Electromagnetic driving device of engine valve for internal combustion engine

[0002] This invention relates to an electromagnetic driving device that operates an engine valve for an internal combustion engine of an automobile. This type of the electromagnetic driving devices have been proposed, for example the prior art disclosed in Japan unexamined publication (Koukai) No.8-21220, in which an intake valve slidably disposed on a cylinder head is operated by a magnetic force. Referring now to FIG. 12, there is an electromagnetic driving device that includes a driving mechanism 103 that controls the opening and closing status of an intake valve 102. The intake valve 102 includes a valve portion 1002athat opens and closes an opening of an intake port 104 and a valve stem 102bthat is integrated with an upper end of the valve portion 102a.The electromagnetic driving mechanism 103 comprises an armature 106 that is encased in a casing 105 fixed on the cylinder head 100, is shaped like a plate, and is couple with the upper end of the valve stem 102b, and a pair of electromagnets. In particular, a closing-electromagnetic 107 and an opening-electromagnetic 108 are housed in the respective upper and lower portion of the casing 105 and are placed opposite side of the armature 106 for attracting the armature 106 so as to open and close the intake port 104. An armature spring 109 is installed between an upper wall of the casing 105 and an upper surface of the armature 106 and urges the valve 102 to close the opening of the intake port 104. Similarly, a valve spring 110 is interposed between a concave portion 101 of the cylinder head 100 and a lower surface of the armature 106, and urges the valve 102 to close the opening of the intake port 104. Further, each coil of the closing and opening-electromagnets 107, 108 is energized through an amplifier 111 according to a control signal produced by an electronic control unit 112. The electronic control unit 112 produces the control signal that controls a power-supply to the closing and opening-electromagnets 107, 108 based on any of plural detected signals, such as an engine revolution detected by an engine revolution sensor 113 and a temperature of coolant detected by the thermometer 114. Also, a power source designated 115 supplies a power to each coil of the closing and opening-electromagnets 107,108. Thereby, the spring forces of the valve and armature spring 109,110 and the attracting forces of the electromagnetic 107,108 are retained in respective springs 109,110 as a potential energy. With this, the valve 102 is alternatively attracted and released by one of the closing and opening electromagnets 107,108 to open or close the opening of the intake port 104 using that potential energy.

[0003] In the prior art, however, the attracting force of the closing and opening-electromagnets 107,108 is larger than the spring forces of the armature and valve spring 109, 110 urging the armature 106 against respective attracting forces, so that the end of the valve portion 102amight collide with a valve seat 104aof the cylinder head when the valve 102 closes the opening of the intake port, and the armature 106 might collide with the opening-electromagnetic 108 when the valve 102 opens the opening of the intake port. Referring to FIG. 13A, 13B, there is shown the principle of the attracting force for the closing and opening-electromagnets 107, 108. First, FIG. 13B shows the characteristics of the spring force between the attracting force of the electromagnets 107,108 and the spring forces of the armature and valve spring 109,110 when the valve 102 closes the opening of the intake port, the armature 106 is attracted to the closing-electromagnetic 107. Thereby, the valve spring 110 is extended and the armature spring 109 is compressed, so that a spring force of the armature spring 109 is accumulated therein. Next when the valve 102 opens the opening of the intake port, the closing electromagnet is de-energized, and alternatively the opening-electromagnet 108 is energized, thereby the armature 106 is attracted to the opening-electromagnetic 108. Therefore, the armature spring 109 is extended and the valve spring 110 is compressed, so that a spring force of the valve spring 110 is accumulated therein. Namely, respective accumulated forces of the armature and valve spring 109, 110 affects the armature 106 to reduce the speed of the armature 106 approaching the electromagnets 107,108. On the other hand, because the attracting force of the electromagnet is increased indirectly by the second power of a distance between the core of the electromagnets 107a, 108a, the attracting forces of the electromagnets are suddenly increased when the armature 106 is close to the electromagnets. Therefore, since the accumulated spring forces are not large enough to reduce the increased attracting force of the electromagnetic, the armature 106 is suddenly urged toward the one of the electromagnets 107, 108 when the armature 106 approaches close to one of the electromagnets 107, 108. As seen in FIG. 13A, due to a sudden increased attracting force of the electromagnets 107,108, the valve 102 collides with the valve seat 104a, when the valve closes the opening of the intake port, and the armature 106 collides with the opening-electromagnet 108, when the valve 102 opens it. Thereby, such a collision causes not only noise but also might cause wear and a fracture of the armature 106 and the valve seat 104a.

[0004] Moreover, the prior art requires an arrangement that balances the force between the attracting force of the closing-electromagnet 107 and the armature spring 109, in order to make the valve portion 102aurged toward the valve seat 104awith an appropriate force. However, since a gap between the armature 106 and the core of the electromagnet 107ais varied because of wear of the armature 106, the valve springs 109, 110 and the valve seat 104aand a heat expansion of the valve stem 102b,thereby the attracting force is also varied from the required value. Thus, the gap will occur between the valve portion 102aand the valve seat 104a,so that the valve portion 102amight not be capable of closing the opening of the intake port 104 tightly and might be covered with foreign matter. If so, the valve also might be melted since the foreign matter prevents dissipating heat therefrom.

[0005] Also, method of assembly of the prior art structure of FIG. 12 will be described. At first the valve 102 is inserted in the cylinder head 101 from the opening of the intake port 104a.Then, the opening-electromagnet 108 is disposed on the cylinder head 101. Finally, the armature 106 is coupled with the end of the valve stem 102bwith installing the armature and valve springs 109, 110. Therefore, the prior art requires that assembly has to be performed using on the cylinder head 101, and an accurate arrangement of upper and lower position of the armature 106 with respect to the electromagnets 107, 108. Accordingly, the prior art increases the cost of the manufacturing and manufacturability.

[0006] It is, therefore, an object to the present invention is to provide an improved electromagnetic driving device for a engine valve which is capable of preventing a collision between a valve and a valve seat of a cylinder head, and a collision between an armature and an electromagnet. Another object of the invention is to provide an improved electromagnetic driving device for an engine valve that can be assemble easily and be installed to the cylinder head.

[0007] In order to achieve these and other objects, there is provided an electromagnetic driving device for an engine that comprises an electromagnetic driving mechanism having first and second electromagnets that are placed on opposite sides of an armature, a controller that controls magnetic forces of the electromagnets in accordance with an engine condition for operating a movement of the armature, a follower member, having first and second follower surfaces that are opposite to each other, that is coupled with the armature, a valve that is linked with the armature for closing and opening an intake or exhaust passage, first and second cams having gradually varied profiles that are pivoted for contacting respective first and second follower surfaces, and a spring that urges the first and second cams toward first and second follower surfaces, respectively.

[0008] Other and further objects, features and advantages of the present invention will appear more fully from the following description.

[0009] FIG. 1 is a vertical sectional drawing, showing an electromagnetic driving device for an engine valve in accordance with the first embodiment of the present invention.

[0010] FIG. 2 is a sectional view taken on line A—A of FIG. 1.

[0011] FIG. 3A is an enlarged drawing, showing a first cam of the first embodiment of the present invention.

[0012] FIG. 3B is an enlarged drawing, showing a second cam of the first embodiment of the present invention.

[0013] FIG. 4 is a graph representation, showing a characteristic of a rotational degree of a cam with respect to a vertical stroke of an armature.

[0014] FIG. 5 is a vertical sectional drawing, showing a valve open state of the first embodiment of the present invention.

[0015] FIG. 6 is a vertical sectional drawing, showing a valve close state of the first embodiment of the present invention.

[0016] FIG. 7A is a graph, showing a characteristic of the timing of an intake valve opening and closing of an intake port of a cylinder head.

[0017] FIG. 7B is a graph, showing a characteristic of a spring force of respective electromagnets and springs.

[0018] FIG. 8 is a fragmentary sectional drawing, showing a cam of an electromagnetic driving device in accordance with a second embodiment of the present invention.

[0019] FIG. 9 is a perspective view, showing a cam in accordance with the second embodiment of the present invention.

[0020] FIG. 10 is a vertical sectional view, showing an electromagnetic driving device of a third embodiment of the present invention.

[0021] FIG. 11 is a perspective view, showing a linkage between an end of valve and a follower of the third embodiment of the present invention.

[0022] FIG. 12 is a vertical sectional view, showing a conventional electromagnetic driving device.

[0023] FIG. 13A is a graph, showing the timing of an intake valve opening and closing an intake port of a cylinder head in accordance with a prior art.

[0024] FIG. 13B is a graph, showing a characteristic of a attracting force of respective electromagnets and a spring force of respective springs.

[0025] An electromagnetic driving device for an engine valve, and in particular the electromagnetic driving device applied to an intake valve of internal combustion engine in accordance with preferred embodiments of the present invention, will be described with reference to the Figures.

[0026] FIG. 1 is a vertical sectional view of the first embodiment that shows the electromagnetic driving device that includes an intake valve 23 that opens and closes the intake port 22 formed in a cylinder head 21. FIG. 1 also shows an electromagnetic driving mechanism 24 that operates the intake valve 23 in order to open and close the intake port 22 according to an engine condition, and a brake mechanism 25 that is disposed in a linkage between the electromagnetic driving mechanism 24 and the intake valve 23. The intake valve 23, having a valve portion 23a, is faced to a combustion chamber, and a valve stem 23bis integrated with an upper end of the valve portion 23aand is sliderably inserted in a valve guide 26. The intake valve 23 closes the intake port when the valve portion 23aseats a circular-shaped valve seat 22a.On the other hand, as the valve portion 23ais apart from the valve seat 22a,the intake valve 23 opens the intake port 22.

[0027] The intake valve 23 is also urged to close the intake port 22 by the valve spring 28 that is interposed between a retainer 23dfixed at an end of valve stem 23cand a concave portion 27 formed in the cylinder head 21.

[0028] The electromagnetic driving device 24 includes an armature 30 shapes like a plate, a pair of electromagnets, a closing-electromagnet 31 and a opening-electromagnet 32, are placed opposite side of the armature 30 and are encased in a casing 29 disposed on the cylinder head 21.

[0029] The armature 30 is capable of moving within a gap formed between the electromagnets 31, 32, and an armature spring 33 is installed on an upper surface of the armature 30 and urges the armature 30 in an opening direction of intake valve 23.

[0030] As shown FIG. 1, the casing 29 having a casing body 29athat is fixed on the cylinder head 21 by means of four bolts 34, and is covered with a casing cover 29bmade of non magnetic material through a plurality of screws 35. A casing holder 36 made of non magnetic material is inserted in an inner circumference of the casing cover 29b,and an upper opening of the casing cover 29bis covered with a lid 37 made of non-magnetic material. The lid 37 is provided with a closing-electromagnet 31 on an inner surface thereof and an air hole 37aat its center portion for establishing an air communication between an inside and outside of the casing cover 29b.The opening-electromagnet 32 is fixed on a bottom of the casing holder 36aso as to face to the closing-electromagnet 31 affixed to the lid 37.

[0031] An upper and lower surface of the armature 30 face the respective closing and opening-electromagnet 32, 33. An upper end of guide rod 38ais coupled with a center portion of the armature 30 through a screw, and a lower end of guide rod 38 is integrated with a follower 45 of the brake mechanism 25. The guide rod 38 is slidably inserted in a cylindrical guide 39 so that an axis X of the guide rod 38ais coaxial with an axis Y of the intake valve 23.

[0032] The closing and opening-electromagnets 31, 32 and provided with fixing cores 31a, 32athat are formed with a U-shape cross section and are disposed on opposite sides of the armature 30. The electromagnetic coils 31b, 32bare wound around an inner wall of the fixing cores 31a,32aand are energized according to an energized signal or a de-energized signal from an electric control unit 40 for attracting the armature 30 upwardly or downwardly.

[0033] The armature spring 33 is interposed between an upper surface of the armature 30 and an under surface of the lid 37, and a spring force of the armature spring 33 is designed so as that the armature 30 is positioned at a midpoint between the electromagnets 31, 32 when both of the electromagnets 31, 32 are de-energized. In that situation, the intake valve 23 is also kept at substantially midpoint between maximum and zero valve lifts.

[0034] The electronic control unit 40 alternatively and repeatedly outputs the energized and de-energized signals to the respective closing and opening-electromagnets 31,32. In order to determine the energized and de-energized signals, a crank sensor 41 detecting a rotational degree of the crank, an engine revolution sensor 42 detecting an engine revolution, a thermometer 31 detecting a temperature of the closing-electromagnets 31, and an air flow meter 44 detecting an engine load are provided, and the outputs of these sensors are fed to the electronic control unit 40. A signal indicating a rotational crank degree from the crank sensor 41 is used for bringing opening and closing timing of the intake valve 23 into sync with the rotational timing of the crank shaft. A signal indicating a revolution of the engine from the engine revolution sensor 42, that is, a revolution of crank shaft, is used for calculating permissible attraction time of the electromagnets 31, 32. A signal indicating a temperature of the closing-electromagnet 31 from the thermometer 43 is used for regulating a increasing resistance of the electromagnetic coil 31bfrom the increasing temperature thereof. A signal indicating a load of the engine from the air flow meter 44 is used for controlling the appropriate opening and closing timing of the intake valve 23 according to an engine condition.

[0035] As shown in FIG. 1 and FIG. 2, the braking mechanism 25 includes the follower 45 that is integrated with the lower end 38bof the guide rod 38, first and second swing cams 46, 47 that are rotatably supported on an inside of the follower 45, and first and second coil springs 48, 49 that urge the first and second swing cams 46, 47 toward respective first and second surfaces 45a, 45bof the follower 45.

[0036] The follower 45 is substantially shaped like a rectangle or a square and comprises an upper and lower portions of the follower 45 that is provided with the respective first and second follower surfaces 45a, 45bso as to face each other. The lower end of the guide rod 38 is integrated with the upper portion of the follower 45, and a protrusion 45cformed on the lower portion of the follower 45 is contacted with the stem end 23cof the valve stem 23b.

[0037] As illustrated in FIG. 2, each first and second swing cam 46, 47 is rotatably supported on a cam support shaft 51 that penetrates respective support holes 46a, 47aformed in the first and second swing cam 46, 47. Each end of the cam support shaft 51 is supported on a boss portion 50a, 50bof the casing 29 located an on opposite side of the first and second cams 46, 47. Namely, the first and second swing cam 46, 47 are supported coaxially on the cam support shaft 51 and adjacent to each other with slidable contact. Also, the axis Q of the cam support shaft 51 intersects with the axis X, Y of the guide rod 38 and the intake valve 23, respectively. Moreover, as shown in FIG. 3A and FIG. 3B, the first and second cams 46, 47 are shaped substantially like an egg in cross section, and a first cam surface 52 formed on entire upper surface of the first cam 46 rotatably contacts with the first follower surface 45a.Similarly, a second cam surface 53 formed on entire lower surface of the second swing cam 47 contacts with the second follower surface 45b.Each first and second cam surface 52, 53 has several cam profiles. The profiles include first and second base profiles 52a, 53athat are defined by a circle having a radius R0 centered on the axis Q of the cam support shaft 51, first and second ramp profiles 52b, 53bhaving gradually increased surfaces defined by radius of curvature R1 centered on the axis Q and being continuously connected with the base profiles 52a, 53a, respectively, and first and second lifting profiles 52c, 53chaving lifting surfaces that are defined by radius of curvature R2 centered on the axis Q that are smaller than the radius of curvature R1 and are continuously connected with the first and second ramp profiles 52b, 53b, respectively. There also are the third and fourth ramp profiles 52d, 53dhaving gradually increased surfaces that are defined by radius of curvature R3 that are smaller than that of R1 and continuously connected with the first and second lifting profiles, respectively, and first and second nose profiles 52e, 53ehaving gradually increased surfaces defined by a radius R3 that are smaller than the radius of curvature R1 and are continuously connected with the first and second lifting profile 52d, 53d.As shown FIG. 4, each of the valve lift profile of the first and second swing cams 46, 47 with respected to rotation θ is designed with are S shape, and the first and second nose profile 52e, 53eare designed so as that a contacting distance between the first and second cam surfaces 52, 53 and the first and second surfaces of the follower 45a, 45bis relatively shorter. Therefore, the shorter contacting distance is possible to make the follower member 45 compact and able to contact with the first and second swing cams 46,47 smoothly when a vertical moving direction of the follower member 45 is changed. As illustrated in FIG. 5 and FIG. 6, first and second gaps Go, Gc are formed between the electromagnets 31, 32 and the armature 30 when the base profiles 52a, 53aof the swing cams 46, 47 are contacted with the respective follower surfaces 45a, 45bof the follower 45. As seen in FIG. 2, the first and second springs 48, 49 are wound around the cam support shaft 52, and each end of the springs 48a,49ais retained in the respective boss portions 50a, 50b.The other end of the springs 48b,49bare secured to the center portion of nose of the swing cams 46, 47, respectively. Thereby, each of the swing cams 46, 47 is urged resiliently against respective follower surfaces 45a, 45b.

[0038] The manner of operation of the first embodiment of the electromagnetic driving device in connection with the drawing will be explained.

[0039] First, when the engine is stopped, the first and second electromagnets 31, 32 are de-energized because no signals from electric control unit 40 is fed to the electromagnets 31, 32. Thereby, the armature 30 is positioned at a middle point of a gap S in balance between spring forces of the springs 28, 33. (See FIG. 1) Thus, the intake valve 23 is moved apart from the valve seat 22aand is lifted, indicating substantially a middle point between zero valve lift and maximum valve lift. In this state, each swing cam 46, 47 is exerted against the respective first and second follower surfaces 45a, 45bby the first and second springs 48, 49, as seen in FIG. 2.

[0040] Next, as seen in FIG. 5, when the engine is started, the electric controller 40 feeds the energized signals to the core 32bof the opening-electromagnet 32, and the armature 30 is attracted toward the opening-electromagnet 32 and is also urged downwardly by the armature spring 33. With this, the follower 45 is also moved downwardly by the guide rod 38 in accordance with the movement of the armature 30, and the protrusion 45cof the follower 45 pushes the intake valve 23 downwardly to open the intake port 22yagainst the valve spring 28.

[0041] On the other hand, when the intake valve 23 is operated in a closing state, the opening electromagnet 32 is de-energized, and the coil 31bof the closing electromagnet 31 is energized. (See FIG. 6)

[0042] Hence, the armature 30 is attracted to the closing-electromagnet 31 and is also urged upwardly by the valve spring 28. Thus, the intake valve 23 is moved upwardly against the spring force of the armature spring 33 and is seated against the valve seat 22ato close the intake port 22.

[0043] As a result, as the follower 45 is moved in a vertical direction, the first and second cam surface 52, 53 of the swing cams 46, 47 are swinging around the axis of the cam support shaft 51 and are contacted with respective the follower surface 45a, 45bagainst the spring force of the first and second springs 48, 49. Namely, as shown in FIG. 7A, the first and second swing cams 46, 47 are moving in a clockwise or counterclockwise direction, so that the swing cams 46, 47 make the intake valve 23 open and close smoothly at the end period of the movement thereof

[0044] As mentioned above, when the intake valve 23 is moved upwardly by attracting force of the closing-electromagnet 31 and the spring force of the valve spring 28, a contacting point P between the second cam surface 53 and the second follower surface 45bis moved from the second lifting profile 53dto the base profile 53a.(See FIG. 5 and FIG. 6) Namely, when the intake valve closes the intake port 22, as shown FIG. 7, the second spring 49 urges the follower 45 downwardly in the opposite direction of the movement of the intake valve 23, and brakes the movement of the intake valve 23 at the end period of valve closing operation. That is, the braking function affects the movement of the armature 30 and the intake valve 23 and decreases the speeds of the movement of the armature 30 and the intake valve 23 through the second swing cam 47 and the second follower surface 45bduring the end period of the closing stroke of the intake valve 23. After that, the base profile 53aof the second swing cam surface 53 is contacted with the second follower surface 45b, so that the intake valve 23 is seated against the valve seat 22agently and smoothly.

[0045] Similarly, the braking function (buffering function) affects the armature 30 and the intake valve 23 at the end period of the opening valve operation. In this situation, the contacting point P between the first swing cam 46 and the first follower surface 45ais moved from the lifting profile 52dto the base profile 52a, so that the first spring 48 urges the follower member 45 toward the opposite direction of the movement of the armature 30. Therefore, the armature 30 is prevented from colliding with the opening-electromagnet 32, and the intake valve 23 exhibits an ideal valve lift characteristic at the end period of the opening stroke thereof In brief, a turning moment on the follower 45 produced by swinging of respective first and second cams 46, 47 performs a braking function at the end period of the opening and closing valve lift, so that a buffering effect is provided on the intake valve 23.

[0046] As mention above, a resultant spring force of valve spring 28, armature spring 33, and respective first and second springs 48, 49 acting on the armature 30 increases suddenly where the armature 30 is at upper and lower positions of the gap S between the electromagnets 31, 32. Namely, as shown in FIG. 7B, the sudden increase of resultant spring force performs as the braking function at the end period of opening and closing valve lift.

[0047] Thereby, as seen in FIG. 7A, especially in areas as shown by dotted-line circle of FIG. 7A, the intake valve 23 is capable of seating against the valve seat 22asmoothly and gently. Therefore, this invention makes it possible to prevent noise, wear and damage caused by the collision between the intake valve 23 and the valve seat 22aand between the armature 30 and the opening electromagnet 32.

[0048] In addition, as illustrated in FIG. 5 and FIG. 6, since the gaps Go, Gc are formed between the upper and lower surfaces of the armature 30 and the respective closing and opening-electromagnets 31, 32 at the uppermost and the lowermost position of the armature 30, this invention makes it possible to prevent the collisions between the armature 30 and respective closing and opening electromagnets 31, 32.

[0049] Moreover, since the electromagnetic driving mechanism 24 is disposed separately from the intake valve 23, the intake valve 23 is capable of seating the valve seat 22atightly, even if a gap exists between the protrusion 38band the end of the stem 23c.Therefore, the intake valve 23 seats the valve seat 22astably and tightly.

[0050] Further, the intake valve 23 and the valve spring 28 are arranged in the conventional way. Therefore, the electromagnetic driving mechanism 24 and the braking mechanism 25 can be assembled in advance and installed on the cylinder head 21 easily.

[0051] Also, in the first embodiment of the present invention, since each of the first and second swing cams 46, 47 is exerted toward respective first and second cam surfaces 45a, 45bby the first and second spring 48, 49, respectively, it is not necessary to manage respective clearances between the first and second follower surfaces 45a, 45band the first and second cam surfaces 52, 53. As mentioned above, the first embodiment doesn't require a close tolerance to manufacture the swing cams 46, 47 and the follower 45 so that the cost of manufacturing can be reduced.

[0052] Moreover, since the swing cams 46, 47 are manufactured and designed with their cam profiles separately, the armature 30 can obtain an appropriate buffering effect at the uppermost and lowermost positions thereof.

[0053] Further, if wear is occurs between the first and second cams 52, 53 and respective first and second follower surfaces 45aand 45b, the first and second cams 52, 53 are always urged and contacted with respective follower surfaces 45a, 45bby the first and second spring 48, 49. With this, the braking function and the buffering effect are never decreased due to wear.

[0054] Moreover, the guide rod 38 is prevented from leaning effectively where the axis Q of the cam support shaft 51 intersects with either the axis X of the guide rod 38 or the axis Y of the valve stem 23.

[0055] Also, in the first embodiment, the follower 45 may be formed to be symmetric with respect to the axis X of the guide rod 38. In this case, it is not only possible to make it compact, but it is not necessary to consider an aspect of the follower 38 when it is assembled.

[0056] Next, since the electromagnetic driving device is identical to the first embodiment, like elements are given like reference characters. FIG. 8 and FIG. 9 are similar to the first embodiment with the exception that it provides a braking mechanism 25 having an torsion coil spring 54 that urges both of the first and second cams 46, 47 toward the follower surfaces 45a, 45b.

[0057] Namely, the torsion coil spring 54 is interposed between the first and second cams 46, 47, and one of the ends of the torsion coil spring 54bis inserted into a first holding hole 46athat is formed on a side surface of the first cam 46, and the other end of the torsion coil spring 54cis inserted in the second holding hole 47athat is formed on a side surface of the second cam 47. Thereby, the torsion coil spring 54 exerts a force on the first and second cams 46, 47 in opposite directions so as that the first and second cam surfaces 52, 53 are resiliently urged to the first and second follower surface 45a, 45b.With the second embodiment, the cost of manufacturing and a saving space can be further lowered in comparison with the foregoing first embodiment, which achieving substantially an equivalent effect to the first embodiment.

[0058] FIG. 10 and FIG. 11 shows a third embodiment of the present invention, and a lower end protrusion 45cof the follower 45 is linked with the valve stem 23 by means of a mechanical linkage having a hook formed in the lower end of the follower 45, a cut-out groove 61 formed at the stem end 23 and provided with a pin hole, and a pin 62 inserted through the pin hole and the cut-out groove 61. The third embodiment also can decommission the armature spring 33 and the valve spring 28 that are used in foregoing embodiment. As shown in FIG. 11, the hook 60 is provided with a groove 60aextending in the lateral direction that engages with the cut-out groove 61 extending in longitudinal direction and shaped like a fork through the pin 62. In addition, the spring forces of the first and second springs 48, 49 are designed to be larger than that of the first and second embodiment, so as to make the intake valve 23 positioned at middle of valve lift stroke, which achieving the same effect to the armature spring 33 and the valve spring 28.

[0059] Therefore, since the armature spring 33 and the valve spring 28 are removed from the service, the third embodiment is simple and easily assembled.

[0060] The present embodiments are to be considered as illustrative and not restrictive and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.

[0061] For example, while the embodiment of the invention shows that the intake valve 23 is subject to the electromagnetic driving device, an exhaust valve also may be controlled. In this case, the exhaust valve is capable of controlling the valve movement smoothly and gently at the end of term of the closing a exhaust, so that it reduce a noise of a exhaust gas.

[0062] The entire contents of basic Japanese Patent Application, application No. 11-126811, filed May 7, 1999 of the application of which priority are claimed, are herein incorporated by reference.