JP6805003B2 - Impellers and pumps - Google Patents
Impellers and pumps Download PDFInfo
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- JP6805003B2 JP6805003B2 JP2017011936A JP2017011936A JP6805003B2 JP 6805003 B2 JP6805003 B2 JP 6805003B2 JP 2017011936 A JP2017011936 A JP 2017011936A JP 2017011936 A JP2017011936 A JP 2017011936A JP 6805003 B2 JP6805003 B2 JP 6805003B2
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- 230000003014 reinforcing effect Effects 0.000 claims description 87
- 238000003466 welding Methods 0.000 description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 238000009434 installation Methods 0.000 description 3
- 239000000725 suspension Substances 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
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Description
本発明は、羽根車及びポンプに関する。 The present invention relates to impellers and pumps.
ポンプに用いられる羽根車について薄肉で軽量な構造を実現するために、羽根車を製缶化することが行われている。しかし、薄肉な板構造では鋳物構造に比べハブとボスの接合部の強度が著しく低下する。厚肉な構造では軽量化は実現できないため、薄肉な板構造でハブとボスの接合の強度を向上させる構造が求められる。 In order to realize a thin and lightweight structure for the impeller used for the pump, the impeller is made into a can. However, in the thin plate structure, the strength of the joint between the hub and the boss is significantly lower than that in the cast structure. Since weight reduction cannot be achieved with a thick structure, a structure that improves the joint strength between the hub and the boss with a thin plate structure is required.
これに対し、特許文献１では、ハブとボスの接合部に補強部材としての補強用プレートを、ハブの内表面とボスの外表面に接合して配置することにより、ハブとボスの接合の強度を向上させることが開示されている。更に特許文献１では、ハブ内外の圧力差を減少させるための穴（バランスホールともいう）がハブに設けられており、ハブとボスの接合部と補強プレートの間にバランスホールが開けられ、補強プレートに開口が開けられていることが開示されている。 On the other hand, in Patent Document 1, the strength of the joint between the hub and the boss is increased by arranging a reinforcing plate as a reinforcing member at the joint between the hub and the boss by joining the inner surface of the hub and the outer surface of the boss. Is disclosed to improve. Further, in Patent Document 1, a hole (also referred to as a balance hole) for reducing the pressure difference between the inside and outside of the hub is provided in the hub, and a balance hole is opened between the joint portion between the hub and the boss and the reinforcing plate for reinforcement. It is disclosed that the plate has an opening.
ハブに設ける穴（バランスホール）は、ハブの吸い込み側と吐き出し側との差圧を逃がすために、できるだけハブの吸い込み側に設けられることが望ましい。ここで、ハブとボスとの角度が規定の角度より小さい場合には、ボスの長軸に対して略垂直方向における補強部材の内縁から補強部材の外縁までの長さ（例えば補強部材がリング状のプレートの場合、内外径差）が小さくなり、バランスホールと同じ長径（例えば真円の場合、直径）の開口を補強部材に開けると、補強部材の強度が落ちてしまい、補強部材の表面と裏面に圧力差に耐えることができないという問題がある。また、ハブとボスとの角度が更に小さくなって、ボスの長軸に対して略垂直方向における補強部材の内縁から補強部材の外縁までの長さが、バランスホールの長径（例えば真円の場合、直径）以下になるほどハブとボスとの角度が小さい場合には、バランスホールと同じ長径（例えば真円の場合、直径）の開口を補強部材に開けることが物理的にできなくなるという問題もある。 It is desirable that the holes (balance holes) provided in the hub be provided on the suction side of the hub as much as possible in order to release the differential pressure between the suction side and the discharge side of the hub. Here, when the angle between the hub and the boss is smaller than the specified angle, the length from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss (for example, the reinforcing member has a ring shape). In the case of the plate, if an opening with the same major axis as the balance hole (for example, in the case of a perfect circle, the diameter) is opened in the reinforcing member, the strength of the reinforcing member will decrease, and the surface of the reinforcing member will be affected. There is a problem that the back surface cannot withstand the pressure difference. Further, the angle between the hub and the boss becomes smaller, and the length from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss is the major axis of the balance hole (for example, in the case of a perfect circle). If the angle between the hub and the boss is smaller than the diameter), there is also a problem that it is physically impossible to open an opening with the same major axis as the balance hole (for example, in the case of a perfect circle, the diameter) in the reinforcing member. ..
このため、ハブに設ける穴（バランスホール）を、補強部材よりも吐き出し側に配置せざるを得なくなってしまう。ここでハブの吸い込み側から吐き出し側に沿って圧力が高くなるので、バランスホールが補強部材よりも吐き出し側（すなわち圧力が高い側）に配置されると、ハブ内外の圧力差を十分に減少させることができない。これにより、回転軸には、吐き出し側から吸い込み側に大きなスラスト力が働いてしまうという問題がある。 Therefore, the hole (balance hole) provided in the hub has to be arranged on the discharge side of the reinforcing member. Here, the pressure increases from the suction side to the discharge side of the hub, so if the balance hole is arranged on the discharge side (that is, the side where the pressure is high) rather than the reinforcing member, the pressure difference between the inside and outside of the hub is sufficiently reduced. Can't. As a result, there is a problem that a large thrust force acts on the rotating shaft from the discharge side to the suction side.
本発明は、上記問題に鑑みてなされたものであり、ハブとボスとの角度が小さい場合であっても、回転軸にかかるスラスト力を低減することを可能とする羽根車及びポンプを提供することを目的とする。 The present invention has been made in view of the above problems, and provides an impeller and a pump capable of reducing the thrust force applied to the rotating shaft even when the angle between the hub and the boss is small. The purpose is.
本発明の第１の態様に係る羽根車は、中空の構造であり、当該中空に回転軸が嵌まって回転力が伝達されるボスと、前記ボスに取り付けられており、且つ複数の穴が設けられたハブと、前記ハブの外表面に取り付けられた複数の羽根と、前記ボスの外表面に取り付けられ、前記穴に比べて前記ハブと前記ボスの接合部から離れた位置において前記ハブの内表面に取り付けられており、且つ複数の開口が設けられた補強部材と、を備え、前記ハブと前記ボスとの角度が規定の角度より小さく、前記複数の開口それぞれの開口の断面積は、前記穴の断面積より小さく、前記開口の数は、前記穴の数よりも多く、前記複数の開口の断面積の合計が、前記複数の穴の断面積の合計以上である。 The impeller according to the first aspect of the present invention has a hollow structure, and has a boss in which a rotating shaft is fitted in the hollow to transmit rotational force, and a boss attached to the boss and having a plurality of holes. The hub provided, the plurality of blades attached to the outer surface of the hub, and the hub attached to the outer surface of the boss at a position farther from the joint between the hub and the boss than the hole. It is provided with a reinforcing member attached to the inner surface and provided with a plurality of openings, the angle between the hub and the boss is smaller than a specified angle, and the cross-sectional area of each of the openings of the plurality of openings is. It is smaller than the cross-sectional area of the holes, the number of the openings is larger than the number of the holes, and the total cross-sectional area of the plurality of openings is equal to or more than the total cross-sectional area of the plurality of holes.
この構成によれば、複数の開口の断面積の合計が、複数の穴の断面積の合計以上であるため、補強部材の表面と裏面に圧力差が生じない。このため、ハブとボスとの角度が規定の角度より小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 According to this configuration, since the total cross-sectional area of the plurality of openings is equal to or greater than the total cross-sectional area of the plurality of holes, there is no pressure difference between the front surface and the back surface of the reinforcing member. Therefore, even when the angle between the hub and the boss is smaller than the specified angle, the thrust force applied to the rotating shaft can be reduced.
本発明の第２の態様に係る羽根車は、第１の態様に係る羽根車であって、前記ボスの長軸に対して略垂直方向における前記補強部材の内縁から前記補強部材の外縁までの長さが、前記穴の長径以下である。 The impeller according to the second aspect of the present invention is the impeller according to the first aspect, from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss. The length is equal to or less than the major axis of the hole.
この構成によれば、ボスの長軸に対して略垂直方向における補強部材の内縁から補強部材の外縁までの長さが当該穴の長径以下であるほどハブとボスとの角度が小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 According to this configuration, the angle between the hub and the boss is so small that the length from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss is equal to or less than the major axis of the hole. However, the thrust force applied to the rotating shaft can be reduced.
本発明の第３の態様に係る羽根車は、第１または２の態様に係る羽根車であって、前記補強部材は、リング状のプレートであり、前記ボスの長軸に対して略垂直方向における前記補強部材の内縁から前記補強部材の外縁までの長さは、前記補強部材の内外径差である。 The impeller according to the third aspect of the present invention is the impeller according to the first or second aspect, and the reinforcing member is a ring-shaped plate in a direction substantially perpendicular to the long axis of the boss. The length from the inner edge of the reinforcing member to the outer edge of the reinforcing member is the difference between the inner and outer diameters of the reinforcing member.
この構成によれば、補強部材がリング状のプレートにおいて、補強部材の内外径差が当該穴の長径以下であるほどハブとボスとの角度が小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 According to this configuration, when the reinforcing member is a ring-shaped plate, the thrust force applied to the rotating shaft is applied even when the angle between the hub and the boss is so small that the difference between the inner and outer diameters of the reinforcing member is smaller than the major diameter of the hole. Can be reduced.
本発明の第４の態様に係る羽根車は、第２または３の態様に係る羽根車であって、前記穴の形状は略円であり、前記ボスの長軸に対して略垂直方向における前記補強部材の内縁から前記補強部材の外縁までの長さが、前記穴の直径以下である。 The impeller according to the fourth aspect of the present invention is the impeller according to the second or third aspect, and the shape of the hole is substantially circular, and the impeller in a direction substantially perpendicular to the long axis of the boss. The length from the inner edge of the reinforcing member to the outer edge of the reinforcing member is equal to or less than the diameter of the hole.
この構成によれば、穴の形状を略円にしたときにおいて、ボスの長軸に対して略垂直方向における補強部材の内縁から補強部材の外縁までの長さが当該穴の直径以下であるほどハブとボスとの角度が小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 According to this configuration, when the shape of the hole is substantially circular, the length from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss is less than or equal to the diameter of the hole. Even when the angle between the hub and the boss is small, the thrust force applied to the rotating shaft can be reduced.
本発明の第５の態様に係る羽根車は、第１から４のいずれかの態様に係る羽根車であって、前記穴の形状は略円であり、前記開口の形状は略円であり、前記開口の直径は、前記穴の直径よりも小さい。 The impeller according to the fifth aspect of the present invention is the impeller according to any one of the first to fourth aspects, and the shape of the hole is a substantially circular shape and the shape of the opening is a substantially circular shape. The diameter of the opening is smaller than the diameter of the hole.
この構成によれば、穴の形状を略円且つ開口の形状を略円にしたときにおいて、ハブとボスとの角度が規定の角度より小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 According to this configuration, when the shape of the hole is approximately circular and the shape of the opening is approximately circular, the thrust force applied to the rotation shaft is reduced even when the angle between the hub and the boss is smaller than the specified angle. can do.
本発明の第６の態様に係るポンプは、第１から５のいずれかの態様に係る羽根車を備える。 The pump according to the sixth aspect of the present invention includes an impeller according to any one of the first to fifth aspects.
この構成によれば、複数の開口の断面積の合計が、複数の穴の断面積の合計以上であるため、補強部材の表面と裏面に圧力差が生じない。このため、ハブとボスとの角度が規定の角度より小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 According to this configuration, since the total cross-sectional area of the plurality of openings is equal to or greater than the total cross-sectional area of the plurality of holes, there is no pressure difference between the front surface and the back surface of the reinforcing member. Therefore, even when the angle between the hub and the boss is smaller than the specified angle, the thrust force applied to the rotating shaft can be reduced.
本発明の一態様によれば、複数の開口の断面積の合計が、複数の穴の断面積の合計以上であるため、補強部材の表面と裏面に圧力差が生じない。このため、ハブとボスとの角度が規定の角度より小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 According to one aspect of the present invention, since the total cross-sectional area of the plurality of openings is equal to or greater than the total cross-sectional area of the plurality of holes, there is no pressure difference between the front surface and the back surface of the reinforcing member. Therefore, even when the angle between the hub and the boss is smaller than the specified angle, the thrust force applied to the rotating shaft can be reduced.
以下、各実施形態について、図面を参照しながら説明する。本実施形態に係るポンプは一例としてポンプ機場などで用いられる大型の立軸ポンプである。なお、ポンプは、横軸ポンプであってもよいし、小型のものであってもよいし、羽根車は１段ではなく複数段であってもよい。 Hereinafter, each embodiment will be described with reference to the drawings. The pump according to this embodiment is, for example, a large vertical shaft pump used in a pump station or the like. The pump may be a horizontal axis pump, a small pump, or the impeller may have a plurality of stages instead of one stage.
図１は、本実施形態に係るポンプの模式図である。図１に示すように、本実施形態に係るポンプ１００は、ポンプベース１１４を有し、ポンプベース１１４は水槽上部のポンプ据付床１０１に設置される。羽根車１を収容するガイドケーシング１０６が吊下管１０２を介してポンプ据付床１０１から吊り下げられる。羽根車１は回転軸１０９の一端部に固定されており、回転軸１０９は外軸受１１０および水中軸受１０８により回転自在に支持される。回転軸１０９は、ガイドケーシング１０６、吊下管１０２、及び吐出曲管１０４内を通って鉛直方向に延びている。回転軸１０９の他端部は、駆動機の一例である電動機１１１の回転軸１１２に連結されている。 FIG. 1 is a schematic view of a pump according to the present embodiment. As shown in FIG. 1, the pump 100 according to the present embodiment has a pump base 114, and the pump base 114 is installed on the pump installation floor 101 above the water tank. The guide casing 106 accommodating the impeller 1 is suspended from the pump installation floor 101 via the suspension pipe 102. The impeller 1 is fixed to one end of the rotating shaft 109, and the rotating shaft 109 is rotatably supported by an outer bearing 110 and an underwater bearing 108. The rotating shaft 109 extends in the vertical direction through the guide casing 106, the suspension pipe 102, and the discharge curved pipe 104. The other end of the rotating shaft 109 is connected to the rotating shaft 112 of the electric motor 111, which is an example of a driving machine.
電動機１１１により回転軸１０９を介して羽根車１を回転させると、水槽内の水（取扱液）が、ガイドケーシング１０６の下端から吸い込まれ、ガイドケーシング１０６、吊下管１０２、吐出曲管１０４を通って図示しない吐出配管に移送される。なお、ポンプ運転時においては、羽根車１や水中軸受１０８を収容するガイドケーシング１０６は、液面よりも下に位置している。 When the impeller 1 is rotated by the electric motor 111 via the rotating shaft 109, the water (handling liquid) in the water tank is sucked from the lower end of the guide casing 106, and the guide casing 106, the hanging pipe 102, and the discharge curved pipe 104 are sucked. It is transferred to a discharge pipe (not shown) through the pipe. During pump operation, the guide casing 106 that houses the impeller 1 and the submersible bearing 108 is located below the liquid level.
図２は、本実施形態に係る羽根車の斜視図である。図３は、本実施形態に係る羽根車の正面図である。図２に示すように、羽根車１は、中空１６の構造であり、当該中空１６に回転軸１０９が嵌まって回転力が伝達されるボス３が設けられている。また羽根車１にはハブ２が設けられており、このハブ２は、ボス３に取り付けられており且つ複数の穴２１、…、２５（図３参照）が設けられている。図３に示すように、穴の形状は一例として略円であり、穴（バランスホールともいう）２１、…、２５の直径はＤ１である。 FIG. 2 is a perspective view of the impeller according to the present embodiment. FIG. 3 is a front view of the impeller according to the present embodiment. As shown in FIG. 2, the impeller 1 has a hollow 16 structure, and the hollow 16 is provided with a boss 3 in which a rotating shaft 109 is fitted and a rotational force is transmitted. Further, the impeller 1 is provided with a hub 2, which is attached to the boss 3 and is provided with a plurality of holes 21, ..., 25 (see FIG. 3). As shown in FIG. 3, the shape of the hole is substantially a circle as an example, and the diameters of the holes (also referred to as balance holes) 21, ..., 25 are D1.
更に図２及び３に示すように、羽根車１には、略円錐形状のハブ２の外表面に溶接で取り付けられた複数の羽根１１、…、１５が設けられている。なお、羽根が５枚あるのは一例であって、羽根の数は何枚であってもよい。 Further, as shown in FIGS. 2 and 3, the impeller 1 is provided with a plurality of blades 11, ..., 15 attached by welding to the outer surface of the hub 2 having a substantially conical shape. It should be noted that the number of blades is 5 as an example, and the number of blades may be any number.
図４は、図３のＡ−Ａ’断面図である。図４に示すようにハブ２には穴２１が設けられている。図５は、図４の矢印Ａ１から見た場合における本実施形態に係る補強部材の正面図である。図４のハブ２とボス３の接合部４において、ハブ２は、ボス３の外表面に溶接によって取り付けられている。また、図４に示すように、羽根車１には、補強部材５が設けられている。図４のボス３と補強部材５の接合部６において、補強部材５は、ボス３の外表面に溶接によって取り付けられている。また図４のハブ２と補強部材５の接合部７において、補強部材５は、穴２１に比べてハブ２とボス３の接合部４から離れた位置においてハブ２の内表面に溶接によって取り付けられている。図５に示すように、本実施形態に係る補強部材５は、一例としてリング状のプレートであり、図４に示すように、補強部材５は一例として、吸い込み側（ｚ軸負側）より吐き出し側（ｚ軸正側）の方が、内外径差が小さくなっている。図５に示すように複数の開口３１、…、４８が周回上に設けられており、その一つの開口３４が図４に示されている。 FIG. 4 is a cross-sectional view taken along the line AA'of FIG. As shown in FIG. 4, the hub 2 is provided with a hole 21. FIG. 5 is a front view of the reinforcing member according to the present embodiment when viewed from the arrow A1 of FIG. At the joint 4 between the hub 2 and the boss 3 in FIG. 4, the hub 2 is attached to the outer surface of the boss 3 by welding. Further, as shown in FIG. 4, the impeller 1 is provided with a reinforcing member 5. At the joint portion 6 between the boss 3 and the reinforcing member 5 in FIG. 4, the reinforcing member 5 is attached to the outer surface of the boss 3 by welding. Further, in the joint portion 7 between the hub 2 and the reinforcing member 5 in FIG. 4, the reinforcing member 5 is attached to the inner surface of the hub 2 by welding at a position farther from the joint portion 4 between the hub 2 and the boss 3 than the hole 21. ing. As shown in FIG. 5, the reinforcing member 5 according to the present embodiment is a ring-shaped plate as an example, and as shown in FIG. 4, the reinforcing member 5 is discharged from the suction side (z-axis negative side) as an example. The difference between the inner and outer diameters is smaller on the side (the positive side of the z-axis). As shown in FIG. 5, a plurality of openings 31, ..., 48 are provided on the circumference, and one opening 34 is shown in FIG.
ハブ２とボス３との角度は規定の角度より小さい。ここで規定の角度とは、補強部材５を、ハブ２とボス３の接合部４とは反対側のボス３の端部に配置した場合において、ボス３の長軸に対して略垂直方向における補強部材５の内縁から補強部材５の外縁までの長さ（すなわち補強部材５の内外径差）が、穴２１、…、２５の直径Ｄ１に所定のマージンを足した長さになる角度である。ここで所定のマージンは、補強部材５の強度が、補強部材５の表面と裏面にかかる圧力差に耐えられるように設定される。 The angle between the hub 2 and the boss 3 is smaller than the specified angle. Here, the defined angle is a direction substantially perpendicular to the long axis of the boss 3 when the reinforcing member 5 is arranged at the end of the boss 3 on the opposite side of the joint portion 4 between the hub 2 and the boss 3. The length from the inner edge of the reinforcing member 5 to the outer edge of the reinforcing member 5 (that is, the difference between the inner and outer diameters of the reinforcing member 5) is an angle obtained by adding a predetermined margin to the diameters D1 of the holes 21, ..., 25. .. Here, a predetermined margin is set so that the strength of the reinforcing member 5 can withstand the pressure difference between the front surface and the back surface of the reinforcing member 5.
本実施形態では、ハブ２とボス３との角度の一例として、図４に示すように、ボス３の長軸に対して略垂直方向における補強部材５の内縁から補強部材５の外縁までの長さ（すなわち補強部材５の内外径差）Ｌ１（図４参照）が穴２１、…、２５の直径Ｄ１以下になるほどハブ２とボス３との角度が小さい。 In the present embodiment, as an example of the angle between the hub 2 and the boss 3, as shown in FIG. 4, the length from the inner edge of the reinforcing member 5 to the outer edge of the reinforcing member 5 in a direction substantially perpendicular to the long axis of the boss 3. The angle between the hub 2 and the boss 3 becomes smaller as the diameter L1 (see FIG. 4) of the reinforcing member 5 (that is, the difference between the inner and outer diameters of the reinforcing member 5) becomes smaller than the diameter D1 of the holes 21, ..., 25.
図５に示すように開口の形状は一例として略円であり、複数の開口３１、…、４８の直径はＤ２である。ここで破線の円ＢＬ１は、ハブ２に設けられた穴２１、…、２５の大きさを表している。このように、開口３１、…、４８の直径Ｄ２は、ハブ２に設けられた穴２１、…、２５の直径Ｄ１よりも小さい。また、補強部材５の内外径差Ｌ１が穴２１、…、２５の直径Ｄ１以下になるほどハブ２とボス３との角度が小さい。そして、複数の開口３１、…、４８の断面積の合計（＝１８×π×（Ｄ２／２）2）が、複数の穴２１、…、２５の断面積の合計（＝５×π×（Ｄ１／２）2）以上である。 As shown in FIG. 5, the shape of the openings is substantially a circle as an example, and the diameters of the plurality of openings 31, ..., 48 are D2. Here, the broken line circle BL1 represents the size of the holes 21, ..., 25 provided in the hub 2. As described above, the diameter D2 of the openings 31, ..., 48 is smaller than the diameter D1 of the holes 21, ..., 25 provided in the hub 2. Further, the angle between the hub 2 and the boss 3 becomes smaller as the inner / outer diameter difference L1 of the reinforcing member 5 becomes smaller than the diameter D1 of the holes 21, ..., 25. Then, the total cross-sectional area of the plurality of openings 31, ..., 48 (= 18 × π × (D2 / 2) 2 ) is the total cross-sectional area of the plurality of holes 21, ..., 25 (= 5 × π × (= 5 × π × (= 5 × π ×)). D1 / 2) 2 ) or more.
この構成により、吸い込み側（羽根車１の正面側）から吸い込まれ、羽根１１とボス２に沿って増圧された水の一部が、吐き出し側（羽根車１の裏面側）から、補強部材５の開口３１、…、４８を通り、更にハブ２の穴２１、…、２５を通って、吸い込み側（羽根車１の表面側）に戻される。このとき、補強部材５の内外径差が穴２１、…、２５の直径以下になるほどハブ２とボス３との角度が小さい場合であっても、複数の開口３１、…、４８の断面積の合計が、複数の穴２１、…、２５の断面積の合計以上であるため、補強部材５の表面と裏面に圧力差が生じない。このため、ハブ２とボス３との角度が小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 With this configuration, a part of the water sucked from the suction side (front side of the impeller 1) and increased in pressure along the blade 11 and the boss 2 is a reinforcing member from the discharge side (rear side of the impeller 1). It is returned to the suction side (the surface side of the impeller 1) through the openings 31, ..., 48 of 5 and further through the holes 21, ..., 25 of the hub 2. At this time, even if the angle between the hub 2 and the boss 3 is so small that the difference between the inner and outer diameters of the reinforcing member 5 is equal to or less than the diameter of the holes 21, ..., 25, the cross-sectional areas of the plurality of openings 31, ..., 48 are Since the total is equal to or greater than the total cross-sectional area of the plurality of holes 21, ..., 25, there is no pressure difference between the front surface and the back surface of the reinforcing member 5. Therefore, even when the angle between the hub 2 and the boss 3 is small, the thrust force applied to the rotation shaft can be reduced.
本実施形態では一例として、鉄板からリング状のプレートを切り出し、切り出したプレートに開口３１、…、４８を設けることで補強用プレートが補強部材５として製造される。そして、本実施形態の羽根車１は、ハブ２とボス３と補強用プレートとを溶接することにより製造する。ここで補強用プレートの溶接は、補強用プレートの全周に渡って溶接してもよいし、部分的に溶接してもよい。 In the present embodiment, as an example, a ring-shaped plate is cut out from an iron plate, and the cut-out plate is provided with openings 31, ..., 48, whereby a reinforcing plate is manufactured as the reinforcing member 5. The impeller 1 of the present embodiment is manufactured by welding the hub 2, the boss 3, and the reinforcing plate. Here, the reinforcing plate may be welded over the entire circumference of the reinforcing plate, or may be partially welded.
例えば、ボス３にハブ２を取り付け、その後に補強用プレートを取り付けて製造してもよいし、ボス３に補強用プレートを取り付け、その後にハブ２を取り付けてもよいし、ハブ２に補強用プレートを取り付け、その後に、ハブ２と補強用プレートが合体したものをボス３に取り付けてもよい。また、ハブ２に羽根１１〜１５を予め付けておく場合と、ハブ２をボス３及び／または補強用プレートに取り付けてから羽根１１〜１５を付ける場合がある。 For example, the hub 2 may be attached to the boss 3 and then the reinforcing plate may be attached to manufacture the boss 3, the reinforcing plate may be attached to the boss 3 and then the hub 2 may be attached, or the hub 2 may be attached to the reinforcing plate. The plate may be attached, and then the hub 2 and the reinforcing plate combined may be attached to the boss 3. Further, there are cases where the blades 11 to 15 are attached to the hub 2 in advance, and there are cases where the blades 11 to 15 are attached after the hub 2 is attached to the boss 3 and / or the reinforcing plate.
続いて図６を用いて補強部材の変形例について説明する。図６は、図４の矢印Ａ１から見た場合における変形例に係る補強部材の正面図である。図６に示すように、変形例に係る補強部材５ｂには、異なる直径を有する二つの周回上に開口５１、…、８０が設けられている。ここで破線の円ＢＬ２は、ハブ２に設けられた穴２１、…、２５の大きさを表している。このように、開口５１、…、８０の直径Ｄ２’は、ハブ２に設けられた穴２１、…、２５の直径Ｄ１よりも小さい。また、補強部材５ｂの内外径差Ｌ１’が穴２１、…、２５の直径Ｄ１以下になるほどハブ２とボス３との角度が小さい。 Subsequently, a modified example of the reinforcing member will be described with reference to FIG. FIG. 6 is a front view of the reinforcing member according to the modified example when viewed from the arrow A1 of FIG. As shown in FIG. 6, the reinforcing member 5b according to the modified example is provided with openings 51, ..., 80 on two circumferences having different diameters. Here, the broken line circle BL2 represents the size of the holes 21, ..., 25 provided in the hub 2. As described above, the diameter D2'of the openings 51, ..., 80 is smaller than the diameter D1 of the holes 21, ..., 25 provided in the hub 2. Further, the angle between the hub 2 and the boss 3 becomes smaller as the inner / outer diameter difference L1'of the reinforcing member 5b becomes smaller than the diameter D1 of the holes 21, ..., 25.
なお、穴２１、…、２５の形状は一例として略円としたが、これに限らず、三角形以上の多角形でも、星形でもよく、どんな形状であってもよい。また、開口３１、…、４８の形状は一例として略円としたが、これに限らず、三角形以上の多角形でも、星形でもよく、どんな形状であってもよい。この場合であっても、補強部材５の複数の開口それぞれの開口の断面積は、ハブ２の穴の断面積より小さい。そして、補強部材５の開口の数は、ハブ２の穴の数よりも多い。複数の開口の断面積の合計が、複数の穴の断面積の合計以上である。ボス３の長軸に対して略垂直方向における補強部材５の内縁から補強部材５の外縁までの長さが穴２１、…、２５の長径以下になるほどハブ２とボス３との角度が小さい。 The shapes of the holes 21, ..., 25 are substantially circular as an example, but the shape is not limited to this, and may be a polygon of a triangle or more, a star shape, or any shape. Further, the shapes of the openings 31, ..., 48 are substantially circular as an example, but the shape is not limited to this, and may be a polygon of a triangle or more, a star shape, or any shape. Even in this case, the cross-sectional area of each of the plurality of openings of the reinforcing member 5 is smaller than the cross-sectional area of the holes of the hub 2. The number of openings in the reinforcing member 5 is larger than the number of holes in the hub 2. The total cross-sectional area of the plurality of openings is equal to or greater than the total cross-sectional area of the plurality of holes. The angle between the hub 2 and the boss 3 becomes smaller as the length from the inner edge of the reinforcing member 5 to the outer edge of the reinforcing member 5 in a direction substantially perpendicular to the long axis of the boss 3 is equal to or less than the major axis of the holes 21, ..., 25.
この場合であっても、複数の開口３１、…、４８の断面積の合計が、複数の穴２１、…、２５の断面積の合計以上であるため、補強部材５の表面と裏面に圧力差が生じない。このため、ハブ２とボス３との角度が小さい場合であっても、回転軸にかかるスラスト力を低減することができる。 Even in this case, since the total cross-sectional area of the plurality of openings 31, ..., 48 is equal to or greater than the total cross-sectional area of the plurality of holes 21, ..., 25, there is a pressure difference between the front surface and the back surface of the reinforcing member 5. Does not occur. Therefore, even when the angle between the hub 2 and the boss 3 is small, the thrust force applied to the rotation shaft can be reduced.
なお、補強部材はリング状のプレートとしたが、複数のリブであってもよい。その場合、補強部材の開口は、リブの間の空間が該当する。しかし、リブの場合、位置合わせが大変であるので溶接が難しい。 Although the reinforcing member is a ring-shaped plate, it may be a plurality of ribs. In that case, the opening of the reinforcing member corresponds to the space between the ribs. However, in the case of ribs, welding is difficult because alignment is difficult.
以上、本発明は上記実施形態そのままに限定されるものではなく、実施段階ではその要旨を逸脱しない範囲で構成要素を変形して具体化できる。また、上記実施形態に開示されている複数の構成要素の適宜な組み合わせにより、種々の発明を形成できる。例えば、実施形態に示される全構成要素から幾つかの構成要素を削除してもよい。更に、異なる実施形態にわたる構成要素を適宜組み合わせてもよい。 As described above, the present invention is not limited to the above-described embodiment as it is, and at the implementation stage, the components can be modified and embodied without departing from the gist thereof. In addition, various inventions can be formed by an appropriate combination of the plurality of components disclosed in the above-described embodiment. For example, some components may be removed from all the components shown in the embodiments. Further, components over different embodiments may be combined as appropriate.
１ 羽根車
１１〜１５ 羽根
１６ 中空
２ ハブ
２１〜２５ 穴
３ ボス
３１〜４８ 開口
４、６、７ 接合部
５、５ｂ 補強部材
５１〜８０ 開口
１００ ポンプ
１０１ ポンプ据付床
１０２ 吊下管
１０４ 吐出曲管
１０６ ガイドケーシング
１０８ 水中軸受
１０９ 回転軸
１１０ 外軸受
１１１ 電動機
１１２ 回転軸
１１４ ポンプベース
1 Impeller 11-15 Blade 16 Hollow 2 Hub 21-25 Hole 3 Boss 31-48 Opening 4, 6, 7 Joint 5, 5b Reinforcing member 51-80 Opening 100 Pump 101 Pump installation floor 102 Suspension pipe 104 Discharge bend Tube 106 Guide casing 108 Submersible bearing 109 Rotating shaft 110 External bearing 111 Electric motor 112 Rotating shaft 114 Pump base
Claims (6)
前記ボスに取り付けられており、且つ複数の穴が設けられたハブと、
前記ハブの外表面に取り付けられた複数の羽根と、
前記ボスの外表面に取り付けられ、前記穴に比べて前記ハブと前記ボスの接合部から離れた位置において前記ハブの内表面に取り付けられており、且つ複数の開口が設けられた補強部材と、
を備え、
前記ハブと前記ボスとの角度が規定の角度より小さく、
前記複数の開口それぞれの開口の断面積は、前記穴の断面積より小さく、
前記開口の数は、前記穴の数よりも多く、
前記複数の開口の断面積の合計が、前記複数の穴の断面積の合計以上である
羽根車。 A hollow structure with a boss in which the rotating shaft fits into the hollow and the rotational force is transmitted.
A hub that is attached to the boss and has a plurality of holes.
A plurality of blades attached to the outer surface of the hub,
A reinforcing member that is attached to the outer surface of the boss, is attached to the inner surface of the hub at a position farther from the joint between the hub and the boss than the hole, and is provided with a plurality of openings.
With
The angle between the hub and the boss is smaller than the specified angle,
The cross-sectional area of each of the plurality of openings is smaller than the cross-sectional area of the holes.
The number of openings is greater than the number of holes
An impeller in which the total cross-sectional area of the plurality of openings is equal to or greater than the total cross-sectional area of the plurality of holes.
請求項１に記載の羽根車。 The impeller according to claim 1, wherein the length from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss is equal to or less than the major axis of the hole.
前記ボスの長軸に対して略垂直方向における前記補強部材の内縁から前記補強部材の外縁までの長さは、前記補強部材の内外径差である
請求項２に記載の羽根車。 The reinforcing member is a ring-shaped plate.
The impeller according to claim 2, wherein the length from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss is the difference between the inner and outer diameters of the reinforcing member.
前記ボスの長軸に対して略垂直方向における前記補強部材の内縁から前記補強部材の外縁までの長さが、前記穴の直径以下である
請求項２または３に記載の羽根車。 The shape of the hole is approximately circular,
The impeller according to claim 2 or 3, wherein the length from the inner edge of the reinforcing member to the outer edge of the reinforcing member in a direction substantially perpendicular to the long axis of the boss is equal to or less than the diameter of the hole.
前記開口の形状は略円であり、
前記開口の直径は、前記穴の直径よりも小さい
請求項１から４のいずれか一項に記載の羽根車。 The shape of the hole is approximately circular,
The shape of the opening is approximately circular and
The impeller according to any one of claims 1 to 4, wherein the diameter of the opening is smaller than the diameter of the hole.
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