Device for driving a drilling and/or percussion tool

Abstract: A device for the driving of a drilling and/or percussion tool provided with a spindle 5 mounted rotatably in the housing 1, the one end of which spindle is suitable for fastening to the tool piece, the other end being accessible to an oscillating percussion body 6 movable in the housing 1 by means of a guideway 7, a rotatable driving shaft 3 bringing the tool spindle into rotation, a transmission being provided with means for the conversion of the rotary motion of the drive shaft into an oscillatory motion of a drive member 8, said member being joined to the percussion body through an elastic member 26 having a non-linear spring characteristic, wherein the drive member is mounted on the drive shaft or a shaft coupled therewith, under an angle deviating from 90 degrees to the centre line thereof, and the elastic member is a plate-like member rotatably connected to the drive member, and being provided with a coupling means engaging with the percussion body, whereby the conversion mechanisme can be made simple and small, whilst the frequency of the oscillatory motion can be boosted considerably giving a better percussion effect on the tool spindle.

Description: The invention relates to a device for driving a drilling and/or percussion tool, provided with a spindle held where necessary rotatably in a housing, the one end of said spindle being adapted to fastening the tool piece, the other end being accessible to an oscillating percussion body movable in the housing by means of a guideway, a rotatable drive shaft bringing the tool spindle into rotation and/or the percussion body into motion via a transmission, said transmission being provided with means for the conversion of the rotary motion of the drive shaft into an oscillatory motion of a drive member, said member being provided with an elastic member having a non-linear spring characteristic, said elastic member being coupled with the percussion body. In a device of this kind, described previously in EP-A-145070 in the name of the present applicant, the drive member and elastic member are relatively heavy and bulky. The invention has for its aim to improve both the conversion means and the elastic member as well in order to obtain a simple construction, occupying less space and having a more favourable weight. The improved device according to the invention is distinguished in that the drive member is mounted in a wobbling or eccentric way on the drive shaft or a shaft coupled therewith, wherein the elastic member is directly connected to the drive member and comprises a plate-like member. Owing to the direct mounting of the drive member on the shaft associated therewith, the conversion mechanism can be made particularly simple and small. Moreover the frequency of the oscillatory motion can be boosted considerably, with retention of sufficient energy per stroke, which in some embodiments has a considerably better percussion effect on the tool spindle as a consequence. In a preferred embodiment the coupling means is a tongue fastened to the plate which projects into an aperture arranged in the percussion body. In this embodiment the percussion body can hence be made small and is thereby suitable for a high oscillation frequency. It can be advantageous to give the aperture a larger dimension in the direction of the stroke than the tongue of the elastic member, so that the desired non-linear spring characteristic is also obtained in the case of stiff elastic members. In another embodiment there is arranged extending along the elastic member a spring plate whereof the spring constant is less than that of the elastic member. Since the spring plate will be cushioned during the movement to a greater or lesser extent against the elastic member, a non-linear spring characteristic is brought about hereby. If the drive member is mounted directly onto the motor shaft it is preferable to provide it on the motor side with a clutch, through which not only is assembly simplified but the bending loads on that shaft are reduced. The invention further relates to a device which is provided with a percussion mechanism, for instance in the form described above, wherein the percussive force is transmitted directly to the tool piece to be coupled to the tool sprindle. To that end the tool spindle is provided according to the invention with a tool-holding body, which is made with means for the rotation-proof fastening of a tool shank in the tool holder, which nonetheless permits an axial movement of the tool with respect to the drive shaft. The above and other characteristics will be further elucidated in the detailed description below of a number of embodiments. In the drawing: Figure 1 shows an axial section of a device according to the invention which is embodied as an electrical hand tool, Figure 2 shows a tension/deflection characteristic of an elastic member proposed according to the invention, Figure 3 shows an axial section corresponding to figure 1 of a part of the device on an enlarged scale, Figure 4 shows a cross section/view according to line IV-IV in figure 3, Figures 5a and 5b show a cross section corresponding to figure 3 of two variants, Figure 6 shows a cross section/view according to the line VI-VI in figure 5a, Figure 7 shows a cross section corresponding to figure 3 of a fourth variant, Figure 8 shows a cross section/view according to the line VIII-VIII in figure 7, Figure 9 shows a longitudinal section of a part of the device of figure 1 according to a fifth variant, Figure 10 shows a cross section corresponding to figure 9 a sixth variant, however with portions of the housing of the device shown cut away, Figure 11 shows a longitudinal section corresponding to figure 9 according to a seventh variant of the device according to the invention, Figure 12 shows a cross section according to the line XII-XII in figure 11, Figure 13 shows a longitudinal section corresponding to figure 11 of a part of the device on an enlarged scale, in which a different tool holding means is shown, Figure 14 shows a cross section corresponding to figure 1, in which the air intake and outlet openings are disposed differently in the housing in order to achieve a variant cooling air flow, Figure 15 shows a view of the front part of an electric hand tool provided with dust removal means suited to a device from figure 14, Figure 16 shows an axial cross section corresponding to figure 1 of an electric hand tool according to an eighth variant with two drive motors, Figure 17 shows a top view of a part of the device of figure 16 according to the line XVII-XVII. Reference number 1 indicates the housing of an electric drilling tool which comprises in the usual way an electric motor 2, of for instance the collector type, and also cooperating with the drive shaft 3 a transmission 4 in the form of a double gear wheel drive and a tool spindle 5. At the free end of the tool spindle 5 a tool (not shown) can be fastened in arbitrary manner. At the opposite inner end of the tool spindle 5 in extension thereof there is included a percussion body 6 which 7 is movable through slide bearings to and fro in housing 1 in a freely slidable way. The driving of the percussion body 6 for engendering reciprocating movement thereof is possible by means of a driving body 8 with an associated elastic member 9, whereof the construction and the operation will be further elucidated hereinbelow. It should be mentioned in this connection that according to the known embodiments for hand tools, the housing is provided with a handgrip 10 in which a switch 11 is mounted for the empowerment and switching off of the electric motor 2. The operation and the function of the switch 11 forms no part of the invention and is assumed known, as is equally the principal operation of the electric motor 2 for driving the tool spindle 5 through the transmission 4. There now follows a description of the driving of the percussion body 6 by means of the drive member 8 and elastic member 9. To that end reference is also made to the cross section on enlarged scale according to figure 3. On the intermediate shaft 12 of the transmission, the drive member 8 is supported, the manner of supporting being modified according to the embodiment of the drive member 8. The drive member 8 can subtend a fixed angle deviating from 90 degrees with respect to the centre line of the intermediate shaft 12, this and other matters being so arranged that the elastic member 9, in the form of a plate to be described in further detail hereinbelow, similarly subtends an angle deviating from 90 degrees to the centre line of intermediate shaft 12. On rotation of the shaft 12 the drive member 8 with the elastic plate 9 will therefore come to acquire a rocking motion which extends between position A (drawn with solid lines in figure 1) and position B (drawn with broken lines). It is observed thereby that the plate 9 is mounted rotatably on the drive member 8, so that the plate 9 undergoes an exclusively reciprocating motion, while the drive member 8 rotates together with the shaft 12. The connection between the drive member 8 and the shaft 12 is brought about via an axial claw coupling, whereof the one part 13 is fixed firmly to the drive member 8, and the other part 14 is slidable with a sleeve 15. The sleeve 15 has a passage opening with internal toothing 16, which cooperates with the toothing 17 on the shaft 12, which toothing 17 engages with the gear wheel 18 of the tool spindle 5. The shaft 12 is moreover provided with a shoulder 18, a compression spring 19 being held between the shoulder 18 and the sleeve 15. It is further observed that the tool spindle 5 is mounted to a certain extent axially slidably in the bearing of the housing, so that on the impression of the tool spindle in the direction of arrow P1 the gear wheel 18 is carried therewith to the right, which slides the sleeve 15 along to the right and causes the part 14 of the dog clutch to engage with the part 13 and thus with the drive member 8. The elastic plate-shaped member 9 has a bush opening through which the percussion body 6 is freely movably bushed, whereby it is to be understood that the body 6 displays a notch 20 at the level of the plate. Into this notch projects a tongue 21 of the plate 9 (see figure 4), this and other matters being so arranged that on reciprocating motion of the plate 9 from position A to position B and vice versa the tongue 21 thrusts against the end faces of the notch 20, through which the percussion body 6 is carried in a retarded manner along with the motion of the plate 9. The dimensioning of the stroke of the plate 9 is such that the percussion body 6 repeatedly hits against the free end of the tool spindle 5, whereby a hammering effect results. The working of the device described above is therefore as follows: When drive shaft 3 is made to rotate, the intermediate shaft 12 will be brought into rotation through the first gear wheel transmission, which intermediate shaft 12 causes via the second gear wheel transmission the gear wheel 18 to rotate and thereby the tool spindle 5. When the tool spindle 5 is impressed, which occurs through the placing of the tool against the workpiece, the shaft is pushed into the housing 1, through which the dog clutch 13, 14 comes into action and the plate 9 will undergo a reciprocating motion. Through this the percussion body 6 will move to and fro in the housing 1 and repeatedly strike against the tool spindle 5, through which the combined rotary and percussion drilling effect is brought about. In the above described embodiment, a non-linear spring characteristic is obtained simply by adopting a relatively stiff plate as the elastic member 9. This and other matters are shown in the force/distance curve in figure 2, wherein the deflection S of the elastic member is shown horizontally and the associated force K is shown on the vertical axis. Since the spring plate 9 has a normal linear spring characteristic, this characteristic can be indicated by the straight line 24. This straight line intersects the horizontal line at point A, which indicates the one position of the spring plate 9 with respect to the notch 20, of which the longitudinal dimension corresponds to the line segment AB. The linear characteristic will continue on the left-hand side of the vertical axis in the system of figure 2 according to the straight line 25. On account of the stepped form of the line 24 and 25 the desired non-linear characteristic is obtained, which is necessary for the special working of the device according to the invention. With a less stiff plate 9, a more strongly inclining characteristic will be obtained, as is indicated by the lines 24′ and 25′ respectively. In particular embodiments it can be advantageous to arrange a second elastic plate next to the elastic plate 9, as is indicated by 26 in figure 1. This second elastic plate 26 (see also figures 3 and 4) has a more pliant spring characteristic and therefore a lower spring constant than plate 9. In the interval AB the spring characteristic indicated by lines 24″ and 25″ will for example be followed until the plate 9 cooperates. The lines 24″ and 25″ intersect the S axis at points C and D. The distance CD is the clearance between the spring systems and the notch 20 of percussion body 6. A construction of the kind will at least cause the sharp angle between line segments BA and 24 to take a smoother course, as is indicated by line segment 27. If there is also a second spring plate 26 arranged to the right side of plate 9, this smoothed course can equally be brought about on the left-hand side of the vertical axis of the system in figure 2 according to line 27′. The embodiment according to figure 3 departs from that in figure 1 insofar as that the dog clutch 13, 14 is in this case absent. The drive body 8 is shaped here in the form of a with respect to shaft 12 tiltable bush, which is clasped between a firmly on shaft 12 mounted collar part 28 with an oblique thrust surface 29 and a freely slidable with respect to the shaft 12 sleeve 30, also with an oblique thrust surface 31. The thrust surfaces 28 and 31 lie mutually parallel. The sleeve 30 is in the manner described hereinabove according to figure 1 similarly movable towards the right by gear wheel 18 in opposition to the pressure of a compression spring 15. When the gear wheel 18 is moved towards the right the thrust surfaces 29 and 31 will hence be moved towards each other, so that the drive member 8 is set into a position deviating from 90 degrees with respect to the shaft 12. In this way the elastic plate 9 will similarly be made to incline in a position between the extremes A, B in figure 1. The working corresponds further to that according to the embodiment in figure 1. It is also observed that the plate 9 is mounted with respect to the drive member 8 by means of a radial ball bearing 32. To that end the plate 9 is fastened between two normal spring washers 33 on the outer ring of the ball bearing housing 32. In a corresponding way, an optional spring plate 26 is mounted. The figures 5a, 5b and 6 show an alternative embodiment of the driving mechanism for the percussion body 6. Identical components are indicated by the same reference numbers. Noteworthy is the form of the springy plate 9 as elastic body. A second spring plate 26 is not used here, but the plate is executed with a meandering tongue 35, of which there are two arranged on each opposing side of the plate 9, such that a lower spring constant is brought about. The extremity of the tongue again projects into a notch 20 in the percussion body 6. The plate 9 is here too clamped between two spring washers 33 on the outer race of a radial ball bearing. The radial ball bearing is fastened to the drive body 8, which is arranged tiltably with respect to the intermediate shaft 12. The drive body 8 is tilted by means of a sliding bush 15, which is now provided with a radially directed steering surface 31′, which cooperates with a radially inward facing steering surface 36 of the driving member 8. Through the movement of the bush 15 towards the right against the pressure of a compression spring, the steering surface 31 will come into contact with the steering surface 35 and cause the member 8 to tilt. Through this the plate 9 acquires an angle deviating from 90 degrees with respect to the intermediate shaft 12 and it can rock to and fro between the two extreme positions A and B in the manner described above. The extremities of the tongues 35 will deflect out of the plane of plate 9, through which a lower spring constant results. Hence the line 24′/25′ in figure 2 can be achieved. Figure 5b departs from the embodiment according to figure 5a in respect of the mounting of the plate 9 in relation to the drive member 8. To that end, use is not made of the radial ball bearing 32, but of an axial thrust bearing 37, where in each case a ball bearing 39 is mounted between the plate 9 and on the one side an axial wall part 40 of the member 8 and on the other side a ring 41. The ring 41 is mounted on a reduced portion of the member 8 by means of a spring washer 42. The drive member is here, similarly corresponding to figure 5a, tiltable by means of a sleeve 15 slidable to the right. Figures 7 and 8 show that the elastic member in the form of a stiff plate 9 cooperates with a specially shaped spring plate 26, which is made more pliable in comparison to the spring plate in figure 4. Through this sharper transitions result at the points A and B of the spring tension/deflection characteristic in the system according to figure 2. The drive member 8 is here executed with a bearing ring 43 arranged directly on the intermediate shaft, around which ring a second bearing ring 44 is mounted whereof the outer surface displays a portion 45, whereof the centre line forms an angle with that of the drilled hole in the shell 43. In this way a radial ball bearing 32 arranged on this outer surface 35 can adopt an oblique position with respect to the intermediate shaft 12, and so too the spring plate 9 which is mounted in the manner according to figure 5a. In this embodiment the clutch between the intermediate shaft 12 and the drive body 8 is absent. The hammering operation of percussion body 6 can be inactivated by fixing this body in the drawn position, for example by passing a pin 6′ through a hole in the slide bearing 7 into the percussion body 6. Figure 9 shows an embodiment in which the percussion body 6 is not accommodated in a sliding support in housing 1 but is suspended in two parallel spring plates 46 The lower end of each plate 46 is fastened in a support 47 of the housing 1. The free upper end of each plate 46 is firmly secured to the percussion body 6. A displacement of the percussion body 6 to the right or to the left respectively in figure 9 results in a translation of the percussion body 6, one of the end positions being drawn in the figure, in this case in contact with the free end of the tool shaft 5. In this embodiment the percussion body is not made with a notch but with two projections 20′ which are arranged at a distance from each other. In the space between the projections 20′, a tongue 21 of a plate 9 can project. In this embodiment the plate is provided on both sides with a spring plate 26. It is clear that the forms of both the plate 9 and of the plate 26 may correspond to the plate forms described above and shown in the preceding figures. The mounting of the plates 9 and 26 respectively can take place in the same way as in the various other embodiments. Finally it is observed that the shaft 12 for the drive body 8 is not coupled to the drive shaft of the motor 2 by means of a first transmission, but through a tongue and groove coupling 48, so that shaft 12 has the same rotation speed as the motor shaft 12. The coupling is located at the position of the first motor bearing 49, this and other details being such that assembly or disassembly of the motor 2 can take place without it being necessary to dismantle the shaft 12. Figure 10 shows an embodiment in which the percussion body 6 is guided in an axial blind drilled hole 50 in the tool spindle. The end of the percussion body 6 projecting outside the drilled hole 50 displays the notch 20, into which a tongue 21 of the spring plate 9 projects. The spring plate is turned over at a central portion 21 to form a sleeve 51 in which a groove 52 is arranged. In this groove 52 a ball cage 53 can be accommodated which similarly runs in a sloping ball track 54 of the drive body 8. The drive body 8 is mounted directly onto the shaft 3 coming from the motor by means of two radial ball bearings 55 separated by a mutual distance. The motor shaft 3 is made with a toothed end portion 17 which cooperates with the gear wheel 18. The toothed part 17 similarly engages with the slidable clutch part 14 of a dog clutch which cooperates with a clutch part 13 of the drive member 8. The part 14 of the dog clutch can be moved to the right or to the left respectively by any arbitrary means, for example by a separate actuation means 55, in order to bring about the coupling between shaft 3 and the drive member 8. It is further observed that a slip coupling in the form of a ball clutch is arranged between the gear wheel 18 and the tool spindle 5. The gear wheel 18 is mounted freely rotatable on the tool spindle 5 between two fixed rings 56 and 57 respectively. A slidable ring 58 can be pushed, owing to axial splines on the outside of the tool spindle 5 and on the inside of the ring 58 respectively, in the direction of the left side face of gear wheel 18 by means of a packet of cupped spring washers 59 which abut against the ring 57. Held in the gear wheel 18 are balls 60 which are each pressed by ring 58 into one chamber of gear wheel 18. The ring is provided with ball-receiving pits. On normal loading the force will be transmitted via gear wheel 18, the ball friction clutch and the ring 58 to the tool spindle 5. On overloading, the ring 58 will be moved to the left against the resistance of the cupped spring washers, whereby the balls 60 are forced out of their pits in the ring 58, whereby the gear wheel 18 can turn freely with respect to the ring 58. The construction shown offers the advantage that the percussion mechanism 6 operates independently of the friction safety clutch. Figures 11 and 12 show a following embodiment in which the rotating drive of a tool can be inactivated while the percussion mechanism remains in operation. To that end the tool spindle 5 is provided with a portion with external splines, upon which is arranged a slidable ring with internal splines 61. In this way the ring 61 is slidable in an axial direction with respect to the spindle 5, but remains non-rotatable in respect thereof. On the side facing gear wheel 18 the ring 61 is provided with dowels 62, which can engage with recesses in the side face of the gear wheel 18. When the dowels 62 fall into these recesses, the gear wheel 18 is non-rotatable with respect to the ring 61. A compression spring is held between a wall part 63 of the housing 1 and the ring 61. At the top of the housing 1 there is mounted a hand-operable rotary knob which is turnable around a vertical axis. On the underside of the knob there is arranged a pin 66 which projects into an annular groove of the ring 61. Through the turning of the knob 65 from the position shown in the drawing through an angle of 180 degrees, the pin 66 will move to the right in figure 11, taking with it the ring 61 in opposition to the pressure of compression spring 64. In that position the dowels 62 come to lie free of the gear wheel 18, whence the gear wheel 18 is freely rotatable with respect to the ring 61 and hence freely rotatable with respect to the tool spindle 5. The other parts of the transmission agree with those described in the embodiment according to figure 1. On the starting of the motor 12 in the shown situation, a rotational motion is imparted to the tool spindle 5, since the intermediate shaft 12 brings the gear wheel 18 into rotation, which transmits the rotational motion to ring 61 and thus to the tool spindle 5. The drive member 8 comes into operation in the manner described hereinabove as soon as the tool spindle 5 is moved towards the right in figure 11, whence the clutch 13, 14 engages and the drive member 8 with the plate 9 connected thereto acquires a rocking motion. This rocking motion is translated into a reciprocating motion of the percussion body 6. If only a percussive motion is required, the knob 65 may be turned around, through which the ring 61 is moved to the right and the coupling between ring 61 and gear wheel 18 does not occur even when the tool spindle 5 is impressed to the right. The rotary motion of intermediate shaft 12 is translated only into a driving of the drive member 8 and the reciprocating motion of plate 9 and thus of percussion body 6. The gear wheel 18 revolves thereby freely on the tool spindle 5 and the tool spindle 5 will exert exclusively a hammering effect. It is observed that the notch 20 in the percussion body 6 is located on the underside or on the side facing the intermediate shaft 12, so that the plate 9 extends exclusively on the underside of the percussion body 6. Here two spring plates 26 and 26′ are arranged next to the plate 9, a U-shaped fissure 68 being arranged for greater elasticity in one or both plates, whereby the spring length is increased. In this embodiment an indication is also made of how the tool, for example a drill-bit G, should preferably be held. This may be with the known drill receiving device, which is screwed onto a screw thread of the tool spindle 5. This holder device consists of a central part 70, around which a threaded part 71 is mounted. At the front of the central part 70 and inside the threaded part 71, wedge shaped jaws 72 are placed, whereof the inward facing parts 73 fall into recesses in the shank of the drill G. The length of the parts 73 is less than the length of the recess in the drill-bit G, so that the drill-bit can undergo a certain axial movement with respect to the receiving apparatus, while nonetheless a rotary motion can be transmitted. In this way it is possible to mount the end face of the drill shank G directly against the end face of the tool spindle, so that the percussive energy is delivered from the percussion body 6 via the tool spindle 5 directly to the drill-bit. An alternative embodiment of the holder head is shown in figure 13, in which the portion of the tool spindle 15 protruding from the housing 1 is executed with regularly around the circumference hollowed out parts 75, into which roller bodies 76 fit. These lie enclosed in both the axial and in the radial sense in the recesses 75. The tool spindle end 5 also carries a sleeve-like piece 76′ with recesses 77 similarly for the receiving of the roller bodies 76. The length of the sleeve-like housing 76′ is such that this can accommodate the shank end of the drill-bit G. This shank end is also made with recesses 78 for the accepting of roller bodies 79. The length of the recess 78 is however here greater than that of the bodies 79, so that an axial movement of the shank G with respect to the roller bodies 79 is possible but not a radial movement. The roller bodies 79 fit analogously to the bodies 75 into chambers 80 of the sleeve 76′. The bodies 75 and 79 respectively are held in their places by the appropriate rings 81 and 82 respectively which are mounted slidably on the outside of the sleeve. Between the rings there is mounted a compression spring 83, which on the one hand ensures that the ring 81 rests against a shoulder 84 of the sleeve 76′ and on the other hand ensures that the ring 82 rests against the end face of a collar 85 mounted firmly on the sleeve 76′. The collar 85 is for instance of plastic material. For the fastening of the collar 85 on the sleeve 76′, the latter is provided with a groove-shaped recess 86 in which a thickened edge 87 of the collar locks grippingly. The sleeve 76′ with the members supported thereby can be removed from the end of tool spindle 5 by sliding ring 81 to the left in opposition to the pressure of the compression spring 83, whence the roller bodies 76 can be moved out of the recesses 75, whereafter sleeve 76′ can be removed. The refitting takes place in reverse manner. A drill shank G can be fitted in a similar way by sliding the ring 82 to the right in opposition to the pressure of spring 83. For the purposes of protection, the ring 82 may also be provided with a skirt part 88 extending over the compression spring 83 and partly over the ring 81. It is to be preferred that the percussion mechanism is cooled, to which end a motor housing 1 is normally provided with cooling air openings (see figure 1). According to the invention it is recommended that the cooling air is passed forcibly along the percussion mechanism and that use is thereby made of the blade wheel 90 already present on electric motor 2. This twin blade wheel 90 serves as usual for the cooling of the electric motor 2, but now also, after the making of appropriately disposed passage openings in the motor housing 1, for the creation of a cooling air stream along the percussion mechanism. To that end, in a partition 91 of the housing 1 there is made a passage opening 92, behind which a filter 93 is situated. Similarly there is made beneath the motor bearing a passage opening 94 (see figure 1) through which a cooling air stream results following arrows P2 and P3 along the percussion mechanism and the motor 2 respectively. The air stream can be discharged via the outlet opening 95. The intake of the air normally takes place through slit-shaped openings in the handgrip 10 of the housing 1. Figure 14 gives a divergent configuration, in which on the underside of the housing 1 there is placed an intake opening 97. Owing to this opening 97 it is possible to carry the air stream via the percussion mechanism and passage opening 92 directly to the motor 2 and to discharge it through an outlet opening 95. In this embodiment the passage opening 94 is absent. The opening 97 is excellently suited for the attachment of a flexible tube, as is shown in figure 15. This flexible tube 98 is connected to a handgrip 100 which is fastened in the usual way by means of a mounting ring to the housing 1. The handgrip 100 is made hollow and comprises a dust bag 101, which is arranged freely inside the handgrip. The dust bag extends from bottom to top and is firmly mounted on the central intake opening 102 inside the handgrip, which stands in connection with a second flexible tube 103. This flexible tube leads to a drill foot 104, which may be joined in known fashion with the handgrip through rod 105. Dust produced by drilling can be led through the hollow drill foot 104 and the tube 103 into the dust bag 101, the air stream being engendered by the fan 90 of the electric motor. Figures 16 and 17 show an embodiment in which the hammer and rotary drilling apparatus is provided with two driving motors 2, 2′, whereof the motor 2 serves for the bringing into rotation of the tool spindle 5 by way of the transmission 110. The tool spindle 5 is mounted in a bush 111 which is rotatably held by rolling bearings 112 in the housing 1 of the machine. The bush 111 is provided with the gear wheel 18 which cooperates with the pinion on the shaft of motor 2. The bush 111 moreover accommodates the percussion body 6, such that the end face of the percussion body 6 can come into contact with the end face of the tool spindle 5. The motor 2′ serves for the driving of a percussion body, to which end the motor drives via a first transmission 113 an intermediate shaft 12 which is mounted by means of a rolling bearing 114 in the housing 1. The side of the transmission 113 remote from the intermediate shaft 12 is provided with an eccentric disc 115, the eccentric pin 116 being mounted by means of a rolling bearing 117 in the drive member 118. The drive member has in top view a triangular form (see figure 17) and is so positioned that the top angle of the triangle is disposed towards the percussion body 6. Along each side of the triangle there is mounted an elastic member 9 in the form of a strip spring 119. The fastening of the strip spring 119 to the drive member 118 can take place in arbitrary fashion, for example using screws 120. At the side close to the percussion body 6 the end of each strip spring is similarly fastened to a triangular body 121, of which the form corresponds to that of the drive member 118. The fastening similarly takes place by means of screws 120. The triangular member 121 is provided with a pin 122, onto which a fork shaped end part 123 of percussion member 6 grips rotatably. Also coupled to the pin 122 is a transverse guide member 124, which member is slidably conducted along parallel guide bars 125. The bars are firmly mounted in the housing 1. In this embodiment too the drive member 118 is mounted rotatably around a motor shaft or a shaft cooperating therewith, which drive member so loads a pair of elastic members 119 that on the actuation of the motor 2′ and as a consequence of the eccentric 115, 116 the distance between the members 118 and 121 is repeatedly enlarged and reduced. This causes a flexing of the flexible members 119, which members uncoil against the flanks of the triangular members 118, 121, which results in a non-linear spring characteristic. The percussion body 6, which is held freely slidably in the housing 1, follows the reciprocating motion of the drive member 118 in a delayed manner such that the strip springs 119 are stretched to a greater or lesser extent. The percussion body 6 thereby repeatedly reaches the end face of the tool spindle 5, which can be brought into rotation by the empowerment of motor 2. The above described device can therefore have three functions, namely rotary drilling only, hammering only or a combination of hammer and rotary drilling. In the last case the full power of the two motors can be utilized, which results in a doubling of the power in comparison to the other embodiments.

Claims: Device for driving a drilling and/or percussion tool, provided with a spindle (5) held where necessary rotatably in a housing (1), the one end of said spindle being adapted to fastening the tool piece, the other end being accessible to an oscillating percussion body (6) movable in the housing by means of a guideway (7), a rotatable drive shaft bringing the tool spindle (5) into rotation and/or the percussion body into motion via a transmission, said transmission being provided with means for the conversion of the rotary motion of the drive shaft into an oscillatory motion of a drive member, said member (8,118) being provided with an elastic member (9,119) having a non-linear spring characteristic, said elastic member being coupled (20,21,121) with the percussion body (6), characterized in that the drive member (8,118) is mounted in a wobbling or eccentric way on the drive shaft (3) or a shaft (12) coupled therewith, wherein the elastic member (9,119) is directly connected to the drive member (8,118) and comprises a plate-like member. Device as claimed in claim 1, characterized in that the drive member (8) is mounted at or can be adjusted to an angle deviating from 90 degrees with the centre line of the drive shaft (5,12), the plate (9) being rotatable arranged on the drive member. Device as claimed in claims 1 and 2, characterized in that the coupling means is a tongue (21) fastened to the plate (9), which projects into an aperture (20) made in the percussion body (6). Device as claimed in claim 3, characterized in that the aperture (20) has in the stroke direction a larger dimension than the thickness of the tongue (21). Device as claimed in claim 3, characterized in that the tongue (21) is the end of a meander shaped spring arm (35). Device as claimed in claims 1-5, characterized in that at least one spring plate (26) extending along the elastic body is arranged, the spring constant of which is less than that of the elastic member (9). Device as claimed in any of the previous claims, characterized in that the plate (9) is mounted rotatably on a drive member (8), embodied as a bush-like support on the drive shaft (12). Device as claimed in claim 7, characterized in that the support (8) is mounted tiltably with respect to the axis of said drive shaft (12). Device as claimed in any of previous claims, characterized in that the percussion body (6) is a pin freely movable with respect to the housing (1). Device as claimed in claim 9 , characterized in that the percussion body (6) is held in slide bearings (7) supported by the housing (1). Device as claimed in claim 9, characterized in that the percussion body (6) is suspended in the housing (1) by means of one or more spring strips (46). Device as claimed in claim 11, characterized in that at least one pair of parallel spring strips (46) are arranged. Device as claimed in claim 9, characterized in that the percussion body (6) is accommodated in a blind hole made in the tool spindle (5). Device as claimed in any of the previous claims, characterized in that the motor shaft (3), bearing said drive member (8), has a coupling (49) on the side of the driving motor. Device as claimed in claim 14, characterized in that the coupling in the drive shaft (3) is of the groove and tongue type (48) and is arranged close to a supporting bearing (49). Device as claimed in any of the previous claims, characterized in that a coupling (15) is incorporated between the drive member (8) and the shaft (3,12) carrying said member (8) said coupling being engaged and released independently of the rotation of the drive shaft. Device as claimed in claim 16, characterized in that the coupling (15) can be actuated by means of an axial displacement of the tool spindle (5). Device as claimed in any of the previous claims, characterized in that the tool spindle (5) is provided with a transmission gear wheel (18) freely rotatable with respect thereto, and if necessary a hand-operated coupling (60) is arranged between the tool spindle (5) and said gear wheel (18). Device as claimed in claim 18, characterized in that the coupling (60) is embodied as a friction slip clutch. Device as claimed in claim 16, characterized in that the coupling is a slip clutch and is provided with ball members (60). Device as claimed in any of the previous claims, in which the housing (1) is divided into compartments by means of partitions (91), characterized in that one or more partitions has a passageway (92,95,97) for the passing through of ventilation air, the flow of which is engendered by the blade wheel (90) of the electric motor (2). Device as claimed in claim 21, characterized in that the blade wheel (90) is embodied in twin form. Device as claimed in claim 22, characaterized in that one or more of the intake passageways is suitable for receiving of an air conduit tube (98), optionally provided with a filter. Electric drill device as claimed in claim 21, and provided with a handgrip (100), characterized in that the handgrip (100) is executed hollow and is provided with a dust catching means as filter (101), the handgrip being provided with connection stubs for the fastening of one or more air conduit tubes (98,103). Device a claimed in claim 24, provided with a motor blade wheel and intake and outlet passageways as claimed in claims 18-23, characterized in that an air conduit tube (98) is arranged between the connection stub in the handgrip (100) and the intake passageway (97). Device as claimed in any of the previous claims, characterized in that the tool spindle (5) is provided with a holding device for the tool (G), said holding device is disposed such that the tool (G) comes into direct contact with the end face of the tool spindle (5). Device as claimed in claim 26, characterized in that the holding device is provided with coupling means (79), at one side, for the tool spindle (5) and, at the other side, for the tool (G), which excludes a rotation, but permits an axial displacement. Device as claimed in claim 27, characterized in that the coupling means are formed by roller bodies (79) accommodated in recesses (78), at least some of the recesses has an axial length which is greater than that of the roller bodies.

Inventors: HOUBEN JAN PETER, MOOLENAAR ANTONIE JOHANNES, HOUBEN, JAN PETER, MOOLENAAR, ANTONIE JOHANNES
Applicants: SKIL EUROP BV, SKIL EUROPE B.V.
Application year: 1989
Main classification: B25D16
IPC codes: E21B21, B23B45, B25D17, B25D16, B25D11, B23Q11, B23Q5