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WO2008080872A1 - Système de refroidissement à circulation d'eau haute/basse température et soupape à quatre voies pour un tel système - Google Patents

Système de refroidissement à circulation d'eau haute/basse température et soupape à quatre voies pour un tel système Download PDF

Info

Publication number
WO2008080872A1
WO2008080872A1 PCT/EP2007/064305 EP2007064305W WO2008080872A1 WO 2008080872 A1 WO2008080872 A1 WO 2008080872A1 EP 2007064305 W EP2007064305 W EP 2007064305W WO 2008080872 A1 WO2008080872 A1 WO 2008080872A1
Authority
WO
WIPO (PCT)
Prior art keywords
port
low temperature
pump
outlet
valve
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/EP2007/064305
Other languages
English (en)
Inventor
Arnaud Contet
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.)
Valeo Systemes Thermiques SAS
Titanx Engine Cooling AB
Original Assignee
Valeo Systemes Thermiques SAS
Valeo Engine Cooling AB
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 Valeo Systemes Thermiques SAS, Valeo Engine Cooling AB filed Critical Valeo Systemes Thermiques SAS
Priority to EP07857926.5A priority Critical patent/EP2097628B1/fr
Publication of WO2008080872A1 publication Critical patent/WO2008080872A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0437—Liquid cooled heat exchangers
    • F02B29/0443—Layout of the coolant or refrigerant circuit
    • 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
    • F01P2005/105—Using two or more 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
    • F01P2037/00—Controlling
    • F01P2037/02—Controlling starting
    • 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
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/02—Intercooler
    • 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
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/06—Retarder

Definitions

  • the present invention concerns a high/low tempera- ture water cooling system comprising a high temperature cooling circuit and a low temperature cooling circuit including : a water cooled charge air cooler for a combustion engine, a low temperature heat exchanger and a pump, said second pump, having a pump inlet and a pump outlet,
  • the invention concerns a four port valve for a high/low temperature water cooling system.
  • a cooling system according to the preamble is known from the international patent application WO 02/48516 Al.
  • an invention is described aiming to lowering fuel consumption of a supercharged combustion engine by optimizing coolant flow through a high temperature cooler or HT cooler and a low temperature or LT cooler.
  • the HT cooler is provided to cool the engine it- self and is fed by a first- coolant pump, wherein the LT cooler is provided to cool at least a water cooled charge air cooler, in short a WCCAC.
  • the WCCAC is connected to a second coolant pump and is provided to cool supercharged air before it is blown into the engine. Since there are two individual cooling circuits, it is possible to adopt individual cooling strategies for both circuits and thus to minimize the heat energy loss for the overall system, which is highly beneficial to fuel consumption.
  • combustion or charge air fed to the engine by a supercharger requires less cooling or no cooling at all to adopt a desirable value of approximately 2O 0 C.
  • the prior art system can account for that by reducing or entirely cutting off coolant flow in its LT cooling circuit.
  • ambient conditions well below the freezing point e.g. -20 0 C
  • the prior art system has no arrangements at all to address these problems.
  • HT engine cooling cir- cuits like the one disclosed in the prior art application, have a thermostat.
  • the thermostat is arranged to control a bypass from the engine coolant outlet to the engine coolant inlet in parallel with the HT heat exchanger.
  • the thermostat is closed entirely and coolant is bypassed the HT heat exchanger in order to be heated more rapidly.
  • the only source for heating the coolant is the engine itself, and especially if the engine is a diesel engine the warm up times tend to be extensive.
  • the prior art sys- tern has no arrangements to address the problems posed by that.
  • the object of the invention is to solve the problems with the prior art high/low temperature water cooling system according to the preamble.
  • said low temperature cooling circuit further including : a multi port valve, a first port of which being connected to the low temperature heat exchanger, a second port of which being connected to a bypass, said second bypass, in parallel with the low temperature heat exchanger, a third port of which being connected to the pump outlet of said second pump, and a fourth port of which being connected to an circuit outlet of said low temperature cooling circuit, wherein said valve is arranged to block the.
  • the HT and LT cooling circuits upstream and downstream the coolant pump in the HT cooling circuit and by providing a bypass in the LT cooling circuit as well, it is by the multi port valve rendered possible for the high/low temperature water cooling sys- tern to fulfil both traditional charge air cooling tasks in a cooling mode and to fulfil additional tasks in a heat up mode.
  • the additional tasks are charge air heating in cold ambient conditions by using hot coolant from the HT cooling circuit in the LT cooling circuit and promo- tion of engine warm up by using hot coolant from the LT cooling circuit in the HT cooling circuit.
  • the high temperature cooling circuit further includes : an engine coolant outlet connected to a high temperature heat exchanger, an engine coolant inlet connected to the high temperature heat exchanger, a thermostat for controlling a first bypass from the engine coolant outlet to the engine coolant inlet in parallel with the high temperature heat exchanger, and a said first coolant pump.
  • the low tem- perature cooling circuit further includes: a circuit outlet connectable to the second coolant pump outlet and to the high temperature cooling circuit upstream the first coolant pump, a circuit inlet connected to the pump inlet and to the high temperature cooling circuit downstream the first coolant pump.
  • the second coolant pump is arranged to be off in the heat up mode and to be on in a charge air cooling mode thus optimizing coolant flow and energy consumption in both modes.
  • the system according to another embodiment the system according to
  • the invention further comprises a water cooled re- tarder connected to the high temperature cooling circuit, wherein said valve is arranged to interconnect the first and forth port and to block the second and third port in a retarder braking mode.
  • the LT heat exchanger can be used to dissipate retarder heat in a mode where no charge air cooling is needed, thus enabling prolonged retarder braking.
  • the second coolant pump is arranged to be off, thus optimizing coolant flow in the LT cooling circuit in that mode.
  • a degassing circuit comprising a high level outlet on the engine, a high level outlet on the high temperature heat exchanger, a high level outlet on the low temperature heat exchanger and a high level outlet on said charge air cooler, all four outlets being connected to a common expansion tank, and further comprising a low level outlet on the expansion tank, said outlet being connected to the high temperature cooling circuit upstream the first coolant pump.
  • the expansion tank common to all four outlets and the sole ex- pansion tank outlet exploit in a most effective and weight saving way that the high temperature and the low temperature cooling circuits are interconnected in the system according to the invention.
  • the multi port valve is arranged to block all four ports in a engine heat up mode when ambient conditions are moderate or in a braking mode when braking without use of said retarder, thus concentrating all of the HT coolant to the HT cooling circuit alone.
  • the present invention concerns also a four port valve for a high/low temperature water cooling system according to the invention, said valve having a circular valve chamber having a first circumferential port, a sec- ond circumferential port 90° apart from said first port, a third circumferential port 45° further apart from said first port than said second port and a fourth circumferential port 90° further apart from said first port than said third port, and a rotatable valve slider tightly fitting inside the valve chamber and having a first and a second circumferential orifice interconnected by a duct extending through the valve slider, said first and second orifice being 135° apart and alignable with two ports at a time.
  • a four port valve designed according to the in- vention is durable and easy to control and thus suitable for rough conditions, such as in a truck.
  • valve is arranged to be controlled electronically and in coordination with the second coolant pump, thereby optimizing coolant flow and energy consumption in a simple way.
  • FIG. 1 is an overall view of a high/low temperature water cooling system according to the invention
  • Figs. 2-4 show three different operational modes of the system in Fig. 1;
  • Fig. 5 is an overall view of a four port valve according to the invention.
  • Figs . 6-9 show four different operational modes of the four port valve in Fig. 5;
  • Fig. 10 is another overall view of the high/low temperature water cooling system with a degassing circuit added.
  • a diesel engine 3 e.g. for a truck, is provided with a high temperature or HT cooling circuit 4 and a water cooled retarder 24 connected to the engine 3.
  • the HT cooling circuit 4 includes an engine coolant outlet 5 connected to an HT heat exchanger 6, an engine coolant inlet 7 connected to the HT heat exchanger 6, a thermostat 8 for controlling a first bypass 9 from the engine coolant out- let 5 to the engine coolant inlet 7 in parallel with the HT heat exchanger 6, and a first coolant pump 10.
  • a low temperature or LT cooling circuit 11 is a low temperature or LT cooling circuit 11 too for a water cooled charge air cooler 2, in short a WCCAC.
  • the WCCAC 2 is arranged to cool supercharged combustion air blown into the diesel engine 3 for enhancing engine performance and forms an integral part of the LT cooling circuit 11, which also includes a low temperature or LT heat exchanger 12 and a second coolant pump 13 having a pump inlet 14 and a pump outlet 15.
  • the LT cooling circuit 11 further includes a circuit outlet 16 connectable to the pump outlet 15 and to the HT cooling circuit 4 upstream the first coolant pump 10, a circuit inlet 17 connected to the pump inlet 14 and to the HT cooling circuit 4 downstream the first coolant pump 10, and a multi port valve 18.
  • the multi port valve 18 is preferably a four port one like the valve shown in greater detail in Fig. 5. It has a first port 19 which is connected to the LT heat ex- changer 12, a second port 20 which is connected to a second bypass 21 in parallel with the LT heat exchanger 12, a third port 22 which is connected to the pump outlet 15, ⁇ and a fourth port 23 which is connected to the circuit outlet 16.
  • the valve 18 is preferably controlled by elec- tronics (not shown) governing the entire high/low temperature water cooling system 1.
  • valve ports 19, 20, 22, 23 are circumferential ports distributed round a circular valve chamber 25.
  • the second port 20 lies circumferentially 90° apart from said first port 19, the third port 22 another 45° further apart from said first port 19 than said second port 20 and the fourth port 23 another 90° further apart from said first port 19 than said third port 22.
  • Inside the four port valve 18 there is a rotatable valve slider 26 tightly fitting inside the valve chamber 25. It has a first and a second circumferential orifice 27, 28 interconnected by a duct 29 extending through the valve slider 26. The first and second orifices 27, 28 lie 135° apart and are alignable with a maximum of two ports 19, 20, 22, 23 at a time.
  • the high/low temperature water cooling system 1 described can adopt different modes of operation by aid of the four port valve 18.
  • the second coolant pump 13 is preferably off (mainly to save energy) and the valve slider 26 is rotated to block the first 19 and third 22 port and to interconnect the second 20 and fourth 23 port.
  • major coolant flows are created through the circuit inlet 17 from the HT cooling circuit 4 to the LT cooling circuit 11 and through the circuit outlet 16 from the LT cooling circuit 11 back to the HT cooling circuit 4.
  • the flow inside the LT cooling circuit 11 itself is a reversed one (created by the first coolant pump 10) and bypasses the LT heat exchanger 12 entirely.
  • the resulting mode is a heat up mode used either to enhance cold engine heat up by heat generated in the WCCAC 2 or to heat the charge air in the WCCAC 2 in cold ambient conditions, e.g. -2O 0 C once the engine 3 is heated up, thereby preventing knocking due to an excess air density.
  • a second operational mode illustrated in Figs. 3 and 7, the second coolant pump 13 is on and the valve slider 26 is rotated to interconnect the first 19 and third 22 port and to block the second 20 and fourth 23 port.
  • this mode there is only a minor coolant flow through the circuit inlet 17 (degassing) and no coolant flow at all through the circuit outlet 16.
  • the flow inside the LT cooling circuit 11 is a forward one (created by the second coolant pump 13) and goes through the LT heat exchanger 12.
  • the resulting mode is. a tradi- tional charge air cooling mode enhancing engine performance in normal driving conditions by increasing density of the charge air boosted into the engine 3.
  • the second coolant pump 13 is off (to save energy and enhancing system performance) and the valve slider 26 is rotated to interconnect the first 19 and third 22 port and to block the second 20 and fourth 23 port.
  • major coolant flows are created through the circuit inlet 17 from the HT cooling circuit 4 to the LT cooling circuit 11 and through the circuit outlet 16 from the LT cooling circuit 11 back to the HT cooling circuit 4.
  • the flow inside the LT cooling circuit 11 itself is a reversed one (created by the first coolant pump 10 ⁇ , but this time it goes through the LT heat exchanger 12.
  • the resulting mode is a retarder cooling mode, in which the LT heat exchanger 12 is used as an extra means to dissipate retarder heat created while retarder braking.
  • a forth operational mode for which the valve position is illustrated in Fig. 9, the second coolant pump 13 is off and the valve slider 26 is rotated to block all four ports 19, 20, 22, 23.
  • This mode in which there is no coolant flow at all inside and to and fro the LT cooling circuit 11 and all coolant circulation is reserved for the HT cooling circuit alone, is an engine heat up mode used mainly when warming up the engine 3 at idling speed.
  • a degassing circuit 30 is shown, said circuit forming an integral part of the high/low temperature water cooling system 1.
  • the degassing- circuit 30 further comprises a low level outlet 36 on the expansion tank 35.
  • the outlet 36 serves to return coolant to the system 1 when the system is cooling down and is connected to the high temperature cooling circuit 4 upstream the first coolant pump 10.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Temperature-Responsive Valves (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un système de refroidissement à circulation d'eau haute/basse température (1) pour un moteur à combustion (3) comprenant un circuit de refroidissement haute température (HT) (4) destiné à refroidir le moteur (3) et un système de refroidissement basse température (LT) (11) destiné à refroidir un refroidisseur d'air de suralimentation refroidi à l'eau (WCCAC) (2) pour l'air de suralimentation conduit au moteur (3). Les circuits de refroidissement HT et LT (4, 11) sont interconnectés en amont et en aval d'une pompe de refroidissement (10) du circuit de refroidissement HT (4), le circuit de refroidissement LT (11) présentant sa propre pompe (13). En outre, le circuit de refroidissement LT (11) présente une dérivation (21) pour échangeur de chaleur LT qui est commandée par une soupape multivoies (18). Ladite soupape (18) permet au moins deux modes de fonctionnement différents, un mode d'échauffement, dans lequel le caloporteur chaud provenant du circuit de refroidissement HT (4) est utilisé pour chauffer l'air de suralimentation dans des conditions ambiantes extrêmement froides, et un mode de refroidissement, dans lequel l'air de suralimentation est refroidi d'une manière traditionnelle.
PCT/EP2007/064305 2006-12-29 2007-12-20 Système de refroidissement à circulation d'eau haute/basse température et soupape à quatre voies pour un tel système Ceased WO2008080872A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07857926.5A EP2097628B1 (fr) 2006-12-29 2007-12-20 Système de refroidissement à circulation d'eau haute/basse température et soupape à quatre voies pour un tel système

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0602837-7 2006-12-29
SE0602837A SE530376C2 (sv) 2006-12-29 2006-12-29 Hög-/lågtemperaturvattenkylsystem med en vattenkyld laddluftkylare för en förbränningsmotor och en fyrvägsventil för ett sådant system

Publications (1)

Publication Number Publication Date
WO2008080872A1 true WO2008080872A1 (fr) 2008-07-10

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/064305 Ceased WO2008080872A1 (fr) 2006-12-29 2007-12-20 Système de refroidissement à circulation d'eau haute/basse température et soupape à quatre voies pour un tel système

Country Status (3)

Country Link
EP (1) EP2097628B1 (fr)
SE (1) SE530376C2 (fr)
WO (1) WO2008080872A1 (fr)

Cited By (20)

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WO2009128768A1 (fr) * 2008-04-18 2009-10-22 Scania Cv Ab Dispositif de refroidissement pour un moteur à combustion interne à suralimentation
WO2010036185A1 (fr) * 2008-09-25 2010-04-01 Scania Cv Ab Agencement dans un système de refroidissement basse température pour un moteur à combustion suralimenté
CN103075239A (zh) * 2011-10-26 2013-05-01 曼卡车和巴士股份公司 用于液体冷却的内燃机的冷却回路
EP2357335A3 (fr) * 2010-01-15 2014-01-01 Bayerische Motoren Werke Aktiengesellschaft Dispositif et procédé de refroidissement d'air de chargement
EP2795078A4 (fr) * 2011-12-23 2015-09-09 Scania Cv Ab Dispositif et procédé pour refroidissement d'agent de refroidissement dans un système de refroidissement dans un véhicule
WO2015168313A1 (fr) * 2014-04-30 2015-11-05 Cummins Inc. Système et procédé destinés à optimiser l'intégration de moteurs et de ralentisseurs sur transmission de véhicule
CN105179061A (zh) * 2015-10-16 2015-12-23 安徽江淮汽车股份有限公司 一种包括有双膨胀水箱的双循环冷却系统
CN105179067A (zh) * 2015-10-16 2015-12-23 安徽江淮汽车股份有限公司 一种包括有辅助水泵的双循环冷却系统改进结构
EP3001006A1 (fr) * 2014-09-29 2016-03-30 Wärtsilä Finland Oy Système de refroidissement pour un moteur à combustion interne à pistons, procédé de fonctionnement d'un moteur à combustion interne à pistons et moteur à combustion interne à pistons
EP2932061A4 (fr) * 2012-12-17 2016-07-27 Scania Cv Ab Système de refroidissement
GB2536656A (en) * 2015-03-24 2016-09-28 Jaguar Land Rover Ltd Heat exchange system
US20170030252A1 (en) * 2014-01-23 2017-02-02 Bayerische Motoren Werke Aktiengesellschaft Method and Device for Ventilating a Heat Management System of an Internal Combustion Engine
WO2017200463A1 (fr) * 2016-05-19 2017-11-23 Scania Cv Ab Système couplé de refroidissement pour un moteur à combustion et un autre objet
DE102017216700A1 (de) 2017-09-21 2019-03-21 Mahle International Gmbh Kühlvorrichtung und Verfahren zum Regeln der Kühlvorrichtung
JP2019065752A (ja) * 2017-09-29 2019-04-25 株式会社デンソー 制御装置
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
WO2019203701A1 (fr) * 2018-04-17 2019-10-24 Scania Cv Ab Système de refroidissement comprenant au moins deux circuits de refroidissement reliés à un réservoir d'expansion commun
DE102018214152B3 (de) * 2018-08-22 2019-11-07 Ford Global Technologies, Llc Kühlsystem für einen Verbrennungsmotor, insbesondere Zylinderkopfkühlung mit Ladeluftkühler
DE102020201350A1 (de) 2020-02-04 2021-08-05 Volkswagen Aktiengesellschaft Baugruppe für ein Kühlsystem eines Kraftfahrzeugs mit einem Wärmetauscher, einem Steuerventil und einer Stellvorrichtung
US11124047B2 (en) 2018-11-03 2021-09-21 Hyundai Motor Company Vehicular HVAC system with liquid-cooled charge air cooler integration

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SE542979C2 (en) * 2018-10-09 2020-09-22 Scania Cv Ab A temperature control system, a vehicle provided therewith and a method for controlling the operation thereof
WO2021083532A1 (fr) 2019-11-01 2021-05-06 Volvo Truck Corporation Système combiné de refroidissement et de freinage hydraulique pour un véhicule, et procédé de refroidissement d'un dispositif de propulsion d'un véhicule et de freinage hydraulique d'une paire de roues d'un véhicule
SE544141C2 (en) * 2020-03-23 2022-01-11 Scania Cv Ab A temperature control system, a vehicle provided therewith and a method for controlling the operation thereof
US12065959B2 (en) 2022-09-09 2024-08-20 Cummins Inc. Thermal management of exhaust gas with charge air heating
WO2025129479A1 (fr) * 2023-12-20 2025-06-26 Cummins Inc. Système de refroidissement et soupape de gestion thermique pour moteurs à combustion interne dotés de retardateurs

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WO2004090303A1 (fr) * 2003-04-11 2004-10-21 Behr Gmbh & Co. Kg Dispositif de circuit pour refroidir l'air de suralimentation et procédé pour faire fonctionner un dispositif de ce type

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US6539899B1 (en) * 2002-02-11 2003-04-01 Visteon Global Technologies, Inc. Rotary valve for single-point coolant diversion in engine cooling system
WO2004085807A1 (fr) * 2003-03-28 2004-10-07 Scania Cv Ab (Publ) Agencement de refroidissement et procede de refroidissement de ralentisseur
WO2004090303A1 (fr) * 2003-04-11 2004-10-21 Behr Gmbh & Co. Kg Dispositif de circuit pour refroidir l'air de suralimentation et procédé pour faire fonctionner un dispositif de ce type

Cited By (37)

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Publication number Priority date Publication date Assignee Title
US8424303B2 (en) 2008-04-18 2013-04-23 Scania Cv Ab Cooling arrangement for a supercharged internal combustion engine
WO2009128768A1 (fr) * 2008-04-18 2009-10-22 Scania Cv Ab Dispositif de refroidissement pour un moteur à combustion interne à suralimentation
US20110041814A1 (en) * 2008-04-18 2011-02-24 Zoltan Kardos Cooling arrangement for a supercharged internal combustion engine
JP2011518279A (ja) * 2008-04-18 2011-06-23 スカニア シーブイ アクチボラグ 過給内燃機関用冷却装置
US8590494B2 (en) 2008-09-25 2013-11-26 Scania Cv Ab Arrangement in a low-temperature cooling system for a supercharged combustion engine
JP2012503740A (ja) * 2008-09-25 2012-02-09 スカニア シーブイ アクチボラグ 過給式内燃機関用の低温冷却システムにおける装置
CN102165162B (zh) * 2008-09-25 2013-06-05 斯堪尼亚商用车有限公司 用于增压燃烧发动机的低温冷却系统中的装置
WO2010036185A1 (fr) * 2008-09-25 2010-04-01 Scania Cv Ab Agencement dans un système de refroidissement basse température pour un moteur à combustion suralimenté
EP2357335A3 (fr) * 2010-01-15 2014-01-01 Bayerische Motoren Werke Aktiengesellschaft Dispositif et procédé de refroidissement d'air de chargement
CN103075239A (zh) * 2011-10-26 2013-05-01 曼卡车和巴士股份公司 用于液体冷却的内燃机的冷却回路
EP2587017A1 (fr) * 2011-10-26 2013-05-01 MAN Truck & Bus AG Circuit de refroidissement pour moteur à combustion interne refroidi par un liquide
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EP2097628A1 (fr) 2009-09-09
SE0602837L (sv) 2008-05-20
SE530376C2 (sv) 2008-05-20
EP2097628B1 (fr) 2018-09-12

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