JP4239921B2 - V-type engine and variable valve mechanism thereof - Google Patents

Description

  The present invention relates to a variable valve mechanism for a V-type engine that changes a maximum valve lift amount of an engine valve (at least one of an intake valve and an exhaust valve), and a V-type engine that includes the variable valve mechanism.

A variable valve mechanism that can change the maximum lift amount and operating angle of an engine valve has been proposed (see Patent Document 1).
The variable valve mechanism includes a control shaft that can move in the axial direction and an actuator that drives the control shaft.

  On the control shaft, a slider gear is provided that can move in the axial direction in conjunction with the control shaft. Also, on the slider gear, there are an input arm that transmits the driving force of the camshaft of the engine valve to the slider gear, and an output arm that opens and closes the engine valve through the driving force of the camshaft transmitted through the slider gear. Is provided. These input arm, output arm, and slider gear are meshed with each other through a helical spline.

In the variable valve mechanism having such a configuration, the relative phase between the input arm and the output arm changes by displacing the control shaft in the axial direction through the actuator. As the relative phase changes, the maximum valve lift amount of the engine valve is changed.
JP 2001-263015 A JP 2003-161127 A

By the way, when the variable valve mechanism is mounted on a V-type engine, it is necessary to adapt the configuration of the variable valve mechanism for each bank in order to ensure an appropriate operation state in each bank.
As shown in FIG. 25, in the variable valve mechanism 252 of the first bank 251 and the variable valve mechanism 254 of the second bank 253, the helical gears of the helical splines 255 and 256 are inclined in opposite directions to the slider gear 257. , 258 may be realized to achieve adaptation to a V-type engine, but in this case, the following becomes a problem.

  In the above configuration, the slider gear 257 of the variable valve mechanism 252 of the first bank 251 and the slider gear 258 of the variable valve mechanism 254 of the second bank 253 are different, so two types of slider gears are required. . That is, when manufacturing the variable valve mechanism, an increase in the number of parts is inevitable.

  Although a variable valve mechanism for a V-type engine has been proposed in Patent Document 2, the configuration is different from that of a variable valve mechanism that changes the maximum valve lift amount through displacement of the control shaft. Not considered.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a variable valve mechanism for a V-type engine that can ensure proper operation in each bank and can be configured with a smaller number of parts. And a V-type engine provided with the variable valve mechanism.

In the following, means for achieving the above object and its effects are described.
<Claim 1>
The invention according to claim 1 is applied to a V-type engine having an engine valve and a camshaft for opening and closing the engine valve, and changes the maximum valve lift amount of the engine valve of the first bank. A valve mechanism and a second variable valve mechanism for changing a maximum valve lift amount of the engine valve of the second bank, wherein the first variable valve mechanism and the second variable valve mechanism are movable in the axial direction. A control shaft; a valve lift mechanism for lifting the engine valve; and an actuator for displacing the control shaft in the axial direction. The valve lift mechanism is provided on the control shaft. A slider gear that is movable in the axial direction in conjunction with the control shaft, and a slider gear provided on the slider gear. An input arm that is driven by a camshaft and an output arm that is provided on the slider gear and lifts the engine valve. The input arm and the output arm through movement of the control shaft The variable valve mechanism of the V-type engine that changes the maximum valve lift amount of the engine valve by relatively rotating the engine valve, and the first variable valve mechanism and the second variable valve mechanism have the same structure. A control shaft and a valve lift mechanism are adopted, and the mounting position of the actuator with respect to the control shaft is set on the opposite side of the first variable valve mechanism and the second variable valve mechanism, and the maximum valve of the V-type engine When changing the lift amount, the control shaft of the first variable valve mechanism It is summarized as further comprising a control means for displacing the opposite direction and the control shaft of the serial second variable valve mechanism actuator for each of the variable valve mechanism as a reference.

  In the above configuration, since the control shaft and the valve lift mechanism having the same structure are adopted in the first variable valve mechanism and the second variable valve mechanism, the variable valve mechanism of the V-type engine can be reduced with a smaller number of parts. Can be configured.

  Incidentally, in the above configuration, the first variable valve mechanism and the second variable valve mechanism are configured through the control shaft and the valve lift mechanism having the same structure, and the mounting position of the actuator with respect to the control shaft is the same as that of the first variable valve mechanism. Since the second variable valve mechanism is set on the opposite side, when each variable valve mechanism is mounted in the corresponding bank, the movement direction of the control shaft and the change direction of the maximum valve lift amount are the first variable movement. The opposite is true between the valve mechanism and the second variable valve mechanism.

  In the above configuration, since the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are displaced in opposite directions with reference to the actuator of each variable valve mechanism, the first bank And the second bank change the maximum valve lift in the same direction. Thereby, it becomes possible to ensure an appropriate operation of the variable valve mechanism in each bank of the V-type engine.

< Claim 2 >
The invention according to claim 2 is a first variable valve mechanism for changing the maximum valve lift amount of the engine valve of the first bank and a second variable valve mechanism for changing the maximum valve lift amount of the engine valve of the second bank. The first variable valve mechanism and the second variable valve mechanism include a control shaft that is movable in the axial direction, and lifts the engine valve. The valve lift mechanism is configured to include an actuator that displaces the control shaft in the axial direction. The valve lift mechanism is provided on the control shaft and is coupled to the control shaft in the axial direction. A slider gear that can be moved to the inlet, and an input provided on the slider gear and driven by the camshaft of the engine valve. An arm and an output arm that is provided on the slider gear and lifts the engine valve, and by relatively rotating the input arm and the output arm through movement of the control shaft, A V-type engine for changing a maximum valve lift amount of the engine valve, wherein a control shaft and a valve lift mechanism having the same structure are adopted in the first variable valve mechanism and the second variable valve mechanism, Regarding the actuator of the first variable valve mechanism and the actuator of the second variable valve mechanism, these actuators are arranged on the same side surface of the V-type engine, and when the maximum valve lift amount of the V-type engine is changed, A control shaft of the variable valve mechanism and a control system of the second variable valve mechanism It is summarized as further comprising a control means for displacing the opposite direction and a shift actuator for each of the variable valve mechanism as a reference.

  In the above configuration, since the control shaft and the valve lift mechanism having the same structure are adopted in the first variable valve mechanism and the second variable valve mechanism, the variable valve mechanism of the V-type engine can be reduced with a smaller number of parts. Can be configured.

  Incidentally, in the above configuration, the first variable valve mechanism and the second variable valve mechanism are configured through the control shaft and the valve lift mechanism having the same structure, and the first variable valve mechanism and the second variable valve mechanism are Since the actuator is arranged on the same side of the V-type engine, the moving direction of the control shaft and the changing direction of the maximum valve lift amount are opposite in the first variable valve mechanism and the second variable valve mechanism.

  In the above configuration, since the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are displaced in opposite directions with reference to the actuator of each variable valve mechanism, the first bank And the second bank change the maximum valve lift in the same direction. Thereby, it becomes possible to ensure an appropriate operation of the variable valve mechanism in each bank of the V-type engine.

< Claim 3 >
According to a third aspect of the present invention, there is provided a variable valve mechanism for a V-type engine that changes a maximum valve lift amount of an engine valve by displacing a slider gear of a valve lift mechanism together with a control shaft through an actuator. A control shaft and a valve lift mechanism having the same structure are used in the first variable valve mechanism for changing the maximum valve lift amount of the engine valve and the second variable valve mechanism for changing the maximum valve lift amount of the engine valve in the second bank. The actuator is mounted on the control shaft at a position opposite to the first variable valve mechanism and the second variable valve mechanism, and when changing the maximum valve lift amount of the V-type engine, Control shaft of first variable valve mechanism and second variable valve mechanism Of the control shaft and the actuator of each of the variable valve mechanism based are summarized as further comprising a control means for displacing the opposite direction.

  In the above configuration, since the control shaft and the valve lift mechanism having the same structure are adopted in the first variable valve mechanism and the second variable valve mechanism, the variable valve mechanism of the V-type engine can be reduced with a smaller number of parts. Can be configured.

  Incidentally, in the above configuration, the first variable valve mechanism and the second variable valve mechanism are configured through the control shaft and the valve lift mechanism having the same structure, and the mounting position of the actuator with respect to the control shaft is the same as that of the first variable valve mechanism. Since the second variable valve mechanism is set on the opposite side, when each variable valve mechanism is mounted in the corresponding bank, the movement direction of the control shaft and the change direction of the maximum valve lift amount are the first variable movement. The opposite is true between the valve mechanism and the second variable valve mechanism.

  In the above configuration, since the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are displaced in opposite directions with reference to the actuator of each variable valve mechanism, the first bank And the second bank change the maximum valve lift in the same direction. Thereby, it becomes possible to ensure an appropriate operation of the variable valve mechanism in each bank of the V-type engine.

< Claim 4 >
The invention according to claim 4 is a first variable valve mechanism for changing the maximum valve lift amount of the engine valve of the first bank and a second variable valve mechanism for changing the maximum valve lift amount of the engine valve of the second bank. The variable valve mechanism of the V-type engine is configured to include, and these variable valve mechanisms change the maximum valve lift amount by displacing the slider gear of the valve lift mechanism together with the control shaft through the actuator. In a certain V-type engine, a control shaft and a valve lift mechanism having the same structure are adopted in the first variable valve mechanism and the second variable valve mechanism, and the actuator of the first variable valve mechanism and the second movable valve mechanism are used. For the actuator of the variable valve mechanism, these actuators are arranged on the same side of the V-type engine, and the V Control for displacing the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism in opposite directions with reference to the actuator of each variable valve mechanism when changing the maximum valve lift of the engine The gist is that it has means.

  In the above configuration, since the control shaft and the valve lift mechanism having the same structure are adopted in the first variable valve mechanism and the second variable valve mechanism, the variable valve mechanism of the V-type engine can be reduced with a smaller number of parts. Can be configured.

  Incidentally, in the above configuration, the first variable valve mechanism and the second variable valve mechanism are configured through the control shaft and the valve lift mechanism having the same structure, and the first variable valve mechanism and the second variable valve mechanism are Since the actuator is arranged on the same side of the V-type engine, the moving direction of the control shaft and the changing direction of the maximum valve lift amount are opposite in the first variable valve mechanism and the second variable valve mechanism.

  In the above configuration, since the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are displaced in opposite directions with reference to the actuator of each variable valve mechanism, the first bank And the second bank change the maximum valve lift in the same direction. Thereby, it becomes possible to ensure an appropriate operation of the variable valve mechanism in each bank of the V-type engine.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS.
In the present embodiment, it is assumed that the variable valve mechanism according to the present invention is embodied as a variable valve mechanism of a V-type 8-cylinder engine.

<Structure of V-type engine>
FIG. 1 shows a planar structure of a V-type engine.
The V-type engine (engine 1) includes a cylinder block 11.

  The cylinder block 11 includes a first bank 12A and a second bank 12B. The first bank 12A indicates a part including one of the cylinder groups arranged in the axial direction of the crankshaft in the cylinder block 11. The second bank 12 </ b> B indicates a part including the other of the cylinder groups arranged in the axial direction of the crankshaft in the cylinder block 11.

  The first bank 12 </ b> A includes a plurality of cylinders 13. A first cylinder head 14 </ b> A is disposed on the top of the cylinder 13. The first cylinder head 14A is provided with a first variable valve mechanism 3A that continuously changes the maximum valve lift amount and operating angle of the intake valve 21 of the first bank 12A.

  The second bank 12 </ b> B includes a plurality of cylinders 13. A second cylinder head 14 </ b> B is disposed on the top of the cylinder 13. The second cylinder head 14B is provided with a second variable valve mechanism 3B that continuously changes the maximum valve lift amount and operating angle of the intake valve 21 of the second bank 12B.

In the present embodiment, the variable valve mechanism 3 of the engine 1 is configured including the first variable valve mechanism 3A and the second variable valve mechanism 3B.
In the engine 1, the first bank 12 </ b> A and the second bank 12 </ b> B are configured substantially symmetrically about the crankshaft 15. Accordingly, the first variable valve mechanism 3A and the second variable valve mechanism 3B are arranged in the banks 12A and 12B so as to be symmetrical about the crankshaft 15.

<Structure of each bank>
FIG. 2 shows a planar structure of the first bank 12A.
FIG. 3 shows a planar structure of the second bank 12B.

  The first cylinder head 14A and the second cylinder head 14B are provided with an intake valve 21 for opening and closing the intake port of the cylinder 13 for each cylinder 13. An exhaust valve 22 that opens and closes the exhaust port of the cylinder 13 is provided for each cylinder 13.

  In each cylinder 13, an intake camshaft 23 is provided in the vicinity of the intake valve 21. The intake cam shaft 23 is provided with intake cams 25 at positions corresponding to the cylinders 13.

  In each cylinder 13, an exhaust camshaft 24 is provided in the vicinity of the exhaust valve 22. The exhaust cam shaft 24 is provided with exhaust cams 26 at positions corresponding to the cylinders 13.

The intake camshaft 23 is rotatably supported through a plurality of intake side partition walls 27.
The exhaust camshaft 24 is rotatably supported through a plurality of exhaust side partition walls 28.
The intake camshaft 23 and the exhaust camshaft 24 are drivingly connected to the crankshaft 15 via a timing chain 29. Hereinafter, of the side surfaces of the engine 1, the side surface on which the timing chain 29 is provided is referred to as a first side surface S1. A side surface facing the first side surface S1 through the engine 1 is defined as a second side surface S2. The first side surface S1 and the second side surface S2 correspond to a pair of side surfaces that face each other with the engine 1 interposed therebetween.

  In the first bank 12A and the second bank 12B, the first variable valve mechanism 3A and the second variable valve mechanism 3B are provided in the vicinity of the intake camshaft 23, respectively. The first variable valve mechanism 3 </ b> A and the second variable valve mechanism 3 </ b> B are provided with a plurality of valve lift mechanisms 4 that lift the intake valve 21 through the torque of the intake camshaft 23. The valve lift mechanism 4 is disposed between a pair of adjacent intake side partition walls 27.

<Overall structure of variable valve mechanism>
FIG. 4 shows a perspective structure of the first variable valve mechanism 3A.
FIG. 5 shows a perspective structure of the second variable valve mechanism 3B.

  The first variable valve mechanism 3A and the second variable valve mechanism 3B include a valve mechanism body 31 and an actuator 32. The valve mechanism main body 31 includes a rocker shaft 33, a control shaft 34, and a valve lift mechanism 4. In the present embodiment, the first variable valve mechanism 3A and the second variable valve mechanism 3B are configured to include a valve mechanism body 31 having the same structure.

  The rocker shaft 33 is disposed so as to extend in the cylinder arrangement direction in each of the cylinder heads 14A and 14B. That is, it is arranged in parallel with the intake camshaft 23. Further, it is fixed through the intake side partition wall 27 so that it cannot rotate and move in the axial direction.

A control shaft 34 is disposed in the rocker shaft 33 so as to be movable in the axial direction.
A valve lift mechanism 4 is provided on the rocker shaft 33 at a position corresponding to each cylinder 13. That is, all the valve lift mechanisms 4 are supported by one common rocker shaft 33.

The control shaft 34 is drivingly connected to the actuator 32. Then, it is moved in the axial direction through the actuator 32.
The mounting position of the actuator 32 with respect to the control shaft 34 of the first variable valve mechanism 3A is set opposite to the mounting position of the actuator 32 with respect to the control shaft 34 of the second variable valve mechanism 3B. That is, when the first variable valve mechanism 3A and the second variable valve mechanism 3B are viewed from the direction W1 in the figure, the actuator 32 is attached to the right end portion of the control shaft 34 in the first variable valve mechanism 3A. In contrast, in the second variable valve mechanism 3B, the actuator 32 is attached to the left end of the control shaft 34. Thus, the first variable valve mechanism 3A and the second variable valve mechanism 3B differ only in the attachment position of the actuator 32 with respect to the control shaft 34.

The actuator 32 is driven through an electronic control unit 9 that controls the engine 1 in an integrated manner.
The electronic control unit 9 includes a CPU that executes various processes related to the control of the engine 1, a memory that stores a control program and information necessary for the control, an input port that controls input and output of signals from the outside, and an output port It is prepared for. In the present embodiment, the control means is configured including the electronic control device 9.

  The electronic control device 9 changes the maximum valve lift amount and the operating angle of the intake valve 21 by displacing the control shaft 34 in the axial direction through the control of the actuator 32.

  In the engine 1, the first variable valve mechanism 3A and the second variable valve mechanism 3B are arranged in the banks 12A and 12B so as to be symmetric with respect to the crankshaft 15. The actuator 32, the second variable valve mechanism 3B, and the actuator 32 of the variable valve mechanism 3A are arranged on the same side surface (second side surface S2 in the present embodiment) of the engine 1 (see FIG. 1).

<Structure of valve mechanism body>
FIG. 6 shows an exploded perspective structure of the valve mechanism main body 31.
FIG. 7 shows a partially broken perspective structure of the input arm and the output arm as seen from the front side (the direction of the arrow W1 in FIGS. 4 and 5).

FIG. 8 shows a partially broken perspective structure of the input arm and the output arm viewed from the back side (in the direction of arrow W2 in FIGS. 4 and 5).
The valve lift mechanism 4 includes a slider gear 41, an input arm 42, and an output arm 43.

  The slider gear 41 is provided on the rocker shaft 33. Further, on the rocker shaft 33, it is provided so as to be able to move in the axial direction in conjunction with the control shaft 34.

  The slider gear 41, the input arm 42, and the output arm 43 are meshed with each other through a helical spline. Further, the input arm 42 and the output arm 43 are assembled to the slider gear 41 in a state where the end surfaces located between the arms 42 and 43 are in contact with each other.

<Slider gear structure>
In the slider gear 41, a helical spline (input-side helical spline 41A) that meshes with the helical spline 42B of the input arm 42 is formed at the center in the axial direction. Moreover, helical splines (output-side helical splines 41B) that mesh with the helical splines 43B of the output arm 43 are formed at both ends in the axial direction. The input-side helical spline 41A and the output-side helical spline 41B are formed so that the inclination directions of the tooth traces are opposite to each other.

<Structure of input arm>
A space extending in the axial direction of the rocker shaft 33 is formed in the input arm 42 main body (housing 42A).

A helical spline 42B that meshes with the input-side helical spline 41A of the slider gear 41 is formed on the inner peripheral side of the housing 42A.
A pair of arms 42CL and 42CR projecting radially outward are formed on the outer peripheral side of the housing 42A. The arm 42CL and the arm 42CR are formed to be parallel to each other.

  A shaft 42D is provided between the arm 42CL and the arm 42CR so as to be parallel to the axial direction of the rocker shaft 33. A roller 42E is rotatably attached to the shaft 42D.

<Structure of output arm>
A space extending in the axial direction of the rocker shaft 33 is formed in the output arm 43 main body (housing 43A).

  A helical spline 43B that meshes with the output-side helical spline 41B of the slider gear 41 is formed on the inner peripheral side of the housing 43A. In addition, the inclination direction of the tooth trace in the helical spline 43B of the output arm 43 is formed opposite to the inclination direction of the tooth stripe in the helical spline 42B of the input arm 42.

  A nose 43C protruding outward in the radial direction is formed on the outer peripheral side of the housing 43A. The nose 43C is formed in a substantially triangular shape. In addition, a cam surface 43D curved in a concave shape is provided on one side thereof.

  In the housing 43 </ b> A, a bearing portion 43 </ b> E for supporting the rocker shaft 33 is provided on an end surface that does not contact the input arm 42 among the end surfaces orthogonal to the central axis of the rocker shaft 33.

<Assembly structure of variable valve mechanism>
FIG. 9 shows a perspective structure of the slider gear 41, the rocker shaft 33 and the control shaft 34.

  In the slider gear 41, a through hole 41C extending in the axial direction is formed on the center axis side. A long hole 41D extending in the circumferential direction is formed between the helical spline 41A and the helical spline 41B.

In the rocker shaft 33, a long hole 33H extending in the axial direction is formed at a position corresponding to the long hole 41D of the slider gear 41.
In the control shaft 34, an insertion hole 34H is formed at a location corresponding to the long hole 33H of the rocker shaft 33.

  When the rocker shaft 33 and the control shaft 34 are inserted into the through hole 41C of the slider gear 41, the locking pin 44 is inserted at a location where the long hole 41D of the slider gear 41 and the long hole 33H of the rocker shaft 33 intersect. Is done. One end of the locking pin 44 is fixed to the insertion hole 34H of the control shaft 34.

In each variable valve mechanism 3A, 3B assembled in this manner, the slider gear 41 moves as follows.
(A) Since the locking pin 44 can move along the long hole 33H of the rocker shaft 33, the slider gear 41 is interlocked with the control shaft 34 when the control shaft 34 is moved in the axial direction. To move in the axial direction.
(B) Since the locking pin 44 is inserted into the elongated hole 41 </ b> D of the slider gear 41, the slider gear 41 swings around the rocker shaft 33 when the torque of the intake camshaft 23 is transmitted to the input arm 42. It becomes like this.

  Thus, the slider gear 41 can move in the axial direction on the rocker shaft 33 while the position in the axial direction on the control shaft 34 is fixed. The rocker shaft 33 (control shaft 34) can be used as a fulcrum.

<Internal structure of valve lift mechanism>
FIG. 10 shows a perspective structure of the valve lift mechanism 4 with the upper half of the input arm 42 and the output arm 43 removed.

  In the valve lift mechanism 4, the input side helical spline 41 </ b> A of the slider gear 41 and the helical spline 42 </ b> B of the input arm 42 are engaged with each other. Further, the output-side helical spline 41B of the slider gear 41 and the helical spline 43B of the output arm 43 are engaged with each other.

  Accordingly, the slider gear 41 is moved in the axial direction together with the control shaft 34, and the relative positions of the slider gear 41, the input arm 42 and the output arm 43 in the axial direction are changed, so that the input arm 42 and the output arm 43 are changed. On the other hand, twisting forces in opposite directions are applied. As a result, the input arm 42 and the output arm 43 rotate relative to each other, and the relative phase difference between the input arm 42 (roller 42E) and the output arm 43 (nose 43C) is changed. In each of the variable valve mechanisms 3A and 3B, all slider gears 41 are fixed to a common control shaft 34. Accordingly, all cylinders of the corresponding banks 12A and 12B are moved as the control shaft 34 moves. 13 maximum valve lifts are changed simultaneously.

In the engine 1, the maximum valve lift amount of the intake valve 21 can be changed by changing the relative phase difference between the input arm 42 and the output arm 43.
(A) When the relative phase difference is the smallest, that is, when the roller 42E and the nose 43C are closest to each other in the circumferential direction of the valve lift mechanism 4, the maximum valve lift amount of the intake valve 21 is the smallest. Hereinafter, the maximum valve lift amount at this time is referred to as the minimum lift amount LMIN.
(B) When the relative phase is the largest, that is, when the roller 42E and the nose 43C are in the most separated state in the circumferential direction of the valve lift mechanism 4, the maximum valve lift amount of the intake valve 21 is the largest. Hereinafter, the maximum valve lift amount at this time is referred to as a maximum lift amount LMAX.

<Valve lift structure of engine>
FIG. 11 shows a cross-sectional structure of the engine 1 along the line D1-D1 in FIG.
The first variable valve mechanism 3A and the second variable valve mechanism 3B are provided between the intake cam 25 of the intake cam shaft 23 and the roller rocker arm 71 in each cylinder head 14A, 14B.

  The roller rocker arm 71 is provided between each variable valve mechanism 3A, 3B and the intake valve 21. One end of the roller rocker arm 71 is supported by a lash adjuster 72 fixed to the cylinder head 12. The other end of the roller rocker arm 71 is in contact with a tappet 73 at the upper end of the intake valve 21.

  The end portion on the tappet 73 side of the roller rocker arm 71 (the tappet side end portion 71T) is urged toward the variable valve mechanisms 3A and 3B by the valve spring 74 of the intake valve 21. Accordingly, the roller 71R of the roller rocker arm 71 is always brought into contact with the valve lift mechanism 4.

The roller 42E of the input arm 42 is urged so as to be always pressed against the intake cam 25 by a spring 75 disposed in a compressed state on the cylinder head 12.
The output arm 43 is in a state where either the base circle portion of the housing 43A or the cam surface 43D of the nose 43C is in contact with the roller 71R of the roller rocker arm 71 at all times.

  In the engine 1 having such a structure, the roller rocker arm 71 is pressed by the output arm 43 through the swing of the valve lift mechanism 4 due to the rotation of the intake camshaft 23. The intake valve 21 is lifted through the swinging of the roller rocker arm 71.

<Change mode of maximum valve lift>
FIG. 12 shows the relationship between the moving direction of the control shaft 34 and the changing direction of the maximum valve lift amount.

  In the first variable valve mechanism 3A, when the control shaft 34 is displaced toward the first side surface S1 of the engine 1 (when displaced in a direction away from the actuator 32), the maximum valve lift amount of the first bank 12A is increased. Change direction. On the other hand, when the control shaft 34 is displaced toward the second side surface S2 of the engine 1 (when the control shaft 34 is displaced in a direction approaching the actuator 32), the maximum valve lift amount of the first bank 12A changes.

  In the second variable valve mechanism 3B, when the control shaft 34 is displaced toward the first side surface S1 of the engine 1 (when displaced in a direction away from the actuator 32), the maximum valve lift amount of the second bank 12B is reduced. Change direction. On the contrary, when the control shaft 34 is displaced toward the second side surface S2 of the engine 1 (when the control shaft 34 is displaced toward the actuator 32), the maximum valve lift amount of the second bank 12B is changed.

  When the electronic control unit 9 detects a request for changing the maximum valve lift, the control shaft 34 of the first variable valve mechanism 3A and the control shaft 34 of the second variable valve mechanism 3B are connected to the respective variable valve mechanisms. By displacing the actuator 32 in the opposite direction with respect to the reference, the maximum valve lift amount is changed in the same direction (the direction in which the maximum valve lift amount increases or decreases) in the first bank 12A and the second bank 12B.

<Valve lift mode by variable valve mechanism>
With reference to FIGS. 13 and 14, the operation state of each variable valve mechanism 3A, 3B when the maximum valve lift amount of the intake valve 21 of each bank 12A, 12B is set to the maximum lift amount LMAX will be described.

  FIG. 13 shows the state of the first variable valve mechanism 3A when the maximum valve lift amount of the intake valve 21 of the first bank 12A is set to the maximum lift amount LMAX. At this time, the control shaft 34 is in a state of being moved in the direction away from the actuator 32 to the maximum (the direction of the first side surface S1 of the engine 1).

  FIG. 14 shows the state of the second variable valve mechanism 3B when the maximum valve lift amount of the intake valve 21 of the second bank 12B is set to the maximum lift amount LMAX. At this time, the control shaft 34 is in a state of moving in the direction approaching the actuator 32 to the maximum (in the direction of the second side surface S2 of the engine 1).

  As shown in FIGS. 13A and 14A, when the base circle portion of the intake cam 25 is in contact with the roller 42E of the input arm 42, the roller 71R of the roller rocker arm 71 is moved to the base circle of the housing 43A. It is in contact with the part. Therefore, the intake valve 21 is maintained in a state where the lift amount is “0” (a state where the intake port 14P of the engine 1 is closed).

  When the roller 42E of the input arm 42 is pushed down through the lift portion of the intake cam 25 as the intake camshaft 23 rotates, the input arm 42 is moved relative to the rocker shaft 33 with reference to FIGS. 13 (a) and 14 (a). Is rotated counterclockwise (in the direction of the arrow). As a result, the slider gear 41 and the output arm 43 are rotated together.

  Accordingly, the cam surface 43D formed on the nose 43C of the output arm 43 is brought into contact with the roller 71R of the roller rocker arm 71, and the roller 71R is pushed down by the pressing of the cam surface 43D.

  As shown in FIGS. 13B and 14B, when the roller 71R of the roller rocker arm 71 is pressed through the cam surface 43D, the roller rocker arm 71 is centered on the contact portion with the lash adjuster 72. By swinging, the intake valve 21 is opened.

  In this operating state, since the relative phase difference between the roller 42E of the input arm 42 and the nose 43C of the output arm 43 around the axis of the rocker shaft 33 is maximum, the intake cam 25 maximizes the roller 42E. The displacement amount of the roller 71R of the roller rocker arm 71 when pushed down to the maximum is the largest. As a result, the intake valve 21 is opened and closed with the largest valve operating angle and valve lift.

  With reference to FIGS. 15 and 16, the operation states of the variable valve mechanisms 3A and 3B when the maximum valve lift amount of the intake valves 21 of the banks 12A and 12B is set to the minimum lift amount LMIN will be described.

  FIG. 15 shows the state of the first variable valve mechanism 3A when the maximum valve lift amount of the intake valve 21 of the first bank 12A is set to the minimum lift amount LMIN. At this time, the control shaft 34 is in a state of moving in the direction approaching the actuator 32 to the maximum (the direction of the second side surface S2 of the engine 1).

  FIG. 16 shows the state of the second variable valve mechanism 3B when the maximum valve lift amount of the intake valve 21 of the second bank 12B is set to the minimum lift amount LMIN. At this time, the control shaft 34 is in a state of being moved in the direction away from the actuator 32 to the maximum (in the direction of the first side face S1 of the engine 1).

  As shown in FIGS. 15A and 16A, when the base circle portion of the intake cam 25 is in contact with the roller 42E of the input arm 42, the contact position of the roller 71R in the output arm 43 is the maximum. Until the cam surface 43D. When the roller 42E of the input arm 42 is pushed down through the lift portion of the intake cam 25 by the rotation of the intake cam shaft 23, the output arm 43 is rotated integrally with the input arm 42.

  However, in this case, the output arm 43 until the pressing of the roller 71R of the roller rocker arm 71 by the cam surface 43D is started by the amount that the contact position of the roller 71R in the output arm 43 is far from the cam surface 43D to the maximum. Is larger than that shown in FIGS. 13 and 14. Further, when the roller 42E of the input arm 42 is pushed down through the lift portion of the intake cam 25, the range of the cam surface 43D that comes into contact with the roller 71R is reduced to only a part of the base end side of the nose 43C. For this reason, the rocking amount of the roller rocker arm 71 corresponding to the depression of the roller 42E by the lift portion of the intake cam 25 becomes small.

  As shown in FIGS. 15B and 16B, when the roller 71R of the roller rocker arm 71 is pressed through the cam surface 43D, the amount of rocking of the roller rocker arm 71 is small, so that the intake valve 21 The valve is opened with a smaller valve lift.

  In this operation state, since the relative phase difference between the roller 42E and the nose 43C around the axis of the rocker shaft 33 is minimum, the displacement of the roller 71R when the intake cam 25 pushes down the roller 42E to the maximum. The amount is the smallest. As a result, the intake valve 21 is opened and closed with the smallest valve operating angle and valve lift.

  In the engine 1, the maximum valve lift amount of the intake valve 21 and the operating angle have a certain correspondence relationship. That is, when the maximum valve lift amount of the intake valve 21 is changed, the operating angle of the intake valve 21 is changed by an amount corresponding to the change amount.

<Maximum valve lift amount change processing>
In the present embodiment, the maximum valve lift amount of the intake valve 21 is changed through the “maximum valve lift amount change process” by the electronic control unit 9.

The “maximum valve lift amount changing process” includes the following processes.
“Lift amount change start determination process” (FIG. 17).
“First variable valve mechanism driving process” (FIG. 18).
“Second variable valve mechanism driving process” (FIG. 19).

With reference to FIGS. 17 to 19, a processing procedure of “maximum valve lift amount change processing” will be described.
This process is executed at predetermined intervals through the electronic control unit 9 during operation of the engine 1.

[Step S100] It is determined whether or not there is a request to change the maximum valve lift amount of the intake valve 21. The request for changing the maximum valve lift amount is detected through a separate process.
[Step S200] The “first variable valve mechanism driving process” is started.

[Step S210] It is determined whether or not the target value of the maximum valve lift amount (target lift amount LTRG) is larger than the current maximum valve lift amount (current lift amount LNOW). The target lift amount LTRG and the current lift amount LNOW are calculated through a separate process.
When the target lift amount LTRG is larger than the current lift amount NLOW (when the maximum valve lift amount needs to be larger than the current lift amount NLOW), the process proceeds to step S220.
When the target lift amount LTRG is smaller than the current lift amount LNOW (when the maximum valve lift amount needs to be smaller than the current lift amount LNOW), the process proceeds to step S230.

  [Step S220] A direction in which the control shaft 34 of the first variable valve mechanism 3A moves away from the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount NLOW (first engine 1). Move to the side S1 direction). That is, the actuator 32 is controlled so as to hold the control shaft 34 of the first variable valve mechanism 3A in the position moved from the current position by the required movement amount MR in the first side surface S1 direction.

  [Step S230] A direction in which the control shaft 34 of the first variable valve mechanism 3A approaches the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount NLOW (second engine 1). Move to the side S2 direction). That is, the actuator 32 is controlled so as to hold the control shaft 34 of the first variable valve mechanism 3A from the current position in the second side surface S2 by the required movement amount MR.

After performing the process of step S220 or step S230, the “first variable valve mechanism driving process” is terminated, and the process proceeds to step S300 of the “lift amount change start determination process”.
[Step S300] The “second variable valve mechanism driving process” is started.

[Step S310] It is determined whether or not the target value of the maximum valve lift amount (target lift amount LTRG) is larger than the current maximum valve lift amount (current lift amount LNOW). The target lift amount LTRG and the current lift amount LNOW are calculated through a separate process.
When the target lift amount LTRG is larger than the current lift amount LNOW (when the maximum valve lift amount needs to be larger than the current lift amount LNOW), the process proceeds to step S320.
When the target lift amount LTRG is smaller than the current lift amount LNOW (when the maximum valve lift amount needs to be smaller than the current lift amount LNOW), the process proceeds to step S330.

  [Step S320] A direction in which the control shaft 34 of the second variable valve mechanism 3B approaches the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount LNOW (second engine 1). Move to the side S2 direction) That is, the actuator 32 is controlled so as to hold the control shaft 34 of the second variable valve mechanism 3B in the position moved from the current position by the required movement amount MR in the direction of the second side surface S2.

  [Step S230] A direction in which the control shaft 34 of the second variable valve mechanism 3B moves away from the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount NLOW (first engine 1). Move to the side S1 direction). That is, the actuator 32 is controlled so as to hold the control shaft 34 of the second variable valve mechanism 3B from the current position to the position moved by the required movement amount MR in the first side surface S1 direction.

After executing the process of step S320 or step S330, the “maximum valve lift amount changing process” is temporarily ended.
<Effect of embodiment>
As described above in detail, according to the variable valve mechanism of the V-type engine according to the first embodiment, the effects listed below can be obtained.

  (1) In the variable valve mechanism of the present embodiment, since the control shaft 34 and the valve lift mechanism 4 having the same structure are employed in the first variable valve mechanism 3A and the second variable valve mechanism 3B, the number is less. The variable valve mechanism 3 can be configured with the number of parts.

  (2) In the variable valve mechanism of the present embodiment, the control shaft 34 of the first variable valve mechanism 3A and the control shaft 34 of the second variable valve mechanism 3B are based on the actuators 32 of the respective variable valve mechanisms. Displacement is made in the opposite direction. Thereby, it becomes possible to ensure an appropriate operation of the variable valve mechanism in each bank of the engine 1.

  (3) In the variable valve mechanism of the present embodiment, the actuator 32 of the first variable valve mechanism 3A and the actuator 32 of the second variable valve mechanism 3B are arranged on the same side surface (second side surface S2) of the engine 1. I am doing so. As a result, workability can be improved during maintenance of the variable valve mechanism 3 or the like.

<Example of change>
In addition, the said 1st Embodiment can also be implemented as the following forms which changed this suitably, for example.

  In the first embodiment, the actuator 32 of the first variable valve mechanism 3A and the actuator 32 of the second variable valve mechanism 3B are arranged on the second side surface S2 of the engine 1, but as follows: It can also be changed. That is, the actuator 32 of the first variable valve mechanism 3A and the actuator 32 of the second variable valve mechanism 3B can be disposed on the first side surface S1 of the engine 1.

  In the first embodiment, the relationship between the moving direction of the control shaft 34 and the changing direction of the maximum valve lift amount in each of the variable valve mechanisms 3A and 3B can be set oppositely.

(Second Embodiment)
A second embodiment of the present invention will be described with reference to FIGS.
The variable valve mechanism of the present embodiment is configured by adding the following changes to the variable valve mechanism of the first embodiment. That is, in the second variable valve mechanism 3B, the mounting position of the actuator 32 with respect to the control shaft 34 is set to the same position as that of the first variable valve mechanism 3A (see FIG. 20).

  In the engine 1, the first variable valve mechanism 3 </ b> A and the second variable valve mechanism 3 </ b> B are disposed in the banks 12 </ b> A and 12 </ b> B so as to be symmetric about the crankshaft 15. Accordingly, the actuator 32 of the first variable valve mechanism 3A is disposed on the second side surface S2, while the actuator 32 of the second variable valve mechanism 3B is disposed on the first side surface S1 (see FIG. 21).

<Change mode of maximum valve lift>
FIG. 21 shows the relationship between the moving direction of the control shaft 34 and the changing direction of the maximum valve lift amount.

  In the first variable valve mechanism 3A, when the control shaft 34 moves toward the first side surface S1 of the engine 1 (when moved away from the actuator 32), the maximum valve lift amount of the first bank 12A increases. Change direction. On the contrary, when the control shaft 34 moves toward the second side surface S2 of the engine 1 (when moving in a direction approaching the actuator 32), the maximum valve lift amount of the first bank 12A changes in a direction that decreases.

  In the second variable valve mechanism 3B, when the control shaft 34 moves toward the second side surface S2 of the engine 1 (when moving away from the actuator 32), the maximum valve lift amount of the second bank 12B increases. Change direction. On the other hand, when the control shaft 34 moves toward the first side surface S1 of the engine 1 (when displaced in a direction approaching the actuator 32), the maximum valve lift amount of the second bank 12B changes.

  When the electronic control unit 9 detects a request for changing the maximum valve lift, the control shaft 34 of the first variable valve mechanism 3A and the control shaft 34 of the second variable valve mechanism 3B are connected to the respective variable valve mechanisms. By displacing the actuator 32 in the same direction with reference to the first bank 12A and the second bank 12B, the maximum valve lift amount is changed in the same direction (direction in which the maximum valve lift amount increases or decreases).

<Maximum valve lift amount change processing>
In the present embodiment, the maximum valve lift amount of the intake valve 21 is changed through the “maximum valve lift amount change process [2]” by the electronic control unit 9.

The “maximum valve lift amount changing process [2]” includes the following processes.
“Lift amount change start determination process [2]” (FIG. 22).
“First variable valve mechanism drive process [2]” (FIG. 23).
“Second variable valve mechanism driving process [2]” (FIG. 24).

With reference to FIGS. 22 to 24, the processing procedure of the “maximum valve lift amount changing process [2]” will be described.
This process is executed at predetermined intervals through the electronic control unit 9 during operation of the engine 1.

[Step T100] It is determined whether or not there is a request to change the maximum valve lift amount of the intake valve 21. The request for changing the maximum valve lift amount is detected through a separate process.
[Step T200] “First variable valve mechanism driving process [2]” is started.

[Step T210] It is determined whether or not the target value of the maximum valve lift amount (target lift amount LTRG) is larger than the current maximum valve lift amount (current lift amount LNOW). The target lift amount LTRG and the current lift amount LNOW are calculated through a separate process.
When the target lift amount LTRG is larger than the current lift amount LNOW (when the maximum valve lift amount needs to be larger than the current lift amount LNOW), the process proceeds to step T220.
When the target lift amount LTRG is smaller than the current lift amount LNOW (when the maximum valve lift amount needs to be smaller than the current lift amount LNOW), the process proceeds to step T230.

  [Step T220] A direction in which the control shaft 34 of the first variable valve mechanism 3A moves away from the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount LNOW (first engine 1). Move to the side S1 direction). That is, the actuator 32 is controlled so as to hold the control shaft 34 of the first variable valve mechanism 3A from the current position to the position moved in the direction of the first side face S1 by the required movement amount MR.

  [Step T230] A direction in which the control shaft 34 of the first variable valve mechanism 3A approaches the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount NLOW (second engine 1). Move to the side S2 direction). That is, the actuator 32 is controlled so as to hold the control shaft 34 of the first variable valve mechanism 3A from the current position to the position moved by the required movement amount MR in the direction of the second side surface S2.

  After executing the process of step T220 or step T230, the “first variable valve mechanism driving process [2]” is terminated, and the process proceeds to step T300 of “lift amount change start determination process [2]”.

[Step T300] “Second variable valve mechanism driving process [2]” is started.
[Step T310] It is determined whether or not the target value of the maximum valve lift amount (target lift amount LTRG) is larger than the current maximum valve lift amount (current lift amount LNOW). The target lift amount LTRG and the current lift amount LNOW are calculated through a separate process.
When the target lift amount LTRG is larger than the current lift amount LNOW (when the maximum valve lift amount needs to be larger than the current lift amount LNOW), the process proceeds to step T320.
When the target lift amount LTRG is smaller than the current lift amount LNOW (when the maximum valve lift amount needs to be smaller than the current lift amount LNOW), the process proceeds to step T330.

  [Step T320] A direction in which the control shaft 34 of the second variable valve mechanism 3B moves away from the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount LNOW (first engine 1). Move to the side S1 direction). That is, the actuator 32 is controlled so as to hold the control shaft 34 of the second variable valve mechanism 3B from the current position in a position moved in the first side face S1 direction by the required movement amount MR.

  [Step T330] A direction in which the control shaft 34 of the second variable valve mechanism 3B approaches the actuator 32 by an amount (required movement amount MR) corresponding to the difference between the target lift amount LTRG and the current lift amount NLOW (second engine 1). Move to the side S2 direction). That is, the actuator 32 is controlled so as to hold the control shaft 34 of the second variable valve mechanism 3B from the current position at the position moved in the second side S2 direction by the required movement amount MR.

After performing the process of step T320 or step T330, the “maximum valve lift amount changing process [2]” is temporarily ended.
<Effect of embodiment>
As described above in detail, according to the variable valve mechanism of the V-type engine according to the second embodiment, in addition to the effects (1) and (2) according to the first embodiment, the following is shown. Effects can be obtained.

  (4) In the variable valve mechanism of the present embodiment, the same structure including the mounting position of the actuator 32 with respect to the control shaft 34 is employed in the first variable valve mechanism 3A and the second variable valve mechanism 3B. ing. As a result, the variable valve mechanism of the V-type engine can be manufactured more efficiently.

  (5) Since the control method of the control shaft 34 in the first variable valve mechanism 3A and the second variable valve mechanism 3B becomes the same by adopting the configuration of the above (4), manufacture of the variable valve mechanism At this time, the control logic of the control shaft 34 can be efficiently constructed.

<Example of change>
In addition, the said 2nd Embodiment can also be implemented as the following forms which changed this suitably, for example.

  In the second embodiment, the actuator 32 of the first variable valve mechanism 3A is disposed on the second side surface S2 of the engine 1, while the actuator 32 of the second variable valve mechanism 3B is disposed on the first side surface S1 of the engine 1. However, it can be changed as follows. That is, the actuator 32 of the first variable valve mechanism 3A can be disposed on the first side surface S1 of the engine 1, while the actuator 32 of the second variable valve mechanism 3B can be disposed on the second side surface S2 of the engine 1. .

  In the second embodiment, the relationship between the moving direction of the control shaft 34 and the changing direction of the maximum valve lift amount in each of the variable valve mechanisms 3A and 3B can be set oppositely.

(Other embodiments)
In addition, elements that can be changed in common with each of the above embodiments are listed below.
In each embodiment described above, the configuration of each variable valve mechanism 3A, 3B is not limited to the illustrated configuration. In short, as long as the slider gear 41 is moved in the axial direction together with the control shaft 34, the input arm 42 and the output arm 43 are relatively rotated, and the maximum valve lift amount of the intake valve 21 is changed through this relative rotation. The configuration of the variable valve mechanism can be changed as appropriate.

  In each of the above embodiments, the present invention is applied to the variable valve mechanism 3 that changes the maximum valve lift amount of the intake valve 21, but the variable valve mechanism that changes the maximum valve lift amount of the exhaust valve 22 The present invention can also be applied.

  In each of the above embodiments, the present invention is applied to the variable valve mechanism of a V-type 8-cylinder engine. However, the present invention is applicable to any variable valve mechanism of any engine as long as it is a variable valve mechanism of a V-type engine. The invention can be applied. Even in such a case, the operational effects according to the operational effects of the above embodiments can be achieved.

The top view which shows the planar structure of the V type engine which mounts the variable valve mechanism about 1st Embodiment which actualized the variable valve mechanism of the V type engine concerning this invention. The top view which shows the planar structure of a 1st bank about the V-type engine carrying the variable valve mechanism of the embodiment. The top view which shows the planar structure of a 2nd bank about the V-type engine carrying the variable valve mechanism of the embodiment. The perspective view which shows the perspective structure of a 1st variable valve mechanism about the variable valve mechanism of the embodiment. The perspective view which shows the perspective structure of a 2nd variable valve mechanism about the variable valve mechanism of the embodiment. The disassembled perspective view which shows the disassembled perspective structure of the valve mechanism main body about the variable valve mechanism of the embodiment. The partially broken perspective view which shows the internal structure of a valve lift mechanism about the variable valve mechanism of the embodiment. The partially broken perspective view which shows the internal structure of a valve lift mechanism about the variable valve mechanism of the embodiment. The disassembled perspective view which shows the assembly structure of the slider gear with respect to the control shaft about the variable valve mechanism of the embodiment. The partially broken perspective view which shows the internal structure of a valve lift mechanism about the variable valve mechanism of the embodiment. Sectional drawing which shows the cross-section along the D1-D1 line | wire of FIG. 1 about the V-type engine of the embodiment. The top view which shows the planar structure of a 1st variable valve mechanism and a 2nd variable valve mechanism about the variable valve mechanism of the embodiment. Sectional drawing which shows the operation | movement aspect of a 1st variable valve mechanism when the maximum valve lift amount is set to the largest lift amount about the variable valve mechanism of the embodiment. Sectional drawing which shows the operation | movement aspect of a 2nd variable valve mechanism when the maximum valve lift amount is set to the largest lift amount about the variable valve mechanism of the embodiment. Sectional drawing which shows the operation | movement aspect of a 1st variable valve mechanism when the maximum valve lift amount is set to the smallest lift amount about the variable valve mechanism of the embodiment. Sectional drawing which shows the operation | movement aspect of a 2nd variable valve mechanism when the maximum valve lift amount is set to the smallest lift amount about the variable valve mechanism of the embodiment. 6 is a flowchart showing a processing procedure of “lift amount change start determination processing” executed through the electronic control unit in the embodiment. 6 is a flowchart showing a processing procedure of “first variable valve mechanism driving process” executed through the electronic control unit in the embodiment. 9 is a flowchart showing a processing procedure of “second variable valve mechanism driving process” executed through the electronic control unit in the embodiment. The perspective view which shows the perspective structure of a 2nd variable valve mechanism about 2nd Embodiment which actualized the variable valve mechanism of the V-type engine concerning this invention. The top view which shows the planar structure of a 1st variable valve mechanism and a 2nd variable valve mechanism about the variable valve mechanism of the embodiment. 9 is a flowchart showing a processing procedure of “lift amount change start determination processing [3]” executed through the electronic control unit in the embodiment. The flowchart which shows the process sequence of "1st variable valve mechanism drive process [2]" performed through the electronic controller in the embodiment. The flowchart which shows the process sequence of "2nd variable valve mechanism drive process [2]" performed through the electronic controller in the embodiment. The top view which shows an example of a structure of the variable valve mechanism suitable for V type engine.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Engine, 11 ... Cylinder block, 12A ... 1st bank, 12B ... 2nd bank, 13 ... Cylinder, 14A ... 1st cylinder head, 14B ... 2nd cylinder head, 15 ... Crankshaft, 21 ... Intake valve, 22 DESCRIPTION OF SYMBOLS ... Exhaust valve, 23 ... Intake cam shaft, 24 ... Exhaust cam shaft, 25 ... Intake cam, 26 ... Exhaust cam, 27 ... Intake side partition, 28 ... Exhaust side partition, 29 ... Timing chain, S1 ... First side, S2 ... second side.

  3 ... Variable valve mechanism, 3A ... First variable valve mechanism, 3B ... Second variable valve mechanism, 31 ... Valve mechanism body, 32 ... Actuator, 33 ... Rocker shaft, 33H ... Long hole, 34 ... Control shaft , 34H ... insertion hole.

  4 ... Valve lift mechanism, 41 ... Slider gear, 41A ... Input side helical spline, 41B ... Output side helical spline, 41C ... Through hole, 41D ... Long hole, 42 ... Input arm, 42A ... Housing, 42B ... Helical spline, 42CL ... arm, 42CR ... arm, 42D ... shaft, 42E ... roller, 43 ... output arm, 43A ... housing, 43B ... helical spline, 43C ... nose, 43D ... cam surface, 43E ... bearing part.

71 ... Roller rocker arm, 71T ... Tappet side end, 71R ... Roller, 72 ... Rush adjuster, 73 ... Tappet, 74 ... Valve spring, 75 ... Spring
9: Electronic control device.

  LMIN ... minimum lift amount, LMAX ... maximum lift amount, LTRG ... target lift amount, LNOW ... current lift amount, MR ... required movement amount.

Claims (4)

A first variable valve mechanism for changing the maximum valve lift amount of the engine valve of the first bank and the engine valve of the second bank applied to a V-type engine having an engine valve and a camshaft for opening and closing the engine valve. A second variable valve mechanism for changing the maximum valve lift amount of
The first variable valve mechanism and the second variable valve mechanism include a control shaft that is movable in the axial direction, a valve lift mechanism that lifts the engine valve, and an actuator that displaces the control shaft in the axial direction. It is configured with
The valve lift mechanism is provided on the control shaft and is movable in the axial direction in conjunction with the control shaft; an input arm provided on the slider gear and driven by the camshaft; An output arm provided on the slider gear for lifting the engine valve;
A variable valve mechanism for a V-type engine that changes the maximum valve lift amount of the engine valve by rotating the input arm and the output arm relative to each other through movement of the control shaft;
A control shaft and a valve lift mechanism having the same structure are employed in the first variable valve mechanism and the second variable valve mechanism,
Setting the mounting position of the actuator to the control shaft on the opposite side in the first variable valve mechanism and the second variable valve mechanism;
When changing the maximum valve lift amount of the V-type engine, the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are moved in opposite directions with reference to the actuators of the respective variable valve mechanisms. A variable valve mechanism for a V-type engine, characterized by comprising control means for displacement.   A V-type configured to include a first variable valve mechanism for changing the maximum valve lift amount of the engine valve of the first bank and a second variable valve mechanism for changing the maximum valve lift amount of the engine valve of the second bank. Equipped with a variable valve mechanism for the engine,
  The first variable valve mechanism and the second variable valve mechanism include a control shaft that is movable in the axial direction, a valve lift mechanism that lifts the engine valve, and an actuator that displaces the control shaft in the axial direction. It is configured with
  The valve lift mechanism is provided on the control shaft and is movable in the axial direction in conjunction with the control shaft, and an input provided on the slider gear and driven by a camshaft of the engine valve. An arm and an output arm that is provided on the slider gear and lifts the engine valve;
  A V-type engine that changes the maximum valve lift of the engine valve by relatively rotating the input arm and the output arm through movement of the control shaft;
  A control shaft and a valve lift mechanism having the same structure are employed in the first variable valve mechanism and the second variable valve mechanism,
  For the actuator of the first variable valve mechanism and the actuator of the second variable valve mechanism, these actuators are arranged on the same side of the V-type engine,
  When changing the maximum valve lift amount of the V-type engine, the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are moved in opposite directions with reference to the actuators of the respective variable valve mechanisms. Equipped with displacement control means
  V-type engine characterized by this.   A variable valve mechanism for a V-type engine that changes the maximum valve lift amount of the engine valve by displacing the slider gear of the valve lift mechanism together with the control shaft through an actuator,
  A control shaft and a valve having the same structure in the first variable valve mechanism for changing the maximum valve lift amount of the engine valve of the first bank and the second variable valve mechanism for changing the maximum valve lift amount of the engine valve of the second bank Adopt lift mechanism,
  Setting the mounting position of the actuator to the control shaft on the opposite side in the first variable valve mechanism and the second variable valve mechanism;
  When changing the maximum valve lift amount of the V-type engine, the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are moved in opposite directions with reference to the actuators of the respective variable valve mechanisms. Equipped with displacement control means
  A variable valve mechanism for a V-type engine.   A V-type configured to include a first variable valve mechanism for changing the maximum valve lift amount of the engine valve of the first bank and a second variable valve mechanism for changing the maximum valve lift amount of the engine valve of the second bank. In a V-type engine that includes a variable valve mechanism of an engine, and each of these variable valve mechanisms changes a maximum valve lift amount by displacing a slider gear of the valve lift mechanism together with a control shaft through an actuator.
  A control shaft and a valve lift mechanism having the same structure are employed in the first variable valve mechanism and the second variable valve mechanism,
  For the actuator of the first variable valve mechanism and the actuator of the second variable valve mechanism, these actuators are arranged on the same side of the V-type engine,
  When changing the maximum valve lift amount of the V-type engine, the control shaft of the first variable valve mechanism and the control shaft of the second variable valve mechanism are moved in opposite directions with reference to the actuators of the respective variable valve mechanisms. Equipped with displacement control means
  V-type engine characterized by this.

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