WO2021038988A1 - Spring member and suspension device - Google Patents

Spring member and suspension device Download PDF

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Publication number
WO2021038988A1
WO2021038988A1 PCT/JP2020/020631 JP2020020631W WO2021038988A1 WO 2021038988 A1 WO2021038988 A1 WO 2021038988A1 JP 2020020631 W JP2020020631 W JP 2020020631W WO 2021038988 A1 WO2021038988 A1 WO 2021038988A1
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WO
WIPO (PCT)
Prior art keywords
spring member
bent
bent portion
spring
load
Prior art date
Application number
PCT/JP2020/020631
Other languages
French (fr)
Japanese (ja)
Inventor
潤 冨永
秀雅 伊藤
信次 飯野
洋介 川井
剛 木下
Original Assignee
日本発條株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日本発條株式会社 filed Critical 日本発條株式会社
Publication of WO2021038988A1 publication Critical patent/WO2021038988A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
    • B60G11/02—Resilient suspensions characterised by arrangement, location or kind of springs having leaf springs only
    • B60G11/08—Resilient suspensions characterised by arrangement, location or kind of springs having leaf springs only arranged substantially transverse to the longitudinal axis of the vehicle
    • 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
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/18—Leaf springs
    • 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
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/18—Leaf springs
    • F16F1/22—Leaf springs with means for modifying the spring characteristic
    • 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
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/18—Leaf springs
    • F16F1/26—Attachments or mountings
    • 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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/366—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers made of fibre-reinforced plastics, i.e. characterised by their special construction from such materials
    • F16F1/368—Leaf springs

Definitions

  • the present invention relates to a spring member and a suspension device.
  • the leaf spring type suspension device is configured by using a strip-shaped spring member (see, for example, Patent Document 1).
  • the spring member is interposed between the arm that supports the wheels and the frame that supports the vehicle body. Specifically, the spring member is held by a right arm that supports the right wheel and a left arm that supports the left wheel.
  • Patent Document 1 in addition to this spring member, it is configured in combination with a method using a coil spring.
  • the spring constant of the spring member in order to improve the riding comfort in a vehicle, it is preferable to lower the spring constant of the spring member so that it can easily follow the vibration.
  • the weight of a vehicle member such as a vehicle body is added to the spring member.
  • the spring flexure in the vertical direction of the vehicle becomes large, and there is a problem that the spring member itself becomes large. Therefore, in order to reduce the deflection of the spring member in the vertical direction of the vehicle due to the deformation of the spring member with respect to the own weight, the spring constant of the spring member must be high within the range in which the own weight of the vehicle member is applied. desired.
  • the spring member of the suspension device has a non-linear spring characteristic in which the deflection (spring constant) changes depending on the load.
  • the suspension device shown in Patent Document 1 since the spring member is held only by the arm, it is difficult to make the spring characteristics non-linear.
  • the present invention has been made in view of the above, and is a spring member and a suspension device capable of achieving both a good ride quality in a vehicle and a reduction in bending of the spring member until the weight of the vehicle member is applied.
  • the purpose is to provide.
  • the spring member according to the present invention rises with respect to a band-shaped first portion in which the relationship between the load and the deflection shows linear spring characteristics and the first portion. It is characterized by having a second portion extending from the surface and exhibiting a non-linear spring characteristic.
  • the spring member according to the present invention has the first and second bent portions that rise and extend from the first portion, respectively, and the first bent portion is After extending from one end to the other end of the first portion, the second bent portion stands up and extends with respect to the first portion, and then bends in a mode opposite to the bending mode of the rising portion. Is characterized in that it extends from the other end of the first portion toward one end, then stands up and extends with respect to the first portion, and then bends in a mode opposite to the bending mode of rising. To do.
  • the second portion is provided on the side opposite to the first portion side with respect to the first and second bent portions, respectively. Further, it has a first connecting portion for connecting the first bent portion and the third bent portion, and a second connecting portion for connecting the second bent portion and the fourth bent portion.
  • the third bent portion rises from the connecting portion with the first connecting portion and extends, and then bends in a mode opposite to the rising bending mode
  • the fourth bent portion is the second connecting portion. It is characterized in that it rises from the connecting portion with and extends, and then bends in a mode opposite to the bending mode of rising.
  • the spring member according to the present invention is characterized in that, in the above invention, the second portion further includes a third connecting portion that connects the third bent portion and the fourth bent portion.
  • the first connecting portion has the minimum distance between the end portion on the first bending portion side and the first portion in the natural state.
  • the minimum distance between the bent portion and the first portion is equal to or less than the minimum distance between the end portion on the side of the second bent portion and the first portion in the natural state of the second connecting portion. It is characterized in that it is not more than the minimum distance between the fourth bent portion and the first portion.
  • the spring member according to the present invention is characterized in that, in the above invention, the spring member is made of fiber reinforced plastic.
  • the spring member according to the present invention is characterized in that, in the above invention, the spring member is made of a material in which the first portion and the second portion are different from each other.
  • the spring member according to the present invention is characterized in that, in the above invention, the first part of the spring member is made of fiber reinforced plastic and the second part is made of spring steel.
  • one end of the first arm and the second arm is displaced in conjunction with the movement of the first arm, and the other end is displaced in conjunction with the movement of the second arm.
  • a spring member having a band-shaped first portion in which the relationship between load and deflection shows linear spring characteristics and a second portion that rises and extends with respect to the first portion, and exhibits non-linear spring characteristics.
  • a supported member supported by the second portion of the spring member.
  • FIG. 1 is a perspective view schematically showing a configuration of a suspension device according to an embodiment of the present invention.
  • FIG. 2 is a view in which a part of the arm of the suspension device shown in FIG. 1 is removed.
  • FIG. 3 is a plan view of the suspension device shown in FIG. 2 as viewed from the direction of arrow A.
  • FIG. 4 is a perspective view schematically showing the configuration of a main part of the suspension device according to the embodiment of the present invention.
  • FIG. 5 is a diagram showing the relationship between the deflection of the spring member and the load in the suspension device according to the embodiment of the present invention.
  • FIG. 6 is a diagram showing the relationship between the deflection and the load in the first portion of the spring member of the suspension device according to the embodiment of the present invention.
  • FIG. 7 is a diagram showing a state of the suspension system in the point P 1 shown in FIG.
  • FIG. 8 is an enlarged view of the deformed portion of the spring member shown in FIG. 7.
  • FIG. 9 is a diagram showing a displacement amount of the left arm with respect to a displacement amount of the right arm due to a load applied to the right arm of the suspension device according to the embodiment of the present invention.
  • FIG. 10 is a perspective view schematically showing the configuration of a main part of the suspension device according to the first modification of the embodiment of the present invention.
  • FIG. 11 is a perspective view schematically showing the configuration of a main part of the suspension device according to the second modification of the embodiment of the present invention.
  • FIG. 12 is a perspective view schematically showing the configuration of a main part of the suspension device according to the third modification of the embodiment of the present invention.
  • FIG. 1 is a perspective view schematically showing a configuration of a suspension device according to an embodiment of the present invention.
  • FIG. 2 is a view in which a part (extending portions 11b, 12b) of the arm of the suspension device shown in FIG. 1 is removed.
  • FIG. 3 is a plan view of the suspension device shown in FIG. 2 as viewed from the direction of arrow A.
  • FIG. 4 is a perspective view schematically showing the configuration of a main part of the suspension device according to the embodiment of the present invention.
  • the suspension device 1 is provided in, for example, a vehicle and is interposed between the right wheel, the left wheel, and the vehicle body (body) to suppress the vibration transmitted from the wheels from being transmitted to the vehicle body.
  • the suspension device 1 includes a right arm 11 that supports the right wheel, a left arm 12 that supports the left wheel, a frame 13 that supports the vehicle body, and a spring member 14 that elastically deforms in response to vibration from the wheels. To be equipped.
  • the suspension device 1 is attached to the vehicle body via the frame 13 and absorbs vibration transmitted from the wheels according to the unevenness of the road surface.
  • the wheels are supported by the arm via, for example, a knuckle or a disc rotor.
  • the right arm 11 has a first support portion 11a that supports the right wheel and one end of the spring member 14, an extension portion 11b extending from the first support portion 11a, and a first support portion of the extension portion 11b. It has a second support portion 11c provided at an end portion opposite to the 11a side and supporting a part of the spring member 14.
  • the right arm 11 is supported by a shaft portion 15 extending in a direction orthogonal to the extending direction of the extending portion 11b, and is rotatable around the central axis of the shaft portion 15.
  • the left arm 12 has a first support portion 12a that supports the left wheel and supports the other end of the spring member 14, an extension portion 12b that extends from the first support portion 12a, and a first support of the extension portion 12b. It has a second support portion 12c provided at an end portion opposite to the portion 12a side and supporting a part of the spring member 14.
  • the left arm 12 is supported by a shaft portion 16 extending in a direction orthogonal to the extending direction of the extending portion 12b, and is rotatable around the central axis of the shaft portion 16.
  • the frame 13 supports the vehicle body.
  • the frame 13 is supported by the spring member 14 and is interposed between the vehicle body and the right wheel, the right arm 11, the left wheel, the left arm 12, and the spring member 14.
  • the frame 13 corresponds to a supported member.
  • the frame 13 may be integrated with the vehicle body. When the frame 13 is integrated with the vehicle body, the vehicle body is connected to the spring member 14 (supported member).
  • the spring member 14 has a first portion 14a extending in a strip shape, and a second portion 14b in which the strip-shaped member is bent and rises and extends with respect to the first portion 14a.
  • One end of the first portion 14a is supported by the right arm 11 and the other end is supported by the left arm 12. Further, the first portion 14a is supported by the right arm 11 and the left arm 12 (second support portions 11c and 12c) at the central portion in the longitudinal direction, respectively.
  • the second portion 14b stands up in a convex shape with respect to the first portion 14a.
  • the second portion 14b is the first with respect to the first bent portion 141 and the second bent portion 142, and the first bent portion 141 and the second bent portion 142, which rise and extend from the first portion 14a, respectively.
  • the third bent portion 143 and the fourth bent portion 144 provided on the side opposite to the portion 14a side (frame 13 side), and the first connecting portion 145 connecting the first bent portion 141 and the third bent portion 143, respectively. It has a second connecting portion 146 that connects the second bent portion 142 and the fourth bent portion 144, and a third connecting portion 147 that connects the third bent portion 143 and the fourth bent portion 144 (FIGS. 3, 4). reference).
  • the first bent portion 141 extends from one end to the other end (for example, from left to right in FIG. 3) of the first portion 14a, then rises and extends with respect to the first portion 14a, and then rises. It bends in the opposite manner to the bending mode. Specifically, the first bent portion 141 is bent in a manner opposite to the bent mode of the first standing portion 141a rising and extending from the first portion 14a and the first standing portion 141a, and the first connecting portion 145. It has a first connecting portion 141b connected to one end of the above, and a first straight portion 141c extending linearly and connecting the first standing portion 141a and the first connecting portion 141b.
  • the second bent portion 142 extends from the other end of the first portion 14a toward one end (for example, from right to left in FIG. 3), then rises and extends with respect to the first portion 14a, and then rises. It bends in the opposite manner to the bending mode. Specifically, the second bent portion 142 is bent in a manner opposite to the bent mode of the second standing portion 142a rising and extending from the first portion 14a and the second standing portion 142a, and the second connecting portion 146. It has a second connecting portion 142b connected to one end of the above, and a second straight portion 142c extending linearly and connecting the second standing portion 142a and the second connecting portion 142b.
  • the third bent portion 143 rises from the connecting portion with the first connecting portion 145 and extends, and then bends in a mode opposite to the rising bending mode. Specifically, the third bent portion 143 is bent in a manner opposite to the bent mode of the third erected portion 143a rising from the other end of the first connecting portion 145 and extending, and the third erected portion 143a. It has a third connecting portion 143b connected to one end of the three connecting portions 147, and a third straight portion 143c extending linearly and connecting the third standing portion 143a and the third connecting portion 143b.
  • the fourth bent portion 144 rises from the connecting portion with the second connecting portion 146 and extends, and then bends in a mode opposite to the rising bending mode. Specifically, the fourth bent portion 144 is bent in a manner opposite to the bent mode of the fourth erected portion 144a extending from the other end of the second connecting portion 146 and the fourth erected portion 144a. 3. It has a fourth connecting portion 144b connected to the other end of the connecting portion 147, and a fourth straight portion 144c extending linearly and connecting the fourth standing portion 144a and the fourth connecting portion 144b.
  • the first bent portion 141 and the third bent portion 143 each have a shape in which a band-shaped member is bent in an S shape.
  • the second bent portion 142 and the fourth bent portion 144 have a shape in which a band-shaped member is bent in the opposite directions to the first bent portion 141 and the third bent portion 143, respectively.
  • the first connecting portion 145 and the second connecting portion 146 extend in the same direction as the first portion 14a in the natural state. That is, in the present embodiment, in the first connecting portion 145, in the natural state, the minimum distance d 11 between the end portion on the first bent portion 141 side and the first portion 14a is on the third bent portion 143 side. It is substantially equivalent to the minimum distance d 12 between the end and the first portion 14a. Further, in the second connecting portion 146, in a natural state, the minimum distance d 21 between the end portion on the second bent portion 142 side and the first portion 14a is the end portion and the first portion on the fourth bent portion 144 side. It is substantially equivalent to the minimum distance d 22 between 14a.
  • the "natural state” here means a state in which no load other than gravity is applied. Further, the "substantially equivalent distance” includes the same distance and a distance that fluctuates due to a manufacturing error.
  • the third connecting portion 147 extends linearly and is attached to the frame 13 to support the frame 13.
  • the entire third connecting portion 147 may be fixed to the frame 13, or a part of the third connecting portion 147 may be fixed to the frame 13.
  • the spring member 14 is formed of, for example, fiber reinforced plastic (Fiber Reinforced Plastics: FRP), metal, or resin. In designing the shape, elastic force, etc. of the spring member 14, FRP has a higher degree of freedom in its design than metal or resin. Further, the spring member 14 may be made of one plate material, or may be made of a plurality of members, for example, the first portion 14a and the second portion 14b may be separate bodies. When the first portion 14a and the second portion 14b are separate bodies, they may be made of different materials. When the first portion 14a and the second portion 14b of the spring member 14 are made of different materials, for example, the first portion 14a is made of fiber reinforced plastic and the second portion 14b is made of spring steel. In the present embodiment, the configuration in which the first portion 14a extends along the longitudinal direction and has a slit penetrating in the direction orthogonal to the longitudinal direction will be described, but the configuration may not have the slit.
  • FRP Fiber Reinforced Plastics
  • the first support portions 11a and 12a respectively accommodate and hold the end portions of the spring member 14. Specifically, the first support portion 11a holds one end of the first portion 14a and the end portion of the first bent portion 141 on the side opposite to the first connecting portion 145 side. The first support portion 12a holds the other end of the first portion 14a and the end portion of the second bent portion 142 on the side opposite to the second connecting portion 146 side. Further, the second support portions 11c and 12c grip the central portion of the spring member 14 by inserting the spring member 14 into the hole. The spring member 14 can move in the direction of being inserted and removed from the first support portions 11a and 12a. Here, the spring member 14 may be fixed to the first support portions 11a and 12a with bolts, clips, or the like to limit the movement in the direction of insertion / removal.
  • FIG. 5 is a diagram showing the relationship between the deflection of the spring member and the load in the suspension device according to the embodiment of the present invention.
  • the spring member 14 flexes non-linearly with respect to the load.
  • FIG. 5 shows the deflection of the spring member 14 when a load that displaces the arm is applied to the end portions (here, the first support portions 11a and 12a) on the wheel connection side of each arm.
  • the load F 1 corresponds to the load applied to the frame 13 such as the vehicle body in the unloaded state of the vehicle.
  • the load F 2 corresponds to the maximum load applied to the frame 13 when the vehicle is loaded.
  • the unloaded state refers to a state in which no human is on board and no load is loaded in the completed vehicle.
  • the loaded state refers to a state in which a person is on board or loaded with a load. In this loaded state, the load in which the load applied to the vehicle is the maximum (the maximum load allowed for using the vehicle) is the maximum load.
  • the spring member 14 has a first high spring constant region R 11 and a second high spring constant region R 12 in which the change in deflection is large with respect to a change in load, and the spring member 14 has a deflection with respect to a change in load. It has a low spring constant region R 20 with a small change.
  • the transition occurs in the first high spring constant region R 11 from the state where the load is 0 and the deflection is 0, and changes to the low spring constant region R 20 with the load F 1 as a boundary.
  • the spring constant changes to the second high spring constant region R 12.
  • the spring member 14 has a non-linear spring characteristic as a whole regarding the relationship between the deflection and the load.
  • FIG. 6 is a diagram showing the relationship between the deflection and the load in the first portion of the spring member of the suspension device according to the embodiment of the present invention. As shown in FIG. 6, only in the first portion 14a, the relationship between the deflection and the load has a linear spring characteristic. Therefore, in the spring member 14, the addition of the second portion 14b to the first portion 14a imparts a non-linear spring characteristic with respect to the relationship between the deflection and the load.
  • the point P 1 corresponds to a state in which the vehicle body or the like is not attached to the frame 13 and the spring member 14 is not bent.
  • the point P 2 is a point corresponding to the load in the unloaded state and the bending at that time, and is a point where the first high spring constant region R 11 changes to the low spring constant region R 20.
  • Point P 3 is a point corresponding to the load in the low spring constant region R 20 and the bending at that time.
  • Point P 4 is a point corresponding to the load in the loaded state and the bending at that time, and is a point where the low spring constant region R 20 changes to the second high spring constant region R 12.
  • the point P 5 corresponds to the load in the second high spring constant region R 12 and the bending at that time, and is a point indicating the bending in the load F 2.
  • FIG. 7 is a diagram showing a state of the suspension system in the point P 1 shown in FIG.
  • FIG. 8 is an enlarged view of the deformed portion of the spring member shown in FIG. 7. In the state of point P 1 the spring member 14 is not deflected, no forces applied by bending the spring member 14.
  • the second bent portion 142 and the fourth bent portion 144 of the spring member 14 are the spring member 14.
  • a buckling phenomenon occurs in which the spring constant deviates in the longitudinal direction (for example, the stretching direction of the first portion 14a), and the spring constant decreases due to this buckling phenomenon.
  • the vehicle body is tilted (rolled) by the action of the spring member 14, and one wheel is on the upper side (vehicle body side) and the other wheel is on the opposite side (here, the opposite in the Z direction).
  • the spring member 14 is displaced to the side
  • the spring member 14 is deformed or tries to return to the original shape, thereby suppressing the inclination (roll angle) of the vehicle body.
  • FIG. 9 shows the displacement amount (left arm 12) of the left arm (left arm 12) with respect to the displacement amount (input) of the right arm due to the load applied to the right arm (right arm 11) of the suspension device according to the embodiment of the present invention. It is a figure which shows output).
  • the left arm 12 is also displaced by the action of the spring member 14. At this time, since the left arm 12 is displaced by a displacement amount substantially equal to the displacement amount of the right arm 11, the above-mentioned tilt suppressing effect can be obtained.
  • the spring member 14 interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first portion.
  • a second portion 14b that rises from 14a and extends extends to support the frame 13.
  • the second portion 14b shows a non-loading deflection, a high spring constant when the vehicle is unloaded, a low spring constant when a load transitioning from the unloaded state to the loaded state is applied, and then. In the loaded state, a load close to the maximum load shows a high spring constant again.
  • the spring member 14 has a reduced stroke (deflection) with respect to a load when a heavy load is applied in the unloaded state or the loaded state.
  • the first portion 14a can suppress the inclination of the vehicle body by displacing the other arm according to the displacement of one arm.
  • FIG. 10 is a perspective view schematically showing the configuration of a main part of the suspension device according to the first modification of the embodiment of the present invention.
  • the stretching directions of the first connecting portion and the second connecting portion of the spring member are different from the stretching directions of the first connecting portion 145 and the second connecting portion 146 according to the embodiment.
  • the configuration is the same as that of the above-described embodiment except for the configuration of the first and second connecting portions.
  • the configurations of the first and second connecting portions will be described.
  • the spring member 14A shown in FIG. 10 has a first portion 14a extending in a band shape and a second portion 14c rising from the first portion 14a and extending.
  • the second portion 14c stands up in a convex shape with respect to the first portion 14a. Specifically, the second portion 14c extends linearly with the first bent portion 141, the second bent portion 142, the third bent portion 143, the fourth bent portion 144, and the third connecting portion 147, and one end thereof is the first.
  • a second connecting portion 148 that is connected to the bent portion 141 and the other end is connected to the third bent portion 143, and a second that extends linearly, one end is connected to the second bent portion 142, and the other end is connected to the fourth bent portion 144. It has a connecting portion 149 and.
  • the minimum distance d 13 between the end portion on the first bent portion 141 side and the first portion 14a is set to the end portion on the third bent portion 143 side and the first portion 14a. Less than the minimum distance d 14 between.
  • the minimum distance d 23 between the end portion on the second bent portion 142 side and the first portion 14a is set to the end portion on the fourth bent portion 144 side and the first portion 14a. Less than the minimum distance d 24 between.
  • the spring member 14A interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first A second portion 14c rising from and extending from the portion 14a supports the frame 13.
  • the second portion 14c shows a non-linear variation in deflection with respect to the load, exhibits a high spring constant in the unloaded state of the vehicle, a low spring constant from the load transitioning from the unloaded state to the loaded state, and then in the loaded state.
  • a load close to the maximum load shows a high spring constant again.
  • the spring constant that the second portion 14c is non-linear with respect to the load it is possible to achieve both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied. Can be done.
  • FIG. 11 is a perspective view schematically showing the configuration of a main part of the suspension device according to the second modification of the embodiment of the present invention.
  • the spring member according to the second modification has a configuration that does not have a component corresponding to the third bent portion 143 and the fourth bent portion 144 according to the embodiment.
  • the spring member 14B shown in FIG. 11 has a first portion 14a extending in a band shape and a second portion 14d rising from the first portion 14a and extending.
  • the second portion 14d stands up with respect to the first portion 14a.
  • the second portion 14d includes a first bent portion 141A and a second bent portion 142A that rise and extend from the first portion 14a, respectively, and a connecting portion 150 that connects the first bent portion 141A and the second bent portion 142A.
  • the first bent portion 141A is connected to the first standing portion 141d extending from the first portion 14a and extending from the first standing portion 141d, and is bent in a mode opposite to the bending mode of the first standing portion 141d. It has a first connecting portion 141e connected to one end of the connecting portion 150. That is, the first bent portion 141A corresponds to a configuration that does not have the first straight portion 141c of the first bent portion 141 described above.
  • the second bent portion 142A is connected to the second standing portion 142d extending from the first portion 14a and extending from the first portion 14a, and is bent in a mode opposite to the bending mode of the second standing portion 142d. It has a second connecting portion 142e connected to the other end of the connecting portion 150. That is, the second bent portion 142A corresponds to a configuration that does not have the second straight portion 142c of the second bent portion 142 described above.
  • the connecting portion 150 is attached to the frame 13 (see FIG. 1) to support the frame 13.
  • the entire connecting portion 150 may be fixed to the frame 13, or a part of the connecting portion 150 may be fixed to the frame 13.
  • the spring member 14B has a non-linear spring characteristic regarding the relationship between the load and the deflection due to the deformation (for example, buckling) of the first bending portion 141A and the second bending portion 142A with respect to the load.
  • the spring member 14B interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first A second portion 14d rising from and extending from the portion 14a supports the frame 13. Similar to the second portion 14b, the second portion 14d shows a high spring constant in the unloaded state of the vehicle, and the low spring constant from the load transitioning from the unloaded state to the loaded state. After that, the high spring constant is shown again at a load close to the maximum load in the loaded state. In this way, by showing the spring constant that the second portion 14d is non-linear with respect to the load, it is possible to achieve both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied. Can be done.
  • FIG. 12 is a perspective view schematically showing the configuration of a main part of the suspension device according to the third modification of the embodiment of the present invention.
  • the spring member according to the third modification has a configuration that does not have components corresponding to the third bent portion 143, the fourth bent portion 144, and the third connecting portion 147 according to the embodiment.
  • the spring member 14C shown in FIG. 12 has a first portion 14a extending in a band shape and a second portion 14e rising from the first portion 14a and extending.
  • the second portion 14e stands up with respect to the first portion 14a.
  • the second portion 14e is on the side of the first portion 14a with respect to the first bent portion 141A and the second bent portion 142A extending from the first portion 14a, respectively, and the first bent portion 141A and the second bent portion 142A.
  • the first frame support portion 151 and the second frame support portion 152 which are provided on opposite sides (frame 13 side) and each support the frame 13, and the first bent portion 141A and the first frame support portion 151 are connected to each other.
  • the spring member 14C corresponds to a configuration in which a part of the connecting portion 150 of the spring member 14B described above is removed.
  • the spring member 14C has a non-linear spring characteristic regarding the relationship between the load and the deflection due to the deformation (for example, buckling) of the first bending portion 141A and the second bending portion 142A with respect to the load.
  • the spring member 14C interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first A second portion 14e rising from and extending from the portion 14a supports the frame 13.
  • the second portion 14e shows a non-linear change in deflection with respect to the load, shows a high spring constant in the unloaded state of the vehicle, shows a low spring constant from the load transitioning from the unloaded state to the loaded state, and then in the loaded state.
  • a load close to the maximum load shows a high spring constant again.
  • each straight portion (first straight portion 141c and second straight portion 142c) of the first bent portion 141 and the second bent portion, and the third bent portion 143 and the fourth bent portion 144. Since the structure does not have the above, the spring member can be miniaturized. This makes it possible to lower the floor when the vehicle is provided as a suspension device.
  • a cushioning member such as rubber may be provided at a portion of the arm in contact with the spring member, and the spring member may be supported via the cushioning member.
  • the support points of the spring member by the second support portions 11c and 12c are not limited to the above-mentioned positions.
  • the position of the spring member 14 closer to the center may be supported, or the positions of the first support portions 11a and 12a may be supported.
  • the spring member 14 is not limited to the configuration held by the first support portions 11a and 12a, and may be held by, for example, a link or a knuckle connected to the arm.
  • first connecting portion 145, 148 and the second connecting portion 146, 149 may be configured to extend in an arc shape or a wavy shape.
  • the spring members 14 and 14A may have a configuration that does not have the third connecting portion 147.
  • the third bent portion 143 and the fourth bent portion 144 each support the frame 13.
  • the spring members 14 and 14A have a configuration in which each bent portion does not have a straight portion (for example, the first straight portion 141c of the first bent portion 141) as in the modified examples 2 and 3. May be.
  • suspension device may be provided in the vehicle in combination with another suspension device such as a suspension device using a coil spring.
  • the suspension device and the spring member according to the present invention are suitable for achieving both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Springs (AREA)

Abstract

A spring member according to the present invention comprises: a band-shaped first part exhibiting spring properties in which a relationship between load and deflection is linear; and a second part rising and extending relative to the first part. The spring member exhibits nonlinear spring properties.

Description

ばね部材及び懸架装置Spring members and suspension devices
　本発明は、ばね部材及び懸架装置に関するものである。 The present invention relates to a spring member and a suspension device.
　従来、車両等に設けられ、路面の凹凸による振動が車輪を経て車体に伝わらないようにする緩衝機能を有し、車両の乗り心地や操縦の安定性などを向上させる懸架装置が知られている。懸架装置のうち、リーフスプリング式の懸架装置は、帯状のばね部材を用いて構成される（例えば、特許文献１を参照）。 Conventionally, there is known a suspension device provided on a vehicle or the like, which has a buffer function for preventing vibration due to unevenness of the road surface from being transmitted to the vehicle body via wheels, and improves the riding comfort and steering stability of the vehicle. .. Among the suspension devices, the leaf spring type suspension device is configured by using a strip-shaped spring member (see, for example, Patent Document 1).
　ばね部材は、車輪を支持するアームと、車体を支持するフレームと間に介在する。具体的に、ばね部材は、右側の車輪を支持する右アーム、左側の車輪を支持する左アームに保持される。特許文献１では、このばね部材に加えて、コイルばねを用いた方式と組み合わせて構成される。 The spring member is interposed between the arm that supports the wheels and the frame that supports the vehicle body. Specifically, the spring member is held by a right arm that supports the right wheel and a left arm that supports the left wheel. In Patent Document 1, in addition to this spring member, it is configured in combination with a method using a coil spring.
特開２０１３－１８９１８９号公報Japanese Unexamined Patent Publication No. 2013-189189
　ところで、車両における乗り心地を良くするには、ばね部材のばね定数を低くして、振動に追従しやすくすることが好ましい。一方で、ばね部材には、車体等の車両の部材の自重が加わる。ばね定数が低いばね部材に、車両の部材の自重が加わると、車両の上下方向のばねの撓みが大きくなってしまい、ばね部材自体が大型化してしまう問題があった。よって、この自重に対してばね部材が変形することによる、車両の上下方向のばね部材の撓みを小さくするためには、車両の部材の自重が加わる範囲では、ばね部材のばね定数が高いことが望まれる。このように、懸架装置のばね部材には、荷重によって撓み（ばね定数）が変化する、非線形なばね特性を有することが望まれていた。しかしながら、特許文献１に示す懸架装置は、アームのみによってばね部材を保持しているため、ばね特性を非線形とすることが難しかった。 By the way, in order to improve the riding comfort in a vehicle, it is preferable to lower the spring constant of the spring member so that it can easily follow the vibration. On the other hand, the weight of a vehicle member such as a vehicle body is added to the spring member. When the weight of the vehicle member is added to the spring member having a low spring constant, the spring flexure in the vertical direction of the vehicle becomes large, and there is a problem that the spring member itself becomes large. Therefore, in order to reduce the deflection of the spring member in the vertical direction of the vehicle due to the deformation of the spring member with respect to the own weight, the spring constant of the spring member must be high within the range in which the own weight of the vehicle member is applied. desired. As described above, it has been desired that the spring member of the suspension device has a non-linear spring characteristic in which the deflection (spring constant) changes depending on the load. However, in the suspension device shown in Patent Document 1, since the spring member is held only by the arm, it is difficult to make the spring characteristics non-linear.
　本発明は、上記に鑑みてなされたものであって、車両における良好な乗り心地と、車両の部材の自重が加わるまでのばね部材の撓みの低減とを両立することができるばね部材及び懸架装置を提供することを目的とする。 The present invention has been made in view of the above, and is a spring member and a suspension device capable of achieving both a good ride quality in a vehicle and a reduction in bending of the spring member until the weight of the vehicle member is applied. The purpose is to provide.
　上述した課題を解決し、目的を達成するために、本発明に係るばね部材は、荷重と撓みとの関係が線形のばね特性を示す帯状の第１部分と、前記第１部分に対して立ち上がって延在する第２部分と、を備え、非線形のばね特性を示すことを特徴とする。 In order to solve the above-mentioned problems and achieve the object, the spring member according to the present invention rises with respect to a band-shaped first portion in which the relationship between the load and the deflection shows linear spring characteristics and the first portion. It is characterized by having a second portion extending from the surface and exhibiting a non-linear spring characteristic.
　また、本発明に係るばね部材は、上記の発明において、前記第２部分は、前記第１部分からそれぞれ立ち上がって延在する第１及び第２屈曲部、を有し、前記第１屈曲部は、前記第１部分の一端から他端に向かって延びた後、前記第１部分に対して立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲し、前記第２屈曲部は、前記第１部分の他端から一端に向かって延びた後、前記第１部分に対して立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する、ことを特徴とする。 Further, in the above-mentioned invention, the spring member according to the present invention has the first and second bent portions that rise and extend from the first portion, respectively, and the first bent portion is After extending from one end to the other end of the first portion, the second bent portion stands up and extends with respect to the first portion, and then bends in a mode opposite to the bending mode of the rising portion. Is characterized in that it extends from the other end of the first portion toward one end, then stands up and extends with respect to the first portion, and then bends in a mode opposite to the bending mode of rising. To do.
　また、本発明に係るばね部材は、上記の発明において、前記第２部分は、前記第１及び第２屈曲部に対して前記第１部分側と反対側にそれぞれ設けられる第３及び第４屈曲部と、前記第１屈曲部と前記第３屈曲部とを連結する第１連結部と、前記第２屈曲部と前記第４屈曲部とを連結する第２連結部と、をさらに有し、前記第３屈曲部は、前記第１連結部との連結部分から立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲し、前記第４屈曲部は、前記第２連結部との連結部分から立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する、ことを特徴とする。 Further, in the spring member according to the present invention, in the above invention, the second portion is provided on the side opposite to the first portion side with respect to the first and second bent portions, respectively. Further, it has a first connecting portion for connecting the first bent portion and the third bent portion, and a second connecting portion for connecting the second bent portion and the fourth bent portion. The third bent portion rises from the connecting portion with the first connecting portion and extends, and then bends in a mode opposite to the rising bending mode, and the fourth bent portion is the second connecting portion. It is characterized in that it rises from the connecting portion with and extends, and then bends in a mode opposite to the bending mode of rising.
　また、本発明に係るばね部材は、上記の発明において、前記第２部分は、前記第３屈曲部と前記第４屈曲部とを連結する第３連結部、をさらに有することを特徴とする。 Further, the spring member according to the present invention is characterized in that, in the above invention, the second portion further includes a third connecting portion that connects the third bent portion and the fourth bent portion.
　また、本発明に係るばね部材は、上記の発明において、前記第１連結部は、自然状態において、前記第１屈曲部側の端部と前記第１部分との間の最小距離が、前記第３屈曲部と前記第１部分との間の最小距離以下であり、前記第２連結部は、自然状態において、前記第２屈曲部側の端部と前記第１部分との間の最小距離が、前記第４屈曲部と前記第１部分との間の最小距離以下である、ことを特徴とする。 Further, in the spring member according to the present invention, in the above invention, the first connecting portion has the minimum distance between the end portion on the first bending portion side and the first portion in the natural state. 3 The minimum distance between the bent portion and the first portion is equal to or less than the minimum distance between the end portion on the side of the second bent portion and the first portion in the natural state of the second connecting portion. It is characterized in that it is not more than the minimum distance between the fourth bent portion and the first portion.
　また、本発明に係るばね部材は、上記の発明において、前記ばね部材は、繊維強化プラスチックからなる、ことを特徴とする。 Further, the spring member according to the present invention is characterized in that, in the above invention, the spring member is made of fiber reinforced plastic.
　また、本発明に係るばね部材は、上記の発明において、前記ばね部材は、前記第１部分と前記第２部分とが互いに異なる材料からなる、ことを特徴とする。 Further, the spring member according to the present invention is characterized in that, in the above invention, the spring member is made of a material in which the first portion and the second portion are different from each other.
　また、本発明に係るばね部材は、上記の発明において、前記ばね部材は、前記第１部分が繊維強化プラスチックからなり、前記第２部分がばね鋼からなる、ことを特徴とする。 Further, the spring member according to the present invention is characterized in that, in the above invention, the first part of the spring member is made of fiber reinforced plastic and the second part is made of spring steel.
　また、本発明に係る懸架装置は、第１アームと、第２アームと、一端が前記第１アームの動きに連動して変位し、他端が前記第２アームの動きに連動して変位する、荷重と撓みとの関係が線形のばね特性を示す帯状の第１部分と、前記第１部分に対して立ち上がって延在する第２部分とを有し、非線形のばね特性を示すばね部材と、前記ばね部材の前記第２部分に支持される被支持部材と、を備えることを特徴とする。 Further, in the suspension device according to the present invention, one end of the first arm and the second arm is displaced in conjunction with the movement of the first arm, and the other end is displaced in conjunction with the movement of the second arm. A spring member having a band-shaped first portion in which the relationship between load and deflection shows linear spring characteristics and a second portion that rises and extends with respect to the first portion, and exhibits non-linear spring characteristics. , A supported member supported by the second portion of the spring member.
　本発明によれば、車両における良好な乗り心地と、車両の部材の自重が加わるまでのばね部材の撓みの低減とを両立することができるという効果を奏する。 According to the present invention, it is possible to achieve both a good ride quality in a vehicle and a reduction in bending of a spring member until the weight of the vehicle member is applied.
図１は、本発明の一実施の形態に係る懸架装置の構成を模式的に示す斜視図である。FIG. 1 is a perspective view schematically showing a configuration of a suspension device according to an embodiment of the present invention. 図２は、図１に示す懸架装置のアームの一部を取り除いた図である。FIG. 2 is a view in which a part of the arm of the suspension device shown in FIG. 1 is removed. 図３は、図２に示す懸架装置を矢視Ａ方向からみた平面図である。FIG. 3 is a plan view of the suspension device shown in FIG. 2 as viewed from the direction of arrow A. 図４は、本発明の一実施の形態に係る懸架装置の要部の構成を模式的に示す斜視図である。FIG. 4 is a perspective view schematically showing the configuration of a main part of the suspension device according to the embodiment of the present invention. 図５は、本発明の一実施の形態に係る懸架装置におけるばね部材の撓みと荷重との関係を示す図である。FIG. 5 is a diagram showing the relationship between the deflection of the spring member and the load in the suspension device according to the embodiment of the present invention. 図６は、本発明の一実施の形態に係る懸架装置の、ばね部材の第１部分における撓みと荷重との関係を示す図である。FIG. 6 is a diagram showing the relationship between the deflection and the load in the first portion of the spring member of the suspension device according to the embodiment of the present invention. 図７は、図５に示す点Ｐ1における懸架装置の状態を示す図である。Figure 7 is a diagram showing a state of the suspension system in the point P 1 shown in FIG. 図８は、図７に示すばね部材の変形部分を拡大した図である。FIG. 8 is an enlarged view of the deformed portion of the spring member shown in FIG. 7. 図９は、本発明の一実施の形態に係る懸架装置の右アームへの荷重の負荷による、右アームの変位量に対する左アームの変位量を示す図である。FIG. 9 is a diagram showing a displacement amount of the left arm with respect to a displacement amount of the right arm due to a load applied to the right arm of the suspension device according to the embodiment of the present invention. 図１０は、本発明の実施の形態の変形例１に係る懸架装置の要部の構成を模式的に示す斜視図である。FIG. 10 is a perspective view schematically showing the configuration of a main part of the suspension device according to the first modification of the embodiment of the present invention. 図１１は、本発明の実施の形態の変形例２に係る懸架装置の要部の構成を模式的に示す斜視図である。FIG. 11 is a perspective view schematically showing the configuration of a main part of the suspension device according to the second modification of the embodiment of the present invention. 図１２は、本発明の実施の形態の変形例３に係る懸架装置の要部の構成を模式的に示す斜視図である。FIG. 12 is a perspective view schematically showing the configuration of a main part of the suspension device according to the third modification of the embodiment of the present invention.
　以下、本発明を実施するための形態を図面と共に詳細に説明する。なお、以下の実施の形態により本発明が限定されるものではない。また、以下の説明において参照する各図は、本発明の内容を理解し得る程度に形状、大きさ、及び位置関係を概略的に示してあるに過ぎない。すなわち、本発明は各図で例示された形状、大きさ、及び位置関係のみに限定されるものではない。 Hereinafter, a mode for carrying out the present invention will be described in detail together with drawings. The present invention is not limited to the following embodiments. In addition, each of the figures referred to in the following description merely schematically shows the shape, size, and positional relationship to the extent that the content of the present invention can be understood. That is, the present invention is not limited to the shape, size, and positional relationship exemplified in each figure.
（実施の形態）
　図１は、本発明の一実施の形態に係る懸架装置の構成を模式的に示す斜視図である。図２は、図１に示す懸架装置のアームの一部（延在部１１ｂ、１２ｂ）を取り除いた図である。図３は、図２に示す懸架装置を矢視Ａ方向からみた平面図である。図４は、本発明の一実施の形態に係る懸架装置の要部の構成を模式的に示す斜視図である。懸架装置１は、例えば車両に設けられ、右側の車輪、左側の車輪、及び車体（ボディ）の間に介在して、車輪から伝わる振動が車体に伝達されることを抑制する。 (Embodiment)
FIG. 1 is a perspective view schematically showing a configuration of a suspension device according to an embodiment of the present invention. FIG. 2 is a view in which a part (extending portions 11b, 12b) of the arm of the suspension device shown in FIG. 1 is removed. FIG. 3 is a plan view of the suspension device shown in FIG. 2 as viewed from the direction of arrow A. FIG. 4 is a perspective view schematically showing the configuration of a main part of the suspension device according to the embodiment of the present invention. The suspension device 1 is provided in, for example, a vehicle and is interposed between the right wheel, the left wheel, and the vehicle body (body) to suppress the vibration transmitted from the wheels from being transmitted to the vehicle body.
　懸架装置１は、右側の車輪を支持する右アーム１１と、左側の車輪を支持する左アーム１２と、車体を支持するフレーム１３と、車輪からの振動に応じて弾性変形するばね部材１４と、を備える。懸架装置１は、フレーム１３を経て車体に取り付けられ、路面の凹凸に応じて車輪から伝達される振動を吸収する。車輪は、例えばナックルやディスクロータ等を経てアームに支持される。 The suspension device 1 includes a right arm 11 that supports the right wheel, a left arm 12 that supports the left wheel, a frame 13 that supports the vehicle body, and a spring member 14 that elastically deforms in response to vibration from the wheels. To be equipped. The suspension device 1 is attached to the vehicle body via the frame 13 and absorbs vibration transmitted from the wheels according to the unevenness of the road surface. The wheels are supported by the arm via, for example, a knuckle or a disc rotor.
　右アーム１１は、右側の車輪を支持するとともに、ばね部材１４の一端を支持する第１支持部１１ａと、第１支持部１１ａから延びる延在部１１ｂと、延在部１１ｂの第１支持部１１ａ側と反対側の端部に設けられ、ばね部材１４の一部を支持する第２支持部１１ｃとを有する。右アーム１１は、延在部１１ｂの延伸方向と直交する方向に延びる軸部１５に支持され、軸部１５の中心軸のまわりに回転可能である。 The right arm 11 has a first support portion 11a that supports the right wheel and one end of the spring member 14, an extension portion 11b extending from the first support portion 11a, and a first support portion of the extension portion 11b. It has a second support portion 11c provided at an end portion opposite to the 11a side and supporting a part of the spring member 14. The right arm 11 is supported by a shaft portion 15 extending in a direction orthogonal to the extending direction of the extending portion 11b, and is rotatable around the central axis of the shaft portion 15.
　左アーム１２は、左側の車輪を支持するとともに、ばね部材１４の他端を支持する第１支持部１２ａと、第１支持部１２ａから延びる延在部１２ｂと、延在部１２ｂの第１支持部１２ａ側と反対側の端部に設けられ、ばね部材１４の一部を支持する第２支持部１２ｃとを有する。左アーム１２は、延在部１２ｂの延伸方向と直交する方向に延びる軸部１６に支持され、軸部１６の中心軸のまわりに回転可能である。 The left arm 12 has a first support portion 12a that supports the left wheel and supports the other end of the spring member 14, an extension portion 12b that extends from the first support portion 12a, and a first support of the extension portion 12b. It has a second support portion 12c provided at an end portion opposite to the portion 12a side and supporting a part of the spring member 14. The left arm 12 is supported by a shaft portion 16 extending in a direction orthogonal to the extending direction of the extending portion 12b, and is rotatable around the central axis of the shaft portion 16.
　フレーム１３は、車体を支持する。フレーム１３は、ばね部材１４に支持され、車体と、右側車輪、右アーム１１、左側車輪、左アーム１２及びばね部材１４との間に介在する。フレーム１３は、被支持部材に相当する。なお、フレーム１３は、車体と一体化されたものであってもよい。フレーム１３が車体と一体化されている場合は、車体がばね部材１４と連結する構成（被支持部材）となる。 The frame 13 supports the vehicle body. The frame 13 is supported by the spring member 14 and is interposed between the vehicle body and the right wheel, the right arm 11, the left wheel, the left arm 12, and the spring member 14. The frame 13 corresponds to a supported member. The frame 13 may be integrated with the vehicle body. When the frame 13 is integrated with the vehicle body, the vehicle body is connected to the spring member 14 (supported member).
　ばね部材１４は、帯状をなして延びる第１部分１４ａと、帯状の部材が屈曲してなり、第１部分１４ａに対して立ち上がって延在する第２部分１４ｂとを有する。
　第１部分１４ａは、一端が右アーム１１に支持され、他端が左アーム１２に支持される。また、第１部分１４ａは、長手方向の中央部において、右アーム１１及び左アーム１２（第２支持部１１ｃ、１２ｃ）にそれぞれ支持される。 The spring member 14 has a first portion 14a extending in a strip shape, and a second portion 14b in which the strip-shaped member is bent and rises and extends with respect to the first portion 14a.
One end of the first portion 14a is supported by the right arm 11 and the other end is supported by the left arm 12. Further, the first portion 14a is supported by the right arm 11 and the left arm 12 ( second support portions 11c and 12c) at the central portion in the longitudinal direction, respectively.
　第２部分１４ｂは、第１部分１４ａに対し、凸状をなして立ち上がってなる。具体的に、第２部分１４ｂは、第１部分１４ａからそれぞれ立ち上がって延在する第１屈曲部１４１及び第２屈曲部１４２と、第１屈曲部１４１及び第２屈曲部１４２に対し、第１部分１４ａ側と反対側（フレーム１３側）にそれぞれ設けられる第３屈曲部１４３及び第４屈曲部１４４と、第１屈曲部１４１と第３屈曲部１４３とを連結する第１連結部１４５と、第２屈曲部１４２と第４屈曲部１４４とを連結する第２連結部１４６と、第３屈曲部１４３と第４屈曲部１４４とを連結する第３連結部１４７とを有する（図３、４参照）。 The second portion 14b stands up in a convex shape with respect to the first portion 14a. Specifically, the second portion 14b is the first with respect to the first bent portion 141 and the second bent portion 142, and the first bent portion 141 and the second bent portion 142, which rise and extend from the first portion 14a, respectively. The third bent portion 143 and the fourth bent portion 144 provided on the side opposite to the portion 14a side (frame 13 side), and the first connecting portion 145 connecting the first bent portion 141 and the third bent portion 143, respectively. It has a second connecting portion 146 that connects the second bent portion 142 and the fourth bent portion 144, and a third connecting portion 147 that connects the third bent portion 143 and the fourth bent portion 144 (FIGS. 3, 4). reference).
　第１屈曲部１４１は、第１部分１４ａの一端から他端（例えば、図３の左から右）に向かって延びた後、第１部分１４ａに対して立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する。具体的に、第１屈曲部１４１は、第１部分１４ａから立ち上がって延びる第１立設部１４１ａと、第１立設部１４１ａの屈曲態様とは逆の態様で屈曲して第１連結部１４５の一端に接続する第１接続部１４１ｂと、直線状に延び、第１立設部１４１ａと第１接続部１４１ｂとを接続する第１直線部１４１ｃとを有する。 The first bent portion 141 extends from one end to the other end (for example, from left to right in FIG. 3) of the first portion 14a, then rises and extends with respect to the first portion 14a, and then rises. It bends in the opposite manner to the bending mode. Specifically, the first bent portion 141 is bent in a manner opposite to the bent mode of the first standing portion 141a rising and extending from the first portion 14a and the first standing portion 141a, and the first connecting portion 145. It has a first connecting portion 141b connected to one end of the above, and a first straight portion 141c extending linearly and connecting the first standing portion 141a and the first connecting portion 141b.
　第２屈曲部１４２は、第１部分１４ａの他端から一端（例えば、図３の右から左）に向かって延びた後、第１部分１４ａに対して立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する。具体的に、第２屈曲部１４２は、第１部分１４ａから立ち上がって延びる第２立設部１４２ａと、第２立設部１４２ａの屈曲態様とは逆の態様で屈曲して第２連結部１４６の一端に接続する第２接続部１４２ｂと、直線状に延び、第２立設部１４２ａと第２接続部１４２ｂとを接続する第２直線部１４２ｃとを有する。 The second bent portion 142 extends from the other end of the first portion 14a toward one end (for example, from right to left in FIG. 3), then rises and extends with respect to the first portion 14a, and then rises. It bends in the opposite manner to the bending mode. Specifically, the second bent portion 142 is bent in a manner opposite to the bent mode of the second standing portion 142a rising and extending from the first portion 14a and the second standing portion 142a, and the second connecting portion 146. It has a second connecting portion 142b connected to one end of the above, and a second straight portion 142c extending linearly and connecting the second standing portion 142a and the second connecting portion 142b.
　第３屈曲部１４３は、第１連結部１４５との連結部分から立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する。具体的に、第３屈曲部１４３は、第１連結部１４５の他端から立ち上がって延びる第３立設部１４３ａと、第３立設部１４３ａの屈曲態様とは逆の態様で屈曲して第３連結部１４７の一端に接続する第３接続部１４３ｂと、直線状に延び、第３立設部１４３ａと第３接続部１４３ｂとを接続する第３直線部１４３ｃとを有する。 The third bent portion 143 rises from the connecting portion with the first connecting portion 145 and extends, and then bends in a mode opposite to the rising bending mode. Specifically, the third bent portion 143 is bent in a manner opposite to the bent mode of the third erected portion 143a rising from the other end of the first connecting portion 145 and extending, and the third erected portion 143a. It has a third connecting portion 143b connected to one end of the three connecting portions 147, and a third straight portion 143c extending linearly and connecting the third standing portion 143a and the third connecting portion 143b.
　第４屈曲部１４４は、第２連結部１４６との連結部分から立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する。具体的に、第４屈曲部１４４は、第２連結部１４６の他端から立ち上がって延びる第４立設部１４４ａと、第４立設部１４４ａの屈曲態様とは逆の態様で屈曲して第３連結部１４７の他端に接続する第４接続部１４４ｂと、直線状に延び、第４立設部１４４ａと第４接続部１４４ｂとを接続する第４直線部１４４ｃとを有する。
　第１屈曲部１４１及び第３屈曲部１４３は、それぞれ帯状の部材をＳ字状に屈曲させた形状をなしている。第２屈曲部１４２及び第４屈曲部１４４は、第１屈曲部１４１及び第３屈曲部１４３とは逆向きに、それぞれ帯状の部材を屈曲させた形状をなしている。 The fourth bent portion 144 rises from the connecting portion with the second connecting portion 146 and extends, and then bends in a mode opposite to the rising bending mode. Specifically, the fourth bent portion 144 is bent in a manner opposite to the bent mode of the fourth erected portion 144a extending from the other end of the second connecting portion 146 and the fourth erected portion 144a. 3. It has a fourth connecting portion 144b connected to the other end of the connecting portion 147, and a fourth straight portion 144c extending linearly and connecting the fourth standing portion 144a and the fourth connecting portion 144b.
The first bent portion 141 and the third bent portion 143 each have a shape in which a band-shaped member is bent in an S shape. The second bent portion 142 and the fourth bent portion 144 have a shape in which a band-shaped member is bent in the opposite directions to the first bent portion 141 and the third bent portion 143, respectively.
　第１連結部１４５及び第２連結部１４６は、自然状態において、第１部分１４ａと同じ方向に延びている。すなわち、本実施の形態では、第１連結部１４５は、自然状態において、第１屈曲部１４１側の端部と第１部分１４ａとの間の最小距離ｄ11が、第３屈曲部１４３側の端部と第１部分１４ａとの間の最小距離ｄ12と略同等である。また、第２連結部１４６は、自然状態において、第２屈曲部１４２側の端部と第１部分１４ａとの間の最小距離ｄ21が、第４屈曲部１４４側の端部と第１部分１４ａとの間の最小距離ｄ22と略同等である。ここでいう「自然状態」とは、重力以外の荷重が加わっていない状態のことをいう。また、「略同等の距離」は、同じ距離と、製造誤差に起因して変動する距離とを含む。 The first connecting portion 145 and the second connecting portion 146 extend in the same direction as the first portion 14a in the natural state. That is, in the present embodiment, in the first connecting portion 145, in the natural state, the minimum distance d 11 between the end portion on the first bent portion 141 side and the first portion 14a is on the third bent portion 143 side. It is substantially equivalent to the minimum distance d 12 between the end and the first portion 14a. Further, in the second connecting portion 146, in a natural state, the minimum distance d 21 between the end portion on the second bent portion 142 side and the first portion 14a is the end portion and the first portion on the fourth bent portion 144 side. It is substantially equivalent to the minimum distance d 22 between 14a. The "natural state" here means a state in which no load other than gravity is applied. Further, the "substantially equivalent distance" includes the same distance and a distance that fluctuates due to a manufacturing error.
　第３連結部１４７は、直線状に延び、フレーム１３に取り付けられてフレーム１３を支持する。第３連結部１４７は、全体がフレーム１３に固着してもよいし、一部がフレーム１３に固着してもよい。 The third connecting portion 147 extends linearly and is attached to the frame 13 to support the frame 13. The entire third connecting portion 147 may be fixed to the frame 13, or a part of the third connecting portion 147 may be fixed to the frame 13.
　ばね部材１４は、例えば、繊維強化プラスチック（Fiber　Reinforced　Plastics：ＦＲＰ）や、金属、樹脂を用いて形成される。ばね部材１４の形状や弾性力等を設計するうえで、ＦＲＰは、金属や樹脂と比して、その設計の自由度が高い。また、ばね部材１４は、一枚の板材からなるものであってもよいし、複数の部材からなるもの、例えば、第１部分１４ａと第２部分１４ｂとを別体としてもよい。第１部分１４ａと第２部分１４ｂとが別体の場合、それぞれが異なる材料で構成されてもよい。ばね部材１４において第１部分１４ａと第２部分１４ｂとが互いに異なる材料からなる場合、例えば、第１部分１４ａが繊維強化プラスチックからなり、第２部分１４ｂがばね鋼からなる。本実施の形態では、第１部分１４ａが、長手方向に沿って延び、該長手方向と直交する方向に貫通するスリットを有する構成を説明するが、当該スリットを有しない構成としてもよい。 The spring member 14 is formed of, for example, fiber reinforced plastic (Fiber Reinforced Plastics: FRP), metal, or resin. In designing the shape, elastic force, etc. of the spring member 14, FRP has a higher degree of freedom in its design than metal or resin. Further, the spring member 14 may be made of one plate material, or may be made of a plurality of members, for example, the first portion 14a and the second portion 14b may be separate bodies. When the first portion 14a and the second portion 14b are separate bodies, they may be made of different materials. When the first portion 14a and the second portion 14b of the spring member 14 are made of different materials, for example, the first portion 14a is made of fiber reinforced plastic and the second portion 14b is made of spring steel. In the present embodiment, the configuration in which the first portion 14a extends along the longitudinal direction and has a slit penetrating in the direction orthogonal to the longitudinal direction will be described, but the configuration may not have the slit.
　ここで、第１支持部１１ａ、１２ａは、それぞればね部材１４の端部を収容して保持する。具体的に、第１支持部１１ａは、第１部分１４ａの一端と、第１屈曲部１４１の第１連結部１４５側と反対側の端部とを保持する。第１支持部１２ａは、第１部分１４ａの他端と、第２屈曲部１４２の第２連結部１４６側と反対側の端部とを保持する。
　また、第２支持部１１ｃ、１２ｃは、孔にばね部材１４を挿通することによって、ばね部材１４の中央部を把持する。なお、ばね部材１４は、第１支持部１１ａ、１２ａに対し挿脱する方向に移動可能である。ここで、ばね部材１４は、ボルトやクリップ等によって第１支持部１１ａ、１２ａに固定し、挿脱される方向への移動を制限してもよい。 Here, the first support portions 11a and 12a respectively accommodate and hold the end portions of the spring member 14. Specifically, the first support portion 11a holds one end of the first portion 14a and the end portion of the first bent portion 141 on the side opposite to the first connecting portion 145 side. The first support portion 12a holds the other end of the first portion 14a and the end portion of the second bent portion 142 on the side opposite to the second connecting portion 146 side.
Further, the second support portions 11c and 12c grip the central portion of the spring member 14 by inserting the spring member 14 into the hole. The spring member 14 can move in the direction of being inserted and removed from the first support portions 11a and 12a. Here, the spring member 14 may be fixed to the first support portions 11a and 12a with bolts, clips, or the like to limit the movement in the direction of insertion / removal.
　続いて、アームに加わる荷重に対するばね部材１４の変形について、図５～図１７を参照して説明する。図５は、本発明の一実施の形態に係る懸架装置におけるばね部材の撓みと荷重との関係を示す図である。ばね部材１４は、図５に示すように、荷重に対して撓みが非線形に変化する。図５では、各アームの車輪接続側の端部（ここでは第１支持部１１ａ、１２ａ）に対してアームを変位させる荷重を加えた際のばね部材１４の撓みを示している。ここで、荷重Ｆ1は、フレーム１３に加わる、車両の無積載状態における車体等の荷重に相当する。荷重Ｆ2は、車両の積載状態においてフレーム１３に加わる最大荷重に相当する。無積載状態とは、完成した車両において、ヒトが乗車しておらず、かつ積載物を積んでいない状態をさす。また、積載状態とは、ヒトが乗車したり、積載物を積んだりしている状態をさす。この積載状態において、車両に加わる荷重が最大の状態の荷重（車両を使用するうえで許可される最大の荷重）が最大荷重となる。 Subsequently, the deformation of the spring member 14 with respect to the load applied to the arm will be described with reference to FIGS. 5 to 17. FIG. 5 is a diagram showing the relationship between the deflection of the spring member and the load in the suspension device according to the embodiment of the present invention. As shown in FIG. 5, the spring member 14 flexes non-linearly with respect to the load. FIG. 5 shows the deflection of the spring member 14 when a load that displaces the arm is applied to the end portions (here, the first support portions 11a and 12a) on the wheel connection side of each arm. Here, the load F 1 corresponds to the load applied to the frame 13 such as the vehicle body in the unloaded state of the vehicle. The load F 2 corresponds to the maximum load applied to the frame 13 when the vehicle is loaded. The unloaded state refers to a state in which no human is on board and no load is loaded in the completed vehicle. In addition, the loaded state refers to a state in which a person is on board or loaded with a load. In this loaded state, the load in which the load applied to the vehicle is the maximum (the maximum load allowed for using the vehicle) is the maximum load.
　ばね部材１４は、図５に示す関係において、荷重の変化に対して撓みの変化が大きい第１高ばね定数領域Ｒ11、第２高ばね定数領域Ｒ12と、荷重の変化に対して撓みの変化が小さい低ばね定数領域Ｒ20とを有する。図５に示す関係では、荷重が０、撓みが０の状態から第１高ばね定数領域Ｒ11で遷移し、荷重Ｆ1を境界として低ばね定数領域Ｒ20に変化する。その後、荷重が大きくなるにしたがってばね定数が高くなり、荷重Ｆ2に到達する前に、第２高ばね定数領域Ｒ12に変化する。このように、ばね部材１４は、撓みと荷重との関係について、全体として、非線形なばね特性を有している。 In the relationship shown in FIG. 5, the spring member 14 has a first high spring constant region R 11 and a second high spring constant region R 12 in which the change in deflection is large with respect to a change in load, and the spring member 14 has a deflection with respect to a change in load. It has a low spring constant region R 20 with a small change. In the relationship shown in FIG. 5, the transition occurs in the first high spring constant region R 11 from the state where the load is 0 and the deflection is 0, and changes to the low spring constant region R 20 with the load F 1 as a boundary. After that, as the load increases, the spring constant increases, and before the load F 2 is reached, the spring constant changes to the second high spring constant region R 12. As described above, the spring member 14 has a non-linear spring characteristic as a whole regarding the relationship between the deflection and the load.
　なお、ばね部材１４では、ばね部材１４全体として非線形のばね特性（図５参照）を示す一方、第１部分１４ａのみでは、線形のばね特性を示す。図６は、本発明の一実施の形態に係る懸架装置の、ばね部材の第１部分における撓みと荷重との関係を示す図である。図６に示すように、第１部分１４ａのみでは、撓みと荷重との関係が線形のばね特性を有している。このため、ばね部材１４では、第１部分１４ａに対して第２部分１４ｂが付加されることによって、撓みと荷重との関係について非線形なばね特性が付与される。 The spring member 14 exhibits a non-linear spring characteristic (see FIG. 5) as a whole, while the first portion 14a alone exhibits a linear spring characteristic. FIG. 6 is a diagram showing the relationship between the deflection and the load in the first portion of the spring member of the suspension device according to the embodiment of the present invention. As shown in FIG. 6, only in the first portion 14a, the relationship between the deflection and the load has a linear spring characteristic. Therefore, in the spring member 14, the addition of the second portion 14b to the first portion 14a imparts a non-linear spring characteristic with respect to the relationship between the deflection and the load.
　図５に戻り、ばね部材１４の挙動について説明する。図５において、点Ｐ1は、車体等がフレーム１３に取り付けられておらず、ばね部材１４が撓んでいない状態に対応する点である。点Ｐ2は、無積載状態における荷重と、その際の撓みに対応する点であって、第１高ばね定数領域Ｒ11から低ばね定数領域Ｒ20に変化する点である。点Ｐ3は、低ばね定数領域Ｒ20における荷重と、その際の撓みに対応する点である。点Ｐ4は、積載状態における荷重と、その際の撓みに対応する点であって、低ばね定数領域Ｒ20から第２高ばね定数領域Ｒ12に変化する点である。点Ｐ5は、第２高ばね定数領域Ｒ12における荷重と、その際の撓みに対応する点であって、荷重Ｆ2における撓みを示す点である。 Returning to FIG. 5, the behavior of the spring member 14 will be described. In FIG. 5, the point P 1 corresponds to a state in which the vehicle body or the like is not attached to the frame 13 and the spring member 14 is not bent. The point P 2 is a point corresponding to the load in the unloaded state and the bending at that time, and is a point where the first high spring constant region R 11 changes to the low spring constant region R 20. Point P 3 is a point corresponding to the load in the low spring constant region R 20 and the bending at that time. Point P 4 is a point corresponding to the load in the loaded state and the bending at that time, and is a point where the low spring constant region R 20 changes to the second high spring constant region R 12. The point P 5 corresponds to the load in the second high spring constant region R 12 and the bending at that time, and is a point indicating the bending in the load F 2.
　図７は、図５に示す点Ｐ1における懸架装置の状態を示す図である。図８は、図７に示すばね部材の変形部分を拡大した図である。ばね部材１４が撓んでいない点Ｐ1の状態において、ばね部材１４には撓みによる力は加わらない。 Figure 7 is a diagram showing a state of the suspension system in the point P 1 shown in FIG. FIG. 8 is an enlarged view of the deformed portion of the spring member shown in FIG. 7. In the state of point P 1 the spring member 14 is not deflected, no forces applied by bending the spring member 14.
　ばね部材１４にさらに荷重が加わって第１高ばね定数領域Ｒ11から低ばね定数領域Ｒ20に変化する状態において、ばね部材１４の第２屈曲部１４２及び第４屈曲部１４４は、ばね部材１４の長手方向（例えば、第１部分１４ａの延伸方向）にずれる座屈現象が起こり、この座屈現象によってばね定数が低下する。 In a state where a load is further applied to the spring member 14 to change from the first high spring constant region R 11 to the low spring constant region R 20 , the second bent portion 142 and the fourth bent portion 144 of the spring member 14 are the spring member 14. A buckling phenomenon occurs in which the spring constant deviates in the longitudinal direction (for example, the stretching direction of the first portion 14a), and the spring constant decreases due to this buckling phenomenon.
　また、懸架装置１では、ばね部材１４の作用によって、例えば車体が傾斜（ロール）して、一方の車輪が上方側（車体側）に、他方の車輪がその反対側（ここではＺ方向の反対側）に変位したときに、ばね部材１４が変形したり、元の形状に戻ろうとしたりすることによって、車体の傾き（ロール角）を抑制する。 Further, in the suspension device 1, for example, the vehicle body is tilted (rolled) by the action of the spring member 14, and one wheel is on the upper side (vehicle body side) and the other wheel is on the opposite side (here, the opposite in the Z direction). When the spring member 14 is displaced to the side), the spring member 14 is deformed or tries to return to the original shape, thereby suppressing the inclination (roll angle) of the vehicle body.
　図９は、本発明の一実施の形態に係る懸架装置の右側アーム（右アーム１１）への荷重の負荷による、右側アームの変位量（入力）に対する左側アーム（左アーム１２）の変位量（出力）を示す図である。図９に示すように、右アーム１１への荷重の入力によって右アーム１１が変位すると、ばね部材１４の作用によって、左アーム１２も変位する。この際、右アーム１１の変位量とほぼ同等の変位量で左アーム１２が変位するため、上述した傾きの抑制効果が得られる。 FIG. 9 shows the displacement amount (left arm 12) of the left arm (left arm 12) with respect to the displacement amount (input) of the right arm due to the load applied to the right arm (right arm 11) of the suspension device according to the embodiment of the present invention. It is a figure which shows output). As shown in FIG. 9, when the right arm 11 is displaced by the input of the load to the right arm 11, the left arm 12 is also displaced by the action of the spring member 14. At this time, since the left arm 12 is displaced by a displacement amount substantially equal to the displacement amount of the right arm 11, the above-mentioned tilt suppressing effect can be obtained.
　以上説明した実施の形態では、アーム（右アーム１１及び左アーム１２）とフレーム１３との間に介在するばね部材１４が、帯状に延びる第１部分１４ａによってアーム同士を接続するとともに、第１部分１４ａから立ち上がって延在する第２部分１４ｂがフレーム１３を支持する。第２部分１４ｂは、荷重に対する撓みが非線形に変化し、車両の無積載状態では高ばね定数を示し、無積載状態から積載状態に遷移する荷重が加わる場合には低ばね定数を示し、その後、積載状態において最大荷重に近い荷重では再び高ばね定数を示す。ばね部材１４は、無積載状態や積載状態の高荷重負荷時において、荷重に対するストローク（撓み）が低減される。このように、第２部分１４ｂが荷重に対して非線形なばね定数を示すことによって、車両における良好な乗り心地と、車両の部材の自重が加わるまでのばね部材の撓みの低減とを両立することができる。また、第１部分１４ａは、一方のアームの変位に応じて他方のアームを変位させることによって、車体の傾きを抑制することができる。 In the embodiment described above, the spring member 14 interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first portion. A second portion 14b that rises from 14a and extends extends to support the frame 13. The second portion 14b shows a non-loading deflection, a high spring constant when the vehicle is unloaded, a low spring constant when a load transitioning from the unloaded state to the loaded state is applied, and then. In the loaded state, a load close to the maximum load shows a high spring constant again. The spring member 14 has a reduced stroke (deflection) with respect to a load when a heavy load is applied in the unloaded state or the loaded state. In this way, by showing the spring constant that the second portion 14b is non-linear with respect to the load, it is possible to achieve both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied. Can be done. Further, the first portion 14a can suppress the inclination of the vehicle body by displacing the other arm according to the displacement of one arm.
（実施の形態の変形例１）
　図１０は、本発明の実施の形態の変形例１に係る懸架装置の要部の構成を模式的に示す斜視図である。本変形例１では、ばね部材における第１連結部及び第２連結部の延伸方向が、実施の形態に係る第１連結部１４５及び第２連結部１４６の延伸方向と異なる。本変形例１では、第１及び第２連結部の構成以外は、上述した実施の形態の構成と同じである。以下、第１及び第２連結部の構成について説明する。 (Modification 1 of the embodiment)
FIG. 10 is a perspective view schematically showing the configuration of a main part of the suspension device according to the first modification of the embodiment of the present invention. In the first modification, the stretching directions of the first connecting portion and the second connecting portion of the spring member are different from the stretching directions of the first connecting portion 145 and the second connecting portion 146 according to the embodiment. In the first modification, the configuration is the same as that of the above-described embodiment except for the configuration of the first and second connecting portions. Hereinafter, the configurations of the first and second connecting portions will be described.
　図１０に示すばね部材１４Ａは、帯状をなして延びる第１部分１４ａと、第１部分１４ａから立ち上がって延在する第２部分１４ｃとを有する。
　第２部分１４ｃは、第１部分１４ａに対し、凸状をなして立ち上がってなる。具体的に、第２部分１４ｃは、第１屈曲部１４１、第２屈曲部１４２、第３屈曲部１４３、第４屈曲部１４４及び第３連結部１４７と、直線状に延び、一端が第１屈曲部１４１に連なり、他端が第３屈曲部１４３に連なる第１連結部１４８と、直線状に延び、一端が第２屈曲部１４２に連なり、他端が第４屈曲部１４４に連なる第２連結部１４９とを有する。 The spring member 14A shown in FIG. 10 has a first portion 14a extending in a band shape and a second portion 14c rising from the first portion 14a and extending.
The second portion 14c stands up in a convex shape with respect to the first portion 14a. Specifically, the second portion 14c extends linearly with the first bent portion 141, the second bent portion 142, the third bent portion 143, the fourth bent portion 144, and the third connecting portion 147, and one end thereof is the first. A second connecting portion 148 that is connected to the bent portion 141 and the other end is connected to the third bent portion 143, and a second that extends linearly, one end is connected to the second bent portion 142, and the other end is connected to the fourth bent portion 144. It has a connecting portion 149 and.
　第１連結部１４８は、自然状態において、第１屈曲部１４１側の端部と第１部分１４ａとの間の最小距離ｄ13が、第３屈曲部１４３側の端部と第１部分１４ａとの間の最小距離ｄ14より小さい。
　第２連結部１４９は、自然状態において、第２屈曲部１４２側の端部と第１部分１４ａとの間の最小距離ｄ23が、第４屈曲部１４４側の端部と第１部分１４ａとの間の最小距離ｄ24より小さい。 In the first connecting portion 148, in a natural state, the minimum distance d 13 between the end portion on the first bent portion 141 side and the first portion 14a is set to the end portion on the third bent portion 143 side and the first portion 14a. Less than the minimum distance d 14 between.
In the second connecting portion 149, in a natural state, the minimum distance d 23 between the end portion on the second bent portion 142 side and the first portion 14a is set to the end portion on the fourth bent portion 144 side and the first portion 14a. Less than the minimum distance d 24 between.
　以上説明した変形例１においても、アーム（右アーム１１及び左アーム１２）とフレーム１３との間に介在するばね部材１４Ａが、帯状に延びる第１部分１４ａによってアーム同士を接続するとともに、第１部分１４ａから立ち上がって延在する第２部分１４ｃがフレーム１３を支持する。第２部分１４ｃは、荷重に対する撓みが非線形に変化し、車両の無積載状態には高ばね定数を示し、無積載状態から積載状態に遷移する荷重から低ばね定数を示し、その後、積載状態において最大荷重に近い荷重では再び高ばね定数を示す。このように、第２部分１４ｃが荷重に対して非線形なばね定数を示すことによって、車両における良好な乗り心地と、車両の部材の自重が加わるまでのばね部材の撓みの低減とを両立することができる。 Also in the modification 1 described above, the spring member 14A interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first A second portion 14c rising from and extending from the portion 14a supports the frame 13. The second portion 14c shows a non-linear variation in deflection with respect to the load, exhibits a high spring constant in the unloaded state of the vehicle, a low spring constant from the load transitioning from the unloaded state to the loaded state, and then in the loaded state. A load close to the maximum load shows a high spring constant again. In this way, by showing the spring constant that the second portion 14c is non-linear with respect to the load, it is possible to achieve both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied. Can be done.
（実施の形態の変形例２）
　図１１は、本発明の実施の形態の変形例２に係る懸架装置の要部の構成を模式的に示す斜視図である。本変形例２に係るばね部材は、実施の形態に係る第３屈曲部１４３及び第４屈曲部１４４に相当する構成要素を有しない構成である。 (Modification 2 of the embodiment)
FIG. 11 is a perspective view schematically showing the configuration of a main part of the suspension device according to the second modification of the embodiment of the present invention. The spring member according to the second modification has a configuration that does not have a component corresponding to the third bent portion 143 and the fourth bent portion 144 according to the embodiment.
　図１１に示すばね部材１４Ｂは、帯状をなして延びる第１部分１４ａと、第１部分１４ａから立ち上がって延在する第２部分１４ｄとを有する。
　第２部分１４ｄは、第１部分１４ａに対し、立ち上がってなる。第２部分１４ｄは、第１部分１４ａからそれぞれ立ち上がって延在する第１屈曲部１４１Ａ及び第２屈曲部１４２Ａと、第１屈曲部１４１Ａと第２屈曲部１４２Ａとを連結する連結部１５０とを有する。 The spring member 14B shown in FIG. 11 has a first portion 14a extending in a band shape and a second portion 14d rising from the first portion 14a and extending.
The second portion 14d stands up with respect to the first portion 14a. The second portion 14d includes a first bent portion 141A and a second bent portion 142A that rise and extend from the first portion 14a, respectively, and a connecting portion 150 that connects the first bent portion 141A and the second bent portion 142A. Have.
　第１屈曲部１４１Ａは、第１部分１４ａから立ち上がって延びる第１立設部１４１ｄと、第１立設部１４１ｄに連なり、該第１立設部１４１ｄの屈曲態様とは逆の態様で屈曲して連結部１５０の一端に接続する第１接続部１４１ｅとを有する。すなわち、第１屈曲部１４１Ａは、上述した第１屈曲部１４１の第１直線部１４１ｃを有しない構成に相当する。 The first bent portion 141A is connected to the first standing portion 141d extending from the first portion 14a and extending from the first standing portion 141d, and is bent in a mode opposite to the bending mode of the first standing portion 141d. It has a first connecting portion 141e connected to one end of the connecting portion 150. That is, the first bent portion 141A corresponds to a configuration that does not have the first straight portion 141c of the first bent portion 141 described above.
　第２屈曲部１４２Ａは、第１部分１４ａから立ち上がって延びる第２立設部１４２ｄと、第２立設部１４２ｄに連なり、該第２立設部１４２ｄの屈曲態様とは逆の態様で屈曲して連結部１５０の他端に接続する第２接続部１４２ｅとを有する。すなわち、第２屈曲部１４２Ａは、上述した第２屈曲部１４２の第２直線部１４２ｃを有しない構成に相当する。 The second bent portion 142A is connected to the second standing portion 142d extending from the first portion 14a and extending from the first portion 14a, and is bent in a mode opposite to the bending mode of the second standing portion 142d. It has a second connecting portion 142e connected to the other end of the connecting portion 150. That is, the second bent portion 142A corresponds to a configuration that does not have the second straight portion 142c of the second bent portion 142 described above.
　連結部１５０は、フレーム１３（図１参照）に取り付けられてフレーム１３を支持する。連結部１５０は、全体がフレーム１３に固着してもよいし、一部がフレーム１３に固着してもよい。 The connecting portion 150 is attached to the frame 13 (see FIG. 1) to support the frame 13. The entire connecting portion 150 may be fixed to the frame 13, or a part of the connecting portion 150 may be fixed to the frame 13.
　ばね部材１４Ｂは、ばね部材１４と同様に、荷重に対する第１屈曲部１４１Ａ及び第２屈曲部１４２Ａの変形（例えば座屈）によって、荷重と撓みとの関係について非線形なばね特性を有する。 Like the spring member 14, the spring member 14B has a non-linear spring characteristic regarding the relationship between the load and the deflection due to the deformation (for example, buckling) of the first bending portion 141A and the second bending portion 142A with respect to the load.
　以上説明した変形例２においても、アーム（右アーム１１及び左アーム１２）とフレーム１３との間に介在するばね部材１４Ｂが、帯状に延びる第１部分１４ａによってアーム同士を接続するとともに、第１部分１４ａから立ち上がって延在する第２部分１４ｄがフレーム１３を支持する。第２部分１４ｄは、第２部分１４ｂと同様に、荷重に対する撓みが非線形に変化し、車両の無積載状態には高ばね定数を示し、無積載状態から積載状態に遷移する荷重から低ばね定数を示し、その後、積載状態において最大荷重に近い荷重では再び高ばね定数を示す。このように、第２部分１４ｄが荷重に対して非線形なばね定数を示すことによって、車両における良好な乗り心地と、車両の部材の自重が加わるまでのばね部材の撓みの低減とを両立することができる。 Also in the second modification described above, the spring member 14B interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first A second portion 14d rising from and extending from the portion 14a supports the frame 13. Similar to the second portion 14b, the second portion 14d shows a high spring constant in the unloaded state of the vehicle, and the low spring constant from the load transitioning from the unloaded state to the loaded state. After that, the high spring constant is shown again at a load close to the maximum load in the loaded state. In this way, by showing the spring constant that the second portion 14d is non-linear with respect to the load, it is possible to achieve both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied. Can be done.
（実施の形態の変形例３）
　図１２は、本発明の実施の形態の変形例３に係る懸架装置の要部の構成を模式的に示す斜視図である。本変形例３に係るばね部材は、実施の形態に係る第３屈曲部１４３、第４屈曲部１４４及び第３連結部１４７に相当する構成要素を有しない構成である。 (Modification 3 of the embodiment)
FIG. 12 is a perspective view schematically showing the configuration of a main part of the suspension device according to the third modification of the embodiment of the present invention. The spring member according to the third modification has a configuration that does not have components corresponding to the third bent portion 143, the fourth bent portion 144, and the third connecting portion 147 according to the embodiment.
　図１２に示すばね部材１４Ｃは、帯状をなして延びる第１部分１４ａと、第１部分１４ａから立ち上がって延在する第２部分１４ｅとを有する。
　第２部分１４ｅは、第１部分１４ａに対し、立ち上がってなる。第２部分１４ｅは、第１部分１４ａからそれぞれ立ち上がって延在する第１屈曲部１４１Ａ及び第２屈曲部１４２Ａと、第１屈曲部１４１Ａ及び第２屈曲部１４２Ａに対し、第１部分１４ａ側と反対側（フレーム１３側）にそれぞれ設けられ、各々がフレーム１３を支持する第１フレーム支持部１５１及び第２フレーム支持部１５２と、第１屈曲部１４１Ａと第１フレーム支持部１５１とを連結する第１連結部１５３と、第２屈曲部１４２Ａと第２フレーム支持部１５２とを連結する第２連結部１５４とを有する。すなわち、ばね部材１４Ｃは、上述したばね部材１４Ｂの連結部１５０の一部を取り除いた構成に相当する。 The spring member 14C shown in FIG. 12 has a first portion 14a extending in a band shape and a second portion 14e rising from the first portion 14a and extending.
The second portion 14e stands up with respect to the first portion 14a. The second portion 14e is on the side of the first portion 14a with respect to the first bent portion 141A and the second bent portion 142A extending from the first portion 14a, respectively, and the first bent portion 141A and the second bent portion 142A. The first frame support portion 151 and the second frame support portion 152, which are provided on opposite sides (frame 13 side) and each support the frame 13, and the first bent portion 141A and the first frame support portion 151 are connected to each other. It has a first connecting portion 153 and a second connecting portion 154 that connects the second bent portion 142A and the second frame supporting portion 152. That is, the spring member 14C corresponds to a configuration in which a part of the connecting portion 150 of the spring member 14B described above is removed.
　ばね部材１４Ｃは、ばね部材１４と同様に、荷重に対する第１屈曲部１４１Ａ及び第２屈曲部１４２Ａの変形（例えば座屈）によって、荷重と撓みとの関係について非線形なばね特性を有する。 Like the spring member 14, the spring member 14C has a non-linear spring characteristic regarding the relationship between the load and the deflection due to the deformation (for example, buckling) of the first bending portion 141A and the second bending portion 142A with respect to the load.
　以上説明した変形例３においても、アーム（右アーム１１及び左アーム１２）とフレーム１３との間に介在するばね部材１４Ｃが、帯状に延びる第１部分１４ａによってアーム同士を接続するとともに、第１部分１４ａから立ち上がって延在する第２部分１４ｅがフレーム１３を支持する。第２部分１４ｅは、荷重に対する撓みが非線形に変化し、車両の無積載状態には高ばね定数を示し、無積載状態から積載状態に遷移する荷重から低ばね定数を示し、その後、積載状態において最大荷重に近い荷重では再び高ばね定数を示す。このように、第２部分１４ｅが荷重に対して非線形なばね定数を示すことによって、車両における良好な乗り心地と、車両の部材の自重が加わるまでのばね部材の撓みの低減とを両立することができる。 Also in the modified example 3 described above, the spring member 14C interposed between the arms (right arm 11 and left arm 12) and the frame 13 connects the arms to each other by the first portion 14a extending in a band shape, and the first A second portion 14e rising from and extending from the portion 14a supports the frame 13. The second portion 14e shows a non-linear change in deflection with respect to the load, shows a high spring constant in the unloaded state of the vehicle, shows a low spring constant from the load transitioning from the unloaded state to the loaded state, and then in the loaded state. A load close to the maximum load shows a high spring constant again. In this way, by showing the spring constant that the second portion 14e is non-linear with respect to the load, it is possible to achieve both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied. Can be done.
　また、変形例２、３では、第１屈曲部１４１及び第２屈曲部の各直線部（第１直線部１４１ｃ及び第２直線部１４２ｃ）、並びに、第３屈曲部１４３及び第４屈曲部１４４を有しない構成のため、ばね部材を小型化することができる。これにより、懸架装置として車両に設けられた際に、低床化することが可能となる。 Further, in the modified examples 2 and 3, each straight portion (first straight portion 141c and second straight portion 142c) of the first bent portion 141 and the second bent portion, and the third bent portion 143 and the fourth bent portion 144. Since the structure does not have the above, the spring member can be miniaturized. This makes it possible to lower the floor when the vehicle is provided as a suspension device.
　ここまで、本発明を実施するための形態を説明してきたが、本発明は上述した実施の形態によってのみ限定されるべきものではない。このように、本発明はここでは記載していない様々な実施の形態等を含みうるものであり、請求の範囲により特定される技術的思想を逸脱しない範囲内において種々の設計変更等を施すことが可能である。 Although the embodiments for carrying out the present invention have been described so far, the present invention should not be limited only to the above-described embodiments. As described above, the present invention may include various embodiments not described here, and various design changes and the like may be made without departing from the technical idea specified by the claims. Is possible.
　なお、上述した実施の形態において、アームのばね部材と接触する部分にゴム等の緩衝部材を配設し、該緩衝部材を介してばね部材を支持するようにしてもよい。 In the above-described embodiment, a cushioning member such as rubber may be provided at a portion of the arm in contact with the spring member, and the spring member may be supported via the cushioning member.
　また、上述した実施の形態において、第２支持部１１ｃ、１２ｃによるばね部材の支持箇所は、上述した位置に限らない。例えば、ばね部材１４のさらに中央寄りの位置を支持してもよいし、第１支持部１１ａ、１２ａ側の位置を支持してもよい。 Further, in the above-described embodiment, the support points of the spring member by the second support portions 11c and 12c are not limited to the above-mentioned positions. For example, the position of the spring member 14 closer to the center may be supported, or the positions of the first support portions 11a and 12a may be supported.
　また、上述した実施の形態において、ばね部材１４は、第１支持部１１ａ、１２ａに保持される構成に限らず、例えば、アームに接続するリンクやナックルに保持される構成であってもよい。 Further, in the above-described embodiment, the spring member 14 is not limited to the configuration held by the first support portions 11a and 12a, and may be held by, for example, a link or a knuckle connected to the arm.
　また、上述した実施の形態において、第１連結部１４５、１４８及び第２連結部１４６、１４９は、弧状や波状をなして延びる構成としてもよい。 Further, in the above-described embodiment, the first connecting portion 145, 148 and the second connecting portion 146, 149 may be configured to extend in an arc shape or a wavy shape.
　また、上述した実施の形態において、ばね部材１４、１４Ａは、第３連結部１４７を有しない構成であってもよい。この構成の場合、第３屈曲部１４３及び第４屈曲部１４４が、それぞれフレーム１３を支持する。 Further, in the above-described embodiment, the spring members 14 and 14A may have a configuration that does not have the third connecting portion 147. In the case of this configuration, the third bent portion 143 and the fourth bent portion 144 each support the frame 13.
　また、上述した実施の形態において、ばね部材１４、１４Ａは、変形例２、３のように、各屈曲部が直線部（例えば、第１屈曲部１４１の第１直線部１４１ｃ）を有しない構成としてもよい。 Further, in the above-described embodiment, the spring members 14 and 14A have a configuration in which each bent portion does not have a straight portion (for example, the first straight portion 141c of the first bent portion 141) as in the modified examples 2 and 3. May be.
　また、上述した実施の形態に係る懸架装置は、コイルばねを用いた懸架装置等の他の懸架装置と組み合わせて車両に設けてもよい。 Further, the suspension device according to the above-described embodiment may be provided in the vehicle in combination with another suspension device such as a suspension device using a coil spring.
　以上説明したように、本発明に係る懸架装置及びばね部材は、車両における良好な乗り心地と、車両の部材の自重が加わるまでのばね部材の撓みの低減とを両立するのに好適である。 As described above, the suspension device and the spring member according to the present invention are suitable for achieving both good riding comfort in the vehicle and reduction of bending of the spring member until the weight of the vehicle member is applied.
　１　懸架装置
　１１　右アーム
　１２　左アーム
　１３　フレーム
　１４、１４Ａ～１４Ｃ　ばね部材
　１４ａ　第１部分
　１４ｂ～１４ｅ　第２部分
　１５、１６　軸部
　１４１、１４１Ａ　第１屈曲部
　１４２、１４２Ａ　第２屈曲部
　１４３　第３屈曲部
　１４４　第４屈曲部
　１４５、１４８、１５３　第１連結部
　１４６、１４９、１５４　第２連結部
　１４７　第３連結部
　１５０　連結部
　１５１　第１フレーム支持部
　１５２　第２フレーム支持部 1 Suspension device 11 Right arm 12 Left arm 13 Frame 14, 14A-14C Spring member 14a 1st part 14b-14e 2nd part 15, 16 Shafts 141, 141A 1st bending 142, 142A 2nd bending 143 3rd Bending part 144 4th bending part 145, 148, 153 1st connecting part 146, 149, 154 2nd connecting part 147 3rd connecting part 150 Connecting part 151 1st frame support part 152 2nd frame supporting part

Claims (9)

  1. 　荷重と撓みとの関係が線形のばね特性を示す帯状の第１部分と、
    　前記第１部分に対して立ち上がって延在する第２部分と、
    　を備え、
    　非線形のばね特性を示す、
    　ことを特徴とするばね部材。     A band-shaped first part in which the relationship between load and deflection shows linear spring characteristics,
    The second part, which stands up and extends with respect to the first part,
    With
    Shows non-linear spring characteristics,
    A spring member characterized by that.
  2. 　前記第２部分は、
    　前記第１部分からそれぞれ立ち上がって延在する第１及び第２屈曲部、
    　を有し、
    　前記第１屈曲部は、前記第１部分の一端から他端に向かって延びた後、前記第１部分に対して立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲し、
    　前記第２屈曲部は、前記第１部分の他端から一端に向かって延びた後、前記第１部分に対して立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する、
    　ことを特徴とする請求項１に記載のばね部材。     The second part is
    The first and second bent portions, which rise and extend from the first portion, respectively.
    Have,
    The first bent portion extends from one end to the other end of the first portion, then stands up and extends with respect to the first portion, and then bends in a mode opposite to the rising bending mode. ,
    The second bent portion extends from the other end of the first portion toward one end, then stands up and extends with respect to the first portion, and then bends in a mode opposite to the rising bending mode. ,
    The spring member according to claim 1, wherein the spring member.
  3. 　前記第２部分は、
    　前記第１及び第２屈曲部に対して前記第１部分側と反対側にそれぞれ設けられる第３及び第４屈曲部と、
    　前記第１屈曲部と前記第３屈曲部とを連結する第１連結部と、
    　前記第２屈曲部と前記第４屈曲部とを連結する第２連結部と、
    　をさらに有し、
    　前記第３屈曲部は、前記第１連結部との連結部分から立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲し、
    　前記第４屈曲部は、前記第２連結部との連結部分から立ち上がって延在し、その後、立ち上がりの屈曲態様とは逆の態様で屈曲する、
    　ことを特徴とする請求項２に記載のばね部材。     The second part is
    The third and fourth bent portions provided on the sides opposite to the first portion side with respect to the first and second bent portions, respectively.
    A first connecting portion that connects the first bent portion and the third bent portion,
    A second connecting portion that connects the second bent portion and the fourth bent portion,
    Have more
    The third bent portion rises from the connecting portion with the first connecting portion and extends, and then bends in a mode opposite to the rising bending mode.
    The fourth bent portion rises from the connecting portion with the second connecting portion and extends, and then bends in a mode opposite to the rising bending mode.
    The spring member according to claim 2, wherein the spring member.
  4. 　前記第２部分は、
    　前記第３屈曲部と前記第４屈曲部とを連結する第３連結部、
    　をさらに有することを特徴とする請求項３に記載のばね部材。     The second part is
    A third connecting portion that connects the third bent portion and the fourth bent portion,
    The spring member according to claim 3, further comprising.
  5. 　前記第１連結部は、自然状態において、前記第１屈曲部側の端部と前記第１部分との間の最小距離が、前記第３屈曲部と前記第１部分との間の最小距離以下であり、
    　前記第２連結部は、自然状態において、前記第２屈曲部側の端部と前記第１部分との間の最小距離が、前記第４屈曲部と前記第１部分との間の最小距離以下である、
    　ことを特徴とする請求項４に記載のばね部材。     In the natural state of the first connecting portion, the minimum distance between the end portion on the first bent portion side and the first portion is equal to or less than the minimum distance between the third bent portion and the first portion. And
    In the natural state of the second connecting portion, the minimum distance between the end portion on the second bent portion side and the first portion is equal to or less than the minimum distance between the fourth bent portion and the first portion. Is,
    The spring member according to claim 4, wherein the spring member.
  6. 　前記ばね部材は、繊維強化プラスチックからなる、
    　ことを特徴とする請求項１～５のいずれか一つに記載のばね部材。     The spring member is made of fiber reinforced plastic.
    The spring member according to any one of claims 1 to 5, wherein the spring member.
  7. 　前記ばね部材は、前記第１部分と前記第２部分とが互いに異なる材料からなる、
    　ことを特徴とする請求項１～５のいずれか一つに記載のばね部材。     The spring member is made of a material in which the first portion and the second portion are different from each other.
    The spring member according to any one of claims 1 to 5, wherein the spring member.
  8. 　前記ばね部材は、前記第１部分が繊維強化プラスチックからなり、前記第２部分がばね鋼からなる、
    　ことを特徴とする請求項７に記載のばね部材。     The spring member has a first portion made of fiber reinforced plastic and a second portion made of spring steel.
    The spring member according to claim 7, wherein the spring member.
  9. 　第１アームと、
    　第２アームと、
    　一端が前記第１アームの動きに連動して変位し、他端が前記第２アームの動きに連動して変位する、荷重と撓みとの関係が線形のばね特性を示す帯状の第１部分と、前記第１部分に対して立ち上がって延在する第２部分とを有し、非線形のばね特性を示すばね部材と、
    　前記ばね部材の前記第２部分に支持される被支持部材と、
    　を備えることを特徴とする懸架装置。     1st arm and
    With the second arm
    One end is displaced in conjunction with the movement of the first arm, and the other end is displaced in conjunction with the movement of the second arm. The relationship between the load and the deflection is a band-shaped first portion showing linear spring characteristics. A spring member having a second portion that stands up and extends with respect to the first portion and exhibits non-linear spring characteristics.
    A supported member supported by the second portion of the spring member,
    Suspension device characterized by being provided with.
PCT/JP2020/020631 2019-08-27 2020-05-25 Spring member and suspension device WO2021038988A1 (en)

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JP2019-154995 2019-08-27

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01247831A (en) * 1988-03-28 1989-10-03 Mitsubishi Steel Mfg Co Ltd Load transmission mechanism having non-linear load characteristic
JPH04362330A (en) * 1991-06-05 1992-12-15 Nhk Spring Co Ltd Frp-made plate spring
JP2011220476A (en) * 2010-04-13 2011-11-04 Nhk Spring Co Ltd Spring

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01247831A (en) * 1988-03-28 1989-10-03 Mitsubishi Steel Mfg Co Ltd Load transmission mechanism having non-linear load characteristic
JPH04362330A (en) * 1991-06-05 1992-12-15 Nhk Spring Co Ltd Frp-made plate spring
JP2011220476A (en) * 2010-04-13 2011-11-04 Nhk Spring Co Ltd Spring

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