EP0064763B1 - Commande, en particulier commande de déplacement dans un véhicule à moteur - Google Patents

Commande, en particulier commande de déplacement dans un véhicule à moteur Download PDF

Info

Publication number
EP0064763B1
EP0064763B1 EP82104073A EP82104073A EP0064763B1 EP 0064763 B1 EP0064763 B1 EP 0064763B1 EP 82104073 A EP82104073 A EP 82104073A EP 82104073 A EP82104073 A EP 82104073A EP 0064763 B1 EP0064763 B1 EP 0064763B1
Authority
EP
European Patent Office
Prior art keywords
drive
displacer
spring brake
drive according
hollow cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP82104073A
Other languages
German (de)
English (en)
Other versions
EP0064763A3 (en
EP0064763A2 (fr
Inventor
Rolf Leistner
Herbert Becker
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.)
Bayerische Motoren Werke AG
Brose Fahrzeugteile SE and Co KG
Original Assignee
Bayerische Motoren Werke AG
Brose Fahrzeugteile SE 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.)
Filing date
Publication date
Application filed by Bayerische Motoren Werke AG, Brose Fahrzeugteile SE and Co KG filed Critical Bayerische Motoren Werke AG
Publication of EP0064763A2 publication Critical patent/EP0064763A2/fr
Publication of EP0064763A3 publication Critical patent/EP0064763A3/de
Application granted granted Critical
Publication of EP0064763B1 publication Critical patent/EP0064763B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G11/00—Manually-actuated control mechanisms provided with two or more controlling members co-operating with one single controlled member
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/665—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for vertically-sliding wings
    • E05F15/689—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for vertically-sliding wings specially adapted for vehicle windows
    • E05F15/692—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for vertically-sliding wings specially adapted for vehicle windows enabling manual drive, e.g. in case of power failure
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/214—Disengaging means
    • E05Y2201/216—Clutches
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/40—Motors; Magnets; Springs; Weights; Accessories therefor
    • E05Y2201/47—Springs
    • E05Y2201/49—Wrap springs
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/50—Application of doors, windows, wings or fittings thereof for vehicles
    • E05Y2900/53—Type of wing
    • E05Y2900/55—Windows

Definitions

  • the invention relates to an adjustment drive, in particular in a motor vehicle, in particular for a window lifter, with a main drive, an auxiliary drive, a releasable clutch in the force path of the main drive and a wrap spring brake element, wherein the wrap spring brake element is widened when the restoring force exerted by the clutch output member.
  • adjustment movements are increasingly being carried out with the aid of adjustment drives (window lifters, seat adjustment or the like).
  • the main drive fails, e.g. B. a drive electric motor, it is very desirable if adjustment movements can still be carried out, with the help of an auxiliary drive that engages the output member of the clutch while removing the rotary coupling between the main drive-side drive member and output member to an emergency adjustment even with a blocking main drive to enable.
  • Adjustment drives of the type mentioned are known (DE-A-2 705 627 and DE-A-2915669).
  • the wrap spring brake element is used exclusively to prevent an automatic return movement of the element driven by the adjustment drive when the main drive is at a standstill.
  • the self-weight of the driven element (e.g. the window) and the shaking forces during the journey can be considered as restoring forces.
  • the wrap spring brake element is expanded by the output member, so that it brakes against a stationary inner circumferential surface of a brake housing.
  • the force transmission takes place due to entrainment of the wrap spring brake element in the sense of a reduction in diameter.
  • the decoupling takes place in the event of a breakdown of the wrap spring brake element independently by axially moving corresponding coupling parts apart.
  • an overload slip clutch in the force path between the electric motor and the cable drum in an electric motor window regulator.
  • This consists of a wrap spring, which is supported on the inner circumference of an electric motor-side drive element and, in the normal case, takes along an output element which is rigidly connected to the cable drum and is designed as a claw part.
  • the wrap spring is pulled together by the claw part and can therefore slide along the inner circumference of the drive part in order to release the slip clutch.
  • a manual override if the electric motor fails is not provided. The manual rotation of the rope drum when the electric motor is at a standstill is very difficult, if not impossible, since the rope drum would have to be twisted with a force that exceeds the triggering force of the overload friction clutch.
  • the object of the invention is to provide a drive of the type mentioned, which offers the possibility of a quick and easy to start and stop manual override.
  • a hollow cylinder element on the inner circumferential surface of which the wrap spring brake element is supported, is connected in a rotationally fixed manner to a main drive-side drive member, that the output member of the clutch is formed by a first claw part, which is in operation of the main drive presses against one of the ends of the wrap spring brake element in the sense of widening the wrap spring brake element, and that a coupling element which is connectable to the auxiliary drive and is designed as a second claw part is provided, which presses against one of the ends of the wrap spring brake element during operation of the auxiliary drive in the sense of a diameter reduction of the wrap spring brake element , and which is designed to take the first coupling part.
  • the disengaging element can be connected to the auxiliary drive via a plug-in coupling; such a coupling is easy to operate and requires little installation space, especially if the decoupling element is provided with an internal polygon for a manual control element.
  • the drive element on an end face perpendicular to its axis of rotation with axially protruding, on a circumferential line distributed webs is formed between engage the webs correspondingly formed on the hollow cylinder element, an intermediate space having a spring element, preferably a rubber element, being formed in the circumferential direction between the victories.
  • a particularly compact arrangement in the axial direction is obtained in that a bearing collar for the rotary mounting of the hollow cylinder element or of the drive element is formed on the drive element or on the hollow cylinder element.
  • the hollow cylinder element is provided with a metallic insert sleeve having the inner peripheral surface, low-wear operation and a consistently high coefficient of friction between the wrap spring and the inner peripheral surface are achieved.
  • the hollow cylinder element itself can be produced inexpensively from less wear-resistant material, for example from plastic.
  • the first claw part is formed in the region of the two ends of the wrap spring with a flat, preferably approximately dovetail-shaped driver, which is attached to an output shaft and is perpendicular to the axis of rotation of the links and projects radially beyond the inside wrap spring diameter.
  • a flat, preferably approximately dovetail-shaped driver which is attached to an output shaft and is perpendicular to the axis of rotation of the links and projects radially beyond the inside wrap spring diameter.
  • the two drivers can be congruent and / or integrally formed with the drive shaft.
  • the drive according to the invention is particularly suitable as a drive for a motor vehicle window regulator.
  • the output member is connected in a rotationally fixed manner to a pinion which meshes with a threaded cable of a cable window lifter or a toothed segment of a rod window lifter.
  • the output member can alternatively be connected in a rotationally fixed manner to a cable drum for the cable of a cable window lifter.
  • the decoupling element is formed with a partial hollow cylinder which forms the second claw part and is arranged between the wrap spring and the output shaft passing through the wrap spring, the axially extending edges of which interact with the radially inwardly bent ends of the wrap spring.
  • a simple mounting of the decoupling element which in turn requires only little installation space in the axial direction, is formed in such a way that the decoupling element is rotatably mounted in a bearing opening of a drive housing with an axial bearing bolt which may be formed with the polygon.
  • the decoupling element which always takes the members with them even in normal operation, can also be mounted on the first claw part by means of a collar which rests on the circumference of a driver disk that carries one of the drivers and is attached to the drive shaft.
  • the drive shown in FIGS. 1 and 2, generally designated 10, establishes the connection between an electric drive motor, not shown, on the motor shaft of which a worm 12 shown on the right in FIG. 1 is fastened and a threaded cable window lifter in a motor vehicle, the threaded cable 14 in Fig. 1 is drawn lower left.
  • worm 12 and threaded cable 14 runs in sequence over the following coaxially mounted rotating parts: a drive member 16 in the form of a worm wheel meshing with the worm 12, a hollow cylindrical element 18 which is non-rotatably coupled to the drive member 16 and torsionally vibration-damped via a damping rubber part 20 , a wrap spring 22, which is supported on the inner circumference of an insert sleeve 24 inserted into the hollow cylindrical element 18, and an output member 26, the upper end of which in FIG. 1 is provided with two drive disks 28, which form a first claw part and interact with the wrap spring 22, and on whose lower end a pinion 30 engaging in the threaded cable 14 is rotatably pushed on.
  • disengaging element 32 adjoining the output member 26 upwards is not in the force path between the screw 12 and the threaded cable 14; it only rotates during normal operation.
  • the disengaging element 32 is used in the event of a fault, for. B. with a defective drive motor to allow manual operation of the window regulator.
  • the rotating parts 16 to 32 described above are mounted in a two-part housing with a lower housing base 34 in FIG. 1, a housing cover 36 with an intermediate sealing ring 38 and a cover 40 attached to the underside of the housing base 34, which serves as a guide for the threaded cable 14 and the threaded cable 14 and the pinion 30 against contamination downwards covers.
  • the housing can be made of plastic or metal.
  • FIG. 3 The vibration-damped, rotationally fixed connection between the drive member 16 and the hollow cylinder element 18 is illustrated in FIG. 3.
  • the hollow cylinder element 18 is formed with a bearing disk 44 perpendicular to the axis of rotation 42 in FIG. 1, from which a hollow cylinder section 46 adjoins upwards in FIG. 1 (indicated by dotted lines in FIG. 3) in the, as already mentioned, the insert sleeve 24 is inserted.
  • the bearing disc 44 is formed with a central bearing opening 48, with which the hollow cylinder element 18 is rotatably mounted on a correspondingly dimensioned bearing collar 50 of the drive element 16.
  • a bearing neck 52 which projects downward and encompasses the bearing collar 50 is formed on the bearing disk 44, as can also be seen in FIG. 3.
  • the webs 54 are distributed in the radial direction on the circumference of the bearing disc 44, each of which ends shortly before the outer circumference of the bearing disc 44 is reached. As shown in FIG. 1, the webs 54 project downward in the axial direction.
  • the drive member 16 is also formed with three webs 56, the side surfaces 58 of which are parallel to the axis of rotation 42 are indicated in FIG. 3 with dash-dot lines.
  • the webs 56 are each at half an angle between the webs 54, with a space remaining between these webs 54 and 56 in the circumferential direction, which is each completely filled by a correspondingly shaped section 60 of the damping rubber part 20. As shown in FIG.
  • the shape of the wrap spring 22 inserted into the insert sleeve 24 can be seen from FIGS. 1 and 2. Accordingly, the wrap spring 22 is wound in the manner of a solenoid, with both ends, the upper end 72 visible in FIG. 1 and the lower end 74 only visible in FIG. 2, being bent radially inward.
  • the outside diameter of the relaxed wrap spring 22 is somewhat larger than the inside diameter of the insert sleeve 24, so that the wrap spring 22 inserted into the insert sleeve 24 presses radially outward against the inner circumferential surface 76 of the insert sleeve 24.
  • the driving disks 28 interact in accordance with the respective rotational position, specifically the driving disk in FIG. 1 with the upper end 72 and the lower driving disk 28 with the lower end 74.
  • the two driving disks 28 are each formed with an approximately dovetail-shaped driver 78 which, as shown in FIG. 2, extends to the inner circumferential surface 76 of the insert sleeve 24. In this way, it is achieved that the ends 72 and 74 are not bent over by the corresponding drivers 78 even at high torques, since the drivers 78 with their outer corners directly apply the corresponding torque to the ends 72 and 74 in each of the bent ends Transfer circumferential wrap spring section.
  • the two catches 78 prevent the windings of the wrap spring 22 lying between them from moving axially upwards or downwards.
  • the two drive disks 28 are pushed onto both sides of a collar 80 of enlarged diameter of the output shaft 68 and are soldered or welded there.
  • the drive plates can also be formed in one piece with the output shaft.
  • the pinion 30 is non-positively pushed onto a reduced-diameter, corrugated section 82.
  • the decoupling element 32 consists of a circular disk 84 perpendicular to the common axis of rotation 42, from which an axial bearing pin 86 projects upwards in FIG.
  • the bearing pin 86 is rotatably mounted in a corresponding bearing opening 90 in the housing cover 36.
  • a partial hollow cylinder 92 whose cylinder axis coincides with the axis of rotation 42, extends downward from the circular disk 84. As can be seen in FIG. 1, the partial hollow cylinder 92 almost reaches in the axial direction up to the bearing disk 44 of the drive member 16.
  • the cross section of the partial hollow cylinder 92 shown in FIG. 2 corresponds to a circular ring from which a sector has been cut out.
  • edges of the partial hollow cylinder 92 which run in the axial and radial directions, are designated by 94 in the figures. As can be seen from FIG. 2, these edges 94 interact with the corresponding ends 72 and 74 of the wrap spring 22 depending on the direction of rotation, as will be explained in more detail below will be tert.
  • Fig. 1 is further shown a slightly radially inwardly projecting collar 96 formed at the upper axial end of the OperahohlzylinJers 92, which rests on the outer periphery of the drive plate 28 and in this way provides for an additional rotary bearing of the disengaging element 32, namely on the output member 26.
  • the window lifter can still be operated by hand immediately by bringing in the manual override key already mentioned on the vehicle tool kit and inserting it with its external polygon into the internal polygon 88.
  • the key is rotated, for example in direction B
  • the partial hollow cylinder 92 accordingly also rotates in this direction (see FIG. 2).
  • the edge 94 lying further down in FIG. 2 comes to bear against the upper end 72 of the wrap spring 22.
  • the edge 94 pulls on the wrap spring 22 in its longitudinal direction, which causes the wrap spring 22 to lift off from the inner circumferential surface 76 and thus a loosening of the frictional engagement between wrap spring 22 and hollow cylinder element 18.
  • the window lifter can of course also be actuated in the opposite direction without any problems, in which case the partial hollow cylinder 92 with its upper edge 94 in FIG. 2 via the lower end 74 of the wrap spring 22 in FIG. 1 to the lower driver 78 presses.
  • the window can be quickly warped with the help of the key, since the key acts directly on the output member 16 and the pinion 30 connected to it without large intermediate translation.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Power-Operated Mechanisms For Wings (AREA)
  • Window Of Vehicle (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (16)

1. Commande d'entraînement (10) équipant notamment un véhicule automobile, en particulier un lève-vitre, et comprenant un entraînement principal (12), un entraînement auxiliaire (32, 88), un accouplement débrayable (18, 26) sur le trajet du flux de forces de l'entraînement principal, ainsi qu'un élément de freinage à ressort hélicoïdal (22), la force de rappel appliquée par l'organe mené (26) de l'accouplement (18, 26) provoquant un élargissement de l'élément de freinage à ressort hélicoïdal (22), caractérisée par le fait que, lorsque l'entraînement principal (12) est en fonction, la transmission de forces s'opère par un élargissement de l'élément de freinage à ressort hélicoïdal (22) tandis que, lorsque l'entraînement auxiliaire (32, 88) est en fonction, il se produit une réduction du diamètre de l'élément de freinage à ressort hélicoïdal (22) en vue de désaccoupler l'entraînement principal (12).
2. Commande d'entraînement selon la revendication 1, caractérisée par le fait qu'un élément cylindrique creux (18), contre la face circonférentielle interne (76) duquel l'élément de freinage à ressort hélicoïdal (22) est en appui en position de repos, est assujetti en rotation à un organe menant (16) de l'entraînement principal ; par le fait que l'organe mené (26) de l'accouplement est formé par une première griffe (28, 78) qui, lorsque l'entraînement principal (12) est en fonction, exerce une poussée sur l'une des extrémités (72, 74) de l'élément de freinage à ressort hélicoïdal dans le sens d'un élargissement de cet élément de freinage à ressort hélicoïdal (22) ; et par le fait qu'il est prévu un élément de désaccouplement (32) qui peut être relié à l'entraînement auxiliaire, est réalisé en tant que seconde griffe (92, 94), exerce une poussée sur l'une des extrémités (72, 74) de l'élément de freinage à ressort hélicoïdal (22), lorsque l'entraînement auxiliaire est en fonction, dans le sens d'une réduction de diamètre de cet élément de freinage à ressort hélicoïdal (22), et est réalisé en vue de l'entraînement de la première griffe.
3. Commande d'entraînement selon la revendication 1 ou 2, caractérisée par le fait que l'entraînement auxiliaire est formé par un entraînement manuel.
4. Commande d'entraînement selon l'une des revendications 2 et 3, caractérisée par le fait que l'élément de désaccouplement (32) peut être relié à l'entraînement auxiliaire par l'intermédiaire d'un accouplement emboîtable.
5. Commande d'entraînement selon la revendication 4, caractérisée par le fait que l'élément de désaccouplement (32) est muni d'une creusure polygonale (88) destinée à un organe d'actionnement manuel.
6. Commande d'entraînement selon l'une des revendications 2 à 5, caractérisée par le fait que l'organe menant (16) est réalisé, sur une face extrême perpendiculaire à son axe de rotation (42), avec des nervures (56) en saillie axiale réparties sur une ligne périphérique et entre lesquelles s'engagent des nervures correspondantes (54) ménagées sur l'élément cylindrique creux (18), un espace intercalaire comportant une pièce élastique, de préférence une pièce d'amortissement (20, 60) en caoutchouc, étant à chaque fois réservé dans le sens périphérique entre lesdites nervures (54, 56).
7. Commande d'entraînement selon l'une des revendications 1-6, caractérisée par le fait qu'un collet de support (50) est ménagé sur l'organe menant (16) ou sur l'élément cylindrique creux (18), afin de supporter en rotation ledit élément cylindrique creux (18) ou ledit organe menant, respectivement.
8. Commande d'entraînement selon l'une des revendications 2-7, caractérisée par le fait que l'élément cylindrique creux (18) est pourvu d'une douille prisonnière métallique (24) présentant la face circonférentielle interne (76).
9. Commande d'entraînement selon l'une des revendications 2-8, caractérisée par le fait que la première griffe est à chaque fois réalisée, au voisinage des deux extrémités (72, 74) de l'élément de freinage à ressort hélicoïdal (22), avec une came d'entraînement (78) qui, configurée de préférence approximativement en queue d'aronde, est plane, est calée sur un arbre de sortie (68), est perpendiculaire à l'axe de rotation (42) des organes (organe menant 16, organe mené 26) et fait saillie radialement au-delà du diamètre interne du ressort hélicoïdal.
10. Commande d'entraînement selon la revendication 9, caractérisée par le fait que les deux cames d'entraînement (78) sont réalisées à silhouettes identiques.
11. Commande d'entraînement selon la revendication 9 ou 10, caractérisée par le fait que les deux cames d'entraînement (78) sont élaborées d'un seul tenant avec l'arbre de sortie (68).
12. Commande d'entraînement selon l'une des revendications 1-11, caractérisée par le fait que l'organe mené (26) est assujetti en rotation à un pignon (30) qui engrène dans un câble cranté (14) d'un lève-vitre à câble, ou dans un segment denté d'un lève-vitre à tringlerie.
13. Commande d'entraînement selon l'une des revendications 1-11, caractérisée par le fait que l'organe mené (26) est assujetti en rotation à un tambour du câble d'un lève-vitre à câble.
14. Commande d'entraînement selon l'une des revendications 2-13, caractérisée par le fait que l'élément de désaccouplement (32) est réalisé avec un appendice cylindrique creux (92) qui forme la seconde griffe, est interposé entre le ressort hélicoïdal (22) et un arbre ou, respectivement, l'arbre de sortie (68) traversant ce ressort hélicoïdal (22), et dont les bords (94) s'étendant dans le sens axial coopèrent avec les extrémités (72, 74) de l'élément de freinage à ressort hélicoïdal (22) cintrées radialement vers l'intérieur.
15. Commande d'entraînement selon l'une des revendications 5-14, caractérisée par le fait que l'élément de désaccouplement (32) est monté à rotation, à l'aide d'un tenon axial de support (86) éventuellement doté de la creusure polygonale (88), dans un orifice de montage (90) du boîtier de l'entraînement.
16. Commande d'entraînement selon la revendication 15, caractérisée par le fait que l'élément de désaccouplement (32) est monté sur la première griffe au moyen d'un collet (96) appliqué contre le pourtour d'un disque d'entraînement (28) qui porte l'une des cames d'entraînement (78) et est calé sur l'arbre de sortie (68).
EP82104073A 1981-05-11 1982-05-10 Commande, en particulier commande de déplacement dans un véhicule à moteur Expired EP0064763B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3118634 1981-05-11
DE3118634A DE3118634C2 (de) 1981-05-11 1981-05-11 Verstellantrieb mit Schlingfederbremselement in einem Kraftfahrzeug, insbesondere für einen Fensterheber

Publications (3)

Publication Number Publication Date
EP0064763A2 EP0064763A2 (fr) 1982-11-17
EP0064763A3 EP0064763A3 (en) 1983-03-16
EP0064763B1 true EP0064763B1 (fr) 1986-02-12

Family

ID=6131994

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104073A Expired EP0064763B1 (fr) 1981-05-11 1982-05-10 Commande, en particulier commande de déplacement dans un véhicule à moteur

Country Status (5)

Country Link
US (1) US4499787A (fr)
EP (1) EP0064763B1 (fr)
JP (1) JPS57193682A (fr)
DE (1) DE3118634C2 (fr)
ES (1) ES512099A0 (fr)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3438254A1 (de) * 1984-10-18 1986-04-24 Brose Fahrzeugteile GmbH & Co KG, 8630 Coburg Verstellantrieb in einem kraftfahrzeug
US4895048A (en) * 1988-04-25 1990-01-23 United Technologies Electro Systems, Inc. Powered actuator with manual override feature
DE4128257C2 (de) * 1990-08-30 1994-01-05 Kuester & Co Gmbh Elektromotorische Antriebsvorrichtung für einen Bowdenzugfensterheber
DE9415540U1 (de) * 1994-09-26 1994-11-17 Staneck, Brigitte, 25876 Schwabstedt Kraftfahrzeug mit motorisch angetriebenen Fensterhebern
JP3209117B2 (ja) * 1996-09-26 2001-09-17 トヨタ車体株式会社 跳ね上げ式車両ドアの開き保持装置
DE29617557U1 (de) * 1996-10-09 1996-12-05 Burger Söhne GmbH + Co, 71065 Sindelfingen Verstellvorrichtung für einen Fahrzeugsitz
JP4590698B2 (ja) * 2000-07-26 2010-12-01 アイシン精機株式会社 車両用ドア操作アクチュエータ
DE20207519U1 (de) * 2002-05-13 2002-07-25 Rose & Krieger Gmbh Co Kg Elektromotorischer Stellantrieb
US6892495B2 (en) * 2003-06-16 2005-05-17 Arvinmeritor Lvs Espana, S.A. Braking system for a vehicle manual window-lifting mechanism
DE10355721A1 (de) * 2003-11-28 2005-06-23 Zf Friedrichshafen Ag Stellantrieb mit einer Schlingfederanordnung
DE102005008437A1 (de) * 2005-02-24 2006-08-31 Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Coburg Fensterheber für ein Kraftfahrzeug
DE102008021861A1 (de) * 2008-05-02 2009-11-05 Schaeffler Kg Fahrwerksaktuator
DE102008002574B4 (de) 2008-06-20 2010-03-18 Robert Bosch Gmbh Verfahren und Vorrichtung zur Ansteuerung einer Glühkerze
DE102009031555A1 (de) * 2009-06-19 2010-12-23 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Antriebsvorrichtung für ein Verstellsystem eines Kraftfahrzeugs
US8912470B2 (en) * 2009-07-01 2014-12-16 Robert Bosch Gmbh Method and device for controlling a glow plug
DE102011102860B4 (de) 2011-05-31 2022-12-22 Zf Active Safety Gmbh Elektromechanisch betätigbare Kraftfahrzeugbremse mit wahlweiser Selbsthemmung
EP2728097A1 (fr) * 2012-11-05 2014-05-07 Grupo Antolín Ingeniería, S.A. Ensemble d'entraînement pour un régulateur de fenêtre motorisé
CN105987108B (zh) * 2015-01-30 2019-07-09 德昌电机(深圳)有限公司 电动驻车系统的执行器及其自锁机构
US9772029B2 (en) 2015-07-09 2017-09-26 Akebono Brake Industry Co., Ltd. Planetary carrier with spring clutch
DE102021117395A1 (de) * 2020-07-27 2022-01-27 Magna Closures Inc. Kraftbetätigungseinheit für angetriebene tür mit einer mechanisch betätigten kupplungs-/bremseinheit

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA492284A (fr) * 1953-04-21 F. Rossmann Peter Dispositif de commande de glace pour vehicules
DE487155C (de) * 1926-11-01 1929-12-02 Dura Company Federsperre fuer Verstellvorrichtung von Schiebefenstern mit einer die Mittelwelle der Antriebskurbel umschliessenden Bremsfeder
US1973671A (en) * 1932-03-25 1934-09-11 Reginald D Stevenson Clutch mechanism
US1997646A (en) * 1933-09-14 1935-04-16 Dura Co Clutch for window regulators
US2185731A (en) * 1936-02-12 1940-01-02 Spring Clutch Control Inc Transmission mechanism
US2620640A (en) * 1945-10-03 1952-12-09 Gen Motors Corp Flexible coupling
US2771789A (en) * 1948-04-10 1956-11-27 Hupp Corp Window regulating device
US2577181A (en) * 1950-03-02 1951-12-04 Edwin S Christensen Clutch
US3008558A (en) * 1958-07-09 1961-11-14 Curtiss Wright Corp Power transmitting device with spring clutch means
FR1493089A (fr) * 1966-07-08 1967-08-25 Paris & Du Rhone Perfectionnements aux dispositifs d'entraînement associés aux mécanismes lèveglace pour véhicules automobiles et analogues
US3618730A (en) * 1969-12-12 1971-11-09 Vari Typer Corp Torque-limiting clutch
US4034575A (en) * 1973-04-11 1977-07-12 Harald Barth Annular elastic component for flexible jaw coupling
US3930566A (en) * 1973-07-04 1976-01-06 Toyota Jidosha Kogyo Kabushiki Kaisha Device for driving a power window
US3930422A (en) * 1973-07-25 1976-01-06 Fuji Electric Company Ltd. Power transmission apparatus
DE2524583C2 (de) * 1975-06-03 1983-06-09 Brose Fahrzeugteile GmbH & Co KG, 8630 Coburg Fensterheber, insbesondere für Kraftfahrzeuge
IT1075909B (it) * 1977-01-20 1985-04-22 Sessa T Dispositivo alzacristalli per autoveicoli di tipo perfezionato
DE2705627C3 (de) * 1977-02-10 1979-12-20 Metallwerk Max Brose Gmbh & Co, 8630 Coburg Kabelfensterheber
IN150947B (fr) * 1978-03-21 1983-01-29 Rockwell Golde Gmbh
JPS552115A (en) * 1978-06-16 1980-01-09 Sukeo Tsurumi Automatic*manual opening*closing machine
DE2915669A1 (de) * 1979-04-18 1980-10-23 Brose & Co Metallwerk Max Elektrischer fensterheberantrieb fuer einen seilzug- oder gestaengefensterheber
DE3008296C2 (de) * 1980-03-04 1987-02-19 Brose Fahrzeugteile GmbH & Co KG, 8630 Coburg Vorrichtung zum Antrieb einer Seiltrommel eines Seilfensterhebers

Also Published As

Publication number Publication date
JPS57193682A (en) 1982-11-29
US4499787A (en) 1985-02-19
EP0064763A3 (en) 1983-03-16
DE3118634A1 (de) 1983-06-01
EP0064763A2 (fr) 1982-11-17
ES8307170A1 (es) 1983-07-01
ES512099A0 (es) 1983-07-01
DE3118634C2 (de) 1984-03-08

Similar Documents

Publication Publication Date Title
EP0064763B1 (fr) Commande, en particulier commande de déplacement dans un véhicule à moteur
EP0175996B1 (fr) Unité d'entraînement notamment pour le déplacement de glaces, de toits ouvrants, de sièges et d'accessoires d'automobiles similaires
DE3418802C2 (de) Vorrichtung zur Betätigung eines Kraftfahrzeug-Türverschlusses
DE112007002049B4 (de) Feder-Rückstellventil mit Betätigungseinrichtung
EP0697571B1 (fr) Actionneur avec dispositif de rappel à ressort
EP1637775B1 (fr) Actionneur linéaire avec commande manuelle en cas d'urgence
DE2758874A1 (de) Verbesserungen an mit drahtzug arbeitenden fensterhebern, insbesondere fuer kraftfahrzeuge
EP1905147B1 (fr) Electroreducteur
WO2000032956A2 (fr) Mecanisme a galets de serrage
DE4403574C1 (de) Antriebsvorrichtung für ein zwischen Endstellungen verstellbares Teil eines Fahrzeuges
DE2913885A1 (de) Lamellenjalousie mit senkrecht angeordneten lamellen
EP0231214B1 (fr) Transmission a ressort enroule
DE19642031A1 (de) Betätigungseinrichtung eines Trennschalters
EP0250852B1 (fr) Entraînement rotatif à double effet pour organe de positionnement
DE19734815C1 (de) Antriebsvorrichtung für ein verstellbares Fahrzeugteil
DE4101705A1 (de) Handgefuehrte elektrowerkzeugmaschine
DE3420789A1 (de) Antriebseinheit
EP0012250A1 (fr) Dispositif pour mouvoir des vitres de portières, des toits ouvrants ou des structures analogues de véhicules automobiles
EP1019606A1 (fr) Ensemble d'entrainement d'arbre pour portes comportant un arbre a barre de torsion et/ou un arbre d'entrainement
EP1028223B1 (fr) Entraînement auxiliaire pour l'entraînement auxiliaire de fermetures de bâtiment
DE3426428C1 (de) Vorrichtung zur hilfweisen Betätigung von Antrieben, insbesondere von Torantrieben
EP1101964A1 (fr) Accouplement de surcharge
DE3503816C2 (fr)
DE19934629A1 (de) Vorrichtung zum Öffnen und Schließen einer an einem Fahrzeug scharnierartig gelagerten Klappe, insbesondere eines Kofferraumdeckels
DE102006052200B4 (de) Antriebseinrichtung mit Freilauffunktion

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): FR GB IT SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): FR GB IT SE

17P Request for examination filed

Effective date: 19830420

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): FR GB IT SE

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19890511

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19900131

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19940316

Year of fee payment: 13

EUG Se: european patent has lapsed

Ref document number: 82104073.0

Effective date: 19900412

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19950510

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19950510