EP2857616B1 - Drive assembly for a motor vehicle lock - Google Patents

Drive assembly for a motor vehicle lock Download PDF

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Publication number
EP2857616B1
EP2857616B1 EP14183229.5A EP14183229A EP2857616B1 EP 2857616 B1 EP2857616 B1 EP 2857616B1 EP 14183229 A EP14183229 A EP 14183229A EP 2857616 B1 EP2857616 B1 EP 2857616B1
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EP
European Patent Office
Prior art keywords
gear mechanism
motor
gear
drive assembly
auxiliary motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP14183229.5A
Other languages
German (de)
French (fr)
Other versions
EP2857616A3 (en
EP2857616A2 (en
Inventor
Serkan Gülkan
Karsten Barth
Martin Bucheli
Roman Joschko
Dirk Dobrajc
Carsten Bruchsteiner
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.)
Brose Schliesssysteme GmbH and Co KG
Original Assignee
Brose Schliesssysteme GmbH and Co KG
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.)
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Publication date
Application filed by Brose Schliesssysteme GmbH and Co KG filed Critical Brose Schliesssysteme GmbH and Co KG
Publication of EP2857616A2 publication Critical patent/EP2857616A2/en
Publication of EP2857616A3 publication Critical patent/EP2857616A3/en
Application granted granted Critical
Publication of EP2857616B1 publication Critical patent/EP2857616B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/02—Power-actuated vehicle locks characterised by the type of actuators used
    • E05B81/04—Electrical
    • E05B81/06—Electrical using rotary motors
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B77/00—Vehicle locks characterised by special functions or purposes
    • E05B77/02—Vehicle locks characterised by special functions or purposes for accident situations
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/12—Power-actuated vehicle locks characterised by the function or purpose of the powered actuators
    • E05B81/14—Power-actuated vehicle locks characterised by the function or purpose of the powered actuators operating on bolt detents, e.g. for unlatching the bolt
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/24—Power-actuated vehicle locks characterised by constructional features of the actuator or the power transmission
    • E05B81/32—Details of the actuator transmission
    • E05B81/34—Details of the actuator transmission of geared transmissions
    • E05B81/38—Planetary gears
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/24—Power-actuated vehicle locks characterised by constructional features of the actuator or the power transmission
    • E05B81/32—Details of the actuator transmission
    • E05B81/42—Cams

Definitions

  • the laying invention relates to a drive arrangement for a motor vehicle lock according to the preamble of claim 1, a motor vehicle lock with such a drive arrangement according to the preamble of claim 12 and a method for controlling such a motor vehicle lock according to the preamble of claim 13.
  • motor vehicle lock is comprehensively understood in the present case. These include in total all side door locks, rear door locks, tailgate locks, trunk lid locks, bonnet locks o. Like ..
  • a method for actuating a pawl wherein normally with a first actuator, the pawl is moved to an open position and in an emergency with a second self-locking actuator, the pawl is moved to an open position.
  • a known motor vehicle lock ( DE 197 10 531 A1 ), from which the invention proceeds, is equipped with the usual closing elements latch and pawl.
  • the latch can be brought into an open position and a closed position in which it is in holding engagement with a closing wedge o.
  • the motor vehicle lock is usually arranged on the associated motor vehicle door or the like, while the closing wedge is arranged on the motor vehicle body.
  • the pawl serves to hold the latch in the respective closed position, wherein a lifting of the pawl leads to an excavated position to release the latch.
  • the motorized lifting of the pawl is in today's motor vehicle locks in the context of increasing the comfort of use increasingly important to. Accordingly, the known motor vehicle lock is equipped with a drive arrangement which is coupled via an output element with the pawl to its lifting.
  • the drive arrangement of the above known motor vehicle lock has a drive motor with a downstream actuator arrangement.
  • the actuator assembly operates on a lever gear coupled to the pawl.
  • the drive motor runs in a first drive direction.
  • emergency operation in particular in the event of a crash, the drive motor operates in a second drive direction.
  • the coupling between actuator assembly and lever mechanism is now made so that the speed ratio between the drive motor and pawl in emergency operation is much higher than in normal operation. This means that at the same engine torque in emergency operation, a higher Aushebekraft, acts on the pawl than in normal operation. This takes into account the fact that it comes in particular in crash-related emergency operation, to deformations that can cause jamming of the closing elements.
  • the increased torque transmission in emergency mode still allows a safe lifting of the pawl.
  • the invention is based on the problem of designing and further developing the known drive arrangement in such a way that a high degree of operational reliability is possible, in particular in the event of a crash with reduced installation space requirements and increased constructional flexibility.
  • a planetary gear can be used in a particularly compact and structurally simple way to realize two different torque ratios.
  • Such a proposed planetary gear is equipped with the transmission elements sun gear, planet carrier and ring gear.
  • the drive assembly for the lifting of the pawl in normal operation has a main motor which is coupled or coupled to a first gear element of the gear elements sun gear, planet carrier and ring gear.
  • the drive assembly is equipped with an auxiliary motor which is coupled to a second transmission element of the gear elements sun gear, planet carrier and ring gear or coupled.
  • the torque ratio between the main engine and pawl and between the auxiliary engine and pawl can be adjusted by appropriate design of the planetary gear specifically.
  • the constructive freedom here is almost unlimited.
  • a further advantage is that the realization of the auxiliary motor results in a certain redundancy to the main engine, so that in case of failure of the main engine, the lifting of the pawl can be taken over by the auxiliary motor.
  • the main motor and the auxiliary motor are each permanently coupled to the respective transmission element in an alternative, which keeps the design effort low.
  • the particularly preferred embodiments according to claims 5 to 9 are directed to advantageous design variants for the drive assembly.
  • a particularly cost-effective embodiment results according to claim 9, characterized in that the auxiliary engine with respect to the main engine emits a comparatively low engine torque, which, however, leads to a comparatively high Aushebekraft due to translation in emergency operation.
  • the auxiliary motor can be designed inexpensively.
  • the auxiliary motor is driven to lift the pawl when an emergency operation, in particular a crash, is detected.
  • the detection of an emergency operation is preferably sensor-based, in particular by a crash sensor.
  • Particularly interesting in the further teaching is the fact that in the event of a crash, the auxiliary motor is driven by the associated drive train, so that in emergency operation with a suitable design correspondingly higher Aushebe concept can act on the pawl.
  • a special control of main engine and auxiliary engine is claimed, which goes back to the above-mentioned, preferred design variants of the engines.
  • it is such that when detecting an emergency operation, in particular a crash, only the auxiliary motor, and not about the main motor, is driven to lift the pawl.
  • the drive assembly 1 is part of the motor vehicle lock 2. It is also conceivable that the drive assembly 1 is formed separately from the motor vehicle lock 2 in the rest.
  • the motor vehicle lock 2 is equipped with the usual closing elements latch 3 and pawl 4, wherein the latch 3 can be brought into an open position, not shown, and in at least one closed position.
  • the lock latch 3 in in the Fig. 1 shown main closed position and can be brought into a Vorsch practitioner.
  • the latch 3 is equipped with a main catch 5 and a pre-catch 6.
  • the receptacle for the closing elements is merely indicated in the drawing in dashed line.
  • the lock latch 3 is in its closed positions in holding engagement with a striker 7 o.
  • the motor vehicle lock 2 is preferably on a motor vehicle door o. The like.
  • the striker 7 o is arranged on the body of the motor vehicle.
  • the pawl 4 is in the in Fig. 1 shown, sunken position in which it holds the latch 3 in the closed position, and in a not shown, excavated position in which it releases the latch 3, brought.
  • the lifting of the pawl 4 is in Fig. 1 connected to a pivoting of the pawl 4 about the pawl axis 4a in the counterclockwise direction, so that the latch bolt 3 to the lock latch axis 3a in Fig. 1 is also pivotable counterclockwise in its open position.
  • the drive assembly 1 is coupled in the illustrated, assembled state via an output element 8 with the pawl 4 to their lifting.
  • the term "coupling” is to be understood here broadly. The example of the coupling between the drive assembly 1 and the pawl 4, this means that any transmission elements between the drive assembly 1 and the pawl 4 may be connected.
  • the output element 8 is configured as an output lever pivotable about an output element axis 8a, a first lever arm 9 facing the planetary gear 12 and a second lever arm 10 of the pawl 4.
  • the coupling between the drive assembly 1 and the pawl 4 is realized here via a protruding from the pawl 4 in the direction of the pawl axis 4a engagement lug 11, with which the second lever arm 10 can be brought into engagement. This is the case when the drive element 8 in Fig. 2 pivots clockwise.
  • a permanent, in particular insoluble coupling is provided between the drive arrangement 1 and the pawl 4.
  • the drive arrangement 1 has a planetary gear 12 with the gear elements sun gear 13, planet carrier 14 and ring gear 15.
  • the planet carrier 14 is, as in Fig. 4 shown equipped in the usual way with planet gears 16. Accordingly, the sun gear 13 meshes with the planet gears 16, which in turn mesh with the ring gear 15.
  • the planetary gear 12 is of conventional construction.
  • the drive assembly 1 has a main motor 17 which is coupled to or coupled to a first gear element, here with the ring gear 15, the gear elements sun gear 13, planet 14 and ring gear.
  • Fig. 4 shows that the ring gear 15 is equipped for this purpose with an outer toothing 18, which serves as a worm wheel for the screw 19 of the main motor 17.
  • the worm gear between the main motor 17 and planetary gear 12 leads, as shown in the drawing, to a particularly compact design.
  • the drive assembly 1 is equipped with an auxiliary motor 20 which is coupled to a second transmission element, here with the sun gear 13, the gear elements sun gear 13, planet gear 14 and ring gear 15 or coupled.
  • the sun gear 13 is arranged on a sun gear plate 21 with a corresponding external toothing 22, as in Fig. 2 is shown.
  • the auxiliary motor 20 is equipped with a worm 23, so that the coupling between the auxiliary motor 20 and planetary gear 12 via a worm gear to be explained yet.
  • the output element 8 is coupled to the third transmission element, here the planet carrier 14, the transmission elements sun gear 13, planet carrier 14 and ring gear 15 or coupled.
  • a transmission element 24 is provided which is connected to the planet carrier 16 and which has a drive contour 25 which acts on the first lever arm 9 of the output element 8.
  • An adjustment of the transmission element 24 in Fig. 2 in the counterclockwise direction causes the drive contour 25 acts on the first lever arm 9 and the output element 8 in Fig. 2 clockwise, lifting the pawl 4, pivots.
  • the first gear element associated with the main motor 17 is the ring gear 15
  • the second gear element associated with the auxiliary motor 20 is the sun gear 13
  • the third gear element associated with the output element 8 is the planet carrier 14 of the planetary gear 12.
  • the main motor 17 is permanently coupled to the first gear element, here with the ring gear 15.
  • the auxiliary motor 20 is permanently coupled to the second transmission element, here with the sun gear 13.
  • the permanent coupling is advantageous because the structural implementation is very easy.
  • the torque transmission between the auxiliary motor 20 and the transmission element associated with the output element 8, here the planet carrier 14, is higher, here and preferably more than five times higher, than the torque ratio between the main motor 17 and the output element 8 associated transmission element, here the planet carrier 14, is.
  • the drive technology coupling between the auxiliary engine 20 and the second transmission element, in this case the sun gear 13, at least one additional torque-transmitting gear stage, here and preferably at least an additional spur gear 25, includes.
  • additional means that in addition to the minimum necessary coupling between the worm 23 of the auxiliary motor 20 and the sun gear 13, a further gear stage 25 is provided.
  • the further gear stage 25 comprises a first spur gear 25a, which is coupled to the worm 23 of the auxiliary motor 20, and a second spur gear 25b, which is coupled to the external toothing 22 of the sun gear disc 21. Both spur gears 25a, 25b are fixedly and axially parallel to each other and rotatable about the axis 25c.
  • auxiliary motor 20 and the driven element 8 associated third gear element here the planetary gear 14, which is preferably more than five times the torque ratio between the main motor 17 and the driven element 8 associated third gear element, here the planet carrier 14 ,
  • the auxiliary motor 20 associated gear ratio even more than fifteen times the corresponding, the main motor 17 associated torque ratio.
  • the above transmission design allows a comparatively weak design of the auxiliary motor 20, wherein at the same time in emergency operation extremely high Aushebe specification on the pawl 4 can be generated.
  • the nominal torque of the main motor 17 is higher, preferably more than five times, more preferably more than seven times, higher than the nominal torque of the auxiliary motor 20.
  • the idling speed of the auxiliary motor 20 is preferably less than the idling speed of the main motor 17th
  • an auxiliary voltage for supplying the auxiliary motor 20 is available in a manner to be explained, which is lower than the supply voltage of the motor vehicle, it is preferably so that the rated voltage of the main motor 17 higher, preferably by more is 1.5 times, more preferably more than twice, higher than the rated voltage of the auxiliary motor 20.
  • a drive control 26 is preferably provided, which in the sense of a clear representation only in Fig. 3 is indicated.
  • the drive controller 26 controls the main motor 17 with a higher supply voltage, preferably with a more than 1.5 times, preferably more than twice, higher supply voltage than is provided in emergency operation for the auxiliary motor 20.
  • the drive control 26 controls the main motor 17 in normal operation and the auxiliary motor 20 in emergency operation so that the engine torque in normal operation higher, preferably higher by more than ten times, than the engine torque in emergency mode. Due to the translation, however, it is so that in emergency operation, the auxiliary motor 17, a higher Aushebekraft, preferably a more than five times higher Aushebekraft, on the pawl 4 exerts than this is accomplished in normal operation by the main motor 17.
  • the main motor 17 and / or the auxiliary motor 20 may be or can be operated unidirectionally.
  • the lifting cycle of the pawl 4 caused by the main motor 17 comprises a forward movement and a return movement of the first gear element, here the ring gear 15.
  • the first gear element here the ring gear 15, and / or the second gear element, here the sun gear 13
  • a control limit 27 is associated or are, in a lifting of the pawl 4 by means of the main motor 17 or the auxiliary motor 20th causes a blockage of the second transmission element and the first transmission element.
  • the control limit 27 defines two end positions of associated transmission element. Further preferably, it is such that the control limit 27 blocks the associated transmission element upon reaching the end position.
  • the first gear element here the ring gear 15, a control limit 27 assigned.
  • the adjusting limiter 27 has a stop element 28 arranged on the ring gear 15, in the movement region of which the two counter-stop elements 29, 30 are located.
  • the control limit 27 limits the forward movement and the return movement of the first gear element, here the ring gear 15, in the context of the lifting cycle caused by the main motor 17.
  • this control limit 27 it is not necessary for emergency operation that the drive technology coupling between the main motor 17 and the first transmission element, here the ring gear 15, is self-locking.
  • the drive technology coupling between the main motor 17 and the first gear element, here the ring gear 15, is not self-locking and the first gear element, here the ring gear 15, a control limit 27 is assigned.
  • the drive technology coupling between the auxiliary motor 20 and the second transmission element, here the sun gear 13 is self-locking.
  • an adjustment limit is also assigned to the second transmission element, in this case the sun gear 13.
  • the ring gear 15 by means of the main motor 17 in Fig. 4 Swing clockwise until the stop element 28 moves into the counter-stop element 30.
  • the sun gear 13 is fixed via the auxiliary motor 20 and the gear stage 25, so that the planet carrier in Fig. 4 pivots clockwise.
  • the return movement in the context of this lifting cycle can be achieved by a corresponding control of the main motor 17. This return movement is limited by the control limit 27, namely by the contact between the stop element 28 and the counter-stop element 29th
  • the auxiliary motor 20 is driven. Due to the non-self-locking coupling between the main motor 17 and ring gear 15, the drive of the auxiliary motor 20 with a pivoting of the sun gear 13 in Fig. 4 connected in a clockwise direction. This is first with a pivoting of the ring gear 15 in Fig. 4 connected in a clockwise direction until the stop member 28 runs in the counter-stop member 30. Subsequently, there is a transmission of the drive torque to the planet 14, so that the planet carrier 14 in Fig. 4 pivots clockwise. This corresponds to a pivoting of the transmission element 24 in FIG Fig. 2 counterclockwise, which in turn leads to the output element 8 to a lifting of the pawl 4.
  • control limit 27 of the ring gear 15 is the fact that prior to the transmission of drive torque to the planet 14 of the auxiliary motor 20 performs a kind of freewheel, namely until the stop member 28 runs in the counter-stop member 30.
  • This freewheel can be advantageous depending on the design of the auxiliary motor 20, since it allows a start-up of the auxiliary motor 20 at low load of the auxiliary motor 20. This opens up further degrees of freedom in the selection of the auxiliary motor 20.
  • the drive assembly 1 is equipped with a housing 33 which may be part of the housing of the motor vehicle lock 2. It is also conceivable that the housing 33 of the drive assembly 1 is configured separately from the housing of the motor vehicle lock 2 otherwise.
  • the housing 33 of the drive assembly 1 receives all gear elements, here the sun gear 13, the planet carrier 14 and the ring gear 15. However, the transmission element 24 and the output element 8 are arranged outside the housing 33. This allows the housing 33rd largely encapsulate the drive assembly 1 to the required for the coupling of the transmission element 24 opening.
  • the housing 33 is designed in two parts and has two half-shells, of which only one is shown in the drawing.
  • the above motor vehicle lock 2 is claimed as such. Reference may be made to all the above explanations, provided that they are suitable for describing the motor vehicle lock 2.
  • the motor vehicle lock 2 is preferably equipped with an above-mentioned drive control 26. Furthermore, it may be advantageous that the motor vehicle lock 2 has an auxiliary voltage source 31, which is provided for the supply of the auxiliary motor 20 in emergency operation, wherein the auxiliary voltage of the auxiliary voltage source 31 is smaller than the supply voltage of the motor vehicle.
  • the auxiliary voltage source 31 is only in Fig. 3 indicated.
  • a method for controlling a proposed motor vehicle lock 2 is claimed. It is essential that the auxiliary motor 20 is driven to lift the pawl 4 when an emergency operation, in particular a crash, is detected.
  • an emergency operation is detected based on a sensor signal, here and preferably based on a sensor signal of a crash sensor 32.
  • a crash sensor 32 is also only in Fig. 3 indicated.
  • the main motor 17 in normal operation and the auxiliary motor 20 are controlled in emergency operation so that the engine torque in Normal operation higher, preferably by more than ten times higher than the engine torque in emergency mode, but with the translation due to emergency operation of the auxiliary motor 20, a higher Aushebekraft, preferably by more than five times higher Aushebekraft, on the pawl 4 exerts than in normal operation for the main engine 17 is the case.

Description

Die verlegende Erfindung betrifft eine Antriebsanordnung für ein Kraftfahrzeugschloss gemäß dem Oberbegriff von Anspruch 1, ein Kraftfahrzeugschloss mit einer solchen Antriebsanordnung gemäß dem Oberbegriff von Anspruch 12 sowie ein Verfahren zur Ansteuerung eines solchen Kraftfahrzeugschlosses gemäß dem Oberbegriff von Anspruch 13.The laying invention relates to a drive arrangement for a motor vehicle lock according to the preamble of claim 1, a motor vehicle lock with such a drive arrangement according to the preamble of claim 12 and a method for controlling such a motor vehicle lock according to the preamble of claim 13.

Der Begriff "Kraftfahrzeugschloss" ist vorliegend umfassend zu verstehen. Dazu gehören insgesamt alle Seitenturschlösser, Hecktürschlösser, Heckklappenschlösser, Heckdeckelschlösser, Motorhaubenschlösser o. dgl..The term "motor vehicle lock" is comprehensively understood in the present case. These include in total all side door locks, rear door locks, tailgate locks, trunk lid locks, bonnet locks o. Like ..

In der WO 2004/040089 A1 ist ein Verfahren zur Betätigung einer Sperrklinke beschrieben, wobei im Normalfall mit einem ersten Stellantrieb die Sperrlinke in eine geöffnete Position bewegt wird und im Notfall mit einem zweiten selbsthemmenden Stellantrieb die Sperrlinke in eine geöffnete Position bewegt wird.In the WO 2004/040089 A1 a method for actuating a pawl is described, wherein normally with a first actuator, the pawl is moved to an open position and in an emergency with a second self-locking actuator, the pawl is moved to an open position.

In der EP 1 074 681 A1 ist Kraftfahrzeugschloss mit einem Antriebsmotor und einem nachgeschalteten Untersetzungsgetriebe beschrieben, welches ein Planetengetriebe einschließt. Im Normalbetrieb wirkt der Antriebsmotor in einer Normaldrehrichtung auf die Sperrklinke und im Notfallbetrieb wirkt der Antriebsmotor in der entgegengesetzten Drehrichtung, der Notfalldrehrichtung, auf die Sperrklinke.In the EP 1 074 681 A1 Motor vehicle lock is described with a drive motor and a downstream reduction gear, which includes a planetary gear. In normal operation, the drive motor acts in a normal direction of rotation on the pawl and in emergency mode, the drive motor acts in the opposite direction of rotation, the emergency direction of rotation, on the pawl.

Ein bekanntes Kraftfahrzeugschloss ( DE 197 10 531 A1 ), von dem die Erfindung ausgeht, ist mit den üblichen Schließelementen Schlossfalle und Sperrklinke ausgestattet. Die Schlossfalle lässt sich in eine Offenstellung und in eine Schließstellung bringen, in der sie in haltendem Eingriff mit einem Schließkeil o. dgl. steht. Dabei ist das Kraftfahrzeugschloss üblicherweise an der zugeordneten Kraftfahrzeugtür o. dgl. angeordnet, während der Schließkeil an der Kraftfahrzeugkarosserie angeordnet ist. Die Sperrklinke dient dem Halten der Schlossfalle in der jeweiligen Schließstellung, wobei ein Ausheben der Sperrklinke in eine ausgehobene Stellung zur Freigabe der Schlossfalle führt.A known motor vehicle lock ( DE 197 10 531 A1 ), from which the invention proceeds, is equipped with the usual closing elements latch and pawl. The latch can be brought into an open position and a closed position in which it is in holding engagement with a closing wedge o. The like. In this case, the motor vehicle lock is usually arranged on the associated motor vehicle door or the like, while the closing wedge is arranged on the motor vehicle body. The pawl serves to hold the latch in the respective closed position, wherein a lifting of the pawl leads to an excavated position to release the latch.

Dem motorischen Ausheben der Sperrklinke kommt bei heutigen Kraftfahrzeugschlössern im Rahmen der Steigerung des Benutzungskomforts zunehmende Bedeutung zu. Entsprechend ist das bekannte Kraftfahrzeugschloss mit einer Antriebsanordnung ausgestattet, die über ein Abtriebselement mit der Sperrklinke zu deren Ausheben gekoppelt ist.The motorized lifting of the pawl is in today's motor vehicle locks in the context of increasing the comfort of use increasingly important to. Accordingly, the known motor vehicle lock is equipped with a drive arrangement which is coupled via an output element with the pawl to its lifting.

Die Antriebsanordnung des obigen bekannten Kraftfahrzeugschlosses, von der die Erfindung ausgeht, weist einen Antriebsmotor mit einer nachgeschalteten Stellelementanordnung auf. Die Stellelementanordnung arbeitet wiederum auf ein mit der Sperrklinke gekoppeltes Hebelgetriebe. Im Normalbetrieb läuft der Antriebsmotor in einer ersten Antriebsrichtung. Im Notbetrieb, insbesondere im Crashfall, arbeitet der Antriebsmotor in einer zweiten Antriebsrichtung. Die Kopplung zwischen Stellelementanordnung und Hebelgetriebe ist nun so getroffen, dass die Drehzahlübersetzung zwischen Antriebsmotor und Sperrklinke im Notbetrieb weitaus höher ist als im Normalbetrieb. Dies bedeutet, dass bei identischem Motormoment im Notbetrieb eine höhere Aushebekraft, auf die Sperrklinke wirkt als im Normalbetrieb. Dies trägt dem Umstand Rechnung, dass es insbesondere im crashbedingten Notbetrieb, zu Verformungen kommt, die ein Verklemmen der Schließelemente bewirken können. Die erhöhte Drehmomentübersetzung im Notbetrieb ermöglicht dennoch ein sicheres Ausheben der Sperrklinke.The drive arrangement of the above known motor vehicle lock, from which the invention proceeds, has a drive motor with a downstream actuator arrangement. The actuator assembly, in turn, operates on a lever gear coupled to the pawl. In normal operation, the drive motor runs in a first drive direction. In emergency operation, in particular in the event of a crash, the drive motor operates in a second drive direction. The coupling between actuator assembly and lever mechanism is now made so that the speed ratio between the drive motor and pawl in emergency operation is much higher than in normal operation. This means that at the same engine torque in emergency operation, a higher Aushebekraft, acts on the pawl than in normal operation. This takes into account the fact that it comes in particular in crash-related emergency operation, to deformations that can cause jamming of the closing elements. The increased torque transmission in emergency mode still allows a safe lifting of the pawl.

Während die bekannte Antriebsanordnung eine hobe Betriebssicherheit des Kraftfahrzeugschlosses auch im Notbetrieb, insbesondere im Crashfall, gewährleistet, führt die dort vorgeschlagene Anwendung eines Hebelgetriebes zu einem erhöhten Bauraumbedarf und zu einer Reduzierung der konstruktiven Flexibilität.While the known drive arrangement ensures a hobe operational safety of the motor vehicle lock even in emergency operation, especially in the event of a crash, the proposed application of a lever mechanism leads to increased space requirements and to a reduction in design flexibility.

Der Erfindung liegt das Problem zugrunde, die bekannte Antriebsanordnung derart auszugestalten und weiterzubilden, dass eine hohe Betriebssicherheit insbesondere im Crashfall bei reduzierten Bauraumanforderungen und erhöhter konstruktiver Flexibilität möglich ist.The invention is based on the problem of designing and further developing the known drive arrangement in such a way that a high degree of operational reliability is possible, in particular in the event of a crash with reduced installation space requirements and increased constructional flexibility.

Das obige Problem wird bei einer Antriebsanordnung durch die Merkmale von Anspruch 1 gelöst.The above problem is solved in a drive arrangement by the features of claim 1.

Wesentlich ist die grundsätzliche Überlegung, dass ein Planetengetriebe auf besonders kompakte und konstruktiv einfache Weise genutzt werden kann, um zwei unterschiedliche Drehmomentübersetzungen zu realisieren. Ein solches vorschlagsgemäßes Planetengetriebe ist mit den Getriebeelementen Sonnenrad, Planetenradträger und Hohlrad ausgestattet.Essential is the fundamental consideration that a planetary gear can be used in a particularly compact and structurally simple way to realize two different torque ratios. Such a proposed planetary gear is equipped with the transmission elements sun gear, planet carrier and ring gear.

Im Einzelnen weist die Antriebsanordnung für das Ausheben der Sperrklinke im Normalbetrieb einen Hauptmotor auf, der mit einem ersten Getriebeelement der Getriebeelemente Sonnenrad, Planetenradträger und Hohlrad gekoppelt oder koppelbar ist. Für das Ausheben der Sperrklinke im Notbetrieb ist die Antriebsanordnung mit einem Hilfsmotor ausgestattet, der mit einem zweiten Getriebeelement der Getriebeelemente Sonnenrad, Planetenradträger und Hohlrad gekoppelt oder koppelbar ist.In detail, the drive assembly for the lifting of the pawl in normal operation has a main motor which is coupled or coupled to a first gear element of the gear elements sun gear, planet carrier and ring gear. For the lifting of the pawl in emergency operation, the drive assembly is equipped with an auxiliary motor which is coupled to a second transmission element of the gear elements sun gear, planet carrier and ring gear or coupled.

Mit der vorschlagsgemäßen Lösung lässt sich die Drehmomentübersetzung zwischen Hauptmotor und Sperrklinke sowie zwischen Hilfsmotor und Sperrklinke durch entsprechende Auslegung des Planetengetriebes gezielt einstellen. Die konstruktive Freiheit ist hier nahezu unbeschränkt.With the proposed solution, the torque ratio between the main engine and pawl and between the auxiliary engine and pawl can be adjusted by appropriate design of the planetary gear specifically. The constructive freedom here is almost unlimited.

Vorteilhaft ist weiter, dass sich durch die Realisierung des Hilfsmotors eine gewisse Redundanz zum Hauptmotor ergibt, so dass bei einem Ausfall des Hauptmotors das Ausheben der Sperrklinke vom Hilfsmotor übernommen werden kann.A further advantage is that the realization of the auxiliary motor results in a certain redundancy to the main engine, so that in case of failure of the main engine, the lifting of the pawl can be taken over by the auxiliary motor.

Bei der besonders bevorzugten Ausgestaltung gemäß Anspruch 4 sind in einer Alternative der Hauptmotor und der Hilfsmotor jeweils permanent mit dem jeweiligen Getriebeelement gekoppelt, was den konstruktiven Aufwand gering hält.In the particularly preferred embodiment according to claim 4, the main motor and the auxiliary motor are each permanently coupled to the respective transmission element in an alternative, which keeps the design effort low.

Die besonders bevorzugten Ausgestaltungen gemäß den Ansprüchen 5 bis 9 sind auf vorteilhafte Auslegungsvarianten für die Antriebsanordnung gerichtet. Eine besonders kostengünstige Ausgestaltung ergibt sich gemäß Anspruch 9 dadurch, dass der Hilfsmotor im Hinblick auf den Hauptmotor ein vergleichsweise geringes Motormoment abgibt, was jedoch übersetzungsbedingt im Notbetrieb zu einer vergleichsweise hohen Aushebekraft führt. Insoweit kann der Hilfsmotor kostengünstig ausgelegt werden.The particularly preferred embodiments according to claims 5 to 9 are directed to advantageous design variants for the drive assembly. A particularly cost-effective embodiment results according to claim 9, characterized in that the auxiliary engine with respect to the main engine emits a comparatively low engine torque, which, however, leads to a comparatively high Aushebekraft due to translation in emergency operation. In that regard, the auxiliary motor can be designed inexpensively.

Nach einer weiteren Lehre gemäß Anspruch 12, der eigenständige Bedeutung zukommt, wird ein Kraftfahrzeugschloss mit einer vorschlagsgemäßen Antriebsanordnung beansprucht. Auf alle Ausführungen zu der Antriebsanordnung darf verwiesen werden, soweit diese geeignet sind, das Kraftfahrzeugschloss zu beschreiben.According to a further teaching according to claim 12, which has independent significance, a motor vehicle lock with a proposed drive arrangement is claimed. Reference may be made to all versions of the drive arrangement, as far as they are suitable to describe the motor vehicle lock.

Nach einer weiteren Lehre gemäß Anspruch 13 wird ein Verfahren zur Ansteuerung eines obigen Kraftfahrzeugschlosses beansprucht.According to another teaching according to claim 13, a method for driving an above motor vehicle lock is claimed.

Wesentlich nach der weiteren Lehre ist, dass der Hilfsmotor zum Ausheben der Sperrklinke angesteuert wird, wenn ein Notbetrieb, insbesondere ein Crashfall, erkannt wird. Die Erkennung eines Notbetriebs erfolgt vorzugsweise sensorbasiert, insbesondere durch einen Crashsensor. Besonders interessant bei der weiteren Lehre ist die Tatsache, dass im Crashfall der Hilfsmotor mit dem dazugehörigen Antriebsstrang angesteuert wird, so dass im Notbetrieb bei geeigneter Auslegung entsprechend höhere Aushebekräfte auf die Sperrklinke wirken können.Essential according to the further teaching is that the auxiliary motor is driven to lift the pawl when an emergency operation, in particular a crash, is detected. The detection of an emergency operation is preferably sensor-based, in particular by a crash sensor. Particularly interesting in the further teaching is the fact that in the event of a crash, the auxiliary motor is driven by the associated drive train, so that in emergency operation with a suitable design correspondingly higher Aushebekräfte can act on the pawl.

Bei den bevorzugten Ausgestaltungen gemäß den Ansprüchen 14 und 15 ist eine spezielle Ansteuerung von Hauptmotor und Hilfsmotor beansprucht, die auf die oben angesprochenen, bevorzugten Auslegungsvarianten der Motoren zurückgeht. In einer ganz besonders bevorzugten Variante ist es so, dass bei der Erkennung eines Notbetriebs, insbesondere eines Crashfalls, ausschließlich der Hilfsmotor, und nicht etwa der Hauptmotor, zum Ausheben der Sperrklinke angesteuert wird.In the preferred embodiments according to claims 14 and 15, a special control of main engine and auxiliary engine is claimed, which goes back to the above-mentioned, preferred design variants of the engines. In a particularly preferred variant, it is such that when detecting an emergency operation, in particular a crash, only the auxiliary motor, and not about the main motor, is driven to lift the pawl.

Im Folgenden wird die Erfindung anhand einer lediglich ein Ausführungsbeispiel darstellenden Zeichnung näher erläutert. In der Zeichnung zeigt

Fig. 1
ein vorschlagsgemäßes Kraftfahrzeugschloss mit einer vorschlagsgemäßen Antriebsanordnung in einer stirnseitigen Ansicht,
Fig. 2
das Kraftfahrzeugschloss gemäß Fig. 1 in einer Seitenansicht II,
Fig. 3
das Kraftfahrzeugschloss gemäß Fig. 1 in einer Seitenansicht III und
Fig. 4
das Kraftfahrzeugschloss gemäß Fig. 1 in einer Ansicht gemäß Fig. 3 ohne Sonnenradteller.
In the following the invention will be explained in more detail with reference to a drawing showing only one exemplary embodiment. In the drawing shows
Fig. 1
a proposed motor vehicle lock with a proposed drive arrangement in a frontal view,
Fig. 2
the motor vehicle lock according to Fig. 1 in a side view II,
Fig. 3
the motor vehicle lock according to Fig. 1 in a side view III and
Fig. 4
the motor vehicle lock according to Fig. 1 in a view according to Fig. 3 without sun wheel plate.

Die dargestellte Antriebsanordnung 1 dient dem motorischen Öffnen eines Kraftfahrzeugschlosses 2. Hier und vorzugsweise ist die Antriebsanordnung 1 Bestandteil des Kraftfahrzeugschlosses 2. Denkbar ist aber auch, dass die Antriebsanordnung 1 getrennt vom Kraftfahrzeugschloss 2 im Übrigen ausgebildet ist.Here and preferably, the drive assembly 1 is part of the motor vehicle lock 2. It is also conceivable that the drive assembly 1 is formed separately from the motor vehicle lock 2 in the rest.

Das Kraftfahrzeugschloss 2 ist mit den üblichen Schließelementen Schlossfalle 3 und Sperrklinke 4 ausgestattet, wobei die Schlossfalle 3 in eine nicht dargestellte Offenstellung und in mindestens eine Schließstellung bringbar ist. Bei dem dargestellten und insoweit bevorzugten Ausführungsbeispiel ist die Schlossfalle 3 in die in Fig. 1 gezeigte Hauptschließstellung sowie in eine Vorschließstellung bringbar. Hierfür ist die Schlossfalle 3 mit einer Hauptraste 5 und einer Vorraste 6 ausgestattet. Die Aufnahme für die Schließelemente ist in der Zeichnung in gestrichelter Linie lediglich angedeutet.The motor vehicle lock 2 is equipped with the usual closing elements latch 3 and pawl 4, wherein the latch 3 can be brought into an open position, not shown, and in at least one closed position. In the illustrated and insofar preferred embodiment, the lock latch 3 in in the Fig. 1 shown main closed position and can be brought into a Vorschließstellung. For this purpose, the latch 3 is equipped with a main catch 5 and a pre-catch 6. The receptacle for the closing elements is merely indicated in the drawing in dashed line.

Die Schlossfalle 3 steht in ihren Schließstellungen in haltendem Eingriff mit einem Schließkeil 7 o. dgl., wobei das Kraftfahrzeugschloss 2 vorzugsweise an einer Kraftfahrzeugtür o. dgl. und der Schließkeil 7 o. dgl. an der Karosserie des Kraftfahrzeugs angeordnet ist.The lock latch 3 is in its closed positions in holding engagement with a striker 7 o. The like., The motor vehicle lock 2 is preferably on a motor vehicle door o. The like. And the striker 7 o. The like. Arranged on the body of the motor vehicle.

Die Sperrklinke 4 ist in die in Fig. 1 dargestellte, eingefallene Stellung, in der sie die Schlossfalle 3 in der Schließstellung hält, und in eine nicht dargestellte, ausgehobene Stellung, in der sie die Schlossfalle 3 freigibt, bringbar. Das Ausheben der Sperrklinke 4 ist in Fig. 1 mit einem Schwenken der Sperrklinke 4 um die Sperrklinkenachse 4a entgegen dem Uhrzeigersinn verbunden, so dass die Schlossfalle 3 um die Schlossfallenachse 3a in Fig. 1 ebenfalls entgegen dem Uhrzeigersinn in ihre Offenstellung schwenkbar ist.The pawl 4 is in the in Fig. 1 shown, sunken position in which it holds the latch 3 in the closed position, and in a not shown, excavated position in which it releases the latch 3, brought. The lifting of the pawl 4 is in Fig. 1 connected to a pivoting of the pawl 4 about the pawl axis 4a in the counterclockwise direction, so that the latch bolt 3 to the lock latch axis 3a in Fig. 1 is also pivotable counterclockwise in its open position.

Die Antriebsanordnung 1 ist in dem dargestellten, montierten Zustand über ein Abtriebselement 8 mit der Sperrklinke 4 zu deren Ausheben koppelbar. Der Begriff "Kopplung" ist hier weit zu verstehen. Am Beispiel der Kopplung zwischen der Antriebsanordnung 1 und der Sperrklinke 4 bedeutet dies, dass beliebige Übertragungselemente zwischen die Antriebsanordnung 1 und die Sperrklinke 4 geschaltet sein können.The drive assembly 1 is coupled in the illustrated, assembled state via an output element 8 with the pawl 4 to their lifting. The term "coupling" is to be understood here broadly. The example of the coupling between the drive assembly 1 and the pawl 4, this means that any transmission elements between the drive assembly 1 and the pawl 4 may be connected.

Das Abtriebselement 8 ist als um eine Abtriebselementachse 8a schwenkbarer Abtriebshebel ausgestaltet, wobei ein erster Hebelarm 9 dem Planetengetriebe 12 und ein zweiter Hebelarm 10 der Sperrklinke 4 zugewandt ist. Die Kopplung zwischen der Antriebsanordnung 1 und der Sperrklinke 4 ist hier über eine von der Sperrklinke 4 in Richtung der Sperrklinkenachse 4a abragende Eingriffsnase 11 realisiert, mit der der zweite Hebelarm 10 in Eingriff bringbar ist. Dies ist der Fall, wenn das Antriebselement 8 in Fig. 2 im Uhrzeigersinn schwenkt. Grundsätzlich kann es auch vorgesehen sein, dass zwischen der Antriebsanordnung 1 und der Sperrklinke 4 eine permanente, insbesondere unlösbare Kopplung vorgesehen ist.The output element 8 is configured as an output lever pivotable about an output element axis 8a, a first lever arm 9 facing the planetary gear 12 and a second lever arm 10 of the pawl 4. The coupling between the drive assembly 1 and the pawl 4 is realized here via a protruding from the pawl 4 in the direction of the pawl axis 4a engagement lug 11, with which the second lever arm 10 can be brought into engagement. This is the case when the drive element 8 in Fig. 2 pivots clockwise. In principle, it can also be provided that a permanent, in particular insoluble coupling is provided between the drive arrangement 1 and the pawl 4.

Die Antriebsanordnung 1 weist ein Planetengetriebe 12 mit den Getriebeelementen Sonnenrad 13, Planetenradträger 14 und Hohlrad 15 auf. Der Planetenradträger 14 ist, wie in Fig. 4 gezeigt, in üblicher Weise mit Planetenrädern 16 ausgestattet. Entsprechend kämmt das Sonnenrad 13 mit den Planetenrädern 16, die wiederum mit dem Hohlrad 15 kämmen. Insoweit ist das Planetengetriebe 12 von üblichem Aufbau.The drive arrangement 1 has a planetary gear 12 with the gear elements sun gear 13, planet carrier 14 and ring gear 15. The planet carrier 14 is, as in Fig. 4 shown equipped in the usual way with planet gears 16. Accordingly, the sun gear 13 meshes with the planet gears 16, which in turn mesh with the ring gear 15. In that regard, the planetary gear 12 is of conventional construction.

Für das Ausheben der Sperrklinke 4 im Normalbetrieb weist die Antriebsanordnung 1 einen Hauptmotor 17 auf, der mit einem ersten Getriebeelement, hier mit dem Hohlrad 15, der Getriebeelemente Sonnenrad 13, Planetenradträger 14 und Hohlrad 15 gekoppelt oder koppelbar ist. Fig. 4 zeigt, dass das Hohlrad 15 hierfür mit einer Außenverzahnung 18 ausgestattet ist, die als Schneckenrad für die Schnecke 19 des Hauptmotors 17 dient. Das Schneckengetriebe zwischen Hauptmotor 17 und Planetengetriebe 12 führt, wie in der Zeichnung dargestellt, zu einem besonders kompakten Aufbau.For the lifting of the pawl 4 in normal operation, the drive assembly 1 has a main motor 17 which is coupled to or coupled to a first gear element, here with the ring gear 15, the gear elements sun gear 13, planet 14 and ring gear. Fig. 4 shows that the ring gear 15 is equipped for this purpose with an outer toothing 18, which serves as a worm wheel for the screw 19 of the main motor 17. The worm gear between the main motor 17 and planetary gear 12 leads, as shown in the drawing, to a particularly compact design.

Für das Ausheben der Sperrklinke 4 im Notbetrieb, insbesondere im Crashfall, ist die Antriebsanordnung 1 mit einem Hilfsmotor 20 ausgestattet, der mit einem zweiten Getriebeelement, hier mit dem Sonnenrad 13, der Getriebeelemente Sonnenrad 13, Planetenradträger 14 und Hohlrad 15 gekoppelt oder koppelbar ist. Hierfür ist das Sonnenrad 13 an einem Sonnenradteller 21 mit einer entsprechenden Außenverzahnung 22 angeordnet, wie in Fig. 2 gezeigt ist. Auch der Hilfsmotor 20 ist mit einer Schnecke 23 ausgestattet, so dass die Kopplung zwischen Hilfsmotor 20 und Planetengetriebe 12 über ein noch zu erläuterndes Schneckengetriebe erfolgt.For the lifting of the pawl 4 in emergency operation, in particular in the event of a crash, the drive assembly 1 is equipped with an auxiliary motor 20 which is coupled to a second transmission element, here with the sun gear 13, the gear elements sun gear 13, planet gear 14 and ring gear 15 or coupled. For this purpose, the sun gear 13 is arranged on a sun gear plate 21 with a corresponding external toothing 22, as in Fig. 2 is shown. Also, the auxiliary motor 20 is equipped with a worm 23, so that the coupling between the auxiliary motor 20 and planetary gear 12 via a worm gear to be explained yet.

Bei dem dargestellten und insoweit bevorzugten Ausführungsbeispiel ist das Abtriebselement 8 mit dem dritten Getriebeelement, hier dem Planetenradträger 14, der Getriebeelemente Sonnenrad 13, Planetenradträger 14 und Hohlrad 15 gekoppelt oder koppelbar. Hierfür ist ein Übertragungselement 24 vorgesehen, das mit dem Planetenradträger 16 verbunden ist und das eine Antriebskontur 25 aufweist, die auf den ersten Hebelarm 9 des Abtriebselements 8 wirkt. Eine Verstellung des Übertragungselements 24 in Fig. 2 entgegen dem Uhrzeigersinn führt dazu, dass die Antriebskontur 25 auf den ersten Hebelarm 9 wirkt und das Abtriebselement 8 in Fig. 2 im Uhrzeigersinn, die Sperrklinke 4 aushebend, schwenkt.In the illustrated and so far preferred embodiment, the output element 8 is coupled to the third transmission element, here the planet carrier 14, the transmission elements sun gear 13, planet carrier 14 and ring gear 15 or coupled. For this purpose, a transmission element 24 is provided which is connected to the planet carrier 16 and which has a drive contour 25 which acts on the first lever arm 9 of the output element 8. An adjustment of the transmission element 24 in Fig. 2 in the counterclockwise direction causes the drive contour 25 acts on the first lever arm 9 and the output element 8 in Fig. 2 clockwise, lifting the pawl 4, pivots.

Wie oben angedeutet, handelt es sich bei dem ersten, dem Hauptmotor 17 zugeordneten Getriebeelement um das Hohlrad 15, bei dem zweiten, dem Hilfsmotor 20 zugeordneten Getriebeelement um das Sonnenrad 13 und bei dem dritten, dem Abtriebselement 8 zugeordneten Getriebeelement um den Planetenradträger 14 des Planetengetriebes 12. Hiermit lassen sich die Anforderungen im Hinblick auf Drehmoment-Übersetzungsverhältnisse und Bauraumanforderungen optimal umsetzen. Eine andere Zuordnung der Getriebeelemente zu Hauptmotor 17 und Hilfsmotor 20 sind jedoch denkbar.As indicated above, the first gear element associated with the main motor 17 is the ring gear 15, the second gear element associated with the auxiliary motor 20 is the sun gear 13 and the third gear element associated with the output element 8 is the planet carrier 14 of the planetary gear 12. With this, the requirements with regard to torque transmission ratios and installation space requirements can be optimally implemented. Another assignment of the transmission elements to main motor 17 and auxiliary motor 20 are conceivable, however.

Es lässt sich der Darstellung gemäß Fig. 3 entnehmen, dass der Hauptmotor 17 permanent mit dem ersten Getriebeelement, hier mit dem Hohlrad 15, gekoppelt ist. Zusätzlich ist es so, dass der Hilfsmotor 20 permanent mit dem zweiten Getriebeelement, hier mit dem Sonnenrad 13, gekoppelt ist. Alternativ kann es vorgesehen sein, dass jeweils nur eine Koppelbarkeit vorgesehen ist, so dass die Kopplung beispielsweise nur dann hergestellt wird, wenn das Ausheben der Sperrklinke 4 ansteht. Die permanente Kopplung ist allerdings vorteilhaft, da die konstruktive Umsetzung ganz besonders einfach ist.It can be according to the representation Fig. 3 see that the main motor 17 is permanently coupled to the first gear element, here with the ring gear 15. In addition, it is such that the auxiliary motor 20 is permanently coupled to the second transmission element, here with the sun gear 13. Alternatively, it may be provided that in each case only one coupling capability is provided, so that the coupling is for example only made when the lifting of the pawl 4 is present. However, the permanent coupling is advantageous because the structural implementation is very easy.

Die Anordnung ist nun insgesamt so getroffen, dass die Drehmomentübersetzung zwischen dem Hilfsmotor 20 und der Sperrklinke 4 höher ist als zwischen dem Hauptmotor 17 und der Sperrklinke 4. Dies bedeutet, dass für eine identische Aushebekraft an der Sperrklinke 4 der Hilfsmotor 20 ein geringeres Motormoment aufbringen muss als der Hauptmotor 17.The arrangement is now taken as a whole that the torque transmission between the auxiliary motor 20 and the pawl 4 is higher than between the main motor 17 and the pawl 4. This means that for an identical Aushebekraft on the pawl 4 of the auxiliary motor 20 apply a lower engine torque must be considered the main engine 17.

Im Einzelnen ist es vorzugsweise so, dass die Drehmomentübersetzung zwischen dem Hilfsmotor 20 und dem dem Abtriebselement 8 zugeordneten Getriebeelement, hier dem Planetenradträger 14, höher, hier und vorzugsweise um mehr als das Fünffache höher, als die Drehmomentübersetzung zwischen dem Hauptmotor 17 und dem dem Abtriebselement 8 zugeordneten Getriebeelement, hier dem Planetenradträger 14, ist.In particular, it is preferable that the torque transmission between the auxiliary motor 20 and the transmission element associated with the output element 8, here the planet carrier 14, is higher, here and preferably more than five times higher, than the torque ratio between the main motor 17 and the output element 8 associated transmission element, here the planet carrier 14, is.

Bei dem dargestellten und insoweit bevorzugten Ausführungsbeispiel ist es zusätzlich so, dass die antriebstechnische Kopplung zwischen dem Hilfsmotor 20 und dem zweiten Getriebeelement, hier dem Sonnenrad 13, mindestens eine zusätzliche Drehmoment-übersetzende Getriebestufe, hier und vorzugsweise mindestens eine zusätzliche Stirnrad-Getriebestufe 25, umfasst. Der Begriff "zusätzlich" bedeutet, dass zusätzlich zu der mindestnotwendigen Kopplung zwischen der Schnecke 23 des Hilfsmotors 20 und dem Sonnenrad 13 eine weitere Getriebestufe 25 vorgesehen ist. Hier und vorzugsweise umfasst die weitere Getriebestufe 25 ein erstes Stirnrad 25a, das mit der Schnecke 23 des Hilfsmotors 20 gekoppelt ist, und ein zweites Stirnrad 25b, das mit der Außenverzahnung 22 des Sonnenradtellers 21 gekoppelt ist. Beide Stirnräder 25a, 25b sind fest und achsparallel miteinander verbunden und um die Achse 25c drehbar.In the illustrated preferred embodiment, it is additionally the case that the drive technology coupling between the auxiliary engine 20 and the second transmission element, in this case the sun gear 13, at least one additional torque-transmitting gear stage, here and preferably at least an additional spur gear 25, includes. The term "additional" means that in addition to the minimum necessary coupling between the worm 23 of the auxiliary motor 20 and the sun gear 13, a further gear stage 25 is provided. Here and preferably, the further gear stage 25 comprises a first spur gear 25a, which is coupled to the worm 23 of the auxiliary motor 20, and a second spur gear 25b, which is coupled to the external toothing 22 of the sun gear disc 21. Both spur gears 25a, 25b are fixedly and axially parallel to each other and rotatable about the axis 25c.

Insgesamt ergibt sich eine Drehmomentübersetzung zwischen Hilfsmotor 20 und dem dem Abtriebselement 8 zugeordneten, dritten Getriebeelement, hier dem Planetenradgetriebe 14, die vorzugsweise mehr als das Fünffache der Drehmomentübersetzung zwischen Hauptmotor 17 und dem dem Abtriebselement 8 zugeordneten, dritten Getriebeelement, hier dem Planetenradträger 14, beträgt. Hier und vorzugsweise ist diese, dem Hilfsmotor 20 zugeordnete Getriebeübersetzung sogar mehr als das Fünfzehnfache der entsprechenden, dem Hauptmotor 17 zugeordneten Drehmomentübersetzung.Overall, there is a torque ratio between the auxiliary motor 20 and the driven element 8 associated third gear element, here the planetary gear 14, which is preferably more than five times the torque ratio between the main motor 17 and the driven element 8 associated third gear element, here the planet carrier 14 , Here and preferably, this, the auxiliary motor 20 associated gear ratio even more than fifteen times the corresponding, the main motor 17 associated torque ratio.

Die obige Getriebeauslegung ermöglicht eine vergleichsweise schwache Auslegung des Hilfsmotors 20, wobei gleichzeitig im Notbetrieb außerordentlich hohe Aushebekräfte an der Sperrklinke 4 erzeugbar sind.The above transmission design allows a comparatively weak design of the auxiliary motor 20, wherein at the same time in emergency operation extremely high Aushebekräfte on the pawl 4 can be generated.

Hier und vorzugsweise ist das Nennmoment des Hauptmotors 17 höher, vorzugsweise um mehr als das Fünffache, weiter vorzugsweise um mehr als das Siebenfache, höher als das Nennmoment des Hilfsmotors 20. Die Leerlaufdrehzahl des Hilfsmotors 20 ist vorzugsweise geringer als die Leerlaufdrehzahl des Hauptmotors 17.Here and preferably, the nominal torque of the main motor 17 is higher, preferably more than five times, more preferably more than seven times, higher than the nominal torque of the auxiliary motor 20. The idling speed of the auxiliary motor 20 is preferably less than the idling speed of the main motor 17th

Da im Notbetrieb, insbesondere im Crashfall, in noch zu erläuternden Konstellationen eine Hilfsspannung zur Versorgung des Hilfsmotors 20 zur Verfügung steht, die niedriger ist als die Versorgungsspannung des Kraftfahrzeugs, ist es weiter vorzugsweise so, dass die Nennspannung des Hauptmotors 17 höher, vorzugsweise um mehr als das 1,5-fache, weiter vorzugsweise um mehr als das Zweifache, höher ist als die Nennspannung des Hilfsmotors 20.Since in emergency operation, in particular in the event of a crash, an auxiliary voltage for supplying the auxiliary motor 20 is available in a manner to be explained, which is lower than the supply voltage of the motor vehicle, it is preferably so that the rated voltage of the main motor 17 higher, preferably by more is 1.5 times, more preferably more than twice, higher than the rated voltage of the auxiliary motor 20.

Aus den obigen, bevorzugten Auslegungsvarianten für Hauptmotor 17 und Hilfsmotor 20 kommt der Ansteuerung der Antriebsanordnung 1 ganz besondere Bedeutung zu. Hierfür ist vorzugsweise eine Antriebssteuerung 26 vorgesehen, die im Sinne einer übersichtlichen Darstellung lediglich in Fig. 3 angedeutet ist.From the above, preferred design variants for main engine 17 and auxiliary motor 20, the control of the drive assembly 1 is of very particular importance. For this purpose, a drive control 26 is preferably provided, which in the sense of a clear representation only in Fig. 3 is indicated.

Im Normalbetrieb steuert die Antriebssteuerung 26 den Hauptmotor 17 mit einer höheren Versorgungsspannung, vorzugsweise mit einer um mehr als das 1,5-fache, vorzugsweise um mehr als das Zweifache, höheren Versorgungsspannung an, als dies im Notbetrieb für den Hilfsmotor 20 vorgesehen ist.In normal operation, the drive controller 26 controls the main motor 17 with a higher supply voltage, preferably with a more than 1.5 times, preferably more than twice, higher supply voltage than is provided in emergency operation for the auxiliary motor 20.

In besonders bevorzugter Ausgestaltung steuert die Antriebssteuerung 26 den Hauptmotor 17 im Normalbetrieb und den Hilfsmotor 20 im Notbetrieb so an, dass das Motormoment im Normalbetrieb höher, vorzugsweise um mehr als das Zehnfache höher, ist als das Motormoment im Notbetrieb. Übersetzungsbedingt ist es dabei jedoch so, dass im Notbetrieb der Hilfsmotor 17 eine höhere Aushebekraft, vorzugsweise eine um mehr als das Fünffache höhere Aushebekraft, auf die Sperrklinke 4 ausübt als dies im Normalbetrieb vom Hauptmotor 17 bewerkstelligt wird.In a particularly preferred embodiment, the drive control 26 controls the main motor 17 in normal operation and the auxiliary motor 20 in emergency operation so that the engine torque in normal operation higher, preferably higher by more than ten times, than the engine torque in emergency mode. Due to the translation, however, it is so that in emergency operation, the auxiliary motor 17, a higher Aushebekraft, preferably a more than five times higher Aushebekraft, on the pawl 4 exerts than this is accomplished in normal operation by the main motor 17.

Grundsätzlich kann es vorgesehen sein, dass der Hauptmotor 17 und/oder der Hilfsmotor 20 unidirektional betreibbar ist bzw. sind. Hier und vorzugsweise ist es allerdings so, dass jedenfalls der durch den Hauptmotor 17 bewirkte Aushebezyklus der Sperrklinke 4 eine Hinbewegung und eine Rückbewegung des ersten Getriebelements, hier des Hohlrads 15, umfasst.In principle, provision may be made for the main motor 17 and / or the auxiliary motor 20 to be or can be operated unidirectionally. However, here and preferably it is the case that in any case the lifting cycle of the pawl 4 caused by the main motor 17 comprises a forward movement and a return movement of the first gear element, here the ring gear 15.

Im Sinne der bei Planetengetrieben üblichen Funktionsweise ist es erforderlich, dass im Normalbetrieb das zweite Getriebeelement, hier das Sonnenrad 13, festgelegt ist und dass im Notbetrieb das erste Getriebeelement, hier das Hohlrad 15, festgelegt ist.In terms of the usual in planetary gearbox operation, it is necessary that in normal operation, the second transmission element, here the sun gear 13, is fixed and that in emergency operation, the first gear element, here the ring gear 15, is fixed.

Entsprechend wird vorgeschlagen, dass dem ersten Getriebeelement, hier dem Hohlrad 15, und/oder dem zweiten Getriebeelement, hier dem Sonnenrad 13, eine Stellbegrenzung 27 zugeordnet ist bzw. sind, die bei einem Ausheben der Sperrklinke 4 mittels des Hauptmotors 17 oder des Hilfsmotors 20 eine Blockierung des zweiten Getriebeelements bzw. des ersten Getriebeelements bewirkt. Hier und vorzugsweise definiert die Stellbegrenzung 27 zwei Endstellungen des zugeordneten Getriebeelements. Weiter vorzugsweise ist es so, dass die Stellbegrenzung 27 das zugeordnete Getriebeelement bei Erreichen der Endstellung blockiert.Accordingly, it is proposed that the first gear element, here the ring gear 15, and / or the second gear element, here the sun gear 13, a control limit 27 is associated or are, in a lifting of the pawl 4 by means of the main motor 17 or the auxiliary motor 20th causes a blockage of the second transmission element and the first transmission element. Here and preferably, the control limit 27 defines two end positions of associated transmission element. Further preferably, it is such that the control limit 27 blocks the associated transmission element upon reaching the end position.

Bei dem dargestellten und insoweit bevorzugten Ausführungsbeispiel ist dem ersten Getriebeelement, hier dem Hohlrad 15, eine Stellbegrenzung 27 zugeordnet. Die Stellbegrenzung 27 weist ein am Hohlrad 15 angeordnetes Anschlagelement 28 auf, in dessen Bewegungsbereich die beiden Gegenanschlagelemente 29, 30 liegen. Insoweit begrenzt die Stellbegrenzung 27 die Hinbewegung und die Rückbewegung des ersten Getriebeelements, hier des Hohlrads 15, im Rahmen des durch den Hauptmotor 17 bewirkten Aushebezyklus. Angesichts dieser Stellbegrenzung 27 ist es für den Notbetrieb nicht erforderlich, dass die antriebstechnische Kopplung zwischen dem Hauptmotor 17 und dem ersten Getriebeelement, hier dem Hohlrad 15, selbsthemmend ist. Entsprechend ist es vorzugsweise so, dass die antriebstechnische Kopplung zwischen dem Hauptmotor 17 und dem ersten Getriebeelement, hier dem Hohlrad 15, nicht selbsthemmend ist und dem ersten Getriebeelement, hier dem Hohlrad 15, eine Stellbegrenzung 27 zugeordnet ist. Alternativ oder zusätzlich ist es vorgesehen, dass die antriebstechnische Kopplung zwischen dem Hilfsmotor 20 und dem zweiten Getriebeelement, hier dem Sonnenrad 13, selbsthemmend ist. Grundsätzlich kann es aber auch vorgesehen sein, dass auch dem zweiten Getriebeelement, hier dem Sonnenrad 13, eine Stellbegrenzung zugeordnet ist.In the illustrated preferred embodiment, the first gear element, here the ring gear 15, a control limit 27 assigned. The adjusting limiter 27 has a stop element 28 arranged on the ring gear 15, in the movement region of which the two counter-stop elements 29, 30 are located. In that regard, the control limit 27 limits the forward movement and the return movement of the first gear element, here the ring gear 15, in the context of the lifting cycle caused by the main motor 17. In view of this control limit 27, it is not necessary for emergency operation that the drive technology coupling between the main motor 17 and the first transmission element, here the ring gear 15, is self-locking. Accordingly, it is preferably such that the drive technology coupling between the main motor 17 and the first gear element, here the ring gear 15, is not self-locking and the first gear element, here the ring gear 15, a control limit 27 is assigned. Alternatively or additionally, it is provided that the drive technology coupling between the auxiliary motor 20 and the second transmission element, here the sun gear 13, is self-locking. In principle, however, it can also be provided that an adjustment limit is also assigned to the second transmission element, in this case the sun gear 13.

Mit der obigen Auslegung lässt sich im Normalbetrieb das Hohlrad 15 mittels des Hauptmotors 17 in Fig. 4 im Uhrzeigersinn schwenken, bis das Anschlagelement 28 in das Gegenanschlagelement 30 fährt. Während dieser Verstellung des Hohlrads 15 ist das Sonnenrad 13 über den Hilfsmotor 20 und die Getriebestufe 25 festgelegt, so dass der Planetenradträger in Fig. 4 im Uhrzeigersinn schwenkt. Dies entspricht einem Schwenken des Übertragungselements 24 in Fig. 2 entgegen dem Uhrzeigersinn, so dass die Sperrklinke 4 über das Abtriebselement 8 ausgehoben wird. Die Rückbewegung im Rahmen dieses Aushebezyklus lässt sich durch eine entsprechende Ansteuerung des Hauptmotors 17 erreichen. Auch diese Rückbewegung wird durch die Stellbegrenzung 27 begrenzt, nämlich durch den Kontakt zwischen dem Anschlagelement 28 und dem Gegenanschlagelement 29.With the above interpretation can be in normal operation, the ring gear 15 by means of the main motor 17 in Fig. 4 Swing clockwise until the stop element 28 moves into the counter-stop element 30. During this adjustment of the ring gear 15, the sun gear 13 is fixed via the auxiliary motor 20 and the gear stage 25, so that the planet carrier in Fig. 4 pivots clockwise. This corresponds to a pivoting of the transmission element 24 in FIG Fig. 2 counterclockwise, so that the pawl 4 is lifted via the output element 8. The return movement in the context of this lifting cycle can be achieved by a corresponding control of the main motor 17. This return movement is limited by the control limit 27, namely by the contact between the stop element 28 and the counter-stop element 29th

Im Notbetrieb, beispielsweise im Crashfall, wird nicht der Hauptmotor 17, sondern in noch zu erläuternder Weise der Hilfsmotor 20 angesteuert. Aufgrund der nicht selbsthemmenden Kopplung zwischen Hauptmotor 17 und Hohlrad 15 ist der Antrieb des Hilfsmotors 20 mit einem Schwenken des Sonnenrads 13 in Fig. 4 im Uhrzeigersinn verbunden. Dies ist zunächst mit einem Schwenken des Hohlrads 15 in Fig. 4 im Uhrzeigersinn verbunden, bis das Anschlagelement 28 in das Gegenanschlagelement 30 läuft. Anschließend kommt es zu einer Übertragung des Antriebsmoments auf den Planetenradträger 14, so dass der Planetenradträger 14 in Fig. 4 im Uhrzeigersinn schwenkt. Dies entspricht einem Schwenken des Übertragungselements 24 in Fig. 2 entgegen dem Uhrzeigersinn, was über das Abtriebselement 8 wiederum zu einem Ausheben der Sperrklinke 4 führt.In emergency operation, for example in the event of a crash, not the main engine 17, but in the manner to be explained, the auxiliary motor 20 is driven. Due to the non-self-locking coupling between the main motor 17 and ring gear 15, the drive of the auxiliary motor 20 with a pivoting of the sun gear 13 in Fig. 4 connected in a clockwise direction. This is first with a pivoting of the ring gear 15 in Fig. 4 connected in a clockwise direction until the stop member 28 runs in the counter-stop member 30. Subsequently, there is a transmission of the drive torque to the planet 14, so that the planet carrier 14 in Fig. 4 pivots clockwise. This corresponds to a pivoting of the transmission element 24 in FIG Fig. 2 counterclockwise, which in turn leads to the output element 8 to a lifting of the pawl 4.

Interessant bei der oben angesprochenen Stellbegrenzung 27 des Hohlrads 15 ist die Tatsache, dass vor der Übertragung von Antriebsmomenten auf den Planetenradträger 14 der Hilfsmotor 20 eine Art Freilauf durchführt, nämlich bis das Anschlagelement 28 in das Gegenanschlagelement 30 läuft. Dieser Freilauf kann je nach Auslegung des Hilfsmotors 20 vorteilhaft sein, da er einen Anlauf des Hilfsmotors 20 bei geringer Belastung des Hilfsmotors 20 erlaubt. Dies eröffnet weitere Freiheitsgrade bei der Auswahl des Hilfsmotors 20.Interesting in the above-mentioned control limit 27 of the ring gear 15 is the fact that prior to the transmission of drive torque to the planet 14 of the auxiliary motor 20 performs a kind of freewheel, namely until the stop member 28 runs in the counter-stop member 30. This freewheel can be advantageous depending on the design of the auxiliary motor 20, since it allows a start-up of the auxiliary motor 20 at low load of the auxiliary motor 20. This opens up further degrees of freedom in the selection of the auxiliary motor 20.

Es darf darauf hingewiesen werden, dass der Begriff "selbsthemmend" vorliegend weit auszulegen ist. Er umfasst auch eine bremsende Ausgestaltung der betreffenden Komponenten, soweit das oben angesprochene, für die Funktionsweise eines Planetengetriebes erforderliche Festlegen des jeweiligen Getriebeelements erfüllt ist.It may be pointed out that the term "self-locking" has to be interpreted broadly in this case. It also includes a braking configuration of the relevant components, as far as the above-mentioned, required for the functioning of a planetary gear setting the respective transmission element is met.

Es darf ferner auf eine konstruktive Besonderheit der dargestellten und insoweit bevorzugten Antriebsanordnung 1 hingewiesen werden. Die Antriebsanordnung 1 ist mit einem Gehäuse 33 ausgestattet, das Bestandteil des Gehäuses des Kraftfahrzeugschlosses 2 sein kann. Denkbar ist aber auch, dass das Gehäuse 33 der Antriebsanordnung 1 separat von dem Gehäuse des Kraftfahrzeugschlosses 2 im Übrigen ausgestaltet ist. Das Gehäuse 33 der Antriebsanordnung 1 nimmt alle Getriebeelemente, hier das Sonnenrad 13, den Planetenradträger 14 und das Hohlrad 15 auf. Das Übertragungselement 24 und das Abtriebselement 8 sind jedoch außerhalb des Gehäuses 33 angeordnet. Damit lässt sich das Gehäuse 33 der Antriebsanordnung 1 bis auf die für die Ankopplung des Übertragungselements 24 erforderliche Durchbrechung weitgehend kapseln. Das Gehäuse 33 ist zweiteilig ausgestaltet und weist zwei Halbschalen auf, von denen in der Zeichnung nur eine dargestellt ist.It may also be pointed to a constructive feature of the illustrated and so far preferred drive assembly 1. The drive assembly 1 is equipped with a housing 33 which may be part of the housing of the motor vehicle lock 2. It is also conceivable that the housing 33 of the drive assembly 1 is configured separately from the housing of the motor vehicle lock 2 otherwise. The housing 33 of the drive assembly 1 receives all gear elements, here the sun gear 13, the planet carrier 14 and the ring gear 15. However, the transmission element 24 and the output element 8 are arranged outside the housing 33. This allows the housing 33rd largely encapsulate the drive assembly 1 to the required for the coupling of the transmission element 24 opening. The housing 33 is designed in two parts and has two half-shells, of which only one is shown in the drawing.

Nach einer weiteren Lehre, der eigenständige Bedeutung zukommt, wird das obige Kraftfahrzeugschloss 2 als solches beansprucht. Auf alle obigen Ausführungen darf verwiesen werden, sofern diese geeignet sind, das Kraftfahrzeugschloss 2 zu beschreiben.According to another teaching, which has independent significance, the above motor vehicle lock 2 is claimed as such. Reference may be made to all the above explanations, provided that they are suitable for describing the motor vehicle lock 2.

Das Kraftfahrzeugschloss 2 ist vorzugsweise mit einer oben angesprochenen Antriebssteuerung 26 ausgestattet. Ferner kann es vorteilhaft sein, dass das Kraftfahrzeugschloss 2 eine Hilfsspannungsquelle 31 aufweist, die für die Versorgung des Hilfsmotors 20 im Notbetrieb vorgesehen ist, wobei die Hilfsspannung der Hilfsspannungsquelle 31 kleiner ist als die Versorgungsspannung des Kraftfahrzeugs. Die Hilfsspannungsquelle 31 ist nur in Fig. 3 angedeutet.The motor vehicle lock 2 is preferably equipped with an above-mentioned drive control 26. Furthermore, it may be advantageous that the motor vehicle lock 2 has an auxiliary voltage source 31, which is provided for the supply of the auxiliary motor 20 in emergency operation, wherein the auxiliary voltage of the auxiliary voltage source 31 is smaller than the supply voltage of the motor vehicle. The auxiliary voltage source 31 is only in Fig. 3 indicated.

Nach einer weiteren Lehre, der ebenfalls eigenständige Bedeutung zukommt, wird ein Verfahren zur Ansteuerung eines vorschlagsgemäßen Kraftfahrzeugschlosses 2 beansprucht. Wesentlich dabei ist, dass der Hilfsmotor 20 zum Ausheben der Sperrklinke 4 angesteuert wird, wenn ein Notbetrieb, insbesondere ein Crashfall, erkannt wird.According to another teaching, which also has independent significance, a method for controlling a proposed motor vehicle lock 2 is claimed. It is essential that the auxiliary motor 20 is driven to lift the pawl 4 when an emergency operation, in particular a crash, is detected.

In besonders bevorzugter Ausgestaltung der weiteren Lehre wird ein Notbetrieb basierend auf einem Sensorsignal, hier und vorzugsweise basierend auf einem Sensorsignal eines Crashsensors 32, erkannt. Ein solcher Crashsensor 32 ist ebenfalls nur in Fig. 3 angedeutet.In a particularly preferred embodiment of the further teaching, an emergency operation is detected based on a sensor signal, here and preferably based on a sensor signal of a crash sensor 32. Such a crash sensor 32 is also only in Fig. 3 indicated.

In weiter bevorzugter Ausgestaltung wird im Normalbetrieb der Hauptmotor 17, wie oben angesprochen, mit einer höheren Versorgungsspannung, vorzugsweise mit einer um mehr als das 1,5-fache, vorzugsweise mit einer mehr um das Zweifache höheren, Versorgungsspannung angesteuert als dies im Notbetrieb für den Hilfsmotor 17 der Fall ist.In a further preferred embodiment, in normal operation, the main motor 17, as mentioned above, with a higher supply voltage, preferably with a more than 1.5 times, preferably with a more than two times higher, supply voltage is controlled than in emergency mode for the Auxiliary engine 17 is the case.

Weiter vorzugsweise ist es so, dass der Hauptmotor 17 im Normalbetrieb und der Hilfsmotor 20 im Notbetrieb so angesteuert werden, dass das Motormoment im Normalbetrieb höher, vorzugsweise um mehr als das Zehnfache höher ist als das Motormoment im Notbetrieb, wobei jedoch übersetzungsbedingt im Notbetrieb der Hilfsmotor 20 eine höhere Aushebekraft, vorzugsweise um mehr als das Fünffache höhere Aushebekraft, auf die Sperrklinke 4 ausübt als dies im Normalbetrieb für den Hauptmotor 17 der Fall ist.Further preferably, it is such that the main motor 17 in normal operation and the auxiliary motor 20 are controlled in emergency operation so that the engine torque in Normal operation higher, preferably by more than ten times higher than the engine torque in emergency mode, but with the translation due to emergency operation of the auxiliary motor 20, a higher Aushebekraft, preferably by more than five times higher Aushebekraft, on the pawl 4 exerts than in normal operation for the main engine 17 is the case.

Claims (15)

  1. Drive assembly for a motor vehicle lock (2), wherein the motor vehicle lock (2) comprises the locking elements lock latch (3) and locking pawl (4), wherein the lock latch (3) can be moved into an open position and into at least one locking position, wherein the locking pawl (4) can be moved into a dropped-in position in which it secures the lock latch (3) in the locking position and into a lifted-out position in which it releases the lock latch (3), wherein, in the mounted state, the drive assembly (1) is coupled or can be coupled via an output element (8) to the locking pawl (4) to lift out the latter,
    wherein the drive assembly (1) comprises a planetary gear mechanism (12) having the gear mechanism elements sun gear (13), planet gear carrier (14) and ring gear (15), and that, for lifting out the locking pawl (4) in normal operation, the drive assembly (1) comprises a main motor (17) which is coupled or can be coupled to a first gear mechanism element of the gear mechanism elements sun gear (13), planet gear carrier (14) and ring gear (15), and that, for lifting out the locking pawl (4) in emergency operation, in particular in a crash situation, the drive assembly (1) comprises an auxiliary motor (20) which is coupled or can be coupled to a second gear mechanism element of the gear mechanism elements sun gear (13), planet gear carrier (14) and ring gear (15).
  2. Drive assembly according to Claim 1, characterized in that the output element (8) is coupled or can be coupled to the third gear mechanism element of the gear mechanism elements sun gear (13), planet gear carrier (14) and ring gear (15), preferably in that the output element (8) is a constituent part of the third gear mechanism element of the gear mechanism elements sun gear (13), planet gear carrier (14) and ring gear (15).
  3. Drive assembly according to Claim 1 or 2, characterized in that the first gear mechanism element is the ring gear (15), the second gear mechanism element is the sun gear (13) and the third gear mechanism element is the planet gear carrier (14) of the planetary gear mechanism (12).
  4. Drive assembly according to one of the preceding claims, characterized in that the main motor (15) is coupled permanently to the first gear mechanism element, and/or in that the auxiliary motor (20) is coupled permanently to the second gear mechanism element.
  5. Drive assembly according to one of the preceding claims, characterized in that the torque transmission between the auxiliary motor (20) and the gear mechanism element assigned to the output element (8) is higher, preferably more than five times higher, than the torque transmission between the main motor (17) and the gear mechanism element assigned to the output element (8).
  6. Drive assembly according to one of the preceding claims, characterized in that the drive coupling between the auxiliary motor (20) and the second gear mechanism element comprises at least one additional torque-transmitting gear mechanism stage (25), in particular at least one additional spur gear mechanism stage (25).
  7. Drive assembly according to one of the preceding claims, characterized in that the rated torque of the main motor (17) is higher, preferably more than five times higher, than the rated torque of the auxiliary motor (20), and/or in that the rated voltage of the main motor (17) is higher, preferably more than 1.5 times, more preferably more than two times higher, than the rated voltage of the auxiliary motor (20).
  8. Drive assembly according to one of the preceding claims, characterized in that there is provided a drive controller (26) which controls the main motor (17) in normal operation with a higher supply voltage, preferably with a supply voltage which is more than 1.5 times, preferably two times, higher than that with which the auxiliary motor (20) is controlled in emergency operation.
  9. Drive assembly according to one of the preceding claims, characterized in that there is provided a drive controller (26) which controls the main motor (17) in normal operation and the auxiliary motor (20) in emergency operation in such a way that the motor torque of the main motor (17) in normal operation is higher, preferably more than ten times higher, than the motor torque of the auxiliary motor (20) in emergency operation, in that, however, due to the transmission ratio in emergency operation, the auxiliary motor (20) exerts a higher lifting-out force on the locking pawl (4) than the main motor (17) in normal operation, preferably a lifting-out force which is more than five times higher.
  10. Drive assembly according to one of the preceding claims, characterized in that the first gear mechanism element and/or the second gear mechanism element is or are assigned a position limiter (27) which causes blocking of the second gear mechanism element or of the first gear mechanism element when the locking pawl (4) is being lifted out by means of the main motor (17) or the auxiliary motor (20), preferably in that the position limiter (27) defines two end positions of the assigned gear mechanism element, preferably in that the position limiter (27) blocks the assigned gear mechanism element on reaching the end position.
  11. Drive assembly according to Claim 10, characterized in that the drive coupling between the main motor (17) and the first gear mechanism element is not self-locking and the first gear mechanism element is assigned a position limiter (27), and/or in that the drive coupling between the auxiliary motor (20) and the second gear mechanism element is self-locking.
  12. Motor vehicle lock having the locking elements lock latch (3) and locking pawl (4), wherein the lock latch (3) can be moved into an open position and into at least one locking position, wherein the locking pawl (4) can be moved into a dropped-in position in which it secures the lock latch (3) in the locking position and into a lifted-out position in which it releases the lock latch (3), wherein a drive assembly (1) is coupled or can be coupled via an output element (8) to the locking pawl (4) to lift out the latter,
    characterized
    in that the drive assembly (1) is configured according to one of the preceding claims.
  13. Method for controlling a motor vehicle lock (2) according to Claim 12,
    characterized
    in that the auxiliary motor (20) is controlled to lift out the locking pawl (4) if an emergency operation, in particular a crash situation, is detected.
  14. Method according to Claim 13, characterized in that the main motor (17) is controlled in normal operation with a higher supply voltage, preferably with a supply voltage which is more than 1.5 times, preferably more than two times, higher than that with which the auxiliary motor (20) is controlled in emergency operation.
  15. Method according to Claim 13 or 14, characterized in that the main motor (17) in normal operation and the auxiliary motor (20) in emergency operation are controlled in such a way that the motor torque in normal operation is higher, preferably more than ten times higher, than the motor torque in emergency operation, in that, however, due to the transmission ratio in emergency operation, the auxiliary motor (20) exerts a higher lifting-out force on the locking pawl (4) than the main motor (17) in normal operation, preferably a lifting-out force which is more than five times higher.
EP14183229.5A 2013-10-04 2014-09-02 Drive assembly for a motor vehicle lock Not-in-force EP2857616B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013111039.8A DE102013111039A1 (en) 2013-10-04 2013-10-04 Drive arrangement for a motor vehicle lock

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EP2857616A2 EP2857616A2 (en) 2015-04-08
EP2857616A3 EP2857616A3 (en) 2016-07-13
EP2857616B1 true EP2857616B1 (en) 2017-11-15

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DE (1) DE102013111039A1 (en)
ES (1) ES2654491T3 (en)

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DE102019126570A1 (en) * 2019-10-02 2021-04-08 Kiekert Aktiengesellschaft Drive arrangement for a motor vehicle lock

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DE202015104678U1 (en) * 2015-09-03 2016-12-06 BROSE SCHLIEßSYSTEME GMBH & CO. KG Motor vehicle lock
DE102016115439A1 (en) * 2016-08-19 2018-02-22 BROSE SCHLIEßSYSTEME GMBH & CO. KG Motor vehicle lock arrangement
DE102018125644A1 (en) * 2018-10-16 2020-04-16 Kiekert Aktiengesellschaft Motor vehicle lock
DE102019115273A1 (en) * 2019-06-06 2020-12-10 Kiekert Aktiengesellschaft Motor vehicle lock
DE102020121519A1 (en) 2020-08-17 2022-02-17 Kiekert Aktiengesellschaft Electrically operable device for a motor vehicle access system
DE102021127452A1 (en) 2021-10-22 2023-04-27 Kiekert Aktiengesellschaft Motor vehicle lock, in particular motor vehicle door lock

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DE19710531B4 (en) 1997-03-14 2007-01-18 Brose Schließsysteme GmbH & Co.KG Motor vehicle door lock
DE19935589A1 (en) * 1999-08-02 2001-02-15 Bosch Gmbh Robert Motor vehicle door lock or the like.
DE10251382A1 (en) * 2002-11-01 2004-05-13 Siemens Ag Method for actuating a pawl in a lock with a rotary latch for a motor vehicle
DE10332446A1 (en) * 2003-07-17 2005-02-10 Kiekert Ag Motor vehicle door lock

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DE102019126570A1 (en) * 2019-10-02 2021-04-08 Kiekert Aktiengesellschaft Drive arrangement for a motor vehicle lock
WO2021063440A1 (en) 2019-10-02 2021-04-08 Kiekert Ag Drive assembly for a motor vehicle lock

Also Published As

Publication number Publication date
ES2654491T3 (en) 2018-02-13
EP2857616A3 (en) 2016-07-13
EP2857616A2 (en) 2015-04-08
DE102013111039A1 (en) 2015-04-09

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