JP6922592B2 - Fuel injection device - Google Patents

Description

The present invention relates to a fuel injection device.

Conventionally, there is known a fuel injection device that opens a injection hole by the operation of a needle valve and injects high-pressure fuel into a combustion chamber of an internal combustion engine.

For example, in Patent Document 1, a fuel injection valve that changes the pressures of the first pressure chamber and the second pressure chamber to gradually lift the first piston and the second piston by the stepwise lift operation of one valve member. Is disclosed. The first piston and the second piston cooperate with the valve member, and the injection rate can be switched and controlled by controlling the lift of the valve member stepwise.

Japanese Unexamined Patent Publication No. 2001-227428

The configuration of Patent Document 1 has the following problems because the intermediate lift amount is determined by the balance between the suction force of the solenoid valve and the spring force of the stopper depending on the magnitude of the drive current.
(1) Since the intermediate lift state becomes unstable (in other words, the lift vibrates), the valve closing timing tends to vary due to the amplitude, period, and phase difference of the vibration.
(2) The lift amount tends to vary due to the variation in the solenoid suction force caused by the variation in the current.
As a result, the variation in the injection rate increases due to the variation in the flow rate of the fuel flowing out of the pressure control chamber.

The present invention was created in view of these points, and an object of the present invention is to reduce the variation in the injection rate in a fuel injection device that changes the injection rate by controlling the drive of the needle valve by the fuel pressure in the pressure control chamber. The purpose is to provide a fuel injection device that reduces fuel injection.

The present invention is a fuel injection device capable of changing the injection rate by driving control of the needle valve (21) by the fuel pressure of the pressure control chamber (31). This fuel injection device includes a housing (10), a first valve (60), a second valve (70, 79), a first valve urging member (66), and a second valve urging member (76). , One or more solenoids (81, 82, 83) and one or more permanent magnets (84, 85, 86, 87).
The housing is formed with a first fuel outflow path (47) communicating with the pressure control chamber and a second fuel outflow path (48) arranged at a position different from the first fuel outflow path and communicating with the pressure control chamber. There is.

The first valve is made of a magnetic material, is housed in a housing, has a flange portion (63) on the proximal end side, and opens and closes the first fuel outflow path.
The second valve is made of a magnetic material, is housed in the housing coaxially with the first valve, has a flange portion (73) on the proximal end side, and opens and closes the second fuel outflow path.
The first valve urging member and the second valve urging member are typically springs, urging the first valve and the second valve in the valve closing direction, respectively.
One or more solenoids are fixed to the housing, generate an electromagnetic force by energization, and can switch the energization direction in the forward direction and the reverse direction.

One or more permanent magnets are formed in an annular shape and are magnetized so that one in the axial direction has an N pole and the other in the axial direction has an S pole.
The permanent magnet is provided in the housing on the tip side of at least one flange portion of the first valve or the second valve, or is mounted on the first valve and the second valve, respectively.

By switching the energizing direction of the solenoid, this fuel injection device is based on at least the relationship between the electromagnetic force of the solenoid, the magnetic force of the permanent magnet, and the urging force of the first valve urging member and the second valve urging member. It is possible to switch at least two of "the valve open state of only the first valve", "the valve open state of only the second valve", and "the valve open state of both the first valve and the second valve". Depending on the mode of the fuel injection device, the condition further includes the relationship between the oil pressure of the fuel flowing out from the first fuel outflow path and the second fuel outflow path.

In the configuration in which the permanent magnet is provided in the housing on the fixed side, when the magnetic flux of the solenoid is generated in the opposite direction to the magnetic flux of the permanent magnet, the attractive force of the permanent magnet is canceled by the electromagnetic force of the solenoid. On the other hand, when the magnetic flux of the solenoid is generated in the same direction as the magnetic flux of the permanent magnet, the attractive force of the permanent magnet is superimposed on the electromagnetic force of the solenoid.
Therefore, for example, in a fuel injection device, when the sum of the offset suction force in the valve closing direction and the urging force of the valve urging member exceeds the oil pressure, the valve opens and the superimposed suction force in the valve closing direction is applied. The valve is configured to open when the sum of the urging force of the valve urging member and the urging force falls below the hydraulic pressure.

In a configuration in which a permanent magnet is mounted on a valve on the movable side, the direction of the magnetic flux generated by the solenoid is switched according to the direction of energization with respect to the magnetic flux of the permanent magnet, so that the permanent magnet of each valve and the facing housing are used. A suction force or a repulsive force is generated in the magnet. The opening / closing operation of each valve can be switched by using this suction force or repulsive force.

In the present invention, the fuel pressure in the pressure control chamber is controlled by opening and closing the first fuel outflow path and the second fuel outflow path by the two valves to switch the injection rate. Since the unstable valve intermediate lift state as in the fuel injection valve of Patent Document 1 is not used, the variation in the injection rate can be reduced. Further, since the injection rate is switched by a discrete operation of switching the energizing direction to the solenoid in the forward direction and the reverse direction, the influence of variation can be reduced.

An axial sectional view showing an overall configuration of a fuel injection device according to the first embodiment. FIG. 1 is a cross-sectional view in the radial direction of the II-II line of FIG. The conceptual diagram of the fuel injection apparatus according to each embodiment. The figure which shows the valve operation at the time of de-energization of the 1st embodiment. The figure which shows the valve operation at the time of the positive direction energization of 1st Embodiment. The figure which shows the valve operation at the time of reverse energization of 1st Embodiment. The figure which shows the valve operation at the time of de-energization of the 2nd embodiment. The figure which shows the valve operation at the time of the positive direction energization of 2nd Embodiment. The figure which shows the valve operation at the time of reverse energization of the 2nd embodiment. The figure which shows the valve operation at the time of de-energization of the 3rd embodiment. The figure which shows the valve operation at the time of the positive direction energization of 3rd Embodiment. The figure which shows the valve operation at the time of reverse energization of the 3rd embodiment. The figure which shows the valve operation at the time of de-energization of the 4th embodiment. The figure which shows the valve operation at the time of the positive direction energization of 4th Embodiment. The figure which shows the valve operation at the time of reverse energization of 4th Embodiment. The figure which shows the valve operation at the time of de-energization of the 5th embodiment. The figure which shows the valve operation at the time of the positive direction energization of 5th Embodiment. The figure which shows the valve operation at the time of reverse energization of 5th Embodiment. The figure which shows the valve operation at the time of de-energization of the sixth embodiment. The figure which shows the valve operation at the time of the positive direction energization of 6th Embodiment. The figure which shows the valve operation at the time of reverse energization of the sixth embodiment. The figure which shows the valve operation at the time of de-energization of the 7th embodiment. The figure which shows the valve operation at the time of the positive direction energization of 7th Embodiment. The figure which shows the valve operation at the time of reverse energization of 7th Embodiment.

Hereinafter, embodiments of the fuel injection device will be described with reference to the drawings. In the description of the plurality of embodiments, substantially the same configuration will be described with the same reference numerals. The present embodiment includes a plurality of embodiments.
The fuel injection device of the present embodiment is attached to a cylinder of an internal combustion engine such as a diesel engine, and injects high-pressure fuel stored in a common rail into the cylinder from an injection hole formed at the tip.

[Overall configuration of fuel injection system]
1 and 2 show the overall configuration of the fuel injection device 100. Note that FIG. 1 is a schematic diagram partially exaggerated or omitted in order to explain the configurations and functions referred to in the present specification. For example, in FIG. 1, the housing 10 is divided into four parts for convenience, but does not necessarily reflect the actual product configuration. For the sake of description, the housing 10 includes the nozzle housing 12, the control chamber plate 13, the orifice plate 14, and the body housing 15 in this order from the tip end side. Further, each plate of the solenoid valve portion 501 also constitutes the housing 10. Note that FIG. 1 shows the configuration of the solenoid valve portion 501 of the first embodiment as a representative.

First, an outline of the configuration of the fuel injection device 100 will be briefly described.
The nozzle housing 12 is formed with a nozzle chamber 26 in which the needle valve 21 is housed.
A pressure control chamber 31 is formed in the control chamber plate 13. The drive of the needle valve 21 is controlled by controlling the fuel pressure in the pressure control chamber 31.
A part of the first fuel outflow path 47 communicating with the pressure control chamber 31, a second fuel outflow path 48, and the like are formed in the orifice plate 14. To be precise, the first fuel outflow path 47 includes a flow path formed in the orifice plate 14 and a flow path formed in the pressure control plate 35.
The body housing 15 is provided with a solenoid valve portion 501. The solenoid valve unit 501 opens and closes the first fuel outflow path 47 and the second fuel outflow path 48 by operating the first valve 60 and the second valve 70 by energizing the solenoid 83 based on the command from the ECU 80.

The housing 10 is formed with a fuel flow path 25 that vertically traverses the body housing 15 to the nozzle housing 12 and communicates with the nozzle chamber 26. High-pressure fuel supplied from the common rail 90 flows into the fuel flow path 25. Further, the orifice plate 14 is formed with a fuel inflow path 49 branched from the fuel flow path 25. When the pressure control plate 35 moves in the opening direction, the high-pressure fuel is introduced into the pressure control chamber 31 from the fuel flow path 25 via the fuel inflow path 49.

Subsequently, the configuration of each part will be described in detail.
The nozzle housing 12 has a bottomed tubular shape, and a nozzle hole 27 is formed at the tip of the nozzle chamber 26. A plurality of injection holes 27 are formed, for example, at predetermined intervals in the circumferential direction. The opening area of the injection hole 27 is a factor that determines the fuel injection rate. Around the injection hole 27 of the nozzle chamber 26, a valve seat on which the tip of the needle valve 21 can be seated is formed.

The needle valve 21 is housed in the nozzle chamber 26 with the needle shaft O as the central axis, and is slidable along the inner wall of the guide 22. The needle valve 21 is constantly urged by the needle spring 23 in the direction of closing the injection hole 27.
The needle valve 21 has a tapered pressure receiving surface 211 on the tip end side and a back pressure surface 212 on the proximal end side. The pressure receiving surface 211 receives the pressure that the needle valve 21 acts in the direction of opening the injection hole 27 by the high pressure fuel flowing into the nozzle chamber 26. The back pressure surface 212 receives pressure that acts on the needle valve 21 in the direction of closing the injection hole 27 by the fuel flowing from the pressure control chamber 31 into the back pressure chamber 24 via the communication passage 32.

When the sum of the pressure in the pressure control chamber 31 and the pressure conversion value of the urging force of the needle spring 23 is larger than the pressure in the nozzle chamber 26, the needle valve 21 closes the injection hole 27.
When the pressure in the pressure control chamber 31 drops due to the operation of the solenoid valve portion 501 described later and the sum of the pressure in the pressure control chamber 31 and the pressure conversion value of the urging force of the needle spring 23 falls below the pressure in the nozzle chamber 26, the needle The valve 21 moves to the back pressure chamber 24 side and opens the injection hole 27. As a result, the fuel in the nozzle chamber 26 is injected from the injection hole 27.

At this time, the moving speed of the needle valve 21 changes depending on the degree of pressure change in the pressure control chamber 31, and as a result, the fuel injection rate is controlled. That is, if the needle valve 21 opens at a relatively high speed, the injection rate increases, and if the needle valve 21 opens at a relatively low speed, the injection rate decreases. Therefore, on the premise that the pressure of the supplied high-pressure fuel is the same, variable control of the injection rate is realized by changing the pressure change in the pressure control chamber 31 to two levels or more.

The control chamber plate 13 is formed with a pressure control chamber 31 that opens to the orifice plate 14 side, and a communication passage 32 that connects the bottom of the pressure control chamber 31 and the back pressure chamber 24.
The pressure control chamber 31 houses a pressure control plate 35 having a first out orifice 36 penetrating in the axial direction. The flow path diameter of the first out orifice 36, which forms a part of the first fuel outflow path 47, is narrowed near the center of the pressure control plate 35, and the flow rate through which the first out orifice 36 passes is controlled. Here, the end surface of the pressure control plate 35 on the orifice plate 14 side is referred to as an upper end surface, and the end surface on the bottom side of the pressure control chamber 31 is referred to as a lower end surface. One end of the control plate spring 37 comes into contact with the lower end surface. Further, the direction in which the upper end surface of the pressure control plate 35 is close to the orifice plate 14 is referred to as a closing direction, and the direction in which the upper end surface of the pressure control plate 35 is separated from the orifice plate 14 is referred to as an opening direction.

In a state where the upper end surface of the pressure control plate 35 is in contact with the orifice plate 14, the area indicated by the satin pattern straddling the orifice plate 14 and the pressure control plate 35 communicates with the first out orifice 36 and is in the middle of the first fuel outflow path 47. An intermediate chamber 475 that constitutes the portion is formed. Further, the end of the orifice plate 14 on the opposite side of the first fuel outflow path 47 from the pressure control chamber 31 forms a sub-out orifice 41 having a narrowed diameter. The flow rate of the sub-out orifice 41 is set to exceed the flow rate of the first out orifice 36.
Further, the orifice plate 14 is formed with a second fuel outflow path 48 communicating with the pressure control chamber 31. As shown in FIG. 2, the second fuel outflow path 48 is described by a broken line because it is formed in a direction orthogonal to the cross section of FIG. The end of the second fuel outflow path 48 opposite to the pressure control chamber 31 forms a second out orifice 42 with a reduced diameter.
A fuel inflow path 49 is formed in the orifice plate 14, and an end portion of the fuel inflow path 49 on the pressure control chamber 31 side forms an in-orifice 490 with a narrowed diameter.

When the fuel injection device 100 is stationary, the pressures of the fuel inflow path 49, the pressure control chamber 31, and the intermediate chamber 475 are the same.
When the needle valve 21 is closed, the pressure in the fuel inflow path 49, which is equivalent to the common rail pressure, is higher than the pressure in the pressure control chamber 31, and the pressure in the pressure control chamber 31 is higher than the pressure in the intermediate chamber 475. At this time, the sum of the force acting on the lower end surface of the pressure control plate 35 and the urging force of the control plate spring 37 exceeds the force acting on the upper end surface of the pressure control plate 35. Therefore, the upper end surface of the pressure control plate 35 comes into contact with the orifice plate 14, and the state in which the fuel inflow path 49 is closed is maintained.

When the needle valve 21 is opened, that is, during fuel injection, the pressure in the fuel inflow path 49, which is equivalent to the common rail pressure, becomes higher than the pressure in the pressure control chamber 31. Then, the force due to the fuel pressure flowing in from the fuel inflow path 49 becomes large, and the pressure difference between the pressure control chamber 31 and the intermediate chamber 475 disappears. At this time, the force acting on the upper end surface of the pressure control plate 35 exceeds the sum of the force acting on the lower end surface of the pressure control plate 35 and the urging force of the control plate spring 37. Therefore, the pressure control plate 35 moves to the bottom side of the pressure control chamber 31.

The sub-out orifice 41 and the second out orifice 42 are opened on the solenoid valve portion 501 side of the orifice plate 14, and are opened and closed by the operation of the valves 60 and 70 of the solenoid valve portion 501. In FIG. 2, the outlines of the valves 60 and 70 in front of the cross-sectional view direction are described as alternate long and short dash lines as virtual lines.
When the first valve 60 is opened, the sub-out orifice 41 communicates with the low pressure chamber flow path 45 recessed in the end surface of the orifice plate 14, and fuel flows out from the sub-out orifice 41. Similarly, when the second valve 70 is opened, the second out orifice 42 communicates with the low pressure chamber flow path 45, and fuel flows out from the second out orifice 42.

The fuel flowing out from the sub-out orifice 41 or the second out orifice 42 is introduced into the low pressure chamber 58 of the body housing 15 via the low pressure chamber flow path 45. Further, the fuel in the low pressure chamber 58 is discharged to the outside via a discharge flow path (not shown).
In the present embodiment, each orifice is such that the fuel flow rate flowing out from the sub-out orifice 41 of the first fuel outflow path 47 and the fuel flow rate flowing out from the second out orifice 42 of the second fuel outflow path 48 are different. The opening area and length of are set.

The solenoid valve portion 501 includes a first valve 60 that opens and closes the first fuel outflow path 47, a second valve 70 that opens and closes the second fuel outflow path 48, and springs 66 and 76 that drive the valves 60 and 70, and a solenoid 83. , Permanent magnet 84 and the like. Common to the solenoid valve portions of each embodiment, the first valve 60 and the second valve 70 are coaxially provided on the central axis V. In this embodiment, the central axis V is offset from the needle axis O.
Here, the terms "first valve 60" and "second valve 70" mean a "valve body" driven by the urging force of the springs 66 and 76 and the attractive force of the solenoid 83 or the permanent magnet 84. Further, the first spring 66 corresponds to the "first valve urging member", and the second spring 76 corresponds to the "second valve urging member".

In the present embodiment, the direction of energization of the solenoid 83 is switched between the forward direction and the reverse direction based on the command from the ECU 80. Therefore, at least three operation modes of non-energization, forward energization, and reverse energization are executed.
Further, regarding the arrangement of the permanent magnet 84, for example, in the solenoid valve portion 501, since the permanent magnet 84 is provided on the valve tip side of the flange portion 63 of the first valve 60, space can be efficiently used. can.
The detailed configuration and operation of such a solenoid valve portion 501 will be described in detail later.

As described above, in the present embodiment, the outflow flow rate from the pressure control chamber 31 is different between when the first fuel outflow path 47 is opened and when the second fuel outflow path 48 is opened, and the fuel outflow path 47 is opened. , 48 is set so that the injection rate can be changed by selecting.
FIG. 3 shows a conceptual diagram of the present embodiment based on the above configuration. FIG. 3 shows the flow of fuel centered on the inflow and outflow of fuel into the pressure control chamber 31 and the operation of the needle valve 21. The communication passage 32 and the back pressure chamber 24 in FIG. 1 are interpreted to be included in the pressure control chamber 31 in FIG.

The high-pressure fuel flows into the fuel flow path 25 from the in-valve 91, which is a hydraulically driven valve on the common rail 90 side, and flows into the pressure control chamber 31 through the in-orifice 490 of the fuel inflow path 49 branched from the fuel flow path 25.
The fuel in the pressure control chamber 31 flows out to the low pressure chamber 58 through two paths, a first fuel outflow path 47 having a first out orifice 36 and a second fuel outflow path 48 having a second out orifice 42. do. The first fuel outflow path 47 is opened and closed by the first valve 60, and the second fuel outflow path 48 is opened and closed by the second valve 70. The illustration of the sub-out orifice 41 is omitted.

For example, when the first valve 60 is opened, the needle valve 21 is lifted in the valve opening direction at a low speed as shown by the white block arrow. On the other hand, when both the first valve 60 and the second valve 70 are opened, the needle valve 21 is lifted in the valve opening direction at high speed as shown by the diagonal block arrow.
As described above, in the present embodiment, the back pressure of the needle valve 21 is adjusted and the lift speed is switched by switching the operation of the first valve 60 and the second valve 70. As a result, it is possible to switch the injection rate of two levels or more.

As described above, the fuel injection device 100 of the present embodiment operates the open / closed state of the first fuel outflow path 47 and the second fuel outflow path 48 by the two valves 60 and 70 to control the fuel pressure in the pressure control chamber 31. By controlling, variable control of the injection amount is realized.
In particular, in the present embodiment, since the unstable valve intermediate lift state as in Patent Document 1 is not used, the variation in the injection rate can be reduced. Further, since the injection rate is switched by a discrete operation of switching the energizing direction to the solenoid in the forward direction and the reverse direction, the influence of variation can be reduced.

Next, with reference to FIGS. 4 to 24, the configurations and operations of the solenoid valve portions 501 to 507 of the first to seventh embodiments will be described in order. The code of the solenoid valve portion is the number of the embodiment in the third digit following "50". In each figure, the magnetic flux and the magnetic force are mainly shown on the left side of the central axis V, and the reference numerals are mainly shown on the right side of the central axis V.
First, the viewpoint of classification of each embodiment and the matters common to the whole will be described.

[A] Valve Arrangement Common to all embodiments, the first valve 60 and the second valves 70 and 79 are arranged coaxially on the central axis V. However, in the first to fourth embodiments, the second valve 70 is formed in a concentric cylindrical shape located on the radial outer side of the shaft portion 61 of the first valve 60. The first valve 60 on the inner side in the radial direction and the second valve 70 on the outer side in the radial direction operate in the same direction to open and close the sub-out orifice 41 and the second out orifice 42 formed in substantially the same plane. This valve arrangement is called "parallel type".

On the other hand, in the fifth to seventh embodiments, the first valve 60 and the second valve 79 are so-called "back-to-back" so that the proximal end side (that is, the anti-tip side) faces each other and the distal end side faces in opposite directions. Is placed in the state of. The first valve 60 and the second valve 79 operate in opposite directions to open and close the sub-out orifice 41 and the second out orifice 42 arranged in the 180 ° direction. This valve arrangement is called "opposed type".

[B] Installation of permanent magnets on the fixed side or movable side Each permanent magnet of the present embodiment is formed in an annular shape around the central axis V so that one in the axial direction has an N pole and the other in the axial direction has an S pole. Is magnetized in. It should be noted that a plurality of divided magnets may be arranged in a plurality in the circumferential direction to form one annular permanent magnet. Also in that configuration, a group of divided magnets arranged in a ring shape is defined as one permanent magnet.
The solenoid may be practically difficult to install on the movable side due to wiring reasons, whereas the permanent magnet may be installed on the fixed side or mounted on the valve on the movable side. The permanent magnets 84 and 85 of the first, second and fifth embodiments are installed on the fixed side. That is, it is fixed to any of the plates of the solenoid valve portions 501, 502, and 505 that are a part of the housing. On the other hand, the permanent magnets 86 and 87 of the third, fourth, sixth and seventh embodiments are mounted on the first valve 60 and the second valves 70 and 79 on the movable side, respectively.

The permanent magnets 84 and 85 installed on the fixed side are provided on the valve tip side with respect to the flange portions 63 and 73 of the corresponding valves 60 and 70. When a permanent magnet is provided on the valve base end side of the flange portions 63 and 73, an extra axial space is required, but this configuration makes it possible to efficiently use the space. On the other hand, even in a configuration in which the permanent magnets 86 and 87 are mounted on the valves 60 and 79 on the movable side, the space can be efficiently used.

Further, as a self-evident premise, it is assumed that the permanent magnet is arranged at a position where the range in which the magnetic flux of the permanent magnet is generated and the range in which the magnetic flux of the solenoid is generated when energized overlap. Preferably, the permanent magnets are arranged so that the point where the magnetic flux density is maximized when the solenoid is energized exists in the overlap region.
By assuming this arrangement, it is possible to control the driving force acting on the first valve 60 and the second valves 70 and 79 by utilizing the relationship between the magnetic flux when the solenoid is energized and the magnetic flux of the permanent magnet. .. The solenoid valve portions 501 to 507 of the present embodiment generate valve driving force in two or more stages by switching the energizing direction of the solenoid, and switch the opening and closing of the first valve 60 and the second valves 70 and 79. Then, the variable control of the injection rate is realized.

[C] Number of solenoids and permanent magnets In the embodiment in which one or two permanent magnets 84 and 85 are installed on the fixed side, the magnetic flux generated when one solenoid 83 is energized is superimposed or offset by the magnetic flux of the permanent magnets. do.
In the embodiment in which the two permanent magnets 86 and 87 are mounted on the movable side, the magnetic flux generated when the one solenoid 83 or the two solenoids 81 and 82 are energized is determined by the relationship between the magnetic fluxes of the permanent magnets 86 and 87. A suction force or a repulsive force is generated.

The solenoid valve portions 501 to 507 of each embodiment switch the energizing direction of the solenoid between the forward direction and the reverse direction based on the command from the ECU 80 to open and close the first valve 60 and the second valves 70 and 79. Switch.
Here, the terms "forward" and "reverse" merely indicate that they are opposite to each other, and do not mean an absolute direction. However, in each of the following embodiments, for convenience, at least the energizing direction in which the first valve 60 opens is defined as a forward direction, and at least the energizing direction in which the second valves 70 and 79 open is described as a reverse direction. That is, it is assumed that the winding direction of the solenoid and the directions of the positive electrode and the negative electrode of the power supply are set so that such an action occurs. In the configuration in which the magnetic poles of the permanent magnets are arranged in reverse with respect to the following embodiment, the energization direction may be appropriately changed so that the magnetic flux generated by the solenoid exerts the same action.

Hereinafter, the operation of each embodiment will be described with reference to the three figures of "when not energized", "when energized in the forward direction", and "when energized in the reverse direction".
In the figure, the urging force of the first spring 66 is referred to as Fsp1, and the urging force of the second spring 76 is referred to as Fsp2. Further, the oil pressure of the fuel flowing out from the sub-out orifice 41 and the second out orifice 42 and acting on the seat surface at the tips of the valves 60 and 70 is referred to as Ff. The hydraulic pressure of the fuel that passes through the first out orifice 36 of the pressure control plate 35 and flows into the sub-out orifice 41 and the hydraulic pressure of the fuel that directly flows into the second out orifice 42 from the pressure control chamber 31 are strictly different. Is not the same, but the distinction is omitted here.

Further, the symbols of the magnetic flux generated by the permanent magnets 84 and 85 on the fixed side are φm1 and φm2. The symbol of the magnetic flux generated by the positive energization of the solenoid 83 is φep, and the symbol of the magnetic flux generated by the negative energization is φen. The magnetic flux of the solenoid 83 is indicated by a alternate long and short dash line. The magnetic fluxes of the permanent magnets 84 and 85 are shown by a solid line when they are not energized or when the magnetic flux of the solenoid 83 is superimposed, and are shown by a broken line when they are canceled by the magnetic flux of the solenoid 83.
Further, regarding the driving force acting on the first valve 60 or the second valves 70 and 79, the symbols of the attractive force of the permanent magnets 84 and 85 are Fm1 and Fm2, and the electromagnetic attractive force generated by the positive and negative energization of the solenoid 83. The symbols of are Fep and Fen.

Further, when the first and second embodiments are energized, it is assumed that the hydraulic pressure Ff of the fuel flowing out from the sub-out orifice 41 and the second out orifice 42 is acting.
In the non-energized state of the first and second embodiments, as a general rule, the hydraulic pressure Ff is not acting or the hydraulic pressure Ff is relatively small, and the first valve 60 and the second valve 70 are closed. It is assumed that you are speaking.

In addition, in the solenoid valve portions 501 to 507, in order to limit the range in which the magnetic attraction force is transmitted to a necessary part, a part of the plate is made of a non-magnetic material, which is a well-known magnetic cutoff in the field of solenoid valves. The technique may be adopted as appropriate.
In each embodiment, a plate assumed to be formed of a non-magnetic material is indicated by dashed line hatching. However, this configuration is only an example, and other means may be used to control the desired magnetic field distribution.

(First Embodiment)
First, with reference to FIG. 4 of the first embodiment, a configuration common to the solenoid valve portions of the parallel type valve arrangement will be described. The solenoid valve portion 501 is divided into three parts, a lower plate 51, an upper plate 52, and a cover plate 53, in this order from the orifice plate 14 side. As with the illustration of the housing 10 in FIG. 1, this illustration is for convenience of explanation.
Hereinafter, according to the direction shown in the drawing, the orifice plate 14 side is referred to as “lower” and the cover plate 53 side is referred to as “upper”. The end surface of the upper plate 52 on the lower plate 51 side is referred to as a lower end surface 524, and the end surface of the lower plate 51 on the orifice plate 14 side is referred to as a lower end surface 514. Further, the end surface of the orifice plate 14 on the lower plate 54 side is referred to as an end surface 141.

The sub-out orifice 41 is formed on the central axis V of the orifice plate 14 and opens to the end surface of the orifice plate 14.
The second out orifice 42 is formed at a position offset from the central axis V of the orifice plate 14 and opens at the end surface of the orifice plate 14.

The first valve 60 is made of a magnetic material and has a shaft portion 61 and a flange portion 63.
The shaft portion 61 penetrates the upper plate 52 and the lower plate 51 on the central axis V.
The flange portion 63 is housed in the recess of the upper plate 52, and is urged by the first spring 66 from the cover plate 53 side toward the bottom surface 523 of the recess. When the seat surface 65 at the tip of the shaft portion 61 comes into contact with the end surface 141 of the orifice plate 14, the sub-out orifice 41 is closed.

The second valve 70 is made of a magnetic material and has a main body cylinder portion 72 and a flange portion 73.
The main body cylinder portion 72 is housed in a hole formed on the central axis V of the lower plate 51 and slides on the inner wall. The shaft portion 61 of the first valve 60 is inserted into the sliding hole 726 formed in the main body cylinder portion 72. That is, the main body tubular portion 72 of the second valve 70 is formed in a tubular shape located on the radial outer side of the shaft portion 61 of the first valve 60.
The flange portion 63 is housed in the recess of the lower plate 51 and is urged by the second spring 76 from the upper plate 52 side toward the recess bottom surface 513 of the lower plate 51. When the seat surface 75 at the lower end of the main body cylinder portion 72 comes into contact with the end surface 141 of the orifice plate 14, the second out orifice 42 is closed.
The above is the basic configuration of the parallel type valve arrangement common to the first to fourth embodiments.

Subsequently, FIGS. 4 to 6 will be referred to with respect to the first embodiment.
In the solenoid valve portion 501 of the first embodiment, one permanent magnet 84 is provided directly below the recessed bottom surface 523 of the upper plate 52 on the fixed side, that is, on the valve tip side of the flange portion 63 of the first valve 60. ing. In the example of the figure, the permanent magnet 84 has an S pole on the bottom surface 523 side of the recess and an N pole on the 524 side of the lower end surface.
One solenoid 83 is provided on the upper plate 52.
The lower plate 51 and the cover plate 53 are made of, for example, a non-magnetic material.

When not energized as shown in FIG. 4, the first valve 60 is closed by the urging force Fsp1 of the first spring 66 and the attractive force of the permanent magnet 84. The second valve 70 is closed by the urging force Fsp2 of the second spring 76.

When energized in the forward direction shown in FIG. 5, a magnetic field is generated in which the flange portion 63 side of the first valve 60 is the north pole and the second valve 70 side is the south pole.
Since the magnetic flux φep of the solenoid 83 is opposite to the magnetic flux φm1 of the permanent magnet 84, the attractive force Fm1 of the permanent magnet 84 is canceled by the electromagnetic force Fep of the solenoid 83. Then, as in the equation (1), when the sum of the offset suction force (Fm1-Fep) and the urging force Fsp1 of the first spring 66 falls below the hydraulic pressure Ff, the first valve 60 opens.
(Fm1-Fep) + Fsp1 <Ff ... (1)
The second valve 70 opens when the force in the valve closing direction including at least the urging force Fsp2 of the second spring 76 falls below the hydraulic pressure Ff.

When energized in the reverse direction shown in FIG. 6, a magnetic field is generated in which the flange portion 63 side of the first valve 60 has an S pole and the second valve 70 side has an N pole.
Since the magnetic flux φen of the solenoid 83 has the same direction as the magnetic flux φm1 of the permanent magnet 84, the attractive force Fm1 of the permanent magnet 84 is superimposed by the electromagnetic force Fen of the solenoid 83. Then, as in the equation (2), when the sum of the superimposed suction force (Fm1 + Fen) and the urging force Fsp1 of the first spring 66 exceeds the hydraulic pressure Ff, the first valve 60 is closed.
(Fm1 + Fen) + Fsp1> Ff ... (2)
The second valve 70 opens when the force in the valve closing direction including at least the urging force Fsp2 of the second spring 76 falls below the hydraulic pressure Ff.

As described above, in the first embodiment, the opening / closing of the first valve 60 is switched by superimposing or canceling the electromagnetic force of the solenoid 83 with the attractive force Fm1 of the permanent magnet 84 by switching the energizing direction of the solenoid 83. .. On the other hand, the second valve 70 opens in any energizing direction. Therefore, the valve open state of both the first valve 60 and the second valve 70 and the valve open state of only the second valve 70 can be switched.

(Second Embodiment)
Refer to FIGS. 7 to 9 for the second embodiment.
In the solenoid valve portion 502 of the second embodiment, in addition to the permanent magnet 84 similar to that of the first embodiment, another permanent magnet 85 is directly below the concave bottom surface 513 of the lower plate 51 on the fixed side, that is, the second. It is provided on the valve tip side with respect to the flange portion 73 of the valve 70. In the example of the figure, the permanent magnet 85 has an N pole on the bottom surface 513 side of the recess and an S pole on the bottom surface 514 side.
One solenoid 83 is provided on the upper plate 52 as in the first embodiment.
The cover plate 53 is made of, for example, a non-magnetic material.

When not energized as shown in FIG. 7, the first valve 60 is closed by the urging force Fsp1 of the first spring 66 and the attractive force Fm1 of the first permanent magnet 84. The second valve 70 is closed by the urging force Fsp2 of the second spring 76 and the attractive force Fm2 of the second permanent magnet 85.

When energized in the forward direction shown in FIG. 8, a magnetic field is formed in which the bottom surface 523 side of the recess of the upper plate 52 is the north pole and the lower end surface 524 side of the upper plate 52 is the south pole.
The first valve 60 is opened by the same canceling action as in the first embodiment.
On the other hand, since the magnetic flux φep of the solenoid 83 is in the same direction as the magnetic flux φm2 of the permanent magnet 85, the attractive force Fm2 of the permanent magnet 85 is superimposed by the electromagnetic force Fep of the solenoid 83. Then, as in the equation (3), when the sum of the superimposed suction force (Fm2 + Fep) and the urging force Fsp2 of the second spring 76 exceeds the hydraulic pressure Ff, the second valve 70 is closed.
(Fm2 + Fep) + Fsp2> Ff ... (3)

When energized in the reverse direction shown in FIG. 9, a magnetic field is formed in which the lower surface 523 side of the recess of the upper plate 52 is the south pole and the lower end surface 524 side of the upper plate 52 is the north pole.
The first valve 60 is closed by the same overlapping action as in the first embodiment.
On the other hand, since the magnetic flux φen of the solenoid 83 is in the opposite direction to the magnetic flux φm2 of the permanent magnet 85, the attractive force Fm2 of the permanent magnet 85 is canceled by the electromagnetic force Fen of the solenoid 83. Then, as in the equation (4), when the sum of the offset suction force (Fm2-Fen) and the urging force Fsp2 of the second spring 76 falls below the hydraulic pressure Ff, the second valve 70 opens.
(Fm2-Fen) + Fsp2 <Ff ... (4)

As described above, in the second embodiment, the electromagnetic force of the solenoid 83 is superimposed or canceled on the attractive forces Fm1 and Fm2 of the permanent magnets 84 and 85 by switching the energizing direction of the solenoid 83, so that the first valve 60 And the opening and closing of the second valve 70 is switched. Therefore, the valve open state of only the first valve 60 and the valve open state of only the second valve 70 can be switched.

(Third Embodiment)
Refer to FIGS. 10 to 12 for the third embodiment.
The solenoid valve portion 503 of the third embodiment is mounted on the first valve 60 and the second valve 70, respectively, on which two permanent magnets 86 and 87 are movable, and one solenoid 83 is provided. ..
The first permanent magnet 86 is mounted on the valve tip side surface of the flange portion 63 of the first valve 60, and the second permanent magnet 87 is mounted on the valve base end side surface of the flange portion 73 of the second valve 70. It is installed. In the example of the figure, the first permanent magnet 86 has an N pole on the side in contact with the flange portion 63 and an S pole on the valve tip side. The second permanent magnet 87 has an S pole on the side in contact with the flange portion 73 and an N pole on the valve base end side.

When the valve is opened, the guard surface 74 of the second valve 70 comes into contact with the lower end surface 524 of the upper plate 52 before the second permanent magnet 87, thereby preventing damage to the second permanent magnet 87.
The solenoid 83 is provided between the recessed bottom surface 523 and the lower end surface 524 of the upper plate 52.
The lower plate 51 and the cover plate 53 are made of, for example, a non-magnetic material.

In the operation explanation of the third and fourth embodiments in which the permanent magnets 86 and 87 are mounted on the movable side, the method of explanation is slightly different from that of the first and second embodiments in which the permanent magnets 84 and 85 are provided on the fixed side. change. That is, in the third and fourth embodiments, the valves 60 and 70 have the keywords "attractive force" or "repulsive force" generated between the permanent magnets 86 and 87 of the valves 60 and 70 and the opposing plates. The opening and closing operation of is described. In the figure when the power is applied, an arrow whose tips face each other represents an attractive force, and an arrow whose tips point in opposite directions represents a repulsive force. The illustration of the arrows is omitted for the attractive force of the permanent magnets 86 and 87 when they are not energized.

However, in terms of focusing on whether the direction of the magnetic flux generated by the solenoid and the direction of the magnetic flux of the permanent magnet are the same or opposite, the explanation based on the principle of superimposition or cancellation of magnetic flux is essential. There is no difference.
Further, in the third and fourth embodiments, the reference to the hydraulic pressure Ff is omitted. The force acting in the valve closing direction is basically larger than the hydraulic pressure Ff.

When not energized as shown in FIG. 10, the first valve 60 is closed by the urging force Fsp1 of the first spring 66 and the attractive force of the first permanent magnet 86. The second valve 70 is closed by the urging force Fsp2 of the second spring 76.

When energized in the forward direction shown in FIG. 11, a magnetic field is generated in which the flange portion 63 side of the first valve 60 has an S pole and the second valve 70 side has an N pole.
Since the magnetic flux φep of the solenoid 83 is opposite to the magnetic flux φm1 of the first permanent magnet 86 and the S poles face each other, the first valve 60 is opened by a repulsive force.
Further, the magnetic flux φep of the solenoid 83 is in the opposite direction to the magnetic flux φm2 of the second permanent magnet 87, and the N poles face each other, so that the second valve 70 is closed by the repulsive force.

When energized in the reverse direction shown in FIG. 12, a magnetic field is generated in which the flange portion 63 side of the first valve 60 is the north pole and the second valve 70 side is the south pole.
The magnetic flux φen of the solenoid 83 is in the same direction as the magnetic flux φm1 of the first permanent magnet 86, and the north pole of the solenoid 83 and the south pole of the first permanent magnet 86 face each other, so that the first valve 60 is closed by an attractive force. do.
Further, the magnetic flux φen of the solenoid 83 is in the same direction as the magnetic flux φm2 of the second permanent magnet 87, and the S pole of the solenoid 83 and the N pole of the second permanent magnet 87 face each other. Open the valve.
Hereinafter, in the context of "the north pole and the south pole face each other", it is assumed that the magnetic pole described first indicates the magnetic pole of the solenoid and the magnetic pole described later indicates the magnetic pole of the permanent magnet, and the description is omitted each time.

As described above, in the solenoid valve portion 503 of the third embodiment, one solenoid 83 applies a magnetic flux that is commonly superimposed or offset to the magnetic flux φm1 of the first permanent magnet 86 and the magnetic flux φm2 of the second permanent magnet 87 when energized. appear. The solenoid valve portion 503 opens one of the first valve 60 and the second valve 70 by using the attractive force or the repulsive force generated between the permanent magnets 86 and 87 and the facing upper plate 52. It operates to close the other valve.

(Fourth Embodiment)
Reference is made to FIGS. 13 to 15 for the fourth embodiment.
The solenoid valve portion 504 of the fourth embodiment is mounted on the first valve 60 and the second valve 70, which have two permanent magnets 86 and 87 on the movable side, respectively, and is provided with two solenoids 81 and 82, respectively. ing.
The first permanent magnet 86 is mounted on the valve base end side surface of the flange portion 63 of the first valve 60, and the second permanent magnet 87 is mounted on the valve tip side surface of the flange portion 73 of the second valve 70. It is installed. In the example of the figure, the first permanent magnet 86 has an S pole on the side in contact with the flange portion 63 and an N pole on the valve base end side. The second permanent magnet 87 has an N pole on the side in contact with the flange portion 73 and an S pole on the valve tip side.

The guard surface 64 of the first valve 60 prevents damage to the first permanent magnet 86 by first contacting the lower end surface 534 of the cover plate 53 with the first permanent magnet 86 when the valve is opened.
The first solenoid 81 is provided on the cover plate 53. The second solenoid 82 is provided on the valve tip side with respect to the concave bottom surface 513 of the lower plate 51.
The upper plate 52 is made of, for example, a non-magnetic material.

When the power is not supplied as shown in FIG. 13, the first valve 60 is closed by the urging force Fsp1 of the first spring 66. The second valve 70 is closed by the urging force Fsp2 of the second spring 76 and the attractive force of the second permanent magnet 87.

When energized in the forward direction shown in FIG. 14, the first solenoid 81 generates a magnetic field in which the lower end surface 534 side of the cover plate 53 has an S pole, and the second solenoid 82 generates a magnetic field in which the bottom surface 513 side of the recess has an N pole. Generated.
Since the magnetic flux φep1 of the first solenoid 81 has the same direction as the magnetic flux φm1 of the first permanent magnet 86 and the S pole and the N pole face each other, the first valve 60 is opened by an attractive force.
The magnetic flux φep2 of the second solenoid 82 has the same direction as the magnetic flux φm2 of the second permanent magnet 87, and the north and south poles face each other, so that the second valve 70 is closed by an attractive force.

When energized in the reverse direction shown in FIG. 15, the first solenoid 81 generates a magnetic field in which the lower end surface 534 side of the cover plate 53 becomes the north pole, and the second solenoid 82 generates a magnetic field in which the recess bottom surface 513 side becomes the south pole. Generated.
Since the magnetic flux φep1 of the first solenoid 81 is in the opposite direction to the magnetic flux φm1 of the first permanent magnet 86 and the N poles face each other, the first valve 60 is closed by the repulsive force.
Since the magnetic flux φep2 of the second solenoid 82 is in the opposite direction to the magnetic flux φm2 of the second permanent magnet 87 and the S poles face each other, the second valve 70 is opened by a repulsive force.

As described above, in the solenoid valve portion 504 of the fourth embodiment, the two solenoids 81 and 82 individually superimpose or cancel the magnetic flux φm1 of the first permanent magnet 86 and the magnetic flux φm2 of the second permanent magnet 87. Occurs when energized. The solenoid valve portion 504 uses an attractive force or a repulsive force generated between the permanent magnets 86 and 87 and the opposite cover plate 53 and the lower plate 51 to make one of the first valve 60 and the second valve 70. It operates to open the valve and close the other.

(Fifth Embodiment)
Next, the fifth to seventh embodiments are "opposed type" embodiments in which the flange portions 63 and 73 of the two valves 60 and 79 are coaxially arranged so as to face each other in the solenoid valve portion.
First, with reference to FIG. 16 of the fifth embodiment, a configuration common to the solenoid valve portions of the opposed valve arrangement will be described. The solenoid valve portion 505 is divided into four parts, a first plate 54, an intermediate plate 55, a second plate 56, and a turning plate 57, in this order from the orifice plate 19 side. The end surface of the first plate 54 on the orifice plate 19 side is referred to as a lower end surface 544. Further, the end face of the orifice plate 19 on the first plate 54 side is referred to as an end face 191 and the end face of the turning plate 57 on the second plate 56 side is referred to as an end face 571.

The sub-out orifice 41 is formed on the central axis V of the orifice plate 19 as in the parallel type, and opens at the end surface of the orifice plate 19.
The second out orifice 42 penetrates the first plate 54, the intermediate plate 55, and the second plate 56 starting from the introduction portion 420 at a position offset from the central axis V of the orifice plate 19. Further, the second out orifice 42 is turned 180 ° from upward to downward by the uppermost turning plate 57 and communicates with the opening 429 opening on the third plate 56 side.

The first valve 60 is made of a magnetic material, has a shaft portion 61 and a flange portion 63, and is housed in the first plate 54, as in the parallel type.
The shaft portion 61 slides on the inner wall of the sliding hole of the first plate 54 formed on the central shaft V. The flange portion 63 is urged by the first spring 66 from the intermediate plate 55 side toward the concave end surface 543 of the first plate 54. When the seat surface 65 at the tip of the shaft portion 61 comes into contact with the end surface 191 of the orifice plate 19, the sub-out orifice 41 is closed.

The second valve 79 is made of a magnetic material, has a shaft portion 71 and a flange portion 73 like the first valve 60, and is housed in the second plate 56.
The shaft portion 71 slides on the inner wall of the sliding hole of the second plate 56 formed on the central shaft V. The flange portion 73 is urged by the second spring 76 from the intermediate plate 55 side toward the recessed end surface 563 of the second plate 56. When the seat surface 75 at the tip of the shaft portion 71 comes into contact with the end surface 571 of the turning plate 57, the second out orifice 42 is closed. The valve closing direction of the second valve 79 is the direction toward the top of the figure, which is opposite to the valve closing direction of the first valve 60.
In short, the first valve 60 and the second valve 79 of the solenoid valve portion 505 are arranged substantially vertically symmetrically with respect to the intermediate plate 55. The above is the basic configuration of the opposed valve arrangement common to the fifth to seventh embodiments.

Subsequently, FIGS. 16 to 18 will be referred to with respect to the fifth embodiment. The fifth embodiment has a slightly different point of view from the above embodiment, and operates the valves 60 and 79 based on the "bias magnetic flux" generated by the magnetic flux of the permanent magnet, based on the magnetic flux generated when the solenoid is energized. explain. In the fifth embodiment, the reference to the hydraulic pressure Ff is omitted.
The solenoid valve portion 505 of the fifth embodiment is housed in an annular groove portion 545 formed in the recessed end surface 543 of the first plate 54 on which one permanent magnet 84 is fixed. The end face on the opening side of the permanent magnet 84 is arranged at a position slightly lowered so as not to protrude from the recess end face 543. That is, the permanent magnet 84 is provided on the valve tip side of the flange portion 63 of the first valve 60. In the example of the figure, the permanent magnet 84 has an N pole on the bottom surface 543 side of the recess and an S pole on the 544 side of the lower end surface.
The first plate 54 and the second plate 56 are made of, for example, a non-magnetic material.

When not energized as shown in FIG. 16, the first valve 60 is closed by the urging force Fsp1 of the first spring 66 and the attractive force of the permanent magnet 84. The second valve 79 is closed by the urging force Fsp2 of the second spring 76.

When energized in the forward direction shown in FIG. 17, a magnetic field is generated in which the first valve 60 side has an S pole and the second valve 79 side has an N pole. The electromagnetic force Fep of the solenoid 83 basically sucks the flange portions 63 and 73 toward the intermediate plate 55 and acts in the direction of opening the first valve 60 and the second valve 79. The second valve 79 opens when the electromagnetic force Fep exceeds the urging force Fsp2 of the second spring 76.
On the other hand, with respect to the first valve 60, the magnetic flux φep of the solenoid 83 and the magnetic flux φm1 of the permanent magnet 84 are in the same direction, and the magnetic flux φm1 of the permanent magnet 84 acts as a bias magnetic flux that increases the magnetic flux of the solenoid 83. Therefore, a larger electromagnetic force Fep ⁺ acts.
That is, due to the influence of the bias magnetic flux in the same direction, the required driving force for opening the first valve 60 is relatively smaller than the required driving force for opening the second valve 79, and the first valve 60 is the second valve. The valve is opened with a smaller current than the valve 79.
As a result, both the first valve 60 and the second valve 79 open when energized in the forward direction.

When energized in the reverse direction shown in FIG. 18, a magnetic field is generated in which the first valve 60 side is the north pole and the second valve 79 side is the south pole. The electromagnetic force Fen of the solenoid 83 basically sucks the flange portions 63 and 73 toward the intermediate plate 55 and acts in the direction of opening the first valve 60 and the second valve 79. The second valve 79 opens when the electromagnetic force Fen exceeds the urging force Fsp2 of the second spring 76.
On the other hand, with respect to the first valve 60, the magnetic flux φen of the solenoid 83 and the magnetic flux φm1 of the permanent magnet 84 are in opposite directions, and the magnetic flux φm1 of the permanent magnet 84 acts as a bias magnetic flux that reduces the magnetic flux of the solenoid 83. Therefore, the reduced electromagnetic force Fen ^- is lower than the urging force Fsp1 of the first spring 66.
That is, due to the influence of the bias magnetic flux in the opposite direction, the required driving force for opening the first valve 60 becomes relatively larger than the required driving force for opening the second valve 79. The energizing current at this time does not reach the required driving force of the first valve 60, and the first valve 60 maintains the closed state.
As a result, the first valve 60 is closed and the second valve 79 is opened when the power is applied in the reverse direction.

In contrast to the fifth embodiment, by providing a permanent magnet on the side of the second plate 56, the first valve 60 is opened in any energizing direction, and the opening and closing of the second valve 79 is switched according to the energizing direction. Can be.
Further, by providing permanent magnets on the first plate 54 and the second plate 56, respectively, one of the first valve 60 and the second valve 79 can be opened and the other can be closed.
Since these configurations can be easily inferred from the drawings of the fifth embodiment, the illustration will be omitted.

(Sixth Embodiment)
Refer to FIGS. 19 to 21 for the sixth embodiment. The sixth embodiment corresponds to the third embodiment of the parallel type, and the notes of symbols and the like correspond to the third embodiment.
The solenoid valve portion 506 of the sixth embodiment is mounted on the first valve 60 and the second valve 79, which have two permanent magnets 86 and 87 on the movable side, respectively, and is provided with one solenoid 83. ..

The first permanent magnet 86 is mounted on the valve tip side surface of the flange portion 63 of the first valve 60, and the second permanent magnet 87 is mounted on the valve tip side surface of the flange portion 73 of the second valve 79. Has been done. In the example of the figure, both the first permanent magnet 86 and the second permanent magnet 87 have an N pole on the side in contact with the flange portions 63 and 73 and an S pole on the valve tip side.
The first plate 54 and the second plate 56 are made of, for example, a non-magnetic material.

When not energized as shown in FIG. 19, the first valve 60 is closed by the urging force Fsp1 of the first spring 66 and the attractive force of the first permanent magnet 86. The second valve 79 is closed by the urging force Fsp2 of the second spring 76 and the attractive force of the second permanent magnet 87.

When energized in the forward direction shown in FIG. 20, a magnetic field is generated in which the first valve 60 side has an S pole and the second valve 79 side has an N pole.
Since the magnetic flux φep of the solenoid 83 is in the same direction as the magnetic flux φm1 of the first permanent magnet 86 and the S pole and the N pole face each other, the first valve 60 is opened by an attractive force.
Further, since the magnetic flux φep of the solenoid 83 is in the opposite direction to the magnetic flux φm2 of the second permanent magnet 87 and the N poles face each other, the second valve 79 is closed by the repulsive force.

When energized in the reverse direction shown in FIG. 21, a magnetic field is generated in which the first valve 60 side is the north pole and the second valve 79 side is the south pole.
Since the magnetic flux φen of the solenoid 83 is in the opposite direction to the magnetic flux φm1 of the first permanent magnet 86 and the N poles face each other, the first valve 60 is closed by the repulsive force.
Further, since the magnetic flux φen of the solenoid 83 is in the same direction as the magnetic flux φm2 of the second permanent magnet 87 and the S pole and the N pole face each other, the second valve 79 is opened by an attractive force.
The sixth embodiment realizes the same operation as the parallel type third embodiment with the opposed type configuration.

(7th Embodiment)
See FIGS. 22-24 for the seventh embodiment. The seventh embodiment corresponds to the fourth embodiment of the parallel type, and the notes and the like of the symbols conform to the third and fourth embodiments.
The solenoid valve portion 507 of the seventh embodiment is mounted on the first valve 60 and the second valve 79 on which two permanent magnets 86 and 87 are movable, respectively, and two solenoids 81 and 82 are provided. ing.
The mounting configuration of the first permanent magnet 86 and the second permanent magnet 87 on the first valve 60 and the second valve 79 is the same as that of the sixth embodiment.
The first solenoid 81 is provided on the valve tip side with respect to the concave bottom surface 543 of the first plate 54. The second solenoid 82 is provided on the valve tip side with respect to the concave bottom surface 563 of the second plate 56.
The intermediate plate 55 is made of, for example, a non-magnetic material.

When not energized as shown in FIG. 22, the first valve 60 is closed by the urging force Fsp1 of the first spring 66 and the attractive force of the first permanent magnet 86. The second valve 79 is closed by the urging force Fsp2 of the second spring 76 and the attractive force of the second permanent magnet 87.

When energized in the forward direction shown in FIG. 23, the first solenoid 81 generates a magnetic field in which the bottom surface of the recess 543 is the south pole, and the second solenoid 82 generates a magnetic field in which the bottom surface of the recess 563 is the north pole.
Since the magnetic flux φep1 of the first solenoid 81 is in the opposite direction to the magnetic flux φm1 of the first permanent magnet 86 and the S poles face each other, the first valve 60 is opened by a repulsive force.
The magnetic flux φep2 of the second solenoid 82 has the same direction as the magnetic flux φm2 of the second permanent magnet 87, and the north and south poles face each other, so that the second valve 79 is closed by an attractive force.

When energized in the reverse direction shown in FIG. 24, the first solenoid 81 generates a magnetic field in which the bottom surface of the recess 543 is the north pole, and the second solenoid 82 generates a magnetic field in which the bottom surface of the recess 563 is the south pole.
The magnetic flux φen1 of the first solenoid 81 has the same direction as the magnetic flux φm1 of the first permanent magnet 86, and the north and south poles face each other, so that the first valve 60 is closed by an attractive force.
Since the magnetic flux φen2 of the second solenoid 82 is in the opposite direction to the magnetic flux φm2 of the second permanent magnet 87 and the S poles face each other, the second valve 79 is opened by the repulsive force.
The seventh embodiment realizes the same operation as the fourth embodiment of the parallel type in a facing type configuration.

(Other embodiments)
(A) In the above embodiment, for the parallel type and opposed type valve arrangements, an example in which the permanent magnets 84 and 85 are provided on the fixed side and an example in which the permanent magnets 86 and 87 are mounted on the movable side are shown. .. In addition, permanent magnets may be provided on both the fixed side and the movable side. Further, various configurations obtained by appropriately combining the above embodiments may be adopted.

(B) In the above embodiment, basically two types of valve opening states are switched, and two levels of injection rate are variably controlled. In another embodiment, by switching between three valve open states: a valve open state of both valves, a valve open state of only the first valve 60, and a valve open state of only the second valves 70 and 79, 3 The level injection rate may be variable.

(C) In the present embodiment, it is essential that two valves, a first valve 60 for opening and closing the first fuel outflow path 47 and a second valve 70 and 79 for opening and closing the second fuel outflow path 48, are provided. It becomes a constituent requirement. However, in addition to these two valves, valves for other purposes may be further provided.
As described above, the present invention is not limited to the above-described embodiment, and can be implemented in various embodiments without departing from the spirit of the invention.

10 (11, 12, 13, 14) ... housing,
21 ... Needle valve, 31 ... Pressure control chamber,
36 ... 1st out orifice (1st fuel outflow path),
41 ... Sub-out orifice (first fuel outflow path),
42 ... 2nd out orifice (2nd fuel outflow path),
47 ... First fuel outflow route,
48 ... Second fuel outflow route,
60 ... 1st valve, 66 ... 1st spring (1st valve urging member),
70, 79 ... 2nd valve, 76 ... 2nd spring (second valve urging member),
81, 82, 83 ... Solenoid,
84, 85, 86, 87 ... Permanent magnets.

Claims (8)

A fuel injection device capable of changing the injection rate by driving control of the needle valve (21) by the fuel pressure of the pressure control chamber (31).
A first fuel outflow path (47) communicating with the pressure control chamber and a second fuel outflow path (48) communicating with the pressure control chamber were formed at positions different from the first fuel outflow path. Housing (10) and
A first valve (60) formed of a magnetic material, housed in the housing, having a flange portion (63) on the proximal end side, and opening and closing the first fuel outflow path.
With the second valve (70, 79) which is formed of a magnetic material, is housed in the housing coaxially with the first valve, has a flange portion (73) on the proximal end side, and opens and closes the second fuel outflow path. ,
A first valve urging member (66) and a second valve urging member (76) that urge the first valve and the second valve in the valve closing direction, respectively.
One or more solenoids (81, 82, 83) that are fixed to the housing, generate electromagnetic force by energization, and can switch the energization direction in the forward direction and the reverse direction.
It comprises one or more permanent magnets (84, 85, 86, 87) formed in an annular shape and magnetized so that one axial direction is the north pole and the other axial direction is the south pole.
The permanent magnet is provided in the housing on the tip side of at least one of the flange portions of the first valve or the second valve, or is mounted on the first valve and the second valve, respectively. Ori,
By switching the energizing direction of the solenoid, the first valve urging member and the urging force of the second valve urging member are based on at least the relationship between the electromagnetic force of the solenoid, the magnetic force of the permanent magnet, and the urging force of the first valve urging member and the second valve urging member. A fuel injection device capable of switching at least two of a valve open state of only one valve, a valve open state of the second valve only, and a valve open state of both the first valve and the second valve. The fuel injection device according to claim 1, wherein the permanent magnets (84, 85) are provided in the housing on the tip end side of at least one of the first valve or the second valve from the flange portion. The fuel injection device according to claim 2, wherein one permanent magnet is provided on the tip side of either the first valve or the second valve from the flange portion. The fuel injection device according to claim 2, wherein two permanent magnets are provided on the tip side of the first valve from the flange portion and on the tip side of the second valve from the flange portion. The fuel injection device according to claim 1, wherein the permanent magnets (86, 87) are mounted on the first valve and the second valve, respectively. A magnetic flux that is commonly superimposed or offset with respect to the magnetic flux of the permanent magnet (86) mounted on the first valve and the magnetic flux of the permanent magnet (87) mounted on the second valve is generated at the time of energization. The fuel injection device according to claim 5, further comprising one solenoid (83). A magnetic flux that is individually superimposed or offset with respect to the magnetic flux of the permanent magnet (86) mounted on the first valve and the magnetic flux of the permanent magnet (87) mounted on the second valve is generated at the time of energization. The fuel injection device according to claim 5, further comprising the two solenoids (81, 82). The permanent magnet is arranged so that the magnetic force generated by the permanent magnet acts as a force in the valve closing direction on at least one of the first valve and the second valve when the solenoid is not energized. The fuel injection device according to any one of 1 to 7.

Images