JPS6252171B2 - - Google Patents
Info
- Publication number
- JPS6252171B2 JPS6252171B2 JP7255080A JP7255080A JPS6252171B2 JP S6252171 B2 JPS6252171 B2 JP S6252171B2 JP 7255080 A JP7255080 A JP 7255080A JP 7255080 A JP7255080 A JP 7255080A JP S6252171 B2 JPS6252171 B2 JP S6252171B2
- Authority
- JP
- Japan
- Prior art keywords
- tapered
- plate
- shape
- leaf spring
- stress
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired
Links
- 230000007423 decrease Effects 0.000 claims description 3
- 239000000463 material Substances 0.000 description 3
- 238000005260 corrosion Methods 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Classifications
-
- 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
- F16F1/185—Leaf springs characterised by shape or design of individual leaves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
Description
本発明は板ばねに関するものである。
平鋼を圧延成形したテーパ部を有する板ばねに
おいて、板端荷重に基づく応力が均等分布をなす
ようにテーパ部の輪郭を放物線形状に形成するこ
とは周知である。すなわち、第1図に例示するよ
うに板幅bが一定で断面が矩形状をなし、板端か
らの距離xにおける板厚txが、図示の記号を用
いてtx=√で表わされる板ばねにおいて
は、荷重Pに基づく応力σxは
σx=6Px/btx 2=6Pl/bt2
となり、距離xとは無関係に一定である。
一方、断面が矩形状であると隅部に亀裂が生じ
易いので、幅方向端部を断面が板厚またはこれの
1/2に等しい半径の円弧状となるようなコバ部を
形成することも周知である。
しかしながら、上述のように長手方向に沿う断
面形状が放物線状をなすテーパ部の幅方向端部
を、たとえば板厚txの1/2に等しい半径の円弧状
に形成したのでは応力分布が不均等になつてしま
う。すなわち、第1図Aに示すような板ばねの断
面が第2図に示すように形成され、R=tx/2で
あるとすれば、板端からxの距離における断面係
数Zxが
Zx=(b−tx)tx 2/6+πtx 3/32
と表わされるから、tx=t√の条件下で
は、応力σx=Px/Zxとx=lにおける応力σl
との比α=σx/σlは
となり、b/tおよびx/lをパラメータとして
計算した結果は付表および第3図に示すようにな
る。これら表および図面から知られるように応力
σxは一定ではなく、基部において最大で板端部
に近ずくほど小さくなる。したがつて、材料の使
用効率が低く重量が大となるばかりでなく、この
ような板ばねを自動車用懸架装置等に適用すれば
摩耗、フレツテイング、腐食等の生じ易い基部が
応力最大になるという不具合を伴なう。このよう
な不具合を改善するために、従来は板間にスペー
サを設けたり、防食処理を施したり、あるいは
SSPなどの対策が行なわれているにすぎない。
The present invention relates to a leaf spring. It is well known that in a leaf spring having a tapered part formed by rolling a flat steel, the profile of the tapered part is formed into a parabolic shape so that the stress based on the plate end load is evenly distributed. In other words, as illustrated in Fig. 1, the plate width b is constant, the cross section is rectangular, and the plate thickness t x at the distance x from the plate edge is expressed as t x =√ using the symbol shown in the figure. In the spring, the stress σ x based on the load P is σ x =6Px/bt x 2 =6Pl/bt 2 and is constant regardless of the distance x. On the other hand, if the cross section is rectangular, cracks are likely to occur at the corners, so the cross section at the end in the width direction is
It is also well known to form an edge portion having an arc shape with a radius equal to 1/2. However, if the widthwise end portion of the tapered portion, which has a parabolic cross-sectional shape along the longitudinal direction, is formed into an arc shape with a radius equal to 1/2 of the plate thickness t x as described above, the stress distribution will be insufficient. It becomes even. That is, if the cross section of a leaf spring as shown in FIG . Since x = (b - t x )t x 2 /6 + πt x 3 /32, under the condition of t x = t√, stress σ x = Px /Z
The ratio α=σ x /σ l is The results of calculation using b/t and x/l as parameters are shown in the attached table and FIG. As is known from these tables and drawings, the stress σ x is not constant, and is maximum at the base and becomes smaller as it approaches the edge of the plate. Therefore, not only is the material used inefficiently and the weight is large, but if such a leaf spring is applied to an automobile suspension system, the stress is greatest at the base where wear, fretting, corrosion, etc. are likely to occur. accompanied by defects. In order to improve these problems, conventional methods have been to install spacers between the plates, apply anti-corrosion treatment, or
It's just that countermeasures such as SSP are being taken.
【表】
本発明は上記事情のもとになされたもので、そ
の目的とするところは、幅方向両端にほぼ半円状
のコバ部を有したテーパ板ばねにおいて、テーパ
部の長手方向に均等な応力分布が得られ、一層の
軽量化が可能となる板ばねを提供することにあ
る。
以下、本発明について図面を参照しながら説明
する。第4図において長手方向ほぼ中央部に設け
られた肉厚の基部1と板端部に形設された目玉部
2との間には、目玉部2寄りに設けられた薄肉部
3を介してテーパ部4が設けられている。そして
このテーパ部4の幅方向両端部には半径Rの半円
形状のコバ部が設けられている。そしてこのテー
パ部4の長手方向の形状は、幅方向の断面が矩形
であると仮定してテーパ部の長手方向各部の応力
が均等分布をなすように計算して得た略放物線状
のテーパ形状の板ばね(第1図A参照)に比べ
て、基端側に対する板端部側の肉厚の減少率が大
きくなるようなテーパ形状としてある。換言する
と、テーパ部4は、板端部寄り端部5と基部寄り
端部6との間における長さlの全領域にわたり、
断面係数Zx(以下、サイフイツクスxは板端部
寄り端部5から距離xの位置に対応することを示
す)が距離xにほぼ比例するように板厚txが設
定されており、かつ幅方向両端断面が板厚txに
関連して定められた所定の曲率1/Rを有する弧
状をなすように形成されている。
上述のように構成された板ばねにおいては、基
部1を固定して目玉部2に対し板厚方向の集中荷
重が加えられた場合、板端部寄り端部5における
板厚方向の荷重をPとすれば、距離xにおける応
力σxは
σx=P・x/Zx …(1)
となるが、上述したようにZx=C・x(Cは比
例定数)であるから
σx=P/C …(2)
となり、テーパ部4の全領域において一定であ
る。したがつて材料の有効利用が可能であり、重
量軽減に寄与することができる。また、幅方向両
端断面が弧状をなしているので、断面矩形状の板
ばねにおけるような隅部の亀裂等の発生を防止す
ることができる。
つぎに、上述のように構成された板ばねを圧延
成形する場合に必要な厚さtxと距離xとの関係
について説明する。第4図に例示するようにR=
tx/2の場合には、上述したように
Zx=b−tx/6tx 2+π/32tx 3…(3)
である。テーパ部4の基部寄り端部6における断
面係数をZl、応力をσlとすれば、
Zl=b−t/6t2+π/32t3 …(4)
σl=P・l/Zl …(5)
である。したがつて、σx=σlとなるためには
Zx/Zl=x/l …(6)
が成立すればよいから、
を解くことにより
tx=2/3Acosθ/3+1/3A …(8)
tx=2/3Acos(120゜−θ/3)+1/3A (9)
tx=2/3Acos(120゜+θ/3)+1/3A (10)
ただし、
θ=arc cos{1+27(16−3π)2/8192
・(16−3π)t3−16bt2/b3・x/l
}
が得られ、これら式(8)(9)(10)のいずれかが距離xに
対応する板厚txを与える。
なお、本発明は、上記実施例のみに限定される
ものではない。たとえば幅方向両端断面の曲率と
板厚との関係は必要に応じ適宜に設定可能であ
る。また、第5図に例示するようにテーパ部7の
輪郭を、上記テーパ部4と近似な輪郭を形成する
複数(図は3つの場合)の直線状部分7a,7
b,7c等から形成するようにしてもよく、ある
いはこれら部分7a,7b,7c等の一部を曲線
状としてもよい。さらに、第6図に例示するよう
に複数(図は2つの場合)の板ばね8,9を厚さ
方向に重合して用いるようにしてもよい。その
他、本発明の要旨とするところの範囲内で種々な
変更ないし応用が可能であることはいうまでもな
い。
本発明は、上述したように、テーパ部の幅方向
両端部にほぼ半円状のコバ部を設けるとともに、
このテーパ部の形状は、矩形断面と仮定して計算
されていた従来の放物線状をなす等応力ばねに比
べて、板端側の肉厚の減少率が大きいようなテー
パ形状としたから、いわゆる丸コバ部を有したテ
ーパばねにあつても断面係数が板端側の端部から
の距離にほぼ比例して漸増するようにすることが
できる。従つてテーパ部の長手方向各部における
応力分布が均等化され、材料の使用効率が高く、
軽量化に寄与することができ、かつ幅方向端部に
おける亀裂等の発生を効果的に防止することがで
きる。[Table] The present invention has been made under the above circumstances, and its object is to provide a tapered leaf spring having approximately semicircular edge portions at both ends in the width direction. It is an object of the present invention to provide a leaf spring which can obtain a stress distribution and which can be further reduced in weight. Hereinafter, the present invention will be explained with reference to the drawings. In FIG. 4, a thin wall portion 3 provided near the eyelet portion 2 is provided between the thick base portion 1 provided approximately in the center in the longitudinal direction and the eyelet portion 2 formed at the end of the plate. A tapered portion 4 is provided. Semicircular edge portions with a radius R are provided at both ends of the tapered portion 4 in the width direction. The shape in the longitudinal direction of this tapered part 4 is a substantially parabolic tapered shape calculated so that the stress at each part in the longitudinal direction of the tapered part is evenly distributed, assuming that the cross section in the width direction is rectangular. Compared to the leaf spring (see FIG. 1A), the tapered shape is such that the rate of decrease in wall thickness on the plate end side relative to the base end side is greater. In other words, the tapered portion 4 spans the entire area of length l between the end 5 near the plate end and the end 6 near the base,
The plate thickness t x is set so that the section modulus Z x (hereinafter, sizing x corresponds to the position x from the edge 5 near the plate edge) is approximately proportional to the distance x , and the width The cross section of both ends in the direction is formed in an arc shape having a predetermined curvature of 1/R determined in relation to the plate thickness t x . In the leaf spring configured as described above, when a concentrated load in the plate thickness direction is applied to the center part 2 with the base 1 fixed, the load in the plate thickness direction at the end 5 near the plate end is P. Then, the stress σ x at distance x is σ x = P・x/Z x …(1) However, as mentioned above, since Z x = C・x (C is a constant of proportionality), σ x = P/C (2), which is constant over the entire area of the tapered portion 4. Therefore, materials can be used effectively and weight can be reduced. Furthermore, since the cross-sections at both ends in the width direction are arcuate, it is possible to prevent cracks from occurring at the corners, which occur in leaf springs having a rectangular cross-section. Next, the relationship between the thickness t x and the distance x required when rolling forming the leaf spring configured as described above will be explained. As illustrated in FIG. 4, R=
In the case of t x /2, as described above, Z x =b-t x /6t x 2 +π/32t x 3 (3). If the section modulus at the base-side end 6 of the tapered portion 4 is Z l and the stress is σ l , then Z l =b-t/6t 2 +π/32t 3 ...(4) σ l =P・l/Z l …(5). Therefore, in order for σ x = σ l , it is sufficient that Z x /Z l = x/l (6) holds true, By solving t x = 2/3Acos θ/3 + 1/3A ...(8) t x = 2/3Acos (120° - θ/3) + 1/3A (9) t x = 2/3Acos (120° + θ/3 )+1/3A (10) However, θ=arc cos{1+27(16-3π) 2 /8192 ・(16-3π)t 3 −16bt 2 /b 3・x/l
} is obtained, and one of these equations (8), (9), and (10) gives the plate thickness t x corresponding to the distance x. Note that the present invention is not limited only to the above embodiments. For example, the relationship between the curvature of the cross-sections at both ends in the width direction and the plate thickness can be appropriately set as necessary. In addition, as illustrated in FIG. 5, the outline of the tapered part 7 is divided into a plurality of (in the case of three in the figure) linear parts 7a, 7 that form an outline similar to the taper part 4.
7a, 7c, etc., or a part of these portions 7a, 7b, 7c, etc. may be formed into a curved shape. Furthermore, as illustrated in FIG. 6, a plurality of leaf springs 8 and 9 (in the case of two leaf springs in the figure) may be used by superimposing them in the thickness direction. It goes without saying that various other modifications and applications can be made within the scope of the gist of the present invention. As described above, the present invention provides approximately semicircular edge portions at both ends in the width direction of the tapered portion, and
The shape of this tapered part is so-called because it has a tapered shape that reduces the wall thickness at the plate end side more than the conventional parabolic constant stress spring, which is calculated assuming a rectangular cross section. Even in the case of a tapered spring having a round edge portion, the section modulus can be made to gradually increase approximately in proportion to the distance from the end on the plate end side. Therefore, the stress distribution in each part of the tapered part in the longitudinal direction is equalized, and the material usage efficiency is high.
This can contribute to weight reduction, and can effectively prevent the occurrence of cracks and the like at the ends in the width direction.
第1図Aは従来の板ばねを例示する側面図、第
1図Bは同図AのB−B線に沿う断面図、第2図
は従来の板ばねの他の断面形状を例示する説明
図、第3図は同例における応力分布状態を説明す
るための線図、第4図Aは本発明の一実施例を示
す部分側面図、第4図Bは同図AのB−B線に沿
う断面図、第5図および第6図は本発明の変形例
を示す部分側面図である。
1……基部、2……目玉部、4,7……テーパ
部、5,6……テーパ部の端部。
FIG. 1A is a side view illustrating a conventional leaf spring, FIG. 1B is a cross-sectional view taken along line BB in FIG. Figure 3 is a diagram for explaining the stress distribution state in the same example, Figure 4A is a partial side view showing one embodiment of the present invention, and Figure 4B is a line BB in Figure A. 5 and 6 are partial side views showing modified examples of the present invention. 1... Base portion, 2... Eyepiece portion, 4, 7... Taper portion, 5, 6... End portion of tapered portion.
Claims (1)
テーパ部を有し板端部に厚さ方向の集中荷重が加
えられる板ばねにおいて、上記テーパ部の幅方向
両端部にほぼ半円状のコバ部を設けるとともに、
上記テーパ部の長手方向の形状は、幅方向の断面
が矩形であると仮定してテーパ部の長手方向各部
の応力が均等分布をなすように計算して得た略放
物線状のテーパ形状の板ばねに比べて、基端側に
対する板端部側の肉厚の減少率が大きいようなテ
ーパ形状としたことを特徴とする板ばね。1. In a leaf spring that has a tapered part where the plate width is approximately constant and the plate thickness gradually decreases toward the plate end, and a concentrated load in the thickness direction is applied to the plate end, a substantially semicircular shape is formed at both ends in the width direction of the tapered part. In addition to providing a shaped edge part,
The shape of the tapered part in the longitudinal direction is a substantially parabolic tapered plate obtained by calculating that the stress in each part of the tapered part in the longitudinal direction is evenly distributed, assuming that the cross section in the width direction is rectangular. A leaf spring characterized by having a tapered shape such that the rate of decrease in wall thickness on the plate end side relative to the base end side is greater than that of the spring.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7255080A JPS56167938A (en) | 1980-05-30 | 1980-05-30 | Leaf spring |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7255080A JPS56167938A (en) | 1980-05-30 | 1980-05-30 | Leaf spring |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS56167938A JPS56167938A (en) | 1981-12-23 |
JPS6252171B2 true JPS6252171B2 (en) | 1987-11-04 |
Family
ID=13492572
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP7255080A Granted JPS56167938A (en) | 1980-05-30 | 1980-05-30 | Leaf spring |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS56167938A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02135507U (en) * | 1989-04-17 | 1990-11-09 |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2087034B (en) * | 1980-01-25 | 1984-06-06 | Ki Inzh Str Inst | Spring and suspension of a vehicle comprising such a spring |
JPS5874926A (en) * | 1981-10-29 | 1983-05-06 | Horikiri Bane Seisakusho:Kk | Tapered leaf spring |
JPS6377676U (en) * | 1986-11-05 | 1988-05-23 | ||
JPH0230543U (en) * | 1988-08-19 | 1990-02-27 | ||
JPH02203024A (en) * | 1989-01-31 | 1990-08-13 | Tochigi Fuji Ind Co Ltd | Clutch cylinder member and viscous coupling |
JP2582291B2 (en) * | 1989-02-03 | 1997-02-19 | いすゞ自動車 株式会社 | Leaf spring |
JPH02110729U (en) * | 1989-02-23 | 1990-09-05 | ||
JPH11218185A (en) * | 1998-02-03 | 1999-08-10 | Kurashiki Kako Co Ltd | Vibration isolating mount |
US20140191486A1 (en) * | 2013-01-10 | 2014-07-10 | Hendrickson Usa, L.L.C. | Multi-tapered suspension component |
JP2015121262A (en) * | 2013-12-24 | 2015-07-02 | 中央発條株式会社 | Suspension spring and method of manufacturing suspension spring |
MA43577A (en) * | 2016-01-04 | 2018-11-14 | Fundiciones De Vera S A | PROCESS FOR MANUFACTURING PROFILES FOR BLADE SPRINGS |
AT520123B1 (en) * | 2017-06-23 | 2023-07-15 | Hendrickson Comm Vehicle Sys Europe Gmbh | Spring leaf for a leaf spring |
-
1980
- 1980-05-30 JP JP7255080A patent/JPS56167938A/en active Granted
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02135507U (en) * | 1989-04-17 | 1990-11-09 |
Also Published As
Publication number | Publication date |
---|---|
JPS56167938A (en) | 1981-12-23 |
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