JP6468016B2

JP6468016B2 - Shock absorber

Info

Publication number: JP6468016B2
Application number: JP2015054499A
Authority: JP
Inventors: 健太三好
Original assignee: Aisin Seiki Co Ltd; Aisin Corp
Current assignee: Aisin Corp
Priority date: 2015-03-18
Filing date: 2015-03-18
Publication date: 2019-02-13
Anticipated expiration: 2035-03-18
Also published as: JP2016173172A

Description

本発明は、緩衝器に関し、特に、減衰力調整機構を備えた緩衝器に係る。 The present invention relates to a shock absorber, and particularly relates to a shock absorber provided with a damping force adjusting mechanism.

車両に搭載される緩衝器（ショックアブソーバ）には、減衰力調整機構を有するものがある。この機構は、減衰力がピストンの作動速度に対して一義的に決まる緩衝器によっては、背反関係にある乗心地と操縦安定性を充足させることができないため、ピストンが発生する減衰力を調整可能とするものであり、種々の形式のものが知られている。例えば下記の特許文献１には、「従来の減衰力調整弁を備えた緩衝器では、例えば減衰特性の調整により、流出量が小さく平らで平面的な減衰力特性を得ることは困難であった。これらの場合、凸凹なあるいは不安定な働きをすることが不可避である。緩衝器にスムーズな挙動をさせて任意の異なるタイプの調整を可能にする必要がある。」（特許文献１の段落〔０００６〕に記載）とし、この課題を解決するため「弁穴を有する弁座及び該弁穴を開閉する弁体を有し、該弁体の一方の面には上記弁穴を介して作動液体の開方向力が作用し、他方の面には閉方向力が作用し、該弁体のストロークに伴って、かつ該ストロークの大きさに応じた減衰力を発生させるように構成された緩衝器の減衰力調整弁において、上記弁体のストロークに伴って同時に作動して上記減衰力を発生させる内側減衰部と外側減衰部を有し、該内側減衰部及び外側減衰部は、上記ストロークに伴って大きさが同時に変化する減衰部面積を有し、該減衰部面積の変化速度に応じて各減衰部の発生する減衰力が異なる大きさに段階的に又は連続的に変化するように構成されており、上記作動液体は上記内側減衰部から外側減衰部への一方向に流れ、かつ該内側減衰部、外側減衰部でのみ実質的な減衰力が発生する」緩衝器の減衰力調整弁が提案されている（同段落〔００１２〕に記載）。 Some shock absorbers (shock absorbers) mounted on vehicles have a damping force adjusting mechanism. This mechanism can adjust the damping force generated by the piston because the damping force is determined uniquely with respect to the operating speed of the piston, and it is impossible to satisfy the contradictory riding comfort and steering stability. Various types are known. For example, in Patent Document 1 below, “With a conventional shock absorber equipped with a damping force adjusting valve, it is difficult to obtain a flat and flat damping force characteristic with a small outflow by adjusting the damping characteristic, for example. In these cases, it is inevitable to work uneven or unstable. It is necessary to allow the buffer to behave smoothly to allow any different types of adjustments ”(paragraph of Patent Document 1). In order to solve this problem, “it has a valve seat having a valve hole and a valve body that opens and closes the valve hole, and one surface of the valve body is operated via the valve hole. A buffer configured to apply a force in the opening direction of the liquid and a force in the closing direction to the other surface to generate a damping force according to the stroke of the valve body and in accordance with the size of the stroke. With the stroke of the valve An inner damping portion and an outer damping portion that act simultaneously to generate the damping force, and the inner damping portion and the outer damping portion have a damping portion area whose size changes simultaneously with the stroke; The damping force generated by each attenuating part changes stepwise or continuously in different magnitudes according to the changing speed of the attenuating part area, and the working liquid flows from the inner attenuating part to the outer attenuating part. A damping force adjusting valve for a shock absorber has been proposed (described in the paragraph [0012]), in which a damping force is generated only in the inner damping portion and the outer damping portion.

特許第３６５５４８９号公報Japanese Patent No. 3655489

上記特許文献に記載の減衰力調整弁においては、弁体のストロークに伴って同時に作動して減衰力を発生させる外側減衰部と内側減衰部からなる二つの減衰部を有し、これらの減衰部は上記ストロークに伴って減衰部面積が変化し、各減衰部が発生する減衰力の大きさが変化することで、上記ストロークの大きさに応じて減衰力を連続的に変化させることとしている。然し乍ら、二つの減衰部が直列に配置された構成となっているので、弁体が開弁方向に大きくストロークしたときには、二つの減衰部の減衰力が合成されることになり、十分な減衰力低減効果を望めない。また、二つの減衰部が弁体のストロークに伴って同時に作動し、内側減衰部のシール部が弁体と弁座の重なりによって構成されるため、弁体及び弁座の幾何学的な許容限度（平面度、同軸度）が小さく、減衰力特性にばらつきが生じやすい。 In the damping force adjusting valve described in the above-mentioned patent document, it has two damping parts consisting of an outer damping part and an inner damping part that act simultaneously with the stroke of the valve body to generate damping force, and these damping parts The damping part area changes with the stroke, and the magnitude of the damping force generated by each damping part changes, so that the damping force is continuously changed according to the magnitude of the stroke. However, since the two damping parts are arranged in series, when the valve body makes a large stroke in the valve opening direction, the damping forces of the two damping parts will be combined, and the sufficient damping force The reduction effect cannot be expected. In addition, since the two damping parts operate simultaneously with the stroke of the valve body and the seal part of the inner damping part is configured by the overlap of the valve body and the valve seat, the geometrical tolerance limits of the valve body and the valve seat (Flatness, coaxiality) is small, and the damping force characteristic tends to vary.

そこで、本発明は、減衰力低減効果が大きく、安定した所望の減衰力特性を確保し得る減衰力調整機構を備えた緩衝器を提供することを課題とする。 Therefore, an object of the present invention is to provide a shock absorber having a damping force adjusting mechanism that has a large damping force reduction effect and can secure a stable desired damping force characteristic.

上記の課題を達成するため、本発明は、作動流体を収容する筒体と、該筒体内を摺動するピストンと、該ピストンに接続するピストンロッドと、前記筒体内で前記ピストンを介して流動する作動流体を制御し減衰力を調整する減衰力調整機構とを備えた緩衝器において、前記減衰力調整機構は、前記筒体に連通する流路が形成され前記筒体に接合されるケースと、該ケース内で前記流路に設けられた弁座部材と、該弁座部材に着座するときに前記流路を遮断し、当該弁座部材から離座するときに前記流路を連通する弁部材と、該弁部材が前記弁座部材に着座する方向に付勢する付勢部材と、前記弁座部材と前記弁部材との間に介装され、前記弁部材に支持される調整弁部材とを備え、前記弁部材は、前記弁座部材の外側で対向するように形成された弁座部を有し、前記調整弁部材は、前記弁座部材及び前記弁座部に当接可能に配設され、前記弁座部材の内側で開口する連通路が形成された可撓性の板状弁体を有し、該板状弁体と前記弁座部によって第１の減衰部が構成されると共に、前記板状弁体と前記弁座部材によって第２の減衰部が構成され、初期位置においては前記板状弁体が前記弁座部及び前記弁座部材に当接した状態にあり、前記板状弁体が前記弁座部材から離座する方向への前記弁部材のストロークの増加に応じて、前記板状弁体が順次前記弁座部及び前記弁座部材から離座し、前記連通路、及び前記板状弁体と前記弁座部との間の第１の間隙を介して前記流路が連通して前記第１の減衰部が作動すると共に、前記板状弁体と前記弁座部材との間の第２の間隙を介して前記流路が連通して前記第２の減衰部が作動し、前記弁部材のストロークの増加に応じて前記流路の開口面積が増加するように設定されているものである。 In order to achieve the above object, the present invention provides a cylinder that contains a working fluid, a piston that slides within the cylinder, a piston rod that is connected to the piston, and a fluid that flows through the piston within the cylinder. And a damping force adjusting mechanism for controlling a working fluid to adjust a damping force, wherein the damping force adjusting mechanism includes a case in which a flow path communicating with the cylinder is formed and joined to the cylinder. A valve seat member provided in the flow path in the case, and a valve that blocks the flow path when seated on the valve seat member and communicates the flow path when separated from the valve seat member A member, an urging member that urges the valve member in a direction in which the valve member is seated on the valve seat member, an adjustment valve member that is interposed between the valve seat member and the valve member and is supported by the valve member The valve member is formed so as to be opposed to the outside of the valve seat member. The adjustment valve member is disposed so as to be able to contact the valve seat member and the valve seat portion, and is formed with a communication passage that opens inside the valve seat member. The plate-like valve body and the valve seat portion constitute a first damping portion, and the plate-like valve body and the valve seat member constitute a second damping portion. In the initial position, the plate-like valve body is in contact with the valve seat portion and the valve seat member, and the valve member in a direction in which the plate-like valve body is separated from the valve seat member. As the stroke increases, the plate-like valve body sequentially separates from the valve seat portion and the valve seat member, and the communication path, and the first between the plate-like valve body and the valve seat portion, The flow path communicates with the gap to operate the first damping part, and the second gap between the plate-shaped valve body and the valve seat member is operated. Serial passage the second damping unit is activated in communication, the opening area of the flow path in accordance with the increase of the stroke of the valve member is what is set to increase.

上記の緩衝器において、前記調整弁部材を構成する前記板状弁体は円板状に形成され、前記板状弁体の中央部から外周縁部に向かって変位量が増加するように、前記弁部材の底面に支持され、前記板状弁体の外周縁部の一方の面で前記弁座部に当接可能に配置されると共に、前記板状弁体の外周縁部の他方の面で前記弁座部材に当接可能に配置され、前記板状弁体の一方の面と前記弁座部との間に空隙が形成され、該空隙に連通するように前記連通路が前記板状弁体に形成されている構成とするとよい。 In the above shock absorber, the plate-like valve body constituting the adjustment valve member is formed in a disc shape, and the displacement amount increases from a central portion of the plate-like valve body toward an outer peripheral edge portion. It is supported on the bottom surface of the valve member and is arranged so as to be able to contact the valve seat portion on one surface of the outer peripheral edge portion of the plate-shaped valve body, and on the other surface of the outer peripheral edge portion of the plate-shaped valve body. The valve seat member is disposed so as to be in contact with the valve seat member, and a gap is formed between one surface of the plate-like valve body and the valve seat portion, and the communication passage communicates with the gap. It is good to be the structure currently formed in the body.

前記板状弁体に形成される前記連通路は、前記板状弁体の中央部から放射状に延出する少なくとも一つのスリット状に形成するとよい。更に、前記弁部材に形成された前記弁座部の着座径は、前記弁座部材の着座径より大に設定されている構成とするとよい。 The communication passage formed in the plate-shaped valve body may be formed in at least one slit shape extending radially from a central portion of the plate-shaped valve body. Furthermore, the seat diameter of the valve seat portion formed on the valve member may be set to be larger than the seat diameter of the valve seat member.

本発明は上述のように構成されているので以下の効果を奏する。即ち、本発明の緩衝器においては、減衰力調整機構が、筒体に連通する流路が形成され筒体に接合されるケースと、ケース内で流路に設けられた弁座部材と、弁座部材に着座するときに流路を遮断し、弁座部材から離座するときに流路を連通する弁部材と、弁部材が弁座部材に着座する方向に付勢する付勢部材と、弁座部材と弁部材との間に介装され、弁部材に支持される調整弁部材とを備えたものであり、弁部材は、弁座部材の外側で対向するように形成された弁座部を有し、調整弁部材は、弁座部材及び弁座部に当接可能に配設され、弁座部材の内側で開口する連通路が形成された可撓性の板状弁体を有し、板状弁体と弁座部によって第１の減衰部が構成されると共に、板状弁体と弁座部材によって第２の減衰部が構成され、初期位置においては板状弁体が弁座部及び弁座部材に当接した状態にあり、板状弁体が弁座部材から離座する方向への弁部材のストロークの増加に応じて、板状弁体が順次弁座部及び弁座部材から離座し、連通路、及び板状弁体と弁座部との間の第１の間隙を介して流路が連通して第１の減衰部が作動すると共に、板状弁体と弁座部材との間の第２の間隙を介して流路が連通して第２の減衰部が作動し、弁部材のストロークの増加に応じて流路の開口面積が増加するように設定されているので、減衰力低減効果が大きく、安定した所望の減衰力特性を確保することができる。 Since this invention is comprised as mentioned above, there exist the following effects. That is, in the shock absorber of the present invention, the damping force adjusting mechanism includes a case in which a flow path communicating with the cylinder is formed and joined to the cylinder, a valve seat member provided in the flow path in the case, and a valve A valve member that shuts off the flow path when seated on the seat member, and communicates the flow path when separated from the valve seat member; and a biasing member that biases the valve member in the direction of seating on the valve seat member; An adjustment valve member interposed between the valve seat member and the valve member and supported by the valve member. The valve member is formed so as to be opposed to the outside of the valve seat member. The adjustment valve member has a flexible plate-shaped valve body that is disposed so as to be in contact with the valve seat member and the valve seat portion and has a communication passage that opens inside the valve seat member. The plate-like valve body and the valve seat portion constitute a first damping portion, and the plate-like valve body and the valve seat member constitute a second damping portion, which is at the initial position. In this state, the plate-shaped valve body is in contact with the valve seat portion and the valve seat member, and the plate-shaped valve body increases in response to an increase in the stroke of the valve member in the direction in which the plate-shaped valve body separates from the valve seat member. The body sequentially moves away from the valve seat part and the valve seat member, and the flow path communicates through the communication path and the first gap between the plate-like valve body and the valve seat part, and the first attenuation part In addition, the flow path communicates via the second gap between the plate-shaped valve body and the valve seat member, the second damping portion is activated, and the flow path is increased in response to an increase in the stroke of the valve member. Since the opening area is set to increase, the damping force reduction effect is large, and a stable desired damping force characteristic can be ensured.

特に、第１及び第２の減衰部が異なる減衰部面積を有するので、減衰力を連続的に変化させることができ、更に第１及び第２の減衰部が並列に配置されていることになるため、弁部材が開弁方向にストロークしたときにも、内側に配置される減衰部に影響されることはなく、減衰力を適切且つ十分に低減することができる。しかも、上記の板状弁部材が可撓性を有するものであるため、板状弁体と弁座部及び弁座部材の重なりによってシール部を構成する必要はなく、両者間の幾何学的な許容限度が大きく、安定した減衰力特性を確保することができる。 Particularly, since the first and second attenuation portions have different attenuation portion areas, the attenuation force can be continuously changed, and the first and second attenuation portions are arranged in parallel. Therefore, even when the valve member strokes in the valve opening direction, it is not affected by the damping portion arranged on the inner side, and the damping force can be appropriately and sufficiently reduced. Moreover, since the plate-shaped valve member is flexible, it is not necessary to form a seal portion by overlapping the plate-shaped valve body, the valve seat portion, and the valve seat member, and the geometrical relationship between the two is not necessary. The allowable limit is large, and stable damping force characteristics can be secured.

上記の緩衝器において、調整弁部材を構成する板状弁体は円板状に形成され、板状弁体の中央部から外周縁部に向かって変位量が増加するように、弁部材の底面に支持され、板状弁体の外周縁部の一方の面で弁座部に当接可能に配置されると共に、板状弁体の外周縁部の他方の面で弁座部材に当接可能に配置され、板状弁体の一方の面と弁座部との間に空隙が形成され、空隙に連通するように連通路が板状弁体に形成されている構成とすれば、幾何学的な許容限度が大きく、安定した減衰力特性を容易に確保することができる。 In the above shock absorber, the plate-like valve body constituting the adjusting valve member is formed in a disc shape, and the bottom surface of the valve member is increased so that the amount of displacement increases from the center portion of the plate-like valve body toward the outer peripheral edge portion. And is arranged so that it can come into contact with the valve seat on one surface of the outer peripheral edge of the plate-like valve body, and can come into contact with the valve seat member on the other surface of the outer peripheral edge of the plate-like valve body If the configuration is such that a gap is formed between one surface of the plate-shaped valve body and the valve seat portion, and a communication path is formed in the plate-shaped valve body so as to communicate with the gap, Therefore, a stable damping force characteristic can be easily secured.

上記の板状弁体に形成される連通路を、板状弁体の中央部から放射状に延出する少なくとも一つのスリット状に形成すれば、板状弁体の中央部を弁部材の底面に支持するだけで、上記の空隙を前述の流路に容易に連通させることができる。更に、弁部材に形成された弁座部の着座径を、弁座部材の着座径より大に設定すれば、第１及び第２の減衰部を容易に且つ確実に並列に配置することができる。 If the communication passage formed in the plate-shaped valve body is formed in at least one slit shape extending radially from the central portion of the plate-shaped valve body, the central portion of the plate-shaped valve body is formed on the bottom surface of the valve member. By simply supporting the gap, the gap can be easily communicated with the flow path. Furthermore, if the seating diameter of the valve seat part formed in the valve member is set larger than the seating diameter of the valve seat member, the first and second damping parts can be easily and reliably arranged in parallel. .

本発明の一実施形態に係る緩衝器に装着された減衰力調整機構の断面図である。It is sectional drawing of the damping force adjustment mechanism with which the buffer which concerns on one Embodiment of this invention was mounted | worn. 本発明の一実施形態に供される調整弁部材の平面図である。It is a top view of the adjustment valve member provided for one Embodiment of this invention. 本発明の一実施形態に供される調整弁部材の別の態様を示す平面図である。It is a top view which shows another aspect of the adjustment valve member provided to one Embodiment of this invention. 本発明の一実施形態に供される減衰力調整機構の一部を拡大して示す断面図である。It is sectional drawing which expands and shows a part of damping force adjustment mechanism with which one Embodiment of this invention is provided. 本発明の一実施形態に係る減衰力調整機構の作動状態を示す断面図である。It is sectional drawing which shows the operating state of the damping force adjustment mechanism which concerns on one Embodiment of this invention. 本発明の一実施形態に係る減衰力調整機構の作動状態を示す断面図である。It is sectional drawing which shows the operating state of the damping force adjustment mechanism which concerns on one Embodiment of this invention. 本発明の一実施形態に係る緩衝器の減衰力特性を従来特性と対比して示すグラフである。It is a graph which shows the damping force characteristic of the buffer concerning one embodiment of the present invention as contrasted with the conventional characteristic.

以下、本発明の望ましい実施形態を図面を参照して説明する。図１は本発明の一実施形態に係る緩衝器に装着された減衰力調整機構を示すもので、作動流体を収容する筒体１が外筒１ａ、内筒１ｂ及びシリンダ１ｃから成り、図１に二点鎖線で示すように、筒体１内を摺動するピストン２と、このピストン２に接続するピストンロッド３を備えている。内筒１ｂとシリンダ１ｃとの間に第１の流路Ｆ１が形成され、外筒１ａと内筒１ｂとの間に第２の流路Ｆ２が形成されている。シリンダ１ｃ内にはピストン２の両側に上室ＵＣ及び下室ＬＣが形成され、シリンダ１ｃの底部の下室ＬＣ内にベースバルブＢＶが配設され、ピストン２内にはピストンバルブＰＶが配設されている。何れのバルブも従前と同様に構成されており、少なくとも、夫々所定の流体圧以上で下方側から上方側への流体の流れを許容し逆方向の流れを遮断する一方向弁機能を有している。このベースバルブＢＶを介して下室ＬＣが第２の流路Ｆ２に連通し、上室ＵＣが第１の流路Ｆ１に連通している。 Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a damping force adjusting mechanism mounted on a shock absorber according to an embodiment of the present invention. A cylindrical body 1 that contains a working fluid is composed of an outer cylinder 1a, an inner cylinder 1b, and a cylinder 1c. As shown by a two-dot chain line, a piston 2 that slides inside the cylindrical body 1 and a piston rod 3 that is connected to the piston 2 are provided. A first flow path F1 is formed between the inner cylinder 1b and the cylinder 1c, and a second flow path F2 is formed between the outer cylinder 1a and the inner cylinder 1b. In the cylinder 1c, an upper chamber UC and a lower chamber LC are formed on both sides of the piston 2, a base valve BV is disposed in the lower chamber LC at the bottom of the cylinder 1c, and a piston valve PV is disposed in the piston 2. Has been. Each valve is configured in the same manner as before, and has at least a one-way valve function that allows fluid flow from the lower side to the upper side at a predetermined fluid pressure or higher and blocks the reverse flow. Yes. Through this base valve BV, the lower chamber LC communicates with the second flow path F2, and the upper chamber UC communicates with the first flow path F1.

上記の筒体１に減衰力調整機構ＤＡが接合され、図１に示すように第１の流路Ｆ１及び第２の流路Ｆ２に連通接続されている。而して、上室ＵＣ内の流体が第１の流路Ｆ１に排出され、減衰力調整機構ＤＡに導入される。そして、減衰力調整機構ＤＡから第２の流路Ｆ２に排出され、ベースバルブＢＶを介して下室ＬＣ内に導入される。尚、第２の流路Ｆ２は所謂リザーバとして機能する。 A damping force adjusting mechanism DA is joined to the cylinder 1 and is connected to the first flow path F1 and the second flow path F2 as shown in FIG. Thus, the fluid in the upper chamber UC is discharged to the first flow path F1 and introduced into the damping force adjusting mechanism DA. And it is discharged | emitted from the damping-force adjustment mechanism DA to the 2nd flow path F2, and is introduce | transduced in the lower chamber LC via the base valve BV. The second flow path F2 functions as a so-called reservoir.

本実施形態の減衰力調整機構ＤＡは、二重筒形状のケース１０が筒体１に接合され、このケース１０内に弁部材３０が収容された状態で、ソレノイドアッセンブリ４０がケース１０に接合されている。ケース１０は、内筒１ｂに開口する円筒部１ｄの内周面に一方の開口端部が液密的に嵌合される内側ケース１１と、これを囲繞するように配設され、第２の流路Ｆ２に連通するように外筒１ａに一方の開口端部が接合される外側ケース１２で構成され、内側ケース１１の他方の開口端部が拡径されて成るフランジ部１１ａが、外側ケース１２の内周面に形成された環状段部１２ａに係止されるように配設される。そして、ソレノイドアッセンブリ４０の段付環状部材４３が、内側ケース１１のフランジ部１１ａの端面に当接すると共に外側ケース１２の内周面に液密的に嵌合した状態で、外側ケース１２の外周面に円筒状の締結部材１３が螺合されて一体となるように構成されている。 In the damping force adjusting mechanism DA of this embodiment, the double cylinder-shaped case 10 is joined to the cylinder 1, and the solenoid assembly 40 is joined to the case 10 with the valve member 30 housed in the case 10. ing. The case 10 is disposed so as to surround the inner case 11 in which one opening end portion is liquid-tightly fitted to the inner peripheral surface of the cylindrical portion 1d that opens to the inner cylinder 1b. The outer casing 1a is joined to the outer cylinder 1a so as to communicate with the flow path F2, and the outer casing 12 has a flange 11a formed by expanding the diameter of the other opening end of the inner casing 11. It arrange | positions so that it may latch on the cyclic | annular step part 12a formed in the 12 inner peripheral surface. The stepped annular member 43 of the solenoid assembly 40 is in contact with the end surface of the flange portion 11a of the inner case 11 and is liquid-tightly fitted to the inner peripheral surface of the outer case 12, so that the outer peripheral surface of the outer case 12 is closed. A cylindrical fastening member 13 is screwed together so as to be integrated.

内側ケース１１の一方の開口端部内には円筒状の弁座部材２１が圧入されており、この開口端面に当接して着座し得るように弁部材２２が内側ケース１１内に収容され、所定の軸方向距離を摺動可能に支持されている。図１に示すように、弁部材２２は有底筒体のカップ形状に形成され、底部に連通孔Ｐ０が形成されると共に、外周面にラビリンス溝が形成されている。更に、弁部材２２の筒体内には、弁部材２２に対し径方向及び軸方向に間隙を以って、有底筒体のハット形状に形成された弁座部材２３が遊嵌され、内側ケース１１の内周面に形成された環状段部１１ｂにフランジ部２３ａが係止されて、弁部材２２に対する上記所定の軸方向距離が維持される。弁部材２２と弁座部材２３との環状間隙には圧縮コイルばねＢ１が収容され、弁部材２２の底部と弁座部材２３のフランジ部２３ａとの間に張設されている。弁座部材２３の底部には連通孔Ｐ１が形成され、その回りに第１の弁座Ｓ１が形成されている。尚、弁部材２２には調整弁部材５０が支持されているが、これについては後述する。 A cylindrical valve seat member 21 is press-fitted into one open end portion of the inner case 11, and a valve member 22 is accommodated in the inner case 11 so as to be able to be seated in contact with the open end surface. Axial distance is slidably supported. As shown in FIG. 1, the valve member 22 is formed in a cup shape of a bottomed cylindrical body, a communication hole P0 is formed at the bottom, and a labyrinth groove is formed on the outer peripheral surface. Further, a valve seat member 23 formed in a hat shape of a bottomed cylindrical body with a gap in the radial direction and the axial direction with respect to the valve member 22 is loosely fitted in the cylindrical body of the valve member 22, and the inner case The flange portion 23a is locked to the annular step portion 11b formed on the inner peripheral surface of the valve 11, so that the predetermined axial distance with respect to the valve member 22 is maintained. A compression coil spring B1 is accommodated in the annular gap between the valve member 22 and the valve seat member 23, and is stretched between the bottom portion of the valve member 22 and the flange portion 23a of the valve seat member 23. A communication hole P1 is formed at the bottom of the valve seat member 23, and a first valve seat S1 is formed therearound. The valve member 22 supports an adjustment valve member 50, which will be described later.

更に、弁部材３０を軸方向移動可能に支持する筒体の支持部材２４が内側ケース１１内に収容され、支持部材２４の一端に形成されたフランジ部２４ａが、弁座部材２３のフランジ部２３ａに当接するように配置されている。弁部材３０と弁座部材２３との環状間隙には圧縮コイルばねＢ２が収容され、弁座部材２３の底部と弁部材３０の大径部３２との間に張設されている。尚、支持部材２４の側壁には径方向に連通孔Ｐ３が形成され、内側ケース１１の側壁にも径方向に連通孔Ｐ４及びＰ５が形成されている。本実施形態の弁部材３０は段付ロッド形状の単一部材で、軸方向の連通孔３３、並びにこれに連通する径方向の連通孔３４及び３５が形成されているが、連通孔３５は省略することとしてもよい。 Further, a cylindrical support member 24 that supports the valve member 30 so as to be movable in the axial direction is accommodated in the inner case 11, and a flange portion 24 a formed at one end of the support member 24 is a flange portion 23 a of the valve seat member 23. It arrange | positions so that it may contact | abut. A compression coil spring B <b> 2 is accommodated in the annular gap between the valve member 30 and the valve seat member 23, and is stretched between the bottom portion of the valve seat member 23 and the large diameter portion 32 of the valve member 30. A communication hole P3 is formed in the radial direction on the side wall of the support member 24, and communication holes P4 and P5 are also formed in the radial direction on the side wall of the inner case 11. The valve member 30 of the present embodiment is a single member having a stepped rod shape, and is formed with an axial communication hole 33 and radial communication holes 34 and 35 communicating with the axial communication hole 33, but the communication hole 35 is omitted. It is good to do.

支持部材２４のフランジ部２４ａには弁部材３０の大径部３２より小径で、弁部材３０の中間部より大径の連通孔Ｐ２が形成されており、その回りに第２の弁座Ｓ２が構成されている。弁部材３０は、第２の弁座Ｓ２に対し大径部３２が着座可能に保持されると共に、支持部材２４の筒体内に、例えば焼結金属製のブシュ２５を介して摺動可能に保持され、弁座部材２３内に圧縮コイルばねＢ２が収容された状態で、支持部材２４のフランジ部２４ａが弁座部材２３のフランジ部２３ａに当接するように配置される。而して、弁部材３０には、弁部材３０の先端部３１によって第１の弁体部Ｖ１が構成されると共に、大径部３２によって第２の弁体部Ｖ２が構成されており、後述するように、第１の弁体部Ｖ１と第１の弁座Ｓ１によって連通孔Ｐ１の流量を制御し得るように構成されている。尚、弁部材３０とブシュ２５との間は液密的嵌合状態とし、流体が通過しないように設定することが好ましい。 A communication hole P2 having a diameter smaller than that of the large diameter portion 32 of the valve member 30 and larger than that of the intermediate portion of the valve member 30 is formed in the flange portion 24a of the support member 24, and a second valve seat S2 is formed around the communication hole P2. It is configured. The valve member 30 is held so that the large-diameter portion 32 can be seated on the second valve seat S2, and slidably held in the cylindrical body of the support member 24 via a bush 25 made of sintered metal, for example. In the state where the compression coil spring B <b> 2 is accommodated in the valve seat member 23, the flange portion 24 a of the support member 24 is disposed so as to contact the flange portion 23 a of the valve seat member 23. Thus, the valve member 30 has a first valve body portion V1 formed by the tip portion 31 of the valve member 30, and a second valve body portion V2 formed by the large diameter portion 32, which will be described later. As described above, the flow rate of the communication hole P1 can be controlled by the first valve body V1 and the first valve seat S1. The valve member 30 and the bush 25 are preferably set in a liquid tight fitting state so that fluid does not pass through.

一方、ソレノイドアッセンブリ４０は、弁部材３０の後端面に当接するように配設される円筒状のプランジャ４１が、金属の深絞り成形によって形成された円筒状のプランジャケース４２内に摺動可能に収容された状態で、プランジャケース４２の開口端部が段付環状部材４３の小径筒体部４３ａに溶接接合され、段付環状部材４３と一体となっている。段付環状部材４３は固定コアとして機能し、その中央部にはテーパ孔（中径孔）４３ｂ、小径孔４３ｃ及び大径孔４３ｄが形成されており、小径孔４３ｃに弁部材３０の胴部が遊嵌されると共に、大径孔４３ｄに支持部材２４が遊嵌され、夫々の微小間隙を流体が通過し得るように配設されている。 On the other hand, in the solenoid assembly 40, a cylindrical plunger 41 arranged so as to contact the rear end surface of the valve member 30 is slidable in a cylindrical plunger case 42 formed by metal deep drawing. In the accommodated state, the open end of the plunger case 42 is welded and joined to the small-diameter cylindrical portion 43 a of the stepped annular member 43 and is integrated with the stepped annular member 43. The stepped annular member 43 functions as a fixed core, and a tapered hole (medium diameter hole) 43b, a small diameter hole 43c, and a large diameter hole 43d are formed at the center thereof, and the body portion of the valve member 30 is formed in the small diameter hole 43c. Are loosely fitted, and the support member 24 is loosely fitted into the large-diameter hole 43d so that the fluid can pass through each minute gap.

更に、プランジャケース４２の回りに円筒状の固定コア４４が配設されると共に、その回りに円筒状のソレノイドコイル４５が配設されている。そして、ソレノイドコイル４５に電気的に接続されるコネクタ４７と共に、これらを収容する円筒状のソレノイドケース４６が段付環状部材４３に接合され、前述のように締結部材１３によって外側ケース１２に接合される。尚、プランジャケース４２内には流体が充填され、プランジャ４１の両端面に付与される圧力が相殺されるので、流体の圧力によってプランジャ４１に対する駆動力が左右されることはない。また、弁部材３０は円筒体ではなく中実部を有するので、弁座部材２３内の流体圧がそのままプランジャ４１側に伝達されることはなく、しかも、プランジャ４１に至る流路は上記の微小間隙で絞られているので、プランジャケース４２内が高圧となることを回避し得る。 Further, a cylindrical fixed core 44 is disposed around the plunger case 42 and a cylindrical solenoid coil 45 is disposed around the fixed core 44. Then, together with a connector 47 electrically connected to the solenoid coil 45, a cylindrical solenoid case 46 for housing them is joined to the stepped annular member 43, and joined to the outer case 12 by the fastening member 13 as described above. The Since the plunger case 42 is filled with fluid and the pressure applied to both end faces of the plunger 41 is canceled out, the driving force for the plunger 41 is not influenced by the pressure of the fluid. Further, since the valve member 30 has a solid part instead of a cylindrical body, the fluid pressure in the valve seat member 23 is not transmitted to the plunger 41 as it is, and the flow path to the plunger 41 is the above-mentioned minute amount. Since it is squeezed by the gap, the inside of the plunger case 42 can be avoided from becoming a high pressure.

而して、本実施形態においては、筒体１に連通する流路（Ｆ１）が形成され筒体１に接合されるケース１０と、ケース１０内で流路（Ｆ１）に設けられた弁座部材２１と、弁座部材２１に着座するときに流路を遮断し、弁座部材２１から離座するときに流路を連通する弁部材２２と、この弁部材２２が弁座部材２１に着座する方向に付勢する付勢部材（圧縮コイルばねＢ１）と、弁座部材２１と弁部材２２との間に介装され、弁部材２２に支持される調整弁部材５０とを備えた減衰力調整機構ＤＡが構成されている。 Thus, in this embodiment, the flow path (F1) communicating with the cylindrical body 1 is formed and the case 10 joined to the cylindrical body 1, and the valve seat provided in the flow path (F1) in the case 10 The valve member 22 that shuts off the flow path when seated on the member 21 and the valve seat member 21 and communicates the flow path when separated from the valve seat member 21, and the valve member 22 sits on the valve seat member 21. Damping force provided with an urging member (compression coil spring B1) for urging in the direction to be moved, and an adjustment valve member 50 interposed between the valve seat member 21 and the valve member 22 and supported by the valve member 22 An adjustment mechanism DA is configured.

本実施形態の弁部材２２は、図４に拡大して示すように、弁座部材２１の外側で対向するように形成された弁座部２２ａを有する。そして、調整弁部材５０は、弁座部材２１及び弁座部２２ａに当接可能に配設され、弁座部材２１の内側で開口する連通路５２が形成された可撓性の板状弁体５１を有しており、板状弁体５１と弁座部２２ａによって第１の減衰部が構成されると共に、板状弁体５１と弁座部材２１によって第２の減衰部が構成されている。 The valve member 22 of the present embodiment has a valve seat portion 22a formed so as to face the outside of the valve seat member 21, as shown in an enlarged view in FIG. The adjusting valve member 50 is disposed so as to be able to contact the valve seat member 21 and the valve seat portion 22a, and is a flexible plate-like valve body in which a communication passage 52 that opens inside the valve seat member 21 is formed. 51, the plate-like valve body 51 and the valve seat portion 22a constitute a first damping part, and the plate-like valve body 51 and the valve seat member 21 constitute a second damping part. .

図１及び図４に示す初期位置においては、板状弁体５１が弁部材２２の弁座部２２ａ及び弁座部材２１に当接した状態にあり、板状弁体５１が弁座部材２１から離座する方向への弁部材２２のストロークの増加に応じて、板状弁体５１が順次弁座部２２ａ及び弁座部材２１から離座し、連通路５２、及び板状弁体５１と弁座部２２ａとの間の第１の間隙Ｇ１（図５及び図６に示す）を介して流路（Ｆ１）が連通して第１の減衰部が作動すると共に、板状弁体５１と弁座部材２１との間の第２の間隙Ｇ２（図６に示す）を介して流路（Ｆ１）が連通して第２の減衰部が作動し、弁部材２２のストロークの増加に応じて流路（Ｆ１）の開口面積が増加するように設定されている。 In the initial position shown in FIGS. 1 and 4, the plate-like valve body 51 is in contact with the valve seat portion 22 a and the valve seat member 21 of the valve member 22, and the plate-like valve body 51 is separated from the valve seat member 21. As the stroke of the valve member 22 increases in the separating direction, the plate-like valve body 51 is sequentially separated from the valve seat portion 22a and the valve seat member 21, and the communication passage 52, the plate-like valve body 51, and the valve The flow path (F1) communicates with the seat portion 22a via the first gap G1 (shown in FIGS. 5 and 6) to operate the first damping portion, and the plate-like valve body 51 and the valve The flow path (F1) communicates with the seat member 21 via the second gap G2 (shown in FIG. 6), and the second damping portion is activated, so that the flow increases as the stroke of the valve member 22 increases. The opening area of the path (F1) is set to increase.

図２及び図４に拡大して示すように、本実施形態の調整弁部材５０は、可撓性を有する金属製円板形状の板状弁体５１で構成され、この板状弁体５１が、中央部５１ａから外周縁部５１ｂに向かって変位量が増加するように、中央部５１ａで弁部材２２の底面に支持され、外周縁部５１ｂの一方の面（図２に二点鎖線で示す枠内のハッチング領域）で環状の弁座部２２ａに当接可能に配置されると共に、外周縁部５１ｂの他方の面（図２に破線で示す枠内のハッチング領域）で弁座部材２１に当接可能に配置される。換言すれば、板状弁体５１は、その外周縁部５１ｂの一方の面で、弁座部２２ａが図２の二点鎖線枠内のハッチング領域に着座し、外周縁部５１ｂの他方の面で、弁座部材２１が図２の破線枠内のハッチング領域に着座するように配置される。 As shown in enlarged views in FIGS. 2 and 4, the adjustment valve member 50 of the present embodiment is configured by a metal disc-shaped plate-shaped valve body 51 having flexibility, and the plate-shaped valve body 51 is configured as follows. The central portion 51a is supported on the bottom surface of the valve member 22 so that the amount of displacement increases from the central portion 51a toward the outer peripheral edge portion 51b. One surface of the outer peripheral edge portion 51b (indicated by a two-dot chain line in FIG. 2) (Hatching area in the frame) is arranged so as to be able to contact the annular valve seat portion 22a, and the other surface of the outer peripheral edge portion 51b (hatching area in the frame shown by a broken line in FIG. 2) is attached to the valve seat member 21. It arrange | positions so that contact | abutment is possible. In other words, the plate-like valve body 51 has one face of the outer peripheral edge 51b, the valve seat 22a is seated in the hatched area in the two-dot chain line frame in FIG. 2, and the other face of the outer peripheral edge 51b. Thus, the valve seat member 21 is arranged so as to be seated in the hatched area in the broken line frame of FIG.

板状弁体５１は可撓性を有し、その中央部に形成された取付孔５１ｃ（図２及び図４に示す）が、弁部材２２の底面に形成された凸部２２ｂ（図４に示す）に圧入されて、弁部材２２に支持されるので、図５及び図６に示すように、外周縁部５１ｂと弁座部２２ａとの間に第１の間隙Ｇ１が形成され、外周縁部５１ｂと弁座部材２１との間に第２の間隙Ｇ２が形成され得る。更に、板状弁体５１の中央部５１ａ（取付孔５１ｃ）から放射状に延出するスリット状の連通路５２が形成されている。そして、図２及び図４に示すように、弁部材２２に形成された弁座部２２ａの着座径（図２に示す二点鎖線枠内のハッチング領域の中心径Ｄ１）は、弁座部材２１の着座径（図２に示す破線枠内のハッチング領域の中心径Ｄ２で示す）より大に設定されている。 The plate-like valve body 51 has flexibility, and a mounting hole 51c (shown in FIGS. 2 and 4) formed in the center thereof is a convex portion 22b (shown in FIG. 4) formed on the bottom surface of the valve member 22. The first gap G1 is formed between the outer peripheral edge portion 51b and the valve seat portion 22a, as shown in FIGS. 5 and 6, so that the outer peripheral edge is supported by the valve member 22. A second gap G2 may be formed between the portion 51b and the valve seat member 21. Furthermore, a slit-like communication passage 52 extending radially from the central portion 51a (mounting hole 51c) of the plate-like valve body 51 is formed. 2 and 4, the seat diameter of the valve seat portion 22a formed on the valve member 22 (the center diameter D1 of the hatched area in the two-dot chain line frame shown in FIG. 2) is the valve seat member 21. Is set to be larger than the seating diameter (indicated by the center diameter D2 of the hatched area in the broken line frame shown in FIG. 2).

而して、図４に示すように、板状弁体５１の一方の面と弁座部２２ａとの間に空隙Ｇ３が形成され、この空隙Ｇ３に連通路５２が連通するように、調整弁部材５０が配設されている。尚、板状弁体５１は、図３に示すように、中央部５１ａ（取付孔５１ｃ）と外周縁部５１ｂとの間に形成された一対の連通孔５３、５３によって、上記の空隙Ｇ３に連通する連通路を構成することとしてもよい。 Thus, as shown in FIG. 4, a regulating valve is formed so that a gap G3 is formed between one surface of the plate-like valve body 51 and the valve seat portion 22a, and the communication path 52 communicates with the gap G3. A member 50 is provided. As shown in FIG. 3, the plate-shaped valve body 51 is formed in the gap G3 by a pair of communication holes 53, 53 formed between the central portion 51a (mounting hole 51c) and the outer peripheral edge portion 51b. It is good also as comprising the communicating path which connects.

次に、上記の構成になる減衰力調整機構ＤＡが装着された緩衝器の全体作動を説明する。図１の停止状態から、例えばピストン２が下室ＬＣ内を圧縮して下降し始めると、下室ＬＣ内の流体がピストンバルブＰＶを介して上室ＵＣに移動し、第１の流路Ｆ１から減衰力調整機構ＤＡの弁座部材２１、連通孔Ｐ０、Ｐ１を介して弁部材２２及び弁座部材２３内に導入され、連通孔Ｐ２乃至Ｐ４を介して第２の流路Ｆ２に排出される。ピストン２の速度の上昇に伴い第１の流路Ｆ１から弁座部材２１に導入される圧力が上昇すると、弁部材２２は圧縮コイルばねＢ１の付勢力に抗して弁座部材２１から離座し、流体は両者間の間隙から連通孔Ｐ５を介して第２の流路Ｆ２に排出される。ピストン２が上室ＵＣ内を圧縮して上昇する場合も減衰力調整機構ＤＡが同様に作動する。 Next, the overall operation of the shock absorber equipped with the damping force adjusting mechanism DA configured as described above will be described. For example, when the piston 2 starts to compress and lower in the lower chamber LC from the stopped state of FIG. 1, the fluid in the lower chamber LC moves to the upper chamber UC via the piston valve PV, and the first flow path F1. Are introduced into the valve member 22 and the valve seat member 23 through the valve seat member 21 and the communication holes P0 and P1 of the damping force adjusting mechanism DA, and discharged to the second flow path F2 through the communication holes P2 to P4. The When the pressure introduced from the first flow path F1 to the valve seat member 21 increases as the speed of the piston 2 increases, the valve member 22 separates from the valve seat member 21 against the biasing force of the compression coil spring B1. The fluid is then discharged from the gap between the two into the second flow path F2 through the communication hole P5. The damping force adjusting mechanism DA operates in the same manner when the piston 2 rises by compressing the inside of the upper chamber UC.

更に、減衰力調整機構ＤＡのソレノイドコイル４５が励磁されると、プランジャ４１が前進駆動され（図１の左方に移動）、圧縮コイルばねＢ２の付勢力に抗して弁部材３０が同方向に駆動され、ソレノイドコイル４５の励磁電流の増加に伴い弁部材３０の先端部（第１の弁体部Ｖ１）が第１の弁座Ｓ１に近接し、最終的には第１の弁体部Ｖ１が第１の弁座Ｓ１に着座する。この間、第１の流路Ｆ１から導入される流体によって弁部材２２の底部の両側に圧力差が生じ、圧縮コイルばねＢ１の付勢力に抗して弁部材２２が図１の右方向に駆動され、弁座部材２１から離座し、流体は両者間の間隙から連通孔Ｐ５を介して第２の流路Ｆ２に排出される。 Further, when the solenoid coil 45 of the damping force adjusting mechanism DA is excited, the plunger 41 is driven forward (moved to the left in FIG. 1), and the valve member 30 moves in the same direction against the biasing force of the compression coil spring B2. As the exciting current of the solenoid coil 45 increases, the tip end portion (first valve body portion V1) of the valve member 30 comes close to the first valve seat S1, and finally the first valve body portion. V1 is seated on the first valve seat S1. During this time, a pressure difference is generated on both sides of the bottom of the valve member 22 by the fluid introduced from the first flow path F1, and the valve member 22 is driven rightward in FIG. 1 against the urging force of the compression coil spring B1. The fluid is separated from the valve seat member 21, and the fluid is discharged from the gap between the two into the second flow path F2 through the communication hole P5.

そして、この間のソレノイドコイル４５に対する励磁電流の制御によって、弁部材２２ひいては調整弁部材５０が弁座部材２１から離座する方向の弁部材２２のストロークの増加に応じて、先ず、板状弁体５１が弁座部２２ａから離座し、図５に示す状態になると、連通路５２、及び板状弁体５１と弁座部２２ａとの間に形成される第１の間隙Ｇ１を介して、流路（Ｆ１）からの流体が図５に矢印で示すように、連通孔Ｐ５（図１に示す）に至る方向（図５の下方）に流れ、前述の第１の減衰部が作動する。 Then, by controlling the exciting current for the solenoid coil 45 during this period, first, the plate-like valve body is increased in response to an increase in the stroke of the valve member 22 in the direction in which the valve member 22 and thus the adjusting valve member 50 is separated from the valve seat member 21. When 51 is separated from the valve seat portion 22a and enters the state shown in FIG. 5, through the communication passage 52 and the first gap G1 formed between the plate-like valve body 51 and the valve seat portion 22a, As indicated by an arrow in FIG. 5, the fluid from the flow path (F1) flows in a direction (downward in FIG. 5) reaching the communication hole P5 (shown in FIG. 1), and the first attenuation section described above is activated.

続いて、板状弁体５１が弁座部材２１からも離座し、図６に示す状態になると、上記の連通路５２、及び板状弁体５１と弁座部２２ａとの第１の間隙Ｇ１に加え、板状弁体５１と弁座部材２１との間に形成される第２の間隙Ｇ２を介して、流路（Ｆ１）からの流体が図６に矢印で示すように、連通孔Ｐ５（図１に示す）に至る方向（図６の下方）に流れ、前述の第２の減衰部が作動し、以後、弁部材２２のストロークの増加に応じて流路（Ｆ１）の開口面積が増加し、通過する流体の流量が増大する。 Subsequently, when the plate-like valve body 51 is also separated from the valve seat member 21 and is in the state shown in FIG. 6, the communication passage 52 and the first gap between the plate-like valve body 51 and the valve seat portion 22a. In addition to G1, through the second gap G2 formed between the plate-like valve body 51 and the valve seat member 21, the fluid from the flow path (F1) is shown in FIG. It flows in the direction (downward in FIG. 6) to reach P5 (shown in FIG. 1), and the above-described second damping section is activated. Thereafter, the opening area of the flow path (F1) according to the increase in the stroke of the valve member 22 Increases and the flow rate of the fluid passing therethrough increases.

而して、調整弁部材５０を通過する流体の流量が変化し、これに応じて、第１及び第２の流路Ｆ１及びＦ２内の流体に付与される減衰力が調整される。例えば、ソレノイドコイル４５に対する励磁電流を増加させると、プランジャ４１に対する前進駆動力が増大し、第１の弁体部Ｖ１と第１の弁座Ｓ１との間を通過する流体の流量は減少するので、発生する減衰力が増大し、所謂ハードな減衰力制御となる。これに対し、ソレノイドコイル４５に対する励磁電流を減少させると、プランジャ４１に対する駆動力が低下し、第１の弁体部Ｖ１と第１の弁座Ｓ１との間を通過する流体の流量が増大するので、発生する減衰力は低下し、所謂ソフトな減衰力制御となるが、何れの場合においても、図７に示すように、破線で示す従前の装置の減衰力特性に比し、本実施形態によれば、ピストン速度が増大したときの減衰力の上昇を抑え（減衰力を低減し）、安定した減衰力特性を確保することができる。 Thus, the flow rate of the fluid passing through the adjustment valve member 50 changes, and the damping force applied to the fluid in the first and second flow paths F1 and F2 is adjusted accordingly. For example, if the exciting current for the solenoid coil 45 is increased, the forward driving force for the plunger 41 is increased, and the flow rate of the fluid passing between the first valve body V1 and the first valve seat S1 is decreased. The generated damping force increases, and so-called hard damping force control is performed. On the other hand, when the exciting current for the solenoid coil 45 is decreased, the driving force for the plunger 41 is decreased, and the flow rate of the fluid passing between the first valve body V1 and the first valve seat S1 is increased. Therefore, the generated damping force is reduced, and so-called soft damping force control is performed. In any case, as shown in FIG. 7, this embodiment is compared with the damping force characteristic of the conventional device indicated by a broken line. According to this, it is possible to suppress an increase in damping force when the piston speed increases (reduce the damping force) and to secure a stable damping force characteristic.

以上のように、本実施形態の減衰力調整機構ＤＡにおいては、調整弁部材５０が弁座部材２１から離座する方向への弁部材２２のストロークの増加に応じて、板状弁体５１が順次弁座部２２ａ及び弁座部材２１から離座し、連通路５２、及び板状弁体５１と弁座部２２ａとの間の第１の間隙Ｇ１を介して流路（Ｆ１）が連通して第１の減衰部が作動すると共に、板状弁体５１と弁座部材２１との間の第２の間隙Ｇ２を介して流路（Ｆ１）が連通して第２の減衰部が作動し、弁部材２２のストロークの増加に応じて流路（Ｆ１）の開口面積が増加するように設定されているので、減衰力低減効果が大きく、安定した所望の減衰力特性を確保することができる。 As described above, in the damping force adjusting mechanism DA of the present embodiment, the plate-shaped valve body 51 is provided in accordance with the increase in the stroke of the valve member 22 in the direction in which the adjusting valve member 50 is separated from the valve seat member 21. Sequentially separate from the valve seat portion 22a and the valve seat member 21, the flow path (F1) communicates through the communication passage 52 and the first gap G1 between the plate-like valve body 51 and the valve seat portion 22a. The first attenuating portion is activated and the flow path (F1) is communicated via the second gap G2 between the plate-like valve body 51 and the valve seat member 21 to activate the second attenuating portion. Since the opening area of the flow path (F1) is set to increase as the stroke of the valve member 22 increases, the damping force reduction effect is great and a stable desired damping force characteristic can be ensured. .

また、弁座部２２ａ及び弁座部材２１が異なる着座径に設定されているので、板状弁体５１と弁座部２２ａで構成される減衰部面積と、板状弁体５１と弁座部材２１で構成される減衰部面積が異なる。即ち、調整弁部材５０によって構成される第１の減衰部と第２の減衰部が異なる減衰部面積を有するので、減衰力を連続的に変化させることができる。しかも、二つの減衰部が並列に配置されていることになるため、弁部材２２が開弁方向にストロークしたときにも、内側に配置される減衰部に影響されることなく、減衰力を適切且つ十分に低減することができる。特に、板状弁体５１が可撓性を有するため、板状弁体５１と弁座部２２ａ及び弁座部材２１の重なりでシール部を構成する必要はなく、両者間の幾何学的な許容限度が大きく、安定した減衰力特性を確保することができる。 Further, since the valve seat portion 22a and the valve seat member 21 are set to have different seating diameters, the damping portion area constituted by the plate-like valve body 51 and the valve seat portion 22a, the plate-like valve body 51 and the valve seat member 21 is different in the area of the attenuation portion. That is, since the first damping part and the second damping part configured by the regulating valve member 50 have different damping part areas, the damping force can be continuously changed. In addition, since the two damping parts are arranged in parallel, even when the valve member 22 strokes in the valve opening direction, the damping force is appropriately adjusted without being affected by the damping part arranged on the inner side. And it can fully reduce. In particular, since the plate-like valve body 51 is flexible, it is not necessary to form a seal portion by overlapping the plate-like valve body 51 with the valve seat portion 22a and the valve seat member 21, and geometrical allowance between them is not required. The limit is large and stable damping force characteristics can be secured.

１筒体
２ピストン
３ピストンロッド
１０ケース
２１、２３弁座部材
２２、３０弁部材
２４支持部材
４０ソレノイドアセンブリ
４１プランジャ
４５ソレノイドコイル
５０調整弁部材
５１板状弁体
５２連通路
Ｆ１第１の流路
Ｆ２第２の流路
Ｓ１第１の弁座
Ｓ２第２の弁座
Ｇ１第１の間隙
Ｇ２第２の間隙
Ｖ１第１の弁体部
Ｖ２第２の弁体部
Ｐ０〜Ｐ５連通孔 DESCRIPTION OF SYMBOLS 1 Tubular body 2 Piston 3 Piston rod 10 Case 21, 23 Valve seat member 22, 30 Valve member 24 Support member 40 Solenoid assembly 41 Plunger 45 Solenoid coil 50 Adjustment valve member 51 Plate-shaped valve body 52 Communication path F1 1st flow path F2 2nd flow path S1 1st valve seat S2 2nd valve seat G1 1st gap G2 2nd gap V1 1st valve body part V2 2nd valve body part P0-P5 Communication hole

Claims

作動流体を収容する筒体と、該筒体内を摺動するピストンと、該ピストンに接続するピストンロッドと、前記筒体内で前記ピストンを介して流動する作動流体を制御し減衰力を調整する減衰力調整機構とを備えた緩衝器において、前記減衰力調整機構は、前記筒体に連通する流路が形成され前記筒体に接合されるケースと、該ケース内で前記流路に設けられた弁座部材と、該弁座部材に着座するときに前記流路を遮断し、当該弁座部材から離座するときに前記流路を連通する弁部材と、該弁部材が前記弁座部材に着座する方向に付勢する付勢部材と、前記弁座部材と前記弁部材との間に介装され、前記弁部材に支持される調整弁部材とを備え、前記弁部材は、前記弁座部材の外側で対向するように形成された弁座部を有し、前記調整弁部材は、前記弁座部材及び前記弁座部に当接可能に配設され、前記弁座部材の内側で開口する連通路が形成された可撓性の板状弁体を有し、該板状弁体と前記弁座部によって第１の減衰部が構成されると共に、前記板状弁体と前記弁座部材によって第２の減衰部が構成され、初期位置においては前記板状弁体が前記弁座部及び前記弁座部材に当接した状態にあり、前記板状弁体が前記弁座部材から離座する方向への前記弁部材のストロークの増加に応じて、前記板状弁体が順次前記弁座部及び前記弁座部材から離座し、前記連通路、及び前記板状弁体と前記弁座部との間の第１の間隙を介して前記流路が連通して前記第１の減衰部が作動すると共に、前記板状弁体と前記弁座部材との間の第２の間隙を介して前記流路が連通して前記第２の減衰部が作動し、前記弁部材のストロークの増加に応じて前記流路の開口面積が増加するように設定されていることを特徴とする緩衝器。 Damping that adjusts damping force by controlling the working fluid that flows through the piston in the tubular body, a piston that slides in the tubular body, a piston rod that is connected to the piston, and a piston rod that is connected to the piston In the shock absorber provided with the force adjusting mechanism, the damping force adjusting mechanism is provided in the flow path in the case where a flow path communicating with the cylindrical body is formed and joined to the cylindrical body. A valve member, a valve member that blocks the flow path when seated on the valve seat member, and communicates the flow path when separated from the valve seat member; and the valve member is connected to the valve seat member An urging member for urging in a seating direction; and an adjusting valve member interposed between the valve seat member and the valve member and supported by the valve member, wherein the valve member includes the valve seat A valve seat portion formed so as to be opposed to the outside of the member; A flexible plate-like valve body that is disposed so as to be able to contact the valve seat member and the valve seat portion and has a communication passage that is open inside the valve seat member; And the valve seat portion constitutes a first damping portion, and the plate-like valve body and the valve seat member constitute a second damping portion, and in the initial position, the plate-like valve body is the valve seat. The plate-like valve elements are sequentially brought into contact with the valve-seat member according to an increase in the stroke of the valve member in a direction in which the plate-like valve element is separated from the valve-seat member. The first passage is separated from the valve seat portion and the valve seat member, and the flow path communicates with the first passage between the plate passage and the valve seat portion. While the attenuating portion is operated, the flow path is communicated through the second gap between the plate-like valve body and the valve seat member, and the second attenuating portion is Dynamic and shock absorber, characterized in that the opening area of the flow path is set so as to increase with an increase in the stroke of the valve member.

前記調整弁部材を構成する前記板状弁体は円板状に形成され、前記板状弁体の中央部から外周縁部に向かって変位量が増加するように、前記弁部材の底面に支持され、前記板状弁体の外周縁部の一方の面で前記弁座部に当接可能に配置されると共に、前記板状弁体の外周縁部の他方の面で前記弁座部材に当接可能に配置され、前記板状弁体の一方の面と前記弁座部との間に空隙が形成され、該空隙に連通するように前記連通路が前記板状弁体に形成されていることを特徴とする請求項１記載の緩衝器。 The plate-like valve body constituting the adjustment valve member is formed in a disk shape, and is supported on the bottom surface of the valve member so that the amount of displacement increases from the central part of the plate-like valve body toward the outer peripheral edge part. And is disposed so as to be able to contact the valve seat portion on one surface of the outer peripheral edge portion of the plate-shaped valve body, and against the valve seat member on the other surface of the outer peripheral edge portion of the plate-shaped valve body. It arrange | positions so that contact is possible, the space | gap is formed between the one surface of the said plate-shaped valve body, and the said valve seat part, and the said communicating path is formed in the said plate-shaped valve body so that it may connect with this space | gap. The shock absorber according to claim 1.

前記板状弁体に形成される前記連通路は、前記板状弁体の中央部から放射状に延出する少なくとも一つのスリット状に形成されていることを特徴とする請求項２記載の緩衝器。 The shock absorber according to claim 2, wherein the communication passage formed in the plate-shaped valve body is formed in at least one slit shape extending radially from a central portion of the plate-shaped valve body. .

前記弁部材に形成された前記弁座部の着座径は、前記弁座部材の着座径より大に設定されていることを特徴とする請求項２又は３記載の緩衝器。 The shock absorber according to claim 2 or 3, wherein a seating diameter of the valve seat portion formed on the valve member is set larger than a seating diameter of the valve seat member.