JPS63111390A - Fluid joint - Google Patents
Fluid jointInfo
- Publication number
- JPS63111390A JPS63111390A JP61257793A JP25779386A JPS63111390A JP S63111390 A JPS63111390 A JP S63111390A JP 61257793 A JP61257793 A JP 61257793A JP 25779386 A JP25779386 A JP 25779386A JP S63111390 A JPS63111390 A JP S63111390A
- Authority
- JP
- Japan
- Prior art keywords
- flow pipe
- inner cylinder
- stationary outer
- outer cylinder
- liner
- 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
- 239000012530 fluid Substances 0.000 title claims description 37
- 230000008878 coupling Effects 0.000 claims description 20
- 238000010168 coupling process Methods 0.000 claims description 20
- 238000005859 coupling reaction Methods 0.000 claims description 20
- 238000007789 sealing Methods 0.000 claims description 14
- 230000002093 peripheral effect Effects 0.000 claims description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 20
- 239000011435 rock Substances 0.000 description 9
- 239000003566 sealing material Substances 0.000 description 8
- 102100027340 Slit homolog 2 protein Human genes 0.000 description 6
- 101710133576 Slit homolog 2 protein Proteins 0.000 description 6
- 238000005422 blasting Methods 0.000 description 4
- 238000005553 drilling Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 1
- 238000009412 basement excavation Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
Landscapes
- Joints Allowing Movement (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
「産業上の利用分野」
本発明は、高圧水を扱う配管の接続に好適な流体継手に
関するものである。DETAILED DESCRIPTION OF THE INVENTION "Field of Industrial Application" The present invention relates to a fluid coupling suitable for connecting piping that handles high-pressure water.
「従来の技術」
従来、トンネル掘削法に採用されているウォータジェッ
トブラスティング工法（ＷＪＢ工法）においては、岩盤
を発破してトンネルを掘削するために、第４図に示すよ
うに、岩盤Ｇに対して多数の発破孔！を形成し、発破孔
ｌにスリット（切り溝）２を形成しておくことが行なわ
れている。このスリット２を形成する理由は、発破によ
る圧力をスリット２の方向に沿わせて効果的に作用させ
るとと乙に、発破面を平滑にするためである。"Conventional technology" In the water jet blasting method (WJB method), which has been conventionally adopted as a tunnel excavation method, in order to excavate a tunnel by blasting the rock mass, a blast is applied to the rock mass G as shown in Figure 4. On the other hand, there are many blast holes! , and a slit (cut groove) 2 is formed in the blast hole l. The reason for forming this slit 2 is to make the blasting surface smooth so that the pressure caused by blasting can be applied effectively along the direction of the slit 2.
ところで、前記工法において発破孔１とスリット２を形
成ずろには、ロッドと穿孔ビットからなる穿孔工具を備
えた削岩機（ドリフタ−等）を用いて発破孔ｌを形成し
た後に、穿孔ビットとロッドを発破孔Ｉから引き出し、
その後にスリット形成用の高圧水ランスを発−破孔ｌ内
に挿入し、高圧水を噴出させつつ高圧水ランスを引き出
してスリット２を形成するといった作業を行っているが
、この作業においては、穿孔ビットとロッドの引き出し
時間と高圧水ランスの挿入時間が全くの作業ロスとなる
問題がある。そこで本発明の出願人は、先に、高圧水ラ
ンスを組み込んだ新規構成のドリフタ−を開発している
。ところがこのドリフタ−を用いてスリット２を形成す
るに際しては、第４図に示すように種々の方向にスリッ
ト２を形成する作業を行う関係から、あるいは、ロッド
の回転角に対して一定の高圧水注入方向が得られること
が好ましい関係から、更に、高圧ポンプに接続した高圧
ホースを常時接続しておき、必要に応じて高圧ポンプま
たはバルブのスイッチの大切を行いたい関係から、ドリ
フタ−内部に施した高圧水配管に、重連した各要求に答
えうる流体継手を組み込む必要がある。By the way, in the above construction method, in order to form the blast hole 1 and the slit 2, after forming the blast hole l using a rock drill (such as a drifter) equipped with a drilling tool consisting of a rod and a drilling bit, Pull out the rod from blast hole I,
After that, a high-pressure water lance for slit formation is inserted into the blast hole 1, and the high-pressure water lance is pulled out while spouting high-pressure water to form the slit 2. In this work, There is a problem in that the time taken to withdraw the drilling bit and rod and the time required to insert the high-pressure water lance results in a complete loss of work. Therefore, the applicant of the present invention has previously developed a drifter with a new configuration incorporating a high-pressure water lance. However, when forming the slit 2 using this drifter, it is difficult to form the slit 2 in various directions as shown in Fig. Because it is preferable to be able to control the injection direction, and because we want to keep the high-pressure hose connected to the high-pressure pump connected at all times and switch on the high-pressure pump or valve as necessary, we installed it inside the drifter. It is necessary to incorporate fluid couplings that can meet multiple demands into high-pressure water piping.
ここで、従来知られている溝体継手の一例を第５図に示
す、第５図に示す従来のスイベル継手４は、逆Ｔ字型の
中空部を内部に形成しん筒体５の内部に回転自在に連結
管６を挿入し、連結管６の抜は止めをなし、連結管６の
外周面と筒体５の内周面との間の摺動部分にシール材７
を配設した構成である。Here, an example of a conventionally known groove body joint is shown in FIG. 5. The conventional swivel joint 4 shown in FIG. The connecting tube 6 is inserted rotatably, the connecting tube 6 is prevented from being removed, and a sealing material 7 is applied to the sliding portion between the outer circumferential surface of the connecting tube 6 and the inner circumferential surface of the cylinder body 5.
This is a configuration in which .
「発明が解決しようとする問題点」
第５図に示す従来構成の流体継手４にあっては、シール
材７がたえず高圧水にさらされ、その上、シール材７と
接触しつつ連結管６が回転摺動するために、シール材７
の摩耗が激しく止水性に難点を有する欠点があった。"Problems to be Solved by the Invention" In the conventional fluid coupling 4 shown in FIG. The sealing material 7 rotates and slides.
It has the disadvantage of severe abrasion and poor water-stopping properties.
本発明は、前記問題に鑑みてなされたもので、回転（）
１動する部分に従来必要であったシール材を無くしてシ
ール材の摩耗による止水性の低下問題を解消するととも
に、用いる高圧水の水圧あ高低に影響を受けることなく
回転摺動部分に所定のシール圧力を得ることができる流
体継手を堤供することを目的とする。The present invention has been made in view of the above-mentioned problem.
1. Eliminates the sealing material that was conventionally required for moving parts, solving the problem of reduced water-stopping performance due to wear of the sealing material, and also allows the rotating and sliding parts to maintain a specified level without being affected by the water pressure of the high-pressure water used. The purpose is to provide a fluid coupling that can obtain sealing pressure.
１問題点を解消するための手段」
本発明は、前記問題点を解消するために、静止外筒と、
この静止外筒に内挿された流通管と、前記流通筒と静止
外筒との間に相互に離間し、かつ、各々静止外筒と流通
管に接触しつつ内筒の長さ方向に移動自在に設けられた
一対の内筒ライナーと、前記静止外筒の開口部側に設け
られたフランジ部と、シール部材とを備えてなり、前記
流通管の周壁に、前記一対の内筒ライナー間の間隙と流
通管の流体通路に開口する内部通路を形成し、前記静止
外筒に前記間隙に通じる流入孔を形成するとともに、内
筒ライナーに付勢部材を付設し、前記フランジ部付に対
向する各内筒ライナーの端面に、前記フランジ部に当接
する接触凸部を周設した乙のである。1. Means for Solving Problem 1" In order to solve the above problem, the present invention provides a stationary outer cylinder,
A flow pipe inserted into the stationary outer cylinder is spaced from each other between the flow cylinder and the stationary outer cylinder, and moves in the length direction of the inner cylinder while contacting the stationary outer cylinder and the flow pipe, respectively. It includes a pair of inner cylinder liners freely provided, a flange part provided on the opening side of the stationary outer cylinder, and a sealing member, and a sealing member is provided between the pair of inner cylinder liners on the peripheral wall of the flow pipe. forming an internal passage that opens into the gap and the fluid passage of the flow pipe; forming an inflow hole communicating with the gap in the stationary outer cylinder; and attaching a biasing member to the inner cylinder liner, facing the flange part. A contact convex portion that comes into contact with the flange portion is provided around the end face of each inner cylinder liner.
「作用」
静止外筒の流入孔から円筒ライナー間の間隙に流入した
流体の圧力と、円筒ライナーおよび静止外筒とフランジ
部と接触凸部とか形成する空隙に流入した流体の圧力と
がバランスするとともに、付勢部材が円筒ライナーを付
勢し、円筒ライナーの接触凸部を所定の力でフランジ部
に押し付け、流体圧力の高低に影響されずに所定のシー
ル力を発生する。また、流入管が静止外筒の内側で回転
する際に、接触凸部がフランジ部に対して回転摺動し、
摺動部分に従来用いていたシール材を用いる必要がない
構成であるために、シール材の摩耗に起因する止水性の
低下現象は生じない。"Operation" The pressure of the fluid flowing into the gap between the cylindrical liners from the inflow hole of the stationary outer cylinder is balanced with the pressure of the fluid flowing into the gap formed by the cylindrical liner, the stationary outer cylinder, the flange, and the contact convex part. At the same time, the biasing member biases the cylindrical liner and presses the contact convex portion of the cylindrical liner against the flange portion with a predetermined force, thereby generating a predetermined sealing force regardless of the level of fluid pressure. Also, when the inflow pipe rotates inside the stationary outer cylinder, the contact convex portion rotates and slides against the flange portion,
Since the structure does not require the use of the sealing material conventionally used in the sliding portion, there is no reduction in water-stopping properties due to wear of the sealing material.
「実施例」
第１図は、本発明の一実施例の流体継手Ａを示ずらので
、この流体継手Ａは、流通管！ｌと、この流通管１１に
外挿された静止外筒１２と、この静止外筒１２と流通管
１１の間に設けられた内筒ライナー１３．１３を主体と
して構成されている。"Embodiment" FIG. 1 does not show a fluid coupling A according to an embodiment of the present invention, so this fluid coupling A is a flow pipe! 1, a stationary outer cylinder 12 fitted over the flow pipe 11, and an inner cylinder liner 13.13 provided between the stationary outer cylinder 12 and the flow pipe 11.
前記流通管１１は、その内部に流体通路１５をｆイし、
流通管ｌ！の一部の外周には大径部１６か形成され、こ
の大径部１６の外周面に各々離間して形成された凹溝１
７にはシール部＋４１８が挿入され、凹溝１７ 、 ｌ
７の間の大径部Ｉ６には、大径部Ｉ６の外周面と流体
通路１５に開口する内部通路１６ａが形成されている。The flow pipe 11 has a fluid passage 15 therein,
Distribution pipe! A large diameter portion 16 is formed on a part of the outer periphery of the large diameter portion 16, and grooves 1 are formed at intervals on the outer circumferential surface of the large diameter portion 16.
A seal portion +418 is inserted into 7, and a groove 17, l
An internal passage 16a that opens to the outer peripheral surface of the large diameter part I6 and the fluid passage 15 is formed in the large diameter part I6 between 7 and 7.
前記静止外筒１２は、前記大径部１６の幅より若干長く
、しかも、大径部１６よりも大きい直径に形成され、静
止外筒１２の開口部には内向きのフランジ部２０が一体
に形成され、このフランジ部２０の内径は前記大径部１
６の直径よりも若干小さく、しかも、前記流通管１１の
外径よりも若干大きく形成されている。そして、静止外
筒１２に、前記フランジ部２０の内側に大径部１６を挿
入して流通ｄ１！が挿通されている。なお、静止外筒１
２の長さ方向中央部には高圧の流体を送る高圧ポンプに
接続される高圧管２１を接続した流入孔２２が形成され
ている。The stationary outer cylinder 12 is slightly longer than the width of the large diameter part 16 and has a larger diameter than the large diameter part 16, and an inward flange part 20 is integrally formed at the opening of the stationary outer cylinder 12. The inner diameter of this flange portion 20 is equal to that of the large diameter portion 1.
6 and slightly larger than the outer diameter of the flow pipe 11. Then, the large diameter portion 16 is inserted into the stationary outer cylinder 12 inside the flange portion 20, and the flow d1! is inserted. In addition, the stationary outer cylinder 1
An inflow hole 22 is formed in the longitudinally central portion of 2 to which a high-pressure pipe 21 connected to a high-pressure pump that sends high-pressure fluid is connected.
一方、大径部１６の外方には、リング状の内筒ライナー
１３．１３が、相互に離間し、かつ、大径部１６の凹溝
１７を覆って摺動自在に外挿されている。そして、内筒
ライナー１３．１３の間には、内筒ライナー１３の端面
１３ａ、１３ａと静止外筒１２と大径部１６に囲まれて
間隙Ｋが形成されている。なお、前記内筒ライナー１３
は、シール部材１８に上り内筒ライナー１３と大径部１
６の間を液密に閉塞された状態で大径部１６に沿って大
径部１６と静止外筒１２に接しつつ流通管ｌｌの長さ方
向に摺動自在に設けられている。更に、各内筒ライナー
１３の端面のうち、フランジ部２０に対向する端面１３
ｂの内周部には、接触凸部２５が周設されている。また
、前記間隙Ｋには、円筒ライナー！ ３．１３を互いに
離れるように付勢するばね部材（付勢部材）２３が設け
られ、ばね部材２３のばね力により円筒ライナー１３．
１３の接触凸部２５は各々フランジ部２０の内周部２６
に当接されている。そして、前記接触凸部２５と内筒ラ
イナー１３の端面１３ｂと静止外筒！２とフランジ部２
０とに囲まれて空隙りが形成されている。なお、円筒ラ
イナー１３．１３間の間隙には、静止外筒１２の流入孔
２２と、流通管１１の内部通路１６ａに連通されている
。On the other hand, ring-shaped inner cylinder liners 13 . . A gap K is formed between the inner cylinder liners 13 and 13, surrounded by the end surfaces 13a, 13a of the inner cylinder liner 13, the stationary outer cylinder 12, and the large diameter portion 16. Note that the inner cylinder liner 13
goes up to the sealing member 18 and connects the inner cylinder liner 13 and the large diameter part 1.
6 is fluid-tightly closed along the large-diameter portion 16 and in contact with the large-diameter portion 16 and the stationary outer cylinder 12 so as to be freely slidable in the length direction of the flow pipe 11. Furthermore, among the end faces of each inner cylinder liner 13, the end face 13 facing the flange portion 20
A contact convex portion 25 is provided around the inner peripheral portion of b. In addition, the gap K is filled with a cylindrical liner! A spring member (biasing member) 23 is provided which biases the cylindrical liners 13.
Each of the thirteen contact convex portions 25 is connected to the inner peripheral portion 26 of the flange portion 20.
is in contact with. Then, the contact convex portion 25, the end surface 13b of the inner cylinder liner 13, and the stationary outer cylinder! 2 and flange part 2
A gap is formed surrounded by 0 and 0. Note that the gap between the cylindrical liners 13 and 13 communicates with the inflow hole 22 of the stationary outer cylinder 12 and the internal passage 16a of the flow pipe 11.
前述の如く構成された流体継手Ａは、例えば１０００
ｋｇ／ ｃｍ”以上もの高圧水を扱う削岩機に組み込ま
れる高圧配管の接続用に使用される。The fluid coupling A configured as described above has, for example, 1000
It is used to connect high-pressure piping built into rock drills that handle high-pressure water of over 100 kg/cm.
即ち、高圧管２１を高圧ポンプに接続し、流通管１１を
ジェットノズルを備えた削岩機のロッドに直接あるいは
間接的に接続する。That is, the high-pressure pipe 21 is connected to a high-pressure pump, and the flow pipe 11 is directly or indirectly connected to a rod of a rock drill equipped with a jet nozzle.
そして、高圧ポンプから高圧管２１に高圧水を送ると、
高圧水は、流入孔２２から円筒ライナー１３．１３間の
間隙Ｋに入り、内部通路１６ａを経て流通管ＩＩの流体
通路１５に移動してジェットノズル側に流動する。この
際、間隙にと空隙りに高圧水が流入し、内筒ライナー１
３の両側に高圧水が流入するために、内筒ライナー１３
には、円筒ライナー１３の間隙に側の端面１３ａの面積
と、反対側の端面１３ｂの面積との差の分から生じる若
干の水圧が作用し、更にばね部材２３の付勢力ら加わっ
て結果的に円筒ライナー１３は互いに離れる方向に付勢
される。こうして円筒ライナーＩ３の接触凸部２５をフ
ランジ部２０の内周面に押し付けてシール力を発生させ
る。Then, when high pressure water is sent from the high pressure pump to the high pressure pipe 21,
The high-pressure water enters the gap K between the cylindrical liners 13 and 13 from the inflow hole 22, moves through the internal passage 16a to the fluid passage 15 of the flow pipe II, and flows toward the jet nozzle. At this time, high pressure water flows into the gap and the inner cylinder liner 1
In order for high pressure water to flow into both sides of the inner cylinder liner 13
A slight water pressure generated from the difference between the area of the end surface 13a on the side and the area of the end surface 13b on the opposite side acts on the gap of the cylindrical liner 13, and the biasing force of the spring member 23 is added, resulting in The cylindrical liners 13 are urged away from each other. In this way, the contact convex portion 25 of the cylindrical liner I3 is pressed against the inner peripheral surface of the flange portion 20 to generate a sealing force.
前述のような状態で削岩機のロッドが回動して流通管１
１が回動する場合は、流通管１１と円筒ライナー１３．
１３が共に静止外筒１２の内部で回動する。そして、こ
の回動の際に、接触凸部２５がフランジ部２５に接触し
つつ摺動してシール力を発生する。即ち、前記構成では
、固定側であるフランジ部２０と回動側である接触凸部
２５との間にシール材がないために、前記回動によりシ
ール材が摩耗することは生じなくなり、止水性が低下す
る問題は生じない。なお、前記回動により接触凸部２５
が損耗することが考えられるが、接触凸部２５が損耗に
より短くなった場合は、間隙にの水圧とばね部材２３の
付勢力に上り内筒ライナー２５がフランジ部２０側に更
に接近することにより接触凸部２５を確実にフランジ部
２０に当接さ仕てシール力が発生する。従って接触凸部
２５か完全に損耗するまでの間、長期間にわたって確実
に所定のシール力を得ることができる。In the above-mentioned condition, the rod of the rock drill rotates and the flow pipe 1
1 rotates, the flow pipe 11 and the cylindrical liner 13.
13 both rotate inside the stationary outer cylinder 12. During this rotation, the contact convex portion 25 slides while contacting the flange portion 25 to generate a sealing force. That is, in the above configuration, since there is no sealing material between the flange portion 20 on the fixed side and the contact convex portion 25 on the rotating side, the sealing material is not worn out due to the rotation, and the water-stopping property is improved. There is no problem of a decrease in the value. Note that due to the rotation, the contact convex portion 25
If the contact protrusion 25 becomes short due to wear, the water pressure in the gap and the biasing force of the spring member 23 will increase, causing the inner cylinder liner 25 to move closer to the flange 20 side. The contact convex portion 25 is brought into reliable contact with the flange portion 20 to generate a sealing force. Therefore, a predetermined sealing force can be reliably obtained over a long period of time until the contact protrusion 25 is completely worn out.
第２図は本発明の第２実施例の流体継手Ｂを示す乙ので
、この例の流体継手Ｂは、第１図に示す流体継手Ａにお
いて静止外筒１２に形成されていたフランジ部２０を静
止外筒Ｉ２とは別体に設けた構成の継手を示すらのであ
る。なお、第２図に示す流体継手Ｂにおいて、第１図に
示す流体継手Ａと同一の構成部分には同一符号を付して
それらの説明は省略する。Since FIG. 2 shows a fluid coupling B according to a second embodiment of the present invention, the fluid coupling B of this example has a flange portion 20 formed on the stationary outer cylinder 12 in the fluid coupling A shown in FIG. This figure shows a joint configured separately from the stationary outer cylinder I2. In the fluid coupling B shown in FIG. 2, the same components as those in the fluid coupling A shown in FIG.
本実施例の流体継手Ｂは、流通管１１の大径部１Ｇの外
方に外向きのフランジ部３０を有するフランジ部材３１
を設け、このフランジ部材３Ｉの外方に、円筒ライナー
３２と静止外筒３３．を設けた構成である。The fluid coupling B of this embodiment has a flange member 31 having an outward flange portion 30 on the outside of the large diameter portion 1G of the flow pipe 11.
is provided, and a cylindrical liner 32 and a stationary outer cylinder 33. are provided on the outside of this flange member 3I. This is a configuration with a
前記フランジ部材３１は、流通管１１の大径部１６を覆
って嵌着された筒体３５と、この筒体３５の両端開口部
に前記大径部１６の両側に位置するように形成された外
向きのフランジ部３０と、筒体３５の両端開口部に大径
部Ｉ６を挟むように形成された内フランジ３６とから構
成され、筒体３５には流通管１１の内部通路１６ａに通
じる透孔３５ａが形成されている。The flange member 31 includes a cylindrical body 35 fitted over the large diameter portion 16 of the flow pipe 11, and is formed at both end openings of the cylindrical body 35 so as to be located on both sides of the large diameter portion 16. It is composed of an outward flange portion 30 and an inner flange 36 formed at both end openings of the cylinder body 35 so as to sandwich the large diameter portion I6. A hole 35a is formed.
前記フランジ部材３１のフランジ部３０．３０の間には
、内筒ライナー３２．３２が互いに離間して設けられ、
フランジ部３０に対向する内筒ライナー３２．３２の端
面外周部に接触凸部３７が周設されている。そして、静
止外筒３３の内面には肉厚部３８が形成され、この肉厚
部３８の内周面に前記内筒ライナー３２．３２に対向す
る凹１’Ｆ３９が形成され、各凹溝３９にはシール部祠
４０が挿入されている。Inner cylinder liners 32.32 are provided spaced apart between the flange portions 30.30 of the flange member 31,
A contact convex portion 37 is provided around the outer periphery of the end face of the inner cylinder liner 32, 32 facing the flange portion 30. A thick part 38 is formed on the inner surface of the stationary outer cylinder 33, and a recess 1'F39 facing the inner cylinder liner 32.32 is formed on the inner peripheral surface of the thick part 38. A seal part hoist 40 is inserted into.
前記構成の流体継手Ｂは、高圧管２１から間隙Ｋに高圧
水が流入し、内筒ライナー３２が移動してその接触凸部
３７がフランジ部３０の内周面に接触してノール力を得
る構造である。また、本実施例の構造では、流通管」ｌ
が回動する場合、流通管ｌ！とフランジ部材３１が共に
回動し、内筒ライナー３２は静止するようになっている
。In the fluid coupling B having the above configuration, high pressure water flows into the gap K from the high pressure pipe 21, the inner cylinder liner 32 moves, and its contact convex portion 37 contacts the inner circumferential surface of the flange portion 30 to obtain a knoll force. It is a structure. In addition, in the structure of this embodiment, the flow pipe "l"
When the flow pipe l! rotates, the flow pipe l! and the flange member 31 rotate together, and the inner cylinder liner 32 remains stationary.
第３図は、本発明の第３実施例の流体継手Ｃを示すもの
で、本実施例においては、先に説明した第１実施例にお
いて設けられた一対の内筒ライナーのうちの一方を特別
な構成としたしのである。FIG. 3 shows a fluid coupling C according to a third embodiment of the present invention. In this embodiment, one of the pair of inner cylinder liners provided in the first embodiment described above is specially It has a unique composition.
その他の構成は第１実施例と同等である。The other configurations are the same as in the first embodiment.
即ち本実施例においては、第３図の右側の内筒ライナー
１３゛の外周部に段部５０を形成し、この段部５０に連
続させて接触凸部２５を形成し、内筒ライナー＋３’の
端面１３ａの面積と端面！３ｂの面積を同一になるよう
に構成した例である。That is, in this embodiment, a step 50 is formed on the outer periphery of the inner cylinder liner 13' on the right side in FIG. Area and end face of end face 13a! This is an example in which the areas of 3b are configured to be the same.
前記構成の流体継手Ｃにあっては、内筒ライナー１３の
端面１３ａに作用する流体圧と内筒ライナー１３の端面
１３ｂに作用する流体圧を同一にすることができ、左右
の内筒ライナー１３，１３゜は、ばね２３によってのみ
付勢され、接触凸部２５．２５がフランジ部２０．２０
に接触して目的を達成する。In the fluid coupling C having the above configuration, the fluid pressure acting on the end surface 13a of the inner cylinder liner 13 and the fluid pressure acting on the end surface 13b of the inner cylinder liner 13 can be made the same, and the left and right inner cylinder liners 13 , 13° is biased only by the spring 23, and the contact convex portion 25.25 is pressed against the flange portion 20.20.
Achieve your goal by contacting.
［発明の効果Ｊ
以上説明したように本発明は、静止外筒と流通管の間に
設けた内筒ライナーの両側に流体を導き、内筒ライナー
の両側に導いた流体圧をバランスさ仕、付勢部材に上り
内筒ライナーの接触凸部をフランジ部に押し付けてシー
ル力を得る構成のために、導く高圧流体の圧力に影響さ
、れずに所定のシール力を得ることができる。従って本
発明の流体継手は、高圧の流体を扱う配管の接続用とし
て好適である。また、流通管は静止外筒の内側で自由に
回動てき、流通管の回動により静止外筒のフランジ部に
当接した内筒ライナーの接触凸部が摺動しつつシール力
を発揮するために、接触凸部が損耗して短くなった場合
でも、内筒ライナーが付勢部材に付勢されて接触凸部の
先端をフランジ部に押し付けるために、シール部分の止
水性低下の問題は生じない特長かある。従って本発明の
流体継手は、岩盤に所要の向きのスリットを形成する削
岩機等のように、高圧水を通す配管を回動させる必要を
生じる装置に用いる配管の接続用として好適である。[Effect of the Invention J As explained above, the present invention introduces fluid to both sides of the inner cylinder liner provided between the stationary outer cylinder and the flow pipe, balances the fluid pressure led to both sides of the inner cylinder liner, Since the sealing force is obtained by pressing the contact convex portion of the inner cylinder liner against the flange portion using the biasing member, a predetermined sealing force can be obtained without being affected by the pressure of the high-pressure fluid introduced. Therefore, the fluid coupling of the present invention is suitable for connecting piping that handles high-pressure fluid. In addition, the flow pipe rotates freely inside the stationary outer cylinder, and as the flow pipe rotates, the contact protrusion of the inner cylinder liner that comes into contact with the flange of the stationary outer cylinder slides and exerts a sealing force. Therefore, even if the contact protrusion is worn out and shortened, the inner cylinder liner is biased by the biasing member and presses the tip of the contact protrusion against the flange, which eliminates the problem of reduced water sealing properties of the seal part. There are some features that do not occur. Therefore, the fluid coupling of the present invention is suitable for connecting piping used in devices that require rotating piping for passing high-pressure water, such as a rock drill that forms slits in a desired direction in rock.
第１図は、本発明の一実施例を示す断面図、第２図は本
発明の第２実施例を示す断面図、第３図は本考案の第３
実施例を示す断面図、第４図はトンネル掘削を行う場合
に岩盤に形成した発破孔とスリットを示す正面図、第５
図は従来のスイベル継手を示す断面図である。
Ａ、Ｉ３・・・・・・流体継手、 Ｋ・・・・・・
間隙、１１・・・・・・流通管、 １２．３３・・
・・・・静止外筒、１３．３２・・・・・・内筒ライナ
ー、１５・・・・・・流体通路、 １６ａ・・・・・
・内部通路、１８．４０・・・・・・ソール部材、
２０．３０・・・・・・フランジ部、２２・・・・・・
流入孔、２３・・・・・・ばね部材（付勢部材）、２５
．３７・・・・・・接触凸部。FIG. 1 is a sectional view showing one embodiment of the present invention, FIG. 2 is a sectional view showing a second embodiment of the present invention, and FIG. 3 is a sectional view showing a third embodiment of the present invention.
FIG. 4 is a cross-sectional view showing the embodiment; FIG. 4 is a front view showing blast holes and slits formed in the rock when excavating a tunnel;
The figure is a sectional view showing a conventional swivel joint. A, I3...Fluid coupling, K...
Gap, 11...Flow pipe, 12.33...
... Stationary outer cylinder, 13.32 ... Inner cylinder liner, 15 ... Fluid passage, 16a ...
・Internal passage, 18.40... Sole member, 20.30... Flange part, 22...
Inflow hole, 23... Spring member (biasing member), 25
．． 37...Contact convex portion.
Claims (1)
静止外筒と流通管との間において流通管の長さ方向に移
動自在に流通管に外挿された一対の内筒ライナーと、前
記静止外筒の開口部側に設けられたフランジ部と、前記
流通管あるいは静止外筒と内筒ライナーとの間に介在さ
れたシール部材とを備えてなり、前記流通管の周壁には
前記一対の内筒ライナー間の間隙と流通管内の流体通路
とに開口する内部通路が形成され、前記静止外筒には前
記間隙に通じる流入孔が形成されるとともに、前記内筒
ライナーには、内筒ライナーをフランジ部側に付勢する
付勢部材が付設され、前記フランジ部に対向する各内筒
ライナーの端面には、前記付勢部材が内筒ライナーに作
用させる付勢力によって前記フランジ部に当接する接触
凸部が周設されてなることを特徴とする流体継手。A stationary outer cylinder, a flow pipe loosely inserted into the stationary outer cylinder, and a pair of inner cylinders fitted onto the flow pipe so as to be movable in the length direction of the flow pipe between the stationary outer cylinder and the flow pipe. a liner, a flange provided on the opening side of the stationary outer cylinder, and a sealing member interposed between the flow pipe or the stationary outer cylinder and the inner cylinder liner, the peripheral wall of the flow pipe is formed with an internal passage that opens into the gap between the pair of inner cylinder liners and the fluid passage in the flow pipe, and the stationary outer cylinder is formed with an inflow hole that communicates with the gap, and the inner cylinder liner has is provided with a biasing member that biases the inner cylinder liner toward the flange portion, and the end face of each inner cylinder liner facing the flange portion is provided with a biasing member that biases the inner cylinder liner toward the inner cylinder liner. A fluid coupling characterized in that a contact convex portion that comes into contact with a flange portion is provided around the flange portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61257793A JPH063274B2 (en) | 1986-10-29 | 1986-10-29 | Fluid fitting |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61257793A JPH063274B2 (en) | 1986-10-29 | 1986-10-29 | Fluid fitting |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63111390A true JPS63111390A (en) | 1988-05-16 |
| JPH063274B2 JPH063274B2 (en) | 1994-01-12 |
Family
ID=17311183
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61257793A Expired - Lifetime JPH063274B2 (en) | 1986-10-29 | 1986-10-29 | Fluid fitting |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH063274B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0274691U (en) * | 1988-11-28 | 1990-06-07 | ||
| JPH0388097U (en) * | 1989-12-26 | 1991-09-09 | ||
| JPH0524685U (en) * | 1991-02-28 | 1993-03-30 | 株式会社タダノ | Mobile crane hydraulic pump controller |
| JPH0651678U (en) * | 1992-12-18 | 1994-07-15 | エヌティエヌ株式会社 | Seal structure between members that rotate relative to each other |
-
1986
- 1986-10-29 JP JP61257793A patent/JPH063274B2/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0274691U (en) * | 1988-11-28 | 1990-06-07 | ||
| JPH0388097U (en) * | 1989-12-26 | 1991-09-09 | ||
| JPH0524685U (en) * | 1991-02-28 | 1993-03-30 | 株式会社タダノ | Mobile crane hydraulic pump controller |
| JP2578115Y2 (en) * | 1991-02-28 | 1998-08-06 | 株式会社タダノ | Hydraulic pump control for mobile crane |
| JPH0651678U (en) * | 1992-12-18 | 1994-07-15 | エヌティエヌ株式会社 | Seal structure between members that rotate relative to each other |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH063274B2 (en) | 1994-01-12 |
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