EP0411483B1 - Schrauber - Google Patents

Schrauber Download PDF

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Publication number
EP0411483B1
EP0411483B1 EP90114415A EP90114415A EP0411483B1 EP 0411483 B1 EP0411483 B1 EP 0411483B1 EP 90114415 A EP90114415 A EP 90114415A EP 90114415 A EP90114415 A EP 90114415A EP 0411483 B1 EP0411483 B1 EP 0411483B1
Authority
EP
European Patent Office
Prior art keywords
screwdriver
shaft
balls
locking
control
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.)
Expired - Lifetime
Application number
EP90114415A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0411483A1 (de
Inventor
Erwin Pfab
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.)
Deprag Schulz GmbH u Co
Original Assignee
Deprag Schulz GmbH u 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 Deprag Schulz GmbH u Co filed Critical Deprag Schulz GmbH u Co
Publication of EP0411483A1 publication Critical patent/EP0411483A1/de
Application granted granted Critical
Publication of EP0411483B1 publication Critical patent/EP0411483B1/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
    • 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
    • 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
    • B25B23/145—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers

Definitions

  • the invention relates to a screwdriver with the features of the preamble of claim 1, cf. DD-A-15 96 16.
  • the button mentioned therein is located next to the screw blade. It stands at a distance beyond the end of the screw blade, bumps against the workpiece surface after the self-tapping screw thread and before tightening, is pushed back by the workpiece contact with further tightening, switches the locking clutch and thus sets the torque clutch in function to limit the torque.
  • the torque clutch is activated during the entire screwing process.
  • the screw-in torque required for the normal screwing-in process for non-thread-forming screws is generally smaller than the tightening torque set on the torque coupling for tightening the screw.
  • these screwdrivers are often not suitable for making screw connections with thread-forming screws. In these cases, the torque to tighten the screw is often greater than the tightening torque when tightening the screw.
  • Such applications occur, for example, in plastic or sheet metal screw connections with self-tapping screws. Special constructions, such as those described in DE-A-28 40 140 or DE-A-30 15 423, have been used for such applications. With these known screwdriver designs, however, it is necessary to bridge the set cut-off torque by hand or after the screwdriver has been switched off beforehand.
  • a screw attachment with torque limitation according to DD-A 159 616, in which an automatic activation of a torque clutch only takes place when the threaded screw is tightened, depending on the distance of the button from the workpiece surface.
  • the torque clutch is locked by a locking ball, either by being supported by a shaft against an output-side clutch half or when tightening the screw is transferred to a recess in the shaft, the output side coupling half being released in the axial direction towards the screwdriver end.
  • This has the disadvantage that the disengagement force is transmitted directly to the button via the coupling half on the output side and the locking balls.
  • the button If the button reaches the workpiece surface, it must move the locking ball against the disengaging force of the output-side coupling half into a position in which the balls are received by the puncture of the shaft. This releases the coupling half on the output side in the axial direction. A high level of wear occurs on the clutch output half. A safe switching function is not guaranteed. In particular, it is not ensured that the pushbutton reliably triggers the switchover process and sets the torque clutch in operation when it hits the workpiece. In the event of a failure of the switchover device, the screw head must be torn off and / or the component deformed.
  • the invention has for its object to provide a screwdriver of the type mentioned in such a way that it can be handled like a conventional torque-disconnectable screwdriver.
  • the screwdriver should apply a large torque when screwing in the screw and automatically realize a previously adjustable switch-off torque when tightening the screw.
  • the connection of the torque clutch should be guaranteed safely.
  • the screwdriver should meet robust industrial requirements and be low-maintenance. A separate handle for switching over from the high screwing torque to the generally lower tightening or switch-off torque should not be necessary.
  • a motor shaft and a screwdriver shaft are rotatably mounted in a screwdriver housing.
  • a torque coupling is installed between the motor shaft and the screwdriver shaft.
  • Means for locking the torque clutch are arranged in the screwdriver shaft. These are referred to as a locking clutch.
  • the means for locking the torque clutch are brought by a likewise axially mounted and displaceable in this direction button depending on the distance from the workpiece surface in a position that either Torque clutch locks to rigid transmission of the engine torque or the torque clutch operates.
  • the locking clutch is constructed so that the button including a sliding sleeve is movably mounted in the axial direction.
  • a radially displaceable second control element corresponds to the sliding sleeve.
  • This control member preferably consists of two control balls mounted radially displaceably in a bore of the screwdriver shaft.
  • An axially displaceable locking pin which is mounted in the screwdriver shaft, corresponds to the control balls. This pin presses the control balls radially outwards against the inner diameter of the sliding sleeve.
  • the locking pin is seen from the control balls in the direction of the motor shaft axially in the screwdriver shaft. At this end, the locking pin corresponds to the first control element, the locking balls.
  • this second control element is constructed analogously to the first control element. The locking balls are acted upon radially outwards by the locking pin and pressed against the circumference of an output-side bore of a clutch output half.
  • the position of the radial guides of the control members (through holes in the screwdriver shaft), the geometry of the locking pin, the geometry of the inner diameter of the sliding sleeve, the geometry of the control members (control balls, locking balls) and the geometry of the output-side bore of the clutch output half are determined so that in each Switch position a largely backlash-free interaction of these parts takes place.
  • the locking pin can be shaped differently at its ends.
  • the ends of the locking pin must ensure that the axial movements of the control balls or the locking balls are effectively transferred into an axial movement of the locking pin with little loss.
  • the locking pin is a cylindrical pin, the cylinder ends of which correspond to a guide ball, which in turn correspond to the control members.
  • the ends of the locking pin are outwardly tapering frustum or cone ends, which are acted upon by the control members.
  • a cylinder pin is preferably used as the locking pin, on the cylinder cover surfaces of which in each case there is a respective guide ball which is guided axially in the screwdriver shaft and in one case corresponds to the control balls and in the other case to the locking balls.
  • the locking pin can also be implemented as a series of balls.
  • Springs cause this arrangement to rest.
  • a 'compression spring is supported with one end against the screwdriver shaft. With its other end, it presses the sliding sleeve and consequently the button into its rest position against a stop on the housing.
  • a helical compression spring acts with one end via an annular flange against the screwdriver shaft, towards the motor shaft against the clutch output half. The preload of this helical compression spring determines the torque that acts when the torque clutch is disengaged and consequently the tightening torque of the screw.
  • the sliding sleeve is moved towards the motor shaft.
  • the control balls can move radially outwards. This allows the locking pin to move towards the screwdriver end and the locking balls can move radially inwards.
  • the clutch output half can now move freely in the axial direction if the tightening torque on the fastening screw is greater than the disengaging torque that is determined by the helical compression spring.
  • the locking coupling By dividing the locking coupling into a control part (control balls, sliding sleeve) and a locking part (control balls, clutch output half), connected by the locking pin, a safe function of the screwdriver is guaranteed.
  • the torque clutch is effective when the fastening screw is tightened.
  • standard parts control balls, locking balls, guide balls and cylindrical pin
  • the large torques which may occur when the screw is screwed in and which press the coupling output half towards the screwdriver end in its disengaged position are absorbed comparatively cheaply by the locking balls and transmitted to the screwdriver shaft. The button is not affected.
  • the effective length of the button can be adjusted by a screw connection between the probe tube and the screw sleeve.
  • the tubular design of the button in the area surrounding the screw blade also offers a particular advantage, namely, if necessary, a guiding and holding function that facilitates the insertion of the screw blade into the slot or cross recess of the screw head, and also the secure insertion of the screw previously fixed on the screwdriver blade favored in the screw hole on the workpiece.
  • annular flange is screwed onto a thread of the screwdriver shaft.
  • It is the adjustable abutment for a helical spring acting axially in the direction of the motor shaft and surrounding the screwdriver shaft, which is supported at one end on the ring flange and at the other end against the drive coupling half.
  • the screwdriver shaft is the abutment for a spring, which is supported with its other end on the motor shaft-side end of the button and presses the button in the output direction.
  • the spring has its abutment in a recess in the screwdriver shaft, which is in the direction of the screwdriver end in front of the thread of the ring flange or has the same effect located on the screw-side surface of the ring flange.
  • the screw connection of the ring flange to the shaft is self-locking. It is used to set the shutdown torque of the torque clutch
  • the screwdriver shaft is supported at its output end in a bearing sleeve of the screwdriver housing.
  • the pins of the button are guided in bores in the bearing sleeve in the axial direction, the pins being limited in their axial mobility by a guide. Due to this mounting, the button can only be moved in the axial direction and is effectively decoupled from the rotary movement of the screwdriver shaft. It is particularly advantageous to use simple geometric parts and parts that are available as standard parts to minimize the manufacturing effort. Due to the structural separation of the torque coupling from the locking coupling, the parts can be dimensioned according to their functional task.
  • the structure of the locking coupling according to the invention enables a screwdriver structure with a comparatively small diameter of the screwdriver housing. Due to the function of the locking balls and the control balls and the decoupling force of the clutch output half acting in the direction of the screw end, which is mainly transmitted to the screwdriver shaft, the button itself is subjected to only slight forces, which leads to a high reliability of the screwdriver.
  • the torque screwdriver is a pneumatic screwdriver, although the subject matter of the invention can also be used analogously in the case of torque screwdrivers driven by an electric motor or other motor.
  • the screwdriver shaft 2 is rotatably mounted in the screwdriver housing 1. It is driven by the motor shaft 3, which in turn is driven by the compressed air motor, not shown.
  • the motor shaft 3 is also rotatably mounted in the screw housing 1, specifically by means of the ball bearing 4.
  • the torque transmission from the motor shaft 3 to the screw shaft 2 takes place via the one designated overall by 5 Torque clutch.
  • the torque clutch 5 is in the inactive or screwed position of the screw drive shown in FIGS.
  • the various switching states of the torque clutch are controlled by a pushbutton 37 through the locking clutch 6.
  • the inactivation state of the torque clutch 5 shown in FIG. 1 is maintained or controlled by the locking clutch 6 integrated in the screwdriver shaft 2 and upstream of the torque clutch 5 in the direction of the screw end 7.
  • the locking clutch 6 consists of the locking pin 28, the locking balls 31, the control balls 32, and the guide balls 29, 30, in cooperation with the clutch output half 14 and the sliding sleeve 38.
  • the screwdriver shaft 2 contains a conventional hexagon socket opening 8 with a ball detent 9 for captively inserting the screw blade 10.
  • the structural design of the torque clutch 5 corresponds essentially to that according to DE-A-28 32 565, there Fig. 1-3: Its drive half 11 facing the motor shaft 3 engages with its clutch claws 12 in corresponding counterclaws 13 of the output clutch half 14 in a form-fitting manner.
  • the output coupling half 14 is mounted on the screwdriver shaft 2 so as to be displaceable in the axial direction 15.
  • the output coupling half 14 In the direction of the screw end 7 - namely in the separating direction leading out of the mutual engagement of the coupling claws 12, 13 - the output coupling half 14 is supported via the helical compression spring 16 on the ring flange 17 which can be screwed onto the screwdriver shaft 2 - namely on this in the axial direction 15.
  • the ring flange 17 is thus displaceable and lockable to change the pretension of the spring 16 in the axial direction 15 on the screwdriver shaft 2. This adjustability serves to change the target torque, that is to say the switch-off or tightening torque of the torque clutch 5.
  • a plurality of pockets 18 for inserting balls 19 are arranged in the annular space surrounded by the sleeve-like output coupling half 14.
  • One of the number of balls 19 is in the surface of the screwdriver shaft 2 corresponding number of helical grooves 20 are introduced, in which the balls 19 are guided.
  • the individual grooves 20 extend only over part of the circumference of the screwdriver shaft 2, for example only over an angular range of approximately 100 °.
  • the grooves 20 provide a guide for the axial displacement of the output coupling half 14 via the balls 19 such that the output coupling half 14 simultaneously performs a rotational movement with respect to the screwdriver shaft 2 in the event of an axial displacement in the direction of the screw end 7.
  • the balls 19 also produce a torque connection between the output clutch half 14 and the screwdriver shaft 2.
  • the end of the sleeve-like output coupling half 14 facing the screw end 7 is designed as a stop flange 21.
  • the stop flange 21 is at least partially chamfered and lies with this chamfer on the conical tip 23 protruding in the radial direction 22 from the screwdriver shaft 2 of the switching bolt 24 guided in the radial direction 22 within the screwdriver shaft 2.
  • the switching pin 24 is supported with its bottom end opposite the cone tip 23 on a helical compression spring 25, which in turn is supported in the axial direction on a collar of the output clutch half 14.
  • the switching pin 24 is provided on its side facing the motor shaft 3 with a recess 26 into which, with a corresponding overlap position, the switching rod 27, which controls the compressed air supply to the drive motor and is displaceably mounted coaxially with the screwdriver shaft 2 and motor shaft 3, can be inserted with its end facing the screw end 7.
  • the shift rod 27 is permanently under a pushing it in the direction of the screw end 7, exerted by the compressed air supply to the compressed air motor, so that when the said overlap position of the recess 26 with the shift rod 27 is automatically displaced in the direction of the screw end 7, thereby penetrates into the recess 26 and thus causes engine shutdown and braking.
  • the locking coupling 6 contains an axially displaceably mounted locking pin 28 in the screwdriver shaft 2, which is arranged coaxially with it. It is expediently designed as a cylindrical pin in FIGS. 1 to 3.
  • the cylinder ends correspond to the guide balls 29, 30, which in turn correspond to the blocking balls 31 or the control balls 32.
  • the locking pin 28 can also be advantageously formed by a series of balls guided in the screwdriver shaft (not shown).
  • the locking pin 28 has conical ends tapering outwards on both sides, which take over the function of the guide balls 29, 30.
  • the cone ends are control inclined surfaces which correspond to the locking balls 31 and the control balls 32.
  • the locking balls 31 and the control balls 32 are the control members which are each guided radially in a radial through bore 35, 36 in the screwdriver shaft 2.
  • Each radial through bore 35, 36 is assigned two control balls 32 or two locking balls 31 such that each guide ball 29, 30 is acted upon on both sides by a locking ball 31 or control ball 32, respectively.
  • the radial through bores 35, 36 are at a distance from one another in the axial direction 15, which is matched to the axial length of the locking pin 28. The vote is made so that the locking balls 31 or control balls 32 can be transferred to a radial inner position only on one of the two guide balls 29, 30, in which they do not protrude from their radial through holes 35 or 36 beyond the diameter of the screwdriver shaft 2 .
  • the locking balls 31 pressed outward from the radial through bore 35 in the radial direction 22 make any axial Possibility of displacement of the clutch output half 14 in the axial direction 15 against the pressure of the helical compression spring 16 prevented. 2, the locking balls 31 inactivate the torque clutch 5, which thus forms a rigid coupling between the motor shaft 3 and screwdriver shaft 2 in this locking position.
  • the button 37 consists of the sliding sleeve 38, pins 40, the screw sleeve 41 and the sensing tube 43.
  • the button 37 surrounds the screwing shaft 2 with a sliding sleeve 38, that in the rest position shown in FIG. 1 with a radial constriction region 39 acts upon the control balls 32 radially and holds them in their radial inner position.
  • the radial constriction region 39 forms the motor-side ring region of the sliding sleeve 38.
  • the constriction region 39 of the sliding sleeve 38 simultaneously forms the guide ring surface for longitudinal displacement in the axial direction 15 on the circumference of the screwdriver shaft 2.
  • the sliding sleeve 38 On its side facing the screw end 7, the sliding sleeve 38 is acted upon by pins 40 which are displaceable in the axial direction 15 in the screw housing and which have the function of thrust drive transmission members. They establish the drive connection between the screw sleeve 41 and the sliding sleeve 38.
  • the storage of the pins 40 in the bearing bush 50 ensures a safe decoupling of the rotary movement of the screwdriver shaft 2 from the button 37, which must not rotate in order not to damage the surface of the workpiece.
  • the pins 40 are limited in their axial mobility by a guide 51. This prevents the pins 40 from falling out when the screw housing 1 is dismantled.
  • the pushbutton 37 also contains an end of the housing 1, which faces the screw end 7 and is displaceable in a longitudinally displaceable manner. This screw connection is secured against unintentional twisting by self-locking or by countering. The screwability serves to change the effective length of the button 37.
  • the screw-side end of the probe tube 43 has a diameter surrounding the head of the fastening screw 44 with a ring spacing.
  • the sliding sleeve 38 of the button 37 is acted upon from the side of the motor shaft 3 by a compression spring 45 which is supported on the screwdriver shaft 2.
  • the operation of the screwdriver is described starting from the rest position of the screwdriver shown in FIG. 1: In this position the motor drive is interrupted (rest position). The button 37 is in its foremost position in the direction of the fastening screw 44 by the compression spring 45. The locking clutch 6 is switched so that the torque clutch 5 is kept out of function.
  • a spring 33 which is supported on the motor shaft 3 presses the screwdriver shaft 2 with the torque coupling 5, the locking coupling 6 and the screw blade 10 attached thereto in the direction of the fastening screw 44 against a stop 34 of the bearing sleeve 50 fixedly connected to the screwdriver housing 1.
  • a shift rod 27 is axially displaceably mounted in the motor shaft 3. In the rest position of the screwdriver, the switching rod 27 acts in its foremost position in the direction of the fastening screw 44, against a stop 53.
  • Fig. 2 shows the next position of a work cycle of the screwdriver.
  • the screw blade 10 is placed on the fastening screw 44.
  • the screwing blade 10 and the screwdriver shaft 2 are shifted towards the motor by slight pressure until they rest against the motor shaft 3.
  • the shift bolt 24, which is mounted in the screwdriver shaft 2 so as to be radially displaceable, displaces the shift rod 27 in the direction of the motor with its scope effective in this position.
  • the shift rod 27 acts on a switch and thereby puts the engine into operation.
  • the feeler tube 43 is screwed so far into the internal thread 42 of the screw sleeve 41 of the button 37 that, in the screwed-in position, its end 46 extends at a distance 47 beyond the end of the screw blade 10.
  • the protruding or effective length of the sensor button is chosen so that the front end 46 of the probe tube 43 over most of the initial Screwing in the screw 44 is out of contact with the workpiece surface 48.
  • the probe tube 43 strikes the workpiece surface 48 with its end 46 (FIG. 3). With the further screwing-in movement, the probe tube 43 is displaced in the axial direction 15 to the side of the motor shaft 3. This displacement movement is transmitted unchanged to the sliding sleeve 38 via the screw sleeve 41 and the pins 40. The sliding sleeve 38 is thereby moved against the pressure of the spring 45, namely under compression thereof, from the overlapping position of its radial constriction region 39 with the control balls 32 in the direction of the motor shaft 3. The free annular space 49 left between the screw-side ring area of the sliding sleeve 38 and the circumference of the screwdriver shaft 2 allows the control balls 32 to be moved radially outward from the radial through bore 36.
  • the shifting pin 24 is displaced radially in the axial direction by the axial displacement of the clutch output half 14. In this position, the shift rod 27 is pushed into the recess 26 of the shift bolt 24 in the direction of the fastening screw 44 against the stop 53. The engine is switched off.
  • the spring 33 presses the screwdriver shaft 2 against the stop 34 of the screwdriver housing 1.
  • the screwdriver is returned to its idle switching state (FIG. 1).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
EP90114415A 1989-07-29 1990-07-27 Schrauber Expired - Lifetime EP0411483B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8909208U DE8909208U1 (de) 1989-07-29 1989-07-29 Schrauber mit Drehmomentkupplung
DE8909208U 1989-07-29

Publications (2)

Publication Number Publication Date
EP0411483A1 EP0411483A1 (de) 1991-02-06
EP0411483B1 true EP0411483B1 (de) 1993-09-15

Family

ID=6841550

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90114415A Expired - Lifetime EP0411483B1 (de) 1989-07-29 1990-07-27 Schrauber

Country Status (2)

Country Link
EP (1) EP0411483B1 (ja)
DE (3) DE8909208U1 (ja)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7314097B2 (en) 2005-02-24 2008-01-01 Black & Decker Inc. Hammer drill with a mode changeover mechanism
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE505895C2 (sv) * 1995-11-16 1997-10-20 Atlas Copco Tools Ab Kraftskruvdragare

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7100916U (de) * 1971-01-12 1971-04-01 Schulz Kg Druckluftschrauber mit automatischer Kupplung
DE2832565C2 (de) * 1978-07-25 1983-12-08 Deprag Schulz Gmbh U. Co, 8450 Amberg Für Schrauber bestimmte Kupplung mit Motorabschaltung und Drehmomenttrennung
DE2840140A1 (de) * 1978-09-15 1980-03-27 Schmid & Wezel Druckluftschrauber mit abschaltumgehung
DE3015423A1 (de) * 1980-04-22 1981-10-29 Robert Bosch Gmbh, 7000 Stuttgart Motorisch beschriebener abschaltschrauber
DD159616A1 (de) * 1981-06-15 1983-03-23 Dieter Evler Schraubvorsatz mit drehmomentbegrenzung
DE3221553A1 (de) * 1982-06-08 1983-12-08 Deutsche Gardner-Denver Gmbh, 7081 Westhausen Druckluftschrauber
US4639996A (en) * 1985-07-12 1987-02-03 Xerox Corporation Screw fastening method

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7314097B2 (en) 2005-02-24 2008-01-01 Black & Decker Inc. Hammer drill with a mode changeover mechanism
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver

Also Published As

Publication number Publication date
DE8909208U1 (de) 1990-03-01
DE9011075U1 (de) 1990-12-06
EP0411483A1 (de) 1991-02-06
DE59002717D1 (de) 1993-10-21

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