WO2015079512A1 - 内燃機関およびその製造方法 - Google Patents
内燃機関およびその製造方法 Download PDFInfo
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- WO2015079512A1 WO2015079512A1 PCT/JP2013/081870 JP2013081870W WO2015079512A1 WO 2015079512 A1 WO2015079512 A1 WO 2015079512A1 JP 2013081870 W JP2013081870 W JP 2013081870W WO 2015079512 A1 WO2015079512 A1 WO 2015079512A1
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- Prior art keywords
- air supply
- supply port
- connection portion
- vortex chamber
- air
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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
- F02M35/10242—Devices or means connected to or integrated into air intakes; Air intakes combined with other engine or vehicle parts
- F02M35/10262—Flow guides, obstructions, deflectors or the like
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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
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
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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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4228—Helically-shaped channels
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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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4235—Shape or arrangement of intake or exhaust channels in cylinder heads of intake channels
-
- 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
- F02M35/10006—Air intakes; Induction systems characterised by the position of elements of the air intake system in direction of the air intake flow, i.e. between ambient air inlet and supply to the combustion chamber
- F02M35/10026—Plenum chambers
- F02M35/10052—Plenum chambers special shapes or arrangements of plenum chambers; Constructional details
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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
- F02M35/10006—Air intakes; Induction systems characterised by the position of elements of the air intake system in direction of the air intake flow, i.e. between ambient air inlet and supply to the combustion chamber
- F02M35/10072—Intake runners
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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
- F02M35/104—Intake manifolds
- F02M35/1045—Intake manifolds characterised by the charge distribution between the cylinders/combustion chambers or its homogenisation
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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
- F02M35/104—Intake manifolds
- F02M35/112—Intake manifolds for engines with cylinders all in one line
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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
- F02M35/1034—Manufacturing and assembling intake systems
- F02M35/10347—Moulding, casting or the like
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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
Definitions
- the present invention relates to an internal combustion engine provided with a plurality of cylinders and a method of manufacturing the same.
- Patent Document 1 discloses a configuration provided with an intake port that functions as a swirl generation port that generates a swirl that swirls along the inner circumferential surface of a cylinder.
- the opening position of the intake port which is a swirl generation port provided in the cylinder on one end side of the cylinder head and the opening position of the intake port which is a swirl generation port provided in the cylinder on the other end side By deflecting the position in the opposite direction from the center of the cylinder, the swirling directions of the swirls generated in the respective cylinders are made to be opposite to each other.
- the intake port core is contracted at the time of manufacture, the direction in which the opening positions of the intake ports shift is the same, and it is possible to suppress the variation in swirl ratio among the cylinders.
- FIG. 7 shows the drawings disclosed in the same document.
- FIG. 7 the periphery of an air supply manifold 101 of a multi-cylinder internal combustion engine having a plurality of cylinders 100 is shown.
- FIG. 7 only one cylinder 100 among the plurality of cylinders is shown as a representative.
- One air supply introduction pipe 103 for supplying air into the air supply manifold 101 is connected to the air supply manifold 101.
- the downstream end of the air supply introduction pipe 103, that is, the connection portion with the air supply manifold 101 is the air supply inlet 103 a for the air supply manifold 101.
- An air supply port 105 is provided between the air supply manifold 101 and each of the cylinders 100.
- the air supply port 105 guides the air to each cylinder 100.
- a vortex chamber 107 is provided between the air supply port 105 and the cylinder 100.
- the vortex chamber 107 forms a swirl with respect to the air supplied from the air supply port 105.
- the vortex chamber inlet 107a is provided at a position eccentric to the central axis line CL of the vortex chamber 107, and the air supplied from the vortex chamber inlet 107a is around the central axis line CL. It is supposed to turn. As shown in FIG.
- a plurality (six in the figure) of air supply ports 111 are connected to one side (the lower side in the figure) of the air supply manifold 110 in a state of being arranged in one direction at equal intervals. ing. Similar to FIG. 7, a vortex chamber 113 is provided at the downstream end of each air supply port 111, and a cylinder 115 is connected to the downstream side of each vortex chamber 113. In FIG. 9, only one cylinder 115 of the plurality of cylinders is shown as a representative. At one end of the air supply manifold 110 (the left end in the figure), an air supply inlet 117 for supplying air into the air supply manifold 110 is provided. The position of the air supply inlet 117 in FIG. 9 is different from the configuration of FIG. 7 in which the air supply inlet 103a is positioned between the air supply manifolds in that it is provided at one end of the air supply manifold 110.
- the air supplied from the air inlet 117 into the air supply manifold 110 flows along one direction (the right side in the figure) in which the air supply manifold 110 extends. Then, the air supply flows into each of the plurality of air supply ports 111 connected to the air supply manifold 110.
- the air supply flowing into the air supply port 111 has a dynamic pressure (inertial force). Therefore, when branched to the air supply port 111, the air supply flows along the outer wall portion 111a located far from the air supply inlet 117. Come to flow.
- the air supplied along the outer wall portion 111 a of the air supply port 111 flows into the vortex chamber 113, forms a predetermined swirl in the vortex chamber 113, and then flows into the cylinder 115 to supply a desired swirl ratio. Form an air flow.
- the air supply port closer to the air supply inlet 117 for example, the first first air supply port 111 (# 1) from the left in the figure and the second air supply second from the left
- the port 111 (# 2) it is possible to obtain a flow distribution in which the mainstream flows along the outer wall portion 111a of the air supply port 111 by the dynamic pressure of the air supply.
- a desired swirl can be obtained in the vortex chamber 113, and as shown in FIG. 10, the first cylinder and the second air supply port 111 (# 2) connected to the first air supply port 111 (# 1).
- the desired swirl ratio can be obtained in the second cylinder connected to.
- the air supply port far from the air supply inlet 117 decreases the dynamic pressure of the air supply as it gets farther from the air supply inlet 117, the main flow of air supply flowing in the air supply port 111 is along the outer wall 111a. As a result, it becomes difficult to obtain a flowing flow distribution, and as a result, the desired swirl can not be obtained in the vortex chamber 113, and the third cylinder connected to the third air supply port 111 (# 3) as shown in FIG.
- the downstream end wall portion 110a of the sixth air supply port 111 (# 6) is continuously connected to the downstream end wall portion 110a located at the most downstream of the air supply manifold 110, the downstream end wall portion 110a is The air supply that has arrived will flow along the continuously connected outer wall portion 111a, and a flow distribution in which the main flow flows along the outer wall portion 111a can be obtained. Therefore, as shown in FIG. 10, in the sixth cylinder connected to the sixth air supply port 111 (# 6), a swirl ratio larger than that of the third cylinder, the fourth cylinder and the fifth cylinder is obtained.
- the air supply flow differs among the cylinders depending on the positional relationship between the air supply inlet provided in the air supply manifold and each air supply port, so that the combustion state can not be equalized and the efficiency decreases. Also, there is a problem that exhaust gas characteristics such as NOx and soot change.
- Patent Document 1 discloses the invention for suppressing the variation in swirl ratio between cylinders, it is not a configuration provided with a vortex chamber, so there is a suggestion to solve the problem of obtaining an equal swirl ratio in the vortex chamber. not exist.
- the patent document 2 mentioned above is a structure provided with the vortex chamber, since the structure which makes the whole air supply port eccentric with respect to the center of a vortex chamber is employ
- the present invention has been made in view of such circumstances, and it is an object of the present invention to provide an internal combustion engine capable of making the combustion state between the cylinders uniform with a simple configuration and a method of manufacturing the same. .
- An internal combustion engine according to the present invention includes: a plurality of cylinders arranged at predetermined intervals in one direction; and an air supply manifold which extends in the one direction and is provided with an air supply inlet to which air is supplied.
- An internal combustion engine comprising: a plurality of vortex chambers respectively connected to end portions of the respective cylinders to form a swirl; and a plurality of air supply ports connecting the air supply manifold and the respective vortex chambers
- the air supply port has a connection portion connected to the air supply manifold, and a central axis of the connection portion of one air supply port is orthogonal to the one direction in which the air supply manifold extends With respect to the orthogonal direction, and is inclined at a predetermined inclination angle in a direction away from the air supply inlet, and the inclination angle of the connection portion of the one air supply port is the same as that of the one supply Other located on the air supply inlet side than air port Characterized in that it is larger than the inclination angle of the connecting portion of the serial air supply port.
- the air supplied from the air inlet into the air supply manifold flows along one direction in which the air supply manifold extends. Then, the air supply flows into each of the plurality of air supply ports connected to the air supply manifold. Since the charge air flowing into the charge port has dynamic pressure (inertial force), the connection immediately after being branched to the charge port is along the outer wall located far from the charge inlet. Come to flow. The air flowed along the outer wall of the connection portion of the air supply port flows into the vortex chamber, forms a predetermined swirl in the vortex chamber, and then flows into the cylinder to flow the air having the desired swirl ratio. Form.
- the air supply port close to the air inlet can obtain a flow distribution in which the main flow of air flows along the outer wall of the air supply port due to the dynamic pressure of the air supply. If the flow distribution in which the main flow of the air supply flows along the outer wall of the air supply port is obtained, the distance between the swirl center and the main flow of the air supply can be increased, so a stronger swirl ratio can be obtained. You can get On the other hand, since the dynamic pressure of the charge air decreases as the charge air port is farther from the charge air inlet, the flow distribution of the main flow of the air charge flowing inside the air charge port is obtained along the outer wall. Becomes difficult.
- the central axis of the connection portion of the air supply port is inclined in the direction away from the air supply inlet with respect to the orthogonal direction orthogonal to the one direction in which the air supply manifold extends.
- the main flow of the air supplied into the air supply port approaches the outer side wall and flows along the outer side wall, and as a result, it is possible to obtain a flow distribution in which the main flow flows along the outer side wall.
- the connection part where the dynamic pressure of the air supply becomes smaller inclines The angle can be increased to allow the main flow of air to flow along the outer wall side.
- the swirl ratios in the respective swirl chambers become equal to each other, and as a result, the flow distribution of the air flowing into the cylinders can be equalized in each of the cylinders. Since equal charge flow can be obtained in each cylinder, the combustion state of each cylinder can be matched, and a decrease in efficiency and a change in exhaust gas characteristics can be avoided. In addition, since the combustion state of each cylinder can be made uniform only by a simple change in which the connection portion of the air supply port is inclined, there is no significant design change such as changing the entire shape of the air supply port. .
- the inclination angle of the present invention is determined by the flow distribution of the charge air flowing into the vortex chamber. For example, the lower limit is 5 °, 8 ° or 10 °, and the upper limit is 60 °, 50 ° It is taken as one of 30 °.
- the inclination angle is set to be gradually larger as the connection portion of the air supply port located farther from the air supply inlet.
- the dynamic pressure of the air supply decreases according to the distance from the air supply inlet, but the inclination angle of the connection portion of the air supply port is increased to take a long flow distance.
- the main flow of the charge air can be brought close to the outer wall by utilizing the inertia force of the charge air, it is possible to obtain a flow distribution in which the main flow flows along the outer wall even if the dynamic pressure of the charge is low. Can. Therefore, the flow distribution flowing into each vortex chamber can be made equal by increasing the inclination angle sequentially as the connection portion of the air supply port located farther from the air supply inlet and having a lower dynamic pressure increases. An equal charge flow can be obtained with the cylinder.
- the air supply port is formed by connecting the connection portion and a vortex chamber introduction portion located closer to the vortex chamber side than the connection portion, and the connection is The part is manufactured by an air supply manifold mold that forms the air supply manifold, and the vortex chamber introduction part is manufactured by a cylinder head mold that forms the vortex chamber and the end of the cylinder. .
- the cylinder head mold that forms the end of the swirl chamber and the cylinder is a mold that determines the shape of the internal combustion engine main body, and thus it is difficult to frequently change design.
- the air supply manifold mold can be determined in shape separately from the internal combustion engine main body, it can be changed in design more frequently than the cylinder head mold. Therefore, in the present invention, the air supply port is divided into the connection portion and the vortex chamber introduction portion, and the vortex chamber introduction portion of the air supply port without shape change is manufactured by a cylinder head mold.
- the connection part of the above was to be manufactured by the air supply manifold mold.
- each of the air supply ports has a connection portion connected to the air supply manifold, and a central axis of the connection portion of one of the air supply ports is the air supply manifold.
- the cylinder head mold that forms the end of the swirl chamber and the cylinder is a mold that determines the shape of the internal combustion engine main body, and thus it is difficult to frequently change design.
- the air supply manifold mold can be determined in shape separately from the internal combustion engine main body, it can be changed in design more frequently than the cylinder head mold. Therefore, in the present invention, the air supply port is divided into the connection portion and the vortex chamber introduction portion, and the vortex chamber introduction portion of the air supply port without shape change is manufactured by a cylinder head mold.
- the connection part of the above was to be manufactured by the air supply manifold mold.
- the present invention by adjusting the flow distribution of the air supply port by inclining the connection portion of the air supply port, variation in the air supply flow of each cylinder can be suppressed and the combustion state can be made uniform. Thereby, the deterioration of the efficiency of the internal combustion engine and the deterioration of the exhaust gas characteristics can be minimized.
- the connection portion of the air supply port is inclined is required, there is no significant design change such as changing the entire air supply port.
- FIG. 10 is a perspective view showing the periphery of an air supply manifold of a conventional internal combustion engine.
- FIG. 7 is a plan view showing the periphery of the air supply manifold in order to explain that the air supply flow is different among the cylinders. It is the graph which showed the swirl ratio for every cylinder of FIG.
- the internal combustion engine of the present invention is, like FIGS. 7 and 9, a multi-cylinder internal combustion engine having a plurality of cylinders.
- FIG. 1 shows the periphery of an air supply manifold 1 of a multi-cylinder internal combustion engine.
- the air supply manifold 1 extends in the x direction (one direction) which is a lateral direction in FIG. 1, and at one end (left end in FIG. 1), an air supply inlet 3 to which air is supplied is provided. .
- the air inlet 3 is at the main flow of air supplied to the air manifold 1.
- a plurality of (six in the figure) air supply ports 5 are connected to one side (downward in the figure) of the air supply manifold 1 in a state of being equally spaced in the x direction.
- the air supply port 5 has a connection portion 7 located on the inlet side, and a vortex chamber introduction portion 11 connected to the downstream side of the connection portion to guide the air supply to the vortex chamber 9.
- the connection portion 7 has an outer wall 7 a located far from the air inlet 3 and an inner wall 7 b located near the air inlet 3.
- the outer side wall 7a and the inner side wall 7b are provided to have substantially the same flow passage cross-sectional area at each flow position of the air supply.
- only the connection part 7 of the air supply port 5 is shown by FIG.
- a vortex chamber 11 is connected downstream of the air supply port 5.
- the vortex chamber 11 is connected to the end of each cylinder 13.
- the air supplied to the inlet of the vortex chamber swirls around the central axis CL to form a predetermined swirl.
- Each of the swirl chambers 11 connected to each cylinder 13 has the same shape. In FIG. 2, only one cylinder 13 of a plurality of (six in the present embodiment) cylinders is shown as a representative.
- the cylinders 13 are arranged at equal intervals along the x direction in which the air supply manifold 1 extends. In the present embodiment, six cylinders 13 are provided in accordance with the air supply port 5 shown in FIG. 1, but are not shown in the figure.
- the central axis CL1 of the connection portion 7 of the air supply port 5 is the air supply inlet 3 (shown in the drawing) in the y direction (orthogonal direction) orthogonal to the x direction 1) is inclined at a predetermined inclination angle in the direction away from (1).
- the sixth connection portion 7 (# 6) of the sixth air supply port 5 (# 6) at the sixth or right end counted from the air supply inlet 3 has an inclination angle of 30 °
- the fifth connection portion 7 (# 5) of the fifth fifth air supply port 5 (# 5) counted from the air supply inlet 3 has an inclination angle of 24 °.
- FIG. 3 shows a comparative example of FIG.
- a general air supply port shape is shown, and the connection portion 7 ′ of the air supply port has an inclination angle of 0 °.
- the shape of the connection portion 7 which is the inlet of the air supply port 5 is only changed with respect to the comparative example.
- the inclination angle of the connection portion 7 of one air supply port 5 is the connection of another air supply port 5 located closer to the air supply inlet 3 than the one air supply port 5. It is set larger than the inclination angle of the part 7. More specifically, the inclination angle of the connection portion 7 of the air supply port 5 is set to increase gradually as the connection portion 7 of the air supply port 5 is located farther from the air supply inlet 3. More specifically, the first connection portion 7 (# 1) of the first air supply port 5 (# 1) at the first or left end counted from the air supply inlet 3 has no inclination angle, and is inclined The angle is 0 °.
- the inclination angles are respectively 6 °, 12 °, 18 °, 24 °, 30 from the second connection portion (# 2) to the sixth connection portion (# 6) which are sequentially farther from the air supply inlet 3. It is set so that it becomes large sequentially like °.
- the inclination angle is determined by the flow distribution of the charge air flowing into the vortex chamber 9, but for example, the lower limit is 5 °, 8 ° or 10 °, and the upper limit is 60 °, 50 ° or 30 °. Is one of
- the air supply port 5 is formed by connecting the connection portion 7 and the vortex chamber introduction portion 11 after casting. That is, the connection part 7 is manufactured by the air supply manifold mold which forms the air supply manifold 1 (refer code
- air is supplied from the air inlet 3 into the air supply manifold 1 through the air supply.
- the air introduced into the air supply manifold 1 flows into the air supply ports 5 while flowing in the x direction.
- the air that has flowed into the air supply ports 5 flows into the connection portion 7 which is the inlet of the air supply port 5, and then flows through the vortex chamber introduction portion 11 into the vortex chamber 9.
- the air supplied into the vortex chamber 9 swirls around the central axis CL of the vortex chamber 9 to form a swirl, and flows into the cylinder 13 at the timing when the air supply valve (see FIG. 8) is opened.
- connection portion 7 of the air supply port 5 is connected to the air inlet 3 with respect to the y direction orthogonal to the x direction in which the air supply manifold 1 extends. It was decided to incline in the direction to go away. By tilting the connecting portion 7 in the direction away from the air inlet 3 in this manner, the air flowing into the air supply port 5 is received by the outer wall 7 a of the connecting portion 7 at a predetermined angle of attack. As a result, the main flow of air supplied into the air supply port 5 approaches the outer wall 7a and flows along the outer wall 7a, and as a result, the main flow flows along the outer wall 7a. be able to.
- the main flow is separated as much as possible from the central axis CL which is the turning center of the vortex chamber 9.
- a drift can be created and a desired swirl ratio can be obtained.
- the dynamic pressure of the air supply ie, x It is possible to flow the main flow of the air supply along the side of the outer wall 7a by increasing the inclination angle as the connecting portion 7 in which the inertial force in the direction becomes smaller.
- each air supply port 5 the flow distribution of the air supply which flows through the air supply port 5 can be adjusted similarly to the other air supply port 5, and the flow distribution of the air which flows into the vortex chamber 9 Can be aligned at each air supply port 5. Therefore, the swirl ratios in the respective swirl chambers 9 become equal to each other, and as a result, the flowing state of the air flowing into the cylinders 13 can be equalized in each of the cylinders 13. As described above, the equal charge flow can be obtained in each cylinder, so that the combustion state of each cylinder can be made to coincide, and the decrease in efficiency and the change in exhaust gas characteristics can be suppressed.
- the inclination angle is set to be gradually larger as the connection portion 7 of the air supply port 5 is located farther from the air supply inlet 3.
- the inclination angle of the connection portion 7 of the air supply port 5 is increased to take a long flow distance.
- each vortex chamber 9 is made equal by increasing the inclination angle sequentially as the connection portion 7 of the air supply port 5 located farther from the air supply inlet 3 and having a lower dynamic pressure is located.
- the same charge air flow can be obtained in each cylinder 13.
- each cylinder 13 can be made uniform only by a simple change in which the connection portion 7 of the air supply port 5 is inclined, significant design change such as changing the entire shape of the air supply port 5 is realized. It does not accompany. Moreover, since such combustion control can be omitted as compared with an internal combustion engine performing combustion control such as controlling the ignition timing for each cylinder, an internal combustion engine with low cost can be provided.
- connection portion 7 is manufactured by the air supply manifold mold forming the air supply manifold 1, and the vortex chamber introduction portion 11 is a cylinder forming the end of the vortex chamber 9 and the cylinder 13. It was decided to manufacture by the head mold. The reason is as follows.
- the cylinder head mold that forms the end of the swirl chamber 9 and the cylinder 13 is a mold that determines the shape of the internal combustion engine main body, and therefore, it is difficult to frequently change the design.
- the air supply manifold mold can be determined in shape separately from the internal combustion engine main body, it can be changed in design more frequently than the cylinder head mold.
- the air supply port 5 is divided into the connection portion 7 and the vortex chamber introduction portion 11, and the vortex chamber introduction portion 11 of the air supply port 5 without shape change is manufactured using a cylinder head mold.
- the connection portion 7 of the air supply port 5 with the change is to be manufactured by the air supply manifold mold.
- the air supply manifold having the connection portion 7 of the air supply port 5 having a desired shape can be manufactured inexpensively.
- the inclination angle of the connection portion 7 is set to be gradually larger as it becomes farther from the air inlet 3, but the present invention is limited to this. is not.
- the dynamic pressure of the air introduced from the air inlet 3 is reduced, and only the connection portion 7 in which the air flowed into the connection portion 7 of the air supply port 5 has less tendency toward the outer wall 7a is inclined.
- a six-cylinder internal combustion engine has been described as an example, but the present invention is not limited to this, and may have two or more cylinders and five or less cylinders, or seven or more cylinders. It is also good. Further, in the present embodiment, although the configuration is described in which the air supply is performed to one cylinder 13 from one place, the present invention is not limited to this. It may be a care.
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Abstract
Description
例えば、下記特許文献1には、気筒の内周面に沿って旋回するスワールを生成するスワール生成ポートとして機能する吸気ポートを備えた構成が開示されている。同文献に記載された発明では、シリンダヘッドの一端側の気筒に設けられたスワール生成ポートである吸気ポートの開口位置と、他端側の気筒に設けられたスワール生成ポートである吸気ポートの開口位置とを互いに逆向きに気筒の中心から偏らせることで、それぞれの気筒内に生成されるスワールの旋回方向を互いに反対向きとするようになっている。これにより、製造時に吸気ポート用中子が収縮したとしても各吸気ポートの開口位置がずれる方向が同一となり、気筒間におけるスワール比のバラツキを抑えることが可能とされている。
給気マニホールド110の一端(同図では左端)には給気マニホールド110内に給気が供給される給気入口117が設けられている。なお、図9の給気入口117の位置は、給気マニホールド110の一端に設けられている点で、給気マニホールドの間に給気入口103aを位置させた図7の構成とは相違する。
なお、図9において左から6番目すなわち右端に位置する第6給気ポート111(#6)は、給気入口117から最も遠いので動圧が最も小さくなっている。しかし、第6給気ポート111(#6)の外側壁部111aが給気マニホールド110の最下流に位置する下流端壁部110aに連続的に接続されているので、この下流端壁部110aに到達した給気が連続的に接続された外側壁部111aに沿って流れることになり、外側壁部111aに沿って主流が流れる流動分布を得ることができる。したがって、図10に示すように、第6給気ポート111(#6)に接続された第6シリンダでは第3シリンダ、第4シリンダ及び第5シリンダよりも大きなスワール比が得られている。
また、上述した特許文献2は、渦室を備えた構成ではあるが、渦室の中心に対して給気ポート全体を偏心させる構成を採用しているので、大幅な設計変更を伴うといった問題がある。
本発明の内燃機関は、一方向に所定の間隔を有して配置された複数の気筒と、前記一方向に延在するとともに、給気が供給される給気入口が設けられた給気マニホールドと、各前記気筒の端部にそれぞれ接続されてスワールを形成する複数の渦室と、前記給気マニホールドと各前記渦室とを接続する複数の給気ポートとを備えた内燃機関において、各前記給気ポートは、前記給気マニホールドに対して接続される接続部を有し、一の前記給気ポートの前記接続部の中心軸線は、前記給気マニホールドが延在する前記一方向に直交する直交方向に対して、前記給気入口から遠ざかる方向に所定の傾斜角度を有して傾斜しており、該一の前記給気ポートの前記接続部の前記傾斜角度は、該一の前記給気ポートよりも前記給気入口側に位置する他の前記給気ポートの前記接続部の傾斜角度よりも大きくされていることを特徴とする。
複数ある給気ポートのうち、給気入口に近い給気ポートは給気が有する動圧によって給気ポートの外側壁部に沿って給気の主流が流れる流動分布を得ることができる。給気ポートの外側壁部に沿って給気の主流が流れる流動分布が得られると、渦室内にスワールが形成される旋回中心と給気の主流との距離を大きくとれるので、より強いスワール比を得ることができる。
一方、給気入口から遠い給気ポートは、給気入口から遠ざかるほど給気の動圧が下がるので、給気ポート内を流れる給気の主流が外側壁部に沿って流れる流動分布を得ることが難しくなる。これでは、渦室内の旋回中心と給気の主流との距離を大きくとることができず、所望のスワール比を得ることができない。
そこで、本発明は、給気ポートの接続部の中心軸線を、給気マニホールドが延在する一方向に直交する直交方向に対して、給気入口から遠ざかる方向に傾斜させることとした。このように接続部を給気入口から遠ざかる方向に傾斜させることにより、給気ポートに流れ込んだ給気を外側壁部で所定の迎え角をもって迎え入れる構成とする。これにより、給気ポートに流れ込んだ給気の主流が外側壁部に近づくとともに外側壁部に沿って流れるようになり、結果として外側壁部に沿って主流が流れる流動分布を得ることができる。
そして、一の給気ポートの接続部の傾斜角度を、給気入口側に位置する他の給気ポートの接続部よりも大きくすることで、給気の動圧が小さくなった接続部ほど傾斜角度を大きくして給気の主流をより外側壁部側に沿って流すことができる。これにより、各給気ポートの位置に応じて給気ポートを流れる給気の流動分布を他の給気ポートと同様に調整することができ、渦室に流れ込む給気の流動分布を各給気ポートで揃えることができる。したがって、各渦室におけるスワール比がそれぞれ同等となり、結果として気筒内に流れ込む給気の流動分布を各気筒にて同等とすることができる。各気筒にて同等の給気流動が得られるので、各気筒の燃焼状態を一致させることができ、効率の低下や排ガス特性の変化を回避することができる。
また、給気ポートの接続部を傾斜させるという簡便な変更だけで各気筒の燃焼状態を均一化させることができるので、給気ポート全体の形状を変更するといった大幅な設計変更を伴うことがない。
なお、本発明の傾斜角度としては、渦室に流れ込む給気の流動分布によって決定されるが、例えば、下限は5°、8°及び10°のいずれかとされ、上限は60°、50°及び30°のいずれかとされる。
そこで、本発明では、給気ポートを接続部と渦室導入部に分け、形状変更を伴わない給気ポートの渦室導入部をシリンダヘッド鋳型で製造することとし、形状変更を伴う給気ポートの接続部を給気マニホールド鋳型によって製造することとした。これにより、所望形状の給気ポートの接続部を有する給気マニホールドを安価に製造することができる。
そこで、本発明では、給気ポートを接続部と渦室導入部に分け、形状変更を伴わない給気ポートの渦室導入部をシリンダヘッド鋳型で製造することとし、形状変更を伴う給気ポートの接続部を給気マニホールド鋳型によって製造することとした。これにより、所望形状の給気ポートの接続部を有する給気マニホールドを安価に製造することができる。
また、給気ポートの接続部を傾斜させるという簡便な変更だけでよいので、給気ポート全体を変更するといった大幅な設計変更を伴うことがない。
本発明の内燃機関は、図7及び図9と同様に、複数の気筒を有する多気筒内燃機関とされている。
なお、傾斜角度としては、渦室9に流れ込む給気の流動分布によって決定されるが、例えば、下限は5°、8°及び10°のいずれかとされ、上限は60°、50°及び30°のいずれかとされる。
本実施形態では、給気ポート5は、鋳造後に、接続部7と、渦室導入部11とを接続することによって形成するようになっている。すなわち、接続部7は、給気マニホールド1を形成する給気マニホールド鋳型によって製造する(図4の符号P1参照)。その一方で、渦室導入部11は、渦室9及び気筒13の端部を形成するシリンダヘッド鋳型によって製造する(図4の符号P2参照)。このようにして、接続部7と渦室導入部11とは、それぞれ別の鋳型で製造される。
図1に示すように、例えば空気とされた給気が給気入口3から給気マニホールド1内に供給される。給気マニホールド1内に導入された給気は、x方向に流れつつ各給気ポート5内へと流れ込む。各給気ポート5内へと流れ込んだ給気は、給気ポート5の入口である接続部7に流入した後に渦室導入部11を通り、渦室9内へと流れ込む。渦室9内へ流れ込んだ給気は、渦室9の中心軸線CL回りに旋回することによってスワールを形成し、給気バルブ(図8参照)が開いたタイミングで気筒13内に流れ込み、所望のスワール比を有する給気流動を形成する。
そして、一の給気ポート5の接続部7の傾斜角度を、給気入口3側に位置する他の給気ポート5の接続部7よりも大きくすることで、給気の動圧(すなわちx方向の慣性力)が小さくなった接続部7ほど傾斜角度を大きくして給気の主流をより外側壁部7a側に沿って流すことができる。これにより、各給気ポート5の位置に応じて給気ポート5を流れる給気の流動分布を他の給気ポート5と同様に調整することができ、渦室9に流れ込む給気の流動分布を各給気ポート5で揃えることができる。したがって、各渦室9におけるスワール比がそれぞれ同等となり、結果として気筒13内に流れ込む給気の流動状態を各気筒13にて同等とすることができる。このように各気筒にて同等の給気流動が得られるので、各気筒の燃焼状態を一致させることができ、効率の低下や排ガス特性の変化を抑制することができる。
また、気筒毎に着火タイミングを制御するといった燃焼制御を行っている内燃機関に比べて、このような燃焼制御を省略することができるので、低コストとされた内燃機関を提供することができる。
例えば、給気入口3から導入される給気の動圧が小さくなり給気ポート5の接続部7に流れ込んだ給気が外側壁部7aへと向かう傾向が少ない接続部7のみを傾斜させるようにしても良い。具体的には、図5に示すように、第3給気ポート5(#3)までは給気の主流の動圧が所定値以上に維持されていると考えられる場合には、第4給気ポート5(#4)から第6給気ポート(#6)のそれぞれの接続部7のみを傾斜するようにしても良い。
また、本実施形態では、1つの気筒13に対して1箇所から給気を行う構成として説明したが、本発明はこれに限定されるものではなく、1つの気筒13に対して複数箇所から給気を行うものであってもよい。
3 給気入口
5 給気ポート
7 接続部
7a 外側壁部
9 渦室
11 渦室導入部
13 気筒
Claims (4)
- 一方向に所定の間隔を有して配置された複数の気筒と、
前記一方向に延在するとともに、給気が供給される給気入口が設けられた給気マニホールドと、
各前記気筒の端部にそれぞれ接続されてスワールを形成する複数の渦室と、
前記給気マニホールドと各前記渦室とを接続する複数の給気ポートと、
を備えた内燃機関において、
各前記給気ポートは、前記給気マニホールドに対して接続される接続部を有し、
一の前記給気ポートの前記接続部の中心軸線は、前記給気マニホールドが延在する前記一方向に直交する直交方向に対して、前記給気入口から遠ざかる方向に所定の傾斜角度を有して傾斜しており、
該一の前記給気ポートの前記接続部の前記傾斜角度は、該一の前記給気ポートよりも前記給気入口側に位置する他の前記給気ポートの前記接続部の傾斜角度よりも大きくされていることを特徴とする内燃機関。 - 前記給気入口から見て遠くに位置する前記給気ポートの前記接続部ほど、前記傾斜角度が順次大きく設定されていることを特徴とする請求項1に記載の内燃機関。
- 前記給気ポートは、前記接続部と、該接続部よりも前記渦室側に位置する渦室導入部とが接続されることによって形成されており、
前記接続部は、前記給気マニホールドを形成する給気マニホールド鋳型によって製造され、
前記渦室導入部は、前記渦室及び前記気筒の前記端部を形成するシリンダヘッド鋳型によって製造されることを特徴とする請求項1又は2に記載の内燃機関。 - 一方向に所定の間隔を有して配置された複数の気筒と、
前記一方向に延在するとともに、給気が供給される給気入口が設けられた給気マニホールドと、
各前記気筒の端部にそれぞれ接続されてスワールを形成する複数の渦室と、
前記給気マニホールドと各前記渦室とを接続する複数の給気ポートと、
を備えた内燃機関の製造方法において、
各前記給気ポートは、前記給気マニホールドに対して接続される接続部を有し、
一の前記給気ポートの前記接続部の中心軸線は、前記給気マニホールドが延在する前記一方向に直交する直交方向に対して、前記給気入口から遠ざかる方向に所定の傾斜角度を有して傾斜しており、
該一の前記給気ポートの前記接続部の前記傾斜角度は、該一の前記給気ポートよりも前記給気入口側に位置する他の前記給気ポートの前記接続部の傾斜角度よりも大きくされ、
前記給気ポートは、前記接続部と、該接続部に接続されるとともに該接続部よりも前記渦室側に位置する渦室導入部とを備え、
前記給気マニホールドを形成する給気マニホールド鋳型によって前記接続部を製造する接続部製造工程と、
前記渦室及び前記気筒の前記端部を形成するシリンダヘッド鋳型によって前記渦室導入部を製造する渦室導入部製造工程と、
前記接続部と前記渦室導入部とを接続して前記給気ポートを製造する給気ポート製造工程と、
を有することを特徴とする内燃機関の製造方法。
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US10408174B2 (en) | 2013-11-27 | 2019-09-10 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Internal combustion engine and method for manufacturing the same |
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EP3078828A4 (en) | 2017-08-23 |
EP3078828B1 (en) | 2019-03-20 |
US20160377036A1 (en) | 2016-12-29 |
EP3078828A1 (en) | 2016-10-12 |
JPWO2015079512A1 (ja) | 2017-03-16 |
US10408174B2 (en) | 2019-09-10 |
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