US3854848A - Device for preventing back-flow in centrifugal pumps operating in parallel - Google Patents

Device for preventing back-flow in centrifugal pumps operating in parallel Download PDF

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US3854848A
US3854848A US29314172A US3854848A US 3854848 A US3854848 A US 3854848A US 29314172 A US29314172 A US 29314172A US 3854848 A US3854848 A US 3854848A
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pump
flow
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/14—Shaft sealings operative only when pump is inoperative
    • F04D29/146—Shaft sealings operative only when pump is inoperative especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0653—Units comprising pumps and their driving means the pump being electrically driven the motor being flooded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F04D13/14—Combinations of two or more pumps the pumps being all of centrifugal type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0077—Safety measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0077—Safety measures
    • F04D15/0083—Protection against sudden pressure change, e.g. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/029—Stopping of pumps, or operating valves, on occurrence of unwanted conditions for pumps operating in parallel
    • 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
    • F04D29/0467—Spherical bearings
    • 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
    • F04D29/18—Rotors
    • F04D29/186—Shaftless rotors
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/548—Specially adapted for liquid pumps
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • 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
    • F04D7/08—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being radioactive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/007—Preventing loss of prime, siphon breakers
    • F04D9/008—Preventing loss of prime, siphon breakers by means in the suction mouth, e.g. foot valves
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F30/00—Fixed transformers not covered by group H01F19/00
    • H01F30/06—Fixed transformers not covered by group H01F19/00 characterised by the structure
    • H01F30/12—Two-phase, three-phase or polyphase transformers
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J3/00—Circuit arrangements for ac mains or ac distribution networks
    • H02J3/38—Arrangements for parallely feeding a single network by two or more generators, converters or transformers
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K17/00—Asynchronous induction motors; Asynchronous induction generators
    • H02K17/02—Asynchronous induction motors
    • H02K17/12—Asynchronous induction motors for multi-phase current
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K17/00—Asynchronous induction motors; Asynchronous induction generators
    • H02K17/02—Asynchronous induction motors
    • H02K17/16—Asynchronous induction motors having rotors with internally short-circuited windings, e.g. cage rotors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K3/00—Details of windings
    • H02K3/04—Windings characterised by the conductor shape, form or construction, e.g. with bar conductors
    • H02K3/12—Windings characterised by the conductor shape, form or construction, e.g. with bar conductors arranged in slots
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K3/00—Details of windings
    • H02K3/04—Windings characterised by the conductor shape, form or construction, e.g. with bar conductors
    • H02K3/28—Layout of windings or of connections between windings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K3/00—Details of windings
    • H02K3/32—Windings characterised by the shape, form or construction of the insulation
    • H02K3/38—Windings characterised by the shape, form or construction of the insulation around winding heads, equalising connectors, or connections thereto
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • H02K5/128—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas using air-gap sleeves or air-gap discs
    • H02K5/1282—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas using air-gap sleeves or air-gap discs the partition wall in the air-gap being non cylindrical
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]

Definitions

  • the device has a closure member in the form of a cylindrical relatively rotationally displaceable closure element, which in one position permits free passage of the back-flow and in another position closes off the back-flow.
  • the closure element has guide elements which are angularly displaced about the axis of rotation of the pump impeller in one direction by the swirl of the stream of medium being conveyed.
  • the object of the invention is to provide for a closure device which automatically interrupts the through-flow through a pump, when the pump impeller is not in operation and which does not require any significant.
  • the back-flow preventing means according to the invention is constructed on the principle of a cock. In accordance with the invention it is operated not by the pressure of the turbine machine, but by the swirl in the FIG. 2 shows diagrammatically asection through the lower portion of the boiling water reactor shown in FIG. 1, in which however only the most essential elements are shown.
  • FIG. 3 shows partly in elevation and partly section a pump with a slide mechanism in accordance with the invention, which automatically-prevents any throughflow in the pump when the pump impeller is not in operation.
  • the boiling water reactor shown in FIG. 1 has a pressure vessel D, which encloses the core K and the envelope chamber M.
  • FIG. 2 shows, again diagrammatically, the lower por tion of the reactor shown in FIG. l..
  • the control rods 2 are surrounded by an envelope 3.
  • the pumps P are located in the envelope chamber M.'-The through-flow takes place in the direction of the arrows 6 and 6, i.e. downwardly in the envelope chamber M and upwardly in the core chamber of the reactor.
  • the stator of the pump motor consists of the pole teeth which are formed by radial sheet metal elements.
  • the magnetic return path is provided by annularsheet metal packets 51 and 51.
  • the coils of the winding 52-each have one turn only and they'are connected to supply leads 53 which again form a conductor; bundle by which the pump is suspended.
  • Through apertures 54 and 55 the medium being conveyed can flow intothe stator chamber and .cool the stator.
  • the frontal surfaces 56 of the pole teeth form a magnetic gap 57.
  • the rotor consists of iron core 58, the bars 59 and short-circuiting rings 60 and 61 of a cage winding.
  • the surface of the rotor facing the air gap 57 lies in a spherical annular region.
  • the rotor is, as in the case of the embodiment'according to FIG. 3, supported by a sphere 62, a dish 63 seflow which is present in the case of every centrifugal machine. Moreover there is even the possibility of converting into pressure the energy content of the swirl which would otherwise be lost. It has been found that devices in accordance with the invention open in every case and that they not only have such a low resistance that practically no pressure loss is produced, but moreover introduce the possibility of producing a gain in pressure by conversion of the after-swirl into pressure.
  • FIG. I shows in diagrammatic and partially sectioned elevation a boiling water reactor in which pumps embodying the invention are located.
  • the stator as well as a dish 64 secured to the rotor.
  • This dish 64 is arranged on a column 65 whichis joined to the rotor viascrew connections.
  • a ring 63' serves the purpose of preventing the rotor from falling down when the pump is shut down.
  • the guide blade ring 66 is secured to the stator, whilst the pump blade ring 67 is located on the rotor.
  • the medium flowing round the stator is conveyed in the direction of the arrow 69 by the pump into a fluid discharge area of the pump where it enters a fixed valve member or end housing 70 of a cock or valve, after which it is discharged through slots 71.
  • a rotatable valve member 73 having a slightly conical inner surface 74 as well as a cylindrical outer surface 75, is supported in the bearings 72 and 72.
  • the outer surface of the rotatable valve member has axially extending slots, which are adapted to register with the slots 71 of the valve member 70.
  • the regions 75' between the slots 71 extend in an azimuth direction over a somewhat greater distance than that over which the slots 71 extend in an azimuth direction, i.e. the regions between these slots 71 are somewhat-wider than the latter.
  • the bridges or space 77 between the slots in the outer cylinder 75 of the rotatable membet valve are somewhat wider than the slots 71 of the fixed valve member.
  • a guide blade ring 78 Secured to the member 73 is a guide blade ring 78 whose blades are so directed that the member is rotated by the swirl of the hydraulic medium in one direction up to an abutment.
  • the slots of the valve register with the slots of the end housing and the bridges of the rotatable member with the bridges of the fixed member. This means that when the pump is operating the medium can freely flow in the direction of the arrow 69 through the pump chamber and be discharged therefrom in the direction of the arrow 80.
  • a spirally wound spring 81 which biasses the rotatable member in the opposite direction to that in which it is turned by the swirl of the flow of medium, causes an angular displacement of this valve member in the opposite direction up to a second abutment.
  • the slots in the outer cylindrical wall 77 of the rotatable member come into register with the bridges 75 of the fixed member on the one hand, and the bridges between the slots in the outer cylindrical wall of the rotatable member with the slots 71 of the fixed member on the other hand.
  • the valve defined by the fixed valve member and the moveable valve member 73 is closed, so that if for example the pump shuts down, no flow of medium produced by adjacent pumps can flew back through it. Thereby the possibilty of a. shunt path for the medium through shut-down pumps is eliminated.
  • a flow. responsive valve device for preventing back-flow of fluidthrough a centrifugal pump when the pump is not operating and when said pump creates a fluid swirl in a pump discharge area when the pump is operating, said valve device comprisinga fixed valve member in the discharge area having apertures therein, a rotatable valve member in the discharge area having apertures therein adapted in a first rotatable position thereof to overlie the apertures in said fixed member to allow fluid flow through the apertures and in a second rotatable position thereof tobe masked by the space between the apertures of said fixed member to' prevent fluid flow through the apertures, spring means urging said rotatable valve member towards said second rotat able position, andblading on said rotatable member cated in said discharge area adapted to be contacted by the fluid swirl when said pump is operating to urge said rotatable member to the first position against the force of the spring means such that the apertures of the first and second members overlie each other when the pump is operating.
  • eachsaid valve member comprises a hollow cylinder and wherein said apertures comprise slots with

Abstract

A device for preventing back-flow through one of several centrifugal pumps connected in parallel in a common circuit when the impeller of the pump is stationary. The device has a closure member in the form of a cylindrical relatively rotationally displaceable closure element, which in one position permits free passage of the back-flow and in another position closes off the back-flow. The closure element has guide elements which are angularly displaced about the axis of rotation of the pump impeller in one direction by the swirl of the stream of medium being conveyed.

Description

United States Patent [191 Laing I 1 Dec. 17, 1974 1 1, DEVICE FOR PREVENTING BACK-FLOW IN CENTRIFUGAL PUMPS OPERATING IN PARALLEL [76] Inventor: Nikolaus Laing, l-lofener Weg 35-37, 7141 Aldingen near Stuttgart, Germany 22 Filed: Sept. 28, 1972 21 Appl. No.2 293,141
[30] Foreign Application Priority Data Oct. 7, 1971 Austria 8658/71 [52] US. Cl 417/424, 417/286, 417/300, 415/146, 415/158, 137/455, 137/511 [51] Int. Cl. F04b 17/00 [58] Field of Search 417/424, 426, 286, 300; 415/146, 147,158, 159; 137/455, 511, 499
[56] g References Cited UNITED STATES PATENTS 1,065,208 6/1913 Brauer 415/159 1,482,547 Dell 137/49, 1,725,344 8/1929 Dennis....., 415/158 2,186,988 l/l940 Osborne 415/159 2,336,010 12/1943 Gregory et a1... 415/159 3,276,384 10/1966 Boone et al v. 415/146 3,589,829 6/1971 Schetinin v 415/159 Primary ExaminerC. J. Husar Attorney, Agent, or FirmPennie & Edmonds 57 ABSTRACT A device for preventing back-flow through one of sev-- eral centrifugal pumps connected in parallel in a common circuit when the impeller of the pump is stationary. The device has a closure member in the form of a cylindrical relatively rotationally displaceable closure element, which in one position permits free passage of the back-flow and in another position closes off the back-flow. The closure element has guide elements which are angularly displaced about the axis of rotation of the pump impeller in one direction by the swirl of the stream of medium being conveyed.
4 Claims, 3 Drawing Figures PATENTED m 1 71974 $854,848
SHEET 2 95 3 Fig.2
DEVICE FOR PREVENTING BACK-FLOW IN CENTRIFUGAL PUMPS OPERATING IN PARALLEL THE PRIOR ART In the operation of a plurality of centrifugal pumps connected in parallel in a circuit, a characteristic is defined in which'the magnitudes of the pressures coincide with the maximum pressure of the individual pumps, whilst the quantity is given by the sum of the individual quantities. The operating point is given by this summation characteristic and its intersection with the throttling characteristic of the system, against which the pumps, connected for multiple flow, operate:
If now one of the pumps shuts down, the liquid being conveyed flows back through this pump, counter to the desired direction of through-flow, into the inlet region.
Thereby the pumping action of the pump unit 001- rupting the back-flow in such pumps have been found unsuitable, since for the purpose of openingthese valves a continuous pressure differential has to be maintained which results in considerable overdimensioning of the pump and appreciable increase in the power consumption of the driving motor. Moreover, particularly in the case of axial flow pumps, great difficulties are encountered in starting up against closed valves, since axial flow pumps are unstable in the region of low throttling values, so that in certain circumstances the minimum pressure required for opening the valves is not reached at all.
THE OBJECT OF THE INVENTION The object of the invention is to provide for a closure device which automatically interrupts the through-flow through a pump, when the pump impeller is not in operation and which does not require any significant.
openingand closing pressure.
DESCRIPTION OF THE INVENTION The back-flow preventing means according to the invention is constructed on the principle of a cock. In accordance with the invention it is operated not by the pressure of the turbine machine, but by the swirl in the FIG. 2 shows diagrammatically asection through the lower portion of the boiling water reactor shown in FIG. 1, in which however only the most essential elements are shown.
FIG. 3 shows partly in elevation and partly section a pump with a slide mechanism in accordance with the invention, which automatically-prevents any throughflow in the pump when the pump impeller is not in operation. l
- The boiling water reactor shown in FIG. 1 has a pressure vessel D, which encloses the core K and the envelope chamber M. In the'envelope chamber M pumps P embodying the invention'are located in which the motor, the stator and the pump impeller each form a unit, which is suspended by the supply leads Z in the envelope chamber.
FIG. 2 shows, again diagrammatically, the lower por tion of the reactor shown in FIG. l.. The control rods 2 are surrounded by an envelope 3. The pumps P are located in the envelope chamber M.'-The through-flow takes place in the direction of the arrows 6 and 6, i.e. downwardly in the envelope chamber M and upwardly in the core chamber of the reactor. The pumps P-are joined to the upper portion of the pressure vessel D by their electrical power supply leads 7 and inserted in a ring 8 which has an aperture for each pump.
In the embodiment shown in FIG. 3, the stator of the pump motor consists of the pole teeth which are formed by radial sheet metal elements. The magnetic return path is provided by annularsheet metal packets 51 and 51. The coils of the winding 52-each have one turn only and they'are connected to supply leads 53 which again form a conductor; bundle by which the pump is suspended. Through apertures 54 and 55 the medium being conveyed can flow intothe stator chamber and .cool the stator. The frontal surfaces 56 of the pole teeth form a magnetic gap 57. The rotor consists of iron core 58, the bars 59 and short- circuiting rings 60 and 61 of a cage winding. The surface of the rotor facing the air gap 57 lies in a spherical annular region. The rotor is, as in the case of the embodiment'according to FIG. 3, supported by a sphere 62, a dish 63 seflow which is present in the case of every centrifugal machine. Moreover there is even the possibility of converting into pressure the energy content of the swirl which would otherwise be lost. It has been found that devices in accordance with the invention open in every case and that they not only have such a low resistance that practically no pressure loss is produced, but moreover introduce the possibility of producing a gain in pressure by conversion of the after-swirl into pressure.
FIG. I shows in diagrammatic and partially sectioned elevation a boiling water reactor in which pumps embodying the invention are located.
cured to the stator as well as a dish 64 secured to the rotor. This dish 64 is arranged on a column 65 whichis joined to the rotor viascrew connections. A ring 63' serves the purpose of preventing the rotor from falling down when the pump is shut down. The guide blade ring 66 is secured to the stator, whilst the pump blade ring 67 is located on the rotor. The medium flowing round the stator is conveyed in the direction of the arrow 69 by the pump into a fluid discharge area of the pump where it enters a fixed valve member or end housing 70 of a cock or valve, after which it is discharged through slots 71. In the fixed valve member, a rotatable valve member 73 having a slightly conical inner surface 74 as well as a cylindrical outer surface 75, is supported in the bearings 72 and 72. The outer surface of the rotatable valve member has axially extending slots, which are adapted to register with the slots 71 of the valve member 70. The regions 75' between the slots 71 extend in an azimuth direction over a somewhat greater distance than that over which the slots 71 extend in an azimuth direction, i.e. the regions between these slots 71 are somewhat-wider than the latter. In the same way the bridges or space 77 between the slots in the outer cylinder 75 of the rotatable membet valve are somewhat wider than the slots 71 of the fixed valve member.
Secured to the member 73 is a guide blade ring 78 whose blades are so directed that the member is rotated by the swirl of the hydraulic medium in one direction up to an abutment. In this position the slots of the valve register with the slots of the end housing and the bridges of the rotatable member with the bridges of the fixed member. This means that when the pump is operating the medium can freely flow in the direction of the arrow 69 through the pump chamber and be discharged therefrom in the direction of the arrow 80. If now the flow is interrupted for any reason, a spirally wound spring 81 which biasses the rotatable member in the opposite direction to that in which it is turned by the swirl of the flow of medium, causes an angular displacement of this valve member in the opposite direction up to a second abutment. In this position the slots in the outer cylindrical wall 77 of the rotatable member come into register with the bridges 75 of the fixed member on the one hand, and the bridges between the slots in the outer cylindrical wall of the rotatable member with the slots 71 of the fixed member on the other hand. ln this position the valve defined by the fixed valve member and the moveable valve member 73 is closed, so that if for example the pump shuts down, no flow of medium produced by adjacent pumps can flew back through it. Thereby the possibilty of a. shunt path for the medium through shut-down pumps is eliminated.
lt is pointed out that the support of the cock 73 can be adjusted by means of a screw 82 which presses on the bearing dish 83. Relief bores 84 provide pressure equalization. Outwa'rdly conical feet 85 facilitate insertion of the pump into the sheet metal ring 86 during installation. Other devices for adjusting the bearing may be provided in place of the screw 82.
I claim:
l. A flow. responsive valve device for preventing back-flow of fluidthrough a centrifugal pump when the pump is not operating and when said pump creates a fluid swirl in a pump discharge area when the pump is operating, said valve device comprisinga fixed valve member in the discharge area having apertures therein, a rotatable valve member in the discharge area having apertures therein adapted in a first rotatable position thereof to overlie the apertures in said fixed member to allow fluid flow through the apertures and in a second rotatable position thereof tobe masked by the space between the apertures of said fixed member to' prevent fluid flow through the apertures, spring means urging said rotatable valve member towards said second rotat able position, andblading on said rotatable member cated in said discharge area adapted to be contacted by the fluid swirl when said pump is operating to urge said rotatable member to the first position against the force of the spring means such that the apertures of the first and second members overlie each other when the pump is operating.
2. A flow responsive valve device according to claim 1 wherein eachsaid valve member comprises a hollow cylinder and wherein said apertures comprise slots with

Claims (4)

1. A flow responsive valve device for preventing back-flow of fluid through a centrifugal pump when the pump is not operating and when said pump creates a fluid swirl in a pump discharge area when the pump is operating, said valve device comprising a fixed valve member in the discharge area having apertures therein, a rotatable valve member in the discharge area having apertures therein adapted in a first rotatable position thereof to overlie the apertures in said fixed member to allow fluid flow through the apertures and in a second rotatable position thereof to be masked by the space between the apertures of said fixed member to prevent fluid flow through the apertures, spring means urging said rotatable valve member towards said second rotatable position, and blading on said rotatable member located in said discharge area adapted to be contacted by the fluid swirl when said pump is operating to urge said rotatable member to the first position against the force of the spring means such that the apertures of the first and second members overlie each other when the pump is operating.
2. A flow responsive valve device according to claim 1 wherein each said valve member comprises a hollow cylinder and wherein said apertures comprise slots with the space between adjacent slots being at least as wide as the slots.
3. A flow responsive valve device according to claim 1 having in addition two spherical bearings mounting the rotatable valve member where the center of both bearings lie on the longitudinal axis of the pump, and adjustable means for moving one of said bearings in an axial direction.
4. A flow responsive valve device according to claim 3 wherein said spring means comprises a spiral spring.
US29314172 1971-10-07 1972-09-28 Device for preventing back-flow in centrifugal pumps operating in parallel Expired - Lifetime US3854848A (en)

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AT865871A AT333904B (en) 1971-10-07 1971-10-07 REACTOR TANK, IN PARTICULAR FOR BOILING WATER REACTORS

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US29310472 Expired - Lifetime US3803432A (en) 1971-10-07 1972-09-28 Bearing structure for mounting rotors in motors having spherical air gaps and including means for limiting axial movement of the rotors

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US29310472 Expired - Lifetime US3803432A (en) 1971-10-07 1972-09-28 Bearing structure for mounting rotors in motors having spherical air gaps and including means for limiting axial movement of the rotors

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US (2) US3854848A (en)
JP (5) JPS4845902A (en)
AT (1) AT333904B (en)
DE (5) DE2246263A1 (en)
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SE (2) SE381715B (en)

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US4021123A (en) * 1974-08-22 1977-05-03 The Perkin-Elmer Corporation Heat exchanger for analysis apparatus
US4035108A (en) * 1971-10-07 1977-07-12 Nikolaus Laing Axial flow pump for a pivotal rotor
US4188173A (en) * 1976-10-06 1980-02-12 The United States Of America As Represented By The Department Of Energy Vertical pump with free floating check valve
US5052660A (en) * 1990-09-17 1991-10-01 William Bergman Electrical wire threading apparatus
US6004096A (en) * 1997-12-30 1999-12-21 American Turbine Pump Co. Inc. Hydro-surge bowl valve
US11808268B2 (en) 2020-10-19 2023-11-07 Milwaukee Electric Tool Corporation Stick pump assembly

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US4730989A (en) * 1984-10-11 1988-03-15 Karsten Laing Rotodynamic pump with spherical bearing
US4599530A (en) * 1984-11-02 1986-07-08 Karsten Laing Rotor supported to be able to wobble
DE3520596A1 (en) * 1985-06-08 1986-12-11 Standard Magnet GmbH & Co, 7148 Remseck LOTELY FASTENED BEARING COLUMN FOR SPHERICAL PUMPS
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DE3609445A1 (en) * 1986-03-20 1987-09-24 Klein Schanzlin & Becker Ag WIRING HARNESS FOR ELECTRICALLY DRIVEN MACHINES
US4874300A (en) * 1987-12-21 1989-10-17 Laing Karsten A Ceramic step bearing in a centrifugal pump
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JPH08232882A (en) * 1995-02-22 1996-09-10 Tiger Vacuum Bottle Co Ltd Centrifugal pump
WO1999053627A1 (en) 1998-04-10 1999-10-21 Chrimar Systems, Inc. Doing Business As Cms Technologies System for communicating with electronic equipment on a network
US6617730B2 (en) * 2001-12-28 2003-09-09 Sunonwealth Eletric Machine Industry Co., Ltd. Rotation shaft support structure of motor
US6713925B2 (en) * 2002-05-20 2004-03-30 Karsten A. Laing Electric motor with reduced axial length
US6713918B2 (en) * 2002-05-20 2004-03-30 Oliver Laing Spherical bearing for electrical machines with permanent magnetic rotors
US20040000824A1 (en) * 2002-05-20 2004-01-01 Laing Karsten A. Electrical motor with spherically supported rotor
US6736616B2 (en) * 2002-05-20 2004-05-18 Oliver Laing Centrifugal pump with integrated motor
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DE102004008158A1 (en) * 2004-02-12 2005-09-22 Laing, Oliver Spherical bearing, electric motor and circulation pump
ATE524866T1 (en) 2006-11-30 2011-09-15 Sonceboz Sa LINEAR DRIVE BY SPINDLE DRIVE
DE102014222241B3 (en) * 2014-10-30 2016-03-31 Continental Automotive Gmbh Electrically driven pump
CN109538490A (en) * 2019-01-09 2019-03-29 浙江维新汽车配件有限公司 A kind of automobile cooling water pump
CN113757157A (en) * 2021-08-19 2021-12-07 鑫磊压缩机股份有限公司 Impeller combined structure of magnetic suspension axial flow fan

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US2336010A (en) * 1942-09-17 1943-12-07 Fairchild Engine & Airplane Supercharger
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US4035108A (en) * 1971-10-07 1977-07-12 Nikolaus Laing Axial flow pump for a pivotal rotor
US4021123A (en) * 1974-08-22 1977-05-03 The Perkin-Elmer Corporation Heat exchanger for analysis apparatus
US4188173A (en) * 1976-10-06 1980-02-12 The United States Of America As Represented By The Department Of Energy Vertical pump with free floating check valve
US5052660A (en) * 1990-09-17 1991-10-01 William Bergman Electrical wire threading apparatus
US6004096A (en) * 1997-12-30 1999-12-21 American Turbine Pump Co. Inc. Hydro-surge bowl valve
US11808268B2 (en) 2020-10-19 2023-11-07 Milwaukee Electric Tool Corporation Stick pump assembly

Also Published As

Publication number Publication date
ATA865871A (en) 1976-04-15
FR2155690A5 (en) 1973-05-18
DE2246264B2 (en) 1974-12-19
DE2265089A1 (en) 1976-07-15
SE400680B (en) 1978-04-03
FR2202391A1 (en) 1974-05-03
US3803432A (en) 1974-04-09
FR2155702A5 (en) 1973-05-18
DE2246298A1 (en) 1973-04-12
JPS4845814A (en) 1973-06-30
FR2202391B1 (en) 1976-08-20
JPS4845904A (en) 1973-06-30
GB1412571A (en) 1975-11-05
DE2246264C3 (en) 1975-07-31
GB1406492A (en) 1975-09-17
FR2156270B1 (en) 1976-08-20
DE2246298C3 (en) 1979-07-05
DE2246263A1 (en) 1973-04-12
GB1410507A (en) 1975-10-15
FR2178259A1 (en) 1973-11-09
SE381715B (en) 1975-12-15
DE2246298B2 (en) 1978-11-09
FR2156270A1 (en) 1973-05-25
JPS4845903A (en) 1973-06-30
AT333904B (en) 1976-12-27
JPS4845902A (en) 1973-06-30
JPS4861903A (en) 1973-08-30
FR2155701A5 (en) 1973-05-18
DE2246265A1 (en) 1973-05-30
GB1412572A (en) 1975-11-05
DE2246264A1 (en) 1973-04-12

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