JPH07165120A - Vehicle hood reinforcement structure - Google Patents

Abstract

(57) [Abstract] [Purpose] The hood of the engine room can be made lighter and its height can be reduced, while suppressing deformation due to external force and enabling protection of parts in the engine room. [Structure] Hood 1 located above the engine room
Further, the vehicle hood reinforcement structure is provided with an inertial mass 13 around a portion having a small clearance between the hood 1 and the engine room internal component 11, and a circle 17 having a radius L that surrounds the periphery with a portion having a small clearance. And T is an arbitrary time of the repulsive force waveform with respect to the impact input to the hood 1,
Let V be the speed at which the wave propagates when the hood 1 is deformed by an impact, and c be the coefficient determined by the form of the hood 1, and L = c · V
・ Characterized by the relationship of T.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle hood reinforcing structure for covering an engine room of a vehicle body.

[0002]

2. Description of the Related Art A conventional vehicle hood energy absorption structure is shown in FIG. 45, for example, as disclosed in Japanese Utility Model Laid-Open No. 55-136682. The hood 1 includes an outer panel 3 and an inner panel 5, and an energy absorbing material 7 is provided on the entire inner surface of the hood 1. Therefore, as shown in FIG. 46A, when the load F acts on the upper surface of the hood 1, the energy absorbing material 7 can effectively absorb the energy, and the rigidity of the entire hood 1 and the existence of the energy absorbing material 7 The deformation can be suppressed as shown in FIG.

[0003]

However, in the above structure, the energy absorbing material 7 is used as the outer panel 3.
Outer panel 3 because it is provided almost all over
Moreover, even if the inner panel 5 itself is thinned to reduce its weight, the weight of the energy absorbing material 7 itself cannot be expected to be as light as expected. Moreover, since the energy absorbing member 7 is present, the hood 1 and the parts 9
Therefore, the hood 1 may be unnecessarily high.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a vehicle hood reinforcing structure which is lighter in weight and can be reduced in height.

[0005]

In order to solve the above-mentioned problems, the invention of claim 1 provides a hood located on the upper side of the engine room in the vicinity of a portion having a small clearance between the hood and parts in the engine room. A reinforcing structure for a vehicle hood provided with an inertial mass, wherein the periphery is a circle having a radius L surrounding a portion having a small clearance, and T is an arbitrary time of a repulsive force waveform with respect to an impact input to the hood, A vehicle hood reinforcement structure characterized in that the speed at which waves propagate when the hood is deformed by the impact is V, a coefficient determined by the form of the hood is C, and L = c · V · T. .

The invention of claim 2 is the vehicle hood reinforcing structure according to claim 1, wherein the hood comprises an outer panel and an inner panel, and the inertial mass is partially fixed to the outer panel. A reinforcing structure for a vehicle hood, which is a separate member.

A third aspect of the present invention is the vehicle hood reinforcement structure according to the second aspect, wherein the separate member has a shape substantially conforming to the lower surface shape of the outer panel. Construction.

The invention according to claim 4 is the vehicle hood reinforcing structure according to claim 1, wherein the hood comprises an outer panel and an inner panel, and the inertial mass is a separate member fixed to the inner panel. A reinforcement structure for a vehicle hood, which is characterized in that

A fifth aspect of the present invention is the vehicle hood reinforcing structure according to the fourth aspect, wherein the separate member is a reinforcing member made of glass wool, urethane or the like.

A sixth aspect of the present invention is the vehicle hood reinforcement structure according to the first aspect, wherein the inertial mass is a vehicle functional component such as a washer reservoir tank, a radiator fluid reservoir tank, and a fuse box. Vehicle hood reinforcement structure

A seventh aspect of the present invention is the vehicle hood reinforcement structure according to the first aspect, wherein the hood includes an outer panel and an inner panel, and the inertial mass is obtained by partially enlarging the inner panel. A reinforcement structure for a vehicle hood, which is a bulge.

An eighth aspect of the present invention is the vehicle hood reinforcement structure according to the first aspect, wherein the hood includes an inner panel and an outer panel, and the inertial mass is a crossing portion of the inner panel. Vehicle hood reinforcement structure characterized by.

[0013]

According to the invention of claim 1 of the above-mentioned means, the deformation of the hood due to the impact input can be remarkably suppressed by the inertial mass provided around the portion having a small clearance with the parts in the engine room. In particular, L = c · V · T considering the arbitrary time T of the repulsive force waveform with respect to the impact input to the hood, the speed V at which the wave propagates when the hood is deformed by impact, and the coefficient c determined by the form of the hood Since it is specified as the periphery, the interference between the engine room component and the hood can be accurately suppressed.

According to the invention of claim 2, in addition to the function of the invention of claim 1, the inertial mass can be constituted by a separate member.

According to the invention of claim 3, in addition to the effect of the invention of claim 2, another member can be attached along the inner surface of the outer panel.

According to the invention of claim 4, in addition to the function of the invention of claim 1, the inertial mass can be a separate member fixed to the inner panel.

According to the invention of claim 5, in addition to the effect of the invention of claim 4, the reinforcing structure of the inner panel can be achieved by using a separate member as a reinforcing material such as glass wool or urethane and a sound vibration countermeasure material.

According to the invention of claim 6, in addition to the operation of the invention of claim 1, the inertial mass can be constituted by vehicle functional parts such as a washer reservoir tank, a radiator fluid reservoir tank and a fuse box.

According to the invention of claim 7, in addition to the operation of the invention of claim 1, the inertial mass can be constituted by the inner panel itself.

According to the invention of claim 8, in addition to the operation of the invention of claim 1, since the inertial mass can be constituted by the inner panel itself and the intersecting portion of the inner panel is utilized, the number of constituent elements is hardly increased.

[0021]

Embodiments of the present invention will be described below.

FIG. 1 is a perspective view schematically showing the relationship between a hood 1 to which a hood reinforcing structure according to a first embodiment of the present invention is applied and a power unit 11 which is a component in an engine room. 2 is a schematic sectional view taken along the line AA of FIG.

As shown in FIGS. 1 and 2, the upper portion of the power unit 11 is a portion where the clearance between the hood 1 and the power unit 11 is small. Therefore, the block 13, which is a separate member as an inertial mass, is adhered and fixed around the power unit 11 by the adhesive material 15. The block 13 is made of metal, resin, urethane, glass wool, or the like.

The periphery is a circle 17 having a radius L and surrounding the power unit 11 when viewed from above. The center of the radius L is set approximately at the center of the power unit 11. A pair of blocks 13 are provided on a circle 17 having a radius L, for example, on the left and right of the power unit 11 in the vehicle width direction.
The block 13 may be continuously provided on the circle 17, or one block 13 may be provided instead of a plurality.

The radius L is defined as T at an arbitrary time of the repulsive force waveform with respect to a shock input to the hood 1, and the speed V at which the wave propagates when the hood 1 is deformed by a shock is assumed. The form of the hood 1 such as the plate thickness of the hood 1. , Where curvature is a parameter coefficient determined by the shape of the inner panel, such as how the inner panel is passed, and is defined by L = c · V · T (1).

Next, the concrete determination of the radius L will be described.
First, the relationship between the repulsive force of the hood 1 and the time when a roof tile or the like hits the hood 1 without the block 13 or the like is as shown by the solid line in FIG. That is, the first peak of the repulsive force appears in the initial stage of the interference of roof tiles and the like with the hood 1, and the second peak appears after the first peak. The second peak is when the hood 1 interferes with the power unit 11 or the like. FIG. 3B shows the relationship between the first peak and the second peak in relation to the stroke of the hood 1. Thus, the second peak appears after the deformation stroke of the hood 1 has considerably advanced. As is apparent from FIG. 3 (b), the hood 1 can be moved to the second position before it interferes with the power unit 11.
It is sufficient to generate the peak of. When viewed in relation to time, a second peak is generated at time T as shown in FIG. Considering this, the distance L can be determined as follows. That is, the time up to the second peak to be generated immediately after the first peak is T
Then, L is obtained from the above equation (1).

Here, c, V and T can be obtained from experiments and model analysis. For example, FIG. 4 shows a simple model 19 of the hood 1, and FIG. 5 shows the analysis result. In FIG. 4, the position of the inertial mass with respect to the load F is 3
The type is displayed. Mass 21 and Mass 2 from near
3 and 25. This square 21,23,25
The relationship between the distance L and the time T depending on the position of was obtained as shown in FIG. The slope of the straight line in this case is c · V. From the above, it was confirmed that the position of the inertial mass with respect to the hood 1 has a great influence on the control of the hood displacement.

The distance L at which the block 13 is provided in FIGS. 1 and 2 is properly set in consideration of the above.

With this setting, the load F is applied to the hood 1 at a position corresponding to the power unit 11 as shown in FIG. 6 (a).
Even if is input, the deformation stroke S of the hood 1 becomes extremely small as shown in FIG. 2B, and the interference with the power unit 11 can be effectively suppressed. Therefore, even if a roof tile or the like hits the hood 1, the collision energy can be effectively absorbed by the hood 1 itself and can be restricted from reaching the power unit 11, and the damage can be effectively prevented. Moreover, since the block 13 is partially provided, the weight increase of the hood 1 can be suppressed. Further, since the block 13 is provided around the power unit 11, it is not necessary to consider the clearance between the block 13 and the power unit 11, and an increase in height with respect to the power unit 11 and the like can be suppressed.

Next, another embodiment will be described. In the following embodiments, the same components as those in the first embodiment will be designated by the same reference numerals, and duplicated description will be omitted.

7 to 9 show a second embodiment of the present invention. FIG. 7 is a schematic bottom view showing the power unit 11 for convenience. FIG. 8 shows BB of FIG.
FIG. 9 is a schematic cross-sectional view taken along the line arrow, and FIG. 9 is an enlarged cross-sectional view of a main part.

In this embodiment, a separate member 27 is fixed to the outer panel as an inertial mass. The separate member 27 is formed of a panel having a thickness larger than that of the outer panel 3, and is joined by laser welding or the like so that the upper surface 27a is flush with the upper surface 3a of the outer panel 3. That is, in this embodiment, the outer panel 3 itself is a steel sheet having a different thickness. Therefore, in this second embodiment, the separate member 27 serves as an inertial mass, which has the same effect as that of the first embodiment, and has the following unique effect.

That is, by making the outer panel 3 a steel sheet of different thickness, the rigidity of the outer panel 3 itself is increased,
Therefore, the entire plate can be made thinner and the weight can be further reduced.

FIG. 10 shows a third embodiment. In this embodiment, another member 29 as an inertial mass is fixed to the lower surface 3b of the outer panel 3 by laser welding or adhesion. The separate member 29 is panel-shaped, and the upper surface 29a is formed in a shape substantially along the lower surface 3b of the outer panel 3, and is fixed by laser welding or the like so that the upper surface 29a is in close contact with the lower surface 3b of the outer panel 3. . Therefore, in the third embodiment, the same effect as that of the second embodiment is obtained, and in addition to the following peculiar effects.

That is, the separate member 29 can be attached substantially along the shape of the lower surface 3b of the outer panel 3, and the attachment can be performed without difficulty. As the separate member 29, a thick portion of the hood insulator or a hood insulator having a high density can be used.

FIG. 11 shows a fourth embodiment. In this embodiment, an annular reinforcing material is used as the separate member 31 fixed to the outer panel 3. The separate member 31 is formed of metal, resin urethane, glass wool, or the like. The width m ₁ of the left and right sides 31a and 31b of the separate member 31 is formed to be larger than the width m ₂ of the other part.
It is formed continuously from a and 31b so that the width is gradually reduced. The left and right sides 31a and 31b are located at the distance L. Therefore, in this embodiment, in addition to the same effects as the first embodiment, the following unique effects are achieved.

That is, since the separate member 31 is provided in a ring shape, the reinforcing effect on the hood 1 can be further improved. In addition, the deformation of the hood 1 at the portion 11 of the power unit can be suppressed in the entire periphery thereof, and a more reliable deformation suppressing effect can be obtained. Furthermore, since the separate member 31 has an annular shape, there is an effect that the number of parts is small. In this embodiment, the separate member 31 is used as the power unit 11.
In accordance with the rectangular shape of the power unit 11, the distance between the periphery of the power unit 11 and the separate member 31 is the same all around, and a reliable deformation suppressing effect according to the shape of the power unit 11 can be obtained. it can.

12 and 13 show a fifth embodiment. 12 is a schematic bottom view of the hood 1, and FIG. 13 is a schematic sectional view taken along the line CC of FIG. In this embodiment, three separate members 32 and 33 are provided at a distance L from the power unit 11. Separate member 32,
Reference numeral 33 is a block or plate of metal, resin, urethane, glass wool or the like, and is fixed inside the inner panel 5.
Therefore, this embodiment has the same effects as the first embodiment, and also has the following unique effects.

That is, since three separate members 32 and 33 are provided, the deformation suppressing effect of the hood 1 can be further enhanced. Since the separate members 32 and 33 are fixed inside the inner panel 5, the external appearance is the same as that without the separate members 32 and 33, and the appearance can be improved.

FIG. 14 shows a sixth embodiment. In this embodiment, another member 35 made of the same material as the other members 32 and 33 of the fifth embodiment is fixed inside the inner panel 5 so as to contact the lower surface 3b of the outer panel 3. Therefore, in this sixth embodiment, in addition to the same effects as the fifth embodiment, the separate member 35 is attached to the lower surface 3b of the outer panel 3.
Since it adheres to, the energy absorption effect can be efficiently obtained.

FIG. 15 shows a seventh embodiment. This FIG. 15 shows a part of the inner panel 5,
A separate member 37 is fixed to the inner panel 5 at the same position as the separate member 35 of the sixth embodiment. The separate member 37 is formed of a lump or plate of metal, resin or the like, and is fixed to the side wall 5a and the bottom wall 5b of the inner panel 5 by welding or the like. As a result, the inertial mass can be formed in the portion of the distance L as described above. Therefore, in this embodiment, the same effect as that of the sixth embodiment is obtained, and in addition, the following peculiar effects are obtained.

That is, since the inner panel 5 itself can be reinforced by the separate member 37, the inner panel 5 can be made thin and the weight can be further reduced.

FIG. 16 shows an eighth embodiment. In this embodiment, another member 39 is fixed to the bottom wall 5b of the inner panel 5. The separate member 39 is formed of metal or resin in a wave shape. Therefore, in this embodiment, in addition to the same effects as the seventh embodiment, the following unique effects are achieved.

That is, by making the wavy shape various, it is possible to make the energy absorption characteristics ideal to match the hood.

17 and 18 show the ninth embodiment. 17 shows a schematic bottom view of the hood 1, and FIG. 18 shows a partial perspective view of the inner panel 5. In this embodiment, a duct 41 for cooling the engine compartment is fixed to the bottom wall 5b in the hood inner panel 5 as a separate member. The duct 41 is made of metal or resin. Therefore, this embodiment has the same effect as the fifth embodiment, and also has the following unique effect.

That is, the duct 41 can take in cooling air and can be used for cooling the inside of the engine compartment.

19 and 20 show a tenth embodiment. 19 is a schematic bottom view of the hood 1, and FIG. 20 is a schematic cross-sectional view taken along the line DD of FIG. In this embodiment, the inertial mass is composed of the vehicle functional parts 43. The vehicle functional component 43 is, for example, a washer reservoir tank, a radiator fluid reservoir tank, a fuse box, or the like. Therefore, in this embodiment, in addition to the operation and effect substantially similar to those of the first embodiment, the following unique effect is obtained.

That is, since the vehicle functional component 43 such as the radiator fluid reservoir tank is used as the inertial mass, there is no particular increase in weight, and the increase in weight of the entire vehicle body can be suppressed.

21 and 22 show the eleventh embodiment. 21 is a schematic bottom view of the hood 1, and FIG. 22 is a schematic sectional view taken along the line EE of FIG. In this embodiment, the inertial mass is constituted by a hood bulge 45 as a vehicle functional component. The hood bulge 45 is fixed to the outer panel 3 by a mounting member 47. Therefore, in this embodiment as well, the same effects as those of the first embodiment can be obtained.
Since the hood bulge 45 constitutes the inertial mass, it is not necessary to provide a special inertial mass, and the increase in weight of the entire vehicle body can be suppressed.

In this embodiment, the mounting member 47 of the hood bulge 45 can be installed at the position of the distance L as an inertial mass.

23 and 24 show a twelfth embodiment. 23 is a schematic bottom view of the hood 1, and FIG. 24 is a schematic cross-sectional view taken along the line GG of FIG. In this embodiment, an air duct 49 which is a vehicle functional component is used as the inertial mass. In addition to the same operational effects as the first embodiment, this embodiment also has the following unique effects.

That is, since the air duct 49 is used as the inertial mass, there is no particular increase in weight, and the increase in weight of the entire vehicle body can be suppressed. Moreover, it can function as the air duct 49. A washer may be used instead of the air duct.

25 and 26 show a thirteenth embodiment. 25 shows a schematic bottom view of the hood 1, and FIG. 26 shows a schematic cross-sectional view taken along the line II of FIG. In this embodiment, the vehicle functional component 51 is used as the inertial mass, and the vehicle functional component 51 is fixed to the inner panel 5. The vehicle functional component 51 is, for example, a radiator fluid reservoir tank, a washer reservoir tank, or a fuse box. Therefore, in this embodiment as well, the same operational effects as those of the tenth embodiment and the like can be obtained, and since the vehicle functional component 51 is attached to the inner panel 5, the attachment can be simplified.

FIG. 27 shows a fourteenth embodiment. In this embodiment, the vehicle functional component 53 integrated with the inner panel 5 is used as the inertial mass. That is, the inner panel 5
The vehicle functional part 53 is accommodated by enlarging a part of the above. The vehicle functional component 53 is a radiator fluid reservoir tank, a washer reservoir tank, a fuse box, or the like. Therefore, in this embodiment and the first embodiment as well, the same effects and advantages as described below are achieved.

That is, the vehicle functional component 53 is used as the inertial mass.
Therefore, the increase in vehicle weight can be suppressed as compared with the case where a special reinforcing member is used. Further, since the vehicle functional component 53 is housed in the inner panel 5, the vehicle functional component 53 can be protected.

28 and 29 show the fifteenth embodiment. 28 is a schematic bottom view of the hood 1, and FIG. 29 is a perspective view of a main part. That is, in this embodiment, the inertial mass is constituted by the sub tank 55 which is a vehicle functional component. The sub tank 55 is housed in the inner panel 5. The sub tank 55 is connected to a liquid tank 59 such as a radiator fluid reservoir tank or a washer reservoir tank via a first hose 57. Further sub tank 5
5 is connected via a second hose 61 so as to send the liquid to a required location. According to this embodiment, the sub tank 55
A constant amount of liquid is always sent from the liquid tank 59 through the first hose 57. Therefore, the function as the inertial mass of the sub tank 55 can always be maintained.
Therefore, in this embodiment as well, the sub-tank 55 has substantially the same effect as that of the fourteenth embodiment, and also has the following unique effect.

That is, since the sub-tank 55 is provided, a sufficient amount of tank liquid can be provided, and the radiator function and the window washer can surely function. Further, the function as the inertial mass can be surely exerted without being influenced by the liquid amount of the liquid tank 59.

30 and 31 show the 16th embodiment. In this embodiment, a reinforcing member 63 is provided between the outer panel 3 and the inner panel 5 as a separate member having an inertial mass. The reinforcing member 36 is formed of metal, resin, urethane, glass wool or the like, and is fixed to both the outer panel 3 and the inner panel 5. Therefore, also in this embodiment, the reinforcing member 63 has substantially the same effect as the fourteenth and fifteenth embodiments, and also has the following unique effect.

That is, since the reinforcing material 63 is installed so as to be in contact with both the outer panel 3 and the inner panel 5, it is possible to efficiently obtain the energy absorbing effect by the inertial mass of the reinforcing material 63 and to improve the appearance. You can

32 and 33 show the seventeenth embodiment. In this embodiment, the inertial mass is formed by the partially enlarged portion 65 of the inner panel 5. The enlarged portion 65 is formed by partially increasing the sectional height H ₁ of the inner panel 5 as H ₂ . The enlarged portion 65 can also be configured by partially increasing the cross-sectional width of the inner panel 5 or partially increasing the plate thickness.
Therefore, in this embodiment also, in addition to the same effects as described above,
The following unique effects are achieved.

That is, since the inertial mass is composed of the inner panel 5 itself and no separate member is provided, an increase in the number of parts can be suppressed. In addition, the reinforcing effect of the outer panel 3 can be increased in the enlarged portion 65.

34, 35 and 36 show the 18th embodiment. 34 shows a schematic bottom view of the hood 1, FIG. 35 shows an enlarged perspective view of a main part of the inner panel, and FIG.
Shows a schematic sectional view taken along the line JJ of FIG. In this embodiment, the inertial mass is formed by the intersecting portion 67 of the inner panel 5. A wavy portion 69 is provided at the crossing portion 67 of the inner panel 5. When the load on the outer panel 3 changes, the crossing portion 67 of the inner panel 5 can be easily deformed by the corrugated portion 69. Therefore, the crossing portion 67 of the inner panel 5 has a structure that does not reduce the inertial mass while reducing the rigidity thereof due to the existence of the corrugated portion 69. Therefore, in this embodiment, the intersection 67
With the inertial mass of (1), substantially the same operational effect as that of the seventeenth embodiment is achieved, and in addition, the following peculiar effects are exhibited.

That is, the size and the like of the wavy portion 69 can be adjusted to make its characteristics ideal.

37 and 38 show the 19th embodiment. FIG. 37 shows an enlarged perspective view of an essential part of the inner panel 5, and FIG. 38 shows a schematic sectional view taken along the line KK of FIG. In this embodiment, the inertial mass is formed by the crossover portion 71 of the inner panel 5, and the crossover portion 71 is provided with the mountain-shaped member 73. Due to the existence of the mountain-shaped member 73, the intersection 71
It suppresses the decrease in inertial mass while reducing the rigidity of the. Therefore, in this embodiment, the same effect as that of the eighteenth embodiment is obtained, and in addition, the following peculiar effects are obtained.

That is, since the ridges of the mountain-shaped members connect the inner panels 5 to each other, the rigidity thereof can be set to a predetermined value.

FIG. 39 shows a twentieth embodiment. This FIG. 39 shows a schematic bottom view of the hood 1, and the inertial mass is composed of a circular portion 75 provided on the inner panel 5. The circular portion 75 is configured to surround the power unit 11. Therefore, also in this embodiment, the circular portion 75 is used as the inertial mass to achieve the same effect as in the seventeenth embodiment, and since the circular portion 75 surrounds the power unit 11, a more reliable hood deformation suppressing effect can be obtained. it can.

FIG. 40 shows a twenty-first embodiment. FIG. 40 shows a schematic bottom view of the hood 1, and the inertial mass is constituted by a partially cut-out circular portion 77 provided on the inner panel 5. The partially cut-out circular portion 77 is also configured to substantially surround the power unit 11. Therefore, also in this embodiment, the partially cut-out circular portion 77 can be used as the inertial mass to achieve substantially the same effect as that of the twentieth embodiment.

FIG. 41 shows the 22nd embodiment. 41. FIG. 41 shows a schematic bottom view of the hood 1, which has an inertial mass formed by a circular portion 79 provided on the inner panel 5. The circular portion 79 surrounds the power unit 11 like the circular portion 75 of the twentieth embodiment. Therefore, also in this embodiment, the circular portion 79 can be used as the inertial mass to achieve substantially the same effect as that of the twentieth embodiment.

FIG. 42 shows the twenty-third embodiment. FIG. 23 shows a schematic bottom view of the hood 1, which has an inertial mass composed of a circular portion 81 and an enlarged portion 83 provided on the inner panel 5. The circular portion 81 is configured to surround the power unit 11. Therefore, in this embodiment, the circular portion 81 and the enlarged portion 83 serve as an inertial mass, and it is possible to obtain substantially the same effect as that of the twentieth embodiment. Further, the presence of the enlarged portion 83 makes it possible to obtain a more reliable deformation suppressing effect.

FIG. 43 shows the 24th embodiment. This FIG. 43 shows a schematic bottom view of the hood 1. This embodiment is applied to the case where there are a plurality of places with a small clearance from the components in the engine room. In this embodiment, an inertial mass 87 is provided at an intermediate portion between the power unit 11 and another engine room component 85. The inertial mass 87 is composed of, for example, a reinforcing material made of metal, resin, urethane, glass wool, or the like, or vehicle functional parts such as a radiator fluid reservoir tank, a washer reservoir tank, and a fuse box. The arrangement state of the inertial mass 87 is as shown in FIG. That is, the distance obtained by the relationship of L = c · V · T for the power unit 11 is L1, and the distance similarly obtained for the engine room component 85 is L2.
And the distance between the engine room 85 and P is set to P, and P ≦ L1
In the case of the relationship of + L2, the inertial mass 87 is installed at at least one of the intersections of the circles having the radii L1 and L2.
As a result, the inertial mass 87 acts on both the power unit 11 and the engine room internal component 85, and the deformation suppressing effect can be similarly obtained even when the engine room internal component having a small clearance is provided at a plurality of locations. . Moreover, an increase in the number of inertial mass 87 can be suppressed.

[0071]

As is clear from the above, according to the invention of claim 1, the effect of suppressing the deformation of the hood can be obtained by the presence of the inertial mass set to the distance L = c · V · T.
It is possible to surely protect the parts in the engine room against external force. Further, since the entire hood 1 is not reinforced, the weight can be reduced. Further, since the energy absorbing member does not exist above the engine room internal parts, the clearance between the engine room internal parts and the hood can be reduced, and the overall height of the hood can be reduced.

According to the invention of claim 2, in addition to the effect of the invention of claim 1, since the inertial mass is constituted by a separate member partially fixed to the outer panel, it can be easily applied to an existing vehicle. .

According to the invention of claim 3, in addition to the effect of the invention of claim 2, since the separate member has a shape substantially conforming to the shape of the lower surface of the outer panel, the function as an inertial mass is sufficiently exerted, and the separate member is attached. Can be reliably performed.

According to the invention of claim 4, in addition to the effect of the invention of claim 1, since the inertial mass is a separate member fixed to the inner panel, it can be easily attached without affecting the outer panel. Further, by providing the inertial mass inside the inner panel, the appearance can be made equal to that without the inertial mass.

According to the invention of claim 5, in addition to the effect of the invention of claim 4, since the separate member is made of a reinforcing material such as glass wool or urethane, the reinforcing effect of the inner panel can be obtained.

According to the invention of claim 6, in addition to the effect of the invention of claim 1, since the inertial mass is constituted by vehicle functional parts such as a washer reservoir tank, a radiator fluid reservoir tank and a fuse box, no special separate member is required. Therefore, the increase in weight can be suppressed.

According to the invention of claim 7, in addition to the effect of the invention of claim 1, since the inertial mass is constituted by the partially enlarged portion of the inner panel, the number of parts is small and the assembling can be facilitated.

According to the invention of claim 8, in addition to the effect of the invention of claim 1, since the inertial mass is formed at the intersection of the inner panel, the number of parts is small and the assembling can be facilitated.

[Brief description of drawings]

FIG. 1 is a schematic perspective view of a hood according to a first embodiment of the present invention.

FIG. 2 is a schematic cross-sectional view taken along the line AA of FIG.

FIG. 3 shows a repulsive force waveform of the hood, (a) is a graph showing the relationship between the repulsive force of the hood and time, and (b) is a graph showing the repulsive force of the hood and the stroke of the hood.

FIG. 4 is a perspective view of a simple model of a hood.

FIG. 5 is a graph showing the relationship between distance L and time T.

6A and 6B are operation explanatory views, in which FIG. 6A is a schematic cross-sectional view of the hood before deformation and FIG.

FIG. 7 is a schematic bottom view of the hood according to the second embodiment.

FIG. 8 is a schematic cross-sectional view taken along the line BB of FIG.

FIG. 9 is an enlarged schematic sectional view of a main part.

FIG. 10 is an enlarged schematic cross-sectional view of a main part according to the third embodiment.

FIG. 11 is a schematic bottom view of the hood according to the fourth embodiment.

FIG. 12 is a schematic bottom view of a hood according to a fifth embodiment.

13 is a schematic sectional view taken along the line CC of FIG.

FIG. 14 is a schematic cross-sectional view of the main parts according to the sixth embodiment.

FIG. 15 is an enlarged perspective view of a main part according to the seventh embodiment.

FIG. 16 is an enlarged perspective view of a main part according to the eighth embodiment.

FIG. 17 is a schematic bottom view of the hood according to the ninth embodiment.

FIG. 18 is an enlarged perspective view of the main part.

FIG. 19 is a schematic bottom view of the hood according to the tenth embodiment.

20 is a schematic cross-sectional view taken along the line DD of FIG.

FIG. 21 is a schematic bottom view of the hood according to the eleventh embodiment.

22 is a schematic cross-sectional view taken along the line EE of FIG.

FIG. 23 is a schematic bottom view of the hood according to the twelfth embodiment.

FIG. 24 is a schematic cross-sectional view taken along the line GG of FIG.

FIG. 25 is a schematic bottom view of the hood according to the thirteenth embodiment.

FIG. 26 is a schematic cross-sectional view taken along the line I-I of FIG. 25.

FIG. 27 is a schematic sectional view of a main part according to the fourteenth embodiment.

FIG. 28 is a schematic bottom view of the hood according to the fifteenth embodiment.

FIG. 29 is a schematic perspective view of the same main part.

FIG. 30 is a schematic cross-sectional view of the main parts according to the seventeenth embodiment.

FIG. 31 is an enlarged perspective view of the main part.

FIG. 32 is a schematic bottom view of the hood according to the seventeenth embodiment.

FIG. 33 is a schematic cross-sectional view of the main part.

FIG. 34 is a schematic bottom view of the hood according to the eighteenth embodiment.

FIG. 35 is an enlarged perspective view of the main part.

36 is a schematic cross-sectional view taken along the line JJ of FIG.

FIG. 37 is an enlarged perspective view of the essential parts according to the nineteenth embodiment.

38 is a schematic sectional view taken along the line KK of FIG.

FIG. 39 is a schematic bottom view of the hood according to the twentieth embodiment.

FIG. 40 is a schematic bottom view of the hood according to the twenty-first embodiment.

FIG. 41 is a schematic bottom view of the hood according to the twenty-second embodiment.

FIG. 42 is a schematic bottom view of the hood according to the twenty-third embodiment.

FIG. 43 is a schematic bottom view of the hood according to the twenty-fourth embodiment.

FIG. 44 is an explanatory view of the arrangement of the reinforcing material.

FIG. 45 is a schematic bottom view of a hood according to a conventional example.

46 (a) and 46 (b) are diagrams for explaining the operation, (a) before deformation and (b).
Is a diagram after deformation.

[Explanation of symbols]

 1 Hood 3 Outer Panel 5 Inner Panel 11 Power Unit (Engine Room Parts) 27 Separate Member (Inertial Mass) 29 Separate Member (Inertial Mass) 31 Separate Member (Inertial Mass) 33 Separate Member (Inertial Mass) 35 Separate Member (Inertial Mass) ) 37 Separate member (inertial mass) 39 Separate member (inertial mass) 43 Vehicle functional part (inertial mass) 45 Hood bulge (inertial mass) 47 Mounting member (inertial mass) 49 Washer nozzle (inertial mass) 51 Vehicle functional part (inertial mass) Mass) 53 Vehicle functional parts (inertial mass) 55 Sub tank (inertial mass) 63 Reinforcement material (inertial mass) 65 Enlarged part (inertial mass) 67 Crossing part (inertial mass) 71 Crossing part (inertial mass) 75 Circular part (inertia) Mass) 77 Partially cutout circular part (inertial mass) 79 Circular part (inertial mass) 81 Circular part (inertial mass) 83 Enlarged part (inertia) The amount) 85 engine room components 87 inertial mass

Claims (8)

[Claims] 1. A reinforcement structure for a vehicle hood, comprising: an hood located on an upper side of an engine room, provided with an inertial mass around a portion having a small clearance between the hood and parts in the engine room; A circle having a radius L surrounding a portion having a small clearance is defined as T, an arbitrary time of a repulsive force waveform with respect to an impact input to the hood is defined as T, and a wave propagation speed when the hood is deformed by the impact is V
And the coefficient determined by the form of the hood is c, and the relation L = c · V · T is satisfied. 2. The vehicle hood reinforcement structure according to claim 1, wherein the hood includes an outer panel and an inner panel, and the inertial mass is a separate member partially fixed to the outer panel. A vehicle hood reinforcement structure characterized by the above. 3. The reinforcement structure for a vehicle hood according to claim 2, wherein the separate member has a shape that is substantially along the shape of the lower surface of the outer panel. 4. The vehicle hood reinforcement structure according to claim 1, wherein the hood includes an outer panel and an inner panel, and the inertial mass is a separate member fixed to the inner panel. The reinforcement structure of the vehicle hood. 5. The vehicle hood reinforcing structure according to claim 4, wherein the separate member is a reinforcing material made of glass wool, urethane or the like and a sound vibration countermeasure material. 6. The vehicle hood reinforcement structure according to claim 1, wherein the inertial mass is a vehicle functional component such as a washer reservoir tank, a radiator fluid reservoir tank, and a fuse box. Reinforced structure. 7. The vehicle hood reinforcement structure according to claim 1, wherein the hood includes an outer panel and an inner panel, and the inertial mass is an enlarged portion in which the inner panel is partially enlarged. A vehicle hood reinforcement structure characterized by the above. 8. The vehicle hood reinforcement structure according to claim 1, wherein the hood includes an inner panel and an outer panel, and the inertial mass is a crossing portion of the inner panel. Reinforcement structure of vehicle hood.