JP4600757B2 - Car body floor panel - Google Patents

Description

  The present invention relates to a floor panel for a vehicle body, and more particularly to a floor panel for a vehicle body that is connected to a frame member disposed in the longitudinal direction of the vehicle body and the vehicle width direction and constitutes the floor of an automobile.

  It is known that the vibrations of the engine and the suspension are transmitted to the floor panel via the frame member, and the floor panel vibrates to generate uncomfortable vehicle interior vibration and noise. Such unpleasant vibration transmitted from the engine or suspension is mainly 400 Hz or less in an automobile, and has a peak at a frequency around 250 Hz, which is road noise caused by tire cavity resonance.

  Conventionally, in order to suppress such vibration noise, it is generally performed to attach a vibration damping material or a vibration damping material to each part of the floor panel and the vehicle body in the vicinity thereof. However, this method requires a very large amount of vibration damping materials and vibration damping materials, and thus has a problem that the vehicle weight increases and the cost also increases. It is also known to increase the rigidity by forming a large number of beads on the floor panel or increasing the panel thickness, thereby shifting the natural frequency of the floor panel to a high band higher than 400 Hz. This method has the advantage of suppressing the resonance peak in the low frequency region, but on the other hand, the vibration in the high frequency region increases on the contrary. Needed a lot and had similar problems.

Also, the floor panel is formed with a plurality of shell structure convex portions that are resistant to bending, compression, and tension, and concave portions extending vertically and horizontally between these convex portions, and a vibration damping material is provided in the concave portions, and concentrated in the concave portions. A panel structure is known in which the generated vibration is attenuated by a damping material (Patent Document 1). In this panel structure, a concave portion is formed between a plurality of convex portions so as to extend vertically and horizontally like a mesh, thereby increasing a vibration energy loss coefficient with respect to bending deformation in all directions.
The applicant has proposed a floor panel structure described in Patent Document 2.

JP-A-6-107235 Japanese Patent Application Laid-Open No. 2004-237871

  Here, when the panel structure of Patent Document 1 is applied to the region surrounded by the frame member of the floor panel, there are a plurality of convex portions, or the concave portions extend vertically and horizontally like a mesh, Vibration and noise cannot be reduced sufficiently. For example, when vibration energy flows into the floor panel from the four sides via the frame member, there is a problem that if there are a plurality of protrusions, vibrations are less likely to concentrate in the recesses, and vibration distortion is dispersed throughout the panel area due to the recesses. There is a problem that the entire panel area is likely to vibrate. On the other hand, in terms of manufacturing, there is also a problem that the cost increases when the damping material is provided in the vertical and horizontal directions like the mesh in accordance with the concave portion.

  On the other hand, the present applicant forms a high-rigidity portion that protrudes upward or downward in the center of the area of the floor panel surrounded by a plurality of frame members, and is flat and low-rigidity in the entire area around the high-rigidity portion. The floor panel structure which formed the part is proposed (patent document 2). According to this floor panel structure, by forming one high-rigidity portion at the center of the region, there is an advantage that vibration can be effectively concentrated on the low-rigidity portion, and without the above-described problems, Vibration and noise can be reduced.

  However, even the floor panel structure shown in Patent Document 2 has the following cases in which it is difficult to reduce vibration and noise. That is, when the high rigidity part is formed by protruding the floor panel itself upward or downward, the protrusion height of the high rigidity part is the exhaust pipe or auxiliary equipment disposed below or above the vehicle body of the floor panel. It is necessary to suppress the height so as not to interfere with the height of the passenger or to prevent the passenger from stepping on the foot comfort (such as the occupant feeling a sense of incongruity by feeling a dent or the like). However, the smaller the protrusion height is, the more difficult it is to sufficiently increase the rigidity of the high-rigidity part. In such a case, vibration is less likely to concentrate on the low-rigidity part. Such a problem is particularly noticeable when the area surrounded by the frame member is relatively large or rectangular.

  In addition, from the viewpoint of securing the foot comfort of passengers, even if the height of the high-rigidity part is increased, a thick carpet that has been hollowed out according to its shape is laid, or the high-rigidity part is filled with urethane, etc. It is conceivable to secure the treading feeling by passing another steel plate member above the floor panel. However, in these cases, there are problems in terms of increase in vehicle weight and cost.

  Therefore, the present invention has been made to solve the above-described problems of the prior art, and even if the floor panel shape is restricted in the height direction, the floor panel is caused by vibration transmitted from the frame member of the vehicle body. It is an object of the present invention to provide a floor panel for a vehicle body that can effectively reduce vibration energy and reduce acoustic radiation from the floor panel.

In order to achieve the above object, the present invention is a floor panel of a vehicle body that is connected to a frame member disposed in a vehicle body longitudinal direction and a vehicle width direction and constitutes a floor of an automobile, and the floor panel includes at least A rectangular panel region, part of which is surrounded by a frame member, is formed, and only one is formed at the center of the rectangular panel region. A rectangular high rigidity that matches the shape of the panel region in plan view. Part, a low-rigidity part formed flat in the whole area around the high-rigidity part, and a damping material provided only in the whole area of the low-rigidity part in the panel region of the floor panel, and having high rigidity The upper part is formed with an upward curved surface part projecting upward from the low rigidity part and a downward curved surface part projecting downward from the low rigidity part, and the upward curved surface part and the downward curved surface part are formed with high rigidity. Line up in the long side direction The high-rigidity portion has a boundary portion with a curvature of 0 between the upper curved surface portion and the lower curved surface portion, and the boundary portion has high rigidity in plan view. It is characterized by being formed to extend in a curved shape in the short side direction of the part .
In the present invention configured as described above, since the high-rigidity portion and the low-rigidity portion are provided, the vibration energy concentrates on the low-rigidity portion due to the difference in stiffness between them. In the low-rigidity portion, the vibration energy of the floor panel is reduced by the large vibration distortion caused by the concentrated vibration energy and the damping ability of the material (steel plate) constituting the floor panel itself. In addition, since the high-rigidity part is formed at the center of the region surrounded by the frame member and the low-rigidity part is formed around the high-rigidity part, vibration is effectively concentrated on the low-rigidity part and greatly distorted. The vibration transmitted to the high-rigidity portion is effectively cut off by the low-rigidity portion, and the vibration energy of the vibration transmitted to the floor panel via the frame member is reduced without being distributed to the entire floor panel. As a result, acoustic radiation from the floor panel can be more reliably reduced.
Furthermore, in the present invention, since the upward curved surface part and the downward curved surface part of the curved surface having a continuous curvature are formed in the highly rigid part, the highly rigid part can be obtained without taking a large height of the highly rigid part. The rigidity of the can be reliably increased. Therefore, without interfering with exhaust pipes and auxiliary equipment provided below and above the vehicle body of the floor panel, or without deteriorating the feeling of stepping on the occupant, The rigidity difference can be obtained with certainty. As a result, even if there is a restriction in the height direction on the floor panel shape, the acoustic radiation from the floor panel due to vibration transmitted from the frame member of the vehicle body can be reduced.
Furthermore, in the present invention, the high-rigidity portion is formed in a rectangular shape, and the upper curved surface portion and the lower curved surface portion of the high-rigidity portion are formed so as to be aligned in the long side direction of the high-rigidity portion. The rigidity in the longitudinal direction can be increased more reliably.
Furthermore, in the present invention, since the boundary portion having a curvature of 0 between the upper curved surface portion and the lower curved surface portion is formed to extend in a curved shape in plan view, vibration energy is concentrated on the boundary portion. Can be prevented. As a result, acoustic radiation from the particularly rigid portion of the floor panel can be more reliably reduced.

In the present invention, preferably, the upper curved surface portion and the lower curved surface portion have the same height.
In the present invention configured as described above , the height of the upper curved surface portion and the lower curved surface portion of the high rigidity portion is the same as each other. Therefore, even if the height of the high rigidity portion is not increased, the high rigidity portion The rigidity of the can be increased more reliably.

In the present invention, preferably, the height of the portion of the high-rigidity portion that protrudes most from the low-rigidity portion is 10 mm or less.
In this invention comprised in this way, it can prevent more reliably that the step comfort of a passenger | crew deteriorates.

  According to the present invention, even if the floor panel shape is restricted in the height direction, the vibration energy of the floor panel due to the vibration transmitted from the frame member of the vehicle body is effectively reduced, and the acoustic radiation from the floor panel is reduced. be able to.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
FIG. 1 is a perspective view showing an underbody of an automobile provided with a floor panel according to an embodiment of the present invention. As shown in FIG. 1, an underbody 1 of an automobile includes a plurality of floor panels 2, 4, 6, 8, 10, 12, 14, and 16 that form a floor portion (floor portion) of a passenger compartment, and these floors. And a plurality of frame members connected to the panel. The plurality of frame members include a front side frame 18, a side sill 20, a floor side frame 22, a rear side frame 24, and a No. 1 to No. No. 9 cross members 26 to 34, No. 9 provided between these cross members and extending in the longitudinal direction of the vehicle body. 1 to No. Three tunnel side members 36-38.

First, the frame member will be described with reference to FIG. A pair of front side frames 18 having a closed cross-sectional structure extending in the longitudinal direction of the vehicle body so as to surround the engine room from both the left and right sides are provided at a front portion of the underbody 1 of the automobile. These front side frames 18 have a closed cross-section No. at the front end of the vehicle body. One cross member 26 is joined, and an engine 40 and a front suspension cross member 42 are attached to the front side frame 18, and a front suspension 44 is attached to the front suspension cross member 42.
The rear end portions of the pair of front side frames 18 are No. 1 extending in the vehicle width direction at the end portion of the floor portion on the vehicle body front side. 2 It is joined to the cross member 27. This No. The two cross members 27 are attached to a downward inclined portion of a dash panel (not shown) that partitions the vehicle compartment and the engine compartment, and a pair of torque box members 27a having a closed cross-sectional structure provided outside the vehicle body of each front side frame 18. And a dash lower cross member 27b having a closed cross-sectional structure disposed so as to be sandwiched between the front side frames 18.

  This No. 2 The pair of side sills 20 provided on the floor portion behind the vehicle body from the cross member 27 has a closed cross-sectional structure, and the front end portion thereof is No.2. The two cross members 27 are joined to both ends in the vehicle width direction. A pair of U-shaped floor side frames 22 extending in the longitudinal direction of the vehicle body are provided between the side sills 20, and the front end portions of the floor side frames 22 are connected to the rear end portions of the front side frames 18. In addition to being joined, 2 It is joined to the cross member 27. These floor side frames 22 are No. 3 cross member 28 and no. 4 so that it protrudes inward in the vehicle width direction between the cross member 29 and 22a. The connecting portion 30a with the 5 cross member 30 is bent in the vehicle width direction, and the other portions extend linearly.

  The rear end portions of the floor side frames 22 are joined to the front end portions of the rear side frames 24 each having a U-shaped cross section and extending in the longitudinal direction of the vehicle body. Further, the front end portions of these rear side frames 24 bend outward in the vehicle width direction, and are also joined to the inner side surface of the side sill 20 in the vehicle width direction. The front end portion has a reinforcing member extending in the vehicle width direction. 24a is provided. These rear side frames 24 extend to the end edge of the floor portion on the rear side of the vehicle body. No. 7 cross member 32 and No. 7 A rear suspension cross member 46 is attached between the eight cross members 33 and a rear suspension 48 is attached to the rear suspension cross member 46.

  No. No. 2 on the vehicle body rear side of the cross member 27. 2 extends in a straight line in the vehicle width direction parallel to the cross member 27. Three cross members 28 are provided. This No. The three cross members 28 are joined to the side sills 20 at both left and right ends in the vehicle width direction, and intersect the floor side frame 22 and are joined to the floor side frame 22 on both the left and right sides in the vehicle width direction. This No. No. 3 on the vehicle body rear side of the cross member 28. No. 3 which extends linearly in the vehicle width direction parallel to the cross member 28 Four cross members 29 are provided, and both left and right end portions in the vehicle width direction are joined to the side sill 20. No. The four cross members 29 intersect with the floor side frame 22 on both the left and right sides in the vehicle width direction and are joined to the floor side frame 22. These No. 3 and no. The four cross members 28 and 29 protrude upward at a substantially central position in the vehicle width direction where the floor tunnel portion 50 is provided.

No. No. 4 on the vehicle body rear side of the cross member 29. 5 to No. 7 cross members 30, 31, and 32 are provided, and the cross members 30 to 32 extend linearly in the vehicle width direction in parallel to each other. No. The left and right ends of the cross member 30 in the vehicle width direction are joined to the floor side frame 22 respectively. 6 and no. The left and right ends in the vehicle width direction of the seven cross members 31 and 32 are joined to the rear side frame 24, respectively. No. 7 on the rear side of the vehicle body of the cross member 32, the center of the vehicle width direction is curved forward. Eight cross members 33 are provided so as to extend in the vehicle width direction, and left and right end portions in the vehicle width direction are respectively joined to the rear side frame 24.
This No. On the rear side of the vehicle body of the 8 cross member 33, a No. of closed cross-sectional structure that extends linearly in the vehicle width direction at the edge of the floor portion on the rear side of the vehicle body. Nine cross members 34 are provided, and both left and right ends in the vehicle width direction are joined to the rear ends of the rear side frame 24, respectively.

  In addition to the front side frame 18, the side sill 20, the floor side frame 22, and the rear side frame 24 described above as reinforcing members in the longitudinal direction of the vehicle body, the vehicle body longitudinal direction is provided at both edges of the floor tunnel portion 50 in the vehicle width direction. No. with a U-shaped cross section 1 to No. Three tunnel side members 36 to 38 are disposed. No. 1 tunnel side member 36 is No.1. 2 cross member 27 and No. 2 3 extends linearly across the cross member 28, and both end portions in the longitudinal direction of the vehicle body are respectively No. 2 cross member 27 and No. 2 3 It is joined to the cross member 28. No. 2 The tunnel side member 37 is 4 cross member 29 and no. 5 extends linearly between the cross member 30 and both end portions in the longitudinal direction of the vehicle body are respectively No. 5 and No. 5 cross members 30. 4 cross member 29 and no. 5 is joined to the cross member 30. No. 3 tunnel side member 38 is No.3. 6 cross member 31 and No. 6 7 extends linearly across the cross member 32, and both ends in the longitudinal direction of the vehicle body are respectively No. 7 and No. 7 cross member 32. 6 cross member 31 and No. 6 7 is joined to the cross member 32.

  The frame member having the U-shaped cross section described above, that is, the floor side frame 22, the rear side frame 24, No. 2 3 to No. 8 cross members 28 to 33 and No. 8 1 to No. Each of the three tunnel side members 36 to 38 is formed such that an open portion having a U-shaped cross section faces upward of the vehicle body, and the lower surface of each floor panel 2, 4, 6, 8, 10, 12, 14, 16 is These are joined to the flange portion of each frame member to form a substantially rectangular closed cross section.

  Next, the floor panel will be described with reference to FIG. As shown in FIG. 1, an underbody 1 of an automobile is provided with first to eighth floor panels 2, 4, 6, 8, 10, 12, 14, and 16 each integrally formed by press-molding steel plates. .

  The first floor panel 2 is No. 2 cross member 27, a pair of side sills 20, and A floor tunnel portion 50 is provided so as to cover the space surrounded by the three cross members 28 and bulges upward so as to extend in the vehicle longitudinal direction at a substantially central position in the vehicle width direction. The front edge of the first floor panel 2 is No. 2 is joined to the vehicle body rear side surface of the cross member 27, and the bottom surfaces of the remaining three sides are connected to the pair of side sills 20 and 3 on the left and right sides in the vehicle width direction. The lower surface of the 1 tunnel side member 36 and the floor side frame 22 are joined. In the first floor panel 2, panel regions S 1 and S 2 surrounded by the frame members 20, 22, 27, 28, 36 are respectively formed on the left and right sides of the floor tunnel portion 50 in the vehicle width direction.

  The second floor panel 4 is No. 3 cross member 28, a pair of side sills 20, and A floor tunnel portion 50 is provided so as to cover the space surrounded by the four cross members 29 and bulges upward so as to extend in the vehicle longitudinal direction at a substantially central position in the vehicle width direction. As for this 2nd floor panel 4, the lower surface of the edge of the 4 sides is No.2. 3 cross member 28, a pair of side sills 20, and The lower surface is bonded to the floor side frame 22 on both the left and right sides in the vehicle width direction. In addition, a fold portion 54 that is bent in a straight line is formed at both edges in the vehicle width direction of the floor tunnel portion 50 of the second floor panel 4, and the floor tunnel portion 50 rises from the fold portion 54. Further, the second floor panel 4 is formed with linear bead portions 56 on both sides thereof along the curved portion 22a of the floor side frame 22 described above. The bead portion 56 is formed by protruding the second floor panel 4 itself upward of the vehicle body. No. 3 cross member 28 no. 4 extends to the cross member 29. In the second floor panel 4, panel regions S 3 and S 4 surrounded by the frame members 20, 22, 28, 29, the bent portion 54 and the bead portion 56 are provided on the left and right sides of the floor tunnel portion 50 in the vehicle width direction. Each is formed.

  The third floor panel 6 is No. 4 cross member 29, floor side frame 22 and No. 4 A floor tunnel portion 50 is formed so as to cover the space surrounded by the five cross members 30 and bulges upward so as to extend in the vehicle longitudinal direction at a substantially central position in the vehicle width direction. As for this 3rd floor panel 6, the lower surface of the edge part of the 4 sides is No.2. 4 cross member 29, each floor side frame 22, and No. 4 cross member 29. 5 on each of the left and right sides in the vehicle width direction. The lower surface of the 2 tunnel side member 37 is joined. In addition, the third floor panel 6 has a No. 3 on both the left and right sides of the floor tunnel portion 50. 4 cross member 29 and no. A bead portion 58 extending linearly in the vehicle width direction is formed in parallel with the five cross member 30. The bead portion 58 is formed by protruding the third floor panel 6 itself upward of the vehicle body. In the third floor panel 6, panel regions S5 and S6 surrounded by the frame members 22, 29, 30, 37 and the bead portion 58 are respectively formed on the left and right sides of the floor tunnel portion 50 in the vehicle width direction. Yes.

  The fourth floor panel 8 is provided outside the third floor panel 6 in the vehicle width direction. 4 extends in the longitudinal direction of the vehicle body so as to cover the space surrounded by the cross member 29, the side sill 20, the floor side frame 22, and the rear side frame 24. It extends to the vicinity of the 8 cross member 33. These fourth floor panels 8 are joined to the frame members 20, 22, 24, and 29.

  The fifth floor panel 10 is No. 5 cross member 30, No. 5 6 The cross member 31, the pair of floor side frames 22 and the pair of rear side frames 24 are provided so as to cover the space, and the lower surfaces of the edges of the four sides are the frame members 22, 24, 30 respectively. , 31. In addition, a fold portion 54 that is bent in a straight line is formed at both edges in the vehicle width direction of the floor tunnel portion 50 of the fifth floor panel 10, and the floor tunnel portion 50 rises from the fold portion 54. In the fifth floor panel 10, panel regions S 7 surrounded by the frame members 22, 24, 30, 31 and the bent portion 54 are respectively formed on the left and right sides of the floor tunnel portion 50 in the vehicle width direction.

  The sixth floor panel 12 is No. 6 cross member 31, No. 6 7 is provided so as to cover the space surrounded by the cross member 32 and the pair of rear side frames 24, and the lower surfaces of the edges of the four sides are respectively joined to the frame members 24, 31, 32, On both the left and right sides in the vehicle width direction, no. The lower surface of the three tunnel side member 38 is joined. In the sixth floor panel 12, panel regions S8 surrounded by the frame members 24, 31, 32, and 38 are respectively formed on the left and right sides of the floor tunnel portion 50 in the vehicle width direction.

The seventh floor panel 14 is No. 7 cross member 32, no. It is provided so as to cover the space surrounded by the eight cross members 33 and the pair of rear side frames 24, and the lower surfaces of the edge portions of the four sides are joined to the frame members 24, 32 and 33, respectively.
The eighth floor panel 16 is No. 8 cross member 33, no. 9 is provided so as to cover the space surrounded by the cross member 34 and the pair of rear side frames 24, and the lower surfaces of the edge portions of the four sides are joined to the frame members 24, 33 and 34, respectively.

In such an underbody 1 of an automobile, vibrations of the engine 40, the front suspension 44, and the rear suspension 48 are respectively transmitted through a pair of floors via the front suspension cross member 42, the front side frame 18, and the rear suspension cross member 46. Largely transmitted to the side frame 22 and the rear side frame 24, and further transmitted to the cross members 26 to 34, the side sill 20, and the tunnel side members 36 to 38, and these vibrations are transmitted to the floor panels 2 to 16. As described above, the vibration transmitted to each floor panel is mainly a vibration of 400 Hz or less having a peak at a frequency in the vicinity of 250 Hz, which is road noise caused by tire cavity resonance. Acoustic radiation from the panel is generated, which becomes a factor of worsening vibration noise in the passenger compartment.
In the embodiment of the present invention, by providing the floor panel 2 with a vibration reduction structure, acoustic radiation from the floor panel 2 due to vibration transmitted from the frame member to the floor panel 2 is suppressed. The other floor panels 4, 6, 8, 10, 14, 16 are composed of conventional panels.

  Here, the vibration reducing structure will be described. The vibration reduction structure is provided with a predetermined high rigidity part (high rigidity part) and a predetermined low rigidity part (low rigidity part) in a predetermined area (panel area) of the floor panel surrounded by frame members. It is a thing. The vibration energy transmitted to the floor panel is concentrated on the low rigidity part due to the difference in rigidity between the high rigidity part and the low rigidity part. The large vibration distortion caused by this concentrated vibration energy and the material constituting the floor panel (steel plate) ) Vibration energy is converted into thermal energy by its own damping ability. As a result, since the vibration of the floor panel is reduced, the acoustic radiation from the floor panel is reduced (vibration reducing effect). Furthermore, when a damping material is provided in the low-rigidity part, the damping material is distorted with the distortion of the low-rigidity part, so that the vibration energy concentrated on the low-rigidity part is further reduced, and as a result, from the floor panel Acoustic radiation is more effectively reduced.

  In addition, by providing the high-rigidity part at the center of the panel area and providing the low-rigidity part so as to surround the high-rigidity part around the entire area, as will be described later, vibration is greatly concentrated on the low-rigidity part. To do. Further, the vibration transmitted from the frame member to the floor panel is reduced before being transmitted to the high rigidity portion (vibration blocking effect). Further, vibration energy of vibration transmitted to the floor panel via the frame member is reduced without being distributed to the entire floor panel. As a result, acoustic radiation from the floor panel can be more reliably reduced.

2 and 3, the effect of reduction of acoustic radiation by such a vibration reduction structure obtained by experiments will be described. FIG. 2 is a plan view (a) showing an experimental model of a floor panel having a vibration reducing structure and a cross-sectional view (b) taken along the line AA, and FIG. 3 is an experimental model of FIG. 2 and a conventional panel. It is a diagram which shows the experimental result obtained from this experimental model.
As shown in FIG. 2, the experimental model is obtained by attaching a panel 62 having a vibration reducing structure to an experimental frame member 60 having a rectangular cross section arranged in a square shape in plan view. The panel 62 is formed by press-molding a steel plate having a thickness of about 0.7 mm, and the size of the panel surrounded by the frame member 60 is about 300 mm in length and width. Yes. The panel 62 is formed with a high-rigidity portion 64 and a flat low-rigidity portion 66 around the high-rigidity portion 64, and a damping material 68 is attached to the low-rigidity portion 66.

In addition, as a conventional panel, an experimental model was prepared in which a steel plate having the same thickness as that of the panel 62 and a panel formed entirely on the surface was attached to the frame member 60 (not shown). The same amount of vibration damping material as that of the panel 62 was pasted on the entire surface of this conventional panel. In the experiment, a part of the frame member 60 to which the floor panel is attached is given a vibration force of a frequency of 500 Hz or less (white noise) with a vibrator, and the vibration magnitude of the panel with respect to the vibration magnitude of the frame. The ratio (vibration rate) was measured.
As shown in FIG. 3, the vibration rate of the panel 62 having the vibration reduction structure is lower than that of the conventional panel over a relatively wide range of a frequency of 400 Hz or less, and particularly, road noise caused by tire cavity resonance. As a result, the peak height appearing in the vicinity of 250 Hz is greatly reduced. Thus, it can be said that the acoustic radiation radiated from the panel is reduced by the vibration reducing structure.

  Next, the first embodiment of the present invention will be specifically described. 1st Embodiment of this invention is applied to the floor panel 2, and the vibration reduction structure is provided in the panel area | region S1 and S2, respectively. Since the structure of the vibration reduction structure of the panel regions S1 and S2 is the same, and is the same on both the left and right sides in the vehicle width direction with respect to the floor tunnel portion 50, hereinafter, FIG. 4 (a) to FIG. ), The panel region S1 on the left side in the vehicle width direction with respect to the traveling direction will be described, and description of the other panel regions will be omitted. FIG. 4A is an enlarged plan view showing the panel region S1 of the floor panel 2 according to the first embodiment. FIGS. 4B and 4C are respectively b- in FIG. 4A. It is sectional drawing which shows the cross-section of the floor panel 2 seen along b line and cc line.

First, as shown in FIG. 4A, the panel region S1 is a rectangular region surrounded by the frame members 20, 22, 27, and 28, and each frame member 20, 22, 27, and 28 is a straight line. The opposing frame members extend in parallel with each other.
In the panel region S1, one high-rigidity portion 70 is formed at the center thereof, and a low-rigidity portion 72 that extends in a square shape so as to surround the high-rigidity portion 70 around the high-rigidity portion 70 is formed. Is formed. In FIG. 4A, contour lines corresponding to the degree of protrusion of the highly rigid portion 70 in the vertical direction of the vehicle body (the out-of-plane direction of the floor panel 2) are also shown. As described later, the high-rigidity portion 70 of the present embodiment is configured by a curved surface having a continuous curvature. In the high-rigidity portion 70, a line other than a line indicating a peripheral edge portion (a boundary portion with the low-rigidity portion 72) 70a. Lines indicate such contour lines.

  Further, as shown in FIGS. 4A to 4C, the low-rigidity portion 72 is provided with a vibration damping material 74 over the entire area. The vibration damping material 74 is an asphalt vibration damping material, and has a rectangular opening along the peripheral edge 70a of the high-rigidity portion 70 and has a sheet shape that extends in a square shape in accordance with the shape of the low-rigidity portion 70. Formed and affixed to the low-rigidity portion 72. The vibration damping material 74 may be another vibration damping material such as a coating type vibration damping material.

  Next, the high-rigidity portion 70 is formed in a rectangular shape that matches the shape of the panel region S1, the four sides of the boundary portion 70a extend linearly, and are parallel to the frame members 20, 22, 27, and 28. It is formed to become. By forming in this way, the rigidity of the low-rigidity portion 72 is not increased, and a difference in rigidity between the high-rigidity portion 70 and the low-rigidity portion 72 is obtained reliably. That is, when the boundary portion 70d extends in a curved shape, the rigidity of the low-rigidity portion 72 is increased. However, if the boundary portion 70d extends linearly, the rigidity of the low-rigidity portion 72 does not need to be increased.

  Further, the high-rigidity portion 70 is formed so that the ratio of the area occupied in the panel region S1 is large in plan view (so that the area is at least larger than that of the low-rigidity portion 72). On the other hand, the width of the low-rigidity portion 72 (relative distance between each side of the boundary portion 70d and each frame member 20, 22, 27, 28) is separated by a predetermined distance so that vibration concentrates on the low-rigidity portion 72. . Thus, the high-rigidity part 70 is formed over most of the panel region S1 so as not to hinder the concentration of vibration on the low-rigidity part 72.

  Next, as shown in FIGS. 4B and 4C, the high-rigidity portion 70 is integrally formed by projecting the floor panel itself in the out-of-plane direction, and at the boundary portion 70a, the low-rigidity portion 72 is formed. It is launched at a discontinuous angle. On the other hand, the low-rigidity portion 72 is formed substantially flat so that its rigidity is smaller than that of the high-rigidity portion 70.

  Next, as shown in FIGS. 4A and 4B, the high-rigidity portion 70 of the present embodiment protrudes upward in the front side region of the vehicle body in the longitudinal direction (with respect to the vehicle compartment). A convex curved surface portion 70b that is formed in a convex shape and a concave curved surface portion 70c that protrudes downward (formed in a concave shape with respect to the passenger compartment) in the rear region are formed. These curved surface portions 70b and 70c are formed in the same size and shape as each other, and their heights (height from the low-rigidity portion 72 in this embodiment) hb and hc are both 4 mm.

  Each of these curved surface portions 70b and 70c is a curved surface having a continuous curvature (a curved surface having no portion where the curvature changes discontinuously). In the present embodiment, each curved surface portion 70b, 70c is formed such that the curvature continuously changes over the entire surface. Further, the high-rigidity portion 70 is formed such that the curvature continuously changes over the curved surface portions 70b and 70c. That is, in the vicinity of the boundary portion 70d between the curved surface portions 70b and 70c, the curved surface continuously changes in curvature from a convex shape to a concave shape (from a concave shape to a convex shape), and the position where the direction of the curvature is reversed (the boundary portion 70d). ), The curvature is zero.

  Thus, the highly rigid part 70 is comprised by the curved surface with the continuous curvature. Further, the high-rigidity portion 70 is formed into a wave shape composed of a convex curved surface and a concave curved surface with continuous curvature (wave-shaped portion) by the curved surface portions 70b and 70c. In particular, in the present embodiment, the two curved surface portions 70b and 70c are formed side by side in the longitudinal direction (long side direction) of the rectangular high-rigidity portion 70, and as shown in FIG. The cross-sectional shape is a wave shape.

Next, the function and effect of the first embodiment will be described.
First, since the high rigidity portion 70 and the low rigidity portion 72 are provided in the panel region S1 (S2) of the floor panel 2, vibration energy is concentrated on the low rigidity portion 72 due to the difference in rigidity between them. . As described above, in the low rigidity portion 72, the vibration energy of the floor panel 2 is reduced, and the acoustic radiation from the floor panel 2 can be reduced. Furthermore, since the low-rigidity portion 72 is provided with the vibration damping material 74, as described above, the acoustic radiation from the panel region can be further effectively reduced.

  Here, in the floor panel 2 of the present embodiment, a vibration system (a “mass point”) is used as the high-rigidity portion 70 and a “spring” is used as the low-rigidity portion 72 that connects the material point (high-rigidity portion 70) and the frame member. It can be considered that a spring-mass system is formed. The frame member can be regarded as an excitation source. In such a vibration system, there is only one mass point (high rigidity portion 70) supported by the spring (low rigidity portion 72), and the heavier the spring, the larger the spring bends (the low rigidity portion 72 is greatly distorted). ) And the vibration of the mass point is reduced (vibration transmitted to the high-rigidity portion 70 is effectively blocked by the spring low-rigidity portion 72 (vibration blocking effect)). In the present embodiment, based on such a viewpoint, only one high-rigidity portion 70 is formed in the central portion of the panel region S1, and the area thereof is relatively large, so that the high-rigidity portion 70 is surrounded in the entire periphery. A low-rigidity portion 72 is formed. Therefore, the low-rigidity portion 72 can be greatly distorted, and as a result, the above-described vibration reduction effect can be obtained more reliably. In addition, among the vibrations transmitted from the frame member to the floor panel, the vibration transmitted to the high-rigidity portion 70 can be effectively blocked by the low-rigidity portion 72, and as a result, the high-rigidity having a relatively large area. Acoustic radiation from the unit 70 is suppressed. Furthermore, vibration energy of vibration transmitted to the floor panel via the frame member is reduced without being distributed to the entire floor panel.

  Next, to increase the rigidity of the high-rigidity part, it is effective to increase the height of the high-rigidity part. It may interfere with the exhaust pipe and auxiliary equipment. However, according to the present embodiment, the high-rigidity portion 70 is formed into a curved wave shape having a continuous curvature by the curved-surface portions 70b and 70c, so that the rigidity can be reliably increased while suppressing the height. I can do it. This is due to the fact that the curvature of the high-rigidity portion 70 can be made relatively smaller than that in the case where the corrugated portion is not provided. Further, since the curved surface portions 70b and 70c have high curved rigidity due to the curved curved surface shape, the rigidity of the highly rigid portion 70 having the wave shape portion can be more reliably increased. Furthermore, since the curvature is continuous over the entire surface of the high-rigidity portion 70, the rigidity of the high-rigidity portion 70 can be reliably increased as a whole. In addition, as long as the curvature is continuous, the curved surface portion may include a portion having a constant curvature (a portion having a circular cross section), and the same action can be obtained even in such a case.

  Here, when the highly rigid portion is formed in a rectangular shape, the greater the distance in the longitudinal direction, the more difficult it is to increase the rigidity unless the protruding height in the out-of-plane direction is increased. However, in the present embodiment, the curved surface portions 70b and 70c of the high-rigidity portion 70 are formed so as to be aligned in the longitudinal direction (long-side direction) of the rectangular high-rigidity portion 70. Therefore, since the corrugations are continuous in the longitudinal direction of the high-rigidity portion 70, the rigidity in the longitudinal direction can be more reliably increased even if the height of the high-rigidity portion is suppressed.

Next, the high-rigidity portion 70 is formed with a convex curved surface portion 70b projecting upward and a concave curved surface portion 70c projecting downward, respectively, and is positioned above or below the low-rigidity portion 72, respectively. As shown in FIG. And since the magnitude | size and shape, especially protrusion height are mutually the same, the rigidity of the highly rigid part 70 can be improved more reliably.
In particular, the protruding heights hb and hc of the curved surface portions 70b and 70c are 4 mm, respectively, and the vertical direction (height direction) between the uppermost portion of the convex curved surface portion 70b and the lowermost portion of the concave curved surface portion 70c. ) Is 8 mm, it is possible to increase the rigidity of the high-rigidity portion 70 while preventing the rider's foot comfort from deteriorating.

  Here, it is preferable that the projecting heights hb and hc of the curved surface portions 70b and 70c from the low-rigidity portion 72 are 10 mm or less in total. It is considered that the rigidity of the highly rigid portion 70 can be increased by the shape portion. For example, the heights of the curved surface portions 70b and 70c are the same and 5 mm or less, or the uppermost portion of the convex curved surface portion 70b and the lowermost portion of the concave curved surface portion 70c with different heights. The relative distance in the vertical direction (height direction) may be 10 mm or less.

  As described above, in the present embodiment, even if there is a restriction in the height direction with respect to the floor panel shape, it is possible to reliably obtain the rigidity difference between the high rigidity portion 70 and the low rigidity portion 72, and as a result, from the floor panel. Acoustic radiation can be reduced.

  Next, a second embodiment of the present invention will be described. The second embodiment of the present invention is applied to the floor panel 2 of the underbody 1 of the automobile shown in FIG. 1, and the configuration of the underbody 1 other than the floor panel 2 is the same as that of the first embodiment described above. is there. Further, similarly to the first embodiment, the vibration reduction structure having the same configuration is provided in each of the panel regions S1 and S2. Here, only the configuration of the panel region S1 of the floor panel 2 will be described with reference to FIGS. 5A to 5D, and description of other configurations will be omitted. FIG. 5 (a) is an enlarged plan view showing a panel region S1 of the floor panel 2 according to the second embodiment of the present invention, and FIGS. 5 (b) to 5 (d) are respectively shown in FIG. 5 (a). It is sectional drawing which shows the cross-section of the floor panel 2 seen along line bb, cc, and dd. In FIG. 5 (a), contour lines are also shown in the same manner as in FIG. 4 (a). In the high-rigidity portion 80, lines other than the line indicating the boundary portion 80a with the low-rigidity portion 82 are as described above. This shows a contour line.

  As shown in FIG. 5A, in the second embodiment, a rectangular high-rigidity portion 80 is formed at the center of the panel region S1 and the high-rigidity portion 80 is formed as in the first embodiment. A low-rigidity portion 82 extending in a square shape is formed so as to surround the high-rigidity portion 80 around the entire periphery. Further, as shown in FIGS. 5B to 5D, the high-rigidity portion 80 is integrally formed with the floor panel itself protruding in the out-of-plane direction, and the low-rigidity portion 82 has high rigidity. It is formed substantially flat so as to be smaller than the rigid portion 80. Further, as shown in FIGS. 5A to 5D, a damping material 84 is provided in the low-rigidity portion 82 as in the first embodiment.

  Next, as shown in FIGS. 5 (a) and 5 (b), the high-rigidity portion 80 includes a convex convex curved surface portion 80b that protrudes upward in a region on the front side in the front-rear direction of the vehicle body, A concave concave curved surface portion 80c protruding downward in the rear region is formed. As shown in FIGS. 5B to 5D, in the second embodiment, both the convex curved surface portion 80b and the concave curved surface portion 80c are positioned above the low-rigidity portion 72. Is formed. That is, the high-rigidity portion 80 is formed with a rising portion 80e that is raised upward at a discontinuous angle from the low-rigidity portion 82 over the entire circumference of the boundary portion 80a. With respect to the upper end position (the reference height he indicated by the two-dot chain line in the upper part of FIG. 5B), the convex curved surface portion 80b protrudes upward to form a convex shape with respect to the passenger compartment, and the concave curved surface portion 80c It protrudes downward and is formed in a concave shape with respect to the passenger compartment.

  The heights hb and hc with respect to the reference height (upper two-dot chain line) of the convex curved surface portion 80b and the concave curved surface portion 80c are 4 mm, which are the same height. Further, the height he of the rising portion 80e is 6 mm. Therefore, the height ha of the portion most protruding from the low-rigidity portion 82 of the high-rigidity portion 80 is 10 mm. Further, the concave curved surface portion 80 c does not protrude downward with respect to the low rigidity portion 82. Thus, in the second embodiment, the entire high-rigidity portion 80 is formed so as to protrude upward with respect to the low-rigidity portion 82.

  Next, as shown in FIGS. 5 (a) and 5 (b), as in the first embodiment, the curved surface portions 80b and 80c are formed in the same size and shape and have continuous curvature. It is composed of curved surfaces. Similarly to the first embodiment, the high-rigidity portion 80 is formed so that the curvature continuously changes over the curved surface portions 80b and 80c, and the curvature is 0 at the boundary portion 80d.

  Thus, also in this 2nd Embodiment, the highly rigid part 80 is comprised by the curved surface with the continuous curvature. The high-rigidity portion 80 has a wave shape in which a convex curved surface and a concave curved surface are continuous by the curved surface portions 80b and 80c. In particular, the curved surface portions 80b and 80c are formed side by side in the longitudinal direction (long-side direction) of the rectangular high-rigidity portion 80, and as shown in FIG. It is formed to become.

Next, the function and effect of the second embodiment will be described.
First, in the present embodiment, the vibration energy of the panel region is reduced by the high-rigidity portion 80 and the low-rigidity portion 82 as in the case of the effects of the first embodiment described above. It can be reduced. Moreover, the vibration energy in the panel region is further reduced by the damping material 84. Further, only one high-rigidity portion 80 is formed at the center portion of the panel region (S1, S2) and the area thereof is relatively large, and the low-rigidity portion 80 surrounds the high-rigidity portion 80 in the entire periphery. 82, the vibration is effectively concentrated on the low-rigidity portion 82 and greatly distorted, and the vibration transmitted to the high-rigidity portion 80 is effectively blocked by the low-rigidity portion 82. The vibration energy of the vibration transmitted to the floor panel 2 via the members 20, 22, 27, 28 is reduced without being distributed to the entire floor panel. As a result, acoustic radiation from the floor panel 2 can be more reliably reduced.

  Next, since the high-rigidity portion 80 is formed into a curved wave shape having a continuous curvature by the two curved-surface portions 80b and 80c, the high-rigidity portion 80 is out of plane for the same reason as in the first embodiment. Even if the amount of protrusion in the direction is small, the rigidity of the high-rigidity portion 80 can be reliably increased. Further, as in the first embodiment, the curved surface portions 80b and 80c have the same size and shape, particularly the height, so that the rigidity of the high-rigidity portion 80 can be increased more reliably.

  Next, since the entire high-rigidity portion 80 is positioned above the low-rigidity portion 82 in the out-of-plane direction, interference with an exhaust pipe or the like disposed below the floor panel can be prevented. In addition, you may form so that the whole highly rigid part may protrude below, In this case, interference with the auxiliary machines etc. which are arrange | positioned at the compartment side can be prevented.

  Furthermore, since the height ha of the portion most protruding from the low-rigidity portion 82 of the high-rigidity portion 80 is 10 mm, the rigidity of the high-rigidity portion 80 can be increased while preventing the rider's foot comfort from deteriorating. I can do it. Here, it is preferable that the height ha of the most protruding portion of the high-rigidity portion 80 from the low-rigidity portion 82 is 10 mm or less. The rigidity of the high rigidity portion 80 can be increased. For example, if the height he of the rising portion 80e is 4 mm, the height ha of the most protruding portion of the high-rigidity portion 80 from the low-rigidity portion 82 is 8 mm, and the concave curved surface portion 80c becomes the low-rigidity portion 82. On the other hand, it can be prevented from protruding downward.

  Next, since the curved surface portions 80b and 80c are formed so as to be aligned in the longitudinal direction (long side direction) of the rectangular high-rigidity portion 80, as in the first embodiment, the unevenness is continuous in the longitudinal direction. Thus, a wave shape formed can be formed. As a result, even if the height of the high rigidity portion is suppressed, the rigidity in the longitudinal direction can be more reliably increased.

  Next, a third embodiment of the present invention will be described. The third embodiment of the present invention is applied to the floor panel 2 of the underbody 1 of the automobile shown in FIG. 1, and the configuration of the underbody 1 other than the floor panel 2 is the same as that of the above-described first embodiment. is there. Further, similarly to the first embodiment, the vibration reduction structure having the same configuration is provided in each of the panel regions S1 and S2. Here, only the configuration of the panel region S1 of the floor panel 2 will be described with reference to FIGS. 6A to 6C, and description of other configurations will be omitted. FIG. 6A is an enlarged plan view showing a panel region S1 of the floor panel 2 according to the third embodiment of the present invention. FIGS. 6B and 6C are respectively the same as FIG. It is sectional drawing which shows the cross-section of the floor panel 2 seen along line bb and cc. In FIG. 6 (a), contour lines are also shown in the same manner as in FIG. 4 (a). In the high-rigidity portion 90, lines other than the line indicating the boundary portion 90a with the low-rigidity portion 92 are as described above. This shows a contour line.

  As shown in FIG. 6A, in the third embodiment, a rectangular high-rigidity portion 90 is formed at the center of the panel region S1 and the high-rigidity portion 90 is formed as in the first embodiment. A low-rigidity portion 92 extending in a square shape is formed so as to surround the high-rigidity portion 90 in the entire surrounding area. Further, as shown in FIGS. 6B and 6C, the high-rigidity portion 90 is integrally formed with the floor panel itself protruding in the out-of-plane direction, and the low-rigidity portion 92 has a high rigidity. It is formed substantially flat so as to be smaller than the rigid portion 90. Further, as shown in FIGS. 6A to 6D, a damping material 94 is provided in the low-rigidity portion 92 as in the first embodiment.

  Next, as shown in FIGS. 6 (a) and 6 (b), the high-rigidity portion 90 of this embodiment has an upward direction in each of the front and rear regions in the vehicle body longitudinal direction. Two protruding curved surface portions 90b and 90c having a protruding shape are formed. As shown in FIG. 6 (b), both of the convex curved surface portions 90b and 90c are formed so as to be positioned on the upper side with respect to the low-rigidity portion 92. It is formed so as to protrude upward in the out-of-plane direction with respect to 92.

  As shown in FIGS. 6A and 6B, similarly to the first embodiment, each curved surface portion 90b, 90c is formed of a curved surface having the same size and shape and having a continuous curvature. Has been. The protruding heights of these convex curved surface portions 90b and 90c from the low-rigidity portion 92 are both 8 mm.

  In the third embodiment, the boundary portion 90d between the curved surface portions 90b and 90c is a curved surface (concave surface) with a continuous curvature that protrudes downward, and as shown in FIG. 90 d extends in the middle of the long side direction of the high-rigidity part 90 and extends linearly in the short-side direction of the high-rigidity part 90. The high-rigidity portion 90 is formed such that the curvature of the concave curved surface of the boundary portion 90d and the convex curved surface portions 90b and 90c continuously change from each other. Therefore, the curvature is 0 at each boundary (two locations) between the boundary portion 90d and the curved surface portions 90b and 90c.

  Thus, also in this 3rd Embodiment, the highly rigid part 90 is comprised by the curved surface with the continuous curvature. Further, the high-rigidity portion 90 has a wave shape in which a convex curved surface and a concave curved surface are continuous by the curved surface portions 90b and 90c. In particular, the curved surface portions 90b and 90c are formed side by side in the longitudinal direction (long side direction) of the rectangular high-rigidity portion 90, and as shown in FIG. It is formed to become.

Next, the function and effect of the third embodiment will be described.
First, in the present embodiment, the vibration energy of the panel region is reduced by the high-rigidity portion 90 and the low-rigidity portion 92 as in the case of the effects of the first embodiment described above. It can be reduced. In addition, the vibration damping material 94 further reduces vibration energy in the panel region. Further, only one high-rigidity portion 90 is formed at the central portion of the panel region (S1, S2), and the area thereof is relatively large. The low-rigidity portion 90 surrounds the high-rigidity portion 90 around the entire periphery. 92 is formed, the vibration is effectively concentrated on the low-rigidity portion 92 and greatly distorted, and the vibration transmitted to the high-rigidity portion 90 is effectively blocked by the low-rigidity portion 92, and the frame The vibration energy of the vibration transmitted to the floor panel 2 via the members 20, 22, 27, 28 is reduced without being distributed to the entire floor panel. As a result, acoustic radiation from the floor panel 2 can be more reliably reduced.

  Next, since the high-rigidity portion 90 is formed in a curved surface having a continuous curvature by the two convex curved surface portions 90b and 90c, the out-of-plane direction of the high-rigidity portion 90 is the same as in the first embodiment. Even if the amount of protrusion is small, the rigidity of the high-rigidity portion 90 can be reliably increased. In particular, the boundary portion 90d is also a curved surface having a continuous curvature, and the rigidity of the high-rigidity portion 90 can be increased more reliably. Furthermore, since the curved surface portions 90b and 90c have the same size and shape, in particular, the height, the rigidity of the high-rigidity portion 90 can be more reliably increased as in the first embodiment.

  Next, since the entire high-rigidity portion 90 is located above the low-rigidity portion 92 in the out-of-plane direction, an exhaust pipe or the like disposed below the floor panel 2 as in the second embodiment. Interference can be prevented. Also in the third embodiment, as in the second embodiment, it is preferable that the height of the most protruding portion of the high-rigidity portion 90 from the low-rigidity portion 92 is 10 mm or less.

  Next, since the curved surface portions 90b and 90c are formed so as to be arranged in the longitudinal direction (long side direction) of the rectangular high-rigidity portion 90, as in the first embodiment, the unevenness is continuous in the longitudinal direction. As a result, even if the protruding height of the high-rigidity portion is suppressed, the rigidity in the longitudinal direction can be more reliably increased.

  Next, a fourth embodiment of the present invention will be described. The fourth embodiment of the present invention is applied to the floor panel 2 of the underbody 1 of the automobile shown in FIG. 1, and the configuration of the underbody 1 other than the floor panel 2 is the same as that of the first embodiment described above. is there. Further, similarly to the first embodiment, the vibration reduction structure having the same configuration is provided in each of the panel regions S1 and S2. Here, only the configuration of the panel region S1 of the floor panel 2 will be described with reference to FIGS. 7A to 7E, and description of other configurations will be omitted. FIG. 7A is an enlarged plan view showing a panel region S1 of the floor panel 2 according to the fourth embodiment of the present invention, and FIGS. 7B to 7E are respectively b in FIG. 7A. It is sectional drawing which shows the cross-section of the floor panel 2 seen along the -b line, the cc line, the dd line, and the ee line. 7A, contour lines are also shown in the same manner as in FIG. 4A. In the high-rigidity portion 100, lines other than the line indicating the boundary portion 100a with the low-rigidity portion 102 are as described above. This shows a contour line.

  As shown in FIG. 7A, in the fourth embodiment, a rectangular high-rigidity portion 100 is formed at the center of the panel region S1 and the high-rigidity portion 100 is formed as in the first embodiment. A low-rigidity portion 102 extending in a square shape so as to surround the high-rigidity portion 100 is formed in the entire surrounding area. Further, as shown in FIGS. 7B to 7D, the high-rigidity portion 100 is integrally formed with the floor panel itself protruding in the out-of-plane direction, and the low-rigidity portion 102 has high rigidity. It is formed substantially flat so as to be smaller than the rigid portion 100. Further, as shown in FIGS. 7A to 7D, the damping material 104 is provided in the low-rigidity portion 102 as in the first embodiment.

  Next, as shown in FIGS. 7A and 7B, the high-rigidity portion 100 includes a convex curved surface portion 100b that protrudes upward in an area on the front side in the longitudinal direction of the vehicle body, and a rear side A concave curved surface portion 100c protruding downward in the region is formed. As shown in FIGS. 7B to 7E, also in the fourth embodiment, similarly to the first embodiment, the convex curved surface portion 70b protrudes upward from the low-rigidity portion 72, and the concave curved surface portion 70c. Are formed so as to protrude downward from the low-rigidity portion 72, and the protruding heights from the low-rigidity portion 102 are each 4 mm.

  Further, each curved surface portion 100b, 100c is configured by a curved surface having a continuous curvature, as in the first embodiment. Further, as shown in FIGS. 7B and 7D, as in the first embodiment, the high-rigidity portion 100 is formed such that the curvature continuously changes over the curved surface portions 100b and 100c. The curvature is 0 at the boundary portion 100d.

  Next, as shown in FIG. 7A, in the fourth embodiment, the convex curved surface portion 100b is formed in a concave shape in plan view (the peripheral edge of the convex curved surface portion 100b extends in a concave shape in plan view). The concave curved surface portion 100c is formed in a convex shape in plan view (the peripheral edge of the concave curved surface portion 100c extends in a convex shape in plan view). And each curved-surface part 100b, 100c is formed so that those boundary parts 100d may extend in the shape of a curve. As described above, the boundary portion 100d having a curvature of 0 is formed so as to extend in a curved shape in the short side direction of the high-rigidity portion 100 at a substantially intermediate position in the long-side direction of the high-rigidity portion 100. The curvature of the curve of the boundary portion 100d is continuous.

  Thus, also in this 3rd Embodiment, the highly rigid part 100 is comprised by the curved surface with the continuous curvature. Further, the high-rigidity portion 100 has a wave shape in which a convex curved surface and a concave curved surface are continuous by the curved surface portions 100b and 100c. In particular, the curved surface portions 100b and 100c are formed side by side in the longitudinal direction (long side direction) of the rectangular high-rigidity portion 100, and as shown in FIG. It is formed to become.

Next, the function and effect of the fourth embodiment will be described.
First, in the present embodiment, the vibration energy of the panel region is reduced by the high-rigidity portion 100 and the low-rigidity portion 102 as in the case of the above-described effects of the first embodiment. It can be reduced. Moreover, the vibration energy in the panel region is further reduced by the damping material 104. In addition, only one high-rigidity part 100 is formed at the center of the panel region (S1, S2) and the area thereof is relatively large, and the low-rigidity part 100 surrounds the high-rigidity part 100 in the entire periphery. 102 is formed, the vibration is effectively concentrated on the low-rigidity portion 102 and greatly distorted, and the vibration transmitted to the high-rigidity portion 100 is effectively blocked by the low-rigidity portion 102, and the frame The vibration energy of the vibration transmitted to the floor panel 2 via the members 20, 22, 27, 28 is reduced without being distributed to the entire floor panel. As a result, acoustic radiation from the floor panel 2 can be more reliably reduced.

  Next, since the high-rigidity portion 100 is formed into a curved wave shape with a continuous curvature by the two curved surface portions 100b and 100c, the high-rigidity portion 100 is out of plane for the same reason as in the first embodiment. Even if the amount of protrusion in the direction is small, the rigidity of the high-rigidity portion 100 can be reliably increased. In the fourth embodiment, similarly to the first embodiment, it is preferable that the projecting heights of the curved surface portions 100b and 100c from the low-rigidity portion 102 are 10 mm or less in total.

  Next, since the curved surface portions 100b and 100c are formed so as to be aligned in the longitudinal direction (long side direction) of the rectangular high-rigidity portion 100, the concave and convex portions are continuous in the longitudinal direction as in the first embodiment. As a result, even if the height of the high-rigidity portion is suppressed, the rigidity in the longitudinal direction can be more reliably increased.

  Next, since the boundary portion 100d where the curvature is 0 extends in a curved shape, it is possible to prevent vibration energy from concentrating on the boundary portion 100d where the curvature is zero. Here, since the curvature of the boundary portion is 0, the amount thereof is smaller than that of the flat and low-rigidity portion, but vibration energy is easily concentrated. In addition, when the boundary portion extends linearly (see the boundary portions 70d, 80d, and 90d in the first to third embodiments), vibration that is bent at the boundary portion is likely to occur, or from the low-rigidity portion. It is considered that vibration energy is easily transmitted. On the other hand, in the fourth embodiment, since the boundary portion 100d extends in a curved shape, it is possible to make it difficult to generate vibration that causes the high-rigidity portion 100 to bend and to concentrate vibration energy. That is, it is considered that the boundary portion 100d having a curvature of 0 has higher rigidity than a linear shape even when the curvature is 0, and vibration energy is less likely to concentrate.

  Here, a modification of the fourth embodiment will be described with reference to FIG. In this modification, the boundary portion 110d extends as shown in FIG. 8, and the two curved surface portions 110b and 110c are formed in the same size and symmetrical shape. In this way, the rigidity of the high rigidity portion 110 can be increased more reliably. Also in this modified example, the above-described effects can be obtained.

  In other embodiments and modifications other than the fourth embodiment, the boundary portions (80d, 90d, 120d, 130d, etc.) of the curved surface portions may extend in a curved shape. Also, the same operation as in the fourth embodiment can be obtained.

  Next, a fifth embodiment of the present invention will be described. The fifth embodiment of the present invention is applied to the floor panel 2 of the underbody 1 of the automobile shown in FIG. 1, and the configuration of the underbody 1 other than the floor panel 2 is the same as that of the above-described first embodiment. is there. Further, similarly to the first embodiment, the vibration reduction structure having the same configuration is provided in each of the panel regions S1 and S2. Here, only the configuration of the panel region S1 of the floor panel 2 will be described with reference to FIGS. 9A to 9D, and description of other configurations will be omitted. FIG. 9A is an enlarged plan view showing the panel region S1 of the floor panel 2 according to the fifth embodiment of the present invention, and FIGS. 9B to 9D are respectively shown in FIG. 9A. It is sectional drawing which shows the cross-section of the floor panel 2 seen along line bb, cc, and dd. In FIG. 9 (a), contour lines are also shown in the same manner as in FIG. 4 (a). In the high-rigidity portion 100, lines other than the line indicating the boundary portion 100a with the low-rigidity portion 102 are as described above. This shows a contour line.

  As shown in FIG. 9A, in the fifth embodiment, a rectangular high-rigidity portion 120 is formed at the center of the panel region S1 and the high-rigidity portion 120 is formed in the same manner as in the first embodiment. A low-rigidity portion 122 extending in a square shape so as to surround the high-rigidity portion 120 is formed in the entire surrounding area. Further, as shown in FIGS. 9B to 9D, the high-rigidity portion 120 is integrally formed with the floor panel itself protruding in the out-of-plane direction, and the low-rigidity portion 122 has a high rigidity. It is formed substantially flat so as to be smaller than the rigid portion 120. Further, as shown in FIGS. 9A to 9D, the damping material 124 is provided in the low-rigidity portion 122 as in the first embodiment.

  Next, as shown in FIG. 9A and FIG. 9B, the high-rigidity portion 120 includes a convex convex curved surface portion 120b that protrudes upward in a region on the front side in the longitudinal direction of the vehicle body, A concave concave curved surface portion 120c that protrudes downward in the rear region is formed. In the fifth embodiment, the respective curved surface portions 120b and 120c themselves are further formed in a wave shape. Specifically, as shown in FIGS. 9A to 9D, the convex curved surface portion 120b includes a sub-curved surface portion 120e formed in a region on the vehicle inner side in the vehicle width direction, and the vehicle body. A sub-curved surface portion 120f formed in a region on the outer side is formed, and a concave curved surface portion 120c includes a sub-curved surface portion 120g formed in a region on the vehicle inner side in the vehicle width direction, and a vehicle body outer side. And a sub-curved surface portion 120h formed in the region.

As shown in FIG. 9B, the sub-curved surface portion 120e of the convex curved surface portion 120b is formed in a convex shape that protrudes further upward from the convex surface indicated by the two-dot chain line, and is shown in FIG. 9C. As described above, the sub-curved surface portion 120f of the convex curved surface portion 120b is formed in a concave shape that protrudes downward with respect to the convex surface indicated by a two-dot chain line. As described above, the convex curved surface portion 120b is further formed with a sub-wave shape portion having concavities and convexities in the vehicle width direction by the sub curved surface portions 120e and 120d.
Further, as shown in FIG. 9B, the sub-curved surface portion 120g of the concave curved surface portion 120c is formed in a concave shape that protrudes further downward from the concave surface indicated by a two-dot chain line, and is shown in FIG. 9C. As described above, the sub curved surface portion 120h of the concave curved surface portion 120c is formed in a convex shape that protrudes upward with respect to the concave surface indicated by a two-dot chain line. As described above, the concave curved surface portion 120c is further formed with a sub-wave shape portion having concavities and convexities in the vehicle width direction by the sub-curved surface portions 120g and 120h.
Further, the curved surface portions 120b (120e, 120f), 120c (120g, 120h) are set so that the distance in the vertical direction (height direction) between the uppermost portion and the lowermost portion of the high-rigidity portion 120 is 10 mm. ) Is formed.

  Next, as shown in FIGS. 9B to 9D, each curved surface portion 120b, 120c is formed of a curved surface having a continuous curvature, as in the first embodiment. That is, in the case of the fifth embodiment, the sub-curved surface portions 120e, 120f, 120g, and 120g are each configured by a curved surface having a continuous curvature, and extend over the sub-curved surface portions 120e and 120f, and the sub-curved surface portions It is formed so that the curvature continuously changes over 120 g and 120 h. Further, as in the first embodiment, the high-rigidity portion 120 is formed such that the curvature continuously changes over the curved surface portions 120b and 120c. The curvature is 0 at the boundary portion 120d between the curved surface portions 120b and 120c, the boundary portion 120m between the sub curved surface portions 120e and 120f, and the boundary portion 120n between the sub curved surface portions 120g and 120h.

  Thus, in the fifth embodiment, the high-rigidity portion 120 is configured by a curved surface having a continuous curvature. Further, the high-rigidity portion 120 has a wave shape in which a convex curved surface and a concave curved surface are continuous in the longitudinal direction by the curved surface portions 120b and 120c and the sub-curved surface portions 120e, 120f, 120g, and 120g. . Also in the short side direction, except for the boundary portion 120d, a convex curved surface and a concave curved surface have a continuous wave shape.

Next, functions and effects of the fifth embodiment will be described.
First, in the fifth embodiment, the vibration energy of the panel region is reduced by the high-rigidity portion 120 and the low-rigidity portion 122 in the same manner as the effects of the first embodiment described above, so that the acoustic radiation from the panel region is reduced. Can be reduced. Moreover, the vibration energy in the panel region is further reduced by the damping material 124. Further, only one high-rigidity part 120 is formed at the center of the panel region (S1, S2) and the area thereof is relatively large, and the low-rigidity part 120 surrounds the high-rigidity part 120 around the entire area. 122 is formed, the vibration is effectively concentrated on the low-rigidity portion 122 and greatly distorted, and the vibration transmitted to the high-rigidity portion 120 is effectively blocked by the low-rigidity portion 122, and the frame The vibration energy of the vibration transmitted to the floor panel 2 via the members 20, 22, 27, 28 is reduced without being distributed to the entire floor panel. As a result, acoustic radiation from the floor panel 2 can be more reliably reduced.

  Next, the high-rigidity portion 120 is formed into a curved surface having a continuous curvature by the two curved surface portions 120b and 120c and the four sub-curved surface portions 120e to 120h formed on them. For the same reason as the form, even if the protruding amount of the high-rigidity portion 120 in the out-of-plane direction is small, the rigidity of the high-rigidity portion 120 can be reliably increased. Since the curved surface portions 120b and 120c are formed so as to be aligned in the longitudinal direction (long side direction) of the rectangular high-rigidity portion 120, as in the first embodiment, the unevenness continues in the longitudinal direction. As a result, even if the height of the high-rigidity portion is suppressed, the rigidity in the longitudinal direction can be more reliably increased.

  In particular, in the fifth embodiment, the curved surface portions 120b and 120c are each formed in a wave shape by the sub curved surface portions 120e to 120h (sub wave shape portions). The rigidity of 120c itself can be further increased. As a result, the rigidity in the longitudinal direction (long side direction) of the high-rigidity portion 120 can be further increased. In the fifth embodiment, the sub-curved surface portions 120e to 120h are formed side by side in the short side direction and have a wave shape in which convex and concave shapes are continuous in the short side direction of the high rigidity portion 120. The rigidity in the side direction can also be increased.

  Similarly to the first embodiment, the difference in height between the most protruding portions from the low-rigidity portion 82 of the high-rigidity portion 120 upward and downward is 10 mm. It is possible to increase the rigidity of the high-rigidity portion 120 while preventing this.

Next, another aspect of the present invention will be described.
First, as shown in FIGS. 10A to 10D, a total of four curved surface portions 130b and 130c are formed, two each in the long side direction and the short side direction of the rectangular high-rigidity portion 130. May be. In the high-rigidity portion 130 shown in FIG. 10, two convex curved surface portions 130b are formed so as to be located on the diagonal line, while two concave curved surface portions 130c are also formed so as to be located on the diagonal line. As shown in FIGS. 10B to 10D, the high-rigidity portion 130 is configured by a curved surface having a continuous curvature, as in the first embodiment. As shown in FIG. 10A, the boundary portion 130d between the curved surface portions 130b and 130c extends in the vehicle body front-rear direction and the vehicle width direction so as to intersect at substantially the center of the high-rigidity portion 120, respectively. In addition, the code | symbol 132 is a low-rigidity part and the code | symbol 134 is a damping material, and all are formed similarly to 1st Embodiment.

  According to the high rigidity portion 130 formed in this way, the rigidity can be more reliably increased in both the vehicle body longitudinal direction and the vehicle width direction. In particular, when the area of the floor panel surrounded by the frame member (panel area S1 or the like) is large, or when forming a square high-rigidity portion in a square area such as the panel area S7, for example. It may be formed as shown in FIG. In the arrangement of the curved surface portions 130b and 130c, each curved surface portion may be formed as in the second to fourth embodiments. Further, three or more curved surface portions may be arranged in the longitudinal direction of the vehicle body and / or the vehicle width direction.

Next, the high-rigidity part may be formed such that three or more curved parts are aligned in the longitudinal direction.
Next, the floor panel 2 to which each of the above-described embodiments is applied is provided across the vehicle width direction and has a plurality of panel regions (S1, S2). Similar effects can be obtained also in a floor panel in which individual panels are used for each panel, and the peripheral edge of each panel is joined to each frame.
Next, for example, as in the above-described floor panels 4, 6, and 10, a part thereof is also surrounded by a bead portion (56, 58) and / or a fold portion (54) that is a vibration regulating portion while being surrounded by a frame member. Even when the same vibration reduction structure as that of the above-described embodiment is provided in the panel regions S4 to S7, the same effect can be obtained.
Next, even if a vibration reducing structure similar to that of the above-described embodiment is formed in a panel region whose shape is not rectangular, for example, the panel regions S4 to S6 of the above-described floor panels 4 and 6, the same effect can be obtained. can get. In this case, the high-rigidity part may be formed in a trapezoidal shape according to the shape of the panel region, for example, and the shape of each curved surface part may be a trapezoidal shape in plan view.

It is a perspective view which shows the underbody of the motor vehicle provided with the floor panel by embodiment of this invention. It is the top view (a) which shows the experimental model of the floor panel which has a vibration reduction structure, and sectional drawing (b) seen along the AA line. It is a diagram which shows the experimental result obtained from the experimental model of FIG. 2, and the experimental model of the conventional panel. It is an enlarged plan view which shows panel area | region S1 of the floor panel 2 by 1st Embodiment of this invention. FIG. 5 is a cross-sectional view showing a cross-sectional structure in the longitudinal direction of the vehicle body as viewed along line bb in FIG. It is sectional drawing which shows the cross-section of the vehicle width direction seen along the cc line of Fig.4 (a). It is an enlarged plan view which shows panel area | region S1 of the floor panel 2 by 2nd Embodiment of this invention. FIG. 6 is a cross-sectional view showing a cross-sectional structure in the longitudinal direction of the vehicle body as viewed along line bb in FIG. It is sectional drawing which shows the cross-section of the vehicle width direction seen along the cc line of Fig.5 (a). It is sectional drawing which shows the cross-section of the vehicle width direction seen along the dd line of Fig.5 (a). It is an enlarged plan view which shows panel area | region S1 of the floor panel 2 by 3rd Embodiment of this invention. It is sectional drawing which shows the cross-sectional structure of the vehicle body front-back direction seen along the bb line of Fig.6 (a). It is sectional drawing which shows the cross-sectional structure of the vehicle width direction seen along the cc line of Fig.6 (a). It is an enlarged plan view which shows panel area | region S1 of the floor panel 2 by 4th Embodiment of this invention. It is sectional drawing which shows the cross-sectional structure of the vehicle body front-back direction seen along the bb line | wire of Fig.7 (a). It is sectional drawing which shows the cross-sectional structure of the vehicle width direction seen along the cc line of Fig.7 (a). It is sectional drawing which shows the cross-section of the vehicle width direction seen along the dd line of Fig.7 (a). It is sectional drawing which shows the cross-sectional structure of the vehicle width direction seen along the ee line of Fig.7 (a). It is an enlarged plan view which shows panel area | region S1 of the floor panel 2 by the modification of 4th Embodiment of this invention. It is an enlarged plan view which shows panel area | region S1 of the floor panel 2 by 5th Embodiment of this invention. It is sectional drawing which shows the cross-sectional structure of the vehicle body front-back direction seen along the bb line | wire of Fig.9 (a). It is sectional drawing which shows the cross-sectional structure of the vehicle body front-back direction seen along the cc line of Fig.9 (a). It is sectional drawing which shows the cross-section of the vehicle width direction seen along the dd line of Fig.9 (a). It is an enlarged plan view which shows panel area | region S1 of the floor panel 2 by the other aspect of this invention. It is sectional drawing which shows the cross-sectional structure of the vehicle body front-back direction seen along the bb line of Fig.10 (a). It is sectional drawing which shows the cross-sectional structure of the vehicle body front-back direction seen along the cc line of Fig.10 (a). It is sectional drawing which shows the cross-section of the vehicle width direction seen along the dd line of Fig.10 (a).

Explanation of symbols

1 Car underbody
2,4,6,8,10,12,14,16 1st to 8th floor panels
S1 to S8 Panel area
18 Front side frame
20 Side sills
22 Floor side frame
24 Rear side frame
26-34 No. 1-No. 9 cross members
36-38 No. 1-No. 3 tunnel side members
40 engine
42 Front suspension cross member
46 Rear suspension cross member
70,80,90,100,110,120,130 High rigidity part
72,82,92,102,112,122,132 Low rigidity part
74,84,94,104,114,124,134 Damping material
70a, 80a, 90a, 100a, 110a, 120a, 130a Peripheral part of high rigidity part (boundary part with low rigidity part)
70b, 80b, 90b, 90c, 100b, 110b, 120b, 130b
70c, 80c, 100c, 110c, 120c, 130c Concave surface of highly rigid part
70d, 80d, 90d, 100d, 110d, 120d, 130d
120e, 120f, 120g, 120h Sub-curved surface of curved surface of high-rigidity
120m, 120n Boundary between sub-curved surfaces

Claims (3)

A vehicle body floor panel connected to a frame member disposed in a vehicle longitudinal direction and a vehicle width direction and constituting a vehicle floor,
The floor panel is formed with a rectangular panel region at least partially surrounded by the frame member,
A rectangular high-rigidity portion formed in the center of the rectangular panel region and adapted to the shape of the panel region in plan view ; and a low-rigidity portion formed flat over the entire area around the high-rigidity portion; A damping material provided only in the entire region of the low-rigidity portion in the panel region of the floor panel ,
The high rigidity portion is formed with an upward curved surface portion protruding upward from the low rigidity portion and a downward curved surface portion protruding downward from the low rigidity portion. The upward curved surface portion and the downward curved surface are formed. The part is formed so as to be aligned in the long side direction of the high-rigidity part and is configured by a curved surface having a continuous curvature.
The high-rigidity portion has a boundary portion having a curvature of 0 between the upper curved surface portion and the lower curved surface portion, and the boundary portion extends in a curved shape in the short side direction of the high-rigidity portion in plan view. The floor panel of the vehicle body is characterized by being formed as follows . The high rigidity portion the upward direction the curved surface portion and the vehicle body floor panel according to claim 1, wherein the height of the downward curved portion are identical to each other in. The floor of the vehicle body panel of highest of protruding portions according to claim 1 is 10mm or less from the low-rigidity portion of the high rigidity portion.

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