EP0984143A2 - Pompe rotative - Google Patents

Pompe rotative Download PDF

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Publication number
EP0984143A2
EP0984143A2 EP99306909A EP99306909A EP0984143A2 EP 0984143 A2 EP0984143 A2 EP 0984143A2 EP 99306909 A EP99306909 A EP 99306909A EP 99306909 A EP99306909 A EP 99306909A EP 0984143 A2 EP0984143 A2 EP 0984143A2
Authority
EP
European Patent Office
Prior art keywords
pump
impeller
cavity
engine
coolant
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Withdrawn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
EP99306909A
Other languages
German (de)
English (en)
Other versions
EP0984143A3 (fr
Inventor
Stephen Walker Tebby
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.)
Concentric Pumps Ltd
Original Assignee
Concentric Pumps Ltd
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 Concentric Pumps Ltd filed Critical Concentric Pumps Ltd
Publication of EP0984143A2 publication Critical patent/EP0984143A2/fr
Publication of EP0984143A3 publication Critical patent/EP0984143A3/fr
Withdrawn legal-status Critical Current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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant 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
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—Details of the magnetic circuit
    • 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
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • 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

Definitions

  • This invention relates to coolant pumps for internal combustion engines.
  • An object of the invention is therefore to mitigate or overcome at least some of these problems.
  • a coolant pump for an I.C. engine comprises a pump cavity housing an impeller rotatable about an axis, the impeller axis being located coaxially with the rotational axis of the crankshaft of the engine.
  • Such a location simplifies drive which may be either direct or geared to the crankshaft without requiring the conventional belt drive as is necessary when the pump axis is parallel to the crankshaft but at a remote location.
  • crankshaft mounted drive pulley for a belt drive system, and drive the coolant pump from that pulley (but not from that belt).
  • the pump is driven by magnetic coupling using a first set of driving magnets in a face of the pulley and a second set of driven magnets, or torque ring, in the corresponding and adjacent impeller face, with a containment shell located between the two sets.
  • the purpose of the shell is to contain the coolant within the pump but permit magnetic flux to couple two sets.
  • the crankshaft location reduces power requirement because of the more efficient coolant flow paths possible from what is essentially a low level location relative to the cooled areas of the engine. Power consumption may be reduced because of reduced cavitation in such a location.
  • the pump can be a regenerative or peripheral type, or a centrifugal type.
  • a coolant pump for an I.C. engine is characterised by the use of a regenerative impeller located in a peripherally discontinuous pump cavity.
  • the impeller may comprise a disc formed with radial flutes extending to its periphery and on both faces of the disc, which fluted marginal zone lies in the pump cavity.
  • the cavity formed between two co-operating components of the pump body provides a substantial clearance about the fluted marginal zone only around the major portion of the impeller disc, typically 330° or thereabouts, but provides a suitable running clearance over the face areas of the disc radially inwardly of the fluted marginal zone and over the remaining 30° or thereabouts of the marginal zone.
  • the cavity connects to inlet and outlet ports at opposite ends of the substantial clearance portion, that is to say at opposite sides of the minimum clearance portion at the periphery.
  • Such a regenerative impeller system may give a pump head which is substantially higher than available with a conventional centrifugal action coolant pump having central inlet and tangential discharge thus obviating the need to rotate the impeller at a speed significantly greater than the crankshaft speed.
  • a magnetic coupling driven regenerative impeller coolant pump has a balance port extending between a generally peripherally extending pumping cavity and the radially inward zone within the pump to encourage pressurised flow of coolant through the pump as lubricant for bearings journalling the pump impeller.
  • a further aspect of the invention provides a coolant pump for an I.C. engine comprising a pump body housing a cavity and an impeller within the cavity, wherein part of the body is formed by the timing case cover adjacent the crankshaft.
  • the pump body is in part integral with the timing case cover.
  • Another aspect of the invention provides a pump for an internal combustion engine having a magnetically driven impeller, which impeller is rotatable peripherally about the crankshaft of the engine.
  • the invention also provides that any one of the features of the invention described above or in the following description, may be combined with any other feature, and/or aspect of the invention.
  • the pump body comprises first component 10 which may be a portion of a timing case mounted on the front end of the engine block and surrounding the crankshaft.
  • the centre-line or rotational axis of the crankshaft is indicated by the line 12.
  • the pump body is completed by a second component or cover 14 which extends over an annular zone towards the outer periphery of the part 10 but not over the zone closer to the axis 12.
  • the parts 10, 14 are, preferably, sealed permanently together along the mating faces indicated by the arrow 16 and define a pumping chamber or cavity 18 therebetween which extends over a substantial portion of the circumference of the parts 10, 14.
  • cavity 18 is indicated in part by the broken lines extending in an arc up to and terminating at port 20 which is formed in a stub tube 22 as also shown in Figure 3.
  • a similar port 24 in a second stub tube 26 is located at the opposite end (clockwise from the first end in this example) of the pump cavity 18.
  • the area between the two ports 20, 24 is not provided with a cavity 18 but is closed off by a web 19 apertured to provide only a close clearance around the periphery of the impeller.
  • the impeller comprises a generally disc-like part 30, see Figure 3, provided with a complete ring of regularly pitched flutes 32 on each of its faces at the outer marginal zone of the disc.
  • the impeller has a small clearance 34 between one face and the adjacent inside face of the pump body part 10, a small clearance 36 between the opposite face of the disc and the adjacent face of the second body part 14 and again a small clearance 38 between the rim of the disc and the web portion 19 which separates the two ports.
  • the impeller is carried on a hub sleeve 40 associated with journal bearing 42 and carries a series of equispaced driven magnet elements 44 in the face adjacent the drive pulley which is described next.
  • the drive pulley 46 is shown engaged with a pair of V belts 48 for the purpose of driving further engine auxiliaries and has a hub 50 in driving association with the crankshaft and located radially inwardly of the pump body part 10. An oil seal 52 is located therebetween.
  • the pulley carries driving magnets 54 which are suitably located to transmit driving torque to driven magnets 44 for example at the same radial location from the axis 12 as the driven magnets 44.
  • the pump further comprises containment shell 60 which in the illustrated embodiment has a tubular portion 62 trapped between a journal bearing 42 and a corresponding portion of the pump body at 64.
  • the shell 60 extends generally radially of axis 12 to contain the thrust bearing 72 and thereafter be appropriately positioned between magnets 44 and 54.
  • the shell 60 essentially extends generally radially of the axis 12 between the opposed magnets 44, 54 and is, in this instance, engaged and retained by the pump body part 14 in the area of the reference numeral 66.
  • a further bearing, acting as a thrust bearing indicated by the reference numeral 72 is axially trapped between the containment shell 60 and the journal bearing 42.
  • the containment shell 60 may be held in place axially by a thrust washer 74 which may possibly be a Circlip (RTM) or equivalent.
  • a balance port 70 is provided extending generally radially between the main pump cavity 18 and interior of the pump. The angular location of this in the present embodiment is seen in Figure 1, close to the port 20.
  • port 20 is the lower pressure inlet port and higher pressure, near the outlet port 24, causes coolant to leak internally, via clearance 34, through to the bearings 40, 42, and 72, and into a balance chamber 75.
  • Flow of coolant, in this instance acting as lubricant, back through to cavity 18 in the vicinity of lower pressure port 20 is mainly through balance port 70 but also through the clearance 36.
  • the described pump differs from the conventional coolant pump in its location, that is at crankshaft level instead of being at the top of the engine. It also differs in its type being a regenerative pump rather than a centrifugal pump. It further differs in being driven by the magnetic coupling action, and again in having a pressurised coolant flow about and through the bearing faces inside the pump.
  • the invention resides in any one of these features, in any combination of them, or in the constructional details which make the feature(s) possible.
  • the thrust bearing 72 is located between the part 10 and the journal bearing 42. Further, it is possible to locate the port 70 by way of a channel formed in the part 10 instead of a channel formed in the part 14.
  • the impeller may be a centrifugal type, rather than regenerative or peripheral type, preferably with a hub diameter greater than the largest diameter of the containment shell 66.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP99306909A 1998-09-03 1999-08-31 Pompe rotative Withdrawn EP0984143A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB9819261.0A GB9819261D0 (en) 1998-09-03 1998-09-03 Improvements to rotary pumps
GB9819261 1998-09-03

Publications (2)

Publication Number Publication Date
EP0984143A2 true EP0984143A2 (fr) 2000-03-08
EP0984143A3 EP0984143A3 (fr) 2001-01-10

Family

ID=10838315

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99306909A Withdrawn EP0984143A3 (fr) 1998-09-03 1999-08-31 Pompe rotative

Country Status (12)

Country Link
EP (1) EP0984143A3 (fr)
JP (1) JP2000080919A (fr)
KR (1) KR20000022854A (fr)
CN (1) CN1246580A (fr)
AU (1) AU4484899A (fr)
BR (1) BR9904041A (fr)
CA (1) CA2281342A1 (fr)
GB (2) GB9819261D0 (fr)
ID (1) ID25731A (fr)
NO (1) NO994269L (fr)
TW (1) TW429285B (fr)
ZA (1) ZA995664B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006058607A1 (fr) * 2004-12-04 2006-06-08 Brinkmann Pumpen Pompe pour liquides sous pression positive
WO2008019815A1 (fr) * 2006-08-17 2008-02-21 Busch Produktions Gmbh Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec
WO2021121798A1 (fr) * 2019-12-18 2021-06-24 Robert Bosch Gmbh Compresseur à canal latéral pour un système de pile à combustible permettant de transporter et/ou de comprimer un gaz

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2315896C1 (ru) * 2006-06-14 2008-01-27 Юлия Алексеевна Щепочкина Устройство для напорного перемещения газа или жидкости
DE102011015784A1 (de) * 2010-08-12 2012-02-16 Ziehl-Abegg Ag Ventilator
CN110513306B (zh) * 2019-08-02 2022-06-03 烟台东德氢能技术有限公司 一种具有破冰功能的氢循环泵

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB856616A (en) * 1956-03-12 1960-12-21 Ferguson Res Ltd Harry Improvements in internal combustion engines
US3720372A (en) * 1971-12-09 1973-03-13 Gen Motors Corp Means for rapidly heating interior of a motor vehicle
IT1164933B (it) * 1979-02-08 1987-04-15 Aspera Spa Motopompa
JPS5885393A (ja) * 1981-11-13 1983-05-21 Hitachi Ltd 立軸ポンプの軸受潤滑装置
DE3534507C2 (de) * 1984-10-17 1986-10-16 AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH, Prof. Dr.Dr.h.c. Hans List, Graz Brennkraftmaschine
JPS62197624A (ja) * 1986-02-26 1987-09-01 Honda Motor Co Ltd 水冷式内燃機関における水ポンプ装置
IT1224053B (it) * 1988-12-30 1990-09-26 Fiat Auto Spa Motore a combustione interna particolarmente per autoveicoli
JPH07111146B2 (ja) * 1989-02-08 1995-11-29 日産自動車株式会社 内燃機関のチェーンカバー装置
US5082428A (en) * 1990-08-16 1992-01-21 Oklejas Robert A Centrifugal pump
DE4106497A1 (de) * 1991-03-01 1992-09-03 Gerhard O Wirges Stromerzeuger
JP3039697B2 (ja) * 1991-03-08 2000-05-08 富士重工業株式会社 小型水冷エンジンのウォータポンプ取付構造及びウォータポンプ駆動方法
RU2083853C1 (ru) * 1993-03-26 1997-07-10 Акционерное общество открытого типа "Ирбитский мотоциклетный завод" Насос системы жидкостного охлаждения двигателя
DE4404791C1 (de) * 1994-02-08 1995-03-30 Mannesmann Ag Baueinheit aus einem Verbrennungsmotor und einem elektrischen Generator
DE19641450B4 (de) * 1996-10-08 2007-08-02 Voith Turbo Gmbh & Co. Kg Antriebseinheit, insbesondere für ein Kraftfahrzeug
DE19641451A1 (de) * 1996-10-08 1997-03-20 Voith Turbo Kg Antriebseinheit, insbesondere für ein Kraftfahrzeug

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006058607A1 (fr) * 2004-12-04 2006-06-08 Brinkmann Pumpen Pompe pour liquides sous pression positive
WO2008019815A1 (fr) * 2006-08-17 2008-02-21 Busch Produktions Gmbh Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec
WO2021121798A1 (fr) * 2019-12-18 2021-06-24 Robert Bosch Gmbh Compresseur à canal latéral pour un système de pile à combustible permettant de transporter et/ou de comprimer un gaz

Also Published As

Publication number Publication date
NO994269L (no) 2000-03-06
CN1246580A (zh) 2000-03-08
AU4484899A (en) 2000-03-16
ZA995664B (en) 2000-04-04
GB9920361D0 (en) 1999-11-03
TW429285B (en) 2001-04-11
BR9904041A (pt) 2000-09-19
NO994269D0 (no) 1999-09-02
JP2000080919A (ja) 2000-03-21
ID25731A (id) 2000-11-02
GB9819261D0 (en) 1998-10-28
GB2341205A (en) 2000-03-08
CA2281342A1 (fr) 2000-03-03
EP0984143A3 (fr) 2001-01-10
KR20000022854A (ko) 2000-04-25

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