EP0401548A1 - Dispositif à outil de vissage - Google Patents

Dispositif à outil de vissage Download PDF

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Publication number
EP0401548A1
EP0401548A1 EP90108986A EP90108986A EP0401548A1 EP 0401548 A1 EP0401548 A1 EP 0401548A1 EP 90108986 A EP90108986 A EP 90108986A EP 90108986 A EP90108986 A EP 90108986A EP 0401548 A1 EP0401548 A1 EP 0401548A1
Authority
EP
European Patent Office
Prior art keywords
coupling element
machine tool
tool according
screwing machine
clutch
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
EP90108986A
Other languages
German (de)
English (en)
Other versions
EP0401548B1 (fr
Inventor
Wolfgang Schreiber
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.)
C&E Fein GmbH and Co
Original Assignee
C&E Fein GmbH and Co
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 C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP0401548A1 publication Critical patent/EP0401548A1/fr
Application granted granted Critical
Publication of EP0401548B1 publication Critical patent/EP0401548B1/fr
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
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/0064—Means for adjusting screwing depth
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings

Definitions

  • Such a power-driven screwing machine tool is known, for example, from European patent application 85115843.6 and also from DE-PS 36 37 852.
  • the clutch works in such a way that when the screw-in depth defined by the depth stop is reached, the clutch triggers and switches off without chattering.
  • Screwing machine tools of this type are mainly used as construction screwdrivers, since a large number of screws with a constant screwing depth are to be screwed in during dry construction.
  • the screw-in depth switch-off which in the normal case interrupts the torque transmission only when the preset screw-in depth is reached, regardless of the counter torque that occurs, can be switched over to a screw-in torque switch-off, the triggering coupling of the screw-in depth switch-off being used as the torque-limiting element, although the release clutch does not primarily have the function of limiting the torque when the screw-in depth is switched off.
  • the blocking element is advantageously designed such that it can be actuated from outside the housing.
  • the blocking element is inactive in an effective position when the clutch is in the rest position and by moving the clutch from the rest position to the working position can be activated.
  • the blocking element does not initially intervene in the rest position, and it is only when the clutch is moved into the working position that the blocking element is activated at the same time.
  • the elements of the driving clutch can still be freely rotated in the rest position, which can be used to let the blocking element become active in its effective position when the clutch is moved into the working position.
  • the depth stop is an element of the screw-in depth switch-off and is not necessary for the function of the screw-in torque switch-off, it has proven to be advantageous in a preferred embodiment if the depth stop can be brought into an ineffective position.
  • the depth stop is held pluggable on the housing and if the blocking element is ineffective when the depth stop is plugged in and effective when the depth stop is removed Position.
  • a scan to that effect If the depth stop is attached or not, and this scanning is used at the same time for actuating the blocking element, a particularly safe handling solution is achieved.
  • the release clutch in the solution according to the invention is primarily designed to switch off in connection with the screw-in depth shutdown at a certain screw-in depth and not when a limit torque is exceeded, there are particular advantages in the solution according to the invention if an adjusting device is provided for adjusting a release characteristic of the release clutch , so that the release clutch can be adjusted to the desired switch-off characteristic, in particular with the screw-in torque switch-off, via this adjusting device.
  • the coupling elements and the intermediate coupling element are arranged on one axis. It is preferably even provided that the coupling elements and the intermediate coupling element are arranged coaxially to the tool drive shaft, a structurally particularly simple solution providing that the coupling elements and the intermediate coupling element are arranged on the tool drive shaft, but at least then the intermediate coupling element and the second coupling element are displaceable relative to the latter have to be.
  • the driving clutch has at least one footprint, which has an incline to the axis of the coupling elements, which acts on a counter surface when the first coupling element and the intermediate coupling element rotate relative to one another, and the intermediate coupling element in the axial direction from the load-free position shifts to the load position.
  • the axial displacement is triggered by a relative rotation between the first coupling element and the intermediate coupling element, which can be easily achieved in the torque transmission according to the invention when the screw-in depth is switched off.
  • the arrangement of the footprint can be done in any way. So it is conceivable, for example, that a footprint with a corresponding slope is used as the footprint tion surface for a ball is provided as a connecting element between the first coupling element and the intermediate coupling element. But it is also conceivable that the footprint is formed by a backdrop on which a scanning pin slides, the slide track can in the simplest case be an inner edge of a bore on which a pin slides with a much smaller diameter than the bore. The footprint can be realized particularly easily if it is designed as the side edge of a claw.
  • the relative rotation between the first coupling element and the intermediate coupling element is limited by a stop surface which is effective in the load position.
  • the stop surface preferably extends transversely to the footprint. If claws are used as connecting elements between the first coupling element and the intermediate coupling element, the stop surface can be designed such that it is a side surface of the claw that is parallel, in particular, to the axis of the coupling elements.
  • the driving clutch in the load-free position positions the first coupling element and the intermediate coupling element relative to one another, in particular with respect to a relative rotation thereof.
  • a blocking of the two elements can thus be achieved in a simple manner, whereas if the elements of the driving clutch in the load-free position were not defined, this would only be possible with additional aids that position the two elements.
  • This positioning can be achieved particularly easily in terms of construction if the side flanks of successive claws of the intermediate coupling element or of the first coupling element center the claw of the first coupling element or of the intermediate coupling element engaging between them in the defined load-free position.
  • the driving clutch is designed so that it requires an inclined surface to generate the axial displacement of the intermediate coupling element during the transition from the no-load position to the load position
  • the coupling it is necessary for the coupling to function that the intermediate coupling element points in the direction its load-free position tion is spring-loaded, in particular between the second coupling element and the intermediate coupling element, a spring that presses them apart is provided.
  • a further advantageous effect is achieved simultaneously with this spring that the first coupling element is spring-loaded in the direction of a load-free position.
  • the release clutch is formed by cams which are arranged on the intermediate coupling element and the second coupling element and face one another.
  • the axial displacement of the tool drive shaft in the direction of the drive can be limited by a rear stop position.
  • the rear stop position is preferably formed by an axial bearing between the tool drive shaft and the housing, the axial bearing in particular being arranged on an end of the tool drive shaft opposite the screwing tool.
  • one adjusting ring has a sliding surface that extends with an incline to the axis of rotation of the relative rotation, on which the other adjusting ring rests with a supporting surface, wherein the supporting surface itself can also be designed as a sliding surface.
  • the relative rotation can be achieved most simply in that one of the adjusting rings is rotatably mounted on the housing and the other adjusting ring is rotatable.
  • the adjustment device is mounted on the wall between the gear housing section and the motor housing section.
  • FIG. 1 An embodiment of a screwing machine tool according to the invention, shown in FIG. 1, comprises a housing, designated as a whole by 10, in which a drive 12 is held, which comprises an electric motor with a rotor 14, which is seated on a motor shaft 16. A front end of the motor shaft 16 is provided with a drive pinion 18.
  • the tool shaft 24 is in turn rotatable with a middle section 40 adjoining the front section 30 in a bearing sleeve 42 of the housing 10 and is displaceable in the direction of its axis 26.
  • the bearing sleeve 42 is in turn screwed into a cylindrical front part 44 of the housing 10 with an internal thread.
  • a rear section 46 of the tool drive shaft 24 extends toward the drive 12, which section is opposite the central section 40 has a reduced diameter.
  • This rear section 46 40 carries the clutch 22 and is in turn received at its rear end 48 in a radial bearing 50 and is additionally provided with an axial bearing 52 which has a ball 56 held in a rear recess 54 of the tool drive shaft 24, which, however, does not always have the Tool drive shaft 24 is supported on a support surface 58, formed by a metal plate 60, but only when the tool drive shaft is in its rear stop position, as is shown, for example, in FIGS. 6 b and c.
  • the axial bearing 52 and the radial bearing 50 are supported by a wall 62 which divides the housing 10 into a motor housing section 64 and a gear housing section 66 located in front of this motor housing section, into which the motor shaft 16 projects with the drive pinion 16 and which receives the clutch 22.
  • a depth stop designated as a whole can be plugged on, which has a fastening sleeve 70 which fits around the cylindrical front part 44 and which adjoins the screwing tool 34 to form an adjusting sleeve carrier 72, in which one as a whole with 74 designated adjusting sleeve is rotatably and adjustable by a thread 76 in the direction of the axis 26.
  • a front support edge 78 of the depth stop 68 surrounding the screwdriver 38 serves as the stop surface, which ultimately determines a screw-in depth of the screw to be screwed in.
  • the depth stop 68 itself is arranged together with its adjusting sleeve 74 coaxially with the axis 26.
  • the cylindrical front part 44 with its cylindrical outer surface 80 is coaxial with the axis 26.
  • a rear part 82 of the adjusting sleeve 74 opposite the supporting edge 78 is additionally provided with external grooves 84 which run parallel to the axis 26 and into which a ball 88 engages by an O-ring 86 and is resiliently acted upon by the O-ring 86 in order to lock the rotational positions of the adjusting sleeve 74.
  • the entire depth stop 68 can be removed from the housing 10, which is possible in that the fastening sleeve 70 can be pulled off in the direction of the axis 26 to the front via the cylindrical front part.
  • the fastening sleeve 70 is locked in place on the cylindrical front part 44 by an O-ring 92, which partially protrudes over an inner surface 90 of the fastening sleeve 70 and is supported in an annular groove in the inner surface 90 and which has the possibility of being incorporated into a cylindrical surface 80 To engage annular groove 94 and thereby fix the fastening sleeve 70 in the direction of the axis 26.
  • a rear end wall 96 bears against an annular surface 98 of the gear housing section 66 that runs perpendicular to the cylindrical lateral surface 80 and limits it to the rear.
  • the clutch 22 includes in particular a first clutch element 100, an intermediate clutch element 102 and a second clutch element 104, all of which are seated on the rear section 46 of the tool drive shaft 24.
  • the first coupling element 100 is non-rotatably and non-displaceably connected to the tool drive shaft 24 and bears with a rear side 106 against an annular surface 108 of the transition between the rear section 46 and the central section 40.
  • the intermediate coupling element 102 is rotatably and displaceably mounted on the rear section 46 in the axial direction.
  • the second coupling element 104 is also rotatable and axially displaceably mounted on the rear section 46 and arranged on the side of the intermediate coupling element 102 associated with the drive 12.
  • the second coupling element 104 carries the gear 20, which is driven by the drive pinion 18.
  • a spring 110 is arranged between the intermediate coupling element 102 and the second coupling element 104, which acts on the intermediate coupling element 102 in the direction of the first coupling element 100 and the second coupling element 104 in the direction of the drive 12.
  • the rear side 112 of the second coupling element 104 bears against a first adjusting ring 114, which in turn counteracts presses a second adjusting ring 116.
  • Both adjusting rings 114 and 116 form a displacement device 118, which will be described in detail later.
  • the rear adjusting ring 116 forms the radial bearing 50 in that it is held by an annular collar 120 of the wall 62.
  • the second adjusting ring 116 has such an extension in the direction of the axis 26 that the tool drive shaft 24 is always held radially by the second adjusting ring 116 with its rear section 46 in all possible axial displacement positions.
  • the clutch 22 is divided into a driver clutch, formed by the first clutch element 100 and the intermediate clutch element 102, and a release clutch, formed by the intermediate clutch element 102 and the second clutch element 104.
  • both the first coupling element 100 and the intermediate coupling element 102 have claws 122 and 124, which are in engagement with one another.
  • the claws are shaped in such a way that they have an elevation 126 and 128, respectively, which face and lower the intermediate coupling element 102 and the first coupling element 100 End faces 130 and 132 extending right to the axis 26, the end faces 130 and 132 having side edges 134 and 136 extending in the radial direction to the axis 26.
  • side surfaces 138 and 140 run in the direction of the respective element, that is to say the first coupling element 100 and the intermediate coupling element 102, these side surfaces 138, 140 representing partial surfaces of planes of a plane group passing through the axis 26.
  • the claws 122 and 124 terminate in side flanks 142 and 144, which have a pitch angle with respect to the axis 26, that is to say at an angle to the end surfaces 130 and 132 and also at an angle the side surfaces 138 and 140, and thereby merge into a support surface 146 and 148, which is aligned parallel to the respective end surface 130 and 132, respectively.
  • the pitch angles between the side flanks 142 and 144 and the axis 26 are preferably identical.
  • claws 122 and 124 are of identical design. However, identically shaped claws 122, 124 offer advantages in terms of production technology.
  • the triggering clutch is formed between the intermediate clutch element 102 and the second clutch element 104 by cams 150 and 152 which are arranged on sides of the two elements 102, 104 which face one another and which have a cam end face 154 or 156 which is perpendicular to the axis 26 stands and cam flanks 158 and 160 emanating from this cam end face, which also have an incline with respect to the axis 26, that is to say are inclined with respect to the cam end faces 154, 156 (FIG. 5).
  • the intermediate coupling element 102 and the second coupling element 104 have ring surface segments 162 and 164 standing in a plane perpendicular to the axis 26.
  • three cams 150 and 152 are provided on both the intermediate coupling element 102 and on the second coupling element 104, between which the largest possible gaps remain, the gaps being a multiple of these, based on the arc length of the cam end face 154, 156 (FIG. 2 , 5).
  • the clutch 22 now works in the known manner so that by placing the screwdriver 38 on the screw 121, the tool drive shaft and thus the clutch is transferred from the rest position to the working position.
  • the claws 122 and 124 of the first coupling element 100 and the intermediate coupling element 102 are centered relative to one another, that is to say the end faces 130 and 132 lie over the entire surface of the respective opposite bearing surfaces 146 and 148.
  • the intermediate coupling element 102 and the second coupling element 104 are spaced apart by the action of the spring 110 which is greater than the sum of the heights with which the cam end faces 154 and 156 rise above the annular surface segments 162 and 164, respectively, so that the Cams 150 and 152 cannot interlock.
  • the torque transmitted to the intermediate coupling element 102 ceases to exist, so that, due to the action of the spring 110, the intermediate coupling element 102 reverses the relative rotation to the first coupling element 100 that was initially carried out in the working position in that the claws 122 and 124 on side flanks 142 and 144 slide back into the position they have in their starting position.
  • the cam 150 is removed from the cam 152 by an additional amount and thus the clutch 22 rattles prevents which would otherwise occur if the cams 150 and 152 collide.
  • the torque transmission to the screw 121 is also omitted, so that the desired interruption of the screwing process occurs at the screwing depth.
  • the coupling 22 is provided with a coupling ring 170, which is once in an inactive position Pins 172 is held (Fig. 2) so that the clutch 22 can function as previously described.
  • the pins 172 are acted upon by the lower end wall 96 of the fastening sleeve 70 in the plugged-on state and hold the coupling ring 170 in a position in which it encompasses the intermediate coupling element 102 and is also held coaxially to the axis 26 by this, but from the intermediate coupling element 102 in the direction of the second coupling element 104 protrudes, the cams 150 and 152 being arranged such that they lie within the coupling ring 170. Furthermore, the union ring is acted upon in its inactive position by a spring 174 in the direction of its active position.
  • the spring 174 encompasses the coupling ring 170 and is supported on the one hand on the second coupling element 104 and, on the other hand, acts on an annular flange 176 which extends radially outward from the coupling ring 170.
  • the coupling ring 170 is also held in the inactive position by the pins 172 in that: these act on the annular flange 176 against the force of the spring 174.
  • the coupling ring 170 can also be displaced parallel to the axis 26.
  • the first coupling element 100 also has wedges extending radially outwards, which have the same shape as the wedges 188, so that the coupling ring 170, starting from the intermediate coupling element 102, also engages with the wedges 190 in a rotationally fixed manner is feasible.
  • the first coupling element 100 and the intermediate coupling element 102 are displaced in the direction of the drive 12 to ensure that the wedges 190 of the first coupling element 100 slide into the grooves 186 of the coupling ring 170 and thus block a relative rotation of the intermediate coupling element 102 to the first coupling element 100 before the cams 150 of the intermediate coupling element 100 with the cams 152 of the second coupling element 104 in Can engage and thus torque transmission takes place.
  • the position in which the adjusting rings 114, 116 have reached the maximum displacement is shown in FIG. 6b.
  • the maximum displacement is chosen so that the engagement height of the cams 150, 152 is maximum, that is to say essentially corresponds to a height of the cams.
  • the twisting of the adjusting rings 114, 116 relative to one another can take place in that, as shown in FIG. 8, the second adjusting ring 116 is firmly anchored to the wall 62 and the first adjusting ring 114 extends radially to the axis 26 to the outside Extending lever 200, which passes through an opening 202 of the gear housing section 66 and has a handle part 204 lying outside the same.
  • the opening 202 is dimensioned so that a pivoting angle of the lever 200 causes a relative rotation of the adjusting rings 114, 116 from the starting position to the position with maximum displacement.
  • the opening 202 is preferably also provided with latching bumps 203, with which the lever 200 can be locked in different positions.
  • the second adjusting ring 116 is enclosed by an annular bead 216 formed on the wall 62 and is rotatably supported in the wall 62 by this annular bead. From this second adjusting ring 116, on its end face 218 opposite the first adjusting ring 114, a pivot pin 220 protrudes, which passes through the wall 62 in a region 222 lying within the annular bead 216 and projects beyond the wall 62 into the motor housing section 64.
  • the pivot pin 220 is preferably aligned parallel to the axis 26.
  • a slide 224 Arranged in the motor housing section 64 is a slide 224 which extends through it transversely to the axis 26 and which has a recess machined in the form of a receptacle 226 for the pivot pin 220.
  • the pivot pin 220 is arranged such that the slide 224 with the receptacle 226 can be displaced approximately tangentially to the arc segment 230, on which the pivot pin 220 runs from the initial position to the position of the maximum displacement when the adjusting rings 114, 116 are rotated relative to one another.
  • the displacement direction 228 of the slide 224 is preferably parallel to an upper housing surface 232.
  • a locking element in the form of a spring-loaded locking ball 234 is provided in the slide 224, which is pressed by a spring 236 against a locking plate 238, which has locking slots 240 running parallel to one another and transverse to the direction of displacement 228 and is firmly anchored to the wall 62 on the side facing the slider 224, the slider 224 resting against the locking plate 238 with a front side 242 and the locking ball 234 projecting beyond the front side 242.
  • the slide 224 has two handle parts 244 and 246 projecting on opposite sides of the housing, the slide being dimensioned such that in the initial position of the adjusting rings 114, 116 one handle part 244 and in the position of maximum displacement the other handle part 246 neighboring areas of the housing 10 laterally protrudes.
  • a particularly favorable exemplary embodiment is advantageously designed such that the slide 224 does not protrude over an overall contour of the housing in any position.
  • the sliding device 118 can thus be adjusted by the slider 224, so that the tripping characteristic of the tripping clutch between the intermediate coupling element 102 and the second coupling element 104 can be adjusted with an effective coupling ring 170, and thus the screwing machine tool according to the invention, in addition to a screw-in depth switch-off with depth stop, which triggers without rattling, a torque switch-off with adjustable trigger characteristic.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
EP90108986A 1989-06-03 1990-05-12 Dispositif à outil de vissage Expired - Lifetime EP0401548B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3918227 1989-06-03
DE3918227A DE3918227C1 (fr) 1989-06-03 1989-06-03

Publications (2)

Publication Number Publication Date
EP0401548A1 true EP0401548A1 (fr) 1990-12-12
EP0401548B1 EP0401548B1 (fr) 1993-08-11

Family

ID=6382052

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90108986A Expired - Lifetime EP0401548B1 (fr) 1989-06-03 1990-05-12 Dispositif à outil de vissage

Country Status (4)

Country Link
US (1) US5094133A (fr)
EP (1) EP0401548B1 (fr)
JP (1) JPH085016B2 (fr)
DE (2) DE3918227C1 (fr)

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Also Published As

Publication number Publication date
JPH0386482A (ja) 1991-04-11
US5094133A (en) 1992-03-10
DE3918227C1 (fr) 1990-11-15
EP0401548B1 (fr) 1993-08-11
DE59002271D1 (de) 1993-09-16
JPH085016B2 (ja) 1996-01-24

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