EP0051923A1 - Tragbare Bohrmaschine - Google Patents

Tragbare Bohrmaschine Download PDF

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Publication number
EP0051923A1
EP0051923A1 EP81304672A EP81304672A EP0051923A1 EP 0051923 A1 EP0051923 A1 EP 0051923A1 EP 81304672 A EP81304672 A EP 81304672A EP 81304672 A EP81304672 A EP 81304672A EP 0051923 A1 EP0051923 A1 EP 0051923A1
Authority
EP
European Patent Office
Prior art keywords
anvil member
fixed
shaft
ring
housing
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
EP81304672A
Other languages
English (en)
French (fr)
Other versions
EP0051923B1 (de
Inventor
Leslie Walter Ford
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.)
Kango Wolf Power Tools Ltd
Original Assignee
Kango Wolf Power Tools Ltd
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 Kango Wolf Power Tools Ltd filed Critical Kango Wolf Power Tools Ltd
Publication of EP0051923A1 publication Critical patent/EP0051923A1/de
Application granted granted Critical
Publication of EP0051923B1 publication Critical patent/EP0051923B1/de
Expired 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
    • B25D11/06—Means for driving the impulse member
    • B25D11/10—Means for driving the impulse member comprising a cam mechanism
    • B25D11/102—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool
    • B25D11/106—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool cam member and cam follower having the same shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/062—Cam-actuated impulse-driving mechanisms
    • B25D2211/064—Axial cams, e.g. two camming surfaces coaxial with drill spindle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/062—Cam-actuated impulse-driving mechanisms
    • B25D2211/067—Cam-actuated impulse-driving mechanisms wherein the cams are involved in a progressive mutual engagement with increasing pressure of the tool to the working surface

Definitions

  • This invention relates to rotary/ percussive portable, power-operated drills, that is to say drills which can be operated with percussive action in addition to the normal rotary action when required, e.g. for drilling masonry.
  • the percussive action is produced by co-operation between a ring of axially facing teeth formed on a member fixed to the main driving shaft and a similar ring of teeth on an annular member which is held against rotation.
  • the member which is held against rotation is in the form of a ring which is fixed to the housing of the drill.
  • the co-operating ring is spring loaded so as to be capable of movement in an axial direction, but being prevented from rotation under the frictional torque produced by co-operation between the two sets of teeth.
  • the ring needs to have considerable inertia in order to ensure that a large proportion of the percussive movement is transmitted to the driving shaft and hence to the bit of the drill.
  • the ring thus takes the form of a spring-loaded anvil member which absorbs a large part of the vibration which would otherwise be transmitted to the user, but ensures that adequate percussive action is transmitted to the bit of the drill.
  • this anvil member must be so designed as to prevent rotation while at the same time not impeding the axial movement.
  • mount the anvil member by means of ball bearings located in axially extending grooves in the anvil member and in the inner surface of the housing of the drill respectively.
  • the anvil member is mounted to yield in an axial direction by means of a coupling comprising a number of axially extending springs surrounding and guided by pins located in corresponding counter bores, one part of the coupling being fixed to the housing and the other to the anvil member, whereby to prevent rotation of the latter.
  • the pins are fixed to the housing of the drill and the counter bores are formed in the anvil member, since this saves space by avoiding the need for a separate part of the housing which is long enough to accommodate the counter bores.
  • the housing of the drill is shown as 1 and supports a main driving shaft 2, of which the part above the centre line shown as 2A is shown in a longitudinal position corresponding to disengagement of a percussion mechanism indicated generally as 3,while the part 2B below the centre line is shown in a longitudinal position corresponding to engagement of the percussion mechanism 3.
  • the electric driving motor and the reduction gearing are not illustrated, but the gearing terminates in a pair of gear wheels 4 and 5 which are splined to the shaft 2 so as to permit sliding motion of the shaft between the positions 2A and 2B.
  • the shaft 2 rotates in a pair of bearings, that at the rear end shown as 7 permitting sliding movement of the shaft as illustrated and that at the forward end shown as 8, being a thrust bearing which enables the longitudinal position of the shaft to be adjusted.
  • annular member 9 formed with a grip ring 10 has a helical end face of which the highest point is shown as 12A and the lowest point as 12B. This co-operates with a complementary helical end face on a fixed ring 13 so that when the member 9 is in the angular position illustrated above the centre line, the member is forced to the left and when in the position below the centre line it moves to the right.
  • a helical compression spring 15 enclosed by a cap member 16 acts on the thrust bearing 8 to force it against a shoulder 14 on the member 9. Operating pressure on the drill bit applied to the shaft 2 pushes the cap 16 to the right until the cap engages the bearing 8. When in the position illustrated above the centre line this movement is not sufficient to engage the percussion mechanism 3 and a purely rotary motion is applied to the shaft. When in the position below the centre line, however, the percussion mechanism is engaged and a percussive action is superimposed on the rotary motion as will now be described.
  • the percussion mechanism 3 includes a ring 21 which is fixed to the shaft 2 and turns in a bearing 22 fixed within a liner 23 within the housing 1.
  • the right hand end face of the ring 21 is formed with a set of teeth 25, the configuration of which is best seen from the elevational view below the centre line.
  • a set of corresponding teeth 26 is formed on the end face of an annular anvil member 28 which forms a relatively loose running fit both with the shaft 2 and with the interior of the liner 23.
  • the anvil member 28 is coupled to the liner 23 and hence to the housing 1 by three pins 30 located at intervals of 120° around the shaft 2.
  • the three pins 30 are supported by a ring 31, passing through corresponding holes in the ring 31 and into holes in the liner 23.
  • each pin 30 is formed with an enlargement 33 and the portion of each pin extending to the left beyond the enlargement 33 forms a loose guide for a compression spring 35 located within a counter bore 36 formed in the anvil member 28.
  • the effect of the three springs 35 is to bias the anvil member 28 to the left into contact with a circlip 38 which is spaced from the bearing 22 by a ring 39.
  • the main shaft when it is in the position 2A, it can rotate freely without affecting the anvil member 28.
  • rotation of the shaft 2 is accompanied by a percussive action as successive teeth ride over one another and then fall into the adjacent recesses. This motion is transmitted to the shaft 2 which is intermittently forced to the left against the effect of the spring 15, but vibration which would otherwise be transmitted to the housing 1 of the drill is absorbed by movement to the right of the anvil member 28 against the effect of the springs35.
  • the anvil member 28 it is necessary for the anvil member 28 to have appreciable mass and hence corresponding inertia since otherwise a large proportion of the percussive action generated would be absorbed by the anvil member rather than being transmitted to the main shaft and hence to the bit. As it is, a major proportion of the percussive action is transmitted to the shaft and all or virtually all of the remainder is absorbed by the anvil member 28, thus avoiding discomfort to the user.
  • anvil member 28 Since the anvil member 28 is a slack fit both on the shaft 2 and within the liner 23, there is no restraint on its axial movement. The reaction between the sets of teeth 25 and 26, however, also generates a frictional torque and it is found that this is resisted by the combination of the pins 30 and the springs 35 within their counter bores 36 without the generation of excessive heat and without the need for any excessive accuracy in machining the parts in question.
EP81304672A 1980-11-11 1981-10-08 Tragbare Bohrmaschine Expired EP0051923B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8036205 1980-11-11
GB8036205A GB2086791B (en) 1980-11-11 1980-11-11 Portable power-operated drill

Publications (2)

Publication Number Publication Date
EP0051923A1 true EP0051923A1 (de) 1982-05-19
EP0051923B1 EP0051923B1 (de) 1985-02-06

Family

ID=10517238

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81304672A Expired EP0051923B1 (de) 1980-11-11 1981-10-08 Tragbare Bohrmaschine

Country Status (3)

Country Link
EP (1) EP0051923B1 (de)
DE (1) DE3168814D1 (de)
GB (1) GB2086791B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0463416A1 (de) * 1990-06-26 1992-01-02 Robert Bosch Gmbh Elektrische Schlagbohrmaschine
EP1834737A1 (de) * 2006-03-18 2007-09-19 Metabowerke GmbH Elektrohandwerkzeuggerät

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2121716B (en) * 1982-06-11 1985-07-31 Coal Ind Hydraulic reciprocating tools
DE3603672A1 (de) * 1986-02-06 1987-08-13 Dischler Helmut Schaltbare und selbsttaetig abschaltbare ueberlastkupplung, insbesondere fuer handwerkzeuge

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB747255A (en) * 1951-11-23 1956-03-28 Wilhelm Lichtblau Rotary boring machines
GB847888A (en) * 1957-07-20 1960-09-14 Friedrich Muthmann Electrically driven percussion drill, particularly for drilling rock, earth and synthetic substances
GB981492A (en) * 1962-12-12 1965-01-27 Bosch Gmbh Robert Improvements in percussion drills
US3433082A (en) * 1967-09-20 1969-03-18 Black & Decker Mfg Co Transmission and selector mechanism for alternate hammer and hammerdrill power tool
GB1366572A (en) * 1973-03-12 1974-09-11 Wolf Electric Tools Ltd Portable drills
US3867988A (en) * 1973-02-02 1975-02-25 Rockwell International Corp Power tools
FR2264634A1 (en) * 1974-03-18 1975-10-17 Bosch Gmbh Robert Percussive drilling machine - has spring loaded gear of drilling spindle percussively moved by ratchet teeth of axially stationary gear

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB747255A (en) * 1951-11-23 1956-03-28 Wilhelm Lichtblau Rotary boring machines
GB847888A (en) * 1957-07-20 1960-09-14 Friedrich Muthmann Electrically driven percussion drill, particularly for drilling rock, earth and synthetic substances
GB981492A (en) * 1962-12-12 1965-01-27 Bosch Gmbh Robert Improvements in percussion drills
US3433082A (en) * 1967-09-20 1969-03-18 Black & Decker Mfg Co Transmission and selector mechanism for alternate hammer and hammerdrill power tool
US3867988A (en) * 1973-02-02 1975-02-25 Rockwell International Corp Power tools
GB1366572A (en) * 1973-03-12 1974-09-11 Wolf Electric Tools Ltd Portable drills
FR2264634A1 (en) * 1974-03-18 1975-10-17 Bosch Gmbh Robert Percussive drilling machine - has spring loaded gear of drilling spindle percussively moved by ratchet teeth of axially stationary gear

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0463416A1 (de) * 1990-06-26 1992-01-02 Robert Bosch Gmbh Elektrische Schlagbohrmaschine
EP1834737A1 (de) * 2006-03-18 2007-09-19 Metabowerke GmbH Elektrohandwerkzeuggerät

Also Published As

Publication number Publication date
GB2086791A (en) 1982-05-19
GB2086791B (en) 1984-05-31
DE3168814D1 (en) 1985-03-21
EP0051923B1 (de) 1985-02-06

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