JP4150920B2 - Valve train with internal cylinder mechanism for internal combustion engine - Google Patents

Description

  The present invention relates to a valve operating apparatus with a cylinder resting mechanism of an internal combustion engine (hereinafter referred to as an engine).

In order to realize an optimum engine output characteristic according to the operation region, various engines have been proposed in which the intake / exhaust valve opening period, the lift amount, and the like are switched (for example, Patent Document 1 and Patent). Reference 2).
In the engine described in Patent Document 1, a driven rocker arm supported on a rocker shaft is swung by a first cam to open and close the intake valve, and a drive rocker arm supported on the rocker shaft adjacent to the driven rocker arm is provided. The second cam is swung. In the cylinder formed on the driven rocker arm, a piston is slidably disposed by hydraulic pressure, and on the driving rocker arm, an engaging protrusion that can be engaged with the piston is formed along with the swing.

  For example, in the low engine speed range, the piston of the driven rocker arm is switched to the lower position and the engagement protrusion of the drive rocker arm is swung to drive the intake valve to open and close following the shape of the first cam by the driven rocker arm. In the high rotation range of the engine, the piston of the driven rocker arm is switched to the upper position and pressed by the engagement protrusion of the drive rocker arm, so that the driven rocker arm is swung together with the drive rocker arm to follow the shape of the second cam. Open and close the valve.

  On the other hand, in the engine described in Patent Document 2, the first rocker arm corresponding to the low speed cam, the second rocker arm corresponding to the high speed cam, and the third rocker arm corresponding to the pause cam are swung on the intake side rocker shaft. A pair of intake valves are driven to open and close in linkage with the first and third rocker arms. A switching pin is provided in each rocker arm so as to be slidable in the axial direction of the rocker shaft by hydraulic pressure, and each rocker arm is connected and released according to the sliding position of the switching pin.

For example, in a low engine speed range, the connection of each rocker arm is released by a switching pin, and one intake valve is driven to open and close following the low speed cam via the first rocker arm, and the other intake valve is connected via the third rocker arm. Is substantially closed by the rest cam. Also, in the high engine speed range, each rocker arm is connected by a switching pin, and all the rocker arms are integrally swung by a high-speed cam, and both intake valves are driven to open and close following the high-speed cam.
JP 2001-41017 A JP 2002-227624 A

  As described above, the engine disclosed in Patent Document 1 performs switching in two operating states in which the intake valve is driven to open and close by the first or second cam. In the engine described in Patent Document 2, intake is performed by the low speed cam and the pause cam. Switching is performed in two operating states, in which the valve is driven to open and close, or the intake valve is driven to open and close with a high-speed cam. For example, in addition to these functions, a cylinder resting function for resting a specific cylinder is added. There is a request.

However, in order to add the cylinder resting function, it is necessary to add a mechanism for pausing the rocker arm (the driven rocker arm in Patent Document 1 and the first and third rocker arms in Patent Document 2) linked to the intake valve. In the technologies of the above-mentioned patent documents, there is a problem that the whole valve operating device becomes larger as the configuration of the valve operating device becomes complicated.
An object of the present invention is to provide a valve operating apparatus with a cylinder resting mechanism for an internal combustion engine that can efficiently arrange the structure of the valve operating apparatus including the cylinder resting mechanism and achieve a compactness of the entire valve operating mechanism. There is.

In order to achieve the above object, the invention according to claim 1 is directed to a first rocker arm whose front end is linked to one of a pair of intake valves or exhaust valves, and is swingably supported on a rocker shaft; A second rocker arm that is swingably supported on the rocker shaft adjacent to one side and driven by the first cam, and a rocker shaft that is swingably supported adjacent to the other side of the first rocker arm. A third rocker arm driven by a second cam having a cam shape different from that of the first cam, a switching mechanism for switching presence / absence of linkage between the first rocker arm and the second or third rocker arm, and control means for controlling the switching, switching mechanism includes a first piston which is slidably mounted on the first cylinder formed in the first rocker arm, to-the first cylinder to the first rocker arm A second piston which is slidably mounted in the second cylinder is formed adjacent to the axial direction of the rocker shaft Te, it is extended to the first piston side along the second rocker arm to the axis of the rocker shaft A first engagement projection provided with an end bent in an L shape so as to be engageable with the first piston, and an L shape extending from the third rocker arm along the axis of the rocker shaft toward the second piston. The tip bent into a shape is made up of a second engagement protrusion provided so as to be engageable with the second piston, and the positions of the first and second pistons are respectively the engagement positions with respect to the first and second engagement protrusions. It switches between the non-engagement positions.

  Accordingly, by switching the positions of the first and second pistons of the switching mechanism between the engaged position and the non-engaged position, the first rocker arm can be switched between the presence or absence of linkage with the second rocker arm or the third rocker arm. When linked to the second rocker arm, one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam, and when linked to the third rocker arm, the intake valve or When one of the exhaust valves is driven to open and close and is not linked to any of the second and third rocker arms, one of the intake valve and the exhaust valve is held closed, and the operating state of the internal combustion engine is switched according to the above switching.

  The second and third rocker arms are arranged on both sides of the first rocker arm, and the first and second rocker arms are extended from the second and third rocker arms with respect to the first and second pistons provided in the first rocker arm. Since the two engaging protrusions are engaged, the members such as the first and second pistons, the second and third rocker arms, etc. are concentrated in one place with the first rocker arm as the center and are efficiently arranged.

According to a second aspect of the present invention, in the first aspect, the control means includes a first mode in which the first rocker arm is driven by the first cam, a second mode in which the first rocker arm is driven by the second cam, The switching of the switching mechanism is controlled so that any one of the third modes in which the first rocker arm is inoperative is set.
Accordingly, in the first mode, the first rocker arm is driven by the first cam, and one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam. In the second mode, the first rocker arm is Driven by the second cam, one of the intake valve and the exhaust valve is driven to open and close following the shape of the second cam. In the third mode, the first rocker arm is deactivated and the intake valve or the exhaust valve is Keep one closed.

  According to a third aspect of the present invention, in the second aspect of the present invention, in the second aspect, in the first mode, the control means engages the first piston with respect to the first engagement protrusion and the second piston with respect to the second engagement protrusion. In the second mode, at least the second piston is engaged with the second engagement protrusion, and in the third mode, the first piston is not engaged with the first engagement protrusion in the second mode. The switching of the switching mechanism is controlled so that the second piston is in the non-engaging position with respect to the second engaging protrusion.

  Therefore, in the first mode, the first piston is in the engaged position with respect to the first engaging protrusion and the second piston is in the non-engaging position with respect to the second engaging protrusion. In cooperation with the second rocker arm, one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam. In the second mode, since at least the second piston is in the engagement position with respect to the second engagement protrusion, the first rocker arm cooperates with the third rocker arm to follow the shape of the second cam. Open or close one of the intake and exhaust valves. In the third mode, since the first piston is in the non-engagement position with respect to the first engagement protrusion and the second piston is in the non-engagement position with respect to the second engagement protrusion, the first rocker arm is in the non-engagement position. Actuated to hold one of the intake and exhaust valves closed.

According to a fourth aspect of the present invention, a distal end is linked to one of a pair of intake valves or exhaust valves, and is adjacent to one side of the first rocker arm, and a first rocker arm swingably supported on the first rocker shaft. A second rocker arm that is swingably supported on the first rocker shaft and driven by the first cam, and is pivotally supported on the first rocker shaft adjacent to the other side of the first rocker arm, A third rocker arm driven by a second cam having a cam shape different from that of the first cam, and a second rocker whose front end is linked to the other of the pair of intake valves or exhaust valves and arranged in parallel with the first rocker shaft. A fourth rocker arm swingably supported on the rocker shaft; a fifth rocker arm swingably supported on the second rocker shaft adjacent to the fourth rocker arm and driven by a third cam; First b A first switching mechanism for switching presence / absence of linkage between the arm and the second or third rocker arm, a second switching mechanism for switching presence / absence of linkage between the fourth rocker arm and the fifth rocker arm, and first and second switching mechanisms. and control means for controlling the switching, the first switching mechanism, and a first piston which is slidably mounted on the first cylinder formed in the first rocker arm, to the first cylinder to the first rocker arm A second piston slidably mounted on a second cylinder formed adjacent to the first rocker shaft in the axial direction, and from the second rocker arm to the first piston side along the axis of the first rocker shaft. A first engagement protrusion, which is extended and bent in an L-shape so as to be engageable with the first piston, and is extended from the third rocker arm so as to be engageable with the second piston. Second engagement The first and second piston positions are switched between an engagement position and a non-engagement position with respect to the first and second engagement protrusions, respectively, and a second switching mechanism is formed on the fourth rocker arm. a third piston slidably mounted play in the third cylinder which is, the third piston is extended is bent in an L-shape in side tip from the fifth rocker arm along the axis of the second rocker shaft The third piston includes a third engagement protrusion provided to be engageable with the third piston, and switches the position of the third piston between an engagement position and a non-engagement position with respect to the third engagement protrusion.

  Therefore, when the positions of the first and second pistons of the first switching mechanism are switched between the engaged position and the non-engaged position, the first rocker arm determines whether or not it is linked to the second rocker arm or the third rocker arm. When switched and linked to the second rocker arm, one of the intake and exhaust valves is driven to open and close following the shape of the first cam, and when linked to the third rocker arm, the intake air follows the shape of the second cam. One of the valve and the exhaust valve is driven to open and close, and when it is not linked to any of the second and third rocker arms, one of the intake valve or the exhaust valve is held closed.

  Further, by switching the position of the third piston of the second switching mechanism between the engagement position and the non-engagement position, the fourth rocker arm can be switched between linkage with the fifth rocker arm, and the fifth rocker arm. Is linked to the third cam, the other of the intake and exhaust valves is driven to open and close, and when not linked to the fifth rocker arm, the other of the intake and exhaust valves is held closed. Therefore, the operating state of the internal combustion engine is switched according to the above switching.

  The first and second rocker arms are arranged on both sides of the first rocker arm, and the first and second rocker arms are extended from the second and third rocker arms with respect to the first and second pistons attached to the first rocker arm. Because of the configuration for engaging the second engagement protrusion, each member such as the first and second pistons, the second and third rocker arms, etc. is concentrated efficiently in one place with the first rocker arm as the center, On the other hand, a fifth rocker arm is disposed adjacent to the fourth rocker arm, and a third engagement protrusion extending from the fifth rocker arm is engaged with a third piston provided on the fourth rocker arm. Therefore, each member such as the third piston and the fifth rocker arm is concentrated at one place with the fourth rocker arm as a center and is efficiently arranged.

  According to a fifth aspect of the present invention, in the fourth aspect, the control means includes a first mode in which the first rocker arm is driven by the first cam and the fourth rocker arm is driven by the third cam. Any one of the second mode in which the rocker arm is driven by the second cam and the fourth rocker arm is driven by the third cam, and the third mode in which the first and fourth rocker arms are inoperative The switching of the first and second switching mechanisms is controlled so that

  Accordingly, in the first mode, the first rocker arm is driven by the first cam, and one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam, and the fourth rocker arm is in the third mode. Driven by the cam, the other of the intake valve and the exhaust valve is driven to open and close following the shape of the third cam. In the second mode, the first rocker arm is driven by the second cam, and either the intake valve or the exhaust valve is driven to open and close following the shape of the second cam, and the fourth rocker arm is driven by the third cam. Driven to open and close the other of the intake valve and the exhaust valve according to the shape of the third cam. In the third mode, the first and fourth rocker arms are deactivated to hold both the intake valve and the exhaust valve closed.

  According to a sixth aspect of the present invention, in the fifth aspect, in the first mode, the control means is configured so that the first piston is engaged with the first engagement protrusion and the second piston is the second engagement protrusion in the first mode. On the other hand, the non-engagement position, and the third piston is set to the engagement position with respect to the third engagement protrusion. In the second mode, at least the second piston is engaged with the second engagement protrusion, and the third piston The piston is set to the engagement position with respect to the third engagement protrusion, and in the third mode, the first piston is not engaged with the first engagement protrusion, and the second piston is not engaged with the second engagement protrusion. The switching of the first and second switching mechanisms is controlled so that the engagement position and the third piston are in the disengagement position with respect to the third engagement protrusion.

  Therefore, in the first mode, the first piston is in the engaged position with respect to the first engaging protrusion and the second piston is in the non-engaging position with respect to the second engaging protrusion. In cooperation with the second rocker arm, one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam, and the third piston is brought into the engagement position with respect to the third engagement protrusion. The fourth rocker arm cooperates with the fifth rocker arm to drive the other of the intake valve and the exhaust valve in accordance with the shape of the third cam. In the second mode, since at least the second piston is in the engagement position with respect to the second engagement protrusion, the first rocker arm cooperates with the third rocker arm to follow the shape of the second cam. Thus, one of the intake valve and the exhaust valve is driven to open and close, and the third piston is brought into the engagement position with respect to the third engagement protrusion, so that the fourth rocker arm cooperates with the fifth rocker arm to The other of the intake valve and the exhaust valve is driven to open and close following the shape of the cam. In the third mode, since the first piston is in the non-engagement position with respect to the first engagement protrusion and the second piston is in the non-engagement position with respect to the second engagement protrusion, the first rocker arm is in the non-engagement position. Since the third piston is brought into the non-engagement position with respect to the third engagement protrusion while the intake valve or the exhaust valve is closed by being actuated, the fourth rocker arm is inactivated and the intake air is taken in. Keep the other of the valve or the exhaust valve closed.

  As described above, according to the valve operating apparatus with a cylinder resting mechanism of the internal combustion engine of the present invention, the configuration of the valve operating apparatus including the cylinder resting mechanism is efficiently arranged to achieve a compact valve operating mechanism as a whole. be able to.

Hereinafter, an embodiment of a valve gear with a cylinder resting mechanism of an engine embodying the present invention will be described.
The engine of the present embodiment is configured as a V-type 6-cylinder gasoline engine having four valves per cylinder, and in particular, a high-speed mode that realizes a high engine output, a low-speed mode that corresponds to a normal engine output, and cylinders in one bank are rested. It is configured to be switchable between idle cylinder modes. For this reason, the valve gears of both banks are each provided with a switching mechanism between the low speed mode and the high speed mode, and in addition, the bank on one side is provided with a cylinder resting mechanism. Therefore, first, the configuration of a bank provided with a cylinder resting mechanism (hereinafter referred to as a cylinder resting bank and the opposite side as a non-cylinderless bank) will be described.

《Cylinder Bank》
1 to 8 show the cylinder heads of the idle cylinder bank, FIG. 1 is a plan view showing the cylinder head, FIG. 2 is a partially enlarged plan view showing details of a valve operating system for one cylinder, and FIG. FIG. 4 is a cross-sectional view showing when the low-speed cam and the exhaust cam corresponding to the AA line of FIG. 2 is a cross-sectional view showing the high-speed cam corresponding to the BB line in FIG. 2 when the high-speed cam is at rest, FIG. 6 is a cross-sectional view showing the high-speed cam corresponding to the BB line in FIG. FIG. 8 is a partial enlarged plan view showing a positional relationship between the driven rocker arm and FIG. Here, the top and bottom of FIG. 1 is the front-rear direction of the engine, the right side of the cylinder head corresponds to the intake side, the left side corresponds to the exhaust side, and the cylinder head of the non-cylinder bank is arranged to the right of the cylinder head And

  As shown in FIGS. 2, 3, and 7, one camshaft 2 of the valve operating device is disposed at a substantially right and left center on the cylinder head 1 so as to extend in the front-rear direction. Each journal portion 2a is supported by the head journal portion and is driven to rotate in synchronization with the crankshaft. An intake rocker shaft 3 (first rocker shaft) is disposed on the upper right side of the camshaft 2, and an exhaust rocker shaft 4 (second rocker shaft) is disposed on the upper left side of the camshaft 2, and these rocker shafts are disposed. 3 and 4 are fixed on the cylinder head 1 by bolts 5 in a posture parallel to the camshaft 2.

  Each cylinder is arranged in the front-rear direction along the camshaft 2, and hereinafter, a valve operating device for one cylinder will be described, but the other cylinders have the same configuration. As shown in FIG. 7, between a pair of adjacent journal portions 2a of the camshaft 2, a low-speed intake cam 6 (first cam, hereinafter abbreviated as a low-speed cam), an exhaust cam 7 ( A cam for one cylinder is formed in the order of a third cam), a rest cam 8, and a high speed side intake cam 9 (second cam, hereinafter abbreviated as a high speed cam). Hereinafter, the configuration of the intake side and exhaust side valve operating devices driven by these cams 6 to 9 and the configuration of the oil passage for switching the valve operating devices will be sequentially described.

<Intake side valve operating device>
As shown in FIGS. 2 and 3, a bearing hole 12 a formed in the boss portion 12 of the intake driven rocker arm 11 (first rocker arm) is fitted into the intake rocker shaft 3, and the intake driven rocker arm is centered on the intake rocker shaft 3. 11 as a whole can swing. Two valve-side arm portions 13 having a bifurcated shape extend from the boss portion 12 toward the right, and an adjustment bolt 14 for adjusting a valve clearance is provided at the tip of each valve-side arm portion 13. Each corresponds to an intake valve (not shown) on the cylinder head 1.

  As shown in FIGS. 7 and 8, one cam side arm portion 15 extends from the boss portion 12 toward the left, and the sliding contact portion 15 a formed at the tip of the cam side arm portion 15 has the above-mentioned rest. It abuts on the cam 8. When the intake driven rocker arm 11 swings clockwise from the state where the sliding contact portion 15a of the cam side arm portion 15 is in contact with the rest cam 8, the intake valve is moved via the adjustment bolt 14 of the valve side arm portion 13. The valve is opened against the valve spring. Hereinafter, the swinging direction of the members constituting the intake side valve operating device such as the intake driven rocker arm 11, the low-speed drive rocker arm 32 and the high-speed drive rocker arm 38, which will be described later, is the valve opening direction clockwise and the counterclockwise valve closing. Defined as direction.

  As shown in FIGS. 2, 3, and 5, a cylindrical low-speed cylinder portion 16 and a high-speed cylinder portion 17 are integrally provided on the boss portion 12 of the intake driven rocker arm 11. The low-speed cylinder portion 16 is formed with a small-diameter lower cylinder 16a (first and third cylinders) having a circular cross section and a large-diameter upper cylinder 16b (first and third cylinders) which are continuously formed in the vertical direction. The lower end of the cylinder 16a opens to the inner peripheral surface of the bearing hole 12a of the boss portion 12, and the upper end of the upper cylinder 16b opens upward.

  A lower piston 18a (first and third pistons) is disposed in the lower cylinder 16a, and the lower piston 18a is in a state where its rotation about the axis of the lower cylinder 16a is restricted by a restriction pin (not shown). It can slide up and down in 16a. An upper piston 18b (first and third pistons) is disposed in the upper cylinder 16b and can slide in the upper and lower directions in the upper cylinder 16b. The upper piston 18b is made of a material having higher rigidity than the lower piston 18a.

  A lid 19 is press-fitted into the opening of the upper cylinder 16b and is prevented from coming off by a snap ring 20. A compression spring 21 is interposed between the lid 19 and the upper piston 18b in the upper cylinder 16b. As shown in FIG. 3, the lower piston 18 a and the upper piston 18 b are always urged downward by the compression spring 21, and a lower position where the lower surface of the lower piston 18 a is in contact with the outer peripheral surface of the intake rocker shaft 3 ( (Engaged position). As shown in FIG. 4, when the lower piston 18a and the upper piston 18b slide upward in the cylinders 16a and 16b against the compression spring 21 from the lower position, the upper portion of the upper piston 18b It contacts the lower part and is switched to the upper position (non-engagement position).

  An operation window 22 is formed on the left side of the low speed cylinder 16, that is, the side facing the camshaft 2, while a relief 23 is recessed on the left side of the lower piston 18 a. In the upper position of the pistons 18a and 18b shown in FIG. 4, the escape portion 23 of the lower piston 18a is exposed to the left through the operation window 22, and in the lower position shown in FIG. Thus, the outer peripheral surface of the upper piston 18b is exposed to the left.

  On the other hand, as shown in FIG. 5, a cylinder 17a (second cylinder) having a circular cross section is formed in the high speed cylinder portion 17 in the vertical direction, and the lower end of the cylinder 17a is inside the bearing hole 12a of the boss portion 12. It opens to the peripheral surface, and the upper end of the cylinder 17a opens upward. A piston 25 (second piston) is disposed in the cylinder 17a, and the piston 25 slides up and down in the cylinder 17a in a state where the rotation about the axis of the cylinder 17a is restricted by a restriction pin (not shown). Can do. The same material as that of the upper piston 18b of the low speed cylinder portion 17 is applied to the piston 25, and the same rigidity is ensured.

  Similar to the low-speed cylinder portion 16, a lid body 27 is fixed to the opening of the cylinder 17 a by a snap ring 26, and a compression spring 28 is interposed between the lid body 27 and the piston 25. As shown in FIG. 5, the piston 25 is always urged downward by the compression spring 28 and is held at a lower position (non-engagement position) in which the lower surface is in contact with the outer peripheral surface of the intake rocker shaft 3. . Further, as shown in FIG. 6, when the piston 25 slides upward in the cylinder 17a against the compression spring 28 from the lower position, the upper part of the piston 25 abuts the lower part of the lid 27 and the upper position ( (Engagement position).

  An operation window 29 is formed on the left side surface of the high-speed cylinder portion 17, while a relief portion 30 is recessed on the left side surface of the piston 25, and the operation window 29 is provided at a position below the piston 25 shown in FIG. The exposed portion 30 of the piston 25 is exposed to the left, and the outer peripheral surface of the piston 25 is exposed through the operation window 29 at the upper position shown in FIG. The compression spring 28 of the high-speed cylinder portion 17 has a smaller overall length than the compression spring 21 of the low-speed side cylinder 16, and has a long overall length so as to ensure a biasing force to the predetermined piston 25. It is disposed offset from the axis of the portion 17 and is held in a spring hole 25a formed on the piston 25 in order to prevent bending due to compression.

  On the other hand, as shown in FIGS. 2 and 3, a boss portion 33 of a low-speed drive rocker arm 32 (second rocker arm) is swingably supported on the front side of the intake driven rocker arm 11 on the intake rocker shaft 3. On the right side of the boss portion 33, a biasing portion 33a protrudes downward, and the entire low-speed drive rocker arm 32 is biased in the valve closing direction by a biasing spring (not shown) connected to the biasing portion 33a. As shown in FIG. 7, a roller 35 provided on the left side is brought into contact with the low-speed cam 6.

  From the upper position of the roller 35 of the low-speed drive rocker arm 32, the operation arm portion 36 (first and third engagement protrusions) extends rearward along the axis of the camshaft 2, and the tip of the operation arm portion 36 is on the right side. It is bent in an L shape toward the intake driven rocker arm 11 located on the side, and corresponds to the operation window 22 of the low speed cylinder portion 16. The low-speed drive rocker arm 32 swings following the shape of the low-speed cam 6 while rolling the roller 35 on the rotating low-speed cam 6, and in the base circle section of the low-speed cam 6 (section where the lift amount is 0), FIG. As shown by a solid line, the valve swings in the valve closing direction to disengage the tip of the operation arm 36 from the operation window 22 to the left and opens in the lift section of the low-speed cam 6 as shown by a two-dot chain line in FIG. The tip of the operation arm 36 is inserted into the operation window 22 by swinging in the valve direction.

  A boss portion 39 of a high-speed drive rocker arm 38 (third rocker arm) is swingably supported on the rear side of the intake driven rocker arm 11 on the intake rocker shaft 3, and is driven at high speed similarly to the low-speed drive rocker arm 32. The rocker arm 38 is urged in the valve closing direction by an urging spring (not shown) via an urging portion 39a, and a roller 40 provided on the left side is brought into contact with the high-speed cam 9 as shown in FIG. .

  From the upper position of the roller 40 of the high-speed drive rocker arm 38, the operation arm portion 41 (second engagement protrusion) extends forward along the axis of the camshaft 2, and the tip of the operation arm portion 41 is positioned on the right side. It is bent in an L-shape toward the intake driven rocker arm 11 and corresponds to the operation window 29 of the high-speed cylinder portion 17. Like the low-speed drive rocker arm 32, the high-speed drive rocker arm 38 swings following the shape of the high-speed cam 9 while rolling the roller 40 on the high-speed cam 9. In the base circle section of the high-speed cam 9, a solid line in FIG. As shown in FIG. 5, it swings in the valve closing direction to disengage the tip of the operation arm 41 to the left from the operation window 29, and in the lift section of the high-speed cam 9, in the valve opening direction as shown by a two-dot chain line in FIG. It swings and the tip of the operation arm 41 is inserted into the operation window 29.

  Here, in the present embodiment, the lower and lower pistons 18a and 18b of the low-speed cylinder unit 16, the piston 25 of the high-speed cylinder unit 17, the operation arm unit 36 of the low-speed drive rocker arm 32, and the operation arm unit 41 of the high-speed drive rocker arm 38 are used. A 1-switching mechanism M1 is configured.

<Exhaust valve operating device>
On the other hand, the exhaust-side valve operating device omits the high-speed cylinder portion 17 of the intake driven rocker arm 11 and the corresponding high-speed drive rocker arm 38 from the intake-side valve operating device, and the configuration will be described below.

  As shown in FIGS. 2 and 3, the exhaust rocker shaft 4 is fitted with a bearing hole 44 a of a boss portion 44 of an exhaust driven rocker arm 43 (fourth rocker arm), and the exhaust driven rocker arm 43 as a whole centering on the exhaust rocker shaft 4. Can swing. Two valve-side arm portions 45 having a bifurcated shape extend from the boss portion 44 toward the left, and the adjustment bolts 46 provided at the tips of the valve-side arm portions 45 are respectively provided on the cylinder head 1. This corresponds to an exhaust valve (not shown).

  As shown in FIG. 7, the boss portion 12 of the intake driven rocker arm 11 and the boss portion 44 of the exhaust driven rocker arm 43 are arranged on the left and right sides with the camshaft 2 interposed therebetween, and both boss portions in the axial direction of the camshaft 2. A part of 12, 44 is polymerized with each other. As shown in FIGS. 7 and 8, one cam side arm portion 47 extends rightward from the boss portion 44, and the sliding contact portion 47a formed at the tip of the cam side arm portion 47 It is in contact with the rest cam 8 while avoiding interference with the sliding contact portion 15a on the driven rocker arm 11 side.

  When the exhaust driven rocker arm 43 swings counterclockwise from this state, the exhaust valve is opened against the valve spring via the adjustment bolt 46 of the valve side arm portion 45. Hereinafter, the swinging direction of the members constituting the exhaust side valve operating device such as the exhaust driven rocker arm 43 and the exhaust driving rocker arm 49 described later is defined as the valve opening direction, and the clockwise direction as the valve closing direction.

2 and 3, a cylindrical cylinder portion 48 is integrally provided on the boss portion 44 of the exhaust driven rocker arm 43. As shown in FIG. 3, the cylinder portion 48 is on the intake driven rocker arm 11 side. The low-speed cylinder portion 16 has the same configuration that is symmetrical to the left and right.
Therefore, the same member number as that of the low-speed cylinder part 16 is attached and the cylinder part 48 is outlined. The lower piston 18a is provided in the lower cylinder 16a of the cylinder part 48, and the upper piston 18b is provided in the upper cylinder 16b. It is slidably arranged in the vertical direction. These pistons 18a and 18b are urged downward by the compression spring 21. At the lower position shown in FIG. 3, the lower surface of the lower piston 18a abuts against the outer peripheral surface of the exhaust rocker shaft 4, and the operation window 22 of the cylinder portion 48 is used. The outer peripheral surface of the upper piston 18b is exposed to the right, and the escape portion 23 of the upper piston 18a is exposed to the right from the operation window 22 at the upper position shown in FIG.

The members such as the lower piston 18 a, the upper piston 18 b, the lid 19, and the compression spring 21 that are housed in the exhaust-side cylinder portion 48 are shared with the members that are housed in the intake-side low-speed cylinder portion 16. It has become.
On the other hand, as shown in FIGS. 2 and 3, an exhaust drive rocker arm 49 (fifth rocker arm) is swingably supported on the front side of the exhaust driven rocker arm 43 on the exhaust rocker shaft 4, and the exhaust drive rocker arm 49 is inhaled. It has the same configuration symmetrical with respect to the low-speed drive rocker arm 32 on the side.

  Therefore, when the same member number as the low-speed drive rocker arm 32 is attached and the outline of the exhaust drive rocker arm 49 is described, the exhaust drive rocker arm 49 is biased in the valve closing direction by a biasing spring (not shown) via the biasing portion 33a. Thus, the roller 35 provided on the right side is brought into contact with the exhaust cam 7. An operation arm portion 36 extends rearward from the exhaust drive rocker arm 49, and the distal end of the operation arm portion 36 is bent in an L shape toward the left side so as to be connected to the operation window 22 of the cylinder portion 48 of the exhaust driven rocker arm 43. It corresponds. The exhaust drive rocker arm 49 swings following the shape of the exhaust cam 7 while rolling the roller 35. In the base circle section of the exhaust cam 7, it swings in the valve closing direction as shown by the solid line in FIG. The tip of the arm portion 36 is moved to the right from the operation window 22, and in the lift section of the exhaust cam 7, the tip of the operation arm portion 36 is operated by swinging in the valve opening direction as shown by a two-dot chain line in FIG. Insert into window 22.

Here, in the present embodiment, the second switching mechanism is configured as M2 by the lower and lower pistons 18a and 18b of the cylinder portion 48 and the operation arm portion 36 of the exhaust drive rocker arm 49.
The description of the valve operating device for one cylinder of the cylinder deactivation bank is completed as described above, but the other cylinders have the same configuration as described above.

<Oil passage>
As shown in FIGS. 1 and 2, the intake rocker shaft 3 is formed with a cylinder resting mode oil passage 51 and a high speed mode oil passage 52 along the axial direction. Opening is made on the front end surface and the rear end surface of the shaft 3. The front end of the idle cylinder mode oil passage 51 is closed by a plug 53, and one end of an L-shaped metal pipe 54 is press-fitted and fixed to the rear end. The front end of the high-speed mode oil passage 52 is connected to a high-speed mode oil control valve 55 (control means, hereinafter referred to as high-speed mode OCV) through an oil supply passage (not shown) formed in the cylinder head 1. The rear end is closed by a plug 56.

  The exhaust rocker shaft 4 is formed with a cylinder resting mode oil passage 57 along the axial direction, and both front and rear ends of the oil passage 57 open to the front end surface and the rear end surface of the exhaust rocker shaft 4. The front end of the idle cylinder mode oil passage 57 is connected to an idle cylinder mode OCV 58 (control means, hereinafter referred to as a low speed mode OCV) via an oil supply path (not shown) formed in the cylinder head 1, and the rear end One end of an L-shaped metal pipe 59 is press-fitted and fixed. The other ends of the intake-side and exhaust-side metal pipes 54 and 59 face each other at a predetermined interval, and both ends of a rubber hose 60 are fitted and connected to each other.

The OCVs 55 and 58 for the high speed mode and the cylinder deactivation mode are supplied with oil from a lubricating oil pump (not shown) provided in the engine, while being controlled by an ECU 61 (control means, abbreviated as an engine control unit) mounted on the vehicle. By switching control, oil is appropriately supplied to the high-speed mode oil passage 52 and the idle cylinder mode oil passage 57.
As shown in FIGS. 2 and 3, the intake rocker shaft 3 is formed with communication paths 63 at three locations (one location is shown in the figure) so as to correspond to the low speed cylinder portion 16 of the intake driven rocker arm 11 of each cylinder. The lower end of each communication passage 63 communicates with the cylinder resting mode oil passage 51, and the upper end of each communication passage 63 opens to the outer peripheral surface of the intake rocker shaft 3 and communicates with the inside of the lower cylinder 16 a of each low speed cylinder portion 16. Yes.

  As shown in FIGS. 2 and 5, the intake rocker shaft 3 is formed with communication passages 64 at three locations (one location is shown in the figure) so as to correspond to the intake driven rocker arm 11 and the high speed cylinder portion 17 of each cylinder. The lower end of each communication passage 64 communicates with the high-speed mode oil passage 52, and the upper end of each communication passage 64 opens to the outer peripheral surface of the intake rocker shaft 3 and communicates with the inside of the cylinder 17 a of each high-speed cylinder portion 17.

  As shown in FIGS. 2 and 3, the exhaust rocker shaft 4 is formed with communication passages 65 at three locations (one location is shown in the figure) so as to correspond to the cylinder portion 48 of the exhaust driven rocker arm 43 of each cylinder. The lower end of each communication passage 65 communicates with the cylinder resting mode oil passage 57, and the upper end of each communication passage 65 opens to the outer peripheral surface of the exhaust rocker shaft 4 to communicate with the inside of the lower cylinder 16 a of each cylinder portion 48. Yes.

《Non-cylinder bank》
On the other hand, the valve operating device of the non-cylinder bank does not include a cylinder resting mechanism but includes only a switching mechanism between the low speed mode and the high speed mode. Specifically, on the intake side, the low-speed cylinder portion 16 and the low-speed drive rocker arm 32 of the intake driven rocker arm 11 are omitted (the high-speed cylinder portion 17 and the high-speed drive rocker arm 38 remain), and the intake driven rocker arm 11 is left. Oscillates directly by the low-speed cam 6 without passing through the low-speed drive rocker arm 32 and always drives the intake valve to open and close.

  On the exhaust side, the cylinder portion 48 and the exhaust drive rocker arm 49 of the exhaust driven rocker arm 43 are omitted, and the exhaust driven rocker arm 43 swings directly by the exhaust cam 7 without passing through the exhaust drive rocker arm 49 and is always exhausted. Open / close drive. Since the intake and exhaust driven rocker arms 11 and 43 always swing in this manner, the rest cam 8 of the camshaft 2 is also omitted. Further, with the omission of the cylinder deactivation mechanism, the cylinder deactivation mode oil passages 51 and 57 of the intake rocker shaft 3 and the exhaust rocker shaft 4 are also omitted.

Next, the operation state of the valve operating apparatus with the cylinder resting mechanism of the engine configured as described above will be described.
The switching control of the OCVs 55 and 58 by the ECU 61 is performed based on the engine rotational speed Ne. For example, in the rotational range where the engine rotational speed Ne is less than the first threshold value Ne1 and the output request to the engine is sufficiently low, the idle cylinder mode (third Mode), the low speed mode (first mode) is executed in the rotational range where the normal engine output is required between the first threshold value Ne1 and the second threshold value Ne2 (> Ne1), and the second threshold value is set. The high speed mode (second mode) is executed in a rotation range where Ne2 or higher and a particularly high engine output is required. Therefore, the operation status of the valve operating device will be described sequentially for each mode.

<Low speed mode>
In the idle cylinder, the ECU 61 switches and controls the high speed mode OCV 55 and the idle cylinder mode OCV 58 to stop the oil supply to the idle cylinder mode oil passage 51 and the high speed mode oil passage 52, respectively.

  As a result, as shown in FIG. 3, the lower piston 18a and the upper piston 18b are held at the lower positions by the urging force of the compression spring 21 in the low-speed cylinder portion 16 of the intake driven rocker arm 11 and the cylinder portion 48 of the exhaust driven rocker arm 43, respectively. Thus, the outer peripheral surface of the upper piston 18 b is exposed through the operation window 22. Further, as shown in FIG. 5, in the high speed cylinder portion 17 of the intake driven rocker arm 11, the piston 25 is held at the lower position by the urging force of the compression spring 28, and the escape portion 30 is exposed through the operation window 29. .

On the other hand, during operation of the engine, the low-speed drive rocker arm 32, the high-speed drive rocker arm 38, and the exhaust drive rocker arm 49 always swing according to the shapes of the corresponding cams 6, 7, and 9, and each operation arm portion 36 is accompanied by the swing. , 41 are inserted into and removed from the operation windows 22, 29 of the driven rocker arms 11, 43.
The high-speed drive rocker arm 38 is swung by itself while inserting and removing the tip of the escape portion 30 exposed from the operation window 29 of the high-speed cylinder unit 17 and is driven like the low-speed drive rocker arm 32 and the exhaust drive rocker arm 49 described below. The rocker arms 11 and 43 are not swung.

  Further, the low-speed drive rocker arm 32 and the exhaust drive rocker arm 49 respond by pressing the outer peripheral surface of the upper piston 18b exposed from the operation window 22 of the low-speed cylinder unit 16 and the cylinder unit 48 when swinging in the valve opening direction. The driven rocker arms 11 and 43 are swung in the valve opening direction to open the intake valve and the exhaust valve. Further, when the low-speed drive rocker arm 32 and the exhaust drive rocker arm 49 are swung in the valve closing direction, the corresponding driven rocker arms 11 and 43 are swung in the valve closing direction due to the urging force of the valve spring accompanying the valve closing of the intake / exhaust valve. Move.

As a result, the intake driven rocker arm 11 swings together with the low speed drive rocker arm 32 to drive the intake valve to open and close following the shape of the low speed cam, and the exhaust driven rocker arm 43 swings together with the exhaust drive rocker arm 49 to form the exhaust cam. Following this, the exhaust valve is driven to open and close.
On the other hand, in the non-cylinder bank, the ECU 61 stops the oil supply to the high-speed mode oil passage 52 by the high-speed mode OCV 55, so that the high-speed drive rocker arm 38 swings in the same manner as the idle cylinder bank, following the shape of the low-speed cam 6. Thus, the intake valve is driven to open and close, and the exhaust valve is driven to open and close following the shape of the exhaust cam 7. Therefore, in this low speed mode, the engine output required in the normal rotation range is realized using the low speed cam 6 and the exhaust cam 7.

<Cylinder mode>
In the idle cylinder bank and the non-vacuum bank, the ECU 61 supplies oil by the idle cylinder mode OCV 58 in the idle cylinder bank while stopping the oil supply to the high-speed mode oil passage 52.

  Oil from the idle cylinder mode OCV 58 circulates in the idle cylinder mode oil passage 57 of the exhaust rocker shaft 4 from the front side to the rear side, and is supplied into the lower cylinder 16 a of the exhaust driven rocker arm 43 through the respective communication paths 65. Further, after passing through the metal pipes 54 and 59 and the hose 60, the intake rocker shaft 3 circulates in the cylinder resting mode oil passage 51 from the rear side to the front side, passes through the communication passages 63, and the intake driven rocker arm 11. It is supplied into the lower cylinder 16a.

  In the lower cylinder 16 a and the upper cylinder 16 b of the intake driven rocker arm 11 and the exhaust driven rocker arm 43, the lower piston 18 a and the upper piston 18 b slide upward while receiving the oil pressure of the supplied oil and resisting the compression spring 21. The position is switched to the upper position, and the escape portion 23 of the lower piston 18 a is exposed through the operation window 22. Therefore, the low-speed drive rocker arm 32 and the exhaust drive rocker arm 49 are swung independently while inserting and detaching the tip from the escape portion 23 exposed from the operation window 22 of the corresponding driven rocker arm 11, 43, and swinging with respect to each driven rocker arm 11, 43. Cancel the operation.

Since the high-speed drive rocker arm 38 is also swung as described above, as a result, the intake and exhaust valves are held closed by the urging force of the valve spring in each cylinder of the idle cylinder, and the intake driven rocker arm 11 and the exhaust driven rocker arm 43 are The sliding contact portions 15a and 47a of the cam-side arms 15 and 47 are held at the valve-closing position in a state where the cam-side arms 15 and 47 are in contact with the rest cam 8.
On the other hand, in the non-cylinder bank, the operation of each cylinder is continued in the same manner as in the low speed mode, and the operation of the vehicle is continued by the torque generated in the bank and This saves fuel consumption.

<High-speed mode>
In the idle cylinder bank, the ECU 61 stops supplying oil to the idle cylinder mode oil passage 51 by the idle cylinder mode OCV 58 and supplies oil to the high speed mode oil passage 52 by the high speed mode OCV 55.

As a result, as in the low speed mode, the outer peripheral surface of the upper piston 18 b is exposed through the operation window 22 in the low speed cylinder portion 16 of the intake driven rocker arm 11 and the cylinder portion 48 of the exhaust driven rocker arm 43.
On the other hand, oil in the high-speed mode oil passage 52 is supplied into the cylinder 17a of the high-speed cylinder portion 17 in the intake driven rocker arm 11 of each cylinder through the communication passage 64. In the cylinder 17 a, the oil pressure of the supplied oil is received and the piston 25 slides upward against the compression spring 28 and is switched to the upper position, and the outer peripheral surface of the piston 25 is exposed through the operation window 29.

As a result, on the exhaust side, as in the low speed mode, the exhaust driven rocker arm 43 swings together with the exhaust drive rocker arm 49 following the shape of the exhaust cam 7, and the exhaust valve is driven to open and close following the shape of the exhaust cam 7.
On the intake side, the pistons 18b and 25 of the low-speed cylinder unit 16 and the high-speed cylinder unit 17 are both exposed and can be pressed by the corresponding drive rocker arms 32 and 38. Since the cam 9 has a wider lift section (that is, operating angle) and a larger lift amount, the actual pressing operation is performed on the high-speed drive rocker arm 38 side, and the low-speed drive rocker arm 32 is swung. That is, in this high speed mode, the intake valve is driven to open and close following the shape of the high speed cam 9.

On the other hand, as with the non-cylinder bank, oil is supplied to the high-speed mode oil passage 52 in the non-cylinder bank, and the intake valve is driven to open and close following the shape of the high-speed cam 9. Therefore, in the high speed mode, a high engine output required in a high rotation range is realized by increasing the valve opening period and the lift amount of the intake valve as compared with the low speed mode.
The valve operating apparatus with a cylinder resting mechanism of the engine according to this embodiment operates as described above. In the present embodiment, the low-speed drive rocker arm 32 and the high-speed drive rocker arm 38 are disposed on the front and rear sides of the intake driven rocker arm 11 as described above, and the low-speed cylinder unit 16 and the high-speed cylinder unit 17 are provided in the intake driven rocker arm 11. The low-speed drive rocker arm 32 and the high-speed drive rocker arm according to the sliding positions of the lower piston 18a and the upper piston 18b slidably provided on the low-speed cylinder portion 16 and the piston 25 slidably provided on the high-speed cylinder portion 17 The operation arm portions 36 and 41 extending from 38 are pressed or swung.

Further, an exhaust driving rocker arm 49 is disposed in front of the exhaust driven rocker arm 43, and a cylinder portion 48 is provided in the exhaust driven rocker arm 43, and sliding positions of the lower piston 18a and the upper piston 18b that are slidably provided on the cylinder portion 48 are provided. Accordingly, the operation arm portion 36 extended from the exhaust drive rocker arm 49 is pressed or swung.
As a result, on the intake side, members such as the low-speed cylinder unit 16 and the high-speed cylinder unit 17, the low-speed drive rocker arm 32, and the high-speed drive rocker arm 38 are efficiently arranged in one place with the intake driven rocker arm 11 as the center. On the exhaust side, each member such as the cylinder portion 48 and the exhaust drive rocker arm 49 is efficiently arranged in one place with the exhaust driven rocker arm 43 as the center. Therefore, the configuration of the valve operating device including the cylinder resting mechanism can be efficiently arranged on the cylinder head 1, and thus the entire valve operating mechanism can be made compact, and hence the engine can be made compact.

  In addition, as a result of concentrating the members of the valve mechanism in one place in this way, the cylinder portions 16, 17, 48 of the driven rocker arms 11, 43 and the drive rocker arms 32, 38, 49 are inevitably approached. Since the tips of the operation arm portions 36, 41 extending from the drive rocker arms 32, 38, 49 correspond to the cylinder portions 16, 17, 48 at the shortest distance, the lengths of the operation arm portions 36, 41 are required. Can be minimized. Therefore, each of the drive rocker arms 32, 38, 49 can be formed in a lean shape to ensure sufficient strength, and the weight can be reduced. As a result, the inertia weight of the entire valve operating apparatus can be reduced.

  This is the end of the description of the embodiment, but the aspect of the present invention is not limited to this embodiment. For example, in the above-described embodiment, the present invention is applied to a V-type 6-cylinder gasoline engine having four valves per cylinder. However, the type and form of the engine are not limited to this as long as the engine includes a valve operating device with a cylinder deactivation mechanism. Or may be applied to an in-line four-cylinder engine having two valves per cylinder.

In the above embodiment, the cylinder resting mechanism is provided not only on the intake side but also on the exhaust side in the cylinder resting bank to hold the exhaust valve in the cylinder resting mode. For example, the cylinder closing mechanism on the exhaust side is omitted. The exhaust driven rocker arm 43 may be directly rocked by the exhaust cam 7.
Furthermore, in the above embodiment, in the high speed mode, not only the piston 25 of the high speed cylinder portion 17 but also the upper piston 18b of the low speed cylinder portion 16 are exposed so that they can be pressed. Since it is on the piston 25 side of the high-speed cylinder portion 17, it is not always necessary to expose the upper piston 18b of the low-speed cylinder portion 16, and the escape portion 23 may be held at the exposed upper position.

It is a top view showing a cylinder head provided with a valve operating device with a cylinder resting mechanism of an engine of an embodiment. It is a partial enlarged plan view which shows the detail of the valve operating apparatus for 1 cylinder. It is sectional drawing which shows the time of the action | operation of the low speed cam corresponding to the AA line of FIG. 2, and an exhaust cam. It is sectional drawing which shows the time of a low-speed cam and exhaust cam corresponding to the AA line of FIG. FIG. 3 is a cross-sectional view showing when the high-speed cam corresponding to line BB in FIG. 2 is at rest. It is sectional drawing which shows the time of the action | operation of the high-speed cam equivalent to the BB line of FIG. It is a partial enlarged plan view which shows the positional relationship of the drive rocker arm with respect to a cam, and a driven rocker arm. It is CC sectional view taken on the line of FIG.

Explanation of symbols

3 Intake rocker shaft (first rocker shaft)
4 Exhaust rocker shaft (second rocker shaft)
6 Low speed cam (first cam)
7 Exhaust cam (third cam)
9 High-speed cam (second cam)
11 Intake driven rocker arm (first rocker arm)
16a Lower cylinder (first and third cylinders)
16b Upper cylinder (first and third cylinders)
17a Cylinder (second cylinder)
18a Lower piston (first and third pistons)
18b Upper piston (first and third pistons)
25 piston (second piston)
32 Low-speed drive rocker arm (second rocker arm)
36 Operation arm portion (first and third engaging protrusions)
38 High-speed drive rocker arm (third rocker arm)
41 Operation arm (second engagement protrusion)
43 Exhaust driven rocker arm (fourth rocker arm)
49 Exhaust drive rocker arm (fifth rocker arm)
55 OCV for high-speed mode (control means)
58 OCV for non-cylinder mode (control means)
61 ECU (control means)
M1 first switching mechanism M2 second switching mechanism

Claims (6)

A first rocker arm whose tip is linked to one of a pair of intake or exhaust valves and is pivotably supported on the rocker shaft;
A second rocker arm that is swingably supported by the rocker shaft adjacent to one side of the first rocker arm and driven by a first cam;
A third rocker arm that is swingably supported on the rocker shaft adjacent to the other side of the first rocker arm and driven by a second cam having a different cam shape from the first cam;
A switching mechanism for switching presence / absence of linkage between the first rocker arm and the second or third rocker arm;
Control means for controlling the switching of the switching mechanism,
The switching mechanism includes a first piston slidably mounted on a first cylinder formed on the first rocker arm, and an axial direction of the rocker shaft with respect to the first cylinder on the first rocker arm. a second piston which is slidably mounted in the second cylinder which is formed adjacent to, said to extend in the first piston side from the second rocker arm along the axis of the rocker shaft in an L-shape A bent engagement tip is provided on the first piston so as to be engageable with the first piston, and an L-shape extending from the third rocker arm along the axis of the rocker shaft toward the second piston. The tip bent into a shape is made up of a second engaging projection that can be engaged with the second piston, and the positions of the first and second pistons are respectively engaged with the first and second engaging projections. Position and Cylinder-closing mechanism with a valve gear of an internal combustion engine, wherein the switching between an engaged position.   The control means includes: a first mode in which the first rocker arm is driven by the first cam; a second mode in which the first rocker arm is driven by the second cam; and the first rocker arm 2. The valve operating apparatus with a cylinder-closing mechanism for an internal combustion engine according to claim 1, wherein switching of the switching mechanism is controlled so as to be in any one of the third modes that are inactive. In the first mode, the control means sets the first piston to an engagement position with respect to the first engagement protrusion, and sets the second piston to a non-engagement position with respect to the second engagement protrusion.
In the second mode, at least the second piston is in an engagement position with respect to the second engagement protrusion,
In the third mode, the first piston is in a disengaged position with respect to the first engagement protrusion, and the second piston is in a disengagement position with respect to the second engagement protrusion. 3. The valve operating apparatus with a cylinder resting mechanism for an internal combustion engine according to claim 2, wherein switching of the switching mechanism is controlled. A first rocker arm whose tip is linked to one of a pair of intake valves or exhaust valves and is pivotally supported on the first rocker shaft;
A second rocker arm that is swingably supported on the first rocker shaft adjacent to one side of the first rocker arm and driven by a first cam;
A third rocker arm that is swingably supported on the first rocker shaft adjacent to the other side of the first rocker arm and driven by a second cam having a different cam shape from the first cam;
A fourth rocker arm whose front end is linked to the other of the pair of intake valves or exhaust valves and is swingably supported on a second rocker shaft disposed in parallel with the first rocker shaft;
A fifth rocker arm that is swingably supported on the second rocker shaft adjacent to the fourth rocker arm and driven by a third cam;
A first switching mechanism for switching presence / absence of linkage between the first rocker arm and the second or third rocker arm;
A second switching mechanism for switching presence / absence of linkage between the fourth rocker arm and the fifth rocker arm;
Control means for controlling switching of the first and second switching mechanisms,
The first switching mechanism includes a first piston slidably mounted on a first cylinder formed on the first rocker arm, and the first rocker shaft with respect to the first cylinder on the first rocker arm. A second piston that is slidably mounted on a second cylinder formed adjacent to the axial direction of the first rocker, and extends from the second rocker arm toward the first piston along the axis of the first rocker shaft. A first engagement protrusion provided to be engaged with the first piston at an end bent in an L shape, and the second piston from the third rocker arm along the axis of the first rocker shaft. The front end of the first piston is extended to the side and bent into an L-shape, and is provided with a second engaging projection that can be engaged with the second piston. And the second engaging protrusion Switching between an engaged position and a disengaged position in which,
The second switching mechanism includes a third piston that is slidably mounted on a third cylinder formed on the fourth rocker arm, and the second rocker arm along the axis of the second rocker shaft from the fifth rocker arm . The tip of the third piston, which is extended to the side of the three pistons and bent in an L shape, includes a third engagement protrusion that can be engaged with the third piston. The position of the third piston is the third engagement. A valve operating apparatus with a cylinder resting mechanism for an internal combustion engine, wherein the valve is switched between an engagement position and a non-engagement position with respect to a protrusion.   The control means includes: a first mode in which the first rocker arm is driven by the first cam and the fourth rocker arm is driven by the third cam; and the first rocker arm is the second rocker. The mode is one of a second mode in which the fourth rocker arm is driven by the cam and the fourth rocker arm is driven by the third cam, and a third mode in which the first and fourth rocker arms are inoperative. 5. The valve operating apparatus with a cylinder resting mechanism for an internal combustion engine according to claim 4, wherein switching of the first and second switching mechanisms is controlled as described above. In the first mode, the control means is configured to engage the first piston with the first engagement protrusion, disengage the second piston with respect to the second engagement protrusion, and The third piston is set to the engagement position with respect to the third engagement protrusion,
In the second mode, at least the second piston is in an engagement position with respect to the second engagement protrusion, and the third piston is in an engagement position with respect to the third engagement protrusion,
In the third mode, the first piston is disengaged from the first engagement protrusion, the second piston is disengaged from the second engagement protrusion, and the third piston is 6. The valve with a cylinder resting mechanism for an internal combustion engine according to claim 5, wherein switching of the first and second switching mechanisms is controlled so as to be in a non-engaging position with respect to the third engaging protrusion. apparatus.

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