JPH04121550U - Resonance prevention spring for restoration - Google Patents
Resonance prevention spring for restorationInfo
- Publication number
- JPH04121550U JPH04121550U JP3472791U JP3472791U JPH04121550U JP H04121550 U JPH04121550 U JP H04121550U JP 3472791 U JP3472791 U JP 3472791U JP 3472791 U JP3472791 U JP 3472791U JP H04121550 U JPH04121550 U JP H04121550U
- Authority
- JP
- Japan
- Prior art keywords
- spring
- bending point
- resonance
- tension spring
- length
- 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
- 230000002265 prevention Effects 0.000 title claims description 10
- 238000005452 bending Methods 0.000 claims abstract description 23
- 230000000694 effects Effects 0.000 description 11
- 238000009434 installation Methods 0.000 description 8
- 239000011295 pitch Substances 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 238000002474 experimental method Methods 0.000 description 5
- 239000000047 product Substances 0.000 description 4
- 238000004804 winding Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000002955 isolation Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- JOYRKODLDBILNP-UHFFFAOYSA-N Ethyl urethane Chemical compound CCOC(N)=O JOYRKODLDBILNP-UHFFFAOYSA-N 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 239000012263 liquid product Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000010079 rubber tapping Methods 0.000 description 1
- 125000000391 vinyl group Chemical group [H]C([*])=C([H])[H] 0.000 description 1
- 229920002554 vinyl polymer Polymers 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Abstract
(57)【要約】 （修正有）
【目的】 作業工数の低減が図れるとともにコスト低減
が図れ、さらには軽量化が図れる復元用共振防止ばねを
提供する。
【構成】 密着巻部と疎巻部とからなる非線型特性を有
する引張ばねを、ばね特性が屈曲点を示す長さ近くに引
張した状態で取付ける。
(57) [Summary] (with amendments) [Purpose] To provide a restoration anti-resonance spring that can reduce work man-hours, reduce costs, and furthermore be lightweight. [Structure] A tension spring having nonlinear characteristics consisting of a tightly wound portion and a sparsely wound portion is installed in a tensioned state near the length where the spring characteristics indicate a bending point.
Description
【０００１】0001
本考案は、カーシート（主にウォークインシート）に使用されるリターンばね に適用して好適である復元用共振防止ばねに関するものである。 This invention is a return spring used in car seats (mainly walk-in seats). This invention relates to a restoring resonance prevention spring suitable for application to.
【０００２】0002
従来、ウォークインシートに使用されるリターンばね（引張ばね）においては 共振（線間タタキ音）防止のため、コイル部の中へスラブウレタンを入れるとか 、コイル部にチューブをかぶせるとかしていた。 Conventionally, in return springs (tension springs) used for walk-in seats, To prevent resonance (wire tapping noise), insert slab urethane into the coil section. , the coil part was covered with a tube.
【０００３】0003
しかしながら、従来技術においては、リターンばねにリターンばねとは別部品 を取付けるものであり、作業工数がかかるばかりか、品質も安定せず、コストも 高いという問題点がある。 本考案は、かかる事情に鑑みてなされたものであり、作業工数の低減が図れる と共に、品質の安定化が図れ、さらにはコスト低減が図れる復元用共振防止ばね を提供することを目的とするものである。 However, in the conventional technology, the return spring is a separate part from the return spring. Not only does it take many man-hours to install, but the quality is not stable and the cost is high. The problem is that it is expensive. The present invention was developed in view of the above circumstances, and it is possible to reduce the number of man-hours required. Along with this, we have developed a vibration prevention spring for restoring, which can stabilize quality and further reduce costs. The purpose is to provide the following.
【０００４】0004
上記目的を達成するため、本考案は、密着巻部と疎巻部とからなる非線型特性 を有する引張ばねを自由長からできるだけ屈曲点長さに近付くように引張した状 態で取付けたことを特徴としている。 In order to achieve the above object, the present invention has a non-linear characteristic consisting of a tightly wound part and a sparsely wound part. The state in which a tension spring with It is characterized by being installed in the same position.
【０００５】[0005]
密着巻部と疎巻部とからなる非線型特性を有する引張ばねを自由長からできる だけ屈曲点長さに近付くように引張した状態で取付けたので、固有振動数が変化 し、ばねにおける共振が防止できる。 A tension spring with nonlinear characteristics consisting of a tightly wound part and a sparsely wound part can be made from free length. Since it was installed under tension so that it approaches the bending point length, the natural frequency changes. However, resonance in the spring can be prevented.
【０００６】[0006]
以下、本考案の一実施例を図１乃至図７に基づいて説明する。 図１において、ウォークインシートのスライドレールにおいては、スライドレ ールアッパー１とスライドレールロアー２との間にリターンばねとしての引張ば ね３が張設されている。 An embodiment of the present invention will be described below with reference to FIGS. 1 to 7. In Figure 1, the slide rail of the walk-in seat is A tension spring as a return spring is provided between the slide rail upper 1 and the slide rail lower 2. 3 is tensioned.
【０００７】 引張ばね３は図２に示す如く自由状態で密着巻部３ａと疎巻部（ピッチ巻部） ３ｂ（ピッチｐ）とからなり、ばね特性が図３の荷重（Ｐ）−撓み（δ）線図に 示すように、従来の線ａに対して線ｂで示す如く非線型特性となっている。従っ て、固有振動数が変化し、ばねにおける共振が防止できるようになっている。な お、図３において、δ1 は取付時、δ2 は最大使用時を示している。As shown in FIG. 2, the tension spring 3 consists of a tightly wound portion 3a and a sparsely wound portion (pitch wound portion) 3b (pitch p) in the free state, and the spring characteristics are as shown in FIG. 3, load (P) - deflection ( As shown in the δ) diagram, it has a nonlinear characteristic as shown by line b in contrast to the conventional line a. Therefore, the natural frequency changes, and resonance in the spring can be prevented. In addition, in FIG. 3, δ 1 represents the time of installation, and δ 2 represents the time of maximum use.
【０００８】 ところで、本実施例において、ばね定数が変化する位置を屈曲点とし、密着巻 部と疎巻部の比率を変えることによって屈曲点を変化させた場合、自由長を変え ることによって屈曲点を変化させた場合のそれぞれの共振防止効果比較及び等ピ ッチ密着巻きの引張りばねとこれのコイル部にビニールチューブをかぶせたもの との共振防止効果比較等を目的とした復元用共振防止ばねによる共振防止実験を 行ったので、この共振防止実験について述べる。[0008] By the way, in this example, the position where the spring constant changes is defined as the bending point, and the close winding is performed. If the bending point is changed by changing the ratio of the winding section to the loose winding section, the free length will change. Comparison of resonance prevention effects and equal pitch when changing the bending point by A tight-wound tension spring with a vinyl tube wrapped around the coil. We conducted a resonance prevention experiment using a restoring resonance prevention spring for the purpose of comparing the resonance prevention effect with the I will now describe this resonance prevention experiment.
【０００９】 実験方法としては、図４の様に引張ばね３をセットし、シート４をレール５上 最後方部まで引張る（ばね長さＬ＝５０６mmまで引張られる）。[0009] The experimental method was to set the tension spring 3 as shown in Figure 4, and place the sheet 4 on the rail 5. Pull it to the rearmost part (pull it to the spring length L = 506 mm).
【００１０】 この状態でレバー６を引張るとシート４が倒れ、引張ばね３の力によりレール ５上をシート４が前方にスライドしてストッパに当たって止まる（このとき、ば ね長さＬは取付時の長さであってＬ＝１９０．２mmである）。0010 In this state, if you pull the lever 6, the seat 4 will fall down, and the force of the tension spring 3 will cause the rail to fall. The seat 4 slides forward on the stopper and stops (at this time, the The screw length L is the length when installed and is 190.2 mm).
【００１１】 そして、シート５がストッパに当たった時からの荷重変動を動歪計により計測 する。 なお、図４において符号７は歪ゲージを示している。そして、データアウトプ ットとして荷重（Ｐ）と時間との関係を示した線図を図５に示すが、図５におい てＳは最大振幅を示している。[0011] Then, the load fluctuation from the time the seat 5 hits the stopper is measured using a dynamic strain meter. do. Note that in FIG. 4, reference numeral 7 indicates a strain gauge. And data output Figure 5 shows a diagram showing the relationship between load (P) and time as a set. S indicates the maximum amplitude.
【００１２】 実験を行ったサンプルの荷重（Ｐ）−ばね長さ（Ｌ）を図６及び図７に示す。 ここで、線径（２φmm），平均コイル径（２２φmm），総巻数（６６．５），ば ね長さＬ＝５０６mm時荷重８．５kgは全て統一してあり、図６は密着巻部と疎巻 部の巻数変化による屈曲点の変化を表わし、図７は自由長の変化による屈曲点の 変化を表わしている。0012 The load (P) vs. spring length (L) of the sample tested is shown in FIGS. 6 and 7. Here, the wire diameter (2φmm), average coil diameter (22φmm), total number of turns (66.5), The load of 8.5 kg when the screw length L = 506 mm is the same for all cases, and Figure 6 shows the closely wound part and loosely wound part. Fig. 7 shows the change in the bending point due to the change in the number of turns of the part. It represents change.
【００１３】 実験結果を表１に示す。[0013] The experimental results are shown in Table 1.
【００１４】[0014]
【表１】 ┌───┬────┬────┬────┬───┬───┬────┬─┐ │ │ │ │ │ │停止後│最大荷重│評│ │ │ │ │ │ │0.8 〜│の最大振│価│ │屈曲点│品番 │密着巻部│疎巻部巻│自由長│1.0 秒│幅の25% │順│ │ │ │巻数 │数 │ │後の最│の振幅に│位│ │ │ │ │ │ │大振幅│なる時間│ │ │ (mm) │ │ │ │ (mm) │ (gr) │ (sec) │ │ ├───┼────┼────┼────┼───┼───┼────┼─┤ │２８０│ SNIC-2 │１９．５│ ４７ │１７３│６９５│５．９ │６│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │２４０│ SNIC-3 │２６．５│ ４０ │１７３│５２２│４．４ │５│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │２００│ SNIC-1 │４１．５│ ２５ │１７３│１１４│０．１５│３│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │190.2 │ SNIC-4 │ ４８ │１８．５│１７３│７９ │０．０９│１│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │１８０│ SNIC-5 │５７．５│ ９ │１７３│４１９│６．６ │７│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │２１６│ SNIC-6 │４１．５│ ２５ │１８３│１７５│０．６ │４│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │１８４│ SNIC-7 │４１．５│ ２５ │１６３│３０３│１０以上│８│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │ ─ │チュー ブナシ│６４．５│ ０ │１７３│９５７│１０以上│９│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │ ─ │チュー ブアリ│６４．５│ ０ │１７３│７８ │０．１９│２│ └───┴────┴────┴────┴───┴───┴────┴─┘[Table 1] ┌───┬────┬────┬────┬───┬───┬────┬─┐ │ │ │ │ │ │After stopping│Maximum load│Evaluation│ │ │ │ │ │ │0.8 ~ │ maximum swing │ value │ │Bending point│Product number │Tightly wound portion │Loosely wound portion │Free length│1.0 seconds│25% of width │Order│ │ │ │number of turns │number │ │to the last│ amplitude│place│ │ │ │ │ │ │Large amplitude│Time│ │ │ (mm) │ │ │ │ (mm) │ (gr) │ (sec) │ │ ├───┼────┼────┼────┼───┼───┼────┼─┤ │280│ SNIC-2 │19.5│ 47 │173│695│5.9 │6│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │240│ SNIC-3 │26.5│ 40 │173│522│4.4 │5│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │200│ SNIC-1 │41.5│ 25 │173│114│0.15│3│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │190.2 │ SNIC-4 │ 48 │18.5 │ 173 │ 79 │ 0.09 │ 1 │ ├───┼────┼────┼────┼───┼───┼────┼─┤ │180│ SNIC-5 │57.5│ 9 │173│419│6.6 │7│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │216│ SNIC-6 │41.5│ 25 │183│175│0.6 │4│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │184│ SNIC-7 │41.5│ 25 │163│303│10 or more│8│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │ ─ │Tube None│64.5│ 0 │173│957│10 or more│9│ ├───┼────┼────┼────┼───┼───┼────┼─┤ │ ─ │Tube Ali│64.5│ 0 │173│78 │0.19│2│ └───┴────┴────┴────┴───┴───┴────┴─┘
【００１５】 表１において、品番がＳＮＩＣ−２，−３，−１，−６においては屈曲点＞取 付時（Ｌ＝１９０．２mm）であり、ＳＮＩＣ−４においては屈曲点＝取付時であ り、ＳＮＩＣ−５，−７においては屈曲点＜取付時である。また、品番で「チュ ーブなし」は等ピッチ密着巻きのままのものであり、「チューブあり」は等ピッ チ密着巻きのコイル部にチューブをかぶせたもので現行流動品に相当するもので ある。[0015] In Table 1, for product numbers SNIC-2, -3, -1, -6, bending point > removal point. (L = 190.2 mm), and in SNIC-4, the bending point = when installed. For SNIC-5 and -7, the bending point is less than the time of installation. Also, the product number ``Without tube'' means that the coils are tightly wound at equal pitches, and ``With tubes'' means that they are wound with equal pitches. This is a tightly wound coil part covered with a tube, and is equivalent to the current liquid product. be.
【００１６】 そして、表１から考察すると、屈曲点＜取付時の場合、取付け状態において密 着巻部が密着していないものは防振効果が少ない。また、屈曲点＝取付時の場合 、防振効果が最大となる。また、屈曲点＞取付時の場合、自由長の変化による屈 曲点の変化、密着巻部と疎巻部の巻数変化による屈曲点の変化ともに、屈曲点が 取付時に近いものほど防振効果が大きい。そして、二段ピッチ引張ばねは、条件 により、コイル部にチューブをかぶせるのと同程度の防振効果を発揮する。[0016] Considering Table 1, if the bending point < at the time of installation, then the If the wrapping part is not tightly attached, the vibration-proofing effect will be low. In addition, if the bending point = at the time of installation , the vibration isolation effect is maximized. In addition, if the bending point > at the time of installation, bending due to change in free length. Both the change in the bending point and the change in the bending point due to the change in the number of turns between the tightly wound part and the sparsely wound part, the bending point is The closer it is to the time of installation, the greater the vibration-proofing effect. And the two-stage pitch tension spring has the condition This provides the same vibration-proofing effect as covering the coil with a tube.
【００１７】 即ち、結論として二段ピッチ引張ばねにより防振効果を狙う場合、屈曲点＝取 付時となるような製品が最も効果が大きく、屈曲点＜取付時となった場合効果が 期待できない。量産に際しての設計上、屈曲点＝取付時を狙うとばらつきがある ため、屈曲点＜取付時となる場合も想定される。従って、ばらつきを考慮した上 で、屈曲点＜取付時とならないよう屈曲点を取付時より高めでなおかつ取付時に 近付けた設計が望ましい。[0017] In other words, the conclusion is that when aiming for a vibration isolation effect with a two-stage pitch tension spring, the bending point = Products that have the greatest effect when installed are the most effective, and the effect is greatest when the bending point < when installed. I can't wait. Due to the design during mass production, there is variation when aiming at the bending point = installation time. Therefore, it is assumed that there may be cases where the bending point is less than the time of installation. Therefore, after considering the variation To avoid bending point Designs that are close together are desirable.
【００１８】 このように、本実施例においては、二段ピッチ引張ばねによりばね特性を非線 型特性として共振防止を図ったので、別部品と併用する必要がなく、作業工数の 低減が図れると共にコスト低減が図れ、更には軽量化が図れる。 なお、本考案はウォークインシートのリターンばねに限らず、共振（線間タタ キ音）防止を必要とする部位に応用できるものである。[0018] In this way, in this example, the spring characteristics are made non-linear by using the two-stage pitch tension spring. Since resonance has been prevented as a mold characteristic, there is no need to use it in conjunction with other parts, reducing work man-hours. It is possible to achieve reductions in weight, cost reduction, and weight reduction. Note that this invention is not limited to the return spring of walk-in seats, but also applies to resonance (tap between lines). It can be applied to areas that require prevention.
【００１９】[0019]
以上述べたように、本考案によれば、別部品と併用する必要がないため、作業 工数の低減が図れると共にコスト低減が図れ、更には軽量化が図れる。 As mentioned above, according to the present invention, there is no need to use other parts together, so the work It is possible to reduce the number of man-hours, reduce costs, and further reduce weight.
【図１】本考案に係る一実施例の使用状態の要部の斜視
図である。FIG. 1 is a perspective view of essential parts of an embodiment of the present invention in use.
【図２】本考案に係る一実施例の引張ばねの正面図であ
る。FIG. 2 is a front view of an embodiment of a tension spring according to the present invention.
【図３】本考案に係る引張ばねの荷重と撓みとの関係を
従来例と対比して示した線図である。FIG. 3 is a diagram showing the relationship between the load and deflection of the tension spring according to the present invention in comparison with a conventional example.
【図４】本考案に係る実験装置の概略説明図である。FIG. 4 is a schematic explanatory diagram of an experimental apparatus according to the present invention.
【図５】本考案に係る実験装置より得られたデータアウ
トプットの荷重と時間との関係を示す線図である。FIG. 5 is a diagram showing the relationship between load and time of data output obtained from the experimental device according to the present invention.
【図６】本考案に係る実験に際して用いたサンプルの荷
重とばね長さとの関係を示した線図である。FIG. 6 is a diagram showing the relationship between the load and spring length of samples used in experiments related to the present invention.
【図７】本考案に係る実験に際して用いたサンプルの荷
重とばね長さとの関係を示した線図である。FIG. 7 is a diagram showing the relationship between the load and spring length of samples used in experiments related to the present invention.
３ 引張ばね ３ａ 密着巻部 ３ｂ 疎巻部 3 Tension spring 3a Closely wound part 3b Loosely wound part
Claims (1)
を有する引張ばねを自由長からできるだけ屈曲点長さに
近付くように引張した状態で取付けたことを特徴とする
復元用共振防止ばね1. Resonance prevention for restoring, characterized in that a tension spring having non-linear characteristics consisting of a tightly wound part and a sparsely wound part is attached in a tensioned state from the free length as close to the bending point length as possible. spring
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3472791U JPH04121550U (en) | 1991-04-16 | 1991-04-16 | Resonance prevention spring for restoration |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3472791U JPH04121550U (en) | 1991-04-16 | 1991-04-16 | Resonance prevention spring for restoration |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH04121550U true JPH04121550U (en) | 1992-10-30 |
Family
ID=31917078
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3472791U Pending JPH04121550U (en) | 1991-04-16 | 1991-04-16 | Resonance prevention spring for restoration |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH04121550U (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57171130A (en) * | 1982-03-18 | 1982-10-21 | Nhk Spring Co Ltd | Method of attaching coiled tension spring |
-
1991
- 1991-04-16 JP JP3472791U patent/JPH04121550U/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57171130A (en) * | 1982-03-18 | 1982-10-21 | Nhk Spring Co Ltd | Method of attaching coiled tension spring |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Estes et al. | Some quantitative properties of anxiety. | |
| JPH04121550U (en) | Resonance prevention spring for restoration | |
| EP0681169B1 (en) | Arrangement for fixing a balancing weight having a glued layer to the imbalance compensating location of a vehicle wheel disc | |
| JPH04501072A (en) | A method for stringing individual strings on a ball game racket and an apparatus for carrying out the method | |
| EP1098194A3 (en) | Nondestructive fatigue test method for ferromagnetic construction materials | |
| US7049507B2 (en) | Aerial cable installation and aerial cable suspension device therefor | |
| WO2003074928A8 (en) | Device for height and gradient compensation | |
| WO2018145918A1 (en) | Method for detecting a driving state of a vehicle | |
| Nourtier et al. | Ionization probability of sputtered atoms: Band-structure and collisional effects | |
| CN102022110B (en) | Exciting tension assembly test device for pulser | |
| DE102004020440B3 (en) | Testing device for quality control of a cable and suitable test method | |
| CN1620562A (en) | Closed end type coil spring of reducing initial bending | |
| JPH05246283A (en) | Tensioning structure for carrier of motor vehicle | |
| CN201884026U (en) | Testing device for excitation tensile force components of pulse generators | |
| Stoloff | A Study of Parking Brake Cable Efficiency as Affected by Construction Type | |
| JPS5843366Y2 (en) | Pole transformer slippage prevention device | |
| JPH06201494A (en) | Method for measuring cable tension | |
| JPS587780Y2 (en) | Pipe busbar vibration isolator | |
| JP3380904B2 (en) | Method and apparatus for measuring fixing load of PC steel | |
| DE633528C (en) | Device for testing motor vehicle brakes | |
| DE2014865B2 (en) | Sound generating device for musical instruments | |
| DE512578C (en) | Spacer clamp | |
| JPS5917219A (en) | Dry transformer | |
| AT524528A1 (en) | Dynamic Rotational Single Sheet Tester | |
| DE2927368A1 (en) | Servo motor for compensated recording instrument - has brake arm on side, released from drive disc by excitation of windings mounted on housing |