WO2013053344A1

WO2013053344A1 - Arrester device for a motor vehicle door unit

Info

Publication number: WO2013053344A1
Application number: PCT/DE2012/000966
Authority: WO
Inventors: Andreas Schmitz; Ömer INAN; Holger Schiffer; Thomas SCHÖNENBERG; Radek Mazal
Original assignee: Kiekert Aktiengesellschaft
Priority date: 2011-10-12
Filing date: 2012-10-04
Publication date: 2013-04-18
Also published as: EP2766546B1; DE202011106703U1; EP2766546A1

Abstract

The invention relates to an arrester device for a motor vehicle door unit, with a chamber (3) which is filled with a hydraulic medium, furthermore with at least one displacer (4) which is connected to a door wing (2), and with at least one valve (5), wherein the outlet cross section (A) of the valve (5) is dimensioned to be larger than the inlet cross section (E) thereof, and the valve (5) and the displacer (4) are each arranged eccentrically in comparison to a common axis of rotation (6) and individually or jointly fill a radial cross section (R) of the chamber (3) such that rotations of the valve (5) and/or of the displacer (4) in relation to the chamber (3) correspond to a cross-sectional jump in the flow of the hydraulic medium through the open valve (5).

Description

Locking device for a motor vehicle door unit

Description:

The invention relates to a locking device for a motor vehicle door unit, with a filled with a hydraulic medium chamber, further comprising at least one connected to a door displacement body, and at least one valve with associated valve body, wherein the outlet cross-section of the valve sized larger than its inlet cross-section is.

A locking device of the construction described above, including associated motor vehicle door unit is described in the context of the generic DE 10 2009 059 882 A1. Such locking devices are used in the core to fix the door in a specific and predetermined pivot position relative to a motor vehicle body or at least bring about a damping of its movement. Such is particularly advantageous in the event that the door is used by an operator as a supplementary entry / exit help. Also, such locking devices have proven useful when collisions of the door should be prevented with adjacent vehicles.

In the generic state of the art according to DE 10 2009 059 882 A1, a motion transmission member is connected to the door leaf for this purpose. This has a drive shaft and a rack. Movements of the door leaf relative to the motor vehicle body now correspond to the toothed rod (linearly) being moved back and forth and consequently causing rotations of the drive shaft. Such rotations of the drive shaft cause a coincident with the drive shaft pump axis also rotates.

In fact, in this context, the displacement body as impeller and the chamber are designed as a pump chamber. The pump chamber has at least one outlet valve and an inlet valve, which are closed or opened from a predetermined pressure of the hydraulic medium in the pump chamber. As a result, the hydraulic medium can flow through an equalization chamber when the valve is open. This has basically proven, but is in need of improvement from the design effort. A comparable structurally complex solution is described in US Pat. No. 5,410,777. Here, a displacement body in the form of a wiper is realized. The filled with the hydraulic medium chamber has a plurality of openings. Depending on the movement of the wiper or the displacement body, the liquid can be discharged through individual connected to the openings discharges. A circulation of the hydraulic medium is possible. Although the known locking device can be integrated as it were in a door hinge of the door leaf. However, the detailed structure is filigree and multi-part and therefore expensive. This is where the invention starts. The invention is based on the technical problem of further developing such a locking device so that the structural complexity and consequently also the costs are reduced.

To solve this technical problem, a generic locking device in the invention is characterized in that the at least one valve and the at least one displacement body each eccentric in comparison to a common axis of rotation

are arranged. In addition, the valve and the displacer body individually or collectively fill a radial cross-section of the chamber. In this way, rotations of the valve and / or of the displacement body respectively correspond to the chamber to a cross-sectional jump in the flow of the hydraulic medium through the open valve.

In the context of the invention, therefore, the displacement body connected to the door is first of all moved relative to the chamber, namely rotated about the axis of rotation. The displacement body is arranged eccentrically in comparison to the respective axis of rotation, usually connected eccentrically to this axis of rotation. This usually applies to the valve as well.

Due to the eccentricity of the displacement body and / or of the valve in the interior of the chamber, a rotational movement of the displacement body and / or of the valve initiated by the door causes the hydraulic medium to be displaced by the displacement body and / or the valve. This displacement process is continued until the pressure in the hydraulic medium has increased so that the valve can open or open. Because the valve and the displacement body fill individually or together from the radial cross-section of the chamber.

In this process, the at least one valve body is lifted off its associated seat. As a result, the hydraulic medium can flow over the inlet cross section to the valve body and then pass through the valve body and continue to flow through the outlet cross section. Since the outlet cross section of the valve is larger than its inlet cross section,

corresponds to this process to the fact that when the valve is open, the total of the locking device of the movement of the door leaf opposite force drops significantly. D. h., The opposite of the locking device of the movement of the door leaf force increases up to a so-called actuating force or breakout force, and then drop off when the valve is open to a significantly lower value. The difference between the larger outlet cross-section and the smaller inlet cross-section, the so-called "cross-sectional jump", thus also corresponds to a force difference of the opposing force or friction force built up by the locking device.

The overall design is such that when the door is stationary, the valve is closed and therefore an operator must apply to the door to reach the force or breakout force, so that the door can be easily moved back and forth when this force or breakout force. If the door leaf then comes to rest again, then ensures that closed (closed) valve that the door is held again. In this way, the locking device is controlled as it were by the movement of the door leaf. Is this at rest or the force or breakout force is not overcome, so the door can be minimal or virtually no move. If, on the other hand, the actuating force or breakaway force is overcome, then a more or less unhindered movement of the door leaf is possible because then the hydraulic medium can flow through the opened valve with little resistance or the displacement body and / or the valve within the chamber with respect to the hydraulic medium friction rotate.

In this way, a particularly compact and realized with a few components solution is provided. In addition, a freewheel can be realized in a simple manner, if, for example, at the beginning of the movement of the door leaf to the chamber, a bypass is available. D. h., This bypass is effective when the door, for example, performs pivotal movements between the vehicle body in the range of 0 ° to 10 ° or 20 °. Only beyond pivoting movements cause the bypass is closed and therefore the force or breakout force must be overcome so that the door can be moved. All this can be achieved in a structurally simple manner, with additional components such as a rack, adjusting elements, etc. are unnecessary. Through this recourse to only a few design elements and in particular the renunciation of external transmission elements, there are also acoustic advantages. Because any friction movements of these transmission elements with a coherent sound generation are not observed. Here are the main benefits.

As already explained, the locking device can be advantageously integrated into a hinge or door hinge for the door leaf. In this case, the axis of rotation coincides with a hinge axis of the door leaf. As already explained, the displacement body and / or the valve are advantageously connected to the axis of rotation. Incidentally, it has proven useful if several valves are provided. As a rule, at least one clockwise valve body and a counterclockwise valve body are provided. The clockwise valve is opened,

when the rotation axis or the door leaf make a clockwise rotation. On the other hand, the counterclockwise valve is used when the rotation axis or the door leaves complete a counterclockwise movement. In this respect, in both directions of actuation of the door leaf with a consistent operation expected. As soon as the door comes to rest, it is more or less fixed by means of the locking device, because then the associated valve (clockwise valve or counterclockwise valve) is closed. Only when starting from this rest position of the door leaf with the sufficient force (force or Losb rech force) is applied, opens the associated valve and allows only slightly damped movement of the door leaf.

To achieve this in detail, a plurality of valve bodies arranged one above the other in the axial direction can be realized. The valve body may be formed trapezoidal in cross-section. In this connection one observes the inlet cross section at the front trapezoidal flank and the outlet cross section at the rear trapezoidal flank. In order to design the inlet cross-section smaller than the outlet cross-section in this case, the front trapezoidal edge has a lower inclination than the trapezoidal trailing edge.

According to the invention, conventional valves can also be used successfully.

According to an alternative or simultaneously realizable variant, it is provided that the valve body is formed arcuate in plan view. The arc shape is adapted to the rotational movement of the valve about the axis of rotation. D. h., The arc of the valve body corresponds to the radial distance of the valve body from the axis of rotation.

A further advantageous solution is characterized in that the valve body has a head-side pin closure. This pin lock ensures that an opening in a valve chamber is closed in the closed state and released in the open state. Between the pin closure and the opening, a gap is observed. This generally applies to the valve body and its associated seat or valve seat. The gap now gives the already mentioned force or breakout force. As soon as the pressure built up in the gap with the aid of the hydraulic medium is sufficient to lift the valve body from its seat or valve seat against the force of an associated valve spring, the relevant force or breakaway force is achieved. Of course, this also depends on the viscosity of the hydraulic medium. Alternatively or additionally, the valve body may also be assigned at least one valve seal. The valve seal builds up corresponding frictional forces and, alternatively or in addition to the gap dimension and the viscosity of the hydraulic medium for the specification of the actuating force or breakout force. D. h., It can be used depending on the viscosity of the hydraulic medium with a predetermined gap and / or a correspondingly formed valve seal and thus constructed frictional forces to ultimately set the desired force respectively breakout force of the locking device total. As a result, variations can be realized in a wide range.

As a further variant plays in this context, of course, the valve body associated with at least one valve spring a role. Because the

Valve spring ensures that the valve body is pressed against its seat or valve seat, and its built-up counterforce must be overcome to open the valve. In addition to the viscosity of the hydraulic medium and / or the already mentioned gap and / or any frictional forces built up by the optional valve seal, the spring constant of the valve spring also plays a role when it comes to the design and dimensioning of the actuating force or breakout force.

As a rule, two diametrically opposite valve bodies or valves are provided with respect to the axis of rotation. The two valve bodies can be connected to each other and stored together on the axis of rotation. In addition, it has proven useful if the chamber and optionally the displacement body and optionally the valve or the valve body are each formed rotationally symmetrical. This allows a particularly simple adaptation to the preferred installation situation in or on a hinge for the door leaf.

As a result, a locking device for a motor vehicle door unit is made available, which is constructionally particularly simple. In addition, there are various options available to adjust the desired force or breakout force within wide limits. As a result, different weights of the door leaf, conditions of use, etc. can be mastered easily and appropriate adjustments can be made. In addition, the fixed actuator according to the invention usually dispenses with external motion transmission elements, consequently operates acoustically very quiet and can be realized inexpensively.

All the more so, as the locking device can be integrated advantageously in a hinge for a door leaf or can be attached to such a hinge. Especially in such an installation situation additional motion transmission elements or elements are disadvantageous under certain circumstances, because their noise is transmitted by structure-borne noise to the associated motor vehicle body.

Alternatively, the locking device can also be mounted in a door wing. In addition, a significant force difference between the one hand of a locking force or the actuating force or breakout force and on the other hand the force on actuation of the door leaf is observed by the jump in cross section between the inlet cross section and outlet cross section at the valve. This allows the operation to be given a particularly intuitive and comprehensible. Here are the main benefits.

In the following the invention will be explained in more detail with reference to a drawing showing only one exemplary embodiment; show it:

Fig. 1, the locking device according to the invention in a principal

Installation situation in a motor vehicle door unit,

2 shows a first embodiment of the locking device,

3 shows a second variant of the locking device,

4 shows a further third embodiment variant,

Fig. 5 shows a fourth example and Fig. 6 shows the principal force curve over the associated travel on

Door.

In Fig. 1 a motor vehicle door unit is shown, which basically consists of a rotatably hinged to a motor vehicle body 1 door 2 and an associated locking device. The locking device has a filled with a hydraulic medium chamber 3. Within the chamber 3, a designed as a displacement body 4 valve 4 can be moved. In contrast, a valve 5 may be designed to be stationary, as it applies to the embodiment variants of FIGS. 2, 3 and 5. In contrast, the embodiment of FIG. 4 is based on a movable displacement body 4 and a movable valve 5 back. In fact, in this embodiment, the displacement body 4 and the valve 5 define a total of rotatable assembly 4, 5, with respect to a rotation axis. 6

In the exemplary embodiment, the axis of rotation 6 at the same time represents a hinge axis 6 of the door leaf 2 relative to the motor vehicle body 1. Actually, the door leaf 2 is pivotably connected to the vehicle body 1 in question, namely about the said hinge axis or axis of rotation 6. As a result, the door leaf 2 can assume actuating movements s perform. For this purpose, a force F is required (see Fig. 6). At the axis of rotation or hinge axis 6 in the embodiment of the displacement body 4 in the

Variant according to FIGS. 2, 3 and 5 connected. In the context of the embodiment according to FIG. 4, both the displacement body 4 and the valve 5, d. H. the assembly 4, 5, connected to the axis of rotation 6.

The valve 5 has a valve body 7 and a valve spring 8 acting on the valve body 7 in the direction of its valve seat 9. In addition, an inlet cross-section E and an outlet cross-section A of the valve 5 are observed. In the exemplary embodiments illustrated, the inlet cross-section E is smaller overall than the outlet cross-section A. dimensioned or the Auslaßqueschnitt A greater than the inlet cross-section E executed. In fact, size ratios E: A of about 1: 1, 5 and more are observed.

The valve body 7 and the entire valve 5 and the displacement body 4 are each arranged eccentrically in comparison to the common axis of rotation 6. In addition, the valve 5 and the displacer 4 fill a radial cross-section R of the chamber 3, individually or in common. In this way, rotations of the valve body 7 respectively of the entire valve 5 and / or of the displacement body 4 with respect to the chamber 3 correspond to a jump in cross-section during the flow of the hydraulic medium through the opened valve 5.

As already explained, in the three exemplary embodiments according to FIGS. 2, 3 and 5, the valve 5 is designed to be stationary, whereas the displacement body 4 is connected to the rotation axis or hinge axis 6 and rotates therewith. As soon as the door leaf 2 is acted upon in this respective embodiment variant and pivoted relative to the motor vehicle body 1,

leads this rotation to the fact that then the displacement body 4 is rotated within the chamber 5 about the rotation axis 6.

As a result, the hydraulic medium is displaced and acted upon in Fig. 2 indicated by an arrow movements the hydraulic medium. This hydraulic medium can initially dodge in this process in a bypass 10 to the chamber 3. D. h., Starting in, for example, the closed position of the door leaf 2 relative to the vehicle body 1, a kind of "freewheel" is first observed because of the displacement of the body displaced hydraulic fluid at the beginning of the clockwise movement in the bypass 10 evades and can evade.

A continuous movement of the displacement body 4 in a clockwise direction now causes the hydraulic medium is more and more acted upon by the displacement body 4 until the associated valve 5 opens. This situation is shown in FIG. 2. The fundamental force curve in this process is shown in FIG. 6. It can be seen that the displacement body 4 must generate a force FST or breakaway force until it is sufficient to lift the valve body 7 from its valve seat 9 can. Once this is the case, the valve 5 is open. Then, the hydraulic medium can flow through the valve 5, starting from the smaller inlet cross-section E passing into the larger outlet cross-section A. As a result, the total of the illustrated locking device the door 2 opposite force decreases by the amount AF corresponding to FIG the force AF must be reduced during the movement

of the door leaf 2 are maintained. If the door leaf 2 comes to a standstill, the valve 5 closes (again) and the door leaf 2 is fixed again with the adjusting force FST. In any case, rotations of the displacement body 4 correspond in the embodiments according to FIGS. 2, 3 and 5 to the fact that the valve 5 opens after exceeding the force FST. This results in a flow of the hydraulic medium displaced by the displacement body 4 through the valve 5. During the flow of the hydraulic medium through the opened valve, the already discussed cross-sectional jump is observed from the inlet cross-section E to the outlet cross-section A. This corresponds substantially to the already described force jump or the amount AF.

Alternatively or in addition to the rotation of the displacement body 4, a rotation of the valve 5 or the valve body 7 is possible and is followed in the variant according to the embodiment of FIG. Here, as already explained, the displacement body 4 and the valve 5 form a structural unit 4, 5. This structural unit 4, 5 is connected to the axis of rotation 6. As soon as the rotation axis 6 rotates as a result of a movement of the door leaf 2 relative to the motor vehicle body 1, the assembly 4, 5 or the valve 5 also comes to rotate within the chamber 3. As a result, the valve body 7 is lifted off the valve seat 9 and can consequently the hydraulic medium through the valve 5 - flow largely unhindered.

It can be seen that, as a rule, a plurality of valve bodies 7 and consequently also a plurality of valves 5 are provided. In general, at least one

Clockwise valve 5a and a respective clockwise valve body 7a and a counterclockwise valve 5b and a counterclockwise valve body 7b provided. This can be seen in the embodiments according to FIGS. 2, 3 and 4.

In addition, a plurality of axially superimposed valve body 7 can be realized, as shown in the embodiment of FIG. 5. In this case, the valve body 7 has a trapezoidal cross section. The inlet cross-section E is formed at an associated front trapezoidal edge, whereas the rear trapezoidal edge provides for the dimensioning of the outlet cross-section A. Due to the cross-sectional ratios already described, the front trapezoidal flank is inclined significantly less than the trapezoidal trailing flank, so that comparable cross-sectional conditions as already explained adjust with a ratio of E: A of approximately 1: 1, 5 and more.

In the context of the variant according to FIG. 3, the valve body 7 is formed arcuately in plan view. In fact, two valve bodies 7 can be found in this context. The arc of the valve body 7 is matched with respect to the associated radius to the radial distance of the valve body 7 in comparison to the axis of rotation 6. In addition, the valve body 7 has a head-side pin closure 11. The pin closure 11 engages in an opening 12 in the region of the valve seat 9. With the help of the opening 12 and the pin closure 11, a valve chamber 13 can be opened and closed.

In the embodiment of FIG. 5, the valve body 7 or the plurality of axially superimposed valve body 7 in the axial direction X with the help the valve spring 8 acted upon. It can also be seen here that in the axial direction X, the valve bodies 7 and the associated displacement bodies 4 are arranged in alternating sequence with one another in the chamber 3. The chamber 3 is rotationally symmetrical. This also applies to the displacement body 4 in the context of the variant according to FIGS. 2 and 3. In addition, the valve 5 is designed in the context of the examples of FIGS. 2 and 3 rotationally symmetrical.

The embodiment according to FIG. 4 is furthermore equipped with at least one valve seal 14 on the valve body 7. The valve seal 14, in conjunction with the valve spring 8, generates frictional forces which must be overcome by an operator with the aid of the door leaf 2 and correspond overall to the actuating force FST. The viscosity of the hydraulic medium also contributes to this. As a rule, one works with a low-viscosity hydraulic medium with one or more valve seals 14. In contrast, with a high-viscosity hydraulic medium such valve seals 14 are usually unnecessary. In this case, a gap remaining between the valve body 7 and its seat 9 gives corresponding forces which have to be overcome or, in the end, contribute to the actuating force FST or pretend to be the same. D. h., Depending on the viscosity of the hydraulic medium and predetermined gap between the valve body 7 and its valve seat. 9

or also the valve seal 14 and its built-up friction forces the force to be overcome

FST accordingly.

Claims

Protection claims:

1. locking device for a motor vehicle door unit, with a filled with a hydraulic medium chamber (3), further comprising at least one of a door (2) connected displacement body (4), and with at least one valve (5), wherein the outlet cross-section (A ) of the valve (5) is greater than its inlet cross-section (E), characterized in that the valve (5) and the displacement body (4) are each arranged eccentrically in comparison to a common axis of rotation (6) and individually or jointly a radial cross-section ( R) of the chamber (3) so that rotations of the valve (5) and / or the displacement body (4) relative to the chamber (3) correspond to a jump in cross-section in the flow of the hydraulic medium through the opened valve (5).

2. Locking device according to claim 1, characterized in that the displacement body (4) and / or the valve (5) to the rotation axis (6) are connected.

3. Locking device according to claim 1 or 2, characterized in that the axis of rotation (6) with a hinge axis (6) of the door leaf (2) coincides.

4. Locking device according to one of claims 1 to 3, characterized in that a plurality of valves (5) are provided, namely at least a clockwise valve (5a) and a counterclockwise valve (5b).

5. Locking device according to one of claims 1 to 4, characterized in that a plurality in the axial direction (A) superimposed valve body (7) are realized.

6. Locking device according to claim 5, characterized in that the valve body (7) is trapezoidal in cross section with the inlet cross-section (E) on the front trapezoidal flank and the outlet cross-section (A) formed on the rear trapezoidal flank.

7. Locking device according to claim 5 or 6, characterized in that the valve body (7) is arcuate.

8. Locking device according to one of claims 5 to 7, characterized in that the valve body (7) has a head-side pin closure (1 1) which closes an opening (12) in a valve chamber (13) in the closed state and releases in the open state ,

9. Locking device according to one of claims 5 to 8, characterized in that two valve bodies (7) are provided.

10. Locking device according to one of claims 5 to 9, characterized in that the valve body (7) is associated with at least one valve spring (8).

1 1. Locking device according to claim 10, characterized in that the valve spring (8) the valve body (7) applied substantially tangentially and / or axially.

12. Locking device according to one of claims 1 to 1 1, characterized in that the chamber (3), optionally the displacement body (4) and optionally the valve (5) are each rotationally symmetrical.

13. Locking device according to one of claims 5 to 12, characterized in that the valve body (7) is associated with at least one valve seal (14).

14. Locking device according to one of claims 5 to 13, characterized in that a gap between the valve body (7) and its valve seat (9) and / or by the valve seal (14) constructed frictional forces specify a force (FST).

15. Locking device according to claim 14, characterized in that, depending on the viscosity of the hydraulic medium with predetermined gap and / or a valve seal (14) predetermined friction is worked.