JP6877587B2 - Buffer and solenoid - Google Patents

Buffer and solenoid Download PDF

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JP6877587B2
JP6877587B2 JP2019562751A JP2019562751A JP6877587B2 JP 6877587 B2 JP6877587 B2 JP 6877587B2 JP 2019562751 A JP2019562751 A JP 2019562751A JP 2019562751 A JP2019562751 A JP 2019562751A JP 6877587 B2 JP6877587 B2 JP 6877587B2
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core
mover
magnetic
solenoid
shock absorber
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JPWO2019130682A1 (en
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山岡　史之
史之 山岡
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Hitachi Astemo Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/121—Guiding or setting position of armatures, e.g. retaining armatures in their end position
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Damping Devices (AREA)
  • Electromagnets (AREA)

Description

本発明は、ピストンロッドのストロークに対して作動流体の流れを制御することで減衰力を発生させる緩衝器に関する。 The present invention relates to a shock absorber that generates a damping force by controlling the flow of a working fluid with respect to the stroke of a piston rod.

特許文献１には、軸方向に配置された磁性部と非磁性部とを接合して一体化させたコア構造のソレノイドを備えたピストン内蔵型の減衰力調整式油圧緩衝器が開示されている。この緩衝器は、可動子の外径が全長にわたって同一で、かつ、磁性部と可動子とのクリアランス（径方向隙間）と、非磁性部と可動子とのクリアランスと、が同一である。 Patent Document 1 discloses a damping force adjusting type hydraulic shock absorber with a built-in piston, which includes a solenoid having a core structure in which a magnetic portion and a non-magnetic portion arranged in the axial direction are joined and integrated. .. In this shock absorber, the outer diameter of the mover is the same over the entire length, and the clearance between the magnetic part and the mover (diameter gap) and the clearance between the non-magnetic part and the mover are the same.

特表２０１２−５０１４１２号公報Special Table 2012-501412

特許文献１に記載された緩衝器は、可動子のコアに対する軸方向移動範囲において、可動子の外周面の全てがコアの内周面に摺動するため、可動子がコアに対して偏心すると、可動子に作用する横方向の磁力が周方向で不均一になり、可動子とコアとの摺動抵抗が増大する。その結果、減衰力のヒステリシス、すなわち、制御電流を増加方向へ変化させたときに発生する減衰力と制御電流を減少方向へ変化させたときに発生する減衰力との差異が大きくなり、減衰力制御性が悪化する。 In the shock absorber described in Patent Document 1, in the axial movement range of the mover with respect to the core, all the outer peripheral surfaces of the mover slide on the inner peripheral surface of the core, so that the mover is eccentric with respect to the core. , The lateral magnetic force acting on the mover becomes non-uniform in the circumferential direction, and the sliding resistance between the mover and the core increases. As a result, the hysteresis of the damping force, that is, the difference between the damping force generated when the control current is changed in the increasing direction and the damping force generated when the control current is changed in the decreasing direction becomes large, and the damping force becomes large. Controllability deteriorates.

本発明は、減衰力制御性を向上させた緩衝器を提供することを課題とする。 An object of the present invention is to provide a shock absorber having improved damping force controllability.

本発明の一実施形態に係る緩衝器は、
作動流体が封入されるシリンダと、
前記シリンダ内に摺動可能に嵌装されるピストンと、
一端が前記ピストンに連結され、他端側が前記シリンダの外部に延出されるピストンロッドと、
ソレノイドに流れる制御電流を制御することで減衰力特性が調整可能な減衰力発生機構と、を備え、
前記ソレノイドは、
通電されることで磁力を発生するコイルと、
前記コイルの内周側に設けられ、内周が円筒状の磁性部と内周が円筒状の非磁性部とを有するコアであって、前記磁性部と前記非磁性部は前記コアの軸方向に沿って配置された前記コアと、
前記コアの内周側を該コアの軸方向へ移動可能な可動子と、を備え、
前記可動子の前記コアに対する前記軸方向の移動範囲において、前記可動子と前記コアとの径方向間距離が大きい部分と該径方向間距離が前記大きい部分よりも小さい部分とを有し、前記小さい部分は、前記コアの非磁性部と対向する位置に設けられると共に摺接する。
The shock absorber according to the embodiment of the present invention is
A cylinder in which the working fluid is sealed and
A piston that is slidably fitted in the cylinder,
A piston rod whose one end is connected to the piston and whose other end extends to the outside of the cylinder.
It is equipped with a damping force generation mechanism whose damping force characteristics can be adjusted by controlling the control current flowing through the solenoid.
The solenoid is
A coil that generates a magnetic force when energized,
Provided on the inner peripheral side of the coil, the inner circumference the inner periphery and a cylindrical magnetic portion with a core and a cylindrical non-magnetic portion, the said magnetic part nonmagnetic portion axially of the core With the core arranged along
A mover capable of moving the inner peripheral side of the core in the axial direction of the core is provided.
In the axial movement range of the mover with respect to the core, the mover has a portion having a large radial distance between the mover and the core and a portion having a portion having a smaller radial distance than the large portion. The small portion is provided at a position facing the non-magnetic portion of the core and is in sliding contact with the core.

本発明の一実施形態に係る緩衝器によれば、緩衝器の減衰力制御性を向上させることができる。 According to the shock absorber according to the embodiment of the present invention, the damping force controllability of the shock absorber can be improved.

第１実施形態に係る緩衝器の断面図である。It is sectional drawing of the shock absorber which concerns on 1st Embodiment. 図１におけるピストンバルブを含む要部の拡大図である。It is an enlarged view of the main part including a piston valve in FIG. 図２におけるソレノイドを含む要部の拡大図である。It is an enlarged view of the main part including a solenoid in FIG. 第１実施形態の説明図であって、ソレノイドにおける磁気流れを示す図である。It is explanatory drawing of 1st Embodiment and is a figure which shows the magnetic flow in a solenoid. 第１実施形態の説明図であって、可動子とコアとのクリアランスを横軸に取り、可動子の発生力を縦軸に取ったときの、ソレノイド推力、区間Ａにおける横力、および区間Ｃにおける横力を示す図表である。In the explanatory view of the first embodiment, the solenoid thrust, the lateral force in the section A, and the section C when the clearance between the mover and the core is taken on the horizontal axis and the generated force of the mover is taken on the vertical axis. It is a chart which shows the lateral force in. 第１実施形態の説明図であって、従来構造のソレノイドを備えた緩衝器の減衰力特性を示す図表である。It is explanatory drawing of 1st Embodiment, and is the figure which shows the damping force characteristic of the shock absorber provided with the solenoid of the conventional structure. 第１実施形態の説明図であって、第１実施形態のソレノイドが適用された緩衝器の減衰力特性を示す図表である。It is explanatory drawing of 1st Embodiment, and is the figure which shows the damping force characteristic of the shock absorber to which the solenoid of 1st Embodiment is applied. 第２実施形態の説明図である。It is explanatory drawing of 2nd Embodiment.

（第１実施形態） 本発明の第１実施形態を添付した図を参照して説明する。便宜上、図１における上下方向を「上下方向」と称する。
図１を参照すると、第１実施形態に係る緩衝器１は、ソレノイド９１を有する減衰力発生機構３１がシリンダ２内のピストンケース２１（ピストン）に内蔵された、いわゆる、ピストン内蔵型の減衰力調整式緩衝器１（以下「緩衝器１」と称する）である。緩衝器１は、シリンダ２の外側に外筒３を設けた複筒構造をなし、シリンダ２と外筒３との間にリザーバ４が形成される。シリンダ２内には、ピストンバルブ５（ピストン）が摺動可能に嵌装される。ピストンバルブ５は、外周側にピストンバンド５Ａが設けられ、シリンダ２内をシリンダ上室２Ａとシリンダ下室２Ｂとの２室に区画する。ピストンバルブ５は、上端がシリンダ上室２Ａに開口する伸び側通路１９と、下端がシリンダ下室２Ｂに開口する縮み側通路２０と、を有する。(First Embodiment) This will be described with reference to the figure to which the first embodiment of the present invention is attached. For convenience, the vertical direction in FIG. 1 is referred to as "vertical direction".
Referring to FIG. 1, the shock absorber 1 according to the first embodiment has a so-called built-in piston damping force in which a damping force generating mechanism 31 having a solenoid 91 is built in a piston case 21 (piston) in a cylinder 2. It is an adjustable shock absorber 1 (hereinafter referred to as "buffer 1"). The shock absorber 1 has a double-cylinder structure in which an outer cylinder 3 is provided on the outside of the cylinder 2, and a reservoir 4 is formed between the cylinder 2 and the outer cylinder 3. A piston valve 5 (piston) is slidably fitted in the cylinder 2. The piston valve 5 is provided with a piston band 5A on the outer peripheral side, and the inside of the cylinder 2 is divided into two chambers, a cylinder upper chamber 2A and a cylinder lower chamber 2B. The piston valve 5 has an extension side passage 19 whose upper end opens into the cylinder upper chamber 2A and a contraction side passage 20 whose lower end opens into the cylinder lower chamber 2B.

シリンダ２の下端部には、シリンダ下室２Ｂとリザーバ４とを区画するベースバルブ７が設けられる。ベースバルブ７には、シリンダ下室２Ｂとリザーバ４とを連通させる通路８，９が設けられる。通路８には、リザーバ４側からシリンダ下室２Ｂ側への油液（作動流体）の流通のみが許容される逆止弁１０が設けられる。通路９には、シリンダ下室２Ｂ側の油液の圧力が設定圧力に達することで開弁し、シリンダ下室２Ｂ側の圧力（油液）をリザーバ４側へ逃がすディスクバルブ１１が設けられる。なお、作動流体として、シリンダ２内には油液が封入され、リザーバ４内には油液およびガスが封入される。また、外筒３の下端にはボトムキャップ１２が接合され、ボトムキャップ１２には取付部材１３が接合される。 A base valve 7 for partitioning the lower chamber 2B of the cylinder and the reservoir 4 is provided at the lower end of the cylinder 2. The base valve 7 is provided with passages 8 and 9 for communicating the lower chamber 2B of the cylinder and the reservoir 4. The passage 8 is provided with a check valve 10 that allows only the flow of oil (working fluid) from the reservoir 4 side to the cylinder lower chamber 2B side. The passage 9 is provided with a disc valve 11 that opens when the pressure of the oil liquid on the lower chamber 2B side of the cylinder reaches a set pressure and releases the pressure (oil liquid) on the lower chamber 2B side of the cylinder to the reservoir 4. As the working fluid, an oil liquid is sealed in the cylinder 2, and an oil liquid and a gas are sealed in the reservoir 4. Further, a bottom cap 12 is joined to the lower end of the outer cylinder 3, and a mounting member 13 is joined to the bottom cap 12.

ピストンバルブ５は、ピストンケース２１を介してピストンロッド６に連結される。ピストンケース２１は、ピストンロッド６の下端（一端）に連結される略円筒形のケース本体２２と、ケース本体２２の下端を閉塞させるケース底部２３と、ケース底部２３の下端から軸方向（下方向）へ延びてピストンバルブ５が装着される軸部２４と、を有する。ケース底部２３と軸部２４とは一部品であり、ケース本体２２とケース底部２３とはねじ部１８によって一体化される。なお、ピストンロッド６の上端側（他端側）は、シリンダ上室２Ａを通過し、さらにシリンダ２および外筒３の上端部に装着されたロッドガイド１４およびオイルシール１５に挿通されてシリンダ２の外部へ延出される。また、外筒３の上端部はキャップ１６によってカバーされ、外筒３の外周にはばね受部材１７が取り付けられる。 The piston valve 5 is connected to the piston rod 6 via the piston case 21. The piston case 21 has a substantially cylindrical case body 22 connected to the lower end (one end) of the piston rod 6, a case bottom 23 that closes the lower end of the case body 22, and an axial direction (downward) from the lower end of the case bottom 23. ), And a shaft portion 24 on which the piston valve 5 is mounted. The case bottom 23 and the shaft 24 are one component, and the case body 22 and the case bottom 23 are integrated by a screw portion 18. The upper end side (the other end side) of the piston rod 6 passes through the cylinder upper chamber 2A, and is further inserted into the rod guide 14 and the oil seal 15 mounted on the upper ends of the cylinder 2 and the outer cylinder 3 to form the cylinder 2. It is extended to the outside of. Further, the upper end portion of the outer cylinder 3 is covered by the cap 16, and the spring receiving member 17 is attached to the outer circumference of the outer cylinder 3.

図２を参照すると、緩衝器１は、ピストンロッド６の移動によって生じるシリンダ上室２Ａとシリンダ下室２Ｂとの間の油液の流れを制御することで減衰力を発生させる減衰力発生機構３１を備える。減衰力発生機構３１は、ピストンバルブ５の下端に設けられるメインバルブ３２を有する。メインバルブ３２は、ピストンバルブ５が伸び側へ移動したときのシリンダ上室２Ａからシリンダ下室２Ｂへの油液の流れを規制することで減衰力を発生させる減衰弁３３と、減衰弁３３に対して閉弁方向へ内圧を作用させる背圧室３４と、シリンダ上室２Ａから背圧室３４へ油液を導入させる背圧室導入通路３５と、を有する。 Referring to FIG. 2, the shock absorber 1 has a damping force generating mechanism 31 that generates a damping force by controlling the flow of oil and liquid between the cylinder upper chamber 2A and the cylinder lower chamber 2B generated by the movement of the piston rod 6. To be equipped. The damping force generating mechanism 31 has a main valve 32 provided at the lower end of the piston valve 5. The main valve 32 includes a damping valve 33 that generates a damping force by regulating the flow of oil and liquid from the cylinder upper chamber 2A to the cylinder lower chamber 2B when the piston valve 5 moves to the extension side, and a damping valve 33. On the other hand, it has a back pressure chamber 34 for applying internal pressure in the valve closing direction, and a back pressure chamber introduction passage 35 for introducing an oil liquid from the cylinder upper chamber 2A into the back pressure chamber 34.

減衰弁３３は、ディスクバルブによって構成され、軸孔にピストンケース２１の軸部２４が挿通される。減衰弁３３の内側周縁部は、ピストンバルブ５の内側周縁部とパイロットケース３６の軸部３６Ａとによって挟持される。減衰弁３３の下面には、環状のパッキン３７（シート部）が設けられる。パッキン３７は、パイロットケース３６の環状壁部３８の内周面に摺動可能に当接される。これにより、減衰弁３３とパイロットケース３６との間に環状の背圧室３４が形成される。減衰弁３３は、ピストンバルブ５の伸び側通路１９の下端開口を被うようにして、外側周縁部がピストンバルブ５の下端に着座される。そして、ピストンバルブ５の上端に形成されて径方向へ延びる通路２７（切欠き）、伸び側通路１９、および減衰弁３３の開弁により形成される流路によって、シリンダ上室２Ａとシリンダ下室２Ｂとを連通させる第１通路が構成される。 The damping valve 33 is composed of a disc valve, and the shaft portion 24 of the piston case 21 is inserted into the shaft hole. The inner peripheral edge of the damping valve 33 is sandwiched between the inner peripheral edge of the piston valve 5 and the shaft portion 36A of the pilot case 36. An annular packing 37 (seat portion) is provided on the lower surface of the damping valve 33. The packing 37 is slidably contacted with the inner peripheral surface of the annular wall portion 38 of the pilot case 36. As a result, an annular back pressure chamber 34 is formed between the damping valve 33 and the pilot case 36. The damping valve 33 covers the lower end opening of the extension side passage 19 of the piston valve 5, and the outer peripheral edge portion is seated at the lower end of the piston valve 5. Then, the cylinder upper chamber 2A and the cylinder lower chamber are formed by the passage 27 (notch) formed at the upper end of the piston valve 5 and extending in the radial direction, the extension side passage 19, and the flow path formed by opening the damping valve 33. A first passage that communicates with 2B is configured.

パイロットケース３６は、パイロットケース３６を上下方向へ貫通する複数個の通路４１を有する。パイロットケース３６の下端には、ディスクバルブ３９が設けられる。ディスクバルブ３９は、軸孔にピストンケース２１の軸部２４が挿通され、パイロットケース３６の通路４１の下端開口を被うようにして、外側周縁部がパイロットケース３６の下端に形成された環状のシート部４０に着座される。そして、背圧室３４の圧力がディスクバルブ３９のセット荷重に達すると、ディスクバルブ３９が開弁される。これにより、背圧室３４の圧力（油液）をシリンダ下室２Ｂへ逃がすことができる。なお、ディスクバルブ３９の内周縁部は、パイロットケース３６の軸部３６Ａとワッシャ４２との間で挟持される。 The pilot case 36 has a plurality of passages 41 penetrating the pilot case 36 in the vertical direction. A disc valve 39 is provided at the lower end of the pilot case 36. The disc valve 39 has an annular shape in which the shaft portion 24 of the piston case 21 is inserted into the shaft hole so as to cover the lower end opening of the passage 41 of the pilot case 36, and the outer peripheral edge portion is formed at the lower end of the pilot case 36. It is seated on the seat portion 40. Then, when the pressure in the back pressure chamber 34 reaches the set load of the disc valve 39, the disc valve 39 is opened. As a result, the pressure (oil liquid) in the back pressure chamber 34 can be released to the cylinder lower chamber 2B. The inner peripheral edge of the disc valve 39 is sandwiched between the shaft portion 36A of the pilot case 36 and the washer 42.

ピストンバルブ５の上端には、ディスクバルブ４３が設けられる。ディスクバルブ４３は、軸孔にピストンケース２１の軸部２４が挿通され、内側周縁部がピストンバルブ５の内側周縁部と弁部材２５の内側周縁部とによって挟持される。ディスクバルブ４３は、ピストンバルブ５の上端に形成された環状凹部４４を被うようにして、外側周縁部がピストンケース５の上端に形成された環状のシート部４５に着座される。弁部材２５は、軸孔にピストンケース２１の軸部２４が挿通され、ピストンケース２１のケース底部２３の下端面に形成された環状凹部を被うようにして、上端面がケース底部２３の下端面に当接される。これにより、ピストンケース２１のケース底部２３と弁部材２５との間には、環状通路５０が形成される。なお、ピストンバルブ５の環状凹部４４には、縮み側通路２０の上端が開口される。 A disc valve 43 is provided at the upper end of the piston valve 5. The shaft portion 24 of the piston case 21 is inserted into the shaft hole of the disc valve 43, and the inner peripheral edge portion is sandwiched between the inner peripheral edge portion of the piston valve 5 and the inner peripheral edge portion of the valve member 25. The disc valve 43 is seated on the annular seat portion 45 whose outer peripheral edge is formed at the upper end of the piston case 5 so as to cover the annular recess 44 formed at the upper end of the piston valve 5. The upper end surface of the valve member 25 is below the case bottom 23 so that the shaft portion 24 of the piston case 21 is inserted into the shaft hole and covers the annular recess formed on the lower end surface of the case bottom 23 of the piston case 21. It comes into contact with the end face. As a result, an annular passage 50 is formed between the case bottom 23 of the piston case 21 and the valve member 25. The upper end of the contraction side passage 20 is opened in the annular recess 44 of the piston valve 5.

弁部材２５の下端には、ディスクバルブ４７が設けられる。ディスクバルブ４７は、軸孔にピストンケース２１の軸部２４が挿通され、内側周縁部がディスク４８と弁部材２５の内側周縁部との間で挟持される。ディスクバルブ４７は、弁部材２５の下端の外側周縁部に形成された環状のシート部４９Ａとシート部４９Ａの内側に形成された環状のシート部４９Ｂとに着座される。弁部材２５とピストンケース２１のケース底部２３との間の環状通路５０は、弁部材２５を軸方向（上下方向）へ貫通する通路２５Ａ、ピストンケース２１の軸部２４の外周面に形成されて軸方向へ延びる通路２８、およびパイロットケース３６の軸部３６Ａに形成された通路４６を介して、背圧室３４に連通される。なお、軸孔に軸部２４が挿通される各部品は、軸部２４の下端部に装着されたナット２６の締め付けにより生じる軸力によってピストンケース２１のケース底部２３に固定される。 A disc valve 47 is provided at the lower end of the valve member 25. The shaft portion 24 of the piston case 21 is inserted into the shaft hole of the disc valve 47, and the inner peripheral edge portion is sandwiched between the disc 48 and the inner peripheral edge portion of the valve member 25. The disc valve 47 is seated on an annular seat portion 49A formed on the outer peripheral edge of the lower end of the valve member 25 and an annular seat portion 49B formed inside the seat portion 49A. The annular passage 50 between the valve member 25 and the case bottom 23 of the piston case 21 is formed on the outer peripheral surface of the shaft portion 24 of the piston case 21 and the passage 25A that penetrates the valve member 25 in the axial direction (vertical direction). It communicates with the back pressure chamber 34 via a passage 28 extending in the axial direction and a passage 46 formed in the shaft portion 36A of the pilot case 36. Each component through which the shaft portion 24 is inserted into the shaft hole is fixed to the case bottom 23 of the piston case 21 by the axial force generated by tightening the nut 26 attached to the lower end portion of the shaft portion 24.

ピストンケース２１のケース底部２３には、ケース底部２３を軸線方向（上下方向）へ貫通する複数本（図２に「１本」のみ表示）の通路５１が設けられる。通路５１は、下端が環状通路５０に開口し、上端がケース底部２３の環状の側壁の内側に形成された室５２に開口される。ピストンケース２１の底面（室５２の底面）には弁座５５が形成され、弁座５５には第１弁体５３の下端に形成された環状のシート部５４が着座される。そして、弁座５５に第１弁体５３のシート部５４が着座されることにより、第１弁体５３とケース底部２３との間に第１弁室５６が形成される。第１弁室５６は、軸部２４に形成された通路５７（軸孔）を介してシリンダ下室２Ｂに連通される。 The case bottom 23 of the piston case 21 is provided with a plurality of passages 51 (only "one" is shown in FIG. 2) penetrating the case bottom 23 in the axial direction (vertical direction). The lower end of the passage 51 opens to the annular passage 50, and the upper end opens to the chamber 52 formed inside the annular side wall of the case bottom 23. A valve seat 55 is formed on the bottom surface of the piston case 21 (bottom surface of the chamber 52), and an annular seat portion 54 formed at the lower end of the first valve body 53 is seated on the valve seat 55. Then, the seat portion 54 of the first valve body 53 is seated on the valve seat 55, so that the first valve chamber 56 is formed between the first valve body 53 and the case bottom portion 23. The first valve chamber 56 communicates with the cylinder lower chamber 2B via a passage 57 (shaft hole) formed in the shaft portion 24.

そして、通路５７、第１弁室５６、第１弁体５３の開弁により形成される流路、室５２、通路５１、およびディスクバルブ４７の開弁により形成される流路によって、シリンダ上室２Ａとシリンダ下室２Ｂとを連通させる第２通路が構成される。換言すると、第２通路は、ディスクバルブ４７が開弁・閉弁されることにより連通・遮断される。また、第２通路は、ピストンバルブ５（ピストンロッド６）が縮み側へ移動され、第１弁室５６の圧力がセット荷重に達して第１弁体５３が開弁されることで、シリンダ上室２Ａとシリンダ下室２Ｂとの間を連通させる。さらに、室５２は、通路５１、環状通路５０、および軸部２４に形成された通路２８を介して背圧室３４に連通される。 Then, the cylinder upper chamber is formed by the flow path formed by opening the passage 57, the first valve chamber 56, and the first valve body 53, the chamber 52, the passage 51, and the flow path formed by opening the disc valve 47. A second passage that connects 2A and the cylinder lower chamber 2B is configured. In other words, the second passage is communicated / shut off by opening / closing the disc valve 47. Further, in the second passage, the piston valve 5 (piston rod 6) is moved to the contraction side, the pressure in the first valve chamber 56 reaches the set load, and the first valve body 53 is opened, so that the first valve body 53 is opened on the cylinder. The chamber 2A and the cylinder lower chamber 2B are communicated with each other. Further, the chamber 52 communicates with the back pressure chamber 34 via the passage 51, the annular passage 50, and the passage 28 formed in the shaft portion 24.

第１弁体５３は、非磁性体であり、大径部５８と小径部５９とを有する段付円柱形に形成される。第１弁体５３の小径部５９は、後述するコア９３の磁性部９６の内周面１１４の下部に摺動可能に嵌装される。第１弁体５３の小径部５９とコア９３の磁性部９６の内周面１１４との間は、シール部材６０（図３参照）によってシールされる。第１弁体５３には、上端が開口するボア６３が形成される。ボア６３には、ニードル型の第２弁体６５が収容される。第２弁体６５は、ボア６３の底面に開口する第２弁室６９の開口周縁部に形成された弁座６４に着座される。第１弁体５３および第２弁体６５のセット荷重は、ソレノイド９１に対する制御電流を調節することによって可変される。そして、第１弁体５３、第２弁体６５、ならびにソレノイド９１の推力により第１弁体５３および第２弁体６５のセット荷重を可変させるアクチュエータによって、サブバルブ６８が構成される。 The first valve body 53 is a non-magnetic material, and is formed in a stepped cylindrical shape having a large diameter portion 58 and a small diameter portion 59. The small diameter portion 59 of the first valve body 53 is slidably fitted to the lower portion of the inner peripheral surface 114 of the magnetic portion 96 of the core 93, which will be described later. The small diameter portion 59 of the first valve body 53 and the inner peripheral surface 114 of the magnetic portion 96 of the core 93 are sealed by a sealing member 60 (see FIG. 3). A bore 63 having an open upper end is formed in the first valve body 53. The bore 63 accommodates a needle-type second valve body 65. The second valve body 65 is seated on a valve seat 64 formed at the opening peripheral edge of the second valve chamber 69 that opens on the bottom surface of the bore 63. The set load of the first valve body 53 and the second valve body 65 is changed by adjusting the control current with respect to the solenoid 91. Then, the sub-valve 68 is configured by the actuator that changes the set load of the first valve body 53 and the second valve body 65 by the thrust of the first valve body 53, the second valve body 65, and the solenoid 91.

第１弁体５３には、ボア６３の底面中央に開口する第２弁室６９、大径部５８を径方向（図２における左右方向）へ延びて第２弁室６９を室５２に連通させる通路７０、および第２弁体６５の開弁時に第２弁室６９をシリンダ下室２Ｂに連通させる通路７１が形成される。第２弁体６５は、上端側の外側周縁部にフランジ部７２が形成される。フランジ部７２の外周面は、ボア６３の内周面に摺動可能に嵌合される。フランジ部７２とボア６３の底面との間には、第２弁体６５を第１弁体５３に対して上方向へ付勢させる圧縮コイルばね７３が介装される。第２弁体６５には、第２弁体６５の上端中央に開口する凹部７４が形成される。凹部７４の底部中央には、作動ピン７５の半球形の下端を受ける内円錐面７６が形成される。 In the first valve body 53, a second valve chamber 69, which opens in the center of the bottom surface of the bore 63, and a large diameter portion 58 extend in the radial direction (left-right direction in FIG. 2) to communicate the second valve chamber 69 with the chamber 52. A passage 71 is formed in which the second valve chamber 69 is communicated with the cylinder lower chamber 2B when the passage 70 and the second valve body 65 are opened. The second valve body 65 has a flange portion 72 formed on the outer peripheral edge portion on the upper end side. The outer peripheral surface of the flange portion 72 is slidably fitted to the inner peripheral surface of the bore 63. A compression coil spring 73 that urges the second valve body 65 upward with respect to the first valve body 53 is interposed between the flange portion 72 and the bottom surface of the bore 63. The second valve body 65 is formed with a recess 74 that opens in the center of the upper end of the second valve body 65. At the center of the bottom of the recess 74, an inner conical surface 76 that receives the hemispherical lower end of the working pin 75 is formed.

作動ピン７５は、下端が第２弁体６５の内円錐面７６で受けられる軸部７７と、下半分が半球形に形成される基部７９と、基部７９の上端中央に形成される凸部７８と、を有する。作動ピン７５は、基部７９の半球面が後述するソレノイド９１の可動子８０に形成された内円錐面８１によって受けられる。内円錐面８１は、可動子８０の上端に開口する大径孔部８２の下端と可動子８０の下端に開口する小径孔部８３の上端とに接続される。可動子８０の小径孔部８３には、作動ピン７５の軸部７７が挿通される。作動ピン７５は、基部７９の外側周縁部とばね受部材８４との間に介装された圧縮コイルばね８５の付勢力によって、基部７９の下側の半球面が可動子８０の内円錐面８１に着座される。 The actuating pin 75 has a shaft portion 77 whose lower end is received by the inner conical surface 76 of the second valve body 65, a base portion 79 whose lower half is formed in a hemispherical shape, and a convex portion 78 formed in the center of the upper end of the base portion 79. And have. The actuating pin 75 is received by the hemispherical surface of the base 79 by the inner conical surface 81 formed on the mover 80 of the solenoid 91, which will be described later. The inner conical surface 81 is connected to the lower end of the large-diameter hole 82 that opens at the upper end of the mover 80 and the upper end of the small-diameter hole 83 that opens at the lower end of the mover 80. The shaft portion 77 of the actuating pin 75 is inserted into the small diameter hole portion 83 of the mover 80. In the actuating pin 75, the lower hemisphere of the base 79 is formed by the urging force of the compression coil spring 85 interposed between the outer peripheral edge of the base 79 and the spring receiving member 84, and the inner conical surface 81 of the mover 80 is formed. Is seated in.

第１弁体５３には、圧縮コイルばね８５のばね力が作動ピン７５および第２弁体６５を介して伝達され、これにより、第１弁体５３は、ソレノイド９１のコア９３に対して下方向へ付勢される。ばね受部材８４は、段付軸形状をなし、大径軸部１４１、小径軸部１４２、および大径軸部１４１と小径軸部１４２との間に形成されて圧縮コイルばね８５の上端を受けるフランジ部１４３を有する。ばね受部材８４は、大径部８４Ａが圧縮コイルばね８５の上端部内側に挿入され、小径軸部１４２がコア９３の磁性部９５の凹部１０８に装着されたリング３０に嵌合される。 The spring force of the compression coil spring 85 is transmitted to the first valve body 53 via the actuating pin 75 and the second valve body 65, whereby the first valve body 53 is lowered with respect to the core 93 of the solenoid 91. Be urged in the direction. The spring receiving member 84 has a stepped shaft shape and is formed between the large-diameter shaft portion 141, the small-diameter shaft portion 142, and the large-diameter shaft portion 141 and the small-diameter shaft portion 142 to receive the upper end of the compression coil spring 85. It has a flange portion 143. In the spring receiving member 84, the large diameter portion 84A is inserted inside the upper end portion of the compression coil spring 85, and the small diameter shaft portion 142 is fitted into the ring 30 mounted in the recess 108 of the magnetic portion 95 of the core 93.

第２弁体６５は、作動ピン７５の軸部７７に外装された圧縮コイルばね８６のばね力により可動子８０に対して下方向へ付勢される。圧縮コイルばね８６は、第２弁体６５の凹部７４の底面と可動子８０との間に介装される。なお、コア９３（磁性部９６）の内側であって第２弁体６５と可動子８０との間の空間８８は、第２弁体６５のフランジ部７２に形成された通路８９を介して第１弁体５３のボア６３に連通される。 The second valve body 65 is urged downward with respect to the mover 80 by the spring force of the compression coil spring 86 mounted on the shaft portion 77 of the actuating pin 75. The compression coil spring 86 is interposed between the bottom surface of the recess 74 of the second valve body 65 and the mover 80. The space 88 inside the core 93 (magnetic portion 96) between the second valve body 65 and the mover 80 is formed through a passage 89 formed in the flange portion 72 of the second valve body 65. It is communicated with the bore 63 of one valve body 53.

ピストンケース２１のケース本体２２の内周面２２Ａの上端部には、コイルキャップ１０５が嵌合される。コイルキャップ１０５の上端には、ピストンケース２１のケース本体２２の軸部１３１の軸孔１３１Ａ内に保持された端子１３３が設けられる。端子１３３は、コイル９２とコネクタ１３５に接続される。端子１３３には、ピストンロッド６の軸孔６Ａに挿通されたハーネス部材１３４の一端（下端）に装着されたコネクタ１３５が接続される。端子１３３とコネクタ１３５は、アダプタ１３２により回転方向に位置決めされている。 A coil cap 105 is fitted to the upper end of the inner peripheral surface 22A of the case body 22 of the piston case 21. At the upper end of the coil cap 105, a terminal 133 held in the shaft hole 131A of the shaft portion 131 of the case body 22 of the piston case 21 is provided. The terminal 133 is connected to the coil 92 and the connector 135. A connector 135 attached to one end (lower end) of the harness member 134 inserted into the shaft hole 6A of the piston rod 6 is connected to the terminal 133. The terminal 133 and the connector 135 are positioned in the rotational direction by the adapter 132.

なお、ピストンロッド６の下端とピストンケース２１のケース本体２２の軸部１３１とは、ねじ部１３６によって連結される。また、可動子８０の内側の大径孔部８２は、ばね受部材８４の軸孔１４４、リング部材３０の軸孔の内側の空間１４５、磁性部９５を軸方向に貫通する通路１４６、コイルキャップ１０５に形成された通路１４７，１４８、コイルキャップ１０５とケース本体２２の蓋部１５０との間に形成される環状通路１４９、およびケース本体２２の蓋部１５０に形成された通路１５１、を介してシリンダ上室２Ａに連通される。これにより、組立時に残留したピストンケース２１内のエアを排出させるエア抜き通路が形成される。 The lower end of the piston rod 6 and the shaft portion 131 of the case body 22 of the piston case 21 are connected by a screw portion 136. Further, the large-diameter hole portion 82 inside the mover 80 includes a shaft hole 144 of the spring receiving member 84, a space 145 inside the shaft hole of the ring member 30, a passage 146 penetrating the magnetic portion 95 in the axial direction, and a coil cap. Through the passages 147 and 148 formed in the 105, the annular passage 149 formed between the coil cap 105 and the lid 150 of the case body 22, and the passage 151 formed in the lid 150 of the case body 22. It communicates with the cylinder upper chamber 2A. As a result, an air bleeding passage for discharging the air remaining in the piston case 21 during assembly is formed.

次に、主に図３を参照して、第１実施形態におけるソレノイド９１を説明する。
ソレノイド９１は、通電により磁力を発生するコイル９２と、コイル９２の内周側に設けられるコア９３と、コア９３の内周側を軸方向（上下方向）へ移動可能な可動子８０と、を備える。コア９３には、軸方向（図３における「上下方向」）に沿って上から順に、磁性部９５、非磁性部９７、磁性部９６が配置される。換言すると、コア９３は、上下に配置された磁性部９５，９６を非磁性部９７を介して結合させることで構成される。コア９３の非磁性部９７は、略円筒形に形成され、内周面９８の上側（上端部）に段部９８Ａを介して大内径部１００が形成され、外周面９９の下側（下端部）に段部９９Ａを介して小外径部１０１が形成される。Next, the solenoid 91 according to the first embodiment will be described mainly with reference to FIG.
The solenoid 91 includes a coil 92 that generates a magnetic force when energized, a core 93 provided on the inner peripheral side of the coil 92, and a mover 80 that can move the inner peripheral side of the core 93 in the axial direction (vertical direction). Be prepared. A magnetic portion 95, a non-magnetic portion 97, and a magnetic portion 96 are arranged on the core 93 in order from the top along the axial direction (“vertical direction” in FIG. 3). In other words, the core 93 is configured by connecting the magnetic portions 95 and 96 arranged above and below via the non-magnetic portion 97. The non-magnetic portion 97 of the core 93 is formed in a substantially cylindrical shape, and a large inner diameter portion 100 is formed on the upper side (upper end portion) of the inner peripheral surface 98 via the step portion 98A, and the lower side (lower end portion) of the outer peripheral surface 99. ), A small outer diameter portion 101 is formed via the step portion 99A.

コア９３の磁性部９５は、略円柱形に形成される。磁性部９５の外周面１０３には、コイル９２の内周面９２Ａの上部が嵌合される。磁性部９５の上端には、小径軸部１０４が形成され、小径軸部１０４は、コイルキャップ１０５の下端面に開口する凹部１０６に嵌合される。磁性部９５には、下端面に開口する内円錐面１０７が形成される。内円錐面１０７の先端部（上端部）には、リング部材３０が嵌着される凹部１０８が形成される。磁性部９５の外周面１０３の下端部には、段部１０３Ａを介して小外径部１０９が形成される。なお、磁性部９５の内円錐面１０７の開口周縁部は、磁性部９５の環状の下端面１１０となる。また、磁性部９５の小径軸部１０４とコイルキャップ１０５の凹部１０６との間は、シール部材１１１によってシールされる。 The magnetic portion 95 of the core 93 is formed in a substantially cylindrical shape. The upper portion of the inner peripheral surface 92A of the coil 92 is fitted to the outer peripheral surface 103 of the magnetic portion 95. A small-diameter shaft portion 104 is formed at the upper end of the magnetic portion 95, and the small-diameter shaft portion 104 is fitted into a recess 106 that opens at the lower end surface of the coil cap 105. The magnetic portion 95 is formed with an inner conical surface 107 that opens to the lower end surface. A recess 108 into which the ring member 30 is fitted is formed at the tip end portion (upper end portion) of the inner conical surface 107. A small outer diameter portion 109 is formed at the lower end portion of the outer peripheral surface 103 of the magnetic portion 95 via the step portion 103A. The opening peripheral edge of the inner conical surface 107 of the magnetic portion 95 is the annular lower end surface 110 of the magnetic portion 95. Further, the small diameter shaft portion 104 of the magnetic portion 95 and the recess 106 of the coil cap 105 are sealed by the sealing member 111.

コア９３の磁性部９６は、略円筒形に形成される。磁性部９６の外周面１１３には、コイル９２の内周面９２Ａの下部が嵌合される。磁性部９６の内周面１１４の上端部には、段部１１４Ａを介して大内径部１１５が形成される。磁性部９６の下部には、ピストンケース２１のケース本体２２の内周面２２Ａに嵌合させるフランジ部１１７が形成される。磁性部９６のフランジ部１１７は、ピストンケース２１のケース底部２３に形成された環状壁部１１６の上端に突き当てられる。これにより、コア９３は、ピストンケース２１に対して軸方向に位置決めされる。なお、磁性部９６の下端には、環状壁部１１６の内周面１１６Ａに嵌合させるボス部１１８が形成される。 The magnetic portion 96 of the core 93 is formed in a substantially cylindrical shape. The lower portion of the inner peripheral surface 92A of the coil 92 is fitted to the outer peripheral surface 113 of the magnetic portion 96. A large inner diameter portion 115 is formed at the upper end portion of the inner peripheral surface 114 of the magnetic portion 96 via the step portion 114A. A flange portion 117 is formed below the magnetic portion 96 to be fitted to the inner peripheral surface 22A of the case body 22 of the piston case 21. The flange portion 117 of the magnetic portion 96 is abutted against the upper end of the annular wall portion 116 formed on the case bottom portion 23 of the piston case 21. As a result, the core 93 is positioned in the axial direction with respect to the piston case 21. At the lower end of the magnetic portion 96, a boss portion 118 that fits into the inner peripheral surface 116A of the annular wall portion 116 is formed.

コア９３は、磁性部９５の下端の小外径部１０９を非磁性部９７の上端の大内径部１００に圧入させ、磁性部９５の外周面１０３の段部１０３Ａと非磁性部９７の上端との間を周方向に沿ってろう付けすることにより、磁性部９５と非磁性部９７とが接合される。他方、コア９３は、非磁性部９７の下端の小外径部１０１を磁性部９６の上端の大内径部１１５に圧入させ、非磁性部９７の外周面９９の段部９９Ａと磁性部９６の上端との間を周方向に沿ってろう付けすることにより、磁性部９６と非磁性部９７とが接合される。磁性部９５，９６および非磁性部９７が一体化された状態において、磁性部９６の内周面１１４の内径と非磁性部９７の内周面９８の内径とは、同一である。すなわち、磁性部９６の内周面１１４と非磁性部９７の内周面９８とは、面一、換言すると、同一の内円筒面上に配置される。 In the core 93, the small outer diameter portion 109 at the lower end of the magnetic portion 95 is press-fitted into the large inner diameter portion 100 at the upper end of the non-magnetic portion 97, and the step portion 103A of the outer peripheral surface 103 of the magnetic portion 95 and the upper end of the non-magnetic portion 97. The magnetic portion 95 and the non-magnetic portion 97 are joined by brazing between the spaces along the circumferential direction. On the other hand, in the core 93, the small outer diameter portion 101 at the lower end of the non-magnetic portion 97 is press-fitted into the large inner diameter portion 115 at the upper end of the magnetic portion 96, and the step portion 99A and the magnetic portion 96 of the outer peripheral surface 99 of the non-magnetic portion 97. The magnetic portion 96 and the non-magnetic portion 97 are joined by brazing between the upper end and the magnetic portion along the circumferential direction. In a state where the magnetic portions 95 and 96 and the non-magnetic portion 97 are integrated, the inner diameter of the inner peripheral surface 114 of the magnetic portion 96 and the inner diameter of the inner peripheral surface 98 of the non-magnetic portion 97 are the same. That is, the inner peripheral surface 114 of the magnetic portion 96 and the inner peripheral surface 98 of the non-magnetic portion 97 are arranged flush with each other, in other words, on the same inner cylindrical surface.

なお、磁性部９５の下端面１１０を非磁性部９７の内周面９８の段部９８Ａに突き当てることにより、磁性部９５と非磁性部９７とが軸方向に相対位置決めされる。また、非磁性部９７の下端を磁性部９６の内周面１１４の段部１１４Ａに突き当てることにより、磁性部９６と非磁性部９７とが軸方向に相対位置決めされる。さらに、磁性部９６のフランジ部１１７とピストンケース２１のケース本体２２との間は、フランジ部１１７の外周面に形成された環状溝に装着されたシール部材１１９によってシールされる。また、磁性部９６の外周面１１３の基端部には、フランジ部１１７に近づくにつれて拡径される外円錐面１２０が形成される。これにより、コイル９２の下端と磁性部９６のフランジ部１１７との間には、軸方向の隙間が形成される。 By abutting the lower end surface 110 of the magnetic portion 95 against the stepped portion 98A of the inner peripheral surface 98 of the non-magnetic portion 97, the magnetic portion 95 and the non-magnetic portion 97 are relatively positioned in the axial direction. Further, by abutting the lower end of the non-magnetic portion 97 against the step portion 114A of the inner peripheral surface 114 of the magnetic portion 96, the magnetic portion 96 and the non-magnetic portion 97 are relatively positioned in the axial direction. Further, the flange portion 117 of the magnetic portion 96 and the case body 22 of the piston case 21 are sealed by a sealing member 119 mounted in an annular groove formed on the outer peripheral surface of the flange portion 117. Further, an outer conical surface 120 whose diameter increases as it approaches the flange portion 117 is formed at the base end portion of the outer peripheral surface 113 of the magnetic portion 96. As a result, an axial gap is formed between the lower end of the coil 92 and the flange portion 117 of the magnetic portion 96.

可動子８０は、略円筒形に形成される。可動子８０の上端部には、上端に近づくにつれて縮径される外円錐面１２４を有するテーパ部１２３が形成される。可動子８０の外円錐面１２４は、磁性部９５の内円錐面１０７に対して一定の軸方向隙間をあけて対向する。可動子８０は、コア９３に対する摺動面となる外周面１２６を有する大径部１２５と、段部１２７を介して大径部１２５の下端に連続する小径部１２８と、を有する。なお、小径部１２８の外周面１２９の下部には環状溝１３０が形成されており、環状溝１３０内には、可動子８０の倒れを規制し、外周面１２９とコア９３の磁性部９６の接触を防止する摺動リング１５８が配置されている。 The mover 80 is formed in a substantially cylindrical shape. At the upper end of the mover 80, a tapered portion 123 having an outer conical surface 124 whose diameter is reduced as it approaches the upper end is formed. The outer conical surface 124 of the mover 80 faces the inner conical surface 107 of the magnetic portion 95 with a certain axial gap. The mover 80 has a large-diameter portion 125 having an outer peripheral surface 126 serving as a sliding surface with respect to the core 93, and a small-diameter portion 128 continuous from the lower end of the large-diameter portion 125 via a step portion 127. An annular groove 130 is formed in the lower portion of the outer peripheral surface 129 of the small diameter portion 128, and the tilting of the mover 80 is restricted in the annular groove 130 so that the outer peripheral surface 129 and the magnetic portion 96 of the core 93 come into contact with each other. A sliding ring 158 is arranged to prevent the above.

可動子８０の大径部１２５の外周面１２６は、コア９３の非磁性部９７の内周面９８に摺動可能に嵌合される。すなわち、可動子８０の大径部１２５の外周面１２６とコア９３の非磁性部９７の内周面９８との間には、一定の摺動クリアランスが形成される。他方、可動子８０の小径部１２８は、磁性部９６の内周面１１４（軸孔）に一定の嵌め合い（隙間嵌め）で嵌合される。換言すると、可動子８０の小径部１２８の外周面１２９と、コア９３の磁性部９６の内周面１１４との間には、一定のクリアランスが形成される。これにより、可動子８０の小径部１２８の外周面１２９と、コア９３の磁性部９６の内周面１１４との、非接触状態が保たれる。 The outer peripheral surface 126 of the large diameter portion 125 of the mover 80 is slidably fitted to the inner peripheral surface 98 of the non-magnetic portion 97 of the core 93. That is, a constant sliding clearance is formed between the outer peripheral surface 126 of the large diameter portion 125 of the mover 80 and the inner peripheral surface 98 of the non-magnetic portion 97 of the core 93. On the other hand, the small diameter portion 128 of the mover 80 is fitted to the inner peripheral surface 114 (shaft hole) of the magnetic portion 96 with a constant fit (gap fit). In other words, a certain clearance is formed between the outer peripheral surface 129 of the small diameter portion 128 of the mover 80 and the inner peripheral surface 114 of the magnetic portion 96 of the core 93. As a result, the non-contact state between the outer peripheral surface 129 of the small diameter portion 128 of the mover 80 and the inner peripheral surface 114 of the magnetic portion 96 of the core 93 is maintained.

すなわち、ソレノイド９１は、可動子８０のコア９３に対する軸方向移動範囲において、可動子８０とコア９３との径方向間距離が大きい部分と小さい部分とを有し、可動子８０のコア９３との径方向間距離が小さい部分（大径部１２５）は、コア９３の非磁性部９７と対向する。図４を参照すると、ソレノイド９１におけるコア９３と可動子８０との間の磁束の受け渡しは、磁性部９６から可動子８０の小径部１２８へ、および可動子８０のテーパ部１２３から磁性部９５の内円錐面１０７へ行われる。なお、コイル９２に対する通電方向が逆の場合、コア９３と可動子８０との間の磁束の受け渡し方向も逆になる。 That is, the solenoid 91 has a portion having a large radial distance between the mover 80 and the core 93 and a portion having a small radial distance between the mover 80 and the core 93 in the axial movement range of the mover 80 with respect to the core 93. The portion having a small radial distance (large diameter portion 125) faces the non-magnetic portion 97 of the core 93. Referring to FIG. 4, the transfer of magnetic flux between the core 93 and the mover 80 in the solenoid 91 is from the magnetic portion 96 to the small diameter portion 128 of the mover 80, and from the taper portion 123 of the mover 80 to the magnetic portion 95. This is done to the inner conical surface 107. When the energization direction with respect to the coil 92 is opposite, the magnetic flux transfer direction between the core 93 and the mover 80 is also opposite.

次に、第１実施形態の作動を説明する。
ここで、緩衝器１は、車両のサスペンション装置のばね上、ばね下間に取り付けられる。車両に振動が発生すると、緩衝器１は、ピストンロッド６のストロークに対して、油液（作動流体）の流れを制御することで減衰力を発生させる。このとき、減衰力発生機構３１は、ピストンロッド６の伸び行程時（以下「伸び行程時」と称する）には、メインバルブ３２の背圧（背圧室３４の圧力）を可変させて減衰弁３３の開弁圧を変化させることで減衰力を調節する。他方、ピストンロッド６の縮み行程時（以下「縮み行程時」と称する）には、ソレノイド９１の推力を制御して第１弁体５３のセット荷重（開弁圧）を変化させることで減衰力を調節する。Next, the operation of the first embodiment will be described.
Here, the shock absorber 1 is attached between the spring and the unsprung of the suspension device of the vehicle. When vibration is generated in the vehicle, the shock absorber 1 generates a damping force by controlling the flow of the oil liquid (working fluid) with respect to the stroke of the piston rod 6. At this time, the damping force generating mechanism 31 changes the back pressure of the main valve 32 (pressure of the back pressure chamber 34) during the extension stroke of the piston rod 6 (hereinafter referred to as “extension stroke”) to reduce the damping valve. The damping force is adjusted by changing the valve opening pressure of 33. On the other hand, during the contraction stroke of the piston rod 6 (hereinafter referred to as "contraction stroke"), the damping force is changed by changing the set load (valve opening pressure) of the first valve body 53 by controlling the thrust of the solenoid 91. To adjust.

そして、伸び行程時には、シリンダ２内のピストンバルブ５（ピストン）の移動によってシリンダ上室２Ａ側の油液（作動流体）が加圧されると、第２弁体６５の閉弁時、すなわち、第２弁体６５が第１弁体５３の弁座６４に着座されているとき、背圧室３４の上流側は、通路４６、通路２８、弁部材２５の内周通路２５Ｂ、およびディスクバルブ４７に形成された背圧室導入通路３５を介してシリンダ上室２Ａに連通される。これにより、加圧されたシリンダ上室２Ａ側の油液は、背圧室導入通路３５、通路２８、および通路４６を介して背圧室３４に導入される。 When the oil liquid (working fluid) on the cylinder upper chamber 2A side is pressurized by the movement of the piston valve 5 (piston) in the cylinder 2 during the extension stroke, the second valve body 65 is closed, that is, When the second valve body 65 is seated on the valve seat 64 of the first valve body 53, the upstream side of the back pressure chamber 34 is the passage 46, the passage 28, the inner peripheral passage 25B of the valve member 25, and the disc valve 47. The cylinder upper chamber 2A is communicated with the back pressure chamber introduction passage 35 formed in the cylinder. As a result, the pressurized oil liquid on the cylinder upper chamber 2A side is introduced into the back pressure chamber 34 via the back pressure chamber introduction passage 35, the passage 28, and the passage 46.

他方、背圧室３４の下流側は、通路４６、通路２８、環状通路５０、通路５１、室５２、および通路７０を介して第２弁室６９に連通される。これにより、ソレノイド９１の推力（制御電流）を制御して背圧室３４の圧力、すなわち、メインバルブ３２の背圧を可変させることにより、減衰弁３３のセット荷重（開弁圧）が調節される。ここで、第２弁室６９の圧力が第２弁体６５のセット荷重に達することで第２弁体６５が開弁されると、背圧室導入路３５から作動流体が流入し、背圧室導入路３５で差圧が発生することで、背圧室３４とシリンダ上室２Ａとの間に差圧が生じる。この差圧がメインバルブ３２のセット荷重以上になると、メインバルブ３２が開弁する。 On the other hand, the downstream side of the back pressure chamber 34 communicates with the second valve chamber 69 via the passage 46, the passage 28, the annular passage 50, the passage 51, the chamber 52, and the passage 70. As a result, the set load (valve opening pressure) of the damping valve 33 is adjusted by controlling the thrust (control current) of the solenoid 91 to change the pressure of the back pressure chamber 34, that is, the back pressure of the main valve 32. To. Here, when the pressure of the second valve chamber 69 reaches the set load of the second valve body 65 and the second valve body 65 is opened, the working fluid flows in from the back pressure chamber introduction path 35, and the back pressure When a differential pressure is generated in the chamber introduction path 35, a differential pressure is generated between the back pressure chamber 34 and the cylinder upper chamber 2A. When this differential pressure exceeds the set load of the main valve 32, the main valve 32 opens.

なお、第２弁体６５の開弁前には、通路２８、伸び側通路１９を介して減衰弁３３に形成されたオリフィス２９を通過する油液によるオリフィス特性の減衰力が得られる。一方、メインバルブ３２の開弁後には、前述した第１通路を流通する油液による、減衰弁３３のバルブ特性の減衰力が得られる。ピストンロッド６がシリンダ２内から退出した分の油液は、リザーバ４から、ベースバルブ７の逆止弁１０を開弁させることでシリンダ下室２Ｂへ流通する。また、伸び行程時における第１弁体５３は、第１弁室５６が通路５７を介してシリンダ下室２Ｂに連通されることから、開弁されない。 Before opening the second valve body 65, the damping force of the orifice characteristic due to the oil liquid passing through the orifice 29 formed in the damping valve 33 via the passage 28 and the extension side passage 19 is obtained. On the other hand, after the main valve 32 is opened, the damping force of the valve characteristics of the damping valve 33 is obtained by the oil liquid flowing through the first passage described above. The amount of oil liquid that the piston rod 6 has exited from the cylinder 2 flows from the reservoir 4 to the cylinder lower chamber 2B by opening the check valve 10 of the base valve 7. Further, the first valve body 53 during the extension stroke is not opened because the first valve chamber 56 communicates with the cylinder lower chamber 2B via the passage 57.

そして、縮み行程時には、シリンダ２内のピストンバルブ５（ピストン）の移動によってシリンダ下室２Ｂ側の油液（作動流体）が加圧されることにより、シリンダ下室２Ｂ側の油液は、縮み側通路２０を通過してディスクバルブ４３を開弁させることで第２通路を連通させ、シリンダ上室２Ａへ流通する。このとき、ディスクバルブ４３によるバルブ特性の減衰力が得られる。なお、ピストンロッド６がシリンダ２内に進入した分の油液は、シリンダ下室２Ｂ内の圧力がベースバルブ７のディスクバルブ１１の開弁圧力に達すると、ディスクバルブ１１が開弁してリザーバ４へ流通する。 Then, during the contraction stroke, the oil liquid (working fluid) on the cylinder lower chamber 2B side is pressurized by the movement of the piston valve 5 (piston) in the cylinder 2, so that the oil liquid on the cylinder lower chamber 2B side shrinks. By passing through the side passage 20 and opening the disc valve 43, the second passage is communicated and distributed to the cylinder upper chamber 2A. At this time, the damping force of the valve characteristic by the disc valve 43 is obtained. When the pressure in the lower chamber 2B of the cylinder reaches the opening pressure of the disc valve 11 of the base valve 7, the disc valve 11 opens and the reservoir of the oil liquid corresponding to the amount of the piston rod 6 entering the cylinder 2. Distribute to 4.

また、縮み行程時には、ソレノイド９１の推力（制御電流）を制御して第１弁体５３のセット荷重（開弁圧）を可変させることで、ソレノイド９１の推力に抗して第１弁体５３が開弁されると、シリンダ下室２Ｂ側の油液は、通路５７、室５２、通路５１、および環状通路５０を通過し、さらに背圧室導入通路３５が形成されたディスクバルブ４７を開弁させてシリンダ上室２Ａへ流通する。このとき、ディスクバルブ４７によるバルブ特性の減衰力が得られる。なお、縮み行程時には、第１弁体５３と第２弁体６５とが一体で移動する。 Further, during the contraction stroke, the thrust (control current) of the solenoid 91 is controlled to change the set load (valve opening pressure) of the first valve body 53, whereby the first valve body 53 opposes the thrust of the solenoid 91. When the valve is opened, the oil liquid on the lower chamber 2B side of the cylinder passes through the passage 57, the chamber 52, the passage 51, and the annular passage 50, and further opens the disc valve 47 in which the back pressure chamber introduction passage 35 is formed. It is valved and distributed to the cylinder upper chamber 2A. At this time, the damping force of the valve characteristic by the disc valve 47 is obtained. During the contraction stroke, the first valve body 53 and the second valve body 65 move integrally.

ここで、特許文献１に記載された従来の緩衝器のように、可動子の外径が全長にわたって同一で、かつ、磁性部と可動子とのクリアランス（径方向隙間）と、非磁性部と可動子とのクリアランスとが同一である場合、可動子のコアに対する軸方向移動範囲において、可動子の外周面の全てがコアの内周面に摺動する。このとき、可動子がコアに対して偏心することで可動子に作用する横力（径方向吸引力）が周方向で不均一になると、可動子とコアとの摺動抵抗が増大し、ソレノイド推力特性のヒステリシスが大きくなる。その結果、コイルへの制御電流に対する増加方向と減少方向との減衰力特性に差異が生じ、減衰力制御性が悪化する。 Here, like the conventional shock absorber described in Patent Document 1, the outer diameter of the mover is the same over the entire length, and the clearance (radial gap) between the magnetic part and the mover and the non-magnetic part When the clearance with the mover is the same, the entire outer peripheral surface of the mover slides on the inner peripheral surface of the core within the axial movement range of the mover with respect to the core. At this time, if the lateral force (radial suction force) acting on the mover becomes non-uniform in the circumferential direction due to the eccentricity of the mover with respect to the core, the sliding resistance between the mover and the core increases, and the solenoid The hysteresis of the thrust characteristic becomes large. As a result, there is a difference in the damping force characteristics between the increasing direction and the decreasing direction with respect to the control current to the coil, and the damping force controllability deteriorates.

これに対し、第１実施形態では、可動子８０の大径部１２５をコア９３の非磁性部９７に対向させることで、可動子８０とコア９３とのクリアランス（径方向間距離）が小さい部分（図４の区間Ｂ）を形成するとともに、可動子８０の小径部１２８をコア９３の磁性部９６に対向させることで、可動子８０とコア９３とのクリアランスが大きい部分（図４の区間Ｃ）を形成し、可動子８０に作用させるソレノイド推力（軸方向吸引力）を確保しながら、図４の区間Ｃにおける横力が小さくなるように、可動子８０の小径部１２８とコア９３の磁性部９６とのクリアランスを適正化させた。なお、可動子８０の大径部１２５とコア９３の非磁性部９７とのクリアランスは、大径部１２５と非磁性部９７との摺動のための微小クリアランスであり、可動子８０の小径部１２８とコア９３の磁性部９６とのクリアランスは、小径部１２８と磁性部９６との非接触状態を保つためのクリアランスである。 On the other hand, in the first embodiment, the large diameter portion 125 of the mover 80 is opposed to the non-magnetic portion 97 of the core 93, so that the clearance (distance between the radial directions) between the mover 80 and the core 93 is small. (Section B in FIG. 4) is formed, and the small diameter portion 128 of the mover 80 is opposed to the magnetic portion 96 of the core 93, so that the clearance between the mover 80 and the core 93 is large (section C in FIG. 4). ), And the magnetism of the small diameter portion 128 of the mover 80 and the core 93 so that the lateral force in the section C of FIG. 4 is reduced while ensuring the solenoid thrust (axial attraction force) acting on the mover 80. The clearance with the part 96 was optimized. The clearance between the large diameter portion 125 of the mover 80 and the non-magnetic portion 97 of the core 93 is a minute clearance for sliding between the large diameter portion 125 and the non-magnetic portion 97, and the small diameter portion of the mover 80. The clearance between the 128 and the magnetic portion 96 of the core 93 is a clearance for maintaining a non-contact state between the small diameter portion 128 and the magnetic portion 96.

そして、図５に示されるのは、図４の区間Ｃにおけるクリアランス、すなわち、可動子８０の小径部１２８とコア９３の磁性部９６とのクリアランス（ここでは単に「クリアランス」と称する）を横軸に取り、コイル９２に流す電流値が固定された状態における可動子８０に作用する力（図４において「発生力」と称する）を縦軸に取った図表である。図５を参照すると、図４の区間Ａで発生する横力は、クリアランスが０を超えて０．３５ｍｍまでの区間で略一定である。また、ソレノイド推力（軸方向吸引力）は、クリアランスが０を超えて０．３５ｍｍまでの区間で漸減する傾向にある。他方、図４の区間Ｃで発生する横力は、クリアランスが０を超えて０．２ｍｍまでの区間で急減し、その後緩やかに減少する傾向にある。 Then, what is shown in FIG. 5 is the clearance in the section C of FIG. 4, that is, the clearance between the small diameter portion 128 of the mover 80 and the magnetic portion 96 of the core 93 (here, simply referred to as “clearance”) on the horizontal axis. It is a chart in which the force acting on the mover 80 (referred to as “generated force” in FIG. 4) in a state where the current value flowing through the coil 92 is fixed is taken on the vertical axis. Referring to FIG. 5, the lateral force generated in the section A of FIG. 4 is substantially constant in the section where the clearance exceeds 0 and reaches 0.35 mm. Further, the solenoid thrust (axial suction force) tends to gradually decrease in a section where the clearance exceeds 0 and reaches 0.35 mm. On the other hand, the lateral force generated in the section C of FIG. 4 tends to decrease sharply in the section where the clearance exceeds 0 and reaches 0.2 mm, and then gradually decreases.

ここで、図４の区間Ｃで発生する横力は、可動子８０の大径部１２５とコア９３の非磁性部９７とのクリアランス（摺動クリアランス）に起因する、コア９３の軸線に対する可動子８０の偏心によるものであり、当該偏心によって、ソレノイド９１の磁束密度が周方向に沿って偏倚し、その結果、可動子８０に径方向の吸引力が作用する。第１実施形態では、可動子８０の小径部１２８とコア９３の磁性部９６とのクリアランスを適正化（第１実施形態では０．１９ｍｍに設定）することにより、ソレノイド推力、すわなち、可動子８０に作用する軸方向吸引力を確保しながら、図４の区間Ｃにおける横力の発生を抑制させるようにした。第１実施形態では、可動子８０の小径部１２８とコア９３の磁性部９６とのクリアランスを適正化することにより、ソレノイド推力の低下と可動子８０に発生する横力の偏倚とを最小限に抑えることが可能であり、可動子８０が軸方向へ移動するときの、可動子８０とコア９３の非磁性部９７との間の摺動抵抗を、大幅に減少させることができる。 Here, the lateral force generated in the section C of FIG. 4 is caused by the clearance (sliding clearance) between the large diameter portion 125 of the mover 80 and the non-magnetic portion 97 of the core 93, and the mover with respect to the axis of the core 93. This is due to the eccentricity of 80, and the eccentricity causes the magnetic flux density of the solenoid 91 to deviate along the circumferential direction, and as a result, a radial attraction force acts on the mover 80. In the first embodiment, the solenoid thrust, that is, movable by optimizing the clearance between the small diameter portion 128 of the mover 80 and the magnetic portion 96 of the core 93 (set to 0.19 mm in the first embodiment). While ensuring the axial suction force acting on the child 80, the generation of the lateral force in the section C of FIG. 4 is suppressed. In the first embodiment, by optimizing the clearance between the small diameter portion 128 of the mover 80 and the magnetic portion 96 of the core 93, the decrease in the solenoid thrust and the deviation of the lateral force generated in the mover 80 are minimized. It can be suppressed, and the sliding resistance between the mover 80 and the non-magnetic portion 97 of the core 93 when the mover 80 moves in the axial direction can be significantly reduced.

図６は、可動子の外周面の全てがコアの内周面に摺動する従来の緩衝器における、ピストン速度（０．１ｍ／ｓ、０．３ｍ／ｓ、０．６ｍ／ｓ）のときの各減衰力特性を示す図表であり、図７は、第１実施形態の緩衝器における減衰力特性を示した図表である。図６、図７から理解できるように、第１実施形態では、減衰力発生機構３１が発生する減衰力のヒステリシス、すなわち、制御電流を増加方向へ変化させたときの減衰力と制御電流を減少方向へ変化させたときの減衰力との差異を小さくすることが可能である。その結果、コイル９２へ通電する電流値と減衰力発生機構３１が発生する減衰力とを対応させることが可能であり、減衰力の制御性を向上させることができる。 FIG. 6 shows the piston speeds (0.1 m / s, 0.3 m / s, 0.6 m / s) in a conventional shock absorber in which the entire outer peripheral surface of the mover slides on the inner peripheral surface of the core. It is a chart showing each damping force characteristic of the above, and FIG. 7 is a chart showing the damping force characteristic in the shock absorber of the first embodiment. As can be understood from FIGS. 6 and 7, in the first embodiment, the hysteresis of the damping force generated by the damping force generating mechanism 31, that is, the damping force and the control current when the control current is changed in the increasing direction is reduced. It is possible to reduce the difference from the damping force when changing in the direction. As a result, it is possible to make the current value of energizing the coil 92 correspond to the damping force generated by the damping force generating mechanism 31, and the controllability of the damping force can be improved.

以下に、第１実施形態の作用効果を示す。
第１実施形態の緩衝器（１）は、作動流体が封入されるシリンダ（２）と、シリンダ（２）内に摺動可能に嵌装されるピストン（２）と、一端がピストン（２１）に連結され、他端側がシリンダ（２）の外部に延出されるピストンロッド（６）と、ソレノイド（９１）に流れる制御電流を制御することで減衰力特性が調整可能な減衰力発生機構（３１）と、を備え、ソレノイド（９１）は、通電されることで磁力を発生するコイル（９２）と、コイル（９２）の内周側に設けられ、軸方向に配置された磁性部（９５，９６）と非磁性部（９７）とを有するコア（９３）と、コア（９３）の内周側を軸方向へ移動可能な可動子（８０）と、を備え、可動子（８０）のコア（９３）に対する軸方向移動範囲において、可動子（８０）とコア（９３）との径方向間距離が大きい部分と小さい部分とを有し、小さい部分は、コア（９３）の非磁性部（９７）と対向する。The effects of the first embodiment are shown below.
The shock absorber (1) of the first embodiment includes a cylinder (2) in which a working fluid is sealed, a piston (2) slidably fitted in the cylinder (2), and a piston (21) at one end. A piston rod (6) whose other end extends to the outside of the cylinder (2) and a damping force generation mechanism (31) whose damping force characteristics can be adjusted by controlling the control current flowing through the solenoid (91). ), And the solenoid (91) is provided on the inner peripheral side of the coil (92) and the coil (92), which generate a magnetic force when energized, and is arranged in the axial direction. A core (93) having a 96) and a non-magnetic portion (97), and a mover (80) capable of moving the inner peripheral side of the core (93) in the axial direction, and a core of the mover (80). In the axial movement range with respect to (93), it has a portion having a large radial distance between the mover (80) and the core (93) and a portion having a small radial distance, and the small portion is a non-magnetic portion of the core (93). It faces 97).

よって、第１実施形態では、可動子（８０）とコア（９３）との径方向間距離が大きい部分の、可動子（８０）とコア（９３）との径方向間距離（第１実施形態では「可動子８０の小径部１２８とコア９３の磁性部９６とのクリアランス」）を適正化することにより、ソレノイド推力の低下と可動子（８０）に発生する横力の偏倚とを最小限に抑えることが可能であり、可動子（８０）が軸方向へ移動するときに発生する、可動子（８０）とコア（９３）との摺動抵抗を大幅に低下させることができる。
これにより、減衰力発生機構（３１）が発生する減衰力のヒステリシス、すなわち、制御電流を増加方向へ変化させたときの減衰力と制御電流を減少方向へ変化させたときの減衰力との差異を小さくすることが可能であり、その結果、減衰力の制御性を向上させることができる。
また、第１実施形態では、可動子（８０）が軸方向へ移動するときに発生する可動子（８０）とコア（９３）との摺動抵抗を最小限に止めることができるので、ソレノイド（９１）の小型化、およびコイル（９２）に対する制御電流の低電流化を図ることが可能であり、延いては緩衝器（１）の小型化、および電力消費の削減を図ることができる。Therefore, in the first embodiment, the radial distance between the mover (80) and the core (93) in the portion where the radial distance between the mover (80) and the core (93) is large (the first embodiment). By optimizing the "clearance between the small diameter portion 128 of the mover 80 and the magnetic portion 96 of the core 93"), the decrease in solenoid thrust and the deviation of the lateral force generated in the mover (80) are minimized. It can be suppressed, and the sliding resistance between the mover (80) and the core (93) generated when the mover (80) moves in the axial direction can be significantly reduced.
As a result, the hysteresis of the damping force generated by the damping force generation mechanism (31), that is, the difference between the damping force when the control current is changed in the increasing direction and the damping force when the control current is changed in the decreasing direction. Can be reduced, and as a result, the controllability of the damping force can be improved.
Further, in the first embodiment, the sliding resistance between the mover (80) and the core (93) generated when the mover (80) moves in the axial direction can be minimized, so that the solenoid (80) can be stopped. It is possible to reduce the size of the 91) and the control current for the coil (92), and thus to reduce the size of the shock absorber (1) and reduce the power consumption.

また、可動子（８０）は、大径部（１２５）と小径部（１２８）とを有し、大径部（１２５）とコア（９３）の非磁性部（９７）とを対向させたので、可動子（８０）とコア（９３）との摺動抵抗を低下させることができる。 Further, since the mover (80) has a large diameter portion (125) and a small diameter portion (128), the large diameter portion (125) and the non-magnetic portion (97) of the core (93) face each other. , The sliding resistance between the mover (80) and the core (93) can be reduced.

また、ソレノイド（９１）を含む減衰力発生機構（３１）がシリンダ（２）に内蔵されるので、第１実施形態を、いわゆるピストン内蔵型の減衰力調整式油圧緩衝器に適用させることができる。
なお、第１実施形態では、ピストン内蔵型の減衰力調整式油圧緩衝器（１）に適用した態様を説明したが、第１実施形態は、ソレノイド（９１）を含む減衰力発生機構（３１）がシリンダ（２）の側壁に横付けされる、いわゆる制御バルブ横付け型の減衰力調整式油圧緩衝器に適用することができる。Further, since the damping force generating mechanism (31) including the solenoid (91) is built in the cylinder (2), the first embodiment can be applied to a so-called piston built-in damping force adjusting type hydraulic shock absorber. ..
In the first embodiment, the mode applied to the damping force adjusting type hydraulic shock absorber (1) having a built-in piston has been described, but in the first embodiment, the damping force generating mechanism (31) including the solenoid (91) has been described. Can be applied to a so-called control valve side-mounted type damping force adjustment type hydraulic shock absorber, which is installed next to the side wall of the cylinder (2).

（第２実施形態） 次に、第２実施形態を図８を参照して説明する。なお、第１実施形態と同一または相当の構成要素については、同一の名称および符号を付与し、詳細な説明を省略する。
第１実施形態では、可動子８０の軸方向移動範囲（図４におけるＢ区間およびＣ区間）におけるコア９３の内径が同一であり、可動子８０に大径部１２５と小径部１２８とを設けることにより、可動子８０とコア９３との径方向間距離が大きい部分（可動子８０の小径部１２８とコア９３の磁性部９６とのクリアランス）と小さい部分（可動子８０の大径部１２５とコア９３の非磁性部９７との摺動クリアランス）とを設けた。(Second Embodiment) Next, the second embodiment will be described with reference to FIG. The same or equivalent components as those in the first embodiment are given the same names and reference numerals, and detailed description thereof will be omitted.
In the first embodiment, the inner diameter of the core 93 in the axial movement range of the mover 80 (B section and C section in FIG. 4) is the same, and the mover 80 is provided with a large diameter portion 125 and a small diameter portion 128. As a result, the distance between the mover 80 and the core 93 in the radial direction is large (clearance between the small diameter portion 128 of the mover 80 and the magnetic portion 96 of the core 93) and the small portion (large diameter portion 125 of the mover 80 and the core). (Sliding clearance with the non-magnetic portion 97) of 93) was provided.

これに対し、第２実施形態では、可動子８０の円筒部１５５（図４におけるＢ区間およびＣ区間）の外径を同一に形成するとともに、コア９３に小内径部１５６（小径部）と大内径部１５７（大径部）とを設けることにより、可動子８０とコア９３との径方向間距離が大きい部分（可動子８０の円筒部１５５とコア９３の磁性部９６とのクリアランス）と小さい部分（可動子８０の円筒部１５５とコア９３の非磁性部９７との摺動クリアランス）とを設けた。 On the other hand, in the second embodiment, the outer diameter of the cylindrical portion 155 (section B and section C in FIG. 4) of the mover 80 is formed to be the same, and the core 93 has a small inner diameter portion 156 (small diameter portion) and a large diameter. By providing the inner diameter portion 157 (large diameter portion), the distance between the mover 80 and the core 93 in the radial direction is large (clearance between the cylindrical portion 155 of the mover 80 and the magnetic portion 96 of the core 93) and small. A portion (sliding clearance between the cylindrical portion 155 of the mover 80 and the non-magnetic portion 97 of the core 93) was provided.

第２実施形態では、コア９３の非磁性部９７の小内径部１５６の内周面１５６Ａと可動子８０の円筒部１５５の外周面１５５Ａとの間に、摺動クリアランスが形成される。なお、可動子８０の円筒部１５５の外周面１５５Ａに形成された環状溝１３０には、非磁性材料からなる摺動リング１５８が装着される。これにより、可動子８０の円筒部１５５の外周面１５５Ａとコア９３の磁性部９６の内周面１１４との非接触状態が保たれる。 In the second embodiment, a sliding clearance is formed between the inner peripheral surface 156A of the small inner diameter portion 156 of the non-magnetic portion 97 of the core 93 and the outer peripheral surface 155A of the cylindrical portion 155 of the mover 80. A sliding ring 158 made of a non-magnetic material is mounted on the annular groove 130 formed on the outer peripheral surface 155A of the cylindrical portion 155 of the mover 80. As a result, the non-contact state between the outer peripheral surface 155A of the cylindrical portion 155 of the mover 80 and the inner peripheral surface 114 of the magnetic portion 96 of the core 93 is maintained.

第２実施形態では、前述した第１実施形態と同等の作用効果を得ることができる。また、第２実施形態では、第１実施形態における可動子８０のように大径部１２５の外周面１２６と小径部１２８の外周面１２９とを別工程で仕上げる必要がないので、加工工数を削減することができる。なお、非磁性部９７の小内径部１５６の内周面１５６Ａとコア９３の磁性部９６の内周面１１４とは、コア９３を一体化させる前の個々の部品の状態で仕上げ加工されるので、第１実施形態に対して加工工数が増加することはない。 In the second embodiment, the same effect as that of the first embodiment described above can be obtained. Further, in the second embodiment, unlike the mover 80 in the first embodiment, it is not necessary to finish the outer peripheral surface 126 of the large diameter portion 125 and the outer peripheral surface 129 of the small diameter portion 128 in a separate process, so that the processing man-hours are reduced. can do. Since the inner peripheral surface 156A of the small inner diameter portion 156 of the non-magnetic portion 97 and the inner peripheral surface 114 of the magnetic portion 96 of the core 93 are finished in the state of individual parts before the core 93 is integrated. , The processing man-hours do not increase as compared with the first embodiment.

なお、上述の第１、第２実施形態では、可動子のコアに対する軸方向移動範囲において、可動子とコアとの径方向間隙間が大きい部分と小さい部分とを有し、小さい部分は、コアの非磁性部と対向する構成を示した。望ましくは可動子のコアに対する全軸方向移動範囲いおいて、径方向隙間が小さい部分は、コアの非磁性部と対向することであるが、軸方向移動範囲において、一部径方向隙間が小さい部分がコアの磁性部と対向するようにするものを排除していない。 In the first and second embodiments described above, in the axial movement range of the mover with respect to the core, the mover and the core have a large radial gap and a small radial gap, and the small part is the core. The configuration facing the non-magnetic part of the above is shown. Desirably, in the all-axial movement range of the mover with respect to the core, the portion having a small radial gap faces the non-magnetic part of the core, but in the axial movement range, a part of the radial gap is small. The one that makes the part face the magnetic part of the core is not excluded.

尚、本発明は上記した実施形態に限定されるものではなく、様々な変形例が含まれる。例えば、上記した実施形態は本発明を分かりやすく説明するために詳細に説明したものであり、必ずしも説明した全ての構成を備えるものに限定されるものではない。また、ある実施形態の構成の一部を他の実施形態の構成に置き換えることが可能であり、また、ある実施形態の構成に他の実施形態の構成を加えることも可能である。また、各実施形態の構成の一部について、他の構成の追加・削除・置換をすることが可能である。 The present invention is not limited to the above-described embodiment, and includes various modifications. For example, the above-described embodiment has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the described configurations. Further, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. Further, it is possible to add / delete / replace a part of the configuration of each embodiment with another configuration.

本願は、２０１７年１２月２６日付出願の日本国特許出願第２０１７−２４９４０７号に基づく優先権を主張する。２０１７年１２月２６日付出願の日本国特許出願第２０１７−２４９４０７号の明細書、特許請求の範囲、図面、及び要約書を含む全開示内容は、参照により本願に全体として組み込まれる。 The present application claims priority under Japanese Patent Application No. 2017-249407 filed December 26, 2017. The entire disclosure, including the specification, claims, drawings, and abstract of Japanese Patent Application No. 2017-249407 filed December 26, 2017, is incorporated herein by reference in its entirety.

１ 緩衝器、２ シリンダ、５ ピストンバルブ（ピストン）、６ ピストンロッド、２１ ピストンケース（ピストン）、３１ 減衰力発生機構、８０ 可動子、９１ ソレノイド、９２ コイル、９３ コア、９５，９６ 磁性部、９７ 非磁性部 1 shock absorber, 2 cylinder, 5 piston valve (piston), 6 piston rod, 21 piston case (piston), 31 damping force generating mechanism, 80 mover, 91 solenoid, 92 coil, 93 core, 95,96 magnetic part, 97 Non-magnetic part

Claims (8)

緩衝器であって、該緩衝器は、
作動流体が封入されるシリンダと、
前記シリンダ内に摺動可能に嵌装されるピストンと、
一端が前記ピストンに連結され、他端側が前記シリンダの外部に延出されるピストンロッドと、
ソレノイドに流れる制御電流を制御することで減衰力特性が調整可能な減衰力発生機構と、を備え、
前記ソレノイドは、
通電されることで磁力を発生するコイルと、
前記コイルの内周側に設けられ、内周が円筒状の磁性部と内周が円筒状の非磁性部とを有するコアであって、前記磁性部と前記非磁性部は前記コアの軸方向に沿って配置された前記コアと、
前記コアの内周側を該コアの軸方向へ移動可能な可動子と、を備え、
前記可動子の前記コアに対する前記軸方向の移動範囲において、前記可動子と前記コアとの径方向間距離が大きい部分と該径方向間距離が前記大きい部分よりも小さい部分とを有し、前記小さい部分は、前記コアの非磁性部と対向する位置に設けられると共に摺接することを特徴とする緩衝器。 It is a shock absorber, and the shock absorber is
A cylinder in which the working fluid is sealed and
A piston that is slidably fitted in the cylinder,
A piston rod whose one end is connected to the piston and whose other end extends to the outside of the cylinder.
It is equipped with a damping force generation mechanism whose damping force characteristics can be adjusted by controlling the control current flowing through the solenoid.
The solenoid is
A coil that generates a magnetic force when energized,
Provided on the inner peripheral side of the coil, the inner circumference the inner periphery and a cylindrical magnetic portion with a core and a cylindrical non-magnetic portion, the said magnetic part nonmagnetic portion axially of the core With the core arranged along
A mover capable of moving the inner peripheral side of the core in the axial direction of the core is provided.
In the axial movement range of the mover with respect to the core, the mover has a portion having a large radial distance between the mover and the core and a portion having a portion having a smaller radial distance than the large portion. A shock absorber characterized in that a small portion is provided at a position facing the non-magnetic portion of the core and is in sliding contact with the core. 請求項１に記載の緩衝器において、
前記可動子は大径部と小径部とを有し、前記大径部と前記コアの非磁性部とが対向することを特徴とする緩衝器。 In the shock absorber according to claim 1,
The mover has a large-diameter portion and a small-diameter portion, and the shock absorber is characterized in that the large-diameter portion and the non-magnetic portion of the core face each other. 請求項１に記載の緩衝器において、
前記コアは大径部と小径部とを有し、前記小径部は前記非磁性部であることを特徴とする緩衝器。 In the shock absorber according to claim 1,
A shock absorber characterized in that the core has a large-diameter portion and a small-diameter portion, and the small-diameter portion is the non-magnetic portion. 請求項１ないし３のいずれか１項に記載の緩衝器において、
前記ソレノイドを含む前記減衰力発生機構が前記シリンダに内蔵されることを特徴とする緩衝器。 In the shock absorber according to any one of claims 1 to 3,
A shock absorber characterized in that the damping force generating mechanism including the solenoid is built in the cylinder. 請求項１ないし３のいずれか１項に記載の緩衝器において、
前記ソレノイドを含む前記減衰力発生機構が前記シリンダの側壁に横付けされることを特徴とする緩衝器。 In the shock absorber according to any one of claims 1 to 3,
A shock absorber characterized in that the damping force generating mechanism including the solenoid is laterally attached to a side wall of the cylinder. 緩衝器の減衰力発生機構に用いられるソレノイドであって、該ソレノイドは、
通電により磁力を発生するコイルと、
前記コイルの内周側に配されたコアであって、該コアの軸方向に沿って内周が円筒状の非磁性部と内周が円筒状の磁性部とを有する前記コアと、
前記コアの内周側に配され、前記軸方向へ移動可能に設けられる可動子と、を備え、
前記可動子の前記コアに対する前記軸方向の移動範囲において、前記可動子と前記コアの径方向間距離が大きい部分と該径方向間距離が前記大きい部分よりも小さい部分とを有し、該小さい部分は前記コアの非磁性部と対向する位置に設けられると共に摺接することを特徴とするソレノイド。 It is a solenoid used for the damping force generation mechanism of the shock absorber , and the solenoid is
A coil that generates a magnetic force when energized,
A core arranged on the inner peripheral side of the coil, the core having a non-magnetic portion having a cylindrical inner circumference and a magnetic portion having a cylindrical inner circumference along the axial direction of the core.
It is provided with a mover arranged on the inner peripheral side of the core and provided so as to be movable in the axial direction.
In the axial movement range of the mover with respect to the core, the mover and the core have a portion having a large radial distance and a portion having a smaller radial distance than the large portion, and the distance is small. A solenoid characterized in that the portion is provided at a position facing the non-magnetic portion of the core and is in sliding contact with the portion. 請求項６に記載のソレノイドにおいて、
前記可動子は大径部と小径部とを有し、該大径部と前記コアの非磁性部とが対向することを特徴とするソレノイド。 In the solenoid according to claim 6,
The solenoid has a large diameter portion and a small diameter portion, and the large diameter portion and the non-magnetic portion of the core face each other. 請求項６に記載のソレノイドにおいて、
前記コアは大径部と小径部とを有し、該小径部は前記非磁性部であることを特徴とするソレノイド。 In the solenoid according to claim 6,
A solenoid characterized in that the core has a large-diameter portion and a small-diameter portion, and the small-diameter portion is the non-magnetic portion.
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