JP7384110B2 - intake device - Google Patents
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- JP7384110B2 JP7384110B2 JP2020086720A JP2020086720A JP7384110B2 JP 7384110 B2 JP7384110 B2 JP 7384110B2 JP 2020086720 A JP2020086720 A JP 2020086720A JP 2020086720 A JP2020086720 A JP 2020086720A JP 7384110 B2 JP7384110 B2 JP 7384110B2
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- 238000002485 combustion reaction Methods 0.000 claims description 18
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 238000003780 insertion Methods 0.000 description 5
- 230000037431 insertion Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 2
- 230000004308 accommodation Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
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- 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
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Description
本発明は、内燃機関の吸気装置に関する。 The present invention relates to an intake system for an internal combustion engine.
従来、この種の吸気装置として、例えば特許文献１に示すものが知られている。こうした吸気装置は、吸気を流入させる開口部を有したサージタンク（収容部）と、サージタンクに接続されてサージタンク内の吸気を内燃機関の複数の気筒に分配してそれぞれ供給する複数の吸気管（供給管）とを備えている。各吸気管は、経路の途中が所定の曲率半径を有して湾曲した構成になっている。 Conventionally, as this type of intake device, the one shown in Patent Document 1, for example, is known. Such an intake device consists of a surge tank (accommodation part) that has an opening through which intake air flows, and a plurality of intake air units that are connected to the surge tank and distribute the intake air in the surge tank to multiple cylinders of an internal combustion engine and supply them to each cylinder. pipe (supply pipe). Each intake pipe has a curved portion with a predetermined radius of curvature.
ところで、上述のような吸気装置では、各吸気管の湾曲下流部の断面において、湾曲内側の吸気通路内面に接する２つの円弧形状部（コーナー部）の曲率半径を、湾曲外側の吸気通路内面に接する２つの円弧形状部（コーナー部）の曲率半径よりも小さくすることで、各吸気管内の湾曲内側と湾曲外側との間での吸気の流速差を減少させて湾曲下流部を流れる吸気の圧力損失を低減するようにしている。 By the way, in the above-mentioned intake device, in the cross section of the curved downstream part of each intake pipe, the radius of curvature of the two circular arc-shaped parts (corner parts) that contact the inner surface of the intake passage on the inner side of the curve is set to the inner surface of the intake passage on the outer side of the curve. By making the radius of curvature smaller than the radius of curvature of the two contacting arc-shaped parts (corner parts), the difference in flow velocity of intake air between the inside curve and the outside curve in each intake pipe is reduced, and the pressure of the intake air flowing in the downstream part of the curve is reduced. We are trying to reduce losses.
しかしながら、上述のような吸気装置では、吸気がサージタンクから各吸気管へ流れる際の圧力損失を低減する工夫が特になされていないため、吸気がサージタンクから各吸気管へ流れる際の圧力損失を低減する上では改善の余地を残すものとなっている。 However, in the above-mentioned intake device, no particular measures have been taken to reduce the pressure loss when the intake air flows from the surge tank to each intake pipe. There is still room for improvement in terms of reduction.
本発明は、このような従来技術に存在する問題点に着目してなされた。その目的は、吸気が収容部から供給管へ流れる際の圧力損失を効果的に低減できる吸気装置を提供することにある。 The present invention was made by focusing on the problems existing in the prior art. The purpose is to provide an intake device that can effectively reduce pressure loss when intake air flows from the storage section to the supply pipe.
以下、上記課題を解決するための手段及びその作用効果について記載する。
上記課題を解決する吸気装置は、吸気を収容可能な収容部と、前記収容部に接続され、前記吸気を前記収容部内に流入させる流入管と、前記収容部における前記流入管と対向しない位置に接続され、前記流入管から前記収容部内に流入した前記吸気を内燃機関側へ供給する供給管と、を備え、前記供給管における前記供給管が延びる方向と直交する断面は、コーナー部が円弧状をなす多角形状をなしており、前記供給管における前記収容部との接続部の断面の複数の前記コーナー部のうち、前記流入管からの前記吸気が前記供給管に流れてくる側に位置する前記コーナー部の曲率半径は、他の前記コーナー部の曲率半径よりも小さくなっていることを要旨とする。
Below, means for solving the above problems and their effects will be described.
An intake device that solves the above problem includes a storage section that can accommodate intake air, an inflow pipe that is connected to the storage section and allows the intake air to flow into the storage section, and a position in the storage section that does not face the inflow pipe. a supply pipe that is connected to the inflow pipe and supplies the intake air that has flowed into the housing portion from the inflow pipe to the internal combustion engine side, and a cross section of the supply pipe perpendicular to the direction in which the supply pipe extends has a corner portion shaped like an arc. It has a polygonal shape, and is located on the side where the intake from the inflow pipe flows into the supply pipe, among the plurality of corner parts of the cross section of the connection part with the storage part of the supply pipe. The gist is that the radius of curvature of the corner portion is smaller than the radius of curvature of the other corner portions.
この構成によれば、供給管の接続部の断面における流入管からの吸気が流れてくる側のコーナー部の曲率半径を小さくすることで、接続部における曲率半径を小さくしたコーナー部側、すなわち流入管からの吸気が流れてくる側の流路断面積を稼ぐことができる。このため、流入管から収容部内に流入した吸気が供給管内に円滑に流れるため、接続部での乱流の発生が抑制される。したがって、吸気が収容部から供給管へ流れる際の圧力損失を効果的に低減できる。 According to this configuration, by reducing the radius of curvature of the corner part of the cross section of the connection part of the supply pipe on the side where the intake air from the inflow pipe flows, The cross-sectional area of the flow path on the side where the intake air flows from the pipe can be increased. Therefore, the intake air that has flowed into the storage section from the inflow pipe flows smoothly into the supply pipe, so that generation of turbulent flow at the connection part is suppressed. Therefore, the pressure loss when the intake air flows from the storage section to the supply pipe can be effectively reduced.
以下、吸気装置をインテークマニホールドに具体化した一実施形態を図面に従って説明する。
図１及び図２に示すように、吸気装置の一例としてのインテークマニホールド１１は、合成樹脂などによって構成され、例えば直列４気筒の車載用の内燃機関１２に取り付けられる。インテークマニホールド１１は、吸気を収容可能な収容部の一例としてのサージタンク１３と、サージタンク１３に接続されて吸気をサージタンク１３内に流入させる流入管１４と、流入管１４からサージタンク１３内に流入した吸気を内燃機関１２側へ分配して供給する例えば４つの供給管の一例としての分岐管１５とを備えている。
An embodiment in which an intake device is implemented as an intake manifold will be described below with reference to the drawings.
As shown in FIGS. 1 and 2, an intake manifold 11 as an example of an intake device is made of synthetic resin or the like, and is attached to, for example, an in-line four-cylinder internal combustion engine 12 for use in a vehicle. The intake manifold 11 includes a surge tank 13 serving as an example of a storage section capable of accommodating intake air, an inflow pipe 14 connected to the surge tank 13 to allow intake air to flow into the surge tank 13, and an inflow pipe 14 that connects the intake air into the surge tank 13. For example, a branch pipe 15 is provided as an example of four supply pipes for distributing and supplying intake air flowing into the internal combustion engine 12 to the internal combustion engine 12 side.
４つの分岐管１５は、サージタンク１３における流入管１４と対向しない位置に、互いに並ぶようにそれぞれ一端側が接続されている。本実施形態において、４つの分岐管１５の並ぶ方向は並び方向Ｘとされ、並び方向Ｘは図１における紙面と直交する方向及び図２における左右方向とそれぞれ一致している。 The four branch pipes 15 are each connected at one end to a position in the surge tank 13 that does not face the inflow pipe 14 so as to be lined up with each other. In this embodiment, the direction in which the four branch pipes 15 are lined up is the line direction X, which coincides with the direction perpendicular to the plane of paper in FIG. 1 and the left-right direction in FIG. 2, respectively.
流入管１４は、並び方向Ｘにおけるサージタンク１３の一端側に接続されている。流入管１４におけるサージタンク１３側とは反対側の端部には、外周側に突出するフランジ部１６が設けられている。フランジ部１６には、複数の挿通孔１６ａが形成されている。図示は省略するが、流入管１４におけるサージタンク１３側とは反対側の端部は、フランジ部１６において各挿通孔１６ａに挿通されるボルトにより、スロットルバルブを有したスロットルボディに固定されている。また、図示は省略するが、サージタンク１３には、内燃機関１２の運転に伴って発生するブローバイガスをサージタンク１３内に導入するガス導入部が設けられている。 The inflow pipe 14 is connected to one end of the surge tank 13 in the arrangement direction X. A flange portion 16 that protrudes toward the outer circumference is provided at the end of the inflow pipe 14 on the side opposite to the surge tank 13 side. A plurality of insertion holes 16a are formed in the flange portion 16. Although not shown, the end of the inflow pipe 14 on the side opposite to the surge tank 13 is fixed to a throttle body having a throttle valve by bolts inserted into each insertion hole 16a in the flange portion 16. . Further, although not shown, the surge tank 13 is provided with a gas introduction portion that introduces blow-by gas generated during operation of the internal combustion engine 12 into the surge tank 13.
各分岐管１５は、サージタンク１３の下方側から上方側に向かってサージタンク１３の外周を囲むように湾曲して延びている。すなわち、各分岐管１５は、湾曲部１７を形成するように延びている。各分岐管１５の先端には、外周側に突出する共通のフランジ部１８が設けられている。 Each branch pipe 15 extends in a curved manner from the lower side of the surge tank 13 toward the upper side so as to surround the outer periphery of the surge tank 13. That is, each branch pipe 15 extends so as to form a curved portion 17. A common flange portion 18 protruding toward the outer circumference is provided at the tip of each branch pipe 15.
フランジ部１８には、複数の挿通孔１８ａが形成されている。図示は省略するが、各分岐管１５におけるサージタンク１３側とは反対側の端部は、フランジ部１８において各挿通孔１８ａに挿通されるボルトにより、内燃機関１２のシリンダヘッドに固定されている。これにより、各分岐管１５が内燃機関１２における各気筒の燃焼室に連通される。 A plurality of insertion holes 18a are formed in the flange portion 18. Although not shown, the end of each branch pipe 15 on the side opposite to the surge tank 13 is fixed to the cylinder head of the internal combustion engine 12 by bolts inserted into the respective insertion holes 18a in the flange portion 18. . Thereby, each branch pipe 15 is communicated with the combustion chamber of each cylinder in the internal combustion engine 12.
図３及び図４に示すように、各分岐管１５における分岐管１５が延びる方向と直交する断面は、４つのコーナー部１９が円弧状をなす略矩形状をなしている。すなわち、各分岐管１５は、サージタンク１３との接続部２０及び接続部２０よりも内燃機関１２側に位置する湾曲部１７を含むほぼ全体の断面が略矩形状をなしている。各分岐管１５が接続部２０においてサージタンク１３内に開口する方向と、流入管１４からサージタンク１３内に吸気が流入する方向とは、ほぼ直交している。 As shown in FIGS. 3 and 4, the cross section of each branch pipe 15 perpendicular to the direction in which the branch pipe 15 extends has a substantially rectangular shape with four corner portions 19 having arcuate shapes. That is, each branch pipe 15 has a substantially rectangular cross section over the entirety thereof, including the connecting portion 20 with the surge tank 13 and the curved portion 17 located closer to the internal combustion engine 12 than the connecting portion 20 . The direction in which each branch pipe 15 opens into the surge tank 13 at the connecting portion 20 and the direction in which intake air flows into the surge tank 13 from the inflow pipe 14 are substantially orthogonal.
図３～図５に示すように、各分岐管１５におけるサージタンク１３との接続部２０の断面の４つのコーナー部２１～２４のうち、流入管１４からの吸気が各分岐管１５に流れてくる側に位置する２つのコーナー部２１，２２の曲率半径は、他の２つのコーナー部２３，２４の曲率半径よりも小さくなっている。 As shown in FIGS. 3 to 5, intake air from the inflow pipe 14 flows into each branch pipe 15 among the four corner parts 21 to 24 of the cross section of the connection part 20 with the surge tank 13 in each branch pipe 15. The radius of curvature of the two corner portions 21 and 22 located on the opposite side is smaller than the radius of curvature of the other two corner portions 23 and 24.
すなわち、各分岐管１５におけるサージタンク１３との接続部２０の断面の４つのコーナー部２１～２４のうち、並び方向Ｘにおける流入管１４側に位置する２つのコーナー部２１，２２の曲率半径は、並び方向Ｘにおける流入管１４側とは反対側に位置する２つのコーナー部２３，２４の曲率半径よりも小さくなっている。 That is, among the four corner parts 21 to 24 of the cross section of the connection part 20 with the surge tank 13 in each branch pipe 15, the radius of curvature of the two corner parts 21 and 22 located on the inflow pipe 14 side in the arrangement direction X is , is smaller than the radius of curvature of the two corner portions 23 and 24 located on the opposite side to the inflow pipe 14 side in the arrangement direction X.
この場合、各分岐管１５の接続部２０の断面の４つのコーナー部２１～２４のうち、並び方向Ｘにおける流入管１４側に位置する２つのコーナー部２１，２２の曲率半径は互いに同じになっており、且つ並び方向Ｘにおける流入管１４側とは反対側に位置する２つのコーナー部２３，２４の曲率半径は互いに同じになっている。 In this case, among the four corner parts 21 to 24 of the cross section of the connecting part 20 of each branch pipe 15, the two corner parts 21 and 22 located on the inflow pipe 14 side in the arrangement direction X have the same radius of curvature. The radii of curvature of the two corner portions 23 and 24 located on the side opposite to the inflow pipe 14 side in the arrangement direction X are the same.
図３及び図６に示すように、各分岐管１５の湾曲部１７の断面における４つのコーナー部２５～２８のうち、内周側に位置する２つコーナー部２５，２６の曲率半径は、外周側に位置する２つのコーナー部２７，２８の曲率半径よりも小さくなっている。この場合、内周側に位置する２つコーナー部２５，２６の曲率半径は互いに同じになっており、且つ外周側に位置する２つのコーナー部２７，２８の曲率半径は互いに同じになっている。 As shown in FIGS. 3 and 6, among the four corner sections 25 to 28 in the cross section of the curved section 17 of each branch pipe 15, the radius of curvature of the two corner sections 25 and 26 located on the inner circumferential side is The radius of curvature is smaller than the radius of curvature of the two corner portions 27 and 28 located on the sides. In this case, the radii of curvature of the two corner portions 25 and 26 located on the inner periphery side are the same, and the radii of curvature of the two corner portions 27 and 28 located on the outer periphery side are the same as each other. .
なお、各分岐管１５の断面における４つのコーナー部１９の曲率半径は、接続部２０から湾曲部１７に向かって徐々に変化している。すなわち、接続部２０の断面におけるコーナー部２１，２２，２３，２４の曲率半径は、湾曲部１７に向かうにつれて湾曲部１７の断面におけるコーナー部２５，２７，２６，２８の曲率半径へとそれぞれ徐々に変化する。図５では、上側が各分岐管１５の湾曲部１７の内周側に対応し、下側が各分岐管１５の湾曲部１７の外周側に対応する。 Note that the radius of curvature of the four corner portions 19 in the cross section of each branch pipe 15 gradually changes from the connecting portion 20 toward the curved portion 17. That is, the radius of curvature of the corner parts 21, 22, 23, 24 in the cross section of the connecting part 20 gradually becomes the radius of curvature of the corner parts 25, 27, 26, 28 in the cross section of the curved part 17 as it approaches the curved part 17. Changes to In FIG. 5, the upper side corresponds to the inner circumferential side of the curved part 17 of each branch pipe 15, and the lower side corresponds to the outer circumferential side of the curved part 17 of each branch pipe 15.
次に、インテークマニホールド１１の作用について説明する。
図４及び図５に示すように、流入管１４からサージタンク１３内に流入した吸気は、サージタンク１３内から４つの分岐管１５に対して接続部２０からそれぞれ流れ込むことで分配される。このとき、各分岐管１５におけるサージタンク１３との接続部２０の断面の４つのコーナー部２１～２４のうち、並び方向Ｘにおける流入管１４側に位置する２つのコーナー部２１，２２の曲率半径は、並び方向Ｘにおける流入管１４側とは反対側に位置する２つのコーナー部２３，２４の曲率半径よりも小さくなっている。
Next, the function of the intake manifold 11 will be explained.
As shown in FIGS. 4 and 5, the intake air that has flowed into the surge tank 13 from the inflow pipe 14 is distributed by flowing into the four branch pipes 15 from the surge tank 13 through the connecting portions 20, respectively. At this time, the radius of curvature of two corner parts 21 and 22 located on the inflow pipe 14 side in the arrangement direction is smaller than the radius of curvature of the two corner portions 23 and 24 located on the side opposite to the inflow pipe 14 side in the arrangement direction X.
このため、各分岐管１５の接続部２０における吸気の流路断面積は、流入管１４からの吸気が流れてくる側の方が、流入管１４からの吸気が流れてくる側とは反対側よりも大きくなる。したがって、流入管１４からサージタンク１３内に流入した吸気の主流が接続部２０から各分岐管１５内に円滑に流れ込むため、接続部２０での乱流の発生が抑制される。この結果、吸気がサージタンク１３から各分岐管１５へ流れる際の圧力損失が効果的に低減される。 Therefore, the cross-sectional area of the intake air flow path at the connection portion 20 of each branch pipe 15 is such that the side where the intake air from the inflow pipe 14 flows is opposite to the side where the intake air from the inflow pipe 14 flows. becomes larger than Therefore, the main flow of intake air that has flowed into the surge tank 13 from the inflow pipe 14 smoothly flows into each branch pipe 15 from the connection part 20, so that the occurrence of turbulence at the connection part 20 is suppressed. As a result, pressure loss when intake air flows from the surge tank 13 to each branch pipe 15 is effectively reduced.
図３及び図６に示すように、サージタンク１３から各分岐管１５へ流れ込んだ吸気は、湾曲部１７内を通って内燃機関１２側へ流れる。このとき、湾曲部１７内を流れる吸気の流速は、通常、内周側の方が外周側よりも速くなる。この点、本実施形態の各分岐管１５の湾曲部１７の断面における４つのコーナー部２５～２８のうち、内周側に位置する２つコーナー部２５，２６の曲率半径は、外周側に位置する２つのコーナー部２７，２８の曲率半径よりも小さくなっている。 As shown in FIGS. 3 and 6, the intake air that has flowed from the surge tank 13 into each branch pipe 15 passes through the curved portion 17 and flows toward the internal combustion engine 12. At this time, the flow velocity of the intake air flowing inside the curved portion 17 is normally faster on the inner circumferential side than on the outer circumferential side. In this respect, among the four corner parts 25 to 28 in the cross section of the curved part 17 of each branch pipe 15 in this embodiment, the radius of curvature of the two corner parts 25 and 26 located on the inner peripheral side is The radius of curvature of the two corner portions 27 and 28 is smaller than that of the two corner portions 27 and 28.
このため、湾曲部１７内においては内周側の方が外周側よりも流路断面積が大きくなるので、湾曲部１７内の内周側を流れる吸気の流速を下げることができる。したがって、湾曲部１７内の内周側を流れる吸気と湾曲部１７内の外周側を流れる吸気との流速差が小さくなって乱流の発生が抑制されるので、湾曲部１７内を流れる吸気の圧力損失が効果的に低減される。 Therefore, within the curved portion 17, the flow passage cross-sectional area is larger on the inner circumferential side than on the outer circumferential side, so that the flow velocity of the intake air flowing on the inner circumferential side within the curved portion 17 can be lowered. Therefore, the difference in flow velocity between the intake air flowing on the inner circumferential side of the curved portion 17 and the intake air flowing on the outer circumferential side of the curved portion 17 is reduced, and the generation of turbulence is suppressed. Pressure loss is effectively reduced.
さらに、各分岐管１５の断面におけるコーナー部１９の曲率半径は、接続部２０から湾曲部１７に向かって徐々に変化している。このため、各分岐管１５は、接続部２０から湾曲部１７にかけての部位において、吸気の圧力損失の低減に対して有利となる。すなわち、吸気がサージタンク１３から各分岐管１５へ流れる際の圧力損失、湾曲部１７内を流れる吸気の圧力損失、及び接続部２０から湾曲部１７にかけての部位を流れる吸気の圧力損失が低減される。 Furthermore, the radius of curvature of the corner portion 19 in the cross section of each branch pipe 15 gradually changes from the connecting portion 20 toward the curved portion 17. For this reason, each branch pipe 15 is advantageous in reducing the pressure loss of intake air in the region from the connecting portion 20 to the curved portion 17. That is, the pressure loss when the intake air flows from the surge tank 13 to each branch pipe 15, the pressure loss of the intake air flowing inside the curved portion 17, and the pressure loss of the intake air flowing through the portion from the connecting portion 20 to the curved portion 17 are reduced. Ru.
以上詳述した実施形態によれば、次のような効果が発揮される。
（１）インテークマニホールド１１において、各分岐管１５におけるサージタンク１３との接続部２０の断面の４つのコーナー部２１～２４のうち、並び方向Ｘにおける流入管１４側に位置する２つのコーナー部２１，２２の曲率半径は、並び方向Ｘにおける流入管１４側とは反対側に位置する２つのコーナー部２３，２４の曲率半径よりも小さくなっている。この構成によれば、各分岐管１５の接続部２０の断面における流入管からの吸気が流れてくる側の２つのコーナー部２１，２２の曲率半径を小さくすることで、接続部２０における曲率半径を小さくした２つのコーナー部２１，２２側、すなわち流入管１４からの吸気が流れてくる側の流路断面積を稼ぐことができる。このため、流入管１４からサージタンク１３内に流入した吸気が各分岐管１５内に円滑に流れるため、接続部２０での乱流の発生が抑制される。したがって、吸気がサージタンク１３から各分岐管１５へ流れる際の圧力損失を効果的に低減できる。
According to the embodiment described in detail above, the following effects are exhibited.
(1) In the intake manifold 11, among the four corner parts 21 to 24 of the cross section of the connection part 20 with the surge tank 13 in each branch pipe 15, two corner parts 21 located on the inflow pipe 14 side in the arrangement direction X , 22 is smaller than the radius of curvature of the two corner portions 23 and 24 located on the side opposite to the inflow pipe 14 side in the arrangement direction X. According to this configuration, by reducing the radius of curvature of the two corner portions 21 and 22 on the side where the intake air from the inflow pipe flows in the cross section of the connecting portion 20 of each branch pipe 15, the radius of curvature at the connecting portion 20 is reduced. The cross-sectional area of the flow path on the two corner portions 21 and 22 sides, that is, on the side from which the intake air from the inflow pipe 14 flows, can be increased by making the size smaller. Therefore, the intake air that has flowed into the surge tank 13 from the inflow pipe 14 flows smoothly into each branch pipe 15, so that the occurrence of turbulent flow at the connection portion 20 is suppressed. Therefore, pressure loss when intake air flows from the surge tank 13 to each branch pipe 15 can be effectively reduced.
（２）インテークマニホールド１１において、各分岐管１５の湾曲部１７の断面における４つのコーナー部２５～２８のうち、内周側に位置する２つコーナー部２５，２６の曲率半径は、外周側に位置する２つのコーナー部２７，２８の曲率半径よりも小さくなっている。通常、湾曲部１７内を流れる吸気の流速は、内周側の方が外周側よりも速くなる。この点、この構成によれば、湾曲部１７内の内周側の方が外周側よりも流路断面積が大きくなるので、湾曲部１７内の内周側を流れる吸気の流速を下げることができる。このため、湾曲部１７内の内周側を流れる吸気と湾曲部１７内の外周側を流れる吸気との流速差が小さくなって乱流の発生が抑制されるので、湾曲部１７内を流れる吸気の圧力損失を効果的に低減できる。 (2) In the intake manifold 11, among the four corner parts 25 to 28 in the cross section of the curved part 17 of each branch pipe 15, the radius of curvature of the two corner parts 25 and 26 located on the inner circumference side is It is smaller than the radius of curvature of the two corner portions 27 and 28 located therein. Normally, the flow velocity of the intake air flowing inside the curved portion 17 is faster on the inner circumferential side than on the outer circumferential side. In this regard, according to this configuration, the flow passage cross-sectional area is larger on the inner circumferential side of the curved portion 17 than on the outer circumferential side, so it is possible to reduce the flow velocity of the intake air flowing on the inner circumferential side of the curved portion 17. can. Therefore, the difference in flow velocity between the intake air flowing on the inner circumferential side of the curved portion 17 and the intake air flowing on the outer circumferential side of the curved portion 17 becomes small, and the generation of turbulence is suppressed, so that the intake air flowing inside the curved portion 17 pressure loss can be effectively reduced.
（３）インテークマニホールド１１において、各分岐管１５の断面におけるコーナー部１９の曲率半径は、接続部２０から湾曲部１７に向かって徐々に変化している。この構成によれば、吸気がサージタンク１３から各分岐管１５へ流れる際の圧力損失、湾曲部１７内を流れる吸気の圧力損失、及び接続部２０から湾曲部１７にかけての部位を流れる吸気の圧力損失を低減できる。 (3) In the intake manifold 11, the radius of curvature of the corner portion 19 in the cross section of each branch pipe 15 gradually changes from the connecting portion 20 toward the curved portion 17. According to this configuration, the pressure loss when the intake air flows from the surge tank 13 to each branch pipe 15, the pressure loss of the intake air flowing inside the curved part 17, and the pressure of the intake air flowing through the region from the connecting part 20 to the curved part 17. Loss can be reduced.
（変更例）
なお、上記実施形態は次のように変更してもよい。
・各分岐管１５の断面におけるコーナー部１９の曲率半径は、必ずしも接続部２０から湾曲部１７に向かって徐々に変化している必要はない。すなわち、各分岐管１５の断面におけるコーナー部１９の曲率半径は、接続部２０から湾曲部１７に向かって急激に変化していてもよい。
(Example of change)
Note that the above embodiment may be modified as follows.
- The radius of curvature of the corner portion 19 in the cross section of each branch pipe 15 does not necessarily need to gradually change from the connecting portion 20 toward the curved portion 17. That is, the radius of curvature of the corner portion 19 in the cross section of each branch pipe 15 may change rapidly from the connecting portion 20 toward the curved portion 17.
・各分岐管１５の湾曲部１７の断面における４つのコーナー部２５～２８のうち、内周側に位置する２つコーナー部２５，２６の曲率半径は、必ずしも外周側に位置する２つのコーナー部２７，２８の曲率半径よりも小さくなっている必要はない。すなわち、各分岐管１５の湾曲部１７の断面における４つのコーナー部２５～２８のうち、内周側に位置する２つコーナー部２５，２６の曲率半径は、外周側に位置する２つのコーナー部２７，２８の曲率半径以上にしてもよい。 - Among the four corner parts 25 to 28 in the cross section of the curved part 17 of each branch pipe 15, the radius of curvature of the two corner parts 25 and 26 located on the inner peripheral side is not necessarily the same as that of the two corner parts located on the outer peripheral side. It is not necessary that the radius of curvature is smaller than 27 and 28. That is, among the four corner parts 25 to 28 in the cross section of the curved part 17 of each branch pipe 15, the radius of curvature of the two corner parts 25 and 26 located on the inner peripheral side is equal to that of the two corner parts located on the outer peripheral side. The radius of curvature may be greater than 27 or 28.
・各分岐管１５の接続部２０の断面の４つのコーナー部２１～２４のうち、並び方向Ｘにおける流入管１４側に位置する２つのコーナー部２１，２２の曲率半径は互いに異なっていてもよいし、並び方向Ｘにおける流入管１４側とは反対側に位置する２つのコーナー部２３，２４の曲率半径は互いに異なっていてもよい。 - Among the four corner parts 21 to 24 of the cross section of the connecting part 20 of each branch pipe 15, the radii of curvature of the two corner parts 21 and 22 located on the inflow pipe 14 side in the arrangement direction X may be different from each other. However, the radii of curvature of the two corner portions 23 and 24 located on the side opposite to the inflow pipe 14 side in the arrangement direction X may be different from each other.
・各分岐管１５の湾曲部１７の断面の４つのコーナー部２５～２８のうち、内周側に位置する２つコーナー部２５，２６の曲率半径は互いに異なっていてもよいし、外周側に位置する２つのコーナー部２７，２８の曲率半径は互いに異なっていてもよい。 - Among the four corner parts 25 to 28 of the cross section of the curved part 17 of each branch pipe 15, the two corner parts 25 and 26 located on the inner circumference side may have different radii of curvature, or The two corner portions 27 and 28 may have different radii of curvature.
・各分岐管１５において接続部２０以外の部位が全て湾曲部１７である場合には、各分岐管１５の断面における４つのコーナー部１９の曲率半径は、接続部２０から湾曲部１７における一定の距離の中で徐々に変化させるようにしてもよい。 - If all parts of each branch pipe 15 other than the connecting part 20 are curved parts 17, the radii of curvature of the four corner parts 19 in the cross section of each branch pipe 15 are constant from the connecting part 20 to the curved part 17. It may also be changed gradually over a distance.
・各分岐管１５の断面形状は、コーナー部が円弧状をなす矩形状（四角形状）以外の多角形状であってもよい。すなわち、各分岐管１５の断面形状は、コーナー部が円弧状をなしていれば、例えば三角形状や五角形状、あるいは六角形状であってもよい。 - The cross-sectional shape of each branch pipe 15 may be a polygonal shape other than a rectangular shape (square shape) in which the corner portions are arcuate. That is, the cross-sectional shape of each branch pipe 15 may be triangular, pentagonal, or hexagonal, for example, as long as the corner portions are arcuate.
・各分岐管１５は、必ずしも湾曲部１７を有している必要はない。すなわち、各分岐管１５は、例えばサージタンク１３から内燃機関１２に向かって直線状に延びるように構成されていてもよい。 - Each branch pipe 15 does not necessarily need to have the curved part 17. That is, each branch pipe 15 may be configured to extend linearly from the surge tank 13 toward the internal combustion engine 12, for example.
・本実施形態のインテークマニホールド１１は、直列４気筒の車載用の内燃機関１２に適用したが、直列３気筒や直列６気筒などの車載用の内燃機関に対して適用してもよい。
・図７に示すように、吸気装置は、インテークマニホールド１１に限らず、インレット３０が設けられたケース３１とアウトレット３２が設けられたキャップ３３とでフィルタエレメント３４が挟持された構成のエアクリーナ３５であってもよい。この場合、インレット３０が流入管を構成し、ケース３１及びキャップ３３が収容部を構成し、アウトレット３２が供給管を構成する。
- Although the intake manifold 11 of the present embodiment is applied to an in-line four-cylinder in-vehicle internal combustion engine 12, it may also be applied to in-line three-cylinder, in-line six-cylinder, or other in-line in-vehicle internal combustion engines.
- As shown in FIG. 7, the intake device is not limited to the intake manifold 11, but also includes an air cleaner 35 having a configuration in which a filter element 34 is sandwiched between a case 31 provided with an inlet 30 and a cap 33 provided with an outlet 32. There may be. In this case, the inlet 30 constitutes an inflow pipe, the case 31 and the cap 33 constitute a housing part, and the outlet 32 constitutes a supply pipe.
１１…吸気装置の一例としてのインテークマニホールド
１２…内燃機関
１３…収容部の一例としてのサージタンク
１４…流入管
１５…供給管の一例としての分岐管
１６，１８…フランジ部
１６ａ，１８ａ…挿通孔
１７…湾曲部
１９，２１～２８…コーナー部
２０…接続部
３０…流入管を構成するインレット
３１…収容部を構成するケース
３２…供給管を構成するアウトレット
３３…収容部を構成するキャップ
３４…フィルタエレメント
３５…吸気装置の一例としてのエアクリーナ
Ｘ…並び方向
DESCRIPTION OF SYMBOLS 11... Intake manifold as an example of an intake device 12... Internal combustion engine 13... Surge tank as an example of a storage part 14... Inflow pipe 15... Branch pipe as an example of a supply pipe 16, 18... Flange part 16a, 18a... Insertion hole 17... Curved part 19, 21-28... Corner part 20... Connecting part 30... Inlet forming an inflow pipe 31... Case forming a housing part 32... Outlet forming a supply pipe 33... Cap forming a housing part 34... Filter element 35... Air cleaner as an example of an intake device X... Arrangement direction
Claims (3)
前記収容部に接続され、前記吸気を前記収容部内に流入させる流入管と、
前記収容部における前記流入管と対向しない位置に接続され、前記流入管から前記収容部内に流入した前記吸気を内燃機関側へ供給する供給管と、を備え、
前記供給管における前記供給管が延びる方向と直交する断面は、コーナー部が円弧状をなす四角形状をなしており、
前記供給管における前記収容部との接続部の断面の４つの前記コーナー部のうち、前記流入管からの前記吸気が前記供給管に流れてくる側に位置する２つの前記コーナー部の曲率半径は、他の２つの前記コーナー部の曲率半径よりも小さくなっていることを特徴とする吸気装置。 a storage section capable of accommodating intake air;
an inflow pipe connected to the housing part and causing the intake air to flow into the housing part;
a supply pipe connected to a position not facing the inflow pipe in the accommodating part and supplying the intake air that has flowed into the accommodating part from the inflow pipe to the internal combustion engine side,
A cross section of the supply pipe perpendicular to the direction in which the supply pipe extends has a rectangular shape with arcuate corners;
The radius of curvature of two corner portions located on the side from which the intake air from the inflow pipe flows into the supply pipe, among the four corner parts of the cross section of the connection part with the storage part in the supply pipe. is smaller than the radius of curvature of the other two corner portions.
前記湾曲部の断面における４つの前記コーナー部のうち、内周側に位置する２つの前記コーナー部の曲率半径は、外周側に位置する２つの前記コーナー部の曲率半径よりも小さくなっていることを特徴とする請求項１に記載の吸気装置。 The supply pipe has a curved portion extending in a curved manner at a position closer to the internal combustion engine than the connecting portion,
Among the four corner portions in the cross section of the curved portion, the radius of curvature of the two corner portions located on the inner peripheral side is smaller than the radius of curvature of the two corner portions located on the outer peripheral side. The intake device according to claim 1, characterized in that:
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| JP2009209762A (en) | 2008-03-04 | 2009-09-17 | Aisan Ind Co Ltd | Resin-made intake manifold |
| JP2016191363A (en) | 2015-03-31 | 2016-11-10 | ダイハツ工業株式会社 | Intake manifold of internal combustion engine |
| JP2017223142A (en) | 2016-06-14 | 2017-12-21 | 愛三工業株式会社 | Intake manifold |
| JP6394154B2 (en) | 2014-07-30 | 2018-09-26 | アイシン精機株式会社 | Intake device |
| US20190219011A1 (en) | 2018-01-15 | 2019-07-18 | Ford Global Technologies, Llc | Fluid delivery port of an integral intake manifold |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009209762A (en) | 2008-03-04 | 2009-09-17 | Aisan Ind Co Ltd | Resin-made intake manifold |
| JP6394154B2 (en) | 2014-07-30 | 2018-09-26 | アイシン精機株式会社 | Intake device |
| JP2016191363A (en) | 2015-03-31 | 2016-11-10 | ダイハツ工業株式会社 | Intake manifold of internal combustion engine |
| JP2017223142A (en) | 2016-06-14 | 2017-12-21 | 愛三工業株式会社 | Intake manifold |
| US20190219011A1 (en) | 2018-01-15 | 2019-07-18 | Ford Global Technologies, Llc | Fluid delivery port of an integral intake manifold |
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