EP0560512A1 - Bohrhammer - Google Patents

Bohrhammer Download PDF

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Publication number
EP0560512A1
EP0560512A1 EP93301443A EP93301443A EP0560512A1 EP 0560512 A1 EP0560512 A1 EP 0560512A1 EP 93301443 A EP93301443 A EP 93301443A EP 93301443 A EP93301443 A EP 93301443A EP 0560512 A1 EP0560512 A1 EP 0560512A1
Authority
EP
European Patent Office
Prior art keywords
piston
tool holder
axis
holder axis
rotary hammer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP93301443A
Other languages
English (en)
French (fr)
Other versions
EP0560512B1 (de
Inventor
Michael Stirm
Ulrich Demuth
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.)
Black and Decker Inc
Original Assignee
Black and Decker Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Black and Decker Inc filed Critical Black and Decker Inc
Publication of EP0560512A1 publication Critical patent/EP0560512A1/de
Application granted granted Critical
Publication of EP0560512B1 publication Critical patent/EP0560512B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/005—Adjustable tool components; Adjustable parameters
    • B25D2250/021—Stroke length

Definitions

  • the invention relates to a rotary hammer with a pneumatic hammer mechanism, the ram of which, in order to generate impacts acting on the hammer bit arranged in a tool holder, is moved by a driven reciprocating piston, an overpressure and an under-pressure being built up alternately between the rear surface of the ram and the piston, the paths of the reciprocating movement of ram and piston lying on a common straight line and the hammer bit being held coaxially to the tool holder axis in the tool holder.
  • a driven intermediate shaft arranged parallel to the common straight line of the movement path of ram and piston is provided, and mounted on said intermediate shaft is a swash plate which is connected by a swash plate finger to the rear end of the piston designed as a hollow piston.
  • This structure requires a driven intermediate shaft which, because of its arrangement parallel to the common straight line of the movement paths of ram and piston, results in an enlargement of the dimensions of the rotary hammer housing in peripheral direction and which, because of the necessary bearings, also necessitates a relatively large mechanical outlay.
  • a swash plate drive which has a swash plate arranged coaxial to the common straight line of the reciprocating movement of piston and ram, said swash plate engaging with its rotatably housed outer ring by means of a swash finger attached to the latter with the rotary-driven spindle element, so that in this way, upon rotation of the spindle element, a reciprocating movement of the piston is achieved.
  • This structure also requires numerous bearings and is structurally expensive.
  • a rotary hammer of the type mentioned initially is developed according to the invention in such a way that the piston has an area arranged eccentrically to the tool holder axis, said area being moved along an endless orbit about the tool holder axis when the piston is driven, and that the orbit is inclined to the tool holder axis with one point of the orbit at a minimum and one point of the orbit at a maximum distance from the tool holder.
  • the reciprocating movement of the piston of the hammer mechanism is thus generated because an area of the piston describes a rotary movement about the tool holder axis and moves along an orbit which is inclined to the tool holder axis.
  • This movement along the orbit of the area of the piston lying eccentric to the tool holder axis causes a reciprocating movement of the piston along the common straight line of the movement paths of piston and ram and thus the alternating generation, customary for pneumatic hammer mechanisms, of overpressure and underpressure between piston and ram.
  • the guide tube non-rotatably accommodating the piston can be rotatably driven about the common straight line of the movement path of piston and orbit.
  • the orbit is preferably elliptical, and the tool holder axis passes through the centre of this ellipse.
  • the common straight line of the movement of piston and ram coincides with the tool holder axis
  • the eccentrically arranged area can be a support area, provided at the rear end of the piston and offset laterally relative to the common straight line.
  • the advantage of such a structure is that the piston used to generate the drive forces for the ram and the ram are reciprocated on that axis on which the hammer bit is also held, so that on the one hand a simple structure results and on the other the ram transmits its impact energy precisely in the direction of the longitudinal extension of the hammer bit.
  • the reciprocating movement of the piston is produced by an orbital movement of the support area, i.e. by a rotary movement of the piston about the common straight line of the movement of piston and ram, to which end the support area is moved along the inclined orbit.
  • the support area can be kept engaged, e. g. by means of spring force, with a support part which is inclined to the common straight line and defines the orbit.
  • the support area can have the form of a rearwardly extending finger.
  • the finger can be connected in swivellable and positive manner to the support part, thus producing a defined and uncritical coupling.
  • the common straight line of the movement of ram and piston is inclined to the tool holder axis, and the eccentrically arranged area is formed by the rear end of the piston lying on the common straight line.
  • the movement paths of piston and ram do not coincide with the tool holder axis, but are inclined to it, so that a circular movement of the common straight line about the tool holder axis, i.e. a movement of the common straight line on a cone-envelope line, permits the piston to be reciprocated by guiding its rear end along an inclined orbit.
  • the guide tube which contains the piston and the ram and whose longitudinal axis coincides with the common straight line can for example be rotary-driven about the tool holder axis.
  • the piston is a hollow piston accommodating the ram, its rear end can be kept engaged by means of spring force with an annular support surface defining the orbit.
  • the support surface can be pivotable about a point lying on the tool holder axis between a piston-drive position inclined the tool holder axis and a piston-rest position lying normal to the tool holder axis.
  • the piston stroke can be set easily by changing the connection point of the other end of the piston rod to the support rod between a piston-drive position lying outside the tool holder axis and a piston-rest position lying on the tool holder axis.
  • the rotary hammer shown in Figure 1 has a conventional housing 1 with pistol grip and switch actuator 3, provided in the transition area between pistol grip and upper part of the housing, for the activation of the electric motor 2.
  • a tool holder 10 which is in the form of a chuck and into which a hammer bit 11 is inserted.
  • a threaded socket is provided which is screwed into a connection part 12 which, through engagement of longitudinal grooves 13 with corresponding ribs in the spindle element 16, is held non-rotatably in said spindle element.
  • Extending into the rear end of spindle element 16 is the front section of a guide tube 19 which accommodates, in sealing and axially reciprocatable manner, a hollow piston 22 closed at the rear end, said hollow piston 22 having on its outside axially extending grooves which engage with rib-like projections of the guide tube 19, so that hollow piston 22 and guide tube 19 are not rotatable relative to each other.
  • the hammer bit 11, the tool holder 10, connection part 12, the spindle element 16, the guide tube 19 and the hollow piston 22 lie with their centre axes all on a common axis 50 which forms the tool holder axis.
  • Axially and reciprocatably arranged in known manner in the hollow piston 22 is a ram 25 which is reciprocated, in a manner likewise known for pneumatic hammer mechanisms, by reciprocating movement of the hollow piston and the resultant build-up of an overpressure between the rear end of the hollow piston and the rear end of the ram and subsequent build-up of an underpressure at this point, and thereby transmits impacts to the rear end of the axially reciprocatable anvil 15, which transmits these impacts onto the rear end of the threaded socket of the tool holder 10, from where they reach the hammer bit 11.
  • the hammer bit 11 could of course also extend rearwards through the tool holder and be impinged upon directly by the anvil.
  • the spindle element 16 is rotatably held in the housing 1 by means of a bearing 18, in a manner not shown in more detail, and accordingly the guide tube 19 is also rotatably positioned in the housing 1 by means of a bearing 21.
  • Spindle element 16 and guide tube 19 are rotatable relative to each other.
  • a gear 17 is formed on the rear end section of spindle element 16 and a gear 20 in the central section of guide tube 19, said gears lying immediately adjacent to each other in the assembled state ( Figures 1 and 2).
  • auxiliary shaft 7 Arranged parallel to the centre axis of the gears 17 and 20, and thus parallel to the axis 50, is an auxiliary shaft 7 on which are provided a gear 8 meshing with gear 17 and a gear 9 meshing with gear 20. Gear 9 also meshes with the pinion 6 formed at the outer end of the armature shaft 5, lying parallel to the axis 50, of the electric motor 2.
  • a fan wheel 4 is secured in the usual way to the armature shaft 5 between pinion 6 and the stator of the electric motor 2.
  • the rotation of the gear 20 effects a rotation of the guide tube 19, which, because of the different dimensions of the gears, also results in a relative rotation of tube 19 and spindle element 16.
  • the hollow piston 22 extends into the guide tube 19, and arranged between an annular shoulder 23 formed at the rear end of the hollow piston 22 and the inner race of bearing 21 is a helical spring 26 which exerts an rearwardly directed force on the hollow piston 22.
  • the rear end of the finger 24 engages with a slot 37 of a support part 35 which has a guide pin 36 at its side facing away from the piston 22.
  • the guide pin 36 extends into a bearing 33 which is arranged in a bearing holder 30.
  • the bearing holder 30 is mounted, in a way which is not shown, by means of lateral securing projections 31 pivotable about an axis 32 in the housing 1, the pivot movement being effected by a hand knob 34 provided at the outside of the housing 1.
  • the pivot axis 32 of bearing holder 30 intersects axis 50.
  • the guide pin 36 of support part 35 is also correspondingly inclined to axis 50. If, in this position, the so-called piston-drive position, the guide tube 19 is rotated by rotation of the armature shaft 5 of the electric motor 2, and the hollow piston 22, as a result of engagement of longitudinal grooves provided at its outside with corresponding axial ribs at the inside of guide tube 19, rotates with the latter, the finger 24 describes an elliptical movement about axis 50.
  • hollow piston 22 is reciprocated in axial direction and thus as known from pneumatic hammer mechanisms, produces a reciprocating movement of the ram 25.
  • the stroke of the reciprocating movement of hollow piston 22 depends on the inclination of support part 35 and can be altered by the user, using hand knob 37, by rotation about the pivot axis 32 between a maximum inclination and thus between a maximum stroke and a perpendicular alignment of bearing holder 30 in relation to axis 50 and thus an "axial standstill" of hollow piston 22, the so-called piston-rest position.
  • the user can in this way adjust between combined drill and hammer operation with desired piston stroke and pure drill operation.
  • piston axis 32 intersects axis 50 and that a particularly compact structure results if the centre line extending perpendicular to axis 50 and passing through the swivel connection between finger 24 and support part 35 passes through the point of intersection of pivot axis 32 and axis 50 when the support part 35 is in the piston-rest position.
  • an extension 38 which has a reception aperture 39 located at a distance from axis 32'.
  • a diagrammatically represented rod system 42 which is coupled with a slide element 40, engages in the reception aperture 39.
  • Slide element 40 is held axially displaceable, in a manner not shown, in the housing 1 by means of guide pins 41 extending parallel to axis 50 and engages with the edge area of an arcuate cutout in positive manner with an annular groove 13' which is formed in the connection part 12' attached at the rear end of tool holder 10.
  • bearing holder 30' is pressed by the force of springs, not shown, which act at slide element 40, into a piston-rest position arranged perpendicular to axis 50, so that, although the rotation of the armature shaft 5 of the electric motor 2 effects a rotation of spindle element 16 and thus of tool holder 10 and also a rotation of guide tube 19 and thus of hollow piston 22, the coaxial alignment of guide pin 36' to axis 50 means that no reciprocating movement of hollow piston 22 and thus no drive of ram 25 in axial direction is produced.
  • slide element 40 reverts to its starting position as a result of spring action, as does bearing holder 30', in which position bearing 30' lies coaxial to axis 50, and the hammer mechanism ceases to generate impacts.
  • the embodiment according to Figure 6 shows a modification of the arrangement for the generation of the reciprocating movement of the hollow piston 122, for which purpose an inclined finger 124 is formed at the rear end of hollow piston 122, said finger extending rearwards and its rear, fork-shaped end lying at a distance from the axis 150 on which the hollow piston 122 and the ram 125 reciprocate and which is the common rotation axis of hollow piston 122, guide tube 19 ( Figures 1 to 3), spindle element 16 ( Figures 1 to 3) and tool holder 10 ( Figures 1 to 3).
  • Bearing holder 130 is housed, pivotable about axis 132, in the housing by means of lateral securing projections 131, and a hand knob 134 is provided at bearing holder 130 for the pivoting of same.
  • the support part 135, which is mounted in bearing 133, has a pin 137 which, together with the fork-shaped end of finger 124, forms a swivel connection 143.
  • the pivot axis 132 of bearing holder 130 intersects axis 150 at the point where the longitudinal axis of pin 137 intersects axis 150.
  • pin 137 is in a plane which extends perpendicular to axis 150, rotation of guide tube 119, and thus of the hollow piston 122 non-rotatably arranged in it, about axis 150 is accompanied by an orbital movement of swivel connection 143 about axis 150 on a circular path which lies in a plane which is normal relative to axis 150, i.e. there is a rotary movement of hollow piston 122 without reciprocating movement in the direction of axis 150.
  • bearing holder 130 is pivoted about axis 132 by corresponding pivoting of hand knob 134 and thus brought into a piston-drive position inclined to axis 150
  • pin 137 is pivoted vis-a-vis the fork-shaped outer end of the finger 124 of hollow piston 122, and there results an elliptical orbit, inclined to axis 150, for swivel connection 143 and thus for the fork-shaped end of finger 124.
  • a rotation of guide tube 119 and thus of hollow piston 122 then results in a corresponding reciprocating movement of hollow piston 122 in the direction of axis 150, so that a reciprocating movement of ram 125 is generated and impacts are transmitted onto the rear end of the hammer bit located in the tool holder.
  • a ball 243 is formed at the rear end of the finger 224 which is provided at the rear end of hollow piston 222 and inclined relative to axis 250 and thus to the centre axis of hollow piston 222, said ball engaging with a cylindrical reception recess 237 of support part 235, which support part 235 has, in the area of the cylindrical reception recess 237, a slot for the through passage of finger 224.
  • the arrangement according to Figure 7 allows a support element 235 to be pivoted, in the same way as in the embodiment according to Figure 6, between a piston-rest position and a piston-drive position.
  • the connection section formed by ball 243 and recess 237 travels about a circular path upon rotation of hollow piston 222, said path lying in a plane which is normal relative to axis 250, so that hollow piston 222 is not reciprocated in the direction of axis 250.
  • the centre line extending perpendicular to axis 250 and through ball 243 passes through the intersection point of axis 250 and axis 232.
  • bearing holder 230 In the piston-drive position, bearing holder 230 is pivoted about axis 232 in such a way that the connection area comprising ball 243 and recess 237 moves, upon rotation of hollow piston 222, on an elliptical orbit inclined to axis 250, which results in a reciprocating movement of hollow piston 222 in the direction of axis 250.
  • the common straight line 351 on which the hollow piston 322 and the ram 325, spherical in this case, are reciprocated is inclined to axis 350 which forms the rotation axis of the spindle element 316 and of the tool holder.
  • the guide tube 319 arranged behind spindle element 316 is inclined to the centre and rotation axis 350, but carries a gear 320 which lies coaxial to axis 350 and meshes with gear 309 which is driven by the pinion 306 of the armature shaft 305,
  • the hollow piston 322 which is provided in guide tube 319 and can be reciprocated along the straight line 351 forming the centre axis of guide tube 319, which hollow piston can in this case be rotatable relative to guide tube 319, is rounded at the rear end and is kept in engagement with an inclined support part 335 by a coil spring 326 which is supported on the hand at the rear end of guide tube 319 and on the other hand at an annular shoulder of hollow piston 322.
  • Arranged on this inclined support part is an annular bearing 337 which engages with the rounded rear end of hollow piston 322.
  • spindle elements 316 rotates in the manner described above about axis 350 and thus effects a rotary movement of the tool holder and of the hammer bit contained in it.
  • the rotation of gear 320 about axis 350 results in a circular movement of guide tube 319 about axis 350.
  • the rear end of hollow piston 322 not only orbits about axis 350 with guide tube 319, but is also reciprocated in the direction of the straight line 351 forming the centre axis of hollow piston 322.
  • support part 335 Through pivoting of support part 335 about the point of intersection of centre of the orbit formed by bearing 337 and axis 350, support part 335 can, as indicated, be brought into a perpendicular position relative to axis 350, so that, as explained above in connection with the other embodiments, circular movement of the rear end of hollow piston 322 about axis 350 does not result in a reciprocating movement of hollow piston 322 in the direction of axis 350, i.e. support part 335 is then in the piston-rest position.
  • the embodiment according to Figure 9 is essentially similar to the embodiment according to Figure 8, the reference numerals for identical and corresponding parts being as in the embodiment according to Figures 1 to 3, except the numerals have been increased by 400.
  • ram 425 is designed in the form shown in the embodiment according to Figures 1 to 3, while piston 422 is not a hollow piston but a conventional piston which can be reciprocated axially in guide tube 419 forthe alternate building up of overpressure and underpressure between the front surface of piston 422 and the rear surface of ram 425.
  • a piston rod 445 Attached to the rear end of piston 422 via a universal or ball-and-socket joint 446 is a piston rod 445 whose outer end is swivellably attached to a slide 447 which is mounted on a support rod 435. While the universal joint 446 at the rear end of piston 422 is at a distance from axis 450 in every operating position, the swivel connection between the outer end of piston rod 445 and slide 447 lies on axis 450 in the piston-rest position shown.
  • a rotary drive of gears 417 and 420 thus results in a rotary movement of the spindle element 416 and thus of the tool holder about axis 450 and to a circular movement of guide tube 419 about axis 450.
  • piston 422 is not reciprocated in the direction of axis 451, as the circular orbit of universal joint 446 lies in a plane perpendicular to axis 450.
  • slide 447 is displaced along support rod 435 so that the swivel connection no longer lies on axis 450, so that an elliptical orbit, inclined to axis 450, of the universal joint 446 of piston 422 about axis 450 and thus an impact-generating reciprocating movement of piston 422 is produced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP93301443A 1992-03-07 1993-02-25 Bohrhammer Expired - Lifetime EP0560512B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4207295A DE4207295A1 (de) 1992-03-07 1992-03-07 Bohrhammer
DE4207295 1992-03-07

Publications (2)

Publication Number Publication Date
EP0560512A1 true EP0560512A1 (de) 1993-09-15
EP0560512B1 EP0560512B1 (de) 1997-12-10

Family

ID=6453501

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93301443A Expired - Lifetime EP0560512B1 (de) 1992-03-07 1993-02-25 Bohrhammer

Country Status (2)

Country Link
EP (1) EP0560512B1 (de)
DE (2) DE4207295A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1437200A1 (de) * 2003-01-10 2004-07-14 Makita Corporation Hin- und herbewegbares Kraftwerkzeug
EP1674206A1 (de) * 2004-12-23 2006-06-28 BLACK & DECKER INC. Hammermechanismus für ein Kraftwerkzeug
CN102105272A (zh) * 2008-07-28 2011-06-22 罗伯特·博世有限公司 冲击装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005027764B4 (de) * 2005-06-15 2010-01-07 Eurocopter Deutschland Gmbh Vibrationsgenerierungsvorrichtung
AT522746A1 (de) * 2019-07-10 2021-01-15 Blum Gmbh Julius Möbelbeschlag
US11858100B2 (en) 2021-04-07 2024-01-02 Milwaukee Electric Tool Corporation Impact power tool

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE449947C (de) * 1925-04-20 1927-10-01 Goshikaisha Nakayama Kogyosho Elektrischer Gesteinsbohrhammer
US2024684A (en) * 1934-07-23 1935-12-17 Erfass Karl Axel Ragnar Motor-driven hammer
CH588632A5 (en) * 1975-03-04 1977-06-15 Bosch Gmbh Robert Impact drill with swashplate - has spring loaded pneumatic impact piston reciprocating inside tool drive sleeve
DE3322964A1 (de) * 1983-06-25 1985-01-24 Eugen Lutz GmbH u. Co Maschinenfabrik, 7130 Mühlacker Schlagwerkzeug, insbesondere bohrhammer
DE3505544A1 (de) * 1985-02-18 1986-08-21 Hilti Ag, Schaan Bohrhammer
US4712625A (en) * 1986-01-14 1987-12-15 Willy Kress Drilling and percussion hammer

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE848589C (de) * 1950-10-19 1952-09-04 Licentia Gmbh Vorsatzgetriebe
DE2917475A1 (de) * 1979-04-30 1980-11-13 Hilti Ag Bohr- oder meisselhammer
DE3227707A1 (de) * 1981-07-24 1983-02-10 Black & Decker, Inc., 19711 Newark, Del. Schlagbohrmaschine
DE3634593A1 (de) * 1986-10-10 1988-04-14 Black & Decker Inc Bohrhammer mit einem luftpolsterschlagwerk

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE449947C (de) * 1925-04-20 1927-10-01 Goshikaisha Nakayama Kogyosho Elektrischer Gesteinsbohrhammer
US2024684A (en) * 1934-07-23 1935-12-17 Erfass Karl Axel Ragnar Motor-driven hammer
CH588632A5 (en) * 1975-03-04 1977-06-15 Bosch Gmbh Robert Impact drill with swashplate - has spring loaded pneumatic impact piston reciprocating inside tool drive sleeve
DE3322964A1 (de) * 1983-06-25 1985-01-24 Eugen Lutz GmbH u. Co Maschinenfabrik, 7130 Mühlacker Schlagwerkzeug, insbesondere bohrhammer
DE3505544A1 (de) * 1985-02-18 1986-08-21 Hilti Ag, Schaan Bohrhammer
US4712625A (en) * 1986-01-14 1987-12-15 Willy Kress Drilling and percussion hammer

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1437200A1 (de) * 2003-01-10 2004-07-14 Makita Corporation Hin- und herbewegbares Kraftwerkzeug
US7059425B2 (en) 2003-01-10 2006-06-13 Makita Corporation Reciprocating power tool
EP1674206A1 (de) * 2004-12-23 2006-06-28 BLACK & DECKER INC. Hammermechanismus für ein Kraftwerkzeug
CN102105272A (zh) * 2008-07-28 2011-06-22 罗伯特·博世有限公司 冲击装置

Also Published As

Publication number Publication date
DE69315609T2 (de) 1998-04-02
DE69315609D1 (de) 1998-01-22
EP0560512B1 (de) 1997-12-10
DE4207295A1 (de) 1993-09-09

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