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WO2022263370A1 - Pompe et véhicule comprenant une telle pompe - Google Patents

Pompe et véhicule comprenant une telle pompe Download PDF

Info

Publication number
WO2022263370A1
WO2022263370A1 PCT/EP2022/066017 EP2022066017W WO2022263370A1 WO 2022263370 A1 WO2022263370 A1 WO 2022263370A1 EP 2022066017 W EP2022066017 W EP 2022066017W WO 2022263370 A1 WO2022263370 A1 WO 2022263370A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
opening
impeller
fluid
damping chamber
Prior art date
Application number
PCT/EP2022/066017
Other languages
German (de)
English (en)
Inventor
Johannes Walter
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
Priority to CN202280043081.6A priority Critical patent/CN117501017A/zh
Publication of WO2022263370A1 publication Critical patent/WO2022263370A1/fr

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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/428—Discharge tongues
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/688—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for liquid pumps

Definitions

  • the invention relates to a pump for a vehicle, in particular a motor vehicle, for pumping a fluid, having the features of claim 1, and a vehicle, in particular a motor vehicle, having the features of the independent claim.
  • Centrifugal pumps are used, for example, in a vehicle to convey a coolant fluid within a coolant circuit.
  • Centrifugal pumps in particular are used here.
  • disturbing noises can arise, in particular due to pressure fluctuations.
  • a pump for a vehicle for pumping a fluid, comprising a pump housing with a pump interior, an inlet for supplying the fluid into the pump interior and an outlet for discharging the Fluids from the pump interior.
  • the fluid can be a gas and/or a liquid.
  • the pump interior fluidically couples the inlet and the outlet to one another.
  • a fluidic connection or a fluidic coupling means that a gas and/or a liquid (fluid) can flow between two fluidically coupled elements or between two elements that are fluidically connected.
  • the pump further includes an impeller.
  • the pump can further comprise a shaft, wherein the impeller can be coupled to the shaft in a rotationally fixed manner.
  • the impeller can be arranged in particular on the shaft.
  • the impeller has multiple impeller blades. These are arranged in particular on the radial outside of the shaft (distributed over the circumference of the shaft).
  • the shaft can drive the impeller.
  • the shaft can cause the impeller to rotate about the longitudinal axis of the shaft.
  • the shaft can be designed as a hollow shaft.
  • the impeller blades can be at least partially hollow.
  • the pump is set up in such a way that the impeller is driven, in particular rotationally, and a fluid, for example a coolant, can thereby be conveyed from the inlet (suction connection) to the outlet (pressure connection).
  • a fluid for example a coolant
  • the impeller can be driven by the shaft.
  • the impeller and/or the impeller blades is/are arranged at least partially inside the pump interior. Additionally or alternatively, the shaft can be arranged at least partially inside the pump interior. In particular, the impeller and the impeller blades can be arranged entirely in the pump interior.
  • the pump housing has a damping device for reducing a pressure generated locally at the radially outer ends of the impeller blades.
  • the radially outer ends of the impeller blades correspond to the ends of the impeller blades facing away from the shaft.
  • This locally generated pressure occurs during the rotation of the impeller (i.e. during operation of the pump), especially at narrow points between the individual impeller blades and the pump housing. This pressure follows the rotation of the impeller blades.
  • the distance between the individual impeller blades (or their radially outer ends) causes pressure fluctuations that can be emitted into the environment as audible noise via the pump housing.
  • the damping device reduces these pressure fluctuations and thus reduces the noise emitted to the environment via the pump housing.
  • the pump can be designed in particular as an electric coolant pump.
  • the pump in particular the pump housing, can have additional components, for example an expansion tank for fluid. It is also conceivable that the pump, in particular the pump housing, can be integrated into an expansion tank for fluid.
  • the pump housing can be a volute housing.
  • the volute housing can have a tongue, in which case the damping device can be arranged in the tongue.
  • the tongue represents the narrowest point between the impeller or the impeller blades and the pump housing. This is where the greatest pressure gradient (pressure peak) can be expected.
  • the tongue separates the part of the pump interior in which the impeller is arranged from the outlet or outlet channel, which extends radially or tangentially away, in particular with respect to the impeller.
  • the pump can be a centrifugal pump, in particular an electronically commutated centrifugal pump (coolant pump).
  • the damping device can have a first opening, a second opening and a damping chamber.
  • the first opening can fluidly connect the pump interior and the damping chamber to one another.
  • the second opening can fluidly connect the damping chamber and the pump interior to one another.
  • the pump interior can be fluidically connected to the damping chamber by means of the first and the second opening.
  • the damping chamber can have a (circular) round cross section.
  • the mean cross section of the first opening can be smaller than the mean cross section of the damping chamber.
  • the mean cross section means the geometric mean of all cross sections of the first opening or the damping chamber perpendicular to the longitudinal axis of the first opening.
  • the cross section of the first opening in a region facing the damping chamber is smaller than the cross section of the damping chamber in a region facing the first opening.
  • the cross section perpendicular to the longitudinal axis of the first opening suddenly increases in size in the transition area from the first opening to the damping chamber.
  • the transition between the first opening and the damping chamber can thus function as a first Carnot diffuser.
  • Fluid can be conveyed in a first flow direction through the first opening into the damping chamber by rotating the impeller or the impeller blades in a first direction of rotation.
  • the cross section perpendicular to the longitudinal axis of the second opening can suddenly increase at the transition between the second opening and the pump interior, so that this transition can function as a second Carnot diffuser when the fluid is conveyed in the first flow direction.
  • the average cross section of the second opening can be smaller than the average cross section of the damping chamber.
  • the mean cross section means the geometric mean of all cross sections of the second opening or of the damping chamber perpendicular to the longitudinal axis of the second opening.
  • the cross section of the second opening in a region facing the damping chamber is smaller than the cross section of the damping chamber in a region facing the second opening.
  • the cross section perpendicular to the longitudinal axis of the second opening suddenly increases in size in the transition area from the second opening to the damping chamber.
  • the transition between the second opening and the damping chamber can function as a third Carnot diffuser.
  • the fluid can be conveyed in a second flow direction through the second opening into the damping chamber by rotating the impeller or the impeller blades in a second direction of rotation.
  • the cross section perpendicular to the longitudinal axis of the first opening can suddenly increase at the transition between the first opening and the pump interior, so that this transition can function as a fourth Carnot diffuser when the fluid is conveyed in the second flow direction.
  • the first direction of rotation is opposite to the second direction of rotation.
  • the first direction of flow is opposite to the second direction of flow.
  • the Carnot effect in both directions of rotation or both directions of flow
  • two Carnot diffusers can be implemented in each flow direction of the fluid.
  • the first opening, the second opening and/or the damping chamber has rounded edges, in particular no sharp edges.
  • the damping chamber has no sharp edges in the area facing the first and/or second opening.
  • the first and/or the second opening does not have any sharp edges in the area facing the damping chamber.
  • the impeller blades can be arranged at irregular distances from one another on the impeller. In this way, the noise occurring during operation of the pump (or during the rotation of the impeller or impeller blades) can be distributed over a broader frequency range, as a result of which the audible noise peaks can be reduced.
  • the impeller blades can be arranged on the impeller at regular intervals from one another.
  • the tongue can have a V-shaped geometry.
  • the cross section, in particular perpendicular to the axis of rotation of the shaft (ie perpendicular to the axial direction), of the tongue can be essentially V-shaped.
  • the tongue can be rounded at its free end to avoid sharp edges. In other words, the end of the tongue protruding into the interior of the pump can be rounded.
  • a vehicle in particular a motor vehicle
  • a pump according to the above statements.
  • the measures described in connection with the pump can serve to further refine the vehicle.
  • the vehicle can be designed as an electric motor vehicle.
  • An embodiment of the invention will be explained below with reference to the accompanying drawings. It shows, each schematically,
  • Figure 1 is a sectional view of a pump according to the invention.
  • Figure 2 shows an enlarged detail from Figure 1.
  • FIG. 1 shows a schematic representation of a pump 10 for conveying a fluid.
  • the pump 10 has a pump housing 12 with a pump interior 14, an inlet 16 for supplying the fluid into the pump interior 14 and an outlet 18 for discharging the fluid from the pump interior 14.
  • the pump 10 further has a shaft 20 and an impeller 22 coupled in a torque-proof manner to the shaft 20 .
  • the impeller 22 has a plurality of impeller blades 24 .
  • the impeller 22 can be driven in a first direction of rotation 11 by means of the shaft 20 .
  • the shaft 20 can be rotated in a second direction of rotation 13 which is opposite to the first direction of rotation 11 .
  • the impeller blades 24 are arranged on the impeller 22 at regular intervals from one another.
  • the impeller blades 24 have a shape that is curved in the second direction of rotation 13 .
  • the impeller 22 and the impeller blades 24 are arranged entirely in the pump interior 14 .
  • the pump 10 is in the form of a centrifugal pump 34 .
  • the pump housing 12 is designed as a volute housing 30 with a tongue 32 .
  • the tongue 32 is rounded at its end projecting into the pump interior 14 .
  • a damping device 26 is arranged in tongue 32 . This serves to reduce a pressure locally generated at the outer ends 28 (or the ends facing away from the shaft 20) of the impeller blades 24.
  • the fluid to be conveyed is sucked in through the inlet 16 and, by the rotation of the impeller 22 on the impeller blades 24, is pushed radially outwards (i.e conveyed radially outwards from the axis of rotation of the shaft 22 .
  • the fluid then exits the pump housing 12 via the outlet 18.
  • the fluid is accelerated along the impeller blades 24 .
  • the narrowest point between the pump housing 12 and the impeller blades 24 (or the impeller 22) is formed by the tongue 32. This is where the locally generated pressure is greatest.
  • the rotation of the impeller 22 causes pressure fluctuations and, in particular, pressure peaks on the tongue 32, which can lead to an annoying noise.
  • the damping device 26 is arranged in the tongue 32 in order to reduce the pressure peaks.
  • FIG. 2 shows an enlarged detail from FIG. 1.
  • the tongue 32 and the damping device 26 are shown enlarged.
  • the damping device 26 has a first opening 36 , a second opening 38 and a damping chamber 40 .
  • the pump interior 14 is fluidically connected to the damping chamber 40 via the two openings 36 , 38 .
  • the fluid flows from the pump interior 14 through the first opening 36 into the damping chamber 40 and from there again through the second opening 38 into the pump interior 14 (first flow direction). .
  • the first and second openings 36, 38 are narrow compared to the damping chamber 40, respectively.
  • the cross section of the first opening 36 is smaller in its region 42 facing the damping chamber 40 than the cross section of the damping chamber 40 in its region 44 facing the first opening 36.
  • the cross section perpendicular to the longitudinal axis of the first opening 36 at the transition from the first opening 36 to the damping chamber 40 becomes much larger. This transition thus represents a first Carnot diffuser (in the first flow direction).
  • the fluid is thus accelerated through the first, in particular narrow, opening 36, so that the kinetic energy of the fluid increases.
  • the fluid then enters the damping chamber 40, where the kinetic energy of the fluid is dissipated due to the cross-sectional expansion (first Carnot diffuser).
  • the fluid is then accelerated through the second, in particular narrow, opening 38 so that the kinetic energy of the fluid increases.
  • the fluid then enters the pump chamber 14, where the kinetic energy of the fluid is dissipated due to the widening of the cross section (second Carnot diffuser). In this way, the locally increased pressure can be reduced in two stages (first and second Carnot diffuser).
  • the fluid flows from the pump interior 14 through the second opening 38 into the damping chamber 40 and from there again through the first opening 36 into the pump interior 14 (second flow direction).
  • the cross section of the second opening 38 is smaller in its region 46 facing the damping chamber 40 than the cross section of the damping chamber 40 in its region 48 facing the second opening 38.
  • the cross section perpendicular to the longitudinal axis of the second opening 38 at the transition from the second opening 38 to the damping chamber 40 is greatly increased. This transition thus represents a third Carnot diffuser (in the second flow direction).
  • the fluid is thus accelerated through the second, in particular narrow, opening 38 so that the kinetic energy of the fluid increases.
  • the fluid then enters the damping chamber 40, where the kinetic energy of the fluid is dissipated due to the cross-sectional expansion (third Carnot diffuser).
  • the fluid is then accelerated through the first, in particular narrow, opening 36 so that the kinetic energy of the fluid increases.
  • the fluid then enters the pump chamber 14, where the kinetic energy of the fluid is dissipated due to the cross-sectional expansion (fourth Carnot diffuser). In this way, the locally increased pressure can be reduced in two stages (third and fourth Carnot diffuser).
  • the first opening 36, the second opening 38 and the damping chamber 40 have rounded edges 50 here. For the sake of clarity, only two edges 50 have been provided with a reference number in FIG. Here the first opening 36, the second opening 38 and the damping chamber 40 have no sharp edges.

Landscapes

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

Abstract

L'invention se réfère à une pompe (10) pour un véhicule, en particulier un véhicule automobile, destinée à transporter un fluide et à un véhicule, en particulier un véhicule automobile, comprenant une telle pompe (10). La pompe comprend un corps de pompe (12) comportant une chambre interne de pompe (14), une entrée (16) pour amener le fluide dans la chambre interne de pompe (14), et une sortie (18) pour refouler le fluide hors de la chambre interne de pompe (14), la pompe comprenant également une roue à aubes (22), la roue (22) comportant de multiples aubes de roue (24), et la roue à aubes (22) et/ou les aubes de roue (24) étant au moins partiellement agencée(s) à l'intérieur de la chambre interne de pompe (14). Le corps de pompe (12) comporte un dispositif d'amortissement (26) pour réduire une pression générée localement sur les extrémités radialement extérieures (28) des aubes de roue (24).
PCT/EP2022/066017 2021-06-16 2022-06-13 Pompe et véhicule comprenant une telle pompe WO2022263370A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202280043081.6A CN117501017A (zh) 2021-06-16 2022-06-13 泵和具有这样的泵的车辆

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021206139.7A DE102021206139A1 (de) 2021-06-16 2021-06-16 Pumpe und ein Fahrzeug mit einer solchen Pumpe
DE102021206139.7 2021-06-16

Publications (1)

Publication Number Publication Date
WO2022263370A1 true WO2022263370A1 (fr) 2022-12-22

Family

ID=82156440

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/066017 WO2022263370A1 (fr) 2021-06-16 2022-06-13 Pompe et véhicule comprenant une telle pompe

Country Status (3)

Country Link
CN (1) CN117501017A (fr)
DE (1) DE102021206139A1 (fr)
WO (1) WO2022263370A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20240060421A1 (en) * 2021-01-08 2024-02-22 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine housing for use in a turbocharger

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107965896A (zh) * 2017-12-26 2018-04-27 海信（广东）空调有限公司 蜗舌、风道装置及空调室内机
DE102023110184A1 (de) 2023-04-21 2024-10-24 Ebm-Papst St. Georgen Gmbh & Co. Kg Radialventilator mit zulaufender Zungengeometrie

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191214668A (en) * 1911-06-23 1912-11-14 Aegidius Elling Improvements in Turbo-pumps or Fans.
US4629394A (en) * 1983-07-25 1986-12-16 Chandler Evans Inc Centrifugal pump having low flow diffuser
US5286162A (en) * 1993-01-04 1994-02-15 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Method of reducing hydraulic instability
FR2780454A1 (fr) * 1998-06-29 1999-12-31 Valeo Climatisation Dispositif d'absorption de bruit pour groupe moto-ventilateur centrifuge
CN104929953B (zh) * 2015-06-23 2017-09-26 浙江工业大学 具有仿生结构的减振降噪离心泵

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006057823A1 (de) 2006-12-06 2008-06-12 Behr Gmbh & Co. Kg Schallgedämpftes, gasführendes Bauteil
DE102014206114A1 (de) 2014-04-01 2015-10-01 Mahle International Gmbh Gehäuse eines Radialgebläses
CN110439860A (zh) 2018-05-04 2019-11-12 宁波方太厨具有限公司 一种离心风机的蜗壳结构
CN110873077A (zh) 2018-08-29 2020-03-10 联想（新加坡）私人有限公司 风扇装置以及电子设备

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191214668A (en) * 1911-06-23 1912-11-14 Aegidius Elling Improvements in Turbo-pumps or Fans.
US4629394A (en) * 1983-07-25 1986-12-16 Chandler Evans Inc Centrifugal pump having low flow diffuser
US5286162A (en) * 1993-01-04 1994-02-15 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Method of reducing hydraulic instability
FR2780454A1 (fr) * 1998-06-29 1999-12-31 Valeo Climatisation Dispositif d'absorption de bruit pour groupe moto-ventilateur centrifuge
CN104929953B (zh) * 2015-06-23 2017-09-26 浙江工业大学 具有仿生结构的减振降噪离心泵

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20240060421A1 (en) * 2021-01-08 2024-02-22 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine housing for use in a turbocharger

Also Published As

Publication number Publication date
CN117501017A (zh) 2024-02-02
DE102021206139A1 (de) 2022-12-22

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