EP0894196B1 - Pompe tourbillonnaire - Google Patents

Pompe tourbillonnaire Download PDF

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Publication number
EP0894196B1
EP0894196B1 EP97920637A EP97920637A EP0894196B1 EP 0894196 B1 EP0894196 B1 EP 0894196B1 EP 97920637 A EP97920637 A EP 97920637A EP 97920637 A EP97920637 A EP 97920637A EP 0894196 B1 EP0894196 B1 EP 0894196B1
Authority
EP
European Patent Office
Prior art keywords
blades
rotor
peripheral pump
pump according
chambers
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 - Lifetime
Application number
EP97920637A
Other languages
German (de)
English (en)
Other versions
EP0894196A1 (fr
Inventor
Hans-Dieter Wilhelm
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP0894196A1 publication Critical patent/EP0894196A1/fr
Application granted granted Critical
Publication of EP0894196B1 publication Critical patent/EP0894196B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D5/00—Pumps with circumferential or transverse flow
    • 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
    • F04D29/188—Rotors specially for 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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/34—Balancing of radial or axial forces on regenerative rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/35—Reducing friction between regenerative impeller discs and casing walls

Definitions

  • the invention relates to a peripheral pump with a driven, rotating in a pump housing Impeller, in each of which in its end faces Wreath of blades for conveying a liquid from one Inlet channel worked up to an outlet channel and with both sides in the area of the blades in the Pump housing incorporated ring channels with vane chambers opposite each other between the blades Form delivery chambers, the impeller in its radially inner area and in the area of its circumferential Edge of the pump housing to limit a sealing gap faces with a small distance and the blades seen in the direction of rotation from the central area of the Rise the impeller towards the end faces, in the area of two opposing blade chambers the blades connect to overflow the Liquid is generated and that the inlet channel with the one delivery chamber and the outlet channel with the other Delivery chamber is connected.
  • peripheral pumps are often used to pump Fuel in a fuel tank of a motor vehicle used and are therefore known.
  • the funding chambers are of one in the middle of the impeller arranged center bar separated from each other.
  • At a Rotation of the impeller creates the blades in the delivery chambers one transverse to the direction of movement of the blades running circulation flow.
  • This circulation flow runs on both sides of the impeller from on each Inlet ports arranged in the pump housing to the Outlet channels.
  • a sill is arranged which is the circulation flow interrupts.
  • This peripheral pump is maintenance free and has a high efficiency.
  • Shape of the blades reduces shock losses from one Impact of the liquid on the front or at Flow around the blades are caused. This Impact losses always occur when the to be funded Liquid from the ring channels in the area of the Impeller. Furthermore, through this design the scoops the liquid as it enters the ring channels accelerated to a speed that initially seen in the direction of rotation of the impeller is higher than the speed of the blades. Then takes the speed in the direction of rotation of the impeller, while the speed is transverse to the direction of rotation elevated. The circulation currents therefore have an in Circumferential direction of the impeller pointing lance shape, what to leads to a high delivery pressure of the peripheral pump.
  • a disadvantage of the known peripheral pump is that it has two inlet channels and two outlet channels. This design leads to an unnecessarily high assembly effort of the Peripheral. Furthermore, the peripheral pump has passed through their two separated from each other by the central bridge Production chambers have a large construction volume.
  • peripheral pumps with axial flow a single outlet channel and a single inlet channel become known in which the liquid from one Conveying chamber flows over to the other conveying chamber.
  • the Liquid flows radially through the impeller outer area of the blade chambers.
  • This design leads to an unfavorable circulation flow profile, by guiding elements on the back of the Buckets must be steered. These guiding elements are intended also reduce the impact losses on the inlet side. However, these guide elements cause friction losses and occupy a large proportion of the volume of the Feed chambers.
  • the peripheral pump in A reduced compared to other peripheral pumps Delivery volume and a lower delivery pressure.
  • the invention is based on the problem of a peripheral pump of the type mentioned in such a way that the smallest possible construction volume with a high one Delivery volume and at the same time a high delivery pressure having.
  • This design makes the peripheral pump axial via a first delivery chamber and a second delivery chamber flows through and has only a single inlet channel and a single outlet channel.
  • the peripheral pump can therefore be carried out with particularly little effort for example in a fuel tank.
  • the impeller has none of the delivery chambers from each other separating center bar, so that the peripheral pump particularly builds narrow.
  • the peripheral pump according to the invention has a particularly high delivery volume because of the vane chambers are not restricted with guide elements.
  • the liquid can almost without disturbing the circulation flow from the first Overflow the delivery chamber into the second delivery chamber, which leads to a particularly high delivery pressure and particularly high efficiency of the peripheral pump according to the invention leads.
  • the slight disturbance of the circulation flow is particularly effective with hot liquids advantageous with a high vapor pressure, as this at a disturbance or a break in the circulation flow to form the pressure reducing and Cavitation damage to the impeller causing steam bubbles tend. Furthermore, the liquid to be pumped is thanks the low friction losses hardly warmed up.
  • shock losses when the circulation flow occurs can be kept to a minimum in the blade chambers restrict if the blades according to another advantageous Development of the invention in the direction of rotation the wheel seen at an angle of 5 to 45 ° to the Surface normals of the end faces of the impeller from that middle area of the impeller to the respective front side climb up.
  • the peripheral pump according to the invention already reaches at a low speed of the impeller high discharge pressure if the buckets according to another advantageous development of the invention in the running direction the impeller seen at an angle of 10 to 20 ° to Surface normals of the end faces of the impeller from that middle area of the impeller to the respective Rise towards the front.
  • a low overall depth and simple manufacturability results themselves when the connection is due to an overlap of the circular delivery chambers is formed.
  • the liquid flows particularly easily from the first Delivery chamber into the second delivery chamber when through Overlap of the production chambers created connection according to another advantageous development of the invention in the radial direction of the impeller to the outside and / or expanded inside. This also leads to a Increase in the maximum achievable delivery pressure.
  • the ratio of the speed of the liquid is normal to the direction of rotation and the average speed in Circulation direction to one another is crucial for stability the circulation flow and thus for the one with the Peripheral pump maximum delivery pressure that can be generated.
  • This Ratio is one at a given working point Peripheral pump in which the circular delivery chambers approximately half on the blade chambers and the ring channels are divided, only depending on the ratio of the average diameter of the ring of the blades to the radius of the production chambers. With such a peripheral pump becomes a high discharge pressure according to another advantageous development of the invention simply because achieved the ratio of the average diameter the rim of the blades to the radius of the delivery chamber greater than 7 and less than 99 is selected.
  • the radius or the chamfer only has to be on the blades Edges exist at which the circulation flow touched the blades. Then the blades form constructively particularly simple if the radius or the Chamfer seen on the edge in the running direction of the impeller the front of the blades in a radially outer area and on the edge of the back in a radially inner Area is arranged.
  • the interference-reducing effect of the radii or the width the chamfer essentially depends on the dimensions of the blades from. For example, large shovels need accordingly large radii or chamfers.
  • the liquid circulates according to another advantageous development the invention is particularly low-interference in the delivery chambers, if the radius or the width of the chamfer is at least 1/70 corresponds to the height of the blades.
  • Axial forces acting on the impeller could damage the impeller when operating the peripheral pump against the pump housing press, which increases wear while at the same time Reduction in the discharge pressure.
  • the axial forces acting on the impeller can be according to another advantageous development of the invention just pick it up when the impeller is on its face several opposing depressions has and each two opposing depressions are interconnected.
  • the wells thus form pressure pockets of an axial plain bearing, the via the sealing gap between the impeller and the pump housing are connected to the delivery chambers.
  • the wells could be in one of the blades seen radially outer region of the impeller his.
  • the impeller has a high peripheral speed, whereby the axial forces already at the start of the Peripheral pump can be included.
  • the peripheral pump is particularly space-saving if the Deepening according to another advantageous development of the invention seen from the blades in radially inner region of the impeller are arranged.
  • the wells have very good volume Emergency running properties in the event of a short-term absence of the liquid to be pumped when the wells according to another advantageous development of the invention are designed trough-shaped.
  • depressions are advantageous according to another Further development of the invention is easy to manufacture if according to another advantageous further development of the Invention in a tangential section through the impeller are pocket-shaped.
  • the impeller is inexpensive to manufacture if it is in accordance another advantageous development of the invention is made of plastic by injection molding. Furthermore, the impeller made of plastic has a particularly low weight, which makes the peripheral pump their maximum delivery rate very quickly after a start reached.
  • Figure 1 shows a longitudinal section of an inventive Peripheral pump with a pump housing 1, in which an impeller 2 is rotatably arranged.
  • the Impeller 2 is non-rotatably at its center on a drive shaft 7 attached.
  • the pump housing 1 has in the area of the blades 6, 6a, 6b on both sides, respectively a ring channel 8, 9.
  • the ring channels 8, 9 form together with blade chambers 10, 10a, 10b shown in FIG between the blades 6, 6a, 6b delivery chambers 11, 12, which each have a circular cross section. at a rotation of the impeller 2 arise in the delivery chambers 11, 12 circulation flows of a to be promoted Liquid.
  • the circulation flows are for clarification marked with arrows in FIGS. 1 and 2.
  • the delivery chambers 11, 12 are here in each case half on the blade chambers 10, 10a, 10b and the ring channels 8, 9 divided and have one another a connection 13 by an intersection of their circular cross sections is generated. Through this connection 13 can fluid from almost swirling one delivery chamber 11 into the other delivery chamber 12 overflow.
  • the impeller 2 In its radially outer area and on its end faces 3, 4, the impeller 2 is the pump housing 1 with a short distance opposite. This creates an um the impeller 2 circumferential sealing gap 14 which the delivery chambers 11, 12 seals.
  • the area of the impeller 2 is in the end faces 3, 4 a plurality of mutually opposite depressions 15, 16 incorporated. Two opposing depressions each 15, 16 are connected to one another by a channel 17. Through the sealing gap 14 between the impeller 2 and the pump housing 1 gets a small amount of leakage the liquid to be pumped to the depressions 15, 16. As a result, the recesses 15, 16 form axial sliding bearings for the impeller 2. In operation of the peripheral pump The impeller 2 thus floats smoothly on a liquid film.
  • Figure 2 shows a tangential section through the Peripheral pump according to the invention from Figure 1 along the Line II - II.
  • the pump housing 1 has an inlet duct 18 and an outlet duct 19, which are arranged on both sides of the impeller 2 Sills 20 are separated.
  • the sill 20 interrupts those generated in the delivery chambers 11, 12 Circulation flows of the liquid to be pumped.
  • the Inlet channel 18 is connected to the first delivery chamber 11 connected immediately behind the sill 20. In the direction of rotation seen immediately in front of the sill 20 the second delivery chamber 12 opens into the outlet channel 19.
  • the blades 6, 6a, 6b are symmetrical in the impeller 2 arranged and rise from an axially central area of the impeller 2 to the end faces 3, 4 of the impeller 2 by an angle ⁇ .
  • the drawn angle ⁇ is here about 15 °.
  • FIG. 3 shows a tangential section of the depressions 15, 16 of the impeller 2 along the line III - III from Figure 1.
  • the depressions 15, 16 are pocket-shaped incorporated into the impeller 2 and over at its center the channel 17 interconnected.

Claims (17)

  1. Pompe centrifuge comprenant un rotor (2) entraíné qui tourne dans un corps de pompe (1) et dans lequel est ménagée, dans chacune de ses faces frontales (3, 4), une couronne (5) respective d'aubes (6) servant à faire circuler un fluide d'un conduit d'entrée (18) jusqu'à un conduit de sortie (19), et, ménagés des deux côtés dans le corps de pompe (1) dans la zone des aubes (6), des conduits annulaires (8, 9) qui forment, avec les chambres d'aube (10, 10a) situées entre les aubes (6), des chambres de déplacement (11, 12) faisant face l'une à l'autre, tandis que, dans sa zone radialement intérieure et dans la zone d'un bord périphérique, le rotor (2) fait face au corps de pompe (1) à une faible distance de façon à délimiter un intervalle d'étanchéité (14), les aubes (6) s'élevant, vu suivant le sens de rotation, de la zone centrale du rotor vers les faces frontales (3, 4), et que, dans la zone de deux chambres d'aube (10, 10a), faisant face l'une à l'autre, des aubes (6), une communication (13) est réalisée afin de faire passer le liquide, le conduit d'entrée (18) étant relié à une chambre de déplacement (11) et le conduit de sortie (19) à l'autre chambre de déplacement (12), caractérisé en ce que les chambres de déplacement (11, 12) présentent une section transversale circulaire dans la zone des chambres d'aube (10, 10a).
  2. Pompe centrifuge suivant la revendication 1, caractérisée en ce que les aubes (6) s'élèvent chacune, vu suivant le sens de déplacement du rotor (2), d'un angle de 5 à 45° vis-à-vis de la normale à la surface des faces frontales (3, 4) du rotor (2), de la zone centrale du rotor (2) vers la face frontale (3, 4) respective.
  3. Pompe centrifuge suivant la revendication 2, caractérisée en ce que les aubes (6) s'élèvent chacune, vu suivant le sens de déplacement du rotor (2), d'un angle de 10 à 20° vis-à-vis de la normale à la surface des faces frontales (3, 4) du rotor (2), de la zone centrale du rotor (2) vers la face frontale (3, 4) respective.
  4. Pompe centrifuge suivant la revendication 1, caractérisée en ce que les aubes (6) s'élèvent, vu suivant le sens de déplacement du rotor (2), en forme de parabole en allant de la zone centrale du rotor (2) vers les faces frontales (3, 4).
  5. Pompe centrifuge suivant au moins l'une des revendications précédentes, caractérisée en ce que les aubes (6) ont des espacements angulaires différents de l'une à l'autre.
  6. Pompe centrifuge suivant au moins l'une des revendications précédentes, caractérisée en ce que la communication (13) est formée par une intersection des chambres de déplacement (11, 12) de forme circulaire.
  7. Pompe centrifuge suivant au moins l'une des revendications précédentes, caractérisée en ce que la communication (13) produite par une intersection des chambres de déplacement (11, 12) est évasée vers l'extérieur et/ou l'intérieur suivant la direction radiale du rotor (2).
  8. Pompe centrifuge suivant au moins l'une des revendications précédentes, dans laquelle les chambres de déplacement de forme circulaire sont réparties approximativement par moitié sur les chambres d'aube et les conduits annulaires, caractérisée en ce que le rapport du diamètre moyen de la couronne (5) des aubes (6) au rayon des chambres de déplacement (11, 12) est choisi supérieur à 7 et inférieure à 99.
  9. Pompe centrifuge suivant la revendication 8, caractérisée en ce que le rapport du diamètre moyen de la couronne (5) des aubes (6) au rayon des chambres de déplacement (11, 12) est choisi supérieur à 15 et inférieur à 30.
  10. Pompe centrifuge suivant au moins l'une des revendications précédentes, caractérisée en ce que des arêtes des aubes (6) faisant saillie dans les chambres de déplacement (11, 12) comportent un arrondi ou présentent un chanfrein.
  11. Pompe centrifuge suivant la revendication 10, caractérisée en ce que le rayon d'arrondi ou le chanfrein est situé, vu suivant le sens de déplacement du rotor (2), dans une zone radialement extérieure sur l'arête de la face avant des aubes (6) et dans une zone radialement intérieure sur l'arête de la face arrière.
  12. Pompe centrifuge suivant la revendication 10 ou 11, caractérisée en ce que le rayon d'arrondi ou la largeur du chanfrein correspond à au moins 1/70 de la hauteur des aubes (6).
  13. Pompe centrifuge suivant au moins l'une des revendications précédentes, caractérisée en ce que le rotor (2) comporte sur ses faces frontales (3, 4) plusieurs parties en retrait (15, 16) situées à l'opposé l'une de l'autre et les parties en retrait de chaque paire de parties en retrait (15, 16) situées à l'opposé l'une de l'autre sont reliées l'une à l'autre.
  14. Pompe centrifuge suivant la revendication 13, caractérisée en ce que les parties en retrait (15, 16) sont situées, vu à partir des aubes (6), dans la zone radialement intérieure du rotor (2).
  15. Pompe centrifuge suivant la revendication 13 ou 14, caractérisée en ce que les parties en retrait (15, 16) ont une configuration en forme de cuvette.
  16. Pompe centrifuge suivant la revendication 13 ou 14, caractérisée en ce que les parties en retrait (15, 16) ont une configuration en forme de poche suivant une coupe tangentielle par le rotor (2).
  17. Pompe périphérique suivant au moins l'une des revendications précédentes, caractérisée en ce que le rotor (2) est réalisé en matière plastique par le procédé de moulage par injection.
EP97920637A 1996-04-18 1997-04-10 Pompe tourbillonnaire Expired - Lifetime EP0894196B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19615322A DE19615322A1 (de) 1996-04-18 1996-04-18 Peripheralpumpe
DE19615322 1996-04-18
PCT/EP1997/001772 WO1997040274A1 (fr) 1996-04-18 1997-04-10 Pompe tourbillonnaire

Publications (2)

Publication Number Publication Date
EP0894196A1 EP0894196A1 (fr) 1999-02-03
EP0894196B1 true EP0894196B1 (fr) 2002-07-17

Family

ID=7791641

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97920637A Expired - Lifetime EP0894196B1 (fr) 1996-04-18 1997-04-10 Pompe tourbillonnaire

Country Status (10)

Country Link
US (1) US6231300B1 (fr)
EP (1) EP0894196B1 (fr)
KR (1) KR20000005502A (fr)
CN (1) CN1093921C (fr)
AR (1) AR011761A1 (fr)
AU (1) AU719375B2 (fr)
BR (1) BR9708779A (fr)
DE (2) DE19615322A1 (fr)
ES (1) ES2180980T3 (fr)
WO (1) WO1997040274A1 (fr)

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DE19943261A1 (de) 1999-09-10 2001-03-15 Mannesmann Vdo Ag Förderpumpe
DE10013908A1 (de) 2000-03-21 2001-09-27 Mannesmann Vdo Ag Förderpumpe
DE10030604A1 (de) * 2000-06-21 2002-01-03 Mannesmann Vdo Ag Seitenkanalpumpe
DE10161662B4 (de) * 2001-12-14 2005-11-10 Siemens Ag Seitenkanalpumpe
US7037066B2 (en) 2002-06-18 2006-05-02 Ti Group Automotive Systems, L.L.C. Turbine fuel pump impeller
US6932562B2 (en) * 2002-06-18 2005-08-23 Ti Group Automotive Systems, L.L.C. Single stage, dual channel turbine fuel pump
JP4310426B2 (ja) * 2002-07-25 2009-08-12 米原技研有限会社 加圧遠心ポンプの気体の混入構造
DE10246694B4 (de) * 2002-10-07 2016-02-11 Continental Automotive Gmbh Seitenkanalpumpe
KR100568547B1 (ko) * 2003-07-28 2006-04-07 현담산업 주식회사 개선된 형상의 임펠러를 구비하는 자동차용 터빈형전동기식연료펌프
DE102006053933A1 (de) * 2006-11-15 2008-05-21 Siemens Ag Seitenkanalpumpe
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
JP6535500B2 (ja) * 2015-04-14 2019-06-26 株式会社川本製作所 渦流ポンプ
CN105782109B (zh) * 2016-03-06 2020-05-12 亿德机电科技（福建）有限公司 一种燃烧机专用泵旋涡叶轮

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Also Published As

Publication number Publication date
DE19615322A1 (de) 1997-10-23
DE59707730D1 (en) 2002-08-22
KR20000005502A (ko) 2000-01-25
US6231300B1 (en) 2001-05-15
WO1997040274A1 (fr) 1997-10-30
AR011761A1 (es) 2000-09-13
BR9708779A (pt) 1999-08-03
CN1216597A (zh) 1999-05-12
CN1093921C (zh) 2002-11-06
AU719375B2 (en) 2000-05-11
ES2180980T3 (es) 2003-02-16
AU2694997A (en) 1997-11-12
EP0894196A1 (fr) 1999-02-03

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