WO2020129236A1 - Électrovanne - Google Patents

Électrovanne Download PDF

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Publication number
WO2020129236A1
WO2020129236A1 PCT/JP2018/047232 JP2018047232W WO2020129236A1 WO 2020129236 A1 WO2020129236 A1 WO 2020129236A1 JP 2018047232 W JP2018047232 W JP 2018047232W WO 2020129236 A1 WO2020129236 A1 WO 2020129236A1
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WO
WIPO (PCT)
Prior art keywords
plunger
spring
valve
groove
solenoid valve
Prior art date
Application number
PCT/JP2018/047232
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English (en)
Japanese (ja)
Inventor
永見　哲郎
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/047232 priority Critical patent/WO2020129236A1/fr
Priority to JP2020561115A priority patent/JP6843316B2/ja
Publication of WO2020129236A1 publication Critical patent/WO2020129236A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid

Definitions

  • 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.
  • 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.
  • 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.
  • 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
  • FIG. 2B shows the valve state
  • FIG. 2B shows the open state of the solenoid valve.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the plunger 5 of the solenoid valve 1 is projected by the urging force of the first spring 4 when the power is off.
  • 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.
  • 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.
  • 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.
  • the operation of the solenoid valve thus configured will be described with reference to FIGS.
  • 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.
  • the solenoid valve 1 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.
  • the pressure difference between the inflow side and the pressure balance chamber 11 side is canceled.
  • the load on the first spring 4 is reduced.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the groove 16 is formed in a V-shaped cross section, it has an effect that it can be easily processed.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

La présente invention concerne une électrovanne présentant une performance stable et permettant d'améliorer la durabilité. Cette électrovanne est pourvue d'un noyau cylindrique (3) qui génère une force magnétique d'attraction au moyen d'une excitation magnétique résultant de l'excitation d'une bobine (2), un premier ressort (4) pour générer une force de poussée dans la direction opposée à la force d'attraction magnétique, un piston en forme de colonne (5) qui se déplace dans la direction axiale du noyau (3) au moyen de la force magnétique d'attraction et de la force de poussée, une soupape cylindrique (6) qui est disposée à une extrémité du piston (5), sur un côté en saillie dudit piston, et qui ouvre et ferme un passage de fluide au moyen du mouvement du piston (5), une plaque en forme de disque (14) prise en sandwich entre la soupape (6) et le piston (5), et un second ressort (13) constitué d'un ressort hélicoïdal qui sollicite la plaque (14) et le piston (5), la plaque (14) présentant une rainure (16) recevant le second ressort (13), et la rainure (16) étant formée de telle sorte qu'un diamètre côté circonférentiel interne (D1) de la rainure (16) est supérieur à un diamètre externe (D2) d'une partie du piston (5) sur laquelle le second ressort (13) s'ajuste de manière lâche, et est inférieur à la somme du diamètre externe (D2) du piston (5) et d'un diamètre de fil (D3) du second ressort (13).
PCT/JP2018/047232 2018-12-21 2018-12-21 Électrovanne WO2020129236A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2018/047232 WO2020129236A1 (fr) 2018-12-21 2018-12-21 Électrovanne
JP2020561115A JP6843316B2 (ja) 2018-12-21 2018-12-21 電磁弁

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/047232 WO2020129236A1 (fr) 2018-12-21 2018-12-21 Électrovanne

Publications (1)

Publication Number Publication Date
WO2020129236A1 true WO2020129236A1 (fr) 2020-06-25

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ID=71102695

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/047232 WO2020129236A1 (fr) 2018-12-21 2018-12-21 Électrovanne

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JP (1) JP6843316B2 (fr)
WO (1) WO2020129236A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5956270U (ja) * 1982-10-02 1984-04-12 有山　勲 分岐栓
JP2008157352A (ja) * 2006-12-22 2008-07-10 Smc Corp 電磁弁
JP2015081632A (ja) * 2013-10-22 2015-04-27 株式会社不二工機 パイロット型制御弁

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5956270U (ja) * 1982-10-02 1984-04-12 有山　勲 分岐栓
JP2008157352A (ja) * 2006-12-22 2008-07-10 Smc Corp 電磁弁
JP2015081632A (ja) * 2013-10-22 2015-04-27 株式会社不二工機 パイロット型制御弁

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Publication number Publication date
JP6843316B2 (ja) 2021-03-17
JPWO2020129236A1 (ja) 2021-03-11

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