EP1727953B1 - Lock, in particular for automotive doors, flaps or the like - Google Patents

Abstract

A lock comprises a rotary latch ( 10 ) with a pre-latch position ( 12 ) and a main latch position ( 11 ), the latch being retained by a catch ( 20 ). A combined, power-driven closing and opening aid ensures an increased comfort when closing or opening the door by means of two drive elements ( 50, 60 ) that can be moved simultaneously, namely a closing element ( 50 ) and an opening element ( 60 ). In order to obtain a compact lock, both drive elements ( 50, 60 ) are arranged on a common drive wheel ( 40 ) with a mutual axial offset. Moreover, the closing element ( 50 ) is movable relative to the opening element ( 60 ) in two rotation planes which are axially offset relative to one another. A carrier ( 14 ) is also provided on the rotary latch ( 10 ), in the plane of the closing element ( 50 ), while the catch ( 20 ) has a release finger ( 23 ) arranged in the plane of the opening element. The opening element ( 60 ) is resiliently received in the drive wheel ( 40 ) and can be automatically moved between a retracted position and an extended position.

Description

The invention is directed to a lock specified in the preamble of claim 1 Art. The proposed combined motorized closing and opening aid increases comfort when closing and when opening the door. By means of a motor, a gear is set in motion both in one direction of travel and in the opposite direction. This transmission has two output elements, one of which act as a closing aid and the other as an opening aid and therefore hereinafter "closing element" or "opening element" to be called. Both output elements are permanently connected to the gearbox and therefore always set in motion at the same time.

In the known lock of this type ( DE 101 33 092 A1 ) run the two output elements in the operating case always in opposite directions, which is why two separate output wheels are required. This is space consuming. The two driven wheels must be dimensioned sufficiently large and the output elements are attached to each other so rotationally offset that their two paths of movement do not overlap. After carrying out the closing operation and the opening operation, the two output elements are moved back from the engine from their respective extreme positions to a central position, which not only complicates the control, but also makes space consuming.

The invention has for its object to develop a reliable lock mentioned in the preamble of claim 1 way to form the space. This is inventively achieved by the measures mentioned in claim 1, which has the following special significance.

For the arrangement of the two output elements, a single output gear, on which these elements sit together, is sufficient. As a result, the previously required second output gear is saved and gained space. When turning the output gear The movement paths of the two output elements cut, does not bother for the following reason.

The closing element effecting the closing operation lies in a first plane of rotation in the lock, which is to be referred to as the "closing level", while the opening element causing the opening operation is located in a second rotational plane which is axially offset relative to it and which is to be called the "opening plane". For the closing element, the rotary latch has a catch arranged in the closing plane. The driver is arranged in the open position of the rotary latch outside the rotary path of the closing element, but it is in the pre-locking position and in the main locking position of the rotary latch in the rotational path of the closing element. The pawl has a solution finger positioned in the opening plane for the opening element. The opening element is resiliently received in the output gear and is automatically adjusted due to its suspension against the release finger. When the release finger presses on the opening element, it is in its inoperative push-in position. When the release finger has released the opening element, this moves into its effective extended position. So it can not come to malfunction despite a common output gear. The lock always works reliably.

It is advantageous to move the reversal points of the movement in the two end positions in the control of the common driven gear. When the door is open, the output gear is in the one end position, which should therefore be called "open end position". If, starting from the open end position, the output gear is operated in one direction, it finally arrives in its other end position when the door is closed. This second end position should therefore be referred to as "closing end position". In order to achieve these two end positions, it is sufficient to let drive the motor drive to block, whereupon the controller stops the motor in both end positions, the rotation or counter rotation of the output gear.

Fig. 1a

die Vorderansicht auf das Schloss, wenn sich die Drehfalle in ihrer Offenlage befindet,

Fig. 1b

die Rückansicht auf das gleiche Schloss in der gleichen Betriebsphase,

Fig. 2

eine perspektivische Explosionsdarstellung der wichtigsten Bestandteile des Schlosses,

Fig. 3,

ebenfalls in perspektivischer Darstellung, einen Bestandteil des in Fig. 2 gezeigten Schlosses, nämlich einer Nockenscheibe, in Blickrichtung des Pfeils III von Fig. 2,

Fig. 4a+4b,

in Analogie zu Fig. 1a und 1b die Vorder- bzw. Rückansicht des Schlosses, nachdem eine mit diesem Schloss ausgerüstete Heckklappe eines Fahrzeugs soweit geschlossen wurde, dass eine Drehfalle in ihre Vorrastlage gelangt ist,

Fig. 5a+5b

in Vorder- und Rückansicht eine nachfolgende Betriebsphase des Schlosses, wo ein Motor ein Abtriebsrad aus dessen ursprünglicher Offen-Endstellung in der einen Laufrichtung etwas verdreht hat,

Fig. 6a+6b

die Vorder- und Rückansicht des Schlosses in einer Betriebsphase, wo das Abtriebsrad in seine andere Schließ-Endstellung überführt und dort gestoppt wurde, wobei die Drehfalle in ihre Hauptrastlage eingefallen ist, und

Fig. 7a+7b

die Vorder- und Rückansicht des Schlosses nach einer Rückdrehung des Abtriebsrads wieder bis zur Offen-Endstellung, allerdings in einem sogenannten "Schneelastfall", wo aufgrund einer Vereisung der Drehfalle oder einer auf die Heckklappe wirkenden Schneelast die Drehfalle sich zwar nicht aufgrund ihrer Federbelastung wieder in ihre Offenlage zurückbewegt hat, aber von einer Klinke freigegeben ist.

Further measures and advantages of the invention will become apparent from the dependent claims, the following description and the drawings. In the Drawings, the invention is shown only in one embodiment, but in different operating phases, operating cases. Show it:

Fig. 1a

the front view of the lock when the catch is in its open position,

Fig. 1b

the rear view of the same lock in the same operating phase,

Fig. 2

an exploded perspective view of the main components of the castle,

3,

likewise in perspective view, a component of the lock shown in FIG. 2, namely a cam disk, in the direction of arrow III of FIG. 2,

FIGS. 4a and 4b

in analogy to FIGS. 1a and 1b, the front and rear view of the lock after a tailgate of a vehicle equipped with this lock has been closed so far that a catch has reached its pre-rest position,

Fig. 5a + 5b

in front and rear view of a subsequent phase of operation of the castle, where a motor has a driven wheel from its original open-end position in the one direction slightly twisted,

Fig. 6a + 6b

the front and rear view of the castle in an operating phase, where the output gear has been transferred to its other closed end position and stopped there, the catch has fallen into its Hauptrastlage, and

Fig. 7a + 7b

the front and rear view of the castle after a reverse rotation of the driven wheel back to the open end position, but in a so-called "snow load case" where due an icing of the catch or acting on the tailgate snow load, the catch has not moved back due to their spring load back to its open position, but is released by a pawl.

The lock according to the invention shown in the figures is intended to sit on a tailgate, not shown, of a vehicle. Of course, such a lock could also be attached to a door. In Fig. 1a and 1b, the tailgate is in the open state. In a housing 19, which appears only in the front view of Fig. 1a, but not in the rear view of Fig. 1b, a rotary latch 10 is mounted on a rotation axis 18. The rotary latch 10 is under a spring load illustrated by the arrow 32. When the door is open, the rotary latch 10 is held by the spring load 32 in an open position illustrated by the auxiliary line 10.1.

The rotary latch 10 has a receptacle 11 for a striker 30, which sits fixed to a dash-dotted line indicated body 33 of the vehicle. In the drawings, the one hanger arm has been broken away, which is why the hanger bar 31 highlighted by hatching becomes visible. When the tailgate is open, the bar web 31 is at a distance from the lock. If the flap is closed in the direction of the arrow 34 of Fig. 1a, then the hoop web 31 moves into the receptacle 11 and rotates the case 10 to the in Fig. 4a and 4b apparent and illustrated by an auxiliary line 10.2 Vorrastlage, of a Latch 20 is determined.

As shown in Fig. 1a, the pawl 20 is rotatably mounted at 29 in the housing 19 and is under the action of a spring not shown in detail. The spring exerts on the latch 20 a clarified by the force of arrow 22 spring load. The pawl 20 has in addition to a locking point 21 also has a release finger arranged in its extension 23, which is supported in the open position 10.1 of Fig. 1a and 1b at a still closer to described output element 50 of a uniform output gear 40. There is then a lock ready position of the pawl 20 illustrated in FIGS. 1a and 1b by the auxiliary line 20.1. The open position 10.1 of the rotary latch 10 is determined by a driver 14 arranged on the rotary latch 10 being supported on a stepped shoulder 24 of the latch 20. Like on Best seen in Fig. 2, the pawl-locking point 21 is formed by the inner end of the pawl shoulder 24.

If, however, the Vorrastlage 10.2 of Fig. 4a and 4b is present, the locking point 21 engages a provided in the catch 20 Vorrast 12. Then engages a receptacle 11 of the catch 10 limiting claw the strap web 31 of the retracted bracket 30. Despite this intervention from the bracket 30 in the rotary latch 10 is still a gap between the tailgate and the body 33 before. It is now important to also close this gap, which is done by motor via a combined closing and opening aid.

In the present case, the closing and opening aid is integrated in the output gear 40 and the output gear 40 is constructed from two disks 41, 42 to be described in more detail below. This can best be seen from the exploded view of FIG. The output gear 40 may also be formed as a compact structure, where the two discs 41, 42 are always moved in conformity and therefore could be formed easily relevant. First, this embodiment, not shown in detail, will be described, this description also applies to the illustrated embodiment with the two cases to each other movable discs 41, 42. This occasional mobility will be described later in detail.

The closing and opening aid comprises a motor not shown in detail and a gear, not shown, at the end of the output gear 40 is seated. In the open position 10.1 and in the pre-locking position 10.2 of the rotary latch, the output gear 40 is in its one end position, which is illustrated by the auxiliary line 40.1. Because this end position 40.1 according to Fig. 1a and 1b is present with the door open, it should be referred to as "open-Endslellung". In the output gear 40, two output elements 50, 60 are integrated, of which the first element 50 is effective in the closing process and therefore should be called "opening element". If a sensor detects the pre-locking position of FIGS. 4a and 4b, then the motor is orbited in one direction by a control device, not shown in more detail, whereby the driven wheel rotates in one direction, which in FIGS. 5a and 5b with the Rotary arrow 44 is marked.

The first, the Zuziehvorgang determining output element 50 is to be called "closing element", while the second, the opening operation serving output element 60 "opening element" to be called. The closing element 50 is associated with the already mentioned a disc 41 from the output gear 40 and consists of a projecting on the rear of the disc cam, which should be called "closing cam". For the same reason, this disc 41 will be referred to as a "cam". This lock cam 50 is located outside the actual plane of rotation of the two discs 41, 42 and is in the same plane as the catch 10 with its outline profile parts, in addition to the Vorrast already described 12 also the driving tooth 14 and a main catch to be described 13 belong. In Fig. 5b, the rotational path 51 of the closing cam 50 during rotation 44 of the output gear 40 is indicated by an arrow 51. While in the open position 10.1 of Fig. 1b of the driving tooth 14 is still outside of the dashed lines there illustrated also rotational path 15 from the locking cam 50, the driving tooth 14 projects in Fig. 4b in the rotary path 51 into it. Therefore, during this rotation 44, as illustrated in FIG. 5b, the closing cam 50 abuts against the driving tooth 14. As a result, the rotary catch 10 is entrained and pivoted in the direction of the movement arrow 15 of FIG. 5 b against its spring load 32.

The motor stops when the output gear 40 has reached its other end position, which is marked in Figs. 6a and 6b with the auxiliary line 40.2. This end position 40.2 is reached after the pawl with its locking point 21 has fallen behind a main catch 10.3 of the rotary latch 10. Then the flap is closed. Therefore, this end position should be called 10.2 "closing end position". Then the strap web 31 has penetrated from the striker 30 deep into the lock and is held by the case 10. As has already been said, the main catch 13, the pre-catch 12 and the driving tooth 14, a profile part in the outline of the rotary latch 10 is arranged. In the closed end position 40.2 the engine stops. This can be done by an end stop against which the engine is running. But it is also possible sensors that detect this closing end position 40.2 and stop the engine via the control unit.

The second output element located on the output gear 40, namely the opening element 60, is arranged opposite the closing element 50 in a second, axially offset rotational plane in the lock, which are to be called analogous to "opening plane". The axial offset between the closing plane and opening plane can best be seen from FIG. 2 on the basis of the pawl 20. While the pawl locking point 21 is arranged in the closing plane of the rotary latch 10, its release finger 23 is axially offset and lies in the opening plane in which the opening element 60 is located. The opening element 60 in the present case consists of a slide which is accommodated in a channel 35 best seen in FIG. 2 and guided longitudinally therein. This guide channel 35 extends in the present case substantially diametrically in the second disc 42, which should therefore be called "slide disk". The slider 60 is under the action of a recognizable in Fig. 2 spring 62, which tends to push the slider end 61 on the outline 36 of the slide disc 42, as can be seen from Fig. 5a. Then the extended position of the slider end 61 marked by the auxiliary line 61.1 is present.

In the open end position 40.1 of the driven gear of Fig. 1a and 4b, the slider end 61 is in alignment with the release finger 23 of the pawl 20. The release finger 23 then exerts a pressure on the slider 60, whereby the slider 60 in his by the Auxiliary line 61.2 illustrated Eindrückposition is pressed. In the above-described motor rotation 44 of the output gear 40, the slider end 61 leaves the release finger 23, which can then be supported on the mentioned outline contour 36 of the slide disc 42, namely on the designated in Fig. 2 with 37 support zone 37. The in Fig. 2 Recognizable spring 62 generates a spring force, which is illustrated by the force arrow 63 in FIG. 5a, which pushes the slider 60 back into its extended position 61.1. By end stops not shown in more detail protrudes the slider end 61 in its extended position 61.1 by a defined piece.

In Fig. 5a is, as I said, the rotary latch 10 is still in its Vorrastlage 10.2. The striker 30 is not retracted sufficiently deep, which still exists a gap between the body 33 and the tailgate. Should the emergency then occur, that the rotation 44 of the output gear 40 must be stopped, For example, because an object threatens to get trapped in the gap, the lock can be quickly reopened by counterrotating the motor. In this counter-rotation of the motor, the output gear 40 and thus the slide disc 42 is rotated in the opposite direction in the sense of the dash-dotted motion arrow 45 of Fig. 5a. The resulting rotational travel of the extended slide end 61 is illustrated in FIG. 5 a by a dot-dashed rotary arrow 38. In this counter rotation, the slider end 61 abuts laterally on the release finger 23 and thereby lifts the locking point 21 of the pawl 20 out of the preliminary catch 12 of the rotary latch 10. Then, the rotary latch 10 due to their spring load force 32 automatically go back to their open position of Fig. 1a. In this way, the slider 60 acts as an opening aid for the tailgate.

Fig. 7a and 7b illustrates a trouble-free operability of the lock according to the invention also in that case, where, as already mentioned, the restoring force 32 is not sufficient to turn the catch 10 from its illustrated therein Haupttrastlage 10.3 in its open position 10.1 of Fig. 1a and 1b, although the pawl 20 is in its marked by the auxiliary line 20.2 release position, where the locking point 21 is outside the rotary latch profile of the main catch 13 and the Vorrast 12. Cause can be, as already mentioned, either an icing of the rotary latch 10 or lying on the tailgate snow load, which is why this operating case is generally referred to as "snow load case".

In order to meet this snow load case, it is important not only to design the output gear 40 from the two previously mentioned disks 41, 42, but also to make the two disks 41, 42 rotatable relative to one another. The rotary drive for the output gear 40 engages the slide disc 42. For this purpose, as shown in FIGS. 1a and 7a, a toothed segment 39 is provided in the peripheral region of the slide disk 42. The rotation of the slide disc 42 is transmitted to the cam 41 by a special coupling, the structure of which can be best described with reference to FIGS. 1b and 2.

The coupling is designed as a special rotary guide, consisting of a pin 17 and a ring-segment-like slot 47. The pin 17 is seated as Fig. 2 shows, on the inner surface 16 of the slide disc 42, which faces an analog inner surface 26 of the cam plate 26. As a result, the pin 17 engages in the annular slot 47. Between the two discs 41, 42 there is a torsion spring not shown in detail, which endeavors to obtain the pin 17 at the apparent from Fig. 1b first rotation stop 48, which is formed by the one slot end of the slot 47. During the rotation 44 of the slide disk 42 according to FIG. 5 a, the rotation 44 is also transmitted to the cam disk 41 via the pin 47 resting against the first rotation stop 48, as can be seen from FIG. 5 b. This remains up to the described closing end position 40.2 of the output gear 40 of Fig. 6a and 6b exist. In that regard, the two discs 41, 42 move in conformity with each other; they act as if they were one piece. In the illustrated embodiment, the limited rotational mobility of the two discs 41, 42 already significant for the following reason.

In the closed end position 40.2, as shown in FIG. 6b, the closing cam 50 has moved away from the output gear 40 via the tooth tip 25 of the driving tooth 14. Not only the front end 52, but also the rear end 53 of the closing cam 50 are beyond the tooth tip 25 of the driving tooth 14. The closing cam 50 has generated an "overstroke" designated by a path 54 in FIG. 6b. As the associated Fig. 6a shows, in this overstroke, the slider 60 has moved accordingly in the embodiment of this castle. The slider end 61 is due to the spring load 63 already preceded come in Fig. 5a in its extended position 61.1. Because of this Überhubs 54 then occurs in the normal case, in the reverse rotation 45 of the driven gear 40 already, which in the snow load case according to Fig. 7a and 7b even in the open-end position 40th I of the output gear 40 can be seen. Specifically, the following is done.

Starting from the closing end position 40.2 shown in FIG. 6a, initially only the slide disk 42 is moved in the opposite direction 45 in the event of a motorized reverse rotation 45 via the toothed segment 39. Therefore, as shown in Fig. 6b, and the pin 17, this counter rotation 45 forcibly from. Because of the mentioned spring load between the two discs 41, 42, the cam 41 of this counter-rotation 45 over the distance of the over stroke 54 initially follow, but a further rotation of the cam 41 is stopped, as soon as the lock cam 50 abuts with its rear end 53 against the tooth tip 25. Then, in the reverse rotation 45, the pin 17 in FIG. 6b continues idling in the annular slot 47. During this further rotation, the torsion spring located between the two discs 41, 42 is tensioned.

In the course of reverse rotation 45, however, as already explained with reference to FIG. 5 a, the extended slider end 61 strikes the release finger 23 on its movement path designated 38 in FIG. 5 a and lifts the pawl 20 out of the latch 10 in the manner already described out. If this knowledge is applied to the previously described situation according to FIG. 6b, the driving tooth 14 with its tooth tip 25 has also moved away from the cam rear end 53 in the case of the spring-related reversal of the latch 10. Then the lock cam 50 is free and the effective between the discs 41, 42 torsion spring then automatically rotates the cam 41 again in the apparent from Fig. 1b rest position, where the pin 17 rests resiliently against the rotation stop 48 again. Then again the lock cam 50 on the one hand and the slider 60 on the other hand are substantially congruent in the same angular range of the two-disc driven gear 40. In the snow load case according to Fig. 7a and 7b is then added the following feature.

The special feature is that in the snow load case, as shown in FIG. 7a, the slider end 61 remains in its extended position 61.1, although the release finger 23, a restoring force 22 of the pawl 20 acts on him. The slider 60 is namely not longitudinally displaceable in this snow load case, but locked in its extended position 61.1. For this purpose, the following simple, space-saving resources are used in the invention.

As is apparent from Fig. 2, the slider end 61 is provided with an axial projection 64 pointing in the direction of the dash-dotted axis 27 there. The axial front end of this axial projection 64 is highlighted in FIGS. 2, 5b, 6b and 7b by dot hatching. When the slider 60 is mounted in the guide channel 35 of the slide disk 42, the axial projection 64 projects beyond the slider inner surface 16 in the direction of the adjacent cam disk 41. As illustrated in FIG. 3, the inner surface 26 of the cam 41 is provided with a channel supplement 28, in which the axial projection 64 from the slider end 61st can be impressed. This is always the case when the guide channel 35 of the slider 42 is aligned with the channel supplement 28 of the cam 41. This is always the case in normal operation during the closing process, but during the opening process because of the overstroke 54 only in the final phase.

If the counter-rotation 45 explained in FIG. 6b stops the cam 41, because, as has been explained, the cam tail 53 is supported on the tooth tip 25 after passing through the over-stroke 54, the axial projection 64 moves with its rotation to the axis 27 of the further rotation 45 Fig. 2 pointing support point 65 on a guide segment 49, which is formed by the circular circumference of the cam 41. As best shown in FIG. 3, the guide segment 49 immediately adjoins the opening of the channel supplement 28 in the cam 41. But when the axial projection 64 runs with its support point 65 on this guide segment 55, the extended slide end 61 is no longer depressible. This can be seen particularly well from Fig. 7b explaining the snow load case. While the channel supplement 28 is almost still in its closed end position 40.2 according to FIG. 6b, the axial projection 64 highlighted by dot hatching has finally moved into the described other open end position 40.1 due to its forced movement in the slide disk 42. In this case, its inwardly directed support point 65 is driven onto the guide segment 55 in the peripheral region of the cam 41 and thus the Eindrückbarkeit the slide end 61 is blocked.

In the end position during snow load case as shown in FIG. 7a, the motor has returned via its gear the slide disk 42 by means of its toothed segment 39 in the direction of the dotted arrow 45 in counter rotation to the already described open end position 40.1. At the same time, as shown in FIG. 7b, the pin 17 seated on the slide disk 42 moves in the annular slot 47 of the blocked cam disk 41 in the direction of the opposite end 49. It does not have to come to a new rotation stop between 17 and 49. Is it possible, for example, by removing the snow load from the flap, the snow load pressure between the bar web 31 and the catch 10 to be solved so far that the return spring 32 again a reverse rotation of the case 10 from its Haupttrastlage 10.3 of Fig. 7b in the open position 10.1 of FIG 1a can cause, then pulls the tensioned torsion spring between the discs 41, 42 and the cam 41 of Fig. 7b in reverse direction according to the dash-dotted arrow 45. In this case, the slide disc 42 remains with its pin 17 in the position shown in FIGS. 7a and 7b rest position. The cam 41 continues to rotate until the stop end 48 of its annular slot 47 abuts the stationary pin 17. Then also in Fig. 7b initially offset channel supplement 48 is again in alignment with the highlighted by dot-hatching axial projection 64. The support point 65 from the axial projection 64 is no longer supported, but free. The restoring force 22 of the pawl 20 can then push back via the release finger 23, the slider end 61 back to the output gear 40. In this case, the slider moves in its dashed lines in Fig. 7a marked guide channel 35 inward and the axial projection 64 dives into the thus aligned channel supplement 68 a. Then, the operating conditions shown in FIGS. 1a and 1b are again present. The lock is ready for use again.

LIST OF REFERENCE NUMBERS

10

catch

10.1

Open position of 10 (Figure 1a)

10.2

Pre-rest position of 10 (FIG. 4a)

10.3

Main load position of 10 (Figure 6a)

11

Recording in 10 for 30

12

Pre-rest on 10

13

Main stop at 10

14

Driver, driving tooth

15

Arrow of pivoting movement of 10 (Figure 5)

16

Inner surface of 42 (Fig. 2)

17

Pins on 41 of the rotary guide

18

Rotation axis of 10

19

Lock housing

20

pawl

20.1

Lock ready position of 20

20.2

Release position, lever position of 20

21

Lockout of 20

22

Arrow of the spring load of 20

23

release finger

24

Shoulder at 20

25

Tooth of 14

26

Inner surface of 41

27

Axle of the lock (Fig. 2)

28

Channel extension in 41 (FIG. 3)

29

Bearing axis of 20

30

striker

31

Ironing bar of 30

32

Arrow of the spring load of 10

33

body

34

Arrow of the folding movement of a flap

35

Channel, guide channel in 42 for 60 (Fig. 2)

36

Outline contour of 42

37

Support zone for 23 at 42 (FIG. 2)

38

Turning arrow of 61 (FIG. 5a)

39

Toothed segment at 42 (FIGS. 1a, 7a)

40

output gear

40.1

Open end position of 40

40.2

Closing end position of 40

41

Disc, cam disc

42

Disc, slide disc

44

first running direction of 40, rotation

45

second mating direction of 40, counter rotation

46

Face of 41

47

Ring segment-like slot in 41 of the rotary guide

48

first rotation stop in 47 for 17 (FIG. 1b)

49

second end of 47 for 17 (Figures 7b, 3)

50

Output element for the closing process, closing element, closing cam

51

Turning path of 50 (FIG. 5b)

52

Front end of 50 (Figure 6b)

53

Rear end of 50 (Figure 6b)

54

Overlift of 50 (Figure 6b)

55

Guide segment, circumference of 41 (FIGS. 2, 7)

60

Output element for the opening process, opening element, slide

61

Spool end of 60 (Figures 2, 5a)

61.1

Extension position of 61 (FIG. 5a)

61.2

Indentation position of 61 (FIG. 1a / 4a)

62

feather

63

Arrow of spring force from 62 to 60 (Figure 6a)

64

Axial projection on 61 (FIG. 2)

65

Support point at 64 (FIG. 2)

Claims (27)

1. Lock assembly, especially for vehicle doors, hoods, or the like,
   with a rotary lock (10) that has an initial catch (12) and a main catch (13) and is subjected to spring loading (32)in the direction of its open position (10.1), when the door is opened,
   with a fixed spigot, strap (30) or the like that when the door is closing moves into the rotary lock (10) and swings it to an initial catch position (10.2) when a spring-loaded (22) latch (20) engages in the initial catch (12) of the rotary lock (10),
   with a combined motorized closing and opening aid for the door, including a gear unit with two drive elements (50, 60) that can be set in motion simultaneously and a control device,
   with by means of the control device in which the first drive element functions as a closing element (50) in a direction of travel (44) of the gear unit when closing and the rotary lock (10) swings further from its initial catch position (10.2) to a main catch position (10.3),
   where the latch (20) engages in the main catch (13) of the rotary lock (10) and the door is closed,
   and with in the opposite direction of travel (45) of the gear unit the second output drive element functioning as an opening element (60) during opening and lifting the latch (20) out of the rotary lock (10),
   causing the released rotary lock (10) to rotate back to its open position (10.1) due to its spring loading (32),
   characterized in that
   both output drive elements (50, 60) are seated on a common output drive wheel (40) axially offset to each other,
   the closing element (50) in the lock is arranged in a first plane of rotation, i.e. a closing plane,
   and the opening element (60) initiating the opening operation is located in a second plane of rotation, axially offset relative to the first plane of rotation, in the lock, i.e. in an opening plane,
   the rotary lock (10) has a carrier (14) for the closing element (50) arranged in the closing plane, which when the rotary lock (10) is in the open position (10.1) is located outside the path of rotation (51) of the closing element (50),
   the carrier (14) is arranged both in the initial catch position (10.2) and in the main catch position (10.3) of the rotary lock (10) in the path of rotation (51) of the closing element (50),
   a release finger (23) for the opening element (60), positioned in the opening plane, is seated on the latch (20),
   the opening element (60) is supported spring-loaded (63) in the output drive wheel (40) and because of the spring loading (63) is automatically held opposite the release finger (23) between an ineffective push-in position (61.2) and an effective extraction position (61.1).
2. Lock assembly according to Claim 1, characterized in that the output drive wheel (40) is rotated by the control device in both directions of travel (44, 45) between two stable end positions (40.1, 40.2),
   i.e. a closing end position (40.2) when the door is closed and an opening end position (40.1) when the door is open.
3. Lock according to Claim 1 or 2, characterized in that the closing element (50) is arranged outside the plane of rotation of the output drive wheel (40).
4. Lock according to one of Claims 1 to 3, characterized in that the opening plane of the opening element (60) is arranged at least partially in the plane of rotation of the output drive wheel (40).
5. Lock assembly according to one or more of Claims 1 to 4, characterized in that the closing element is formed from cam (closing cam 50) projecting from a drive wheel (40) and the carrier is formed from a carrier tooth (14) projecting downwards from the rotary lock (10).
6. Lock assembly according to Claim 5, characterized in that the locking cams (50) project axially from the front surface (46) of the output drive wheel (40).
7. Lock assembly according to Claim 5 or 6, characterized in that the rotary lock (10) is arranged in the closing plane and its carrier tooth (14) is formed from a profiled part in the contour of the rotary lock (10).
8. Lock assembly according to one of Claims 5 to 7, characterized in that the latch (20), at least in the locked position (21) engaging with the initial catch (12) or main catch (13) of the rotary lock (10) is arranged in the closing plane but its release finger (23) is in the offset opening plane.
9. Lock assembly according to one or more of Claims 1 to 8, characterized in that the spring-loaded opening element (60) is in its push-in position (61.2) only in the area of the open end position (40.1) of the output drive wheel (40).
10. Lock assembly according to one or more of Claims 1 to 9, characterized in that the spring-loaded opening element consists of a slide (60) sliding longitudinally in the output drive wheel (40),
    with its one slide end (61) spring loaded by the spring loading (63) in the extraction position (61.1).
11. Lock assembly according to Claim 9, characterized in that in the extracted position (61.1) the slide end (61) projects radially beyond the contour of the output drive wheel (40).
12. Lock assembly according to Claim 10 or 11, characterized in that the output drive wheel (40) has a channel (35) for longitudinal guidance of the slide (60).
13. Lock according to Claim 12, characterized in that the guide channel (35) runs essentially diametrically in the output drive wheel (40).
14. Lock assembly according to one or more of Claims 1 to 13, characterized in that at least in the normal case the slide end (61) on one hand and the closing cam (50) on the other hand are essentially positioned in the same rotational angle area of the output drive wheel (40).
15. Lock assembly according to one or more of Claims 1 to 14, characterized in that the output drive wheel (40) consists of two discs (41, 42) that, depending on the case, can rotate, depending on the case, limited relative to each other,
    i.e. on one hand consisting of a slide disc (42) receiving the opening element of the slide (60),
    and on the other hand of a disc with a closing element or with the closing cam (50), i.e. a cam disc (41).
16. Lock assembly according to Claim 15, characterized in that the rotary drive of the output drive wheel (40) engages on the slide disc (42),
    the rotation of the slide disc (42) is transmitted to the cam disc (41) by a coupling positioned in-between,
    when the slide disc (42) is rotated in the direction of travel (44), which determines the closing operating, the coupling always rotates the cam disc (41) with it,
    but when the slide disc (42) is rotated in the opposite direction of travel (45), which determines the opening operation, the cam disc (41) can be decoupled, depending on the case, and remains at rest with, in the decoupling case, only the slide disc (42) rotating back (45).
17. Lock assembly according to Claim 16, characterized in that between the two discs (41, 42) is arranged a rotary spring the spring loading of which rotates the decoupled cam disc (41) back into a defined starting rotational position relative to the slide disk (42).
18. Lock assembly according to Claim 16 or 17, characterized in that the coupling consists of a rotary guide (17, 27),
    and that a rotary stop (48) is arranged at the one end of the rotary guide (17, 27).
19. Lock assembly according to Claim 17 or 18, is characterized in that the spring arranged between the two discs (41, 42) is spring loaded so as to return the rotary guide (17, 47) back to rest on the rotary stop (48).
20. Lock assembly according to Claim 18 or 19, characterized in that the rotary guide consists on one hand of a spigot (17) on the slide disc (42) or on the cam disc
    and on the other hand of slot (47), in the form of an annular segment, in the cam disc (41) or slide disc, in which the spigot (17) is guided.
21. Lock according to one or more of Claims 1 to 20, characterized in that during a motorized closing operation the output drive wheel (40) rotates back over the rotation position, where the locking point (21) of the latch (20) is aligned with the main catch (13) of the rotary lock (10), to the closing end position (40.2) and thus creates an "overtravel" (54)
    and that the latch (20) has sufficient time during this overtravel (54) to engage securely behind the main catch (13) of the rotary lock (10).
22. Lock assembly according to Claim 21, characterized in that in the closing end position (40.2) of the output drive wheel (40) the locking cam (50) engages behind a toothed cap (25) of the carrier tooth (14) of the rotary lock (10).
23. Lock assembly according to Claim 22, characterized in that in a "snowfall case" where after the return rotation of the output drive wheel (40) in the opposite direction of travel (45) the spring loading (32) is not sufficient to swing the released rotary lock (10) back into its open position (10.1), the locking cam (51) strikes against the toothed cap (25) of the carrier tooth (14) during the return rotation (45) of the output drive wheel (40) and stops the further rotation of the cam disc (41),
    but the slide disc (42) continues to rotate back to the open end position (40.1), this decoupling the cam disc (41) in the rotary guide (17, 47) and tensions the rotary spring,
    the slide end (61) remains arrested in the extracted position (61.1) and, on the return rotation (45) of the slider disc (42), lifts the latch (40) out of the rotary lock (10) and then holds it in the lifted out position (20.2)
    until the released rotary lock (10) has swung back into its open position (10.1).
24. Lock assembly according to Claim 23, characterized in that after the rotary lock (10) has swung back the slide end (61) is again pushed back by the latch (20) into its push-in position (61.2) in the slide disc (42).
25. Lock assembly according to Claim 23 or 24, characterized in that the slide (60) has a support point (65) that is aligned opposite its spring loading (63),
    the support point (65) is assigned to at least a pitch-circle shaped guide element (55) on the cam disc (42), with the pitch circle essentially being coaxial with its axis of rotation (27),
    the support point (65) is normally outside the guide element (55) and makes the slide (60) capable of being pushed in,
    but, in the snow load case, when the slide disc (42) is being rotated back the support point (65) slides along the guide segment (55) of the stationary cam disc (41) until the opening end position (40.1) of the slide disc (42),
    and the support point (65) lying against the guide segment (55) holds the slide end (61) in its extracted position (61.1) until the spring-loaded rotary lock (10) has swung back into its open position (10.1)
    and the slide (60) then in the open position (10.1) is again capable of being pushed in when the rotary spring of the rotary guide (17, 47) has rotated the cam disc (41) back until the support point (65) on the slide (60) has left the guide segment (55) on the cam disc (41).
26. Lock assembly according to Claim 25, characterized in that the guide segment (55) is created by the disc contour of the cam disc (42).
27. Lock assembly according to Claim 24 or 25, characterized in that the channel (35) serving as a longitudinal guide of the slide (60) is arranged in the slide disc (42)
    and the slide end (61) is a projection (axial projection 64) opposite the height of the slide disc (60) pointing in the direction of the rotary axis (27),
    a channel extension (28) on the inside (26) of the cam disc (41) is assigned to the slide projection (64),
    in which the axial projection (64) normally then moves into if the slide (60) is brought to its push-in position (61.2),
    the cam disc (41) has the pitch circle segment (55) in contact with the channel extension (28)
    a shoulder area between the axial projection (64) of the slide end (61) forms a support point (65) which in the snowfall case is supported on the cam disc (41).

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