DE19860746A1 - Opening, closing displacement elements in motor vehicles involves pivoting displacement element about axis parallel to its surface, pressing it against body seal after reaching end position - Google Patents

Abstract

The method involves pivoting the displacement element (1) about an axis essentially parallel to the surface of the displacement element and pressing it against a body seal (8) after reaching an end position or a freely selectable position along the displacement path. An Independent claim is also included for an arrangement for implementing the method.

Description

The invention relates to a method for opening and closing ß of adjustment elements in motor vehicles according to the upper Concept of claim 1 and a device for performing ren of the procedure.

Window panes, sunroofs and others, in the body rie of a motor vehicle attached adjustment elements not over their entire adjustment path through lateral Guides are supported and in closed condition a guide and / or seal will come in at height ren vehicle speeds due to the overpressure in the Vehicle interior and negative pressure on the outer surface of the  Adjustment element pressed outwards. This leads to other when closing the adjustment element during the Make it move outside the seal and the window pane is no longer closed seals sufficiently.

From DE 20 27 241 C1 it is to avoid this effect known, frameless windows on motor vehicles of a window lifter with the lower edge of the pane on a guide rail is guided so that the Window pane towards the end of the upward movement movement inwards against a sealing strip. To this purpose are on the window pane and on the body Grating plate interacting inclined surfaces provided the Tilting movement in a final phase of the upward movement Support and the window pane transversely to the plane of the pane tense.

The disadvantage of this arrangement is that the Kippbewe leading to lead within the door body wedges or inclined surfaces the combined upward and tilting movement at the end of the closing process with erhebli forces to overcome the friction on the inclined surfaces Chen is connected and under unfavorable conditions Disc can no longer reach its closed position.

DE 41 22 554 A1 describes a motor vehicle door with a known door window frame arranged in the door body, the vertical to accommodate the window pane two fende guide rails that lie with their bottom the end sections protrude into the door body. Here two retaining bolts are attached to the inside of the door are each surrounded by a compression spring with preload  against the lower end portion of the guide seemed to act so that the overhead end of the Door window frame in the rest position towards the inside of the door is pivoted. The door is in the closed position of the door frame with increased contact pressure on the assigned Seal the door.

The disadvantage of this arrangement is that the compression springs over the entire disc stroke on the guide rails and thus the frictional force during the pane increase hubs. The always at the side of the disc lift Gasket pressing the edges of the pane reduce over it in addition, the durability of the seal.

DE 32 43 123 C2 is a window regulator for motor vehicles witness known, the one pressing on the window pane Driver, a guide rail and a cable drive for Adjust the driver along the guide rail between has two end positions. In the area of the closed window corresponding end position is the Carrier by means of bevels from a transport pivoting position into a sealing pivoting position. One transmits one of the ramp surfaces Coupling body the actuating force of the drive on the Driver and is on the driver between a neutral position lung and an operating position back and forth gela gert, during the transition of the coupling body into the insert position the one ramp with the assigned other ramp surface for swiveling the driver cooperates.  

Another disadvantage of this arrangement is that the Tilting movement with an upward movement of the window pane connected at the end of the closing process, resulting in a increased friction at the end of the closing process and thus requires a greater effort. This can happen with correspondingly large forces to trigger a mistake Pinch protection if the required closing forces exceed the maximum permissible pinching force.

The object of the present invention is a method for opening and closing adjustment elements in motor vehicles testify to the type mentioned at the beginning, which at Moving the adjustment element over the entire adjustment away the seals are not additionally stressed and yet a sufficiently high pressure force of the adjusting element in its closed position or within the adjustment path in a selected adjustment position guaranteed.

This object is achieved by a method with solved the features of claim 1.

The solution according to the invention provides minimal friction when moving the adjustment element over the entire Adjustment path safe and ensures that the seals not be additionally claimed and sufficient high pressure force of the adjusting element after the Adjustment strokes either in the closed position of the adjustment elements or within the adjustment range. By the separation of the adjustment movement from the tilting or Swiveling movements are only slight displacement forces Adjustment of the adjusting element required so that at a motor drive of the adjusting elements also motors small power can be used because the  Adjustment of the adjusting element required forces of the pressure forces are decoupled or the temporal Working area of the motors in one lifting area and one Sealing area is expanded.

Furthermore, the solution according to the invention ensures Pretension of the adjusting element only when it is on press on the seal within the adjustment path or in the closed position is required, resulting in a high Service life of the seals is reached.

A method of opening and closing motor vehicle This distinguishes window panes as adjustment elements records that the window pane after reaching the vorege level or definable position on the displacement path in the we substantially parallel to the X axis of the vehicle and perpendicular pivoted to the window plane (Y axis of the vehicle) and pressed against a seal on the vehicle door opening becomes.

The pivoting of the window pane against the door seal can be limited to one side edge of the window pane be so that, for example, the one on the B-pillar Motor vehicle adjacent side edge of a window pane parallel to the X-axis of the vehicle and perpendicular to the Schei level is pivoted while the to the A-pillar adjacent side edge of the window pane of a Transla tion in the Y direction of the motor vehicle is subjected to a pivoting of the window on the A-pillar because of the unfavorable leverage ratio almost no effect has the disc preload while translating the Window pane in the Y direction in the area of the A-pillar achieved better tightness of the window pane.  

The pivoting of the adjusting element can be done on both meaningful position in the course of the displacement path as well after reaching one of the adjustment's closed positions elements corresponding end position of the displacement of the adjusting element causing the driver to take place. On Swiveling the adjustment element in a freely selectable Position between the one and the other end position the displacement path of the driver is optionally electrical motorized via appropriate control electronics or manually using a lever. In case of a electrical adjustment can pivot against the door seal immediately when the window regulator is at a standstill drive or after a definable downtime of the adjusting element so that it is assumed can be that no further closing movement of the window disc is done. In order to move the window pane in the half-open position in the Y direction of the vehicle avoid and a tight contact of the window to the To achieve side door seals, the window pane be pivoted around the X axis and against the door seal pressed.

The separation of the management and shifting function in Adjustment of the adjustment element by the sealing function after reaching an intermediate position specified by the user tion on the displacement path between two end positions or when reaching a closed position can be force or depending on the route.  

With a force-dependent pivoting of the adjusting element the adjustment element is exceeded after exceeding a essentially in the direction of adjustment of the adjusting element acting, predetermined biasing force pivoted and against pressed the body gasket. The opening credits force preferably adjusted by means of a spring so that it is larger than that for adjusting the adjusting element required displacement force and less than the sum of the displacement force and the excess force, that is the permissible force required to adjust the Verstellele force required is.

The specification of the preload force by the arrangement of a A spring with a specified spring characteristic ensures a safe decoupling of the displacement movement from to Sealing required swiveling movement under consideration stiffness on the displacement path and specified anti-trap conditions that apply to a Object or part of the body acting when closing Limit the adjustment element. This fulfills the Spring has a double function, namely not only that of the one swiveling movement, but also guaranteed in the event of a so-called "hard pinching" an additional way of Drive unit by mutually moving the Functional parts, so that adequate protection against pinching is ensured.

As an alternative to the force-dependent pivoting of the adjuster fundamentally perpendicular to the displacement movement the adjustment element can be moved on a displacement path, on which the adjustment when reaching the closed position element moved perpendicular to the plane of the adjusting element and with a given pressure force against the body  seal is pressed. The path-dependent pivoting the adjustment element is thus carried out by the design of the Displacement in the area of the end position and not through the specification of a pretensioning force in the closed position is to be overcome.

The pressure force with which the adjusting element against the Body gasket presses is essentially due to the Kinematics of the mutually movable parts of the force transmission support element and by the characteristic of the drive adjustable.

The pivot axis or the pivot point of the adjusting element can optionally on the guide receiving the driver a guide rail, as constructive in the driver put pivot axis or fulcrum or as a fictional, not constructively designed swivel axis or as a fictitious, not be designed constructively fulcrum, wherein the pivot axis or the fulcrum preferably the eigen have a momentary pole.

The different ways of arranging the swivel The axis or the pivot point essentially depend on the Construction of the adjustment device and leave great constructive freedom. When training the Pivot axis or the pivot point of the adjusting element as constructive driver is the swivel axis or Pivotal point preferably between two movable to each other Parts of the driver arranged.

In another embodiment, the pivot axis lies or the fulcrum on the opposite of the contact direction opposite side of the adjustment element.  

The pivot axis or the pivot point of the adjustment element do not have to be geometrical in relation to the adjustment device tion, but can also be based on a roll the specified distance.

The manufacturing tolerances of the parts that move with respect to one another the individual parts of the driver when swiveling back perpendicular to the movement direction of the driver pressed against each other. this happens in particular by a device to compensate for Her positional tolerances resulting from a on the floor surface of the Driver base body trained, asymmetrical Aus same tooth and one face the equalizing tooth with one on the inclined surface of the differential tooth aligned inlet slope of the recess Coupling body exists, with the compensating tooth at relax nenden spring element on the inlet slope into the recess tion of the coupling body slides.

The inventive method for opening and closing Adjustment elements leaves different constructive designs additions. In the drawing are some examples le and are explained in more detail below, taking the various ways of realizing the Process features according to the invention not on the in Drawing shown embodiments limited are. The drawing shows:

Fig. 1-4 schematic representations of part of a motor vehicle window lifter with a device for force-dependent Ver pivoting a window in the closed position;

Fig. 5 is a side view of a Verstellvorrich device for opening and closing a window pane during the displacement movement of the window pane;

Fig. 6 is a side view of a Verstellvorrich device for a window pane in the pivoting movement of the window pane;

Fig. 7 is a side view of the functional elements of the adjustment device according to Figs 5 and 6.

Fig. 8 is an exploded view of the Verstellvor direction shown in FIGS. 5 to 7 and

Fig. 9 is an enlarged view of a Einrich device to compensate for manufacturing tolerances of the mutually movable parts of the driver;

Fig. 10-12 an illustration of the movement phases of tolerance compensation;

Fig. 13 is a schematic representation of part of a motor vehicle window lifter with a device for path-dependent Ver pivoting a window in the closed position and

Fig. 14-15 show two perspective views of a device for position-dependent pivoting of a window pane.

The part of a motor vehicle window lifter shown schematically in FIG. 1 shows a window pane 1 , the lower window edge 12 of which is held in a window connection or mounting 2a and between a completely open and a completely closed end position, in which the upper window edge 11 at one Seal 8 with pre-given pressure force is present, is adjustable on a displacement between one and the other end position. The window connection 2 a is firmly connected to a coupling body 6 a, which is part of a two-part driver, the second part of which consists of a driver base body 3 a.

The coupling body 6 a is in the adjustment direction A of the window pane 1 relative to the carrier base body 3 a movable and articulated via a nipple chamber 50 to a rope 5 , which is connected to a manual or motor's drive of the motor vehicle window regulator, not shown. The coupling body is also used to adjust the window pane, so that a self-adjusting concept is created which makes a coarser setting or even a waiver of adjustment possible during assembly.

The driver base body 3 a is positively connected via driver guides 31 , 32 with a guide rail 4 so that it can be moved along the guide rail 4 between an upper and lower end position. Between an end face 61 of the coupling body 6 a and facing projections 23 , 33 of the washer connection 2 a and the driver base body 3 a, a spring 7 a is arranged as a clamping element before, the spring force is such that it is larger than that for adjusting the Window 1 between the lower and upper end position required displacement force, but less than the sum of the United displacement force and the excess force to limit the pinching force.

Reaches the main carrier body 3 a which corresponds to the closing position on the window pane 1 , and the coupling body 6 a is moved further by the rope 5 in the direction of arrow A against the biasing force of the spring 7 a, the spring 7 a is compressed and the Scheibenanbin extension 2 a about the pivot point D of the rotatable mutually lying end faces 23 , 33 of the disk connection 2 a and the driver base body 3 a as a result of the adjacent wedge surfaces 20 , 60 of the disk connection 2 a and the coupling body 6 a in the direction of arrow B. , That is, based on a motor vehicle in the Y direction depending on the wedge angle of the coupling body 6 a moves around the pivot point D when the wedge between the coupling body 6 b and the disc connection 2 a, the driver base body 3 a and the disc connection 2 a swung apart in the end position.

So that with the window connection 2 a connected Fen sterscheibe 1 is pivoted about the X-axis of the vehicle and the upper window edge 11 pressed against the seal 8 of a motor vehicle door.

The biasing force of the spring 7 a causes that when a sliding force acts on the coupling body 6 a during the displacement of the window pane 1 this does not perform a pivoting movement and thus does not tip against the seal 8 , ie there is no relative movement between the mutually movable parts of the driver on.

The wedge angle of the adjoining wedge surfaces 20 , 60 of the washer connection 2 a and the coupling body 6 a determines the force with which the washer is pressed against the seal and is in the range of a few degrees of angle.

Fig. 2 shows a schematic representation of part of a motor vehicle window regulator with a window pane 1 , the lower window edge 12 is held in a Scheibenan binding 2 b, which is connected to a coupling body 6 b of a shared driver. The coupling body by 6 b has a wedge surface 62 which faces a wedge surface 30 of a carrier base body 3 b, the driver shared by the wedge surfaces 30 , 62 controlling the force via the wedge angle with which the window pane be 1 against the seal 8 is pressed.

In recesses of the inclined surfaces 30 and 62 of the coupling body 6 b and the driver base body 3 b, a spring 7 b is arranged as a compression spring, which strives to push the coupling body 6 b and the driver base body 3 b apart. Also in this embodiment, the coupling body 6 b can be used to adjust the window pane 1 , so that a self-adjusting concept is created, which makes a coarser setting or a setting without the window pane 1 possible during assembly.

The driver base body 3 b is connected via a nipple chamber 50 with a rope 5 of the window regulator and about Füh approximately 31 , 32 positively connected to a guide rail ne 4 and arranged movably on this between two end positions. The coupling body 6 b has a guide 63 which is connected to the guide rail 4 , but which, in contrast to the guide elements 31 , 32 of the carrier base body 3 b, can be pivoted in the plane of the drawing around the guide rail 4 and thus forms a pivot point D of the adjusting device .

After reaching a closing position corresponding to the upper end position of the driver 3 b and when a further force is exerted on the cable 5 , the spring 7 b is compressed after the pretensioning force has been exceeded and the coupling body is compressed by 6 b as a result of the sloping surfaces 62 and 30 of the coupling body 6 b and driver 3 b pivoted about the pivot point D, so that the upper pane edge 11 of the window pane 1 is pivoted in the direction of arrow B, that is to say in the Y direction of the motor vehicle, and is pressed against the seal 8 of a motor vehicle door.

Fig. 3 shows in a plan view and Fig. 4 in a section along the line IV-IV another Ausführungsbei game for a force-dependent pivoting of a window pane around the X-axis and thus perpendicular to the pane surface in the Y direction of a motor vehicle when it is reached an upper end position corresponding to the closed position.

In this exemplary embodiment, the coupling body 6 c consists of a deflection segment which is connected via a nipple chamber 50 to a cable 5 of a motor vehicle window lifter, which is guided around an upper cable pulley 40 articulated on a guide rail 4 .

A driver base body 3 c connected to a window connection 2 c about a pivot point D, about which the window connection 2 c can be pivoted, is connected to the guide rail 4 via guide elements 31 , 32 . The deflecting segment 6 c is supported by a spring 7 c relative to the carrier base body by 3 c, so that when the prestressing force specified by the spring 7 c is exceeded and further transmission of a displacement force in the direction of arrow A via the cable 5 on the deflection segment 6 c pivoted about the pivot point D and thus, as a result of the wedge surfaces between the deflection segment 6 c and the window connection 2 c, the window pane 1 is pressed against the pivot point D and thus in the Y direction of the motor vehicle against the seal 8 . The tensioned during the closing movement of the window pane 1 beyond a defined preload and in the opening movement of the window pane up to the defined pre-tensioned spring 7 c again causes the window pane 1 to act during the shifting movement because of the action on the carrier base body 3 c Displacement force of the rope 5 does not perform a pivoting movement and tilts against the seal 8 .

In FIGS. 5 through 8 an embodiment of a modular construction of the individual system components is an adjustment device with a force-dependent adjustment of a motor vehicle window pane 1 is shown, which after exceeding a d given by a spring element 7 biasing force of a pivoting movement of the window pane 1 in the direction of arrow B effected according to FIG. 6, by appropriate design of the individual elements of the Ver the pivot point D adjusting device in the space located and an arbitrarily large radius R, the seal determines the extent of pivotal movement and so that the pressing force of the window pane of the door.

The window pane 1 is held in a pane connection 2 d, which can be inserted via connecting surfaces 25 with correspondingly designed receiving slots 66 of a coupling body 6 d and can be positively connected to the coupling body 6 d. In a recess 68 of the coupling body 6 d, a toothing element 26 can be used, which engages through a corresponding recess in the window connection 2 d and serves to secure the position of the window pane 1 .

The coupling body 6 d represents part of a two-part driver, the division of which takes place via concave / convex guide surfaces. The convex guide surface 65 of the coupling body 6 d is displaceable relative to the concave guide surface 35 of the carrier base body 3 d against the biasing force of the spring element 7 d, which is inserted into a recess 36 of the carrier base body 3 d and opposite the coupling body 6 d at one angled upper edge 67 of the coupling body 6 d is supported.

The driver base body 3 d is in a manner not shown ter on the guide rail of a window lifter leads, while the coupling body 6 d is connected in a suitable manner with the cable of a window regulator drive.

FIGS. 5 and 6 illustrate in a schematic side view of the process of pivoting of the window pane 1 in achieving the closed position of the window pane 1 corresponding upper end position of the adjusting device.

Is in this position on the connected via a cable receptacle 38 with the cable of the window regulator drive Mitneh mer 3 further d a displacement force on the rope on the carrier 3 exerted d, as will be shown in Fig. 5 spaced-apart top edges 37, 67 of the coupling body 6 d and the driver 3 d against the biasing force of the Federele element 7 d moved towards each other so that the convex guide surface 65 of the coupling body 6 d on the concave guide surface 35 of the driver 3 d slides and thus the coupling body 6 d a pivoting movement around the fictitious in Space located pivot point D executes and the window pane 1 is pivoted in the direction of arrow B.

In order to compensate for the manufacturing tolerances of the individual components of the adjusting device, a tolerance compensation is provided in the adjusting device according to FIG. 9 shown in FIGS . 5 to 8 in the form of a surface that runs obliquely to the direction of movement of the coupling body 6 d and the driver base body 3 d is seen both in the carrier base body 3 d and on the coupling body 6 d. The tolerance compensation consists of a on the bottom surface of the carrier body 3 d arranged compensating tooth 39 with a self-locking bevel, which includes an angle of, for example, α = 7 ° with respect to the vertical and a tooth holder 69 with a running bevel, the angle of which is the angle of self-locking slope to the vertical corresponds.

Figs. 10 to 12 illustrate the operation of the To leranzausgleichs.

Reaches the adjusting device according to FIG. 10, the top end stop, the driver main body is 3 d against the biasing force of the spring member 7 moved d and accordingly the above-described function of the Verstellvor direction as shown in FIGS. 5 to 8, the disc connectivity 2 d together with the coupling body 6 d pivoted. If the motor vehicle window pane moves back from the end stop, it is first pivoted back into the movement position, the driver base body 3 d moving under the action of the biasing force of the spring element 7 d in the opposite direction. Here, the equalizing tooth 39 slides on the inclined surface and the inlet slope of the tooth holder 69 into the tooth holder 69 .

Due to the inclined surface of the compensating tooth 39 and the inlet slope of the tooth receptacle 69 , the further movement of the carrier base body 3 d and the coupling body per 6 d and the disk connection 2 d are contracted under the action of the prestressing force of the spring element 7 d and existing tolerances are compensated in this way .

As an alternative to the exemplary embodiments described above, for a force-dependent pivoting of the window pane around the X axis or in the Y direction of a vehicle, FIG. 13 shows a schematic illustration for a pivoting pivoting of a window pane after reaching one of the closed positions of the window pane Corresponding upper end position of the window pane.

In this embodiment, which represents only one of several conceivable functional principles, the window pane 1 is connected to a one-piece driver 9 , which is connected via a nipple chamber 50 to the cable of a window lifter, which drives the driver 9 between an upper and a lower one End position moved along a guide rail 4 e. The agitator 9 is located with a front-side abutment surface 91 is optionally substituted with lower biasing force on the guide rail 4 e slidably, and is connected via a guide member 92 a form-locking rail with the guide 4 e.

The guide element 92 is designed such that the driver 9 swings ver in the plane of the drawing about the guide rail 4 e when the stop surface 91 slides into a recess 41 of the guide rail 4 e. The resulting pivoting movement of the driver 9 about the pivot point D leads to a pivoting of the window pane 1 in the direction of arrow B, so that the upper pane edge 11 is pressed against the vehicle door seal 8 .

In Figs. 14 and 15 a further variant of a path-dependent control of the pivoting movement is shown a Mitneh mers, FIG. 14, the wafer transport Stel lung of the driver and Fig. 15 shows the pivoted position of the follower.

The driver is composed of a form-fitting on the guide rail 4 sliding carrier body 3 f and a movable coupling body 6 f, which performs pivoting movements in the ± -Y direction for applying a motor vehicle window pane to the window seal. The coupling body 6 f is connected via an axis of rotation 94 to the carrier base body 3 f, that is to say the axis of rotation 94 represents the connection between the part which is positively connected to the guide rail 4 and the movable part of the carrier.

The coupling body 6 f is controlled in the ± -Y direction via a spring-loaded pin 93 , which controls the travel-dependent tilting of the coupling body 6 f. This control can be triggered both by a recess 42 in the guide rail 4 by the recess 42 releases the sprung pin 93 in a certain position of the driver, but it can also be carried out on the entire adjustment path between the lower and the upper end stop . For this purpose, the spring-loaded pin 93 is connected, for example, to a mechanical release device which releases the pivoting movement of the coupling body at any intermediate position between the lower and upper end stops.

If after the application of the motor vehicle window pane to the window seal, the window pane is moved further in the closing or opening direction, the spring-loaded pin 93 is first moved back into its spring-loaded position and thus the motor vehicle window pane is released from the system to the window seal, that is to say in the Transport position pivoted back before the disk movement continues in the opening or closing direction. When Errei Chen the upper end stop, the spring-loaded pin 93 falls into the recess 42 of the guide rail and in this way triggers the pivoting movement of the coupling body 6 f against the carrier body 3 f connected to the guide rail 4 . Here too, when the window is opened, the spring-loaded pin 93 is first moved back into its position and thus the coupling body 6 f is pivoted back into the transport position before the opening movement of the window pane takes place.

The pivoting of the coupling body 6 f relative to the entraining base body 3 f can also be carried out by an electric motor, electromagnetic table or the like, by a corresponding control pulse being given to the driver in an arbitrary position between the lower and upper end stops when the window pane is at a standstill. which causes the pivoting of the coupling body 6 f relative to the main carrier body 3 f. Before continuing the opening and closing movement of the window pane, the coupling body 6 f is moved back into its neutral or transport position before the further opening and closing movement of the window pane is carried out.

In the same way, when the upper end stop is reached, the pivoting movement of the coupling body 6 f is carried out with respect to the carrier base body 3 f, and thus the motor vehicle window pane is applied to the window seal. When opening the window pane, the coupling body is first pivoted back into the transport position by 6 f, before the carrier base body is moved in the opening direction on the guide rail 4 .

Claims (33)

1.Method for opening and closing adjustment elements such as window panes, sunroofs and the like in motor vehicles, in particular window panes for motor vehicles with window frame-less vehicle doors, with an adjustment device with at least one driver receiving the adjustment element, which along a guide rail on a displacement path between two end positions by means of a Power transmission element is moved, characterized in that the adjusting element ( 1 ) after reaching an end position or a freely selectable position on the sliding movement after completion of the shifting movement about an axis which runs essentially parallel to the disk surface of the adjusting element ( 1 ), and pivoted is pressed against a body seal ( 8 ). 2. The method according to claim 1 for window panes of motor vehicles, characterized in that the window pane be ( 1 ) after reaching the predetermined or predeterminable position on the displacement path substantially parallel to the X-axis of the vehicle and perpendicular to the glass plane ne (Y-axis of the vehicle) is pivoted and pressed against a seal ( 8 ) at the vehicle door opening. 3. The method according to claim 1 or 2, characterized in that the adjusting element ( 1 ) after reaching one of the closed position of the adjusting element ( 1 ) correspond to the end position of the driver ( 3 a- 3 f; 6 a- 6 f) pivots ver and is pressed against the body seal ( 8 ). 4. The method according to claim 1, characterized in that the adjusting element ( 1 ) at standstill in any position between the one and the other end position on the displacement path of the driver ( 3 a- 3 f; 6 a- 6 f) pivoted and against the body seal ( 8 ) is pressed ge. 5. The method according to claim 4, characterized in that the adjusting element ( 1 ) pivots ver after a downtime and is pressed against the body seal ( 8 ). 6. The method according to claim 4 or 5, characterized in that the adjusting element ( 1 ) pivots ver by an electric motor and is pressed against the body seal ( 8 ). 7. The method according to claim 4 or 5, characterized in that the adjusting element ( 1 ) is pivoted manually via a Hebelbe actuation and pressed against the body seal ( 8 ). 8. The method according to claim 1 or 2, characterized in that the adjusting element ( 1 ) after exceeding a substantially in the direction of adjustment (A) of the United adjusting element ( 1 ) acting, predetermined biasing force and ge against the body seal ( 8 ) presses becomes. 9. The method according to claim 1 or 2, characterized net gekennzeich that the adjusting element (1) is moved on a displacement path on which the achievement of the Schließpositi on the adjusting element (1) is moved perpendicularly to the plane of Verstel lelements (1) and with A predetermined pressure force is pressed against the body seal ( 8 ). 10. The method according to claim 8, characterized in that the biasing force is preferably adjusted by means of a spring ( 7 a- 7 f) so that it is greater than the pushing force required for adjusting the adjusting element ( 1 ). 11. The method according to claim 10, characterized in that the biasing force is preferably adjusted by means of a spring ( 7 a- 7 f) so that it is smaller than the sum of the displacement force and the excess force (the permissible force which is used to adjust the Ver actuating force required exceeds). 12. The method according to at least one of the preceding claims, characterized in that the pressing force is essentially adjustable by the kinematics of mutually movable parts of the driver ( 3 a- 3 f; 6 a- 6 f) and by the characteristic curve of the drive. 13. The method according to at least one of the preceding claims, characterized in that the pivot axis or the pivot point (D) of the adjusting element ( 1 ) on the driver ( 3 a- 3 f; 6 a- 6 f) on taking a leadership Guide rail ( 4 ) is. 14. The method according to at least one of the preceding claims 1 to 12, characterized in that the pivot axis or the pivot point (D) of the adjusting element ( 1 ) as a constructive in the driver ( 3 a- 3 f; 6 a- 6 f) placed on (R) pivot axis or pivot point (D) is formed. 15. The method according to claim 14, characterized in that the pivot axis or the pivot point (D) between two mutually movable parts of the driver ( 3 a- 3 f; 6 a- 6 f). 16. The method according to at least one of the preceding claims 1 to 12, characterized in that the pivot axis or the pivot point (D) of the adjusting element ( 1 ) as a fictitious (r), not constructively designed (r) pivot axis or pivot point (D) is formed, which preferably has the properties of a momentary pole. 17. The method according to claim 16, characterized in that the pivot axis and the pivot point (D) of the adjusting element (1) on which the pressing direction is opposed to the side of the adjusting element (1). 18. The method according to at least one of the preceding claims 1 to 11, characterized in that the pivot axis or the pivot point (D) of the adjusting element ( 1 ) rolls on a predetermined distance. 19. The method according to at least one of the preceding claims, characterized in that the mutually movable parts of the driver ( 3 a- 3 f; 6 a- 6 f) when pivoting back for the purpose of tolerance compensation perpendicular to the direction of movement of the driver ( 3 a- 3 f ; 6 a- 6 f) are pressed against each other. 20. Device for performing the method according to at least one of the preceding claims, characterized in that at least part of the driver ( 3 a- 3 f; 6 a- 6 f) substantially parallel to the X-axis of the vehicle and perpendicular to the plane of the window (Y axis of the vehicle) is pivotable. 21. The apparatus according to claim 20, characterized in that the driver ( 3 a- 3 f; 6 a- 6 f) from a coupling body ( 6 a- 6 f) which with an adjusting element ( 1 ) receiving adjusting element connection ( 2nd a- 2 d) is firmly connected, and consists of a form-fitting with the guide rail ( 4 ) connected driver base body ( 3 a- 3 f), and that the coupling body ( 6 a- 6 f) via a biasing element ( 7 a - 7 f) connected to the driver base body ( 3 a- 3 f) and sliding in the direction of movement of the driver ( 3 a- 3 f; 6 a- 6 f) and perpendicular to the surface of the adjusting element ( 2 a- 2 f) is supported on the slave body ( 3 a - 3 f). 22. The apparatus according to claim 21, characterized in that the adjusting element connection ( 2 a) and the Mitneh mer base body ( 3 a) are connected to one another via a swivel joint, that the coupling body ( 6 a) is coupled to the force transmission element ( 5 ) and via a wedge surface ( 60 ) with the adjusting element connection ( 2 a) is connected and with one of the wedge surface ( 60 ) opposite surface on the driver base body ( 3 a) slidably and that the biasing element ( 7 a) between an end face ( 61 ) of the Coupling body ( 6 a) on the one hand and the articulated connection between the adjusting element connection ( 2 a) and the driver base body ( 3 a) on the other hand is arranged. ( Fig. 1) 23. The device according to claim 21, characterized in that the coupling body ( 6 b) on the guide rail ( 4 ) is steered and rotatable about the articulation ( 63 ) that the connection between the coupling body ( 6 b) and that to the force transmission element ( 5 ) connected Mitneh mer base body ( 3 b) of mutually assigned Keilflä surfaces ( 30 , 62 ) of the coupling body ( 6 b) and the Mitneh mer base body ( 3 b) and that the Vorspannele element ( 7 b) in the Wedge surfaces ( 30 , 62 ) is embedded. ( Fig. 2) 24. The device according to claim 21, characterized in that the coupling body ( 6 d) and the driver base body ( 3 d) are connected to each other via transverse to the adjustment direction, arched guide surfaces ( 35 , 65 ) on which the coupling body ( 6 d) slides along with the main body ( 3 d) against the biasing force of the pre-tensioning element ( 7 d). ( Fig. 5-8) 25. The device according to claim 24, characterized in that the curved guide surface ( 65 ) of the coupling body on the adjusting element connection ( 2 d) opposite side surface of the coupling body ( 6 d) and the curved te guide surface ( 35 ) of the carrier base body ( 3rd d) on the guide rail connection of the carrier base body ( 3 d) opposite side surface is arranged. 26. The apparatus according to claim 25, characterized in that the coupling body ( 6 d) a convex guide surface ( 65 ) and the driver base body ( 3 d) one of the konve xen guide surface ( 65 ) of the coupling body ( 6 d) adapted te concave guide surface ( 35 ) and that the biasing element ( 7 d) is arranged between a support point ( 67 ) on the coupling body ( 6 d) and a biasing element receptacle ( 36 ) on the carrier base body ( 3 d). 27. The apparatus according to claim 20, characterized in that with the adjusting element ( 1 ) Mitneh mer ( 3 e) with a coupling element ( 92 ) on the guide rail ( 4 ) rotatably articulated and with a Gleitele element ( 91 ) on the Guide rail ( 4 ) is supported that the guide rail ( 4 ) has a recess ( 41 ) into which the sliding element ( 91 ) in the closing position of the adjusting element ( 1 ) corresponding end position of the driver ( 3 e) slides that the adjusting element ( 1 ) is pivoted and pressed onto the seal ( 8 ). ( Fig. 13) 28. The device according to at least one of the preceding claims, characterized in that the driver ( 3 f, 6 f) from a with the guide rail ( 4 ) connected NEN carrier base ( 3 f) and one with the driver base body ( 3rd f) via an axis of rotation ( 94 ) connected and pivotable in the Y direction of the vehicle coupling body ( 6 f), and that a switching element ( 93 ) the pivoting movement of the coupling body ( 6 f) depending on an additional control command and / or The position of the carrier base body ( 3 f) on the adjustment path including the end stops enables or blocks. 29. The device according to claim 28, characterized in that the switching element has a spring-loaded pin ( 93 ) between the driver base body ( 3 f) and the coupling body ( 6 f), and that in the guide rail ( 4 ) provided recesses ( 42 ) release the sprung pin ( 93 ) in certain positions of the carrier base body ( 3 f). 30. The device according to at least one of the preceding claims 20 to 29, characterized in that the Ver element connection ( 2 a- 2 e), the driver ( 3 e) or the coupling body ( 6 a- 6 d) and the driver base body ( 3 a- 3 d) consist of each other in the form, in mutually movable and mutually displaceable elements. 31. The device according to claim 30, characterized in that the adjusting element connection ( 2 a- 2 d) and the Kop pelkörper ( 6 a- 6 d) can be locked together. 32. Device according to at least one of the preceding claims, characterized in that the mutually movable parts of the driver ( 3 a- 3 f; 6 a- 6 f) are provided with a device ( 39 , 69 ) to compensate for manufacturing tolerances. 33. Apparatus according to claim 32, characterized in that means for compensating manufacturing tolerances from an asymmetrical compensating tooth ( 39 ) and one of the compensating tooth ( 39 ), which are formed on the bottom surface of the entraining base body ( 3 d), face one with the on the inclined surface of the compensating tooth ( 39 ) aligned inlet bevel recess ( 69 ) of the coupling body ( 6 d), the compensating tooth ( 39 ) with the spring element ( 7 d) relaxing over the inlet bevel into the recess ( 69 ) of the coupling body ( 6 d) glides.