DE102005006916B4 - Hinge for a vehicle flap - Google Patents

Abstract

Hinge for a vehicle door, comprising
a first hinge part (2, 2 ', 2'',2''') arranged on a vehicle frame or vehicle flap,
a second hinge part (3; 3 ';3'';3''') disposed on the other of the vehicle frame or vehicle door, wherein the first hinge part (2; 2 ';2'';2''') and the second hinge part (3; 3 ';3'';3''') are pivotally connected together,
a reversing lever (7; 7 ';7'';7''') having at least one first joint (10; 10 ';10'';10''') and a second joint (13; 13 ';13''). 13 '''), wherein the bell crank (7; 7'; 7 ''; 7 ''') is connected to the second hinge (13; 13'; 13 ''; 13 ''') with respect to the first hinge part (2, 2 ', 2'',2''') movable part is pivotally mounted, and
a spring element (11; 11 ';11'';11''') which comprises the first hinge part (2; 2 ';2'';2''') and the deflection lever (7; 7 ';7''; 7 ''') is coupled to the first hinge (10; 10'; 10 ''; 10 '''),
characterized,
that the bellcrank ...

Description

The The invention relates to a hinge for a vehicle door the preamble of claim 1 and a method for opening a Vehicle flap according to the preamble of claim 32, include a on a first of vehicle frame or vehicle door arranged Hinge part, one on the other vehicle frame or vehicle flap arranged second hinge part, wherein the first hinge part and the second hinge part are pivotally connected to each other, a lever with at least a first joint and a second Joint, wherein the lever with the second joint at a respect to the first hinge part movable part is pivotally mounted, and a spring element that the first hinge part and the lever coupled to the first joint.

DE 197 123 82 C1 shows a hinge for a vehicle door, wherein a first hinge part is arranged on a vehicle frame and a second hinge part on a vehicle door, wherein the first hinge part and the second hinge part are pivotally connected to each other by means of a four-bar linkage. The four-bar linkage has a first and a second link, wherein each of the two links are each arranged pivotably on the first hinge part and the second hinge part. On the second hinge part, a bell crank is pivotally connected to a first joint, wherein the bell crank has a second joint, on which a gas spring is ajar, which is fixed with a second end to the first hinge part. The reversing lever has a support with the first link of the four-bar linkage. A disadvantage of this type of hinges is the fact that the given by the support of the lever with a handlebar force acts on the handlebars such that it counteracts the opening movement of the hinge, so that the support by the gas spring the opening force by the support is reduced and opening the vehicle door is possible only with additional, great effort.

DE 198 46 600 A1 shows a hinge for a vehicle door, wherein a first hinge part is arranged on the vehicle frame and a second hinge part on the vehicle door, wherein the first hinge part and the second hinge part pivotally connected to each other by means of a four-bar linkage comprising a first link and a second link are. The first link and the second link are pivotally mounted on the first hinge part and the second hinge part, respectively. A gas spring is disposed with a first end on the first hinge part and a second end on the second hinge part. On the hinge part disposed on the vehicle frame, a V''shaped leaf spring is provided which engages with a roller disposed on the second hinge part. In a closed position of the hinge, the V''shaped leaf spring is completely compressed by the roller. When opening the vehicle door, the leaf spring generates an upward force on the roller and thus causes the vehicle door to be opened, the roller rolling over the leaf spring to a free end and the upward force being reduced during opening of the vehicle door. At a certain opening angle of the vehicle door in which the force of the V-shaped leaf spring is too small to assist the opening movement, the gas spring takes over the support of the opening movement of the flap.

US 5,788,312 A shows a hinge for a vehicle door, in which a first hinge part on a vehicle door and a second hinge part are arranged on a vehicle frame. The first hinge part and the second hinge part are pivotally connected to each other by means of a hinge pin. On the first hinge part, a spring element is arranged, which is fastened with a further end to the vehicle frame, so that the first hinge part and the second hinge part are coupled by means of the spring element.

DE 201 189 61 U1 shows a hinge for a vehicle door, in which a first hinge part on a vehicle door and a second hinge part are arranged on a vehicle frame. The first hinge part and the second hinge part are pivotally connected to each other by means of a hinge pin. The first hinge part has a U-shaped design, wherein on a first leg of the U, the vehicle door is arranged and on a second leg of the U, the second hinge part is pivotally provided. Arranged on the arc of the U-shaped first hinge part is a spring element which is connected to a power source at a second end. When the vehicle door is opened, it springs open under the action of the spring element and the vehicle flap opens depending on the design of the spring element. In the fully open position of the vehicle door, the spring element is relieved by means of the power source, so that a small, and not directed against the spring element force is necessary to close the vehicle door.

DE 101 179 35 A1 shows a hinge for a vehicle door, wherein a first hinge part is arranged on a vehicle door, which is pivotally connected via a hinge pin with a second frame part arranged on a vehicle frame. An opening unit is attached to the second hinge part via a U-shaped extension ordered, which has a driven by an electric motor spindle, which is arranged in a spindle nut.

It The object of the invention is a hinge for a vehicle door the preamble of claim 1 and a method for opening a vehicle door specify according to the preamble of claim 32, which is a safe and reliable opening of the Vehicle flap allows.

These Task is in the aforementioned hinge for a vehicle door according to the invention with the Characteristic features of claim 1 solved by that the lever a support with the re having the first hinge part movable part.

moreover This object is achieved in the aforementioned method for opening a Vehicle flap according to the invention with the characterizing features of claim 32 solved by that in a first opening angle range the lever a support with the re of the first hinge part movable part, and in that a second opening angle range the support of the reversing lever with respect of the first hinge part movable part is canceled.

By the inventive provision a support of the reversing lever with respect to the first hinge part movable part is used for the opening movement of the vehicle door a first opening angle range and a second opening angle range defined, wherein the first opening angle range includes a closed position of the vehicle door and the second Area a completely open position. In the first opening angle range the deflection lever has a support with the re of the first hinge part movable part, while the support in the second opening angle range is canceled. Since in the first opening angle range contrary the weight of the vehicle door a large force to open necessary is, is about to open the vehicle door in the first opening area to support, by means of the support the deflection lever caused by the spring element and the opening movement supporting the vehicle flap Transferring force to the hinged part connected to the vehicle flap. In the second opening angle range is the support lifted the reversing lever, so that transmitted to the vehicle door Force is given only by the spring element, whereby a by too big Force resulting striking of the flap in the Endöffnungsstellung avoided and a safe opening the vehicle door possible is.

The two opening angle ranges are by a so-called dead center position of the reversing lever and of the spring element separated from each other. The dead center position is while the pivoting of the two hinge parts achieved when the linkage the spring element on the first hinge part, the first joint and the second joint of the reversing lever lie on a connecting line.

In the first opening angle range the power is over a first effective lever arm and in the second opening angle range via a second transfer the effective lever arm to the hinge part attached to the vehicle door.

By the spring element and the first effective lever arm is in the first opening angle range an opening supportive Torque for generates the hinged part connected to the vehicle door. The opening supportive Torque is due to the introduced force of the spring element, the Length of the first effective lever arm and by the sine of an angle α, which between the force introduction direction of the spring element and the Given the first effective lever is given.

In the second opening angle range is due to the spring element and the second effective lever arm an opening supportive Torque for generates the hinged part connected to the vehicle door. The opening supportive Torque is due to the introduced force of the spring element, the Length of the second effective lever arm and by the sine of an angle α ', which between the force introduction direction of the spring element and the second effective Lever arm is given, given.

At the Shut down the vehicle door in the second opening angle range is the closing movement given by the dead weight of the vehicle door, these Movement is slowed down by the force of the spring element. During the closing movement the vehicle flap is the swing speed of the vehicle door getting bigger, so that in the first opening angle range greater power the closing movement must be directed against. By supporting the bellcrank with with respect the first hinge part of the movable part is opposite to the closing movement directed, thereby increasing slamming the vehicle door due to its own weight avoided is. This avoids, for example, objects or an arm of a user between the vehicle door and the vehicle frame is trapped.

In a preferred embodiment the bell crank has a first and a second arm, the support being provided with the first hinge member movable part on one of the first and second arms and the second hinge on the other arm on the first arm and the second arm. This ensures that the opening-supporting force is securely and reliably transmitted to the arranged on the vehicle door second hinge part. By providing a first and a second arm for the reversing lever of the reversing lever is also adapted to the geometry of the vehicle door and the vehicle frame, so that the space for the hinge is advantageously reduced.

Conveniently, the first arm and the second arm have different lengths, whereby the adaptation to the vehicle geometry continues to be ensured is. Due to the different lengths have the first joint and the second joint at a variable distance from each other, so that the dead center position between the lever and the spring element is also variable and thus the dead center position corresponding opening position the vehicle door can be adjusted according to the vehicle type can.

Of the first arm and the second arm of the bell crank define a connection point, on which the second joint of the reversing lever is advantageously provided is. This ensures that the lever a simple geometry and thus without major Assembly effort can be connected to the spring element. Further characterized the spring element is thus connected to the lever, that the introduction of force by the spring element safely and reliably means of the reversing lever on the respect the first hinge part movable part in the second opening angle range transmitted can be.

In a first advantageous embodiment, the first arm and the second arm of the bell crank an angle of about 90 degrees to each other. In a further advantageous embodiment the first arm and the second arm at an angle of about 135 degrees to each other. Due to the variable design of the angle between the first arm and the second arm is the variable adaptation of Reversing lever and the associated opening and closing properties of the various types of vehicles further secured.

It It is understood that the first arm and the second arm of the bell crank can have any angle to each other to the adaptation of the Hinge to the vehicle door of any vehicle type on to enable. Further, it is understood that the angle between the first arm and the second depending on the vehicle door any other amount can. The lengths the first and the second arm and the angle between the first and the second arm are here of the kinematics and statics the vehicle door and the vehicle frame given.

In a first preferred embodiment, the first hinge part and the second hinge part pivotable by means of a four-bar linkage coupled together. The four-bar linkage comprises a first link and a second link, each pivotally mounted on the first link Hinge part and pivotally hinged to the second hinge part.

one of the first and second links is suitably approximately S-shaped formed, whereby the opening movement the vehicle door one for the user has easy to use Verschwenkungsbahn.

Is appropriate the first link as a short link and the second link as a long link formed, whereby the pivoting movement of the vehicle door, which by the geometry of the first hinge part and the second Hinge part pivotally connecting four-joint is given, accordingly the length the two handlebars to a vehicle type is individually customizable.

It It goes without saying that the first handlebar is also a long handlebar and the second link may be formed as a short link.

Are useful the linkage of the first link, the second link and the first Joint of the bell crank provided on a connecting line, thereby the assembly effort for attaching the first link and the second Handlebar of the four-bar linkage as well as the reversing lever is reduced.

At an opening angle of approximately 45 degrees, the first joint and the second joint of the reversing lever and the articulation of the spring element on the first hinge part advantageously lie on a connecting line. As a result, the dead center position between the lever and the spring element is defined, which divides the opening movement of the vehicle door in the first opening angle range and the second opening angle range. In the first opening angle range of the vehicle flap, the spring element acts on the second hinge part with a torque with respect to the first articulation of the reversing lever. The torque acts to assist opening the vehicle door, wherein the torque by the introduced force of the spring element, the length of the first effective lever arm, by the virtual connection of the first joint and the linkage of the handlebars and by the sine of the angle α between the force introduction direction of the spring element and the first effective lever arm is given. In the second opening angle range, the spring element urges the second hinge part with a torque with respect to the second joint, which is provided on the movable relative to the first hinge part, with an opening-supporting torque, wherein the torque by the introduced force of the spring element, the length of the second effective Lever arm, which is given by the virtual connection of the second joint and the articulation of the handlebars and by the sine of the angle α 'between the force introduction direction of the spring element and the second effective lever arm.

The support the reversing lever is advantageous after an opening angle of about 45 degrees lifted, whereby the supportive force by the spring element to the opening reduces the vehicle door according to the second opening angle range is and the opening movement the vehicle door to be continued controlled by the user can.

Of the Lever is preferably on one of the first link and the second link of the four-bar pivotally arranged. Advantageous Here is that the first effective lever arm of the first opening angle range through the first joint of the reversing lever and the articulation of one Handlebar given to the first hinge part, the second effective Lever in the second opening angle range through the second joint of the reversing lever and the articulation of the one Handlebar is given to the first hinge part.

alternatives the bellcrank is advantageously pivotable on the second hinge part arranged. Here, the first effective lever arm is advantageous in the first opening angle range through the support of the reversing lever and the articulation of the two links on the second hinge part and in the second opening angle range the second joint of the reversing lever and the articulation of one of the two Handlebar given to the second hinge part.

In Another preferred embodiment is the first hinge part and the second hinge part pivotable by means of a hinge pin connected with each other. The lever is here pivotable provided the second hinge part, wherein the support of the Reversing lever is also provided on the second hinge part.

Advantageous the second hinge part has a projection, the deflection lever is pivotally mounted on the projection. This will achieve that the articulation of the reversing lever a distance to the rest Has second hinge part, so that in a proper opening angle reached the dead center position of the spring element and the reversing lever becomes. Due to the dead center position of the spring element and the reversing lever become the first opening angle range and the second opening angle range defined, wherein in the first opening angle range a first effective lever through the articulation of the second hinge part on the first hinge part, the hinge pin, and through the linkage the deflection lever is given to the projection. In the second opening angle range is a second effective lever through the articulation of the first Hinge part and the second hinge part and by the linkage the spring element is given to the lever at the first joint.

In the first opening angle range the spring element urges the second hinge part with a Torque that due to the introduced force of the spring element, the length the first effective lever and the angle α between the direction of force introduction and the first effective lever is given. During the flap opening movement becomes the position of the projection and thus the articulation of the reversing lever with respect to the second hinge part of the hinge pin changed on a circular path, wherein the angle α between the first effective lever and the compression spring changes, so the torque while the flap opening movement is reduced. In the dead center position this is through the first effective lever torque given minimal. Moreover, in the dead center position the support the reversing lever with the second hinge part advantageously canceled, wherein by the spring element in the second opening area defined thereby now a torque with respect of the second articulation of the reversing lever is given to the projection.

The Spring element is appropriate either designed as tension or as a compression spring, resulting in an adaptation of the hinge system to the through the vehicle door and the vehicle frame predetermined geometry for the hinge is possible. By optionally designed as a tension or compression spring spring element the lever can optionally with a tensile force or a compressive force be charged.

to support the flap movement is advantageously provided a motor for Example is coupled to the spring element, wherein the motor both the opening movement as well as the closing movement the vehicle door advantageously supported.

Further Features and advantages of the invention will become apparent from the dependent claims and the following description.

The The invention is described below with reference to the accompanying drawings of four preferred embodiments explained in more detail.

1 shows a first embodiment of a hinge according to the invention in a closed position.

2 shows the hinge of the invention 1 in a partially open position.

3 shows the hinge of the invention 1 in a completely open position.

4 shows a second embodiment of the hinge according to the invention in a closed position.

5 shows the hinge of the invention 4 in a partially open position.

6 shows the hinge of the invention 4 in a completely open position.

7 shows a third embodiment of a hinge according to the invention in a closed position.

8th shows the hinge of the invention 7 in a partially open position.

9 shows the hinge of the invention 7 in a completely open position.

10 shows a fourth embodiment of the hinge according to the invention from a closed position.

11 shows the hinge of the invention 10 in a partially open position.

12 shows the hinge of the invention 10 in a completely open position.

In 1 to 3 is a first embodiment of a hinge according to the invention 1 for a vehicle door, in which a first hinge part 2 with a second hinge part 3 by means of a four-link 4 is pivotally coupled, the four-bar linkage 4 a first handlebar 5 and a second handlebar 6 having.

The first handlebar 5 is with a first linkage 5a on the first hinge part 2 and with a second linkage 5b on the second hinge part 3 arranged pivotally. The first handlebar 5 has a linear extent.

The second handlebar 6 has an S-shaped form, wherein the second link 6 with at a first end of the S by means of a linkage 6a pivotable on the first hinge part 2 is arranged. At a second end of the S-shaped second link 6 this is by means of a linkage 6b pivotable on the second hinge part 3 arranged.

On the second handlebar 6 is a bellcrank 7 pivotally mounted, wherein the lever 7 a first arm 8th and a second arm 9 has, which are rigidly fixed to each other in a connection point and have an angle of 90 ° to each other. The first arm 8th is as a long arm and the second arm 9 formed as a short arm.

It is understood that the angle between the first arm 8th and the second arm 9 may also be different from 90 °.

The lever 7 has a first joint 10 on that in the connection point of the first arm 8th and the second arm 9 is provided, wherein at the first joint 10 a first end of a spring element 11 is arranged pivotally. The spring element 11 is with a second end to the first hinge part 2 arranged pivotally. The spring element 11 includes a tension spring 12 ,

The lever 7 points at the connection point of the first arm 8th with the second arm 9 opposite end of the first arm 8th a second joint 13 on, with the bellcrank 7 pivotable on the second link 6 of the four-link 4 is arranged. The joint 13 defines a pivot point for the Umlenkhebl 7 ,

The lever 7 indicates at the connection point of the first arm 8th and the second arm 9 opposite end of the second arm 9 a support 14 with the second handlebar 6 of the four-link 4 on.

In 1 the hinge according to the invention is shown in a closed position, wherein the lever 7 with the support 14 on the second handlebar 6 is applied.

In 2 is the hinge of the invention 1 in a partially open position, a so-called transition position, shown, wherein the lever 7 and the tension spring 12 are aligned with each other in a so-called dead center position. The dead center position shows a so-called limit position for the lever 7 and the tension spring 12 , In the dead center position is the first joint 10 and the second joint 13 of the reversing lever 7 as well as the linkage 11a of the spring element 11 on the second hinge part 2 on a connecting line V aligned with each other.

By the dead center position of the reversing lever 7 and the spring element 11 is the pivoting range of the first hinge part 2 and the second hinge part 3 divided into a first opening angle range and a second opening angle range.

In the dead center position of the reversing lever 7 with the spring element 11 have the first hinge part 2 and the second hinge part 3 an opening angle of about 45 degrees.

In the first opening angle range of the vehicle door, which includes an angle of 0 degree corresponding to a closed position of the vehicle door to an opening angle of about 45 degrees corresponding to the dead center position, the bell crank is supported 7 with the on the second arm 9 arranged support 14 on the second handlebar 6 of the four-link 4 from.

Through the first joint 10 of the reversing lever on which the tension spring 12 is pivotally mounted, and the linkage 6a of the second link 6 on the first hinge part 2 is a first effective lever 15 by means of the support 14 Are defined. Between the force introduction direction of the spring element 11 and the first effective lever arm 15 is given an angle α, wherein the angle α during the opening movement in the first opening angle range of the first hinge part 2 and the second hinge part 3 increased.

By through the spring element 11 introduced force, the length of the first effective lever arm 15 and by the sine of the angle α is a torque with respect to the first joint supporting the opening movement of the vehicle door 10 given.

Of the Angle α passes through during the opening movement in the first opening angle range the vehicle door approximately the angular range of about 60 ° to approximately 100 °, where the torque is maximum at an angle of α = 90 °.

The force introduction direction of the spring element 11 changes by the pivoting movement of the reversing lever 7 However, during the pivoting movement in the first opening angle range their direction, but is always directed such that by the support 14 of the reversing lever 7 with the second handlebar 6 an opening assisting pulling force on the second hinge part 3 '' is transmitted.

In the in 2 shown dead center position is the force introduction direction of the spring element 11 on the connecting line V of the first joint 10 and the second joint 13 of the reversing lever 7 and the linkage 11a of the spring element 11 arranged.

In the second opening angle range is a second effective lever 16 through the second joint 13 and the linkage 6a of the second link 6 on the first hinge part 2 Are defined. Between the force introduction direction of the spring element 11 and the second effective lever 16 is given an angle α ', wherein the angle α' during the opening movement between the first hinge part 2 and the second hinge part 3 increased.

A torque assisting the opening movement of the vehicle door in the second opening angle range is due to the introduced force of the spring element 11 , the length of the second effective lever arm 16 and given by the sine of the angle α '. The angle α 'passes through an angular range of about 60 ° to about 80 °, so that in the fully open position by the torque on the second hinge part 3 transmitted force is so large that the vehicle door is kept open.

The support 14 of the reversing lever 7 on the second handlebar 6 of the four-link 4 is canceled during the pivotal movement of the vehicle door in the second opening angle range. Furthermore, the first joints remain 10 , the second joint 13 and the linkage 11a of the spring element 11 during the pivoting movement in the second opening angle range on the connecting line V.

In the above embodiment, the hinge according to the invention has been explained in detail, wherein the deflection lever pivotally mounted on the second link 6 of the four-link 4 is arranged. It is understood that the lever on the first link 5 of the four-link 4 can be provided.

In 4 to 6 a second embodiment of a hinge for a vehicle door according to the invention is shown, wherein identical and functionally identical components are assigned the same reference numerals. In the following, the differences compared to the first exemplary embodiment are essentially discussed.

This in 4 to 6 Hinged hinge for a vehicle door comprises a first hinge part 2 and a second hinge part 3 using a four-bar linkage 4 the first handlebar 5 and a second handlebar 6 pivotally connected to each other.

The first handlebar 5 has a first arm 51 on that in a linkage 5a ' pivotable on the first hinge part 2 is arranged and a second arm 52 in a linkage 5b ' pivotable on the second hinge part 3 is arranged. The first arm 51 and the second arm 52 are rigidly interconnected and have approximately an angle of 135 ° to each other.

It is understood that between the first arm 51 and the second arm 52 Depending on the geometry of the vehicle frame and the vehicle door any other angle may be provided.

The second handlebar 6 ' of the four-link 4 ' extends straight and is at a first end to a linkage 6a ' on the first hinge part 2 and with a second end in a linkage 6b ' on the second hinge part 3 arranged pivotally.

The second hinge part 3 ' indicates the second hinge part 3 facing side a projection 31 on, on which the bellcrank 7 ' with the first arm 8th' pivotable on the second joint 13 ' is arranged. The second joint 13 ' defines a pivot point for the bellcrank 7 , being the first joint 10 ' in the pivotal movement of the two hinge parts to each other about the second joint 13 ' on one by the first arm 8th' moved as radius given circular path.

The second arm 9 ' of the reversing lever 7 ' points with the first hinge part 2 opposite side of the second hinge part 3 ' the support 14 ' on. The second hinge part 3 ' has a corresponding overhang for this purpose 3a ' on, at the the lever 7 ' with the support 14 ' is applied.

The first arm 8th' of the reversing lever 7 ' is as a short arm and the second arm 9 ' is designed as a long arm, with the first arm 8th' and the second arm 9 ' have an angle of 90 degrees to each other.

In the junction of the two arms 8th' and 9 ' of the reversing lever 7 ' is the first joint 10 provided, on which the spring element 11 ' is arranged pivotably with a first end. With the second end is the spring element 11 ' in the linkage 11a ' on the first hinge part 2 arranged. The spring element 11 ' includes a compression spring 12 ' ,

In 5 becomes the hinge according to the invention 1' shown in a partially open position, wherein the lever 7 ' and the compression spring 12 ' are aligned with each other in a so-called dead center position. In the dead center position is the first joint 10 ' and the second joint 13 ' of the reversing lever 7 ' as well as the linkage 11a 'of the spring element 1.1 'on the second hinge part 2 aligned with each other on a connecting line V '.

By the dead center position of the reversing lever 7 ' and the spring element 11 ' is the pivoting range of the first hinge part 2 and the second hinge part 3 ' divided into a first opening angle range and a second opening angle range.

In the dead center position of the reversing lever 7 ' with the spring element 11 ' have the first hinge part 2 and the second hinge part 3 an opening angle of about 40 degrees to each other.

In the first opening angle range of the vehicle door, which includes an angle of 0 degree corresponding to a closed position of the vehicle door to an opening angle of about 40 degrees corresponding to the dead center position, the bell crank 7 ' with the second arm 9 a support 14 ' with the at the second hinge part 3 arranged projection 3 ' on.

Through the virtual connection of the linkage 6b ' of the second link 6 ' on the second part of the cabinet 3 ' and the first joint 10 ' the Umlenkhebls 7 ' is a first effective lever arm 15 ' Are defined. Between the force introduction direction of the spring element 11 ' and the first effective lever arm 15 ' is given an angle α, wherein the angle α during the opening movement between the first hinge part 2 and the second hinge part 3 ' reduced.

By through the spring element 11 ' introduced force, the length of the first effective lever arm 15 ' and by the sine of the angle α is a torque with respect to the first joint supporting the opening movement of the vehicle door 10 ' Given by the torque on the bellcrank 7 ' a force is effected in such a way that over the Abstüztung 14 ' a compressive force on the second hinge part 3 ' is given, which is the opening movement of the second hinge part 3 ' supported.

Of the Angle α passes through during the opening movement in the first opening angle range the vehicle door approximately the angular range of 130 ° to approximately 100 °.

The force introduction direction of the spring element 11 ' changes by the pivoting movement of the reversing lever 7 ' However, during the Schwenkbeweung in the first opening angle range their direction, but is always directed so that by the support 14 ' of the reversing lever 7 ' with the second hinge part 3 ' an opening assisting pressing force on the second hinge part 3 ' is transmitted.

In the in 4 dead center position shown is the force introduction direction of the spring element 11 ' on the connecting line V 'of the first joint 10 ' and the second joint 13 ' of the reversing lever 7 ' and the linkage 11a ' of the spring element 11 ' arranged.

In the second opening angle range is a second effective lever 16 ' through the second joint 13 ' and the linkage 6a ' of the second link 6 on the second hinge part 3 ' Are defined. Between the force introduction direction of the spring element 11 ' and the second effective lever 16 ' is given an angle α ', wherein the angle α' during the opening movement between the first hinge part 2 and the second hinge part 3 ' reduced.

A torque assisting the opening movement of the vehicle door in the second opening angle range is due to the introduced force of the spring element 11 ' , the length of the second effective lever arm 16 ' and given by the sine of the angle α '. The angle α 'passes through an angular range of about 145 ° to about 80 °, so that in the fully open position by the torque on the second hinge part 3 transmitted force is so large that the vehicle door is kept open.

The support 14 ' of the reversing lever 7 ' on the second hinge part 3 ' is canceled during the pivotal movement of the vehicle door in the second opening angle range. Furthermore, the first joints remain 10 ' , the second joint 13 ' and the linkage 11a 'of the spring element 11 ' during the pivoting movement in the second opening angle range on the connecting line V ', so that the force introduction direction of the spring element 11 ' with respect to the second hinge part 3 ' always the same direction.

In 7 to 9 is a third embodiment of a hinge according to the invention 1'' shown, wherein identical or functionally identical components are assigned the same reference numerals. In the following, the differences compared to the previous exemplary embodiments are essentially discussed.

This in 7 to 9 shown embodiment of a hinge according to the invention 1'' includes a vehicle frame associated with the first hinge part 2 '' and a vehicle door associated second hinge part 3 '' , where the first hinge part 2 '' and the second hinge part 3 '' by means of a hinge pin 20 are pivotally connected to each other about a pivot axis S.

The second hinge part 3 '' has a so-called gooseneck geometry, starting from the pivotal connection by means of the hinge pin 20 with the first hinge part 2 '' has a linear extension, an arcuate extent and a linear extension for attachment to the vehicle door.

The first hinge part 2 '' has a projection in the first linear extension 21 on top, with the second hinge part 3 '' has an angle of 90 °.

At the second hinge part 3 '' opposite end of the projection 21 is the bellcrank 7 '' with the first arm 8th'' pivotable in the second joint 13 '' arranged.

The second arm 9 '' of the reversing lever 7 '' points to the second hinge part 3 '' the support 14 '' on. The first arm 8th'' is here as a long arm and the second arm 9 '' formed as a short arm, with the first arm 8th'' and the second arm 9 '' have an angle of approximately 135 degrees to each other.

It is understood that also the first arm 8th'' as a short arm and the second arm 9 '' can be formed as a long one. Further, it is understood that between the first arm 8th'' and the second arm 9 '' every other angle can be provided.

At the second arm 9 '' facing end of the first arm 8th'' is the first joint 10 '' provided, on which the spring element 11 '' is arranged pivotally. With a second end is the spring element 11 '' swiveling in a linkage 11''a on the first hinge part 2 '' pivotally provided. The spring element 11 '' includes a tension spring 12 '' ,

In 8th is the hinge of the invention 1'' shown in a partially open position, wherein the partially open position by a so-called dead center position of the deflection lever 7 '' and the spring element 11 '' is defined. The dead center position of the reversing lever 7 '' and the spring element 11 '' is given by the fact that the linkage 11a '' of the spring element 11 '' on the first hinge part 2 '' as well as the first joint 10 '' and the second joint 13 '' of the reversing lever 7 '' are arranged on a connecting line V ''.

In the first opening angle range of the vehicle door in which the vehicle door passes through an angle of 0 degree corresponding to a closed position to an angle of approximately 80 degrees corresponding to the position of the cooking point, is a first effective lever 15 '' by a virtual connection between the hinge axis S and the first joint 10 '' given. The first effective lever 15 '' points with the force introduction direction of the spring element 11 '' an angle α, wherein the angle α during the pivoting movement in the first opening angle range approximately through an angular range of 70 ° to 110 °.

In the first opening angle range, the force for assisting the opening movement of the vehicle door by means of the first effective lever arm 15 '' on the second hinge part 3 '' transmitted, in which case an opening-supporting torque by the introduced force of the spring element 11 '' , the length of the first effective lever arm 15 '' and by the sine of the angle α between the force introduction direction of the spring element 11 '' and the first effective lever arm 15 '' given is.

By the torque is by means of the support 14 '' of the reversing lever 7 '' with the second hinge part 3 '' an opening assisting pressing force on the second hinge part 3 '' causes, wherein the force introduction direction of the spring element 11 '' according to the pivoting of the reversing lever 7 '' is oriented, so that during the pivoting movement in the first opening angle range always an opening-supporting pressure force on the support 14 '' on the second hinge part 3 '' acts.

In the second opening angle range corresponding to the dead center position 8th until the entire opening of the vehicle door accordingly 9 is given, is a second effective lever 16 '' for transmitting the force to the second hinge part 3 '' by the virtual connection of the pivot axis S and the second joint 13 '' defined, wherein the second effective lever arm 16 '' an angle α 'with the force introduction direction of the spring element 11 '' having.

In the second opening angle range is the support 14 '' of the reversing lever 7 '' with the second hinge part 3 '' and the opening assisting torque is canceled by the introduced force of the spring element, the length of the second effective lever arm 16 '' and by the sine of the angle α between the force introduction direction of the spring element 11 '' and the effective lever arm 16 '' given, wherein the torque with respect to the second joint 13 '' is oriented.

During the pivoting movement in the second opening angle range remain the first joint 10 '' and the second joint 13 '' of the reversing lever 7 '' and the linkage 11''a of the spring element 11 '' on a second hinge part 2 '' oriented on the connecting line V '' to each other, wherein the angle α 'between the second effective lever 16 '' and the connecting line V "passes through an angular range of about 80 degrees to about 160 degrees during the pivotal movement in the second opening angle range.

The first joint 10 '' , the second joint 13 '' and the linkage 11a '' of the spring element 11 '' remain during the pivoting movement in the second opening angle range on the connecting line V '', so that the force introduction direction of the spring element 11 '' with respect to the second hinge part 3 '' always the same direction.

In 10 to 12 is a fourth embodiment of a hinge according to the invention 1''' wherein identical or functionally identical components are assigned the same reference numerals. In the following, the differences compared to the third exemplary embodiment are essentially discussed.

In 10 to 12 is a hinge according to the invention 1''' in which a first hinge part 2 ''' by means of a hinge pin 20 pivotable about a pivot axis S with a second hinge part 3 ''' connected is.

The first hinge part 2 ''' has an L-shaped shape with a first part 2a ''' and a second part 2 B''' on, with the first part 2a ''' and the second part 2 B''' have an angle of 90 ° to each other.

At the second part 2 B''' opposite end of the first part 2a ''' is the second hinge part 3 ''' by means of the hinge pin 20 arranged pivotally. At the first part 2a ''' opposite end of the second part 2 B''' is the spring element 11 ''' with the linkage 11a ''' pivotally provided. With the second end is the spring element 11 ''' pivotable on the first joint 10 ''' of the reversing lever 7 ''' arranged. The spring element 11 ''' includes a compression spring 12 ''' ,

The functioning of the hinge 1''' is essentially identical to that of the hinge 1'' of the previous embodiment, wherein leditglich instead of a tension spring a compression spring 12 ''' is provided, which accordingly from an opposite side to the lever 7 ''' attacks.

The invention has been explained above with reference to embodiments in which the movable relative to the first hinge part, on which the lever is pivotally mounted by means of the second articulation and with which the lever has a support, is given by the second hinge part, both at a pivotal connection of the two hinge parts by means of a hinge pin as well as by means of a four-bar linkage with two links. Moreover, with respect to the first hinge part movable part is also by one of the two links of the Given four-jointed.

Claims (32)

Hinge for a vehicle door, comprising a first hinge part (10) arranged on a vehicle frame or vehicle door ( 2 ; 2 '; 2 ''; 2 ''' ), a second hinge part disposed on the other of the vehicle frame or vehicle door (US Pat. 3 ; 3 '; 3 ''; 3 ''' ), wherein the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) and the second hinge part ( 3 ; 3 '; 3 ''; 3 ''' ) are pivotally connected together, a lever ( 7 ; 7 '; 7 ''; 7 ''' ) with at least one first joint ( 10 ; 10 '; 10 ''; 10 ''' ) and a second joint ( 13 ; 13 '; 13 ''; 13 ''' ), wherein the lever ( 7 ; 7 '; 7 ''; 7 ''' ) with the second joint ( 13 ; 13 '; 13 ''; 13 ''' ) at a respect to the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) movable part is pivotally mounted, and a spring element ( 11 ; 11 '; 11 ''; 11 ''' ), which is the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) and the lever ( 7 ; 7 '; 7 ''; 7 ''' ) at the first joint ( 10 ; 10 '; 10 ''; 10 ''' ), characterized in that the reversing lever ( 7 ; 7 '; 7 ''; 7 ''' ) a support ( 14 ; 14 '; 14 ''; 14 ''' ) with respect to the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) has movable part. Hinge according to claim 1, characterized in that the deflection lever ( 7 ; 7 '; 7 ''; 7 ''' ) a first arm ( 8th ; 8th'; 8th''; 8th''' ) and a second arm ( 9 ; 9 '; 9 ''; 9 ''' ) having. Hinge according to claim 2, characterized in that the support ( 14 ; 14 '; 14 ''; 14 ''' ) on one of the first arm ( 8th ; 8th'; 8th''; 8th''' ) or the second arm ( 9 ; 9 '; 9 ''; 9 ''' ) and the second joint ( 13 ; 13 '; 13 ''; 13 ''' ) on the other of the first arm ( 8th ; 8th'; 8th''; 8th''' ) and the second arm ( 9 ; 9 '; 9 ''; 9 ''' ) is provided. Hinge according to claim 2 or 3, characterized in that the first arm ( 8th ; 8th'; 8th''; 8th''' ) one of the second arm ( 9 ; 9 '; 9 ''; 9 ''' ) has different lengths. Hinge according to one of claims 2 to 4, characterized in that the second joint ( 13 ; 13 '; 13 ''; 13 ''' ) of the reversing lever ( 7 ; 7 '; 7 ''; 7 ''' ) at a connection point of the first arm ( 8th ; 8th'; 8th''; 8th''' ) and the second arm ( 9 ; 9 '; 9 ''; 9 ''' ) is arranged. Hinge according to one of claims 2 to 5, characterized in that the first arm ( 8th''; 8th''' ) and the second arm ( 9 ''; 9 ''' ) have an angle of 135 ° to each other. Hinge according to one of claims 1 to 5, characterized in that the deflection lever ( 7 ; 7 ' ) Is L-shaped. Hinge according to claim 7, characterized in that the first joint ( 13 ; 13 ' ) of the reversing lever ( 7 . 7 ' ) is formed on the knee of the L. Hinge according to one of claims 1 to 8, characterized in that the first hinge part ( 2 ; 2 ' ) and the second hinge part ( 3 ; 3 ' ) by means of a four-bar linkage ( 4 ; 4 ' ) are pivotally coupled together, wherein the four-bar linkage ( 4 ; 4 ' ) a first handlebar ( 5 ; 5 ' ) and a second handlebar ( 6 ; 6 ' ), each pivotally mounted on the first hinge part (11). 2 ; 2 ' ) and pivotable on the second hinge part ( 3 ; 3 ' ) are articulated. Hinge according to claim 9, characterized in that at least one of the first link ( 5 ; 5 ' ) and the second link ( 6 ; 6 ' ) Is S-shaped. Hinge according to claim 9 or 10, characterized in that the first link ( 5 ; 5 ' ) as a short link and the second link ( 6 ; 6 ' ) is designed as a long arm. Hinge according to claim 9 or 10, characterized in that the first link ( 5 ; 5 ' ) as a long handlebar and the second link ( 6 ; 6 ' ) is designed as a short link. Hinge according to one of claims 9 to 12, characterized in that the articulation ( 5b . 5b ' ) of the first link ( 5 ), the linkage ( 6b ; 6b ' ) of the second link ( 6 ) and the first joint ( 10 ; 10 ' ) of the reversing lever ( 7 ; 7 ' ) lie on a connecting line. Hinge according to one of claims 9 to 13, characterized in that the first joint ( 10 . 10 ' ), the second joint ( 13 ; 13 ' ) of the reversing lever ( 7 ; 7 ' ) and the linkage ( 11a ; 11a ') of the spring element ( 11 ) on the first hinge part ( 2 ; 2 ' ) are at an opening angle of 45 ° on a connecting line (V; V '). Hinge according to one of claims 9 to 14, characterized in that the spring element ( 11 ; 11 ' ) the second hinge part ( 3 ; 3 ' ) at least up to an opening angle of 45 ° with a torque with respect to the first joint ( 10 ; 10 ' ). Hinge according to one of claims 9 to 15, characterized in that the support ( 14 . 14 ' ) of the lever ( 7 ; 7 ' ) can be canceled after an opening angle of 45 °. Hinge according to one of claims 9 to 16, characterized in that the deflection lever ( 7 ) on one of the first link ( 5 ) or the second handlebar ( 6 ) is pivotally mounted. Hinge according to claim 17, characterized in that in a first opening angle range an effective lever arm for opening the vehicle door by the first joint ( 10 ) of the reversing lever ( 7 ) and the linkage ( 5a ) of a handlebar ( 5 ) on the first hinge part ( 2 ) and in a second opening angle range through the second joint ( 13 ) of the reversing lever ( 7 ) and the linkage ( 5a ) of a handlebar ( 5 ) on the first hinge part ( 2 ) given is. Hinge according to one of claims 9 to 17, characterized in that the deflection lever ( 7 ' ) on the second hinge part ( 3 ' ) is pivotally mounted. Hinge according to claim 19, characterized in that in a first opening angle range an effective lever arm for opening the vehicle door by the support ( 14 ' ) of the reversing lever ( 7 ' ) and the linkage ( 6b ' ) one of the two handlebars ( 6 ' ) on the second hinge part ( 3 ' ) and in a second opening angle range through the second joint ( 13 ' ) of the reversing lever ( 7 ' ) and the linkage ( 6b ' ) of one of the two links ( 6 ' ) on the second hinge part ( 3 ' ) given is. Hinge according to one of claims 1 to 8, characterized in that the first hinge part ( 2 ''; 2 ''' ) and the second hinge part ( 3 ''; 3 ''' ) by means of a hinge pin ( 20 ) are pivotally connected together. Hinge according to claim 21, characterized in that the deflection lever ( 7 ''; 7 '' ) on the second hinge part ( 3 ''; 3 ''' ) is pivotally mounted. Hinge according to claim 21 or 22, characterized in that the second hinge part ( 3 ''; 3 ''' ) a lead ( 22 ), and that the lever ( 7 ''; 7 ''' ) on the projection ( 22 ) is pivotally mounted. Hinge according to claim 23, characterized in that the projection ( 20 ) with the second hinge part ( 3 ''; 3 ''' ) has an angle of 90 °. Hinge according to one of claims 21 to 24, characterized in that the second hinge part ( 3 ''; 3 ''' ) has an at least partially S-shaped profile. Hinge according to one of claims 21 to 25, characterized in that the first joint ( 10 ''; 10 ''' ), the second joint ( 13 ''; 13 ''' ) and the linkage ( 11a ''; 11a ''' ) of the spring element ( 11 ''; 11 ''' ) on the first hinge part ( 2 ''; 2 ''' ) are at an opening angle of 80 ° on a connecting line (V '', V '''). Hinge according to one of claims 21 to 26, characterized in that the spring element ( 11 ''; 11 ''' ) the second hinge part ( 3 ''; 3 ''' ) at least up to an opening angle of 90 ° with a torque with respect to the first joint ( 10 ''; 10 ''' ). Hinge according to one of claims 1 to 27, characterized in that the spring element ( 11 ; 11 '' ) as a tension spring ( 12 ; 12 '' ) is trained. Hinge according to one of claims 1 to 27, characterized in that the spring element ( 11 '; 11 ''' ) as a compression spring ( 12 '; 12 ''' ) is trained. Hinge according to claim 29, characterized in that the spring element ( 11 '; 11 ''' ) is designed as a gas spring. Hinge according to one of claims 1 to 30, characterized that a motor for support the flap movement is provided. A method for opening a vehicle door, comprising a first hinge part arranged on one of a vehicle frame or vehicle door (US Pat. 2 ; 2 '; 2 ''; 2 ''' ) and arranged on the other of the vehicle frame or vehicle door second hinge part ( 3 ; 3 '; 3 ''; 3 ''' ), wherein the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) and the second hinge part ( 3 ; 3 '; 3 ''; 3 ''' ) are pivotally connected together, a lever ( 7 ; 7 '; 7 ''; 7 ''' ) with at least one first joint ( 10 ; 10 '; 10 ''; 10 ''' ) and a second joint ( 13 ; 13 '; 13 ''; 13 ''' ), wherein the lever ( 7 ; 7 '; 7 ''; 7 ''' ) with the second joint ( 13 ; 13 '; 13 ''; 13 ''' ) at a respect to the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) movable part is pivotally mounted, and a spring element ( 11 ; 11 '; 11 ''; 11 ''' ), which is the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) and the lever ( 7 ; 7 '; 7 ''; 7 ''' ) at the first joint ( 10 ; 10 '; 10 ''; 10 ''' ) coupled, characterized in that in a first opening angle range of the lever ( 7 ; 7 '; 7 ''; 7 ''' ) a support ( 14 ; 14 '; 14 ''; 14 ''' ) with respect to the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) has movable part, and that in a second opening angle range the support ( 14 ; 14 '; 14 ''; 14 ''' ) of the reversing lever with respect to the first hinge part ( 2 ; 2 '; 2 ''; 2 ''' ) moving part is canceled.