JP4336565B2 - Intake device for internal combustion engine - Google Patents

Description

  The present invention relates to an intake device for an internal combustion engine used in an automobile or the like.

In Patent Document 1, a plurality of intake branches respectively communicating with a plurality of intake ports protrude into an intake collector having an elongated cross-sectional shape in a vertical direction substantially along the side wall of the cylinder head, and a protruding direction of the intake branch in the intake collector An intake device for an internal combustion engine in which an air cleaner is disposed at a position deviated from the above is disclosed.
JP 2002-276487 A.

  However, in the configuration of Patent Document 1, the opening of the intake branch is orthogonal to the surface having the largest area among the surfaces forming the collector, that is, the vertical direction substantially along the side wall of the cylinder head, and the cylinder head It opens toward the side wall substantially parallel to the side wall. For this reason, factors affecting the sound emission, such as pressure waves and blown gas from the intake branch, directly act on the surface that has the largest area among the surfaces forming the collector. There is a risk of doing.

Accordingly, an intake device for an internal combustion engine according to the present invention is such that an intake branch communicating with each of a plurality of intake ports protrudes in a collector, from an intake inlet formed in the collector into the collector. In the collector, the three-dimensional region defined by extending the intake inlet toward the downstream side of the intake flow and the intake branch are configured not to cross each other . The branch opening portion of the intake branch that is opened in the direction is characterized in that it does not point at least the surface having the largest area among the surfaces forming the collector.

  According to the present invention, factors that affect the radiated sound, such as pressure waves and blown gas, do not directly act on the large surface area of the radiated sound that deteriorates among the wall surfaces constituting the collector. Deterioration can be suppressed.

  Hereinafter, an embodiment in which the present invention is applied to a four-cylinder gasoline internal combustion engine will be described in detail with reference to the drawings. First, referring to FIG. 8, a variable valve mechanism that can change the valve lift characteristics (valve timing and valve lift amount) of the intake valve 1 will be described as a configuration common to all the embodiments. This variable valve mechanism can change the operating angle change mechanism 10 that can change the operating angle and valve lift amount of the intake valve 1, and the phase (for example, the center phase) of the operating angle of the intake valve with respect to the crankshaft (not shown). And a phase change mechanism 20.

  The operating angle changing mechanism 10 includes a drive shaft 11 and a control shaft 12 that extend in parallel to each other in the cylinder row direction. The drive shaft 11 rotates around the shaft by the rotational power transmitted from the crankshaft. A swing cam 13 that can contact the valve lifter 2 of the intake valve 1 is rotatably fitted on the drive shaft 11, and an eccentric cam 14 is fixed or integrally formed for each cylinder. The axis of the outer peripheral surface of the eccentric cam 14 is eccentric with respect to the axis of the drive shaft 11, and a ring-shaped first link 15 is rotatably fitted on the outer peripheral surface of the eccentric cam 14.

  A control cam 16 is fixed or integrally formed on the control shaft 12 for each cylinder. The axis of the outer peripheral surface of the control cam 16 is eccentric with respect to the axis of the control shaft 12, and the central portion of the rocker arm 17 is rotatably fitted on the outer peripheral surface of the control cam 16. One end of the rocker arm 17 is rotatably connected to the tip of the first link 15, and the other end of the rocker arm 17 is rotatably connected to one end of the rod-shaped second link 18. The other end of the second link 18 is rotatably connected to the tip of the swing cam 13.

  Therefore, when the drive shaft 11 rotates around the shaft in conjunction with the rotation of the crankshaft, the first link 15 fitted on the eccentric cam 14 operates in a substantially translation direction, and the translational motion of the first link 15 is the rocker arm. The swing cam 13 swings through the second link 18 after being converted into the swing motion of 17. This swinging swing cam 13 abuts against and presses the valve lifter 2 of the intake valve 1, whereby the intake valve 1 is driven to open and close against the reaction force of a valve spring (not shown).

  Further, when the control shaft 12 is rotationally driven by the actuator 19, the center position of the control cam 16 which is the rocking center of the rocker arm 17 is changed, and the posture of the rocker arm 17 and the links 15, 18 is changed to be rocked. The swing characteristic of the cam 13 changes. Thereby, both the operating angle of the intake valve 1 and the valve lift amount are continuously changed.

  In the operating angle changing mechanism 10 having such a configuration, since the swing cam 13 that opens and closes the intake valve 1 is coaxially attached to the drive shaft 11, the shaft misalignment between the swing cam 13 and the drive shaft 11, etc. In addition to being excellent in control accuracy, the rocker arm 17 and the links 15 and 18 can be gathered around the drive shaft 11 to achieve compactness and excellent in engine mountability. Further, since many of the connecting portions between the members, such as the bearing portion of the eccentric cam 14 and the first link 15 and the bearing portion of the control cam 16 and the rocker arm 17, are in surface contact, lubrication is performed. Easy, durable and reliable. Further, when the operating angle changing mechanism 10 is applied to a general fixed valve system having a fixed cam and a camshaft, the swing cam 13 and the drive shaft 11 are placed at the positions of the fixed cam and the camshaft. The layout can be arranged and the layout can be changed very little, so that the application is very easy.

  The phase changing mechanism 20 continuously changes the center phase of the lift operating angle of the intake valve by changing the phase of the drive shaft 11 (camshaft in the case of a fixed valve system) with respect to the crankshaft. A type using a vane, a type using a helical spline, and the like are known, and detailed description thereof is omitted.

  The ECU (engine control unit) 4 as a control means performs general engine control such as fuel injection control based on the engine operating state detected by various sensors and the like, and also includes an actuator 19 of the operating angle changing mechanism 10 and The operation of the phase change mechanism 20 (actuator thereof) is controlled to change and control the valve lift characteristic of the intake valve.

  By using such a variable valve mechanism, for example, a response delay in reducing the pressure in the collector that occurs when the automobile is decelerated is eliminated, and the degree of freedom in designing the collector volume is increased.

  Next, the intake device according to the first embodiment of the present invention will be described with reference to FIGS. 1 and 2.

  As shown in FIG. 1, one end of intake ports 34 of a plurality of (four in this embodiment) cylinders constituting the cylinder row is opened on the intake-side side wall 32 of the cylinder head 30. A mounting bracket 36 is fixed to the side wall 32 so as to cover the port opening 35 of the intake port 34. The mounting bracket 36 is directly attached with one collector 38 made of a lightweight resin material and having an elongated cross-sectional shape in the vertical direction substantially along the side wall 32.

  When this collector 38 is regarded as a rectangular parallelepiped, the side extending in the cylinder row direction (side substantially parallel to the crankshaft centerline) has the longest length, and the side extending in the cylinder axis direction (side substantially parallel to the cylinder centerline P) ) Is the next longest, and the length of the side extending in the intake / exhaust direction (the side substantially perpendicular to the two sides) is the shortest. Therefore, the area surrounded by the side extending in the cylinder row direction and the side extending in the cylinder axis direction (side surface 38a corresponds to this surface) is the largest, and the side extending in the cylinder row direction and the side extending in the intake / exhaust direction are the largest. The area of the surrounded surface (the upper surface 38b and the lower surface 38c correspond to this surface) is the next largest, and the area of the surface surrounded by the side extending in the cylinder axis direction and the side extending in the suction / discharge direction is the smallest.

  Here, the collector 38 will be supplemented. When considering the vehicle mountability of an engine, there are many restrictions on the full width direction of the engine. As described above, the controllability of the collector volume is increased by controlling the intake air amount of the engine using the variable valve mechanism. Since the fully open output decreases as the collector capacity decreases, the collector capacity should be increased in terms of output performance. Thus, when the intake air amount is adjusted by changing the valve lift characteristic of the intake valve closer to the combustion chamber than the collector, the collector capacity can be sufficiently increased without concern about a decrease in intake response. However, in order to secure the collector volume, when it is arranged vertically in the engine room, it is restricted by the full width of the vehicle, and the full width of the engine is also restricted. In addition, when the engine room is placed horizontally, the full width of the engine is limited by the length of the engine room in the vehicle front-rear direction. Therefore, if the collector volume is to be limited with a certain limited engine full width, the volume is increased in the downward direction in the vehicle vertical direction where there is a relatively living space. Therefore, the collector 38 in the present embodiment has an elongated cross-sectional shape in the vertical direction substantially along the side wall 32.

  For example, as shown in FIG. 2, the collector 38 includes a collector main body 39 constituting the main body of the collector 38, a collector upper part 40 constituting the upper portion of the collector 38, an intake branch 41 attached to the collector main body 39, a collector A collector side wall portion 42 that is attached after the intake branch 41 is included in the main body portion 39, and is composed of a collector side wall portion 42. The intake branch 41 is built in the collector 38, so that the length of the branch is ensured and the intake device is compact. It is planned. The collector main body 39, the collector upper part 40, the intake branch 41, and the collector side wall part 42 are connected to each other with a seal member (not shown) interposed therebetween.

  Of the surfaces forming the collector 38, the surface is substantially parallel to the surface formed by the crankshaft centerline (not shown) perpendicular to the paper surface of FIG. 1 and the cylinder centerline P (see FIG. 1). The area of the surface (the side surface 38a in FIG. 1) consisting of the collector side wall portion 42 and the one side surface of the collector upper portion 40 continuous with the collector side wall portion 42 is maximized.

  The collector upper portion 40 is formed with an intake air inlet 43 that is open along the cylinder row direction. The intake air inlet 43 has an intake air amount control valve that controls the amount of intake air supplied into the collector 38. (Not shown in the first embodiment) is attached.

  The intake branch 41 has a plurality of communication passages 44 that respectively communicate with the plurality of intake ports 34, protrudes into the collector 38, and is an intake branch 41 that is an opening of each communication passage 44 that opens into the collector 38. Each branch opening 45 is formed so as to be directed upward in the vertical direction along the side wall 32 of the cylinder head 30, that is, upward (upper surface 38 b) in FIG. 1 or FIG. 2. In other words, the intake branch 41 has a surface in which the branch opening 45 is substantially parallel to the surface formed by the crankshaft centerline and the cylinder centerline P among the surfaces forming the collector 38, that is, the collector side wall. The portion 42 and one side surface of the collector upper portion 40 continuous to the collector side wall portion 42 are formed so as not to face the surface having the largest area among the surfaces forming the collector 38.

  Furthermore, the surface including the opening edge of the branch opening 45 is substantially orthogonal to the surface formed by the crankshaft center line and the cylinder center line P, and is substantially the upper surface 38b or the lower surface 38c of the collector 38. It is parallel.

  Here, as an idea of the area, it may be considered as a projected area from the viewpoint of a radiated sound that a passenger can experience. In this case, in the intake device shown in FIGS. 1 and 2, each branch opening 45 of the intake branch 41 opened in the collector 38 has a projected area of the collector 38 in the opening (axial center) direction of the branch opening 45. It can be said that the direction is not the maximum.

  In addition, the intake branch 41 has a three-dimensional region defined by extending the intake inlet 43 toward the intake flow downstream side in the collector 38 and the intake branch 41 so as not to cross each other, that is, the three-dimensional The intake branch 41 is formed so as not to overlap the region.

  The intake branch 41 can be set so that the branch opening 45 is directed upward or downward in FIGS. 1 and 2 from the viewpoint of suppressing the overall width of the engine. However, the intake inlet 43 is connected via an intake air amount control valve. Since the intake air that has flowed into the collector 38 from the flow into the intake branch 41 flows into the intake branch 41, the branch opening 45 is on the side where the intake air is supplied into the collector 38 via the intake air amount control valve, that is, the intake air inlet to which the intake air amount control valve is attached. The pressure loss of the intake air can be further reduced by disposing it so as to open toward the 43 side.

  As described above, in the present embodiment, the pressure wave, the blow back gas, and the like from the intake branch 41 do not directly act on the large wall surface that causes the deterioration of the radiated sound among the wall surfaces constituting the collector 38. Therefore, the deterioration of the radiated sound can be suppressed.

  Further, since each opening 45 of the intake branch 41 opens toward the intake introduction port 43 to which the intake air amount control valve is attached, air flows from the intake air amount control valve to each communication passage 44 of the intake branch 41. The pressure loss at the time can be reduced, and the decrease in volume efficiency when a high torque is required can be reduced.

  The intake branch 41 is formed in the collector 38 such that the intake branch 41 does not intersect the three-dimensional region defined by extending the intake inlet 43 toward the intake flow downstream side. Therefore, it is possible to achieve both the effect of improving the volume efficiency by the branch length (passage length of the communication passage 44) and the suppression of the increase in intake pressure loss.

  Hereinafter, although other embodiments of the present invention will be described, the same components as those in the first embodiment described above are denoted by the same reference numerals, and description thereof will be omitted.

  3 to 5 show a second embodiment of the present invention. In the second embodiment, a reinforcing member 50 as a reinforcing structure is integrated with the collector 38 with respect to the intake device of the first embodiment described above.

  As shown in FIGS. 4 and 5, the reinforcing member 50 has an elongated rectangular plate shape, and a through hole 51 is formed at a substantially central position. The reinforcing member 50 is located on the side opposite to the direction in which the branch opening 45 in the collector 38 is directed, that is, below the intake branch 41 in FIG. 3, and the upper container chamber on the upper side in FIG. 52 and a lower container chamber 53 on the lower side in FIG.

  In other words, the collector 38 has the reinforcing member 50 on the opposite side of the direction in which the branch opening 45 is directed, and the collector surface where the branch opening 45 is not directed by the reinforcing member 50, that is, the collector side wall 42 and the collector A surface that is formed of one side surface of the collector upper portion 40 that is continuous with the side wall portion 42 and that forms the collector 38 is reinforced.

  The upper container chamber 52 and the lower container chamber 53 communicate with each other through the through hole 51.

  In such a second embodiment, it is possible to further suppress radiated sound by reinforcing a wall surface having a large area that causes deterioration of radiated sound.

  In the second embodiment, the upper container chamber 52 and the lower container chamber 53 function as one container chamber and two container chambers depending on the operating conditions of the engine. However, as the through hole 51 is set larger, the effect of the reinforcing member 50 is only to reinforce the wall surface having a large area that causes deterioration of the radiated sound.

  6 and 7 show a third embodiment of the present invention. In the third embodiment, an air cleaner 61 as an air chamber is connected to the collector 38 via the intake air amount control valve 60 so as to be close to the collector 38 with respect to the intake device of the first embodiment described above. . Note that reference numeral 62 in FIG. 6 denotes a filter element that cleans the intake air.

  In the third embodiment, the collector 38 and the air cleaner 61 can be regarded as substantially one container chamber in a high torque region where the valve opening of the intake air amount control valve 60 is large. In other words, when the valve opening degree of the intake air amount control valve 60 is large, the collector 38 and the air cleaner 61 function as a substantially single collector chamber, so that the pressure amplitude attenuation effect near the intake original sound is further exhibited. Therefore, the effect of reducing the intake sound and the radiated sound due to the pulsation of the intake air can be further exhibited.

  The technical idea of the present invention that can be grasped from the above embodiment will be listed together with the effects thereof.

  (1) One collector is directly attached to a side wall of a cylinder head where a plurality of intake ports are open or an attachment member attached to the side wall, and an intake branch communicating with each of the plurality of intake ports is provided in the collector. In the projecting intake device of the internal combustion engine, the branch opening portion of the intake branch opened in the collector does not point to a surface having a large area among the surfaces forming the collector. As a result, factors that affect radiated sound, such as pressure waves and blown gas, do not act directly on the large surface area of the collector that makes the radiated sound worse, thus suppressing deterioration of the radiated sound. can do.

  (2) In the configuration described in (1), more specifically, the collector has a vertically elongated cross-sectional shape substantially along the side wall of the cylinder head, and the branch opening is formed on the side wall of the cylinder head. It is oriented in the up and down direction.

  (3) One collector is directly attached to the side wall of the cylinder head in which a plurality of intake ports are open or an attachment member attached to the side wall, and an intake branch communicating with each of the plurality of intake ports is provided in the collector. In the projecting intake device of the internal combustion engine, the branch opening portion of the intake branch opened in the collector opens in a direction substantially orthogonal to the plane formed by the crankshaft centerline and the cylinder centerline. As a result, the same effect as the above (1) can be obtained.

  (4) One collector is directly attached to the side wall of the cylinder head in which a plurality of intake ports are open or an attachment member attached to the side wall, and an intake branch communicating with each of the plurality of intake ports is provided in the collector. In the projecting intake device of the internal combustion engine, the collector has a vertically elongated cross-sectional shape substantially along the side wall of the cylinder head, and the branch opening portion of the intake branch opened in the collector is substantially along the side wall of the cylinder head. Do not point in the direction perpendicular to the vertical direction. As a result, the same effect as the above (1) can be obtained.

  (5) In the configuration according to any one of (1) to (4), an intake air amount control valve for controlling an intake air amount supplied into the collector is provided, and the branch opening is a side wall of the cylinder head Is opened toward the side where intake air is supplied into the collector via the intake air amount control valve. As a result, when air flows from the intake air amount control valve into the intake branch, the pressure loss can be reduced, and the volumetric efficiency drop when a high torque is required can be reduced.

  (6) In the configuration according to any one of (1) to (5), intake air is introduced into the collector from an intake air inlet formed in the collector, and the intake air introduction is performed in the collector. The three-dimensional region defined by extending the mouth toward the downstream side of the intake flow does not intersect the intake branch. As a result, when air flows into the intake branch from the intake air amount control valve, the pressure loss can be reduced, the length of the intake branch can be secured, and the decrease in volume efficiency when high torque is required can be reduced. it can.

  (7) In the configuration according to any one of (1) to (6), the collector has a reinforcing structure on a side opposite to a direction in which the branch opening is directed, and the branch opening is formed by the reinforcing structure. The face of the collector that is not oriented is reinforced. Thereby, the surface that causes the radiated sound can be reinforced, and the radiated sound can be suppressed.

  (8) In the configuration according to any one of (5) to (7), an air chamber is disposed in proximity to the collector via the intake air amount control valve. Thereby, when the valve opening degree of the air control valve is large, the collector and the air chamber function as a substantially single collector chamber, so that the pressure amplitude attenuation effect near the intake original sound can be further exhibited.

  (9) In the configuration according to any one of (1) to (4), an intake air amount control valve for controlling the intake air amount supplied into the collector is provided, and the collector is provided via the intake air amount control valve. Adjacent air chambers are arranged.

  (10) In the configuration according to any one of (1) to (9), a variable valve mechanism that can change a valve lift characteristic of the intake valve, and an intake air amount is adjusted by controlling the variable valve mechanism Control means.

  (11) In the configuration described in (10) above, the variable valve mechanism includes a drive shaft that rotates in conjunction with the crankshaft of the engine and an outer periphery of the drive shaft that is swingably fitted to drive the intake valve. An eccentric cam that is eccentrically provided on the drive shaft and rotates integrally with the drive shaft, and is fitted on the outer periphery of the eccentric cam so as to be relatively rotatable. 1 link, a control shaft that is arranged substantially parallel to the drive shaft and is rotationally driven by the operating angle changing actuator, a control cam that is eccentrically provided on the control shaft and rotates integrally with the control shaft, The control cam is fitted on the outer periphery of the control cam so as to be relatively rotatable, and a rocker arm having one end connected to the tip of the first link, the other end of the rocker arm, and a first cam connected to the swing cam. With 2 links .

BRIEF DESCRIPTION OF THE DRAWINGS Explanatory drawing which shows schematic structure of 1st Embodiment of the intake device of the internal combustion engine which concerns on this invention. The disassembled perspective view of the collector of the intake device of the internal combustion engine which concerns on this invention. Explanatory drawing which shows schematic structure of 2nd Embodiment of the intake device of the internal combustion engine which concerns on this invention. The top view of a reinforcement member. Sectional drawing along the AA line of FIG. Sectional drawing of the principal part of 3rd Embodiment of the intake device of the internal combustion engine which concerns on this invention. The perspective view of 3rd Embodiment of the intake device of the internal combustion engine which concerns on this invention. The perspective view of the variable valve mechanism common to all the embodiments.

Explanation of symbols

4 ... ECU4 (control means)
10 ... Working angle changing mechanism (variable valve operating device)
20 ... Phase change mechanism (variable valve operating device)
34 ... Intake port 38 ... Collector 41 ... Intake branch 45 ... Branch opening

Claims (10)

One collector is directly attached to the side wall of the cylinder head in which a plurality of intake ports are open or a mounting member attached to this side wall, and the intake branches respectively communicating with the plurality of intake ports are projected into the collector. In an intake device for an internal combustion engine,
Intake is introduced into the collector from an intake inlet formed in the collector, and a three-dimensional region defined by extending the intake inlet toward the downstream side of the intake air flow in the collector; The intake branch is configured not to cross each other,
Branch opening of the intake branches opens into the collector of the surfaces forming the collector, the internal combustion engine, characterized in that not directed to the surface in which at least the area becomes maximum intake system. The collector exhibits the shape has elongated in the vertical direction along substantially the sidewall of the cylinder head, the branch opening to claim 1, characterized in that directing the vertical direction along substantially the sidewall of the cylinder head An intake device for an internal combustion engine as described. One collector is directly attached to the side wall of the cylinder head in which a plurality of intake ports are open or a mounting member attached to this side wall, and the intake branches respectively communicating with the plurality of intake ports are projected into the collector. In an intake device for an internal combustion engine,
Intake is introduced into the collector from an intake inlet formed in the collector, and a three-dimensional region defined by extending the intake inlet toward the downstream side of the intake air flow in the collector; The intake branch is configured not to cross each other,
An intake device for an internal combustion engine, wherein a branch opening portion of an intake branch opened in a collector opens in a direction substantially perpendicular to a plane formed by a crankshaft center line and a cylinder center line. One collector is directly attached to the side wall of the cylinder head in which a plurality of intake ports are open or a mounting member attached to this side wall, and the intake branches respectively communicating with the plurality of intake ports are projected into the collector. In an intake device for an internal combustion engine,
Intake is introduced into the collector from an intake inlet formed in the collector, and a three-dimensional region defined by extending the intake inlet toward the downstream side of the intake air flow in the collector; The intake branch is configured not to cross each other,
Collector exhibits a shape has elongated in the vertical direction along substantially the sidewall of the cylinder head, the branch opening of the intake branches opens into the collector, not directed to a direction perpendicular to the vertical direction along substantially the sidewall of the cylinder head An intake device for an internal combustion engine characterized by the above.   An intake air amount control valve for controlling an intake air amount supplied into the collector, and the branch opening is formed in the collector through the intake air amount control valve in the vertical direction substantially along the side wall of the cylinder head. The intake device for an internal combustion engine according to any one of claims 1 to 4, wherein the intake device opens toward a side to which intake air is supplied. The collector has a reinforcing structure on the opposite side of the direction in which the branch opening is directed, and a surface of the collector to which the branch opening is not directed is reinforced by the reinforcing structure. 6. An intake device for an internal combustion engine according to any one of 5 above. The intake device for an internal combustion engine according to claim 5 or 6 , wherein an air chamber is arranged close to the collector via the intake air amount control valve.   5. An intake air amount control valve for controlling an intake air amount supplied into the collector, and an air chamber is disposed in proximity to the collector via the intake air amount control valve. An intake device for an internal combustion engine according to any one of the above. Claim 1-8 for the variable valve mechanism capable of changing a valve lift characteristic of the intake valve, and control means for adjusting the intake air quantity by controlling the variable valve mechanism, characterized in that it has a An intake device for an internal combustion engine according to claim 1. The variable valve mechanism is provided between a drive shaft that rotates in conjunction with the crankshaft of the engine and a swing cam that is fitted on the outer periphery of the drive shaft so as to be swingable and drives the intake valve. And
An eccentric cam provided eccentric to the drive shaft and rotating integrally with the drive shaft;
A first link that is fitted on the outer periphery of the eccentric cam so as to be relatively rotatable;
A control shaft disposed substantially parallel to the drive shaft and driven to rotate by an operating angle changing actuator;
A control cam provided eccentric to the control shaft and rotating integrally with the control shaft;
A rocker arm that is fitted on the outer periphery of the control cam so as to be relatively rotatable and has one end connected to the tip of the first link;
10. The intake device for an internal combustion engine according to claim 9 , further comprising: a second link connected to the other end of the rocker arm and the swing cam.

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