VARIABLE VALVE ACTUATING APPARATUS

Abstract

A variable valve actuating apparatus for an internal combustion engine includes a drive cam, a control shaft, a control cam, a rocker arm, and a swing cam. The drive cam is rotated by the internal combustion engine. The control shaft is supported for rotation about a rotation axis. The control cam is coupled to the control shaft, and is eccentric with respect to the rotation axis of the control shaft. The rocker arm is linked with the drive cam, and arranged to swing about the control cam in response to rotary motion of the drive cam. The rocker arm includes a recess slidably engaged with an outer radial periphery of the control cam. The swing cam is linked with the rocker arm, and arranged to swing in response to swinging motion of the rocker arm for opening and closing an engine valve of the internal combustion engine.

Description

BACKGROUND OF THE INVENTION

The present invention relates generally to internal combustion engines, and particularly to variable valve actuating apparatuses or systems for varying at least a lift of an engine valve, such as an intake valve or exhaust valve, of an internal combustion engine.

Japanese Patent Application Publication No. 2002-38913 corresponding to U.S. Pat. No. 6,499,454 discloses a variable valve actuating system for varying at least a lift of an intake valve set of an internal combustion engine. This variable valve actuating system includes: a drive shaft rotated by a crankshaft; a drive cam fixedly mounted to an outer radial periphery of the drive shaft; a transmitting mechanism for converting rotary motion of the drive cam to swinging motion of a swing cam, the transmitting mechanism including a rocker arm, a link arm and a link rod; and the swing cam that slides on a top surface of a valve lifter for opening and closing an intake valve. The link arm links the drive cam with the rocker arm. The link rod links the rocker arm with the swing cam. The rocker arm is linked at one end portion with one end of the link arm and one end of the link rod, and has a relatively large hole at another end portion in which a control cam is rotatably supported. The control cam is fixed and eccentric with respect to a control shaft. The variable valve actuating system is configured to control the position of the control cam according to an engine operating state by rotating the control shaft by an actuator. Movement of the control cam causes a change in the range of motion of the swing cam, and thereby causes changes in the lift and operating angle of the intake valve.

SUMMARY OF THE INVENTION

For assembling the variable valve actuating system described above and disclosed in Japanese Patent Application Publication No. 2002-38913, it is necessary to attach the control cam to the rocker arm by inserting the control cam into the hole formed in the rocker arm in the longitudinal direction of the control shaft. This imposes some requirements on the entire assembling process, for example, for avoiding interference between components.

In view of the foregoing, it is desirable to provide a variable valve actuating apparatus or system which can be assembled more easily.

According to one aspect of the present invention, a variable valve actuating apparatus for an internal combustion engine, comprises: a drive cam adapted to be rotated by the internal combustion engine; a control shaft supported for rotation about a rotation axis; a control cam coupled to the control shaft, wherein the control cam is eccentric with respect to the rotation axis of the control shaft; a rocker arm linked with the drive cam, and arranged to swing about the control cam in response to rotary motion of the drive cam, the rocker arm including a recess slidably engaged with an outer radial periphery of the control cam; and a swing cam linked with the rocker arm, and arranged to swing in response to swinging motion of the rocker arm for opening and closing an engine valve of the internal combustion engine. The variable valve actuating apparatus may further comprise: a device for maintaining contact between the recess of the rocker arm and the outer radial periphery of the control cam; and a drive shaft adapted to be rotated by the internal combustion engine, wherein: the drive cam is fixedly mounted to an outer radial periphery of the drive shaft; change of a rotational position of the control shaft causes a movement of the control cam with respect to the drive shaft, and causes at least a change in a lift of the engine valve; and the rotational position of the control shaft is controlled according to an operating state of the internal combustion engine. The variable valve actuating apparatus may further comprise: a drive shaft adapted to be rotated by the internal combustion engine, wherein the drive cam is mounted for rotation therewith to an outer radial periphery of the drive shaft; and an actuator for controlling a rotational position of the control shaft according to an operating state of the internal combustion engine, wherein the recess of the rocker arm has an entrance directed opposite to a portion of the rocker arm which is linked with the swing cam. The variable valve actuating apparatus may further comprise: a drive shaft adapted to be rotated by the internal combustion engine, wherein the drive cam is mounted for rotation therewith to an outer radial periphery of the drive shaft; and an actuator for controlling a rotational position of the control shaft according to an operating state of the internal combustion engine, wherein when the engine valve is open, the recess of the rocker arm is pressed on the outer radial periphery of the control cam by an elastic force of a valve spring provided for the engine valve.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a front view of a variable valve actuating system according to a first embodiment of the present invention in a position for a minimum lift set point.

FIG. 2 is a front view of the variable valve actuating system of FIG. 1 in the position for the minimum lift set point at a moment when an associated intake valve is opened.

FIG. 3 is a front view of the variable valve actuating system of FIG. 1 in a position for a maximum lift set point at a moment when the intake valve is closed.

FIG. 4 is a front view of the variable valve actuating system of FIG. 1 in the position for the maximum lift set point at a moment when the intake valve is opened.

FIG. 5 is a plan view of the variable valve actuating system of FIG. 1.

FIG. 6 is a side view of the variable valve actuating system of FIG. 1.

FIG. 7 is a graphic diagram showing lift curves of the intake valve which are achieved by the variable valve actuating system of FIG. 1.

FIG. 8 is a front view of a variable valve actuating system according to a second embodiment of the present invention.

FIG. 9 is a plan view of the variable valve actuating system of FIG. 8.

FIG. 10 is a side view of the variable valve actuating system of FIG. 8.

FIG. 11 is a graphic diagram showing lift curves of intake valves which are achieved by the variable valve actuating system of FIG. 8.

FIG. 12 is an enlarged view of a structure in which a rocker arm engages with a control cam in a variable valve actuating system according to a third embodiment of the present invention.

FIG. 13 is a plan view of the variable valve actuating system according to the third embodiment.

FIG. 14 is a side view of the variable valve actuating system according to the third embodiment.

FIG. 15 is a front view of a variable valve actuating system according to a fourth embodiment of the present invention.

FIG. 16 is a front view of the variable valve actuating system of FIG. 15 in a position for a minimum lift set point at a moment when an associated intake valve is opened.

FIG. 17 is a front view of the variable valve actuating system of FIG. 15 in a position for a maximum lift set point at a moment when the intake valve is closed.

FIG. 18 is a front view of the variable valve actuating system of FIG. 15 in the position for the maximum lift set point at a moment when the intake valve is opened.

FIG. 19 is a plan view of the variable valve actuating system of FIG. 15.

FIG. 20 is a side view of the variable valve actuating system of FIG. 15.

FIG. 21 is a front view of a variable valve actuating system according to a fifth embodiment of the present invention.

FIG. 22 is a front view of the variable valve actuating system of FIG. 21 in a position for a minimum lift set point at a moment when an associated intake valve is opened.

FIG. 23 is a front view of the variable valve actuating system of FIG. 21 in a position for a maximum lift set point at a moment when the intake valve is closed.

FIG. 24 is a front view of the variable valve actuating system of FIG. 21 in the position for the maximum lift set point at a moment when the intake valve is opened.

FIG. 25 is a plan view of the variable valve actuating system of FIG. 21.

FIG. 26 is a side view of the variable valve actuating system of FIG. 21.

FIG. 27 is a plan view of a variable valve actuating system according to a sixth embodiment of the present invention.

FIG. 28 is a front view of the variable valve actuating system of FIG. 27.

FIG. 29 is a front view of a variable valve actuating system according to a seventh embodiment of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

FIGS. 1 to 6 show a variable valve actuating apparatus or system according to a first embodiment of the present invention for an engine valve set of an internal combustion engine which is an intake valve set in this example. The variable valve actuating system according to the first embodiment generally includes an intake valve set which includes two intake valves 3, 3 per cylinder, a drive shaft 4, a drive cam 5 per cylinder, a swing arm set which includes two swing arms 6, 6 per cylinder, a swing cam set which includes two swing cams 7, 7 per cylinder, a transmitting mechanism 8 per cylinder, and a control mechanism 9. Each intake valve 3 is slidably mounted in a valve guide not shown in a cylinder head 1, for opening and closing an intake port formed in cylinder head 1. Drive shaft 4 is hollow, having a longitudinal axis extending in a longitudinal direction of the engine. Drive cam 5 is fixedly mounted to drive shaft 4. Each swing arm 6 is arranged close to an upper end of intake valve 3. Each swing cam 7 opens and closes intake valve 3 by moving the swing arm 6. Transmitting mechanism 8, which is of a multiple link type, links drive cam 5 with swing cams 7, 7, and converts rotary motion of drive cam 5 into swinging motion of swing cams 7, 7. Controlled according to an engine operating state, control mechanism 9 varies the lift of intake valves 3, 3 by moving a fulcrum of a rocker arm 15 of transmitting mechanism 8.

Each intake valve 3 is provided with a valve spring 10, and biased by valve spring 10 in a direction to close the intake port, as shown in FIG. 6. Each valve spring 10 is disposed between the bottom of a substantially cylindrical bore formed or provided in an upper end portion of cylinder head 1, and a spring retainer provided in an upper end portion of a valve stem of intake valve 3.

Drive shaft 4 is rotatably mounted in cylinder head 1. Drive shaft 4 includes longitudinal ends rotatably supported on bearings provided in an upper portion of cylinder head 1. Drive shaft 4 is adapted to be rotated by a crankshaft of the engine. Specifically, drive shaft 4 receives a torque from the crankshaft through a rotation transmitting mechanism which is, for example, a chain drive mechanism including a timing sprocket provided at one longitudinal end of drive shaft 4, and a timing chain wounded around the timing sprocket. When driven by the crankshaft, the drive shaft 4 rotates in a clockwise direction as shown by an arrow in FIG. 1.

Drive cam 5 is arranged between swing cams 7, 7 in the longitudinal direction of drive shaft 4, shaped like a circular disc, and formed with a hole extending in a longitudinal direction of drive cam 5 (in the longitudinal direction of drive shaft 4), as shown in FIGS. 1 and 6. Drive cam 5 is coupled to or fixedly mounted on an outer radial periphery of drive shaft 4 for rotation therewith, where drive shaft 4 extends through the hole of drive cam 5. Drive cam 5 is thus adapted to be rotated by the crankshaft of the engine. The hole is positioned in drive cam 5 so that drive cam 5 has an eccentric circular cam profile. The central axis Y of drive cam 5 is offset in a predetermined radial direction from the central axis X of drive shaft 4 by a predetermined distance.

Each swing arm 6 extends in a lateral direction of drive shaft 4, and has a first end portion 6a which includes a slightly recessed lower surface in contact with the stem end of intake valve 3, and a second end portion 6b which includes a semispherically recessed lower surface in contact with and slidably supported by the tip of a hydraulic lash adjuster 11 retained in a retainer hole 2 formed in cylinder head 1. Swing arm 6 is thus arranged to swing about the tip of hydraulic lash adjuster 11. Swing arm 6 is provided with a needle roller 12 substantially at a center of swing arm 6. Needle roller 12 is rotatably supported with respect to swing arm 6, and is in rolling contact with swing cam 7, serving to reduce the friction between swing cam 7 and swing arm 6.

Hydraulic lash adjuster 11 has a general structure, including a body 13a, and a plunger 13b. Body 13a is cylindrically shaped with an open top and a closed bottom, and inserted and fixedly mounted in retainer hole 2. Plunger 13b is mounted in body 13a for sliding through the top opening of body 13a. Plunger 13b has a semispherical upper end in sliding contact with the second end portion 6b of swing arm 6. Hydraulic fluid is supplied from a reservoir through a check valve to a high pressure chamber defined between the inner bottom of body 13a and the outer bottom of plunger 13b. Hydraulic lash adjuster 11 serves to constantly maintain the clearance between the tip of plunger 13b and the second end portion 6b of swing arm 6 (and the clearance between swing cam 7 and needle roller 12) substantially equal to zero by suitable supply of hydraulic fluid.

Each swing cam 7 includes a fitting recess 7a which is generally U-shaped, and fit on the outer radial periphery of drive shaft 4, so that swing cam 7 is swingably supported with respect to drive shaft 4, i.e. swing cam 7 is supported for swinging about the central axis X of drive shaft 4 with the fitting recess 7a in sliding contact with the outer radial periphery of drive shaft 4. Swing cam 7 has a cam surface 7b at the lower side which is adapted to be in contact with needle roller 12 of swing arm 6. The cam surface 7b of swing cam 7 includes a base circle surface region closer to drive shaft 4, a ramp surface region extending like a circular arc from the base circle surface region toward a cam nose 7c, and a lift surface region extending from the ramp surface region toward an apex of the cam nose which defines a possible maximum lift set point of intake valve 3. The cam surface 7b abuts on the top surface of a corresponding portion of the outer radial periphery of needle roller 12 of swing arm 6, and the contact point of the cam surface 7b shifts among the base circle surface region, ramp surface region and lift surface region in dependence on the swing position of swing cam 7. Swing cam 7 is arranged so that when swing cam 7 swings in the same direction as drive shaft 4 (clockwise direction as viewed in FIG. 1), the contact point of cam surface 7b shifts toward the lift surface region for increasing the opening of intake valve 3. The cam nose 7c of swing cam 7 is formed with a pin hole 7e extending in the longitudinal direction of drive shaft 4. A connecting pin 20 is inserted through pin hole 7e for connecting swing cam 7 and a link rod 17. The structure that swing cam 7 is directly mounted to drive shaft 4 eliminates the necessity of an additional support shaft for supporting swing cam 7. This is effective for cost reduction and downsizing of the variable valve actuating system. Swing cam 7 is linked with rocker arm 15, and arranged to swing in response to swinging motion of rocker arm 15 for opening and closing the intake valve 3.

Transmitting mechanism 8 includes a rocker arm 15, a link arm 16, a link rod set which includes two link rods 17, 17 per cylinder, as shown in FIG. 5. Rocker arm 15 is arranged above drive shaft 4, extending generally in the lateral direction of the engine. Rocker arm 15 is linked with drive cam 5, and arranged to swing about control cam 26 in response to rotary motion of drive cam 5, as detailed below. Link arm 16 links rocker arm 15 with drive cam 5. Each link rod 17 links rocker arm 15 with the cam nose 7c of the respective swing cam 7.

Rocker arm 15 includes a first longitudinal end portion defining a recess, and a second longitudinal end portion opposite to the first longitudinal end portion in a longitudinal direction of rocker arm 15, wherein the second longitudinal end portion is linked with swing cam 7 for transmitting swinging motion of rocker arm 15 to swing cam 7. Specifically, rocker arm 15 is generally A-shaped in a lateral direction of drive shaft 4 as shown in FIG. 6, and includes a first end portion 15a, and a longitudinal end portion set which is Y-shaped as viewed in FIG. 5 and includes two second end portions 15b, 15b. The first end portion 15a of rocker arm 15 includes a recess 21 which is slidably engaged with an outer radial periphery of a control cam 26 for allowing rotation of control cam 26. The recess 21 of rocker arm 15 and the outer radial periphery of control cam 26 have shapes fit on each other. Each second 5 end portion 15b of rocker arm 15 includes a pin hole 15c extending in the longitudinal direction of drive shaft 4. A connecting pin 22 extends through the pin holes 15c, 15c of the second end portions 15b, 15b which are coaxially positioned.

The recess 21 of rocker arm 15 has an inner cylindrical surface 21b which appears as a generally semicircular arc fit on the outer radial periphery of control cam 26 as viewed in the longitudinal direction of drive shaft 4 in FIG. 1. Recess 21 has an inner diameter that is slightly larger than the outer diameter of control cam 26. Recess 21 includes an entrance 21a directed downward as viewed in FIG. 1, i.e. directed toward intake valve 3 or toward hydraulic lash adjuster 11. The first end portion 15a of rocker arm 15 is thus slidably supported with respect to control cam 26 for rotating or swinging about control cam 26 so that the second end portions 15b, 15b can move upward and downward.

The first end portion 15a of rocker arm 15 is biased by a compression coil spring 24 toward control cam 26 or toward drive shaft 4. Compression coil spring 24 includes a first end fixed to a rocker cover 14, and a second end in pressing contact with the outer periphery of first end portion 15a. Compression coil spring 24 serves as a device for mechanically pressing the recess 21 of rocker arm 15 on the outer radial periphery of control cam 26, constantly maintaining contact between the inner cylindrical surface 21b of the recess 21 and the outer radial periphery of control cam 26, and preventing the recess 21 of rocker arm 15 from escaping from control cam 26.

Link arm 16 includes a circular portion 16a, and a projecting portion 16b. Circular portion 16a has a relatively large outer diameter, and has a fitting hole 16c at the center. The fitting hole 16c is slidably fit on the outer radial periphery of drive cam 5 for allowing relative rotation of drive cam 5. Projecting portion 16b is projecting from circular portion 16a in a radial direction of circular portion 16a, and disposed between the second end portions 15b, 15b of rocker arm 15 as viewed the lateral direction of drive shaft 4 in FIG. 5. Projecting portion 16b includes a pin hole 16d extending in the longitudinal direction of drive shaft 4 between both opposite surfaces, through which connecting pin 22 extends. Projecting portion 16b is thus rotatably supported with respect to second end portions 15b, 15b through connecting pin 22.

Each link rod 17 is composed of a single piece made by press forming and folding. Link rod 17 has a U-shaped cross section as viewed in FIG. 5, which is advantageous in compactness. Link rods 17, 17 are arranged outside of the second end portions 15b, 15b of rocker arm 15 in the longitudinal direction of drive shaft 4 as viewed in FIG. 5. Link rod 17 has a first end portion 17a including a pin hole through which connecting pin 22 extends, and a second end portion 17b including a pin hole through which connecting pin 20 extends. Link rod 17 is rotatably connected at the first end portion 17a to the second end portion 15b of rocker arm 15 through connecting pin 22, and rotatably connected at the second end portion 17b to the cam nose 7c of swing cam 7 through connecting pin 20.

As described above, connecting pin 22 pivotally connects all of the projecting portion 16b of link arm 16, the first end portions 17a of link rods 17, and the second end portions 15b, 15b of rocker arm 15. Connecting pin 22 is provided with snap rings 22a, 22a at both longitudinal ends for preventing the connected members from escaping from the connecting pin 22. Also, each connecting pin 20 is swaged at both longitudinal ends so as to prevent the link rod 17 and swing cam 7 from escaping from connecting pin 20.

Control mechanism 9 includes a control shaft 25, control cam 26, and an actuator 41. Control shaft 25 is arranged above drive shaft 4, extending in parallel to drive shaft 4. Control shaft 25 is supported for rotation about a rotation axis which is a central axis P of control shaft 25. Control cam 26 is coupled or fixedly mounted to control shaft 25 for serving as a fulcrum for rocking motion of rocker arm 15. The rotational position of control shaft 25 is regulated or controlled by actuator 41.

Control shaft 25 includes a pair of shaft parts on both sides of the center of the cylinder in the longitudinal direction of control shaft 25 as shown in FIG. 5. The ends of the shaft parts confronting each other are provided with flanges 25a, 25a between which the first end portion 15a of rocker arm 15 is slidably supported. The flanges 25a, 25a of control shaft 25 serves to prevent the first end portion 15a from inclining when rocker arm 15 is rocking.

Control cam 26 is formed in a cylindrical shape having a smaller outer diameter than control shaft 25. Control cam 26 is supported by and arranged between the flanges 25a, 25a of control shaft 25 as viewed in FIG. 5. Control cam 26 is eccentric with respect to the central axis P of control shaft 25. Specifically, control cam 26 has a central axis Q which is offset from the central axis P of control shaft 25 by an eccentric distance a, where the eccentric distance a is substantially as large as the diameter of control shaft 25, as shown in FIG. 1. Accordingly, control cam 26 has an outer portion 26a projecting beyond the outer radial periphery of control shaft 25, where the outer portion 26a is substantially half of control cam 26, as viewed in FIG. 1. Control shaft 25 and control cam 26 are thus formed as a unit shaped like a crank.

Actuator 41 in control mechanism 9 includes an electric motor, and a speed reducer, such as a ball screw mechanism. The electric motor is fixed to a rear end wall of cylinder head 1. The speed reducer is arranged to transmit an output torque of the electric motor to control shaft 25. The electric motor is a linear DC motor which is driven according to a control signal outputted from an electric controller not shown. The controller measures or calculates an engine operating state with reference to feedback signals from sensors, and controls the electric motor according to the engine operating state. The sensors include a crank angle sensor for measuring engine speed, an airflow meter for measuring intake air quantity, an engine coolant temperature sensor for measuring engine coolant temperature, and a potentiometer for measuring the rotational position of control shaft 25.

The following describes operations of the variable valve actuating system according to the first embodiment. The rotational position of control shaft 25 is controlled according to the engine operating state, and change of the rotational position of control shaft 25 causes a movement of control cam 26 with respect to drive shaft 4, and causes at least a change in the lift of intake valve 3, as detailed below.

For example, when the engine is at idle or at low speed, the controller issues such a control signal to the electric motor of control mechanism 9 that the electric motor rotates and outputs a torque which is transmitted to control shaft 25 through the speed reducer, and accordingly, control shaft 25 rotates in a clockwise direction by a corresponding angle as viewed in FIG. 1. The rotation of control shaft 25 causes the central axis Q of control cam 26 to revolve about the central axis P of control shaft 25 to a position below and slightly on the left of the central axis P so that the outer portion 26a of control cam 26 moves away from drive shaft 4. This moves the rocker arm 15 leftward so that an angle θ between rocker arm 15 and link arm 16 increases, and moves the connecting pin 22 generally in the counterclockwise direction about drive shaft 4 as viewed in FIG. 1. Accordingly, swing cam 7 is rotated through link rod 17 in the counterclockwise direction as viewed in FIG. 1 so that the cam nose 7c of swing cam 7 is moved upward. When drive cam 5 rotates under the condition described above and shown in FIG. 1, the second end portions 15b, 15b of rocker arm 15 are moved upward and downward through link arm 16. When the second end portions 15b, 15b are moved downward as shown in FIG. 1, swing cam 7 is moved downward through link rod 17. Under this condition, the amount of depression of swing arm 6 caused by the cam surface 7b of swing cam 7 is relatively small. This setting achieves a minimum valve lift set point.

In this way, when the engine is at idle or at low speed, the lift of each intake valve 3 is set by the variable valve actuating system at the minimum lift set point L as shown in FIG. 7. This retards the opening timing of intake valve 3 (intake valve opening timing IVO), and produces no valve overlap in which both of intake valve 3 and an exhaust valve are opened. This provides the engine with a small pumping loss, an improved combustion process, an improved fuel efficiency, and stable rotation performance.

For example, when the engine shifts to a predetermined high speed region from a predetermined low speed region, the controller issues such a control signal that the electric motor and speed reducer of control mechanism 9 rotate in a reverse direction, and accordingly, control shaft 25 rotates control cam 26 in the counterclockwise direction as viewed in FIG. 1. The rotation of control shaft 25 causes the central axis Q of control cam 26 to revolve about the central axis P of control shaft 25 to a position below and on the right of the central axis P of control shaft 25 as shown in FIGS. 3 and 4 so that the outer portion 26a of control cam 26 moves toward drive shaft 4. This moves the rocker arm 15 rightward so that the angle θ between rocker arm 15 and link arm 16 decreases, and moves the connecting pin 22 generally in the clockwise direction about drive shaft 4 as viewed in FIG. 3. Accordingly, swing cam 7 is rotated through link rod 17 in the clockwise direction as viewed in FIG. 3 so that cam nose 7c of swing cam 7 is moved downward. Accordingly, the contact point of cam surface 7b of swing cam 7 with respect to needle roller 12 of swing arm 6 moves toward the cam nose 7c (toward the lift region). When drive cam 5 rotates under the condition described above and shown in FIG. 3, the second end portions 15b, 15b of rocker arm 15 are moved upward and downward through link arm 16. When second end portions 15b, 15b are moved downward as shown in FIG. 4, swing cam 7 is moved downward through link rod 17. Under this condition, the amount of depression of swing arm 6 caused by the cam surface 7b of swing cam 7 is relatively large. This setting achieves a maximum valve lift set point.

In this way, when the engine is at high speed, the lift of intake valve 3 is set by the variable valve actuating system at the maximum lift set point L1 as shown in FIG. 7. This advances the opening timing of intake valve 3 (intake valve opening timing IVO) so as to produce and increase a valve overlap in which both of intake valve 3 and the exhaust valve are opened, and retards the closing timing of intake valve 3 (intake valve closing timing IVC). This provides the engine with an improved intake air charging efficiency, and thereby, a high engine output.

When the engine returns from the high speed region to the low speed region, the lift of the intake valve 3 is set to the minimum lift set point L. The central axis Q of control cam 26 as a pivot for swinging motion of the first end portion 15a of rocker arm 15 moves to the position shown in FIG. 1 so as to move the link arm 16 in the counterclockwise direction about drive cam 5 with respect to the position for the maximum lift set point L1. This advances the lift peak phase so that the intake valve opening timing IVO advances little at about top dead center, and the intake valve closing timing IVC advances significantly, with respect to the condition of the maximum lift set point L1, as shown in FIG. 7. The intake valve opening timing IVO closer to top dead center for the condition of the minimum lift set point L is effective for allowing a suitable control of valve overlap. This makes it possible to reduce an increase of residual burned gas, and suppress adverse effects on fuel efficiency, at the minimum lift set point L.

In this way, the variable valve actuating system can control the lift and operating angle of the engine valve set continuously between the minimum lift set point L and the maximum lift set point L1 by actuating the control shaft 25 according to engine operating state.

The provision of the recess 21 of the first end portion 15a of rocker arm 15 enables an operator to easily attach the rocker arm 15 to control cam 26 only by engaging the recess 21 of rocker arm 15 with control cam 26 in the radial direction of control cam 26. This leads to a low manufacturing cost in view of efficiency of assembling operation.

The arrangement that the projecting portion 16b of link arm 16 and the first end portion 17a of link rod 17 are connected through the common connecting pin 22 at the second end portions 15b, 15b of rocker arm 15, is effective for allowing the reaction force of the valve spring 10 applied to link rod 17 and the driving torque applied from drive cam 5 to link arm 16 to cancel each other when intake valve 3 opens and closes under the condition of the maximum lift set point L1. Accordingly, the load acting on the central axis Q of control cam 26 from rocker arm 15 is relatively small, and the required driving torque of actuator 41 is relatively small accordingly.

The crank structure of control shaft 25 and control cam 26 allows a large eccentric distance a between the central axis P of control shaft 25 and the central axis Q of control cam 26. This allows a large range of movement of the central axis Q as a fulcrum of rotation of rocker arm 15, and a large amount of change of the lift, operating angle, and peak lift phase, of intake valve 3. The crank structure of control shaft 25 and control cam 26 is also effective for reducing the outer diameter of control shaft 25. This leads to downsizing of parts such as bearings and thereby downsizing of the entire variable valve actuating system. The simple structure of the first end portion 15a of rocker arm 15 also leads to downsizing of the entire variable valve actuating system.

The structure that the first end portion 15a of rocker arm 15 is sandwiched and slidably held between the flanges 25a, 25a of control shaft 25, is effective for preventing the first end portion 15a from inclining when rocker arm 15 is rocking, and thereby, is effective for preventing abnormal wear between control cam 26 and first end portion 15a.

The structure of transmitting mechanism 8 where the elastic force of valve spring 10 and the driving force of drive cam 5 are well balanced is effective for preventing stress concentration and occurrence of deformation.

The provision of compression coil spring 24 is effective for keeping constant contact between the recess 21 of rocker arm 15 and the outer radial periphery of control cam 26, and thereby efficiently transmitting the movement of control cam 26 to rocker arm 15.

When the engine is stopping, an alternating torque occurs in the engine and acts on control cam 26 in the direction toward the minimum lift set point L. However, when actuator 41 applies no torque to control shaft 25, the elastic force of compression coil spring 24 is effective for mechanically moving and holding the control cam 26 to a position for an intermediate lift set point between the minimum lift set point L and maximum lift set point L1, specifically, to a position slightly displaced from the position for the minimum lift set point L toward the position for the maximum lift set point L1. This enables the engine to restart well.

The structure that control cam 26 is located at the first end portion 15a of rocker arm 15 is effective for reducing the contact load between recess 21 and control cam 26 because the elastic force of valve spring 10 is absorbed by drive cam 5.

The structure that the inner peripheral surface of recess 21 has substantially the same shape as the outer radial periphery of control cam 26, is effective for providing a wide contact area between rocker arm 15 and control cam 26, and thereby preventing stress concentration therebetween.

FIGS. 8 to 10 show a variable valve actuating system according to a second embodiment of the present invention. In the second embodiment, the structures of rocker arm 15 and swing cams 7, 7 are modified, and two drive cams 5, 5 and two link arms 16, 16 are provided for swing cams 7, 7, with respect to the first embodiment.

Rocker arm 15 is shaped so that the entrance 21a of recess 21 is directed at an angle θ1 of about 30 degrees downward with reference to a line connecting the central axis Q of control cam 26 and the central axis O of connecting pin 22, and the second end portion 15b is single, not branched. The second end portion 15b has a tip having a small width formed with a pin hole 15c through which connecting pin 22 extends. The second end portion 15b is rotatably connected substantially to the center of connecting pin 22 in the longitudinal direction of connecting pin 22.

Compression coil spring 24 for biasing the first end portion 15a of rocker arm 15 is located at the position shown in FIG. 8 along the direction toward the central axis Q of control cam 26 so that the inner cylindrical surface 21b of the recess 21 is constantly pressed to the outer radial periphery of control cam 26.

Each drive cam 5 is fixed to or integrated with drive shaft 4, and is arranged at an interval from the other drive cam 5, as shown in FIG. 10. Each link arm 16 includes a circular portion 16a, and a projecting portion 16b, as in the first embodiment. The circular portion 16a includes the fitting hole 16c in which drive cam 5 is rotatably supported. The projecting portion 16b is rotatably supported by connecting pin 22 extending through the pin hole 16d. Projecting portions 16b, 16b are arranged on both sides of the second end portion 15b of rocker arm 15 in the longitudinal direction of drive shaft 4 as shown in FIG. 9.

The cam surfaces 7b, 7b of swing cams 7, 7 have different profiles as shown in FIG. 8. The cam surface 7b of one swing cam 7 is concaved or offset with respect to the cam surface 7b of the other swing cam 7.

The drive shaft 4 and control shaft 25 are rotatably supported on bearings which are arranged between transmitting mechanisms 8, 8 in the longitudinal direction.

The structure of recess 21 that entrance 21a is directed downward by the angle of about 30 degrees with respect to the reference line is effective for providing a tight contact between the rocker arm 15 and control cam 26, and allowing the rocker arm 15 to follow the eccentric movement of control cam 26 well. Even when the difference between the profiles of the cam surfaces 7b, 7b of swing cams 7, 7 causes the rocker arm 15 via connecting pin 22 to incline, the structure of recess 21 is also effective for resisting the moment of inclination of rocker arm 15 and connecting pin 22. This enables the variable valve actuating system to precisely control the lift and operating angle of intake valve 3.

The structure that two drive cams 5, 5 are arranged close to each other in the longitudinal direction of drive shaft 4 per cylinder, is effective for preventing the connecting pin 22 and rocker arm 15 from inclining, even when drive cams 5, 5 are shaped to have different cam profiles so as to differentiate the lifts of intake valves 3, 3 from each other.

The structure that the cam surfaces 7b, 7b of swing cams 7, 7 have different profiles, is effective for slightly differentiating the lifts of intake valves 3, 3 from each other under the condition of the minimum lift set point L as shown in FIG. 11, promoting in cylinder intake swirl, improving the combustion process, stabilizing the engine rotation, and enhancing the fuel efficiency.

FIGS. 12 to 14 show a variable valve actuating system according to a third embodiment of the present invention. This variable valve actuating system is presented by modifying the first embodiment so that two control cams 26, 26 are provided per cylinder, and accordingly, rocker arm 15 has two branched first end portions 15a, 15a. Control shaft 25 and drive shaft 4 are rotatably supported by bearings not shown.

Each first end portion 15a of rocker arm 15 has a C-shaped recess 21, where the entrance 21a of recess 21 has a narrower entrance width Z than the outer diameter of control cam 26, as shown in FIG. 12. On the other hand, each control cam 26 has flat surfaces 26b, 26b at the outer radial periphery which are parallel to each other, as shown in FIG. 12. The distance between flat surfaces 26b, 26b is smaller than the outer diameter of control cam 26, and slightly smaller than the entrance width Z of recess 21. The flat surfaces 26b, 26b of one control cam 26 is located in the same circumferential position as those of the other control cam 26. In this way, the outer radial periphery of control cam 26 partly has a thickness in a radial direction of control cam 26 which is narrower than the entrance 21a of recess 21 of rocker arm 15, and control cam 26 is engaged with rocker arm 15 in such a rotational position that control cam 26 is prevented from escaping through the entrance 21a from the recess 21 of rocker arm 15.

Attaching the rocker arm 15 to control cams 26, 26 is implemented by allowing the edges of entrance 21a of each recess 21 to be in contact with the edges of the flat surfaces 26b, 26b of control cam 26, then sliding the rocker arm 15 in the radial direction of control cams 26, 26 so as to fit the inner cylindrical surface 21b of each recess 21 to a portion of the outer radial periphery of control cam 26 between the flat surfaces 26b, 26b, finally rotating the rocker arm 15 about the control cams 26, 26 to a predetermined rotational position. Each recess 21 is thus engaged with the circular outer radial periphery of control cam 26, and prevented from escaping from control cam 26. In this way, attaching the rocker arm 15 to control cam 26 is simply implemented so as to achieve stable and reliable engagement between rocker arm 15 and control cam 26. According to the structure described above, compression coil spring 24 for maintaining the rocker arm 15 in contact with control cam 26 is omitted, in contrast to the first embodiment. This leads to reduction in the number of parts, and thereby leads to reduction in manufacturing cost, and improvement in assembling operation.

The structure that rocker arm 15 is rotatably supported by control cams 26, 26 which are arranged at an interval, is effective for preventing the rocker arm 15 from inclining, even when the cam surfaces 7b, 7b of swing cams 7, 7 have different profiles.

FIGS. 15 to 20 show a variable valve actuating system according to a fourth embodiment of the present invention. In this embodiment, two transmitting mechanisms 8, 8 are provided for intake valves 3, 3 independently of each other. Specifically, as shown in FIGS. 19 and 20, two drive cams 5, 5 are provided per intake valve 3, and the total four drive cams 5 are attached to drive shaft 4 at predetermined intervals. Accordingly, link arm 16 is provided per drive cam 5.

Control shaft 25 are provided with two control cams 26, 26 for two intake valves 3, 3. Control shaft 25 has flat surfaces 25b, 25b at the outer radial periphery each of which is located outside of control cam 26 in the longitudinal direction. Each control cam 26 is linked with the respective one of two rocker arms 15, 15. As in the third embodiment, each first end portion 15a has a C-shaped recess 21, where the entrance 21a of recess 21 has a narrower entrance width Z than the outer diameter of control cam 26. On the other hand, each control cam 26 has flat surfaces 26b, 26b at the outer radial periphery which are parallel to each other. The distance between flat surfaces 26b, 26b is smaller than the outer diameter of control cam 26, and slightly smaller than the entrance width Z of the recess 21 of rocker arm 15. The entrance 21a of each recess 21 is directed substantially in the longitudinal direction of rocker arm 15, or in the longitudinal direction of the first end portion 15a of rocker arm 15 toward the longitudinal end of rocker arm 15, opposite to connecting pin 22 which is linked with swing cam 7 and is related to actuation of intake valve 3. Control shaft 25 and drive shaft 4 are supported by a bearing 33.

Each rocker arm 15 has a pin hole 15c at the second end portion 15b through which connecting pin 22 passes. Rocker arm 15 is rotatably linked with the first end portion 17a of link rod 17 through the connecting pin 22. Each rocker arm 15 also has a pin hole 15d substantially at the center of rocker arm 15 in the longitudinal direction through which a respective connecting pin 28 passes. Rocker arm 15 is rotatably linked with the projecting portions 16b, 16b of link arms 16, 16 through the connecting pin 28. One pair of link arms 16, 16 are arranged on both sides of one combination of rocker arm 15 and link rod 17, and the outer pair of link arms 16, 16 are arranged on both sides of the other combination of rocker arm 15 and link rod 17, in the longitudinal direction of drive shaft 4, as shown in FIGS. 19 and 20.

The variable valve actuating system described above operates as follows. For example, when the engine is at low speed and low load, control shaft 25 is controlled to rotate to the position shown in FIGS. 15 and 16 as in the first embodiment, so that the lift of intake valve 3 is set at the minimum lift set point L. When the engine shifts to a predetermined high speed region, control shaft 25 is controlled to rotate in the counterclockwise direction as shown in FIGS. 17 and 18, so that the lift of intake valve 3 is set at the maximum lift set point L1.

Attaching the rocker arm 15 to control cam 26 is implemented as in the third embodiment by allowing the edges of entrance 21a of recess 21 to be in contact with the edges of the flat surfaces 26b, 26b of control cam 26, then sliding the rocker arm 15 in the radial direction of control cam 26 so as to fit the inner cylindrical surface 21b of recess 21 to a portion of the outer radial periphery of control cam 26 between the flat surfaces 26b, 26b, finally rotating the rocker arm 15 about the control cam 26 to a predetermined rotational position. Each recess 21 is thus engaged with the circular outer radial periphery of control cam 26, and prevented from escaping from control cam 26. In this way, attaching the rocker arm 15 to control cam 26 is simply implemented so as to achieve stable and reliable engagement between rocker arm 15 and control cam 26. According to the structure described above, compression coil spring 24 for maintaining the rocker arm 15 in contact with control cam 26 is omitted, in contrast to the first embodiment.

The structure that the entrance 21a of recess 21 is directed opposite to connecting pin 22 is effective for maintaining tight contact between rocker arm 15 and control cam 26 without compression coil spring 24, because the force from valve spring 10 is transmitted to act the rocker arm 15 in the direction from the inner cylindrical surface 21b of recess 21 toward the outer radial periphery of control cam 26.

The structure that each intake valve 3 is provided with the respective drive cam 5 and rocker arm 15 is effective for allowing to adjust the lift of intake valve 3 independently of the other intake valve 3 by adjusting the profiles of drive cam 5 and control cam 26 independently of the other drive cam 5 and control cam 26.

The structure that the projecting portion 16b of link arm 16 is connected to substantially the center of rocker arm 15 is effecting for expanding the range of movement of link rod 17 and swing cam 7. Simultaneously, the load acting on the recess 21 of rocker arm 15 increases. However, the increased load can be resisted because the recess 21 is rightly and stably engaged with control cam 26.

FIGS. 21 to 26 show a variable valve actuating system according to a fifth embodiment of the present invention. In this embodiment, drive cam 5 is oval-shaped as viewed in the longitudinal direction of drive shaft 4 in FIG. 21. Rocker arm 15 is arranged to extend generally in the horizontal direction above the drive cam 5, and includes a roller support shaft 30 on which a roller 29 is rotatably supported. Roller 29 is in rolling contact with the outer radial periphery of drive cam 5.

Specifically, drive cam 5 is prepared separately from or independently of drive shaft 4, including a sleeve 5c as shown in FIG. 25. Drive cam 5 is fixed to the outer radial periphery of drive shaft 4 by a fixing pin 35 which passes through the sleeve 5c and drive shaft 4. Each cylinder is provided with one drive cam 5. Drive cam 5 has such an asymmetrical cam profile that at least at the maximum lift set point L1, intake valve 3 accelerates more rapidly when ascending to a peak of lift than when descending from the peak. Drive cam 5 includes an ascending flank 5a and a descending flank 5b which have different profiles as shown in FIG. 21. The ascending flank 5a is substantially straight, while the descending flank 5b is curved outwardly. Accordingly, the acceleration of intake valve 3 is larger when ascending (opening) than when descending (closing).

Rocker arm 15 is integrally formed, and shaped like a crank as viewed in FIG. 25. The first end portion 15a of rocker arm 15 is formed with a recess 21 which is directed upward as viewed in FIG. 21 and slidably engaged with control cam 26. The second end portion 15b of rocker arm 15 is rotatably supported with respect to the first end portion 17a of link rod 17 through the connecting pin 22 which passes through the pin hole 15c. Recess 21 is U-shaped as in the first embodiment, and the entrance 21a is directed upward in the direction of gravity or opposite to a direction in which a force of gravity acts.

Roller 29 is rotatably supported on roller support shaft 30 in a space 31 which is defined in the center of rocker arm 15 as shown in FIG. 25.

Swing cams 7, 7 are arranged at a predetermined interval, and connected to each other by a cylindrical member 32, as shown in FIG. 25. Each swing cam 7 is triangularly shaped, including a cam surface 7b at the bottom edge. Cylindrical member 32 is rotatably supported on the outer radial periphery of drive shaft 4.

Cylindrical member 32 includes a journal 32a at the center in the longitudinal direction as shown in FIG. 25, and rotatably supported on bearing 33 which is provided at an upper end portion of cylinder head 1. Drive shaft 4 is rotatably supported inside of and by cylindrical member 32.

Link rod 17 is liked with swing cam 7 by connecting pin 20 which passes through the hole of second the end portion 17b of link rod 17 and a projecting portion 7d of swing cam 7, where the projecting portion 7d is formed opposite to the cam nose 7c.

Compression coil spring 24 is arranged between the roller 29 and the tip of the second end portion 15b of rocker arm 15. Compression coil spring 24 has a relatively large spring constant, and pushes the second end portion 15b of rocker arm 15 downward. Accordingly, roller 29 is pressed on the outer radial periphery of drive cam 5 in a radial direction of drive cam 5. Simultaneously, the first end portion 15a of rocker arm 15 is pushed upward, and the inner cylindrical surface 21b of recess 21 is pressed on the bottom surface of control cam 26, while roller 29 serves as a fulcrum.

For example, when the engine is operating at low speed and low load, control shaft 25 is controlled to rotate so that the central axis Q of control cam 26 is substantially in a position just above the central axis P of control shaft 25, as shown in FIGS. 21 and 22. Accordingly, the second end portion 15b of rocker arm 15 is moved to a relatively low position so that swing cam 7 is rotated in the counterclockwise direction via link rod 17, and a portion of cam surface 7b closer to the base circle is in contact with needle roller 12 of swing arm 6. Under the condition described above, the range of movement of the contact point of swing cam 7 is close to the base circle as shown in FIGS. 21 and 22, so that the lift of intake valve 3 is set at the minimum lift set point L.

On the other hand, when the engine shifts to a predetermined high speed and high load region, control shaft 25 is controlled to rotate in the clockwise direction so that the central axis Q of control cam 26 is moved to a position below and on the right of the central axis P of control shaft 25, as shown in FIGS. 23 and 24. Accordingly, the second end portion 15b of rocker arm 15 is moved to a relatively high position so that swing cam 7 is rotated in the clockwise direction via link rod 17, and a portion of cam surface 7b closer to the lift region is in contact with needle roller 12 of swing arm 6. Under the condition described above, the range of movement of the contact point of swing cam 7 is close to the cam nose 7c as shown in FIGS. 23 and 24, so that the lift of intake valve 3 is set at the maximum lift set point L1.

When the central axis Q of control cam 26 is just above the central axis P of control shaft 25 as shown in FIGS. 21 and 22, rocker arm 15 is moved to the left as compared to the position shown in FIGS. 23 and 24. This movement is opposite to the direction of rotation of drive shaft 4. Accordingly, the peak lift phase of intake valve 3 advances as shown in FIG. 7, as compared to the position shown in FIGS. 23 and 24. This changes the intake valve opening timing IVO little, and changes the intake valve closing timing IVC significantly. This is effective as in the first embodiment. The construction that the acceleration of intake valve 3 is larger when ascending (opening) than when descending (closing), is effective for preventing the drive cam 5 from bounding out of contact with roller 29, and thereby, preventing the intake valve 3 from disordered movement.

The structure that the recess 21 of rocker arm 15 is directed upward in the direction of gravity, is effective for allowing the recess 21 to collect lubricating fluid which is scattered inside the housing of the variable valve actuating system, and thereby improving the condition of lubrication between rocker arm 15 and control cam 26. The recess 21 of rocker arm 15 according to this embodiment is also effective in view of assembling and downsizing of the variable valve actuating system as in the first embodiment. When intake valve 3 is open, the recess 21 of rocker arm 15 is also pressed on the outer radial periphery of control cam 26 by the elastic force of 10.

FIGS. 27 and 28 show a variable valve actuating system according to a sixth embodiment of the present invention. In this embodiment, the structure of swing cam 7 is modified with respect to that in the fifth embodiment. Specifically, an upper portion of the structure of cylindrical member 32 and swing cams 7, 7 is cut off so as to form a U-shaped recess 34 whose inner diameter is slightly larger than the outer diameter of drive shaft 4 so that the recess 34 engages with the outer radial periphery of drive shaft 4. The U-shape of cylindrical member 32 is possible, because the projecting portion 7d is located opposite (about 180 degrees) to the cam nose 7c with respect to cylindrical member 32, so that cylindrical member 32 is resistant to inclination with respect to drive shaft 4, although projecting portion 7d is provided offset to one swing cam 7. Cylindrical member 32 is provided with ribs 34b, 34b which are projecting radially from cylindrical member 32, in order to compensate for a fall in bending rigidity of cylindrical member 32 due to the U-shape.

The construction described above is effective for allowing to attach the swing cams 7, 7 to drive shaft 4 by engaging the drive shaft 4 with recess 34 through entrance 34a in the radial direction of drive shaft 4, not in the longitudinal direction of drive shaft 4, and thus making it easy to attach the swing cams 7, 7 to drive shaft 4, although drive shaft 4 is provided with flanges at the longitudinal ends for positioning so that it may be difficult to attach the swing cams 7, 7 to drive shaft 4 in the longitudinal direction. The integrated structure of drive cam 5 and drive shaft 4 is effective for reducing the sizes of the structure in the radial direction and longitudinal direction, and thereby reducing the size of the entire variable valve actuating system. The variable valve actuating system according to the sixth embodiment produces other advantageous effects as in the fifth embodiment.

FIG. 29 shows a variable valve actuating system according to a seventh embodiment of the present invention. In this embodiment, the shape of drive cam 5 is modified into a circular disc as in the first embodiment, as compared to the fifth and sixth embodiments.

Specifically, drive cam 5 in the form of a circular disc is attached to drive shaft 4 in a manner that the central axis Y of drive cam 5 is arranged eccentric by a predetermined distance from the central axis X of drive shaft 4, and the outer radial periphery of drive cam 5 is slidably fit on the circular portion 16a of link arm 16.

Link arm 16 is rotatably supported with respect to rocker arm 15 by connecting pin 28 which passes through the pin hole 15c. Pin hole 15c is formed in a substantially central portion of rocker arm 15 in the longitudinal direction of rocker arm 15.

The first end portion 15a of rocker arm 15 is pressed by compression coil spring 24 upward and leftward to control cam 26 in the radial direction of control cam 26, so that the inner cylindrical surface 21b of recess 21 is constantly maintained in contact with the outer radial periphery of control cam 26. Rocker arm 15 is linked at the second end portion 15b with the projecting portion 7d of swing cam 7 through connecting pins 20 and 22 and link rod 17, as in the fifth embodiment.

The variable valve actuating system according to the sixth embodiment operates as in the fifth embodiment, but differs from the fifth embodiment in that the spring constant of compression coil spring 24 may be small, because movement of rocker arm 15 is supported by drive cam 5 via link arm 16. The spring constant of compression coil spring 24 may be small, if the first end portion 15a of rocker arm 15 as a fulcrum of movement of rocker arm 15 can be softly supported by compression coil spring 24.

The structure that compression coil spring 24 presses the first end portion 15a of rocker arm 15 from below, is effective for eliminating the necessity of arrangement of compression coil spring 24 above rocker arm 15, and thereby reducing the height of the entire variable valve actuating system.

The variable valve actuating system according to the present embodiments may be applied to exhaust valves. The locations of control shaft 25 and control cam 26 may be adjusted according to specifications and sizes of the variable valve actuating system.

The entire contents of Japanese Patent Application 2008-074824 filed Mar. 24, 2008 are incorporated herein by reference.

Although the invention has been described above by reference to certain embodiments of the invention, the invention is not limited to the embodiments described above. Modifications and variations of the embodiments described above will occur to those skilled in the art in light of the above teachings. The scope of the invention is defined with reference to the following claims.

Claims

1. A variable valve actuating apparatus for an internal combustion engine, comprising: a drive cam adapted to be rotated by the internal combustion engine;a control shaft supported for rotation about a rotation axis;a control cam coupled to the control shaft, wherein the control cam is eccentric with respect to the rotation axis of the control shaft;a rocker arm linked with the drive cam, and arranged to swing about the control cam in response to rotary motion of the drive cam, the rocker arm including a recess slidably engaged with an outer radial periphery of the control cam; anda swing cam linked with the rocker arm, and arranged to swing in response to swinging motion of the rocker arm for opening and closing an engine valve of the internal combustion engine.

2. The variable valve actuating apparatus as claimed in claim 1, further comprising a device for maintaining contact between the recess of the rocker arm and the outer radial periphery of the control cam.

3. The variable valve actuating apparatus as claimed in claim 2, further comprising a drive shaft adapted to be rotated by the internal combustion engine, wherein: the drive cam is fixedly mounted to an outer radial periphery of the drive shaft;change of a rotational position of the control shaft causes a movement of the control cam with respect to the drive shaft, and causes at least a change in a lift of the engine valve; andthe rotational position of the control shaft is controlled according to an operating state of the internal combustion engine.

4. The variable valve actuating apparatus as claimed in claim 2, wherein the device is a device for mechanically pressing the recess of the rocker arm on the outer radial periphery of the control cam.

5. The variable valve actuating apparatus as claimed in claim 2, wherein: the recess of the rocker arm has an entrance that is narrower than a diameter of the recess;the outer radial periphery of the control cam partly has a thickness in a radial direction of the control cam which is narrower than the entrance of the recess of the rocker arm; andthe control cam is engaged with the rocker arm in such a rotational position that the control cam is prevented from escaping through the entrance from the recess of the rocker arm.

6. The variable valve actuating apparatus as claimed in claim 2, wherein the control shaft includes a flange supporting the control cam.

7. The variable valve actuating apparatus as claimed in claim 2, wherein the recess of the rocker arm and the outer radial periphery of the control cam have shapes fit on each other.

8. The variable valve actuating apparatus as claimed in claim 2, wherein the recess of the rocker arm has an entrance directed opposite to a direction in which a force of gravity acts.

9. The variable valve actuating apparatus as claimed in claim 2, further comprising a drive shaft adapted to be rotated by the internal combustion engine, and coupled to the drive cam, wherein the swing cam is swingably supported with respect to the drive shaft.

10. The variable valve actuating apparatus as claimed in claim 2, wherein the rocker arm includes a first longitudinal end portion defining the recess, and a second longitudinal end portion opposite to the first longitudinal end portion in a longitudinal direction of the rocker arm, and wherein the second longitudinal end portion is linked with the swing cam for transmitting swinging motion of the rocker arm to the swing cam.

11. The variable valve actuating apparatus as claimed in claim 10, further comprising a link rod linking the rocker arm with the swing cam.

12. The variable valve actuating apparatus as claimed in claim 2, further comprising a roller rotatably supported with respect to the rocker arm, and arranged in rolling contact with the drive cam.

13. The variable valve actuating apparatus as claimed in claim 2, wherein the drive cam has such an asymmetrical cam profile that at least at a maximum lift set point, the engine valve accelerates more rapidly when ascending to a peak of lift than when descending from the peak.

14. The variable valve actuating apparatus as claimed in claim 2, further comprising an actuator for controlling a rotational position of the control shaft according to an operating state of the internal combustion engine, wherein when the actuator applies no torque to the control shaft, the control cam is mechanically held at a position for an intermediate lift set point of the engine valve between a minimum lift set point and a maximum lift set point of the engine valve.

15. The variable valve actuating apparatus as claimed in claim 1, further comprising an actuator for controlling a rotational position of the control shaft according to an operating state of the internal combustion engine, wherein the recess of the rocker arm has an entrance directed opposite to a portion of the rocker arm which is linked with the swing cam.

16. The variable valve actuating apparatus as claimed in claim 15, further comprising a drive shaft adapted to be rotated by the internal combustion engine, wherein the drive cam is mounted for rotation therewith to an outer radial periphery of the drive shaft.

17. The variable valve actuating apparatus as claimed in claim 15, wherein the outer radial periphery of the control cam has an outer diameter which is larger than a width of an entrance of the recess of the rocker arm, and the outer radial periphery of the control cam partly has a thickness in a radial direction of the control cam which is smaller than the width of the entrance of the recess of the rocker arm.

18. The variable valve actuating apparatus as claimed in claim 15, wherein the control shaft includes a flange supporting the control cam.

19. The variable valve actuating apparatus as claimed in claim 15, wherein the recess of the rocker arm and the outer radial periphery of the control cam have shapes fit on each other.

20. The variable valve actuating apparatus as claimed in claim 15, further comprising a drive shaft adapted to be rotated by the internal combustion engine, and coupled to the drive cam, wherein the swing cam is swingably supported with respect to the drive shaft.

21. The variable valve actuating apparatus as claimed in claim 15, wherein the rocker arm includes a first longitudinal end portion defining the recess, and a second longitudinal end portion opposite to the first longitudinal end portion in a longitudinal direction of the rocker arm, and wherein the second longitudinal end portion is linked with the swing cam for transmitting swinging motion of the rocker arm to the swing cam.

22. The variable valve actuating apparatus as claimed in claim 21, further comprising a link rod linking the rocker arm with the swing cam.

23. The variable valve actuating apparatus as claimed in claim 15, wherein the recess of the rocker arm has an entrance directed in a longitudinal direction of a longitudinal end portion of the rocker arm toward a longitudinal end of the rocker arm.

24. The variable valve actuating apparatus as claimed in claim 1, further comprising an actuator for controlling a rotational position of the control shaft according to an operating state of the internal combustion engine, wherein when the engine valve is open, the recess of the rocker arm is pressed on the outer radial periphery of the control cam by an elastic force of a valve spring provided for the engine valve.

25. The variable valve actuating apparatus as claimed in claim 24, further comprising a drive shaft adapted to be rotated by the internal combustion engine, wherein the drive cam is mounted for rotation therewith to an outer radial periphery of the drive shaft.

26. The variable valve actuating apparatus as claimed in claim 24, further comprising a device for preventing the recess of the rocker arm from escaping from the control cam.