JP4143842B2 - 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 corresponding to the operating region, various engines have been proposed in which the intake / exhaust valve opening period, the lift amount, and the like are switched (for example, see Patent Document 1). .
In the engine described in Patent Document 1, the driven rocker arm supported on the rocker shaft is swung by the first low-speed cam to open and close the intake valve, and is supported on the rocker shaft adjacent to the driven rocker arm. The drive rocker arm is swung by the second cam for high speed. 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 intake valve.
JP 2001-41017 A

As described above, in the engine of Patent Document 1, switching is performed in two operating states in which the intake valve is opened and closed by the first or second cam. In addition to these functions, the specific cylinder is deactivated. There is a demand for adding a non-cylinder function.
In this case, for example, similarly to the second cam, another drive rocker arm is swung by the first cam, and a pair of pistons are slid on the driven rocker arm so that the engagement protrusions of these drive rocker arms can be engaged. A configuration that can be moved freely is conceivable. In such a valve operating apparatus, the driven rocker arm swings with either one of the drive rocker arms according to the sliding position of both pistons, and drives the intake valve to open and close according to the shape of the corresponding cam. When the engagement rocker arms of the drive rocker arm are swung together, the driven rocker arm keeps the intake valve closed and performs the cylinder resting operation.

  By the way, the piston of the driven rocker arm is switched using oil discharged from an oil pump for lubricating the engine. However, since the rotational speed of the oil pump is low in the low engine speed range, a sufficient discharge amount cannot be expected. For this reason, in the low rotation region where the first cam for low speed is switched, the sliding of the piston due to the hydraulic pressure becomes slow, and there is a problem that the operating state of the engine cannot be switched quickly.

  An object of the present invention is to quickly switch the piston of a rocker arm even in a low rotation range where a sufficient oil pump discharge amount cannot be expected, and thereby to switch the operating state of the internal combustion engine with good responsiveness. An object of the present invention is to provide a valve operating apparatus with a cylinder resting mechanism.

In order to achieve the above object, the invention according to claim 1 is directed to a first rocker arm whose tip is linked to one of an intake valve and an exhaust valve and is swingably supported by a rocker shaft, and one side of the first rocker arm. Is pivotally supported on the rocker shaft adjacent to the second rocker arm driven by the first cam for low speed, and is pivotally supported on the rocker shaft adjacent to the other side of the first rocker arm. A third rocker arm driven by the second cam for high speed, a first piston slidably mounted on a first cylinder formed on the first rocker arm, and a first rocker arm. A second piston slidably mounted on a second cylinder formed adjacent to the cylinder, and a first engagement protrusion extending from the second rocker arm and engagable with the first piston. The third lock A second engaging projection that extends from the arm so as to be engageable with the second piston, and hydraulic pressure is applied to the first and second pistons to position the pistons in the first and second engagements. A first and second switching mechanism that switches between an engagement position and a non-engagement position with respect to the protrusion; and a control unit that controls switching between the first and second switching mechanisms. It is formed smaller than the diameter of the piston, and the first piston is vertically divided into a first part that engages with the first engaging protrusion and a second part that does not engage with the first engaging protrusion. It is.

  Accordingly, the first and second pistons are switched between the engaged position and the non-engaged position by receiving the hydraulic pressure by the first and second switching mechanisms, and the first rocker arm is switched to the first piston by the second rocker arm. When the first engagement protrusion is engaged, one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam for low speed, and the second engagement protrusion of the third rocker arm is engaged with the second piston. Is engaged to drive the opening and closing of either the intake valve or the exhaust valve following the shape of the second cam for high speed, and when the engagement projection is not engaged with any of the first and second pistons, One of the valve and the exhaust valve is held closed, and the operating state of the internal combustion engine is switched according to the above switching.

  Since the first cam for low speed is used in a lower rotation range than the second cam for high speed, the first piston is switched with respect to the switching of the second piston for operating the second cam. The switching of the first piston for operating the cam is performed in a lower rotation range. Here, a sufficient discharge amount cannot be expected for the hydraulic pressure supply source in the low rotation range of the engine, but since the diameter of the first piston is smaller than the diameter of the second piston, in the low rotation range where the oil supply is insufficient. In addition, the first piston is quickly switched, and the operating state of the internal combustion engine can be switched with good responsiveness.

In addition , compared with the second portion of the first piston that mainly receives hydraulic pressure, the first portion engages with the first engagement protrusion of the second rocker arm, and the entire first rocker arm is resisted by inertial mass. Therefore, high rigidity is required. By dividing the first part and the second part, it is possible to apply a material having high rigidity only to the first part, and to use a material having low rigidity, that is, an inexpensive material, for the second part. The manufacturing cost is reduced as compared with the case where the entire first piston is made of a material having high rigidity.

A second aspect of the present invention, in claim 1, the second portion of the first piston, together with the housing and slidable in a first cylinder, in which are formed smaller in diameter than the first portion.
Accordingly, the diameter of the second portion that receives the hydraulic pressure is reduced to enable quick switching of the first piston, and the first engagement protrusion of the second rocker arm is securely secured by sufficiently securing the diameter of the first portion. Engagement is possible.

According to a third aspect of the present invention, in the first aspect, the control means is a first mode in which the first rocker arm is driven by the first cam, and a second mode in which the first rocker arm is driven by the second cam. And the switching of the first and second switching mechanisms so as to be in any one of the third modes in which the first rocker arm is inoperative.
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 fourth aspect of the present invention, there is provided a first rocker arm whose tip is linked to one of the intake valve and the exhaust valve and is swingably supported on the first rocker shaft, and adjacent to one side of the first rocker arm. A second rocker arm that is swingably supported by one rocker shaft and driven by a first cam for low speed, and is pivotally supported by the first rocker shaft adjacent to the other side of the first rocker arm. The third rocker arm driven by the second cam for high speed and the tip of the third rocker arm are linked to the other of the intake valve or the exhaust valve, and can swing freely on the second rocker shaft arranged parallel to the first rocker shaft. A fourth rocker arm that is supported, 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, and a first rocker arm. First A first piston slidably mounted on the cylinder; a second piston slidably mounted on a second cylinder formed adjacent to the first cylinder on the first rocker arm; and a fourth rocker arm A third piston slidably mounted on the formed third cylinder; a first engagement protrusion extending from the second rocker arm and engagable with the first piston; and a third rocker arm A second engagement protrusion extending from the second piston so as to be engageable with the second piston, a third engagement protrusion extending from the fifth rocker arm and provided to be engageable with the third piston, A first hydraulic pressure is applied to the first, second and third pistons to switch the positions of the pistons between the engaged position and the non-engaged position with respect to the first, second and third engaging protrusions. The second and third switching mechanisms and the first, second and second And control means for controlling the switching of the switching mechanism, the diameter of the first and third pistons together to form smaller than the diameter of the second piston, the first and third piston, the first and third engaging projections And a second part that is not engaged with the first and third engaging protrusions, and is divided into two parts in the vertical direction .

  Accordingly, the first and second pistons are switched between the engaged position and the non-engaged position by receiving the hydraulic pressure by the first and second switching mechanisms, and the first rocker arm is switched to the first piston by the second rocker arm. When the first engagement protrusion is engaged, one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam for low speed, and the second engagement protrusion of the third rocker arm is connected to the second piston. When engaged, one of the intake valve and the exhaust valve is driven to open and close following the shape of the second cam for high speed, and when the engagement protrusion is not engaged with any of the first and second pistons, the intake valve Alternatively, hold one of the exhaust valves closed.

  Further, the third piston is switched between the engaged position and the non-engaged position by receiving the hydraulic pressure by the third switching mechanism, and the fourth rocker arm has the third engagement protrusion of the fifth rocker arm on the third piston. When engaged, the other of the intake valve and the exhaust valve is driven to open and close following the shape of the third cam, and when the third engagement protrusion of the fifth rocker arm is not engaged with the third piston, the intake valve or the exhaust valve is driven. Hold the other valve closed. Therefore, the operating state of the internal combustion engine is switched according to the above switching.

  The first cam for low speed is used in a lower rotation range than the second cam for high speed, while the third cam corresponding to the first and second cams rotates from the low rotation range to high rotation. It is used to the area. Therefore, with respect to switching of the second piston for operating the second cam, switching of the first piston for operating the first cam and switching of the third piston for operating the third cam. Will be performed in a lower rotation range. Here, in the low engine speed range, a sufficient discharge amount cannot be expected for the hydraulic pressure supply source. However, since the diameters of the first and third pistons are smaller than the diameter of the second piston, the oil supply is insufficiently low. The first and third pistons are quickly switched even in the rotational range, and the operating state of the internal combustion engine can be switched with good responsiveness.

In addition , the first portion of the first piston engages with the first engagement protrusion of the second rocker arm as compared to the second portions of the first and third pistons that mainly receive hydraulic pressure. Since the first portion of the first portion engages with the third engagement protrusion of the fifth rocker arm and swings the entire first rocker arm against the inertial mass, high rigidity is required. By dividing the first part and the second part, it is possible to apply a material having high rigidity only to the first part, and to use a material having low rigidity, that is, an inexpensive material, for the second part. The manufacturing cost is reduced as compared with the case where the entire first and third pistons are made of a material having high rigidity.

According to a fifth aspect of the present invention, in the fourth aspect , the second portions of the first and third pistons are housed and slid in the first and third cylinders, and are formed to have a smaller diameter than the first portion. It is.
Accordingly, the second portion that receives the hydraulic pressure is reduced in diameter to enable quick switching between the first and third pistons, and the diameter of the first portion of the first piston is sufficiently secured to ensure that the second rocker arm has a second diameter. The first engagement protrusion can be reliably engaged, and the diameter of the first portion of the third piston can be sufficiently secured, and the third engagement protrusion of the fifth rocker arm can be reliably engaged.

According to a sixth 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, second and third 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.

As described above, according to the valve operating apparatus with a cylinder resting mechanism for an internal combustion engine according to the first, third , fourth , and sixth aspects of the present invention, the rocker arm of the rocker arm can be operated even in a low rotation range where a sufficient oil pump discharge amount cannot be expected. the piston quickly switched, with as possible out to switch the operating state of the internal combustion engine with a good response, first and second portions of the first piston (claim 1,3), or the first and third piston Appropriate materials are applied to the first part and the second part (claims 4 and 6) , respectively, thereby reducing the manufacturing cost.

According to the cylinder deactivation mechanism with a valve gear of an internal combustion engine according to a second aspect of the invention, in addition to claim 1, securely engage the second first engagement protrusion of the rocker arm relative to the first piston, A highly reliable switching operation can be realized .

According to the valve operating apparatus with a cylinder resting mechanism for an internal combustion engine of a fifth aspect of the invention, in addition to the fourth aspect , the first engagement protrusion of the second rocker arm is reliably engaged with the first piston, A highly reliable switching operation can be realized by reliably engaging the third engagement protrusion of the fifth rocker arm with the third piston.

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, second portion) is disposed in the lower cylinder 16a, and the lower piston 18a is restricted from rotating around the axis of the lower cylinder 16a by a restriction pin (not shown). Thus, it can slide in the lower cylinder 16a in the vertical direction. An upper piston 18b (first and third pistons, first portion) is disposed in the upper cylinder 16b and can slide in the upper cylinder 16b in the vertical direction. 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 the lower piston 18 a is in 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. Is retained. 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.

  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 diameter of the piston 25 is larger than the diameter of the lower piston 18a of the low-speed cylinder portion 16, and is set to be approximately equal to the diameter of the upper piston 18b. The same material as that of the upper piston 18b is applied to the piston 25, and equivalent rigidity is obtained. Is secured.

  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 where 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 comes into contact with the lower part of the lid 27 and moves to the upper position. Switched.

  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.

<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.
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 (hereinafter referred to as OCV) via an oil supply passage (not shown) formed in the cylinder head 1, and the rear end is a plug 56. It is blocked by.

  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 the idle cylinder mode OCV 58 via an oil supply passage (not shown) formed in the cylinder head 1, and one end of an L-shaped metal pipe 59 is press-fitted and fixed to the rear end. Has been. 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.

  Here, in the present embodiment, the first cylinder for switching the lower piston 18a and the upper piston 18b of the low-speed cylinder portion 16 of the intake driven rocker arm 11 by the cylinder mode oil passage 51, the cylinder mode OCV 58, and the communication path 63. A switching mechanism is configured, and the second switching mechanism for switching the piston 25 of the high-speed cylinder portion 17 of the intake driven rocker arm 11 is configured by the high-speed mode oil passage 52, the high-speed mode OCV 55, and the communication passage 64, and the cylinder-rest mode A third switching mechanism for switching the lower piston 18a and the upper piston 18b of the cylinder portion 48 of the exhaust driven rocker arm 43 is configured by the oil passage 57, the cylinder rest mode OCV 58, and the communication passage 65.

《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 is executed. The low speed mode is executed in the rotational range where the normal engine output is required between the first threshold Ne1 and the second threshold Ne2 (> Ne1), and a particularly high engine output is required above the second threshold Ne2. The high speed mode is executed in the rotation range. 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 this embodiment, the lower piston 18a of the low speed cylinder portion 16 and the lower piston 18a of the cylinder portion 48 of the exhaust driven rocker arm 43 are compared with the piston 25 of the high speed cylinder portion 17 of the low speed driven rocker arm 11 as described above. Is set to a small diameter, and the effects of the configuration will be described in detail below.

  First, since the oil for switching the pistons 18a, 18b, 25 of the intake and exhaust driven rocker arms 11, 43 is supplied from the engine oil pump, sufficient oil discharge is possible in the low engine speed range where the pump rotational speed is reduced. The amount cannot be expected. Therefore, although the piston 25 is quickly switched in the high speed cylinder portion 17 of the intake driven rocker arm 11 under a sufficient oil discharge amount in the high rotation range (second threshold value Ne2), the low speed cylinder portion 16 of the intake driven rocker arm 11; In the cylinder portion 48 of the exhaust driven rocker arm 43, the piston is switched under a low oil discharge amount in the low rotation range (first threshold value Ne1).

  Here, it is the lower piston 18a that actually receives the hydraulic pressure in each of the cylinder parts 16 and 48, but these lower pistons 18a are smaller in diameter than the piston 25 in the high-speed cylinder part 17, so that the discharge amount of the oil pump Even if the oil supply into the lower cylinder 16a is slow due to the shortage, the lower piston 18a quickly slides to the upper position. As a result, the switching from the low speed mode to the non-cylinder mode can be completed with good responsiveness, and drivability can be improved.

  In the present embodiment, the low speed cylinder portion 16 and the upper piston 18b of the cylinder portion 48 are configured to be pressed by the operation arm portion 36 of the low speed and exhaust drive rocker arms 32 and 49 when the upper piston 18b is in the lower position. Conversely, the upper arm 18b may be configured to be pressed by the operating arm 36 when the upper piston 18b is in the upper position. In this case, the lower piston 18a is changed to a small diameter so as to switch from the non-cylinder mode to the low speed mode. Can be speeded up. Since switching from the idle cylinder mode to the low speed mode is performed in response to the driver's acceleration request such as accelerator depression, the delay in mode switching immediately gives the driver a bad impression such as poor acceleration. The effect which can prevent a serious situation beforehand is acquired.

  On the other hand, the low-speed and exhaust drive rocker arms 32 and 49 are required to have a predetermined pressing stroke to open the intake and exhaust valves via the intake and exhaust driven rocker arms 11 and 43, and the driven rocker arm 11 and The clearance 23 of the lower piston 18a 43 needs to have a depth (left and right dimensions in FIG. 3) that can avoid the pressing stroke. Further, since the lower piston 18a requires a sufficient thickness even after the relief portion 23 is formed, in order to satisfy these requirements of the pressing stroke, the depth of the relief portion 23, and the thickness, in the valve opening direction. The swinging drive rocker arms 32 and 49 need to be brought into contact with the upper piston 18b on the nearer side, and the upper piston 18b must necessarily be increased in diameter.

  In this embodiment, since the pistons of the low-speed cylinder part 16 and the cylinder part 48 are divided into two parts, the lower piston 18a and the upper piston 18b, the lower piston 18a can be reduced in diameter as described above to enable quick piston switching. In addition, the upper piston 18b can be increased in diameter without being restricted by the diameter of the lower piston 18a. Therefore, the upper piston 18b can be pressed by the low-speed and exhaust drive rocker arms 32, 49 with a sufficient pressing stroke, thereby reliably switching from the non-cylinder mode to the low-speed mode, thereby improving the reliability of the valve gear. Can be made.

  Furthermore, the division of the lower piston 18a and the upper piston 18b has an advantage in terms of manufacturing cost. That is, compared with the lower piston 18a that mainly receives hydraulic pressure, the upper piston 18b is pressed by the operating arm portion 36 of the low-speed and exhaust drive rocker arms 32 and 49, so that the driven rocker arms 11 and 43 as a whole have an inertial mass. High rigidity is required because of rocking against resistance, and high wear resistance is also required because the tip of the operation arm portion 36 collides with each rocking.

  When the lower piston 18a and the upper piston 18b are manufactured integrally, it is necessary to manufacture the whole piston with an expensive material (for example, a material subjected to carburizing and quenching) so as to satisfy the characteristics required for the upper piston 18b. However, in this embodiment, it is possible to apply an expensive material only to the upper piston 18b and to apply a cheaper material (for example, a material not subjected to carburizing and quenching) to the lower piston 18a. Manufacturing cost 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.
Further, in the above-described embodiment, the pistons of the low speed cylinder portion 16 and the cylinder portion 48 are divided into the lower piston 18a and the upper piston 18b in the vertical direction so that the diameter of the lower piston is reduced with respect to the upper piston, and both pistons 18a , 18b are made of different materials, but it is not always necessary to make such a configuration. For example, the lower piston 18a and the upper piston 18b may have the same diameter or the same material, or both pistons 18a, 18b may be integrated. .

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, second part)
18b Upper piston (first and third pistons, first part)
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)
51 Oil passage for closed cylinder mode (first switching mechanism)
52 High-speed mode oil passage (second switching mechanism)
55 OCV for high speed mode (second switching mechanism)
57 Oil passage for closed cylinder mode (third switching mechanism)
58 OCV for idle cylinder mode (first and third switching mechanism)
61 ECU (control means)
63 Communication path (first switching mechanism)
64 communication path (second switching mechanism)
65 communication path (third switching mechanism)

Claims (6)

A first rocker arm whose tip is linked to one of the intake valve or the exhaust valve and is pivotally supported on the rocker shaft;
A second rocker arm that is swingably supported on the rocker shaft adjacent to one side of the first rocker arm and driven by a first cam for low speed;
A third rocker arm that is swingably supported on the rocker shaft adjacent to the other side of the first rocker arm and is driven by a second cam for high speed;
A first piston slidably mounted on a first cylinder formed on the first rocker arm;
A second piston slidably mounted on a second cylinder formed adjacent to the first cylinder on the first rocker arm;
A first engagement protrusion extending from the second rocker arm and provided to be engageable with the first piston;
A second engagement protrusion extending from the third rocker arm and provided to be engageable with the second piston;
First and second switching mechanisms that apply hydraulic pressure to the first and second pistons to switch the positions of the pistons between an engagement position and a non-engagement position with respect to the first and second engagement protrusions. When,
Control means for controlling switching of the first and second switching mechanisms,
A diameter of the first piston is made smaller than a diameter of the second piston , and the first piston is engaged with the first engaging protrusion and the first portion engaging with the first engaging protrusion. A valve operating apparatus with a cylinder resting mechanism for an internal combustion engine, wherein the second part is divided into two parts vertically . The second portion of the first piston, wherein while receiving and sliding in the first cylinder, the cylinder deactivation mechanism for an internal combustion engine according to claim 1, characterized in that has a smaller diameter than the first portion Valve-operated device.   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 first and second switching mechanisms is controlled so as to be in any one of the third modes inactivated. . A first rocker arm whose tip is linked to one of an intake valve or an exhaust valve 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 is driven by a first cam for low speed;
A third rocker arm that is swingably supported by the first rocker shaft adjacent to the other side of the first rocker arm and is driven by a second cam for high speed;
A fourth rocker arm whose tip is linked to the other of the intake valve or the exhaust valve and is swingably supported by 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 piston slidably mounted on a first cylinder formed on the first rocker arm;
A second piston slidably mounted on a second cylinder formed adjacent to the first cylinder on the first rocker arm;
A third piston slidably mounted on a third cylinder formed on the fourth rocker arm;
A first engagement protrusion extending from the second rocker arm and provided to be engageable with the first piston;
A second engagement protrusion extending from the third rocker arm and provided to be engageable with the second piston;
A third engagement protrusion extending from the fifth rocker arm and provided to be engageable with the third piston;
A hydraulic pressure is applied to the first, second and third pistons to switch the positions of the pistons between the engagement position and the non-engagement position with respect to the first, second and third engagement protrusions. A first, second and third switching mechanism;
Control means for controlling switching of the first, second and third switching mechanisms,
A first portion for forming a diameter of the first and third pistons smaller than a diameter of the second piston, and engaging the first and third pistons with the first and third engaging protrusions; 2. A valve operating apparatus with a cylinder resting mechanism for an internal combustion engine, wherein the valve is divided into two parts in the vertical direction, the second part not engaging with the first and third engaging protrusions . The second portion of the first and third piston, together with the housing and slides on the first and third cylinder, according to claim 4, characterized in that it is formed smaller in diameter than the first portion A valve operating apparatus with a cylinder resting mechanism for an internal combustion engine. 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, second and third switching mechanisms is controlled as described above.

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