JP2008064132A - Solenoid control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a solenoid control valve capable of obtaining the smooth movement by ensuring the concentricity of a spool valve of the solenoid control valve with a movable plunger, and obtaining the excellent movable responsiveness by reducing the weight of the spool valve. <P>SOLUTION: The solenoid control valve comprises an electromagnetic driving unit 37 for driving a movable plunger 42 through electric conduction, an aluminum alloy-made spool valve 38 which selectively opens/closes a plurality of ports according to the moving position in the axial direction and is moved in one direction by the driving force of the movable plunger, and a first spring member 49 for urging the spool valve from the direction opposite to the driving direction by the movable plunger. A second spring member 55 for urging the spool valve from the direction opposite to the urging direction by the first spring member is provided, opposing end faces 44a, 42a of the movable plunger and the spool valve are constantly abutted on each other from the axial direction by the opposing spring forces of the spring members to ensure the integration property and the concentricity. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an electromagnetic control valve used for, for example, a valve timing control device for an internal combustion engine that variably controls a valve lift of an engine valve on the intake side or exhaust side of the internal combustion engine according to the engine operating state.

  As this type of conventional electromagnetic control valve, for example, the one described in Patent Document 1 below is known.

  This electromagnetic control valve is provided in a cylinder head of an internal combustion engine and is used for a valve timing control device of an intake valve or an exhaust valve. A substantially bottomed cylindrical valve body and an axial direction in the valve body A spool valve movably provided, a movable plunger (movable iron core) that moves the spool valve in one direction against the spring force of the spring member, and a solenoid that drives the movable plunger by applying electromagnetic force And a so-called pull type that pulls the movable plunger toward the solenoid portion by energizing the solenoid portion.

  The spool valve and the movable plunger are integrally formed from the axial direction by, for example, welding, caulking or screwing in order to reduce the number of parts such as bearings.

Then, when the solenoid is energized, the movable plunger (movable iron core) moves in the axial direction toward the solenoid, so that the spool valve also moves in the same direction. As a result, the valve timing variable mechanism is operated by selectively opening and closing a plurality of supply / discharge ports formed in the valve body.
JP 2002-310324 A

  However, although the conventional electromagnetic control valve can reduce the number of parts by integrally connecting the spool valve and the movable plunger, when the integration is performed by welding, the spool valve is the same as the movable plunger. You must use a ferrous material to pass magnetic force. For this reason, the weight of the spool valve is inevitably increased, and the movement responsiveness in the axial direction of the spool valve is reduced due to the increase in inertial mass, and vibration may occur.

  Further, when the spool valve and the movable plunger are coupled by caulking or screwing as described above, the spool valve can be formed of a material different from that of the movable plunger. In this case, the spool valve and the movable plunger High coaxiality and cylindricity may not be obtained.

  As a result, smooth movement of the spool valve and the movable plunger cannot be obtained, and there is a possibility that the spool valve and the movable plunger may be locked.

  The present invention has been devised in view of the technical problems of the prior art, and does not directly couple the spool valve and the movable plunger by welding or the like, but utilizes an opposing biasing force from the axial direction. It is an object of the present invention to provide an electromagnetic control valve that can be formed of different materials by bringing them into contact with each other, and that does not require high coaxiality.

  According to the first aspect of the present invention, the electromagnetic drive unit that drives the movable plunger when energized, and the plurality of ports are selectively opened and closed according to the movement position in the axial direction. A spool valve that moves in a direction, and a first biasing member that biases the spool valve from a direction opposite to the driving direction by the movable plunger, and biases the spool valve from a direction opposite to the biasing direction of the first biasing member. A second urging member is provided to urge the front end edge of the movable plunger and the front end edge of the spool valve facing the front end edge.

  According to the present invention, the movable plunger and the spool valve are always brought into contact with each other from the axial direction by the urging forces of the first urging means and the second urging means in the mutually opposing directions, so that the unity and the coaxiality are achieved. In order to ensure smoothness of the spool valve, it is not necessary to integrate the movable plunger and the spool valve by special connection processing such as welding or caulking. High machining accuracy is not required.

  The invention according to claim 2 is characterized in that the spool valve is formed of a material different from the movable plunger of the iron-based material.

  Since it is possible to freely select a material other than the iron-based material for the spool valve, it becomes possible to use a low processing or low cost material. As a result, processing costs and material costs can be reduced.

  The invention according to claim 3 is characterized in that the spool valve is formed of an aluminum material or a synthetic resin material.

  According to the present invention, the weight of the spool valve can be reduced, the inertial mass can be reduced, and the operation response of the spool valve in the axial direction can be improved.

  Embodiments of an electromagnetic control valve according to the present invention will be described below in detail with reference to the drawings.

  In the first embodiment, the electromagnetic control valve is applied to a valve timing control device for a vane type internal combustion engine described in, for example, Japanese Patent Application Laid-Open No. 2006-70726 filed earlier by the present applicant.

  An outline of the valve timing control device will be described with reference to FIG. 2. A timing sprocket 1 that is rotationally driven via a timing chain by a crankshaft outside the engine of the engine, and can be rotated relative to the timing sprocket 1. A camshaft 2 provided, a phase conversion mechanism 3 disposed between the sprocket 1 and the camshaft 2 for converting the relative rotational positions of the two, and a hydraulic circuit 4 for operating the phase conversion mechanism 3; It has.

  The camshaft 2 is rotatably supported by a cylinder head (not shown) via a cam bearing, and a plurality of drive cams for opening the intake valve via a valve lifter are integrally provided at a predetermined position on the outer peripheral surface. Yes.

  The phase conversion mechanism 3 includes a housing 5 having the timing sprocket 1 disposed at one end of the camshaft 2 on the outer periphery, and is fixed to the one end of the camshaft 2 from the axial direction by the cam bolt. Four retardations each defined by a vane member 6 rotatably accommodated therein, four shoes 7 integrally formed on the inner periphery of the housing 5 and four vanes 8 of the vane member 6. An oil chamber 9 and an advance oil chamber 10 are provided.

  The housing 5 includes a front plate and a rear plate that close the front and rear opening ends, and these are integrally coupled together by four bolts 11 from the axial direction by tightening.

  Each of the shoes 7 has a substantially trapezoidal side surface, and a substantially U-shaped seal member 12 is fitted in a seal groove formed along the axial direction at each tip portion.

  The vane member 6 is integrally formed of a metal material, and the vane rotor 6a fixed to one end portion of the camshaft 2 from the axial direction by the cam bolt 13 inserted through the insertion hole formed in the center from the axial direction, and the vane rotor The four vanes 8 are provided so as to project radially at substantially equal intervals in the circumferential direction of the outer peripheral surface of 6a.

  The vane rotor 6a is rotatably supported while sliding on a seal member 12 fitted to the top surface of the tip of each shoe 7, and communicates with each retarded oil chamber 9 in the inner radial direction. Four retard angle oil holes and four advance angle oil holes (not shown) communicating with each advance oil chamber 10 are formed.

  Each of the vanes 8 is disposed between the shoes 7 and has a substantially U-shaped seal member that is in sliding contact with the inner peripheral surface of the housing 5 in a seal groove that is formed in the axial direction on each tip surface. 14 is fitted. Further, between the maximum width vane 8 and the rear plate, there is provided a lock mechanism 15 for restraining free rotation of the vane member 6 on the most retarded angle side shown in FIG.

  As shown in FIGS. 1 and 2, the hydraulic circuit 4 includes first and second hydraulic pressures that communicate with the retard angle and advance oil chambers 9 and 10 via the retard angle passages and the advance angle passages. An oil pump 31 that supplies hydraulic oil in the oil pan 35 into the oil chambers 9 and 10 through the hydraulic passages 27 and 28, and a downstream side of the oil pump 31. And an electromagnetic control valve 33 that selectively switches the hydraulic passages 27 and 28 and the drain passage 29 in accordance with a control signal from the controller 32.

  This electromagnetic control valve 33 is a pull-type direction switching valve that switches the flow between on and off, and as shown in FIG. 1, a cylindrical valve body 36 inserted and fixed inside the cylinder head, An electromagnetic drive unit 37 provided on one end side of the valve body 36 and a valve body 36 are accommodated in the valve body 36 so as to be movable (slidable) in the axial direction, and the electromagnetic drive is driven by the driving force of the electromagnetic drive unit 37. The spool valve 38 is mainly composed of a spool valve 38 that is attracted and moved by a movable plunger 42 described later to the portion 37 side.

  The valve body 36 is formed with a valve hole 39 for accommodating the spool valve 38 inside one end closed, and a supply port 36a opened to the valve hole 39 from the radial direction at a substantially central position of the peripheral wall. It has been drilled. In addition, first and second output ports 36b and 36c that open to the valve hole 39 and communicate with the hydraulic passages 27 and 28, respectively, are formed from both sides of the supply port 36a from the radial direction. In addition, a drain port 36d communicating with the oil pan 35 through the drain passage 29 is formed along the radial direction at a side portion of the second output port 36c. Further, a different drain port 36e communicating with the first output port 36b as appropriate is formed in the vicinity of the first output port 36b on the opposite side of the drain port 36d in the axial direction. The drain port 36e also communicates with the oil pan 35 through the drain passage 29. Each port is provided with a filter for filtering dust, contamination, and the like.

  The valve body 36 has a seal ring 50 that is fitted and fixed on the outer periphery of one end portion of the valve body 36 and seals between the valve body 36 and a casing 37a, which will be described later. A seal ring 51 for sealing is fixedly fitted. Further, an annular oil reservoir 52 is formed on the inner peripheral surface of the one end facing the seal ring 51, and the oil reservoir 52 and the drain port 36d are communicated with one end of the valve hole 39. An annular communication groove 53 is formed. A discharge hole 36f is formed on the bottom wall of the valve body 36 to ensure good slidability of the spool valve 38.

  The spool valve 38 is integrally formed of an aluminum alloy material instead of an iron-based material. As shown in FIGS. 1 and 3, the supply port 36a and the first and second outputs are provided on the outer peripheral surface of the valve shaft 38a. Cylindrical first to third land portions 43 to 45, which are three valve bodies that selectively open and close the ports 36b and 36c and the drain ports 36d and 36e according to their movement positions, are integrally formed at a predetermined interval. ing. A communication hole 46 communicating with the oil reservoir 52 is formed through the spool valve 38 in the inner axial direction.

  The electromagnetic drive unit 37 includes a cylindrical electromagnetic coil 40 disposed inside the casing 37a, and a substantially covered cylindrical fixed yoke 41 that is fixed to the outer end of the casing 37a and is extinguished and excited by the electromagnetic coil 40. And a movable plunger (movable iron core) 42 slidably accommodated inside the fixed yoke 41.

  The electromagnetic coil 40 is energized or de-energized on and off from the controller 32.

  The movable plunger 42 is formed in a substantially columnar shape, and a communication port 47 that is a communication means communicating with the oil reservoir 52 and the communication hole 46 is formed in the inner axial direction.

  Then, between the fixed yoke 41 and the movable plunger 42, the spool valve 38 is urged to the right in FIG. 1 via the movable plunger 42, that is, opposite to the moving direction of the excited movable plunger 42. A first spring member 49 that is a compression coil spring that is biased in the direction is provided.

  The first spring member 49 is elastically supported by a cylindrical accommodation hole 48 formed at one end side in the axial direction of the inner end portion of the fixed yoke 41 via a retainer 54, while the other end portion is movable. The plunger 42 is elastically supported on the bottom surface of the holding groove formed at one end edge of the communication port 47 of the plunger 42.

  A second spring member 55 that is a compression coil spring that urges the spool valve 38 toward the movable plunger 42 is accommodated in the bottom of the valve hole 39 in which the third land portion 45 of the spool valve 38 slides. Has been.

  One end of the second spring member 55 is held on the inner bottom surface of the third land portion 45, and the other end is held on the bottom surface of the valve hole 39.

  Then, the second land portion 44 and the movable plunger 42 of the spool valve 38 have their opposing surfaces 44a, 42a always in the axial direction by the spring force in the opposing direction of the first spring member 49 and the second spring member 55. It is biased to abut. The spring force of the first spring member 49 is set larger than the spring force of the second spring member 55.

  As shown in FIG. 4, the spring load a of the first spring member 49 increases as the spool valve 38 moves leftward in FIG. 1, whereas the spring load of the second spring member 55 increases. As b decreases, the opposing spring forces (balance load c) are set to gradually increase as shown by the thick solid line.

  Therefore, according to this embodiment, the energization from the controller 32 to the electromagnetic control valve 33 is interrupted in a predetermined low speed range from the time of engine start and the extremely low speed during idling. Accordingly, the spool valve 38 is balanced by the opposing spring force of the first spring member 49 and the second spring member 55 and held at the position shown in FIG. 1, and the first land portion 43 is connected to the supply port 36a and the second output. At the same time as the communication with the port 36c, the first land portion 43 blocks the communication between the supply port 36a and the first output port 36b, and connects the first output port 36b and the drain port 36d. Therefore, the hydraulic oil pumped from the oil pump 31 is supplied from the first hydraulic passage 27 to each retarded oil chamber 9, while the hydraulic oil in each advanced oil chamber 10 is drained from the second hydraulic passage 28. The oil is returned to the oil pan 35 through the port 36e and the drain passage 29.

  For this reason, the vane member 6 is held at the maximum left rotation position shown in FIG. 2, and the relative rotation phase of the timing sprocket 1 and the camshaft 2 is controlled to the most retarded angle side. As a result, the startability of the engine is improved and a stable rotation of the engine during idling is obtained.

  When the engine shifts from the low rotation range to the middle rotation range, which is a steady operation range, an ON signal is output from the controller 32 to the electromagnetic control valve 33 and energized, and the movable plunger 42 is excited. Therefore, the movable plunger 42 moves to the left in the maximum direction from the position shown in FIG. 1 against the spring force of the first spring member 49 while being assisted by the spring force of the second spring member 55, and the spool valve 38 is attracted and moved in the same direction.

  For this reason, the land portions 43 to 45 of the spool valve 38 allow the supply port 36a and the first output port 36b to communicate with each other, and simultaneously block the communication with the drain port 36e, while the supply port 36a and the second output port 36c. The communication between the second output port 36c and the drain port 36d is made simultaneous with the disconnection of the communication with the drain port 36d.

  Accordingly, the hydraulic pressure pumped from the oil pump 31 is supplied from the second hydraulic passage 28 into each advance oil chamber 10 to increase the internal pressure, and the hydraulic pressure in each retard oil chamber 9 is changed to the oil pan 35. It is discharged inside and the inside becomes low pressure. Thereby, the vane member 6 rotates rightward from the position of FIG. 2, and the relative rotational phase of the timing sprocket 1 and the camshaft 2 is converted to the advance side. As a result, the opening / closing timing of the intake valve is advanced, the engine combustibility is improved during the steady operation, and fuel consumption and output can be improved.

  Further, when the engine shifts to a high rotation range, an off signal is output from the controller 32 to the electromagnetic drive unit 37 and the power is not supplied. For this reason, the movable plunger 42 has a large driving force when moved to the maximum right as shown in FIG. 1 against the spring force of the second spring member 55 by the strong spring force of the first spring member 49. As described above, the spool valve 38 communicates the supply port 36a and the second output port 36c, and communicates the first output port 36b and the drain port 36e.

  As a result, the hydraulic pressure is supplied to each retarded oil chamber 9 and becomes high pressure, while the hydraulic pressure in each advanced oil chamber 10 is discharged into the oil pan 35 and becomes low pressure. However, it rotates to the maximum left as shown in FIG. 2 to control the relative rotational phase of the timing sprocket 1 and the camshaft 2 to the retard side. As a result, the opening / closing timing of the intake valve is retarded, and the engine output in such a high rotation / high load region can be improved.

  According to this embodiment, the opposing surfaces 44a and 42a of the spool valve 38 and the movable plunger 42 are always in contact with each other from the axial direction by the opposing spring force of the first spring member 49 and the second spring member 55. It becomes a state and integrity and coaxiality can be ensured. That is, since the spool valve 38 and the movable plunger 42 are pressed against each other from the axial direction by the opposing spring force of the two spring members 49 and 55, even when moving in the axial direction. The spool valve 38 moves integrally with the movable plunger 42 always in contact. For this reason, the smooth slidability of the spool valve 38 is obtained, and the movable plunger 42 and the spool valve 38 do not need to be integrated by special connection processing such as welding or caulking as in the prior art. High processing accuracy is not required to obtain high performance.

  In addition, since the spool valve 38 can be freely selected from materials other than iron-based materials, it is possible to use low processing and low cost materials. As a result, processing costs and material costs can be reduced.

  In particular, in this embodiment, since the spool valve 38 is made of an aluminum alloy material, the weight of the spool valve 38 can be reduced, the inertial mass is reduced, and the operation responsiveness in the axial direction of the spool valve 38 is reduced. It becomes possible to improve.

  Most of the hydraulic oil and air that has flowed into the accommodation hole 48 is discharged from the communication port 47 through the communication hole 46 of the spool valve 38 to the outside through the discharge hole 36f and partly movable. The oil flows into the oil reservoir 52 from the communication port 47 of the plunger 42, passes through the communication groove 53, and is discharged into the oil pan 35 through the drain port 36 d and the drain passage 29. For this reason, the mobility of the movable plunger 42 and the spool valve 38 in the axial direction is not hindered by hydraulic oil and the like, and smooth mobility can always be ensured.

  5 to 13 show various modifications of the structure of the movable plunger 42 and the spool valve 38. The structure shown in FIG. 5 is in communication with the accommodation hole 48 on the rear end face of the movable plunger 42 facing the accommodation hole 48 side. A cross-shaped groove 56 communicating with the port 47 is formed. On the other hand, in the spool valve 38, the communication hole 46 is eliminated, and a radial groove 57 that connects the communication port 47 and the oil reservoir 52 is formed in the opposed end surface 44 a.

  As a result, hydraulic oil or air that has flowed into the accommodation hole 48 or the like can be quickly discharged from the oil reservoir 52 via the communication groove 53.

  6, cross-shaped grooves 56a and 56b are formed on both front and rear end faces of the movable plunger 42. On the spool valve 38 side, shafts are provided at four locations in the circumferential direction of the outer peripheral surface of the second land portion 44. Directional grooves 58 are formed. As a result, even if the communication groove 53 is eliminated, the hydraulic oil or the like flowing into the accommodation hole 48 can be quickly discharged from the oil reservoir 52 through the axial grooves 58 to the drain port 36d.

  7 shows a cross-shaped groove 59 formed only on the opposite end face 44a side of the spool valve 38. FIG. 8 shows each of the movable plunger 42 and the second land portion 44 of the spool valve 38. Axial grooves 58 and 60 are formed on the outer peripheral surface. Further, what is shown in FIG. 9 is one in which an axial groove 60 is formed only on the outer peripheral surface of the movable plunger 42.

  In addition, what is shown in FIGS. 10 to 13 is a further different variation in the case where the outer peripheral surface of the second land portion 44 and the outer peripheral surface of the movable plunger 42 are formed in a bullet shape.

  Also in these cases, since the hydraulic oil and air in the accommodation hole 48 and the oil reservoir 52 can be quickly discharged to the outside, the movable plunger 42 and the spool valve 38 can always move smoothly.

  FIG. 14 shows the second embodiment. The basic structure is a pull-type structure as in the first embodiment, and the spool valve 38 is driven by the opposing spring force of the first spring member 49 and the second spring member 55. And the movable plunger 42 are in contact with each other from the axial direction, but the spool valve 38 is stopped at the intermediate movement position of the spool valve 38 in the left direction by the electromagnetic drive unit 37. It is a thing.

  That is, the electromagnetic control valve 33 is formed in a so-called proportional control type in which the driving force of the electromagnetic driving unit 37 is proportionally increased or decreased in accordance with the energization amount from the controller 32. A cup-shaped spring retainer 61 in which the tip end of the valve shaft 38a is slidable in the axial direction is provided in a holding groove formed at a position corresponding to the oil reservoir of the valve body 36. In addition, a third spring member 62 is elastically mounted between the front end surface of the bottom wall 61a of the spring retainer 61 and the bottom surface of the holding groove. The third spring member 62 biases the spool valve 38 in the same direction as the first spring member 62 after moving a predetermined amount in the left direction via the spring retainer 61. A clearance C having a predetermined width is formed between the inner surface of the bottom wall 61 a of the spring retainer 61 and the front end surface 44 a of the second land portion 44 of the spool valve 38.

  Therefore, when the spool valve 38 moves a predetermined amount in the left direction against the spring force of the first spring member 49 by the pulling force of the movable plunger 42, the tip end surface 44 a of the second land portion 44 contacts the bottom surface of the spring retainer 61. Touch. At this stage, the combined force with the first spring member 49 acts to temporarily stop the leftward movement of the electromagnetic drive spool valve 38.

  Thereafter, when the energization amount to the electromagnetic drive unit 37 further increases and exceeds a predetermined amount, the movable plunger 42 moves further to the left against the spring force of the first and third spring members 49 and 62. The spool valve 38 is moved in the same direction.

  More specifically, as shown in FIGS. 15A and 15B, the spool valve 38 moves in accordance with a proportional energization amount to the electromagnetic drive unit 37, but at the initial energization (I1 region), the thrust force It moves against only the spring force of the first spring member 49. Then, since the urging force of the third spring member 62 acts when the front end surface 44a of the second land portion 44 comes into contact with the bottom wall 61a of the spring retainer 61, as shown in FIG. Although the energization amount to the portion 37 rises proportionally, the spool valve 38 does not move and is held at the intermediate position (M) until the predetermined energization amount (I2) to the electromagnetic drive portion 37. . In other words, at this intermediate position, the spool valve 38 can be held at the intermediate position in a stopped state against the driving force of the electromagnetic drive unit 37 even if it is affected by a disturbance or the like.

  FIG. 16 is a characteristic diagram showing the relationship between the spring load of the first to third spring members and the amount of movement of the spool valve 38, where a is the spring force of the first spring member 49 and b is the second spring member. 55 indicates the spring force of 55, c indicates the counter load of the first and second spring members 49 and 55, and d indicates the spring force of the third spring member 62.

  As described above, when the spool valve 38 moves to the left by a predetermined amount by energization of the electromagnetic drive unit 37 and the tip end surface 44a of the second land portion 44 contacts the spring retainer 61, the third spring member 62 is moved. Therefore, if the amount of energization to the electromagnetic drive unit 37 is within the range of M shown in the drawing, the spool valve 38 is maintained in the stopped state. When the energization amount I3 is more than that, the characteristic is indicated by e by overcoming the combined spring force (a + d) of the first and third spring members 49, 62 and moving further leftward.

  Thereafter, when the energization amount to the electromagnetic drive unit 37 becomes equal to or greater than a predetermined value (I3), the increased biasing force of the first and second spring members 49 and 62 is overcome and the spool valve 38 is further moved to a desired position in one direction. Can be moved to.

  As described above, in this embodiment, the intermediate movement position of the spool valve 38 can be controlled stably and with high accuracy. As a result, the control accuracy of the valve timing of the intake valve can be improved.

  The drain port 36e can be communicated with the drain port 36d through a drain hole 36f formed in the valve body 36.

  Further, the electromagnetic control valve 33 can be applied not only to the valve timing control device but also to a device that variably controls only the intake valve or the bubble lift of both the intake valve and the exhaust valve, for example.

  FIG. 17 shows a third embodiment in which the electromagnetic control valve 33 is applied to a push type instead of a pull type.

  That is, when the electromagnetic drive unit 37 is energized from the controller 32, the movable plunger 42 is driven in the right direction in the drawing to push the spool valve 38 in the same direction, and accordingly, the first and second spring members. The first spring member 49 for urging the spool valve 38 to the left is disposed on the bottom side of the valve body 36, and the second spring member 55 facing the first spring member 49 is disposed in the accommodation hole 48. Is arranged.

  Therefore, the front end of the large diameter portion 38b at the front end of the spool valve 38 and the front end of the push rod 42b of the movable plunger 42 are always in contact with each other by the opposing spring force of the spring members 49 and 55. The same effect as the first embodiment can be obtained.

  The electromagnetic control valve of the present invention is not limited to the above-described embodiments, and is applicable not only to the valve timing control device and valve lift control device of an internal combustion engine, but also to hydraulic control and flow paths of other devices. It can be applied to switching control. In addition to the proportional control type and the on / off type, the electromagnetic control valve can be of a multistage type.

  Further, the spool valve can be formed of a synthetic resin material or other lightweight material.

  Furthermore, the spring force (spring load) of the first spring member and the second spring member can be freely changed according to the target device.

The technical ideas other than the invention described in the claims, as grasped from the embodiment, will be described below.
(A) An electromagnetic control valve characterized in that the spring force of the first urging member and the second urging member is arbitrarily set.

Thereby, it becomes possible to freely set the initial position of the spool valve by the both spring forces, and the opening / closing positions of the plurality of opening holes can be freely selected.
(B) An accommodation hole for accommodating the second urging member is provided at one end of a sliding hole in which the movable plunger is slidably accommodated, and an inner axial direction or an outer peripheral surface axial direction of the movable plunger In addition, the electromagnetic control valve is provided with communication means for communicating the receiving hole and the drain port.

According to the present invention, air and hydraulic oil flowing into the accommodation hole can be discharged to the outside from the drain port via the communication means, so that the movable plunger and the spool valve can always be quickly moved in the axial direction. Can be secured.
(C) An oil reservoir that communicates with the communicating means is provided in one end of the valve body in which the spool valve is slidably accommodated on the movable plunger side, and the oil reservoir and the drain port communicate with each other. An electromagnetic control valve characterized in that a communication groove is formed.

According to this invention, the air and hydraulic oil that have flowed into the accommodation hole on the one end side of the movable plunger and the oil reservoir on the other end side can be quickly discharged from the drain port to the outside via the communication means and the communication groove. Therefore, the quick movement of the movable plunger and the spool valve in the axial direction can always be ensured.
(D) An electromagnetic control valve characterized in that the spool valve is provided so as to be movable in an axial direction in a linear, multi-stage or on / off manner by an electromagnetic drive unit and a movable plunger.

1 is a longitudinal sectional view showing an electromagnetic control valve according to a first embodiment of the present invention. It is a principal part front view of the valve timing control apparatus with which a present Example is applied. It is a perspective view which shows the spool valve and movable plunger with which a present Example is provided. It is a characteristic view which shows the relationship between the spring load of the 1st, 2nd spring member in a present Example, and the movement amount of a spool valve. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a perspective view which shows the deformability of a spool valve and a movable plunger. It is a longitudinal cross-sectional view of the electromagnetic control valve which shows 2nd Example of this invention. A is a characteristic diagram showing the relationship between the amount of current applied to the electromagnetic drive and the amount of movement of the spool valve in this embodiment, and B is the relationship between the amount of current applied to the electromagnetic drive and the thrust of the electromagnetic drive. FIG. It is a characteristic view which shows the relationship between the spring deformation amount accompanying the electricity supply to the electromagnetic drive part in a present Example, and a spring urging | biasing force. It is a longitudinal cross-sectional view of the electromagnetic control valve which shows 3rd Example of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Timing sprocket 2 ... Cam shaft 3 ... Phase conversion mechanism 4 ... Hydraulic circuit 6 ... Vane member 9 ... Retarded oil chamber 10 ... Advance oil chamber 27/28 ... Hydraulic passage 31 ... Oil pump 33 ... Electromagnetic control valve 36 ... Valve body 36a ... Supply port 36b / 36c ... First and second output ports 37 ... Electromagnetic drive part 38 ... Spool valve 38a ... Valve shaft 42 ... Movable plunger 43-45 ... First to third land part 49 ... First spring Member 55 ... second spring member

Claims (3)

An electromagnetic drive unit that drives the movable plunger by being energized;
A spool valve that selectively opens and closes a plurality of ports according to a movement position in an axial direction, and moves in one direction by a driving force of the movable plunger;
A first biasing member that biases the spool valve from a direction opposite to the driving direction by the movable plunger,
A second urging member that urges the front end edge of the movable plunger and the front end edge of the spool valve facing the front end edge from the axial direction by urging from the direction opposite to the urging direction of the first urging member. An electromagnetic control valve characterized by comprising: The electromagnetic control valve according to claim 1, wherein the spool valve is formed of a material different from the movable plunger of the iron-based material. The electromagnetic control valve according to claim 2, wherein the spool valve is formed of an aluminum material or a synthetic resin material.

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