EP0773854B1 - Power screwdriver and process for tightening screws - Google Patents

Power screwdriver and process for tightening screws Download PDF

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Publication number
EP0773854B1
EP0773854B1 EP95919965A EP95919965A EP0773854B1 EP 0773854 B1 EP0773854 B1 EP 0773854B1 EP 95919965 A EP95919965 A EP 95919965A EP 95919965 A EP95919965 A EP 95919965A EP 0773854 B1 EP0773854 B1 EP 0773854B1
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EP
European Patent Office
Prior art keywords
input shaft
screwdriver
speed
output shaft
drive motor
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
EP95919965A
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German (de)
French (fr)
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EP0773854A1 (en
Inventor
Gerold Mueller
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • B25B23/1456—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers having electrical components
    • 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
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • 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
    • B25B23/1453—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers for impact wrenches or screwdrivers

Definitions

  • the invention is based on a screwdriver of the type of claim 1 or a method for tightening a Screw connection according to the preamble of claim 8. It is already a screwdriver with hydraulic Impulse mechanism known (US 4,418,764), in which the amount of the tightening torque effective on the screwing tool Change the cross section of an overflow channel by means of an adjusting screw can be fixed.
  • the overflow channel is between a high pressure chamber and a Low pressure chamber arranged and serves to equalize the pressure a print medium.
  • the screwdriver is included provided with a mechanical shutdown device that Rotary drive depending on the pressure of the pressure medium switches off.
  • the screwdriver according to the invention has the advantage that a simple Structure of the screwdriver is made possible.
  • a desired one Tightening torque is easy to specify, one The cross section of the overflow channel does not change is required.
  • By detecting the change in the angle of rotation ⁇ of the output shaft between successive Angular momentum of the striking mechanism and by comparing the Angle change ⁇ with a threshold value ⁇ is also a Switch-off criterion for the drive motor can be specified so that a mechanical shutdown device is not required.
  • the speed setpoints are raised by means of a handle easy to select by the operator.
  • an electric motor especially one electronically commutated motor as a rotary drive becomes one good drive dynamics achieved, so that the rotary drive too with a relatively high load between successive Angular momentum can be accelerated to the specified target speed is.
  • the provision of an electric motor also has the advantage that the screwdriver is network-independent by means of an accumulator is operable. With the help of a recording device the speed change ⁇ n of the input shaft can easily Closed on the present tightening torque M. become.
  • FIG. 1 shows a section through a Handheld screwdriver designed according to the invention and FIG. 2 a section along line II-II in Figure 1.
  • a handheld screwdriver designated by 10 in FIG. 1 has a Housing 11, in which a drive motor 12 is housed.
  • a drive shaft 13 of the drive motor 12 is via a Pinion 14 and a transmission gear 15 with a Input shaft 16 of a striking mechanism 17 in a rotationally locking manner coupled.
  • the striking mechanism 17 in turn has one Output shaft 18, which with its striking mechanism 17th end facing away from the housing 11 of the hand screwdriver 10 protrudes and there is a tool holder 19 for a not wrench shown in detail.
  • the drive motor 12 is an electric motor, in particular a electronically commutated motor trained and over electrical connecting lines 20, 21 controllable.
  • the Housing 11 forms an approximately radial of a drive axis 22 away handle 23.
  • a Print trigger 24 housed, by means of which Drive motor 12 on or off via a switching device 25 can be switched off.
  • the handle 23 is an accumulator 26, the Drive motor 12 supplied with electrical drive energy and this about electrical not shown Connecting lines with the drive motor 12 or the Switching device 25 is connected.
  • the hammer mechanism 17 is a hydraulic pulse hammer mechanism educated.
  • the input shaft 16 forms an approximately cylindrical rotating body 30, which has an axial bore 31 for receiving the output shaft 18 and with a Radial bore 32 provided for receiving a reciprocating piston 33 is.
  • the reciprocating piston 33 in turn has an axial Through hole 34 which extends through the output shaft 18 becomes.
  • Within the rotating body 30 are one High pressure chamber 35 and a low pressure chamber 36 formed with each other via an overflow channel 37 are connected.
  • the overflow channel 37 runs inside the wall of the rotating body 30.
  • the inside of the rotary body 30 is with a pressure medium, for example, a hydraulic oil filled. On the outside it is Inside of the rotating body 30 through a cover 38 an opening of the radial bore 32 and through sealant 39 sealed on the output shaft 18.
  • Between Reciprocating piston 33 and output shaft 18 are one Active connection via a cam control 40.
  • the cam 52 is designed such that the control cam 51 once per complete relative rotation from output shaft 18 to Reciprocating piston 33 this displacement towards one Reduction of the volume of the high pressure chamber 35 down imposes. This always occurs when the control cam 51 on a tax paragraph 53 of the control curve 52.
  • the reciprocating piston 33 is retracted by means of a return spring 54 the pulse output back to its starting position deferred.
  • the continuity equation applies to the volume flow dV / dt, ie the volume of the overflowing pressure medium corresponds exactly to the reduction in the volume of the high-pressure chamber 35.
  • ⁇ (t) represents the difference in the angular velocities of input shaft 16 and output shaft 18 and ⁇ indicates the difference in rotational angle between these two shafts during the pulse output.
  • this angle of rotation difference ⁇ can be set equal to the angle of rotation ⁇ of the input shaft 18.
  • differential angular velocity ⁇ (t) then also corresponds in good approximation to the angular velocity and thus the rotational speed n of the input shaft 16.
  • the above relationship therefore makes it clear that the volume flow dV / dt and thus the pressure difference ⁇ p (t) or the momentum M can be influenced by the differential angular velocity ⁇ (t) by the speed n of the input shaft 16.
  • the screwdriver 10 with means 27 for preselecting the speed n of the input shaft 16 to be provided.
  • This is the way it is Tool holder 19 tapped momentum M even without Cross-section change of the overflow channel 37 controllable.
  • the speed n of the input shaft 16 and the drive speed of the drive motor 13 via the respective Gear ratio i of the transmission gear 15 directly related the preselection of the speed n over a Appropriate control of the drive motor 12 take place.
  • the means 27 for preselecting the speed n of the input shaft 16 have a handle 41 according to the exemplary embodiment Set a target speed n to.
  • the handle 41 is for example, as protruding from the housing 11 Knob 47 formed with the switching device 25th interacts in such a way that the operator does the necessary Speed n can select at which the desired Sets momentum moment M on the output shaft 18.
  • the Switching device 25 is with corresponding electrical or electronic control means.
  • the handle 41 used to specify the desired torque setpoint is by different switching positions of the rotary knob 47th marked with corresponding torque default values and the assignment of these torque setpoints to the corresponding speed setpoints internally e.g. by means of a Table is done in a storage element.
  • the means 27 for preselecting the speed n of the input shaft 16 in the exemplary embodiment Speed control device 42 which has a sensor 43 comprises, which detects the actual speed of the input shaft 16 and via connecting lines 45, 46 in signal form to a Comparison device 42a of the speed control device 42 forwards. The regulates in the event of a speed deviation Speed control device 42 the drive motor 12 accordingly, so that a stiff characteristic can be achieved is.
  • any speed sensor can be used as sensor 43 Find use.
  • the transducer 43 is designed as an incremental sensor, which in addition to the detection of the speed n also the determination of the angle of rotation ⁇ of the input shaft 16 between the consecutive angular momentum.
  • Input shaft 16 and drive shaft 13 are mentioned at Screwing process coupled with each other so that also in the arrangement of the transducer 43 shown the drive shaft 13 via the gear ratio i Speed n and the respective angle of rotation ⁇ of the input shaft 16 can be determined.
  • the start of a pulse delivery can for example based on the speed curve n (t) significant drop in speed ⁇ n can be detected.
  • Angle of rotation ⁇ of the input shaft 16 can be directly on the pro Angle of rotation occurred angle of rotation (change in angle of rotation ⁇ ) of the output shaft 18 are closed because the Input shaft 16 via the cam controller 40 with the Output shaft 18 is coupled.
  • a Evaluation device 44 is provided which the Speed control device 42 is assigned and which of the Sensor 43 recorded and via the connecting lines 45, 46 processed signals processed. The Evaluation device 44 thus forms together with the Sensor 43 a device for detecting the Angle change ⁇ of the output shaft 18 per angular momentum.
  • the Evaluation device 44 In addition to the speed n of the input shaft 13, the Evaluation device 44 also the one already mentioned Speed drop ⁇ n determined during the screwing process and as a measure for determining the on the tool holder 19th tapped momentum moment M used. This is sufficiently precise, since it can be assumed that a correspondingly strong one with a large pulse output Speed drop ⁇ n and vice versa. At the same time by the beginning of the speed drop ⁇ n also the beginning of the Pulse delivery signals what is for the aforementioned determination of the angle of rotation ⁇ of the input shaft 16 or Angle change ⁇ of the output shaft 18 is helpful. The evaluation device 44 thus forms together with the Sensor 43 also has a device for detecting the Speed drop ⁇ n of the input shaft 16.
  • the ratio is also in the evaluation device 44 ⁇ n / ⁇ of speed change ⁇ n of the input shaft 16 for Angle change ⁇ of the output shaft 18 is determined and as Determining variable for determining the target speed of the Input shaft 16 used.
  • ⁇ n / ⁇ can be applied to the existing screwing case (hard / soft) can be inferred because the speed drop ⁇ n is proportional to the momentum M.
  • M the existing screwing case
  • ⁇ n / ⁇ is a hard screwdriving due to a large ratio M / ⁇ characterized, a soft screwdriving case by a small one.
  • the screw connection can be particularly tighten exactly to a desired torque.
  • evaluation device 44 can be used, for example, with a Memory element be provided in the reference values of the Ratio ⁇ n / ⁇ can be saved. By comparing the determined during the current screwing process Actual ratio ⁇ n / ⁇ with the reference quantities can be corresponding speed correction on the drive motor 12 be made automatically.
  • evaluation device 44 is a limit value ⁇ stored, which is a minimal change in the angle of rotation ⁇ Output shaft 18 between successive angular pulses indicates. If this limit value ⁇ is in the course of Screwing process reached, i.e. if ⁇ ⁇ ⁇ , it becomes Tightening torque of the screw connection successive angular momentum no longer worth mentioning increases and the evaluation device 44 switches the Drive motor 12 accordingly.
  • the invention is not based on the described Embodiment limited. So the screwdriver can too with any other hydraulic pulse hammer mechanism, for example that known from US 4,418,764 Lamellar impact mechanism. Also a Transmission gear between drive motor and striking mechanism is not always necessary depending on the motor type.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Schrauber nach der Gattung des Anspruchs 1 bzw. von einem Verfahren zum Anziehen einer Schraubverbindung nach der Gattung des Anspruchs 8. Es ist schon ein Schrauber mit hydraulischem Impulsschlagwerk bekannt (US 4,418,764), bei dem der Betrag des am Schraubwerkzeug wirksamen Schraubmoments durch Veränderung des Querschnitts eines Überströmkanals mittels einer Einstellschraube festlegbar ist. Der Überströmkanal ist zwischen einer Hochdruckkammer und einer Niederdruckkammer angeordnet und dient dem Druckausgleich eines Druckmediums. Darüber hinaus ist der Schrauber mit einer mechanischen Abschalteinrichtung versehen, die den Drehantrieb in Abhängigkeit des Drucks des Druckmediums abschaltet.The invention is based on a screwdriver of the type of claim 1 or a method for tightening a Screw connection according to the preamble of claim 8. It is already a screwdriver with hydraulic Impulse mechanism known (US 4,418,764), in which the amount of the tightening torque effective on the screwing tool Change the cross section of an overflow channel by means of an adjusting screw can be fixed. The overflow channel is between a high pressure chamber and a Low pressure chamber arranged and serves to equalize the pressure a print medium. In addition, the screwdriver is included provided with a mechanical shutdown device that Rotary drive depending on the pressure of the pressure medium switches off.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Schrauber mit den Merkmalen des Anspruchs 1 bzw. das erfindungsgemäße Verfahren mit den Merkmalen des Anspruchs 8 hat demgegenüber den Vorteil, daß ein einfacher Aufbau des Schraubers ermöglicht wird. Ein gewünschtes Schraubmoment ist auf einfache Weise vorgebbar, wobei eine Veränderung des Querschnitts des Überströmkanals nicht erforderlich ist. Durch die Erfassung der Drehwinkeländerung Δϕ der Ausgangswelle zwischen aufeinanderfolgenden Drehimpulsen des Schlagwerks und durch den Vergleich der Drehwinkeländerung Δϕ mit einem Schwellwert ε ist zudem ein Abschaltkriterium für den Antriebsmotor angebbar, so daß eine mechanische Abschalteinrichtung nicht benötigt wird.The screwdriver according to the invention Features of claim 1 and the invention Method with the features of claim 8 has the advantage that a simple Structure of the screwdriver is made possible. A desired one Tightening torque is easy to specify, one The cross section of the overflow channel does not change is required. By detecting the change in the angle of rotation Δϕ of the output shaft between successive Angular momentum of the striking mechanism and by comparing the Angle change Δϕ with a threshold value ε is also a Switch-off criterion for the drive motor can be specified so that a mechanical shutdown device is not required.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 genannten Schraubers möglich. Mittels einer Handhabe sind die Drehzahlsollwerte auf einfache Weise durch den Bediener vorwählbar. Durch Verwendung eines Elektromotors, insbesondere eines elektronisch kommutierten Motors als Drehantrieb wird eine gute Antriebsdynamik erreicht, so daß der Drehantrieb auch bei relativ starker Belastung zwischen aufeinanderfolgenden Drehimpulsen auf die vorgegebene Solldrehzahl beschleunigbar ist. Das Vorsehen eines Elektromotors hat zudem den Vorteil, daß der Schrauber mittels eines Akkumulators netzunabhängig betreibbar ist. Mit Hilfe einer Einrichtung zur Erfassung der Drehzahländerung Δn der Eingangswelle kann auf einfache Weise auf das vorliegende Schraubmoment M geschlossen werden. Zusammen mit einer Einrichtung zur Erfassung der Drehwinkeländerung Δϕ der Ausgangswelle des Schlagwerks zwischen aufeinanderfolgenden Drehimpulsen kann dann eine Bestimmungsgröße für den vorliegenden Schraubfall (hart/weich) ermittelt werden. Es ist somit ein einfaches und genaues Verfahren zum Anziehen der Schraubverbindung angebbar, mittels dessen die erforderliche Drehzahl n der Eingangswelle des Schlagwerkes (Solldrehzahl) in Abhängigkeit des jeweiligen Schraubfalls vorgebbar ist. Auf diese Weise läßt sich eine hohe Genauigkeit des Einschraubmomentes der Schraubverbindung erzielen.By the measures listed in the subclaims advantageous further developments and improvements of the Claim 1 mentioned screwdriver possible. The speed setpoints are raised by means of a handle easy to select by the operator. By Use of an electric motor, especially one electronically commutated motor as a rotary drive becomes one good drive dynamics achieved, so that the rotary drive too with a relatively high load between successive Angular momentum can be accelerated to the specified target speed is. The provision of an electric motor also has the advantage that the screwdriver is network-independent by means of an accumulator is operable. With the help of a recording device the speed change Δn of the input shaft can easily Closed on the present tightening torque M. become. Together with a facility for recording the Angle of rotation change Δϕ of the output shaft of the striking mechanism between successive angular pulses can then be a Determinant for the present screwdriving case (hard / soft) can be determined. It is therefore a simple one and exact procedure for tightening the screw connection specifiable, by means of which the required speed n Impact mechanism input shaft (target speed) in Dependency of the respective screwing case can be specified. On this way a high accuracy of the Achieve screwing torque of the screw connection.

Zeichnungendrawings

Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Schnitt durch einen erfindungsgemäß ausgebildeten Handschrauber und Figur 2 einen Schnitt gemäß Linie II-II in Figur 1.An embodiment of the invention is in the drawings shown and in the following description explained. 1 shows a section through a Handheld screwdriver designed according to the invention and FIG. 2 a section along line II-II in Figure 1.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Ein in Figur 1 mit 10 bezeichneter Handschrauber hat ein Gehäuse 11, in dem ein Antriebsmotor 12 untergebracht ist. Eine Antriebswelle 13 des Antriebsmotors 12 ist über ein Ritzel 14 und ein Übersetzungsgetriebe 15 mit einer Eingangswelle 16 eines Schlagwerks 17 drehschlüssig gekoppelt. Das Schlagwerk 17 weist seinerseits eine Ausgangswelle 18 auf, die mit ihrem dem Schlagwerk 17 abgewandten Ende aus dem Gehäuse 11 des Handschraubers 10 herausragt und dort eine Werkzeughalterung 19 für ein nicht näher dargestelltes Schraubwerkzeug trägt.A handheld screwdriver designated by 10 in FIG. 1 has a Housing 11, in which a drive motor 12 is housed. A drive shaft 13 of the drive motor 12 is via a Pinion 14 and a transmission gear 15 with a Input shaft 16 of a striking mechanism 17 in a rotationally locking manner coupled. The striking mechanism 17 in turn has one Output shaft 18, which with its striking mechanism 17th end facing away from the housing 11 of the hand screwdriver 10 protrudes and there is a tool holder 19 for a not wrench shown in detail.

Der Antriebsmotor 12 ist als Elektromotor, insbesondere als elektronisch kommutierter Motor ausgebildet und über elektrische Anschlußleitungen 20, 21 ansteuerbar. Das Gehäuse 11 bildet einen etwa radial von einer Antriebsachse 22 weggerichteten Handgriff 23. Im Handgriff 23 ist ein Druckabzug 24 untergebracht, mittels dessen der Antriebsmotor 12 über eine Schalteinrichtung 25 an- bzw. ausschaltbar ist. Am dem Antriebsmotor 12 abgewandten Ende des Handgriffs 23 sitzt ein Akkumulator 26, der den Antriebsmotor 12 mit elektrischer Antriebsenergie versorgt und hierzu über nicht näher gezeigte elektrische Verbindungsleitungen mit dem Antriebsmotor 12 bzw. der Schalteinrichtung 25 verbunden ist.The drive motor 12 is an electric motor, in particular a electronically commutated motor trained and over electrical connecting lines 20, 21 controllable. The Housing 11 forms an approximately radial of a drive axis 22 away handle 23. In the handle 23 is a Print trigger 24 housed, by means of which Drive motor 12 on or off via a switching device 25 can be switched off. At the end facing away from the drive motor 12 the handle 23 is an accumulator 26, the Drive motor 12 supplied with electrical drive energy and this about electrical not shown Connecting lines with the drive motor 12 or the Switching device 25 is connected.

Das Schlagwerk 17 ist als hydraulisches Impulsschlagwerk ausgebildet. Die Eingangswelle 16 bildet einen etwa zylindrischen Rotationskörper 30, der mit einer Axialbohrung 31 zur Aufnahme der Ausgangswelle 18 und mit einer Radialbohrung 32 zur Aufnahme eines Hubkolbens 33 versehen ist. Der Hubkolben 33 hat seinerseits eine axiale Durchgangsbohrung 34, die von der Ausgangswelle 18 durchragt wird. Innerhalb des Rotationskörpers 30 sind eine Hochdruckkammer 35 und eine Niederdruckkammer 36 ausgebildet, die über einen Überströmkanal 37 miteinander verbunden sind. Der Überströmkanal 37 verläuft dabei innerhalb der Wandung des Rotationskörpers 30. Das Innere des Rotationskörpers 30 ist mit einem Druckmedium, beispielsweise einem Hydrauliköl gefüllt. Nach außen ist das Innere des Rotationskörpers 30 durch einen Deckel 38 an einer Öffnung der Radialbohrung 32 und durch Dichtmittel 39 an der Ausgangswelle 18 dicht abgeschlossen. Zwischen Hubkolben 33 und Ausgangswelle 18 besteht eine Wirkverbindung über eine Nockensteuerung 40.The hammer mechanism 17 is a hydraulic pulse hammer mechanism educated. The input shaft 16 forms an approximately cylindrical rotating body 30, which has an axial bore 31 for receiving the output shaft 18 and with a Radial bore 32 provided for receiving a reciprocating piston 33 is. The reciprocating piston 33 in turn has an axial Through hole 34 which extends through the output shaft 18 becomes. Within the rotating body 30 are one High pressure chamber 35 and a low pressure chamber 36 formed with each other via an overflow channel 37 are connected. The overflow channel 37 runs inside the wall of the rotating body 30. The inside of the rotary body 30 is with a pressure medium, for example, a hydraulic oil filled. On the outside it is Inside of the rotating body 30 through a cover 38 an opening of the radial bore 32 and through sealant 39 sealed on the output shaft 18. Between Reciprocating piston 33 and output shaft 18 are one Active connection via a cam control 40.

Beim Betrieb des Antriebsmotors 12 wird zunächst die Eingangswelle 16 und damit der Rotationskörper 30 über das Übersetzungsgetriebe 15 drehend angetrieben. Aufgrund von Reibkräften wird dabei die Ausgangswelle 18 ebenfalls drehend mitgenommen. Sobald ein an der Werkzeughalterung 19 abgegriffenes Schraubmoment das Reibmoment übersteigt, können sich die Ausgangswelle 18 und die Eingangswelle 16 bzw. der Rotationskörper 30 gegeneinander verdrehen. Die mit dem Schraubwerkzeug verbundene Ausgangswelle 18 dreht dann langsamer als der beispielsweise in Richtung eines Pfeiles 50 (Figur 2) drehende Rotationskörper 30 mit Hubkolben 33. Wie aus Figur 2 hervorgeht, besteht die Nockensteuerung 40 aus einem fest mit der Ausgangswelle 18 verbundenen Steuernocken 51 und einer innerhalb der Durchgangsbohrung 34 am Hubkolben 33 angeordneten Steuerkurve 52. Die Steuerkurve 52 ist derart ausgebildet, daß der Steuernocken 51 einmal pro vollständiger Relatiwerdrehung von Ausgangswelle 18 zum Hubkolben 33 diesem eine Verschiebung in Richtung auf eine Verkleinerung des Volumens der Hochdruckkammer 35 hin aufzwingt. Dies erfolgt immer dann, wenn der Steuernocken 51 auf einen Steuerabsatz 53 der Steuerkurve 52 aufläuft. Mittels einer Rückstellfeder 54 wird der Hubkolben 33 nach der Impulsabgabe wieder in seine Ausgangsstellung zurückgestellt. Während der Verschiebung des Hubkolbens 33 wird das Druckmedium in der Hochdruckkammer 35 mit Druck beaufschlagt, der dazu führt, daß über die Nockensteuerung 40 ein Impulsmoment M auf die Ausgangswelle 18 übertragen wird. Der Betrag des Impulsmomentes M ist dabei von der Druckdifferenz Δp zwischen der Hochdruckkammer 35 und der Niederdruckkammer 36 abhängig, d.h. M = f(Δp). Der zeitliche Verlauf der Druckdifferenz Δp wird durch den durch den Überströmkanal 37 hindurchströmenden Volumenstrom dV/dt des Druckmediums bestimmt, d.h. Δp (t) = f(dV/dt).When operating the drive motor 12, the Input shaft 16 and thus the rotating body 30 via the Transmission gear 15 driven in rotation. Owing to The output shaft 18 also becomes frictional forces rotated along. As soon as one on the tool holder 19 tapped torque exceeds the friction torque, the output shaft 18 and the input shaft 16 or the rotating body 30 against each other. With the output shaft 18 connected to the screwing tool then rotates slower than that, for example, in the direction of an arrow 50 (FIG. 2) rotating rotary body 30 with reciprocating piston 33. As can be seen from FIG. 2, there is the cam control 40 from a fixedly connected to the output shaft 18 Control cam 51 and one within the through hole 34 on the piston 33 arranged cam 52. The cam 52 is designed such that the control cam 51 once per complete relative rotation from output shaft 18 to Reciprocating piston 33 this displacement towards one Reduction of the volume of the high pressure chamber 35 down imposes. This always occurs when the control cam 51 on a tax paragraph 53 of the control curve 52. The reciprocating piston 33 is retracted by means of a return spring 54 the pulse output back to its starting position deferred. During the displacement of the reciprocating piston 33 becomes the pressure medium in the high pressure chamber 35 with pressure acted on, which leads to the cam control 40 transmit a momentum moment M to the output shaft 18 becomes. The amount of momentum M is from Pressure difference Δp between the high pressure chamber 35 and the Low pressure chamber 36 dependent, i.e. M = f (Δp). The temporal The course of the pressure difference Δp is determined by the Overflow channel 37 flowing volume flow dV / dt of Pressure medium determined, i.e. Δp (t) = f (dV / dt).

Da das Druckmedium in erster Näherung als inkompressibel angenommen werden kann, gilt für den Volumenstrom dV/dt die Kontinuitätsgleichung, d.h. das Volumen des überströmenden Druckmediums entspricht genau der Verkleinerung des Volumens der Hochdruckkammer 35. Durch Umformung erhält man für den Volumenstrom: dV/dt = dV/dγ * dγ/dt = dV/dγ * ω(t) wobei ω(t) die Differenz der Winkelgeschwindigkeiten von Eingangswelle 16 und Ausgangswelle 18 darstellt und γ die Drehwinkeldifferenz zwischen diesen beiden Wellen während der Impulsabgabe angibt. Näherungsweise kann diese Drehwinkeldifferenz γ gleich dem Drehwinkel α der Eingangswelle 18 gesetzt werden. Die genannte Differenz-Winkelgeschwindigkeit ω(t) entspricht dann ebenso in guter Näherung der Winkelgeschwindigkeit und somit der Drehzahl n der Eingangswelle 16. Durch die obenstehende Beziehung wird also verdeutlicht, daß der Volumenstrom dV/dt und damit die Druckdifferenz Δp(t) bzw. das Impulsmoment M über die Differenz-Winkelgeschwindigkeit ω(t) durch die Drehzahl n der Eingangswelle 16 beeinflußbar ist.Since the pressure medium can be assumed to be incompressible in the first approximation, the continuity equation applies to the volume flow dV / dt, ie the volume of the overflowing pressure medium corresponds exactly to the reduction in the volume of the high-pressure chamber 35. dV / dt = dV / dγ * dγ / dt = dV / dγ * ω (t) where ω (t) represents the difference in the angular velocities of input shaft 16 and output shaft 18 and γ indicates the difference in rotational angle between these two shafts during the pulse output. Approximately, this angle of rotation difference γ can be set equal to the angle of rotation α of the input shaft 18. The named differential angular velocity ω (t) then also corresponds in good approximation to the angular velocity and thus the rotational speed n of the input shaft 16. The above relationship therefore makes it clear that the volume flow dV / dt and thus the pressure difference Δp (t) or the momentum M can be influenced by the differential angular velocity ω (t) by the speed n of the input shaft 16.

Erfindungsgemäß wird daher vorgeschlagen, den Schrauber 10 mit Mitteln 27 zur Vorwahl der Drehzahl n der Eingangswelle 16 zu versehen. Auf diese Weise ist das an der Werkzeughalterung 19 abgreifbare Impulsmoment M auch ohne Querschnittsänderung des Überströmkanals 37 steuerbar. Da die Drehzahl n der Eingangswelle 16 und die Antriebsdrehzahl des Antriebsmotors 13 über das jeweilige Übersetzungsverhältnis i des Übersetzungsgetriebes 15 direkt zusammenhängen, kann die Vorwahl der Drehzahl n über eine entsprechende Ansteuerung des Antriebsmotors 12 erfolgen.According to the invention, it is therefore proposed to use the screwdriver 10 with means 27 for preselecting the speed n of the input shaft 16 to be provided. This is the way it is Tool holder 19 tapped momentum M even without Cross-section change of the overflow channel 37 controllable. There the speed n of the input shaft 16 and the drive speed of the drive motor 13 via the respective Gear ratio i of the transmission gear 15 directly related, the preselection of the speed n over a Appropriate control of the drive motor 12 take place.

Die Mittel 27 zur Vorwahl der Drehzahl n der Eingangswelle 16 weisen gemäß dem Ausführungsbeispiel eine Handhabe 41 zum Einstellen einer Solldrehzahl n auf. Die Handhabe 41 ist beispielsweise als aus dem Gehäuse 11 herausragender Drehknopf 47 ausgebildet, der mit der Schalteinrichtung 25 derart zusammenwirkt, daß der Bediener die erforderliche Drehzahl n vorwählen kann, bei der sich das gewünschte Impulsmoment M an der Ausgangswelle 18 einstellt. Die Schalteinrichtung 25 ist dazu mit entsprechenden elektrischen bzw. elektronischen Steuermitteln versehen. Für den Anwender besonders vorteilhaft ist es, wenn die Handhabe 41 zur Vorgabe des gewünschten Drehmomentsollwertes benutzt wird, indem verschiedene Schaltstellungen des Drehknopfes 47 mit entsprechenden Drehmoment-Vorgabewerten gekennzeichnet sind und die Zuordnung dieser Drehmomentsollwerte zu den entsprechenden Drehzahlsollwerten intern z.B. mittels einer Tabelle in einem Speicherelement erfolgt.The means 27 for preselecting the speed n of the input shaft 16 have a handle 41 according to the exemplary embodiment Set a target speed n to. The handle 41 is for example, as protruding from the housing 11 Knob 47 formed with the switching device 25th interacts in such a way that the operator does the necessary Speed n can select at which the desired Sets momentum moment M on the output shaft 18. The Switching device 25 is with corresponding electrical or electronic control means. For it is particularly advantageous for the user if the handle 41 used to specify the desired torque setpoint is by different switching positions of the rotary knob 47th marked with corresponding torque default values and the assignment of these torque setpoints to the corresponding speed setpoints internally e.g. by means of a Table is done in a storage element.

Darüber hinaus weisen die Mittel 27 zur Vorwahl der Drehzahl n der Eingangswelle 16 im Ausführungsbeispiel eine Drehzahlregeleinrichtung 42 auf, die einen Aufnehmer 43 umfaßt, der die Istdrehzahl der Eingangswelle 16 erfaßt und über Verbindungsleitungen 45, 46 in Signalform an eine Vergleichseinrichtung 42a der Drehzahlregeleinrichtung 42 weiterleitet. Bei einer Drehzahlabweichung regelt die Drehzahlregeleinrichtung 42 den Antriebsmotor 12 entsprechend nach, so daß eine steife Kennlinie erzielbar ist.In addition, the means 27 for preselecting the speed n of the input shaft 16 in the exemplary embodiment Speed control device 42, which has a sensor 43 comprises, which detects the actual speed of the input shaft 16 and via connecting lines 45, 46 in signal form to a Comparison device 42a of the speed control device 42 forwards. The regulates in the event of a speed deviation Speed control device 42 the drive motor 12 accordingly, so that a stiff characteristic can be achieved is.

Als Aufnehmer 43 kann ein beliebiger Drehzahlsensor Verwendung finden. Im dargestellten Ausführungsbeispiel ist der Aufnehmer 43 als inkrementaler Meßwertgeber ausgebildet, der neben der Erfassung der Drehzahl n auch die Bestimmung des Drehwinkels α der Eingangswelle 16 zwischen den aufeinanderfolgenden Drehimpulsen zuläßt. Wie bereits erwähnt sind Eingangswelle 16 und Antriebswelle 13 beim Schraubvorgang drehschlüssig miteinander gekoppelt, so daß auch bei der dargestellten Anordnung des Aufnehmers 43 an der Antriebswelle 13 über das Übersetzungsverhältnis i die Drehzahl n und der jeweilige Drehwinkel α der Eingangswelle 16 ermittelbar sind. Der Beginn einer Impulsabgabe kann beispielsweise anhand des Drehzahlverlaufes n(t) durch deutlichen Drehzahlabfall Δn erkannt werden. Any speed sensor can be used as sensor 43 Find use. In the illustrated embodiment the transducer 43 is designed as an incremental sensor, which in addition to the detection of the speed n also the determination of the angle of rotation α of the input shaft 16 between the consecutive angular momentum. As before Input shaft 16 and drive shaft 13 are mentioned at Screwing process coupled with each other so that also in the arrangement of the transducer 43 shown the drive shaft 13 via the gear ratio i Speed n and the respective angle of rotation α of the input shaft 16 can be determined. The start of a pulse delivery can for example based on the speed curve n (t) significant drop in speed Δn can be detected.

Mittels des zwischen zwei Drehimpulsen zurückgelegten Drehwinkels α der Eingangswelle 16 kann direkt auf den pro Drehimpuls aufgetretenen Verdrehwinkel (Drehwinkeländerung Δϕ) der Ausgangswelle 18 geschlossen werden, da die Eingangswelle 16 über die Nockensteuerung 40 mit der Ausgangswelle 18 gekoppelt ist. Vom gesamten Drehwinkel α zwischen zwei aufeinanderfolgenden Drehimpulsen müssen hierzu lediglich 360 Grad abgezogen werden, d.h. Δϕ = α - 2π. Zur Ermittlung der Drehwinkeldifferenz Δϕ ist eine Auswerteeinrichtung 44 vorgesehen, der die Drehzahlregeleinrichtung 42 zugeordnet ist und die die vom Aufnehmer 43 aufgenommenen und über die Verbindungsleitungen 45, 46 übertragenen Signale weiterverarbeitet. Die Auswerteeinrichtung 44 bildet somit zusammen mit dem Aufnehmer 43 eine Einrichtung zur Erfassung der Drehwinkeländerung Δϕ der Ausgangswelle 18 je Drehimpuls.By means of the distance traveled between two angular pulses Angle of rotation α of the input shaft 16 can be directly on the pro Angle of rotation occurred angle of rotation (change in angle of rotation Δϕ) of the output shaft 18 are closed because the Input shaft 16 via the cam controller 40 with the Output shaft 18 is coupled. Of the total angle of rotation α between two successive angular pulses subtract only 360 degrees, i.e. Δϕ = α - 2π. To determine the angle of rotation difference Δϕ is a Evaluation device 44 is provided which the Speed control device 42 is assigned and which of the Sensor 43 recorded and via the connecting lines 45, 46 processed signals processed. The Evaluation device 44 thus forms together with the Sensor 43 a device for detecting the Angle change Δϕ of the output shaft 18 per angular momentum.

Neben der Drehzahl n der Eingangswelle 13 wird mittels der Auswerteeinrichtung 44 auch der bereits erwähnte Drehzahlabfall Δn während des Schraubvorgangs ermittelt und als Maß für Bestimmung des an der Werkzeughalterung 19 abgegriffenen Impulsmomentes M verwendet. Dies ist hinreichend genau, da davon ausgegangen werden kann, daß sich bei großer Impulsabgabe ein entsprechend starker Drehzahlabfall Δn einstellt und umgekehrt. Gleichzeitig wird durch den Beginn des Drehzahlabfalles Δn auch der Beginn der Impulsabgabe signalisiert, was für die erwähnte Ermittlung des Drehwinkels α der Eingangswelle 16 bzw. der Drehwinkeländerung Δϕ der Ausgangswelle 18 hilfreich ist. Die Auswerteeinrichtung 44 bildet somit zusammen mit dem Aufnehmer 43 auch eine Einrichtung zur Erfassung des Drehzahlabfalles Δn der Eingangswelle 16.In addition to the speed n of the input shaft 13, the Evaluation device 44 also the one already mentioned Speed drop Δn determined during the screwing process and as a measure for determining the on the tool holder 19th tapped momentum moment M used. This is sufficiently precise, since it can be assumed that a correspondingly strong one with a large pulse output Speed drop Δn and vice versa. At the same time by the beginning of the speed drop Δn also the beginning of the Pulse delivery signals what is for the aforementioned determination of the angle of rotation α of the input shaft 16 or Angle change Δϕ of the output shaft 18 is helpful. The evaluation device 44 thus forms together with the Sensor 43 also has a device for detecting the Speed drop Δn of the input shaft 16.

In der Auswerteeinrichtung 44 wird zusätzlich das Verhältnis Δn/Δϕ von Drehzahländerung Δn der Eingangswelle 16 zur Drehwinkeländerung Δϕ der Ausgangswelle 18 ermittelt und als Bestimmungsgröße für die Festlegung der Solldrehzahl der Eingangswelle 16 herangezogen. Mit Hilfe des Verhältnisses Δn/Δϕ kann auf den vorliegenden Schraubfall (hart/weich) rückgeschlossen werden, da der Drehzahlabfall Δn proportional zum Impulsmoment M ist. Bekanntermaßen ist ein harter Schraubfall durch ein großes Verhältnis M/Δϕ gekennzeichnet, ein weicher Schraubfall durch ein kleines. Entsprechendes gilt auch für das Verhältnis Δn/Δϕ. Da der Schraubfall Auswirkungen auf die erzielbare Genauigkeit des Anziehmomentes der Schraubverbindung hat, ist die Kenntnis dieser Größe von großer Bedeutung. Wird das ermittelte Verhältnis Δn/Δϕ als Bestimmungsgröße für die Vorwahl der Solldrehzahl der Eingangswelle 16 in der Auswerteeinrichtung 44 verwendet, läßt sich die Schraubverbindung besonders genau auf ein gewünschtes Drehmoment anziehen. Die Auswerteeinrichtung 44 kann hierzu beispielsweise mit einem Speicherelement versehen sein, in dem Referenzgrößen des Verhältnisses Δn/Δϕ abspeicherbar sind. Durch Vergleich des während des aktuellen Schraubvorganges ermittelten Istverhältnisses Δn/Δϕ mit den Referenzgrößen kann eine entsprechende Drehzahlkorrektur am Antriebsmotor 12 automatisch vorgenommen werden.The ratio is also in the evaluation device 44 Δn / Δϕ of speed change Δn of the input shaft 16 for Angle change Δϕ of the output shaft 18 is determined and as Determining variable for determining the target speed of the Input shaft 16 used. With the help of the relationship Δn / Δϕ can be applied to the existing screwing case (hard / soft) can be inferred because the speed drop Δn is proportional to the momentum M. As is known, is a hard screwdriving due to a large ratio M / Δϕ characterized, a soft screwdriving case by a small one. The same applies to the ratio Δn / Δϕ. Since the Impact on the achievable accuracy of the Has the tightening torque of the screw connection this size of great importance. Is that determined Ratio Δn / Δϕ as a determinant for the preselection of Target speed of the input shaft 16 in the evaluation device 44 used, the screw connection can be particularly tighten exactly to a desired torque. The For this purpose, evaluation device 44 can be used, for example, with a Memory element be provided in the reference values of the Ratio Δn / Δϕ can be saved. By comparing the determined during the current screwing process Actual ratio Δn / Δϕ with the reference quantities can be corresponding speed correction on the drive motor 12 be made automatically.

Die Ermittlung der Drehwinkeländerung Δϕ der Ausgangswelle 18 zwischen aufeinanderfolgenden Drehimpulsen durch die Auswerteeinrichtung 44 erlaubt auch die Angabe eines Abschaltkriteriums für den Drehantrieb. In der Auswerteeinrichtung 44 ist hierzu ein Grenzwert ε abgespeichert, der eine minimale Drehwinkeländerung Δϕ der Ausgangswelle 18 zwischen aufeinanderfolgenden Drehimpulsen angibt. Wird dieser Grenzwert ε im Verlauf des Schraubvorganges erreicht, d.h. ist Δϕ ≤ ε, wird das Verschraubungsmoment der Schraubverbindung durch aufeinanderfolgende Drehimpulse nicht mehr nennenswert erhöht und die Auswerteeinrichtung 44 schaltet den Antriebsmotor 12 entsprechend ab.The determination of the angle of rotation change Δϕ of the output shaft 18 between successive angular pulses through the Evaluation device 44 also allows the specification of a Switch-off criterion for the rotary drive. In the For this purpose, evaluation device 44 is a limit value ε stored, which is a minimal change in the angle of rotation Δϕ Output shaft 18 between successive angular pulses indicates. If this limit value ε is in the course of Screwing process reached, i.e. if Δϕ ≤ ε, it becomes Tightening torque of the screw connection successive angular momentum no longer worth mentioning increases and the evaluation device 44 switches the Drive motor 12 accordingly.

Die Erfindung ist nicht auf das beschriebene Ausführungsbeispiel beschränkt. So kann der Schrauber auch mit einem beliebigen anderen hydraulischen Impulsschlagwerk, beispielsweise dem aus der US 4,418,764 bekannten Lamellenschlagwerk ausgestattet sein. Auch ein Übersetzungsgetriebe zwischen Antriebsmotor und Schlagwerk ist je nach Motortyp nicht in jedem Falle erforderlich.The invention is not based on the described Embodiment limited. So the screwdriver can too with any other hydraulic pulse hammer mechanism, for example that known from US 4,418,764 Lamellar impact mechanism. Also a Transmission gear between drive motor and striking mechanism is not always necessary depending on the motor type.

Claims (8)

  1. Screwdriver, in particular hand screwdriver, with a hydraulic percussion mechanism (17) which has an input shaft (16), capable of being driven in rotation by means of a drive motor (12), and an output shaft (18), coupled to a toolholder (19) and rotatable relative to the input shaft (16), and which possesses at least one high-pressure chamber (35) and at least one low-pressure chamber (36) which are each filled with a pressure medium and are connected to one another by at least one overflow duct (37), the pressure medium in the high-pressure chamber (35) being capable of being loaded with pressure in the event of a rotation of the input shaft (16) and output shaft (18) relative to one another, characterized in that, for the purpose of influencing a momentum (M) capable of being taken off at the output shaft (18), the screwdriver (10) has means (27) for preselecting a rotational speed (n) of the input shaft (16), the said means having a rotational-speed regulating device (42) for the drive motor (12).
  2. Screwdriver according to Claim 1, characterized in that the means (27) for preselecting the rotational speed (n) or the momentum (M) have a switching device (25) for setting various momentum desired values by means of various rotational-speed desired values.
  3. Screwdriver according to Claim 1, characterized in that the drive motor (12) is formed by an electric motor.
  4. Screwdriver according to Claim 3, characterized in that the electric motor is designed as an electronically commutated motor.
  5. Screwdriver according to Claim 3, characterized in that the electric motor is capable of being operated independently of the mains by means of an accumulator (26).
  6. Screwdriver according to Claim 1, characterized in that the screwdriver (10) is provided with a device (43, 44) for detecting a rotational-speed change (Δn) of the input shaft (16).
  7. Screwdriver according to Claim 1 or 6, characterized in that the screwdriver (10) is provided with a device (43, 44) for detecting a rotary-angle change (Δϕ) of the output shaft (18).
  8. Method for tightening a screw connection by means of a screwdriver (10), which is provided with a drive motor (12) and with a percussion mechanism (17) generating a moment of momentum, the said percussion mechanism (17) possessing an input shaft (16), capable of being driven in rotation by means of the drive motor (12), and having an output shaft (18) coupled to a tool holder (19) for a screwing tool, characterized in that the desired rotational speed of the input shaft (16) is preselected, in that, during the screwing operation, the ratio Δn/Δϕ of the rotational-speed change (Δn) of the input shaft (16) to the rotary-angle change (Δϕ) of the output shaft (18) is determined, and in that this ratio Δn/Δϕ is used in an evaluation device (44) as a determining variable for preselecting the desired rotational speed of the input shaft (16).
EP95919965A 1994-08-03 1995-06-01 Power screwdriver and process for tightening screws Expired - Lifetime EP0773854B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4427452A DE4427452A1 (en) 1994-08-03 1994-08-03 Screwdriver and method for tightening a screw connection using the screwdriver
DE4427452 1994-08-03
PCT/DE1995/000711 WO1996004106A1 (en) 1994-08-03 1995-06-01 Power screwdriver and process for tightening screws

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EP0773854A1 EP0773854A1 (en) 1997-05-21
EP0773854B1 true EP0773854B1 (en) 2000-01-26

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DE (2) DE4427452A1 (en)
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US8286723B2 (en) 2010-01-07 2012-10-16 Black & Decker Inc. Power screwdriver having rotary input control
US8418778B2 (en) 2010-01-07 2013-04-16 Black & Decker Inc. Power screwdriver having rotary input control
USRE44311E1 (en) 2004-10-20 2013-06-25 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor

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US9266178B2 (en) 2010-01-07 2016-02-23 Black & Decker Inc. Power tool having rotary input control
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USRE44311E1 (en) 2004-10-20 2013-06-25 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
USRE44993E1 (en) 2004-10-20 2014-07-08 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
USRE45112E1 (en) 2004-10-20 2014-09-09 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
US8286723B2 (en) 2010-01-07 2012-10-16 Black & Decker Inc. Power screwdriver having rotary input control
US8418778B2 (en) 2010-01-07 2013-04-16 Black & Decker Inc. Power screwdriver having rotary input control

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EP0773854A1 (en) 1997-05-21
WO1996004106A1 (en) 1996-02-15
DE59507705D1 (en) 2000-03-02
DE4427452A1 (en) 1996-02-08
JPH10503432A (en) 1998-03-31

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