JPS626119B2 - - Google Patents
Info
- Publication number
- JPS626119B2 JPS626119B2 JP58034508A JP3450883A JPS626119B2 JP S626119 B2 JPS626119 B2 JP S626119B2 JP 58034508 A JP58034508 A JP 58034508A JP 3450883 A JP3450883 A JP 3450883A JP S626119 B2 JPS626119 B2 JP S626119B2
- Authority
- JP
- Japan
- Prior art keywords
- thrust
- motor
- seal ring
- thrust disk
- disk
- 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
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 8
- 239000000498 cooling water Substances 0.000 claims abstract description 5
- 230000001105 regulatory effect Effects 0.000 claims description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 5
- 239000012530 fluid Substances 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0416—Axial thrust balancing balancing pistons
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明はサブマージブルポンプに係り、特に主
インペラ部に軸スラスト低減装置を装着すること
が困難な構造のサブマージブルポンプに好適な軸
スラスト低減装置に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a submersible pump, and in particular, an axial thrust reduction method suitable for a submersible pump having a structure in which it is difficult to install an axial thrust reduction device on the main impeller part. Regarding equipment.
従来のサブマージブルポンプは例えば特開昭57
―88288号公報に示されるように、サブマージブ
ルモータ部の上方側に主インペラを備えている。
そして、主インペラによつて生ずる上向きの水力
的軸方向スラスト荷重は、その全荷重をモータ室
内に設けたスラスト軸受によつて支持している。
このスラスト軸受におけるスラストデイスクはモ
ータへの冷却水循環用の補助インペラ機能も兼ね
備えている。
Conventional submersible pumps, for example,
- As shown in Publication No. 88288, a main impeller is provided above the submersible motor section.
The entire upward hydraulic axial thrust load generated by the main impeller is supported by a thrust bearing provided within the motor chamber.
The thrust disk in this thrust bearing also functions as an auxiliary impeller for circulating cooling water to the motor.
〔発明が解決しようとする問題点〕
上記の従来技術において、主インペラの水力的
軸スラスト荷重のすべてを支持するスラスト軸受
は大型で高価となり、また苛酷な荷重条件で使用
されるため、長寿命が期待できなく、さらには、
スラスト軸受の多大なメカロスによりポンプ効率
が低減する等の欠点を有していた。[Problems to be solved by the invention] In the above-mentioned conventional technology, the thrust bearing that supports all of the hydraulic axial thrust load of the main impeller is large and expensive, and is used under severe load conditions, so it has a long lifespan. can't be expected, and furthermore,
This had drawbacks such as reduced pump efficiency due to large mechanical loss in the thrust bearing.
本発明は、スラスト軸受へ伝わる軸スラスト荷
重を低減させると共に補助インペラのポンプ効率
を向上させることができる軸スラスト荷重低減装
置を提供することを目的とする。 An object of the present invention is to provide an axial thrust load reducing device that can reduce the axial thrust load transmitted to a thrust bearing and improve the pump efficiency of an auxiliary impeller.
本発明の上記の目的は、モータ及び軸受の冷却
のために水を循環する補助インペラの機能を兼ね
るスラストデイスクの外周面、及び内周面近くに
流路抵抗となるモータ軸線と平行な細隙部を構成
するシールリングを設けることにより達成され
る。
The above object of the present invention is to provide a slit parallel to the motor axis that acts as a flow resistance near the outer circumferential surface and inner circumferential surface of a thrust disk that also functions as an auxiliary impeller for circulating water for cooling the motor and bearings. This is achieved by providing a sealing ring that constitutes a section.
スラストデイスクの下面側にはシールリングに
よつて調圧室が形成され、このスラストデイスク
の下面側の調圧室内の圧力とスラストデイスクの
上面側の調圧室内の圧力とにより、スラスト軸受
へ伝わる軸スラスト荷重を低減すると共に、スラ
ストデイスクの外周面側に設けたシールリングに
より逆流が低減され補助インペラのポンプ効率を
向上させることができる。
A pressure regulating chamber is formed on the bottom side of the thrust disk by a seal ring, and the pressure inside the pressure regulating chamber on the bottom side of the thrust disk and the pressure inside the pressure regulating chamber on the top side of the thrust disk are transmitted to the thrust bearing. In addition to reducing the axial thrust load, the seal ring provided on the outer peripheral surface of the thrust disk reduces backflow and improves the pumping efficiency of the auxiliary impeller.
以下、本発明の一実施例を第１図により説明す
る。本発明によるサブマージブルポンプは、ポン
プ室Ａ内に設けた主インペラ１、案内羽根２及び
モータ室Ｂ内に設けたモータ固定子３、モータ回
転子４、シヤフト７ａ，７ｂ、モータ室Ｂ内にお
けるシヤフト７ａ，７ｂの上部を支持するラジア
ル軸受５ａ，５ｂ、シヤフト７ａ，７ｂの下部に
設けられたスラスト軸受６ａ，６ｂ、スラスト軸
受６ａ，６ｂ間に設けられ、かつモータ冷却水循
環用補助インペラを兼ねるスラストデイスク８、
補助インペラの吐出水が吸込側に逆流する時の流
路となるスラストデイスク８の外周面に細隙部９
ａを形成するためのシールリング９、シールリン
グ９とスラスト軸受６ｂとの間に形成された調圧
室１３及びスラストデイスク８の内周面近くにモ
ータ軸線と平行な細隙部１２ａを形成するように
モータ室ケースB1に設けたシールリング１２よ
りなつている。またスラストデイスク８にはポン
プ用穴８ａが複数個設けられている。
An embodiment of the present invention will be described below with reference to FIG. The submersible pump according to the present invention includes a main impeller 1 and guide vanes 2 provided in a pump chamber A, a motor stator 3 and a motor rotor 4 provided in a motor chamber B, and shafts 7a and 7b provided in a motor chamber B. Radial bearings 5a, 5b supporting the upper parts of the shafts 7a, 7b; thrust bearings 6a, 6b provided at the lower parts of the shafts 7a, 7b; installed between the thrust bearings 6a, 6b, and also serving as an auxiliary impeller for circulating motor cooling water. Thrust disk 8,
A slit 9 is provided on the outer peripheral surface of the thrust disk 8, which serves as a flow path when water discharged from the auxiliary impeller flows back to the suction side.
A narrow gap 12a parallel to the motor axis is formed near the inner peripheral surface of the seal ring 9, the pressure regulating chamber 13 formed between the seal ring 9 and the thrust bearing 6b, and the thrust disk 8. It consists of a seal ring 12 provided in the motor chamber case B1 . Further, the thrust disk 8 is provided with a plurality of pump holes 8a.
次に上述した本発明の装置の一実施例の動作を
第１図および第２図によつて説明する。 Next, the operation of one embodiment of the above-mentioned apparatus of the present invention will be explained with reference to FIGS. 1 and 2.
第２図に示すように、ポンプが回転している時
スラストデイスク８に設けられた穴８ａによつて
揚水された冷却水の大部分は、上側のスラスト軸
受６ａのパッド間を通つてシヤフト７ｂの外周に
流れ出て、さらに上側に流れモータ固定子３を冷
却し、第１図に示す外部の熱交換器２０内を流れ
てモータ室Ｂの下部に戻る。また揚水された水の
一部は、シールリング９によつて構成される細隙
部９ａを流れ、さらに調圧室１３、下側のスラス
ト軸受６ｂのパツド間、シールリング１２によつ
て構成されるモータ軸線と平行な細隙部１２ａを
通つて、補助インペラの吸込口つまり穴８ａの入
口へ逆流する。調圧室１３内の圧力P3は吸込圧P1
と吐出圧P2との間の圧力になるわけであるが、こ
の圧力P3はシールリング９，１２の形状寸法
（径、長さ、すきま等）によつて、任意に制御が
可能である。さて、主インペラの推力W1は第２
図に示すように一般に上向きに働く。この荷重を
上側のスラスト軸受６ａにより支持するわけであ
るが、このスラスト軸受に加わる荷重を低減する
には、調圧室１３の圧力P3を吐出圧P2より小さく
し吸込圧P1に近づけることによりスラストデイス
ク８には下向きの水力軸スラストW2が発生す
る。この方向は、主インペラ１に発生するスラス
トの方向と反対であるから、スラスト軸受６ａへ
伝わるスラスト荷重が低減させることができる。
ところで、この水力軸スラストW2が過大である
と、上側のスラスト軸受６ａの荷重が０もしくは
過少になつて軸方向の位置決めが不安定になつて
振動が発生したり、また、メカロス低減から本来
ロータの自重程度しか負荷能力のない下側のスラ
スト軸受６ｂへの荷重が過大になり、下側のスラ
スト軸受の損傷をきたす。 As shown in FIG. 2, when the pump is rotating, most of the cooling water pumped up by the hole 8a provided in the thrust disk 8 passes between the pads of the upper thrust bearing 6a and flows to the shaft 7b. It flows out to the outer periphery of the motor chamber B, further flows upward to cool the motor stator 3, flows inside the external heat exchanger 20 shown in FIG. 1, and returns to the lower part of the motor chamber B. In addition, a part of the pumped water flows through the slit 9a formed by the seal ring 9, and further flows through the pressure regulating chamber 13, between the pads of the lower thrust bearing 6b, and the seal ring 12. It flows back to the suction port of the auxiliary impeller, ie, the inlet of the hole 8a, through the narrow gap 12a parallel to the motor axis. The pressure P3 in the pressure regulating chamber 13 is the suction pressure P1
This pressure is between the pressure P2 and the discharge pressure P2 , but this pressure P3 can be controlled arbitrarily by changing the dimensions (diameter, length, clearance, etc.) of the seal rings 9 and 12. . Now, the thrust force W 1 of the main impeller is the second
It generally works upwards as shown in the figure. This load is supported by the upper thrust bearing 6a, but in order to reduce the load applied to this thrust bearing, the pressure P 3 in the pressure regulating chamber 13 is made smaller than the discharge pressure P 2 and closer to the suction pressure P 1 . As a result, a downward hydraulic axis thrust W2 is generated on the thrust disk 8. Since this direction is opposite to the direction of the thrust generated in the main impeller 1, the thrust load transmitted to the thrust bearing 6a can be reduced.
By the way, if this hydraulic shaft thrust W 2 is too large, the load on the upper thrust bearing 6a becomes zero or too small, making axial positioning unstable and causing vibrations, or preventing the mechanical loss from being reduced. The load on the lower thrust bearing 6b, which has a load capacity of only about the rotor's own weight, becomes excessive, causing damage to the lower thrust bearing.
そこで最適のスラスト荷重が加わるように調圧
室１３の圧力P3を最適の圧力に制御できるよう
に、シールリング９，１２を設置したことが、本
発明の特徴であつて、前述したようにシールリン
グ９，１３の形状、寸法により圧力P3を制御でき
る。なお、明らかなように、シールリング９がな
い場合は圧力P3は圧力P2となり、スラスト低減効
果はない。またシールリング１２がない場合は圧
力P3は圧力P1と等しくなり、圧力P3が一意的に決
まり、W2の値を制御できないものである。 Therefore, the feature of the present invention is that the seal rings 9 and 12 are installed so that the pressure P3 in the pressure regulating chamber 13 can be controlled to the optimum pressure so that the optimum thrust load is applied. The pressure P 3 can be controlled by the shapes and dimensions of the seal rings 9 and 13. As is clear, if the seal ring 9 is not provided, the pressure P3 becomes the pressure P2 , and there is no thrust reduction effect. Furthermore, if there is no seal ring 12, the pressure P3 is equal to the pressure P1 , the pressure P3 is uniquely determined, and the value of W2 cannot be controlled.
第３図は本発明の装置別の実施例を示すもので
あつて、第２図の実施例と異なる点は、ポンプ穴
８ａを斜め穴としたことである。これにより、シ
ールリング９の長さを長くすることができ、同一
の流路抵抗を実現させる場合、すきまを増大させ
ることができ、スラストデイスク８とシールリン
グ９，１２の接触がさけられる。 FIG. 3 shows another embodiment of the present invention, which differs from the embodiment shown in FIG. 2 in that the pump hole 8a is an oblique hole. Thereby, the length of the seal ring 9 can be increased, and when the same flow path resistance is to be achieved, the clearance can be increased, and contact between the thrust disk 8 and the seal rings 9, 12 can be avoided.
第４図は本発明の装置のさらに別の実施例を示
すものであつて、スリーブ１４をスラストデイス
ク８の内周側近傍の下端に設けると共にその外側
にモータ軸と平行な細隙部１２ａを形成するシー
ルリング１２をモータ室ケースB1に設けて細隙
部１２ａの流路抵抗を形成したものである。スリ
ーブ１４の端面とモータ室ケースB1との間隙１
５およびシールリング１２の端面とスラストデイ
スク８との間隙１６はスラスト軸受６ａ，６ｂが
摩耗してもこれらの対向する面が接触または衝突
しないような寸法に設定されている。このように
構成したことにより、遠心ポンプ作用によりシー
ルリングからのもれを少なくしたもので、細隙部
１２ａの増大が図れるのでスリーブ１４とシール
リング１２との接触をさけうる。 FIG. 4 shows still another embodiment of the device of the present invention, in which a sleeve 14 is provided at the lower end near the inner circumferential side of the thrust disk 8, and a narrow gap 12a parallel to the motor shaft is provided on the outside thereof. The seal ring 12 to be formed is provided in the motor chamber case B1 to form a flow path resistance of the narrow gap 12a. Gap 1 between the end face of the sleeve 14 and the motor chamber case B 1
A gap 16 between the end surfaces of the seal ring 12 and the thrust disk 8 is set to such a size that even if the thrust bearings 6a and 6b wear, these opposing surfaces do not come into contact or collide. With this configuration, leakage from the seal ring is reduced by the action of the centrifugal pump, and the narrow gap 12a can be increased, so that contact between the sleeve 14 and the seal ring 12 can be avoided.
第５図は本発明の装置の別の一実施例を示すも
ので、スリーブ１４をスラストデイスク８の内周
側近傍の下端に設け、このスリーブ１４の内側お
よび外側にそれぞれシールリング１７，１８を設
けたもので、シール長がさらに長くなり、従つて
細隙部１７ａ，１８ａのすきまを増大でき、スリ
ーブ１４とシールリング１７，１８との接触をさ
けうる。 FIG. 5 shows another embodiment of the device of the present invention, in which a sleeve 14 is provided at the lower end near the inner peripheral side of the thrust disk 8, and seal rings 17 and 18 are provided on the inside and outside of this sleeve 14, respectively. By providing this, the seal length is further increased, the gap between the narrow gaps 17a and 18a can be increased, and contact between the sleeve 14 and the seal rings 17 and 18 can be avoided.
以上述べたように、本発明によれば、従来技術
によるサブマージブルポンプの補助インペラと兼
用のスラストデイスクの内外周面にシールリング
を設けることにより、スラスト軸受に加わる荷重
を低減させて、スラスト軸受の小形化、長寿命化
を図ることができ、大巾に信頼性を向上できる。
また、シールリングを２箇所に設置したので、補
助インペラの揚水の逆流が小さくなり、補助イン
ペラの効率も増大する。さらに本構造では、各シ
ールリングのすきまの増大を図れるので、回転中
ロータとシールリングとの接触を防止できる。
As described above, according to the present invention, seal rings are provided on the inner and outer circumferential surfaces of the thrust disk that also serves as the auxiliary impeller of a submersible pump according to the prior art, thereby reducing the load applied to the thrust bearing. The device can be made smaller, have a longer service life, and greatly improve reliability.
Furthermore, since the seal rings are installed at two locations, the backflow of water pumped by the auxiliary impeller is reduced, and the efficiency of the auxiliary impeller is also increased. Furthermore, with this structure, the clearance between each seal ring can be increased, so that contact between the rotor and the seal rings during rotation can be prevented.
第１図は本発明の装置の一例を備えたサブマー
ジブルポンプの縦断面図、第２図は第１図に示す
本発明の装置を一部拡大して示す縦断面図、第３
図〜第５図はそれぞれ本発明の装置の他の実施例
の一部分を示す縦断面図である。
１…主インペラ、６ａ，６ｂ…スラスト軸受、
８…補助インペラを兼ねるスラストデイスク、
９，１２…シールリング、１３…調圧室、１４…
スリーブ、Ａ…ポンプ室、Ｂ…モータ室。
FIG. 1 is a vertical cross-sectional view of a submersible pump equipped with an example of the device of the present invention, FIG. 2 is a vertical cross-sectional view partially enlarging the device of the present invention shown in FIG. 1, and FIG.
5 to 5 are longitudinal cross-sectional views showing parts of other embodiments of the apparatus of the present invention. 1... Main impeller, 6a, 6b... Thrust bearing,
8...Thrust disk that also serves as an auxiliary impeller,
9, 12... Seal ring, 13... Pressure regulation chamber, 14...
Sleeve, A...pump room, B...motor room.
Claims (1)
タ部を設け、このモータの上向き側のシヤフトに
主インペラ部を設け、モータの下向き側のシヤフ
トにモータ冷却水循環のための複数個のポンプ用
穴を有する補助インペラを兼ねるスラストデイス
クを設け、このスラストデイスクの下面，上面に
それぞれ対向するスラスト軸受をモータ室ケース
に設けたサブマージブルポンプにおいて、補助イ
ンペラの吐出水が吸込側に逆流する時の流路とな
るスラストデイスクの外周面との間に細隙部を形
成するようにモータ室ケースに第１のシールリン
グを設け、スラストデイスクの内周面近傍にモー
タ軸線と平行な細隙部を形成する第２のシールリ
ングを設け、前記スラストデイスクの下面側およ
び上面側にそれぞれ調圧室を形成したことを特徴
とするサブマージブルポンプの軸スラスト低減装
置。 ２ スラストデイスクの内周面側の第２のシール
リング部は、スラストデイスクの内周面との間に
モータ軸線と平行な細隙部を形成するように、モ
ータ室ケースに設けたシールリングを備えたこと
を特徴とする特許請求の範囲第１項記載のサブマ
ージブルポンプの軸スラスト荷重低減装置。 ３ スラストデイスクの内周面側の第２のシール
リング部は、モータ室ケースに設けたシールリン
グと、これに対向するようにスラストデイスクに
設けたスリーブとによつて少なくとも１つのモー
タ軸線と平行な細隙部を形成したことを特徴とす
る特許請求の範囲第１項記載のサブマージブルポ
ンプの軸スラスト荷重低減装置。[Claims] 1. A submersible motor section is provided in the motor chamber casing, a main impeller section is provided on the upward shaft of the motor, and a plurality of pumps for circulating motor cooling water are provided on the downward shaft of the motor. In a submersible pump, in which a thrust disk that also serves as an auxiliary impeller and a thrust disk that also serves as an auxiliary impeller is provided, and a motor chamber case is provided with thrust bearings that face the lower and upper surfaces of the thrust disk, the water discharged from the auxiliary impeller flows back to the suction side. A first seal ring is provided in the motor chamber case so as to form a narrow gap between the outer circumferential surface of the thrust disk and the outer circumferential surface of the thrust disk, which forms a flow path, and a narrow gap parallel to the motor axis is provided near the inner circumferential surface of the thrust disk. An axial thrust reduction device for a submersible pump, characterized in that a second seal ring is provided to form a pressure regulating chamber on a lower surface side and an upper surface side of the thrust disk. 2 The second seal ring part on the inner peripheral surface side of the thrust disk is connected to the seal ring provided in the motor chamber case so as to form a narrow gap parallel to the motor axis between the second seal ring part and the inner peripheral surface of the thrust disk. An axial thrust load reduction device for a submersible pump according to claim 1, further comprising: 3 The second seal ring portion on the inner peripheral surface side of the thrust disk is parallel to at least one motor axis by a seal ring provided on the motor chamber case and a sleeve provided on the thrust disk so as to be opposed to the seal ring. The axial thrust load reduction device for a submersible pump according to claim 1, characterized in that a narrow gap portion is formed.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58034508A JPS59160093A (en) | 1983-03-04 | 1983-03-04 | Shaft thrust load reducing device for submergible pump |
| AT84101200T ATE27341T1 (en) | 1983-03-04 | 1984-02-06 | AXIAL THRESHOLD COMPENSATION DEVICE FOR PUMPS. |
| EP84101200A EP0121053B1 (en) | 1983-03-04 | 1984-02-06 | Axial thrust reducing device for pumps |
| DE8484101200T DE3463824D1 (en) | 1983-03-04 | 1984-02-06 | Axial thrust reducing device for pumps |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58034508A JPS59160093A (en) | 1983-03-04 | 1983-03-04 | Shaft thrust load reducing device for submergible pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59160093A JPS59160093A (en) | 1984-09-10 |
| JPS626119B2 true JPS626119B2 (en) | 1987-02-09 |
Family
ID=12416197
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58034508A Granted JPS59160093A (en) | 1983-03-04 | 1983-03-04 | Shaft thrust load reducing device for submergible pump |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0121053B1 (en) |
| JP (1) | JPS59160093A (en) |
| AT (1) | ATE27341T1 (en) |
| DE (1) | DE3463824D1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6389309U (en) * | 1986-11-29 | 1988-06-10 | ||
| JP2005105904A (en) * | 2003-09-30 | 2005-04-21 | Mitsubishi Heavy Ind Ltd | Bearing device and compressor using the same |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH088319Y2 (en) * | 1988-07-18 | 1996-03-06 | 株式会社荏原製作所 | Centrifugal pump balance disk type axial thrust balancer |
| DE3929750A1 (en) * | 1989-03-04 | 1990-09-06 | Klein Schanzlin & Becker Ag | AXIAL DISCHARGE RELIEF DEVICE |
| US5340272A (en) * | 1992-08-19 | 1994-08-23 | Bw/Ip International, Inc. | Multi-stage centrifugal pump incorporating a sealed thrust bearing |
| FI940630A (en) * | 1994-02-11 | 1995-08-12 | Ahlstroem Oy | centrifugal |
| US6071091A (en) * | 1998-02-12 | 2000-06-06 | Lemieux; Guy B. | Integral motor/generator and pump/turbine with hydrostatic bearings |
| US7612143B2 (en) | 1999-08-04 | 2009-11-03 | Hybrid Plastics, Inc. | Metallized nanostructured chemicals alloyed into polymers |
| US7820761B2 (en) | 1999-08-04 | 2010-10-26 | Hybrid Plastics, Inc. | Metallized nanostructured chemicals as cure promoters |
| JP4347173B2 (en) | 2004-09-15 | 2009-10-21 | 三菱重工業株式会社 | Canned motor pump |
| DE102006011613A1 (en) * | 2006-03-14 | 2007-09-20 | Ksb Aktiengesellschaft | Centrifugal pump with axial thrust balancing device |
| CN103195745B (en) * | 2013-04-24 | 2015-08-19 | 东风汽车公司 | A kind of cooling waterpump of new-energy automobile |
| CN110454509A (en) * | 2019-08-30 | 2019-11-15 | 福建福清核电有限公司 | A kind of pumping over profile shaft holds thrust disc |
| CN111998005B (en) * | 2020-08-25 | 2022-02-18 | 南京工程学院 | A cooling flushing structure for water lubricated thrust bearing |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56132497A (en) * | 1980-02-18 | 1981-10-16 | Hitachi Ltd | Axial thrust equalizer |
| JPS5788288A (en) * | 1980-11-21 | 1982-06-02 | Hitachi Ltd | Internal pump |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB518428A (en) * | 1937-10-06 | 1940-02-27 | Sulzer Ag | Improvements in or relating to rotary immersion pumps |
| DE922807C (en) * | 1945-03-06 | 1955-01-24 | Aeg | Device to compensate for the axial thrust of multistage centrifugal pumps |
| FR1276208A (en) * | 1960-12-14 | 1961-11-17 | Pump without packing or stuffing box with passage of the liquid through an internal section of the inlet bearing | |
| US3420184A (en) * | 1967-05-17 | 1969-01-07 | Julius L Englesberg | Pump employing magnetic drive |
| GB1351826A (en) * | 1971-11-29 | 1974-05-01 | Carter Co J C | Lubricating cooling and balancing of pump and motor units |
-
1983
- 1983-03-04 JP JP58034508A patent/JPS59160093A/en active Granted
-
1984
- 1984-02-06 EP EP84101200A patent/EP0121053B1/en not_active Expired
- 1984-02-06 AT AT84101200T patent/ATE27341T1/en not_active IP Right Cessation
- 1984-02-06 DE DE8484101200T patent/DE3463824D1/en not_active Expired
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56132497A (en) * | 1980-02-18 | 1981-10-16 | Hitachi Ltd | Axial thrust equalizer |
| JPS5788288A (en) * | 1980-11-21 | 1982-06-02 | Hitachi Ltd | Internal pump |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6389309U (en) * | 1986-11-29 | 1988-06-10 | ||
| JP2005105904A (en) * | 2003-09-30 | 2005-04-21 | Mitsubishi Heavy Ind Ltd | Bearing device and compressor using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0121053B1 (en) | 1987-05-20 |
| EP0121053A1 (en) | 1984-10-10 |
| ATE27341T1 (en) | 1987-06-15 |
| DE3463824D1 (en) | 1987-06-25 |
| JPS59160093A (en) | 1984-09-10 |
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