driven rotation. The rotary hammer is in the operating mode for hammering or chiselling. Further rotation of the switching element 25 clockwise out of the position according to Figure 7 into the position according to Figure 9 does not bring about a change in the position of the sleeve 19, so that the hammer mechanism remains activated. How-ever, since the radial distance of the cam surface 28 of the cam element 27 from the switching element 25 increases further, the slider part 30, 35 is displaced further forward. This results in a further forward displacement of the coupling sleeve 17, so that the teeth or projections protruding radially outwards at its front end enter into positive engagement with the corresponding recesses in the housing-fixed zone 24, and so the hammer spindle 8 is locked against rotation. It should be mentioned that the coupling sleeve 17 is loaded by action of the spring 41 in forward direction in such a way that, when there is a relative twisting of the coupling sleeve 17 and the housing- fixed zone 24, a positive engagement comes about between them if it was not possible to create this positive engagement at first, because the end faces of the projections or teeth of the coupling sleeve 17 come to rest against the end faces lying between the recesses in the housing-fixed zone 24.

Claims: CLAIMS 1 Rotary hammer with a hammer housing (1) , - a tool holder (2) which is provided at the front end of the hammer housing (1) and which can be rotatingly driven by the electric motor (6) about the axis of the hammer spindle (8), a hammer mechanism which is provided in the hammer housing (1) for generating impacts acting on the rear end of a hammer bit or chisel bit inserted into the tool holder (2) and a switching element (25) which is rotatable from the outside about its main axis (26) and which has a cam section (27) , for switching between at least three operating modes, of which the first is pure drilling, the second hammer drilling and the third chiselling, characterised in that the armature shaft (7) of the electric motor (6) is arranged perpendicular to the axis of the hammer spindle (8) , that the armature shaft (7) can selectively be coupled with a drive shaft (13) for the hammer mechanism, that the armature shaft (7) drives a drive sleeve (16) which is arranged rotatable on the hammer spindle (8) and which can be coupled with the hammer spindle (8) via a coupling sleeve (17) which sits non-rotatable but axially displaceable on the hammer spindle (8), that the cam section (27) of the switching element (25) acts on the coupling sleeve (17) via a slider part (30, 35) which can be moved parallel to the axis of the hammer spindle (8), so that the coupling sleeve (17) can be moved between a position of engagement with the drive sleeve (16) and a release position separated from the drive sleeve (16) , and that there is provided at the switching element (25) an actuating section (29) which is eccentric relative to the main axis (26) and which cooperates with a coupling part (19) which can be moved coaxially relative to the drive shaft (13), in order to move the coupling part (19) between a position coupling the drive shaft (13) with the armature shaft (7) and a position in which the drive connection between the armature shaft (7) and the drive shaft (13) is broken. 2 Rotary hammer according to claim 1, characterised in that, in a withdrawn position, the coupling sleeve (17) is in positive engagement with the drive sleeve (16) and, in an advanced position, is in positive engagement with a housing- fixed zone (24) , and that the coupling sleeve (17) is spring- loaded in the direction of the withdrawn position. 3 Rotary hammer according to claim 2, characterised in that the slider part (30, 35) is spring-loaded in the direction of the advanced position of the coupling sleeve (17) . 4 Rotary hammer according to one of claims 1 to 3 , characterised in that the cam section (27) has a cam surface (28) which runs spirally around the main axis (26) of the switching element (25) and against which the rear end (31) of the slider part (30, 35) rests, and that the front end of the slider part (30, 35) is fork-shaped and, in order to displace the coupling sleeve (17) into its advanced position, engages with its fork arms (37) with a support surface provided on the outer surface of the coupling sleeve (17) . 5 Rotary hammer according to one of claims 1 to 4, characterised in that the coupling part (19) is spring- loaded in the direction of the coupling with the drive shaft (13) . 6 Rotary hammer according to one of claims 1 to 5, characterised in that the coupling part consists of a sleeve (19) which sits non-rotatable but axially displace-able " on the drive shaft (13) and has a radially outwardly directed flange (20) , and that the actuating section (29) of the switching element (25) can be brought into engagement with the flange (20) which displaces the sleeve-shaped coupling part (19) .

Inventors: LAUTERWALD MARTIN, LAUTERWALD, MARTIN
Applicants: BLACK & DECKER INC, BLACK & DECKER INC.
Application year: 1998
Main classification: B25D16
IPC codes: B23B45, B25D16