WO2015161957A1

WO2015161957A1 - Spring drive for a closure element of a motor vehicle

Info

Publication number: WO2015161957A1
Application number: PCT/EP2015/055209
Authority: WO
Inventors: Harald Krüger; Sebastian Heinze
Original assignee: Brose Fahrzeugteile Gmbh & Co. Kg, Hallstadt
Priority date: 2014-04-22
Filing date: 2015-03-12
Publication date: 2015-10-29
Also published as: KR20160146883A; CN106489041B; CN106489041A; JP6552522B2; JP2017521608A; DE102014105624A1; KR102329145B1

Abstract

The invention relates to a spring drive for a closure element (2) of a motor vehicle, comprising a spring arrangement (3) and comprising a first drive connection (4) and a second drive connection (5) which are adjustable relative to one another along a geometric longitudinal axis (6), wherein the two drive connections (4, 5) are spring-loaded apart from one another by the spring arrangement (3) in an extended state, and wherein the drive connections (4, 5) are adjustable toward one another counter to the spring-loading in a retracted state. It is proposed that the spring arrangement (3) be configured as a tension spring arrangement, whose tensile force runs along the geometric longitudinal axis (6).

Description

Spring drive for a closure element of a motor vehicle

The invention relates to a spring drive for a closure element of a motor vehicle according to the preamble of claim 1 and a drive arrangement for a closure element of a motor vehicle according to claim 12.

The term "closure element" is comprehensively understood in the present case, including tailgates, trunk lids, hoods, side doors, sliding doors, lifting roofs, sash windows, etc.

First and foremost, however, the spring drive in question finds application in tailgates and rear lids in motor vehicles. He regularly serves a manual or motorized adjustment of the closure element against its weight.

The known spring drive (DE 20 2004 015 535 U1), from which the invention proceeds, in a variant, a helical compression spring for biasing the spring drive in an extended state. The spring drive has two drive connections, which are adjustable relative to each other along a geometric longitudinal axis of the spring drive. The two drive terminals of the spring drive are pressed apart by means of the pressure force of the helical compression spring in the extended state.

Although the known spring drive shows a comparatively simple structure. However, the installation of such a spring drive is associated with considerable risks. This is because the helical compression spring must be preloaded during assembly. In the event of improper installation, the helical compression spring may suddenly relax, which, in view of the high driving force required for tailgates, is accompanied by a considerable risk of injury. The bias of the helical compression spring can lead to an uncontrolled relaxation of the helical compression spring in the event of a crash.

In another variant, DE 20 2004 015 535 U1 shows the use of a helical tension spring, whereby, however, the spring drive is spring-biased into the retracted state. Such a spring drive is only possible with very special applicable to the essential constructional conditions. A similar spring drive with a coil spring is shown in EP 2 664 816 A2.

The invention is based on the problem to design the known spring drive such and further, that a large spring preload in the extended state with increased assembly and reliability is feasible.

The above problem is solved in a spring drive according to the preamble of claim 1 by the features of the characterizing part of claim 1.

Essential is the fundamental consideration that the use of a designed as Zugfederanordnung spring arrangement leads to a particularly high mounting and reliability. The reason for this is that even in the case of uncontrolled relaxation of the spring arrangement no expansion of the spring assembly takes place, which brings the above-mentioned risks. Rather, a relaxation of the spring assembly is connected only with a contraction, ie with a contraction of the spring assembly, which does not regularly lead to any kind of endangerment of the environment of the spring drive.

Specifically, it is proposed that the spring arrangement is designed as a tension spring arrangement whose traction extends along the geometric longitudinal axis of the spring drive. The term "along the geometric longitudinal axis" is to be understood here broadly and means that the direction of the tensile force extends next to the geometric longitudinal axis, but an exactly parallel extent is not mandatory here.

Particularly compact designed the proposed spring drive according to claim 2, by the spring assembly is positioned between the two drive terminals. For this purpose, it is necessary that the two drive connections are each coupled to the opposite spring connection of the spring arrangement. For this purpose, corresponding coupling elements can be felt through the spring arrangement (claim 5) or be guided past the outside of the spring arrangement (claim 6). In the particularly preferred embodiment according to claim 7, the spring arrangement is designed as a helical tension spring arrangement with at least one helical tension spring. The helical tension spring can provide a screw thread for an above coupling element in a preferred variant with their screw threads.

The proposed spring drive can also take on a damping function in addition to the generation of driving forces. Accordingly, it is proposed according to claim 9 that driving technology between the two drive terminals, a damping arrangement is provided. In a particularly preferred variant, this may be a fluid damping arrangement which can be connected in a particularly elegant manner to the above coupling elements.

Another additional function may be directed to an equipment of the spring drive with a further spring arrangement, which causes a further spring bias between the two drive connections in the retracted state or in the extended state. Such a further spring arrangement, for example, lead to an additional spring preload in the fully retracted state. This can be used, for example, to provide a particularly high spring support in the first section of an opening movement of the closure element. This can be advantageous depending on the kinematics and the weight distribution of the closure element.

According to a further teaching according to claim 12, which has independent significance, a drive arrangement for a closure element of a motor vehicle is claimed.

Essential to the further teaching is the idea to combine a motor drive with an above-described, according to the proposal spring drive. The spring drive preferably has the function of supporting the motor drive against the weight of the closure element. Thus, a power-reduced and as a result cost-effective design of the motor drive is possible without the assembly and reliability of the drive assembly is reduced overall. In the particularly preferred embodiment according to claim 13, the motor drive and the spring drive are arranged on opposite sides of the closure element associated Verschlusselementöfmung, whereby a symmetrical force can be achieved in the closure element. With a suitable design, this makes it possible to simplify the structural design of the closure element, without having to accept a return to the driving force of the spring drive distortion of the closure element in purchasing.

In a particularly preferred embodiment according to claim 15, the arrangement of the two drives is taken so symmetrical that the expansions of the respective drive movements during the adjustment of the Verschlussele- element are identical. In a visually particularly appealing and manufacturing technology advantageous variant, the housing of the two drives are provided with identical outer dimensions, so that the two drives are not distinguishable, at least at first glance.

In the following the invention will be explained in more detail with reference to a drawing illustrating only embodiments. In the drawing shows

1 shows the rear portion of a motor vehicle with a tailgate associated drive assembly having a motor drive and a proposed spring drive,

2 shows a proposed spring drive in a first embodiment a) in the retracted state and b) in the extended state, in each case in longitudinal section,

3 shows a proposed spring drive in a second embodiment a) in the retracted state and b) in the extended state, in each case in longitudinal section,

Fig. 4 shows a proposed spring drive in a third embodiment a) in the retracted state and b) in the extended state, each in longitudinal section and 5 shows a proposed spring drive in a further embodiment a) in the retracted state and b) in the extended state, in each case in longitudinal section.

The drive assembly 1 shown in Fig. 1 has a left illustrated motor drive la and a spring drive lb shown on the right. The drive assembly 1 is used for the motorized adjustment of a tailgate 2 of a motor vehicle. However, all other closure elements mentioned in the introductory part of the description are also advantageously applicable. All following versions of a tailgate apply equally to all other conceivable closure elements.

The spring drive lb here provides a support of the closure element 2 in terms of its weight. It is equipped with a spring arrangement 3, which provides the driving force for the spring drive 1b.

The spring drive 1b has a first drive connection 4 and a second drive connection 5, which are adjustable relative to one another along a geometric longitudinal axis 6 of the spring drive 1b and which are arranged here and preferably on the geometric longitudinal axis 6. This can be seen from a comparison of the various states of the spring drive 1b shown in FIGS. 2 to 5.

Fig. 1 shows that the two drive terminals 4, 5 must be pressed to support the closure element 2 against its weight in the extended state. Accordingly, it is proposed that the two drive terminals 4, 5 are spring-biased by the spring assembly 3 apart in the extended state. Thus, the spring drive lb supports a Öffhungsbewegung the tailgate 2 against its weight.

Conversely, the drive terminals 4, 5 in the context of a closing movement of the tailgate 2 against the spring bias of the spring assembly 3 toward each other in a retracted state adjustable, which is shown in Figs. 2 to 5 in view a). The spring bias in the extended state is indicated in the drawing by the reference numeral 7. 2 to 5 show that the spring bias is realized in the extended state by means of the spring assembly 3, characterized in that the spring assembly 3 is designed as a tension spring arrangement, the train spring force 8 along the geometric longitudinal axis 6 of the spring drive 1b. Accordingly, the views a) in FIGS. 2 to 5 are each the deflected position of the spring arrangement 3, while the views b) in FIGS. 2 to 5 are the relaxed or only slightly tensioned position of the spring arrangement 3 acts. A retraction of the spring drive 1b is thus accompanied by a tensioning of the spring arrangement 3. Here, it becomes clear that an unintentional and thus uncontrolled release of the spring arrangement 3 can possibly lead to an abrupt contraction of the spring arrangement 3, which does not increase the assembly and operational safety of the spring assembly 3 negatively influenced.

In terms of a particularly compact design, the spring assembly 3 is positioned between the two drive terminals 4, 5, as shown in Figs. 2 to 5. The spring arrangement 3 has two spring connections 9, 10 for discharging tension-spring force 8, which extends in the above sense along the geometric longitudinal axis 6 of the spring drive 1b.

In order to achieve that the spring drive 1b is spring-biased in its extended state, the first drive connection 4 is coupled to the spring connection 10 facing the second drive connection 5, while the second drive connection 5 is coupled to the spring connection 9 facing the first drive connection 4. The drive terminals 4, 5 are so to speak, cross-coupled with the spring terminals 9, 10, so that the tension spring arrangement shows the effect of a compression spring arrangement as a result.

A particularly robust arrangement results from the fact that two housing parts 11, 12 are provided which are each coupled to one of the drive connections 4, 5 and which telescope into one another. The housing parts 11, 12 are here and preferably designed like a tube and aligned along the geometric longitudinal axis 6 of the spring drive 1b. For its drive-engineering coupling with the spring arrangement 3, the first drive connection 4 is assigned a first coupling element 13. Accordingly, the second drive connection 5 is assigned to its drive-technical coupling with the spring arrangement 3, a second coupling element 14. The coupling elements 13, 14 serve for the above cross-wise coupling of the drive connections 4, 5 with the spring connections 9, 10.

In all the illustrated embodiments, the two coupling elements 13, 14 run telescopically myander. As a result, an overall particularly compact design can be achieved.

For the design of the coupling elements 13, 14 numerous structural variants are conceivable. In principle, at least one of the coupling elements 13, 14 may be closed, in particular solid, as shown for example in FIG. 2. Fig. 3 shows, however, that the first coupling element 13 and / or the second coupling element 14 may be configured rohrformig or can. In a particularly preferred embodiment, there are both coupling elements 13, 14 designed rohrformig there. With the embodiment of both coupling elements 13, 14 as rohrformige coupling elements 13, 14 can be compared with an arrangement of FIG. 2, an additional space, namely an additional space within the coupling elements 13, 14, generate, for example, in the context of the realization of an integrated gas spring , Electric motor o. The like. May be advantageous. This is the case, in particular, when the first coupling element 13 is open toward the interior of the second coupling element 14, as can likewise be seen from the illustration in FIG. 3. Such a gas pressure damper may be configured in the manner of a fluid gas pressure damper which will be explained later.

It can be seen from the illustrations according to FIGS. 2 to 5 that the coupling element 13 assigned to the first drive connection 4 is felt through the spring assembly 3. The coupling element 9 is configured here and preferably in the manner of a piston rod. Further preferably, it is provided that designed as a piston rod coupling element 13 is designed as mentioned above rohrformig. As a result of the fact that the tubular coupling element 13 is designed to be open to the interior of the other coupling element 14, additional installation space results, as likewise mentioned above, which is suitable for set functions, in particular for the integration of a gas spring can be used.

It can be further seen from the illustrations according to FIGS. 2 to 5 that the coupling element 14 assigned to the second drive connection 5 is guided past the spring arrangement 3 on the outside. For this purpose, the coupling element 14 is preferably designed tubular and forms in a particularly preferred embodiment, an above-mentioned housing part 12 of the spring drive 1b. In principle, it can also be provided that both coupling elements 13, 14 are passed through the spring assembly 3 or that both coupling elements 13, 14 are guided past the outside of the spring assembly 3. However, the embodiment in which a coupling element 13 is guided through the spring arrangement 3 and the other coupling element 14 is guided past the outside of the spring arrangement 3, however, leads to a structurally particularly simple structure.

For the structural design of the spring assembly 3, various advantageous variants are conceivable. For example, the spring arrangement 3 can be designed as a resilient band or the like. Here and preferably, however, the spring arrangement 3 is designed as a helical tension spring arrangement with at least one helical tension spring 15. The spring arrangement 3 can also have more than one helical tension spring 15, wherein the helical tension springs are then arranged parallel and / or in series. In addition to a high degree of robustness, the configuration of the spring arrangement 3 as a helical tension spring arrangement is advantageous, since the screw threads thereof can be used for the simple fastening of the coupling elements 13, 14. Specifically, it is proposed for this purpose that at least one coupling element 13, 14, here and preferably both coupling elements 13, 14, is bolted to the Schraubenzugfederanord- 3 or are, the screw turns of the Schraubenzugfederanordnung 3 at least one screw thread, here and preferably two screw thread 18, 19, provide for the screw. Accordingly, the coupling elements 13, 14 equipped with Gegenschraubgewinden 16, 17. If, as mentioned above, a coupling element 13 is passed through the spring assembly 3 and the other coupling element 14 outside of the Fe deranordnung 3 vorbeabführt, the proposed screw connection can be realized particularly easily by the Schraubenzugfederanordnung 3 forms a female screw 19 for one coupling element 13 and forms an outer screw thread 18 for the other coupling element 14.

A further increase in the compactness of the spring drive lb results from the fact that, as shown in FIGS. 2 to 5, the Schraubenzugfederanordnung 3 in the region of its two spring terminals 9, 10 different spring diameter d, D. In this case, it is preferable that the helical tension spring arrangement 3 has the largest spring diameter D on one of the two spring connections 9, 10, here and preferably on the spring connection 9 facing the first drive connection 4, and that the helical tension spring arrangement 3 otherwise has smaller spring diameters. This ensures in a compact design that the first coupling element 13 can be screwed by the spring assembly 3 through with the spring terminal 10 and the second coupling element 14 outside of the spring assembly 3 over with the spring terminal 9.

There are different variants for changing the spring diameter of the Schraubenzugfederanordnung 3 along the geometric longitudinal axis 6 of the spring drive lb conceivable. Here, and preferably, the spring diameter decreases continuously from the first spring connection 9 to the second spring connection 10. In the exemplary embodiment shown in FIG. 4, a damping arrangement 20 for the speed-dependent braking of relative movements between the drive connections 4, 5 is provided between the two drive connections 4, 5 in terms of drive technology. In a particularly preferred embodiment, the damping arrangement of the braking of relative movements with particularly high speed, in particular to avoid impact loads and noise when reaching one of the end positions of the closure element 2 is used.

For the embodiment of the damping arrangement 20, a number of advantageous variants are conceivable. In the exemplary embodiments illustrated in FIGS. 4 and 5, the damping arrangement 20 is designed as a fluid damping arrangement. staltet having a current in a fluid cylinder 21 displacer 22. In this case, a merely indicated flow passage S is provided between the fluid cylinder 21 and the displacer piston 22, through which a fluid located in the fluid cylinder 21 can flow from one side of the displacer piston 22 to the other side of the displacer piston 22. The damping effect is based on the throttle effect of the flow passage S back. The fluid may be a liquid or a gas mixture, in particular air.

The D ämpfungsanordnung 20 is integrated in the embodiments shown in FIGS. 4 and 5 in a particularly compact design in the spring drive lb. In detail, the displacer piston 22 is connected to the first coupling element 13, while the fluid cylinder 21 is provided by the second, tubular coupling element 14. In this case, the fluid cylinder 21 is open in the drawing down, so that only the part of the fluid cylinder 21 located above the displacer piston 22 is involved in the damping. In such an embodiment, the fluid is of course air.

The spring drive 1b has a further function, namely the function of limiting the relative movement of the two drive terminals 4, 5 to each other, here the limitation of the retraction movement. For this limitation, a stop assembly 23 with a stop 24 and a counter-stop 25 is provided. Upon reaching the retracted position (Fig. 4b, 5b), the stop 24 comes into engagement with the counter-stop 25 and blocks the further adjustment of the retraction movement. Particularly advantageous in terms of a compact design is the fact that the stop 24 is arranged on the displacer 22 and the counter-stop 25 on the second, the fluid cylinder 21 providing the coupling element 14. This dual use of components, namely on the one hand for the damping assembly 20 and on the other hand for the stop assembly 23 is advantageous from a cost point of view.

Finally, FIG. 5 shows an embodiment for a proposed spring drive 1b, to which a further function is assigned. For this purpose, the spring drive 1b associated with a further spring assembly 26 which causes a further spring bias between the two drive terminals 4, 5 in the retracted state or in the extended state. Here, the further spring preload Depending on the design tension before reaching the fully retracted or extended state act.

Here and preferably, it is such that the further spring assembly 26 exclusively in the retracted state, a further spring bias between the two drive terminals 4, 5 causes. Preferably, it is such that the further spring arrangement 26 is designed as a compression spring arrangement. The compression spring arrangement has here and preferably two compression springs 27, 28 which act exclusively in the retracted state between the two drive connections 4, 5. In detail, it is provided that the compression spring assembly 26 is relaxed in the extended state of the spring drive 1b and is compressed only when reaching the retracted state of the spring drive 1b. The compression springs 27, 28 are here and preferably helical compression springs 27, 28th

In principle, it may be provided that an unillustrated drive motor is integrated into the spring drive 1b, by means of which a relative movement of the two drive connections 4, 5 can be effected preferably in both adjustment directions. However, in the case of the exemplary embodiment shown, it is the case that, in addition to the spring drive 1b, a separate motor drive la is provided for the motorized adjustment of the closure element 2. The proposed spring drive 1b serves to support at least part of the motorized adjustment of the closure element 2. The combination of the motor drive 1a with the proposed spring drive 1b can lead to a particularly cost-effective drive arrangement 1 due to the reduced power requirements of the motor drive la.

1 shows that the closure element 2 serves to close a closure element opening 2a, the motor drive 1a and the spring drive 1b being arranged on opposite sides of the closure element opening 2a in the mounted state. This makes it possible to achieve a symmetrical force effect of the drive arrangement 1 on the closure element 2, so that a distortion of the closure element 2 is counteracted. The motor drive 1a and the spring drive 1b are each arranged with closed closure element 2 in a kind of gutter 29, so that the slim design of the two drives 1a, 1b is of particular importance. Accordingly, the motor drive la is preferably designed as a spindle drive and has a drive motor, not shown, and a drive motor downstream of the drive motor, not shown spindle spindle nut gearbox for generating drive movements. With regard to the basic construction on the designed as a spindle drive motor drive la reference may be made to DE 10 2008 062 391 A1, which goes back to the applicant and the content of which is made in full extent to the subject of the present application.

Due to the above-mentioned symmetry of the drive assembly 1, it is preferably such that the expansions of the drive movements of the motor drive la and the spring drive lb during the adjustment of the closure element 2 are identical. Further preferably, the drive movements of the two drives 1a, 1b during the adjustment of the closure element 2 are aligned parallel to each other. Interestingly, however, is the fact that the driving forces of the two drives 1a, 1b are preferably different. In particular, the motor drive la preferably acts bidirectionally, while the spring drive lb acts only in the extension direction.

An optically particularly attractive embodiment results from the fact that the motor drive la and the spring drive 1b each have a housing with two housing parts 11, 12, which run telescopically into one another, wherein the housing have substantially identical outer dimensions. Basically, a usability of one and the same housing part 11, 12 for both drives la, lb conceivable, which reduces how the manufacturing costs of the two drives 1a, 1b.

Finally, it should be pointed out that the proposed spring drive 1b can also be used without a motor drive 1a, ie as a passive support drive. Finally, it is conceivable that two proposed spring drives 1 b can be provided, which, as shown in principle in FIG. 1, are arranged in the mounted state on opposite sides of the closure element opening 2 a.

Claims

claims

A spring drive for a closure element (2) of a motor vehicle, comprising a spring arrangement (3) and a first drive connection (4) and a second drive connection (5), which are adjustable relative to each other along a geometric longitudinal axis (6), the two Drive terminals (4, 5) are spring-biased apart by the spring arrangement (3) in an extended state, and wherein the drive terminals (4, 5) against the spring bias towards each other in a retracted state are adjustable, characterized

that the spring arrangement (3) is designed as a tension spring arrangement, the tensile force of which runs along the geometric longitudinal axis (6).

2. Spring drive according to claim 1, characterized in that the spring arrangement (3) is positioned between the two drive connections (4, 5) and has two spring connections (9, 10) for the withdrawal of tension spring force, that the first drive connection (4) is coupled to the spring connection (10) facing the second drive connection (5), and that the second drive connection (5) is coupled to the spring connection (9) facing the first drive connection (4).

3. spring drive according to claim 1 or 2, characterized in that two housing parts (11, 12) are provided which are each coupled to one of the drive terminals (4, 5) and telescope into one another.

4. Spring drive according to one of the preceding claims, characterized in that the first drive connection (4) for its drive-engineering coupling with the spring arrangement (3) is associated with a first coupling element (13) and that the second drive connection (5) to its drive technology coupling with the spring arrangement (3) is associated with a second coupling element (14), preferably, that the two coupling elements (13, 14) telescope into one another, more preferably that the first coupling element (13) and / or the second coupling element (14) designed tubular is or are, more preferably, that the first coupling element (13) to the interior of the second coupling element (14) is open.

5. spring drive according to claim 4, characterized in that at least one coupling element (13) by the spring assembly (3) is hmdurchgeführt or preferably, that for this purpose at least one coupling element (13) is designed in the manner of a piston rod or are, preferably in that the coupling element (13) designed in the manner of a piston rod is of tubular design.

6. Spring drive according to claim 4 or 5, characterized in that at least one coupling element (14) is guided past the outside of the spring arrangement (3) or are, preferably, that for this purpose at least one coupling element (14) is designed rohrformig or are further preferably a housing part (12) of the spring drive (lb) forms.

7. spring drive according to one of the preceding claims, characterized in that the spring arrangement (3) is designed as Schraubenzugfederanordnung with at least one Schraubenzugfeder (15), preferably, that at least one coupling element (13, 14) with the Schraubenzugfederanordnung (3) is screwed or and that the screw threads of the helical tension spring arrangement (3) provide at least one screw thread (18, 19) for the screw connection, preferably in that the helical tension spring arrangement (3) forms an internal screw thread (19) for one of the coupling elements (13) for the other of the coupling elements (14) forms an external screw thread (18).

8. Spring drive according to claim 7, characterized in that the Schraubenzugfederanordnung (3) in the region of its two spring terminals (9, 10) has different spring diameters (d, D).

9. spring drive according to one of the preceding claims, characterized in that drive technology between the two drive terminals (4, 5) a damping arrangement (20) for speed-dependent braking of relative movements between the drive terminals (4, 5) is provided, preferably that the Dämpfungsanordnimg ( 20) is designed as a fluid damping arrangement with a displacement piston (22) running in a fluid cylinder (21), preferably in that one of the drive connections (4, S) with the fluid cylinder (21) and the other of the drive connections (4, 5 ) are coupled to the displacer (22).

10. Spring drive according to one of the preceding claims, characterized in that a stop arrangement (23) for limiting the relative movement of the two drive connections (4, 5) is provided to each other.

11. Spring drive according to one of the preceding claims, characterized in that a further spring arrangement (26) is provided and that the further spring arrangement (26), in particular exclusively, in the retracted state or in the extended state, a further spring bias between the two drive terminals (4, 5), preferably, that the further spring arrangement (26) is designed as a compression spring arrangement.

12. Drive arrangement for a closure element (2) of a motor vehicle with a motor drive (1 a) for the motorized adjustment of the Verschlussele- element (2) and with a spring drive (1 b) according to one of the preceding claims to support at least a portion of the motorized adjustment of the closure element (2).

13. Drive arrangement according to claim 12, characterized in that the closure element (2) for closing a closure element opening (2a) and that in the assembled state of the motor drive (1a) and the spring drive (1b) on opposite sides of the closure element opening (2a) are.

14. Drive arrangement according to claim 12 or 13, characterized in that the motor drive (1a) is designed as a spindle drive and has a drive motor and a drive motor downstream of the drive spindle spindle nut gearbox for generating drive movements.

15. Drive arrangement according to one of claims 12 to 14, characterized in that the expansions of the drive movements of the motor drive (1a) and the spring drive (1b) during the adjustment of the closure element (2) are identical, preferably, that the drive movements of the motor drive (1a) and the spring drive (1b) during the adjustment of the closure element (2) are aligned parallel to each other.