JP4196193B2 - 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 deactivation mechanism of an internal combustion engine (hereinafter referred to as an engine), and more particularly to an oil passage for supplying and discharging operating hydraulic pressure to a switching mechanism of the valve operating apparatus.

In order to realize the optimum engine output characteristics according to the operating region, various engines have been proposed that perform switching of the intake / exhaust valve opening period and lift amount, or deactivation of a specific cylinder ( For example, see Patent Document 1).
The engine described in Patent Document 1 is configured as an SOHC type in which an intake / exhaust valve is driven to open and close by a single camshaft, and the valve operating device is provided with a switching mechanism for switching the valve opening period and the lift amount of the intake valve. ing. 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 swingably supported on the intake side rocker shaft, and each rocker arm has a rocker shaft. The switch pin is slidable in the axial direction. The switching pin is slid by receiving the hydraulic pressure from an oil control valve (OCV) as a hydraulic pressure switching means through an oil passage formed in the rocker shaft, and connects and releases the rocker arms according to the sliding position.

In the low engine speed range, the connection of the rocker arms is released by the switching pin, 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 deactivated via the third rocker arm. The valve is held substantially closed by the 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 to drive both intake valves to follow the high-speed cam.
JP 2002-227624 A

As described above, in the engine described in Patent Document 1, a switching mechanism is provided only on the intake side in order to switch the valve opening period and lift amount of the intake valve. When the engine is applied to a cylinder that is closed, a switching mechanism is provided for both the intake and exhaust valve operating devices.
In this case, it is necessary to form an oil passage on the exhaust-side rocker shaft in addition to the intake-side rocker shaft, and to add an OCV to supply / discharge hydraulic pressure to / from the exhaust-side oil passage. Further, the OCV and the oil passage of the rocker shaft are connected via a head side oil passage formed in the cylinder head, but it is also necessary to newly form a head side oil passage in the cylinder head corresponding to the added OCV. Arise. Therefore, there is a problem that the manufacturing cost increases due to the increase in the OCV and the complicated processing of the cylinder head related to the head side oil passage.

  It is an object of the present invention to reduce the number of hydraulic pressure switching means for supplying and discharging hydraulic pressure to and from the oil passage of the rocker shaft and reduce the number of head side oil passages connecting the hydraulic pressure switching means and the oil passage. 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 reduce the cost.

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 an intake valve and an exhaust valve and is swingably supported on the first rocker shaft; A second rocker arm that is swingably supported on the first rocker shaft adjacent to one side and driven by the first cam, and swings on the first rocker shaft adjacent to the other side of the first rocker arm. A third rocker arm that is freely supported and driven by a second cam having a cam shape different from that of the first cam, and a tip is linked to the other of the intake valve or the exhaust valve, and is arranged in parallel with the first rocker shaft. A fourth rocker arm swingably supported by the second rocker shaft, and a fifth rocker pivotally supported by the second rocker shaft adjacent to the fourth rocker arm and driven by a third force. Rocker arm , A first switching mechanism for switching presence / absence of linkage between the first rocker arm and the second rocker arm, a second switching mechanism for switching presence / absence of linkage between the first rocker arm and the third rocker arm, a fourth rocker arm, and a fifth A third switching mechanism for switching presence / absence of linkage with the rocker arm, and first and second formed in the first and second rocker shafts along the axial direction and capable of supplying hydraulic pressure to the first and third switching mechanisms. Two oil passages, a third oil passage formed in parallel with the first oil passage along the axial direction in the first rocker shaft, and capable of supplying hydraulic pressure to the second switching mechanism, and the first and second rockers A first hydraulic pressure switching means connected to one of the first and second oil passages on one end side of the shaft and capable of supplying and discharging hydraulic pressure to one of the first and second oil passages, and the hydraulic pressure to the third oil passage. A second hydraulic switching means capable of discharging, consists substantially U-shaped metal pipe, the other end side of the first and second rocker shaft is pressed at both ends to the first and second oil passages both oil passage And a connecting member for connecting the two to each other.

  Therefore, the first rocker arm can be linked to the second rocker arm by the first switching mechanism, the second rocker arm can be linked by the second switching mechanism, and the second rocker arm can be linked to the second and third rocker arms. Depending on the state, one of the intake valve and the exhaust valve is driven to open and close following the shape of the first cam or the second cam, and one of the intake valve and the exhaust valve is not linked to the second and third rocker arms. Hold the valve closed. The fourth rocker arm can be linked to the fifth rocker arm by a third switching mechanism, and when linked to the fifth rocker arm, the other of the intake and exhaust valves is driven to open and close following the shape of the third cam. At the same time, when not linked, the other of the intake valve and the exhaust valve is kept closed.

Therefore, the internal combustion engine is operated with output characteristics corresponding to the cam shape that drives the intake and exhaust valves to open and close, and the cylinder is closed when the intake and exhaust valves are closed.
The first and third switching mechanisms are supplied with operating hydraulic pressure from the first hydraulic pressure switching means via the first and second oil passages, and the second switching mechanism is supplied from the second hydraulic pressure switching means via the third oil passage. Working hydraulic pressure is supplied. Hydraulic pressure from the first hydraulic switching means, after the first and is supplied to one and within the oil passage of the first or the second oil passage from one end of the second rocker shaft and flows to the other end, substantially It passes through a connecting member made of a U-shaped metal pipe , is supplied to the other of the first or second oil passage, and circulates in the oil passage to one end side. Supply to the 3 switching mechanism is made.

  In other words, since the operating oil pressure is supplied to the first and second oil passages by a single first oil pressure switching means, it is not necessary to provide the first oil pressure switching means individually for each oil passage, In the cylinder head provided with the valve device, it is only necessary to form one head-side oil passage that connects the first hydraulic pressure switching means and one of the first or second oil passages. As compared with the case where a plurality of head side oil passages are individually formed corresponding to the above, machining on the cylinder head side is simplified.

(2) A first rocker arm whose tip is linked to one of an intake valve or an exhaust valve and is swingably supported on the first rocker shaft;
A second rocker arm swingably supported on the first rocker shaft adjacent to one side of the first rocker arm and driven by the first cam, and a first adjacent to the other side of the first rocker arm. A first rocker shaft is pivotally supported on the rocker shaft and driven by a second cam having a different cam shape from the first cam, and a tip is linked to the other of the intake valve or the exhaust valve. A fourth rocker arm swingably supported on a second rocker shaft disposed in parallel with the second rocker shaft and a second rocker shaft adjacent to the fourth rocker arm so as to swing freely. The fifth rocker arm to be driven, the first switching mechanism for switching the link between the first rocker arm and the second rocker arm, and the link between the first rocker arm and the third rocker arm are switched. A second switching mechanism, a third switching mechanism for switching presence / absence of linkage between the fourth rocker arm and the fifth rocker arm, and first and third switching mechanisms formed along the axial direction in the first and second rocker shafts. First and second oil passages capable of supplying hydraulic pressure to the mechanism, and formed in parallel with the first oil passage along the axial direction in the first rocker shaft, and capable of supplying hydraulic pressure to the second switching mechanism The first oil pressure that is connected to one of the first and second oil passages on one end side of the third oil passage and the first and second rocker shafts, and that can supply and discharge the working oil pressure to one of the first and second oil passages. The switching means, the second hydraulic pressure switching means capable of supplying and discharging operating hydraulic pressure to and from the third oil passage, and the first and second rocker shafts at one end are press-fitted at the other ends of the first and second rocker shafts , respectively. L-shaped metal pie If, Ri Do a resin or rubber hose connecting the other end of the pipes to each other, in which the first and second oil passage and a connecting member for connecting each other.

Therefore, the same effect as that of the invention of claim 1 can be obtained, and the operating oil pressure from the first oil pressure switching means passes through one of the first and second oil passages and then passes through the pipe and the hose to be the first. Or it is supplied to the other of the second oil passages. And since the hose made of resin or rubber has flexibility, even if there is some error in the relative position between the first and second oil passages, both oil passages can be connected without any trouble, Oil leakage at the press-fitting point is prevented.

According to a third aspect of the present invention, in the first or second aspect , the first rocker arm supported on the first rocker shaft is linked to the intake valve, and the fourth rocker arm supported on the second rocker shaft is linked to the exhaust valve. When the disengagement between the first rocker arm and the second and third rocker arms and the disengagement between the fourth rocker arm and the fifth rocker arm are released, the hydraulic pressure is supplied by the first oil pressure switching means. By controlling the exhaust, after the fourth rocker arm and the fifth rocker arm are linked, the first rocker arm and the second rocker arm are linked, and the second hydraulic pressure switching means includes the first rocker arm and the first rocker arm. The hydraulic pressure is controlled to be supplied and discharged so as to maintain non-linkage with the third rocker arm.

Therefore, when the first rocker arm is not linked to the second and third rocker arms and the fourth rocker arm is not linked to the fifth rocker arm, both the intake valve and the exhaust valve are closed. The valve is held and cylinder resting operation is performed.
When releasing the disengagement of both from this state, first, the fourth rocker arm is linked to the fifth rocker arm by the third switching mechanism as the hydraulic pressure is supplied and discharged by the first hydraulic pressure switching means. The exhaust valve is driven to open and close following the shape of the third cam, and then the disengagement between the first rocker arm and the third rocker arm is maintained as the hydraulic pressure is supplied and discharged by the second hydraulic pressure switching means. Thus, the first switching mechanism links the first rocker arm to the second rocker arm to drive the intake valve to follow the shape of the first cam.

That is, since the exhaust valve starts operating at a timing earlier than the operation of the intake valve, the combustion gas remaining in the cylinder (combustion gas immediately before the cylinder is closed) is discharged by opening the exhaust valve. Later, when the intake valve is opened, a new air-fuel mixture flows into the cylinder, and normal combustion is realized from the beginning of the return from the cylinder resting operation.
Preferably, according to the present invention, the first rocker arm supported on the first rocker shaft is linked to the intake valve and the fourth rocker arm supported on the second rocker shaft is used as the exhaust valve. The first hydraulic pressure switching means is connected to the second oil passage on one end side of the second rocker shaft, and the first and second oil passages are connected to each other by the connecting member on the other end side of the first and second rocker shafts. It can be embodied as a valve operating device with a cylinder resting mechanism of an internal combustion engine connected to the engine.

  In this case, the first hydraulic pressure switching is performed to release the disengagement between the first rocker arm and the second and third rocker arms and the disengagement between the fourth rocker arm and the fifth rocker arm. When the hydraulic pressure is supplied or discharged by the means, first, the third switching mechanism is operated through the second oil passage, and the fourth rocker arm is linked to the fifth rocker arm to follow the shape of the third cam. Then, the exhaust valve is driven to open and close, and then the first switching mechanism is operated via the connecting member and the first oil passage, and the first rocker arm is linked to the second rocker arm to follow the shape of the first cam. Since the intake valve is driven to open and close, the exhaust valve starts to operate at a timing that precedes the operation of the intake valve, and the same effect as the invention of claim 4 can be achieved.

As described above, according to the valve operating apparatus with a cylinder resting mechanism for an internal combustion engine according to the first aspect of the present invention, the number of hydraulic pressure switching means for supplying and discharging the hydraulic pressure to and from the oil passage of the rocker shaft is reduced, and the hydraulic pressure switching means. The number of head-side oil passages connecting the oil passages and the oil passages can be reduced, thereby reducing the manufacturing cost.
According to the valve operating apparatus with a cylinder resting mechanism of the internal combustion engine of the second aspect of the invention, in addition to the first aspect, even if some error occurs in the relative position between the first and second oil passages, It is possible to improve the reliability by preventing oil leakage at the press-fitting location.

According to the valve operating apparatus with a cylinder resting mechanism for an internal combustion engine according to a third aspect of the present invention, in addition to the first or second aspect , the exhaust valve is actuated prior to the intake valve when returning from the cylinder resting operation. Thus, the remaining combustion gas can be discharged, thereby quickly increasing the engine output and meeting the driver's acceleration request with certainty, thereby realizing good drivability.

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, and the camshaft 2 is a cylinder (not shown). 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 opened in the clockwise direction and closed in the counterclockwise direction. 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 part 16 is formed with a small-diameter lower cylinder 16a and a large-diameter upper cylinder 16b having a circular cross section in the vertical direction, and the lower end of the lower cylinder 16a is the inner periphery of the bearing hole 12a of the boss part 12 The upper cylinder 16b is open upward.

  A lower piston 18a is disposed in the lower cylinder 16a. The lower piston 18a slides in the vertical direction in the lower cylinder 16a in a state where the rotation about the axis of the lower cylinder 16a is restricted by a restriction pin (not shown). Can do. An upper piston 18b 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 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 opens to the inner peripheral surface of the bearing hole 12a of the boss portion 12. The upper end of the cylinder 17a opens upward. A piston 25 is disposed in the cylinder 17a, and the piston 25 can slide 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). 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 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 extends rearward along the axis of the camshaft 2, and the tip of the operation arm portion 36 is connected to the intake driven rocker arm 11 located on the right side. It is bent in an L-shape and corresponds to the operation window 22 of the low-speed cylinder unit 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 41 extends forward along the axis of the camshaft 2, and the distal end of the operation arm 41 extends to the intake driven rocker arm 11 located on the right side. It is bent in an L shape and corresponds to the operation window 29 of the high-speed cylinder unit 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 first switching mechanism M1 is configured by the lower and lower cylinders 16a and 16b of the low speed cylinder portion 16, the lower and lower pistons 18a and 18b, and the operation arm portion 36 of the low speed drive rocker arm 32, and the high speed cylinder. The cylinder 17a of the part 17, the piston 25, and the operation arm part 41 of the high-speed drive rocker arm 38 constitute a second switching mechanism M2.

<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 lower and lower cylinders 16a and 16b of the cylinder portion 48, the lower and lower pistons 18a and 18b, and the operation arm portion 36 of the exhaust drive rocker arm 49 constitute a third switching mechanism M3.
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 rest mode oil passage 51 (first oil passage) and a high speed mode oil passage 52 (third oil passage) along the axial direction. Both front and rear ends of both oil passages 51 and 52 are open to the front end face and the rear end face of the intake rocker 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 (connecting member) 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 (second hydraulic pressure switching means, hereinafter referred to as a high speed mode OCV) through a head side oil passage (not shown) formed in the cylinder head 1. ) And the rear end is closed by a plug 56.

  The exhaust rocker shaft 4 is formed with a cylinder resting mode oil passage 57 (second oil passage) along the axial direction, and both front and rear ends of the oil passage 57 are opened to the front end surface and the rear end surface of the exhaust rocker shaft 4. is doing. The front end of the cylinder resting mode oil passage 57 is a cylinder resting mode oil control valve 58 (first hydraulic pressure switching means through a head-side oil passage (not shown) formed in the cylinder head 1 and hereinafter referred to as a cylinder resting mode OCV. And one end of an L-shaped metal pipe 59 (connecting member) is press-fitted and fixed to the rear end. 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 an elastomer or rubber hose 60 (connecting member) are fitted and connected to each other.

The OCVs 55 and 58 for the high speed mode and the idle cylinder mode are supplied with oil from a lubricating oil pump (not shown) provided in the engine and are switched and controlled by an ECU 61 (engine control unit) mounted on the vehicle. Oil is appropriately supplied to the oil passage 52 and the cylinder passage 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 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 intake and exhaust cylinder resting mode oil passages 51 and 57 are connected via the metal pipes 54 and 59 and the hose 60 as described above, and from the single low speed mode OCV 58 to the exhaust side. The oil is supplied to the idle cylinder mode oil passage 57, and the operation and effects obtained by the configuration will be described below.

  First, since oil is supplied to the cylinder passage mode oil passages 51 and 57 for intake and exhaust by a single OCV 58 for the low speed mode, the OCV 58 for the low speed mode is individually provided for each oil passage 51 and 57. Compared to the above, the manufacturing cost can be reduced. Further, the cylinder head 1 only needs to be formed with one head side oil passage connecting the OCV 58 for the low speed mode and the exhaust side cylinder resting oil passage 57, corresponding to each cylinder resting oil passage 51, 57. As compared with the case where a plurality of head-side oil passages are individually formed, the processing on the cylinder head 1 side can be simplified, which also contributes to a reduction in manufacturing cost.

  Moreover, since the intake / exhaust cylinder passage oil passages 51 and 57 are connected via the flexible hose 60, there is a slight error in the relative position between the two cylinder suspension mode oil passages 51 and 57. Even if it occurs, both the cylinder resting mode oil passages 51 and 57 can be connected without any trouble, and oil leakage at the press-fitting locations of the metal pipes 54 and 59 can be prevented and reliability can be improved. .

  On the other hand, since the oil from the OCV 58 for the low speed mode is supplied to the oil passage 51 for the cylinder side mode on the intake side after passing through the oil path 57 for the cylinder side mode on the exhaust side, when returning from the cylinder mode to the low speed mode First, the oil supply to the cylinder portion 48 of the exhaust driven rocker arm 43 is stopped, and then the oil supply to the low speed cylinder portion 16 of the intake driven rocker arm 11 is stopped. As a result, the exhaust valve starts operating at a timing that precedes the operation of the intake valve, so that the combustion gas remaining in the cylinder (the combustion gas immediately before the cylinder is closed) is discharged by opening the exhaust valve. After that, a new air-fuel mixture flows into the cylinder by opening the intake valve, and normal combustion can be realized from the beginning of the return to the low speed mode.

  For example, conversely, if the intake valve precedes the exhaust valve, the air-fuel mixture that has been prevented from flowing into the cylinder by the combustion gas in the cylinder may flow backward to the intake side, causing backfire. It is necessary to take measures such as delaying the start of the process by one stroke. In the present embodiment, since such a countermeasure is not necessary, the engine output can be increased promptly when returning to the low speed mode to reliably respond to the driver's acceleration request, thereby realizing good drivability. it can.

  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 intake / exhaust cylinder resting mode oil passages 51, 57 are connected via the metal pipes 54, 59 and the hose 60. Instead, they are formed in a U shape as shown in FIG. Both the cylinder resting mode oil passages 51 and 57 may be connected using the metal pipe 101 (connecting member), and even in this case, the same effect as that of the above embodiment can be obtained. In addition, the rigid metal pipe is difficult to absorb the relative position error between the idle cylinder mode oil passages 51 and 57, but if the bellows portion 101a is formed in the middle of the metal pipe 101 as shown in FIG. Due to the deformation of the bellows portion 101a, the metal pipe 101 is given flexibility so that the relative position error can be absorbed.

  Further, in the above embodiment, the exhaust valve is operated prior to the intake valve when returning from the idle cylinder mode by connecting the low speed mode OCV 58 to the exhaust cylinder idle mode oil passage 57. There is no need for this effect. Therefore, the low speed mode OCV 58 may be connected to the intake side cylinder deactivation mode oil passage 51.

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. It is a fragmentary top view which shows the other example which connected the oil path for cylinder rest modes of intake / exhaust with the U-shaped metal pipe. It is a partial valve closing figure which shows another example which formed the bellows part in the metal pipe.

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)
32 Low-speed drive rocker arm (second rocker arm)
38 High-speed drive rocker arm (third rocker arm)
43 Exhaust driven rocker arm (fourth rocker arm)
49 Exhaust drive rocker arm (fifth rocker arm)
51 Oil passage for closed cylinder mode (first oil passage)
52 Oil passage for high speed mode (3rd oil passage)
54 Metal pipe (connecting member)
55 OCV for high speed mode (second hydraulic pressure switching means)
57 Oil passage for closed cylinder mode (second oil passage)
58 OCV for first cylinder mode (first hydraulic pressure switching means)
59 Metal pipe (connecting member)
60 hose (connecting member)
101 Metal pipe (connecting member)
M1 first switching mechanism M2 second switching mechanism M3 third switching mechanism

Claims (3)

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 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 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 by the second rocker shaft adjacent to the fourth rocker arm and is driven by a third force;
A first switching mechanism for switching presence / absence of linkage between the first rocker arm and the second rocker arm;
A second switching mechanism for switching presence / absence of linkage between the first rocker arm and the third rocker arm;
A third switching mechanism for switching presence / absence of linkage between the fourth rocker arm and the fifth rocker arm;
First and second oil passages formed along the axial direction in the first and second rocker shafts, and capable of supplying hydraulic pressure to the first and third switching mechanisms;
A third oil passage formed in parallel with the first oil passage along the axial direction in the first rocker shaft, and capable of supplying operating oil pressure to the second switching mechanism;
First hydraulic pressure switching means connected to one of the first or second oil passages on one end side of the first and second rocker shafts and capable of supplying and discharging operating hydraulic pressure to one of the first or second oil passages; ,
Second hydraulic pressure switching means capable of supplying and discharging operating hydraulic pressure to and from the third oil passage;
A connecting member that is made of a substantially U-shaped metal pipe and is press-fitted at both ends into the first and second oil passages on the other end side of the first and second rocker shafts to connect the oil passages to each other; A valve operating apparatus with a cylinder resting mechanism for an internal combustion engine, comprising: 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 driven by a first cam;
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 having a different cam shape from the first cam;
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 by the second rocker shaft adjacent to the fourth rocker arm and is driven by a third force;
A first switching mechanism for switching presence / absence of linkage between the first rocker arm and the second rocker arm;
A second switching mechanism for switching presence / absence of linkage between the first rocker arm and the third rocker arm;
A third switching mechanism for switching presence / absence of linkage between the fourth rocker arm and the fifth rocker arm;
First and second oil passages formed along the axial direction in the first and second rocker shafts, and capable of supplying hydraulic pressure to the first and third switching mechanisms;
A third oil passage formed in parallel with the first oil passage along the axial direction in the first rocker shaft, and capable of supplying operating oil pressure to the second switching mechanism;
First hydraulic pressure switching means connected to one of the first or second oil passages on one end side of the first and second rocker shafts and capable of supplying and discharging operating hydraulic pressure to one of the first or second oil passages; ,
Second hydraulic pressure switching means capable of supplying and discharging operating hydraulic pressure to and from the third oil passage;
A substantially L-shaped metal pipe whose one end is press-fitted into the first and second oil passages on the other end side of the first and second rocker shafts, and the other end sides of both pipes are connected to each other. Ri Do a resin or rubber hose to a connecting member connecting said first and second oil passage to each other
A valve operating apparatus with a cylinder resting mechanism for an internal combustion engine, comprising: The first rocker arm supported on the first rocker shaft is linked to an intake valve, and the fourth rocker arm supported on the second rocker shaft is linked to an exhaust valve;
When the first rocker arm and the second and third rocker arms are unlinked, and when the fourth rocker arm and the fifth rocker arm are unlinked, the operation by the first hydraulic pressure switching means is performed. By controlling the supply and discharge of hydraulic pressure, after the fourth rocker arm and the fifth rocker arm are linked, the first rocker arm and the second rocker arm are linked, and the second hydraulic pressure switching means , said first rocker arm and said third cylinder deactivation mechanism with valve train according to claim 1 or 2, wherein the internal combustion engine and controls the hydraulic pressure supply and discharge to maintain the non-association with the rocker arm apparatus.

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