JP2008255975A - Vibration damping washer - Google Patents

Vibration damping washer Download PDF

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Publication number
JP2008255975A
JP2008255975A JP2007112870A JP2007112870A JP2008255975A JP 2008255975 A JP2008255975 A JP 2008255975A JP 2007112870 A JP2007112870 A JP 2007112870A JP 2007112870 A JP2007112870 A JP 2007112870A JP 2008255975 A JP2008255975 A JP 2008255975A
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vibration
damping base
elastic plate
vibration washer
washer according
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Seizo Watanabe
誠三 渡辺
Yoshimichi Okazaki
義路 岡崎
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Uchiyama Manufacturing Corp
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Uchiyama Manufacturing Corp
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/14Arrangements of injectors with respect to engines; Mounting of injectors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/85Mounting of fuel injection apparatus
    • F02M2200/858Mounting of fuel injection apparatus sealing arrangements between injector and engine

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Vibration Prevention Devices (AREA)
  • Springs (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Bolts, Nuts, And Washers (AREA)
  • Gasket Seals (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration damping washer with a wide degree of freedom in design such as selection of an elastic modulus or the like, excellent in application aptitude for a portion like a supporting part of an injector on which a vibration load is repeatedly applied. <P>SOLUTION: The vibration damping washer is provided between two counter plane surfaces 1b, 2a two members 1, 2 on which the load is applied, and composed of an annular composite 6 formed by integrating an elastic plate material 4 formed in an annular shape and a vibration damping base material layer 5 made of rubber or resin. The elastic plate material 4 includes undulate shape parts 4a, 4b, 4c shaped in a direction "a" for the load being applied, and is provided with a plurality of through-holes 4d along the circumference. Part of a plate surface of the elastic plate material 4 is exposed from the vibration damping base material layer 5 or covered with a thin film of the vibration damping base material layer 5, and the elastic plate material 4 is buried in the vibration damping base material layer 5 in a state of the vibration damping base material layer 5 engaging in the through-hole 4d. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

本発明は、例えば、エンジン等の内燃機関における直噴式の燃料噴射装置(インジェクター)をシリンダヘッドにおいて支持する部分に挟装される制振ワッシャに関する。   The present invention relates to a vibration washer that is sandwiched by a portion that supports a direct injection type fuel injection device (injector) in an internal combustion engine such as an engine in a cylinder head.

自動車用エンジンにおいては、ロッカーカバーやオイルパン等のカバー部材のシリンダヘッド或いはシリンダブロックに対するボルトによる取付部にシールワッシャが挟装される。また、シリンダヘッドにインジェクターをその燃料噴射口が燃焼室に臨むよう支持し、この支持部分には燃焼ガスの外部への漏出を防止するシールワッシャが挟装される。これらのシールワッシャは、挟装部をシールすると共に、防音防振効果が期待されるものであり、特許文献1及び特許文献2には、このようなシール部材としてのシールワッシャが開示されている。特許文献1及び特許文献2に開示されたシールワッシャは、いずれも金属製のバネ性芯材にゴム等の弾性材を一体としたものであり、長期にわたりシール性及び防振性を維持し得るものである。特に、特許文献2のシールワッシャは、エンジンヘッド部の2平面間の隙間に挟装されるもので、インジェクター自体が燃焼圧の影響で軸方向上下に振動することによる上記隙間の広狭変動に対する追随性を維持し、長期間にわたりシールできるものとされている。   In an automobile engine, a seal washer is sandwiched between a cylinder head of a cover member such as a rocker cover or an oil pan, or a mounting portion by a bolt with respect to a cylinder block. Further, an injector is supported on the cylinder head so that its fuel injection port faces the combustion chamber, and a seal washer for preventing leakage of combustion gas to the outside is sandwiched in this supporting portion. These seal washers seal the sandwiched portion and are expected to have a soundproof and vibration-proof effect. Patent Documents 1 and 2 disclose such seal washers as seal members. . The seal washers disclosed in Patent Document 1 and Patent Document 2 are both made by integrating an elastic material such as rubber with a metal spring-like core material, and can maintain sealability and vibration isolation properties over a long period of time. Is. In particular, the seal washer disclosed in Patent Document 2 is sandwiched in a gap between two planes of the engine head portion, and follows the fluctuation in the gap due to the injector itself vibrating vertically in the axial direction under the influence of combustion pressure. It is supposed that it can maintain its properties and can be sealed for a long time.

また、特許文献3には、金網の空隙をゴムで充填した複合材料シートからなるインジェクター用ガスケットが開示されている。
実開昭63−158615号公報 特開2004−36775号公報 特開2006−71023号公報
Patent Document 3 discloses an injector gasket made of a composite material sheet in which a gap in a wire mesh is filled with rubber.
Japanese Utility Model Publication No. 63-158615 JP 2004-36775 A JP 2006-71023 A

特許文献1及び2のシールワッシャは、シール部(リップ部)のつぶし代範囲とバネ性芯材(ワッシャ座金)のU字状曲折部とにより上記隙間の広狭変動に追随させんとするもので、その変形幅が大きいことから、隙間の広狭変動が大きくてもシール性の維持が図られる。而して、これらの場合、荷重を受ける部分にゴムが介在する為、ゴムのへたりが発生し軸力の低下が起こる。また、特許文献3に開示されたインジェクター用ガスケットは、ゴムが金網の空隙に充填されるから、金網の担持力によりそのへたりが抑えられるが、荷重方向に対する金網の弾性範囲が狭く制振機能を高めるには、上記シートを複数枚重ねることが必要となる。そして、これら特許文献1〜3に開示されたシールワッシャ或いはインジェクター用ガスケットにおいては、制振機能を担う弾性率が、バネ性芯材或いは金網の仕様(芯材の板厚、曲げ加工態様、金網の線径、編み方等)に大きく依存する為、その弾性率選定等の設計自由度が狭く、上記のような制振ワッシャへの応用には、一層の改善が望まれていた。   The seal washers of Patent Documents 1 and 2 are intended to follow the fluctuation of the gap by the crushing margin range of the seal part (lip part) and the U-shaped bent part of the spring core material (washer washer). Since the deformation width is large, the sealing performance can be maintained even if the gap variation is large. Thus, in these cases, since rubber is interposed in the portion that receives the load, rubber sag occurs, and the axial force is reduced. In addition, since the gasket for an injector disclosed in Patent Document 3 is filled with rubber in the gap of the wire mesh, the sag of the wire mesh is suppressed by the holding force of the wire mesh, but the elastic range of the wire mesh with respect to the load direction is narrow. In order to increase the number, it is necessary to stack a plurality of the sheets. And in these gaskets for seal washers or injectors disclosed in Patent Documents 1 to 3, the elastic modulus responsible for the damping function is the specification of the spring core material or wire mesh (the thickness of the core material, the bending mode, the wire mesh). The degree of freedom in design such as elastic modulus selection is narrow, and further improvement has been desired for application to the above-described vibration washer.

本発明は、上記のような実情に鑑みなされたもので、弾性率選定等の設計自由度が広く、インジェクターの支持部のように繰り返し振動荷重が負荷される部分での応用適性に優れた制振ワッシャを提供することを目的としている。   The present invention has been made in view of the above circumstances, and has a wide design freedom such as elastic modulus selection, and is excellent in application suitability in a portion where a repeated vibration load is applied, such as a support portion of an injector. The purpose is to provide a shaking washer.

本発明に係る制振ワッシャは、荷重が負荷される2つの部材の対向する2平面間に挟装される制振ワッシャであって、環状に形成された弾性板材とゴム又は樹脂からなる制振基材層とを一体とした環状複合体からなり、上記弾性板材は、上記荷重が負荷される方向に賦形された起伏形状部を含み、且つ周方向に沿って複数の透孔を備え、上記弾性板材は、その板面の一部が制振基材層より露出乃至は制振基材層の薄膜で覆われると共に上記透孔内に制振基材層が係入した状態で制振基材層に埋入されていることを特徴とする。   The vibration damping washer according to the present invention is a vibration damping washer sandwiched between two opposing flat surfaces of two members to which a load is applied, and is composed of an elastic plate member formed in an annular shape and rubber or resin. It consists of an annular composite integrated with a base material layer, and the elastic plate material includes an undulating shape portion shaped in the direction in which the load is applied, and has a plurality of through holes along the circumferential direction, The elastic plate material is partly exposed from the vibration damping base material layer or covered with a thin film of the vibration damping base material layer, and the vibration damping material layer is engaged in the through hole. It is embedded in the base material layer.

本発明において、前記弾性板材は、内周側部分及び外周側部分の段違い状平板部と、両平板部を繋ぐ傾斜板部とよりなる皿ばね状部材からなり、上記段違い状平板部と傾斜板部とにより前記起伏形状部が形成されるよう構成されたものとすることができる。また、前記弾性板材は、平板部と山形状部とよりなり、この平板部と山形状部とにより前記起伏形状部が形成されるよう構成されたものとすることもできる。この場合、前記山形状部が、前記弾性板材の周方向に沿って連続的な突条体や、複数の不連続山部からなるものとすることができる。更に、前記弾性板材は、山部と谷部とが周方向に繰り返す波形部材からなり、前記起伏形状部が、この山部と谷部とにより形成されるよう構成されたものとすることもできる。   In the present invention, the elastic plate material comprises a disc spring-like member comprising a stepped flat plate portion on the inner peripheral side portion and the outer peripheral side portion, and an inclined plate portion connecting both flat plate portions, and the stepped flat plate portion and the inclined plate. The undulating shape portion may be formed by the portion. Further, the elastic plate member may be composed of a flat plate portion and a mountain-shaped portion, and the undulating shape portion may be formed by the flat plate portion and the mountain-shaped portion. In this case, the mountain-shaped portion may be a continuous ridge body or a plurality of discontinuous mountain portions along the circumferential direction of the elastic plate member. Further, the elastic plate member may be formed of a corrugated member in which a peak portion and a valley portion repeat in the circumferential direction, and the undulating shape portion may be formed by the peak portion and the valley portion. .

また、前記透孔は、円形であって周方向に等間隔で形成されているもの、或いは、矩形状であって周方向に等間隔且つ周方向に配向するよう形成されているものとすることができる。更に、前記環状複合体の外周部の少なくとも前記2平面に対面する部位には金属製リング部材が一体とされているものとしても良い。そして、前記環状複合体の内周部に、前記制振基材層によるグロメット部が形成されているものとしても良い。   Further, the through holes are circular and are formed at equal intervals in the circumferential direction, or are rectangular and are formed so as to be oriented at equal intervals in the circumferential direction and in the circumferential direction. Can do. Furthermore, a metal ring member may be integrated with at least a portion of the outer peripheral portion of the annular composite facing the two planes. And the grommet part by the said damping base material layer is good also as what is formed in the inner peripheral part of the said cyclic | annular composite_body | complex.

本発明に係る制振ワッシャは、インジェクターのような振動する装置を支持する部位、即ち、荷重が負荷される2つの部材の対向する2平面間にこれを挟装するよう用いれば、弾性板材とこれに一体とされたゴム又は樹脂からなる制振基材層との相乗作用によって、振動が吸収され、振動による異音発生が抑制される。また、制振基材層内に埋入された状態の弾性板材と制振基材層とが相乗したゴム弾性又は樹脂特有の弾性作用により、挟装時の2平面間の相互の面圧が発現し、そのシール性が得られる。しかも、弾性板材は、その板面の一部がエラストマー層より露出乃至は制振基材層の薄膜で覆われているから、上記荷重の弾性板材に負荷される割合が大きく、制振基材層のへたりが大幅に軽減され、長く振動吸収機能及びシール性が維持される。更に、透孔内に制振基材層の一部が係入し、そのアンカー効果により、弾性板材と制振基材層との強固な一体化が図られる。そして、弾性板材に形成される透孔の大きさ及び数を変えることにより、弾性板材と制振基材層とが複合した環状複合体の弾性率(ばね定数)の適宜選定が可能となり、設計自由度が広がり、インジェクターの支持部のように振動荷重の負荷態様が多様な部分での応用適性が増大する。   The vibration washer according to the present invention is a part that supports a vibrating device such as an injector, that is, if it is used so as to be sandwiched between two opposing planes of two members to be loaded, an elastic plate material and Vibration is absorbed by the synergistic action with the vibration damping base material layer made of rubber or resin integrated therewith, and generation of abnormal noise due to vibration is suppressed. In addition, due to rubber elasticity or resin-specific elastic action in which the elastic plate material embedded in the damping base layer and the damping base layer are synergistic, the mutual surface pressure between the two planes during clamping is It develops and its sealing property is obtained. In addition, since the elastic plate material is partially exposed from the elastomer layer or covered with a thin film of the vibration damping base material layer, the ratio of the load applied to the elastic plate material is large. The sag of the layer is greatly reduced, and the vibration absorbing function and the sealing performance are maintained for a long time. Furthermore, a part of the vibration damping base material layer is inserted into the through hole, and the elastic plate material and the vibration damping base material layer are firmly integrated by the anchor effect. Then, by changing the size and number of the through holes formed in the elastic plate material, it becomes possible to appropriately select the elastic modulus (spring constant) of the annular composite in which the elastic plate material and the damping base material layer are combined. The degree of freedom is widened, and the aptitude for application is increased in a portion where the load mode of the vibration load is various, such as the support portion of the injector.

前記弾性板材を、内周側部分及び外周側部分の段違い状平板部と、両平板部を繋ぐ傾斜板部とよりなる皿ばね状部材からなるもの、或いは、平板部と山形状部とよりなるもの、更には、山部と谷部とが周方向に繰り返す波形部材からなるものとすれば、これらの形状的特性に応じた、環状複合体の弾性率の適宜選定が可能となり、より設計自由度が広がる。平板部と山形状部とよりなるものとする場合は、山形状部を連続的なものとするか不連続なものとするかによっても、弾性率の多様な設定が可能となる。更に、弾性板材の弾性を担う主たる部位としてのこれら起伏形状部と、透孔の形成態様とが密接に関連して、弾性板材の弾性率に大きく影響し、薄型でありながら、環状複合体の弾性率の選定可変範囲がより広くなる。   The elastic plate material is composed of a disc spring-like member composed of a stepped flat plate portion of the inner peripheral portion and the outer peripheral portion and an inclined plate portion connecting both flat plate portions, or a flat plate portion and a mountain-shaped portion. In addition, if it is made of a corrugated member in which a crest and a trough repeat in the circumferential direction, it is possible to appropriately select the elastic modulus of the annular composite according to these geometric characteristics, and more design freedom The degree spreads. When the flat plate portion and the mountain-shaped portion are formed, various elastic modulus settings are possible depending on whether the mountain-shaped portion is continuous or discontinuous. Further, these undulating portions as the main parts responsible for the elasticity of the elastic plate material and the formation mode of the through holes are closely related, greatly affecting the elastic modulus of the elastic plate material, and being thin, The selection variable range of the elastic modulus becomes wider.

また、前記透孔として、円形或いは矩形状であって周方向に等間隔で形成されているものとすれば、その形成が簡易であると共に、周方向に沿った均等な弾性率の発現を可能とし、後者の場合、周方向に配向するよう形成されているものとすれば、透孔の形成面積を大きく確保することができ、弾性率の選定自由度がより広がることになる。   In addition, if the through holes are circular or rectangular and are formed at equal intervals in the circumferential direction, the formation thereof is simple, and an even elastic modulus can be expressed along the circumferential direction. In the latter case, if it is formed so as to be oriented in the circumferential direction, a large formation area of the through holes can be secured, and the degree of freedom in selecting the elastic modulus is further expanded.

前記環状複合体の外周部の少なくとも前記2平面に対面する部位に金属製リング部材を一体としたものとすれば、高い反発力により高周波域での振動にも優れた制振性が得られる。更に、前記環状複合体の内周部に、前記制振基材層によるグロメット部が形成されているものとすれば、荷重が負荷される2つの部材の対向する2平面間に挟装した場合、このグロメット部の圧縮弾性変形により、シール性がより向上する。   If a metal ring member is integrated with at least a portion of the outer peripheral portion of the annular composite facing the two planes, vibration suppression in a high frequency region can be obtained due to high repulsive force. Furthermore, when the grommet part by the said damping base material layer is formed in the inner peripheral part of the said cyclic | annular composite_body | complex, when sandwiched between two opposing planes of two members to be loaded The sealing property is further improved by the compression elastic deformation of the grommet portion.

以下に本発明の最良の実施の形態について、図面に基づいて説明する。図1は本発明の制振ワッシャの一実施形態を示す平面図、図2は図1におけるX−X線矢視断面図、図3は同制振ワッシャを介してシリンダヘッドにインジェクターを支持させた状態を示す縦断面図、図4は他の実施形態の図1と同様図、図5〜図9は更に他の実施形態の図2と同様図である。   The best mode for carrying out the present invention will be described below with reference to the drawings. 1 is a plan view showing an embodiment of the vibration washer of the present invention, FIG. 2 is a cross-sectional view taken along line XX in FIG. 1, and FIG. 3 is a diagram showing a cylinder head supported by the cylinder head via the vibration washer. FIG. 4 is a view similar to FIG. 1 of another embodiment, and FIGS. 5 to 9 are views similar to FIG. 2 of another embodiment.

図3は、エンジン等の内燃機関のシリンダヘッド1に、本発明の制振ワッシャ3を介してインジェクター2を支持した状態を示し、白抜矢示方向先側が燃料の噴射口であり、この噴射口が燃焼室(不図示)に臨むものである。尚、インジェクター2の内部には、燃料の流通管路等が形成されるが、図では便宜上この図示を省略している。インジェクター2は途中に段差部2aを有する円柱形であり、シリンダヘッド1に形成された支持孔1aに挿入され、支持孔1a周囲の肩部1bに制振ワッシャ3を介して段差部2aを担持させることによりシリンダヘッド1に支持される。従って、肩部1bと、段差部2aとが、制振ワッシャ3が挟装される2つの部材(シリンダヘッド1及びインジェクター2)の対向する2平面とされる。   FIG. 3 shows a state in which an injector 2 is supported on a cylinder head 1 of an internal combustion engine such as an engine via a vibration washer 3 of the present invention. The mouth faces a combustion chamber (not shown). In addition, although the fuel distribution pipe line etc. are formed in the inside of the injector 2, this illustration is abbreviate | omitted in the figure for convenience. The injector 2 has a columnar shape having a stepped portion 2a in the middle, is inserted into a support hole 1a formed in the cylinder head 1, and carries the stepped portion 2a through a vibration washer 3 on a shoulder portion 1b around the support hole 1a. As a result, the cylinder head 1 is supported. Therefore, the shoulder portion 1b and the stepped portion 2a serve as two opposing planes of the two members (the cylinder head 1 and the injector 2) on which the damping washer 3 is sandwiched.

インジェクター2は、燃料噴射時には、その噴射動作に伴い白抜矢示方向(荷重負荷方向)a及びその反方向に振動を繰り返す。従って、上記2平面1b、2a間では、その振動に伴う衝撃音が発生し、エンジン駆動時の騒音の一因となる。然るに、この2平面1b、2a間には、制振ワッシャ3が挟装されるから、制振ワッシャ3によってその振動が抑えられ、騒音の発生が抑制される。この制振ワッシャ3の構成について、以下にその詳細を述べる。   During fuel injection, the injector 2 repeats vibration in the direction indicated by white arrow (loading direction) a and in the opposite direction in accordance with the injection operation. Therefore, an impact sound accompanying the vibration is generated between the two planes 1b and 2a, which contributes to noise during driving of the engine. However, since the damping washer 3 is sandwiched between the two planes 1b and 2a, the vibration is suppressed by the damping washer 3, and the generation of noise is suppressed. Details of the configuration of the vibration washer 3 will be described below.

図1乃至図3に示すように、本実施形態の制振ワッシャ3は、環状に形成された皿ばね状弾性板材4とゴム又は樹脂からなる制振基材層5とを一体とした環状複合体6からなる。この弾性板材4は、金属板を打抜きプレス加工したものであり、内周側部分及び外周側部分に段違い状に形成された環状平板部4a,4bと、両平板部4a,4bを繋ぐ環状傾斜板部4cとよりなる皿ばね形状とされ、段違い状平板部4a,4bと、傾斜板部4cとにより起伏形状部が賦形形成され、複数の円形の透孔4d…が両平板部4a,4bに跨るよう周方向に沿って傾斜板部4cに形成されている。両平板部4a,4bの片面(前記2平面1b、2a側の面)は、図例では制振基材層5の薄膜(厚みd;数μm〜50μm)で覆われているが、露出していても良い。そして、弾性板材4は、略全体が制振基材層5内に埋入された状態とされ、各透孔4d…内には制振基材層5が係入している。このように、両平板部4a,4bの2平面1b、2aに対面する側の面が制振基材層5より露出乃至は制振基材層5の薄膜で覆われているから、2平面1b、2aと直接若しくは制振基材層5の薄膜を介して接し、この部分では弾性板材4に対して負荷される荷重の割合が大きくなる。また、傾斜板部4cは制振基材層5内に埋入した状態であるから、弾性板材4に対する荷重の負荷は制振基材層5を介してなされる。環状複合体6の内周部には、制振基材層5によるグロメット部5aが厚み方向両側(前記2平面1b、2a側)に突出する山形ビード状に形成されている。   As shown in FIGS. 1 to 3, the vibration washer 3 of this embodiment is an annular composite in which a disc spring-like elastic plate 4 formed in an annular shape and a vibration damping base material layer 5 made of rubber or resin are integrated. It consists of a body 6. This elastic plate material 4 is obtained by punching and pressing a metal plate. An annular inclined plate connecting the flat plate portions 4a and 4b to the annular flat plate portions 4a and 4b formed in steps on the inner peripheral portion and the outer peripheral portion. The plate portion 4c has a disc spring shape, and the undulating shape portion is shaped by the stepped flat plate portions 4a and 4b and the inclined plate portion 4c, and a plurality of circular through holes 4d. It forms in the inclination board part 4c along the circumferential direction so that 4b may be straddled. One side of the flat plate portions 4a and 4b (the surfaces on the two planes 1b and 2a side) is covered with a thin film (thickness d; several μm to 50 μm) of the damping base material layer 5 in the illustrated example, but is exposed. May be. And the elastic board 4 is made into the state by which the substantially whole was embedded in the damping base material layer 5, and the damping base material layer 5 is engaging in each through-hole 4d .... In this way, since the surfaces facing the two planes 1b and 2a of both flat plate portions 4a and 4b are exposed from the damping base layer 5 or covered with the thin film of the damping base layer 5, the two planes 1b and 2a are contacted directly or through a thin film of the damping base material layer 5, and the ratio of the load applied to the elastic plate member 4 is increased in this portion. Further, since the inclined plate portion 4 c is embedded in the vibration damping base material layer 5, the load on the elastic plate material 4 is applied via the vibration damping base material layer 5. Grommet portions 5a formed of the damping base material layer 5 are formed on the inner peripheral portion of the annular composite 6 in a chevron bead shape projecting on both sides in the thickness direction (the two planes 1b and 2a sides).

本発明において、制振基材層5を構成するゴム又は樹脂としては、ゴム状の弾性体を意味する広義のエラストマー(ゴム及び熱可塑性エラストマーが含まれる)や樹脂が対象とされる。ゴムとしては、FKM、NBR、H−NBR、EPDM、CR、ACM、AEM、VMQ及びFVMQ等のゴム材が用いられる。また、熱可塑性エラストマー(以下、TPEという)としては、塩素化ポリエチレン系TPE、官能基付与型スチレン−エチレン−ブチレン−スチレンブロックコポリマー、ランダムタイプの水素添加型スチレン−ブタジエンコポリマー、イソブラント化ポリオレフィン系TPE、シンジオタクチック−1,2ポリブタジエン系TPE、スチレン系TPE、スチレン−ブタジエン−スチレンブロックコポリマー、スチレン−エチレン−ブチレン−スチレンブロックコポリマー、スチレン−エチレン−プロピレン−スチレンブロックコポリマー、スチレン−イソブチレン−スチレンブロックコポリマー、ブレンド型ポリオレフィン系TPE、ポリアミド系TPE、ポリエステル系TPE、トランス−1,4ポリイソプレン系TPE、天然ゴム系TPE、ポリオレフィン系TPE、ポリウレタン系TPE、動的加硫型ポリオレフィン系TPE、ポリ塩化ビニル系TPE等のTPE材が用いられる。更に、樹脂としては、PTFE(ポリテトラフルオロエチレン;テフロン樹脂(登録商標))、PPS(ポリフェニレンサルファイド)、PEEK(ポリエチレンエーテルケトン)、PA(ナイロン;ポリアミド)等の樹脂材が用いられる。制振基材層5は、これらのゴム材、TPE材或いは樹脂材をベースとして形成され、環状に形成された上記コイルスプリング4及び円環状金属板7を所定の金型(不図示)内に配し、未加硫或いは未硬化の上記ゴム材、TPE材或いは樹脂材を金型のキャビティ内に注入して加硫或いは硬化させることにより、環状複合体6と円環状金属板7とが一体とされた制振ワッシャ3が得られる。この成型の際に、上記平板部4a,4bの2平面1b、2aに対面する側の面にゴム材、TPE材或いは樹脂材が回り込み、上記厚みdの制振基材層5の薄膜が不可避的に形成される。この薄膜を除去して、平板部4a,4bの上記片面を制振基材層5より露出させても良いが、図のように残した状態で使用しても、へたり等の悪影響を生じることがない。尚、上記厚みdが50μmを超えると、制振基材層5のへたりが生じ易くなる。   In the present invention, the rubber or resin constituting the damping base layer 5 is a broad meaning elastomer (including rubber and thermoplastic elastomer) or resin meaning a rubber-like elastic body. As the rubber, rubber materials such as FKM, NBR, H-NBR, EPDM, CR, ACM, AEM, VMQ and FVMQ are used. Thermoplastic elastomers (hereinafter referred to as TPE) include chlorinated polyethylene-based TPE, functional group-added styrene-ethylene-butylene-styrene block copolymer, random-type hydrogenated styrene-butadiene copolymer, and iso-blunted polyolefin-based TPE. Syndiotactic-1,2 polybutadiene TPE, styrene TPE, styrene-butadiene-styrene block copolymer, styrene-ethylene-butylene-styrene block copolymer, styrene-ethylene-propylene-styrene block copolymer, styrene-isobutylene-styrene block Copolymer, blend type polyolefin TPE, polyamide TPE, polyester TPE, trans-1,4 polyisoprene TPE, natural rubber PE, polyolefin based TPE, polyurethane TPE, dynamic vulcanised polyolefin TPE, TPE material such as polyvinyl chloride-based TPE is used. Furthermore, as the resin, resin materials such as PTFE (polytetrafluoroethylene; Teflon resin (registered trademark)), PPS (polyphenylene sulfide), PEEK (polyethylene ether ketone), PA (nylon; polyamide) are used. The damping base layer 5 is formed using these rubber material, TPE material, or resin material as a base, and the coil spring 4 and the annular metal plate 7 formed in an annular shape are placed in a predetermined mold (not shown). The annular composite 6 and the annular metal plate 7 are integrated by injecting the unvulcanized or uncured rubber material, TPE material or resin material into the mold cavity and curing or curing. The vibration damping washer 3 is obtained. During this molding, a rubber material, a TPE material, or a resin material wraps around the surfaces of the flat plate portions 4a, 4b facing the two flat surfaces 1b, 2a, and the thin film of the vibration damping base material layer 5 having the thickness d is inevitable. Formed. The thin film may be removed to expose the one surface of the flat plate portions 4a and 4b from the damping base material layer 5. However, even if it is used in the state left as shown in the figure, adverse effects such as sag occur. There is nothing. If the thickness d exceeds 50 μm, the damping base material layer 5 tends to sag.

上記制振ワッシャ3は、図3に示すように、エンジン等の内燃機関のシリンダヘッド1にインジェクター2を支持する部位に挟装される。この挟装状態ではグロメット部5aが圧縮弾性変形(図3の拡大部分参照)し、その復元弾力に伴う弾性面圧によって、支持孔1a内の燃焼ガスの漏出が阻止される。また、インジェクター2の噴射動作に伴う白抜矢示方向aの振動荷重は、2平面1b、2aを介して環状複合体6に負荷される。この負荷は、弾性板材4の両平板部4a,4bを繋ぐ傾斜板部4cを圧偏する方向及び制振基材層5の厚み方向に作用し、その複合した弾性によって吸収され、振動が抑えられて騒音の発生が抑制される。特に、環状複合体6は、弾性板材4の傾斜板部4cによる弾性と制振基材層5の厚み方向の弾性とが複合した弾性を発現するから、弾性板材4のみに依存しないばね定数の小さな構造の弾性体とされる。   As shown in FIG. 3, the vibration washer 3 is sandwiched by a portion that supports the injector 2 in a cylinder head 1 of an internal combustion engine such as an engine. In this sandwiched state, the grommet portion 5a undergoes compression elastic deformation (see the enlarged portion in FIG. 3), and the leakage of combustion gas in the support hole 1a is prevented by the elastic surface pressure accompanying the restoring elasticity. Moreover, the vibration load in the white arrow direction a accompanying the injection operation of the injector 2 is applied to the annular composite 6 via the two planes 1b and 2a. This load acts in the direction in which the inclined plate portion 4c connecting the two flat plate portions 4a and 4b of the elastic plate member 4 is biased and the thickness direction of the damping base material layer 5, and is absorbed by the combined elasticity to suppress vibration. This suppresses the generation of noise. In particular, since the annular composite 6 exhibits elasticity in which the elasticity of the inclined plate portion 4 c of the elastic plate 4 and the elasticity in the thickness direction of the damping base layer 5 are combined, a spring constant that does not depend only on the elastic plate 4 is obtained. It is an elastic body with a small structure.

環状複合体6は、弾性板材4と制振基材層5との一体化により、安定な変形が得られ、ゴム状弾性或いは樹脂特有の弾性と減衰性とが相乗し優れた制振効果を発揮する。また、ゴム材、TPE材或いは樹脂材の使用により、シール機能の為のグロメット部5aの形成が容易であり、図3に示すようなインジェクター2の支持部に用いれば、支持孔1aからの燃焼ガスの漏出阻止も確実になされる。そして、弾性板材4の復元弾力により、制振基材層5のへたりが抑えられるから、長く振動吸収機能及びシール性が維持される。しかも、弾性板材4は、周方向に複数の透孔4d…を備えているから、弾性板材4の一部のみが荷重を受ける構造となり、これによって、環状複合体6のばね定数の設定がし易く、使用条件に応じた設計自由度が広くなる。また、両平板部4a,4bの片面が制振基材層5より露出乃至は制振基材層5の薄膜で覆われるよう構成されるから、この両平板部4a,4bの片面により荷重の多くを受けることになり、制振基材層5のへたり抑止効果が助長される。弾性板材4と一体とされる制振基材層5は、上記透孔4d…内に係入し、そのアンカー効果により強固な一体化が図られ、薄型でありながら、ばね定数が小さく、耐久性の優れた制振ワッシャ3が得られる。   The annular composite 6 can be stably deformed by the integration of the elastic plate member 4 and the vibration damping base material layer 5, and has an excellent vibration damping effect by synergistic rubber-like elasticity or resin-specific elasticity and damping. Demonstrate. In addition, the use of a rubber material, a TPE material, or a resin material makes it easy to form the grommet portion 5a for the sealing function, and if used for the support portion of the injector 2 as shown in FIG. 3, combustion from the support hole 1a. Gas leakage is also reliably prevented. And since the sag of the damping base material layer 5 is suppressed by the restoring elasticity of the elastic plate member 4, the vibration absorbing function and the sealing performance are maintained for a long time. In addition, since the elastic plate 4 is provided with a plurality of through holes 4d in the circumferential direction, only a part of the elastic plate 4 is subjected to a load, whereby the spring constant of the annular composite 6 is set. It is easy and the degree of freedom in design according to the use conditions is widened. Further, since one surface of both flat plate portions 4a and 4b is configured to be exposed from the vibration damping base material layer 5 or covered with a thin film of the vibration damping base material layer 5, the load on the one surface of both flat plate portions 4a and 4b is reduced. A large amount is received, and the effect of suppressing the sag of the vibration damping base material layer 5 is promoted. The damping base material layer 5 integrated with the elastic plate member 4 is inserted into the through-holes 4d, and is firmly integrated by the anchor effect. Although it is thin, it has a small spring constant and is durable. A vibration washer 3 having excellent properties can be obtained.

図4は、本発明の制振ワッシャの別の実施形態を示す。図4の制振ワッシャ3においては、透孔4d…の形状が矩形状である点で上記と異なる。図例では各辺が直線状の略台形状であることを示しているが、曲線状の各辺による矩形状であっても良い。また、この矩形状の透孔4d…は、周方向に傾いた状態、即ち同一周方向に配向した状態で且つ等間隔に形成されている。上記実施形態のように透孔4dを円形とする場合は、パンチング治具として汎用のものが使用できるので加工に有利であるが、透孔4dを本実施形態のような形成態様にすれば、その形成面積を大きく確保し易く、これにより、弾性板材4の弾性率の選定自由度がより広がる。その他の構成は上記と同様であるから、共通部分に同一の符号を付し、その説明を割愛する。   FIG. 4 shows another embodiment of the vibration washer of the present invention. 4 is different from the above in that the shape of the through holes 4d is rectangular. In the illustrated example, each side has a substantially trapezoidal shape that is linear, but a rectangular shape with each curved side may be used. Further, the rectangular through holes 4d are formed at equal intervals in a state inclined in the circumferential direction, that is, in a state oriented in the same circumferential direction. When the through-hole 4d is circular as in the above embodiment, a general-purpose punching jig can be used, which is advantageous for processing. However, if the through-hole 4d is formed as in this embodiment, It is easy to ensure a large formation area, thereby further expanding the degree of freedom in selecting the elastic modulus of the elastic plate member 4. Since other configurations are the same as described above, common portions are denoted by the same reference numerals, and descriptions thereof are omitted.

図5〜図9は更に別の実施形態を示す。図5に示す制振ワッシャ3では、上記同様の複合環状体6の上下両面(前記2平面1b,2aに対面する部位)に、円環状金属板(金属製リング部材)7が一体とされている。その他の構成は上記と同様である。このような制振ワッシャ3も、図3に示すように、エンジン等の内燃機関のシリンダヘッド1にインジェクター2を支持する部位に挟装される。この挟装状態では上記同様グロメット部5aが圧縮弾性変形し、その復元弾力に伴う弾性面圧よって、支持孔1a内の燃焼ガスの漏出が阻止される。また、インジェクター2の噴射動作に伴う白抜矢示方向aの振動荷重は、円環状金属板7を介して環状複合体6に負荷される。従って、円環状金属板7に荷重が直接負荷されることになるから、耐荷重が大となる。そして、この負荷は、弾性板材4の傾斜板部4cを圧偏する方向及び制振基材層5の厚み方向に作用し、その複合した弾性によって吸収され、振動が抑えられて騒音の発生が抑制される。尚、図5では弾性板材4の段違い状平板部4a,4bの上下両面に円環状金属板7が密着的に一体とした例を示しているが、円環状金属板7とこの平板部4a,4bとの間に制振基材層5による薄膜が介在されていても良い。
この実施形態は、図1乃至図4に示すいずれの実施形態にも適用される。また、その他の構成は上記と同様であるので、共通部分に同一の符号を付し、ここでもその説明を割愛する。
5 to 9 show still another embodiment. In the vibration washer 3 shown in FIG. 5, an annular metal plate (metal ring member) 7 is integrally formed on the upper and lower surfaces (portions facing the two planes 1b and 2a) of the composite annular body 6 similar to the above. Yes. Other configurations are the same as described above. As shown in FIG. 3, such a vibration washer 3 is also sandwiched by a portion that supports the injector 2 in a cylinder head 1 of an internal combustion engine such as an engine. In this sandwiched state, the grommet portion 5a is compressed and elastically deformed as described above, and the leakage of the combustion gas in the support hole 1a is prevented by the elastic surface pressure accompanying the restoring elasticity. Further, the vibration load in the white arrow direction a accompanying the injection operation of the injector 2 is applied to the annular composite 6 via the annular metal plate 7. Accordingly, the load is directly applied to the annular metal plate 7, and the load resistance is increased. This load acts in the direction in which the inclined plate portion 4c of the elastic plate member 4 is biased and the thickness direction of the damping base layer 5, and is absorbed by the combined elasticity to suppress vibrations and generate noise. It is suppressed. 5 shows an example in which the annular metal plate 7 is closely integrated with the upper and lower surfaces of the stepped flat plate portions 4a, 4b of the elastic plate member 4. However, the annular metal plate 7 and the flat plate portions 4a, 4a, 4b, The thin film by the damping base material layer 5 may be interposed between 4b.
This embodiment is applied to any of the embodiments shown in FIGS. In addition, since the other configuration is the same as described above, the same reference numerals are given to the common parts, and the description thereof is omitted here.

図6に示す制振ワッシャ3は、前記弾性板材4が、内外周部に位置する平板部4eと弾性板材4の周方向に沿って連続的な突条体の山形状部4fとよりなり、この平板部4eと山形状部4fとにより前記起伏形状部が形成され、山形状部4fに、内外周部の平板部4eに跨る状態で透孔4dが形成されている。弾性板材4は、上記同様制振基材層5に略全体が埋入された状態で一体化され、環状複合体6が構成される。平板部4eの下面(シリンダヘッド1の肩部1b側の面)と、山形状部4fの頂面(インジェクター2の段差部2a側の面)は、制振基材層5より露出乃至は制振基材層5の薄膜で覆われるよう構成されている。また、環状複合体6の上下両面には、円環状金属板7が一体とされている。従って、図3のような使用状態においては、円環状金属板7に荷重が直接負荷されることになるから、耐荷重が大となる。そして、この負荷は、弾性板材4の山形状部4fを圧偏する方向及び制振基材層5の厚み方向に作用し、上記同様その複合した弾性によって吸収され、振動が抑えられて騒音の発生が抑制される。   In the vibration washer 3 shown in FIG. 6, the elastic plate member 4 is composed of a flat plate portion 4e located on the inner and outer peripheral portions and a mountain-shaped portion 4f of a continuous ridge body along the circumferential direction of the elastic plate member 4, The undulating shape portion is formed by the flat plate portion 4e and the mountain-shaped portion 4f, and a through-hole 4d is formed in the mountain-shaped portion 4f so as to straddle the flat plate portion 4e at the inner and outer peripheral portions. The elastic plate material 4 is integrated in a state where substantially the whole is embedded in the vibration damping base material layer 5 as described above, and the annular composite 6 is configured. The lower surface of the flat plate portion 4e (the surface on the shoulder 1b side of the cylinder head 1) and the top surface of the mountain-shaped portion 4f (the surface on the stepped portion 2a side of the injector 2) are exposed or controlled by the damping base material layer 5. The vibration base layer 5 is configured to be covered with a thin film. An annular metal plate 7 is integrated on the upper and lower surfaces of the annular composite 6. Therefore, in the use state as shown in FIG. 3, since the load is directly applied to the annular metal plate 7, the load resistance is increased. This load acts in the direction of pressure-biasing the mountain-shaped portion 4f of the elastic plate member 4 and the thickness direction of the damping base layer 5, and is absorbed by the combined elasticity as described above to suppress vibrations and reduce noise. Occurrence is suppressed.

図7に示す制振ワッシャ3は、図6の例の変形例であって、弾性板材4が周方向に沿って連続的な2条の同心状突条体からなる山形状部4fを備え、その内外周部及び両山形状部4f間に平板部4eが形成されたものである。3条の平板部4eと2条の山形状部4fとにより起伏形状部が形成され、各山形状部4fに、両側の平板部4eに跨る状態で透孔4dが形成されている。弾性板材4は、上記同様制振基材層5に略全体が埋入された状態で一体化されて環状複合体6が構成される。平板部4eの下面と、山形状部4fの頂面は、制振基材層5より露出乃至は制振基材層5の薄膜で覆われるよう構成されている。また、環状複合体6の上下両面には、円環状金属板7が一体とされている。このように、2条の山形状部4fを形成することにより、環状複合体6の弾性率の設定自由度がより広くなる。   The vibration washer 3 shown in FIG. 7 is a modification of the example of FIG. 6, and the elastic plate member 4 includes a mountain-shaped portion 4 f composed of two concentric protrusions continuous along the circumferential direction. A flat plate portion 4e is formed between the inner and outer peripheral portions and the both mountain shaped portions 4f. An undulating shape portion is formed by the three flat plate portions 4e and the two mountain-shaped portions 4f, and through holes 4d are formed in each mountain-shaped portion 4f so as to straddle the flat plate portions 4e on both sides. The elastic plate member 4 is integrated in a state in which the elastic plate member 4 is substantially entirely embedded in the vibration damping base material layer 5 to form the annular composite 6. The lower surface of the flat plate portion 4e and the top surface of the mountain-shaped portion 4f are configured to be exposed or covered with a thin film of the vibration damping base material layer 5 from the vibration damping base material layer 5. An annular metal plate 7 is integrated on the upper and lower surfaces of the annular composite 6. Thus, by forming the two mountain-shaped portions 4f, the degree of freedom of setting the elastic modulus of the annular composite 6 becomes wider.

図8に示す制振ワッシャ3は、図6の例の更に別の変形例であって、上記山形状部4fが、複数の不連続山部からなる。即ち、弾性板材4の平板部4eに、その周方向に沿って複数の山部を独立的に賦形形成して山形状部4fとなし、この複数の山部からなる山形状部4fとその周辺部の平板部4eとにより起伏形状部が形成され、各山形状部4fに、両側の平板部4eに跨る状態で透孔4dが形成されている。この山形状部4fは、周方向に1列に配列されているものに限らず、複数列に配列されているものであっても良い。その他の構成は、図6、図7に示す例と同様である。このように、複数の山形状部4fを形成するようにすれば、その個数等の適宜等により、環状複合体6の弾性率の設定変更が可能となり、その設計自由度がより広くなる。
図6〜図8に示す実施形態の他の構成は上記と同様であるので、共通部分に同様の符号を付し、その説明を割愛する。
The vibration washer 3 shown in FIG. 8 is still another modification of the example of FIG. 6, and the mountain-shaped portion 4 f includes a plurality of discontinuous mountain portions. That is, a plurality of crests are independently formed on the flat plate portion 4e of the elastic plate member 4 along the circumferential direction to form a crest-shaped portion 4f, and a crest-shaped portion 4f composed of the plurality of crests and the A undulating shape portion is formed by the flat plate portion 4e at the peripheral portion, and through holes 4d are formed in each mountain shape portion 4f so as to straddle the flat plate portions 4e on both sides. The mountain-shaped portions 4f are not limited to being arranged in one row in the circumferential direction, and may be arranged in a plurality of rows. Other configurations are the same as those shown in FIGS. 6 and 7. In this manner, if a plurality of mountain-shaped portions 4f are formed, the setting of the elastic modulus of the annular composite 6 can be changed depending on the number of the portions, etc., and the degree of freedom in design becomes wider.
Since the other configurations of the embodiment shown in FIGS. 6 to 8 are the same as those described above, the same reference numerals are given to the common portions, and descriptions thereof are omitted.

図9に示す制振ワッシャ3は、前記弾性板材4が、山部4gと谷部4hとが繰り返す波形部材からなり、前記起伏形状部が、この山部4gと谷部4hとにより形成され、山部4gに透孔4dが形成されている。弾性板材4は、上記同様エラストマー層5に略全体が埋入された状態で一体化されて環状複合体6が構成される。谷部4hの下面(シリンダヘッド1の肩部1b側の面)と、山部4gの頂面(インジェクター2の段差部2a側の面)は、制振基材層5より露出乃至は制振基材層5の薄膜で覆われるよう構成されている。また、環状複合体6の上下両面には、円環状金属板7が一体とされている。従って、図3のような使用状態においては、円環状金属板7に荷重が直接負荷されることになるから、耐荷重が大となる。この負荷は、弾性板材4を圧偏する方向及び制振基材層5の厚み方向に作用し、上記同様その複合した弾性によって吸収され、振動が抑えられて騒音の発生が抑制される。この場合、弾性板材4はウエーブワッシャ状の形状をなすから、その特有のばね特性と制振基材層5との相乗した弾性によって、優れた制振機能が発現される。そして、透孔4dの形成態様と関連付けて、環状複合体6の弾性率の設定が適宜なし得る点は上記と同様である。その他の構成は上記各実施形態と同様であるから、共通部分に同一の符号を付し、ここでもその説明を割愛する。   In the vibration washer 3 shown in FIG. 9, the elastic plate member 4 is formed of a corrugated member in which a peak portion 4g and a valley portion 4h are repeated, and the undulating shape portion is formed by the peak portion 4g and the valley portion 4h. A through hole 4d is formed in the mountain portion 4g. The elastic plate material 4 is integrated in a state where substantially the whole is embedded in the elastomer layer 5 in the same manner as described above to constitute the annular composite 6. The bottom surface of the valley portion 4h (the surface on the shoulder portion 1b side of the cylinder head 1) and the top surface of the peak portion 4g (the surface on the stepped portion 2a side of the injector 2) are exposed or vibration-damped from the vibration damping base material layer 5. The base layer 5 is configured to be covered with a thin film. An annular metal plate 7 is integrated on the upper and lower surfaces of the annular composite 6. Therefore, in the use state as shown in FIG. 3, since the load is directly applied to the annular metal plate 7, the load resistance is increased. This load acts in the direction in which the elastic plate member 4 is biased and in the thickness direction of the vibration damping base material layer 5, and is absorbed by the combined elasticity as described above, suppressing vibrations and suppressing the generation of noise. In this case, since the elastic plate member 4 has a wave washer-like shape, an excellent vibration damping function is manifested by the synergistic elasticity of the unique spring characteristics and the vibration damping base material layer 5. And the point which can set suitably the elasticity modulus of the cyclic | annular composite body 6 in connection with the formation mode of the through-hole 4d is the same as the above. Since other configurations are the same as those of the above embodiments, common portions are denoted by the same reference numerals, and description thereof is omitted here.

尚、本発明の制振ワッシャは、インジェクターの支持部に用いればその制振・防音効果により、自動車のエンジンにおける騒音低減化に大きく寄与するので、この分野での応用が特に望ましいが、これに限らず、その他の振動発生部位にも用いれば同様の効果を得ることができる。また、透孔4dとして、形状が円形及び台形状のものについて例示したが、長方形、正方形、その他の多角形、長円形、楕円形等であっても良い。更に、図6〜図9に示す実施形態において、環状複合体6の両面に円環状金属板7を一体とした例を示したが、円環状金属板7を設けるか否かは、適用条件に応じて適宜設定される。加えて、透孔4dの形成位置は図示の位置に限らず、例えば平板部や谷部であってもよい。   In addition, since the vibration damping washer of the present invention greatly contributes to noise reduction in the engine of an automobile due to its vibration damping and soundproofing effect when used in the support portion of the injector, its application in this field is particularly desirable. The same effect can be obtained if it is used not only for other vibration generating parts. Further, although the through holes 4d are illustrated as being circular and trapezoidal in shape, they may be rectangular, square, other polygons, oval, ellipse, or the like. Furthermore, in the embodiment shown in FIGS. 6 to 9, the example in which the annular metal plate 7 is integrated on both surfaces of the annular composite 6 has been shown, but whether or not the annular metal plate 7 is provided depends on the application conditions. It is set accordingly. In addition, the formation position of the through-hole 4d is not limited to the illustrated position, and may be, for example, a flat plate portion or a valley portion.

本発明の制振ワッシャの一実施形態を示す平面図である。It is a top view which shows one Embodiment of the damping washer of this invention. 図1におけるX−X線矢視断面図である。FIG. 2 is a cross-sectional view taken along line XX in FIG. 1. 同制振ワッシャを介してシリンダヘッドにインジェクターを支持させた状態を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state which made the cylinder head support the injector via the damping washer. 他の実施形態の制振ワッシャを示す図1と同様図である。It is a figure similar to FIG. 1 which shows the damping washer of other embodiment. 更に他の実施形態の制振ワッシャを示す図2と同様図である。It is the same figure as FIG. 2 which shows the damping washer of other embodiment. 更に他の実施形態の制振ワッシャを示す図2と同様図である。It is the same figure as FIG. 2 which shows the damping washer of other embodiment. 図6の実施形態の変形例を示す図2と同様図である。It is a figure similar to FIG. 2 which shows the modification of embodiment of FIG. 図6の実施形態の別の変形例を示す図2と同様図である。FIG. 7 is a view similar to FIG. 2 showing another modification of the embodiment of FIG. 6. 更に他の実施形態の制振ワッシャを示す図2と同様図である。It is the same figure as FIG. 2 which shows the damping washer of other embodiment.

符号の説明Explanation of symbols

1 シリンダヘッド(部材)
1b 肩部(平面)
2 インジェクター(部材)
2a 段差部(平面)
3 制振ワッシャ
4 弾性板材
4a 内周側部分の環状平板部(起伏形状部)
4b 外周側部分の環状平板部(起伏形状部)
4c 環状傾斜板部(起伏形状部)
4d 透孔
4e 平板部(起伏形状部)
4f 山形状部(起伏形状部)
4g 山部(起伏形状部)
4g 谷部(起伏形状部)
5 制振基材層
5a グロメット部
6 環状複合体
7 円環状金属板(金属製リング部材)
a 荷重負荷方向
1 Cylinder head (member)
1b shoulder (plane)
2 Injector
2a Step part (plane)
3 Damping washer 4 Elastic plate 4a Annular flat plate on the inner circumference side (undulation)
4b Annular flat plate part on the outer periphery side (undulation shape part)
4c Annular inclined plate (undulated shape)
4d Through-hole 4e Flat plate part (undulation shape part)
4f Mountain shape part (undulation shape part)
4g mountain part (undulation shape part)
4g Valley (undulation shape part)
5 Damping Base Layer 5a Grommet 6 Ring Composite 7 Ring Metal Plate (Metal Ring Member)
a Load direction

Claims (10)

荷重が負荷される2つの部材の対向する2平面間に挟装される制振ワッシャであって、
環状に形成された弾性板材とゴム又は樹脂からなる制振基材層とを一体とした環状複合体からなり、上記弾性板材は、上記荷重が負荷される方向に賦形された起伏形状部を含み、且つ周方向に沿って複数の透孔を備え、上記弾性板材は、その板面の一部が制振基材層より露出乃至は制振基材層の薄膜で覆われると共に上記透孔内に制振基材層が係入した状態で制振基材層に埋入されていることを特徴とする制振ワッシャ。
A vibration washer sandwiched between two opposing planes of two members to which a load is applied,
It consists of an annular composite in which an elastic plate material formed in an annular shape and a damping base layer made of rubber or resin are integrated, and the elastic plate material has an undulating shape portion shaped in the direction in which the load is applied. Including a plurality of through-holes along the circumferential direction, and the elastic plate member is partly exposed from the damping base layer or covered with a thin film of the damping base layer and the through-hole. A damping washer characterized by being embedded in a damping base layer with the damping base layer engaged therein.
請求項1に記載の制振ワッシャにおいて、
前記弾性板材が、内周側部分及び外周側部分の段違い状平板部と、両平板部を繋ぐ傾斜板部とよりなる皿ばね状部材からなり、上記段違い状平板部と傾斜板部とにより前記起伏形状部が形成されることを特徴とする制振ワッシャ。
The vibration washer according to claim 1,
The elastic plate material comprises a disc spring-like member comprising a stepped flat plate portion of the inner peripheral side portion and the outer peripheral side portion and an inclined plate portion connecting both flat plate portions, and the stepped flat plate portion and the inclined plate portion A vibration washer having a undulating shape.
請求項1に記載の制振ワッシャにおいて、
前記弾性板材が、平板部と山形状部とよりなり、この平板部と山形状部とにより前記起伏形状部が形成されることを特徴とする制振ワッシャ。
The vibration washer according to claim 1,
The vibration washer characterized in that the elastic plate member comprises a flat plate portion and a mountain-shaped portion, and the undulating shape portion is formed by the flat plate portion and the mountain-shaped portion.
請求項3に記載の制振ワッシャにおいて、
前記山形状部が、前記弾性板材の周方向に沿って連続的な突条体からなることを特徴とする制振ワッシャ。
The vibration washer according to claim 3,
The vibration washer according to claim 1, wherein the mountain-shaped portion is formed of a continuous ridge body along a circumferential direction of the elastic plate member.
請求項3に記載の制振ワッシャにおいて、
前記山形状部が、複数の不連続山部からなることを特徴とする制振ワッシャ。
The vibration washer according to claim 3,
The vibration washer according to claim 1, wherein the mountain-shaped portion includes a plurality of discontinuous mountain portions.
請求項1に記載の制振ワッシャにおいて、
前記弾性板材が山部と谷部とが周方向に繰り返す波形部材からなり、前記起伏形状部が、この山部と谷部とにより形成されることを特徴とする制振ワッシャ。
The vibration washer according to claim 1,
The vibration washer is characterized in that the elastic plate member is formed of a corrugated member in which a crest and a trough repeat in the circumferential direction, and the undulating portion is formed by the crest and trough.
請求項1乃至請求項6のいずれかに記載の制振ワッシャにおいて、
前記透孔が円形であって、周方向に等間隔で形成されていることを特徴とする制振ワッシャ。
The vibration washer according to any one of claims 1 to 6,
The vibration washer is characterized in that the through holes are circular and are formed at equal intervals in the circumferential direction.
請求項1乃至請求項6のいずれかに記載の制振ワッシャにおいて、
前記透孔が矩形状であって、周方向に等間隔且つ周方向に配向するよう形成されていることを特徴とする制振ワッシャ。
The vibration washer according to any one of claims 1 to 6,
The damping washer according to claim 1, wherein the through holes are rectangular and are formed so as to be oriented at equal intervals in the circumferential direction and in the circumferential direction.
請求項1乃至8のいずれかに記載の制振ワッシャにおいて、
前記環状複合体の外周部の少なくとも前記2平面に対面する部位には金属製リング部材が一体とされていることを特徴とする制振ワッシャ。
The vibration washer according to any one of claims 1 to 8,
A vibration washer comprising a metal ring member integrated with at least a portion of the outer peripheral portion of the annular composite facing the two planes.
請求項1乃至9のいずれかに記載の制振ワッシャにおいて、
前記環状複合体の内周部に、前記制振基材層によるグロメット部が形成されていることを特徴とする制振ワッシャ。
The vibration washer according to any one of claims 1 to 9,
A vibration washer having a grommet portion formed of the vibration damping base material layer formed on an inner peripheral portion of the annular composite.
JP2007112870A 2007-03-12 2007-04-23 Vibration damping washer Withdrawn JP2008255975A (en)

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