JP2010216554A - Solenoid valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a solenoid valve for actualizing stable flow control by preventing the eccentric wear of a valve member. <P>SOLUTION: At a site of the valve member 40 where a communication hole 43 communicating a fuel passage 41 with a space 93 is opened at an outer peripheral face portion 44, radial distances h1, h2 between an inner peripheral face portion 34 of a valve body 30 and the outer peripheral face portion 44 of the valve member 40 are unequal to each other at both opening ends of the communication hole 43 in the peripheral direction of a cylindrical portion of the valve body 30. Thus, the distribution resistance of fuel to flow out of the communication hole 43 into the space 93 and that of fuel to flow through the space 93 into the communication hole 43 are different from each other in the peripheral direction of the valve body 30. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an electromagnetic valve for controlling the flow rate of a fluid, for example, an electromagnetic valve for metering fuel supplied to a diesel engine or the like.

  As a prior art, there is an electromagnetic valve disclosed in Patent Document 1 below. This solenoid valve includes a valve case that is a valve housing, a valve body that is a valve member that is reciprocally movable in the valve case in the axial direction of the valve case, and a solenoid unit that is a drive unit that reciprocally drives the valve body The flow rate of the fluid passing through the valve case is adjusted according to the displacement position of the valve body in the valve case by the solenoid unit.

JP 2002-39420 A

  However, in the above-described conventional solenoid valve, the axial direction of the valve body is slightly inclined with respect to the axial direction of the normal valve case, and the valve body is in a plurality of locations (usually two locations) separated in the axial direction. Is supported in contact with. Therefore, when the valve body is displaced in the valve case by driving the solenoid portion, the valve body and the valve case slide while being in contact with each other at the same site. If sliding is repeated while the valve body and the valve case are in contact with each other at the same site, uneven wear occurs, the inclination of the valve body increases, and the sliding resistance of the contact portion increases. There is a problem that stable flow rate adjustment becomes difficult.

  The present invention has been made in view of the above points, and an object thereof is to provide an electromagnetic valve capable of preventing uneven wear and performing stable flow rate adjustment.

In order to achieve the above object, in the invention described in claim 1,
A valve housing having a cylindrical portion;
A valve member provided to be capable of reciprocating in the cylindrical portion in the axial direction of the cylindrical portion;
Drive means for reciprocating the valve member,
An electromagnetic valve that adjusts the flow rate of fluid flowing in the valve housing according to the displacement position of the valve member in the valve housing by the driving means,
The valve member
A first fluid passage extending in the axial direction of the valve member and circulating a fluid;
A first fluid passage, and a second fluid passage communicating with the housing inner space formed between the inner peripheral surface portion of the valve housing cylindrical portion and the outer peripheral surface portion of the valve member,
In the portion where the second fluid passage opens at the outer peripheral surface portion of the valve member, the radial distance between the inner peripheral surface portion of the valve housing cylindrical portion and the outer peripheral surface portion of the valve member is unequal at both ends of the opening in the cylindrical portion circumferential direction. It is characterized by that.

  According to this, the flow resistance in the housing inner space of the fluid flowing out from the second fluid passage or flowing into the second fluid passage differs at both ends in the circumferential direction at the portion where the second fluid passage opens at the outer peripheral surface portion of the valve member. Therefore, when the fluid is circulated through the second fluid passage, a stress rotating around the axis can be applied to the valve member due to a difference in flow rate at both ends of the circumferential opening of the housing inner space. In this way, it is possible to prevent repeated sliding while the valve housing and the valve member are in contact with each other at the same site, prevent uneven wear, and perform stable flow rate adjustment.

  According to a second aspect of the present invention, in the electromagnetic valve according to the first aspect, the second fluid passage is formed so that the axis intersects the axis of the valve member. According to this, since the second fluid passage is a passage extending radially outward from the central axis of the valve member, it is easy to form the second fluid passage in the valve member.

  According to a third aspect of the present invention, in the electromagnetic valve according to the first or second aspect, the outer peripheral surface portion of the valve member includes a curved surface portion along the inner peripheral surface portion of the valve housing cylindrical portion and an inner portion of the valve housing cylindrical portion. A flat portion spaced apart from the peripheral surface portion, and a space between the inner peripheral surface portion of the valve housing and the flat surface portion of the valve member is an internal space of the housing, and the second fuel passage is a flat portion in the circumferential direction of the valve housing cylindrical portion It is characterized by opening at the edge of the.

  According to this, it is possible to easily form a configuration in which the radial distance between the inner peripheral surface portion of the valve housing cylindrical portion and the outer peripheral surface portion of the valve member is unequal at both ends of the second fluid passage opening in the cylindrical portion circumferential direction. .

In the invention according to claim 4,
A valve housing having a cylindrical portion;
A valve member provided to be capable of reciprocating in the cylindrical portion in the axial direction of the cylindrical portion;
Drive means for reciprocating the valve member,
An electromagnetic valve that adjusts the flow rate of fluid flowing in the valve housing according to the displacement position of the valve member in the valve housing by the driving means,
The valve member
A first fluid passage extending in the axial direction of the valve member and circulating a fluid;
A second fluid passage communicating the first fluid passage and the outer periphery of the valve member;
The axis of the second fluid passage is in a torsional positional relationship with respect to the axis of the valve member.

  According to this, when the fluid flows through the second fluid passage, the fluid that moves in the axial direction of the second fluid passage that is in a torsional positional relationship that does not intersect the axis of the valve member causes the valve member to move around the axis. Rotating stress can be applied. Therefore, it is possible to prevent repeated sliding while the valve housing and the valve member are in contact with each other at the same site, to prevent uneven wear and to perform stable flow rate adjustment.

  According to a fifth aspect of the present invention, in the electromagnetic valve according to the fourth aspect, the second fluid passage is between the first fluid passage, the inner peripheral surface portion of the valve housing cylindrical portion, and the outer peripheral surface portion of the valve member. In the portion that communicates with the formed housing inner space and the second fluid passage opens at the outer peripheral surface portion of the valve member, the radial distance between the inner peripheral surface portion of the valve housing cylindrical portion and the outer peripheral surface portion of the valve member is Further, it is characterized in that the opening ends in the circumferential direction of the cylindrical portion are unequal.

  According to this, the flow resistance in the housing inner space of the fluid flowing out from the second fluid passage or flowing into the second fluid passage differs at both ends in the circumferential direction at the portion where the second fluid passage opens at the outer peripheral surface portion of the valve member. Therefore, when the fluid flows through the second fluid passage, not only the force caused by the fluid moving in the axial direction of the second fluid passage that is in a torsional positional relationship that does not intersect the axis of the valve member, but also the circumferential direction of the space in the housing Due to the difference in flow rate at both ends of the opening, stress that rotates around the axis can be applied to the valve member. In this way, it is possible to reliably prevent sliding while the valve housing and the valve member are in contact with each other at the same site, reliably prevent uneven wear, and perform stable flow rate adjustment. .

  Further, the invention according to claim 6 is characterized in that the second fluid passage is a passage on the downstream side of the fluid flow with respect to the first fluid passage. According to this, the stress which rotates to a fixed direction always around an axis line can be applied with respect to a valve member with the fluid which flows from a 1st fluid path to a 2nd fluid path in order. Accordingly, it is possible to more reliably prevent sliding while the valve housing and the valve member are in contact with each other at the same site, and more reliably prevent uneven wear and perform stable flow rate adjustment.

  According to the seventh aspect of the present invention, the drive means includes a coil spring that compresses the one end of the valve member in contact with the valve member and biases the valve member in the axial direction of the valve housing cylindrical portion. The rotation direction of the valve member when the fluid flows through the second fluid passage is the same as the winding direction when moving from the other end of the coil spring to the one end. According to this, the rotating valve member is not easily caught on the end of the coil spring that is urging the valve member with stress. Therefore, the valve member can be rotated stably.

  The invention according to claim 8 is characterized in that a plurality of second fluid passages are provided, and the plurality of second fluid passages are arranged symmetrically around the axis of the valve member. According to this, the stress rotating around the axis can be stably applied to the valve member. Therefore, it is possible to more reliably prevent sliding while the valve housing and the valve member are in contact with each other at the same site, and more reliably prevent uneven wear and perform stable flow rate adjustment. it can.

  In the invention according to claim 9, the drive means has an electromagnetic drive part that changes the position of the valve member in the housing in accordance with a current value to be energized, and the dither current is included in the current applied to the electromagnetic drive part. It is characterized by being superimposed. According to this, it is possible to easily form an oil film between the valve member and the valve housing by finely oscillating the valve member, and to reduce the sliding resistance. Therefore, the rotation of the valve member can be facilitated, and the sliding can be reliably prevented while the valve housing and the valve member are in contact with each other at the same portion.

  In the invention according to claim 10, the fluid is fuel supplied to the internal combustion engine, and the fuel inlet side of the high pressure fuel pump that pressurizes and discharges the fuel to the pressure accumulating chamber for storing the fuel injected into the internal combustion engine. And is a solenoid valve that adjusts the flow rate of fuel supplied to the high-pressure fuel pump. According to this, in the fuel injection system that injects high-pressure fuel into the internal combustion engine, it is possible to maintain the accuracy of the fuel injection amount by performing appropriate flow rate control by the electromagnetic valve, and to perform proper operation control of the internal combustion engine. be able to.

It is a block diagram which shows the common rail type fuel injection system which employ | adopted the solenoid valve 3 in 1st Embodiment to which this invention is applied. It is II arrow directional view of FIG. It is a longitudinal cross-sectional view which shows the structure of the valve member 40 in 1st Embodiment. It is the IV-IV sectional view taken on the line in FIG. FIG. 3 is a diagram schematically showing a relationship between a valve body 30 and a valve member 40. It is a longitudinal cross-sectional view which shows the structure of the valve member 40 in 2nd Embodiment. It is the VII-VII sectional view taken on the line in FIG. It is principal part sectional drawing in other embodiment.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. In the case where only a part of the configuration is described in each embodiment, the other parts of the configuration are the same as those described previously. In addition to the combination of parts specifically described in each embodiment, the embodiments may be partially combined as long as the combination is not particularly troublesome.

(First embodiment)
FIG. 1 shows a common rail fuel injection system employing the solenoid valve 3 in the first embodiment to which the present invention is applied. The common rail type fuel injection system mainly includes a fuel tank 1, a feed pump (feed pump) 2, an electromagnetic valve 3 as a flow rate control device, a high pressure fuel pump 6, and a common rail 7 as a pressure accumulating chamber. The feed pump 2, the solenoid valve 3, and the high-pressure fuel pump 6 surrounded by the one-dot chain line in FIG. 1 are configured as an integral fuel injection pump device.

  The fuel tank 1 stores normal-pressure fuel, and the fuel inside the fuel tank 1 is supplied to the electromagnetic valve 3 by the feed pump 2 via the fuel flow paths 11 and 21. A check valve 22 is disposed on the downstream side of the feed pump 2, and when the pressure of the fuel supplied by the feed pump 2 becomes higher than a predetermined pressure, the fuel returns to the fuel tank 1 side. Is done. As the feed pump 2, for example, a trochoid pump or a vane pump can be used.

  The electromagnetic valve 3 includes a valve body 30 as a valve housing, a valve member 40, an electromagnetic drive unit 50, and the like. The valve body 30 is formed in a substantially cylindrical shape, and the valve member 40 is slidably accommodated inside the cylindrical portion. A plurality (two in this example) of openings 31 are formed in the valve body 30 in the circumferential direction. The opening 31 is connected to a fuel supply path 61 that supplies fuel to the high-pressure fuel pump 6. A bush 32 is oil-tightly pressed into the end of the valve body 30 on the feed pump 2 side. A through hole 32 a formed in the central portion of the bush 32 is connected to the fuel flow path 21. Further, the through hole 32 a is a fuel inlet through which fuel flows into the electromagnetic valve 3.

  The valve member 40 is formed in a substantially bottomed cylindrical shape, and is accommodated in the cylindrical portion of the valve body 30 so as to be slidable in the axial direction. A fuel passage 41 corresponding to a first fluid passage extending in the axial direction is formed inside the valve member 40, and a plurality of (four in this example) communication holes 42 are connected to the fuel passage 41. The communication hole 42 forms a fuel passage whose axis is perpendicular to the axis of the fuel passage 41.

  The end of the communication hole 42 on the valve body 30 side serves as a fuel outlet through which fuel flows out of the electromagnetic valve 3. When the valve member 40 moves in the axial direction (vertical direction in FIG. 1) of the valve body 30, the communication hole 42 of the fuel passage 41 and the opening 31 of the valve body 30 are communicated or blocked.

  In the valve member 40, a recess is formed over the entire circumference of the outer peripheral surface 44 at the position where the communication hole 42 is formed in the axial direction, thereby forming an annular groove 92. Specifically, when the valve member 40 moves in the axial direction of the cylindrical portion of the valve body 30, the annular groove 92 and the opening 31 of the valve body 30 are communicated or blocked.

  A spring 33 is in contact with the end of the valve member 40 on the bush 32 side. The end of the spring 33 on the side opposite to the valve member is in contact with the bush 32. The spring 33 biases the valve member 40 toward the electromagnetic drive unit 50. The spring 33 and the electromagnetic drive unit 50 constitute drive means for driving the valve member 40 back and forth in the axial direction of the valve body 30.

  The fuel passage 41 extending in the axial direction of the valve member 40 is closed at the end on the electromagnetic drive unit 50 side, and a plurality of (2 in this example) are provided in the fuel passage 41 near the closed end of the fuel passage 41. Communication hole 43 is connected. The communication hole 43 communicates the fuel passage 41 with the space 93 formed between the inner peripheral surface portion 34 of the valve body 30 and the outer peripheral surface portion 44 of the valve member 40 on the electromagnetic drive unit 50 side in the valve body 30. Yes. The communication hole 43 prevents a pressure difference from being generated between the fuel passage 41 and the space 93 when the valve member 40 is displaced.

  The space 93 is a housing inner space formed between the inner peripheral surface portion of the valve housing cylindrical portion and the outer peripheral surface portion of the valve member in the present embodiment, and the communication hole 43 is the first fluid passage and the inner space of the housing in the present embodiment. It corresponds to the 2nd fluid passage which communicates. The communication hole 43 that is the second fluid passage will be described in detail later.

  The electromagnetic drive unit 50 includes a solenoid unit and a movable member. The solenoid unit includes a yoke 51, a coil 52, a stator 53, a stator 54, a guide 55, and a stator cover 56. The yoke 51 is formed of a cylindrical magnetic material. The coil 52 is disposed on the inner peripheral side of the yoke 51 and is connected to the electrode member 81 of the connector 8. The stator 53 and the stator 54 are made of a magnetic material, and are connected to a guide 55 made of a non-magnetic material by, for example, welding. The stator 53, the stator 54, and the guide 55 are integrally formed by fitting or welding to the inner peripheral side of the coil 52. The stator cover 56 is fixed by being press-fitted into the stator 54.

  The valve body 30 is inserted on the inner peripheral side of the lower edge of the stator 54 in FIG. 1, and the stator 54 and the valve body 30 are fixed by, for example, caulking. The movable member has a shaft 57 and an armature 58, and the shaft 57 is press-fitted on the inner peripheral side of the armature 58. The movable member is slidably disposed on the inner peripheral side of the stator 53, the stator 54, and the guide 55, and is supported by the linear bearing 59a and the linear bearing 59b.

  Since the armature 58 is made of a magnetic material, the magnetic force generated from the coil 52 forms a magnetic circuit that passes through the stator 53, the armature 58, the stator 54, and the yoke 51. Therefore, the shaft 57 and the armature 58 are attracted to the stator 54. Since the end of the armature 58 on the stator cover 56 side is formed in a tapered shape, the size of the gap between the armature 58 and the stator 54 according to the strength of the magnetic force acting between the armature 58 and the stator 54. Changes. Therefore, the movement distance of the armature 58 and the shaft 57 changes (the displacement position changes) according to the current value applied to the coil 52. The upper end portion of the armature 58 in the axial direction is supported by a washer 581.

  The end of the shaft 57 on the side of the stator cover 56 and the end of the valve member 40 on the side opposite to the bush are in contact. Therefore, the valve member 40 moves according to the movement of the armature 58 and the shaft 57. In FIG. 1, the electromagnetic valve 3 is illustrated so that the axis is in the vertical direction in the drawing, but the mounting orientation on the fuel injection pump device does not have to be the vertical direction in the drawing, for example, the axial direction is It is preferable to arrange it in the horizontal direction.

  The high-pressure fuel pump 6 pressurizes the fuel in the pressurizing chamber 63 by the reciprocating movement of the plunger 62. In the high-pressure fuel pump 6, the flow rate of the discharged fuel changes according to the flow rate of the fuel flowing into the pressurizing chamber 63. The plunger 62 is reciprocated in the vertical direction in FIG. 1 according to the rotation of the crankshaft 64 by a cam 65 disposed on the crankshaft 64 of the engine (not shown).

  The high-pressure fuel pump 6 is provided with a check valve 66 and a check valve 67. When the plunger 62 is lowered, the fuel is sucked in via the electromagnetic valve 3 and the fuel supply path 61. Is pressurized and discharged to the common rail 7. A fuel pipe 68 is connected to the discharge side of the high-pressure fuel pump 6, and the end of the fuel pipe 68 opposite to the high-pressure fuel pump 6 is connected to the common rail 7. In FIG. 1, one set of the combination of the plunger 62 and the pressurizing chamber 63 is shown, but a plurality (for example, two or three sets) of the plunger 62 and the pressurizing chamber 63 may be provided.

  The common rail 7 is connected to the fuel pipe 68 and holds the fuel pressurized by the high-pressure fuel pump 6 in a pressure accumulation state. An injector 71 that injects fuel into each cylinder of the engine is connected to the common rail 7 in accordance with the number of cylinders. The fuel held in the common rail 7 in a pressure-accumulated state is injected from the injector 71. A return pipe 72 is connected to the common rail 7, and surplus fuel in the common rail 7 is returned to the fuel tank 1 via the return pipe 72.

  Although not shown, the low pressure fuel that flows into the control pressure chamber of each injector 71 and is discharged from the low pressure port of the injector 71 such as fuel or leak fuel used for the operation of the injector, and the fuel injection pump device Low-pressure fuel such as leak fuel also joins the return pipe 72 and returns to the fuel tank 1.

  The common rail fuel injection system of the present embodiment is connected to an ECU 100 that is a control means. The ECU 100 controls the solenoid valve 3 to optimally control the flow rate of fuel discharged from the high-pressure fuel pump 6 based on the input fuel pressure inside the common rail 7, the engine speed Ne, the accelerator opening α, and the like. The output value of the current applied to the coil 52 is controlled. Further, the ECU 100 controls the opening / closing timing of an electromagnetic valve (not shown) of the injector 71 connected to the common rail 7. Thereby, the fuel injection timing and the amount of fuel into each cylinder of the engine are controlled.

  Here, the opening 31 formed in the valve body 30 will be described. FIG. 2 is a view taken in the direction of arrow II in FIG. As illustrated in FIG. 2, the opening 31 formed in the valve body 30 includes a first opening 311, a second opening 312, and a third opening 313. The first opening 311, the second opening 312 and the third opening 313 form one opening 31. The opening 31 is continuously formed in the axial direction of the valve body 30 in the order of the first opening 311, the third opening 313, and the second opening 312 from the electromagnetic drive unit 50 side.

  The first opening 311 and the second opening 312 are each formed in a substantially rectangular shape, and the areas of the first opening 311 and the second opening 312 are different from each other. The length of the first opening 311 in the direction perpendicular to the axis of the valve body 30, that is, the width of the first opening 311 is smaller than the width of the second opening 312. Therefore, the area change rate of the opening 31 in the axial direction of the valve body 30 is larger in the second opening 312 than in the first opening 311.

  In addition, a third opening 313 that connects the first opening 311 and the second opening 312 is formed between the first opening 311 and the second opening 312. The third opening 313 is formed in a substantially trapezoidal shape that connects the first opening 311 and the second opening 312. Therefore, the shape of the opening 31 is as shown in FIG. By adopting the opening 31 having such a shape, the flow rate of the fuel supplied to the high-pressure fuel pump 6 is made non-linear with respect to the current value applied to the coil 52.

  Next, the principal part structure of the valve member 40 is demonstrated. 3 is a cross-sectional view showing the configuration of the valve member 40, and FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. In FIG. 4, the valve body 30 is also illustrated. As shown in FIG. 3, the valve member 40 includes a fuel passage 41, a communication hole 42 and a communication hole 43 that communicate the fuel passage 41 and the outer peripheral side of the outer peripheral surface portion 44. 3 and 4, illustration of the chamfered shape of the peripheral edge of each end of the communication hole 42 and the communication hole 43 is omitted.

  In the vicinity of the right end of the valve member 40 in FIG. 3, as shown in FIG. 4, the communication hole 43 is formed so that the axis is orthogonal to the axis of the valve member 40. In other words, the communication hole 43 extends from the center of the valve member 40 in the radially outward direction.

  4, the outer peripheral surface portion 44 of the valve member 40 includes a curved surface portion 441 along the inner peripheral surface portion 34 of the valve body 30 cylindrical portion and a flat surface portion 442 spaced from the inner peripheral surface portion 34 of the valve body 30 cylindrical portion. A space 93 is formed between the inner peripheral surface portion 34 of the valve body 30 and the flat surface portion 442 of the valve member 40. The end of the communication hole 43 on the space 93 side is open to an edge (near the end) in the circumferential direction of the valve body 30 in the flat portion 442.

  Thereby, in the part where the communication hole 43 opens at the outer peripheral surface portion 44 of the valve member 40, the radial distance between the inner peripheral surface portion 34 of the valve body 30 and the outer peripheral surface portion 44 of the valve member 40 is the same as that of the cylindrical portion of the valve body 30. In the circumferential direction, the both ends of the communication hole 43 are unequal. As shown in FIG. 4, the radial distance h <b> 1 between the inner peripheral surface portion 34 and the outer peripheral surface portion 44 of the valve member 40 at the end portion on the right-hand side in the drawing at the opening portion of the communication hole 43 is substantially zero. On the other hand, the inner circumferential surface portion 34 and the outer circumferential surface portion 44 of the valve member 40 are separated from each other at the end portion on the left-hand side in the drawing at the opening portion of the communication hole 43, and the radial distance h2 is larger than the distance h1. .

  As is apparent from FIG. 4, the two communication holes 43 are arranged symmetrically around the axis of the valve member 40.

  Next, the operation of the common rail fuel injection system including the electromagnetic valve 3 based on the above configuration will be described.

  As shown in FIG. 1, the feed pump 2 supplies fuel from the fuel tank 1 to the electromagnetic valve 3. The supplied fuel flows into the solenoid valve 3 from the through hole 32a of the bush 32 which is a fuel inlet. The inflowing fuel is supplied to the communication hole 42 via the fuel passage 41 formed inside the valve member 40.

  When the current value applied to the coil 52 is 0, that is, when the coil 52 is not energized, the valve member 40 is urged toward the electromagnetic drive unit 50 by the urging force of the spring 33. The shaft 57 abutting on the valve member 40 together with the valve member 40 and the armature 58 integrated with the shaft 57 are biased toward the counter valve member. The movement of the shaft 57 and the armature 58 is restricted when the stepped portion 53a of the stator 53 and the washer 581 come into contact with each other, and the shaft 57 and the armature 58 stop at the position where the stepped portion 53a and the washer 581 come into contact. Sometimes the valve member 40 also stops.

  When a current is applied to the coil 52, the armature 58 is attracted toward the stator 54 by the magnetic field generated in the coil 52. Then, the shaft 57 moves along with the armature 58 toward the valve member 40. As the shaft 57 moves, the valve member 40 moves in a direction to compress the spring 33. That is, the valve member 40 moves downward in FIG. The amount of movement of the armature 58 and the shaft 57 is determined by the current value applied to the coil 52.

  As the valve member 40 moves downward in FIG. 1, the communication hole 42 formed in the valve member 40 and the opening 31 of the valve body 30 overlap (specifically, the annular groove 92 and the opening 31 are connected to each other). overlap). As a result, the communication hole 42 and the opening 31 communicate with each other, and the fuel inside the fuel passage 41 flows out to the fuel supply path 61 via the communication hole 42 and the opening 31. Further, the shape of the outer peripheral surface portion 44 of the valve member 40 or the inner peripheral surface portion 34 of the valve body 30 is changed so that the communication hole 42 and the opening 31 communicate with each other at a current value of 0, and the valve member 40 is shown in FIG. The movement between the communication hole 42 and the opening 31 may be blocked by moving downward. The area where the communication hole 42 and the opening 31 communicate with each other changes as the valve member 40 moves. That is, the area in which the communication hole 42 and the opening 31 communicate with each other varies depending on the change in the current value applied to the coil 52.

  By changing the area where the communication hole 42 and the opening 31 communicate with each other, the flow rate of the fuel flowing out from the fuel passage 41 to the fuel supply passage 61 changes, and the flow rate of the fuel supplied to the high-pressure fuel pump 6 is controlled. The The fuel flowing out to the fuel supply path 61 is supplied to the pressurizing chamber 63 of the high-pressure fuel pump 6 through the check valve 66. The fuel supplied to the pressurizing chamber 63 is pressurized by the plunger 62, and when the pressure in the pressurizing chamber 63 reaches a predetermined pressure, the check valve 67 is opened and the pressurized fuel is discharged to the fuel pipe 68. . The fuel discharged to the fuel pipe 68 is held in the common rail 7 in a pressure-accumulated state, and is injected from the injector 71 into each cylinder of the engine at a predetermined time.

  When the solenoid valve 3 adjusts the flow rate of the fuel in accordance with the fluctuation of the operating state of the engine, the valve member 40 reciprocates in the axial direction in the valve body 30 by the fluctuation of the current value applied to the coil 52. . When the current value applied to the coil 52 increases, the valve member 40 is displaced downward in FIG. 1, and the volume of the space 93 increases accordingly. As the volume of the space 93 increases, part of the fuel in the fuel passage 41 flows into the space 93 through the communication hole 43. At this time, the communication hole 43 is a downstream side passage with respect to the fuel passage 41.

  As indicated by white arrows in FIG. 4, the fuel that has flowed into the space 93 from the communication hole 43 has a radial distance h <b> 2 between the inner peripheral surface portion 34 and the outer peripheral surface portion 44 at both ends in the circumferential direction at the opening portion of the communication hole 43. Since it is much larger than h1, it flows in the counterclockwise direction in the figure. Due to the reaction of the fuel flow, the valve member 40 rotates in the clockwise direction as shown by the solid arrow in FIG.

  As shown in FIG. 1, the spring 33 used in the electromagnetic valve 5 is a coil spring, and the winding direction when turning from the end on the bush 32 side to the end on the valve member 40 side is right-handed. . That is, the rotation direction of the valve member 40 when the fuel flows from the fuel passage 41 to the communication passage 43 is the same as the winding direction when the spring 33 is directed toward the valve member 40. As a result, the rotating valve member 40 is not easily caught by the end of the spring 33 that is compressed while being in contact with the valve member 40 and urges the valve member 40 to stress. Therefore, the valve member 40 can be rotated stably.

  On the other hand, when the current value applied to the coil 52 decreases, the valve member 40 is displaced upward in FIG. 1, and the volume of the space 93 decreases accordingly. As the volume of the space 93 decreases, a part of the fuel in the space 93 flows into the fuel passage 41 through the communication hole 43. At this time, the communication hole 43 becomes an upstream side passage with respect to the fuel passage 41. At this time, the fuel flows in the direction opposite to the direction indicated by the white arrow in FIG. 4, and the valve member 40 rotates counterclockwise in the figure, but the amount of rotation is larger than that in the case where the fuel flows out from the communication hole 43 into the space 93. Relatively small.

  According to the above-described configuration and operation, the inner peripheral surface portion 34 of the valve body 30 and the outer periphery of the valve member 40 are formed at the portion where the communication hole 43 that communicates the fuel passage 41 and the space 93 of the valve member 40 opens at the outer peripheral surface portion 44. The distance in the radial direction from the surface 44 is unequal at both ends of the opening of the communication hole 43 in the circumferential direction of the cylindrical portion of the valve body 30 (h1 and h2 are different), and flows out from the communication hole 43 into the space 93. The flow resistance of the fuel that flows into the communication hole 43 from the space 93 or the space 93 differs in the circumferential direction of the valve body 30. Therefore, when the fuel flows through the communication hole 43, a stress that rotates around the axis can be applied to the valve member 40. In particular, a large rotational force is generated when the fuel flows out from the communication hole 43 into the space 93.

  In order for the valve member 40 to slide within the valve body 30, a slight clearance is required between the valve body 30 and the valve member 40. Therefore, as schematically shown in FIG. 5, the axial direction of the valve member 40 is slightly inclined with respect to the axial direction of the normal valve body 30, and the valve member 40 has a plurality of locations (usually illustrated) that are separated in the axial direction. As shown, the valve body 30 is supported by being supported at two locations. Therefore, when the valve member 40 is reciprocally displaced in the valve body 30 by driving the electromagnetic drive unit 50, if sliding is repeated while the valve member 40 and the valve body 30 are in contact with each other, Wear occurs, the inclination of the valve member 40 increases, the sliding resistance of the contact portion increases, and stable flow rate adjustment becomes difficult.

  In the present embodiment, when the valve member 40 is displaced in the axial direction of the valve body 30, the valve member 40 can be rotated in addition to the movement in the axial direction, and the valve body 30 and the valve member 40 are the same part. It is possible to prevent the sliding from being repeated while being in contact with each other, to prevent uneven wear and to perform stable flow rate adjustment. As a result, in the fuel injection system that injects high-pressure fuel into the engine, the flow rate control by the solenoid valve 3 can be performed to maintain the accuracy of the fuel injection amount, and the proper operation control of the engine can be stably performed. It can be carried out.

  Further, the communication hole 43 opens at the edge of the flat portion 442 of the outer peripheral surface portion 44 of the valve member 40 in the circumferential direction of the valve body 30. Therefore, it is possible to easily form a configuration in which the radial distance between the inner peripheral surface portion 34 of the valve body 30 and the outer peripheral surface portion 44 of the valve member 40 is unequal at both ends of the opening in the circumferential direction.

  Further, a plurality of communication holes 43 and spaces 93 are provided, and the plurality of communication holes 43 and spaces 93 are arranged symmetrically around the axis of the valve member 40. Therefore, the stress rotating around the axis can be stably applied to the valve member 40 as the fuel flows.

  In addition, the communication hole 43 is formed so that the axis intersects the axis of the valve member 40. Therefore, the formation process of the communication hole 43 to the valve member 40 is easy.

  Although omitted in the above description, a dither current is superimposed on the current applied to the electromagnetic drive unit 50 by the ECU 100. Therefore, the valve member 40 is finely displaced and oscillated by the dither current, so that an oil film can be easily formed between the valve member 40 and the valve body 30, and the sliding resistance can be further reduced. Thereby, rotation of the valve member 40 also becomes easy and it can prevent reliably that sliding is repeated in the state which the valve body 30 and the valve member 40 contacted in the same site | parts.

(Second Embodiment)
Next, a second embodiment will be described based on FIG. 6 and FIG.

  The second embodiment is different from the first embodiment in that a rotational force is applied to the valve member 40 due to the configuration of the communication hole. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  FIG. 6 is a cross-sectional view showing the configuration of the valve member 40 in the second embodiment, and FIG. 7 is a cross-sectional view taken along the line VII-VII in FIG. In FIG. 7, the valve body 30 is also illustrated. As shown in FIG. 6, the valve member 40 includes a fuel passage 41, and a communication hole 142 and a communication hole 143 that allow the fuel passage 41 and the outer peripheral surface portion 44 to communicate with each other. In FIGS. 6 and 7, illustration of chamfered shapes of the peripheral edges of the both end openings of the communication hole 142 and the communication hole 143 is omitted.

  In the valve member 40 of the present embodiment, the communication hole 143 is formed so that the axis is orthogonal to the axis of the valve member 40. The end of the communication hole 143 on the space 93 side is open at the center in the circumferential direction of the flat portion 442. Therefore, no rotational force is generated on the valve member 40 by the fuel flowing through the communication hole 143.

  In the valve member 40 of the present embodiment, as illustrated in FIG. 7, the communication hole 142 is formed at a position where the axis is offset radially outward from the position orthogonal to the axis of the valve member 40. In other words, the communication hole 142 extends from the position eccentric from the center of the valve member 40 in the radially outward direction. That is, the axial line of the communication hole 142 is in a twisted positional relationship with respect to the axial line of the valve member 40. The fuel passage 41 is a first fluid passage in the present embodiment, and the communication hole 142 is a second fluid passage in the present embodiment.

  As described in the first embodiment, in the cross-sectional portion illustrated in FIG. 7, the outer peripheral surface portion 44 of the valve member 40 is an annular groove portion 92, and the inner peripheral surface portion 34 of the valve body 30 and the outer periphery of the valve member 40. An annular space 921 is formed between the surface portion 44. The end of the communication hole 142 on the annular space 921 side is open to the bottom surface of the annular groove 92.

  As is clear from FIG. 7, the plurality of (four in this example) communication holes 142 are arranged symmetrically around the axis of the valve member 40.

  When the solenoid valve 3 adjusts the flow rate of the fuel in accordance with the fluctuation of the operating state of the engine, the valve member 40 reciprocates in the axial direction in the valve body 30 by the fluctuation of the current value applied to the coil 52. . Regardless of the current value applied to the coil 52, when fuel is supplied from the solenoid valve 3 to the high pressure fuel pump 6, the fuel in the fuel passage 41 flows into the annular space 921 through the communication hole 142. The communication hole 142 is always a downstream side passage with respect to the fuel passage 41.

  As indicated by the white arrow in FIG. 7, the valve member 40 rotates clockwise as shown in FIG. 7 by the reaction of the fuel flowing through the communication hole 142 and discharged from the communication hole 142 to the annular space 921. Rotate in the direction.

  As in the case of the first embodiment, the rotation direction of the valve member 40 when the fuel flows from the fuel passage 41 to the communication hole 142 is the same as the winding direction when the spring 33 moves toward the valve member 40. ing. As a result, the rotating valve member 40 is not easily caught by the end of the spring 33 that is compressed while being in contact with the valve member 40 and urges the valve member 40 to stress. Therefore, the valve member 40 can be rotated stably.

  According to the configuration and operation described above, the axis of the communication hole 142 is twisted with respect to the axis of the valve member 40, and when the fuel flows through the communication hole 142, the twist does not intersect with the axis of the valve member 40. The fuel that moves in the axial direction of the communication hole 142 in the positional relationship can apply a stress that rotates around the axis to the valve member 40.

  Therefore, when fuel flows through the communication hole 142, the valve member 40 can be rotated, and sliding is prevented from being repeated while the valve body 30 and the valve member 40 are in contact with each other at the same portion. In addition, it is possible to prevent uneven wear and perform stable flow rate adjustment. As a result, in the fuel injection system that injects high-pressure fuel into the engine, the flow rate control by the solenoid valve 3 can be performed to maintain the accuracy of the fuel injection amount, and the proper operation control of the engine can be stably performed. It can be carried out.

  A plurality of communication holes 142 are provided, and the plurality of communication holes 142 are arranged symmetrically around the axis of the valve member 40. Therefore, the stress rotating around the axis can be stably applied to the valve member 40 as the fuel flows.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  In the first embodiment, the inner peripheral surface portion 34 of the valve body 30 and the outer peripheral surface portion 44 of the valve member 40 at a portion where the communication hole 43 that communicates the fuel passage 41 and the space 93 of the valve member 40 opens at the outer peripheral surface portion 44. And the radial distance is made unequal at both ends of the communication hole 43 in the circumferential direction of the cylindrical portion of the valve body 30, and a rotational force is applied to the valve member 40. In the second embodiment, the axis of the communication hole 142 is As a positional relationship of twist with respect to the axis of the valve member 40, a rotational force is applied to the valve member 40, but is not limited thereto.

  For example, the axial line of the communication hole 43 may be twisted with respect to the axis of the valve member 40 to apply a rotational force to the valve member 40, or the communication hole 42 may be an outer peripheral surface portion 44 and an annular groove portion 42. The radial distance between the inner peripheral surface portion 34 of the valve body 30 and the outer peripheral surface portion 44 of the valve member 40 at the portion opened inward is unequal at both ends of the communication hole 42 in the circumferential direction of the valve body 30 cylindrical portion. A rotational force may be applied to 40.

  Further, the above two means may be combined. For example, as shown in FIG. 8, the valve body 30 in a position where the axis of the communication hole 142 is twisted with respect to the axis of the valve member 40 and the communication hole 142 opens into the annular groove 92 at the outer peripheral surface 44. The radial distance between the inner peripheral surface portion 34 and the outer peripheral surface portion 44 of the valve member 40 is unequal at both ends of the communication hole 42 opening in the circumferential direction of the cylindrical portion of the valve body 30 (see h1 and h2 in FIG. 8). A rotational force may be applied to 40. In this case, it can be said that the annular space 92 is a housing inner space formed between the inner peripheral surface portion of the valve housing cylindrical portion and the outer peripheral surface portion of the valve member, and the communication hole 142 is the first fluid in the present embodiment. This corresponds to a second fluid passage communicating the passage and the housing internal space.

  In each of the above embodiments, the communication hole has an axis in a plane orthogonal to the axis of the valve member 40, but the axis of the communication hole is inclined with respect to the plane orthogonal to the axis of the valve member 40. It doesn't matter.

  Moreover, in each said embodiment, although the solenoid valve 3 adjusted the flow volume of the fuel in a fuel injection pump apparatus, it is not limited to this. For example, it is effective to apply the present invention to an electromagnetic valve that adjusts the flow rate of a hydraulic control device or the like that uses various types of hydraulic oil as fluid.

3 Solenoid valve 30 Valve body (valve housing)
33 Spring (coil spring, part of drive means)
34 Inner peripheral surface (inner peripheral surface of valve housing)
40 Valve member 41 Fuel passage (first fluid passage)
43 communication hole (second fluid passage in the first embodiment)
44 Outer peripheral surface (outer peripheral surface of valve member)
50 Electromagnetic drive part (part of drive means)
93 space (inside housing space)
142 communication hole (second fluid passage in the second embodiment)
441 Curved portion 442 Plane portion

Claims (10)

A valve housing having a cylindrical portion;
A valve member provided so as to be capable of reciprocating in the cylindrical portion in the axial direction of the cylindrical portion;
Drive means for reciprocatingly driving the valve member,
An electromagnetic valve for adjusting a flow rate of fluid flowing through the valve housing in accordance with a displacement position of the valve member in the valve housing by the driving means;
The valve member is
A first fluid passage extending in the axial direction of the valve member and circulating the fluid;
A first fluid passage, and a second fluid passage communicating with the inner space of the housing formed between the inner peripheral surface portion of the cylindrical portion and the outer peripheral surface portion of the valve member,
In a portion where the second fluid passage opens at the outer peripheral surface portion of the valve member, the radial distance between the inner peripheral surface portion of the cylindrical portion and the outer peripheral surface portion of the valve member is not at both ends of the opening in the cylindrical portion circumferential direction. And so on.   The electromagnetic valve according to claim 1, wherein the second fluid passage is formed so that an axis thereof intersects with an axis of the valve member. The outer peripheral surface portion of the valve member has a curved surface portion along the inner peripheral surface portion of the cylindrical portion and a flat surface portion separated from the inner peripheral surface portion of the cylindrical portion, and a space between the inner peripheral surface portion and the flat surface portion is the housing. It is an internal space,
3. The electromagnetic valve according to claim 1, wherein the second fuel passage is opened at an edge portion of the planar portion in the circumferential direction. A valve housing having a cylindrical portion;
A valve member provided so as to be capable of reciprocating in the cylindrical portion in the axial direction of the cylindrical portion;
Drive means for reciprocatingly driving the valve member,
An electromagnetic valve for adjusting a flow rate of fluid flowing through the valve housing in accordance with a displacement position of the valve member in the valve housing by the driving means;
The valve member is
A first fluid passage extending in the axial direction of the valve member and circulating the fluid;
A second fluid passage communicating the first fluid passage with the outer periphery of the valve member;
The electromagnetic valve, wherein an axis of the second fluid passage is in a twisted positional relationship with respect to an axis of the valve member. The second fluid passage communicates with the first fluid passage and a housing inner space formed between an inner peripheral surface portion of the cylindrical portion and an outer peripheral surface portion of the valve member;
In a portion where the second fluid passage opens at the outer peripheral surface portion of the valve member, the radial distance between the inner peripheral surface portion of the cylindrical portion and the outer peripheral surface portion of the valve member is not at both ends of the opening in the cylindrical portion circumferential direction. The electromagnetic valve according to claim 4, wherein   The electromagnetic valve according to any one of claims 1 to 5, wherein the second fluid passage is a passage on the downstream side of the fluid flow with respect to the first fluid passage. The driving means includes a coil spring that is compressed while contacting one end of the valve member and biases the valve member in an axial direction of the cylindrical portion;
The rotation direction of the valve member when fluid flows through the first fluid passage and the second fluid passage is the same as the winding direction when the other end portion of the coil spring is directed to the one end portion. The solenoid valve according to claim 6. A plurality of the second fluid passages are provided,
The solenoid valve according to any one of claims 1 to 7, wherein the plurality of second fluid passages are arranged symmetrically around an axis of the valve member. The drive means has an electromagnetic drive unit that changes the position of the valve member in the housing according to a current value to be energized,
The solenoid valve according to claim 1, wherein a dither current is superimposed on a current applied to the electromagnetic drive unit. The fluid is a fuel supplied to the internal combustion engine;
It is disposed on the fuel inlet side of a high-pressure fuel pump that pressurizes and discharges the fuel to a pressure accumulating chamber that stores fuel to be injected into the internal combustion engine, and adjusts the flow rate of fuel supplied to the high-pressure fuel pump. The electromagnetic valve according to any one of claims 1 to 9.

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