JPH03172698A - Pressure pulsation absorbing device - Google Patents
Pressure pulsation absorbing deviceInfo
- Publication number
- JPH03172698A JPH03172698A JP30938289A JP30938289A JPH03172698A JP H03172698 A JPH03172698 A JP H03172698A JP 30938289 A JP30938289 A JP 30938289A JP 30938289 A JP30938289 A JP 30938289A JP H03172698 A JPH03172698 A JP H03172698A
- Authority
- JP
- Japan
- Prior art keywords
- gas
- pressure pulsation
- liquid
- piping
- porous
- 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
- 230000010349 pulsation Effects 0.000 title claims abstract description 35
- 239000007788 liquid Substances 0.000 claims abstract description 37
- 239000000463 material Substances 0.000 claims abstract description 16
- 239000011148 porous material Substances 0.000 claims abstract description 6
- 238000013016 damping Methods 0.000 abstract description 4
- 239000002184 metal Substances 0.000 abstract description 4
- 229910052751 metal Inorganic materials 0.000 abstract description 4
- 230000035699 permeability Effects 0.000 abstract description 2
- 238000007789 sealing Methods 0.000 abstract 2
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 7
- 239000006096 absorbing agent Substances 0.000 description 4
- 230000002238 attenuated effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、例えば水や油を移送するポンプなどの配管に
適用される圧力脈動吸収装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a pressure pulsation absorbing device applied to piping such as a pump for transferring water or oil.
第７図は従来の圧力脈動吸収装置の構造説明図である。 FIG. 7 is a structural explanatory diagram of a conventional pressure pulsation absorbing device.
図において、従来の圧力脈動吸収装置には同図（ａ）に
示すサイドブランチ（枝管）１０、同郡Φ）に示す拡大
管１１、同図（Ｃ）に示すレサーバタンク１２、同図（
ｄ）に示すアキュムレータ１３などがあり、何れも配管
１に比べてかなり大きな形状で、配管１内における液体
５の圧力脈動を吸収して減衰させる。In the figure, the conventional pressure pulsation absorbing device includes a side branch (branch pipe) 10 shown in FIG. (
There is an accumulator 13 shown in d), which has a considerably larger shape than the pipe 1, and absorbs and attenuates the pressure pulsation of the liquid 5 within the pipe 1.
上記のような従来の圧力脈動吸収装置において、第７図
（ａ）に示すサイドブランチ１０は、チューニングされ
る周波数の幅が狭く、僅かな脈動の変化で大幅に吸収量
が異る。また、同図ら）に示す拡大管１１は、大きな拡
大比をとらないと吸収効果が得られず、大形化、圧力損
失の増加、流れによる２次騒音の発生などの併置を伴う
。また、同図（Ｃ）に示すリザーバタンク１２は容量が
大きく、設置場所が限定される。また、同図（ｄ）に示
すアキュムレータ１３は大きく、高価で、また配管１内
の１部にのみ作用するので、吸収効果に限界がある。In the conventional pressure pulsation absorbing device as described above, the side branch 10 shown in FIG. 7(a) has a narrow frequency range to be tuned, and the amount of absorption varies greatly with a slight change in pulsation. In addition, the expansion tube 11 shown in FIGS. 3A and 3B cannot obtain an absorption effect unless it has a large expansion ratio, and is accompanied by an increase in size, an increase in pressure loss, and the generation of secondary noise due to the flow. In addition, the reservoir tank 12 shown in FIG. 3(C) has a large capacity, and its installation location is limited. In addition, the accumulator 13 shown in FIG. 3(d) is large and expensive, and acts only on a portion of the pipe 1, so there is a limit to its absorption effect.
本発明に係る圧力脈動吸収装置は上記課題の解決を目的
にしており、多孔材を介して配管内の液体と接して保持
されるとともに内部に気体が封入され柔軟性を有する材
料で作られた容器を備えた構成を特徴としている。The pressure pulsation absorbing device according to the present invention aims to solve the above problems, and is made of a flexible material that is held in contact with the liquid in the piping through a porous material, and has gas sealed inside. It is characterized by a configuration that includes a container.
即ち、本発明に係る圧力脈動吸収装置においては、内部
に気体が封入された柔軟な容器が多孔材により配管内の
液体と接するように保持されており、容器内の気体が配
管内における液体の圧力脈動を吸収して減衰させる。That is, in the pressure pulsation absorbing device according to the present invention, a flexible container with gas sealed inside is held by a porous material so as to be in contact with the liquid in the piping, and the gas in the container absorbs the liquid in the piping. Absorbs and dampens pressure pulsations.
第１図乃至第４図はそれぞれ本発明の第一乃至第四の実
施例に係る圧力脈動吸収装置の構造説明図、第５図およ
び第６図はこれらの作用説明図である。第１図において
、第一の実施例に係る圧力脈動吸収装置は図に示すよう
に、配管ｌを拡大させたケーシング２に対して配管１と
同一径の多孔板或いは多孔質金属など通気性のある材料
で作られた多孔管４が設置され、この多孔管４とケーシ
ング２との間にできた環状部にゴムなど柔軟で延性に冨
む材料で作られた気体容器３が設置されている。気体容
器３には気体封入栓７が設けられており、ここから気体
６が封入されている。1 to 4 are structural explanatory diagrams of pressure pulsation absorbers according to first to fourth embodiments of the present invention, and FIGS. 5 and 6 are explanatory diagrams of their operation. In Fig. 1, the pressure pulsation absorbing device according to the first embodiment has a casing 2 with an enlarged pipe 1 and a permeable material such as a perforated plate or porous metal having the same diameter as the pipe 1. A perforated pipe 4 made of a certain material is installed, and a gas container 3 made of a flexible and ductile material such as rubber is installed in an annular portion formed between the perforated pipe 4 and the casing 2. . The gas container 3 is provided with a gas filling stopper 7, from which gas 6 is sealed.
第２図において、第二の実施例に係る圧力脈動吸収装置
は図に示すように、配管１を拡大させずに多孔板或いは
多孔質金属などで作られた多孔管４の径を絞り、第一の
実施例と同様に液体柱の周囲がゴムなどの柔軟で延性に
富む材料で製られた気体容器３と接するようにしている
。In FIG. 2, the pressure pulsation absorber according to the second embodiment reduces the diameter of the porous pipe 4 made of a porous plate or porous metal without enlarging the pipe 1, as shown in the figure. As in the first embodiment, the periphery of the liquid column is in contact with a gas container 3 made of a flexible and ductile material such as rubber.
第３図において、第三の実施例に係る圧力脈動吸収装置
は図に示すように、多孔板或いは多孔質金属などで作ら
れた多孔管４を筒状にしてその中に予め気体６を封入し
た気体容器３を入れ、それを配管１内に設置している。In FIG. 3, the pressure pulsation absorbing device according to the third embodiment has a porous tube 4 made of a porous plate or porous metal shaped into a cylinder, and a gas 6 is sealed in advance as shown in the figure. A gas container 3 is placed inside the piping 1.
第４図において、第四の実施例に係る圧力脈動吸収装置
は図に示すように、配管１の一側部に多孔管４を介して
ポケット２を設け、その中に気体容器３を設けており、
第三の実施例と同様に液体柱の一部がゴムなどの柔軟で
延性に冨む材料を介して気体６と接するようにしている
。In FIG. 4, the pressure pulsation absorber according to the fourth embodiment has a pocket 2 provided on one side of the piping 1 through a porous pipe 4, and a gas container 3 provided therein. Ori,
As in the third embodiment, a portion of the liquid column is brought into contact with the gas 6 through a flexible and ductile material such as rubber.
なお、上記の４実施例における気体容器３の材料として
は、配管１内の液体５と音響特性インピーダンスが殆ん
ど一致する特性をもつものが良く、水の場合にはρＣゴ
ムが最適である。It should be noted that the material for the gas container 3 in the above four embodiments should preferably have a characteristic whose acoustic characteristic impedance almost matches that of the liquid 5 in the pipe 1, and in the case of water, ρC rubber is optimal. .
このように、上記の第一および第二の実施例に係る圧力
脈動吸収装置は、ゴムのような柔軟で延性に冨んだ材料
で作られた環状の気体容器３を配管ｌの内壁に内接して
設置し、この気体容器３の内部に配管１内を通る液体５
と圧力がバランスするように気体６を充填することによ
り、液体柱の周わりに圧縮性に冨む気体６を配置するよ
うにし、また気体容器３を多孔板や通気性を有する多孔
質の材料で作られた多孔管４の中に入れることにより、
気体容器３の形状を保つとともに液体５の周囲が気体６
で包まれるようになっている。従って、配管ｌ内の液体
５の圧力脈動は、後述の理由により最小のｃｕｔ ｏｆ
ｆ周波数以下の低周波数領域で大幅に減衰する。その減
衰量は気体容器３の長さに比例し、必要に応じて自由に
調節できる。また、液体５と気体６との境界はゴムなど
柔軟で延性に富む材料によって離隔されていて液体５中
に気体６が混合することはないが、力は相互に作用し合
って自由境界面に近いものが得られる。さらに、多孔板
などで製られた多孔管４内に気体容器３を挿入すること
により、液体５の圧力が下がっても気体６の圧力は多孔
管４で支えられ、気体容器３が破裂することはない。こ
のため、気体容器３は非常に柔軟な材料を使用でき、自
由境界面の条件に掻く近付けることができる。また、液
体５の圧力が設定値以上に上昇した場合は、気体容器３
は縮むだけであり、特に問題は起こらない。ポンプなど
の圧力脈動は一般に周波数が低く、非常に効果的に減衰
できる。仮に、液体柱の周わりを気体６が包む理想的な
自由境界面の条件が実現できれば、理論的には十分に低
い周波数頭域で配管ｌの直径相当の長さ当り約３８ｄｂ
と大きな圧力脈動の減衰が得られる。実際には種々の制
約があるためにここまで減音はしないが、最小のｃｕｔ
ｏｆｆ周波数以下の総ての周波数で減衰が期待できる
。As described above, the pressure pulsation absorbing devices according to the first and second embodiments have an annular gas container 3 made of a flexible and ductile material such as rubber inside the inner wall of the pipe 1. The liquid 5 passing through the pipe 1 inside the gas container 3
By filling the gas 6 so that the pressure is balanced, the highly compressible gas 6 is placed around the liquid column, and the gas container 3 is made of a perforated plate or a porous material with air permeability. By putting it into the made porous tube 4,
While maintaining the shape of the gas container 3, the surroundings of the liquid 5 are filled with gas 6.
It is designed to be wrapped in Therefore, the pressure pulsation of the liquid 5 in the pipe 1 is minimized by the minimum cut of
Significant attenuation occurs in the low frequency region below the f frequency. The amount of attenuation is proportional to the length of the gas container 3, and can be freely adjusted as necessary. In addition, the boundary between the liquid 5 and the gas 6 is separated by a flexible and ductile material such as rubber, so the gas 6 does not mix into the liquid 5, but the forces interact with each other and form a free boundary surface. You can get something close. Furthermore, by inserting the gas container 3 into a perforated tube 4 made of a perforated plate or the like, even if the pressure of the liquid 5 drops, the pressure of the gas 6 will be supported by the perforated tube 4, and the gas container 3 will not burst. There isn't. Therefore, a very flexible material can be used for the gas container 3, and the conditions of the free boundary surface can be closely approached. Additionally, if the pressure of the liquid 5 rises above the set value, the gas container 3
will simply shrink, and no particular problem will occur. Pressure pulsations from pumps and the like generally have low frequencies and can be damped very effectively. If an ideal free boundary surface condition in which the gas 6 surrounds the liquid column can be realized, theoretically the frequency range will be approximately 38 dB per length equivalent to the diameter of the pipe l in a sufficiently low frequency range.
This results in large pressure pulsation attenuation. In reality, due to various restrictions, the sound will not be reduced to this extent, but the minimum cut
Attenuation can be expected at all frequencies below the off frequency.
仮に、液体柱の周わりを気体６が包む理想的な自由境界
面の条件が実現できたとする。この場合、第５図に示す
ような液体柱の中の圧力脈動は配管の断面内で特定の圧
力脈動モードを形成して伝播していく。配管内の任意の
点（ｘ、 ｙ、 ｚ）で（ｍ、ｎ）モードを形成す
る音圧ＰＭ１％（Ｘ＋３’。Suppose that an ideal free boundary surface condition in which the gas 6 surrounds the liquid column can be realized. In this case, the pressure pulsations in the liquid column as shown in FIG. 5 form a specific pressure pulsation mode within the cross section of the pipe and propagate. Sound pressure PM1% (X+3') forming (m, n) mode at any point (x, y, z) in the pipe.
２） は次式で表わされる。2) is expressed by the following equation.
Ｐ□（ｘ＋ｙ＋ｚ） ＝
ここで、Ｚ、、Ｘ、はそれぞれＸ方向、２方向の配管の
断面寸法、Ａ□はｘ＝０断面における振幅、ｇｙｍ＋
ｇｕｎはそれぞれＸ方向、２方向のｍ次。P□(x+y+z) = Here, Z, , X are the cross-sectional dimensions of the piping in the X direction and two directions, respectively, A□ is the amplitude at the x=0 cross section, gym+
The guns are m-order in the X direction and 2 directions, respectively.
ｎ次の固有値で、配管壁の境界条件によって求まる。ω
は角周波数、ｔは時刻、Ｃは音速である。It is an n-th eigenvalue, determined by the boundary conditions of the pipe wall. ω
is the angular frequency, t is the time, and C is the speed of sound.
τ、７は（ｍ、ｎ）モードを形成してＸ方向に伝播する
圧力脈動の透過係数で、次式で与えられる。τ, 7 is the transmission coefficient of pressure pulsations that form the (m, n) mode and propagate in the X direction, and is given by the following equation.
・・・・・・・・・・・・（２）
ここで、復号−は下流方向への伝播を、＋は上流方向へ
の伝播を表わす、λは波長である。τ、７の根号内が正
の場合はＸ方向に圧力脈動の減衰は無いが、複素数また
は純虚数のときはＸ方向に減衰する。単位長さ当りの減
音＠ Ａ ｔｔ、、は次式で表わされる。(2) Here, decoding - represents propagation in the downstream direction, + represents propagation in the upstream direction, and λ is the wavelength. When the radical of τ, 7 is positive, there is no attenuation of pressure pulsation in the X direction, but when it is a complex number or a pure imaginary number, it is attenuated in the X direction. The sound reduction per unit length @A tt, is expressed by the following formula.
ω
Ａｔｔ、、＝ −８，６８１，（ｒ、、＋） （ｄｂ
／ｍ） −（３）に
こで、１．（）はアーキュメントの虚数部を示す。ｇｙ
ｍ＋ ｇ、ｎ は配管壁の表面インピーダンスを自
由境界面の条件とした次式の解である。ω Att,, = −8,681, (r,, +) (db
/m) -(3) smile, 1. () indicates the imaginary part of the arcument. gy
m+g,n is the solution of the following equation with the surface impedance of the pipe wall as a free boundary surface condition.
ここで、πは円周率、ｉは虚数単位、ζ７．ぐ２はそれ
ぞれＸ方向、２方向に垂直な配管壁の表面インピーダン
スである。通常の銅製やコンクリート製の剛壁の配管で
はζ７．ζ、−■となり、但し、ｍ、ｎ＝ｏ、１゜
２、３ ・ ・ ・
となる。つまり、ｍ＝ｎ＝ｏなる解が存在し、また式（
２）からあらゆる波長（周波数）に対してτ。。Here, π is pi, i is an imaginary unit, and ζ7. 2 is the surface impedance of the pipe wall perpendicular to the X direction and the 2 directions, respectively. Normal pipes with rigid walls made of copper or concrete have a diameter of ζ7. ζ, −■, but m, n=o, 1°2, 3 ・ ・ ・ . In other words, there is a solution m=n=o, and the formula (
2) for any wavelength (frequency). .
王１なる解が存在し、１．（τ。。）＝０となって式（
３）からＡ ｔ ｔ ｏ。＝０なる解が存在する。即ち
、どのような周波数に対しても配管断面内を平面波（配
管断面内で音圧ゲイン、位相が一定な音波モード）とし
て減衰することなく伝播する。There is a solution called King 1, and 1. (τ..)=0 and the formula (
3) to A t to. =0 exists. That is, any frequency propagates within the pipe cross section as a plane wave (a sound wave mode with constant sound pressure gain and phase within the pipe cross section) without attenuation.
液体柱の外側が気体で包まれている場合は、気体の音響
特性インピーダンスは液体の音響特性インピーダンスに
比べて非常に小さく、この場合はζア、ζｚ”ｉｏとな
る。この関係を式（４）、 （５）に代入すると、
但し、ｆは周波数である。When the outside of the liquid column is surrounded by gas, the acoustic characteristic impedance of the gas is very small compared to the acoustic characteristic impedance of the liquid, and in this case, ζa and ζz”io. ), (5), where f is the frequency.
内が≧Ｏの場合は１．（τ□） ＝０となるが、根号内がくＯ 〉０となって減衰が生じる。If the inside is ≧O, then 1. (τ□) = 0, but the radical O >0 and attenuation occurs.
波数を
・・・・・・・・・・・・・・・・・・・・・（８）前
述のように、根号
＝０となって減衰量
の場合は１．（τａｎ）
つまり、ｃｕｔ ｏｆｆ周
とすると、ｆ≧ｆｃｍで（ｍ、ｎ）モードは伝播し、ｆ
＜ ｆ ｃ、、で（ｍ、ｎ）モードは減衰する。The wave number is 1. (τan) In other words, if the cut off period is f≧fcm, the (m, n) mode propagates, and f
< f c, , the (m, n) mode is attenuated.
液体柱の周囲が気体の場合は、ｆ ＣＩＩＦＩの最小値
が但し、ｍ、ｎ＝１．２．３ ・ ・ ・となり、ｍ＝
０またはｎ＝０なる解は存在しない。When the surroundings of the liquid column are gas, the minimum value of f CIIFI is, however, m, n=1.2.3 ・ ・ ・ , m=
There is no solution where 0 or n=0.
この場合の透過係数は次式のようになる。The transmission coefficient in this case is as shown in the following equation.
となる。つまり、ｆ＜ｆｃｔｔ以下の周波数はどのよう
なモードも形成できず、減衰してしまうことになる。こ
れに対して、液体柱の外側が剛壁の場合にはｍ＝ｎ＝０
の解が存在するため、ｆ ｃｍｎの最小値はｒｃｏ。＝
Ｏとなり、総ての周波数が伝播モードを形成できる。becomes. In other words, no mode can be formed at frequencies below f<fctt, and the frequencies are attenuated. On the other hand, if the outside of the liquid column is a rigid wall, m=n=0
Since there exists a solution of , the minimum value of f cmn is rco. =
0, and all frequencies can form propagation modes.
因みに、’ｙ ””ｌｘ ＝１ｍの配管で液体を水とす
ると、Ｃ！：１１５００ｍ／ｓｅｃであるのでｆｃ＋＋
＝１０６１Ｈｚとなり、これ以下の周波数の圧力脈動
は減衰することになる。ｆ ＝５００Ｈｚの場合につい
て、式（８）。By the way, if the liquid is water in a pipe of 'y "" lx = 1 m, C! :11500m/sec, so fc++
= 1061 Hz, and pressure pulsations at frequencies below this are attenuated. For the case f = 500 Hz, equation (8).
（３）を用いて減衰量を求めると、Ａ ｔｔ＋ １＝
３４ ｄｂ／ｍとなり、理論的には非常に大きな減衰効
果が得られる。なお、参考までに液体柱の周囲が剛壁の
場合を第６図（ａ）に、また液体柱の周囲が気体の場合
を同図ら）に、それぞれの内部音圧モードを２次元表示
で示す。前者の場合は壁面で音圧層のモードであるのに
対し、後者の場合は壁外面で音圧節のモードが成り立つ
必要があり、これからみてもｍ＝０の解は成り立たない
ことが容易に推察される。When calculating the attenuation amount using (3), Attt+ 1=
34 db/m, which theoretically provides a very large attenuation effect. For reference, the internal sound pressure modes are shown in two-dimensional representations in Figure 6 (a) when the liquid column is surrounded by a rigid wall, and in Figure 6 (a) when the liquid column is surrounded by gas). . In the former case, the mode is the sound pressure layer on the wall surface, whereas in the latter case, the mode of the sound pressure node must hold on the outer surface of the wall, and it is easy to see from this that the solution for m = 0 does not hold. It is inferred.
また、本実施例は配管の断面が矩形の場合について述べ
たが、断面が円形、或いはその他任意の形状の場合でも
同様である。Further, although the present embodiment has been described with respect to the case where the cross section of the piping is rectangular, the same applies to cases where the cross section is circular or any other arbitrary shape.
また、第三および第四の実施例に係る圧力脈動吸収装置
は、ゴムのような柔軟で延性に富んだ材料で作られた柱
状の気体容器３を配管ｌ内に挿入し、その気体容器３の
内部に配管ｌを通る液体５と圧力がバランスするように
気体６を充填することにより、液体柱の一部に必ず圧縮
性に富む気体６が配置され、また気体容器３を多孔板や
通気性を有する多孔質の材料で製られた多孔管４の中に
入れることにより、気体容器３の形状を保つとともに液
体５の内部に気体６が存在して液体５と気体６との間で
直接力が作用し合うようになっている。この場合は、液
体５の周囲が気体６で包まれている場合はど顕著な圧力
脈動の減衰効果は得られないが、液体５中に気体６が占
める割合いに応じて相当の減衰量が得られる。また、既
存の配管１を変更せずに気体容器３を挿入するだけで実
施が可能である。圧力脈動の減衰量は第一および第二の
実施例の場合と同様に気体容器３の長さに比例し、また
多孔管４の作用も同様である。In addition, the pressure pulsation absorbing devices according to the third and fourth embodiments include a columnar gas container 3 made of a flexible and highly ductile material such as rubber, which is inserted into the pipe l, and the gas container 3 By filling the inside of the container with gas 6 so that the pressure is balanced with the liquid 5 passing through the pipe 1, the highly compressible gas 6 is always placed in a part of the liquid column. By placing the gas in the porous tube 4 made of a porous material with properties, the shape of the gas container 3 is maintained, and the gas 6 is present inside the liquid 5, so that the liquid 5 and the gas 6 are directly connected to each other. Forces interact with each other. In this case, if the liquid 5 is surrounded by the gas 6, no significant pressure pulsation damping effect will be obtained, but depending on the proportion of the gas 6 in the liquid 5, a considerable amount of attenuation will occur. can get. Further, the present invention can be implemented by simply inserting the gas container 3 without changing the existing piping 1. The amount of attenuation of the pressure pulsation is proportional to the length of the gas container 3 as in the first and second embodiments, and the effect of the perforated tube 4 is also similar.
本発明に係る圧力脈動吸収装置は前記の１ｉｌ）／）構
成されており、容器内の気体が配管内における液体の圧
力脈動を吸収して減衰させるので、小形で安価であると
ともに、最小のｃｕｔ ｏｆｆ周波数以下の総ての周波
数で減衰が行われる。The pressure pulsation absorbing device according to the present invention has the above-described structure, and the gas in the container absorbs and attenuates the pressure pulsation of the liquid in the piping, so it is small and inexpensive, and has a minimum cut. Attenuation is performed at all frequencies below the off frequency.
第１図乃至第４図はそれぞれ本発明の第一乃至第四の実
施例に係る圧力脈動吸収装置の断面図で、（ｂ）図はそ
れぞれの（ａ）図におけるｂ−ｂ断面図、第５図および
第６図はこれらの作用説明図、第７図（ａ）〜（ｄ）は
それぞれ従来の圧力脈動吸収装置の断面図である。
１・・・配管、２・・・ケーシング、３・・・気体容器
、４・・・多孔管、５・・・液体、６・・・気体、７・
・・気体封入栓。1 to 4 are sectional views of pressure pulsation absorbers according to first to fourth embodiments of the present invention, respectively, and FIG. 1(b) is a bb sectional view in FIG. 5 and 6 are explanatory diagrams of these functions, and FIGS. 7(a) to 7(d) are sectional views of conventional pressure pulsation absorbing devices, respectively. DESCRIPTION OF SYMBOLS 1... Piping, 2... Casing, 3... Gas container, 4... Porous pipe, 5... Liquid, 6... Gas, 7...
・Gas filled plug.
Claims (1)
に内部に気体が封入され柔軟性を有する材料で作られた
容器を備えたことを特徴とする圧力脈動吸収装置。A pressure pulsation absorbing device comprising a container made of a flexible material that is held in contact with a liquid in piping through a porous material, has a gas sealed inside, and is made of a flexible material.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1309382A JP2734478B2 (en) | 1989-11-30 | 1989-11-30 | Pressure pulsation absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1309382A JP2734478B2 (en) | 1989-11-30 | 1989-11-30 | Pressure pulsation absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03172698A true JPH03172698A (en) | 1991-07-26 |
| JP2734478B2 JP2734478B2 (en) | 1998-03-30 |
Family
ID=17992335
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1309382A Expired - Lifetime JP2734478B2 (en) | 1989-11-30 | 1989-11-30 | Pressure pulsation absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2734478B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0814469A (en) * | 1994-07-01 | 1996-01-16 | Hitachi Constr Mach Co Ltd | Hydraulic pulsation reducing device |
| JPH08500658A (en) * | 1993-06-22 | 1996-01-23 | ゲフィピ アクチェン ゲゼルシャフト | Vibration noise attenuator for hydraulic equipment |
| JPH1130387A (en) * | 1997-07-09 | 1999-02-02 | Mitsubishi Heavy Ind Ltd | Fluctuating pressure reduction device |
| WO2005092515A1 (en) * | 2004-03-25 | 2005-10-06 | Toray Industries, Inc. | Painting device, painting method, and display member provided therefrom |
| JP2010104883A (en) * | 2008-10-29 | 2010-05-13 | Hitachi Maxell Ltd | Coating apparatus and method of manufacturing functional support using the same |
| JP2016087482A (en) * | 2014-10-29 | 2016-05-23 | 中外炉工業株式会社 | Coating device and coating method |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS563394A (en) * | 1979-06-18 | 1981-01-14 | Tonen Sekiyukagaku Kk | Damping device of water hammer |
-
1989
- 1989-11-30 JP JP1309382A patent/JP2734478B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS563394A (en) * | 1979-06-18 | 1981-01-14 | Tonen Sekiyukagaku Kk | Damping device of water hammer |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08500658A (en) * | 1993-06-22 | 1996-01-23 | ゲフィピ アクチェン ゲゼルシャフト | Vibration noise attenuator for hydraulic equipment |
| JPH0814469A (en) * | 1994-07-01 | 1996-01-16 | Hitachi Constr Mach Co Ltd | Hydraulic pulsation reducing device |
| JPH1130387A (en) * | 1997-07-09 | 1999-02-02 | Mitsubishi Heavy Ind Ltd | Fluctuating pressure reduction device |
| WO2005092515A1 (en) * | 2004-03-25 | 2005-10-06 | Toray Industries, Inc. | Painting device, painting method, and display member provided therefrom |
| JP2010104883A (en) * | 2008-10-29 | 2010-05-13 | Hitachi Maxell Ltd | Coating apparatus and method of manufacturing functional support using the same |
| JP2016087482A (en) * | 2014-10-29 | 2016-05-23 | 中外炉工業株式会社 | Coating device and coating method |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2734478B2 (en) | 1998-03-30 |
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