EP4285030A1 - Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine - Google Patents

Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine

Info

Publication number
EP4285030A1
EP4285030A1 EP22700777.0A EP22700777A EP4285030A1 EP 4285030 A1 EP4285030 A1 EP 4285030A1 EP 22700777 A EP22700777 A EP 22700777A EP 4285030 A1 EP4285030 A1 EP 4285030A1
Authority
EP
European Patent Office
Prior art keywords
radial
gap
flow machine
housing assembly
rotor
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.)
Pending
Application number
EP22700777.0A
Other languages
German (de)
English (en)
Inventor
Georg DICK
Benjamin Grothe
Theodor Hüser
Dominik NIESS
Thorsten WILLE-RIESS
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.)
Hella GmbH and Co KGaA
Original Assignee
Hella GmbH and Co KGaA
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 Hella GmbH and Co KGaA filed Critical Hella GmbH and Co KGaA
Publication of EP4285030A1 publication Critical patent/EP4285030A1/fr
Pending 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
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication 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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/98—Lubrication

Definitions

  • the invention relates to a radial-flow machine, in particular a radial-flow working machine, for example a radial pump, with cooling and lubrication by a medium flowing through the machine, the medium flowing from a high-pressure side to a low-pressure side of the radial-flow machine.
  • the rotor assembly comprises a rotor of an electric motor and an impeller
  • the motor includes, in addition to the rotor, a stator that is part of the housing assembly,
  • a distance is provided between the first area of the housing assembly and the first area of the rotor assembly, which forms a first gap, which is connected on one side to the high-pressure side and on another side to the low-pressure side of the radial flow machine, so that during operation the radial flow machine, a bypass flow of the medium flowing through the radial flow machine flows through the first gap and in the process dissipates heat from the rotor and/or the stator of the motor, • wherein the first bearing has a second gap provided between a first bearing part of the rotor assembly and a first bearing part of the housing assembly,
  • first gap is connected to the second gap on the low-pressure side or high-pressure side, so that during operation of the radial-flow machine, part of the medium flowing through the radial-flow machine flows through the second gap, thereby lubricating the bearing.
  • Such radial flow machines in particular such radial pumps, are known to the inventors. They have the advantage that the motor is cooled and the first bearing partially lubricated with the help of the bypass flow flowing through the first gap. If the secondary flow is then also routed through the second gap, complete lubrication of the first bearing is possible.
  • the secondary flow of the medium is guided from the first gap into the second gap, it passes through an area of transition from the first to the second gap.
  • the secondary flow can be deflected in this area.
  • Particles entrained by the bypass flow can settle and collect in the first bearing. This can arise, for example, because zones arise in the transition area between the first gap and the second gap, in which the flow speed of the medium is low.
  • the bypass flow can be reduced by deposited particles. This can negatively affect both the cooling of the motor and the lubrication of the first bearing. The settling of particles should therefore be avoided.
  • the invention was therefore based on the object of preventing particles from settling in the first bearing.
  • This object is achieved according to the invention in that bypass openings or bypass channels are provided in an area of the transition from the first gap to the second gap, which connect this area of the transition to the low-pressure side of the radial-flow machine, so that during operation of the radial-flow machine only part of the The medium flowing through the first gap also flows through the second gap.
  • the larger part of the secondary flow is preferably conducted through the bypass openings or bypass channels. This larger part of the secondary flow then takes the particles entrained in the secondary flow with it, so that they cannot settle in the first bearing.
  • connection of the bypass openings or bypass channels to the transition region is preferably designed in such a way that the part of the secondary flow guided through the bypass openings or bypass channels is diverted less often than in the prior art, so that fewer zones of low flow velocity can arise in the first bearing.
  • the bypass openings or bypass channels preferably have a cross section that offers a lower resistance to the part of the bypass flow than the second gap, so that the part of the bypass flow flowing through the bypass openings or bypass channels is larger than the part of the bypass flow flowing through the second gap.
  • each bypass opening or each bypass channel prefferably has a smallest cross-section and for a length and a width or a diameter of at least one of these smallest cross-sections to be greater than the distance between the first area of the housing assembly and the first area of the rotor assembly in the area of the second column.
  • the sum of the smallest cross sections of the bypass openings or bypass channels is greater than the smallest cross section of the second gap.
  • the first bearing part of the housing assembly can be formed by an annular groove.
  • the first bearing part of the rotor assembly can be formed by a first ring which dips into the annular groove and is part of the rotor assembly.
  • a part of the first gap can be formed between a radially outer boundary surface of the ring groove and a radially outer surface of the first ring.
  • the second gap can be formed between a radially inner boundary surface of the ring groove and a radially inner surface of the first ring.
  • the area of the transition from the first gap to the second gap can be formed between an axial boundary surface of the annular groove and an axial surface of the first ring.
  • the radially inner boundary surface of the annular groove can be a radially outer surface of a second ring, which is part of the housing assembly.
  • the bypass openings or bypass channels that connect the region of transition from the first gap to the second gap with the low-pressure side of the radial flow machine can be provided in the second ring.
  • the bypass openings or bypass channels can in particular be through-holes running radially in the second ring.
  • the first bearing can be a radial plain bearing.
  • a bearing bush of this slide bearing can be part of the rotor assembly.
  • FIG. 1 shows a longitudinal section through a radial pump according to the invention.
  • the radial pump P shown has a housing assembly 1 , a rotor assembly 2 and a control assembly 3 .
  • the housing assembly 1 has a first housing part 11, a second housing part 12, a cover 13, a cover 14 and a stator 15 of an electric motor 15, 25 of the radial pump P.
  • the first housing part 11 and the second housing part 12 enclose a first housing interior space in which the rotor assembly 2 is rotatably arranged via a first bearing and a second bearing.
  • the first housing interior has a first area which is surrounded by a first area 1a of the housing assembly 1 .
  • a first area 2a of the rotor assembly is arranged.
  • a second area 2b of the rotor assembly 2 is arranged in a second area of the housing interior, which is enclosed by a second area 1b of the housing assembly 1 .
  • the first area 1a of the housing assembly is formed by the stator 15 and a part of the first housing part 11, in which the stator 15 is arranged in an outer peripheral depression.
  • a first bearing part of the housing assembly 1 is formed, which forms part of the first bearing.
  • a first annular groove is formed in a wall of the first housing part 11 lying in the axial direction. Rolling bodies can be arranged in the first annular groove or other bearing elements can be arranged which facilitate rotation.
  • the first annular groove is provided between a radially inner wall of the first region 1a of the housing assembly and a ring 1111.
  • the second area 1b of the housing assembly is essentially formed by part of the second housing part 12 and only to a small extent by the first housing part 11.
  • a second bearing part of the housing assembly 1 is formed, which forms part of the second bearing.
  • a second annular groove is formed in a wall of the second housing part 12 lying in the axial direction. Rolling elements or other bearing elements which facilitate rotation can be arranged in the second annular groove.
  • the first and the second annular groove lie on opposite sides of the first housing interior.
  • the second housing part 12 has an inlet connection 121 on the low-pressure side and an outlet connection 122 on the high-pressure side, via which the medium conveyed by the radial pump P can flow into the first housing interior and out of the first housing interior.
  • the inlet connection 121 is connected to the first housing interior via an inlet channel 123 .
  • the first housing interior is connected to the drain connection 122 via drain channels 114 , 124 , 115 , 125 .
  • the drain channels 114 , 124 , 115 , 125 are formed by grooves 114 , 115 in the first housing part 11 and by grooves 124 , 125 in the second housing part 12 .
  • the rotor 2 has two components, namely an impeller 21 and a rotor 25 of the electric motor 15, 25.
  • the impeller 21 is a hollow shaft, the ends 212, 213 of which form rings which are rotatably arranged in the first and in the second annular groove of the housing assembly 1.
  • the first ring 212 of the impeller plunging into the first ring groove forms a first bearing part of the rotor assembly 2
  • the second ring 213 of the impeller plunging into the second ring groove forms a second bearing part of the rotor assembly 2. Together with the first bearing part and the second bearing part of the housing assembly these the first and second bearing.
  • the first area 2a of the rotor assembly has the rotor 25 of the motor 15,25. This is used in an outer peripheral depression of an impeller 21 .
  • the second area 2b of the rotor assembly 2 forms an impeller with impeller blades 211.
  • the inlet channel 123 opens into the center of this impeller between the impeller blades 211. It forms a low-pressure side of the radial pump P.
  • the inflowing medium is pressed into the discharge channels 114, 124, 115, 125 by the rotation of the rotor assembly 2 and thus of the impeller blades. This increases the pressure of the medium.
  • the outflow channels 114, 124, 115, 125 are arranged on a high-pressure side of the radial pump P. Between the first area 2a of the rotor assembly 2 including the first ring 212 and the first area 1a of the housing assembly 1 is between a radially outer surface of the first area 2a of the rotor assembly 2 and a radially inner surface of the first area 1a of the housing assembly 1 a first gap is provided which extends into the first annular groove. On the side opposite the first annular groove, the first gap is connected to the high-pressure side of the radial pump P, namely to at least one of the outflow channels 114, 124, 115, 125.
  • a second gap is formed between a radially inner surface of the first ring 212 and a radially inner boundary surface of the annular groove.
  • the radially inner limiting surface of the ring groove is a radially outer surface of the ring 111 which is part of the housing assembly and protrudes from the wall of the first housing part 11 lying in the axial direction.
  • the second gap is connected to the low-pressure side of the radial pump, namely the center between the impeller vanes 21 1 , via a cavity in the impeller.
  • a transition area U is provided between the first gap S1 and the second gap S2, which connects the two gaps S1, S2. This transition area U is formed between an axial boundary surface of the ring groove and an axial surface of the first ring 212 .
  • the transition area U is not only connected to the low-pressure side of the radial pump P via the second gap S2. Rather, bypass channels are provided in the ring 1 1 1 of the first housing part, which connect the transition region U via the interior of the impeller to the low-pressure side of the radial pump P.
  • the bypass channels have a larger cross section than the second gap S2.
  • the second housing interior which is enclosed by part of the second housing part 12, the cover 13 and the lid 14, the control assembly 3 is arranged.
  • the control assembly 3 has a printed circuit board 31 on which various electrical components 32 are arranged. These electrical components 32 and conductor tracks on the printed circuit board 31 form an electrical circuit with which the motor 15, 25 is controlled and supplied with power.
  • the centrifugal pump has a device connector, part 131 of which is an integral part of the cover 13 . Electrical contacts of the device plug are connected to the circuit.
  • a secondary flow is branched off from the pumped medium on the high-pressure side and is passed through the first gap S1. This secondary flow ensures cooling of the electric motor 15, 25.
  • the secondary flow flows through the transition area U. From the transition area U, a smaller part flows through the second gap and ensures lubrication in the first bearing there. A larger part of the secondary flow flows through the bypass openings past the second gap onto the low-pressure side. This larger part of the secondary flow entrains particles that are transported in the secondary flow and thereby prevents them from settling in the transition area U or in the second gap and thus leading to damage to the bearing.

Landscapes

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

Abstract

L'invention concerne une machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine, le milieu s'écoulant d'un côté haute pression vers un côté basse pression de la machine à écoulement continu radial, • avec un ensemble boîtier (1) et un ensemble rotor (2) qui est monté rotatif dans un espace intérieur de l'ensemble boîtier (1), • au moins un premier palier étant fourni pour le montage de l'ensemble rotor (2) dans l'ensemble boîtier (1), • l'ensemble rotor (2) comprenant un rotor (25) d'un moteur électrique (15, 25) et une turbine (21), • le moteur (15, 25) comprenant, en plus du rotor (25), un stator (15) qui fait partie de l'ensemble boîtier (1), • le rotor (25) du moteur (15, 25) étant agencé dans une première région (2a) de l'ensemble rotor (2), et le stator (15) étant agencé dans une première région (1a) de l'ensemble boîtier (1), • la première région (1a) de l'ensemble boîtier (1) entourant la première région (2a) de l'ensemble rotor (2).
EP22700777.0A 2021-01-29 2022-01-14 Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine Pending EP4285030A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021102149.9A DE102021102149A1 (de) 2021-01-29 2021-01-29 Radialströmungsmaschine mit Kühlung und Schmierung durch ein durch die Maschine fließendes Medium
PCT/EP2022/050727 WO2022161791A1 (fr) 2021-01-29 2022-01-14 Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine

Publications (1)

Publication Number Publication Date
EP4285030A1 true EP4285030A1 (fr) 2023-12-06

Family

ID=80035006

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22700777.0A Pending EP4285030A1 (fr) 2021-01-29 2022-01-14 Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine

Country Status (5)

Country Link
US (1) US20230366410A1 (fr)
EP (1) EP4285030A1 (fr)
CN (1) CN116583678A (fr)
DE (1) DE102021102149A1 (fr)
WO (1) WO2022161791A1 (fr)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3288073A (en) 1964-12-01 1966-11-29 Pall Corp Canned pump having reduced hydraulic thrust
DE2618593A1 (de) * 1976-04-28 1977-11-10 Hermetic Pumpen Gmbh Spaltrohrmotor-pumpenaggregat
EP0268015B1 (fr) 1986-11-20 1992-07-01 HERMETIC-PUMPEN GmbH Pompe avec moteur électrique à rotor noyé ou avec accouplement magnétique
DE3715484A1 (de) 1987-05-09 1988-11-17 Klaus Union Armaturen Magnetischer pumpenantrieb
AT502566B1 (de) * 2005-10-13 2007-08-15 Tcg Unitech Systemtechnik Gmbh Kühlmittelpumpe
KR101250969B1 (ko) 2012-02-20 2013-04-05 캄텍주식회사 차량용 워터펌프
DE102016100535B4 (de) * 2015-12-18 2021-11-18 Bühler Motor GmbH Bürstenloser Elektromotor für eine Pumpe, Pumpe mit einem solchen Elektromotor und Kühlverfahren
JP6878255B2 (ja) * 2017-11-20 2021-05-26 愛三工業株式会社 遠心ポンプ

Also Published As

Publication number Publication date
CN116583678A (zh) 2023-08-11
US20230366410A1 (en) 2023-11-16
DE102021102149A1 (de) 2022-08-04
WO2022161791A1 (fr) 2022-08-04

Similar Documents

Publication Publication Date Title
EP2273124B1 (fr) Pompe centrifuge et procédé d'équilibrage de la poussée axiale dans une pompe centrifuge
DE3932228A1 (de) Turbovakuumpumpe
DE60111879T2 (de) Inline-Pumpe
EP0248104B1 (fr) Pompe rotative
DE10303097A1 (de) Rotor-/Stator-Homogenisierapparat
DE102009029716A1 (de) Elektromotor
EP0170175A2 (fr) Pompe régénérative avec équilibrage des forces
DE3019633A1 (de) Oeldichtungsanordnung
EP1936200B1 (fr) Pompe à vide à palettes étanchéifiée à l'aide de lubrifiants
EP2516868B1 (fr) Turbine à eau ou pompe à eau ou autre machine hydraulique
DE3800336A1 (de) Dichtungsfreie pumpe
DE102019206205B3 (de) Gleitringdichtungsanordnung, insbesondere für heiße Medien, sowie Pumpenanordnung
DE102020104663A1 (de) Elektrische antriebsmaschine zum antreiben eines kraftfahrzeugs
DE2158518C3 (de) Horizontale mehrstufige Zentrifugalpumpe
WO2020074318A1 (fr) Pompe conçue en particulier pour un circuit de liquide dans un véhicule
DE69716552T2 (de) Dichtung/lagervorrichtung
EP4285030A1 (fr) Machine à flux continu radial avec refroidissement et lubrification au moyen d'un milieu qui s'écoule à travers la machine
EP1292774A1 (fr) Pompe a canal lateral
DE3526517C2 (fr)
DE102019217510A1 (de) Rotor, Elektromaschine und Kraftfahrzeug
DE3313950C2 (fr)
DE102016225196B4 (de) Elektromotorische Ölpumpe
DE69419864T2 (de) Fluidmaschine mit Induktionsmotor
EP2165085B1 (fr) Pompe pour un appareil electromenager
EP0584106B1 (fr) Pompe a anneau liquide a flux multiples

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20230810

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)