JP2010164118A - Method and apparatus for sealing shaft sealing device for slurry - Google Patents
Method and apparatus for sealing shaft sealing device for slurry Download PDFInfo
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本発明は、固形物を含むスラリーを取扱うポンプ、分散機、撹拌機、粉砕機等（以下、これらを総称して単に粉砕機という。したがって本発明において粉砕機とは、ポンプ、分散機、撹拌機、粉砕機等を含むものとなる。）に設けられ、メカニカルシールを備えた軸封装置において、メカニカルシールの回転環と固定環との摺動部にスラリー中の固形物が入り込んで噛みこむことによりシール効果が損なわれるのを防止する方法及び装置に関する。 The present invention refers to a pump, a disperser, a stirrer, a pulverizer, etc. (hereinafter collectively referred to simply as a pulverizer. These pulverizers in the present invention are a pump, a disperser, a stirrer, etc. In a shaft seal device provided with a mechanical seal, solid matter in the slurry enters and slides into the sliding portion between the rotating ring and stationary ring of the mechanical seal. It is related with the method and apparatus which prevent that a sealing effect is impaired by this.
メカニカルシールは、回転軸に取付けられる回転環と、該回転環に押付けられるケーシング側の固定環よりなり、スラリーを取扱う粉砕機では、回転軸の軸封装置として、メカニカルシールを回転軸の軸方向に一対配置し、メカニカルシール間にシール液を注入して回転環と固定環の摺動部の潤滑と冷却を行うダブルメカニカルシールが多く採用されている。 The mechanical seal is composed of a rotating ring attached to the rotating shaft and a casing-side fixed ring pressed against the rotating ring. In a pulverizer handling slurry, the mechanical seal is used as a shaft sealing device for the rotating shaft in the axial direction of the rotating shaft. Many double mechanical seals are used which are disposed in pairs and inject a sealing liquid between the mechanical seals to lubricate and cool the sliding portions of the rotating ring and the stationary ring.
図１は、この種粉砕機用ダブルメカニカルシールの一例を示すもので、粉砕機のケーシング１に固定の本体２には、その左右にそれぞれメカニカルシール３、４が取付けられている。このうち、メカニカルシール３は、回転軸５に取着されるスリーブ６のケーシング内に突出する端部に取付けられる回転環７と、本体２に取付けられるケーシング側の固定環８と、該固定環８を回転環７に押付けるコイルバネ９とよりなっている。図中、１１及び１２はｏリングである。メカニカルシール４も、その基本構造はメカニカルシール３と同じであり、説明を省略する。 FIG. 1 shows an example of a double mechanical seal for this kind of pulverizer. Mechanical seals 3 and 4 are attached to the left and right sides of a main body 2 fixed to the casing 1 of the pulverizer. Among these, the mechanical seal 3 includes a rotary ring 7 attached to an end portion of the sleeve 6 attached to the rotary shaft 5 protruding into the casing, a fixed ring 8 on the casing side attached to the main body 2, and the fixed ring. The coil spring 9 presses 8 against the rotating ring 7. In the figure, 11 and 12 are o-rings. The basic structure of the mechanical seal 4 is the same as that of the mechanical seal 3, and the description thereof is omitted.
メカニカルシール３、４間には、回転環７と固定環８の摺動部１４の潤滑と冷却を行うためにシール液が注入される。このシール液は図２に示す循環用ポンプ１７によってタンク１６から注入口１８に注入され、回転環７と固定環８の摺動部１４の潤滑と冷却を行ったのち注出口１９より注出されてタンク１６に戻されるサイクルで循環されるようになっており、シール液の液圧（以下、単にシール圧という）を上げるため図示していないが、抽出口１９からタンク１６に至る流路上にリリーフ弁が設けられている。タンク１６に戻されたシール液は、タンク１６のジャケット１６ａに通される冷却水によって冷却される。 Sealing liquid is injected between the mechanical seals 3 and 4 in order to lubricate and cool the sliding portions 14 of the rotating ring 7 and the stationary ring 8. The sealing liquid is injected from the tank 16 into the inlet 18 by the circulation pump 17 shown in FIG. 2, lubricates and cools the sliding portion 14 of the rotary ring 7 and the stationary ring 8, and then is poured out from the outlet 19. Although not shown in order to increase the liquid pressure of the sealing liquid (hereinafter simply referred to as the sealing pressure), it is circulated on the flow path from the extraction port 19 to the tank 16. A relief valve is provided. The sealing liquid returned to the tank 16 is cooled by cooling water passed through the jacket 16 a of the tank 16.
シールが行われるときの図１に示す摺動部に作用する軸方向の力は、シール圧による固定環８の回転環７への押付力をＦ１、コイルバネ９による固定環８の回転環７への押付力をＮ、シール圧により固定環８を回転環７より引離す方向に押戻す押戻し力をＦ２とすると、
Ｆ１＋Ｎ＞Ｆ２
の関係があり、これにより固定環８は回転環７に押付けられ、シールされるようになっている。ここでＦ１は図３において、固定環８の内外の径をｄ１及びｄ２とし、シール圧をｐ´とすると、Ｆ１＝π／４・（ｄ１ ２−ｄ２ ２）・ｐ´で表され、Ｆ２は固定環８と回転環７が接触する摺動部１４までの径をｄ３とすると、Ｆ２＝π／４・（ｄ３ ２−ｄ２ ２）・ｐ´で表される。
The axial force acting on the sliding portion shown in FIG. 1 when the sealing is performed is the pressing force of the stationary ring 8 against the rotating ring 7 by the sealing pressure F 1 , and the rotating ring 7 of the stationary ring 8 by the coil spring 9. When the pressing force of the N, the push-back to push-back force in a direction detaching from the rotating ring 7 fixed ring 8 by the seal pressure and F 2,
F 1 + N> F 2
Thus, the stationary ring 8 is pressed against the rotating ring 7 and sealed. Here, F 1 is F 1 = π / 4 · (d 1 2 −d 2 2 ) · p where, in FIG. 3, the inner and outer diameters of the stationary ring 8 are d 1 and d 2 and the sealing pressure is p ′. represented by 'and F 2 is the diameter of up to the sliding portion 14 which contacts the stationary ring 8 rotary ring 7 and d 3, F 2 = π / 4 · (d 3 2 -d 2 2) · p' It is represented by
スラリーを取扱う粉砕機において用いられるダブルメカニカルシールよりなる軸封装置では、シール圧は機内圧よりも高く設定され、摺動部の隙間も数μｍ以下に設定されているが、それにもかかわらず、スラリー中の固形物が摺動部の隙間に入り込んで噛み込み、シール効果を損なうことがある。こうした固形物の噛み込みは、摺動部の隙間が運転中の回転軸の振動によって開くことにより生ずるものと考えられる。 In the shaft seal device consisting of a double mechanical seal used in a pulverizer that handles slurry, the seal pressure is set higher than the internal pressure, and the gap of the sliding part is also set to several μm or less, nevertheless, The solid matter in the slurry may get into the gaps in the sliding portion and bite, which may impair the sealing effect. It is considered that such solid bite is caused by the gap between the sliding portions being opened by the vibration of the rotating shaft during operation.
本発明は、メカニカルシールの回転環と固定環との摺動部にスラリー中の固形物が入り込むのを防止し、シール効果を安定して維持させることができるシール方法及び装置を提供することを目的とする。 It is an object of the present invention to provide a sealing method and apparatus capable of preventing a solid matter in a slurry from entering a sliding portion between a rotating ring and a fixed ring of a mechanical seal and stably maintaining a sealing effect. Objective.
請求項１に係わる発明は、ダブルメカニカルシールを備え、メカニカルシール間にシール液が注入されるスラリー用粉砕機の軸封装置における、メカニカルシールの回転環と固定環との摺動部にスラリー中の固形物が入りこむのを防止するシール方法であって、シール液にスラリーとは化学反応を生じないシール液を用い、運転中、固定環の回転環への押付力よりも固定環の引き離し力を大にして、固定環と回転環の隙間を拡大させ、ある隙間にした状態で、該隙間を通して設定量のシール液を機内に通すようにしたことを特徴とする。 The invention according to claim 1 includes a double mechanical seal, and in a slurry at a sliding portion between a rotating ring and a stationary ring of a mechanical seal in a shaft seal device of a slurry pulverizer in which a seal liquid is injected between the mechanical seals. This is a sealing method that prevents solids from entering, and the sealing liquid uses a sealing liquid that does not cause a chemical reaction with the slurry, and during operation, the separation force of the stationary ring is greater than the pressing force of the stationary ring against the rotating ring. The gap between the stationary ring and the rotating ring is enlarged, and a predetermined amount of sealing liquid is passed through the gap in a state where the gap is set to a certain gap.
請求項２に係わる発明は、請求項１に係わる発明を実施する装置に関するもので、ダブルメカニカルシールを備え、メカニカルシール間にシール液が注入されるスラリー用粉砕機の軸封装置において、メカニカルシールが回転軸側の回転環と、ケーシング側の固定環と、該固定環を回転環に押しつけるバネとからなると共に、シール液を液圧ｐで回転環と固定環の摺動部に注入する注入手段を設け、かつ下記（１）〜（３）式を満たすことを特徴とする。
Ａ１＜Ａ２ （１）
Ｐ ＜ｐ （２）
Ｐ・Ａ３＋（ｐ＋Δｐ）・Ａ１＋（Ｎ＋ΔＮ）＝（ｐ＋Δｐ）・Ａ２ （３）
ここで、Ａ１は固定環を回転環に押付ける方向にシール圧が作用する固定環の受圧面積、Ａ２は固定環を回転環より引き離す方向にシール圧が作用する固定環の受圧面積、Ａ３は固定環を回転環に押付ける方向に機内圧Ｐが作用する固定環の受圧面積、Ｎ＋ΔＮは、前記液圧ｐのシール液の注入により前記隙間が開き、これにより増加したシール圧ｐ＋Δｐと均衡したときのバネのバネ力である。
The invention according to claim 2 relates to an apparatus for carrying out the invention according to claim 1, and is provided with a mechanical seal in a shaft seal device of a pulverizer for slurry, which is provided with a double mechanical seal and in which a sealing liquid is injected between the mechanical seals. Is composed of a rotating ring on the rotating shaft side, a fixed ring on the casing side, and a spring that presses the fixed ring against the rotating ring, and injecting the seal liquid into the sliding portion of the rotating ring and the fixed ring with a hydraulic pressure p Means are provided, and the following expressions (1) to (3) are satisfied.
A 1 <A 2 (1)
P <p (2)
P · A 3 + (p + Δp) · A 1 + (N + ΔN) = (p + Δp) · A 2 (3)
Here, A 1 is the pressure receiving area of the fixed ring receiving area of the stationary ring that acts sealing pressure in the direction to press the stationary ring to the rotating ring, A 2 is the sealing pressure in the direction of separating the fixed ring from the rotary ring acts, a 3 is the pressure receiving area of the stationary ring acts machine pressure P in a direction to press the stationary ring to the rotating ring, N + .DELTA.N, the liquid opens the gap by the injection of the sealing liquid pressure p, sealing pressure p + Delta] p was increased by this This is the spring force of the spring when balanced.
請求項３に係わる発明は、請求項２に係わる発明において、固定環と回転環との摺動部が固定環より大径をなすことを特徴とし、
請求項４に係わる発明は、請求項２又は３に係わる発明において、注入手段が定量ポンプであることを特徴とする。
The invention according to claim 3 is characterized in that, in the invention according to claim 2, the sliding portion between the stationary ring and the rotating ring has a larger diameter than the stationary ring,
The invention according to claim 4 is the invention according to claim 2 or 3, wherein the injection means is a metering pump.
本発明によると、運転中、固定環を回転環に押付ける押付力よりも回転環より引離す力が大となるため、固定環と回転環の摺動部の隙間が若干拡大してある隙間となり、機内圧Ｐより圧力の大なるシール液が前記隙間を通して機内に僅かな量であるが設定量ずつ常時流入し、これにより摺動部にスラリー中の固形物が入り込むのが防止され、シール効果を安定して維持させることができる。またポンプに定量ポンプを用いることによりシール液の流入を設定量で供給することができる。なお、定量ポンプが脈流を生ずるタイプのものである場合には、脈流を避けるためアキュムレータを設ける必要がある。 According to the present invention, during operation, since the force that separates the stationary ring from the rotating ring is greater than the pressing force that presses the stationary ring against the rotating ring, the clearance between the stationary ring and the sliding part of the rotating ring is slightly enlarged. The sealing liquid having a pressure larger than the internal pressure P is always a small amount into the machine through the gap, but constantly flows in a set amount, thereby preventing the solid matter in the slurry from entering the sliding portion. The effect can be maintained stably. Further, by using a metering pump as the pump, it is possible to supply the seal liquid in a set amount. When the metering pump is of a type that generates a pulsating flow, it is necessary to provide an accumulator to avoid the pulsating flow.
以下、本発明の実施形態について図面により説明する。図中、図１〜図３に示す従来構造と同一構造部分には同一符号を付して、その説明を省略する。
図４は、本発明に係わる回転軸１の軸封装置を構成する粉砕機用ダブルメカニカルシールを示すもので、ケーシング１に固定の本体２には、その左右にメカニカルシール２１、４が取付けられている。
Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the figure, the same components as those in the conventional structure shown in FIGS.
FIG. 4 shows a double mechanical seal for a pulverizer constituting the shaft seal device of the rotary shaft 1 according to the present invention. The main body 2 fixed to the casing 1 is provided with mechanical seals 21 and 4 on the left and right sides thereof. ing.
メカニカルシール２１は、回転軸５に取着されるスリーブ６のケーシング１内に突出する端部に取付けられる回転環２２と、本体２に取付けられるケーシング側の固定環２３と、該固定環２３を回転環２２に押付けるバネとしてのコイルバネ９よりなり、回転環２２は固定環２３に向かって径が漸次拡大して形成され、また固定環２３は一側に回転環２２に向かって径が拡大するテーパ部２４を有し、最大径のテーパ部端は固定環２３より大径で、回転環２２に押付けられ、回転環２２が摺動する摺動部２５となっている。 The mechanical seal 21 includes a rotary ring 22 attached to an end portion of the sleeve 6 attached to the rotary shaft 5 and protruding into the casing 1, a fixed ring 23 on the casing side attached to the main body 2, and the fixed ring 23. The coil spring 9 is a spring that presses against the rotating ring 22, and the rotating ring 22 is formed with a diameter that gradually increases toward the fixed ring 23, and the fixed ring 23 increases in diameter toward the rotating ring 22 on one side. The end of the taper portion having the maximum diameter is larger than the fixed ring 23 and is pressed against the rotating ring 22 to form a sliding portion 25 on which the rotating ring 22 slides.
ここでテーパ部２４の内面にはシール液によるシール圧ｐが作用し、外面にはスラリーの機内圧Ｐが作用するようになっており、固定環２３を回転環２２に押付ける方向にシール液のシール圧が作用する固定環側端面の受圧面積Ａ１は、図６に示すように固定環側端面の内外の径をそれぞれＤ３及びＤ２とすると、Ａ１＝π／４（Ｄ３ ２−Ｄ２ ２）で表され、固定環２３を回転環２２より引き離す方向にシール液のシール圧ｐが作用するテーパ部内面の受圧面積Ａ２は摺動部２５までの径をＤ１とすると、Ａ２＝π／４（Ｄ１ ２−Ｄ２ ２）で表される。また機内圧Ｐが作用するテーパ部外面の受圧面積Ａ３は、テーパ部端の外径をＤ４とすると、Ａ３＝π／４（Ｄ４ ２−Ｄ３ ２）で表される。またコイルバネ９のバネ力をＮとすると、固定環２３を回転環２２に押し付ける軸方向の力はｐ・Ａ１＋Ｐ・Ａ３＋Ｎとなり、この力よりも固定環２３を回転環２２より引き離す軸方向の力ｐ・Ａ２が大となり、Ｐ・Ａ３＋ｐ・Ａ１＋Ｎ＜ｐ・Ａ２となると、固定環２３が回転環２２より引離され、固定環２３と回転環２２の隙間が拡大する。 Here, the sealing pressure p by the sealing liquid acts on the inner surface of the taper portion 24, and the in-machine pressure P of the slurry acts on the outer surface, and the sealing liquid is pressed in the direction of pressing the stationary ring 23 against the rotating ring 22. The pressure receiving area A 1 of the fixed ring side end face on which the seal pressure acts is given by A 1 = π / 4 (D 3) where the inner and outer diameters of the fixed ring side end face are D 3 and D 2 as shown in FIG. 2− D 2 2 ), the pressure receiving area A 2 of the inner surface of the tapered portion where the sealing pressure p of the sealing liquid acts in the direction in which the stationary ring 23 is separated from the rotating ring 22 is the diameter to the sliding portion 25 as D 1 . Then, it is represented by A 2 = π / 4 (D 1 2 -D 2 2 ). Further, the pressure receiving area A 3 of the outer surface of the taper portion on which the in-machine pressure P acts is represented by A 3 = π / 4 (D 4 2 −D 3 2 ), where D 4 is the outer diameter of the end of the taper portion. When the spring force of the coil spring 9 is N, the axial force pressing the fixed ring 23 against the rotating ring 22 is p · A 1 + P · A 3 + N. The shaft that pulls the fixed ring 23 away from the rotating ring 22 than this force. When the directional force p · A 2 becomes large and P · A 3 + p · A 1 + N <p · A 2 , the stationary ring 23 is pulled away from the rotating ring 22, and the clearance between the stationary ring 23 and the rotating ring 22 is increased. Expanding.
上記隙間が拡大すると、バネ力Ｎが増加すると共に、シール圧ｐが増加し、シール圧がｐ＋Δｐに増加し、かつバネ圧がＮ＋ΔＮに増加して均衡したとき、すなわち下記（３）式を満たすとき上記隙間が一定に維持され、ｐ＋Δｐのシール圧でシール液が機内に流入する。
Ｐ・Ａ３＋（ｐ＋Δｐ）・Ａ１＋（Ｎ＋ΔＮ）＝（ｐ＋Δｐ）・Ａ２ （３）
When the gap is enlarged, the spring force N is increased, the seal pressure p is increased, the seal pressure is increased to p + Δp, and the spring pressure is increased to N + ΔN to be balanced, that is, the following expression (3) is satisfied. When the gap is kept constant, the sealing liquid flows into the machine with a sealing pressure of p + Δp.
P · A 3 + (p + Δp) · A 1 + (N + ΔN) = (p + Δp) · A 2 (3)
図５は図２と同様のシール液の循環経路を示すもので、図２と異なる点は、シール液を循環させる循環用ポンプ２７のほかに設定のシール圧ｐのシール液を摺動部２５に注入する注入手段としてのポンプ２９を設け、かつ注出口１９からタンク１６に至る流路上のリリーフ弁を省いたことである。図２に示す従来の循環用ポンプ１７は、リリーフ弁の存在によりシール圧ｐ´を発生させるが、前述の循環用ポンプ２７は、これと異なり、循環時に発生する圧力損失に相当する圧力のみを発生させ、シール液を循環させる機能のみを有するものである。これに対しポンプ２９は、循環用ポンプ２７が発生する圧力よりも大きな圧力のシール圧ｐを発生させるものである。 FIG. 5 shows a circulation path of the sealing liquid similar to that in FIG. 2. The difference from FIG. 2 is that the sealing liquid having a set sealing pressure p is applied to the sliding portion 25 in addition to the circulating pump 27 for circulating the sealing liquid. And a relief valve on the flow path from the spout 19 to the tank 16 is omitted. The conventional circulation pump 17 shown in FIG. 2 generates the seal pressure p ′ due to the presence of the relief valve. However, the circulation pump 27 described above differs from this in that only the pressure corresponding to the pressure loss generated during the circulation is generated. It has only the function to generate and circulate the sealing liquid. On the other hand, the pump 29 generates a seal pressure p having a pressure larger than the pressure generated by the circulation pump 27.
ポンプ２９の駆動によりシール圧ｐが発生し、この圧力でシール液がメカニカルシール２１間に注入されると、固定環２３と回転環２２との摺動部２５の隙間が拡大するが、その拡大は前記（３）式を満たした段階で停止して一定に維持され、これにより、機内圧Ｐより高圧のｐ＋Δｐのシール液が摺動部２５を通って機内に流れ、摺動部２５にスラリー中の固形物が入り込むのを防止する。図１に示す従来の機構では、シール圧をｐ´よりｐにし、更にｐより上げても、固定環８の回転環７への押付力が強くなるだけで摺動部１４にシール液を通すことはできないが、本機構により前記（３）式が満たされる条件のもとでポンプ２９作動中は常時、摺動部２５に設定量のシール液を通すことが可能になる。 When the sealing pressure p is generated by driving the pump 29 and the sealing liquid is injected between the mechanical seals 21 at this pressure, the gap between the sliding portion 25 between the fixed ring 23 and the rotating ring 22 is expanded. Is stopped and maintained constant when the above equation (3) is satisfied. As a result, a seal liquid of p + Δp higher than the internal pressure P flows into the machine through the sliding part 25, and the slurry is transferred to the sliding part 25. Prevents solids from entering. In the conventional mechanism shown in FIG. 1, even if the sealing pressure is changed from p ′ to p and further increased from p, the pressing force of the stationary ring 8 against the rotating ring 7 is increased, and the sealing liquid is passed through the sliding portion 14. Although this is not possible, this mechanism allows a set amount of sealing liquid to be passed through the sliding portion 25 at all times while the pump 29 is operating under the condition that the expression (3) is satisfied.
前述の実施形態において、ポンプ２９の駆動が停止され、シール圧が低下すると、固定環２３が回転環２２に押付けられてシール液が摺動部２５に流れるのが停止される。
本実施形態のポンプ２９としては、遠心ポンプを用いることもできるが、好ましくは定量ポンプが用いられる。その理由は、遠心ポンプを用いた場合、シール液を摺動部２５に供給すると、機内圧Ｐが変動したとき、摺動部２５を流れるシール液の流量が変化し、機内圧Ｐが低下すると、必要量以上のシール液が摺動部２５を流れるようになるが、定量ポンプを使用すると、機内圧Ｐが変動しても、シール液の流量は変わらず、摺動部２５に定量ずつ流れるようになる。この場合にはしたがって、定量ポンプは摺動部２５を流れる流量に相当するシール液を供給するものとなる。なお、定量ポンプを用いる場合、該定量ポンプが脈流を生ずるものである場合には、脈流を避けるためにアキュムレータが設けられる。
In the above-described embodiment, when the driving of the pump 29 is stopped and the sealing pressure is reduced, the stationary ring 23 is pressed against the rotating ring 22 and the flow of the sealing liquid to the sliding portion 25 is stopped.
A centrifugal pump can be used as the pump 29 of this embodiment, but a metering pump is preferably used. The reason is that if a centrifugal pump is used and the sealing liquid is supplied to the sliding portion 25, the flow rate of the sealing liquid flowing through the sliding portion 25 changes and the internal pressure P decreases when the internal pressure P fluctuates. More than the necessary amount of sealing liquid flows through the sliding portion 25. However, if a metering pump is used, the flow rate of the sealing liquid does not change even if the internal pressure P fluctuates, and flows into the sliding portion 25 in a fixed amount. It becomes like this. In this case, therefore, the metering pump supplies the sealing liquid corresponding to the flow rate flowing through the sliding portion 25. When a metering pump is used, if the metering pump generates a pulsating flow, an accumulator is provided to avoid the pulsating flow.
シール液をメカニカルシール２１間に注入する手段としては、前述のポンプ２９のほか、タンク１６から供給されるシール液に設定圧ｐを掛けるために、例えばタンク１６に注入される高圧ガス、好ましくは圧縮空気を用いることができ、また図２に示す従来技術のように、抽出口１９からタンク１６に至る流路上にリリーフ弁を設けて循環用ポンプ２７のみでシール液を設定圧にすることも可能である。この場合にはしたがって循環用ポンプとリリーフ弁が注入手段を構成するものとなる。 As a means for injecting the sealing liquid between the mechanical seals 21, in addition to the above-described pump 29, for example, a high-pressure gas injected into the tank 16 in order to apply a set pressure p to the sealing liquid supplied from the tank 16, preferably Compressed air can be used, and a relief valve can be provided on the flow path from the extraction port 19 to the tank 16 as in the prior art shown in FIG. Is possible. In this case, therefore, the circulation pump and the relief valve constitute the injection means.
本実施形態で用いられるシール液としては、スラリーと化学反応を生じないようなものであればよく、とくに限定されない。こうしたものとしては例えばスラリーの溶液と同じ溶液、好ましくは水が用いられる。 The sealing liquid used in the present embodiment is not particularly limited as long as it does not cause a chemical reaction with the slurry. For example, the same solution as the slurry solution, preferably water, is used.
図５に示される実施形態では、シール液を冷却するのにタンク１６がジャケット１６ａを備え、該ジャケット１６ａに冷却水を通すことによってシール液を冷却するようになっているが、ジャケット１６ａを設けるのに代えて熱交換機を設け、これにより注出口１９を出たシール液を冷却するようにしてもよい。
また前述のテーパ部２４は軸と直交するクランクアーム形状をなしていてもよい。
In the embodiment shown in FIG. 5, the tank 16 is provided with a jacket 16a for cooling the sealing liquid, and the sealing liquid is cooled by passing cooling water through the jacket 16a. However, the jacket 16a is provided. Instead of this, a heat exchanger may be provided so that the sealing liquid exiting the spout 19 may be cooled.
Further, the aforementioned taper portion 24 may have a crank arm shape orthogonal to the axis.
１・・ケーシング
２・・本体
３、４、２１・・メカニカルシール
５・・回転軸
７、２２・・回転環
８、２３・・固定環
９・・コイルバネ
１４、２５・・摺動部
１６・・タンク
１７、２７・・循環用ポンプ
１８・・注入口
１９・・注出口
２４・・テーパ部
２９・・ポンプ
1 .. Casing 2 .. Body 3, 4, 21 .. Mechanical seal 5 .. Rotating shaft 7, 22 .. Rotating ring 8, 23 .. Fixed ring 9 .. Coil springs 14, 25. · Tanks 17 and 27 · · Circulation pump 18 · · Inlet 19 · · Outlet 24 · · Tapered portion 29 · · Pump
Claims (4)
Ａ１＜Ａ２ （１）
Ｐ ＜ｐ （２）
Ｐ・Ａ３＋（ｐ＋Δｐ）・Ａ１＋（Ｎ＋ΔＮ）＝（ｐ＋Δｐ）・Ａ２ （３）
ここで、Ａ１は固定環を回転環に押付ける方向にシール圧が作用する固定環の受圧面積、Ａ２は固定環を回転環より引き離す方向にシール圧が作用する固定環の受圧面積、Ａ３は固定環を回転環に押付ける方向に機内圧Ｐが作用する固定環の受圧面積、Ｎ＋ΔＮは、前記液圧ｐのシール液の注入により前記隙間が開き、これにより増加したシール圧ｐ＋Δｐと均衡したときのバネのバネ力である。 An apparatus for carrying out the method according to claim 1, comprising a double mechanical seal, and a shaft sealing device for a slurry pulverizer in which a sealing liquid is injected between the mechanical seals, wherein the mechanical seal is a rotary ring on the rotary shaft side. And an injection means for injecting the sealing liquid into the sliding portion of the rotating ring and the stationary ring with a hydraulic pressure p, and comprising a stationary ring on the casing side and a spring pressing the stationary ring against the rotating ring, and the following (1 ) To (3) are satisfied.
A 1 <A 2 (1)
P <p (2)
P · A 3 + (p + Δp) · A 1 + (N + ΔN) = (p + Δp) · A 2 (3)
Here, A 1 is the pressure receiving area of the fixed ring receiving area of the stationary ring that acts sealing pressure in the direction to press the stationary ring to the rotating ring, A 2 is the sealing pressure in the direction of separating the fixed ring from the rotary ring acts, a 3 is the pressure receiving area of the stationary ring acts machine pressure P in a direction to press the stationary ring to the rotating ring, N + .DELTA.N, the liquid opens the gap by the injection of the sealing liquid pressure p, sealing pressure p + Delta] p was increased by this This is the spring force of the spring when balanced.
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|---|---|---|---|
| JP2009006544A JP2010164118A (en) | 2009-01-15 | 2009-01-15 | Method and apparatus for sealing shaft sealing device for slurry |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009006544A JP2010164118A (en) | 2009-01-15 | 2009-01-15 | Method and apparatus for sealing shaft sealing device for slurry |
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| JP2010164118A true JP2010164118A (en) | 2010-07-29 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103032492A (en) * | 2011-09-28 | 2013-04-10 | 株式会社电装 | Hydraulic braking device and valve timing adjusting apparatus |
| CN104696517A (en) * | 2013-12-04 | 2015-06-10 | 丹东波纹管密封有限公司 | Integrated double mechanical seal |
| CN104964038A (en) * | 2015-07-06 | 2015-10-07 | 苏州捷宁模塑有限公司 | Fluoroplastic device used for mechanical seal |
| US9200545B2 (en) | 2013-08-27 | 2015-12-01 | Denso Corporation | Torque control device and valve timing control apparatus |
| KR20190098330A (en) * | 2018-02-14 | 2019-08-22 | 주식회사 셀텍 | a mechanical seal for the stirrer of a fermentation equipment |
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| JPH01168064U (en) * | 1988-05-18 | 1989-11-27 | ||
| JP2006046477A (en) * | 2004-08-04 | 2006-02-16 | Tanken Seal Seiko Co Ltd | Double mechanical seal for sealed object containing nano particle |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01168064U (en) * | 1988-05-18 | 1989-11-27 | ||
| JP2006046477A (en) * | 2004-08-04 | 2006-02-16 | Tanken Seal Seiko Co Ltd | Double mechanical seal for sealed object containing nano particle |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103032492A (en) * | 2011-09-28 | 2013-04-10 | 株式会社电装 | Hydraulic braking device and valve timing adjusting apparatus |
| US8733307B2 (en) | 2011-09-28 | 2014-05-27 | Denso Corporation | Hydraulic braking device and valve timing adjusting apparatus |
| US9200545B2 (en) | 2013-08-27 | 2015-12-01 | Denso Corporation | Torque control device and valve timing control apparatus |
| CN104696517A (en) * | 2013-12-04 | 2015-06-10 | 丹东波纹管密封有限公司 | Integrated double mechanical seal |
| CN104964038A (en) * | 2015-07-06 | 2015-10-07 | 苏州捷宁模塑有限公司 | Fluoroplastic device used for mechanical seal |
| KR20190098330A (en) * | 2018-02-14 | 2019-08-22 | 주식회사 셀텍 | a mechanical seal for the stirrer of a fermentation equipment |
| KR102074682B1 (en) | 2018-02-14 | 2020-02-07 | 주식회사 셀텍 | a mechanical seal for the stirrer of a fermentation equipment |
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