JPH025949B2 - - Google Patents
Info
- Publication number
- JPH025949B2 JPH025949B2 JP56046245A JP4624581A JPH025949B2 JP H025949 B2 JPH025949 B2 JP H025949B2 JP 56046245 A JP56046245 A JP 56046245A JP 4624581 A JP4624581 A JP 4624581A JP H025949 B2 JPH025949 B2 JP H025949B2
- Authority
- JP
- Japan
- Prior art keywords
- narrow grooves
- sliding surface
- mechanical seal
- annular groove
- sliding
- 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
- 238000007789 sealing Methods 0.000 claims description 25
- 239000007788 liquid Substances 0.000 claims description 20
- 239000012530 fluid Substances 0.000 claims description 13
- 230000002093 peripheral effect Effects 0.000 claims description 12
- 238000005086 pumping Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 description 14
- 230000000694 effects Effects 0.000 description 4
- 230000001050 lubricating effect Effects 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000012360 testing method Methods 0.000 description 3
- 239000006061 abrasive grain Substances 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005530 etching Methods 0.000 description 1
- 238000005187 foaming Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000003672 processing method Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
- F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
- F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Sealing (AREA)
Description
【発明の詳細な説明】
本発明はメカニカルシールに関し、さらに詳し
くは液体ならびにガスの双方を密封するメカニカ
ルシールにおいて、摺接面の面性状に改良を施こ
すことによつて密封性と耐久性の双方に優れたメ
カニカルシールを提供することを目的とする。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to mechanical seals, and more particularly to mechanical seals that seal both liquid and gas, by improving the surface properties of the sliding surfaces to improve sealing performance and durability. The aim is to provide superior mechanical seals to both parties.
従来、メカニカルシールにおいて、その洩れを
阻止するため当該メカニカルシールを構成するシ
ートリングおよび従動リングの摺接面に関して
は、該摺接面の面精度を向上させ、該摺接面の面
圧を大にして密封能力を向上する方法、また該摺
接面に切り傷を形成し、そのポンピング効果によ
つて密封能力を向上する方法が広く知られてい
る。しかし上記従来技術はともに密封性が改善さ
れる反面、摺動発熱量が増大し、該摺接面に熱変
形、摩耗等の熱劣化を生じたり、さらには該摺接
面に焼付、クラツク、発泡等の密封破壊が生じた
りして結果的に耐久密封性が低下する欠点を有し
ていた。 Conventionally, in mechanical seals, in order to prevent leakage, the surface precision of the sliding surfaces of the seat ring and driven ring that constitute the mechanical seal has been improved and the surface pressure of the sliding surfaces has been increased. There are widely known methods of improving the sealing ability by forming cuts on the sliding contact surface and using the pumping effect thereof to improve the sealing ability. However, while both of the above conventional techniques improve the sealing performance, the amount of heat generated by sliding increases, causing thermal deterioration such as thermal deformation and wear on the sliding contact surface, and furthermore, causing seizure, cracking, etc. on the sliding contact surface. This has the disadvantage that seal failure such as foaming occurs, resulting in a decrease in durable sealing performance.
本願出願人は以上の点に鑑み、先般、流体を密
封するメカニカルシールに関して、その構成部品
であるシートリングもしくは従動リングの摺接面
に、その両端を上記摺接面の外周端ならびに内周
端に至到させ、かつその方向を相対的回転方向の
前方ならびに後方に傾斜させる所要数の細溝を設
けるとともに該細溝のうちポンピング作用をなさ
しめるための相対的回転方向の細溝を支配的に設
けたメカニカルシールを発明し、これを出願した
が（特願昭55−153840号）（特開昭57−79363号公
報）、本発明は上記発明に係る摺接面にさらに所
要の環状溝を形成することによつて密封流体であ
る液体のほかにガスをも密封するメカニカルシー
ルの密封性および耐久性を向上する点に改良を施
こしたものである。すなわち上記発明は密封液体
に対しては極めて高性能の密封力ならびに潤滑力
を奏するものの、液体とともにガスをも密封する
場合には該密封ガスが摺接面間から洩れる虞れを
有していた。すなわち、細溝の本数や傾きは使用
条件を考慮して決定されるのであるが、本数が少
なかつたり、傾きが緩やかだつたりする場合には
摺接面の外周端から内周端に至るまでに細溝を横
切らなかつたり、横切る本数が少なかつたりす
る。ところが、メカニカルシールの停止中には細
溝以外の部分では液体膜がなくなつてしまい、そ
のためにガス洩れのおそれがあつたのである。そ
こで本発明はこれに対処せんと、ガス洩れの防止
に効果的な流体膜（油膜）の形成、維持に着目
し、密封液体ならびに密封ガスの洩れを阻止する
メカニカルシールにおいて、その構成部品であり
密封部を形成するシートリングもしくは従動リン
グの摺接面に、該摺接面の仮想中心点と略同一の
中心点になる環状溝を形成するとともにその両端
を上記摺接面の外周端ならびに内周端に至到さ
せ、かつその方向を相対的回転方向ならびに後方
に傾斜させる所要数の細溝を設け、さらに該細溝
のうちポンピング作用をなさしめるための細溝
を、その吸排能力において支配的に設けたことを
特徴とする。このように構成することにより、摺
接面の外周端から内周端に至るには必らず環状溝
を横切らなければならなくなる。そして、環状溝
の部分ではメカニカルシール停止中でも液体膜が
形成されている。したがつて、細溝の本数が少な
かつたり、傾きが緩やかだつたりしてもこの液体
膜によりガス洩れは効果的に防止される。このよ
うな作用効果を得るためには、環状溝と密封流体
の間に連続した摺接面部分が存在し、この摺接面
部分に細溝すなわち停止時に密封液体の流れが生
じない細い溝が形成されていることが必要であ
る。 In view of the above points, the applicant recently proposed that, regarding a mechanical seal that seals fluid, both ends of the sliding contact surface of the seat ring or driven ring, which is a component part thereof, be attached to the outer peripheral end and the inner peripheral end of the sliding contact surface. A required number of narrow grooves are provided so that the direction of the narrow grooves reaches forward and backward in the direction of relative rotation. However, the present invention has invented and applied for a mechanical seal provided in the above invention (Japanese Patent Application No. 55-153840) (Japanese Unexamined Patent Publication No. 57-79363). The mechanical seal is improved in that it improves the sealing performance and durability of the mechanical seal, which seals not only liquid but also gas as a sealing fluid. In other words, although the above-mentioned invention exhibits extremely high sealing force and lubricating force for sealed liquid, when sealing gas as well as liquid, there is a risk that the sealing gas may leak from between the sliding surfaces. . In other words, the number and inclination of the narrow grooves are determined by taking into consideration the conditions of use, but if the number of narrow grooves is small or the inclination is gentle, the grooves will extend from the outer edge to the inner edge of the sliding surface. Sometimes the thin grooves are not crossed, or the number of narrow grooves crossed is small. However, while the mechanical seal was stopped, the liquid film disappeared in areas other than the narrow grooves, posing a risk of gas leakage. Therefore, in order to solve this problem, the present invention focuses on the formation and maintenance of a fluid film (oil film) that is effective in preventing gas leakage. An annular groove whose center point is approximately the same as the virtual center point of the sliding surface is formed on the sliding surface of the seat ring or driven ring that forms the sealing part, and both ends of the groove are connected to the outer peripheral edge and the inner surface of the sliding surface. A required number of narrow grooves are provided that reach the circumferential edge and whose direction is inclined toward the relative rotational direction and rearward, and further, among the narrow grooves, the narrow grooves for performing the pumping action are controlled by their suction/discharge ability. It is characterized by having been set up. With this configuration, the annular groove must necessarily be crossed in order to reach the inner peripheral end from the outer peripheral end of the sliding surface. A liquid film is formed in the annular groove even when the mechanical seal is stopped. Therefore, even if the number of narrow grooves is small or the slope is gentle, gas leakage can be effectively prevented by this liquid film. In order to obtain such effects, there must be a continuous sliding surface between the annular groove and the sealing fluid, and this sliding surface must have a narrow groove, that is, a narrow groove in which the sealing fluid does not flow when the fluid is stopped. It is necessary that it be formed.
以下、本発明の一実施例を図面にしたがつて説
明すると、図中１は要部を拡大して表わした外部
加圧型のメカニカルシールであつて、ハウジング
２に固定されたシートリング３と、該シートリン
グ３に挿通される回転軸４に固定され、かつ該回
転軸４とともに回転する従動リング５の摺接によ
つて当該メカニカルシール１の外周に封入された
液体ＡおよびガスＢの洩れを阻止せんとするもの
であり、上記従動リング５の摺接面５ａには環状
溝６ならびに細溝７，７…８，８…が形成されて
いる。該環状溝６は当該メカニカルシール１の回
転中には、該環状溝６内に液体Ａを保留して独自
の流体膜（油膜）を形成、維持し、ガスＢの洩れ
を阻止するとともに回転軸４に伴なつて当該メカ
ニカルシール１が停止した時、上記従動リング５
の摺接面５ａとシートリング３の摺接面３ａ間に
存在していた流体膜（油膜）が消滅（油膜切れ）
し、摺接面３ａ，５ａ間に密封ガスＢの洩れが生
ずることがないように当該メカニカルシール１の
停止中にも流体膜（油膜）を形成、維持するもの
で、摺接面５ａの仮想中心点Ｏと略同一の中心点
に形成されるが、その形成個所をさらに具体的に
示すならば、第３図に示すように摺接面５ａの摺
接面幅ｄにおいて、該摺接面５ａの外周端５ｂお
よび内周端５ｃから各々摺接面幅ｄの１／４以上
離れた（すなわち摺接面幅ｄを該摺接面５ａ半径
方向に四等分割（外周端５ｂ側よりd1，d2，d3，
d4とする）して、そのd2およびd3に該当する摺接
面５ａの中央部面）個所とする。また該環状溝６
の溝深さおよび溝幅も当該メカニカルシール１の
停止中に流体膜（油膜）を形成、維持するに充分
な数値とし、すなわち溝深さを10μ以上、溝幅を
30μ以上に形成するが望ましい。第４図は該環状
溝６の溝深さとガス洩れ量の関係を示す試験グラ
フであつて、溝深さを10μ未満とすると極端に密
封性能が低下することを示している。また溝幅の
最大限は該摺接面５ａの摺接面幅ｄの１／２
（１／2d）である。つぎに上記細溝７，７，…
８，８…は上記従動リング５の回転方向（矢印
Ｃ）に対して摺接面５ａ直径方向の後方に傾斜す
る細溝７，７，…と、同じく前方に傾斜する細溝
８，８…とからなり、両方向の細溝７，７…８，
８…ともその両端を摺接面５ａの外周端５ｂなら
びに内周端５ｃに至到させるとともに相互に交叉
するように形成される。該細溝７，７…８，８…
の平面形状は第２図に示すような直線状に限られ
ず、第５図に示すように曲線状としてもよく、さ
らに直線状と曲線状の細溝の混合としてもよい。
該細溝７，７…８，８…は上記従動リング５の回
転に伴なつて密封した液体Ａを吸排することによ
つて摺接面３ａ，５ａ間の潤滑ならびに密封を目
的とするものであつて、まず当該メカニカルシー
ル１が被装着機器等の所定個所（第１図参照）に
装着され、当該メカニカルシール１の従動リング
５が回転軸４に伴なつて回転すると、密封液体Ａ
はその粘性作用と摺接面５ａの回転方向によつて
上記前方傾斜の細溝８，８…内に吸入され、該細
溝８，８…内に保留されつつ軸中心方向へ移動
し、上記環状溝６との交叉点へ至つてその方向を
二分し、一方の該環状溝６へ移行する液体Ａは該
環状溝６を充満させるとともに他方の上記前方傾
斜の細溝８，８…を直進する液体Ａは上記後方傾
斜の細溝７，７…との交叉点にまで至り、該交叉
点において後方傾斜の細溝７，７…に移行し摺接
面５ａの内周端５ｃに至ることなく吸入側（外周
端５ｂ側）へ排出される。しかして液体Ａは上記
前方傾斜の細溝８，８…内を移動するとき潤滑流
体膜（油膜）を形成して従動リング５の摺接面５
ａとシートリング３の摺接面３ａ間を潤滑する。
したがつて細溝７，７…８，８…は前方傾斜の細
溝８，８…が主潤滑部、後方傾斜の細溝７，７…
が主密封部として機能するものであり、したがつ
て両細溝７，７…８，８…は摺接面３ａ，５ａ間
に吸入された流体量を上回る排出能力を有するよ
うに、換言すれば後方傾斜の細溝７，７…の排出
能力が前方傾斜の細溝８，８…の吸入能力を上回
るように、該後方傾斜の細溝７，７…の数量、形
状もしくは方向などが支配的になるように設けら
れる。この場合、当該メカニカルシール１の停止
時における液体Ａの洩れを完全に止めるためには
細溝７，７…８，８…の影響を受けないようにし
なければならず、そのためには該細溝７，７…
８，８…を0.2〜0.7μ以内に仕上げることにより
目的を達する。またある程度の洩れを許容する場
合、停止時間が短い場合、機器において停止時、
液がメカシール部に来ない場合または停止時に圧
力がなくなる場合には細溝７，７…８，８…は
1.0〜3μ程度までは許容され、この範囲であれば
通常のシール効果を得ることができる。したがつ
て細溝７，７…８，８…の深さはその目的によつ
て0.2〜3μの範囲にコントロールされる。また前
方傾斜の細溝８，８…と後方傾斜の細溝７，７…
の形成比率は
前方傾斜の細溝８，８…の数／後方傾斜の細溝７，７
…の数＝１／5000〜１／２
となるように形成するとよい（細溝７，７…８，
８…の大きさを同一にするとき）。 Hereinafter, one embodiment of the present invention will be described with reference to the drawings. In the drawing, reference numeral 1 denotes an external pressure type mechanical seal whose main parts are enlarged, and includes a seat ring 3 fixed to a housing 2, The leakage of liquid A and gas B sealed on the outer periphery of the mechanical seal 1 is prevented by the sliding contact of the driven ring 5, which is fixed to the rotating shaft 4 inserted through the seat ring 3 and rotates together with the rotating shaft 4. The sliding surface 5a of the driven ring 5 is formed with an annular groove 6 and narrow grooves 7, 7...8, 8... During the rotation of the mechanical seal 1, the annular groove 6 retains the liquid A in the annular groove 6 to form and maintain its own fluid film (oil film), thereby preventing leakage of the gas B and preventing the rotation shaft from leaking. 4, when the mechanical seal 1 stops, the driven ring 5
The fluid film (oil film) that existed between the sliding contact surface 5a of the seat ring 3 and the sliding contact surface 3a of the seat ring 3 disappears (oil film runs out)
However, in order to prevent leakage of the sealing gas B between the sliding surfaces 3a and 5a, a fluid film (oil film) is formed and maintained even when the mechanical seal 1 is stopped. It is formed at approximately the same center point as the center point O, but if the location where it is formed is shown more specifically, as shown in FIG. 1/4 or more of the sliding surface width d from the outer peripheral end 5b and inner peripheral end 5c of 5a (that is, the sliding surface width d is divided into four equal parts in the radial direction of the sliding surface 5a (d from the outer peripheral end 5b side) 1 , d2 , d3 ,
d 4 ), and the center portion of the sliding surface 5a corresponding to d 2 and d 3 ). Also, the annular groove 6
The groove depth and groove width should also be set to values sufficient to form and maintain a fluid film (oil film) while the mechanical seal 1 is stopped, that is, the groove depth should be 10 μ or more and the groove width should be
It is desirable to form it to a thickness of 30μ or more. FIG. 4 is a test graph showing the relationship between the groove depth of the annular groove 6 and the amount of gas leakage, and shows that when the groove depth is less than 10 μm, the sealing performance is extremely degraded. The maximum groove width is 1/2 of the sliding surface width d of the sliding surface 5a.
(1/2d). Next, the above-mentioned narrow grooves 7, 7,...
8, 8... are narrow grooves 7, 7,... which are inclined rearward in the diametrical direction of the sliding surface 5a with respect to the rotational direction (arrow C) of the driven ring 5, and narrow grooves 8, 8... which are also inclined forward. It consists of narrow grooves 7, 7...8, in both directions.
8... are formed so that both ends thereof reach the outer peripheral end 5b and inner peripheral end 5c of the sliding surface 5a and intersect with each other. The narrow grooves 7, 7...8, 8...
The planar shape is not limited to the linear shape shown in FIG. 2, but may be curved as shown in FIG. 5, or may be a mixture of linear and curved narrow grooves.
The narrow grooves 7, 7...8, 8... are intended to lubricate and seal between the sliding surfaces 3a, 5a by sucking and discharging the sealed liquid A as the driven ring 5 rotates. First, the mechanical seal 1 is attached to a predetermined location of a device to be attached (see Fig. 1), and when the driven ring 5 of the mechanical seal 1 rotates with the rotating shaft 4, the sealing liquid A is released.
is sucked into the forward-sloping narrow grooves 8, 8... by its viscous action and the rotating direction of the sliding surface 5a, and moves toward the axial center while being retained in the narrow grooves 8, 8... The liquid A reaches the intersection point with the annular groove 6 and bisects the direction, and the liquid A moving to one of the annular grooves 6 fills the annular groove 6 and goes straight through the other narrow grooves 8, 8, which are inclined forward. The liquid A reaches the point of intersection with the rearwardly inclined narrow grooves 7, 7, . Instead, it is discharged to the suction side (outer peripheral end 5b side). When the liquid A moves in the forward-sloping narrow grooves 8, 8..., it forms a lubricating fluid film (oil film) on the sliding surface 5 of the driven ring 5.
lubricate between a and the sliding surface 3a of the seat ring 3.
Therefore, the narrow grooves 7, 7...8, 8... are the main lubrication parts, and the narrow grooves 8, 8... which are inclined forward are the main lubricating parts, and the narrow grooves 7, 7... which are inclined backward.
In other words, both the narrow grooves 7, 7...8, 8... have a discharge capacity exceeding the amount of fluid sucked between the sliding surfaces 3a, 5a. For example, the quantity, shape, direction, etc. of the backwardly inclined narrow grooves 7, 7, etc. are controlled so that the discharge capacity of the backwardly inclined narrow grooves 7, 7... exceeds the suction capacity of the forwardly inclined narrow grooves 8, 8... It is set up so that it becomes a target. In this case, in order to completely stop the leakage of liquid A when the mechanical seal 1 is stopped, it is necessary to prevent it from being affected by the narrow grooves 7, 7...8, 8... 7,7...
The purpose is achieved by finishing 8, 8... within 0.2 to 0.7μ. In addition, when a certain amount of leakage is allowed, when the downtime is short, or when the equipment is stopped,
If the liquid does not reach the mechanical seal or if the pressure disappears when stopped, the narrow grooves 7, 7...8, 8...
A thickness of about 1.0 to 3μ is permissible, and a normal sealing effect can be obtained within this range. Therefore, the depth of the narrow grooves 7, 7...8, 8... is controlled within the range of 0.2 to 3μ depending on the purpose. Also, forward-sloping narrow grooves 8, 8... and backward-sloping narrow grooves 7, 7...
The formation ratio is: Number of forward-sloping narrow grooves 8, 8.../Backward-sloping narrow grooves 7, 7
It is preferable to form them so that the number of grooves is 1/5000 to 1/2 (narrow grooves 7, 7...8,
8) when making the size of... the same).
以上のように構成されるメカニカルシール１に
あつて従動リング５の摺接面５ａに形成される環
状溝６と細溝７，７…８，８…は圧倒的に広面積
を有し、かつ極めて精度にラツピングされた平坦
部に対しあらかじめ密封能力ならびに潤滑能力を
計算した上で形成されるもので、以下のような方
法によつて形成される。すなわち第一の形成方法
は上記従動リング５の摺接面５ａにあらかじめ感
光剤を塗布して上記環状溝６ならびに細溝７，７
…８，８…を感光印画させ、その後、該細溝６な
らびに細溝７，７…８，８…をエツヂング処理す
る方法であり、第二の形成方法は上記従動リング
５の摺接面５ａにインク類をもつて上記環状溝６
ならびに細溝７，７…８，８…をスタンプもしく
は印刷し、その後、該環状溝６ならびに細溝７，
７…８，８…をエツヂング処理する方法である。
この二方法によれば上記環状溝６等が設計図に図
示できる形状である限り、任意の形状（構成数を
含む）の環状溝６と細溝７，７…８，８…を極め
て精度かつ廉価に形成することが可能である。第
三の形成方法は上記第一および第二の形成方法を
部分的に使用するものであり、すなわち、まず上
記環状溝６を型成形法、機械加工法、レーザー加
工法等で形成した後に細溝７，７…８，８…につ
いてのみ上記第一および第二の形成方法によつて
その形成をする方法である。またその形成順序は
逆としてもよい。第四の形成方法は上記環状溝６
ならびに細溝７，７…８，８…を砥粒もしくは砥
粒を用いた製品または切削工具を用いて形成する
方法である。以上のような方法によつて品質の安
定した上記構成になるメカニカルシール１の量産
化が可能である。 In the mechanical seal 1 constructed as described above, the annular groove 6 and the narrow grooves 7, 7, 8, 8, . . . formed on the sliding surface 5a of the driven ring 5 have an overwhelmingly wide area, and It is formed by calculating the sealing ability and lubrication ability of a flat part that has been wrapped with great precision in advance, and is formed by the following method. That is, the first forming method is to apply a photosensitive agent to the sliding surface 5a of the driven ring 5 in advance to form the annular groove 6 and the narrow grooves 7, 7.
...8, 8... is photosensitive printed, and then the narrow grooves 6 and the narrow grooves 7, 7...8, 8... are etched. The second forming method is the sliding surface 5a of the driven ring 5. The annular groove 6 is filled with ink.
and the narrow grooves 7, 7...8, 8... are stamped or printed, and then the annular groove 6 and the narrow grooves 7,
This is a method of etching 7...8,8...
According to these two methods, as long as the annular groove 6 etc. have a shape that can be illustrated in the design drawing, the annular groove 6 and narrow grooves 7, 7, 8, 8, etc. of any shape (including the number of configurations) can be formed with extremely high precision. It can be formed at low cost. The third forming method partially uses the first and second forming methods described above, that is, first the annular groove 6 is formed by a molding method, a machining method, a laser processing method, etc., and then a thin groove is formed. In this method, only the grooves 7, 7...8, 8... are formed by the first and second forming methods described above. Moreover, the order of formation may be reversed. The fourth method is to form the annular groove 6.
Also, the narrow grooves 7, 7...8, 8... are formed using abrasive grains, a product using abrasive grains, or a cutting tool. By the method described above, it is possible to mass-produce the mechanical seal 1 having the above-mentioned structure with stable quality.
第６図および第７図は以上の構成になるメカニ
カルシール１の密封性能、耐久性能の試験グラフ
であつて、摺接面５ａに上記環状溝６ならびに細
溝７，７…８，８…を形成した本願発明品が従来
品に比して極めて優れた性能を発揮し得ることを
示している。なお上記実施例においては従動リン
グ５の摺接面５ａに上記構成の環状溝６ならびに
細溝７，７…８，８…を形成したものを示した
が、当該環状溝６ならびに細溝７，７…８，８…
はシートリング３の摺接面３ａに形成してもよ
く、この場合には該シートリング３の相対的回転
方向に対して摺接面３ａ直径方向の後方に傾斜す
る細溝７，７…がその吸排能力において支配的と
なるように形成される。さらにメカニカルシール
１は外部加圧型に限らず内部加圧型であつてもよ
い。ただしこの場合は上記細溝７，７…８，８…
のうち前方傾斜の細溝８，８…が密封効果を奏
し、後方傾斜の細溝７，７…が潤滑効果を奏する
ので、形成にあたつてその所要構成数は逆点す
る。またその成形は摺接面３ａ，５ａのラツピン
グの前後いずれでもよく、さらに上記環状溝６は
かならずしも正円形状であることを要せず、また
複数本形成してもよい。 FIGS. 6 and 7 are test graphs of the sealing performance and durability performance of the mechanical seal 1 having the above structure, in which the annular groove 6 and narrow grooves 7, 7...8, 8... are formed on the sliding surface 5a. This shows that the formed product of the present invention can exhibit extremely superior performance compared to conventional products. In the above embodiment, the annular groove 6 and the narrow grooves 7, 7, 8, 8, etc. having the above structure are formed on the sliding surface 5a of the driven ring 5, but the annular groove 6 and the narrow grooves 7, 8, 8, . 7...8,8...
may be formed on the sliding surface 3a of the seat ring 3. In this case, narrow grooves 7, 7, . It is formed to be dominant in its suction and discharge ability. Furthermore, the mechanical seal 1 is not limited to an externally pressurized type, but may be an internally pressurized type. However, in this case, the narrow grooves 7, 7...8, 8...
Among them, the forwardly inclined narrow grooves 8, 8... have a sealing effect, and the backwardly inclined narrow grooves 7, 7... have a lubricating effect, so the required number of grooves in forming them is opposite. Further, the forming may be performed either before or after the wrapping of the sliding surfaces 3a, 5a, and the annular groove 6 does not necessarily have to have a perfect circular shape, and a plurality of grooves may be formed.
本発明は以上のような構成からなり、メカニカ
ルシールのシートリングもしくは従動リングの摺
接面に所要の環状溝ならびに細溝を形成すること
により、液体とガスの双方を密封する場合に極め
て優れた密封性能と耐久性能を得ることができ
る。また本発明メカニカルシールはその雰囲気条
件によつて、その洩れ量ならびに発熱量を自在に
制御でき、その効果は極めて大きい。 The present invention has the above-described configuration, and by forming the required annular groove and narrow groove on the sliding surface of the seat ring or driven ring of a mechanical seal, it is extremely excellent in sealing both liquid and gas. Sealing performance and durability can be obtained. In addition, the mechanical seal of the present invention can freely control the amount of leakage and the amount of heat generated depending on the atmospheric conditions, which is extremely effective.
図面は本発明の一実施例を示すもので、第１図
は本発明に係るメカニカルシールの取付状態を示
す要部拡大正断面図、第２図および第５図は本発
明メカニカルシールの従動リング摺接面の正面
図、第３図は第２図における―線一部拡大断
面図、第４図、第６図および第７図は本発明メカ
ニカルシールの試験グラフである。
１…メカニカルシール、２…ハウジング、３…
シートリング、３ａ…シートリングの摺接面、４
…回転軸、５…従動リング、５ａ…従動リングの
摺接面、６…環状溝、７，８…細溝、Ａ…密封液
体、Ｂ…密封ガス。
The drawings show one embodiment of the present invention, and FIG. 1 is an enlarged front sectional view of the main part showing the installed state of the mechanical seal according to the present invention, and FIGS. 2 and 5 are a driven ring of the mechanical seal according to the present invention. FIG. 3 is a partially enlarged sectional view taken along the line -- in FIG. 2, and FIGS. 4, 6, and 7 are test graphs of the mechanical seal of the present invention. 1... Mechanical seal, 2... Housing, 3...
Seat ring, 3a... Seat ring sliding surface, 4
... Rotating shaft, 5... Driven ring, 5a... Sliding surface of driven ring, 6... Annular groove, 7, 8... Thin groove, A... Sealing liquid, B... Sealing gas.
Claims (1)
シートリングに挿通される回転軸に固定され、か
つ該回転軸とともに回転する従動リングの摺接に
よつて密封流体である液体およびガスの洩れを阻
止するメカニカルシールにおいて、上記シートリ
ングもしくは従動リングの摺接面に、該摺接面の
仮想中心点と略同一の中心点になる環状溝を形成
するとともにその両端を上記摺接面の外周端なら
びに内周端に至到させ、かつその方向を相対的回
転方向の前方ならびに後方に傾斜させる所要数の
細溝を設け、さらに該細溝のうちポンピング作用
をなさしめるための細溝を、その吸排能力におい
て支配的に設けたことを特徴とするメカニカルシ
ール。1. Preventing leakage of liquid and gas, which are sealing fluids, by sliding contact between a seat ring fixed to the housing and a driven ring that is fixed to a rotating shaft inserted through the seat ring and rotates together with the rotating shaft. In a mechanical seal, an annular groove is formed on the sliding surface of the seat ring or the driven ring, the center of which is approximately the same as the virtual center point of the sliding surface, and both ends of the annular groove are connected to the outer peripheral edge of the sliding surface and the inner surface of the sliding surface. A required number of narrow grooves are provided that reach the circumferential edge and whose directions are inclined forward and backward in the relative rotation direction, and among the narrow grooves, the narrow grooves for performing a pumping action are determined by their suction and discharge capacity. A mechanical seal characterized by being dominantly provided in.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4624581A JPS57161367A (en) | 1981-03-31 | 1981-03-31 | Mechanical seal |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4624581A JPS57161367A (en) | 1981-03-31 | 1981-03-31 | Mechanical seal |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57161367A JPS57161367A (en) | 1982-10-04 |
| JPH025949B2 true JPH025949B2 (en) | 1990-02-06 |
Family
ID=12741757
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4624581A Granted JPS57161367A (en) | 1981-03-31 | 1981-03-31 | Mechanical seal |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57161367A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0461435A (en) * | 1990-06-29 | 1992-02-27 | Nec Corp | Optical repeater |
| JPH05218974A (en) * | 1991-11-15 | 1993-08-27 | Nec Corp | Optical amplifier repeater |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017209482A1 (en) * | 2017-06-06 | 2018-12-06 | Audi Ag | Ring for a mechanical seal |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB888198A (en) * | 1958-06-13 | 1962-01-31 | Goetzewerke | Shaft seal |
| US3973781A (en) * | 1972-05-23 | 1976-08-10 | Veb Gummikombinat Berlin | Self-lubricating seal |
-
1981
- 1981-03-31 JP JP4624581A patent/JPS57161367A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB888198A (en) * | 1958-06-13 | 1962-01-31 | Goetzewerke | Shaft seal |
| US3973781A (en) * | 1972-05-23 | 1976-08-10 | Veb Gummikombinat Berlin | Self-lubricating seal |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0461435A (en) * | 1990-06-29 | 1992-02-27 | Nec Corp | Optical repeater |
| JPH05218974A (en) * | 1991-11-15 | 1993-08-27 | Nec Corp | Optical amplifier repeater |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57161367A (en) | 1982-10-04 |
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