JPH0425546Y2 - - Google Patents
Info
- Publication number
- JPH0425546Y2 JPH0425546Y2 JP1986113916U JP11391686U JPH0425546Y2 JP H0425546 Y2 JPH0425546 Y2 JP H0425546Y2 JP 1986113916 U JP1986113916 U JP 1986113916U JP 11391686 U JP11391686 U JP 11391686U JP H0425546 Y2 JPH0425546 Y2 JP H0425546Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- slit
- oil chamber
- slit valve
- 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.)
- Expired
Links
- 239000003921 oil Substances 0.000 claims description 42
- 239000010720 hydraulic oil Substances 0.000 claims description 13
- 238000013016 damping Methods 0.000 claims description 7
- 239000006096 absorbing agent Substances 0.000 claims description 5
- 230000035939 shock Effects 0.000 claims description 5
- 230000000694 effects Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Fluid-Damping Devices (AREA)
Description
【考案の詳細な説明】
（産業状の利用分野）
本考案はスリツトバルブを組込んだ減衰力発生
用のバルブ機構に関する。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a valve mechanism for generating damping force incorporating a slit valve.
（従来の技術）
油圧緩衝器内に設ける減衰力発生用のバルブ機
構として内周側又は外周側にスリツト（オリフイ
ス）を切欠した板状のスリツトバルブを組込んだ
ものが知られている。具体的な構造を第７図に基
いて説明すると、シリンダ１００内にピストンロ
ツド１０１を上方から挿入し、このピストンロツ
ド１０１下端にシリンダ１００内周面に摺接する
ピストン１０２を取付け、このピストン１０２上
方のピストンロツド１０１外周にカラー１０３及
びストツパ１０４を嵌着し、ストツパ１０４とピ
ストン１０２との間にバルブケース１０５を設
け、このバルブケース１０５内に下方から順次ス
リツト１０６ａを外周に形成したスリツトバルブ
１０６、板バルブ１０７、フリーピストン１０８
及びスプリング１０９を組込み、スプリング１０
９を組込み、スプリング１０９の弾発力にてスリ
ツトバルブ１０６下面をピストン１０２上部に設
けたバルブシート１１０に当接せしめている。(Prior Art) As a valve mechanism for generating damping force provided in a hydraulic shock absorber, one incorporating a plate-shaped slit valve with a slit (orifice) cut out on the inner or outer circumference side is known. The specific structure will be explained based on FIG. 7. A piston rod 101 is inserted into the cylinder 100 from above, a piston 102 that slides on the inner peripheral surface of the cylinder 100 is attached to the lower end of the piston rod 101, and the piston rod above the piston 102 is attached to the lower end of the piston rod 101. A collar 103 and a stopper 104 are fitted on the outer periphery of 101, a valve case 105 is provided between the stopper 104 and the piston 102, and slit valves 106 and plate valves 107 are formed in this valve case 105 with slits 106a sequentially formed on the outer periphery from the bottom. , free piston 108
and spring 109 are assembled, and spring 10
9 is assembled, and the lower surface of the slit valve 106 is brought into contact with a valve seat 110 provided above the piston 102 by the elastic force of a spring 109.
而して、伸び工程においてピストンロツド１０
２が低速で上昇する場合には、ピストン１０２上
方の油室内の圧力によつて板バルブ１０７は撓ま
ず、矢印ａに示すようにスリツト１０６ａの部分
を通つて作動油は流れる。そして、ピストン速度
が中、高速域になると、ピストン上方の油室内の
圧力が高まり、第８図に示すように板バルブ１０
７及びスリツトバルブ１０６が撓み、矢印ａ，ｂ
に示す経路で作動油が流れる。 Therefore, in the elongation process, the piston rod 10
2 rises at a low speed, the plate valve 107 is not bent by the pressure in the oil chamber above the piston 102, and the hydraulic oil flows through the slit 106a as shown by arrow a. When the piston speed reaches a medium or high speed range, the pressure inside the oil chamber above the piston increases, and as shown in FIG.
7 and the slit valve 106 are bent, arrows a and b
Hydraulic oil flows through the path shown in .
（考案が解決しようとする問題点）
上述した従来のバルブ構造にあつては、ピスト
ン低速域において、高圧の油室から低圧の油室へ
スリツトを介して作動油が流れる。そして、この
ときピストン上下の油室の圧力差が大きいため、
バルブの部分において作動油が泡立ち（キヤビテ
ーシヨン現象）、所謂スイツシユ音と称する騒音
を発生する。(Problems to be Solved by the Invention) In the conventional valve structure described above, hydraulic oil flows from the high pressure oil chamber to the low pressure oil chamber through the slit in the low piston speed range. At this time, since there is a large pressure difference between the oil chambers above and below the piston,
Hydraulic oil bubbles in the valve area (cavitation phenomenon), producing a so-called swiss noise.
（問題点を解決するための手段）
上記問題点を解決すべく本考案は、スリツトバ
ルブを組込んだバルブ構造において、スリツトバ
ルブが当接するバルブシートの一部に減衰力を発
生しているときに高圧となる油室と低圧となる油
室の中間の圧力を生じて高圧の油室との差圧を小
さく抑える中間室を形成した。(Means for Solving the Problems) In order to solve the above problems, the present invention provides a valve structure incorporating a slit valve, in which high pressure is generated when a damping force is generated in a part of the valve seat that the slit valve contacts. An intermediate chamber was created to generate a pressure between the oil chamber with high pressure and the oil chamber with low pressure, thereby suppressing the differential pressure between the high pressure oil chamber and the high pressure oil chamber.
（作用）
作動油が高圧の油室から低圧の油室に流れる途
中で、中間圧室を通るため、圧力差が小さくな
り、キヤビテーシヨン現象が抑制されスイツシユ
音も発生しない。(Function) Since the hydraulic oil passes through an intermediate pressure chamber on the way from the high pressure oil chamber to the low pressure oil chamber, the pressure difference is reduced, the cavitation phenomenon is suppressed, and no swishing noise is generated.
（実施例）
以下に本考案の実施例を添付図面に基いて説明
する。(Example) An example of the present invention will be described below based on the accompanying drawings.
第１図は本考案に係るバルブ機構を適用した油
圧緩衝器の下部の縦断面図、第２図は第１図の要
部拡大図であり、緩衝器はアウターシリンダ１の
底部をボトムキヤツプ２によつて閉塞し、このボ
トムキヤツプ２にインナーシリンダ３の底部を固
着し、このインナーシリンダ３内に上方からピス
トンロツド４を挿入し、このピストンロツド４下
端に固着したピストン５をインナーシリンダ３内
周面に摺接せしめ、ピストン５によつてインナー
シリンダ３内を上部油室S1及び下部油室S2に画成
し、下部油室S2とアウターシリンダ１及びインナ
ーシリンダ３間の油溜り室S3とをボトムキヤツプ
２に穿設した油孔６にて連通している。 FIG. 1 is a longitudinal sectional view of the lower part of a hydraulic shock absorber to which the valve mechanism according to the present invention is applied, and FIG. 2 is an enlarged view of the main part of FIG. The bottom of the inner cylinder 3 is fixed to the bottom cap 2, the piston rod 4 is inserted from above into the inner cylinder 3, and the piston 5 fixed to the lower end of the piston rod 4 is attached to the inner peripheral surface of the inner cylinder 3. The inside of the inner cylinder 3 is defined by the piston 5 into an upper oil chamber S 1 and a lower oil chamber S 2 , and an oil sump chamber S between the lower oil chamber S 2 and the outer cylinder 1 and the inner cylinder 3. 3 through an oil hole 6 drilled in the bottom cap 2.
また、ピストン５上部には減衰力発生用のバル
ブ機構７を、インナーシリンダ３底部にはボトム
バルブ機構８を設けている。 Further, a valve mechanism 7 for generating damping force is provided at the top of the piston 5, and a bottom valve mechanism 8 is provided at the bottom of the inner cylinder 3.
バルブ機構７は第２図に示す如く、ピストン５
上方のピストンロツド４外周にカラー９及びスト
ッパ１０を嵌着し、ストツパ１０とピストン５の
間にバルブケース１１を設け、このバルブケース
１１内に下方から順次スリツトバルブ１２、板バ
ルブ１３、フリーピストン１４及びスプリング１
５を組込み、スプリング１５の弾発力でスリツト
バルブ１２下面をピストン５上部のバルブシート
１６に当接している。ここで、スリツトバルブ１
２は第３図に示すように外周部に等間隔でスリツ
ト１２ａ…を形成しており、またスリツトバルブ
１２下面を支持するバルブシート１６の内周部に
は起立部１７を設け、この起立部１７外側の凹部
をピストンが摺動する際に上部油室S1と下部油室
S2の油圧の中間の圧力となる中間圧室S4としてい
る。 The valve mechanism 7 has a piston 5 as shown in FIG.
A collar 9 and a stopper 10 are fitted around the outer circumference of the upper piston rod 4, a valve case 11 is provided between the stopper 10 and the piston 5, and a slit valve 12, a plate valve 13, a free piston 14, and a valve case 11 are disposed in order from below. Spring 1
5 is assembled, and the lower surface of the slit valve 12 is brought into contact with the valve seat 16 above the piston 5 by the elastic force of the spring 15. Here, slit valve 1
As shown in FIG. 3, slits 12a are formed at equal intervals on the outer periphery of the valve seat 16, and an upright portion 17 is provided on the inner periphery of the valve seat 16 that supports the lower surface of the slit valve 12. When the piston slides in the outer recess, the upper oil chamber S1 and the lower oil chamber
The intermediate pressure chamber S4 has a pressure between the hydraulic pressure of S2 .
更に、ピストンが静止している状態では、スリ
ツトバルブ１２下面と起立部１７上面との間隔
G1は板バルブ１３上面とフリーピストンロツド
１４の外側下面との間隔G2よりも大となるよう
に設定されている。具体的には隙間G1を0.24乃至
0.34mmとし、隙間G2を約0.14mmとする。このよう
に設定すると、隙間G1，G2の差が0.1〜0.2mmと大
きいため、低速域から中速域にかけて作動油が中
間圧室S4を通るのでスイツシユ音の発生は有効に
阻止される。 Furthermore, when the piston is stationary, the distance between the lower surface of the slit valve 12 and the upper surface of the upright portion 17 is
G1 is set to be larger than the distance G2 between the upper surface of the plate valve 13 and the outer lower surface of the free piston rod 14. Specifically, the gap G1 is 0.24 to
The gap is 0.34 mm, and the gap G 2 is approximately 0.14 mm. With this setting, since the difference between the gaps G 1 and G 2 is as large as 0.1 to 0.2 mm, the hydraulic oil passes through the intermediate pressure chamber S 4 from the low speed range to the medium speed range, effectively preventing the swishing noise from occurring. Ru.
以上の如き構成からなるバルブ機構の作用を第
４図及び第５図に基いて説明する。先ずピストン
ストローク速度が低速の場合の伸び行程にあつて
は、上部油室S1の圧力により第４図に示すように
フリーピストン１４が相対的に下動し、フリーピ
ストン１４の内周部にて板バルブ１３及びスリツ
トバルブ１２の内周部を下方に撓ませる。しかし
ながらスリツトバルブ１２の内部部下面を起立部
１７上面に当接するに至らず、上部油室S1の作動
油は矢印ａで示すように、バルブケース１１の隙
間、スリツト１２ａ、中間圧室S4，及びピストン
５の油孔を通つて下部油室S2内に流入する。 The operation of the valve mechanism constructed as described above will be explained based on FIGS. 4 and 5. First, in the extension stroke when the piston stroke speed is low, the free piston 14 moves relatively downward due to the pressure in the upper oil chamber S1 as shown in FIG. The inner circumferential portions of the plate valve 13 and the slit valve 12 are bent downward. However, the inner lower surface of the slit valve 12 does not come into contact with the upper surface of the upright portion 17, and the hydraulic oil in the upper oil chamber S 1 flows through the gap in the valve case 11, the slit 12a, the intermediate pressure chamber S 4 , as shown by arrow a. and flows into the lower oil chamber S2 through the oil hole of the piston 5.
そしてこの時、中間圧室S4内の圧力は上部油室
S1及び下部油室S2内の圧力の中間圧となるため、
作動油がバルブ機構の部分を通過する際にキユビ
テーシヨン現象は生じにくく、スイツシユ音の発
生もない。 At this time, the pressure in the intermediate pressure chamber S4 is reduced to the upper oil chamber.
Since the pressure is intermediate between the pressure in S 1 and the pressure in the lower oil chamber S 2 ,
When the hydraulic oil passes through the valve mechanism, the cubitation phenomenon is less likely to occur, and there is no swishing noise.
更にピストンストローク速度が中高速域となる
と、上部油室S1の圧力が更に高くなり、板バルブ
１３及びスリツトバルブ１２は第５図に示すよう
に下方に撓み、作動油は前述の矢印ａで示す流れ
と、矢印ｂに示すようにバルブケース１１の隙
間、フリーピストン１４の油孔１４ａ及びピスト
ン５の油孔５ａを通つて下部油室S2内に流入す
る。 Furthermore, when the piston stroke speed reaches a medium to high speed range, the pressure in the upper oil chamber S1 becomes even higher, and the plate valve 13 and the slit valve 12 are bent downward as shown in FIG. The oil flows into the lower oil chamber S2 through the gap in the valve case 11, the oil hole 14a of the free piston 14, and the oil hole 5a of the piston 5, as shown by arrow b.
一方ボトムバルブ機構８も前記バルブ機構７と
同様に、ボトムキヤツプ２上にバルブケース１８
を設け、このバルブケース１８内に下方から順次
スリツトバルブ１９、板バルブ２０、フリーピス
トン２１及びスプリング２２を組込み、更にスリ
ツトバルブ１９下面が当接するバルブシート２３
には前記同様の中間圧室S5を形成している。 On the other hand, like the valve mechanism 7, the bottom valve mechanism 8 also has a valve case 18 on the bottom cap 2.
A slit valve 19, a plate valve 20, a free piston 21, and a spring 22 are sequentially assembled into the valve case 18 from below, and a valve seat 23 is provided, which the lower surface of the slit valve 19 comes into contact with.
An intermediate pressure chamber S5 similar to that described above is formed in the chamber.
尚、ボトムバルブ機構８にあつては、圧縮行程
の場合にスリツトバルブ１９がバルブシート２３
に押付けられ、この場合に油室S3内の作動油がバ
ルブケース１８の隙間、スリツトバルブ１９のス
リツト、中間圧室S5及び油孔６を介して油溜室S3
内に流入し、このとき中間圧室S5の存在によりキ
ヤビテーシヨン及びスイツシユ発生が抑制され
る。第６図は別実施例のバルブ機構を示す断面図
であり、この実施例にあつてはピストン５上面内
周部に前記実施例の如き起立部１７を形成せず、
段部２４を形成し、この段部２４とスリツトバル
ブ１２との間を中間圧室S4としている。このよう
な構成としても前記同様の作用をなす。 In the case of the bottom valve mechanism 8, the slit valve 19 is connected to the valve seat 23 during the compression stroke.
In this case, the hydraulic oil in the oil chamber S3 flows through the gap in the valve case 18, the slit in the slit valve 19, the intermediate pressure chamber S5 , and the oil hole 6 into the oil reservoir chamber S3.
At this time, the existence of the intermediate pressure chamber S5 suppresses cavitation and swishing. FIG. 6 is a sectional view showing a valve mechanism of another embodiment. In this embodiment, the upright portion 17 as in the previous embodiment is not formed on the inner circumferential portion of the upper surface of the piston 5.
A step 24 is formed, and an intermediate pressure chamber S4 is formed between the step 24 and the slit valve 12. Even with such a configuration, the same effect as described above is achieved.
（考案の効果）
以上に説明したように本考案に係るバルブ機構
によれば、減衰力を発生せしめるべく高圧の油室
から低圧の油室にバルブ機構の部分を通つて作動
油が流れる際に、バルブ機構の高圧側の油室の圧
力に応じた中間圧室が形成されて高圧の油室との
差圧を小さく抑えるため、作動油がバルブ機構を
通過するときにキヤビテーシヨンが生じることが
なく、スイツシユ音の発生も防止することができ
る。(Effect of the invention) As explained above, according to the valve mechanism according to the invention, when hydraulic oil flows through the valve mechanism part from the high pressure oil chamber to the low pressure oil chamber in order to generate damping force. , an intermediate pressure chamber corresponding to the pressure in the oil chamber on the high pressure side of the valve mechanism is formed to keep the differential pressure with the high pressure oil chamber small, so cavitation does not occur when the hydraulic oil passes through the valve mechanism. , it is also possible to prevent the occurrence of swishing noise.
第１図は本考案に係るバルブ機構を適用した油
圧緩衝器の縦断面図、第２図は第１図の要部拡大
図、第３図はスリツトバルブの平面図、第４図及
び第５図はバルブ機構の作用を示す第２図と同様
の断面図、第６図は別実施例を示す第２図と同様
の断面図、第７図及び第８図は従来のバルブ機構
の断面図である。
尚、図面中３はシリンダ、５はピストン、７，
８はバルブ機構、１１，１８はバルブケース、１
２，１９はスリツトバルブ、１３，２０は板バル
ブ、１６，２３はバルブシート、１７は起立部、
S1，S2，S3は油室、S4，S5は中間圧室である。
Figure 1 is a longitudinal sectional view of a hydraulic shock absorber to which the valve mechanism according to the present invention is applied, Figure 2 is an enlarged view of the main parts of Figure 1, Figure 3 is a plan view of the slit valve, Figures 4 and 5. is a sectional view similar to FIG. 2 showing the operation of the valve mechanism, FIG. 6 is a sectional view similar to FIG. 2 showing another embodiment, and FIGS. 7 and 8 are sectional views of a conventional valve mechanism. be. In addition, in the drawing, 3 is a cylinder, 5 is a piston, 7,
8 is a valve mechanism, 11 and 18 are valve cases, 1
2 and 19 are slit valves, 13 and 20 are plate valves, 16 and 23 are valve seats, 17 is an upright part,
S 1 , S 2 , and S 3 are oil chambers, and S 4 and S 5 are intermediate pressure chambers.
Claims (1)
ことで一方の油室を高圧に他方の油室を低圧に
し、高圧の油室から低圧の油室へバルブ構造を介
して作動油を流通させることで減衰力を発生する
ようにした油圧緩衝器において、前記バルブ機構
はスリツトバルブを含み、このスリツトバルブを
支持するバルブシートには、スリツトバルブのス
リツト部から流入した作動油の流路に介設する起
立部をスリツトバルブに近接して設け、このスリ
ツトバルブが撓んだときの上記起立部との間の隙
間の減少によつて高圧の油室側からの圧力に応じ
た中間圧力を生じて高圧の油室との差圧を小さく
抑える中間圧室をスリツトバルブの下流側に形成
したことを特徴とする油圧緩衝器の減衰力発生用
バルブ機構。 By sliding the piston along the cylinder circumferential surface, one oil chamber is made to have high pressure and the other oil chamber is made to be low pressure, and hydraulic oil is circulated from the high pressure oil chamber to the low pressure oil chamber via the valve structure. In a hydraulic shock absorber configured to generate a damping force, the valve mechanism includes a slit valve, and a valve seat supporting the slit valve has an upright portion interposed in a flow path for hydraulic oil flowing from the slit portion of the slit valve. The slit valve is installed close to the slit valve, and when the slit valve is bent, the gap between the slit valve and the above-mentioned upright portion is reduced, creating an intermediate pressure corresponding to the pressure from the high-pressure oil chamber side. A valve mechanism for generating damping force for a hydraulic shock absorber, characterized in that an intermediate pressure chamber for suppressing differential pressure to a small level is formed downstream of a slit valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1986113916U JPH0425546Y2 (en) | 1986-07-24 | 1986-07-24 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1986113916U JPH0425546Y2 (en) | 1986-07-24 | 1986-07-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6320542U JPS6320542U (en) | 1988-02-10 |
| JPH0425546Y2 true JPH0425546Y2 (en) | 1992-06-18 |
Family
ID=30996167
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1986113916U Expired JPH0425546Y2 (en) | 1986-07-24 | 1986-07-24 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0425546Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH058352Y2 (en) * | 1986-08-07 | 1993-03-02 | ||
| JP4162231B2 (en) * | 2003-08-27 | 2008-10-08 | カヤバ工業株式会社 | Hydraulic shock absorber |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6147134B2 (en) * | 1980-02-25 | 1986-10-17 | Takeda Chemical Industries Ltd |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6131556Y2 (en) * | 1981-04-25 | 1986-09-13 | ||
| JPS59142539U (en) * | 1983-03-15 | 1984-09-22 | 株式会社昭和製作所 | Sticking prevention structure for hydraulic shock absorber valves |
| JPS6147134U (en) * | 1984-08-31 | 1986-03-29 | 株式会社 昭和製作所 | Hydraulic shock absorber damping force generator |
-
1986
- 1986-07-24 JP JP1986113916U patent/JPH0425546Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6147134B2 (en) * | 1980-02-25 | 1986-10-17 | Takeda Chemical Industries Ltd |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6320542U (en) | 1988-02-10 |
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