EP0071807A2 - Système de refroidissement à liquide de moteur avec pompe rotative - Google Patents

Système de refroidissement à liquide de moteur avec pompe rotative Download PDF

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Publication number
EP0071807A2
EP0071807A2 EP82106465A EP82106465A EP0071807A2 EP 0071807 A2 EP0071807 A2 EP 0071807A2 EP 82106465 A EP82106465 A EP 82106465A EP 82106465 A EP82106465 A EP 82106465A EP 0071807 A2 EP0071807 A2 EP 0071807A2
Authority
EP
European Patent Office
Prior art keywords
liquid
pump
cooling
impeller
blades
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Withdrawn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
EP82106465A
Other languages
German (de)
English (en)
Other versions
EP0071807A3 (fr
Inventor
Herbert Joseph Hauser, Jr.
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP0071807A2 publication Critical patent/EP0071807A2/fr
Publication of EP0071807A3 publication Critical patent/EP0071807A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • 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
    • 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
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F04D13/14—Combinations of two or more pumps the pumps being all of centrifugal type
    • 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
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/187—Arrangements or mounting of liquid-to-air heat-exchangers arranged in series

Definitions

  • the liquid cooling explained at the outset is intended in particular for internal combustion engines, which may be vehicle engines or other machines.
  • a high temperature coolant circuit is provided for cooling the vehicle engine.
  • This coolant circuit comprises a machine cooling water jacket, a circulation pump and a radiator.
  • Various embodiments of such cooling systems are described in U.S. Patents 2,760,468, 3,080,857 and 3,425,400.
  • an auxiliary coolant circuit of low temperature is additionally provided in order to cool the air drawn in by the machine and - if necessary - the lubricating oil.
  • Such an auxiliary coolant circuit includes an air-water heat exchanger, a circulation pump, a radiator and, if necessary, an oil-water heat exchanger (see e.g. U.S. Patent 3,439,657). So far, all dual-circuit cooling systems have required a pair of liquid pumps, primarily because the two coolant circuits operate at different temperatures and different flow rates.
  • the invention is therefore based on the object of improving the liquid cooling described at the outset with regard to its pump system or of developing a pump system which is particularly suitable for such a liquid cooling.
  • the pump system consists of a single pump, the housing of which together with an impeller rotating in this housing forms a first and a second liquid chamber, which are independent of one another.
  • This liquid cooling is particularly intended for gasoline or diesel internal combustion engines in which the above-mentioned first cooling device consists of a cooling water jacket enclosing the engine.
  • the second cooling device can be an air-liquid intercooler.
  • the pump according to the invention is able to circulate two separate and mutually independent coolant flows through the two coolant circuits, which are expediently designed to be closed, the amount of coolant pumped in each case in the two coolant circuits being the same, but also different.
  • the impeller can have a plurality of blades on two opposite sides, which drive the cooling liquid through the two liquid chambers.
  • the blades can be curved on one side of the impeller, while the blades on the opposite side run radially.
  • the first blade set works as a centrifugal pump, while the other blade set works as a turbine pump.
  • a centrifugal pump of the type described above can be found in US Pat. No. 2,760,468.
  • the two sets of blades of the impeller rotate in a common liquid chamber, to which separate inlets for the two coolant flows, but only a common outlet for the coolant, are connected. It is with this pump therefore not possible to apply two independent coolant circuits of different temperatures and / or flow rates at the same time.
  • the centrifugal pump according to the invention differs from this known embodiment essentially in that the impeller with its disk-shaped wall divides the liquid chamber into separate first and second, independent liquid chambers to which a first and a second outlet for the cooling liquid are connected.
  • the disk-shaped wall can be provided with a peripheral seal which, together with the pump housing, separates the two annular liquid chambers from one another.
  • the liquid cooling according to the invention therefore only requires a single pump for two completely independently controlled coolant circuits and as a result has a simpler and less expensive structure. Due to the pump according to the invention, the coolant flows in the two coolant circuits can have different temperatures and / or flow rates. In addition, the new pump can deliver different flow rates at the same time.
  • a two-circuit cooling system 10 is connected to an internal combustion engine 12.
  • the latter has a plurality of cylinders 14 in an engine block 16, within which a cooling water jacket enclosing all cylinders 14 is arranged.
  • the cooling system 10 comprises two separate and independent coolant circuits in which a coolant circulates.
  • the first coolant circuit comprises a radiator 18 which is connected via a line 20 to an inlet 21 which leads to a liquid pump 22.
  • the coolant leaves the pump 22 via an outlet 23 and is passed via a line 24 into the cooling water jacket of the engine block 16.
  • the coolant of a thermostat 26 passes via a return line 28 back into the radiator 18.
  • a this radiator 18 immediate bypass 3 0 directs the cooling medium through the inlet 21 22 to the pump
  • This bypass 30 is then turned on when the Thermostat 26 a coolant prevents flow through the radiator 18, as is the case, for example, with a cold start.
  • a second coolant circuit is useful for engines 12 with an exhaust gas turbocharger 34.
  • the latter serves to increase the amount of air available for combustion in the chambers of the engine 12. By cooling the intake air, a denser amount of air is available for combustion.
  • the exhaust gases of the engine 12 driving the exhaust gas turbocharger 34 are passed through an exhaust gas manifold 36 against a turbine rotor 38 which is seated on a shaft 40 and, by its rotation, drives a compression wheel 42 which is seated on the same shaft 40.
  • the exhaust gases exiting into the atmosphere at the exhaust 44 drive the compressor wheel 42, which draws in and compresses fresh atmospheric air into an intake line 46.
  • the second coolant circuit now cools the air coming from the exhaust gas turbocharger 34 before it enters the combustion chambers of the cylinders 14.
  • This second coolant circuit comprises a radiator 48, which is connected via a line 50 to a heat exchanger 52 (see FIG. 1), which is normally referred to as an intercooler and causes a heat exchange from the air to a cooling liquid without these two media being mixed together .
  • the coolant thus heated leaves the heat exchanger 52 and reaches a second side of the pump 22 via a line 54 via an inlet 56. After flowing through the pump 22, the coolant emerges at a second outlet 58 and is returned to the radiator via a return line 60 48 fed.
  • An oil cooler not shown in the drawing, is sometimes provided for cooling the lubricating oil for the machine 12.
  • the lubricating oil cooler is preferably switched into line 54 or 58.
  • the second coolant circuit also serve to cool the lubricating oil.
  • the coolant pump 22 consists of a housing 62 in which an impeller 64 rotates. The latter is pressed onto a drive shaft 66, which carries a pulley 67, which e.g. is driven by a crankshaft.
  • the impeller 64 forms, together with an intermediate wall 68 provided in the housing 62, which can be formed separately or in one piece with the housing 62, a first and a second liquid chamber 70, 72.
  • the first liquid chamber 70 forms part of the first coolant circuit and communicates with the inlet 21 and the outlet 23, while the second liquid chamber 72 forms part of the second coolant circuit and communicates with the second inlet 56 and the second outlet 58.
  • Both liquid chambers 70, 72 are designed completely separately and independently of one another in an annular manner, the only liquid exchange between the two chambers being able to take place via a leak along a seal 73 which is arranged on the circumference of the impeller 64.
  • the size of the two liquid chambers 70, 72 can be the same and / or different, but preferably the first liquid chamber 70, which is connected to the cooling water jacket of the machine 12, is larger than the second liquid chamber 72, which is connected to the air-liquid heat exchanger 52 communicates.
  • the disk-shaped impeller 64 has a central axial opening 74 for mounting the shaft 66. Furthermore, the impeller 64 has a multiplicity of relatively large curved blades 76 which are seated on one side of a disk-shaped partition wall 78, the opposite side of which carries a large number of radial blades 80.
  • the curved blades 76 convey the coolant, which is supplied approximately centrally axially, through the first liquid chamber 70, while the radial blades 80 promote the coolant supplied approximately on the outer circumference of the impeller through the second liquid chamber 72.
  • the inflowing coolant is expediently supplied perpendicular to the central axis of the impeller 64.
  • the partition 78 of the impeller 64 provided on its circumference with the seal 73 is aligned with the intermediate wall 68 and prevents any liquid exchange between the two liquid chambers 70, 72.
  • the seal 73 could alternatively also be attached to the intermediate wall 68.
  • the curved blades 76 together with the first liquid chamber 70 form a centrifugal pump with a high delivery volume and low delivery pressure
  • the radial blades 80 in connection with the second liquid chamber 72 form a turbine pump with a low delivery volume but high delivery pressure.
  • This blade design is not absolutely necessary, but is expedient since the cooling water jacket of the machine 12 has relatively large flow cross sections, compared to which the flow cross sections of the heat exchanger 52 are comparatively narrow. Therefore, the heat exchanger 52 requires a higher pressure for the coolant flowing through than the water jacket for the coolant flowing through it.
  • first and second liquid chambers 70, 72 can be of the same size, and that the blades of the impeller 64 can have a similar or different design depending on the use of the pump 22.
  • the blades on both sides of the Impeller 64 be curved.
  • the liquid cooling 10 and the pump 22 of the invention theoretically operate as follows in a multi-cylinder diesel equipped with an exhaust gas turbocharger that has been brought to its normal operating temperature:
  • the exhaust gas turbocharger 34 sucks Air with a temperature of about 38 ° C and a pressure of about 1 kgjcm 2 from the atmosphere via the suction line 46. Due to the compression of the air, the temperature rises to approximately 177 ° C. and the pressure to approximately 1.76 kg / cm 2 before the air flows through the air-liquid intercooler 52.
  • the coolant circulating in the second coolant circuit has a temperature of approximately 60 ° C.
  • the coolant in the first coolant circuit leaves the radiator 18 at approximately 93 ° C. and a pressure of approximately 1.05 kg / cm 2 and is pumped through the cooling water jacket of the machine 12, where the temperature of the coolant rises to approximately 99 ° C. .
  • the coolants of both coolant circuits are returned to the radiators 18 and 48 assigned to them, where the coolant is cooled down by the passing air before it circulates again through the system 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Supercharger (AREA)
EP82106465A 1981-08-03 1982-07-17 Système de refroidissement à liquide de moteur avec pompe rotative Withdrawn EP0071807A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/289,543 US4385594A (en) 1981-08-03 1981-08-03 Two-circuit cooling system and pump for an engine
US289543 1981-08-03

Publications (2)

Publication Number Publication Date
EP0071807A2 true EP0071807A2 (fr) 1983-02-16
EP0071807A3 EP0071807A3 (fr) 1983-08-31

Family

ID=23111989

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82106465A Withdrawn EP0071807A3 (fr) 1981-08-03 1982-07-17 Système de refroidissement à liquide de moteur avec pompe rotative

Country Status (7)

Country Link
US (1) US4385594A (fr)
EP (1) EP0071807A3 (fr)
JP (1) JPS5827810A (fr)
BR (1) BR8204437A (fr)
CA (1) CA1179907A (fr)
ES (1) ES514653A0 (fr)
ZA (1) ZA825547B (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4004936A1 (de) * 1989-02-17 1990-08-23 Aisin Seiki Brennkraftmaschine mit einem wassergekuehlten zwischenkuehler
DE19719199A1 (de) * 1996-10-26 1998-04-30 Knecht Filterwerke Gmbh Kühlmittelpumpe, insbesondere für ein Kraftfahrzeug
US5779008A (en) * 1994-10-12 1998-07-14 Voith Turbo Gmbh & Co. Kg Drive unit with engine and retarder
DE19705631A1 (de) * 1997-02-14 1998-08-20 Audi Ag Zusatzkühleinrichtung für Verbrennungsmotoren
DE102010010593A1 (de) 2010-03-08 2011-09-08 Audi Ag Kreiselpumpe
EP2971786A4 (fr) * 2013-03-13 2016-10-19 Ghsp Inc Conception à deux pompes possédant une surface d'interface coplanaire
EP3456981A1 (fr) * 2017-09-13 2019-03-20 MAN Truck & Bus AG Pompe à fluide de refroidissement pour un circuit de fluide de refroidissement d'un moteur à combustion interne
DE102018203931B3 (de) 2018-03-15 2019-06-06 Audi Ag Antriebseinrichtung mit in einem gemeinsamen Gehäuse angeordneten Kühlmittelpumpen sowie Verfahren zum Betreiben einer solchen Antriebseinrichtung
DE102018220150A1 (de) * 2018-11-23 2020-05-28 Mahle International Gmbh Pumpenmodul für Kühlmittel

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US4488055A (en) * 1982-03-10 1984-12-11 James Toyama Fluid pipe generator
DE3407521C1 (de) * 1984-03-01 1985-03-14 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Fluessigkeitskuehlsystem fuer eine aufgeladene Brennkraftmaschine
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JPH0734231Y2 (ja) * 1988-03-23 1995-08-02 アイシン精機株式会社 ２系統冷却ウオータポンプ
US4967716A (en) * 1989-04-27 1990-11-06 Deere & Company Internal combustion engine with integral intercooler
US5188065A (en) * 1992-03-05 1993-02-23 Richard Lyndhurst Water pump
DE10018046A1 (de) * 2000-04-12 2001-11-29 Volkswagen Ag Wärmetauscher mit einem einen Gehäusedeckel aufweisenden Gehäuse
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KR20020095884A (ko) * 2001-06-18 2002-12-28 현대자동차주식회사 인터쿨러의 흡입공기 냉각장치
US6561169B2 (en) * 2001-07-23 2003-05-13 Ford Motor Company Charge air management system for automotive engine
US6779515B2 (en) * 2002-08-01 2004-08-24 Ford Global Technologies, Llc Charge air conditioning system with integral intercooling
US6883314B2 (en) * 2002-08-01 2005-04-26 Caterpillar Inc. Cooling of engine combustion air
KR20040022527A (ko) * 2002-09-09 2004-03-16 현대자동차주식회사 워터펌프를 이용한 인터쿨러의 냉각장치
US6868809B1 (en) 2004-05-27 2005-03-22 Borgwarner Inc. Coolant motor fan drive
US6976479B1 (en) * 2004-08-10 2005-12-20 Electro-Motive Diesel, Inc. Engine with optimized engine charge air-cooling system
US7287493B2 (en) * 2004-11-10 2007-10-30 Buck Supply Co., Inc. Internal combustion engine with hybrid cooling system
US7287494B2 (en) * 2004-11-10 2007-10-30 Buck Supply Co., Inc. Multicylinder internal combustion engine with individual cylinder assemblies and modular cylinder carrier
US7543558B2 (en) 2004-11-10 2009-06-09 Buck Diesel Engines, Inc. Multicylinder internal combustion engine with individual cylinder assemblies
US7261068B1 (en) * 2006-02-16 2007-08-28 Deere & Company Vehicular thermostatically-controlled dual-circuit cooling system and associated method
JP2007224786A (ja) * 2006-02-22 2007-09-06 Komatsu Ltd 排気ガス再循環装置
DE102007005391A1 (de) * 2007-02-03 2008-08-07 Behr Gmbh & Co. Kg Kühleranordnung für einen Antriebsstrang eines Kraftfahrzeugs
CN101617110B (zh) * 2007-02-20 2014-06-25 摩丁制造公司 热交换器系统及其操作方法
US20090078220A1 (en) * 2007-09-25 2009-03-26 Ford Global Technologies, Llc Cooling System with Isolated Cooling Circuits
US7958854B2 (en) * 2008-05-09 2011-06-14 Caterpillar Inc. Multi-stage cooling system
US8109242B2 (en) * 2008-10-17 2012-02-07 Caterpillar Inc. Multi-thermostat engine cooling system
US8316814B2 (en) 2009-06-29 2012-11-27 Buck Kenneth M Toploading internal combustion engine
US8579060B2 (en) * 2010-01-13 2013-11-12 Demmer Corporation Double heat exchanger radiator assembly
CN102080672A (zh) * 2010-09-18 2011-06-01 中国兵器工业集团第七○研究所 一种离心式冷却水泵
US9039385B2 (en) 2011-11-28 2015-05-26 Ford Global Technologies, Llc Jet pump assembly
DE102012223069A1 (de) * 2012-12-13 2014-06-18 Bayerische Motoren Werke Aktiengesellschaft Kühlmittelkreislauf für eine Brennkraftmaschine
US9739194B2 (en) * 2013-03-04 2017-08-22 Ford Global Technologies, Llc Charge-air intercooler system with integrated heating device
US10495025B2 (en) * 2013-03-15 2019-12-03 Conleymax Inc. Flameless combo heater
US9982585B2 (en) * 2013-03-15 2018-05-29 Conleymax Inc. Flameless fluid heater
USD737332S1 (en) 2014-04-17 2015-08-25 Callaway Cars, Inc. Induction housing
US10595706B2 (en) * 2014-07-23 2020-03-24 Whirlpool Corporation Dishwasher with air system
EP3362657B1 (fr) * 2015-10-12 2019-12-18 Angelo Miretti Moteur ayant un dispositif de protection contre les explosions
JP7181443B2 (ja) * 2018-02-14 2022-12-01 日本電産サンキョー株式会社 冷却装置
DE102020130488A1 (de) * 2019-12-16 2021-06-17 ECO Holding 1 GmbH Vorrichtung zur Handhabung von Fluid innerhalb eines zumindest teilweise elektrisch angetriebenen Fahrzeugs
DE102020214000B4 (de) * 2020-11-06 2022-08-04 Thermo Electron Led Gmbh Zentrifuge mit elastokalorischer kühlung und verfahren zur kühlung einer zentrifuge
CN113140758A (zh) * 2021-04-09 2021-07-20 上海电气集团股份有限公司 一种自旋式氢气回流装置

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4004936A1 (de) * 1989-02-17 1990-08-23 Aisin Seiki Brennkraftmaschine mit einem wassergekuehlten zwischenkuehler
US5779008A (en) * 1994-10-12 1998-07-14 Voith Turbo Gmbh & Co. Kg Drive unit with engine and retarder
DE19719199A1 (de) * 1996-10-26 1998-04-30 Knecht Filterwerke Gmbh Kühlmittelpumpe, insbesondere für ein Kraftfahrzeug
DE19705631A1 (de) * 1997-02-14 1998-08-20 Audi Ag Zusatzkühleinrichtung für Verbrennungsmotoren
DE19705631B4 (de) * 1997-02-14 2010-07-22 Audi Ag Zusatzkühleinrichtung für Verbrennungsmotoren
DE102010010593A1 (de) 2010-03-08 2011-09-08 Audi Ag Kreiselpumpe
DE102010010593B4 (de) * 2010-03-08 2018-02-08 Audi Ag Kreiselpumpe
EP2971786A4 (fr) * 2013-03-13 2016-10-19 Ghsp Inc Conception à deux pompes possédant une surface d'interface coplanaire
US9752590B2 (en) 2013-03-13 2017-09-05 Ghsp, Inc. Two pump design with coplanar interface surface
EP3456981A1 (fr) * 2017-09-13 2019-03-20 MAN Truck & Bus AG Pompe à fluide de refroidissement pour un circuit de fluide de refroidissement d'un moteur à combustion interne
DE102018203931B3 (de) 2018-03-15 2019-06-06 Audi Ag Antriebseinrichtung mit in einem gemeinsamen Gehäuse angeordneten Kühlmittelpumpen sowie Verfahren zum Betreiben einer solchen Antriebseinrichtung
DE102018220150A1 (de) * 2018-11-23 2020-05-28 Mahle International Gmbh Pumpenmodul für Kühlmittel

Also Published As

Publication number Publication date
EP0071807A3 (fr) 1983-08-31
ES8402389A1 (es) 1984-01-16
ZA825547B (en) 1984-03-28
ES514653A0 (es) 1984-01-16
CA1179907A (fr) 1984-12-27
JPS5827810A (ja) 1983-02-18
BR8204437A (pt) 1983-07-19
US4385594A (en) 1983-05-31

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