EP2014889A1 - Procédé de gestion thermique d'un moteur à combustion interne - Google Patents

Procédé de gestion thermique d'un moteur à combustion interne Download PDF

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Publication number
EP2014889A1
EP2014889A1 EP07110663A EP07110663A EP2014889A1 EP 2014889 A1 EP2014889 A1 EP 2014889A1 EP 07110663 A EP07110663 A EP 07110663A EP 07110663 A EP07110663 A EP 07110663A EP 2014889 A1 EP2014889 A1 EP 2014889A1
Authority
EP
European Patent Office
Prior art keywords
coolant
fluid
fluid coolant
circuit
temperature
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Withdrawn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
EP07110663A
Other languages
German (de)
English (en)
Inventor
Göran ALMKVIST
Roy Ekdahl
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.)
Ford Global Technologies LLC
Original Assignee
Ford Global Technologies LLC
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 Ford Global Technologies LLC filed Critical Ford Global Technologies LLC
Priority to EP07110663A priority Critical patent/EP2014889A1/fr
Priority to CNA2008101249548A priority patent/CN101328830A/zh
Priority to JP2008162206A priority patent/JP2009002346A/ja
Publication of EP2014889A1 publication Critical patent/EP2014889A1/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Withdrawn legal-status Critical Current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
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads
    • 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
    • F01P7/162—Controlling of coolant flow the coolant being liquid by thermostatic control by cutting in and out of 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
    • 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
    • F01P7/164—Controlling of coolant flow the coolant being liquid by thermostatic control by varying pump speed
    • 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
    • F01P2060/08—Cabin heater

Definitions

  • the present invention relates to a method for thermally managing an internal combustion engine which comprises an engine block with a fluid coolant flow passage therein, a cylinder head secured to the engine block and provided with a fluid coolant flow passage therein, and a first fluid coolant circuit comprising the fluid coolant flow passages, the internal combustion engine being provided with a second fluid coolant circuit connected to the first fluid coolant circuit and comprising a heat exchanger for transferring heat from the fluid coolant, a coolant pump for producing coolant flow in the first fluid coolant circuit, temperature sensing means and valve means. Further, the present invention relates to an engine system comprising the above-mentioned internal combustion engine and at least one engine control unit adapted to performing the steps of such methods.
  • US-A-5,735,238 discloses a heat management system for an internal combustion engine which provides a heat intensifying circuit to hasten engine warm-up.
  • the coolant flow circuit includes only a coolant pump, cooling passages on the exhaust side of the cylinder head and the heat exchanger for the passenger compartment.
  • US-A-5,337,704 describes a cooling system for an internal combustion engine, which provides an initial engine warm-up flow circuit extending from a coolant pump, through cooling passages in the cylinder head, through a heat exchanger used to warm up the passenger compartment and back to the pump, whereby a temperature responsive flow control valve or thermostat prohibits a flow of a coolant from the cylinder head to cooling passages in the engine block.
  • DE-A1-41 05 199 discloses an internal combustion engine having a heat distribution circuit with a radiator, a latent heat store, a pump and a balancing container.
  • a valve is arranged to stop the flow of coolant to the crankcase, and the balancing container and the latent heat store are connected in series between the cylinder head and the pump. The aim is to ensure the speediest possible heating-up of the cylinder head from a cold start.
  • DE-A1-40 32 701 describes a combustion engine, where the main coolant circuit has a main pump which takes coolant from the heat exchanger and pumps it first through the engine block and then through the cylinder head and back to the heat exchanger. For a rapid warm-up, the main coolant circuit is shut off and coolant is pumped via a secondary circuit by an electrically driven pump through the cylinder head only.
  • the secondary circuit contains a heat accumulator.
  • the secondary circuit also has a heat exchanger and an interior heater.
  • US 4,319,547 discloses a liquid cooled internal combustion engine having coolant cavities in the cylinder block and cylinder head, connected to a coolant circulating pump through a temperature controlled regulating device.
  • the arrangement is such that below a selected temperature coolant circulates through the cylinder head only while above this temperature the coolant circulates through both the cylinder head and the cylinder block.
  • JP 57193712 describes a method for shortening the time warm-up of an internal combustion engine in cold weather and sufficiently cool its cylinder, by using cooling water to cool the cylinder head and by using lubricating oil to cool the cylinder block.
  • a cooling water passage extends between a cylinder head and a radiator so that cooling water is circulated by a pump.
  • the object of the present invention is thus to improve the thermal management of an internal combustion engine, and overcome the above-mentioned drawbacks.
  • ⁇ T the difference between the temperature of the fluid coolant supplied to the first fluid coolant circuit from the second fluid coolant circuit and the temperature of the fluid coolant discharged from the first fluid coolant circuit to the second fluid coolant circuit is about 5°C, as the temperature of the coolant discharged from the first fluid coolant circuit is about 90°C and the temperature of the coolant supplied to the first fluid coolant circuit is about 85°C.
  • ⁇ T is at least 10°C, which represents such a low flow rate of the coolant so that the temperature of the coolant in the cylinder head is kept above 90°C, which higher than in prior art engines.
  • heat enhances the wear on engine oil, as the degradation of the oil is enhanced by heat.
  • a coolant with a lower temperature in relation to prior art, enters the engine.
  • the inventor has found, because of the cooler coolant entering the engine, that the engine oil in the oil sump is kept at a lower temperature in relation to prior art, which results in a lower temperature of the engine oil, whereby the durability of the engine oil is enhanced and the oil consumption is thus decreased.
  • the entry of the coolant from the second fluid coolant circuit to the first fluid coolant circuit is positioned in the engine block, i.e. when entering the engine, the coolant is first guided to the engine block and subsequently to the cylinder head.
  • the coolant pump is controlled to produce such a coolant flow so that the coolant temperature of the cylinder head is above 100°C. Tests performed by the inventor have shown that the friction in the engine is still further decreased above this temperature level, resulting in a decrease in fuel consumption.
  • the coolant pump is controlled to produce such a coolant flow so that the coolant temperature of the cylinder head is above 105°C. Tests performed by the inventor have shown that the friction in the engine is yet further decreased above this temperature level, resulting in a further decrease in fuel consumption.
  • the coolant pump is controlled to produce such a coolant flow so that the coolant temperature of the cylinder head is between 110-120°C. Tests performed by the inventor have shown that the friction in the engine is yet further decreased within this temperature range, resulting in a further decrease in fuel consumption.
  • the coolant pump is controlled to produce such a coolant flow so that the temperature of the coolant supplied to the first fluid coolant circuit from the second fluid coolant circuit is below 85°C.
  • the inventor has found that the entry of coolant, having a temperature below this temperature level, into the engine, further enhances the durability of the engine oil and the oil consumption is further decreased.
  • the coolant pump is controlled to produce such a coolant flow so that the temperature of the coolant supplied to the first fluid coolant circuit from the second fluid coolant circuit is below 75°C, advantageously below 70°C, or even below 65°C.
  • the inventor has found that the entry of coolant, having a temperature below these temperature levels, into the engine, is especially advantageous as a further increase of the durability of the engine oil is attained, and the oil consumption is further decreased.
  • the coolant pump is controlled to rapidly increase the flow rate of the coolant upon risk of knock, whereby the cylinder head is rapidly cooled off by the cold coolant provided by the present invention, and a fast knock control is provided and knock is prevented.
  • a fast knock control is provided and knock is prevented.
  • the major part of the heat from the combustion in the engine goes into the cylinder head, and the main part of the heat transmitted from the cylinder head to the engine block is transmitted via the coolant.
  • the coolant flow according to this method the heat is kept in the cylinder head and the heat transfer from the cylinder head, via the coolant, to the engine block is radically reduced.
  • a coolant with a lower temperature enters the engine and the first fluid coolant circuit, in relation to cases with higher flow rates defined by a smaller ⁇ T, whereby less heat per coolant mass flow unit is transferred to the engine block.
  • the engine is provided with a first fluid coolant circuit allowing an internal flow from the cylinder head to the engine block, the heat transfer via the coolant within in the engine is also radically reduced because of said low coolant flow.
  • the second fluid coolant circuit only includes the coolant pump, and no heat exchangers, it is in principal the pipes or tubes of the second fluid coolant circuit which transfer heat from the coolant flowing in the second fluid coolant circuit.
  • a lower flow rate of the coolant in the second fluid coolant circuit results in a larger heat transfer per coolant mass flow unit from the coolant via said pipes or tubes, since the coolant spends more time in said pipes or tubes, and thus provides a larger decrease in the temperature of the coolant, i.e. a larger ⁇ T.
  • a higher flow rate of the coolant in the second fluid coolant circuit results in a lower heat transfer per coolant mass flow unit from the coolant present in said pipes of tubes, since the coolant spends less time in said pipes or tubes, and thus provides a smaller decrease in the temperature of the coolant, i.e. a smaller ⁇ T.
  • the second fluid coolant circuit includes one or more heat exchangers, but then also these transfer heat from the fluid coolant.
  • the total amount of coolant passing through the second fluid coolant circuit per time unit is larger when the flow rate of the coolant is higher, the total heat transfer from the second fluid coolant circuit is larger.
  • the heating of the transfer oil can be included in the warm-up process for active heating.
  • the coolant pump is prevented from pumping the coolant, or by controlling the coolant pump to produce said coolant flow at least until the coolant temperature of the cylinder head has reached 100°C. Tests performed by the inventor have shown that the friction in the engine is still further decreased above this temperature level, resulting in a decrease in fuel consumption.
  • the coolant pump is prevented from pumping the coolant, or the coolant pump is controlled to produce said coolant flow at least until the coolant temperature of the cylinder head has reached 105°C. Tests performed by the inventor have shown that the friction in the engine is yet further decreased above this temperature level, resulting in a further decrease in fuel consumption.
  • the coolant pump is prevented from pumping the coolant, or the coolant pump to produce said coolant flow at least until the coolant temperature of the cylinder head has reached 110°C. Tests performed by the inventor have shown that the friction in the engine is still further decreased above this temperature level, resulting in a further decrease in fuel consumption.
  • the coolant is pumped by means of a pump drivable decoupled from the engine.
  • a pump drivable decoupled from the engine.
  • This can be an electric coolant pump, or a mechanically driven coolant pump which is drivable decoupled from the engine, e.g. a displacement pump.
  • other coolant pumps which can work decoupled from the engine are possible.
  • a mechanically driven coolant pump which is adapted to be "short-circuited", i.e. being provided with an additional circuit which can connect the outlet of the pump to the inlet of the pump.
  • the focus may be to rapidly warm-up the passenger compartment.
  • the second fluid coolant circuit comprises a heat exchanger for transferring heat from the fluid coolant and for warming a passenger compartment
  • the heat originating from the cylinder head is transferred from the coolant in the heat exchanger for warming the passenger compartment, instead of aiming to retain as much heat as possible in the cylinder head.
  • the flow rate of the coolant defined by ⁇ T ⁇ 10°C, also here is lower than in prior art, less energy or heat is transferred to the engine block and is in stead transferred to the passenger compartment, because of the above-mentioned facts.
  • the external heater on diesel engines can be replaced, because all heat which would be transferred from the engine block to the ambient instead is available for the passenger compartment warm-up
  • the coolant discharged from the fluid coolant flow passage of the cylinder head is guided to the heat exchanger for warming the passenger compartment.
  • a heat transfer from the coolant to the engine block at the outlet of the first fluid coolant circuit is prevented, allowing more heat to be transferred from the coolant in passenger compartment heat exchanger.
  • the general inventive concept of the methods of the present invention is to provide a considerably low flow rate of the coolant during the engine warm-up phase or during steady state as presented above, a flow rate which is considerably lower in relation to prior art, or even provide a substantially stagnant coolant in the engine during a considerable part of the engine warm-up phase or during the whole warm-up phase.
  • the coolant pump is controlled to produce such a coolant flow so that the temperature of the coolant supplied to the first fluid coolant circuit from the second fluid coolant circuit is at least 20°C lower than the temperature of the coolant discharged from the first fluid coolant circuit to the second fluid coolant circuit.
  • Tests preformed by the inventor have shown that the flow rate of the coolant at this level results in that the heat transfer to the engine block is further reduced, and more heat is contained in the cylinder head or transferred to the passenger compartment.
  • the coolant pump is controlled to produce such a coolant flow so that the temperature of the coolant supplied to the first fluid coolant circuit from the second fluid coolant circuit is at least 30°C lower than the temperature of the coolant discharged from the first fluid coolant circuit to the second fluid coolant circuit.
  • Tests preformed by the inventor have shown that the flow rate of the coolant at this level results in that the heat transfer to the engine block is still further reduced, and even more heat is contained in the cylinder head or transferred to the passenger compartment.
  • the methods of the present invention can be applied to different kinds of fluid coolant circuit designs, e.g. applied to a secondary fluid coolant circuit which only circulates coolant in the cylinder head during the warm-up phase not entering the engine block, applied to fluid coolant circuits with first fluid coolant circuits having an inlet for coolant provided in the cylinder head and/or the engine block, and an outlet for coolant provided in the cylinder head and/or the engine block, where the coolant is pumped from the engine block to the cylinder head, or vice versa, and applied to fluid coolant circuits with additional equipment included in the second fluid coolant circuit or the first fluid coolant circuit.
  • the methods of the present invention are advantageous for both petrol engines and diesel engines, especially during the warm-up phase of diesel engines, as the emissions of CO and HC are reduced because of the hotter combustion chamber and that the catalytic converter is subjected to a faster warm-up.
  • the present invention also provides an engine system as defined in claim 21.
  • Fig. 1 schematically illustrates an engine system comprising an internal combustion engine 101 to which the methods of the present invention can be applied.
  • the engine 101 comprises an engine block 102 with a fluid coolant flow passage 104 therein, a cylinder head 106 secured to the engine block 102 and provided with a fluid coolant flow passage 108 therein, and a first fluid coolant circuit 109 comprising the fluid coolant flow passages 104, 108.
  • the internal combustion engine 101 is provided with a second fluid coolant circuit 111 connected to the first fluid coolant circuit 109 and comprising a heat exchanger 110, in the form of a radiator 110, with an inlet and an outlet for transferring heat from the coolant, an electric coolant pump 112 with an inlet and an outlet for producing coolant flow in the fluid coolant circuits, an oil cooler 116 for transferring heat from the motor oil, and temperature sensing means 115 and valve means 117 included in a thermostat 118.
  • the temperature sensing means 115 is, inter alia, adapted to measure the coolant temperature of the cylinder head 106.
  • the coolant temperature of the cylinder head 106 can for instance be measured by providing a leak flow of coolant from the cylinder head, the temperature of which leak flow is measured.
  • the thermostat 118 receives, via its two inlets, coolant from the radiator 110, the internal combustion engine 101 and the oil cooler 116, and is arranged to control the coolant flow therefrom by means of its valve means 117.
  • the engine system also comprises an engine control unit (ECU) 120, which can be provided as one unit, or as more than one logically interconnected physical units.
  • the engine control unit 120 is adapted to receive data and control the electric coolant pump 112, the radiator 110, the oil cooler 116, and the thermostat 118.
  • Fig. 2 schematically illustrates a first and a second aspect of the method according to the present invention for thermally managing an internal combustion engine 101 during engine warm-up upon cold start.
  • the coolant flow through the radiator 110 is stopped by the valve means of the thermostat 118 in a conventional way, at step 201.
  • the ECU 120 controls the electric coolant pump 112 to stand still, and prevents it from pumping the coolant, and thus provides a substantially stagnant fluid coolant in the first fluid coolant circuit 109.
  • the coolant temperature of the cylinder head 106 is sensed by the temperature sensing means 115 of the thermostat 118, and the ECU 120 receives this temperature data.
  • the ECU 120 If the coolant temperature of the cylinder head is below 110°C, the ECU 120 still controls the electric coolant pump 112 to stand still and thus prevented from pumping the coolant. If the coolant temperature of the cylinder head is above or equal to 110°C, the ECU 120 controls the electric coolant pump 112 to produce such a coolant flow in the fluid coolant circuits, at step 204, to keep a coolant temperature of 110°C in the cylinder head 106.
  • the coolant temperature of the cylinder head 106 is sensed by the temperature sensing means 115 of the thermostat 118, and the ECU 120 receives this temperature data.
  • the ECU 120 controls the electric coolant pump 112 to keep pumping the coolant at above-mentioned low flow rate. If the coolant temperature of the cylinder head is above or equal 110°C, the ECU 120 controls the electric coolant pump 112 to pump the coolant at such a flow rate to keep a coolant temperature of about 110°C in the cylinder head 106, at step 207, which at least initially results in a flow rate increase.
  • T out is conventionally 90°C and T in is conventionally 85°C, which gives a 5 degrees difference between Tout and T in .
  • T out corresponds to the coolant temperature of the cylinder head 106, and when the coolant temperature of the cylinder head 106 reaches 110°C, T out is about 110°C.
  • steps 204 and 207 of the first and second aspects of the method for thermally managing an internal combustion engine 101 during engine warm-up proceed to the first step, 208, of a third aspect of the method according to the present invention, for thermally managing an internal combustion engine 101 during warmed-up conditions of the engine, i.e. steady state.
  • the coolant flow through the radiator 110 is allowed by the valve means of the thermostat 118 in a conventional way, when necessary.
  • the coolant temperature of the cylinder head 106 is sensed by the temperature sensing means 115 of the thermostat 118, and the ECU 120 receives this temperature data.
  • the ECU 120 controls the electric coolant pump 112 to keep pumping the coolant at the same flow rate, at step 211. If the coolant temperature of the cylinder head is outside said range, the ECU 120 controls the electric coolant pump 112 to adjust the flow rate of the coolant, at step 212. If knock occurs, the ECU 120 controls the electric coolant pump 112 to rapidly increase the flow rate of the coolant, at step 213, whereby the cylinder head 106 is rapidly cooled off by the cold coolant, and a fast knock control is provided.
  • Fig. 3 illustrates further aspects of the methods according to the present invention. Instead of performing steps 202-204 or steps 205-207, during the engine warm-up as disclosed in Fig. 2 , first, steps 201-203 are performed, and subsequently, steps 205-207 are performed, whereupon the steps of the third aspect of the method as disclosed in connection with Fig. 2 are performed.
  • steps 201-204 and/or steps 201 & 205-207 can be performed without proceeding to steps 208-213, and steps 208-213 can be performed without first performing steps 201-204 and/or steps 201 & 205-207.
  • first and second aspects of the method according to the present invention can be applied to the same engine system, alternating, or subsequently as disclosed in Fig. 3 , or one can choose to apply only one of the first and second aspects of the method according to the present invention.
  • the coolant temperature in the cylinder head 106 is between 110°C and 120°C during steady state.
  • Fig. 4 schematically illustrates a second engine system comprising an internal combustion engine 401 to which the methods of the present invention can be applied.
  • the engine 401 comprises an engine block 402 with a fluid coolant flow passage 404 therein, a cylinder head 406 secured to the engine block 402 and provided with a fluid coolant flow passage 408 therein, and a first fluid coolant circuit 409 comprising the fluid coolant flow passages 404, 408.
  • the first fluid coolant circuit 409 has more passages adapted to guide coolant from the cylinder head to the engine block internally within the engine.
  • the engine system comprises a second heat exchanger 412 for transferring heat from the fluid coolant and for warming a passenger compartment.
  • the second heat exchanger 412 receives coolant discharged from the fluid coolant flow passage of the cylinder head 406.
  • the other elements of this engine system correspond the elements of the engine system of Fig. 1 and are provided with the same reference signs.
  • the second heat exchanger 412 can also be present when applying the aspects discloses in connection with Figures 2 and 3 , connected or disconnected.
  • the coolant pump 112 is controlled to produce such a coolant flow so that the temperature T in of the fluid coolant supplied to the first fluid coolant circuit 409 from the second fluid coolant circuit 111 is about 25°C lower than the temperature T out of the fluid coolant discharged from the first fluid coolant circuit 409 to the second fluid coolant circuit 111. Because of the low flow rate of the coolant in the second heat exchanger 412, the coolant is subjected to a large temperature decrease in the second heat exchanger 412. According to this aspect, the flow rate of the coolant is higher in relation to the aspects of Figs. 2 and 3 , but the flow rate of the coolant is still considerably lower in relation to prior art engine systems including a heat exchanger for warming a passenger compartment.
  • ⁇ T is at least 20°C, advantageously at least 25°C, or even at least 30°C, for all methods of the present invention.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP07110663A 2007-06-20 2007-06-20 Procédé de gestion thermique d'un moteur à combustion interne Withdrawn EP2014889A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP07110663A EP2014889A1 (fr) 2007-06-20 2007-06-20 Procédé de gestion thermique d'un moteur à combustion interne
CNA2008101249548A CN101328830A (zh) 2007-06-20 2008-06-18 热管理内燃发动机的方法
JP2008162206A JP2009002346A (ja) 2007-06-20 2008-06-20 エンジンの熱管理方法、及び、エンジン・システム

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07110663A EP2014889A1 (fr) 2007-06-20 2007-06-20 Procédé de gestion thermique d'un moteur à combustion interne

Publications (1)

Publication Number Publication Date
EP2014889A1 true EP2014889A1 (fr) 2009-01-14

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EP07110663A Withdrawn EP2014889A1 (fr) 2007-06-20 2007-06-20 Procédé de gestion thermique d'un moteur à combustion interne

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EP (1) EP2014889A1 (fr)
JP (1) JP2009002346A (fr)
CN (1) CN101328830A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9416720B2 (en) 2011-12-01 2016-08-16 Paccar Inc Systems and methods for controlling a variable speed water pump
CN112127985A (zh) * 2019-06-24 2020-12-25 奥迪股份公司 驱动装置的冷却剂回路和运行冷却剂回路的方法

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8475337B2 (en) * 2009-05-07 2013-07-02 Toyota Jidosha Kabushiki Kaisha Vehicle heat management device
WO2011067857A1 (fr) * 2009-12-04 2011-06-09 トヨタ自動車株式会社 Dispositif de refroidissement de moteur
US8813692B2 (en) * 2011-05-19 2014-08-26 GM Global Technology Operations LLC System and method for determining coolant flow in an engine
KR101339257B1 (ko) * 2012-09-24 2013-12-09 현대자동차 주식회사 차량의 엔진 냉각 시스템 및 방법
JP6330275B2 (ja) 2013-08-29 2018-05-30 セイコーエプソン株式会社 記録装置
US9188053B2 (en) * 2013-08-31 2015-11-17 Ford Global Technologies, Llc Methods and devices for controlling a vehicle coolant pump
CN104612877A (zh) * 2014-11-28 2015-05-13 中联重科股份有限公司渭南分公司 一种车辆暖机控制设备、系统、方法及工程机械
US9611781B2 (en) * 2015-01-09 2017-04-04 GM Global Technology Operations LLC System and method of thermal management for an engine
CN108263202B (zh) * 2017-12-14 2020-12-01 浙江吉利新能源商用车有限公司 一种多增程器发动机冷却装置
CN110793777B (zh) * 2019-10-23 2021-05-25 清华大学 一种模拟柴油机进气道环境进气预热效果的测试装置

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56148677A (en) * 1980-04-18 1981-11-18 Toyota Motor Corp Controlling method for ignition timing of engine
US4559907A (en) * 1983-03-31 1985-12-24 Nissan Motor Co., Ltd. Load responsive temperature control arrangement for internal combustion engine
FR2571431A1 (fr) * 1984-10-09 1986-04-11 Renault Vehicules Ind Dispositif de refroidissement pour moteur a combustion interne
EP0442489A1 (fr) * 1990-02-16 1991-08-21 Nippondenso Co., Ltd. Procédé de refroidissement d'un moteur à combustion interne et le dispositif de refroidissement pour cela
EP0557113A2 (fr) * 1992-02-19 1993-08-25 Honda Giken Kogyo Kabushiki Kaisha Système de refroidissement pour moteur
DE19803884A1 (de) * 1998-01-31 1999-08-05 Bayerische Motoren Werke Ag Flüssigkeitsgekühlte Brennkraftmaschine mit einem Kühlkreislauf mit zumindest einer Pumpe
EP1239129A2 (fr) * 2001-03-06 2002-09-11 Calsonic Kansei Corporation Système de refroidissement pour un moteur à combustion interne refroidi par eau et procédé pour le commander
GB2420847A (en) * 2004-12-04 2006-06-07 Ford Global Tech Llc Engine cooling system with independent control of coolant supply through a cylinder head and a cylinder block
JP2006214280A (ja) * 2005-02-01 2006-08-17 Mazda Motor Corp エンジンの冷却装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2704806B2 (ja) * 1992-04-09 1998-01-26 本田技研工業株式会社 エンジンの冷却装置
JP2004084526A (ja) * 2002-08-26 2004-03-18 Toyota Motor Corp 内燃機関
JP2007016718A (ja) * 2005-07-08 2007-01-25 Toyota Motor Corp エンジンの冷却装置
JP4561529B2 (ja) * 2005-08-23 2010-10-13 トヨタ自動車株式会社 内燃機関冷却装置の故障検出システム
JP4561546B2 (ja) * 2005-09-08 2010-10-13 トヨタ自動車株式会社 内燃機関の冷却装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56148677A (en) * 1980-04-18 1981-11-18 Toyota Motor Corp Controlling method for ignition timing of engine
US4559907A (en) * 1983-03-31 1985-12-24 Nissan Motor Co., Ltd. Load responsive temperature control arrangement for internal combustion engine
FR2571431A1 (fr) * 1984-10-09 1986-04-11 Renault Vehicules Ind Dispositif de refroidissement pour moteur a combustion interne
EP0442489A1 (fr) * 1990-02-16 1991-08-21 Nippondenso Co., Ltd. Procédé de refroidissement d'un moteur à combustion interne et le dispositif de refroidissement pour cela
EP0557113A2 (fr) * 1992-02-19 1993-08-25 Honda Giken Kogyo Kabushiki Kaisha Système de refroidissement pour moteur
DE19803884A1 (de) * 1998-01-31 1999-08-05 Bayerische Motoren Werke Ag Flüssigkeitsgekühlte Brennkraftmaschine mit einem Kühlkreislauf mit zumindest einer Pumpe
EP1239129A2 (fr) * 2001-03-06 2002-09-11 Calsonic Kansei Corporation Système de refroidissement pour un moteur à combustion interne refroidi par eau et procédé pour le commander
GB2420847A (en) * 2004-12-04 2006-06-07 Ford Global Tech Llc Engine cooling system with independent control of coolant supply through a cylinder head and a cylinder block
JP2006214280A (ja) * 2005-02-01 2006-08-17 Mazda Motor Corp エンジンの冷却装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9416720B2 (en) 2011-12-01 2016-08-16 Paccar Inc Systems and methods for controlling a variable speed water pump
US10119453B2 (en) 2011-12-01 2018-11-06 Paccar Inc Systems and methods for controlling a variable speed water pump
US10914227B2 (en) 2011-12-01 2021-02-09 Paccar Inc Systems and methods for controlling a variable speed water pump
CN112127985A (zh) * 2019-06-24 2020-12-25 奥迪股份公司 驱动装置的冷却剂回路和运行冷却剂回路的方法
US11549765B2 (en) 2019-06-24 2023-01-10 Audi Ag Coolant circuit for a drive device and method for operating a coolant circuit

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