JPH0320131A - Spring device - Google Patents
Spring deviceInfo
- Publication number
- JPH0320131A JPH0320131A JP15391189A JP15391189A JPH0320131A JP H0320131 A JPH0320131 A JP H0320131A JP 15391189 A JP15391189 A JP 15391189A JP 15391189 A JP15391189 A JP 15391189A JP H0320131 A JPH0320131 A JP H0320131A
- Authority
- JP
- Japan
- Prior art keywords
- spring
- coil
- coil spring
- spring seat
- seat member
- 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.)
- Pending
Links
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 5
- 239000010959 steel Substances 0.000 claims abstract description 5
- 229910000838 Al alloy Inorganic materials 0.000 claims abstract description 4
- 229920003002 synthetic resin Polymers 0.000 claims abstract description 4
- 239000000057 synthetic resin Substances 0.000 claims abstract description 4
- 239000011295 pitch Substances 0.000 claims description 11
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims 1
- 229910052782 aluminium Inorganic materials 0.000 claims 1
- 239000000463 material Substances 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 9
- 238000004804 winding Methods 0.000 abstract description 7
- 238000013016 damping Methods 0.000 abstract description 5
- 230000002093 peripheral effect Effects 0.000 abstract 2
- 239000013589 supplement Substances 0.000 abstract 1
- 238000002485 combustion reaction Methods 0.000 description 7
- 239000013585 weight reducing agent Substances 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 239000000725 suspension Substances 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 239000013078 crystal Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 229920006015 heat resistant resin Polymers 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
- F01L1/462—Valve return spring arrangements
-
- 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
- F16F1/04—Wound springs
- F16F1/12—Attachments or mountings
- F16F1/125—Attachments or mountings where the end coils of the spring engage an axial insert
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
Abstract
Description
【発明の詳細な説明】
［発明の目的］
〈産業上の利用分野〉
本発明は、例えば、車輌川懸架装置あるいは内燃機関の
弁ばね装置などのように、往復運動を行うべき可動部材
に対して弾発的な復元力を与えるためのばね装置に関す
る。[Detailed Description of the Invention] [Object of the Invention] <Industrial Application Field> The present invention is applicable to a movable member that is to perform reciprocating motion, such as a vehicle suspension system or a valve spring system for an internal combustion engine. The present invention relates to a spring device for providing elastic restoring force.
〈従来の技術〉
ピストン式内燃機関の動弁装置，に用いられる弁ばねの
ように、高速運動を行なう装置に用いられるばね装置や
、車輌の懸架装置に用いられるばね装置のように、衝撃
的な振動を受けるばね装置にあっては、ばね自体の共振
に基因する不整運動の生ずることが問題にされている。<Prior art> Spring devices used in devices that perform high-speed motion, such as valve springs used in valve operating devices of piston-type internal combustion engines, and spring devices used in vehicle suspension systems, are In spring devices that are subjected to severe vibrations, there is a problem in that irregular motion occurs due to resonance of the spring itself.
このような問題に対する解決手段として、特公昭４７−
２２３６３５号公報には、コイルのピッチを不均一にす
ることにより非線形なばね特性を獲得し、これによって
ばね装置の共振点を高める技術が教示されている。As a solution to such problems,
Japanese Patent No. 223635 teaches a technique for obtaining nonlinear spring characteristics by making the pitch of the coil non-uniform, thereby increasing the resonance point of the spring device.
一方、圧縮コイルばねにおいては、ばねの巻軸の湾萌を
避けるために、その端部を平坦に仕上げて座を形成する
ことがある。特に高い作動精度が要求されるばね装置に
おいては、端部のみを密着巻きとしたうえでその端面を
研削したクローズドエンドのコイルばねを用いることが
通例である。On the other hand, in a compression coil spring, in order to prevent the winding shaft of the spring from bulging, the ends of the spring are sometimes finished flat to form a seat. In spring devices that require particularly high operating accuracy, it is customary to use a closed-end coil spring in which only the end portion is tightly wound and the end surface is ground.
〈発明が解決しようとする課題〉
ところが、密着巻きした部分はばねの有効巻数としては
寄与せず、むしろ密着時の高さ寸法を増大させ、ばね単
体、あるいはばね装置の重量増大を招く不都合がある。<Problems to be Solved by the Invention> However, the closely wound portion does not contribute to the effective number of turns of the spring, but rather increases the height dimension when tightly wound, causing the disadvantage of increasing the weight of the spring itself or the spring device. be.
このことは、特に上記した不等ピッチコイルばねの場合
に顕著となる。This is particularly noticeable in the case of the above-mentioned unequal pitch coil springs.
本発明は、このような問題点を解消すべくなされたもの
であり、その主な目的は、小形化及び軽量化を推進し、
より一層の高速化を達成し得る高性能のばね装置を提供
することにある。The present invention was made to solve these problems, and its main purpose is to promote downsizing and weight reduction,
The object of the present invention is to provide a high-performance spring device that can achieve even higher speeds.
［発明の構成］
〈課題を解決するための手段〉
このような目的は、本発明によれば、往復運動を行うべ
き可動部材に対して弾発的な復元力を与えるためのばね
装置であって、前記可動部材に係合する端部をオープン
エンドにしてなりかつ鋼材からなるコイルばねと、前記
コイルばねのオープンエンド端を支承するばね座部材と
を有することを特徴とするばね装置を提供することによ
り達成される。[Structure of the Invention] <Means for Solving the Problems> According to the present invention, the purpose is to provide a spring device for applying an elastic restoring force to a movable member that is to perform reciprocating motion. and a spring seat member that supports the open end of the coil spring. This is achieved by
〈作用〉
このようにすれば、鋼材からなる圧縮コイルばねの可動
側端部の軽量化を達戊し得ると同時に、ばねの軸線方向
寸法を実質的に短縮することができる。<Function> In this way, it is possible to reduce the weight of the movable side end of the compression coil spring made of steel, and at the same time, it is possible to substantially shorten the axial dimension of the spring.
く実施例〉
以下、本発明の好適実施例について、添付の図面を参照
して詳細に説明する。Embodiments Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.
第１図及び第２図は、本発明に基づく圧縮コイルばねを
、内燃機関の動弁装置に適用すべく構成されたコイルば
ね１及びその各端を支承するばね座部材２・３の一例を
示している。FIGS. 1 and 2 show an example of a coil spring 1 and spring seat members 2 and 3 supporting each end thereof, which are configured to apply a compression coil spring according to the present invention to a valve train of an internal combustion engine. It shows.
一般的に、従来形式の弁ばねの各端部は、クローズドエ
ンドにされ、更に軸線方向に直交する平坦面を形成する
ために、その各端部が研削加工されているＤ Ｉ Ｓ−
２７０４）。また、特に巻軸の湾萌を嫌う装置の場合に
は、端末の密着巻き部分は１．５巻き程度とされること
が通例であるが、この部分は、ばねの有効巻数として寄
与しないばかりでなく、密着時の高さ寸法の単寸化を咀
害し、運動部分の質量増大を招くこととなっている。し
かるに、本発明に基づくコイルばね１は、例えば弁ばね
用ＳｉＣｒ鋼線（Ｊ Ｉ Ｓ−Ｇ３５６６）からなり、
その各端部１ａ・１ｂをオープンエンドにされ、かつそ
の素線の最外端が研削されると共に、本実施例において
は、その全長に亘って略均一なピッチで巻かれている。Generally, each end of a conventional valve spring is closed-ended, and each end is ground to form an axially perpendicular flat surface.
2704). In addition, in the case of devices that do not particularly like the winding shaft's curling, it is customary to make the tightly wound portion of the end about 1.5 turns, but this portion does not contribute to the effective number of turns of the spring. This prevents the height dimension from being made uniform when the parts are in close contact with each other, leading to an increase in the mass of the moving parts. However, the coil spring 1 according to the present invention is made of, for example, SiCr steel wire for valve springs (JIS-G3566),
Each of the ends 1a and 1b is made open-ended, and the outermost end of the wire is ground, and in this embodiment, it is wound at a substantially uniform pitch over its entire length.
ばね座部材２●３は、合成樹脂、あるいはアルミニウム
合金からなり、コイルばね１の各端部１ａ・１ｂの研削
面を補完してコイルばねｌの巻軸に直交する平坦面を形
成するための扇形のフランジ４・５がそれぞれの外端側
に形成されると共に、コイルばね１の内周に密接して嵌
合する円筒部６●７がそれぞれの内端側に形成されてお
り、これらフランジ４・５と円筒部６・７との間に形成
された肩面８●９により、コイルばね１の各端部１ａ・
１ｂを支承するようにされている。このようにして、円
筒部６・７にコイルを巻付けることにより、円筒部６・
７の外周面とコイル内周面との間の摩擦抵抗によるダン
ピング効果が得られる。The spring seat member 2●3 is made of synthetic resin or aluminum alloy, and is used to complement the ground surfaces of each end 1a and 1b of the coil spring 1 to form a flat surface perpendicular to the winding axis of the coil spring 1. Sector-shaped flanges 4 and 5 are formed on each outer end side, and cylindrical portions 6 and 7 that closely fit into the inner periphery of the coil spring 1 are formed on each inner end side, and these flanges 4 and 5 and the cylindrical portions 6 and 7, each end 1a and 9 of the coil spring 1
1b. In this way, by winding the coil around the cylindrical parts 6 and 7,
A damping effect is obtained due to the frictional resistance between the outer circumferential surface of No. 7 and the inner circumferential surface of the coil.
尚、符号４ａ・５ａは、コイルばね１の最終端が当接し
てコイルばね１とばね座部材２・３との間の相対周方向
変位を規制するための突起である。Incidentally, reference numerals 4a and 5a are protrusions with which the final ends of the coil spring 1 come into contact to restrict relative circumferential displacement between the coil spring 1 and the spring seat members 2 and 3.
第３図は、第１◆２図に示した，コイルばね１及びばね
座部材２・３を動弁装置に適用した態様を示すもので、
弁１０は、ポートの開口に形成された弁座１１と共働す
ることにより、吸気弁または排気弁として混合気の吸入
及び燃焼ガスの排出を制御する。弁１０のステム部１２
は、シリンダヘッド内に圧人されたステムガイド１３内
に摺合しており、このステム部１２の最外端部には、コ
ツタ１４及びリテーナ１５を介して、一方のばね座部材
２が係止されている。一方、他方のばね座部材３は、金
属製あるいは耐熱樹脂製のワツシャ１６を介し、シリン
ダヘッドにおけるステムガイド１３が突出する部分に形
戊された環状平坦面により支持されている。尚、符号１
７は、燃焼室内へのオイルの侵入を防止するためのステ
ムシールである。FIG. 3 shows an embodiment in which the coil spring 1 and spring seat members 2 and 3 shown in FIGS. 1◆2 are applied to a valve train.
The valve 10 controls intake of the air-fuel mixture and discharge of combustion gas as an intake valve or an exhaust valve by cooperating with a valve seat 11 formed at the opening of the port. Stem portion 12 of valve 10
slides into a stem guide 13 pressed into the cylinder head, and one spring seat member 2 is locked to the outermost end of this stem portion 12 via a retainer 14 and a retainer 15. has been done. On the other hand, the other spring seat member 3 is supported by an annular flat surface formed in the portion of the cylinder head from which the stem guide 13 protrudes, via a washer 16 made of metal or heat-resistant resin. Furthermore, code 1
7 is a stem seal for preventing oil from entering the combustion chamber.
ステム部１２の外端には、その一端を油圧式ラッシュア
ジャスタ１８を介してシリンダヘッドに揺動可能に支持
されたロツカアーム１９の一端が当接している。更に、
ロツカアーム１９の中間部上面には、カム軸２０に形成
されたカム輪郭面２０ａが当接している。従って、本実
施例においては、カム軸２０が回転駆動されると、カム
輪郭面２０ａを介してロッカーアーム１９がラッシュア
ジャスタ１８を支点として下向きに傾動し、弁１０のス
テム部１２が、コイルばね１の付勢力に抗して第３図に
おける下向きに駆動され、弁１０が開かれる。One end of a rocker arm 19, whose one end is swingably supported by the cylinder head via a hydraulic lash adjuster 18, is in contact with the outer end of the stem portion 12. Furthermore,
A cam contour surface 20a formed on the camshaft 20 is in contact with the upper surface of the intermediate portion of the rocker arm 19. Therefore, in this embodiment, when the camshaft 20 is rotationally driven, the rocker arm 19 tilts downward about the lash adjuster 18 via the cam contour surface 20a, and the stem portion 12 of the valve 10 is rotated by the coil spring. The valve 10 is opened by being driven downward in FIG. 3 against the urging force of 1.
第４ａ図は、第３図に示した構造の動弁装置における５
．２０Ｏｒｐｍ時のばね応力波形を、従来構造のクロー
ズドエンド不等ピッチコイルばねと、第１図に示した本
発明構造のばね座部材付オープンエンド等ピッチコイル
ばねとで比較したグラフを示している。このグラフによ
ると、細線で示す従来構造ばねに比し、太線で示す本発
明構造ばねは、サージング波の低減に極めて大きな効果
のあることが分かる。Fig. 4a shows the 5th part of the valve train having the structure shown in Fig. 3.
．． 2 is a graph comparing spring stress waveforms at 20 Orpm between a closed end unequal pitch coil spring of conventional structure and an open end unequal pitch coil spring with a spring seat member of the present invention structure shown in FIG. 1. According to this graph, it can be seen that the structural spring of the present invention shown by the thick line has an extremely large effect on reducing surging waves compared to the conventional structural spring shown by the thin line.
第４ｂ図は、縦軸に負荷応力比（αＣ＝実測応力／設計
応力）をとり、横軸にエンジン回転速度をとって示すグ
ラフである。このグラフによると、細線で示す従来構造
ばねの場合は，、エンジン回転速度が４．００Ｏｒｐｍ
を越えると応力増加が顕著に発生するが、太線で示す本
発明構造ばねによれば、５．００Ｏｒｐｍを越える回転
速度に至るまで、弁ばねの応力増加が好適に抑制される
ことが分かる。FIG. 4b is a graph showing the load stress ratio (αC=actual stress/design stress) on the vertical axis and the engine rotation speed on the horizontal axis. According to this graph, in the case of the conventional structure spring shown by the thin line, the engine rotation speed is 4.00 rpm.
When the rotation speed exceeds 5.00 rpm, stress increases significantly, but according to the structural spring of the present invention shown by the thick line, it can be seen that the stress increase in the valve spring is suitably suppressed until the rotation speed exceeds 5.00 Orpm.
第４Ｃ図は、軽量化の効果を示すもので、バルブバウン
ス量を示すグラフである。従来構造ばねに比して本発明
構造ばねは、２５パーセント程度の軽量化が達成されて
いるので、バルブバウンス急増エンジン回転速度が約３
０Ｏｒ ｐｍ高まり、エンジンの高速化に寄与し得るこ
とが分かる。FIG. 4C shows the effect of weight reduction and is a graph showing the amount of valve bounce. Compared to conventional structural springs, the structural spring of the present invention achieves a weight reduction of approximately 25%, so that the rapid engine rotational speed of the valve bounce can be reduced by approximately 3%.
It can be seen that the engine speed can be increased by 0 Or pm, contributing to higher speeds of the engine.
第５図は、本発明の第２の実施例を示している。FIG. 5 shows a second embodiment of the invention.
本実施例のコイルばね２１は、各端部２１ａ・２ｌｂを
オープンエンドにされると共に、可動端２１ａ側が粗巻
に、基端２ｌｂ側が密券にされた不等２段ピッチコイル
ばねとされている。そしてこれら各端部２１ａ・２ｌｂ
をそれぞれ支承するばね座部材２２・２３は、前記第１
実施例に示したコイル内周に嵌人する円筒部６・７に代
えて、コイル外周を受容する円筒部２６・２７を有して
いる。The coil spring 21 of this embodiment is an unequal pitch coil spring in which each end 21a and 2lb are open-ended, the movable end 21a side is loosely wound, and the base end 2lb side is tightly wound. There is. And each of these end portions 21a and 2lb
The spring seat members 22 and 23 respectively support the first
In place of the cylindrical parts 6 and 7 that fit around the inner periphery of the coil shown in the embodiment, cylindrical parts 26 and 27 that receive the outer periphery of the coil are provided.
第６図は、本発明の第３の実施例を示している。FIG. 6 shows a third embodiment of the invention.
上記した各実施例のばね座部材は、素線最外端の研削面
を補完する部分のみが形成されたフランジを有している
が、本実施例においては、フランジ３４・３５を全周に
形戊し、これらフランジ３４●３５と円筒部３６●３７
との間に形成された肩面３８●３９にてコイルばね３１
の各端部３１ａ●３ｌｂを支承することをもって、コイ
ルばね３１の各端部３１ａ・３ｌｂに形成した研削面が
相手部材に直接接触しないようにしている。これによれ
ば、ばね座部材３４・３５自体の粘弾性によるダンピン
グ効果が期待できる。The spring seat member of each of the embodiments described above has a flange formed only in a portion that complements the ground surface of the outermost end of the wire, but in this embodiment, the flanges 34 and 35 are formed around the entire circumference. Shape these flanges 34*35 and cylindrical parts 36*37
Coil spring 31 at shoulder surface 38●39 formed between
By supporting the respective ends 31a and 3lb of the coil spring 31, the ground surfaces formed on the respective ends 31a and 3lb of the coil spring 31 are prevented from coming into direct contact with the mating member. According to this, a damping effect can be expected due to the viscoelasticity of the spring seat members 34 and 35 themselves.
第７図は、本発明の第４の実施例を示している。FIG. 7 shows a fourth embodiment of the invention.
本実施例におけるコイルばね４１は、前記した第１実施
例と同様に、等ピッチで巻かれると共にオープンエンド
にされ、しかもその各端部４１ａ◆４ｌｂは、何ら研削
されることなく、そのまま合成樹脂製のばね座部材４２
・４３内にインサートモールドされている。そして本実
施例においては、コイルばね４１の最終端は、ばね座部
材４２・４３の端面にまで達している。無論、ばね座部
材４２・４３の内部にて各端部４１ａ・４ｌｂが終息す
るようにしても良い。尚、ばね座部材４２●４３がアル
ミニウム合金等の金属からなる場合でも、同様なインサ
ートモールドが可能である。The coil spring 41 in this embodiment is wound at equal pitches and has an open end, as in the first embodiment, and each end portion 41a◆4lb is made of synthetic resin without being ground in any way. spring seat member 42 made of
・Insert molded inside 43. In this embodiment, the final end of the coil spring 41 reaches the end surfaces of the spring seat members 42 and 43. Of course, the ends 41a and 4lb may end inside the spring seat members 42 and 43. Incidentally, even when the spring seat members 42 and 43 are made of metal such as an aluminum alloy, similar insert molding is possible.
第８図〜第１２図は、それぞれ本発明の変形実施例を示
している。第８図は、第１図に示したばね座部材２・３
にオープンエンドの不等２段ピッチコイルばね５１を組
合わせたものであり、第１実施例に対応する部分には同
一の符号を付してその詳細な説明を省略する。8 to 12 each show a modified embodiment of the present invention. FIG. 8 shows the spring seat members 2 and 3 shown in FIG.
and an open-end unequal pitch coil spring 51, and parts corresponding to those in the first embodiment are given the same reference numerals and detailed explanation thereof will be omitted.
第９図に示すコイルばね６１は、オープンエンドにされ
た各端部６１ａ・６ｌｂを有すると共に、可動端６１ａ
側を小径にしてなる円錐コイルばねとされている。モし
て各端部６１ａ・６ｌｂには、上記各実施例と同一思想
に基づくばね座部相６２●６３がそれぞれ係止している
。The coil spring 61 shown in FIG. 9 has open ends 61a and 6lb, and a movable end 61a.
It is a conical coil spring with a smaller diameter on the side. Furthermore, spring seat portions 62 and 63 based on the same concept as those of the above-mentioned embodiments are engaged with each of the end portions 61a and 6lb, respectively.
第１０図は、各嘲部７１ａ・７ｌｂが縮径された樽形コ
イルばね７１の例を示しており、両端７１ａ●７ｌｂ共
にオープンエンドとし、それぞれにばね座部材７２・７
３を取付けている。FIG. 10 shows an example of a barrel-shaped coil spring 71 in which the diameters of the respective bending portions 71a and 7lb are reduced, both ends 71a and 7lb are open ends, and spring seat members 72 and 7 are respectively provided.
3 is installed.
これら円錐コイルばねによれば、非線形のばね特性を獲
得し、かつ可動端側の軽量化をより一層推進すると共に
、素線のねじり応力を軽減し得る。These conical coil springs can obtain nonlinear spring characteristics, further promote weight reduction on the movable end side, and reduce torsional stress in the strands.
第１１図は、第２実施例のコイルばね２１と同様に、基
端８ｌｂ側が密巻とされた不等２段ピッチコイルばね８
１であるが、基端８ｌｂ側のみがクローズドエンドとさ
れ、かつ研削処理されている。これにより、ばね座部材
８２を可動端８１ａ側にのみ取り付け、基端８ｌｂ側の
ばね座部材を省略し得るようにしている。これによると
、密着高さ寸法が幾分か増大するものの、特に動弁装置
に用いる場合には、基端側の質量の影響は桶めて小さく
、クローズドエンドとすることによる重量増大はさほど
問題とはならず、また鋼材からなるコイルばねの場合に
は、巻線構造による線間摩耗の問題が生じないので、む
しろ部晶点数を削減したい向きには有利である。。FIG. 11 shows an unequal two-stage pitch coil spring 8 whose proximal end 8lb side is tightly wound, similar to the coil spring 21 of the second embodiment.
1, but only the proximal end 8lb side is closed-ended and has been ground. Thereby, the spring seat member 82 is attached only to the movable end 81a side, and the spring seat member on the base end 8lb side can be omitted. According to this, although the contact height dimension increases somewhat, the influence of the mass on the proximal end side is relatively small, especially when used in a valve train, and the increase in weight due to the closed end is not a problem. In addition, in the case of a coil spring made of steel, there is no problem of wear between wires due to the winding structure, so it is rather advantageous for those who want to reduce the number of crystal points. .
また、本実施例の思想は、第１，２図に示すように、基
端９ｌｂ側を大径かつ密巻とし、可動端９１ａ側を小径
かつ粗巻とした２段ピッチ円錐コイルばね９１にも適用
することができ、この場合にも、可動端９１ａ側にのみ
ばね座部材９２を設ければ良い。In addition, as shown in FIGS. 1 and 2, the idea of this embodiment is to create a two-stage pitch conical coil spring 91 with a large diameter and tightly wound on the base end 9lb side and a small diameter and coarsely wound on the movable end 91a side. Also, in this case, the spring seat member 92 only needs to be provided on the movable end 91a side.
以上、各実施例に示した態様は、それぞれを適宜に組み
合わせて実施することも可能なことは言うまでもない。It goes without saying that the embodiments shown in each embodiment can be implemented by appropriately combining them.
尚、上記実施例は、本発明を内燃機関の動弁装置に適用
した場合についてのみ説明したが、本発明は、内燃機関
などの用途に限らず、例えば車輌用懸架装置など、往復
運動を行うべき可動部材に対して弾発的な復元力を与え
る構戊を具備する任意の機械装置に適用し得るものであ
る。Although the above embodiments have been described only in the case where the present invention is applied to a valve train of an internal combustion engine, the present invention is not limited to applications such as internal combustion engines, but is applicable to applications that perform reciprocating motion, such as suspension systems for vehicles. The present invention can be applied to any mechanical device having a structure that provides an elastic restoring force to a movable member.
［発明の効果］
このように本発明によれば、ばね装置の特に可動端側を
軽量化し得るので、機械装置の運転速度の高速化を図る
ことができる。また、有効巻数に寄与しない捨巻き部分
を排除してコイルばねの密着高さを低減し得るので、ば
ね装置の小形化を図ることができる。更に、上記したよ
うにばね座部材の形状により、ばね座部材とコイルばね
との間の摩擦抵抗に基づくダンピング効果、あるいはば
ね座部材自体の粘弾性特性に基づくダンピング効果をも
得ることができる。従って、全体として内燃機関などの
機械装置の高速化及びコンパクト化を図る上に、極めて
多大な効果を奏することができる。[Effects of the Invention] As described above, according to the present invention, the weight of the spring device, particularly at the movable end side, can be reduced, so that the operating speed of the mechanical device can be increased. Further, since the height of the coil spring in close contact with the coil spring can be reduced by eliminating the discarded portion that does not contribute to the effective number of turns, the spring device can be made smaller. Furthermore, as described above, depending on the shape of the spring seat member, it is possible to obtain a damping effect based on the frictional resistance between the spring seat member and the coil spring, or a damping effect based on the viscoelastic properties of the spring seat member itself. Therefore, an extremely large effect can be achieved in increasing the speed and compactness of mechanical devices such as internal combustion engines as a whole.
第１図は、動弁装置用に構成された本発明に基づくコイ
ルばね及びばね座部材を示す側面図であり、第２図は、
ばね座部材の端面図である。
第３図は、本発明が適用された動弁装置の一例を示す部
分断面図である。
第４ａ図〜第４Ｃ図は、従来構造の弁ばねと本発明構造
の弁ばねとの特性を比較して示すグラフの一例である。
第５図は、本発明装置の第２の実施例を示す第１図と同
様の図であり、第６図は、同じく第３の実施例を示す縦
断面図であり、第７図は、同じく第４の実施例を示す縦
断面図である。
第８図〜第１２図は、それぞれ本発明装置の変形実施例
を示す第１図と同様の図である。
１・・・コイルばね １ａ・１ｂ・・・外端部２●
３・・・ばね座部材 ４◆５・・・フランジ６・７・・
・円筒部 ８・９・・・肩面第１
図
第２図
Ｒぺ
第３図
＜そ，＼べ一FIG. 1 is a side view showing a coil spring and a spring seat member according to the present invention configured for a valve train, and FIG.
It is an end view of a spring seat member. FIG. 3 is a partial sectional view showing an example of a valve train to which the present invention is applied. FIGS. 4a to 4C are examples of graphs comparing and showing the characteristics of a valve spring having a conventional structure and a valve spring having a structure according to the present invention. FIG. 5 is a diagram similar to FIG. 1 showing a second embodiment of the device of the present invention, FIG. 6 is a longitudinal cross-sectional view also showing a third embodiment, and FIG. It is a longitudinal cross-sectional view showing a fourth example as well. 8 to 12 are views similar to FIG. 1 showing modified embodiments of the apparatus of the present invention, respectively. 1...Coil spring 1a, 1b...Outer end 2●
3... Spring seat member 4◆5... Flange 6, 7...
・Cylindrical part 8・9...Shoulder surface 1 Figure 2 Figure 3 Rpe Figure 3
Claims (6)
元力を与えるためのばね装置であって、前記可動部材に
係合する端部をオープンエンドにしてなり、かつ鋼材か
らなるコイルばねと、前記コイルばねのオープンエンド
端を支承するばね座部材とを有することを特徴とするば
ね装置。(1) A spring device for applying an elastic restoring force to a movable member that is to perform reciprocating motion, the end of which engages with the movable member being open-ended, and the coil being made of steel. A spring device comprising: a spring; and a spring seat member supporting an open end of the coil spring.
とする第１請求項に記載のばね装置。(2) The spring device according to claim 1, wherein the coil springs have unequal pitches.
とする第１もしくは第２請求項に記載のばね装置。(3) The spring device according to claim 1 or 2, wherein the open end end is reduced in diameter.
は外周に接触する円筒状部分を有することを特徴とする
第１ないし第３請求項のいずれかに記載のばね装置。(4) The spring device according to any one of claims 1 to 3, wherein the spring seat member has a cylindrical portion that contacts the inner circumference or outer circumference of the coil spring.
ウム合金からなることを特徴とする第１項ないし第４請
求項のいずれかに記載のばね装置。(5) The spring device according to any one of claims 1 to 4, wherein the spring seat member is made of aluminum or an aluminum alloy.
とする第１ないし第４請求項のいずれかに記載のばね装
置。(6) The spring device according to any one of claims 1 to 4, wherein the spring seat member is made of a synthetic resin material.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15391189A JPH0320131A (en) | 1989-06-16 | 1989-06-16 | Spring device |
| DE19904019072 DE4019072C2 (en) | 1989-06-16 | 1990-06-15 | Spring system |
| US07/837,561 US5246215A (en) | 1989-06-16 | 1992-02-18 | Spring seat member with notch for ground spring end |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15391189A JPH0320131A (en) | 1989-06-16 | 1989-06-16 | Spring device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0320131A true JPH0320131A (en) | 1991-01-29 |
Family
ID=15572799
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15391189A Pending JPH0320131A (en) | 1989-06-16 | 1989-06-16 | Spring device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH0320131A (en) |
| DE (1) | DE4019072C2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62200795A (en) * | 1986-02-28 | 1987-09-04 | 住友ベークライト株式会社 | Manufacture of laminate for flexible printed circuit |
| US5906362A (en) * | 1996-08-15 | 1999-05-25 | Exedy Corporation | Coil spring assembly and damper mechanism |
| JP2010084881A (en) * | 2008-10-01 | 2010-04-15 | Kyocera Mita Corp | Drive transmission device and image forming apparatus including the same |
| JP2011051012A (en) * | 2009-09-03 | 2011-03-17 | Korea Inst Of Science & Technology | Method of manufacturing shape memory alloy coil spring |
| JP2014040791A (en) * | 2012-08-22 | 2014-03-06 | Aisan Ind Co Ltd | Flow rate control valve |
| JP2014511979A (en) * | 2011-03-21 | 2014-05-19 | テスコム・コーポレーション | Vibration damping spring clip for pressure regulator |
| JP2014202305A (en) * | 2013-04-05 | 2014-10-27 | 三菱自動車工業株式会社 | Spring supporting structure |
| WO2020090249A1 (en) * | 2018-10-29 | 2020-05-07 | ミネベアミツミ株式会社 | Motor |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4125155C1 (en) * | 1991-07-30 | 1993-02-04 | Robert Bosch Gmbh, 7000 Stuttgart, De | |
| EP0539955B1 (en) * | 1991-10-30 | 1998-02-18 | Togo Seisakusho Corporation | Spring assembly for automatic transmission of automotive vehicle and the like |
| DE102009060231B4 (en) * | 2009-12-23 | 2021-04-29 | Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh | Compression spring and method of manufacturing the same |
| US9416836B2 (en) | 2011-03-04 | 2016-08-16 | Piolax, Inc | Spring assembly |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5218349B1 (en) * | 1966-06-11 | 1977-05-20 | ||
| JPS5646128A (en) * | 1979-08-22 | 1981-04-27 | Chuo Spring Co Ltd | Cushion for coil spring |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1878128A (en) * | 1927-11-10 | 1932-09-20 | Packard Motor Car Co | Valve spring |
| US2514394A (en) * | 1945-01-09 | 1950-07-11 | Frank J Irving | Coupling |
| DE1930244A1 (en) * | 1969-06-13 | 1970-12-17 | Euratom | Process for explosive welding of two metal parts |
| DE2942135A1 (en) * | 1979-10-18 | 1981-04-30 | Volkswagenwerk Ag, 3180 Wolfsburg | UNDERLAY OF ELASTIC MATERIAL FOR COIL SPRINGS OF A MOTOR VEHICLE SUSPENSION |
-
1989
- 1989-06-16 JP JP15391189A patent/JPH0320131A/en active Pending
-
1990
- 1990-06-15 DE DE19904019072 patent/DE4019072C2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5218349B1 (en) * | 1966-06-11 | 1977-05-20 | ||
| JPS5646128A (en) * | 1979-08-22 | 1981-04-27 | Chuo Spring Co Ltd | Cushion for coil spring |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62200795A (en) * | 1986-02-28 | 1987-09-04 | 住友ベークライト株式会社 | Manufacture of laminate for flexible printed circuit |
| US5906362A (en) * | 1996-08-15 | 1999-05-25 | Exedy Corporation | Coil spring assembly and damper mechanism |
| JP2010084881A (en) * | 2008-10-01 | 2010-04-15 | Kyocera Mita Corp | Drive transmission device and image forming apparatus including the same |
| US8656801B2 (en) | 2008-10-01 | 2014-02-25 | Kyocera Document Solutions Inc. | Drive transmission device and image forming apparatus including the same |
| JP2011051012A (en) * | 2009-09-03 | 2011-03-17 | Korea Inst Of Science & Technology | Method of manufacturing shape memory alloy coil spring |
| JP2014511979A (en) * | 2011-03-21 | 2014-05-19 | テスコム・コーポレーション | Vibration damping spring clip for pressure regulator |
| JP2014040791A (en) * | 2012-08-22 | 2014-03-06 | Aisan Ind Co Ltd | Flow rate control valve |
| JP2014202305A (en) * | 2013-04-05 | 2014-10-27 | 三菱自動車工業株式会社 | Spring supporting structure |
| WO2020090249A1 (en) * | 2018-10-29 | 2020-05-07 | ミネベアミツミ株式会社 | Motor |
| JPWO2020090249A1 (en) * | 2018-10-29 | 2021-11-04 | ミネベアミツミ株式会社 | motor |
| US11870321B2 (en) | 2018-10-29 | 2024-01-09 | Minebea Mitsumi Inc. | Motor |
Also Published As
| Publication number | Publication date |
|---|---|
| DE4019072C2 (en) | 1993-12-23 |
| DE4019072A1 (en) | 1990-12-20 |
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