Abstract:
A vehicle component has a vehicle body part in combination with an acoustic insulating structure which interacts therewith. The acoustic insulating structure has an outer covering having a shield. The shield is spaced at a distance from the vehicle body part by an intermediate layer. In a particular embodiment, the intermediate layer is at least partially filed with a foam layer which is pressed against the body part by the shield. The shield is preferably perforated and the foam layer is protected against humidity and moisture by a thin plastic film. The outer covering can be conventionally fastened to the underside of the body part.

Description:
FIELD OF THE INVENTION 
     The present invention concerns a vehicle component according to the preamble of claim  1  and an external cover for this. 
     DESCRIPTION OF THE RELATED ART 
     It is known to equip the floor panel of a vehicle with an acoustically active i.e. sound-insulating and/or sound-absorbing interior lining. Usually such a lining has a sound-insulating damping layer which is laid or glued directly onto the floor plate. In vehicles of higher comfort, on this vibration-damping and sound-insulating layer is applied a further sound-absorbing foam or fibre fleece layer and a heavy airtight carpet layer. These additional layers are matched to each other acoustically so that they can interact with each other as an acoustic spring-mass system. It is also known to apply a protective coating to the outside of the floor panel. This protective coating protects the floor panel mechanically and/or chemically for example against stone chips or road salt. Naturally this protective coating, referred to below as the underfloor coating, also contributes to additional damping of the vibrations of the floor panel. 
     As underfloor protect-on usually a relatively expensive PVC coating of approximately 1 mm thickness is sprayed on. Such a layer leads to a weight increase of around 1-1.5 kg/m 2  and undesirably releases large quantities of chlorine on recycling. 
     SUMMARY OF THE INVENTION 
     It has been found that the multiplicity of layers and coatings of different functions applied to the floor plate undesirably increase the total weight of the vehicle and undesirably reduce the passenger space, in particular the foot space. The general aim of the modern vehicle industry however is to make vehicles lighter, more spacious and more economic. 
     It is therefore the task of the present invention to create a vehicle component which allows the foot space of the vehicle to be structured more spaciously without loss of acoustic effectiveness. 
     In addition a vehicle component is created which in comparison with conventional vehicle floor configurations is lighter and more cost effective and in particular raises no special disposal problems. 
     This task is solved according to the invention with the vehicle component according to claim  1  and an outer covering according to claim  13 , and in particular in that on the outside of the body part is applied a strengthening shield at a distance from the said part which together with the body part forms a double floor structure. This double floor structure has a sound-insulating effect and can be combined with further sound-insulating and/or sound-absorbing elements. 
     In a preferred development of the vehicle component according to the invention a foam layer, in particular a soft foam, is introduced in the cavity of the double floor where the foam, preferably on its side facing the body part, is fitted with a profile. Such profiled dissipatively acting layers are known for example from EP 0 474 593 (which is hereby included in full scope as a constituent of this application) and rest loosely against the body part and damp the body vibrations. For this the soft foam and double floor are dimensioned such that the profiled soft foam is pressed against the body part by the shield of the double floor. 
     In a further preferred design of the vehicle component according to the invention the double floor is combined with an ultralight absorption package of the known type (for example according to WO98/18657, the content of which forms part of this application). Instead of a heavy layer this has a microporous stiffening layer. In this embodiment both the sound-insulating bituminous damping layer inside the vehicle and the heavy layer of the spring-mass system of the interior lining can be omitted. 
     This creates an acoustically active vehicle component which is considerably lighter than conventional systems and in the interior of the vehicle has a lower thickness. It is evident that by suitable combination of the double floor according to the invention with sound-insulating and/or sound-absorbing systems,of the known type, the acoustic efficacy can be improved further. 
     Preferred developments are defined by the features of the sub-claims. 
     The invention is now explained in more detail below with reference to design examples and the figures. Here: 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 shows a diagrammatic view of a conventional vehicle floor; 
     FIG. 2 shows a diagrammatic view of the vehicle component according to the invention; 
     FIG. 2 a  shows an enlarged view of a portion of the vehicle component of FIG.  2 . 
     FIG. 3 is a diagrammatic view of a further development of a vehicle component according to the invention; 
     FIG. 4 is a diagram of the acoustic efficacy of the various vehicle components with different equipment. 
    
    
     DETAILED DESCRIPTION 
     The vehicle floor  1  shown in FIG. 1 has a conventional structure. On the inside of the floor plate  2 , for example a steel plate approximately 0.8 mm thick, is applied a bituminous damping layer  3 . This damping layer  3  usually weighs around 2.3 kg/m 2  and is glued in place. On this damping layer  3 , depending on vehicle equipment level, is applied a more or less heavy sound-absorbing spring-mass system  4 , the spring layer  5  of which consists of a fibre fleece approximately 20 mm thick, an open-pore foam or a foam flock fleece (KFF), the mass layer  6  of which consists of a heavy layer (EPDM) weighing approximately 3.2 kg/m 2  or a corresponding decor or carpet layer. On the outside  8  the floor plate  2  has an underfloor coating  7  approximately 1 mm thick which usually consists of sprayed on PVC. The total weight of the acoustically active structure applied to such a vehicle floor  1  is therefore at least 8.0 kg/m 2 . 
     In contrast FIG. 2 shows a vehicle component  10  equipped according to the invention. In its simplest embodiment this has a shield  11  at a distance from the outside  8  of the floor plate  2  and together with the floor plate  2  forms a double floor  13 . The cavity between the floor plate  2  and the shield  11  in this simple embodiment has a thickness of a few millimetres, in particular 5 to 15 mm, and is filled only with air. In a preferred embodiment this cavity is filled with a sound-insulating and/or sound-absorbing intermediate layer  12 . Suitable materials for this intermediate layer are open-pored and known to the expert for some time. In order to clamp the shield  11  to the body part  2 , suitable means  17  are provided. These means can comprise any conventional connection technology known today for example bolting, clipping etc. and in particular can use the weld bolts normally used in vehicles. The body part  2  consists of a conventional body panel for example made of a 0.8 mm thick steel plate whereas the shield  11 , in a preferred embodiment, consists of a fibre-and/or filler-reinforced plastic 0.5 mm to 3.0 mm thick, preferably 1.0 mm to 2.4 mm thick, with a basis weight of around 3 kg/M 2 . 
     The double floor arrangement according to the invention, because of the spring effect of the air, leads to improved sound insulation outside the sandwich resonance of the spring-mass structure. 
     Suitable materials for structuring the shield  11  according to the invention are shown in the table below: 
     
       
         
               
               
               
               
               
               
               
             
               
               
               
               
               
               
               
             
           
               
                   
                   
               
               
                   
                   
                   
                   
                   
                   
                 E-modulus of 
               
               
                   
                 Fibre Filler 
                   
                   
                   
                   
                 bending in 
               
               
                   
                 in w. % 
                 Fibre Type 
                 Matrix 
                 Group 
                 Density 
                 GPa 
               
               
                   
                   
               
             
             
               
                   
               
             
          
           
               
                 GMT 
                 20 
                 Glass 
                 PP 
                 Thermoplastic 
                 1.03 
                 2.9 
               
               
                 LFT 
                 20 
                 Glass 
                 PP 
                 Thermoplastic 
                 1.03 
                 2.9 
               
               
                 LFI 
                 20-25 
                 Glass 
                 PUR 
                 Thermoset 
                  0.5-1.15 
                 2.0-5.5 
               
               
                 NMT 
                 30 
                 Green flax 
                 PP 
                 Thermoset 
                 1.02-1.03 
                 3.5 
               
               
                 R-RIM 
                 20 
                 Glass 
                 PUR 
                 Thermoset 
                 1.2 
                 1.2 
               
               
                 Injection 
                 20 
                 Glass 
                 PP 
                 Thermoplastic 
                 1.04 
                 3.8 
               
               
                 moulding 
               
               
                 SMC 
                 25 
                 Glass 
                 UP resin 
                 Thermoset 
                 1.7-2.0 
                 8.5-14 
               
               
                   
               
             
          
         
       
     
     The particularly advantageous feature of these materials is their high rigidity and low density. Further density reductions can be achieved via other additional fillers e.g. by means of hollow glass balls with a particle size of 10 to 200 μm and an effective density of 0.14 to 0.70 g/cm 3 . Suitable fibre fillers are aramite, carbon, hybrid, textile, glass, natural, polyamide, polyester or mineral fibres. 
     In a preferred embodiment the shield  11  has perforations i.e. at least a partial hole structure. These perforations can have a diameter of 0.5 mm to 3 mm, preferably 1.0 mm, and are for example arranged at intervals of approximately 2.5 mm from each other. In order to protect the open-pore intermediate layer  12  from moisture and humidity, advantageously at least between shield  11  and intermediate layer  12  is applied a thin plastic film. On the outside of shield  12  can be applied an open-pore fibre or carpet layer to achieve additional protection against stone chips and/or water. Such a fibre and/or carpet layer also improves the air flow behaviour on the outside of shield  11  (shark-skin principle). Such a double floor is particularly suitable for the outer covering of wheel arches. The acoustic efficacy of the double floor according to the invention is particularly useful in this application. 
     In a further development of the double floor arrangement according to the invention on the inside  9  of the body part  2  is provided a conventionally constructed sound-insulating spring-mass system  14 . In this embodiment this comprises a sound-dissipating porous layer of reduced thickness acting as a spring (soft light foam, heavy foam or fibre fleece layer) and a slight heavy layer  6  acting as a mass. Or on the inside  9  of body part  2  is provided a sound-insulating and sound-absorbing spring-mass system  14  similar to the system described in WO98/18657, consisting of a porous layer  14  acting as a spring and a microporous cover layer  16  acting as a light mass. 
     In a further development of the double floor arrangement according to the invention, on the inside  9  of body part  2  is provided a conventionally constructed sound-absorbing spring-mass system  14 . In this embodiment this comprises an absorber layer  15  (light foam layer) acting as a spring and a porous cover or heavy layer  16  acting as a mass layer. The double floor arrangement according to the invention thus allows the omission of the damper layer  3  and underfloor coating  7  conventionally applied. This allows the weight of the acoustically active structure to be reduced substantially. In particular, the sound-insulating damping layer  3  can be dispensed with the interior lining  14 , and the protective coating  7  can be dispensed with the outer layer  13 . This leads to a weight saving of more than 2 kg/m 2  without restricting the acoustic effect as corresponding comparison measurements confirm. At the same time the thickness of the interior structure  14  can be reduced. 
     In a preferred development of the vehicle component according to the invention as shown in FIG. 3, the intermediate layer  12  consists of an elastic PU foam  19 . This foam  19  has a profile which lies on the outside  8  of body part  2  and in particular is pressed by shield  11  onto this body part  2 . This provokes a vibration damping of the body part  2 . The profiling of this foam  19  leads to the formation of a labyrinth-like air layer  18  between the body part  2  and the foam layer  19 , which air layer  18  also has a dissipative effect in interaction with the vibrating body part  2 . Evidently this foam layer  19  can be used to make contact both over the full area and also partially. In a particular embodiment the cavity between the shield  11  and the body part  2  is filled only partially with an intermediate layer  12 . In addition the inside  9  of the body part  2  can also be partially covered with a damping layer  3 . 
     In further developments of the construction according to the invention, instead of a conventional spring-mass system  14  an ultralight absorption package is used. Such absorption packages are for example described in WO98/18657 and instead of a heavy layer  6 ,  16  have a microporous stiffening layer which has a total air flow resistance of 500 Nsm −3 &lt;R t &lt;2500 Nsm −3  and a surface mass of 0.5 kg/m 2 &lt;m F &lt;1.6 kg/m 2 . The bending strength of such a microporous stiffening layer is 0.005 Nm&lt;B&lt;10.5 Nm. 
     The diagram in FIG. 4 shows the acoustic efficacy of the various vehicle components. Curve  22  shows the acoustic behaviour of a conventional structure according to FIG.  1 . 
     The development of this curve  22  in the area of 200 Hz shows a characteristic insulation minimum and clearly shows that with this sound-damping structure the sound insulation efficacy runs essentially linear at higher frequencies and at approximately 10,000 Hz has a value of around 80 dB. This development corresponds rather precisely to the acoustic behaviour of the double floor according to the invention in combination with a classic spring-mass system. In contrast curve  21  shows the sound insulation behaviour of the sound-absorbing ultralight insulation system cited above (according to WO98/18657) on a conventional floor plate equipped with underfloor protection and damping coating. Here the sound insulation efficacy R has no resonance loss and shows an improvement in comparison with the configuration in curve  22  of up to 10 dB in the area of around 200 Hz. The insulation efficacy R of the configuration according to curve  21  rises above 500 Hz almost linear with the—logarithmic—frequency and with a slightly lesser gradient. The acoustic behaviour of a preferred design form according to the invention is indicated by curve  23 . In this embodiment the double floor according to the inversion is combined with the ultralight insulation system according to WO95/18657. 
     The benefits of the vehicle component according to the invention are immediately evident to the expert. In particular with the vehicle component according to the invention the heavy vibration-damping layers are replaced by stiffening and sound-absorbing layers. The reduction in layer thickness in the area of this vehicle foot room achieved by the vehicle component according to the invention proves particularly advantageous. It is evident that by omission of the heavy vibration-damping layers, the arrangement according to the invention is more economic than conventional insulation systems. The external noise reduction in the wheel arches because of the improved sound insulation effect has proved particularly advantageous. At the same time the present arrangement gives improved corrosion protection and with this arrangement a lower CW value can be achieved if the double floor arrangement is fitted with a surface structure (carpet or golf ball structure) on the outside. Further developments of the double floor arrangement according to the invention and suitable combinations with other acoustically active systems of known types lie within the scope of the knowledge of a person skilled in the art and are not explained in more detail here. It is evident that the double floor arrangement according to the invention can be used not only on vehicle floors or in wheel arches but equally well for engine encapsulation.