JP4724727B2 - mechanical seal - Google Patents

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JP4724727B2
JP4724727B2 JP2008082696A JP2008082696A JP4724727B2 JP 4724727 B2 JP4724727 B2 JP 4724727B2 JP 2008082696 A JP2008082696 A JP 2008082696A JP 2008082696 A JP2008082696 A JP 2008082696A JP 4724727 B2 JP4724727 B2 JP 4724727B2
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ring
stationary
seal
seal ring
mechanical seal
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JP2009236207A (en
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崇 藤原
正樹 宮本
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Nippon Pillar Packing Co Ltd
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Description

本発明は、接触形及び非接触形を含むメカニカルシールに関するものである。   The present invention relates to a mechanical seal including a contact type and a non-contact type.

メカニカルシールは、特許文献１や特許文献２等において開示されたものが知られている。特許文献１のものは、回転密封環と静止密封環とが摩擦接触しながら相対回転することでシールする接触形のメカニカルシールを開示している。   As the mechanical seal, those disclosed in Patent Document 1, Patent Document 2, and the like are known. The thing of patent document 1 is disclosing the contact-type mechanical seal which seals by carrying out relative rotation, while a rotation sealing ring and a stationary sealing ring make frictional contact.

特許文献２が示すタンデム型ドライコンタクト軸封装置においては、回転密封環と静止密封環との夫々の対向端面の相対回転によって生じる動圧と、弾性機構による静止密封環の回転密封環への押付け力とがバランスすることにより、各対向端面どうしの間が非接触状態に保持されながらシールされるメカニカルシールを開示している。   In the tandem dry contact shaft sealing device disclosed in Patent Document 2, the dynamic pressure generated by the relative rotation of the opposing end surfaces of the rotary seal ring and the stationary seal ring, and the pressing of the stationary seal ring to the rotary seal ring by the elastic mechanism A mechanical seal is disclosed in which a force is balanced and the opposing end surfaces are sealed while being held in a non-contact state.

従来、特許文献２に示される構造と同等の構造を持つメカニカルシールとして、図７に示されるものが使用されていた。即ち、軸心Ｐを有する回転軸１と一体回転する回転密封環２と、シールハウジング３に対して回転不能で、かつ、回転軸１の軸心Ｐ方向に移動自在に支持される静止密封環４と、静止密封環４を軸心Ｐ方向への移動が自在な状態に外嵌するボス部５Ａを有するとともにシールハウジング３に固定されるリテーナ５と、静止密封環４を回転密封環２に押付けてシール部Ｓを形成すべくリテーナ５と静止密封環４との間に介装される弾性機構６と、ボス部５Ａと静止密封環４との間をシールするためのシールリング７とを有して、回転密封環２と静止密封環４との間がシールされるように構成されるメカニカルシールＡが構成されている。   Conventionally, as a mechanical seal having a structure equivalent to the structure shown in Patent Document 2, the one shown in FIG. 7 has been used. That is, the rotary seal ring 2 that rotates integrally with the rotary shaft 1 having the axis P, and the stationary seal ring that is non-rotatable with respect to the seal housing 3 and is supported so as to be movable in the direction of the axis P of the rotary shaft 1. 4, a retainer 5 having a boss 5 </ b> A that externally fits the stationary seal ring 4 so as to be movable in the direction of the axis P, and fixed to the seal housing 3, and the stationary seal ring 4 as the rotary seal ring 2. An elastic mechanism 6 interposed between the retainer 5 and the stationary seal ring 4 to press and form a seal portion S, and a seal ring 7 for sealing between the boss portion 5A and the stationary seal ring 4 The mechanical seal A is configured so that the space between the rotary seal ring 2 and the stationary seal ring 4 is sealed.

ハウジングにボルト止めされるリテーナ５は、弾性機構を構成する複数のコイルスプリング６を収容配置する本体部５Ｂと、ハウジング３に内嵌される外フランジ部５Ｃとを有しており、外フランジ部５Ｃとハウジング３との間をシールするＯリング８が装備されている。ボス部５Ａと、回転軸１にシール外嵌される第１スリーブ９にシール外嵌される第２スリーブ１０との径方向間には大気側に連通する間隙が形成されている。回転密封環２は、静止密封環４からの押圧力を受止めることができるように、第２スリーブ１０にシール外嵌される環状鍔部１１に軸心Ｐ方向でのシール状態で支持されている。   The retainer 5 that is bolted to the housing has a main body portion 5B that houses and arranges a plurality of coil springs 6 that constitute an elastic mechanism, and an outer flange portion 5C that is fitted inside the housing 3, and the outer flange portion. An O-ring 8 that seals between 5C and the housing 3 is provided. A gap that communicates with the atmosphere side is formed between the boss portion 5A and the second sleeve 10 that is fitted to the first sleeve 9 that is fitted to the rotary shaft 1 by seal. The rotary seal ring 2 is supported in a sealed state in the direction of the axis P by an annular flange portion 11 fitted to the second sleeve 10 so that the pressing force from the stationary seal ring 4 can be received. Yes.

静止密封環４は、回転密封環２のシール面２ａに対向するシール面４ａの反対側（背面側）となる根元部の内周端を断面矩形に径外側に切欠くようにしてその部分にシールリングであるＯリング７を装備しているとともに、その内周面がボス部５Ａに軸心Ｐ方向に移動可能に外嵌されている。静止密封環４の根元部とコイルスプリング６との間には円環状の受板１２が介装されている。   The stationary seal ring 4 is formed in such a portion that the inner peripheral end of the root portion opposite to the seal surface 4a facing the seal surface 2a of the rotary seal ring 2 (back side) is cut out to the outside in a rectangular cross section. An O-ring 7 that is a seal ring is provided, and an inner peripheral surface thereof is externally fitted to the boss portion 5A so as to be movable in the direction of the axis P. An annular receiving plate 12 is interposed between the root portion of the stationary seal ring 4 and the coil spring 6.

この従来技術によるメカニカルシールＡにおいては、図７に示すように、互いにシール部材である回転密封環２はＳｉｃ製で、静止密封環４はカーボン製で、リテーナ５はステンレス材（ＳＵＳ）製で、Ｏリング７はゴム製であるが、使用状況によっては不具合の出ることが判ってきた。それは使用状況が高温になったときには、ステンレス材製リテーナ５の熱膨張による寸法増大、及び、熱膨張係数が比較的大きなゴム製Ｏリング７の径寸法増大に対して、比較的熱膨張係数の小さなカーボン製静止密封環４は余り寸法増大しないため、Ｏリング７と静止密封環４との径方向での締め代が増大して静止密封環４の軸心Ｐ方向の動きが渋くなり、コイルスプリング６による押圧力を阻害することとなって追従不良となる不具合である。   In this conventional mechanical seal A, as shown in FIG. 7, the rotary seal ring 2 which is a seal member is made of Sic, the stationary seal ring 4 is made of carbon, and the retainer 5 is made of stainless steel (SUS). The O-ring 7 is made of rubber, but it has been found that problems occur depending on the usage conditions. When the usage condition becomes high, the thermal expansion coefficient of the stainless steel retainer 5 is increased due to thermal expansion and the diameter of the rubber O-ring 7 having a relatively large thermal expansion coefficient is increased. Since the small stationary seal ring 4 made of carbon does not increase in size so much, the tightening margin in the radial direction between the O-ring 7 and the stationary seal ring 4 is increased, and the movement of the stationary seal ring 4 in the axial center P direction becomes uncomfortable. This is a problem in that the pressing force by the spring 6 is hindered, resulting in poor tracking.

そこで、上記不具合を解消すべく、図６に示すような静止密封環４のシール構造を持つメカニカルシールＡが開発された。即ち、静止密封環４を、回転密封環２との間にシール部Ｓを形成する先端側静止輪部４Ａと、弾性機構６による押圧力を受ける根元側静止輪部４Ｂと、を軸心Ｐ方向に並べてボス部５Ａに外嵌することで構成し、根元側静止輪部４Ｂの回転密封環側端にＯリング７を設ける構造である。この場合のＯリング７は、先端側静止輪部４Ａと根元側静止輪部４Ｂとの間、及び先端側静止輪部４Ａとボス部５Ａとの間もシールするとともに、根元側静止輪部４Ｂに受ける押圧力を先端側静止輪部４Ａに伝える部材にもなるという多機能部品に兼用構成されている。   Therefore, in order to solve the above problems, a mechanical seal A having a seal structure of the stationary seal ring 4 as shown in FIG. 6 has been developed. In other words, the stationary seal ring 4 includes a distal-side stationary ring part 4A that forms a seal part S between the stationary seal ring 4 and the root-side stationary ring part 4B that receives a pressing force by the elastic mechanism 6, and the axis P The O-ring 7 is provided at the end of the root-side stationary ring portion 4B on the side of the rotary sealing ring. In this case, the O-ring 7 seals between the distal-side stationary wheel portion 4A and the root-side stationary wheel portion 4B and between the distal-side stationary wheel portion 4A and the boss portion 5A, and at the same time, the root-side stationary wheel portion 4B. This is also used as a multifunctional part that also serves as a member that transmits the pressing force received to the distal side stationary ring portion 4A.

この比較例によるメカニカルシールＡにおいては、図６に示すように、先端側静止輪部４Ａがカーボン製で、根元側静止輪部４ＢはＳＵＳ製にすること（その他は第１従来技術のものと同じ材料である）により、従来技術の前記不具合を解消しようと試みられた。しかしながら、改善は見られるものの、高温時のリテーナ５、Ｏリング７、及び根元側静止輪部４Ｂの寸法変化により、やはりＯリング７の締め代増大によって根元側静止輪部４Ｂの動きに渋さが出現することが皆無にはならず、前述の追従不良が残る場合のあるものとなっていた。
特開２００５−１１３９８３号公報 特許第４０００３２４号公報 In the mechanical seal A according to this comparative example, as shown in FIG. 6, the tip side stationary ring portion 4A is made of carbon, and the root side stationary ring portion 4B is made of SUS (the others are those of the first prior art). Attempts to eliminate the above-mentioned drawbacks of the prior art. However, although improvement can be seen, the movement of the base side stationary ring part 4B is also aggravated by the increase in the tightening margin of the O ring 7 due to the dimensional change of the retainer 5, the O ring 7 and the base side stationary ring part 4B at high temperatures. The occurrence of the above has not been completely eliminated, and the above-mentioned poor tracking may remain.
JP 2005-113983 A Japanese Patent No. 40000003

本発明の目的は、メカニカルシールにおける静止密封環のリテーナボス部に対するシール構造の更なる工夫により、高温条件下の使用においてもＯリングの締め代増大による前述の不具合である静止密封環の追従不良、即ちシール不良が起らないように改善されたメカニカルシールを実現して提供する点にある。   The purpose of the present invention is to further improve the seal structure for the retainer boss portion of the stationary seal ring in the mechanical seal, so that the follow-up failure of the stationary seal ring, which is the above-mentioned problem due to increased tightening allowance of the O-ring, even when used under high temperature conditions That is, a mechanical seal improved so as not to cause a sealing failure is realized and provided.

請求項１に係る発明は、回転軸１と一体回転する回転密封環２と、シールハウジング３に対して回転不能で、かつ、前記回転軸１の軸心Ｐ方向に移動自在に支持される静止密封環４と、前記静止密封環４を前記軸心Ｐ方向への移動が自在な状態に外嵌するボス部５Ａを有するとともに前記シールハウジング３に固定されるリテーナ５と、前記静止密封環４を前記回転密封環２に押付けるべく前記リテーナ５と前記静止密封環４との間に介装される弾性機構６と、前記ボス部５Ａと前記静止密封環４との間をシールするためのシールリング７とを有して、前記回転密封環２と前記静止密封環４との間がシールされるように構成されるメカニカルシールにおいて、
前記静止密封環４が、前記回転密封環２との間にシール部Ｓを形成する先端側静止輪部４Ａと、前記弾性機構６による押圧力を受けるＰＥＥＫ製の根元側静止輪部４Ｂと、を前記軸心Ｐ方向に並べてステンレス材製の前記ボス部５Ａに外嵌することで構成されており、前記根元側静止輪部４Ｂと前記ボス部５Ａとの間に前記シールリング７が介装されるとともに、前記根元側静止輪部４Ｂの熱膨張係数が前記ボス部５Ａの熱膨張係数より大となるように設定されていることを特徴とするものである。 Invention, the rotary seal ring 2 to rotate integrally with the rotary shaft 1, a non-rotatable relative to the seal housing 3, and is movably supported in the axial direction P of the rotary shaft 1 according to claim 1 A stationary seal ring 4; a retainer 5 that has a boss portion 5A that externally fits the stationary seal ring 4 so as to be movable in the direction of the axis P; and is fixed to the seal housing 3; and the stationary seal ring In order to seal between the elastic mechanism 6 interposed between the retainer 5 and the stationary sealing ring 4 and the boss portion 5A and the stationary sealing ring 4 so as to press the 4 against the rotary sealing ring 2. A mechanical seal configured to seal between the rotary seal ring 2 and the stationary seal ring 4;
The stationary seal ring 4 is a distal stationary ring portion 4A that forms a seal portion S between the stationary seal ring 4 and the rotational seal ring 2; a PEEK root stationary ring portion 4B that receives a pressing force by the elastic mechanism 6; Are arranged in the direction of the axis P and externally fitted to the boss portion 5A made of stainless steel, and the seal ring 7 is interposed between the root-side stationary ring portion 4B and the boss portion 5A. In addition, the thermal expansion coefficient of the base side stationary ring portion 4B is set to be larger than the thermal expansion coefficient of the boss portion 5A.

請求項２に係る発明は、請求項１に記載のメカニカルシールにおいて、前記シールリング７が、前記根元側静止輪部４Ｂと前記先端側静止輪部４Ａとの間をシールする手段に兼用されていることを特徴とするものである。 The invention according to claim 2 is the mechanical seal according to claim 1 , wherein the seal ring 7 is also used as a means for sealing between the root side stationary ring part 4B and the tip side stationary ring part 4A. it is characterized in that there.

請求項１の発明によれば、詳しくは各実施形態の項にて述べるが、高温条件下においてボス部及びシールリングが熱膨張によって寸法が増大する際の締め代がきつくなることが緩和又は抑制されるものとなり、根元側静止輪部の軸心方向の移動のし易さが維持され、静止密封環の追従不良、即ちシール不良が起らないように改善されたメカニカルシールを提供することができる。 According to the first aspect of the present invention , the details of each embodiment will be described, but the tightening margin when the dimensions of the boss part and the seal ring increase due to thermal expansion under high temperature conditions is alleviated or suppressed. It is possible to provide a mechanical seal that is easy to move in the axial direction of the root side stationary ring portion and is improved so that the follow-up failure of the stationary sealing ring, that is, the sealing failure does not occur. it can.

請求項２の発明によれば、一つのシールリングで複数箇所のシールが可能となる多機能部品化が行える利点がある。 According to the invention of claim 2 , there is an advantage that a multi-functional part can be obtained in which a plurality of places can be sealed with one seal ring.

以下に、本発明によるメカニカルシールの実施の形態を、図面を参照しながら説明する。図１〜図４はそれぞれ第１実施例、参考実施例、第２実施例、第３実施例の非接触形のメカニカルシールを示す断面図、図５は、実施例１によるメカニカルシールを含むタンデム型のメカニカルシール装置を示す要部の断面図である。 Embodiments of a mechanical seal according to the present invention will be described below with reference to the drawings. 1 to 4 are sectional views showing non-contact type mechanical seals of the first embodiment, the reference embodiment, the second embodiment, and the third embodiment , respectively. FIG. 5 is a tandem including the mechanical seal according to the first embodiment. It is sectional drawing of the principal part which shows the mechanical seal apparatus of a type | mold.

〔実施例１〕
図５にタンデム型のメカニカルシール装置ＴＭが示されている。このメカニカルシール装置ＴＭは、回転軸１の軸心Ｐ上においてプロセス側に配置される接触形の第１メカニカルシールＭと、大気側に配置される非接触形の第２メカニカルシールＡとを有して構成されており、プラント設備等において薬液、原油関係液、洗浄液等のプロセス液のシールに用いられる。 [Example 1]
FIG. 5 shows a tandem mechanical seal device TM. This mechanical seal device TM has a contact-type first mechanical seal M arranged on the process side on the axis P of the rotary shaft 1 and a non-contact-type second mechanical seal A arranged on the atmosphere side. And is used for sealing process liquids such as chemical liquids, crude oil related liquids, and cleaning liquids in plant facilities and the like.

第１メカニカルシールＭは、図５に示すように、回転軸１と一体回転する回転密封環２２と、ハウジング３に相対回動不能で、かつ、回転軸１の軸心Ｐ方向に移動可能な静止密封環２４と、静止密封環２４を回転密封環２に押付けてシール部Ｓを形成するための弾性機構である複数のコイルスプリング２６と、を有して構成されている。回転密封環２２は、回転軸１に外嵌シール外嵌されるスリーブ２１の環状鍔部２１Ａにシール状態で、かつ、相対回動不能に受止め支持されている。尚、２３は、環状鍔部２１Ａから軸心Ｐ方向に突設されて回転密封環２２に作用する回り止めピンである。   As shown in FIG. 5, the first mechanical seal M is not rotatable relative to the rotary sealing ring 22 that rotates integrally with the rotary shaft 1 and the housing 3, and is movable in the direction of the axis P of the rotary shaft 1. The stationary sealing ring 24 and a plurality of coil springs 26 that are elastic mechanisms for pressing the stationary sealing ring 24 against the rotary sealing ring 2 to form the seal portion S are configured. The rotary sealing ring 22 is received and supported in a sealed state and in a relatively non-rotatable manner on an annular flange 21A of a sleeve 21 that is externally fitted to the rotary shaft 1. Reference numeral 23 denotes a detent pin that protrudes from the annular flange 21A in the direction of the axis P and acts on the rotary seal ring 22.

静止密封環２４は、回転密封環２２に接触作用してシール部Ｓを形成するための先端静止部２４ａと、ハウジング３の環状内突起周部３ａにシール内嵌される静止本体部２４ｂと、コイルスプリング２６の付勢力を受けるリテーナ部２４ｃとから成り、スリーブ２１に遊外嵌されている。複数のコイルスプリング２６は、ハウジング３に固定内嵌される支持環状体２５に収容配置されており、その支持環状体２５には、リテーナ部２４ｃに螺着される回止めボルト２７が貫通されている。尚、２８は静止本体部２４ｂとリテーナ部２４ｃとの抜止めボルトである。   The stationary seal ring 24 is configured to contact the rotary seal ring 22 to form a seal portion S, a stationary stationary portion 24a, a stationary main body portion 24b fitted into the annular inner protrusion peripheral portion 3a of the housing 3, The retainer portion 24 c receives the urging force of the coil spring 26 and is loosely fitted to the sleeve 21. The plurality of coil springs 26 are accommodated and arranged in a support annular body 25 that is fixedly fitted in the housing 3, and a rotation stop bolt 27 that is screwed to the retainer portion 24 c is passed through the support annular body 25. Yes. Reference numeral 28 denotes a retaining bolt for the stationary main body 24b and the retainer 24c.

つまり、第１メカニカルシールＭにおいては、コイスプリング２６が静止密封環２４を軸心Ｐ方向で回転密封環２２に押付けて、それら両密封環２４，２２が相対回転しながら接触するシール部Ｓを形成しており、プロセス側のプロセス液を漏れないようにシールする一次シールとして機能するものとなっている。次に、第２メカニカルシールＡについて説明する。   In other words, in the first mechanical seal M, the coil spring 26 presses the stationary seal ring 24 against the rotary seal ring 22 in the direction of the axis P, and the seal portion S in which both the seal rings 24 and 22 come into contact with each other while rotating relative to each other. It is formed and functions as a primary seal that seals the process liquid on the process side so as not to leak. Next, the second mechanical seal A will be described.

第２メカニカルシールＡは、図５，図１に示すように、回転密封環環２と静止密封環４との夫々の対向端面２ａ，４ａの相対回転によって生じる動圧と、コイルスプリング（弾性機構の一例）６による静止密封環４の回転密封環２への押付け力とがバランスすることにより、各対向端面２ａ，４ａどうしの間が非接触状態に保持されながらシールされるように構成される非接触形のものに構成されている。   As shown in FIGS. 5 and 1, the second mechanical seal A includes a dynamic pressure generated by relative rotation of the opposed end faces 2a and 4a of the rotary seal ring 2 and the stationary seal ring 4 and a coil spring (elastic mechanism). An example) The pressing force of the stationary seal ring 4 to the rotary seal ring 2 by 6 is balanced so that the opposing end surfaces 2a and 4a are sealed while being held in a non-contact state. It is configured as a non-contact type.

つまり、実施例１によるメカニカルシールＡは、図６に示す比較例のメカニカルシールをさらに発展させたものであって、基本的には同じ構造のものであり、同一の箇所には同一の符号を付してその説明が為されたものとする。尚、図５に示す第２メカニカルシールＡと、図１〜図４及び図６に示すメカニカルシールＡとは、構成部品に若干の違いはあるが原理構造は同じであり、ここでは便宜上同等のメカニカルシールとして説明する。   That is, the mechanical seal A according to Example 1 is a further development of the mechanical seal of the comparative example shown in FIG. 6 and basically has the same structure, and the same portions are denoted by the same reference numerals. It is assumed that the explanation has been made. The second mechanical seal A shown in FIG. 5 and the mechanical seal A shown in FIGS. 1 to 4 and 6 have the same principle structure, although there are some differences in the components. It will be described as a mechanical seal.

図６に示す比較例のメカニカルシールと異なるのは静止密封環４のみである。違いは、根元側静止輪部４Ｂを合成樹脂材であるＰＥＥＫ製としたことである。つまり、ＰＥＥＫは熱膨張係数が大きいので、高温条件下においてリテーナ５及びＯリング７が熱膨張によって寸法が増大する際の締め代がきつくなることが緩和又は抑制されるものとなり、根元側静止輪部４Ｂの軸心Ｐ方向の移動のし易さが維持される。その結果、静止密封環４の追従不良、即ちシール不良が起らないように改善されたメカニカルシールを実現することができるのである。 Only the stationary seal ring 4 is different from the mechanical seal of the comparative example shown in FIG. The difference is that the base stationary ring portion 4B is made of PEEK, which is a synthetic resin material. That is, since PEEK has a large coefficient of thermal expansion, the tightening allowance when the dimensions of the retainer 5 and the O-ring 7 increase due to thermal expansion under high-temperature conditions is alleviated or suppressed. The ease of movement of the portion 4B in the direction of the axis P is maintained. As a result, it is possible to realize an improved mechanical seal so that the follow-up failure of the stationary seal ring 4, that is, the seal failure does not occur.

つまり、実施例１のメカニカルシールＡにおいては、静止密封環４が、回転密封環２との間にシール部Ｓを形成する先端側静止輪部４Ａと、コイルスプリング６による押圧力を受ける根元側静止輪部４Ｂと、を軸心Ｐ方向に並べてボス部５Ａに外嵌することで構成されており、根元側静止輪部４Ｂとボス部５Ａとの間にＯリング７が介装されるとともに、根元側静止輪部４Ｂの熱膨張係数がボス部５Ａの熱膨張係数より大となるように設定されている。 That is, in the mechanical seal A of the first embodiment, the stationary seal ring 4 has a distal end side stationary ring portion 4 </ b> A that forms a seal portion S between the stationary seal ring 2 and the root side that receives a pressing force by the coil spring 6. The stationary ring portion 4B is arranged in the direction of the axis P and externally fitted to the boss portion 5A, and an O-ring 7 is interposed between the root side stationary ring portion 4B and the boss portion 5A. The thermal expansion coefficient of the root side stationary ring part 4B is set to be larger than the thermal expansion coefficient of the boss part 5A.

また、Ｏリング７は、根元側静止輪部４Ｂと先端側静止輪部４Ａとの間をシールする手段、及び、先端側静止輪部４Ａとボス部５Ａとの間をシールする手段に兼用されているとともに、コイルスプリング６によって根元側静止輪部４Ｂに加わる押圧力を先端側静止輪部４Ａに伝達する部材にも兼用される多機能部品とされている。但し、押圧力が強い場合には、Ｏリング７が一定量変形した後に、根元側静止輪部４Ｂが直接に先端側静止輪部４Ａに当接して押圧力を伝える構成となるように、根元側静止輪部４Ｂと先端側静止輪部４Ａとの軸心Ｐ方向での隙間ｅが設定されている。   The O-ring 7 is also used as a means for sealing between the root side stationary ring part 4B and the tip side stationary ring part 4A and a means for sealing between the tip side stationary ring part 4A and the boss part 5A. At the same time, the coil spring 6 is a multi-functional part that is also used as a member that transmits the pressing force applied to the root stationary ring portion 4B to the distal stationary ring portion 4A. However, when the pressing force is strong, the root side stationary ring portion 4B directly contacts the tip side stationary ring portion 4A and transmits the pressing force after the O-ring 7 is deformed by a certain amount. A clearance e is set in the direction of the axis P between the stationary stationary wheel portion 4B and the distal stationary wheel portion 4A.

そして、図６に示される比較例によるメカニカルシールでも、厳しい条件ではまだ不安があるものの、従来のものに比べると改善されて実用化できそうなレベルにはなっていた。従って、図６に示す比較例のものでも発明に値するものであると考えられるが、実施例１のものは更なる改善により、前記不安（高温条件下では、場合によっては静止密封環４の追従不良のおそれが残ること）を拭い去ることができる迄に改善されたメカニカルシールとすることができたのである。   The mechanical seal according to the comparative example shown in FIG. 6 is still uneasy under severe conditions, but has been improved to a level where it can be put into practical use as compared with the conventional one. Accordingly, even the comparative example shown in FIG. 6 is considered to be worthy of the invention, but the example 1 is further improved, and the anxiety (following the stationary sealing ring 4 in some cases under high temperature conditions). It was possible to obtain an improved mechanical seal until it was possible to wipe off the possibility of failure).

〔参考実施例〕
参考実施例によるメカニカルシールＡは、図２に示すように、図６に示す比較例のメカニカルシールにおける静止密封環４が異なるものである。即ち、静止密封環４が、Ｓｉｃ製の回転密封環２との間にシール部Ｓを形成するカーボン製の先端側静止輪部４Ａと、コイルスプリング６による押圧力を受ける根元側静止輪部４Ｂと、を軸心Ｐ方向に並べてボス部５Ａに外嵌することで構成されている。 [ Reference Example ]
As shown in FIG. 2, the mechanical seal A according to the reference example is different from the stationary seal ring 4 in the mechanical seal of the comparative example shown in FIG. 6. That is, the stationary seal ring 4 is made of a carbon tip end stationary ring portion 4A that forms a seal portion S with the Sic rotary seal ring 2, and a root side stationary ring portion 4B that receives a pressing force by the coil spring 6. Are aligned in the direction of the axis P and externally fitted to the boss portion 5A.

そして、ステンレス材製の根元側静止輪部４Ｂとステンレス材製のボス部５Ａとの間にシールリングであるゴム製のＯリング７が介装されるとともに、根元側静止輪部４ＢにおけるＯリング７を収容する環状切欠き部分１３の内径Ｄが、ボス部５Ａに外嵌装着されている状態のＯリング７の外径ｄよりも十分大きくなる（Ｄ＞ｄ）ように設定されている。   A rubber O-ring 7 as a seal ring is interposed between the stainless steel base stationary ring part 4B and the stainless steel boss part 5A, and the O ring in the root stationary ring part 4B. 7 is set to be sufficiently larger (D> d) than the outer diameter d of the O-ring 7 that is externally fitted to the boss portion 5A.

環状切欠き部分１３は、断面形状が矩形を為して根元側静止輪部４Ｂの回転密封環側端の内径側に形成されており、その側周壁（符記省略）とボス部５Ａの外周面（符記省略）との間をシールするＯリング７は、図１に示す実施例１のメカニカルシールと同様の多機能部品となる状態に構成されている。   The annular notch 13 has a rectangular cross-sectional shape and is formed on the inner diameter side of the rotary seal ring side end of the root side stationary ring portion 4B, and its side peripheral wall (not shown) and the outer periphery of the boss portion 5A The O-ring 7 that seals between the surfaces (not shown) is configured to be a multifunctional component similar to the mechanical seal of the first embodiment shown in FIG.

参考実施例のメカニカルシールＡにおいては、常温状態においてはＯリング７と環状切欠き部分１３とには径方向のクリアランス〔（Ｄ−ｄ）／２〕が形成されているので、高温となってボス部５Ａ及びＯリング７が膨張しても、環状切欠き部分１３に位置するＯリング７を介して根元側静止輪部４Ｂとボス部５Ａとが径方向に強く押されてＯリング７の締め代がきつくなるということが生じないものとなる。また、高温となって各部品（５Ａ，７，４Ｂ）が熱膨張した際に、上記クリアランスが無くなってＯリング７を、その外径部からコイルスプリング６による押圧力を阻害しない程度に締める構成でも良い。その結果、静止密封環４の追従不良、即ちシール不良が起らないように改善されたメカニカルシールを実現することができるのである。 In the mechanical seal A of the reference example , since the radial clearance [(D−d) / 2] is formed in the O-ring 7 and the annular cutout portion 13 at room temperature, the temperature becomes high. Even if the boss portion 5A and the O-ring 7 are expanded, the root-side stationary ring portion 4B and the boss portion 5A are strongly pressed in the radial direction via the O-ring 7 located in the annular cutout portion 13, and the O-ring 7 The tightness will not become tight. Further, when each component (5A, 7, 4B) is thermally expanded at a high temperature, the clearance is eliminated, and the O-ring 7 is tightened from the outer diameter portion to the extent that the pressing force by the coil spring 6 is not hindered. But it ’s okay. As a result, it is possible to realize an improved mechanical seal so that the follow-up failure of the stationary seal ring 4, that is, the seal failure does not occur.

〔実施例２〕
実施例２によるメカニカルシールＡは、図３に示すように、根元側静止輪部４Ｂのボス部５Ａを内嵌する内孔部１４における先端側静止輪部側の端部を、先端側静止輪部４Ａ側が大径となる先拡がり状の円錐面１５に形成するとともに、円錐面１５とボス部５Ａとの間にＯリング（シールリングの一例）７が介装される構成を有している。この場合のＯリング７も、実施例１、参考実施例のものと同様の多機能部品になっている。 [ Example 2 ]
As shown in FIG. 3, the mechanical seal A according to the second embodiment is configured so that the end portion on the distal end side stationary wheel portion side of the inner hole portion 14 into which the boss portion 5 </ b > A of the root side stationary ring portion 4 </ b> B is fitted is disposed. The portion 4A side is formed on a conical surface 15 having a large diameter, and an O-ring (an example of a seal ring) 7 is interposed between the conical surface 15 and the boss portion 5A. . The O-ring 7 in this case is also a multi-functional component similar to that of the first embodiment and the reference embodiment .

つまり、根元側静止輪部４ＢにおけるＯリングの装着される部分を円錐面（断面でテーパとなる面）１５としてあるので、常温状態（大気温度程度）並びに高温状態の広い温度範囲において、外径部からコイルスプリング６による押圧力を阻害しない程度にＯリング７を締めることが常に行えるものとなる。その結果、静止密封環４の追従不良、即ちシール不良が起らないように改善されたメカニカルシールを実現することができるのである。   That is, since the portion where the O-ring is mounted on the root side stationary ring portion 4B is a conical surface (a surface tapered in cross section) 15, the outer diameter in a wide temperature range of normal temperature (about atmospheric temperature) and high temperature. The O-ring 7 can always be tightened to such an extent that the pressing force by the coil spring 6 is not hindered from the portion. As a result, it is possible to realize an improved mechanical seal so that the follow-up failure of the stationary seal ring 4, that is, the seal failure does not occur.

〔実施例３〕
実施例３によるメカニカルシールＡは、図４に示すように、根元側静止輪部４ＢにおけるＯリング（シールリングの一例）７を収容する収容凹部１６の内径Ｗが、ボス部５Ａに外嵌装着されている状態のＯリング７の外径ｄよりも十分大きく（Ｗ＞ｄ）なるように設定され、かつ、収容凹部１６におけるシールリング７を弾性機構６の付勢力によって先端側静止輪部４Ａに向けて押圧することとなる側周面１７が、その径内側ほど軸心Ｐ方向で先端側静止輪部４Ａから離れる先拡がり状の円錐面に形成される構成を有している。 [ Example 3 ]
As shown in FIG. 4, the mechanical seal A according to the third embodiment has an inner diameter W of an accommodation recess 16 that accommodates an O-ring (an example of a seal ring) 7 in the root-side stationary ring portion 4 </ b> B and is externally attached to the boss portion 5 </ b> A. The outer diameter d of the O-ring 7 is set to be sufficiently larger (W> d), and the seal ring 7 in the housing recess 16 is moved by the urging force of the elastic mechanism 6 to the distal stationary ring portion 4A. The side peripheral surface 17 to be pressed toward the side has a configuration in which it is formed in a conical surface having a flared shape that is further away from the distal-side stationary ring portion 4A in the direction of the axis P toward the inner side.

つまり、常温状態においては、Ｏリング７と収容凹部１６とには十分な径方向のクリアランスが形成されており、各部品（５Ａ，７，４Ｂ）が熱膨張する高温状態時でも収容凹部１６に位置するＯリング７を介して根元側静止輪部４Ｂとボス部５Ａとが径方向に強く押されてＯリング７の締め代がきつくなるということが生じないものとなる。また、高温となって各部品（５Ａ，７，４Ｂ）が熱膨張した際に、上記クリアランスが無くなってＯリング７を、その外径部からコイルスプリング６による押圧力を阻害しない程度に締める構成でも良い。   That is, in the normal temperature state, a sufficient radial clearance is formed between the O-ring 7 and the receiving recess 16, and even in a high temperature state where each component (5A, 7, 4B) is thermally expanded, The root-side stationary ring portion 4B and the boss portion 5A are strongly pressed in the radial direction via the positioned O-ring 7 so that the tightening margin of the O-ring 7 does not occur. Further, when each component (5A, 7, 4B) is thermally expanded at a high temperature, the clearance is eliminated, and the O-ring 7 is tightened from the outer diameter portion to the extent that the pressing force by the coil spring 6 is not hindered. But it ’s okay.

その結果、静止密封環４の追従不良、即ちシール不良が起らないように改善されたメカニカルシールを実現することができるのである。そして、収容凹部１６の円錐面となる側周面１７により、Ｏリング７と根元側静止輪部４Ｂとのシール性が、温度範囲の如何に拘らずに向上する利点もある。尚、根元側静止輪部４Ｂと先端側静止輪部４Ａとの間隙ｅによる前述の効果は、参考実施例、実施例２，３のものにでも同様に発揮される。 As a result, it is possible to realize an improved mechanical seal so that the follow-up failure of the stationary seal ring 4, that is, the seal failure does not occur. And there exists an advantage which the sealing performance of the O-ring 7 and the root side stationary ring part 4B improves by the side peripheral surface 17 used as the conical surface of the accommodation recessed part 16 irrespective of a temperature range. In addition, the above-described effect due to the gap e between the root side stationary ring portion 4B and the tip side stationary ring portion 4A is also exhibited in the reference embodiment and the second and third embodiments .

実施例１のメカニカルシールの構造を示す要部の断面図Sectional drawing of the principal part which shows the structure of the mechanical seal of Example 1. 参考実施例のメカニカルシールの構造を示す要部の断面図Sectional drawing of the principal part which shows the structure of the mechanical seal of a reference Example . 実施例２のメカニカルシールの構造を示す要部の断面図Sectional drawing of the principal part which shows the structure of the mechanical seal of Example 2 . 実施例３のメカニカルシールの構造を示す要部の断面図Sectional drawing of the principal part which shows the structure of the mechanical seal of Example 3 . タンデム型メカニカルシール装置の構造を示す要部の断面図Sectional drawing of the principal part which shows the structure of a tandem type mechanical seal device 比較例によるメカニカルシールの構造を示す要部の断面図Sectional drawing of the principal part which shows the structure of the mechanical seal by a comparative example 従来構造によるメカニカルシールの構造を示す要部の断面図Sectional drawing of the principal part which shows the structure of the mechanical seal by a conventional structure

１ 回転軸
２ 回転密封環
３ シールハウジング
４ 静止密封環
４Ａ 先端側静止輪部
４Ｂ 根元側静止輪部
５ リテーナ
５Ａ ボス部
６ 弾性機構
７ シールリング
１３ シールリングを収容する部分
１４ 内孔部
１５ 円錐面
１６ シールリングを収容する収容凹部
１７ 側周面
Ｄ シールリングを収容する部分の内径
Ｐ 軸心
Ｓ シール部
Ｗ シールリングを収容する収容凹部の内径
ｄ シールリングの外径 DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Rotating sealing ring 3 Seal housing 4 Stationary sealing ring 4A Tip side stationary ring part 4B Root side stationary ring part 5 Retainer 5A Boss part 6 Elastic mechanism 7 Seal ring 13 Part which accommodates seal ring 14 Inner hole part 15 Cone Surface 16 Receiving recess for housing the seal ring 17 Side peripheral surface D Inner diameter of the portion for housing the seal ring P Shaft S Seal portion W Inner diameter of the housing recess for housing the seal ring

Claims (2)

回転軸と一体回転する回転密封環と、
シールハウジングに対して回転不能で、かつ、前記回転軸の軸心方向に移動自在に支持される静止密封環と、
前記静止密封環を前記軸心方向への移動が自在な状態に外嵌するボス部を有するとともに前記シールハウジングに固定されるリテーナと、
前記静止密封環を前記回転密封環に押付けるべく前記リテーナと前記静止密封環との間に介装される弾性機構と、
前記ボス部と前記静止密封環との間をシールするためのシールリングとを有して、
前記回転密封環と前記静止密封環との間がシールされるように構成されるメカニカルシールであって、
前記静止密封環が、前記回転密封環との間にシール部を形成する先端側静止輪部と、前記弾性機構による押圧力を受けるＰＥＥＫ製の根元側静止輪部と、を前記軸心方向に並べてステンレス材製の前記ボス部に外嵌することで構成されており、
前記根元側静止輪部と前記ボス部との間に前記シールリングが介装されるとともに、前記根元側静止輪部の熱膨張係数が前記ボス部の熱膨張係数より大となるように設定されているメカニカルシール。 A rotary seal ring that rotates integrally with the rotary shaft;
A stationary sealing ring that is non-rotatable with respect to the seal housing and is supported so as to be movable in the axial direction of the rotating shaft;
A retainer that has a boss part that fits the stationary seal ring in a state in which the stationary seal ring is movable in the axial direction and is fixed to the seal housing;
An elastic mechanism interposed between the retainer and the stationary sealing ring to press the stationary sealing ring against the rotating sealing ring;
A seal ring for sealing between the boss portion and the stationary seal ring,
A mechanical seal configured to be sealed between the rotary seal ring and the stationary seal ring,
The stationary sealing ring includes a distal-side stationary ring portion that forms a seal portion between the stationary sealing ring and a PEEK-made stationary stationary ring portion that receives a pressing force by the elastic mechanism in the axial direction. It is configured by fitting outside the boss part made of stainless steel side by side,
The seal ring is interposed between the root-side stationary ring part and the boss part, and the coefficient of thermal expansion of the root-side stationary ring part is set to be larger than the coefficient of thermal expansion of the boss part. Mechanical seal. 前記シールリングが、前記根元側静止輪部と前記先端側静止輪部との間をシールする手段に兼用されている請求項１に記載のメカニカルシール。 The mechanical seal according to claim 1, wherein the seal ring is also used as a means for sealing between the root-side stationary ring portion and the tip-side stationary ring portion .
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CN105952903A (en) * 2016-06-30 2016-09-21 台州市星光真空设备制造有限公司 Mechanical seal

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5593519B2 (en) * 2010-03-31 2014-09-24 イーグル工業株式会社 Piping connection mechanism for seal device and mechanical seal device
CN102313021B (en) * 2011-09-22 2014-04-02 丹东克隆集团有限责任公司 Mechanical sealing device for integrated water seal
WO2013054610A1 (en) * 2011-10-11 2013-04-18 イーグル工業株式会社 Divided mechanical seal device
CN102506177B (en) * 2011-10-28 2014-04-30 合肥通用机械研究院 Sealing device with double floating end faces
CN102635696B (en) * 2012-04-24 2015-07-22 大连橡胶塑料机械股份有限公司 Mechanical sealing device for underwater pelletizing
CN107932382A (en) * 2018-01-10 2018-04-20 郑州飞龙汽车部件有限公司 A kind of sealing ring installs fixture
CN112589723A (en) * 2020-12-10 2021-04-02 福建福清核电有限公司 Assembly tool and method for box-packed mechanical seal

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0396469U (en) * 1990-01-23 1991-10-02

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2513323B2 (en) * 1989-09-07 1996-07-03 トヨタ自動車株式会社 Abnormality detection device for hydraulic pressure source device

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0396469U (en) * 1990-01-23 1991-10-02

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105952903A (en) * 2016-06-30 2016-09-21 台州市星光真空设备制造有限公司 Mechanical seal

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