WO2008032491A1

WO2008032491A1 - Electromagnetic valve device for engine

Info

Publication number: WO2008032491A1
Application number: PCT/JP2007/064503
Authority: WO
Inventors: Noriaki Fujii; Tomoya Fujimoto; Hisao Sakai; Keiko Yoshida
Original assignee: Honda Motor Co., Ltd.
Priority date: 2006-09-13
Filing date: 2007-07-24
Publication date: 2008-03-20
Also published as: TW200827534A; EP2063076A4; EP2063076A1; EP2063076A8; US20100059003A1; KR20090055601A

Abstract

An electromagnetic valve device (20) for an engine. The valve device (20) has an armature (23) having one end pivotally supported at a cylinder head by a fixing shaft (38) and the other end in contact with a stem (18) of an air intake valve (17). The intake valve (17) is opened and closed by attracting a first attraction surface (23b) and second attraction surface (23c) of the armature (23) by a first electromagnet (21) fixed to the cylinder head and by a second electromagnet (22) rockably supported on the cylinder head by the fixing shaft (38). In opening and closing operation of the intake valve (17), the amount of lift of the air intake valve (17) can be varied as desired by rocking the second electromagnet (22) to vary the angle between the first and second electromagnets (21, 22). Rocking either of the first and second electromagnets (21, 22) is sufficient for the purpose, and in addition, it is not necessary to change the position of the armature (23). These make the electromagnetic valve device (20) compact.

Description

Specification

Engine solenoid valve

Technical field

The present invention relates to an electromagnetic valve device of an engine that opens and closes a valve by an armature that is alternately attracted and oscillated by a first electromagnet and a second electromagnet.

Background art

An upper disc (amateur) whose tip is connected to the drive valve and whose base end is pivotally supported by a disc base movable in a direction perpendicular to the opening and closing direction of a drive valve provided on a cylinder head of an engine And lower disc (amateur), an electromagnet disposed on the inner side of both discs, and a pair of permanent magnets disposed on the outside of both discs, and controlling energization of the electromagnet to The drive valve is opened and closed by alternately attracting to and reciprocating from the permanent magnet, and the disk base is moved by the actuator to change the lever ratio of both disks, thereby changing the lift amount of the drive valve. It is known from the following patent document 1.

Patent Document 1: Japanese Patent Application Publication No. 2006-22776

Disclosure of the invention

Problem that invention tries to solve

[0003] By the way, in the above-mentioned conventional type, it is necessary to move the disk base supporting one electromagnet, two permanent magnets and two disks (amateur) with an actuator.

There has been a problem that the overall size of the solenoid valve device is increased, which causes a great restriction in arranging in a narrow space in the cylinder head of the engine.

The present invention has been made in view of the above-mentioned circumstances, and it is an object of the present invention to miniaturize an electromagnetic valve device in which a valve is opened and closed with an arbitrary lift amount by an electromagnet.

Means to solve the problem

[0005] In order to achieve the above object, according to a first feature of the present invention, an armature is pivotally supported at one end on an engine body and the other end abuts on a valve stem; A first electromagnet capable of adsorbing the first adsorbing surface of the first and the second adsorbing surface of the armature And an electromagnet of at least one of the first and second electromagnets is pivotally supported about a fixed axis fixed in position with respect to the engine body. An electromagnetic valve device of an engine is proposed.

According to a second feature of the present invention, in addition to the first feature, the one electromagnet causes the valve to lift and defines the lift amount of the valve. An electromagnetic valve device for the engine is proposed.

According to a third aspect of the present invention, in addition to the first or second aspect, the valve spring includes a pair of valve springs for urging the armature to a neutral position, and one of the valve springs is An electromagnetic valve device for an engine is proposed, wherein a spring seat to be supported is fixed to the engine body, and a spring seat to support the other valve spring moves in response to the swing of the one electromagnet.

According to a fourth feature of the present invention, in addition to the third feature, the other valve spring and the spring seat for supporting the valve spring are disposed on the outer periphery of the stem of the valve, An electromagnetic valve device for an engine is proposed, wherein the spring seat is integrally connected to the one electromagnet to move.

[0009] According to a fifth aspect of the present invention, in addition to any of the above first to fourth features, the armature is pivotally supported via the fixed shaft. An electromagnetic valve system is proposed.

According to a sixth aspect of the present invention, in addition to the fifth aspect, the other electromagnet of the first and second electromagnets is provided with a fixing portion for fixing the fixed shaft. An electromagnetic valve device for an engine is proposed.

According to a seventh feature of the present invention, in addition to the first feature, a first valve spring for biasing the valve in the valve closing direction, and a valve for biasing the valve in the valve opening direction. A solenoid valve device for an engine is proposed, comprising: a second valve spring, wherein the second valve spring biases a lever provided on the one end side of the armature.

[0012] According to an eighth feature of the present invention, in addition to the feature of claim 7, the one electromagnet includes a lever provided at one end side pivotally supported by the fixed shaft, and the armature lever Apply a biasing force to one end of the second valve spring, and An electromagnetic valve device for an engine is proposed, characterized in that an urging force on the other end side of the second valve spring is applied to a lever of a magnet.

According to a ninth aspect of the present invention, in addition to the eighth aspect, at least a portion of the force of the armature of the armature and the lever of the one electromagnet is viewed in the cylinder row direction. An electromagnetic valve device for an engine is proposed.

According to a tenth feature of the present invention, in addition to the eighth or ninth feature, a guide pivotally supported at one end by the lever of the armature and provided with a first spring seat at the other end. The end of the second spring seat provided on the lever of the one electromagnet penetrates the end of the second valve spring supported on the outer periphery of the guide rod. (2) A solenoid valve device of an engine is proposed which is characterized in that it abuts on a spring seat.

According to an eleventh feature of the present invention, in addition to the eighth to tenth features, an actuator for swinging the one electromagnet drives the other end side of the electromagnet. A solenoid valve device of the engine is proposed.

The cylinder head 12 and the head cover 13 of the embodiment correspond to the engine body of the present invention, and the intake valve 17 of the embodiment corresponds to the valve of the present invention. The first electromagnet 21 of the embodiment Corresponds to the other electromagnet of the present invention, the second electromagnet 22 of the embodiment corresponds to one electromagnet of the present invention, and the inner block member 27 of the embodiment corresponds to the fixed portion of the present invention. The first valve spring 47 and the second valve spring 51 of the form correspond to the valve spring of the present invention.

Effect of the invention

[0017] According to the first aspect of the present invention, an armature of which one end is pivotally pivotally supported about a fixed axis fixed in position with respect to the engine body and the other end abuts on the stem of the valve. Since the first adsorption surface and the second adsorption surface are respectively attracted by the first and second electromagnets, the valve lift amount can be arbitrarily changed by oscillating at least one of the first and second electromagnets. . In addition, since it is good if only at least one of the first and second electromagnets is swung and there is no need to move the position of the armature, it is possible to make the electromagnetic valve device compact. In particular, one of the electromagnets is swung to change the lift amount of the valve. Therefore, the solenoid valve can be made compact in the axial direction of the valve.

Further, according to the second feature of the present invention, since the valve lift is generated by the swinging electromagnet and the valve lift amount is defined, the valve can be opened as reliably as possible. The lift amount of the valve can be changed while suppressing the deterioration of the collision noise at the time of the valve.

According to a third aspect of the present invention, of the pair of valve springs for urging the armature to the neutral position, a spring seat for supporting one of the valve springs is fixed to the engine main body, Since the spring seat supporting the valve spring is moved according to the swing of the one electromagnetic stone, the armature's neutral position shifts significantly even if the engine is stopped when the one electromagnet is in any swing position. It is possible to prevent the armature from being attracted to the first electromagnet or the second electromagnet when the engine is started.

Further, according to the fourth feature of the present invention, since the other valve spring and the spring seat for supporting the valve plug are arranged on the outer periphery of the stem of the valve, it is possible to make the electromagnetic valve device compact. Since the spring seat, which is not the only one, is integrally connected to the one electromagnet and moves in response to the swing of the one electromagnet, the armature can be reliably biased to the neutral position.

Further, according to a fifth aspect of the present invention, since the one electromagnet and the armature are pivotally supported on the same fixed shaft, even when the one electromagnet is swung, the armature is attracted to the electromagnet. The same positional relationship as the above makes it easy to manage the attraction surfaces of the electromagnet and the armature.

Further, according to the sixth aspect of the present invention, since the fixing portion for fixing the fixed shaft to the other of the first and second electromagnets is provided, the positional relationship between the other electromagnet and the armature is It is stable, and it becomes easy to manage the adsorption surface of the other electromagnet and the armature, and it is not necessary to separately secure a member for providing a fixed shaft.

[0023] According to a seventh aspect of the present invention, of the first valve spring for urging the valve in the valve closing direction and the second valve spring for urging the valve in the valve opening direction, the second valve spring is an armature. Since the lever provided at one end side pivotally supported by the fixed shaft is biased, the second It is not necessary to arrange the valve spring on the extension of the stem of the valve, and the solenoid valve can be miniaturized.

According to an eighth feature of the present invention, the lever provided at one end of the armature and the lever provided at one end of the one electromagnet each have one end of the second valve spring and the other. Since the biasing force on the end side is applied, the armature can be rocked by the spring force of the second valve spring according to the rocking of one of the electromagnets, and one of the electromagnets is in any rocking position. Even if the engine is stopped, the armature's neutral position is prevented from shifting significantly, and when the engine is started, the force S is applied to ensure that the armature is attracted to the first electromagnet or the second electromagnet.

Further, according to a ninth aspect of the present invention, since the armature lever and the lever of one of the electromagnets are disposed so as to overlap at least partially in the direction of the cylinder row, the electromagnetic valve device Can be miniaturized.

[0026] According to a tenth feature of the present invention, a second spring is provided on a lever of one of the electromagnets with a guide rod pivotally supported at one end by an armature lever and provided at the other end with a first spring seat. Since the seat is penetrated and one end and the other end of the second valve spring supported on the outer periphery of the guide rod are respectively brought into contact with the first spring seat and the second spring seat, the guide rod serves as a support member for the second valve spring. The ability to reduce the number of parts by

Further, according to the first aspect of the present invention, since the actuator for swinging one electromagnet drives the other end side of the electromagnet, that is, the side away from the fixed shaft for pivoting the electromagnet, Reduce the load on the actuator and increase the positioning accuracy of the swing position of the electromagnet.

Brief description of the drawings

[FIG. 1] FIG. 1 is a cross-sectional view of a cylinder head of an engine provided with a solenoid valve device according to a first embodiment. (First embodiment)

[FIG. 2] FIG. 2 is an enlarged view of an essential part of FIG. (First embodiment)

[FIG. 3] FIG. 3 is an exploded perspective view of the solenoid valve device. (First embodiment)

[FIG. 4] FIG. 4 is an exploded perspective view of a swing drive part of a second electromagnet. (First embodiment) Garden 5] Fig. 5 is an explanatory view of the operation at low lift and high lift (neutral state). (First embodiment)

Garden 6] Figure 6 is an explanatory view of the operation at the time of low lift and high lift (maximum lift state). (First embodiment)

Garden 7] FIG. 7 is a cross-sectional view of a cylinder head of an engine provided with a solenoid operated valve gear according to a second embodiment. Second Embodiment

[FIG. 8] FIG. 8 is an enlarged view of an essential part of FIG. Second Embodiment

[FIG. 9] FIG. 9 is a perspective view of FIG. Second Embodiment

Garden 10] FIG. 10 is an exploded perspective view of the solenoid valve device. Second Embodiment

[FIG. 11] FIG. 11 is an exploded perspective view of a second electromagnet and its rocking drive part. Second Embodiment

)

Garden 12] Figure 12 is an action explanatory view (neutral state) at low lift and high lift. (2nd embodiment)

Garden 13] Figure 13 is an explanatory view of the operation at the time of low lift and high lift (maximum lift state). Second Embodiment

Explanation of sign

12 cylinder head (engine body)

13 Head cover (engine body)

17 Intake valve (valve)

18 stem

21 1st electromagnet (the other electromagnet)

22 Second electromagnet (one electromagnet)

23 Amateur

23b First suction surface

23c Second suction surface

23d lever

27 Inner block member (fixed part)

34d lever 44 Spring seat

47 1st Baluf '' Spring

49 Spring seat

51 2nd Baluf '' Spring

43 Acts

150 guide lock f

151 First Spring: Tongue Sheet

152 Second Spring: Tongue Sheet

153 Second Balf '' Spring

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described based on the attached drawings.

Example 1

FIGS. 1 to 6 show a first embodiment of the present invention.

As shown in FIG. 1, the cylinder head 12 is coupled to the top surface of the cylinder block 11 of the engine, and the head cover 13 is coupled to the top surface of the cylinder head 12. An intake port 14 is formed on the cylinder head 12, and the intake valve 17 for opening and closing the valve hole 16 opened to the combustion chamber 15 can be slidable on a valve guide 19 provided on the cylinder head 12. Guided by

As shown in FIGS. 1 to 4, the electromagnetic valve device 20 for opening and closing the pair of intake valves 17 with the same timing and the same lift amount includes a pair of first electromagnets 21 and a pair of second electromagnets 22. And a pair of amateurs 23 and a pair of biasing rods 24.

The first electromagnet 21 has a core 25 formed by laminating a large number of steel plates, a pair of cones 26 wound around four coil grooves 25 a formed in the core 25, and an inner block overlapped on the inner end of the core 25. The inner block member 27, the core 25 and the outer block member 28 are integrally fastened by four bolts 29, and a member 27 and an outer block member 28 superimposed on the outer end of the core 25. The three mounting arms 27a of the inner block member 27 are fastened to the mounting portion 12a of the cylinder head 12 with bolts 30 respectively, and the three mounting arms 28a of the outer block member 28 are each bolted 31 The first electromagnet 21 is fixed to the cylinder head 12 by fastening it to the mounting portion 12 b of the cylinder head 12 at this time.

The second electromagnet 22 has a core 32 in which a large number of steel plates are stacked, a pair of core members 33 wound in four coil grooves 32 a formed in the core 32, and an inner block overlapped on the inner end of the core 32. The inner block member 34, the core 32 and the outer block member 35 are integrally fastened by four bolts 36, and a member 34 and an outer block member 35 superimposed on the outer end of the core 32. The inner block member 34 is provided with two hinge arms 34a and two link arms 34b, and the outer block member 35 is provided with three spring seat support arms 35a.

The armature 23 is a plate-like member having two hinge arms 23a at its inner end and two rollers 37 rotatably supported at its outer end. The fixed shaft 38 is press-fitted to the three mounting arms 27a of the inner block member 27 of the first electromagnet 21. The two hinge arms 23a of the armature 23 and the inner block of the second electromagnet 22 are fitted around the fixed shaft 38. The two hinge arms 34a of the member 34 are rotatably fitted relative to each other. Thus, the armature 23 and the second electromagnet 22 are pivoted so as to be able to swing independently of each other about the fixed axis 38. The fixed shaft 38 means that the position does not move with respect to the cylinder head 11, and may rotate at the same position.

Two link arms 39 a provided on a control shaft 39 rotatably supported by the cylinder head 12 and two link arms 34 b of the inner block member 34 of the second electromagnet 22 are both ends of the control link 40. Each is pivoted by pins 41 and 42 respectively. Therefore, when the control shaft 39 is reciprocated by the actuator 43 such as an electric motor, the second electromagnet 22 swings around the fixed shaft 38 via the control link 40.

A cylindrical spring seat 44 is slidably fitted in a guide recess 12 c formed coaxially with the intake valve 17 in the cylinder head 12, and a pin 45 provided on the spring seat 44 is a second electromagnet 22. It engages with a long hole 35b provided at the tip of the spring seat support arm 35a of the outer block member 35. Therefore, when the second electromagnet 22 swings, the spring sheet 44 moves up and down along the guide recess 12c following it. The reason why the pin 45 provided on the spring seat support arm 35a is engaged with the long hole 35b with which the pin 45 provided is engaged is that the spring seat support arm 35a of the outer block member 35 swings around the fixed shaft 38. This is because the seat 44 moves linearly along the guide recess 12c.

A first valve spring 47 is compressed between a spring seat 46 provided on the upper end of the stem 18 of the intake valve 17 and the spring seat 44. The first valve spring 47 biases the intake valve 17 in the valve closing direction (upward), and the upper end of the stem 18 of the intake valve 17 abuts against the roller 37 of the armature 23 by the biasing force.

A biasing rod 24 coaxially disposed with the stem 18 of the intake valve 17 is slidably supported by a rod guide 48 provided on the support portion 13 a of the head cover 13. The second valve spring 51 is compressed between the spring seat 49 integrally formed on the rod guide 48 and the spring seat 50 provided at the lower part of the biasing rod 24, and the second valve spring 51 The lower end of the biasing rod 24 abuts against the roller 37 of the armature 23. A hydraulic shock absorbing mechanism 52 is provided at the top of the rod guide 48 to cushion an impact when the intake valve 17 is seated.

Next, the operation of the first embodiment of the present invention having the above configuration will be described.

When the second electromagnet 22 is rocked around the fixed shaft 38 by the actuator 43 via the control shaft 39 and the control link 40, the lower surface of the first magnet 21 fixed to the cylinder head 12 is rocked. The angle formed with the top surface of the second electromagnet 22 changes. FIG. 5 (A) corresponds to the case where the angle α is small and the intake valve 17 is driven with a low lift amount, and FIG. 5 (B) corresponds to the state where the angle / 3 is large. It corresponds to the case of driving with high lift amount.

When the first and second electromagnets 21 and 22 are not excited, the armature 23 is always the first and second electromagnets regardless of whether the second electromagnet 22 is in the low lift state or in the high lift state. It stops at a generally neutral position in the bowl-like space formed between 21 and 22. The reason is as follows

In the low lift state, the armature 23 is pushed up by the stem 18 of the intake valve 17 biased upward by the first valve spring 47, and biased downward by the second valve spring 51. Depressed by 24, the push-up force and the push-up force stop at a balanced neutral position. In this neutral position, the occurrence of the first and second valve springs 47 and 51 so that the armature 23 stops approximately at the center between the first and second electromagnetic stones 21 and 22. Force is adjusted.

When the second electromagnet 22 is lowered to the high lift state from this state, the spring seat 44 supporting the lower end of the first valve spring 47 is lowered together with the second electromagnet 22 so that the first and second valve springs 47 , 51 extend equally. As a result, the armature 23 swings downward from the low lift state, and stops at a substantially central neutral position in the space between the first and second electromagnets 21 and 22 even in the high lift state.

Assuming that the lower end of the first valve spring 47 is supported immovably by the cylinder head 12, the armature 23 is in the low lift state even if the second electromagnet 22 swings downward in the high lift state. There is a problem that the clearance between the armature 23 and the second electromagnet 22 becomes large with respect to the balance between the armature 23 and the first electromagnet 21 without moving from there.

As described above, if the armature 23 does not stop near the center between the first and second electromagnets 21 and 22 when the engine is stopped, the second electromagnet 22 is excited at the moment the engine is started and the armature 23 is attracted. In the case of a cylinder with such timing, a large adsorptive force is required for the second electromagnet 22 where the distance to the armature 23 becomes large, and problems such as an increase in the size of the second electromagnet 22 and an increase in power consumption occur.

On the other hand, in the present embodiment, since the armature 23 is stopped approximately at the center between the first and second electromagnets 21 and 22 when the engine is stopped, the first and second electromagnets are started when the engine is started. Even in the case of being excited from either of 21 and 22, the problem described above is solved by eliminating the need for a particularly large adsorption force.

Further, since the first valve spring 47 and the spring seat 44 are disposed on the outer periphery of the stem 18 of the intake valve 17, the spring seat 44 can be made compact only by enabling the second electromagnet 22 to have the pin 45 and the long hole. Since the connection is made via 35b, the spring seat 44 can be moved according to the swing of the second electromagnet 22, and the armature 23 can be reliably urged to the neutral position regardless of the swing position of the second electromagnet 22. it can.

Thus, when the first electromagnet 21 is excited, the first adsorption surface 23b of the armature 23 is attracted to the lower surface of the first electromagnet 21, whereby the armature 23 pivots upward around the fixed shaft 38. While pressing the second valve spring 51, the urging rod 24 is pushed up by the roller 37. this At the same time, the intake valve 17 whose stem 18 is pushed up by the spring force of the first valve spring 47 is seated on the valve hole 16 to close. With the intake valve 17 closed, the dimensional relationship of each part is set such that the first adsorption surface 23b of the armature 23 is in close contact with the lower surface of the first electromagnet 21. The impact at the moment when the intake valve 17 is seated in the valve hole 16 is buffered by the hydraulic shock absorbing mechanism 52 which suppresses the upward movement of the upper end of the biasing rod 24.

When the first electromagnet 21 is de-energized to excite the second electromagnet 22 from the closed state of the intake valve 17, the second attraction surface 23 c of the armature 23 is attracted to the upper surface of the second electromagnet 22. Then, the armature 23 swings downward about the fixed shaft 38, and the intake valve 17 is opened by depressing the stem 18 with the force S and the roller 37 without compressing the first valve spring 47. At this time, the urging rod 24 follows the armature 23 by the spring force of the second valve spring 51 and descends. When the second suction surface 23c of the armature 23 is in close contact with the upper surface of the second electromagnet 22, the lift amount of the intake valve 17 is the maximum lift amount, and as shown in FIG. It changes arbitrarily according to the rocking position of.

Since the second electromagnet 22 and the armature 23 swing around the common fixed shaft 38, as shown in FIG.

Even in the low lift state of (A) or in the high lift state of FIG. 6 (B), the second attraction surface 23c of the armature 23 can be brought into close contact with the top surface of the second electromagnet 22. Management of the second suction surface 23c of the user 23 becomes easy. Further, since the fixed shaft 38 is provided to the first electromagnet 21 fixed to the cylinder head 11, the position of the first electromagnet 21 and the armature 23 can be eliminated only by eliminating the need to secure a place for providing the fixed shaft 38 to the cylinder head 11. The relationship is stable, and management of the lower surface of the first electromagnet 21 and the first attraction surface 23b of the armature 23 is easy.

Thus, by changing the swing position of the second electromagnet 22, the maximum lift amount of the intake valve 17 can be arbitrarily changed, and the excitation of the first and second electromagnets 21 and 22 is also possible. By changing the timing of demagnetization and demagnetization, it is possible to change the valve timing of the intake valve 17 arbitrarily. At that time, it is only necessary to change the position of the first electromagnet 21 and the second armature 22 so as to change the positions of the first electromagnet 21 and the second armature 23. Therefore, all of the first and second electromagnets 21 and 22 and the second armature 23 are moved. The electromagnetic valve device 20 can be configured in a compact size S compared to the one to be driven. Moreover, the first electromagnet 2 that regulates the closing position of the intake valve 17 2 Since 1 is fixed immovably, the intake valve 17 can be seated with high accuracy. Example 2

7 to 13 show a second embodiment of the present invention.

As shown in FIG. 7, the cylinder head 12 is coupled to the top surface of the cylinder block 11 of the engine, and the head cover 13 is coupled to the top surface of the cylinder head 12. An intake port 14 is formed on the cylinder head 12, and the intake valve 17 for opening and closing the valve hole 16 opened to the combustion chamber 15 can be slidable on a valve guide 19 provided on the cylinder head 12. Guided by

As shown in FIGS. 7 to 11, the electromagnetic valve device 20 for opening and closing the pair of intake valves 17 at the same timing and the same lift amount includes a pair of first electromagnets 21 and a pair of second electromagnets 22. And a pair of amateurs 23.

The first electromagnet 21 has a core 25 formed by laminating a large number of steel plates, a pair of cones 26 wound around four coil grooves 25 a formed in the core 25, and an inner block overlapped on the inner end of the core 25. The inner block member 27, the core 25 and the outer block member 28 are integrally fastened by four bolts 29, and a member 27 and an outer block member 28 superimposed on the outer end of the core 25. The three mounting arms 27a of the inner block member 27 are fastened to the mounting portion 12a of the cylinder head 12 with the bolts 30, respectively, and the three mounting arms 28a of the outer block member 28 are each mounted with the bolts 31 for mounting the cylinder head 12 The first electromagnet 21 is fixed to the cylinder head 12 by fastening to the portion 12 b.

The second electromagnet 22 has a core 32 in which a large number of steel plates are stacked, a pair of core members 33 wound in four coil grooves 32 a formed in the core 32, and an inner block overlapped on the inner end of the core 32. The inner block member 34, the core 32 and the outer block member 35 are integrally fastened by four bolts 36, and a member 34 and an outer block member 35 superimposed on the outer end of the core 32. The inner block member 34 is provided with four hinge arms 34a and four levers 34c extending the hinge arms 34a.

Two armatures 23 are plate-like members having a first suction surface 23b and a second suction surface 23c, and two levers 23a and two levers further extending them at the inner end. 23d and two rollers 37 are rotatably supported at the outer end. Of the first electromagnet 21 The fixed shaft 38 is press-fitted to the four mounting arms 27 a of the side block member 27, and a total of four hinge arms 23 a of the armature 23 on the outer periphery of the fixed shaft 38 and the inner block member 34 of the second electromagnet 22. The four hinge arms 34a are fitted rotatably relative to each other. Thus, the armature 23 and the second electromagnet 22 are pivoted so as to be able to independently swing about the fixed axis 38. The fixed shaft 38 means that the position does not move with respect to the cylinder head 11, and may rotate at the same position.

The two link arms 39a provided on the control shaft 39 rotatably supported by the cylinder head 12 and the outer block member 28 of the second electromagnet 22 and the force control link 40 are provided with pins 41 and 42 respectively. Be pivoted. Therefore, when the control shaft 39 is reciprocally rotated by an actuator 43 such as an electric motor, the second electromagnet 22 swings around the fixed shaft 38 via the control link 40. In this way, since the end of the second electromagnet 22 far from the fixed shaft 38 is driven by the actuator 43, not only the small output actuator 43 can be used, but the backlash of the second electromagnet 22 around the fixed shaft 38 is reduced. It can be done.

The first valve spring 47 is compressed between the upper surface of the cylinder head 12 and the spring sheet 46 provided on the upper end of the stem 18 of the intake valve 17. The first valve spring 47 biases the intake valve 17 in the closing direction (upward), and the biasing force of the first valve spring 47 causes the upper end of the stem 18 of the intake valve 17 to pass through the rush adjuster 145 for the roller 37 of the armature 23. Abuts on the lower surface. Further, a hydraulic shock absorbing mechanism 148 provided on the cylinder head 12 abuts on the upper surface of the roller 37 of the armature 23.

The proximal end of the guide rod 150 is pivotally supported via the pin 149 between the ends of a pair of levers 23 d which extend the pair of hinge arms 23 a of each armature 23, and the first end of the guide rod 150 is A spring seat 151 is formed on the body.

On the other hand, two U-shaped second spring seats 152 each have two pins 54 between two pairs of levers 34 c obtained by extending two pairs of hinge arms 34 a of the inner block member 34 of the second electromagnet 22. , 54, and two guide rods 150 are loosely penetrated through guide holes 152a formed at the centers of these second spring seats 152. Then, one end of a second valve spring 153 compressed so as to fit on the outer periphery of the guide rod 150 abuts on the first spring seat 151 and the other end abuts on the second spring seat 152. Around the outer periphery of the guide rod 150 Since the second valve spring 153 is supported, the shape of the second valve spring 153 can be stabilized and the first and second spring seats 151 and 152 can be reliably urged only by the compact structure.

A spring guide 55 is fixed to the upper surface of the inner block member 27 of the first electromagnet 21 by two bolts 56 and 56, and two spring guide holes 55 a formed on the spring guide 55 are two. The second valve springs 153, 153 are slidably fitted. When the axes of the pin 149 and the pins 54, 54 coincide with each other, the second spring sheet 152 swings around the guide rod 150 force S pin 149 and the second spring sheet 152 simultaneously, and the second valve The force S may cause the position of the spring 153 to become unstable, and the above problem may be solved by regulating the position of the second valve spring 153, 153 by the spring guide holes 55a, 55 of the spring guide 55. Saru.

Next, the operation of the second embodiment of the present invention having the above configuration will be described.

When the second electromagnet 22 is swung around the fixed shaft 38 by the actuator 43 via the control shaft 39 and the control link 40, the lower arm of the first magnet 21 fixed to the cylinder head 12 is swung. The angle formed with the top surface of the second electromagnet 22 changes. FIG. 12 (A) corresponds to the case where the angle α is small and the intake valve 17 is driven with a low lift amount, and FIG. 12 (B) corresponds to the state where the angle / 3 is large. When driving with a high lift amount.

In the low lift state, the armature 23 is pushed up by the stem 18 of the intake valve 17 biased upward by the first valve spring 47. On the other hand, the guide rod 150 whose first spring sheet 151 is pressed by one end of the second valve spring 153 whose other end is supported by the second spring seat 152 of the second electromagnet 22 is a guide rod of the second spring sheet 152. As the amount of protrusion from 152a increases, the armature 23 is biased about the fixed shaft 38 downward, ie, to depress the stem 18 of the intake valve 17. Thus, the intake valve 17 is closed. By adjusting the spring force of the first valve spring 47 biased in the valve direction and the spring force of the second valve spring 153 biased in the valve opening direction, the armature 23 is firstly adjusted. It stops in the approximately center neutral position between the 2nd electromagnets 21 and 22.

From this state, when the second electromagnet 22 is lowered to the high lift state via the control shaft 39 operated by the actuator 43 and the controller link 40, as shown in FIG. 12 (B), it is integrated with the second electromagnet 22. The lever 34d pivots clockwise around the fixed shaft 38, and the other end of the second valve spring 153 is compressed by the second spring seat 152 provided on the lever 34d. Then, the guide rod 150 is pushed up together with the first spring seat 151 that abuts one end of the second valve spring 153, and the armature 23 with the lever 23d pulled by the guide rod 150 swings downward around the fixed shaft 38. Do.

As a result, the roller 37 of the armature 23 pushes down the upper end of the stem 18 of the intake valve 17 to open the intake valve 17 while compressing the first valve spring 47. At this time, the resilient force by which the compressed first valve spring 47 pushes the intake valve 17, that is, the armature 23, balances with the spring force by which the compressed second valve spring 153 pushes the armature 23. Also in this high lift state, the armature 23 stops at a substantially central neutral position in the space between the first and second electromagnets first and second electromagnets 21 and 22.

When the engine is stopped with the second electromagnet 22 rocked downward to change the valve lift, the armature 23 is positioned between the first and second electromagnets 21 and 22. Assuming that the cylinder does not stop at a neutral position substantially in the center of the space and is in contact with the first electromagnet 21, at the moment when the engine is started, the second electromagnet 22 is excited to attract the armature 23 at the moment of starting adsorption. A large adsorptive force is required for the second electromagnet 22 which increases the distance to the armature 23, and this causes problems such as an increase in the size of the second electromagnet 22 and an increase in power consumption.

On the other hand, in the present embodiment, the armature 23 is stopped approximately at the center between the first and second electromagnets 21 and 22 when the engine is stopped, so the first and second electromagnets are started when the engine is started. Even in the case of being excited from either of 21 and 22, the problem described above is solved by eliminating the need for a particularly large adsorption force.

Thus, when the first electromagnet 21 is excited, the first adsorption surface 23b of the armature 23 is attracted to the lower surface of the first electromagnet 21, whereby the second valve spring 153 is compressed while the armature is compressed. The reference numeral 23 pivots upward around the fixed shaft 38. At the same time, the intake valve 17 whose stem 18 is pushed up by the force of the first valve spring 47 is seated in the valve hole 16 to close. Then, the shock at the moment when the intake valve 17 is seated in the valve hole 16 is buffered by the hydraulic shock absorbing mechanism 148 and the rush agitator 145 is used with the first adsorption surface 23 b of the armature 23 in close contact with the lower surface of the first electromagnet 21. The intake valve 17 is seated in the valve hole 16.

When the first electromagnet 21 is de-energized to excite the second electromagnet 22 from the closed state of the intake valve 17, the second attraction surface 23 c of the armature 23 is attracted to the upper surface of the second electromagnet 22. Then, the armature 23 swings downward around the fixed shaft 38, and while compressing the first valve spring 47, the stem 37 is pushed down by the roller 37 while the second valve spring 153 is extended. Opens. When the second adsorption surface 23c of the armature 23 is in close contact with the upper surface of the second electromagnet 22, the lift amount of the intake valve 17 is the maximum lift amount, and as shown in FIG. It changes arbitrarily depending on the movement position.

Since the second electromagnet 22 and the armature 23 swing around the common fixed axis 38, the second lift of the armature 23 is in the low lift state of FIG. 13 (A) or in the high lift state of FIG. 13 (B). 2) The suction surface 23c can be brought into close contact with the top surface of the second electromagnet 22, and management of the top surface of the second electromagnet 22 and the second suction surface 23c of the armature 23 becomes easy. Further, since the fixed shaft 38 is provided to the first electromagnet 21 fixed to the cylinder head 12, it is not necessary to secure a place where the fixed shaft 38 is provided to the cylinder head 12. The positional relationship becomes stable, and management of the lower surface of the first electromagnet 21 and the first attraction surface 23b of the armature 23 becomes easy.

As described above, the maximum lift amount of the intake valve 17 can be arbitrarily changed by changing the swing position of the second electromagnet 22, and the excitation of the first and second electromagnets 21 and 22 can be performed. By changing the timing of demagnetization and demagnetization, it is possible to change the valve timing of the intake valve 17 arbitrarily. At that time, it is only necessary to change the position of the first electromagnet 21 and the second armature 22 so as to change the positions of the first electromagnet 21 and the second armature 23. Therefore, all of the first and second electromagnets 21 and 22 and the second armature 23 are moved. The electromagnetic valve device 20 can be configured in a compact size S compared to the one to be driven. In addition, since the first electromagnet 21 that regulates the valve closing position of the intake valve 17 is immovably fixed, the intake valve 17 can be seated with high accuracy. Furthermore, conventionally, the second valve spring 153 is disposed on the extension of the first valve spring 47 on the outer periphery of the stem 18 of the intake valve 17! /, But in the present embodiment the second valve spring 153 Since it is moved to the fixed shaft 38 side, it is not necessary to secure a space for arranging the second valve spring 153 on the extension of the stem 18, and the electromagnetic valve device 20 can be configured compactly S. In addition, the lever 23d of the armature 23 and the lever 34c of the second electromagnet 22 are partially overlapped in the cylinder row direction (see FIGS. 12 and 13), so the solenoid valve device 20 can be made more compact. It can be configured.

Although the embodiments of the present invention have been described above, various design changes can be made to the present invention without departing from the scope of the present invention.

For example, in the embodiment, the force applying the present invention to the intake valve 17 can be applied to the exhaust valve.

In the embodiment, only the second electromagnet 22 of the first and second electromagnets 21 and 22 is oscillated, but both of the first and second electromagnets 21 and 22 are oscillated. Also good.

In the embodiment, the pair of armatures 23 are driven at the same timing and lift amount, but it is possible to move the armature 23 at different timings and lift amounts for each intake valve 17.

Claims

The scope of the claims

[1] One end is pivotally supported by the engine body (12) and the other end is a stem (1 of the valve (17)

8) an armature (23) in contact with the first electromagnet (21) capable of attracting the first attraction surface (23b) of the armature (23); and a second attraction surface (23c) of the armature (23) And a second electromagnet (22) capable of adsorbing

At least one electromagnet (22) of the first and second electromagnets (21, 22) is pivotally supported about a fixed shaft (38) fixed in position with respect to the engine body (12). An electromagnetic valve device of an engine characterized by

[2] The engine electromagnet according to claim 1, wherein the one electromagnet (21) causes the valve (17) to lift and defines the lift amount of the valve (17). Valve device.

[3] A spring seat (49) provided with a pair of valve springs (47, 51) for urging the armature (23) to the neutral position, and supporting one valve spring (51) is the engine main body (13 ), And the spring seat (44) supporting the other valve spring (47) moves in response to the swing of the one electromagnet (22). The solenoid valve device of the engine as described in.

[4] The other valve spring (47) and the spring seat (44) supporting the valve spring (47) are disposed on the outer periphery of the stem (18) of the valve (17), and the spring seat (44) 4. The electromagnetic valve device for an engine according to claim 3, wherein said one electromagnet is integrally connected to said one electromagnet (22) and moves.

[5] The electromagnetic valve according to any one of claims 1 to 4, wherein the armature (23) is pivotally supported via the fixed shaft (38). apparatus.

[6] The other electromagnet (21) of the first and second electromagnets (21, 22) is provided with a fixing portion (27) for fixing the fixed shaft (38). An engine solenoid valve device according to Item 5.

[7] A first valve spring (47) for urging the valve (17) in the valve closing direction, and the valve

And a second valve spring (153) for urging (17) in the valve opening direction, the second valve spring (153) attaching a lever (23d) provided on the one end side of the armature (23). Force The solenoid valve device of the engine according to claim 1, characterized in that:

[8] The one electromagnet (22) includes a lever (34c) provided at one end side pivotally supported by the fixed shaft (38), and the second valve spring is attached to the lever (23d) of the armature (23) (153) is applied with an urging force at one end side, and an urging force at the other end side of the second valve spring (153) is applied to the lever (34d) of the one electromagnet (22). The solenoid valve device of the engine according to claim 7.

9. The device according to claim 8, characterized in that at least a portion of the lever (23d) of the armature (23) and the lever (34c) of the one electromagnet (22) are overlapped in the direction of the cylinder line. The electromagnetic valve gear of the described engine.

[10] A guide rod (150) pivotally supported at one end by the lever (23d) of the armature (23) and provided with a first spring seat (151) at the other end is the one of the electromagnet (22). The second spring seat (152) provided on the lever (34c) is penetrated, and one end and the other end of the second valve spring (153) supported on the outer periphery of the guide rod (150) are respectively the first spring sheet A solenoid valve device for an engine according to claim 7 or 8, characterized in that it abuts on the (151) and the second spring sheet (152).

11. The force according to any one of claims 8 to 10, wherein the actuator (43) for swinging the one electromagnet (22) drives the other end side of the electromagnet (22). The solenoid valve device of the engine described in.