JPH10331617A - Valve gear of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To finely vary a working characteristic of an engine valve and to miniaturize a valve gear of an internal combustion engine free to vary the working characteristic of the engine valve which is a suction valve and an exhaust valve in accordance with a driving state of the engine. SOLUTION: This device is constituted so that a first constitutional element 38 is interlocked with and connected to a camshaft 28 and a second constitutional element 37 is connected to an engine valve V1 out of each of the constitutional elements of a motive power transmission means 36 with a carrier 39 to support an inner ring 37, an outer ring 38 and a planetary rotor 40 free to rotate as the constitutional element. A regulating member 57 of a rotational movement quantity control means 48 to control rotational movement quantity of a third constitutional element 39 in accordance with a driving state of an engine is made contact with the third constitutional element 39, and the working direction of the regulating members 57 is set different from working direction of the third constitutional element at a contact point with the third constitutional element 39.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve train for an internal combustion engine, and more particularly to a valve train for an internal combustion engine capable of changing the operating characteristics of an engine valve such as an intake valve or an exhaust valve in accordance with the operating state of the engine. About.

[0002]

2. Description of the Related Art Conventionally, such a valve train is already known, for example, from Japanese Patent Publication No. 7-107368.

[0003]

By the way, in the above-mentioned prior art, the rocker arm connected to the engine valve is driven by selectively switching between a plurality of types of valve cams having different cam profiles. The operating characteristics of the engine valve are switched between two or three stages according to the operating state of the engine. However, in order to further improve engine performance such as engine output torque, fuel consumption and exhaust properties, it is desirable that the operating characteristics of the engine valve can be more finely switched in accordance with the engine operating state. In the configuration of the valve device, more types of valve operating cams having different cam profiles are required, which increases the size of the valve operating device, and is difficult to realize.

Therefore, the applicant of the present invention has provided a planetary gear type or planetary friction type power transmission means between the camshaft and the engine valve, and connected a rotation amount control means to one component of the power transmission means. By controlling the amount of rotation of the components by the amount of rotation control means, a valve operating device capable of finely changing the operating characteristics of the engine valve with a small configuration that eliminates the need for a plurality of valve operating cams has already been developed. Proposal (Japanese Patent Application No. 8-232283)
No.) However, in this case, the rotation amount control means is constituted by a regulating member that contacts the component and an actuator that is connected to the regulating member, and the operating direction of the regulating member and the actuator is such that the regulating member contacts the regulating member at a contact point. It is the same as the operation direction of the component, and the force acting on the regulating member from the component is transmitted to the actuator as it is, so that the size of the actuator must be increased, and the installation space for the actuator must be set relatively wide. I can't get it.

The present invention has been made in view of the above circumstances, and provides a valve operating device for an internal combustion engine that enables the operating characteristics of an engine valve to be finely changed and that can be further downsized. The purpose is to:

[0006]

SUMMARY OF THE INVENTION In order to achieve the above object, an invention according to claim 1 is directed to a valve operating device for an internal combustion engine capable of changing the operating characteristics of an engine valve according to the operating state of the engine. An inner ring rotatably supported on the shaft around the axis of the support shaft, an outer ring surrounding the inner ring enabling rotation about the same axis as the inner ring, and a planetary rotator disposed between the inner ring and the outer ring. A carrier rotatably supported about an axis parallel to the axis of the inner ring and the outer ring, and rotating in conjunction with the revolution of the planetary rotator about the inner ring; Power transmission means in which the component (1) enables rotation operation in accordance with the rotation of the camshaft and is interlocked and connected to the valve operating cam of the camshaft, and the second component is connected to the engine valve; Third component of each component of the means A regulating member which is brought into contact with the third component to regulate the amount of rotation of the third component, and whose operating direction at the point of contact with the third component is set to a direction different from that of the third component; An actuator coupled to the restricting member for enabling the restricting member to be held at a fixed position against a force acting on the restricting member from the component, and controlling the rotation amount of the third component to operate the engine. Turning amount control means for controlling according to the state.

[0007] According to the above configuration, of the three components constituting the power transmission means, the first and second components are:
The rotation amount of the third component is controlled by the rotation amount control means in conjunction with and connected to the camshaft and the engine valve, respectively. The rotation of the component, that is, the operation characteristic of the engine valve is controlled, and the rotation amount of the third component is more finely controlled by the rotation amount control means, so that the operation characteristic of the engine valve is more finely controlled. It becomes possible to control. In addition, the power transmission means is composed of three components, that is, the inner ring, the outer ring, and the carrier, which are rotatably arranged around the same axis, so that the power transmission means can be made compact. The size of the valve train can be reduced. In addition, the regulating member provided in the rotation amount control means makes the operating direction at the point of contact with the third component different from the operating direction of the third component. The force acting on the actuator is not transmitted to the actuator as it is, so that the force exerted by the actuator can be relatively small, making it possible to reduce the size of the actuator and make the installation space for the actuator relatively small. Become.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, the operating directions of the third component and the regulating member at the contact point are substantially perpendicular to each other. , The force acting on the actuator from the third component side becomes extremely small, and it is possible to further reduce the size and space of the actuator.

According to a third aspect of the present invention, in addition to the configuration of the first or second aspect of the invention, the regulating member is a regulating cam provided on a rotating shaft connected to the actuator. Accordingly, the amount of rotation of the third component can be controlled with a simple configuration in which the force from the third component is directed to the center of the rotation axis to minimize the force acting on the actuator.

According to a fourth aspect of the present invention, in addition to the configuration of the third aspect, a rotation axis common to a plurality of cylinders in which the valve opening periods of the engine valves do not overlap is parallel to the camshaft. With this arrangement, the amount of rotation of the third component in the power transmission means of a plurality of cylinders can be controlled by one actuator, so that the number of parts can be reduced, and the valve train in a multi-cylinder internal combustion engine can be further improved. It can be made compact.

According to a fifth aspect of the present invention, in addition to the configuration of the fourth aspect of the present invention, an actuator operating around the same axis as the rotation shaft is connected to one end of the rotation shaft. By providing a detecting means for detecting the angular displacement position of the rotating shaft on the other end side of the rotating shaft, it is possible to further reduce the number of detecting means, and in a multi-cylinder internal combustion engine The arrangement of the valve gear can be made more compact.

According to a sixth aspect of the present invention, in addition to the configuration of any of the third to fifth aspects, the rotating shaft is located on a side opposite to the cam shaft with respect to the support shaft. By being disposed, the rotation shaft is disposed at a position separated from the cam shaft while avoiding the shape of the first component being interlocked with and connected to the cam shaft being restricted,
The degree of freedom in setting the shape of the first component is increased, and in particular, SO
In the HC internal combustion engine, the configuration of one of the intake valve and the exhaust valve is not limited by the other.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

FIGS. 1 to 4 show a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view of an essential part of a four-cylinder internal combustion engine.
2 is a cross-sectional view taken along the line 2-2 of FIG. 1, FIG. 3 is a perspective view of intake side valve gears of the second and third cylinders of the four-cylinder internal combustion engine, and FIG. FIG. 2 is a diagram showing a simplified configuration of FIG.

In FIG. 1, in a multi-cylinder SOHC type internal combustion engine such as a four-cylinder engine, a combustion chamber is provided for each cylinder between an upper surface of a piston slidably fitted to a cylinder block (not shown) and a cylinder head 14. Fifteen
Are formed, and each combustion chamber 15
… A pair of intake valve openings 16 so as to open to the ceiling surface of ...
And a pair of exhaust valve ports 17 is provided for each cylinder,
The two intake valve ports 16 are connected to an intake port 18, and the two exhaust valve ports 17 are connected to an exhaust port 19.

[0016] As the intake valves V _I ... stem 20 ... are of the intake valve ports 16 ... individually openable pair of engine valves slidably fitted with the guide tube 21 ... to the respectively provided in the cylinder head 14 And retainers 22 provided at the upper ends of the stems 20 projecting upward from the respective guide cylinders 21.
A coil-shaped valve spring 23 which surrounds the respective stem 20 ... are provided between the cylinder head 14, with the intake valves V _I ... in a direction to close the intake valve ports 16 ... by their valve springs 23 ... Be inspired. The two exhaust valve ports 17 ... individually openable pair of exhaust valves V _E ... stems 24 ... of slidably fitted with the guide tube 25 ... to the respectively provided in the cylinder head 14, the guide tube Coiled valve springs 27 surrounding the stems 24 are provided between the cylinder head 14 and the retainers 26 provided at the upper end of the stems 24 projecting upward from the cylinders 25. 2
7, the exhaust valves V _E are biased in a direction to close the exhaust valve ports 17.

The two intake valves V _I and the two exhaust valves V _E.
Between them, a camshaft 2 parallel to the axis of a crankshaft (not shown)
8 are rotatably disposed so as to be positioned below the upper end and the upper end of both exhaust valves V _E ... of the intake valves V _I ..., the crank the cam shaft 28 at a reduction ratio of 1/2 Interlocked and connected to the axis. In addition, an oil bath 30 is formed on the upper surface of the cylinder head 14, and the camshaft 28
Is arranged at a position where the intake valve cam 29 _I and the exhaust valve cam 29 _E of the camshaft 28 can be immersed in oil in the oil bath 30.

Both intake valves V_I… And the intake valve on the camshaft 28
Cam 29_IBetween the camshaft 28 and the intake valve
V_I… The intake-side valve train 31 that can be converted to the opening and closing movement of_IBut
Provided, both exhaust valves V_E... and the exhaust side movement of the camshaft 28
Valve cam 29_EExhaust the rotational movement of the camshaft 28
Valve V_EExhaust-side valve train 31 that can be converted to the opening and closing movement of ... _E
Is provided.

Exhaust side valve gear 31_EIs flat with the camshaft 28
Rocker arm shaft 32 fixedly arranged with a vertical axis
And are rotatably supported by the rocker arm shaft 32 and
Ki valve V _E… And the exhaust side valve cam 20_EProvided between
And a rocker arm 33. One end of rocker arm 33
The exhaust valve cam 29_ECam slipper 34 that contacts
The other end of the rocker arm 33 has two exhaust valves V
_E, A pair of tappet screws 35 respectively contacting the upper ends of
… Are screwed in, respectively, with adjustable advance / retreat positions.
You.

[0020] Referring also to FIGS. 2 and 3, the intake-side valve operating device 31 _I is one with a power transmission means 36 for each cylinder, the power transmission means 36, rotating around the axis A sun gear 37 which is a possible inner ring;
A ring gear 38, which is an outer ring surrounding the sun gear 37 so as to be rotatable around the same axis, and planet gears 40, which are a plurality of planetary rotating bodies, are rotated about an axis parallel to the axis of the sun gear 37 and the ring gear 38. A carrier 39 which freely supports and rotates in conjunction with the rotation of the planet gears 40 around the sun gear 37 constitutes a planet gear type.

The sun gear 37 among the three components constituting the power transmission means 36, the sun gear 37, the ring gear 38 and the carrier 39, has an axis parallel to the cam shaft 28, It is rotatably supported by a shaft 41 which is fixedly disposed in the valve V _I ... between. An arm 42 extending toward the camshaft 28 is provided integrally with a ring gear 38 which is one of the above-mentioned components, and a roller 43 rotatably supported by a tip end of the arm 42 includes a camshaft 28.
The is contacted to the intake side valve operating cam 29 _I. That is, the ring gear 38 is connected to the intake valve cam 29 _I on the intake side of the camshaft 28.
The interlocking, which are linked, a ring gear 38 is rotationally driven by an intake-side valve operating cam 29 _I in accordance with the rotation of the cam shaft 28. Moreover interlocking of the intake side valve operating cam 29 _I of the ring gear 38, connecting point or contact point to the intake side valve operating cam 29 _I of the roller 43, the intake valves V _I ... and the camshaft 2
8 is arranged.

Connecting arms 44, 44 extending to both intake valves V _I ... On both sides of a ring gear 38 are fixed to a sun gear 37, which is another component of the power transmission means 36. the tip of these linking arms 44, 44, the tappet screws 45, 45 which respectively contact the upper end of the stem 20, 20 in both the intake valves V _I ... it is screwed respectively be adjustable forward and backward position. As a result, the sun gear 37 is linked and connected to the two intake valves V _I.
The intake valves V _I ... are opened and closed in response to the rotation of the sun gear 37.

The carrier 39, which is the remaining component of the three components constituting the power transmission means 36, has support plates 39a, 39a at both ends, respectively.
7 and the ring gear 38 are coaxially inserted. The planetary gears 40 meshing with the outer periphery of the sun gear 37 and the inner periphery of the ring gear 38 are arranged at a plurality of places, for example, six places at equal intervals in the circumferential direction of the carrier 39. Both ends are rotatably supported by both support plates 39a, 39a.

The two supporting plates 39a, 3 provided on the carrier 39
A regulating arm 46 extending to the opposite side to the camshaft 28 is provided integrally with one of the members 9a.

[0025] By the way, arm the intake-side valve operating cam 29 _I 42
Is pressed, the ring gear 38 is moved in the direction indicated by the arrow 5 in FIG.
0, the two intake valves V _I ... And the sun gear 37 are provided with a valve spring 23.
Since a relatively large spring load of about kgf is exerted, freely revolving, and operates the intake valves V _I ... is opened and closed in the same direction as the arrow 50 is the carrier 39 when the revolution of the carrier 39 is not restricted I will not do it. However, when the revolution of the carrier 39 is restricted, will be the revolution quantity control amount corresponding respective planetary gears 40 ... with rotation ring gear 38 rotates operated, the intake valves V _I ... it is opened actuated, The maximum lift amount and the valve opening period of both intake valves V _I ...
That is, the operation characteristics can be changed steplessly.

The rotation amount i.e. revolution of the carrier 39 is intended to be controlled steplessly rotation amount control means 48, valve springs 23 ... spring force for urging the intake valves V _I ... in the closing direction Acting on the carrier 39 via the sun gear 37 and the respective planetary gears 40, the regulating arm 46 is urged upward, whereas the operating position of the regulating arm 46 is steplessly adjusted by the rotation amount control means 48. Is controlled. Thus to valve springs 23 ... spring force of serves as a large according to the operation of the intake valves V _I ... opening direction of the force to push up towards the control arm 46 upwards is also the intake valves V _I It becomes large according to the valve opening operation of ...
By changing the force rotation amount control means 48 exerts, the control arm 46 results in a force acting from above and below are balanced when both the intake valves V _I ... is opened to a certain degree, its position revolution of the carrier 39 is restricted to, the intake valves V _I
Are also restricted to positions where the forces are balanced as described above.

The spring force of the valve springs 23 is relatively large as described above.
If the force opposing the spring force of 3 is borne only by the rotation amount control means 48, the rotation amount control means 48 will be enlarged. Therefore, an auxiliary regulating arm 51 extending upward is integrally provided on the one support plate 39a of the carrier 39, and an auxiliary force applying means 52 is connected to the auxiliary regulating arm 51.

The auxiliary force applying means 52 includes a head cover 47
A supporting cylinder 53 fixedly supported on the supporting cylinder 51, a piston 54 having one end in contact with the auxiliary regulating arm 51 and slidably fitted to the supporting cylinder 53, and a spring in a direction in which the piston 54 pushes the auxiliary regulating arm 51. A spring 55 is provided between the support cylinder 53 and the piston 54 for exerting a force.

According to such an auxiliary force applying means 52,
The spring force exerted by the spring 55 can be applied to the auxiliary regulating arm 51, that is, the carrier 39, in the same direction as the regulating force from the rotation amount control means 48, and one of the forces opposing the spring force of the valve springs 23. The part can be borne by the assisting force applying means 52.

The turning amount control means 48 includes a turning shaft 56 having an axis parallel to the cam shaft 28, a regulating cam 57 as a regulating member provided integrally with the turning shaft 56, and a turning shaft 56.
And an actuator 58 such as a step motor connected coaxially to one end of the arm, and the regulating cam 57 is brought into contact with the regulating arm 46 so as to apply a regulating force to the regulating arm 46. Thereby, the regulating cam 57 and the regulating arm 46 are
The operating direction of the regulating cam 57 is substantially perpendicular to the operating direction of the regulating arm 46 at the point of contact. That is, the regulating arm 46 rotates around the axis of the support shaft 41 and the regulating cam 5
7, the regulating cam 57 rotates around the axis of the rotating shaft 56 parallel to the support shaft 41, and moves substantially horizontally at the point of contact with the regulating arm 46. Will work.

By the way, as shown in FIG.
In a four-cylinder internal combustion engine having four cylinders arranged in series
Therefore, the ignition order of those cylinders is the first cylinder, the third cylinder,
A fourth cylinder and a second cylinder;
In the third cylinder, the intake valve V_I… The valve opening periods overlap
And in the first and fourth cylinders, the intake valve V
_IThe valve opening periods of ... do not overlap. Like this
And intake valve V_IMultiple valve opening periods that do not overlap
In the cylinder, the carriers 39 in the power transmission means 36.
The timing at which regulatory power is exerted differs from one another. There
In a four-cylinder internal combustion engine, the second and third cylinders
A rotation amount control means 48 having a rotation shaft 56;
Rotation amount control means 4 having a rotation shaft 56 common to the fourth cylinder
8 are provided, and one of the rotation shafts 56 is
The regulating arms 46 of the power transmission means 36, 36 in the three cylinders,
A pair of regulating cams 57, 57 that respectively contact the
And the other rotating shaft 56 has the first and fourth cylinders.
To the regulating arms 46 of the power transmission means 36
A pair of restricting cams 57, 57 that come into contact with each other are provided.
You.

The rotating shafts 56, 56 are arranged on the opposite side of the cam shaft 28 with respect to the support shaft 41 common to the cylinders. Detecting means 59 for detecting angular displacement positions of the moving shafts 56, 56;
59, and the detecting means 59 is, for example,
Gears 60 provided on the outer periphery of the other end of the
And a sensor 61 for detecting 0.

[0033] Next, to explain the action of this first embodiment, the intake-side valve operating device 31 _I, 3 one component constituting the power transmitting means 36 is a planetary gear type, i.e. the sun gear 37, ring gear 38 and The ring gear 38 and the sun gear 37 of the carrier 39 are
8, the intake valve cam 29 _I and the intake valve V _I ...
Since the rotation amount of the carrier 39, that is, the revolving amount, is continuously controlled by the rotation amount control means 48, the two intake valves V
The operating characteristics of _I ... can be controlled steplessly and finely.

The power transmission means 36 has three components, ie, a sun gear 37 and a ring gear 38.
And the carrier 39 is of a planetary gear type comprised disposed rotatably around the same axis, it is possible to reduce the size of the compact namely valve operating device 31 _I of the power transmission means 36, power transmission means The respective components 37, 38, and 39 constituting the fuel cell 36 are meshed with each other, so that the intake valve V
It is possible to accurately control the operating characteristics of _I.

[0035] In such a power transmitting means 36, rotation of the ring gear 38 against rotation amount of the sun gear 37 is a small one, the ring gear 37 is linked to the intake side valve operating cam 29 _I of the cam shaft 28, connected is, the sun gear 37 is linked to the intake valves V _I ..., since it is intended to be connected, the required lift amount i.e. the intake-side valve operating cam 29 _I for rotation of the sun gear 37 in the intake valves V _I ... The size can be set relatively small. Accordingly, the load received by the ring gear 38 from the intake side valve operating cam 29 _{I can} be made relatively small to contribute to the reduction of the valve operating load, and the roller 43 supported by the arm 42 of the ring gear 38 can be reduced.
There can be further reduced valve operating load since rolling contact with the intake-side valve operating cam 29 _I. Further, since the intake valve cam 29 _I is relatively small, the valve cam 29
Space required for rotation of the _I, and the space required for operation of the arm 42 of the ring gear 38 becomes relatively small, thus it is possible to achieve a compact valve operating chamber to place the intake-side valve operating device 31 _I .

[0036] Moreover a single ring gear 38 is disposed on the pair of intake valves V _I ... between adjacent in the axial direction of the cam shaft 28, to the intake valves V _I ... sun gear 37 in the axial direction on both sides of the ring gear 38 interlocking respectively, by being intended to be connected, V _I ... a pair of intake valves in the power transmission means 36 is compactly disposed between the intake valves V _I ..., that for opening and closing the can change its operating characteristics it can be, can be more compact intake-side valve operating device 31 _I.

Furthermore camshaft 28 is disposed at a position sandwiched between the intake valves V _I ... and the exhaust valves V _E ... at lower than the upper end of the intake valves V _I ... and the exhaust valves V _E ..., intake valves V _I ... a The interlocking and connecting points of the intake-side valve-operating cam 29 _I and the ring gear 38 are arranged between the camshaft 28 and the camshaft 28 so that the power transmission means 36 is arranged close to the upper surface of the cylinder head 14, The valve train can be made more compact. Moreover, since the intake side and exhaust side valve cams 29 _I and 29 _E are immersed in the oil in the oil bath 30 formed on the upper surface of the cylinder head 14, the oil bath that can be immersed is formed. The power transmission means 36 can be sufficiently lubricated by scooping up the oil with the side and exhaust side valve cams 29 _I and 29 _E.

The operating direction of the regulating arm 46 connected to the carrier 39 and the operating direction of the regulating cam 57 are the same as those in FIGS.
Are different from each other at the contact points
Therefore, the force acting on the regulating cam 57 is not transmitted to the actuator 58 as it is, so that the force exerted by the actuator 58 can be relatively small, and the size of the actuator 58 can be reduced, and the installation space for the actuator 58 can be reduced. It can be made relatively small. In particular, the regulating cam 39 is provided on the rotating shaft 56, and the operating direction of the carrier 39 and the operating direction of the regulating cam 57 are substantially orthogonal at the contact points of the 39 and 57, so that the regulating arm Control cam 5 from 46
Since the force acting on the actuator 7 is directed to the center of the rotating shaft 56, the force acting on the actuator 58 is extremely small, and the actuator 58 can be further reduced in size and space.

Moreover, in a multi-cylinder internal combustion engine, the intake valve V
_A plurality of cylinders in which the valve opening periods of _I ... Do not overlap, such as the second and third cylinders and the first and fourth cylinders, are provided with common rotation shafts 56, 56 arranged in parallel with the camshaft 28. The amount of rotation of the carriers 39, 39 in the power transmission means 36, 36 for each of the two cylinders can be controlled by one actuator 58, so that the number of parts can be reduced, and the intake-side valve train 31 in the multi-cylinder internal combustion engine can be used. _I can be made more compact.

Further, since the rotating shafts 56, 56 are disposed on the opposite side of the cam shaft 28 with respect to the support shaft 41, the shape of the ring gear 38 which is linked to and connected to the cam shaft 28 is prevented from being limited. As a result, the rotating shafts 56, 56 are arranged at positions separated from the cam shaft 28. Therefore, the degree of freedom in setting the shape of the arm 42 in the ring gear 38 increases. In the SOHC type internal combustion engine as in this embodiment, the exhaust-side valve operating device by an intake-side valve operating device 31 _I 31
The configuration of _E is not limited, and the exhaust-side valve gear 31
_The degree of freedom in setting the shape of the rocker arm 33 in _E increases.

In addition, one end of the rotating shaft 56 is provided with an actuator 58 that operates around the same axis as the rotating shaft 56.
Are connected to each other, and a detecting means 59 for detecting the angular displacement position is provided on the other end side of the rotating shaft 56, so that the number of the detecting means 59 can be further reduced, and the multi-cylinder internal combustion engine is provided. it can be the arrangement of the intake-side valve operating device 31 _I in the engine more compact.

FIG. 5 shows a second embodiment of the present invention, in which a regulating arm 4 connected to a carrier 39 (see FIGS. 1 to 3).
6 ', a regulating member 63 extending in a direction substantially perpendicular to the operating direction 62 of the regulating arm 46' is reciprocated along the longitudinal direction of the regulating member 63 so that the carrier 3
9 may be controlled.

[0043] In the above embodiment, in the power transmission means 36, interlocking the sun gear 37 to the intake valve V _I is connected, the ring gear 38 is interlocked with the cam shaft 28 is coupled, the carrier 3
9 is controlled by the rotation amount control means 48, but the sun gear 37, the ring gear 38 and the carrier 3
Of 9, in conjunction with any one of the intake valves V _I, is connected, also the other one is interlocked with the cam shaft 28, are coupled, one rotation amount of residual need be controlled by the rotational-amount control means 48 .

As another embodiment of the present invention, a linear solenoid or the like can be used as the rotation amount control means, and the power transmission means is disclosed in JP-A-5-33840 and JP-A-5-79450. JP-A-5-157
It is also possible to use planetary friction type power transmission means (traction drive) as disclosed in JP-A-149-149, JP-A-6-34005 and JP-A-6-66360, respectively.

It is also possible to control the amount of rotation of the component, which is interlocked with and connected to the amount-of-rotation control means, of the power transmission means in a plurality of stages instead of steplessly. In this case, the number of stages is set to be larger. By doing so, the operating characteristics of the engine valve can be finely controlled.

[0046] order to further modify the operating characteristics of the intake valves V _I, it is also possible to change only one of the valve opening lift and the valve opening period of the intake valves V _I, the exhaust valve as the engine valve It is also possible to apply the present invention.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible to do.

[0048]

As described above, according to the first aspect of the present invention, the first and second components of the inner race, the outer race and the carrier, which are the components of the power transmission means, are connected to the camshaft and the engine valve. The rotation characteristics of the third component are controlled by the rotation amount control means, whereby the operation characteristics of the engine valve due to the rotation of the camshaft are controlled. By controlling the rotation amount more finely by the rotation amount control means, it becomes possible to more finely control the operation characteristics of the engine valve. And the power transmission means
Since the inner ring, the outer ring, and the carrier that constitute it are arranged so as to be rotatable around the same axis, the power transmission means can be compactly assembled, and the size of the valve train can be reduced. . In addition, the regulating member provided in the rotation amount control means makes the operating direction at the point of contact with the third component different from the operating direction of the third component. By preventing the force acting on the actuator from being transmitted to the actuator as it is, the actuator can be downsized and the installation space for the actuator can be made relatively small.

According to the second aspect of the present invention, the operation direction at the contact point between the third component and the regulating member is set substantially at a right angle, so that the actuator acts from the third component side. The force can be made extremely small, and the actuator can be further reduced in size and space.

According to the third aspect of the present invention, the third configuration has a simple configuration in which the force acting on the actuator is minimized so that the force from the third component side is directed to the center of the rotation shaft. The amount of rotation of the element can be controlled.

According to the fourth aspect of the present invention, the rotation amount of the third component in the power transmission means of a plurality of cylinders can be controlled by one actuator, so that the number of parts can be reduced and the multi-cylinder internal combustion engine can be reduced. The valve operating device can be configured more compactly.

According to the fifth aspect of the present invention, the number of detecting means can be reduced, and the arrangement of the valve train in the multi-cylinder internal combustion engine can be made more compact.

According to the sixth aspect of the present invention, the rotation shaft is moved away from the cam shaft while avoiding the limitation of the shape of the first component which is linked and connected to the cam shaft. It is possible to increase the degree of freedom of the shape setting of the first component by arranging it. Particularly, in the case of the SOHC type internal combustion engine, one of the intake valve and the exhaust valve operates the other valve operating device. It is possible to prevent the configuration from being limited.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a main part of a four-cylinder internal combustion engine.

FIG. 2 is a sectional view taken along line 2-2 of FIG.

FIG. 3 is a perspective view of intake-side valve trains of second and third cylinders of a four-cylinder internal combustion engine.

FIG. 4 is a diagram showing a simplified configuration of a rotation amount control means in a four-cylinder internal combustion engine.

FIG. 5 is a side view of a main part of the second embodiment.

[Explanation of symbols]

28 camshaft 29 _I valve cam 36 power transmission means 37 sun gear as inner ring 38 ring gear as outer ring 39 carrier 40 planetary rotator intake as planetary gears 48 ... rotation amount control means 56 regulating as ... pivot shaft 57 ... restricting member cam 58 ... actuator 63 ... restricting member V _I ... engine valve as valve

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁶ Identification code FI F02D 13/02 F02D 13/02 G

Claims (6)

[Claims] 1. A engine engine valves in accordance with the operating condition of (V _I)
In a valve train of an internal combustion engine capable of changing the operation characteristics of the
An inner ring (37) rotatably supported on the support shaft (41) about the axis of the support shaft (41), and surrounding the inner ring (37) by enabling rotation about the same axis as the inner ring (37). An outer ring (38) and a planetary rotator (40) disposed between the inner ring (37) and the outer ring (38) are rotatably supported around an axis parallel to the axis of the inner ring (37) and the outer ring (38). And the inner ring (3) of the planetary rotating body (40).
7) Carrier (39) that rotates in conjunction with the revolution around it
Are the constituent elements, and those constituent elements (37, 38, 3
The first component of 9) (38) is interlocked with the valve operating cam (29 _I) of the cam shaft (28) as allow turnable operation in accordance with the rotation of the cam shaft (28), is connected, the 2 components (37) the engine valve (V _I) power transmission means connected to the (36); each component of the power transmission means (36) (3
7 to 39), the third component (39) is brought into contact with the third component (39) in order to regulate the amount of rotation of the third component (39), and the operation direction at the point of contact with the third component (39). Is set in a direction different from that of the third component (39), and a force acting on the restriction member (57, 63) from the third component (39). An actuator (58) connected to the restricting member (57, 63) for enabling the restricting member (57, 63) to be held at a fixed position; And a turning amount control means (48) for controlling according to the operating state of the internal combustion engine. 2. The third component (3) at the point of contact.
2. The valve train for an internal combustion engine according to claim 1, wherein the operating directions of the regulating member and the regulating member are set to directions substantially perpendicular to each other. 3. The internal combustion engine according to claim 1, wherein the restricting member is a restricting cam provided on a rotating shaft connected to the actuator. Valve train. 4. A rotary shaft (56) common to a plurality of cylinders in which the valve opening periods of the engine valve (V _I ) do not overlap is arranged in parallel with the cam shaft (28). 4. The valve train for an internal combustion engine according to claim 3. 5. An actuator (58) that operates around the same axis as the rotating shaft (56) is connected to one end of the rotating shaft (56), and is connected to the other end of the rotating shaft (56). Detecting means (5) for detecting the angular displacement position of the rotating shaft (56)
The valve gear of an internal combustion engine according to claim 4, wherein (9) is provided. 6. The rotating shaft (56) is connected to the support shaft (4).
The valve train of an internal combustion engine according to any one of claims 3 to 5, wherein the valve train is arranged on the side opposite to the camshaft (28) with respect to 1).