EP1934479A1 - Pompe a palettes - Google Patents

Pompe a palettes

Info

Publication number
EP1934479A1
EP1934479A1 EP06793383A EP06793383A EP1934479A1 EP 1934479 A1 EP1934479 A1 EP 1934479A1 EP 06793383 A EP06793383 A EP 06793383A EP 06793383 A EP06793383 A EP 06793383A EP 1934479 A1 EP1934479 A1 EP 1934479A1
Authority
EP
European Patent Office
Prior art keywords
rotor
grooves
annular groove
rotation
groove
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Withdrawn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
EP06793383A
Other languages
German (de)
English (en)
Inventor
Christian Langenbach
Arno Lorenz
Rocco Guarino
Vito Spinelli
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 EP1934479A1 publication Critical patent/EP1934479A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/22—Manufacture essentially without removing material by sintering
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the invention relates to a fl uid cell pump according to the preamble of claim 1.
  • This flight cell pump has a
  • Rotor has distributed over its circumference a plurality of grooves which extend at least substantially radially to the axis of rotation of the rotor and in each of which a flugelformiges Forder element is guided displaceably.
  • the Pumpengehause has a surrounding the rotor, to its axis of rotation eccentric peripheral wall, against which the wings with their radially outer ends.
  • the pump housing has in the direction of the axis of rotation of the rotor to these adjacent Gehausestirnwande.
  • the inventive flight-wave pump with the features of claim 1 has the advantage that their production is simplified, since the introduction of at least one annular groove in the rotor is possible in a simpler manner than in the Gehausestirnwand.
  • Embodiments and developments of the inventive vane pump specified allows a two-sided pressurization of the rotor, so that acts on these at least substantially no axial forces and the wear of the rotor and the Gehausestirnwande can be kept low.
  • the embodiment of claim 3 allows at least approximately the avoidance of axial forces on the rotor at the same time limited extent of the annular grooves in the two end faces of the rotor.
  • Particularly advantageous is the embodiment according to claim 4, by a annular groove only two successive grooves in the rotor are connected to each other, as this possible leakage losses can be kept low.
  • FIG. 1 shows a plane-zonal pump in a simplified representation in a cross-section along line II in FIG. 3
  • FIG. 2 shows the flight-cell pump in a cross-section along line II-II in FIG. 3 according to a first exemplary embodiment
  • FIG. 3 shows the plane-cell pump in a longitudinal section along line III-III.
  • III in Figure 1 and Figure 4 the vane pump in a cross section along line II-II according to a second exemplary embodiment.
  • a Flugelzellenpumpe is shown, which is preferably provided for requesting fuel, in particular diesel fuel.
  • the vane pump By the vane pump while fuel from a storage container is required to a high-pressure pump.
  • the vane pump may be arranged separately from the high pressure pump, attached to the high pressure pump or integrated into the high pressure pump.
  • the vane pump has a pump housing 10, which is designed in several parts, and a drive shaft 12, which projects into the pump housing 10.
  • the pump housing 10 has two
  • Gehausestirnwande 14,16 through which in the axial direction, that is, in the direction of the axis of rotation 13 of the drive shaft 12, a pump chamber is limited. In the circumferential direction, the pump chamber is bounded by a peripheral wall 18, the einstuckig with one of Gehausestirnwande 14,16 or can be formed separately from these.
  • the rotor 20 has the housing end walls 14,16 facing end faces 201 and 202.
  • a rotor 20 is arranged in the pump chamber, which rotor is connected in a rotationally fixed manner to the drive shaft 12, for example via a groove / spring connection 22.
  • the rotor 20 has a plurality of circumferentially distributed, at least substantially radially to the axis of rotation 13 of the rotor 20 extending grooves 24.
  • the grooves 24 extend, starting from the outer jacket of the rotor 20, towards the axis of rotation 13 and into the rotor 20.
  • four grooves 24 are provided, wherein fewer or more than four grooves 24 may be provided.
  • a disk-shaped Forderelement 26 is slidably disposed, which is hereinafter referred to as a wing and protrudes with its radially outer end portion of the groove 24.
  • a radially inner interior 25 is limited in the respective groove 24.
  • the inside of the peripheral wall 18 of the Pumpengehauses 10 is formed eccentrically to the rotational axis 13 of the rotor 20, for example, circular or other shape.
  • a suction region is provided, in which at least one mammal opening 28 mouths.
  • a suction groove 30 which is elongate in the circumferential direction of the rotor 20 and is approximately kidney-shaped curved is preferably formed in at least one housing end wall 14, 16, into which the mammal opening 28 mouths.
  • the mammal opening 28 preferably opens into the suction groove 30 in its end region facing counter to the direction of rotation 21 of the rotor 20.
  • the mammal opening 28 is connected to an inlet leading from the storage container.
  • a pressure area is also provided, in which at least a Drucko réelle 32 mouths.
  • a pressure groove 34 which is elongate in the circumferential direction of the rotor 20 and is approximately in the shape of a kidney is preferably formed in at least one housing end wall 14, 16, into which the pressure opening 32 extends.
  • the Drucko réelle 32 tastes in the pressure groove 34 preferably in the direction of rotation 21 of the rotor 20 facing end region.
  • the Drucko réelle 32 is connected to a leading to the high pressure pump drain.
  • the mammal opening 28, the suction groove 30, the Drucko réelle 32 and the pressure groove 34 are arranged at a radial distance from the rotational axis 13 of the rotor 20 near the inside of the peripheral wall 18.
  • the wings 26 abut with their radially outer ends on the inside of the peripheral wall 18 and slide on this during the rotational movement of the rotor 20 in the direction of rotation 21 along.
  • the volume of the chambers 36 increases, so that they are filled with fuel.
  • the pressure groove 34 and the Drucko réelle 32 is disposed in a peripheral region in which the volume of the chambers 36 is reduced during the rotational movement in the direction of rotation 21 of the rotor 20, so that from this fuel in the pressure groove 34 and from this into the Drucko réelle 32 is displaced ,
  • annular groove 38 extending over the entire circumference of the rotor 20 is provided, which is connected to the inner regions 25 delimited by each wing 26 in the respective groove 24. Subsequently, the annular groove 38 is referred to as annular groove 38.
  • the annular groove 38 may for example be such that their radial inner edge at least approximately at the same radial distance from the axis of rotation 13 of the rotor 20 extends as the radially inner edge of the grooves 24 in the rotor 20, wherein the annular groove 38 then approximately tangentially into the grooves 24.
  • the radially inner edge of the annular groove 38 extends at a smaller radial distance from the rotational axis 13 than the radially inner edge of the grooves 24, the annular groove 38, for example, approximately radially into the grooves 24.
  • the annular groove 38 can also run at a smaller radial distance from the rotational axis 13 than the radially inner edges of the grooves 24 and be connected via a respective further groove in the rotor 20 with the inner regions 25 of the grooves 24.
  • the annular groove 38 can also extend at a greater radial distance from the axis of rotation 13 than the radially inner edge of the grooves 24, but should run at a smaller radial distance from the axis of rotation 13 than the radially inner ends of the wings 26.
  • the annular groove 38 divided into several annular groove sections. It may be provided that in each case an annular groove 38 is provided in both end faces 201,202 of the rotor 20 or alternatively it may also be provided that only in one end face 201 or 202 of the rotor 20, an annular groove 38 is provided. From the pressure groove 34 leads in the end face 201,202 of the rotor 20, in which the annular groove 38 is arranged, facing
  • a connecting groove 40 from which ends approximately at a distance of the annular groove 38 of the rotation axis 13 and through which the annular groove 38 is thus connected to the pressure groove 34 and thus the pressure range.
  • the connecting groove 40 may also be provided a connecting hole.
  • a sealing region 39 is formed, in which between the rotor 20 and the adjacent Gehausestirnwand 14,16 only a small axial distance is present. In the area around the drive shaft 12, there is only a small amount Pressure, so that between the annular groove 38 and the area around the drive shaft 12 is a pressure drop.
  • annular groove 38 on an end face 201 or 202 of the rotor 20 does not extend over the entire circumference of the rotor 38 but only over a part of the circumference, wherein a plurality of circumferentially offset from each other annular grooves 38 are provided could be.
  • a plurality of annular grooves 38 may be provided, which connect only the inner regions 25 of two successive grooves 24 of the rotor 20 with each other. This means that in the embodiment according to FIG. 2, two sections 381, 382 of the annular groove 38 are dispensed with.
  • a bilateral and symmetrical arrangement of the annular grooves 38 on the rotor 20 has the advantage that act on the rotor 20 at least approximately no resulting forces in the direction of its axis of rotation 13 and no tilting moments perpendicular to the axis of rotation 13, so that the rotor 20 at least approximately centrally between the two Gehausestirnwanden 14,16 circulates without coming into contact with these. If sections of annular grooves 38 which do not extend over the entire circumference of the rotor 20 are provided in both end faces 201, 202 of the rotor 20, the leakage through the sealing region 39 can be kept small.
  • the connecting groove 40 may extend, for example radially or inclined to a radial with respect to the axis of rotation 13 of the pressure groove 34 inwardly.
  • the connecting groove 40 can, in particular, run in such a way that it approaches the annular groove 38 in the direction of rotation 21 of the rotor 20.
  • the connecting groove 40 can extend helically curved.
  • the connecting groove 40 preferably preferably at least approximately tangentially into the pressure groove 34 and / or on the other hand at least approximately tangentially in the annular groove 38.
  • the Connecting groove 40 in the counter to the direction of rotation 21 of the rotor 20 facing end portion of the pressure groove 34.
  • the at least one annular groove 38 is preferably introduced in the rotor 20 by primary molding and not by a machining process.
  • the rotor 20 can be produced, for example, by means of a pressing or forging process, in which case the corresponding shape of the pressing or forging tool then forms the at least one annular groove 38 in the rotor 20 during production thereof.
  • the rotor 20 may be made of sintered metal to ensure sufficient strength and wear resistance of the rotor 20.
  • the annular groove 38 is connected to the pressure groove 34 connecting groove 40 is arranged or it can be arranged in both Gehausestirnwanden 14 and 16 respectively at least one connecting groove 40, which then preferably mirror images of each other in the Gehausestirnwanden 14 and 16 are arranged. It can also be provided that only in a housing end wall 14 or 16, the suction groove 30 and / or the pressure groove 34 is formed, wherein the other
  • Gehausestirnwand 16 and 14 is formed smooth, or that in both Gehausestirnwanden 14 and 16 each have a suction groove 30 and / or pressure groove 34 is formed, which are then preferably arranged mirror images of each other in the Gehausestirnwanden 14 and 16.
  • Mouth opening 28 and the Drucko réelle 32 is but only provided in a housing end wall 14 or 16, wherein in a Gehausestirnwand 14, the infant opening 28 is provided and in the other housing wall 16, the Drucko réelle 32 is provided.
  • the rotor 20 and the wings 26 are loaded in the axial direction on both sides at least approximately equal, so that no or only one low resultant force on the rotor 20 and the wings 26 in the direction of the axis of rotation 13 acts.
  • the depth of the at least one annular groove 38 in the rotor 20 and the connecting groove 40 in the housing end wall 14,16 amounts, for example, between 0.1 and 2mm, preferably the width of the grooves 38,40 is greater than the depth.
  • FIG. 4 shows the flight-cell pump according to a second exemplary embodiment, in which the essential structure is the same as in the first exemplary embodiment.
  • the two end faces 201,202 of the rotor 20 each have at least one annular groove 38 is introduced, wherein the annular grooves 38 of one end face 201 extend over a different peripheral portion of the rotor 20 than the annular grooves 38 of the other end face 202.
  • the Rotor 20 four grooves 24, wherein two annular grooves 383 of the one end face 201 each extend over approximately 90 ° between each two consecutive grooves 24 and are diametrically opposite each other.
  • the two annular grooves 384 of the other end face 202 also extend over approximately 90 °, but are offset from the grooves 383 of the end face 201 offset by 90 ° so that they do not overlap, and extend between each two consecutive grooves 24th
  • the annular grooves 384 of the end face 202 are shown in dashed lines in Figure 4, as these on the opposite end face 202 of the rotor 20 are arranged and thus are not actually visible in Figure 4.
  • the embodiment according to FIG. 4 can also be transferred to other embodiments of the rotor 20 in which it has an even number of slots 24.
  • the annular grooves 38 each extend only between two successive grooves 24 and the annular grooves 38 of the two end faces 201,202 are arranged offset from one another in the circumferential direction, so that they do not overlap.
  • this arrangement of the annular grooves 38 at least substantially no axial forces in the direction of the axis of rotation 13 on the rotor 20 are produced which would have pressed these against one of the housing end walls 14, 16 and thus would cause increased wear.
  • the leakage can be kept low by the sealing area 39.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne une pompe à palettes qui présente un corps (10) dans lequel est disposé un rotor (20) qui est entraîné en rotation par un arbre d'entraînement (12), ce rotor (20) présentant plusieurs rainures (24) réparties sur sa périphérie qui s'étendent au moins sensiblement radialement par rapport à l'axe de rotation (13) du rotor (20) et dans chacune desquelles un élément de refoulement (26) en forme de palette est guidé de façon coulissante. Les parois d'extrémité (14, 16) du corps (10) de la pompe sont adjacentes au rotor (20) dans le sens de son axe de rotation (13). Au moins une rainure annulaire (38) entourant l'axe de rotation (13) du rotor (20) est formée dans au moins une des faces (201, 202) dudit rotor (20), cette rainure annulaire (38) étant reliée aux zones intérieures (25) délimitées par les palettes (26) dans les rainures (24) du rotor (20) et à la zone de pression (32, 34). Ladite rainure annulaire (38) est formée dans le rotor (20) de préférence par façonnage.
EP06793383A 2005-09-30 2006-09-11 Pompe a palettes Withdrawn EP1934479A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005047175A DE102005047175A1 (de) 2005-09-30 2005-09-30 Flügelzellenpumpe
PCT/EP2006/066201 WO2007039405A1 (fr) 2005-09-30 2006-09-11 Pompe a palettes

Publications (1)

Publication Number Publication Date
EP1934479A1 true EP1934479A1 (fr) 2008-06-25

Family

ID=37461569

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06793383A Withdrawn EP1934479A1 (fr) 2005-09-30 2006-09-11 Pompe a palettes

Country Status (6)

Country Link
US (1) US7845922B2 (fr)
EP (1) EP1934479A1 (fr)
JP (1) JP2009510311A (fr)
CN (1) CN101273200B (fr)
DE (1) DE102005047175A1 (fr)
WO (1) WO2007039405A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004060554A1 (de) 2004-12-16 2006-06-22 Robert Bosch Gmbh Flügelzellenpumpe
WO2010129970A2 (fr) * 2009-05-07 2010-11-11 Cheetah Technologies (Pty) Ltd Moteur à air
GB2486007B (en) * 2010-12-01 2017-05-10 Itt Mfg Enterprises Inc Sliding vane pump
DE102013001246A1 (de) * 2013-01-25 2014-07-31 Gkn Sinter Metals Holding Gmbh Verfahren zur Herstellung eines Flügels für eine Flügelzellenpumpe, Flügel für eine Flügelzellenpumpe sowie Flügelzellenpumpe
US9605673B2 (en) * 2013-10-17 2017-03-28 Tuthill Corporation Pump with pivoted vanes
EP3350447B1 (fr) * 2015-09-14 2020-03-25 Torad Engineering, LLC Dispositif d'hélice à aubes multiples
JP7243528B2 (ja) * 2019-08-29 2023-03-22 株式会社デンソー ベーンポンプ
DE102022202358A1 (de) 2022-03-09 2023-09-14 Mahle International Gmbh Gerotoreinrichtung und Pumpeneinrichtung mit Gerotoreinrichtung

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Publication number Priority date Publication date Assignee Title
GB186271A (en) * 1921-11-23 1922-09-28 John Alexander Mair Improvements in rotary pumps
US2004958A (en) 1931-08-22 1935-06-18 Mitchell Bryce Rotary pump
US2423271A (en) 1942-09-11 1947-07-01 Frank A Talbot Rotary motor, pump, and the like
US2544987A (en) * 1947-01-04 1951-03-13 Vickers Inc Power transmission
US2653550A (en) * 1950-10-07 1953-09-29 Vickers Inc Power transmission
US3574493A (en) * 1969-04-21 1971-04-13 Abex Corp Vane-type pumps
US4455129A (en) 1981-05-19 1984-06-19 Daikin Kogyo Co., Ltd. Multi-vane type compressor
JPS61142381A (ja) * 1984-12-14 1986-06-30 Mazda Motor Corp ベ−ンポンプ
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JPS63167089A (ja) * 1986-12-27 1988-07-11 Kayaba Ind Co Ltd ベ−ンポンプ
JPS63280883A (ja) 1987-05-14 1988-11-17 Toyota Autom Loom Works Ltd 可変容量型ベ−ン圧縮機
JPH01155096A (ja) 1987-12-10 1989-06-16 Suzuki Motor Co Ltd ベーン型回転圧縮機
US5265457A (en) 1990-02-16 1993-11-30 Sumitomo Electric Industries, Ltd. Method of forming an oil groove on the end surface of a rotor of an aluminum alloy
JPH0469686A (ja) * 1990-07-10 1992-03-04 Ricoh Co Ltd 電子写真装置
JPH0469686U (fr) * 1990-10-25 1992-06-19
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DE19952167A1 (de) * 1998-12-24 2000-06-29 Mannesmann Rexroth Ag Pumpenanordnung mit zwei Hydropumpen
CN2591277Y (zh) * 2002-09-05 2003-12-10 金文彪 无磨擦叶片泵
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DE102004060554A1 (de) 2004-12-16 2006-06-22 Robert Bosch Gmbh Flügelzellenpumpe

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Title
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Also Published As

Publication number Publication date
US20080253913A1 (en) 2008-10-16
CN101273200A (zh) 2008-09-24
US7845922B2 (en) 2010-12-07
JP2009510311A (ja) 2009-03-12
CN101273200B (zh) 2010-06-16
WO2007039405A1 (fr) 2007-04-12
DE102005047175A1 (de) 2007-04-05

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