JP2002156092A - Submerged bearing lubrication system - Google Patents
Submerged bearing lubrication systemInfo
- Publication number
- JP2002156092A JP2002156092A JP2000351363A JP2000351363A JP2002156092A JP 2002156092 A JP2002156092 A JP 2002156092A JP 2000351363 A JP2000351363 A JP 2000351363A JP 2000351363 A JP2000351363 A JP 2000351363A JP 2002156092 A JP2002156092 A JP 2002156092A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- lubricating liquid
- underwater
- underwater bearing
- lubrication system
- 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.)
- Pending
Links
Landscapes
- Details Of Reciprocating Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sliding-Contact Bearings (AREA)
- Rolling Contact Bearings (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、水中軸受を常に潤
滑液で濡れた状態とする水中軸受潤滑システムに関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an underwater bearing lubrication system in which an underwater bearing is always wet with a lubricating liquid.
【０００２】[0002]
【従来の技術】先行待機運転ポンプは、大雨などによる
急激な出水に備えて、吸込水槽の水位が未だ揚水運転が
できるレベルの水位に到る前の低水位の状況から運転が
行われる。そこで、吸込水槽の水位が揚水レベルに達す
るまでは、ポンプは揚水がなされずに気中運転がなされ
る。その間、主ポンプの回転軸を支承する水中軸受には
揚水が供給されることがなく、濡れた状態とならずに水
中軸受は乾いた状態で運転がなされる。かかる運転で
は、水中軸受に大きな摩擦熱が生じ、破損する虞があ
る。2. Description of the Related Art A preparatory standby operation pump is operated in a low water level state before the water level of a suction water tank reaches a water level at which a pumping operation can still be performed in preparation for a sudden water discharge due to heavy rain or the like. Therefore, until the water level in the suction tank reaches the pumping level, the pump is operated in the air without pumping. During that time, no pumping water is supplied to the underwater bearing that supports the rotating shaft of the main pump, and the underwater bearing is operated in a dry state without becoming wet. In such an operation, large frictional heat is generated in the underwater bearing, and there is a possibility that the bearing is damaged.
【０００３】この水中軸受が乾いた状態で運転される不
具合を改善すべく、従来にあっては、図９に示すごと
く、たとえば立軸ポンプ１０の回転軸１２および水中軸
受１４，１６全体を同軸状の保護管１８で覆い、この保
護管１８の下端部をメカニカルシール２０で水密状態と
し、保護管１８内に潤滑液ポンプ２２で潤滑液漕２４か
ら潤滑液を注入する構造が普及している。In order to improve the problem that the underwater bearing is operated in a dry state, conventionally, as shown in FIG. 9, for example, the rotating shaft 12 of the vertical shaft pump 10 and the entire underwater bearings 14 and 16 are coaxial. A structure in which the lower end of the protective tube 18 is made water-tight with a mechanical seal 20 and a lubricating liquid is injected from a lubricating liquid tank 24 into the protective tube 18 by a lubricating liquid pump 22 is widely used.
【０００４】[0004]
【発明が解決しようとする課題】図９に示す従来構造に
あっては、保護管１８内を潤滑液が流下するものであ
り、保護管１８内の潤滑液の圧力は小さなものである。
なお、下端部に設けたメカニカルシール２０は、潤滑液
を循環利用するために、潤滑液が保護管１８内の下端部
から放出されるのを阻止するものである。ところで、保
護管１８の外部に揚水がない気中運転状態と、保護管１
８の外部に揚水がある揚水運転状態と、保護管１８の一
部が揚水に浸漬する気水撹拌運転状態とでは、保護管１
８の付加算量がそれぞれに大きく変化し、保護管１８の
固有振動数が大幅に変化する。この付加算量とは、例え
ば、保護管１８の外側に揚水があるときに保護管１８が
振動したとすると、振動した分だけ保護管１８の回りの
揚水を押しのけることとなり、その揚水の質量が振動体
としての保護管１８に付加されることをいう。そこで、
この付加算量が大きくなると保護管１８の固有振動数は
減少し、付加算量が小さくなると保護管１８の固有振動
数が増加する。したがって、保護管１８の固有振動数
は、揚水運転状態が最も小さく、気中運転状態で最も大
きくなる。先行待機運転ポンプは、起動時には気水運転
から気水撹拌運転を経て揚水運転に至り、保護管１８の
付加算量をも考慮した固有振動数は範囲が広く、その範
囲内に回転軸の回転数と一致する固有振動数が存在する
と、共振を生じる。このために、保護管１８が破損を生
じ易い、という不具合があった。また、揚水運転による
保護管１８の内外圧力差により、揚水がメカニカルシー
ル２０を介して保護管１８内に侵入する虞があり、この
揚水の侵入に伴い揚水に含まれる砂や泥がメカニカルシ
ール２０および水中軸受１４，１６の摺接部に侵入し、
摺接面を損傷させる危険もあった。In the conventional structure shown in FIG. 9, the lubricating liquid flows down in the protective tube 18, and the pressure of the lubricating liquid in the protective tube 18 is small.
The mechanical seal 20 provided at the lower end prevents the lubricating liquid from being released from the lower end inside the protective tube 18 in order to circulate and use the lubricating liquid. By the way, in the aerial operation state where no water is pumped outside the protection tube 18, the protection tube 1
In the pumping operation state in which water is pumped outside the pump 8 and in the air / water stirring operation state in which a part of the protective tube 18 is immersed in the pumping, the protective tube 1
The addition amount of 8 greatly changes, and the natural frequency of the protection tube 18 greatly changes. For example, assuming that the protection tube 18 vibrates when water is pumped outside the protection tube 18, pumping around the protection tube 18 is displaced by an amount corresponding to the vibration, and the mass of the pumped water is reduced. It means that it is added to the protection tube 18 as a vibrator. Therefore,
The natural frequency of the protection tube 18 decreases as the addition amount increases, and the natural frequency of the protection tube 18 increases as the addition amount decreases. Therefore, the natural frequency of the protection tube 18 is the smallest in the pumping operation state and is largest in the air operation state. The preparatory standby operation pump starts pumping operation from air-water operation to air-pumping operation through air-water stirring operation at startup, and the natural frequency in consideration of the additional amount of the protection tube 18 has a wide range, and the rotation of the rotating shaft is within the range. If a natural frequency equal to the number exists, resonance occurs. For this reason, there was a problem that the protection tube 18 was easily damaged. Further, there is a possibility that pumping water may enter the protection tube 18 via the mechanical seal 20 due to a pressure difference between the inside and outside of the protection tube 18 due to the pumping operation. And penetrate into the sliding contact portions of the underwater bearings 14 and 16,
There was also a risk of damaging the sliding surface.
【０００５】本発明は、上記のごとき従来技術の不具合
を改善すべくなされたもので、水中軸受を濡らす潤滑液
の圧力を、軸受ケースの外側の圧力に応じて僅かに高く
調整するようにした水中軸受潤滑システムを提供するこ
とを目的とする。また、破損する虞のある保護管を必要
としない立軸ポンプの水中軸受潤滑システムを提供する
ことを目的とする。The present invention has been made to solve the above-mentioned problems of the prior art, and the pressure of the lubricating liquid for wetting the underwater bearing is adjusted slightly higher according to the pressure outside the bearing case. It is an object to provide an underwater bearing lubrication system. It is another object of the present invention to provide an underwater bearing lubrication system for a vertical shaft pump that does not require a protective tube that may be damaged.
【０００６】[0006]
【課題を解決するための手段】かかる目的を達成するた
めに、本発明の水中軸受潤滑システムは、軸受ケースの
内部に水中軸受を設けるとともに、前記軸受ケースの軸
方向両端側に軸封部材を設けて潤滑液室とし、この潤滑
液室内の潤滑液で前記水中軸受が濡れるようになし、前
記潤滑液室に流入管の一端を連通開口してこの流入管を
介して前記潤滑液室に前記潤滑液が流入し得るようにな
し、しかも前記潤滑液室内の前記潤滑液の圧力が前記軸
受ケースの外側の圧力より僅かに高くなるように調整す
る調整機構を設けて構成されている。In order to achieve the above object, the underwater bearing lubrication system of the present invention has an underwater bearing inside a bearing case and a shaft sealing member at both axial ends of the bearing case. The lubricating liquid chamber is provided to make the underwater bearing wet with the lubricating liquid in the lubricating liquid chamber. One end of an inflow pipe is opened to the lubricating liquid chamber, and the lubricating liquid chamber is connected to the lubricating liquid chamber through the inflow pipe. An adjusting mechanism is provided for adjusting the pressure of the lubricating fluid in the lubricating fluid chamber to be slightly higher than the pressure outside the bearing case.
【０００７】また、軸受ケースの内部に水中軸受を設け
るとともに、前記軸受ケースの軸方向両端側に軸封部材
を設けて潤滑液室とし、この潤滑液室内の潤滑液で前記
水中軸受が濡れるようになし、前記潤滑液室に流入管お
よび流出管の一端をそれぞれ連通開口して、潤滑液ポン
プより吐出した前記潤滑液を前記流入管を介して前記潤
滑液室に流入させ前記流出管を介して流出させるように
なし、しかも前記潤滑液室内の前記潤滑液の圧力が前記
軸受ケースの外側の圧力より僅かに高くなるように調整
する調整機構を設けて構成しても良い。In addition, a submerged bearing is provided inside the bearing case, and shaft sealing members are provided at both ends in the axial direction of the bearing case to form a lubricating liquid chamber. The lubricating liquid in the lubricating liquid chamber may wet the submerged bearing. One end of an inflow pipe and one end of an outflow pipe are respectively opened to the lubricating liquid chamber, and the lubricating liquid discharged from a lubricating liquid pump flows into the lubricating liquid chamber through the inflow pipe and flows through the outflow pipe. And an adjusting mechanism for adjusting the pressure of the lubricant in the lubricant chamber to be slightly higher than the pressure outside the bearing case.
【０００８】さらに、主ポンプの回転軸および水中軸受
を覆って保護管を設け、この保護管の軸方向両端側を水
密構造となし、前記保護管内に流入管と流出管を介して
潤滑液を流入させる水中軸受潤滑システムにおいて、前
記流出管に潤滑液圧力センサーと流量調整弁を設け、前
記主ポンプの流路に、その流路内の流体圧力を検出する
圧力センサーを設け、前記潤滑液圧力センサーの検出値
が前記圧力センサーの検出値よりも、所定値だけ高い値
となるように前記流量調整弁を調整する調整機構を設け
て構成することもできる。Further, a protection tube is provided so as to cover the rotating shaft and the underwater bearing of the main pump, and both ends in the axial direction of the protection tube are formed in a watertight structure, and the lubricating liquid is supplied into the protection tube via an inflow pipe and an outflow pipe. In the underwater bearing lubrication system to be supplied, a lubricating fluid pressure sensor and a flow rate regulating valve are provided in the outflow pipe, and a pressure sensor for detecting a fluid pressure in the main pump is provided in a flow path of the main pump. It is also possible to provide an adjusting mechanism for adjusting the flow regulating valve so that the detected value of the sensor becomes higher than the detected value of the pressure sensor by a predetermined value.
【０００９】[0009]
【発明の実施の形態】以下、本発明の第１実施例を、図
１ないし図３を参照して説明する。図１は、本発明の水
中軸受潤滑システムの第１実施例の構造図である。図２
は、本発明で用いる水中軸受の一例の縦断面図である。
図３は、図２のＡ−Ａ矢視断面図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described below with reference to FIGS. FIG. 1 is a structural diagram of a first embodiment of the underwater bearing lubrication system of the present invention. FIG.
1 is a longitudinal sectional view of an example of an underwater bearing used in the present invention.
FIG. 3 is a sectional view taken along the line AA of FIG.
【００１０】図１において、主ポンプの一例としての立
軸ポンプ３０は、その回転軸３２が水中軸受３４，３６
で回転自在に支承される。なお、従来例のごとき保護管
は設けられていない。そして、これらの水中軸受３４，
３６の構造は、図２，３に示すごとく、回転軸３２にス
リーブ３８が嵌合固着され、このスリーブ３８に軸方向
に長尺な摺動部材片４０，４０…が摺接し、これらの摺
動部材片４０，４０…が略円筒状の合成ゴム部材４２を
介して金属シェル４４の内周に固着される。なお、摺動
部材片４０，４０…は、周方向に離して配設され、その
間には軸方向に長い隙間が設けられて通水路４８，４８
が形成される。さらに、この金属シエル４４が上部軸受
ケース５０と下部軸受ケース５２に挿入され、これらの
上部軸受ケース５０と下部軸受ケース５２が揚水管に固
定される筒状の支持部材５４に挿入固定される。そし
て、上部軸受ケース５０の上端部および下部軸受ケース
５２の下端には、スリーブ３８との間にそれぞれ軸封部
材５４，５６が配設されて水密構造とされる。そしてま
た、上部軸受ケース５０と下部軸受ケース５２内には、
摺動部材片４０，４０…の軸方向両端側の隙間で通水路
４８，４８…が連通された潤滑液室５８が形成される。
なお、上部軸受ケース５０と下部軸受ケース５２の間
に、適宜なＯリングなどが介装されて水密構造とされる
ことは勿論である。さらに、この潤滑液室５８の両端部
に流入管６０の一端と流出管６２の一端がそれぞれ連通
開口され、これらの流入管６０と流出管６２は揚水管の
外側に導出される。ここで、摺動部材４０，４０…と合
成ゴム部材４２および金属シエル４４で、水中軸受が構
成される。また、上部軸受ケース５０と下部軸受ケース
５２で軸受ケースが構成される。In FIG. 1, a vertical shaft pump 30 as an example of a main pump has a rotating shaft 32 whose underwater bearings 34 and 36 are provided.
It is rotatably supported by. It should be noted that no protective tube is provided as in the conventional example. And these underwater bearings 34,
As shown in FIGS. 2 and 3, a sleeve 38 is fitted and fixed to the rotating shaft 32, and long sliding member pieces 40, 40,... Are fixed to the inner periphery of the metal shell 44 via a synthetic rubber member 42 having a substantially cylindrical shape. The sliding member pieces 40, 40,... Are arranged apart from each other in the circumferential direction, and a long gap is provided in the axial direction between the sliding member pieces 40, 40.
Is formed. Further, the metal shell 44 is inserted into the upper bearing case 50 and the lower bearing case 52, and the upper bearing case 50 and the lower bearing case 52 are inserted and fixed to a cylindrical support member 54 fixed to the pumping pipe. Shaft sealing members 54 and 56 are disposed between the upper end of the upper bearing case 50 and the lower end of the lower bearing case 52 and the sleeve 38 to form a watertight structure. Further, in the upper bearing case 50 and the lower bearing case 52,
A lubricating liquid chamber 58 is formed in which the water passages 48 are communicated with each other at the gaps at both axial ends of the sliding member pieces 40.
It is needless to say that an appropriate O-ring or the like is interposed between the upper bearing case 50 and the lower bearing case 52 to form a watertight structure. Further, one end of the inflow pipe 60 and one end of the outflow pipe 62 are respectively opened at both ends of the lubricating liquid chamber 58, and the inflow pipe 60 and the outflow pipe 62 are led out of the pumping pipe. Here, the sliding members 40, 40, the synthetic rubber member 42 and the metal shell 44 constitute an underwater bearing. The upper bearing case 50 and the lower bearing case 52 constitute a bearing case.
【００１１】なお、軸封部材５４，５６は、従来のグラ
ンドパッキンに相当するシール部材が回転軸３２に対し
て斜めに取り付けられており、回転軸３２は回転により
シール部材に摺接する状態と揚水または潤滑液に晒され
る状態とが繰り返され、それだけ潤滑性が向上し、摺動
抵抗は小さなものとなる。ここで、軸封部材５４，５６
の揚水側を回転軸３２と直交する面にあるようにし、潤
滑液室５８側のみが回転軸３２に対して斜めとなるよう
にして、潤滑液によってのみ潤滑性を向上させるように
しても良い。In the shaft sealing members 54 and 56, a sealing member corresponding to a conventional gland packing is mounted obliquely with respect to the rotary shaft 32. Or, the state of being exposed to the lubricating liquid is repeated, so that the lubricating property is improved and the sliding resistance is reduced. Here, the shaft sealing members 54 and 56
The pumping side may be on a surface orthogonal to the rotating shaft 32, and only the lubricating liquid chamber 58 side may be inclined with respect to the rotating shaft 32, so that lubricity may be improved only by the lubricating liquid. .
【００１２】さらに、配管構造について説明する。潤滑
液漕２４より、潤滑液ポンプ６４ａと流量計６６ａを介
して流入管６０ａが一方の水中軸受３６の潤滑液室５８
に連通開口される。そして、この水中軸受３６より、流
出管６２ａが潤滑液圧力センサー６８ａと流量計７０ａ
および流量調節弁７２ａを介して潤滑液漕２４に潤滑液
が戻るように配管される。また、潤滑液漕２４より、潤
滑液ポンプ６４ｂと流量計６６ｂを介して流入管６０ｂ
が他方の水中軸受３４の潤滑液室５８に連通開口され
る。そして、この他方の水中軸受３４より、流出管６２
ｂが潤滑液圧力センサー６８ｂと流量計７０ｂおよび流
量調節弁７２ａを介して潤滑液漕２４に潤滑液が戻るよ
うに配管される。なお、流量調整弁７２ａ，７２ｂは、
それぞれ調整モータ７４ａ，７４ｂでその弁の開度が調
整される。さらに、吐出しエルボに、吐出す流体の流体
圧力を検出する圧力センサー７６が設けられる。そし
て、流量計６６ａ，６６ｂ、７０ａ，７０ｂと潤滑液圧
力センサー６８ａ，６８ｂおよび圧力センサー７６の検
出信号が制御部７８に与えられ、この制御部７８の出力
信号で調整モータ７４ａ，７４ｂが制御されて、流量調
整弁７２ａ，７２ｂの弁の開度が調整される。Next, the piping structure will be described. From the lubricating liquid tank 24, the inflow pipe 60a is connected to the lubricating liquid chamber 58 of one of the underwater bearings 36 via the lubricating liquid pump 64a and the flow meter 66a.
Is opened. The outflow pipe 62a is connected to the lubricating fluid pressure sensor 68a and the flow meter 70a by the underwater bearing 36.
In addition, piping is provided so that the lubricating liquid returns to the lubricating liquid tank 24 via the flow control valve 72a. The lubricating liquid tank 24 also receives an inflow pipe 60b through a lubricating liquid pump 64b and a flow meter 66b.
Is opened to communicate with the lubricating liquid chamber 58 of the other underwater bearing 34. The outflow pipe 62 is provided by the other underwater bearing 34.
b is connected to the lubricating tank 24 via the lubricating liquid pressure sensor 68b, the flow meter 70b, and the flow control valve 72a so that the lubricating liquid returns to the tank 24. In addition, the flow control valves 72a and 72b
The opening of the valve is adjusted by the adjusting motors 74a and 74b, respectively. Further, the discharge elbow is provided with a pressure sensor 76 for detecting the fluid pressure of the fluid to be discharged. The detection signals from the flow meters 66a, 66b, 70a, 70b, the lubricating fluid pressure sensors 68a, 68b, and the pressure sensor 76 are supplied to the control unit 78, and the adjustment motors 74a, 74b are controlled by the output signals from the control unit 78. Thus, the opening of the flow control valves 72a and 72b is adjusted.
【００１３】かかる構成において、制御部７８は、以下
のごとき動作を行う。まず、吐出しエルボに設けた圧力
センサー７６の検出値が大気圧であれば、立軸ポンプ３
０は気中運転状態であり、水中軸受３４，３６はいずれ
も揚水に没することなく、その外側は大気圧である。そ
こで、制御部７８は、潤滑液圧力センサー６８ａ，６８
ｂが大気圧より僅かに高い圧力を検出するまで調整モー
タ７４ａ，７４ｂに流量調整弁７２ａ，７２ｂの弁を大
きく開くように信号を与える。また、立軸ポンプ３０が
揚水運転になると、吐出しエルボに設けた圧力センサー
７６は吐出す流体の大きな流体圧力が検出値となる。そ
して、水中軸受３４，３６は、揚水に没した状態とな
る。一方の水中軸受３４が揚水から受ける圧力は、吐出
しエルボに設けた圧力センサー７６よりＬ１だけ低い位
置にあるので、吐出し流体の流体圧力よりＬ１に応じた
水体積の重さによる圧力だけ大きなものとなる。同様
に、他方の水中軸受３６が揚水から受ける圧力は、吐出
し流体の流体圧よりＬ２に応じた水体積の重さによる圧
力だけ大きなものとなる。そこで、制御部７８は、吐出
しエルボに設けた圧力センサー７６の検出値とＬ１，Ｌ
２から、水中軸受３４，３６の外側の圧力をそれぞれに
演算し、さらにこれらの演算値より僅かに高い圧力をそ
れぞれに設定する。そして、水中軸受３４に対して、そ
の外側の演算された圧力より僅かに高い圧力が潤滑液圧
力センサー６８ｂで検出されるように調整モータ７４ｂ
を制御して流量調整弁７２ｂの開度を調整する。また、
水中軸受３６に対しても、その外側の演算された圧力よ
り僅かに高い圧力が潤滑液圧力センサー６８ａで検出さ
れるように調整モータ７４ａを制御して流量調整弁７２
ａの開度を調整する。なお、流量調整弁７２ａ，７２ｂ
の弁の開度を大きくすれば、水中軸受３４，３６内の潤
滑液室５８の圧力は下降し、弁の開度を小さくすれば、
圧力が上昇することは勿論である。このようにして、上
記配管構造および制御部７８は、水中軸受３４，３６内
の潤滑液の圧力が、軸受ケースの外側の圧力よりも僅か
に高くなるように調整する調整機構として作用する。In such a configuration, the control unit 78 performs the following operation. First, if the detected value of the pressure sensor 76 provided in the discharge elbow is the atmospheric pressure, the vertical pump 3
Numeral 0 indicates an aerial operation state, and neither of the underwater bearings 34, 36 is submerged in pumping water, and the outside thereof is at atmospheric pressure. Therefore, the control unit 78 controls the lubricating fluid pressure sensors 68a, 68
Until b detects a pressure slightly higher than the atmospheric pressure, a signal is sent to the adjusting motors 74a and 74b so that the valves of the flow rate adjusting valves 72a and 72b are greatly opened. When the vertical pump 30 is in the pumping operation, the pressure sensor 76 provided on the discharge elbow detects a large fluid pressure of the discharged fluid as a detection value. Then, the underwater bearings 34 and 36 are immersed in the pumping water. Since the pressure received by the underwater bearing 34 from the pumping is lower than the pressure sensor 76 provided in the discharge elbow by L1, the pressure is larger than the fluid pressure of the discharge fluid by the pressure due to the weight of the water volume according to L1. It will be. Similarly, the pressure that the other underwater bearing 36 receives from pumping is higher than the fluid pressure of the discharge fluid by the pressure due to the weight of the water volume according to L2. Therefore, the control unit 78 determines the detection value of the pressure sensor 76 provided on the discharge elbow and L1, L
From 2, the pressures outside the underwater bearings 34 and 36 are calculated respectively, and further, pressures slightly higher than these calculated values are set. The adjusting motor 74b is applied to the underwater bearing 34 so that a pressure slightly higher than the calculated pressure outside the underwater bearing 34 is detected by the lubricating fluid pressure sensor 68b.
Is controlled to adjust the opening of the flow control valve 72b. Also,
With respect to the underwater bearing 36 as well, the adjusting motor 74a is controlled so that the pressure slightly higher than the calculated pressure outside the underwater bearing 36 is detected by the lubricating fluid pressure sensor 68a.
Adjust the opening of a. The flow control valves 72a, 72b
If the opening of the valve is increased, the pressure of the lubricating liquid chamber 58 in the underwater bearings 34, 36 decreases, and if the opening of the valve is reduced,
Needless to say, the pressure increases. In this way, the piping structure and the control section 78 function as an adjusting mechanism for adjusting the pressure of the lubricating liquid in the underwater bearings 34 and 36 to be slightly higher than the pressure outside the bearing case.
【００１４】さらに、流入管６０ａ，６０ｂに設けた流
量計６６ａ，６６ｂと、流出管６２ａ，６２ｂに設けた
流量計７０ａ，７０ｂのそれぞれ計測値の差から、潤滑
液室５８を水密構造とする軸封部材５４，５６からの潤
滑液の漏れ量が測定できる。そして、この計測値の差か
ら、軸封部材５４，５６の損傷程度を推定することがで
きる。そこで、この漏れ量が所定値より大きくなれば、
軸封部材５４，５６を交換するなどの保守を確実に行う
ことができる。Further, the lubricating fluid chamber 58 has a watertight structure based on the difference between the measured values of the flow meters 66a and 66b provided in the inflow pipes 60a and 60b and the flow meters 70a and 70b provided in the outflow pipes 62a and 62b. The leakage amount of the lubricating liquid from the shaft sealing members 54 and 56 can be measured. The degree of damage to the shaft sealing members 54 and 56 can be estimated from the difference between the measured values. Therefore, if this leakage amount becomes larger than a predetermined value,
Maintenance such as replacement of the shaft sealing members 54 and 56 can be reliably performed.
【００１５】次に、本発明の第２実施例を、図４および
図５を参照して説明する。図４は、本発明の水中軸受潤
滑システムの第２実施例の構造図である。図５は、駆動
電動機の入力と吐出し量を示す特性図である。図４にお
いて、図１と同じまたは均等な部材には同じ符号を付け
て重複する説明を省略する。Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 4 is a structural diagram of a second embodiment of the underwater bearing lubrication system of the present invention. FIG. 5 is a characteristic diagram showing the input and the discharge amount of the drive motor. 4, the same or equivalent members as those in FIG. 1 are denoted by the same reference numerals, and redundant description will be omitted.
【００１６】図４において、回転軸３２は、減速装置８
０を介して駆動電動機８２に駆動連結されるが、この駆
動電動機８２の運転動力の大きさを運転動力検出手段８
４で検出する。駆動電動機８２の運転動力は、図５にそ
の一例を示すごとく、気中運転と気水撹拌運転および揚
水運転で、それぞれに大きな違いがある。そこで、この
運転動力の大きさの違いから、立軸ポンプ３０がいかな
る運転状況にあるか判別できる。In FIG. 4, the rotating shaft 32 is
0, the driving power is connected to the driving motor 82. The driving power of the driving motor 82 is
4 to detect. As shown in FIG. 5, the driving power of the driving motor 82 has a great difference between the in-air operation, the air-water stirring operation, and the pumping operation. Therefore, it is possible to determine the operating state of the vertical pump 30 from the difference in the operating power.
【００１７】そこで、図４に示す実施例では、気中運転
および揚水運転状態では、制御部７８は、図１に示す実
施例と同様に、吐出しエルボに設けた圧力センサー７６
で検出する圧力に基づいて調整モータ７４ａ，７４ｂを
制御して流量調整弁７２ａ，７２ｂの弁の開度を調整す
る。しかし、気水撹拌運転状態では、制御部７８は、以
下のごとき作用を行う。気水撹拌運転状態では、下側の
水中軸受３６は空気が混合された揚水中に没するが、上
側の水中軸受３４は大気中にあり、吐出しエルボからは
流体が吐き出されない。そこで、吐出しエルボに設けた
圧力センサー７６は大気圧しか検出できず、図１と同様
にして水中軸受３６の潤滑液の圧力を調整するならば、
揚水中に没する下側の水中軸受３６の潤滑液の圧力が軸
受ケースの外側の圧力よりも低く設定され、揚水が水中
軸受３６内に侵入する虞がある。このために、運転動力
検出手段８４から駆動電動機８２の入力に応じた信号が
与えられる制御部７８は、この入力に応じた信号から立
軸ポンプ３０の運転状態を判別し、気水撹拌運転である
と判別すると、下側の水中軸受３６に対しては、その潤
滑液の圧力を気水撹拌運転において予測される揚水の水
位に応じて１．２〜１．３気圧程度に適宜に設定し、ま
た上側の水中軸受３４は大気中であるからこれより僅か
に高い圧力に設定する。なお、図４の第２実施例では、
運転動力検出手段８４とその検出した信号から運転状況
を判別する制御部７８の一部分で、立軸ポンプ３０の運
転状態が気水撹拌運転であることを判定する判定手段が
構成される。Therefore, in the embodiment shown in FIG. 4, in the aerial operation and the pumping operation state, the control unit 78 controls the pressure sensor 76 provided on the discharge elbow as in the embodiment shown in FIG.
The adjusting motors 74a and 74b are controlled on the basis of the pressure detected in step (1) to adjust the opening of the flow control valves 72a and 72b. However, in the air-water stirring operation state, the control unit 78 performs the following operation. In the air / water stirring operation state, the lower underwater bearing 36 is immersed in the pumped water mixed with air, but the upper underwater bearing 34 is in the atmosphere, and the fluid is not discharged from the discharge elbow. Therefore, if the pressure sensor 76 provided on the discharge elbow can detect only the atmospheric pressure, and if the pressure of the lubricating liquid of the underwater bearing 36 is adjusted in the same manner as in FIG.
The pressure of the lubricating liquid of the lower underwater bearing 36 immersed in the pumping water is set lower than the pressure outside the bearing case, and there is a possibility that the pumping water enters the underwater bearing 36. For this reason, the control unit 78 to which a signal corresponding to the input of the drive motor 82 is given from the operating power detection means 84 determines the operating state of the vertical shaft pump 30 from the signal corresponding to this input, and the air-water stirring operation is performed. When it is determined that the underwater bearing 36 is lower, the pressure of the lubricating liquid is appropriately set to about 1.2 to 1.3 atm in accordance with the level of pumping water predicted in the air / water stirring operation, Also, since the upper underwater bearing 34 is in the atmosphere, it is set at a slightly higher pressure. In the second embodiment shown in FIG.
The driving power detecting means 84 and a part of the control unit 78 for determining the operating condition from the detected signal constitute a determining means for determining that the operating state of the vertical shaft pump 30 is the air / water stirring operation.
【００１８】さらに、本発明の第３実施例を、図６を参
照して説明する。図６は、本発明の水中軸受潤滑システ
ムの第３実施例の構成図である。図６において、図１お
よび図４と同じまたは均等な部材には同じ符号を付けて
重複する説明を省略する。Further, a third embodiment of the present invention will be described with reference to FIG. FIG. 6 is a configuration diagram of a third embodiment of the underwater bearing lubrication system of the present invention. 6, the same or equivalent members as those in FIGS. 1 and 4 are denoted by the same reference numerals, and redundant description will be omitted.
【００１９】図６において、回転軸３２にベベルギアを
設け、このベベルギアに、潤滑液ポンプ８８ａ，８８ｂ
の駆動軸に固定されたベベルギアが噛合される。この噛
合する２つのベベルギアからなる駆動連結部８６は、回
転軸３２に潤滑液ポンプ８８ａ，８８ｂが駆動連結され
ればいかなる連結機構が用いられても良い。この第３実
施例では、潤滑液ポンプ８８ａ，８８ｂの駆動用の電源
を必要としない。In FIG. 6, a bevel gear is provided on the rotating shaft 32, and lubricating liquid pumps 88a, 88b are provided on the bevel gear.
The bevel gear fixed to the drive shaft is meshed. Any connection mechanism may be used for the drive connection portion 86 including the two bevel gears that mesh with each other as long as the lubricating liquid pumps 88a and 88b are drive-connected to the rotating shaft 32. In the third embodiment, a power supply for driving the lubricant pumps 88a and 88b is not required.
【００２０】そしてさらに、本発明の第４実施例を、図
７を参照して説明する。図７は、本発明の水中軸受潤滑
システムの第４実施例の構成図である。図７において、
図１と図４および図６と同じまたは均等な部材には同じ
符号を付けて重複する説明を省略する。Further, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 7 is a configuration diagram of a fourth embodiment of the underwater bearing lubrication system of the present invention. In FIG.
The same or equivalent members as those in FIGS. 1, 4 and 6 are denoted by the same reference numerals, and redundant description will be omitted.
【００２１】図７に示す第４実施例では、水中軸受３
４，３６の潤滑液室５８から潤滑液を流出させる流出管
が設けられていない。また、水中軸受３４，３６と同じ
高さ位置に揚水管内の圧力を検出できるように圧力セン
サー９０ａ，９０ｂが設けられる。さらに、潤滑液ポン
プ６４ａ，６４ｂに接続された配管は、２つに分岐さ
れ、一方は流量計６６ａ，６６ｂを介して流入管６０
ａ，６０ｂとして水中軸受３４，３６の潤滑液室５８に
それぞれ連通開口される。なお、水中軸受３４，３６の
潤滑液室５８は、流入管６０ａ，６０ｂのための開口が
設けられるだけであり、潤滑液の流出のための開口は設
けられていない。そして、分岐された配管の他方は、流
量調整弁７２ａ，７２ｂを介して潤滑液漕２４に連通さ
れる。ここで、潤滑液圧力センサー６８ａ，６８ｂは流
入管６０ａ，６０ｂにそれぞれ設けられる。さらに、潤
滑液圧力センサー６８ａ，６８ｂと圧力センサー９０
ａ，９０ｂおよび流量計６６ａ，６６ｂの検出信号は制
御部７８に与えられ、制御部７８からの信号で調整モー
タ７４ａ，７４ｂが制御される。In the fourth embodiment shown in FIG.
There is no outflow pipe for allowing the lubricating liquid to flow out of the lubricating liquid chambers 58 of the fourth and thirty-six. Further, pressure sensors 90a and 90b are provided at the same height position as the underwater bearings 34 and 36 so as to detect the pressure in the pumping pipe. Further, the pipe connected to the lubricating liquid pumps 64a and 64b is branched into two pipes, one of which is connected to the inflow pipe 60 via flow meters 66a and 66b.
The openings a and 60b communicate with the lubricating fluid chambers 58 of the underwater bearings 34 and 36, respectively. The lubricating liquid chambers 58 of the underwater bearings 34, 36 are provided only with openings for the inflow pipes 60a, 60b, and are not provided with openings for the outflow of the lubricating liquid. Then, the other of the branched pipes is communicated with the lubricating liquid tank 24 via the flow control valves 72a and 72b. Here, the lubricating fluid pressure sensors 68a and 68b are provided in the inflow pipes 60a and 60b, respectively. Further, the lubricant pressure sensors 68a and 68b and the pressure sensor 90
The detection signals of the flowmeters a and 90b and the flow meters 66a and 66b are provided to the control unit 78, and the adjustment motors 74a and 74b are controlled by the signals from the control unit 78.
【００２２】かかる構成において、流量調整弁７２ａ，
７２ｂの弁の開度を調整することで、流入管６０ａ，６
０ｂの圧力が調整できる。そこで、圧力センサー９０
ａ，９０ｂの検出値より、潤滑液圧力センサー６８ａ，
６８ｂの検出値が僅かに高くなるように、制御部７８は
調整モータ７４ａ，７４ｂを制御して流量調整弁７２
ａ，７２ｂを調整する。そして、流量計６６ａ，６６ｂ
により水中軸受３４，３６における潤滑液の漏れ量を検
出する。In such a configuration, the flow control valve 72a,
By adjusting the opening degree of the valve 72b, the inflow pipes 60a, 60
The pressure of 0b can be adjusted. Therefore, the pressure sensor 90
a, 90b, the lubricating fluid pressure sensor 68a,
The control unit 78 controls the adjustment motors 74a and 74b so that the detection value of the flow control valve 72b becomes slightly higher.
a and 72b are adjusted. And the flow meters 66a, 66b
Thus, the amount of leakage of the lubricating liquid in the underwater bearings 34, 36 is detected.
【００２３】この第４実施例では、水中軸受３４，３６
と同じ高さで揚水管内の流体の圧力を圧力センサー９０
ａ，９０ｂで検出するので、この検出値より僅かに高い
圧力に水中軸受３４，３６内の圧力を設定すれば良く、
制御部７８における演算が容易である。特に、気中運転
と気水撹拌運転および揚水運転のいずれの運転状態であ
っても、制御部７８による水中軸受３４，３６内の圧力
を設定する方法が同じで良く、制御部７８の構成が簡単
化できる。しかも、水中軸受３４，３６の外側の圧力を
圧力センサー９０ａ，９０ｂで検出するので、水中軸受
３４．３６内の圧力を所望の圧力に確実に設定し得る。
さらに、流出管が設けられておらず、それだけ配管構造
が簡単である。In the fourth embodiment, the underwater bearings 34, 36
The pressure of the fluid in the pumping pipe at the same height as the pressure sensor 90
a, 90b, the pressure in the underwater bearings 34, 36 may be set to a pressure slightly higher than the detected value.
The calculation in the control unit 78 is easy. In particular, the method of setting the pressure in the underwater bearings 34 and 36 by the control unit 78 may be the same regardless of the operating state of the air operation, the air / water stirring operation, and the pumping operation. Can be simplified. In addition, since the pressure outside the underwater bearings 34 and 36 is detected by the pressure sensors 90a and 90b, the pressure inside the underwater bearings 34 and 36 can be reliably set to a desired pressure.
Further, no outflow pipe is provided, and the piping structure is correspondingly simple.
【００２４】なお、第４実施例では、水中軸受３４，３
６へ流入する潤滑液を、漏れ量の分だけ補給できれば良
く、大きな流量を必要としない。そこで、潤滑液ポンプ
６４ａ，６４ｂに代えて、潤滑液を所望の圧力に調整し
て供給できるならば、アキュムレータ等いかなる構造で
あっても良い。In the fourth embodiment, the underwater bearings 34, 3
It is sufficient that the lubricating liquid flowing into the nozzle 6 can be supplied by an amount corresponding to the leakage amount, and a large flow rate is not required. Therefore, any structure such as an accumulator may be used as long as the lubricating liquid can be adjusted to a desired pressure and supplied instead of the lubricating liquid pumps 64a and 64b.
【００２５】ところで、上記第１ないし第４実施例にあ
っては、いずれも保護管を不用とするとともに水中軸受
３４、３６の潤滑液の圧力を外側よりも僅かに高く設定
するように構成したものである。ここで、図９に示す保
護管１８を用いる従来技術にあっては、保護管１８内の
潤滑液の圧力が低く、揚水運転状態では内外の圧力差に
より揚水が保護管１８内に侵入する虞があることは前述
の通りである。そこで、本発明の潤滑液の圧力を外側よ
りも僅かに高く設定する技術を、保護管１８内の潤滑液
に適用するならば、揚水が保護管１８内に侵入すること
を防ぐことができる。これは、常時揚水運転を行うポン
プでも効果的である。かかる観点から創作したのが、本
発明の第５実施例である。In the first to fourth embodiments, the protection tube is not required and the pressure of the lubricating liquid in the underwater bearings 34, 36 is set slightly higher than the outside. Things. Here, in the prior art using the protection tube 18 shown in FIG. 9, the pressure of the lubricating liquid in the protection tube 18 is low, and in the pumping operation state, pumping water may enter the protection tube 18 due to a pressure difference between the inside and outside. Is as described above. Therefore, if the technique of setting the pressure of the lubricating liquid of the present invention slightly higher than that of the outside is applied to the lubricating liquid in the protection tube 18, it is possible to prevent pumping water from entering the protection tube 18. This is also effective for a pump that always performs a pumping operation. The fifth embodiment of the present invention was created from such a viewpoint.
【００２６】本発明の第５実施例を、図８を参照して説
明する。図８は、本発明の水中軸受潤滑システムの第５
実施例の構成図である。図８において、図９と同じまた
は均等な部材には同じ符号を付けて重複する説明を省略
する。A fifth embodiment of the present invention will be described with reference to FIG. FIG. 8 shows a fifth embodiment of the underwater bearing lubrication system of the present invention.
It is a lineblock diagram of an example. 8, the same or equivalent members as those in FIG. 9 are denoted by the same reference numerals, and redundant description will be omitted.
【００２７】図８に示す第５実施例では、従来例のごと
き回転軸１２および水中軸受１４，１６全体を保護管１
８で覆う構造である。まず、保護管１８の両端側に軸封
部材９２，９４を設けて、保護管１８内を水密構造の潤
滑液室５８とし、その上端部に潤滑液ポンプ２２で潤滑
液漕２４から潤滑液が流入管６０を介して注入される。
また、潤滑液室５８の下端部に連通開口する流出管６２
は、潤滑液圧力センサー６８と流量調整弁７２を介して
潤滑液漕２４に戻る。流量調整弁７２には、これを調整
するための調整モータ７４が設けられる。そして、吐出
しエルボには、吐出し流体の圧力を検出する圧力センサ
ー７６が設けられる。潤滑液圧力センサー６８および圧
力センサー７６の検出信号が制御部７８に与えられ、制
御部７８の出力信号で調整モータ７４が制御されて流量
調整弁７２の弁の開度が調整される。In the fifth embodiment shown in FIG. 8, the rotary shaft 12 and the underwater bearings 14, 16 as in the conventional example are entirely covered with the protective tube 1.
8. First, shaft sealing members 92 and 94 are provided at both ends of the protective tube 18 to form a watertight lubricating liquid chamber 58 inside the protective tube 18, and lubricating liquid is supplied from the lubricating liquid tank 24 by the lubricating liquid pump 22 to the upper end thereof. It is injected through the inflow pipe 60.
Further, an outflow pipe 62 communicating with the lower end of the lubricating liquid chamber 58 is opened.
Returns to the lubricating liquid tank 24 via the lubricating liquid pressure sensor 68 and the flow control valve 72. The flow regulating valve 72 is provided with an adjusting motor 74 for adjusting the flow. The discharge elbow is provided with a pressure sensor 76 for detecting the pressure of the discharge fluid. The detection signals of the lubricating fluid pressure sensor 68 and the pressure sensor 76 are provided to the control unit 78, and the adjustment motor 74 is controlled by the output signal of the control unit 78 to adjust the opening degree of the flow control valve 72.
【００２８】かかる構成において、流出管６２の潤滑液
圧力センサー６８の検出値が、吐出しエルボに設けた圧
力センサー７６の検出した圧力に吐出しエルボと下側の
水中軸受１６の高低差Ｌ１による水体積による重さを加
算した圧力よりも、僅かに高い圧力となるように、制御
部７８は流量調整弁７２を調整する。このようにして、
保護管１８内の潤滑液の圧力が、揚水管内の流体の圧力
に応じて設定され、揚水が保護管１８内に侵入すること
がない。そして、この第５実施例は、図９に示すごとき
保護管１８を有する従来構造のポンプを改造することに
より、本発明を簡単に適用することができる。In this configuration, the detection value of the lubricating fluid pressure sensor 68 of the outflow pipe 62 is determined by the height difference L1 between the discharge elbow and the lower underwater bearing 16 at the pressure detected by the pressure sensor 76 provided in the discharge elbow. The control unit 78 adjusts the flow control valve 72 so that the pressure is slightly higher than the pressure obtained by adding the weight based on the water volume. In this way,
The pressure of the lubricating liquid in the protection tube 18 is set according to the pressure of the fluid in the water pumping tube, so that the pumped water does not enter the protection tube 18. In the fifth embodiment, the present invention can be easily applied by modifying a conventional pump having a protection tube 18 as shown in FIG.
【００２９】上述の第５実施例では、保護管１８の上端
部に流入管６０を連通開口させて潤滑液が保護管１８内
を流下するようにしているが、保護管１８の下端部に流
入管６０を連通開口させ、上端部に流出管６２を連通さ
せても良い。このような配管にあっては、流出管６２の
開口位置と吐出しエルボに設けた圧力センサー７６の位
置がほぼ同じ高さであり、流出管６２に設けた潤滑液圧
力センサー６８の圧力を、吐出しエルボに設けた圧力セ
ンサー７６の圧力よりも僅かに高く設定すれば良い。In the above-described fifth embodiment, the inflow pipe 60 is opened at the upper end of the protection pipe 18 so that the lubricating liquid flows down in the protection pipe 18. The pipe 60 may be opened for communication, and the outflow pipe 62 may be connected to the upper end. In such a pipe, the opening position of the outflow pipe 62 and the position of the pressure sensor 76 provided in the discharge elbow are almost the same height, and the pressure of the lubricating fluid pressure sensor 68 provided in the outflow pipe 62 is What is necessary is just to set it slightly higher than the pressure of the pressure sensor 76 provided in the discharge elbow.
【００３０】なお、上記実施例において、潤滑液は、水
またはグリセリン水溶液などの他の液体のいかなるもの
であっても良い。また、流出管に潤滑液圧力センサを設
けて水中軸受内の潤滑液の圧力を検出しているが、流入
管に潤滑液圧力センサーを設けて適宜に潤滑液の圧力を
検出するようにしても良い。そして、潤滑液の圧力の調
整は、流出管に設けた流量調整弁の弁の開度の調整に限
られず、潤滑液ポンプの吐出し圧力自体を調整するもの
であっても良い。さらに、軸受ケースの外側の圧力より
も水中軸受内の潤滑液の圧力を僅かに高く設定するが、
その圧力差は、潤滑液の粘度や軸封部材の水密性能およ
び機械的強度などに応じて実験等により適当な値を選定
すれば良い。In the above embodiment, the lubricating liquid may be any other liquid such as water or an aqueous glycerin solution. Further, a lubricating liquid pressure sensor is provided in the outflow pipe to detect the pressure of the lubricating liquid in the underwater bearing. However, a lubricating liquid pressure sensor may be provided in the inflow pipe to appropriately detect the pressure of the lubricating liquid. good. The adjustment of the pressure of the lubricating liquid is not limited to the adjustment of the opening of the flow control valve provided in the outflow pipe, but may be the adjustment of the discharge pressure itself of the lubricating liquid pump. Furthermore, the pressure of the lubricating fluid in the underwater bearing is set slightly higher than the pressure outside the bearing case,
An appropriate value for the pressure difference may be selected by experiments or the like in accordance with the viscosity of the lubricating liquid, the watertightness of the shaft sealing member, the mechanical strength, and the like.
【００３１】[0031]
【発明の効果】本発明は、上述のごとく構成されている
ので、以下のごとき格別な効果が得られる。Since the present invention is constructed as described above, the following special effects can be obtained.
【００３２】請求項１または２記載の水中軸受潤滑シス
テムは、水中軸受内の潤滑液の圧力を、その外側の圧力
より僅かに高く設定するので、揚水が水中軸受内に侵入
することがなく、揚水に含まれる砂や泥で水中軸受の摺
接面が損傷を受けることがない。そして、内外の圧力差
が小さいことから、潤滑液の漏れがなく、また漏れても
極めて僅かである。また、従来のごとき保護管を必要と
せず、保護管の破損などの重大な故障の虞がなく、それ
だけ信頼性が向上する。In the underwater bearing lubrication system according to the first or second aspect, the pressure of the lubricating fluid in the underwater bearing is set slightly higher than the pressure outside the underwater bearing, so that pumping water does not enter the underwater bearing. The sliding surface of the underwater bearing is not damaged by sand or mud contained in the pumped water. Further, since the pressure difference between the inside and outside is small, there is no leakage of the lubricating liquid, and the leakage is very slight. In addition, a conventional protective tube is not required, and there is no possibility of a serious failure such as breakage of the protective tube, and the reliability is improved accordingly.
【００３３】請求項３記載の水中軸受潤滑システムは、
揚水運転で、ポンプ流路内の流体の圧力を検出し、その
圧力センサーと水中軸受が設けられた高低差から、軸受
ケースの外側の流体の圧力を演算し、演算された圧力よ
り水中軸受内の潤滑液の圧力を僅かに高く設定し、気中
運転では水中軸受内の潤滑液の圧力を大気圧より僅かに
高く設定するので、揚水運転と気中運転のいずれでも潤
滑液の圧力を適正に設定できる。しかも、流路内の流体
圧力から水中軸受内に設定すべき圧力値を簡単に演算し
得る。The underwater bearing lubrication system according to claim 3 is
In the pumping operation, the pressure of the fluid in the pump flow path is detected, and the pressure of the fluid outside the bearing case is calculated from the height difference between the pressure sensor and the underwater bearing. The lubricating fluid pressure in the underwater bearing is set slightly higher than the atmospheric pressure during in-air operation, so the lubricating fluid pressure is appropriate for both pumping operation and in-air operation. Can be set to Moreover, the pressure value to be set in the underwater bearing can be easily calculated from the fluid pressure in the flow path.
【００３４】請求項６記載の水中軸受潤滑システムは、
流出管に設けた流量調節弁の弁の開度を調整すること
で、水中軸受内の潤滑液の圧力を容易に調整できる。[0034] The underwater bearing lubrication system according to claim 6 comprises:
The pressure of the lubricating liquid in the underwater bearing can be easily adjusted by adjusting the opening of the flow control valve provided in the outflow pipe.
【００３５】請求項７記載の水中軸受潤滑システムは、
流入管と流出管に設けた流量計で検出され流量の差か
ら、軸封部材からの潤滑液の漏れ量が演算でき、軸封部
材の摩耗度合いなどを判定でき、分解点検等をすること
なしに、軸封部材の適正な保守管理がなし得る。According to a seventh aspect of the present invention, there is provided an underwater bearing lubrication system.
From the difference between the flow rates detected by the flow meters provided on the inflow pipe and the outflow pipe, the amount of leakage of the lubricating fluid from the shaft sealing member can be calculated, the degree of wear of the shaft sealing member can be determined, and there is no need for disassembly and inspection In addition, proper maintenance of the shaft sealing member can be achieved.
【００３６】請求項８記載の水中軸受潤滑システムは、
潤滑液ポンプが主ポンプの回転軸に連結駆動されてい
て、潤滑液ポンプを駆動するための電源が不用である。The underwater bearing lubrication system according to claim 8 is
Since the lubricating liquid pump is connected to and driven by the rotation shaft of the main pump, a power supply for driving the lubricating liquid pump is unnecessary.
【００３７】請求項９記載の水中軸受潤滑システムは、
駆動電動機の運転動力の大きさから気水撹拌運転を判別
して、この気水撹拌運転状態における水中軸受内の潤滑
液の圧力を適宜に設定できるので、主ポンプがいかなる
運転状況であっても、水中軸受に揚水が侵入したりまた
潤滑液が漏れたりすることがない。According to a ninth aspect of the present invention, there is provided an underwater bearing lubrication system.
Since the steam-water stirring operation can be determined from the magnitude of the driving power of the drive motor and the pressure of the lubricating liquid in the underwater bearing can be set appropriately in this steam-water stirring operation state, even if the main pump is in any operation state. In addition, no pumping water enters the underwater bearing and no lubricating fluid leaks.
【００３８】請求項１０記載の水中軸受潤滑システム
は、保護管内の潤滑液の圧力を、運転状況および揚水の
圧力などから、外側より僅かに高くなるように設定する
ようにしたので、保護管内に揚水が侵入することがな
い。しかも、従来の保護管を用いた構造のポンプに対し
て、簡単な改造により本発明を適用することができる。In the underwater bearing lubrication system according to the tenth aspect, the pressure of the lubricating fluid in the protection tube is set to be slightly higher than the outside in consideration of the operating conditions and the pressure of pumping water. Pumping does not enter. Moreover, the present invention can be applied to a pump having a structure using a conventional protective tube by a simple modification.
【図１】本発明の水中軸受潤滑システムの第１実施例の
構造図である。FIG. 1 is a structural diagram of a first embodiment of a submerged bearing lubrication system of the present invention.
【図２】本発明で用いる水中軸受の一例の縦断面図であ
る。FIG. 2 is a longitudinal sectional view of an example of a submerged bearing used in the present invention.
【図３】図２のＡ−Ａ矢視断面図である。FIG. 3 is a sectional view taken along line AA of FIG. 2;
【図４】本発明の水中軸受潤滑システムの第２実施例の
構造図である。FIG. 4 is a structural diagram of a second embodiment of the underwater bearing lubrication system of the present invention.
【図５】駆動電動機の入力と吐出し量を示す特性図であ
る。FIG. 5 is a characteristic diagram showing an input and a discharge amount of a drive motor.
【図６】本発明の水中軸受潤滑システムの第３実施例の
構成図である。FIG. 6 is a configuration diagram of a third embodiment of the underwater bearing lubrication system of the present invention.
【図７】本発明の水中軸受潤滑システムの第４実施例の
構成図である。FIG. 7 is a configuration diagram of a fourth embodiment of the underwater bearing lubrication system of the present invention.
【図８】本発明の水中軸受潤滑システムの第５実施例の
構成図である。FIG. 8 is a configuration diagram of a fifth embodiment of the underwater bearing lubrication system of the present invention.
【図９】従来の立軸ポンプの水中軸受潤滑システムの一
例を示す図である。FIG. 9 is a diagram showing an example of a conventional underwater bearing lubrication system for a vertical shaft pump.
１０，３０ 立軸ポンプ １２，３２ 回転軸 １４，１６，３４，３６ 水中軸受 １８ 保護管 ２２，６４，６４ａ，６４ｂ，８８ａ，８８ｂ 潤滑液
ポンプ ２４ 潤滑液漕 ４８ 通水路 ５０ 上部軸受ケース ５２ 下部軸受ケース ５４，５６，９２，９４ 軸封部材 ５８ 潤滑液室 ６０，６０ａ，６０ｂ 流入管 ６２，６２ａ，６２ｂ 流出管 ６６ａ，６６ｂ，７０ａ，７０ｂ 流量計 ６８，６８ａ，６８ｂ，９０ａ，９０ｂ 潤滑液圧力セ
ンサー ７２ａ，７２ｂ 流量調整弁 ７４ａ，７４ｂ 調整モータ ７６ 圧力センサー ７８ 制御部 ８２ 駆動電動機 ８４ 運転動力検出手段 ８６ 駆動連結部10,30 Vertical shaft pump 12,32 Rotary shaft 14,16,34,36 Underwater bearing 18 Protective tube 22,64,64a, 64b, 88a, 88b Lubricating liquid pump 24 Lubricating liquid tank 48 Water passage 50 Upper bearing case 52 Lower bearing Cases 54, 56, 92, 94 Shaft sealing member 58 Lubricating liquid chamber 60, 60a, 60b Inflow pipe 62, 62a, 62b Outflow pipe 66a, 66b, 70a, 70b Flow meter 68, 68a, 68b, 90a, 90b Lubricating liquid pressure Sensors 72a, 72b Flow control valves 74a, 74b Adjustment motor 76 Pressure sensor 78 Control unit 82 Drive motor 84 Operating power detection means 86 Drive connection unit
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ０４Ｄ 29/04 Ｆ１６Ｃ 17/14 Ｆ１６Ｃ 17/14 Ｆ０４Ｂ 21/00 Ｑ ──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. 7 Identification symbol FI Theme coat ゛ (Reference) F04D 29/04 F16C 17/14 F16C 17/14 F04B 21/00 Q
Claims (10)
ともに、前記軸受ケースの軸方向両端側に軸封部材を設
けて潤滑液室とし、この潤滑液室内の潤滑液で前記水中
軸受が濡れるようになし、前記潤滑液室に流入管の一端
を連通開口してこの流入管を介して前記潤滑液室に前記
潤滑液が流入し得るようになし、しかも前記潤滑液室内
の前記潤滑液の圧力が前記軸受ケースの外側の圧力より
僅かに高くなるように調整する調整機構を設けて構成し
たことを特徴とする水中軸受潤滑システム。An underwater bearing is provided inside a bearing case, and shaft sealing members are provided at both axial ends of the bearing case to form a lubricating liquid chamber, so that the underwater bearing is wetted by the lubricating liquid in the lubricating liquid chamber. One end of an inflow pipe communicates with the lubricating liquid chamber so that the lubricating liquid can flow into the lubricating liquid chamber through the inflow pipe. An underwater bearing lubrication system characterized by comprising an adjusting mechanism for adjusting the pressure slightly higher than the pressure outside the bearing case.
ともに、前記軸受ケースの軸方向両端側に軸封部材を設
けて潤滑液室とし、この潤滑液室内の潤滑液で前記水中
軸受が濡れるようになし、前記潤滑液室に流入管および
流出管の一端をそれぞれ連通開口して、潤滑液ポンプよ
り吐出した前記潤滑液を前記流入管を介して前記潤滑液
室に流入させ前記流出管を介して流出させるようにな
し、しかも前記潤滑液室内の前記潤滑液の圧力が前記軸
受ケースの外側の圧力より僅かに高くなるように調整す
る調整機構を設けて構成したことを特徴とする水中軸受
潤滑システム。2. An underwater bearing is provided inside a bearing case, and shaft sealing members are provided at both axial ends of the bearing case to form a lubricating liquid chamber. The lubricating liquid in the lubricating liquid chamber may wet the underwater bearing. One end of an inflow pipe and one end of an outflow pipe are respectively opened to the lubricating liquid chamber, and the lubricating liquid discharged from a lubricating liquid pump flows into the lubricating liquid chamber through the inflow pipe and flows through the outflow pipe. Underwater bearing lubrication characterized by comprising an adjusting mechanism for adjusting the pressure of the lubricating fluid in the lubricating fluid chamber to be slightly higher than the pressure outside the bearing case. system.
ステムにおいて、前記水中軸受を回転軸に設けた主ポン
プの流路に、その流路内の流体圧力を検出する圧力セン
サーを設け、揚水運転において、前記圧力センサーの検
出値と、前記圧力センサーの配設位置と前記水中軸受の
配設位置の高低差から前記軸受ケースの外側の圧力を演
算するとともに、この演算した圧力よりも前記潤滑液室
内の圧力が僅かに高くなるように前記調整機構で調整
し、前記圧力センサーで吐出し圧力が検出されない気中
運転において、前記潤滑液室内の圧力が大気圧より僅か
に高くなるように前記調整機構で調整するように構成し
たことを特徴とする水中軸受潤滑システム。3. The underwater bearing lubrication system according to claim 1, wherein a pressure sensor for detecting a fluid pressure in the passage is provided in a flow path of a main pump provided with the underwater bearing on a rotating shaft, and pumping is performed. In operation, a pressure outside the bearing case is calculated from a detected value of the pressure sensor and a height difference between a position where the pressure sensor is disposed and a position where the underwater bearing is disposed, and the lubrication is calculated based on the calculated pressure. Adjusted by the adjusting mechanism so that the pressure in the liquid chamber becomes slightly higher, and in the aerial operation in which the discharge pressure is not detected by the pressure sensor, the pressure in the lubricating liquid chamber is slightly higher than the atmospheric pressure. An underwater bearing lubrication system characterized by being configured to be adjusted by an adjustment mechanism.
おいて、前記圧力センサーが主ポンプの吐出しエルボに
配設されることを特徴とした水中軸受潤滑システム。4. The underwater bearing lubrication system according to claim 3, wherein the pressure sensor is disposed on a discharge elbow of a main pump.
ステムにおいて、複数の前記水中軸受を主ポンプの回転
軸に軸方向に離して配設し、それぞれの前記潤滑液室内
の前記潤滑液の圧力がそれぞれに前記軸受ケースの外側
の圧力よりも僅かに高くなるように前記調整機構で調整
するように構成したことを特徴とする水中軸受潤滑シス
テム。5. The underwater bearing lubrication system according to claim 1, wherein a plurality of said underwater bearings are disposed axially apart from each other on a rotating shaft of a main pump, and a plurality of said underwater bearings are disposed in each of said lubricant chambers. The underwater bearing lubrication system, wherein the pressure is adjusted by the adjusting mechanism so that the pressure is slightly higher than the pressure outside the bearing case.
おいて、前記流出管に潤滑液圧力センサーと流量調整弁
を設け、この潤滑液圧力センサーの検出値が前記軸受ケ
ースの外側の圧力より僅かに高くなるように、前記流量
調整弁を前記調整機構で調整するように構成したことを
特徴とする水中軸受潤滑システム。6. The underwater bearing lubrication system according to claim 2, wherein a lubricating fluid pressure sensor and a flow regulating valve are provided in the outflow pipe, and the detected value of the lubricating fluid pressure sensor is slightly lower than the pressure outside the bearing case. The underwater bearing lubrication system, wherein the flow control valve is adjusted by the adjusting mechanism so as to be higher.
おいて、前記流入管と流出管にそれぞれ流量計を設け、
前記流入管と流出管の流量の差から前記軸封部材からの
前記潤滑液の漏れ量を検出する機構を設けたことを特徴
とする水中軸受潤滑システム。7. The underwater bearing lubrication system according to claim 2, wherein a flow meter is provided for each of the inflow pipe and the outflow pipe.
An underwater bearing lubrication system comprising a mechanism for detecting a leakage amount of the lubricating liquid from the shaft sealing member from a difference in flow rate between the inflow pipe and the outflow pipe.
おいて、潤滑液ポンプを前記水中軸受を設けた主ポンプ
の回転軸と連結駆動して構成したことを特徴とする水中
軸受潤滑システム。8. The underwater bearing lubrication system according to claim 2, wherein a lubricating liquid pump is driven by being connected to a rotary shaft of a main pump provided with the underwater bearing.
おいて、前記主ポンプの駆動電動機の運転動力の大きさ
から気水撹拌運転状態であることを判定する判定手段を
設け、前記主ポンプの気水撹拌運転状態で前記圧力セン
サーが揚水に晒されず前記軸受ケースが揚水に水没する
場合には、前記判定手段による気水撹拌運転の判定によ
り、前記潤滑液室内の圧力が予め設定された所定の圧力
となるように前記調整機構で調整するように構成したこ
とを特徴とする水中軸受潤滑システム。9. The underwater bearing lubrication system according to claim 3, further comprising: a judging means for judging a state of a water / water agitation operation from a magnitude of an operation power of a drive motor of the main pump, and In the case where the pressure sensor is not exposed to pumping and the bearing case is submerged in pumping in the water stirring operation state, the pressure in the lubricating fluid chamber is set to a predetermined value by the determination of the air / water stirring operation by the determination unit. The underwater bearing lubrication system, wherein the pressure is adjusted by the adjusting mechanism so that the pressure becomes the following pressure.
って保護管を設け、この保護管の軸方向両端側を水密構
造となし、前記保護管内に流入管と流出管を介して潤滑
液を流入させる水中軸受潤滑システムにおいて、前記流
出管に潤滑液圧力センサーと流量調整弁を設け、前記主
ポンプの流路に、その流路内の流体圧力を検出する圧力
センサーを設け、前記潤滑液圧力センサーの検出値が前
記圧力センサーの検出値よりも所定値だけ高い値となる
ように前記流量調整弁を調整する調整機構を設けて構成
したことを特徴とする水中軸受潤滑システム。10. A protective tube is provided so as to cover the rotating shaft of the main pump and the underwater bearing, and both ends in the axial direction of the protective tube have a watertight structure, and lubricating liquid is supplied into the protective tube via an inflow pipe and an outflow pipe. In the underwater bearing lubrication system to be supplied, a lubricating fluid pressure sensor and a flow rate regulating valve are provided in the outflow pipe, and a pressure sensor for detecting a fluid pressure in the main pump is provided in a flow path of the main pump. An underwater bearing lubrication system, comprising: an adjusting mechanism that adjusts the flow control valve so that a detected value of the sensor is higher than a detected value of the pressure sensor by a predetermined value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000351363A JP2002156092A (en) | 2000-11-17 | 2000-11-17 | Submerged bearing lubrication system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000351363A JP2002156092A (en) | 2000-11-17 | 2000-11-17 | Submerged bearing lubrication system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002156092A true JP2002156092A (en) | 2002-05-31 |
Family
ID=18824436
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000351363A Pending JP2002156092A (en) | 2000-11-17 | 2000-11-17 | Submerged bearing lubrication system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002156092A (en) |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007127026A (en) * | 2005-11-02 | 2007-05-24 | Hitachi Engineering & Services Co Ltd | Lubricating system for submerged bearing device |
| WO2008090994A1 (en) * | 2007-01-22 | 2008-07-31 | Ebara Corporation | Multi-stage high-pressure pump |
| JP2011021586A (en) * | 2009-07-21 | 2011-02-03 | Torishima Pump Mfg Co Ltd | Screw pump |
| NO20151391A1 (en) * | 2015-09-23 | 2011-12-19 | Baker Hughes Oilfield Operations Inc | Subsea pump system |
| JP2012219728A (en) * | 2011-04-11 | 2012-11-12 | Ebara Corp | Submerged bearing device and horizontal shaft pump |
| JP2014031752A (en) * | 2012-08-02 | 2014-02-20 | Torishima Pump Mfg Co Ltd | Pump |
| JP2015094263A (en) * | 2013-11-11 | 2015-05-18 | 三菱重工業株式会社 | Bearings and pump |
| GB2537699A (en) * | 2015-04-20 | 2016-10-26 | Skf Ab | Method of measuring a volume of a lubricant inside a bearing arrangement |
| JP2017166423A (en) * | 2016-03-16 | 2017-09-21 | 株式会社酉島製作所 | pump |
| JP2017172530A (en) * | 2016-03-25 | 2017-09-28 | 株式会社酉島製作所 | Vertical shaft pump |
| JP2018084193A (en) * | 2016-11-24 | 2018-05-31 | 株式会社荏原製作所 | Vertical shaft pump |
| CN108223396A (en) * | 2017-12-11 | 2018-06-29 | 中国水利水电科学研究院 | A kind of high-precision water pump bath scaled model experimental device |
| CN108331723A (en) * | 2018-03-22 | 2018-07-27 | 许占欣 | A kind of magnetic suspending wind turbine generator oil immersed type multiple bearing combination shaft |
| JP2019183697A (en) * | 2018-04-05 | 2019-10-24 | 株式会社荏原製作所 | Horizontal shaft pump device |
| JP2020007983A (en) * | 2018-07-10 | 2020-01-16 | 株式会社酉島製作所 | pump |
| JP2021085390A (en) * | 2019-11-29 | 2021-06-03 | 株式会社酉島製作所 | pump |
| CN114484246A (en) * | 2021-12-31 | 2022-05-13 | 陕西正通煤业有限责任公司 | Pneumatic double-shield TBM cutter head grease pump standby pump and using method thereof |
| CN115013320A (en) * | 2022-06-20 | 2022-09-06 | 广东鹏洋应急科技有限公司 | Automatic adjusting high-pressure water pump |
-
2000
- 2000-11-17 JP JP2000351363A patent/JP2002156092A/en active Pending
Cited By (27)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4628252B2 (en) * | 2005-11-02 | 2011-02-09 | 株式会社日立エンジニアリング・アンド・サービス | Lubricating system for underwater bearing equipment |
| JP2007127026A (en) * | 2005-11-02 | 2007-05-24 | Hitachi Engineering & Services Co Ltd | Lubricating system for submerged bearing device |
| WO2008090994A1 (en) * | 2007-01-22 | 2008-07-31 | Ebara Corporation | Multi-stage high-pressure pump |
| JP2008175182A (en) * | 2007-01-22 | 2008-07-31 | Ebara Corp | Multistage high pressure pump |
| JP4642788B2 (en) * | 2007-01-22 | 2011-03-02 | 株式会社荏原製作所 | Multistage high pressure pump |
| US8540478B2 (en) | 2007-01-22 | 2013-09-24 | Ebara Corporation | Multistage high-pressure pump |
| JP2011021586A (en) * | 2009-07-21 | 2011-02-03 | Torishima Pump Mfg Co Ltd | Screw pump |
| JP2012219728A (en) * | 2011-04-11 | 2012-11-12 | Ebara Corp | Submerged bearing device and horizontal shaft pump |
| JP2014031752A (en) * | 2012-08-02 | 2014-02-20 | Torishima Pump Mfg Co Ltd | Pump |
| JP2015094263A (en) * | 2013-11-11 | 2015-05-18 | 三菱重工業株式会社 | Bearings and pump |
| GB2537699A (en) * | 2015-04-20 | 2016-10-26 | Skf Ab | Method of measuring a volume of a lubricant inside a bearing arrangement |
| NO341009B1 (en) * | 2015-09-23 | 2017-08-07 | Baker Hughes Oilfield Operations Inc | Subsea pump system |
| NO20151391A1 (en) * | 2015-09-23 | 2011-12-19 | Baker Hughes Oilfield Operations Inc | Subsea pump system |
| JP2017166423A (en) * | 2016-03-16 | 2017-09-21 | 株式会社酉島製作所 | pump |
| JP2017172530A (en) * | 2016-03-25 | 2017-09-28 | 株式会社酉島製作所 | Vertical shaft pump |
| JP2018084193A (en) * | 2016-11-24 | 2018-05-31 | 株式会社荏原製作所 | Vertical shaft pump |
| CN108223396B (en) * | 2017-12-11 | 2024-04-26 | 中国水利水电科学研究院 | High-precision water pump model experimental device |
| CN108223396A (en) * | 2017-12-11 | 2018-06-29 | 中国水利水电科学研究院 | A kind of high-precision water pump bath scaled model experimental device |
| CN108331723A (en) * | 2018-03-22 | 2018-07-27 | 许占欣 | A kind of magnetic suspending wind turbine generator oil immersed type multiple bearing combination shaft |
| JP2019183697A (en) * | 2018-04-05 | 2019-10-24 | 株式会社荏原製作所 | Horizontal shaft pump device |
| JP7051542B2 (en) | 2018-04-05 | 2022-04-11 | 株式会社荏原製作所 | Horizontal axis pump device |
| JP2020007983A (en) * | 2018-07-10 | 2020-01-16 | 株式会社酉島製作所 | pump |
| JP2021085390A (en) * | 2019-11-29 | 2021-06-03 | 株式会社酉島製作所 | pump |
| JP7294997B2 (en) | 2019-11-29 | 2023-06-20 | 株式会社酉島製作所 | pump |
| CN114484246A (en) * | 2021-12-31 | 2022-05-13 | 陕西正通煤业有限责任公司 | Pneumatic double-shield TBM cutter head grease pump standby pump and using method thereof |
| CN114484246B (en) * | 2021-12-31 | 2023-09-05 | 陕西正通煤业有限责任公司 | Pneumatic double-shield TBM cutter head grease pump standby pump and use method thereof |
| CN115013320A (en) * | 2022-06-20 | 2022-09-06 | 广东鹏洋应急科技有限公司 | Automatic adjusting high-pressure water pump |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2002156092A (en) | Submerged bearing lubrication system | |
| CA1172907A (en) | Method and mechanism for controlling the pressure at shaft-sealing part of an apparatus | |
| CN107074334B (en) | For the sealing device of ship, propulsion unit, ship and method for sealing propeller for ship axis | |
| RU2179653C2 (en) | Hydraulic machine sealing system | |
| EP1586798B1 (en) | Seal construction | |
| JP4637614B2 (en) | Submersible pump oil monitoring device | |
| JP3933586B2 (en) | Pump bearing monitoring apparatus and method | |
| JP6966388B2 (en) | pump | |
| JP2000027788A (en) | Method for operating vertical shaft pump, and vertical shaft pump | |
| CA1106697A (en) | Submersible pump arrangement | |
| US4913629A (en) | Wellpoint pumping system | |
| US1026101A (en) | Centrifugal pump. | |
| JP6831490B1 (en) | pump | |
| JPH10184584A (en) | Submerged pump | |
| EP0118403B1 (en) | Back flow preventing device in the outlet pipe of a pump | |
| US4598219A (en) | Submersible motor | |
| JP7383557B2 (en) | pump | |
| JP4240301B2 (en) | Turbo pump | |
| JP7148429B2 (en) | waterproof motor | |
| SU1679062A1 (en) | Pump plant | |
| JP4719027B2 (en) | Casing drainage mechanism of hydraulic machine and operation method of hydraulic machine | |
| JP2012219718A (en) | Bracket and submersible pump | |
| JPH0335911Y2 (en) | ||
| JP2017096201A (en) | pump | |
| JP3525335B2 (en) | Sealed gas-liquid vacuum pump device |