JPS5834691B2 - Leaf spring for vehicle suspension - Google Patents
Leaf spring for vehicle suspensionInfo
- Publication number
- JPS5834691B2 JPS5834691B2 JP13626481A JP13626481A JPS5834691B2 JP S5834691 B2 JPS5834691 B2 JP S5834691B2 JP 13626481 A JP13626481 A JP 13626481A JP 13626481 A JP13626481 A JP 13626481A JP S5834691 B2 JPS5834691 B2 JP S5834691B2
- Authority
- JP
- Japan
- Prior art keywords
- leaf spring
- plate
- spring
- thickness
- leaf
- 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
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)
- Vehicle Body Suspensions (AREA)
- Springs (AREA)
Description
【発明の詳細な説明】 本発明は車両懸架用板はねに関する。[Detailed description of the invention] TECHNICAL FIELD The present invention relates to a plate for suspension of a vehicle.
車両懸架用板ばねにおいては応力分布を均等化して重量
軽減を図るため、車両の車輪側および車体側にそれぞれ
連結される中央部および板端部の間に、板端方向に厚さ
が減少するテーパ部を設けたものが知られている。In leaf springs for vehicle suspension, in order to equalize stress distribution and reduce weight, the thickness decreases in the direction of the leaf ends between the central part and the leaf ends, which are connected to the vehicle wheels and body, respectively. A type having a tapered portion is known.
このような板ばねを厚さ方向に複数枚重合してなる重ね
板ばね装置においては、設計応力を高く設定して重合枚
数を減することによりさらに軽量化を推進することがで
きる。In a stacked leaf spring device formed by stacking a plurality of such leaf springs in the thickness direction, weight reduction can be further promoted by setting a high design stress and reducing the number of stacked leaf springs.
しかしながら、たとえば大型トラック等においては通常
3〜4枚の板ばねが用いられており、これをさらに減少
させることは外見上から不安感を招くばかりでなく、板
はね相互間の板間摩擦抵抗が減少するため操縦安定性が
劣化する惧れがあるので、板ばねの枚数を減することに
よる軽量化は回顧である。However, for example, large trucks usually use 3 to 4 leaf springs, and further reducing this number not only creates a sense of uneasiness in appearance, but also creates friction between the leaf springs. There is a risk that the steering stability will deteriorate due to a decrease in the number of leaf springs, so reducing the weight by reducing the number of leaf springs is an afterthought.
また、たとえば1〜2枚の板ばねを有する小型トラック
等においては、応力に余裕があっても枚数をさらに減少
することは困難である。In addition, for example, in a small truck having one or two leaf springs, it is difficult to further reduce the number of leaf springs even if there is sufficient stress.
一方、応力を高く設定すれば板幅を狭くすることによっ
ても軽量化が可能であるが、板ばねの全長にわたって板
幅を狭くすると、車両との連結部における構造をも変更
する必要を生じ、関係部品の種類が増加するため管理に
手数を要し、かつ連結作業も煩雑になるなどの不具合を
伴なう。On the other hand, if the stress is set high, it is possible to reduce the weight by narrowing the plate width, but if the plate width is narrowed over the entire length of the leaf spring, it becomes necessary to change the structure at the connection with the vehicle. This increases the number of types of related parts, which requires a lot of effort to manage, and also causes problems such as complicated connection work.
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、板ばねの枚数や車両との連結構造などの
変更を伴なうことなく軽量化を推進可能な車両懸架用板
ばねを提供することにある。The present invention has been made under the above circumstances, and its purpose is to reduce the weight of a vehicle suspension plate without changing the number of leaf springs or the connection structure with the vehicle. The purpose is to provide a spring.
以下、本発明を図示の一実施例について説明する。Hereinafter, the present invention will be described with reference to an illustrated embodiment.
第1図において板ばね装置1は単数または厚さ方向に重
合された複数(図は3つの場合)の板ばね2・・・を備
えている。In FIG. 1, a leaf spring device 1 includes a single leaf spring or a plurality of leaf springs 2 (in the case of three leaf springs in the figure) stacked in the thickness direction.
板ばね2は長手方中央部3、板端部4,4およびこれら
両部3と4,4との間に位置して板端方向に厚さが減少
するテーパ部5,5を有し、たとえばばね鋼から一体に
形成されている。The leaf spring 2 has a longitudinal center part 3, plate end parts 4, 4, and tapered parts 5, 5 located between these parts 3 and 4, 4 and whose thickness decreases in the direction of the plate ends, For example, it is made in one piece from spring steel.
中央部3・・・はUボルト6.6を介して車両のアクス
ル7に連結されるようになっている。The central portion 3... is connected to the axle 7 of the vehicle via a U-bolt 6.6.
1番目の板ばね2は両端部4,4に一体に形成された目
玉部8,8を備えている。The first leaf spring 2 has eye portions 8, 8 integrally formed on both end portions 4, 4.
これら目玉部8,8の一方はブラケット9を介し、他方
はシャックル10を介してそれぞれ車体11に連結され
るようになっている。One of these eyepiece parts 8, 8 is connected to a vehicle body 11 through a bracket 9, and the other through a shackle 10.
以上の一般的構成は従来装置におけると同様であってよ
い。The above general configuration may be the same as that of the conventional device.
上記板はね2は、第2図A、Bに例示するようにテーパ
部5の板幅b1が中央部3および板端部4の各板幅す。In the plate spring 2, as illustrated in FIGS. 2A and 2B, the plate width b1 of the tapered portion 5 is equal to the width of each of the central portion 3 and the plate end portions 4.
およびb2よりも狭く、かつ全長にわたってほぼ一定と
なるように形成されている。and b2, and is formed to be substantially constant over the entire length.
同図において中央部3の厚さt。In the figure, the thickness of the central portion 3 is t.
に対し板端部4の厚さhおよび、負荷点から距離Xの位
置における厚さtxは、たとえば、
t+ = to (t2 /l>%
tx−to (x/f)%
のように定められている。On the other hand, the thickness h of the plate end 4 and the thickness tx at a distance X from the load point are determined as follows, for example: ing.
また、負荷点からの距離Xが1 、<x<t 2および
L 3<x<L4の領域における板幅bxは、たとえば
bx−b2+(b、−b2Xx4+)/(t2−、ff
+)bX−、g、 +(b2− b+ Xx−ム)/(
ムー23)のようにそれぞれ定められている。Further, the plate width bx in the region where the distance X from the load point is 1, <x<t2 and L3<x<L4 is, for example, bx-b2+(b,-b2Xx4+)/(t2-,ff
+) bX-, g, +(b2- b+ Xx-mu)/(
23).
いま、第3図に示すように固定された基端部の厚さがt
、基端部から自由端までの長さがL、幅がb、自由端部
から距離Xの位置における厚さtxが1x−t (x/
L) 3Aであたえられるテーパはねを考えると、縦弾
性係数をEとすれは、自由端部に厚さ方向の集中荷重P
が作用したときの自由端部におけるたわめδおよび基端
部における応力σは、δ=8PL3/Ebt3
・・・・・・(1)σ−6PL/bt
・・・・・・(2)と表わされる。Now, as shown in Fig. 3, the thickness of the fixed proximal end is t.
, the length from the base end to the free end is L, the width is b, and the thickness tx at a distance X from the free end is 1x-t (x/
L) Considering the taper spring given by 3A, if the longitudinal elastic modulus is E, then the concentrated load P in the thickness direction on the free end
The deflection δ at the free end and the stress σ at the proximal end when
・・・・・・(1) σ-6PL/bt
It is expressed as (2).
また重量Wは、比重をγとしてW−rbt美L(X/L
芦dx=(2/3)γbtu、・・・・・・(3)とな
る。In addition, the weight W is W-rbt beauty L (X/L
Ashi dx=(2/3)γbtu, (3).
したがって、I=bがそれぞれblおよびb2(ただし
b+<b2)、基端部の厚さtがそれぞれt、および1
.(ただしt + > t 2 )ではね定数(P/δ
)が相等しい2つのばねを比較すると、上記記号にサフ
ィックス1および2を付して表わせば、式(1)を用い
、かつδにδ2とおいてbl t+3””b2 t23
・・・・・・(4)が得られる。Therefore, I=b are bl and b2 (where b+<b2), respectively, and the thickness t of the proximal end is t and 1, respectively.
.. (however, t + > t 2 ), the spring constant (P/δ
) are the same, if we add the suffixes 1 and 2 to the above symbols, then using equation (1) and setting δ to δ2, we get bl t+3""b2 t23
...(4) is obtained.
また、式(2)および(3)からσ、/σ2””” b
2 t 22/ b+ t+ 2W、/W2二b+り1
/b2t2
が得られるから、式(4)を用いて
σ、/σ2二t + /l 2 > 1
Wl/W2=t 22/112<1
となることが知られる。Also, from equations (2) and (3), σ, /σ2””” b
2 t 22/ b+ t+ 2W, /W22b+ri1
Since /b2t2 is obtained, it is known that σ, /σ22t + /l 2 > 1 Wl/W2=t 22/112<1 using equation (4).
すなわち、幅がす、< b2で基端部の厚さがt+>t
2である2種類のテーパはねにおいては、基端部の応力
はσ、〉σ2であるが重量はW、<W2となることが知
られる。That is, the width is < b2 and the thickness of the proximal end is t + > t
It is known that in the two types of taper springs No. 2, the stress at the base end is σ, >σ2, but the weight is W, <W2.
第4図に板幅比(b、/b2)に対する重量比(W、/
’W2)、応力比(σ、/σ2)、厚さ比(t+/12
)の関係を示す。Figure 4 shows the weight ratio (W, /b2) to the plate width ratio (b, /b2).
'W2), stress ratio (σ, /σ2), thickness ratio (t+/12
).
また、第2図A、Bにおける各部の寸法を第1表に示す
ように定めた実施例Aと、板幅が一定で中央部の厚さt
。In addition, Example A in which the dimensions of each part in FIGS.
.
が実施例Aより薄い比較例Cと、板幅が一定で実施例A
より中央部の厚さt。Comparative Example C is thinner than Example A, and Example A has a constant plate width.
Thickness t at the center.
が厚くかつ重合枚数nが少ない比較例りとの性能を第2
表に比較して示す。The performance compared to the comparative example, which is thicker and has a smaller number of polymerized sheets n, is compared to the second example.
A comparison is shown in the table.
同表から明らかなように実施例Aは比較例CおよびDに
比しばね定数が同等で、荷重1100kgに対する中央
部における応力σが比較例りに比し約14係小さく、か
つ重量Wは比較例Cに比し約16%軽い。As is clear from the table, Example A has the same spring constant as Comparative Examples C and D, the stress σ at the center against a load of 1100 kg is approximately 14 times smaller than that of the Comparative Example, and the weight W is lower than that of the Comparative Example. Approximately 16% lighter than Example C.
そして、長手方向(X方向)における応力σ分布は第2
図Cに例示するようになる。The stress σ distribution in the longitudinal direction (X direction) is the second
This is illustrated in Figure C.
さらに、各部の寸法(第2図参照)が第3表に示すよう
に定められたメインスプリングMに対し、テーパ部およ
び板端部の板幅す、およびす、が狭く形成されたヘルパ
スプリングH8を付加した実施例Bと、板幅が全長にわ
たって一定なヘルパスプリングH2を付加した比較例E
との特性を第4表に示す。Furthermore, compared to the main spring M whose dimensions of each part (see Fig. 2) are determined as shown in Table 3, the helper spring H8 has a narrower plate width at the tapered part and the plate end. Embodiment B with the addition of , and Comparative example E with the addition of a helper spring H2 with a constant plate width over the entire length.
The characteristics are shown in Table 4.
すなわち、ヘルパスプリングのみについてテーパ部の板
幅を狭くすることにより総重量を約4%(ヘルパスプリ
ングのみでは約14%)軽くすることができる。That is, by narrowing the plate width of the tapered portion of only the helper spring, the total weight can be reduced by about 4% (about 14% for only the helper spring).
なお、本発明は上記実施例のみに限定されるものではな
く、たとえば板ばね装置を構成する板はねの数は必要に
応じて適宜に設定可能であるとともに親子形板ばね装置
等にも適用可能であり、その他、本発明の要旨とすると
ころの範囲内で種々の変更ないし応用が可能である。It should be noted that the present invention is not limited to the above-mentioned embodiments. For example, the number of leaf springs constituting the leaf spring device can be appropriately set as necessary, and the present invention can also be applied to parent-child leaf spring devices. In addition, various modifications and applications are possible within the scope of the gist of the present invention.
本発明は、上述したようにテーパ部の板幅を中央部およ
び板端部の各板幅よりも狭く形成するようにしたので、
板幅が一定なものに比し板ばねの数を減することなく重
量を軽減することができる。In the present invention, as described above, the width of the tapered portion is made narrower than the width of each of the central portion and the edge portion of the plate.
The weight can be reduced without reducing the number of leaf springs compared to those with a constant leaf width.
また、中央部および板端部の板幅を一定に保持したまま
軽量化し得るので車両の車輪側および車体側などとの連
結用部品を標準化することができ、部品の製作および管
理が簡単かつ容易となる。In addition, the weight can be reduced while keeping the width of the center and edge parts constant, making it possible to standardize parts for connection to the vehicle wheels and body, making parts manufacturing and management simple and easy. becomes.
さらに、中央部は板幅を広く設定し得ることから応力が
低くなり、Uボルト等による締付力が弛緩するようなこ
とがあってもセンタボルト孔周縁部における応力増大を
防止したり、フレッティングに起因する折損事故の発生
を抑制し得るなどの効果がある。Furthermore, since the plate width can be set wide in the center, stress is low, and even if the tightening force of U-bolts, etc. is loosened, stress can be prevented from increasing at the periphery of the center bolt hole, and flexing can be prevented. This has the effect of suppressing the occurrence of breakage accidents caused by
第1図は本発明の一実施例を示す側面図、第2図A、B
およびCは同例における板ばね部分の側面図、下面図お
よび応力分布図、第3図AおよびBはテーパばねの側面
および上面を例示する説明図、第4図は同例における板
幅比と重量比、応力比および厚さ比との関係を示す線図
である。
1・・・・・・板ばね装置、2・・・・・・板ばね、3
・・・・・・中央部、4・・・・・・板端部、5・・・
・・・テーパ部、7・・・・・・アクスル、11・・・
・・・車体。Figure 1 is a side view showing one embodiment of the present invention, Figures 2A and B
and C are side views, bottom views, and stress distribution diagrams of the leaf spring portion in the same example, Figures 3A and B are explanatory diagrams illustrating the side and top surfaces of the tapered spring, and Figure 4 is the plate width ratio in the same example. FIG. 3 is a diagram showing the relationship between weight ratio, stress ratio, and thickness ratio. 1... Leaf spring device, 2... Leaf spring, 3
...Central part, 4...Plate end, 5...
...Tapered part, 7...Axle, 11...
...Car body.
Claims (1)
央部および板端部と、これら中央部および板端部の間に
位置して板端方向に厚さが減少するテーパ部とを一体に
有するものにおいて、上記テーパ部の板幅を上記中央部
および板端部の各板幅より狭く形成したことを特徴とす
る車両懸架用板ばね。1. Integrally includes a center portion and plate end portions connected to the vehicle wheel side and vehicle body side, respectively, and a tapered portion located between the center portion and plate end portions and decreasing in thickness in the direction of the plate end. A leaf spring for suspending a vehicle, characterized in that the width of the tapered portion is narrower than the widths of the central portion and the end portions of the plate.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP13626481A JPS5834691B2 (en) | 1981-08-31 | 1981-08-31 | Leaf spring for vehicle suspension |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP13626481A JPS5834691B2 (en) | 1981-08-31 | 1981-08-31 | Leaf spring for vehicle suspension |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5837332A JPS5837332A (en) | 1983-03-04 |
JPS5834691B2 true JPS5834691B2 (en) | 1983-07-28 |
Family
ID=15171117
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP13626481A Expired JPS5834691B2 (en) | 1981-08-31 | 1981-08-31 | Leaf spring for vehicle suspension |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5834691B2 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6066506U (en) * | 1983-10-14 | 1985-05-11 | 日野自動車株式会社 | leaf spring |
CN102734364A (en) * | 2012-07-17 | 2012-10-17 | 山东理工大学 | Analytical design method of camber and surface shape of automobile plate spring |
US20140191486A1 (en) | 2013-01-10 | 2014-07-10 | Hendrickson Usa, L.L.C. | Multi-tapered suspension component |
AT520123B1 (en) * | 2017-06-23 | 2023-07-15 | Hendrickson Comm Vehicle Sys Europe Gmbh | Spring leaf for a leaf spring |
-
1981
- 1981-08-31 JP JP13626481A patent/JPS5834691B2/en not_active Expired
Also Published As
Publication number | Publication date |
---|---|
JPS5837332A (en) | 1983-03-04 |
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