KR950014409B1 - Valve moving apparatus for i.c. engine - Google Patents

Abstract

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Description

Valve driving device of internal combustion board

1 is a cross-sectional view of the main portion of the cylinder head (A-A in FIG. 2) showing the valve driving device of the internal combustion engine according to the first embodiment of the present invention.

2 is a cross-sectional view of the center of the cylinder head (B-B in FIG. 11).

3 is a plan view of a valve driving device with a cylinder rest mechanism.

4 is a cross-sectional view taken along line C-C in FIG.

5 is a D-D cross-sectional view of FIG.

6 is an exploded perspective view of the valve drive device.

Fig. 7 is a sectional view showing a switching mechanism of the valve drive device.

8 is a hydraulic path diagram of the valve drive device.

9 is an operation explanatory diagram of the switching mechanism.

10 is a sectional view of a valve driving apparatus without a cylinder rest mechanism.

11 is a plan view of a cylinder head.

Fig. 12 is a graph showing the time change of the high speed side switching hydraulic pressure in the valve drive device.

Figure 13 is a graph showing the load against the compression height of the arm spring.

14 shows the relationship between the cycle time of the engine and the operation of the assist oil pump.

FIG. 15 is an operation explanatory diagram of the assist oil pump. FIG.

FIG. 16 is a detailed view of the portion X at the arrow in FIG.

FIG. 17 is a detailed view of the portion Z in the arrows in FIG. 16. FIG.

18 is a cross-sectional view of the cover.

19 is a perspective view of a snap ring.

20 is a cross-sectional view of the rocker shaft portion.

Fig. 21 is a sectional view of the rocker shaft portion showing the through holes.

Fig. 22 is a sectional view of a partner switching mechanism inverting the low speed rocker arm.

23 is a cross-sectional view of the arm spring of the present invention.

24 is a cross-sectional view taken along line A-A of FIG.

25 is a cross-sectional view taken along line B-B in FIG.

Fig. 26 is a sectional side view of the rocker arm which is a modification of the first embodiment.

FIG. 27 is a perspective view of a line XXVII-XXVII in FIG. 26. FIG.

FIG. 28 is a perspective view of a line XXVIII-XXVIII in FIG. 27. FIG.

29 is a perspective view showing a main portion of a valve driving apparatus according to a modification of the present invention.

30 is a perspective view of a XXXI-XXXI line in FIG. 29;

31 is a perspective view of a XXXI-XXXI line in FIG. 29;

32 is a plan view of a rocker arm assembly according to a second embodiment of the present invention.

33 is a plan view of a cylinder head of an engine without a valve operation stop mechanism.

34 is an explanatory diagram of the arrangement of rocker arms and the like in the bonded state and the relationship with the valve;

35 is a plan view of a cylinder head of an engine having a valve stop mechanism.

36 is an explanatory diagram of the arrangement of rocker arms and the like in the bonded state and the relationship with the valve.

Fig. 37 is a front view of a state where the chamfering method of the hole inlet of the present invention is carried out.

38 is a perspective view of the XXXVIII-XXXVIII line in FIG. 37;

FIG. 39 is a perspective view of a XXXIX-XXXIX line in FIG. 38; FIG.

FIG. 40 is a cross-sectional view of the upper part of the engine provided with an ignition floc housing along the E-E chassis in FIG.

Fig. 41 is a cross-sectional view taken along the line F-F in Fig. 40;

42 is a sectional view showing a structure of a valve drive system with a variable valve timing mechanism as a modification of the present invention (D-D viewing cross-sectional view of FIG. 3).

Fig. 43 is a sectional view of a rocker arm of a valve drive system with variable valve timing mechanism.

44 is an exploded perspective view of a rocker arm of a valve drive system with a variable valve timing mechanism;

45 is a diagram showing the inertia characteristics and arm spring force characteristics of the valve drive system of the valve drive system with variable valve timing mechanism of the present invention (graph showing the inertia characteristics and spring force characteristics according to the arm spring compression height).

Fig. 46 is a main structural view showing a valve contact portion of a valve drive system with a variable valve timing mechanism according to the present invention.

47 is a sectional view of the lubrication structure.

48 is a sectional view of a valve drive of the engine.

49 is a plan view of FIG. 48;

50 is a diagram showing the relationship between the valve lift amount and the spring force.

51 is a diagram showing the relationship between the amount of valve lift and the force applied to the valve.

52 is an explanatory diagram of an uncomfortable state when spring force is always applied.

53 is a sectional view showing the main parts of another modification.

54 is a diagram showing the relationship between the valve lift amount and the spring force.

55 is a diagram showing a relationship between a valve lift amount and a force applied to a spring force.

56 is a sectional view showing the main parts of another modification.

57 is a diagram showing the relationship between the valve lift amount and the spring force.

58 is a graph showing the hydraulic pressure of a conventional internal combustion engine cylinder at rest.

Fig. 59 is a plan view of a cylinder head showing a belt driving device of an engine having a conventional cylinder rest mechanism.

60 is a hydraulic path diagram of a conventional valve driving apparatus.

* Explanation of symbols for main parts of the drawings

10: large diameter portion 11: cylinder head

12: intake cam shaft 13: exhaust cam shaft

14: low speed cam 15: high speed cam

16: camshaft housing 17: cam cap

18,19,24: Bolt 21: Intake rocker shaft

22: Exhaust rocker shaft part 23: Rocker shaft cap

25: cylinder head cover 30: T-type lever

30L: T-type lever (L) 31,32: Adjusting screw body

33,70,40,41,330,333: Rock part 34,334: Low speed rocker arm

35,65,335,365: High speed rocker arm 36,67: Adjustment screw

36A: Adjusting screw body 36B: Diameter enlargement part

36C: Outside circumference 36D: Curved projection

37,68,337,368: Adjusting nut

38,39,66,69,696,338,339,366,369: Roller Bearing

38B, 66B, 152,153: Bearing 42,43,71,371,521A: Arm spring

44,524 Cylinder 45,96525

46,54,54A, 60A, 60,75,92,95,99,514,526: Compression Spring

47,48,50,72: Switching mechanism 51,58,73,501a: Through hole

51A, 58A: Spring hole 52,52A, 59,59A, 74,513: Rock pin

52B, 59B: Plunger 53: Spring Seat

55, 61, 76, 502C: engagement hole 56, 62, 77: hydraulic passage

57,63,78,113,151: Oil passage 64: Low speed lava section

66A, 69A: Axial 79: Intake valve

79A, 80A: Step 80: Exhaust valve

81,82,531: Valve spring 83: Intake port

84 exhaust port 85 combustion chamber

86: hydraulic control device 87: oil pump

88: accumulator 89: high speed switching oil control valve

90: cylinder rest oil control valve 90: cylinder rest switch oil control valve

91,98: piston 93: cover

94: Bolt 97: Oil Pump Cam

100, 101, 102, 103: Euro 104: Engine control unit

105: floc tube 106: ignition floc

107: recess 108: nut

111: cover 111a: bottom edge

112: snap ring 154: oil groove

155: salt passage 156: oil supply passage

157: oil supply hole 223: clip

223A: Plate part 312,313: Camshaft

314,315: High speed cam 316: Camshaft housing

316A: Rocker shaft journal 317: Cam cap

321,322 Shaft part 321A: Killer part

323: Rocker shaft cam 330L: T-type lever-L

331,332: valve drive device 379: valve

389,390: Oil control valve 400: Valve step

401,402: spring retainer 420: pad

420A: curved surface recess 421: reliner

422 line 430 oil ejection hole

432 oil 431 oil pump

501: rocker shaft portion 503,504: rocker arm portion

503a, 504a: Base end 503b, 503b: Front end

503C: Upper surface 503d: Boss

505: roller 506: cam

509a: step head 520: support portion

520a: hole 521: spring

522: bolt 525a: protrusion

532: snap ring 533: toxin spring.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve driving apparatus of an internal combustion engine that performs operation control of an intake valve and an exhaust valve disposed in an automobile engine or the like.

In general, the opening and closing control of the intake valve and the exhaust valve in an automobile engine is set in accordance with the operation state obtained from the engine rotation speed, the depression amount of the accelerator, and the like. In such a valve drive device, it is proposed to change the profile of the cam in order to reduce fuel consumption at low speed and to perform efficient intake and exhaust at high speed depending on the operating state. This is done by changing the opening / closing timing, lift amount, opening period, etc. of the intake valve and exhaust valve at low or high speeds.

That is, in an automotive engine, a high speed cam and a low speed cam are disposed on a cam shaft, and the high speed cam has a cam profile that can obtain a valve opening / closing timing corresponding to a high speed operation, while a low speed cam corresponds to a low speed operation. It has a cam profile to get the valve opening and closing timing. During the engine operation, the high-speed cam or the low-speed cam is selectively used in accordance with the operating state, so that the opening and closing timing of the intake valve and the exhaust valve can be obtained.

Moreover, in such an engine for automobiles, the cylinder rest mechanism which conventionally proposed the cylinder rest mechanism which reduced fuel economy by stopping two cylinders at the time of an idle operation or a low load operation, for example in the case of a four cylinder engine. That is, in the valve driving apparatus, the piston is operated during the idle operation or the low load operation, but the operation of the intake valve and the exhaust valve is stopped so that fuel is not supplied.

In general, the cylinder restraint mechanism for stopping the operation of the intake valve and the exhaust valve is operated by arranging a switching mechanism on the rocker arm and controlling the switching mechanism by hydraulic pressure. In this case, the hydraulic pressure is supplied from the main oil pump of the engine to the switching mechanism via the flow path. However, in order to operate the switching mechanism, high hydraulic pressure cannot be obtained from the main oil pump of the engine only by operating oil pressure. That is, as shown in FIG. 58, there is a minimum required switching hydraulic pressure for operating the switching mechanism, and the working hydraulic pressure from the main oil pump of the engine becomes less than this switching hydraulic pressure. Therefore, the assist oil pump is provided separately from the engine main oil pump, so that the operating hydraulic pressure of the switching mechanism is equal to or higher than the operating required hydraulic pressure.

In Fig. 59, the hydraulic path of the valve driving device is shown in the plane of the cylinder head showing the valve driving device of the engine having the conventional cylinder rest mechanism, and in Fig. 60.

As shown in FIG. 59 and FIG. 60, the cam shaft 1202 is rotatably mounted in the center arm part in the cylinder head 1201, and the cam which is not shown in a predetermined position is integrally formed. The pair of rocker shafts 1203 are rotatably mounted in the cylinder head 1201 in parallel with the camshaft 1202. Each rocker shaft 1203 is equipped with a proximal end of a rocker arm 1206 having a rocker arm 1204 and a switching mechanism 1205, and the rocking ends of the rocker arms 1204 and 1206 are each intake or It opposes the upper end of the exhaust valve 1207. At the end of the cylinder head 1201, an assist oil pump 1208, an accumulator 1209, and an oil control valve 1210 are mounted. The assist oil pump 1208 may be driven by a drive cam 1211 equipped with one end of the cam shaft 1202, and the oil control valve 1210 may be operated by a control signal of the control unit 1212. It is supposed to be.

When the cam shaft 1202 rotates, the rocker arm 1204 and the rocker arm 1206 are shaken by the cam to drive the intake and exhaust valves 1207. At the time of idle operation or low load operation of the engine, two cylinders in four cylinders are stopped for operation. That is, the oil pump 1208 is driven by the drive cam 1211 of the cam shaft 1202, and the hydraulic pressure is stored in the accumulator 1209. On the other hand, the control unit 1212 determines the operating state of the engine based on signals from various sensors, sends a control signal to the oil control valve 1210, and switches it. Then, the hydraulic pressure switches the mechanism of the rocker arm 1206 ( 1205, the driving of the corresponding intake and exhaust valves 1207 is stopped. Accordingly, the engine is operated only by driving of the intake and exhaust valves 1207 corresponding to the rocker arm 1204.

In the valve drive device of the conventional engine described above, a switching mechanism 1205 is attached to a part of the rocker arm 1206 to stop two of the two cylinders during idle operation or low load operation. Therefore, an oil pump 1208, an accumulator 1209, etc. are required, and these must be attached to the cylinder head 1201. Conventionally, as described above, the upper end of the cylinder head 1201 is provided, but a part of the engine protrudes upward. And the cylinder head cover which covers the upper part of the cylinder head 1201 must also be made into the shape which one part protruded upward according to it, and the height of an engine will become high. This not only caused an increase in size, but also made layout difficult when the vehicle was mounted.

An object of the present invention is to solve such a problem and to improve the rigidity of the rocker shaft portion by forming a large diameter portion on the rocker shaft portion and rotatably supporting the rocker arm on the large diameter portion. In the present invention, the oil pump is disposed between the intake camshaft and the exhaust camshaft so that the oil pump is driven by the oil pump installed on the camshaft, and the oil pump and the accumulator are disposed up and down, thereby saving space. It is aimed at making a device compact and making it easy to lay out when a vehicle is mounted.

Moreover, an object of this invention is to provide the valve drive device of an internal combustion engine which reliably supplied the required hydraulic pressure and prevented the malfunction of the valve.

In addition, the present invention applies a spring having a small subordinate force to the high speed rocker arm with a small inertial force, while a spring having a large subordinate force is applied to each of the rocker arms to a low speed rocker arm with a large inertial force It is an object to reduce friction by preventing unnecessary force from working.

Moreover, an object of this invention is to provide the valve drive device of an internal combustion engine which aimed at the improvement of the operability of a switching mechanism at the time of cylinder rest.

According to the present invention, the shape of a cover made of sheet metal to be attached to the engagement hole is also deformed when a load is applied to the engagement hole in the rocker shaft part by setting the pressure in the hydraulic passage in accordance with the operating state of the internal combustion engine. It aims to follow and deform | transform. In addition, the present invention is to supply the hydraulic pressure into the hydraulic passage in accordance with the operating state of the internal combustion engine, to form an oil passage communicating with the hydraulic passage in the rocker shaft portion on the inner circumferential surface of the through hole, and to lock the through hole It aims to have a cylindrical shape without grooves on the outer circumference.

In addition, the present invention forms a lubricating oil passage for supplying lubricating oil to the sliding portions of the cylinder and the plunger constituting the low speed lava spring and the high speed angular spring, so that the lubricating oil is reliably supplied to each of the arm springs, and no wear occurs. The purpose is to prevent malfunction.

It is an object of the present invention to provide a lubrication apparatus for a valve drive mechanism of an internal combustion engine, in which the lubrication passage to the arm spring is common, and the reduction of the processing time is achieved.

An object of the present invention is to supply hydraulic pressure into a hydraulic passage in accordance with an operating state of an internal combustion engine, and to make the lock pin and the engagement hole be in line contact when the lock pin is inserted into the engagement hole of the rocker arm.

According to the present invention, the pressure in the hydraulic passage is set in accordance with the operating state of the internal combustion engine, so that the plunger of the coupling plunger in the rocker shaft is set to selectively integrate the first or second sub-rocker arm with the rocker shaft or Integral release or both of these sub-rocker arms with respect to the rocker shaft. The present invention forms the biasing means insertion portion in the rocker shaft separate from the through-hole in the rocker shaft, thereby setting the diameter of the protrusion of the lock pin of the through-hole to a small diameter. It aims to do it.

It is an object of the present invention to use the same camshaft holder or the like in an engine having only a valve opening / closing timing changing mechanism or an engine having a valve operation stopping mechanism.

An object of the present invention is to chamfer an inlet of a through hole bored in a direction orthogonal to the axial direction of the rocker shaft portion, and to improve the productivity of the rocker shaft portion.

An object of the present invention is to form a concave portion in the floc housing, to closely move the rocking arm swing center toward the center, and to keep the cam shaft and the like close to the engine center to achieve compactness of the cylinder head.

In addition, an object of the present invention is to provide a valve drive system with a variable valve timing mechanism in which the low speed roller is made of a lighter material than the high speed roller, so that the movement characteristics of the valve drive system can be improved with a low cost. .

An object of the present invention is to use an elephantpur structure at a contact portion with a valve of a rocker arm so that the valve clearance can be maintained in an appropriate state without the need for complicated maintenance.

An object of the present invention is to provide an oil ejection hole at one end of the rocker arm directed to the contact surface between the roller and the cam, and to sufficiently lubricate the roller.

The present invention provides a valve drive mechanism of an engine capable of smoothly performing a return from the cylinder rest operation of the valve drive mechanism of the engine that can change the cylinder rest or the valve timing to the entire cylinder operation, or the change of the valve timing. It aims to do it.

An internal combustion engine of the present invention includes a cam shaft on which a cam is mounted, a rocker shaft portion adjacent to the cam shaft and rotatably mounted to a support member of an engine, and integrally formed with the rocker shaft portion to provide the rocker. A lever member formed of a large diameter portion having an outer diameter larger than the outer diameter of the shaft portion, an arm portion formed integrally with the large diameter portion and contacting the valve for intake and exhaust air, and rotatably mounted to the large diameter portion, and swinged by the cam. And a switching mechanism means for engaging or disengaging the rocker arm and the large diameter portion, and hydraulic supply means for operating the switching mechanism means according to an engine operating state by hydraulic pressure. The shaft has a low speed cam and a high speed cam, and the rocker arm is rotatably mounted to each of the large diameter portions on both sides of the arm portion. And a low speed rocker arm and a high speed rocker arm respectively driven by a speed cam and the high speed cam, wherein the low speed rocker arm and the high speed rocker arm are respectively driven by the low speed cam and the high speed cam. And roller bearing means rotatably mounted to the arm and the high speed rocker arm, respectively, wherein the roller bearing means are attached to the respective caps by the first arm spring means mounted to the low speed rocker arm and the support member. Is urged to abut, the lever member is urged to abut the valve by a urging means mounted to the support member, and the urging means is formed so as to act on the valve only in an initial stage of the valve lift. The biasing means is formed by a second arm spring means mounted to the support member, and the biasing means is formed by a leaf spring mounted to the support member. And the biasing means is formed by a lotion spring mounted to the support member, and the first arm spring means biases the spring force that biases the low speed rocker arm to spring the high speed rocker arm. The hydraulic pressure supply means has an oil passage formed in the cam cap that supports the camshaft to supply lubricating oil to the first arm spring, and the roller bearing means has a low speed roller. The bearing means is formed of a lighter material than the high speed roller bearing means, the low speed roller bearing means is made of ceramic, and the high speed roller bearing means is made of iron-based metal.

In addition, the internal combustion engine of the present invention, the cam shaft has a low speed cam and a high speed cam, the rocker arm is rotatably mounted to the large diameter portion and has a high speed rocker arm driven by the high speed cam, The lever member is formed to be driven by the low speed cam, and the high speed rocker arm is provided with a high speed roller bearing means which is driven by the high speed cam and rotatably mounted to the high speed rocker arm. Has a low speed roller bearing means which is driven by a low speed cam and is rotatably mounted to the low speed rocker arm, wherein the high speed rocker arm is formed by the first arm spring means mounted to the support member. A roller bearing means is urged to abut on the high speed cam, and the lever member is loaded by the urging means mounted to the support member. The urging means is formed to act on the valve only in an initial stage of the valve lift, and the urging means is formed by a second arm spring means mounted to the support member. The biasing means is formed by a leaf spring mounted to the support member, and the biasing means is formed by a torsion spring mounted to the support member, and the biasing force of the spring of the first arm spring means The hydraulic pressure supply means has an oil passage formed in the cam cap that supports the camshaft to supply lubricating oil to the first arm spring. And the low speed roller bearing means is formed of a lighter material than the high speed roller bearing means. The low speed roller bearing means is formed of ceramic, the high speed roller bearing means is formed of ferrous metal, and the hydraulic pressure supply means respectively supplies oil to the low speed roller bearing means and the high speed roller bearing means. An oil ejection hole is formed in the rocker shaft to supply the oil ejection hole. The oil ejection hole includes an oil pump at an outlet thereof, and the hydraulic supply means is configured to supply oil pressure from an oil pump of the engine for high speed. And an oil control valve for supplying the oil room of the switching mechanism means of the rocker arm.

In the internal combustion engine of the present invention, the cam shaft has a plurality of low speed cams and a plurality of high speed cams, a plurality of the lever members are disposed, and the part of the rocker arm is provided on the large diameter portions on both sides of the part of the arm. Each of which is rotatably mounted and driven by the low speed cam and the high speed cam, respectively, and the rocker arm of the other part is adjacent to one side of the arm part of the other part driven by the low speed cam, and has a large diameter part of the one side. And a low speed rocker arm mounted on both sides of the arm part and rotatably mounted at both sides of the rocker arm part of the high speed rocker arm. The length of the high-speed rocker arm mounted on one side of the arm of the other part and the image of the large diameter part formed on one side of the arm of the other part; The hydraulic pressure supply means is configured so that the hydraulic pressure from the oil pump of the engine is formed inside the high speed rocker arm on the rocker arm of the part and the other part. A first oil control valve for supplying an oil room and hydraulic pressure from the oil pump to a pressure accumulator and a second oil pump to be formed inside the low speed rocker arm on the part of the rocker arm. And a second oil control valve for supplying to the oil room, wherein the hydraulic pressure supply means ejects oil formed in the rocker shaft to supply oil to the high speed roller bearing means disposed on the high speed rocker arm. And an oil pump at the outlet thereof, and the second oil control valve includes an intake cam shaft and an exhaust cam. It is arrange | positioned between the said shaft, The said 2nd oil control valve is formed on the said accumulator, and the said 2nd oil pump is formed in the said one cam shaft, and the number more than the number of cylinders of valve rest is carried out. The cam is driven by an excitation cam, and the cam is formed at one end of the intake cam shaft.

In addition, the internal combustion engine of the present invention, wherein the switching mechanism means is formed in the engaging hole formed in the rotational surface of the rocker arm for rotating the rocker shaft portion, and inside the rocker shaft portion in the axial direction and the vertical direction of the rocker shaft portion, A projecting position projecting from the receiving position accommodated in the through hole to the engaging hole when the roller bearing means contacts the roller bearing means in the base circle of the cam; And a lock pin which is attached to the protruding mole particles and locks to the engagement hole when the two center axes coincide with each other, an oil room formed between one of the lock pins and the rotating surface of the rocker arm, and the other end of the rock pins. And a compression spring formed between the portion and the rocker arm rotating surface, wherein the switching mechanism means is formed in the lock pin. And a flow path formed in the engagement hole to block the oil room, the flow path communicating with the engagement hole, the cover including a low speed rocker arm rotatably mounted to the large diameter part. It is provided in the engagement hole, the switching mechanism means, the passage formed in the lock pin and in communication with the engagement hole, the hydraulic passage formed in the rocker shaft portion, the passage so as to communicate the passage and the hydraulic passage. And an oil passage formed on an inner circumferential surface of the hole, wherein the oil passage is formed in an annular shape, and the switching mechanism means comprises: a compression spring installed on an end surface of the lock pin opposite to the oil room end surface; Having a spring seat engaged with the compression spring and supported by the rocker arm, the outer diameter of the spring seat being It is formed so as to have a diameter larger than the large diameter of the engagement hole, The switching mechanism means has a spring hole formed separately from the through hole in the rocker shaft portion, the compression spring disposed in the spring hole, The end edge of the through hole is formed by chamfering with a round column cutter.

In addition, the internal combustion engine of the present invention, wherein the switching mechanism means is formed in the engaging hole formed in the rotation surface of the rocker arm for rotating the rocker shaft portion, and in the rocker shaft portion in the axial direction perpendicular to the axial direction of the rocker shaft portion, When the roller bearing means is in contact with the base member of the cam, the center axis thereof protrudes from the accommodation position accommodated in the through hole toward the engagement hole, the through hole eccentric with respect to the center axis of the engaging hole. And a lock pin which is mounted to the projecting position to protrude to the protruding position, and locks to engage with the engaging hole when the through hole overlaps the engaging hole, and an oil room formed between the rear end of the lock pin and the rotating surface of the high speed rocker arm. And a central axis of the engagement hole is more than the center axis of the through hole. A double having two camshafts formed eccentrically toward the means. over. head. An engine of a camshaft type, having a floc tube disposed between the rocker arms, having a recess formed in an inner surface of the floc tube with the rocker arm, wherein the lever member is attached to a contact portion of the valve. An adjustment screw, a pad in linear contact with one end of the adjustment screw, a surface contacting the valve, and a retainer for attaching the pad to the adjustment screw, wherein the hydraulic pressure supply means is configured to supply hydraulic pressure from the oil pump of the engine. It has an oil groove for supplying oil to the journal portion of the cam shaft.

In the above, the first embodiment of the present invention will be described in detail with reference to Figs.

The internal combustion engine of this embodiment is a double with two cam shafts in the cylinder head. over. head. The camshaft engine DOHC is a four-cylinder engine with two valves for intake and two valves for exhaust.

3 to 5 and 11, the cylinder head 11 has a pair of intake camshafts 12 and exhaust camshafts 13 parallel to each other along the longitudinal direction thereof. The low speed cam 14 having a small lift amount and the high speed cam 15 having a large lift amount are formed integrally with each cylinder. The pair of camshafts 12 and 13 is connected to the cylinder head by bolts 18 and 19 in a state of being clamped by the upper portion of the camshaft housing 16 and the plurality of cam caps 17. It is fixed to the upper part of 11, and is rotatably supported by the cylinder head 11.

In addition, the cylinder head 11 has a pair of intake rocker shafts which are parallel to each other along the longitudinal direction thereof and parallel to the pair of cam shafts l2 and 13 in detail. 21 and an exhaust rocker shaft 22 are provided for each cylinder. The pair of rocker shafts 21 and 22 is bolted to the lower portion of the cam shaft housing 16 of the support portion material and bolts 19, ( It is fixed to the lower part of the cylinder head 11 by 24, and is supported by the cylinder head 11 in rotation. In addition, the cylinder head cover 25 is fixed to the upper portion of the cylinder head 11.

Each rocker shaft portion (21) and (22) is a valve drive device which is switched between a valve opening and closing timing for high speed operation and a valve opening and closing timing for low speed operation, a valve opening and closing timing for high speed operation and a valve opening and closing timing for low speed operation. At the same time, it is equipped with a valve driving device that can rest the cylinder during low load operation. That is, as shown in FIG. 11, the upper and lower two-valve valve drive devices 31 of the four cylinders have a cylinder rest mechanism, and the central two-cylinder valve drive device 32 does not have a cylinder rest mechanism. .

Here, the valve drive device 31 with the cylinder restraint mechanism will be described. As shown in FIG. 6, the T-shaped lever 30 of the lever part material integrally forms the proximal end of the arm part 33 which has a substantially T-shape in plan view from the middle arm part of the exhaust rocker shaft part 22. As shown in FIG. The rocker arm 34 for low speed and the rocker arm 35 for high speed are attached to the large diameter part 10 of both sides of the exhaust rocker shaft part 22 as a sub rocker arm.

The adjusting screw 36 is attached to the swinging end of the arm 33 by the adjusting nut 37, and the lower end of the adjusting screw 36 is in contact with the upper end of the exhaust valve 80 described later.

On the other hand, the low speed rocker arm 34 has its proximal end mounted on the large diameter portion 10 of the rocker shaft portion 22 to be rotatably supported, and its swinging end has a roller bearing 38 mounted thereon. The roller bearing 38 is adapted to engage the low speed cam 14. Similarly, in the high speed rocker arm 35, the proximal end thereof is protrudingly attached to the large diameter portion 10 of the rocker shaft portion 22 to be rotatably supported, and the roller bearing 39 is attached to the swinging end thereof. The roller bearing 39 is fitted with the high speed cam 15.

In addition, as shown in FIG. 5, the low speed rocker arm 34 and the high speed rocker arm 35 each have an arm portion 40 opposite to the swinging end portions on which roller bearings 38 and 39 are mounted. And (41) are integrally formed, and arm springs (42) and (43) as first arm spring means act on the arm portions (40) and (41). The arm springs 42 and 43 are constituted by a cylinder 44 fixed to the cam cap 17, a plunger 45 and a compression spring 46, and the tip of the plunger 45 is arm 40. ), (41) are pressed, and the rocker arms 34 and 35 shown on the left side in FIG. 5 are rotated clockwise, and the rocker arms 34 and 35 shown on the right half. Each is clockwise.

Therefore, in general, the low speed rocker arm 34 and the high speed rocker arm 35 are arm springs 42 and 43, and the roller bearings 38 and 39 as roller bearing means are camshafts 12. ) And (13) are in contact with the outer circumferential surface of the low speed cam (14) and the high speed cam (15). When the cam shafts (12) and (13) rotate, the respective cams (14) and (15) The rocker arm 34 and the rocker arm 35 for high speed can be rocked.

As shown in FIG. 7, the low speed rocker arm 34 and the high speed rocker arm 35 are integrated with the rocker shaft portion 22 by switching mechanisms 47 and 48 as switching mechanism means. It is designed to rotate. When the switching mechanism 47 is described, the through hole 51 is formed in the rocker shaft portion 22 along the radial direction at the position corresponding to the low speed rocker arm 34, and the lock pin is formed in the through hole 51. The 52 is mounted in a movable manner and is urged in one direction by the compression spring 54 supported by the spring seat 53. On the other hand, the low speed rocker arm 34 is provided with a fastening hole 55 at a position corresponding to the through hole 51 of the rocker shaft 22, and the fastening hole 55 is provided with a compression hole 54 in the fastening hole 55. The rock pin 52 which was urged so as to be engaged is engaged. The rocker shaft portion 22 is provided with a hydraulic passage 56 communicating with the through hole 51 along the axial direction thereof, and the lock pin 52 communicates with the hydraulic passage 56 and at the same time has an engagement hole ( A flow passage 57 is formed to open toward the engagement with 55.

In addition, when the switching mechanism 48 is demonstrated, the rocker shaft part 22 is provided with the through-hole 58 along the radial direction in the position corresponding to the high speed rocker arm 35, and this through-hole 58 ), The lock pin 59 is mounted on the moving material and is urged in one direction by the compression spring 60. On the other hand, the fastening rocker arm 35 is provided with an engaging hole 61 at a position corresponding to the through hole 58 of the rocker shaft portion 22, and the lock pin 59 is hooked to the compression spring 60. It escapes from the fitting hole 61. In addition, the rocker shaft 22 is provided with a hydraulic passage 62 communicating with the through hole 58 along the axial direction thereof, and communicates with the end opposite to the engagement hole 61 of the through hole 58. The flow path 62 is formed.

In general, as shown in FIG. 9 (a), the low speed rocker arm 34 is engaged with the engagement hole 55 by the lock pin 52 biased by the compression spring 54. As shown in FIG. It is integrated with the rocker shaft part 22, and can rotate with the arm part 33 via this rocker shaft part 22. As shown in FIG. On the other hand, the rocker shaft 35 for the high speed rocker arm 35 is pushed out of the engagement hole 61 by the compression spring 10, and the engagement with the rocker shaft portion 22 is released to release the rocker shaft. It does not rotate integrally with the part 22. Accordingly, the low speed cam 14 and the high speed cam 15 rock the low speed rocker arm 34 and the high speed rocker arm 35, but only the driving force transmitted by the low speed rocker arm 34 moves the rocker shaft 22. It transmits to the arm part 33 through it, and is able to rock this arm part 33. As shown in FIG.

When hydraulic pressure is supplied to each of the hydraulic passages 56 and 62 of the rocker shaft part 22, as shown in FIG. 9 (b), in the low speed rocker arm 34, the hydraulic oil flows in the flow path. It flows to the engagement hole 55 of the through hole 51 via 57, and the lock pin 52 exits from the engagement hole 55 against the opposing force of the compression spring 54. As shown in FIG. Then, the engagement between the low speed rocker arm 34 and the rocker shaft 22 is released so as not to rotate integrally. On the other hand, in the high speed rocker arm 35, the pressurized oil flows to the opposite side of the engagement hole 61 of the through hole 58 via the flow path 63, and the lock pin 59 of the compression spring 60 is removed. It engages with the engagement hole 61 against the counter force.

Then, the high speed rocker arm 35 and the rocker shaft portion 22 are engaged with each other so that both of them can rotate integrally. Accordingly, the low speed cam 14 and the high speed cam 15 rock the low speed rocker arm 34 and the high speed rocker arm 35, but only the driving force transmitted by the high speed rocker arm 35 is the rocker shaft portion 22. FIG. Is transmitted to the arm portion 33 via the) to swing the T-shaped lever 30.

In addition, when hydraulic pressure is supplied only to the hydraulic passage 56 of the rocker shaft portion 22, as shown in FIG. 9C, in the low speed rocker arm 34, the dark oil passes through the through hole 51. The lock pin 52 flows out toward the engagement hole 55, and the lock pin 52 exits from the engagement hole 55, and the engagement between the low speed rocker arm 34 and the rocker shaft part 22 is released so as not to rotate integrally. . On the other hand, in the high speed rocker arm 35, the lock pin 59 is pulled out of the engagement hole 61 by the compression spring 60, and the engagement with the rocker shaft part 22 is canceled, and both are integrated. Does not rotate. Accordingly, the low speed cam 14 and the high speed cam 15 cause the low speed rocker arm 34 and the high speed rocker arm 35 to be misaligned, but the driving force is not transmitted to the rocker shaft portion 22, and the arm portion 33 ) Is not working and is supposed to be in cylinder rest state.

In the valve driving device 32 without a cylinder rest mechanism, as shown in FIG. 10, the T-shaped lever (L) 30L of the lever part material is provided at one end of the exhaust rocker shaft portion 22. As shown in FIG. The low-velocity lava part 63 which has a substantially T-shape in plan view is integrally provided, and the high speed rocker arm 65 is attached to the large diameter part 10 of the other end part. A roller bearing 66 is attached to the swinging end of the low speed rocker arm 64. Then, the roller bearing 66 is mounted on the swinging end of the low speed lava unit 64 so that the low speed cam 14 can be engaged, and the adjustment screw 67 is mounted by the adjustment nut 68. The lower end of the adjustment screw 67 abuts on the upper end of the exhaust valve 80.

On the other hand, the high speed rocker arm 65 is rotatably supported by its proximal end mounted to the rocker shaft portion 22, and the roller end 69 is mounted on the swing end thereof, and the roller bearing 69 It is designed to engage the high speed cam 15.

Moreover, the high speed rocker arm 65 is integrally formed with the arm part 70 on the opposite side to the rocking end on which the roller bearing 69 is mounted, and this arm part 70 has an arm spring as a first arm spring means ( 71 acts to bias the high speed rocker arm 65 in one direction. In addition, the high speed rocker arm 65 can rotate integrally with the rocker shaft portion 22 by the switching mechanism 72. That is, the through hole 73 is formed in the rocker shaft part 22 corresponding to the high speed rocker arm 65 so that the lock pin 74 can be mounted freely and is pushed by the compression spring 75. It is. On the other hand, a fastening hole 76 is formed in the high speed rocker arm 65, and the lock pin 74 is pulled out of the fastening hole 76 by the compression spring 75. The rocker shaft portion 22 is provided with a hydraulic passage 77 communicating with the through hole 73 along the lateral direction thereof, and at the end opposite to the engagement hole 76 of the through hole 73. A communication channel 78 is formed.

In general, the locker arm 65 for the high speed rocker arm 65 is pulled out of the engagement hole 76 by the compression spring 75, and the engagement with the rocker shaft portion 22 is released so that the locker 74 is released. It does not rotate integrally with the shaft portion 22. Therefore, the low speed cam 14 and the high speed cam 15 oscillate the low speed lava portion 64 and the high speed rocker arm 65, or the driving force of the low speed cam 14 is transmitted to the exhaust valve 80. It is possible to swing the exhaust valve 80. When the hydraulic pressure is supplied to the hydraulic passage 77 of the rocker shaft portion 22, in the high speed rocker arm 65, the engagement hole 75 of the through hole 73 is provided via the hydraulic oil passage 78. ) And the lock pin 59 is engaged with the engagement hole 76. Then, the high speed rocker arm 65 and the rocker shaft portion 22 are lowered and can rotate integrally with the rocker shaft portion 22.

Therefore, the high speed cam 15 oscillates the high speed rocker arm 35, and its driving force is transmitted to the exhaust valve 80 via the rocker shaft portion 22 and the low speed lava portion 64, and the exhaust valve ( 80) can swing.

In the above description of the valve drive devices 31 and 32, only the exhaust side has been described, but the intake side has the same structure, and each camshaft 12 is adapted to the valve opening / closing timing of the intake and exhaust. Only the formation positions in the circumferential direction of the cams 14 and 15 of the (13) are made different.

By the way, as shown in FIG. 5, the intake valve 79 and the exhaust valve 80 are mounted to the cylinder head 1l in a self-propelled manner, and the intake port 83 is provided by the valve springs 81 and 82. ) And the exhaust port 84 are closed. Accordingly, the upper and lower ends of the intake valve 79 and the exhaust valve 80 are pressed by driving the arm 33 (low speed rock unit 64), thereby opening and closing the intake port 83 and the exhaust port 84. Thus, it is possible to communicate with the combustion chamber 85.

As shown in FIG. 1, FIG. 2, and FIG. 11, the switching mechanisms 47, (of the valve drive devices 31, 32) are provided at the rear part of the cylinder head (upper part in FIG. 11). A hydraulic control device 86 as a hydraulic supply means for operating the 48 and 72 is provided. The hydraulic control device 86 is composed of an oil pump 87 as a second oil pump, an accumulator 88, an oil control valve 89 for high speed switching, an oil control valve 90 for cylinder rest switching, and the like. have.

The oil pump 87 and the condenser 88 are located between the intake camshaft 12 and the exhaust camshaft 13, and both of them are disposed upside down in parallel, and both of them have a horizontal direction. . That is, the rear side of the cam cap housing 16 and the cam cap 17 of the cylinder head 11, the piston 91 of the oil pump 87 on the upper side to prevent horizontal movement, and also to the compression spring 92 The plunger 96 is secured by a bolt 94 via a cover 93. The plunger 96 is connected to the piston 91 of the oil pump 87 via a compression spring 95. This plunger 96 can be driven by an oil pump cam 97 integrally formed at one end of the intake cam shaft 12.

In addition, the piston 98 of the side pressure gauge 88 is horizontally moved under the side of the cam cap housing 16 and the cam cap 17 by a compression spring 99, and is similarly covered by a cover ( It is fixed by the bolt 94 via 93. In addition, the diameters of the piston 91 of the oil pump 89 and the piston 98 of the accumulator 88 are the same and can be shared. The high speed switching oil control valve 89 and the cylinder rest switching oil control valve 80 as the second oil control valve are attached to the cylinder head 11.

As shown in FIG. 1, FIG. 2, and FIG. 8, the high speed switching oil control valve 89 is directly connected to the main oil pump of the engine (not shown) via the oil passage 100, and at the same time the oil passage 101 is shown. ) Is connected to the hydraulic passage 62 via. In addition, the cylinder rest switching oil control valve 90 is connected to the accumulator 88 and the oil pump 87 and the main oil pump via the flow path 102 and the hydraulic passage 56 through the flow path 103. ) The oil control valves 89 and 90 can be operated by the control signals of the engine control unit 104.

In addition, the switching mechanism 72 of the valve driving device 32 can be operated by the hydraulic control device 86 similarly to the valve driving device 31, and the hydraulic passage 77 of the rocker shaft part 22 is provided. The oil control 89 is connected via a flow path (not shown). As shown in FIG. 2, the cylinder head 11 is provided with a hollow-shaped floc tube 105 standing up in each cylinder, and each of the ignition flops 106 is formed inside each of the flow tube 105. As shown in FIG. ) Is mounted, and its tip portion is directed into each combustion chamber 85.

The operation of the four cylinder engine of the first embodiment will be described below. The engine control unit 104 detects the operating state of the engine according to the detection results of various sensors, and selects a cam profile suitable for the engine when the engine is in a low speed driving state. In this case, the engine control unit 104 selects each oil. A control signal is output to the control valves 89 and 90, and the valves 89 and 90 are closed. Then, hydraulic pressure is not supplied to each of the hydraulic passages 56, 62, and 77, and the valve drive device 31 is driven at a low speed by the lock pin 52, as shown in FIG. 9 (a). The rocker arm 34 and the rocker shaft portion 22 are integrated, and the engagement between the high speed rocker arm 35 and the rocker shaft portion 22 is dismantled. Therefore, when the cam shafts 12 and 13 rotate, the low speed rocker arm 34 is swung by the low speed cam 14, and the driving force is transmitted to the arm part 33 via the rocker shaft part 22. The T-shaped lever 30 swings so that the pair of adjustment screws 36 at the swing end drive the intake valve 79 and the exhaust valve 80. On the other hand, in the valve drive device 32, as shown in FIG. 10, the high speed rocker arm 65 is disengaged from the rocker shaft portion 22, and the cam shafts 12 and 13 are closed. When rotating, the T-hever lever 30L swings by the low speed cam 14, and the pair of adjustment screws 67 of the swing end drive the intake valve 79 and the exhaust valve 80. As shown in FIG. In addition, the intake valve 79 and the exhaust valve 80 are driven by a valve opening / closing ream corresponding to the low speed operation, and the engine is operated at a low speed.

When the engine control unit 104 detects the high speed driving state of the engine, the engine control unit 104 outputs a control signal to each oil control valve 89, 90, and each valve 89, 90. To open. Then, hydraulic oil is supplied to each of the hydraulic passages 56, 62, and 77, and at the time of high-speed running of the engine, the valve drive device 31, as shown in Fig. 9 (b), The lock pin 52 escapes from the engagement hole 55 by the hydraulic oil, and the engagement between the low speed rocker arm 34 and the rocker shaft part 22 is released. Moreover, the lock pin 59 is engaged with the engagement hole 61, and the high speed rocker arm 35 and the rocker shaft part 22 are integrated. Therefore, the high speed rocker arm 35 is rocked by the high speed cam 15, and the T-shaped lever 30 is rocked to drive the intake valve 79 and the exhaust valve 80. On the other hand, in the valve drive device 32, the lock pin 59 is engaged with the engagement hole 76 by the supply pressure oil so that the high speed rocker arm 65 and the rocker shaft part 22 are integrated. Therefore, the T-shaped lever (L) 30L is swung by the high speed cam 15 via the high speed rocker arm 65 to drive the intake valve 79 and the exhaust valve 80. In this way, the intake valve 79 and the exhaust valve 80 are driven by the valve opening / closing timing corresponding to the high speed operation, and the engine is operated at the high speed.

When the engine control unit 104 detects the driving state of the engine or the low load running state, the engine control unit 104 stops two of the four cylinders to reduce fuel economy. That is, the engine control unit 104 outputs a control signal to each of the oil control valves 89 and 90 and opens only the valve 90. Then, the hydraulic oil is supplied to the hydraulic passage 56, and the valve drive device 31 is engaged with the low speed rocker arm 34 and the rocker shaft portion 22 as shown in FIG. 9 (c). Is released. Therefore, the driving force of the low speed cam 14 and the high speed cam 15 is not transmitted to the T-shaped lever 30, and the valve driving device 31 does not operate, and the cylinder rests. On the other hand, in the valve driving device 32, the low speed lava unit 64 is swung by the low speed cam 14 to drive the intake valve 79 and the exhaust valve 80. In this way, the engine is driven by driving only the intake valve 79 and the exhaust valve 80 of the valve drive device 32.

Thus, the valve drive device of the engine of the first embodiment includes an oil pump 87 and an accumulator 88 for operating the switching mechanism 50 of the valve drive device 31, each oil control valve 89, (90) and the like, since the oil pressure control device 86 has disposed the oil pump 87 and the accumulator 88 up and down between the intake cam shaft 12 and the exhaust cam shaft 13, this oil pump The 87 and the accumulator 88 can be efficiently disposed, so that the layout of the cylinder head 11 becomes compact, so that a part of the engine does not protrude upwards or the height of the engine becomes high.

Moreover, since the oil pump 87 made the diameter of each piston 91,98 of the accumulator 88 the same, not only this piston 91,98 is common but also the periphery It can also realize common use and can reduce cost.

In addition, the valve drive device of the engine of the present embodiment is a cylinder resting switch to the low speed hydraulic passage 56 for operating the low speed lock pin 52 in the switching mechanism 47 of the valve drive device 31. The high speed side hydraulic passage 62 for connecting the main oil pump of the engine via the oil control valve 90, the accumulator 88, and the oil pump 87, and operating the lock pin 59 on the high speed side. Since the main oil pump of the engine is directly connected via the high speed switching oil control valve 89, each oil pump is connected to the low speed hydraulic passage 56 and the high speed hydraulic passage 62 in the high speed operation state of the engine. Sufficient pressure oil is supplied from the

This is apparent from the graph of the time change of the high speed side switching hydraulic pressure shown in FIG. 12. By bypassing the oil pump 87 to the high speed side hydraulic passage 62 shown in solid lines on the same plane, the main oil pump is connected. The high speed side switching hydraulic pressure at the time of direct connection is always higher than the high speed switching holding hydraulic pressure. On the other hand, as in the prior art, the high speed switching hydraulic pressure when the main oil pump is connected to the high speed hydraulic passage indicated by the dotted line via the assist pump may be the high speed switching holding hydraulic pressure at the high speed switching. Therefore, as in the present embodiment, when the main oil pump of the engine is directly connected to the high speed side hydraulic passage 62 for operating the high speed side lock pin 59, the low speed lock pin 52 and the high speed rock pin at the time of high speed switching. 59 is surely and quickly operated, a cam fill suitable for the high-speed driving state is selected, and the intake 79 and the exhaust valve 80 can be operated.

Therefore, the malfunction of the intake and exhaust valves can be prevented, so that the internal combustion engine can obtain the output required for high speed operation, and can improve the driveability.

In the valve driving apparatus of the engine of the present embodiment, the force of the compression spring 46 of the low speed arm spring 42 is made larger than the force of the compression spring 46 of the high speed arm spring 43. Is setting. Therefore, as shown in FIG. 13, the inertial force acting on the low speed rocker arm 34 indicated by the dashed line is the spring force of the compression spring 46 of the low speed arm spring 42 indicated by the solid line. At the same time, the inertial force acting on the high speed rocker arm 35 indicated by the double-dotted line follows the spring force of the compression spring 46 of the high speed arm spring 43 indicated by the dotted line, respectively. Only the force acts on the rocker arms 34 and 35 so that the friction is reduced and the operability can be improved.

In the valve driving apparatus of the engine of the present embodiment, the engine is a four-cylinder engine, but as shown in FIG. 14, the cycle dimen- sion of suction, compression, expansion, and exhaust is different for each cylinder. That is, as shown in FIG. 14, the cycles of the two valve driving apparatuses having the cylinder rest mechanism are different, and the intake valve 79 and the exhaust valve 80 are not operated (each cam 14, ( The timing of each of the rocker shafts 34 and 35 by the base circle section of 15) is also out of the intake side and the exhaust side. Therefore, the non-operation timing of both valves 79 and 80 is in the range S1 in one valve drive device, and in the range S2 in the other valve drive device.

At this time, the oil pump 87 is driven by an oil pump cam 97 having two cam portions at its outer circumference, and as shown in FIGS. 14 and 15, one rotational drive of the oil pump cam 97 is performed. Thus, the oil pump 87 performs two cycles of suction-discharge-suction-discharge, that is, (d) → (a) → (b) → (c) → (d). In addition, when the accumulator amount of the accumulator 88 is sufficient by the operation of the oil pump 87, the oil pump 87, as shown in FIG. The piston 91 is not operated by just doing so.

Therefore, the range S1 of one valve drive device is the discharge section of the oil pump 87, that is, the operating state of (c)-(d) of FIG. Also, the range S2 of the other valve driving device is also a discharge section of the oil pump 87, that is, an operating state of (a) to (b) in FIG. Therefore, at the time of switching of the oil control valve 90, the oil pressure required for the switching operation of the lock pin 52 can be obtained quickly, and the rising delay time of the oil pressure of the oil pump 87 becomes cam, and the oil pressure supply becomes quick. A switch for smooth cylinder rest can be performed, and the original purpose of the cylinder rest mechanism can be sufficiently achieved to reduce fuel consumption during idle operation of the engine and low load operation.

According to the valve drive device of the internal combustion engine of the present invention, one or more cylinder rest mechanisms are provided in the multi-cylinder internal combustion engine by providing a switching mechanism operated by hydraulic control between the rocker shaft and the rocker arm to stop the valve drive during low speed operation. Since the oil pump is connected to the cylinder rest mechanism via the oil rest valve for cylinder rest switching, and the oil pump cam for driving the oil pump is formed at one end of the cam shaft more than the number of cylinders resting. When the oil control valve is operated at the cylinder rest, the required hydraulic pressure is supplied sufficiently, so that the lock pin can be operated quickly, so that there is no delay of the hydraulic oil rise of the assist oil pump, and switching for smooth cylinder rest can be performed. As a result, the operability of the switching mechanism during cylinder rest can be improved. The original purpose of the cylinder rest mechanism, which aims to reduce fuel consumption, is fully achieved. In addition, the capacity of the accumulator can be reduced or eliminated, and the cost can be reduced and the space can be reduced.

Next, the configuration of the low speed rocker arm 34 will be described in more detail with reference to FIGS. 16 to 22. As shown in FIGS. 16 and 17, the cover 111 is fitted into the engagement hole 55, and the cover 111 is fixed to the low speed rocker arm 34 by the snap ring 112. have. The lid 111 is made of sheet metal, and as shown in Fig. 18, the edge 11la of the bottom surface is inclined at an angle α. The upper side of the lid 111 is fixed to the low speed rocker arm 34 by the snap ring 112 shown in FIG.

When the low speed rocker arm 34 is rotated by the low speed cam 14, the engagement hole 55 is repeatedly loaded by the lock pin 52, and the elastic deformation is repeated. Since the cover 111 is made of sheet metal, the cover 111 is deformed in accordance with the deformation of the engagement hole 55, so that the cover 111 does not fall out or cracks or gaps are generated in the low speed rocker arm 34.

As shown in FIG. 16, FIG. 20, and FIG. 21, the oil passage 113 which guides the oil pressure from the hydraulic passage 56 to the flow path 57 is formed in the inner periphery of the through-hole 51. FIG. It is. Therefore, the lock pin 52 can be made into a round pillar shape, the breakage of the lock pin 52 can be prevented, and reliability can be improved.

As shown in FIG. 20, the diameter T of the spring sheet 53 of the lock pin 52 is set larger than the diameter t of the head part inserted into the engagement hole 55. As shown in FIG. As a result, as shown in FIG. 22, even when the low speed rocker arm 34 is reversed to face the spring seat 3 and the engagement hole 55 at the start of assembly, the compression force of the compression spring 54 is reduced. The spring seat 53 is not fitted into the engagement hole 55 by this.

Therefore, since the cover 111 made of sheet metal is attached to the engagement hole 55, even if the engagement hole 55 deforms, the cover 111 follows the deformation and deforms, and the cover 111 is pulled out or low speed. Cracks and gaps do not occur in the reactor arm 34. For this reason, oil leakage does not occur and there is no possibility that the low speed rocker arm 34 will be damaged.

Moreover, since the cover of the engagement hole is formed of sheet metal, the cover is deformed in accordance with the deformation of the engagement hole, so that the cover does not come off or cracks or gaps occur in the sub-rocker arm. For this reason, oil leakage does not generate | occur | produce and there is no possibility of breaking of a sub rocker arm.

In addition, since the oil passage communicating with the hydraulic passage is formed on the inner circumferential surface of the through hole, the lock pin can be formed into a round column without groove in the outer circumference. For this reason, the rigidity of a lock pin increases, breakage is prevented, and reliability improves.

In addition, since the diameter of the lock means support base of the lock pin is set to be larger than the diameter of the head portion, even if the support means support seat faces the engagement hole by the rotation of the sub-locker arm, the support means support seat is fitted to the engagement hole. There is no work. For this reason, the sub rocker arm is not locked at the inverted position.

Next, the lubrication flow path for supplying lubricating oil to the cam journal portion of the intake cam shaft 12 and the exhaust cam shaft 13 and the sliding portions of the low speed arm spring 42 and the high speed arm spring 43 will be described in detail. do.

As shown in FIGS. 4 and 5, the oil passage 151 is formed along the longitudinal direction (the direction perpendicular to the paper surface in the east view) on the exhaust side (left side in the figure) of the cylinder head 11. The oil passage 151 is connected to a main oil pump of the engine. In the intake camshaft 12 and the exhaust camshaft 13, the camshaft housing 16 is hold | maintained by the cam cap 17. As shown in FIG. As shown in detail in FIG. 25, the cam cap 17 forms an intake and exhaust material-integrated type, and has a semicircular exhaust side and an intake bearing portion for supporting the intake cam shaft 12 and the exhaust cam shaft 13, respectively. 152 and 153 are formed, and an oil groove 154 connecting the bearing portions 152 and 153 is formed on the lower surface. In addition, the bearing portion 153 on the exhaust side and the oil passage 151 are connected to each other by a connecting passage 155 formed through the cylinder head 11 and the cam shaft housing 16 along the vertical direction. .

Therefore, the engine oil as lubricating oil supplied from the main oil pump of the engine to the oil passage 151 is supplied to the bearing portion 153 on the exhaust side via the respective connecting passages 155, and to the oil groove 154. It is supplied to the bearing part 152 of the intake side by this.

23 to 25, the proximal end communicates with the intermediate portion of the oil groove 154 in the cam cap 17, and the distal end is between the low speed arm spring 42 and the high speed arm spring 43. As shown in FIGS. An extending oil supply passage 156 is formed. An oil supply port 157 is formed in the outer peripheral portion of the low speed arm spring 42 and the cylinder 44 in the high speed arm spring 43 so that the tip end of the oil supply path 155 communicates with each other.

Therefore, the engine oil flowing into the connecting passage 155 is supplied to the low speed arm spring 42 and the high speed arm spring 43 after passing through the oil supply path 156, and the cylinder 44 from each oil supply port 157. And the sliding part of the plunger 45 is provided.

As described above, in the valve driving apparatus of the engine of the first embodiment, the semicircular bearing portions 152 of the intake cam shaft 12 and the exhaust cam shaft 13 are formed at the same time the oil passage 151 is formed in the cylinder head 11. Oil grooves 154 communicating with and 153 are connected to each other by a connecting passage 155, and the oil grooves 154 and the oil of the low-speed and high-speed arm springs 42 and 43 are connected. An oil supply passage 156 is formed to connect the supply port 157. Therefore, the engine oil supplied from the main oil pump of the engine to the oil passage 151 flows into the oil groove 154 through each connection passage 155, and the engine oil passes through the oil supply passage 156. It is supplied to the sliding part of the cylinder 44 and the plunger 45 from each of the oil supply ports 157 of the low speed arm spring 42 and the high speed pressure spring 43, and the intake cam shaft 12 and the exhaust cam shaft Engine oil can be easily supplied to each of the bearing portions 152 and 153 of (13), and the oil supply path is also one, so that the processing can be simplified, and the number of machining operations can be reduced. No wear and tear of (42) and (43) can be prevented.

Next, the relationship between the through holes 51, 58 and the engagement holes 55, 61, which is a modification of the first embodiment, will be described in detail with reference to Figs. 7 and 26 through 28. .

When the base members of the cams 14 and 15 face the roller bearings 38 and 39, the through holes 51 and 58, that is, the lock pins 52 and 59, engage with the engaging holes ( 55 and 61 face each other. The center S of the engaging holes 55 and 61 and the center P of the lock pins 52 and 59 are shifted by a shift amount T, and the rocker arm portions 34 and 35 are cams 14 and 15. The centers S of the engaging holes 55 and 61 are shifted to the front in the rotation direction when the cam surface is rotated. The shift amount T is half of the gap between the engagement holes 55 and 61 and the lock pins 52 and 59.

That is, T = ∮D-∮d) / 2

However, 는 D is the diameter of the engagement holes 55, 61, and d is the diameter of the lock pins 52, 59.

Therefore, when the lock pins 52 and 59 protrude into the engagement holes 55 and 61, as shown in FIG. 28, the lock pins 52 and 59 hang in the range of length 1. As shown in FIG. The line is in line contact with the inner circumference of the alignment holes 55 and 61, and the lock pins 52 and 59 are in a state of receiving a load from the line.

In the above mechanism, the projecting immersion operation of the lock pin is made such that the through hole on the rocker shaft side and the engaging hole on the rocker arm are made to coincide only when facing the base circle of the cam of the roller bearing on the rocker arm. The shape position of the lock pin does not change unintentionally, whereby a highly reliable drive force transmission control can be performed.

In addition, when the lock pin and the engagement hole face each other, the center position of the engagement hole is moved forward in the rotational direction of the rocker arm. Therefore, when the lock pin protrudes, the locking pin engages with the engagement hole in line contact with each other. At the same time, it is possible to suppress the loosening of rocker arms.

Next, based on FIG. 29, FIG. 30, and FIG. 31, the modification of the support upward of a lock pin is demonstrated in detail.

The spring hole as the urging means inserting portion in which the compression springs 54A and 60A as the urging means are disposed in the rocker shaft portion 22 on the hydraulic passages 56 and 62 of the through holes 51 and 58. 51A and 58A are formed, and the through-holes 51 and 58 and the spring hole 51A and 58A are provided in parallel.

The lock pins 52A and 59A have the engagement holes 55 and 61 as their heads, and the flanges in the longitudinal direction of the through holes 51 and 58 in the long direction and the opposite ends of the flanges. 52B and 59B are formed. Clips 223 are attached to the flanges 52B and 59B, and plate portions 223A protruding into the spring holes 51A and 58A are disposed in the clips 223. Compression springs 54A and 60A are disposed on the upper surface of the plate portion 223A.

Accordingly, the lock pins 52A and 59A are normally urged downward in FIG. 29 so that the head is immersed into the through-holes 51 and 58 from the engagement holes 55 and 61. The type position is set.

Further, in this modification, the biasing direction of the compression spring 54A biasing the lock pin 52A is opposite to the biasing direction of the compression spring 54 biasing the lock pin 52 of the first embodiment. In this modified example, the hydraulic pressure supply to the hydraulic passage 56 described in the first embodiment is reversed.

Since the compression springs 54A and 60A were disposed in the spring holes 51A and 58A, the lock pins 52A and 59A had a simple round column shape, and the through holes 51, The diameters of the protrusions of the lock pins 52A and 59A at 58 can be the minimum diameters at which the lock pins 52A and 59A can move. For this reason, the torsional rigidity of the rocker shaft part 22 improves, and the processing of the lock pins 52A and 59A becomes easy.

In addition, in the above modification, the structure of the state where the normal positions of the lock pins 52A and 59A are immersed in the through holes 51 and 58 of the rocker shaft portion 22 has been described. It is also possible to make it engage with the engaging holes 55 and 61 of the rocker arms 34 and 35. FIG.

Next, a valve drive device according to a second embodiment of the present invention will be described.

As shown in FIG. 32, the valve driving device 332 without cylinder rest integrally mounts the proximal end of the arm portion 330 having the color portion 321A on the rocker shaft portion 321 to form a T-shape. A lever (L) 320L is formed, and the high speed rocker arm 365 is detachably mounted adjacent thereto. The other end of the roller bearing portion 366 is provided with an adjusting nut 368 therefor at a portion abutting the step end of the valve.

The T-shaped lever (L) 330L, which is operated at low speed startup, has a roller bearing 366 engaged with the cam for low speed. The high speed rocker arm 365 is provided with a roller bearing 369 connected to the high speed cam.

The length from the end face of the color portion 321A of the valve drive device 332 to the end face of the high speed rocker arm 365 is "L".

T-shaped lever (L) 330 is formed, and both sides of the rocker arm 334 for the low speed and the rocker arm 335 for the high speed are coupled to and detachable from the rocker shaft part 322. Is done. The other end of the arm part 330 is provided with the adjustment nut 337 in the part which abuts on the step end of a valve. The low speed rocker arm 334 and the high speed rocker arm 335 are provided with roller bearings 338 and 339 at the tip, and the roller bearings 338 and 339 are in contact with the low speed cam and the high speed cam. do.

The depth from the end face of the low speed rocker arm 384 of the valve drive device 331 to the end face of the high speed rocker arm 335 is (L) as in the valve drive device 331.

4 and 33 to 36 show camshaft housings in which the valve driving devices 331 and 332 are supported. A camshaft housing 316 is mounted on the cylinder head 11. . On the lower surface of the camshaft housing 316, rocker shaft journal portions 316A are formed at regular intervals along the crankshaft direction of the engine, and in the adjacent journal portion 316A, the valve drive device 331 or ( Both ends of the rocker shafts 321 and 322 of 332 are fitted and held by mounting the rocker shaft cap 323 to the camshaft housing 316.

In addition, camshafts 312 and 313 are mounted on the upper surface of the camshaft housing 316 and are held by the cam cap 317. The cam shafts 312 and 313 have roller bearings 366 on the rocker shafts 321 and 322 of the valve driving devices 331 and 332, and cams for high speed and high speed. 314 and 315 are formed.

33 and 34 show a state in which only the valve driving device 332 without a cylinder rest without the valve operation stop mechanism is mounted. In Fig. 33, the right side represents the intake side and the left side represents the exhaust side. 37, an arm spring 37l for keeping the high speed rocker arm 365 in contact with the high speed cam 315 at the time of separation from the cam shaft portion 322 of the high speed rocker arm 365 is attached to the cam cap 317. Is maintained. The coupling of the high speed rocker arm 364 with the camshaft 322 is performed by, for example, oil pressure and spring force, and an oil control valve 389 for it is mounted at the end of the camshaft housing 316. 34 shows the contact state between the adjustment nut 368 at the end of the rocker arm 365 and the step end of the valve 379 in combination with the plane of the valve driving device 332 and the adjustment nut 368. The center of the valve 379 is centered by d _{1 with} respect to the center.

35 and 36 show the engines replaced with those of the valve driving apparatus with the cylinder rest mechanism in order to make the cylinders rest the first and fourth cylinders. The camshaft housing 316, rocker shaft cam 323, etc. can be shared as it is. However, at the time of cylinder rest, since the arm spring 371 needs to be applied to the low speed rocker arm 334, two cam caps 317 are provided with the arm springs 371 and thereon. It is necessary to change to one pair 317a. Moreover, since the oil control valve 390 for cylinder rest is needed, it is attached to the edge part of the camshaft housing 316, etc.

FIG. 36 shows the contact state between the adjustment nut 368 at the end of the rocker arm 330 and the step end of the valve 379 together with the plane of the cylinder restraint valve driving apparatus 331. In this embodiment, d _{3 is} shifted to the opposite side as shown in the drawing. This is caused by increasing the thickness of the low speed rocker arm 334 to improve rigidity while shifting to the opposite side. All. Of course, there is no difference between the opening and closing functions of the valve.

According to the rocker arm supporting structure according to the second embodiment, the axial dimension of the rocker arm assembly is the same as that with or without the valve operation stop mechanism, so that the cam shaft holder and the like can be shared. It is advantageous in terms of cost.

Next, the housing of the ignition plug will be described in detail on the basis of Figs. 7, 10, 11, 40 and 41. [0036] The cylinder head 11 has 1 parallel to each other along its longitudinal direction. The pair of hop cam shafts 12 and the exhaust cam shafts 13 are disposed so that each of the cylinders has a low speed cam 14 having a small lift amount and a high speed cam 15 having a large lift amount integrally. It is. The pair of cam shafts 12 and 13 are rotatably supported by the cylinder head 11 in the state of being clamped by the upper portion of the cam shaft housing 16 and the plurality of cam caps 7.

In addition, the cylinder head 11 has a pair of intake rocker shafts 21 and exhaust which are parallel to each other along the longitudinal direction thereof and parallel to the pair of cam shafts 12 and 13. The furnace shaft shaft portion 22 is disposed for each cylinder. The pair of rocker shaft portions 2l and 22 are clamped by the lower portion of the camshaft housing 16 and the plurality of rocker shaft cams 23 to be rotatably supported by the cylinder head 11. .

Each rocker shaft portion (21) and (22) has a valve drive device which is switched between a valve opening and closing timing for high speed operation and a valve opening and closing timing for low speed operation, a valve opening and closing timing for high speed operation and a valve opening and closing timing for low speed operation. It is equipped with a valve drive that can be switched at the same time and can rest the cylinder during low load operation. That is, as shown in FIG. 11, the upper and lower two-valve valve driving devices 31 of the four cylinders have a cylinder rest mechanism, and the central two-cylinder valve driving device 32 has a cylinder rest mechanism. not.

The valve drive devices 31 and 32 have the same configuration on the intake side and the exhaust side. As shown in Figs. 7 and 10, the valve drive device 32 having no cylinder rest mechanism is a rocker. The arm portion 33 is integrally formed on the shaft portion 22, and the high speed rocker arm 35 is mounted adjacent to the rocker shaft portion 22 so that the arm portion 33 can be separated from the rocker shaft portion 22. The swing end is in contact with the upper end of the valves 79 and 80, and the roller bearings 38 and 39 disposed on the arm 33 have a low-speed cam 14 on the cam shaft 13 described above. High speed cam l5 is fitted.

In this engine, the ignition plug 106 is mounted at the position corresponding to the center of each cylinder of the cylinder head 11, with the combustion chamber 85 facing the leading end. The ignition flash 106 is covered with a pipe-shaped ignition flash tube 105, the upper portion of which is held by a cylinder head cover 25.

The ignition plug tube 105 is located between the arm 33 of the valve drive device on the intake side and the exhaust side. Therefore, as shown in FIG. 40, FIG. 41, the recessed part 107 is formed in the part which faces the arm part 33 in the trunk | drum. By forming the concave portion 107, the swinging center of the arm portion 33 can be approached further toward the center without interfering with the ignition plug tube 105, so that the cam shafts 12 and 13 are also the engine center. Approach, the upper width of the cylinder head can be made smaller.

The recessed portion 107 is constituted by flattening a portion of the pipe-shaped ignition plug tube l05, but the inner dimension L is a tool detachable from the nut portion 108 of the ignition plug 106. Take as large as possible to pass.

In addition, the present embodiment is not limited to an engine provided with a valve driving apparatus, and can be applied to a normal engine, and even in that case, since the arrangement intervals of the peripheral members can be filled, the compactness of the cylinder head can be achieved. have.

According to the housing of the ignition plug according to the present invention, the recessed portion is formed in the pipe-shaped housing so that the gap with the peripheral agent such as the rocker arm can be filled as much as possible, thereby making the cylinder head compact. Moreover, since it is not necessary to shave a part of rocker arms etc. in order to achieve compactness, the rigidity of each member can be maintained.

Next, the mounting structure of the low speed side roller bearings 38, 66, and the high speed side bearings 39, 69 will be described based on FIG. 7, 10, 42, 43, 44. FIG. It explains in detail.

First, in the valve driving apparatus 32 without cylinder rest, the roller bearing 66 which can contact the low speed cam 14 is provided in the intermediate part of the T-type lever L 30L. The roller bearing 66 is rotatably supported on the shaft 68A supported by the intermediate portion of the T-shaped lever (L) 30L so as to rotate smoothly via the roller bearing portion 66B. .

On the other hand, the high speed rocker arm 65 is supported to be rotatable with respect to the rocker shaft portion 22 at one end, and the roller bearing which can abut the high speed cam 15 at the other end thereof ( 69). The roller bearing 69 is also rotatably supported on the shaft 69A supported by the rocker arm 65 so as to be able to rotate smoothly via the roller bearing portion 69B.

By the way, similarly to FIG. 5, also in FIG. 42, valve springs 81 and 82 of the valve steps 400 and 80 of the valves 80 and 79 are interposed. As a result, the valves 79 and 80 are biased toward the upper end of the valve direction 400 in the closing direction. Accordingly, the T-shaped lever (L) 30L is also biased toward the cams 14 and 15 through the valve springs 81 and 82, and the bias force of the springs 81 and 82 is applied. It acts as a return force when the T-shaped lever (L) 30L swings.

On the other hand, the rocker arm 65 receives the force of the valve springs 81 and 82 by integrating the T-shaped lever (L) 30L in the linking mode, but does not receive it in the non-linking mode. It is necessary to provide a means for biasing toward the cams 14 and 15 so that the rocker arm 65 can follow the cams 14 and 15. Therefore, the rocker arm 65 is provided with an arm spring 71 as shown in FIG.

In addition, the spring force of the compression spring 46 is set so as to counter the inertial force acting on the high speed rocker arm 65. That is, if the inertial force acting on the high speed rocker arm 65 is as shown by the curve a2 in FIG. 45, the spring force of the compression spring 46 is correspondingly indicated by the curve b2 in FIG. As can be set relatively small.

In this valve drive system, the low speed roller bearing 66 is formed of a material that is lighter than the high speed roller bearing 69. That is, while the high speed roller bearing 69 is formed of a general iron-based metal material or the like, the low speed roller bearing 66 is formed of a material which is light in weight such as ceramic and has required wear resistance.

By the way, the valve clearance of the valves 79 and 80 of the T-shaped lever L 30L (ie, in the non-linked mode, the T-shaped lever L 30L is driven through the low speed cam 14). The valve clearance of the valves 79 and 80 of the T-shaped lever (L) 30L can be adjusted by the adjusting screw 67. However, in the interlocking mode, the T-type lever L ( The valve clearance when the 30L) is integrally moved with the rocker arm 65 is different from that in the non-linked mode, so that the valve clearance in the linked mode (i.e. at high speed) can be adjusted by some means. Doing.

In addition, adjustment of the valve clearance circulated here is mainly an initial adjustment at the time of installation.

Therefore, in this valve drive system structure, a plurality of types of high-speed roller bearings 69 having different outer diameters are prepared, so that the valve clearance of the T-shaped lever (L) 30L is appropriate in the linking mode so as to be suitable. As shown in FIG. 44, the high speed roller bearing 69 is fitted to the rocker arm 65. As shown in FIG.

As a result, in the valve driving apparatus without cylinder rest, since the low speed roller bearing 66 is formed of a lightweight material at low speed and at high speed, the T-shaped lever L by the low speed roller bearing 66 is obtained. The increase in the weight of the valve drive system of 30L is suppressed to the slightest, and the movement characteristic of the valve drive system (that is, the performance of appropriately driving the valve corresponding to the cam profiles of the cams 14 and 15) is improved.

Therefore, the valves 79 and 80 are always appropriate, and grooves are performed at appropriate timings in the combustion chamber of each cylinder, so that engine performance can be improved.

In addition, since the low speed roller bearing 66 is formed of a lightweight material, the inertial weight of the series of valve springs 81 and 82 attached to the valves 79 and 80 is also reduced, so that the valve spring 81 ) And (82) can also be set to have a smaller spring force, that is, a smaller and lighter weight, thereby reducing the friction of this portion and improving the engine performance.

In this valve drive opening structure, one clearance in the interlocking mode (here low speed) is adjusted by the adjustment screw 67, and the valve clearance in the interlocking mode (here high speed) is a high speed roller bearing 69. Since the initial diameter of the valve clearance is appropriate, the adjustment can be performed reliably and easily.

Since the T-shaped lever (L) 30L and the rocker arm 65 are attached to the roller together, wear due to contact with the cams 14 and 15 is extremely small, and the above-described valve clearance The change over time can be almost ignored, and in a maintenance-free state, it is possible to maintain good operation of the valve drive system.

In addition, as described above, the valve clearance is adjusted by selecting the outer diameter of the high speed roller bearing 69, and it is necessary to prepare a plurality of types of different outer diameters for the high speed roller bearing 69, and as such high speed rollers The manufacturing cost of the bearing 69 is likely to rise. However, the high speed roller bearing 69 is formed of a metal material such as iron-based steel which can be manufactured at a relatively low price, so that the cost increase can be suppressed to be small. On the other hand, the low speed roller bearing 66 is formed of a material such as a relatively expensive ceramic, but only one type of the low speed roller bearing 66 needs to be prepared, and thus the low speed roller bearing 66 The increase in cost can also be suppressed.

Next, in the valve driving device 31 with a cylinder restraint mechanism, the rocker arms 34 and 35 are all rocker arms with rollers, and the low speed rocker arms 34 are rocker shafts at one end thereof. It is supported to be rotated with respect to the part 22, and at the other end, the low speed roller bearing 38 which can contact the low speed cam 14 is provided. This low-speed roller bearing 38 is rotatably supported so as to be able to rotate smoothly through the bearing 38B on the shaft 38A supported by the rocker arm 34.

On the other hand, the high speed rocker arm 35 is supported to be rotatable with respect to the rocker shaft portion 22 at one end thereof, and the high speed rocker arm 35 can contact the high speed cam 15 at the other end thereof. The roller bearing 39 is provided. The roller bearing 39 is also rotatably supported on the shaft 39A supported by the rocker arm 35 so as to be able to rotate smoothly via the bearing portion 39B.

Also in this valve drive system, the low speed roller bearing 38 is formed of a material that is lighter than the high speed roller bearing 39. That is, while the high speed roller bearing 39 is formed of a general iron-based metal material or the like, the low speed roller bearing 38 is formed of a material having lightweight and required wear resistance such as ceramic.

By the way, the same arm springs 42 and 43 are provided in the rocker arm 34 for low speed and the rocker arm 35 for high speed for the following reasons.

As described above, the arm spring 42 of the rocker arm 34 on the low speed side among the rocker arms 34 and 35 is formed in the high speed rotation area after the valve driving mode is switched to the high speed driving mode. Although followability is required, the inertial force acting on the rocker arm 34 for the low speed becomes large in accordance with the speed, and also large due to the narrow cam profile of the valve opening angle of the low speed cam 14. For this reason, it is generally necessary to set the spring force of the compression spring 46 of the arm spring 42 so that it may cover this.

That is, generally, the inertia force (refer to curve a1 of FIG. 45) of the low speed rocker arm 34 is large compared with the inertia force (refer to curve a2 of FIG. 45) of the high speed rocker arm 35, and is the lowest in each. The required arm spring force is also required to be larger than that for the low speed (see straight line b1 in FIG. 45) than that for the high speed (see straight line b2 in FIG. 45).

However, the low speed roller bearing 38 provided on the rocker arm 34 is made of a material that is lighter than the high speed roller bearing 39 provided on the rocker arm 35 for high speed. The weight of 34 is reduced, and the inertial force of the rocker arm 34 is reduced. That is, in this rocker arm 34, the inertia force is reduced by the light weight of the low speed roller bearing 38, and the inertia force characteristic as shown by the curve a3 in FIG.

Therefore, the minimum required arm spring force for the rocker arm 34 for the low speed becomes as indicated by the curve b3 in FIG. 45, and is smaller than that of the conventional one (refer to the gig line b1 in FIG. 45). (See straight line b2 in FIG. 45).

For this reason, even if the arm spring force of the characteristic shown by this straight line b3 is set to the rocker arm 34 for high speeds, the excessive amount of the arm spring force applied to the high speed side will be extremely small.

Therefore, even if the same arm springs 42 and 43 are provided in the rocker arm 34 for the low speed and the rocker arm 35 for the high speed, no significant loss is caused.

Rather, by installing the same arm springs 42 and 43 on both rocker arms 34 and 35 in this way, the cost reduction by the common use of parts and the wrong weave of the arm springs 42 and 43 You can expect great benefits, such as avoiding mismatches.

By the way, the clearance between the valves 79 and 80 of the T-shaped lever 30 can be adjusted by the adjustment screw 36. However, this adjustment is performed by the T-type lever 30 using a rocker arm for a low speed. 34, but in accordance with the low speed mode which does not link with the rocker arm 35 for high speed.

On the other hand, since the T-type lever 30 is not associated with the low speed rocker arm 34, in the high speed mode in which the T-type lever 30 is associated with the high speed rocker arm 35, the valve clearance of the T-type lever 30 is reduced in the low speed mode. Since it is different from the above, it is easy to make it possible to adjust the valve clearance in the linked mode (i.e., at high speed) by the means of some means (primarily when squeezing).

Therefore, in this valve drive system structure, a plurality of different types of outer diameters are prepared as the high speed roller bearings 39, and a suitable outer diameter is selected so that the valve clearance of the T-type lever 30 is appropriate in the high speed mode. The high speed roller bearing 39 is attached to the rocker arm 35 (see also FIG. 44).

Since it is formed of a material, the weight of the low speed rocker arm 34 is reduced by that much, and the inertia force of this rocker arm 34 is reduced.

Therefore, the arm spring force required for the rocker arm 34 for the low speed is the lowest as shown by the straight line b3 in FIG. 45, and is smaller than the conventional one (see the straight line b1 in FIG. 45). (Refer to the straight line b2 in FIG. 45), the friction of this portion is reduced, and the engine performance can be improved.

Moreover, although the same arm springs 42 and 43 are provided in the rocker arm 34 for low speed, and the rocker arm 35 for high speed, in this setting, the rocker arm for high speed ( 35) does not cause great frictional loss, and it brings great advantages such as Ohiri, cost reduction by the common use of parts, and avoiding wrong squeeze of wrong springs (42) and (43). Can be. Of course, since the low-speed roller bearing 38 is formed of a lighter material than the high-speed roller bearing 39, the increase in the weight of the valve driving system of the T-type lever 30 by the low-speed roller bearing 38 It is suppressed by a trivial thing, and the movement characteristic (performance of driving a valve appropriately corresponding to the cam profile of the poles, cams 4 and 15) improves.

Therefore, the valves 79 and 80 are always driven properly, and grooves are performed at an appropriate timing in the combustion chamber of each cylinder, so that engine performance can be improved.

Also in this valve drive system structure, the valve clearance in the low speed mode is adjusted by the adjustment screw 36, and the valve clearance in the high speed mode is adjusted by selecting the outer diameter of the roller bearing 39 for high speed. There is an advantage that the initial setting can be made surely and easily as appropriate.

Since the rocker arms 34 and 35 are provided with rollers together, wear due to contact with the cams 14 and 15 is extremely small, and the change in the valve clearance over time is almost negligible. It is possible to maintain good operation of the valve drive system in a state of maintenance.

In addition, as described above, the valve clearance is adjusted by selecting the outer diameter of the high speed roller bearing 39, and it is necessary to prepare a plurality of types of different outer diameters as the high speed roller bearing 39. The manufacturing cost of the bearing 39 tends to rise. However, since the roller bearing 39 for high speed is formed from metal materials, such as iron type, which can be manufactured with a comparatively cheap value, cost increase can be suppressed with a small thing. On the other hand, the low speed roller bearing 38 is made of a material such as a relatively expensive ceramic, but only one type of the low speed roller bearing 38 needs to be prepared. The increase of can also be suppressed.

In addition, the structure of a mode switching means, the structure of a main rocker arm, a sub rocker arm, etc. are not limited to the thing of this embodiment.

Next, a modification of the adjustment screws 36 and 67 will be described based on FIG. 46. FIG.

An elephant structure E is formed in the contact portion between the adjustment screws 36 and 67 and the valves 79 and 80.

For example, the adjustment screw 36 will be described. As shown in FIG. 46, the adjustment screw 36 has an elephant structure E formed at the lower end of the adjustment screw main body 36A on the arm 33. have.

The elephant structure E includes an adjusting screw body 36A, a pad 420 in contact with the adjusting screw body 36A, and a retainer that restrains the pad 420 from being separated from the adjusting screw body 36A. It consists of 42l.

A diameter enlarged portion 36B is formed below the adjusting screw body 36A, and a curved projection 36D is formed at the lower end of the diameter enlarged portion 36B. In addition, the curved shape recessed part 420A is formed in the pede 420. As shown in FIG. The curved concave portion 420A and the curved upper projection portion 36D are in line contact with a line 422 as shown in FIG. The lower surface of the pad 420 is in surface contact with the ends of the steps 79A and 80A of the valves 79 and 80. The retainer 421 is attached to fit the outer circumference 36C of the diameter-expanded portion 36B of the adjustment screw body 36A.

By such line contact between the curved concave portion 420A and the curved protrusion 36D and the surface contact between the pad 420 and the valve 80, wear of the contact portion is greatly suppressed.

Since the contact part of the adjustment screw 67, the valves 79, and 80 is comprised similarly, description is abbreviate | omitted.

In addition, the line contact between the curved upper projection 36D of the adjusting screw body 36A and the curved recess 420A of the pad 420 and the surface contact between the pad 420 and the valves 79 and 80. As a result, point contact of this portion is avoided, and wear of the contact portion is significantly suppressed.

This reduction in wear makes it possible to almost ignore the change in the valve clearance over time, and maintain a good operation of the valve drive system in a maintenance-free state.

That is, when each rocker arm 34, 35, 64, 65 is in a phase state in contact with the base member of the cam l4, 15, two sets of rocker arms 34, 35 are provided. The rotational phases of the (64) and (65) reliably coincide with each other, so that the locking pins 52, 59, and 74 can perform the insertion operation smoothly, so that the valve timing can be switched by the variable valve timing mechanism. Can be performed appropriately.

At the time of assembling the valve drive system, an adjustment screw capable of adjusting the valve clearance is provided at the contact portion of the valve drive arm with the intake valve or the exhaust valve so that the relief structure is formed on the adjustment screw. In addition, it is possible to adjust the valve clearance, reduce the time-dependent change in the valve clearance, and maintain the good operation of the valve drive system without maintenance.

The elephant structure includes a first contact member disposed on the valve driving arm, and a second contact member disposed between the first contact member and a step end portion of the intake valve or exhaust valve. And a convex curved surface is formed on the first contact member, a concave curved surface is formed on the second contact member, and this concave curved surface with the convex curved surface is in linear contact with the second contact member. Since the contact member is configured to be in surface contact with the step end, even if the valve clearance is adjusted by the adjustment screw, the point contact between the valve drive arm and the valve is always reliably avoided, so that the operation of the valve drive system can be maintained. have.

Next, the lubrication structures of the roller bearings 339, 366, and 369 are described in detail in the contact surface direction with the cams 14 and 15 based on FIG. 32 (A), (B), and 47. FIG. The oil jet hole (oil jet) 430 which faces the oil jet hole 430 is formed, and the oil pump 431 is formed in the outlet part of this oil jet hole 430.

When the oil pressure of the oil in the hydraulic passages 62 and 77 is high, the oil is spouted from the oil ejection hole 430, so that the roller bearings 338, 366, 369 and the cams 14, ( It is supplied directly to the contact surface of 15) and lubrication is performed.

When the hydraulic pressure is low, as shown in FIG. 47, the oil 432 clumps into the oil pump 431. As the oil pump 431 is inclined due to rocking arms 335, 365 and arm 333, the oil in the oil pump 431 overflows quickly and the roller bearings 339 and 366 ), 369 is supplied with a large amount of oil. As a result, the roller bearings 339, 366, 369 and the cams 14, 15 are lubricated reliably.

The oil is not supplied to the roller bearing 338 from the hydraulic passage 56 in the rocker arm 334 in order to prevent malfunction of the lock pin 52 accompanying the pressure change while supplying this oil. To lubricate the roller bearing 338 by other oil supply means, not shown.

The present invention is not limited to the above embodiment, but is applicable to a roller rocker arm of a type in which one end is supported by the rush regulator and the other end is in contact with the valve end, and a rocker arm of its type is also applicable. The size shape is not limited to that of the embodiment.

According to the rocker arm lubrication structure of the present invention, the oil pump is formed at the outlet of the oil ejection hole, and when the hydraulic pressure is low, the oil confined here overflows due to the rocker arm oscillation and is applied to the rollers at once. When lubrication is always performed reliably, reliability and durability are improved. Moreover, since only an oil pump is formed, it does not cause cost up.

Next, the jump prevention during the lift of the valves 79 and 80 will be described based on FIGS. 48 to 52.

48 and 49, the support portion 520 in which the base ends 503a and 503a are fixed to the rocker shaft portion 501 is, for example, a portion that is not related to the movement of the valve drive mechanism. The valve drive mechanism is formed integrally with the cylinder head 11 provided. The spring 521 as the biasing means is, for example, a band-shaped leaf spring, and the base end is fixed by the bolt 522 to the end face of the support part 520, and the rocker is curved near the base end. It extends in the direction of the tip portion 503b along the upper surface 503C of the arm portion 503, and the tip portion is pressed against the center of the upper surface 503C.

The spring 521 presses the upper surface 503C of the rocker arm portion 503 so that the rocker arm portion 503 and the rocker arm portion 504 are centered on the rocker shaft portion 501 in the clockwise direction. Press to rotate. And the initial load of this spring 521 is set to a value larger than the torque by the frictional force between the rocker arm 502 and the rocker shaft part 501 rotatably supported by the rocker shaft part 501, The rocker shaft portion 501 is prevented from being co-rotated by the rocker arm 502.

As shown in FIG. 50, the spring 521 has a weak spring force as the lift amount of the valves 79 and 80 increases, that is, as the rocker arm 503 rotates downward. (Gradual decrease), and more than a certain lift amount does not apply a spring force.

The lock pin 513 is extruded from the through hole 50la of the rocker shaft part 501 by the spring force of the compression spring 514 when the hydraulic pressure is not applied, and the front end thereof is engaged with the engaging hole of the rocker arm 502 ( 502C) and engage with the rocker arm 502 and the rocker shaft portion 501. As a result, the rocker arm portions 503 and 504 swing through the rocker arm 502 and the rocker shaft portion 501 as the cam 506 rotates to drive the valves 79 and 80. do.

When the cylinder rests, the lock pin 513 is released from the rocker shaft portion 501 against the spring force of the compression spring 514 by hydraulic pressure, and the rocker shaft portion 501 is engaged with the rocker arm 502. Even if the rocker arm 502 is rocked due to the rotation of the cam 506, the rocker arm portions 503 and 504 remain stationary without rocking, and the valves 79 and 80 are each free. Is held in a stopped (valve closed) state. Therefore, the cylinders of these valves 79 and 80 are stopped (cylinder rest).

The rocker shaft portion 501 does not rotate because the rocker shaft portions 501 and the rocker arm portions 503 and 504 that are integral to the rocker shaft portion 501 are restricted to the valve end in the rising section of the cam 506. Further, the rocker arm portions 503 and 504 are cams because the tip portions 503b and 504b are pressed against the step heads of the valves 79 and 80 by the spring force of the spring 521. Jumping in the falling section of 506 is prevented, and therefore the rocker shaft portion 501 is prevented from being co-rotated by the rocker arm 502. As a result, the through-hole 502C of the rocker arm 502 and the lock pin 5l3 remain in agreement with each other in the base section of the cam 506 when the cylinder rests, and the tip of the lock pin 513 It is in the state which can be fitted to the through-hole 502C of the rocker arm 502. FIG. This makes it possible to smoothly return from the stop state of the valves 79 and 80 to the operation state.

Since the biasing direction of the spring 521 is opposite to the biasing direction of the valve springs 81 and 82, the biasing force of the spring 521 is always applied when the valves 79 and 80 are lifted. When the valve is driven, as shown in FIG. 52, the spring force is added to the inertial forces of the valves 79 and 80 so that the valves 79 and 80 themselves jump out, and the desired valve Driving characteristics cannot be obtained. For this reason, the spring force of the spring 521 acts before the lift or before the lift and on the basis of the lift. Speaking in relation to the roller 505 of the rocker arm 502 and the cam 506, it only works when the roller 505 is in contact with the base member of the cam 506, or only at the time of the base member and the lift initial stage, In other parts, the spring force does not act or hardly acts on the step heads 509a of the valves 79 and 80.

As a result, as shown in FIG. 51, when the valves 79 and 80 are lifted, the spring force by the spring 521 is not applied at all, and jumping of the valves 79 and 80 is prevented. Will be.

The valve driving mechanism shown in FIG. 53 uses an arm spring 521A instead of the spring 521, and the rocker arm 503 is located at an upper position of the rocker arm 503 in the support portion 520. As shown in FIG. Holes 520a are formed in the upper and lower sides near the tip portion 503b of the cylinder. A cylinder 524 is fitted in the hole 520a with the opening end facing downward, and the plunger in the cylinder 524. 525 is slidably fitted in the axial direction toward the closed end, and a compression spring 526 is compressed between the cylinder 524 and the plunger 525. And the protrusion 525a which protruded in the center of the closed end surface of the plunger 525 is pressed against the boss 503d which protruded near the front-end | tip 503b of the upper surface 503C of the rocker arm 503. As shown in FIG. A snap ring 532 is provided inside the opening end of the cylinder 524 as a stopper.

Therefore, although the plunger 525 has applied the rocker arm 503 and 504 to the rocker arm 503 and 504 by the spring force of the spring 526, it is rocker arm 503 and 504. When slightly rotates, the lower end of the cylinder 524 abuts against the snap ring 532 and cannot be lowered further, and the spring force is not applied to the rocker arms 503 and 504. That is, as shown in FIG. 54, the spring force acts only at the beginning of the lift of the valves 79 and 80, and the rest is not applied at all.

Therefore, as in the foregoing description, the springing of the rocker arms 503 and 504 in the lowering section of the cam 506 at the time of cylinder rest is prevented, and the rocker shaft 501 is made of the rocker arm ( 502 is prevented from being co-rotated, and as shown in FIG. 55, when the valves 79 and 80 are driven, useless force is applied to the valves 79 and 80. Therefore, jumping of the valves 79 and 80 is prevented, and the desired valve driving characteristics can be obtained.

56 shows that a torsion spring is used as another modification. That is, the torsion spring 533 is fitted to the base end 503a of the rocker arm 503 to fix one end, and the other end is fixed to the fixed support 520. When the torsion spring 533 is used, as shown by a in FIG. 57, the spring force is gradually reduced in accordance with the lift amount of the valves 79 and 80, and is indicated by b in the drawing. As described above, the spring force for pressing the valves 79 and 80 according to the lift amount of the valves 79 and 80 gradually decreases and then disappears, and then the spring force in the opposite direction, that is, in the same direction as the valve spring 531. You can also let the spring force of. Therefore, when the valves 79 and 80 are opened and closed, the springs of the valves 79 and 80 are more reliably prevented.

As the spring 531, tension springs or the like can be used in addition to the above, and other than the spring can also be used as the biasing means.

In addition, although the case was applied to the valve driving mechanism of the variable cylinder engine according to FIGS. 48 to 57, the present invention is not limited thereto, and the T-type lever 30 of FIG. 6 or the T-type lever of FIG. The spring 521 and the arm spring 521A may also be applied to (L) 30L, and it is possible to apply to the valve drive mechanism which can change a valve timing according to the operation state of another engine.

The urging means 521, 521A, 533, which presses the distal end of the rocker arm 503 to the system head 509a, is disposed so that the base circumferential section of the cam 506 during cylinder rest can be disposed. The lock pin 513 inserted into the through hole 502C of the rocker shaft part 501 is prevented from shifting between the rocker shaft part 501 and the through-hole 502C of the rocker arm 502. It is possible to easily fit the through-hole 502C of the 503, and to smoothly perform the return from the cylinder rest operation to the entire cylinder operation or the change of the valve timing.

In addition, since the biasing means does not apply the biasing force only before the lift of the valve or until the beginning of the lift, the valve does not spring up at the time of opening and closing of the valve, and also does not cause an increase in friction. There is no need to make the spring hard.

Claims (51)

A cam shaft on which the cam is mounted, a rocker shaft portion adjacent to the cam shaft and rotatably mounted to the support member of the engine, and integrally formed with the rocker shaft portion to have an outer diameter larger than the outer diameter of the rocker shaft portion. A lever member formed of an excitation large diameter portion, an arm portion integrally formed with the large diameter portion, and contacted with a valve for intake and exhaust air, a rocker arm rotatably mounted to the large diameter portion, and rocked by the cam; And a switching mechanism means for engaging or disengaging the arm from the large diameter portion, and hydraulic pressure supply means for operating the switching mechanism means according to the engine operating state by hydraulic pressure. The camshaft of claim 1, wherein the camshaft has a low speed cam and a high speed cam, and the rocker arm is rotatably mounted to the large diameter portions of both sides of the arm, respectively, and is driven by the low speed cam and the high speed cam, respectively. A valve drive device for an internal combustion engine, characterized by having a low speed rocker arm and a high speed rocker arm. 3. The roller bearing means according to claim 2, wherein the low speed rocker arm and the high speed rocker arm are driven by the low speed cam and the high speed cam, respectively, and are rotatably mounted to the low speed rocker arm and the high speed rocker arm, respectively. Valve drive device of the internal combustion engine, characterized in that provided with. 4. The low speed rocker arm and the high speed rocker arm are biased to abut the respective roller bearing means against the respective cams by a first arm spring means mounted to the support member. Valve driving device of an internal combustion engine. 5. The valve driving apparatus of the internal combustion engine according to claim 4, wherein the lever bias is biased to contact the valve by a biasing means mounted to the support member. 6. The valve driving apparatus of claim 5, wherein the biasing means is configured to bias the valve only in an initial stage of the valve lift. The valve driving device of the internal combustion engine according to claim 5, wherein the biasing means is formed by a second arm spring means mounted to the support member. 6. The valve driving apparatus of claim 5, wherein the biasing means is formed by a leaf spring mounted to the support member. The valve driving device of the internal combustion engine according to claim 5, wherein the biasing means is formed by a torsion spring mounted to the support member. 5. The valve of an internal combustion engine according to claim 4, wherein the first arm spring means sets the bias force of the spring biasing the low speed rocker arm to be greater than the bias force of the spring biasing the high speed rocker arm. Drive system. 5. The valve driving apparatus of claim 4, wherein the hydraulic pressure supply means has an oil passage formed in a cam cap that supports the cam shaft to supply lubricant oil to the first arm spring. 4. The valve driving apparatus of claim 3, wherein the roller bearing means is formed of a material having a lighter weight than the roller bearing means for the low speed roller bearing. 13. The valve driving apparatus of claim 12, wherein the low speed roller bearing means is formed of a ceramic, and the high speed roller bearing means is formed of an iron-based metal. 2. The cam shaft of claim 1, wherein the cam shaft has a low speed cam and a high speed cam, the rocker arm is rotatably mounted to the large diameter portion, and has a high speed rocker arm driven by the high speed cam. Valve driving apparatus of the internal combustion engine, characterized in that formed to be driven by the low speed cam. 15. The high speed rocker arm according to claim 14, wherein the high speed rocker arm is provided with a high speed roller bearing means rotatably mounted to the high speed rocker arm, and the lever member is driven by the low speed cam. And a low speed roller bearing means rotatably mounted to said low speed rocker arm. The valve drive of the internal combustion engine according to claim 15, wherein the high speed rocker arm is biased to contact the high speed roller bearing means with the high speed cam by a first arm spring means mounted to the support member. Device. 17. The valve driving apparatus of claim 16, wherein the lever bias is biased to contact the valve by a biasing means mounted to the support member. 18. The valve driving apparatus of claim 17, wherein the biasing means is configured to bias the valve only at an initial stage of the valve lift. 18. The valve driving apparatus of claim 17, wherein the biasing means is formed by a second arm spring means mounted to the support member. 18. The valve driving apparatus of claim 17, wherein the biasing means is formed by a leaf spring mounted to the support member. 18. The valve driving apparatus of claim 17, wherein the biasing means is formed by a torsion spring mounted to the support member. 18. The valve driving apparatus of an internal combustion engine according to claim 17, wherein the force of the spring of said first arm spring means is set larger than the force of the spring of said second arm spring means. 17. The valve drive device according to claim 16, wherein the hydraulic pressure supply means has an oil passage formed in a cam cap that supports the cam shaft to supply lubricant oil to the first arm spring. The valve driving apparatus of the internal combustion engine according to claim 15, wherein the low speed roller bearing means is made of a material that is lighter than the high speed roller bearing means. 25. The valve driving apparatus of claim 24, wherein the low speed roller bearing means is formed of a ceramic, and the high speed roller bearing means is formed of an iron-based metal. The internal combustion engine according to claim 15, wherein the hydraulic pressure supply means has an oil ejection hole formed in the rocker shaft to supply oil to the low speed roller bearing means and the high speed roller bearing means, respectively. Valve drive system. 29. The valve driving apparatus of claim 28, wherein the oil ejection hole has an oil pump at its outlet. 15. The valve drive of the internal combustion engine according to claim 14, wherein the hydraulic pressure supply means includes an oil control valve for supplying hydraulic pressure from the oil pump of the engine to the oil room of the switching mechanism means of the high speed rocker arm. Device. 2. The cam shaft according to claim 1, wherein the cam shaft has a plurality of low speed cams and a plurality of high speed cams, a plurality of the lever members are disposed, and the rocker arms of the part are rotatable to the large diameter portions of both sides of the arm part, respectively. And a rocker arm of the other portion, which is driven by the low speed cam and the high speed cam, respectively, and is rotatable to a large diameter portion of the one side adjacent to one side of an arm portion of the other portion driven by the low speed cam. The valve driving device of the internal combustion engine, characterized in that formed so as to be driven by the high-speed cam at the same time. The length of each of the rocker arm portions of the low speed rocker arm and the rocker arm portion of the high speed rocker arm, which are attached to both of the arm portions, on one side of the arm of the other portion. And a high speed rocker arm to be mounted and a length equal to the length in both directions of the large diameter portion formed on one side of the arm of the other portion. The oil pressure supply means according to claim 29, wherein the hydraulic pressure supply means supplies the hydraulic pressure from the oil pump of the engine to the oil room of the switching mechanism means formed in the high speed rocker arm on the side of the rocker arm of the part and the other part. And a second oil supply valve for supplying oil pressure from the oil pump to the oil chamber of the switching mechanism means formed inside the low speed rocker arm on the part of the rocker arm via the accumulator and the second oil pump. A valve drive device for an internal combustion engine, comprising an oil control valve. The internal combustion engine according to claim 31, wherein the hydraulic pressure supply means has an oil ejection hole formed in the rocker shaft to supply oil to the high speed roller bearing means disposed in the high speed rocker arm. Valve drive system. 33. A valve driving apparatus for an internal combustion engine according to claim 32, wherein said oil ejection hole has an oil pump at its outlet. 32. The valve drive device according to claim 31, wherein the second oil control valve is disposed between the intake cam shaft and the exhaust cam shaft. 35. A valve driving apparatus for an internal combustion engine according to claim 34, wherein said second oil control valve is formed on said accumulator. 36. A valve driving apparatus for an internal combustion engine according to claim 35, wherein said second oil pump is formed by said cam shaft and is driven by a cam having a number of cylinders or more in valve rest. 37. The valve drive device according to claim 36, wherein the cam is formed at one end of the intake cam shaft. The lock mechanism according to claim 1, wherein the switching mechanism means is formed with an engagement hole formed in the rotational surface of the rocker arm for rotating the rocker shaft portion, and in the rocker shaft portion in an axial direction perpendicular to the rocker shaft portion. When the roller bearing means is in contact with the base of the cam, the through hole is aligned with the central axis of the engaging hole and the projection hole protrudes toward the engaging hole from the accommodation position accommodated in the through hole. A lock pin which is mounted to the protruding mole and protrudes to the protruding position, and is engaged with the engagement hole when the two central axes coincide with each other, an oil room formed between one end of the lock pin and the rotating surface of the rocker arm; Val of an internal combustion engine characterized by having a compression spring formed between the other end of the rock pin and the rotating surface of the rocker arm Drive device. 39. The switch mechanism according to claim 38, wherein the switching mechanism means has a flow path formed in the lock pin and communicating with the engagement hole, and a cover made of sheet metal mounted in the engagement hole to block the oil room. Valve driving device of an internal combustion engine. 40. A valve driving apparatus for an internal combustion engine according to claim 39, wherein said cover is provided in an engaging hole of a low speed rocker arm mounted rotatably on said large diameter portion. 42. The through hole according to claim 40, wherein said switching mechanism means includes a flow path formed in said lock pin and communicating with said engagement hole, a hydraulic passage formed in said rocker shaft portion, and a communication path between said flow path and said hydraulic path. The valve drive device of the internal combustion engine, characterized in that it has an oil passage formed on the circumferential surface. 42. The valve drive device according to claim 41, wherein the oil passage is formed in an annular shape. 41. The lock mechanism according to claim 40, wherein the switching mechanism means has a compression spring installed on an end surface of the lock pin opposite to the oil room end surface, and a spring seat engaged with the compression spring and supported by the rocker arm. And an outer diameter of the spring seat to be larger than an inner diameter of the engagement hole. The valve drive device of an internal combustion engine according to claim 38, wherein said switching mechanism means includes a spring hole formed in said rocker shaft part separately from said through hole, and a compression spring disposed in said spring hole. . The valve driving apparatus of an internal combustion engine according to claim 38, wherein the end edge of said through hole is formed by chamfering with a round pillar cutter. The cam according to claim 1, wherein the switching mechanism means is formed in a colleting hole formed in a rotation surface of the rocker arm for rotating the rocker shaft portion, and in the rocker shaft portion in a direction perpendicular to the axial direction of the rocker shaft portion. When the roller bearing means is in contact with the base circle, the center axis thereof extends to the through hole which is eccentric with respect to the center axis of the engaging hole, and to the protruding position protruding toward the engaging hole to the receiving position accommodated in the through hole. It is provided with protruding mole particles, and includes a lock pin that engages with the engagement hole when the through hole overlaps the engagement hole, and oil formed between the rear end of the lock pin and the rotating surface of the high speed rocker arm. A valve drive device of an internal combustion engine. The internal combustion engine according to claim 46, wherein the center axis of the engaging hole is formed to be eccentric toward the roller bearing means than the center axis of the through hole. The valve drive device of an internal combustion engine according to claim 1, wherein the engine is a double over head camshaft type having two cam shafts. 49. A valve driving apparatus for an internal combustion engine according to claim 48, wherein a floc tube disposed between the rocker arms is disposed, and a recess is formed in a portion of the floc tube facing the rocker arm. 2. The lever member according to claim 1, wherein the lever member includes an adjustment screw attached to the contact portion of the valve, a pad in line contact with one end of the adjustment screw, and a surface contact with the valve, and the pad mounted to the adjustment screw. A valve drive device for an internal combustion engine, comprising a retainer. 2. The valve driving apparatus of claim 1, wherein the hydraulic air pressure means has an oil groove for supplying oil from the oil pump of the engine to the journal portion of the cam shaft.