WO2008032491A1 - Dispositif de robinet électromagnétique pour un moteur - Google Patents

Dispositif de robinet électromagnétique pour un moteur Download PDF

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Publication number
WO2008032491A1
WO2008032491A1 PCT/JP2007/064503 JP2007064503W WO2008032491A1 WO 2008032491 A1 WO2008032491 A1 WO 2008032491A1 JP 2007064503 W JP2007064503 W JP 2007064503W WO 2008032491 A1 WO2008032491 A1 WO 2008032491A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
electromagnet
armature
spring
engine
Prior art date
Application number
PCT/JP2007/064503
Other languages
English (en)
Japanese (ja)
Inventor
Noriaki Fujii
Tomoya Fujimoto
Hisao Sakai
Keiko Yoshida
Original Assignee
Honda Motor Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2006247611A external-priority patent/JP5025195B2/ja
Priority claimed from JP2006334786A external-priority patent/JP4691009B2/ja
Application filed by Honda Motor Co., Ltd. filed Critical Honda Motor Co., Ltd.
Priority to US12/441,244 priority Critical patent/US20100059003A1/en
Priority to EP07791228A priority patent/EP2063076A4/fr
Publication of WO2008032491A1 publication Critical patent/WO2008032491A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/10—Connecting springs to valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/24—Safety means or accessories, not provided for in preceding sub- groups of this group
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
    • F01L2009/2105—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids comprising two or more coils
    • F01L2009/2109—The armature being articulated perpendicularly to the coils axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
    • F01L2009/2125—Shaft and armature construction
    • F01L2009/2126—Arrangements for amplifying the armature stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
    • F01L2009/2132—Biasing means
    • F01L2009/2134—Helical springs
    • F01L2009/2136—Two opposed springs for intermediate resting position of the armature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • 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.
  • 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
  • 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.
  • Patent Document 1 Japanese Patent Application Publication No. 2006-22776
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the armature is pivotally supported via the fixed shaft.
  • An electromagnetic valve system is proposed.
  • 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.
  • 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 comprising: a second valve spring, wherein the second valve spring biases a lever provided on the one end side of the armature.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the fixing portion for fixing the fixed shaft to the other of the first and second electromagnets 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.
  • 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.
  • 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.
  • the electromagnetic valve device can be miniaturized.
  • 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 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.
  • 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 is an enlarged view of an essential part of FIG. (First embodiment)
  • FIG. 3 is an exploded perspective view of the solenoid valve device. (First embodiment)
  • 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).
  • Figure 6 is an explanatory view of the operation at the time of low lift and high lift (maximum lift state). (First embodiment)
  • 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.
  • FIG. 8 is an enlarged view of an essential part of FIG. Second Embodiment
  • FIG. 9 is a perspective view of FIG. Second Embodiment
  • FIG. 10 is an exploded perspective view of the solenoid valve device. Second Embodiment
  • FIG. 11 is an exploded perspective view of a second electromagnet and its rocking drive part.
  • Figure 12 is an action explanatory view (neutral state) at low lift and high lift. (2nd embodiment)
  • Figure 13 is an explanatory view of the operation at the time of low lift and high lift (maximum lift state).
  • FIGS. 1 to 6 show a first embodiment of the present invention.
  • 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
  • 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.
  • 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.
  • FIG. 5 (A) corresponds to the case where the angle ⁇ is small and the intake valve 17 is driven with a low lift amount
  • FIG. 5 (B) corresponds to the state where the angle / 3 is large. It corresponds to the case of driving with high lift amount.
  • 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
  • the armature 23 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.
  • 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.
  • 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.
  • 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.
  • the second electromagnet 22 is excited at the moment the engine is started and the armature 23 is attracted.
  • 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.
  • 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.
  • 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.
  • the first electromagnet 21 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 12 (A) corresponds to the case where the angle ⁇ is small and the intake valve 17 is driven with a low lift amount
  • FIG. 12 (B) corresponds to the state where the angle / 3 is large.
  • 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
  • the armature 23 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.
  • 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.
  • the armature 23 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.
  • the intake valve 17 is closed.
  • the armature 23 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the timing of demagnetization and demagnetization it is possible to change the valve timing of the intake valve 17 arbitrarily.
  • the electromagnetic valve device 20 can be configured in a compact size S compared to the one to be driven.
  • the intake valve 17 can be seated with high accuracy.
  • 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.
  • 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.
  • the force applying the present invention to the intake valve 17 can be applied to the exhaust valve.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

La présente invention a trait à un dispositif de robinet électromagnétique (20) pour un moteur. Le dispositif de robinet (20) est doté d'un induit (23) dont une extrémité est supportée de manière pivotante au niveau d'une culasse par l'intermédiaire d'un arbre de fixation (38) et dont l'autre extrémité est en contact avec le corps de valve (18) d'une soupape d'admission d'air (17). La soupape d'admission (17) est ouverte et fermée en attirant une première surface d'attraction (23b) et une seconde surface d'attraction (23c) de l'induit (23) par l'intermédiaire d'un premier électroaimant (21) fixé à la culasse et par l'intermédiaire d'un second électroaimant (22) supporté de façon à pouvoir se balancer sur la culasse par l'intermédiaire de l'arbre de fixation (38). Lors de l'opération d'ouverture et de fermeture de la soupape d'admission (17), le degré de soulèvement de la soupape d'admission d'air (17) peut varier en fonction des besoins en balançant le second électroaimant (22) afin de varier l'angle entre les premier et second électroaimants (21, 22). Le balancement de l'un ou l'autre des premier et second électroaimants (21, 22) est suffisant pour cette fin et, en outre, il n'est pas nécessaire de changer la position de l'induit (23). Ceci permet d'obtenir un dispositif de robinet électromagnétique (20) compact.
PCT/JP2007/064503 2006-09-13 2007-07-24 Dispositif de robinet électromagnétique pour un moteur WO2008032491A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US12/441,244 US20100059003A1 (en) 2006-09-13 2007-07-24 Engine electromagnetic valve operating device
EP07791228A EP2063076A4 (fr) 2006-09-13 2007-07-24 Dispositif de robinet électromagnétique pour un moteur

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2006247611A JP5025195B2 (ja) 2006-09-13 2006-09-13 エンジンの電磁動弁装置
JP2006-247611 2006-09-13
JP2006-334786 2006-12-12
JP2006334786A JP4691009B2 (ja) 2006-12-12 2006-12-12 エンジンの電磁動弁装置

Publications (1)

Publication Number Publication Date
WO2008032491A1 true WO2008032491A1 (fr) 2008-03-20

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PCT/JP2007/064503 WO2008032491A1 (fr) 2006-09-13 2007-07-24 Dispositif de robinet électromagnétique pour un moteur

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US (1) US20100059003A1 (fr)
EP (1) EP2063076A4 (fr)
KR (1) KR20090055601A (fr)
TW (1) TW200827534A (fr)
WO (1) WO2008032491A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001303995A (ja) * 2000-04-26 2001-10-31 Toyota Motor Corp 内燃機関
JP2006046176A (ja) * 2004-08-04 2006-02-16 Toyota Motor Corp 電磁駆動弁
JP2007046503A (ja) * 2005-08-08 2007-02-22 Toyota Motor Corp 電磁駆動弁

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2665926B1 (fr) * 1990-08-17 1994-07-01 Renault Dispositif d'actionnement pour soupape notamment dans un moteur a combustion interne.
DE10120401A1 (de) * 2001-04-25 2002-10-31 Daimler Chrysler Ag Vorrichtung zur Betätigung eines Gaswechselventils
US20050076866A1 (en) * 2003-10-14 2005-04-14 Hopper Mark L. Electromechanical valve actuator

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001303995A (ja) * 2000-04-26 2001-10-31 Toyota Motor Corp 内燃機関
JP2006046176A (ja) * 2004-08-04 2006-02-16 Toyota Motor Corp 電磁駆動弁
JP2007046503A (ja) * 2005-08-08 2007-02-22 Toyota Motor Corp 電磁駆動弁

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2063076A4 *

Also Published As

Publication number Publication date
EP2063076A8 (fr) 2009-09-30
TW200827534A (en) 2008-07-01
EP2063076A1 (fr) 2009-05-27
EP2063076A4 (fr) 2010-05-05
US20100059003A1 (en) 2010-03-11
KR20090055601A (ko) 2009-06-02

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