JP4922115B2 - Solenoid valve mounting structure - Google Patents

Description

  The present invention relates to an electromagnetic valve mounting structure used in a variable valve timing mechanism capable of controlling the opening / closing timing of intake and exhaust valves constituting an engine.

  2. Description of the Related Art Conventionally, there is known a variable valve timing mechanism that changes the rotation phase of a camshaft relative to the rotation of a crankshaft and changes the opening / closing timing of an intake / exhaust valve to improve engine output and fuel efficiency. This variable valve timing mechanism generally has an actuator that changes the rotational phase of the camshaft relative to the rotation of the crankshaft, and an oil control valve that controls the supply and discharge of the hydraulic fluid of the actuator according to the operating state of the engine. .

  The actuator and the oil control valve are communicated with each other through the advance side oil passage and the retard side oil passage, and the working oil is circulated through the advance side oil passage under the switching action of the oil control valve. The actuator is actuated to the advance side, while the operating oil is circulated through the retard side oil passage to actuate the actuator to the retard side to change the valve opening / closing timing.

  As the oil control valve, for example, an electromagnetic valve having a solenoid portion that is excited under energization is used, and the first control valve for changing the rotation phase of the intake valve camshaft and the rotation phase of the exhaust valve camshaft. And a second control valve for changing. And the 1st and 2nd control valve is arrange | positioned in parallel with respect to the timing belt cover with which the side part of an engine is mounted | worn (for example, refer patent document 1).

JP 2006-118497 A

  By the way, since the first and second control valves generally use solenoid valves that are driven under the excitation action of solenoids, the solenoid portion incorporating the solenoid has a structure such as a spool or the like. It is formed in a large diameter with respect to the part having the valve body. Therefore, as described above, when the first and second control valves are arranged in parallel in the same direction, large-diameter solenoid parts are arranged adjacent to each other, and accordingly, the first control valve of the first control valve is arranged. It is necessary to ensure a large interval between the axis and the axis of the second control valve, and it is also necessary to provide a clearance of a predetermined interval between the first control valve and the second control valve.

  On the other hand, in recent years, the space of an engine room of a vehicle equipped with an engine having such a variable valve timing mechanism has been reduced in size, and miniaturization and space saving of components constituting the engine are desired. However, in the case described above, the installation space for the first and second control valves in the vicinity of the timing belt cover becomes large.

  The present invention has been made in consideration of the above problems, and provides a mounting structure for a solenoid valve that can save space when mounting a plurality of solenoid valves and can effectively use the space. Objective.

In order to achieve the above-mentioned object, the present invention provides a plurality of electromagnetic valves for controlling a supply state of hydraulic oil to a variable valve timing mechanism which is mounted on an engine and can change the opening / closing timing of an intake / exhaust valve provided in the engine. In the solenoid valve mounting structure for mounting the valve,
The plurality of solenoid valves have a large diameter portion and a small diameter portion adjacent to the large diameter portion along the axial direction,
On the other hand and the other solenoid valve, with each other in the axial line is disposed so as to be substantially parallel, mounting et is the opposite direction to the small diameter portion of each other are close to the small diameter portion, the solenoid valve It is provided so that it may mutually overlap in the direction orthogonal to the axis of the.

  According to the present invention, in an electromagnetic valve having a large diameter portion and a small diameter portion, one electromagnetic valve and the other electromagnetic valve are provided so that their axes are parallel to each other, and the small diameter portions are close to each other. Are attached from opposite directions to each other.

  Therefore, when a plurality of solenoid valves are mounted, the large diameter portions having large diameters can be separated from each other, and the small diameter portions having small diameters can be brought close to each other, so that the plurality of solenoid valves are adjacently mounted in the same direction. Compared to the case, the distance between the axes of the solenoid valves can be reduced. Therefore, a plurality of solenoid valves can be arranged in a compact space and installed in a smaller space. As a result, for example, space saving in an engine room provided with a plurality of electromagnetic valves can be achieved, and a limited space in the engine room can be effectively utilized.

  Further, by providing the small diameter portion so as to overlap each other in the direction orthogonal to the axis of the solenoid valve, the spacing between the axes of the plurality of solenoid valves can be further reduced, thereby further saving space. Can be achieved.

  Furthermore, since the plurality of electromagnetic valves are provided on the cover member that covers the side of the engine, the electromagnetic valve can be easily attached and detached, so that the maintainability can be improved.

  Furthermore, it is preferable that the large diameter portion is a solenoid portion that is excited under the action of electric current, and the small diameter portion is a sleeve that is internally provided with a spool that is displaced along the axial direction under the excitation action of the solenoid portion.

  According to the present invention, the following effects can be obtained.

  That is, when a plurality of solenoid valves are mounted, a large diameter portion having a large diameter can be separated from each other, and a small diameter portion having a small diameter can be disposed close to each other. Compared with the case where it attaches to, the distance between the axes of the said solenoid valve can be made small. Therefore, a plurality of solenoid valves can be arranged compactly and installed in a smaller space, space saving can be achieved, and the space can be effectively utilized.

  Further, by arranging the plurality of solenoid valves so as to be coaxial with each other through the straight through-holes, the electromagnetic valves are compared with the case where the plurality of solenoid valves are adjacently mounted in the same direction. Since the distance between the axes of the valves can be eliminated, a plurality of solenoid valves can be arranged in a compact manner and installed in a smaller space. Furthermore, since a plurality of solenoid valves can be attached to a single through hole, it is possible to reduce the number of manufacturing steps and the manufacturing cost for processing the through hole.

  A preferred embodiment of a solenoid valve mounting structure according to the present invention will be described in detail below with reference to the accompanying drawings.

  In FIG. 1, reference numeral 10 indicates an engine to which a solenoid valve mounting structure according to an embodiment of the present invention is applied.

  As shown in FIG. 1, the engine 10 is mounted in an engine room of a vehicle (not shown). A piston 16 is connected to a crankshaft 12 constituting the engine 10 via a connecting rod 14. Timing between the sprocket 18 provided at one end of the crankshaft 12 and the cam sprockets 24 a and 24 b provided on the intake camshaft 20 and the exhaust camshaft 22 disposed in parallel above the crankshaft 12. The chain 26 is wound. The sprocket 18, the cam sprockets 24a and 24b, and the timing chain 26 are covered with a chain cover (cover member) 32 (see FIG. 2) that is mounted on the side surfaces of the cylinder head 28 and the cylinder block 30.

  Here, in the engine room, the crankshaft 12 is mounted horizontally so that the crankshaft 12 is substantially orthogonal to the traveling direction of the vehicle and the end portions thereof are on the side frames provided on the left and right sides in the engine room. The case of this four-cylinder engine will be described.

  A variable valve timing mechanism capable of changing the relative phases of the intake camshaft 20 and the exhaust camshaft 22 and changing the opening / closing timing of the intake valve 33a and the exhaust valve 33b is formed on the side surface of the cylinder head 28 constituting the engine 10. A valve unit 34 is mounted.

  As shown in FIG. 2, the side surface of the cylinder head 28 includes a mounting portion 36 to which the valve unit 34 is mounted. The mounting portion 36 is provided with a supply oil path 38 through which hydraulic oil is supplied, and variable. First and second oil passages 40 and 42 for supplying hydraulic oil to a variable valve timing mechanism (not shown) of the valve timing mechanism are formed.

  The first oil passage 40 communicates with a variable valve timing mechanism provided on the intake camshaft 20 side, and includes an advance passage 44a for advancing the intake camshaft 20 and a retard passage 46a for retarding. Composed. The second oil passage 42 communicates with a variable valve timing mechanism provided on the exhaust camshaft 22 side, and, similarly to the first oil passage 40, an advance passage 44b for advancing the exhaust camshaft 22. And a retard passage 46b for retarding the angle. The mounting portion 36 is provided with a plurality of screw holes 48 into which a fixing bolt 86 for fixing the valve unit 34 is screwed.

  As shown in FIGS. 2 to 7, the valve unit 34 is mounted on the side surface of the cylinder head 28 through a unit hole 50 opened on the side surface of the chain cover 32, and is fixed to the cylinder head 28. A pair of a first control valve (solenoid valve) 54 and a second control valve (solenoid valve) 56 held with respect to the housing 52 and a cylinder head 28 are mounted on the side surface of the housing 52. The filter 58 is held.

  The housing 52 is formed in a block shape having a substantially rectangular cross section, and is mounted so that one end of the opening is in contact with the cylinder head 28. First and second valve holes 60 and 62 into which a part of the first and second control valves 54 and 56 are inserted are opened on both side surfaces of the housing 52, respectively. The first and second valve holes 60, 62 extend in the horizontal direction toward the inside of the housing 52, and are formed in parallel to each other with a predetermined interval in the vertical direction.

  An annular groove 64 (see FIGS. 6 and 7) is formed on an end surface of the housing 52 that is in contact with the cylinder head 28, and a seal member 66 is attached to the groove 64. The seal member 66 is made of, for example, an O-ring, liquid packing, and the like. When the valve unit 34 including the housing 52 is mounted on the side surface of the cylinder head 28, the seal member 66 is interposed between the housing 52 and the cylinder head 28. Sandwiched between. As a result, the hydraulic oil introduced into the valve unit 34 is prevented from leaking to the outside, and liquid tightness is maintained.

  On the other hand, inside the housing 52, a supply passage 68 for supplying hydraulic oil from the engine 10, communication passages 70 a and 70 b communicating the first and second valve holes 60 and 62 and the supply passage 68, A first advance side passage 72 and a first retard side passage 74 that are communicated with the first valve hole 60, and the flow state of the hydraulic oil is switched under the switching action of the first control valve 54, and the second valve hole 62. The hydraulic oil is discharged through the first valve hole 60 and the second advance side passage 76 and the second retard side passage 78 in which the flow state of the hydraulic oil is switched under the switching action of the second control valve 56. The first drain hole 80 and the second drain hole 82 through which the hydraulic oil is discharged through the second valve hole 62 are provided.

  The supply passage 68 is opened to one end portion side of the housing 52 in a substantially rectangular shape, and is formed horizontally from one end portion side to the other end portion of the housing 52, and the communication passages 70a and 70b are provided in the housing 52. 52 communicates with the supply passage 68 on the other end side and extends vertically upward so as to be orthogonal to the supply passage 68.

  The communication passages 70 a and 70 b are formed by cutting or the like in the vertically downward direction from the upper side of the housing 52, and are formed so as to penetrate the first and second valve holes 60 and 62 and the supply passage 68. The hole opened at the top of the housing 52 is closed by a plug 83 formed in a substantially conical shape. As a result, the hydraulic fluid flowing through the communication passages 70a and 70b, the first and second valve holes 60 and 62, and the supply passage 68 does not leak to the outside through the opened hole.

  That is, the communication passages 70 a and 70 b penetrate perpendicularly to the first and second valve holes 60 and 62 formed on the other end portion side of the housing 52, and are supplied to the supply passage 68. Is supplied to the first and second valve holes 60 and 62 through the communication passages 70a and 70b.

  A recess 68a (see FIG. 7) having a slightly larger diameter is formed at the opening end of the supply passage 68, and a mesh portion 112 of a filter 58 described later is fitted therein, and an end face facing the supply passage 68 Is formed with an annular groove 116 recessed in a rectangular shape, and the seal part 114 of the filter 58 is mounted in the groove 116.

  The first advance side passage 72 and the first retard side passage 74 are provided above the supply passage 68 in parallel with a predetermined distance from each other, from one end side of the opened housing 52 toward the other end side. It is extended. One end portions of the first advance side passage 72 and the first retard side passage 74 are connected to the advance passage 44a and the retard passage 46a that constitute the first oil passage 40 of the cylinder head 28, respectively. At the same time, the other end portions are respectively connected to and communicated with the first valve hole 60.

  Further, the second advance angle side passage 76 and the second retard angle side passage 78 are provided above the first advance angle side passage 72 and the first retard angle side passage 74 in parallel with a predetermined distance from each other and opened. The housing 52 extends from one end side toward the other end side. One end portions of the second advance side passage 76 and the second retard side passage 78 are connected to the advance passage 44b and the retard passage 46b that constitute the second oil passage 42 of the cylinder head 28, respectively. At the same time, the other ends are connected to and communicate with the second valve holes 62 (see FIG. 7).

  That is, the first advance side passage 72, the first retard side passage 74, the second advance side passage 76, and the second retard side passage 78 are respectively arranged in a lattice shape spaced apart from each other by a predetermined distance. A second retard side passage 78 is provided above the corner side passage 72, and a second advance side passage 76 is provided above the first retard side passage 74.

  The housing 52 has a pair of ribs 52a and 52b extending in the vertical direction above the supply passage 68. One rib 52a includes a first advance side passage 72 and a second retard angle. A side passage 78 is provided, and a first retard side passage 74 and a second advance side passage 76 are provided on the other rib 52b. As shown in FIGS. 3 and 5, the pair of ribs 52 a and 52 b are provided in parallel with a predetermined distance from each other, and connect the upper portion of the supply passage 68 and the inner wall surface of the housing 52.

  Thus, by providing a pair of ribs 52a and 52b in which the first advance side passage 72, the first retard side passage 74, the second advance side passage 76, and the second retard side passage 78 are formed. The rigidity of the housing 52 opened toward the cylinder head 28 using the ribs 52a and 52b can be improved, and the upper ends of the ribs 52a and 52b are joined in the vicinity of the mounting flange 85. Therefore, the mounting rigidity of the mounting flange 85 can be improved.

  The first drain hole 80 is formed at the other end of the housing 52, communicates with the first valve hole 60, and has 1 on each side around the first advance side passage 72 and the first retard side passage 74. It is provided one by one. Similar to the first drain hole 80, the second drain hole 82 is formed at the other end of the housing 52, communicates with the second valve hole 62, and has a second advance side passage 76 and a second retard side passage. One is provided on each side of 78.

  Then, excess hydraulic oil in the variable valve timing mechanism is discharged from the first and second valve holes 60 and 62 to the drain chamber 84 formed in the housing 52 through the first and second drain holes 80 and 82. Then, the oil is discharged to an oil pan (not shown) of the engine 10 through a drain oil passage 87 (see FIG. 2) provided in the cylinder head 28.

  On the other hand, a plurality of mounting flanges 85 are provided outside the housing 52. A fixing bolt 86 is inserted into a hole formed in the mounting flange 85 and screwed into the screw hole 48 of the cylinder head 28. A valve unit 34 including a housing 52 is fixed to the cylinder head 28.

  As shown in FIGS. 8 to 10, the first control valve 54 is fixed to the cylindrical sleeve 88a, a spool 90a slidably fitted into the sleeve 88a, and the sleeve 88a. A solenoid portion 92a that displaces the spool 90a in the axial direction (in the direction of arrow A in FIG. 8) under the action, and the spool 90a is attached toward the solenoid portion 92a (in the direction of arrow B in FIG. 8). And a spring 94a.

  Further, as shown in FIG. 9, the diameter D1 of the solenoid portion 92a is formed larger than the diameter D2 of the sleeve 88a. That is, the solenoid portion 92a becomes the large diameter portion in the first control valve 54, and the sleeve 88a including the spool 90a becomes the small diameter portion.

  The second control valve 56 is formed in the same shape as the first control valve 54, and is fixed to the cylindrical sleeve 88b, a spool 90b slidably fitted inside the sleeve 88b, and the sleeve 88b. A solenoid portion 92b that displaces the spool 90b in the axial direction (in the direction of arrow A in FIG. 8) under energization, and the spool 90b toward the solenoid portion 92b (in the direction of arrow B in FIG. 8). And an urging spring 94b.

  As shown in FIG. 9, the diameter D1 of the solenoid portion 92b is formed larger than the diameter D2 of the sleeve 88b. The solenoid portion 92b becomes a large diameter portion in the second control valve 56, and the spool 90b is The sleeve 88b to be included becomes a small diameter portion.

  In the first and second control valves 54 and 56, the solenoid portions 92a and 92b are respectively excited based on a control signal from a controller (not shown), and the spools 90a and 90b are separated from the solenoid portions 92a and 92b (see FIG. 8, the spools 90 a and 90 b are displaced along the axial direction against the resilient force of the springs 94 a and 94 b.

  The sleeves 88a and 88b include inflow ports 96a and 96b disposed in the center along the axial direction, and advance ports 98a and 98b and retard ports 100a and 100b provided on both sides of the inflow ports 96a and 96b. And a pair of drain ports 102a and 102b provided on both sides of the advance ports 98a and 98b and the retard ports 100a and 100b around the inflow ports 96a and 96b. The inflow ports 96a and 96b, the advance ports 98a and 98b, the retard ports 100a and 100b, and the drain ports 102a and 102b are provided at predetermined intervals along the axial direction of the sleeves 88a and 88b.

  On the other hand, the spools 90a and 90b include central grooves 104a and 104b formed at the center along the axial direction, a pair of land portions 106a and 106b adjacent to both sides of the central grooves 104a and 104b, and the land portions 106a. , 106b and a pair of grooves 108a, 108b formed on both sides. The central grooves 104a and 104b and the grooves 108a and 108b are recessed annularly at a predetermined depth with respect to the outer peripheral surfaces of the land portions 106a and 106b.

  The sleeve 88a and the spool 90a constituting the first control valve 54 are inserted into the first valve hole 60 of the housing 52, and the rotational phase of the intake camshaft 20 is changed under the switching action of the first control valve 54. The first control valve 54 is fixed via a bolt 111 inserted into the hole of the bracket 110a in a state where the end of the solenoid 92a is in contact with the side surface of the housing 52.

  Similarly, the sleeve 88b and the spool 90b constituting the second control valve 56 are inserted into the second valve hole 62 of the housing 52, and the rotational phase of the exhaust camshaft 22 is changed under the switching action of the second control valve 56. Is done. The second control valve 56 is fixed via a bolt 111 inserted through the hole of the bracket 110b in a state where the end of the solenoid 92b is in contact with the side surface of the housing 52.

  That is, the first control valve 54 and the second control valve 56 are mounted so that the sleeves 88a and 88b and the spools 90a and 90b are alternately arranged with respect to the housing 52 (see FIGS. 9 and 10). Accordingly, for example, as in the valve unit 34a shown in FIG. 11, the first control shown in FIG. 9 is compared with the case where the first and second control valves 54a and 56a are arranged on the same side surface of the housing 52c. An interval S1 between the center line L1 of the valve 54 and the center line L2 of the second control valve 56 is set to an interval S2 between the center line L1 of the first control valve 54a and the center line L2 of the second control valve 56a. It arrange | positions so that it may become small (S1 <S2).

  In other words, since the solenoid parts 92a and 92b having a large diameter do not adjoin each other, it is possible to arrange the sleeves 88a and 88b having a small diameter so that their center lines L1 and L2 are close to each other. As a result, the distance S1 between the first control valve 54 and the second control valve 56 is reduced, and the height direction of the valve unit 34 (which is perpendicular to the axis of the first and second control valves 54, 56) ( Miniaturization can be achieved in the direction of arrow E).

  The filter 58 is formed in a substantially rectangular cross section corresponding to the opening of the supply passage 68 and has a mesh portion 112 formed in a mesh shape, and a seal portion 114 provided so as to surround the outer peripheral side of the mesh portion 112. Including. The mesh portion 112 is formed in a sheet shape having a plurality of holes, and the seal portion 114 is formed of an O-ring integrally held on the outer edge portion of the mesh portion 112. The filter 58 is disposed so that the mesh portion 112 faces the supply passage 68, is fitted into the recess 68 a of the supply passage 68, and the seal portion 114 is provided at the opening of the supply passage 68. When mounted on the groove 116 and the valve unit 34 is mounted on the side surface of the cylinder head 28, it is sandwiched between the one end surface of the housing 52 and the side surface without rattling. In this case, the filter 58 is sandwiched between the cylinder head 28 and the housing 52 in close contact with each other without a gap. As a result, the liquid tightness between the supply passage 68 and the supply oil passage 38 is maintained, and the hydraulic oil supplied from the supply oil passage 38 does not leak.

  The engine 10 to which the electromagnetic valve mounting structure according to the embodiment of the present invention is applied is basically configured as described above. Next, the operation and effects thereof will be described.

  First, an operation when the opening / closing timing of the intake valve 33a is shifted to the advance side will be described with reference to FIG. When the opening / closing timing of the intake valve 33a is shifted to the advance side, the solenoid portion 92a of the first control valve 54 is driven based on a control signal from a controller (not shown), and the spool of the first control valve 54 is driven. By moving 90a from the intermediate position in a direction away from the solenoid 92a (in the direction of arrow C1), the inflow port 96a and the advance port 98a of the first control valve 54 are communicated with each other, and the drain The port 102a communicates with the retard port 100a.

  As a result, hydraulic oil is supplied to the supply oil passage 38 of the cylinder head 28 by the oil pump mounted on the engine 10, and the hydraulic oil passes through the filter 58 to the supply passage 68 and the communication passage 70 a of the valve unit 34. It flows and is supplied to the inflow port 96a. Then, after this hydraulic oil flows from the communicating inflow port 96a to the first advance side passage 72, the advance passage for the first oil passage 40 formed in the cylinder head 28 shown in FIG. After passing through 44a, it flows into an advance side hydraulic chamber (not shown) formed in the actuator of the variable valve timing mechanism.

  At this time, the hydraulic oil in the retard side hydraulic chamber of the actuator flows to the retard passage 46a of the first oil passage 40 and the retard port 100a of the first control valve 54, and then from the drain port 102a to the first drain. The oil is discharged to the drain oil passage 87 of the cylinder head 28 through the hole 80.

  Next, when the opening / closing timing of the intake valve 33a is shifted to the retard side, the solenoid portion 92a of the first control valve 54 is deenergized based on a control signal from a controller (not shown), and the spring 94a is released. Under the action, the spool 90a of the first control valve 54 is moved from the intermediate position toward the solenoid portion 92a (in the direction of arrow C2). As a result, the inflow port 96a and the retard port 100a communicate with each other, and the drain port 102a and the advance port 98a communicate with each other. Then, after the hydraulic fluid supplied from the supply passage 68 to the inflow port 96a through the communication passage 70a flows to the first advance side passage 72, the first oil formed in the cylinder head 28 shown in FIG. It flows into a retarded hydraulic chamber (not shown) formed in the actuator of the variable valve timing mechanism through the retarded passage 46a of the path 40.

  At this time, after the hydraulic oil in the advance side hydraulic chamber (not shown) of the actuator flows to the advance passage 44a of the first oil passage 40 and the advance port 98a of the first control valve 54, the drain port The oil is discharged from 102 a through the first drain hole 80 to the drain oil passage 87 of the cylinder head 28.

  The rotational phase of the intake camshaft 20 is shifted to the advance side or the retard side by the hydraulic oil introduced into the advance side hydraulic chamber or the retard side hydraulic chamber of the actuator, and is passed through the intake cam shaft 20. The opening / closing timing of the intake valve 33a is changed.

  Thus, the filter 58 is provided so as to face the supply oil passage 38 and the supply passage 68 when the hydraulic oil is supplied from the supply oil passage 38 of the cylinder head 28 to the supply passage 68 of the valve unit 34. Therefore, the foreign matter in the hydraulic oil is surely removed by the mesh portion 112 of the filter 58. That is, foreign matter is prevented from entering the valve unit 34 having the first and second control valves 54 and 56. In other words, foreign matters and the like can be removed on the upstream side of the first and second control valves 54 and 56.

  On the other hand, the action when the opening / closing timing of the exhaust valve 33b is shifted to the advance side or the retard side is substantially the same as the case where the opening / closing timing of the intake valve 33a is shifted to the advance side or the retard side. Instead of driving the first control valve 54 when changing the opening / closing timing of the intake valve 33a, the second control valve 56 is driven, and an inflow port 96b to which hydraulic oil is supplied and an advance port 98b or a retard port The state of communication with 100b is switched, and the hydraulic oil is supplied to an advance-side hydraulic chamber or a retard-side hydraulic chamber (not shown) formed in the actuator of the variable valve timing mechanism. Thereby, the rotational phase of the exhaust camshaft 22 may be shifted to the advance side or the retard side, and the opening / closing timing of the exhaust valve 33b may be changed. Note that the detailed description of the case where the opening / closing timing of the exhaust valve 33b is shifted to the advance side or the retard side is omitted.

  As described above, in the present embodiment, the first and second valve holes 60 and 62 are formed on both side surfaces of the housing 52 that constitutes the valve unit 34, are spaced apart from each other by a predetermined distance, and are formed substantially in parallel. The sleeves 88a and 88b and the spools 90a and 90b of the first and second control valves 54 and 56 are inserted into the first and second valve holes 60 and 62, respectively. As a result, the solenoid portions 92a and 92b of the first and second control valves 54 and 56 having an enlarged diameter with respect to the sleeves 88a and 88b are disposed separately on both side surfaces of the housing 52. The center line L1 of the first control valve 54 and the center line L2 of the second control valve 56 can be arranged close to each other.

  As a result, the center-to-center distance S1 between the first and second control valves 54 and 56 can be reduced, and the valve unit 34 including the first and second control valves 54 and 56 can be downsized. Accordingly, it is possible to promote space saving in the engine room, and the limited space in the engine room can be effectively used.

  In addition, the sleeves 88a and 88b of the first and second control valves 54 and 56 are respectively inserted into the first and second valve holes 60 and 62 formed on both side surfaces of the housing 52, so that the assembling work can be easily performed. It can be performed. Therefore, it is possible to improve the assembling workability of the valve unit 34 including the first and second control valves 54 and 56.

  Further, in the above-described embodiment, the case where the first and second control valves 54 and 56 are mounted on the housing 52 of the valve unit 34 has been described. However, the present invention is not limited to this. You may make it mount | wear with respect to the chain cover 32 which covers the side part of the engine 10 directly. In this case, it is easy to form the mounting portions of the first and second control valves 54 and 56 and the oil passage through which the hydraulic oil flows, and the manufacturing process and cost can be reduced. Further, since the first and second control valves 54 and 56 can be easily attached and detached, the maintainability can be improved.

  Furthermore, the center line L1 of the first control valve 54 and the center line L2 of the second control valve 56 are brought close to each other, and the interval S1 between the center line L1 and the center line L2 is reduced, thereby reducing the first valve hole. Since the length of the communication path 70b that communicates the 60 and the second valve hole 62 can be set short, it is possible to suppress pressure loss when hydraulic fluid flows through the communication path 70b.

  Next, a valve unit 150 to which the electromagnetic valve mounting structure according to the modification is applied will be described with reference to FIG. In addition, the same referential mark is attached | subjected to the component same as the valve unit 34 which concerns on this Embodiment mentioned above, and the detailed description is abbreviate | omitted.

  In the valve unit 150, a housing 152 is formed in a substantially rectangular shape in cross section, and a valve hole (through hole) 154 is penetrated so as to open at both ends thereof. The valve hole 154 penetrates in a straight line along the longitudinal direction (arrow C1, C2 direction) of the housing 152, and the first control valve 54 is mounted from one side (arrow C2 direction) of the housing 152 to the other side. The second control valve 56 is mounted from the side (arrow C1 direction). The valve hole 154 is formed with the same diameter along the axial direction, and the length along the axial direction is the sleeve 88a, 88b of the first and second control valves 54, 56 inserted therein. It is set longer than the length including the longitudinal direction.

  Further, inside the housing 152, a supply passage 156 to which hydraulic oil is supplied from the cylinder head 28 (see FIG. 2), and a communication passage 158 that communicates with the supply passage 156 and extends toward the valve hole 154 side. Branch passages 160a and 160b connected to the communication passage 158, branching into a bifurcated shape, extending along the longitudinal direction of the housing 152 (in the directions of arrows C1 and C2), and then connected to the valve hole 154, respectively. Have

  One branch passage 160 a extends from the communication passage 158 substantially in parallel with the first control valve 54 and communicates with the first control valve 54 side in the valve hole 154. The other branch passage 160 b extends from the communication passage 158 substantially in parallel with the second control valve 56 and communicates with the second control valve 56 side in the valve hole 154. In addition, a drain hole 162 that is introduced into the valve hole 154 and discharges excess hydraulic oil to the outside is formed at a substantially central portion along the axial direction of the valve hole 154.

  As described above, the valve hole 154 in which the first and second control valves 54 and 56 are mounted is made common and formed in a straight line along the axial direction of the housing 152 (the directions of the arrows C1 and C2). The center lines L1 and L2 of the first and second control valves 54 and 56 can be arranged coaxially, and the solenoid parts 92a and 92b having large diameters are not adjacent to each other. Miniaturization can be achieved in the height direction (arrow E direction) of the valve unit 150 that is orthogonal to the axis of the first and second control valves 54 and 56.

  Further, since a single valve hole 154 may be formed in the housing 152, man-hours and manufacturing costs for processing the valve hole 154 can be reduced.

  The electromagnetic valve mounting structure according to the present invention is not limited to the above-described embodiment, and various configurations can be adopted without departing from the gist of the present invention.

1 is a schematic configuration diagram of an engine including a valve unit to which a solenoid valve mounting structure according to an embodiment of the present invention is applied. FIG. 2 is an enlarged exploded perspective view showing a state where the valve unit of FIG. 1 is detached from a cylinder head. It is the single-piece | unit perspective view seen from the one end part side which opened the valve unit in FIG. FIG. 4 is an exploded perspective view of the valve unit shown in FIG. 3. It is a front view of the valve unit shown in FIG. FIG. 4 is a half sectional perspective view of a housing constituting the valve unit of FIG. 3. It is sectional drawing along the VII-VII line of FIG. FIG. 4 is a longitudinal sectional view of first and second control valves shown in FIG. 3. FIG. 9 is a partial cross-sectional view of the valve unit showing a state in which the first and second control valves of FIG. 8 are mounted on a housing. It is an expanded sectional view of the valve unit shown in FIG. It is a partial cross section figure of the valve unit which shows a comparative example. It is a partial cross section figure of the valve unit concerning a modification.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Engine 12 ... Crankshaft 28 ... Cylinder head 32 ... Chain cover 34, 34a, 150 ... Valve unit 52, 52c, 152 ... Housing 54, 54a ... 1st control valve 56, 56a ... 2nd control valve 58 ... Filter 60 ... 1st valve hole 62 ... 2nd valve hole 68, 156 ... Supply passage 70a, 70b, 158 ... Communication passage 88a, 88b ... Sleeve 90a, 90b ... Spool 92a, 92b ... Solenoid part 96a, 96b ... Inflow port 98a, 98b ... Advance ports 100a, 100b ... Delay ports 102a, 102b ... Drain port 154 ... Valve holes 160a, 160b ... Branch passage 162 ... Drain holes

Claims (3)

In an electromagnetic valve mounting structure for mounting a plurality of electromagnetic valves that are mounted on an engine and that control the supply state of hydraulic oil to a variable valve timing mechanism that can change opening and closing timings of intake and exhaust valves provided in the engine,
The plurality of solenoid valves have a large diameter portion and a small diameter portion adjacent to the large diameter portion along the axial direction,
On the other hand and the other solenoid valve, with each other in the axial line is disposed so as to be substantially parallel, mounting et is the opposite direction to the small diameter portion of each other are close to the small diameter portion, the solenoid valve A mounting structure for an electromagnetic valve, wherein the electromagnetic valve is provided so as to overlap each other in a direction orthogonal to the axis . The mounting structure according to claim 1,
The electromagnetic valve mounting structure, wherein the plurality of electromagnetic valves are provided on a cover member that covers a side portion of the engine. In the mounting structure according to any one of claims 1 and 2,
The large-diameter portion is a solenoid portion that is excited under an energization action of an electric current, and the small-diameter portion is a sleeve in which a spool that is displaced along the axial direction is energized under the excitation action of the solenoid portion. The solenoid valve mounting structure.

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