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WO2018181281A1 - Pompe à fluide à basse température et dispositif de transfert de fluide à basse température - Google Patents

Pompe à fluide à basse température et dispositif de transfert de fluide à basse température Download PDF

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Publication number
WO2018181281A1
WO2018181281A1 PCT/JP2018/012376 JP2018012376W WO2018181281A1 WO 2018181281 A1 WO2018181281 A1 WO 2018181281A1 JP 2018012376 W JP2018012376 W JP 2018012376W WO 2018181281 A1 WO2018181281 A1 WO 2018181281A1
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WO
WIPO (PCT)
Prior art keywords
permanent magnet
cryogenic fluid
shaft
base portion
magnetic bearing
Prior art date
Application number
PCT/JP2018/012376
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English (en)
Japanese (ja)
Inventor
山田　裕之
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2018181281A1 publication Critical patent/WO2018181281A1/fr

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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
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means

Definitions

  • the present invention relates to a cryogenic fluid pump and a cryogenic fluid transfer device.
  • low temperature fluid pumps for feeding low temperature liquefied gas and the like are known.
  • a pump used for an application where the pump cannot be stopped due to a failure or maintenance such as a pump used for cooling a superconducting device that requires continuous operation for a long period of time.
  • a magnetic bearing requiring no maintenance is adopted.
  • Patent Document 1 discloses a cryogenic fluid pump having a configuration in which a magnetic bearing requiring no maintenance is employed as a bearing.
  • the bias current applied to the electromagnetic coil of the magnetic bearing in this manner causes heat generation in the magnetic bearing, resulting in problems such as vaporization of low temperature fluid and reduced pump efficiency.
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a cryogenic fluid pump and a cryogenic fluid transfer device capable of suppressing vaporization of cryogenic fluid. It is.
  • the pump for cryogenic fluid includes an impeller, a rotating shaft, a housing, and a magnetic bearing.
  • the rotating shaft is connected to the impeller.
  • the housing holds the rotating shaft inside.
  • a magnetic bearing supports a rotating shaft rotatably with respect to a housing
  • the magnetic bearing includes a yoke and at least one coil.
  • the yoke constitutes at least a part of the magnetic circuit. At least one coil surrounds a portion of the yoke.
  • the yoke includes at least one permanent magnet disposed at a position constituting a part of the magnetic circuit.
  • the cryogenic fluid transfer device includes a container that accommodates cryogenic fluid, the cryogenic fluid pump, and a flow conduit.
  • the cryogenic fluid pump is installed in the container such that the impeller is disposed inside the container.
  • the circulation pipe is connected to the container and is used for circulating a low-temperature fluid to which kinetic energy is imparted by a low-temperature fluid pump.
  • the generated force with respect to the control current in the magnetic bearing can be linearized without flowing a bias current.
  • a cryogenic fluid pump and a cryogenic fluid transfer device capable of suppressing vaporization of the cryogenic fluid are obtained.
  • FIG. 3 is a partial schematic cross-sectional view along the rotation axis direction of the cryogenic fluid pump shown in FIG. 2.
  • FIG. 4 is a schematic sectional view taken along line IV-IV in FIG. 3.
  • It is a partial cross-sectional schematic diagram of the pump for low temperature fluids as a comparative example. It is a schematic diagram for demonstrating control of the magnetic bearing of the pump for low temperature fluids concerning this embodiment.
  • FIG. 6 is a schematic cross-sectional view for explaining a magnetic bearing according to a modification of the first embodiment.
  • FIG. It is a partial cross section schematic diagram along the rotating shaft direction of the cryogenic fluid pump which concerns on Embodiment 2 of this invention.
  • FIG. 13 is a schematic cross-sectional view taken along line XIII-XIII in FIG. It is a partial cross section schematic diagram of the pump for low temperature fluids as a reference example.
  • FIG. 10 is a partial cross-sectional schematic diagram of a cryogenic fluid pump according to a modification of the second embodiment.
  • FIG. 16 is a schematic cross-sectional view taken along line XVI-XVI in FIG. 15. It is a schematic diagram of the cryogenic fluid transfer apparatus which concerns on Embodiment 3 of this invention. It is a cross-sectional schematic diagram of the pump for low temperature fluids used for the low temperature fluid transfer apparatus shown in FIG.
  • the cryogenic fluid transfer apparatus 1 mainly includes a cryogenic fluid pump 100, a container 2, an inflow portion 3, and an outflow portion 4.
  • the cryogenic fluid pump 100 includes a portion disposed outside the container 2 and a portion disposed inside the container 2.
  • the cryogenic fluid pump 100 is attached to the pressure wall 5 of the container 2. Details of the cryogenic fluid pump 100 will be described later.
  • the container 2 is for storing therein a low-temperature fluid such as a low-temperature liquefied gas.
  • the cryogenic fluid is, for example, liquid nitrogen (LN 2 ).
  • the container 2 is configured as a pressure-resistant container, and includes a main body that stores a low-temperature fluid therein and a pressure wall 5.
  • the main body has an opening at the top.
  • the pressure wall 5 is connected to the main body so as to close the opening of the main body.
  • the pressure wall 5 faces the internal space that stores the cryogenic fluid in the container 2.
  • the pressure wall 5 is disposed, for example, above the internal space of the container 2.
  • a through hole 5 a is formed in the pressure wall 5.
  • the hole axis of the through hole 5a is, for example, arranged coaxially with the central axis of the first axis constituting the shaft 9 of the pump 100 described later.
  • a concave portion that is recessed toward the inner peripheral surface side with respect to the outer peripheral surface 5b of the pressure wall 5 is disposed.
  • the said recessed part is a part into which the fixing member 14 mentioned later is screwed.
  • the material that constitutes the pressure wall 5 is a material that is approved for use as a constituent material of a high-pressure gas container by laws and regulations, and includes, for example, stainless steel (SUS) or aluminum (Al).
  • the inflow part 3 includes a pipe line connected to the internal space of the container 2.
  • the cryogenic fluid flows into the container 2 through the pipe line of the inflow portion 3.
  • the outflow part 4 includes a pipe line connected to the internal space of the container 2. The cryogenic fluid flows out of the container 2 through the pipe line of the outflow portion 4.
  • the inflow part 3 and the outflow part 4 are configured as a part of a distribution pipe through which a low-temperature fluid flows.
  • the distribution pipe includes a reservoir tank (not shown) and a refrigerator (not shown).
  • the inflow part 3 is connected to a reservoir tank, for example.
  • the outflow part 4 is connected with the refrigerator, for example.
  • the above-described cryogenic fluid transfer device includes the container 2 for housing the cryogenic fluid, the cryogenic fluid pump 100, and the flow pipe including the inflow portion 3 and the outflow portion 4.
  • the cryogenic fluid pump 100 is installed in the container 2 such that the impeller 8 is disposed inside the container 2 as shown in FIG.
  • the distribution pipe is connected to the container 2 and is used for circulating the low-temperature fluid LG to which kinetic energy is given by the low-temperature fluid pump 100.
  • a cryogenic fluid pump 100 (hereinafter also simply referred to as a pump) according to Embodiment 1 shown in FIGS. 2 to 4 is applied to the cryogenic fluid transfer apparatus 1 shown in FIG. It arrange
  • the pump 100 includes a first housing portion 6 disposed inside the container 2 and a second housing portion 7 disposed outside the container 2 as a housing that is an outer member.
  • the inside of the container 2 means a portion located inside the outer peripheral surface 5 b of the pressure wall 5 of the container 2.
  • the outside of the container 2 means a portion located outside the outer peripheral surface 5 b of the pressure wall 5 of the container 2.
  • the first housing part 6 and the second housing part 7 are configured separately from the pressure wall 5 of the container 2.
  • the first housing portion 6 accommodates the impeller 8 and the first portion 9 a of the shaft 9 inside.
  • the first housing 6 is provided with an inlet 6a and an outlet 6b as openings.
  • the inflow port 6a is disposed at a lower end portion of the first housing portion 6 and opens downward.
  • the outlet 6 b opens in the tangential direction of the outer peripheral surface of the impeller 8 as viewed from the extending direction of the central axis of the impeller 8 (extending direction of the central axis of the shaft 9).
  • the upper end portion of the first housing portion 6 is connected to and fixed to the lower end portion of the second housing portion 7. Specifically, a portion located on the outer peripheral side in the upper surface of the upper end portion of the first housing portion 6 is connected and fixed to the lower surface of the lower end portion of the second housing portion 7.
  • the lower end portion of the second housing portion 7 is disposed in the through hole 5 a disposed in the pressure wall 5 of the container 2.
  • the lower end portion of the second housing portion 7 is configured to block most of the through hole 5a.
  • the lower end portion of the second housing portion 7 has an outer peripheral side surface facing the inner peripheral end surface of the through hole 5a in the radial direction (radial direction) perpendicular to the extending direction.
  • the second housing part 7 accommodates the second part 9b of the shaft 9, the motor 10, the radial magnetic bearing 11, and the thrust magnetic bearing 12 therein.
  • the detailed configuration of the radial magnetic bearing 11 will be described later.
  • the second housing portion 7 includes a flange portion 7a that protrudes outward in the radial direction above the lower end portion thereof.
  • the flange portion 7a is continuous in the circumferential direction.
  • a plurality of fixing through holes are arranged in the flange portion 7a.
  • Each of the plurality of fixing through holes is disposed at a distance from each other in the circumferential direction with respect to the central axis of the shaft 9.
  • the hole axis of each fixing through hole is, for example, along the central axis.
  • One end of each fixing through hole is disposed on the lower surface of the flange portion 7a, and the other end of each fixing through hole is disposed on the upper surface of the flange portion 7a.
  • the lower surface of the flange portion 7a is opposed to a portion surrounding the entire periphery of the through hole 5a on the outer peripheral surface 5b of the pressure wall 5 in the direction along the central axis.
  • a recess is formed on the outer peripheral surface 5b of the pressure wall 5 facing one end of the fixing through hole.
  • a screw as a fixing member 14 is inserted and fixed in the fixing through hole and the recess. In this way, the flange portion 7 a is connected to the outer peripheral surface 5 b of the pressure wall 5.
  • the second housing part 7 includes, for example, a third housing part 7c and a fourth housing part 7d.
  • casing part 7c is a cylindrical member.
  • casing part 7d is a lid-shaped member comprised so that the upper edge part of the 3rd housing
  • the lower end portion of the third housing portion 7 c constitutes the lower end portion of the second housing portion 7.
  • the upper end portion of the third housing portion 7c is in contact with and fixed to the lower end portion of the fourth housing portion 7d.
  • a flange portion is formed at each of the upper end portion of the third housing portion 7c and the lower end portion of the fourth housing portion 7d.
  • the flange portion of the third housing portion 7c and the flange portion of the fourth housing portion 7d are arranged so as to overlap each other. Through holes are formed in these flange portions. A screw as a fixing member is inserted and fixed in the through hole.
  • casing part 7 is exposed to air
  • the material constituting the first housing part 6 and the second housing part 7 is a material that is permitted to be used as a constituent material of a high-pressure gas container by laws and regulations, for example, stainless steel (SUS) or aluminum. (Al) is included.
  • the impeller 8 rotates when the shaft 9 rotates, and imparts kinetic energy to the low temperature fluid LG in the container 2.
  • the impeller 8 is configured as a centrifugal impeller, for example.
  • the impeller 8 is connected to one end of the first portion 9 a of the shaft 9.
  • the shaft 9 includes a first part 9a and a second part 9b. In the extending direction, one end of the first portion 9a is connected to the impeller 8, and the other end of the first portion 9a is connected to one end of the second portion 9b.
  • the central axis of the first part 9a is arranged coaxially with the central axis of the second part 9b.
  • the central axis of the shaft 9 is the central axis of the first part 9 a and the second part 9 b and is arranged coaxially with the central axis of the impeller 8.
  • the shaft 9 is rotationally driven by a motor 10.
  • the second portion 9 b of the shaft 9 is supported in a non-contact manner by the radial magnetic bearing 11 and the thrust magnetic bearing 12.
  • the shaft 9 is supported so that its central axis is coaxial with the rotation axis of the motor 10.
  • the extending direction of the central axis of the shaft 9 is, for example, along the vertical direction.
  • two radial magnetic bearings 11 are arranged on both sides of the motor 10 in the extending direction.
  • the thrust magnetic bearing 12 is disposed above the other end of the second portion 9b of the shaft 9.
  • the shaft 9, the motor 10, the radial magnetic bearing 11, and the thrust magnetic bearing 12 constitute a drive unit that drives the impeller 8 to rotate.
  • the cryogenic fluid pump 100 includes an impeller 8, a shaft 9 as a rotation shaft, first housing 6 and second housing 7 as housings, and magnetic bearings.
  • the radial magnetic bearing 11 is mainly provided.
  • the shaft 9 is connected to the impeller 8.
  • the radial magnetic bearing 11 supports the shaft 9 so as to be rotatable with respect to the second housing part 7.
  • the radial magnetic bearing 11 includes a yoke and at least one coil 11b.
  • the yoke constitutes at least a part of the magnetic circuit 11e. At least one coil 11b surrounds a part of the yoke.
  • the yoke includes at least one permanent magnet 11c arranged at a position constituting a part of the magnetic circuit 11e.
  • the yoke in the cryogenic fluid pump, includes a base portion 11a and a plurality of protrusions 11d having first to fourth protrusions 11d1 to 11d4.
  • the base portion 11 a is disposed on the outer peripheral side of the shaft 9 so as to extend along the circumferential direction of the shaft 9 with a space from the surface of the shaft 9. From another viewpoint, the base portion 11a has an annular shape that surrounds the outer periphery of the shaft 9 in the circumferential direction.
  • the plurality of projecting portions 11 d are arranged at equal intervals in the circumferential direction of the shaft 9.
  • the at least one permanent magnet 11c includes a first permanent magnet 11c1 and a second permanent magnet 11c2.
  • the 1st permanent magnet 11c1 is arrange
  • the permanent magnet 11c is arrange
  • the 1st permanent magnet 11c1 and the 2nd permanent magnet 11c2 are arrange
  • the adjacent end portions of the first permanent magnet 11c1 and the second permanent magnet 11c2 have the same N pole.
  • the end portions adjacent in the circumferential direction have the same polarity as the end portions of the adjacent permanent magnets 11c in the circumferential direction.
  • Magnets that can be used as the permanent magnet 11c are mainly neodymium (Nd—Fe—B) magnets, Samakoba (Sm—Co) magnets, and Alnico (Al—Ni—Co) magnets.
  • the radial magnetic bearing 11 has a permanent magnet combined system in which a part of the magnetic circuit 11e includes the permanent magnet 11c.
  • the generated force with respect to the control current in the magnetic bearing 11 can be linearized. For this reason, it is possible to prevent the generation of heat in the radial magnetic bearing 11 due to the flow of the bias current.
  • the low-temperature fluid LG to which the low-temperature fluid pump 100 is applied from being vaporized by the heat, and the efficiency of the low-temperature fluid pump 100 from being reduced due to the vaporization of the low-temperature fluid LG.
  • FIG. 6 is a schematic diagram showing an example of a control mechanism for explaining the control of the radial magnetic bearing 11 shown in FIGS.
  • the control mechanism includes amplifiers 41 and 42 connected to the coil 11b to supply control currents ic1 and ic2 to the coil 11b of the radial magnetic bearing 11, and a control unit 40 that controls the amplifiers 41 and 42. Including mainly.
  • the amplifier 41 supplies a control current ic1 to one coil 11b.
  • the amplifier 42 supplies the control current ic2 to the other coil 11b by the control signal from the control unit 40.
  • the permanent magnet 11c in the radial magnetic bearing 11, it is not necessary to flow a bias current as described above.
  • the amplifiers 41 and 42 an amplifier having an H bridge circuit that allows a bidirectional current to flow can be used.
  • FIG. 5 is a partial cross-sectional schematic diagram of a cryogenic fluid pump as a comparative example.
  • the radial magnetic bearing 11 does not include a permanent magnet
  • FIG. 4 is different from the cryogenic fluid pump 100 shown in FIGS. 1 to 4 in that it has a control mechanism for supplying a bias current to the coil 11b.
  • the bias current ib output from the power supply unit 23 is added to the currents ic1 and ic2 from the amplifiers 51 and 52 and supplied to the coil 11b.
  • the generated force with respect to the control current is linearized by the bias current ib.
  • linearization of the generated force by the bias current will be described with reference to FIGS.
  • FIG. 8 is a schematic diagram for explaining the relationship between the coil current and the magnetic force in the electromagnet.
  • FIG. 8A is a schematic diagram showing a state in which an electromagnet corresponding to a radial magnetic bearing is disposed opposite to the shaft 9.
  • FIG. 8B is a graph showing the relationship between the current i flowing through the coil 11b and the magnetic force F generated in the electromagnet in the configuration shown in FIG.
  • the horizontal axis indicates the current i
  • the vertical axis indicates the magnetic force F.
  • the relationship between the current i and the magnetic force F is a quadratic function as shown by the following mathematical formula (1).
  • Equation (1) B is the magnetic flux density
  • S is the magnetic path cross-sectional area
  • N is the number of coil turns
  • i is the current supplied to the coil
  • x is the gap between the electromagnet and the shaft 9 shown in FIG. Means each.
  • FIG. 9 is a schematic diagram showing a case where the electromagnets used for the radial magnetic bearing are arranged to face each other with the shaft 9 interposed therebetween.
  • FIG. 9A is a schematic diagram showing a state in which the electromagnets are arranged to face each other with the shaft 9 interposed therebetween.
  • FIG. 9B is a graph showing the relationship between the current i flowing through the coil 11b and the magnetic force F generated in the electromagnet in the configuration shown in FIG. 9A.
  • the vertical axis and the horizontal axis in the graph of FIG. 9B are the same as those of the graph of FIG.
  • the permanent magnet 11c is applied to the radial magnetic bearing 11 in this embodiment.
  • the magnetomotive force in the magnetic circuit in the permanent magnet combination method employed in the present embodiment is expressed by the following mathematical formula (2).
  • l i represents the magnetic path length
  • l p represents the length of the permanent magnet 11c shown in FIG. 6
  • H represents the strength of the magnetic field inside the permanent magnet.
  • the magnetomotive force of the permanent magnet is added, and the magnetic flux density is a function of (Ni-Hlp). That is, in the radial magnetic bearing 11 according to the present embodiment, the magnetic force can be controlled by the coil current i.
  • FIG. 10 shows a linearized state of the coil current i and the magnetic force F due to the bias magnetic flux generated by the permanent magnet 11c.
  • the relationship between the coil current i and the magnetic force F can be linearized up to a region twice the magnetic force F generated by the bias magnetic flux.
  • first permanent magnet 11c1 to the part of the base portion 11a, the first magnetic circuit that circulates around the first protrusion 11d1 and the second protrusion 11d2, and the second permanent magnet 11c2 to the base portion 11a.
  • the third protrusion 11d3 and the fourth protrusion 11d4 and the second magnetic circuit that circulates can be formed.
  • the first permanent magnet 11c1 and the second permanent magnet 11c2 have the same poles at the ends adjacent to each other in the circumferential direction.
  • the polarity of the inner peripheral portion facing the shaft 9 is It is the same.
  • the magnetic poles are not switched between the second protrusion 11d2 and the third protrusion 11d3 when the shaft 9 rotates.
  • the end portions adjacent to each other in the circumferential direction of the first permanent magnet 11c1 and the second permanent magnet 11c2 are different poles (that is, in the second protrusion 11d2 and the third protrusion 11d3).
  • the number of switching of the magnetic poles in the yoke that is, the number of switching of the magnetic poles of the yoke in the circumferential direction of the shaft 9 when the shaft 9 rotates can be reduced.
  • the loss in the shaft 9 that is the rotor due to the switching of the magnetic poles can be reduced, so that a reduction in the efficiency of the cryogenic fluid pump 100 can be suppressed.
  • the cryogenic fluid transfer device 1 using the cryogenic fluid pump 100 as described above since the inflow of heat from the radial magnetic bearing 11 of the cryogenic fluid pump 100 to the cryogenic fluid can be suppressed, vaporization and efficiency of the cryogenic fluid can be suppressed. Is suppressed.
  • the cryogenic fluid pump shown in FIG. 11 is applied to the cryogenic fluid transfer device shown in FIG. 1, and basically has the same configuration as the cryogenic fluid pump shown in FIGS.
  • the shapes of the base portion 11a and the permanent magnet 11c are different from those of the cryogenic fluid pump shown in FIGS. That is, in the cryogenic fluid pump shown in FIG. 11, a plurality of permanent magnets 11 c including the first and second permanent magnets 11 c 1 and 11 c 2 are cross sections along a radial direction that is a direction perpendicular to the circumferential direction.
  • the cross-sectional area of the base portion 11a is larger than the cross-sectional area in the cross section along the radial direction of the region where the plurality of projecting portions 11d including the first to fourth projecting portions 11d1 to 11d4 are connected. Further, the base portion 11a has a cross-sectional area in a radial direction that approaches at least one of the first and second permanent magnets 11c1 and 11c2, or at least one of the plurality of permanent magnets 11c. It is comprised so that it may become large as it approaches. From another point of view, the inner circumferential surface facing the shaft 9 in the portion adjacent to the permanent magnet 11c in the base portion 11a is closer to the inner circumferential side (shaft 9 side) closer to the permanent magnet 11c. It is inclined with respect to. The shape of the outer peripheral surface of the base portion 11a viewed from the extending direction of the shaft 9 is circular as shown in FIG.
  • the cross-sectional area in the cross section along the radial direction of at least one permanent magnet 11c including the first and second permanent magnets 11c1 and 11c2 is relative to the cross-sectional area of the permanent magnet 11c in the configuration shown in FIG. Therefore, the thickness of the permanent magnet 11c in the circumferential direction can be relatively reduced while maintaining the magnetic flux generated by the permanent magnet 11c.
  • the magnetic resistance in the magnetic circuit of the permanent magnet 11c can be reduced as compared with the case where the thickness of the permanent magnet 11c in the circumferential direction is relatively thick as shown in FIG.
  • the controllability of the radial magnetic bearing 11 can be improved, and the control current value of the radial magnetic bearing 11 when a load is applied can be reduced.
  • the cryogenic fluid pump including the radial magnetic bearing 11 shown in FIGS. 12 and 13 is a pump that can be applied to the cryogenic fluid transfer device shown in FIG. 1 and basically includes the cryogenic fluid shown in FIGS.
  • the shape of the yoke constituting the radial magnetic bearing 11 is different from that of the cryogenic fluid pump shown in FIGS. That is, in the cryogenic fluid pump shown in FIGS. 12 and 13, the yoke includes a plurality of portions arranged at intervals in the circumferential direction of the shaft 9 so as to surround the outer periphery of the shaft 9.
  • the yoke includes a plurality of base portions 11a including the first and second base portions 11a1 and 11a2, and the first to fourth projecting portions 11d1 to 11d4.
  • the plurality of base portions 11a including the first and second base portions 11a1 and 11a2 are arranged at intervals along the circumferential direction of the shaft 9 on the outer peripheral side of the shaft 9 as shown in FIG.
  • the first and second projecting portions 11d1 and 11d2 project from the first base portion 11a1 toward the shaft 9 and are spaced from each other in the axial direction of the shaft 9.
  • the third protruding portion 11d3 protrudes from the second base portion 11a2 toward the shaft 9 and is on the same side as the first protruding portion 11d1 when viewed from the center of the first base portion 11a1 in the axial direction of the shaft 9. Placed in.
  • the 4th protrusion part 11d4 is arrange
  • the fourth projecting portion 11d4 is formed so as to project from the second base portion 11a2 toward the shaft 9.
  • a coil 11b is wound around the first to fourth protrusions 11d1 to 11d4.
  • the at least one permanent magnet 11c includes first and second permanent magnets 11c1 and 11c2.
  • the first permanent magnet 11c1 is disposed between the first protruding portion 11d1 and the second protruding portion 11d2 in the first base portion 11a1.
  • the second permanent magnet 11c2 is disposed between the third projecting portion 11d3 and the fourth projecting portion 11d4 in the second base portion 11a2.
  • the first permanent magnet 11c1 and the second permanent magnet 11c2 are arranged such that the same pole (N pole in FIG. 12) is located at the end on the first protrusion 11d1 side in the axial direction.
  • the base part 11a in which the permanent magnet 11c as described above is disposed at the center part, the two projecting parts 11d disposed at both ends in the axial direction of the base part 11a, and the two projecting parts 11d are respectively wound.
  • a plurality of units composed of two coils 11b arranged so as to rotate are arranged so as to be arranged along the outer periphery of the shaft 9 at intervals in the circumferential direction as shown in FIG.
  • the cryogenic fluid pump provided with the radial magnetic bearing 11 and the cryogenic fluid transfer device provided with the cryogenic fluid pump shown in FIGS. 12 and 13 basically have the cryogenic fluid transfer device and the cryogenic temperature shown in FIGS. The same effect as the fluid pump can be obtained. Further, a plurality of units are arranged at intervals along the outer periphery of the shaft 9, and as shown in FIG. 12, the first protrusion 11d1 and the third protrusion 11d3 have the same polarity (for example, N pole). It is a magnetic pole. That is, the radial magnetic bearing 11 is a so-called homopolar radial magnetic bearing.
  • the permanent magnet combined use system is applicable also to the homopolar type radial magnetic bearing 11.
  • FIG. 14 That is, in the homopolar type radial magnetic bearing as the reference example shown in FIG. 14, the permanent magnet is not arranged on the base portion 11a of the yoke, so that it is the same as the radial magnetic bearing shown in FIG. In addition, it is necessary to pass a bias current for linearizing the generated force.
  • the radial magnetic bearing shown in FIG. 14 has the same configuration as the radial magnetic bearing shown in FIGS. 12 and 13 except that it does not include a permanent magnet.
  • the bias current in the radial magnetic bearing shown in FIG. 14 causes heat generation and can cause vaporization of the low temperature fluid.
  • the use of the permanent magnet 11c eliminates the need for the bias current as described above, and the same effect as in the first embodiment can be obtained.
  • the cryogenic fluid pump provided with the radial magnetic bearing 11 shown in FIGS. 15 and 16 is a pump applicable to the cryogenic fluid transfer device shown in FIG. 1, and is a pump of the cryogenic fluid pump shown in FIGS. 12 and 13. It is a modification.
  • the cryogenic fluid pump shown in FIGS. 15 and 16 basically has the same configuration as the cryogenic fluid pump shown in FIGS. 12 and 13, but the arrangement of the coil 11b in the radial magnetic bearing 11 is as shown in FIG. And, it is different from the cryogenic fluid pump shown in FIG. That is, in the cryogenic fluid pump shown in FIGS.
  • At least one coil 11b includes a first coil 11b1 and a second coil 11b2.
  • the first coil 11b1 is disposed so as to surround the first permanent magnet 11c1.
  • the second coil 11b2 is arranged so as to surround the periphery of the second permanent magnet 11c2.
  • a coil 11b is arranged so as to surround the permanent magnet 11c in each unit of the radial magnetic bearing 11 arranged so as to surround the outer periphery of the shaft 9, so as to surround the permanent magnet 11c.
  • the same effect as the cryogenic fluid pump shown in FIGS. 12 and 13 can be obtained.
  • the magnetic resistance (also referred to as magnetic path resistance) of the portion where the first and second permanent magnets 11c1 and 11c2 are arranged is substantially the same as the magnetic resistance of air, and compared with other portions of the base portion 11a.
  • the leakage flux in the first and second permanent magnets 11c1 and 11c2 is provided by arranging the first and second coils 11b1 and 11b2 so as to surround the first and second permanent magnets 11c1 and 11c2. Can be suppressed.
  • the cryogenic fluid transfer device 1 shown in FIGS. 17 and 18 basically has the same configuration as the cryogenic fluid transfer device 1 shown in FIG. 1, but the configuration of the cryogenic fluid pump 100 is shown in FIG. Different from the cryogenic fluid transfer device 1. That is, in the cryogenic fluid transfer apparatus 1 shown in FIGS. 17 and 18, the motor 30 of the cryogenic fluid pump 100 is disposed outside the pressure wall 5, and the shaft 9 as the first shaft is the second of the motor 30. The shaft 31 and the magnetic coupling 20 are coupled so as to transmit the rotational force. A shaft 9 supported by two radial magnetic bearings 11 is disposed inside the container 2.
  • the cryogenic fluid pump 100 according to the third embodiment shown in FIG. 17 and FIG. 18 is similar to the cryogenic fluid pump 100 shown in FIGS. 1 to 4 and penetrates the pressure wall 5 of the container 2. It arrange
  • the cryogenic fluid pump 100 rotationally drives the impeller 8, a rotating shaft including the shaft 9 and the second shaft 31 as a first shaft, a housing, a radial magnetic bearing 11 as a magnetic bearing, and the second shaft 31.
  • the motor 30 is mainly provided.
  • the shaft 9 constituting the rotating shaft and the second shaft 31 are coupled by the magnetic coupling 20 so as to be able to transmit the rotational force in a non-contact manner.
  • the two radial magnetic bearings 11 support the shaft 9 so as to be rotatable with respect to the housing.
  • the two radial magnetic bearings 11 are spaced apart from each other in the extending direction of the shaft 9.
  • the magnetic coupling 20 includes a first coupling member 22 fixed to the end of the shaft 9 and a second coupling member 21 fixed to the end of the second shaft 31.
  • the second joint member 21 has a cup shape.
  • the first joint member 22 is disposed inside the second joint member 21. Magnets are arranged in the opposing portions of the first joint member 22 and the second joint member 21. Due to the magnetic force generated by the magnet, the first joint member 22 and the second joint member 21 can transmit the rotational force without contact.
  • the thrust magnetic bearing 12 is disposed at a position adjacent to the first joint member 22 in the shaft 9. Further, in the shaft 9, the radial magnetic bearing 11 is disposed at a portion located on the opposite side of the first joint member 22 when viewed from the thrust magnetic bearing 12.
  • the housing includes a first housing portion, a second housing portion 7 and a lid 18.
  • the first housing part includes a housing part 6f, a flange part 6c, an impeller shaft cover 6d, and an impeller cover 6e.
  • the upper end portion of the housing portion 6 f is disposed in the through hole 5 b of the pressure wall 5.
  • the flange portion 6c is connected to the upper end portion of the housing portion 6f.
  • the first housing part is arranged such that the flange part 6 c extends on the outer peripheral surface 5 b of the pressure wall 5.
  • the second housing portion 7 has a cylindrical shape, and a flange portion is formed at an end portion on the impeller 8 side.
  • casing part 7 is arrange
  • Through holes for passing the fixing member 14 are formed in the flange portion of the second housing portion 7 and the flange portion 6c of the first housing portion, respectively. This through hole is arranged so as to overlap with a recess formed in the outer peripheral surface 5 b of the pressure wall 5. Then, the fixing member 14 is screwed and fixed into the through hole and the recess, whereby the first housing portion and the second housing portion 7 are fixed to the pressure wall 5.
  • An opening is formed above the second housing part 7.
  • a lid 18 is disposed so as to close the opening of the second housing part 7.
  • a magnetic coupling 20 is disposed in an inner region of the casing surrounded by the lid 18 and the second casing portion 7.
  • a motor 30 is installed on the outer peripheral side of the lid 18.
  • a second shaft 31 is connected to the motor 30.
  • An opening for inserting a part of the motor 30 is formed in the lid 18.
  • a part of the motor 30 is inserted and fixed in the opening.
  • the second shaft 31 is disposed so as to protrude toward the inner peripheral side of the second housing portion 7 from the portion inserted into the opening.
  • the housing portion 6f, the impeller shaft cover 6d, and the impeller cover 6e of the first housing portion are disposed inside the container 2.
  • the housing portion 6f has a cylindrical shape.
  • the impeller shaft cover 6d is located on the side of the housing portion 6f facing the impeller 8, and is connected to the housing portion 6f.
  • the impeller cover 6e is connected to the impeller shaft cover 6d and is disposed so as to surround the impeller 8.
  • the impeller cover 6e is provided with an inlet 6a and an outlet 6b as openings.
  • a radial magnetic bearing 11 is connected to the housing portion 6f.
  • the rotating shaft is for driving the impeller 8 to rotate.
  • the portion of the shaft 9 that is surrounded by the impeller shaft cover 6 d is connected to the impeller 8.
  • the extending direction of the shaft 9 is, for example, the gravitational direction (vertical direction).
  • the housing holds the shaft 9 and the second shaft 31 as the rotation shaft inside.
  • the radial magnetic bearing 11 supports the shaft 9 constituting the rotating shaft so as to be rotatable with respect to the housing portion 6f which is a housing.
  • the rotating shaft, the motor 30, the radial magnetic bearing 11 and the thrust magnetic bearing 12 constitute a drive unit that rotationally drives the impeller 8.
  • cryogenic fluid transfer device 1 and the cryogenic fluid pump 100 shown in FIGS. 17 and 18 the same effects as those of the cryogenic fluid transfer device 1 and the cryogenic fluid pump 100 shown in FIGS. 1 to 4 can be obtained. Furthermore, in the cryogenic fluid transfer apparatus 1 shown in FIGS. 17 and 18, the radial magnetic bearing 11 of the cryogenic fluid pump 100 is disposed inside the container 2. In such a configuration, since the radial magnetic bearing 11 according to the first embodiment or the second embodiment of the present invention described above is applied to the radial magnetic bearing 11, a bias current is applied to the coil of the radial magnetic bearing 11 as in the past. The generated force with respect to the control current of the radial magnetic bearing 11 can be linearized without flowing, and the heat generation due to the bias current can be prevented, so the effect of suppressing the vaporization of the low-temperature fluid inside the container 2 is remarkable.
  • the present invention can be applied to a pump or a transfer device for transferring a low-temperature fluid used for cooling a superconducting device.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe à fluide à basse température et un dispositif de transfert de fluide à basse température avec lesquels il est possible de réduire la vaporisation du fluide à basse température. La pompe à fluide à basse température est équipée d'une roue-hélice, d'un arbre rotatif (9), d'un corps de pompe et d'un palier magnétique (11). L'arbre rotatif (9) est relié à la roue-hélice. L'arbre rotatif (9) est contenu dans le corps de pompe. Le palier magnétique (11) supporte l'arbre rotatif (9) de manière à pouvoir tourner par rapport au corps de pompe. Le palier magnétique (11) comprend une culasse et au moins une bobine (11b). La culasse constitue au moins une partie d'un circuit magnétique (11e). L'au moins une bobine (11b) entoure une partie de la culasse. La culasse comprend au moins un aimant permanent (11c) disposé au niveau d'une position constituant une partie du circuit magnétique (11e).
PCT/JP2018/012376 2017-03-27 2018-03-27 Pompe à fluide à basse température et dispositif de transfert de fluide à basse température WO2018181281A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-061418 2017-03-27
JP2017061418A JP2018162865A (ja) 2017-03-27 2017-03-27 低温流体用ポンプおよび低温流体移送装置

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WO2018181281A1 true WO2018181281A1 (fr) 2018-10-04

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Cited By (2)

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Publication number Priority date Publication date Assignee Title
JP2021143640A (ja) * 2020-03-12 2021-09-24 Ntn株式会社 低温流体用ポンプおよび低温流体移送装置
JP2021143645A (ja) * 2020-03-13 2021-09-24 Ntn株式会社 低温流体用ポンプ

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* Cited by examiner, † Cited by third party
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WO2021015034A1 (fr) * 2019-07-19 2021-01-28 株式会社イワキ Pompe
JP7471976B2 (ja) * 2020-09-23 2024-04-22 Ntn株式会社 流体ポンプ及び流体移送装置
CN115263923B (zh) * 2022-09-20 2022-12-23 山东天瑞重工有限公司 一种永磁偏置径向磁轴承

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JP2001041238A (ja) * 1999-07-28 2001-02-13 Seiko Seiki Co Ltd 複合型電磁石及びラジアル磁気軸受
JP2007120635A (ja) * 2005-10-28 2007-05-17 Iwaki Co Ltd ハイブリッド型磁気軸受
WO2009050767A1 (fr) * 2007-10-18 2009-04-23 Iwaki Co., Ltd. Moteur à lévitation magnétique et pompe
JP2010106908A (ja) * 2008-10-29 2010-05-13 Oitaken Sangyo Sozo Kiko 磁気軸受
JP2013057250A (ja) * 2011-09-07 2013-03-28 Taiyo Nippon Sanso Corp 低温液化ガスポンプ
KR101343879B1 (ko) * 2013-07-24 2013-12-20 한국기계연구원 래디얼 보조 베어링이 구비된 복합 자기 베어링
CN106402159A (zh) * 2016-12-06 2017-02-15 中国工程物理研究院材料研究所 一种永磁偏置磁悬浮转轴

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Publication number Priority date Publication date Assignee Title
JP2001041238A (ja) * 1999-07-28 2001-02-13 Seiko Seiki Co Ltd 複合型電磁石及びラジアル磁気軸受
JP2007120635A (ja) * 2005-10-28 2007-05-17 Iwaki Co Ltd ハイブリッド型磁気軸受
WO2009050767A1 (fr) * 2007-10-18 2009-04-23 Iwaki Co., Ltd. Moteur à lévitation magnétique et pompe
JP2010106908A (ja) * 2008-10-29 2010-05-13 Oitaken Sangyo Sozo Kiko 磁気軸受
JP2013057250A (ja) * 2011-09-07 2013-03-28 Taiyo Nippon Sanso Corp 低温液化ガスポンプ
KR101343879B1 (ko) * 2013-07-24 2013-12-20 한국기계연구원 래디얼 보조 베어링이 구비된 복합 자기 베어링
CN106402159A (zh) * 2016-12-06 2017-02-15 中国工程物理研究院材料研究所 一种永磁偏置磁悬浮转轴

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021143640A (ja) * 2020-03-12 2021-09-24 Ntn株式会社 低温流体用ポンプおよび低温流体移送装置
JP2021143645A (ja) * 2020-03-13 2021-09-24 Ntn株式会社 低温流体用ポンプ
JP7374029B2 (ja) 2020-03-13 2023-11-06 Ntn株式会社 低温流体用ポンプ

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