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WO2015124244A1 - Rotor et arbre de pompe - Google Patents

Rotor et arbre de pompe Download PDF

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Publication number
WO2015124244A1
WO2015124244A1 PCT/EP2014/079362 EP2014079362W WO2015124244A1 WO 2015124244 A1 WO2015124244 A1 WO 2015124244A1 EP 2014079362 W EP2014079362 W EP 2014079362W WO 2015124244 A1 WO2015124244 A1 WO 2015124244A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
receptacle
axis
pump shaft
shaft
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.)
Ceased
Application number
PCT/EP2014/079362
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 WO2015124244A1 publication Critical patent/WO2015124244A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • F04D29/044—Arrangements for joining or assembling shafts
    • 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
    • F04D29/20—Mounting rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0852—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft
    • F16D1/0858—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft due to the elasticity of the hub (including shrink fits)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/102—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via polygon shaped connections

Definitions

  • the invention relates to an impeller for a pump and a impeller assembly of a pump and a pump shaft.
  • Gasoline pumps are often designed as turbine pumps in which a turbine-wheel impeller is driven by a pump shaft and thus can deliver gasoline.
  • the impeller has in its center a receptacle into which the pump shaft is inserted.
  • the pump shaft and the receptacle can be made in cross-section D-shaped, d. H. a cylindrical surface and a flat driving surface include. This can lead to large torsional forces between the pump shaft and the impeller, such as may occur when starting the impeller, an edge of the shaft presses on the driving surface of the recording and this is exposed to a large amount of wear.
  • One aspect of the invention relates to an impeller for a pump, for example for a gasoline pump, such as can be used in a vehicle.
  • the impeller comprises a receptacle centered on an axis of the impeller for receiving a pump shaft and a plurality of blades disposed about the axis.
  • Blades may for example be formed by openings in the impeller, which are arranged around the receptacle. By rotation of the impeller, the blades can convey a fluid, such as fuel, from one side of the impeller to the other.
  • the receptacle is made of at least one extending around the axis
  • the (for example flat) driving surface may have a smaller distance from the axis than the radius of the cylindrical surface, so that a form-fitting
  • the receptacle has a recess between the cylinder inner surface and the driving surface, which is adapted to receive an edge of the shaft. In this way, the edge of the shaft under load can not on the
  • the driving surface is a convex surface.
  • convex can be understood that the
  • Carrier surface is curved inwardly with respect to the axis.
  • the driving surface may comprise, for example, a cylindrical surface curved towards the axis or of a plurality of cylindrical surfaces curved towards the axis be composed. With a convex driving surface, the distribution of the compressive stress can be promoted by the contact surface between the pump shaft and impeller is increased.
  • a maximum diameter of the recess is less than 15%, preferably less than 10%, of the radius of the cylinder inner surface.
  • the radius of the cylinder inner surface 3 mm (which corresponds approximately to the radius of the shaft) and the maximum
  • Diameter of the recess about 0.3 mm.
  • the receptacle has at least two driving surfaces, wherein the driving surfaces may be arranged symmetrically about the axis.
  • the receptacle (exactly) have two driving surfaces, which are arranged opposite to each other. But it is also possible that the recording has only one driving surface.
  • One or more of the driving surface may be connected on both sides via two recesses with a cylindrical surface.
  • the impeller further comprises a decoupling area surrounding the receptacle formed by at least one opening and / or at least one recess extending around the receptacle.
  • a decoupling area surrounding the receptacle formed by at least one opening and / or at least one recess extending around the receptacle.
  • an inner portion of the impeller may be mechanically decoupled from the receptacle around the receptacle.
  • the decoupling region can be regarded as a spring and / or damping region, with which large torsional forces can be damped and / or the resonance point of the arrangement of impeller and shaft can be shifted towards a low rotational frequency.
  • the decoupling region can be formed, for example, by one or more banana-shaped openings which surround the axis outside the receptacle. These openings can also be used as
  • Pressure equalization openings between the two sides of the impeller serve. It is also possible that one or more of these openings through
  • Recesses are replaced, in which only the thickness of the impeller is reduced.
  • the webs may be formed by intervening (banana-shaped) openings.
  • the web or the webs can be understood as a spring member and / or attenuator between the inner and the outer region.
  • Another aspect of the invention relates to an impeller assembly that includes a pump shaft and an impeller, such as an impeller, as described above and below.
  • the impeller assembly comprises a pump shaft rotatable about an axis and an impeller having a centered receptacle for receiving the pump shaft and having a plurality of blades disposed about the axis.
  • the receptacle has a cylinder inner surface running around the axis, which corresponds to a cylinder outer surface of the pump shaft, and has a driving surface, which corresponds to a drive surface of the pump shaft, so that the pump shaft is in a form-locking engagement with the receptacle.
  • the driving surface of the receptacle is convex and the drive surface of the pump shaft concavely curved. Also in this way it is possible (possibly without recesses) to move the contact surface between the pump shaft and recording away from an edge of the pump shaft and enlarge. But it is also possible that the impeller additionally one or more
  • the impeller in this case (exactly) have one, two or three concave driving surfaces.
  • a contact radius (in the region of a contact surface) of the pump shaft with the receptacle is at least 90% of a radius of the cylinder outer surface of the pump shaft.
  • Recesses and / or the driving surface or driving surface can be designed so that the contact radius, d. H. the distance from the axis at which the shaft contacts the receptacle is less than 10% of the radius of the cylinder inner surface of the receptacle or the cylinder outer surface of the receptacle
  • the impeller is made of plastic and / or the pump shaft is made of metal.
  • a plastic impeller wear can be reduced with the recesses and / or with the concave contact surfaces (driving surface and driving surface).
  • Fig. 1 shows schematically a gasoline pump with an impeller assembly according to an embodiment of the invention.
  • Fig. 2 shows a plan view of an impeller assembly according to a
  • FIG. 3 shows a detail of the impeller arrangement of FIG. 2.
  • Fig. 4 shows a plan view of an impeller assembly according to another embodiment of the invention.
  • FIG. 5 shows a detail of the impeller arrangement of FIG. 4.
  • Fig. 6 shows a section of an impeller assembly according to another embodiment of the invention.
  • FIG. 1 shows a gasoline pump 10, which is arranged in a housing 12
  • Impeller 14 includes, which pumps fuel from an inlet 16 to a drain 18 upon rotation. The fuel is thereby conveyed by a plurality of blades 20 from one side of the impeller to the other.
  • the impeller 14 is driven by a pump shaft 22, which with a
  • the pump shaft 22 is inserted in a positive fit with one end 26 in a receptacle 28 of the impeller 14.
  • the pump shaft 22 may have a circular cross-section outside the receptacle 28, while it is not circular at the end, but edged to a corresponding non-circular
  • the impeller 14 and a matching pump shaft 22 thereby form an impeller assembly 30 with a positive connection via the end 26 in the receptacle 28th
  • Fig. 2 shows a plan view of an impeller assembly 30.
  • the circular impeller 14, which is made for example of plastic, has an axis A, to which also the pump shaft 22, which is made for example of metal, and the receptacle 28 in the middle of the impeller 14 are centered.
  • the pump shaft 22 which is made for example of metal
  • Edge of the impeller 14 are formed obliquely to the axis A extending openings in the impeller 14, between which the blades 20 are provided.
  • Pressure compensation openings 36 serve to balance a pressure between the two sides of the impeller.
  • the banana-shaped depressions 32 (which do not penetrate the impeller 14 in the direction of the axis, but have a smaller material thickness) form a
  • the inner portion 40 and the outer portion 42 are connected by webs 34, which between the
  • Recesses 32 are formed. These webs 34 can be considered as damping or spring elements to the inner portion 40 of the outer
  • Range 42 (for example, by shifting a resonant frequency) to decouple.
  • FIG. 3 The receptacle 28 and the inserted end 26 of the shaft 22 of FIG. 2 are shown enlarged in FIG. 3.
  • the end 26 of the shaft 22 has two opposite cylindrical surfaces 44 about the axis A, which are interconnected via two opposing planar drive surfaces 46. Between each cylindrical surface 44 and a drive surface 46, the end 26 of the shaft 22 has an edge 48 which is parallel to the axis A.
  • the shaft 22 and the cylindrical surfaces 44 have
  • a radius of about 3 mm for example, a radius of about 3 mm.
  • the receptacle 28 in turn has two opposite cylindrical surfaces 50 (for example, with a slightly larger radius than about 3 mm), the over
  • Recesses 52 are connected to two opposite, flat driving surfaces 54.
  • the recesses 52 are rounded concave, have no edges and / or parallel to the axis A.
  • the recesses 52 may be characterized in that their
  • Inner surface is at least partially further away from the axis A, as an (imaginary) continuous extension of the driving surfaces 54 of the recording in the direction of the cylindrical surfaces 50 and / or an (imaginary) continuous extension of the cylindrical surfaces 50 in the direction of
  • each between the driving surface 54 and the Cylindrical surface 54 are arranged and extending in the direction away from the shaft 22.
  • the flat driving surface 54 passes via the recess 52 with a radius of curvature of about 0.6 mm in the cylindrical surface 50, wherein it strikes the cylindrical surface 50 at about 40 °.
  • the maximum diameter of the recesses 52 is about 3 mm, that is about 10% of the radius of the shaft.
  • the edges 48 are in the region of the recesses 52 and the force is transmitted over a surface 56 adjacent the edges 48, which is greater than when the corresponding edge 48 on the driving surface 54th would press. In this way, the stress of the receptacle 28 can be reduced by the shaft 22.
  • the surface 56 is approximately 2.7 mm away from the axis A, ie about 90% of the radius of the shaft 22.
  • FIG. 4 shows a further embodiment of an impeller assembly 30, in which the impeller 14 no pressure equalization openings 36 outside the
  • Decoupling region 38 in which the decoupling region 38 banana-shaped openings 32 'which replace the wells 32 of FIG. 2 and at the same time serve as pressure equalization openings.
  • impeller assembly 30 of Fig. 4 has a triangular shaped
  • Receiving 28 ' in which a corresponding end 26' of a pump shaft 22 'is inserted.
  • the end 26 'of the shaft 22 has three symmetrically arranged cylindrical surfaces 44 about the axis A, which has three symmetrically arranged, convex
  • Drive surfaces 46 are connected together. Between each cylindrical surface 44 and a drive surface 46, the end 26 of the shaft 22 has an edge 48 which is parallel to the axis A. Just as in the Fig. 3, the Shaft 22 and the cylindrical surfaces 44, for example, have a radius of about 3 mm.
  • the receptacle 28 has three symmetrically arranged cylindrical surfaces 50 (for example, also with a radius slightly larger than about 3 mm), which are connected to three symmetrically arranged, concave driving surfaces 54.
  • the drive surfaces 46 and the driving surfaces 54 are curved so that the contact surface 56 between the end 26 'and the receptacle 28' is approximately 90% of the radius of the shaft 22 away from the axis A.
  • the drive surfaces 46 and the driving surfaces 54 (in the middle) have a cylindrical shape with a radius of about 15 mm, wherein the
  • Passage surfaces on their sides 54 with a radius of curvature of about 0.6 mm in the cylindrical surfaces 50 pass over and meet them at an angle of about 40 °.
  • FIG. 6 shows a detail of a further embodiment of an impeller assembly 30, with a receptacle 28 ", which is D-shaped with recesses 52, and in which a D-shaped end 26 'of the shaft 22 with convex drive surface 46 is inserted
  • the dimensions of the drive surface 46 and the driving surface 54 may be as in Fig. 5, the dimensions of the recesses 52 as in FIG.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un rotor (14) destiné à une pompe (10), lequel comprend un logement (28, 28'') centré sur un axe (A) du rotor (14) pour recevoir un arbre de pompe (22) et une pluralité d'ailettes (20) agencées autour de l'axe (A), le logement (28, 28'') étant formé d'au moins une surface intérieure cylindrique (50) s'étendant autour de l'axe (A) et d'au moins une surface d'entraînement (54) permettant à l'arbre de pompe (22) de venir en prise par complémentarité de forme dans le logement. Le logement (28, 28'') présente un évidement (52) entre la surface intérieure cylindrique (50) et la surface d'entraînement (54) qui est conçu pour recevoir une arête (48) de l'arbre (22).
PCT/EP2014/079362 2014-02-18 2014-12-29 Rotor et arbre de pompe Ceased WO2015124244A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014202909.0 2014-02-18
DE102014202909.0A DE102014202909A1 (de) 2014-02-18 2014-02-18 Laufrad und Welle einer Benzinpumpe

Publications (1)

Publication Number Publication Date
WO2015124244A1 true WO2015124244A1 (fr) 2015-08-27

Family

ID=52292932

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/079362 Ceased WO2015124244A1 (fr) 2014-02-18 2014-12-29 Rotor et arbre de pompe

Country Status (2)

Country Link
DE (1) DE102014202909A1 (fr)
WO (1) WO2015124244A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021103444A1 (de) * 2021-02-15 2022-08-18 Kiekert Aktiengesellschaft Elektromotorische Antriebseinheit für kraftfahrzeug-technische Anwendungen
DE102024111082A1 (de) * 2024-04-19 2025-10-23 Frideco Ag Pumpenvorrichtung, Pumpe und Verfahren zur Herstellung einer Pumpenvorrichtung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60180783U (ja) * 1984-05-11 1985-11-30 豊興工業株式会社 液体歯車ポンプ
JPS61223282A (ja) * 1985-03-26 1986-10-03 Honda Motor Co Ltd オイルポンプ装置
US4692092A (en) * 1983-11-25 1987-09-08 Nippondenso Co., Ltd. Fuel pump apparatus for internal combustion engine
DE4338475A1 (de) * 1993-11-10 1995-05-11 Bmw Rolls Royce Gmbh Wellen-Nabenverbindung mit einer Leichtmetall-Nabe
WO2006002463A1 (fr) * 2004-06-30 2006-01-12 Ringprop Trading Limited Système de moyeu d'hélice
EP1837522A1 (fr) * 2005-01-12 2007-09-26 Mitsubishi Materials PMG Corporation Rotor interieur pour pompe a engrenages internes

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4692092A (en) * 1983-11-25 1987-09-08 Nippondenso Co., Ltd. Fuel pump apparatus for internal combustion engine
JPS60180783U (ja) * 1984-05-11 1985-11-30 豊興工業株式会社 液体歯車ポンプ
JPS61223282A (ja) * 1985-03-26 1986-10-03 Honda Motor Co Ltd オイルポンプ装置
DE4338475A1 (de) * 1993-11-10 1995-05-11 Bmw Rolls Royce Gmbh Wellen-Nabenverbindung mit einer Leichtmetall-Nabe
WO2006002463A1 (fr) * 2004-06-30 2006-01-12 Ringprop Trading Limited Système de moyeu d'hélice
EP1837522A1 (fr) * 2005-01-12 2007-09-26 Mitsubishi Materials PMG Corporation Rotor interieur pour pompe a engrenages internes

Also Published As

Publication number Publication date
DE102014202909A1 (de) 2015-08-20

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