JP5559713B2 - Shock absorber for saddle riding vehicle - Google Patents

Description

  The present invention relates to an improvement in a shock absorber for a saddle-ride vehicle.

  Conventionally, as a shock absorber for a straddle vehicle, for example, there is a front fork of a two-wheeled vehicle. Such a front fork can adjust a damping force of a built-in shock absorber body.

  Specifically, a cylinder connected to the outer tube, a piston that is slidably inserted into the cylinder and divides the inside of the cylinder into a compression side chamber and an extension side chamber, and one end that is inserted into the cylinder and has the outer tube A shock absorber body having a piston rod connected to an inner tube slidably inserted into the piston and having the other end connected to the piston, a passage communicating with the compression side chamber and the extension side chamber of the shock absorber body, A check valve that is provided in the middle of the passage and allows only a flow from the compression side chamber to the expansion side chamber, or conversely, only a flow from the extension side chamber to the compression side chamber, a needle valve provided in the middle of the passage, and a piston Some include a stepping motor that is fixed to the other end of the rod and drives a needle valve (see, for example, Patent Document 1).

  In this front fork, when the piston is extended, the piston valve provided on the piston gives resistance to the flow of hydraulic oil to exert a damping force, and when contracted, the base valve provided at the end of the cylinder causes the base valve to flow out from the cylinder to the reservoir. In addition to this, the damping force is exerted by giving resistance to the oil flow, but in addition to this, the damping force generated by the front fork is adjusted by driving the needle valve and adjusting the flow resistance in the needle valve. Can be variable.

JP 2008-14431 A

  According to the front fork described above, since a stepping motor is used to drive the needle valve, it takes time to change the valve opening, and the damping force of the front fork is adjusted by active control such as skyhook control. Even if it tries to do so, the response of the damping force adjustment is not in time, and it is difficult to implement the above control.

  In the front fork, a solenoid can be used to improve the response of the damping force adjustment. However, in a shock absorber for a saddle-riding vehicle such as a front fork, the stroke amount is much longer than that of a four-wheeled vehicle and the flow rate is large. Therefore, the pressure acting on the needle valve becomes very high. If the solenoid is driven by a solenoid, the thrust of the solenoid needs to be very large. For this reason, 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 make it possible to use a small solenoid at a low cost, and to perform a saddle ride capable of actively controlling the damping force adjustment. It is to provide a dual buffer.

In order to achieve the above-mentioned object, the problem-solving means of the present invention includes a cylinder, a piston that is slidably inserted into the cylinder, and that divides the cylinder into a pressure side chamber and an extension side chamber, and a cylinder A shock absorber body that is inserted between the piston rod and connected to the piston, and is interposed between the vehicle body and the axle of the saddle vehicle, and one or both of when the shock absorber body is extended and contracted In the shock absorber for a saddle-ride vehicle provided with a flow path that allows passage of liquid and a damping force adjustment mechanism that is provided in the middle of the flow path and adjusts the damping force, the damping force adjustment mechanism is provided in the flow path. And a solenoid that drives the spool valve in the flow path using the spool valve as a movable iron core , and the spool valve has a cylindrical shape that can be slidably inserted into the solenoid. , the spool Characterized in that of equal thrust applied from the thrust and the other end side for receiving from the one end by the passage pressure.

  In the straddle vehicle shock absorber of the present invention, the thrust that presses the spool valve from one end side to the other end side by the pressure of the flow path and the thrust that presses the other end side to the one end side compete with each other. Is not moved in the axial direction, so even if the pressure of the flow path becomes high, the adjustment of the flow area of the flow path by the solenoid is not affected, and the thrust of the solenoid is overcome by the pressure of the flow path. Thus, the problem of having to be made large can be solved, and the damping force can be adjusted by driving the spool valve with a small solenoid.

  According to the shock absorber for a saddle-riding vehicle 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 shock absorber for saddle riding vehicles in one Embodiment. It is an expanded sectional view of the damping force adjustment mechanism in one embodiment.

  The present invention will be described below based on the embodiments shown in the drawings. As shown in FIG. 1, a shock absorber 1 for a saddle-ride vehicle according to an embodiment includes a cylinder 2 and an extension side chamber that is slidably inserted into the cylinder 2 and is filled with a liquid such as hydraulic oil. A shock absorber body D having a piston 3 partitioned into R1 and a pressure side chamber R2, a piston rod 4 inserted into the cylinder 2 and connected to the piston 3, and a liquid only when the shock absorber body D is extended. A passage 5 that allows passage, a damping force adjustment mechanism V that is provided in the middle of the passage 5 and that adjusts the damping force generated by the shock absorber 1, and a vehicle body (not shown) of a straddle vehicle such as a two-wheeled vehicle are connected to the passage 5. The vehicle body side tube 10 connected to the piston rod 4 and the axle side tube connected to the cylinder 2 while being slidably inserted into the vehicle body side tube 10 and connected to the axle (not shown) of the saddle-ride type vehicle. With 11 It has been made.

  Hereinafter, each part of the shock absorber 1 for the saddle riding vehicle will be described in more detail. The shock absorber body D has a piston rod 4 connected to a vehicle body side tube 10 via a housing 6 to be described later, a cylinder 2 is connected to an axle side tube 11, and the vehicle body side tube 10 and the axle side tube 11 are interposed between them. While being interposed, it is accommodated in a space L closed by the vehicle body side tube 10 and the axle side tube 11. In this embodiment, the straddle vehicle shock absorber 1 is an inverted front fork in which the axle-side tube 11 is inserted into the vehicle-body side tube 10. An upright front fork inserted into the tube 11 may be used.

  A suspension spring 12 is interposed between the piston rod 4 and the cylinder 2 of the shock absorber body D. The suspension spring 12 is connected to the vehicle body side tube 10 and the axle side tube via the shock absorber body D. 11, the vehicle body of the straddle vehicle (not shown) is elastically supported by the suspension spring 12 in a direction in which the straddle vehicle shock absorber 1 is extended. Yes.

  As shown in FIG. 1, the shock absorber main body D includes a cylinder 2 connected to the axle tube 11, and an extension side chamber R <b> 1 that is slidably inserted into the cylinder 2 and serves as two working chambers. And a piston 3 partitioned into a pressure side chamber R2, a piston rod 4 having one end connected to the piston 3 and the other end connected to the vehicle body side tube 10, and an extension side chamber R1 and a pressure side chamber R2 provided in the piston 3. A damping passage 13 that provides resistance to the flow of liquid that passes through and a pressure-side damping passage 15 that is provided at the lower end of the cylinder 2 and that provides resistance to the flow of liquid from the pressure-side chamber R2 toward the reservoir R. And a bottom member 14 having a suction passage 16 that allows only the flow of liquid toward the chamber R2, and the extending side chamber R1 and the pressure side chamber R2 have hydraulic fluid as liquid. Liquid is filled, it is in the reservoir R liquids and gases are filled.

  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 damping force adjusting mechanism V. 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.

  And the suspension spring 12 is interposed between the rod guide 17 and the cylindrical spring receiver 18 provided on the outer periphery of the housing 6, and the shock absorber body D is urged in the extension direction by the suspension spring 12. The straddle vehicle shock absorber 1 is also urged by the suspension spring 12 in the extending direction.

  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 other side has a pressure side. A damping valve that allows only the flow of liquid from the chamber R2 toward the extension side chamber R1 may be provided.

  The reservoir R is formed in the space L and outside the buffer body D, and the reservoir R is filled with liquid and gas. 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 saddle-ride vehicle shock absorber 1, since the compression side damping force can be generated by the damping valve 15b, only the liquid flow from the compression side chamber R2 to the extension side chamber R1 is allowed as described above. When the passage is provided, the attenuation valve may not be provided in the passage.

  Next, the damping force adjusting mechanism V will be described. The damping force adjusting mechanism V is provided in the middle of the flow path 5 described above, and includes a housing 6 having a hollow portion 6a, a spool valve 7 that is slidably inserted into the hollow portion 6a of the housing 6, The spool valve 7 is used as a movable iron core and includes a solenoid 8 that drives the spool valve 7 within the hollow portion 6a.

  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 port 6b, a housing portion 6c that opens from the upper end in FIG. 2 and communicates with the hollow portion 6a and accommodates the solenoid 8 with a larger diameter than the hollow portion 6a, a flange 6d provided on the outer periphery of the upper end, and a lower diameter outer periphery. The small diameter portion 6e, the step portion 6f, and the groove 6g provided along the axial direction on the outer periphery of the small diameter portion 6e. In this case, the port 6b extends in the radial direction. The groove 6g communicates with the hollow portion 6a.

  Further, a screw hole portion 6h is provided on the lower inner periphery in FIG. 2 of the hollow portion 6a of the housing 6, and a screw portion 4f is provided on the outer periphery of the upper end of the piston rod 4, so that the inside of the screw hole portion 6h. A screw can be fastened while inserting the upper end of the piston rod 4. 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. Therefore, consideration is given so that the screw hole portion 6h 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 of the shock absorber body D. Moreover, the hollow part 6a is connected to the reservoir | reserver R formed out of the buffer body D through the port 6b and the groove | channel 6g. Therefore, in the case of this embodiment, the flow path 5 is constituted by the communication passage 4d, the hole 4b, the hollow portion 6a, the port 6b, and the groove 6g described above, and the extension side chamber R1 and the reservoir R communicate with each other. ing. Further, in this case, the flow path 5 allows only the passage of liquid from the extension side chamber R1 to the reservoir R by the check valve 4e. The check valve for setting the flow path 5 to be one-way is not provided in the piston connecting portion 4c but may be provided in another location. Specifically, for example, the check valve is provided in the hole 4b of the piston rod body 4a. Alternatively, the piston rod body 4a may be provided at the open end of the hole 4b at the upper end in FIG.

  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 part 6 i is provided on the upper outer periphery of the housing 6 in FIG. 2 so that the screw can be fastened to the housing 6 at the opening end of the vehicle body side tube 10. The piston rod 4 can be connected to the vehicle body side tube 10.

The spool valve 7 has a cylindrical shape, and is slidably inserted into the hollow portion 6a of the housing 6 and the solenoid 8 with one end facing downward, and the lower end in FIG. In FIG. 2, the hollow portion 7a that opens from one end, the spool port 7b that opens from the outer periphery and communicates with the hollow portion 7a, and the other end that communicates with the hollow portion 7a. A pressure introducing hole 7c that guides the pressure of the flow path 5 on the upper end side, and an annular groove 7d that is provided on the outer periphery along the circumferential direction and communicates with the spool port 7b.

  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. 2 and a case 30 formed of a magnetic material, and a coil 31a as a mold resin 31b. A cylindrical mold coil 31 that is formed by molding and accommodated between the outer cylinder 30b and the inner cylinder 30a, a cylindrical filler ring 32 integrated with the mold coil 31, and a filler ring 32 A cylindrical base 33 that is fitted to the inner periphery and is magnetic, an adjuster 34 that is screwed into the base 33, and a biasing spring 35 that is interposed between the adjuster 34 and the spool valve 7. The spool valve 7 is made of a magnetic material and is used as a movable iron core so that the spool valve 7 can be driven by energizing the coil 31a.

  The inner cylinder 30a of the case 30 is set to have an inner diameter that allows the spool valve 7 to be freely inserted. Even if the inner cylinder 30a is accommodated in the accommodating portion 6c of the housing 6 together with the outer cylinder 30b, the movement of the spool valve 7 Is not disturbed. The inner diameter of the inner cylinder 30a may be set so that the spool valve 7 can slide. In this case, the inner circumference of the inner cylinder 30a is flush with the hollow portion 6a of the housing 6. do it.

  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. Further, when the coil 31a is molded with the mold resin 31b, the filler ring 32 is also integrated with the inner periphery of the coil 31a with the mold resin 31b. An inner cylinder 30a of the case 30 is press-fitted into the inner periphery of the filler ring 32, and the case 30 and the molded coil 31 are integrated.

  The base 33 includes a cylindrical portion 33a that is press-fitted to the inner periphery of the filler ring 32 together with the inner cylinder 30a, and a flange 33b that is provided on the outer periphery of the upper end of the cylindrical portion 33a in FIG. 30 and the molded coil 31 are positioned coaxially by a filler ring 32, and the filler ring 32 also functions as a seal member that seals between the case 30 and the base 33. Further, a gap 40 is provided between the cylindrical portion 33 a of the base 33 and the inner cylinder 30 a of the case 30, so that the base 33 and the case 30 are magnetically connected via the spool valve 7. A circuit is formed. In this case, the filler ring 32 also serves to form both the cylindrical portion 33a and the inner cylinder 30a in the axial direction and form a gap 40 therebetween. The gap 40 may actually be a gap, but may be filled with a non-magnetic ring. When the base 33 and the case 30 are integrated with the non-magnetic ring, a filler ring is used. It is also possible to omit 32.

  The outer diameter of the flange 33 b of the base 33 is set to be larger than at least the outer diameter of the molded coil 31. Further, a nut member 37 having a screw portion on the outer periphery is screwed to the inner periphery of the upper end in FIG. 2 which is the opening end of the housing portion 6c of the housing 6. When the nut member 37 is attached to the housing 6 in this manner, the case 30, the molded coil 31, the filler ring 32, and the base 33 are sandwiched between the housing 6 and the nut member 37 and fixed to the housing 6.

  Further, 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 to the inner periphery of the cylindrical portion 33a of the base 33, and the lower end in FIG. A biasing spring 35 is interposed between the spool valve 7 and the spool valve 7 in a compressed state.

  Here, the pressure introducing hole 7c in the spool valve 7 opens from the upper end in FIG. 2 which is the other end of the spool valve 7 and communicates with the empty portion 7a, and the portion connected to the empty portion 7a is set to have a small diameter. A step portion 7e is formed in the pressure introducing hole 7c, and a biasing spring 35 is interposed between the step portion 7e and the adjuster 34. Then, the adjuster 34 is moved forward and backward 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 compression length of the biasing spring 35 is adjusted to bias the spool valve 7. The initial load applied by the spring 35 can be adjusted.

  While the saddle vehicle is traveling, a large acceleration in the vertical direction acts on the shock absorber 1 for the saddle vehicle. Since the direction of this acceleration substantially coincides with the sliding direction of the spool valve 7, this embodiment is described. Then, in order to reduce the weight of the spool valve 7 and to reduce the inertia force of the spool valve 7 due to the acceleration and suppress the vibration of the spool valve 7, the spool valve 7 is used as a movable iron core in the solenoid 8. The movable core is not required and the weight of the movable part in the damping force adjusting mechanism V is reduced. In this embodiment, in order to further reduce the weight of the spool valve 7, the inner diameters of the empty portion 7a and the pressure introducing hole 7c are increased, and the depth of the empty portion 7a is increased as much as possible. The thickness of each part of the spool valve 7 is made thin. In addition, since the structure which accommodates the urging | biasing spring 35 in the pressure introduction hole 7c is employ | adopted, the accommodation space of the urging | biasing spring 35 is ensured and the full length of the solenoid 8 including the adjuster 34 can be shortened.

  As described above, when the spool valve 7 is urged by the urging 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 upper end of the piston rod 4, further movement of the spool valve 7 toward the piston rod 4 is restricted, and the spool valve 7 is positioned at the lowest position. .

  At the lowest position, the annular groove 7d of the spool valve 7 faces the port 6b, the spool port 7b and the port 6b are in communication with each other, and the flow path 5 is 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. And the wrap area of the port 6b (opposite area between the annular groove 7d and the port 6b) can be reduced to narrow the flow path 5 (reduce the flow path area). Furthermore, the lap area of the annular groove 7d and the port 6b can be adjusted by controlling the movement amount of the spool valve 7 according to the energization amount of the coil 31a. That is, 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. The position of the valve 7 can be adjusted. In this way, the solenoid valve 8 can drive the spool valve 7 in the vertical direction in FIG.

  Then, by narrowing the flow path 5 by the annular groove 7d and the port 6b, the resistance given to the flow of the liquid that attempts to pass through the flow path 5 is made larger than when the spool valve 7 is in the lowest position. be able to. In this case, the larger the retraction amount of the spool valve 7, the smaller the lap area between the annular groove 7d and the port 6b and the greater the degree of throttling of the flow path 5, so that the retraction amount of the spool valve 7 increases. Thus, the resistance given to the flow of liquid passing through the flow path 5 is increased.

  Further, the pressure in the flow path 5 not only acts on the lower end serving as one end of the spool valve 7, but also acts on the upper end serving as the other end of the spool valve 7 through the pressure introducing hole 7c. A thrust force that pushes the spool valve 7 from one end side to the other end side by the pressure of the passage 5 (an upward thrust force in FIG. 2) and a thrust force that pushes the spool valve 7 from the other end side to the one end side by the pressure of the flow path 5 (see FIG. 2 and a downward thrust) are set equal to each other. That is, the pressure receiving area on one end side of the spool valve on which the pressure in the flow path acts so as to push the spool valve 7 upward in FIG. 2, and the spool on which the pressure in the flow path acts so as to push down the spool valve 7 in FIG. The pressure receiving area on the other end side of the valve is set to be equal. Specifically, the outer diameter of the spool valve 7 is set to a single diameter except for the annular groove 7d so that both pressure receiving areas are the same. Has been. The annular groove 7d is provided so that the port 6b and the spool port 7b can communicate with each other even when the spool valve 7 rotates in the circumferential direction. An annular groove communicated with 6b may be provided to omit the annular groove 7d. In this case, all of the outer peripheral diameter of the spool valve 7 may be set to a single diameter. When the annular groove is provided on the housing 6 side, the spool port 7b is provided on the inner periphery of the hollow portion 6a of the housing 6 and directly faces the annular groove communicated with the port 6b. 7, the flow path area of the flow path 5 can be adjusted by adjusting the lap area of the spool port 7 b and the annular groove by driving in the up-down direction which is the axial direction of 7. Further, the annular groove may be provided in both the spool valve 7 and the housing 6. However, when the spool valve 7 is prevented from rotating in the circumferential direction with respect to the housing 6, the annular groove is omitted. May be.

  Further, the pressure receiving area on one end side of the spool valve that receives the pressure of the flow path 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 that receives the pressure of the flow path 5 so as to press the spool valve 7 downward in FIG. 2 and the area that receives the pressure of the flow path 5 so as to press the spool valve 7 upward in FIG. What is necessary is just to provide the thrust and the other end, for example, by providing a step portion in the middle of the spool valve 7 and pressing the spool valve 7 that applies the pressure of the flow path 5 to the upper and lower surfaces of the step portion from one end side to the other end side. You may make it make the thrust pressed from the side to one end side equal.

  Subsequently, the operation of the straddle vehicle shock absorber 1 configured as described above will be described. When the straddle vehicle shock absorber 1 in which the piston 3 moves upward in FIG. 1 with respect to the cylinder 2, the damping passage 13 resists the flow of the liquid moving from the expansion side chamber R 1 to the compression side chamber R 2 compressed by the piston 3. In addition, the damping force adjusting mechanism V provides resistance to the liquid flow from the extension side chamber R1 to the reservoir R. In other words, in this embodiment, the shock absorber 1 for the saddle riding vehicle exhibits the extension side damping force by the damping passage 13 and the damping force adjusting mechanism V at the time of extension. 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 extended, and the piston rod 4 retreats from the cylinder 2 when the shock absorber 1 extends. The change in the volume in the cylinder 2 occurring at is compensated.

  On the contrary, when the straddle vehicle shock absorber 1 in which the piston 3 moves downward in FIG. 1 with respect to the cylinder 2 is contracted, a damping passage is formed in the flow of liquid moving from the compression side chamber R2 to the extension side chamber R1 compressed by the piston 3. 13, and a liquid corresponding to a volume decrease in the cylinder 2 generated by the piston rod 4 entering the cylinder 2 is discharged to the reservoir R through the compression side damping passage 15 of the bottom member 14 and is supplied into the cylinder 2. Therefore, the pressure side damping passage 15 also provides resistance to the flow of liquid. Therefore, when the shock absorber 1 for the saddle riding vehicle is contracted, the damping side passage 13 and the pressure side damping passage 15 exhibit a compression side damping force. In this case, the liquid 5 is prevented from flowing through the flow path 5, so the damping force The adjusting mechanism V is not involved in the generation of the compression side damping force.

  That is, in this embodiment, in the damping force adjusting mechanism V, the spool valve 7 can be driven to make the flow passage area of the flow passage 5 variable. The damping force can be adjusted.

  When adjusting the damping force, the spool valve 7 is driven by the solenoid 8 as necessary to change the flow path area of the flow path 5. The pressure of the flow path 5 is changed at both ends by the pressure introduction holes 7 c of the spool valve 7. And the pressure receiving area of both is equal, and the thrust that presses the spool valve 7 from one end side to the other end side by the pressure of the flow path 5 and the thrust that presses the other end side to the one end side are antagonistic, 7 is not moved in any axial direction. As a result, in this straddle vehicle shock absorber 1, even if the pressure in the flow path 5 becomes high, the adjustment of the flow path area of the flow path 5 by the solenoid 8 is not affected. The problem of having to be increased to overcome the pressure in the passage 5 can be solved, and the spool valve 7 can be driven by the small solenoid 8 to adjust the damping force.

  In addition, since the spool valve 7 does not move due to the pressure of the flow path 5, in this straddle vehicle shock absorber 1, the generated damping force of the straddle and ride shock absorber 1 is caused by the pressure of the flow path 5. A sufficient vibration control effect can be obtained without fluctuation.

  Further, since the spool valve 7 can be driven without increasing the size of the solenoid 8, the shock absorber 1 for the saddle riding vehicle does not impair the mountability to the saddle riding vehicle, and the cost is high. There is no problem that the economy is also lost.

  In addition, in the saddle riding vehicle shock absorber 1, the solenoid 8 can be used without sacrificing the mountability, so that the damping force adjustment response of the saddle riding vehicle shock absorber 1 is greatly improved. The damping force can be adjusted by active control such as skyhook control.

  Furthermore, 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. In addition, since the weight of the movable part such as the spool valve 7 can be reduced, it is possible to suppress the damping force from being changed by the vibration acceleration input to the saddle riding vehicle shock absorber 1 and to generate a stable damping force. And adjustment becomes possible.

  The shock absorber 1 includes a vehicle body side tube 10 connected to the vehicle body of the saddle vehicle and an axle side tube 11 connected to the axle of the saddle vehicle, and is connected to the tip of the piston rod 4. The piston rod 4 is connected to the vehicle body side tube 10 through the housing 6 and the cylinder 2 is connected to the axle side tube 11 so that the shock absorber body D is formed in the space L formed by the vehicle body side tube 10 and the axle side tube 11. The reservoir R is formed in the space L and outside the shock absorber body D, and the flow path 5 passes through the piston rod 4 so that the compression side chamber R2 or the extension side chamber R1 in the cylinder 2 and the housing 6 are hollow. By connecting the part 6a and the port 6b to the reservoir R, the damping force adjusting mechanism V can be concentrated above the vehicle body side tube 10, and the solenoid 8 can be energized. In addition, the damping force adjusting mechanism V is connected to the vehicle body side of the saddle vehicle that is damped by the shock absorber 1 for the saddle vehicle, so that the vibration of the spool valve 7 during vehicle traveling is suppressed. It is possible to suppress the fluctuation of the damping force due to the vibration.

  Further, the shock absorber 1 for the saddle riding vehicle includes a hole 4b in which the piston rod 4 forms a part of the flow path 5 along the axial direction, and the housing 6 connected to the piston rod 4 and the tip of the piston rod 4. Are connected so that the hollow portion 6a and the hole 4b are coaxial and in series. As a result, 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 does not protrude sideways, and the driving direction of the spool valve 7 is changed to the axis of the piston rod 4. Compared with the case where the distance between the two is not matched, the shock absorber 1 for the saddle riding vehicle can be made slim. Of course, in exchange for the effect, the driving direction of the spool valve 7 can be set to a direction different from the expansion / contraction direction of the shock absorber 1 for the saddle riding vehicle, that is, not to coincide with the axis of the piston rod 4. In this case, since the vibration of the vehicle does not match the driving direction, it is possible to suppress the vibration in the driving direction of the spool valve 7 due to the vibration.

  Further, the shock absorber 1 for the saddle riding vehicle includes a housing portion 6c in which the housing 6 is connected to the hollow portion 6a and accommodates the solenoid 8, and the housing portion 6c faces outward in FIG. And an adjuster 34 that adjusts the initial load of the biasing spring 35 of the solenoid 8 is provided facing the outside of the saddle-ride vehicle 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 urging 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 saddle riding vehicle shock absorber 1 may be made uniform by correcting the amount of current applied to the solenoid 8.

  The straddle vehicle shock absorber 1 is provided with an annular groove 7d communicating with the spool port 7b along the circumferential direction on the outer periphery of the spool valve 7, and the solenoid valve 8 is driven by the solenoid 8 to drive the port 6b and the annular groove 7d. By changing the lap area, the flow path 5 is narrowed to adjust the damping force. Thereby, the circumferential displacement between the port 6b and the spool port 7b is allowed by the annular groove 7d, and the process of providing the annular groove 7d becomes easier than the provision of the annular groove on the housing 6 side, and the cost can be reduced.

  Further, in the shock absorber 1 for the saddle riding vehicle, the outer diameter of the spool valve 7 is set to a single diameter except for the portion of the annular groove 7d. Thereby, the pressure receiving areas at both ends of the spool valve 7 can be easily set to be equal. In addition, this makes it possible to simplify the shape of the spool valve 7 and also to make the inner peripheral diameter of the hollow portion 6a a single diameter, so that the processing is facilitated and the cost of the shock absorber 1 for straddle vehicle can be reduced.

  In the above description, the damping force adjusting mechanism V allows the passage 5 to allow liquid to pass only when the straddle vehicle shock absorber 1 extends, and the straddle vehicle shock absorber 1 extends. Since it functions as a damping force generating element that generates a side damping force, it is possible to adjust the extension side damping force of the straddle vehicle shock absorber 1, but only when the straddle vehicle shock absorber 1 contracts. 5 may be set so as to allow passage of liquid, and the compression side damping force may be adjusted by functioning as a damping force generating element that generates the compression side damping force of the saddle riding vehicle shock absorber 1. That is, if the pressure side chamber R2 is communicated with the hollow portion 4b instead of the expansion side chamber R1 in the communication passage 4d provided in the piston connecting portion 4c, the damping force adjusting mechanism V can adjust the compression side damping force. it can. If it does in this way, it can set so that a liquid may pass through channel 5 only at the time of contraction operation of shock absorber 1.

  In addition, when the flow path 5 is set so as to communicate the expansion side chamber R1 and the compression side chamber R2, the damping force adjusting mechanism V has a damping force both when the straddle vehicle shock absorber 1 is extended and contracted. It may be set to perform adjustment. 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.

  Further, in the above description, the flow path area of the flow path 5 is set to decrease when the spool valve 7 is retracted. However, the spool valve 7 is set at the lowest position so that the flow path area of the flow path 5 is minimized. The flow path area of the flow path 5 may be increased by retreating the spool valve 7 or the flow path 5 may be completely blocked. .

  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.

  In addition, the shock absorber body D may be configured to exhibit a damping force only when extended when the damping force adjusting mechanism V exhibits the damping force when the shock absorber 1 is extended, or the damping force adjusting mechanism. When V exhibits a damping force when the shock absorber 1 contracts, a configuration in which the damping force is exerted only when the shock absorber 1 contracts may be adopted, and the straddle vehicle shock absorber 1 is applied to the vehicle in a pair of left and right wheels. May be set such that one of the left and right straddle vehicle shock absorbers 1 exhibits a damping force when extended, and the other exhibits a damping force when contracted.

  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 Saddle vehicle buffer 2 Cylinder 3 Piston 4 Piston rod 4b Air hole 5 Flow path 6 Housing 6a Hollow part 6b Port 6c Housing part 7 Spool valve 7a Empty part 7b Spool port 7c Pressure introduction hole 7d Annular groove 8 Solenoid 10 Car body Tube 11 Axle side tube 34 Adjuster 35 Biasing spring D Buffer body L Space R Reservoir R1 Extension side chamber R2 Pressure side chamber V Damping force adjustment mechanism

Claims (8)

A cylinder, a piston that is slidably inserted into the cylinder and divides the cylinder into a pressure side chamber and an extension side chamber, and a piston rod that is inserted into the cylinder and connected to the piston. A shock absorber body interposed between the vehicle body and the axle of the saddle vehicle, a flow passage that allows liquid to pass through one or both of the expansion and contraction of the shock absorber body, and in the middle of the flow passage A shock absorber for a saddle-riding vehicle provided with a damping force adjusting mechanism that is provided and adjusts the damping force.
The damping force adjusting mechanism includes a spool valve provided in the flow path and a solenoid that drives the spool valve in the flow path using the spool valve as a movable iron core , and the spool valve is disposed inside the solenoid. A shock absorber for a straddle vehicle , which is slidably inserted into a cylinder and has a thrust received from one end side by the flow path pressure of the spool valve equal to a thrust received from the other end side.   The damping force adjusting mechanism has an urging spring interposed between the spool valve and the solenoid,
  The spool valve includes a hollow portion that opens from one end receiving the pressure of the flow passage, a spool port that opens from an outer periphery and communicates with the hollow portion, and communicates with the hollow portion and has a flow passage on the other end side. The shock absorber for a straddle vehicle according to claim 1, further comprising: a pressure introducing hole for guiding pressure; and a step portion provided on an inner periphery of the spool valve and in contact with one end of the biasing spring. The damping force adjusting mechanism includes a hollow part that forms a part of the flow path and a port that opens from the outside and communicates with the hollow part and forms a part of the flow path together with the hollow part. Housing with
An empty portion that opens from one end side that receives the pressure of the flow channel, a spool port that opens from the outer periphery and communicates with the empty portion, and a pressure introduction that communicates with the empty portion and guides the pressure of the flow channel to the other end side With holes,
The spool valve is slidably inserted into the hollow portion,
The shock absorber for a saddle-ride vehicle according to claim 1 or 2 , wherein the liquid passes through the spool port and the port. A vehicle body side tube connected to the vehicle body of the saddle riding vehicle, and an axle side tube connected to the axle;
The piston rod is connected to the vehicle body side tube through the housing connected to the tip of the piston rod, and the cylinder is connected to the axle side tube to connect the shock absorber body to the vehicle body side tube and the axle side tube. And housed in the space formed by
Forming a reservoir in the space and outside the shock absorber body,
The shock absorber for a saddle-riding vehicle according to claim 3 , wherein the flow path passes through the piston rod in the axial direction and communicates with the reservoir. The piston rod has a hole that forms a part of the flow path along the axial direction, and the piston rod and the housing connected to the tip of the piston rod coaxially connect the hole and the hollow part. The shock absorber for a saddle-ride vehicle according to claim 3 or 4 , wherein the shock absorber is connected so as to be in series. The housing includes a housing portion that is connected to the hollow portion and houses the solenoid, and is fixed to the opening end of the vehicle body side tube with the housing portion facing outside, and the solenoid biases the spool valve. to comprise an adjuster for adjusting an initial load of biasing spring and the biasing spring, any one of 5 the adjuster from claim 3, characterized in that to face to the outside from the open end of the vehicle body side tube A shock absorber for a saddle-ride vehicle described in 1. An annular groove that communicates with the spool port along the circumferential direction is provided on the outer periphery of the spool valve, and the spool valve is driven by the solenoid to adjust the damping force by restricting the flow path between the port and the annular groove. The shock absorber for a saddle-ride vehicle according to any one of claims 3 to 6 . The shock absorber for a saddle-riding vehicle according to claim 7 , wherein an outer diameter of the spool valve is set to a single diameter except for an annular groove portion.

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