EP3184823A1 - Pompe centrifuge - Google Patents

Pompe centrifuge Download PDF

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Publication number
EP3184823A1
EP3184823A1 EP15201513.7A EP15201513A EP3184823A1 EP 3184823 A1 EP3184823 A1 EP 3184823A1 EP 15201513 A EP15201513 A EP 15201513A EP 3184823 A1 EP3184823 A1 EP 3184823A1
Authority
EP
European Patent Office
Prior art keywords
turbine wheel
centrifugal pump
pump
flow
transducer
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP15201513.7A
Other languages
German (de)
English (en)
Other versions
EP3184823B1 (fr
Inventor
Erik Bundesen Svarre
Jan Carøe Aarestrup
Peter Elvekjaer
Flemming Munk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Holdings AS
Original Assignee
Grundfos Holdings AS
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 Grundfos Holdings AS filed Critical Grundfos Holdings AS
Priority to ES15201513T priority Critical patent/ES2731851T3/es
Priority to EP15201513.7A priority patent/EP3184823B1/fr
Priority to DK15201513.7T priority patent/DK3184823T3/da
Priority to RU2016149666A priority patent/RU2649722C1/ru
Priority to US15/384,603 priority patent/US10823183B2/en
Priority to CN201611190591.9A priority patent/CN106968968B/zh
Publication of EP3184823A1 publication Critical patent/EP3184823A1/fr
Application granted granted Critical
Publication of EP3184823B1 publication Critical patent/EP3184823B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • 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
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/086—Units comprising pumps and their driving means the pump being electrically driven for submerged use the pump and drive motor are both submerged
    • 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
    • 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
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/128—Adaptation of pump systems with down-hole electric drives
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B47/00—Survey of boreholes or wells
    • E21B47/008—Monitoring of down-hole pump systems, e.g. for the detection of "pumped-off" conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/08—Multi-stage pumps the stages being situated concentrically
    • 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
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/10—Units comprising pumps and their driving means the pump being electrically driven for submerged use adapted for use in mining bore holes
    • 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
    • F04D15/0088—Testing machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal 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
    • F04D29/007—Details, component parts, or accessories 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • 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
    • F04D29/22—Rotors specially for centrifugal 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the invention relates to a centrifugal pump.
  • Centrifugal pumps are usually driven by electric drive motors.
  • the control of these drive motors and, consequently, the control of the centrifugal pump can be done the better, the more knowledge about the possibly changing during operation operating state of the centrifugal pump.
  • These flow parameters also include the flow rate through the centrifugal pump.
  • the object of the invention is to provide a centrifugal pump, wherein the flow rate through the centrifugal pump can be detected with a relatively low-cost construction with high accuracy.
  • the centrifugal pump according to the invention is preferably a multi-stage pump.
  • the centrifugal pump preferably has more than one pump stage, which is equipped with an impeller rotatably mounted on a pump shaft.
  • the pump stage also has at least one stator to provide the output side of the pump stage a possible twist-free flow available.
  • the centrifugal pump is designed as a multi-stage centrifugal pump, in which in the direction of the pump shaft a plurality of mutually flow-connected pump stages, each with an impeller and at least one stator are provided.
  • the centrifugal pump has a turbine wheel.
  • This turbine wheel is arranged on the pump shaft without movement coupling with the pump shaft.
  • the pump shaft passes through a centrally formed on the turbine wheel hub, wherein the pump shaft can rotate relative to the surrounding turbine and / or vice versa.
  • the turbine wheel forms a transmitter of a flow measuring device, with which the flow rate through the centrifugal pump or the flow velocity of the funded by the centrifugal pump fluid is detected within the centrifugal pump.
  • the turbine wheel in principle has an embodiment in which the delivery flow to the turbine wheel exerts a torque about its central axis.
  • the turbine As a transmitter, the turbine generates a proportional to the flow measurement signal, which is received by a signal receiver of the flow measuring device and then, for example, in the control of a drive motor for driving the centrifugal pump can flow.
  • the measurement signal generated by the turbine wheel can be the torque exerted by the delivery flow on the turbine wheel or a rotational speed of a rotational movement of the turbine wheel caused by the torque, as described below will be discussed in more detail with preferred developments of the centrifugal pump according to the invention.
  • the bearing friction of a radial bearing optionally located between the pump shaft and the turbine wheel and / or solids entering a clearance between the pump shaft and the turbine wheel may cause frictional engagement between the pump shaft and the turbine wheel.
  • Such a frictional engagement causes considerable measurement inaccuracies in the flow measurement, since it causes the actual torque acting on the turbine wheel of the applied torque from the flow to the turbine wheel, which forms the basis for determining the flow rate directly or indirectly, especially at small Speeds of the pump shaft and concomitantly with low flow rate of the centrifugal pump differs.
  • the torque exerted by the delivery flow on the turbine wheel is directed in opposite direction to a torque exerted on the impeller of the at least one pump stage via the pump shaft. That is, when the pump shaft and the thus fixed impeller of the at least one pump stage in the direction of flow of the centrifugal pump are driven clockwise, the blading of the turbine wheel is such that the turbine wheel is subjected to left-handed force from the flow through the centrifugal pump.
  • the blading of the turbine wheel is typically designed so that the turbine wheel is subjected to dextrorotatory force from the flow through the centrifugal pump. It has been shown that the torque exerted by the flow on the turbine wheel torque in this embodiment, even at a relatively low flow rate of the centrifugal pump forms a largely proportional to the flow rate size, so that the flow rate can be determined with sufficient accuracy.
  • the turbine wheel is arranged downstream of a last pump stage of the centrifugal pump. Accordingly, the turbine wheel is arranged in a centrifugal pump with only one pump stage in the flow direction of this pump stage behind the pump stage and arranged at a multi-stage centrifugal pump in the flow direction of the pump stages behind the furthest from the fluid inlet of the pump pump stage.
  • This measure also aims to increase the measurement accuracy in the flow measurement, since the turbine wheel is in this way as far as possible from occurring possibly in the region of the fluid inlet of the centrifugal pump flow and pressure changes.
  • the pressure chamber downstream of the last pump stage usually provides enough space for the arrangement of the turbine wheel, so that the arrangement of the turbine wheel does not affect the overall size of the centrifugal pump.
  • a rotational speed of a rotational movement of the turbine wheel caused by the delivery flow through the centrifugal pump can be used as the measurement signal generated by the turbine wheel.
  • the turbine wheel is rotatably mounted on the pump shaft.
  • the turbine wheel is thus preferably rotatable by the flow through the centrifugal pump relative to the pump shaft and in the opposite direction of rotation to the direction of rotation of the pump shaft.
  • At least one signal means which moves relative to a signal receiver of a measuring transducer of the flow measuring device, is expediently arranged on the turbine wheel.
  • the at least one signal means is arranged on a largest outer circumference of the turbine wheel.
  • this largest outer circumference is generally formed by an outer ring surrounding the outer circumference of the blades of the turbine wheel, and accordingly it is particularly favorable to arrange the at least one signal means on the outer circumference of this outer ring.
  • At least three signal means are arranged on the outer circumference of the turbine wheel, which have a different distance from one another in the direction of rotation of the turbine wheel.
  • the at least three differently spaced in the direction of rotation of the turbine wheel signal means allow in conjunction with a corresponding evaluation, in addition to the rotational speed and to determine the direction of rotation of the turbine wheel.
  • this direction of rotation of the turbine wheel should normally be directed counter to the direction of rotation of the pump shaft, under certain circumstances, for example due to the penetration of solid particles into the space between the hub of the turbine wheel and the pump shaft, due to a consequent jamming of the turbine wheel with the pump shaft , coincide with the direction of rotation of the pump shaft.
  • the rotational direction of the turbine wheel always coincides with the rotational direction of the pump shaft due to the friction between the turbine wheel and the pump shaft when the delivery rate of the pump is below a certain value.
  • the flow measuring device is not functional.
  • such a non-operational capability of the flow measuring device can due to the According to the invention possible detection of a wrong direction of rotation of the turbine directly detected and subsequently corrected.
  • the rotational speed and direction of rotation of the turbine wheel may be generally determined with all known sensor arrangements for determining the velocity of a moving body relative to a stationary body.
  • a magnetic-inductive speed measurement is provided.
  • the at least one signal means is a permanent magnet and the signal receiver of the transducer is a magnetic flux sensor.
  • the at least one signal means is a light reflector which rotates through the beam path upon rotation of the turbine wheel a light source is moved, wherein the transducer has a light sensor which is arranged in the reflection beam path of the reflector.
  • the light sensor receives at each passage of the at least one light reflector through the beam path of a relative to the turbine fixedly arranged light source emitted light beam, a light signal from a signal connected to the transducer control device, the rotational speed of the turbine wheel and concomitantly the flow through the Centrifugal pump determined.
  • this can also be advantageously arranged rotationally fixed in the centrifugal pump, wherein the pump shaft can rotate in the interior of the turbine wheel.
  • the flow of the turbine wheel through the flow causes no rotational movement of the turbine wheel, but still acting on the turbine torque can be detected and thus directly form the basis for determining the flow rate or the flow rate of the fluid flowing through the centrifugal pump ,
  • the flow measuring device on a transducer in the form of a force transducer which is arranged such that it measures a torque acting on the turbine wheel.
  • the transducer is expediently arranged fixed in or on the centrifugal pump, wherein it is in operative connection with the turbine wheel.
  • sensors suitable for detecting forces or moments such as strain gauges, piezoelastic sensors and the like, can be used as force transducers.
  • the force transducer is not in direct contact with the turbine wheel, but is operatively connected via a suitable for the transmission of forces or moments component with the turbine wheel, which makes it possible to arrange the force transducer at a particularly favorable location in the centrifugal pump.
  • at least one recess is formed on the outer circumference of the turbine wheel, into which engages a torque arm in contact with the force transducer.
  • the moment arm is in this case formed by a torsionally stiff component, by means of which a torque acting on the turbine wheel can be transmitted in an unadulterated manner to the force transducer arranged at a distance from the turbine wheel.
  • the moment arm is expediently with a free end in contact with the force transducer and engages with another end positively in the at least one recess on the turbine wheel.
  • the turbine wheel is aligned during assembly of the centrifugal pump in such a way that the moment arm engages positively in the recess formed on the turbine wheel.
  • This work is facilitated by the fact that, as is further preferred, formed over the outer circumference of the turbine wheel, a plurality of recesses for receiving the moment arm, so that the moment arm for attachment to the turbine wheel in any of the formed on the outer circumference of the turbine wheel recesses can intervene positively.
  • the measuring transducer of the flow measuring device is arranged outside the interior of the pump housing of the centrifugal pump.
  • This embodiment in which the transducer does not engage in the interior of the pump housing, but quite in a Wandungsteil the pump housing may be integrated, is advantageous in that electrical components of the transducer are protected in this way from the flow in the interior of the pump housing, without these components must be encapsulated in a complicated manner fluidly against the flow through the centrifugal pump.
  • an opening is formed on the outer wall of the pump housing, on the outside of which the transducer is arranged.
  • This arrangement of the transducer has the advantage that the transducer is not only sufficiently protected from the flow in the pump housing, but also, for example, is easily accessible for maintenance or repair purposes.
  • the opening on which the transducer is arranged expediently removable destructive, are also used to vent the pump housing when removing the transducer so that no additional opening must be formed on the pump housing for this purpose.
  • the in the Fig. 1 and 2 illustrated centrifugal pump has a pump housing 2, which is formed by a lower housing part 4, an adjoining hollow cylindrical housing middle part 6 and a subsequent upper housing part 8.
  • a fluid inlet 10 and a fluid outlet 12 of the centrifugal pump are formed on the lower housing part 4.
  • the fluid inlet 10 is in fluid communication with five pump stages 14 of the centrifugal pump, which are arranged one above the other in the region of the housing middle part 6 in the direction of the housing upper part 8.
  • Each of the pump stages 14 has a fixed housing 16 in the pump housing, in which an impeller 18 and a guide or stator 20 are arranged, which in Fig. 5 are shown.
  • the housings 16 are in each case flow-connected to adjacent housings 16, with a last housing 16 in the direction of the upper housing part 16 being flow-connected via an opening 22 to a pressure chamber 24 formed in the region of the upper housing part 8.
  • the wheels 18 of the pump stages 14 are rotatably connected to a pump shaft 26, which is concentric with the middle part of the housing 6 extends through the pump housing 2 and protrudes from the pump housing 2 on the upper housing part 8.
  • the pump shaft 26 is connected to the motor shaft of a drive motor, not shown, which is mounted on a formed on the upper housing part 8 motor chair 28.
  • the impellers 18 of the individual pump stages convey a fluid from the fluid inlet 10 through the pump stages 14 to the pressure chamber 24, from where the fluid flows via an annular gap 30 between the wall of the housing middle part 6 and the housing 16 of the pump stages to the fluid outlet 12 of the centrifugal pump passes.
  • the fluid outlet 12 could also be located at the opposite axial end of the centrifugal pump.
  • a turbine wheel 32 Downstream of the last in the flow direction, directly adjacent to the pressure chamber 24 pump stage 14, a turbine wheel 32 is rotatably mounted in the pressure chamber 24.
  • This turbine wheel 32 is arranged around the pump shaft 26, wherein the pump shaft 26 passes through a hub 34 of the turbine wheel 32 and the turbine wheel 32 is rotatably mounted on the pump shaft 26.
  • a plurality of blades 36 extend radially outward, where they are connected to an outer ring 38 of the turbine wheel 32.
  • the blades 36 of the turbine wheel 32 are arranged in the flow direction of the centrifugal pump directly above the formed on the last pump stage 14 opening 22 through which the flow reaches the pressure chamber 24 in the axial direction of the pump housing by the centrifugal pump.
  • the turbine wheel 32 forms a transmitter of a flow measuring device, with which the flow rate through the centrifugal pump during operation of the centrifugal pump is continuously determined to then flow, for example, in the control of the drive motor for the centrifugal pump.
  • a transmitter that is in the Fig. 1 and 2 shown turbine wheel 32 equipped with three signal means in the form of permanent magnets 42 which are arranged in three recesses 44 which are formed on the outer peripheral side of the outer ring 38 of the turbine wheel 32 in relation to the direction of rotation of the turbine wheel 32 different distances from each other.
  • an opening 46 is formed on the upper housing part 8 of the pump housing 2, an opening 46 is formed.
  • This opening 46 is penetrated by a transducer 48 of the flow measuring device, which extends into the immediate vicinity of the outer ring 38 of the turbine wheel 32.
  • This sensor 48 has a signal receiver in the form of a magnetic flux sensor, which detects the magnetic fields emanating from the three permanent magnets 42 upon rotation of the turbine wheel 32, whereupon a control device signal-connected to the sensor 48, which is not shown in the drawings, the rotational speed of the turbine wheel 32 and concomitantly determines the flow rate through the centrifugal pump. Due to the different spacing of the permanent magnets 42 from one another, the control device can also determine the direction of rotation of the turbine wheel 32.
  • centrifugal pump differs from that in the Fig. 1 and 2 shown centrifugal pump only in terms of the design of the flow measuring device.
  • the transmitter of the flow measuring device is formed by a rotatably mounted on the pump shaft 26 rotatably mounted turbine wheel 32 ', wherein the pump shaft 26, a hub 34' of the turbine wheel 32 'passes through.
  • the type and arrangement of the blades 36 of the turbine wheel 32 ' correspond to those of the turbine wheel 32 of the centrifugal pump shown in Figs.
  • a threaded opening 50 is formed on the housing upper part 8 of the pump housing 2, into which a flow sensor 48' of the flow measuring device is screwed, although the sensor 48 'partially engages in the opening 50, but not in the interior of the pressure chamber 24 protrudes.
  • the opening 50 can be used to vent the pump housing.
  • Fig. 6 not immediately apparent, has the transducer 48 'via a light source and a light sensor, which are arranged substantially on the outside of the housing top 8 and the outside of the pump housing 2.
  • centrifugal pump differs from the in the Fig. 1 and 2 shown centrifugal pump only in terms of the design of the flow measuring device.
  • a transmitter is formed by a turbine wheel 32 ".
  • the arrangement of this turbine wheel 32" in the pressure chamber 24 is such that the pump shaft 26 reaches through a hub 34 "of the turbine wheel 32".
  • the type and arrangement of the blades 36 of the turbine wheel 32 “correspond to those of the turbine wheels 32 and 32 '.”"On an outer ring 38" of the turbine wheel 32 ", a plurality of recesses 52 are uniformly distributed on its outer circumference, the meaning of which will be discussed below.
  • an opening 54 is formed on the upper housing part 8 of the pump housing 2, whose central axis is directed onto the outer circumference of the outer ring 38" of the turbine wheel 32 ".
  • This sleeve 56 is penetrated by a moment arm 58, which engages in the interior of the pressure chamber 24.
  • the moment arm 58 is fixed in a form-fitting manner transversely to its longitudinal extent
  • the moment arm 58 has a cylindrical projection 60 whose outer cross section corresponds to the cross section of the recesses 52 formed on the outer ring 38 "of the turbine wheel 32". With the projection 60, the moment arm 58 engages in one of the recesses 52 on the outer ring 38 "of the turbine wheel 32", whereby the turbine wheel 32 is prevented from rotating.
  • a measuring transducer 48 "of the flow measuring device also engages in the sleeve 56.
  • This transducer 48" has a signal receiver, not visible in the drawing, in the form of a force transducer, which is in contact with the moment arm 58.
  • the turbine wheel 32 can not rotate this, but the flow causes a torque or a force on the turbine wheel 32 "of the turbine wheel 32" on the torque arm 58 is forwarded to the transducer 48 "and is detected there by the force transducer, whereupon a signal connected to the force transducer controller, which is also not shown in the drawing, on the basis of the detected torque or the detected force of the flow through the centrifugal pump is determined.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geophysics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
EP15201513.7A 2015-12-21 2015-12-21 Pompe centrifuge Active EP3184823B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
ES15201513T ES2731851T3 (es) 2015-12-21 2015-12-21 Bomba centrífuga
EP15201513.7A EP3184823B1 (fr) 2015-12-21 2015-12-21 Pompe centrifuge
DK15201513.7T DK3184823T3 (da) 2015-12-21 2015-12-21 Centrifugalpumpe
RU2016149666A RU2649722C1 (ru) 2015-12-21 2016-12-19 Лопастной насос
US15/384,603 US10823183B2 (en) 2015-12-21 2016-12-20 Centrifugal pump
CN201611190591.9A CN106968968B (zh) 2015-12-21 2016-12-21 离心泵

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15201513.7A EP3184823B1 (fr) 2015-12-21 2015-12-21 Pompe centrifuge

Publications (2)

Publication Number Publication Date
EP3184823A1 true EP3184823A1 (fr) 2017-06-28
EP3184823B1 EP3184823B1 (fr) 2019-03-27

Family

ID=54850509

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15201513.7A Active EP3184823B1 (fr) 2015-12-21 2015-12-21 Pompe centrifuge

Country Status (6)

Country Link
US (1) US10823183B2 (fr)
EP (1) EP3184823B1 (fr)
CN (1) CN106968968B (fr)
DK (1) DK3184823T3 (fr)
ES (1) ES2731851T3 (fr)
RU (1) RU2649722C1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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CN117823415B (zh) * 2024-03-04 2024-05-03 山东华立供水设备有限公司 一种多级离心泵

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DK3184823T3 (da) 2019-07-08
RU2649722C1 (ru) 2018-04-04
CN106968968A (zh) 2017-07-21
EP3184823B1 (fr) 2019-03-27
US20170175749A1 (en) 2017-06-22
CN106968968B (zh) 2019-03-15
ES2731851T3 (es) 2019-11-19

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