EP2946116A1 - Pompe à canaux latéraux dont les canaux latéraux présentent une section transversale asymétrique - Google Patents

Pompe à canaux latéraux dont les canaux latéraux présentent une section transversale asymétrique

Info

Publication number
EP2946116A1
EP2946116A1 EP14700029.3A EP14700029A EP2946116A1 EP 2946116 A1 EP2946116 A1 EP 2946116A1 EP 14700029 A EP14700029 A EP 14700029A EP 2946116 A1 EP2946116 A1 EP 2946116A1
Authority
EP
European Patent Office
Prior art keywords
channel
side channel
impeller
inlet
outlet
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.)
Withdrawn
Application number
EP14700029.3A
Other languages
German (de)
English (en)
Inventor
Ina Constantinides
Paul Skljarow
Michael Kuehn
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2946116A1 publication Critical patent/EP2946116A1/fr
Withdrawn legal-status Critical Current

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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/001—Shear force 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
    • F04D5/008—Details of the stator, e.g. channel shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet
    • F05B2250/503—Inlet or outlet of regenerative pumps

Definitions

  • the present invention relates to a side channel pump for conveying fluids. Furthermore, the invention relates to a fuel pump with such a side channel pump.
  • Fluids such as liquids and gases can be pumped and / or pressurized with different types of pumps.
  • Fluids such as liquids and gases can be pumped and / or pressurized with different types of pumps.
  • Automotive vehicles are often used to pump fuel from a tank to an internal combustion engine.
  • the pump should for this purpose have the ability to deliver fuel reliably and in sufficient quantity under different environmental conditions.
  • the fuel should be able to be pumped both during a cold start and during high heating, which can easily lead to gas bubble formation within the fuel.
  • the pump should be durable and have a long life of for example more than 10 years
  • Embodiments of the present invention advantageously allow to increase the longevity of a side channel pump or a fuel pump equipped with such a side channel pump and / or to minimize wear phenomena.
  • a side channel pump which has a housing which encloses a pumping chamber. Within the pumping chamber, an impeller is rotatably received. Furthermore, within the pumping chamber a
  • the housing has a opening into the inlet side channel
  • the impeller has near its outer periphery in a blade region a plurality of radially outwardly extending ones
  • the proposed side channel pump is characterized in that the inlet side channel averaged along the flow path has a smaller cross section than the outlet side channel.
  • the proposed side channel pump may be considered to be based on the findings and ideas discussed below.
  • a fluid to be delivered is sucked through the inlet channel into the pumping chamber.
  • the impeller rotates, driven for example by an electric motor.
  • the blades of the impeller act on the fluid such that parts of the fluid are entrained.
  • Adjacent to the blades of the impeller are at both opposite sides of the impeller side channels.
  • the inlet channel opens into the inlet side channel.
  • Impellers interact with the fluid in such a way that the fluid is partially entrained in the direction of rotation of the impeller and is partially pressed away from the impeller to one of the side channels.
  • the fluid after it has flowed through the inlet channel into the pumping chamber, spirals along a flow path that runs from the inlet channel along the
  • Impeller and / or by the ejection of the fluid through the outlet channel a force is exerted on the impeller, which tries to move the impeller toward the inlet side. Due to such a force, the impeller may rub during operation of the pump on an inlet side wall of the housing or, for example, a suction cover, which can lead to wear and to a significant drop in the delivery rate of the pump.
  • the cross section of the inlet-side side channel should have a smaller cross-section over the entire flow path than the outlet-side side channel. This concludes however, it is not to be understood that the inlet side channel has a larger cross section than the opposite outlet side in small parts of the flow path, such as directly adjacent to the inlet channel
  • the inlet side channel should preferably over substantially more than half of the flow path, i. For example, over at least 50%, preferably over at least 60%, and more preferably over at least 75%, of the flowpath between the inlet channel and the outlet channel has a smaller cross-section than the outlet side channel.
  • Embodiment of the invention at least 60%, preferably at least 75% or 90% of the positions along the flow path a smaller cross-section than the outlet side side channel at the same position along the flow path.
  • the inlet-side side channel has at least 50% of the positions along the flow path a smaller by between 5% and 30%, preferably between 10% and 25% smaller cross section than the outlet side channel at the same position along the
  • the inlet-side side channel has a smaller depth at at least 50% of the positions along the flow path than the outlet-side side channel at the same position along the Flow path.
  • the asymmetry of the cross sections of the side channels can be achieved mainly by an easy-to-implement
  • the depths of the two side channels can be implemented.
  • the depths of the two side channels may differ, for example, between 5% and 30%, preferably between 10% and 25%.
  • Fig. 1 shows a perspective, partially cut away view
  • Fig. 2 shows an exploded view of a pump part of a
  • Fig. 3 shows a plan view of a housing part of a side channel pump with a side channel formed therein.
  • Fig. 4 shows a highly schematic of a cross-sectional view through a
  • Fig. 5 shows a highly schematic of a cross-sectional view through a
  • FIG. 1 shows the essential structure of a side channel pump 1.
  • an impeller 3 which is sometimes also referred to as an impeller, enclosed within a housing 5 of a housing
  • the impeller 3 has near its outer periphery
  • the impeller 3 can thereby rotate within the pumping chamber 7 and is set during operation of the pump 1, for example, by a coupled to the impeller 3 via a shaft 29 electric motor 13 in rotation.
  • the housing 5 is designed such that parts of the
  • Housing 5 which are also referred to as suction cover 15 and intermediate housing 17, walls 19, 21 form, which border on predominant areas of the end faces of the disk-shaped impeller 3 and spaced from these at best by a narrow gap 23.
  • the impeller 3 is rotated by the electric motor 13 via a shaft 29 connected to these two components.
  • the blades 11 of the impeller 3 interact with the fluid in the pumping chamber 7, e.g. Fuel from a tank via a line (not shown) coming sucked through an extending through the housing 5 inlet 25 into the pumping chamber 7.
  • the fluid is pressurized, conveyed through the pumping chamber, and finally through an outlet 27, e.g. towards an internal combustion engine (not shown).
  • the impeller 3 is enclosed by the housing 5 and in particular by the suction cover 15 and the intermediate housing 17. As can be seen in the exploded view of Figure 2, is within the of the suction cover 15 and the
  • pumping chamber 7 is thereby formed by an inlet-side side channel 31 formed in the suction cover 15, one in the intermediate housing 17
  • outlet side channel 33 and a free volume between the blades 11 of the impeller 3 is formed.
  • walls 19, 21 of the suction lid 15 and the intermediate casing 17 almost directly adjoin corresponding end faces of the impeller 3, possibly being separated therefrom by a narrow gap of e.g. ⁇ are spaced.
  • Fluid to be delivered comes from the inlet 25 and reaches the pumping chamber 7 via an inlet channel 35 which opens into the inlet-side side channel 31. From there, the fluid is distributed via the pumping chamber 7, that is, also into regions between the blades 11 of the rotor 3 and into the
  • the inlet-side side channel 31 formed in the suction cover 15 extends from the inlet channel 35 in an annular manner along the flow path 39 in a partial circle of about 300 ° up to a region 41 on which it is located in the opposite intermediate housing 17 the local outlet-side side channel 33 leads into the outlet channel 37. He passes a vent hole 43.
  • FIG. 5 shows a corresponding configuration for a side channel pump according to a
  • the inlet-side side channel 31 and the outlet-side side channel 33 are formed with equal widths B, but have different depths KTi, KT 2 . Therefore, their cross sections are different and they are with respect to a plane transverse to the side channels
  • the channel depths KTi, KT 2 may differ from each other by 10% to 25%.
  • the two channel depths KTi, KT 2 may be in the range of 1 to 2mm, but the channel depth KTi of the inlet-side channel 31 to be smaller by 0.1 to 0.2 mm than the channel depth KT 2 of the outlet-side side channel 33rd
  • the width and / or shape of the side channels 31, 33 can be selected differently so that the cross-section of the inlet-side side channel 31 is somewhat smaller than that of the outlet-side side channel 33.
  • Cross-section of the inlet-side side channel 31 can be achieved that the force Fi, which is exerted due to the building up in the inlet-side side channel 31 pressure on the impeller 3, is approximately equal to a force F 2 , which due to in the exhaust side Side channel 33 constructive pressure on the impeller 3 is exerted in the opposite direction.

Landscapes

  • 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 canaux latéraux permettant une réduction de l'usure. La pompe à canaux latéraux présente un carter qui entoure une chambre de pompe (7). Une roue à aubes (3) est logée dans la chambre de pompe (7) de manière à pouvoir tourner. Un canal latéral (31) côté entrée et un canal latéral (33) côté sortie sont par ailleurs formés dans la chambre de pompe (7). La roue à aubes (3) présente dans une partie aubes à proximité de sa circonférence extérieure une pluralité d'aubes (11) s'étendant radialement vers l'extérieur. Le canal latéral (31) côté entrée et le canal latéral (33) côté sortie passent sur des côtés opposés de la roue à aubes (3) et sont tous deux adjacents à la roue à aubes (3). Les deux canaux latéraux (31, 33) s'étendent tous deux le long d'un trajet d'écoulement allant sous forme partiellement annulaire d'un canal d'entrée vers un canal de sortie. La pompe à canaux latéraux selon l'invention est caractérisée en ce que le canal latéral (31) côté sortie présente en moyenne le long du trajet d'écoulement une section transversale plus petite que celle du canal latéral (33) côté sortie. La roue à aubes (3) peut de ce fait être maintenue en équilibre de forces pendant son fonctionnement. Il est ainsi possible de limiter la friction entre la roue à aubes (3) et les parois adjacentes (19, 21), et donc de réduire les risques d'apparition d'une usure.
EP14700029.3A 2013-01-18 2014-01-02 Pompe à canaux latéraux dont les canaux latéraux présentent une section transversale asymétrique Withdrawn EP2946116A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013200713.2A DE102013200713A1 (de) 2013-01-18 2013-01-18 Seitenkanalpumpe mit asymmetrischen Querschnitten der Seitenkanäle
PCT/EP2014/050017 WO2014111272A1 (fr) 2013-01-18 2014-01-02 Pompe à canaux latéraux dont les canaux latéraux présentent une section transversale asymétrique

Publications (1)

Publication Number Publication Date
EP2946116A1 true EP2946116A1 (fr) 2015-11-25

Family

ID=49918710

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14700029.3A Withdrawn EP2946116A1 (fr) 2013-01-18 2014-01-02 Pompe à canaux latéraux dont les canaux latéraux présentent une section transversale asymétrique

Country Status (5)

Country Link
US (1) US20150354573A1 (fr)
EP (1) EP2946116A1 (fr)
CN (1) CN104937276A (fr)
DE (1) DE102013200713A1 (fr)
WO (1) WO2014111272A1 (fr)

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1703566C3 (de) * 1968-06-11 1974-06-12 Georg 6901 Dilsberg Fabig Selbstansaugende Seitenkanalpumpe
JPS6079193A (ja) 1983-10-05 1985-05-04 Nippon Denso Co Ltd 車両用燃料ポンプ
JPS6425494U (fr) * 1987-08-05 1989-02-13
US5372475A (en) * 1990-08-10 1994-12-13 Nippondenso Co., Ltd. Fuel pump
JP2757646B2 (ja) 1992-01-22 1998-05-25 株式会社デンソー 燃料ポンプ
DE4343078B4 (de) 1993-12-16 2007-09-13 Robert Bosch Gmbh Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine
DE10348008A1 (de) * 2003-10-15 2005-05-19 Siemens Ag Kraftstoffpumpe
JP2006161600A (ja) * 2004-12-03 2006-06-22 Mitsubishi Electric Corp 円周流ポンプ
JP2008101469A (ja) * 2006-10-17 2008-05-01 Denso Corp 燃料ポンプ
WO2008053818A1 (fr) * 2006-10-28 2008-05-08 Imed Japan Co., Ltd. Pompe à écoulement en hélice pour du sang
DE102010004379A1 (de) * 2009-12-16 2011-06-22 Continental Automotive GmbH, 30165 Kraftstoffpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014111272A1 *

Also Published As

Publication number Publication date
DE102013200713A1 (de) 2014-07-24
CN104937276A (zh) 2015-09-23
WO2014111272A1 (fr) 2014-07-24
US20150354573A1 (en) 2015-12-10

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