FR2878600A1 - SOLENOID - Google Patents

Abstract

A solenoid valve comprises a first core and a second core facing each other, and two electromagnetic coils each wrapped around one of the cores. An armature is positioned between the first core and the second core. An armature rod extends from the armature to traverse the second core. A valve member is positioned at an opposite side of the armature rod from the armature. An armature rod guide is disposed on one side of the armature that corresponds to the valve member. The reinforcement rod guide extends from the second core toward the valve member. The reinforcing rod extends through the reinforcing rod guide and is supported by it. As a result, the size of a solenoid valve along the valve axis is reduced.

Description

1 2878600

SOLENOID

  BACKGROUND OF THE INVENTION The present invention relates to a solenoid valve that controls an electromagnetic force in two cores by activating an electromagnetic coil to activate a reinforcement between the two cores, thereby causing a reinforcing rod to move and a valve element to open and close an orifice.

  For example, Japanese Patent Laid-open Publication No. 2002-371 810 discloses a direct acting valve train for rotating a valve cam, wherein an airtight clearance adjuster is positioned. within a coil spring with a retainer so that the length along the valve axis is reduced.

  The solenoid valve comprises two cores and an armature. The armature is moved between the cores and along the valve shaft to displace an armature rod, so that a valve member opens and closes an orifice. In this configuration, the armature rod must be reliably supported. As a result, two support members such as bushings are positioned at positions furthest apart from each other.

  The valve lift of the solenoid valve stem is detected by a valve lift sensor at the proximal portion of the armature, which is opposed to the valve member. However, because the valve lift sensor is positioned at a position that is further outside the support members such as bushings, the valve lift sensor is positioned at a position which is outside the two sockets, the distance between them is maximized along the valve axis. As a result, it is difficult to reduce the size of the solenoid valve along the valve axis.

  Similarly, to open and close an orifice with a valve element, two coil springs may be provided on the valve shaft, and the retaining elements receiving the ends of the coil springs must be provided on the valve shaft. This configuration makes it difficult to reduce the size of the solenoid valve along the valve axis.

  SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to reduce the size of a solenoid valve along the valve axis.

  In order to achieve the above-mentioned object, the present invention provides a solenoid valve comprising a first core and a second core facing each other. The solenoid valve comprises two electromagnetic coils each wrapped around one of the cores. An armature is positioned between the first core and the second core. An armature rod extends from the armature to traverse the second core. A valve member is positioned at an opposite side of the armature rod from the armature. The value of the electric current applied to the electromagnetic windings is controlled so that the armature is moved between the first core and the second core, whereby the armature moves along its axis to actuate the electromagnetic element. valve. An armature rod guide is provided on one side of the armature that corresponds to the valve element. The reinforcement rod guide extends from the second core to the valve member. The reinforcing rod extends through the reinforcing rod guide and is supported by it.

  The present invention further provides a solenoid valve comprising a first core and a second core facing each other and two electromagnetic coils each wrapped around one of the cores. An armature is positioned between the first core and the second core. An armature rod extends from the armature to traverse the second core. An element is positioned at an opposite side of the reinforcing rod from the armature. The value of the electric current applied to the electromagnetic windings is controlled so that the armature is moved between the first core and the second core, whereby the armature moves along its axis to actuate the electromagnetic element. valve. A first retainer is provided at a distal end of the armature rod. A second retaining member is provided at one end of the valve member which is facing the distal end of the armature. A first coil spring is positioned between the first retainer and the second core. The first coil spring biases the armature rod towards the valve member. The second retainer receives an end of a second coil spring that biases the valve member toward the armature rod. The second retaining member has an inner receiving portion 2878600 positioned within the second coil spring. The inner receiving portion has a receiving space that receives at least a portion of the first retainer.

  Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

  The invention, in conjunction with its objects and advantages, may be better understood by reference to the following description of the presently preferred embodiments in association with the accompanying drawings, in which: FIG. 1 is a cross-sectional view illustrating Fig. 2 is an enlarged cross-sectional view showing the solenoid valve shown in Fig. 1; Figs. 3 (A) and 3 (B) are diagrams showing a structure using a device. In the first embodiment of the invention, FIGS. 4 (A) and 4 (B) are schematic diagrams illustrating a structure using a compression type game adjuster in the first embodiment. Embodiment, Figs. 5 (A) and 5 (B) are schematic diagrams showing a structure using another compression type game adjuster in the first Embodiment 6 (A) and 6 (B) are schematic diagrams showing a structure employing a mechanical clearance adjuster in the first embodiment. FIG. 7 is an enlarged cross-sectional view illustrating a solenoid valve. according to a second embodiment, and Fig. 8 is an enlarged cross-sectional view illustrating a solenoid valve according to a third embodiment.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS

  Figure 1 is a cross-sectional view illustrating a solenoid valve 2 according to a first embodiment, used in a multi-cylinder internal combustion engine. Figure 2 is an enlarged cross-sectional view illustrating the solenoid valve 2. In the drawings, a retainer (described below) and a mechanism within the retainer are shown in cross-sections. except for a spring. Other embodiments are illustrated in the same way in the corresponding drawings.

  The solenoid valve 2 comprises an electromagnetic drive unit 4 and a valve element 6 intended to selectively open an inlet orifice or an exhaust orifice provided on a cylinder head H. The electromagnetic drive unit 4 is housed in a housing 8. The housing 8 comprises an upper housing member 10 and a lower housing member 12.

  An actuator portion 20 is housed in the housing 8.

  Except for the upper surface and the lower surface, the actuator portion 20 is covered with a resin mold portion 20a. The internal structure of the actuator portion 20 is integrated. The actuator portion 20 includes a first core, which is an upper core 22, and a second core, which is a lower core 24. The cores 22, 24 have vertical through-holes 22a, 24a in central portions, respectively.

  An armature rod 32 of a frame 30 is inserted into the through hole 22a of the upper core 22 from below. In particular, the reinforcing rod 32 is inserted into the through-hole 22a from the proximal portion (upper portion as seen in FIG. 1) of the armature rod 22. The core 32a intended to detect the linear displacement of the armature 30 is attached to the proximal end of the armature rod 32. A valve lift sensor 34 is attached to the through hole 22a of the upper core 22. The valve lift sensor 34 includes a linear displacement sensing coil (corresponding to an actuating amount detecting section, or sensing element) 34a, which is inserted into the through hole 22a from above. The linear displacement sensing core 32a attached to the armature rod 32 is inserted into the linear displacement sensing coil 34a. The valve lift sensor 34 detects the actuation value of the armature rod 32 through the displacement amount of the linear displacement sensor 2878600 32a in the through hole 22a, thereby detecting the lift of valve of the valve member 6 via the sensed actuation amount.

  A proximal portion of a cylindrical reinforcing rod guide 36 is inserted into the through hole 24a of the lower core 24. The lower housing member 12 has an insertion hole in which the armature rod 32 is inserted. The reinforcement rod guide 36 is inserted into the insertion hole of the lower housing member 12. The distal portion of the reinforcement rod guide 36 (lower portion as seen in FIG. the bottom from the through hole 24a. That is, the reinforcement rod guide 36 extends from the lower core 24 to the valve member 6. The reinforcing rod 32 is received by the reinforcing rod guide 36. This structure eliminates the need for support members such as sockets in each of the upper core 22 and the lower core 24, while allowing the entire frame 30 to be accurately guided by the reinforcing rod guide 36 along the valve shaft. The armature 30 has a guide hole 30a positioned at a position remote from the armature rod 32. A rotation limiting shaft 30b is inserted into the guide hole 30a. The rotation limiting axis 30b is attached to the resin mold portion 20a while being held parallel to the through holes 22a, 24a. This structure prevents the armature 30 from rotating relative to the cores 22, 24 when the armature 30 is actuated.

  An upper retainer (first retainer) 38 is attached to the distal end of the armature rod 32. A spring seat 40 is disposed on the lower surface of the lower casing member 12. A top spring (first coil spring) 42 is disposed between the upper retainer 38 and the spring seat 40. The upper spring 42 biases the armature rod 32 toward the valve member 6.

  A lower retainer (second retainer) 44 is attached to the proximal end (the upper end) of a valve stem 6a of the valve member 6, which proximal end faces the distal end. of the armature rod 32. A lower spring (second coil spring) 46 is positioned between the lower retainer 44 and the cylinder head H. This structure biases the valve stem 6a toward the armature 30.

  An inner receiving portion, or a cylindrical proximal portion 44a, of the lower retaining member 44 is positioned within a proximal portion (upper portion) of the lower spring 46. A receiving space 44b is defined at the bottom inside of the proximal portion 44b. A clearance adjuster 48 is positioned at the lower portion of the receiving space 44a and between the armature rod 32 and the valve stem 6a. Because there is no oil to be supplied to the slack adjuster 48 from the outside, the slack adjuster 48 operates smoothly in the receiving space 44b. A slack adjuster 48 may be a circulation type sealed slack adjuster 8, a compression type slack adjuster, or a slack adjuster.

  As an oil-flow type sealed clearance adjuster, a sealed hydraulic clearance adjuster disclosed in Japanese Patent Publication No. 2002-371810 can be used. For example, as shown in Fig. 3 (A), a circulating type sealed clearance adjuster 8 may be used. The slack adjuster 48 includes a plunger body 60 having a cylindrical circumferential wall, and a plunger 62. The plunger body 60 is filled with oil, and the plunger 62 slides along the axial valve direction. A pressure chamber 64 is defined between the plunger 62 and the lower portion of the plunger body 60. A plunger spring 66 is provided in the pressure chamber 64 to bias the plunger 62 in a direction increasing the volume of the pressure chamber. 64, or in the direction of the armature rod 32.

  A protrusion 68 is formed on the upper surface of the plunger 62. The protrusion 68 slides in an upper opening 60a of the plunger body 60 while preventing oil leakage. Similarly, the distal end (the lower end) of the armature rod 32 is inserted into the upper opening 60a and comes into contact with the protuberance 68.

  An oil passage 70 is formed in the plunger 62 to connect the pressure chamber 64 to a reservoir chamber 72 located above the plunger 62. A seat surface 70a provided at the opening of the passageway is provided. 70 in the pressure chamber 64 receives a non-return ball 74. The distance between the non-return ball 74 and the seat surface 70a is limited by a retaining element 76. As a result, when the pressure in the pressure chamber 64 is greater than the pressure in the reservoir chamber 72, the non-return ball 74 comes into contact with the seat surface 70a as shown in FIG. 3 (B) and closes the oil passage 70. By therefore, the oil is prevented from moving from the pressure chamber 64 to the reservoir chamber 72 through the oil passage 70.

  A sub-tank chamber 78 is defined above the plunger body 60. The sub-tank chamber 78 is partially defined by a rubber wall 80. The volume of the sub-tank chamber 78 is varied according to at the expansion and contraction of the rubber wall 80. Through holes 60b are formed in the plunger body 60 to allow the oil to move between the reservoir chamber 72 and the sub-tank chamber 78.

  The free space between the armature rod 32 and the valve stem 6a can be varied due to variations in engine temperature, manufacturing tolerances, and component wear. Such variations in the free space between the armature rod 32 and the valve stem 6a are absorbed by the displacement of the plunger 62 in the axial valve direction in the plunger body 60. As a result, the noise produced by a collision during the actuation of the solenoid valve 2 is prevented.

  For example, when the free space between the armature rod 32 and the valve stem 6a is reduced, the holding pressure applied to the clearance adjuster 48 by the valve stem 6a and the armature rod 32 is increased. As a result, the pressure in the pressure chamber 64 is increased to a value greater than the pressure in the reservoir chamber 72.

  As a result, as shown in FIG. 3 (B), the check ball 74 comes into contact with the seat surface 70a to close the oil passage 70. At this time, the oil in the chamber 2878600 pressure 64 progressively escapes to the reservoir chamber 72 between the plunger 62 and a sliding surface 82 of the plunger body 60. This moves the plunger 62 toward the valve stem 6a to absorb the reduction of the free space between the armature rod 32 and the valve stem 6a. In this case, the volume of oil that is displaced from the reservoir chamber 72 to the sub-tank chamber 78 through the through hole 60b corresponds to the volume of a portion of the protrusion 68 that enters the body. of diver 60.

  When the free space between the armature rod 32 and the valve stem 6a is increased, the holding pressure applied to the clearance adjuster 48 by the valve stem 6a and the armature rod 32 is decreased. Then, the force of the plunger spring 66 decreases the pressure in the pressure chamber 64, thus the pressure in the pressure chamber 64 is decreased to a lower value than the pressure in the reservoir chamber 72. As shown in FIG. (A), the check ball 74 separates from the seat surface 70a to open the oil passage 70. As a result, the force of the plunger spring 66 brings the oil into the reservoir chamber 72 at flow rapidly to the pressure chamber 64 through the oil passage 70. At the same time, the plunger 62 is moved toward the armature rod 32 to absorb the increase in free space between the reinforcement rod 32 and the valve stem 6a. In this case, the volume of oil corresponding to the volume of a portion of the protrusion 68 that is retracted from the plunger body 60 is moved from the sub-tank chamber 78 to the reservoir chamber 72 through the hole crossing 60b.

  As a compression type game adjuster, a game adjuster disclosed in Japanese Patent Publication No. 2003-166406 may be used. For example, as shown in Fig. 4 (A), a compression type clearance adjuster 148 may be used. The game adjustment device 148 comprises two bases 150, 152, which generally have the same shape. A spring 154 is positioned between the bases 150, 152 to urge the bases 150, 152 away from each other.

  A recess 150a is formed on the upper surface of the upper base 150 to receive the distal end (lower end) of the armature rod 32. The proximal end (upper end) of the valve stem 6a comes into contact 5 with the lower surface of the lower base 152.

  The protuberances 156, 158, which face each other, are formed in central portions of the bases 150, 152, respectively. Opposite surfaces 156a, 158a are formed on the distal ends of the protuberances 156, 158, respectively. A cylindrical rubber wall 160 is formed to surround opposite surfaces 156a, 158a. The upper end and the lower end of the cylindrical rubber wall 160 are attached to the upper base 150 and the lower base 152, respectively, while preventing oil leakage. As a result, a tightly closed viscous fluid chamber 162 is defined between the protuberances 156, 158. A viscous fluid (fluid having a high viscosity) such as grease or oil fills the viscous fluid chamber 162 .

  The free space between the armature rod 32 and the valve stem 6a can be varied due to variations in engine temperature, manufacturing tolerances, and component wear. In such a case, the spring 154 causes the upper base 150 to come into contact with the armature rod 32 and the lower base 152 to come into contact with the valve stem 6a. As a result, variations in the free space between the armature rod 32 and the valve stem 6a are absorbed, and noise produced by the collision during actuation of the solenoid valve 2 is prevented.

  For example, when the free space between the armature rod 32 and the valve stem 6a is reduced, the holding pressure applied to the clearance adjuster 148 by the valve stem 6a and the armature rod 32 is increased. As a result, the spring 154 is compressed, and the distance between the upper base 150 and the lower base 152 is reduced. This absorbs the reduction in free space between the armature rod 32 and the valve stem 6a. At this moment, the two protuberances 156, 158 approach one another. However, because the cylindrical rubber wall 160, which surrounds the viscous fluid chamber 162, is deformed outwardly, the viscous fluid in the viscous fluid chamber 162 is displaced towards 2878600 a space formed by the deformation around the viscous fluid chamber 162. protuberances 156, 158.

  When the free space between the armature rod 32 and the valve stem 6a is increased, the holding pressure applied to the clearance adjuster 148 by the valve stem 6a and the armature rod 32 is decreased. As a result, the spring 154 becomes longer and the distance between the upper base 150 and the lower base 152 is increased. This absorbs the increase in free space between the armature rod 32 and the valve stem 6a. At this moment, the distance between the protuberances 156, 158 increases. However, because the rubber wall 160 is deformed inward, the increase in volume between the opposed surfaces 156a, 158a is taken into account even if the amount of viscous fluid of the viscous fluid chamber 162 is constant.

  When the valve member 6 opens the inlet port or the exhaust port, the viscous fluid chamber 162 operates as described below. When the electromagnetic drive unit 4 is controlled so that the armature 30 pushes the armature rod 32 downwards, the force of the lower spring 46 which acts to push the valve stem 6a upward is increased. when the armature rod 32 is moved down. Therefore, the upper base 150 approaches the lower base 152 while compressing the spring 154, so that the volume between the opposed surfaces 156a, 158a begins to decrease. The reduction in volume between the opposed surfaces 156a, 158a is absorbed by an outward deformation of the rubber wall 160.

  When the volume between the opposed surfaces 156a, 158a is reduced and the viscous fluid is compressed out of the gap between the opposed surfaces 156a, 158a as described above, the fluid friction force of the viscous fluid, or the force compression, is generated. The compressive force is increased when the distance between the opposed surfaces 156a, 158a is reduced. Therefore, when the protuberance 156 comes into contact with the protuberance 158 as shown in Fig. 4 (B), the relative velocity is rapidly reduced. Thus, a collision between the protuberances 156a, 158a is absorbed. As a result, collision noise is significantly reduced. Since the use of such a compressive force allows a compact structure to generate a large force, the size and weight of the slack adjuster 148 can be reduced.

  While the armature 30 raises the armature rod 32 when the valve member 6 closes the intake port or the exhaust port, the spring force 154 and the resilient restoring force of the wall Rubber 160 returns the viscous fluid to the gap between opposing surfaces 156a, 158a.

  Fig. 5 (A) illustrates another example of a compression type game adjuster. The game adjuster 248 comprises two bases 250, 252, which generally have the same shape. A metal bellows 254 is positioned between the bases 250, 252 to connect the bases 250, 252 to each other. The bellows 254 is welded to the peripheral portions of the bases 252, 252 so that a sealed fluid chamber 256 is defined therein. A viscous fluid 256a, such as grease and oil, and a gas 256b, such as air and nitrogen, are sealed in the fluid chamber 256. The gas 256b solicits the bases 250, 252 to discard them.

  A recess 250a is formed on the upper surface of the upper base 250 to receive the distal end of the armature rod 32. The proximal end of the valve stem 6a engages the lower surface of the lower base 252 .

  Protuberances 258, 260 are formed opposite each other in central portions of the bases 250, 252, respectively. The opposing surfaces 258a, 260a are formed on the distal ends of the protuberances 258, 260, respectively. The ratio of the viscous fluid 256a and the gas 256b in the fluid chamber 256 is adjusted so that the viscous fluid 256a always exists in the space between the opposed surfaces 258a, 260a.

  The free space between the armature rod 32 and the valve stem 6a can be varied due to variations in engine temperature, manufacturing tolerances, and component wear. In such a case, the pressure of the gas 256b causes the upper base 250 to come into contact with the armature rod 32 and the lower base 252 to come into contact with the valve stem 6a. As a result, variations in the free space between the armature rod 32 and the valve stem 6a are absorbed, and the noise produced by a collision during actuation of the solenoid valve 2 is prevented.

  For example, when the free space between the armature rod 32 and the valve stem 6a is decreased, the holding pressure applied to the clearance adjuster 248a by the valve stem 6a and the armature rod 32 and increased. Therefore, the gas 256b is compressed to compress the viscous fluid 256a between the opposed surfaces 258a, 260a, so that the bellows 254 is compressed along the valve axis. As the distance between the upper base 250 and the lower base 252 is reduced, the reduction in free space between the armature rod 32 and the valve stem 6a is absorbed.

  When the free space between the armature rod 32 and the valve stem 6a is increased, the holding pressure applied to the clearance adjuster 248 by the valve stem 6a and the armature rod 32 is decreased. As a result, the gas 256b expands so that the viscous fluid 256a enters the gap between the opposing surfaces 258a, 260a. The bellows 254 extends along the valve axis so that the distance between the upper base 250 and the lower base 252 is increased to absorb the increase in free space between the armature rod 32 and the rod valve 6a.

  When the valve member 6 opens the inlet port or the exhaust port, the fluid chamber 256 operates as described below. When the electromagnetic drive unit 4 is controlled so that the armature 30 pushes the armature rod 32 downwards, the force of the lower spring 46 which acts to push the valve stem 6a upward is increased when the reinforcing rod 32 is moved downwards. Therefore, the upper base 250 approaches the lower base 252 while compressing the gas 256b and thus compressing the bellows 254, so that the volume between the opposed surfaces 258a, 260a begins to decrease.

  When the volume between the opposed surfaces 258a, 260a is reduced and the viscous fluid 256a is compressed out of the gap between the opposed surfaces 258a, 260a, as described above, the compression force described above is generated. Therefore, when the protuberance 258 contacts the protrusion 260 as shown in Fig. 2878600 (B), the relative velocity is rapidly reduced. Therefore, the collision between the protuberances 258, 260 is absorbed. As a result, collision noise is significantly reduced. As described above, the use of such a compressive force reduces the size and weight of the clearance adjuster 248. While the armature 30 lifts the armature rod 32 when the valve member 6 closing the inlet port or the exhaust port, the gas pressure 256b returns the viscous fluid to the gap between the opposing surfaces 258a, 260a.

  As a mechanical clearance adjuster, a game adjuster described in Japanese Patent Publication Laid-open No. 05-010 109 can be used. For example, a game adjuster 348 as shown in Fig. 6 (A) can be used. The clearance adjuster 348 has two bases 350, 352. The upper base 350 has a cylindrical wall portion 350a extending from the peripheral portion. A helical spline 350b of right-hand screw is formed on the outer circumferential surface of the wall portion 350a. The lower base 352 has a cylindrical wall portion 352a extending from the peripheral portion to receive the upper base 350. A right-hand helical spline 352b is formed on the inner circumferential surface of the wall portion 352a. The helical groove 352b engages with the helical groove 350b of the upper base 350. Thus, when the upper base 350 is rotated clockwise with respect to the lower base 352 as seen from above the distance between a convex upper surface 350c of the upper base 350 and a lower flat surface 352c of the lower base 352 is reduced. On the contrary, when the upper base 350 is rotated counterclockwise, the distance between the upper surface 350c of the upper base 350 and the lower surface 352c of the lower base 352 is increased.

  A helical torsion spring 354 is provided between the upper base 350 and the lower base 352. An upper end 354a of the torsion spring 354 is engaged with an engagement hole 350d formed in the upper base 350. The lower end 354b Coil spring of 14 2878600 torsion 354 engages with an engagement hole 352d formed in lower base 352.

  In a state where the reinforcing rod 32 comes into contact with the upper surface 350c of the upper base 350 and the valve stem 6a comes into contact with the lower surface 352c of the lower base 352, the torsion coil spring 354 generates a counterclockwise moment as seen from above. As a result, the bases 350, 352 generate an axial force to urge themselves away from each other by means of the helical torsion spring 354 and right helical splines 350b, 352b.

  The free space between the armature rod 32 and the valve stem 6a can be varied due to variations in engine temperature, manufacturing tolerances, and component wear. In such a case, the axial force due to the moment causes the upper base 350 to come into contact with the armature rod 32 and the lower base 352 to come into contact with the valve stem 6a. As a result, the variations in the free space between the armature rod 32 and the valve stem 6a are absorbed, and the noise produced by a collision during actuation of the solenoid valve 2 is prevented.

  For example, when the free space between the armature rod 32 and the valve stem 6a is reduced, the holding pressure applied to the clearance adjuster 348 by the valve stem 6a and the armature rod 32 is increased. As a result, the distance between an opposing surface 350e of the upper base 350 and an opposing surface 352e of the lower base 352 tends to be reduced. In this case, the upper base 350 is rotated in a clockwise direction counterclockwise of the torsion spring 354 at the counterclockwise moment, so that the distance between the upper base 350 and the lower base 352 is reduced. Therefore, the reduction of the free space between the armature rod 32 and the valve stem 6a is absorbed.

  When the free space between the armature rod 32 and the valve stem 6a tends to be increased, the upper base 350 is rotated counterclockwise by a counter-clockwise moment. a helical coil spring watch 354, so that the distance 2878600 between the upper base 350 and the lower base 352 is increased. Therefore, the increase of the free space between the armature rod 32 and the valve stem 6a is absorbed.

  If the electromagnetic drive unit 4 is controlled so that the armature 30 pushes the armature rod 32 downwards when the valve element 6 opens the intake port or the exhaust port, the force of the lower spring 46 which acts to push the valve stem 6a upward is increased when the armature rod 32 is moved down. Therefore, the upper base 350 is rotated clockwise about the valve axis and approaches the lower base 352. At this time, the distance between the opposing surfaces 350e, 352e is reduced, and the opposing surfaces 350e, 352e come into contact with each other finally as shown in Figure 6 (B). The relative speed, when the surfaces 350e, 352e come into contact with each other, is sufficiently reduced by the resistance due to the clockwise moment of the helical torsion spring 354, the force components and friction caused by the helical splines 352, 352b, and the frictional force between the armature rod 32 and the upper surface 350c of the upper base 350.

  As a result, the collision between the opposing surfaces 350e, 352e is absorbed, and the collision noise is significantly reduced. When the armature 30 raises the armature rod 32 when the valve member 6 closes the intake port or the exhaust port, the torsion coil spring 354 increases the distance between the opposing surfaces 350e, 352e .

  As shown in an enlarged partial view of FIG. 2, in the solenoid valve 2, the inner diameter Rds of the lower spring 46, the outer diameter Rdro of the lower retaining element 44 (proximal portion 44a), the inner diameter Rdri of the lower retaining element 44 (proximal portion 44a), the outer diameter Rur of a spring seat 38a of the upper retaining element 38, and the outer diameter Rus of the upper spring 46 satisfy the following expression 1.

  16 2878600 [Expression, 1] Rds> Rdro> Rdri> Rur, Rus According to the relation represented by the expression 1, a part of the upper retaining element 38, which comprises at least the spring seat 38a in this mode embodiment, is positioned in the receiving space 44b.

  In this state, as shown in FIG. 1, the supply of a drive current from the control unit to the coils 52, 54 through the connector 50 actuates the armature 30 in the axial valve direction. The driving force of the armature 30 is transmitted to the valve stem 6a via the armature rod 32 and the clearance adjuster 48, 148, 248, 348 so that the valve 6 opens or closes the inlet port or the exhaust port. The valve lift of the valve member 6 is detected by the lift sensor 34 when the linear displacement sensing core 32a is moved into the linear displacement sensing coil disposed in the through hole 22a of the upper core 22.

  The first embodiment described above has the following advantages.

  (1) Since the reinforcing rod guide 36 is disposed in the lower core 24 at the side of the valve member 6, the armature rod 32 is reliably supported by the rod guide. As a result, the upper core 22 at the side opposite the valve member 6 does not need to have a support member such as a socket. From the point of view, no socket is provided. Thus, the linear displacement detection coil 34a of the lift sensor 34 is introduced into the through hole 32a of the upper core 22.

  This allows the lift sensor 34 to be positioned near the valve member 6. Therefore, it is easily prevented that the axial dimension of the solenoid valve 2 increases.

  (2) In the solenoid valve 2 having two coil springs (the upper spring 42 and the lower spring 46), the proximal portion 44a of the lower retainer 44 is positioned in the proximal portion (upper portion) of the lower spring 46 The portion of the upper retainer 38 is positioned in the receiving space 44b defined in the cylindrical proximal portion 44a.

  Accordingly, in comparison with the case where the upper retainer 38 and the lower retainer 44 simply come into contact with each other with respect to the axial valve direction and a case where the upper retaining element 38 and the lower retaining element 44 separate completely from one another, the axial dimension of the solenoid valve 2 is reduced by the length of the portion of the upper retaining element 38 which is inserted into the receiving space 44b defined in the proximal portion 44a of the lower retainer 44.

  As a result, it is also easily prevented that the axial dimension of the solenoid valve 2 is increased.

  (3) The clearance adjuster 48, 148, 248 or 348 is positioned between the armature rod 32 and the valve member 6.

  Since the clearance adjusting device 48, 148, 248 or 348 is thus arranged in the solenoid valve 2, the noise during the actuation of the solenoid valve 2 is reduced even if the pusher clearance is eliminated to simplify the control. Valve.

  Further, because the slack adjuster 48, 148 248 or 348 is positioned in the receiving space 44b defined in the proximal portion 44a of the lower retainer 44 with a portion of the retainer higher 38, it is further easily prevented that the axial dimension of the solenoid valve 2 increases.

  (4) As described above, a slack adjuster of the oil circulation type (Fig. 3) is used as a slack adjuster 48. In other cases, a slack adjuster compression type 148 or 248 (FIGS. 4 and 5), or a mechanical clearance adjuster 348 (FIG. 6) is used. These clearance adjusters 48, 148, 248 or 348 do not require any new oil filling. This increases the flexibility of the arrangement and thus facilitates the installation of the clearance adjusters 48, 148, 248, 348 with the solenoid valve 2. Therefore, it is easily prevented that the axial dimension of the solenoid valve 2 increases.

  Fig. 7 is an enlarged cross-sectional view illustrating a solenoid valve according to a second embodiment. The differences from the first embodiment are illustrated in Figure 7. The other 2878600 configurations are identical to those of the first embodiment.

  In this embodiment, an upper retainer 338 and a lower retainer 144 each have an inner receiving portion, or a proximal portion 138a, 144a, and receiving spaces 138b, 114b are defined in the cylindrical proximal portions. 138a, 144a respectively. The receiving spaces 138b, 144b each generally receive half of a clearance adjuster 198 except for a section corresponding to a length rc along the axial valve direction. That is, the receiving spaces 138b, 144b receive the clearance adjuster 198 from the opposite directions. Since the upper retainer 138 and the lower retainer 144 have the same shape and are arranged in opposite directions, the upper retainer 138 is not inserted into the receiving space 144b of the lower retainer 144.

  As a slack adjuster 198, any of the slack adjusters 48, 148, 248, 348 shown in Figures 3 to 6 of the first embodiment is used.

  The second embodiment as described above has the following advantages.

  (1) The proximal portion 138a of the upper retainer 138 is positioned within the distal portion (lower portion) of the upper spring 192, and the proximal portion 144a of the lower retainer 144 is positioned at the inside of the proximal portion (upper portion) of the lower spring 196. The slack adjuster 198 is positioned in the receiving spaces 138b, 144b defined in the proximal portions 138a, 144a.

  Therefore, even if the pusher clearance in the solenoid valve 2 is eliminated to simplify the valve control, the noise during the actuation of the solenoid valve 2 is reduced. Likewise, the valve dimension along the valve axis is reduced. This prevents the size of the solenoid valve 2 from increasing along the axial direction of the valve.

  (2) The same advantages as advantages (1) and (4) of the first embodiment are obtained.

  Figure 8 is an enlarged cross-sectional view illustrating a solenoid valve according to a third embodiment. The differences with respect to the first embodiment are illustrated in FIG. 8. The other configurations are the same as those of the first embodiment.

  In this embodiment, no game adjustment device is provided and the armature rod 32 and the valve stem 6a are arranged such that a pusher game tc exists between them when the valve 6 closes the inlet port or the exhaust port. An upper retainer 238 is wholly received in a receiving space 244b defined in a cylindrical proximal portion 244a, which functions as an inner receiving portion, of a lower retainer 244. When the valve member 6 opens the inlet port or the exhaust port, the armature rod 32 is brought closer to the valve stem 6a by controlling the electromagnetic force. Immediately before the armature rod 32 comes into contact with the valve stem 6a, the speed of the armature rod 32 is rapidly reduced so that no significant impact takes place. Then, the armature rod 32 is moved rapidly to open the intake port or the exhaust port. When the valve member 6 closes the inlet port or the exhaust port, immediately before the armature rod 32 separates from the valve stem 6a, i.e. immediately before that the valve member 6 does not strike the valve seat around the inlet port or the exhaust port, the speed of the armature rod 32 is rapidly reduced so that no significant impact takes place. Then, because only the armature rod 32 is moved, the pusher game tc is created as shown in FIG. 8.

  The third embodiment described above has the following advantages.

  (1) The same advantage (1) as the first embodiment is obtained.

  (2) The proximal portion 244a of the lower retainer 244 is positioned within the proximal portion (upper portion) of the lower spring 46. All of the upper retainer 238 is positioned in the 2878600 space of receiving 244b defined in the cylindrical proximal portion 244a.

  Because the upper retainer 238 is positioned in the receiving space 244b, the axial dimension of the solenoid valve 2 is reduced. In particular, since no clearance adjusting device is provided between the armature rod 32 and the valve member 6, the upper retainer 238 can be inserted deep into the receiving space 244b. .

  As a result, it is furthermore easily prevented that the axial dimension of the solenoid valve 2 increases.

  The invention can be applied to the following embodiments.

  (a) In the first embodiment, a portion of the upper retainer 38 is positioned in the receiving space 44b. However, all of the upper retainer 38 may be located in the receiving space 44b by shortening the clearance adjuster 48 in the axial valve direction or making the receiving space 44b deeper.

  In the third embodiment, the entire upper retainer 238 is received in the receiving space 244b. However, only a portion of the upper retainer 238 can be positioned in the receiving space 244b.

  (b) In the first and third embodiments as shown in Figures 1 and 8, the proximal portion 44a, 224a of the lower retainer 44, 244 is positioned within the proximal portion (upper portion ) of the lower spring 46, and a portion of the upper retainer 38, 238 is positioned in the receiving space 44b, 244b defined in the proximal portion 44a, 244a. This configuration can be reversed with respect to dimensions. That is, the proximal portion, or the inner receiving portion, of the upper retainer may be positioned within the distal (lower) portion of the upper spring, and a portion or the entire lower retaining element, i.e., at least a portion of the lower retaining element, can be positioned in the receiving space defined within the proximal portion of the element upper retainer.

  (C) In the illustrated embodiments, no bushing is provided in the through hole 22a of the upper core 22 as shown in FIG. 1. However, if there is a void space after the disposition of the lift sensor 34 in the through-hole 22, a bushing may be disposed in the space to receive the reinforcing rod 32. This further stabilizes the actuation of the reinforcing rod 32 along the axial valve direction and prevents the axial dimension of the solenoid valve 2 increases.

Claims (7)

  A solenoid valve, comprising: a first core (22) and a second core (22) facing each other, two electromagnetic coils (52, 54) each wound around one of the cores (22, 24); ), an armature (30) positioned between the first core (22) and the second core (24), an armature rod (32) extending from the armature (30) to traverse the second core (24). ), and a valve member (6) positioned at an opposite side of the armature rod (32) from the armature (30), where the electric current value applied to the electromagnetic coils (52, 54) is controlled so that the armature (30) is moved between the first core (22) and the second core (24), whereby the armature (30) moves along its axis for actuating the valve element (6), the solenoid valve being characterized in that: a first retaining element (38) is disposed at a distal end of the armature rod (32), where a seco nd retainer (44) is disposed at one end of the valve member (6) which faces the distal end of the armature (30), where a first coil spring (42) is positioned between the first retaining element (38) and the second core (24), the first coil spring (42) urging the armature rod (32) towards the valve element (6), and the second element retainer (44) receives an end of a second coil spring (46) which urges the valve member (6) toward the armature rod (32), and wherein the second retainer (44, 144 , 244) has an inner receiving portion (44a, 144a, 244a) positioned within the second coil spring (46), and wherein the inner receiving portion (44a, 144a, 244a) has a receiving space (44b , 144b, 244b) which receives at least a portion of the first retainer (38, 238).   A solenoid valve, comprising: a first core (22) and a second core (24) facing each other, two electromagnetic coils (52, 54), each wound around one of the cores (22, 24), a positioned armature (30) between the first core (22) and the second core (24), an armature rod (32) extending from the armature (30) through the second core ( 24), and a valve member (6) positioned at an opposite side of the armature rod (32) from the armature (30), where the value of the electric current applied to the electromagnetic coils (52) , 54) is controlled so that the armature (30) is moved between the first core (22) and the second core (24), whereby the armature (30) moves along its axis for actuating the valve element (6), the solenoid valve being characterized in that: a first retaining element (138) is disposed at a distal end of the armature rod (32), where a dry said retaining element (44) is disposed at one end of the valve element (6) which faces the distal end of the armature (30), where a first coil spring (42) is positioned between the first retaining element (138) and the second core (24), the first coil spring (192) urging the armature rod (32) towards the valve element (6) and the second element retainer (44) receives an end of a second coil spring (46) which urges the valve member (6) toward the armature rod (32), and wherein the first retainer (138) has a an inner receiving portion (138a) positioned within the first coil spring (192), and wherein the inner receiving portion (138a) has a receiving space (138b) that receives at least a portion of the second retainer.   The solenoid valve according to claim 1 or 2, characterized in that a slack adjuster (48, 148, 248, 348) is positioned between the reinforcing rod (32) and the valve member (6). ).   The solenoid valve according to claim 1 or 2, characterized in that a slack adjuster (48, 148, 248, 348) is positioned between the armature rod (32) and the valve member (6). , and the slack adjuster (48, 148, 248, 348) is received in the receiving space (44b, 138b, 144b).   5. Solenoid valve according to claim 3 or 4, characterized in that the slack adjuster (48, 148, 248, 348) is configured to operate without oil supplied from the outside.   The solenoid valve according to claim 5, characterized in that the slack adjuster is any one of a sealed oil-flow type slack adjuster (48), a slack adjuster compression type play (148, 248) or a mechanical play adjuster (348).   Solenoid valve according to one of Claims 1 to 6, characterized in that the solenoid valve (2) is assembled in an internal combustion engine, in which the valve element (6) selectively opens and closes an orifice intake or an exhaust port of the internal combustion engine.