WO2006059724A1 - 車体パネル構造体 - Google Patents
車体パネル構造体 Download PDFInfo
- Publication number
- WO2006059724A1 WO2006059724A1 PCT/JP2005/022202 JP2005022202W WO2006059724A1 WO 2006059724 A1 WO2006059724 A1 WO 2006059724A1 JP 2005022202 W JP2005022202 W JP 2005022202W WO 2006059724 A1 WO2006059724 A1 WO 2006059724A1
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- WO
- WIPO (PCT)
- Prior art keywords
- panel
- inner panel
- vehicle body
- wave
- cross
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D25/00—Superstructure or monocoque structure sub-units; Parts or details thereof not otherwise provided for
- B62D25/08—Front or rear portions
- B62D25/10—Bonnets or lids, e.g. for trucks, tractors, busses, work vehicles
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
- B60R21/00—Arrangements or fittings on vehicles for protecting or preventing injuries to occupants or pedestrians in case of accidents or other traffic risks
- B60R21/02—Occupant safety arrangements or fittings, e.g. crash pads
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
- B60R21/00—Arrangements or fittings on vehicles for protecting or preventing injuries to occupants or pedestrians in case of accidents or other traffic risks
- B60R21/34—Protecting non-occupants of a vehicle, e.g. pedestrians
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D25/00—Superstructure or monocoque structure sub-units; Parts or details thereof not otherwise provided for
- B62D25/02—Side panels
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D25/00—Superstructure or monocoque structure sub-units; Parts or details thereof not otherwise provided for
- B62D25/08—Front or rear portions
- B62D25/10—Bonnets or lids, e.g. for trucks, tractors, busses, work vehicles
- B62D25/105—Bonnets or lids, e.g. for trucks, tractors, busses, work vehicles for motor cars
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
- B60R21/00—Arrangements or fittings on vehicles for protecting or preventing injuries to occupants or pedestrians in case of accidents or other traffic risks
- B60R21/34—Protecting non-occupants of a vehicle, e.g. pedestrians
- B60R2021/343—Protecting non-occupants of a vehicle, e.g. pedestrians using deformable body panel, bodywork or components
Definitions
- the present invention relates to a vehicle body panel structure that is used as a panel for automobile body hoods, roofs, doors, trunk lids, etc., and has excellent head impact resistance in pedestrian protection, particularly bending rigidity and tension rigidity.
- the present invention relates to a body panel structure made of metal such as aluminum alloy or steel having excellent rigidity.
- panel structures of body members such as automobiles have an outer panel (referred to as an exterior panel or an outer plate: hereinafter referred to simply as an outer panel) and an inner panel (referred to as an inner panel or an inner panel). (Hereinafter referred to simply as “inner”) and a closed cross-sectional structure through a force space is used.
- outer panel referred to as an exterior panel or an outer plate: hereinafter referred to simply as an outer panel
- inner panel referred to as an inner panel or an inner panel
- f frequency
- c sound velocity
- aperture ratio aperture ratio
- t plate thickness
- b aperture radius (half the hole diameter)
- d thickness of the back air layer.
- Patent Document 1 Japanese Patent Laid-Open No. 2001-199287 describes claim 4 in the claim 4 and describes the hole diameter from 0.1 mm to 3 mm. There is.
- Patent Document 2 Japanese Patent Laid-Open No. 2003-50586
- Ueda Tanaka, Utsuno and others set a suitable hole diameter of 3 mm or less and an aperture ratio of 3% or less. It can be easily obtained if it is 1000HZ or less as described in kai 2001 122050.
- the frequency band where the exterior plate and the interior plate are formed so as to face each other and the sound absorption effect is a sound absorption coefficient of 0.3 or more.
- a porous soundproof structure having a width of 10% or more with respect to the resonance frequency has been proposed.
- the thickness of the interior panel ranges from 0.3 mm to lmm, and the aperture ratio ranges from 1% to 5%.
- the hole diameter ranges from 0.5 mm to 3 mm, and the effect of these parameters on the sound absorption rate has been investigated.
- the aperture ratio is 3% or less and the hole diameter is 3 mm or less, particularly when the hole diameter is 1 mm or less, a sufficient sound absorbing effect is obtained, and a predetermined effect seems to be obtained.
- the above publication further proposes a porous soundproof structure in which two or more interior boards are provided via an air layer.
- the vehicle body hood structure that satisfies both the sound absorbing structure and the pedestrian protection structure is still undeveloped.
- Patent Document 3 JP-A-6-298014
- Patent Document 4 JP-A-6-81407
- Patent Document 5 JP-A 2000-276178
- a wide-band sound absorption characteristic can be obtained by stacking a plurality of flat plate-shaped multi-hole plates and providing a plurality of back air layers whose cross-sectional shapes change.
- a wide range of resonance frequencies exist with changes in the thickness of the back air layer, and as a result, the sound absorption characteristic having the peak characteristic that appears in the case of only one perforated plate disappears. This is because a substantially uniform broadband sound absorption characteristic can be obtained in a wide frequency range.
- Patent Document 6 Japanese Patent Laid-Open No. 2003-226264
- Patent Document 7 Japanese Patent Laid-Open No. 2003-252246
- Patent Document 8 Japanese Patent Laid-Open No. 2003-261070
- HIC values head performance criteria
- HIC [1 / (t 2-t 1) ⁇ t 1 1 2 adt] 2 ⁇ 5 "2 tl)
- a is the three-axis combined acceleration at the center of gravity of the head (unit: G)
- tl is the time when tl ⁇ t2
- the action time (t2— (tl) is set to 15 msec or less.
- the collision resistance between an adult head and a child head In terms of sex, the HIC value of 1000 or less is stipulated as a condition that the hood should have. Among them, the head collision speed at the time of head collision test is 40kmZ, adult head (weight 4.8kg, outer diameter 165mm, collision angle 65 degrees) and child head (weight 2.5kg, outer diameter) 130mm, collision angle 50 degrees).
- the pedestrian head At the time of a head collision, the pedestrian head first collides with the outer and then undergoes deformation, and the reaction force is transmitted to the rigid parts such as the engine in the engine room via the inner. An excessive impact force is generated in the part.
- the first acceleration wave generated mainly by collision with the outer (generated approximately 5 ms after the start of the collision) and the second acceleration wave generated when the inner collides with the rigid body ( The collision starting force also occurs after approximately 5 ms.
- the magnitude of the first acceleration wave is mainly determined by the elasticity and rigidity of the outer, and the magnitude of the second acceleration wave is mainly determined by the plasticity and rigidity of the inner.
- the kinetic energy of the head is the force absorbed by the deformation energy of these outer and inner heads.
- the head movement distance exceeds the clearance between the outer body and a rigid object such as an engine, the head will react to the reaction force from the rigid object. You will be directly affected, and will receive an excessive impact force that greatly exceeds the HIC limit of 1000, resulting in fatal damage.
- the HIC value can be reduced even if the head movement distance is small (Issue 1).
- the rigid body such as the outer body and engine.
- WAD1500 a line with a contour distance of 1500mm from the ground cover at the front end of the vehicle body to the hood collision position
- Satisfying the HIC value of 1000 for both children and adults with different impact characteristics is extremely difficult and has been raised as a problem.
- WAD1500 line force The clearance between the outer and the rigid surface is just above the engine, and there is a demand for effective measures to improve impact resistance (EEVC Working Group 17 Report).
- the HIC value be uniform regardless of the collision site (Problem 2).
- the HIC value increases at the position just above the frame in the case of the beam-type hood structure and at the position of the apex of the cone in the case of the cone-type hood structure. This is because these parts receive a high reaction force from a rigid body whose deformation is small even if it collides with a rigid body part whose local rigidity is high. For this reason, from the viewpoint of safety, there is a demand for a hood structure that can obtain a generally uniform HIC value regardless of the collision site.
- A1 alloy material that can reduce the weight of the vehicle body (Issue 3). Even if an A1 alloy material that can be lightweight is used as the hood material, it is necessary to have excellent head crash resistance. A1 alloy material is often used for lightweight hoods, but in this case, it is generally considered disadvantageous from the viewpoint of pedestrian protection compared to the case of using iron. The elastic modulus and specific gravity of the A1 alloy material are both about one-third that of steel. To absorb the kinetic energy of the head with the hood, the film rigidity and weight of the A1 alloy hood as a panel structure are This is due to the lack of steel hoods.
- the bending stiffness of the plate is proportional to ET 3 (assuming Young's modulus E and plate thickness T), and the membrane stiffness is proportional to ET.
- the HIC value increases with the conventional hood structure, making it extremely difficult to satisfy the limit value of the HIC value.
- Patent Document 1 Japanese Patent Laid-Open No. 2001-199287
- Patent Document 2 Japanese Patent Laid-Open No. 2003-50586
- Patent Document 3 Japanese Patent Laid-Open No. 6-298014
- Patent Document 4 JP-A-6-81407
- Patent Document 5 Japanese Unexamined Patent Publication No. 2000-276178
- Patent Document 6 Japanese Patent Laid-Open No. 2003-226264
- Patent Document 7 Japanese Patent Laid-Open No. 2003-252246
- Patent Document 8 Japanese Unexamined Patent Publication No. 2003-261070
- the HIC value can be reduced even when the head movement distance is small.
- the present invention has been made in view of a serious problem, and can reduce the HIC value even when the head movement distance is small, and makes the HIC value uniform regardless of the collision portion with the hood. Furthermore, an object of the present invention is to provide a vehicle body panel structure that can sufficiently reduce the HIC value even with an A1 alloy hood and contributes to weight reduction of the vehicle body. Another object of the present invention is to provide a vehicle body panel structure having good sound absorption characteristics even without an insulator. Means for solving the problem
- the vehicle body panel structure according to the first invention of the present application includes an outer panel, an inner panel disposed on the inner surface of the outer panel, and a further inner surface of the inner panel.
- Each of the inner panel and the reinforcing inner panel has a plurality of irregularities whose corrugated cross-sectional shape is in the longitudinal direction of the vehicle body, and the outer panel and the inner panel are joined to each other.
- the direction in which the corrugated cross-sectional corrugations of the inner panel and the reinforced inner panel are formed with respect to the longitudinal direction of the vehicle body It is preferable to be assembled to the vehicle body so that it tilts.
- a vehicle body panel structure includes, as described in claim 4, an outer panel, an inner panel disposed on the inner surface of the outer panel, and a further inner surface of the inner panel.
- a reinforced inner panel, and the inner panel The first and second protrusions and reinforced inner panels each have a plurality of first irregularities formed so that the cross-sectional shape in the first direction forms a wave shape on the entire surface, and the cross-sectional shape in the second direction intersecting the first direction forms a wave shape.
- a vehicle body panel structure includes, as described in claim 5, an outer panel, an inner panel disposed on the inner surface of the outer panel, and a further inner surface of the inner panel.
- Each of the inner panel and the reinforcing inner panel has a plurality of concentric corrugations formed concentrically on the entire surface, and the outer panel and the inner panel
- a closed cross section formed by the inner panel and the reinforced inner panel is formed below the joint, and a closed section formed by the outer panel and the inner panel is formed above the joint between the inner panel and the reinforced inner panel.
- the panels are joined so as to have a cross section.
- a vehicle body panel structure includes an outer panel, an inner panel disposed on the inner surface of the outer panel, and a further inner surface of the inner panel.
- the inner panel and the reinforced inner panel have a plurality of irregularities having a corrugated cross-sectional shape over the entire surface in the longitudinal direction of the panel structure, and a corrugated cross-sectional shape intersecting the irregularities.
- Each panel is joined so as to have a closed cross section formed by the outer panel and the inner panel above the joint between the inner panel and the reinforced inner panel. It is characterized that you have.
- the double corrugation includes a wave in which the direction of the corrugated cross-sectional corrugation is parallel to the longitudinal direction of the panel structure. Orthogonal to wave It is preferable to have a double wave shape formed by the intersecting waves.
- the double corrugation is such that a direction in which the concave corrugated cross-sectional corrugation forms is oblique to a longitudinal direction of the panel structure. And a double wave formed by a wave that intersects this wave at a predetermined angle.
- a vehicle body panel structure includes an outer panel, an inner panel disposed on the inner surface of the outer panel, and a further inner surface of the inner panel.
- Each of the inner panel and the reinforced inner panel has a plurality of irregularities having a corrugated cross section on the entire surface, and the irregularities each have the corrugated cross section.
- Convex / concaves whose direction coincides with the width direction or longitudinal direction of the vehicle body, the corrugated shape of the cross section is inclined with respect to the longitudinal direction of the car body, and a plurality of first shapes are formed so that the cross-sectional shape in the first direction is corrugated A plurality of concavities and convexities, and a plurality of concentric circularly shaped cross-sectional irregularities, each of which has a plurality of second concaves and convexes so that the cross-sectional shape in the second direction intersecting the first direction forms a corrugation
- the cross-sectional shape is A combination of at least two of the corrugations of a double corrugation formed by a plurality of concavities and convexities forming a mold and a plurality of concavities and convexities whose cross-sectional shape intersects with the concavities and convexities.
- the double-wave hood structure using the inner corrugated cross section and the reinforced inner structure makes it possible to stretch the hood structure even if the outer and inner are thinned.
- the rigidity can be greatly increased.
- sufficient rigidity can be obtained with respect to bending rigidity and torsional rigidity, and as a result, deformation of the hood against an external load can be suppressed.
- pedestrian protection it is possible to increase the collision resistance in the collision between the head and the hood, improving safety,
- the HIC value can be reduced even when the head movement distance is small.
- AIC alloy hood can reduce the HIC value sufficiently. Etc. can be realized.
- the vehicle body panel structure of the present invention has a simple configuration in which the inner is a wave-type inner as described above, and, as in the prior art, the rigidity of the body can be increased without increasing the thickness of the inner. In addition, the bending rigidity can be increased, and light weight can be achieved. Press molding from a flat panel to the above-mentioned corrugated panel is easy, and the inner itself is easy to manufacture.
- a cross-sectional shape of the unevenness is preferably a spline shape.
- the cross-sectional shape of the unevenness may be a trapezoid.
- the cross-sectional shape of the unevenness is a wave shape, and a wave height or wavelength smaller than the wave height or wavelength of the wave shape. It may be a shape that is a combination of the corrugated shapes.
- a cross-sectional wave of the inner panel or the reinforced inner panel in a head collision in pedestrian protection, from the viewpoint of improving collision resistance, a cross-sectional wave of the inner panel or the reinforced inner panel.
- the mold shape preferably satisfies 0.5 ⁇ p / d ⁇ 2.8, where p is the wave wavelength and d is the pedestrian outer diameter. If p / d is within this range, the HIC value can be reduced.
- Such a configuration is applicable to the inner and the reinforcing inner, and can be applied to a trapezoidal shape or a spline shape in cross section.
- the cross-sectional corrugated shape of the inner panel or the reinforcing inner panel is a collision at a head collision in pedestrian protection.
- the wave height of the inner panel is hi
- the wave height of the reinforced inner panel is h2
- the outer diameter of the pedestrian's head is d
- 0.05 (hl + h2) / d ⁇ 0. 3 5 Is preferably satisfied. If hi + h2 is within this range, the HIC value can be reduced.
- Such a configuration can be applied to the inner and the reinforcing inner, and can be applied to a trapezoidal shape or a spline shape in cross section. In the case of a flat plate with a reinforced inner wave height S of zero, 0.05 ⁇ hl / d ⁇ 0.35.
- any one of the force of the outer panel, the inner panel, and the reinforcing inner panel is an aluminum compound.
- it is made of gold or steel.
- the inner panel and the outer panel are joined by flexible coupling.
- the soft joint portions are arranged in a staggered manner or in a dispersed manner.
- the inner panel and the Z or the reinforced inner panel have a sound absorbing effect with an aperture ratio of 3% or less and a hole diameter of 3mm or less. It is preferable that a plurality of through holes are formed.
- the sound-absorbing effect follows the resonance principle of Helm Honorets, and has a closed cross-sectional structure characteristic compared with the conventional porous sound-absorbing panel disclosed in JP-A-61-249878, JP-A-2000-56777, and JP-A-2003-20586. If a small hole is made in the inner panel of the mold hood, the hood should have a sound absorbing effect.
- a steel sheet with a thickness of 0.5 mm has a sound absorption effect of about 0.5 in the frequency region below lkHZ when the aperture ratio is 1% and the hole diameter is 0.5 mm.
- a steel plate with a thickness of 0.8 mm seems to have the same effect with an aperture ratio of 2% and a hole diameter of 2 mm.
- the aperture ratio is 3% or less and the hole diameter is 3 mm or less.
- the hood has two air layers, an outer and an inner, an inner and a reinforcing inner, and a fine hole is provided in the inner and the reinforcing inner.
- the size of the fine holes is quite difficult to punch by punching fine holes that are less than about the plate thickness based on common general knowledge in manufacturing.If mass production is assumed, the hole diameter is 0. In the case of 5 mm, the range is from 0.5 mm to 3 mm, and in the case of a plate thickness of 0.8 mm, the force is limited to a range of about 0.8 mm.
- the wavelength or wave height of the inner panel and Z or the reinforcing inner panel may be determined in the vehicle body width direction or the vehicle body longitudinal direction. It is preferred that it be non-uniform.
- the sound absorbing property may be improved according to claim 20.
- the wavelength or wave height of the left and right waveforms in one wavelength in the cross-sectional wave shape of the inner panel and Z or the reinforced inner panel is asymmetric and has a distorted waveform cross section.
- the outer panel is made of steel, and the inner panel and the reinforcing inner panel are made of an aluminum alloy. Is preferred to be.
- the weight of the outer panel increases, the magnitude of the first wave of acceleration at the time of head collision increases to about 200 G, the second acceleration decreases, and the HIC value It can be suppressed to 1000 or less.
- the inner surface of the outer panel is made of one or more of steel, aluminum alloy, or lead to improve pedestrian protection performance. It is preferable that the reinforcing plate is affixed. Increasing the local weight of the outer panel, increasing the magnitude of the first acceleration wave at the time of head collision, and setting it to about 200G will reduce the second acceleration wave and suppress the HIC value to 1000 or less. it can. The placement location, number, thickness, etc. of the metal plates are appropriately selected.
- the vehicle body panel structure according to the present invention is applicable to automobile roofs, doors, and trunk lids. Further, the vehicle body panel structure according to the present invention is applicable to a roof, a door, a floor, or a side wall of a railway vehicle.
- the vehicle body panel structure according to the present invention has a head in a closed space between the outer panel and the inner panel or a closed space between the inner panel and the reinforcing inner panel. It is preferable to apply a predetermined internal pressure having a collision energy absorption effect. This reduces the head acceleration second wave, reduces the HIC value, and improves pedestrian protection performance.
- a bag-like object is disposed in a closed space between the outer panel and the inner panel or a closed space between the inner panel and the reinforcing inner panel. It is preferable to apply an internal pressure in the bag-like material.
- the bag-like material for example, a natural or synthetic resin is preferably used.
- the vehicle body panel structure according to the present invention absorbs energy in a closed space between the outer panel and the inner panel or a closed space between the inner panel and the reinforced inner panel. It is preferable to embed a material. Thereby, the absorption effect of the head collision energy of the hood is increased, and the pedestrian protection performance is improved.
- the energy absorbing material for example, foamed styrene is preferably used.
- a vehicle body panel structure includes, as described in claim 30, an outer panel and a bead having a cross-sectional corrugated shape disposed on the inner surface of the outer panel and parallel to the vehicle width direction.
- the inner panel has a corrugated shape of 0.5 ⁇ p / d ⁇ when the wave wavelength is p and the pedestrian's head outer diameter is d. 2. It is characterized by satisfying 0.05 ⁇ hl / d ⁇ 0.35 when the force satisfying 8 or the wave height of the inner panel is hi and the pedestrian head outer diameter is d.
- This body panel structure is lightweight and has excellent pedestrian protection performance and sound absorption performance.
- the wave height hla of the inner panel in the adult head collision range is the above in the child head collision range.
- the inner panel wave height is larger than hlc, which is preferred.
- the vehicle body panel structure is lightweight and has excellent pedestrian protection performance and sound absorption performance.
- the cross-sectional corrugated shape of the inner panel is a double wave in the center of the panel. It is preferable to have a corrugated shape other than the mold shape. As a result, a vehicle body panel structure excellent in pedestrian protection can be obtained.
- a vehicle body panel structure according to a seventh invention of the present application comprises, as described in claim 33, an outer panel and a bead having a cross-sectional wave shape disposed on the inner surface of the outer panel and parallel to the vehicle width direction.
- a vehicle body panel structure combined with a reinforcing inner panel having a cross-sectional corrugated bead parallel to the direction of the inner panel or the reinforcing inner panel has a cross-sectional corrugated shape in the adult head collision range.
- the corrugated shape of the cross section of the inner panel or the reinforced inner panel is within an adult head collision range.
- the wave height of the inner panel is hla
- the wave height of the reinforced inner panel is h2a
- the adult head outer diameter is da
- 0.05 (hla + h2a) / da ⁇ 0.35 is satisfied
- the wave height of the inner panel in the child head collision range is hlc
- the wave height of the reinforcing inner panel is h2c
- the child's head outer diameter is dc
- 0.05 (hlc + h2c) / dc ⁇ 0.35 Is preferably satisfied. This gives the optimum value of the wave height for pedestrian protection.
- the cross-sectional corrugated shape of the inner panel has a double wave shape at the center of the panel. It is preferable to have a corrugated shape other than the mold shape. As a result, a vehicle body panel structure excellent in pedestrian protection can be obtained.
- the inner panel and the reinforcing inner panel each have a cross-sectional corrugated shape having a different wavelength or wave height. It is.
- the inner surface of the reinforcing inner panel is the same as or different from the inner panel or the reinforcing inner panel. This is done by placing a second reinforcing inner panel with a corrugated cross section.
- the inner panel, the reinforcing inner panel, or the second reinforcing inner panel may have a corrugated cross-sectional shape.
- the inner panel, the reinforcing inner panel, or the second reinforcing inner panel is not separated by a wave and It can also have a partially broken wave. By doing so, a vehicle body panel structure excellent in pedestrian protection can be obtained.
- the hood tension rigidity can be remarkably increased.
- a vehicle body hood structure having sufficient torsional rigidity and bending rigidity can be provided.
- the HIC value can be reduced even if the clearance between the outer and the rigid body is small, the HIC value is almost uniform regardless of the location of collision with the hood, and even an aluminum hood is sufficient. It is possible to provide a pedestrian protection vehicle body hood structure excellent in head collision resistance that can reduce the value.
- a porous plate for the inner or reinforcing inner it is possible to provide a sound-absorbing vehicle body hood structure having broadband sound-absorbing characteristics and excellent pedestrian protection performance.
- the static rigidity of the hood can be increased by the substantially trapezoidal inner or reinforcing inner, and the head collision in pedestrian protection can be achieved.
- the head acceleration can be reduced.
- the static rigidity of the hood can be increased by the inner or the reinforced inner in which the substantially corrugated shape is superimposed on the approximately corrugated shape, and walking is also possible. Head acceleration due to head collision in person protection can be reduced.
- the wavelength and wave of the double-wave hood structure The preferable range of high is as shown in claims 13 and 14 and is a wide preferable range.
- the hood is made of aluminum or steel.
- the joint between the outer and the inner is made into a soft joint, and the joint portions are arranged in a staggered manner, thereby providing excellent pedestrian protection.
- the vehicle body panel structure is obtained.
- the inner and the reinforcing inner are preferably rigidly connected.
- the use of a perforated plate having a closing rate of 3% or less and a hole diameter of 3 mm or less as the inner or reinforcing inner makes it possible to obtain a vehicle body having excellent broadband sound absorption characteristics.
- a food panel can be realized.
- the wavelength or wave height of the inner panel and the reinforcing inner panel is not set in the vehicle body width direction or the vehicle body longitudinal direction.
- the left and right wave shapes in one wavelength are asymmetric with respect to the wavelength or wave height, Due to the distorted wave-shaped cross-section, the natural vibration mode of the sound field is complicated, the sound absorption characteristics are wideband, and the sound absorption characteristics are improved.
- the outer panel is made of steel, and the inner panel and the reinforcing inner are made of aluminum or an aluminum alloy.
- the head acceleration first wave increases to about 200G and the head acceleration second wave decreases, resulting in an HIC value. Decreases.
- the vehicle body panel structure can be applied to a roof, a door, a trunk lid of a vehicle body, or a roof, a door, a floor, a side wall, etc. of a railway vehicle. Or it can improve the collision resistance of railway vehicles and can also enhance the sound absorption effect.
- an energy absorbing member such as a foaming polystyrene is provided in a closed space between the outer panel and the inner panel or a closed space between the inner panel and the reinforcing inner panel.
- the inner panel and the outer panel each having a substantially wave-shaped bead substantially parallel to the vehicle width direction are combined.
- the vehicle body panel structure it is possible to provide a vehicle body panel structure that is lightweight and has excellent pedestrian protection performance or sound absorption performance.
- the inner wave height (hla) force in the adult head collision range The inner wave height (hlc) in the child head collision range By making it larger, it is possible to provide a vehicle body panel structure that is lightweight and has excellent pedestrian protection performance or sound absorption performance.
- a hood excellent in pedestrian protection can be provided.
- the inner panel having the corrugated cross-sectional shape bead substantially parallel to the vehicle width direction, the reinforcing inner and the outer
- the vehicle body panel structure combined with the Force that wavelength (pa) satisfies 0.5 ⁇ pa / da ⁇ 2.8, or wavelength (pc) in child head collision range satisfies 0.5 ⁇ pc / dc ⁇ 2.8
- the optimum wavelength value for pedestrian protection is obtained.
- the wave height (hla) of the inner and the wave height (h2a) of the reinforcing inner in the adult head collision range are 0.05 (hla). + h2a) / d ⁇ 0.
- a hood structure excellent in pedestrian protection can be provided.
- a hood structure excellent in pedestrian protection can be provided.
- a hood structure excellent in pedestrian protection can be provided as in the above-described invention.
- FIG. 1 is a perspective view showing an embodiment of an inner in the present invention.
- FIG. 2 is a cross-sectional view taken along line AA in FIG.
- FIG. 3 is a perspective view of a vehicle body panel structure according to the present invention.
- FIG. 4 is a cross-sectional view of a double wave type vehicle body panel structure having a spline type inner according to the present invention.
- FIG. 5 is a perspective view showing an embodiment of a spline type inner in the present invention.
- FIG. 6 is a cross-sectional view showing an embodiment of a spline type inner in the present invention.
- FIG. 7 is a cross-sectional view showing an embodiment of a substantially trapezoidal wave inner in the present invention.
- FIG. 8 is a cross-sectional view showing an embodiment of a substantially wave-type inner in the present invention.
- FIG. 9 is a cross-sectional view showing an embodiment of a substantially wave type inner in the present invention.
- FIG. 10 is a cross-sectional view showing an embodiment of a substantially wave-type inner in the present invention.
- FIG. 11 is a cross-sectional view showing an embodiment of a substantially wave-type inner in the present invention.
- FIG. 12 is a cross-sectional view showing an embodiment of a substantially wave type inner in the present invention.
- 13 A cross-sectional view showing an embodiment of a substantially wave-type inner in which small waves are superimposed in the present invention.
- FIG. 14 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 15 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 16 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 17 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 18 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 19 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 20 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 21 is a schematic diagram (side view) of a head collision model of a double wave type vehicle body panel structure according to the present invention.
- FIG. 22 is a schematic view (front view) of a head collision model of a double wave type vehicle body panel structure according to the present invention.
- FIG. 23 is a model view (perspective view) of a corrugated inner one and a head model according to the present invention.
- FIG. 24 is a model view (perspective view) of a double wave type vehicle body panel structure according to the present invention.
- FIG. 26 is an explanatory diagram showing a head acceleration waveform in the double wave type vehicle body panel structure according to the present invention.
- FIG. 27 is an explanatory diagram showing the relationship between the clearance L and the HIC value.
- FIG. 30 is a perspective view showing a head collision position in the conventional wave type hood structure.
- FIG. 31 is a schematic view showing an adhesion portion between an outer and an inner.
- FIG. 32 is a schematic diagram showing the relationship between the frequency and the aperture ratio in a perforated plate.
- FIG. 33 is a schematic view showing the relationship between the hole diameter and the aperture ratio in a perforated plate.
- FIG. 34 is a schematic diagram showing the relationship between the hole diameter and the aperture ratio in a perforated plate.
- FIG. 35 is a schematic diagram showing the relationship between the back air layer and the frequency in a perforated plate.
- FIG. 36 is a diagram showing a sound field eigenvalue analysis model (two-dimensional slit model) in a double wave type vehicle body panel structure.
- FIG. 37 is a diagram showing a result of sound field eigenvalue analysis in a double-wave body panel structure.
- FIG. 38 is a diagram showing a sound field eigenvalue analysis result in a double wave type vehicle body panel structure.
- FIG. 39 is a diagram showing a result of sound field eigenvalue analysis in a double wave type vehicle body panel structure.
- FIG. 40 is a diagram showing a sound field eigenvalue analysis result in a double wave type vehicle body panel structure.
- FIG. 41 is a diagram showing a sound field eigenvalue analysis result in a double wave type vehicle body panel structure.
- FIG. 42 is a diagram showing a sound field eigenvalue analysis result in a double wave type vehicle body panel structure.
- FIG. 47 is an explanatory view showing a joined state between the inner one and the reinforcing inner one.
- FIG. 49 is an explanatory diagram of a crash bead of a double wave type vehicle body panel structure.
- FIG. 50 is an explanatory diagram showing a head acceleration waveform for suppressing the HIC value to 1000 or less.
- FIG. 51 is an explanatory diagram when a reinforcing plate is attached to the outer lower surface of the double-wave type vehicle body panel structure.
- FIG. 52 is an explanatory diagram when eight reinforcing plates are attached to the outer lower surface of the double-wave body panel structure.
- FIG. 53 is a view showing a state in which the outer, inner, and reinforcing inner of the double wave type vehicle body panel structure are coupled with rivets or the like.
- FIG. 54 is a cross-sectional view of a double-wave type vehicle body panel structure in which a rubber or resin bag is provided to ensure the internal pressure sealability.
- FIG. 55 is an explanatory view showing a structure in which an energy absorbing member is embedded in a closed space between an inner panel and a reinforced inner panel.
- FIG. 56 is a perspective view showing an embodiment of a corrugated inner in the present invention.
- FIG. 57 is a perspective view showing an inner and a head collision position in a structure in which a reinforcing inner having a corrugated bead in the vehicle width direction and an inner having a corrugated bead in the longitudinal direction of the vehicle body are combined.
- FIG. 58 is a perspective view showing a reinforcing inner in a structure in which a reinforcing inner having corrugated beads in the vehicle width direction and an inner having corrugated beads in the longitudinal direction of the vehicle body are combined.
- ⁇ 59 This is a comparison of the analysis results of a structure that combines a reinforced inner with a corrugated bead in the vehicle width direction and an inner one with a corrugated bead in the longitudinal direction of the vehicle body.
- Vehicle width Fig. 6 is a diagram comparing the analysis results of a single-wave structure with an inner with a corrugated bead in the direction compared to a conventional structure.
- FIG. 61 is an explanatory diagram showing an analysis model of a double-wave type vehicle body panel structure in which an inner having a wave-shaped bead in the vehicle width direction and a reinforcing inner are combined.
- FIG. 62 is an explanatory diagram showing an analysis model of a double-wave type vehicle body panel structure in which an inner having a wave-shaped bead in the vehicle width direction and a reinforcing inner are combined.
- FIG. 63 is an explanatory diagram showing an analysis model of a double-wave body panel structure that combines an inner having a corrugated bead in the vehicle width direction and a reinforcing inner.
- FIG. 64 is a view showing an analysis result of a double wave type vehicle body panel structure in which an inner having a wave type bead in the vehicle width direction and a reinforcing inner are combined.
- FIG. 65 is a view showing an analysis result of a double wave type vehicle body panel structure in which an inner having a wave type bead in the vehicle width direction and a reinforcing inner are combined.
- FIG. 66 is a diagram showing an analysis result of a double wave type vehicle body panel structure in which an inner one having a corrugated bead in the vehicle width direction and a reinforcing inner are combined with a conventional analysis result.
- FIG. 67 is a view showing an analysis model of a double-wave type vehicle body panel structure in which a corrugated bead in the vehicle width direction and a corrugated bead in the longitudinal direction of the vehicle body are combined with a reinforcing inner.
- FIG. 68 is a view showing an analysis model of a double-wave type vehicle body panel structure in which a reinforced inner is combined with a corrugated bead in the vehicle width direction and a corrugated bead in the longitudinal direction of the vehicle body.
- FIG. 69 is a diagram showing an analysis result of a double wave type vehicle body panel structure in which a wavy bead in the vehicle width direction and a wavy bead in the longitudinal direction of the vehicle body are combined with a reinforcing inner.
- FIG. 70 is a diagram showing an analysis result of a double-wave type vehicle body panel structure in which an inner and a reinforcing inner mixed with wave-shaped beads in the vehicle width direction and wave-shaped beads in the vehicle body longitudinal direction are combined.
- FIG. 71 is a diagram showing an analysis result of a double-wave type vehicle body panel structure in which a wavy bead in a vehicle width direction and a wavy bead in a longitudinal direction of a vehicle body are mixed and a reinforcing inner is combined.
- FIG. 72 shows a cross-sectional shape of a corrugated vehicle panel structure having corrugated beads in the vehicle width direction and corrugated bead inners in the longitudinal direction of the vehicle body.
- FIG. 73 is a cross-sectional view of a corrugated vehicle panel structure having corrugated beads in the vehicle width direction and corrugated bead inners in the longitudinal direction of the vehicle body.
- FIG. 74 is a view showing a cross-sectional shape of a double wave type vehicle body panel structure having a wave type inner one in the vehicle width direction and a wave type reinforcing inner.
- FIG. 75 is a cross-sectional view of a double-wave body panel structure having a corrugated inner one in the vehicle width direction and a corrugated reinforcing inner.
- FIG. 76 is a view showing a cross-sectional shape of a double wave type vehicle body panel structure in which a wave shape bead in the vehicle width direction and a wave shape bead in the vehicle body longitudinal direction are combined.
- FIG. 77 is a view showing a cross-sectional shape of a double wave type vehicle body panel structure in which a wavy bead in the vehicle width direction and a wavy bead in the longitudinal direction of the vehicle body are combined.
- FIG. 78 is a diagram showing an example of an inner body panel body structure that does not cross twice in the center of the body.
- FIG. 79 is a view showing an example of an inner body of a vehicle body panel structure that does not cross twice in the center of the vehicle body.
- FIG. 80 is a diagram showing an example of an inner body panel structure that does not cross twice in the center of the body.
- FIG. 81 is a diagram showing an example of an inner body panel body structure that does not cross twice in the center of the body.
- FIG. 82 is a diagram showing an example of an inner body panel structure that does not cross twice in the center of the body.
- FIG. 83 is a diagram showing an example of an inner body panel body structure that does not cross twice in the center of the body.
- FIG. 84 is a diagram showing an example of an inner body panel body structure that does not cross twice in the center of the body.
- FIG. 85 is a diagram showing an example of an inner body of a vehicle body panel structure that does not cross twice in the center of the vehicle body.
- FIG. 86 is a diagram showing an example of an inner body panel body structure that does not cross twice in the center of the body.
- FIG. 87 is a diagram showing an example of an inner body of a vehicle body panel structure that does not cross twice in the center of the vehicle body.
- FIG. 88 is a diagram showing an example of an inner body of a vehicle body panel structure that does not cross twice in the center of the vehicle body.
- FIG. 89] is a diagram showing an example of an inner body of a vehicle body panel structure having one place that intersects twice in the center of the body.
- FIG. 90 is a diagram showing an example of the inner body of the vehicle body panel structure having one place that intersects twice in the center of the vehicle body.
- FIG. 91 is a diagram showing a relationship between a wavelength and an HIC value in a single transverse wave vehicle body panel structure.
- FIG. 92 is a diagram showing a relationship between a wave height and an HIC value in a single transverse wave vehicle body panel structure.
- FIG. 93 is a diagram showing the relationship between the clearance and the HIC value in the single transverse wave vehicle body panel structure.
- FIG. 94 is a diagram showing a relationship between a wavelength and an HIC value in a double transverse wave vehicle body panel structure.
- FIG. 95 is a diagram showing the relationship between the wave height and the HIC value in a double transverse wave vehicle body panel structure.
- FIG. 96 A diagram showing the relationship between the clearance and the HIC value in the double transverse wave vehicle body panel structure.
- This is a diagram showing the distribution shape of waves, and a diagram showing the mixed shape of transverse waves and longitudinal waves.
- FIG. 98 is a diagram showing a wave distribution shape, and showing an example of a change in the shape of a longitudinal wave.
- FIG. 99 is a view showing the cross-sectional shapes of the inner one and the reinforcing inner one.
- FIG. 100 is a diagram showing the cross-sectional shapes of the inner and reinforcing inners.
- FIG. 101 is an explanatory view showing a vehicle body hood structure configured with outer, inner, reinforcing inner, and second reinforcing inner power.
- ⁇ 102 shows an analysis model diagram of a rectangular shape composed of an outer and corrugated inner
- FIG. 103 is an analysis model diagram in which an outer is not displayed in the analysis model.
- FIG. 104 is an analysis result diagram showing the influence of the head collision direction and the wave direction on the HIC value.
- FIG. 105 is a diagram showing an inner, a reinforcing inner, or a second reinforcing inner in which the direction of the wave is substantially the longitudinal direction of the vehicle body and a part of the wave is divided.
- FIG. 106 is a diagram showing an inner, a reinforcing inner, or a second reinforcing inner in which the direction of the wave is substantially the width direction of the vehicle body and a part of the wave is divided.
- FIG. 107 is a diagram showing an inner, a reinforcing inner, or a second reinforcing inner in which the direction of the wave is a substantially oblique direction of the vehicle body and a part of the wave is divided.
- FIG. 108 is a diagram showing an inner, a reinforcing inner, or a second reinforcing inner in which the direction of the wave is an arbitrary direction of the vehicle body and a part of the wave is divided.
- the direction of the wave is substantially the longitudinal direction of the vehicle body, and shows a wave in which a part of the wave is divided and an inner, reinforcing inner or second reinforcing inner in which the waves are mixed. It is a figure.
- the direction of the wave is substantially the longitudinal direction of the vehicle body, and shows a wave in which a part of the wave is divided and an inner, a reinforcing inner or a second reinforcing inner in which the waves are mixed. It is a figure.
- FIG. 111 is a diagram showing a wave in which the direction of the wave is an oblique direction of the vehicle body and a part of the wave is divided and an inner, a reinforcing inner or a second reinforcing inner in which the waves are mixed.
- the direction of the wave is the substantially vehicle width direction of the vehicle body, and a wave in which a part of the wave is divided is divided into an inner mixed with the wave, a reinforcing inner, or a second reinforcing inner.
- FIG. 114 is a diagram showing a head acceleration waveform when the wavelength is 160 mm, the wave height is 30 mm, and the clearance is 70 mm in the single transverse wave hood structure.
- 115 is a modified view at the time of a head collision after 0 msec in FIG. 114.
- FIG. 116 is a modified view at the time of a head collision after 6 msec in FIG.
- FIG. 117 is a modified view at the time of a head collision after 11 msec in FIG.
- FIG. 118 is a modified view at the time of a head collision after 17 msec in FIG. 114.
- FIG. 119 is a perspective view showing an inner panel having a transverse wave double structure in which the wavelength is waved.
- FIG. 120 is a perspective view showing another inner panel having another transverse wave structure in which the wavelength is waved.
- FIG. 121 is a perspective view showing an inner panel having a double-sided transverse wave structure whose wavelength is non-target, and 122 is a perspective view showing another inner panel having a double-sided wave structure whose wavelength is non-target.
- ⁇ 123 It is a perspective view showing an inner panel of a single-sided transverse wave whose wavelength is left and right non-target.
- Adhesive such as rosin
- FIG. 1 is a perspective view of an inner panel (inner) in an embodiment of a vehicle body panel structure according to the present invention
- FIG. 2 is a cross-sectional view taken along line AA in FIG. In Fig. 1, the mesh is inserted so that the corrugated shape is easy to understand! /
- the inner la is represented by an aluminum alloy or a high-tensile steel plate. It is made of lightweight and high-strength metal, and the length of the vehicle body extends over the entire panel except for the peripheral edges 9a, 9b (9a: vehicle body front side, 9b: driver's seat side) and 10a, 10b (vehicle width side).
- a plurality of substantially wave-shaped beads (projections) 2a extending in the vertical direction are provided substantially parallel to each other. It should be noted that curved wave beads such as concentric circles or ellipses, which will be described later, are formed substantially in parallel with each other.
- a corrugated bead 2a has an arcuate bead convex part 5 that protrudes toward the back side of the outer panel (outer) 4a and has a gentle cross section in the longitudinal direction or a longitudinal shape.
- a corrugation having a curvilinear force continuous in a sine wave shape in the vehicle width direction is formed by an arcuate shape having a gentle cross-section that is recessed on the opposite side or a bead concave portion 6 having a bowl shape in the longitudinal direction.
- seven linear corrugated beads 2a are provided on the surface of the inner la in parallel with each other and at a distance from each other.
- the corrugated bead 2a shown in FIG. 1 and FIG. 2 includes the bead recess 6 and has substantially the same width in the longitudinal direction.
- the corrugated bead 2a is not necessarily required to have the same width in the longitudinal direction including the bead recess 6.
- a constriction or depression that is partially narrowed may be provided to form a shape that protects the occupant by absorbing the impact as a starting point for the entire inner deformation in the event of a vehicle collision.
- the width may be gradually narrowed or the width may be increased according to the vehicle body design.
- the conditions such as the cross-sectional shape (width, height, inclination angle of the slope), number (number), and length of the corrugated bead 2a and the bead recess 6 are not particularly limited to the present embodiment. Absent. However, in consideration of the display of rigidity and the ease of molding, it is preferable to select a range force in which the wave height h of the cross-sectional shape is 10 to 60 mm and the wavelength p is 90 to 300 mm.
- the cross-sectional shape and conditions of these substantially wave-shaped beads 2a and bead recesses 6 are tension rigidity, torsional rigidity, bending rigidity, and that molding is possible or easy (formability), etc. It is suitably selected from the relationship.
- the thickness of the outer edge portion (outer peripheral portion) of the inner is made thicker than the thickness of the central portion, and the tip of the panel or panel structure is applied. It can be combined with other means to enhance the rigidity of the panel or panel structure, etc. as appropriate for bending load.
- a reinforced inner panel (hereinafter simply referred to as "reinforced inner one") 40 is integrated so that the apex portions of the inner one and the inner one are coupled.
- the connecting portion is connected using, for example, an adhesive or a rivet.
- the double wave structure increases the absorbed energy at the time of head collision, improves the head collision resistance, and increases the sound absorption rate from the viewpoint of noise countermeasures.
- the cross-sectional shape of the inner and the reinforcing inner is basically a sinusoidal substantially wave shape, but it is more practical to use a spline curve with a high degree of curvature.
- . 4 to 6 show examples in which the cross-sectional shape is a spline curve.
- Fig. 4 is a diagram showing a cut surface in the vehicle width direction at the center of the hood. As shown in Fig. 4, the engine room usually has a complicated arrangement of parts, and this spline shape enables a flexible inner shape design that takes into account the parts arrangement.
- FIG. 5 is a perspective view showing the inner part of the spline shape, and FIGS.
- the reinforcing inner has the same shape as the inner one, and the combination of the cross-sectional shapes of the inner and the reinforcing inner is basically the same shape, and the wave length is different but the wavelength is the same. However, it may be possible to combine different shapes.
- a spline curve is a curve formed by smoothly connecting curves having different large and small curvatures.
- the spline waveform is formed by superimposing a plurality of waves having different large and small curvatures such as an embossed shape on the basis of a substantially wave-shaped waveform (including a substantially trapezoidal shape) based on the same meaning as a spline curve. It is defined as a waveform.
- the embossed shape may extend over the entire inner and reinforced inner areas, or may be limited to local areas such as the R section.
- the cross-sectional shape of the inner and the reinforcing inner according to the present invention is basically a sine curve.
- a substantially trapezoidal shape may be used for the cross-sectional shape.
- Figure 7 (a) shows a schematic diagram of the trapezoidal cross section
- Fig. 7 (b) shows a variation of the trapezoidal cross section.
- Figure 7 (a) shows the case where both the convex and concave parts are trapezoidal
- Figure 7 (b) shows the case where the convex part is trapezoidal and the concave part is arcuate.
- these trapezoidal corrugations are such that both the inner and the reinforcing inner have the same shape, but one of the inner and the reinforcing inner may be a sine curve or a spline curve.
- local rigidity may be adjusted by providing small irregularities or overlapping small waves on the curved surfaces of the inner and reinforcing inners. If unevenness is provided by a small bead extending in the longitudinal direction of the vehicle body, the rigidity in the vehicle body direction is increased and the head collision resistance may be locally increased.
- FIG. 8 to 10 are cross-sectional views showing an example of a double-wave cross-sectional shape when the inner one and the reinforcing inner one are vertically symmetrical.
- Figure 8 shows five cases in which the inner and reinforcing inners are vertically symmetrical.
- 8A to 8E a vehicle body panel structure is formed by the outer 4 and the vertically symmetrical inner 1 and reinforcing inner 40 disposed on the back surface thereof.
- Figure 9 shows one case where the inner and reinforcing inners are vertically symmetrical.
- the inner 1 and the reinforcing inner 40 in FIG. 9 are examples in which predetermined intervals are provided between the recesses or between the protrusions
- FIG. 10 shows one case in which the inner and the reinforcing inner are symmetrical in the vertical direction. This is an example in which fine irregularities are provided on the surface of the cross-sectional curve.
- Figs. 11 (a) to 11 (d) and Fig. 12 are examples in the case of asymmetrical upper and lower, and Fig. 11 (a) is an example in which a small convex portion is provided in the concave portion of the reinforcing inner 40, Fig. 11 (b) is an example in which a part of the convex part of the inner 1 is a straight line, and FIG. 11 (c) is a combination of the inner 1 in which a part of the convex part is a straight line and the reinforcing inner 40 having a small convex part in the concave part.
- FIG. 11 (d) shows an example in which a part of the concave portion of the reinforcing inner 40 is a straight line.
- FIG. 12 is an example in which fine irregularities are provided on the surface of the cross-section curve of the reinforcing inner 40.
- FIGS. 13 (a) to (d) are diagrams showing a double-wave cross-sectional shape when the inner and the reinforcing inner are vertically symmetric
- FIGS. 13 (b) to (d) FIG. 14 is a diagram showing an example in which small waves are superimposed on the cross-sectional corrugated shape of FIG. 13 (a) so as to be vertically symmetrical. That is, in FIG. 13 (a), this vehicle body panel structure shows a cross-sectional shape before the wavelet is overlapped, and shows a case where the inner 1 and the reinforcing inner 40 are vertically symmetrical.
- Fig. 13 (b) shows one wavelength in Fig. 13 (a).
- FIG. 13 (c) shows the cross-sectional shape of two small waves superimposed on Fig. 13 (c).
- Fig. 13 (d) shows the cross-sectional shape of three small waves superimposed on one wavelength in Fig. 13 (a).
- FIG. 13 (a) is a diagram showing a cross-sectional shape in which four small waves are superimposed on one wavelength.
- the plurality of substantially wave-shaped beads are substantially parallel to the vehicle width direction or longitudinal direction of the panel structure, substantially oblique to the longitudinal direction of the panel structure, or approximately the panel structure. It is preferable that they are provided in a concentric arrangement with respect to the center. Further, the plurality of substantially corrugated beads have a corrugated cross-sectional shape in the second direction intersecting the first direction and the first irregularities formed so that the cross-sectional shape in the first direction is corrugated. Thus, a plurality of second irregularities may be formed.
- FIGS. 14 to 17 and 56 show perspective views of examples of the substantially wave-shaped bead arrangement of the inner and the reinforcing inner, and FIG. 73 shows a cross-sectional view thereof.
- the inner If in FIG. 14 is formed in a region in which linear corrugated beads 2f and 2g whose ridgelines are inclined with respect to the longitudinal direction of the vehicle body are divided on both sides in the vehicle body width direction.
- the corrugated beads 2f and 2g shown in FIG. 14 are arranged in a nose shape so that their ridge lines meet each other in the vehicle body direction.
- the inner lg in FIG. 15 is a force in which linear corrugated beads 2f and 2g whose ridgelines are inclined with respect to the longitudinal direction of the vehicle body are formed in a region divided in the vehicle body width direction.
- the corrugated beads 2f and 2g shown in Fig. 1 are arranged in an inverted C shape with their ridges facing away from each other!
- the inner lb of Fig. 16 has a plurality of substantially wave-shaped beads 2b concentrically provided substantially in parallel with each other over the entire surface of the panel. That is, the uneven shape of the corrugated bead 2b of the inner lb shown in FIG. 16 is a concentric circle.
- a plurality of substantially wave-shaped beads 2c and 2d are provided in an elliptical shape so as to be substantially parallel to each other over the entire surface of the panel. That is, the inner lc shown in FIG. 17 is provided with an elliptical corrugated bead 2d at the center and linear corrugated beads 2c on both sides thereof.
- a plurality of substantially wave-shaped beads intersect a wave substantially parallel to the longitudinal direction of the panel structure and a wave substantially perpendicular thereto. It can be provided in a double wave array. Examples of the substantially wave type bead arrangement of the inner and the reinforcing inner are shown as perspective views in FIGS. 18 and 19, respectively.
- the inner Id in Fig. 18 increases the bonding area between the outer and inner ones in such a manner that a plurality of substantially wave-shaped beads 2a, 2e force S are perpendicular to each other across the entire panel. That is, in the inner Id shown in FIG. 18, as in FIG. 1, the corrugated bead 2a having a straight ridge line extending in the longitudinal direction of the vehicle and the corrugated 2e extending in the vehicle width direction are orthogonal to each other. It is formed like this.
- the inner If in Fig. 19 has a plurality of substantially wave-shaped beads 2a (vertical beads) and 2e (horizontal beads) that run vertically and horizontally across the entire surface of the panel. The bonding area of is reduced.
- the corrugated bead 2a and 2e wave cross-sectional shape shown in FIG. 19 is a sine curve.
- the inner If shown in FIG. 19 is formed so that the corrugated bead 2a whose ridgeline extends in the vehicle body longitudinal direction and the corrugated bead 2e whose ridgeline extends in the vehicle body width direction are orthogonal to each other.
- the cross-sectional shape of 2e is a spline shape.
- FIG. 20 shows a perspective view of an example of a substantially wave-type bead arrangement of the inner and the reinforcing inner.
- the inner lh shown in FIG. 20 has straight corrugated beads 2f and 2g extending at an incline with respect to the longitudinal direction of the vehicle body, and both are formed on the entire surface of the vehicle body panel.
- FIG. 16 shows an aspect in which the oblique substantially wave-shaped beads 2f and 2g in FIG. 15 cross each other.
- the integration of the inner, the reinforcing inner and the outer is basically performed in the same manner as the panel structure described in FIG.
- the substantially wave-shaped bead when the substantially wave-shaped inner according to the present invention is viewed in plan, the substantially wave-shaped bead includes a parallel or oblique shape with respect to the longitudinal direction of the hood, or an elliptical shape with respect to the approximate center of the substantially wave-shaped inner. Alternatively, they can be arranged in parallel so as to form concentric circles or a double wave shape that is a combination of these arrangements. These arranged substantially wave-shaped beads form the inner cross-sectional shape over the entire panel surface. Note that the specific provisions for each of these arrays do not impair the effect of improving the rigidity, which is not a strict meaning, and allow some deviation in the range. Parallel, trapezoidal, concentric circles, etc. are almost parallel. , Substantially trapezoidal, substantially concentric, etc.
- the inner If and lg in Figs. 14 and 15 described above are substantially wave-shaped beads 2f and 2g, which are V-shaped (U-shaped.
- the inner force shown in FIG. 56 shows a manner in which substantially wave-type beads are distributed substantially parallel to the vehicle width direction. In FIG. 56, the substantially wave-shaped beads are distributed in parallel to the vehicle width direction.
- the hood structure shown in Fig. 2 has a resin layer 7 disposed on the top of the substantially labyrinth bead 2 of the inner la, and the sebum layer 7 is used as an adhesive to form a flat top part 5a of the substantially corrugated bead 2a. It shows a state in which the back surface of the outer 4a formed into a circular arc shape is joined to each other and a closed cross-sectional structure is formed through a space.
- the integral structure as the hood structure is fixed together with the adhesive by hem (bending) the peripheral edge of the inner la and the outer 4 and the hem 4b of the outer peripheral 4 rim. It is done.
- the resin layer 7 can also be provided with vibration suppression, noise reduction (shock insulation), shock buffering effect, etc. by selecting the characteristics and type of the resin. And in order to improve these effects, it is possible to fill the gap between the inner la and the outer 4 such as the top of the corrugated bead 5 with only the top 5a of the corrugated bead 5 and the cushioning material, etc. good.
- FIG. 3 as a perspective view of the double wave type hood structure of FIG. 2, the wave type hood structure in which the inner la and the heater 4 are integrated together is the conventional cone type hood structure. Like the beam type hood structure, it is further reinforced locally by reinforcing members such as Hinge Reinforcement 21 and Latch Reinforcement 2 2! RU
- the conventional wave-type inner can absorb the kinetic energy of the head very well and greatly reduce the HIC value. It is possible. That is,
- the wavelength of the wave-type inner By setting the wavelength of the wave-type inner to the value before and after the head-related injuries, it becomes a structure that supports the head with one wave when the head collides, and the head is softly deformed. As a result, the second acceleration wave decreases and the HIC value decreases.
- the head collision energy is efficiently absorbed by adding a reinforcing inner to the conventional wave type hood structure.
- the value is further reduced compared to the conventional wave type hood structure, and the head collision resistance is increased.
- a soft joining method is applied between the outer and inner ones, and local adhesive portions are provided in the ridges of the corrugated inner ones in a dusty or dispersed manner to protect pedestrians.
- the outer and inner rattling vibrations are not impaired. As a result, the head acceleration wave is disturbed and the HIC value can be lowered.
- the corrugated inner In the engine room, there are hard parts such as the engine, battery, and Raje night.
- the design of the corrugated inner one needs to take into account the arrangement of these parts.
- the arrangement of these parts varies from car to car, and the cross-sectional shape of the corrugated inner is modified from a simple and regular corrugated shape to a corrugated shape with irregularly varying wavelengths, wave heights, and waveforms. be able to.
- the corrugated cross-sectional shape is preferably a shape as shown in Fig. 4, for example, which is defined by a shape function that can represent an arbitrary three-dimensional shape such as a spline function.
- the inner having such a wave shape of the spline function is defined as a spline inner one, which is one form of the wave inner.
- Fig. 4 is a cross-sectional shape in a cross section in the longitudinal direction of the hood, and represents an outer, a spline-type inner, a spline-type reinforcing inner, and a rigid body surface in the engine room.
- the positional relationship between the spline-type inner and spline-type reinforcing inners and the rigid surface is that the wave troughs collide evenly on the rigid surface when the head collides, and the reaction force from the rigid surface is corrugated. Give consideration to the entire surface.
- the cross-sectional shape is such that it is evenly supported by the valleys Dl and D2 of the spline wave ( The same applies to B2, B3, and B4).
- the cross-sectional shape can be made such that the wavelength is increased and the wave valleys D2 and D3 are evenly supported. If the wavelength is shortened and the number of waves is increased at this part, the bending rigidity of the inner car in the vehicle width direction decreases, the vertical displacement increases, and head collision resistance decreases. Are connected by one wave (the same applies to A2). However, there is no problem in providing waves in an allowable range with a low HIC value.
- the spline-type inner can achieve substantially constant head collision resistance regardless of the arrangement of rigid bodies in the engine room that are different for each vehicle.
- the arrangement of rigid objects in the engine room is very complex, and the spline wave height and wavelength can be flexibly changed in the vehicle width and vehicle longitudinal direction, so the shape of the spline-type inner is a complicated curved surface. It becomes.
- a reinforcing plate is attached to the inner side, unevenness (so-called embossing) is locally attached to the spline inner, or a small wave
- embossing unevenness
- the outer weight can be increased locally, and the value of the first acceleration wave at the time of head collision can be increased to about 200G.
- the present inventors have clarified that the optimum shape of the head acceleration waveform is obtained, and as a result, the HIC value decreases.
- the metal used for the outer, inner, and reinforcing inner a commonly used A1 alloy plate or high-tensile steel plate is appropriately employed. However, since it is necessary to make the thickness extremely thick from the viewpoint of characteristics such as material strength, it is unrealistic to obtain the desired rigidity in the present invention. Not applicable as body panel structure material.
- the vehicle panel structure of the present invention does not require the use of a high-strength steel plate and is particularly high. Even without using a strong A1 alloy, it is possible to achieve sufficiently high rigidity.
- the A1 alloy itself used for the inner or outer applied to the present invention is usually used for this kind of non-node.
- Commonly used AA 3 ⁇ 4 [IS standard [Koyoru 3000 series, 5000 series, 6000 series, 7 000 series, etc. .
- These A1 alloy sheets are manufactured by a conventional method such as rolling and are appropriately tempered before use.
- the corrugated cross section has a sine wave shape, and the wave distribution is a hood. In the case of being parallel to the longitudinal direction, it was examined.
- FIG. 21 is a side view showing an outline of a corrugated inner pedestrian head collision model applied to the present invention
- FIG. 22 is a front view.
- Figures 23 and 24 show perspective views of the head collision model.
- a corrugated inner 1 is provided on the inner surface of the outer 4, and a reinforcing inner 40 is provided on the inner surface of the corrugated inner 1. Bonded by 30.
- Reference numeral 23 denotes a pedestrian's head, and reference numeral 24 denotes a rigid surface.
- each dimension includes the head outer diameter d, the collision speed v, the collision angle OC, the distance L in the collision direction between the outer and the rigid surface, the thickness c of the adhesive, the wave height hl of the corrugated inner, Represents the wave height h2 of the reinforced inner and the wavelength p of the corrugated inner and reinforced inner.
- Table 1 The analysis conditions for the pedestrian's head model are shown in Table 1 below.
- the head collision model is a simple model consisting of a spherical head model for the head and a hood structure and a rigid surface.
- the rigid body surface simulates a rigid objective such as an engine that is difficult to model in the engine room, and has a clearance L in the vertical direction with a curved surface parallel to the outer.
- the hood model is a regular sedan with inner and reinforcing inners made of 5000 series aluminum material, and the outer one made of 6000 series aluminum material, with a double plate structure with a hood longitudinal curvature of 3100mm and a width curvature of 4300mm.
- This model was modeled as a plastic body.
- the joint between the outer and inner is not modeled, and the thickness c of the joint is modeled to loosen the gap.
- the three points in the black triangle in Fig. 23 are the support parts, the other parts are not constrained, the hood structure deforms greatly at the time of head collision, and the collision part is a rigid surface Collide with.
- FIG. 23 and FIG. 62 are diagrams showing analysis models.
- the head collision position is in the center of the hood.
- Fig. 24 shows the wave portion of the double-wave type hood structure.
- the reinforcing inner on the bottom surface of the corrugated inner is fixed at the contact portion with the inner, and the inner and reinforcing inners are shown.
- One is a closed space.
- the conventional corrugated hood structure has no reinforcing inner.
- Fig. 25 shows the analysis results for the wave type hood structure
- Fig. 26 shows the analysis results for the double wave type (longitudinal wave) hood structure
- Fig. 66 shows the analysis results for the double wave type (transverse wave) hood structure. .
- the HIC value for the wave type hood structure was 966, but the HIC value for the double wave type (longitudinal wave) hood structure dropped to 657, and the double wave type (transverse wave) In the case of the hood structure, the HIC value has dropped to 635.
- the double-wave hood structure efficiently absorbs the head collision energy, and the magnitude of the second acceleration wave is particularly reduced from 120G to 80G.
- the effect of the head-to-head collision resistance of the double-wave hood structure was confirmed.
- Fig. 28 shows the analysis results of the child head collision with respect to wavelength. From Fig. 28, the HIC value of the double-wave hood structure is significantly lower than that of the conventional type, and the preferred range is 0.5 when the wavelength is p and the outer diameter of the pedestrian's head is d. It was confirmed that p / d ⁇ 2.8. This preferred range can also be applied to adult head collisions.
- the wavelength When the wavelength is short, the bending rigidity in the vehicle body longitudinal direction of the inner and reinforcing inners increases, and the rigidity of the hood becomes too high, and the HIC value exceeds the limit value. On the other hand, if the wavelength is too large, the bending rigidity in the longitudinal direction of the vehicle will decrease, the rigidity of the hood will be too low, the head will collide with the rigid surface, and the HIC value will exceed the limit value. It is extremely important that the wavelength is within a suitable range.
- FIG. 29 shows the analysis result of the child head collision in the same manner as for the wave height.
- the HIC value of the double wave type hood structure is significantly lower than that of the conventional type, the wave height of the inner is hl, the wave height of the reinforced inner is h2, and the pedestrian's head outer diameter is d. It was confirmed that 0. 05 ⁇ (hl + h2) / d ⁇ 0.35. This preferred range can also be applied to adult head collisions.
- the bending rigidity in the longitudinal direction of the car body decreases, the rigidity of the hood becomes too low, the head collides with the rigid surface, and the HIC value exceeds the limit value.
- the wave height is high, the bending rigidity in the longitudinal direction of the car body of the inner and reinforcing inners increases, the rigidity of the hood becomes too high, and the HIC value exceeds the limit value. It is extremely important that the wavelength is within a suitable range.
- the effect of the head collision position was investigated using a double-wave hood structure.
- the analysis conditions were a child head collision, the vertical clearance L between the outer and rigid surfaces was 70 mm, the head collision position is shown in Fig. 30, and the analysis results are shown in Table 3. From Table 3, even if the head collision position changed, the HIC value was almost constant. As a result, it was confirmed that the HIC value of the double-wave hood structure was almost uniform with respect to the collision site. Regardless of the collision position, the HIC value is constant. It can be said that it is extremely useful for safety.
- the outer and inner ones tend to vibrate together, eliminating rattling vibrations, resulting in an increase in the second acceleration wave.
- the HIC value has been confirmed to increase.
- the basic structure is the same and the same mechanism occurs, so the same bonding method is required. For this reason, in the present invention, a method for adhering the corrugated inner one and the outer in the double-wave hood structure may be defined.
- the double wave hood structure of the present invention it is preferable to have two air layers between the outer and inner, between the inner and the reinforcing inner, and to provide fine holes in the inner or the reinforcing inner.
- the sound absorption performance is improved by the pedestrian protection performance alone.
- the size of the fine holes it is quite difficult to punch fine holes that are less than the plate thickness by general common sense in manufacturing. If mass production is assumed, the minimum value of the hole diameter is Although it is about the thickness, a separate study is necessary to economically increase the smaller holes.
- the hole diameter lmm from Fig. 33 is set. It can be seen that the target frequency can be satisfied when the aperture ratio is 2% or less and the aperture ratio is 3% or less when the hole diameter is 3mm.
- FIG. 33 shows the relationship between the hole diameter and the aperture ratio when the target frequency is 1000 Hz or less and the plate thickness is 0.8 mm. It can be seen that if the back air layer is 30 mm or less, the target frequency can be obtained with a hole diameter of 3 mm or less and an aperture ratio of 3% or less. It can be seen from FIG. 34 that the same conclusion can be obtained even when the plate thickness is 0.4 mm.
- the thickness of the inner plate is 0.8 mm
- the aperture ratio is 0.5%
- the slit width is 0.05 mm
- the slit length is 100 mm
- the thickness of the reinforcing inner plate is 0.3 mm
- the aperture ratio is 0.5%
- the slit width was 0.05 mm and the slit length was 100 mm.
- the wave height was 15 mm for both inner and reinforcing inner.
- Fig. 35 shows the relationship between the back air layer and frequency in this case
- Fig. 36 shows the analysis model. In the analysis model, the area sandwiched between the outer and inner ones is C1 and C2, and the area between the inner and reinforcing inner is B part (see Fig. 36).
- the slit cross-sectional shape is as shown in the enlarged view of part A in the figure, and slits with a width of 0.05 mm were provided at intervals of 10 mm in the inner and the reinforcing inner so that the aperture ratio was 0.5%.
- FIG. 37 is a diagram showing a natural vibration mode of a sound field when a wavelength is 160 mm and one symmetric wavelength is modeled.
- Fig. 37 is a symmetrical one-wavelength two-dimensional slit model showing the sound pressure distribution diagram and natural frequency in the valley mode from the first-order mode to the ninth-order mode.
- the sound pressure is displayed as a normal value and distributed in the range of 1 to -1.
- sound pressure 1.0 occurs at C1 and C2 (numbers are shown in the figure), and the natural frequency is 720HZ. This mode seems to be a vibration mode due to the back air layer (average value is 7.5 mm) between the outer and inner ones.
- Fig. 37 is a diagram showing a natural vibration mode of a sound field when a wavelength is 160 mm and one symmetric wavelength is modeled.
- Fig. 37 is a symmetrical one-wavelength two-dimensional slit model showing the sound pressure distribution diagram and natural frequency in the valley mode from the first-order mode to the ninth
- the natural frequency is 720 Hz when the thickness of the back air layer is 16 mm. It is. For this reason, it is considered that the vibration mode is in the region where the back air layer with the C1 part and the C2 part being part of the B part is 16mm.
- secondary mode Is 997HZ which is the natural frequency at the back air layer thickness of 8.5mm in CI and C2, and roughly corresponds to the average value of the back air layer of the outer and inner ones of 7.5mm.
- the C1 part has a sound pressure of 1.0, while the C2 part has a sound pressure of 1.0 and the sign is reversed.
- the vibration modes are almost similar to the second-order mode, but each is thought to be a mode in which the back air layer gradually becomes smaller.
- the 8th and 9th modes are vibration modes due to the back air layer between the reinforced inner and inner. In this way, it can be seen that in the double-wave structure, there are two air layers that only change the thickness of the back air layer, resulting in a complicated vibration mode.
- FIG. 39 shows the analysis results of modeling the wave shape of left and right symmetrical waves with the same dimensions, and the sound pressure distribution and natural vibration in each mode from the first mode to the fifth mode.
- FIG. 38 is a diagram showing the relationship between the vibration order and the natural frequency. From Fig. 39, the vibration mode no-turn is a force similar to the case of one wave. The vibration mode becomes more complicated due to the influence of adjacent waves, and as shown in Fig. 38, there are 9 to 25 vibration modes below 2000HZ. Has increased. Conventionally, it is known that broadband sound absorption characteristics can be obtained by stacking double perforated plates, but the sound absorption characteristics of the double-wave hood structure shown here are obtained by connecting the peak values of each vibration mode.
- Fig. 40 shows the broadband sound absorption characteristics expected from the left-right symmetric 4-wavelength two-dimensional slit model.
- the natural frequency below 2000HZ is increased to 33.
- the vibration mode has become more complicated by making the force wave shape asymmetric due to the increase in the areas of C1, C2, and B due to a slight increase in wavelength.
- vibration modes are concentrated in a frequency range of 20 OOHZ or less, and the broadband performance of sound absorption performance is improved. I can say that.
- Fig. 42 shows the analysis results
- Fig. 38 shows the relationship between the vibration order and the natural frequency.
- Fig. 42 shows a four-wavelength two-dimensional slit model that is tilted asymmetrically and shows the sound pressure distribution diagram and natural frequency in each mode from the first-order mode to the fifth-order mode.
- the clearance between the outer and the inner is 3 mm
- the clearance between the inner and the reinforcing inner is 0.3 mm.
- the vibration mode becomes more complex due to the complexity of the shape, and the natural frequency shifts to the low frequency side.
- the characteristic that this natural frequency shifts to the low frequency side, which is difficult to suppress the vibration on the low frequency side can be said to be excellent as a sound absorbing characteristic required for the hood.
- the natural vibration order of 2000HZ or less is 34, and it can be said that a wide range of sound absorption is obtained.
- the basic structure of the pedestrian sound absorption hood is to make the vibration mode of the sound field complex, and to achieve wideband sound absorption characteristics by increasing the natural vibration mode below 2 OOOHZ as much as possible. It can be said that it is sufficient to satisfy the person protection performance.
- the design concept for the double-wave hood structure is considered as follows.
- the left and right cross-sectional shapes at one wavelength are made asymmetrical, and the vibration mode of the sound field is complicated.
- the wave shape in one wavelength is asymmetrical on the left and right (see Fig. 41), and not only the wavelength but also the wave height may be asymmetrical.
- the vibration mode of the sound field can be complicated by changing the wavelength of adjacent waves or making the cross-sectional shape of the waves non-uniform in the longitudinal direction of the vehicle body of the hood.
- the wavelength or wave height of the inner panel and the reinforced inner panel is not uniform in the vehicle width direction or the longitudinal direction of the vehicle body. Can be complicated.
- FIG. 43 is a diagram showing an embodiment in which the wavelengths of adjacent waves are changed, and shows an embodiment when the wavelengths are not uniform in the vehicle width direction and the vehicle body longitudinal direction.
- Figure 44 shows that the cross-sectional shape of the wave is uneven in the longitudinal direction of the hood.
- FIGS. 45 and 46 show examples in which the wavelength or wave height is not uniform in the vehicle width direction or the longitudinal direction of the vehicle body.
- the outer and inner ones are flexibly coupled by adhesive portions arranged in a staggered manner.
- the rattling vibration between the outer and inner ones disappears, the second acceleration wave increases, and the HIC value increases.
- the clearance between the outer and inner is usually lmm to 10mm, preferably about 2mm to 5mm. Clearance is also small in terms of pedestrian protection. This is because if the time at which the first wave is generated at the time of head collision can be advanced, the same effect as the effect of increasing the clearance from the outer surface to the rigid surface can be obtained, and the collision speed to the rigid surface can be reduced.
- the clearance between the outer and the inner is large.
- the movement of air between adjacent wavelengths is facilitated, and low-order frequency modes appear in the natural vibration mode of the sound field, and the vibration modes become more complicated.
- the frequency range in which sound can be absorbed is expanded, the vibration mode order below the target 2000HZ is increased, and sound absorption performance is improved.
- the pedestrian protection and the sound absorption performance are in conflict with each other with respect to the clearance between the outer and the inner. Therefore, it is necessary to balance well.
- the inner and the reinforced inner are preferably made of a resin adhesive or a mechanical bond such as a bolt or rivet. From the viewpoint of pedestrian protection, it is desirable that the inner and reinforcing inners are rigidly connected at the contact area. This is the force that absorbs the impact load that is transmitted to the reinforced inner part by the entire reinforced inner part, thereby increasing the amount of energy absorption and avoiding the collision of the head with the rigid surface.
- the sound field natural vibration mode of the air layer is better when the adjacent back air layer between the inner and reinforced inners is closed for each wavelength than when it is not closed. Forms complex vibration mode and improves sound absorption performance. For this reason, it is better for the viewpoint power of sound absorption that there is a sufficient gap through which air can pass between the inner and the reinforcing inner.
- Figure 47 shows how the inner and the reinforced inner are connected to satisfy both pedestrian protection and sound absorption conditions.
- Fig. 47 is a view of the directional force of the corrugated inner, which is perpendicular to the longitudinal direction of the vehicle body.
- the corrugated inner surface has small wave-like irregularities with a wave height of about lmm to 10mm.
- the part indicated by reference numeral 25 is an adhesion part, and it is necessary to secure a sufficient adhesion area in the vehicle width direction.
- the adhesive may be a resin adhesive, but an adhesive having high rigidity and high adhesive strength is preferable so that the inner and the reinforcing inner can be firmly bonded. It is also possible to use rivets, spot welding, etc. for strong reinforcement.
- the hole shape of the perforated plate is usually circular, but may be a slit, rectangle, triangle, star, polygon, or the like.
- the Helmholtz resonance principle can also be applied to these shapes.
- the preferred range of wavelength and wave height for pedestrian protection is extremely wide, and the sound absorption performance is easily satisfied. Sections 13 and 14).
- the double wave having the outer panel, the inner panel disposed on the inner surface of the outer panel, and the reinforcing inner panel disposed on the inner surface of the inner panel.
- the perforated plate is not suitable for painting because the holes are filled with paint when painted.
- the hood is painted by the method of squeezing! /, And putting the outer and inner ones together into a container filled with paint.
- Such a method is not possible with a sound absorbing hood, and it is necessary to paint the outer singly and then assemble the inner and the reinforced inner.
- the conventional method of connecting the outer and the inner by hem bending is not appropriate for the sound absorbing hood.
- a method has already been designed in which the outer circumference of the outer is bent approximately 90 degrees and the inner and outer are joined.
- the sound absorbing hood includes a reinforcing inner.
- FIG. 53 is an explanatory view showing a crush bead in a double wave type hood structure.
- a crush bead is applied to the inner and the reinforcing inner except the outer periphery of the hood. If the bead is too deep and the bead width is too large, the rigidity of the hood inner in the longitudinal direction of the vehicle body will be reduced and the pedestrian protection performance will be reduced. The width is determined.
- the bead width may be determined by setting the bead depth to around 10 mm, in accordance with the multi-corner adopting the same closed section structure as the hood structure.
- a crush bead is provided on the reinforcing inner as in the case of the inner.
- the bead is dug vertically downward as in the case of the inner.
- the outer panel is made of steel and the inner panel and the reinforcing inner are made of aluminum.
- the HIC value is about 1000.
- Figure 50 shows the ideal acceleration waveform.
- Fig. 50 by using a steel plate for the outer panel, the weight of the outer panel increases and the magnitude of the first acceleration wave at the time of head collision increases. By setting this size to about 200G, the head collision energy is consumed and the second acceleration wave is lowered. As a result, an ideal acceleration waveform is obtained, and the HIC value can be suppressed to 1000 or less.
- the outer plate thickness of the steel plate is about 0.7 mm.
- a metal plate made of steel, aluminum, lead, or the like is attached to the lower surface of the outer panel at appropriate times in the double-wave hood structure.
- the second acceleration wave decreases and the HIC value can be suppressed to 1000 or less.
- Detailed conditions such as the type, location, number, and thickness of metal plates will be examined in a timely manner.
- This method is also applicable to the force double wave type hood structure that the inventor has shown in Japanese Patent Application No. 2002-239976 that it can be applied to the conventional wave type hood structure. .
- FIGS. 51 and 52 Such an embodiment is shown in FIGS. 51 and 52.
- a reinforcing plate is attached by a rivet 43 to the driver's seat side of the hood, which is the adult head collision area.
- the HIC value is reduced in an adult head collision with a heavy head weight.
- the double-wave type vehicle body panel structure such as the double-wave type vehicle body hood structure is excellent in rigidity, collision resistance, and has sound absorption characteristics. It can be applied to roofs, doors, trunk lids, etc. Furthermore, it can be applied to the panel structure of a railway car body.
- Figure 54 shows an example.
- the rubber or resin bag 44 shown in FIG. 54 may be independently attached to each wave.
- an appropriate value may be set for each location where the magnitude of the internal pressure need not be the same.
- a rubber or resin bag 44 may be used, and the sealing performance may be ensured only by the outer, inner and reinforcing inner. In this case, the sealing must be maintained at the joints of each member using an adhesive or the like.
- FIG. 55 shows the implementation side.
- the energy absorption unit villages 45 such as styrene foam are connected independently for each wave! /.
- the inner has a substantially wave-shaped bead in the longitudinal direction of the vehicle body
- the reinforcing inner has a substantially wave-shaped bead in the vehicle width direction.
- head collision analysis child head collision
- Figures 57 and 58 show the analysis models.
- FIG. 76 is a simplified cross-sectional view viewed from the side of the hood
- FIG. 77 is a simplified cross-sectional view viewed from the front of the hood. Head collision positions are 5 points 1 to 5 shown in Fig.57.
- Figure 59 shows the analysis results.
- the head crash performance is almost the same as the case without the conventional reinforcing inner, and the performance is slightly better than when the wave direction is the inner and the reinforcing inner in the longitudinal direction of the vehicle body.
- the result was to take.
- this structure can be said to have superior performance compared to the conventional type in that sound absorption performance is added.
- FIG. 61 is an overall view of the analysis model
- Fig. 62 is a diagram showing the inner shape of Fig. 61
- Fig. 63 is a diagram showing the shape of the inner and reinforcing inners at the center
- Fig. 74 is a simplified view from the side of the hood. It is sectional drawing.
- Fig. 64 shows the head acceleration waveform when it collides with the peak of the wave of the child head force inner.
- Figure 65 shows the head acceleration waveform when the child's head collides with a wave trough.
- Fig. 66 and Figs. 94 to 96 show a comparison with the conventional analysis results.
- the cross-sectional corrugated shape of the inner panel or the reinforced inner panel is defined as pa at the wavelength of the inner panel or the reinforced inner panel in the adult head collision range.
- the outer diameter of the head of an adult is da
- 0.5 ⁇ pa / da ⁇ 2.8 is satisfied
- the inner wave height (hla) of the inner head collision range and the wave height (h2a) of the reinforcing inner panel satisfy 0.05 (hla + h2a) / da ⁇ 0.35, or the child head collision. It is preferable that the wave height (hlc) of the inner in the range and the wave height (h2c) of the reinforcing inner panel satisfy 0.05 ⁇ (hlc + h2c) / dc ⁇ 0.35.
- the collision energy can be efficiently and appropriately absorbed in both cases of an adult head collision and a child head collision.
- the collision energy increases at the time of an adult head collision, it is necessary to make the wave height larger than at the time of a child collision. It becomes possible to make it larger than the wave height of the part collision part. Therefore, a more optimal pedestrian protection hood can be obtained.
- FIG. 72 is a cross-sectional view of a simple model.
- Fig. 60, Fig. 91, Fig. 92, and Fig. 93 show a single-wave type vehicle body panel structure, and an inner wave is a substantially wave type with the vehicle width direction.
- FIG. 7 is a diagram showing the results of analysis of pedestrian protection performance when a bead is used.
- the pedestrian protection performance in the case of a body panel structure with a single transverse wave (collision with a mountain) where the inner has a substantially wave-shaped bead in the vehicle width direction is A vehicle body panel structure of a type (single longitudinal wave, colliding with a mountain), and the inner one has a substantially wave-shaped bead in the longitudinal direction of the vehicle body, and generally matches the pedestrian protection performance It can be seen that excellent pedestrian protection performance can be obtained by setting a suitable wavelength.
- the vehicle body panel structure is a single transverse wave (collision with a mountain), and the inner one has a substantially wave-shaped bead in the vehicle width direction, so it is lightweight and walking. It can be seen that it is useful as a vehicle body hood panel structure with excellent person protection performance.
- Figure 114 shows the head acceleration waveform for a single shear wave hood structure with a wavelength of 160 mm, a wave height of 30 mm, and a clearance of 7 Omm. The mechanism for reducing the HIC value in the single shear wave hood structure was discussed.
- Fig. 115 to Fig. 118 show the deformation figures at the time of head collision at 0msec, 6msec, 11msec and 17msec in Fig. 114 respectively.
- the acceleration at this time is the head of Fig. 114 It can be read from the acceleration waveform diagram.
- (1) is Omsec
- (2) is 6 msec
- (3) is l lmse c
- (4) is 17 msec.
- This head acceleration waveform is different from the conventional longitudinal wave in that it can be attributed to the occurrence of the third wave of the caloric velocity. It turns out that it is due to influence.
- the head receives the acceleration third wave due to the adjacent transverse wave, the acceleration second wave due to the approach to the rigid body surface decreases, and as a result, the acceleration waveforms of the acceleration second wave and acceleration third wave are smoothed, As a result, the HIC value decreases.
- the transverse inner wave in the vehicle width direction as described above the pedestrian protection performance is improved. However, such an effect cannot be obtained unless a suitable range of wavelength and wave height is selected.
- the stiffness of the inner is too high, causing a rapid increase in the second acceleration wave, and the HIC value increases.
- the stiffness of the inner is too low, and the head becomes a rigid surface.
- the HIC value greatly exceeds the limit value of 1000. The same applies to the wave height. If the wave height is too large, the inner rigidity becomes too high, and if the wave height is too small, the rigidity is insufficient and the HIC value increases.
- the inner wave height (hla) force in the adult head collision range is larger than the inner wave height (hlc) in the child head collision range.
- the collision energy can be absorbed efficiently and appropriately for both head collision and child head collision. In other words, since the collision energy increases at the time of an adult head collision, it is necessary to make the wave height larger than that at the time of a child collision, but such a structure makes it possible. Therefore, a more optimal pedestrian protection hood can be obtained.
- FIG. 73 is a cross-sectional view of the hood viewed from the side of the vehicle body.
- the wave heights of the inner and reinforcement inners in the adult head collision range are larger than the wave heights of the inner and reinforcement inners in the child head collision range, respectively.
- the wavelength and wave height need not be constant values.
- a double wave type hood in which a wavy bead in the vehicle width direction and a wavy bead in the longitudinal direction of the vehicle body are mixed with a reinforced inner.
- a child head collision analysis was performed on the structure.
- the plate thickness is lmm, 0.8mm, and 0.3mm for the outer, inner and reinforcing inners, respectively, and the material is aluminum alloy.
- Fig. 67 shows the inner shape of the analysis model
- Fig. 68 shows the shape of the inner part and the inner part of the reinforcing inner part.
- FIG. FIG. 69 shows a head acceleration waveform when the child head force inner collides with the peak
- the double-wave hood that combines the inner and the reinforced inner which is a mixture of the wavy bead in the vehicle width direction and the wavy bead in the longitudinal direction of the vehicle body, is extremely superior to the conventional structure.
- the outer of double-wave hood structure is a combination of inner and reinforced inner mixed with wave-shaped bead in the vehicle width direction and wave-shaped bead in the longitudinal direction of the car body. The head impact performance is further improved by attaching a reinforcing plate to the inner surface of the head.
- the inner wave height (hla) in the adult head collision range is larger than the inner wave height (hlc) in the child head collision range or the reinforced inner wave height in the adult head collision range.
- the wave height (h2a) is larger than the wave height (h2c) of the reinforcement inner in the child head collision range, and the vehicle body panel structure allows the collision energy during an adult head collision and the collision energy during a child head collision. Since energy can be absorbed efficiently, pedestrian protection performance is improved.
- the cross-sectional shape of the inner and the reinforcing inner is a wave other than the wave shape that double intersects the center of the panel. It preferably has a mold shape.
- the vehicle body panel structure is excellent in protecting pedestrians.
- Figure 78, Figure 79, Figure 80, Figure 81 and Figure 82 to Figure 88, Figure 97, and Figure 98 are single-wave hood structures, and waves other than the corrugated wave that intersects the hood center twice.
- FIG. 3 is a view showing a panel structure having a mold, that is, a vehicle body panel structure having a corrugated shape that does not cross twice in the center of the hood.
- a panel structure having a mold that is, a vehicle body panel structure having a corrugated shape that does not cross twice in the center of the hood.
- an outer panel, an inner panel disposed on the inner surface of the outer panel, and a reinforcing inner panel disposed further on the inner surface of the inner panel, the inner panel and the reinforcing inner panel are Cross sections with different wavelengths and wave heights on the entire surface
- FIG. 99 and FIG. 100 are views showing a vehicle body panel structure in which such an inner panel and a reinforced inner panel have cross-sectional corrugated shapes with different wavelengths and wave heights on the entire surface.
- Fig. 99 shows the case where the wavelength of the inner is longer than the wavelength of the reinforced inner
- Fig. 100 is the opposite. Since the clearance between the outer surface and the rigid surface varies depending on the collision position of the hood, the head collision resistance can be maintained even with such a structure.
- FIG. 101 is an explanatory view showing a vehicle body panel structure in which an outer, an inner, a reinforcing inner, and a second reinforcing inner force are also configured.
- the second reinforcing inner 46 to the vehicle body panel structure including the outer 4, the inner 1, and the reinforcing inner 40, the head collision performance and the sound absorbing performance are remarkably improved.
- FIG. 102 the head is a child's head.
- the four corners of the rectangular plate are considered as simple support conditions.
- the clearance between the rigid surface and the outer is 50 mm.
- a child's head was used, and an aluminum alloy with a plate thickness of lmm was used as the outer, and a plate thickness of 0.8 mm was used as the inner.
- the clearance from the outer to the rigid body is 50mm with the size of lm (meter) X lm, and the head collision direction is 0 degree in the same direction as the wave, 90 degrees in the direction of the orthogonal, 0 degree, 30 degree, 45 HIC values were obtained for the cases of 60 degrees, 60 degrees, and 90 degrees.
- the definition of the head collision direction is shown in FIG.
- FIG. 103 an angle formed by the wave direction and the head collision direction is defined.
- the analysis results are shown in Fig. 104. From these figures, it can be seen that the head collision direction does not significantly affect the increase or decrease of the HIC value. That is, the characteristic of the wave-type inner is that the HIC value is constant regardless of the head collision, and that the HIC is constant regardless of the head collision direction.
- the outer In a normal hood, the outer has a curvature, the outer has a higher vertical position on the driver's seat side, and the length in the vehicle width direction is shorter than the length in the longitudinal direction. This It is wrong that the influence of these shapes affects the HIC value of the corrugated hood structure. It has already been confirmed that the HIC value tends to be lower when the direction of the wave is in the vehicle width direction than in the longitudinal direction. This is because the length in the vehicle width direction is shorter than the length in the longitudinal direction. This is thought to be because the bending rigidity of the head increased and the absorption efficiency of the collision energy of the head collision energy increased.
- the direction of the wave and the direction of the collision are sometimes not specified and are arbitrary.
- the head hood structure has excellent head collision resistance and excellent pedestrian protection. This is clear.
- a vehicle body panel structure having a substantially wave-shaped cross-sectional shape in which the inner, the reinforcing inner, or the second reinforcing inner is divided, and the wave direction is inclined in the vehicle width direction or the vehicle width direction. explain about. As described above, it has been confirmed that the head collision can be ensured even if the direction of the wave is arbitrary, so we examined the case where a part of the wave was broken. In the case where a part of the wave is divided and the direction of the wave as shown in FIG.
- the head impact can be secured in the same manner even when the wave direction is the vehicle width direction (lateral direction) or the oblique direction. Examples are shown in FIG. 106, FIG. 107, and FIG.
- the HIC value increases in the head collision in this part because the rigidity is locally reduced in the divided part. It is preferable to keep the divided parts as narrow as possible and to suppress the wave height as much as possible.
- the direction of the wave of the inner body of the vehicle body panel structure, the reinforcing inner or the second reinforcing inner is not particularly specified, and is arbitrary and has an undivided wave and a partially broken wave.
- a vehicle body panel structure will be described.
- 109 to 113 are views showing the shape of the inner body of the vehicle body panel structure that has the undivided wave and the partially divided wave. Since the local rigidity is reduced at the part where the wave is divided, the head collision resistance is reduced. Therefore, it is preferable to make the divided part as narrow as possible and to suppress the wave height at this part as much as possible.
- the transverse wave structure has better pedestrian protection performance than the longitudinal wave structure
- the double transverse wave structure has better pedestrian protection performance than the single transverse wave structure. Is excellent. For this reason, the knowledge about the wave cross-sectional shape and wave distribution obtained with the longitudinal wave structure for sound absorption performance and pedestrian protection performance can be applied directly to the transverse wave structure.
- FIG. 119, FIG. 120, FIG. 121 and FIG. Fig. 119 and Fig. 120 are diagrams showing a double-sided inner panel of a transverse wave when the wavelength is waved.
- Figs. 121 and 122 are inner panels of a double-sided transverse wave when the wavelength of the cross-sectional structure of the wave is left and right.
- FIG. Even in such an inner panel having a transverse wave double structure, it is possible to realize a broadband sound absorption characteristic in the sound absorption characteristic.
- the cross-sectional shapes shown in FIGS. 6 to 13 described above can also be applied to a single or double transverse wave structure.
- the wavelength of the cross-sectional structure of the wave may be asymmetrical as shown in Fig. 123.
- the wavelength of the wave cross-sectional structure is preferably symmetrical. This is because the energy absorption efficiency is more symmetrical.
- the shape is such that the top of the wave is distorted toward the front end of the vehicle body, but the same effect can be obtained by a shape in which the top of the wave is distorted toward the driver's seat.
- the present invention relates to a vehicle body panel material such as an automobile body hood, a roof, a door, a trunk lid, etc. And useful.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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AT05811769T ATE473903T1 (de) | 2004-12-02 | 2005-12-02 | Wandstruktur für fahrzeugkarosserie |
DE602005022349T DE602005022349D1 (de) | 2004-12-02 | 2005-12-02 | Wandstruktur für fahrzeugkarosserie |
EP05811769A EP1829769B1 (en) | 2004-12-02 | 2005-12-02 | Vehicle body panel structure |
US11/720,805 US7988222B2 (en) | 2004-12-02 | 2005-12-02 | Vehicle body panel structure |
JP2006546653A JPWO2006059724A1 (ja) | 2004-12-02 | 2005-12-02 | 車体パネル構造体 |
Applications Claiming Priority (2)
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JP2004-350506 | 2004-12-02 | ||
JP2004350506 | 2004-12-02 |
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PCT/JP2005/022202 WO2006059724A1 (ja) | 2004-12-02 | 2005-12-02 | 車体パネル構造体 |
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US (1) | US7988222B2 (ja) |
EP (1) | EP1829769B1 (ja) |
JP (1) | JPWO2006059724A1 (ja) |
KR (1) | KR100919348B1 (ja) |
CN (1) | CN101068705A (ja) |
AT (1) | ATE473903T1 (ja) |
DE (1) | DE602005022349D1 (ja) |
WO (1) | WO2006059724A1 (ja) |
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- 2005-12-02 JP JP2006546653A patent/JPWO2006059724A1/ja active Pending
- 2005-12-02 AT AT05811769T patent/ATE473903T1/de not_active IP Right Cessation
- 2005-12-02 CN CNA200580041643XA patent/CN101068705A/zh active Pending
- 2005-12-02 EP EP05811769A patent/EP1829769B1/en not_active Not-in-force
- 2005-12-02 WO PCT/JP2005/022202 patent/WO2006059724A1/ja active Application Filing
- 2005-12-02 DE DE602005022349T patent/DE602005022349D1/de active Active
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Cited By (9)
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WO2011118016A1 (ja) * | 2010-03-26 | 2011-09-29 | トヨタ自動車株式会社 | 車両用フード構造 |
JP5408336B2 (ja) * | 2010-03-26 | 2014-02-05 | トヨタ自動車株式会社 | 車両用フード構造 |
US9033407B2 (en) | 2010-03-26 | 2015-05-19 | Toyota Jidosha Kabushiki Kaisha | Vehicle hood structure |
JP2014502232A (ja) * | 2010-12-08 | 2014-01-30 | ダイムラー・アクチェンゲゼルシャフト | 補強支柱を有する自動車車体 |
US9090289B2 (en) | 2010-12-08 | 2015-07-28 | Daimler Ag | Motor vehicle body with stiffening struts |
JP2017105292A (ja) * | 2015-12-09 | 2017-06-15 | Jfeスチール株式会社 | 軽量高剛性の自動車用鋼製フードパネル部品およびその製造方法 |
WO2020149312A1 (ja) * | 2019-01-15 | 2020-07-23 | 日本製鉄株式会社 | 自動車の側部構造及び自動車 |
JPWO2020149312A1 (ja) * | 2019-01-15 | 2021-09-30 | 日本製鉄株式会社 | 自動車の側部構造及び自動車 |
JP7088319B2 (ja) | 2019-01-15 | 2022-06-21 | 日本製鉄株式会社 | 自動車の側部構造及び自動車 |
Also Published As
Publication number | Publication date |
---|---|
EP1829769A1 (en) | 2007-09-05 |
KR20070085595A (ko) | 2007-08-27 |
CN101068705A (zh) | 2007-11-07 |
US7988222B2 (en) | 2011-08-02 |
EP1829769A4 (en) | 2009-03-18 |
EP1829769B1 (en) | 2010-07-14 |
JPWO2006059724A1 (ja) | 2008-06-05 |
US20100019540A1 (en) | 2010-01-28 |
ATE473903T1 (de) | 2010-07-15 |
DE602005022349D1 (de) | 2010-08-26 |
KR100919348B1 (ko) | 2009-09-25 |
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