JP2007263324A - Hydraulic shock absorber - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To assemble a suspension spring to an outer periphery of a damper cylinder, attain compact structure eliminating the need of a sub tank, and perform temperature compensation of hydraulic oil not affecting a set load of the suspension spring, in a hydraulic shock absorber. <P>SOLUTION: In the hydraulic shock absorber 10, a first mounting member 91 is disposed to one end of the damper cylinder 11, a second mounting member 92 is disposed to the other end of a piston rod 20 facing the outside from the other end of the damper cylinder 11, or is disposed to a second piston 22, the suspension spring 95 is interposed between a spring receiver 94 disposed to the outer periphery of the damper cylinder 11 and a spring receiver 94 disposed to the second mounting member 92, a temperature compensation chamber 100 for hydraulic oil is disposed to the second mounting member 92. The temperature compensation chamber 100 is partitioned by a movable partition member 101 into a compensated oil chamber 100A and a gas chamber 100B, the compensated oil chamber 100A communicates with a hollow part 20A of the piston rod 20, and each of first and second oil chambers 31, 32 is respectively connected with the hollow part 20A of the piston rod 20 by means of orifice oil passages 111, 112. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a hydraulic shock absorber.

As a hydraulic shock absorber used on the rear wheel side of a motorcycle or the like, as described in Patent Document 1, a cylinder hole is formed in the swing arm, a fixed partition member is provided in the cylinder hole, and the fixed partition member is penetrated. Two pistons that are slidably contacted in the cylinder are provided at both ends of the piston rod that is slidably provided, and two upper and lower oil chambers that are partitioned by a fixed partition member are provided inside the two pistons. In addition to providing an oil passage communicating with the two oil chambers in the member, providing a damping force generating means in the oil passage, providing an oil passage communicating with the two oil chambers by bypassing the fixed partition member outside the damper cylinder, A damping force adjusting means is provided in the oil passage, a suspension spring is provided in a sub tank attached to the vehicle body side, and the oil pressure in the oil reservoir chamber partitioned from the upper oil chamber by the upper piston in the cylinder hole is adjusted. Lead to sub tank There is structure to urge the suspension spring by.
JP2004-306708

  In the prior art of Patent Document 1, it is difficult to form a cylinder hole in the swing arm, and since a suspension spring is provided in a sub tank attached to the vehicle body side, a hydraulic shock absorber for a motorcycle or the like is provided. There are difficulties in improving the degree of freedom of placement and reducing the weight.

  In addition, the temperature compensation of the hydraulic oil is performed in the oil reservoir chamber of the cylinder and the sub tank, but the pressure rising force of the hydraulic oil that has undergone volume expansion due to the temperature rise urges the suspension spring in the sub tank, and the initial setting of the suspension spring. Raise the load to the people.

  An object of the present invention is to provide two pistons at both ends of a piston rod that slides through a fixed partition member provided in a damper cylinder, and to provide a damping force generating means in an oil passage provided in the fixed partition member. In a hydraulic shock absorber that provides damping force adjustment means in the oil passage that bypasses the fixed partition wall member, a suspension spring is assembled on the outer periphery of the damper cylinder, realizing a compact structure that does not require a sub tank and affecting the set load of the suspension spring This is to compensate the temperature of the hydraulic oil that does not.

  According to the first aspect of the present invention, a fixed partition member is provided in the damper cylinder, and the first and second ends of the piston rod slidably provided through the fixed partition member are slidably contacted in the damper cylinder. And the second two pistons, the first and second oil chambers defined by the fixed partition member inside the first and second pistons in the cylinder, and the first fixed partition member. And an oil passage that communicates with the second oil chamber, a damping force generating means is provided in the oil passage, an oil passage that bypasses the fixed partition member and communicates the first and second oil chambers, In the hydraulic shock absorber provided with a damping force adjusting means in the oil passage, a first mounting member is provided at one end of the damper cylinder, and a second mounting is performed on the other end of the piston rod facing the outside from the other end of the damper cylinder or the second piston. Provide a member on the outer periphery of the damper cylinder A suspension spring is interposed between the spring support and the spring support provided on the second mounting member, a temperature compensation chamber for the hydraulic oil is provided on the second mounting member, and the temperature compensation chamber is configured to be a compensation oil chamber by a movable partition member. It is divided into a gas chamber, the hollow portion of the piston rod communicates with the compensation oil chamber, and each of the first and second oil chambers communicates with the hollow portion of the piston rod through an orifice oil passage. .

  According to a second aspect of the present invention, in the first aspect of the invention, the damping force adjusting means is incorporated in an outer surface bulging portion of the damper cylinder, and the outer surface bulging portion is used as a spring receiver on the damper cylinder side. Is.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, a pressure side stopper rubber is further provided at one end of the piston rod or the tip of the first piston, and the left side stopper rubber is provided on the inner surface of the first mounting member at the time of maximum compression. It is designed to make it possible to collide.

(Claim 1)
(a) By providing a temperature compensation chamber for hydraulic oil in the second mounting member, and communicating with the compensation oil chamber of the temperature compensation chamber by an orifice oil passage and a hollow portion provided in the piston rod for the first and second oil chambers. In a compact structure in which a suspension spring is assembled to the outer periphery of the damper cylinder and a sub tank is not required, a temperature compensation chamber that does not affect the set load of the suspension spring can be incorporated in the second mounting member. The degree of freedom of arrangement of the hydraulic shock absorber in the motorcycle increases, and the weight can be reduced.

(Claim 2)
(b) The damping force adjusting means is built in the outer surface bulging portion of the damper cylinder, and this outer surface bulging portion is used as a spring bearing on the damper cylinder side, so that a new spring receiving part is not required.

(Claim 3)
(c) A pressure-side stopper rubber is also provided at one end of the piston rod or the tip of the first piston, and this pressure-side stopper rubber can be brought into contact with the inner surface of the first mounting member at the maximum compression. Therefore, the compression side stopper rubber can be brought into contact with the inner surface of the first mounting member inside the damper cylinder to ensure the bottoming preventing effect.

  1 is a schematic cross-sectional view showing the most extended state of the hydraulic shock absorber, FIG. 2 is a schematic cross-sectional view showing the most compressed state of the hydraulic shock absorber, FIG. 3 is a schematic cross-sectional view taken along line III-III in FIG. Is a schematic enlarged sectional view showing the upper half of the hydraulic shock absorber, FIG. 5 is an enlarged sectional view showing the lower half of the hydraulic shock absorber, FIG. 6 is a schematic enlarged sectional view showing the compression side damping force adjusting device, and FIG. It is a model expanded sectional view which shows a side damping force adjustment apparatus.

  The hydraulic shock absorber 10 is used on the rear wheel side of the motorcycle as shown in FIGS. 1 to 3, and a fixed partition member 12 is provided in the damper cylinder 11. The damper cylinder 11 is liquid-tightly inserted and screwed into a cylindrical upper cylinder 11A formed by integrally forming a first mounting member 91, which will be described later, and a cylindrical lower cylinder 11B via O-rings 11C and 11D. The flange of the cylindrical bolt 13 is fitted into the inner peripheral step portion on the side where the lower cylinder 11B of the upper cylinder 11A is inserted, and the flange of the cylindrical bolt 13 is connected to the inner periphery of the upper cylinder 11A. The pressure is fixed between the stepped portion and the end surface of the lower cylinder 11B. A fixed partition member 12 is inserted into a central cylindrical portion of the cylindrical bolt 13 together with a constituent member of a damping force generating means 40 to be described later, and the fixed partition member 12 and the like are connected to a damper cylinder by a nut 14 screwed to the cylindrical bolt 13. 11 is fixed inside. The fixed partition member 12 is liquid-tightly fixed inside the cylinder 11 through an O-ring 12A.

  The hydraulic shock absorber 10 is slidably contacted in the cylinder 11 with one end and the other end of a piston rod 20 slidably provided through a central cylindrical portion of a cylindrical bolt 13 in which a fixed partition member 12 is inserted. First and second pistons 21 and 22 are provided. An air hole 15 is formed through one end of the upper cylinder 11 </ b> A on which the first piston 21 slides, and the lower cylinder 11 </ b> B on which the second piston 22 slides has an atmosphere open end 16. The first piston 21 is screwed to one end of the piston rod 20 and includes a seal ring 21A and a bush 21B that are in sliding contact with the inner periphery of the cylinder 11 (upper cylinder 11A) on the outer periphery. A sleeve 24 is screwed to the other end of the piston rod 20 together with a lock nut 23, and a second piston 22 is screwed to the outer periphery of the sleeve 24. The second piston 22 includes a seal ring 22A and a bush 22B that are in sliding contact with the inner periphery of the cylinder 11 (lower cylinder 11B) on the outer periphery.

(Damping force generating means 40) (FIG. 4)
The hydraulic shock absorber 10 is provided with first and second oil chambers 31 and 32 that are partitioned by both end faces of the fixed partition member 12 inside the two pistons 21 and 22 in the cylinder 11. The member 12 is provided with a pressure side oil passage 33 and an extension side oil passage 34 communicating with the first oil chamber 31 and the second oil chamber 32, and a damping force generating means 40 is provided in the oil passages 33 and 34. The damping force generating means 40 inserts the valve stopper 41, the pressure side plate valve 42, the fixed partition plate member 12, the extension side plate valve 43, and the valve stopper 44 into the central cylindrical portion of the cylindrical bolt 13 described above, and attaches them to the above described above. Fasten with nut 14.

  Accordingly, during the compression stroke of the hydraulic shock absorber 10, the damping force generating means 40 causes the oil in the second oil chamber 32 to open the pressure side plate valve 42 of the pressure side oil passage 33 as shown by arrow C in FIG. It is guided to the chamber 31 and generates a compression side damping force. Further, during the extension stroke of the hydraulic shock absorber 10, the oil in the first oil chamber 31 is led to the second oil chamber 32 by opening the extension side valve 43 of the extension side oil passage 34 as indicated by an arrow T in FIG. Generates extensional damping force.

  The hydraulic shock absorber 10 has a cylinder 11 (upper cylinder 11A) provided with a pressure side bypass oil passage 35 and an extension side bypass oil passage 36 that bypass the fixed partition wall member 12 and communicate the first oil chamber 31 and the second oil chamber 32. In addition, the compression side damping force adjusting means 50 and the extension side damping force adjusting means 70 are provided in each of the oil passages 35 and 36. The compression side damping force adjusting means 50 and the extension side damping force adjusting means 70 are built in the outer surface bulging portions 17 and 18 of the cylinder 11 (upper cylinder 11A).

(Compression side damping force adjusting means 50) (FIG. 6)
The compression-side damping force adjusting means 50 is provided in the compression-side bypass oil passage 35 for the working oil from the second oil chamber 32 to the first oil chamber 31 of the cylinder 11 when the hydraulic shock absorber 10 is compressed. A bottom piece 51, a washer 52, and a color joint 53 are sequentially inserted into a storage hole provided in the portion 17, and these are fixed by a plug bolt 54 that is screwed to the cylinder 11. A hollow center rod 55 is inserted into the bottom piece 51, and the pressure side main plate valve 56, the valve stopper 57, and the pressure side sub plate valve 58 are sandwiched between the center rod 55 and the bottom piece 51. Fixed to. The pressure side main plate valve 56 and the pressure side sub plate valve 58 can be opened by the outflow of oil during compression, and become check valves when extended.

  On the other hand, a valve spring adjuster 60 is rotatably provided on the plug bolt 54, and a spring receiver 61 is screwed onto the valve spring adjuster 60. The spring receiver 61 is linearly movable via a key 61A provided on the inner periphery of the plug bolt 54. A valve presser 62 is slidably fitted on the outer periphery of the cylindrical guide of the center rod 55, and the valve presser 62 abuts on the outer peripheral edge of the compression side main plate valve 56. A valve spring 63 is interposed between the spring receiver 61 and the valve presser 62. The spring force of the valve spring 63 applied to the pressure side main plate valve 56 is adjusted by moving the spring receiver 61 linearly by the screwing operation of the valve spring adjuster 60, thereby adjusting the pressing force applied to the pressure side main plate valve 56, and thus the pressure side main plate valve 56. The compression side damping force by the compression side main plate valve 56 can be adjusted when the piston speed of the hydraulic shock absorber 10 is medium to high.

  A nut 64 is fixed to the inner periphery of the tip of the valve spring adjuster 60. The nut 64 is liquid-tightly fitted to the inner periphery of the cylindrical guide of the center rod 55 and is screwed with a needle valve 65. . A needle adjuster 66 is rotatably provided at the center of the valve spring adjuster 60, and the needle adjuster 66 allows the needle valve 65 to be screwed with respect to the nut 64. The needle valve 65 advances and retreats to the orifice 67 at the center of the center rod 55 so that the degree of restriction of the orifice 67 can be adjusted. The needle adjuster 66 includes a ball 68A that is urged by a set spring 68. By rotating the needle adjuster 66, the ball 68A is sequentially engaged with engaging recesses at a plurality of positions in the circumferential direction of the valve spring adjuster 60. Thus, it is possible to adjust the compression side damping force when the degree of throttling of the orifice 67 by the needle valve 65 and the piston speed of the hydraulic shock absorber 10 is low.

  Accordingly, in the compression stroke of the hydraulic shock absorber 10 by the compression side damping force adjusting means 50, when the relative speed between the cylinder 11 and the piston rod 20 is low as shown by arrows C1 and C2 in FIGS. The oil that the second piston 22 extrudes from the second oil chamber 32 passes through the orifice 67 and further opens the pressure side sub-plate valve 58 to flow into the first oil chamber 31 (at the extremely low speed, the pressure-side sub plate valve 58 is closed). The compression side damping force is obtained by the throttle resistance by the needle valve 65 and the deflection resistance of the compression side sub-plate valve 58 during this period. This damping force is adjusted by adjusting the degree of restriction of the orifice 67 by the needle adjuster 66. When the relative speed between the cylinder 11 and the piston rod 20 is medium to high, the oil pushed out from the second oil chamber 32 by the second piston 22 pushes open the pressure-side main plate valve 56 and flows into the first oil chamber 31. The compression side damping force is obtained by the deflection resistance of the compression side main plate valve 56. This damping force is adjusted by adjusting the set load of the valve spring 63 by the valve spring adjuster 60.

(Extension side damping force adjusting means 70) (FIG. 7)
The extension side damping force adjusting means 70 is provided in the extension side bypass oil passage 36 for the working oil from the first oil chamber 31 to the second oil chamber 32 of the cylinder 11 when the hydraulic shock absorber 10 is extended. A bottom piece 71, a washer 72, and a collar joint 73 are sequentially inserted into a storage hole provided in the bulging portion 18, and these are fixed by a plug bolt 74 that is screwed onto the cylinder 11. A hollow center rod 75 is inserted into the bottom piece 71. The center rod 75 sandwiches the expansion side main plate valve 76, the valve stopper 77, and the expansion side sub plate valve 78 between the bottom piece 71, and the bottom 79 with the nut 79. It is fixed to the piece 71. The extension side main plate valve 76 and the extension side sub plate valve 78 can be opened by the outflow of oil during extension, and become check valves during compression.

  On the other hand, a valve spring adjuster 80 is rotatably provided on the plug bolt 74, and a spring receiver 81 is screwed onto the valve spring adjuster 80. The spring receiver 81 is linearly movable via a key 81A provided on the inner periphery of the plug bolt 74. A valve presser 82 is slidably fitted on the outer periphery of the cylindrical guide of the center rod 75, and the valve presser 82 abuts with the outer peripheral edge of the extension side main plate valve 76. A valve spring 83 is interposed between the spring receiver 81 and the valve presser 82. When the valve spring adjuster 80 is screwed, the spring receiver 81 is linearly moved to advance and retreat, thereby adjusting the holding force applied by the valve spring 83 to the expansion side main plate valve 76, and the valve opening pressure of the expansion side main plate valve 76. As a result, the extension side damping force by the extension side main plate valve 76 can be adjusted when the piston speed of the hydraulic shock absorber 10 is medium to high.

  Further, a nut 84 is fixed to the inner periphery of the tip of the valve spring adjuster 80, and the nut 84 is liquid-tightly fitted to the inner periphery of the cylindrical guide of the center rod 75 and is screwed with a needle valve 85. . A needle adjuster 86 is rotatably provided at the center of the valve spring adjuster 80, and the needle adjuster 86 enables the needle valve 85 to be screwed with respect to the nut 84. The needle valve 85 advances and retreats to and from the orifice 87 at the center of the center rod 75 so that the degree of restriction of the orifice 87 can be adjusted. The needle adjuster 86 includes a ball 88A that is urged by a set spring 88. By rotating the needle adjuster 86, the ball 88A is sequentially engaged with engaging recesses at a plurality of positions in the circumferential direction of the valve spring adjuster 80. Thus, it is possible to adjust the expansion side damping force when the degree of restriction of the orifice 87 by the needle valve 85 and, consequently, the piston speed of the hydraulic shock absorber 10 is low.

  Accordingly, when the relative speed of the cylinder 11 and the piston rod 20 is low as shown by arrows T1 and T2 in FIGS. 2, 3, and 7 in the extension stroke of the hydraulic shock absorber 10 by the extension side damping force adjusting means 70. The oil extruded from the first oil chamber 31 by the first piston 21 passes through the orifice 87 and further opens the expansion side sub-plate valve 78 to flow into the second oil chamber 32 (at the extremely low speed, the expansion side sub-plate valve 78 The expansion side damping force is obtained by the throttle resistance by the needle valve 85 and the deflection resistance of the expansion side sub-plate valve 78 during this period. This damping force is adjusted by adjusting the degree of restriction of the orifice 87 by the needle adjuster 86. Further, when the relative speed between the cylinder 11 and the piston rod 20 is medium to high, the oil pushed out from the first oil chamber 31 by the first piston 21 pushes open the extension main plate valve 76 and flows into the second oil chamber 32, The extension side damping force is obtained by the deflection resistance of the extension side main plate valve 76 during this period. This damping force is adjusted by adjusting the set load of the valve spring 83 by the valve spring adjuster 80.

  The hydraulic shock absorber 10 is provided with a first attachment member 91 attached to the vehicle body side (or the axle side) at one end top surface portion of the cylinder 11 (upper cylinder 11A). Further, the hydraulic shock absorber 10 is integrated with the other end of the piston rod 20 facing the outside from the other end open end of the cylinder 11 (lower cylinder 11B) or the second piston 22, in this embodiment, the second piston 22. A second attachment member 92 that is attached to (or the vehicle body side) is provided.

  In the hydraulic shock absorber 10, a suspension spring 95 is interposed between a spring receiver 93 provided on the outer periphery of the cylinder 11 (upper cylinder 11 </ b> A) and a spring receiver 94 provided on the second mounting member 92. In the present embodiment, the spring receiver 93 uses the downward end surfaces of the above-described outer bulging portions 17 and 18 provided in the cylinder 11 (upper cylinder 11A). The spring receiver 94 is supported by a retaining ring 92 </ b> A that is locked in the outer peripheral groove of the second mounting member 92.

  In the hydraulic shock absorber 10, a temperature compensation chamber 100 for hydraulic oil is provided in the second mounting member 92. The temperature compensation chamber 100 is divided into a compensation oil chamber 100A and a gas chamber 100B by a movable partition member 101 such as a free piston, and the hollow portion 20A of the piston rod 20 communicates with the compensation oil chamber 100A. Is connected to the hollow portion 20A of the piston rod 20 through the orifice oil passage 111 provided in the piston rod 20, and the second oil chamber 32 is connected to the hollow portion 20A of the piston rod 20 through the orifice oil passage 112 provided in the piston rod 20. . As a result, the oil that has undergone volume expansion due to the temperature rise of the hydraulic shock absorber 10 passes from the first oil chamber 31 or the second oil chamber 32 through the orifice oil passages 111 and 112 of the piston rod 20 from the hollow portion 20A to the compensation oil chamber 100A. Can be spilled into. The gas chamber 100B can be a pressurized chamber.

  The hydraulic shock absorber 10 is provided with a pressure side stopper rubber 120 made of foamed urethane or the like at one end of the piston rod 20 or the front end of the first piston 21, in this embodiment, the front end of the first piston 21. 120 abuts on the top surface of one end of the upper cylinder 11A, in other words, the inner surface of the first mounting member 91, and restricts the end of the most compressed stroke.

  The hydraulic shock absorber 10 is provided with an extension-side stopper rubber 130 on the end face of the cylindrical bolt 13 facing the first oil chamber 31, and the end face of the first piston 21 abuts with the extension-side stopper rubber 130 at the time of maximum extension, so that the maximum extension is achieved. Restrict stroke end. The cylindrical bolt 13 includes an oil hole 13A that guides the oil in the first oil chamber 31 to the fixed partition member 12 side.

The operation of the hydraulic shock absorber 10 will be described.
(1) During the compression stroke of the hydraulic shock absorber 10, the piston rod 20 enters the cylinder 11 and compresses the suspension spring 95 to reduce the impact received by the vehicle from the road surface. At the same time, the damping force generating means 40 guides the oil in the second oil chamber 32 to the first oil chamber 31 by opening the pressure side plate valve 42 of the pressure side oil passage 33 as shown by arrow C in FIG. Is generated. In addition, when the relative speed between the cylinder 11 and the piston rod 20 is low as shown by arrows C1 and C2 in FIG. 1, FIG. 3, and FIG. The oil extruded from 32 passes through the orifice 67 and further opens the pressure side sub-plate valve 58 to flow into the first oil chamber 31 (at the time of extremely low speed, the pressure-side sub plate valve 58 is closed). The compression side damping force is obtained by the deflection resistance of the compression side sub-plate valve 58. This damping force is adjusted by adjusting the degree of restriction of the orifice 67 by the needle adjuster 66. Further, when the relative speed between the cylinder 11 and the piston rod 20 is medium to high, the oil pushed out from the second oil chamber 32 by the second piston 22 pushes open the pressure side main plate valve 56 and flows into the first oil chamber 31. The compression side damping force is obtained by the deflection resistance of the compression side main plate valve 56. This damping force is adjusted by adjusting the set load of the valve spring 63 by the valve spring adjuster 60.

  (2) During the extension stroke of the hydraulic shock absorber 10, the damping force generating means 40 causes the oil in the first oil chamber 31 to open the extension side plate valve 43 of the extension side oil passage 34 as indicated by the arrow T in FIG. 2 It is led to the oil chamber 32 and generates an extension side damping force. Further, when the relative speed of the cylinder 11 and the piston rod 20 is low as shown by arrows T1, T2 in FIGS. The oil extruded from the chamber 31 passes through the orifice 87, further pushes open the expansion side sub-plate valve 78 and flows into the second oil chamber 32 (at the extremely low speed, the expansion side sub-plate valve 78 is closed). The expansion side damping force is obtained by the drawing resistance due to the above and the deflection resistance of the expansion side sub-plate valve 78. This damping force is adjusted by adjusting the degree of restriction of the orifice 87 by the needle adjuster 86. Further, when the relative speed between the cylinder 11 and the piston rod 20 is medium to high, the oil pushed out from the first oil chamber 31 by the first piston 21 pushes open the extension main plate valve 76 and flows into the second oil chamber 32, The extension side damping force is obtained by the deflection resistance of the extension side main plate valve 76 during this period. This damping force is adjusted by adjusting the set load of the valve spring 83 by the valve spring adjuster 80.

  The expansion / contraction vibration of the suspension spring 95 is controlled by the damping force on the compression side and the extension side in the above (1) and (2).

According to the present embodiment, the following operational effects can be obtained.
(a) The temperature compensation chamber 100 for the hydraulic oil is provided in the second mounting member 92, and the temperature compensation is performed by the orifice oil passages 111 and 112 in which the first and second oil chambers 31 and 32 are provided in the piston rod 20 and the hollow portion 20A. A temperature compensation chamber that does not affect the set load of the suspension spring 95 in a compact structure in which the suspension spring 95 is assembled on the outer periphery of the damper cylinder 11 and no sub tank is required by contacting the compensation oil chamber 100A of the chamber 100. 100 can be built in the second mounting member 92. The degree of freedom of arrangement of the hydraulic shock absorber 10 on the motorcycle increases, and the weight can be reduced.

  (b) The damping force adjusting means 50 and 70 are built in the outer surface bulging portions 17 and 18 of the damper cylinder 11, and the outer surface bulging portions 17 and 18 are used as spring receivers 93 on the damper cylinder 11 side. Spring bearing parts are not required.

  (c) A pressure-side stopper rubber 120 is also provided at one end of the piston rod 20 or the tip of the first piston 21 so that the pressure-side stopper rubber 120 can abut against the inner surface of the first mounting member 91 at the time of maximum compression. Therefore, the compression side stopper rubber 120 can be brought into contact with the inner surface of the first mounting member 91 inside the damper cylinder 11 to ensure the bottoming preventing effect.

  The embodiment of the present invention has been described in detail with reference to the drawings. However, the specific configuration of the present invention is not limited to this embodiment, and even if there is a design change or the like without departing from the gist of the present invention. It is included in the present invention.

FIG. 1 is a schematic cross-sectional view showing the most extended state of the hydraulic shock absorber. FIG. 2 is a schematic cross-sectional view showing the most compressed state of the hydraulic shock absorber. 3 is a schematic cross-sectional view taken along line III-III in FIG. FIG. 4 is a schematic enlarged sectional view showing the upper half of the hydraulic shock absorber. FIG. 5 is an enlarged cross-sectional view showing the lower half of the hydraulic shock absorber. FIG. 6 is a schematic enlarged sectional view showing the compression side damping force adjusting device. FIG. 7 is a schematic enlarged sectional view showing the extension side damping force adjusting device.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Hydraulic buffer 11 Damper cylinder 12 Fixed partition member 20 Piston rod 20A Hollow part 21 1st piston 22 2nd piston 31 1st oil chamber 32 2nd oil chamber 33 Pressure side oil path 34 Extension side oil path 35 Pressure side bypass oil path 36 Extension side bypass oil passage 40 Damping force generation means 42 Pressure side plate valve 43 Extension side plate valve 50 Front side damping force adjustment means 56 Pressure side main plate valve 58 Pressure side sub plate valve 65 Needle valve 70 Extension side damping force adjustment means 76 Extension side main plate valve 78 Extension side sub-plate valve 85 Needle valve 91 First attachment member 92 Second attachment member 93 Spring receiver 94 Spring receiver 95 Suspension spring 100 Temperature compensation chamber 100A Compensation oil chamber 100B Gas chamber 101 Movable partition member 111 Orifice oil passage 112 Orifice oil Road 120 Pressure side stopper rubber

Claims (3)

A fixed partition member is provided in the damper cylinder.
First and second pistons that are slidably contacted in the damper cylinder are provided at one end and the other end of the piston rod that are slidably provided through the fixed partition member,
First and second oil chambers defined by a fixed partition member are provided inside the first and second pistons in the cylinder,
An oil passage communicating the first and second oil chambers is provided in the fixed partition member, and a damping force generating means is provided in the oil passage,
In the hydraulic shock absorber provided with an oil passage that bypasses the fixed partition member and communicates the first and second oil chambers, and provided with damping force adjusting means in the oil passage,
A first mounting member is provided at one end of the damper cylinder,
A second mounting member is provided on the other end of the piston rod facing the outside from the other end of the damper cylinder or the second piston;
A suspension spring is interposed between a spring receiver provided on the outer periphery of the damper cylinder and a spring receiver provided on the second mounting member;
The second mounting member is provided with a temperature compensation chamber for hydraulic oil, the temperature compensation chamber is divided into a compensation oil chamber and a gas chamber by a movable partition member, and the hollow portion of the piston rod is communicated with the compensation oil chamber. A hydraulic shock absorber characterized in that each of the oil chambers is connected to the hollow portion of the piston rod by an orifice oil passage.   2. The hydraulic shock absorber according to claim 1, wherein the damping force adjusting means is built in an outer surface bulging portion of the damper cylinder, and the outer surface bulging portion serves as a spring bearing on the damper cylinder side.   3. The hydraulic shock absorber according to claim 1, wherein a pressure-side stopper rubber is provided at one end of the piston rod or the tip of the first piston, and the left-side stopper rubber can be brought into contact with the inner surface of the first mounting member at the time of maximum compression.

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