WO2004005724A1 - Pompe a fluide a prise automatique et son stator - Google Patents

Pompe a fluide a prise automatique et son stator Download PDF

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Publication number
WO2004005724A1
WO2004005724A1 PCT/GB2003/002902 GB0302902W WO2004005724A1 WO 2004005724 A1 WO2004005724 A1 WO 2004005724A1 GB 0302902 W GB0302902 W GB 0302902W WO 2004005724 A1 WO2004005724 A1 WO 2004005724A1
Authority
WO
WIPO (PCT)
Prior art keywords
pumping channel
channel portions
rotor blades
pumping
pump
Prior art date
Application number
PCT/GB2003/002902
Other languages
English (en)
Inventor
Ian David Stones
Original Assignee
The Boc Group Plc
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 The Boc Group Plc filed Critical The Boc Group Plc
Priority to AU2003281289A priority Critical patent/AU2003281289A1/en
Publication of WO2004005724A1 publication Critical patent/WO2004005724A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/127—Multi-stage pumps with radially spaced stages, e.g. for contrarotating 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to a regenerative fluid pump.
  • a regenerative fluid pump known hereto is shown schematically in Figure 6.
  • the prior art pump 100 is a radial regenerative fluid pump which compresses fluid on a fluid flow path extending between an inlet 102 and an outlet 104 of the pump.
  • the pump comprises a plurality of concentric circumferential channels 105 (represented by concentric circles in Figure 6).
  • the channels comprise respective pumping channel portions 106 along which fluid compression takes place and which together form the fluid flow path.
  • the channels further comprise respective stripper channel portions 108 (shown in broken lines) which allow the passage of the pump's rotor blades from the outlets of respective pumping channel portions 106 to the inlets thereof.
  • fluid enters the pump inlet 102 and is compressed by the rotor blades in the radially outermost pumping channel portion 106, pressure being lowest at the inlet and highest at the outlet thereof.
  • fluid is diverted by a diversion channel 10 (shown by arrows in Figure 6) to the inlet of a radially inner pumping channel portion.
  • rotor blades having passed along the outermost pumping channel move into the stripper channel portion 108 and back to the inlet of the outermost pumping channel.
  • stripper channel portion Although most fluid is diverted radially inwardly by the diversion channel there is some seepage through the stripper channel portion due to the action of the rotor blades and the pressure gradient from the inlet to the outlet of the stripper channel portion.
  • the stripper channel portion is manufactured for small running clearance adjacent the rotor blades to reduce seepage.
  • Fluid continues along the fluid flow path in the same manner as described above until it reaches the pump outlet 104.
  • the maximum arc angle encountered in the prior art to date is 90° of the circumferential channel (i.e. the pumping channel portions extends over an arc angle of 270°). It has also been understood that compression ratio in a pumping channel portion increases as its length increases.
  • the present invention provides a regenerative fluid pump comprising a rotor having rotor blades, and a stator comprising a plurality of concentric channels which comprise pumping channel portions along which said rotor blades move for compressing fluid between respective inlets and respective outlets of the pumping channel portions and stripper channel portions for allowing said rotor blades to pass from said outlets to said inlets of the pumping channel portions, wherein at least one of said pumping channels extends for less than 270° of the circumferential channel.
  • the present invention also provides a regenerative fluid pump comprising a rotor having rotor blades, and a stator comprising a plurality of concentric channels which comprise pumping channel portions along which said rotor blades move for compressing fluid between respective inlets and respective outlets of the pumping channel portions and stripper channel portions for allowing said rotor blades to pass from said outlets to said inlets of the pumping channel portions, wherein the ratio of lengths of the pumping channel portion and stripper channel portion is less than 3:1.
  • the present invention also provides a stator for a regenerative fluid pump comprising a rotor having rotor blades, the stator comprising a plurality of concentric channels which comprise pumping channel portions along which said rotor blades move for compressing fluid between respective inlets and respective outlets of the pumping channel portions and stripper channel portions for allowing said rotor blades to pass from said outlets to said inlets of the pumping channel portions, wherein at least one of said pumping channels extends for less than 270° of the circumferential channel.
  • the present invention also provides a stator for a regenerative fluid pump comprising a rotor having rotor blades, the stator comprising a plurality of concentric channels which comprise pumping channel portions along which said rotor blades move for compressing fluid between respective inlets and respective outlets of the pumping channel portions and stripper channel portions for allowing said rotor blades to pass from said outlets to said inlets of the pumping channel portions, wherein the ratio of lengths of the pumping channel portion and stripper channel portion is less than 3:1.
  • Figure 1 is a graph showing pressure along a fluid flow path of a prior art regenerative fluid pump plotted against distance from the outlet of the pump;
  • FIG. 2 is a similar graph for a regenerative fluid pump embodying the present invention.
  • Figure 3 is a portion of the graph of Figure 1 ;
  • Figure 4 is a schematic representation of a regenerative fluid pump embodying the present invention
  • Figure 5 is a view of a stator for a regenerative fluid pump embodying the present invention
  • Figure 6 is a schematic view of a prior art regenerative fluid pump.
  • Figure 7 is a view of a stator for the prior art regenerative fluid pump shown in Figure 6.
  • Figure 1 From an analysis of the behaviour of the prior art regenerative fluid pump shown in Figures 6 and 7, the relationship shown in Figure 1 is revealed, which plots pressure against distance from the pump outlet 104.
  • the pump inlet 102 is also referenced in Figure 1.
  • Six pumping stages are shown in Figure 1 as can be seen from the shape of the graph.
  • fluid entering the pump inlet 102 is compressed by the rotor blades passing along the outermost, or first, pumping channel portion 106a.
  • the compression ratio in the pumping channel portion 106a increases exponentially as fluid approaches the outlet of the pumping channel, with the pressure at the inlet of the pumping channel portion being about 1 mbar and the pressure at the outlet being about 3 mbar. This can be seen in Figure 1 by the portion of the graph referenced 106a.
  • the compression ratio suddenly drops.
  • Figure 2 is a graph showing the relationship between pressure and distance from the pump outlet of a regenerative fluid pump according to one embodiment of the present invention a stator of which is shown in Figure 5 and will be described in detail below.
  • the length (or arc angle) of the pumping channel portions is reduced compared with the prior art pump shown in Figure 7. Even though the overall length of the pumping channel portions has been reduced from about 1750 mm to about 1000 mm, there is no change in total compression ratio between the pumps. The reason for this, is that, for each pumping channel portion, the curve has been condensed but the change in pressure from outlet to inlet remains similar. This can be explained with reference to the curve for a single prior art pumping channel portion as shown in Figure 3.
  • FIG 3 only the portion of the curve of Figure 1 for the second pumping channel portion 106b is shown.
  • the inlet pressure is shown to be 3 mbar.
  • the pressure at the outlet of the pumping channel portion is about 10 mbar, however, half way between the outlet and inlet the pressure is only 3.18 mbar. It will be seen therefore that relatively little compression occurs over the first half of the pumping channel portion.
  • Figure 4 shows a schematic view of a regenerative fluid pump 10 with reduced pumping channel portions.
  • the pump shown schematically in Figure 4 comprises four pumping stages although, more or less stages may be provided, as required.
  • Pump 10 comprises a rotor (not shown) having rotor blades for compressing fluid on a fluid flow path between an inlet 12 and an outlet 14 of the pump.
  • the pump 10 comprises multiple circumferential concentric channels 16 which comprise pumping channel portions 18 along which rotor blades move for compressing said fluid between inlets and outlets of the pumping channel portions 18 and stripper channel portions 20 which allow movement of said rotor blades from said outlets to said inlets of the pumping channel portions.
  • the respective pumping channel portions 18 have been reduced in length as compared with the pumping channel portions 106 in Figure 6.
  • a reduction in the pumping channel portions results in a proportional increase in the length of the respective stripper channel portions 20 and in the schematic representation shown, the lengths of respective pumping channel portions 18 and respective stripper channel portions 20 are approximately equal (i.e. pumping channel portions 18 and stripper channel portions 20 both extend over an arc angle of about 180° of respective circumferential channels 16).
  • the ratio of respective lengths for the pumping channel portions and the stripper channel portions in at least one of the circumferential channels 16 is about 1 :1.
  • stator 30 is specifically adapted for a pump comprising six pumping stages. Operation of stator 30 in combination with a rotor (not shown) will now be described with reference to Figure 5 and the graph shown in Figure 2. Fluid enters the pump at inlet 12 of the stator where it is swept into the first pumping channel portion 18a by rotor blades moving along the portion 18a. The fluid pressure profile along portion 18a is represented by the portion of the graph referenced 18a in Figure 2.
  • the pressure at the inlet 12 is about 1 mbar and the pressure at the outlet of the first pumping channel is about 3 mbar which is similar to the first pumping channel portion 106a in the prior art pump even though portion 18a is only about half the length of portion 106a.
  • fluid is diverted to the inlet of the second pumping channel portion 18b, by diversion channel 22a.
  • the rotor blades having passed along the first pumping channel portion move into the first stripper channel portion 20a which allows them to return to the inlet of the first pumping channel portion.
  • the first pumping channel portion and the first stripper channel portion together constitute a circumferential channel 16. Fluid continues through the remaining five circumferential channels in a similar manner to that described for the first channel and for brevity will not be described further.
  • the change in compression ratio along respective pumping channel portions 18 is less significant at the radially inner pumping channel portions. This is because of their shorter length as compared with the radially outer pumping channel portions. With this in mind, it may not be desirable to reduce the length of the radially inner pumping channel portions 18, since to do so may decrease the compression ratio of that stage of the pump. In this regard, it will be seen from Figure 5 that the radially innermost pumping channel portion 18f extends over an arc angle of about 270° of the respective circumferential channel 16.
  • the speed of the fluid in the pumping channel portions is relatively slow because of the positive pressure gradient from the inlet to the outlet thereof.
  • This positive pressure gradient acts as a resistance to movement of the rotor blades.
  • fluid density is relatively high.
  • there is a negative pressure gradient in the stripper channel portions which applies relatively little resistance to movement of the rotor blades. Since, there is relatively little seepage of fluid along the stripper channel portions fluid density is also relatively low.
  • the reduced pumping channel portions 18 shown in Figures 4 and 5 provides greater efficiency than the prior art pump shown in Figures 6 and 7.
  • the arc angles of the pumping channel portions in Figures 4 and 5 are reduced to about 180° of the circumferential channel 16.
  • the present invention is not restricted to arc angles of about 180° and may be about 250° provided it is less than 270°.
  • the ratio of the respective lengths of pumping channel portions to stripper channel portions is less than 3:1.
  • a reduction in the length of the pumping channel portions in at least one (and not all) of the circumferential channels provide some efficiency benefits.
  • the majority of the compression from the first channel is achieved in the last 20% of the pumping channel.
  • the length of this channel could, therefore, be reduced to an arc of approximately 60° and still retain some of the benefit of the invention.
  • a suitable practical minimum value for the proportion of the arc that is configured to act as a pumping channel is 90° and preferably no less than 120°.
  • the particular configuration for any particular stator being determined by a number of factors such as rotor velocity, blade/channel design, gas flow rate, pressure and gas type. Consequently, the optimum configuration of the stator is determined on a case by cases bases.
  • the present invention has been described with reference to a radial type regenerative fluid pump, but it should be further understood that it applies also to axial type regenerative fluid pumps where the circumferential channels have similar respective radii and are provided internally of a cylindrical stator body.

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

Abstract

L'invention concerne une pompe à fluide à prise automatique (10) comprenant un rotor (non représenté) ayant des ailettes destinées à la compression d'un fluide sur un chemin d'écoulement de fluide entre une entrée (12) et une sortie (14) de la pompe. La pompe (10) comprend de multiples canaux circonférentiels (16) comportant respectivement une partie canal de pompage (18) le long de laquelle les ailettes se déplacent pour la compression du fluide entre une entrée et une sortie du canal de pompage (18); et une partie canal stripper (20) qui permet le mouvement des ailettes de rotor entre la sortie et l'entrée de la partie canal de pompage. Les parties canal de pompage (18) respectives d'au moins un canal circonférentiel s'étendent sur un angle d'arc inférieur à 270°.
PCT/GB2003/002902 2002-07-05 2003-07-04 Pompe a fluide a prise automatique et son stator WO2004005724A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003281289A AU2003281289A1 (en) 2002-07-05 2003-07-04 Regenerative fluid pump and stator for the same

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0215708.9 2002-07-05
GBGB0215708.9A GB0215708D0 (en) 2002-07-05 2002-07-05 A regenerative fluid pump and stator for the same

Publications (1)

Publication Number Publication Date
WO2004005724A1 true WO2004005724A1 (fr) 2004-01-15

Family

ID=9939989

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2003/002902 WO2004005724A1 (fr) 2002-07-05 2003-07-04 Pompe a fluide a prise automatique et son stator

Country Status (3)

Country Link
AU (1) AU2003281289A1 (fr)
GB (1) GB0215708D0 (fr)
WO (1) WO2004005724A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2737215A1 (fr) * 2011-07-28 2014-06-04 Pierburg GmbH Soufflante à canal latéral dotée de plusieurs canaux d'alimentation répartis sur la circonférence
US9376518B2 (en) 2013-08-28 2016-06-28 Exxonmobil Chemical Patents Inc. Racemo selective metallation process

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR404632A (fr) * 1908-10-24 1909-12-07 Marcel Armengaud Compresseur-ventilateur centrifuge à haute pression et à marche relativement lente
DE724875C (de) * 1939-12-19 1942-09-09 Siemens Ag Umlaufpumpe zur Foerderung von Gasen
US3324799A (en) * 1965-08-05 1967-06-13 Trw Inc Radial staging for reentry compressor
FR1523028A (fr) * 1967-05-17 1968-04-02 Rotron Mfg Co Compresseur à étages
FR2122157A5 (fr) * 1971-01-13 1972-08-25 Bbc Brown Boveri & Cie
US3768920A (en) * 1971-07-14 1973-10-30 Eberspaecher J Multi-flow air blower for fuel operated motor vehicle heaters
DE19818667A1 (de) * 1998-04-27 1999-10-28 Becker Kg Gebr Kreiselverdichter
EP1059456A2 (fr) * 1999-06-11 2000-12-13 Gebrüder Becker GmbH & Co. Compresseur à canal latéral
EP1170508A1 (fr) * 2000-06-21 2002-01-09 Varian, Inc. Pompe a effet visqueux

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR404632A (fr) * 1908-10-24 1909-12-07 Marcel Armengaud Compresseur-ventilateur centrifuge à haute pression et à marche relativement lente
DE724875C (de) * 1939-12-19 1942-09-09 Siemens Ag Umlaufpumpe zur Foerderung von Gasen
US3324799A (en) * 1965-08-05 1967-06-13 Trw Inc Radial staging for reentry compressor
FR1523028A (fr) * 1967-05-17 1968-04-02 Rotron Mfg Co Compresseur à étages
FR2122157A5 (fr) * 1971-01-13 1972-08-25 Bbc Brown Boveri & Cie
US3768920A (en) * 1971-07-14 1973-10-30 Eberspaecher J Multi-flow air blower for fuel operated motor vehicle heaters
DE19818667A1 (de) * 1998-04-27 1999-10-28 Becker Kg Gebr Kreiselverdichter
EP1059456A2 (fr) * 1999-06-11 2000-12-13 Gebrüder Becker GmbH & Co. Compresseur à canal latéral
EP1170508A1 (fr) * 2000-06-21 2002-01-09 Varian, Inc. Pompe a effet visqueux

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2737215A1 (fr) * 2011-07-28 2014-06-04 Pierburg GmbH Soufflante à canal latéral dotée de plusieurs canaux d'alimentation répartis sur la circonférence
US9376518B2 (en) 2013-08-28 2016-06-28 Exxonmobil Chemical Patents Inc. Racemo selective metallation process

Also Published As

Publication number Publication date
AU2003281289A1 (en) 2004-01-23
GB0215708D0 (en) 2002-08-14

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