JPH0544600Y2 - - Google Patents
Info
- Publication number
- JPH0544600Y2 JPH0544600Y2 JP1988105391U JP10539188U JPH0544600Y2 JP H0544600 Y2 JPH0544600 Y2 JP H0544600Y2 JP 1988105391 U JP1988105391 U JP 1988105391U JP 10539188 U JP10539188 U JP 10539188U JP H0544600 Y2 JPH0544600 Y2 JP H0544600Y2
- Authority
- JP
- Japan
- Prior art keywords
- hub
- mass body
- spring member
- outer diameter
- inner diameter
- 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 - Lifetime
Links
- 239000013013 elastic material Substances 0.000 claims description 4
- 229910001018 Cast iron Inorganic materials 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 238000004073 vulcanization Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 238000009987 spinning Methods 0.000 description 1
Landscapes
- Pulleys (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は、自動車エンジンのクランクシヤフト
など各種の駆動系に生起される振動を吸収するダ
ンパの改良に関するものである。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an improvement of a damper that absorbs vibrations generated in various drive systems such as the crankshaft of an automobile engine.
従来から、たとえば第３図および第４図に示す
ように自動車エンジンのクランクシヤフトに嵌着
されるハブ１の外周に所要の質量を備える質量体
２、振動リングを離間配置して該ハブ１と質量体
２の間に所要のバネ定数を備えるゴム状弾性材製
のバネ部材３を介装し、前記シヤフトに対して一
種の共振系を構成して該シヤフトに生じる振動
（主に捩り振動）を吸収減衰するトーシヨナルダ
ンパが知られている。質量体２の外径部には無端
ベルトを掛合するプーリ溝２ｂが形成され、当該
ダンパと無端ベルトを介してエンジンのウオータ
ーポンプや各種の補機類にシヤフトのトルクを伝
達するようになつている。
Conventionally, as shown in FIGS. 3 and 4, for example, a hub 1 fitted to a crankshaft of an automobile engine has been fitted with a mass body 2 having a required mass and a vibration ring, which are spaced apart from each other on the outer periphery of the hub 1. A spring member 3 made of a rubber-like elastic material having a required spring constant is interposed between the mass bodies 2 to form a kind of resonance system for the shaft to generate vibrations (mainly torsional vibrations) in the shaft. Torsional dampers that absorb and attenuate are known. A pulley groove 2b for engaging an endless belt is formed on the outer diameter of the mass body 2, and shaft torque is transmitted to the engine's water pump and various auxiliary equipment via the damper and the endless belt. There is.
上記ダンパにおいてハブ１、質量体２およびバ
ネ部材３はそれぞれ単純な円環形に成形され、バ
ネ部材３をハブ１と質量体２の間に加硫接着また
は圧入することによつて一体に組み付けられてい
るが、この構成故に次の問題が指摘される。
In the above damper, the hub 1, the mass body 2, and the spring member 3 are each formed into a simple annular shape, and the spring member 3 is integrally assembled between the hub 1 and the mass body 2 by vulcanization bonding or press-fitting. However, due to this configuration, the following problems are pointed out.
すなわちバネ部材３が疲労などによつて破損し
た場合、直ちにハブ１が質量体２に対して空廻り
してトルクの伝達が停止されることからこれに伴
なつてウオーターポンプや補機類の作動が止まつ
てエンジンが停止したりエンジンに焼付きなどの
破損を生じる虞がある。またバネ部材が破損する
と質量体の唯一の支持構造が無くなつてしまうた
めに質量体がクランクシヤフトの外周から軸方向
に飛び出し、飛び出した先にある機器またはボン
ネツトにぶつかつてこれらを壊す虞がある。質量
体の飛び出しは回転の慣性によるもので、その衝
撃荷重は相当大きなものである。 In other words, if the spring member 3 is damaged due to fatigue or the like, the hub 1 immediately spins around with respect to the mass body 2 and torque transmission is stopped, which causes the operation of the water pump and auxiliary equipment to stop. There is a risk that the engine may stop and cause damage such as seizure of the engine. Furthermore, if the spring member is damaged, the only supporting structure for the mass body is lost, and the mass body may axially protrude from the outer periphery of the crankshaft, colliding with equipment or the bonnet in front of it and damaging them. . The protrusion of the mass body is due to rotational inertia, and the impact load is quite large.
本考案は以上の点に鑑み、上記従来技術のみら
れる問題を解消すべく案出されたものであつて、
この目的を達成するため、ハブの外周側に質量体
を離間配置し、前記ハブと前記質量体の間にゴム
状弾性材製のバネ部材を介装してなるダンパにお
いて、前記ハブの外径部と前記質量体の内径部に
それぞれ凸部を設けて前記バネ部材の破損時に回
転方向に係合する、廻り止めを設け、前記ハブの
外径部と前記質量体の内径部を全周にわたつて平
行なテーパ状にするとともに前記ハブの外径部に
おける軸方向一方の端縁の外径寸法を前記質量体
の内径部における軸方向他方の端縁の内径寸法よ
り大きくして前記バネ部材の破損時に軸方向に係
合する抜け止めを設けることにした。
In view of the above points, the present invention has been devised to solve the problems found in the above-mentioned prior art.
To achieve this purpose, in a damper, a mass body is arranged at a distance on the outer circumferential side of a hub, and a spring member made of a rubber-like elastic material is interposed between the hub and the mass body. and a convex part on the inner diameter part of the mass body, respectively, to provide a detent that engages in the rotational direction when the spring member is damaged, and the outer diameter part of the hub and the inner diameter part of the mass body are provided around the entire circumference. The spring member is formed into a parallel tapered shape across the body, and the outer diameter of one axial end edge of the outer diameter portion of the hub is larger than the inner diameter dimension of the other axial end edge of the inner diameter portion of the mass body. We decided to provide a retainer that engages in the axial direction when the
ハブと質量体はともに鋳鉄や鈑金などの剛体に
よつて成形され、両部材を直接回転方向に係合さ
せることにより廻り止めを設定することができ
る。本考案はこの点に着目し、ハブと質量体に互
いに回転方向に係合する凸部を設けたものであ
る。また併せて両部材を直接軸方向に係合させる
ことにより抜け止めを設定することができること
に着目してハブと質量体に互いに軸方向に係合す
るテーパを設けたものである。
Both the hub and the mass body are formed of rigid bodies such as cast iron or sheet metal, and rotation can be prevented by directly engaging the two members in the rotational direction. The present invention focuses on this point and provides the hub and the mass body with protrusions that engage with each other in the rotational direction. In addition, the hub and the mass body are provided with tapers that engage with each other in the axial direction, focusing on the fact that the hub and the mass body can be prevented from coming off by directly engaging the two members in the axial direction.
つぎに本考案の実施例を図面にしたがつて説明
する。
Next, embodiments of the present invention will be described with reference to the drawings.
第１図および第２図に示すようにハブ１の外周
の所要の質量を備える質量体２、振動リングが離
間配置され、該ハブ１と質量体２の間に所要のバ
ネ定数を備えるゴム状弾性材製のバネ部材３を介
装されている。ハブ１の外径部にその径寸法を拡
縮して多数（図では８等配）の凸部１ａが形成さ
れ、質量体２の内径部に前記ハブ１の外径部との
間隔を全周にわたつて均一に保つようにして多数
の凸部２ａが形成されており、この両凸部１ａ，
２ａを回転方向に係合可能に組み合わせ、すなわ
ちハブ１側の凸部１ａの最大外径寸法l1を質量体
２側の凸部２ａの最小内径寸法l2より大きく設定
することによりバネ部材３破損時の応急的に作動
する廻り止め（トルク伝達部）が構成されてい
る。バネ部材３はハブ１と質量体２の間の蛇行形
の空間に加硫接着や圧入によつて充填されるが耐
久性の観点から無理な応力を生じさせないように
加硫接着することが望ましい。ハブ１は鈑金、質
量体２は鋳鉄製になり、質量体２の外径部には従
来と同様にプーリ溝２ｂが設けられている。 As shown in FIGS. 1 and 2, a mass body 2 having a required mass on the outer periphery of a hub 1, a vibration ring spaced apart from each other, and a rubber-shaped body having a required spring constant between the hub 1 and the mass body 2. A spring member 3 made of an elastic material is interposed. A large number (8 equally spaced in the figure) of convex portions 1a are formed on the outer diameter of the hub 1 by expanding and contracting its diameter, and the inner diameter of the mass body 2 has a distance from the outer diameter of the hub 1 to the entire circumference. A large number of convex portions 2a are formed so as to be uniform throughout the area, and both convex portions 1a,
2a so that they can be engaged in the rotational direction, that is, by setting the maximum outer diameter l1 of the protrusion 1a on the hub 1 side to be larger than the minimum inner diameter l2 of the protrusion 2a on the mass body 2 side, the spring member 3 A rotation stopper (torque transmission section) is configured that operates temporarily in the event of damage. The spring member 3 is filled in the meandering space between the hub 1 and the mass body 2 by vulcanization bonding or press fitting, but from the viewpoint of durability, it is preferable to vulcanize bonding so as not to cause excessive stress. . The hub 1 is made of sheet metal, the mass body 2 is made of cast iron, and the mass body 2 is provided with a pulley groove 2b on its outer diameter as in the conventional case.
上記ダンパはハブ１と質量体２に相対的な廻り
止めを構成してハブ１の空廻りを防止することが
できるが、更にバネ部材３の破損時に質量体２が
ハブ１から抜脱してフロント側へ飛び出すのを防
止する構造を備えている。すなわち第２図に示す
ようにハブ１の外径部と質量体２の内径部を全周
にわたつて平行なテーパ状に成形し、かつハブ１
外径部のフトント側（図上左側）端縁の外径寸法
l1を質量体２内径部のシヤフト（エンジン）側
（図上右側）端縁の内径寸法l3より大きく設定し
てなり、バネ部材３の破損時にハブ１と質量体２
が直接軸方向に係合して質量体２がフロント側へ
飛び出すのを防ぐものである。 The above damper can prevent the hub 1 from spinning by forming a relative rotation stopper between the hub 1 and the mass body 2, but furthermore, when the spring member 3 is damaged, the mass body 2 may come off from the hub 1 and the front It has a structure that prevents it from jumping out to the side. That is, as shown in FIG. 2, the outer diameter part of the hub 1 and the inner diameter part of the mass body 2 are formed into parallel tapered shapes over the entire circumference,
Outer diameter dimension of the end edge of the outer diameter section (on the left side in the diagram)
l 1 is set larger than the inner diameter dimension l 3 of the end edge of the shaft (engine) side (right side in the figure) of the inner diameter part of the mass body 2, so that when the spring member 3 is damaged, the hub 1 and the mass body 2
are directly engaged in the axial direction to prevent the mass body 2 from protruding toward the front side.
本考案のダンパは以上説明したようにバネ部材
が破損してもトルク伝達を続けることができよう
にしたもので、従来技術にみられたエンジンの停
止や焼付きなどの不都合が発生するのを未然に防
止することができる。またバネ部材が破損しても
質量体がクランクシヤフトの外周から軸方向に飛
び出すことが無いようにしたために、質量体が飛
び出した先にある機器またはボンネツトにぶつか
つてこれらを壊すのを未然に防止することができ
る。
As explained above, the damper of the present invention is designed to continue transmitting torque even if the spring member is damaged, thereby avoiding problems such as engine stoppage and seizure that occur with conventional technology. This can be prevented. In addition, even if the spring member is damaged, the mass body will not fly out in the axial direction from the outer periphery of the crankshaft, which prevents the mass body from colliding with and damaging equipment or the bonnet in front of it. can do.
第１図は本考案の実施例に係るダンパの半裁正
面図、第２図は半裁断面図、第３図は従来例に係
るダンパの半裁正面図、第４図は半裁断面図であ
る。
１……ハブ、１ａ，２ａ……凸部、２……質量
体、２ｂ……プーリ溝、３……バネ部材。
FIG. 1 is a half-cut front view of a damper according to an embodiment of the present invention, FIG. 2 is a half-cut sectional view, FIG. 3 is a half-cut front view of a damper according to a conventional example, and FIG. 4 is a half-cut sectional view. DESCRIPTION OF SYMBOLS 1... Hub, 1a, 2a... Convex part, 2... Mass body, 2b... Pulley groove, 3... Spring member.
Claims (1)
ハブ１と前記質量体２の間にゴム状弾性材製のバ
ネ部材３を介装してなるダンパにおいて、 前記ハブ１の外径部と前記質量体２の内径部に
それぞれ凸部１ａ，２ａを設けて前記バネ部材３
の破損時に回転方向に係合する廻り止めを設け、 前記ハブ１の外径部と前記質量体２の内径部を
全周にわたつて平行なテーパ状にするとともに前
記ハブ１の外径部における軸方向一方の端縁の外
径寸法を前記質量体２の内径部における軸方向他
方の端縁の内径寸法より大きくして前記バネ部材
３の破損時に軸方向に係合する抜け止めを設けた
こと特徴とするダンパ。[Claims for Utility Model Registration] A damper in which a mass body 2 is arranged at a distance on the outer circumferential side of a hub 1, and a spring member 3 made of a rubber-like elastic material is interposed between the hub 1 and the mass body 2. , Protrusions 1a and 2a are provided on the outer diameter part of the hub 1 and the inner diameter part of the mass body 2, respectively, so that the spring member 3
A detent is provided that engages in the rotational direction when the hub 1 is damaged, and the outer diameter portion of the hub 1 and the inner diameter portion of the mass body 2 are tapered parallel to each other over the entire circumference, and the outer diameter portion of the hub 1 is The outer diameter of one end in the axial direction is made larger than the inner diameter of the other end in the axial direction in the inner diameter portion of the mass body 2 to provide a retainer that engages in the axial direction when the spring member 3 is damaged. A damper with this feature.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1988105391U JPH0544600Y2 (en) | 1988-08-11 | 1988-08-11 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1988105391U JPH0544600Y2 (en) | 1988-08-11 | 1988-08-11 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0227046U JPH0227046U (en) | 1990-02-22 |
| JPH0544600Y2 true JPH0544600Y2 (en) | 1993-11-12 |
Family
ID=31337962
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1988105391U Expired - Lifetime JPH0544600Y2 (en) | 1988-08-11 | 1988-08-11 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0544600Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2015014298A (en) * | 2013-07-03 | 2015-01-22 | Nok株式会社 | Rotational fluctuation absorbing damper |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58170944A (en) * | 1982-03-31 | 1983-10-07 | Tokai Rubber Ind Ltd | Cylindrical torsional damper |
-
1988
- 1988-08-11 JP JP1988105391U patent/JPH0544600Y2/ja not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58170944A (en) * | 1982-03-31 | 1983-10-07 | Tokai Rubber Ind Ltd | Cylindrical torsional damper |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0227046U (en) | 1990-02-22 |
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