EP1301726A1 - Electromagnetically actuated, single-surface friction coupling, without a rotor slip ring - Google Patents

Electromagnetically actuated, single-surface friction coupling, without a rotor slip ring

Info

Publication number
EP1301726A1
EP1301726A1 EP01957967A EP01957967A EP1301726A1 EP 1301726 A1 EP1301726 A1 EP 1301726A1 EP 01957967 A EP01957967 A EP 01957967A EP 01957967 A EP01957967 A EP 01957967A EP 1301726 A1 EP1301726 A1 EP 1301726A1
Authority
EP
European Patent Office
Prior art keywords
armature
rotor
axially
friction clutch
rotor element
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.)
Withdrawn
Application number
EP01957967A
Other languages
German (de)
French (fr)
Inventor
Rudolf Schneider
Helmut Fronius
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE2000135277 external-priority patent/DE10035277A1/en
Priority claimed from DE2000135276 external-priority patent/DE10035276A1/en
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP1301726A1 publication Critical patent/EP1301726A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
    • F16D27/112—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members with flat friction surfaces, e.g. discs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D2027/008—Details relating to the magnetic circuit, or to the shape of the clutch parts to achieve a certain magnetic path

Definitions

  • the invention relates to an electromagnetically actuated, slip ring-free single-face friction clutch with a cup-shaped anchor element.
  • An electromagnetically actuated friction clutch with such an anchor element is shown in the unpublished DE 199 51 630.
  • This coupling has a rotatably mounted rotor element, a fixed magnetic body with a magnet coil and a rotatable, but axially displaceably mounted, pot-like anchor element.
  • the anchor element has an annular disk-shaped area and a cylindrical jacket-shaped area.
  • the armature element dips into an annular groove of the magnet body with a cylinder-shaped region, it being possible for magnetic flux to be transmitted via a narrow, radial air gap.
  • This type of electromagnetically actuated clutches is inexpensive to manufacture, requires little space and is highly reliable.
  • Such a coupling is suitable for hand-held impact drills for selectively coupling or uncoupling the drive motor from the output side
  • the coupling responds to high loads and / or deflection movements of the housing of the impact drill, such as occur when the drilling tool gets caught. This can avoid a risk of injury to the machine operator.
  • the coupling described in DE 199 51 630 is intended to be installed in an impact drill in such a way that the rotor element is constantly driven by the drive motor and the armature element. ment is constantly connected to the drilling tool or the drilling tool holder.
  • the invention is therefore based on the object of reducing the undesirable reaction moments which can still occur after the clutch has been released to a minimum.
  • the clutch should also be able to be further developed in such a way that the time until the drive side comes to a standstill after a triggering process.
  • the rotor element is on the output side and the armature element is on the drive side. arranged on the side. Due to the shape of the pot, the anchor element on its cylindrical surface at a large distance from the center of rotation has considerable portions of its total mass and therefore has a large moment of inertia. In contrast, the rotor element has a smaller diameter and lower mass fractions that are far from the center of rotation. It therefore has a much smaller mass moment of inertia, which means that the angular momentum that has to be reduced on the output side after the clutch is released is much smaller. Tear out of a hand-held tool after the clutch has been released is reduced to a minimum.
  • the friction surface of the rotor element is assigned to the side of the annular disk-shaped region of the armature element, which lies opposite the region of the armature element in the form of a cylinder jacket.
  • the friction surface of the rotor element lies, so to speak, outside the cup-shaped armature on the pot bottom, the rotor element lying essentially outside the axial installation space occupied by the armature element.
  • the rotor element is therefore very close to the output side, which enables a short, output-side shaft with a correspondingly small moment of inertia.
  • the anchor element can be axially displaced between two end positions, it being in the the first end position is frictionally coupled to the rotor element and in the second end position is frictionally connected to a stationary brake ring.
  • This embodiment can advantageously be developed in that the armature element is connected or connectable to an armature shaft by means of an axially deflectable spring element, the armature element being biased axially against the brake ring by the spring element.
  • this brake which is formed by simple means, is actuated by the biasing force of the spring element.
  • ⁇ sondere in combination with an embodiment in which the friction surface of the rotor element is assigned to the side of the ringschei- benförmigen portion of the anchor element which faces the cylinder jacket-shaped portion of the anchor element, is provided with extremely simple means, a clutch-brake combination.
  • the anchor element then has a friction surface at both axial ends.
  • a friction surface is arranged on the ring disk-shaped area of the armature, so to speak on the bottom of the pot, opposite the rotor element and a friction surface on the end face of the cylinder jacket-shaped area opposite the brake ring.
  • the friction surfaces of the rotor element and the brake ring form axial stops, between which the armature element can be moved back and forth.
  • a space-saving design of the coupling is characterized in that a flange is provided on the armature shaft for connection to the spring element, which carries the armature element, which conducts a magnetic flux between the magnet body and the rotor element in the case of a current-carrying magnet coil. If a first part of the flange extends axially along an inner circumferential surface of the magnet body with a narrow radial air gap and a second part of the flange comprises a hub of the rotor element with a narrow radial air gap, the magnetic flux can in each case with little over the narrow radial air gaps
  • the flange In addition to the function of mechanically coupling the armature element to the drive-side armature shaft, the flange also fulfills the function of magnetically coupling the rotor element to the magnet body.
  • the electromagnetically actuated coupling according to the invention and its embodiments are suitable due to their low output moment of inertia, their compact design and their low manufacturing costs for the optional coupling or decoupling of a drive motor and a drilling or percussion drilling tool in a hand-held drilling or percussion drilling machine.
  • 2 denotes a rotor element arranged on a rotor shaft 4.
  • the rotor shaft 4 is rotatably supported by means of bearings, not shown.
  • a fixed magnetic body 6 is provided with a magnetic coil 8, which is arranged between an inner lateral surface 10 and an outer lateral surface 12 of the magnetic body.
  • the magnetic body 6 is arranged fixed in the housing 14 of the clutch, so that the power supply to the magnetic coil 8 takes place without a slip ring.
  • a ball bearing 16 is NEN retaining ring 18 is held, which sits on a drive-side armature shaft 20.
  • a flange 22 sits on the armature shaft 20 in a rotationally fixed manner, to which an axially resilient but torsionally rigid spring element 26 is fastened by means of fastening screws 24.
  • a possible embodiment of the spring element is described in the aforementioned DE 199 51 630. It is stated that the content of this earlier application is included in the disclosure content of the present application.
  • the spring element 26 carries the anchor element 28, which is thus connected to the flange 22 in a torsionally rigid manner, but is axially deflectable relative to the flange.
  • the anchor element 28 is cup-shaped with an annular disk-shaped area 28A and a cylindrical jacket-shaped area 28B. There is a narrow radial air gap between the cylindrical jacket-shaped region 28B of the armature element and the outer jacket surface 12 of the magnet body 6, via which a magnetic flux can be transmitted from the armature element to the magnet body or vice versa.
  • a bridgeable, axial working air gap S is located between the annular-disk-shaped area 28A of the armature element and an axially opposite, annular-disk-shaped friction surface 30 of the rotor element 2 magnetic poles that create an attractive force. Due to the attractive force, the armature element 28 is deflected axially in the direction of the rotor element, so that the working air gap S is bridged and the two elements are connected to one another in a friction-locked manner.
  • the clutch takes up this switching position in a hand-held drill or impact drill during operation. A drilling or impact drilling tool is then driven by a drive motor.
  • the tool on the output side is decoupled from the drive motor by switching off the magnet coil 8.
  • the anchor element 28 is separated from the rotor element by a prestressing force of the spring element 26.
  • the output side of the clutch which is formed by the rotor element 2 and the rotor shaft 4, has only a very low mass moment of inertia, as a result of which a further deflection movement after the clutch is released is reduced to a minimum.
  • the friction surface 30 of the rotor element 2 shown in FIG. 1 is assigned to the side of the annular disk-shaped area 28A of the armature element 28, which lies opposite the cylinder jacket-shaped area 28B of the armature element 28.
  • the axial movement of the armature element 28 is limited on the one hand by the rotor element 2 and on the other hand by a brake ring 32.
  • the anchor element 28 is axially displaceable between two end positions, in the first, left end position it is frictionally coupled to the rotor element 2 and in the second, right end position it is in frictional engagement with the fixed brake ring 32.
  • the spring element 26 exerts an axial prestressing force on the armature element 28, by means of which the armature element is pressed axially against the brake ring.
  • the armature shaft 20 with the armature element 28 and the drive motor connected to it braked to a standstill in a short time. This means that the machine operator only has a very short waiting time before the machine is ready for operation again after a triggering process.
  • the flange 22 which establishes the drive connection between the armature shaft 20 and the spring element 26 or the armature element 28, extends with a narrow radial air gap along part of the inner circumferential surface 10 of the magnet body 6. A magnetic flux from the magnet body is generated via the narrow radial air gap transferred to the flange. In a second region of the flange, a hub 34 of the rotor element 2 with a narrow radial air gap is encompassed.
  • a magnetic flux which is represented by the line 36 and which occurs when the magnet coil 8 flows through current, thus flows from the radially inner circumferential surface 10 of the magnet body 6 via an air gap to the flange 22, from there via a narrow radial air gap to the hub 34 of the Rotor element, from there via the bridged working air gap S to the cup-shaped armature element 28 and from there via a narrow radial air gap to the outer lateral surface 12 of the magnet body 6.

Abstract

The invention relates to an electromagnetically actuated single-surface friction coupling without a rotor slip ring. Said coupling comprises: a rotor element (2), a fixed magnet body (6) and a well-shaped armature element (28) which can be displaced in an axial manner. A cylindrical jacket section (28B) of the armature element (28) extends along the external jacket surface (12) of the magnet body (6) and is separated from the latter by a narrow radial air-gap. A working air-gap (S), which can be bridged, is situated between the armature element (28) and a friction surface (30) of the rotor element. To maintain the lowest possible inertia torque for the power take-off, the rotor element (2) is located on the power take-off side and the armature element (28) is located on the drive side.

Description

Elektromagnetisch betätigbare, schleifringlose Einflächen-Reibungskupplung Electromagnetically operated, slip ring-free single-face friction clutch
Die Erfindung betrifft eine elektromagnetisch betätigbare, schleifringlose Einflächen-Reibungskupplung mit einem topfartig ausgebildeten Ankerelement.The invention relates to an electromagnetically actuated, slip ring-free single-face friction clutch with a cup-shaped anchor element.
Eine elektromagnetisch betätigbare Reibungskupplung mit einem derartigen Ankerelement ist in der nicht vorveröffentlichten DE 199 51 630 gezeigt. Diese Kupplung weist ein drehbar gelagertes Rotorelement, einen feststehenden Magnetkörper mit einer Magnetspule und ein drehbares, jedoch axial verschieblich gelagertes, topfartiges Ankerelement auf. Das Ankerelement weist einen ringscheibenförmigen Bereich und einen zylindermantelförmigen Bereich auf. Das Ankerelement taucht mit einem zylinderman- telförmigen Bereich in eine Ringnut des Magnetkorpers ein, wobei über einen engen, radialen Luftspalt Magnetfluß über- tragen werden kann. Diese Bauart von elektromagnetisch betätigbaren Kupplungen ist kostengünstig herstellbar, weist einen geringen Bauraumbedarf und eine hohe Zuverlässigkeit auf. Eine derartige Kupplung eignet sich bei handgeführten Schlagbohrmaschinen zum wahlweisen Kuppeln oder Entkuppeln des Antriebsmotors vom abtriebsseitigenAn electromagnetically actuated friction clutch with such an anchor element is shown in the unpublished DE 199 51 630. This coupling has a rotatably mounted rotor element, a fixed magnetic body with a magnet coil and a rotatable, but axially displaceably mounted, pot-like anchor element. The anchor element has an annular disk-shaped area and a cylindrical jacket-shaped area. The armature element dips into an annular groove of the magnet body with a cylinder-shaped region, it being possible for magnetic flux to be transmitted via a narrow, radial air gap. This type of electromagnetically actuated clutches is inexpensive to manufacture, requires little space and is highly reliable. Such a coupling is suitable for hand-held impact drills for selectively coupling or uncoupling the drive motor from the output side
Bohrwerkzeug. Die Kupplung spricht auf hohe Lasten und/oder Auslenkbewegungen des Gehäuses der Schlagbohrmaschine an, wie sie beim Verhaken des Bohrwerkzeugs auftreten. Hierdurch kann ein Verletzungsrisiko des Maschinenbedieners vermieden werden. Die in der DE 199 51 630 beschriebene Kupplung ist dafür vorgesehen, so in einer Schlagbohrmaschine eingebaut zu werden, daß das Rotorelement trieblich ständig mit dem Antriebsmotor und das Ankerele- ment trieblich ständig mit dem Bohrwerkzeug bzw. der Bohrwerkzeugaufnahme in Verbindung steht.Drilling tool. The coupling responds to high loads and / or deflection movements of the housing of the impact drill, such as occur when the drilling tool gets caught. This can avoid a risk of injury to the machine operator. The coupling described in DE 199 51 630 is intended to be installed in an impact drill in such a way that the rotor element is constantly driven by the drive motor and the armature element. ment is constantly connected to the drilling tool or the drilling tool holder.
Es hat sich gezeigt, daß, bedingt durch abtriebssei- tige Übersetzungen, nach dem Auslösen der Kupplung bis zum völligen Stillstand der abtriebsseitigen Elemente noch unerwünschte Reaktionsmomente auf das Gehäuse der Schlagbohrmaschine wirken.It has been shown that, owing to translations on the output side, after the clutch has been released until the elements on the output side have come to a complete standstill, undesirable reaction moments still act on the housing of the impact drill.
Ein weiteres Problem besteht darin, dass nach einem Auslösen der Kupplung zwar die Abtriebs-seite mit dem Bohrwerkzeug praktisch unmittelbar zum Stillstand kommt, die Antriebsseite der Kupplung und der Antriebsmotor nach Unterbrechung der Spannungsversorgung des Antriebsmotors, bedingt durch den gespeicherten Drehimpuls, jedoch noch einige Sekunden nachläuft. Die Maschine ist erst dann wieder betriebsbereit, wenn der Antriebsmotor zum Stillstand gekommen ist. Da in der Regel nach einem Auslösevorgang schnell wieder die Arbeit mit dem Bohrwerkzeug aufgenommen werden soll, wird die Zeit, die bis zum ' Stillstand der Antriebs-seite verstreicht, als unerträglich lange empfunden.Another problem is that after the clutch has been triggered, the output side with the drilling tool comes to a standstill almost immediately, the drive side of the clutch and the drive motor after a break in the power supply to the drive motor, due to the stored angular momentum, for a few seconds lags. The machine is only ready for operation again when the drive motor has come to a standstill. Because usually after a release operation quickly the work is to be included with the drill again, the time until the 'standstill side drive elapses, is perceived as unbearably long.
Der Erfindung liegt daher die Aufgabe zugrunde, die unerwünschten Reaktionsmomente, die noch nach dem Auslösen der Kupplung auftreten können, auf ein Minimum zu reduzieren. Die Kupplung soll außerdem so weitergebildet werden können, dass die Zeit bis zum Stillstand der Antriebsseite nach einem Auslösevorgang verkürzt wird.The invention is therefore based on the object of reducing the undesirable reaction moments which can still occur after the clutch has been released to a minimum. The clutch should also be able to be further developed in such a way that the time until the drive side comes to a standstill after a triggering process.
Diese Aufgabe wird gelöst durch eine elektromagnetisch betätigbare, schleifringlose Einflächen-Reibungskupplung mit den Merkmalen des Hauptanspruchs. Demnach ist also das Rotorelement abtriebsseitig und das Ankerelement antriebs- seitig angeordnet. Aufgrund der Topfform weist das Ankerelement an seiner Zylindermantelfläche in großem Abstand vom Drehzentrum erhebliche Anteile seiner Gesamtmasse auf und besitzt daher ein großes Massenträgheitsmoment. Das Rotorelement weist demgegenüber einen geringeren Durchmesser und geringere Massenanteile, die weit vom Drehzentrum entfernt sind, auf. Es besitzt daher ein sehr viel kleineres Massenträgheitsmoment, wodurch der Drehimpuls, der nach dem Auslösen der Kupplung abtriebsseitig abgebaut werden muß, sehr viel kleiner ist. Ein Ausreißen eines handgeführten Werkzeugs nach dem Auslösevorgang der Kupplung wird hierdurch auf ein Minimum reduziert.This object is achieved by an electromagnetically actuated, slip ring-free single-face friction clutch with the features of the main claim. Accordingly, the rotor element is on the output side and the armature element is on the drive side. arranged on the side. Due to the shape of the pot, the anchor element on its cylindrical surface at a large distance from the center of rotation has considerable portions of its total mass and therefore has a large moment of inertia. In contrast, the rotor element has a smaller diameter and lower mass fractions that are far from the center of rotation. It therefore has a much smaller mass moment of inertia, which means that the angular momentum that has to be reduced on the output side after the clutch is released is much smaller. Tear out of a hand-held tool after the clutch has been released is reduced to a minimum.
In einer vorteilhaften Ausgestaltung der Erfindung ist die Reibfläche des Rotorelements der Seite des ringscheibenförmigen Bereichs des Ankerelements zugeordnet, welche dem zylindermantelförmigen Bereich des Ankerelements gegenüberliegt. Im geschalteten Zustand der Kupplung liegt die Reibfläche des Rotorelements also sozusagen außerhalb des topfför igen Ankers am Topfboden an, wobei das Rotorelement im wesentlichen außerhalb des vom Ankerelement beanspruchten axialen Bauraums liegt. Das Rotorelement befindet sich dadurch sehr nahe an der Abtriebsseite, wodurch eine kurze, abtriebsseitige Welle mit entsprechend kleinem Trägheitsmoment ermöglicht wird.In an advantageous embodiment of the invention, the friction surface of the rotor element is assigned to the side of the annular disk-shaped region of the armature element, which lies opposite the region of the armature element in the form of a cylinder jacket. When the clutch is in the switched state, the friction surface of the rotor element lies, so to speak, outside the cup-shaped armature on the pot bottom, the rotor element lying essentially outside the axial installation space occupied by the armature element. The rotor element is therefore very close to the output side, which enables a short, output-side shaft with a correspondingly small moment of inertia.
Entsprechend dem höheren antriebsseitigen Massenträgheitsmoment der Kupplung verbleibt nach einem Auslösevorgang ein höherer antriebsseitiger Drehimpuls im System. Um die Zeit bis zum Stillstand der Antriebsseite nach einem Auslösevorgang zu verkürzen, ist in einer vorteilhaften Ausgestaltung der Erfindung das Ankerelement zwischen zwei Endlagen axial verschiebbar, wobei es in der ersten Endlage reibschlüssig mit dem Rotorelement gekoppelt ist und in der zweiten Endlage reibschlüssig an einem feststehenden Bremsring anliegt.In accordance with the higher drive moment of inertia of the clutch, a higher drive-side angular momentum remains in the system after a triggering process. In order to shorten the time until the drive side comes to a standstill after a triggering process, in an advantageous embodiment of the invention the anchor element can be axially displaced between two end positions, it being in the the first end position is frictionally coupled to the rotor element and in the second end position is frictionally connected to a stationary brake ring.
Diese Ausgestaltung kann vorteilhaft dadurch weitergebildet werden, daß das Ankerelement mittels eines axial auslenkbaren Federelements mit einer Ankerwelle verbunden bzw. verbindbar ist, wobei das Ankerelement durch das Federelement axial gegen den Bremsring vorgespannt ist. Im stromlosen Zustand, der nach einer Auslösung der Kupplung herrscht, wird diese mit einfachen Mitteln gebildete Bremse durch die Vorspannkraft des Federelements betätigt. Insbe¬ sondere in Kombination mit einer Ausführungsform, bei der die Reibfläche des Rotorelements der Seite des ringschei- benförmigen Bereichs des Ankerelements zugeordnet ist, welche dem zylindermantelförmigen Bereich des Ankerelements gegenüberliegt, wird mit äußerst einfachen Mitteln eine Kupplungs-Bremskombination geschaffen. Das Ankerelement weist dann an beiden axialen Enden jeweils eine Reibfläche auf. Eine Reibfläche ist am ringscheibenförmigen Bereich des Ankers, sozusagen am Topfboden, gegenüber dem Rotorelement und eine Reibfläche an der Stirnfläche des zylindermantelförmigen Bereichs gegenüber dem Bremsring angeordnet. Die Reibflächen des Rotorelements und des Bremsrings bilden axiale Anschläge, zwischen denen das Ankerelement hin- und herbewegbar ist.This embodiment can advantageously be developed in that the armature element is connected or connectable to an armature shaft by means of an axially deflectable spring element, the armature element being biased axially against the brake ring by the spring element. In the de-energized state, which prevails after the clutch has been triggered, this brake, which is formed by simple means, is actuated by the biasing force of the spring element. In particular ¬ sondere in combination with an embodiment in which the friction surface of the rotor element is assigned to the side of the ringschei- benförmigen portion of the anchor element which faces the cylinder jacket-shaped portion of the anchor element, is provided with extremely simple means, a clutch-brake combination. The anchor element then has a friction surface at both axial ends. A friction surface is arranged on the ring disk-shaped area of the armature, so to speak on the bottom of the pot, opposite the rotor element and a friction surface on the end face of the cylinder jacket-shaped area opposite the brake ring. The friction surfaces of the rotor element and the brake ring form axial stops, between which the armature element can be moved back and forth.
Eine bauraumgünstige Ausgestaltung der Kupplung zeichnet sich dadurch aus, daß auf der Ankerwelle ein Flansch zur Verbindung mit dem Federelement, welches das Ankerelement trägt, vorgesehen ist, welcher bei stromdurchflossener Magnetspule einen Magnetfluß zwischen dem Magnetkörper und dem Rotorelement leitet. Wenn ein erster Teil des Flansches sich mit engem radialen Luftspalt axial entlang einer inneren Mantelfläche des Magnetkorpers erstreckt und ein zweiter Teil des Flansches eine Nabe des Rotorelements mit engem radialen Luftspalt umfaßt, kann der Magnetfluß jeweils über die engen radialen Luftspalte mit geringemA space-saving design of the coupling is characterized in that a flange is provided on the armature shaft for connection to the spring element, which carries the armature element, which conducts a magnetic flux between the magnet body and the rotor element in the case of a current-carrying magnet coil. If a first part of the flange extends axially along an inner circumferential surface of the magnet body with a narrow radial air gap and a second part of the flange comprises a hub of the rotor element with a narrow radial air gap, the magnetic flux can in each case with little over the narrow radial air gaps
Verlust zwischen den mit unterschiedlichen Drehzahlen sich drehenden Teilen übertragen werden. Neben der Funktion, das Ankerelement an die antriebsseitige Ankerwelle mechanisch zu koppeln, wird von dem Flansch also auch die Funktion, das Rotorelement magnetisch an den Magnetkörper zu koppeln, erfüllt.Loss between the parts rotating at different speeds. In addition to the function of mechanically coupling the armature element to the drive-side armature shaft, the flange also fulfills the function of magnetically coupling the rotor element to the magnet body.
Die erfindungsgemäße, elektromagnetisch betätigbare Kupplung und ihre Ausführungsformen eignen sich aufgrund ihres geringen abtriebsseitigen Massenträgheitsmoments, ihrer kompakten Bauform und ihrer geringen Herstellkosten zur wahlweisen Koppelung bzw. Entkoppelung eines Antriebsmotors und eines Bohr- oder Schlagbohrwerkzeugs in einer handgeführten Bohr- oder Schlagbohrmaschine.The electromagnetically actuated coupling according to the invention and its embodiments are suitable due to their low output moment of inertia, their compact design and their low manufacturing costs for the optional coupling or decoupling of a drive motor and a drilling or percussion drilling tool in a hand-held drilling or percussion drilling machine.
Die Erfindung wird anhand der beigefügten Zeichnung näher erläutert.The invention is explained in more detail with reference to the accompanying drawing.
In der einzigen Figur ist mit 2 ein auf einer Rotor- welle 4 angeordnetes Rotorelement bezeichnet. Die Rotorwelle 4 ist mittels nicht dargestellter Lager drehbar gelagert. Ein feststehender Magnetkörper 6 ist mit einer Magnetspule 8 versehen, die zwischen einer inneren Mantelfläche 10 und einer äußeren Mantelfläche 12 des Magnetkorpers angeordnet ist. Der Magnetkörper 6 ist feststehend im Gehäuse 14 der Kupplung angeordnet, so daß die Stromversorgung der Magnetspule 8 schleifringlos erfolgt. Im Innenmantel 10 des Magnetkorpers 6 ist ein Kugellager 16 durch ei- nen Sicherungsring 18 gehalten, welches auf einer antriebs- seitigen Ankerwelle 20 sitzt. Auf der Ankerwelle 20 sitzt drehfest ein Flansch 22, an dem mittels Befestigungsschrauben 24 ein axial federndes, jedoch drehsteifes Federelement 26 befestigt ist. Eine mögliche Ausgestaltung des Federelements ist in der erwähnten DE 199 51 630 beschrieben. Es wird erklärt, daß der Inhalt dieser früheren Anmeldung vom Offenbarungsgehalt der vorliegenden Anmeldung umfaßt wird.In the single figure, 2 denotes a rotor element arranged on a rotor shaft 4. The rotor shaft 4 is rotatably supported by means of bearings, not shown. A fixed magnetic body 6 is provided with a magnetic coil 8, which is arranged between an inner lateral surface 10 and an outer lateral surface 12 of the magnetic body. The magnetic body 6 is arranged fixed in the housing 14 of the clutch, so that the power supply to the magnetic coil 8 takes place without a slip ring. In the inner casing 10 of the magnetic body 6, a ball bearing 16 is NEN retaining ring 18 is held, which sits on a drive-side armature shaft 20. A flange 22 sits on the armature shaft 20 in a rotationally fixed manner, to which an axially resilient but torsionally rigid spring element 26 is fastened by means of fastening screws 24. A possible embodiment of the spring element is described in the aforementioned DE 199 51 630. It is stated that the content of this earlier application is included in the disclosure content of the present application.
Das Federelement 26 trägt das Ankerelement 28, das somit drehsteif mit dem Flansch 22 verbunden ist, jedoch gegenüber dem Flansch axial auslenkbar ist. Das Ankerelement 28 ist topfförmig mit einem ringscheibenförmigen Be- reich 28A und einem zylindermantelförmigen Bereich 28B ausgebildet. Zwischen dem zylindermantelförmigen Bereich 28B des Ankerelements und der äußeren Mantelfläche 12 des Magnetkorpers 6 befindet sich ein enger radialer Luftspalt, über den ein Magnetfluß vom Ankerelement auf den Magnetkör- per bzw. umgekehrt übertragen werden kann. Zwischen dem ring-scheibenförmigen Bereich 28A des Ankerelements und einer axial gegenüberliegenden, ringscheibenförmigen Reibfläche 30 des Rotorelements 2 befindet sich ein überbrückbarer, axialer Arbeitsluftspalt S. Wird die Magnetspule 8 von elektrischem Strom durchflössen, bilden sich im Bereich des Arbeitsluftspalts S am Rotorelement und am Ankerelement magnetische Pole aus, die eine Anziehungskraft bewirken. Durch die Anziehungskraft wird das Ankerelement 28 axial in Richtung des Rotorelements ausgelenkt, so daß der Arbeits- luftspalt S überbrückt ist und die beiden Elemente reibschlüssig miteinander verbunden sind. Diese Schaltstellung nimmt die Kupplung in einer handgeführten Bohr- oder Schlagbohrmaschine während des Betriebs ein. Ein Bohr- bzw. Schlagbohrwerkzeug wird dann von einem Antriebsmotor angetrieben. Tritt eine Überlast auf oder wird eine über ein vorgegebenes Maß hinausgehende Auslenkbewegung des Gehäuses der Maschine festgestellt, so wird das abtriebsseitige Werkzeug vom Antriebsmotor entkoppelt, indem die Magnetspule 8 stromlos geschaltet wird. Durch eine Vorspannkraft des Federelements 26 wird das An- kerelement 28 vom Rotorelement getrennt.The spring element 26 carries the anchor element 28, which is thus connected to the flange 22 in a torsionally rigid manner, but is axially deflectable relative to the flange. The anchor element 28 is cup-shaped with an annular disk-shaped area 28A and a cylindrical jacket-shaped area 28B. There is a narrow radial air gap between the cylindrical jacket-shaped region 28B of the armature element and the outer jacket surface 12 of the magnet body 6, via which a magnetic flux can be transmitted from the armature element to the magnet body or vice versa. A bridgeable, axial working air gap S is located between the annular-disk-shaped area 28A of the armature element and an axially opposite, annular-disk-shaped friction surface 30 of the rotor element 2 magnetic poles that create an attractive force. Due to the attractive force, the armature element 28 is deflected axially in the direction of the rotor element, so that the working air gap S is bridged and the two elements are connected to one another in a friction-locked manner. The clutch takes up this switching position in a hand-held drill or impact drill during operation. A drilling or impact drilling tool is then driven by a drive motor. If an overload occurs or a deflection movement of the housing of the machine that goes beyond a predetermined amount is detected, the tool on the output side is decoupled from the drive motor by switching off the magnet coil 8. The anchor element 28 is separated from the rotor element by a prestressing force of the spring element 26.
Die Abtriebsseite der Kupplung, die vom Rotorelement 2 und der Rotorwelle 4 gebildet wird, weist nur ein sehr geringes Massenträgheitsmoment auf, wodurch eine weitere Aus- lenkbewegung nach der Auslösung der Kupplung auf ein Minimum reduziert wird.The output side of the clutch, which is formed by the rotor element 2 and the rotor shaft 4, has only a very low mass moment of inertia, as a result of which a further deflection movement after the clutch is released is reduced to a minimum.
Die Reibfläche 30 des in Fig. 1 dargestellten Rotorelements 2 ist der Seite des ringscheibenförmigen Be- reichs 28A des Ankerelements 28 zugeordnet, welche dem zylindermantelförmigen Bereich 28B des Ankerelements 28 gegenüberliegt. Die axiale Bewegung des Ankerelements 28 wird einerseits durch das Rotorelement 2 und auf der anderen Seite durch einen Bremsring 32 begrenzt. Das Ankerele- ment 28 ist zwischen zwei Endlagen axial verschiebbar, wobei es in der ersten, linken Endlage reibschlüssig mit dem Rotorelement 2 gekoppelt ist und in der zweiten, rechten Endlage reibschlüssig an dem feststehenden Bremsring 32 anliegt. Im stromlosen Zustand der Kupplung übt dabei das Federelement 26 eine axiale Vorspannkraft auf das Ankerelement 28 aus, durch welche das Ankerelement axial gegen den Bremsring gedrückt wird. Nach einem Auslösen der Kupplung wird die Ankerwelle 20 mit dem Ankerelement 28 sowie der damit trieblich verbundene Antriebsmotor in kurzer Zeit bis zum Stillstand abgebremst. Dadurch ergibt sich für den Ma- schinenbediener nur eine sehr kurze Wartezeit, bis die Maschine nach einem Auslösevorgang wieder betriebsbereit ist.The friction surface 30 of the rotor element 2 shown in FIG. 1 is assigned to the side of the annular disk-shaped area 28A of the armature element 28, which lies opposite the cylinder jacket-shaped area 28B of the armature element 28. The axial movement of the armature element 28 is limited on the one hand by the rotor element 2 and on the other hand by a brake ring 32. The anchor element 28 is axially displaceable between two end positions, in the first, left end position it is frictionally coupled to the rotor element 2 and in the second, right end position it is in frictional engagement with the fixed brake ring 32. In the currentless state of the clutch, the spring element 26 exerts an axial prestressing force on the armature element 28, by means of which the armature element is pressed axially against the brake ring. After triggering the clutch, the armature shaft 20 with the armature element 28 and the drive motor connected to it braked to a standstill in a short time. This means that the machine operator only has a very short waiting time before the machine is ready for operation again after a triggering process.
Der Flansch 22, der die triebliche Verbindung zwischen Ankerwelle 20 und dem Federelement 26 bzw. dem Ankerelement 28 herstellt, erstreckt sich mit engem radialen Luftspalt entlang einem Teil der inneren Mantelfläche 10 des Magnetkorpers 6. Über den engen radialen Luftspalt wird ein Magnetfluß von dem Magnetkörper auf den Flansch übertragen. In einem zweiten Bereich des Flansches wird eine Nabe 34 des Rotorelements 2 mit engem radialen Luftspalt umfaßt. Ein Magnetfluß, der durch die Linie 36 dargestellt ist und der sich bei stromdurchflossener Magnetspule 8 einstellt, fließt also von der radial inneren Mantelfläche 10 des Magnetkorpers 6 über einen Luftspalt auf den Flansch 22, von dort über einen engen radialen Luftspalt auf die Nabe 34 des Rotorelements, von dort über den überbrückten Arbeits- luftspalt S auf das topfförmige Ankerelement 28 und von dort über einen engen radialen Luftspalt auf die äußere Mantelfläche 12 des Magnetkorpers 6. The flange 22, which establishes the drive connection between the armature shaft 20 and the spring element 26 or the armature element 28, extends with a narrow radial air gap along part of the inner circumferential surface 10 of the magnet body 6. A magnetic flux from the magnet body is generated via the narrow radial air gap transferred to the flange. In a second region of the flange, a hub 34 of the rotor element 2 with a narrow radial air gap is encompassed. A magnetic flux, which is represented by the line 36 and which occurs when the magnet coil 8 flows through current, thus flows from the radially inner circumferential surface 10 of the magnet body 6 via an air gap to the flange 22, from there via a narrow radial air gap to the hub 34 of the Rotor element, from there via the bridged working air gap S to the cup-shaped armature element 28 and from there via a narrow radial air gap to the outer lateral surface 12 of the magnet body 6.
Bezugs zeichenReference sign
2 Rotorelement2 rotor element
4 Rotorwelle4 rotor shaft
6 Magnetkörper6 magnetic bodies
8 Magnetspule8 solenoid
10 innere Mantelfläche10 inner lateral surface
12 äußere Mantelfläche12 outer surface
14 Gehäuse14 housing
16 Lager16 bearings
18 Sicherungsring18 circlip
20 Ankerwelle20 armature shaft
22 Flansch22 flange
24 Schraube24 screw
26 Federelement26 spring element
28 Ankerelement28 anchor element
28A ringscheibenförmiger Bereich28A ring-shaped area
28B zylindermantelförmiger Bereich28B cylinder jacket-shaped area
30 Reibfläche30 friction surface
32 Bremsring32 brake ring
34 Nabe34 hub
36 Magnetfluß 36 magnetic flux

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Elektromagnetisch betätigbare, schleifringlose Ein- flächen-Reibungskupplung mit einem drehbar gelagerten1. Electromagnetically actuated, slip ring-free single-surface friction clutch with a rotatably mounted one
Rotorelement (2), mit einem feststehenden Magnetkörper (6), welcher mit einer Magnetspule (8) versehen ist und mit einem drehbaren, jedoch axial verschieblich gelagerten Ankerelement (28), wobei das Ankerelement (28) topfartig mit einem ringscheibenförmigen Bereich (28A) und einem zylindermantelförmigen Bereich (28B) ausgebildet ist, wobei sich der zylindermantelförmige Bereich des Ankerelements (28B) mit engem radialen Luftspalt axial entlang einer äußeren Mantelfläche (12) des Magnetkorpers erstreckt, und zwischen dem ringscheibenförmigen Bereich (28A) des Ankerelements und einer axial gegenüberliegenden, ringscheibenförmigen Reibfläche (30) des Rotorelements (2) ein überbrückbarer, axialer Arbeitsluftspalt (S) vorhanden ist, wobei das Ankerelement (28) durch Magnetkraft axial verschiebbar und reibschlüssig mit dem Rotorelement (2) kuppelbar ist, und wobei das Rotorelement (2) abtriebsseitig und das Ankerelement (28) antriebsseitig angeordnet ist.Rotor element (2), with a fixed magnetic body (6), which is provided with a magnetic coil (8) and with a rotatable, but axially displaceably mounted armature element (28), the armature element (28) being cup-shaped with an annular disk-shaped area (28A) and a cylindrical jacket-shaped region (28B) is formed, the cylindrical jacket-shaped region of the armature element (28B) with a narrow radial air gap extending axially along an outer lateral surface (12) of the magnetic body, and between the annular disk-shaped region (28A) of the armature element and an axially opposite one , an annular disk-shaped friction surface (30) of the rotor element (2) has an axial working air gap (S) which can be bridged, the armature element (28) being axially displaceable and frictionally coupled to the rotor element (2) by magnetic force, and the rotor element (2) on the output side and the anchor element (28) is arranged on the drive side.
2. Reibungskupplung nach Anspruch 1, dadurch g e - k e n n z e i c h n e t , daß die Reibfläche (30) des2. A friction clutch according to claim 1, characterized in that the friction surface (30) of the
Rotorelements der Seite des ringscheibenförmigen Bereichs (28A) des Ankerelements (28) zugeordnet ist, welche dem zylindermantelförmigen Bereich (28B) des Ankerelements (28) gegenüberliegt.The rotor element is assigned to the side of the annular disk-shaped region (28A) of the anchor element (28), which is opposite to the cylinder jacket-shaped region (28B) of the anchor element (28).
3. Reibungskupplung nach Anspruch 1 oder 2, dadurch g e k e n n z e i c h n e t , daß das Ankerelement (28) zwischen zwei Endlagen axial verschiebbar ist, wobei es in der ersten Endlage reibschlüssig mit dem Rotorelement (2) gekoppelt ist und in der zweiten Endlage reibschlüssig an einem feststehenden Bremsring (32) anliegt.3. A friction clutch according to claim 1 or 2, characterized in that the anchor element (28) is axially displaceable between two end positions, wherein it the first end position is frictionally coupled to the rotor element (2) and in the second end position is frictionally connected to a fixed brake ring (32).
4. Reibungskupplung nach Anspruch 3, dadurch g e k e n n z e i c h n e t , daß das Ankerelement (28) mittels eines axial auslenkbaren Federelements (26) mit einer Ankerwelle (20) verbunden ist, wobei das Ankerelement (28) durch das Federelement (26) axial gegen den Bremsring (32) vorgespannt ist.4. Friction clutch according to claim 3, characterized in that the armature element (28) is connected by means of an axially deflectable spring element (26) to an armature shaft (20), the armature element (28) by the spring element (26) axially against the brake ring ( 32) is biased.
5. Reibungskupplung nach Anspruch 4, dadurch g e k e n n z e i c h n e t , daß auf der Ankerwelle (20) ein Flansch zur Verbindung mit dem Federelement (26) vorgesehen ist, der bei stromdurchflossener Magnetspule (8) einen5. A friction clutch according to claim 4, characterized in that a flange is provided on the armature shaft (20) for connection to the spring element (26), which has a current through the magnet coil (8)
Magnetfluß (26) zwischen dem Magnetkörper (6) und dem Ro- tor-element leitet.Magnetic flux (26) between the magnet body (6) and the rotor element conducts.
6. Reibungskupplung nach Anspruch 5, dadurch g e - k e n n z e i c h n e t , daß ein erster Teil des Flansches sich mit engem radialen Luftspalt axial entlang einer inneren Mantelfläche (10) des Magnetkorpers (6) erstreckt und ein zweiter Teil des Flansches eine Nabe (34) des Rotorelements mit engem radialen Luftspalt umfaßt.6. Friction clutch according to claim 5, characterized in that a first part of the flange with a narrow radial air gap extends axially along an inner circumferential surface (10) of the magnetic body (6) and a second part of the flange is a hub (34) of the rotor element with a narrow radial air gap.
7. Handgeführte Bohr- oder Schlagbohrmaschine mit einer elektromagnetisch betätigbaren Einflächen- Reibungskupplung nach einem der vorhergehenden Ansprüche. 7. Hand-held drilling or impact drilling machine with an electromagnetically actuated single-surface friction clutch according to one of the preceding claims.
EP01957967A 2000-07-20 2001-07-14 Electromagnetically actuated, single-surface friction coupling, without a rotor slip ring Withdrawn EP1301726A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10035276 2000-07-20
DE2000135277 DE10035277A1 (en) 2000-07-20 2000-07-20 Unifacial sliding clutch and brake combination, for operating electromagnetically with no slip ring, has a rotor element, a fixed magnetic body and a pot-shaped armature element sliding on bearings
DE2000135276 DE10035276A1 (en) 2000-07-20 2000-07-20 Unifacial sliding clutch for operating electromagnetically with no slip ring has a rotor element, a fixed magnetic body and a pot-shaped armature element sliding on bearings.
DE10035277 2000-07-20
PCT/EP2001/008141 WO2002008627A1 (en) 2000-07-20 2001-07-14 Electromagnetically actuated, single-surface friction coupling, without a rotor slip ring

Publications (1)

Publication Number Publication Date
EP1301726A1 true EP1301726A1 (en) 2003-04-16

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EP01957967A Withdrawn EP1301726A1 (en) 2000-07-20 2001-07-14 Electromagnetically actuated, single-surface friction coupling, without a rotor slip ring

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US (1) US6827189B2 (en)
EP (1) EP1301726A1 (en)
WO (1) WO2002008627A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020061848A1 (en) * 2000-07-20 2002-05-23 Ajay Bhatia Compounds and methods for treatment and diagnosis of chlamydial infection
US7732959B2 (en) * 2005-06-10 2010-06-08 Warner Electric Technology, Llc Rotational coupling device
US7975818B2 (en) * 2005-06-10 2011-07-12 Warner Electric Technology Llc Rotational coupling device
US7493996B2 (en) * 2005-06-10 2009-02-24 Warner Electric Technology Llc Rotational coupling device
US20070209896A1 (en) * 2006-03-10 2007-09-13 Pardee James A Rotational coupling device
US7527134B2 (en) 2006-04-03 2009-05-05 Warner Electric Technology Llc Rotational coupling device
CN102529933B (en) * 2012-01-11 2014-12-17 龙口中宇机械有限公司 Braking air pump, manufacture method for same and control method for same
US9874254B2 (en) * 2016-01-29 2018-01-23 Warner Electric Technology Llc Electromagnetic brake for a power transmission assembly

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2490044A (en) * 1947-02-14 1949-12-06 Sperry Corp Magnetic clutch
US3036679A (en) * 1958-01-17 1962-05-29 Novi Equipment Co Magnetic clutch structure
US3415347A (en) * 1967-01-26 1968-12-10 Stearns Electric Corp Pole structure for electromagnetic clutch or brake with stationary magnet and method of manufacture thereof
FR1558574A (en) * 1968-01-16 1969-02-28
DE1913883A1 (en) * 1969-03-19 1970-10-08 Siemens Ag Electromagnetic brake or clutch
US3994379A (en) * 1975-06-16 1976-11-30 Facet Enterprises, Inc. Motor Components Division Self-adjusting electromagnetic clutch
US4126215A (en) * 1976-12-20 1978-11-21 Facet Enterprises, Inc. Sealed electromagnetic torque translating device
US4285421A (en) * 1979-11-13 1981-08-25 General Motors Corporation Electromagnetic clutch
JPH0663545B2 (en) 1985-07-05 1994-08-22 神鋼電機株式会社 Electromagnetic coupling device
DE3540964A1 (en) * 1985-11-19 1987-05-21 Bosch Gmbh Robert MOTOR DRIVEN TOOL FOR DRILLING OR IMPACT DRILLING
DE3823387C2 (en) 1988-07-09 2000-11-02 Mannesmann Sachs Ag Arrangement for controlling an automatically operated friction clutch
FR2648886B1 (en) 1989-06-27 1991-09-27 Valeo DRIVE PULLEY OF AT LEAST ONE ACCESSORY, PARTICULARLY FOR A MOTOR VEHICLE, AND ACCESSORY NOSE ASSOCIATED WITH SUCH A PULLEY
US5285882A (en) * 1992-12-23 1994-02-15 Dana Corporation Clutch with spacer for supporting a bearing
JP3419121B2 (en) 1994-11-25 2003-06-23 神鋼電機株式会社 Electromagnetic clutch with brake
DE29907942U1 (en) 1999-05-05 1999-07-29 Zahnradfabrik Friedrichshafen Electromagnetically operated single-surface clutch or single-surface brake
DE19951630B4 (en) 1999-10-26 2004-07-01 Zf Friedrichshafen Ag Electromagnetically actuated, slip ringless single-face friction clutch
DE10057139A1 (en) * 2000-11-17 2002-05-23 Hilti Ag Electric hand tool with safety clutch

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0208627A1 *

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US6827189B2 (en) 2004-12-07
US20040104095A1 (en) 2004-06-03

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