WO2011129286A1 - ウインドシールドガラス支持構造 - Google Patents
ウインドシールドガラス支持構造 Download PDFInfo
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- WO2011129286A1 WO2011129286A1 PCT/JP2011/058964 JP2011058964W WO2011129286A1 WO 2011129286 A1 WO2011129286 A1 WO 2011129286A1 JP 2011058964 W JP2011058964 W JP 2011058964W WO 2011129286 A1 WO2011129286 A1 WO 2011129286A1
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- WIPO (PCT)
- Prior art keywords
- windshield glass
- vibration
- vehicle
- resonance
- dynamic damper
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D25/00—Superstructure or monocoque structure sub-units; Parts or details thereof not otherwise provided for
- B62D25/08—Front or rear portions
- B62D25/081—Cowls
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
- F16F7/1028—Vibration-dampers; Shock-absorbers using inertia effect the inertia-producing means being a constituent part of the system which is to be damped
Definitions
- the present invention relates to a windshield glass support structure that is applied to an electric vehicle or the like and supports the lower end portion of the windshield glass.
- a windshield glass support structure for the purpose of effectively reducing the booming noise is known.
- a brace that forms a closed cross section is arranged at a position that becomes a resonance node in each resonance mode (see, for example, Patent Document 1).
- the primary resonance frequency is also affected. become. Further, when the primary resonance frequency is close to the frequency of the resonance phenomenon in the passenger compartment, low-frequency noise such as road noise and booming noise may occur.
- the resonance frequency in which the windshield glass is the mass and the support rigidity of the windshield glass is the spring constant varies when at least one of the mass and the spring constant changes.
- the support rigidity of the windshield glass, that is, the spring constant increases.
- the resonance frequency of another resonance mode for example, the first resonance mode
- low frequency noise refers to vehicle interior noise caused by primary resonance at the lower end of the windshield glass.
- Low-frequency noise includes, for example, road noise generated by contact between the tire and the road surface during driving (harmful noise such as gos and bumps) and noise called harsh noise generated by the inertia of the engine (harmful noise such as boons). ) Etc.
- the present invention has been made in view of such problems of the conventional technology. And the objective is to provide the windshield glass support structure which can ensure the quietness of a vehicle interior by suppressing generation
- a windshield glass support structure includes a windshield glass, a lower end support member that extends in the vehicle width direction of the vehicle and supports the lower end portion of the windshield glass, and both end portions of the windshield glass in the vehicle width direction.
- a dynamic damper provided at a portion of the lower end support member that becomes the antinode of resonance in the vehicle width direction.
- the dynamic damper is an additional vibration system having an additional spring and an additional mass with respect to the main vibration system having the glass support rigidity by the lower end support member as the main spring and the windshield glass as the main mass.
- the resonance frequency of the dynamic damper is set to a frequency band in which the additional mass swings in the opposite phase with respect to the vibration phase in which the lower end portion of the windshield glass swings in the vehicle longitudinal direction resonance mode caused by the vibration input.
- FIG. 1 is a perspective view showing an electric vehicle employing the windshield glass support structure of the first embodiment.
- FIG. 2 is a plan view (a) and a front view (b) showing a cowl top in the windshield glass support structure of the first embodiment.
- FIG. 3 is a cross-sectional view (a) and an enlarged view (b) showing a central portion in the vehicle width direction in the windshield glass support structure of the first embodiment.
- FIG. 4 is a cross-sectional view showing an end portion in the vehicle width direction in the windshield glass support structure of the first embodiment.
- FIG. 5 is a perspective view showing a cowl top stamping plate in a windshield glass support structure of a comparative example.
- FIG. 6 is a perspective view showing a stamping plate for a cowl top in the windshield glass support structure of the first embodiment.
- FIG. 7 is a diagram showing a vibration model in the windshield glass support structure of the comparative example.
- FIG. 8 is an explanatory diagram showing a low-frequency noise generation mechanism in a vehicle that employs a windshield glass support structure of a comparative example.
- FIG. 9 shows a frequency characteristic (a) of the vibration level at the center of the lower end of the windshield glass and a frequency characteristic (b) of the vibration level before and after the cowl top in the vehicle employing the windshield glass support structure of the comparative example.
- FIG. 10 is a diagram illustrating the frequency characteristics of the sound pressure level in the passenger compartment in a vehicle that employs the windshield glass support structure of the comparative example.
- FIG. 11 shows the vibration model (a) when the stamped portion mass is removed in the windshield glass support structure of Example 1, and the frequency characteristic (b) of the vibration level at the center of the lower end of the windshield glass.
- FIG. 12 shows the vibration model (a) when the stamped portion mass and the stamped portion spring are added in the windshield glass support structure of Example 1, and the frequency characteristics (b) of the vibration level at the center of the lower end of the windshield glass. ).
- FIG. 13 is a diagram showing frequency characteristics of vibration levels before and after the cowl top when a stamped portion mass and a stamped portion spring are added in the windshield glass support structure of the first embodiment.
- FIG. 11 shows the vibration model (a) when the stamped portion mass is removed in the windshield glass support structure of Example 1, and the frequency characteristic (b) of the vibration level at the center of the lower end of the windshield glass.
- FIG. 12 shows the vibration
- FIG. 14 is a diagram for explaining the action of suppressing the vibration level at the center of the lower end of the windshield glass by the dynamic damper in the windshield glass support structure of the first embodiment.
- FIG. 15 is a diagram illustrating frequency characteristics of the sound pressure level in the vehicle interior in the electric vehicle employing the windshield glass support structure of the first embodiment.
- FIG. 16 is a schematic plan view showing an electric vehicle employing the windshield glass support structure of the second embodiment.
- FIG. 17 is a schematic plan view showing an electric white train that employs the windshield glass support structure of the third embodiment.
- FIG. 18 is a perspective view showing an application example 1 (a) and an application example 2 (b) of a windshield glass support structure employing a dynamic damper using a stamped plate.
- FIG. 1 is a perspective view showing an electric vehicle (an example of an electric vehicle) employing the windshield glass support structure of the first embodiment.
- 2 to 6 are views showing the windshield glass support structure and each component of the first embodiment.
- the electric vehicle employing the windshield glass support structure according to the first embodiment includes a vehicle body S, a windshield glass 1, a roof header 2, and a cowl top 3 (lower end support member). Yes. Furthermore, the electric vehicle includes a dash upper panel 4, a dash lower panel 5, a cowl cover 6, and a dynamic damper 7.
- the vehicle body S has a box-shaped monocoque body structure without a frame and made by bonding a large number of body panels by spot welding or the like.
- the vehicle body S includes a pair of left and right side members 9, a front pillar 10, a center pillar 11, and the like.
- the windshield glass 1 is a windshield of an automobile that blocks wind as shown in FIG.
- the upper end portion of the windshield glass 1 is supported by a roof header 2 which is an upper end support member extending in the vehicle width direction.
- the lower end part of the windshield glass 1 is supported by the cowl top 3 which is a lower end support member extended in a vehicle width direction.
- the left and right end portions of the windshield glass 1 are supported by the step portions of the pair of left and right front pillars 10.
- the cowl top 3 is a member that has a curved shape with a center portion protruding toward the vehicle front side (in the direction of the arrow FR) and both ends toward the vehicle rear side.
- the cowl top 3 is fixed by welding along the upper end portion of the dash upper panel 4 (see FIGS. 3 and 4).
- the cowl top 3 has a glass support surface 3 a that supports the inner surface of the lower end portion of the windshield glass 1. Both end portions 3 b and 3 c of the cowl top 3 are fixed to lower positions of the front pillar 10.
- the adhesive 12 is interposed between the glass support surface 3a of the cowl top 3 and the inner surface of the lower end portion of the windshield glass 1, whereby the lower end portion of the windshield glass 1 is fixed to the glass support surface 3a. (See FIG. 3B).
- the dash upper panel 4 and the dash lower panel 5 are connected vertically by welding to constitute a dash panel.
- the internal space of the vehicle body S is defined into a motor room M on the front side of the vehicle and a vehicle room R on the rear side of the vehicle.
- an electric motor 13 as a driving power source is mounted in the motor room M.
- an unillustrated seat on which a passenger is seated is mounted in the passenger compartment R.
- the cowl cover 6 is a lid member of the air box 14 made of a flexible synthetic resin material or the like.
- the air box 14 includes a cowl top 3 that supports the inner surface of the lower end portion of the windshield glass 1, a dash upper panel 4, and a cowl extension panel 15. And let the cross-sectional shape of the air box 14 be the open cross section in which the clearance gap t continues in a vehicle width direction. That is, a gap t is provided between the end of the cowl top 3 and the end of the cowl extension panel 15 on the upper side of the air box 14. As a result, the air box 14 is set to have a low box rigidity for pedestrian protection measures.
- the cowl cover 6 is a member that closes the upper gap t, and is attached in such a manner as to sandwich the lower end portion of the windshield glass 1 as shown in FIGS. 3 and 4.
- the cowl cover 6 also has a function of sealing a bonnet (not shown) provided at the top of the motor room M so as to be opened and closed.
- the dynamic damper 7 is provided as an additional vibration system for the center position of the cowl top 3 in the vehicle width direction with respect to the main vibration system having the glass support rigidity of the cowl top 3 as a main spring and the windshield glass 1 as a main mass. It is done.
- the dynamic damper 7 has an additional spring and an additional mass.
- the dynamic damper 7 sets the resonance frequency fd so as to suppress the primary resonance mode that vibrates in the vehicle front-rear direction among the resonance at the lower end of the windshield glass caused by the vibration input.
- the resonance frequency fd of the dynamic damper 7 uses the additional spring k and the additional mass m as a frequency adjustment allowance. For example, when the additional spring k is determined, when the additional mass m is increased, the resonance frequency fd shifts to the low frequency side, and when the additional mass m is decreased, the resonance frequency fd shifts to the high frequency side.
- the dynamic damper 7 uses a stamping plate for stamping a vehicle chassis number provided on the cowl top 3.
- the stamping plate 72A extends from the central curved portion of the cowl top 3A as it is below the vehicle, and the stamping plate is attached to the cowl top with a high mounting rigidity in the vehicle front-rear direction. It is integrated with.
- a linear portion 71 is provided by linearizing the central curved portion of the cowl top 3 along the vehicle width direction. The additional spring was made easy to be elastically deformed by lowering the mounting rigidity.
- a stamping plate 72 (flat plate portion) continuously extending from the linear portion 71 as an additional spring is provided below the stamping plate 72.
- the stamping plate 72 is slightly longer below the stamping plate than the stamping plate of the comparative example. The additional mass was extended to increase the mass for the extension.
- the stamping plate 72 has a stamping surface 73 for stamping a vehicle chassis number in order to leave the original stamping function.
- the operation will be described.
- the “problem of the windshield glass support structure of the comparative example” will be described.
- the action of the windshield glass support structure of the first embodiment will be described by dividing it into “a vibration damping mechanism of a dynamic damper”, “a resonance frequency setting action of a dynamic damper”, and “a low frequency noise suppression action of a vehicle interior”. .
- HIC Head Injury Criteria
- the cross-sectional shape of the air box that supports the lower end of the windshield glass is a closed cross-section
- the rigidity of the air box increases and it may be difficult to achieve the HIC target. is there. Therefore, the cross-sectional shape of the air box tends to be an open cross section that is lower than the rigidity of the closed cross section, and the HIC target tends to be secured.
- a windshield glass support structure of a comparative example a structure in which the lower end portion of the windshield glass is supported by an air box having an open cross-sectional shape and no dynamic damper is set is assumed.
- the cross-sectional shape of the air box is an open cross section, the numerical target of HIC can be achieved.
- the lower the numerical target of the HIC aiming at high pedestrian protection performance, the lower the support rigidity of the lower end of the windshield glass.
- the windshield glass support structure of the comparative example is based on a vibration model in which the windshield glass is a mass (W / S mass) and the front and rear support rigidity of the cowl top is a spring (CWL TOP spring). Can be represented.
- the square of the windshield glass includes the square of the cowl top and the square of the stamped plate (the stamped portion square).
- the lower end of the windshield glass is primarily resonated.
- this primary resonance is performed in the vehicle longitudinal direction by a primary vibration mode in which both ends of the windshield glass in the vehicle width direction are nodes of resonance and the central portion of the windshield glass in the vehicle width direction is antinode of resonance. Vibrates with a large amplitude. And the low frequency noise will generate
- the primary resonance frequency fw at the lower end portion of the windshield glass is the vibration level peak value as in the frequency characteristic at the lower end center portion of the windshield glass shown in FIG. Appears at about 60 Hz.
- the vibration level before and after the cowl top gradually increases as the frequency increases, and becomes a high vibration level (amplitude) in the primary resonance region around 60 Hz.
- a peak characteristic in which the sound pressure level increases in the primary resonance region B around 60 Hz appears. And it turns out that the peak characteristic of this sound pressure level becomes a generation factor of low frequency noise.
- the lower end of the windshield glass is caused by the decrease in the support rigidity when there is an excitation input in the low frequency range. Primary resonance occurs. As a result, low-frequency noise such as road noise and booming noise is generated.
- the inventor analyzed the generation mechanism of the low frequency noise caused by the excitation input.
- low-frequency noise is caused by the input system of the vibration input being tires and wheels
- the transmission system of the vibration input is the suspension and the vehicle body
- the main factor causing low-frequency noise in the passenger compartment is the windshield glass. It was clarified that this was due to the mechanism.
- the vehicle travels by driving the electric motor 13 with a quiet sound.
- the quietness in the passenger compartment is maintained to such an extent that conversation can be enjoyed without stress as compared with a vehicle traveling by driving the engine.
- the interior of the passenger compartment is kept quiet in this way and the atmosphere in the cabin is low-frequency noise, the low-frequency noise becomes more annoying to the passengers than the engine vehicle, causing discomfort to the passengers. I will give it.
- Example 1 the dynamic damper 7 was set while supporting the lower end portion of the windshield glass 1 with the air box 14 having an open cross-sectional shape in order to achieve both pedestrian protection performance and low-frequency noise suppression.
- the vibration control mechanism of the dynamic damper will be described.
- the “dynamic damper” is an additional vibration system composed of an additional spring and an additional mass, and is called a dynamic vibration absorber having a specific resonance frequency.
- the main vibration system subject to vibration suppression is set to X
- the additional vibration system corresponding to the dynamic damper is set to Y
- the resonance frequency of the additional vibration system Y matches the resonance frequency of the main vibration system X.
- the resonance frequency (mountain) of the main vibration system X which is one, is divided into two resonance frequencies (mountains) due to an increase in the degree of freedom of vibration.
- These two resonance frequencies (mountains) appear in a frequency region before and after the resonance frequency (valley) tuned by the additional vibration system Y and have a vibration level lower than one resonance frequency (mountain).
- This dynamic damper is characterized in that it can obtain a damping action by adding a small mass without requiring a major design change of the main vibration system.
- the dynamic damper has a damping action of suppressing the vibration level when the main vibration system attempts to resonate.
- the damping action of the dynamic damper is equivalent to the action that apparently increases the support rigidity of the main vibration system and suppresses the vibration level only in the resonance frequency range of the main vibration system. It can be said.
- the resonance frequency fd is set so as to suppress the vibration mode in the vehicle front-rear direction due to the primary resonance among the resonance of the lower end portion of the windshield glass caused by the vibration input.
- the setting operation of the resonance frequency fd in the dynamic damper 7 of the first embodiment will be described.
- the main vibration system X in which the dynamic damper 7 of the first embodiment is installed has a windshield glass 1 as a mass (W / S mass), and the front and rear support rigidity of the cowl top 3 is a spring ( The vibration model is CWL (TOP spring). At this time, the square of the cowl top 3 is included in the square of the windshield glass.
- the main vibration system X is divided into two resonance frequencies fs1 and fs2, and a region between the two resonance frequencies fs1 and fs2 is a reverse phase region in which the vibration damping action by the dynamic damper 7 is exhibited.
- this reverse phase region as shown in the frequency characteristics of the cowl top longitudinal vibration level in FIG. 13, the longitudinal vibration of the cowl top 3 becomes the maximum vibration level at the resonance frequency fs1 (about 46 Hz). Then, the longitudinal vibration level of the cowl top 3 decreases as it goes toward the resonance frequency fs2 (about 63 Hz).
- the resonance frequency fd of the dynamic damper 7 is not necessarily matched with the primary resonance frequency fw1 at the lower end of the windshield glass.
- the resonance frequency of the main vibration system X is divided into two, and the two resonance frequencies fw1, fd are provided in the opposite phase region of fs1 to fs2 that exhibits the damping function as the dynamic damper 7. Should be set to include.
- the resonance frequency fd of the dynamic damper 7 may be set slightly higher than the primary resonance frequency fw1, or may be higher than the primary resonance frequency fw1. A slightly lower setting is also possible.
- Example 1 the portion corresponding to the additional mass and the additional spring of the dynamic damper 7 was formed by an integral structure of the cowl top 3 using the stamping plate 72. That is, the additional mass is tuned with the size (mass) of the stamping plate 72, and the additional spring is tuned with the ridgeline shape (straightening) of the cowl top 3.
- the resonance frequency fd of the dynamic damper 7 By setting the resonance frequency fd of the dynamic damper 7 by this tuning operation, the primary resonance frequency fw1 at the lower end of the windshield glass is divided into two resonance frequencies fs1 and fs2, and the vibration level of the primary resonance frequency fw is suppressed. .
- the dynamic damper 7 is in the opposite phase region.
- the additional mass by the stamping plate 72 starts to swing in the opposite phase with respect to the vibration phase in which the windshield glass 1 swings.
- the primary resonance vibration mode of the windshield glass 1 is a vibration mode in which both ends of the windshield glass 1 in the vehicle width direction are used as resonance nodes and the center portion in the vehicle width direction is used as a resonance antinode (FIG. 8). reference).
- the dynamic damper 7 is provided at the center position in the vehicle width direction of the cowl top 3, that is, at a position corresponding to the antinode of the primary resonance mode. For this reason, the vibration level (amplitude) of the lower end portion of the windshield glass can be effectively suppressed as compared with the case where the dynamic damper 7 is provided at a portion other than the central portion of the cowl top 3 in the vehicle width direction.
- the dynamic damper 7 provided at the center of the cowl top 3 in the vehicle width direction effectively suppresses the vibration level of the primary mode among the resonance of the lower end of the windshield glass with respect to the excitation input. Due to the vibration damping action of the dynamic damper 7, the vibration level (amplitude) of the lower end portion of the windshield glass can be effectively reduced.
- the height of the sound pressure level is suppressed as shown in the primary resonance region B ′ around 60 Hz, and the sound pressure level is higher than the sound pressure level of the comparative example.
- the width is reduced by ⁇ S (dB). With this sound pressure width ⁇ S (dB), low-frequency noise such as road noise and booming noise can be reduced to such an extent that it does not disturb the passenger.
- the frequency characteristic of FIG. 15 is an example of measuring the sound pressure level at the position of the inner ear of the occupant seated in the front seat when the vehicle attachment points of the front suspension and the rear suspension are unit-excited. That is, it is data obtained by accurately simulating low-frequency noise felt by passengers in the passenger compartment due to actual excitation input.
- both end portions in the vehicle width direction of the windshield glass 1 are resonated.
- the dynamic damper 7 is provided at a portion of the lower end support member that becomes an antinode of resonance in the vehicle width direction.
- the dynamic damper 7 is an additional vibration system having an additional spring and an additional mass with respect to the main vibration system having the glass support rigidity by the lower end support member as the main spring and the windshield glass 1 as the main mass.
- the resonance frequency fd of the dynamic damper 7 is set to a frequency band in which the additional mass is swung in an opposite phase to the vibration phase in which the lower end portion of the windshield glass is swung in the vehicle longitudinal direction resonance mode generated by the vibration input.
- the dynamic damper 7 is provided at the center of the lower end support member in the vehicle width direction. Then, the resonance frequency fd of the dynamic damper 7 is set to a frequency band in which the additional mass swings in the opposite phase to the vibration phase in which the lower end of the windshield glass swings in the primary resonance mode among the vehicle longitudinal resonance modes generated by the vibration input. Set.
- the lower end support member is a member that has a curved shape in which the center portion protrudes toward the vehicle front side and both ends toward the vehicle rear side.
- the dynamic damper 7 is a flat plate portion (striking portion) continuously extending from the straight portion 71 downward to the vehicle, with the straight portion 71 obtained by straightening the central curved portion of the lower end support member along the vehicle width direction as an additional spring.
- the engraved plate 72) is an additional mass.
- the vehicle front-rear direction resonance mode at the lower end portion of the windshield glass is suppressed by the dynamic damper 7 configured integrally with the lower end support member without increasing the number of parts. be able to.
- the flat plate portion is a stamping plate 72 having a stamping surface 73 for stamping a vehicle chassis number.
- the dynamic damper 7 can be easily provided while minimizing cost increase and design change.
- the lower end support member is a cowl top 3 having a glass support surface 3 a that is fixed along the upper end portion of the dash upper panel 4 and supports the lower end portion of the windshield glass 1.
- the cross-sectional shape of the air box 14 having the cowl top 3 and the dash upper panel 4 is an open cross-sectional shape in which the gap t is continuous in the vehicle width direction.
- the pedestrian protection performance by suppressing the lower end support rigidity of the windshield glass 1 and the low frequency noise by suppressing the vibration at the lower end of the windshield glass. It is possible to achieve coexistence with suppression.
- Example 2 is an example in which low-frequency noise generated due to vibration in the third-order resonance mode among the vehicle longitudinal resonance modes at the lower end of the windshield glass is suppressed.
- FIG. 16 is a schematic plan view showing an electric vehicle (an example of an electric vehicle) employing the windshield glass support structure of the second embodiment.
- a dynamic damper 7 ' is provided.
- the dynamic dampers 7 ′ are provided at a total of three locations, that is, one location in the center of the cowl top 3 in the vehicle width direction and 2 locations that are 1/6 from both ends.
- each dynamic damper 7 ' has a glass support rigidity by the cowl top 3 as a main spring, and an additional mass as an additional vibration system with respect to the main vibration system as the main mass of the windshield glass 1. Has a spring.
- Example 1 an example as a countermeasure for the primary resonance mode is shown. This is realized by setting a dynamic damper 7 at the center of the cowl top 3 in the vehicle.
- dynamic dampers 7 ′ are provided at three positions that are antinodes of resonance in the third resonance mode of the cowl top 3.
- the damping action for suppressing the vibration is shown as in the first embodiment, and the vibration level of the tertiary resonance is lowered. Therefore, it is possible to suppress low-frequency noise generated due to vibration caused by the tertiary resonance mode.
- Example 3 is an example in which low-frequency noise generated due to vibration caused by a left-right asymmetric secondary resonance mode among the vehicle longitudinal resonance modes at the lower end of the windshield glass is suppressed.
- FIG. 17 is a schematic plan view showing an electric vehicle (an example of an electric vehicle) adopting the windshield glass support structure of the third embodiment.
- the antinodes of resonance in the vehicle width direction of the cowl top 3 are in two places. appear. That is, as shown in FIG. 17, the antinodes of the resonance appear in two places with a large amplitude and a small amplitude. Therefore, a dynamic damper 7 ′′ is provided at the position of the antinode of the resonance having a large amplitude. That is, the dynamic damper 7 ′′ is provided at one place offset from the center portion of the cowl top 3 in the vehicle width direction.
- the dynamic damper 7 ′′ has a glass support rigidity by the cowl top 3 as a main spring and an additional mass as an additional vibration system in addition to the main vibration system as the main mass of the windshield glass 1. Has a spring.
- the windshield glass support structure of the present invention has been described based on Examples 1 to 3.
- the specific configuration is not limited to these examples.
- Example 1 shows an example in which low-frequency noise generated due to vibration in the primary resonance mode among the vehicle longitudinal direction resonance modes at the lower end of the windshield glass is suppressed.
- Example 2 the example which suppresses the low frequency noise which generate
- Example 3 the example which suppresses the low frequency noise generated by the vibration by the asymmetrical secondary resonance mode was shown.
- the order of the vehicle longitudinal resonance mode is not limited to the first to third embodiments.
- a dynamic damper can be used as a countermeasure against a plurality of resonance modes having different orders. Can also be provided.
- a straight plate 71 obtained by straightening the central curved portion of the cowl top 3 along the vehicle width direction is used as an additional spring, and a stamping plate 72 continuously extending downward from the straight portion 71 is provided. Additional squares were used. However, a separate dynamic damper may be added to the cowl top without using the existing stamping plate 72.
- the stamping plate 72 was used as an additional mass, and the lower end of the plate was slightly extended.
- the extension of the lower end of the cowl top and the mass adjustment (mass / position) can provide a dynamic damper function and control the resonance of the windshield glass.
- a stamping plate 72 'extending downward from the first embodiment may be used.
- a mass body 74 may be provided at the lowermost portion of the stamping plate 72.
- Example 1 the straight portion 71 obtained by straightening the curved portion is used as the additional spring.
- a notch structure, a slit structure, a thinned structure, or the like known as a fragile structure may be used as an additional spring.
- two or more of these fragile structures and the straight portion 71 may be combined to form an additional spring.
- the cross-sectional shape of the air box 14 having the cowl top 3 and the dash upper panel 4 is an open cross-sectional shape in which the gap t is continuous in the vehicle width direction.
- the cross-sectional shape of the air box may be a closed cross-sectional shape, and the purpose may be focused on suppressing the vibration caused by the resonance mode (eg, primary resonance mode, secondary resonance mode, tertiary resonance mode, etc.) of the lower end of the windshield glass. .
- Examples 1 to 3 show examples in which the windshield glass support structure is applied to an electric vehicle. However, it can be applied to electric vehicles such as hybrid vehicles and fuel cell vehicles, as well as to engine vehicles. In addition, when applied to an electric vehicle in which the quietness in the vehicle interior is maintained, it is possible to effectively suppress annoying low-frequency noise that is more worrisome for the occupant than the engine vehicle.
- the vibration input from the tire reaches the windshield glass via the suspension and the vehicle body
- the lower end of the windshield glass is vibrated in the vehicle longitudinal resonance mode.
- the excitation input becomes the resonance frequency band of the dynamic damper
- the additional mass starts to swing in the opposite phase to the vibration phase in which the lower end portion of the windshield glass swings.
- the vibration level (amplitude) in the vehicle front-rear direction at the lower end of the windshield glass is kept small.
- the vehicle longitudinal direction resonance mode at the lower end of the windshield glass is a vibration mode in which both ends of the windshield glass in the vehicle width direction are nodes of resonance.
- the dynamic damper is provided at a portion that becomes an antinode of resonance in the vehicle width direction of the lower end support member. Therefore, the vibration level (amplitude) of the lower end portion of the windshield glass is effectively reduced.
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Abstract
Description
fd=1/(2π)√(k/m)…(1)
歩行者の頭部がウインドシールドガラスの下端部に衝突したと仮定したとき、頭部への衝撃を緩和する性能を「歩行者保護性能」という。この歩行者保護性能は、ウインドシールドガラスの下端部が頭部へ与える衝撃の強さを表す指標値であるHIC(頭部損傷基準:Head Injury Criteria)を用いて表現する。
上記低周波騒音の課題に対し、解決手法の1つとして、カウルトップの支持剛性を高め、ウインドシールドガラス下端部の一次共振周波数を高周波数側に移動させて低周波騒音を抑制する手法がある。しかしながら、この解決手法では、低周波騒音の抑制は達成できても、カウルトップの支持剛性が高まることで、歩行者保護性能を悪化させてしまう。
実施例1のダイナミックダンパー7は、加振入力により生じるウインドシールドガラス下端部の共振のうち、一次共振による車両前後方向の振動モードを抑制するように共振周波数fdを設定したものである。以下、実施例1のダイナミックダンパー7における共振周波数fdの設定作用を説明する。
凹凸路等の走行中、入力系であるタイヤからの加振が、伝達系であるサスペンションと車体を経由してウインドシールドガラス1に到達することで、一次共振によりウインドシールドガラス1を車両前後方向に振動させようとする。このとき、加振入力がダイナミックダンパー7の共振周波数帯域になると、ウインドシールドガラス1が振れる振動位相に対し、打刻プレート72による付加マスが逆位相に振れ出す。その結果、ウインドシールドガラス下端の一次共振による振動レベル(振幅)を小さく抑える。
3 カウルトップ(下端支持部材)
4 ダッシュアッパーパネル
5 ダッシュロワパネル
7 ダイナミックダンパー
14 エアーボックス
71 直線部
72 打刻プレート
Claims (5)
- ウインドシールドガラスと、
車両の車幅方向に延び、前記ウインドシールドガラスの下端部を支持する下端支持部材と、
前記ウインドシールドガラスの車幅方向の両端部を共振の節としたとき、前記下端支持部材の車幅方向における共振の腹となる部位に設けられたダイナミックダンパーと、
を備え、
前記下端支持部材によるガラス支持剛性を主バネとし前記ウインドシールドガラスを主マスとする主振動系に対し、付加バネと付加マスを有する付加振動系とし、
前記ダイナミックダンパーの共振周波数を、加振入力により生じる車両前後方向の共振モードでウインドシールドガラスの下端部が振れる振動位相に対し、前記付加マスが逆位相に振れる周波数帯域に設定したことを特徴とするウインドシールドガラス支持構造。 - 前記ダイナミックダンパーは、前記下端支持部材の車幅方向の中央部に設け、
前記ダイナミックダンパーの共振周波数を、加振入力により生じる車両前後方向の共振モードのうち一次共振モードでウインドシールドガラスの下端部が振れる振動位相に対し前記付加マスが逆位相に振れる周波数帯城に設定したことを特徴とする請求項1に記載のウインドシールドガラス支持構造。 - 前記下端支持部材は、中央部が車両前方側に突出し、両端部が車両後方側に向かう湾曲形状をなす部材であり、
前記ダイナミックダンパーは、前記下端支持部材の中央湾曲部を車幅方向に沿って直線化した直線部を前記付加バネとし、前記直線部から連続して車両下方に延在させた平板部を前記付加マスとしたことを特徴とする請求項2に記載のウインドシールドガラス支持構造。 - 前記平板部は、車両のシャシ番号を打刻する打刻面を有する打刻プレートであることを特徴とする請求項3に記載のウインドシールドガラス支持構造。
- 前記下端支持部材は、ダッシュアッパ一パネルの上端部に沿って固定され、前記ウインドシールドガラスの下端部を支持するガラス支持面を有するカウルトップであり、
前記カウルトップと前記ダッシュアッパーパネルを有して構成したエアーボックスの断面形状を、上面に設けられた隙間が車幅方向に連続する開断面形状としたことを特徴とする請求項1乃至4のいずれか一項に記載のウインドシールドガラス支持構造。
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