US20150354573A1 - Side-channel pump with asymmetrical cross-sections of the side channels - Google Patents

Side-channel pump with asymmetrical cross-sections of the side channels Download PDF

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Publication number
US20150354573A1
US20150354573A1 US14/761,987 US201414761987A US2015354573A1 US 20150354573 A1 US20150354573 A1 US 20150354573A1 US 201414761987 A US201414761987 A US 201414761987A US 2015354573 A1 US2015354573 A1 US 2015354573A1
Authority
US
United States
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.)
Abandoned
Application number
US14/761,987
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English (en)
Inventor
Michael Kuehn
Paul Skljarow
Ina Constantinides
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
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CONSTANTINIDES, INA, KUEHN, MICHAEL, SKLJAROW, PAUL
Publication of US20150354573A1 publication Critical patent/US20150354573A1/en
Abandoned 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
    • F04D5/002—Regenerative pumps
    • F04D5/008—Details of the stator, e.g. channel shape
    • 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
    • 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 delivering fluids. Furthermore, the invention relates to a fuel pump having a side channel pump of this type.
  • Fluids such as liquids and gases can be delivered and/or pressurized by way of different types of pumps.
  • pumps are frequently used to deliver fuel from a tank to an internal combustion engine.
  • the pump should have the capability of delivering fuel reliably and in a sufficient quantity under various ambient conditions.
  • the fuel should be capable of being delivered both in the case of a cold start and in the case of pronounced heating, in the case of which the formation of gas bubbles within the fuel can occur readily.
  • the pump should have a long service life and should be capable of retaining its delivery properties reliably over a long service life of, for example, more than 10 years.
  • Embodiments of the present invention make it advantageously possible to increase the service life of a side channel pump or a fuel pump which is equipped with a side channel pump of this type and/or to keep wear phenomena low.
  • a side channel pump which has a housing which encloses a pump chamber.
  • An impeller is accommodated within the pump chamber such that it can rotate.
  • an inlet-side side channel and an outlet-side side channel are configured within the pump chamber.
  • the housing has an inlet channel which opens into the inlet-side side channel and an outlet channel which leads away from the outlet-side side channel.
  • the impeller has, in a blade region close to its outer circumference, a multiplicity of radially outwardly extending blades.
  • the inlet-side side channel and the outlet-side side channel run on opposite sides of the impeller and both adjoin the impeller.
  • the two side channels both extend along a flow path from the inlet channel in a partially annular manner to the outlet channel.
  • the side channel pump which is proposed is distinguished by the fact that the inlet-side side channel has, averaged along the flow path, a smaller cross section than the outlet-side side channel.
  • the side channel pump which is proposed can be considered to be based on the findings and concepts which are explained in the following text.
  • a fluid to be delivered is sucked in through the inlet channel into the pump chamber.
  • the impeller rotates in the pump chamber, for example driven by an electric motor.
  • the blades of the impeller act on the fluid in such a way that parts of the fluid are carried along.
  • Side channels are situated in a manner which is adjacent to the blades of the impeller on both opposite sides of the impeller.
  • the inlet channel opens into the inlet-side side channel.
  • both side channels adjoin the impeller and are open toward the blades of the impeller, fluid which is sucked in through the inlet channel can firstly pass to the blades of the rotating impeller and can be carried along by the blades which move parallel to the side channels, and secondly a proportion of the fluid which is sucked in can also pass the blades and can pass between two adjacent blades toward the opposite outlet-side side channel.
  • the blades of the impeller interact with the fluid in such a way that the fluid is partially carried along in the rotational direction of the impeller and is partially pressed away from the impeller toward one of the side channels.
  • the fluid moves in a spiral manner along a flow path which leads from the inlet channel along the side channels toward the outlet channel.
  • a considerable amount of energy is transmitted from the impeller to the fluid, with the result that the fluid can be delivered to the outlet channel and at the same time it can be pressurized and can then leave the pump chamber through the outlet channel.
  • the single-sided force loading of the impeller which has been observed can be avoided or at least reduced during operation of the pump by virtue of the fact that the two side channels are configured with different cross-sectional areas.
  • the cross section of the inlet-side side channel should have, averaged over the entire flow path, a smaller cross section than the outlet-side side channel.
  • the inlet-side side channel can have a larger cross section in small parts of the flow path, such as directly adjacently with respect to the inlet channel, than the opposite outlet-side side channel.
  • the inlet-side side channel should have, over preferably considerably more than half the flow path, that is to say, for example, over at least 50%, preferably over at least 60% and, more preferably, over at least 75% of the flow path between the inlet channel and the outlet channel, a smaller cross section than the outlet-side side channel.
  • the inlet-side side channel has, at 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 at least 50% of the positions along the flow path, a cross section which is smaller by between 5% and 30%, preferably between 10% and 25%, than the outlet-side side channel at the same position along the flow path. It has been observed that even minor asymmetries of this type with regard to the channel cross sections can lead to a considerable reduction of undesired forces on the impeller and therefore to reduced wear.
  • the inlet-side side channel has, at at least 50% of the positions along the flow path, a smaller depth 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 implemented mainly by way of a modification of the depths of the two side channels which is simple to implement.
  • the depths of the two side channels can differ from one another, for example, by between 5% and 30%, preferably between 10% and 25%.
  • FIG. 1 shows a perspective, partially cut-away view of a side channel pump.
  • FIG. 2 shows an exploded view of a pump part of a side channel pump.
  • FIG. 3 shows a plan view of a housing part of a side channel pump with a side channel which is configured therein.
  • FIG. 4 shows a greatly diagrammatic cross-sectional view through a pump chamber and adjoining housing parts of a conventional side channel pump.
  • FIG. 5 shows a greatly diagrammatic cross-sectional view through a pump chamber and adjoining housing parts of a side channel pump according to one embodiment of the present invention.
  • FIG. 1 shows the essential construction of a side channel pump 1 .
  • an impeller 3 which is in part also called an impeller wheel is accommodated within a pump chamber 7 which is enclosed by a housing 5 .
  • the impeller 3 Close to its outer circumference 9 , the impeller 3 has a multiplicity of blades 11 which run at least partially in the radial direction.
  • the impeller 3 can move rotationally within the pump chamber 7 and is set in rotation during operation of the pump 1 , for example by an electric motor 13 which is coupled to the impeller 3 via a shaft 29 .
  • the housing 5 is configured in such a way that parts of the housing 5 , which are also called the intake cover 15 and the intermediate housing 17 , form walls 19 , 21 which adjoin the end faces of the disk-shaped impeller 3 over predominant regions and are spaced apart from said end faces at any rate by a narrow gap 23 .
  • the impeller 3 is set in rotation by the electric motor 13 via a shaft 29 which is connected to said two components.
  • fuel for example, coming from a tank via a line (not shown) is sucked into the pump chamber 7 through an inlet 25 which reaches through the housing 5 .
  • the fluid is pressurized, is conveyed through the pump chamber and is finally ejected through an outlet 27 , for example, toward an internal combustion engine (not shown).
  • the impeller 3 is enclosed by the housing 5 and, in particular, by the intake cover 15 and the intermediate housing 17 .
  • the impeller 3 is accommodated here within the space which is enclosed by the intake cover 15 and the intermediate housing 17 .
  • a free volume remains within said space, through which free volume a fluid can flow and which free volume is called a pump chamber 7 .
  • the pump chamber 7 is formed by an inlet-side side channel 31 which is configured in the intake cover 15 , an outlet-side side channel 33 which is configured in the intermediate housing 17 , and a free volume between the blades 11 of the impeller 3 .
  • walls 19 , 21 of the intake cover 15 and the intermediate housing 17 adjoin corresponding end faces of the impeller 3 almost directly, said walls 19 , 21 being spaced apart from said end faces at any rate by a narrow gap of, for example, 100 ⁇ m.
  • Fluid to be delivered comes from the inlet 25 and reaches the pump chamber 7 via an inlet channel 35 which opens into the inlet-side side channel 31 . From there, the fluid is distributed over the pump chamber 7 , that is to say also into regions between the blades 11 of the impeller 3 and into the opposite outlet-side side channel 33 . Here, driven by the rotating impeller 3 , it moves along a flow path 39 (see FIG. 3 ) which reaches from the inlet channel 35 as far as toward an outlet channel 37 .
  • the fluid flows partially through the inlet-side side channel 31 , partially through the outlet-side side channel 33 and is partially carried along by the blades 11 of the impeller.
  • the fluid circulates in a spiral movement between the individual part regions of the pump chamber 7 .
  • the fluid which is pressurized here leaves the pump chamber 7 through the outlet channel 37 , flows through the electric motor 13 in the example which is shown in FIG. 1 , and then leaves the housing 5 through the outlet 27 .
  • the inlet-side side channel 31 which is configured in the intake cover 15 reaches from the inlet channel 35 in an annular manner along the flow path 39 in a part circle of approximately 300° as far as toward a region 41 , at which, in the opposite intermediate housing 17 , the outlet-side side channel 33 there leads into the outlet channel 37 .
  • it passes a degassing bore 43 .
  • FIG. 4 shows the configuration of an intake cover 15 , an intermediate housing 17 and the impeller 3 which is accommodated therein for the case of a conventional side channel pump.
  • FIG. 5 shows a corresponding configuration for a side channel pump according to one embodiment of the present invention.
  • the inlet-side side channel 31 and the outlet-side side channel 33 are dimensioned with identical widths B and identical depths KT 1 , KT 2 and therefore have identical cross sections with an otherwise identical shape.
  • the impeller 3 can come into mechanical contact with the intake cover 15 , that is to say without a gap 23 which lies in between. Solid body friction can therefore occur between the impeller 3 and the intake cover 15 , which solid body friction is substantially more pronounced than liquid friction, as occurs as long as the impeller 3 is spaced apart from the intake cover 15 via a gap 23 and the fluid to be delivered, that is to say low-viscosity fuel, for example, can flow through the gap.
  • the inlet-side side channel 31 and the outlet-side side channel 33 are configured with identical widths B, they have different depths KT 1 , KT 2 . Their cross sections therefore differ and they are asymmetrical with regard to a plane which runs transversely with respect to the side channels 31 , 33 and centrally through the impeller 3 .
  • the channel depths KT 1 , KT 2 can differ from one another, for example, by from 10% to 25%.
  • the two channel depths KT 1 , KT 2 can lie in the range from 1 to 2 mm, but the channel depth KT 1 of the inlet-side side channel 31 can be smaller by from 0.1 to 0.2 mm than the channel depth KT 2 of the outlet-side side channel 33 .
  • the width and/or shape of the side channels 31 , 33 can also be selected to be different in such a way that the cross section of the inlet-side side channel 31 is somewhat smaller than that of the outlet-side side channel 33 .
  • Gaps 23 can therefore be ensured between both end faces and respectively adjoining walls 19 , 21 of the intake cover 15 or the intermediate housing 17 .
  • the spacing which prevails in this way of the impeller 3 from the adjoining walls 19 , 21 and the low liquid friction which prevails as a result between the end faces of the impeller 3 and said side walls 19 , 21 can contribute to reduced wear phenomena and therefore to an increased service life of the side channel pump 1 .
US14/761,987 2013-01-18 2014-01-02 Side-channel pump with asymmetrical cross-sections of the side channels Abandoned US20150354573A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102013200713.2 2013-01-18
DE102013200713.2A DE102013200713A1 (de) 2013-01-18 2013-01-18 Seitenkanalpumpe mit asymmetrischen Querschnitten der Seitenkanäle
PCT/EP2014/050017 WO2014111272A1 (de) 2013-01-18 2014-01-02 Seitenkanalpumpe mit asymmetrischen querschnitten der seitenkanäle

Publications (1)

Publication Number Publication Date
US20150354573A1 true US20150354573A1 (en) 2015-12-10

Family

ID=49918710

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/761,987 Abandoned US20150354573A1 (en) 2013-01-18 2014-01-02 Side-channel pump with asymmetrical cross-sections of the side channels

Country Status (5)

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

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5372475A (en) * 1990-08-10 1994-12-13 Nippondenso Co., Ltd. Fuel pump
US20060120852A1 (en) * 2004-12-03 2006-06-08 Mitsubishi Denki Kabushiki Kaisha Circumferential flow pump

Family Cites Families (9)

* 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 (de) * 1987-08-05 1989-02-13
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
JP2008101469A (ja) * 2006-10-17 2008-05-01 Denso Corp 燃料ポンプ
JP5298854B2 (ja) * 2006-10-28 2013-09-25 ｉＭｅｄ Ｊａｐａｎ株式会社 血液用らせん流ポンプ
DE102010004379A1 (de) * 2009-12-16 2011-06-22 Continental Automotive GmbH, 30165 Kraftstoffpumpe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5372475A (en) * 1990-08-10 1994-12-13 Nippondenso Co., Ltd. Fuel pump
US20060120852A1 (en) * 2004-12-03 2006-06-08 Mitsubishi Denki Kabushiki Kaisha Circumferential flow pump

Also Published As

Publication number Publication date
WO2014111272A1 (de) 2014-07-24
DE102013200713A1 (de) 2014-07-24
CN104937276A (zh) 2015-09-23
EP2946116A1 (de) 2015-11-25

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Legal Events

Date Code Title Description
AS Assignment

Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KUEHN, MICHAEL;SKLJAROW, PAUL;CONSTANTINIDES, INA;SIGNING DATES FROM 20150730 TO 20150805;REEL/FRAME:037097/0836

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION