JPH07233884A - Solenoid valve device - Google Patents

Abstract

PURPOSE:To obtain the excellent characteristics of the valve closing responsiveness, valve opening responsiveness, and durability of a solenoid valve device which can be used in a suitable manner as electromagnetic spill valve arranged in a Diesel engine. CONSTITUTION:As for a solenoid valve device which permits the communication and cut-off of the fluid passages 77 and 78 formed in a housing 70, by opening and closing a valve by driving a spool 71 by the magnetic force generated by a solenoid 72, the spool 71 is constituted by arranging a plurality of spool valve parts 84-86 in series. The fluid passages 77 and 78 are branched to plural parts in correspondence with the number of arrangements of the spool valve parts 84-86, and is constituted of a plurality of branched passages 80a, 81a, and 81b, which are arranged in parallel to the spool 71.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a solenoid valve device, and more particularly to a solenoid valve device suitable for use as a solenoid spill valve installed in a diesel engine.

[0002]

2. Description of the Related Art Generally, a diesel engine using an electronically controlled fuel injection control device has an electromagnetic spill valve in a fuel injection pump for pressure-feeding fuel to a diesel engine.
This electromagnetic spill valve is an electromagnetic valve device in which a solenoid provided therein generates magnetic force based on an input signal, and the magnetic force opens and closes the valve.

The input port of the electromagnetic spill valve is connected to the fuel pressurizing chamber and the output port is connected to the fuel low pressure chamber. Then, based on a signal from a microcomputer constituting the fuel injection control device, at the time of fuel injection, the electromagnetic spill valve is closed to cut off the input port and the output port, thereby sending the fuel under pressure to the diesel engine. When the injection is stopped, the electromagnetic spill valve is opened and the input port and the output port are communicated with each other, so that the fuel is spilled into the fuel low pressure chamber and the fuel supply to the diesel engine is stopped.

The structure of this type of solenoid valve device (electromagnetic spill valve) is disclosed in, for example, Japanese Patent Application Laid-Open No. 60-128941. The electromagnetic spill valve disclosed in the publication is a so-called inward opening type electromagnetic spill valve. Figure 5
FIG. 3 is a main part configuration diagram showing an inward open type electromagnetic spill valve 100 in an enlarged manner.

As shown in the figure, an inward opening type electromagnetic spill valve 100 is composed of a housing 101, a valve body 102, a solenoid 103, and the like. In the housing 101, an input port 104 and an output port 105 are provided. Fuel passage composed of 10
6 are formed. The valve body 102 is a collar portion arranged on the upper portion.
It is composed of 102a and a valve portion 102b arranged in the lower portion, and at least the collar portion 102a is formed of a magnetic material.

When the solenoid 103 is energized to generate a magnetic force, the flange 102a is attracted by the magnetic force, so that the valve body 102 moves downward and the input port 104 and the output port 105
The fuel passage 106 is blocked by closing the valve seat 108 disposed between the valve seat 102b and the valve seat 102b from the inside. on the other hand,
When the energization of the solenoid 103 is stopped, the valve body 102 is moved upward by the elastic force of the spring 107, and the input port 104 and the output port 105 are communicated again.

On the other hand, in contrast to the inward opening type electromagnetic spill valve 100, an outward opening type electromagnetic spill valve is known. FIG. 6 is a configuration diagram of a main part showing an externally opened electromagnetic spill valve 110. still,
6, the inward opening type electromagnetic spill valve 100 shown in FIG.
The same reference numerals are given to the configurations corresponding to the configurations described above and the description thereof will be omitted.

In the outwardly opening type electromagnetic spill valve 110, a valve portion 111a is arranged at the lower end portion of a valve body 111, and the arrangement position of the valve portion 111a is higher than that of the valve seat 108. It is in the lower position. Therefore, the valve element is
When the valve 111 moves upward, the valve portion 111b closes the valve seat 108 from the outside, thereby blocking the fuel passage 106.
On the other hand, when the power supply to the solenoid 103 is stopped, the spring 10
The valve element 111 moves downward due to the elastic force of 7, and the input port 10
4 and the output port 105 are connected to each other.

[0009]

However, in the above-mentioned conventionally used inward-opening type electromagnetic spill valve 100 and externally-opening type electromagnetic spill valve 110, the substantial pressure receiving area for receiving the fuel pressure of the valve bodies 102, 111 is used. Is different between when the valve is opened and when it is closed, the opening and closing operations of the valve bodies 102 and 111 are affected by the fuel pressure, and the valve opening response or valve closing response decreases, and there is a shock when the valve is closed. There was a problem that durability deteriorates due to sitting.

That is, in the case of the inward opening type electromagnetic spill valve 100, the pressure of the fuel flowing from the input port 104 is a main problem, and when the valve is closed, the lower end surface 102c of the valve body 102 is the pressure receiving surface of the inflowing fuel. Therefore, when the valve is closed, the side surface of the valve portion 102b becomes the pressure receiving surface. However, since the valve body 102 moves up and down, it is only the lower end surface 102c of the valve body 102 that the fuel pressure affects the vertical movement of the valve body 102, and the pressure applied to the side surface of the valve portion 102b. Does not affect the vertical movement of the valve body 102.
Therefore, the substantial (valve disc 10
The pressure receiving area is different when the valve is open and when it is closed.

On the other hand, in the externally opened electromagnetic spill valve 110, the internal pressure of the fuel existing in the output port 105 becomes a problem when the valve is opened, and the lower end portion 111b of the valve element 111 serves as a pressure receiving surface for this internal pressure. Further, when the valve is closed, the pressure of the fuel flowing from the input port 104 becomes a main problem, and the side surface of the valve portion 111a becomes the pressure receiving surface. Since the valve body 111 also moves up and down, the fuel pressure affects the vertical movement of the valve body 111 only at the lower end portion 111b of the valve body 111. Therefore, the open-type electromagnetic spill valve 110
The substantial pressure-receiving area (which affects the operation of the valve element 111) of is different when the valve is open and when it is closed.

FIG. 7 collectively shows the quality of the valve closing response, the valve opening response, and the durability of the inward opening electromagnetic spill valve 100 and the outward opening electromagnetic spill valve 110. . In the same figure, the circles indicate good, and the triangles indicate bad. As shown in the figure, in the conventional solenoid valve device (electromagnetic spill valve), all of the valve closing response, the valve opening response, and the durability could not be made good.

The durability of the open-type electromagnetic spill valve 110 is inferior because, when the valve body 111 is closed, the force required to close the valve body 111 is not only the magnetic force of the solenoid 103 but also the output port 105. Since the internal pressure of the fuel existing in the valve works upward, the force to close the valve body 111 increases and the valve body 111 is closed.
This is due to the lower end portion 111c of the abutment abutting against the valve seat 108.

The present invention has been made in view of the above points, and is configured so that the pressure receiving areas of the valve body are equal in both the valve opening direction and the valve closing direction, so that the valve closing response and the valve opening response can be improved. It is an object of the present invention to provide a solenoid valve device that can obtain good characteristics in terms of both durability and durability.

[0015]

In order to solve the above-mentioned problems, in the present invention, a valve body is driven by an electromagnetic force to perform a valve opening and closing operation, and a fluid passage formed in a housing is opened. In the solenoid valve device for communicating and shutting off, the valve body has a structure in which a plurality of spool valve parts are arranged in series, and the fluid passage is branched into a plurality of parts corresponding to the number of spool valve parts. The present invention is characterized in that it is constituted by a plurality of branch passages, and that the plurality of branch passages are arranged in parallel with the valve body.

[0016]

By configuring the solenoid valve device as described above, the fluid passage is divided into a plurality of branch passages in accordance with the number of spool valve portions arranged, and the plurality of branch passages are formed. By arranging in parallel with the valve body, the area of the surface where the fluid pressure formed on the valve body applies pressure in the valve opening direction (valve opening direction pressure receiving area)
Then, the area of the surface where the fluid pressure formed on the valve body applies pressure in the valve closing direction (valve closing direction pressure receiving area) can be made substantially the same area.

By making the valve-opening direction pressure-receiving area and the valve-closing direction pressure-receiving area the same, the fluid pressure urges the valve body in the valve closing direction and the fluid pressure closes the valve body. The pressures applied in the directions cancel each other out. Thereby, the influence of the fluid pressure on the opening / closing operation of the valve body can be reduced, and the responsiveness of the opening / closing valve operation at the time of opening and closing the valve can be improved.

[0018]

Embodiments of the present invention will now be described with reference to the drawings.

FIG. 1 is a main part configuration diagram showing a solenoid valve device 16 which is an embodiment of the present invention, and FIG. 2 is an enlarged view showing a spool constituting the solenoid valve device 16, and FIG. FIG. 2 is a sectional view showing a fuel injection pump 1 using the solenoid valve device 16 shown in FIG. 1 as an electromagnetic spill valve. First, the fuel injection pump 1 provided with the electromagnetic valve device 16 (hereinafter referred to as an electromagnetic spill valve) will be described with reference to FIG.

The fuel injection pump 1 takes in the fuel pumped up from the fuel tank 3 to the pump low pressure side passage 6 by the feed pump 2 into the gallery (fuel low pressure chamber) 5 through the pump high pressure side passage 4, and the injection magnetism and the injection amount are obtained. The adjusted high-pressure fuel is pressure-fed from the delivery valve 7 to the injection nozzle of the diesel engine.

The inside of the fuel injection pump 1 is a cylindrical cylinder 12 provided in a pump housing 11, a rotor 13 is rotatably fitted to the inner peripheral surface of the cylinder 12 to switch the fuel passage, And a solenoid spill valve (solenoid valve) that is a main part of the present invention that causes fuel pressurized in a plunger chamber (fuel pressurizing chamber) 14 formed in the rotor 13 to overflow from a fuel passage in the rotor 13 (spill). Device) 16 and the like.

Inside the cylinder 12, the intake passage 21 for supplying fuel from the gallery 5 to the plunger chamber 14 via the communication passage 34, and the fuel pressurized in the plunger chamber 14 are sent under pressure to the delivery valve 7. Discharge passage 22,
Overflow passages 23 for releasing fuel from the blanker chamber 14 to the gallery 5 in order to adjust the fuel injection amount are provided respectively, and these passages 21, 22, and 23 are provided on the cylinder inner peripheral wall surface 12 respectively.
The outer peripheral surface of the rotor small-diameter portion 12a sliding at a is opened.

The rotor small diameter portion 13a for distributing the fuel is
A suction port 31 for inserting the fuel supplied to the plunger chamber 14 from the suction passage 21, a discharge port 32 for discharging the high-pressure fuel pressurized in the plunger chamber 14 to the discharge passage 22,
Overflow port 33 for discharging fuel to overflow passage 23 for adjusting the fuel injection amount, and these ports 31, 32, 33
There are provided communication passages 34, one end of which communicates with the other and the other end of which communicates with the plunger chamber 14.

The rotor large diameter portion 13b, which has a larger outer diameter than the rotor small diameter portion 13a and serves as a fuel pressurizing portion, has two through holes 35 which are orthogonal to the radial direction, and two through holes 35 are formed in each through hole 35. A total of four plungers 36 are fitted so as to be slidable in the radial direction, and the plunger chamber 14 is formed between the inner end surfaces of these plungers 36.

On the outer end surface of the plunger 36 in the radially outward direction,
A roller shoe 38 that rotatably holds the roller 39 is provided in a shoe guide groove (not shown in the drawing) so as to be slidable in the radial direction. The inner cam 40 is provided radially outward of the roller 39.
Inner peripheral surfaces 40a face each other, and cam ridges are formed in the circumferential direction of the inner peripheral surfaces. The plunger 36, which is biased radially outward by the fuel pressure and centrifugal force of the plunger chamber 14,
By one end thereof, the roller 39 is passed through the roller shoe 38.
Is in pressure contact with the cam surface formed on the inner peripheral surface 40a of the inner cam.

In the fuel suction process in which the plunger 36 moves radially outward by the rotation of the rotor 13, the suction passage 2
1 and the suction port 31 communicate with each other, and are arranged so that the suction passage 21 and the suction port 31 are closed in the compression process. Further, the discharge port 32 of the rotor 13 communicates with the discharge passage 22 of the cylinder 12 in the discharge process. The discharge passage 22 communicates with the delivery valve 7 via a passage 57 in the pump housing 11. Delivery valve 7
Is connected to a pipe (not shown), and the other end of the pipe is connected to an injection nozzle mounted on a diesel engine.

An electromagnetic spill valve 16 is arranged in the fuel passage downstream of the overflow passage 23, and the electromagnetic spill valve 16 connects or disconnects the overflow passage 23 and the gallery 5. The electromagnetic spill valve 16 is a signal indicating the operating state of the diesel engine, for example, a signal from an accelerator opening sensor,
Drive control is performed based on a signal from the rotation sensor or the like.

Pulser 2 provided on the rotor large diameter portion 13b
A rotation speed signal detected by a rotation sensor 28 provided at a position facing 6 is a control device (microcomputer) 6
0, the control device 60 controls the rotation sensor 28
The engine operating state is determined based on the signals supplied from various sensors including the rotational speed signal from the engine. Then, the valve opening timing of the electromagnetic spill valve most suitable for the above engine operating state is calculated, this valve opening timing is converted into time, and a valve opening signal is transmitted to the electromagnetic spill valve 16 and transmitted.

When the rotor 13 is rotated by the rotation of the diesel engine, the plunger 36 moves toward the inner cam 40.
, A suction step of reciprocating in the radial direction along the cam profile to suck fuel from the gallery 5 into the plunger chamber 14 and a pressure feeding step of assuring high pressure fuel from the plunger chamber 14 to the injection nozzle via the delivery valve 7 are repeatedly performed. Then, in synchronization with this, the electromagnetic spill valve 16 adjusts the overflow timing, that is, controls the fuel injection amount.

Next, the structure of the electromagnetic spill valve 16 disposed in the fuel injection pump 1 having the above structure will be described in detail below with reference to FIG.

The electromagnetic spill valve 16 is roughly composed of a housing 70, a spool 71, a solenoid 72, a coil spring 73 and the like.

The housing 70 is made of, for example, a non-magnetic metal, and a spool mounting hole 74 for mounting the spool 71 is formed in a central portion thereof, and a flange displacement space 75, a solenoid mounting portion 76 and the like are provided in an upper portion. Are formed. An inflow-side fluid passage 77 and an outflow-side fluid passage 78 are formed on both sides of the spool mounting hole 74 with the spool mounting hole 74 interposed therebetween.

The inflow side fluid passage 77 is branched into a plurality (two in this embodiment) from the inlet port 79 to form a first inflow side branch passage 80a and a second inflow side branch passage 80b. In addition, the outflow side fluid passage 78 is also bifurcated to form a first outflow side branch passage 81a and a second outflow side branch passage 81b, and the respective branch passages 81a and 81b are integrated to form the outlet port 82. It has been configured to. Further, the first inflow side branch passage 80a and the first outflow side branch passage 81a are configured to face each other with the spool mounting hole 74 interposed therebetween, and the second inflow side branch passage 80b and the first outflow side are arranged. The branch passage 81b is also configured to face each other with the spool mounting hole 74 interposed therebetween.

The above-mentioned inlet port 79 is connected to the overflow passage 23 when mounted on the fuel injection pump 1,
Further, the outlet port 82 is connected to the gallery 5. Therefore, the high-pressure fuel compressed in the plunger chamber 14 is introduced into the inlet port 79 via the overflow passage 23, and the high pressure fuel introduced into the inlet port 79 by the opening operation of the electromagnetic spill valve 16 as described later. The fuel is the inflow side fluid passage 77.
To the gallery 5 from the outlet port 82 through the outflow side fluid passage 78. Further, the electromagnetic spill valve 16 is closed to cause the inflow side fluid passage 7
7 and the outflow side fluid passage 78 are cut off, and the overflow (spill) of high-pressure fuel to the gallery 5 is stopped.

The spool 71 serving as a valve element has a collar portion 83 formed at the upper end portion in the figure, and a plurality of spool valve portions 84 to 86 (three in this embodiment) under the collar portion 83. Connection shaft 8 having a smaller diameter than the diameter of each spool valve portion 84-86 connecting the spool valve portions 84-86.
7 and 88. Further, the plurality of spool valve portions 84 to 86 are arranged so as to be arranged in series in the axial direction of the spool 71 (directions indicated by arrows A1 and A2 in the drawing). These spool valve parts 84 to 8
6 is connected and integrated by the connecting shafts 87 and 88 as described above. The spool 71 is inserted and mounted in a spool mounting hole 74 formed in the housing 70, and in this mounted state, the collar portion 83 has the collar portion displacement space 7
It is configured to be located within 5. Also, spool 7
When mounting 1 in the housing 70, the coil spring 73 is interposed between the lower end of the spool 71 and the bottom of the spool mounting hole 74. The spool valve parts 84 to 8
6 is configured to be movable in the directions of arrows A1 and A2 while maintaining a liquid-tight state in the spool mounting hole 74 formed in the housing 70.

Further, the collar portion 83 constituting the spool 71 is made of a magnetic material, and each spool valve portion 84.
The diameter is set to be larger than the diameter size of ~ 86. This collar part 83
A solenoid mounting portion 76 is formed at a predetermined position of the housing 70 facing the solenoid mounting portion 76.
A solenoid 72 is mounted inside. Therefore, when the solenoid 72 is energized, the collar portion 83 is attracted in the A1 direction against the coil spring 73 by the generated magnetic force, and the spool 71 moves downward. When the energization of the solenoid 72 is stopped, the elastic restoring force of the coil spring 73 causes the collar portion 83 to move upward in the A2 direction.

FIG. 1 shows a state in which the energization of the solenoid 72 is stopped, that is, the electromagnetic spill valve 16 is opened.

When the electromagnetic spill valve 16 is opened, the spool 71 is moved upward in the A2 direction by the elastic force of the coil spring 73 as described above, and the first inflow side branch passage 80a is formed opposite to the spool 71. And the first outflow side branch passage 81a, the first connecting shaft 87 is located between the second inflow side branch passage 80b and the second outflow side branch passage 81b, which are also formed to face each other. Has a configuration in which the second connecting shaft 88 is positioned.

As described above, since the connecting shafts 87 and 88 are smaller in diameter than the spool valve parts 84 to 86, the first inflow-side branch passage 80a and the first outflow passage 80a. The side branch passage 81a, and the second inflow side branch passage 80b and the second outflow side branch passage 81b are communicated together. Therefore, the high-pressure fuel introduced into the inlet port 79 is the inlet port 79, the first and second inflow side branch passages 80a and 80b, and the connecting shafts 87 and 8 as shown by the arrows in the figure.
8, the first outflow side branch passages 81a and 81b, and the outlet port 82 in this order. As a result, the high-pressure fuel compressed in the plunger chamber 14 is spilled to the gallery 5 via the electromagnetic spill valve 16.

On the other hand, FIG. 4 shows a state in which the solenoid 72 is energized, that is, the electromagnetic spill valve 16 is closed.

When the electromagnetic spill valve 16 is closed, the spool 71 moves downward in the A1 direction due to the magnetic force generated by the solenoid 72 as described above, and the first inflow side branch passage 80a is formed opposite to the spool 71. And the first outflow-side branch passage 81a, the first spool valve portion 84 is located between the first inflow-side branch passage 8a and the second inflow-side branch passage 8a.
The first spool valve portion 85 is located between the 0b and the second outflow side branch passage 81b.

The diameters of the spool valve portions 84 and 85 are substantially the same as the diameters of the spool valve portions 84 to 86. The spool valve portions 84 and 85 are liquid-tight in the spool mounting hole 74. It is configured to be movable while maintaining. Therefore, the first inflow side branch passage 80a and the first outflow side branch passage 81a, and the second inflow side branch passage 80b and the second outflow side branch passage 81b are both blocked. Therefore, the overflow (spill) of the high-pressure fuel compressed in the plunger chamber 14 to the gallery 5 is stopped.

The force exerted by the high-pressure fuel flowing in the electromagnetic spill valve 16 on the spool 71 when the electromagnetic spill valve 16 is open will now be described with reference to FIGS. 1 and 2.

The electromagnetic spill valve 16 is opened, the first inflow side branch passage 80a and the first outflow side branch passage 81a communicate with each other, and the second inflow side branch passage 80b and the second outflow side branch are provided. In a state where the spool 71 is in communication with the passage 81b, the spool 71 receives pressure by the high-pressure fuel flowing in the electromagnetic spill valve 16. In particular, the moving direction of the spool 71 (A1, A2) that affects the valve opening and closing characteristics of the electromagnetic spill valve 16.
Direction), the pressure due to the high-pressure fuel is the lower surface (first pressure receiving surface) 8 of the first spool valve portion 84.
4a, an upper surface (second pressure receiving surface) 85a of the second spool valve portion 85, a lower surface (third pressure portion) of the second spool valve portion 85.
Pressure receiving surface) 85b and the upper surface (fourth pressure receiving surface) 86a of the third spool valve portion 86, respectively.

As described above, in the electromagnetic spill valve 16 according to this embodiment, the spool 71 has a structure in which three spool valve portions 84 to 86 are arranged in series. Further, the inflow-side fluid passage 77 is composed of a first inflow-side branch passage 80a and a second inflow-side branch passage 80b which are branched into two, and the outflow-side fluid passage 78 is branched into a bifurcated shape. 1 outflow side branch passage 81a and 2nd outflow side branch passage 81
and b. Further, the branched branch passages 80a, 80b, 81a, 81b extend in a direction orthogonal to the moving direction (A1, A2 direction) of the spool 71, that is, in parallel with the spool 71 serving as a valve body. Is configured.

Therefore, the force exerted by the high-pressure fuel flowing between the first spool valve portion 84 and the second spool valve portion 85 in the moving direction of the spool 71 is, as shown in FIG. The pressure P1 acting on the surface 84a and the pressure P2 acting on the second pressure receiving surface 85a are obtained. The force exerted by the high-pressure fuel flowing between the second spool valve portion 85 and the third spool valve portion 86 in the moving direction of the spool 71 is the pressure P3 acting on the third pressure receiving surface 85ab and the fourth pressure P3.
The pressure P4 acts on the pressure receiving surface 86a.

Further, the spool 71 is a cylindrical member, the spool valve portions 84 to 86 have the same diameter, and the connecting shafts 87 and 88 are also cylindrical members. It is the same. Therefore, the areas of the first to fourth pressure receiving surfaces 84a, 85a, 85b, 86a are all the same. Therefore, the pressure P1 acting on the first pressure receiving surface 84a and the pressure P acting on the second pressure receiving surface 85a.
2 becomes equal (P1 = P2), and similarly the third pressure receiving surface 8
The pressure P3 acting on 5ab and the pressure P4 acting on the fourth pressure receiving surface 86a are also equal (P3 = P4).

Further, the acting direction of the pressure P1 acting on the first pressure receiving surface 84a and the pressure P acting on the second pressure receiving surface 85a.
The acting directions of 2 are opposite to each other, and the acting direction of the pressure P3 acting on the third pressure receiving surface 85ab and the acting direction of the pressure P4 acting on the fourth pressure receiving surface 86a are also opposite to each other. . Therefore, the forces exerted by the high-pressure fuel in the moving direction of the spool 71 are offset each other, and the influence exerted by the high-pressure fuel on the opening / closing operation of the spool 71 can be reduced. The responsiveness of can be improved. Further, since the opening / closing valve operation by the spool 71 is performed by the spool 71 sliding in the A1 and A2 directions, the valve body does not come into contact with the valve seat by shock as in the conventional case, and the spool 7
1 and the housing 70 can be prevented from being damaged, and the electromagnetic spill valve 1
The durability of 6 can also be improved.

In the above-described embodiment, three spool valve portions are provided and the branch passage is divided into two on the inflow side and the outflow side corresponding to this, but the number of spool valve portions and The number of branch passages is not limited to this, and it goes without saying that the number of dispositions is not particularly limited as long as the pressures acting on the pressure receiving surfaces cancel each other out as described above. is there.

In the above embodiment, the areas of the first to fourth pressure receiving surfaces 84a, 85a, 85b and 86a are all the same, but they are opposed to each other in the moving direction of the spool 71. Pressure receiving surface (first pressure receiving surface 84a in this embodiment)
And the second pressure receiving surface 85a, and the third pressure receiving surface 85b and the fourth
If the pressure receiving surfaces 86a) of the
The pressure receiving areas of the pressure receiving surface 84a and the second pressure receiving surface 85a of
Even if the pressure receiving areas of the third pressure receiving surface 85b and the fourth pressure receiving surface 86a are different, the pressures P1 and P2 are offset,
The pressures P3 and P4 can also be offset. Therefore,
The effect of the present invention can be obtained by configuring at least the areas of the pressure receiving surfaces facing each other in the moving direction of the spool 71 to be equal.

Further, in the above embodiment, the electromagnetic valve device according to the present invention is used as the electromagnetic spill valve installed in the fuel injection pump. However, the electromagnetic valve device according to the present invention is applied to the fuel injection pump. Is not limited to the application of
It can be widely applied as a valve device for opening and closing a high pressure fluid.

[0052]

As described above, according to the present invention, the area of the surface where the fluid pressure formed on the valve body applies the pressure in the valve opening direction (valve opening direction pressure receiving area) and the area formed on the valve body. The applied fluid pressure can make the same area as the area of the surface that applies pressure to the valve body in the valve closing direction (pressure receiving area in the valve closing direction). Therefore, the fluid pressure biases the valve element in the valve closing direction. Since the pressure and the pressure by which the fluid pressure biases the valve element in the valve closing direction cancel each other out, the influence of the fluid pressure on the opening / closing operation of the valve element can be reduced, and when the valve is opened and closed. It has features such as improving the responsiveness of the on-off valve operation when the valve is open.

[Brief description of drawings]

FIG. 1 is a main part configuration diagram showing a state in which an electromagnetic valve device (electromagnetic spill valve) according to an embodiment of the present invention is opened.

FIG. 2 is an enlarged view showing a spool arranged in the solenoid valve device (electromagnetic spill valve) shown in FIG.

3 is a sectional view showing a fuel injection pump using the solenoid valve device shown in FIG. 1 as an electromagnetic spill valve.

FIG. 4 is a main part configuration diagram showing a closed state of a solenoid valve device (electromagnetic spill valve) according to an embodiment of the present invention.

FIG. 5 is a main part configuration diagram showing an enlarged view of a conventional inward opening type electromagnetic spill valve.

FIG. 6 is a main-part configuration diagram showing an enlarged view of a conventional outward-opening type electromagnetic spill valve.

FIG. 7 is a diagram collectively showing characteristics of a conventional inward opening type electromagnetic spill valve and an outside opening type electromagnetic spill valve.

[Explanation of symbols]

 1 Fuel Injection Pump 2 Feed Pump 3 Fuel Tank 4 Pump High Pressure Side Passage 5 Gallery (Fuel Low Pressure Chamber) 6 Pump Low Pressure Side Passage 6 7 Delivery Valve 11 Pump Housing 12 Cylinder 13 Rotor 14 Plunger Chamber (Fuel Pressurization Chamber) 16 Electromagnetic Spill Valve (electromagnetic valve device) 21 Intake passage 22 Discharge passage 23 Overflow passage 26 Pulsar 28 Rotation sensor 31 Intake port 32 Discharge port 33 Overflow port 36 Plunger 38 Roller shoe 39 Roller 40 Inner cam 60 Control device 70 Housing 71 Spool 72 Solenoid 73 Coil spring 77 Inflow side fluid passage 78 Outflow side fluid passage 79 Inlet port 80a First inflow side branch passage 80b Second inflow side branch passage 81a First outflow side branch passage 81b Second outflow side branch passage 82 Outlet port 84 first spool valve portion 84a first pressure receiving surface 85 second spool valve portion 85a second pressure receiving surface 85b third pressure receiving surface 86 third spool valve portion 86a fourth pressure receiving surface 87 first Connection shaft 88 Second connection shaft

Claims (1)

[Claims] 1. A solenoid valve device for opening and closing a valve by driving the valve with an electromagnetic force to connect and disconnect a fluid passage formed in a housing, the valve comprising a plurality of spool valves. A plurality of branch passages are formed by branching the fluid passage into a plurality of branch passages corresponding to the number of the spool valve portions, and the plurality of branch passages. Is arranged in parallel with the valve body.