JP2020153302A - Bearing structure of electric fluid pump - Google Patents
Bearing structure of electric fluid pump Download PDFInfo
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- JP2020153302A JP2020153302A JP2019052870A JP2019052870A JP2020153302A JP 2020153302 A JP2020153302 A JP 2020153302A JP 2019052870 A JP2019052870 A JP 2019052870A JP 2019052870 A JP2019052870 A JP 2019052870A JP 2020153302 A JP2020153302 A JP 2020153302A
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- bearing
- bearing means
- support shaft
- impeller
- regulating portion
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Classifications
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- 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
- F04D29/046—Bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
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- 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
- F04D29/06—Lubrication
- F04D29/061—Lubrication especially adapted for liquid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
本発明は、吸入口を有するケーシングと、当該ケーシングに設けられて前記吸入口の内側に配置される保持部に少なくとも一端部が保持される支持軸と、当該支持軸が挿通される内孔を有する円筒状の軸受筒部を有して滑り軸受機能を発揮する軸受手段と、前記支持軸に前記軸受手段を介して回転自在に支持されるとともに前記軸受手段に固定されるインペラおよびロータと、少なくとも前記インペラの回転時には前記ケーシング内の固定位置に在るようにして前記軸受手段の前記吸入口側への移動を規制する第１規制部と、前記軸受手段の前記吸入口とは反対側への移動を規制して前記ケーシング内に固定配置される第２規制部とを備え、取扱流体に浸される前記軸受手段の前記第１規制部および前記第２規制部間での軸方向移動が可能とされる電動流体ポンプに関し、特に軸受構造の改良に関する。 The present invention provides a casing having a suction port, a support shaft provided in the casing in which at least one end is held by a holding portion provided inside the suction port, and an inner hole through which the support shaft is inserted. A bearing means that has a cylindrical bearing cylinder portion and exhibits a sliding bearing function, and an impeller and a rotor that are rotatably supported by the support shaft via the bearing means and fixed to the bearing means. At least to the side opposite to the suction port of the bearing means and the first regulating portion that regulates the movement of the bearing means to the suction port side so as to be at a fixed position in the casing when the impeller rotates. The bearing means is provided with a second restricting portion that is fixedly arranged in the casing by restricting the movement of the bearing means, and the axial movement between the first regulating portion and the second regulating portion of the bearing means immersed in the handling fluid Regarding possible electric fluid pumps, especially regarding improvement of bearing structure.
このような電動流体ポンプは、特許文献１で既に知られている。 Such an electric fluid pump is already known in Patent Document 1.
上記特許文献１で開示されたものでは、支持軸にすべり軸受を介して支持されるインペラおよびロータが前記滑り軸受に固定され、この滑り軸受の両端に対向してスラスト板が配置され、一方のスラスト板および滑り軸受間にインペラの回転時に流体を滑り軸受および支持軸間に吸引する吸引手段が設けられ、他方のスラスト板および滑り軸受間にインペラの回転時に流体を滑り軸受および支持軸間から排出する排出手段が設けられるようにしており、インペラの回転時には、滑り軸受および支持軸間を潤滑すべく流体が常に流通している。このため流体中に混在する異物、たとえば微小な塵、錆びた金属の粉、滑り軸受の摩耗粉等が滑り軸受の摺動面に巻き込まれ、それによって回転抵抗の増大や異常摩耗が生じてしまう可能性がある。 In the one disclosed in Patent Document 1, an impeller and a rotor supported on a support shaft via a slide bearing are fixed to the slide bearing, and thrust plates are arranged opposite to both ends of the slide bearing, and one of them is provided. A suction means is provided between the thrust plate and the slide bearing to suck the fluid between the slide bearing and the support shaft when the impeller rotates, and between the other thrust plate and the slide bearing, the fluid is drawn between the slide bearing and the support shaft when the impeller rotates. A discharge means for discharging is provided, and when the impeller rotates, a fluid is constantly flowing to lubricate between the slide bearing and the support shaft. For this reason, foreign substances mixed in the fluid, such as minute dust, rusted metal powder, and wear powder of the slide bearing, are caught in the sliding surface of the slide bearing, which causes an increase in rotational resistance and abnormal wear. there is a possibility.
本発明は、かかる事情に鑑みてなされたものであり、インペラ回転中には支持軸および軸受手段間を取扱流体が流通するのを抑止し、回転抵抗の増大や異常摩耗が生じるのを防止して軸受手段の耐久性向上に寄与し得るようにした電動流体ポンプにおける軸受構造を提供することを目的とする。 The present invention has been made in view of such circumstances, and suppresses the flow of the handling fluid between the support shaft and the bearing means during impeller rotation, and prevents an increase in rotational resistance and abnormal wear. It is an object of the present invention to provide a bearing structure in an electric fluid pump capable of contributing to the improvement of the durability of the bearing means.
上記目的を達成するために、本発明は、吸入口を有するケーシングと、当該ケーシングに設けられて前記吸入口の内側に配置される保持部に少なくとも一端部が保持される支持軸と、当該支持軸が挿通される内孔を有する円筒状の軸受筒部を有して滑り軸受機能を発揮する軸受手段と、前記支持軸に前記軸受手段を介して回転自在に支持されるとともに前記軸受手段に固定されるインペラおよびロータと、少なくとも前記インペラの回転時には前記ケーシング内の固定位置に在るようにして前記軸受手段の前記吸入口側への移動を規制する第１規制部と、前記軸受手段の前記吸入口とは反対側への移動を規制して前記ケーシング内に固定配置される第２規制部とを備え、取扱流体に浸される前記軸受手段の前記第１規制部および前記第２規制部間での軸方向移動が可能とされる電動流体ポンプにおいて、前記軸受筒部の前記内孔の内面に、前記軸受手段の軸方向両端間にわたって前記支持軸および前記軸受手段間に前記取扱流体を流通させることを可能とした潤滑溝が形成され、前記軸受手段の前記第１規制部側の第１端面に、前記インペラの回転時には当該インペラが受ける圧力に応じた前記第１端面の前記第１規制部への圧接によって閉じられるものの前記インペラの停止時には前記第１端面の前記第１規制部への圧接が解除されるのに応じて開放状態となる凹部が前記支持軸の半径方向に沿う内端部を前記潤滑溝に連通させるとともに前記半径方向に沿う外端部を閉じた形状を有して形成され、前記軸受手段の前記第２規制部側の第２端面に前記潤滑溝に通じる排出溝が前記取扱流体を半径方向外方側に排出することを可能として形成されることを第１の特徴とする。 In order to achieve the above object, the present invention comprises a casing having a suction port, a support shaft provided in the casing and having at least one end held by a holding portion arranged inside the suction port, and the support. A bearing means that has a cylindrical bearing cylinder portion having an inner hole through which a shaft is inserted and exhibits a sliding bearing function, and a bearing means that is rotatably supported by the support shaft via the bearing means and the bearing means. The impeller and rotor to be fixed, the first restricting portion that regulates the movement of the bearing means to the suction port side so as to be at a fixed position in the casing at least when the impeller rotates, and the bearing means. The first regulating portion and the second regulating portion of the bearing means immersed in the handling fluid are provided with a second regulating portion that is fixedly arranged in the casing by restricting movement to the side opposite to the suction port. In an electric fluid pump capable of axially moving between bearing means, the handling fluid is provided between the support shaft and the bearing means on the inner surface of the inner hole of the bearing cylinder portion over both axial ends of the bearing means. A lubricating groove is formed so that the bearing means can be circulated, and the first end surface of the first end surface of the bearing means on the first regulating portion side according to the pressure received by the impeller when the impeller rotates. 1 A recess that is closed by pressure welding to the regulating portion but is opened when the pressure contact of the first end surface to the first regulating portion is released when the impeller is stopped is along the radial direction of the support shaft. The inner end portion is formed so as to communicate with the lubrication groove and the outer end portion along the radial direction is closed, and the inner end portion is connected to the lubrication groove on the second end surface of the bearing means on the second regulation portion side. The first feature is that the discharge groove is formed so that the handling fluid can be discharged outward in the radial direction.
また本発明は、第１の特徴の構成に加えて、前記軸受手段は、第１の前記潤滑溝が形成される第１の前記内孔を有する第１の軸受筒部に前記第１規制部に対向するとともに前記凹部が形成される第１規制部側フランジ部が一体に設けられて成る第１の滑り軸受と、第２の前記潤滑溝が形成される第２の前記内孔を有する第２の軸受筒部に前記第２規制部に対向するとともに前記排出溝が形成される第２規制部側フランジ部が一体に設けられて成る第２の滑り軸受とで構成されることを第２の特徴とする。 Further, in the present invention, in addition to the configuration of the first feature, the bearing means has the first regulation portion in the first bearing cylinder portion having the first inner hole in which the first lubrication groove is formed. A first slide bearing that is integrally provided with a flange portion on the side of the first regulating portion that faces the surface and is formed with the recess, and a second inner hole in which the second lubrication groove is formed. The second bearing cylinder portion is composed of a second slide bearing that faces the second regulation portion and is integrally provided with a flange portion on the side of the second regulation portion in which the discharge groove is formed. It is a feature of.
本発明は、第１の特徴の構成に加えて、前記軸受手段が、前記第１規制部および前記第２規制部間に配置される単一の前記軸受筒部の軸方向両端面に、前記凹部および前記排出溝がそれぞれ形成されて成ることを第３の特徴とする。 In the present invention, in addition to the configuration of the first feature, the bearing means is provided on both axial end faces of the single bearing cylinder portion arranged between the first regulating portion and the second regulating portion. The third feature is that the recess and the discharge groove are formed respectively.
さらに本発明は、第１〜第３の特徴の構成のいずれかに加えて、前記支持軸の軸線が、前記保持部で保持される前記支持軸の一端部側を上方位置として上下方向に指向して配置されることを第４の特徴とする。 Further, in the present invention, in addition to any of the configurations of the first to third features, the axis of the support shaft is oriented in the vertical direction with one end side of the support shaft held by the holding portion as an upward position. The fourth feature is that they are arranged in a similar manner.
本発明の第１の特徴によれば、インペラの回転時には、そのインペラが受ける圧力に応じて軸受手段の第１規制部側の第１端面が第１規制部に圧接されることによって第１端面に形成された凹部が閉じられることになり、軸受手段の内孔に形成された潤滑溝への取扱流体の流れが塞き止められる。一方、インペラが停止すると、第１規制部への第１端面の圧接が解除されることによって凹部が開放状態となり、凹部から潤滑溝を経て排出溝へと取扱流体が流通することができる。すなわちインペラの回転時には、軸受手段および支持軸間を取扱流体が流通することはなく、インペラの停止時に軸受手段および支持軸間を取扱流体が流通することが可能となる。このためインペラの回転によって取扱流体が流動することによって異物が巻き上げられるのに伴って懸濁状態となった取扱流体が軸受手段および支持軸間を流通することが防止され、異物が沈殿するインペラ停止時だけ軸受手段の摺動面での取扱流体の交換が行なわれることになり、摩耗粉等の異物の噛み込みによる軸受手段の異常摩耗や回転抵抗の増大等の不具合が生じるのを回避し、軸受手段の耐久性向上に寄与することができる。また第１規制部が回転不能である場合には、インペラ回転時に軸受手段側からのスラスト荷重を第１規制部で受けるようにして前記第１端面が前記第１規制部に摺動接触することになるが、第１端面に形成された凹部に溜まった取扱流体で第１端面および第１規制部間の潤滑が可能であり、これにより破損や異常摩耗が生じるのを防止して耐焼き付け性を高め、耐久性の向上を図ることができる。 According to the first feature of the present invention, when the impeller rotates, the first end surface of the bearing means on the first regulating portion side is pressed against the first regulating portion according to the pressure received by the impeller, so that the first end surface is pressed against the first regulating portion. The recess formed in the bearing means is closed, and the flow of the handling fluid to the lubricating groove formed in the inner hole of the bearing means is blocked. On the other hand, when the impeller is stopped, the pressure contact of the first end surface to the first regulation portion is released, so that the recess is opened, and the handling fluid can flow from the recess to the discharge groove through the lubrication groove. That is, when the impeller rotates, the handling fluid does not flow between the bearing means and the support shaft, and when the impeller is stopped, the handling fluid can flow between the bearing means and the support shaft. For this reason, the handling fluid flows due to the rotation of the impeller, and as the foreign matter is wound up, the suspended handling fluid is prevented from flowing between the bearing means and the support shaft, and the foreign matter is settled at the impeller stop. Only when the fluid handled on the sliding surface of the bearing means is exchanged, problems such as abnormal wear of the bearing means and an increase in rotational resistance due to the biting of foreign matter such as abrasion powder are avoided. It can contribute to improving the durability of the bearing means. When the first regulating portion is non-rotatable, the first end face is in sliding contact with the first regulating portion so that the thrust load from the bearing means side is received by the first regulating portion when the impeller rotates. However, the handling fluid accumulated in the recess formed on the first end face can lubricate between the first end face and the first regulation part, which prevents breakage and abnormal wear and prevents seizure resistance. It is possible to improve the durability.
また本発明の第２の特徴によれば、軸受手段を構成する第１および第２の滑り軸受のうち第１の滑り軸受が有する第１規制部側フランジ部が第１規制部に対向し、第２の滑り軸が有する第２規制部側フランジ部が第２規制部に対向するので、第１および第２規制部と、軸受手段との接触面積を大きくして面圧を低く抑え、第１の滑り軸受および第１規制部間の種抵抗を低減することができる。 Further, according to the second feature of the present invention, the first regulating portion side flange portion of the first sliding bearing among the first and second sliding bearings constituting the bearing means faces the first regulating portion. Since the flange portion on the second regulating portion side of the second sliding shaft faces the second regulating portion, the contact area between the first and second regulating portions and the bearing means is increased to suppress the surface pressure to a low level. It is possible to reduce the seed resistance between the slide bearing 1 and the first regulating portion.
本発明の第３の特徴によれば、軸受手段が単一の軸受筒部から成るものであることによって部品点数の低減を図ることができる。 According to the third feature of the present invention, the number of parts can be reduced because the bearing means is composed of a single bearing cylinder.
さらに本発明の第４の特徴によれば、保持部で保持される支持軸の一端部側を上方位置として支持軸の軸線を上下方向に指向させたことにより、インペラ停止時には重力によって前記第１端面を第１規制部から離間させることができる。 Further, according to the fourth feature of the present invention, the axis of the support shaft is directed in the vertical direction with one end side of the support shaft held by the holding portion as an upper position, so that the first one is caused by gravity when the impeller is stopped. The end face can be separated from the first regulating portion.
本発明の実施の形態について添付の図面を参照しながら説明する。 Embodiments of the present invention will be described with reference to the accompanying drawings.
本発明の第１の実施の形態について図１〜図３を参照しながら説明すると、先ず図１において、この電動流体ポンプは、ポンプ室６を内部に有するケーシング７と、ケーシング７に支持される支持軸８と、その支持軸８に回転自在に支持されて前記ポンプ室６に収容されるインペラ９と、当該インペラ９とともに回転するようにして前記ポンプ室６に収容されるロータ１０と、前記ケーシング７外で前記ロータ１０を囲繞するように配置されるステータ１１とを備える。 The first embodiment of the present invention will be described with reference to FIGS. 1 to 3. First, in FIG. 1, the electric fluid pump is supported by a casing 7 having a pump chamber 6 inside and a casing 7. The support shaft 8, the impeller 9 rotatably supported by the support shaft 8 and housed in the pump chamber 6, the rotor 10 housed in the pump room 6 so as to rotate with the impeller 9, and the above. A stator 11 is provided outside the casing 7 so as to surround the rotor 10.
前記ケーシング７は、前記ポンプ室６の中央部上端に開口する吸入口１２を形成するようにして上下方向に延びる吸入筒部１３ｂならびに前記ポンプ室６内の外周部に連なって接線方向に延びる吐出筒部１３ｃを有するポンプケース１３と、当該ポンプケース１３との間に前記ポンプ室６を形成するようにして前記ポンプケース１３に結合される缶状のケース部材１４とで構成される。 The casing 7 is connected to the suction cylinder portion 13b extending in the vertical direction so as to form a suction port 12 opening at the upper end of the central portion of the pump chamber 6 and the outer peripheral portion in the pump chamber 6 and extends in the tangential direction. It is composed of a pump case 13 having a tubular portion 13c and a can-shaped case member 14 that is coupled to the pump case 13 so as to form the pump chamber 6 between the pump case 13.
前記ポンプケース１３は下方に開放した皿状のポンプケース主部１３ａと、そのポンプケース主部１３ａの上端中央部に連設される前記吸入筒部１３ｂと、前記ポンプケース１３の外周に連設される前記吐出筒部１３ｃと、前記ポンプケース主部１３ａ下端から半径方向外方に張り出す第１のフランジ部１３ｄとを一体に有するようにして合成樹脂で形成され、前記第１のフランジ部１３ｄは、前記ポンプケース主部１３ａの半径方向に沿う外方側か内方側よりも低くなるようにした段付きに形成される。 The pump case 13 is connected to a dish-shaped pump case main portion 13a that is open downward, a suction cylinder portion 13b that is connected to the central portion of the upper end of the pump case main portion 13a, and an outer periphery of the pump case 13. The discharge cylinder portion 13c to be formed and the first flange portion 13d projecting outward in the radial direction from the lower end of the pump case main portion 13a are integrally formed of the synthetic resin, and the first flange portion is formed. The 13d is formed with a step so as to be lower than the outer side or the inner side along the radial direction of the pump case main portion 13a.
前記ケース部材１４は、前記ポンプケース主部１３ａの内径よりも小さな内径を有して上方を開放した有底円筒部１４ａと、その有底円筒部１４ａの上端部から半径方向外方に張り出して前記第１のフランジ部１３ｄに下方から当接、嵌合される第２のフランジ部１４ｂとを一体に有して合成樹脂により形成される。 The case member 14 has a bottomed cylindrical portion 14a having an inner diameter smaller than the inner diameter of the pump case main portion 13a and opening upward, and the case member 14 projecting outward in the radial direction from the upper end portion of the bottomed cylindrical portion 14a. It is formed of a synthetic resin having a second flange portion 14b that comes into contact with and is fitted to the first flange portion 13d from below.
前記ケーシング７には、中間ケース部材１５と、その中間ケース部材１５を前記ケーシング７との間に挟むカバー部材１６が結合される。前記中間ケース部材１５は、前記有底円筒部１４ａを同軸に囲繞する円筒状のケース部材主部１５ａと、そのケース部材主部１５ａの上部から半径方向外方に張り出す第３のフランジ部１５ｂと、前記ケース部材主部１５ａの下部から半径方向外方に張り出す第４のフランジ部１５ｃとを一体に有し、前記ケース部材主部１５ａの上部および前記第３のフランジ部１５ｂは、前記第２のフランジ部１４ｂに前記第３のフランジ部１５ｂを下方から当接させるようにして前記第２のフランジ部１４ｂに嵌合され、前記第１のフランジ部１３ｄおよび第３のフランジ部１５ｂが相互間に前記第２のフランジ部１４ｂを挟んで結合される。 An intermediate case member 15 and a cover member 16 that sandwiches the intermediate case member 15 between the casing 7 are coupled to the casing 7. The intermediate case member 15 includes a cylindrical case member main portion 15a that coaxially surrounds the bottomed cylindrical portion 14a, and a third flange portion 15b that projects outward in the radial direction from the upper portion of the case member main portion 15a. And a fourth flange portion 15c projecting outward in the radial direction from the lower portion of the case member main portion 15a, and the upper portion of the case member main portion 15a and the third flange portion 15b are described. The third flange portion 15b is brought into contact with the second flange portion 14b from below so as to be fitted to the second flange portion 14b, and the first flange portion 13d and the third flange portion 15b are brought into contact with each other. The second flange portion 14b is sandwiched and connected to each other.
前記カバー部材１６は、下端部を閉じた有底円筒状に形成されるカバー部材主部１６ａと、そのカバー部材主部１６ａの上端部から半径方向外方に張り出して前記中間ケース部材１５の下端部の前記第４のフランジ部１５ｃに下方から結合される第５のフランジ部１６ｂが一体に設けられて成り、前記第４のフランジ部１５ｃおよび前記第５のフランジ部１６ｂ間には環状のシール部材１７が挟持される。 The cover member 16 protrudes outward in the radial direction from the cover member main portion 16a formed in a bottomed cylindrical shape with the lower end portion closed and the upper end portion of the cover member main portion 16a, and the lower end of the intermediate case member 15. A fifth flange portion 16b to be integrally provided to the fourth flange portion 15c of the portion is integrally provided, and an annular seal is provided between the fourth flange portion 15c and the fifth flange portion 16b. The member 17 is sandwiched.
前記ケース部材１４における前記有底円筒部１４ａの外面には前記ステータ１１が固定されており、このステータ１１は前記中間ケース部材１５における前記ケース部材主部１５ａで囲繞される。また前記カバー部材１６の前記カバー部材主部１６ａ内には、制御回路基板１８が収容、固定される。 The stator 11 is fixed to the outer surface of the bottomed cylindrical portion 14a of the case member 14, and the stator 11 is surrounded by the case member main portion 15a of the intermediate case member 15. Further, the control circuit board 18 is housed and fixed in the cover member main portion 16a of the cover member 16.
前記支持軸８の少なくとも一端部、この実施の形態では前記支持軸８の最上方位置にある一端部は、前記ケーシング７における前記ポンプケース１３に設けられて前記吸入口１２の内側に配置される保持部２０に保持される。 At least one end of the support shaft 8, in this embodiment, one end at the uppermost position of the support shaft 8 is provided in the pump case 13 in the casing 7 and is arranged inside the suction port 12. It is held by the holding unit 20.
前記保持部２０は、前記吸入筒部１３ｂの前記ポンプ室６側の端部内の中央部に配置されるものであり、前記支持軸８の前記一端部を嵌合させるようにして下方に開放した嵌合凹部２１を有し、前記吸入筒部１３ｂの前記ポンプ室６側の端部内周に、周方向に間隔をあけて配置される複数の支持腕部２２を介して一体に連設される。 The holding portion 20 is arranged at the central portion in the end portion of the suction cylinder portion 13b on the pump chamber 6 side, and is opened downward so as to fit the one end portion of the support shaft 8. It has a fitting recess 21, and is integrally provided on the inner circumference of the end portion of the suction cylinder portion 13b on the pump chamber 6 side via a plurality of support arm portions 22 arranged at intervals in the circumferential direction. ..
図２を併せて参照して、前記支持軸８の前記一端部寄りの外周の一部には平坦な切欠き面２３が形成されており、前記嵌合凹部２１は前記支持軸８の横断面形状に対応した断面形状を有するように形成される。すなわち前記支持軸８の一端部は、前記保持部２０に回転不能に保持される。 With reference to FIG. 2, a flat notch surface 23 is formed on a part of the outer periphery of the support shaft 8 near the one end portion, and the fitting recess 21 is a cross section of the support shaft 8. It is formed so as to have a cross-sectional shape corresponding to the shape. That is, one end of the support shaft 8 is non-rotatably held by the holding portion 20.
また前記ケース部材１４は、前記有底円筒部１４ａの下端閉塞部から上方に延びる円筒状の支持筒部１４ｃを一体に有しており、前記支持軸８の他端部は前記支持筒部１４ｃ内に嵌合される。しかも前記支持筒部１４ｃは、前記支持軸８の全長のおよそ３０％程度を受け入れ可能とした受け口長さを有するように形成される。これにより、前記支持筒部１４ｃは、前記ケース部材１４の一部を構成して前記支持筒部１４ｃに一体に連なる前記有底円筒部１４ａの外周に固定された前記ステータ１１に対して、前記支持軸８を精度よく位置決めし、かつ同軸に保持することになる。 Further, the case member 14 integrally has a cylindrical support cylinder portion 14c extending upward from the lower end closing portion of the bottomed cylindrical portion 14a, and the other end portion of the support shaft 8 is the support cylinder portion 14c. Fitted inside. Moreover, the support cylinder portion 14c is formed so as to have a receiving port length that can accept about 30% of the total length of the support shaft 8. As a result, the support cylinder portion 14c is fixed to the outer periphery of the bottomed cylindrical portion 14a which constitutes a part of the case member 14 and is integrally connected to the support cylinder portion 14c. The support shaft 8 is accurately positioned and held coaxially.
また前記ロータ１０は、ロータハブ２４と、そのロータハブ２４に固定されるボンド磁石２５とから成る。前記ロータハブ２４は、前記支持筒部１４ｃを同軸に囲繞する円筒状の磁石支持部２４ａと、その磁石支持部２４ａよりも小径に形成されて前記支持軸８を同軸に囲繞しつつ前記磁石支持部２４ａの上端部から上方に延出される延出筒部２４ｂとが同軸にかつ一体に連設されて成り、前記ボンド磁石２５は前記磁石支持部２４ａの外周にアウトサート成形され、前記延出筒部２４ｂの上部には、前記インペラ９がスナップフィット等によって固定される。 Further, the rotor 10 includes a rotor hub 24 and a bond magnet 25 fixed to the rotor hub 24. The rotor hub 24 has a cylindrical magnet support portion 24a that coaxially surrounds the support cylinder portion 14c, and the magnet support portion 24a that is formed to have a diameter smaller than that of the magnet support portion 24a and that coaxially surrounds the support shaft 8. The extension cylinder portion 24b extending upward from the upper end portion of the 24a is coaxially and integrally connected to the extension cylinder portion 24b, and the bond magnet 25 is outsert-formed on the outer periphery of the magnet support portion 24a to form the extension cylinder. The impeller 9 is fixed to the upper portion of the portion 24b by a snap fit or the like.
前記ロータ１０と、そのロータハブ２４が有する前記延出筒部２４ｂに固定される前記インペラ９とは、前記支持軸８に、滑り軸受機能を発揮する軸受手段２７を介して回転自在に支持されており、この軸受手段２７は、インペラ９で圧送する取扱流体たとえば冷却水を潤滑液として利用すべく当該取扱流体に浸される。 The rotor 10 and the impeller 9 fixed to the extension cylinder portion 24b of the rotor hub 24 are rotatably supported by the support shaft 8 via a bearing means 27 that exhibits a slide bearing function. The bearing means 27 is immersed in the handling fluid to be pumped by the impeller 9, for example, cooling water to be used as a lubricating liquid.
前記軸受手段２７は、少なくとも前記インペラ９の回転時には前記ケーシング７内に固定配置される第１規制部としてのワッシャ２８と、前記ケーシング７内に固定配置される第２規制部としての前記支持筒部１４ｃとの間で軸方向に移動可能であり、前記軸受手段２７の前記吸入口１２側への移動は前記ワッシャ２８で規制され、前記軸受手段２７の前記吸入口１２とは反対側への移動は前記支持筒部１４ｃで規制される。 The bearing means 27 includes a washer 28 as a first regulating portion fixedly arranged in the casing 7 and a support cylinder as a second regulating portion fixedly arranged in the casing 7 at least when the impeller 9 rotates. It is movable in the axial direction with the portion 14c, and the movement of the bearing means 27 toward the suction port 12 is restricted by the washer 28, and the bearing means 27 moves to the opposite side of the suction port 12. The movement is restricted by the support cylinder portion 14c.
図２に注目して、前記ワッシャ２８は前記保持部２０に下方から当接することが可能であり、前記支持軸８を挿通させるようにして前記ワッシャ２８がその中央部に有する挿通孔２９は、前記支持軸８の前記切欠き面２３に対応した直線部２９ａを内周の一部に有して、前記支持軸８の横断面形状に対応した形状に形成される。すなわち前記ワッシャ２８は，前記ケーシング７に固定的に支持される前記支持軸８の軸線まわりに回転することはなく、前記軸受手段２７の前記吸入口１２側への移動時には前記保持部２０に当接されることにより実質的にケーシング７内の固定位置となるように配置されることになる。 Focusing on FIG. 2, the washer 28 can be brought into contact with the holding portion 20 from below, and the insertion hole 29 that the washer 28 has in the central portion thereof allows the support shaft 8 to be inserted. A straight portion 29a corresponding to the cutout surface 23 of the support shaft 8 is provided in a part of the inner circumference, and is formed in a shape corresponding to the cross-sectional shape of the support shaft 8. That is, the washer 28 does not rotate around the axis of the support shaft 8 fixedly supported by the casing 7, and hits the holding portion 20 when the bearing means 27 moves toward the suction port 12. When they are in contact with each other, they are arranged so as to be substantially fixed in the casing 7.
前記軸受手段２７は、前記ワッシャ２８および前記支持筒部１４ｃ間に配置される第１および第２の滑り軸受３０，３１で構成され、第１の滑り軸受３０が前記ワッシャ２８および第２の滑り軸受３１間に配置され、第２の滑り軸受３１が、第１の滑り軸受３０および前記支持筒部１４ｃ間に配置される。 The bearing means 27 is composed of first and second slide bearings 30 and 31 arranged between the washer 28 and the support cylinder portion 14c, and the first slide bearing 30 is the washer 28 and the second slide. It is arranged between the bearings 31 and the second slide bearing 31 is arranged between the first slide bearing 30 and the support cylinder portion 14c.
前記第１の滑り軸受３０は、前記支持軸８を挿通させる第１の内孔３２を有する第１の軸受筒部３０ａに前記ワッシャ２８に対向する第１規制部側フランジ部としての第６のフランジ部３０ｂが一体に設けられて成る。 The first slide bearing 30 is a sixth as a flange portion on the side of the first regulation portion facing the washer 28 in the first bearing cylinder portion 30a having the first inner hole 32 through which the support shaft 8 is inserted. The flange portion 30b is integrally provided.
図３を併せて参照して、前記第２の滑り軸受３１は、前記支持軸８を挿通させる第２の内孔３３を有する第２の軸受筒部３１ａに前記支持筒部１４ｃに対向する第２規制部側フランジ部としての第７のフランジ部３１ｂが一体に設けられて成る。 With reference to FIG. 3, the second slide bearing 31 faces the support cylinder portion 14c in the second bearing cylinder portion 31a having the second inner hole 33 through which the support shaft 8 is inserted. 2. A seventh flange portion 31b as a flange portion on the regulation portion side is integrally provided.
前記第１の軸受筒部３０ａが有する第１の内孔３２の内面ならびに前記第２の軸受筒部３１ａが有する第２の内孔３３の内面には、前記軸受手段２７の軸方向両端間にわたって前記支持軸８および前記軸受手段２７間に前記取扱流体を流通させることを可能とした第１および第２の潤滑溝３４，３５が形成される
また前記軸受手段２７の前記ワッシャ２８側の端面、すなわち第６のフランジ部３０ｂの前記ワッシャ２８に対向する第１端面３０ｃには、前記インペラ９の回転時には当該インペラ９が受ける圧力に応じた前記第１端面３０ｃの前記第ワッシャ２８への圧接によって閉じられるものの前記インペラ９の停止時には前記第１端面３０ｃの前記ワッシャ２８への圧接が解除されるのに応じて開放状態となる凹部３６が、前記支持軸８の半径方向に沿う内端部を前記第１の潤滑溝３４に連通させるとともに前記半径方向に沿う外端部を閉じた形状を有して形成される。
The inner surface of the first inner hole 32 included in the first bearing cylinder portion 30a and the inner surface of the second inner hole 33 included in the second bearing cylinder portion 31a extend between both ends in the axial direction of the bearing means 27. First and second lubrication grooves 34 and 35 are formed between the support shaft 8 and the bearing means 27 to allow the handling fluid to flow. Further, the end face of the bearing means 27 on the washer 28 side. That is, the first end surface 30c of the sixth flange portion 30b facing the washer 28 is pressed against the washer 28 of the first end surface 30c according to the pressure received by the impeller 9 when the impeller 9 is rotated. The recess 36, which is closed but is opened in response to the release of the pressure contact of the first end surface 30c to the washer 28 when the impeller 9 is stopped, forms an inner end portion of the support shaft 8 along the radial direction. It is formed so as to communicate with the first lubrication groove 34 and have a shape in which the outer end portion along the radial direction is closed.
しかも前記第１の潤滑溝３４は、前記第１の内孔３２の内面の周方向に間隔をあけた複数箇所たとえば３箇所に形成され、複数個たとえば３個の前記凹部３６が、複数の前記第１の潤滑溝３４に個別に対応して前記第１端面３０ｃに形成され、前記ワッシャ２８の外径は、前記第１端面３０ｃが前記ワッシャ２８に圧接されたときに全ての前記凹部３６を閉じ得る大きさに設定される。 Moreover, the first lubrication groove 34 is formed at a plurality of locations, for example, three locations spaced apart from each other in the circumferential direction of the inner surface of the first inner hole 32, and the plurality of, for example, the three recesses 36 are formed in the plurality of locations. Individually corresponding to the first lubrication groove 34, the first end surface 30c is formed, and the outer diameter of the washer 28 is such that all the recesses 36 are pressed against the washer 28 when the first end surface 30c is pressed against the washer 28. It is set to a size that can be closed.
また前記軸受手段２７の前記支持筒部１４ｃ側の端面、すなわち第７のフランジ部３１ｂの前記支持筒部１４ｃに対向する第２端面３１ｃには、前記第２の潤滑溝３５に通じる排出溝３７が前記取扱流体を半径方向外方側に排出することを可能として形成される。 Further, the end surface of the bearing means 27 on the support cylinder portion 14c side, that is, the second end surface 31c of the seventh flange portion 31b facing the support cylinder portion 14c has a discharge groove 37 leading to the second lubrication groove 35. Is formed so that the handling fluid can be discharged outward in the radial direction.
しかも前記第２の潤滑溝３５は、前記第２の内孔３３の内面の周方向に間隔をあけた複数箇所たとえば３箇所に形成され、複数個たとえば３個の前記排出溝３７が、複数の前記第２の潤滑溝３５に個別に対応して前記第２端面に形成される。 Moreover, the second lubrication groove 35 is formed at a plurality of places, for example, three places spaced apart from each other in the circumferential direction of the inner surface of the second inner hole 33, and the plurality of, for example, three discharge grooves 37 are plurality. It is formed on the second end surface individually corresponding to the second lubrication groove 35.
次にこの第１の実施の形態の作用について説明すると、支持軸８と、インペラ９およびロータ１０との間には、前記インペラ９および前記ロータ１０が固定されるとともに滑り軸受機能を発揮する軸受手段２７が、前記インペラ９の回転時には固定位置となるようにしてケーシング７の吸入口１２側に配置されるワッシャ２８ならびに前記吸入口１２から離間した位置で前記ケーシング７に固定配置される支持筒部１４ｃ間で移動することを可能としつつ取扱流体に浸される軸受手段２７が設けられ、前記軸受手段２７が有する第１および第２の軸受筒部３０ａ，３１ａが有する第１および第２の内孔３２，３３には、前記軸受手段２７の軸方向両端間にわたって前記支持軸８および前記軸受手段２７間に取扱流体を流通させることを可能とした第１および第２の潤滑溝３４，３５が形成され、前記軸受手段２７の前記ワッシャ２８側の第１端面３０ｃに、前記インペラ９の回転時には当該インペラ９が受ける圧力に応じた前記第１端面３０ｃの前記ワッシャ２８への圧接によって閉じられるものの前記インペラ９の停止時には前記第１端面３０ｃの前記ワッシャ２８への圧接が解除されるのに応じて開放状態となる凹部３６が前記支持軸８の半径方向に沿う内端部を前記第１および第２の潤滑溝３４，３５に連通させるとともに前記半径方向に沿う外端部を閉じた形状を有して形成され、前記軸受手段２７の前記支持筒部１４ｃ側の第２端面３１ｃに前記第１および第２の潤滑溝３４，３５に通じる排出溝３７が前記取扱流体を半径方向外方側に排出することを可能として形成される。 Next, the operation of the first embodiment will be described. A bearing in which the impeller 9 and the rotor 10 are fixed and a sliding bearing function is exhibited between the support shaft 8 and the impeller 9 and the rotor 10. The means 27 is a washer 28 arranged on the suction port 12 side of the casing 7 so as to be in a fixed position when the impeller 9 is rotated, and a support cylinder fixedly arranged on the casing 7 at a position away from the suction port 12. A bearing means 27 that is immersed in the handling fluid while being able to move between the portions 14c is provided, and the first and second bearing cylinder portions 30a and 31a of the bearing means 27 have the first and second bearing means 27. In the inner holes 32 and 33, the first and second lubricating grooves 34 and 35 that allow the handling fluid to flow between the support shaft 8 and the bearing means 27 across both ends in the axial direction of the bearing means 27. Is formed and closed to the first end surface 30c of the bearing means 27 on the washer 28 side by pressure contact of the first end surface 30c to the washer 28 according to the pressure received by the impeller 9 when the impeller 9 is rotated. However, when the impeller 9 is stopped, the recess 36, which is opened in response to the release of the pressure contact of the first end surface 30c to the washer 28, forms the inner end portion of the support shaft 8 along the radial direction. The bearing means 27 is formed on the second end surface 31c of the bearing means 27 on the support cylinder portion 14c side so as to communicate with the second lubrication grooves 34 and 35 and have a shape in which the outer end portion along the radial direction is closed. The discharge grooves 37 leading to the first and second lubrication grooves 34 and 35 are formed so as to enable the handling fluid to be discharged outward in the radial direction.
したがってインペラ９の回転時には、そのインペラ９が受ける圧力に応じて軸受手段２７の前記ワッシャ２８側の第１端面３０ｃが前記ワッシャ２８に圧接されることによって第１端面３０ｃに形成された凹部３６が閉じられることになり、軸受手段２７の第１および第２の内孔３２，３３に形成された第１および第２の潤滑溝３４，３５への取扱流体の流れが塞き止められる。一方、インペラ９が停止すると、前記ワッシャ２８への第１端面３０ｃの圧接が解除されることによって前記凹部３６が開放状態となり、前記凹部３６から第１および第２の潤滑溝３４，３５を経て排出溝３７へと取扱流体が流通することができる。すなわちインペラ９の回転時には、軸受手段２７および支持軸８間を取扱流体が流通することはなく、インペラ９の停止時に軸受手段２７および支持軸８間を取扱流体が流通することが可能となる。このためインペラ９の回転によって取扱流体が流動することによって異物が巻き上げられるのに伴って懸濁状態となった取扱流体が軸受手段２７および支持軸８間を流通することが防止され、異物が沈殿するインペラ９の停止時だけ軸受手段２７の摺動面での取扱流体の交換が行なわれることになり、摩耗粉等の異物の噛み込みによる軸受手段２７の異常摩耗や回転抵抗の増大等の不具合が生じるのを回避し、軸受手段２７の耐久性向上に寄与することができる。 Therefore, when the impeller 9 is rotated, the recess 36 formed in the first end surface 30c is formed by pressing the first end surface 30c of the bearing means 27 on the washer 28 side with the washer 28 according to the pressure received by the impeller 9. It will be closed and the flow of the handling fluid to the first and second lubrication grooves 34 and 35 formed in the first and second inner holes 32 and 33 of the bearing means 27 will be blocked. On the other hand, when the impeller 9 is stopped, the pressure contact of the first end surface 30c to the washer 28 is released, so that the recess 36 is opened, and the recess 36 passes through the first and second lubrication grooves 34 and 35. The handling fluid can flow to the discharge groove 37. That is, when the impeller 9 is rotating, the handling fluid does not flow between the bearing means 27 and the support shaft 8, and when the impeller 9 is stopped, the handling fluid can flow between the bearing means 27 and the support shaft 8. Therefore, the handling fluid flows due to the rotation of the impeller 9, and the handling fluid in a suspended state is prevented from flowing between the bearing means 27 and the support shaft 8 as the foreign matter is wound up, and the foreign matter settles. Only when the impeller 9 is stopped, the fluid handled on the sliding surface of the bearing means 27 is exchanged, and there are problems such as abnormal wear of the bearing means 27 and an increase in rotational resistance due to the biting of foreign matter such as abrasion powder. Can be avoided, and the durability of the bearing means 27 can be improved.
またワッシャ２８が回転不能であることにより、インペラ９の回転時に前記軸受手段２７側からのスラスト荷重を前記ワッシャ２８で受けるようにして前記第１端面３０ｃが前記ワッシャ２８に摺動接触することになるが、第１端面３０ｃに形成された前記凹部３６に溜まった取扱流体で第１端面３０ｃおよび前記ワッシャ２８間の潤滑が可能であり、これにより破損や異常摩耗が生じるのを防止して耐焼き付け性を高め、耐久性の向上を図ることができる。 Further, since the washer 28 is non-rotatable, the first end surface 30c is in sliding contact with the washer 28 so that the washer 28 receives a thrust load from the bearing means 27 side when the impeller 9 is rotated. However, the handling fluid accumulated in the recess 36 formed in the first end surface 30c can lubricate between the first end surface 30c and the washer 28, thereby preventing breakage and abnormal wear and withstanding resistance. It is possible to improve the seizure property and improve the durability.
また前記軸受手段２７は、第１の潤滑溝３４が形成される第１の内孔３２を有する第１の軸受筒部３０ａに前記ワッシャ２８に対向するとともに前記凹部３６が形成される第６のフランジ部３０ｂが一体に設けられて成る第１の滑り軸受３０と、第２の潤滑溝３５が形成される第２の内孔３３を有する第２の軸受筒部３１ａに前記支持筒部１４ｃに対向するとともに前記排出溝３７が形成される第７のフランジ部３１ｂが一体に設けられて成る第２の滑り軸受３１とで構成されるので、前記ワッシャ２８および前記支持筒部１４ｃと、前記軸受手段２７との接触面積を大きくして面圧を低く抑え、第１の滑り軸受３０および前記ワッシャ２８間の摺動抵抗を低減することができる。 Further, the bearing means 27 faces the washer 28 and the recess 36 is formed in the first bearing cylinder portion 30a having the first inner hole 32 in which the first lubrication groove 34 is formed. The support cylinder portion 14c is formed in a second bearing cylinder portion 31a having a first slide bearing 30 integrally provided with a flange portion 30b and a second inner hole 33 in which a second lubrication groove 35 is formed. Since it is composed of a second slide bearing 31 which is integrally provided with a seventh flange portion 31b which faces the discharge groove 37 and forms the discharge groove 37, the washer 28, the support cylinder portion 14c, and the bearing. The contact area with the means 27 can be increased to keep the surface pressure low, and the sliding resistance between the first sliding bearing 30 and the washer 28 can be reduced.
さらに前記支持軸８の軸線が、前記保持部２０で保持される前記支持軸８の一端部側を上方位置として上下方向に指向して配置されるので、インペラ９の停止時には重力によって前記第１端面３０ｃを前記ワッシャ２８から離間させることができる。 Further, since the axis of the support shaft 8 is arranged so as to be oriented in the vertical direction with one end side of the support shaft 8 held by the holding portion 20 as an upward position, the first one is caused by gravity when the impeller 9 is stopped. The end face 30c can be separated from the washer 28.
本発明の第２の実施の形態について図４を参照しながら説明すると、この電動流体ポンプは、たとえば内燃機関に冷却水を循環させるためにシリンダブロックに取付けられるものであり、ポンプ室４１を内部に有するケーシング４２と、ケーシング４２に支持される支持軸４３と、その支持軸４３に回転自在に支持されて前記ポンプ室４１に収容されるインペラ４４と、当該インペラ４４とともに回転するようにして前記ポンプ室４１に収容されるロータ４５と、前記ケーシング４２外で前記ロータ４５を囲繞するように配置されるステータ４６とを備える。 Explaining the second embodiment of the present invention with reference to FIG. 4, this electric fluid pump is attached to a cylinder block for circulating cooling water to an internal combustion engine, for example, and has a pump chamber 41 inside. 42, a support shaft 43 supported by the casing 42, an impeller 44 rotatably supported by the support shaft 43 and housed in the pump chamber 41, and the impeller 44 rotating together with the impeller 44. A rotor 45 housed in the pump chamber 41 and a stator 46 arranged so as to surround the rotor 45 outside the casing 42 are provided.
前記ケーシング４２は、吸入口４７を有するアルミニウム合金等の軽金属から成るポンプケース４８と、当該ポンプケース４８との間に前記ポンプ室４１を形成するようにして前記ポンプケース４８に結合される缶状のケース部材４９とで構成され、ケース部材４９は、内燃機関の作動時に上昇する冷却水の温度上昇に耐え得る耐熱性を有する非磁性材、たとえばＰＰＳ樹脂などの合成樹脂で形成される。また前記ケース部材４９を前記ポンプケース４８との間に挟むカバー部材５０が前記ポンプケース４８および前記ケース部材４９に結合される。 The casing 42 has a can shape that is coupled to the pump case 48 so as to form the pump chamber 41 between the pump case 48 made of a light metal such as an aluminum alloy having a suction port 47 and the pump case 48. The case member 49 is made of a non-magnetic material having heat resistance capable of withstanding the temperature rise of the cooling water that rises when the internal combustion engine operates, for example, a synthetic resin such as PPS resin. Further, a cover member 50 that sandwiches the case member 49 with the pump case 48 is coupled to the pump case 48 and the case member 49.
前記ケース部材４９の外面には、前記カバー部材５０で覆われるようにして前記ステータ４７が固定されており、前記カバー部材５０内には、制御回路基板５１が収容、固定される。 The stator 47 is fixed to the outer surface of the case member 49 so as to be covered with the cover member 50, and the control circuit board 51 is housed and fixed in the cover member 50.
前記支持軸４３の少なくとも一端部、この実施の形態では前記支持軸４３の一端部は、前記ケーシング４２における前記ポンプケース４８に設けられて前記吸入口４７の内側に配置される保持部５２に回転不能に嵌合、保持され、前記支持軸４３の他端部は、前記ケース部材４９に一体に設けられる支持筒部４９ａに嵌合される。 At least one end of the support shaft 43, in this embodiment, one end of the support shaft 43 rotates on a holding portion 52 provided on the pump case 48 in the casing 42 and arranged inside the suction port 47. It is improperly fitted and held, and the other end of the support shaft 43 is fitted to the support cylinder portion 49a integrally provided with the case member 49.
前記ロータ４５は、ロータハブ５３と、そのロータハブ５３に固定されるボンド磁石５４とから成り、ボンド磁石５４から突出して前記インペラ４４側に延びるようにして前記ロータハブ５３の一部を構成する延出筒部５３ａに前記インペラ４４が一体に形成される。 The rotor 45 is composed of a rotor hub 53 and a bond magnet 54 fixed to the rotor hub 53, and is an extension cylinder that constitutes a part of the rotor hub 53 so as to protrude from the bond magnet 54 and extend toward the impeller 44. The impeller 44 is integrally formed with the portion 53a.
前記ロータ４５および前記インペラ４４は、前記支持軸４３に、軸受手段としての単一の滑り軸受５５を介して回転自在に支持される。この滑り軸受５５は、前記支持軸４３を挿通させて前記保持部５２に対向する第１規制部としてのワッシャ６０と、第２規制部としての前記支持筒部４９ａとの間に配置される軸受筒部５５ａを有するものであり、前記ロータ４５の前記ロータハブ５３における前記延出筒部５３ａに前記軸受筒部５５ａが嵌入、固定される。また前記軸受筒部５５ａには前記支持軸４３を挿通させる内孔５６が設けられ、この内孔５６の内面には軸方向両端間にわたる潤滑溝５７が形成される。 The rotor 45 and the impeller 44 are rotatably supported by the support shaft 43 via a single slide bearing 55 as a bearing means. The slide bearing 55 is a bearing arranged between the washer 60 as the first restricting portion facing the holding portion 52 through which the support shaft 43 is inserted and the support cylinder portion 49a as the second regulating portion. It has a cylinder portion 55a, and the bearing cylinder portion 55a is fitted and fixed to the extension cylinder portion 53a in the rotor hub 53 of the rotor 45. Further, the bearing cylinder portion 55a is provided with an inner hole 56 through which the support shaft 43 is inserted, and a lubrication groove 57 extending between both ends in the axial direction is formed on the inner surface of the inner hole 56.
前記保持部５２および前記滑り軸受５５間にはワッシャ６０が介装されており、前記軸受筒部５５ａの軸方向両端面に、前記ワッシャ６０側に臨む凹部５８と、前記支持筒部４９ａ側に臨む排出溝５９とがそれぞれ形成される。すなわち前記滑り軸受５５の前記ワッシャ６０に対向する第１端面５５ｂには前記凹部５８が形成され、前記滑り軸受５５の前記支持筒部４９ａに対向する第２端面５５ｃには前記排出溝５９が形成される。 A washer 60 is interposed between the holding portion 52 and the slide bearing 55, and a recess 58 facing the washer 60 side and a support cylinder portion 49a side are provided on both axial end surfaces of the bearing cylinder portion 55a. Discharge grooves 59 facing each other are formed. That is, the recess 58 is formed in the first end surface 55b of the slide bearing 55 facing the washer 60, and the discharge groove 59 is formed in the second end surface 55c of the slide bearing 55 facing the support cylinder portion 49a. Will be done.
この第２の実施の形態によっても上記第１の実施の形態と同様の効果を奏することができるとともに、部品点数を低減することができる。 The second embodiment also has the same effect as that of the first embodiment, and the number of parts can be reduced.
以上、本発明の実施の形態について説明したが、本発明は上記実施の形態に限定されるものではなく、特許請求の範囲に記載された本発明を逸脱することなく種々の設計変更を行うことが可能である。 Although the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various design changes are made without departing from the present invention described in the claims. Is possible.
たとえば上述の実施の形態では、図１および図４で示すように、ロータ１０，４５と、ステータ１１，４６とが、支持軸８，４３の軸線に沿う方向でほぼ同一位置にあって半径方向に整列するように配置されているが、本発明は、そのような配置には限定されない。たとえばロータハブ２４，５３の全長を短縮する等によってロータ１０，４５がステータ１１，４６よりもインペラ９，４４側にわずかに突出するようにしてもよい。そうすればインペラ９，４４の停止時にはロータ１０，４５が具備するボンド磁石２５，５４およびステータ１０，４６間の磁力により、重力にかかわらず軸受手段２７および滑り軸受５５の第１端面３０ｃ，５５ｂを第１規制部であるワッシャ２８，６０から離間させることができる。 For example, in the above-described embodiment, as shown in FIGS. 1 and 4, the rotors 10 and 45 and the stators 11 and 46 are substantially at the same position along the axes of the support shafts 8 and 43 and are in the radial direction. Although arranged to be aligned with, the invention is not limited to such an arrangement. For example, the rotors 10 and 45 may be slightly projected toward the impellers 9 and 44 from the stators 11 and 46 by shortening the total length of the rotor hubs 24 and 53. Then, when the impellers 9 and 44 are stopped, the magnetic force between the bond magnets 25 and 54 and the stators 10 and 46 included in the rotors 10 and 45 causes the bearing means 27 and the first end faces 30c and 55b of the slide bearing 55 regardless of gravity. Can be separated from the washer 28, 60 which is the first regulation part.
７，４２・・・ケーシング
８，４３・・・支持軸
９，４４・・・インペラ
１０，４５・・・ロータ
１２，４７・・・吸入口
１４ｃ，４９ａ・・・第２規制部である支持筒部
２０，５２・・・保持部
２７・・・軸受手段
２８，６０・・・第１規制部であるワッシャ
３０，３１・・・滑り軸受
３０ａ，３１ａ，５５ａ・・・軸受筒部
３０ｂ・・・第１規制部側フランジ部である第６の５フランジ部
３０ｃ，５５ｂ・・・第１端面
３１ｂ・・・第２規制部側フランジ部である第７のフランジ部
３１ｃ，５５ｃ・・・第２端面
３２，３３，５６・・・内孔
３４，３５，５７・・・潤滑溝
３６，５８・・・凹部
３７，５９・・・排出溝
５５・・・軸受手段である滑り軸受
7,42 ... Casing 8,43 ... Support shaft 9,44 ... Impeller 10,45 ... Rotor 12,47 ... Suction port 14c, 49a ... Support that is the second regulation part Cylinders 20, 52 ... Holding portions 27 ... Bearing means 28, 60 ... Washers 30, 31 ... Sliding bearings 30a, 31a, 55a ... Bearing cylinders 30b ... 6th 5 flange portions 30c, 55b ... 1st end surface 31b ... 7th flange portions 31c, 55c ... which are the 2nd regulation portion side flange portions. Second end faces 32, 33, 56 ... Inner holes 34, 35, 57 ... Lubrication grooves 36, 58 ... Recesses 37, 59 ... Discharge grooves 55 ... Slide bearings as bearing means
Claims (4)
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| KR102334918B1 (en) * | 2020-12-21 | 2021-12-06 | 한전케이피에스 주식회사 | Apparatus for inspection of excitor rotor shaft alignment and method thereof |
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| KR102334918B1 (en) * | 2020-12-21 | 2021-12-06 | 한전케이피에스 주식회사 | Apparatus for inspection of excitor rotor shaft alignment and method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111720355B (en) | 2022-02-01 |
| JP7126467B2 (en) | 2022-08-26 |
| CN111720355A (en) | 2020-09-29 |
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