JPH04191594A - Piping vibration preventing device - Google Patents
Piping vibration preventing deviceInfo
- Publication number
- JPH04191594A JPH04191594A JP31979090A JP31979090A JPH04191594A JP H04191594 A JPH04191594 A JP H04191594A JP 31979090 A JP31979090 A JP 31979090A JP 31979090 A JP31979090 A JP 31979090A JP H04191594 A JPH04191594 A JP H04191594A
- Authority
- JP
- Japan
- Prior art keywords
- inner cylinder
- passage
- cylinder
- piping
- spiral
- 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
- 239000012530 fluid Substances 0.000 claims abstract description 24
- 230000010349 pulsation Effects 0.000 claims abstract description 20
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 8
- 239000010959 steel Substances 0.000 claims abstract description 8
- 230000002265 prevention Effects 0.000 claims description 12
- 238000013016 damping Methods 0.000 claims description 6
- 238000003466 welding Methods 0.000 abstract description 3
- 238000000034 method Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
- 238000013461 design Methods 0.000 description 3
- 238000005520 cutting process Methods 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 229910000851 Alloy steel Inorganic materials 0.000 description 1
- 229910000975 Carbon steel Inorganic materials 0.000 description 1
- 229910001018 Cast iron Inorganic materials 0.000 description 1
- 229910001208 Crucible steel Inorganic materials 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000010962 carbon steel Substances 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Pipe Accessories (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の目的〕
（産業上の利用分野）
本発明はポンプ等の排出圧力に脈動を生ずる流体機械に
接続した配管に取付けて、排出流体の脈動を除去または
減衰させ、下流に配設した配管の振動を防止する装置に
関する。[Detailed Description of the Invention] [Object of the Invention] (Industrial Field of Application) The present invention is a system for removing or attenuating the pulsation of the discharged fluid by attaching it to a pipe connected to a fluid machine such as a pump that causes pulsations in the discharge pressure. , relates to a device for preventing vibration of piping installed downstream.
（従来の技術）
従来、配管の振動を防止するため、ポンプ等の排出圧力
の脈動を除去または減衰させる方法としてはつぎのよう
なものが知られている。すなわち、（ａ）第１０図に示
すように、主流路１０の側方に端部が閉じた分岐管１１
を設け、分岐管１１の閉止部１２から反射してくる圧力
波が分岐部に戻ったとき主流の脈動から半波長遅れるよ
うに分岐の長さを決定する。そして閉止部１２から反射
した圧力波が主流路１０内の主流に伝達されることによ
り、合流点（分岐点）下流の流れをはソ平滑にする。こ
こで、分岐管１２の主流路の１０の中心からの長さはｆ
２ （ｎ−１）＋１１ Ｘλ／４となる（ここにｎは
正の整数、λは脈動の波長である）。(Prior Art) Conventionally, the following methods are known as methods for removing or attenuating pulsations in the discharge pressure of a pump or the like in order to prevent vibrations in piping. That is, (a) as shown in FIG. 10, a branch pipe 11 whose end is closed on the side of the main channel 10
is provided, and the length of the branch is determined so that when the pressure wave reflected from the closing part 12 of the branch pipe 11 returns to the branch part, it is delayed by half a wavelength from the pulsation of the main stream. The pressure waves reflected from the closing part 12 are transmitted to the main flow in the main flow path 10, thereby making the flow downstream of the confluence (branching point) smooth. Here, the length of the main flow path of the branch pipe 12 from the center of 10 is f
2 (n-1)+11 Xλ/4 (where n is a positive integer and λ is the wavelength of the pulsation).
（ｂ）第１１図および第１２図に示すように、主流路１
０から分岐し下流で再び主流路１０に合流するＵ字型バ
イパス管１３、またはらせん状バイパス管１４を設ける
。そして、それぞれバイパス管１３．１４を通った脈動
する圧力波が主流路１０との合流部で主流路１０内の脈
動する圧力波から半波長遅れるようにバイパス管１３．
１４の長さをそれぞれ決定する。これによりバイパス管
１３．１４を通った脈動圧力波が主流路１０内の主流に
伝達されることにより、合流点（分岐点）下流の流れを
はゾ平滑にすることができる。バイパス管１３．１４の
長さは（ｎ＋１／２）λとなる。(b) As shown in FIGS. 11 and 12, the main flow path 1
A U-shaped bypass pipe 13 or a spiral bypass pipe 14 is provided which branches from 0 and joins the main flow path 10 again downstream. Bypass pipes 13 and 14 are arranged such that the pulsating pressure waves passing through bypass pipes 13 and 14 are delayed by half a wavelength from the pulsating pressure waves in main flow passage 10 at the junction with main flow passage 10, respectively.
14 lengths are determined. As a result, the pulsating pressure waves passing through the bypass pipes 13 and 14 are transmitted to the main flow in the main flow path 10, so that the flow downstream of the merging point (branching point) can be made very smooth. The length of the bypass pipes 13 and 14 is (n+1/2)λ.
（発明が解決しようとする課題）
しかしながら、上記の従来のいずれの方法も管から分岐
管またはバイパス管を設けるため、かなりのスペースを
必要とし、さらに、そのためのサポートや保温を必要と
する。とくに、第１２図のものではバイパス管１４の形
成に３次元の曲げ加］−が必要であるため、その加工お
よび保守が極めて困難であった。(Problems to be Solved by the Invention) However, in any of the above-mentioned conventional methods, a branch pipe or a bypass pipe is provided from the pipe, so a considerable space is required, and furthermore, support and heat insulation are required for this purpose. In particular, the one shown in FIG. 12 requires three-dimensional bending to form the bypass pipe 14, making its processing and maintenance extremely difficult.
本発明は、このような点に鑑みてなされたもので、ポン
プ等流体機械に接続する配管において、脈動による配管
振動の防止を、余分なスペースを要することなく、特別
な流路の設計方法および制振材料を利用して一層効果あ
るものとし、しかも流体機械に近い所でその下流の配管
内の脈動を防止または減少することを目的とする。The present invention has been made in view of these points, and uses a special flow path design method and method to prevent piping vibration caused by pulsation in piping connected to fluid machines such as pumps, without requiring extra space. The purpose is to make use of vibration damping materials more effective and to prevent or reduce pulsation in piping downstream of fluid machinery in locations close to it.
（課題を解決するための手段）
本発明は、流体機械から吐出された流体を二つの流路に
分岐し、これらの流路を通過した後合流させて脈動を減
衰する配管振動防止装置において、周囲にらせん板を固
定した内筒を外筒内に同心に配置し、内筒内に内側流路
を、また、内筒と外筒との間にらせん状流路を形成し、
さらにらせん板を制振鋼板により構成したことを特徴と
する配管振動防止装置に関する。(Means for Solving the Problems) The present invention provides a piping vibration prevention device that branches fluid discharged from a fluid machine into two flow paths, and after passing through these flow paths, merges the fluid to damp pulsation. An inner cylinder with a spiral plate fixed around it is arranged concentrically within the outer cylinder, an inner flow path is formed within the inner cylinder, and a spiral flow path is formed between the inner cylinder and the outer cylinder,
The present invention further relates to a piping vibration prevention device characterized in that the spiral plate is made of a damping steel plate.
また内側通路の断面積Ａｉと外側通路の断面積Ａｏとの
総和がこれら通路に接続される配管の断面積Ａｐにほぼ
等しく、かつ、断面積Ａｔと断面積Ａｏがほぼ等しく、
また、内側通路と外側通路の入口部における分岐点から
合流点に至るそれぞれの流体通路の長さの管が圧力脈動
波の波長の１／２にほぼ等しく、さらに、外側通路のら
せん部の１ピッチの長さをＰとすると、らせん部１ピッ
チ分での内側通路と外側通路の距離の差が（ここで、ｄ
ｏ・・・外側通路の内径
ｄｉ・・・内側通路の内径）
であることを特徴とする配管振動防止装置に関する。Further, the sum of the cross-sectional area Ai of the inner passage and the cross-sectional area Ao of the outer passage is approximately equal to the cross-sectional area Ap of the piping connected to these passages, and the cross-sectional area At and the cross-sectional area Ao are approximately equal,
Further, the length of each fluid passage from the branch point to the confluence point at the entrance of the inner passage and the outer passage is approximately equal to 1/2 of the wavelength of the pressure pulsating wave, and furthermore, the length of the tube of the spiral portion of the outer passage If the length of the pitch is P, then the difference in distance between the inner passage and the outer passage for one pitch of the spiral part is (here, d
o...Inner diameter of outer passage di...Inner diameter of inner passage) The present invention relates to a piping vibration prevention device characterized in that: o...inner diameter of outer passageway di...inner diameter of inner passageway).
（作 用）
つぎに第５図と第６図に基づいて本発明の配管振動防止
装置の流路の設計方法に基づく作用を説明する。(Function) Next, the function based on the flow path design method of the piping vibration prevention device of the present invention will be explained based on FIGS. 5 and 6.
（ａ）内側通路４の断面積Ａｉと外側通路３の断面積Ａ
。との総和は、圧力損失等の関係より、これらに接続さ
れる接続配管６ａの断面積Ａ にできるだけ近づけるよ
うにする。(a) Cross-sectional area Ai of the inner passage 4 and cross-sectional area A of the outer passage 3
. The sum of these should be made as close as possible to the cross-sectional area A of the connecting pipe 6a connected to these, considering pressure loss and the like.
（ｂ）また、出口部１ｂの合流点で、位相の異なる圧力
脈動液がバランスよく打ち消し合うためには、内側通路
４を通過してきた圧力脈動液と外側通路３を通過してき
た圧力脈動波がほぼ等しい圧−６＝
力波としての力（圧力×断面積）をもつことが望ましい
。したがって内側通路４の断面積Ａｉと外側通路３の断
面積Ａ。とをほぼ等しくする。(b) Also, in order for the pressure pulsating liquids having different phases to cancel each other out in a well-balanced manner at the confluence point of the outlet portion 1b, it is necessary that the pressure pulsating liquid that has passed through the inner passage 4 and the pressure pulsating waves that have passed through the outer passage 3 It is desirable to have approximately equal pressure - 6 = force as a force wave (pressure x cross-sectional area). Therefore, the cross-sectional area Ai of the inner passage 4 and the cross-sectional area A of the outer passage 3. and be approximately equal.
（ｃ）内側通路４と外側通路３の入口部１ａにおける分
岐点から合流点に至るそれぞれの流体通路の長さの差は
、圧力脈動の位相が１８０°ずれる距離、すなわち圧力
脈動の波長の１／２とする。(c) The difference in the length of the fluid passages from the branching point at the inlet 1a of the inner passage 4 and the outer passage 3 to the confluence point is the distance over which the phase of the pressure pulsation shifts by 180°, that is, 1 of the wavelength of the pressure pulsation. /2.
例えば、３０００ｒｐｍの羽根枚数５枚のポンプであれ
ば、水中の音速を１４００ｍ／ｓとしたとき、１波長は
１４００／ （３０００／６０）Ｘ５＝５．６ｍとなり
半波長は２．８ｍとなる。For example, in the case of a 3000 rpm pump with 5 blades, when the sound speed in water is 1400 m/s, one wavelength is 1400/(3000/60)X5=5.6 m, and a half wavelength is 2.8 m.
（ｄ）いま、外側通路３のらせん部の１ピッチの長さを
Ｐとすると、第５図と第６図に示すとおり、らせん部１
ピッチ分で内側通路４と外側通路３の距離の差は、
となる。ここで、ｄｏは、外側通路の内径、ｄｉは内側
通路の内径である。(d) Now, if the length of one pitch of the spiral portion of the outer passage 3 is P, as shown in FIGS. 5 and 6, the spiral portion 1
The difference in distance between the inner passage 4 and the outer passage 3 by the pitch is as follows. Here, do is the inner diameter of the outer passage, and di is the inner diameter of the inner passage.
（実施例）
以下、本発明の配管振動防止装置の実施例を第１図およ
び第２図を参照して説明する。(Example) Hereinafter, an example of the piping vibration prevention device of the present invention will be described with reference to FIGS. 1 and 2.
本発明の配管振動防止装置は、図示しない流体機械の吐
出口に接し、あるいは近接して設置される。The piping vibration prevention device of the present invention is installed in contact with or in the vicinity of a discharge port of a fluid machine (not shown).
本発明の配管振動防止装置は二重の同心円筒形すなわち
外筒１および内筒２を同心に設け、これら内外筒内に二
つの流路を形成したものである。The piping vibration prevention device of the present invention has a double concentric cylindrical shape, that is, an outer cylinder 1 and an inner cylinder 2 are provided concentrically, and two flow paths are formed in these inner and outer cylinders.
外筒１内にこれと同心に設けられた内筒２は外筒１より
もいくぶんその長さが短く、かつ内筒２の上流および下
流の入口部１ａと出口部１ｂには流体が分岐および合流
するための空間が設けられている。外筒１と内筒２との
間に一定の流路断面を保持するため、内筒２はその上流
端および下流端において鋼片すなわち複数の固定用駒７
．８によって外筒１の内壁に同心に支持されている。な
お、外筒１は内部を流れる流体の圧力を受けるため耐圧
性が必要であるが、内筒２はその両側からはゾ同じ圧力
を受けるためそれ程の耐圧性は必要ない。An inner cylinder 2 provided concentrically within the outer cylinder 1 is somewhat shorter than the outer cylinder 1, and fluid is branched into an inlet 1a and an outlet 1b upstream and downstream of the inner cylinder 2. Space is provided for merging. In order to maintain a constant cross section of the flow path between the outer cylinder 1 and the inner cylinder 2, the inner cylinder 2 has steel pieces, that is, a plurality of fixing pieces 7 at its upstream and downstream ends.
．． 8 concentrically supported on the inner wall of the outer cylinder 1. Note that the outer cylinder 1 needs to have pressure resistance because it receives the pressure of the fluid flowing inside, but the inner cylinder 2 does not need such pressure resistance because it receives the same pressure from both sides.
図示しない流体機械から吐出された流体は、接続配管６
ａから本発明の装置内に流入し、装置の入口部１ａにお
いて外筒１と内筒２の間の環状の外側通路３と内筒２内
部の内側通路４とに分岐して流入する。それぞれ外側通
路３および内側通路４を通った流体は出口部１ｂにおい
て合流し、さらに下流に接続配管６ｂを介して流れる。The fluid discharged from the fluid machine (not shown) is connected to the connecting pipe 6
It flows into the apparatus of the present invention from a, and branches into an annular outer passage 3 between the outer cylinder 1 and the inner cylinder 2 and an inner passage 4 inside the inner cylinder 2 at the entrance part 1a of the apparatus. The fluids that have passed through the outer passage 3 and the inner passage 4 join together at the outlet portion 1b, and flow further downstream via the connecting pipe 6b.
外側通路３と内側通路４との間には、入口部１ａから出
口部１ｂまでの間に所定の通過距離の差を生じさせるた
め内筒２の周りにほぼその全長にわたってらせん状に流
体を導くリボン状板５が設けられている。リボン状板５
は内筒２の外周面に溶接により固定され、らせん板が形
成される。Between the outer passage 3 and the inner passage 4, fluid is guided around the inner cylinder 2 in a spiral over almost its entire length in order to create a predetermined difference in passage distance between the inlet part 1a and the outlet part 1b. A ribbon-like plate 5 is provided. Ribbon plate 5
is fixed to the outer peripheral surface of the inner cylinder 2 by welding to form a spiral plate.
リボン状板５は、例えば、第３図（ａ）のような内環の
一部Ｃを切断してこれを第３図（ｂ）。The ribbon-shaped plate 5 can be made, for example, by cutting a part C of the inner ring as shown in FIG. 3(a) and then cutting it as shown in FIG. 3(b).
（ｃ）のように円環の切断部Ｃを互い違いに引張って変
形させ内筒２に巻きつける。このリボン状板５を何枚も
連結して円筒２に巻きつけ、継目Ｓで接合すれば第４図
に示すような所望の長さのらせん状流路を内筒２の外周
に沿って形成することまた、本発明装置の使用利料とし
ては炭素鋼、低合金鋼、ステンレス鋼等がある。しかし
、耐圧部材でない内筒２とリボン状板５とを最近家庭用
電器にも広く使用されるようになって制振鋼板（鋼板と
樹脂を組み合わせた複合材料で振動エネルギを樹脂のず
れ、伸び、あるいは圧縮に要する熱エネルギとして吸収
させ、共振、共鳴によって発生する振動、騒音が低減さ
れる。）によって製作すれば、本装置内においても振動
を一層抑制することが期待できる。As shown in (c), the cut portions C of the ring are pulled alternately to deform and wrap around the inner cylinder 2. By connecting a number of ribbon-like plates 5, wrapping them around the cylinder 2, and joining them at a seam S, a spiral flow path of a desired length as shown in FIG. 4 can be formed along the outer periphery of the inner cylinder 2. Furthermore, the use of the apparatus of the present invention includes carbon steel, low alloy steel, stainless steel, etc. However, the inner cylinder 2 and the ribbon-shaped plate 5, which are not pressure-resistant members, have recently been widely used in home appliances, and vibration-damping steel plates (composite materials that combine steel plates and resin) are used to absorb vibration energy from the displacement and elongation of the resin. (or the thermal energy required for compression is absorbed, thereby reducing vibrations and noise generated by resonance.), it can be expected that vibrations can be further suppressed even within this device.
つぎに、本発明の装置の組立方法を説明する。Next, a method of assembling the device of the present invention will be explained.
第７図から第９図に示すように、ます内筒２にリボン状
板５を溶接等の方法によって継目Ｓで接合してらせん状
に固定する。そして、これを外筒１内に挿入し、外筒１
の内壁の両端部付近に、固定用駒７．８によって外筒１
に同心に固定する。このようにして二重同心管が得られ
る。As shown in FIGS. 7 to 9, the ribbon-like plate 5 is joined to the square inner cylinder 2 at a seam S by a method such as welding and fixed in a spiral shape. Then, insert this into the outer cylinder 1, and
The outer cylinder 1 is fixed by fixing pieces 7.8 near both ends of the inner wall of the
Fix it concentrically. In this way a double concentric tube is obtained.
図示しない流体機械から接続用配管６ａを通して供給さ
れた流体は入口部１ａにおいて内側通路４および外側通
路３とに分岐して分流し、制振鋼製のリボン状板５によ
って脈動がいくぶん緩和されるとともに、両道路３，４
の長さに差があるため、それぞれの脈動に位相差が生じ
、出口部１ｂにおいて合流した後は、脈動はほとんど緩
和され、はゾ静的な流れとしてその下流に接続配管６ｂ
を介して供給される。このため接続配管５ ａ ％ ６
ｂに騒音を発生したり損傷を生じたりすることが避け
られる。Fluid supplied from a fluid machine (not shown) through a connecting pipe 6a is branched into an inner passage 4 and an outer passage 3 at the inlet portion 1a, and pulsation is somewhat alleviated by a ribbon-shaped plate 5 made of damping steel. Along with both roads 3 and 4
Due to the difference in length, a phase difference occurs in each pulsation, and after merging at the outlet 1b, the pulsation is almost relaxed, and the flow becomes a static flow downstream of the connecting pipe 6b.
Supplied via. Therefore, connection piping 5 a % 6
It is possible to avoid generating noise or causing damage to b.
また、内筒２およびらせん部を鋳鉄または鋳鋼により一
体に製作することもできる。Further, the inner cylinder 2 and the spiral portion can be integrally manufactured from cast iron or cast steel.
本発明はポンプ等の流体機械において発生し、接続され
た各部分に振動を惹起し、ひいては計器、サポート等を
損傷する可能性のもある圧力脈動をコンパクトな装置内
で特別な流路設計および制振鋼板の助けを借りて、長さ
に差がある二つの流路に分岐し、二つの流れの圧力脈動
に位相を生じさせることにより、防止あるいは低減させ
る。本発明の装置は、コンパクトであるため脈動発生源
の直近に使用でき、その結果、配管装置の信頼性を大幅
に向上させることができる。The present invention uses a special flow path design to eliminate pressure pulsations that occur in fluid machines such as pumps, which can cause vibrations in connected parts and even damage instruments, supports, etc. With the help of damping steel plates, the pressure pulsations in the two flows are prevented or reduced by branching into two channels with different lengths and creating a phase in the pressure pulsations of the two flows. Since the device of the present invention is compact, it can be used close to the pulsation source, and as a result, the reliability of the piping system can be significantly improved.
第１図は本発明の配管振動防止装置の縦断面図、第２図
は第１図の■−■矢視線に沿った横断面図、第３図はリ
ボン状板の製作方法を示す説明図、第４図はらせん状通
路の概念図、第５図と第６図はリボン状板のピッチの決
め方を示す説明図、第７図は本発明の配管振動防止装置
の組立方法を示す・説明図であり、第８図は第７図のＡ
部の拡大図、第９図は同じくＢ部の拡大図、第１０図か
ら第１２図は従来の配管振動防止装置の説明図である。
１・・・外筒、２・・・内筒、３・・・外側通路、４・
・・内側通路、５・・・リボン状板、６ａ、６ｂ・・・
接続配管、出願人代理人 佐 藤 −雄Fig. 1 is a longitudinal sectional view of the piping vibration prevention device of the present invention, Fig. 2 is a transverse sectional view taken along the -■ arrow line in Fig. 1, and Fig. 3 is an explanatory diagram showing a method of manufacturing a ribbon-shaped plate. , FIG. 4 is a conceptual diagram of a spiral passage, FIGS. 5 and 6 are explanatory diagrams showing how to determine the pitch of ribbon-like plates, and FIG. 7 is a diagram showing and explaining a method of assembling the piping vibration prevention device of the present invention. Figure 8 is A of Figure 7.
FIG. 9 is an enlarged view of section B, and FIGS. 10 to 12 are explanatory diagrams of a conventional piping vibration prevention device. 1...Outer cylinder, 2...Inner cylinder, 3...Outer passage, 4...
...Inner passageway, 5...Ribbon-shaped plate, 6a, 6b...
Connection piping, applicant's representative Mr. Sato
Claims (1)
、これらの流路を通過した後合流させて脈動を減衰する
配管振動防止装置において、周囲にらせん板を固定した
内筒を外筒内に同心に配置し、前記内筒内に内側流路を
、また、前記内筒と前記外筒との間にらせん状流路を形
成したことを特徴とする配管振動防止装置。 ２、前記らせん板を制振鋼板により構成したことを特徴
とする請求項１記載の配管振動防止装置。 ３、前記内側通路の断面積Ａｉと前記外側通路の断面積
Ａｏとの総和がこれら通路に接続される配管の断面積Ａ
ｐにほぼ等しく、かつ、前記断面積Ａｉと前記断面積Ａ
ｏがほぼ等しく、また、前記内側通路と前記外側通路の
入口部における分岐点から合流点に至るそれぞれの流体
通路の長さの差が圧力脈動波の波長の１／２にほぼ等し
く、さらに、前記外側通路のらせん部の１ピッチの長さ
をＰとすると、前記らせん部１ピッチ分での前記内側通
路と前記外側通路の距離の差が、 √［Ｐ＾２＋｛π／２（ｄｏ＋ｄｉ｝＾２−Ｐ］（ここ
で、ｄｏ・・・外側通路の内径 ｄｉ・・・内側通路の内径） であることを特徴とする請求項１記載の配管振動防止装
置。[Claims] 1. A piping vibration prevention device that branches fluid discharged from a fluid machine into two flow paths, and after passing through these flow paths, merges the fluid to damp pulsation. A piping system characterized in that a fixed inner cylinder is arranged concentrically within an outer cylinder, an inner flow path is formed within the inner cylinder, and a spiral flow path is formed between the inner cylinder and the outer cylinder. Anti-vibration device. 2. The piping vibration prevention device according to claim 1, wherein the spiral plate is made of a damping steel plate. 3. The sum of the cross-sectional area Ai of the inner passage and the cross-sectional area Ao of the outer passage is the cross-sectional area A of the piping connected to these passages.
approximately equal to p, and the cross-sectional area Ai and the cross-sectional area A
o are approximately equal, and the difference in the length of the fluid passages from the branching point to the confluence at the entrance of the inner passage and the outer passage is approximately equal to 1/2 of the wavelength of the pressure pulsating wave, and further, If the length of one pitch of the spiral portion of the outer passage is P, then the difference in distance between the inner passage and the outer passage for one pitch of the spiral portion is √[P^2+{π/2(do+di}) ^2-P] (where do...inner diameter of the outer passage di...inner diameter of the inner passage).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31979090A JPH04191594A (en) | 1990-11-22 | 1990-11-22 | Piping vibration preventing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31979090A JPH04191594A (en) | 1990-11-22 | 1990-11-22 | Piping vibration preventing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH04191594A true JPH04191594A (en) | 1992-07-09 |
Family
ID=18114213
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP31979090A Pending JPH04191594A (en) | 1990-11-22 | 1990-11-22 | Piping vibration preventing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH04191594A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7704061B2 (en) | 2003-11-17 | 2010-04-27 | Hitachi, Ltd. | Oil pump |
| CN103883835A (en) * | 2014-04-18 | 2014-06-25 | 兰州理工大学 | Pipeline damping device |
-
1990
- 1990-11-22 JP JP31979090A patent/JPH04191594A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7704061B2 (en) | 2003-11-17 | 2010-04-27 | Hitachi, Ltd. | Oil pump |
| CN103883835A (en) * | 2014-04-18 | 2014-06-25 | 兰州理工大学 | Pipeline damping device |
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