EP2653687A1 - Dispositif de refroidissement de moteur - Google Patents

Dispositif de refroidissement de moteur Download PDF

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Publication number
EP2653687A1
EP2653687A1 EP10860673.2A EP10860673A EP2653687A1 EP 2653687 A1 EP2653687 A1 EP 2653687A1 EP 10860673 A EP10860673 A EP 10860673A EP 2653687 A1 EP2653687 A1 EP 2653687A1
Authority
EP
European Patent Office
Prior art keywords
cooling
engine
cooling medium
flow
cooling water
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Withdrawn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
EP10860673.2A
Other languages
German (de)
English (en)
Other versions
EP2653687A4 (fr
Inventor
Daishi Takahashi
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.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
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 Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of EP2653687A1 publication Critical patent/EP2653687A1/fr
Publication of EP2653687A4 publication Critical patent/EP2653687A4/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Withdrawn legal-status Critical Current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
    • F01P3/00—Liquid cooling
    • F01P3/12—Arrangements for cooling other engine or machine parts
    • F01P3/16—Arrangements for cooling other engine or machine parts for cooling fuel injectors or sparking-plugs
    • 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
    • F01P2003/028—Cooling cylinders and cylinder heads in series

Definitions

  • the present invention relates to an engine cooling apparatus.
  • Patent Document 1 discloses a cooling apparatus for a multi-cylinder engine designed to prevent excessive cooling of the cylinder block.
  • Patent Document 2 discloses a cooling apparatus for an internal combustion engine designed to positively cool the wall surface of the combustion chamber on the exhaust-port side thereof and to thus improve the cooling efficiency of the internal combustion engine.
  • FIG. 10 is a diagram that illustrates the breakdown of heat balance of an engine.
  • FIG. 10 illustrates the general breakdown of a spark ignition internal combustion engine for the full load and that for the partial load.
  • the spark ignition internal combustion engine generates heat that is not used for the net work, such as an exhaust loss and a cooling loss.
  • Reduction in the cooling loss that occupies a large ratio to the entire energy loss is a very important factor to improve the thermal efficiency (fuel economy).
  • a reason for the difficulty in reduction of the cooling loss may be such that the general engine does not have a structure that locally changes the state of thermal conduction. That is, the general engine has a structural difficulty in cooling a portion necessary for cooling by a necessary degree.
  • the state of thermal condition of the engine may be changed by changing the flow rate of cooling water in accordance with the engine speed by a mechanical water pump driven by the power of the engine.
  • the water pump that wholly adjusts the flow rate of the cooling water is not capable of locally changing the conduction state of heat in accordance with the engine working state even by using a variable water pump capable of changing the flow rate.
  • FIG. 11 is a diagram that illustrates the inner wall temperature and the coefficient of overall heat transfer of a cylinder.
  • these are illustrated for a case of the regular structure and cases where the thermal insulation is improved.
  • the regular structure there is illustrated a case of a general engine equipped with a single system of cooling water circulation path through which the cooling water is circulated from the lower portion of the cylinder block to the cylinder head against the gravity.
  • the cases where the thermal insulation is improved there are illustrated a case where the wall thickness of the cylinder is increased and the material thereof is changed, and another case where heat isolation by air, which has higher adiabaticity is employed.
  • the present invention takes the above problem into consideration and aims at providing an engine cooling apparatus capable of achieving both reduction in the cooling loss and improvement in knocking.
  • the present invention is an engine cooling apparatus comprising: a cylinder block and a cylinder head in which a first cooling medium path and a second cooling medium path are provided, the first cooing medium path causing cooling medium to flow through an exhaust-side portion of the cylinder block and causing cooling medium to flow through an exhaust-side portion of the cylinder head including a predetermined region around a spark plug provided to the cylinder head, and the second cooling medium path being incorporated into a cooling medium circulation path different from that into which the first cooling medium path is incorporated, and causing cooling medium to flow through an intake-side portion of the cylinder block and causing the cooling medium to flow through an intake-side portion of the cylinder head.
  • the present invention is preferably structured to be further equipped with cooling medium control means that causes cooling medium to flow through the first cooling medium path when cooling medium is circulated through the engine and makes a flow rate of cooling medium that flows through the second cooling medium path at low or medium load lower than that at high load.
  • the present invention is preferably structured so that the engine is an engine in which exhaust recirculation is performed and is structured to be further equipped with a cooling device capable of cooling exhaust returned to the engine by a thermal exchange with cooling medium circulated, and a first branch portion splitting cooling medium that flows through the first cooling medium path into a flow that passes through the cooling device.
  • the present invention is preferably structured to be further equipped with a heater capable of heating air by a thermal exchange with cooling medium circulated, and a second branch portion splitting cooling medium that flows through the first cooling medium path into a flow that passes through the heater.
  • the present invention is capable of achieving both reduction in the cooling loss and improvement in knocking.
  • FIG. 1 is a diagram of a structural outline of an engine cooling apparatus (hereinafter referred to as cooling apparatus) 1A.
  • the cooling apparatus 1A is mounted in a vehicle, which is not illustrated.
  • the cooling apparatus 1A is composed of a water pump (hereinafter referred to as W/P) 11, a radiator 12, a thermostat 13, a flow rate adjustment valve 14 and an engine 50.
  • W/P water pump
  • the W/P 11 is cooling medium pumping means pumps cooling water, which is a cooling medium.
  • the W/P 11 is a variable W/P capable of varying the flow rate of the cooling water to be pumped.
  • the W/P 11 may be a mechanical W/P driven by the power of the engine 50.
  • the cooling water pumped by the W/P 11 is supplied to the engine 50.
  • the cooling water pumped by the W/P 11 is specifically supplied to the W/Js 501 and 502.
  • FIG. 2 is a diagram that illustrates the W/Js 501 and 502.
  • FIG. 3 is a diagram that illustrates two cooled regions R1 and R2 of the W/Js 501 and 502.
  • FIG. 4 is an enlarged view of the cooled regions R1 and R2.
  • FIG. 2 is a perspective view of the engine 50 and illustrates a structural outline of the W/Js 501 and 502.
  • FIG. 3 is a plan view of the engine 50 and illustrates the cooled regions R1 and R2.
  • FIG. 4 illustrates an enlarged view of the cooled regions R1 and R2 per cylinder of the engine 50.
  • the cooled region R1 is a region of a cylinder head 52 cooled by the first W/J 501
  • the cooled region R2 is a region of the cylinder head 52 cooled by the second W/J 502.
  • the engine 50 is composed of a cylinder block 51, the cylinder head 52, a gasket 53, and a spark plug 54.
  • a cylinder 51a is formed in the cylinder block 51.
  • the cylinder head 52 is provided to the cylinder block 51 so that the gasket 53 is interposed therebetween.
  • the gasket 53 has high heat isolation.
  • the spark plug 54 is provided to the cylinder head 52 for each cylinder 51a.
  • the cylinder block 51 and the cylinder head 52 form a combustion chamber along with a piston, which is not illustrated.
  • the first W/J 501 causes the cooling water to flow through an exhaust-side portion of the cylinder block 51 and causes the cooling water to flow through an exhaust-side portion of the cylinder head 52 including a predetermined region around the spark plug 54.
  • the predetermined region is a region of the cylinder head 52 around the spark plug 54 that can be cooled. Therefore, the portion of the cylinder head 52 around the spark plug 54 is included in the cooled region R1.
  • the second W/J 502 causes the cooling water to flow through an intake-side portion of the cylinder block 51 and causes the cooling water to flow through an intake-side portion of the cylinder head 52.
  • the W/Js 501 and 502 have a vertical-flow structure in which the cooling water flows in from the cylinder block 51 and flows out of the cylinder head 52.
  • the W/Js 501 and 502 are arranged so that the cooling water flows in from a front side of the engine 50 and flows out of a rear side of the engine 50 on which the power of the engine 50 is output.
  • the cooling apparatus 1A has a plurality of cooling water circulation paths.
  • the cooling water circulation paths include a first circulation path C1 in which the first W/J 501 is incorporated.
  • the cooling water that flows through the first circulation path C1 is pumped by the W/P 11, and flows through the first W/J 501. Then, the cooling water returns to the W/P 11 via the thermostat 13 or via the radiator 12 and the thermostat 13.
  • the radiator 12 is a heat exchanger, and performs a heat exchange between the circulated cooling water and air to thus cool the cooling water.
  • the thermostat 13 changes the flow path that communicates with the inlet side of the W/P 11. Specifically, the thermostat 13 sets the flow path that bypasses the radiator 12 to the communicating state in a case where the temperature of the cooling water is lower than a predetermined value, and sets the flow path that includes the radiator 12 to the communicating state in a case where the temperature of the cooling water is higher than or equal to the predetermined value.
  • the cooling water circulation paths include a second circulation path C2 in which the second W/J 502 is incorporated.
  • the cooling water that flows through the second circulation path C2 is pumped by the W/P 11, and flows through the flow rate adjustment valve 14. Then, the cooling water returns to the W/P 11 via the thermostat 13 or via the radiator 12 and the thermostat 13.
  • the flow rate adjustment valve 14 is provided in a portion of the second circulation path C2 that is located after the flow path branches into the circulation paths C1 and C2 and is located at the upstream side of the engine 50.
  • the flow rate adjustment valve 14 is cooling capacity adjustment means capable of adjusting the cooling capacity of the second W/J 502 by adjusting the flow rate of the cooling water that flows through the second W/J 502.
  • the flow rate adjustment valve 14 is cooling capacity adjustment means capable of suppressing the cooling capacity of the second W/J 502 without suppressing the cooling capacity of the first W/J 501.
  • the flow rate adjustment valve 14 is cooling capacity adjustment means capable of suppressing the cooling capacity of the second W/J 502 without suppressing the cooling capacity of the first W/J 501.
  • the flow rate adjustment valve 14 is cooling capacity adjustment means capable of adjusting the flow rate of the cooling water that flows through the first W/J 501 to increase the cooling capacity of the first W/J 501 in a case where the flow rate of the cooling water that passes through the second W/J 502 is adjusted to suppress the cooling capacity of the second W/J 502.
  • the cooling apparatus 1A is designed to prevent the cooling water that flows through the first circulation path C1 from flowing through the second W/J 502 until one circulation is finished after the cooling water is pumped by the W/P 11. Further, the cooling apparatus 1A is designed to prevent the cooling water that flows through the second circulation path C2 from flowing through the first W/J 501 until one circulation is finished after the cooling water is pumped by the W/P 11. That is, the cooling apparatus 1A is designed to incorporate the first W/J 501 and the second W/J 502 into the mutually different cooling medium circulation paths.
  • the first W/J 501 corresponds to a first cooling medium path
  • the second W/J 502 corresponds to a second cooling medium path.
  • FIG. 5 is a diagram of a structural outline of an ECU 70.
  • the cooling apparatus 1A is further equipped with the ECU 70, which is an electronic control device.
  • the ECU 70 is provided with a microcomputer composed of a CPU 71, a ROM 72 and a RAM 73, and input/output circuits 75 and 76. These structures are mutually connected via a bus 74.
  • various sensors and switches which may include a crank angle sensor 81 for detecting the speed of the engine 50, an airflow meter 82 for measuring the amount of intake air, an accelerator position sensor 83 for detecting the accelerator position, and a temperature sensor 84 sensing the temperature of the cooling water.
  • the load on the engine 50 is detected by the ECU 70 on the basis of the outputs of the airflow meter 82 and the accelerator position sensor 83.
  • Various control objects such as the W/P 11 and the flow rate adjustment valve 14 are electrically connected to the ECU 70.
  • the ROM 72 is configured to store programs that describe various processes executed by the CPU 71 and map data.
  • the ECU 70 functionally realizes various control means, determination means, detection means and calculation means by executing the processes on the basis of the programs stored in the ROM 72 while using a temporary memory area formed in the RAM 73 as necessary.
  • the ECU 70 functionally realizes control means that controls the W/P 11 and the flow rate adjustment valve 14.
  • the control means performs a control to drive the W/P 11 in a case where the cooling water is circulated through the engine 50.
  • the cooling water is caused to flow through the W/J 501 in the case where the cooling water is circulated through the engine 50.
  • the case where the cooling water is circulated through the engine 50 is, for example, a case where the engine is in operation.
  • the case where the cooling water is circulated through the engine 50 may be another case where a predetermined time has passed after the engine cold start.
  • the control means performs a control to have a smaller opening angle of the flow rate adjustment valve 14 than that at high load when the engine 50 is at low or medium load in the case where the cooling water that is circulated through the engine 50 is caused to flow through the second W/J 502.
  • the flow rate of the cooling water that flows through the second W/J 502 at low or medium load of the engine 50 is made lower than that at high load.
  • the control means is capable of fully opening the flow rate adjustment valve 14 when the engine 50 is at high load.
  • the control means is capable of fully closing the flow rate adjustment valve 14 or opening the valve 14 in a mode in which boiling of the cooling water can be prevented.
  • the control means is capable of driving the W/P 11 to perform a control to have a larger ejection amount as the engine 50 is at a higher speed.
  • the W/P 11, the flow rate adjustment valve 14 and the ECU 70 correspond to the cooling medium control means.
  • the ECU 70 determines whether the engine is in operation (step S1). When a negative determination is made, the ECU 70 stops the W/P 11 (step S7). Then, the ECU 70 ends the present flowchart once. In contrast, when a positive determination is made, the ECU 70 drives the W/P 11 (step S2). Thus, the cooling water always flows through the first W/J 501 in the case where the cooling water is circulated through the engine 50.
  • the ECU 70 detects the load on the engine 50 (step S3).
  • the ECU 70 determines whether the load detected is high (step S4).
  • the ECU 70 opens the flow rate adjustment valve 14 (step S5).
  • the ECU 70 opens the flow rate adjustment valve 14 at an angle smaller than that at high load including closing the valve (step S6).
  • the flow rate of the cooling water that flows through the second W/J 502 at low or medium load is made lower than that at high load.
  • FIG. 7 is a diagram that illustrates the heat transfer ratio and the surface area ratio of the combustion chamber in association with the crank angle. As illustrated in FIG. 7 , the heat transfer ratio rises around the top dead center in the compression stroke. The surface area ratio of the cylinder head 52 and that of the piston becomes comparatively high around the top dead center in the compression stroke. Thus, the cooling loss is greatly influenced by the temperature of the cylinder head 52.
  • Knocking depends on the compression-end temperature. It is seen that the cylinder 51 a has a high surface area ratio in the intake and compression strokes that influence the compression-end temperature. Thus, it is seen that knocking is greatly influenced by the temperature of the cylinder 51 a. Further, knocking is more greatly influenced by the exhaust-side portion of the cylinder 51a than the intake-side portion because intake air hits the wall surface of the combustion chamber.
  • the cooling apparatus 1A is configured to cause the cooling water to flow through the first W/J 501, so that the exhaust-side portion of the engine 50 can be cooled.
  • the exhaust-side portion of the cylinder 51a can be cooled.
  • the exhaust-side portion of the engine 50 is a portion that is likely to have high temperature due to exhaust.
  • the cooling apparatus 1A causes the cooling water to flow through the first W/J 501, so that the occurrence of knocking can be suppressed appropriately.
  • the reliability of the engine 50 can be secured.
  • the cooling apparatus 1A restricts the flow rate of the cooling water that flows through the second W/J 502, so that the cooling loss in the intake-side portion of the engine 50 can be reduced. This reduces the cooling loss in the intake-side portion of the cylinder head 52. Further, the cooling apparatus 1A has the vertical flow structure that is relatively easily manufacturable because the first W/J 501 is provided on the exhaust side of the engine 50 and the second W/J 502 is provided on the intake side of the engine 50.
  • the cooling apparatus 1A is based on the above knowledge and is capable of locally changing the state of the heat transfer by the simple vertical-flow structure. It is thus possible to achieve both reduction in the cooling loss and improvement in knocking and to thus improve the thermal efficiency.
  • the cooling apparatus 1A causes the cooling water to always flow through the first W/J 501, and is thus capable of suppressing the occurrence of knocking appropriately. Simultaneously, the reliability of the engine 50 can be ensured properly.
  • the flow rate of the cooling water caused to flow through the second W/J 502 is made lower than that at high load, and the cooling loss at low or medium load can be reduced. It is thus possible to achieve both reduction in the cooling loss and improvement in knocking and to thus improve the thermal efficiency.
  • the cooling apparatus 1A in the case where the flow rate adjustment valve 14 adjusts the flow rate of the cooling water that flows through the second W/J 502 so as to suppress the cooling capacity of the second W/J 502, the flow rate of the cooling water that flows through the first W/J 501 is adjusted to increase the cooling capacity of the first W/J 501.
  • the cooling apparatus 1A is capable of further cooling the intake air. As a result, the occurrence of knocking can be suppressed more appropriately.
  • FIG. 8 is a diagram of a structural outline of a cooling apparatus 1B.
  • the cooing apparatus 1B is further provided with an EGR apparatus 21 and a first branch portion 22, as compared with the cooling apparatus 1A.
  • the EGR apparatus 21 performs exhaust recirculation in the engine 50.
  • the engine 50 is an engine that employs exhaust recirculation.
  • the EGR apparatus 21 is equipped with an EGR pipe 211, an EGR flow rate adjustment valve 212, and an EGR cooler 213.
  • the EGR pipe 211 feeds the exhaust back to the engine 50.
  • the EGR cooler 213 cools the exhaust returned to the engine 50 by a heat exchange with the cooling water.
  • the EGR cooler 213 corresponds to a cooling device.
  • the first branch portion 22 derives a flow that passes through the EGR cooler 213 from the cooling water that flows through the first W/J 501.
  • the cooling water that flows through the first W/J 501 is cooling water circulated through the first circulation path C1.
  • branching of the cooling water that flows through the first W/J 501 is achieved by branching off from the cooling water that flows through a portion of the first circulation path C1 located between the branching into the circulation paths C1 and C2 and the merging thereof.
  • the first branch portion 22 splits the cooling water that flows through the first W/J 501 at the downstream side of the first W/J 501, and the split cooling water flows through the EGR cooler 213.
  • the cooling water that flows through the EGR cooler 213 may be merged in a portion of the first circulation path C 1 located at the downstream side of the first branch portion 22 and at the upstream side of the merging point of the circulation paths C1 and C2.
  • the EGR cooler 213 is provided for the purpose of preventing the occurrence of knocking in the recirculation of the exhaust at high temperatures through the engine 50.
  • the occurrence of a temperature rise of the exhaust to be recirculated or boiling of the cooling water is an issue of concern when the flow rate of the cooling water caused to flow through the EGR cooler 213 is reduced or the circulation of the cooling water through the EGR cooler 213 is stopped along with reduction in the cooling loss of the engine 50.
  • the cooling apparatus 1B derives, from the cooling water that flows through the first W/J 501, a flow of cooing water that passes through the EGR cooler 213.
  • the cooling apparatus 1B makes it possible to use the EGR apparatus 21 appropriately. It is thus possible to improve the fuel economy by the exhaust recirculation. Since the cooling water that flows through the first W/J 501 is split at the downstream side of the first W/J 501, it is possible to prevent the cooling performance of the first W/J 501 by being affected.
  • FIG. 9 is a diagram of a structural outline of a cooling apparatus 1C.
  • the cooling apparatus 1C is further equipped with a heater core 31 and a second branch portion 32, as compared with the cooling apparatus 1A.
  • a similar change may be applied to the cooling apparatus 1B, for example.
  • the heater core 31 is used for heating in the vehicle, and heats air by a thermal exchange with the circulated cooling water.
  • the heater core 31 corresponds to a heater.
  • the second branch portion 32 derives a flow that passes through the heater core 31 from the cooling water that flows through the first W/J 501. Specifically, the cooling water that passes through the first W/J 501 is split at the downstream side of the first W/J 501, and split water is caused to flow through the heater core 31.
  • the cooing water that flows through the heater core 31 can be merged with the original flow in a portion of the first circulation path C 1 located at the downstream side of the second branch portion 32 and at the upstream side of the merging point of the circulation paths C1 and C2.
  • the cooling apparatus 1C derives a flow of cooling water that passes through the heater core 31 from the cooling water that flows through the first W/J 501.
  • the cooling apparatus 1C is capable of suppressing degradation of heating performance of the vehicle that may take place along with reduction in the cooing loss of the engine 50. That is, it is possible to use heating appropriately.
  • the cooling water having a large amount of heat receiving can be utilized for heating by causing the cooling water that flows through the first W/J 501 to branch off at the downstream side of the first W/J 501. As a result, it is possible to appropriately improve the heating performance.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP10860673.2A 2010-12-13 2010-12-13 Dispositif de refroidissement de moteur Withdrawn EP2653687A4 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/072416 WO2012081081A1 (fr) 2010-12-13 2010-12-13 Dispositif de refroidissement de moteur

Publications (2)

Publication Number Publication Date
EP2653687A1 true EP2653687A1 (fr) 2013-10-23
EP2653687A4 EP2653687A4 (fr) 2014-11-05

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10860673.2A Withdrawn EP2653687A4 (fr) 2010-12-13 2010-12-13 Dispositif de refroidissement de moteur

Country Status (5)

Country Link
US (1) US20130247848A1 (fr)
EP (1) EP2653687A4 (fr)
JP (1) JP5541371B2 (fr)
CN (1) CN103261616B (fr)
WO (1) WO2012081081A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016001988A1 (fr) * 2014-06-30 2016-01-07 日産自動車株式会社 Moteur à combustion interne
EP3163057A4 (fr) * 2014-06-30 2017-06-21 Nissan Motor Co., Ltd Moteur à combustion interne
JP6264325B2 (ja) * 2015-06-05 2018-01-24 トヨタ自動車株式会社 内燃機関の制御装置
JP6225950B2 (ja) * 2015-06-23 2017-11-08 トヨタ自動車株式会社 内燃機関の冷却装置
JP6465315B2 (ja) * 2016-11-30 2019-02-06 株式会社Ｓｕｂａｒｕ 多気筒エンジン冷却装置
JP6791089B2 (ja) * 2017-10-11 2020-11-25 株式会社豊田自動織機 シリンダヘッドの冷却装置
CN107956569A (zh) * 2017-11-28 2018-04-24 东风商用车有限公司 一种发动机冷却管理系统

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2807245A (en) * 1954-10-19 1957-09-24 Gen Motors Corp Water heated intake manifold and control system therefor
US4109617A (en) * 1976-12-22 1978-08-29 Ford Motor Company Controlled flow cooling system for low weight reciprocating engine
JP2537043B2 (ja) * 1986-12-12 1996-09-25 ヤマハ発動機株式会社 車両用２サイクル水冷エンジンの冷却装置
JPH08177483A (ja) 1994-12-26 1996-07-09 Nissan Motor Co Ltd 多気筒エンジンの冷却装置
JP3885260B2 (ja) * 1996-09-30 2007-02-21 マツダ株式会社 エンジンの冷却装置
US5735238A (en) * 1996-10-21 1998-04-07 Ford Global Technologies, Inc. Heat management system for internal combustion engines
JP2001164988A (ja) * 1999-12-07 2001-06-19 Toyota Motor Corp シリンダヘッド
KR100559848B1 (ko) * 2002-09-27 2006-03-10 현대자동차주식회사 엔진의 냉각 시스템
DE10306695A1 (de) * 2003-02-18 2004-09-16 Daimlerchrysler Ag Brennkraftmaschine mit einem Kühlmittelkreislauf
JP4100279B2 (ja) * 2003-07-16 2008-06-11 三菱自動車工業株式会社 シリンダヘッド先行冷却式のエンジン
DE10332947A1 (de) * 2003-07-19 2005-02-03 Daimlerchrysler Ag Brennkraftmaschine für ein Kraftfahrzeug
JP4175389B2 (ja) * 2006-06-05 2008-11-05 トヨタ自動車株式会社 エンジンの冷却装置
DE502007001624D1 (de) * 2007-01-17 2009-11-12 Ford Global Tech Llc Integriertes Motorkühlsystem
JP4372799B2 (ja) * 2007-02-19 2009-11-25 トヨタ自動車株式会社 内燃機関の制御システム
JP4998339B2 (ja) 2008-03-12 2012-08-15 トヨタ自動車株式会社 内燃機関の冷却装置
JP2010169010A (ja) * 2009-01-23 2010-08-05 Aisin Seiki Co Ltd 内燃機関の冷却装置
EP2322785B1 (fr) * 2009-07-30 2018-09-19 Ford Global Technologies, LLC Système de refroidissement
EP2309106B1 (fr) * 2009-07-30 2017-06-07 Ford Global Technologies, LLC circuit de refroidissement
EP2508727B1 (fr) * 2009-12-01 2016-03-09 Toyota Jidosha Kabushiki Kaisha Dispositif de refroidissement de moteur
DE102010002082B4 (de) * 2010-02-18 2013-09-19 Ford Global Technologies, Llc Separat gekühlter Abgassammler zur Aufrechterhaltung einer No-Flow Strategie des Zylinderblockkühlmittelmantels
WO2012120668A1 (fr) * 2011-03-09 2012-09-13 トヨタ自動車株式会社 Dispositif de commande de moteur

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2012081081A1 *

Also Published As

Publication number Publication date
JPWO2012081081A1 (ja) 2014-05-22
CN103261616B (zh) 2015-04-01
CN103261616A (zh) 2013-08-21
WO2012081081A1 (fr) 2012-06-21
EP2653687A4 (fr) 2014-11-05
US20130247848A1 (en) 2013-09-26
JP5541371B2 (ja) 2014-07-09

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