JPS63246579A - Relief valve of hydraulic motor - Google Patents
Relief valve of hydraulic motorInfo
- Publication number
- JPS63246579A JPS63246579A JP8063587A JP8063587A JPS63246579A JP S63246579 A JPS63246579 A JP S63246579A JP 8063587 A JP8063587 A JP 8063587A JP 8063587 A JP8063587 A JP 8063587A JP S63246579 A JPS63246579 A JP S63246579A
- Authority
- JP
- Japan
- Prior art keywords
- spring
- pressure
- spring seat
- relief
- seat
- 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.)
- Granted
Links
- 230000035939 shock Effects 0.000 abstract description 7
- 239000003921 oil Substances 0.000 description 26
- 230000007935 neutral effect Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Landscapes
- Safety Valves (AREA)
Abstract
Description
【発明の詳細な説明】
[発明の属する技術分野]
本発明は慣性体駆動回路に使用する油圧モータのリリー
フ弁に関する。DETAILED DESCRIPTION OF THE INVENTION [Technical field to which the invention pertains] The present invention relates to a relief valve for a hydraulic motor used in an inertial drive circuit.
慣性体駆動回路は一般に油圧ポンプから切換弁により回
転方向と停止を制御された後油圧モータに導かれて慣性
体を駆動している。しかして油圧モータの回転中に切換
弁を中立にして慣性体を停止させると、油圧モータの戻
り側は閉ざされることにより油圧力は急上昇してエネル
ギが増加しショックを発生して歯車等を破損させること
がある。Generally, the inertial body drive circuit drives the inertial body by a hydraulic pump whose rotation direction and stop is controlled by a switching valve, and which is then guided by a hydraulic motor. However, when the switching valve is set to neutral while the hydraulic motor is rotating to stop the inertial body, the return side of the hydraulic motor is closed, causing a sudden increase in hydraulic pressure and an increase in energy, which causes shock and damages gears, etc. Sometimes I let it happen.
[従来技術]
このため従来から第5図に示すリリーフ弁を油圧回路に
設置して油圧力の急上昇を防いでいた。[Prior Art] For this reason, a relief valve shown in FIG. 5 has been conventionally installed in a hydraulic circuit to prevent a sudden increase in hydraulic pressure.
t55図において1はリリーフ弁で2はリリーフ弁1の
弁本体で供給通路3および戻り通路4を有し、同通路3
・4に連通する孔5を有しており。In the t55 diagram, 1 is a relief valve, and 2 is the valve body of the relief valve 1, which has a supply passage 3 and a return passage 4, and the passage 3
- Has a hole 5 that communicates with 4.
回礼5の内側にスリーブ6が液密的に嵌着されている。A sleeve 6 is fitted inside the circumference 5 in a liquid-tight manner.
このスリーブ6は内部に大径部7aおよび小径部7bを
有する段付孔7が形成されている。This sleeve 6 has a stepped hole 7 formed therein having a large diameter portion 7a and a small diameter portion 7b.
また弁本体2の孔5開口部側に螺合するキャップ8は内
部に孔9を有しその一側を前記スリーブ6に接し他側を
プラグ10にて孔9を閉塞する。A cap 8 screwed onto the opening side of the hole 5 of the valve body 2 has a hole 9 therein, and one side of the cap 8 is in contact with the sleeve 6, and the other side is closed with a plug 10.
11は孔11aを有するシートで弁本体2に取り付けで
ある。Reference numeral 11 denotes a seat having a hole 11a and is attached to the valve body 2.
段付孔7の大径部7aに摺動可能に挿入された外側ボベ
ツ)12は一端を開放した孔13を有し偏心孔14を有
する他端面を前記シート11に接しその移動により前記
供給通路3を戻り通路4に連通ずる。前記外側ポペット
12の孔13に挿入された内側ポペット15は、その内
部に孔15aおよびこれに連なる大径の孔15bを有す
る。The outer bobbin (12) slidably inserted into the large diameter portion 7a of the stepped hole 7 has a hole 13 with one end open, and the other end surface having an eccentric hole 14 is in contact with the sheet 11, and its movement opens the supply passage. 3 is connected to the return passage 4. The inner poppet 15 inserted into the hole 13 of the outer poppet 12 has a hole 15a and a large diameter hole 15b connected thereto.
16はロッドでその一側を内側ボペツ)15の大径の孔
15bに他側をバネ座17の孔18に挿入され図示の位
置で右方向への移動をプラグ10の端面にて制限されて
いる。また前記ロッド16の内部に設けられた軸方向通
路19は一方を孔15a・偏心孔14を介して供給通路
3に接続し、他方には外周方向に開口する横孔2oが設
けられている。16 is a rod whose one side is inserted into the large diameter hole 15b of the plug 15 (with its other side inserted into the hole 18 of the spring seat 17), and its rightward movement is restricted by the end face of the plug 10 at the position shown in the figure. There is. Further, the axial passage 19 provided inside the rod 16 is connected to the supply passage 3 via the hole 15a and the eccentric hole 14 on one side, and has a horizontal hole 2o opening toward the outer circumference on the other side.
バネ座17はキャップ8の孔9およびロッド16の外周
に挟まれ軸方向に移動可能に挿入されており、その内孔
18にロッド16の横孔2oに対応する環状溝21およ
びこの溝21に連なり外周のバネ庫室24に開口する通
路22を設けている。また前記バネ座17の移動により
横孔20の開口量を漸減せしめる。バネ庫室24はバネ
座17およびキャップ8・プラグ1oとで形成されてい
る。25はバネで一側をバネ座17に接し他側をバネ受
け27・受け26を介して外側ポペット12に接する。The spring seat 17 is sandwiched between the hole 9 of the cap 8 and the outer periphery of the rod 16 and is inserted so as to be movable in the axial direction. A passage 22 is provided that opens into a continuous spring storage chamber 24 on the outer periphery. Further, by moving the spring seat 17, the opening amount of the horizontal hole 20 is gradually reduced. The spring chamber 24 is formed by the spring seat 17, the cap 8, and the plug 1o. 25 is a spring that contacts the spring seat 17 on one side and the outer poppet 12 on the other side via a spring receiver 27 and a receiver 26.
28はタンクTに通じるバネ室である。28 is a spring chamber communicating with the tank T.
次にこの従来例の作動について述べる。まず、供給通路
3の圧力が低いとき、リリーフ弁1は非作動状態にあり
、外側ボペッ)12は受け26およびバネ受け27を介
してバネ25により左方に押されシート11に接し、か
つバネ座17がプラグlOに接した位置にあり、供給通
路3と戻り通路4とを第5図に示すようにしゃ断する。Next, the operation of this conventional example will be described. First, when the pressure in the supply passage 3 is low, the relief valve 1 is in an inoperative state, and the outer boppet 12 is pushed leftward by the spring 25 through the receiver 26 and the spring receiver 27 and comes into contact with the seat 11, and The seat 17 is in contact with the plug lO, and cuts off the supply passage 3 and the return passage 4 as shown in FIG.
いま、供給通路3の作動油の圧力が上昇すると、この圧
油は外側ポペット12に作用しバネ25に抗して外側ポ
ペット12を右方向に移動し供給通路3と戻り通路4を
連通しリリーフ作用を開始する。一方では圧油は外側ボ
ベッ)12の偏心孔14.孔15aを介して軸方向通路
19に、ざらに横孔20、環状溝21・通路22を経て
バネ庫室24に導入される。このバネ庫室24の圧油は
供給通路3の圧力上昇に対応してバネ座17をバネ庫室
24の圧力によりバネ25に抗して図示の位置から左方
へ移動する。これによりバネ25はさらに圧縮されるた
めリリーフ圧力は上昇してゆく、このバネ座17の移動
によりロッド16の横孔20は徐々に開口面積を減少す
ると共にバネ庫室24への圧油を減量する。さらにバネ
座17は移動し横孔20の開口が閉じられ、バネ庫室2
4への圧油の流入が実質的になくなるのでバネ座17の
右方眼位置は保たれる。このように設定圧力の上昇は上
限値に近ずくにつれてその増加量をゆるやかになるため
リリーフ弁1の始動時における急上昇圧力に起因するシ
ョックを緩和することができる。また、供給通路3の圧
力が設定値以下になると、バネ庫室24の圧力が低くな
り、バネ座17はバネ25の弾性力にて図示の位置に戻
り次の動作に備える。Now, when the pressure of the hydraulic oil in the supply passage 3 increases, this pressure oil acts on the outer poppet 12, moves the outer poppet 12 to the right against the spring 25, and connects the supply passage 3 and the return passage 4 to provide relief. Begins action. On the other hand, the pressure oil is inserted into the eccentric hole 14 of the outer cylinder 12. It is introduced into the axial passage 19 through the hole 15a, roughly through the horizontal hole 20, an annular groove 21 and a passage 22, and into the spring storage chamber 24. The pressure oil in the spring chamber 24 moves the spring seat 17 leftward from the illustrated position against the spring 25 due to the pressure in the spring chamber 24 in response to the rise in pressure in the supply passage 3 . As a result, the spring 25 is further compressed, and the relief pressure increases. Due to this movement of the spring seat 17, the opening area of the horizontal hole 20 of the rod 16 gradually decreases, and the pressure oil to the spring chamber 24 is reduced. do. Furthermore, the spring seat 17 moves and the opening of the horizontal hole 20 is closed, and the spring storage chamber 2
Since the flow of pressure oil into the spring seat 4 is substantially eliminated, the right side position of the spring seat 17 is maintained. In this way, the increase in the set pressure becomes more gradual as it approaches the upper limit, so that the shock caused by the sudden pressure increase when the relief valve 1 is started can be alleviated. Further, when the pressure in the supply passage 3 becomes lower than the set value, the pressure in the spring chamber 24 becomes low, and the spring seat 17 returns to the illustrated position by the elastic force of the spring 25 in preparation for the next operation.
前述した従来例は供給通路3の圧力が上昇すると先づ外
側ボペッ)12がバネ25に抗して右行し、これと同時
にバネ座17の右側のバネ庫室24に圧油が流入し、バ
ネ座17はバネ25の力(即ちリリーフ圧力)を高くし
ながら左行する。In the conventional example described above, when the pressure in the supply passage 3 increases, the outer boppet 12 first moves to the right against the spring 25, and at the same time, pressure oil flows into the spring storage chamber 24 on the right side of the spring seat 17. The spring seat 17 moves to the left while increasing the force (ie, relief pressure) of the spring 25.
バネ座17の左行にともない圧油の通る横孔20の面積
は小さくなりやがてこれを閉じリリーフ圧力は設定圧力
になる。このように従来方式はリリーフ弁の始動時にお
ける圧力ピークを減少させる効果はある。しかしながら
バネ座17の圧油に対する作用面積、即ちバネ座17の
キャップ8に対する嵌合部面積は第5図に示すように、
バネ25の直径面積より大きく低い圧力でもバネ座17
は移動を開始し、必要な高圧時読に横孔20はバネ座1
7により閉ざされており、横孔20を閉じた後の大きな
ピークを解消してショックを低減することは不可能であ
った。As the spring seat 17 moves to the left, the area of the horizontal hole 20 through which the pressure oil passes becomes smaller and is eventually closed so that the relief pressure becomes the set pressure. As described above, the conventional method has the effect of reducing the pressure peak at the time of starting the relief valve. However, the area where the spring seat 17 acts on the pressure oil, that is, the area where the spring seat 17 fits into the cap 8 is as shown in FIG.
Even if the pressure is larger and lower than the diameter area of the spring 25, the spring seat 17
starts moving, and the horizontal hole 20 is connected to the spring seat 1 to read the required high pressure.
7, it was impossible to eliminate the large peak after closing the horizontal hole 20 and reduce the shock.
[発明の目的]
本発明はこのような欠点を除去したものでその目的は、
供給通路の油圧が高くなったときバネを圧縮してリリー
フ圧力を高くするバネ座の油圧作用面積を小さくして、
低い圧力ではリリーフ弁が所定圧力に達しないようにす
ることにより、リリーフ弁の始動時における圧力ピーク
を解消しもってショックを低減するようにした油圧モー
タのリリーフ弁を提供することにある。[Object of the invention] The present invention eliminates such drawbacks, and its object is to:
When the hydraulic pressure in the supply passage becomes high, the spring seat compresses the spring and increases the relief pressure by reducing the hydraulic action area of the spring seat.
To provide a relief valve for a hydraulic motor that reduces shock by eliminating pressure peaks at the time of starting the relief valve by preventing the relief valve from reaching a predetermined pressure at low pressures.
[発明の要点]
本発明における油圧モータのリリーフ弁は、供給側の圧
油をバネ座の油室に導入することによりバネ座を移動さ
せこの移動によりバネを圧縮してリリーフ圧力を調整す
るリリーフ弁において、バネ座の圧油作用面積をバネ外
径の投影面積より小さくしたことを特徴にしている。[Summary of the Invention] The relief valve for the hydraulic motor according to the present invention is a relief valve that moves the spring seat by introducing pressure oil on the supply side into the oil chamber of the spring seat, and this movement compresses the spring to adjust the relief pressure. The valve is characterized in that the pressure oil acting area of the spring seat is smaller than the projected area of the spring outer diameter.
[発明の実施例]
以下本発明の一実施例を示した第1図ないし第3図につ
いて説明する。第1図において油圧ポンプ31からの圧
油は切換弁32により中立と正転逆転を制御されて油圧
モータ33に送られて慣性体34を駆動する。油圧ポン
プ31の圧油は上記の流れと同時に制御弁35から背圧
チェック弁36とフィルタ37を並列にしてタンク38
に戻されている。油圧モータ33に接続された管路39
と40とは分岐してリリーフ弁4LAと41Bとの供給
通路42Aと42Bとに結ばれ、かつ両管路39と40
とは逆止弁43Aと43Bとにより結ばれて1本になり
、中間で両リリーフ弁41Aと41Bの出口通路44A
と44Bに接続された後背圧チェック弁36等の上流側
に接続されている。なお上記したAとBとを付した2部
材はいずれも同一である。[Embodiment of the Invention] Hereinafter, a description will be given of FIGS. 1 to 3 showing an embodiment of the present invention. In FIG. 1, pressure oil from a hydraulic pump 31 is controlled to be neutral, normal or reverse by a switching valve 32, and is sent to a hydraulic motor 33 to drive an inertial body 34. At the same time as the above-mentioned flow, the pressure oil of the hydraulic pump 31 is supplied to the tank 38 from the control valve 35 through the back pressure check valve 36 and filter 37 in parallel.
has been returned to. Pipeline 39 connected to hydraulic motor 33
and 40 are branched and connected to supply passages 42A and 42B of relief valves 4LA and 41B, and both pipelines 39 and 40
is connected by check valves 43A and 43B to become one, and in the middle is an outlet passage 44A of both relief valves 41A and 41B.
and 44B on the upstream side of the rear back pressure check valve 36 and the like. Note that the two members labeled A and B described above are the same.
次に上述したリリーフ弁41A等の細部を第2図につい
て説明する。弁本体51にはOリング52を置いてスリ
ーブ53が液密的に螺着されており、その先端は弁本体
51の油室54内に位置しかつシート55を介して弁本
体51の内壁を押し付け、−劣後端にはOリング56を
介してプラグ57が固着されている。スリーブ53の内
孔58にはポペット59が摺動自在に挿入されており、
ポペット59と一体のロッド60の後端は、スリーブ5
3の内孔61へ摺動自在に挿入されたバネ座62の内孔
へ摺動自在に挿入さている。ポペット59の背面とバネ
座62との間には座金63を介してバネ64が設けられ
ていることにより、供給通路42A−B(第1図参照)
に接続された供給口65の圧力が低いときポペット59
の先端はシート55の弁座に接している。ポペット59
とロッド60との中央には図において左側からシート5
5を介して供給口65に開口した通路66と、絞り67
とバネ座62の作動部である油室68に開口した通路6
9が直列に設けである。Next, details of the above-mentioned relief valve 41A etc. will be explained with reference to FIG. A sleeve 53 is liquid-tightly screwed onto the valve body 51 by placing an O-ring 52 thereon, and its tip is located within the oil chamber 54 of the valve body 51 and is attached to the inner wall of the valve body 51 via a seat 55. A plug 57 is fixed to the pressed and inferior end via an O-ring 56. A poppet 59 is slidably inserted into the inner hole 58 of the sleeve 53.
The rear end of the rod 60 integrated with the poppet 59 is connected to the sleeve 5
The spring seat 62 is slidably inserted into the inner hole of the spring seat 62, which is slidably inserted into the inner hole 61 of No.3. A spring 64 is provided between the back surface of the poppet 59 and the spring seat 62 via a washer 63, so that the supply passage 42A-B (see FIG. 1)
When the pressure of the supply port 65 connected to the poppet 59 is low,
The tip of the valve is in contact with the valve seat of the seat 55. poppet 59
In the center of the rod 60 and the sheet 5 from the left side in the figure.
5 and a passage 66 that opens to the supply port 65 and a throttle 67.
and a passage 6 that opens into an oil chamber 68 which is the operating part of the spring seat 62.
9 are provided in series.
また弁本体51には出口通路44AΦB(第1図参照)
に接続された出ロア0ならびに、スリーブ53の内孔5
8と油室54とを連通ずる横孔71と72とが設けであ
る。In addition, the valve body 51 has an outlet passage 44AΦB (see Fig. 1).
The lower output 0 connected to the inner hole 5 of the sleeve 53
8 and the oil chamber 54 are provided with horizontal holes 71 and 72 that communicate with the oil chamber 54.
次に前述した実施例の動作を説明する。第1図において
切換弁32が図示の中立状態のとき、供給通路42A−
B従って供給口65(第2図参照)の圧力はなくリリー
フ弁41A・Bは非作動状態、即ちポペット59の先端
はバネ64により左方へ押し圧されてシート55に接し
ており供給口65と出ロア0とはしゃ断されている。Next, the operation of the embodiment described above will be explained. In FIG. 1, when the switching valve 32 is in the neutral state shown, the supply passage 42A-
B Therefore, there is no pressure at the supply port 65 (see FIG. 2), and the relief valves 41A and 41B are in an inoperative state. That is, the tip of the poppet 59 is pressed leftward by the spring 64 and is in contact with the seat 55, and the supply port 65 It is cut off from the output lower 0.
次いで切換弁32を中立状態から上方位置へ切り換える
と圧油は管路39から油圧モータ33に流入しこれを正
転させる。この回転中に切換弁32を中立位置に切り換
えても慣性体34のため油圧モータ33は直ちに停止せ
ず管路40の圧力は上昇する。従って供給通路42Bを
通って供給口65の圧力は上昇し、この圧力はポペット
59に作用してこれをバネ64に抗して右方向に移動さ
せ、供給口65と出ロアoとをシート55と横孔71を
介して連通させることによりリリーフ作用を開始する。Next, when the switching valve 32 is switched from the neutral state to the upper position, pressure oil flows into the hydraulic motor 33 from the pipe line 39 and causes it to rotate normally. Even if the switching valve 32 is switched to the neutral position during this rotation, the hydraulic motor 33 does not stop immediately because of the inertia body 34, and the pressure in the pipe line 40 increases. Therefore, the pressure in the supply port 65 increases through the supply passage 42B, and this pressure acts on the poppet 59 to move it to the right against the spring 64, thereby moving the supply port 65 and the lower outlet o to the seat 55. The relief action is started by communicating with the side hole 71 through the horizontal hole 71.
同時に圧油はポペット59とロッド6oの通路66と6
9そして絞り67を通って油室68に導入され、油室6
8の圧油は供給・口65の圧力上昇に対応して圧力が上
昇しバネ座62をバネ64に抗して左方へ移動させる。At the same time, the pressure oil flows through the passages 66 and 6 of the poppet 59 and the rod 6o.
9 and is introduced into the oil chamber 68 through the throttle 67.
The pressure of the pressure oil 8 increases in response to the increase in pressure at the supply port 65, and moves the spring seat 62 to the left against the spring 64.
この結果バネ64はさらに圧縮されるためリリーフ圧力
は上昇する。バネ座62の左行はそのフランジ部の左側
面77が弁本体51の壁面78に接するまでのストロー
ク交を移動すると停止し、この停止したときのリリーフ
圧が設定圧力である。As a result, the spring 64 is further compressed and the relief pressure increases. The leftward movement of the spring seat 62 stops when the left side surface 77 of the flange part moves through the stroke until it comes into contact with the wall surface 78 of the valve body 51, and the relief pressure at this stop is the set pressure.
このようにしてリリーフされた油は出ロア0から第1図
の出口通路44Bと逆止弁43Aを通って管路39に至
り油圧モータ33に供給される。The oil thus relieved passes from the outlet lower 0 through the outlet passage 44B and the check valve 43A shown in FIG. 1, reaches the pipe line 39, and is supplied to the hydraulic motor 33.
なお油室68への圧油の流入は途中に絞り67があるた
めゆるやかであり、従ってリリーフ圧力の上昇もゆるや
かであって急激な圧力上昇によるショックを緩和してい
る。さらにストローク交を大きくすれば設定圧力を高く
することも可能である。Note that the flow of pressure oil into the oil chamber 68 is gradual due to the presence of the throttle 67 in the middle, and therefore the rise in relief pressure is also gradual, thereby alleviating the shock caused by a sudden pressure rise. Further, by increasing the stroke intersection, it is possible to increase the set pressure.
第3図において下方は切換弁の操作位置を示し上方はこ
の操作位置に対応するリリーフ弁のリリーフ圧力を示し
た線図であって、切換弁が動作位置から中立位置に切り
換えられるとリリーフ圧力は円弧で結んだゆるやかな曲
線で上昇することが示されている・
第4図は本発明の他の実施例を示した図であって、切換
弁32と油圧モータ33とリリーフ弁41A@B間の接
続が前述した実施例と異なるのみで、本発明の主題であ
るリリーフ弁41A・Bは全く同−故詳しい説明を省略
する。In Fig. 3, the lower part shows the operating position of the switching valve, and the upper part shows the relief pressure of the relief valve corresponding to this operating position.When the switching valve is switched from the operating position to the neutral position, the relief pressure increases. 4 is a diagram showing another embodiment of the present invention, in which the distance between the switching valve 32, the hydraulic motor 33, and the relief valve 41A@B is shown to rise in a gentle curve connected by circular arcs. The relief valves 41A and 41B, which are the subject matter of the present invention, are the same as those of the above-mentioned embodiments, except for the connection of the relief valves 41A and 41B, so a detailed description thereof will be omitted.
[発明の効果]
本発明における油圧モータのリリーフ弁は以上説明にし
たように、バネを圧縮してリリーフ圧力を高くするバネ
座の圧油作用面積はバネ外径の投影面積より小さく、即
ち従来例に比較すると小さくなったのでリリーフの設定
圧力は高くなった。[Effects of the Invention] As explained above, in the relief valve of the hydraulic motor according to the present invention, the pressure oil acting area of the spring seat that compresses the spring and increases the relief pressure is smaller than the projected area of the outer diameter of the spring. Compared to the example, it was smaller, so the relief setting pressure was higher.
このためリリーフ開始時におけるピークを十分解消しシ
ョックを減少させる利点を有する。This has the advantage of sufficiently eliminating the peak at the start of relief and reducing shock.
第1図ないし第3図は本発明の一実施例を示し第1図は
機構図、i2図は第1図の要部拡大図、第3図は切換弁
の操作位置とこの位置に対するリリーフ弁のリリーフ圧
力を示した線図、第4図は本発明の他の実施例における
機構図、第5図は従来例の断面図である。
41A@41B・・・リリーフ弁、62・・・バネ座。
64・・・バネ、68・・・油室。Figures 1 to 3 show one embodiment of the present invention, Figure 1 is a mechanical diagram, Figure i2 is an enlarged view of the main part of Figure 1, and Figure 3 shows the operation position of the switching valve and the relief valve corresponding to this position. FIG. 4 is a diagram showing the relief pressure in another embodiment of the present invention, and FIG. 5 is a sectional view of a conventional example. [email protected] valve, 62...Spring seat. 64...Spring, 68...Oil chamber.
Claims (1)
バネ座を移動させこの移動によりバネを圧縮してリリー
フ圧力を調整するリリーフ弁において、前記バネ座の圧
油作用面積を前記バネ座外径の投影面積より小さくした
リリーフ弁。In a relief valve that moves the spring seat by introducing pressure oil on the supply side into the oil chamber of the spring seat and compresses the spring by this movement to adjust the relief pressure, the pressure oil acting area of the spring seat is defined as the pressure oil acting area of the spring seat. A relief valve whose projected area is smaller than the seat outside diameter.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62080635A JP2571928B2 (en) | 1987-04-01 | 1987-04-01 | Hydraulic motor relief valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62080635A JP2571928B2 (en) | 1987-04-01 | 1987-04-01 | Hydraulic motor relief valve |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS63246579A true JPS63246579A (en) | 1988-10-13 |
JP2571928B2 JP2571928B2 (en) | 1997-01-16 |
Family
ID=13723829
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP62080635A Expired - Lifetime JP2571928B2 (en) | 1987-04-01 | 1987-04-01 | Hydraulic motor relief valve |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2571928B2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0262176U (en) * | 1988-10-28 | 1990-05-09 | ||
JPH0266780U (en) * | 1988-10-31 | 1990-05-21 | ||
EP3961074A4 (en) * | 2019-04-20 | 2023-01-11 | Kawasaki Jukogyo Kabushiki Kaisha | Relief valve |
WO2023028759A1 (en) * | 2021-08-30 | 2023-03-09 | Engineered Controls International, Llc | Excess flow valve for cryogenic fluid tank |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5514945A (en) * | 1978-07-20 | 1980-02-01 | Toyota Motor Corp | Construction of combustion chamber in internal combustion engine |
JPS57107001U (en) * | 1980-12-23 | 1982-07-01 | ||
JPS622804U (en) * | 1985-06-20 | 1987-01-09 |
-
1987
- 1987-04-01 JP JP62080635A patent/JP2571928B2/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5514945A (en) * | 1978-07-20 | 1980-02-01 | Toyota Motor Corp | Construction of combustion chamber in internal combustion engine |
JPS57107001U (en) * | 1980-12-23 | 1982-07-01 | ||
JPS622804U (en) * | 1985-06-20 | 1987-01-09 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0262176U (en) * | 1988-10-28 | 1990-05-09 | ||
JPH0266780U (en) * | 1988-10-31 | 1990-05-21 | ||
EP3961074A4 (en) * | 2019-04-20 | 2023-01-11 | Kawasaki Jukogyo Kabushiki Kaisha | Relief valve |
WO2023028759A1 (en) * | 2021-08-30 | 2023-03-09 | Engineered Controls International, Llc | Excess flow valve for cryogenic fluid tank |
Also Published As
Publication number | Publication date |
---|---|
JP2571928B2 (en) | 1997-01-16 |
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