WO2020129236A1

WO2020129236A1 - Electromagnetic valve

Info

Publication number: WO2020129236A1
Application number: PCT/JP2018/047232
Authority: WO
Inventors: 永見　哲郎
Original assignee: 三菱電機株式会社
Priority date: 2018-12-21
Filing date: 2018-12-21
Publication date: 2020-06-25
Also published as: JP6843316B2; JPWO2020129236A1

Abstract

Provided is an electromagnetic valve which has stable performance, and with which durability can be improved. This electromagnetic valve is provided with a cylindrical core (3) which generates a magnetic force of attraction by means of magnetic excitation resulting from energization of a coil (2), a first spring (4) for generating an urging force in the opposite direction to the magnetic force of attraction, a column-shaped plunger (5) which moves in the axial direction of the core (3) by means of the magnetic force of attraction and the urging force, a cylindrical valve (6) which is provided at one end of the plunger (5), on a projecting side thereof, and which opens and closes a fluid passage by means of the movement of the plunger (5), a disk-shaped plate (14) sandwiched between the valve (6) and the plunger (5), and a second spring (13) formed from a coil spring which urges the plate (14) and the plunger (5), wherein: the plate (14) has a groove (16) accommodating the second spring (13); and the groove (16) is formed in such a way that an inner circumferential side diameter (D1) of the groove (16) is greater than an outer diameter (D2) of a part of the plunger (5) onto which the second spring (13) fits loosely, and is less than the sum of the outer diameter (D2) of the plunger (5) and a wire diameter (D3) of the second spring (13).

Description

solenoid valve

The present invention relates to a solenoid valve used for an air bypass valve that controls the flow rate of an intake bypass passage of a turbocharger system.

An engine equipped with a turbocharger has an intake bypass passage that recirculates the air flowing through the throttle valve in the intake passage to the turbocharger and a solenoid valve to adjust the boost pressure. This electromagnetic valve opens and closes the intake bypass passage by bringing a valve seat formed in the intake bypass passage into contact with the valve member. Further, since the valve member is seated on the valve seat against the air flowing when the valve is closed, a pressure balance chamber is provided on the downstream side of the valve member to reduce the necessary driving force.

Therefore, in the conventional air bypass valve, when the pilot valve portion is de-excited, the seal element of the piston pressed by the elastic force of the spring member comes into contact with the opening on the discharge side of the supercharger of the valve body and the supercharger. The communication between the discharge side and the suction side of the turbocharger is blocked. On the other hand, when the pilot valve portion is energized, the movable iron core overcomes the elastic force of the spring member by the electromagnetic force, and the piston strokes to open the valve. (For example, Patent Document 1)

JP, 2016-14414, A

The solenoid valve used in the conventional air bypass valve described above has both ends of the spring member supported on the bottom surface of the inner diameter hole of the piston and the end surface of the large diameter portion of the casing, and is mounted on the outer peripheral portion of the large diameter portion, The elastic force of the spring member causes the sealing element of the piston to contact the valve body. Therefore, since the compression and extension are repeated with the spring member in contact with the piston and the casing, the piston, the casing, and the spring member are worn. As a result, there is a problem that the urging force of the spring member is reduced and the performance of the solenoid valve is reduced, and the spring member is damaged to shorten the life of the solenoid valve.

Also, in the solenoid valve in which a gap is provided between the piston and the casing and the spring member, when the piston tilts due to the pressure or vibration of the fluid, the spring member also contacts the casing in a tilted state together with the piston. Further, when the piston rotates in the circumferential direction due to the pressure or vibration of the fluid, the torsion of the spring member causes the spring member to contact the casing in a tilted state. Therefore, the casing and the spring member are partially worn by repeated compression and expansion of the spring member. As a result, there is a problem in that the spring member is insufficient in urging force to reduce the performance of the solenoid valve, and the spring member is damaged to shorten the life of the solenoid valve.

The present invention has been made to solve the above-mentioned problems, and an object thereof is to obtain a solenoid valve that has stable performance and improved durability.

The solenoid valve according to the present invention includes a cylindrical core that is excited by energization of a coil to generate a magnetic attraction force, a first spring that generates a biasing force in a direction opposite to the magnetic attraction force, and a magnetic attraction force and a biasing force. A cylindrical plunger that moves in the axial direction of the core, a cylindrical valve that is provided at one end on the protruding side of the plunger and that opens and closes the fluid passage by the movement of the plunger, and is sandwiched between the valve and the plunger. A disk-shaped plate and a second spring formed of a coil spring that urges the plate and the plunger are provided, and the plate has an annular groove that accommodates the second spring, and the diameter of the groove on the inner peripheral side is A groove is formed that is larger than the outer diameter of the plunger in the portion where the second spring is loosely fitted and smaller than the sum of the outer diameter of the plunger and the wire diameter of the second spring.

The solenoid valve configured as described above has a disc-shaped plate sandwiched between the valve and the plunger, and includes the plate and the second spring formed of a coil spring for urging the plunger. The plate has an annular groove for accommodating the second spring, and the diameter of the inner peripheral side of the groove is larger than the outer diameter of the plunger at the portion where the second spring is loosely fitted, and the outer diameter of the plunger and the second spring An annular groove formed to be smaller than the combined wire diameter was provided. As a result, the movement of the second spring is restrained and regulated, and the second spring is prevented from coming into contact with the plunger to be worn, thereby stabilizing the performance and improving the durability. It has the effect that a valve can be obtained.

It is a block diagram which shows the example which used the solenoid valve concerning Embodiment 1 of this invention for the air bypass valve of a turbocharger system, and FIG.1(a) shows the closed state of a solenoid valve, FIG. ) Indicates the open state of the solenoid valve. FIG. 2A is a cross-sectional view showing a structure in which an electronic valve is opened and closed in an example in which the solenoid valve according to Embodiment 1 of the present invention is used as an air bypass valve of a turbocharger system, and FIG. 2B shows the valve state, and FIG. 2B shows the open state of the solenoid valve. It is an expanded sectional view showing the valve part of the solenoid valve concerning Embodiment 1 of this invention. It is a perspective view which shows the plate of the solenoid valve concerning Embodiment 1 of this invention. [Fig. 5] Fig. 5 is a cross-sectional view of a main part of the solenoid valve according to the first embodiment of the present invention. Fig. 5(a) shows a state where the spring is housed in the groove of the plate, and Fig. 5(b) shows that the spring is close to the plunger side. Shows the state of It is a principal part sectional view which shows the modification of the solenoid valve concerning Embodiment 1 of this invention.

Hereinafter, in order to explain the present invention in more detail, modes for carrying out the present invention will be described with reference to the accompanying drawings.

Embodiment 1
A solenoid valve according to Embodiment 1 of the present invention will be described with reference to FIGS. 1 is a configuration diagram showing an example in which the solenoid valve according to Embodiment 1 of the present invention is used as an air bypass valve of a turbocharger system, and FIG. 1(a) shows a closed state of the solenoid valve, FIG. 1B shows the open state of the solenoid valve. FIG. 2 is a cross-sectional view showing a structure in which an electronic valve is opened and closed in an example in which the solenoid valve according to the first embodiment of the present invention is used as an air bypass valve of a turbocharger system, and FIG. The closed state of the solenoid valve is shown, and FIG. 2B shows the opened state of the solenoid valve. FIG. 3 is an enlarged sectional view showing a valve portion of the solenoid valve according to the first embodiment of the present invention. FIG. 4 is a perspective view showing a plate of the solenoid valve according to the first embodiment of the present invention. FIG. 5 is a cross-sectional view of a main part of the solenoid valve according to the first embodiment of the present invention. FIG. 5(a) shows a state where the spring is housed in the annular groove of the plate, and FIG. 5(b) shows the spring. Shows the state of being closer to the plunger side. FIG. 6 is a cross-sectional view of essential parts showing a modified example of the solenoid valve according to the first embodiment of the present invention.

As shown in FIGS. 1A and 1B, in the turbocharger system 100, the solenoid valve 1 is provided to adjust the supercharging pressure of the intake passage 102 in the engine in which the turbocharger 101 is mounted. The air bypass valve 103 is used as an air bypass valve for adjusting the flow rate of the intake bypass passage 103.
The turbocharger system 100 includes an exhaust passage 104 for circulating exhaust gas for driving the turbo-charger 101, and an intake passage 102 for circulating intake air compressed by the turbocharger 101 to an engine via an intercooler. A throttle valve 105 arranged inside the intake passage 102 for controlling the supply of compressed air to the engine, and a turbocharger 101, an intake passage 102, a throttle valve 105, and engine damage due to excessively compressed air. In order to prevent the above, the intake bypass passage 103 that releases the compressed air to the upstream side of the turbocharger 101 and the solenoid valve 1 that is used as an air bypass valve that opens and closes the intake bypass passage 103 are configured.
A waste gate valve 106 is provided on the exhaust side to control the flow rate of the exhaust gas flowing through the exhaust passage 104 that drives the turbocharger 101 to the downstream side of the turbocharger 101.

As shown in FIG. 1A, the air compressed by the turbocharger 101 is circulated to the engine when the throttle valve 105 is open. In this state, the solenoid valve 1 is closed.

As shown in FIG. 1(b), the solenoid valve 1 is opened when the throttle valve 105 is closed. As a result, the excessively compressed air staying in the intake passage 102 is released to the upstream side of the turbocharger 101 by the intake bypass passage 103.

As shown in FIGS. 2A and 2B, the solenoid valve 1 is provided with a substantially cylindrical coil 2 and is provided inside the coil 2 and is excited by the coil 2 to generate a magnetic attraction force. The substantially cylindrical core 3 and the substantially cylindrical plunger 5 which is projected by receiving the urging force of the first spring 4 and which is pulled in by the magnetic attraction force of the core 3 and which are provided at the tip of the plunger 5 on the protruding side. And a valve 6 having a substantially cylindrical shape. The solenoid valve 1 is attached to the housing 7 of the intake bypass passage 103 by a bolt 8. A power supply for driving the solenoid valve 1 is connected to the connector 9 provided on the solenoid valve 1. Further, a pressure balancing chamber 11 communicating with the intake bypass passage 103 is provided on the downstream side of the valve 6 through a communication hole 10 provided in the valve 6. As a result, the differential pressure between the intake bypass passage 103 on the upstream side of the valve 6 and the pressure balancing chamber 11 is canceled, and the urging force of the first spring 4 to the plunger 5 and the electromagnetic force generated by the coil 2 and the core 3 are canceled. The suction power is reduced.

As shown in FIG. 2( a ), the plunger 5 of the solenoid valve 1 is projected by the urging force of the first spring 4 when the power is off. As a result, the valve 6 provided at the protruding end of the plunger 5 contacts the valve seat 12 provided on the housing 7, and the intake bypass passage 103 is closed.

As shown in FIG. 2( b ), when the power is on, the solenoid valve 1 has the plunger 5 retracted by the electromagnetic attraction force of the coil 2 and the core 3. As a result, the valve 6 is separated from the valve seat 12, and the intake bypass passage 103 is opened.

In the coil 2, an insulated electric wire is wound around a bobbin (not shown) made of a substantially cylindrical resin. The coil 2 is electrically connected to a terminal (not shown) of the connector 9.

The core 3 has a substantially cylindrical shape made of an iron material, has a flange on the protruding side of the plunger 5, and the opposite side of the flange is arranged inside the coil 2.

The first spring 4 is a compression coil spring and is loosely fitted on the plunger 5. Further, the first spring 4 has one end fixed to the core 3 and the other end fixed to the valve 6, and urges the valve 6 and the plunger 5 to which the valve 6 is fixed toward the protruding side. .. As a result, the valve 6 is seated on the valve seat 12, and the solenoid valve 1 is closed.

As shown in FIGS. 3 and 4, the plunger 5 has an axial shape made of a magnetic material and is slidably arranged inside the core 3. Further, the plunger 5 is formed with a step portion 51 having an outer diameter dimension D2 having a small diameter toward the tip on the protruding side, and a step portion 52 having a diameter smaller than the step portion 51.

The valve 6 has a substantially cylindrical shape made of resin, and a wall portion 61 that partitions the inside is formed in the radial direction. Further, the valve 6 is inserted into the step portion 52 through a hole provided in the center of the wall portion 61, and the plate 14 on the step portion 51 side biased by the second spring and the tip of the plunger 5 on the protruding side. It is sandwiched between the washer 15 and the washer 15. The valve 6 has a play and is attached to the plunger 5.

The second spring 13 is a compression coil spring in which the wire cross section is circular, and is loosely fitted in the step portion 51. Further, the second spring 13 has one end housed in the plunger 5 and the other end housed in the annular groove 16 of the plate 14 to urge the plunger 5. As a result, the valve 6 is pressed and fixed to the washer 15. The coil diameter of the second spring 13 is set to be equal to the center diameter of the annular groove 16 of the plate 14.

The plate 14 is disc-shaped, and has an annular groove 16 having a V-shaped cross section for accommodating the end portion of the second spring 13. Further, the plate 14 is inserted into the step portion 52 through a hole provided at the center, and the valve 6 is sandwiched between the plate 6 and the washer 15 by the urging force of the second spring 13. Further, the diameter dimension D1 on the inner peripheral side of the groove 16 is larger than the outer diameter dimension D2 of the step portion 51 of the plunger 5, and the outer diameter dimension D2 of the step portion 51 of the plunger 5 and the strand of the second spring. It is configured to be smaller than the combination of the wire diameter dimension D3. That is, the following relational expressions are satisfied.
D2<D1<D2+D3

The washer 15 has a disk shape and is fixed to the tip of the plunger 5 on the protruding side by caulking or the like. Further, the washer 15 sandwiches the valve 6 with the plate 14 by the urging force of the second spring 13.

Next, the operation of the solenoid valve thus configured will be described with reference to FIGS.
As shown in FIG. 1B, the excessively compressed intake air flowing through the intake passage 102 flows into the intake bypass passage 103 branching from the intake passage 102, and the upstream side of the turbocharger 101 is opened and closed by opening and closing the solenoid valve 1. To be missed. As shown in FIG. 2A, in the electromagnetic valve 1, when the power is off, the valve 6 is applied to the valve seat 12 provided in the housing 7 of the intake bypass passage 103 by the urging force of the first spring 4. In contact with each other, the intake bypass passage 103 is closed. At this time, the inflowing inflow flows into the pressure balancing chamber 11 through the communication hole 10 and is balanced. That is, the pressure difference between the inflow side and the pressure balance chamber 11 side is canceled. As a result, the load on the first spring 4 is reduced. As shown in FIG. 2B, the electromagnetic valve 1 pulls the plunger 5 against the urging force of the first spring 4 by the electromagnetic attraction force of the coil 2 and the core 3 in the state where the power is ON, and the valve 6 is turned on. The intake bypass passage 103 is opened apart from the valve seat 12. As a result, the inflowing intake air flows through the intake bypass passage 103 as bypass air and is escaped to the upstream side of the turbocharger 101.

As shown in FIGS. 3, 4 and 5, the valve 6 is attached to the plunger 5 with play and is biased by the second spring 13 via the plate 14 to the washer 15. .. Therefore, even if the valve 6 is seated on the valve seat 12 with an inclination with respect to the axis of the plunger 5, the play is corrected by the elastic force of the spring.
Further, the plate 14 is formed with an annular groove 16 having a V-shaped cross section, in which one end of the second spring 13 abuts and is housed. As a result, the pressure of the intake air flowing through the intake bypass passage 103 suppresses the movement of the second spring 13 by the groove 16 even when the valve 6 is opened and closed while being tilted or rotated in the circumferential direction.
Further, the inner peripheral diameter dimension D1 of the groove 16 is larger than the outer diameter dimension D2 of the step portion 51 of the plunger 5, and the outer diameter dimension D2 of the step portion 51 of the plunger 5 and the strand of the second spring are equal to each other. It is configured to be smaller than the combination of the wire diameter dimension D3. As a result, even when the second spring 13 moves, the second spring 13 remains in the inclined portion of the groove 16 and the movement of the second spring 13 is restricted. Therefore, contact between the second spring 13 and the plunger 5 is avoided.

As described above, in the solenoid valve shown in the first embodiment, the plate 14 has an annular groove having a V-shaped cross section in which one end of the second spring 13 abuts and is housed. 16, the inner diameter of the groove 16 on the inner peripheral side is larger than the outer diameter dimension D2 of the step portion 51 of the plunger 5, and the outer diameter dimension D2 of the step portion 51 of the plunger 5 and the second spring It was made smaller than a combination of the wire diameter dimension D3 of the strand. As a result, the movement of the second spring 13 is suppressed, and at the same time, the movement of the second spring 13 is restricted by staying in the inclined portion of the groove 16. As a result, it is possible to prevent the second spring 13 from coming into contact with the plunger 5 and being worn, and it is possible to stabilize the performance and improve the durability.

Further, since the groove 16 is formed in a V shape in cross section, the strand of the second spring is centered because the cross section of the wire is circular. As a result, the position of the second spring can be stabilized, and the performance can be stabilized.

Further, since the groove 16 is formed in a V-shaped cross section, it has an effect that it can be easily processed.

In the first embodiment described above, the groove 16 has a V-shaped cross section, but as shown in FIG. 6, the groove 16b formed in the plate 14b may have an arc-shaped cross section.

Even in the groove 16b configured in this manner, the movement of the second spring 13 is suppressed, and the movement is restricted by staying in the arc portion of the groove 16. As a result, it is possible to prevent the second spring 13 from coming into contact with the plunger 5 and being worn, and it is possible to stabilize the performance and improve the durability.
Further, since the groove 16b has an arc-shaped cross section, the strand of the second spring is centered because the wire has a circular cross section. As a result, the position of the second spring can be stabilized, and the performance can be stabilized.
Further, in the groove 16b, since the cross section is continuously formed in an arc shape, the dimensional error in the radial direction is absorbed. As a result, it is possible to reduce the processing accuracy of the components that form the solenoid valve 1 and to perform the processing easily.

By the way, the solenoid valve shown in the above-described embodiment is described as an air bypass valve for adjusting the flow rate of the intake bypass passage, which is provided for adjusting the supercharging pressure of the intake passage in the engine equipped with the turbocharger. However, it is needless to say that the flow rate is not limited to the air bypass valve, and the flow rate of the fluid different from the intake air may be adjusted.

Further, in the present invention, within the scope of the invention, it is possible to freely combine the respective embodiments, modify any of the constituent elements of each of the embodiments, or omit any constituent element of each of the embodiments. ..

The solenoid valve of the present invention can be used as an air bypass valve that controls the flow rate of the intake bypass passage of the turbocharger system.

1 solenoid valve, 2 coils, 3 cores, 4 first springs, 5 plungers, 6 valves, 7 housings, 8 bolts, 9 connectors, 10 communication holes, 11 pressure balancing chambers, 12 valve seats, 13 second springs, 14, 14b plate, 15 washer, 16, 16b groove, 51, 52 step portion, 61 wall portion, 100 turbocharger system, 101 turbocharger, 102 intake passage, 103 intake bypass passage, 104 exhaust passage, 105 throttle valve, 106 wastegate Valve, D1 groove inner diameter side, D2 plunger step outside diameter, D3 second spring wire diameter

Claims

A cylindrical core that is excited by energizing the coil to generate a magnetic attraction force,
A first spring that produces a biasing force in a direction opposite to the magnetic attraction force;
A cylindrical plunger that moves in the axial direction of the core by the magnetic attraction force and the biasing force,
A cylindrical valve provided at one end on the protruding side of the plunger, which opens and closes a fluid passage by the movement of the plunger,
A disc-shaped plate sandwiched between the valve and the plunger,
A second spring formed of a coil spring that biases the plate and the plunger;
The plate has a groove for accommodating the second spring, and an inner diameter of the groove is larger than an outer diameter of the plunger in a portion where the second spring is loosely fitted, and the outer diameter of the plunger is larger than the outer diameter of the plunger. And a wire diameter of the second spring, which is smaller than a combination thereof.
The solenoid valve according to claim 1, wherein the groove has a V-shaped cross section.
The solenoid valve according to claim 1, wherein the groove has an arc-shaped cross section.
The solenoid valve according to any one of claims 1 to 3 is an air bypass valve that controls a flow rate of an intake bypass passage of an engine equipped with a turbocharger.