WO2016135820A1 - 内燃機関の吸気系配管構造 - Google Patents
内燃機関の吸気系配管構造 Download PDFInfo
- Publication number
- WO2016135820A1 WO2016135820A1 PCT/JP2015/055006 JP2015055006W WO2016135820A1 WO 2016135820 A1 WO2016135820 A1 WO 2016135820A1 JP 2015055006 W JP2015055006 W JP 2015055006W WO 2016135820 A1 WO2016135820 A1 WO 2016135820A1
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- WO
- WIPO (PCT)
- Prior art keywords
- cylinder
- intercooler
- combustion engine
- internal combustion
- intake
- Prior art date
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 70
- 230000007423 decrease Effects 0.000 claims 1
- 238000001816 cooling Methods 0.000 description 61
- 239000007788 liquid Substances 0.000 description 61
- 230000000052 comparative effect Effects 0.000 description 17
- 230000000694 effects Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/10091—Air intakes; Induction systems characterised by details of intake ducts: shapes; connections; arrangements
- F02M35/10144—Connections of intake ducts to each other or to another device
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
- F02B29/0475—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly the intake air cooler being combined with another device, e.g. heater, valve, compressor, filter or EGR cooler, or being assembled on a special engine location
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/10242—Devices or means connected to or integrated into air intakes; Air intakes combined with other engine or vehicle parts
- F02M35/10268—Heating, cooling or thermal insulating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/104—Intake manifolds
- F02M35/1045—Intake manifolds characterised by the charge distribution between the cylinders/combustion chambers or its homogenisation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/104—Intake manifolds
- F02M35/112—Intake manifolds for engines with cylinders all in one line
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to an intake system piping structure of an internal combustion engine.
- Some vehicles such as automobiles, have an intercooler that cools intake air that has been supercharged by a turbocharger and has risen in temperature. By doing in this way, the intake efficiency to the internal combustion engine combustion chamber of a vehicle can be improved.
- JP2009-270508A discloses an internal combustion engine with an intercooler in which an intake manifold and an intercooler are integrated.
- the intercooler is arranged so that the cylinder line direction center line of the internal combustion engine and the width direction center line of the intercooler substantially coincide with each other in consideration of intake air distribution.
- the cylinder line direction center line of the internal combustion engine is the center between the axial direction center lines of two cylinders that are provided farthest apart from each other in the cylinder line.
- the intercooler may not be arranged in this way due to the arrangement of auxiliary machines such as alternators. If the intercooler cannot be arranged so that the center line in the cylinder row direction of the internal combustion engine coincides with the center line in the width direction of the intercooler, the distribution of the inflowing air will be significantly different among the cylinders. . Therefore, even when the center line in the cylinder row direction of the internal combustion engine cannot coincide with the center line in the width direction of the intercooler, it is desirable that the distribution of the inflowing air is not significantly different among the cylinders.
- An object of the present invention is to distribute the inflowing air even if the intercooler cannot be arranged so that the center line in the cylinder row direction of the internal combustion engine and the center line in the width direction of the intercooler are substantially coincident. Is not to make a significant difference between them.
- an intake system piping structure of an internal combustion engine has an intake manifold connected to an end-side first cylinder and an end-side second cylinder that are provided farthest from each other in a cylinder row in which a plurality of cylinders are arranged. And an intercooler connected to the intake manifold.
- the intake system piping structure of the internal combustion engine is such that the center in the width direction on the intake inlet side of the intercooler and the center in the width direction on the manifold side of the intercooler are the center line in the axial direction of the end side first cylinder and the end side first.
- An intercooler is disposed offset from the central cylinder row direction center line with the axial center line of the two cylinders toward the end side second cylinder side.
- the intake system piping structure of the internal combustion engine is such that the offset amount from the center line in the cylinder direction in the width direction on the intake inlet side of the intercooler is the center line in the cylinder line direction in the center in the width direction on the manifold side of the intercooler.
- the intercooler is arranged so as to be larger than the offset amount from the.
- FIG. 1 is a front view of an internal combustion engine with an intercooler in the present embodiment.
- FIG. 2 is a plan view of the internal combustion engine with an intercooler in the present embodiment.
- FIG. 3 is a front view of the internal combustion engine with an intercooler in the first comparative example.
- FIG. 4 is a front view of the internal combustion engine with an intercooler in the second comparative example.
- FIG. 1 is a front view of an internal combustion engine with an intercooler in the present embodiment.
- FIG. 2 is a plan view of the internal combustion engine with an intercooler in the present embodiment.
- the intake system piping structure of the internal combustion engine 1 with an intercooler is shown.
- the internal combustion engine 1 with an intercooler includes a liquid cooling intercooler 11 (corresponding to an intercooler), an intake manifold 12, an intake passage member 13, and a cylinder block 14.
- the intercooler-equipped internal combustion engine 1 includes a first cylinder CY1 (corresponding to an end first cylinder), a second cylinder CY2, a third cylinder CY3, and a fourth cylinder CY4 (corresponding to an end second cylinder).
- the intercooler-equipped internal combustion engine 1 is provided with an auxiliary machine such as an alternator 21 around it.
- Liquid cooling intercooler 11 cools the air passing through the inside. Then, the density of intake air that has been compressed and heated by a supercharger or the like is increased, and the intake efficiency of each cylinder is increased.
- the flow path in the liquid cooling intercooler 11 is formed in such a shape that the intake air flows in a direction substantially along the side surface 11 s of the liquid cooling intercooler 11.
- the liquid cooling intercooler 11 is connected to the inlet of the manifold portion 12a.
- the intake manifold 12 includes a manifold portion 12a and a branch portion 12b.
- the air flow paths in the manifold portion 12a and the branch portion 12b are also formed in a shape that substantially conforms to these outer shapes.
- the inlet of the manifold portion 12a is connected to the outlet of the liquid cooling intercooler 11.
- four branch portions 12b extend from the manifold portion 12a.
- the four branch portions 12b are connected to the cylinders CY1 to CY4 in the cylinder block 14.
- the intake passage member 13 causes the intake air compressed by a supercharger (not shown) to flow into the liquid cooling intercooler 11.
- the flow path in the intake passage member 13 is also formed in the intake passage member 13 in a direction substantially along the outer shape of the intake passage member 13.
- the intake passage member 13 is connected to the bottom inlet (connecting portion 11f) of the liquid cooling intercooler 11 from the fourth cylinder CY4 side.
- the cylinder block 14 includes four cylinders of a first cylinder CY1, a second cylinder CY2, a third cylinder CY3, and a fourth cylinder CY4.
- the first cylinder CY1, the second cylinder CY2, the third cylinder CY3, and the fourth cylinder CY4 are arranged in a line in the cylinder row direction (left-right direction in FIG. 1).
- the first cylinder CY1 and the fourth cylinder CY4 are provided farthest from each other.
- Each cylinder in the cylinder block 14 is connected to four branch portions 12 b of the intake manifold 12.
- FIG. 1 shows a cylinder row direction center line C1 at the center of the axial center line CT1 of the first cylinder CY1 and the axial center line CT4 of the fourth cylinder CY4.
- FIG. 1 also shows a center line C ⁇ b> 2 in the width direction of the liquid cooling intercooler 11.
- the center line C2 in the width direction of the liquid cooling intercooler 11 is a center line between the side walls 11s excluding the protrusions of the liquid cooling intercooler 11 in the width direction of the liquid cooling intercooler 11.
- FIG. 1 shows that the distance between the center line C2 and the left and right side walls 11s is equal w.
- FIG. 1 also shows an orthogonal line CL that is orthogonal to the axial center line CT1 of the first cylinder CY1 and the axial center line CT4 of the fourth cylinder CY4.
- the center C2a in the width direction on the intake inlet side of the liquid cooling intercooler 11 and the center C2b in the width direction on the intake manifold 12 side of the liquid cooling intercooler 11 are
- the liquid cooling intercooler 11 is arranged so as to be offset to the fourth cylinder CY4 side with respect to the center line C1 in the cylinder row direction between the axial centerline CT1 of the first cylinder CY1 and the axial centerline CT4 of the fourth cylinder CY4. It is installed.
- the offset amount of the center C2a in the width direction on the intake inlet side of the liquid cooling intercooler 11 from the cylinder row direction center line C1 is the cylinder row direction of the center C2b in the width direction on the intake manifold 12 side of the liquid cooling intercooler 11.
- the liquid cooling intercooler 11 is disposed so as to be larger than the offset amount from the center line C1.
- the center C2a in the width direction of the liquid cooling intercooler 11 on the inlet side of the liquid cooling intercooler 11 is more than the center C2b in the width direction of the liquid cooling intercooler 11 on the outlet side of the liquid cooling intercooler 11.
- the liquid cooling intercooler 11 is disposed so as to be inclined toward the fourth cylinder CY4 side.
- the liquid-cooled intercooler 11 may be arranged so that the center C2 in the width direction of the liquid-cooled intercooler 11 does not coincide with the cylinder row direction center line C1 in relation to an auxiliary machine such as the alternator 21. Even in such a case, in the present embodiment, the liquid cooling intercooler 11 is provided near the fourth cylinder CY4, and the center C2a in the width direction on the inlet side of the liquid cooling intercooler 11 is in the width direction on the outlet side. The liquid cooling intercooler 11 is disposed so as to be closer to the fourth cylinder CY4 than the center C2b. Therefore, air is allowed to flow into the fourth cylinder CY4 through the paths indicated by arrows A1 and A2 shown in FIG. 1 without providing a sharply bent portion in the flow path of the air flowing into the fourth cylinder CY4. Can do.
- the air inflow path to the fourth cylinder CY4 can be a path without a sharp bend, the air of almost the same amount as that of the first cylinder CY1 is caused to flow into the fourth cylinder CY4. be able to. As a result, the inflow amount of air from the first cylinder CY1 to the fourth cylinder CY4 can be prevented from being significantly different among the cylinders.
- the effect of this embodiment will be described in more detail by comparison with an internal combustion engine of a later comparative example.
- the intake passage member 13 is connected from the fourth cylinder CY4 side to the intake inlet side of the liquid cooling intercooler 11.
- the intake passage member 13 is disposed such that the bottom portion 13a of the intake passage member 13 in the direction extending below the liquid cooling intercooler 11 is parallel to the orthogonal line CL.
- connection part 11f of the liquid cooling intercooler 11 and the intake passage member 13 the cross-sectional area is expanded as much as possible so that the intake efficiency is increased.
- the intake passage member 13 is extended so that its bottom portion 13a is parallel to the orthogonal line CL. Connect directly to the bottom of the cooler 11. In other words, the intake passage member 13 is directly connected to the bottom of the liquid cooling intercooler 11 while extending parallel to the orthogonal line CL without standing up. Therefore, the overall length of the intake system piping structure of the internal combustion engine 1 can be shortened in the vertical direction, and a compact internal combustion engine 1 can be provided.
- connection portion 11 f between the intake passage member 13 and the liquid cooling intercooler 11 is the bottom of the liquid cooling intercooler 11.
- the distance from the connection portion 11 f to the bottom portion 13 a of the intake passage member 13 is gradually shortened from the fourth cylinder CY 4 side toward the first cylinder CY 1.
- the intake passage member 13 can be directly connected to the bottom of the liquid cooling intercooler 11 so as to be parallel to the orthogonal line CL. Therefore, although the liquid-cooled intercooler 11 is inclined, the overall length of the intake system piping structure of the internal combustion engine 1 can be shortened in the vertical direction, and a compact internal combustion engine 1 can be provided.
- the liquid cooling is performed so that the lower end 11b on the fourth cylinder CY4 side of the liquid cooling intercooler 11 coincides with the upper end 13b of the portion extending in parallel with the orthogonal line CL of the intake passage member 13.
- the intercooler 11 and the intake passage member 13 are connected.
- the lower end 11 c on the first cylinder CY 1 side of the liquid cooling intercooler 11 is disposed below the upper end of the intake passage member 13. And the liquid cooling intercooler 11 and the intake passage member 13 are connected under such an arrangement relationship.
- the liquid cooling intercooler 11 and the intake passage member 13 are connected, so that the intake passage member 13 does not stand up below the liquid cooling intercooler 11 and directly on the bottom of the liquid cooling intercooler 11. Can be connected. Therefore, the compact length of the internal combustion engine 1 can be provided by shortening the vertical length of the entire intake system piping structure of the internal combustion engine 1.
- the liquid cooling intercooler 11 and the intake manifold 12 are connected so that the upper end 11d of the liquid cooling intercooler 11 on the fourth cylinder CY4 side coincides with the lower surface 12c of the manifold portion 12a. Is done. Further, the upper end 11e on the first cylinder CY1 side of the liquid cooling intercooler 11 is disposed at a position lower than the lower surface 12c of the manifold portion 12a. And the liquid cooling intercooler 11 and the manifold part 12a are connected under such an arrangement relationship.
- the right upper end 11d of the liquid-cooled intercooler 11 is directly connected to the lower surface 12c of the manifold portion 12a. Therefore, the vertical length of the entire intake system piping structure of the internal combustion engine 1 is shortened, A compact internal combustion engine 1 can be provided.
- FIG. 3 is a front view of the internal combustion engine with an intercooler in the first comparative example.
- the internal combustion engine with an intercooler 101 in the first comparative example includes a liquid cooling intercooler 111, an intake manifold 112, an intake passage member 113, and a cylinder block 114.
- the intercooler-equipped internal combustion engine 101 includes a first cylinder CY1, a second cylinder CY2, a third cylinder CY3, and a fourth cylinder CY4.
- the reference numerals are different, but the function of each element is the same as that of this embodiment.
- the center line C101 in the cylinder row direction substantially coincides with the center line C102 in the width direction of the liquid cooling intercooler.
- the liquid cooling intercooler 111 is arranged. In this way, the intake air distribution is not significantly different among the cylinders.
- FIG. 4 is a front view of the internal combustion engine with an intercooler in the second comparative example.
- the internal combustion engine with an intercooler 201 in the second comparative example includes a liquid cooling intercooler 211, an intake manifold 212, an intake passage member 213, and a cylinder block 214.
- the intercooler-equipped internal combustion engine 201 includes a first cylinder CY1, a second cylinder CY2, a third cylinder CY3, and a fourth cylinder CY4.
- the reference numerals are different, but the function of each element is the same as that of the present embodiment.
- the alternator 121 could not be disposed at a desired position due to interference with the liquid cooling intercooler 111.
- the width direction of the liquid-cooled intercooler 211 extends from the cylinder row direction center line C201 to the fourth cylinder CY4 side (right side in FIG. 4).
- the liquid-cooled intercooler 211 is arranged so that the center line C202 is offset.
- the connection portion between the liquid-cooled intercooler 211 and the manifold portion 212a has a sharp bend due to the connection with the manifold portion 212a. Cr1 is generated. Further, the intake passage member 213 has a restriction that the position of the upright portion 213e cannot be moved. Therefore, if the liquid-cooled intercooler 211 is simply translated to the right as described above, the bend around the connecting portion between the liquid-cooled intercooler 211 and the intake passage member 213 is steeper than that of the first comparative example. The portion Cr2 is generated.
- the internal combustion engine 1 since the sharply bent portion does not occur, the amount of air flowing into the fourth cylinder CY4 is not significantly reduced unlike the second comparative example. By doing in this way, in this embodiment, distribution of the air which flows in can be prevented from differing remarkably between cylinders.
- the internal combustion engine 1 according to the present embodiment has the above-described configuration, the length in the vertical direction of the entire intake system piping structure of the internal combustion engine 1 can be shortened. And the compact internal combustion engine 1 can be provided. Accordingly, for example, there is an advantage that another auxiliary machine can be disposed under the intake passage member 13 or a work space can be provided.
- the first cylinder CY1 corresponds to the end-side first cylinder
- the fourth cylinder CY4 corresponds to the end-side fourth cylinder.
- the fourth cylinder CY4 corresponds to the end-side first cylinder.
- the first cylinder CY1 may correspond to the end-side fourth cylinder.
- the liquid cooling intercooler 11 is arranged so that the center C2b in the width direction of the liquid cooling intercooler 11 at the outlet of the liquid cooling intercooler 11 is offset from the cylinder row direction center line C1 to the first cylinder CY1 side. Will be. Further, the center C2a in the width direction of the liquid cooling intercooler 11 on the inlet side of the liquid cooling intercooler 11 is more than the center C2b in the width direction of the liquid cooling intercooler 11 on the outlet side of the liquid cooling intercooler 11.
- the liquid cooling intercooler 11 is disposed so as to be inclined to the side.
- the intake passage member 13 is connected to the connection portion 11f of the liquid cooling intercooler 11 from the first cylinder CY1 side.
- an in-line four-cylinder internal combustion engine has been described as an example.
- the number of cylinders may be larger or smaller.
- the cylinders at both ends of these cylinders correspond to the first end cylinder and the second end cylinder.
- the internal combustion engine having the in-line cylinder arrangement is described as an example.
- the internal combustion engine having the V-type cylinder arrangement as well as the in-line cylinder arrangement, one of the cylinder rows arranged in two rows is arranged.
- the above embodiment can be similarly applied.
- the cylinders at both ends of the three cylinders correspond to the end-side first cylinder and the end-side second cylinder.
- the liquid-cooled intercooler 11 has been described as an example.
- the intercooler may be an air-cooled intercooler instead of the liquid-cooled intercooler.
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Abstract
Description
Claims (5)
- 複数の気筒が並ぶ気筒列において互いに最も離れて設けられた端側第1気筒と端側第2気筒に接続された吸気マニフォルドと、前記吸気マニフォルドに接続されたインタークーラと、を備える内燃機関の吸気系配管構造であって、
前記インタークーラの吸気入口側における幅方向の中心と、前記インタークーラのマニフォルド側における幅方向の中心が、前記端側第1気筒の軸方向中心線と前記端側第2気筒の軸方向中心線との中央の気筒列方向中心線よりも前記端側第2気筒側にオフセットし、
前記インタークーラの吸気入口側における幅方向の中心の前記気筒列方向中心線からのオフセット量が、前記インタークーラのマニフォルド側における幅方向の中心の前記気筒列方向中心線からのオフセット量よりも大きくなるように、前記インタークーラが配設される、
内燃機関の吸気系配管構造。 - 請求項1に記載の内燃機関の吸気系配管構造であって、
前記端側第2気筒側から前記インタークーラの吸気入口側に接続する吸気通路部材を備え、
前記吸気通路部材の底部が、前記端側第1気筒の軸方向中心線と前記端側第2気筒の軸方向中心線とに直交する直交線と平行である、内燃機関の吸気系配管構造。 - 請求項2に記載の内燃機関の吸気系配管構造であって、
前記吸気通路部材は前記端側第2気筒側から前記端側第1気筒側に向かうにつれて、前記吸気通路部材と前記インタークーラとの接続部から前記吸気通路部材の底部までの距離が短くなる、内燃機関の吸気系配管構造。 - 請求項3に記載の内燃機関の吸気系配管構造であって、
前記インタークーラの前記端側第2気筒側の下端が前記吸気通路部材の上端に一致するとともに、前記インタークーラの前記端側第1気筒側の下端が前記吸気通路部材の上端よりも下方に配置される、内燃機関の吸気系配管構造。 - 請求項1乃至請求項4のいずれか一項に記載の内燃機関の吸気系配管構造であって、
前記吸気マニフォルドはマニフォルド部とブランチ部とを有し、
前記インタークーラの前記端側第2気筒側の上端が前記マニフォルド部の下面に一致するとともに、前記インタークーラの前記端側第1気筒側の上端が前記マニフォルド部の下面よりも下方に配置される、内燃機関の吸気系配管構造。
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
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KR1020177023509A KR101851917B1 (ko) | 2015-02-23 | 2015-02-23 | 내연 기관의 흡기계 배관 구조 |
PCT/JP2015/055006 WO2016135820A1 (ja) | 2015-02-23 | 2015-02-23 | 内燃機関の吸気系配管構造 |
CA2977335A CA2977335C (en) | 2015-02-23 | 2015-02-23 | Intake system piping structure of internal combustion engine |
RU2017129811A RU2652263C1 (ru) | 2015-02-23 | 2015-02-23 | Трубопроводная конструкция системы впуска двигателя внутреннего сгорания |
US15/552,638 US10655575B2 (en) | 2015-02-23 | 2015-02-23 | Intake system piping structure of internal combustion engine |
EP15883118.0A EP3263863A4 (en) | 2015-02-23 | 2015-02-23 | Intake system piping structure for internal combustion engine |
CN201580076697.3A CN107250502B (zh) | 2015-02-23 | 2015-02-23 | 内燃机的进气系统配管构造 |
MX2017010454A MX2017010454A (es) | 2015-02-23 | 2015-02-23 | Estructura de tuberias del sistema de admision de motor de combustion interna. |
JP2017501571A JP6409952B2 (ja) | 2015-02-23 | 2015-02-23 | 内燃機関の吸気系配管構造 |
Applications Claiming Priority (1)
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PCT/JP2015/055006 WO2016135820A1 (ja) | 2015-02-23 | 2015-02-23 | 内燃機関の吸気系配管構造 |
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US (1) | US10655575B2 (ja) |
EP (1) | EP3263863A4 (ja) |
JP (1) | JP6409952B2 (ja) |
KR (1) | KR101851917B1 (ja) |
CN (1) | CN107250502B (ja) |
CA (1) | CA2977335C (ja) |
MX (1) | MX2017010454A (ja) |
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WO2020254847A1 (ja) * | 2019-06-21 | 2020-12-24 | 日産自動車株式会社 | 熱交換装置 |
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2015
- 2015-02-23 RU RU2017129811A patent/RU2652263C1/ru active
- 2015-02-23 US US15/552,638 patent/US10655575B2/en not_active Expired - Fee Related
- 2015-02-23 JP JP2017501571A patent/JP6409952B2/ja active Active
- 2015-02-23 CA CA2977335A patent/CA2977335C/en active Active
- 2015-02-23 EP EP15883118.0A patent/EP3263863A4/en not_active Withdrawn
- 2015-02-23 CN CN201580076697.3A patent/CN107250502B/zh active Active
- 2015-02-23 WO PCT/JP2015/055006 patent/WO2016135820A1/ja active Application Filing
- 2015-02-23 KR KR1020177023509A patent/KR101851917B1/ko active IP Right Grant
- 2015-02-23 MX MX2017010454A patent/MX2017010454A/es unknown
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Also Published As
Publication number | Publication date |
---|---|
EP3263863A1 (en) | 2018-01-03 |
CA2977335A1 (en) | 2016-09-01 |
CN107250502A (zh) | 2017-10-13 |
US20180017026A1 (en) | 2018-01-18 |
US10655575B2 (en) | 2020-05-19 |
RU2652263C1 (ru) | 2018-04-25 |
CA2977335C (en) | 2018-01-02 |
MX2017010454A (es) | 2017-11-28 |
KR101851917B1 (ko) | 2018-06-07 |
EP3263863A4 (en) | 2018-01-24 |
JPWO2016135820A1 (ja) | 2017-11-30 |
CN107250502B (zh) | 2020-04-14 |
KR20170102027A (ko) | 2017-09-06 |
JP6409952B2 (ja) | 2018-10-24 |
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