JPS6321814Y2 - - Google Patents
Info
- Publication number
- JPS6321814Y2 JPS6321814Y2 JP17789280U JP17789280U JPS6321814Y2 JP S6321814 Y2 JPS6321814 Y2 JP S6321814Y2 JP 17789280 U JP17789280 U JP 17789280U JP 17789280 U JP17789280 U JP 17789280U JP S6321814 Y2 JPS6321814 Y2 JP S6321814Y2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- piston
- hole
- passage
- poppet
- 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
- 230000007423 decrease Effects 0.000 description 7
- 230000009471 action Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
Landscapes
- Safety Valves (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は油圧回路の圧力を制御するリリーフ弁
に関し、より詳しくは作動時のサージ圧を除去す
る改良に関する。[Detailed Description of the Invention] [Industrial Field of Application] The present invention relates to a relief valve for controlling pressure in a hydraulic circuit, and more particularly to an improvement for eliminating surge pressure during operation.
油圧制御装置において比較的負荷の大きい油圧
モータの起動（又は制動）時、切換弁を操作して
圧油を供給すると供給（又は戻り）回路の圧力が
同回路に設けられたリリーフ弁の設定圧力まで急
速に上昇するので、リリーフ弁の開閉に係るポペ
ツト等の部材や管路内の流体の持つ慣性等により
サージ圧が発生しその大きさは圧力の上昇速度が
速ければ速い程大きく、油圧制御装置に有害な衝
撃を与え騒音を発生すると共に、ひいては系の破
損の原因ともなる。このような有害なサージ圧の
発生を抑止するために、初期設定圧力を比較的低
くしたリリーフ弁の供給通路に生起する供給圧力
を、圧力設定用バネの背後から前記供給圧力で出
力を増加させるように作用するピストンを設け、
ピストンの移動によるバネの出力の増加と供給圧
力の増加とが互にフイードバツクし合つて最終設
定圧力に達する構成とし、圧力の上昇速度を減殺
するため供給圧力をピストンに伝達する回路に絞
りを設けバネ出力の増加速度を制御する技術は特
開昭51−72726号公報等により公知である。
When starting (or braking) a hydraulic motor that has a relatively large load in a hydraulic control system, when the switching valve is operated to supply pressure oil, the pressure in the supply (or return) circuit changes to the set pressure of the relief valve installed in the same circuit. Surge pressure is generated by parts such as poppets that open and close the relief valve and the inertia of the fluid in the pipe, and the magnitude of the surge pressure increases as the pressure rises faster. This not only gives a harmful impact to the equipment and generates noise, but also causes damage to the system. In order to suppress the generation of such harmful surge pressure, the output of the supply pressure generated in the supply passage of the relief valve whose initial setting pressure is relatively low is increased by the supply pressure from behind the pressure setting spring. Provide a piston that acts like this,
The increase in spring output due to the movement of the piston and the increase in supply pressure feed back each other to reach the final set pressure, and a throttle is provided in the circuit that transmits the supply pressure to the piston to reduce the rate of increase in pressure. A technique for controlling the rate of increase in spring output is known from, for example, Japanese Patent Laid-Open No. 72726/1983.
〔考案が解決しようとする問題点〕
しかしながら、前記技術に開示された絞りは調
整によつて開口を変化させうるものではあるが、
リリーフ弁作動時には前記調整によりプリセツト
した固定絞りとして作用する。したがつてバネの
橈みを増加させるピストンは加えられる圧力が初
期設定圧力を越えるとほゞ一定の速さで偏倚する
のでリリーフ弁の入口圧力も単調な速さで上昇
し、リリーフ弁の最終設定圧力近傍でもその速さ
が衰えることはない。その結果、絞りの開度を大
きくしリリーフ弁供給圧力の上昇速度を大きくす
ると第２図ａに見られるように依然としてサージ
圧が発生し、絞り弁開度を小さくすると第２図ｂ
に示す如くサージ圧の発生を抑止できるが圧力上
昇に時間がかゝり応答性を悪くする問題点があつ
た。[Problems to be solved by the invention] However, although the aperture disclosed in the above technology can change the aperture by adjustment,
When the relief valve is activated, it acts as a fixed throttle preset by the adjustment described above. Therefore, when the applied pressure exceeds the initial set pressure, the piston that increases the radius of the spring deviates at a nearly constant speed, so the inlet pressure of the relief valve also rises at a monotonous rate, and the final pressure of the relief valve increases. The speed does not decrease even when the pressure is close to the set pressure. As a result, if the opening of the throttle valve is increased and the rising speed of the relief valve supply pressure is increased, surge pressure still occurs as shown in Figure 2a, and if the opening of the throttle valve is decreased, surge pressure is generated as shown in Figure 2b.
As shown in Fig. 3, although the generation of surge pressure can be suppressed, there is a problem in that it takes time for the pressure to rise, resulting in poor response.
本考案は前記問題点を解決するものであつて、
以下にその内容を実施例に対応する第１図を用い
て説明する。
The present invention solves the above problems, and includes:
The contents will be explained below using FIG. 1 corresponding to the embodiment.
一端がシート１１に面し供給通路３と戻り通路
４とを連通・遮断するポペツト１２を本体の孔に
挿入し、前記孔と同軸の孔９に前記シート１１よ
り大なる受圧面積を有するピストン１７を挿入
し、ピストン１７の背面が露出する空間を閉止し
て背室２４を形成し、圧縮されたバネ２８の両端
でそれぞれポペツト１２をシート１１へ、ピスト
ン１７を背室２４背後の壁面へ弾圧し、ポペツト
１２の他端側の軸心に穿設され供給通路３と連通
した孔１３に一端を、他端はピストン１７の軸心
を貫通する孔１８に差動部材３１をそれぞれ摺動
自在に嵌合する。さらに、供給通路３と背室２４
との間に、ピストン１７と差動部材３１との嵌合
部分に形成されバネ２８の弾圧力に対向し印加さ
れる背室２４の圧力によつて動くピストンの移動
量に応じて開口を減ずる可変絞り３０と、差動部
材３１の内部を介して供給通路３を可変絞りの一
側に連通する通路と、ピストン１７内部を介して
背室２４を可変絞り３０の他側へ連通する通路と
を設ける。 A poppet 12 whose one end faces the seat 11 and communicates/blocks the supply passage 3 and the return passage 4 is inserted into a hole in the main body, and a piston 17 having a larger pressure-receiving area than the sheet 11 is inserted into a hole 9 coaxial with the hole. is inserted, the space where the back surface of the piston 17 is exposed is closed to form a back chamber 24, and both ends of the compressed spring 28 press the poppet 12 against the seat 11 and the piston 17 against the wall behind the back chamber 24. One end of the differential member 31 is slidably inserted into a hole 13 formed in the axial center of the other end of the poppet 12 and communicated with the supply passage 3, and the other end is slidably inserted into a hole 18 that passes through the axial center of the piston 17. Fits in. Furthermore, the supply passage 3 and the back chamber 24
The opening is reduced in accordance with the amount of movement of the piston, which is formed at the fitting portion between the piston 17 and the differential member 31 and moves by the pressure of the back chamber 24, which is applied in opposition to the elastic force of the spring 28. The variable throttle 30, a passage that communicates the supply passage 3 with one side of the variable throttle through the inside of the differential member 31, and a passage that communicates the back chamber 24 with the other side of the variable throttle 30 through the inside of the piston 17. will be established.
供給通路３に圧力が生起するとシート１１に着
座しているポペツト１２のシート内径に露出した
部分に右向きの力が作用すると共に孔１４を経て
孔１３に流入した供給通路の圧油はポペツト１２
の孔１３に相当する面積に対し左向きの力をポペ
ツトに作用させる。従つて孔１３の投影面積に作
用する右および左向きの力は相殺し、ポペツト１
２に作用する圧油の力はシート１１の面積から孔
１３の面積を差し引いた残余の作用面積に印加さ
れる右向きの力のみであり、図示の状態に押圧さ
れたバネ２８の力を前記ポペツト１２の作用面積
で除した値（以下これを初期設定圧力と伝う）以
下ではポペツト１２は着座し続ける。一方供給通
路３の圧油は孔１４、差動部材３１の芯部に設け
た通路を経、可変絞り３０、通路２２を経てピス
トン１７の背面にその圧力を作用させ、ピストン
１７を左方へ移動させようとするが、図示の状態
のバネ２８の押圧力をピストン１７の作用面積で
除した値（以下これをピストンの初動圧力と示
う〕よりも前記圧力が低い状態では図示の位置を
維持し続ける。
When pressure is generated in the supply passage 3, a rightward force acts on the portion of the poppet 12 seated on the seat 11 exposed to the inner diameter of the seat, and the pressure oil in the supply passage that flows into the hole 13 via the hole 14 flows into the poppet 12.
A leftward force is applied to the poppet over an area corresponding to the hole 13. Therefore, the rightward and leftward forces acting on the projected area of the hole 13 cancel each other out, and the poppet 1
The force of the pressure oil acting on the poppet 2 is only a rightward force applied to the remaining acting area after subtracting the area of the hole 13 from the area of the seat 11. 12 (hereinafter referred to as the initial setting pressure), the poppet 12 continues to be seated. On the other hand, the pressure oil in the supply passage 3 passes through the hole 14, a passage provided in the core of the differential member 31, the variable throttle 30, and the passage 22, and applies its pressure to the back of the piston 17, causing the piston 17 to move to the left. However, if the pressure is lower than the value obtained by dividing the pressing force of the spring 28 in the illustrated state by the action area of the piston 17 (hereinafter referred to as the initial pressure of the piston), the illustrated position will not be achieved. Continue to maintain.
供給通路３の圧力がゆつくり上昇する場合、そ
の圧力がピストン１７の初動圧力を越えるとピス
トン１７はその圧力に応じてバネ２８の橈みを増
加させ乍ら左方へ移動し可動範囲の左方限に達す
る。この時、バネ２８はその出力が最終設定圧に
対応する量だけ橈んでいる。上記供給圧力の上昇
過程において、ピストン１７を左行させるための
圧油は、ピストンの移動に応じて通過面積が減少
する可変絞りの開口を通過するが流量が少くてよ
いため圧力損失が無く、供給圧力そのまゝを背面
に受けたピストン１７が移動し、供給圧力が初期
設定圧力を超えても既に更に高い設定圧力までバ
ネ２８が橈んでいるため、ポペツト１２は閉止し
ており供給圧力が最終設定圧を越えた時に始めて
開口する。また、負荷圧を受けて油圧モータを保
持する場合、負荷圧がピストン１７に作用しバネ
２８の橈みを負荷圧に対応する以上に増加させて
いるので負荷を逸走させることは無い。 When the pressure in the supply passage 3 rises slowly, and the pressure exceeds the initial pressure of the piston 17, the piston 17 moves to the left while increasing the deflection of the spring 28 according to the pressure, and moves to the left of the movable range. reach a limit. At this time, the spring 28 is deflected by an amount whose output corresponds to the final set pressure. In the above process of increasing the supply pressure, the pressure oil for moving the piston 17 to the left passes through the opening of the variable throttle whose passage area decreases according to the movement of the piston, but since the flow rate may be small, there is no pressure loss. The piston 17 receives the same supply pressure on its back side and moves, and even if the supply pressure exceeds the initial set pressure, the spring 28 is already bent to a higher set pressure, so the poppet 12 is closed and the supply pressure is It opens only when the final set pressure is exceeded. Further, when the hydraulic motor is held in response to load pressure, the load pressure acts on the piston 17 and increases the radius of the spring 28 beyond the load pressure, so the load does not run away.
急激な起動・制動を行つた場合供給圧力が急速
に上昇しようとする。この圧力はピストン１７の
背面に伝達されピストンの左行を促すが、左行に
つれ可変絞り３０の開口が減少し、ピストン１７
を左行させるために供給される油量の減少を来た
しピストンの左行速度が減少し、その結果、バネ
２８の橈み増加による設定圧力の増加速度が鈍
る。他方、供給通路３に充満し行き場の無い圧油
の圧力は急速に上昇するので前述の増加し続ける
設定圧力を越えポペツト１２を右行させ供給通路
３の圧油を戻り通路４へ放出する。ピストン１７
はその後も減速しながら左行し続けそれにつれて
供給通路３の圧力も漸増し終極的にピストン１７
がその可動範囲の左端に達すると供給通路３の圧
油は最終設定圧力に達し、その圧力を維持する。 When starting or braking suddenly, the supply pressure tends to rise rapidly. This pressure is transmitted to the back surface of the piston 17 and urges the piston to move leftward, but as it moves leftward, the opening of the variable throttle 30 decreases, and the piston 17
As a result, the amount of oil supplied to move the piston to the left decreases, and the speed of the piston to move to the left decreases. As a result, the speed at which the set pressure increases due to the increase in the radius of the spring 28 slows down. On the other hand, the pressure of the pressure oil filling the supply passage 3 and having nowhere else to go rises rapidly, exceeding the above-mentioned ever-increasing set pressure, causing the poppet 12 to move to the right and releasing the pressure oil in the supply passage 3 to the return passage 4. piston 17
continues to move to the left while decelerating, and as the pressure in the supply passage 3 gradually increases, eventually the piston 17
When reaches the left end of its movable range, the pressure oil in the supply passage 3 reaches the final set pressure and maintains that pressure.
以下本考案の一実施例を説明する。第１図にお
いて２は供給通路３、戻り通路４および孔５を設
けた弁本体、６はスリーブである。弁本体の孔５
には受け２６、ポペツト１２、シート１１を内挿
したスリーブ６が挿入されキヤツプ８で挟持され
る。キヤツプ８の孔９には受け２６に当接するバ
ネ受け２７、バネ２８を介在させてピストン１７
を挿入し、プラグ１０で閉止する。供給通路３と
孔１４で連通するポペツト１２の孔１３には差動
部材３１を構成する内側ピストン１５および内側
ピストン１５の孔に一端を嵌合したロツド１６を
挿入する。ロツド１６の他端はピストン１７の軸
心の孔１８に挿入する。ピストン１７の軸心の孔
１８には環状溝２１が設けられ、該溝２１と、ピ
ストン１７の左行に応じて開口を減ずるようロツ
ド１６に設けられた横孔２０とで可変絞り３０を
形成する。横孔２０はロツド１６および内側ピス
トン１５の軸心に設けられた通路１９、ポペツト
１２の孔１４を経て供給通路３に連通し、ピスト
ン１７の環状溝は横孔２２を経て背室２４へ連通
する。なお、可変絞り３０を形成する横孔をピス
トン１７に、環状溝をロツド１６の外周に設けて
もよい。
An embodiment of the present invention will be described below. In FIG. 1, 2 is a valve body provided with a supply passage 3, a return passage 4 and a hole 5, and 6 is a sleeve. Hole 5 in the valve body
A sleeve 6 with a receiver 26, a poppet 12, and a seat 11 inserted therein is inserted and held between the caps 8. A spring receiver 27 that contacts the receiver 26 and a spring 28 are interposed in the hole 9 of the cap 8, and the piston 17 is inserted into the hole 9 of the cap 8.
and close it with the plug 10. An inner piston 15 constituting the differential member 31 and a rod 16 whose one end is fitted into the hole of the inner piston 15 are inserted into the hole 13 of the poppet 12 which communicates with the supply passage 3 through the hole 14. The other end of the rod 16 is inserted into a hole 18 in the axial center of the piston 17. An annular groove 21 is provided in the axial hole 18 of the piston 17, and a variable throttle 30 is formed by the groove 21 and a horizontal hole 20 provided in the rod 16 so as to reduce the opening according to the leftward movement of the piston 17. do. The horizontal hole 20 communicates with the supply passage 3 through a passage 19 provided at the axis of the rod 16 and the inner piston 15, and the hole 14 of the poppet 12, and the annular groove of the piston 17 communicates with the back chamber 24 through the horizontal hole 22. do. Note that a horizontal hole forming the variable throttle 30 may be provided in the piston 17, and an annular groove may be provided in the outer periphery of the rod 16.
この実施例のリリーフ弁では供給通路圧力が低
い間はバネ２８の弾圧力がピストン１７とバネ受
け２７、受け２６を介してポペツト１２とを互い
に離すよう作用しそれぞれプラグ１０およびシー
ト１１に当接し供給通路３と戻り通路４の間を遮
断する。内側ポペツトとロツド１６は供給通路３
の圧力により圧力の高低にかゝわりなく常に右方
に押されプラグ１０に当接している。 In the relief valve of this embodiment, while the supply passage pressure is low, the elastic force of the spring 28 acts to separate the piston 17 from the poppet 12 via the spring receivers 27 and 26, and abuts the plug 10 and the seat 11, respectively. The supply passage 3 and the return passage 4 are cut off. Inner poppet and rod 16 are supply passage 3
Regardless of the level of pressure, it is always pushed to the right and comes into contact with the plug 10.
圧力が上昇し始めると、ポペツト１２はシート
１１の内径とポペツト１２の孔１３との投影面積
の差で与えられる作用面積に加わる供給圧力によ
りバネ２８の弾圧力に拘し右方に移動しようと
し、他方、ポペツト１２の孔１４、内側ピストン
１５およびロツド１６の軸心の通路１９、可変絞
り３０、横孔２２を経て背室２４に流入した供給
通路３の圧油により、より大きい作用面積を持つ
ピストン１７が左行しバネ２８の弾圧力を増大さ
せる。この状態は従来例を最大開口で使用した場
合に相当し極めて速い圧力の立上りを示す。供給
通路圧力が上昇するにつれピストン１７が左行し
続けるが、自己の左行に応じて可変絞りを構成す
る横孔２０を環状溝２１の右端で覆い開度を減ず
る。従つてピストン１７の左行速度、それに応じ
て設定圧力の上昇速度が低下するので第３図に示
すように緩やかにサージ圧を伴なうことなく最終
設定圧力に到達する。 When the pressure starts to rise, the poppet 12 tries to move to the right under the elastic force of the spring 28 due to the supply pressure applied to the area of action given by the difference between the inner diameter of the seat 11 and the projected area of the hole 13 of the poppet 12. On the other hand, the pressure oil in the supply passage 3 that flows into the back chamber 24 through the hole 14 of the poppet 12, the passage 19 of the axis of the inner piston 15 and the rod 16, the variable throttle 30, and the horizontal hole 22 provides a larger area of action. The piston 17 held moves to the left and increases the elastic force of the spring 28. This state corresponds to the case where the conventional example is used with the maximum opening, and shows an extremely rapid rise in pressure. As the supply passage pressure increases, the piston 17 continues to move to the left, but depending on the piston's left movement, the right end of the annular groove 21 covers the horizontal hole 20 constituting a variable throttle to reduce the opening degree. Therefore, the leftward movement speed of the piston 17 and the rising speed of the set pressure decrease accordingly, so that the final set pressure is reached gradually without any surge pressure, as shown in FIG.
以上述べたように本考案によれば、弁の開閉を
司るポペツトを弾圧し圧力を設定するバネの撓み
を供給圧力に応じて増加させるべく移動するピス
トンを設け、ピストンの移動に必要な圧油の供給
通路にピストンの移動に応じて通過面積の変化す
る開口を設けたので、油圧モータの急激な起動・
制動を行なつても供給通路の圧油は操作直後速や
かに圧力が上昇し、最終設定圧力に近付くにつれ
て圧力上昇速度が小さくなる。よつて、圧力の立
上りが速いことから応答性の低下を伴わず、最終
設定圧力附近では圧力上昇速度が充分減速され、
サージ圧が発生しにくいリリーフ弁を提供でき
た。
As described above, according to the present invention, a piston is provided that moves to increase the deflection of the spring that presses the poppet that controls the opening and closing of the valve and sets the pressure in accordance with the supply pressure, and the pressure oil required for the movement of the piston is Since the supply passage has an opening whose passage area changes according to the movement of the piston, sudden startup of the hydraulic motor and
Even if braking is performed, the pressure of the pressure oil in the supply passage increases immediately after the operation, and the rate of pressure increase becomes smaller as the pressure approaches the final set pressure. Therefore, since the pressure rises quickly, there is no decrease in responsiveness, and the pressure rise speed is sufficiently slowed down near the final set pressure.
We were able to provide a relief valve that is less likely to generate surge pressure.
第１図は本考案による一実施例を示す縦断面
図、第２図は従来技術によるリリーフ弁の供給通
路に生起する圧力と時間の関係を示す図、第３図
は本考案によるリリーフ弁の供給通路に生起する
圧力と時間の関係を示す図である。
１…リリーフ弁、２…弁本体、３…供給通路、
４…戻り通路、１１…シート、１２…ポペツト、
１３…孔、１７…ピストン、２８…バネ、３０…
可変絞り、３１…差動部材。
FIG. 1 is a longitudinal cross-sectional view showing an embodiment of the present invention, FIG. 2 is a diagram showing the relationship between the pressure generated in the supply passage of a relief valve according to the prior art and time, and FIG. 3 is a diagram showing the relationship between pressure and time of the relief valve according to the present invention. FIG. 3 is a diagram showing the relationship between the pressure generated in the supply passage and time. 1... Relief valve, 2... Valve body, 3... Supply passage,
4...Return passage, 11...Seat, 12...Poppet,
13...hole, 17...piston, 28...spring, 30...
variable aperture, 31... differential member;
Claims (1)
給通路３と戻り通路４とを連通・遮断するポペツ
ト１２と、前記孔と同軸の孔９に挿入され前記シ
ート１１より大なる受圧面積を有するピストン１
７と、ピストン１７の背面が露出する空間を閉止
して形成した背室２４と、圧縮され両端がそれぞ
れポペツト１２をシート１１へ、ピストン１７を
背室２４背後の壁面へ弾圧するバネ２８と、ポペ
ツト１２の他端側の軸心に穿設され供給通路３と
連通した孔１３に一端を、他端はピストン１７の
軸心を貫通する孔１８とにそれぞれ摺動自在に嵌
合された差動部材３１と、供給通路３の圧油を前
記背室２４へ供給すべく設けた通路よりなるリリ
ーフ弁において、前記供給通路３と背室２４との
間の通路が、ピストン１７と差動部材３１との嵌
合部分に形成されバネ２８の弾圧力に対向し印加
される背室の圧力によって動くピストンの移動量
に応じて開口を減ずる可変絞り３０と、差動部材
３１の内部を介して供給通路３を可変絞りの一側
に連通する通路と、ピストン１７内部を介して背
室２４を可変絞り３０の他側へ連通する通路より
なることを特徴とするリリーフ弁。 A poppet 12 is inserted into a hole in the main body and has one end facing the sheet 11 to communicate/block the supply passage 3 and the return passage 4, and a poppet 12 is inserted into a hole 9 coaxial with the hole and has a pressure-receiving area larger than the sheet 11. piston 1
7, a back chamber 24 formed by closing the space where the back surface of the piston 17 is exposed, and a compressed spring 28 whose both ends press the poppet 12 against the seat 11 and the piston 17 against the wall behind the back chamber 24, respectively. One end of the poppet 12 is slidably fitted into a hole 13 bored in the axis of the other end of the poppet 12 and communicating with the supply passage 3, and the other end is slidably fitted into a hole 18 passing through the axis of the piston 17. In the relief valve including a moving member 31 and a passage provided to supply pressure oil from the supply passage 3 to the back chamber 24, the passage between the supply passage 3 and the back chamber 24 is connected to the piston 17 and the differential member. A variable aperture 30 is formed at the fitting portion of the differential member 31 and reduces the opening in accordance with the amount of movement of the piston that is moved by the pressure of the back chamber that opposes the elastic force of the spring 28. A relief valve comprising a passage communicating the supply passage 3 with one side of the variable throttle and a passage communicating the back chamber 24 with the other side of the variable throttle 30 through the inside of the piston 17.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17789280U JPS6321814Y2 (en) | 1980-12-11 | 1980-12-11 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17789280U JPS6321814Y2 (en) | 1980-12-11 | 1980-12-11 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57100675U JPS57100675U (en) | 1982-06-21 |
| JPS6321814Y2 true JPS6321814Y2 (en) | 1988-06-15 |
Family
ID=29972183
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17789280U Expired JPS6321814Y2 (en) | 1980-12-11 | 1980-12-11 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6321814Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009512824A (en) * | 2005-10-20 | 2009-03-26 | ポクラン イドロリク アンドゥストリ | Valve with buffered opening system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0527683Y2 (en) * | 1987-03-23 | 1993-07-15 | ||
| KR100400691B1 (en) * | 1996-08-22 | 2003-12-31 | 코프스-불칸, 인코포레이티드 | Spring-Assisted Multi-Nozzles and Heat Reduction |
| JP5664856B2 (en) * | 2010-12-28 | 2015-02-04 | 株式会社不二越 | Relief valve |
-
1980
- 1980-12-11 JP JP17789280U patent/JPS6321814Y2/ja not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009512824A (en) * | 2005-10-20 | 2009-03-26 | ポクラン イドロリク アンドゥストリ | Valve with buffered opening system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57100675U (en) | 1982-06-21 |
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