EP3825063B1 - Manual machine tool - Google Patents
Manual machine tool Download PDFInfo
- Publication number
- EP3825063B1 EP3825063B1 EP20208763.1A EP20208763A EP3825063B1 EP 3825063 B1 EP3825063 B1 EP 3825063B1 EP 20208763 A EP20208763 A EP 20208763A EP 3825063 B1 EP3825063 B1 EP 3825063B1
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- European Patent Office
- Prior art keywords
- switch
- contour
- torque
- machine tool
- hand
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- 238000000034 method Methods 0.000 description 9
- 238000011144 upstream manufacturing Methods 0.000 description 9
- 230000005540 biological transmission Effects 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000001960 triggered effect Effects 0.000 description 4
- 230000004069 differentiation Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000009795 derivation Methods 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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Classifications
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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
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
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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
- B25B23/141—Mechanical overload release couplings
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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
- B25B23/147—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for electrically operated wrenches or screwdrivers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
- B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
- B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
Definitions
- the invention relates to an electric hand-held power tool, in particular a cordless screwdriver, with a preferably electric drive accommodated in a housing, which drives a drive shaft, with an output unit which can be non-positively connected to the drive by means of a mechanical shut-off clutch, in order to transfer torque from the drive to a to transfer the application tool connected to the output unit, wherein the mechanical shut-off clutch comprises a switching ring which is mounted axially against the force of a return spring and at least one switching element guided on a control cam, the control cam being limited at one end by a first switching contour for providing a release torque of the shut-off clutch and at the other end by a limiting contour is.
- the document EP 0 476 999 A1 shows an electric hand tool according to the preamble of claim 1.
- This shut-off clutch includes a switching ring, which is axially adjusted against the force of a return spring when the predefinable tightening torque is exceeded and thereby unlocks, or opens or releases, the shut-off clutch.
- the torque of the drive train In order to open the shut-off clutch, the torque of the drive train must ultimately overcome the force of the return spring. With increasing torque that is introduced into the shut-off clutch, the introduced torque is transmitted to the shift ring until the force of the return spring, which counteracts the shift ring in the axial direction, is less than the force component that is due to the applied torque in the axial direction direction.
- the switching ring is then deflected axially against the force of the restoring spring and relative rotation occurs between the first switching contour and the switching element.
- This axial deflection of the switching ring and thus ultimately the opening of the shut-off clutch is usually used as a sensor signal in order to switch off the drive and, if necessary, brake it and thus bring it to a standstill.
- a microswitch can be used here for switching or a magnetic field can also be changed by the axial deflection.
- a switching slide with a magnet accommodated therein is also axially deflected during the axial deflection of the switching ring.
- the induced by the axial deflection of the magnet Detect changes in the magnetic field, which can then be used as a sensor signal to switch off the drive.
- the force of the return spring pushes the switching ring axially back in the direction of the drive and forces the switching element back onto the control cam.
- the part of the shut-off clutch which is non-rotatably connected to the drive is then rotated further by the available rotational energy of the drive until the motor comes to a standstill. If the drive speed is low, the drive is switched off and braked so quickly that the shut-off clutch does not trip again. In order to ensure a defined screwing process, the drive is often continued to be operated at a very low speed after a short time until the first switching contour is again in contact with the switching element. The shut-off clutch is now in its starting position for the next screw connection.
- shut-off clutch is associated with an acoustic effect that can usually be referred to as a clicking noise. If the shut-off clutch now releases several times, this is often irritating for the user, since he then assumes that the screw connection was incorrectly executed if he hears the clicking noise several times.
- the object of the present invention is therefore to reduce the above-mentioned disadvantages, in particular to provide a hand-held power tool that provides improved process reliability at high screwing speeds.
- the second switching contour ultimately provides a pre-shift torque, which also leads to an axial deflection of the switching ring, which is mounted axially against the force of the return spring.
- This additional axial deflection is used to generate an upstream signal well before the actual triggering torque is reached, which ultimately corresponds to the tightening torque, in order to switch off or brake the drive at this early point in time, or at least to prepare for these steps.
- it is also alternatively or additionally provided, in addition to detecting the axial adjustment of the switching ring, to also detect a relative rotation of the switching ring with respect to the part of the shut-off clutch non-rotatably connected to the drive shaft.
- This relative rotation ultimately occurs when the pre-shift torque is exceeded and the shifting element over the second shifting contour slides away and then comes to rest at the first switching contour.
- the second switching contour can therefore already detect an increasing torque before the actual triggering of the shut-off clutch, in order to initiate or prepare for shutting off or braking the drive.
- the first shifting contour has a shifting point whose tangent slope defines the release torque of the shut-off clutch, and if the cam is assigned a second shifting contour with a pre-shift point whose tangent slope defines the pre-shift torque that is smaller than the release torque . Since the triggering torque or the pre-shifting torque can be determined on the basis of the slope of the tangent at the switching point or at the pre-shifting point, this provides a simple way of defining the triggering torque and the pre-shifting torque. In this context, it has also turned out to be advantageous if the gradient of the tangent at the switching point is greater than the gradient of the tangent at the upstream switching point. If the stroke of the second switching contour is the same as or less than that of the first switching contour, this ensures when the second switching contour is triggered that the pre-shift torque can be clearly distinguished from the triggering torque of the first switching contour.
- the ratio between the gradient of the tangent of the switching point and the gradient of the tangent of the upstream switching point is preferably 1.2:1 or greater, preferably 1.5:1 or greater and particularly preferably 1.8:1 or greater and more preferably 4 :1 or less, preferably 3:1 or less and most preferably 2:1. This ensures that the value of the pre-shift torque is significantly lower than the value of the triggering torque in order to be able to make a reliable distinction between the pre-clamping torque and the triggering torque.
- the angle between the slope of the tangent of the switching point and a plane that is oriented perpendicularly to the drive shaft is preferably 50° or greater, preferably 55° or greater and particularly preferably 60° or greater and greater preferably 80° or less, preferably 75° or less, and more preferably 70° or less. If this angle becomes too large, there is a risk that the shifting element can only slide over the first shifting contour with difficulty when the shut-off clutch is released, ie that the release torque in particular increases too much.
- the angle between the slope of the tangent of the upstream switching point and a plane which is oriented perpendicularly to the drive shaft is preferably 20° or greater, preferably 25° or greater and particularly preferably 30° or is greater and more preferably 45° or less, preferably 40° or less and particularly preferably 35° or less. This also ensures that a suitable differentiation can be made between the pre-clutching torque and the triggering torque.
- the cam has a constant slope in the area of the second switching contour. In particular, this can be implemented particularly easily in terms of manufacturing technology.
- the resulting characteristic increase in torque can be used to detect that the shifting element is in the area of the second shifting contour, which then initiates or initiates the switching off and/or braking of the drive can be executed.
- conclusions can be drawn about the torque rate. The faster the axial deflection occurs, the harder the screwdriving is. Ultimately, this makes it possible to control the switch-off or braking behavior of the drive depending on the hardness of the screwdriving application.
- the control curve includes a first maximum, which defines the triggering torque, and a second maximum, which defines the pre-clutching torque.
- the use of two maxima ultimately means that the deflection of the switching ring, which can be adjusted axially against the spring force of the restoring spring, can be shifted by the second switching contour significantly before the deflection by the first switching contour.
- the first maximum is greater than the second maximum. This takes into account the fact that the switching signal is generated by the deflection of the axially adjustable switching ring, ie ultimately the axial deflection of the switching ring is to be detected.
- a differentiation can then be made between the pre-clamping torque and the triggering torque.
- a relative rotation can also be caused by the maxima between the adjusting ring and the part of the shut-off clutch which is non-rotatably connected to the drive shaft.
- the ratio of the height of the first maximum to the height of the second maximum is preferably 1.5:1 or greater, preferably 3:1 or greater and particularly preferably 4:1 or greater and more preferably 10: 1 or less, preferably 8:1 or less and more preferably 6:1 or less and most preferably 5:1. This also ensures that a clear differentiation can be made between the pre-shift torque and the triggering torque, which ultimately reduces the risk that the axial deflection of the switching ring induced by the pre-shift torque is held for the movement induced by the triggering torque.
- the amount of the derivation of the course of the control curve in the area of the first shifting contour and the second shifting contour is greater than 0. This ultimately provides a continuously rising control curve between the two shifting contours which, however, both the pre-shift torque and the release torque are delimited by a clearly defined shift contour. In addition, this ensures that after the release of the shut-off clutch and the shutting off and braking of the drive, the shifting element cannot permanently reach an intermediate position between the first shifting contour and the second shifting contour.
- the boundary contour of an adjacent second control cam is formed on the first switching contour of a first cam. In this way, in particular, the production outlay is further reduced.
- the edge of the delimiting contour is steeper than the first switching contour. This means that when the direction of travel of the drive is reversed—that is, to loosen an existing screw connection—the loosening torque is greater than the tightening torque of the screw connection.
- the shut-off clutch includes a cam ring which is connected to the drive shaft in a torque-proof manner and on which the cam ring is formed.
- a functional division is created in particular, the mechanical overload individual components.
- the switching element is designed as a switching ball.
- the shifting element is designed, for example, as a shifting cylinder that is guided on the cam.
- the restoring spring is designed as a compression spring whose spring force is adjustable.
- the spring force is adjustable.
- due to the adjustability of the spring force it can be achieved that different screw connections can be carried out with the electric hand-held power tool.
- FIG 1 shows a perspective view of an electric hand tool 1, which is formed in the embodiment shown as an industrial cordless screwdriver 2 with high precision, more precisely as a baton angle screwdriver 3, which is usually used in industrial series screw connections.
- This baton angle screwdriver 3 has a drive 5 accommodated in a housing 4, the direction of rotation of which can be adjusted by means of a control switch 6 in order to give the user the opportunity to undo a screw connection again.
- the electrical energy required to supply power to the drive 5 is provided by an accumulator 7 which is detachably attached to the baton angle screwdriver 3 .
- Accumulator 7 pioneering end is formed on the rod angle wrench 3 a receptacle 8, with the various attachments or tools can be connected. In the embodiment shown, this is an example of an angle head 9.
- the one in the figure 2 The section of a longitudinal section through the baton angle wrench 3 shown in the illustration shows that the drive 5 drives a drive shaft 11 via a gear 10 .
- the drive shaft 11 is non-positively connected to an output unit 13 via a mechanical shut-off clutch 12 .
- This output unit 13 ends in the receptacle 8 to which the various attachments or application tools can be attached.
- FIG. 1 shows a first embodiment of the shut-off clutch 12, this comprises a switching ring 15 which is mounted axially against the force of a return spring 14 and which is designed to be essentially non-rotatable with a switching element 16 which is formed as a switching ball 17 in the exemplary embodiment shown .
- the switching ball 17 runs on a control cam 18 which is formed on a cam ring 19 which is connected to the drive shaft 11 in a rotationally fixed manner.
- the torque applied by the drive 5 is introduced from the transmission 10 at the cam ring 19 into the shut-off clutch 12 and is ultimately transmitted to the output unit 13 when the shut-off clutch 12 is closed.
- the torque is transmitted from the control curve 18 formed on the cam ring 19 to the switching ring 15 via the switching element 16, which is provided in triplicate in the exemplary embodiment shown.
- the switching elements 16 are each accommodated captively on the switching ring 15 in a ball pocket 20, but have certain degrees of freedom of movement here.
- the Shift ring 15 is mounted on the output unit 13 axially against the force of the prestressed return spring 14 which is mounted between the shift ring 15 and a pressure ring 21 .
- the axial position of the pressure ring 21 in the direction of the receptacle 8 is limited by means of an adjusting ring 22 which is adjustably mounted on the output unit 13 via a threaded connection 23 .
- the cam ring 19 is rotatably mounted with respect to the output unit 13 in order to enable the relative rotation required for triggering the shut-off clutch 12 .
- the cam 18 is delimited at one end by a first switching contour 24 and at the other end by a delimiting contour 25 .
- the release torque of the shut-off clutch 12, which corresponds to the screwing torque is provided by the first shifting contour 24.
- the control cam 18 also includes a second switching contour 26, the function of which is explained in particular below with reference to FIG Figures 4 to 8 is explained in more detail.
- the second switching contour 26 becomes visible, which is formed between the delimiting contour 25 and the first switching contour 24 .
- This second switching contour 26 provides a pre-switching torque that is smaller than the triggering torque.
- the control curve 18 has a curve with a curvature or radius adapted to the switching element 16 in the area of the first switching contour 24, the control curve 18 has a constant gradient in the area of the second switching contour 26, i.e. it is ultimately a straight line educated.
- the amount of the derivation of the course of the cam 18 in the area of the first shifting contour 24 and the second shifting contour 26 is constantly greater than 0 and the second derivative of the course of the cam 18 is greater than or equal in the area of the first shifting contour 24 and the second shifting contour 26 0.
- the figure 4 can also be seen that on the first switching contour 24 of a first cam 18, the boundary contour 25 of an adjacent second cam 18 is formed.
- the Figures 5 to 7 show the course of the triggering behavior of the handheld power tool 1 according to the invention, implemented by the cam 18.
- the figure 5 shows the state of the shut-off clutch 12 during screwing.
- the shifting element 16 rests against the second shifting contour 26 which defines the pre-shift torque, and the torque is transmitted from the drive 5 via the transmission 10 and the closed shut-off clutch 12 to the output unit 13 .
- the torque of the drive 5 introduced at the cam ring 19 is transmitted to the switching ring 15 until the pre-shift torque is exceeded.
- the switching element 16 then slides on the second switching contour 26, as in FIG figure 6 shown.
- the switching ring 15 is adjusted axially against the force of the return spring 14 .
- This axial displacement of the switching ring 15 can now be detected, for example by means of a magnet and a corresponding Hall sensor, and used to prepare for or already initiate the switching off and braking of the drive 5 at this early point in time by means of appropriate drive electronics.
- the switching ring 15 moves further axially against the force of the return spring 14 misaligned. This is the particular figure 7 refer to.
- This displacement is now also detected, for example by the magnets already mentioned and the Hall sensor, and the switching off and braking of the drive 5 is completed and the screwing is thus ended.
- the force of the return spring 14 then presses the switching ring 15 with the switching element 16 back onto the control curve 18 of the cam ring 19.
- the second switching contour 26 ensures that an earlier signal for braking the drive shaft 11 occurs in good time so that the repeated triggering of the shut-off clutch 12 is avoided.
- the cam ring 19 continues to be rotated at a very low speed by the drive 5 until the second switching contour 26 reaches the switching element 16 . There it comes to a standstill.
- the shut-off clutch 12 is now in its starting position for the next screw connection, in which the switching element 16 rests against the second switching contour 26 .
- the first switching contour 24 has a switching point 31 whose tangent gradient defines the release torque of the shut-off clutch 12 .
- the pre-shift torque is defined by the slope of the tangent of a pre-shift point 32 which is associated with the second shift contour 26 .
- the tangent slope of the switching point 31 is greater than the tangent slope of the upstream switching point 32, which ultimately means that the upstream torque is smaller than the triggering moment, which is determined by the tangent slope in the switching point 31 of the first switching contour 24.
- the ratio between the gradient of the tangent of the switching point 31 and the gradient of the tangent of the upstream switching point 32 is around 2:1.
- the angle between the slope of the tangent of the switching point 31 and a plane 33 that is perpendicular to the drive shaft 11 is oriented between 60° and 70°.
- the angle between the slope of the tangent of the upstream switching point 32 and the plane 33 is between 30° and 35°.
- figure 9 shows a perspective view of a cam 18 of a second embodiment of the shut-off clutch 12.
- the cam 18 has a first maximum 34, which forms the first shifting contour 24 and defines the triggering moment, and a second maximum 35, which forms the second shifting contour 26 and the Pre-torque defined.
- the first maximum 34 is greater than the second maximum 35 and the ratio of the height of the first maximum 34 to the height of the second maximum 35 is 5:1.
- the slope of the edge of the first maximum 34 is greater than the slope of the edge of the second maximum 35.
- figure 10 and figure 11 show in a partially sectional view the axial adjustment of the switching ring 15 when the applied torque exceeds the pre-shift torque.
- the switching element 16, which is formed as a switching ball 17 is adjusted by the level of the second maximum 35, which forms the pre-shift torque. Due to the lower height of the second maximum 35 compared to the first maximum 34, there is also less axial displacement of the switching ring 15 than when the switching element 16 is adjusted by the height of the first maximum 34, which occurs when the shut-off clutch 12 is released. This difference in the axial adjustment can thus be used again in order to be able to differentiate whether the axial adjustment of the switching ring 15 was effected by the pre-clutching torque or by the triggering torque.
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Description
Die Erfindung betrifft eine elektrische Handwerkzeugmaschine, insbesondere einen Akkuschrauber, mit einem in einem Gehäuse aufgenommenen vorzugsweise elektrischen Antrieb, der eine Antriebswelle antreibt, mit einer Abtriebseinheit, die mittles einer mechanischen Abschaltkupplung mit dem Antrieb kraftschlüssig verbindbar ist, um Drehmoment von dem Antrieb auf ein mit der Abtriebseinheit verbundenes Einsatzwerkzeug zu übertragen, wobei die mechanische Abschaltkupplung einen axial gegen die Kraft einer Rückstellfeder gelagerten Schaltring und mindestens ein auf einer Steuerkurve geführtes Schaltelement umfasst, wobei die Steuerkurve einenends durch eine erste Schaltkontur zur Bereitstellung eines Auslösemoments der Abschaltkupplung und anderenends durch eine Begrenzungskontur begrenzt ist.The invention relates to an electric hand-held power tool, in particular a cordless screwdriver, with a preferably electric drive accommodated in a housing, which drives a drive shaft, with an output unit which can be non-positively connected to the drive by means of a mechanical shut-off clutch, in order to transfer torque from the drive to a to transfer the application tool connected to the output unit, wherein the mechanical shut-off clutch comprises a switching ring which is mounted axially against the force of a return spring and at least one switching element guided on a control cam, the control cam being limited at one end by a first switching contour for providing a release torque of the shut-off clutch and at the other end by a limiting contour is.
Das Dokument
Bei Schraubern, insbesondere bei Akkuschraubern, die für industrielle Serienverschraubungen, beispielsweise bei der Produktion von Automobilen, verwendet werden, besteht die Notwendigkeit, Verschraubungen prozesssicher, also bei einem definierten Anzugsmoment, mit sehr hoher Wiederholpräzision und bei einer möglichst hohen Einschraubdrehzahl durchzuführen. Ein derartiger Akkuschrauber ist beispielsweise aus der
Diese axiale Auslenkung des Schaltrings und damit letztlich das Öffnen der Abschaltkupplung wird üblicherweise als Sensorsignal verwendet, um den Antrieb abzuschalten und diesen ggf. zu bremsen und damit zum Stillstand zu bringen. Hierbei kommen verschiedene Techniken zum Einsatz. Insbesondere kann hier ein Mikroschalter zum Schalten verwendet werden oder durch die axiale Auslenkung auch ein Magnetfeld verändert werden. Im Rahmen der Erfindung ist es aber auch vorgesehen, dass hierzu bei der axialen Auslenkung des Schaltrings auch ein Schaltschieber mit einem darin aufgenommenen Magneten axial ausgelenkt wird. Mittels eines Hall-Sensors lässt sich die durch die axiale Auslenkung des Magneten induzierte Änderung des Magnetfelds erfassen, was dann als Sensorsignal zur Abschaltung des Antriebs verwendet werden kann.This axial deflection of the switching ring and thus ultimately the opening of the shut-off clutch is usually used as a sensor signal in order to switch off the drive and, if necessary, brake it and thus bring it to a standstill. Various techniques are used for this. In particular, a microswitch can be used here for switching or a magnetic field can also be changed by the axial deflection. In the context of the invention, however, it is also provided that, for this purpose, a switching slide with a magnet accommodated therein is also axially deflected during the axial deflection of the switching ring. Using a Hall sensor, the induced by the axial deflection of the magnet Detect changes in the magnetic field, which can then be used as a sensor signal to switch off the drive.
Nach dem Auslösen der Abschaltkupplung wird der Schaltring durch die Kraft der Rückstellfeder axial wieder in Richtung des Antriebs gedrückt und zwingt das Schaltelement wieder zurück auf die Steuerkurve. Der mit dem Antrieb drehfest verbundene Teil der Abschaltkupplung wird dann durch die vorhandene Rotationsenergie des Antriebs solange weitergedreht, bis der Motor zum Stillstand kommt. Bei einer geringen Drehzahl des Antriebs erfolgt das Ausschalten und Abbremsen des Antriebs dabei so schnell, dass ein erneutes Auslösen der Abschaltkupplung vermieden wird. Um einen definierten Schraubvorgang zu gewährleisten wird zudem häufig nach kurzer Zeit der Antrieb noch so lange mit einer sehr niedrigen Drehzahl weiterbetrieben, bis die erste Schaltkontur wieder an dem Schaltelement anliegt. Nun ist die Abschaltkupplung in ihrer Ausgangsposition für die nächste Verschraubung.After the shut-off clutch has been triggered, the force of the return spring pushes the switching ring axially back in the direction of the drive and forces the switching element back onto the control cam. The part of the shut-off clutch which is non-rotatably connected to the drive is then rotated further by the available rotational energy of the drive until the motor comes to a standstill. If the drive speed is low, the drive is switched off and braked so quickly that the shut-off clutch does not trip again. In order to ensure a defined screwing process, the drive is often continued to be operated at a very low speed after a short time until the first switching contour is again in contact with the switching element. The shut-off clutch is now in its starting position for the next screw connection.
Wenn jedoch der Verschraubungsvorgang bei einer zu hohen Einschraubdrehzahl vorgenommen wird, so besteht die Gefahr, dass die Rotationsenergie so groß ist, dass die Bremszeit nicht mehr ausreicht, um nach dem Auslösen der Abschaltkupplung den Motor so rechtzeitzeitig zum Stillstand zu bringen, dass die Abschaltkupplung tatsächlich nur einmal ausgelöst wird. Es kommt in diesen Fällen vielmehr zu mindestens einer weiteren Auslösung der Abschaltkupplung, bevor der Antrieb abgebremst wird und zum Stillstand kommt. Das mehrmalige Auslösen der Abschaltkupplung führt jedoch zu einem erhöhten Anzugsmoment und somit zu einer Prozessunsicherheit innerhalb des Verschraubungsprozesses. Zudem ist das Auslösen der Abschaltkupplung mit einem akustischen Effekt verbunden, der üblicherweise als Klack-Geräusch bezeichnet werden kann. Löst die Abschaltkupplung nun mehrmals aus, so ist dies für den Nutzer häufig irritierend, da dieser dann davon ausgeht, dass die Verschraubung fehlerhaft ausgeführt wurde, wenn er das Klack-Geräusch mehrfach wahrnimmt.However, if the screwing process is carried out at a screwing speed that is too high, there is a risk that the rotational energy is so great that the braking time is no longer sufficient to bring the motor to a standstill in good time after the shut-off clutch has been released so that the shut-off clutch actually stops only triggered once. Rather, in these cases there is at least one further triggering of the shut-off clutch before the drive is braked and comes to a standstill. However, the multiple triggering of the shut-off clutch leads to an increased tightening torque and thus to process uncertainty within the screwing process. In addition, the triggering of the shut-off clutch is associated with an acoustic effect that can usually be referred to as a clicking noise. If the shut-off clutch now releases several times, this is often irritating for the user, since he then assumes that the screw connection was incorrectly executed if he hears the clicking noise several times.
Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, die vorgenannten Nachteile zu reduzieren, insbesondere also eine Handwerkzeugmaschine bereitzustellen, die eine verbesserte Prozesssicherheit bei hohen Verschraubungsdrehzahlen bereitstellt.The object of the present invention is therefore to reduce the above-mentioned disadvantages, in particular to provide a hand-held power tool that provides improved process reliability at high screwing speeds.
Diese Aufgabe wird durch eine elektrische Handwerkzeugmaschine nach dem Anspruch 1 gelöst.This object is achieved by an electric hand tool according to claim 1.
Durch die zweite Schaltkontur wird letztlich ein Vorschaltmoment bereitgestellt, das ebenfalls zu einem axialen Auslenken des axial gegen die Kraft der Rückstellfeder gelagerten Schaltrings führt. Diese zusätzliche axiale Auslenkung wird dazu verwendet, bereits deutlich vor dem Erreichen des eigentlichen Auslösemoments, das letztlich dem Anzugsmoment entspricht, ein zeitlich vorgelagertes Vorschaltsignal zu erzeugen, um den Antrieb bereits zu diesem frühen Zeitpunkt abzuschalten oder abzubremsen oder zumindest diese Schritte bereits vorzubereiten. Im Rahmen der Erfindung ist es hierbei aber auch alternativ oder ergänzend vorgesehen, neben der Detektion der axialen Verstellung des Schaltrings, auch eine Relativverdrehung des Schalrings gegenüber dem drehfest mit der Antriebswelle verbundenen Teil der Abschaltkupplung zu detektieren. Diese Relativverdrehung tritt letztlich dann auf, wenn das Vorschaltmoment überschritten wird und das Schaltelement über die zweite Schaltkontur hinweg gleitet und dann an der ersten Schaltkontur zur Anlage kommt. Durch die zweite Schaltkontur kann also bereits vor dem eigentlichen Auslösen der Abschaltkupplung ein zunehmendes Drehmoment erfasst werden, um damit die Abschaltung oder ein Abbremsen des Antriebs einzuleiten oder vorzubereiten.The second switching contour ultimately provides a pre-shift torque, which also leads to an axial deflection of the switching ring, which is mounted axially against the force of the return spring. This additional axial deflection is used to generate an upstream signal well before the actual triggering torque is reached, which ultimately corresponds to the tightening torque, in order to switch off or brake the drive at this early point in time, or at least to prepare for these steps. Within the scope of the invention, however, it is also alternatively or additionally provided, in addition to detecting the axial adjustment of the switching ring, to also detect a relative rotation of the switching ring with respect to the part of the shut-off clutch non-rotatably connected to the drive shaft. This relative rotation ultimately occurs when the pre-shift torque is exceeded and the shifting element over the second shifting contour slides away and then comes to rest at the first switching contour. The second switching contour can therefore already detect an increasing torque before the actual triggering of the shut-off clutch, in order to initiate or prepare for shutting off or braking the drive.
Als vorteilhaft hat es sich hierbei auch erwiesen, wenn die erste Schaltkontur einen Schaltpunkt aufweist, dessen Tangentensteigung das Auslösemoment der Abschaltkupplung definiert, und wenn der Steuerkurve eine zweite Schaltkontur mit einem Vorschaltpunkt zugeordnet ist, dessen Tangentensteigung das Vorschaltmoment definiert, das kleiner ist als das Auslösemoment. Da sich anhand der Steigung der Tangente an dem Schaltpunkt beziehungsweise an dem Vorschaltpunkt das Auslösemoment beziehungsweise das Vorschaltmoment bestimmen lässt, wird hierdurch eine einfache Möglichkeit bereitgestellt, das Auslösemoment und das Vorschaltmoment zu definieren. In diesem Zusammenhang hat es sich dann auch als vorteilhaft gezeigt, wenn die Tangentensteigung in dem Schaltpunkt größer ist als die Tangentensteigung in dem Vorschaltpunkt. Sofern der Hub der zweiten Schaltkontur gleich oder geringer ist als der der ersten Schaltkontur, wird hierdurch beim Auslösen der zweiten Schaltkontur sichergestellt, dass das Vorschaltmoment deutlich von dem Auslösemoment der ersten Schaltkontur unterschieden werden kann.It has also proven to be advantageous here if the first shifting contour has a shifting point whose tangent slope defines the release torque of the shut-off clutch, and if the cam is assigned a second shifting contour with a pre-shift point whose tangent slope defines the pre-shift torque that is smaller than the release torque . Since the triggering torque or the pre-shifting torque can be determined on the basis of the slope of the tangent at the switching point or at the pre-shifting point, this provides a simple way of defining the triggering torque and the pre-shifting torque. In this context, it has also turned out to be advantageous if the gradient of the tangent at the switching point is greater than the gradient of the tangent at the upstream switching point. If the stroke of the second switching contour is the same as or less than that of the first switching contour, this ensures when the second switching contour is triggered that the pre-shift torque can be clearly distinguished from the triggering torque of the first switching contour.
Bewährt hat es sich auch, wenn das Verhältnis zwischen der Tangentensteigung des Schaltpunkts und der Tangentensteigung des Vorschaltpunkts vorzugsweise 1,2:1 oder größer, bevorzugt 1,5:1 oder größer und besonders bevorzugt 1,8:1 oder größer und weiter vorzugsweise 4:1 oder kleiner, bevorzugt 3:1 oder kleiner und ganz besonders bevorzugt 2:1 ist. Hierdurch wird gewährleistet, dass der Wert des Vorschaltmoments signifikant niedriger als der Wert des Auslösemoments ist, um eine sichere Unterscheidung zwischen dem Vorschaltmoment und dem Auslösemoment treffen zu können.It has also proven useful if the ratio between the gradient of the tangent of the switching point and the gradient of the tangent of the upstream switching point is preferably 1.2:1 or greater, preferably 1.5:1 or greater and particularly preferably 1.8:1 or greater and more preferably 4 :1 or less, preferably 3:1 or less and most preferably 2:1. This ensures that the value of the pre-shift torque is significantly lower than the value of the triggering torque in order to be able to make a reliable distinction between the pre-clamping torque and the triggering torque.
Außerdem hat es sich auch noch als vorteilhaft erwiesen, wenn der Winkel zwischen der Tangentensteigung des Schaltpunkts und einer Ebene, die senkrecht zu der Antriebswelle orientiert ist, vorzugsweise 50° oder größer, bevorzugt 55° oder größer und besonders bevorzugt 60° oder größer und weiter vorzugsweise 80° oder kleiner, bevorzugt 75° oder kleiner und besonders bevorzugt 70° oder kleiner ist. Wird dieser Winkel zu groß, so besteht die Gefahr, dass das Schaltelement beim Auslösen der Abschaltkupplung nur erschwert über die erste Schaltkontur gleiten kann, dass also insbesondere das Auslösemoment zu stark ansteigt. In diesem Zusammenhang hat es sich dann auch als besonders vorteilhaft gezeigt, wenn der Winkel zwischen der Tangentensteigung des Vorschaltpunkts und einer Ebene, die senkrecht zu der Antriebswelle orientiert ist, vorzugsweise 20° oder größer, bevorzugt 25° oder größer und besonders bevorzugt 30° oder größer und weiter vorzugsweise 45° oder kleiner, bevorzugt 40° oder kleiner und besonders bevorzugt 35° oder kleiner ist.-Auch hierdurch wird dann erreicht, dass eine geeignete Differenzierung zwischen dem Vorschaltmoment und dem Auslösemoment vorgenommen werden kann.In addition, it has also proven to be advantageous if the angle between the slope of the tangent of the switching point and a plane that is oriented perpendicularly to the drive shaft is preferably 50° or greater, preferably 55° or greater and particularly preferably 60° or greater and greater preferably 80° or less, preferably 75° or less, and more preferably 70° or less. If this angle becomes too large, there is a risk that the shifting element can only slide over the first shifting contour with difficulty when the shut-off clutch is released, ie that the release torque in particular increases too much. In this context, it has also been found to be particularly advantageous if the angle between the slope of the tangent of the upstream switching point and a plane which is oriented perpendicularly to the drive shaft is preferably 20° or greater, preferably 25° or greater and particularly preferably 30° or is greater and more preferably 45° or less, preferably 40° or less and particularly preferably 35° or less. This also ensures that a suitable differentiation can be made between the pre-clutching torque and the triggering torque.
Fertigungstechnisch hat es sich hierbei auch als vorteilhaft gezeigt, wenn die Steuerkurve im Bereich der zweiten Schaltkontur eine konstante Steigung aufweist. Insbesondere lässt sich dies fertigungstechnisch besonders einfach realisieren. Zudem kann durch den hierdurch entstehenden charakteristischen Anstieg des Moments erfasst werden, dass sich das Schaltelement im Bereich der zweiten Schaltkontur befindet, wodurch dann das Abschalten und/oder das Abbremsen des Antriebs initiiert oder ausgeführt werden kann. Zudem können durch die Erfassung und Auswertung der zeitlichen Dauer der axialen Auslenkung des Schaltrings bei einer bekannten Einschraubdrehzahl Rückschlüsse auf die Drehmomentrate gezogen werden. Je schneller die axiale Auslenkung erfolgt, desto härter ist auch der Schraubfall. Dies ermöglicht es damit letztlich das Ausschalt- oder Abbremsverhalten des Antriebs abhängig von der Härte des Schraubfalls zu steuern. So kann bei einem harten Schraubfall - also bei einem zeitlich kurzen Anstieg - ein frühzeitiges und starkes Bremsen initiiert werden, während bei einem weichen Schraubfall - also bei einem zeitlich längeren Anstieg - der Bremsvorgang später bzw. schwächer erfolgen oder sogar gänzlich unterbleiben kann. Das Abschalten beziehungsweise das Abbremsen des Antriebs wird dabei von einer Elektronik der Handwerkzeugmaschine gesteuert.In terms of manufacturing technology, it has also proven to be advantageous if the cam has a constant slope in the area of the second switching contour. In particular, this can be implemented particularly easily in terms of manufacturing technology. In addition, the resulting characteristic increase in torque can be used to detect that the shifting element is in the area of the second shifting contour, which then initiates or initiates the switching off and/or braking of the drive can be executed. In addition, by recording and evaluating the duration of the axial deflection of the switching ring at a known screwing-in speed, conclusions can be drawn about the torque rate. The faster the axial deflection occurs, the harder the screwdriving is. Ultimately, this makes it possible to control the switch-off or braking behavior of the drive depending on the hardness of the screwdriving application. In the case of a hard screwdriving operation - ie with a short increase in time - early and strong braking can be initiated, while in the case of a soft screwdriving operation - ie with a temporally longer increase - the braking process can take place later or more weakly or even be omitted entirely. The switching off or braking of the drive is controlled by electronics in the hand-held power tool.
Als günstig hat es sich aber auch erwiesen, wenn die Steuerkurve ein erstes Maximum, das das Auslösemoment definiert, und ein zweites Maximum umfasst, das das Vorschaltmoment definiert. Durch die Verwendung zweier Maxima wird letztlich erreicht, dass die Auslenkung des axial gegen die Federkraft der Rückstellfeder verstellbaren Schaltrings durch die zweite Schaltkontur zeitlich deutlich vor die Auslenkung durch die erste Schaltkontur verlagert werden kann. Bewährt hat es sich in diesem Zusammenhang aber insbesondere auch, wenn das erste Maximum größer ist als das zweite Maximum. Dies trägt dabei dem Umstand Rechnung, dass durch die Auslenkung des axial verstellbaren Schaltrings das Schaltsignal erzeugt wird, also letztlich die axiale Auslenkung des Schaltrings erfasst werden soll. Durch die unterschiedliche Höhe der Maxima kann dann eine Differenzierung zwischen dem Vorschaltmoment und dem Auslösemoment vorgenommen werden. Zudem kann durch die Maxima auch eine Relativverdrehung zwischen dem Stellring und dem mit der Antriebswelle drehfest verbundenen Teil der Abschaltkupplung einfacher erfasst werden.However, it has also proven to be advantageous if the control curve includes a first maximum, which defines the triggering torque, and a second maximum, which defines the pre-clutching torque. The use of two maxima ultimately means that the deflection of the switching ring, which can be adjusted axially against the spring force of the restoring spring, can be shifted by the second switching contour significantly before the deflection by the first switching contour. In this context, however, it has also proven particularly useful if the first maximum is greater than the second maximum. This takes into account the fact that the switching signal is generated by the deflection of the axially adjustable switching ring, ie ultimately the axial deflection of the switching ring is to be detected. Due to the different height of the maxima, a differentiation can then be made between the pre-clamping torque and the triggering torque. In addition, a relative rotation can also be caused by the maxima between the adjusting ring and the part of the shut-off clutch which is non-rotatably connected to the drive shaft.
Als vorteilhaft hat es sich auch erwiesen, wenn das Verhältnis der Höhe des ersten Maximums zu der Höhe des zweiten Maximums vorzugsweise 1,5:1 oder größer, bevorzugt 3:1 oder größer und besonders bevorzugt 4:1 oder größer und weiter vorzugsweise 10:1 oder kleiner, bevorzugt 8:1 oder kleiner und besonders bevorzugt 6:1 oder kleiner und ganz besonders bevorzugt 5:1 ist. Auch hierdurch wird sichergestellt, dass zwischen dem Vorschaltmoment und dem Auslösemoment klar differenziert werden kann, wodurch letztlich die Gefahr reduziert wird, dass die durch das Vorschaltmoment induzierte axiale Auslenkung des Schaltrings für die durch das Auslösemoment induzierte Bewegung gehalten wird.It has also proven to be advantageous if the ratio of the height of the first maximum to the height of the second maximum is preferably 1.5:1 or greater, preferably 3:1 or greater and particularly preferably 4:1 or greater and more preferably 10: 1 or less, preferably 8:1 or less and more preferably 6:1 or less and most preferably 5:1. This also ensures that a clear differentiation can be made between the pre-shift torque and the triggering torque, which ultimately reduces the risk that the axial deflection of the switching ring induced by the pre-shift torque is held for the movement induced by the triggering torque.
Im Rahmen der Erfindung hat es sich zudem als besonders vorteilhaft erwiesen, wenn der Betrag der Ableitung des Verlaufs der Steuerkurve im Bereich der ersten Schaltkontur und der zweiten Schaltkontur größer ist als 0. Hierdurch wird letztlich zwischen den beiden Schaltkonturen eine kontinuierlich ansteigende Steuerkurve bereitgestellt, bei der aber sowohl das Vorschaltmoment als auch das Auslösemoment jeweils durch eine klar definierte Schaltkontur abgegrenzt sind. Zudem wird hierdurch sichergestellt, dass nach dem Auslösen der Abschaltkupplung und dem Abschalten und Abbremsen des Antriebs das Schaltelement nicht permanent in eine Zwischenposition zwischen die erste Schaltkontur und die zweite Schaltkontur gelangen kann. Dies würde dann nämlich dazu führen, dass bei einem weiteren Schraubvorgang durch die Zwischenposition des Schaltelements das zweite Vorschaltmoment nicht genützt werden könnte, wodurch die Gefahr bestünde, dass der folgende Schraubvorgang nicht rechtzeitig beendet werde könnte und damit die Abschaltkupplung mehrmalig ausgelöst würde.In the context of the invention, it has also proven to be particularly advantageous if the amount of the derivation of the course of the control curve in the area of the first shifting contour and the second shifting contour is greater than 0. This ultimately provides a continuously rising control curve between the two shifting contours which, however, both the pre-shift torque and the release torque are delimited by a clearly defined shift contour. In addition, this ensures that after the release of the shut-off clutch and the shutting off and braking of the drive, the shifting element cannot permanently reach an intermediate position between the first shifting contour and the second shifting contour. This would then lead to the fact that in a further screwing process due to the intermediate position of the switching element, the second pre-clutching torque could not be used, which would result in the risk that the following screwing process would not work could be ended in time and thus the shut-off clutch would be triggered several times.
Bewährt hat es sich zudem, wenn die zweite Ableitung des Verlaufs der Steuerkurve im Bereich der ersten Schaltkontur und der zweiten Schaltkontur größer oder gleich 0 ist. Dies führt letztlich dazu, dass die Steigung - und damit das auf das Schaltelement wirkende Moment - kontinuierlich größer wird.It has also proven useful if the second derivative of the progression of the control curve is greater than or equal to 0 in the area of the first switching contour and the second switching contour. Ultimately, this means that the gradient—and thus the torque acting on the shifting element—becomes continuously greater.
Als günstig hat es sich auch erwiesen, wenn das Schaltelement und die Steuerkurve mehrfach, insbesondere dreifach vorgesehen sind. Hierdurch wird neben einem symmetrischen Aufbau der Abschaltkupplung insbesondere auch eine verbesserte Übertragung der Momente erreicht.It has also proven to be favorable if the switching element and the cam are provided in multiples, in particular in triplicate. In this way, in addition to a symmetrical design of the shut-off clutch, an improved transmission of the torques is achieved in particular.
Als vorteilhaft hat es sich auch gezeigt, wenn an der ersten Schaltkontur einer ersten Steuerkurve die Begrenzungskontur einer benachbarten zweiten Steuerkurve ausgebildet ist. Hierdurch wird insbesondere der Fertigungsaufwand weiter reduziert. In diesem Zusammenhang hat es sich zudem auch als günstig gezeigt, wenn die Flanke der Begrenzungskontur steiler ist als die erste Schaltkontur. Hierdurch wird dann nämlich erreicht, dass beim Umkehren der Laufrichtung des Antriebs - also zum Lösen einer bestehenden Schraubverbindung - das Lösemoment größer ist als das Anzugsmoment der Schraubverbindung.It has also proven to be advantageous if the boundary contour of an adjacent second control cam is formed on the first switching contour of a first cam. In this way, in particular, the production outlay is further reduced. In this context, it has also proven to be advantageous if the edge of the delimiting contour is steeper than the first switching contour. This means that when the direction of travel of the drive is reversed—that is, to loosen an existing screw connection—the loosening torque is greater than the tightening torque of the screw connection.
Als besonders günstig hat es sich zudem auch gezeigt, wenn die Abschaltkupplung einen drehfest mit der Antriebswelle verbundenen Nockenring umfasst, auf dem die Steuerkurve ausgebildet ist. Durch den vorzugsweise axial unverschiebbaren Nockenring wird insbesondere eine Funktionsaufteilung geschaffen, die einer mechanischen Überbelastung der einzelnen Bauteile vorbeugt. In diesem Zusammenhang hat es sich dann auch als vorteilhaft gezeigt, wenn das Schaltelement als eine Schaltkugel ausgebildet ist. Im Rahmen der Erfindung ist es hierbei aber auch vorgesehen, dass das Schaltelement beispielsweise als ein Schaltzylinder ausgebildet ist, der auf der Steuerkurve geführt ist.It has also proven to be particularly favorable if the shut-off clutch includes a cam ring which is connected to the drive shaft in a torque-proof manner and on which the cam ring is formed. By preferably axially non-displaceable cam ring a functional division is created in particular, the mechanical overload individual components. In this context, it has also been shown to be advantageous if the switching element is designed as a switching ball. In the context of the invention, however, it is also provided that the shifting element is designed, for example, as a shifting cylinder that is guided on the cam.
Bewährt hat es sich zudem auch, wenn die Rückstellfeder als eine Druckfeder ausgebildet ist, deren Federkraft einstellbar ist. Insbesondere durch die Verstellbarkeit der Federkraft kann erreicht werden, dass mit der elektrischen Handwerkzeugmaschine verschiedene Verschraubungen ausgeführt werden können.It has also proven itself when the restoring spring is designed as a compression spring whose spring force is adjustable. In particular, due to the adjustability of the spring force, it can be achieved that different screw connections can be carried out with the electric hand-held power tool.
Im Folgenden wird die Erfindung an mehreren in den Zeichnungen dargestellten Ausführungsbeispielen näher erläutert; es zeigen:
- Fig. 1
- eine perspektivische Ansicht einer Handwerkzeugmaschine,
- Fig. 2
- einen Ausschnitt eines Längsschnitts durch die Handwerkzeugmaschine aus der
Figur 1 , - Fig. 3
- eine Seitenansicht einer ersten Ausführungsform einer Abschaltkupplung,
- Fig. 4
- eine perspektivische Ansicht einer Steuerkurve der ersten Ausführungsform der Abschaltkupplung,
- Fig. 5
- einen ersten Schaltzustand der ersten Ausführungsform der Abschaltkupplung,
- Fig. 6
- einen zweiten Schaltzustand der ersten Ausführungsform der Abschaltkupplung,
- Fig. 7
- einen dritten Schaltzustand der ersten Ausführungsform der Abschaltkupplung,
- Fig. 8
- eine Detailansicht der Steuerkurve der ersten Ausführungsform der Abschaltkupplung,
- Fig. 9
- eine perspektivische Ansicht einer Steuerkurve einer zweiten Ausführungsform der Abschaltkupplung,
- Fig. 10
- einen ersten Schaltzustand der zweiten Ausführungsform der Abschaltkupplung, und
- Fig. 11
- einen zweiten Schaltzustand der zweiten Ausführungsform der Abschaltkupplung.
- 1
- a perspective view of a hand tool,
- 2
- a detail of a longitudinal section through the hand tool from the
figure 1 , - 3
- a side view of a first embodiment of a shut-off clutch,
- 4
- a perspective view of a cam of the first embodiment of the shut-off clutch,
- figure 5
- a first switching state of the first embodiment of the shut-off clutch,
- 6
- a second switching state of the first embodiment of the shut-off clutch,
- 7
- a third switching state of the first embodiment of the shut-off clutch,
- 8
- a detailed view of the cam of the first embodiment of the shut-off clutch,
- 9
- a perspective view of a cam of a second embodiment of the shut-off clutch,
- 10
- a first switching state of the second embodiment of the shut-off clutch, and
- 11
- a second switching state of the second embodiment of the shut-off clutch.
Akkumulator 7 wegweisenden Ende ist an dem Stabwinkelschrauber 3 eine Aufnahme 8 ausgebildet, mit der verschiedene Aufsätze oder Einsatzwerkzeuge verbunden werden können. In dem gezeigten Ausführungsbeispiel ist dies exemplarisch ein Winkelkopf 9.
Dem in der
Wie insbesondere auch der
Aus der
Die
Der
- 11
- Handwerkzeugmaschinehand tool
- 22
- Akkuschraubercordless screwdriver
- 33
- Stabwinkelschrauberbaton angle wrench
- 44
- GehäuseHousing
- 55
- Antriebdrive
- 66
- Stellschalterdial switch
- 77
- Akkumulatoraccumulator
- 88th
- AufnahmeRecording
- 99
- Winkelkopfangle head
- 1010
- Getriebetransmission
- 1111
- Antriebswelledrive shaft
- 1212
- Abschaltkupplungshut-off clutch
- 1313
- Abtriebseinheitoutput unit
- 1414
- Rückstellfederreturn spring
- 1515
- Schaltringswitching ring
- 1616
- Schaltelementswitching element
- 1717
- Schaltkugelshift ball
- 1818
- Steuerkurvecam
- 1919
- Nockenringcam ring
- 2020
- Kugeltascheball pocket
- 2121
- Druckringpressure ring
- 2222
- Stellringcollar
- 2323
- Gewindeverbindungthreaded connection
- 2424
- erste Schaltkonturfirst switching contour
- 2525
- Begrenzungskonturboundary contour
- 2626
- zweite Schaltkontursecond switching contour
- 3131
- Schaltpunktswitching point
- 3232
- Vorschaltpunktupstream switching point
- 3333
- Ebenelevel
- 3434
- erstes Maximumfirst max
- 3535
- zweites Maximumsecond maximum
Claims (15)
- Electric hand-held machine tool (1), in particular cordless screwdriver (2), having a preferably electric drive (5), which is accommodated in a housing (4) and drives a drive shaft (11), having an output drive unit (13), configured to be in frictional connection to the drive (5) by means of a mechanical shut-off clutch (12), in order to transmit torque from the drive (5) to an insert tool connected to the output drive unit (13), wherein the mechanical cut-off clutch (12) comprises a switch ring (15) mounted axially against the force of a return spring (14) and at least one switch element (16) guided on a control curve (18), wherein the control curve (18) is bounded at one end by a first switch contour (24), which serves to provide a release torque of the cut-off clutch (12), when the switch element (16) slides over the first switch contour (24) and thereby generates a sensor signal to disengage the drive (5), and wherein the control curve (18) is delimited at the other end by a delimiting contour (25), characterized in that a second switch contour (26) is assigned to the control curve (18), which serves to provide a pre-switch torque, when the switch element (16) slides over the second switch contour (26) and is thereby configured to generate a pre-switch signal, which precedes the sensor signal in time, wherein the pre-switch torque is smaller than the triggering torque.
- Electric hand-held machine tool (1) according to claim 1, characterized in that the first switch contour (24) has a switch point (31) whose tangent slope defines the tripping torque of the cut-off clutch (12), and in that the control curve (18) is assigned a second switch contour (26) having a pre-switch point (32) whose tangent slope defines the pre-switch torque which is smaller than the tripping torque.
- Hand-held machine tool (1) according to claim 2, characterized in that the tangent slope of the switch point (31) is greater than the tangent slope of the pre-switch point (32).
- Hand-held machine tool (1) according to claim 2 or 3, characterized in that the ratio between the tangent slope of the switch point (31) and the tangent slope of the pre-switch point (32) is preferably 1.2:1 or greater, preferably 1.5:1 or greater and particularly preferably 1.8:1 or greater, and further preferably 4:1 or less, preferably 3:1 or less and very particularly preferably 2:1.
- Hand-held machine tool (1) according to any one of claims 2 to 4, characterized in that the angle between the tangent slope of the switch point (31) and a plane (33) oriented perpendicular to the drive shaft (11) is preferably 50° or greater, preferably 55° or greater, and particularly preferably 60° or greater, and further preferably 80° or less, preferably 75° or less, and particularly preferably 70° or less.
- Hand-held machine tool (1) according to any one of claims 2 to 5, characterized in that the angle between the tangent slope of the pre-switch point (32) and the plane (33) oriented perpendicular to the drive shaft (11) is preferably 20° or greater, preferably 25° or greater, and more preferably 30° or greater, and further preferably 45° or less, preferably 40° or less, and more preferably 35° or less.
- Hand-held machine tool (1) according to any one of claims 1 to 6, characterized in that the control curve (18) has a constant slope in the region of the second switch contour (26).
- Hand-held machine tool (1) according to one of claims 1 to 7, characterized in that the control curve (18) comprises a first maximum (34), which defines the triggering torque, and a second maximum (35), which defines the pre-switch torque.
- Hand-held machine tool (1) according to claim 8, characterized in that the first maximum (34) is greater than the second maximum (35).
- Hand-held machine tool (1) according to claim 8 or 9, characterized in that the ratio of the height of the first maximum (34) to the height of the second maximum (35) is preferably 1.5:1 or greater, preferably 3:1 or greater and most preferably 4:1 or greater, and further preferably 10:1 or less, preferably 8:1 or less and most preferably 6:1 or less and most preferably 5:1.
- Hand-held machine tool (1) according to one of claims 1 to 10, characterized in that the magnitude of the derivative of the course of the control curve (18) in the region of the first switch contour (24) and the second switch contour (26) is greater than 0.
- Hand-held machine tool (1) according to one of claims 1 to 11, characterized in that the second derivative of the course of the control curve (18) in the region of the first switch contour (24) and the second switch contour (26) is greater than or equal to 0.
- Hand-held machine tool (1) according to one of claims 1 to 12, characterized in that the switch element (16) and the control curve (18) are provided in multiple, in particular in triplicate.
- Hand-held machine tool (1) according to one of claims 1 to 13, characterized in that the delimiting contour (25) of an adjacent second control curve (18) is formed on the first sift contour (24) of a first control curve (18).
- Hand-held machine tool (1) according to one of claims 1 to 14, characterized in that the cut-off clutch (12) comprises a cam ring (19), which is connected to the drive shaft (11) in a rotationally fixed manner and on which the control curve (18) is formed.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202019106525.7U DE202019106525U1 (en) | 2019-11-22 | 2019-11-22 | Hand machine tool |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3825063A1 EP3825063A1 (en) | 2021-05-26 |
EP3825063B1 true EP3825063B1 (en) | 2023-08-09 |
Family
ID=73497693
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20208763.1A Active EP3825063B1 (en) | 2019-11-22 | 2020-11-19 | Manual machine tool |
Country Status (6)
Country | Link |
---|---|
US (1) | US11701758B2 (en) |
EP (1) | EP3825063B1 (en) |
CN (1) | CN112828817B (en) |
DE (1) | DE202019106525U1 (en) |
ES (1) | ES2964576T3 (en) |
HU (1) | HUE063690T2 (en) |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2820381A (en) * | 1956-04-04 | 1958-01-21 | Kent Moore Organization Inc | Reversible, torque-limiting wrench |
US3442362A (en) * | 1967-08-31 | 1969-05-06 | Ingersoll Rand Co | Torque release and shut-off mechanism for pneumatic tools |
US3596542A (en) * | 1969-05-01 | 1971-08-03 | Chicago Pneumatic Tool Co | Pneumatic push-start, torque shut-off screw driver |
DE3510605A1 (en) * | 1985-03-23 | 1986-10-02 | C. & E. Fein Gmbh & Co, 7000 Stuttgart | CLUTCH FOR POWER DRIVEN SCREW TOOLS |
JPH0825146B2 (en) * | 1990-09-19 | 1996-03-13 | 株式会社マキタ | Clutch device in electric screwdriver |
US5372206A (en) * | 1992-10-01 | 1994-12-13 | Makita Corporation | Tightening tool |
US5505676A (en) * | 1994-01-25 | 1996-04-09 | The Stanley Works | Clutch torque control |
FR2776220B1 (en) * | 1998-03-19 | 2000-05-05 | Maire Charles Ets | PNEUMATIC SCREWDRIVER |
DE19845018C1 (en) * | 1998-09-30 | 1999-12-16 | Fein C & E | Powered screwdriver tool |
SE520916C2 (en) * | 1999-12-28 | 2003-09-09 | Atlas Copco Tools Ab | Nut wrench with torque clutch with trigger sensor for power shut-off |
DE10124569A1 (en) * | 2001-05-14 | 2002-11-21 | C & E Fein Gmbh & Co Kg | Power driven screwdriver with torque limiting clutch |
DE102004038829A1 (en) * | 2004-08-04 | 2006-03-16 | C. & E. Fein Gmbh | Screwdrivers |
JP4359716B2 (en) * | 2004-10-21 | 2009-11-04 | 株式会社マキタ | Tightening tool |
DE102004059331B4 (en) * | 2004-12-09 | 2021-02-18 | Robert Bosch Gmbh | Hand machine tool with a clutch |
US7665392B2 (en) * | 2006-02-08 | 2010-02-23 | Makita Corporation | Tightening tool |
DE102015201573A1 (en) * | 2015-01-29 | 2016-08-04 | Robert Bosch Gmbh | Impact device, in particular for an impact wrench |
DE102016220001A1 (en) * | 2015-10-15 | 2017-04-20 | Robert Bosch Gmbh | Hand tool |
DE102017102497A1 (en) * | 2017-02-08 | 2018-08-09 | C. & E. Fein Gmbh | Torque-dependent releasable coupling for a hand tool |
US10801552B2 (en) * | 2018-07-26 | 2020-10-13 | C&E Fein Gmbh | Torque-dependant, releasable clutch for a hand-held power tool |
-
2019
- 2019-11-22 DE DE202019106525.7U patent/DE202019106525U1/en active Active
-
2020
- 2020-11-19 HU HUE20208763A patent/HUE063690T2/en unknown
- 2020-11-19 ES ES20208763T patent/ES2964576T3/en active Active
- 2020-11-19 EP EP20208763.1A patent/EP3825063B1/en active Active
- 2020-11-20 CN CN202011313322.3A patent/CN112828817B/en active Active
- 2020-11-23 US US17/101,776 patent/US11701758B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
HUE063690T2 (en) | 2024-02-28 |
CN112828817B (en) | 2022-11-15 |
US20210154807A1 (en) | 2021-05-27 |
DE202019106525U1 (en) | 2021-02-26 |
EP3825063A1 (en) | 2021-05-26 |
CN112828817A (en) | 2021-05-25 |
US11701758B2 (en) | 2023-07-18 |
ES2964576T3 (en) | 2024-04-08 |
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