JP4545698B2 - Premixed compression self-ignition engine - Google Patents

Description

  The present invention relates to a premixed compression self-ignition engine in which an air-fuel mixture in which fuel and air are premixed is compressed in a combustion chamber to be self-ignited and burned.

  A premixed compression self-ignition engine that self-ignites by supplying an air-fuel mixture premixed with air and fuel to a combustion chamber in a cylinder and compressing the air-fuel mixture is known, for example, from Patent Document 1.

  This premixed compression self-ignition engine has the advantage of high thermal efficiency because it can be operated at a higher compression ratio than a spark ignition engine. Moreover, since the combustion temperature can be lowered, the production of NOx can also be suppressed. However, since the air-fuel mixture is ignited naturally, it is difficult to control the ignition timing, and it is important to prepare conditions for appropriate ignition.

  In particular, when the engine is started, since the engine is not warmed and the intake air temperature is low, operation by compression auto-ignition is very difficult.

Therefore, in the technique of Patent Document 1, the cylinder head is provided with a spark plug, and at the start of the engine, warm-up is performed by performing an operation by spark ignition, and the intake air temperature is set to a temperature suitable for the compression auto-ignition operation. When it rises, it raises the compression ratio in the cylinder and raises the excess air ratio to perform compression self-ignition.
JP 2005-69097 A

  Japanese Patent Application Laid-Open No. 2004-228561 describes that when the operation is switched from the spark ignition operation to the compression self-ignition operation, the intake valve closing timing is advanced (advanced) in order to increase the compression ratio in the cylinder. However, there is no disclosure on how to advance the closing timing of the intake valve.

  On the other hand, a variable valve apparatus having a valve closing timing adjustment mechanism that can adjust the closing timing of the intake valve is also known in the past. However, if the valve closing timing adjustment mechanism is frequently used, there is a problem that failure tends to occur. is there. In addition, when the valve closing timing adjusting mechanism uses hydraulic pressure, there is a problem that if an operation is performed in which the hydraulic pressure is applied for a long time, a hydraulic pressure loss occurs and efficiency is deteriorated. Therefore, it is preferable to operate without using a variable valve device as much as possible.

  Therefore, the present invention adjusts the closing timing of the intake valve by using a valve closing timing adjustment mechanism that adjusts the closing timing of the intake valve during operation by spark ignition performed at a limited timing such as at the time of starting. When operating by compression ignition for a long period of time such as steady operation, the valve closing timing adjustment mechanism can be opened and closed by opening and closing the intake valve only with the valve operating mechanism without using the valve closing timing adjustment mechanism. An object of the present invention is to provide a premixed compression self-ignition engine which is shortened, efficient and excellent in durability.

The invention according to claim 1 is a premixed compression self-ignition engine that burns by self-igniting and combusting an air-fuel mixture premixed with fuel and air in a combustion chamber at least in steady operation. An intake valve that opens and closes an intake port that introduces air-fuel mixture into the chamber, a valve operating device that opens and closes the intake valve, a valve closing timing adjustment mechanism that adjusts the closing timing of the intake valve by the valve operating device, An ignition device that sparks and ignites an air-fuel mixture in the combustion chamber, and the valve operating device includes a valve spring that biases the intake valve in a closing direction, and a valve arm that is swingably supported by the cylinder head. A cam mechanism interlocking with the rotation of the crankshaft, and when the cam mechanism pushes out the valve arm, the intake valve moves in the opening direction. Chamber and the hydraulic chamber An operation member that moves to the valve arm side or the counter-valve arm side according to the amount, a hydraulic oil inlet passage that supplies hydraulic oil from an oil pump to the hydraulic chamber, and a solenoid type that opens and closes the hydraulic oil inlet passage A driving solenoid on-off valve, a hydraulic oil outlet passage for discharging hydraulic oil from the hydraulic chamber, a solenoid-type outlet electromagnetic on-off valve for opening and closing the hydraulic oil outlet passage, and an opening in the hydraulic chamber to open the hydraulic oil A fixed orifice and a variable orifice communicating with the outlet passage, wherein the opening position of the variable orifice is provided closer to the valve arm than the opening position of the fixed orifice, and the opening diameter of the variable orifice is The opening diameter of the fixed orifice is larger, and the operation member is brought into contact with the valve arm by the operation of the driving electromagnetic on-off valve and the outlet electromagnetic on-off valve to open the intake valve. Are those of the operating member is moved can be spaced apart from the valve arm, during engine starting, the intake valve by the valve closing timing adjusting mechanism while the intake valve is opened and closed by the valve mechanism The closing timing is adjusted to lower the effective compression ratio in the combustion chamber, and the ignition device is operated to perform a spark ignition operation. During steady operation, the valve closing timing adjustment mechanism is not operated, and the valve actuation is performed. The apparatus is configured to perform a compression auto-ignition operation by opening and closing the intake valve by means of a device to increase the effective compression ratio in the combustion chamber as compared to when the engine is started.

  According to a second aspect of the present invention, in the first aspect of the invention, the spark ignition operation at the time of engine start and the compression self-ignition operation at the time of steady operation are shifted according to the engine speed. Features.

  According to a third aspect of the present invention, in the first aspect of the present invention, the valve closing timing adjustment mechanism is configured to vary the closing timing of the intake valve in accordance with a variation in engine speed. And

  According to a fourth aspect of the present invention, in the first aspect of the present invention, the warm-up state at the time of starting the engine is determined by the temperature of the engine cooling water or the intake air temperature to the combustion chamber, and the valve according to the warm-up state. The closing timing of the intake valve is adjusted by a closing timing adjusting mechanism.

According to a fifth aspect, in the invention according to the first aspect, when starting the engine, characterized in that it is provided with a starter pump motor for supplying hydraulic pressure to said operating member.

  According to the first aspect of the present invention, in the spark ignition operation performed at a limited time such as when the engine is started, the intake valve is opened and closed by the valve operating device, and the valve closing timing adjusting mechanism is operated to close the intake valve. In compression self-ignition operation that is performed for a long time as a steady operation by adjusting the timing, the intake valve is opened and closed only by the valve operating device without operating the valve closing timing adjusting mechanism. Therefore, it is possible to shorten the usage time of the valve closing timing adjustment mechanism over the entire operation time of the engine, to prevent the deterioration of efficiency associated with the use of the valve closing timing adjustment mechanism, and to improve the durability of the valve closing timing adjustment mechanism. Can be improved.

  According to the invention of claim 2, it is possible to appropriately shift from the spark ignition operation to the compression self-ignition operation between the engine start and the steady operation.

  According to the invention of claim 3, since the effective compression ratio can be gradually changed according to the fluctuation of the engine speed, a stable operation can be maintained.

  According to the invention of claim 4, knocking or misfire is reliably prevented from the time of engine start by adjusting the intake valve close timing by the valve close timing adjustment mechanism in consideration of the warm-up state at the time of engine start. be able to.

  According to the fifth aspect of the present invention, an appropriate hydraulic pressure can be supplied to the operating member by the electric starting pump regardless of the engine speed from the time of starting the engine.

[Outline of premixed compression self-ignition engine]
FIG. 1 is a schematic sectional view of a premixed compression self-ignition engine according to an embodiment of the present invention, and FIG. 2 is a schematic plan view thereof. The premixed compression self-ignition engine 11 according to the present embodiment is a four-cylinder four-cycle engine, and includes an engine body 11 </ b> A that includes a cylinder block 12, a cylinder head 15, and a crankcase 18. Four cylinders (cylinders) 13 are provided in the cylinder block 12, and pistons 14 are slidably fitted in the cylinders 13. The cylinder head 15 is provided with an intake port 16 and an exhaust port 17, and the intake port 16 and the exhaust port 17 are opened and closed by an intake valve 19 and an exhaust valve 20, respectively. The intake valve 19 and the exhaust valve 20 are opened and closed by valve gears 21 and 22, respectively.

  An intake pipe 24 is connected to the intake port 16, and an exhaust pipe 26 having an exhaust manifold 25 is connected to the exhaust port 17. As shown in FIG. 2, the intake pipe 24 includes a main intake pipe 27, an intake surge tank 28 connected to the main intake pipe 27, and a plurality of branched intake pipes connected from the intake surge tank 28 to each cylinder 13. Tube 29.

  As shown in FIG. 1, the main intake pipe 27 is provided with a throttle valve 31, a mixer 33, and a heating device 35. The air introduced into the main intake pipe 27 is adjusted in flow rate by the throttle valve 31 and mixed with the fuel injected from the fuel control valve 32 by the mixer 33. The mixture of air and fuel is heated by the heating device 35 and flows into the intake surge tank 28, and is sucked into the combustion chambers in the cylinders 13 from the branch intake pipes 29 through the intake ports 16 (intake stroke). . The air-fuel mixture supplied in the combustion chamber in the intake stroke is compressed in the compression stroke, and is ignited when the piston 14 comes near the top dead center, thereby pushing down the piston 14 (expansion stroke). The combustion gas is discharged from the exhaust port 17 through the exhaust pipe 26 in the exhaust stroke.

  As shown in FIG. 1, the engine 11 includes a controller 45, and the controller 45 controls the throttle valve 31, the fuel control valve 32, the heating device 35, and the like. The engine 11 is provided with a cooling water temperature sensor 47, an intake air temperature sensor 48, an in-cylinder pressure sensor 49, an engine speed sensor 50, a torque sensor 51, and the like. To be input.

  As shown in FIG. 2, the heating device 35 heats the air-fuel mixture to an appropriate temperature in order to stably operate the engine 11, and is provided in one path 38 of the main intake pipe 27 branched into two paths. The heat exchanger 40 is provided. The heat exchanger 40 uses engine cooling water as a heat exchange medium, and the cooling water circulated through the engine main body 11A is supplied to the heat exchanger 40 via the flow path 41 and via the flow path 42. It is returned to the cooler (not shown). Metering valves 43 and 44 are provided in both paths 38 and 39 of the main intake pipe 27, respectively.

  The heat exchanger 40 is not provided in the other path 39 of the main intake pipe 27, and the air-fuel mixture passing through the path 39 is introduced as it is into the intake surge tank 28 without being heated. The metering valves 43 and 44 adjust (including stop) the inflow amount of the air-fuel mixture into the paths 38 and 39 of the main intake pipe 27. For example, only one of the metering valves 43 is opened. The air-fuel mixture can be heated rapidly by passing the air-fuel mixture only through 38, and only the other metering valve 44 is opened and the air-fuel mixture is passed through only the passage 39 so that the air-fuel mixture is not heated. (Relative cooling). Further, by opening both the metering valves 43 and 44, the heated air-fuel mixture and the unheated air-fuel mixture can be mixed to perform fine temperature control.

[Operation method of premixed compression self-ignition engine]
The premixed compression self-ignition engine 11 burns the air-fuel mixture by compression auto-ignition. In this embodiment, as shown in FIG. 1, an ignition plug (ignition device) 37 for spark-igniting the air-fuel mixture is provided. A cylinder head 15 is provided. The spark plug 37 is mainly used for facilitating ignition at the time of starting or the like when the periphery of the combustion chamber is not sufficiently warm.

  That is, the premixed compression self-ignition engine 11 of the present embodiment mainly performs compression self-ignition operation during steady operation, but can also be operated by spark ignition during start-up.

  Specifically, warm-up operation is performed by spark ignition during start-up, and when the engine speed increases, the compression ratio and the excess air ratio are adjusted accordingly to cause compression autoignition. Then, it is detected by a sensor or the like that the torque has risen to a predetermined level, and at that time, the spark plug 37 is turned off, and the process proceeds to the compression self-ignition operation.

  Note that the spark plug 37 is also used as an auxiliary to assist combustion when the engine becomes misfired due to other conditions such as intake air temperature and torque even during steady operation by compression self-ignition.

  In general, the conditions suitable for operation differ between the spark ignition operation and the compression auto-ignition operation. In particular, the compression auto-ignition operation requires that the temperature in the combustion chamber be the auto-ignition temperature. In the ignition operation, knocking occurs when the temperature in the combustion chamber reaches the self-ignition temperature. Therefore, in the present embodiment, the effective compression ratio of the combustion chamber is lowered when performing a spark ignition operation at the time of starting, and by relatively increasing the effective compression ratio when performing a compression auto-ignition operation at the time of steady operation. The condition according to each driving is realized. The effective compression ratio is changed by adjusting the closing timing of the intake valve 19.

  FIG. 3 shows the correlation between the valve closing timing of the intake valve 19 and the effective compression ratio when the intake valve 19 is closed during the compression stroke after the intake valve 19 is opened in the intake stroke (when the intake valve 19 is closed late). It is a graph which shows. In the figure, it can be seen that the effective compression ratio increases when the valve closing timing is advanced, and the effective compression ratio decreases when the valve closing timing is retarded. Therefore, when the compression ignition operation is performed, the valve closing timing is advanced, and when the spark ignition operation is performed, the valve closing timing is retarded.

The movement of the intake valve 19 will be described in detail with reference to FIGS.
FIG. 4 is a schematic longitudinal sectional view showing the operation of the intake valve 19 when the compression self-ignition operation is performed. FIG. 4A shows a state in which the intake stroke starts, the piston 14 is in the vicinity of the top dead center, and the intake valve 19 is open. From this state, the air-fuel mixture is drawn into the combustion chamber from the intake port 16 by lowering the piston 14. FIG. 4B shows a state where the intake stroke has ended (a state where the compression stroke has started). The piston 14 is near the bottom dead center, and the intake valve 19 is closed from the open state. FIG. 4C shows a state where the compression stroke has been completed, and the piston 14 is in the vicinity of the top dead center. Therefore, the air-fuel mixture taken into the combustion chamber in the intake stroke is compressed by the stroke α1 from the bottom dead center to the top dead center and burns by self-ignition.

  On the other hand, FIG. 5 is a schematic longitudinal sectional view showing the operation of the intake valve 19 when performing a spark ignition operation. FIG. 5A shows a state in which the intake stroke starts, the piston 14 is in the vicinity of the top dead center, and the intake valve 19 is open. This state is the same as in the case of performing compression self-ignition. FIG. 5B shows a state in which the intake stroke is completed. The piston 14 is in the vicinity of the bottom dead center, but the intake valve 19 remains open. FIG. 5C shows a state where the piston 14 is slightly raised from the bottom dead center to the Z position, and the intake valve 19 is delayed (retarded) and closed. Therefore, the air-fuel mixture in the combustion chamber is only discharged from the intake port 19 and is not compressed at the stroke α2 until the piston 14 rises from near the bottom dead center to the Z position. FIG. 5D shows a state where the compression stroke has been completed, and the piston 14 is in the vicinity of the top dead center. The air-fuel mixture in the combustion chamber is compressed with a stroke α3 from the Z position in FIG. 5C to the vicinity of the top dead center in (D). That is, in the spark ignition operation, the compression stroke is shorter and the effective compression ratio is smaller than in the compression self-ignition operation. The air-fuel mixture is ignited by the spark plug 37 near the top dead center of the piston 14 and burned.

  Next, the valve operating device 21 for operating the intake valve 19 and the valve closing timing adjusting mechanism 100 as shown in FIGS. 4 and 5 will be described in detail.

[Structure of valve gear]
FIG. 6 is a longitudinal sectional view showing the valve operating device 21 of the intake valve 19. An intake valve 19 that opens and closes the intake port 16 is disposed in the cylinder head 15, and a valve shaft 19 </ b> A of the intake valve 19 is slidably supported by the cylinder head 15 via a valve bearing body 55. It protrudes into the upper valve arm chamber 56. A disc-shaped spring receiver 57 is fixed to the upper end portion of the valve shaft 19 </ b> A, and a valve spring 58 is provided between the spring receiver 57 and the bottom surface of the valve arm chamber 56. The intake valve 19 is biased upward by a valve spring 58 and is seated on the valve seat portion 59.

  A valve arm 61 is swingably supported by the valve arm chamber 56 via a valve arm shaft 60. The valve arm 61 is supported by the valve arm shaft 60 at a midway portion in the longitudinal direction (left-right direction in FIG. 6), and one end portion in the longitudinal direction is in contact with the upper end surface of the valve shaft 19A from above. The other end of the valve arm 61 is screwed with a first bolt 62 for transmitting cam power and a second bolt 63 for the hydraulic valve closing timing adjusting mechanism 100. Projecting from the lower surface of the valve arm 61 by a certain amount and fixed by lock nuts 64 and 65 so that the projecting amount can be adjusted. The first bolt 62 is located closer to the valve arm axis O1 than the second bolt 63. That is, the distance from the valve arm axis O1 to the first bolt 62 is shorter than the distance from the valve arm axis O1 to the second bolt 63.

  The first bolt 62 is connected to the intake cam 69 via a push rod 67 and a tappet 68. The intake valve drive cam mechanism 70 is connected to the first bolt 62, the push rod 67, the tappet 68, the intake cam 69, and the like. Is configured. The intake cam 69 is formed on a cam shaft 71 parallel to the valve arm shaft 60, and is connected to the crankshaft so as to rotate once by two rotations of the crankshaft as is well known. The tappet 68 is slidably fitted and supported in a support hole 72 formed in the engine body 11 </ b> A, and the lower end portion of the push rod 67 is inserted into the tappet 68.

  FIG. 7 is an enlarged view of an arrow VII portion in FIG. 6, and a joint portion 74 having a spring receiving collar 73 is integrally fixed to an upper end portion of the push rod 67. A concave portion 75 is formed at the upper end of the joint portion 74 as a connecting portion with the first bolt 62. A lower end portion of the first bolt 62 is inserted into the recess 75 so as to be movable in the moving direction of the push rod 67. An auxiliary spring 77 is provided between the collar 73 of the joint portion 74 and the annular stepped portion 76 formed in the cylinder head 15. The push rod 67 is urged downward by the auxiliary spring 77, and the tappet 68 (FIG. 6) is always in contact with the intake cam 69.

  Therefore, as shown in FIG. 6, the intake cam 69 rotates with the rotation of the cam shaft 71, and the tappet 68 abutted on the intake cam 69 slides up and down. When the tappet 68 slides up and down, the valve arm 61 swings through the push rod 67 so that the intake valve 19 opens and closes the intake port 16. Further, as shown in FIG. 4A, the intake cam 69 opens the intake valve 19 when the piston 14 is in the vicinity of the top dead center when the intake stroke starts, and as shown in FIG. The shape is set so that the intake valve 19 is closed when the piston 14 is in the vicinity of bottom dead center when the intake stroke is completed.

[Structure of valve closing timing adjustment mechanism 100]
In FIG. 7, the upper end of a hydraulic valve-opening holding piston (operating member) 80 provided in the cylinder head 15 is opposed to the lower end of the second bolt 63 screwed into the valve arm 61 so as to come into contact therewith. ing. The valve-opening holding piston 80 is fitted in a hydraulic chamber 81 formed in the cylinder head 15 so as to be slidable in the vertical direction, and moves upward by supplying hydraulic oil to the hydraulic chamber 81. ing. The hydraulic chamber 81 includes a hydraulic oil inlet 82 a formed on the lower end side wall of the hydraulic chamber, a small-diameter fixed orifice 83 formed on the side wall slightly above the lower end of the hydraulic chamber 81, and a fixed height higher than the fixed orifice 83. A variable orifice 84 formed upward is opened.

  The hydraulic oil inlet 82a is connected to the oil pump P1 via an electromagnetic opening / closing valve 85 for driving a valve opening holding piston. The fixed orifice 83 and the variable orifice 84 merge with each other, and are then connected to the oil tank OT via a hydraulic oil outlet electromagnetic opening / closing valve 86.

  FIG. 8 is a detailed cross-sectional view of the hydraulic valve closing timing adjustment mechanism 100. A discharge port 87 having a safety valve 87a is opened on the bottom wall of the hydraulic chamber 81, and the pressure in the hydraulic chamber 81 is equal to or higher than a predetermined value. Then, the safety valve 87a is opened, and the hydraulic oil in the hydraulic chamber 81 is allowed to escape from the discharge port 87.

  The drive electromagnetic on-off valve 85 is composed of a drive spool 88, a solenoid 89, and the like. The drive spool 88 is formed in a cylindrical shape, has a small diameter portion 88a at the center in the axial direction, and has large diameter portions 88b and 88c at both ends (upper and lower ends) in the axial direction. The drive spool 88 is fitted in a cylindrical hole 90 formed in the hydraulic oil inlet passage 82 so as to be axially slidable. A return spring 91 is interposed between the bottom surface of the cylindrical hole 90 and the lower end of the spool 88.

  When the solenoid 89 is not energized, the small diameter portion 88a is located in the hydraulic oil inlet passage 82, and the hydraulic oil inlet passage 82 is in an open state. Accordingly, hydraulic oil is supplied from the oil pump P1 into the hydraulic chamber 81. When the solenoid 89 is energized, the spool 88 is pushed down against the return spring 91, and the hydraulic oil inlet passage 82 is blocked by the upper large diameter portion 88b.

  A seating buffer mechanism is configured by the fixed orifice 83 and the variable orifice 84 that open to the side wall of the hydraulic chamber 81. The variable orifice 84 formed on the upper side has an inner diameter of, for example, 5 mm, and is gradually closed by the outer peripheral surface of the valve opening holding piston 80 as the valve opening holding piston 80 is lowered, so that the opening area with respect to the hydraulic chamber 81 is reduced. It has become. The fixed orifice 83 formed on the lower side has a very small inner diameter of, for example, 1 mm.

  The hydraulic oil outlet electromagnetic on-off valve 93 disposed in the hydraulic oil outlet passage 92 (hydraulic oil discharge portion) through which the fixed orifice 83 and the variable orifice 84 communicate is similar to the driving electromagnetic on-off valve 85 and the drive spool 94 and solenoid. 95 or the like.

  The drive spool 94 is formed in a cylindrical shape, has a small diameter portion 94a at the center in the axial direction, has large diameter portions 94b and 94c at both ends (upper and lower ends) in the axial direction, and a hydraulic oil outlet passage 92. And is slidably fitted in the cylindrical hole 96 formed in the axial direction. A return spring 97 is interposed between the cylindrical hole 96 and the lower end of the spool 94. When the solenoid 95 is not energized, the small diameter portion 94a is positioned in the hydraulic oil outlet passage 92, and the hydraulic oil outlet passage 92 is in an open state. Accordingly, the hydraulic oil in the hydraulic chamber 81 is discharged from both the orifices 83 and 84. When the solenoid 95 is energized, the drive spool 94 is pushed down against the return spring 97, and the hydraulic oil outlet passage 92 is closed by the upper large-diameter portion 94b.

[Operation of valve operating device 21 and valve closing timing adjusting mechanism 100]
FIG. 9 is a diagram showing the valve lift characteristics of the intake valve 19. A curve X1 indicated by a solid line indicates a valve lift characteristic when the intake valve 19 is opened and closed only by the valve drive cam mechanism 70 (the valve operating device 21) without using the valve closing timing adjusting mechanism 100 shown in FIG. A curve X2 indicated by a one-dot chain line shows an example of the valve lift characteristic when the closing timing of the intake valve 19 is retarded using the valve closing timing adjusting mechanism 100 while the valve drive cam mechanism 70 is operated.

  When the intake valve 19 is operated with the valve lift characteristic of the curve X 1, the drive electromagnetic on-off valve 85 shown in FIG. 8 is closed, the valve opening holding piston 80 is lowered, and the valve opening holding piston 80 is moved to the valve arm 61. Do not work. In this state, the intake valve 19 is driven only by the valve drive cam mechanism 70.

  When the intake valve 19 is operated with the valve lift characteristic of the curve X2, hydraulic oil is supplied to the hydraulic chamber 81 by opening the drive electromagnetic on-off valve 85 in parallel with the valve opening operation by the valve drive cam mechanism 70, and the intake air Simultaneously or subsequently to the time when the valve 19 reaches the maximum open position A1 in FIG. 6, the valve opening holding piston 80 also protrudes upward to the maximum protrusion height H1 (FIG. 8). The on-off valve 85 is set to be closed. On the other hand, the hydraulic oil outlet electromagnetic on-off valve 93 is kept closed until the position A2 in FIG. 9 is reached after the valve opening holding piston 80 starts to rise, and is opened at the position A2.

  As a result, as shown in FIG. 6, first, the other end of the valve arm 61 is pushed up by the push rod 67 of the valve drive cam mechanism 70, thereby opening the intake valve 19 against the valve spring 58. Then, it opens from the seating position A0 to the maximum opening position A1 indicated by a virtual line. That is, the valve is opened with the valve lift characteristic shown in the valve opening operation period T1 of the curve X1 in FIG.

  After the intake valve 19 is fully opened, the push rod 67 starts to descend, but the valve-opening holding piston 80 is maintained at the maximum height H1, thereby holding the valve arm 61 via the second bolt 63. The valve 19 is held in a fully opened state. That is, at the position A1, a transition is made from the solid curve X1 to the dashed-dotted curve X2.

  When the valve holding period T2 ends with the intake valve 19 fully open, the hydraulic oil outlet electromagnetic on-off valve 93 in FIG. 8 opens at the position A2, and the hydraulic oil in the hydraulic chamber 81 begins to be discharged from the orifices 83 and 84. The valve-opening holding piston 80 starts to descend from the maximum height H1.

  When the opening portion of the variable orifice 84 starts to be closed by the outer peripheral surface of the valve opening holding piston 80 in the downward stroke of the valve opening holding piston 80, the amount of hydraulic oil discharged from the variable orifice 84 decreases, thereby causing the valve opening holding piston 84 to decrease. As a result, the lowering speed of the intake valve 19 becomes slower, and the closing speed of the intake valve 19 shown in FIG. 6 also becomes slower. That is, the seating speed of the intake valve 19 starts to be buffered.

[System configuration of valve operating device and valve closing timing adjustment mechanism]
FIG. 10 is an engine system conceptual diagram showing a configuration relating to operations of the valve operating device 21 of the intake valve 19 and the valve closing timing adjusting mechanism 100 in particular. The engine 11 is provided with a starter motor 102, an oil pump P1 for engine lubricating oil, valve gears 21 and 22, a spark plug 37, and the like. Further, the engine 11 is provided with an intake air temperature sensor 48, a lubricating oil temperature sensor 103, and a cooling water temperature sensor 47, and these detected values are input to the controller.

  The valve closing timing adjusting mechanism 100 is connected to the oil pump P1 via a driving electromagnetic on-off valve 85 and a hydraulic oil outlet electromagnetic on-off valve 93 (hereinafter collectively referred to as a valve closing timing control valve 104) to operate the hydraulic oil. Is also connected to an additional oil pump (starting pump) P2 to supply hydraulic oil. A solenoid valve 105 for turning on / off the driving of the hydraulic circuit is provided in the hydraulic oil passage to the valve closing timing adjusting mechanism 100. An electric pump is used as the additional oil pump P2, and it can be operated by energization even when the engine 11 is stopped.

  In such a system configuration, the operation from the start of the engine 11 to the steady operation will be described. FIG. 11 is a time chart from the start of the engine 11 to the steady operation. The engine 11 is started by the starter motor 102 at time t1, and at the same time, the additional oil pump P2 is activated, the ignition signal to the spark plug 37 is turned on, and the operation by spark ignition is started.

  At this time, the valve closing timing of the intake valve 19 is adjusted to the retard side by the operation of the valve closing timing adjusting mechanism 100. That is, the intake valve 19 operates with the valve lift characteristic of the curve X2 shown in FIG. Further, the hydraulic additional oil pump P2 is activated simultaneously with the starter motor 102 being turned on, so that the hydraulic pressure can be immediately supplied to the valve closing timing adjusting mechanism 100.

  The starter motor 102 is turned off at time t2 when the engine speed increases to a predetermined level. The valve closing timing adjusting mechanism 100 gradually follows the closing timing of the intake valve 19 to the advance side substantially following the increase in the engine speed. That is, the time during which the valve-opening holding piston 80 protrudes (T2 in FIG. 9) is gradually shortened, and the time during which the intake valve 19 is opened during the compression stroke is gradually shortened. As a result, the effective compression ratio is increased and the conditions under which compression self-ignition occurs are prepared.

  The additional oil pump P2 is stopped at time t3 when the engine speed further increases to a predetermined level. This is because the oil pressure to the valve closing timing adjusting mechanism 100 can be sufficiently supplied by the oil pump P1 alone by increasing the engine speed.

  When the effective compression ratio increases and the temperature in the combustion chamber reaches the self-ignition temperature, compression self-ignition occurs in the combustion chamber. At time t4, when the torque increases to a predetermined level, the ignition signal is turned off. And after that, the driving | operation by compression self-ignition is mainly performed.

  Therefore, in the present embodiment, the effective compression ratio is abruptly changed because the effective compression ratio is gradually increased by gradually advancing the closing timing of the intake valve 19 corresponding to the increase in the engine speed. Therefore, it is possible to shift from the spark ignition operation to the compression ignition operation while maintaining a stable state.

  The closing timing of the intake valve 19 is adjusted to the most advanced side slightly before the engine speed reaches the rating. At this time, the valve closing timing adjustment 100 is not operated. That is, the valve closing timing adjustment mechanism 100 is used only for a limited period at the time of starting, and at least during steady operation by compression auto-ignition after turning off the ignition signal, the valve closing timing adjustment mechanism 100 is operated. Instead, the intake valve 19 is opened / closed only by the valve operating device 21. Therefore, since the hydraulic pressure supply to the valve closing timing adjusting mechanism 100 can be stopped during a steady operation performed for a long time, the efficiency of the valve closing timing adjusting mechanism 100 does not deteriorate due to the loss of the hydraulic pressure. The durability can be improved by shortening the use time.

  The warm-up state when starting the engine 11 is usually different depending on the state before the start. If the closing timing of the first intake valve 19 at the time of starting is always constant, a misfire occurs when the engine 11 is cold. When it is warm, knocking is likely to occur.

  Therefore, in this embodiment, the valve closing timing adjusting mechanism 100 is controlled so that the closing timing of the first intake valve 19 at the time of starting is changed according to the warm-up state of the engine 11. FIG. 12 is a part of a time chart in the case where the closing timing of the intake valve is adjusted according to the warm-up state of the engine 11, and a solid line Y1 of the intake valve closing timing indicates a state at the time of engine warm start. A dotted line Y2 indicates a state at the time of engine cold start.

  When the engine 11 is started in a cold state, the closing timing of the intake valve 19 is advanced and the effective compression ratio is increased (Y2) than when the engine 11 is started in a warm state. This promotes combustion and prevents misfire. Conversely, when the engine is started in a warm state, the closing timing of the intake valve 19 is retarded to lower the effective compression ratio (Y1) to prevent knocking.

  The warm-up state of the engine at the time of starting can be determined based on the engine coolant temperature and the intake air temperature. When the temperature of the engine cooling water is used, for example, the cooling water temperature immediately before the starter motor 102 is turned on, the time from when the starter motor 102 is turned on until the first explosion, or when the starter motor 102 is turned off is set to It is detected by the temperature sensor 47 (FIG. 10), and the closing timing of the intake valve 19 is adjusted according to the temperature. When the intake air temperature is used, the intake air temperature is detected by the intake air temperature sensor 48 (FIG. 10) between the time when the starter motor 102 is turned on and the first explosion, or when the starter motor 102 is turned off, and the temperature is changed accordingly. The closing timing of the intake valve can be adjusted.

[Other Embodiments]
The present invention is not limited to the above-described embodiment, and can be appropriately modified as follows, for example.

  (1) In the above embodiment, the valve closing timing adjusting mechanism 100 lowers the effective compression ratio of the combustion chamber by retarding the closing timing of the intake valve 19 from the closing timing of the intake valve 19 by the valve operating device 21. Although it is configured, it is also possible to reduce the effective compression ratio by advancing the closing timing of the intake valve 19 by the valve operating device 21 (closing the intake valve 19 during the intake stroke). .

  (2) In the above embodiment, the hydraulic valve closing timing adjusting mechanism 100 is used. However, a mechanical valve closing timing adjusting mechanism such as a cam type may be used.

  (3) In the above embodiment, a four-cylinder premixed compression self-ignition engine is exemplified, but the number of cylinders is not limited at all.

  (4) In the above embodiment, the heating device 35 for heating the air-fuel mixture uses engine cooling water as a heat exchange medium, but engine lubricating oil or exhaust gas may be used. Furthermore, the heating device 35 can be configured by an electric heater or a flame burner.

1 is a schematic longitudinal sectional view of an engine according to an embodiment of the present invention. It is the same schematic plan view. It is a graph which shows the correlation of the valve closing time of an intake valve, and an effective compression ratio. It is a schematic longitudinal cross-sectional view which shows operation | movement of the intake valve at the time of performing the driving | operation by compression self-ignition. It is a schematic longitudinal cross-sectional view which shows operation | movement of the intake valve at the time of performing operation by spark ignition. It is a longitudinal cross-sectional view which shows the valve operating apparatus of an intake valve. It is an enlarged view of the arrow VII part of FIG. It is a detailed sectional view of a hydraulic valve closing timing adjustment mechanism. It is a figure which shows the valve lift characteristic of an intake valve. 1 is a conceptual diagram of an engine system showing a configuration relating to a valve operating device for an intake valve and a valve closing timing adjusting mechanism. It is a time chart from engine starting to steady operation. It is a part of time chart in the case of adjusting the closing timing of the intake valve according to the warm-up state of the engine.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Engine 16 Intake port 19 Intake valve 21 Valve operating device 37 Ignition device 80 Opening holding piston (operation member)
100 Valve closing timing adjustment mechanism

Claims (5)

A premixed compression self-ignition engine that is self-ignited and combusted by compressing an air-fuel mixture premixed with fuel and air in a combustion chamber at least in steady operation;
An intake valve for opening and closing an intake port for introducing an air-fuel mixture into the combustion chamber, a valve operating device for opening and closing the intake valve, and a valve closing timing adjusting mechanism for adjusting the closing timing of the intake valve by the valve operating device; And an ignition device for spark-igniting the air-fuel mixture in the combustion chamber,
The valve operating apparatus includes a valve spring that urges the intake valve in a closing direction, a valve arm that is swingably supported by a cylinder head, and a cam mechanism that interlocks with rotation of a crankshaft. When the cam mechanism pushes out the valve arm, the intake valve moves in the opening direction,
The valve closing timing adjustment mechanism supplies a hydraulic chamber, an operation member that moves to the valve arm side or the counter-valve arm side according to the amount of oil in the hydraulic chamber, and hydraulic oil from an oil pump to the hydraulic chamber. A hydraulic oil inlet passage; a solenoid-type driving solenoid on-off valve that opens and closes the hydraulic oil inlet passage; a hydraulic oil outlet passage that discharges hydraulic oil from the hydraulic chamber; and a solenoid-type solenoid valve that opens and closes the hydraulic oil outlet passage. An outlet solenoid on-off valve, and a fixed orifice and a variable orifice that open to the hydraulic chamber and communicate with the hydraulic oil outlet passage, wherein the opening position of the variable orifice is greater than the opening position of the fixed orifice. Provided on the valve arm side, the opening diameter of the variable orifice is larger than the opening diameter of the fixed orifice. The operating member is intended that the operating member is moved said intake valve in an opening direction in contact with the valve arm can be spaced apart from the valve arm,
When starting the engine, the valve closing device opens and closes the intake valve, and the valve closing timing adjusting mechanism adjusts the closing timing of the intake valve to lower the effective compression ratio in the combustion chamber and activates the ignition device. To perform a spark ignition operation,
During steady operation, the valve closing timing adjustment mechanism is not operated, and the intake valve is opened / closed by the valve operating device so that the effective compression ratio in the combustion chamber is higher than when the engine is started. A premixed compression self-ignition engine characterized by being configured to perform an ignition operation.   The premixed compression self-ignition engine according to claim 1, wherein the spark ignition operation at the time of engine start and the compression self-ignition operation at the time of steady operation are shifted according to the engine speed. .   2. The premixed compression self-ignition engine according to claim 1, wherein the valve closing timing adjusting mechanism is configured to change the closing timing of the intake valve in accordance with a change in engine speed.   The warm-up state at the time of starting the engine is determined by the temperature of the engine cooling water or the intake air temperature to the combustion chamber, and the closing timing of the intake valve is adjusted by the valve closing timing adjusting mechanism according to the warm-up state. 2. The premixed compression self-ignition engine according to claim 1, wherein the engine is configured. During starting the engine, wherein the starting pump electric supplying hydraulic pressure is provided in the operating member, according to claim 1 homogeneous charge compressed ignition engine according.

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