JP2014109248A5 - - Google Patents

Description

4-cylinder engine and operation method of 4-cylinder engine

The present invention relates to a four-cylinder engine in which an explosion interval of four cylinders is 270 degrees-180 degrees-90 degrees-180 degrees in terms of crank angle, and a method for operating the four-cylinder engine .

  Conventionally, as a crankshaft of a four-cylinder engine mounted on a vehicle, a one-plane type crankshaft (180-degree crankshaft) in which four crankpins are located on one virtual plane is described in Patent Document 1. There are two-plane type crankshafts. Two crank pins of the two-plane type crankshaft are arranged on two virtual planes orthogonal to each other when viewed from the axial direction of the crankshaft.

  A vehicle equipped with a 4-cylinder engine using this type of 2-plane crankshaft or a V-type 4-cylinder engine having a 1-plane crankshaft has a feeling that the accelerator operation and the behavior of the vehicle body match. Known to give to. The reason for this is thought to be that the inertia torque of the engine is almost eliminated by this crank layout. The explosion interval of this type of four-cylinder engine is often 270 degrees-180 degrees-90 degrees-180 degrees in crank angle.

  The combustion pressure and generated torque of such a four-cylinder engine change as shown in FIG. In FIG. 28, the horizontal axis indicates the crank angle, and the vertical axis indicates the combustion pressure and the generated torque. FIG. 28 shows an example in which the ignition order is the first cylinder → the third cylinder → the second cylinder → the fourth cylinder. In this case, if an explosion occurs in the first cylinder at the crank angle indicated by A in FIG. 28, the explosion in the third cylinder occurs when the crank angle B is 270 degrees ahead of the crank angle A. Arise. Then, when the crankshaft is further rotated 180 degrees and the crank angle is C, an explosion occurs in the second cylinder. After that, when the crankshaft is rotated 90 degrees and the crank angle is D, an explosion occurs in the fourth cylinder. . Thereafter, when the crankshaft further rotates 180 degrees and reaches the crank angle E, explosion occurs again in the first cylinder. On the other hand, the torque generated on the output shaft of this 4-cylinder engine rises at the same interval as the explosion interval. That is, torque is generated at unequal intervals as in unequal intervals explosions.

Japanese Patent No. 4553346

  In a four-cylinder engine with an explosion interval of 270 ° -180 ° -90 ° -180 ° in crank angle, a problem occurs when the rotational speed is low. This problem is that a passenger in a vehicle equipped with this type of engine feels uncomfortable. The main reason for feeling uncomfortable is that the explosion intervals of the four cylinders are unequally spaced, and the drive energy per unit time becomes uneven. The drive energy here is energy for rotating the output shaft of the engine (vehicle drive wheel). The magnitude of the torque applied to the output shaft changes so as to be proportional to the magnitude of the drive energy.

  The torque rises twice in a short time due to explosion occurring in two cylinders with an explosion interval of 90 degrees in crank angle. When the torque rises twice in such a short time, for example, in the engine shown in FIG. 28, when an explosion occurs in the second cylinder at the crank angle C and in the fourth cylinder at the crank angle D, This is when an explosion occurred. That is, because the torque is continuously generated in such a short time, the driving energy becomes high in a part of one cycle, and the driving energy per unit time is uneven as described above. Become.

  When the engine speed is low, an occupant of a vehicle equipped with this four-cylinder engine may experience such a torque increase that occurs continuously in a short time as a single torque increase. The magnitude of the torque that is remembered as this one time torque increase is likely to be felt larger than the magnitude of the torque that increases during the other two explosions. This is because it takes a long time for the torque to rise due to the torque rising twice in a short time. That is, as indicated by a two-dot chain line in FIG. 28, the occupant actually feels that the torque generated twice is generated only once, and in other cylinders (the first cylinder and the third cylinder). The illusion that a greater torque was generated than when an explosion occurred.

  For this reason, the occupant feels an irregular torque change when the engine speed is low, and feels uncomfortable.

The present invention has been made to solve such a problem. In an operating state in which an occupant is likely to feel torque fluctuation, a four-cylinder engine with unequal interval explosion in which a change in driving energy per unit time is small, and the four-cylinder engine. An object is to provide a method of operating an engine .

To this end, 4-cylinder engine according to the present invention includes a cylinder head having a cylinder body, attached to the Shirindabode I, an intake port and an exhaust port for each of the cylinder bore having four cylinder holes, a spark plug of the cylinder bore each mounted to the cylinder head, the ignition device including the spark plug, an intake apparatus connected to the intake port, and an exhaust device connected to said exhaust port, said cylinder bore The four pistons slidably fitted inside and a crankshaft connected to these pistons via connecting rods, and the explosion interval of the four cylinders constituted by the four cylinder holes is determined by the crank angle. a 270 ° -180 ° -90 ° -180 °, when the rotational speed of the engine is lower than a predetermined value, the firing interval is 9 At least the indicated mean effective pressure of one cylinder of the two cylinders as a degree, and characterized in that the explosion space is further provided with a make lower discomfort canceller than the indicated mean effective pressure of the other cylinders not 90 degrees To do.

The present invention is characterized in that, in the above invention, the amount by which the indicated mean effective pressure is reduced increases as the engine speed decreases and the load increases.

According to the present invention, in the above invention, the discomfort canceling unit utilizes a phenomenon in which the illustrated mean effective pressure decreases due to a delay in ignition timing, and at least one of the two cylinders having the explosion interval of 90 degrees. The ignition timing of this cylinder is delayed from the ignition timing of other cylinders whose explosion interval is not 90 degrees.

According to the present invention, in the above invention, the intake device connected to two cylinders having an explosion interval of 90 degrees is provided in one surge tank connected to the intake ports of both cylinders, and the surge tank. The discomfort canceling unit uses a phenomenon that the illustrated mean effective pressure decreases as the intake air amount decreases, and by controlling the opening of the throttle valve, The intake air amount of two cylinders having an explosion interval of 90 degrees is made smaller than the intake air amount of other cylinders having an explosion interval of not 90 degrees.

According to the present invention, in the invention, the intake device connected to two cylinders having an explosion interval of 90 degrees includes a throttle valve for each cylinder, and the discomfort eliminating unit reduces the intake air amount. By utilizing the phenomenon that the indicated mean effective pressure decreases, by controlling the opening degree of the throttle valve, the intake air amount of at least one of the two cylinders having the explosion interval of 90 degrees, The explosion interval is smaller than the intake air amount of other cylinders that are not 90 degrees.

The present invention provides the variable valve mechanism according to the invention, wherein the intake device connected to two cylinders having an explosion interval of 90 degrees is capable of changing an opening / closing timing and a lift amount of an intake valve for opening / closing the intake port. The discomfort eliminating unit utilizes a phenomenon in which the illustrated mean effective pressure decreases as the amount of intake air decreases, and the explosion interval is set to 90 by controlling the operation of the variable valve mechanism. It is characterized in that the intake air amount of at least one of the two cylinders at a degree is made smaller than the intake air amount of the other cylinders whose explosion interval is not 90 degrees.
A method of operating a four-cylinder engine according to the present invention includes a cylinder body having four cylinder holes, a cylinder head attached to the cylinder body and having an intake port and an exhaust port for each cylinder hole, and attached to the cylinder head. A spark plug for each of the cylinder holes, an ignition device including the spark plug, an intake device connected to the intake port, an exhaust device connected to the exhaust port, and slidable in the cylinder hole The explosion interval of a four-cylinder engine having four pistons fitted to each other and crankshafts connected to these pistons via connecting rods is 270 ° -180 ° -90 ° -180 ° in crank angle, When the engine speed is lower than a predetermined value, at least one of the two cylinders having the explosion interval of 90 degrees The shown mean effective pressure, firing interval is carried out by lower than indicated mean effective pressure of the other cylinders not 90 degrees.
The present invention is characterized in that, in the operation method of the four-cylinder engine, the amount by which the indicated mean effective pressure is reduced increases as the engine speed decreases and the load increases.
According to the present invention, in the operation method of the four-cylinder engine, the ignition timing of at least one of the two cylinders having the explosion interval of 90 degrees is delayed from the ignition timing of the other cylinders having the explosion interval not 90 degrees. Thus, the indicated mean effective pressure of at least one of the two cylinders having the explosion interval of 90 degrees is reduced.
According to the present invention, in the operation method of the four-cylinder engine, the intake device connected to the two cylinders having the explosion interval of 90 degrees includes one surge tank connected to the intake ports of the two cylinders, One throttle valve provided in the surge tank, and controlling the opening degree of the throttle valve so that the intake air amount of two cylinders having an explosion interval of 90 degrees is set to another cylinder whose explosion interval is not 90 degrees. The illustrated mean effective pressure of the two cylinders having the explosion interval of 90 degrees is reduced by making the amount less than the intake air amount.
According to the present invention, in the operation method of the four-cylinder engine, the intake device connected to two cylinders having an explosion interval of 90 degrees includes a throttle valve for each cylinder, and controls an opening degree of the throttle valve. By setting the intake air amount of at least one of the two cylinders having the explosion interval of 90 degrees to be smaller than the intake air amount of the other cylinders having the explosion interval not 90 degrees, the explosion interval is 90 degrees. The illustrated mean effective pressure of at least one of the two cylinders is reduced.
According to the present invention, in the operation method of the four-cylinder engine, the intake device connected to two cylinders having the explosion interval of 90 degrees can change the opening / closing timing and lift amount of the intake valve that opens and closes the intake port A variable valve mechanism that controls the operation of the variable valve mechanism, and determines the intake air amount of at least one of the two cylinders with an explosion interval of 90 degrees, and the explosion interval is not 90 degrees. The illustrated mean effective pressure of at least one of the two cylinders having the explosion interval of 90 degrees is reduced by making the amount less than the intake air amount of the cylinder.

According to the four-cylinder engine and the operation method of the four-cylinder engine according to the present invention, the output torque of the engine rises twice in a short time due to an explosion occurring in two cylinders whose explosion interval is 90 degrees in crank angle. . When the occupant feels torque fluctuations of the engine, that is, when the engine speed is lower than a predetermined value, the indicated mean effective pressure of at least one of the two cylinders having an explosion interval of 90 degrees in crank angle However, it falls below the indicated mean effective pressure of the other cylinders whose explosion interval is not 90 degrees.

As a result, the magnitude of torque generated in at least one of the two cylinders having an explosion interval of 90 degrees in crank angle is smaller than the magnitude of torque generated in the other two cylinders. As a result, the phenomenon that the drive energy becomes higher than others in a part of one cycle due to the continuous generation of torque in a short time is suppressed. Therefore, according to the present invention, it is possible to provide a four- cylinder engine in which the driving energy of the engine is uniform and a method for operating the four-cylinder engine .

As described above, a passenger of a vehicle equipped with a four-cylinder engine having an explosion interval of 270 ° -180 ° -90 ° -180 ° is when the torque increases continuously in a short time when the crank angle is 90 °.恰, it is easy to feel the illusion that the torque increased at once. In addition, the occupant feels that the magnitude of the torque is large because the occupant feels that the time during which the torque is increasing is relatively long.
However, according to the four-cylinder engine and the operation method of the four-cylinder engine according to the present invention, when an explosion occurs in two cylinders having an explosion interval of 90 degrees in crank angle, an explosion occurs in the other two cylinders. It is possible to give the occupant a feeling that the torque is increased by 1 degree with the same magnitude as that of the vehicle.

As described above, according to the four-cylinder engine and the operation method of the four-cylinder engine, it is possible to cause the occupant to experience vibrations, torque fluctuations, and the like equivalent to those of the three-cylinder engine that is not far apart from each other. A three-cylinder engine in which explosions occur at equal intervals does not give any sense of incongruity to a passenger of a vehicle equipped with this engine.
Therefore, by applying the four-cylinder engine and the four-cylinder engine operation method according to the present invention to the vehicle engine , the passenger feels uncomfortable even when the passenger is in an operating state in which engine torque fluctuations are easily felt. It becomes difficult.

It is sectional drawing which shows the structure of the 4-cylinder engine by 1st Embodiment. It is a top view which shows the structure of the intake device of the 4-cylinder engine by 1st Embodiment. It is a perspective view which shows the structure of the crankshaft and power transmission system by 1st Embodiment. It is a block diagram which shows the structure of the control system of the 4-cylinder engine by 1st Embodiment. It is a figure which shows the change of the position of the piston and crankpin of each cylinder by 1st Embodiment. It is a figure which shows the ignition timing map for the 1st, 3rd cylinder by 1st Embodiment. It is a figure which shows the ignition timing map for the 2nd, 4th cylinder by 1st Embodiment. It is a graph which shows the change of the combustion pressure with respect to the crank angle by 1st Embodiment, and the generated torque. It is a flowchart for demonstrating operation | movement (4-cylinder engine operating method) of the control apparatus by 1st Embodiment. It is a top view which shows the structure of the intake device of the 4-cylinder engine by 2nd Embodiment. It is a block diagram which shows the structure of the control system of the 4-cylinder engine by 2nd Embodiment. It is a map which shows the throttle valve opening degree of the 2nd, 4th cylinder by 2nd Embodiment. It is a flowchart for demonstrating operation | movement (4-cylinder engine operating method) of the control apparatus by 2nd Embodiment. It is a top view which shows the modification 1 of the intake device by 2nd Embodiment. It is a top view which shows the modification 2 of the intake device by 2nd Embodiment. It is a top view which shows the structure of the intake device of the 4-cylinder engine by 3rd Embodiment. It is a block diagram which shows the structure of the control system of the 4-cylinder engine by 3rd Embodiment. It is a map which shows the throttle-valve opening of the 2nd, 4th cylinder by 3rd Embodiment. It is a flowchart for demonstrating operation | movement (4-cylinder engine operating method) of the control apparatus by 3rd Embodiment. It is a top view which shows the modification 1 of the intake device by 3rd Embodiment. It is a top view which shows the modification 2 of the intake device by 3rd Embodiment. It is a top view which shows the structure of the intake device of the 4-cylinder engine by 4th Embodiment. It is a block diagram which shows the structure of the control system of the 4-cylinder engine by 4th Embodiment. It is a map which shows the intake valve opening degree of the 2nd and 4th cylinder by 4th Embodiment. It is a flowchart for demonstrating operation | movement (4-cylinder engine operating method) of the control apparatus by 4th Embodiment. It is a top view which shows the modification 1 of the intake device by 4th Embodiment. It is a top view which shows the modification 2 of the intake device by 4th Embodiment. It is a graph which shows the change of the combustion pressure with respect to the crank angle in the conventional 4-cylinder engine, and the generated torque.

(First embodiment)
Hereinafter, an embodiment of a four-cylinder engine and a method for operating the four- cylinder engine according to the present invention will be described in detail with reference to FIGS.
A four-cylinder engine 1 shown in FIG. 1 is a four-cycle in-line four-cylinder engine or a four-cycle parallel four-cylinder engine mounted on a vehicle (not shown). FIG. 1 shows only main components of the four-cylinder engine 1. As shown in FIG. 1, the four-cylinder engine 1 includes a cylinder body 3 having four cylinder holes 2, a cylinder head 4 attached to the cylinder body 3, a head cover 5 attached to the cylinder head 4, and the like. It has.

  As shown in FIG. 2, the four cylinder holes 2 are formed in the cylinder body 3 in a state of being aligned in a row in the radial direction. In the four-cylinder engine, a first cylinder to a fourth cylinder are configured by using these four cylinder holes 2. In FIG. 2, the first cylinder is indicated by reference numeral # 1, and the second cylinder is indicated by reference numeral # 2. The third cylinder is indicated by reference numeral # 3, and the fourth cylinder is indicated by reference numeral # 4. The first to fourth cylinders are arranged in order from the top in FIG.

As shown in FIG. 1, pistons 6 are slidably fitted in the four cylinder holes 2, respectively. These pistons 6 are connected to crankshafts 8 to be described later via connecting rods 7, respectively.
In the cylinder head 4, recesses 4 a that form the ceiling wall of the combustion chamber S are formed at positions facing the cylinder holes 2. These recesses 4a are formed in a circular shape when viewed from the cylinder hole 2 side.

In these recesses 4a, the downstream end of the intake port 9 is bifurcated and opened, and the upstream end of the exhaust port 10 is bifurcated and opened.
The cylinder head 4 drives two intake valves 11 for opening and closing the intake port 9, two exhaust valves 12 for opening and closing the exhaust port 10, and driving these intake valves 11 and exhaust valves 12. The valve operating device 13, the ignition plug 14, and the fuel injection injector 15 (see FIG. 4) are provided. As the fuel injector 15, one that injects fuel into the intake port 9 or the intake pipe 17 upstream of the intake port 9 or the recess 4a can be used.

  As shown in FIG. 2, the upstream end of the intake port 9 opens to one side of the cylinder head 4 and is connected to the intake device 16. The intake device 16 includes one surge tank 18 connected to each intake port 9 by an intake pipe 17. The surge tank 18 is provided with a throttle valve 19 at one end in the direction in which the cylinder holes 2 are arranged, and is connected to an air cleaner (not shown) via the throttle valve 19. The throttle valve 19 is remotely operated by an occupant.

  The intake duct 20 that connects the air cleaner to the throttle valve 19 is provided with an air amount measuring device 21 for measuring the flow rate of the air flowing through the intake duct 20. The air amount measuring device 21 can be constituted by an air flow meter, for example. The air amount measuring device 21 is connected to a control device 22 to be described later, and sends detection data that can specify the intake air amount to the control device 22.

The downstream end of the exhaust port 10 opens to the other side of the cylinder head 4 as shown in FIG. Each exhaust pipe 24 of the exhaust device 23 is connected to the downstream end of all the exhaust ports 10 .
The valve gear 13 is of the DOHC type having an intake cam shaft 25 and an exhaust cam shaft 26. The intake camshaft 25 and the exhaust camshaft 26 are connected to the crankshaft 8 via a winding transmission member (not shown). The valve operating system of the valve operating device 13 is not limited to the DOHC type, and other valve operating systems such as the SOHC type may be used.
The spark plug 14 is provided for each cylinder hole 2 and is attached to the central portion of the recess 4 a in the cylinder head 4. The spark plug 14 constitutes an ignition device 27 (see FIG. 4) of the four-cylinder engine 1 together with a control device 22 described later.

As shown in FIG. 3, the crankshaft 8 is a so-called two-plane type and includes crank pins 31 to 34 for each cylinder. The first cylinder crankpin 31 and the fourth cylinder crankpin 34 of the crankshaft 8 according to this embodiment are located on the first virtual plane PL1. The first cylinder crankpin 31 is connected to the first cylinder piston 6 via a connecting rod 7. The crank pin 34 for the fourth cylinder is connected to the piston 6 of the fourth cylinder via the connecting rod 7. The second cylinder crankpin 32 and the third cylinder crankpin 33 of the crankshaft 8 are located on a second imaginary plane PL2 orthogonal to the first imaginary plane PL1. The second cylinder crank pin 32 is connected to the piston 6 of the second cylinder via a connecting rod 7. The crank pin 33 for the third cylinder is connected to the piston 6 of the third cylinder via the connecting rod 7.

The crankpins 31 to 34 of the crankshaft 8 are shown in FIG. 5 as the crankshaft 8 rotates in the direction indicated by the arrow in FIG. 3, that is, clockwise when viewed from the first cylinder side to the fourth cylinder side. To move. FIG. 5 is a diagram showing the positions of the piston 6 and the crank pins 31 to 34 of each cylinder when the crankshaft 8 is rotated by 90 degrees. As shown in FIG. 5, the ignition order of the four-cylinder engine 1 when using the crankshaft 8 is the order of the first cylinder , the third cylinder , the second cylinder , and the fourth cylinder.

  The explosion interval between the explosion occurring in the first cylinder and the explosion occurring in the third cylinder is 270 degrees in crank angle. The explosion interval between the explosion occurring in the third cylinder and the explosion occurring in the second cylinder is 180 degrees in crank angle. The explosion interval between the explosion occurring in the second cylinder and the explosion occurring in the fourth cylinder is 90 degrees in crank angle. The explosion interval between the explosion occurring in the fourth cylinder and the explosion occurring in the first cylinder is 180 degrees.

That is, the explosion interval of the four-cylinder engine 1 is 270 degrees-180 degrees-90 degrees-180 degrees in crank angle. As described above, the four-cylinder engine 1 having such an explosion interval may give a passenger an uncomfortable feeling. However, the four-cylinder engine 1 according to this embodiment is unlikely to give the passenger an uncomfortable feeling due to the action of the discomfort eliminating means 35 (see FIG. 1) described later. This discomfort eliminating means 35 corresponds to the “discomfort eliminating unit” referred to in the present invention. The discomfort eliminating means 35 determines the indicated mean effective pressure of at least one of the second and fourth cylinders having an explosion interval of 90 degrees when the engine operating state is a predetermined state. A configuration is adopted in which the average effective pressure of the first cylinder and the third cylinder, which are not 90 degrees, is lowered from the indicated average effective pressure. The indicated mean effective pressure is obtained by dividing the work directly applied to the piston 6 by the combustion gas by the stroke volume. As will be described in detail later, the discomfort eliminating means 35 according to this embodiment utilizes a phenomenon in which the indicated mean effective pressure decreases due to the ignition timing being delayed.

  As shown in FIG. 3, driving wheels 44 are connected to the crankshaft 8 via a clutch 41, a transmission 42, and a power transmission mechanism 43. The power transmission mechanism 43 shown in FIG. 3 is drawn so that the axis of the drive wheels 44 is orthogonal to the axis of the crankshaft 8. However, the present invention is not limited to such a limitation. That is, the power transmission mechanism 43 can be configured such that the axis of the drive wheel 44 is parallel to the axis of the crankshaft 8.

A crank angle detection sensor 45 for detecting the rotational speed of the engine based on the rotation angle of the crankshaft 8 is disposed in the vicinity of the clutch 41 shown in FIG. The crank angle detection sensor 45 sends detection data that can specify the rotation angle of the crankshaft 8 to the control device 22.
The transmission 42 shown in FIG. 3 includes a shift position sensor 46 for detecting a shift position. The shift position sensor 46 sends detection data that can specify the number of shift stages of the transmission 42 to the control device 22. Since the number of gears is a numerical value that can identify the speed ratio of the transmission 42, it can also be used to obtain the vehicle speed by calculation in association with the engine speed.

As shown in FIG. 4, the control device 22 includes a fuel control unit 51, an ignition timing control unit 52, and a storage unit 53.
The fuel control unit 51 controls the fuel injection amount and fuel injection timing of the fuel injection injector 15.
The ignition timing control unit 52 sets the ignition timings of the first cylinder to the fourth cylinder based on a predetermined procedure, and sends an ignition signal to the ignition device 27 when the ignition timing is reached. In this embodiment, the ignition timing control unit 52 and the ignition device 27 constitute the discomfort eliminating means 35 described above.

The setting of the ignition timing by the ignition timing control unit 52 is performed so as to reduce a sense of discomfort experienced by the occupant due to unequal interval explosions when the occupant is in an operating state in which it is easy for the occupant to feel torque fluctuations of the engine. In this embodiment, in order to reduce the uncomfortable feeling, when the engine speed is lower than a predetermined value and the load is in a predetermined region, the indicated mean effective pressures of the second cylinder and the fourth cylinder are changed. The two cylinders (No. 1 and No. 3 cylinders whose explosion interval is not 90 degrees) are reduced below the indicated mean effective pressure. In this embodiment, the method of reducing the indicated mean effective pressure is a method of retarding the ignition timing. That is, in the four-cylinder engine 1 according to this embodiment, as will be described in detail later, the ignition timings of the second cylinder and the fourth cylinder are higher than the ignition timings of the other two cylinders in an operating state in which torque fluctuations are easily felt. It is retarded by a predetermined amount. Control in which the ignition timing control unit 52 retards the ignition timings of the second cylinder and the fourth cylinder as compared with the ignition timings of the other cylinders in this manner is simply referred to as “retard angle control”.

  The ignition timing of the first cylinder to the fourth cylinder can be set using maps as shown in FIGS. 6 and 7, for example. 6 and 7 show maps in which the ignition timing is assigned to the engine speed and load. FIG. 6 is an ignition timing map showing ignition timings of the first cylinder and the third cylinder. FIG. 7 is an ignition timing map showing ignition timings for the second cylinder and the fourth cylinder. These maps are stored in the storage unit 53 of the control device 22.

  The amount of retardation when the retardation control is performed is set so that the amount of decrease in the indicated mean effective pressure due to the retardation increases in accordance with the operating state of the engine. The operating state of the engine can be specified using the rotational speed and load of the engine. That is, the retard amount is basically set so that the amount of decrease in the indicated mean effective pressure increases as the engine speed decreases and the load increases.

The ignition timings of the second cylinder and the fourth cylinder shown in FIG. 7 are A-α degrees when the ignition timing is before the top dead center (BTDC) A degrees in the first cylinder and the third cylinder, that is, an α degree retardation. Is done. Further, when the ignition timing is B degrees in the first cylinder and the third cylinder, the ignition timing of the second cylinder and the fourth cylinder is B-β degrees, that is, compared with the ignition timing of the first cylinder and the third cylinder. Be retarded by β degrees. When the ignition timing is C degrees in the first cylinder and the third cylinder, the ignition timing of the second cylinder and the fourth cylinder is C-γ degrees, that is, γ degrees compared to the ignition timings of the first cylinder and the third cylinder. Be retarded. When the ignition timing is D degrees in the first cylinder and the third cylinder, that is, when the engine speed and load are high, the ignition timings of the second cylinder and the fourth cylinder are also D degrees. The magnitudes of the absolute values of α, β, and γ are not necessarily in this order.

The maps shown in FIGS. 6 and 7 are provided for each gear stage of the transmission. The map used when the number of gears is, for example, 1st speed is formed so as to be adapted to the driving state when the vehicle speed is low, including when the vehicle starts. That is, if the vehicle speed is the same, the first-speed map is formed so that the amount of retardation is smaller than the second-speed map. That is, the map is formed so that the amount of retardation increases as the number of gears increases at the same vehicle speed.

When the ignition timing becomes later than usual, the indicated mean effective pressure during combustion decreases. For this reason, when the retard amount corresponding to the operating state of the engine is read from the above-described map and the ignition timings of the second cylinder and the fourth cylinder are retarded by the retard amount from the ignition timings of the other two cylinders, The indicated mean effective pressures of the second and fourth cylinders are lower than those of the other two cylinders. That is, as shown in FIG. 8, the combustion pressures of the second and fourth cylinders are lower than the combustion pressures of the first and third cylinders. As the combustion pressure decreases, torques T2 and T4 generated by explosions in the second and fourth cylinders become smaller than the torques T1 and T3 of the other cylinders. The occupant may have an illusion that the torques T2 and T4 generated in this manner are generated only once. That is, the occupant may feel as if the combined torque TA has been generated only once, as indicated by a two-dot chain line in FIG.

The magnitude of the torque T2, which exploded in the second cylinder occurs occurred, the magnitude of the torque T4 which is exploded in the fourth cylinder occurs caused, as described above, exploded in the other two cylinders occurs caused less than the magnitude of the torque T1, T3. Therefore, it is easy for the occupant to feel that the magnitude of the synthetic torque TA does not greatly differ from the magnitudes of the torques T1 and T3 generated by explosions in other cylinders.

Next, a method for operating the four-cylinder engine according to this embodiment will be described . The control device 22 configured as described above operates as shown in the flowchart of FIG. That is, after the four-cylinder engine 1 is started in step S1 in the flowchart of FIG. 9, the control device 22 determines in step S2 whether the engine speed is lower than a predetermined value and whether the load is in a predetermined region. Is determined. The predetermined value or the predetermined region here is a value or a region in which the occupant easily feels a torque fluctuation of the engine, that is, a value or a region in which the retardation control is required. Specifically, in step S <b> 2, first, the control device 22 reads an ignition timing map (FIG. 6 and FIG. 7) corresponding to the current gear position number from the storage unit 53. Then, the control device 22 applies the current engine speed and the engine load to this ignition timing map, and reads the ignition timing of each cylinder from each map.

  When the rotational speed and load of the four-cylinder engine 1 are in the region indicated by symbol D in the maps shown in FIGS. 6 and 7, that is, when the retard control is not required, the process proceeds from step S2 to step S3. The ignition timing is controlled so that the ignition timings before the top dead center (BTDC) of the first to fourth cylinders coincide with each other without performing control.

  On the other hand, when the engine rotational speed and the load are in the area indicated by reference signs A to C in the map shown in FIG. At this time, the ignition timings of the first and third cylinders are set to the ignition timing read from the ignition timing map shown in FIG. The ignition timings of the second and fourth cylinders are set to the ignition timings read from the ignition timing map shown in FIG. 7, that is, the ignition timings delayed from the ignition timings of the first and third cylinders. The control device 22 repeatedly performs the above control while the engine is operating to control the ignition timing.

In the four-cylinder engine 1 configured as described above, when the engine speed is lower than a predetermined value and the load is in a predetermined region and the occupant is in an operating state in which the engine torque is likely to be felt, the explosion interval The ignition timings of the two cylinders (the second cylinder and the fourth cylinder) having a crank angle of 90 degrees are delayed from the ignition timings of the other cylinders by a predetermined delay amount. For this reason, the indicated mean effective pressure of the two cylinders whose explosion interval is 90 degrees in crank angle is lower than the indicated mean effective pressure of the other two cylinders. As a result, the magnitudes of torques T2 and T4 that increase due to explosions occurring in the second and fourth cylinders are smaller than the magnitudes of torques T1 and T3 that increase due to explosions occurring in the first and third cylinders.

In addition, when torques T2 and T4 smaller than torques T1 and T3 are continuously generated in a short time, the occupant has the same magnitude as when an explosion occurred in the other cylinders (first and third cylinders). It is easy to make an illusion that the torque has risen once.
That is, according to the four-cylinder engine 1 and the operation method of the four-cylinder engine according to this embodiment, when an explosion occurs in two cylinders (the second cylinder and the fourth cylinder) having an explosion interval of 90 degrees in crank angle. In addition, it is possible to give the occupant a feeling that the torque rises once with the same magnitude as when an explosion occurred in the other two cylinders (the first and third cylinders). For this reason, the four-cylinder engine 1 makes the occupant experience vibration, torque fluctuation, and the like equivalent to those of a three-cylinder engine where the explosion interval is not so far away. A three-cylinder engine in which explosions occur at equal intervals does not give the passengers any sense of incongruity.

Therefore, according to this embodiment, even when the occupant is in an operating state where it is easy to feel torque fluctuations of the engine, a 4-cylinder engine that does not give the occupant a sense of incongruity, in other words, a 4-cylinder engine in which the drive energy is uniform. And the operating method of this 4-cylinder engine can be provided. When the present invention was applied to a four-cylinder engine of an automobile and the inventor ran the automobile, there was no sense of incongruity that caused an unequal interval explosion.

By the way, it is known that the fuel consumption of an engine deteriorates as the ignition timing is retarded.
In this embodiment, the retard amount of the ignition timing is set so that the indicated mean effective pressure decreases according to the operating state of the engine. For this reason, the retardation amount can be set small so as to be a necessary minimum. Therefore, according to this embodiment, it is possible to provide a four-cylinder engine and a driving method of the four- cylinder engine that can achieve both the elimination of the uncomfortable feeling given to the occupant and the fuel consumption.

In this embodiment, the indicated mean effective pressure of the second and fourth cylinders with an explosion interval of 90 degrees retards the ignition timing for the first and third cylinders with an explosion interval of not 90 degrees. Can be lowered. The ignition timing of the engine can be easily changed by electronic control by the control device 22.
Therefore, the four-cylinder engine 1 according to this embodiment can be realized using an existing four-cylinder engine while suppressing an increase in cost.

The ignition timing of the second cylinder and the ignition timing of the fourth cylinder according to this embodiment are the same. However, the present invention is not limited to such a limitation. That is, the ignition timing of the ignition timing and fourth cylinder of the second cylinder may be different ignition timing from each other. Further, it is possible to adopt a configuration in which the ignition timing of one cylinder of the second cylinder and the fourth cylinder coincides with the ignition timing of the first cylinder or the third cylinder, and the ignition timing of the other cylinder is retarded. .
That is, when the present invention is applied to the four-cylinder engine 1 in which the ignition timing of the second cylinder and the ignition timing of the fourth cylinder can be changed, the discomfort eliminating means 35 includes two cylinders (2 The ignition timing of at least one of the second cylinder and the fourth cylinder) is delayed from the ignition timing of the other cylinders (the first cylinder and the third cylinder) whose explosion interval is not 90 degrees.

In order to realize such ignition timing control, for example, an ignition timing map for the second cylinder and an ignition timing map for the fourth cylinder formed separately from the ignition timing map for the second cylinder are used. It is possible.
By adopting such a configuration, it is possible to individually control the magnitude of the torque generated when an explosion occurs in the second cylinder and the magnitude of the torque generated when an explosion occurs in the fourth cylinder. For this reason, by adopting this configuration, it becomes possible to easily achieve uniform driving energy of the engine.

Oite to the first embodiment, conditions for firing interval reduces from the indicated mean effective pressure of two cylinders two cylinders indicated mean effective pressure of the other of the 90 degrees, the rotational speed of the engine is in a predetermined smaller than the value, the load is to have a predetermined area. However, the present invention can add the vehicle speed to one of these conditions without being limited to such a limitation. In this case , as described in paragraph 0034 , the vehicle speed can be obtained by calculation from the engine speed detected by the crank angle detection sensor 45 and the number of shift stages detected by the shift position sensor 46 . In this case, the vehicle speed can be obtained by connecting a vehicle speed sensor 54 to the control device 22 as shown in FIG.

(Second Embodiment)
In order to reduce the indicated mean effective pressure of the two cylinders having an explosion interval of 90 degrees, as shown in FIGS. 10 to 13, members identical or equivalent to those described with reference to FIGS. 1 to 9 are given the same reference numerals, and detailed description thereof is omitted as appropriate.

The four-cylinder engine 1 shown in FIG. 10 is different from the four-cylinder engine in the first embodiment shown in FIGS. 1 to 9 in the configuration of the ignition system and the intake device 16, and the other configurations are the same. is there. Ignition system of a four-cylinder engine 1 according to this embodiment, since to differentiate the intake air amount for each cylinder as will be described later, the ignition timing in all the cylinders are configured to optimize. In this embodiment, the retardation control as shown in the first embodiment is not performed. The intake device 16 according to this embodiment includes a first intake device 61 and a second intake device 62.

  The first intake device 61 includes a first surge tank 63. The first surge tank 63 is connected to the intake port 9 of the first cylinder via a first intake pipe 64 and is connected to the intake port 9 of the third cylinder via a third intake pipe 65. ing. That is, the first surge tank 63 is connected only to the first and third cylinders. An electric first throttle valve 66 is provided at one end of the first surge tank 63. An air amount measuring device 21 is provided on the upstream side of the intake air from the first throttle valve 66.

  The second intake device 62 includes a second surge tank 67 adjacent to the first surge tank 63. The second surge tank 67 is connected to the intake port 9 of the second cylinder via a second intake pipe 68 and is connected to the intake port 9 of the fourth cylinder via a fourth intake pipe 69. Has been. That is, the second surge tank 67 is connected only to the second cylinder and the fourth cylinder. An electric second throttle valve 70 is provided at one end of the second surge tank 67. An air amount measuring device 21 is provided on the upstream side of the intake air from the second throttle valve 70. The operations of the second throttle valve 70 and the first throttle valve 66 are controlled by a throttle valve control unit 71 of the control device 22 shown in FIG.

The throttle valve control unit 71 controls the opening degrees of the first throttle valve 66 and the second throttle valve 70 based on the operation amount of the accelerator operator 72 (see FIG. 11) operated by the occupant. The opening degree of the first throttle valve 66 increases or decreases so as to be proportional to the operation amount of the accelerator operation element 72. The opening degree of the second throttle valve 70 is set to be smaller than the opening degree of the first throttle valve 66 when the occupant feels torque fluctuations of the engine easily, and the first opening degree when the occupant is in any other operating state . The opening of the throttle valve 66 is made coincident.

The throttle valve control unit 71 according to this embodiment controls the opening degree of the second throttle valve 70 using the map shown in FIG.
The map shown in FIG. 12 shows that the opening degree of the second throttle valve 70 is smaller by α, β, γ degrees than the opening degree of the first throttle valve 66 (A degree, B degree, C degree, D degree). Opening degrees (A-α degrees, B-β degrees, C-γ degrees) are assigned to the engine speed and load. This map is provided for each shift stage number of the transmission 42 and is stored in the storage unit 53 of the control device 22.

  When the opening degree of the second throttle valve 70 is reduced, the intake air amount is reduced in the second cylinder and the fourth cylinder, and the indicated mean effective pressure during combustion of these cylinders is reduced. The discomfort eliminating means 35 according to this embodiment utilizes the phenomenon that the indicated mean effective pressure decreases as the intake air amount decreases, and is constituted by the throttle valve control unit 71 and the second throttle valve 70. ing.

Next, a method for operating the four-cylinder engine according to this embodiment will be described. The control device 22 according to this embodiment operates as shown in the flowchart of FIG. That is, after the engine is started in step S1 of the flowchart shown in FIG. 13, the control device 22 determines in step S2 whether the engine speed is lower than a predetermined value and whether the load is in a predetermined region. To do. The predetermined value or the predetermined region here is a value or a region in which an occupant easily feels a torque fluctuation of the engine, that is, a value or a region where control for reducing the intake air amount is necessary. Specifically, in step S <b> 2, first, the control device 22 reads a map (FIG. 12) corresponding to the current gear position number from the storage unit 53. Then, the control device 22 applies the current engine speed and the engine load to this map, and reads the opening degree for reducing the opening degree of the second throttle valve 70 from this map.

If the engine speed and load are in the region indicated by D in the map shown in FIG. 12, the process proceeds from step S2 to step P1, and the opening of the first throttle valve 66 and the opening of the second throttle valve 70 are opened. Both throttle valves 66 and 70 are driven so that the degrees coincide.
On the other hand, when the engine speed and the load are in the region indicated by reference signs A to C in the map shown in FIG. 12, the process proceeds from step S2 to step P2, and the opening of the second throttle valve 70 is reduced. At this time, the opening degree of the second throttle valve 70 is α, β, γ degree from the opening degree (A, B, C, D degree) of the first throttle valve 66 read from the map shown in FIG. It is set to the opening degree (A-alpha degree, B-beta degree, C-gamma degree) made small only. The control device 22 repeatedly performs the above control while the engine is in operation, and controls the opening degree of the first throttle valve 66 and the second throttle valve 70.

In the operation method of the four- cylinder engine 1 and the four- cylinder engine according to this embodiment, the engine speed is lower than a predetermined value, the load is in a predetermined region, and the occupant can easily feel the engine torque fluctuation. In some cases, the intake air amount of the two cylinders (the second cylinder and the fourth cylinder) whose explosion interval is 90 degrees in the crank angle decreases, and the indicated mean effective pressure is higher than the indicated mean effective pressure of the other two cylinders. Reduced. For this reason, even when this embodiment is adopted, the same effect as that obtained when the first embodiment is adopted can be obtained.

In this embodiment, the second intake device 62 connected to the second cylinder and the fourth cylinder with an explosion interval of 90 degrees has one surge tank (first engine) connected to the intake port 9 of both cylinders. 2 surge tanks 67) and one throttle valve (second throttle valve 70) provided in the surge tank. The discomfort eliminating means 35 according to this embodiment controls the opening degree of the second throttle valve 70 so that the intake air amount of the two cylinders with an explosion interval of 90 degrees can be reduced. This is less than the intake air amount of the cylinder. In this embodiment, the indicated mean effective pressure of the second and fourth cylinders is such that the intake air amount is smaller than that of the other first and third cylinders whose explosion intervals are not 90 degrees. The throttle valve 70 can be lowered by controlling the opening of the throttle valve 70.

For this reason, the intake air amount of the second cylinder and the fourth cylinder at which the explosion interval is 90 degrees is controlled by one throttle valve (second throttle valve 70). That is, the size of the indicated mean effective pressure of the second cylinder, and is approximately equal magnitude of the indicated mean effective pressure of the fourth cylinder. Moreover, the indicated mean effective pressures of these cylinders are smaller than the indicated mean effective pressures of the first and third cylinders.
Therefore, the indicated mean effective pressures of the second cylinder and the fourth cylinder, which have an explosion interval of 90 degrees, can be controlled evenly. Therefore, there is a variation in the magnitude of the torque that increases due to the explosion occurring in these two cylinders. No longer occurs. As a result, according to this embodiment, it is possible to provide a four-cylinder engine and a method for operating the four- cylinder engine that can easily control the indicated mean effective pressure.

(Modification according to the second embodiment)
The first air intake device 61 when the air from one surge tank and 2 and fourth cylinders (second surge tank 67) employs a configuration that is supplied, Fig. 14 (Modification 1) and 15 It can be configured as shown in (Modification 2). 14 and 15, members identical or equivalent to those described with reference to FIGS. 1 to 13 are given the same reference numerals, and detailed descriptions thereof are omitted as appropriate.

  A first intake device 61 shown in FIG. 14 is the first modification and includes a first cylinder throttle valve 73 and a third cylinder throttle valve 74. These throttle valves 73 and 74 may be of an electric type or those connected to the accelerator operator 72 via an operation wire (not shown). The first cylinder throttle valve 73 is connected to the intake port 9 of the first cylinder via an intake pipe 75. The third cylinder throttle valve 74 is connected to the intake port 9 of the third cylinder via an intake pipe 76. The first cylinder throttle valve 73 and the third cylinder throttle valve 74 are interlocked so as to have the same opening degree. Further, the opening degree of the first cylinder throttle valve 73 and the opening degree of the third cylinder throttle valve 74 increase or decrease in proportion to the operation amount of the accelerator operation element 72.

A first intake device 61 shown in FIG. 15 is the second modification, and includes a first variable valve mechanism 77 provided in the first cylinder and a second variable operation provided in the third cylinder. And a valve mechanism 78. The first variable valve mechanism 77 and the second variable valve mechanism 78 can continuously change the opening / closing timing and the lift amount of the intake valve 11. That is, the intake air amount of the first cylinder is controlled by the first variable valve mechanism 77 changing the opening degree of the intake valve 11 of the first cylinder. The intake air amount of the third cylinder is controlled by the second variable valve mechanism 78 changing the opening degree of the intake valve 11 of the third cylinder.
Even if the first intake device 61 is configured as shown in FIGS. 14 and 15, the same effect as that obtained when the second embodiment is adopted can be obtained.

Oite to the second embodiment, conditions for firing interval reduces from the indicated mean effective pressure of two cylinders two cylinders indicated mean effective pressure of the other of the 90 degrees, the rotational speed of the engine is in a predetermined smaller than the value, the load is to have a predetermined area. However, the present invention can add the vehicle speed to one of the conditions without being limited to such a limitation. In this case, the vehicle speed, as also described in paragraph 0034 of this specification, be determined by calculation from the speed step number detected by the gear position sensor 46 and the rotational speed of the engine detected by the crank angle sensor 45 it can. In this case, the vehicle speed can be obtained by connecting a vehicle speed sensor 79 to the control device 22 as shown in FIG.

(Third embodiment)
In order to reduce the indicated mean effective pressure of the two cylinders having an explosion interval of 90 degrees, as shown in FIGS. 16 to 19, it can be carried out using an intake device. 16 to 19, members identical or equivalent to those described with reference to FIGS. 1 to 15 are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate.
The four-cylinder engine 1 shown in FIG. 16 is different from the four-cylinder engine in the first embodiment shown in FIGS. 1 to 9 in the configuration of the ignition system and the intake device 16, and the other configurations are the same. is there. The ignition system of the four-cylinder engine 1 according to this embodiment is configured so that the ignition timing is optimal in all cylinders. In this embodiment, the retardation control as shown in the first embodiment is not performed.

  The intake device 16 of the four-cylinder engine 1 shown in FIG. 16 includes a first intake device 81 for the first cylinder, a second intake device 82 for the second cylinder, and a third intake device for the third cylinder. 83 and a fourth intake device 84 for the fourth cylinder. These first to fourth intake devices 81 to 84 include electric throttle valves 86 to 89 connected to the intake ports 9 of the respective cylinders via an intake pipe 85. An air amount measuring device 21 is provided for each throttle valve on the upstream side of the intake air from these throttle valves 86 to 89.

The operations of these throttle valves 86 to 89 are controlled by a throttle valve control unit 91 of the control device 22 shown in FIG.
The throttle valve control unit 91 controls the opening degree of the four throttle valves 86 to 89 based on the operation amount of the accelerator operation element 72 operated by the occupant. The opening degrees of the first cylinder throttle valve 86 and the third cylinder throttle valve 88 increase or decrease in proportion to the operation amount of the accelerator operation element 72.

The opening degrees of the second cylinder throttle valve 87 and the fourth cylinder throttle valve 89 are such that the first cylinder throttle valve 86 and the third cylinder throttle valve 88 are in an operating state in which the occupant can easily feel engine torque fluctuations. The opening is set to be smaller than the opening, and is matched with the opening of the first cylinder throttle valve 86 and the third cylinder throttle valve 88 in other operating states .
The throttle valve control unit 91 according to this embodiment sets the opening degrees of the second cylinder throttle valve 87 and the fourth cylinder throttle valve 89 using the map shown in FIG.

  The map shown in FIG. 18 shows the opening degree of the second cylinder throttle valve 87 and the fourth cylinder throttle valve 89 as the opening degree of the first cylinder throttle valve 86 and the third cylinder throttle valve 88 (A degree, B degree). , C degrees, D degrees), the opening degree (A-α degrees, B-β degrees, C-γ degrees) to be reduced by α, β, γ degrees is assigned to the engine speed and load. is there. This map is provided for each shift stage number of the transmission 42 and is stored in the storage unit 53 of the control device 22.

  When the opening degree of the second cylinder throttle valve 87 and the fourth cylinder throttle valve 89 decreases, the intake air amount decreases in the second cylinder and the fourth cylinder, and the indicated mean effective pressure at the time of combustion of these cylinders becomes smaller. descend. The discomfort eliminating means 35 according to this embodiment utilizes the phenomenon that the indicated mean effective pressure decreases as the intake air amount decreases. The throttle valve control unit 91 and the second cylinder throttle valves 87 and 4 are used. And a cylinder throttle valve 89.

Next, a method for operating the four-cylinder engine according to this embodiment will be described. The control device 22 according to this embodiment operates as shown in the flowchart of FIG. That is, after the engine is started in step S1 of the flowchart shown in FIG. 19, the control device 22 determines in step S2 whether the engine speed is lower than a predetermined value and whether the load is in a predetermined region. To do. The predetermined value or the predetermined region here is a value or a region in which an occupant easily feels a torque fluctuation of the engine, that is, a value or a region where control for reducing the intake air amount is necessary. Specifically, in step S <b> 2, first, the control device 22 reads a map (FIG. 18) corresponding to the current gear position number from the storage unit 53. Then, the controller 22 assigns the current engine speed and engine load to this map, and opens the opening of the throttle valve 87 for the second cylinder and the throttle valve 89 for the fourth cylinder from this map. Read the degree.

When the engine speed and the load are in the region indicated by the symbol D in the map shown in FIG. 18, the process proceeds from step S2 to step Q1, and all throttle valves 86 to 89 have the same opening degree. Valves 86-89 are driven.
On the other hand, when the engine speed and the load are in the region indicated by reference signs A to C in the map shown in FIG. 18, the process proceeds from step S2 to step Q2, and the second cylinder throttle valve 87 and the fourth cylinder throttle valve. The opening degree of 89 is made small. At this time, the opening degrees of the second cylinder throttle valve 87 and the fourth cylinder throttle valve 89 are determined by the opening of the first cylinder throttle valve 86 and the third cylinder throttle valve 88 read from the map shown in FIG. The degree of opening (A-α degree, B-β degree, C-γ degree) is set smaller than the degree (A degree, B degree, C degree, D degree) by α, β, γ degrees. The control device 22 repeatedly performs the above control while the engine is being operated to control the opening degree of all the throttle valves 86-89.

In the operation method of the four- cylinder engine 1 and the four- cylinder engine according to this embodiment, the engine speed is lower than a predetermined value, the load is in a predetermined region, and the occupant can easily feel the engine torque fluctuation. At a certain time, the intake air amount of the two cylinders (the second cylinder and the fourth cylinder) whose explosion interval is 90 degrees in crank angle decreases. As a result, the indicated mean effective pressure of the two cylinders whose explosion interval is 90 degrees in crank angle is lower than the indicated mean effective pressure of the other two cylinders. For this reason, even when this embodiment is adopted, the same effect as that obtained when the first embodiment is adopted can be obtained.

In this embodiment, the second intake device 82 and the fourth intake device 84 connected to the second and fourth cylinders having an explosion interval of 90 degrees include throttle valves 87 and 89 for each cylinder. ing. The discomfort canceling means 35 according to this embodiment controls the opening degree of the throttle valves 87 and 89, so that the intake air amount of the two cylinders with an explosion interval of 90 degrees can be reduced to other than the explosion interval of 90 degrees. This is less than the intake air amount of the cylinder. The illustrated mean effective pressures of the second cylinder and the fourth cylinder according to this embodiment are such that the intake air amount is smaller than that of the other first and third cylinders whose explosion intervals are not 90 degrees. It is lowered by controlling the opening degree of the cylinder throttle valve 87 and the fourth cylinder throttle valve 89.

According to this embodiment, when the occupant is in an operating state where it is easy to feel engine torque fluctuations, the intake air amounts of the second and fourth cylinders are reduced by the throttle valves 87 and 89 for each cylinder. For this reason, according to the operation method of the four- cylinder engine 1 and the four-cylinder engine according to this embodiment, the illustrated mean effective pressure is reduced with good responsiveness in the second cylinder and the fourth cylinder. It becomes difficult to remember.

The opening degree of the second cylinder throttle valve 87 and the opening degree of the fourth cylinder throttle valve 89 according to this embodiment are the same. However, the present invention is not limited to such a limitation. That is, the opening degree of the opening and the fourth cylinder throttle valve 89 of the second cylinder throttle valve 87 may be a different opening from each other. Of the second cylinder throttle valve 87 and the fourth cylinder throttle valve 89, the opening of one throttle valve matches the opening of the first cylinder throttle valve 86 or the third cylinder throttle valve 88. A configuration in which the opening of the other throttle valve is lower than the opening of the first cylinder throttle valve 86 or the third cylinder throttle valve 88 can be adopted.
That is, when the present invention is applied to the four-cylinder engine 1 having the second cylinder throttle valve 87 and the fourth cylinder throttle valve 89, the discomfort eliminating means 35 controls the opening degree of these throttle valves 87 and 89. By doing so, the intake air amount of at least one of the two cylinders (the second cylinder and the fourth cylinder) having the explosion interval of 90 degrees is set to the other cylinder (the first cylinder and the cylinder having the explosion interval of 90 degrees). This is less than the intake air amount of the third cylinder).

In order to individually control the opening degree of the throttle valves 87 and 89 in this way, for example, a map indicating the opening degree of the second cylinder throttle valve 87 and a fourth cylinder throttle valve formed separately from this map are used. It is conceivable to use a map indicating the opening degree of 89.
By adopting such a configuration, it is possible to individually control the magnitude of the torque generated when an explosion occurs in the second cylinder and the magnitude of the torque generated when an explosion occurs in the fourth cylinder. For this reason, by adopting this configuration, it becomes possible to easily achieve uniform driving energy of the engine.

(Modification according to the third embodiment)
Intake devices connected to the first cylinder and the third cylinder in the case of adopting a configuration in which air is supplied from the throttle valve for each cylinder to the second cylinder and the fourth cylinder are shown in FIG. 20 (modified example 1) and FIG. It can be configured as shown in Modification 2). 20 and 21, the same or equivalent members as those described with reference to FIGS. 1 to 19 are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate.

FIG. 20 is a diagram showing a first modification . The intake port 9 of the first cylinder and the intake port 9 of the third cylinder shown in FIG. 20 are connected to one surge tank 93 via an intake pipe 92, respectively. At one end of the surge tank 93, an electric or wire operated throttle valve 94 is provided. The opening degree of the throttle valve 94 is controlled so as to be proportional to the operation amount of the accelerator operation element 72 as in the embodiment shown in FIG.

FIG. 21 is a diagram showing a second modification . The first intake device 81 for the first cylinder shown in FIG. 21 includes a first variable valve mechanism 95 provided in the first cylinder. The third intake device 83 for the third cylinder includes a second variable valve mechanism 96 provided in the third cylinder. The first variable valve mechanism 95 and the second variable valve mechanism 96 can continuously change the opening / closing timing and the lift amount of the intake valve 11. That is, the intake air amount of the first cylinder is controlled by the first variable valve mechanism 95 changing the opening degree of the intake valve 11 of the first cylinder. The intake air amount of the third cylinder is controlled by the second variable valve mechanism 96 changing the opening degree of the intake valve 11 of the third cylinder.
Even if the first and third intake devices 81 and 83 connected to the first cylinder and the third cylinder are configured as shown in FIGS. 20 and 21, the same effect as when the second embodiment is adopted. Is obtained.

Oite to the third embodiment, the condition for firing interval reduces from the indicated mean effective pressure of two cylinders two cylinders indicated mean effective pressure of the other of the 90 degrees, the rotational speed of the engine is in a predetermined smaller than the value, the load is to have a predetermined area. However, the present invention can add the vehicle speed to one of the conditions without being limited to such a limitation. In this case , as described in paragraph 0034 , the vehicle speed can be obtained by calculation from the engine speed detected by the crank angle detection sensor 45 and the number of shift stages detected by the shift position sensor 46 . In this case, the vehicle speed can be obtained by connecting a vehicle speed sensor 97 to the control device 22 and using the vehicle speed sensor 97 as shown in FIG.

(Fourth embodiment)
In order to reduce the indicated mean effective pressure of the two cylinders having an explosion interval of 90 degrees, as shown in FIGS. 22 to 25, an intake device can be used. 22 to 25, members identical or equivalent to those described with reference to FIGS. 1 to 21 are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate.
The four-cylinder engine 1 shown in the drawing is different from the four-cylinder engine in the first embodiment in the configuration of the ignition system and the intake device 16, and the other configurations are the same. The ignition system of the four-cylinder engine 1 according to this embodiment is configured so that the ignition timing is optimal in all cylinders. In this embodiment, the retardation control as shown in the first embodiment is not performed.

  The intake device 16 of the four-cylinder engine 1 shown in FIG. 22 includes variable valve mechanisms 101 to 104 for each cylinder, and one surge tank 106 connected to the intake port of each cylinder by an intake pipe 105. The variable valve mechanisms 101 to 104 are capable of continuously changing the opening / closing timing and the lift amount of the intake valve 11. That is, the intake air amount of each cylinder is controlled by changing the opening degree of the intake valve 11 of each cylinder by the variable valve mechanism for each cylinder. An air amount measuring device 21 is provided in each intake pipe 105 of each cylinder.

  At one end of the surge tank 106, a throttle valve 107 for controlling the intake air amount of each cylinder in cooperation with the variable valve mechanisms 101 to 104 is provided. The throttle valve 107 is of an electric type or a wire operation type. The opening degree of the throttle valve 107 is controlled so as to be proportional to the operation amount of the accelerator operation element 72 as in the embodiment shown in FIG. The surge tank 106 according to this embodiment can be connected to an air cleaner (not shown) without passing through the throttle valve 107.

The operations of the four variable valve mechanisms 101 to 104 are controlled by the intake air amount control unit 108 of the control device 22 shown in FIG.
The intake air amount control unit 108 controls the operations of the four variable valve mechanisms 101 to 104 based on the operation amount of the accelerator operation element 72 operated by the occupant. The opening / closing timing and lift amount of the first cylinder intake valve 11 changed by the variable valve mechanism 101 of the first cylinder, and the opening / closing timing of the third cylinder intake valve 11 changed by the variable valve mechanism 103 of the third cylinder The lift amount is increased or decreased so as to be proportional to the operation amount of the accelerator operation element 72. Hereinafter, the opening / closing timing and the lift amount of the intake valve 11 are simply referred to as “opening degree”.

The opening degree of the intake valve 11 for the second cylinder 11 and the intake valve 11 for the fourth cylinder is determined by the intake valve 11 for the first cylinder 11 and the intake valve 11 for the third cylinder when the occupant is in an operating state where it is easy for the passenger to feel torque fluctuations. The opening is set smaller than the opening, and is matched with the opening of the first cylinder intake valve 11 and the third cylinder intake valve 11 in other operating states .
The intake air amount control unit 108 according to this embodiment sets the opening degrees of the second cylinder intake valve 11 and the fourth cylinder intake valve 11 using the map shown in FIG.

  The map shown in FIG. 24 shows the opening degree of the intake valve 11 for the second cylinder and the intake valve 11 for the fourth cylinder as the opening degree of the intake valve 11 for the first cylinder 11 and the intake valve 11 for the third cylinder (A degree, B degree). , C degrees, D degrees), the opening degree (A-α degrees, B-β degrees, C-γ degrees) to be reduced by α, β, γ degrees is assigned to the engine speed and load. is there. This map is provided for each shift stage number of the transmission 42 and is stored in the storage unit 53 of the control device 22.

  When the opening degree of the intake valve 11 for the second cylinder 11 and the intake valve 11 for the fourth cylinder becomes smaller, the intake air amount decreases in the second cylinder and the fourth cylinder, and the indicated mean effective pressure at the time of combustion of these cylinders becomes smaller. descend. The discomfort eliminating means 35 according to this embodiment utilizes a phenomenon in which the illustrated mean effective pressure decreases as the intake air amount decreases, and the intake air amount control unit 108 and the variable valve mechanism of the second cylinder. 102 and a variable valve mechanism 104 of the fourth cylinder.

Next, a method for operating the four-cylinder engine according to this embodiment will be described. The control device 22 according to this embodiment operates as shown in the flowchart of FIG. That is, after the engine is started in step S1 of the flowchart shown in FIG. 25, the control device 22 determines in step S2 whether the engine speed is lower than a predetermined value and whether the load is in a predetermined region. To do. The predetermined value or the predetermined region here is a value or a region in which an occupant easily feels a torque fluctuation of the engine, that is, a value or a region where control for reducing the intake air amount is necessary.

Specifically, in step S <b> 2, first, the control device 22 reads a map (FIG. 24) corresponding to the current gear position number from the storage unit 53. Then, the control device 22 assigns the current engine speed and engine load to this map, and opens the opening of the second cylinder intake valve 11 and the fourth cylinder intake valve 11 from this map. Read the degree.
When the engine rotational speed and the load are in the region indicated by D in the map shown in FIG. 24, the routine proceeds from step S2 to step R1, and all the variable valve actuations are performed so that the openings of all the intake valves 11 match. Mechanisms 101-104 are driven.

  On the other hand, if the engine speed and load are in the region indicated by reference signs A to C in the map shown in FIG. 24, the process proceeds from step S2 to step R2, and the second cylinder intake valve 11 and the fourth cylinder intake valve. The opening degree of 11 is made small. At this time, the opening degree of the intake valve 11 for the second cylinder and the intake valve 11 for the fourth cylinder is determined by the opening of the intake valve 11 for the first cylinder 11 and the intake valve 11 for the third cylinder read from the map shown in FIG. The degree of opening (A-α degree, B-β degree, C-γ degree) is set smaller by α, β, γ degrees than the degree (A degree, B degree, C degree, D degree). The control device 22 repeatedly performs the above control while the engine is in operation, and controls the operations of all the variable valve mechanisms 101 to 104.

In the four-cylinder engine 1 and the four-cylinder engine operation method according to this embodiment, the engine speed is smaller than a predetermined value, the load is in a predetermined region, and the occupant can easily feel the engine torque fluctuation. In some cases, the intake air amount of the two cylinders (the second cylinder and the fourth cylinder) whose explosion interval is 90 degrees in the crank angle decreases, and the indicated mean effective pressure is higher than the indicated mean effective pressure of the other two cylinders. Reduced. For this reason, even when this embodiment is adopted, the same effect as that obtained when the first embodiment is adopted can be obtained.

In this embodiment, the intake device 16 connected to the second and fourth cylinders having an explosion interval of 90 degrees includes variable valve mechanisms 102 and 104 that can control the opening degree of the intake valve 11. Yes. The discomfort canceling means 35 according to this embodiment controls the operation of the variable valve mechanisms 102 and 104 to reduce the intake air amount of two cylinders having an explosion interval of 90 degrees, and the explosion interval is not 90 degrees. This is less than the intake air amount of the cylinder. The illustrated mean effective pressures of the second cylinder and the fourth cylinder according to this embodiment are such that the intake air amount is smaller than that of the other first and third cylinders whose explosion intervals are not 90 degrees. It is lowered by controlling the opening degree of the cylinder intake valve 11 and the fourth cylinder intake valve 11.

According to this embodiment, when the occupant is in an operating state where it is easy to feel engine torque fluctuations, the intake air amounts of the second and fourth cylinders are reduced by the variable valve mechanisms 102 and 104 for each cylinder. For this reason, according to the operation method of the four- cylinder engine 1 and the four-cylinder engine according to this embodiment, the illustrated mean effective pressure is reduced with good responsiveness in the second cylinder and the fourth cylinder. It's hard to remember.

The opening degree of the intake valve 11 for the second cylinder according to this embodiment and the opening degree of the intake valve 11 for the fourth cylinder are the same. However, the present invention is not limited to such a limitation. That is, the opening degree of the intake valve 11 for the second cylinder and the opening degree of the intake valve 11 for the fourth cylinder can be different from each other. In addition, the opening degree of one of the intake valves 11 for the second cylinder and the intake valve 11 for the fourth cylinder coincides with the opening degree of the intake valve 11 for the first cylinder or the intake valve 11 for the third cylinder. The opening of the other intake valve 11 may be lower than the opening of the first cylinder intake valve 11 or the third cylinder intake valve 11 .
That is, when the present invention is applied to the four-cylinder engine 1 having the variable valve mechanism 102 for the second cylinder and the variable valve mechanism 104 for the fourth cylinder, the discomfort eliminating means 35 is the variable valve mechanism. By controlling the operation of the cylinders 102 and 104, the intake air amount of at least one of the two cylinders (the second cylinder and the fourth cylinder) having an explosion interval of 90 degrees is set so that the explosion interval is not 90 degrees. Less than the intake air amount of the first cylinder and the third cylinder.

In order to individually control the opening degree of the intake valve 11 as described above, for example, a map showing the opening degree of the second cylinder intake valve 11 and a fourth cylinder intake valve 11 formed separately from this map are used. It is conceivable to use a map indicating the opening.
By adopting such a configuration, it is possible to individually control the magnitude of the torque generated when an explosion occurs in the second cylinder and the magnitude of the torque generated when an explosion occurs in the fourth cylinder. For this reason, by adopting this configuration, it becomes possible to easily achieve uniform driving energy of the engine.

(Modification according to the fourth embodiment)
FIG. 26 (Modification 1) and FIG. 27 (Modification 2) show the intake devices connected to the 1st and 3rd cylinders when the 2nd and 4th cylinders have variable valve mechanisms respectively. Can be configured. 26 and 27, the same or equivalent members as those described with reference to FIGS. 1 to 25 are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate.

  FIG. 26 is a diagram showing Modification Example 1. The intake port 9 of the first cylinder and the intake port 9 of the third cylinder shown in FIG. 26 are connected to one surge tank 112 via an intake pipe 111, respectively. . At one end of the surge tank 112, an electric or wire operated throttle valve 113 is provided. The opening degree of the throttle valve 113 is controlled so as to be proportional to the operation amount of the accelerator operator 72 as in the embodiment shown in FIG.

FIG. 27 is a diagram showing a modification 2. A first cylinder throttle valve 115 is connected to an intake port 9 of the first cylinder shown in FIG. A third cylinder throttle valve 117 is connected to an intake port 9 of the third cylinder via an intake pipe 116. These throttle valves 115 and 117 can be electrically operated or can be connected to the accelerator operator 72 via an operation wire (not shown). The first cylinder throttle valve 115 and the third cylinder throttle valve 117 are interlocked so as to have the same opening degree. Further, the opening degree of the first cylinder throttle valve 115 and the opening degree of the third cylinder throttle valve 117 increase or decrease in proportion to the operation amount of the accelerator operation element 72.
Even if the intake device connected to the first and third cylinders is configured as shown in FIGS. 26 and 27, the same effect as that obtained when the fourth embodiment is adopted can be obtained.

  In each of the above-described embodiments, an example has been shown in which the discomfort eliminating means 35 uses a map to reduce the indicated mean effective pressure of the second cylinder and the fourth cylinder. However, the present invention is not limited to such a limitation. That is, the operation amount of an actuator (ignition device 27, throttle valve, variable valve mechanism, etc.) that lowers the indicated mean effective pressure of the second cylinder and the fourth cylinder can be obtained only by calculation.

  Further, in each of the above-described embodiments, the four-cylinder engine 1 in which the two cylinders having the explosion interval of 90 degrees in the crank angle are the second cylinder and the fourth cylinder is shown. However, when the positions of the crank pins 31 to 34 are different from the crankshaft 8 shown in FIG. 3, the two cylinders having the explosion interval of 90 degrees are not necessarily the second and fourth cylinders. For this reason, in carrying out the present invention, an operation state in which an occupant can easily feel engine torque fluctuations in two cylinders with an explosion interval of 90 degrees without depending on the positions of the crank pins 31 to 34, without depending on the positions of the crank pins 31 to 34. At this time, the indicated mean effective pressure is reduced.

  Further, in the four-cylinder engine 1 shown in each of the above-described embodiments, all the cylinders are arranged in a line in the axial direction of the crankshaft 8. However, the present invention is not limited to such a limitation. That is, the present invention can be applied to a V-type four-cylinder engine. In a V-type four-cylinder engine with an explosion interval of 270 ° -180 ° -90 ° -180 ° in crank angle, the angle formed by the cylinder axis of one cylinder row and the cylinder axis of the other cylinder row is the crankshaft It is 90 degrees when viewed from the axial direction. The crankshaft used for the 90 degree V-type engine is of the 1 plane type.

Oite to the fourth embodiment, the condition for firing interval reduces from the indicated mean effective pressure of two cylinders two cylinders indicated mean effective pressure of the other of the 90 degrees, the rotational speed of the engine is in a predetermined smaller than the value, the load is to have a predetermined area. However, the present invention can add the vehicle speed to one of the conditions without being limited to such a limitation. In this case , as described in paragraph 0034 , the vehicle speed can be obtained by calculation from the engine speed detected by the crank angle detection sensor 45 and the number of shift stages detected by the shift position sensor 46 . In this case, the vehicle speed can be obtained by connecting a vehicle speed sensor 118 to the control device 22 and using the vehicle speed sensor 118 as shown in FIG.

  DESCRIPTION OF SYMBOLS 1 ... 4 cylinder engine, 2 ... Cylinder hole, 3 ... Cylinder body, 4 ... Cylinder head, 6 ... Piston, 7 ... Connecting rod, 8 ... Crankshaft, 9 ... Intake port, 10 ... Exhaust port, 14 ... Spark plug, 16 ... Intake device, 18, 63, 67, 93, 106, 112 ... Surge tank, 19, 66, 70, 73, 74, 86-89, 94, 107, 113, 115, 117 ... Throttle valve, 22 ... Control device , 23 ... exhaust device, 27 ... ignition device, 52 ... ignition timing control unit, 71, 91 ... throttle valve control unit, 77, 78, 95, 96, 101-104 ... variable valve mechanism, 108 ... intake air amount control Department.

Claims (12)

A cylinder body having four cylinder holes;
Wherein mounted on Shirindabode I, a cylinder head having an intake port and an exhaust port for each of the cylinder bore,
A spark plug of the cylinder bore each mounted to the cylinder head,
An ignition device including the spark plug;
An intake device connected to the intake port;
An exhaust device connected to the exhaust port;
Four pistons slidably fitted in the cylinder holes;
A crankshaft connected to these pistons via connecting rods,
The explosion interval of the four cylinders constituted by the four cylinder holes is 270 degrees-180 degrees-90 degrees-180 degrees in crank angle,
When the rotational speed of the engine is lower than a predetermined value, the indicated mean effective pressure of at least one of the two cylinders whose explosion interval is 90 degrees is the indicated mean effective pressure of the other cylinders whose explosion interval is not 90 degrees. further comprising and has a four-cylinder engine make lower discomfort canceller than the effective pressure. 2. The four-cylinder engine according to claim 1, wherein the amount by which the indicated mean effective pressure is reduced increases as the engine speed decreases and the load increases. 3. The four-cylinder engine according to claim 1 or 2, wherein the uncomfortable feeling canceling portion utilizes a phenomenon in which the indicated mean effective pressure decreases due to an ignition timing being delayed, and the explosion interval is 90 degrees. A four-cylinder engine characterized in that the ignition timing of at least one of the cylinders is delayed from the ignition timing of other cylinders whose explosion interval is not 90 degrees. The four-cylinder engine according to claim 1 or 2, wherein the intake device connected to the two cylinders having an explosion interval of 90 degrees includes one surge tank connected to the intake ports of both the cylinders, With one throttle valve provided in this surge tank,
The uncomfortable feeling canceling part utilizes the phenomenon that the indicated mean effective pressure decreases as the amount of intake air decreases, and the explosion interval becomes 90 degrees by controlling the opening of the throttle valve. 4-cylinder engine, characterized in that one of the intake air amount of the cylinder, explosion spacing is to less than the intake air amount of the other cylinders not 90 degrees. The four-cylinder engine according to claim 1 or 2, wherein the intake device connected to two cylinders having an explosion interval of 90 degrees includes a throttle valve for each cylinder,
The uncomfortable feeling canceling part utilizes the phenomenon that the indicated mean effective pressure decreases as the amount of intake air decreases, and the explosion interval becomes 90 degrees by controlling the opening of the throttle valve. A four-cylinder engine characterized in that an intake air amount of at least one of the cylinders is made smaller than an intake air amount of another cylinder whose explosion interval is not 90 degrees. The four-cylinder engine according to claim 1 or 2, wherein the intake device connected to two cylinders having an explosion interval of 90 degrees changes an opening / closing timing and a lift amount of an intake valve that opens and closes the intake port. Equipped with a variable valve mechanism
The uncomfortable feeling canceling unit utilizes a phenomenon in which the indicated mean effective pressure decreases as the amount of intake air decreases, and the explosion interval becomes 90 degrees by controlling the operation of the variable valve mechanism. A four-cylinder engine characterized in that an intake air amount of at least one of the two cylinders is made smaller than an intake air amount of another cylinder whose explosion interval is not 90 degrees. A cylinder body having four cylinder holes;
A cylinder head attached to the cylinder body and having an intake port and an exhaust port for each cylinder hole;
A spark plug for each cylinder hole attached to the cylinder head;
An ignition device including the spark plug;
An intake device connected to the intake port;
An exhaust device connected to the exhaust port;
Four pistons slidably fitted in the cylinder holes;
The explosion interval of a four-cylinder engine having a crankshaft connected to these pistons via connecting rods is 270 degrees -180 degrees -90 degrees -180 degrees in crank angle,
When the rotational speed of the engine is lower than a predetermined value, the indicated mean effective pressure of at least one of the two cylinders whose explosion interval is 90 degrees is the indicated mean effective pressure of the other cylinders whose explosion interval is not 90 degrees. A method for operating a four-cylinder engine, wherein the operating pressure is lower than an effective pressure. 8. The four-cylinder engine operating method according to claim 7, wherein the amount by which the indicated mean effective pressure is reduced increases as the engine speed decreases and the load increases. How to run the engine. 9. The method of operating a four-cylinder engine according to claim 7 or claim 8, wherein the ignition timing of at least one of the two cylinders having the explosion interval of 90 degrees is set to that of another cylinder whose explosion interval is not 90 degrees. A method of operating a four-cylinder engine, characterized in that the indicated mean effective pressure of at least one of two cylinders having an explosion interval of 90 degrees is reduced by delaying from an ignition timing. 9. The method of operating a four-cylinder engine according to claim 7 or claim 8, wherein the intake device connected to the two cylinders having an explosion interval of 90 degrees includes one surge connected to the intake ports of the two cylinders. A tank and one throttle valve provided in the surge tank;
By controlling the opening degree of the throttle valve and reducing the intake air amount of two cylinders having an explosion interval of 90 degrees to the intake air amount of other cylinders having an explosion interval not 90 degrees, the explosion interval is reduced. A method of operating a four-cylinder engine, wherein the indicated mean effective pressure of two cylinders at 90 degrees is reduced. The operation method of a four-cylinder engine according to claim 7 or claim 8, wherein the intake device connected to two cylinders having an explosion interval of 90 degrees includes a throttle valve for each cylinder,
  By controlling the opening degree of the throttle valve, the intake air amount of at least one of the two cylinders having the explosion interval of 90 degrees is made smaller than the intake air amount of the other cylinders having the explosion interval not 90 degrees. Thus, the indicated effective effective pressure of at least one of the two cylinders having the explosion interval of 90 degrees is reduced. 9. The method of operating a four-cylinder engine according to claim 7 or claim 8, wherein the intake device connected to the two cylinders having an explosion interval of 90 degrees includes an opening / closing timing and lift of an intake valve that opens and closes the intake port. Equipped with a variable valve mechanism that can change the amount,
The operation of the variable valve mechanism is controlled, and the intake air amount of at least one of the two cylinders with the explosion interval of 90 degrees is smaller than the intake air amount of the other cylinders with the explosion interval not 90 degrees. By doing so, the indicated mean effective pressure of at least one of the two cylinders having the explosion interval of 90 degrees is reduced.