JPH0712084A - Rear thrust bearing structure in magnet pump - Google Patents

Rear thrust bearing structure in magnet pump

Info

Publication number
JPH0712084A
JPH0712084A JP10631394A JP10631394A JPH0712084A JP H0712084 A JPH0712084 A JP H0712084A JP 10631394 A JP10631394 A JP 10631394A JP 10631394 A JP10631394 A JP 10631394A JP H0712084 A JPH0712084 A JP H0712084A
Authority
JP
Japan
Prior art keywords
thrust bearing
impeller
casing
pump
spindle
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.)
Granted
Application number
JP10631394A
Other languages
Japanese (ja)
Other versions
JP2632132B2 (en
Inventor
Kazuo Okada
和雄 岡田
Toshihiko Kondo
利彦 近藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Iwaki Co Ltd
Original Assignee
Iwaki Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Iwaki Co Ltd filed Critical Iwaki Co Ltd
Priority to JP6106313A priority Critical patent/JP2632132B2/en
Publication of JPH0712084A publication Critical patent/JPH0712084A/en
Application granted granted Critical
Publication of JP2632132B2 publication Critical patent/JP2632132B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

PURPOSE:To improve durability of a magnet pump, and reduce cost by radiating effectively sliding motional frictional heat generated in a rear thrust bearing part at abnormal operation time such as idle running of a pump, and preventing adverse influence upon surrounding members while restraining a temperature rise in a slidingly movable part. CONSTITUTION:A rear thrust bearing 41 is arranged opposite movably slidingly on a shaft end surface 42 of a spindle 34 being in a cantilever condition on the rear side in the vicinity of an impeller 26. Sliding motional frictional heat generated here is radiated excellently by being influenced by cooling operation of agitation in a casing of the impeller 26 and by a heat radiating effect by a circulating flow, and a temperature rise in a slidingly movable part is restrained, and adverse influence upon surrounding members by the heat can be prevented.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【産業上の利用分野】本発明は、対向配置した駆動マグ
ネットと従動マグネットとのマグネットカップリングに
よりポンプ室内のインペラを回転駆動してポンプ動作を
遂行するマグネットポンプに係り、インペラを含む従動
回転体部分に係るスラストを支えるフロント側及びリア
側のスラスト軸受の内、特にリアスラスト軸受の改良に
関するものである。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a magnet pump for rotationally driving an impeller in a pump chamber by a magnetic coupling of a driving magnet and a driven magnet which face each other, and a driven rotating body including the impeller. The present invention relates to an improvement in a front thrust bearing and a rear thrust bearing, which support a thrust related to a part, particularly, a rear thrust bearing.

【0002】[0002]

【従来の技術】この種のマグネットポンプは、例えば図
3に示す構造のものが知られている。すなわち、図3に
示す公知のマグネットポンプ1は、内部にポンプ室2を
区画するとともに軸線X−Xで示す軸方向に沿う吸込口
3と周方向に沿う吐出口4とを備えたフロントケーシン
グ5と、該ポンプ室2内に回転自在に配置されフロント
側(図において右側)が吸込口3に対向するインペラ6
と、該フロントケーシング5と共働してポンプ室2を流
体密に囲う有底筒状のリアケーシングと、該リアケーシ
ング7の外に配置されるとともに駆動マグネット8を環
状に備え、ポンプ本体9内に配置された駆動モータ(図
示せず)より回転駆動力を得る駆動回転体10と、前記
リアケーシング7内に配置されるとともに該リアケーシ
ングを介して前記駆動マグネット8とマグネットカップ
リングをなすように対向する従動マグネット11を環状
に備え前記インペラと一体回転可能な従動回転体12
と、リアケーシング7の底部7aに該底部より一体に突
設したボス13を介して基端部が固定されるとともに片
持ばりの態様で軸方向に突出し該突出部14a上に前記
従動回転体12をスリーブ状軸受15を介して回転自在
に支持するスピンドル14とを備えてなる構成となって
いる。
2. Description of the Related Art A magnet pump of this type is known, for example, having a structure shown in FIG. That is, the known magnet pump 1 shown in FIG. 3 defines a pump chamber 2 inside and includes a front casing 5 having a suction port 3 along the axial direction indicated by the axis XX and a discharge port 4 along the circumferential direction. And an impeller 6 that is rotatably arranged in the pump chamber 2 and has a front side (right side in the drawing) facing the suction port 3.
And a bottomed cylindrical rear casing that cooperates with the front casing 5 to fluid-tightly surround the pump chamber 2, and a drive magnet 8 that is arranged outside the rear casing 7 and has a ring shape. A drive rotor 10 that receives a rotational drive force from a drive motor (not shown) disposed therein, and a drive coupling that is disposed in the rear casing 7 and forms a magnetic coupling with the drive magnet 8 via the rear casing. A driven rotary body 12 which is provided with a driven magnet 11 opposed to each other like a ring and is rotatable integrally with the impeller.
A base end portion of the rear casing 7 is fixed to the bottom portion 7a of the rear casing 7 via a boss 13 that is integrally projected from the bottom portion, and the base portion is axially protruded in a cantilevered manner and the driven rotor is provided on the protrusion 14a. And a spindle 14 that rotatably supports 12 via a sleeve bearing 15.

【0003】上記公知のマグネットポンプ1において、
駆動回転体10の回転に追従して従動回転体12が回転
駆動され、これによってインペラ6が回転してポンプ給
送流体が吸込口3より矢印で示すようにポンプ室2内に
流入し、吐出口4より矢印で示すように送り出される。
このポンプ動作中、ポンプ室2内の流体の一部は、循環
流としてリアケーシング7の内奥部にも回り込み、該従
動回転体12と一体に設けられたスリーブ状軸受15と
スピンドル14との間の摺動部15aに破線の矢印で示
すように該軸受15の後端側より流入して前端側へ抜け
てインペラ6の中央部に設けた連通孔16を通って循環
し、摺動部15aの摩擦による発熱を抑える冷却作用な
らびに潤滑作用を果すようになっている。該摺動部15
aには螺旋状あるいはスプライン状の流通溝が形成され
ている。
In the above-mentioned known magnet pump 1,
The driven rotary body 12 is driven to rotate following the rotation of the drive rotary body 10, whereby the impeller 6 rotates and the pump feed fluid flows from the suction port 3 into the pump chamber 2 as shown by the arrow, and is discharged. It is sent out from the outlet 4 as shown by the arrow.
During this pump operation, a part of the fluid in the pump chamber 2 also circulates as a circulating flow into the inner rear part of the rear casing 7, and the sleeve-shaped bearing 15 and the spindle 14 which are integrally provided with the driven rotating body 12 As shown by the broken line arrow in the sliding portion 15a between them, the bearing 15 flows in from the rear end side, escapes to the front end side and circulates through the communication hole 16 provided in the central portion of the impeller 6, and the sliding portion 15a has a cooling effect and a lubricating effect that suppress heat generation due to friction. The sliding portion 15
A spiral or splined flow groove is formed in a.

【0004】ポンプ作動中、インペラ6の吸込口3に対
向したフロント側が負圧になる関係上、インペラ6とと
もに従動回転体12の従動回転部分は、通常吸込口3の
方向、すなわちフロント方向にスラストを受けるため、
これを支えるリング状フロントスラスト軸受17がフロ
ントケーシング5に設けられ、該フロントスラスト軸受
17に対しインペラ6側に設けたマウスリング18が摺
接する構成となっている。又、該従動回転部分には吸込
口3と反対の方向、すなわちリア方向にスラストが作用
することがある。それは、ポンプ空運転やエア巻込み等
による異常運転が発生した際に従動回転部分がスラスト
方向に振動しながら回転するためである。従って、リア
方向のスラストを支えるリアスラスト軸受19がスピン
ドル14の回りにおいてボス13上に設けられ、リア方
向のスラスト発生時に該リアスラスト軸受18に対して
スリーブ状軸受15の後端縁を摺接させる構成となって
いる。
Since the front side of the impeller 6 facing the suction port 3 has a negative pressure during operation of the pump, the driven rotating portion of the driven rotor 12 together with the impeller 6 normally thrusts in the direction of the suction port 3, that is, in the front direction. To receive
A ring-shaped front thrust bearing 17 that supports this is provided in the front casing 5, and a mouth ring 18 provided on the impeller 6 side is in sliding contact with the front thrust bearing 17. Further, thrust may act on the driven rotating portion in the direction opposite to the suction port 3, that is, in the rear direction. This is because the driven rotating portion rotates while vibrating in the thrust direction when an abnormal operation such as a pump idle operation or air entrainment occurs. Therefore, a rear thrust bearing 19 that supports the thrust in the rear direction is provided on the boss 13 around the spindle 14, and the rear end edge of the sleeve-shaped bearing 15 is slidably contacted with the rear thrust bearing 18 when the thrust in the rear direction occurs. It is configured to let.

【0005】[0005]

【発明が解決しようとする課題】上述したようにポンプ
の空運転やエア巻込み等の異常運転発生時にリアスラス
ト軸受に対してスリーブ状軸受の後端縁が摺接する状態
となるが、この摺接部分で発生する摩擦熱が問題となる
のであった。すなわち、リアスラスト軸受はフロントス
ラスト軸受と異なりリアケーシングの内奥部に設けられ
ているため、摩擦熱の放熱が悪く、昇温した場合に軸受
部分の焼き付きを生じさせ、特にリアケーシング等の周
囲部材に合成樹脂の成型品を用いたものでは溶融による
部材の破損を招くといった熱による悪影響が問題であっ
た。又、スリーブ状軸受の後端縁はリアスラスト軸受と
摺接した状態となると、スピンドルとの間の摺動部に入
る循環流の発熱及び循環不良が発生し、一層事態を悪化
させる問題があった。
As described above, the rear end edge of the sleeve-shaped bearing is in sliding contact with the rear thrust bearing when an abnormal operation such as an idle operation or air entrainment of the pump occurs. The frictional heat generated in the contact area was a problem. That is, unlike the front thrust bearing, the rear thrust bearing is provided in the inner rear part of the rear casing, so that the heat dissipation of frictional heat is bad and seizure of the bearing part occurs when the temperature rises, especially around the rear casing. In the case of using a synthetic resin molded product as a member, there is a problem of adverse effects due to heat such as damage to the member due to melting. Further, when the rear end edge of the sleeve-shaped bearing is in sliding contact with the rear thrust bearing, there is a problem that heat generation and poor circulation of the circulating flow entering the sliding portion between the spindle-shaped bearing and the spindle further aggravate the situation. It was

【0006】上記問題改善のために、リアスラスト軸受
等の摺動部周囲に耐熱材を採用し断熱を図る構造も提案
されている。しかし、この場合には、断熱構造とするた
めのコストアップが避けられず、又断熱材により熱が周
囲に分散しないために、短時間の空運転であっても摺動
部が急激に昇温し、直後の呼水により、いわゆるヒート
ショックを発生し易いといった問題があった。
In order to solve the above problems, a structure has been proposed in which a heat-resistant material is used around the sliding portion such as a rear thrust bearing to provide heat insulation. However, in this case, the cost increase due to the heat insulating structure is unavoidable, and since the heat is not dispersed to the surroundings by the heat insulating material, the temperature of the sliding part rapidly rises even in a short idle operation. However, there is a problem that so-called heat shock is likely to occur due to the immediate priming.

【0007】従って、本発明は上記従来の諸問題に鑑み
なされたもので、その目的はポンプの空運転等の異常運
転の発生した場合にも、摺動部の摩擦熱の発生を極力抑
制でき、摺動部周囲を断熱構造とする必要がなく、リア
ケーシング等の周囲部材に樹脂成型品を心配なく用い
得、ポンプ全体の耐久性の向上ならびにコストダウンを
図り得るマグネットポンプにおけるリアスラスト軸受の
構造を提供することにある。
Therefore, the present invention has been made in view of the above-mentioned problems of the prior art, and an object thereof is to suppress the generation of frictional heat of a sliding portion as much as possible even when an abnormal operation such as an idle operation of a pump occurs. , It is not necessary to have a heat insulating structure around the sliding portion, and resin molded products can be used for the surrounding members such as the rear casing without worrying about the durability of the pump and the rear thrust bearing in the magnet pump. To provide the structure.

【0008】[0008]

【課題を解決するための手段】上記本発明の目的達成の
ために、本発明においては、内部にポンプ室を区画する
とともに軸方向に沿う吸込口と周方向に沿う吐出口とを
備えたフロントケーシングと、該ポンプ室内に回転自在
に配置されフロント側が前記吸込口に対向するインペラ
と、該フロントケーシングと共働してポンプ室を流体密
に囲う有底筒状のリアケーシングと、該リアケーシング
外に配置されるとともに駆動マグネットを有する駆動回
転体と、前記リアケーシング内に配置されるとともに該
リアケーシングを介して前記駆動マグネットとマグネッ
トカップリングをなすように対向する従動マグネットを
有し前記インペラと一体回転可能な従動回転体と、前記
リアケーシングの底部に固定されるとともに片持ばりの
態様で軸方向に突出し該突出部に前記従動回転体を回転
自在に支持するスピンドルとを備えてなるマグネットポ
ンプを前提として、前記スピンドルの軸端面に対向して
軸方向に沿ってリアスラスト軸受部材を該スピンドルの
軸端面に摺接可能に配置し、該リアスラスト軸受部材を
支持する支持部を前記インペラのリア側又は従動回転体
のフロント側に設けた構成のリアスラスト軸受の構造を
提案するものである。
In order to achieve the above-mentioned object of the present invention, in the present invention, a pump chamber is defined inside, and a front is provided with a suction port along the axial direction and a discharge port along the circumferential direction. A casing, an impeller rotatably disposed in the pump chamber and having a front side facing the suction port, a bottomed cylindrical rear casing that cooperates with the front casing to fluid-tightly surround the pump chamber, and the rear casing. The impeller having a drive rotor disposed outside and having a drive magnet, and a driven magnet disposed inside the rear casing and facing the drive magnet via the rear casing so as to form a magnetic coupling. And a driven rotary body that is rotatable integrally with the rear casing, and is fixed to the bottom portion of the rear casing and projects in the axial direction in a cantilever manner. On the premise of a magnet pump having a spindle for rotatably supporting the driven rotating body on the protruding portion, a rear thrust bearing member is provided axially opposite the shaft end surface of the spindle along the axial direction. A structure of a rear thrust bearing is provided, which is arranged so as to be slidably contactable with an end face and has a support portion for supporting the rear thrust bearing member provided on the rear side of the impeller or the front side of the driven rotating body.

【0009】更に、本発明によれば、相互に摺接可能な
前記スピンドルの軸端面とリアスラスト軸受部材のいず
れか一方の摺接部を球面状に形成してなる構成のリアス
ラスト軸受の構造も提案するものである。
Further, according to the present invention, the structure of the rear thrust bearing having a configuration in which one of the shaft end surface of the spindle and the rear thrust bearing member, which are capable of sliding contact with each other, is formed into a spherical shape. Is also proposed.

【0010】[0010]

【作用】上記本発明によるリアスラスト軸受によれば、
リアスラスト軸受部材がスピンドルの軸端面に対して摺
接可能に配置され、該リアスラスト軸受部材を支持する
支持部をインペラの背面側、すなわちリア側又は従動回
転体のフロント側に設けられる。従って、ポンプの異常
運転等により従動回転体とインペラの従動回転部分がス
ラスト方向に揺動し、リア方向に移動した際には、該リ
アスラスト軸受部材が固定状態にあるスピンドルの軸端
面に接触し摺接する状態となる。該リアスラスト軸受部
材は、リアケーシングの内奥部とは異なりインペラの近
傍において背後のリア側に配置されているため、熱の分
散がし易く、又、インペラのケーシング内攪拌による冷
却効果を受け易いため、該リアスラスト軸受部材とスピ
ンドルの軸端面との摺動時の発生熱が良好に放熱され、
該スラスト軸受部材を含む摺動部分の昇温が抑えられ
る。又、スピンドルとスリーブ状軸受との間を通る循環
流の流路は遮断されることがないので、該スピンドルま
わりの良好な冷却作用ならびに潤滑作用が維持されると
ともに該循環流がリアスラスト軸受部分にも及ぼされ、
一層良好な放熱がなされる。
According to the rear thrust bearing of the present invention,
A rear thrust bearing member is arranged so as to be slidably contactable with the shaft end surface of the spindle, and a support portion for supporting the rear thrust bearing member is provided on the back side of the impeller, that is, on the rear side or the front side of the driven rotary body. Therefore, when the driven rotor and the driven rotating portion of the impeller oscillate in the thrust direction due to abnormal operation of the pump or the like and move in the rear direction, the rear thrust bearing member comes into contact with the shaft end surface of the spindle in the fixed state. It will be in sliding contact. The rear thrust bearing member is arranged on the rear side behind the impeller in the vicinity of the inner part of the rear casing unlike the rear inner part of the rear casing, so that heat is easily dissipated and the rear thrust bearing member receives a cooling effect by stirring in the casing of the impeller. Since it is easy, the heat generated during sliding between the rear thrust bearing member and the shaft end surface of the spindle is radiated well,
The temperature rise of the sliding portion including the thrust bearing member can be suppressed. Further, since the flow path of the circulation flow passing between the spindle and the sleeve-shaped bearing is not blocked, good cooling action and lubrication action around the spindle are maintained, and the circulation flow becomes the rear thrust bearing portion. Is also affected,
Better heat dissipation is achieved.

【0011】更に、スピンドルの軸端面とリアスラスト
軸受部材のいずれか一方の摺接部を球面状とする構成で
は、摺接面積がわずかとなり、その発熱を非常に小さく
抑えることが可能である。
Further, in the structure in which one of the shaft end surface of the spindle and the sliding contact portion of the rear thrust bearing member is spherical, the sliding contact area becomes small, and the heat generation can be suppressed to a very small level.

【0012】[0012]

【実施例】以下、図1及び図2を参照して本発明に係る
リアスラスト軸受の構造を具体化したマグネットポンプ
の実施例を以下説明する。図1に示すマグネットポンプ
20において、21は内部に駆動モータ(図示せず)を
内蔵したポンプ本体、22は該ポンプ本体に取付けられ
内部にポンプ室23を区画するとともに軸線X−Xで示
す軸方向に沿う吸込口24と周方向に沿う吐出口25と
を備えたフロントケーシング、26は該ポンプ室23内
に回転自在に配置されフロント側(図において右側)が
吸込口24に対向するインペラ、27はフロントケーシ
ング22に設けられインペラ26上に設けられたマウス
リング28を摺接させるリング状のフロントスラスト軸
受、29はポンプ本体21に組み付けられ該フロントケ
ーシング22と共働してポンプ室23を流体密に囲う有
底筒状のリアケーシング、30はリアケーシング29の
外に配置されるとともに駆動マグネット31を環状に備
えポンプ本体21内の駆動モータより回転駆動力を得る
駆動回転体、32はリアケーシング29内に配置される
とともに該リアケーシングを介して駆動マグネット31
とマグネットカップリングをなすように対向する従動マ
グネット33を環状に備え前記インペラ26を一体回転
状態に組付固定した従動回転体、34はリアケーシング
29の底部29aに該底部より一体に突設したボス35
によって固定されるとともに片持ばりの態様で軸方向に
突出したスピンドルである。
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a magnet pump embodying the structure of a rear thrust bearing according to the present invention will be described below with reference to FIGS. 1 and 2. In the magnet pump 20 shown in FIG. 1, 21 is a pump main body having a drive motor (not shown) built therein, 22 is attached to the pump main body, defines a pump chamber 23 inside, and is an axis indicated by an axis XX. A front casing having a suction port 24 along the direction and a discharge port 25 along the circumferential direction, an impeller 26 rotatably arranged in the pump chamber 23, and the front side (right side in the drawing) faces the suction port 24, Reference numeral 27 denotes a ring-shaped front thrust bearing provided on the front casing 22 for slidingly contacting a mouth ring 28 provided on the impeller 26. Reference numeral 29 is attached to the pump body 21 and cooperates with the front casing 22 to move the pump chamber 23. A bottomed cylindrical rear casing 30 that is fluid-tightly enclosed is disposed outside the rear casing 29, and a drive magnet 31 is also provided. Drive rotor to obtain a rotational driving force from the driving motor in the pump body 21 with the annular, 32 drive magnet 31 via the rear casing while being located within the rear casing 29
And a driven rotor 33 having a ring-shaped driven magnet 33 facing each other so as to form a magnetic coupling with the impeller 26 assembled and fixed in an integrally rotating state. 34 is integrally provided on a bottom portion 29a of the rear casing 29 so as to project from the bottom portion. Boss 35
Is a spindle that is fixed by and axially protrudes in the form of a cantilever.

【0013】スピンドル34の突出部34a上には、ス
リーブ状軸受36を介して従動回転体32が回転自在に
支持されている。該軸受36は従動回転体32に固着さ
れているとともにスピンドル34との摺動部36aには
螺旋状ないしスプライン状の流通溝が形成されており、
ポンプ作動中、ポンプ室23に流入したポンプ給送流体
の一部は循環流としてリアケーシング29の内奥部に回
り込むとともに破線の矢印で示すように該軸受36の後
端縁より該摺動部36aに入り冷却作用ならびに潤滑作
用を果す。
A driven rotating body 32 is rotatably supported on the protruding portion 34a of the spindle 34 via a sleeve-shaped bearing 36. The bearing 36 is fixed to the driven rotating body 32, and a spiral or splined flow groove is formed in the sliding portion 36a with the spindle 34.
During the operation of the pump, a part of the pump feed fluid flowing into the pump chamber 23 circulates as a circulating flow into the inner portion of the rear casing 29, and as shown by a broken arrow, from the rear end edge of the bearing 36 to the sliding portion. It enters into 36a and performs a cooling action and a lubricating action.

【0014】ポンプ作動開始において、まず駆動モータ
の通電により駆動回転体30が回転し、これに追従して
従動回転体32がスピンドル34上でインペラ26と一
体に回転する。これによってポンプ給送流体が矢印で示
すように吸込口24よりポンプ室23内に流入するとと
もに吐出口25を介して図示しない供給部位へと送り出
される。
At the start of pump operation, the drive rotor 30 is first rotated by energization of the drive motor, and the driven rotor 32 is rotated integrally with the impeller 26 on the spindle 34 following this. As a result, the pump feed fluid flows from the suction port 24 into the pump chamber 23 as shown by the arrow, and is also delivered to the supply site (not shown) via the discharge port 25.

【0015】以上説明したマグネットポンプの構成部分
は、図3で説明した従来構造のものと同様である。な
お、各部材の使用材質としては、インペラ26,リアケ
ーシング29及び従動回転体32は合成樹脂の成型品で
製作される。又、スリーブ状軸受36,フロントスラス
ト軸受27,マウスリング28及びスピンドル35は耐
食性、硬度等に優れたセラミック材料により製作される
のが望ましい。
The components of the magnet pump described above are the same as those of the conventional structure described in FIG. As a material used for each member, the impeller 26, the rear casing 29, and the driven rotary body 32 are manufactured by molding synthetic resin. The sleeve bearing 36, the front thrust bearing 27, the mouth ring 28, and the spindle 35 are preferably made of a ceramic material having excellent corrosion resistance and hardness.

【0016】図1に示すマグネットポンプの実施例につ
いて本発明の特徴とするリアスラスト軸受の構造部分に
つき以下説明する。すなわち、インペラ26が吸込口2
4に対向する前面側ないしフロント側とは反対の背面側
ないしリア側において該インペラ26の背面中央部にボ
ス状の支持部40を一体に設け、ここにリアスラスト軸
受部材41を取付けて軸線X−Xに沿って突出するよう
に支持させ、該支持部40より露出したリアスラスト軸
受部材41の摺接部41aを図示のように先細りの形状
として、その先端部を球面状に形成し、これをスピンド
ル34の平坦な軸端面42に対向させる構成である。
又、ポンプ給送流体を循環させる連通孔43は、インペ
ラ26の中央部にリアスラスト軸受部材41を配置する
関係上、中央部を外れた両側に貫通形成した構成であ
る。
With respect to the embodiment of the magnet pump shown in FIG. 1, the structural portion of the rear thrust bearing which is a feature of the present invention will be described below. That is, the impeller 26 has the suction port 2
4, a boss-shaped support portion 40 is integrally provided at the center of the back surface of the impeller 26 on the front surface side or the back surface side or the rear side opposite to the front side, and the rear thrust bearing member 41 is attached thereto to attach the axis line X. The rear contact portion 41a of the rear thrust bearing member 41 exposed from the supporting portion 40 is made to have a tapered shape as shown in the drawing, and its tip is formed into a spherical shape. Is opposed to the flat shaft end surface 42 of the spindle 34.
Further, the communication hole 43 for circulating the pumping fluid is formed so as to penetrate through the both sides outside the central portion because the rear thrust bearing member 41 is arranged in the central portion of the impeller 26.

【0017】上記構成において、ポンプの定常運転の間
は、従動回転体32はインペラ26とともにフロント方
向のスラストを受けるためにフロントスラスト軸受27
にマウスリング28が接触して摺動回転を行なう。この
間、リアスラスト軸受部材41はスピンドルの軸端面4
2とは非接触状態にあるが、ポンプの空運転あるいはエ
ア巻き込み等によって従動回転部分は軸方向に振動を生
じリア方向のスラストを受けた場合には、該リアスラス
ト軸受部材41の摺動部41aがスピンドルの軸端面4
2に接触し、これによってリア方向のスラストが受け止
められる。この接触状態で従動回転部分が回転を継続す
ることにより摺動部41aで摩擦熱が発生するが、摩擦
熱の発生部位が従来構造のようなリアケーシングの内奥
部でなくインペラ26の近傍においてその直後のリア側
にあるため、インペラ26のケーシング内攪拌による冷
却効果を受け易く、該摩擦熱も良好に放熱され、摺動部
周囲の昇温が抑制される。
In the above structure, the driven rotor 32 receives the thrust in the front direction together with the impeller 26 during the steady operation of the pump.
The mouth ring 28 comes into contact with and slides and rotates. During this time, the rear thrust bearing member 41 is fixed to the shaft end surface 4 of the spindle.
Although not in contact with 2, the sliding portion of the rear thrust bearing member 41 when the driven rotating portion vibrates in the axial direction and receives rearward thrust due to idle operation of the pump, air entrainment, or the like. 41a is the shaft end surface 4 of the spindle
2, and the thrust in the rear direction is received. Friction heat is generated in the sliding portion 41a by continuing rotation of the driven rotating portion in this contact state. However, the friction heat is generated in the vicinity of the impeller 26, not in the inner portion of the rear casing as in the conventional structure. Since it is located on the rear side immediately after that, the cooling effect due to stirring in the casing of the impeller 26 is easily received, the frictional heat is radiated well, and the temperature rise around the sliding portion is suppressed.

【0018】又、リアスラスト軸受部材41の摺動部4
1aを球面形状とすることによりスピンドルの軸端面4
2との摺接面積がわずかとなり、その部位における発熱
を一層抑制できる。
Further, the sliding portion 4 of the rear thrust bearing member 41
By making 1a spherical, the shaft end surface 4 of the spindle
The sliding contact area with 2 becomes small, and heat generation at that portion can be further suppressed.

【0019】更に、スリーブ状軸受36の後端縁とボス
35との間には従来構造のようなリアスラスト軸受が設
けられず、リアスラスト軸受部材41がスピンドルの軸
端面42に接触した状態にあっても常にこの間隙が維持
されるため、破線の矢印で示すように、リアケーシング
29の内奥部に回り込んだ流体は、循環流として該軸受
36の後端縁より摺動部36a中を流れ前端縁より出て
インペラ26に形成した連通孔43を通して循環する。
従って、スリーブ状軸受36とスピンドル34との間の
冷却作用ならびに潤滑作用も常に良好な状態に保たれ、
焼き付きや部品破損等の恐れも解消される。又、該循環
流が常にリアスラスト軸受部材41の周囲に及ぼされる
ため、これにより一層、放熱が促進される。
Further, a rear thrust bearing as in the conventional structure is not provided between the rear end edge of the sleeve-like bearing 36 and the boss 35, and the rear thrust bearing member 41 is in contact with the shaft end surface 42 of the spindle. Since this gap is always maintained even if there is, the fluid that has flowed into the inner rear portion of the rear casing 29 is circulated as a circulating flow from the rear end edge of the bearing 36 into the sliding portion 36a. Circulates through the communication hole 43 formed in the impeller 26 from the front edge of the flow.
Therefore, the cooling action and the lubricating action between the sleeve-shaped bearing 36 and the spindle 34 are always kept in a good state,
It also eliminates the risk of seizure or damage to parts. Further, since the circulating flow always extends around the rear thrust bearing member 41, heat dissipation is further promoted.

【0020】図2には図1の実施例で示したリアスラス
ト軸受の変形構造を示してある。これを図1と対応する
部分に同一の参照番号を伏して説明すると、この変形構
造では、リアスラスト軸受部材41を支持する支持部を
インペラ26上に設ける構成に代えて、従動回転体32
の一部をなすとともにフロント側を構成する中間部材4
4上に設ける構成としたものである。すなわち、該中間
部材44を有底筒状に形成してスリーブ状軸受36の外
周部に固定し、その底部44aをスピンドル35の軸端
面42とインペラ26のリア側との間に位置させ、この
底部44aを支持部として、ここにリアスラスト軸受部
材41を取付固定させたものである。
FIG. 2 shows a modified structure of the rear thrust bearing shown in the embodiment of FIG. This will be described by giving the same reference numerals to the parts corresponding to those in FIG. 1. In this modified structure, instead of the structure in which the support part for supporting the rear thrust bearing member 41 is provided on the impeller 26, the driven rotary body 32 is replaced.
Member 4 which forms a part of the and which constitutes the front side
It is configured to be provided on the No. 4. That is, the intermediate member 44 is formed in a cylindrical shape having a bottom and is fixed to the outer peripheral portion of the sleeve-shaped bearing 36, and the bottom portion 44a is located between the shaft end surface 42 of the spindle 35 and the rear side of the impeller 26. The rear thrust bearing member 41 is attached and fixed to the bottom portion 44a as a support portion.

【0021】上記変形構造においては、リアスラスト軸
受部材41の摺動部41aを平坦面形状とし、これに対
しスピンドル34の軸端面42に球面形状の摺動部42
aを形成してあるが、このように球面形状の摺動部を相
互に摺動するいずれか一方に設けることにより上述した
効果が得られる。但し、相互の摺動部分がともに平坦面
のものでも従来にない実質的効果が得られるものであ
り、摺動部を球面形状としたものに限定されるものでは
ない。
In the above modified structure, the sliding portion 41a of the rear thrust bearing member 41 has a flat surface shape, while the axial end surface 42 of the spindle 34 has a spherical sliding portion 42.
Although a is formed, the above-described effects can be obtained by providing the spherical sliding portions on either one of the sliding portions. However, even if the mutual sliding portions are both flat surfaces, a substantial effect which has not been obtained can be obtained, and the sliding portion is not limited to the spherical shape.

【0022】又、中間部材44の底部44aには連通孔
45が形成され、インペラ26の中央部に形成した連通
孔43と連通し、スリーブ状軸受36の摺動部36aを
経て流れ出た循環流を破線で示すように循環させ、これ
によってリアスラスト軸受部材41のところで発生する
摺動摩擦熱が一層良好に放熱される。
A communication hole 45 is formed in the bottom portion 44a of the intermediate member 44, communicates with the communication hole 43 formed in the central portion of the impeller 26, and flows out through the sliding portion 36a of the sleeve bearing 36. Are circulated as shown by the broken line, and thereby the sliding friction heat generated at the rear thrust bearing member 41 is radiated more favorably.

【0023】以上、本発明の実施例ならびに変形構造を
説明したが、本発明はこれに限定されるものではない。
Although the embodiment and the modified structure of the present invention have been described above, the present invention is not limited to this.

【0024】[0024]

【発明の効果】以上のように、本発明によれば、リアス
ラスト軸受を従来構造のようなリアケーシングの内奥部
に設ける構成に代えてインペラのリア側又は従動回転体
のフロント側に配置し、スピンドルの軸端面に摺動させ
る構成としたので、摺動部の発熱が良好に放熱される。
特にインペラのケーシング内での攪拌による冷却作用が
及ぶために、より良好な放熱がなされ摺動部周囲の昇温
による部材破損等に不具合が解消され、又、スリーブ状
軸受とスピンドルとの間の循環流の流路は遮断されるこ
とがないので、常に安定した冷却作用ならびに潤滑作用
が得られるとともに該循環流が常にリアスラスト軸受部
分に及ぼされるので、一層良好な放熱がなされ、断熱構
造等の特別の措置を採る必要がなく、リアケーシング等
の周囲部材に合成樹脂の成型品を用い得、耐久性に富み
コストダウンが容易なマグネットポンプを提供できる。
As described above, according to the present invention, the rear thrust bearing is arranged on the rear side of the impeller or the front side of the driven rotating body, instead of the conventional structure in which the rear thrust bearing is provided inside the rear casing. However, since it is configured to slide on the shaft end surface of the spindle, the heat generated in the sliding portion is radiated well.
In particular, since the cooling action by stirring in the casing of the impeller is exerted, better heat dissipation is performed, and problems such as member damage due to temperature rise around the sliding part are eliminated, and there is also a gap between the sleeve-shaped bearing and the spindle. Since the flow path of the circulating flow is not blocked, a stable cooling action and a lubricating action are always obtained, and since the circulating flow is always exerted on the rear thrust bearing portion, a better heat dissipation is achieved and a heat insulating structure or the like is provided. It is possible to provide a magnet pump which has a high durability and is easy to reduce the cost because it is possible to use a molded product of synthetic resin for the peripheral member such as the rear casing without the need to take special measures.

【図面の簡単な説明】[Brief description of drawings]

【図1】本発明に係るリアスラスト軸受の構造を具体化
したマグネットポンプの実施例の要部破断全体図であ
る。
FIG. 1 is an overall broken view of essential parts of an embodiment of a magnet pump that embodies a structure of a rear thrust bearing according to the present invention.

【図2】本発明に係るリアスラスト軸受の変形構造を示
すマグネットポンプの要部拡大断面図である。
FIG. 2 is an enlarged sectional view of a main part of a magnet pump showing a modified structure of a rear thrust bearing according to the present invention.

【図3】従来構造に係るリアスラスト軸受を備えたマグ
ネットポンプの要部断面図である。
FIG. 3 is a cross-sectional view of essential parts of a magnet pump including a rear thrust bearing according to a conventional structure.

【符号の説明】[Explanation of symbols]

20 マグネットポンプ 26 インペラ 29 リアケーシング 32 従動回転体 34 スピンドル 40 支持部 41 リアスラスト軸受部材 42 スピンドルの軸端面 44 中間部材 44a 底部(支持部) 20 Magnet Pump 26 Impeller 29 Rear Casing 32 Driven Rotating Body 34 Spindle 40 Supporting Part 41 Rear Thrust Bearing Member 42 Spindle Shaft End Surface 44 Intermediate Member 44a Bottom Part (Supporting Part)

Claims (2)

【特許請求の範囲】[Claims] 【請求項1】内部にポンプ室(23)を区画するととも
に軸方向に沿う吸込口(24)と周方向に沿う吐出口
(25)とを備えたフロントケーシング(22)と、該
ポンプ室内に回転自在に配置されフロント側が前記吸込
口に対向するインペラ(26)と、該フロントケーシン
グと共働してポンプ室を流体密に囲う有底筒状のリアケ
ーシング(29)と、該リアケーシング外に配置される
とともに駆動マグネット(31)を有する駆動回転体
(30)と、前記リアケーシング内に配置されるととも
に該リアケーシングを介して前記駆動マグネットとマグ
ネットカップリングをなすように対向する従動マグネッ
ト(33)を有し前記インペラと一体回転可能な従動回
転体(32)と、前記リアケーシングの底部(29a)
に固定されるとともに片持ばりの態様で軸方向に突出し
該突出部(34a)に前記従動回転体を回転自在に支持
するスピンドル(34)とを備えてなるマグネットポン
プにおいて、前記スピンドルの軸端面(42)に対向し
て軸方向に沿ってリアスラスト軸受部材(41)を該ス
ピンドルの軸端面に摺接可能に配置し、該リアスラスト
軸受部材を支持する支持部(40,44a)を前記イン
ペラ(26)のリア側又は従動回転体(32)のフロン
ト側に設けたことを特徴とするマグネットポンプにおけ
るリアスラスト軸受の構造。
1. A front casing (22) which defines a pump chamber (23) inside and has a suction port (24) along the axial direction and a discharge port (25) along the circumferential direction, and inside the pump chamber. An impeller (26) that is rotatably arranged and has a front side facing the suction port, a bottomed cylindrical rear casing (29) that cooperates with the front casing to fluid-tightly surround a pump chamber, and an outside of the rear casing. And a driven rotating body (30) having a driving magnet (31) and a driven magnet which is disposed in the rear casing and faces the driving magnet via the rear casing so as to form a magnetic coupling. A driven rotating body (32) having (33) and capable of rotating integrally with the impeller; and a bottom portion (29a) of the rear casing.
And a spindle (34) that is fixed to the shaft and axially projects in a cantilevered manner and that rotatably supports the driven rotating body on the projection (34a). The rear thrust bearing member (41) is arranged so as to be slidably contactable with the shaft end surface of the spindle along the axial direction facing the (42), and the support portion (40, 44a) for supporting the rear thrust bearing member is provided. A structure of a rear thrust bearing in a magnet pump, which is provided on a rear side of an impeller (26) or a front side of a driven rotary body (32).
【請求項2】相互に摺接可能な前記スピンドル(26)
の軸端面(42)とリアスラスト軸受部材(41)のい
ずれか一方の摺接部(41a,42a)を球面状に形成
してなる請求項1に記載のマグネットポンプにおけるリ
アスラスト軸受の構造。
2. The spindle (26) capable of sliding contact with each other.
The structure of the rear thrust bearing in the magnet pump according to claim 1, wherein the sliding contact portion (41a, 42a) of either one of the shaft end surface (42) and the rear thrust bearing member (41) is formed into a spherical shape.
JP6106313A 1994-04-22 1994-04-22 Structure of rear thrust bearing in magnet pump Expired - Fee Related JP2632132B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP6106313A JP2632132B2 (en) 1994-04-22 1994-04-22 Structure of rear thrust bearing in magnet pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP6106313A JP2632132B2 (en) 1994-04-22 1994-04-22 Structure of rear thrust bearing in magnet pump

Publications (2)

Publication Number Publication Date
JPH0712084A true JPH0712084A (en) 1995-01-17
JP2632132B2 JP2632132B2 (en) 1997-07-23

Family

ID=14430501

Family Applications (1)

Application Number Title Priority Date Filing Date
JP6106313A Expired - Fee Related JP2632132B2 (en) 1994-04-22 1994-04-22 Structure of rear thrust bearing in magnet pump

Country Status (1)

Country Link
JP (1) JP2632132B2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007517162A (en) * 2003-12-30 2007-06-28 ワナー・エンジニアリング・インコーポレーテッド Magnetically driven hydraulically balanced centrifugal pump
JP2015220910A (en) * 2014-05-20 2015-12-07 株式会社不二工機 Magnet rotor type motor and pump including the same

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008050958A (en) * 2006-08-23 2008-03-06 Iwaki Co Ltd Self-priming pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6088313A (en) * 1983-10-19 1985-05-18 Matsushita Electric Ind Co Ltd Rotary encoder
JPS61145755A (en) * 1984-12-19 1986-07-03 Sony Corp Recording and reproducing device
JPH02188689A (en) * 1988-12-20 1990-07-24 Karsten A Laing Motor unit for centrifugal pump
JPH05111534A (en) * 1991-10-22 1993-05-07 Nikkiso Co Ltd Blood pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6088313A (en) * 1983-10-19 1985-05-18 Matsushita Electric Ind Co Ltd Rotary encoder
JPS61145755A (en) * 1984-12-19 1986-07-03 Sony Corp Recording and reproducing device
JPH02188689A (en) * 1988-12-20 1990-07-24 Karsten A Laing Motor unit for centrifugal pump
JPH05111534A (en) * 1991-10-22 1993-05-07 Nikkiso Co Ltd Blood pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007517162A (en) * 2003-12-30 2007-06-28 ワナー・エンジニアリング・インコーポレーテッド Magnetically driven hydraulically balanced centrifugal pump
JP4772696B2 (en) * 2003-12-30 2011-09-14 ワナー・エンジニアリング・インコーポレーテッド Magnetically driven hydraulically balanced centrifugal pump
JP2015220910A (en) * 2014-05-20 2015-12-07 株式会社不二工機 Magnet rotor type motor and pump including the same

Also Published As

Publication number Publication date
JP2632132B2 (en) 1997-07-23

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