WO2004020799A1 - エンジンの冷却装置 - Google Patents
エンジンの冷却装置 Download PDFInfo
- Publication number
- WO2004020799A1 WO2004020799A1 PCT/JP2003/010785 JP0310785W WO2004020799A1 WO 2004020799 A1 WO2004020799 A1 WO 2004020799A1 JP 0310785 W JP0310785 W JP 0310785W WO 2004020799 A1 WO2004020799 A1 WO 2004020799A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cylinder
- control plate
- port side
- water jacket
- exhaust port
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/064—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces the packing combining the sealing function with other functions
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
- F02F1/14—Cylinders with means for directing, guiding or distributing liquid stream
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F11/00—Arrangements of sealings in combustion engines
- F02F11/002—Arrangements of sealings in combustion engines involving cylinder heads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
- F16J15/0818—Flat gaskets
-
- 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
- F01P2003/021—Cooling cylinders
-
- 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
- F01P2003/024—Cooling 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
- F01P2007/143—Controlling of coolant flow the coolant being liquid using restrictions
-
- 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
- F01P2050/00—Applications
- F01P2050/30—Circuit boards
-
- 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
Definitions
- the present invention relates to a cooling device for an engine, and more particularly, to a cooling device for an engine having a water jacket that opens to the surface of a cylinder head.
- a cylinder head having an intake port formed on one side and an exhaust port formed on the other side and a cylinder wall formed on a cylinder block and defining a cylinder bore are surrounded by the cylinder head.
- a water jacket opened on the surface of the mouthpiece, a gasket sandwiched between the cylinder head and the cylinder block to seal between the two, and a waterjacket provided on the gasket.
- Japanese Patent Application Laid-Open Publication No. 2000-502700 is known.
- the cooling water in the outer jacket is controlled by the control plate. It controls the flow of air to efficiently cool the engine.
- the flow of the cooling water in the water jacket is controlled as in the cooling device for the engine in the above-mentioned publication, the following problems still occur.
- the first problem is that in the combustion chamber of the engine, It is known that the temperature on the exhaust port side is higher, and this is the same on the exhaust port side of the cylinder wall.
- a cooling water passage for supplying cooling water to the water jacket is provided in the cylinder block, but a cylinder wall provided at a position close to an inlet of the cooling water passage is provided.
- the cooling water temperature in the vicinity is higher than the cooling water temperature in the vicinity of the cylinder wall provided at a position distant from the inlet, and the cooling water temperature in the latter is higher than that of the cylinder wall.
- the cooled cylinder wall is not sufficiently cooled, and the cylinder wall is deformed due to thermal expansion, which causes problems such as oil rise and poor sealing of the gasket.
- the engine cooling device has a cylinder head having an intake port formed on one side and an exhaust port formed on the other side, and a cylinder bore formed in a cylinder block.
- a water jacket that surrounds the periphery of the partitioned cylinder wall and is opened on the surface of the cylinder block, and a gasket that is sandwiched between the cylinder head and the cylinder block to seal between them And a control plate provided in the gasket and inserted into the water jacket.
- the control plate is formed in an arc shape along the shape of the water jacket, and is provided only on the intake port side.
- the engine cooling device includes a cylinder head having an intake port formed on one side and an exhaust port formed on the other side, and a cylinder bore formed in a cylinder block.
- the outer jacket which surrounds the periphery of the cylinder wall to be opened and is opened on the surface of the cylinder block, and the gasket which is sandwiched between the cylinder head and the cylinder block to seal therebetween.
- a control plate provided in the gasket and inserted into the water jacket.
- the control plate is formed in an arc shape along the shape of the water jacket, is provided on each of the intake port side and the exhaust port side, and is formed between the control plate and the cylinder wall on the exhaust port side.
- the gap is characterized by being narrower than the gap between the control plate and the cylinder wall on the intake port side.
- the engine cooling device has an intake on one side.
- a cylinder head that forms a port and has an exhaust port formed on the other side, and a cylinder wall that is formed in the cylinder block and surrounds a cylinder wall that defines a cylinder bore, and is opened on the surface of the cylinder block.
- a plurality of the cylinder bores are provided, and the control plate is formed in an arc shape along the shape of the water jacket, and is provided on each of the intake port side and the exhaust port side for each cylinder bore. Further, the distance between the control plate and the cylinder wall in the cylinder bore provided at a position close to the inlet of the cooling water passage for supplying the cooling water to the water jacket is provided at a position distant from the inlet. It is characterized by being set wider than the distance between the control plate and the cylinder wall in the cylinder bore.
- the engine cooling device includes a cylinder head having an intake port formed on one side and an exhaust port formed on the other side, and a cylinder bore formed in a cylinder block.
- a control plate provided in the gasket and inserted into the water jacket.
- a plurality of cylinder bores are provided, and the control plate is formed in an arc shape along the shape of the water jacket.
- the control plates on the intake port side provided on each of the intake port side and the exhaust port side and provided for each cylinder bore are connected to each other, and the control plates on the exhaust port side provided for each cylinder bore are provided. Are interconnected,
- the cooling water reaches a predetermined temperature. It is characterized by a thermo valve that opens when it rises.
- Fig. 1 is a plan view showing the surface of the cylinder block.
- FIG. 2 is a plan view showing a gasket according to the first embodiment of the present invention.
- FIG. 3 is a cross-sectional view taken along a line II-II of FIG.
- FIG. 4 is a plan view showing a gasket according to a second embodiment of the present invention.
- FIG. 5 is a cross-sectional view taken along a line V_V in FIG.
- FIG. 6 is a cross-sectional view taken along the line BB of FIG. 4 showing an aspect different from that of FIG. 5,
- FIG. 7 is a plan view showing a gasket of the third embodiment of the present invention, and
- FIG. 9 is a plan view showing a gasket according to a fourth embodiment of the present invention, and
- FIG. 9 is an enlarged view showing the thermovalve in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
- FIG. 1 is a plan view of the surface of a cylinder hook 1 in a three-cylinder engine viewed from a cylinder head (not shown).
- the cylinder block 1 has three cylinder walls 3 and each cylinder block 3
- the inside of the damper wall 3 is a cylinder bore 2.
- a water jacket 4 is formed surrounding each cylinder wall 3 and communicates with each other.
- the water jacket 4 is opened on the surface of the cylinder block 1 and further formed on the water jacket 4.
- a cooling water passage 5 for supplying cooling water is formed.
- the cylinder block 1 has an oil hole 6 through which lubricating oil flows, a bolt hole 7 used to fasten the cylinder head to the cylinder block 1, and a blow-by hole 8 through which blow-by gas flows. Is formed.
- FIG. 2 shows a gasket 11 in the present embodiment, and the gasket 11 is sandwiched between a cylinder head and a cylinder block 1 to seal them. .
- the two-dot chain line in FIG. 2 indicates the positions of the water jacket 4 and the cooling water passage 5 in the cylinder block 1.
- the gasket 11 is provided with a combustion chamber hole 12, an oil hole 13, a bolt hole 14, and a blow-by hole 15 in accordance with the cylinder bore 2, oil hole 6, bolt hole 7, and blow-by hole 8, respectively. Have been.
- a water hole 16 is provided in the vicinity of the combustion chamber hole 12 at the position furthest away from the cooling water passage 5 and at a position where the water jacket 4 overlaps with the water jacket 4.
- the cooling water flowing into the jacket 4 flows through the water jacket 4 and then flows out to the cylinder head side through the water hole 16.
- a control plate protruding toward the cylinder block 1 is provided in the upper jacket 4 on the intake port side in the gasket 11.
- the control plate 21 is formed in an arc shape along the shape of the water jacket 4 as shown by a dotted line in FIG. As shown in the figure, in this embodiment, the control plate 21 is not provided at the position where the water hole 17 is formed, but the control plate 21 is placed along the water hole. It may be provided.
- FIG. 3 is a cross-sectional view taken along the line III-III of FIG. 2.
- the control plate 21 is provided so as to protrude into the water jacket 4 by a predetermined amount, and the upper end of the control plate 21 is Welded to gasket 1 1.
- the flow rate of the cooling water flowing into the water jacket 4 from the cooling water passage 5 is larger at the exhaust port side than at the intake port side. It becomes.
- the cooling efficiency of the cylinder wall 3 by the cooling water on the exhaust port side increases, so that the temperature difference between the intake port side and the exhaust port side of the cylinder wall 3 decreases.
- the volume of the control plate 21 flows through the water jacket 4 on the intake port side.
- the flow rate of the cooling water decreases, and the flow rate of the cooling water flowing through the water jacket 4 on the exhaust port side increases accordingly.
- the cooling efficiency of the cooling water on the exhaust port side is increased. Therefore, since the cylinder wall 3 on the exhaust port side is cooled more than the cylinder wall 3 on the intake port side, the temperature difference between the cylinder wall 3 generated between the intake port side and the exhaust port side is reduced. It is possible to prevent the cylinder wall 3 on the exhaust port side from being deformed by thermal expansion.
- FIGS. 2 and 3 show a gasket 11 showing a second embodiment of the present invention.
- the gasket 11 is provided with water jackets on both the intake port side and the exhaust side of the engine.
- a control plate 21 protruding toward the cylinder block 1 is provided in the gate 4, and the control plate 21 also follows the shape of the water jacket 4 in this embodiment as shown by the dotted line in FIG. It is formed in an arc shape.
- the end of the control plate 21 on the intake port side is formed up to the end of the water hole 17 formed on the intake port side.
- the end of the control plate 21 on the exhaust port side is formed up to the end of the water hole 17 drilled on the exhaust port side, and another control plate 21 is provided between the two water holes 17. Is formed.
- FIG. 5 shows a cross section taken along the line V--V in FIG. 4, where T is the thickness of the control plate 21 and a is the distance between the cylinder wall 3 and the surface of the control plate 21. This figure shows not only the VV section of FIG. 4 but also the control plates 21.
- the plate thickness T of the control plate 21 is made constant, and the distance a between the control plate 21 and the cylinder wall 3 is made different between the intake port side and the exhaust port side, so that the cylinder wall 3 is formed. It is designed to prevent deformation due to thermal expansion.
- the cooling water flowing between the cylinder wall 3 and the control plate 21 on the exhaust port side will cause The boundary layer on the wall surface is thinner than the boundary layer on the wall surface of the cylinder wall 3 on the intake port side.
- the cooling efficiency of the cylinder wall 3 on the exhaust port side is increased, and the temperature difference generated between the intake port side and the exhaust port side of the cylinder wall 3 can be reduced, so that the exhaust port side can be reduced. It is possible to prevent the cylinder wall 3 from being deformed by thermal expansion.
- FIG. 5 the distance between the center of the control plate 21 and the cylinder wall 3 is shown.
- the thickness T of the control plate 21 may be made different, and the thickness T of the control plate 21 on the exhaust port side may be made larger than the thickness T of the intake port side.
- the distance a between the control plate 21 and the cylinder wall 3 on the exhaust port side is smaller than the distance a on the intake port side, so that the wall surface of the cylinder wall 3 on the exhaust port side
- the boundary layer at the port is thinner than the boundary layer at the intake port.
- the temperature difference between the intake port side and the exhaust port side of the cylinder wall 3 is the same as when the distance between the control plate 21 and the cylinder wall 3 is different between the exhaust port side and the intake port side. Since it can be reduced, it is possible to prevent the cylinder wall 3 on the exhaust port side from being deformed by thermal expansion.
- the thickness T of the control plate 21 is constant, but as shown in FIG. 6, the thickness of the control plate 21 is changed in the depth direction of the water jacket 4. I'm sorry.
- the thickness T of the gasket 11 side of the control plate 21 is set to be large, and the thickness T of the bottom side of the water jacket 4 is reduced, so that the gasket 11 side is formed. Is smaller than the value of the distance a on the bottom side of the water jacket 4.
- FIG. 7 shows a gasket 11 according to a third embodiment of the present invention.
- a control plate 21 is arranged similarly to the second embodiment, and control is performed on both the intake port side and the exhaust port side. A plate 21 is provided.
- the distance between the control plate 21 and the cylinder wall 3 at the cylinder bore 2 at a position close to the inlet of the cooling water passage 5 is set to the distance between the control plate 21 and the control plate 21 at the cylinder bore 2 at a position away from the inlet
- the distance between the cylinder and the cylinder wall 3 is set wider.
- the control plate 2 surrounding the cylinder bore 2 adjacent to the inlet of the cooling water passage 5 described above.
- the thickness of the control plate 21 surrounding the cylinder bore 2 at the position furthest away from the cooling water passage 5 is set to be smaller than the thickness of the control plate 21.
- the cooling water that has just flowed into the water jacket 4 from the cooling water passage 5 is not heated by the cylinder wall 3 or the like, and has a slightly lower flow velocity but a sufficiently high cooling effect.
- the cooling water that has reached the cylinder wall 3 at the position furthest away from the cooling water passage 5 has already been cooled by the other cylinder wall 3, and the water temperature has risen. Is lower than the cooling water cooling efficiency near the inlet of the cooling water passage 5.
- the cylinder wall 3 at the position furthest away from the cooling water passage 5 becomes hotter than the other cylinder walls 3 due to insufficient cooling, and is deformed by thermal expansion, resulting in oil rise and gasket. In this case, the sealing failure of 11 will be caused. Further, in the case of a multi-cylinder engine as in the present embodiment, when only one of the cylinder bores 2 becomes high in temperature, the amount of fuel injected into the combustion chamber is limited, or the advance angle of the piston is limited. As a result, the engine performance cannot be fully exhibited.
- the distance a between the control plate 21 and the cylinder wall 3 is made different for each cylinder bore 2 so that the cylinder wall 3 at the position of the cylinder bore 2 furthest away from the cooling water passage 5 is separated.
- the cylinder wall 3 located farthest from the cooling water passage 5 can be efficiently cooled, so that the temperature difference generated between the cylinder walls 3 can be reduced, and The cylinder wall 3 at the separated position can be prevented from being deformed by thermal expansion.
- the distance between the control plate 21 and the cylinder wall is kept constant while the thickness of the control plate 21 is constant as in the second embodiment.
- the same result as described above can be obtained even if the thickness of the control plate 21 is changed, and as shown in FIG. 5, the plate thickness of the control plate 21 on the gasket side and the bottom surface of the water jacket 4 is reduced. It may be different.
- FIG. 8 shows a gasket 11 showing a fourth embodiment of the present invention.
- the control plates 21 are provided on the intake port side and the exhaust port side of each of the cylinder bores 2.
- the control plates 21 on the exhaust port side of the adjacent cylinder bores 2 are connected to each other, and the control plates 21 on the intake port side are also connected to each other.
- thermo valve 22 that opens when the temperature of the cooling water reaches a predetermined temperature is provided, and a water hole 1 of the gasket 11 is provided. Except for the position overlapping with 7, the water jacket is divided by the control plate 21 into an inner peripheral chamber on the cylinder wall side and an outer peripheral chamber on the outer side.
- FIG. 9 is an enlarged view of the above-mentioned thermo valve 22.
- the solid line shows the state where the thermo valve 22 is open, and the two-dot chain line shows the state where the thermo valve 22 is closed.
- This thermo valve is composed of two bimetallic materials. One end of each bimetallic material is fixed to the end of the control plate 21 on the intake port side and the exhaust port side, and the other end. Are provided so as to be in contact with each other when the thermo-valves 22 are closed.
- thermo valve 22 When the temperature of the cooling water around the thermo valve 22 reaches a predetermined temperature, the bimetal material is deformed toward the cylinder wall 3, and the thermo valve 22 is opened. When the cooling water has not reached the predetermined temperature, the thermo valve 22 is in a closed state.
- the temperature of the cylinder bore 2 is not high, and it is not necessary to cool the cylinder bore 2 with cooling water.
- the cooling water flows into the water jacket by the water pump and starts cooling the cylinder wall.
- the cooling water hinders a rise in the temperature of the cylinder wall, which increases the time it takes for the engine to warm up, and the fuel efficiency during warm-up operation is generally worse than the fuel efficiency after warming-up. The longer the time it takes to warm up, the worse the fuel economy will be.
- the temperature of the cylinder bore 2 rises when the engine is started, and until the cooling water around the cylinder wall 3 in the inner peripheral chamber 4a reaches a predetermined temperature, the thermo valve 2 2 Is closed, the cooling water hardly flows, and has no effect of cooling the cylinder wall 3.Therefore, the cylinder wall 3 quickly rises in temperature without being cooled by the cooling water, and the engine Warm-up is performed promptly.
- the thermo valve 22 keeps the closed state, so even if the cooling water flows into the water jacket 4 from the cooling water passage 5, the cooling water flows into the inner peripheral chamber 4a. Without flowing through the outer peripheral chamber 4 b, it flows to the cylinder head side through the water hole 17 as it is.
- the bimetal material is deformed and the thermo valve 22 opens, so the cooling water from the cooling water passage 5 is cooled by the thermo valve. It flows into the inner peripheral chamber 4a through 22.
- the thermo-valve 22 is opened, the cooling water flows directly from the thermo-valve 22 into the inner peripheral chamber 4a, and the cooling water flows through the inner peripheral chamber 4a as it is. Therefore, the cylinder bore 2 is cooled well.
- the time required for warming up the engine can be shortened, and after the engine has been warmed up, the cooling water can be circulated to the inner peripheral chamber 4a side to effectively provide the cylinder bore. 2 can be cooled.
- the space between the cylinder wall 3 and the control plate 21 is made different so that the cooling water near the cylinder wall 3 on the intake port side and the exhaust port side.
- the first aspect by increasing the flow rate of the cooling water on the exhaust port side of the cylinder bore, it is possible to prevent the cylinder wall on the exhaust port side from being deformed by thermal expansion.
- the boundary layer on the wall surface of the cylinder wall on the exhaust port side of the cylinder bore is thinned, so that the cylinder wall on the exhaust port side can be prevented from being deformed by thermal expansion. it can.
- the boundary layer on the wall surface of the cylinder wall in the cylinder bore located at a position separated from the cooling water passage is thinned, thereby separating from the cooling water passage 5.
- the cylinder wall at the separated position can be prevented from being deformed by thermal expansion.
- the water jacket is divided into the cylinder wall side and the outer peripheral side by the control plate, so that the engine warm-up operation is quickly performed, and the cooling of the cylinder bore is performed after the warm-up is performed. It is done effectively.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/526,246 US7047915B2 (en) | 2002-08-30 | 2003-08-26 | Engine cooling device |
EP03791302A EP1541830A4 (en) | 2002-08-30 | 2003-08-26 | MOTOR COOLING DEVICE |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002256203A JP4085253B2 (ja) | 2002-08-30 | 2002-08-30 | エンジンの冷却装置 |
JP2002-256203 | 2002-08-30 |
Publications (1)
Publication Number | Publication Date |
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WO2004020799A1 true WO2004020799A1 (ja) | 2004-03-11 |
Family
ID=31972940
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/010785 WO2004020799A1 (ja) | 2002-08-30 | 2003-08-26 | エンジンの冷却装置 |
Country Status (4)
Country | Link |
---|---|
US (1) | US7047915B2 (ja) |
EP (2) | EP2578836A3 (ja) |
JP (1) | JP4085253B2 (ja) |
WO (1) | WO2004020799A1 (ja) |
Cited By (2)
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DE102005048650A1 (de) * | 2005-10-11 | 2007-04-12 | Daimlerchrysler Ag | Fertigungsverfahren und Bauweise für Gussbauteile mit Formhohlräumen |
DE202007009222U1 (de) * | 2007-03-12 | 2008-07-31 | Hengst Gmbh & Co.Kg | Dichtung als Kanalwandung |
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US7766902B2 (en) * | 2003-08-13 | 2010-08-03 | Wisconsin Alumni Research Foundation | Microfluidic device for drug delivery |
JP4446989B2 (ja) * | 2006-09-08 | 2010-04-07 | トヨタ自動車株式会社 | シリンダブロックおよび内燃機関 |
US8986250B2 (en) * | 2008-08-01 | 2015-03-24 | Wisconsin Alumni Research Foundation | Drug delivery platform utilizing hydrogel pumping mechanism |
US8795259B2 (en) * | 2008-08-01 | 2014-08-05 | Wisconsin Alumni Research Foundation | Drug delivery platform incorporating hydrogel pumping mechanism with guided fluid flow |
US20100313860A1 (en) * | 2009-06-15 | 2010-12-16 | Gm Global Technology Operations, Inc. | Apparatus for removal of oil from positive crankcase ventilation system |
US8328757B2 (en) * | 2010-01-08 | 2012-12-11 | Wisconsin Alumni Research Foundation | Bladder arrangement for microneedle-based drug delivery device |
JP5466143B2 (ja) * | 2010-12-16 | 2014-04-09 | トヨタ自動車株式会社 | 軸部材のすべり軸受構造 |
US9429063B2 (en) * | 2014-03-14 | 2016-08-30 | Hyundai Motor Company | Cylinder block |
KR101619278B1 (ko) * | 2014-10-29 | 2016-05-10 | 현대자동차 주식회사 | 냉각수 제어밸브를 갖는 엔진시스템 |
JP6354732B2 (ja) * | 2015-11-02 | 2018-07-11 | 株式会社豊田自動織機 | シリンダブロックおよびエンジン本体 |
US9951712B2 (en) * | 2015-11-30 | 2018-04-24 | Ford Global Technologies, Llc | Internal combustion engine with interbore cooling |
US9790888B2 (en) | 2015-11-30 | 2017-10-17 | Ford Global Technologies, Llc | Internal combustion engine |
CN106438134B (zh) * | 2016-11-30 | 2019-03-15 | 天津市日博自动化物流装备有限公司 | 一种发动机用防水透气布总成 |
CN108049984A (zh) * | 2018-01-23 | 2018-05-18 | 中国重汽集团济南动力有限公司 | 一种控制机体缸盖冷却水流场的汽缸垫 |
JP7255543B2 (ja) * | 2020-04-08 | 2023-04-11 | トヨタ自動車株式会社 | 内燃機関 |
CN114278454A (zh) * | 2020-09-27 | 2022-04-05 | 深圳臻宇新能源动力科技有限公司 | 水套隔片、冷却装置和发动机 |
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US6138619A (en) * | 1995-12-22 | 2000-10-31 | Ab Volvo | Device for control of flow of cooling medium |
JP2001020738A (ja) * | 1999-07-09 | 2001-01-23 | Toyota Motor Corp | 内燃機関の冷却装置 |
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JP2936888B2 (ja) * | 1992-05-07 | 1999-08-23 | 日産自動車株式会社 | 内燃機関のシリンダブロック |
DE4407984A1 (de) * | 1994-03-10 | 1995-09-14 | Opel Adam Ag | Kühlsystem für eine Hubkolbenbrennkraftmaschine |
JPH09189258A (ja) * | 1995-12-29 | 1997-07-22 | Suzuki Motor Corp | 内燃機関のシリンダブロック |
DE10011143B4 (de) * | 2000-03-07 | 2013-09-19 | Bayerische Motoren Werke Aktiengesellschaft | Flüssigkeitsgekühlte Brennkraftmaschine mit einem Zweikreiskühlsystem |
US6581550B2 (en) * | 2000-06-30 | 2003-06-24 | Toyota Jidosha Kabushiki Kaisha | Cooling structure of cylinder block |
-
2002
- 2002-08-30 JP JP2002256203A patent/JP4085253B2/ja not_active Expired - Fee Related
-
2003
- 2003-08-26 WO PCT/JP2003/010785 patent/WO2004020799A1/ja active Application Filing
- 2003-08-26 EP EP12193264.4A patent/EP2578836A3/en not_active Withdrawn
- 2003-08-26 US US10/526,246 patent/US7047915B2/en not_active Expired - Fee Related
- 2003-08-26 EP EP03791302A patent/EP1541830A4/en not_active Withdrawn
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US6138619A (en) * | 1995-12-22 | 2000-10-31 | Ab Volvo | Device for control of flow of cooling medium |
JP2001020738A (ja) * | 1999-07-09 | 2001-01-23 | Toyota Motor Corp | 内燃機関の冷却装置 |
Non-Patent Citations (1)
Title |
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See also references of EP1541830A4 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005048650A1 (de) * | 2005-10-11 | 2007-04-12 | Daimlerchrysler Ag | Fertigungsverfahren und Bauweise für Gussbauteile mit Formhohlräumen |
DE102005048650B4 (de) * | 2005-10-11 | 2007-09-13 | Daimlerchrysler Ag | Fertigungsverfahren und Bauweise für Gussbauteile mit Formhohlräumen |
DE202007009222U1 (de) * | 2007-03-12 | 2008-07-31 | Hengst Gmbh & Co.Kg | Dichtung als Kanalwandung |
Also Published As
Publication number | Publication date |
---|---|
JP4085253B2 (ja) | 2008-05-14 |
US7047915B2 (en) | 2006-05-23 |
EP1541830A1 (en) | 2005-06-15 |
JP2004092547A (ja) | 2004-03-25 |
EP1541830A4 (en) | 2011-07-20 |
US20050268868A1 (en) | 2005-12-08 |
EP2578836A2 (en) | 2013-04-10 |
EP2578836A3 (en) | 2014-12-03 |
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