EP2893194B1 - Pompe pour canal latéral et procédé de fonctionnement d'une pompe pour canal latéral - Google Patents

Pompe pour canal latéral et procédé de fonctionnement d'une pompe pour canal latéral Download PDF

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Publication number
EP2893194B1
EP2893194B1 EP13756173.4A EP13756173A EP2893194B1 EP 2893194 B1 EP2893194 B1 EP 2893194B1 EP 13756173 A EP13756173 A EP 13756173A EP 2893194 B1 EP2893194 B1 EP 2893194B1
Authority
EP
European Patent Office
Prior art keywords
pump
rpm
overspeed
speed
channel
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.)
Active
Application number
EP13756173.4A
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German (de)
English (en)
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EP2893194A1 (fr
Inventor
Heiner KÖSTERS
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.)
Sterling Industry Consult GmbH
Original Assignee
Sterling Industry Consult GmbH
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 Sterling Industry Consult GmbH filed Critical Sterling Industry Consult GmbH
Priority to EP13756173.4A priority Critical patent/EP2893194B1/fr
Publication of EP2893194A1 publication Critical patent/EP2893194A1/fr
Application granted granted Critical
Publication of EP2893194B1 publication Critical patent/EP2893194B1/fr
Active legal-status Critical Current
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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
    • 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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • 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
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial 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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/006—Regenerative pumps of multistage type the stages being axially offset
    • 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
    • F04D9/004—Priming of not self-priming pumps
    • F04D9/006—Priming of not self-priming pumps by venting gas or using gas 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
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/02—Self-priming pumps

Definitions

  • the invention relates to a side channel pump and a method for operating a side channel pump.
  • an impeller rotates in a working chamber provided with a side channel.
  • JP 2002 03174 describes a side channel pump unit an impeller which rotates in a working chamber provided with a side channel.
  • the invention is based on the object, a side channel pump and a method for operating a side channel pump imagine that allow suction of gas even if no amount of liquid is contained in the working chamber of the pump. Based on the above-mentioned prior art, the object is achieved with the features of the independent claims. Advantageous embodiments can be found in the subclaims.
  • the side channel pump with gas-filled working chamber in a first step, is operated at an overspeed. In a second step, the speed is reduced to an operating speed to deliver a liquid.
  • Side channel pumps are generally designed for a maximum speed that they can use to deliver fluid. Overspeed refers to a speed that is above this maximum speed.
  • the operating speed at which the pump according to the invention conveys fluid is at most as large as the maximum speed. The operating speed may also be below the maximum speed.
  • the working chamber of the side channel pump is filled with gas, if in the working chamber no amount of liquid is contained, which could seal the radial leakage gap between the impeller and the housing with a liquid ring.
  • the pump makes a fast-running blower when pumping gas, with the despite the considerable leakage gaps a good suction performance is achieved.
  • the speed is reduced and, as in a conventional side channel pump, liquid is pumped during normal operation.
  • the overspeed is considerably above the operating speed.
  • the overspeed may be at least 50%, preferably at least 70%, more preferably at least 90% higher than the operating speed. Based on the maximum speed, the overspeed is preferably greater by at least 30%, more preferably by at least 50%, more preferably by at least 70%.
  • the drive power is lower when pumping gas than when pumping liquids.
  • the drive power in operation with overspeed is at least 10%, preferably at least 30%, more preferably at least 50% lower than the drive power at operating speed.
  • the operating speed and the maximum speed may be between 1200 rpm and 4000 rpm.
  • the volume flow of liquid which the pump delivers at operating speed is preferably greater than 1 m 3 / h, more preferably greater than 10 m 3 / h, more preferably greater than 30 m 3 / h.
  • the overspeed may be, for example, between 3600 rpm and 7000 rpm.
  • the overspeed in slow-running pumps where the operating speed is between 1200 rpm and 2000 rpm, the overspeed may be 3600 rpm to 5000 rpm. at faster running pumps with an operating speed of between 2000 rpm and 4000 rpm, the overspeed can be between 5000 rpm and 7000 rpm.
  • the pumps according to the invention are frequently used in installations in which it is of great importance that the pumped liquid does not escape to the outside.
  • This purpose is useful when a side channel pump is used which is sealless.
  • Sealless means that the end of the shaft on which the drive motor acts is located entirely within the pump housing. Since the shaft is not guided through the housing to the outside, no shaft seal is required at this point.
  • a magnetic coupling may be provided between the output shaft of the motor and the drive shaft of the pump.
  • the magnet of the output shaft can be arranged radially outside the magnet of the drive shaft, wherein the housing between the two magnets is designed as a so-called split pot.
  • the efficiency of the pump can be improved if a side channel pump is used, in which a plurality of side chambers with a provided working chambers are arranged one behind the other.
  • the outlet opening of the first working chamber leads to the inlet opening of the second working chamber, so that the conveyed medium successively passes through all the working chambers.
  • the pump is therefore multi-level.
  • an impeller rotates.
  • the impeller is enclosed between two end faces of the working chamber, wherein the side channel is formed in one of the end faces.
  • the side channel corresponds to a depression in the end face, which means that the between the impeller and the end face existing leakage gap in the region of the side channel is increased.
  • the side channel may extend in an arcuate path from the inlet opening to the outlet opening of the working chamber.
  • the arcuate path may substantially correspond to the path that the impeller also describes on the way from the inlet opening to the outlet opening.
  • the input stage of the pump should be designed to withstand this sudden load.
  • the input stage may be a centrifugal stage.
  • an impeller In a centrifugal stage, an impeller is provided with a plurality of passages extending from a central portion of the impeller to a peripheral portion of the impeller. The pumping action of such a centrifugal stage results from the fact that the conveyed medium moves under centrifugal force through the channel from the central area to the peripheral area.
  • the pump Since the drive power is low when operating at overspeed, the pump is decelerated quickly as soon as the liquid has entered the input stage. Before the liquid enters the subsequent impeller and side channel stages, the speed has already decreased significantly, so that the subsequent stages of the sudden load are only exposed to a lesser extent.
  • the side channel pump according to the invention is provided with a controller adapted to operate the pump at an overspeed when the working chamber of the pump is gas filled and to reduce the speed to an operating speed when liquid enters the pump. It is possible that the controller is set up so that it causes an active braking of the pump. However, this is not necessary. As soon as liquid enters the pump, the resistance increases, so that the speed of the pump decreases even if the drive power remains unchanged. Periodically, the drive motor is designed so that it can not keep the pump at overspeed even when operating at maximum power after fluid has entered the pump. The controller may therefore be arranged to wait for the liquid to enter until the speed has reduced itself to the desired operating speed and then increase the drive power so that the pump is kept constantly at the operating speed.
  • the pump can be configured in multiple stages by a plurality of side channels provided with working chambers are arranged one behind the other.
  • each working chamber is an impeller arranged, wherein the working chamber, the impeller and the side channel can be designed conventionally.
  • the input stage of the pump can be designed as a centrifugal stage.
  • the pump can be developed with further features which are described with reference to the method according to the invention.
  • a preferred field of application for the method according to the invention and the pump according to the invention is the conveyance of liquefied gas from a tank. This takes place, for example, at LPG filling stations, where liquefied petrol vehicles are refueled from a tank that is often buried in the ground.
  • the tank is partially filled with liquefied gas in the liquid state, the upper part of the tank and in particular the line leading to the pump according to the invention are occupied by vaporized liquid gas.
  • the pressure in the tank and the line thus corresponds to the vapor pressure of the liquid gas when the pump is not in operation.
  • the vapor of the liquefied gas is sucked in. This initially has the consequence that the pressure in the line drops and thereby passes more liquid gas into the gaseous state. If the pump has only a low suction power, it will continue to do so and only the newly vaporized gas will be continuously pumped.
  • the suction power of the pump according to the invention is large enough that a reduction in the temperature in the line is achieved, which results in that the vapor pressure in the line is lower than the vapor pressure in the tank. Due to the pressure difference, the liquid from the tank rises into the pipe and can be sucked by the pump. It is with the method according to the invention Therefore, it is possible to convey the liquefied gas from the tank in liquid form.
  • a shaft 14 is rotatably mounted in a pump housing 15.
  • the pump housing 15 is provided with an inlet opening 16 and an outlet opening 17, wherein the inlet opening 16 is arranged concentrically with the shaft 14.
  • the inlet opening 16 opposite the end of the pump housing 15 is formed as a gap pot 18, are arranged within the magnetic elements 19 which are connected to the shaft 14. Outside the containment shell 18 magnetic elements 20 are arranged, which are connected to the output shaft of an electric motor 21 are connected.
  • the electric motor 21 is provided with a controller 35.
  • the magnetic elements 20 When the electric motor 21 is put into operation, the magnetic elements 20 perform a rotational movement about the split pot 18. By transmitting the magnetic forces and the shaft 14 is rotated so that it rotates synchronously with the output shaft of the electric motor 21. With one end of the shaft 14 opening into the inlet port 16 and the other end of the shaft 14 received in the containment shell 18, the pump is sealless in the sense that there is no location at which the interior and exterior of the pump only separated by a shaft seal. This has the advantage that leakage of the pumped medium can be safely prevented.
  • the pump according to the invention comprises four stages, in each of which an impeller 22 rotates in a working chamber 23.
  • the impellers 22 have radially arranged wings with open vane spaces which are closely surrounded by the housing 15. Axially next to the impeller 22, the housing 15 forms an impeller 22 toward open side channel 24 in which the fluid is conveyed by impulse exchange with the impeller 22.
  • the inlet end of the side channel 24 is located opposite an inlet opening of the working chamber 23, which is formed in the housing Fig. 1 is not visible.
  • the entering through the inlet opening medium passes through the interstices of the wings through to the side channel 24. From the outlet opening of the preceding working chamber 23 each extends in Fig. 1 only schematically indicated channel 25 through the pump housing 15 through to the inlet opening the subsequent working chamber 23. The pumped medium thus passes successively through the four stages of the pump.
  • the input stage 26 of the pump is designed as a centrifugal stage.
  • An impeller 27 connected to the shaft 14 is provided with channels 40 extending from a central portion to a peripheral portion of the impeller 27. The medium entering the channels 40 in the central area is moved outward by the centrifugal force. From the outer end of the impeller 27, a passage extends through the pump housing 15 to the inlet port of the first working chamber 23.
  • the pump is designed to deliver fluids.
  • the pump is operated at a speed of, for example, 3000 rpm and the liquid is conveyed at a volume flow of, for example, 35 m 3 / h.
  • the pump 28 according to the invention is connected to a liquefied gas tank 29.
  • a riser 31 extends from the lower part of the tank 29 to the inlet opening 16 of the pump 28.
  • a conduit 34 is connected, which leads to a vehicle 32, which is to be refueled with LPG 30.
  • the flow rate of the pump is so great that it can not be completely absorbed by the car 32.
  • gas bubbles are separated from the flow and returned to the tank 29.
  • the tank 29 is filled with liquid gas 30 to about one third.
  • the remaining space in the tank 29 and in the riser 31 is filled with vaporized LPG, the Pressure therefore corresponds to the vapor pressure of the liquefied gas.
  • the liquid gas first enters the pump 28 in a gaseous state. Since with the application of negative pressure in the tank 29 continues to evaporate liquefied gas, the suction power of the pump must be large in this phase to still suck liquid gas through the riser 31 in the liquid state. According to the invention, this is achieved in that the pump is operated in this phase with an overspeed, which is well above the operating speed.
  • the overspeed with which the pump is virtually operated as a fan for example, be 7000 U / min. This speed is well above the speed at which the pump can operate at maximum when fluid is being delivered.
  • the performance of the pump when operated as a fan, is lower than in normal operation, where fluid is delivered. So if a low power is sufficient to accelerate the pump to overspeed, it follows that the working chambers 23 of the pump are filled with gas.
  • the controller 35 is thus configured to operate the electric motor 21 at the low speed overspeed.
  • the controller 35 is designed to increase the power of the electric motor 21 as soon as the pump 28 is decelerated to operating speed to maintain the pump at that speed. This operating condition is maintained until the car 32 is fully fueled. Once this is the case, the pump 28 is turned off.
  • Fig. 3 the process of the invention is shown in schematic form.
  • a car 32 to be refueled is connected to a line 34 of the arrangement according to the invention in step 10.
  • the low power pump 28 is accelerated to a speed of 7000 rpm.
  • the controller 35 is configured to adjust the power of the electric motor 21 in step 120 to maintain the speed of the pump 28 constant at the operating speed of 3000 rpm.
  • the pump 28 is turned off in step 130.
  • step 140 the line 34 is disconnected from the car 32 and the refueling process is completed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (15)

  1. Procédé d'exploitation d'une pompe à canal latéral (28), dans lequel une roue à aubes (22) tourne dans une chambre de travail (23) munie d'un canal latéral (24), avec les étapes suivantes :
    a. exploitation de la pompe à canal latéral (28) avec une chambre de travail (23) remplie de gaz lors d'une vitesse de rotation excessive ;
    b. réduction de la vitesse de rotation à une vitesse de rotation de service afin de refouler un liquide.
  2. Procédé selon la revendication 1, caractérisé en ce que la vitesse de rotation excessive est supérieure d'au moins 50 %, de préférence d'au moins 70 %, de préférence d'au moins 90 % à la vitesse de rotation de service.
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que la puissance d'entraînement à l'étape a. est inférieure d'au moins 10 %, de préférence d'au moins 30 %, de préférence d'au moins 50 % à la puissance d'entraînement à l'étape b.
  4. Procédé selon l'une des revendications 1 à 3, caractérisé en ce que la vitesse de rotation de service est entre 1200 tr/min et 4000 tr/min.
  5. Procédé selon l'une des revendications 1 à 4, caractérisé en ce que la vitesse de rotation excessive est entre 3600 tr/min et 7000 tr/min.
  6. Procédé selon la revendication 4 ou 5, caractérisé en ce que la vitesse de rotation de service est de l'ordre de 1200 tr/min à 2000 tr/min et la vitesse de rotation excessive est de l'ordre de 3600 tr/min à 5000 tr/min ou en ce que la vitesse de rotation de service est de l'ordre de 2000 tr/min à 4000 tr/min et la vitesse de rotation excessive est de l'ordre de 5000 tr/min à 7000 tr/min.
  7. Procédé selon l'une des revendications 1 à 6, caractérisé en ce que la pompe à canal latéral (28) est réalisée sans joint d'étanchéité.
  8. Procédé selon l'une des revendications 1 à 7, caractérisé en ce que la pompe à canal latéral (28) comprend une pluralité de chambres de travail (23) munies d'un canal latéral (24).
  9. Procédé selon l'une des revendications 1 à 8, caractérisé en ce que l'étage d'entrée (26) de la pompe à canal latéral (28) est conçu comme un étage centrifuge.
  10. Procédé selon la revendication 9, caractérisé en ce que l'étage centrifuge (28) comprend une roue (27) à l'intérieur de laquelle une pluralité de canaux (40) s'étend d'une zone centrale vers une zone périphérique.
  11. Procédé selon la revendication 10, caractérisé en ce que les canaux (40) sont répartis uniformément sur la circonférence de la roue (27).
  12. Procédé selon l'une des revendications 1 à 11, caractérisé en ce qu'un gaz liquide (39) est refoulé à partir d'un réservoir (29).
  13. Pompe à canal latéral avec une roue à aubes (22), qui tourne dans une chambre de travail (23) muni d'un canal latéral (24), caractérisée en ce qu'un dispositif de commande (35) est prévue, qui est conçue pour exploiter la pompe (28) avec une vitesse de rotation excessive lorsque la chambre de travail (23) de la pompe (28) est remplie de gaz, et pour réduire la vitesse de rotation à une vitesse de rotation de service lorsqu'un liquide entre dans la pompe (28).
  14. Dispositif constitué d'une pompe à canal latéral (28) selon la revendication 13, et d'un réservoir de gaz liquide (29), dans lequel le réservoir de gaz liquide (29) est relié avec l'ouverture d'admission (16) de la pompe (28).
  15. Dispositif selon la revendication 14, caractérisé en ce que le réservoir de gaz liquide (29) est disposé plus bas que la pompe à canal latéral (28).
EP13756173.4A 2012-09-03 2013-09-03 Pompe pour canal latéral et procédé de fonctionnement d'une pompe pour canal latéral Active EP2893194B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13756173.4A EP2893194B1 (fr) 2012-09-03 2013-09-03 Pompe pour canal latéral et procédé de fonctionnement d'une pompe pour canal latéral

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP12182748 2012-09-03
EP13756173.4A EP2893194B1 (fr) 2012-09-03 2013-09-03 Pompe pour canal latéral et procédé de fonctionnement d'une pompe pour canal latéral
PCT/EP2013/068168 WO2014033317A1 (fr) 2012-09-03 2013-09-03 Pompe à canal latéral et procédé d'utilisation d'une pompe à canal latéral

Publications (2)

Publication Number Publication Date
EP2893194A1 EP2893194A1 (fr) 2015-07-15
EP2893194B1 true EP2893194B1 (fr) 2016-11-30

Family

ID=46785296

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13756173.4A Active EP2893194B1 (fr) 2012-09-03 2013-09-03 Pompe pour canal latéral et procédé de fonctionnement d'une pompe pour canal latéral

Country Status (5)

Country Link
US (1) US9709060B2 (fr)
EP (1) EP2893194B1 (fr)
CN (1) CN104619989B (fr)
AU (1) AU2013310852B2 (fr)
WO (1) WO2014033317A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015197467A1 (fr) * 2014-06-24 2015-12-30 Sterling Industry Consult Gmbh Pompe à canal latéral
CN107939750B (zh) * 2017-12-26 2024-02-27 杭州大路实业有限公司 一种气液混输提升离心油泵
CN108730233B (zh) * 2018-04-13 2021-01-15 江苏大学 一种提高侧流道泵效率的方法

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD95183A5 (fr) * 1970-12-31 1973-01-12
NZ197872A (en) * 1980-08-05 1985-03-20 Sihi Gmbh & Co Kg Self priming multi-stage centrifugal pump for liquids near boiling point
DE4328268C2 (de) * 1993-08-23 2001-08-16 Pierburg Ag Seiten- oder Peripheralkanalpumpe zur Brennstofförderung
CN2187695Y (zh) * 1993-12-28 1995-01-18 贺新聪 转鼓式油气混输泵
DE19522560A1 (de) 1995-06-21 1997-01-02 Sihi Ind Consult Gmbh Vakuumpumpe mit einem Paar innerhalb eines axial durchströmten Schöpfraums umlaufender Verdrängerrotoren
JP2002031074A (ja) * 2000-07-18 2002-01-31 Matsumoto Kikai Kk カスケードポンプ
DE102007013872A1 (de) * 2007-03-20 2008-09-25 Gardner Denver Deutschland Gmbh Vakuumsystem für hohe Zusatzflüssigkeitsmengen
US20090208346A1 (en) * 2008-02-15 2009-08-20 Mcloughlin John E System and method of controlling pump pressure

Also Published As

Publication number Publication date
CN104619989A (zh) 2015-05-13
AU2013310852A1 (en) 2015-03-12
US20150211530A1 (en) 2015-07-30
US9709060B2 (en) 2017-07-18
WO2014033317A1 (fr) 2014-03-06
EP2893194A1 (fr) 2015-07-15
AU2013310852B2 (en) 2017-01-05
CN104619989B (zh) 2017-03-08

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