JP5771067B2 - Solenoid valve and front fork - Google Patents

Description

  The present invention relates to improvements in solenoid valves and front forks.

  Conventionally, as a solenoid valve, a housing having a hollow portion and a port communicating with the hollow portion, a spool valve that is slidably inserted into the hollow portion, a spool spring that urges the spool valve, and a spool spring There is known one provided with a solenoid that drives a spool valve against the urging force (see, for example, Patent Document 1).

  In such a solenoid valve, the spool valve is driven by the solenoid with respect to the housing, the port is opened and closed with the outer periphery of the spool valve facing the port, or the degree of opening of the port is adjusted, so that the flow path area If this is provided in the middle of the passage through which the hydraulic oil passes when the shock absorber extends and contracts, the flow resistance given to the flow of hydraulic oil passing through the passage can be made variable. The damping force of the vessel can be adjusted.

JP 2010-19319 A

  Since the solenoid valve can change the flow path area with good response to the command to change the flow path area, for example, if it is incorporated in the suspension of a vehicle, the damping force of the shock absorber can be adjusted with good response. Make active control such as skyhook control easy.

  By the way, in the conventional solenoid valve, the fluid force acts on the spool valve by the flow of the hydraulic oil that passes through the spool valve. Specifically, this fluid force acts to prevent the spool valve from being driven when the spool valve is driven in a direction in which the spool port is blocked by the inner peripheral surface of the housing. In other words, when trying to reduce the flow path area, a fluid force for expanding the flow path area acts on the spool valve.

  Here, considering the case where the solenoid valve is incorporated in a shock absorber built in the front fork of the saddle vehicle, the shock absorber built in the front fork of the saddle vehicle has a stroke amount compared to the shock absorber used in a four-wheeled vehicle. Since the amount of oil passing through the solenoid valve increases, a large fluid force acts on the spool valve due to the flow of hydraulic oil passing through the spool valve. As described above, when a solenoid valve is incorporated in a shock absorber built in a front fork of a saddle-ride vehicle, it is necessary to use a solenoid capable of exerting thrust sufficient to overcome the fluid force in order to adjust the flow path area. There is a problem that the solenoid becomes larger and the mounting property on the saddle vehicle is impaired, and the cost is increased and the economy is also impaired.

  Accordingly, the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a solenoid valve capable of actively controlling damping force adjustment by enabling the use of a small solenoid at low cost. In addition, it is possible to use a small solenoid at a low cost, and to provide a front fork capable of actively controlling the damping force adjustment.

In order to achieve the above-described object, the problem-solving means of the present invention includes a spool valve having an empty portion and a spool port that opens from the outer periphery to the empty portion, and one of the spool ports in sliding contact with the outer periphery of the spool valve. And a solenoid that drives the spool valve in the axial direction, and a flow path is formed with the empty portion as the upstream and the spool port as the downstream. A solenoid valve for adjusting a flow path area, comprising: a spool spring that urges the spool valve in an axial direction; and a pair of shutter springs that elastically support the shutter member across both axial ends thereof; There a plurality of pores, at least some of these pores are offset in the axial direction, the mass Mb of the spool valve, the scan Spring multiplier Kb of Lumpur spring, combined spring constant Ks of the mass Ms and the shutter springs of said shutter member, characterized in that it is set to satisfy a relationship of Mb / Kb = Ms / Ks.

  According to the solenoid valve and the front fork of the present invention, it is possible to use a small solenoid at a low cost, and the damping force adjustment can be actively controlled.

It is sectional drawing of the solenoid valve and front fork in one Embodiment. It is an expanded sectional view of the solenoid valve in one embodiment. It is a partial expanded sectional view of the spool valve of the solenoid valve in one embodiment. It is a partial expanded sectional view of the spool valve and shutter member of the solenoid valve in one embodiment.

  The present invention will be described below based on the embodiments shown in the drawings. As shown in FIGS. 1 to 3, the solenoid valve 1 according to the embodiment includes a spool valve 7 having a hollow portion 21a and a plurality of pores 23a that form a spool port that opens from the outer periphery to the hollow portion 21a. The shutter member 9 is slidably brought into contact with the outer periphery of the spool valve 7 to block a part or all of the pores 23a, and the solenoid 8 drives the spool valve 7 in the axial direction.

  In this embodiment, the solenoid valve 1 can adjust the extension-side damping force generated when the shock absorber D built in the front fork F extends.

  The front fork F includes a vehicle body side tube 10 connected to a vehicle body (not shown) of a straddle vehicle such as a two-wheeled vehicle, and an axle shaft that is connected to an axle (not shown) of the saddle vehicle and is slidably fitted into the vehicle body side tube 10. A side tube 11, a shock absorber D interposed between the vehicle body side tube 10 and the axle side tube 11, and a solenoid valve 1 are configured.

  Specifically, the shock absorber D includes a cylinder 2 and a piston that is slidably inserted into the cylinder 2 and divides the cylinder 2 into an extension side chamber R1 and a pressure side chamber R2 filled with a liquid such as hydraulic oil. 3, a piston rod 4 inserted into the cylinder 2 and having one end connected to the piston 3, and a damping force adjusting passage 5 that allows passage of liquid only when the shock absorber D is extended, and a solenoid valve 1 is provided in the middle of the damping force adjusting passage 5 to adjust the extension side damping force generated when the shock absorber D extends.

  The other end of the piston rod 4 is connected to the vehicle body side tube 10 via the housing 6 in which the spool valve 7 of the solenoid valve 1 is accommodated, and the cylinder 2 is connected to the axle side tube 11 so that the shock absorber D is connected. Is housed in a space L that is inside the front fork F closed by the vehicle body side tube 10 and the axle side tube 11 while being interposed between the vehicle body side tube 10 and the axle side tube 11. In the present embodiment, the front fork F is an inverted front fork in which the axle side tube 11 is inserted into the vehicle body side tube 10, but on the contrary, the vehicle body side tube 10 is connected to the axle side tube 11. It may be an upright front fork to be inserted.

  Further, a suspension spring 12 is interposed between the piston rod 4 and the cylinder 2 of the shock absorber D. The suspension spring 12 connects the vehicle body side tube 10 and the axle side tube 11 via the shock absorber D. The elastic force is exerted in the direction in which the shock absorber 1 is extended, that is, in the direction in which the shock absorber 1 is extended, and the vehicle body of the saddle riding vehicle (not shown) is elastically supported by the suspension spring 12.

  Further, a reservoir R is formed in the space L and outside the cylinder 2. Further, as shown in FIG. 1, the shock absorber D includes a damping passage 13 provided in the piston 3, which communicates the extension side chamber R <b> 1 and the pressure side chamber R <b> 2 and provides resistance to the flow of liquid passing through the piston 3. A bottom member 14 having a pressure-side damping passage 15 provided at the lower end and providing resistance to the flow of liquid from the pressure-side chamber R2 to the reservoir R, and a suction passage 16 allowing only the flow of liquid from the reservoir R to the pressure-side chamber R2. It has. The extension side chamber R1 and the pressure side chamber R2 are filled with a liquid such as hydraulic oil as a liquid, and the reservoir R is filled with the liquid and the gas.

  In more detail, the cylinder 2 is being fixed to the bottom part of the axle side tube 11 formed in the bottomed cylinder shape via the bottom member 14 fitted by the lower end. A rod guide 17 is provided at the upper end of the cylinder 2 to support the piston rod 4 so as to be slidable. The piston rod 4 includes a piston rod body 4a having a hole 4b penetrating in the vertical direction in FIG. 1 along the axial direction, and a piston connecting portion that is fixed to the lower end of the piston rod body 4a in FIG. 4c, and the tip that is the upper end in FIG. 1 is fixed to the upper end of the vehicle body side tube 10 via the housing 6 that houses the spool valve 7 in the solenoid valve 1. The piston connecting portion 4c includes a communication passage 4d that communicates the hole 4b and the extension side chamber R1, and a check valve that is provided in the middle of the communication passage 4d and that allows only a liquid flow from the extension side chamber R1 toward the hole 4b. 4e, and the annular piston 3 is fixed to the lower end in FIG.

  A suspension spring 12 is interposed between the rod guide 17 and a cylindrical spring receiver 18 provided on the outer periphery of the housing 6, and the shock absorber D is urged in the extension direction by the suspension spring 12. The container D is also urged in the extending direction by the suspension spring 12.

  The piston 3 is fixed to the lower end in FIG. 1 of the piston rod 4, and the damping passage 13 provided in the piston 3 is provided in the middle of the passage 13a and the passage 13a that connects the extension side chamber R1 and the pressure side chamber R2. A damping valve 13b is provided to provide resistance to the flow of liquid passing therethrough. In this case, the damping valve 13b is a throttle valve or the like, and the damping passage 13 has a bidirectional flow of the liquid flowing from the expansion side chamber R1 to the compression side chamber R2 and the flow of the liquid from the compression side chamber R2 to the expansion side chamber R1. Although the flow is allowed, two or more passages are provided, and a damping valve that allows only the flow of the liquid from the extension side chamber R1 to the pressure side chamber R2 is provided in a part of the passages, and the pressure side is provided in the other passages. A damping valve that allows only the flow of liquid from the chamber R2 toward the extension side chamber R1 may be provided.

  The pressure-side damping passage 15 formed in the bottom member 14 resists the flow of the liquid passing through the passage 15a that connects the pressure-side chamber R2 and the reservoir R, and allowing only the flow of the liquid from the pressure-side chamber R2 to the reservoir R. And a one-way passage allowing only the flow of liquid from the pressure side chamber R2 to the reservoir R. On the other hand, the suction passage 16 formed in the bottom member 14 includes a passage 16a that connects the reservoir R and the pressure side chamber R2, and a check valve 16b that allows only the flow of liquid from the reservoir R to the pressure side chamber R2. This is a one-way passage that allows only the flow of liquid from the reservoir R to the pressure-side chamber R2 in the opposite direction to the pressure-side attenuation passage 15. In the shock absorber 1, since the compression side damping force can be generated by the damping valve 15b, a passage allowing only the flow of the liquid from the compression side chamber R2 to the extension side chamber R1 is provided as described above. In this case, it is not necessary to provide a damping valve in the passage.

  Next, the solenoid valve 1 will be described. In the case of this embodiment, the solenoid valve 1 is provided in the middle of the damping force adjusting passage 5, and the spool valve 7, the shutter member 9 slidably contacting the outer periphery of the spool valve 7, and the spool valve 7 in the axial direction. And a solenoid 8 to be driven. These are accommodated in a cylindrical housing 6.

  As shown in FIGS. 1 and 2, the housing 6 has a cylindrical shape. The housing 6 opens from the lower end in FIG. 2 and is formed inside, and opens from the side and communicates with the hollow portion 6a. A housing port 6b, a housing portion 6c that opens from the upper end in FIG. 2 and communicates with the hollow portion 6a and has a larger diameter than the hollow portion 6a and accommodates the solenoid 8; a flange 6d provided on the outer periphery of the upper end; A small-diameter portion 6e and a step portion 6f provided with a small diameter and a groove 6g provided along the axial direction on the outer periphery of the small-diameter portion 6e are configured. In this case, the housing port 6b extends in the radial direction. It extends and communicates the groove 6g and the hollow portion 6a.

  A hollow portion 6a of the housing 6 is provided with a screw portion 6i below the small inner diameter portion 6h provided with a lower diameter in FIG. 2 and a screw portion on the outer periphery of the upper end of the piston rod 4. 4f is provided, and the screw part 4f at the upper end of the piston rod 4 can be screwed into the screw part 6i so that the housing 6 and the piston rod 4 can be screwed together. In this embodiment, a nut 19 is screwed onto the screw portion 4f, and the upper end of the nut 19 in FIG. 2 is brought into contact with the lower end of the housing 6 in FIG. Thus, consideration is given so that the screw portion 6i and the screw portion 4f are not loosened.

  When the housing 6 is coupled to the piston rod 4 in this way, the hollow portion 6a is coaxially connected in series with the hole 4b of the piston rod 4, and the hollow portion 6a is connected via the hole 4b and the communication path 4d. And communicated with the extension side chamber R1 in the shock absorber D. Further, the hollow portion 6a communicates with the reservoir R described above via the housing port 6b and the groove 6g. Therefore, in the case of this embodiment, the damping force adjusting passage 5 is constituted by the communication passage 4d, the hole 4b, the hollow portion 6a, the housing port 6b, and the groove 6g described above, and the extension side chamber R1 and the reservoir R Is communicated. Further, in this case, the damping force adjusting passage 5 is configured to permit only passage of liquid from the extension side chamber R1 to the reservoir R by the check valve 4e. The check valve for setting the damping force adjusting passage 5 to one-way is not provided in the piston coupling portion 4c but may be provided in another location. Specifically, for example, in the hole 4b of the piston rod body 4a Or may be provided at the opening end of the hole 4b at the upper end in FIG. 1 of the piston rod body 4a.

  A collar 20 that supports the upper end of a cylindrical spring receiver 18 that supports the upper end of the suspension spring 12 is fitted to the outer periphery of the small-diameter portion 6e of the housing 6, and the collar 20 is disposed so as to cover the port 6b. Therefore, the groove 6g is provided to ensure communication between the port 6b and the reservoir R. However, if the port 6b does not interfere with the collar 20 or the spring receiver 18, the groove 6g can be omitted. is there.

  Further, a screw portion 6 j is provided on the upper outer periphery of the housing 6 in FIG. 2 so that the housing 6 can be screwed to the opening end of the vehicle body side tube 10. The piston rod 4 can be connected to the vehicle body side tube 10.

  Subsequently, the shutter member 9 has a cylindrical shape and is inserted into the hollow portion 6a of the housing 6 so as to be slidable in the axial direction. The shutter-side annular groove 9a is formed on the outer periphery along the circumferential direction. An inner circumferential annular groove 9b formed in the circumferential direction along the circumference, and a shutter port 9c communicating the shutter side annular groove 9a and the inner circumferential annular groove 9b are provided.

  The shutter member 9 is sandwiched between a pair of shutter springs 25 and 26 at both axial ends as upper and lower ends, and in a state where there is no load, the urging force of the shutter springs 25 and 26 is balanced. Is positioned. The shutter spring 25 is interposed between an inner peripheral step 6k provided by forming a small inner diameter portion 6h below the hollow portion 6a of the housing 6 and the lower end of the shutter member 9 in FIG. The other shutter spring 26 is interposed between a case 30 in the solenoid 8 to be described later in detail and the upper end of the shutter member 9 in FIG. 2, and the shutter springs 25 and 26 are both contracted, The member 9 is urged from above and below.

  Therefore, since the shutter member 9 is elastically supported by the shutter springs 25 and 26, when the front fork F is vibrated with an external force, it vibrates in the vertical direction in FIG. In the stroke range, the axial length of the shutter-side annular groove 9a is always set so that the shutter-side annular groove 9a always faces the housing port 6b, and the shutter member 9 can block the housing port 6b. There is no such thing. Even if the shutter member 9 may block a part of the housing port 6b, the flow passage area here becomes equal to or larger than the maximum value of the flow passage area determined by the shutter member 9 and the spool valve 7. In other words, consideration is given so as not to give a larger resistance on the housing port 6b side than the diaphragm formed by the shutter member 9 and the spool valve 7.

  As described above, the shutter member-side annular groove 9a communicated with the shutter port 9c along the circumferential direction is provided on the outer periphery of the shutter member 9, so that the shutter member 9 moves in the axial direction with respect to the housing 6. Further, the communication between the shutter port 9c and the housing port 6b can be ensured, and there is an advantage that the communication between the shutter port 9c and the housing port 6b can be ensured by subjecting the shutter member 9 to a peripheral processing that is easy to process. . Instead of providing the shutter-side annular groove 9a, a housing-side annular groove is provided on the inner periphery of the hollow portion 6a of the housing 6 along the circumferential direction and communicated with the housing port 6b, and this always faces the shutter port 9c. Thus, communication between the shutter port 9c and the housing port 6b may be ensured.

  Further, the upper and lower ends of the shutter member 9 are each set to have a small outer diameter, and the shutter springs 25 and 26 are arranged on the outer periphery of the small diameter portion, and the shutter member 9 and the spool valve 7 are arranged. The fitting length is increased to ensure stable relative sliding between the shutter member 9 and the spool valve 7.

  Next, the spool valve 7 is slidably inserted into the shutter member 9, and is housed in the hollow portion 6a of the housing 6 together with the shutter member 9 so as to be movable in the vertical direction in FIG. Yes. Specifically, in this case, the spool valve 7 includes a spool valve main body 21 and a cylindrical magnetic member 22 that is fitted to and integrated with the other end of the spool valve main body 21. The spool valve body 21 is made of a material such as synthetic resin, aluminum, aluminum alloy, or magnesium alloy, and is made of a material having a specific gravity smaller than that of the magnetic member 22. In addition, when using a synthetic resin, it is preferable to use a material that is highly slidable and resistant to wear. For example, polyacetal, polybutylene terephthalate, polyphenylene sulfide, polyimide, polyamideimide, polyether ketone can be used. When the working liquid is oil, a phenol resin can be used in addition to the above.

  The spool valve main body 21 receives the pressure of the liquid passing through the damping force adjusting passage 5 at the lower end in FIG. 2 which is the opposite end of the solenoid opposite to the side facing the solenoid 8. A hollow portion 21a that opens from the solenoid side end, a plurality of pores 23a that form a spool port that opens from the outer periphery and communicates with the void portion 21a, and a solenoid that communicates with the void portion 21a and faces the solenoid 8 of the spool valve 7 A pressure introducing hole 21c for guiding the pressure of the liquid is provided on the upper end side in FIG. 2, which is the side end side, and a fitting portion 21d formed with a small outer diameter at the solenoid side end.

  The magnetic member 22 is formed of a magnetic material such as iron, nickel, cobalt, an alloy containing these, or ferrite, and has a cylindrical shape. The base 22a on the upper side in FIG. 2 and the bottom from the base 22a in FIG. And a cylindrical socket 22b that is thinner than the base 22a and has a single outer diameter. The fitting portion 21e of the spool valve main body 21 is fitted into the socket 22b. When combined, the spool valve body 21 is integrated. When the magnetic member 22 is fitted, the spool valve main body 21 and the magnetic member 22 are firmly integrated by, for example, press-fitting. When the spool valve main body 21 is formed of a metal material, it may be shrink-fitted when the magnetic member 22 is fitted. The integration can also be performed by applying an adhesive to the fitting portion.

  Specifically, as shown in FIG. 3, the pores 23a are fitted into the four through holes 21b that lead the pore member 23 having a large number of pores 23a from the outer periphery of the spool valve body 21 to the empty portion 21a. By combining, the spool valve 7 is provided. In this case, each pore member 23 is a sintered vent in this case, and is provided with 216 pores 23a, and each of the pores 23a communicates with the inside and outside of the spool valve body 21 independently. ing. In this case, 16 rows are formed by shifting in the circumferential direction a row formed by arranging 8 to 16 pores 23a in the axial direction of the spool valve 7. As described above, some of the pores 23a are arranged in the circumferential direction. However, one or more pores 23a are always provided so as to be shifted in the axial direction of the spool valve 7. It is also possible to provide a plurality of pores in the spool valve body 21 without depending on the pore member 23. However, it is easier to use a sintered vent having pores from the beginning than to make pores. In addition, the passage area and the number of installed pores 23a may be set so that the maximum flow passage area required in the solenoid valve 1 can be secured with at least all the pores 23a being opened.

  Then, when these pores 23a face the inner peripheral surface which is a part other than the inner peripheral annular groove 9b of the shutter member 9, they are blocked by the inner peripheral surface and are opposed to the inner peripheral annular groove 9b. Only open. Since the open pore 23a communicates with the shutter port 9c, it communicates with the housing port 6b via the shutter port 9c, and the damping force adjusting passage 5 is opened. In this embodiment, when the spool valve 7 is moved toward the solenoid 8, the number of pores 23 a that are blocked by the inner peripheral surface of the shutter member 9 is increased. By changing the position, the number of holes 23a to be blocked can be adjusted, and in this way, the degree of blocking of the spool port formed by the holes 23a can be changed. That is, when the spool valve 7 is moved to the solenoid 8 side, the number of pores 23a blocked by the inner peripheral surface of the shutter member 9 increases, and the flow path area in the solenoid valve 1 is reduced (the flow path is narrowed). Be able to. Since the pores 23a are arranged so that at least a part thereof is shifted in the axial direction as the moving direction of the spool valve 7, when the spool valve 7 is driven by the solenoid 8 as described above, the fine holes 23a are blocked by the shutter member 9. The number of holes 23a can be changed. That is, not all of the pores 23a are arranged in the circumferential direction of the spool valve 7, and some of them may be arranged in the circumferential direction, but at least the pores 23a that are axially displaced from each other are provided. It is done.

  When the liquid that is about to move from the extension side chamber R1 to the reservoir R via the damping force adjusting passage 5 passes through the solenoid valve 1, the damping force adjusting passage 5 is set to be one-way. 6 passes through the hollow portion 21a of the spool valve 7, the spool port formed by the pores 23a and the shutter port 9c in this order, and then passes through the housing port 6b and reaches the reservoir R. That is, the flow path in the solenoid valve 1 is formed by the empty portion 21a, the spool port, the shutter port 9c, and the housing port 6b. In the empty portion 21a and the spool port, the empty portion 21a is upstream of the flow path, and the spool port is It is downstream of the flow path.

  Thus, in the solenoid valve 1, the flow path area in the flow path configured as described above can be adjusted according to the relative position in the axial direction between the spool valve 7 and the shutter member 9. As a result of restricting the flow path, the inner circumferential surface of the shutter member 9 may be set so as to block all the pores 23a of the spool valve 7, that is, the spool port is completely closed to block the flow path. Alternatively, the spool port may be set not to be completely blocked by not blocking all of the pores 23a.

  Further, in this case, an inner circumferential annular groove 9b is provided on the inner periphery of the shutter member 9, and even if the spool valve 7 rotates in the circumferential direction with respect to the shutter member 9, the spool formed by the pores 23a regardless of the rotational position. The port and the shutter port 9c can communicate with each other, but the shutter member 9 and the spool valve 7 do not rotate relative to each other in the circumferential direction. This may be omitted.

  It should be noted that the shutter member 9 only needs to be able to adjust the degree of blocking of the spool port by making sliding contact with the outer periphery of the spool valve 7 so that the inner peripheral surface thereof is opposed to the pore 23a. Therefore, the shape is not particularly limited as long as the number of blocking of the pores 23a can be adjusted by sliding on the outer periphery of the spool valve 7 without providing a shutter port or the like.

  The solenoid 8 includes an inner cylinder 30a, an outer cylinder 30b, an inner cylinder 30a and an annular bottom portion 30c connecting the lower ends of the outer cylinder 30b in FIG. A cylindrical mold coil 31 which is formed by molding and accommodated between the outer cylinder 30b and the inner cylinder 30a, and a cylindrical and magnetic base which is inserted into the inner periphery of the mold coil 31 33, a nonmagnetic ring 32 that provides an annular gap between the base 33 and the inner cylinder 30 a of the case 30, an adjuster 34 that is screwed into the base 33, and an adjuster 34 and a spool valve 7. And a spool spring 35 to be mounted. The solenoid 8 can drive the spool valve 7 by energizing the coil 31a with the magnetic member 22 in the spool valve 7 as a movable iron core.

  The inner cylinder 30a of the case 30 has its inner diameter set so that the spool valve 7 can be movably inserted therein and smaller than the inner diameter of the hollow portion 6a, and is housed in the housing portion 6c of the housing 6. The movement of the spool valve 7 is not hindered, and the upper end of the shutter spring 26 in FIG. 2 can be supported. The inner diameter of the inner cylinder 30a may be set to a diameter that allows the spool valve 7 to slide.

  Further, the positioning of the case 30 in the radial direction with respect to the housing 6 may be performed by fitting the outer cylinder 30b and the housing portion 6c of the housing 6 or the inside of the hollow portion 6a of the housing 6 and the inner cylinder 30a of the case 30. When the spool valve 7 is brought into sliding contact with the circumference, the spool valve 7 can be used. The case 30 and the housing 6 are tightly sealed by an annular seal 36 interposed between the annular bottom 30c of the case 30 and the housing 6.

  The molded coil 31 includes a cylindrical connector 31d that houses a power supply terminal 31c for energizing the coil 31a. The connector 31d is integrated with the coil 31a by a molded resin 31b. By connecting the power supply terminal 31c in the connector 31d to an external power supply (not shown), the coil 31a can be energized from the outside.

  The base 33 has a cylindrical shape and is inserted into the inner periphery of the molded coil 31, and includes an annular convex portion 33a that protrudes toward the spool valve side on the outer periphery of the spool valve side end, which is the lower end in FIG. The outer periphery of the annular convex portion 33a is chamfered in a tapered shape. A nonmagnetic ring 32 formed of a material such as nonmagnetic stainless steel such as aluminum, copper, zinc, SUS305 or high manganese steel is interposed between the annular protrusion 33a and the inner cylinder 30a of the case 30. The nonmagnetic ring 32 is integrated with the case 30 and the base 33 by brazing or the like. The non-magnetic ring 32 forms a gap between the base 33 and the case 30 when the magnetic member 22 is attracted by the base 33 that is magnetized when the coil 31 a is energized, and the magnetic path passes through the magnetic member 22. In addition, the case 30 and the base 33 are integrated, and the space between the case 30 and the base 33 is also sealed.

  Further, an annular end ring 38 having a split 38a that allows the connector 31d to pass therethrough is laminated on the outer periphery of the base 33 and on the upper ends of the mold coil 31 and the case 30 in FIG. A nut member 37 is screwed to the inner periphery of the upper end in FIG. 2 which is the opening end of the housing portion 6 c of the end ring 38 from above in FIG. 2, and the mold coil 31 and the housing 6 are joined by the nut member 37 and the housing 6. The member is fixed to the housing 6 by sandwiching the case 30, the nonmagnetic ring 32 integrated with the case 30, and the base 33.

  In order to provide a gap between the base 33 and the inner cylinder 30 a of the case 30, a non-magnetic ring 32 is interposed, and a cylindrical filler ring is provided on the outer periphery of the inner cylinder 30 a of the case 30 and the outer periphery of the base 33. The case 30 and the base 33 may be integrated while providing a gap so that the non-magnetic ring 32 can be omitted. When using the filler ring, it is necessary to secure a fitting length with the filler ring, so that the axial length of the inner cylinder 30a of the case 30 is integrated with the case 30 and the base 33 by the nonmagnetic ring 32. Longer than. In other words, it is advantageous in that the total length of the non-movable part of the solenoid 8 can be shortened by adopting a structure in which the case 30 and the base 33 are integrated by the nonmagnetic ring 32.

  In turn, the adjuster 34 is axial and has a screw portion on the outer periphery of the base end, which is the upper end in FIG. 2, and is screwed onto the inner periphery of the cylindrical portion 33a of the base 33. A spool spring 35 is interposed between the lower end and the spool valve 7 in a compressed state.

  Here, the pressure introduction hole 21c in the spool valve 7 has a portion communicating with the hollow portion 21a set to a small diameter, and a step portion 21e is formed in the pressure introduction hole 21c, and the step portion 21e and the adjuster 34 are connected to each other. A spool spring 35 is interposed therebetween. Then, the adjuster 34 is advanced and retracted in the vertical direction in FIG. 2 which is the axial direction with respect to the base 33 in the manner of a feed screw, and the spool spring 35 is moved to the spool valve 7 by adjusting the compression length of the spool spring 35. The initial load applied by can be adjusted.

  In addition, since the structure which accommodates the spool spring 35 in the magnetic member 22 is employ | adopted, the accommodation space of the spool spring 35 is ensured and the full length of the solenoid 8 including the adjuster 34 can be shortened.

  When the solenoid 8 configured in this manner is energized to the coil 31a, the base 33 is magnetized to generate an attractive force for attracting the magnetic member 22, and the spool valve 7 is resisted against the urging force of the spool spring 35 as shown in FIG. It can be driven to the middle-upper side. The magnetic member 22 is thicker than the socket 22b in a state where the magnetic member 22 is attracted to the base 33, that is, in a state where the upper end in FIG. 2 of the base portion 22a of the magnetic member 22 is completely in contact with the inner periphery of the lower end in FIG. The base portion 22a of the case 30 is opposed to the inner cylinder 30a of the case 30 in the radial direction, and the socket 22b is fitted to the outer periphery of the other end of the spool valve main body 21 and faces the inner cylinder 30a. Therefore, consideration is given so that the magnetic flux density is not saturated due to the cross-sectional area of the magnetic path becoming too small and the attractive force is not reduced.

  Returning, as described above, when the spool valve 7 is biased by the spool spring 35, the spool valve 7 is positioned at the lowest position in the hollow portion 6a. Specifically, when the lower end of the spool valve 7 comes into contact with the inner peripheral step portion 6k of the housing 6, further movement of the spool valve 7 toward the piston rod 4 is restricted, and the spool valve 7 is moved to the lowest position. Positioned.

  In this lowest position, in this case, all of the pores 23a of the spool valve 7 face the inner circumferential annular groove 9b, and the housing port 6b is in communication with the shutter port 9c, so that the damping force adjusting passage 5 becomes an open state. That is, in this state, not all the pores 23a are blocked by the inner peripheral surface of the shutter member 9, so that the entire opening area of the pores 23a is effective and the spool port is fully opened.

  In this embodiment, the coil 31a is energized to suck the spool valve 7 toward the base 33, and the spool valve 7 is retracted upward in FIG. 2 in the hollow portion 6a. Are not opposed to the inner circumferential annular groove 9b but are blocked by the inner circumferential surface of the shutter member 9, so that the flow passage area can be reduced. Furthermore, by controlling the amount of movement of the spool valve 7 by the amount of current supplied to the coil 31a, the number of pores 23a that are blocked while facing the inner peripheral surface of the shutter member 9 can be adjusted.

  In this way, the spool valve 7 can be driven upward in FIG. 2 by energizing the coil 31a, and if the energization to the coil 31a is stopped, the spool valve 7 can be driven downward in FIG. Thus, the position of the spool valve 7 can be adjusted. The flow path can be narrowed by controlling the number of the pores 23a to be blocked according to the position of the spool valve 7, and the coil 31a is energized to give a flow of liquid that is going to pass through the flow path. The resistance can be increased compared to when the spool valve 7 is in the lowest position. In this case, the larger the amount of retraction of the spool valve 7, the greater the number of blocking of the pores 23a and the greater the degree of restriction of the flow path. On the contrary, the flow path area may be increased as the retracting amount of the spool valve 7 is increased.

  As described above, by driving the spool valve 7 with the solenoid 8, the flow passage area in the solenoid valve 1 can be adjusted. According to this solenoid valve 1, as shown in FIG. Since a part of the spool valve 7 is formed by a plurality of fine holes 23a that are shifted in the axial direction, all of the fine holes 23a are not uniformly blocked by the shutter member 9, and each of the fine holes 23a is finely divided. The flow rate of the liquid flowing through the hole 23a is smaller than that forming a spool port with a single hole. Therefore, when the spool valve 7 is driven to shut off the pores 23a with the shutter member 9, the fluid force that pushes the spool valve 7 in a direction that prevents the pores 23a from being blocked is reduced. If blocked by the shutter member 9, the liquid does not pass through the pores 23a, so the blocked pores 23a do not contribute to the generation of fluid force.

  That is, according to the solenoid valve 1 of the present invention, when the spool valve 7 is moved in the direction to shut off the spool port, the fluid force that hinders the movement of the spool valve 7 is reduced as compared with the conventional solenoid valve. be able to.

  As a result, in the solenoid valve 1 of the present invention, it is not necessary to use a solenoid capable of exerting a large thrust for adjusting the flow path area, so that a small solenoid can be used at low cost. According to the solenoid valve 1 of the present invention, since a small solenoid valve can be used, it can be mounted on the front fork F, and the damping force adjustment can be actively controlled.

  In addition, the installation number of the pores 23a is arbitrary, and if at least two or more, the fluid force can be reduced. However, if the installation number is increased to some extent, the effect of reducing the fluid force can be enhanced.

  Returning to this embodiment, if the mass of the spool valve 7 is Mb, the spring multiplier of the spool spring 35 is Kb, the mass of the shutter member 9 is Ms, and the combined spring constant of the shutter springs 25 and 26 is Ks, then Mb / It is set so as to satisfy the relationship of Kb = Ms / Ks.

  Therefore, when acceleration in the vertical direction in FIG. 2, which is the axial direction of the spool valve 7, is applied to the solenoid valve 1 by an external input, the spool valve 7 is supported by the spool spring 35. An inertial force is generated to move relative to the housing 6, and the shutter member 9 similarly generates an inertial force to move relative to the housing 6.

  When the acceleration is α, the inertial force of the spool valve 7 is Mb · α, and when it is moved relative to the housing 6 by the displacement Xb, this balances with the urging force of the spool spring 35. Therefore, Mb · α = Kb · Xb holds. Further, the inertial force of the shutter member 9 is Ms · α, and when it moves by the displacement Xs with respect to the housing 6, this balances with the urging force of the shutter springs 25 and 26, so that Ms · α = Ks · Xs holds. .

  Then, the displacement Xb of the spool valve 7 becomes Xb = Mb · α / Kb, and the displacement Xs of the shutter member 9 becomes Xs = Ms · α / Ks, but Mb / Kb = Ms / Ks. Therefore, Xb = Ks, and the displacement Xb of the spool valve 7 and the displacement Xs of the shutter member 9 are equal.

  Therefore, even if acceleration in the vertical direction in FIG. 2, which is the axial direction of the spool valve 7, is applied to the solenoid valve 1 by an external input, the spool valve 7 is not displaced relative to the variable shutter 9. It will be understood that the road area does not change.

  While the vehicle is traveling, a large acceleration in the vertical direction acts on the shock absorber D. Since the direction of this acceleration substantially coincides with the sliding direction of the spool valve 7, in this embodiment, the spool valve 7 In order to reduce the inertia force of the spool valve 7 due to the acceleration and further reduce the vibration of the spool valve 7, the magnetic member 22 and the magnetic member 22 functioning as a movable iron core are used. The spool valve body 21 having a small specific gravity is also used to reduce the weight of the spool valve 7 as a movable part of the solenoid valve 1. In this embodiment, in order to further reduce the weight of the spool valve body 21, the inner diameters of the hollow portion 21a and the pressure introduction hole 21c are increased to reduce the thickness as much as possible.

  In the case of this embodiment, the pressure of the liquid passing through the solenoid valve 1 not only acts on the lower end in FIG. 2 of the spool valve 7 which is the non-solenoid side end but also the pressure of the spool valve 7 by the pressure introducing hole 21c. The solenoid also acts on the solenoid side end, and the spool pressure is applied to the spool valve 7 from the non-solenoid side end side to the solenoid end side by the liquid pressure and the liquid pressure. The thrust that pushes the valve 7 from the solenoid side end side to the anti-solenoid side end side (downward thrust in FIG. 2) is set to be equal. That is, the pressure receiving area on the side opposite to the solenoid side of the spool valve 7 where the pressure of the passing liquid acts so as to push the spool valve 7 upward in FIG. 2, and the pressure acts so as to push the spool valve 7 downward in FIG. The pressure receiving area on the solenoid side end side of the spool valve 7 is set to be equal. Further, the pressure receiving area on one end side of the spool valve that receives the pressure of the damping force adjusting passage 5 of the spool valve 7 and the pressure receiving area on the other end side of the spool valve need not necessarily be both end faces of the spool valve 7. That is, the area receiving the pressure of the damping force adjusting passage 5 so as to press the spool valve 7 downward in FIG. 2 and the area receiving the pressure of the damping force adjusting passage 5 so as to press the spool valve 7 upward in FIG. For example, the spool valve 7 is provided in the middle of the spool valve 7 so that the pressure of the damping force adjusting passage 5 is applied to the upper surface and the lower surface of the step portion from one end side to the other end side. The pushing force and the pushing force from the other end side to the one end side may be made equal.

  Next, the operation of the front fork F configured as described above will be described. When the front fork F in which the piston 3 moves upward in FIG. 1 with respect to the cylinder 2 is extended, the shock absorber D is also extended and is attenuated by the flow of liquid moving from the expansion side chamber R1 to the compression side chamber R2 compressed by the piston 3. A resistance is given by the passage 13 and a resistance is given by the solenoid valve 1 against the flow of liquid from the extension side chamber R1 to the reservoir R. That is, in this embodiment, the front fork F exerts an extension side damping force by the damping passage 13 and the solenoid valve 1 when extended. Note that liquid is supplied from the reservoir R through the suction passage 16 provided in the bottom member 14 to the pressure side chamber R2 that expands when the front fork F extends, and the piston rod 4 retreats from the cylinder 2 when the front fork F extends. The change in the volume in the cylinder 2 occurring at is compensated.

  On the contrary, when the front fork F in which the piston 3 moves downward in FIG. 1 with respect to the cylinder 2 contracts, the shock absorber D also contracts, and the liquid that moves from the compression side chamber R2 compressed by the piston 3 to the extension side chamber R1. A resistance is given to the flow by the damping passage 13, and the liquid corresponding to the volume reduction in the cylinder 2 caused by the penetration of the piston rod 4 into the cylinder 2 is discharged to the reservoir R through the compression side damping passage 15 of the bottom member 14. Therefore, the volume change in the cylinder 2 is compensated, so that the pressure side damping passage 15 also provides resistance to the liquid flow. Therefore, when the shock absorber D is contracted, the damping side passage 13 and the pressure side damping passage 15 exhibit a compression side damping force. In this case, no liquid flows through the damping force adjusting passage 5. Does not participate in the generation of the compression damping force.

  That is, in this embodiment, in the solenoid valve 1, the resistance applied to the flow of the liquid passing through the damping force adjusting passage 5 can be adjusted by driving the spool valve 7 and adjusting the flow passage area. It is possible to adjust the extension side damping force during the extension.

  When adjusting the damping force, the spool valve 7 is driven by the solenoid 8 as necessary to change the flow path area. In the solenoid valve 1, at least a part of the spool port is the shaft of the spool valve 7. Since it is formed by a plurality of fine holes 23a arranged in a shifted direction, when the spool valve 7 is moved in a direction to block the spool port, it is possible to reduce the fluid force that hinders the movement of the spool valve 7. .

  As a result, in the solenoid valve 1 of the present invention, it is not necessary to use a solenoid capable of exerting a large thrust for adjusting the flow path area, so that a small solenoid can be used at low cost.

  According to the solenoid valve 1 of the present invention, since a small solenoid valve can be used, the solenoid valve 1 can be mounted on the front fork F, and the damping force adjustment responsiveness is remarkably improved. Can be actively controlled.

  In addition, the solenoid valve 1 includes a spool valve 7, a shutter member 9, a pair of shutter springs 25 and 26 that elastically support both ends of the shutter member 9 in the axial direction, and a spool spring 35. The mass Mb of the spool valve 7, the spring multiplier Kb of the spool spring 35, the mass Ms of the shutter member 9, and the combined spring constant Ks of the shutter springs 25 and 26 satisfy the relationship of Mb / Kb = Ms / Ks. Therefore, even if a large acceleration in the axial direction of the spool valve 7 acts on the solenoid valve 1 from the outside, the spool valve 7 and the shutter member 9 do not move relative to each other in the axial direction. The relative position of the shutter member 9 does not change. As a result, the damping force generated by the solenoid valve 1 can be prevented from changing vibrationally without becoming the targeted damping force, and a stable damping force can be exhibited.

  In the above description, the spool valve 7 is urged by only a single spool spring 35. However, the spool valve 7 is elastically supported at both ends in the axial direction by a pair of springs, like the shutter member 9. In this case, the spring constant of the spool spring may be set so as to satisfy the above relationship as a combined spring constant of the two springs.

  Thus, since the solenoid valve 1 can suppress fluctuations in the flow path area in response to external vibration input, the solenoid valve 1 is suitable for a front fork used in an environment in which vibration is constantly input. The damping force adjustment responsiveness of the present invention can be dramatically improved, and the damping force adjustment can be performed by active control such as skyhook control while exhibiting a stable damping force. It is most suitable for a shock absorber used in a saddle-riding vehicle that is suitable for running on rough roads where a large vertical acceleration acts.

  Further, in the present embodiment, the spool valve 7 is composed of a magnetic member 22 functioning as a movable iron core and a spool valve body 21 having a specific gravity smaller than that of the magnetic member 22, compared with a case where the whole is composed of a magnetic member. Since the weight of the entire spool valve 7 which is a movable part in the solenoid valve 1 is reduced, the spool valve 7 is acted on by the large acceleration in the vertical direction that is input to the shock absorber 1 while the vehicle is running. Since the inertial force to be generated can be made small and the vibration of the spool valve 7 can be made small, the damping force generated by the solenoid valve 1 is further changed in a vibrational manner instead of the targeted damping force. This can be prevented and a more stable damping force can be exhibited.

  Further, the solenoid valve 1 has a cylindrical magnetic member 22 and is integrated with the other end of the spool valve main body 21, opens from the solenoid side end of the spool valve main body 21 and communicates with the empty portion 21 a, and the spool valve 7. A pressure introduction hole 21c for guiding the pressure of the liquid passing through the solenoid valve 1 on the solenoid side end side, and the pressure of the passage liquid acts on both ends by the pressure introduction hole 7c of the spool valve 7, Both pressure receiving areas are the same. That is, the thrust received from the non-solenoid side end due to the pressure of the passing liquid acting on the spool valve 7 is made equal to the thrust received from the solenoid side end. As a result, the thrust that presses the spool valve 7 from the non-solenoid side end side to the solenoid side end side and the thrust that presses the spool valve 7 from the solenoid side end side to the anti-solenoid side end side are antagonized by the pressure of the passing liquid. In this solenoid valve 1, even if the pressure of the passing liquid becomes high, the solenoid 8 does not affect the adjustment of the flow area. As a result, the problem that the thrust of the solenoid 8 must be increased so as to overcome the pressure of the passing liquid can be solved, and the damping force can be adjusted by driving the spool valve 7 with the small solenoid 8. Further, since the spool valve 7 does not move due to the pressure of the passing liquid, the generated damping force does not fluctuate due to the pressure of the passing liquid in the solenoid valve 1, and a sufficient damping effect can be obtained. Can do. Further, since it is not affected by pressure, the spool valve 7 can be driven without increasing the size of the solenoid 8, so that the solenoid valve 1 can be mounted on a small vehicle such as a straddle vehicle. There is no problem that the cost is increased and the economy is also lost.

  Further, since the spool valve 7 is a movable iron core, the solenoid valve 8 and the spool valve 7 are arranged close to each other so that the spool valve 7 can be driven without using a separate long movable iron core, etc. In addition to improving the weight of the movable part such as the spool valve 7, it is possible to suppress the damping force from being changed by the vibration acceleration input to the shock absorber 1, and to generate and adjust the stable damping force. It becomes.

  The solenoid 8 includes an inner cylinder 30a through which the spool valve 7 can be inserted, an outer cylinder 30b disposed on the outer peripheral side of the inner cylinder 30a, and an annular bottom portion connecting the inner cylinder 30a and the outer cylinder 30b. A case 30 provided with 30c, a coil 31a accommodated in the case 30, and an inner cylinder 30a of the case 30 opposed to each other through an annular gap and inserted into the inner periphery of the coil 31a and connected to the coil 31a. A base 33 for attracting the spool valve 7 by energization, and the magnetic member 22 is at least a base portion 22a radially facing the inner cylinder 30a of the case 30 while being attracted to the base 33, and a spool valve body from the base portion 22a. 21 is extended to the side of 21 and is opposed to the inner cylinder 30a of the case 30 in the radial direction, and is fitted into a fitting portion 21e formed with a smaller diameter outer periphery of the other end of the spool valve body 21. Jo of and a socket 22b. As a result, the thickness of the base portion 22a facing the inner cylinder 30a of the case 30 can always be secured, so that the cross-sectional area of the magnetic path becomes too small, the magnetic flux density is saturated, and the attractive force is reduced. Therefore, the vibration of the spool valve 7 can be further suppressed, and it is possible to contribute to more stable damping force.

  The piston rod 4 includes a vehicle body side tube 10 connected to the vehicle body of the saddle riding vehicle and an axle side tube 11 connected to the axle of the saddle riding vehicle via a housing 6 connected to the tip of the piston rod 4. Are connected to the vehicle body side tube 10 and the cylinder 2 is connected to the axle side tube 11 to accommodate the shock absorber body D in the space L formed by the vehicle body side tube 10 and the axle side tube 11. The reservoir R is formed outside the cylinder 2, the damping force adjusting passage 5 passes through the piston rod 4, and the pressure side chamber R2 or the extension side chamber R1 in the cylinder 2 communicates with the hollow portion 6a of the housing 6, and the port 6b Is connected to the reservoir R, so that the solenoid valve 1 can be concentrated above the vehicle body side tube 10 and the solenoid 8 can be easily energized. Since the solenoid valve 1 is connected to the vehicle body side of the saddle-riding vehicle that is damped by the shock absorber D, the vibration of the spool valve 7 during vehicle travel can be suppressed, and the damping force caused by the vibration Variations can be suppressed.

  The piston rod 4 includes a hole 4b that forms a part of the damping force adjusting passage 5 along the axial direction, and the piston rod 4 and the housing 6 connected to the tip of the piston rod 4 include a hollow portion 6a. Since the air holes 4b are connected so as to be coaxial and in series, the driving direction of the spool valve 7 coincides with the axial direction of the piston rod 4, so that the solenoid 8 that drives the spool valve 7 projects sideways. The shock absorber D can be made slim compared to the case where the driving direction of the spool valve 7 is set to the direction intersecting the axis of the piston rod 4. Of course, in exchange for the effect, the driving direction of the spool valve 7 may be different from the expansion / contraction direction of the shock absorber D, that is, it may not coincide with the axis of the piston rod 4. Therefore, the vibration in the drive direction of the spool valve 7 can be suppressed by the vibration.

  In addition, by making the shape and structure of the spool valve 7 as described above, it is possible to enjoy the various advantages described above, but even if the shape and structure of the spool valve 7 is different from the above-described shape and structure, By setting the mass Mb of the spool valve 7, the spring multiplier Kb of the spool spring 35, the mass Ms of the shutter member 9, and the combined spring constant Ks of the shutter springs 25 and 26 so as to satisfy the relationship of Mb / Kb = Ms / Ks. It is natural that the effect can be obtained.

  In this embodiment, the shutter member 9 is provided between the housing 6 and the spool valve 7. However, the housing 6 is used as a shutter member and the inner peripheral surface of the housing 6 is slidably contacted with the outer periphery of the spool valve 7. Thus, the pores 23a may be blocked and opened.

  Further, the housing 6 includes a housing portion 6c that is connected to the hollow portion 6a and houses the solenoid 8, and is fixed to the opening end of the vehicle body side tube 10 with the housing portion 6c facing outward in FIG. An adjuster 34 for adjusting the initial load of the spring 35 is provided facing the outside of the shock absorber 1 from the opening end of the vehicle body side tube 10. Thereby, since the adjuster 34 can be externally operated, the initial load can be easily adjusted. In addition, when the spring constant of the spool spring 35 varies, by performing this initial load adjustment, it is possible to perform a uniform damping force adjustment without variation among products. The damping force adjustment of the shock absorber 1 may be made uniform by correcting the amount of current applied to the solenoid 8.

  As described above, the solenoid valve 1 is configured such that the damping force adjusting passage 5 allows the liquid to pass only when the shock absorber D is extended, and generates the expansion side damping force of the shock absorber D. Since it functions as a damping force generating element, the extension side damping force of the shock absorber D can be adjusted, but only when the shock absorber D contracts, the damping force adjusting passage 5 allows the liquid to pass therethrough. It may be set to function as a damping force generating element that generates the compression side damping force of the shock absorber D and adjust the compression side damping force. That is, if the pressure side chamber R2 is communicated to the hollow portion 4b instead of the expansion side chamber R1 through the communication passage 4d provided in the piston coupling portion 4c, the solenoid valve 1 can adjust the compression side damping force. If it does in this way, it can set so that a liquid may pass through damping force adjustment passage 5 only at the time of contraction operation of shock absorber D.

  Further, when the damping force adjusting passage 5 is set so as to communicate the extension side chamber R1 and the compression side chamber R2, the solenoid valve 1 adjusts the damping force both when the shock absorber D is extended and contracted. It may be set as follows. In this case, for example, the housing is used as a piston rod or piston coupling part to accommodate the spool valve, and the piston rod or piston coupling part is provided with a flow path that connects the expansion side chamber R1 and the pressure side chamber R2, and the spool valve is driven by a solenoid. Just do it.

  Furthermore, as described above, the flow path area is set to decrease when the spool valve 7 is retracted, but the spool valve 7 is set to minimize the flow path area at the lowest position, The flow path area may be increased by retreating the spool valve 7.

  Further, the housing 6 may be integrated with the piston rod 4 to be a single component, or the housing 6 may be constituted by a plurality of components.

  Further, in the above embodiment, the connector 31d for energizing the coil 31a is integrated with the molded coil 31, but the connector 31d is separated from the molded coil 31, and the coil 31a and the power supply terminal 31c are connected by a cord. Alternatively, the connector and the power terminal may be eliminated, and the coil 31a may be connected to an external power source only through a cord.

  This is the end of the description of the embodiment of the present invention, but the scope of the present invention is of course not limited to the details shown or described.

DESCRIPTION OF SYMBOLS 1 Solenoid valve 2 Cylinder 3 Piston 4 Piston rod 5 Damping force adjustment path 7 Spool valve 8 Solenoid 9 Shutter member 10 Car body side tube 11 Axle side tube 21 Spool main body 21a Empty part 21b Through-hole 21c Pressure introduction hole 22 Magnetic member 23 Small hole Member 23a Fine hole 35 Spool spring F Front fork.

R Reservoir R1 Stretch side chamber R2 Pressure side chamber

Claims (5)

A spool valve having a hollow portion and a spool port that opens from the outer periphery to the hollow portion;
A shutter member that is slidably contacted with the outer periphery of the spool valve and capable of blocking part or all of the spool port;
A solenoid that drives the spool valve in the axial direction;
In the solenoid valve in which the flow path is formed with the empty portion as the upstream and the spool port as the downstream, and the flow area is adjusted by the degree of blocking of the spool port,
A spool spring for urging the spool valve in the axial direction;
A pair of shutter springs that elastically support the shutter member across both axial ends thereof,
The spool port is composed of a plurality of pores, and at least a part of these pores are arranged shifted in the axial direction ,
The spool valve mass Mb, the spring multiplier Kb of the spool spring, the mass Ms of the shutter member, and the combined spring constant Ks of the shutter spring are set so as to satisfy the relationship of Mb / Kb = Ms / Ks. Characteristic solenoid valve.   The spool port is formed by providing the spool valve with a through hole that communicates from the outer periphery to the empty portion, and fitting a fine hole member having all of the fine holes into the through hole. Item 2. The solenoid valve according to Item 1. The spool valve includes a cylindrical spool body and a magnetic member that is integrated with a solenoid side end of the spool body and functions as a movable iron core of the solenoid, and the spool valve body has a specific gravity of the magnetic member. The solenoid valve according to claim 1 or 2 , wherein the solenoid valve is smaller than a specific gravity. The empty portion is opened from the side opposite to the solenoid that receives the pressure of the liquid passing through the spool valve, opens from the solenoid side end to the spool valve, and communicates with the empty portion toward the solenoid side end of the spool valve. the pressure introducing hole for guiding the pressure of the passing liquid is provided, any one of claims 1 to 3, characterized in that equal thrust received from thrust and the solenoid-side receiving from the opposite solenoid side by the pressure acting on the spool valve one The solenoid valve according to item. A vehicle body side tube connectable to the vehicle body of the saddle riding vehicle, an axle side tube connectable to the axle of the saddle riding vehicle and slidably fitted to an inner periphery or an outer periphery of the vehicle body side tube; A cylinder connected to the axle side tube, a piston that is slidably inserted into the cylinder and divides the cylinder into an extension side chamber and a pressure side chamber, and one end inserted into the cylinder. Is connected to the piston and the other end is connected to the vehicle body side tube, a damping force adjusting passage that communicates one of the compression side chambers and a reservoir provided outside the cylinder, and the damping force. The front fork provided with the solenoid valve as described in any one of Claim 1 to 4 provided in the middle of the adjustment channel | path.

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