DE10141628A1 - Lock system for a hinged vehicle engine compartment hood has one section attached to the chassis, with a damper to increase passive security - Google Patents

Abstract

The lock structure for a swing flap, and especially the hood (2) for a vehicle engine compartment, is a lock or hinge with one section secured to the chassis (K) and another section to release the hood to swing open. The first section has a spring damper (14) or a body with plastic distortion, for increased passive security, which can be deflected to release the hood. The multi-linkage hinge (1) has at least two links (8,10) which connect the hood to the chassis, where one link (10) has a length adjustment for deflection against a holding spring (13).

Description

The invention relates to a fitting arrangement for a hinged flap, in particular bonnet a motor vehicle, in particular in the form of a lock ses or a hinge, with a first, on the Fastenable body part and with a second fitting part assigned to the flap, which Parts for opening the flap shift relative to each other are cash.

To increase the passive safety of a person Motor vehicle has already been proposed Trigger-controlled bonnet in a gap spacer catapult lung. This distance position allows then a delayed relocation in the event of an accident the flap against a damping element.

The invention has for its object a fitting arrangement of the type in question in such a way that with the extensive inclusion of the hardware components the passive safety of the motor vehicle is increased.

This task is initially and essentially at a fitting arrangement with the features of the claim 1 solved, it being based on the fact that the Be impact arrangement assigned a damping element in such a way is that after overcoming one on the flap in Klap limit force acting in the closing direction due to a displacement of the damping element differs.

As a result of such a design is a generic appropriate fitting arrangement created, which the opening  the flap or the bonnet in a known per se Permitted way, with the existing ones Fitting components. These can be the lock or also be the hinge. It may even be possible of course, to include both. As an additional component this serves to increase passive safety Fitting arrangement associated damping element. This is designed to open and close the The hood or flap are made in the usual manner can without affecting the damping element exercises. Only after overcoming a limit force which can be around 1000 N, the motor can hood or the flap against the force of the Damping element shift to, for example a pedestrian head impact energy absorbing on the Pedestrians to reduce possible injuries tions. For example, it is possible to have one additional adjustment range in the hinge area of 55 mm to realize. The additional adjustment path in the Lock area can be approx. 25 mm. An advantageous te further training is that the damping element ment is a feather. So it's a cost low-priced component. Then is a favorable ge possible to accommodate the spring. Alterna However, the damping element can also be plastic be deformable deformation body. The deformation also occurs when the corresponding is exceeded Limit force. The plastically deformable deformation For example, bodies can be saved as art to save costs Create a molded part. Then the inventor opens design according to the possibility that the Fitting arrangement is a multi-joint hinge, with at least two connect the body to the flap the handlebars, being a handlebar against the force of one Retaining spring for evasion is variable in length. This  Measure is taken when different Handlebar lengths, for example with a four-bar share nier available. Then by the spring at one Alternative shifting of the bonnet one shift same possible against the damping element, the Retaining spring the evasive movement of her assigned Pivot point allowed. This can be achieved that the position of the pivot changes to avoid it is cash. The fact that the pivot pin can be moved against spring force in one Slotted hole. The slot is in one Handlebar while the pivot pin on the corresponding Handlebar sits. The slot then takes the retaining spring on, which in turn on the pivot in question acts. Another possibility is that the Hinge pin can be moved relative to the holding bracket is. Is it the flap-side hold console, so in the event of an accident with giving way the bonnet by moving it back Hinge pin opposite the bracket within the Elongated hole moves. To the inventive idea at raum saving, inexpensive to build realize, it is provided that the fitting arrangement a multi-joint, in particular a four-joint hinge is, with at least two the body with the flap connecting links, the damping element is a torsion link associated with a joint. Also last teres is designed to open the flap or the hood can be made in known Marnier can, and that assigned to the hood or flap hardware components. With the bonnet closed or Flap can also continue in the closing direction relocate against the strength of one Joint associated torsion link. The latter leaves create space-saving and the fitting arrangement  assign. Here too it can be realized that only after The motor overcomes a certain limit force hood or the flap against the force of the Torsion shifted. So it works accordingly supported bonnet or flap for a pedestrian Head impact energy absorbing. Technically favorable it turns out that the torsion link one is firmly connected to a first joint element and on the other hand forms an attack against wel in the closed position of the flap jump of the fixed with a second joint element where the pivot occurs. Stop and lead are positioned so that in the closed position Acting on the flap loads the torsion link will, while opening the flap the projection away from the stop and therefore not the opening ver storage impaired. The torsion link can the rest can be designed differently visibly the choice of materials. It turned out to be particularly favorable it that the torsion member is a spring element or is an elastomer body, in particular a rubber body, which, in particular, also enables length deviation.

This length deviation occurs when the handlebars have different lengths. To despite this mate rial choice to form a stable stop is the water from one of the pivot pins, fixed with the Torsion link on the one hand connected sleeve tet. The torsion link itself can be made solid his. However, it is also a spoke-like structure of the torsion link possible. When loading the The torsion member will then train the spokes sprucht. There is also the possibility that the torsion element is prestressed in relation to the joint, in particular wings formed by the sleeve before fixed stops of the joint element. The  the corresponding preload is then already at the festival place the torsion member on the joint element generated. With the flap closed and the flap closed The same must first be the one from the previous one voltage resulting limit force exceeded the. This design is also space-saving and costly affordable to implement. To enable evasion the bonnet or flap may shift elastically evasive stop to fix the position the flap closed position.

In this way, the attack fulfills a double function by adding to its evasibility forms a hood stop. This is how it looks in detail from that the one fixed to the body or fixed associated with the flap associated hinge bracket strike against the restoring force of a print or sheet spring when a counterstop is applied with a limit force can be avoided. Regarding the joint Carrier can be a flap or check series-side holding bracket act. The flap side Holding bracket fulfills another task in that it forms the abutment for a damping element, which turned away from the holding bracket End supported on the body side. With the engine closed hood is the damping element, if it is a spring acts with a corresponding limit force biased. Only when this is exceeded can an inward shift of the hood against the Effect of the damping element take place. Another Version is characterized in that the damping element a compression spring or one on an angle lever attacking tension spring is. So that passive safety for example, only when driving or from a certain one Speed of the motor vehicle is activated is the evasibility by means of an electro in particular  mechanically displaceable blocking member lockable. As soon as the vehicle starts moving and one has reached certain speed, shifts the blocking member in a release position and leaves then dodging the hood. Looks in detail this so that the blocking member has the angle lever bewegungsblockiert. Then there is the possibility that a handlebar of one when a trigger is exceeded sekraft plastically deforming deformation body is formed. Then one with an elongated hole and retaining spring designed handlebars are eliminated. Another Embodiment is provided that the shortenable re handlebars when swiveling into the open position supported on a control curve and this when moving leaves in the alternative position. The control curve serves to support the bonnet when opening and closing the same. The control curve is such that it however, the shift to the alternative position allows.

To shorten the length of a handlebar at one The handlebar is to enable a multi-joint hinge telescopic. There is also the possibility that at least one of the articulation points or the holding bracket avoid the body or flap can. For this it is advisable that the hinge or the console carrying the lock can be avoided in Guided tours. To increase the value in use the invention proposes that the console dodge availability can be canceled by means of a blocking member, which especially when the vehicle is at a standstill Takes blocking position. Is the blocking member the Assigned hood lock, the blocking member occurs when opening the flap in the blocking position and leaves this with a delay after closing the flap.

That means that during the closing movement and the loading of the rotary latch taking place in the process  and striker no evasive movement take place can. The release of the Hood by the blocking member its blocking position lung leaves with a delay. A version can do this look that the blocking member is one of the catch or the pawl of a rotary latch lock ter swivel lever is. The aforementioned inventive concept can also be realized in such a way that Spring-loaded lock in the opening direction Is held in the closed position after opening itself in Opening direction shifted from a damper in the Open position is supported and after closing the Moved back to the held position, the damper is effective in the held position is going. Furthermore, the blocking member can use the two forces bridge initiation points in the damping element.

At the beginning it was executed that the damping element can be a deformation body. This can be According to the invention cheaply form as an angle. Again another way of exploring the idea of the invention realize, is that of the spin trapped striker on the force introduction supports the damping element. Different can such a design should be chosen that the Damping element is assigned to the striker. Beson cost-saving, it proves that the Damping element as a deflection, especially at an angle shape of the striker is designed. Then you can too such an arrangement must be made that the U-shaped striker opposite his console is. Finally, a variant of the Invention still characterized in that the pivot pin open to enable the alternative shift axially shifted from its storage position, being at the swivel shift between opening and  Closed position is axially tied and this fes selection can be canceled.

Several embodiments of the Invention explained with reference to the drawings. It shows:

Fig. 1, the first embodiment of a groove formed in the form of a hinge mounting arrangement for the bonnet of a motor vehicle, Subject Author fend the closed position of the bonnet,

Fig. 2 is a view like Fig. 1, wherein the hood in deviation energy under absorption of impact is lowered against the force of a Dämpfungsele ments,

Fig. 3 in veteinfachter representation, the second exporting approximate shape of a hinge in the closed position of the bonnet,

Fig. 4, the hood absorbie in the swung-in power impact energy,

Fig. 5 is a schematic representation of a third form of a bonnet from guide side blade niers, wherein a link is a plastically warp Barer deformation body and wherein the hood is in its closed position,

Fig. 6 shows the sequence view of FIG. 5, on the lowered position of the hood,

Fig. 7 shows a schematic representation of a fourth form of a bonnet from guide side blade niers with the closed position more engaging bonnet,

Fig. 8 shows the sequence diagram of FIG. 7 wherein the hood is in the lowered position befin det,

Fig. 9 shows a schematic representation of a fifth form of a bonnet from guide niers side blade,

Fig. 10 shows the sequence view of FIG. 9 taken in from the closed position at the lowered Stoßbeaufschla supply hood,

Fig. 11 a schematic representation of a sixth embodiment of the hood supplied arrange th hinge, wherein the hinge is guided in the support bracket deflectable in karosseriesei term guides, on the closed position of the bonnet,

Fig. 12 shows the seventh embodiment in a schematic illustration, wherein the mounting arrangement in the form is formed of a hood associated with the lock in the active Stel lung gebrachtem blocking member,

Fig. 13 is a view similar to FIG. 12, namely when in the release position gebrachtem blocking member and of the Haubenabsenkbewegung mitverla gertem lock,

Fig. 14, the eighth embodiment in schematic illustration, wherein the hood is in its closed position,

Fig. 15 is a view similar to FIG. 14, namely at in-gap open position bonnet,

Figure 16 is a schematic illustration of the ninth embodiment of a mounting arrangement in which the lock and thus the engine hood is located. In the closed position,

Fig. 17 a of Fig. 16 similar representation, namely at lacked in the gap opening position ter bonnet,

Fig. 18 voltage, the tenth embodiment of a Beschlaganord, wherein the gefange of the rotary latch ne striker supported on the force introduction point of a damping element,

Fig. 19 shows the sequence view of FIG. 18, namely at the lowered hood along with a deformation of the damping element,

Fig. 20 shows a different design of a Schließbü gels, wherein the damping element is designed as an angular deflection of the striker, on the approximate shape eleventh exporting,

Fig. 21 is a view similar to FIG. 20, namely at ausgebogenem be accompanied with a lowering of the Motorhau striker,

Fig. 22 proper, the twelfth embodiment of a Beschlagan, wherein the damping element is also associated with the captured by the rotary latch striker, said motor hood which occupies the closed position,

Fig. 23, the illustration as FIG. 22, namely at a reduced bonnet under absorption of the impact energy acting on it,

Fig. 24, the thirteenth embodiment, wherein the U-shape is designed striker cushioned relative to its console, on the spring-loaded out position,

Fig. 25 is the same view as FIG. 24, namely at eingefedertem bracket shooting, which corresponds to the eingefe derten position of an engine hood,

26 shows the fourteenth embodiment of a designed in the form of a hinge, fen. Fitting assembly schematically illustrated with the Ge closed position more engaging bonnet secured against axial displacement in Gelenkzap,

Fig. 27 a of Fig. 26 similar representation, namely in the lowered hood and along with the lowering movement Shared pivot pin,

Fig. 28 is a longitudinal section through the secured in the axial direction of the pivot pin,

Fig. 29 a of Fig. 28 similar representation, namely in free-Shared to the axial displacement of the pivot pin,

Fig. 30 is a designed in the form of a closure fitting arrangement in the Schließstelung a participating bonnet, on the fifteen te embodiment,

Fig. 31, the sequence diagram of FIG. 30, namely at the lowered hood along with a deformation of the damping element,

Fig. A schematic representation of the sixteenth embodiment 32, wherein the Beschlaganord voltage in the form of a lock-based damping elements designed accordingly the closed position of the bonnet,

Fig. 33, Fig. 32 similar representation, namely in the lowered hood, connected to a downward displacement of the lock while the lock housing erfolgendem deforming the supporting damping members,

Fig. 34, a seventeenth embodiment, in view schemati shear, wherein the hinge is a six-link hinge and a present intermediate opening position of the bonnet,

Fig. 35 the hood, in its Geschlossensellung and dot-dash lines in the alternate position

Fig. 36, an eighteenth embodiment of the Beschlagan properly closed hood, schemati Siert illustrates

Fig. 37 the section along the line XXXVII-XXXVII in Fig. 36

Fig. 38 is a perspective view of the fitted with the torsion joint,

Fig. 39 a of FIG. 36 corresponding representation, relating to the shunting position or abgesenk te position of the bonnet,

Fig 40 position. Which also FIG. 36 similar Dar, namely with the hood open,

Fig. 41, the mounting arrangement in a perspective view, with differing with respect to the eighteenth embodiment of the permanently connected to the body articulation support is ela cally ausweichbarer Lagefixie stop for the valve-closed position tion zugeord a net,

Shown schematically FIG. 42, this abgeänder te configuration corresponding to the closed position of the bonnet,

Fig. 43 shows a cross section through FIG. 42, namely in the region of the stop,

Fig. 44 is a view similar to FIG. 43, but at over fahrenem abutment and lowered bonnet,

Fig. 45 a schematic representation of the nineteenth embodiment of the fitting arrangement in specific matic representation, relating to the closed position of the bonnet,

Fig. 46 is a perspective view of the prestressed torsion of the Subject Author fenden joint,

Fig. 47 is a view similar to FIG. 45, but in abge countersunk hood and thereby loaded torsion

Fig. 48, the bonnet in its open position,

Fig. 49 shows a differently designed torsion link, which has a spoke-like structure, namely in the. Position which corresponds to the closed bonnet, and

Fig. 50 is an illustration like Fig. 49, namely with a tensile torsion member, which occurs when the bonnet is lowered from the closed position thereof.

According to the first embodiment, shown in FIGS. 1 and 2, the fitting arrangement is designed in the form of a hinge 1 for bonnets 2 . Specifically, the hinge 1 has a first fitting part 3 fastened to the bodywork (not illustrated ) and a second fitting part 4 assigned to the hood 2 , which is the carrier of the hood plate 5 . The fitting parts 3 , 4 can be displaced relative to one another in order to open the hood 2 . For this purpose, the first fitting part 3 has two pivot pins 6 and 7 arranged one behind the other. Around the hinge pin fen 7 is an upper link 8 , which is coupled via a hinge pin 9 with the hood-side fitting part 4 . The pivot pin 6 supports a handlebar 10 that is shorter than the handlebar 8 . At its free end, this forms an elongated hole 11 , into which a pivot pin 12 extending from the second fitting part 4 projects. An in the slot 11 Haltfe 13 , which is designed as a compression spring, is supported on the pivot pin 12 on the one hand. The other end of the retaining spring 13 is supported at the lower end of the elongated hole 11 , cf. Fig. 1. The second fitting part 4 is acted upon beyond the hinge pin 9 by a damping element 14 , which is formed as a compression spring and acts with a bias of about 1000 N on the hood 2 , in the closed position of the same as shown in FIG .. 1

The following mode of action occurs:

Act on the hood 2 from above forces that are below 1000 N, the hood 2 remains in its closed position according to FIG. 1. In an accident, in particular head impact, act on the hood 2 greater forces than 1000 N in the downward direction the bonnet 2 . This leads to a swiveling of the links 8 , 10 to a lowering of the bonnet 2 into the position according to FIG. 2. Due to the different lengths of the links 8 and 10 , the elongated hole 11 of the link 10 moves on a different circular path than the pin 12 , The practically occurring length change of the handlebar 10 is accordingly compensated for by the retaining spring 13 .

The second embodiment according to FIGS. 3 and 4 basically works on the same principle as the first embodiment. The same components are therefore provided with the same reference numbers. The first fitting part 3 , that is, the body-side, is mounted around the handlebars 8 , 10 of different lengths, the second fitting part 4 carrying the hood plate (not shown ) . Deviatingly, the pivot pin 6 is now guided in an elongated hole 15 of the first fitting part 1 and loaded by a spring, not shown, so that when the bonnet is lowered from the closed position according to FIG. 3 into FIG. 4, an evasive movement of the pivot pin 6 is possible is.

In this version, the hood 2 or the second fitting part carrying it is loaded by a damping element 16 . Regarding the same, there is a tension spring with one end fixed to the body, the other end engages an angle lever 17 , which in turn is articulated around a pin 18 of the first fitting part 3 . In detail, this means that the shorter lever arm of the angle lever 17 acts on the second fitting part 4 on the underside, while the tension spring 16 acts on the longer lever arm.

As in the first embodiment, the Zugfe 16 is biased at about 1000 N. Forces which act on the bonnet below half this value do not result in a downward displacement of the bonnet. If, for example, the force acting on the bonnet in the event of a head impact exceeds 1000 N, this leads to a lowering displacement of the bonnet, accompanied by a pivoting of the links 8 , 10 . At the same time, the angle lever 17 pivots into the position according to FIG. 4. Due to the different lengths of the rods 8 , 10 , the pivot pin 6 moves against spring force in the elongated hole 15 . The forces occurring in an accident are therefore largely absorbed by this configuration.

In order to ensure that the hood can only be deflected when the vehicle is in motion, the deflection can be blocked by means of an electromechanically displaceable blocking member 19 . This looks like that the blocking member 19 blocks the angle lever 17 in motion. With regard to the blocking member 19 , as shown in FIG. 3, the armature of an electromagnet 20 assigned to the first fitting part 3 can be moved back and forth. In the closed position of the hood and thereby correspondingly relocated second fitting part 4, the blocking member 19 passes over a cross pin 21 of the bell crank 17th Accordingly, this cannot pivot. Only when the blocking member 19 is moved back electromagnetically into the dot-dash position according to FIG. 3 is the angle lever 17 released for pivoting. This can happen from a certain speed or when the motor of the motor vehicle is started.

The fitting arrangement in accordance with FIGS. 5 and 6, concerning the third embodiment is, like the preceding embodiments of a four-joint hinge tet decor with dark. According to Fig. 5 and 6, this illustrates schematically veran. The same components have the same reference number. At the bonnet 2 engages with about 1000 N biased damping element 14 , which is designed as a compression spring and which is supported on the body side with one end. In this version, the handlebar 10 is formed by a deformation body D which plastically deforms when a trigger is exceeded. This is in the embodiment of FIGS. 5 and 6 by a lever made of plastic angle, of which one angle limb over the Gelenkzap fen 12 with the hood 2 is pivoted. The other angle leg in turn forms an elongated hole 22 which is penetrated by the pivot pin 6 on the body . This configuration also ensures that after the predetermined limit force has been exceeded, an evasive displacement of the bonnet 2 from the closed position according to FIG. 5 into the position according to FIG. 6 can take place. The force exerted on the handlebar 10 or the deformation body D leads to a bending of the deformation body D.

The fourth embodiment according to FIGS. 7 and 8 also includes a four-joint hinge. The handlebars and pivot pins have the same reference numerals as the previous embodiments. On the hood 2 engages in the form of a compression spring damping element 14 on. The shorter handlebar 10 forms an elongated hole 23 into which the body-side pivot pin 6 protrudes. In the closed position of the hood 2 according to FIG. 7, the articulation pin 6 is located at the lower end of the obliquely upward elongated hole 23 of the handlebar 10 which also has the same inclination. Beyond the elongated hole 23 , the handlebar 10 carries a support pin 24 which, in the closed position of the bonnet 2, is supported at one end of a trough-shaped control curve 25 . The latter runs concentrically to the pivot pin 6 . When the bonnet is swung open, the support pin 24 passes through the control cam 25 and leads to the required support of the handlebar 10 .

If the bonnet 2 is loaded with a force, for example in the event of a head impact, and if this force is greater than the limiting force exerted by the damping element 14 , the bonnet 2 is shifted in the direction of a lowering into the position shown in FIG. 8. Here, the support pin 24 of the handlebar 10 leaves its end contact with the control curve 25 , so that a change in length of the handlebar 10 is possible, cf. Fig. 8.

The fifth embodiment of the fitting arrangement according to FIGS. 9 and 10 is also constructed in a similar way to that before. There is a multi-joint hinge in the form of a four-joint hinge. The same parts therefore have the same reference numerals. Deviatingly, the handlebar 10 is now designed to be telescopic, namely consisting of the two handlebar sections 26 and 27 , to which a holding spring 28 designed as a compression spring is assigned. The hood 2 or its second fitting part 4 is loaded by a damping element 14 , which is designed as a prestressed compression spring.

If the pretension exerted by the damping element 14 is exceeded, the bonnet 2 shifts in the downward direction in the event of an impact and leads to an absorption of the forces occurring in the process. At the same time, there is a change in the length of the handlebar 10 , which is made possible by its telescopic nature.

According to the sixth embodiment of FIG. 11, the hood 2 is also a four-hinge net zugeord. The same components are also provided with the same reference numerals. Deviating are now the articulation points 6 , 7 relative to the body K. In the exemplary embodiment according to FIG. 11, this is such that the pivot pins 6 , 7 are assigned to the first fitting part 3 , which is designed as a holding bracket. The same is guided with downward-facing rails 29 in guides 30 on the body. Two end side of the holding bracket 3 engaging, designed in the form of preloaded compression springs damping elements 14 strain the holding bracket 3 in a stop position. In this version, too, a load on the bonnet leads to a dodge of the bonnet 2 downwards, the length change acting on the handlebar 10 being compensated for by spring deflection by appropriate displacement of the pivot pins during the downward movement of the holding bracket 3 .

While the previous embodiments of the fitting arrangement relate to the hinge, in the seventh embodiment according to FIGS. 12 and 13 the fitting arrangement is dealt with as a lock associated with the hood. According to FIGS. 12 and 13, the lock has a lock housing 31 , which is assigned to the body and interacts with a locking bracket, not shown, assigned to the bonnet. The lock or its lock housing 31 is guided in checks 32 on the series side. The lock or lock housing 31 is held in its basic position by means of ball catches 33 , in which the lock housing is supported on the body by means of two damping elements 14 on the body K. The same are also biased. An electromechanically actuated blocking member 34 is provided so that the lock cannot be moved when the bonnet is closed violently. The latter is pivoted in the contact position below the lock housing 31 .

So that the hood can evade after closing the hood in an accident, the blocking member is pivoted either after closing the hood or after switching on the ignition or at a certain speed of the motor vehicle, so that an evasive displacement of the lock 31 or Hood can be made in the downward direction.

In the eighth embodiment of the fitting arrangement according to FIGS. 14 and 15, this is also designed as a hood closure. The lock 35 is guided in guides 32 in the vertical direction. The lock 35 la gert in a known manner, a rotary latch 36 which can be locked by means of a pawl 37 in the closed position of the hood. A damping element 14 in the form of a prestressed compression spring acts on the lock. On the rotary latch axis 36 'of the lock ses 35 , a pivot lever 38 is arranged. The same forms a blocking member. With a driving projection 39 , the pivot lever 38 protrudes into the movement path of a driver 40 formed on the rotary latch 36 . On the pivot lever 38 engages a damper 41 , which in the closed position of the bonnet according to FIG. 14 shifts the pivot lever 38 so that it leaves its support position to a holding shoulder 42 of the body. In this closed position, illustrated in FIG. 14, of the bonnet 2 , the striker 43 carried by it is captured by the rotary latch 36. If the bonnet 2 is now subjected to a greater force which exceeds the limiting force exerted by the damping element 14 , the bonnet may become loose 2 with the lock 35 in the dash-dotted position shown in FIG. 14.

Opening the lock 35 requires a shift of the pawl 37 counterclockwise. This can happen, for example, by means of a Bowden cable that engages in the direction of the arrow x on the pawl 37 . At the same time, the rotary latch 36 can pivot into the release position and release the striker 43 , whereupon the bonnet 2 can be moved into the open position. Along with the pivoting of the rotary latch 36 into the position according to FIG. 15, the pivot lever 38 is pivoted via its catch 40, which lever moves to the support shoulder 42 in the supporting position. It is noted that FIGS. 14 and 15 are illustrated schematically. If the hood 2 is now closed, the striker 43 acts on the rotary latch 36 and pivots it. The closing force that occurs does not result in any downward displacement of the lock 35 due to the pivoting lever 38 representing a blocking member. Only when the closed position according to FIG. 14 is present is the pivot lever 38 pivoted out of its blocking position with a time delay, specifically into the position according to FIG. 14.

In the ninth embodiment according to FIGS. 16 and 17, the fitting arrangement is designed as a hood-side lock 44 . It stores the catch 36 and the ratchet ke 37th This blocks the rotary latch 36 in the position capturing the striker 43 . A compression spring 45 loads the lock 44 in the opening direction. Furthermore, a downward-directed guide plunger 46 is assigned to the lock 44 . The latter passes through a pressure plate 47 , which in turn is supported on the underside of a body-side guide plate 48 . On the pressure plate 47 acts a guide plunger 46 at the lower end comprehensive compression spring, which forms the damping element 14 . Above the Druckplat te 47 , the guide plunger 46 is equipped with a stop 49 .

In order to secure the lock 44 against an upward displacement in the closed position, a double-armed locking lever 50 is provided. Its hinge axis 51 is assigned to the body. In a slot 52 of the ratchet lever 50 engages a coupling pin 53 of a transmission lever 54 , which in turn is coupled to the coupling pin 55 with the pawl 37 . Then the lock 44 is associated with a damper 56 , which we are kungless in the held position of the lock. The held position of the lock 44 is determined by the upper, angled end 50 'of the locking lever 50 , cf. Fig. 16. Now acts in this Stel development on the bonnet a greater force than the limit force emanating from the damping element 14 , this results in a downward displacement of the lock 44 and thus the bonnet, the lock on the impact 49 on the pressure plate 47 and thus acts on the damping element 14 . During this publishers tion, the coupling pin 43 can move within the elongated hole 52nd

The opening of the hood requires a release shift of the pawl 37 counterclockwise direction. The rotary latch 36 is then no longer blocked and releases the striker 43 . Connected to a pivoting of the pawl 37 into the release position, the locking lever 50 is pivoted via the transmission lever 54 , the end 50 'of which releases the lock 44 , whereupon the compression spring 45 takes effect and brings about the opening position according to FIG. 17. Then the end 50 'of the locking lever 50 is supported laterally on the lock 44 .

If the bonnet is now closed and the striker 43 is brought into engagement with the rotary latch 36 , the closing force that occurs is absorbed by the damper 56 , which then acts like a rigid element. The striker can rotate the catch 36 so that the pawl can then enter its locking position. The position according to FIG. 16 then occurs, in which the damper 56 has no effect.

Deviatingly, it is possible to arrange the compression spring 45 in the coaxial direction also on the guide plunger 46 , above the stop 49th

According to the tenth embodiment of the fitting arrangement, illustrated in FIGS. 18 and 19, this is also designed as a lock. There is also a schematic representation here. From the lock, the rotary latch 36 and the pawl 37 are illustrated. The striker 43 is attached to the hood 2 . The striker 43 caught by the catch 36 is supported on the force introduction point 57 of a damping element 58 . The Dämpfungsele element 58 is designed in this version as a deformation body and is made of appropriate plastic. The deformation body is created in an angular shape with the predetermined bending point 59 assigned to the angular apex. The end 60 of the damping element 58 opposite the force introduction point 57 is in turn supported on the body K. The damping element 58 is also designed such that it is able to absorb a limiting force of approximately 1000 N without this causing the damping element 58 to bend. A greater force acts on the bonnet 2 than the limit force, this leads via the striker 43 to a deformation of the damping element 58 into the position according to FIG. 19, combined with an evasive displacement of the bonnet 2 in the downward direction, with corresponding impact forces being compensated for.

According to the eleventh embodiment according to FIGS. 20 and 21, the damping element 61 is assigned to the striker 43 itself. The striker 43 in turn is created in a U-shape, the damping elements 61 starting from the U-legs starting in the form of bends, which in turn are set in a check pattern on the series side. However, attachment on the hood side is also possible. The DAMPING te 61 are constructed such that up to a limit force, no deformation of the striker or the damping elements takes place 61st Only when the limit force is exceeded, the striker 43 can assume the position according to FIG. 21, the damping elements, resulting in bends, deforming accordingly and accordingly allowing an evasive movement of the hood or flap.

Referring to FIG., 22 and 23 which form the twelfth execution of the mounting arrangement illustrated, the damping element 61 is also associated with the striker 43. The damping element 61 is fixed on the bonnet 2 . The damping element 61 is designed as a supply, in particular in the angular shape of the striker. As long as the loads acting on the bonnet are below a limit force, there is no deformation of the damping element. Only when the limit force is exceeded does the damping element 61 deform, so that the position according to FIG. 23 is then reached. This allows the hood 2 to be lowered into an evasive position.

In addition, the catch 36 and the pawl 37 having, not shown in this embodiment, lock could also perform an evasive shift.

The thirteenth embodiment, shown in FIGS. 24, 25 includes a spring-loaded striker 43 in a U-shape. This is cushioned against its console 62 , which in turn is assigned to the body. This looks like that on the U-legs, beyond a stop plate 43 'of the striker damping elements 14 in the form of compression springs are supported. Preloading of the damping elements or compression springs is also possible here. If a limit force is exceeded, the striker 43 can then shift from its position according to FIG. 24 into the position according to FIG. 25, specifically against the force of the damping elements 14 . This shift allows the hood 2 or a corresponding flap to evade.

According to the fourteenth embodiment according to FIGS. 26 and 27, the fitting arrangement is designed as a four-joint hinge. Analogous reference numerals are used accordingly. A locking lever 63 sits on the pivot pin 7 next to the handlebar 8 . An unillustrated Drehfe the loads this clockwise. The swivel displacement is limited by a stop pin 64 of the handlebar 8 . In this stop position of FIG. 26, which speaks ent the closed position of the bonnet 2, the free end of the lock lever 63 extends in front of a head plate 6 'of the pivot pin 6, which has a bearing aperture extends through the first fitting part 3 and a corresponding console. A compression spring 65 arranged on the hinge pin 6 loads the hinge pin in the direction of the locking lever 63 . However, the pivot pin 6 cannot shift due to the locking lever 63 located in the displacement path. The handlebar 10 thus remains in coupling engagement with the articulated pin 6 . The coupling position is not abandoned when the bonnet is opened. A body-side support surface 66 then serves as an abutment for the locking lever 63 . If the bonnet 2 , starting from its closed position according to FIG. 26, is subjected to a greater force which exceeds the limiting force emanating from the damping element 14 , this leads to a downward displacement of the bonnet to a pivoting of the handlebar 8 , which over the Stop pin 64 takes the locking lever 63 , whereupon this leaves the support position for the pivot pin 6 . The compression spring 65 can now take effect and transfer the pivot pin 6 from the position shown in FIG. 28 to the position shown in FIG. 29. It is taken care that the pivot pin still remains within the bearing of the first fitting part 3 . Due to the axial displacement of the pivot pin 6 , the handlebar 10 is released, so that no change in the length thereof is required. The bonnet 2 can therefore deflect resiliently in the event of an impact by a person while reducing the risk of injury.

According to the fifteenth embodiment according to FIGS. 30 and 31, the lock 67 has a rotary latch 36 and a pawl 37 . The striker 43 is caught by the rotary latch 36 . Down the castle 67 continues in parallel to each other Füh approximately 68 webs. The upper end of the same is the verbun by a cross pin 69 , which is supported at the force application point 57 of an angularly shaped damping element 58 . The lower end of the damping element 57 is supported on a vertical slot 70 of the guide webs 68 through the body-fixed support pin 71 . Because of this configuration, it is possible for the lock 67 and the flap or hood connected to it to be lowered. In the corresponding Absen effect by means of a load force, which is higher than the force exerted by the damping element 58 limit force, the damping element 58 flexes along with a lowering movement of the lock 67 and the associated flap or hood. The position according to FIG. 31 is brought about here.

A lock 72 is also illustrated in the sixteenth embodiment according to FIGS. 32 and 33. This works in a known manner with the striker 43 , which is attached to a hood 2 or flap. Each side region of the lock 72 is supported in an angular form against the body K by means of a damping element 58 . The damping elements 59 are designed so that they do not deform until a predetermined limit force is reached. If this limit force is exceeded, however, the damping elements 58 deform to the predetermined bending points 59, starting from the position of FIG. 32, into that of FIG. 33 and thereby allow a downward displacement of the lock 72 and the locking bracket 43 coupled to it, which is in turn fixed to the bonnet 2 or flap. There can thus also be an evasive movement of the same, reducing persons falling against the bonnet.

With regard to the fitting arrangement shown in FIGS . 34 and 35, it is a six-joint hinge 1 '. The fitting part, which is assigned to the body and is not designated in any more detail, is the carrier of two pivot pins 73 and 84 arranged one above the other. A link 74 leading to the bonnet 2 is pivotally articulated around the pivot pin 73 . The hinge pin on the hood is numbered 75 . Furthermore, the hood 2 carries on a boom 76 a hinge pin 77 for a handlebar 78th Its free end is coupled to a link 80 via a pivot pin 79 . The latter and the link 74 are connected to one another via a pivot bearing 81 . Beyond it, the link 80 continues and is coupled via a pivot pin 82 to a link 83 , which in turn supports the other end around the pivot pin 84 .

The diagrams in FIGS. 34 and 35 are schematic. Fig. 34 shows an intermediate position of the bonnet 2 ben during the closing of the same. In Fig. 35, the closed position of the hood 2 is illustrated with solid lines. As in the previous exemplary embodiments, one of the handlebars, primarily the handlebar 80 , can be under the influence of an unillustrated, prestressed spring, which represents the damping element. If, starting from the closed position of the bonnet, a force is exerted on it which exceeds the limiting force of the damping element, then a lowering movement of the bonnet 2 can take place parallel to itself. A variable length of a handlebar does not occur here, so that a separate Haltfe can be omitted.

According to the eighteenth embodiment of the fitting arrangement, shown in FIGS. 36 to 44, this is designed as a hinge 1 . This has a first fitting part 3 fastened to the bodywork (not shown ) in the form of an articulated support. A second fitting part 4 assigned to the bonnet is then provided. The latter also represents an articulated support. To open the hood, the fitting parts 3 , 4 can be displaced relative to one another. For this purpose, the first fitting part 3 has two pivot pins 6 and 7 arranged one behind the other. To the hinge pin fen 7 supports the upper link 8 , which is connected via the Ge pivot pin 9 to the hinge bracket 4 . The handlebar 10, which is shorter than the handlebar 8, is mounted around the pivot pin 6 . This is connected to the hood-side hinge bracket 4 via the hinge pin 12 . In this way, a four-joint hinge is realized.

The damping element 86 is now a torsion link assigned to the pivot pin 6 . In detail, the joint in question looks so that the hinge pin 6 is firmly and immovably associated with the hinge bracket 3 or first loading part. The pivot pin 6 extends through an elongated hole 87 in the first joint element or handlebar 10 . The pivot pin 6 then passes through a metal sleeve 88 . The same is rotatably embedded in the damping element 86 or torsion member. Regarding the damping element 86 or torsion member, it is a rubber body. The same is non-rotatably assigned to the first joint element or link 10 . The sleeve 88 is surmounted beyond the rubber body by a stop 89 , which is supported in the closed position of the bonnet on a radial projection 90 of the pivot pin 6 which is in the same cross-sectional plane. Since the pivot pin 6 is fixedly connected to the second joint element or the joint support 3 , the projection 90 also has a defined assignment to this second joint element 3 .

If increased forces act on the bonnet, such as occur, for example, in the event of a collision with a person, the position of the bonnet can be adjusted as shown in FIG. 39, which corresponds to a lowered position of the bonnet. Here, the torsion member 86 is tensioned because the stop 89 is supported on the projection 90 , while the handlebar 10 or the first joint element rotates relative to the pivot pin 6 . This is accompanied by a slight displacement of the handlebar 10 relative to the fixed pivot pin 6 . This is possible due to the elongated hole 87 and the elasticity of the rubber damping element 86 . When opening the bonnet, the handlebars 8 , 10 rotate in the other direction, the stop 89 being removed from the projection 90 . As a result, the torsion element 86 then remains unaffected.

The configuration of the fitting arrangement according to FIGS. 41 to 44 corresponds essentially to the previous descriptions. Deviating is now additionally hen a stop 91 for fixing the position of the flap closed position. In this way, a hood stop is also created. This stop 91 is also designed in such a way that it only evades when a specific load is overcome, for example in the event of a head impact.

Specifically, for this purpose the first fitting part 3 or the joint carrier formed by it has a bearing pot 92 beyond the joint pin 7 . The peg-like stop 91 is guided in this. The same is composed of a head 94 and a frustoconical surface 93 and an adjoining, smaller diameter shaft 95 . On the latter, a compression spring 96 is arranged, which is supported on the one hand on the head 94 and on the other hand on the pot bottom of the pot 92 . An end collar 97 of the shaft 95 limits the displacement of the stop in the direction of spring action.

The stop 91 interacts with a counter stop 98 of the fitting part 4 connected to the bonnet. Preferably, the counter-stop 98 is adjustable so that in the closed position of the engine hood the counter-stop 98 is supported on the truncated cone surface 93 of the stop 91 to achieve a linear contact, see FIG. 43.

If the hood now lowers in the event of a personal accident, the fitting part 4 or the joint carrier forming it is shifted along with it. This means that when a limit force is exceeded, the counter-stop 98 causes the stop 91 to move to a different position, which is shown in FIG. 44. Then the stop 91 has been run over and is supported on the end face on the joint support 4 .

The nineteenth embodiment shown in FIGS. 45 to 48 largely corresponds to the eighteenth embodiment. The same components have the same reference numbers. Deviatingly, the torsion member or the damping element 86 which represents this is pretensioned relative to the first joint element or the handlebar 10 . This is done in that wings 99 extend from the sleeve 88 in a diametrically opposite position. These act together with fixed stops 100 of the joint element 10 . Before the insertion of the damping element 86 , the wings 99 have a twisted arrangement to the fixed stops 100 and must be brought behind the fixed stops 100 to achieve a bias of the damping element 86 , the sleeve 88 rotating relative to the damping element 86 , because of its non-rotatable assignment to the joint element 10 .

In this version, too, the sleeve 88 forms a stop 89 , which lies in the closed position of the hood in front of the projection 90 of the pivot pin 6 , cf. in particular FIG. 46.

If the hood, starting from their Ge closed position of FIG. 45, for example. Burdened impact by a head, so this leads to overcome the limit force associated to a lowering of the hood with a twisting of the arm 10 opposite the pivot pin 6. This shift leads to a further tensioning of the torsion element 86 , since the stop 89 is supported on the projection 90 of the non-rotatable pivot pin 6 , see FIG. 47.

When the bonnet is opened, the position shown in FIG. 48 is established. Here, the stop 89 moves away from the projection 90 . The prestressed position of the rubber tire of the torsion member 86 is maintained.

In Fig. 49 a different embodiment of a damping element 101 is illustrated. This forms the torsion link. The latter has a hub 102 which is non-rotatably connected to the sleeve 8 , 8 . The sleeve forms the stop 89 . The latter works together with the projection 90 of the pivot pin 6 . From the hub 102 move integrally approximately tangentially to the hub 102 aligned spokes 103, which are in turn integrally connected to an outer rim 104th Both the outer ring 104 , the spokes 103 and the hub 102 consist of an elastically deformable material, for example a corresponding plastic. The outer ring 104 is connected to the first joint element or link 10 in a rotationally fixed manner. When assigning this damping element 101 to the hinge of a bonnet, when the same moves downward from the closed position, the outer ring 104 is displaced relative to the supported hub 102 , the spokes 103 being subjected to tension. The position shown in FIG. 50 is established.

All features disclosed are (by themselves) fiction sentlich. In the disclosure of the registration is hereby also the disclosure content of the associated / attached Priority documents (copy of pre-registration) full included in content, also for the purpose of characteristics of these documents in claims of the present application to include.

Claims (37)

1. Fitting arrangement for a swing-open flap, in particular hood ( 2 ), on a motor vehicle, in particular in the form of a lock or a hinge, with a first fitting part which can be fastened to the body (K) and with a second, the flap ( 2 ) associated fitting part, which parts can be displaced relative to one another to open the flap, characterized in that the fitting arrangement is a damping element ( 14 , 16 , 58 , 61 , 86 , 101 ) is assigned such that after overcoming one on the flap ( 2 ) limit force acting in the flap closing direction evades the flap due to a displacement of the damping element ( 14 , 16 , 58 , 61 , 86 , 101 ). 2. Fitting arrangement according to claim 1 or in particular according thereto, characterized in that the damping element ( 14 , 16 ) is a spring. 3. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the damping element ( 58 ) is a plastically deformable deformation body. 4. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the fitting arrangement is a Mehrge steering hinge ( 1 ) with at least two the body rie (K) with the flap ( 2 ) connecting links ( 8 , 10 ), wherein a handlebar ( 10 ) against the force of a retaining spring ( 13 ) is variable in length to avoid. 5. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the position of the pivot pin ( 12 ) can be changed for evasion. 6. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the pivot pin ( 6 , 12 ) is displaceable against spring force in an elongated hole ( 13 , 15 ). 7. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the pivot pin ( 6 , 7 ) relative to the holding bracket ( 3 ) is displaceable. 8. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the fitting arrangement is a multi-joint, in particular a four-joint hinge, with at least two connecting the body with the flap to the handlebars ( 8 , 10 ) , wherein the damping element ( 86 , 101 ) is a torsion member assigned to a joint. 9. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the torsion member ( 86 , 101 ) is on the one hand firmly connected to a first joint element ( 10 ) and on the other hand forms a stop ( 89 ) against which in the closed position of the flap, a projection ( 90 ) of the hinge pin ( 6 ) firmly connected to a second joint element ( 3 ) occurs. 10. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the torsion member ( 86 , 101 ) is a spring element or an elastomer body, in particular a rubber body, which in particular also permits a length extension. 11. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the stop ( 89 ) of the torsion of the ( 86 ) from a on the pivot pin ( 6 ) mounted, firmly connected to the torsion member ( 86 ) on the one hand sleeve ( 88 ) is formed. 12. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the torsion member ( 101 ) has a spoke-like structure. 13. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the torsion member ( 86 ) is prestressed with respect to the first joint element ( 10 ), in particular wings ( 99 ) formed from the sleeve ( 88 ) before fixed stops ( 100 ) of the articulated element ( 10 ). 14. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized by an elastically evasible stop ( 91 ) for fixing the position of the flap closed position. 15. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the stop ( 91 ) associated with a joint carrier ( 3 ) fixedly connected to the body or firmly to the flap against the restoring force of a compression or leaf spring ( 96 ) can be deflected when a limit force is applied to a counterstop ( 98 ). 16. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the flap-side holding bracket ( 4 ) is supported by the damping element ( 14 , 16 ). 17. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the damping element is a Druckfe the ( 14 ) or on an angle lever ( 17 ) attack de tension spring ( 16 ). 18. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the compression or tension spring ( 14 , 16 ) is biased. 19. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the evasibility can be blocked by means of a blocking member ( 19 , 34 , 38 ) which can be displaced in particular electromechanically. 20. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the blocking member ( 19 ) blocks the angle lever ( 17 ) in motion. 21. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that a link ( 10 ) is formed by a deformation body (D) which plastically deforms when a release force is exceeded. 22. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the shortenable handlebar ( 10 ) is supported on a control cam ( 25 ) when swiveling into the open position and leaves it in the alternative position when it is released. 23. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the handlebar ( 10 ) is telescopic. 24. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that at least one of the articulation points ( 6 , 7 ) or the holding bracket ( 85 ) can avoid the body (K) or the flap ( 2 ). 25. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the bracket ( 85 ) carrying the hinge ( 1 ) or the lock ( 31 , 35 ) is guided in guides ( 30 or 32 ) so as to be avoidable. 26. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the console-evasibility speed can be canceled by means of a blocking member ( 34 , 38 ) which assumes the blocking position particularly when the vehicle is at a standstill. 27. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the blocking member ( 38 ) enters the blocking position when the flap ( 2 ) is opened and, after the flap has been closed, leaves it with a time delay. 28. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the blocking member ( 38 ) is a pivot lever controlled by the rotary latch ( 36 ) or the pawl ( 37 ) of a rotary latch lock ( 35 ). 29. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the lock ( 44 ) is spring-loaded in the opening direction in the closed position, after opening is shifted in the opening direction, by a damper ( 56 ) in the opening position is supported and after closing the lock ( 44 ) is shifted back into the held position, the damper ( 56 ) having no effect in the held position. 30. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the console ( 31 ) is guided linearly and the blocking member ( 34 ) bridges the two force introduction points into the damping element ( 14 ). 31. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the deformation body ( 58 ) forms an angle. 32. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the locking bracket ( 43 ) caught by the catch ( 36 ) is supported at the force introduction point ( 57 ) of the damping element ( 58 ). 33. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the damping element ( 14 , 61 ) is assigned to the striker ( 43 ). 34. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the damping element ( 61 ) is designed as a bend, in particular in the angular form of the closing bracket ( 43 ). 35. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the U-shaped locking bracket ( 43 ) is cushioned relative to its bracket ( 62 ). 36. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the pivot pin ( 6 ) is displaced axially from its storage position in order to enable the alternative displacement, wherein it is axially tied during the pivoting displacement between the open and closed positions and these are fixed selection can be canceled. 37. Fitting arrangement according to one or more of the preceding claims or in particular according thereto, characterized in that the fitting arrangement is a six-joint hinge ( 1 ') and that the bonnet ( 2 ), starting from its closed position, a largely parallel lowering shift in the hinge area rich the evasive movement.