JP5116533B2 - Sliding bearing device and pump device - Google Patents

Sliding bearing device and pump device Download PDF

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JP5116533B2
JP5116533B2 JP2008090840A JP2008090840A JP5116533B2 JP 5116533 B2 JP5116533 B2 JP 5116533B2 JP 2008090840 A JP2008090840 A JP 2008090840A JP 2008090840 A JP2008090840 A JP 2008090840A JP 5116533 B2 JP5116533 B2 JP 5116533B2
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bearing
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JP2009243589A (en
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雅史 井上
晃 庄崎
修 名越
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Kubota Corp
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Description

本発明は、例えば無注水のドライ状態と水によって潤滑される注水状態との両方の状態で使用される滑り軸受装置、および、この滑り軸受装置を備えたポンプ装置に関する。   The present invention relates to a sliding bearing device used in both a dry state in which no water is poured and a water pouring state lubricated by water, and a pump device including the sliding bearing device.

従来、例えば、図１３に示すように、ケーシング８２の下端に吸込口８３を有する立軸斜流ポンプ装置８１がある。ケーシング８２内には回転自在な主軸８４が挿通されており、主軸８４の下端に羽根車８５が設けられている。ケーシング８２の上部には、主軸８４を回転駆動させる駆動装置８６（電動機）が設けられている。主軸８４は滑り軸受装置８７によって回転自在に支持されている。   Conventionally, for example, as shown in FIG. 13, there is a vertical shaft mixed flow pump device 81 having a suction port 83 at the lower end of a casing 82. A rotatable main shaft 84 is inserted into the casing 82, and an impeller 85 is provided at the lower end of the main shaft 84. A driving device 86 (electric motor) that rotationally drives the main shaft 84 is provided on the upper portion of the casing 82. The main shaft 84 is rotatably supported by a sliding bearing device 87.

図１４，図１５に示すように、滑り軸受装置８７は、主軸８４の外周面に摺接する軸受体８８と、軸受体８８の周囲に設けられたハウジング８９と、軸受体８８とハウジング８９との間に設けられた円筒形状の緩衝用ゴム９０とを有している。   As shown in FIGS. 14 and 15, the sliding bearing device 87 includes a bearing body 88 that is in sliding contact with the outer peripheral surface of the main shaft 84, a housing 89 provided around the bearing body 88, and the bearing body 88 and the housing 89. And a cylindrical cushioning rubber 90 provided therebetween.

ハウジング８９は、金属製の円筒形状の部材であり、ケーシング８２内に設けられた固定部材９１に固定されている。ハウジング８９の内周面には、複数本の嵌合凹部９２が形成されている。   The housing 89 is a metal cylindrical member, and is fixed to a fixing member 91 provided in the casing 82. A plurality of fitting recesses 92 are formed on the inner peripheral surface of the housing 89.

軸受体８８は円筒状の軸受シェル９３と摺接部材９４とで構成されている。摺接部材９４は、セラミックスや樹脂等からなり、軸受シェル９３の内側に圧入固定されている。摺接部材９４の内周面とポンプ装置の主軸８４の外周面とが摺接する。上記軸受シェル９３の外周面には、複数本の嵌合凹部９５が形成されている。   The bearing body 88 includes a cylindrical bearing shell 93 and a sliding contact member 94. The sliding contact member 94 is made of ceramics, resin, or the like, and is press-fitted and fixed inside the bearing shell 93. The inner peripheral surface of the sliding contact member 94 and the outer peripheral surface of the main shaft 84 of the pump device are in sliding contact. A plurality of fitting recesses 95 are formed on the outer peripheral surface of the bearing shell 93.

緩衝用ゴム９０の内外周面には、上記嵌合凹部９２，９５に嵌合する嵌合凸部９６，９７が形成されている。緩衝用ゴム９０には、軸方向に沿って直線状の貫通孔９８が複数形成されており、これら貫通孔９８によって緩衝用ゴム９０のばね定数が所定の値に調整される。   On the inner and outer peripheral surfaces of the cushioning rubber 90, fitting convex portions 96 and 97 that fit into the fitting concave portions 92 and 95 are formed. A plurality of linear through holes 98 are formed in the shock absorbing rubber 90 along the axial direction, and the spring constant of the shock absorbing rubber 90 is adjusted to a predetermined value by these through holes 98.

これによると、主軸８４が所定の回転方向に回転すると、主軸８４の外周面が摺接部材９４の内周面に摺接する。この際、緩衝用ゴム９０の各嵌合凸部９６，９７がハウジング８９の嵌合凹部９２と軸受シェル９３の嵌合凹部９５とに嵌合しているため、軸受体８８は、回り止めされ、主軸８４と共回りすることはない。   According to this, when the main shaft 84 rotates in a predetermined rotation direction, the outer peripheral surface of the main shaft 84 comes into sliding contact with the inner peripheral surface of the sliding contact member 94. At this time, since the fitting convex portions 96 and 97 of the cushioning rubber 90 are fitted in the fitting concave portion 92 of the housing 89 and the fitting concave portion 95 of the bearing shell 93, the bearing body 88 is prevented from rotating. The main shaft 84 does not rotate together.

上記立軸斜流ポンプ装置８１は先行待機運転を行うものであり、揚水を行う揚水運転と、揚水を行わない待機運転とに切り替え可能である。運転開始時は、待機運転に切り替えた状態で、駆動装置８６を駆動し、主軸８４の回転速度を所定の回転速度まで次第に上昇させる。この際、滑り軸受装置８７は自揚水による潤滑作用が発揮されないドライ状態であるため、滑り軸受装置８７に対する主軸８４の摺動抵抗が増大する。   The vertical shaft mixed-flow pump device 81 performs a preliminary standby operation, and can be switched between a pumping operation in which pumping is performed and a standby operation in which pumping is not performed. At the start of operation, the drive device 86 is driven in a state of switching to standby operation, and the rotational speed of the main shaft 84 is gradually increased to a predetermined rotational speed. At this time, since the sliding bearing device 87 is in a dry state in which the lubricating action due to self-lifting water is not exhibited, the sliding resistance of the main shaft 84 with respect to the sliding bearing device 87 increases.

主軸８４の回転速度が所定の回転速度に達した後、吸水位が上昇して設定水位Ｈに達すると、待機運転から揚水運転に切り替えて、揚水を開始する。この際、主軸８４の回転速度は所定の回転速度に保たれており、また、自揚水によって滑り軸受装置８７が潤滑および冷却されるため、滑り軸受装置８７に対する主軸８４の摺動抵抗が減少する。   After the rotational speed of the main shaft 84 reaches a predetermined rotational speed, when the water absorption level rises and reaches the set water level H, the standby operation is switched to the pumping operation, and the pumping is started. At this time, the rotation speed of the main shaft 84 is maintained at a predetermined rotation speed, and the sliding bearing device 87 is lubricated and cooled by the self-pumping water, so that the sliding resistance of the main shaft 84 with respect to the sliding bearing device 87 is reduced. .

その後、吸水位が設定水位Ｈよりも低下し、立軸斜流ポンプ装置８１を引き続き駆動させる必要が無いと判断された場合、駆動装置８６の駆動を停止させて、ケーシング８２内の水を吸込口８３から排出する。この際、主軸８４には駆動装置８６の駆動トルクが作用せず、主軸８４は、自揚水による潤滑作用が発揮されないドライ状態で、惰性で回転しながら所定の回転速度から次第に減速し、最終的に停止する。   Thereafter, when it is determined that the water absorption level is lower than the set water level H and it is not necessary to continue to drive the vertical shaft diagonal flow pump device 81, the drive of the drive device 86 is stopped and the water in the casing 82 is sucked into the suction port. Eject from 83. At this time, the driving torque of the driving device 86 does not act on the main shaft 84, and the main shaft 84 gradually decelerates from a predetermined rotational speed while rotating with inertia in a dry state where the lubricating action due to self-pumping water is not exhibited. To stop.

また、緩衝用ゴム９０の径方向の荷重の増加分ΔＰに対する径方向の変位の増加分をΔＲとすると、軸受装置８７のばね定数がΔＰ／ΔＲで定義される。緩衝用ゴム９０に形成される貫通孔９８の数を減少させることにより、緩衝用ゴム９０を用いた軸受装置８７のばね定数が増大する。反対に、貫通孔９８の数を増加させることにより、緩衝用ゴム９０を用いた軸受装置８７のばね定数が低下する。   Further, assuming that the increase in radial displacement relative to the increase in load ΔP in the radial direction of the buffer rubber 90 is ΔR, the spring constant of the bearing device 87 is defined by ΔP / ΔR. By reducing the number of through holes 98 formed in the buffer rubber 90, the spring constant of the bearing device 87 using the buffer rubber 90 is increased. On the contrary, by increasing the number of through holes 98, the spring constant of the bearing device 87 using the buffer rubber 90 is lowered.

また、図１６は他の従来の滑り軸受装置１００の縦断面図であり、円筒状の軸受体１０２の下部にフランジ部１０３が設けられ、軸受体１０２の回転を阻止するための回り止め部材１０１がフランジ部１０３に設けられて軸方向に挿通されている。
特開２００２−２６６７９２ FIG. 16 is a longitudinal sectional view of another conventional sliding bearing device 100. A flange portion 103 is provided at a lower portion of a cylindrical bearing body 102, and a rotation preventing member 101 for preventing the rotation of the bearing body 102. Is provided in the flange portion 103 and is inserted in the axial direction.
JP 2002-266792

上記の従来形式では、揚水運転中に、径方向の比較的大きな荷重Ｐが軸受体８８に作用し、このような径方向の大きな荷重Ｐを十分に受けるために、緩衝用ゴム９０の貫通孔９８の数を減少させて緩衝用ゴム９０を用いた軸受装置８７のばね定数を増大させている。   In the above-described conventional type, a relatively large load P in the radial direction acts on the bearing body 88 during the pumping operation, and in order to sufficiently receive such a large load P in the radial direction, The spring constant of the bearing device 87 using the cushioning rubber 90 is increased by decreasing the number 98.

しかしながら、上記のように軸受装置８７のばね定数を増大させると、これに応じてポンプ装置８１全体の固有振動数も上昇する。このため、駆動装置８６の駆動が停止して、主軸８４がドライ状態で惰性で回転しながら所定の回転速度から次第に減速していく際、主軸８４の回転速度が十分に低下していない高速の時に、ポンプ装置８１の固有振動数と一致して共振が発生し、主軸８４の後ろ回り振動を誘発するので、主軸８４の回転速度の高さに応じた大きな力（衝撃）が発生するといった問題がある。   However, when the spring constant of the bearing device 87 is increased as described above, the natural frequency of the pump device 81 as a whole increases accordingly. For this reason, when the drive of the drive device 86 is stopped and the main shaft 84 is gradually decelerated from the predetermined rotation speed while rotating in inertia in the dry state, the rotation speed of the main shaft 84 is not sufficiently reduced. Sometimes, resonance occurs in accordance with the natural frequency of the pump device 81 and induces backward vibration of the main shaft 84, so that a large force (impact) corresponding to the rotational speed of the main shaft 84 is generated. There is.

また、主軸８４は惰性で回転しているため、共振周波数を通過せしめるだけの充分に強大なトルクすなわち減速力を持たず、共振を回避することができないという問題や、複数存在する全ての固有振動数を充分に高くすることによって共振を回避するのは、非現実的な剛性を要するという問題がある。   Further, since the main shaft 84 rotates by inertia, there is a problem that the resonance cannot be avoided because there is not a torque that is sufficiently strong to pass the resonance frequency, that is, a deceleration force, and all the natural vibrations that exist in plural. Avoiding resonance by making the number sufficiently high has the problem of requiring unrealistic rigidity.

反対に、緩衝用ゴム９０の貫通孔９８の数を増加させて緩衝用ゴム９０を用いた軸受装置８７のばね定数を低減させると、これに応じて固有振動数も低下するが、緩衝用ゴム９０が径方向に変位し易くなるため、軸受体８８に作用する径方向の荷重Ｐを十分に受けることができなくなる。したがって、径方向の荷重Ｐに対する軸受体８８の径方向への変位量が増大し、径方向の荷重Ｐに対して主軸８４が径方向へ大きく変位して、羽根車８５がケーシング８２の内周面に接触するといった問題がある。   On the contrary, when the number of through holes 98 of the shock absorbing rubber 90 is increased to reduce the spring constant of the bearing device 87 using the shock absorbing rubber 90, the natural frequency is also lowered accordingly. Since 90 is easily displaced in the radial direction, the radial load P acting on the bearing body 88 cannot be sufficiently received. Therefore, the amount of displacement of the bearing body 88 in the radial direction with respect to the radial load P increases, the main shaft 84 is greatly displaced in the radial direction with respect to the radial load P, and the impeller 85 moves to the inner periphery of the casing 82. There is a problem of touching the surface.

更に、主軸８４の回転速度が変化しない場合であっても、ドライ状態において軸受体８８の摺動面は異物の混入等に起因して摩擦条件が変化して共振を起こす場合があり、この場合、主軸８４は駆動装置８６の駆動力の供給が継続する、いわゆる強制振動状態に陥る。このような主軸８４の強制振動を外部と遮断するためには、前述のばね定数を十分に低くする必要があるが、上記と同様に羽根車８５とケーシング８２との接触等の問題があるので、振動を遮断することができないという問題がある。   Further, even when the rotational speed of the main shaft 84 does not change, the sliding surface of the bearing body 88 may resonate due to the change of friction conditions due to foreign matters mixed in the dry state. The main shaft 84 falls into a so-called forced vibration state in which the driving force of the driving device 86 continues to be supplied. In order to block such forced vibration of the main shaft 84 from the outside, it is necessary to make the aforementioned spring constant sufficiently low, but there is a problem such as contact between the impeller 85 and the casing 82 as described above. There is a problem that vibration cannot be cut off.

本発明は、共振時に発生する力（衝撃）を低減することができるとともに、軸受体に作用する径方向の荷重を十分に受けることができる滑り軸受装置、および、このような滑り軸受装置を備えたポンプ装置を提供することを目的とする。   The present invention includes a sliding bearing device capable of reducing a force (impact) generated at the time of resonance and sufficiently receiving a radial load acting on the bearing body, and such a sliding bearing device. An object of the present invention is to provide a pump device.

上記目的を達成するために、本第１発明は、主軸と摺接する軸受体と、軸受体の周囲に設けられたハウジングと、軸受体とハウジングとの間に設けられた弾性体とを備えたポンプ用の滑り軸受装置であって、
軸受体の径方向の荷重の増加分ΔＰに対する軸受体の径方向の変位の増加分をΔＲとすると、軸受装置のばね定数がΔＰ／ΔＲで定義され、
前記ばね定数は、軸受体の径方向への変位が所定値を超えると、径方向への変位が所定値以下のときよりも、大きな値になるように構成されており、
弾性体は第一の弾性部材と第二の弾性部材とを有し、
第二の弾性部材が軸受体の軸方向の両端に位置し、
第一の弾性部材が第二の弾性部材間に位置し、
第一の弾性部材は、径方向の荷重が作用していないときであっても軸受体に接しているか又は近接しており、
第二の弾性部材は、径方向の荷重が作用していないとき軸受体から径方向に所定の間隔をあけて離間しており、
軸受体と第二の弾性部材との径方向の間隔が軸受体と第一の弾性部材との径方向の間隔よりも大きく、
第二の弾性部材は、軸受体の径方向への変位が所定値に達したときに軸受体に接するように構成され、
第一の弾性部材の弾性率が第二の弾性部材の弾性率よりも小さいものである。 In order to achieve the above object, the first invention includes a bearing body that is in sliding contact with the main shaft, a housing provided around the bearing body, and an elastic body provided between the bearing body and the housing. A sliding bearing device for a pump,
When the increase in radial displacement of the bearing body relative to the increase in load ΔP in the radial direction of the bearing body is ΔR, the spring constant of the bearing device is defined as ΔP / ΔR,
The spring constant is configured to have a larger value when the radial displacement of the bearing body exceeds a predetermined value than when the radial displacement is a predetermined value or less ,
The elastic body has a first elastic member and a second elastic member,
The second elastic member is located at both axial ends of the bearing body;
The first elastic member is located between the second elastic members;
The first elastic member is in contact with or close to the bearing body even when a radial load is not acting,
The second elastic member is spaced from the bearing body at a predetermined interval in the radial direction when a radial load is not applied,
The radial interval between the bearing body and the second elastic member is larger than the radial interval between the bearing body and the first elastic member,
The second elastic member is configured to contact the bearing body when the radial displacement of the bearing body reaches a predetermined value,
The elastic modulus of the first elastic member is smaller than the elastic modulus of the second elastic member .

これによると、主軸の変位によって軸受体の径方向に荷重が作用した場合、荷重の大きさに応じて弾性体が径方向に変形する。この時、上記径方向の荷重が小さく、軸受体の径方向への変位が所定値以下となる場合、軸受装置のばね定数は上記所定値を超えた場合に比べて小さくなる。   According to this, when a load acts in the radial direction of the bearing body due to the displacement of the main shaft, the elastic body is deformed in the radial direction according to the magnitude of the load. At this time, when the radial load is small and the radial displacement of the bearing body is a predetermined value or less, the spring constant of the bearing device is smaller than that when the predetermined value is exceeded.

このため、上記所定値以下に変位した場合のばね定数が上記所定値を超えて変位した場合と同じ値を有する大きなばね定数となる弾性体を用いた従来の滑り軸受装置に比べて、変位が上記所定値以下の範囲では、軸受装置の固有振動数が低下する。したがって、駆動装置を停止して、主軸がドライ状態で惰性で回転しながら所定の回転速度から次第に減速していく際、低下させた固有振動数と一致して共振が発生するのは、主軸の回転速度が十分に低下した場合である。この時点では、主軸が有する回転エネルギーは散逸して低下しており、これにより、共振時に発生する力（衝撃）が低減される。   For this reason, the displacement is smaller than that of a conventional plain bearing device using an elastic body having a large spring constant having the same value as that when the spring constant is displaced beyond the predetermined value. In the range below the predetermined value, the natural frequency of the bearing device decreases. Therefore, when the drive unit is stopped and the main shaft rotates in inertia in a dry state and gradually decelerates from a predetermined rotational speed, resonance occurs in accordance with the reduced natural frequency. This is a case where the rotation speed is sufficiently lowered. At this time, the rotational energy of the main shaft has been dissipated and reduced, thereby reducing the force (impact) generated during resonance.

また、主軸を回転駆動して揚水を行っている際、上記径方向の荷重が大きくなれば、軸受体の径方向への変位が所定値を超え、軸受装置のばね定数は上記所定値以下の場合に比べて大きくなる。これにより、上記径方向の荷重を十分に受けることができ、径方向の荷重に対する軸受体の径方向への変位量が低減される。したがって、径方向の荷重に対する主軸の径方向への変位量が低減されるため、羽根車がケーシングの内周面に接触するのを防止することができる。   Further, when pumping water by rotating the main shaft, if the radial load increases, the radial displacement of the bearing body exceeds a predetermined value, and the spring constant of the bearing device is less than the predetermined value. It becomes larger than the case. Thereby, the said radial load can fully be received and the displacement amount to the radial direction of the bearing body with respect to the radial load is reduced. Therefore, since the amount of displacement of the main shaft in the radial direction with respect to the load in the radial direction is reduced, it is possible to prevent the impeller from contacting the inner peripheral surface of the casing.

また、主軸によって軸受体の径方向に荷重が作用した場合、上記径方向の荷重が小さく、軸受体の径方向への変位が所定値以下であれば、第一の弾性部材が軸受体に接し、第二の弾性部材が軸受体から径方向に離間する。これにより、弾性体のばね定数は上記所定値を超えた場合に比べて小さくなる。 Further, when a load is applied in the radial direction of the bearing member by the spindle, the load of the radial rather small, if the displacement in the radial direction of the bearing member is less than the predetermined value, the first resilient member bearing body The second elastic member is separated from the bearing body in the radial direction. Thereby, the spring constant of an elastic body becomes small compared with the case where the said predetermined value is exceeded.

また、上記径方向の荷重が大きくなり、軸受体の径方向への変位が所定値を超えれば、第一の弾性部材が軸受体に接した状態で、さらに、第二の弾性部材が軸受体に接する。これにより、弾性体のばね定数は上記所定値以下の場合に比べて大きくなる。
また、ドライ状態（揚水しない軽負荷時）等には、軸受装置の中央部で主軸を保持するので、主軸が傾く方向に変位しても大きな反力が発生せず、このため共振し難くなる。
また、径方向の変位が所定値を超えた際に、軸受装置のばね定数が増大する軸受装置を簡単な構造で実現できる。
本第２発明は、第一の弾性部材は軸受体の軸方向の中央部に接触しているものである。 Further, when the radial load increases and the radial displacement of the bearing body exceeds a predetermined value, the second elastic member is further in contact with the bearing body and the second elastic member is further in contact with the bearing body. To touch. Thereby, the spring constant of an elastic body becomes large compared with the case below the said predetermined value.
Further, in a dry state (light load without pumping) or the like, the main shaft is held at the center portion of the bearing device, so even if the main shaft is displaced in a tilting direction, a large reaction force is not generated, and therefore it is difficult to resonate. .
Further, a bearing device in which the spring constant of the bearing device increases when the radial displacement exceeds a predetermined value can be realized with a simple structure.
In the second aspect of the invention, the first elastic member is in contact with the axial central portion of the bearing body.

本第３発明は、第一および第二の弾性部材は保持部材の内側に設けられたゴムであるものである。
これによると、製作および組み立てが容易になる。 In the third aspect of the invention, the first and second elastic members are rubber provided inside the holding member.
This facilitates production and assembly.

本第４発明は、第一の弾性部材の内周面に、周方向において複数の凹凸が形成されているものである。
これによると、径方向の変位が所定値を超えた際に、軸受装置のばね定数が増大する軸受装置を簡単な構造で実現できる。 In the fourth invention, a plurality of irregularities are formed in the circumferential direction on the inner circumferential surface of the first elastic member.
According to this, the bearing device in which the spring constant of the bearing device increases when the radial displacement exceeds a predetermined value can be realized with a simple structure.

本第５発明は、軸受体に回り止め部材が設けられ、
回り止め部材は周方向において弾性体に係合しているものである。
これによると、主軸の回転に伴って軸受体が回転してしまうのを防止することができる。そして、従来では、回り止め部材を軸方向に設けるために、軸受体にフランジ部を設けていたが、本第５発明によれば、軸受体にフランジ部を設ける必要は無くなる。これにより、軸受体の軽量化が可能になり、慣性力を減少させることができるため、大きな反力が発生せず、共振し難くなる。 In the fifth aspect of the present invention, the bearing member is provided with a detent member.
The anti-rotation member is engaged with the elastic body in the circumferential direction.
According to this, it is possible to prevent the bearing body from rotating as the main shaft rotates. Conventionally, in order to provide the anti-rotation member in the axial direction, the flange portion is provided in the bearing body. However, according to the fifth invention, it is not necessary to provide the flange portion in the bearing body. As a result, the weight of the bearing body can be reduced, and the inertial force can be reduced. Therefore, a large reaction force is not generated, and the resonance hardly occurs.

本第６発明は、ハウジングに、軸受体の一端部に対向する緩衝部材が設けられているものである。
これによると、主軸の回転方向および軸方向の荷重が軸受体に作用した場合の反力が減少するので、共振しにくくなる。 In the sixth invention, the housing is provided with a buffer member facing one end of the bearing body.
According to this, since the reaction force when the rotational direction of the main shaft and the axial load act on the bearing body is reduced, it is difficult to resonate.

本第７発明は、前記第１発明から第６発明のいずれか１項に記載の滑り軸受装置を備えたポンプ装置であって、
揚水を行う揚水運転と揚水を行わない待機運転とに切り替え可能であるものである。 The seventh invention is a pump device comprising the sliding bearing device according to any one of the first to sixth inventions,
It is possible to switch between a pumping operation in which pumping is performed and a standby operation in which pumping is not performed.

以上のように本発明によると、例えば主軸がドライ状態（揚水しない軽負荷状態）で惰性で回転しながら所定の回転速度から次第に減速していく際、共振するとしても、主軸の回転速度が十分に低下した時に、固有振動数と一致するので、共振時に発生する力（衝撃）が低減される。   As described above, according to the present invention, for example, when the main shaft rotates with inertia in a dry state (light load state without pumping) and gradually decelerates from a predetermined rotational speed, the rotational speed of the main shaft is sufficiently high even if it resonates. Therefore, the force (impact) generated during resonance is reduced.

また、例えば揚水により負荷が増大したときには、径方向の荷重を十分に受けることができ、径方向の荷重に対する軸受体の径方向への変位量が低減される。したがって、径方向の荷重に対する主軸の径方向への変位量が低減され、羽根車がケーシングの内周面に接触するのを防止することができる。   Further, for example, when the load increases due to pumping, the load in the radial direction can be sufficiently received, and the amount of displacement of the bearing body in the radial direction with respect to the radial load is reduced. Therefore, the amount of displacement of the main shaft in the radial direction with respect to the radial load is reduced, and the impeller can be prevented from coming into contact with the inner peripheral surface of the casing.

以下、本発明における第１の実施の形態を図面を参照して説明する。
図１，図２に示すように、１は先行待機運転が行える立軸斜流ポンプ装置（ポンプ装置の一例）である。立軸斜流ポンプ装置１のケーシング２の下端には吸込口３が形成されている。ケーシング２内には主軸４が挿通されており、主軸４の下端に羽根車５が設けられている。ケーシング２の上方には、主軸４を回転駆動させるモータ等の駆動装置６が設けられている。 Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
As shown in FIGS. 1 and 2, reference numeral 1 denotes a vertical shaft mixed flow pump device (an example of a pump device) that can perform a prior standby operation. A suction port 3 is formed at the lower end of the casing 2 of the vertical shaft mixed-flow pump device 1. A main shaft 4 is inserted into the casing 2, and an impeller 5 is provided at the lower end of the main shaft 4. A driving device 6 such as a motor for rotating the main shaft 4 is provided above the casing 2.

上記主軸４は上下複数の滑り軸受装置１１，１２によって軸心１５を中心に回転自在に支持されている。これら滑り軸受装置１１，１２はそれぞれ、ケーシング２内に設けられた固定部材１６に設けられている。また、ケーシング２には、吸込口３に空気を吸気する吸気管１７が設けられている。この吸気管１７は弁等からなる気水切替装置１８によって開閉されるように構成されている。尚、上記立軸斜流ポンプ１は、羽根車５が回転して水を吸い上げる揚水運転と、羽根車５が回転しているが水を吸い上げない待機運転（気中運転）とに切り替え可能である。   The main shaft 4 is rotatably supported around a shaft center 15 by a plurality of upper and lower plain bearing devices 11 and 12. Each of these plain bearing devices 11 and 12 is provided on a fixing member 16 provided in the casing 2. The casing 2 is provided with an intake pipe 17 that sucks air into the intake port 3. The intake pipe 17 is configured to be opened and closed by an air / water switching device 18 comprising a valve or the like. The vertical shaft mixed flow pump 1 can be switched between a pumping operation in which the impeller 5 rotates to suck up water and a standby operation (in-air operation) in which the impeller 5 rotates but does not suck up water. .

図３に示すように、上記主軸４は、軸本体４ａと、軸受箇所において軸本体４ａに外嵌された円筒状のスリーブ４ｂとで構成されており、固定部材１６を貫通している。
上記滑り軸受装置１１は以下のように構成されている。 As shown in FIG. 3, the main shaft 4 includes a shaft main body 4 a and a cylindrical sleeve 4 b that is externally fitted to the shaft main body 4 a at a bearing location, and penetrates the fixing member 16.
The sliding bearing device 11 is configured as follows.

図３〜図５に示すように、滑り軸受装置１１は、主軸４を回転自在に保持する円筒状の軸受体２０と、軸受体２０の外側周囲に配置された金属製の円筒状のハウジング２１とを有している。軸受体２０はハウジング２１内に設けられており、軸受体２０とハウジング２１との間には、弾性体２２が設けられている。   As shown in FIGS. 3 to 5, the sliding bearing device 11 includes a cylindrical bearing body 20 that rotatably holds the main shaft 4, and a metal cylindrical housing 21 that is disposed around the outside of the bearing body 20. And have. The bearing body 20 is provided in the housing 21, and an elastic body 22 is provided between the bearing body 20 and the housing 21.

軸受体２０は、金属製の円筒状のシェル２３と、シェル２３の内周側に取付けられた円筒状の摺接部材２４とで構成されている。また、摺接部材２４は、例えばセラミック製であり、主軸４に外嵌されており、内周面が主軸４のスリーブ４ｂに摺接自在である。   The bearing body 20 includes a metal cylindrical shell 23 and a cylindrical sliding contact member 24 attached to the inner peripheral side of the shell 23. The slidable contact member 24 is made of, for example, ceramic and is externally fitted to the main shaft 4, and an inner peripheral surface thereof is slidably contactable with the sleeve 4 b of the main shaft 4.

また、ハウジング２１は、固定部材１６に設けられた円筒状の胴部２１ａと、胴部２１ａの上部に設けられた上部カバー２１ｂと、胴部２１ａの下部に設けられた下部カバー２１ｃとを有している。   The housing 21 has a cylindrical body portion 21a provided on the fixing member 16, an upper cover 21b provided on the upper portion of the body portion 21a, and a lower cover 21c provided on the lower portion of the body portion 21a. is doing.

弾性体２２は、金属製で円筒状の保持部材２６と、保持部材２６の内周面に取り付けられた第一および第二の弾性部材２７，２８とを有している。保持部材２６は、軸方向において複数個（図３では３個）の保持リング３０に分割されており、ハウジング２１の胴部２１ａ内に嵌め込まれ、複数のねじ２９によって取付け固定されている。尚、保持部材２６は３個の保持リング３０からなるが、３個以外の複数個でもよい。   The elastic body 22 includes a metal-made cylindrical holding member 26 and first and second elastic members 27 and 28 attached to the inner peripheral surface of the holding member 26. The holding member 26 is divided into a plurality of (three in FIG. 3) holding rings 30 in the axial direction, is fitted into the body portion 21 a of the housing 21, and is fixedly attached by a plurality of screws 29. The holding member 26 includes three holding rings 30, but a plurality other than three may be used.

第一および第二の弾性部材２７，２８は円環状に形成され、第二の弾性部材２８は保持部材２６の軸方向における両端部（上下両端部）に位置し、第一の弾性部材２７は両第二の弾性部材２８間に位置している。このような構成により、第一又は第二の弾性部材２７，２８を備えた複数の保持リング３０を積み重ねることで、弾性体２２を形成することができるため、組み立て性が向上する。尚、保持部材２６は円筒状でなくてもよく、円筒の一部や角筒状であってもよい。   The first and second elastic members 27, 28 are formed in an annular shape, the second elastic member 28 is located at both ends (upper and lower ends) in the axial direction of the holding member 26, and the first elastic member 27 is It is located between both the second elastic members 28. With such a configuration, the elastic body 22 can be formed by stacking the plurality of holding rings 30 including the first or second elastic members 27 and 28, so that the assemblability is improved. The holding member 26 may not be cylindrical, but may be a part of a cylinder or a rectangular tube.

図６に示すように、第一の弾性部材２７の内周面には、周方向において複数の凹部３１と凸部３２とが形成されている。この凹部３１の大きさを変えることで軸受装置１１のばね定数を調整することができる。また、第二の弾性部材２８の内周面には、軸方向の溝３３が周方向において所定間隔毎に複数形成されている。尚、第一の弾性部材２７はシェル２３の軸方向（上下方向）における中央部に接触している。   As shown in FIG. 6, a plurality of concave portions 31 and convex portions 32 are formed on the inner peripheral surface of the first elastic member 27 in the circumferential direction. The spring constant of the bearing device 11 can be adjusted by changing the size of the recess 31. A plurality of axial grooves 33 are formed at predetermined intervals in the circumferential direction on the inner circumferential surface of the second elastic member 28. The first elastic member 27 is in contact with the central portion of the shell 23 in the axial direction (vertical direction).

軸受体２０のシェル２３には、径方向外向きに突出する複数の回り止めねじ３５（回り止め部材の一例）が設けられている。第一および第二の弾性部材２７，２８にはそれぞれ、内外周面に開口する複数の係止孔３６が形成されている。また、ハウジング２１の胴部２１ａと弾性体２２の保持部材２６とには、胴部２１ａの外周面と保持部材２６の内周面とに貫通する複数の貫通孔３７が形成され、これら各貫通孔３７と各係止孔３６とが径方向において連通している。各回り止めねじ３５は各係止孔３６内に挿入され、これによって、各回り止めねじ３５は周方向において各弾性部材２７，２８に係合している。   The shell 23 of the bearing body 20 is provided with a plurality of anti-rotation screws 35 (an example of an anti-rotation member) protruding outward in the radial direction. Each of the first and second elastic members 27 and 28 is formed with a plurality of locking holes 36 that open to the inner and outer peripheral surfaces. The body 21a of the housing 21 and the holding member 26 of the elastic body 22 are formed with a plurality of through holes 37 penetrating the outer peripheral surface of the body 21a and the inner peripheral surface of the holding member 26. The hole 37 and each locking hole 36 communicate with each other in the radial direction. Each detent screw 35 is inserted into each retaining hole 36, whereby each detent screw 35 is engaged with each elastic member 27, 28 in the circumferential direction.

図３〜図５に示すように、第一の弾性部材２７の内周面は、主軸４が停止しているときであっても、軸受体２０のシェル２３の外周面に接触している。また、第二の弾性部材２８の内周面は、主軸４が停止しているとき、上記シェル２３の外周面から径方向へ所定の間隔Ｓをあけて離間している。   As shown in FIGS. 3 to 5, the inner peripheral surface of the first elastic member 27 is in contact with the outer peripheral surface of the shell 23 of the bearing body 20 even when the main shaft 4 is stopped. Further, the inner peripheral surface of the second elastic member 28 is spaced apart from the outer peripheral surface of the shell 23 by a predetermined distance S when the main shaft 4 is stopped.

ハウジング２１の上部カバー２１ｂの内側と下部カバー２１ｃの内側とには、円環状の上部の緩衝部材３９と下部の緩衝部材４０とが設けられている。上部の緩衝部材３９は軸受体２０のシェル２３の上方に対向し、下部の緩衝部材４０は、軸受体２０のシェル２３の下方に対向して、シェル２３の下端部を下方から支持する。   An annular upper buffer member 39 and a lower buffer member 40 are provided on the inner side of the upper cover 21 b and the lower cover 21 c of the housing 21. The upper buffer member 39 faces the upper side of the shell 23 of the bearing body 20, and the lower buffer member 40 faces the lower side of the shell 23 of the bearing body 20 and supports the lower end portion of the shell 23 from below.

第一および第二の弾性部材２７，２８と上部および下部の緩衝部材３９，４０との材質はゴムであり、このうち、第一の弾性部材２７と上部および下部の緩衝部材３９，４０とには柔軟なゴムが用いられている。また、第二の弾性部材２８には、第一の弾性部材２７よりも硬いゴムが用いられている。尚、第二の弾性部材２８の弾性係数は第一の弾性部材２７の弾性係数の約２〜３倍に設定されている。   The material of the first and second elastic members 27 and 28 and the upper and lower buffer members 39 and 40 is rubber. Among these, the first elastic member 27 and the upper and lower buffer members 39 and 40 Is made of flexible rubber. The second elastic member 28 is made of a harder rubber than the first elastic member 27. The elastic coefficient of the second elastic member 28 is set to about 2 to 3 times the elastic coefficient of the first elastic member 27.

図７に示すように、弾性体２２の径方向の荷重Ｐの増加分ΔＰに対する径方向の変位Ｒの増加分をΔＲとすると、軸受装置１１のばね定数がΔＰ／ΔＲで定義される。また、図８のグラフは、軸受体２０の径方向への変位Ｒと径方向の荷重Ｐとの関係を示すものである。   As shown in FIG. 7, when the increase in the radial displacement R with respect to the increase ΔP in the radial load P of the elastic body 22 is ΔR, the spring constant of the bearing device 11 is defined as ΔP / ΔR. The graph of FIG. 8 shows the relationship between the radial displacement R of the bearing body 20 and the radial load P.

これによると、ばね定数（実線のグラフ（イ）の傾きに相当）は、軸受体２０の径方向への変位Ｒが所定値Ａを超えると、上記変位Ｒが所定値Ａ以下のときよりも、大きな値になるように構成されている。第二の弾性部材２８の内周面は、軸受体２０の径方向への変位Ｒが所定値Ａに達したときに、所定の間隔Ｓが０になって、軸受体２０のシェル２３の外周面に接触するように構成されている。   According to this, when the displacement R in the radial direction of the bearing body 20 exceeds a predetermined value A, the spring constant (corresponding to the slope of the solid line graph (A)) is greater than when the displacement R is not more than the predetermined value A. , Configured to be a large value. The inner circumferential surface of the second elastic member 28 has a predetermined interval S of 0 when the radial displacement R of the bearing body 20 reaches a predetermined value A, and the outer periphery of the shell 23 of the bearing body 20 It is comprised so that a surface may be contacted.

ここで、図８のグラフ（イ）において、径方向への変位Ｒが０から所定値Ａまでの範囲のばね定数（グラフ（イ）の傾き）は、第一の弾性部材２７のみが軸受体２０のシェル２３に接触し、第二の弾性部材２８はシェル２３から離間しているため、第一の弾性部材２７のみが関与する第１のばね定数ｋａになる。   Here, in the graph (A) in FIG. 8, only the first elastic member 27 has a spring constant (inclination of the graph (A)) in the range where the radial displacement R is from 0 to a predetermined value A. Since the second elastic member 28 is in contact with the 20 shells 23 and is separated from the shell 23, the first spring constant ka in which only the first elastic member 27 is involved is obtained.

また、径方向への変位Ｒが所定値Ａよりも大きい範囲のばね定数は、第一の弾性部材２７と第二の弾性部材２８とが共にシェル２３に接触しているため、第一の弾性部材２７と第二の弾性部材２８とを合わせた第２のばね定数ｋｂになる。この第２のばね定数ｋｂは第１のばね定数ｋａよりも大きな値である。尚、参考として、二点鎖線のグラフ（ロ）は第一の弾性部材２７のみで軸受装置１１を構成したときのばね定数を示し、点線のグラフ（ハ）は第二の弾性部材２８のみで軸受装置１１を構成したときのばね定数を示している。このように弾性率の異なる弾性部材２７，２８を用いることで、所定値Ａの変位量を境にして軸受装置１１のばね定数を大きく変えることができる。   Further, the spring constant in the range where the radial displacement R is larger than the predetermined value A has the first elasticity because both the first elastic member 27 and the second elastic member 28 are in contact with the shell 23. The second spring constant kb is obtained by combining the member 27 and the second elastic member 28. The second spring constant kb is larger than the first spring constant ka. For reference, a two-dot chain line graph (B) shows the spring constant when the bearing device 11 is composed of only the first elastic member 27, and a dotted line graph (C) shows only the second elastic member 28. The spring constant when the bearing apparatus 11 is comprised is shown. As described above, by using the elastic members 27 and 28 having different elastic moduli, the spring constant of the bearing device 11 can be greatly changed with the displacement amount of the predetermined value A as a boundary.

尚、従来の軸受装置であってもゴムの材料特性やその構造から、主軸の径方向の変位が大きくなるとばね定数は徐々に増加するが、本発明で言うばね定数の変化は図８に示すような大きな変化を言う。   Even in the conventional bearing device, the spring constant gradually increases as the radial displacement of the main shaft increases due to the material properties and structure of the rubber. The change in the spring constant referred to in the present invention is shown in FIG. Say such a big change.

尚、図２に示す別の滑り軸受装置１２は、上記滑り軸受装置１１と同じ構造であり、滑り軸受装置１１とは上下反対向きに設けられている。
以下、上記構成における作用を説明する。 2 has the same structure as that of the slide bearing device 11, and is provided in an upside down direction with respect to the slide bearing device 11.
Hereinafter, the operation of the above configuration will be described.

上記立軸斜流ポンプ装置１は先行待機運転を行うものであり、図９のグラフに示すように、運転開始時は、気水切替装置１８を開いて待機運転に切り替え、この状態で、駆動装置６を駆動し、主軸４の回転速度を所定の回転速度Ｖまで次第に上昇させる。この際、滑り軸受装置１１，１２は自揚水による潤滑作用が発揮されないドライ状態である。   As shown in the graph of FIG. 9, the vertical shaft mixed-flow pump device 1 performs a preliminary standby operation. At the start of the operation, the air / water switching device 18 is opened to switch to the standby operation. 6 is driven, and the rotational speed of the main shaft 4 is gradually increased to a predetermined rotational speed V. At this time, the sliding bearing devices 11 and 12 are in a dry state in which the lubricating action by self-lifting water is not exhibited.

主軸４の回転速度が所定の回転速度Ｖに達した後、吸水位が上昇して設定水位Ｈに達すると、気水切替装置１８を閉じて待機運転から揚水運転に切り替え、揚水を開始する。この際、主軸４の回転速度（角速度）は所定の回転速度Ｖに保たれており、また、自揚水によって滑り軸受装置１１，１２が潤滑および冷却されるため、滑り軸受装置１１，１２に対する主軸４の摺動抵抗が減少する。   After the rotational speed of the main shaft 4 reaches the predetermined rotational speed V, when the water absorption level rises and reaches the set water level H, the air / water switching device 18 is closed to switch from the standby operation to the pumping operation, and the pumping is started. At this time, the rotational speed (angular speed) of the main shaft 4 is maintained at a predetermined rotational speed V, and the sliding bearing devices 11 and 12 are lubricated and cooled by the self-pumping water. 4 sliding resistance is reduced.

その後、吸水位が設定水位Ｈよりも低下し、立軸斜流ポンプ装置１を引き続き駆動させる必要が無いと判断された場合、気水切替装置１８を開き、駆動装置６の駆動を停止させて、ケーシング２内の水を吸込口３から排出し、運転を停止する。この際、主軸４には駆動装置６の駆動トルクが作用せず、主軸４は、自揚水による潤滑作用が発揮されないドライ状態で、惰性で回転しながら所定の回転速度Ｖから次第に減速し、最終的に停止する。   After that, when it is determined that the water absorption level is lower than the set water level H and it is not necessary to continue driving the vertical shaft diagonal flow pump device 1, the air / water switching device 18 is opened, and the drive of the drive device 6 is stopped. The water in the casing 2 is discharged from the suction port 3 and the operation is stopped. At this time, the driving torque of the driving device 6 does not act on the main shaft 4, and the main shaft 4 gradually decelerates from a predetermined rotational speed V while rotating with inertia in a dry state where the lubricating action due to self-lifting water is not exhibited. Stop.

運転中、主軸４によって軸受体２０の径方向に荷重Ｐが作用した場合、この荷重Ｐが小さく、軸受体２０の径方向への変位Ｒが所定値Ａ以下であれば、第一の弾性部材２７のみが軸受体２０のシェル２３に接触し、第二の弾性部材２８はシェル２３から離間した状態となる。これにより、弾性体２０のばね定数は第２のばね定数ｋｂよりも小さい第１のばね定数ｋａとなる。   During operation, when a load P is applied in the radial direction of the bearing body 20 by the main shaft 4, if the load P is small and the radial displacement R of the bearing body 20 is equal to or less than a predetermined value A, the first elastic member Only 27 comes into contact with the shell 23 of the bearing body 20, and the second elastic member 28 is separated from the shell 23. Thereby, the spring constant of the elastic body 20 becomes the first spring constant ka smaller than the second spring constant kb.

また、上記径方向の荷重Ｐが大きく、軸受体２０の径方向への変位Ｒが所定値Ａを超えれば、第一の弾性部材２７が軸受体２０のシェル２３に接触した状態で、さらに、第二の弾性部材２８もシェル２３に接触する。これにより、軸受装置１１のばね定数は第１のばね定数ｋａよりも大きい第２のばね定数ｋｂとなる。   Further, if the radial load P is large and the radial displacement R of the bearing body 20 exceeds a predetermined value A, the first elastic member 27 is in contact with the shell 23 of the bearing body 20, The second elastic member 28 also contacts the shell 23. As a result, the spring constant of the bearing device 11 becomes a second spring constant kb that is larger than the first spring constant ka.

ここで、図１０のグラフは、主軸４の回転角速度ω（周波数（Ｈｚ））と振動伝達率Ｔｒと回転不釣合い力との関係を示すものである。実線のグラフ（ニ）は従来のポンプ装置における回転角速度ωと振動伝達率Ｔｒとの関係を示しており、大きなばね定数ｋｂを有する滑り軸受装置である。また、点線のグラフ（ホ）は本実施の形態のポンプ装置１における回転角速度ωと振動伝達率Ｔｒとの関係を示しており、大小２種類のばね定数ｋａ，ｋｂを有する滑り軸受装置１１（１２）である。   Here, the graph of FIG. 10 shows the relationship among the rotational angular velocity ω (frequency (Hz)) of the main shaft 4, the vibration transmissibility Tr, and the rotational unbalance force. The solid line graph (d) shows the relationship between the rotational angular velocity ω and the vibration transmissibility Tr in the conventional pump device, and is a sliding bearing device having a large spring constant kb. A dotted line graph (e) shows the relationship between the rotational angular velocity ω and the vibration transmissibility Tr in the pump device 1 of the present embodiment, and the plain bearing device 11 (having two types of spring constants ka and kb). 12).

これによると、本実施の形態では第１のばね定数ｋａが第２のばね定数ｋｂより小さいため、グラフ（ホ）に示すように、本実施の形態のポンプ装置１の固有振動数Ｂ１が従来のポンプ装置の固有振動数Ｂ２よりも低下する。   According to this, since the first spring constant ka is smaller than the second spring constant kb in the present embodiment, as shown in the graph (e), the natural frequency B1 of the pump device 1 according to the present embodiment is conventional. This is lower than the natural frequency B2 of the pump device.

したがって、図９のグラフに示すように、運転停止時、駆動装置６が停止して、主軸４がドライ状態で惰性で回転しながら所定の回転速度Ｖから次第に減速していく際、すなわち、図１０に示すように主軸４の角速度ωが左へ低下していく際、固有振動数Ｂ２より低くなった固有振動数Ｂ１に達したときに共振が発生するが、この時の主軸４の角速度ω（すなわち回転速度）が十分に低下しているので、共振時に発生する力（衝撃）が低減される。   Therefore, as shown in the graph of FIG. 9, when the operation is stopped, the drive device 6 is stopped, and when the main shaft 4 is gradually decelerated from the predetermined rotational speed V while rotating by inertia in a dry state, As shown in FIG. 10, when the angular velocity ω of the main shaft 4 decreases to the left, resonance occurs when the natural frequency B1 lower than the natural frequency B2 is reached. The angular velocity ω of the main shaft 4 at this time Since (ie, the rotational speed) is sufficiently reduced, the force (impact) generated at the time of resonance is reduced.

また、上記図１０の一点鎖線のグラフ（ヘ）は主軸４の回転角速度ωと回転不釣合い力との関係を示すものであり、回転不釣合い力は、図７に示すように、主軸４が所定の方向Ｃに回転しているときの軸受体２０の摺接面（すなわち摺接部材２４の内周面）に対する垂直抗力Ｎと同じになり、下記の式１で示される。   Also, the dot-dash line graph (f) in FIG. 10 shows the relationship between the rotational angular velocity ω of the main shaft 4 and the rotational unbalance force, and the rotational unbalance force is shown in FIG. This is the same as the normal resistance N to the sliding contact surface of the bearing body 20 (that is, the inner peripheral surface of the sliding contact member 24) when rotating in the predetermined direction C, and is expressed by the following formula 1.

回転不釣合い力＝垂直抗力Ｎ＝Ｍ×ｅ×ω２ 式１
尚、Ｍは主軸４の質量、ｅは比不釣合量（主軸４の図心と重心との距離）である。
また、主軸４が回転しているときの摩擦力Ｆとその偶力−Ｆとは下記の式２，式３で示される。 Rotation unbalance force = Vertical drag N = M × e × ω 2 Formula 1
Here, M is the mass of the main shaft 4 and e is the unbalance amount (the distance between the centroid of the main shaft 4 and the center of gravity).
The frictional force F and the couple -F when the main shaft 4 is rotating are expressed by the following formulas 2 and 3.

Ｆ＝μ×Ｎ＝μ×Ｍ×ｅ×ω２ 式２
尚、μは摩擦係数である。
−Ｆ＝−μ×Ｍ×ｅ×ω２ 式３
上記式３に示すように、偶力−Ｆは主軸４の角速度の２乗に比例するため、本実施の形態のポンプ装置１が固有振動数Ｂ１（図１０のグラフ（ホ））で共振しているときの偶力−Ｆ１は、上記角速度ωが低いので、従来のポンプ装置が固有振動数Ｂ２（図１０のグラフ（ニ））で共振しているときの偶力−Ｆ２よりも大幅に小さくなる。これにより、主軸４の重心が主軸４の回転方向Ｃとは反対方向へ移動することによって生じる自励振動（後ろ回り振動）を抑制することができる。 F = μ × N = μ × M × e × ω 2 Formula 2
Note that μ is a friction coefficient.
−F = −μ × M × e × ω 2 Formula 3
As shown in the above equation 3, the couple -F is proportional to the square of the angular velocity of the main shaft 4, so that the pump device 1 of the present embodiment resonates at the natural frequency B1 (graph (e) in FIG. 10). Since the angular velocity ω is low, the couple -F1 is significantly greater than the couple -F2 when the conventional pump device resonates at the natural frequency B2 (graph (D) in FIG. 10). Get smaller. Thereby, the self-excited vibration (backward vibration) generated when the center of gravity of the main shaft 4 moves in the direction opposite to the rotation direction C of the main shaft 4 can be suppressed.

また、揚水運転中に径方向の荷重Ｐが増大して、図８に示すように、軸受体２０の径方向への変位Ｒが所定値Ａを超えると、弾性体２２のばね定数が小さな値の第１のばね定数ｋａから大きな値の第２のばね定数ｋｂに変わる。これにより、上記径方向の荷重Ｐを十分に受けることができ、径方向の荷重Ｐに対する軸受体２０の径方向への変位量Ｒが低減される。したがって、径方向の荷重Ｐに対する主軸４の径方向への変位量が低減されるため、羽根車５がケーシング２の内周面に接触するのを防止することができる。   Further, when the radial load P increases during the pumping operation and the radial displacement R of the bearing body 20 exceeds a predetermined value A as shown in FIG. 8, the spring constant of the elastic body 22 becomes a small value. The first spring constant ka is changed to a second spring constant kb having a large value. Thereby, the said radial load P can fully be received, and the displacement amount R to the radial direction of the bearing body 20 with respect to the radial load P is reduced. Therefore, since the amount of displacement of the main shaft 4 in the radial direction with respect to the radial load P is reduced, the impeller 5 can be prevented from contacting the inner peripheral surface of the casing 2.

また、図３に示すように、回り止めねじ３５は、各係止孔３６内に挿入され、周方向において各弾性部材２７，２８に係合しているため、主軸４の回転に伴って軸受体２０が回転してしまうのを防止することができる。   Further, as shown in FIG. 3, the rotation-preventing screw 35 is inserted into each locking hole 36 and engaged with each elastic member 27, 28 in the circumferential direction. It is possible to prevent the body 20 from rotating.

このとき、従来では、図１６に示すように、回り止め部材１０１を軸方向に設けるために、軸受体１０２にフランジ部１０３を設けていたが、本実施の形態によれば、図３に示すように、軸受体２０にフランジ部を設ける必要は無くなる。これにより、軸受体２０の軽量化が可能になり、慣性力を減少させることができるため、大きな反力が発生せず、共振し難くなる。   At this time, conventionally, as shown in FIG. 16, the flange portion 103 is provided in the bearing body 102 in order to provide the anti-rotation member 101 in the axial direction, but according to the present embodiment, it is shown in FIG. 3. Thus, it is not necessary to provide the flange portion on the bearing body 20. As a result, the weight of the bearing body 20 can be reduced, and the inertial force can be reduced. Therefore, a large reaction force is not generated and the resonance hardly occurs.

また、軸受体２０のシェル２３は上部の緩衝部材３９と下部の緩衝部材４０との上下間に挟まれているため、軸受体２０が上下方向（軸方向）にずれるのを防止することができるとともに、軸方向の荷重が軸受体２０に作用した場合の反力が減少するので、共振しにくくなる。   Further, since the shell 23 of the bearing body 20 is sandwiched between the upper and lower cushioning members 39 and 40, it is possible to prevent the bearing body 20 from shifting in the vertical direction (axial direction). At the same time, since the reaction force when an axial load acts on the bearing body 20 is reduced, it is difficult to resonate.

また、図８のグラフに示すように、変位Ｒが所定値Ａ以下の領域では、軸受装置１１のばね定数が十分に低くなるため、主軸４の強制振動を外部と遮断することができる。また、変位Ｒが所定値Ａを超えた領域では、軸受装置１１のばね定数が大きな値に切換るため、径方向の荷重Ｐに対する主軸４の径方向への変位量が抑制され、これにより、羽根車５がケーシング２に接触するのを防止できる。   Further, as shown in the graph of FIG. 8, in the region where the displacement R is equal to or less than the predetermined value A, the spring constant of the bearing device 11 is sufficiently low, so that the forced vibration of the main shaft 4 can be shut off from the outside. Further, in the region where the displacement R exceeds the predetermined value A, the spring constant of the bearing device 11 is switched to a large value, so that the amount of displacement in the radial direction of the main shaft 4 with respect to the radial load P is suppressed. The impeller 5 can be prevented from contacting the casing 2.

上記第１の実施の形態では、図３に示すように、第一の弾性部材２７の内周面は、主軸４が停止しているときであっても、軸受体２０のシェル２３の外周面に接触しているが、シェル２３の外周面から径方向へ所定の間隔Ｓよりも小さな間隔をあけて離間してもよい。   In the first embodiment, as shown in FIG. 3, the inner peripheral surface of the first elastic member 27 is the outer peripheral surface of the shell 23 of the bearing body 20 even when the main shaft 4 is stopped. However, they may be spaced apart from the outer peripheral surface of the shell 23 in the radial direction with an interval smaller than the predetermined interval S.

上記第１の実施の形態では、図６に示すように、第一の弾性部材２７を１個設けているが、複数個設けてもよい。また、第二の弾性部材２８を２個設けているが、１個又は３個以上の複数個設けてもよい。   In the first embodiment, as shown in FIG. 6, one first elastic member 27 is provided, but a plurality of first elastic members 27 may be provided. Further, although the two second elastic members 28 are provided, one or a plurality of three or more may be provided.

上記第１の実施の形態では、柔軟な（弾性率が小さく低硬度の）第一の弾性部材２７を１個と硬い（弾性率が大きく高硬度の）第二の弾性部材２８を上下２個設け、第一の弾性部材２７を両第二の弾性部材２８間に配置しているが、第２の実施の形態として、図１１に示すように、第一の弾性部材２７を上下２個と第二の弾性部材２８を１個設け、第二の弾性部材２８を両第一の弾性部材２７間に配置してもよい。   In the first embodiment, one flexible first elastic member 27 (low elastic modulus and low hardness) and two hard second elastic members 28 (high elastic modulus and high hardness) are provided at the top and bottom. The first elastic member 27 is disposed between the second elastic members 28. As a second embodiment, as shown in FIG. One second elastic member 28 may be provided, and the second elastic member 28 may be disposed between the first elastic members 27.

また、上記第１の実施の形態では、第一および第二の弾性部材２７，２８をそれぞれ保持部材２６の内周面に設けたが、第３の実施の形態として、第二の弾性部材２８を保持部材２６の内周面に設け、第二の弾性部材２８の内周面に第一の弾性部材２７を設けてもよい。   In the first embodiment, the first and second elastic members 27 and 28 are provided on the inner peripheral surface of the holding member 26. However, as the third embodiment, the second elastic member 28 is provided. May be provided on the inner peripheral surface of the holding member 26, and the first elastic member 27 may be provided on the inner peripheral surface of the second elastic member 28.

上記各実施の形態では、第一の弾性部材２７と緩衝部材３９，４０の弾性率と、第二の弾性部材２８の弾性率とが異なるものを使用しているが、これに限定されるものではなく、同じ弾性率の材料であってもよい。   In each of the above embodiments, the first elastic member 27 and the buffer members 39 and 40 have different elastic moduli from the elastic modulus of the second elastic member 28. However, the present invention is not limited to this. Instead, the same elastic modulus material may be used.

また、第４の実施の形態として、第一の弾性部材２７の弾性率を第二の弾性部材２８の弾性率より小さくしたものであってもよい。
また、第５の実施の形態として、図１２に示すように、弾性体２２を、保持部材２６と、保持部材２６の内周面に取り付けられた円筒状のゴム製の弾性部材４５とで構成してもよい。弾性部材４５の内周面には径方向内側へ突出する突出部４６が全周にわたり形成されている。 Further, as the fourth embodiment, the elastic modulus of the first elastic member 27 may be smaller than the elastic modulus of the second elastic member 28.
As a fifth embodiment, as shown in FIG. 12, the elastic body 22 includes a holding member 26 and a cylindrical rubber elastic member 45 attached to the inner peripheral surface of the holding member 26. May be. A protruding portion 46 that protrudes radially inward is formed on the inner peripheral surface of the elastic member 45 over the entire circumference.

突出部４６は、主軸４が停止しているときであっても、軸受体２０のシェル２３の外周面に接触している。また、弾性部材４５の内周面は、主軸４が停止しているとき、上記シェル２３の外周面から径方向へ所定の間隔Ｓをあけて離間している。   The protrusion 46 is in contact with the outer peripheral surface of the shell 23 of the bearing body 20 even when the main shaft 4 is stopped. Further, the inner peripheral surface of the elastic member 45 is spaced apart from the outer peripheral surface of the shell 23 by a predetermined distance S in the radial direction when the main shaft 4 is stopped.

上記各実施の形態では、第一および第二の弾性部材２７，２８としてゴムを用いたが、ゴムの代わりに金属ばねや空気ばね等を用いてもよい。
上記各実施の形態では、図３に示すように、主軸４は軸本体４ａとスリーブ４ｂとで構成されているが、スリーブ４ｂが無く、軸本体４ａのみで構成されているものでもよい。この場合、摺接部材２４が軸本体４ａの外周面に摺接する。 In each of the above embodiments, rubber is used as the first and second elastic members 27 and 28, but a metal spring, an air spring, or the like may be used instead of rubber.
In each of the above embodiments, as shown in FIG. 3, the main shaft 4 is composed of the shaft main body 4a and the sleeve 4b. In this case, the sliding contact member 24 is in sliding contact with the outer peripheral surface of the shaft body 4a.

上記各実施の形態では、軸受体２０はシェル２３と摺接部材２４とで構成されているが、シェル２３が無く、摺接部材２４のみで構成されているものでもよい。この場合、第一および第二の弾性部材２７，２８の内周面が摺接部材２４の外周面に接触する。   In each of the above-described embodiments, the bearing body 20 is configured by the shell 23 and the sliding contact member 24. However, the bearing body 20 may be configured by only the sliding contact member 24 without the shell 23. In this case, the inner peripheral surfaces of the first and second elastic members 27 and 28 are in contact with the outer peripheral surface of the sliding contact member 24.

上記各実施の形態では、弾性体２２は保持部材２６と第一および第二の弾性部材２７，２８とで構成されているが、保持部材２６が無く、第一および第二の弾性部材２７，２８のみで構成されているものでもよい。この場合、第一および第二の弾性部材２７，２８はハウジング２１の胴部２１ａの内周面に取り付けられる。   In each of the above embodiments, the elastic body 22 includes the holding member 26 and the first and second elastic members 27 and 28. However, the holding member 26 is not provided, and the first and second elastic members 27, 28 may be comprised only. In this case, the first and second elastic members 27 and 28 are attached to the inner peripheral surface of the trunk portion 21 a of the housing 21.

上記各実施の形態では、ポンプ装置の一例として立軸斜流ポンプ装置１を挙げたが、立軸軸流ポンプ装置や横軸ポンプ装置等、その他の形式のポンプ装置であってもよい。また、気水切替型の先行待機運転ポンプを例に説明したが、気水混合型の先行待機運転ポンプであってもよい。   In each of the above embodiments, the vertical shaft diagonal flow pump device 1 is described as an example of the pump device, but other types of pump devices such as a vertical shaft pump device and a horizontal shaft pump device may be used. In addition, the air / water switching type advance standby operation pump has been described as an example, but an air / water mixing type advance standby operation pump may be used.

本発明の第１の実施の形態におけるポンプ装置の縦断面図である。It is a longitudinal cross-sectional view of the pump apparatus in the 1st Embodiment of this invention. 同、ポンプ装置の羽根車の部分の縦断面図である。It is a longitudinal cross-sectional view of the impeller part of the pump device. 同、ポンプ装置の滑り軸受装置の縦断面図である。It is a longitudinal cross-sectional view of the sliding bearing device of the pump device. 図３におけるＸ１−Ｘ１矢視図である。It is a X1-X1 arrow line view in FIG. 図３におけるＸ２−Ｘ２矢視図である。FIG. 4 is an X2-X2 arrow view in FIG. 3. 同、ポンプ装置の滑り軸受装置の第一および第二の弾性部材の斜視図である。It is a perspective view of the 1st and 2nd elastic member of the sliding bearing apparatus of a pump apparatus similarly. 同、ポンプ装置の滑り軸受装置の第一の弾性部材の平面図である。It is a top view of the 1st elastic member of the slide bearing apparatus of a pump apparatus equally. 同、ポンプ装置の滑り軸受装置の軸受体の径方向への変位と径方向の荷重との関係を示すグラフである。It is a graph which shows the relationship between the displacement to the radial direction of the bearing body of the sliding bearing apparatus of a pump apparatus, and a radial load. 同、ポンプ装置の運転パターンと主軸の回転速度との関係を示すグラフである。It is a graph which shows the relationship between the driving | operation pattern of a pump apparatus, and the rotational speed of a main axis | shaft similarly. 同、ポンプ装置の主軸の角速度と振動伝達率との関係を示すグラフである。It is a graph which shows the relationship between the angular velocity of the main axis | shaft of a pump apparatus, and a vibration transmissibility similarly. 本発明の第２の実施の形態におけるポンプ装置の滑り軸受装置の縦断面図である。It is a longitudinal cross-sectional view of the sliding bearing apparatus of the pump apparatus in the 2nd Embodiment of this invention. 本発明の第５の実施の形態におけるポンプ装置の滑り軸受装置の縦断面図である。It is a longitudinal cross-sectional view of the sliding bearing apparatus of the pump apparatus in the 5th Embodiment of this invention. 従来のポンプ装置の縦断面図である。It is a longitudinal cross-sectional view of the conventional pump apparatus. 同、ポンプ装置の滑り軸受装置の縦断面図である。It is a longitudinal cross-sectional view of the sliding bearing device of the pump device. 同、ポンプ装置の滑り軸受装置の一部分の平面図である。It is a top view of a part of the sliding bearing device of the pump device. 他の従来のポンプ装置の縦断面図である。It is a longitudinal cross-sectional view of another conventional pump device.

符号の説明Explanation of symbols

１ 立軸斜流ポンプ装置（ポンプ装置）
４ 主軸
１１，１２ 滑り軸受装置
２０ 軸受体
２１ ハウジング
２２ 弾性体
２６ 保持部材
２７ 第一の弾性部材
２８ 第二の弾性部材
３１ 凹部
３２ 凸部
３５ 回り止めねじ（回り止め部材）
４０ 緩衝部材
Ａ 所定値
Ｐ 径方向の荷重
Ｒ 径方向の変位
Ｓ 所定の間隔 1 Vertical shaft mixed flow pump device (pump device)
4 Main shafts 11 and 12 Slide bearing device 20 Bearing body 21 Housing 22 Elastic body 26 Holding member 27 First elastic member 28 Second elastic member 31 Recess 32 Protrusion 35 Non-rotating screw (anti-rotating member)
40 Buffer member A Predetermined value P Radial load R Radial displacement S Predetermined spacing

Claims (7)

主軸と摺接する軸受体と、軸受体の周囲に設けられたハウジングと、軸受体とハウジングとの間に設けられた弾性体とを備えたポンプ用の滑り軸受装置であって、
軸受体の径方向の荷重の増加分ΔＰに対する軸受体の径方向の変位の増加分をΔＲとすると、軸受装置のばね定数がΔＰ／ΔＲで定義され、
前記ばね定数は、軸受体の径方向への変位が所定値を超えると、径方向への変位が所定値以下のときよりも、大きな値になるように構成されており、
弾性体は第一の弾性部材と第二の弾性部材とを有し、
第二の弾性部材が軸受体の軸方向の両端に位置し、
第一の弾性部材が第二の弾性部材間に位置し、
第一の弾性部材は、径方向の荷重が作用していないときであっても軸受体に接しているか又は近接しており、
第二の弾性部材は、径方向の荷重が作用していないとき軸受体から径方向に所定の間隔をあけて離間しており、
軸受体と第二の弾性部材との径方向の間隔が軸受体と第一の弾性部材との径方向の間隔よりも大きく、
第二の弾性部材は、軸受体の径方向への変位が所定値に達したときに軸受体に接するように構成され、
第一の弾性部材の弾性率が第二の弾性部材の弾性率よりも小さいことを特徴とする滑り軸受装置。 A sliding bearing device for a pump comprising a bearing body that is in sliding contact with the main shaft, a housing provided around the bearing body, and an elastic body provided between the bearing body and the housing,
When the increase in radial displacement of the bearing body relative to the increase in load ΔP in the radial direction of the bearing body is ΔR, the spring constant of the bearing device is defined as ΔP / ΔR,
The spring constant is configured to have a larger value when the radial displacement of the bearing body exceeds a predetermined value than when the radial displacement is a predetermined value or less ,
The elastic body has a first elastic member and a second elastic member,
The second elastic member is located at both axial ends of the bearing body;
The first elastic member is located between the second elastic members;
The first elastic member is in contact with or close to the bearing body even when a radial load is not acting,
The second elastic member is spaced from the bearing body at a predetermined interval in the radial direction when a radial load is not acting,
The radial interval between the bearing body and the second elastic member is larger than the radial interval between the bearing body and the first elastic member,
The second elastic member is configured to contact the bearing body when the radial displacement of the bearing body reaches a predetermined value,
A sliding bearing device, wherein the elastic modulus of the first elastic member is smaller than the elastic modulus of the second elastic member . 第一の弾性部材は軸受体の軸方向の中央部に接触していることを特徴とする請求項１記載の滑り軸受装置。 The sliding bearing device according to claim 1, wherein the first elastic member is in contact with an axial center portion of the bearing body . 第一および第二の弾性部材は保持部材の内側に設けられたゴムであることを特徴とする請求項１または請求項２記載の滑り軸受装置。 The sliding bearing device according to claim 1 or 2, wherein the first and second elastic members are rubber provided inside the holding member. 弾性体の内周面に、周方向において複数の凹凸が形成されていることを特徴とする請求項１から請求項３のいずれか１項に記載の滑り軸受装置。 The sliding bearing device according to any one of claims 1 to 3, wherein a plurality of irregularities are formed in the circumferential direction on an inner circumferential surface of the elastic body . 軸受体に回り止め部材が設けられ、
回り止め部材は周方向において弾性体に係合していることを特徴とする請求項１から請求項４のいずれか１項に記載の滑り軸受装置。 A rotation preventing member is provided on the bearing body,
The sliding bearing device according to any one of claims 1 to 4, wherein the rotation preventing member is engaged with the elastic body in the circumferential direction . ハウジングに、軸受体の一端部に対向する緩衝部材が設けられていることを特徴とする請求項１から請求項５のいずれか１項に記載の滑り軸受装置。 The sliding bearing device according to any one of claims 1 to 5, wherein the housing is provided with a buffer member facing one end of the bearing body . 前記請求項１から請求項６のいずれか１項に記載の滑り軸受装置を備えたポンプ装置であって、A pump device comprising the sliding bearing device according to any one of claims 1 to 6,
揚水を行う揚水運転と揚水を行わない待機運転とに切り替え可能であることを特徴とするポンプ装置。A pump device characterized in that it can be switched between a pumping operation in which pumping is performed and a standby operation in which pumping is not performed.
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