JPS58211038A - Hydraulic damper - Google Patents
Hydraulic damperInfo
- Publication number
- JPS58211038A JPS58211038A JP9536382A JP9536382A JPS58211038A JP S58211038 A JPS58211038 A JP S58211038A JP 9536382 A JP9536382 A JP 9536382A JP 9536382 A JP9536382 A JP 9536382A JP S58211038 A JPS58211038 A JP S58211038A
- Authority
- JP
- Japan
- Prior art keywords
- plate
- cylinder
- constant
- inner diameter
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- 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
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は液圧緩衝器とりわけピストンスピードが低い時
には略二次曲線的に減衰力が増大し、ピストンスピード
が所定値以上になると減衰力が漸増するようにした液圧
緩衝器に関し、特に前記略二次曲線的な立上り減衰特性
をも九せるためのコンスタントプレート及びプレートパ
ルプを改良することによフ減衰力特性の仕様に対する自
由度を犬にすることができるよりにしたものである。DETAILED DESCRIPTION OF THE INVENTION The present invention provides a hydraulic shock absorber in which the damping force increases in a substantially quadratic curve when the piston speed is low, and the damping force gradually increases when the piston speed exceeds a predetermined value. With regard to shock absorbers, by improving the constant plate and plate pulp in order to reduce the above-mentioned substantially quadratic rise damping characteristics, it is possible to increase the degree of freedom in specifying the damping force characteristics. This is what I did.
この種の液圧緩衝器は第１図に示す如く構成されている
。即ち、オイル等の作動液体が充填されたシリンダ１内
に、作動液体の制限的流通を許す、上下面の連通孔２と
該連通孔２を常時一部閉塞するグレートパルプ８とから
なる減衰力発生手段４を備えたピストン６を摺動自在に
嵌挿して、シリンダ１内部を上、下室６，７に隅取する
と共に、該シリンダ１の底部に、作動液体の制限的流通
を許す、上下面の連通孔８と該連通孔８を常時一部閉塞
するル−トパルプ９とからなる減衰力発生手段１０を備
えたボトムボディ１１を取付け、該ボトムボディ１１の
前記連通孔８を介して前記下室７と、シリンダ１および
該シリンダ１を囲繞する外筒１２の間に形成される作動
液体のリザーバ室１３とを連通させ、前記シリンｒ１の
頂部から前記ピストン５に固着され友ピストンロッド１
４を突出させることにより形成されている。１５゜１６
は前記ピストン５の上面およびボトムボディ１１の上面
に設けられ次環状突起、１７．１８は環状突起１５．１
６との間で前記プレートパルプ８又は９を挾持するパル
プリテーナ、１９．２０はパルプリテーナ１７．１８を
介してグレートパルプ８，９を環状突起１５．１６に軽
く押し付けているスプリング、２１．２２はスプリング
１９゜２０を取付けているスプリング受座、２８．２４
はスプリング受座２１．２２に設けられた液通路、２５
．２６はパルプリテーナ１７．１８に設けられ几液通孔
である。そして斯様な液圧緩衝器はピストンロッド１４
の端部を車体のばね上に、シリンダ１側をばね下に、そ
れぞれ固着することによ夕車両に装着されていて、ピス
トンロッド１４の低速の伸び行程では上室６内の作動液
体は前記スプリング受座２１に設けｔ液通路２８、パル
プリテーナ１７に設は几液通孔２５、コンスタントプレ
ー）８ｂの切欠３ ｍ、ピストン６の連通孔２を通り、
下室７内に流入し、作動液体が前記切欠８ａを通過する
際の流通抵抗によってピストン速度の増大に伴って略二
次曲線的に増加する減衰力を生じ、一方リザーバ室１３
内の作動液体はパルプリテーナ１８及びグレートパルプ
９をスズリング２０に抗して容易に押し上げてボトムボ
ディ１１の環状突起１６から離間させ、グレートパルプ
９とボトムボディ１１の隙間から下室７内に流入してピ
ストンロッド１４の退出体積を補償するよう忙なってい
ルト共にピストンロッド１４の高速の伸ヒ行程では第２
図Ａに示した如くプレートパルプ８を撓ませて、該ル−
トパルプ８とパルプリテーナ１７の間に作動液体の流路
２７ａを新九に形成して減衰力を漸増させるようになっ
ている。This type of hydraulic shock absorber is constructed as shown in FIG. That is, in the cylinder 1 filled with a working liquid such as oil, there is a damping force formed by a communication hole 2 on the upper and lower surfaces that allows limited circulation of the working liquid and a great pulp 8 that always partially closes the communication hole 2. A piston 6 equipped with a generating means 4 is slidably inserted into the cylinder 1 to corner the inside of the cylinder 1 into upper and lower chambers 6 and 7, and to allow limited flow of working fluid to the bottom of the cylinder 1. A bottom body 11 equipped with a damping force generating means 10 consisting of a communication hole 8 on the upper and lower surfaces and a root pulp 9 that always partially closes the communication hole 8 is attached, and a damping force generating means 10 is installed. The lower chamber 7 communicates with a reservoir chamber 13 for working fluid formed between the cylinder 1 and an outer cylinder 12 surrounding the cylinder 1, and a companion piston rod is fixed to the piston 5 from the top of the cylinder r1. 1
4 is formed by protruding. 15°16
17.18 is an annular projection 15.1 provided on the upper surface of the piston 5 and the upper surface of the bottom body 11.
A pulp retainer 19.20 holds the plate pulp 8 or 9 between the pulp retainer 17.18 and a spring 21.22 that lightly presses the great pulp 8, 9 against the annular protrusion 15.16 through the pulp retainer 17.18. 28.24 is the spring catch where the spring 19゜20 is attached.
are the liquid passages provided in the spring seats 21 and 22, and 25
．． 26 is a liquid passage hole provided in the pulp retainer 17, 18. And such a hydraulic shock absorber is a piston rod 14.
The end of the piston rod 14 is fixed to the spring of the vehicle body, and the cylinder 1 side is fixed to the bottom of the spring. A liquid passage 28 provided in the spring seat 21, a liquid passage hole 25 provided in the pulp retainer 17, a notch 3 m in the constant plate 8b, and a communication hole 2 in the piston 6.
The flow resistance when the working fluid flows into the lower chamber 7 and passes through the notch 8a generates a damping force that increases approximately quadratically as the piston speed increases, while the reservoir chamber 13
The working liquid inside easily pushes up the pulp retainer 18 and the great pulp 9 against the tin ring 20 to separate them from the annular protrusion 16 of the bottom body 11, and flows into the lower chamber 7 through the gap between the great pulp 9 and the bottom body 11. During the high speed extension stroke of the piston rod 14, the second
As shown in Figure A, bend the plate pulp 8 and
A working fluid flow path 27a is formed between the top pulp 8 and the pulp retainer 17 to gradually increase the damping force.
またピストンロッド１４の低速の圧縮行程では下室７内
の作動液体は前記スプリング受座２２に設けた液通孔”
）、 ４ 、ノ（Ｋブリテーカ１８に設けた？ｉ［［ａ
孔２Ｂ、 コンスタントグレー）９ｂの切欠９ａを通り
、リザーバ室１Ｂ内に流入し、作動液体が前記切欠９島
を通過する際の流通抵抗によって前記の伸び行程と同様
に減衰力を生じ、またピストンロッド１４の高速の圧縮
行程では第２図Ｂに示し九如くプレートパルプ９を撓ま
せて、該プレートパルプ９とパルプリテーナ１８の間に
作動流体の流路２７ｂを形成して減衰力を漸増させるよ
うになっている。なおピストンロッド１４の圧縮行程に
おいて下室７内の作動液体はパルプリテーナ１７及びプ
レートパルプ８をスプリング１９に抗して容易に押し上
げてピストン５の環状突起１６から離間させ、プレート
パルプ８とピストン６の隙間を介して上、下室６，７を
連通させるようになっている。Also, during the low-speed compression stroke of the piston rod 14, the working fluid in the lower chamber 7 flows through the fluid passage hole provided in the spring seat 22.
), 4, ノ(?i[[a
The working fluid flows through the notch 9a of the hole 2B (constant gray) 9b into the reservoir chamber 1B, and due to the flow resistance when the working fluid passes through the notch 9 island, a damping force is generated in the same way as in the extension stroke, and the piston During the high-speed compression stroke of the rod 14, the plate pulp 9 is bent as shown in FIG. It looks like this. In addition, during the compression stroke of the piston rod 14, the working fluid in the lower chamber 7 easily pushes up the pulp retainer 17 and the plate pulp 8 against the spring 19 and separates them from the annular projection 16 of the piston 5. The upper and lower chambers 6 and 7 are communicated through a gap.
ところで従来のル−トパルプ８，９は＠１図、第２図Ａ
１第２図Ｂおよび第８図に示したように内径側に切欠８
１・・・８ａ、９ｍ・・・９ｍを設けたリング状のコン
スタントプレー）８ｂ、９ｂの下１１１１に、前記切欠
径ＩＤよりも小さな内径Ｄ４のす／グ状のプレー）８ｅ
・・・３ｏ、９ｅ−Ｈ・９ｃを重ね合わせることにより
形成されてい几ためピストンロッド１４の低速移動時に
おいては、前記切欠８＆・・・３ｍ。By the way, conventional root pulps 8 and 9 are shown in Figure 1 and Figure 2A.
1. As shown in Fig. 2B and Fig. 8, there is a notch 8 on the inner diameter side.
1...8a, 9m...9m (ring-shaped constant play) 8b, below 9b (1111), a ring-shaped play (4) with an inner diameter D4 smaller than the notch diameter ID) 8e
... 3o, 9e-H and 9c are overlapped, and when the piston rod 14 moves at low speed, the notches 8 & . . 3 m are formed.
９ａ・・・９ａにより形成される作動液体の流路を通過
し、また高速移動時においては、該流路とプレートパル
プが撓むことによって生じる流路２７ａ。A flow path 27a that passes through the flow path of the working liquid formed by 9a...9a, and is created by the flow path and the plate pulp being bent during high-speed movement.
２７ｂとから、即ち、いずれもパルプ８，９の内周部か
らそのまま流入し、プレートパルプ３，９の下面近くで
過流を形成して異音発生の原因になるという欠点があっ
た。27b, that is, from the inner periphery of the pulps 8 and 9, and a turbulent flow is formed near the lower surfaces of the plate pulps 3 and 9, causing abnormal noise.
そこでプレートパルプ８，９を第４，５図に示したよう
に、外径側に切欠径がＤ鵞になるように切欠８ｄ・・・
８ｄ、９ｄ・・・９ｄを設けたリング状のコンスタント
グレートｏｅ 、９ｅを、前記切欠径り雪よりも不妊な
内径Ｄ３のリング状のアッパプレート８ｆ、９ｆと、前
記切欠径Ｄ１よりも大きな内径Ｄ４のリング状のロアグ
レー）８．．９．とで挟着して形成することにより前記
切欠８ｄ・・・８ｄ 、 ９ｄ・・・９ｄによジ作動液
体の流路をグレートパルプの外周部！７に形成して、ピ
ストンロッド１４の低速移動時における渦流の発生をな
くし異音の発生を防止し、ま几ピストンロッド１４の高
速移動時においてはグレートパルプ８，９が撓むことに
より、これらパルプ８，９とパルプリテーナ１７．１８
の間に形成される作動液体の流路２７ｍ、２７ｂと、前
記切欠８ ｄ ・８ ｄ 、 ９ ｄ ・９ ｄ Ｋ
Ｊ： ＃）形成される作動液体の流路を分離して、プレ
ートパルプ８，９の内周部と外周部とから作動液を流通
させて渦流の発生を防止してピストンロッド１４の高速
移動時における渦流が原因で起る異音の発生を防止する
よう圧した液圧緩衝器も開発されるに至つ友（例えば特
公昭４４−７７８２号）。Therefore, as shown in FIGS. 4 and 5, the plate pulps 8 and 9 have notches 8d...
A ring-shaped constant grate OE, 9e provided with 8d, 9d...9d is connected to a ring-shaped upper plate 8f, 9f having an inner diameter D3 that is smaller than the cutout diameter, and an inner diameter larger than the cutout diameter D1. D4 ring-shaped lower gray)8. ．． 9. By sandwiching and forming the flow path of the working liquid through the notches 8d...8d, 9d...9d, the outer periphery of the great pulp! 7 to eliminate the generation of vortices and prevent the generation of abnormal noise when the piston rod 14 moves at low speed, and when the piston rod 14 moves at high speed, the grate pulps 8 and 9 are bent. Pulp 8, 9 and pulp retainer 17.18
Working liquid flow paths 27m and 27b formed between the notches 8d and 8d, 9d and 9dK
J: #) The flow path of the working liquid that is formed is separated and the working liquid is allowed to flow from the inner and outer circumferences of the plate pulps 8 and 9 to prevent the generation of vortices and allow the piston rod 14 to move at high speed. Hydraulic shock absorbers were also developed to prevent abnormal noises caused by eddy currents (for example, Japanese Patent Publication No. 7782/1983).
ところが従来は第４図に示した如くロアプレー）８ｇ
、９ｇの内径Ｄ４を環状突起１５．１８の内径１）Ｉと
略同径に形成してい次ため、これらロアプＬ’−ト８ｇ
、９ｇはピストンロッド１４の高速移動時においても撓
むことなく、従ってル−トパルプ８，９の減衰力特性の
仕様に対しては如何なる影響力も持たなかった。前記の
如く四アブレート８ ｇ ＋ ９ ｇの内径を環状突起
１５．１８の内径と略同径に形成した理由は従来のプレ
ートパルプ８．９においてロアル−） ８ ｇ ＋ ９
ｇ社、専ら切欠８ｄ−１・８ｄ、９ｄ・・・９ｄを流
通する作動液体により環状突起１５．１６が摩耗するの
を防ぐことを目的として使用されておシ、このような目
的を達成するためには前記した如くロアプレート８、．
９ｇを環状突起１５．１６と略同径、同幅のリング状に
形成すればそれで充分だからである。However, conventionally, as shown in Figure 4, the lower play) 8g
, the inner diameter D4 of 9g is formed to be approximately the same diameter as the inner diameter 1) I of the annular projection 15.18.
, 9g did not bend even when the piston rod 14 moved at high speed, and therefore did not have any influence on the specifications of the damping force characteristics of the root pulps 8 and 9. As mentioned above, the reason why the inner diameter of the four ablate 8g + 9g is approximately the same as the inner diameter of the annular protrusion 15.18 is that in the conventional plate pulp 8.9, the inner diameter of the four ablate 8g + 9g
Company G is used exclusively for the purpose of preventing the annular projections 15, 16 from being worn out by the working fluid flowing through the notches 8d-1, 8d, 9d...9d, and achieves this purpose. For this purpose, lower plate 8, .
This is because it is sufficient to form 9g into a ring shape having approximately the same diameter and width as the annular protrusion 15.16.
本発明はロアグレー） ８ ｇ ＋ ９ ｇに、前記環
状突起１５．１６の摩耗防止機能の外に、プレートバル
ブ８，９の減衰力特性決定への影響力（減衰力特性決定
への関与機能）を持几せると共に、コンスタントプレー
）Ｂ＠、９＠の切欠８ｄ・・・８ｄ。In addition to the wear prevention function of the annular projections 15 and 16, the present invention has an influence on the damping force characteristic determination of the plate valves 8 and 9 (a function involved in the damping force characteristic determination). and constant play) B@, 9@ notch 8d...8d.
９ｄ・・・９ｄとアッパプレー）８ｆ 、９ｆの下面と
、ロアグレート８．．９ｇの上面とで形成される流路を
可及的に長く形成して流体の整流化を促進し、異音の発
生をよシ効果的に防止することを目的として為され次も
のであ、す、その要旨とする構成は第６図以下の図面に
示したよう忙ロアプレート８ｇｐ９ｇの内径Ｄ４を環状
突起１５．１６の内径Ｄ１よりも小径に形成し次ことに
ある・図面に示す実施例においてロアプレート８ｇ。9d...9d and upper play) 8f, the lower surface of 9f, and lower grade 8. ．． The purpose of this is to make the flow path formed by the upper surface of 9g as long as possible to promote rectification of the fluid and to more effectively prevent the generation of abnormal noise. The gist of the structure is that the inner diameter D4 of the busy lower plate 8gp9g is made smaller than the inner diameter D1 of the annular projection 15.16 as shown in the drawings from FIG. 6 onwards. Lower plate 8g.
９ｇの内径Ｄ４を環状突起１５．１６の内径Ｄ１よりも
小径に形成したこと以外は第４，６図に示した従来例の
場合と全く同様に、外径側に切欠８ｄ・・・８ｄ 、９
ｄ・・・９ｄを設は次リング状コンスタントグレート８
・、９・を、前記切欠径Ｄ！よりも小さな内径Ｄ３のリ
ング状アッパプレート８１．９１と、前記切欠径Ｄ！よ
りも大きな内径Ｄ４のリング状四アグレー）８．．９．
とで挾着することにより形成でれている。Except that the inner diameter D4 of 9g is smaller than the inner diameter D1 of the annular projection 15.16, it is exactly the same as the conventional example shown in FIGS. 9
d...9d is set as the next ring-shaped constant grating 8
. , 9. is the notch diameter D! The ring-shaped upper plate 81.91 has an inner diameter D3 smaller than the notch diameter D! 8. ．． 9.
It is formed by clamping it with.
従ツＣＵ７７レー ） ８ ｇ 、 ９ ｇｔ！ＤＩ−
８４＝ａｆｅけ環状突起１５．１６の内径側に突出して
、該突出部分が所謂撓み代になシ、ピストンロッド１４
の高速移動時にコンスタントグレート８・、９ｅ４ｐ
７ ツ／＜１１／−）８ｆ、９ｆと共に撓んでこれらコ
ンスタントグレー）８ｅ、９ｅやアッパル−）８ｆ 、
９ｆと同様にプレートバルブ８．９の減衰力特性決定の
要素となると共にコンスタントグレート８・、９ｅとア
ッパプレー）８ｆ 、９ｆとの間に挾着するロアグレー
ト８ ｇ ｔ ９ ｇ Ｏ内径Ｄ’を小さくしたために
切欠８ｄ・・・８ｄ、９ｄ・・・９ｄによる流路を長く
形成することができ、異音の発生を更に効果的に防止で
きるのである。なお従来と同一部分には同一符号を付し
て重複する説明を省略する。Subordinate CU77 race) 8 g, 9 gt! DI-
84 = afe protruding to the inner diameter side of the annular protrusion 15, 16, the protruding portion is not a so-called bending allowance, the piston rod 14
Constant Great 8・, 9e4p when moving at high speed
7/<11/-) 8f, 9f and these constant gray) 8e, 9e and upper-) 8f,
Similarly to 9f, the lower grating 8 is a factor in determining the damping force characteristics of the plate valve 8.9, and is also clamped between the constant grating 8, 9e and the upper play (8f, 9f). Since the notches 8d...8d and 9d...9d are made smaller, the flow paths can be formed longer, and the generation of abnormal noise can be more effectively prevented. Note that parts that are the same as those in the prior art are designated by the same reference numerals and redundant explanations will be omitted.
以上説明し友ように本発明は作動液体が充填されたシリ
ンダ内に、作動液体の制限的流通を許す、上下面の連通
孔と、該連通孔を常時閉塞するプレートバルブとからな
る減衰力発生手段を備えたピストンを摺動自在に嵌挿し
て、シリンダ内部を上。As explained above, the present invention generates a damping force by forming a communication hole on the upper and lower surfaces that allows limited circulation of the working liquid in a cylinder filled with the working liquid, and a plate valve that constantly closes the communicating hole. A piston equipped with means is slidably inserted into the cylinder, and the inside of the cylinder is lifted up.
下室に隔成すると共に該シリンダの底部に、作動液体の
制限的流通を許す、上下面の連通孔と該連通孔を常時閉
塞するプレートバルブとからなる減衰力発生手段を備え
たボトムボディを取付け、該ボトムボディの前記連通孔
を介して前記下室と、シリンダおよび該シリンダを囲繞
する外筒の間に形成される作動液体のリザーバ室とを連
通させ、前記シリンダの頂部から前記ピストンに固着さ
れ次ピストンロンドを突出させてなる液圧緩衝器におい
て、前記プレートバルブを、外径側に切欠を設けたリン
グ状コンスタントプレートと、該コンスタンドプレート
の切欠径よりも小さな内径のリング状アッパプレートと
、前記コンスタントグレートの切欠径よりも大きな内径
に形成されていてｌｅアッパプレートとの間で前記コン
スタントグレートを挟着しているリング状ロアグレート
七で構成すると共に、該ロアグレートの内径を、ピスト
ンおよびボトムボディの上面に設けた環状突起よシも小
径に形成したのでロアプレートは環状突起の摩耗防止機
能、異音発生防止機能はもとよジ、減衰力特性決定への
関与機能を持ち、プレートパルプの減衰力特性の仕様に
対する自由度を大とすることができるという実用上優れ
た効果がある。A bottom body is provided at the bottom of the cylinder, which is separated from the lower chamber and is equipped with a damping force generating means consisting of a communication hole on the upper and lower surfaces and a plate valve that always closes the communication hole, which allows limited flow of the working fluid. mounting, communicating the lower chamber through the communication hole of the bottom body with a reservoir chamber for a working fluid formed between a cylinder and an outer cylinder surrounding the cylinder, and connecting the piston from the top of the cylinder. In a hydraulic shock absorber which is fixed and has a protruding piston rond, the plate valve is formed by a ring-shaped constant plate having a notch on the outer diameter side, and a ring-shaped upper part having an inner diameter smaller than the notch diameter of the constant plate. The plate and the ring-shaped lower grating 7 are formed to have an inner diameter larger than the notch diameter of the constant grate and sandwich the constant grate between the upper plate, and the inner diameter of the lower grate is The annular protrusions on the top surface of the piston and bottom body are also made to have a small diameter, so the lower plate not only has the function of preventing wear of the annular protrusions and the generation of abnormal noise, but also has the function of contributing to the determination of damping force characteristics. This has the advantageous practical effect of increasing the degree of freedom in specifying the damping force characteristics of plate pulp.
第１図は従来の液圧緩衝器の断面図、第２図Ａ及び第２
図Ｂは同、プレートパルプが撓んだ状態の断面図、第８
図は第・１図、第２図Ａ１第２図Ｂの液圧緩衝器のプレ
ートパルプを構成する内径側に切欠を設けたコンスタン
トグレートとロアグレートの平面図、第４図は外径側に
切欠を設けたコンスタントプレートを使用した従来の液
圧緩衝器の断面図、＠５図は第４図の液圧緩衝器のプレ
ートパルプを構成する外径側に切欠を設は几コンスタン
トプレートとアッパグレートおよびロアプレートの平面
図、第６図は本発明の液圧緩衝器の断面図、第７図は第
６図のピストン部分の拡大図、第８図は同ボトムボディ
部分の拡大図、第９図は第７図のＩＸ−ＩＸ線断面図で
ある。
１・・・シリンダ、２・・・連通孔、３・・・グレート
パル７”、８ｄ・・・切欠、 ８ ｅ・・・コンスタン
トグレート、８ｆ・・・アッパグレート、８ｇ・・・ロ
アグレート、４・・・減衰力発生手段、５・・・ピスト
ン、６，７・・・上。
下室、８・・・連通孔、９・・・プレートノ（ルプ、９
ｄ・・・切欠、９・・・・コンスタントグレート、９ｆ
・・・アッパル−Ｆｓ９ｇ・・・ロアグレート、１０・
・・減衰力発生手段、１１・・・ボトムボディ、１２・
・・外筒、１８・・・ＩＪ ｆ−バ室、１４・・・ピス
トン部分ド、 １７５．１６・・・環状突起。
第１図Figure 1 is a sectional view of a conventional hydraulic shock absorber, Figure 2 A and 2
Figure B is a cross-sectional view of the plate pulp in a bent state.
The figure is a plan view of the constant grate and lower grate with notches on the inner diameter side that make up the plate pulp of the hydraulic shock absorber shown in Fig. 1, Fig. 2 A1, Fig. 2 B, and Fig. 4 is a plan view of the constant grate and lower grate with notches on the inner diameter side. A cross-sectional view of a conventional hydraulic shock absorber using a constant plate with a notch. 6 is a sectional view of the hydraulic shock absorber of the present invention; FIG. 7 is an enlarged view of the piston portion of FIG. 6; FIG. 8 is an enlarged view of the bottom body portion of the same; FIG. 9 is a sectional view taken along the line IX-IX in FIG. 7. 1...Cylinder, 2...Communication hole, 3...Grate pal 7", 8d...Notch, 8e...Constant grade, 8f...Upper grade, 8g...Lower grade, 4... Damping force generating means, 5... Piston, 6, 7... Upper. Lower chamber, 8... Communication hole, 9... Plate no.
d...Notch, 9...Constant great, 9f
...Uppal-Fs9g...Lower Great, 10.
... damping force generating means, 11 ... bottom body, 12.
...Outer cylinder, 18...IJ f-bar chamber, 14...Piston portion door, 175.16...Annular projection. Figure 1
Claims (1)
体の制限的流通を許す、上下面の連通孔と、該連通孔を
常時閉塞するプレートバルブとからなる減衰力発生手段
を備えたピストンを摺動自在に嵌挿してシリンダ内部を
上、下室に隔成すると共に、同じく、該シリンダの底部
に、作動液体の制限的流通を許す、上下面の連通孔と、
咳連通孔を常時閉塞するプレートバルブとからなる減衰
力発生手段を備えたボトムボディを取付け、核ボトムボ
ディの前記連通孔を介して前記下室と、シリンダおよび
該シリンダを囲繞する外筒の間に形成される作動液体の
リザーバ室とを連通させ、前記シリンダの頂部から前記
ピストンに固着されたピストンロンドを突出させてなる
液圧緩衝器において、前記プレートバルブを、外径側に
切欠を設けたリング状のコンスタントル−トと、該コン
スタントプレートの切欠径よりも小場な内径のリング状
のアッパプレートと、前記コンスタントスレートの切欠
径よりも大きな内径に形成されていて前記アッパグレー
トとの間で前記コンスタン） ’；’ｌ／−）を挟着し
ているリング状のロアグレートとで構成すると共に、核
ロアプレートの内径を、ピストンおよびボトムボディの
上面に設は皮環状突起よりも小径に形成したことを特徴
とする液圧緩衝器。(1) A piston is provided with a damping force generating means consisting of a communication hole on the upper and lower surfaces, which allows limited flow of the working liquid, and a plate valve that constantly closes the communicating hole, in a cylinder filled with working liquid. a communication hole on the upper and lower surfaces that is slidably inserted to separate the inside of the cylinder into upper and lower chambers, and also at the bottom of the cylinder that allows limited flow of the working fluid;
A bottom body equipped with a damping force generating means consisting of a plate valve that constantly closes the cough communication hole is attached, and the space between the lower chamber and the cylinder and the outer cylinder surrounding the cylinder is provided through the communication hole of the core bottom body. In the hydraulic shock absorber, the plate valve is provided with a notch on the outer diameter side in the hydraulic shock absorber, which communicates with a reservoir chamber for working fluid formed in the cylinder, and has a piston rod fixed to the piston protrude from the top of the cylinder. a ring-shaped constant root, a ring-shaped upper plate having an inner diameter smaller than the notch diameter of the constant plate, and a ring-shaped upper plate having an inner diameter larger than the notch diameter of the constant slate, which is connected to the upper plate. It consists of a ring-shaped lower plate sandwiching the above-mentioned Constant) ';'l/-) between them, and the inner diameter of the nuclear lower plate is set on the upper surface of the piston and bottom body so that it is smaller than the skin annular projection. A hydraulic shock absorber characterized by being formed with a small diameter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9536382A JPS58211038A (en) | 1982-06-02 | 1982-06-02 | Hydraulic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9536382A JPS58211038A (en) | 1982-06-02 | 1982-06-02 | Hydraulic damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58211038A true JPS58211038A (en) | 1983-12-08 |
Family
ID=14135541
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9536382A Pending JPS58211038A (en) | 1982-06-02 | 1982-06-02 | Hydraulic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58211038A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6161344U (en) * | 1984-09-28 | 1986-04-25 | ||
| JPS6187242U (en) * | 1984-11-13 | 1986-06-07 | ||
| JPS6297337U (en) * | 1985-12-09 | 1987-06-20 | ||
| JPS63210429A (en) * | 1987-02-24 | 1988-09-01 | Kayaba Ind Co Ltd | Shock absorber |
| JPS63160456U (en) * | 1987-04-09 | 1988-10-20 | ||
| FR2747451A1 (en) * | 1996-04-10 | 1997-10-17 | Trw Fahrwerksyst Gmbh & Co | SHOCK ABSORBING VALVE |
| EP1860341A2 (en) | 2006-05-24 | 2007-11-28 | Koni B.V. | Nonreturn valve for a shock absorber |
| US20130257011A1 (en) * | 2012-03-27 | 2013-10-03 | Showa Corporation | Damping force generator for hydraulic shock absorber |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5088476A (en) * | 1973-10-12 | 1975-07-16 | ||
| JPS514467A (en) * | 1974-06-28 | 1976-01-14 | Tokico Ltd | Kanshokino gensuiryokuhatsuseisochi |
| JPS5495872A (en) * | 1978-01-13 | 1979-07-28 | Kayaba Ind Co Ltd | Damping force generating system for hydraulic buffer |
-
1982
- 1982-06-02 JP JP9536382A patent/JPS58211038A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5088476A (en) * | 1973-10-12 | 1975-07-16 | ||
| JPS514467A (en) * | 1974-06-28 | 1976-01-14 | Tokico Ltd | Kanshokino gensuiryokuhatsuseisochi |
| JPS5495872A (en) * | 1978-01-13 | 1979-07-28 | Kayaba Ind Co Ltd | Damping force generating system for hydraulic buffer |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6161344U (en) * | 1984-09-28 | 1986-04-25 | ||
| JPH043138Y2 (en) * | 1984-11-13 | 1992-01-31 | ||
| JPS6187242U (en) * | 1984-11-13 | 1986-06-07 | ||
| JPS6297337U (en) * | 1985-12-09 | 1987-06-20 | ||
| JPS63210429A (en) * | 1987-02-24 | 1988-09-01 | Kayaba Ind Co Ltd | Shock absorber |
| JPH0517465Y2 (en) * | 1987-04-09 | 1993-05-11 | ||
| JPS63160456U (en) * | 1987-04-09 | 1988-10-20 | ||
| FR2747451A1 (en) * | 1996-04-10 | 1997-10-17 | Trw Fahrwerksyst Gmbh & Co | SHOCK ABSORBING VALVE |
| EP1860341A2 (en) | 2006-05-24 | 2007-11-28 | Koni B.V. | Nonreturn valve for a shock absorber |
| NL1031880C2 (en) * | 2006-05-24 | 2007-11-30 | Koni Bv | One-way valve for a shock absorber. |
| EP1860341A3 (en) * | 2006-05-24 | 2007-12-12 | Koni B.V. | Nonreturn valve for a shock absorber |
| US7766137B2 (en) | 2006-05-24 | 2010-08-03 | Koni B.V. | Nonreturn valve for a shock absorber |
| US20130257011A1 (en) * | 2012-03-27 | 2013-10-03 | Showa Corporation | Damping force generator for hydraulic shock absorber |
| CN103363009A (en) * | 2012-03-27 | 2013-10-23 | 株式会社昭和 | Damping force generator for hydraulic shock absorber |
| US9022186B2 (en) * | 2012-03-27 | 2015-05-05 | Showa Corporation | Damping force generator for hydraulic shock absorber |
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