EP0048095B1 - Pumpe für schwere Gase - Google Patents

Pumpe für schwere Gase Download PDF

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Publication number
EP0048095B1
EP0048095B1 EP19810303882 EP81303882A EP0048095B1 EP 0048095 B1 EP0048095 B1 EP 0048095B1 EP 19810303882 EP19810303882 EP 19810303882 EP 81303882 A EP81303882 A EP 81303882A EP 0048095 B1 EP0048095 B1 EP 0048095B1
Authority
EP
European Patent Office
Prior art keywords
pump
gas
inlet
outlet
manifold
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.)
Expired
Application number
EP19810303882
Other languages
English (en)
French (fr)
Other versions
EP0048095A1 (de
Inventor
Idwal Miles Thomas
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.)
Sellafield Ltd
Original Assignee
British Nuclear Fuels 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 British Nuclear Fuels PLC filed Critical British Nuclear Fuels PLC
Publication of EP0048095A1 publication Critical patent/EP0048095A1/de
Application granted granted Critical
Publication of EP0048095B1 publication Critical patent/EP0048095B1/de
Expired 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/086—Carter

Definitions

  • This invention relates to pumps for pumping heavy gases.
  • FR-A-636 382 One type of known pump is shown in FR-A-636 382, in which there is shown a bell shaped inlet passage which is disposed with its widest cross section inside a pump.
  • An object of the present invention is to tend to provide a pump which is able to pump heavy gases more efficiently than hitherto.
  • a pump for pumping heavy gases comprises two co-operating rotors, the rotors each have an arm for sweeping gas from the pump inlet to its outlet, the arms causing a compression of the gas during part of their movement, an inlet/outlet manifold being provided on the pump, which inlet/outlet manifold includes passages for inlet of gas and for outlet of gas the inlet passage being bell shaped and being disposed with its widest cross section inside the pump and is characterised in that the outlet passage varies from a part annular cross section within the pump to a circular cross section where the manifold is connected to an output conduit, the passages thereby being constructed to provide a minimal velocity change of gas travelling through them, whereby pressure losses of gas within them is minimal, said minimal velocity change being achieved by minimising mechanical obstruction from within the passages, the minimal pressure loss reducing pulsations within the gas owing to said compression and hence allowing efficient pumping of the gas.
  • FIG. 1 An inlet for the pump is generally indicated by 1 and an outlet by 2.
  • the inlet 1 and outlet 2 form part of a manifold 3, which manifold 3 is bolted to a housing of the pump 4 by means of studs 5 and 6, which themselves are secured by nuts 7.
  • the description is to be read as though a manifold 30 (to be described below) were substituted for manifold 3, which is only illustrated to show manifold positioning.
  • a motor for the pump is generally indicated by 8 and this motor drives the pump via a shaft 9.
  • the shaft 9 carries the pinion 10, which pinion engages a second pinion 11.
  • the pinion 11 is carried upon a shaft 12.
  • the shafts 9 and 12 carry two rotors (13, 14) in the form of gear pump members, respectively, within the manifold 3.
  • the configuration of the members 13 and 14 can be seen more clearly in Figure 2 to which reference is now also directed, members 13, 14 having an arm 95, 96 respectively.
  • the pump gears 10 and 11 and the motor 8 are sealed from gas entering and leaving the pump by means of an endplate 17 which carries seals 18 for the shafts 9 and 12.
  • the shafts 9 and 12 are mounted in tapered roller bearings 19 and 20, respectively.
  • the motor 8 has a housing 21 which is secured to a plate 22 bolted to the casing 4 by bolts 23. Bearings 24 and 25 are provided on the shafts 9 and 12 respectively, on that part of the casing 4 to which the plate 22 is secured. Therefore, it can be seen that it is not possible for gas to escape from the manifold 3 and the region where the pump members 13 and 14 are located into the remainder of the pump.
  • FIGs 3, 4, 5 and 6 in which a manifold 30 in accordance with the invention is fitted to the pump in place of the manifold 3 (of Figures 1 and 2).
  • the manifold 30 is secured to the remainder of the pump by means of boss portions 31 containing passages 32 for bolts or studs.
  • the inlet passage into the manifold is in the form of a segment of a circle for the area of cross section of fluid flow. Two recesses 34 and 35 are provided on the segment.
  • Figure 4 there is shown a modified manifold without the recesses.
  • the inlet passage 33 is bell-shaped as may be seen from Figure 5, the innermost part of the inlet being the part of widest diameter.
  • the bell shape provides a buffer volume of gas for damping pulsations.
  • an attachment flange 36 is provided for attachment of the inlet manifold to for example pipes (not shown).
  • the recesses 34 and 35 which can be seen on the end sauN of the inlet manifold in Figure 3, correspond..,to a slight convolution of the flow passrge as it goes through the manifold.
  • the manifold 30 has an outlet passage which can be rnost clearly seen reference to Figure 6.
  • the outhet passage indicated by 40 is widest at its 'outermost end and narrowest at its innermost end in Figure 6.
  • the cross-section of the flow is circular at its outermost end and in the form of a part annular (the part being ninety degrees) passage at its innermost end. The passage widens to one hundred and ten degrees as it approaches the circular part.
  • FIG. 7 shows a diagrammatic model of operational parameters of the pump.
  • the pump is indicated by 60.
  • Input pressure to the pump is indicated by P1 and outlet pressure by P2.
  • P3 which is that pressure which occurs after an inlet port impedance indicated by 11.
  • P4 which pressure is a pressure above the outlet pressure P2 of an amount equal to the pressure lost through an outlet port impedance indicated by 12.
  • FIG. 8 in which pump pressure is plotted as ordinate and location along a pump as abscissa.
  • the graph of Figure 8 shows, as a full curve, the pressure of air and, as a dotted curve, the pressures of uranium hexafluoride.
  • P1 and P2 are the same for the pump in both cases.
  • the graph it can be seen that there is a greater drop between P1 and P3 in the case of uranium hexafluoride than air, and similarly in the case of pressure P4 and P2. Therefore, the pump has to do more work with uranium hexafluoride than with air. Consequently, a problem may arise with overheating of the pump.
  • Figure 9 shows a pump in a situation where P1 equals P2, that is to say when there is no throughput of fluid through the pump. This is a point that occurs in operation, at that point where the pump members referred to above in connection with Figure 1 as 13 and 14 are at their compression point in their cycle which will be explained in more detail below.
  • the pump member 13 rotates in a clockwise manner and the pump member 14 in an anti-clockwise manner. Fluid is drawn in through the inlet and exhausted through the exhaust.
  • the members 13 and 14 have arms 95 and 96, which come together during part of the stroke of the pump. This position is shown in Figure 2 and corresponds td a compression position of the pump. Therefore, fluid is drawn in and pushed around by the member 13, slightly compressed in the interaction between the members 13 and 14 and then pushed out of the exhaust manifold by the member 14.
  • the inlet port and outlet port have impedances 11 and 12 which become of significance when uranium hexafluoride is being pumped when compared with the pumping of air. Therefore, it is important that these impedances be reduced, so that too much power is not used by the pump tending to cause overheating thereof. Therefore, the inlet of the manifold 30 is constructed so as to have reduced mechanical obstruction therein, i.e. substantially no mechanical obstruction to ingress of the heavy gas so that a minimal gas velocity is achieved. Also, the inlet widens out in the bell shape described above with reference to Figure 5. However, such- an enlarged inlet port may give rise to rotor slippage.
  • uranium hexafluoride would be an improved fluid for the purpose of pumping the input compared with air. This is because the volumetric slippage between the rotors for a given pump outlet and inlet pressure is less for a dense gas than a light gas thereby enhancing the pump throughput, the relative density of uranium hexafluoride to air being 12:2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (1)

1. Pumpe für schwere Gase, mit zwei zusammenwirkenden Rotoren (13, 14), welche jeweils einen Arm (95, 96) für die strechende Förderung von Gas vom Einlaß (1) der Pumpe zu ihrem Auslaß (2) aufweisen, wobei die Arme über ein Teil ihrer Bewegung eine Kompression des Gase bewirken, unt mit einem an der Pumpe vorgesehenen Einlaß/Auslaß-Verteilerstück (30), welches Durchlässe (33, 40) für den Einlaß von Gas und den Auslaß von Gas aufweist, wobei der Einlaß (33) glockenförmig ausgebildet und mit seinem größten Querschnitt innerhalb der Pumpe angeordnet ist, dadurch gekennzeichnet, daß der Auslaß (40) von einem teilringförmigen Querschnitt innerhalb der Pumpe zu einem kreisförmigen Querschnitt an der Stelle variiert, an welcher das Verteilerstück mit einer Auslaßleitung verbunden ist, wodurch die Durchlässe (33, 40) so ausgebildet sind, daß das sie durchströmende Gas eine. minimale Geschwindigkeitsänderung erfährt, wodurch Druckverluste des Gases darin auf ein Mindestmaß verringert sind, wobei die minimale Geschwindigkeitsänderung durch Verringerung von mechanischen Hindernissen in den Durchlässen auf ein Mindestmaß erzielt ist und der minimale Druckverlust aufgrund der Kompression in dem Gas auftretende, pulsierende Druckschwankungen verringert und damit ein wirksames Pumpen des Gases ermöglicht.
EP19810303882 1980-09-05 1981-08-25 Pumpe für schwere Gase Expired EP0048095B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8028827 1980-09-05
GB8028827 1980-09-05

Publications (2)

Publication Number Publication Date
EP0048095A1 EP0048095A1 (de) 1982-03-24
EP0048095B1 true EP0048095B1 (de) 1983-12-14

Family

ID=10515897

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19810303882 Expired EP0048095B1 (de) 1980-09-05 1981-08-25 Pumpe für schwere Gase

Country Status (2)

Country Link
EP (1) EP0048095B1 (de)
DE (1) DE3161646D1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9316539D0 (en) * 1993-08-10 1993-09-29 Drum Int Ltd Rotary compressor
DE29905249U1 (de) * 1999-03-22 1999-12-30 Werner Rietschle GmbH + Co. KG, 79650 Schopfheim Pumpe zur Erzeugung von Druck und Unterdruck
US6729863B2 (en) 1999-03-22 2004-05-04 Werner Rietschle Gmbh & Co. Kg Rotary pump having high and low pressure ports in the housing cover
DE20216504U1 (de) * 2002-10-25 2003-03-06 Werner Rietschle GmbH + Co. KG, 79650 Schopfheim Verdrängermaschine mit gegensinnig laufenden Rotoren
DE102010015151A1 (de) * 2010-04-16 2011-10-20 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Verdichterflansch für Schraubenverdichter

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR636382A (de) * 1928-04-07
US2469936A (en) * 1945-03-14 1949-05-10 Paul C Tabbert Rotary pump
US3513476A (en) * 1967-06-21 1970-05-19 Tokyo Shibaura Electric Co Rotary compressors
US3844696A (en) * 1973-08-21 1974-10-29 Gen Motors Corp Fluid pump noise reduction means

Also Published As

Publication number Publication date
EP0048095A1 (de) 1982-03-24
DE3161646D1 (en) 1984-01-19

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