EP2573301A2 - Rear lock for a motor vehicle - Google Patents

Abstract

The tailgate lock has a closing element (2) which is set in the closed position. A rotary latch (5) and a pawl (9) movable between the release position and engaged position in the direction of the closing element, are biased during the open position of the closing element. The pawl is set in the release position, when the rotary latch is out of engagement. When the latch is in engaged position, the latch is prevented from moving in the direction of open position. A delay unit is coupled to the latch, according to movement speed of latch, for the release of closing element.

Description

The invention is directed to a rear lock for a motor vehicle, with a locking element in the closed position and in the direction of a closing element releasing open position biased catch and a pawl which is movable between a release position and an engagement position, wherein the pawl in the release position with the The catch is disengaged and engaged in the engaged position with the catch in such a way that the catch is prevented from moving in the direction of the open position.

A rear lock of the aforementioned type, which can be referred to quite generally as a motor vehicle door lock, is for example from the DE 10 2007 024 672 A1 known and used for example in a tailgate of a motor vehicle. Such a rear lock or such a motor vehicle door lock comprises a lock element, which is connected to a boot lid and is usually equipped with a rotary latch, and a lock counterpart connected to a body of the motor vehicle, which may be in the form of a striker or striker. In order to open the tailgate, a user actuates (eg by means of an electronic key) a control device, by means of which the tailgate can be opened by means of a drive element, which is preferably operated by an electric motor. In this case, a pivotally mounted pawl from an engagement position in which the pawl is in engagement with the rotary latch, deflected in the direction of a release position of the drive element until it has reached the release position and is no longer engaged with the catch, whereby a rotational movement the catch is released from the closed position in the direction of an open position.

In the closed position of the tailgate this is biased for example against a seal. Under bias is to be understood here that the sealing gasket pressure caused by a flap seal counteracts the closing of the motor vehicle door. As a result, there is a high pressure in the opening direction of the tailgate due to the compressed from the tailgate seal. When the pawl is disengaged from the catch, the pressure built up by the seal builds up rapidly in the form of a so-called unloading stroke and the tailgate moves abruptly and jerkily in the direction of the opening direction, which is negatively noticeable in an acoustically audible opening noise and leads to losses in comfort.

The invention has for its object to provide a solution that provides a rear lock or a motor vehicle door lock in a structurally simple manner and cost, in which the opening noise is reduced to a minimum, or at least in which the opening process no clearly audible and the comfort negatively impairing Noise generated.

In a rear lock of the type described above and also generally in a motor vehicle door lock, the object is achieved in that delay means are provided which are coupled to the rotary latch to delay a speed of movement of the rotary latch to release the closing element. In this case, the movement of the rotary latch in the rear lock according to the invention can be a rotation or rotational movement. It may also be several delay means or even a single delay means. In the further course of the description, therefore, the input and the plurality of delay means are simultaneously addressed.

Advantageous and expedient refinements and developments of the invention will become apparent from the dependent claims.

By the invention, a rear lock, but also quite generally a motor vehicle door lock, available which enhances the comfort and quality of the closure and its operation. The motor vehicle door lock according to the invention, in particular the rear lock, is characterized by a functional design and has a simple and inexpensive construction. Due to the delayed movement of the rotary latch and the trigger mechanism of the motor vehicle door lock and the rear lock according to the present invention, the pawl and the rotary latch during a movement operation of the pawl in the direction of the release position are still in engagement. Although this movement does not allow the opening of the tailgate. However, by this (initial or initial) movement during the opening process, the bias of the tailgate degrades because the defined and delayed movement of the pawl causes a relative movement between the motor vehicle door lock and the closing element and thus relieving the tailgate, wherein the rotary latch to a predetermined rotational movement is turned in the open position. This ultimately allows the tailgate to move a defined stroke relative to the closure member, thereby relieving the preload and pressure previously responsible for the acoustically perceptible and disturbing opening noise in prior art automotive door closures known in the art. Accordingly, the invention provides that the bias between the tailgate or motor vehicle door lock and closing element is reduced before the pawl and the rotary latch are disengaged.

The invention also provides a motor vehicle door lock with a locking element in the closed position and in the direction of an open position releasing the open position biased latch, a pawl which engages in an engaged position with the rotary latch in such a manner that the rotary latch on a movement in the direction of the open position is prevented, and a drive element, with which a coupling portion of the pawl is coupled for movement and which the pawl between the engaged position and a Release position moves, in which the pawl with the catch is disengaged, so that the catch can move in the direction of the open position, the task here is inventively achieved in that the drive element, the pawl during movement from the engaged position in the direction of the release position moved so that during this movement with the pawl still engaged rotary catch moves in the direction of the open position.

Likewise, the invention provides a method for opening a motor vehicle door lock (in particular a rear lock), wherein the motor vehicle door lock in the closed position a closing element encompassing and in the direction of the closure member releasing open position biased rotary latch, a pawl in a latching position with the catch in such a manner is that the catch is prevented from moving in the direction of the open position, and a drive element to which a coupling portion of the pawl is coupled and which moves the pawl between the engaged position and a release position in which the pawl is disengaged from the catch, so that the catch can move in the direction of the open position, wherein the pawl and the catch are disengaged for opening by the pawl is at least partially pivoted away from the rotary latch, wherein the pawl is moved by the drive element during movement from the engagement position in the direction of the release position such that during this movement with the pawl still engaged rotary catch is moved in the direction of the open position.

In an embodiment of the rear lock according to the invention, it is then of particular advantage that the rotary latch is coupled via the pawl with the delay means such that the speed of movement of the rotary latch for releasing the rotary latch is controlled. It is thus well noted a controlled movement of the catch, which is caused by the coupling with the pawl.

The controlled movement of the pawl can be realized in an embodiment of the rear lock according to the invention and also a general motor vehicle door closure that a pivotable about a pivot rotary joint is provided, which is rotatable about a rotation axis pawl mounted on the pivot radially offset from the pivot point. In this way, it is possible that the axis of rotation of the pawl, for example, is moved along a circular-segment-shaped trajectory, without the pawl thereby disengaged from the rotary latch.

A particularly powerful and at the same time efficient way of coupling the pawl can be achieved by a kind of double toggle lever. To this end, the invention provides in an embodiment of a push rod, of which a first end is pivotally and radially offset from a rotational axis of a rotary lever or radial approach is coupled thereto and coupled by a second end to the rotary joint in the region of the axis of rotation of the pawl such is that moves the axis of rotation of the pawl along a circular segment-shaped trajectory about the pivot point of the pivot joint during movement of the push rod. Thus, a first toggle lever is defined by the second end of the push rod and the fixedly mounted pivot, wherein the pawl is coupled via the rotation axis with the pivot and with the push rod. A second toggle lever is defined by the first end of the push rod and its eccentric or radially offset with respect to the axis of rotation coupling with the rotary lever, so that a total of a double toggle is present.

In a further embodiment of the rear lock and in general of the motor vehicle door lock, the invention provides that the rotary joint is coupled with a variable-length lever, which is designed to brake the movement of the pawl from the engaged position to an intermediate position and braking from the intermediate position into the release position. This configuration causes the movement of the pawl from the engaged position to the release position and back to the engaged position by a motor-driven Drive element is controlled guided. The drive element is used in a first movement section from the engaged position to an intermediate position as a drive for the pawl, whereas the drive element acts as a brake during the movement of the pawl from the intermediate position to the release position. The change in the operation of the drive element results from the fact that the intermediate position defines a load change for the drive element.

In an embodiment of the rear lock and generally the motor vehicle door lock, the invention provides that the intermediate position is a dead center of the pawl, in which at least the force acting on the pawl force of the catch and the axis of rotation of the pawl are arranged lying in a line. In this case, the dead center position or intermediate position describes a position of the pawl, which can only be changed by a force transverse to the line, which is formed by the axis of rotation and the force acting on the pawl force of the rotary latch.

The above-mentioned in some embodiments of the invention as a possible complementary feature drive element can now according to the invention now quite concretely effect in a movement of the pawl from the engaged position to the release position, the movement of the rotary joint around the axis of rotation.

It is of particular advantage, in particular, if the delay means simultaneously effect an actuation of the pawl. Thus, the delay means serve not only the delay of the movement of the rotary latch, but also an actuation and possibly movement of the pawl.

In the rear lock according to the invention and also in the general motor vehicle door lock according to the invention, the rotary joint and / or the push rod and / or the drive element may be the delay means, which allows a simple and inexpensive construction of the rear lock and the motor vehicle door lock.

As an alternative to the above-mentioned embodiment of the retarder, the invention provides a damping element, in particular a mechanical, hydraulic or pneumatic damping element, serves as a retarding means. In particular, the damping element may be a linear damping element, wherein the damping element does not serve as an end stop for cushioning the end movement of the rotary latch, but rather dampens, brakes and thereby delays the initial movement of the rotary latch.

In general, the invention for the motor vehicle door lock described above and for the method that the movement of the drive member is a rotational movement, during the movement of the pawl from the engaged position in the direction of the release position with respect to the rotary latch substantially tangential movement of the pawl and then, to disengage the pawl and the catch, causing a movement of the pawl that points substantially radially away from the catch. This movement refers to a latching portion of the pawl, which engages in the engaged position with the rotary latch. In other words, the drive element for opening the motor vehicle door lock is rotated such that the pawl or at least a portion of the pawl, ie the latching portion, initially during movement from the engaged position in the direction of the release position is moved substantially tangentially with respect to the rotary latch and then to disengage the pawl and the catch, is moved substantially radially away from the catch. The movement of the pawl executed during the opening process of the motor vehicle door lock is thus divided into two or consists of a sequence of movements in which the pawl is moved in at least two different spatial directions. To initially take the pressure from the tailgate in the closed position or to relieve the preloaded tailgate, there is a substantially tangential movement of the pawl with respect to the rotary latch. In this movement, the pawl is still engaged with the catch, but depending on the tangential distance to which the Pawl is moved, the rotary latch allows a rotation in the open position, whereby the pressure of the tailgate degrades. Only after the pressure reduction or the reduction of the bias is then carried out with the help of the radial sideways movement of the pawl disengage the catch, which then releases the closing element for opening the tailgate. The resulting from at least two movements in different directions in space opening movement of the pawl thus allows the degradation of acting on the tailgate in the closed position bias by the pawl causes a controlled movement of the tailgate in the opening direction for a certain stroke.

To reduce the opening noise by reducing the bias between the tailgate or vehicle door lock and closing element, before the pawl and the rotatably mounted about an axis of rotation rotary latch disengaged, the invention also provides that the axis of rotation of the pawl during the movement of the pawl in Direction of the release position relative to the axis of rotation of the rotary latch, preferably translationally moves. During the movement of the axis of rotation in the direction of the axis of rotation, the pawl is indeed still engaged with the rotary latch, however, can rotate due to the translational and tangential to the rotary latch movement of the pawl, the rotary latch in the direction of its open position.

Thus, the bias voltage with which the tailgate is biased in the closed position, is degraded gradually and not abruptly, it is in the rear lock and motor vehicle door lock further advantageous if the movement from the engaged position in the direction of the release position of the pivot on the pivot or rotatable attached axis of rotation of the pawl is a circular section-shaped movement. It is conceivable, for example, quarter-circle or semi-circular movements.

A structurally particularly simple way for defined guidance of the pawl in the release position continues to be that in the engaged position with the catch in engagement locking portion of the pawl is guided by means of a guide member and / or mounted on the pawl control pin movement. In this guided movement, the pawl is moved radially away from the rotary latch during the opening process, it being particularly advantageous if only the engaging with the catch portion of the pawl, ie the latching portion, and not the entire pawl moves away from the rotary latch becomes.

A particularly favorable transmission of the driving force of the drive element to the pawl is possible by a transmission lever which is in operative connection with the pawl. According to the invention, the advantages given by a lever in terms of power transmission are used here.

In a further embodiment according to the invention is then provided that the transmission lever is provided with a slot in which a movement-coupled with the pawl pin is guided. The mechanical coupling of pin and transmission lever is reminiscent of a kind of slotted guide, but in contrast, the transmission lever, depending on the position, which is caused by the rotational movement of the transmission lever rotating drive element, a forced movement of the pin in the slot. The leverage changes due to the pin slidably held in the slot, since in particular the lever length of the transmission lever varies depending on the position of the pin. In this way, the invention provides a kind of variable-length lever.

In order to enable a particularly efficient power transmission of the driving force provided by the drive element, the invention provides in an embodiment that the pivotally mounted about the pivot pivot lever forms an operative connection between the transmission lever and the pawl, wherein the pin and the coupling portion each offset radially to the pivot point the articulated lever is arranged on the toggle lever and are mounted so that a movement of the pin directly rotates the toggle lever and indirectly rotates the axis of rotation.

Finally, it is provided in an embodiment of the motor vehicle door lock according to the invention that the pawl is biased in the direction of the engagement position. In this way, the pawl is permanently urged in the direction of the engagement position, which can be achieved for example by means of at least one spring element, which may be formed as a tension or compression spring. It is sufficient if only the portion of the pawl is biased, which can be brought into engagement with the rotary latch or is in engagement with the rotary latch.

It is understood that the features mentioned above and those yet to be explained can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention. The scope of the invention is defined only by the claims.

• Figur 1 einen erfindungsgemäßen Kraftfahrzeugtürverschluss (Heckschloss) gemäß einer ersten Ausführungsform in perspektivischer Einzelteildarstellung,
• Figur 2 den Kraftfahrzeugtürverschluss aus Figur 1 im zusammengebauten Zustand in perspektivischer Ansicht,
• Figur 3 eine perspektivische Rückansicht des in Figur 2 dargestellten Kraftfahrzeugtürverschlusses,
• Figur 4 den Kraftfahrzeugtürverschluss gemäß der ersten Ausführungsform in einer geschlossenen Stellung,
• Figur 5 den Kraftfahrzeugtürverschluss gemäß der ersten Ausführungsform in einer Stellung zwischen der geschlossenen und einer geöffneten Stellung,
• Figur 6 den Kraftfahrzeugtürverschluss gemäß der ersten Ausführungsform in einer weiteren Stellung zwischen der geschlossenen und der geöffneten Stellung,
• Figur 7 den Kraftfahrzeugtürverschluss gemäß der ersten Ausführungsform in geöffneter Stellung,
• Figur 8 den Kraftfahrzeugtürverschluss gemäß der ersten Ausführungsform beim Schließvorgang in einer Stellung kurz vor dem Erreichen der geschlossenen Stellung,
• Figur 9 einen erfindungsgemäßen Kraftfahrzeugtürverschluss (Heckschloss) gemäß einer zweiten Ausführungsform in Vorderansicht,
• Figur 10 den Kraftfahrzeugtürverschluss gemäß der zweiten Ausführungsform in einer Rückansicht,
• Figur 11 den Kraftfahrzeugtürverschluss aus Figur 10 in einer Einzelteildarstellung,
• Figur 12 den Kraftfahrzeugtürverschluss aus Figur 10 in Eingriffsstellung bzw. geschlossener Stellung,
• Figur 13 den Kraftfahrzeugtürverschluss aus Figur 10 in Freigabestellung bzw. geöffneter Stellung,
• Figur 14 einen erfindungsgemäßen Kraftfahrzeugtürverschluss (Heckschloss) gemäß einer dritten Ausführungsform in Vorderansicht,
• Figur 15 eine Einzelteildarstellung von einer Sperrklinke, einem Drehgelenk, einem Antriebselement, einem Führungselement und einer Drehfalle des Heckschlosses aus Figur 14,
• Figur 16 das in Figur 15 gezeigte Antriebselement in einer Schnittansicht,
• Figur 17 den Kraftfahrzeugtürverschluss bzw. das Heckschloss aus Figur 14 in Schließposition in einer schematischen Darstellung,
• Figur 18 den Kraftfahrzeugtürverschluss aus Figur 14 in einem ersten Schritt einer Öffnungsbewegung in schematischer Darstellung,
• Figur 19 den Kraftfahrzeugtürverschluss aus Figur 14 in einem zweiten Schritt einer Öffnungsbewegung bzw. in einer Zwischenstellung in schematischer Darstellung,
• Figur 20 den Kraftfahrzeugtürverschluss aus Figur 14 in einem dritten Schritt einer Öffnungsbewegung in schematischer Darstellung,
• Figur 21 den Kraftfahrzeugtürverschluss aus Figur 14 in einem vierten Schritt einer Öffnungsbewegung in schematischer Darstellung und
• Figur 22 den Kraftfahrzeugtürverschluss aus Figur 14 in einer geöffneten Stellung in schematischer Darstellung.

Further details, features and advantages of the subject matter of the invention will become apparent from the following description taken in conjunction with the drawings in which exemplary preferred embodiments of the invention are shown. In the drawing shows:

• FIG. 1 a motor vehicle door lock (rear lock) according to the invention according to a first embodiment in perspective Einzelteildarstellung,
• FIG. 2 the motor vehicle door lock FIG. 1 in assembled condition in perspective view,
• FIG. 3 a perspective rear view of the in FIG. 2 shown motor vehicle door lock,
• FIG. 4 the vehicle door latch according to the first embodiment in a closed position,
• FIG. 5 the motor vehicle door lock according to the first embodiment in a position between the closed and an open position,
• FIG. 6 the motor vehicle door lock according to the first embodiment in a further position between the closed and the open position,
• FIG. 7 the motor vehicle door lock according to the first embodiment in the open position,
• FIG. 8 the motor vehicle door lock according to the first embodiment when closing in a position shortly before reaching the closed position,
• FIG. 9 a motor vehicle door lock (rear lock) according to the invention according to a second embodiment in front view,
• FIG. 10 the motor vehicle door lock according to the second embodiment in a rear view,
• FIG. 11 the motor vehicle door lock FIG. 10 in a single part presentation,
• FIG. 12 the motor vehicle door lock FIG. 10 in the engaged position or closed position,
• FIG. 13 the motor vehicle door lock FIG. 10 in release position or open position,
• FIG. 14 a motor vehicle door lock (rear lock) according to the invention according to a third embodiment in front view,
• FIG. 15 an itemized view of a pawl, a hinge, a drive element, a guide element and a catch of the rear lock FIG. 14 .
• FIG. 16 this in FIG. 15 shown drive element in a sectional view,
• FIG. 17 the motor vehicle door lock or the rear lock FIG. 14 in closed position in a schematic representation,
• FIG. 18 the motor vehicle door lock FIG. 14 in a first step of an opening movement in a schematic representation,
• FIG. 19 the motor vehicle door lock FIG. 14 in a second step of an opening movement or in an intermediate position in a schematic representation,
• FIG. 20 the motor vehicle door lock FIG. 14 in a third step of an opening movement in a schematic representation,
• FIG. 21 the motor vehicle door lock FIG. 14 in a fourth step of an opening movement in a schematic representation and
• FIG. 22 the motor vehicle door lock FIG. 14 in an open position in a schematic representation.

The FIGS. 1 to 22 show schematically in different views only the essential elements of the invention of a motor vehicle door lock 1, in particular a tailgate lock assembly or a rear lock, wherein the FIGS. 1 to 8 a first embodiment, the FIGS. 9 to 13 a second embodiment and the FIGS. 14 to 22 represent a third embodiment of the motor vehicle door closure or rear lock 1 according to the invention.

While the vehicle door latch 1 according to the first embodiment in FIG FIG. 1 is shown in a single part illustration, show the FIGS. 2 to 8 the assembled motor vehicle door lock 1. The FIGS. 4 to 7 show different positions of the components of the motor vehicle door lock 1 during the opening process, whereas FIG. 8 shows a position during the closing process.

The motor vehicle door lock 1 mounted on a tailgate of a motor vehicle, which can also be referred to as a rear lock 1, engages in a schematic manner for the purpose of closing and only in FIG FIG. 4 dashed shown closing element 2 a. The closing element 2 may be formed, for example, as a locking pin or striker and is attached to a vehicle frame. The in FIG. 1 shown in an exploded view of the motor vehicle door closure 1 according to the first embodiment comprises interconnectable housing elements 3 and 4, a rotary latch 5 which is rotatably mounted about an axis of rotation 6 on the housing element 2 and a rotary latch jaw 7, in which the closing element 2 engages. The rotary latch 5 is characterized by a in FIG. 3 only schematically indicated Spring element 8 biased such that it strives to be in the in the FIGS. 4 to 7 shown counterclockwise (arrow A) to rotate, so that the closing element 2 (in the FIGS. 4 to 7 downwards) is released. To share in the FIG. 4 shown locked state, the catch 5 is held by a pawl 9 by a locking portion 10 of the pawl 9 is in engagement with a latching arm 11 on the rotary latch jaw 7. In the FIG. 4 shown position is the so-called locking position, in which the catch 5 are in a closed position and the pawl 9 in an engaged position. With the help of the rotary latch 5 biasing spring force, the rotary latch 5 presses with its locking arm 11 in the locking position on the locking portion 10 of the pawl 9, whereby the closing element 2 is fixed in the rotary latch jaw 7, as from FIG. 4 is apparent. In other words, the rotary latch 5 is biased in the direction of the closing element 2 releasing open position. In the engaged position thus the pawl 9 is engaged with the rotary latch 5 in such a way that the rotary latch 5 is prevented from moving in the direction of the open position.

The pawl 9 is connected via a rotary joint 12 with a motion element not shown in detail for the first embodiment drive element. The rotary joint 12 is rotatably mounted on the housing element 4 about a rotation axis (pivot point 13). At the pivot 12, which is partially disc-shaped, a bolt-shaped connecting element is mounted as a rotation axis 14 for the pawl 9, which is arranged radially offset from the pivot point 13 on the pivot joint 12 and attached thereto. The connecting element in the form of the axis of rotation 14 connects the coupled to the drive element pivot 12 with a arranged in the region of the rotation axis 14 coupling portion 15 of the pawl 9, so that the pivot joint 12, the pawl 8 between the engaged position and a release position in which the pawl 9 with the catch 5 is disengaged moves. The pawl 9 is thus pivotally connected by means of the connecting element or the axis of rotation 14 the rotary joint 12 radially offset from the pivot point 13 stored. As soon as the pawl 9 is in the release position, the rotary latch 5 can move or rotate in the direction of the open position. Preferably, the pawl 9 is biased in the direction of the engagement position, which, for example, by means of an example only in FIG FIG. 3 It is sufficient if the area of the latching portion 10 of the pawl 9 is urged by the spring force in the engaged position and thus in the direction of the rotary latch 5 and the latching arm 11 of the rotary latch 5.

In order to prevent an acoustically audible and disturbing opening noise of the tailgate under tension and thus the motor vehicle door lock or rear lock 1, the invention provides that the coupled to the drive element pivot 12 moves the pawl 9 during movement from the engaged position in the direction of the release position in that the rotary catch 5, which is still in engagement with the pawl 9 during this movement, moves in the direction of the open position. The coupled with the catch 5 pawl 9 acts here as a delay means to delay the speed of opening the movement, in particular the rotational movement of the catch 5 to release the closing element 2 and simultaneously avoiding the opening noise and slow down. By this (delayed) movement, the bias of the tailgate is reduced or reduced, since the tailgate can move due to the described movement coupling by a defined stroke from the locked position. This process is in the FIGS. 4 to 7 shown, where FIG. 4 the locking position, FIG. 7 the release position of the pawl 9 and FIGS. 5 and 6 Positions of the catch 5 and the pawl 9 show that lie between the locking position and the release position.

Hereinafter, the operations when opening the vehicle door lock and the rear lock 1 of the first embodiment will be explained.

In the FIGS. 4 to 7 is a movement curve 17 of the rotation axis 14 and the coupling portion 15 which is connected via the rotation axis 14 and the rotary joint 12 with the drive element, shown in dashed lines. The movement curve 17 essentially corresponds to the control recesses 18 and 19, which are formed in the housing elements 3 and 4. From the movement curve 17, it can be seen that the movement of the coupling portion 15 of the pawl 9, which is pivotally mounted on the rotation axis 14, from the position of engagement in the direction of the release position is a circular-segment-shaped movement, which is shown in FIGS FIGS. 4 to 7 counterclockwise in the direction of arrow A. Accordingly, a rotational movement or rotational movement of the rotary joint 12 about the pivot point 13 causes the coupling section 15 or the rotational axis 14 of the pawl 8 to be moved along a circular section. The control recesses 18 and 19 formed in the housing elements 3 and 4 can additionally guide the movement of the axis of rotation 14. However, the control recesses 18 and 19 are dispensable, so that they can be omitted in the motor vehicle door lock or rear lock 1 according to the invention.

Upon closer inspection of the FIGS. 4 to 7 can be seen that the rotational movement or rotational movement of the rotary joint 12 counterclockwise initially causes a substantially tangential with respect to the rotary latch 5 movement of the latching portion 10 of the pawl 9. Although the coupling portion 15 of the pawl 9 moves along the circular segment-shaped movement curve 17, however, the latching portion 10 of the pawl 9 is initially moved substantially tangentially to the rotary latch 5. In other words, the pawl 9 in a first step relative to the rotary latch 5 of FIG. 4 to FIG. 5 moved down, thereby allowing the rotary latch 5 can rotate in the direction of arrow A, whereby the overall acting on the tailgate bias is reduced. During the movement of the pawl 9 from the in FIG. 5 shown position in the in FIG. 6 position shown then takes place both a tangential Movement of the locking portion 10 of the pawl 9 with respect to the rotary latch 5 and a radial movement of the locking portion 10 of the pawl 9 away from the rotary latch 5, which can be seen from the fact that the latching portion 10 to a certain extent by the latching arm 11 of the rotary latch 5 is disengaged. In a final step of the movement of the pawl 9 in the direction of the release position, ie from the position in FIG. 6 to the position in FIG. 7 , Then causes the rotational movement of the pivot joint 12 a substantially radially away from the catch 5 movement of the latching portion 10 of the pawl 9 to disengage the pawl 9 and the catch 5, as it finally in FIG. 7 is shown. In this position, in which the rotary latch 5 in the open position and the pawl 9 are in the release position, the latching arm 11 and the latching portion 10 are disengaged and can move past each other, the rotary latch 5 continue to rotate in the direction of arrow A. is, so that the closing element 2 can move out of the rotary latch jaw 7 out. In this way, the pawl 9 and the catch 5 are brought to open a tailgate disengaged by the pawl 9 is at least partially pivoted away from the rotary latch 8. In this case, as mentioned above, the pawl 8 is moved by the rotary joint 12 during movement from the engaged position in the direction of the release position such that in this movement with the pawl 9 still engaged rotary latch 5 is moved in the direction of the open position , The rotary joint 12, which is coupled to the drive element, is rotated to open the motor vehicle door lock or the rear lock 1 such that the pawl 9 or at least a portion of the pawl 9 (ie the latching portion 10) initially during movement from the engaged position in the direction the release position is moved substantially tangentially with respect to the rotary latch 5 and then, in order to disengage the pawl 9 and the catch 5, is moved substantially radially away from the rotary latch 5.

In the overall movement of the pawl 9, as described above, the movement of the coupling portion 15, which follows due to the movement coupling with the rotary joint 12 of the circular segment-shaped or circular section-shaped movement curve 17, deviates from the movement of the latching portion 10 of the pawl 9. The latching portion 10, which is in the engaged position of the pawl 9 with the rotary latch 5 is engaged, is guided by means of a guide member 20 movement. The guide member 20 is on the housing member 3 of the motor vehicle door lock or rear lock langordnet and pivotally mounted about an axis 21 thereto. Furthermore, the guide element 20 has a guide recess 22 with two opposing abutment surfaces, which leads or controls a movement of the engageable with the catch 5 locking portion 10 of the pawl 9 toward the rotary latch 5 or away from the rotary latch. In particular, in the guide recess 22, the movement of a control pin 23 can be performed, which is formed in the region of the latching portion 10 of the pawl 9 (see FIGS. 4 and 8 ). The movement of the guide element 20 itself can be achieved by a movement limiting recess 24 formed in the housing element 3 (see FIG FIG. 1 ) be limited. The latching portion 10 of the pawl 9 may, as mentioned above, be biased in the direction of the engagement position by means of the spring element 16, so that the formed in the region of the locking portion 10 control pin 23 during the in the FIGS. 4 to 7 shown movement is urged radially in the direction of the rotary latch 5 at the extreme end of the formed in the guide member 20 guide recess 22.

As an alternative to the guide element 20, a radial movement away from the rotary latch 5 could be effected by itself. For this purpose, an outer portion of the rotary latch 5 could have a radial projection 25, as in FIG FIG. 4 indicated by dashed lines or shown. Upon rotation of the rotary latch 5 then the radial projection 25 would arrive at sufficient rotation in abutment with the pawl 9 and the Pawl 9 push away or deflect such that the locking portion 10 and the locking arm 11 are disengaged.

In FIG. 8 a position of the rear lock or the motor vehicle door lock 1 is shown during the closing operation, in which the coupling portion 15 of the pawl 9 is again in the engaged position, whereas the locking portion 10 of the pawl 9 is disposed radially away from the rotary latch 5, wherein the control pin 23rd a central position in the guide recess 22 of the guide member 20 occupies. Due to the fact that the control pin 23 of the locking portion 10 can be urged radially against the force of the spring element 16 in the guide recess 22 of the guide member 20 away from the rotary latch 5, it is possible that the rotary latch 5 rotates in the direction of arrow B during the closing operation and in this movement, the latching arm 11 slides past the latching section 10. In this case, the bias of the pawl 9 ensures that when the latching arm 11 has passed the latching portion 10, both interlock or that the latching portion 10 then pushes over the latching arm 11 and ensures engagement of pawl 9 and 5 catch, so that in FIG. 4 shown closed position is taken again. The process of closing but should not be considered here in detail, because the invention is primarily directed to the processes when opening the motor vehicle door lock or the rear lock. 1

In the FIGS. 9 to 13 the motor vehicle door lock or the rear lock 1 according to the second embodiment is shown. With reference to the FIGS. 9 to 13 It can be seen that the motor vehicle door lock or the rear lock 1 according to the second embodiment - as well as the first embodiment - the housing element 3, which for reasons of clarity, only in FIG. 9 is shown, around and on the axis of rotation 6 rotatably mounted rotary latch 5 with the rotary latch jaw 7, in which the closing element 2 is arranged in the engaged position, and with the locking arm 11, which with the locking portion 10 of the pawl 9 in the engaged position is engaged, and with a drive element 26 (see, eg FIG. 10 or 11 ) coupled rotary joint 12, which is rotatable about a pivot point 13 (rotation axis) comprises. In a representation of the spring elements 8, 16 was in the FIGS. 9 to 13 omitted, wherein the second embodiment may also have corresponding spring elements, so that the rotary latch 5 in the direction of arrow A ( FIGS. 12 and 13 ), ie in the direction of its open position, spring-loaded or biased. In addition, the pawl 9 may be biased by means of such a spring element in the direction of the engagement position or spring preloaded. This structure and the interaction of pawl 9 and rotary latch 5 is substantially identical to the operation of these components in the first embodiment, so that dispenses with a repetition of the description and reference is made to the corresponding statements to the first embodiment.

Also, in the second embodiment, the pawl 9 is connected to the rotary joint 13 coupled for movement. However, there are differences in this coupling between the first and second embodiments, which will be discussed later in the description of the second embodiment.

While the rotary latch 5 is rotatably supported on the housing element 3 with the aid of the stationary axis of rotation 6, the coupling section 15 of the pawl 9 is mounted or mounted pivotably on the rotary joint 12 via the axis of rotation 14. The rotation axis 14 is not stationary in contrast to the rotation axis 6, but moves during the movement of the pawl 9 in the direction of the release position relative to the axis of rotation 6 of the rotary latch 5 translationally along in the FIGS. 12 and 13 As a result of this movement curve 17, the coupling section 15 of the pawl 9 undergoes a circular segment-shaped movement which is not a rotational movement but a substantially translational movement with respect to the rotary latch 5. Thus takes place for the rotation axis 14 and the coupling portion 15 is a circular-segment-shaped movement when the pawl 9 from the open position ( FIG. 12 ) into the release position ( FIG. 13 ) emotional. The position of the axis of rotation 14 with respect to the fixed axis of rotation 6 of the rotary latch 5 is therefore not constant, but changes during the movement of the pawl 9 from the open position to the release position. This change in the position of the rotation axis 14 and the coupling portion 15 is in turn caused by the coupled to the drive member 26 pivot 12, but in the second embodiment, a push rod 28 between the drive member 26 and rotation axis 14 or coupling portion 15 is interposed, which controls the driving force of Drive element 26 first transmits to the push rod 26, then to the pivot 12 and only then to the rotation axis 14 and the coupling portion 15 of the pawl 9. Like, for example FIG. 11 it can be seen, a first end 29 of the push rod 28 is coupled to the drive element 26. In this case, the first end 29 of the push rod 28 is mounted radially offset from a rotational axis 30 of the drive element 26 on a radial shoulder 31 of the drive element 26 on this rotatable or pivotable. The push rod 28 is slightly bent, wherein a second end 32 of the push rod 28 receives the movement coupled to the coupling portion 15 of the pawl 9 pivot 12 and the rotational axis 14 of the pawl 9. To guide the movement of the second end 32 of the push rod 28 and the coupling portion 15 of the pawl 9, the rotary joint 12 is rotatably mounted on the attached to the housing element 3 pivot point 13. Radially offset from the pivot point 13 of the rotary joint 12, the push rod 28 and the rotation axis 14 of the pawl 9 is connected to the rotary joint 12, so that the rotation axis 14 are rotatable and pivotable with a corresponding movement of the push rod 28.

In FIG. 12 the motor vehicle door lock or the rear lock 1 according to the second embodiment is shown in the locking or engagement position, whereas in FIG. 13 the open position of the motor vehicle door lock or rear lock 1 is shown. The movement of the locking portion 10 of the pawl 9 from its in FIG. 12 shown engaged position in the in FIG. 13 illustrated open position takes place along the movement path 33, which is shown schematically in the respective box on the side of the motor vehicle door lock (rear lock) 1, wherein the point 34 marks the current position (engagement position) of the latching section 10 on the movement path 33. By the rotational movement of the drive element 26 (indicated by the arrow C in FIG FIG. 12 ), the push rod 28 from the in FIG. 12 position shown in the position of FIG. 13 pivoted. In this case, the movement of the second end 32 of the push rod 28 is guided by the rotary joint 12 along the movement curve 17, so that thereby also the rotation axis 14 and the coupling portion 15 of the pawl 9, which are coupled to the second end 32 of the push rod 28, along move the movement curve 17. Through this coupling, the coupling portion 15 of the pawl 9 undergoes a substantially circular segment-shaped movement. In contrast, the movement of the latching section 10 out of the engagement position in the direction of the release position is in a first movement section a movement of the latching section 10 substantially tangential with respect to the rotary latch 5, which is characterized by the vertical course of the movement path 33. As a result, the pawl 9 is still engaged with the rotary latch 5 in engagement. However, the tangential movement of the locking portion 10 allows a rotational movement of the rotary latch 5 in the direction of the open position, so that the bias of the tailgate, which prevails when the shutter is closed, is reduced without the shutter is open. This movement corresponds to that in the FIGS. 4 and 5 In a second movement section of the latching section 10, this is then moved radially away from the rotary latch 5, which is characterized by the substantially vertical course of the movement path 33 to the pawl 9 and the rotary latch fifth to disengage. This procedure corresponds to that in the FIGS. 5 and 6 shown movement sequence of the first embodiment of the motor vehicle door closure. 1

The power transmission of the drive element 26 via the radial projection 31, which corresponds to a transmission lever and the force is transmitted to the push rod 28, from which the force is then transmitted to the rotation axis 14 and the coupling portion 15 of the pawl 9. The push rod 28 is rotatably mounted on a pivot point 36 arranged at the free end of the radial shoulder 31. In this case, the transmitted force is converted by the rotary joint 12 in a defined movement of the coupling portion 15, as described above. With regard to the power transmission, the rotary joint 12 defines a first toggle lever and the radial extension 31 a second toggle lever, whereby a particularly powerful movement coupling is effected. The second toggle secures the first toggle, especially since the moments on the second toggle are very small, so it can be well secured by low forces. For reasons of safety, it is further desirable that the motor vehicle door lock or the rear lock 1 remain in the closed position even in the event of a vehicle accident. Therefore, the vehicle door latch 1 must withstand the acceleration forces prevailing in a vehicle accident, so that the pawl 9 and the rotary latch 5 are not disengaged. For this purpose, the pawl 9 a bend 35 (see Figures 10 and 13 ) in the engaged position ( Figures 10 and 12 ) on which acting as an end stop and the movement of the pawl 9 beyond the engagement position addition fulcrum 13 of the rotary joint 12 is applied. In this position, in which the bend 35 of the pawl 9 rests against the pivot point 13, ie in the engaged position, the push rod 28 assumes a position in which it has exceeded a dead center and thereby locked in the engaged position self-locking. The pivot point acting as a guide axis 13 serves as a mechanical stop which limits the movement of the pawl 9 from the open position into the engaged position.

The motor vehicle door lock or the rear lock 1 of the first and second embodiment is characterized in that that the noise during opening is kept to a minimum and in particular the noise during the discharge stroke is minimized. This is achieved in that the pawl 9 and the catch 5 are moved to each other during the opening process such that the tailgate and thus the motor vehicle door latch 1 can remove relative to the closing element 2, whereby the load on the tailgate pressure or the bias of the tailgate is first reduced, before the pawl 9 and the rotary latch 5 finally disengaged to release the closing element 2. In particular, this is achieved by the pivot joint 12, which defines a pivot axis 27 for the pawl 9, relative to the axis of rotation 6 of the rotary latch 5 is moved during the opening process, whereby the first tangential movement to the rotary latch 5 and then pointing away radially from the rotary latch 5 Movement of the locking portion 9 of the pawl 9 is implemented. In the opening operation of the second embodiment, the rotary joint 12, the drive member 26 and the rotary joint 12 with the drive member 26 bewegungskoplopende push rod 28 constitute the delay means to delay the speed of rotation of the rotary latch 5 to release the closing element 2.

In the FIGS. 14 to 22 is a motor vehicle door lock or a rear lock 1 shown according to a third embodiment. Also, the rear lock 1 according to the third embodiment includes only in the FIGS. 14 to 22 schematically illustrated closing element 2, which may be attached to a vehicle frame, when the rear lock 1 is attached to the tailgate. It is also conceivable, of course, that the closing element 2 can be attached to the tailgate and the rear lock 1 to the vehicle frame. The motor vehicle door lock 1 further comprises the only in FIG. 14 shown housing element 3, in which further components of the motor vehicle door lock 1 added, under and are attached. For clarity, the housing element 3 in the FIGS. 15 to 22 not shown further. The motor vehicle door lock 1 additionally comprises the rotary latch 5, which is rotatably mounted about the axis of rotation 6 on the housing element 3 and which has the rotary latch jaw 7, in which the closing element 2 engages in the closed position. The catch 5 is biased by a spring element not shown in more detail or spring (force) acted upon or spring preloaded that it strives to, for example, in FIG. 17 shown closed position or closed position to rotate clockwise about the axis of rotation 6, so that the rotary latch 5 in the open position, the closing element 2 with respect to FIG. 22 releases downwards. Thus, the rotary latch 5 engages in the closed position, the closing element 2, wherein it is biased in the direction of the closing element 2 releasing open position.

To the motor vehicle door lock 1 in the in FIG. 14 or FIG. 17 shown closed position, the rotary latch 5 is held by the pawl 9 by the locking portion 10 of the pawl 9 is engaged with the latching arm 11 on the rotary latch jaw 7. In this case, in addition to the catch 5 in addition, the pawl 9 may be biased or spring preloaded at least in its engaged position by means of a spring element to hold the engagement position with the catch 5 due to the acting spring force. The spring force causes a rotational force in the clockwise direction about the rotation axis 14, around which the pawl 9 is rotatably mounted on the housing element 3. The example in the Figures 14 and 17 shown position is the locking position of the motor vehicle door latch 1, in which the catch 5 in the closed position and the pawl 9 are in the engaged position. In the locking position, the prestressed rotary latch 5 presses with its latching arm 11 on the latching section 10 of the pawl 9, whereby the closing element 2 is fixed in the rotary latch jaw 7. In the engaged position, the pawl 9 is engaged with the rotary latch 5 in such a way that the rotary latch 5 is prevented from moving in the direction of the open position.

The pawl 9, which is at least pivoted to open the rear lock (motor vehicle door lock) 1 and is brought out of engagement with the rotary latch 5, with the interposition of the rotary joint (articulated lever) 12 is connected to the drive member 26 and coupled for movement, wherein the drive member 26 can be driven by a motor, not shown, for example with worm gear with helical teeth. It should be noted that in the FIGS. 14 to 22 shown drive member 26 is shown partially cut to also represent components that are located lying behind the drive element 26. The rotary joint or the articulated lever 12 is plate-shaped or disc-shaped and rotatably mounted on the housing element 3 about the pivot point 13. On the rotatably mounted rotary joint (articulated lever) 12, the axis of rotation 14 of the pawl 9 is mounted, which in turn rests rotatably on the disc-shaped rotary joint (articulated lever) 12. In this case, the rotational axis 14 of the pawl 9 is synonymous with the coupling portion 15 which is movable by the drive member 26 and the pawl 9 moves between the engaged position and the release position. Characterized in that the rotational axis 14 is arranged laterally offset from the pivot point 13, a rotation of the pivot joint (articulated lever) 12 causes the axis of rotation 14 of the pawl 9 relative to the axis of rotation 6 of the rotary latch in a movement between the engaged position and the release position 5 moves and moves. The described movement of the axis of rotation 14 of the pawl 9 is the for FIGS. 12 and 13 already described circular-segment-shaped movement along the movement curve 17, because the rotation axis 14 is not attached to the housing element 3, but on the rotatable hinge (articulated lever) 12. Through this coupling, it is possible that the pawl 9 is moved during movement from the engaged position in the direction of the release position such that in this movement with the pawl 9 still engaged or located rotary latch 5 in the direction of the open position moves or rotates. By this movement, an existing bias of the tailgate can be reduced, since the tailgate due to the described motion coupling to a defined stroke of the Locking position can move, so that a disturbing opening noise is significantly reduced.

The movement of the locking portion 10 of the pawl 9 from its in the Figures 14 and 17 shown locking or engagement position in the open position of the motor vehicle door lock or rear lock 1, in which the pawl 9 and the catch 5 are disengaged, carried by the rotational movement of the swivel joint (articulated lever) 12, whereby at the pivot (articulated lever) 12th Radially offset from the pivot point 13 mounted rotational axis 14 of the pawl 9 is moved in a circular section. By contrast, in the first movement section from the engagement position in the direction of the release position, the latching section 10 carries out the essentially tangential movement relative to the rotary latch 5 or at least one section (for example the latching section 10) is moved tangentially with respect to the rotary latch 5. As a result, the pawl 9 is still engaged with the rotary latch 5 in engagement. However, the tangential movement (downward movement with respect to FIG. 20 ) of the locking portion 10, a rotational movement of the rotary latch 5 in the direction of the open position, so that the bias prevailing when the shutter is closed, is degraded without the shutter is open. In the second movement portion of the pawl 9 and the latching portion 10, the latching portion 10 is then radially from the rotary latch 5 (to the right outside with respect to FIG. 21 ) to move the pawl 9 and the catch 5 out of engagement.

The drive member 26 is rotationally coupled via the pivot (the lever arm) 12 with the coupling portion 15 of the pawl 9, so that the drive member 26 moves the pawl 9. Here, in this case, the rotary joint 12 is coupled to the rotary latch 5 delay means to delay the speed of rotation of the rotary latch 5 to release the closing element 2. The coupling portion 15 corresponds in the illustrated third embodiment, the rotation axis 14 of the pawl 9. He can but in an alternative embodiment, on another portion of the Pawl 9 may be provided. In the release position, the rotary latch 5 can move in the direction of the open position to release the closing element 2. During the movement from the engagement position in the direction of the release position, the drive element 26 moves the pawl 9 such that during this movement with the pawl 9 still engaged rotary latch 5 is moved or moved in the direction of the open position. In particular, the movement of the drive member 26 is a rotational movement, during the movement of the pawl 9 from the engaged position in the direction of the release position with respect to the rotary latch 5 substantially tangential movement of the pawl 9 and then to the pawl 9 and the catch 5 except To bring about a substantially radially away from the rotary latch 5 pioneering movement of the pawl 9 causes.

That in the FIGS. 15 and 16 Drive element 26 shown in detail has a base body 37, which has a cylindrical shape and is rotatably mounted about the rotation axis (pivot point) 30 on a housing component of the motor vehicle door lock or rear lock 1. The outer periphery of the main body 37 is provided with a toothing, which may be in engagement with a helical toothing of a worm gear of a motor. On the base body 37, a transmission lever 38 is formed, which is arranged offset to the rotational axis (pivot point) 30 of the drive element 26 and which extends relative to the rotational axis (pivot point) 30 tangentially. The transmission lever 38 of the drive element 26 is in operative connection with the pawl 9. By the motor driven base body 37, which from the closed position, a rotational movement of the drive member 26 in the direction of the arrow D (see FIGS. 17 and 18 ) causes to open the rear lock or the motor vehicle door lock 1, a pin 39 is moved over the transmission lever 38, which is attached to the pivot (articulated lever) 12 offset to the pivot point 13. The rotation of the drive element 26 causes the pin 39 in a formed in the transmission lever 38 slot 40th is moved, during the opening operation due to the rotation of the drive member 26, the pin 39 is moved away from the rotational axis (the pivot point) 30 of the drive member 26. Here, the rotatably mounted about the pivot point 13 pivot (articulated lever) 12 forms an operative connection between the transmission lever 38 of the drive element 26 and the pawl 9. As for example FIG. 18 can be seen, the pin 39 and the coupling portion 15 and the rotational axis 14 of the pawl 9 are each radially offset from the pivot point 13 of the pivot joint (articulated lever) 12 at the pivot (articulated lever) 12 is arranged and mounted.

A rotation of the drive member 26 in a clockwise direction (with respect to the FIGS. 17 to 21 ) in the direction of the arrow D causes a rotational movement of the rotary joint (articulated lever) 12 also in a clockwise direction (in the direction of arrow C), whereby the eccentrically or radially offset to the pivot point 13 and rotatably mounted on the rotary joint (articulated lever) 12 rotational axis 14th the pawl 9 in the region of the coupling portion 15 rotates and moves in a circle-shaped manner about the pivot point 13 of the swivel joint (articulated lever) 12, whereas the latching portion 10 of the pawl 9 of the above-described tangential and then radial movement curve 33 (see, for example FIG. 17 ) follows during the opening process. A movement of the pin 39 rotates directly the pivot (articulated lever) 12 and indirectly the coupling portion 15 of the pawl. 9

For the third embodiment of the rear lock or the motor vehicle door lock 1, it is provided that the drive element 26 initially absorbs kinetic energy before the load acts on the transmission lever 38 for moving the pawl 9. For this purpose, it is provided that for opening the motor vehicle door lock 1, the drive element 26 moves from a starting start position AS in a Anfahrendposition AE, the drive element 26 moves only after reaching the Anfahrendposition AE the pawl 9 from the engaged position in the direction of the release position. The starting start position AS and the starting end position AE are in FIG. 18 indicated, wherein the dashed line represents the position of the transmission lever 38 in the starting start position AS. Upon movement of the drive element 26 between the starting start position AS and the Anfahrendposition AE standing in operative connection with the pawl 9 pin 39 is not moved. Rather, the drive element 26 rotates from the starting start position AS, to receive sufficient momentum or sufficient kinetic energy until reaching the Anfahrendposition AE so that the pawl 9 can be moved in the direction of the release position , Thus, the pin 39 is not moved during this rotational movement of the drive member 26, whereby the drive member 26 would be charged, the slot 40 has a neutral radius, which is synonymous with a freewheeling portion 41 (see FIG. 16 ). Thus, in the movement of the drive member 26 between the starting start position AS and the Anfahrendposition AE, the pin 39 is guided in the freewheeling portion 41 of the slot 40, wherein the freewheeling portion 41 radially outwardly offset to a constant radius with respect to the axis of rotation (pivot) 30 of the drive element 26 is formed extending. Adjoining the freewheeling section 41 is a transfer section 42 of the elongate hole 40, which extends essentially tangentially with respect to the constant radius. Once the pin 39 is in the transmission section 42, the operative connection between the transmission lever 38 and the pawl 9 is made, wherein upon rotation of the drive member 26 in the direction of arrow D of the transmission lever 38, the pin 39 within the slot 40 from the axis of rotation (fulcrum ) 30 away pushes or pushes, whereby the pin 39 rotates the pivot joint (articulated lever) 12, whereupon the pivot joint (articulated lever) 12 deflects the pawl 9 and the axis of rotation 14 relative to the axis of rotation 6 of the rotary latch 5 shifts. As in particular from FIG. 18 it can be seen, the freewheeling section 41 extends in a circular section in an angular range α between 18 ° and 32 ° about the axis of rotation (Fulcrum) 30 of the drive element 26. In the illustrated embodiment, the freewheel defining angle range α is approximately 20 °, wherein the total opening rotational movement of the drive element 26 about the rotation axis (pivot point) 30 is less than 180 °. The freewheeling section 41 allows a load-free starting of the drive element 26 and of the drive element 26 driving motor, wherein only after startup of the engine and upon reaching the Anfahrendposition AE, in which the torque is sufficient to move the pawl 9, the substantially non-positive operative connection between Transmission lever 38, pin 39, pivot (articulated lever) 12 and pawl 9 is made and the pawl 9 is moved. By the freewheeling portion 41 thus the pawl 9 and the attached to the pivot (articulated lever) 12 pin 39 is decoupled from the rotational movement of the drive member 26 for a first period of the opening operation of the motor vehicle door lock or rear lock 1.

During the movement from the engaged position into the release position, the pawl 9 passes through an intermediate position, which in FIG. 19 is shown. It is characteristic that the pawl 9 is drivingly moved from the engagement position to the intermediate position of the drive member 26 and that the movement of the pawl 9 is braked from the intermediate position to the release position of the drive member 26. In this sense, the drive member 26 is formed or driven in such a way by the motor, not shown, with a torque that the drive member 26 driving the movement of the pawl 9 from the engaged position to the intermediate position and the movement of the pawl 9 from the intermediate position in the Release position is formed braking. The position occupied by the pawl 9 intermediate position corresponds to a dead center of the pawl 9. As in FIG. 19 is indicated by the dashed line 21, in the dead center position acting on the pawl 9 force of the rotary latch 5, which in relation to the Representation downward, and the axis of rotation 14 of the pawl 9 in a line, ie, the line 43, lying horizontally, further also the pivot point 13 of the pivot joint (articulated lever) 12 is located in dead center on the line 43.

By acting on the pawl 9 force of the biased rotary latch 5 would be without the driving force of the drive element 26, the pawl 9 again in the in FIG. 17 shown position, the engagement position, move, since it has not exceeded the dead center or the dead center, with the force of the rotary latch 5 in particular the rotary joint (articulated lever) 12 with the attached pawl 9 rotates back. Thus, to move the pawl 9 to the release position and beyond the dead center, the drive member 26 must drive the pawl 9, wherein the drive member 26, the rotation axis 14 of the pawl 9 via the transmission lever 38, the pin 39 and the pivot (articulated lever) 12th drives.

Only when in the FIG. 19 shown dead center position of the rotational axis 14 of the pawl 9 is exceeded, the force of the rotary latch 5 can act such that the pawl 9 is urged as a result of the action of force in the direction of the release position. So that the pawl 9 is not accelerated by the force of the rotary latch 5 and possibly damaged, the drive element 26 serves as a brake when the axis of rotation 14 of the pawl 9 has exceeded the dead center. In this case, the drive element 26 continues its rotation in a clockwise direction at a constant rotational speed until the pawl 9 has reached the release position.

With reference to the FIGS. 17 to 22 are different times of movement of the pawl 9 shown from the engaged position to the release position, wherein FIG. 17 the engaged position and FIG. 19 the above-explained intermediate position or dead center point show. In FIG. 20 the drive element 26 has already rotated and the transmission lever 38 is pivoted clockwise, whereby the position of the pin 9 has changed within the slot 40 without the pin 39 itself or the pivot (toggle) 12 would have moved. On the other hand, then drive between FIG. 18 and FIG. 19 the drive member 26 and the transmission lever 38, the pin 39 such that this rotates the pivot (articulated lever) 12 in a clockwise direction about the pivot point 13, which then turn the rotation axis 14 of the pawl 9 also rotate about the pivot point 13 and the axis of rotation 14 of Pawl 9 reaches the dead center or intermediate position.

In FIG. 20 the drive member 26 has rotated further with the transmission lever 38 in the clockwise direction, whereby the pin 39 is now moved away from the axis of rotation (pivot point) 30 of the drive member 26 and urged. Characterized the pivot (articulated lever) 12 is further moved about its pivot point 13, wherein the rotation axis 14 of the pawl 9, the circular section-shaped movement (movement curve 17) learns and is moved over the intermediate position or dead center. As described above, the drive member 26 now brakes the movement of the pawl 9 and counteracts the force of the rotary latch 5 to move the pawl 9 controlled to the release position and deflect. As soon as the pawl 9 has moved over the dead center, and the rotary latch 5 moves in the direction of its open position.

The release position takes the pawl 9 already in FIG. 21 a, wherein in this illustration a position is shown, in which the latching portion 10 of the pawl 9 has just come out of engagement with the latching arm 11 of the rotary latch 5. In FIG. 22 then only the rotary latch 5 has rotated further clockwise due to their spring bias and here takes the open position in which the closing element 2 is released and passes out of the rotary latch jaw 7, so that a total of the motor vehicle door lock or the rear lock 1 is opened. Characterized in that the drive element 26, the movement of the pawl 9 from the engaged position in the intermediate position driving and braking from the intermediate position into the release position is formed, the drive element 26 acts behind the dead center position as a brake, the movement of the pawl 9 completely by the drive element 26th is guided from the engaged position to the release position and the drive member 26 holds the pawl 9 quasi after exceeding the intermediate position or the dead center and prevents the movement of the pawl 9 is accelerated. Thus, in the dead center position, a kind of load change for the drive element 26th

As has already been described above, during the opening movement in the first movement section, the latching section 10 performs a substantially tangential movement with respect to the rotary latch 5, wherein the pawl 9 continues to engage with the rotary latch 5, but after the dead center has been exceeded turns in the direction of the open position. In the second movement section then the latching portion 10 of the pawl 9 is moved radially away from the rotary latch 5, to disengage the pawl 9 and the rotary latch 5. In order to avoid a possible apparent closure in the return of the pawl 9, the motor vehicle door lock 1 comprises a guide element 44, which in FIG. 15 is shown in a single part representation. By the guide member 44, it is the pawl 9 when returning from the open position into the closed position only then possible to engage in the catch when the axis of rotation 14 of the pawl substantially in FIG. 17 shown position along the circular segment-shaped movement curve 17 has taken.

As stated above for the rear lock according to the invention or the motor vehicle door lock 1, the swivel joint 12 or the push rod 28 or the drive element 26 may be the delay means. Also, any combination of the three components (pivot 12, push rod 28, drive member 26) or all three components together can represent the delay means to the rotational speed of the rotary latch 5 during the opening process at least initially, ie for example in a first third of the movement from the closed position in Direction of the open position, to delay. The delay is controlled, ie the rotational speed is controlled by the delay means, including in the three preceding Embodiments the pawl 9 is used, via which the rotary latch 5 is coupled to the / the delay means.

For example, serve as a retarding means, the rotary joint 12 which is rotatable about the pivot point 13, wherein the pivotable about the rotation axis 14 pawl 9 is mounted on the pivot 12 radially offset from the pivot point 13.

Alternatively, the push rod 28 may be the retarder alone or together with the pivot 12. A first end 29 of the push rod 28 is pivotally and radially offset from the rotational axis 30 of the rotary lever or radial shoulder 31 coupled thereto, wherein the second end 32 of the push rod 28 is coupled to the pivot 12 in the region of the axis of rotation 14 of the pawl 9 so that during movement of the push rod 28, the rotational axis 14 of the pawl 9 along a circular-segment-shaped movement path 17 moves about the pivot point 13 of the rotary joint 12.

On the other hand, the swivel joint 12 may be coupled to a variable-length lever which is designed as a transmission lever 38 with a slot 30 in which a pin or control pin 39 coupled to the swivel joint moves displaceably as a result of a rotation of the transmission lever 38, wherein the lever resp Transmission lever 38, the movement of the pawl 9 from the engaged position driving in an intermediate position and braking from the intermediate position in the release position is formed. Here, then, the intermediate position (according to the third embodiment) is a dead center of the pawl 9, in which at least the forces acting on the pawl 9 force of the rotary latch 5 and the axis of rotation 14 of the pawl 9 are arranged lying in a line 43.

As another alternative, the drive member 26 may be provided as a delay means, the drive member 26 causes the movement of the pivot joint 12 about the pivot point 13 in the movement of the pawl 9 from the engaged position to the release position around and controlled and delayed.

The above-mentioned, different embodiments generally lead to the feature that the delay means at the same time cause actuation of the pawl 9.

Of course, the invention described above is not limited to the described and illustrated embodiments. It will be appreciated that numerous modifications which are obvious to a person skilled in the art according to the intended application can be made to the embodiments shown in the drawing without departing from the scope of the invention. For example, a damping element, which may in particular be a mechanical, hydraulic or pneumatic damping element, serve as an alternative delay means. Such serving as a delay means damping element would then act directly on the rotary latch 5 and the rotational movement of the rotary latch 5 from the closed position to possibly delay the open position linear, where it may be sufficient in terms of avoiding the disturbing opening noise when the delay means the first third of Rotary movement of the rotary latch 5 delays the degradation of the bias of the tailgate due to a compressed seal. If the delay means is designed as acting on the rotary latch 5 damping element, the delayed movement of the rotary latch 5 is decoupled to release the closing element 2 of the pawl 9. Only the pawl 9 must be disengaged from the catch 5, which can be done at the beginning of the opening process, in which case, after the pawl 9 is no longer engaged with the rotary latch 5, that damping element caused by a spring element rotational movement of the rotary latch. 5 delayed accordingly. Furthermore, the invention includes everything that is contained in the description and / or illustrated in the drawing, including what is obvious to the person skilled in the art, which deviates from the specific exemplary embodiments.

Claims (10)

Rear lock (1) for a motor vehicle, with
a in the closed position a closing element (2) encompassing and in the direction of the closing element (2) releasing open position biased rotary latch (5) and
a pawl (9) which is movable between a release position and an engagement position, wherein the pawl (9) in the release position with the rotary latch (5) is disengaged and in the engaged position with the rotary latch (5) is engaged, the the rotary latch (5) is prevented from moving in the direction of the open position,
characterized,
in that delay means are provided which are coupled to the rotary latch (5) in order to delay a speed of movement of the rotary latch (5) in order to release the closing element (2). Rear lock (1) according to claim 1, characterized in that the rotary latch (5) via the pawl (9) is coupled to the delay means such that the speed of movement of the rotary latch (5) to release the rotary latch (5) is controlled. Rear lock (1) according to claim 1 or 2, characterized in that a about a pivot point (13) rotatable pivot (12) is provided, wherein about a rotation axis (14) rotatable pawl (9) on the pivot (12) radially offset is attached to the fulcrum (13). Rear lock (1) according to claim 3, characterized in that a push rod (28) is provided, of which a first end (29) is pivotally and radially offset to a rotational axis (30) of a rotary lever (31) coupled thereto and of the a second end (32) with the pivot (12) in the region of the axis of rotation (14) of the Pawl (9) is coupled such that upon movement of the push rod (28) the axis of rotation (14) of the pawl (9) along a circular segment-shaped movement path (17) about the pivot point (13) of the rotary joint (12) moves. Rear lock (1) according to claim 3, characterized in that the rotary joint (12) with a variable-length lever (38) is coupled, the driving of the pawl (9) from the engaged position driving in an intermediate position and braking from the intermediate position to the release position is trained. Rear lock (1) according to claim 5, characterized in that the intermediate position is a dead center position of the pawl (9), in which at least the force acting on the pawl (9) force of the rotary latch (5) and the axis of rotation (14) of the pawl (9 ) are arranged lying in a line (43). A rear lock (1) according to claim 3 or 4, characterized in that a drive element (26) is provided, which upon movement of the pawl (9) from the engaged position to the release position, the movement of the rotary joint (12) about the pivot point (13). causes around. Rear lock (1) according to one of the preceding claims, characterized in that the delay means simultaneously effect an actuation of the pawl (9). Rear lock (1) according to one of claims 3-8, characterized in that the pivot (12) and / or the push rod (28) and / or the drive element (26) is the delay means. Rear lock (1) according to claim 1, characterized in that a damping element, in particular a mechanical, hydraulic or pneumatic damping element, serves as a retarding agent.

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