WO2005057017A1 - 流体搬送機械 - Google Patents
流体搬送機械 Download PDFInfo
- Publication number
- WO2005057017A1 WO2005057017A1 PCT/JP2004/018517 JP2004018517W WO2005057017A1 WO 2005057017 A1 WO2005057017 A1 WO 2005057017A1 JP 2004018517 W JP2004018517 W JP 2004018517W WO 2005057017 A1 WO2005057017 A1 WO 2005057017A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- rotating shaft
- fluid
- magnetic levitation
- impeller
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/048—Bearings magnetic; electromagnetic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/006—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps double suction pumps
Definitions
- the present invention relates to a fluid conveyance machine, and more particularly to a fluid machine such as a pump suitable for high-speed operation.
- a magnetic levitation motor can generate a radial force by biasing a magnetic flux distribution in which two rotating magnetic fields between its rotor and stator are superimposed. That is, two rotating magnetic fields having two different numbers of poles are formed on the stator, and a superposition of the two rotating magnetic fields having different numbers of poles imparts a static magnetic force to the rotor in the radial direction, and also applies the rotating driving force to the rotor.
- a magnetic levitation motor to be applied is known.
- This magnetic levitation motor has both functions of a radial magnetic bearing and a motor, and has a function of generating a rotational driving force to the rotor and supporting the rotor in a non-contact manner with the radial wall by the magnetic levitation force.
- the function of supporting the rotating shaft in a non-contact manner in the radial direction enables the non-contact supporting of the rotating shaft even in an environment where ordinary bearings cannot be used, for example, in an ultra-low temperature air atmosphere.
- this magnetic levitation motor can be used for a fluid transfer machine that extremely mixes impurities such as ultrapure water. Is preferred.
- a normal centrifugal pump generates fluid force in the suction direction (axial direction) during operation, and the load on the axial bearing increases. Therefore, when the output of the pump is increased by an operation such as increasing the rotation speed, the axial force applied to the rotating shaft increases. In order to support the increased axial force, the axial magnetic bearing must be increased in size to cope with it, so that the shaft dimension becomes longer.
- the output of the centrifugal pump increases as the rotational speed increases, so that the same output can be obtained with a smaller impeller through high-speed rotation operation.
- This downsizing can reduce the weight of the rotating body, increase the resonance frequency of the shaft, and facilitate magnetic levitation control.
- high-speed operation of the pump induces cavitation and damages the impeller, so there is a limit to increasing the rotation speed. Disclosure of the invention
- the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a fluid conveyance machine having a compact structure capable of high-speed operation.
- a fluid conveyance machine having a small and compact structure capable of high-speed operation.
- the fluid conveyance machine includes a rotating shaft, a double suction type pump, at least one magnetic levitation motor having a function of a radial magnetic bearing that supports the rotating shaft in a non-contact manner, and a motor that rotationally drives the rotating shaft.
- the double-suction type pump has a double-suction type impeller attached to the rotating shaft, a pump casing arranged to surround the impeller, and a pressure balance mechanism for positioning the rotating shaft in the axial direction. .
- the rotary shaft is supported in a non-contact manner in the radial direction by the magnetic levitation motor, and is positioned in the thrust direction by the pressure balance mechanism of the two suction pumps.
- Axial disks can be omitted. Therefore, the length of the rotating shaft can be reduced.
- the rotating shaft is supported in a non-contact manner by a magnetic levitation motor, friction and wear of the bearing do not occur, and the rotational speed limit determined by the bending frequency due to shortening of the rotating shaft increases, making it suitable for high-speed operation.
- the structure is obtained.
- the rotation speed at which cavitation starts to occur can be increased, and cavitation hardly occurs even at high speed operation. High-speed stable pump operation is possible.
- the pump output can be increased, Impact can be achieved.
- the double suction type pump is disposed substantially at the center of the rotating shaft, and two magnetic levitation motors are disposed on both sides of the pump on the rotating shaft.
- the frequency of the axis eigenvalue increases, and the floating stability region expands to a higher frequency, which can contribute to the improvement of floating stability.
- the pump casing may include a double pump. In this case, the radial component of the fluid force acting on the rotating body can be reduced, and the energy loss can be reduced. Further, the pump casing may include a diffuser. Also according to this, the radial component of the fluid force acting on the rotating body can be reduced, and the energy loss can be reduced.
- the pressure balance mechanism includes a pair of variable gaps between both sides of the double suction type impeller and the casing, and the size of the pair of variable gaps allows the double suction type impeller to be provided. It is preferable to balance the pressure on both sides of the pressure. This makes it possible to easily and reliably position the rotating shaft provided with the pump impeller in the axial direction without using an axial disk and an axial bearing. As described above, according to the present invention, the shaft length is shortened, the influence of the cavitation is minimized, and high-speed operation is enabled. Can be provided. Brief Description of Drawings
- FIG. 1 is a front sectional view of a fluid conveyance machine according to one embodiment of the present invention.
- FIG. 2 is a cross-sectional view illustrating an example of a volume portion of the fluid conveyance machine illustrated in FIG.
- FIG. 3 is a front sectional view showing an example of the inside of the pump of the fluid conveyance machine shown in FIG.
- FIG. 4 is a cross-sectional view showing another example of the polute portion of the fluid transport machine shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
- FIGS. 1 to 4 members or Elements are denoted by the same reference numerals, and redundant description will be omitted.
- FIG. 1 shows a double suction type pump (fluid transfer machine) according to an embodiment of the present invention.
- the fluid conveying machine is provided with a double suction type pump 16 at the center.
- the rotary shaft 11 of the pump 16 is driven to rotate by magnetic levitation motors 12 and 13 arranged on both sides of the pump 16 and is not contacted by the magnetic levitation motors 12 and 13 as radial magnetic bearings.
- Displacement sensors 19 are arranged on both sides of the magnetic levitation motors 12 and 13, and the controller (not shown) controls the magnetic levitation motor based on the measured displacement of the rotating shaft 11.
- Touch down bearings 20 are arranged on both sides of the displacement sensor 19.
- the double-suction pump 16 is a centrifugal pump that includes a symmetrical impeller 21 and pressurizes fluid sucked in the axial direction from both left and right sides in the centrifugal direction (radial direction and tangential direction of the outer periphery). That is, the fluid sucked in from the suction port 17 flows through the flow paths 17 a and 17 b on both sides of the pump casing 31, and flows axially from the opening 16 a of the casing to the pump chamber 16 b ⁇ . The fluid is pressurized in the centrifugal direction by the impeller 21 and discharged from the discharge port 18 through the double / reposit 22 shown in FIG.
- FIG. 2 shows a cross-sectional configuration of a main part of the pump 16.
- a double-suction impeller 21 is fixedly attached to the rotating shaft 11, and guides the fluid pressurized in the centrifugal direction by the rotation of the impeller 21 to the discharge port 18 via the pole 22.
- the volute 22 has a partition wall 23 so that two volutes 22a and 22b can be formed, and the whole is a double / volume.
- the polytes 22a and 22b are provided with respective inlets A and B, and the inlets A and B are arranged at a rotationally symmetric position rotated 180 ° with respect to the rotation axis.
- FIG. 3 shows an enlarged cross-sectional configuration inside the pump casing.
- the impeller 21 fixed to the rotating shaft 11 has a double-suction type left-right symmetric structure, and is sucked from the openings 16a of the casings 31 on both sides in the axial direction.
- the fluid is pressurized in the centrifugal direction by the blades of the rotating impeller 21 and the double polymer
- the liquid is discharged from the discharge port 18 through the port 22 (22a, 22b).
- the pump 16 includes a pressure balance mechanism for positioning the rotary shaft 11 in the axial direction by the double suction type pump 16.
- the impeller 21 has symmetrical shrouds 32, 32, and its convex portions 32a, 32b face the inner surface of the casing 31, respectively, forming gaps. Ie, a pair of clearance between the inner surface of the convex portion 32 a and the casing 31 of the shroud 32 C A t and C AR is formed, the flow of force [[pressurized fluid is returned to the suction side of the impeller It constitutes the gap resistance of the road. Similarly, a pair of gaps C R , C R are also formed between the protrusion 32 b of the shroud 32 and the inner peripheral surface of the casing 31, and similarly, a flow path in which the pressurized fluid returns to the suction side of the impeller Of the gap resistance.
- this pressure balance mechanism is as follows. If the rotating shaft 11 moves to the left in the figure, the gap CAL on the left becomes smaller and the gap CAR on the right becomes larger. Therefore, the pressure of the chamber 35 L becomes high, whereas, the pressure P R of the chamber 35 R may turn reduced. Due to the difference between the pressures P L and P R , the rotating shaft 11 fixed to the shrouds 32 and 32 is returned to the substantially central portion of the chambers 35 L and 35 R, and is positioned there. You. Since the protrusion 32 b of the shroud 32 has sufficient axial length to lie along the inner peripheral surface 31 b of the casing 31, the rotary shaft 1 1 is a gap between C R be moved in the axial direction constant Can be kept. Thereby, the gap resistance in the return flow path of the fluid pressurized by the pump to the chambers 35 L and 35 R can be kept constant.
- the suction specific speed S which is an index of the limit of cavitation, is H NPSH [m] for the required effective suction head, Q [m 3 min] for the flow rate, and n for the rotation speed.
- s [min _1 ] _ ris' Q 1/2 is required.
- Both suction pumps are symmetrical in the axial direction, and are characterized by having suction ports on both sides of the shaft. If the rotation speed is n d , the suction specific speed S is
- the magnetic levitation motors 12 and 13 form two rotating magnetic fields having two different poles by windings and wires (not shown) provided on the stator 14, and the rotor 1 fixed to the rotating shaft 11. 5 is driven to rotate and magnetically levitated. That is, for example, by forming a rotating magnetic field of two poles and four poles on the stator 14, the rotor 15 is driven to rotate as a motor by the rotating magnetic field of two poles, and the rotating magnetic field of two poles and the rotating magnetic field of four poles are formed. The superposition of and forms a static magnetic flux distribution in the radial direction. By controlling this magnitude, the rotating shaft 11 can be levitated and supported at any radial position as a radial magnetic bearing.
- the floating position of the rotating shaft 11 is controlled by detecting the position of the rotating shaft by a displacement sensor 19 and controlling the stator 14 by a controller (not shown) so as to support the rotating shaft 11 at a predetermined position. This can be done by adjusting the magnitude and phase of the quadrupole rotating magnetic field (control magnetic field) supplied to the motor.
- the structure of a general axial magnetic bearing is composed of a disk fixed to a shaft and electromagnets arranged to face each other so as to sandwich the disk from the axial direction.
- the entire length of the rotating shaft becomes longer.
- the dangerous frequency of the shaft decreases, and high-speed rotation becomes difficult.
- the addition of an axial bearing increases the surface area of the rotating body, and as the surface area increases, the friction loss of the fluid surrounding the rotating body increases. As a result, the energy loss of the equipment also increases.
- the axial magnetic bearing is completely unnecessary.
- the resonance frequency can be increased, and the fluid loss occurring in the axial magnetic bearing portion can be completely eliminated.
- both suction pumps 16 in the center of the shaft and arranging the magnetic levitation motors 12 and 13 at both ends, it becomes a lightweight and compact device, and it is possible to eliminate the weight imbalance of the rotating shaft. .
- the frequency of the _ axis eigenvalue can be increased, and the floating stability of the rotating body can be contributed.
- the rotating shaft 11 can be completely symmetrical in the axial direction, including the pump part. If it is long, it can take the maximum value.
- the two magnetic levitation motors have the same dimensions, and the two magnetic levitation motors have exactly the same shaft support stiffness. Therefore, bearing unbalance does not occur and high-speed rotation is facilitated.
- the structure of the two motors by making the structure of the two motors the same, a mass production effect is produced.
- the radial force component of the fluid force acting on the rotating body can be greatly reduced, thereby minimizing the radial displacement of the rotating body supported by magnetic levitation. Fluid transfer with less vibration Can provide the machine.
- the effect of reducing the vibration in the radial direction is not limited to the shape of the double volume casing as described above, but the fluid force acting on the rotating body can be obtained by the diffuser 26 properly arranged as shown in FIG. Radial components can be greatly reduced, and a similar effect can be obtained.
- the combination of the two suction pumps and the magnetic levitation motor makes it possible to eliminate the need for an axial bearing and reduce the shaft length. Can be provided. Furthermore, the reduction in shaft length and the difficulty of cavitation of both suction pumps make it possible to rotate at a higher speed than before, which is also useful for reducing the size and increasing the output of the pump.
- the present invention is applicable to a fluid machine such as a pump suitable for high-speed operation.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/581,701 US20070110595A1 (en) | 2004-12-06 | 2004-12-06 | Fluid conveying machine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003410940A JP2005171825A (ja) | 2003-12-09 | 2003-12-09 | 流体搬送機械 |
JP2003-410940 | 2003-12-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005057017A1 true WO2005057017A1 (ja) | 2005-06-23 |
Family
ID=34674960
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/018517 WO2005057017A1 (ja) | 2003-12-09 | 2004-12-06 | 流体搬送機械 |
Country Status (3)
Country | Link |
---|---|
JP (1) | JP2005171825A (ja) |
CN (1) | CN1890469A (ja) |
WO (1) | WO2005057017A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2896101A1 (fr) * | 2006-01-10 | 2007-07-13 | Mecanique Magnetique Sa Soc D | Dispositif de filtrage de particules dans une machine tournante a paliers magnetiques actifs |
GB2493938A (en) * | 2011-08-23 | 2013-02-27 | Framo Eng As | Double motor pump with variable speed drive |
RU2537205C1 (ru) * | 2013-12-18 | 2014-12-27 | Открытое акционерное общество "Турбонасос" | Магистральный нефтяной насос и рабочее колесо магистрального нефтяного насоса |
CN106351849A (zh) * | 2015-07-13 | 2017-01-25 | 昆山江津长抗干磨磁力泵有限公司 | 一种结构改进的磁力泵 |
CN116104771A (zh) * | 2023-04-10 | 2023-05-12 | 山东天瑞重工有限公司 | 一种磁悬浮流体输送装置 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4959424B2 (ja) * | 2007-05-31 | 2012-06-20 | 勇 青谷 | ポンプ装置 |
EP2085106B1 (en) * | 2008-01-31 | 2017-07-19 | ResMed Limited | Respiratory apparatus |
US9377027B2 (en) * | 2011-08-11 | 2016-06-28 | Itt Manufacturing Enterprises Llc. | Vertical double-suction pump having beneficial axial thrust |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0219695A (ja) * | 1988-07-07 | 1990-01-23 | Kubota Ltd | 遠心式ポンプ |
JPH0717990U (ja) * | 1993-08-24 | 1995-03-31 | 友野工業株式会社 | ディスク形マグネットカップリング渦流ポンプ |
JPH0849692A (ja) * | 1994-08-04 | 1996-02-20 | Hitachi Ltd | 両吸込うず巻ポンプ |
JPH1084655A (ja) * | 1996-09-10 | 1998-03-31 | Ebara Corp | 磁気浮上モータ |
JP2003013883A (ja) * | 2001-06-29 | 2003-01-15 | Nikkiso Co Ltd | 遠心ポンプ |
JP3383023B2 (ja) * | 1993-09-17 | 2003-03-04 | 株式会社日立製作所 | 遠心形流体機械 |
-
2003
- 2003-12-09 JP JP2003410940A patent/JP2005171825A/ja not_active Withdrawn
-
2004
- 2004-12-06 WO PCT/JP2004/018517 patent/WO2005057017A1/ja active Application Filing
- 2004-12-06 CN CNA2004800366012A patent/CN1890469A/zh active Pending
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0219695A (ja) * | 1988-07-07 | 1990-01-23 | Kubota Ltd | 遠心式ポンプ |
JPH0717990U (ja) * | 1993-08-24 | 1995-03-31 | 友野工業株式会社 | ディスク形マグネットカップリング渦流ポンプ |
JP3383023B2 (ja) * | 1993-09-17 | 2003-03-04 | 株式会社日立製作所 | 遠心形流体機械 |
JPH0849692A (ja) * | 1994-08-04 | 1996-02-20 | Hitachi Ltd | 両吸込うず巻ポンプ |
JPH1084655A (ja) * | 1996-09-10 | 1998-03-31 | Ebara Corp | 磁気浮上モータ |
JP2003013883A (ja) * | 2001-06-29 | 2003-01-15 | Nikkiso Co Ltd | 遠心ポンプ |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2896101A1 (fr) * | 2006-01-10 | 2007-07-13 | Mecanique Magnetique Sa Soc D | Dispositif de filtrage de particules dans une machine tournante a paliers magnetiques actifs |
GB2493938A (en) * | 2011-08-23 | 2013-02-27 | Framo Eng As | Double motor pump with variable speed drive |
GB2493938B (en) * | 2011-08-23 | 2014-08-13 | Framo Eng As | Double motor pump with variable speed drive |
NO340425B1 (no) * | 2011-08-23 | 2017-04-18 | Framo Eng As | Tomotorspumpe for undervannsbruk |
RU2537205C1 (ru) * | 2013-12-18 | 2014-12-27 | Открытое акционерное общество "Турбонасос" | Магистральный нефтяной насос и рабочее колесо магистрального нефтяного насоса |
CN106351849A (zh) * | 2015-07-13 | 2017-01-25 | 昆山江津长抗干磨磁力泵有限公司 | 一种结构改进的磁力泵 |
CN116104771A (zh) * | 2023-04-10 | 2023-05-12 | 山东天瑞重工有限公司 | 一种磁悬浮流体输送装置 |
Also Published As
Publication number | Publication date |
---|---|
JP2005171825A (ja) | 2005-06-30 |
CN1890469A (zh) | 2007-01-03 |
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