JPH08210573A - Rotary sealing joint - Google Patents
Rotary sealing jointInfo
- Publication number
- JPH08210573A JPH08210573A JP4242495A JP4242495A JPH08210573A JP H08210573 A JPH08210573 A JP H08210573A JP 4242495 A JP4242495 A JP 4242495A JP 4242495 A JP4242495 A JP 4242495A JP H08210573 A JPH08210573 A JP H08210573A
- Authority
- JP
- Japan
- Prior art keywords
- rotary
- rotary seal
- pressurizing
- seal joint
- hole
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L27/00—Adjustable joints, Joints allowing movement
- F16L27/08—Adjustable joints, Joints allowing movement allowing adjustment or movement only about the axis of one pipe
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Joints Allowing Movement (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、工作機械の主軸等の回
転シール継手に関し、圧力流体の漏れを最少限に抑制す
るのみならず、回転シール継手の接触面圧力制御を可能
としたものに係わる。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary seal joint for a spindle of a machine tool and the like, which not only suppresses leakage of pressure fluid to a minimum but also enables control of contact surface pressure of the rotary seal joint. Involve
【０００２】[0002]
【従来の技術】従来、工作機械の主軸等の回転シール継
手においては、特開平４ー６０２８１号に見るように、
固定円管と回転円管とを非接触に半径方向隙間を有して
その長手方向に嵌め込み、この嵌合する挿入面には環状
溝を設け、この溝に連通した吸引路に吸引装置を設けた
回転シール部材が提供されている。この回転シール部材
によると、冷却液の往路と復路とを合せても１方にのみ
環状の溝と吸引路とを設ければ良く、シール構造として
シンプルである利点をもつ。また、特開平６ー２４１３
６６号では、ロータリジョイントの回転軸と移動軸との
対向面に設けた一対のシール部材を非接触状態に付勢す
るダイヤフラムがハウジングと移動軸との間に張設され
ている。そして、流体流路へ気体を流通させる場合は、
ポートに気体を導入し、一対のシール部材を非接触状態
のままにし、流体を流通させる場合は、ポートに液体を
導入し、その圧力でダイヤフラムを押圧して、一対のシ
ール部材を接触状態にするものである。2. Description of the Related Art Conventionally, in rotary seal joints such as spindles of machine tools, as disclosed in Japanese Patent Laid-Open No. 60281/1992,
A fixed circular pipe and a rotating circular pipe are fitted in a non-contact manner with a radial gap therebetween in the longitudinal direction thereof, and an annular groove is provided on the fitted insertion surface, and a suction device is provided in the suction passage communicating with this groove. A rotary seal member is provided. According to this rotary seal member, even if the forward path and the return path of the cooling liquid are combined, it is sufficient to provide the annular groove and the suction path in only one direction, and there is an advantage that the sealing structure is simple. In addition, JP-A-6-2413
In No. 66, a diaphragm, which urges a pair of seal members provided on the opposing surfaces of the rotary shaft and the moving shaft of the rotary joint in a non-contact state, is stretched between the housing and the moving shaft. And, when the gas is circulated to the fluid channel,
When introducing gas into the port and leaving the pair of seal members in a non-contact state to allow the fluid to flow, introduce liquid into the port and press the diaphragm with that pressure to bring the pair of seal members into contact. To do.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、上記特
開平４ー６０２８１号の回転シール部材によると、吸引
装置のトラブルで吸引力が低下して固定円管と回転円管
との嵌合する挿入面の環状溝からの油漏れを発生する。
また、固定円管と回転円管との嵌合隙間は、回転円管の
アンバランスや回転振動により変動するから、潤滑の吸
引回収効率が低下する。更に、特開平６ー２４１３６６
号のロータリジョイントでは、ポートに気体を導入時に
は一対のシール部材を非接触状態のままにし、流体を流
通させる場合はその圧力でダイヤフラムを押圧し、一対
のシール部材を接触状態にするものであるから、シール
部材の動作機構が煩雑である上に、圧力変動等で動作が
不安定となって流体の吸引効率を低下させたり、又、多
くの故障の原因を発生させる要因を包含している。However, according to the rotary seal member disclosed in Japanese Patent Laid-Open No. 4-60281, the suction force is reduced due to a trouble of the suction device, and the insertion surface where the fixed circular pipe and the rotary circular pipe are fitted to each other. Oil leaks from the annular groove.
Further, the fitting gap between the fixed circular pipe and the rotary circular pipe varies due to unbalance and rotary vibration of the rotary circular pipe, so that the suction and recovery efficiency of lubrication decreases. Furthermore, JP-A-6-241366
In the rotary joint of No. 3, when a gas is introduced into the port, the pair of seal members are kept in a non-contact state, and when the fluid is circulated, the pressure is applied to the diaphragm to bring the pair of seal members into a contact state. Therefore, in addition to the complicated operation mechanism of the seal member, the operation is unstable due to pressure fluctuation and the like, which lowers the fluid suction efficiency and causes many failures. .
【０００４】結局の所、一対のシール部材または、固定
円管と回転円管との嵌合隙間からの油漏れの発生を免れ
ることが出来ないほか、油漏れの吸引回収装置が必要不
可欠なものとなっている。従って、結果的にシール部材
の動作機構を煩雑とし、この周辺機器を大掛かりなもの
にしてしまうという問題がある。After all, oil leakage from the pair of seal members or the fitting gap between the fixed circular pipe and the rotary circular pipe cannot be avoided, and an oil leakage suction and recovery device is indispensable. Has become. Therefore, there is a problem that the operating mechanism of the seal member becomes complicated and the peripheral equipment becomes large-scale.
【０００５】本発明は、上記従来の回転シール部材が持
つ問題に鑑み、流体等の加圧力制御で加圧力を調節付与
されて接触する加圧部材により回転シール部材の回転側
部材に接触付与することで、油漏れなく且つ高速回転等
に対応できる主軸等の回転シール継手を提供することを
目的とする。In view of the problems of the above-described conventional rotary seal member, the present invention applies contact pressure to the rotary side member of the rotary seal member by means of a pressurizing member that is adjusted and applied by fluid pressure control. Therefore, it is an object of the present invention to provide a rotary seal joint for a main shaft or the like that can handle high-speed rotation without oil leakage.
【０００６】[0006]
【課題を解決するための手段】本発明は上記目的を達成
すべく、請求項１において、ドローイングバーの中心孔
への冷却潤滑液の供給や主軸尾端孔からの冷却潤滑液の
排出若しくは主軸尾端孔への供給を支配する回転シール
継手において、ドローイングバーや主軸等の回転体の端
部に嵌着させた回転部材と、この回転部材の端面に流体
等の加圧力制御で加圧力を調節付与されて接触する加圧
部材を固定体等に装備させてなることを特徴とする回転
シール継手である。In order to achieve the above-mentioned object, the present invention provides, in claim 1, the supply of the cooling lubricating liquid to the central hole of the drawing bar, the discharge of the cooling lubricating liquid from the tail end hole of the main spindle, or the main spindle. In the rotary seal joint that controls the supply to the tail end hole, the rotary member fitted to the end of the rotating body such as the drawing bar and the main shaft, and the pressurizing force of fluid etc. on the end surface of this rotary member The rotary seal joint is characterized in that a fixed member or the like is equipped with a pressure member that is adjusted and comes into contact with the fixed member.
【０００７】又、請求項２は、請求項１において、回転
部材の端面に所定の加圧力で接触する加圧部材は、冷却
潤滑液の供給流量や供給圧に比例的又は一定値で加圧力
制御する構成としたことを特徴する回転シール継手であ
る。According to a second aspect of the present invention, in the first aspect, the pressurizing member that comes into contact with the end surface of the rotating member with a predetermined pressurizing force pressurizes with a proportional or constant value to the supply flow rate or supply pressure of the cooling lubricating liquid. It is a rotary seal joint characterized in that it is configured to control.
【０００８】請求項３は、請求項１において、回転部材
の端面に所定の加圧力で接触する加圧部材は、主軸の回
転・停止に関連して加圧力制御する構成としたことを特
徴する回転シール継手である。According to a third aspect of the present invention, in the first aspect, the pressurizing member that comes into contact with the end surface of the rotary member with a predetermined pressurizing force is configured to control the pressurizing force in relation to the rotation / stop of the main shaft. It is a rotary seal joint.
【０００９】又、請求項４は、請求項１において、回転
部材の材質をセラミックス材にて構成する他、加圧部材
はその材質を耐摩耗性及び耐熱性，低摩擦係数等に優れ
たカーボン材にて構成したことを特徴とする回転シール
継手である。According to a fourth aspect of the present invention, the rotating member is made of a ceramic material, and the pressure member is made of a carbon material excellent in wear resistance, heat resistance, and low friction coefficient. This is a rotary seal joint characterized by being made of a material.
【００１０】[0010]
【作用】本発明によると、回転部材とこれに流体等の加
圧力制御で加圧力を調節付与されて接触する加圧部材と
により、この両者間の接触圧が最適圧に調節制御され、
ドローイングバーや主軸等の回転体の回転及び停止の外
部要因に係わりなく、冷却潤滑液を漏らすことな無く回
転シール継手の機能を果たす。According to the present invention, the contact pressure between the rotary member and the pressure member, which is brought into contact with the rotary member by adjusting the pressurizing force of the fluid or the like, is adjusted to the optimum pressure.
It functions as a rotary seal joint without leaking the cooling lubricant regardless of external factors such as rotation and stop of the rotating body such as the drawing bar and the main shaft.
【００１１】本発明の請求項４よると、請求項１，２，
３による作用に加え、回転体の高速回転時でも回転シー
ル継手に液漏れや発熱，異常摩耗等が見られず、１０年
以上もの長寿命を保証する作用が発揮される。According to claim 4 of the present invention, claims 1, 2,
In addition to the effect of No. 3, liquid leakage, heat generation, abnormal wear, etc. are not observed in the rotary seal joint even when the rotary body rotates at high speed, and the effect of guaranteeing a long life of 10 years or more is exhibited.
【００１２】[0012]
【実施例】以下、図面に示す実施例につき説明する。図
１は本発明に係る主軸等の回転シール継手を備えた主軸
装置の全体断面図であり、図２は本発明に係る主軸等の
回転シール継手を備えた主軸装置の部分拡大断面図であ
る。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments shown in the drawings will be described below. FIG. 1 is an overall sectional view of a spindle device including a rotary seal joint such as a spindle according to the present invention, and FIG. 2 is a partially enlarged sectional view of a spindle device including a rotary seal joint such as a spindle according to the present invention. .
【００１３】図１において、主軸装置１００の主軸１
は、その先端側を２つの軸受２，３によって支持され、
また後端側を１つの軸受４によって支持されている。上
記主軸１には、その中腹部１ＡにビルトインモータＢＭ
のローター５を嵌着しており、軸心位置に明けた内周孔
１Ｂには多層の皿バネ６とドローイングバー７を内装
し、主軸先端のテーパー穴１Ｃに挿入した工具Ｔを強力
に引き込み嵌着する。そして、上記ドローイングバー７
の後端７Ａには、アンクランプ装置１０のピストン１１
がシリンダ１２内に装嵌し、図示の後退したクランプ
と、ドローイングバー７側へ前進するときドローイング
バー７を強力に押出してアンクランプ動作する。しかし
て、通常は図１，２に示すように、ピストン１１が後退
したアンクランプ状態にある。In FIG. 1, the spindle 1 of the spindle device 100.
Is supported at its tip end by two bearings 2, 3,
The rear end side is supported by one bearing 4. The main shaft 1 has a built-in motor BM in the middle portion 1A thereof.
No. 5 rotor is fitted, and a multilayer disc spring 6 and a drawing bar 7 are installed in the inner peripheral hole 1B opened at the axial center position, and the tool T inserted into the tapered hole 1C at the tip of the main shaft is pulled in strongly. Fit in. And the above drawing bar 7
At the rear end 7A, the piston 11 of the unclamp device 10 is
Is fitted in the cylinder 12, and the drawing bar 7 is strongly pushed out to perform the unclamping operation when the drawing clamp is retracted and the drawing bar 7 is advanced to the drawing bar 7 side. Then, normally, as shown in FIGS. 1 and 2, the piston 11 is in a retracted unclamped state.
【００１４】上記アンクランプ装置１０のピストン１１
の尾端孔部１１Ａには、主軸１の軸芯冷却と３つの軸受
２，３，４のアンダーレース潤滑を行うための冷却潤滑
液Ｃが供給されている。ピストン１１の尾端孔部１１Ａ
に供給された冷却潤滑液Ｃは、接触式の第一回転シール
継手Ｋ１を介してピストン１１の通孔１１Ｂからドロー
イングバー７の中心孔７Ｂ内に送り込まれ、ドローイン
グバー７の先端に開口した通孔７Ｃからドローイングバ
ー７の外周に面した主軸１の内周孔１Ｂに流入する。主
軸１の内周孔１Ｂに流入した冷却潤滑液Ｃの大部分は、
主軸１の全長にわたって冷却すると共に、主軸中腹部１
Ａで多量に発生するローター５からの熱を冷却し、主軸
尾端孔部１Ｅと機枠Ｂ間に介在させた接触式の第二回転
シール継手Ｋ２の内周隙間Ｘを通って機枠Ｂの通孔Ｂ１
から外部へ軸芯冷却済液として放出する。これら冷却潤
滑液Ｃは、図示しない冷却装置により、冷却後に再び接
触式の第一回転シール継手Ｋ１を介してピストン１１の
通孔１１Ｂからドローイングバー７の中心孔７Ｂ内に送
り込まれる。The piston 11 of the unclamp device 10
The tail end hole portion 11A is supplied with a cooling lubricating liquid C for cooling the shaft core of the main shaft 1 and for underrace lubrication of the three bearings 2, 3 and 4. Piston 11 tail end hole 11A
The cooling lubricating liquid C supplied to the inside of the drawing bar 7 is sent from the through hole 11B of the piston 11 into the central hole 7B of the drawing bar 7 through the contact type first rotary seal joint K1 and is opened at the tip of the drawing bar 7. It flows from the hole 7C into the inner peripheral hole 1B of the main shaft 1 facing the outer periphery of the drawing bar 7. Most of the cooling lubricating liquid C flowing into the inner peripheral hole 1B of the main shaft 1 is
While cooling the entire length of the main shaft 1, the main shaft abdomen 1
The heat from the rotor 5 which is generated in a large amount in A is cooled, and passes through the inner peripheral gap X of the contact type second rotary seal joint K2 interposed between the main shaft tail end hole portion 1E and the machine frame B to form the machine frame B. Through hole B1
Is discharged to the outside as a shaft core cooled liquid. These cooling lubricating liquids C are sent into the center hole 7B of the drawing bar 7 from the through hole 11B of the piston 11 again through the contact type first rotary seal joint K1 after cooling by a cooling device (not shown).
【００１５】他方、主軸１の内周孔１Ｂに流入した冷却
潤滑液Ｃの一部分は、３つの軸受２，３，４のアンダー
レース潤滑を行うべく、内周孔１Ｂから半径方向に明け
た通孔１Ｆ，１Ｇ，１Ｈが各軸受２，３，４の内輪２
Ａ，３Ａ，４Ａに連絡している。これにより、冷却潤滑
液Ｃの一部分は、内周孔１Ｄから通孔１Ｆ，１Ｇ，１Ｈ
を通って各軸受２，３，４の内輪２Ａ，３Ａ，４Ａへ供
給され、アンダーレース潤滑を実施する。主軸１の先端
側軸受２，３を潤滑後の冷却潤滑液Ｃは、主軸固定機枠
１２側のドレン通路１２Ａから放出路１２Ｂに集めら
れ、又、主軸１の後端側軸受４を潤滑後の冷却潤滑液Ｃ
は、主軸固定機枠Ｂ側のドレン通路１２Ｃから放出路１
２Ｄに集められ、各々潤滑済液として放出する。On the other hand, a part of the cooling lubricating liquid C that has flowed into the inner peripheral hole 1B of the main shaft 1 passes through the inner peripheral hole 1B in the radial direction in order to perform underrace lubrication of the three bearings 2, 3 and 4. Inner ring 2 of each bearing 2, 3 and 4 has holes 1F, 1G and 1H
Contact A, 3A, 4A. As a result, a part of the cooling lubricating liquid C flows from the inner peripheral hole 1D to the through holes 1F, 1G, 1H.
And is supplied to the inner rings 2A, 3A, 4A of the bearings 2, 3, 4 to carry out underrace lubrication. The cooling lubricant C after lubricating the tip end side bearings 2 and 3 of the main spindle 1 is collected from the drain passage 12A on the main spindle fixed machine frame 12 side to the discharge passage 12B, and after the rear end side bearing 4 of the main spindle 1 is lubricated. Cooling lubricant C
From the drain passage 12C on the main shaft fixing machine frame B side to the discharge passage 1
Collected in 2D, each released as a lubricated liquid.
【００１６】尚、ビルトインモータＢＭの巻線コイル１
３を備えた固定子側の冷却ジャケット１３Ａには、外筒
冷却液Ｃ１が主軸固定機枠１２側の通路１２Ｅから送り
込まれ、冷却済の外筒冷却液Ｃ１が通路１２Ｆから外部
へ放出される。この外筒冷却液Ｃ１は、図示しない冷却
装置により、冷却後に再び通路１２Ｅから送り込まれ
る。The winding coil 1 of the built-in motor BM
The outer cylinder cooling liquid C1 is sent from the passage 12E on the main spindle fixing machine frame 12 side to the stator side cooling jacket 13A provided with 3, and the cooled outer cylinder cooling liquid C1 is discharged to the outside from the passage 12F. . The outer cylinder cooling liquid C1 is fed again from the passage 12E after being cooled by a cooling device (not shown).
【００１７】上記第一回転シール継手Ｋ１，第二回転シ
ール継手Ｋ２の概要構成を図２に示す。先ず、ピストン
１１の中心通孔１１Ｂからドローイングバー７の後端中
心孔７Ａ内に冷却潤滑液Ｃを送り込むための第一回転シ
ール継手Ｋ１は、ドローイングバー７の後端７Ｃに嵌着
した回転部材２０と、この後端面に流体シリンダ３０，
ピストン３１で加圧力Ｐ１を付与して接触する加圧部材
４０がピストン１１の中心通孔１１Ｂ内の拡径部１１Ｃ
に装備している。又、主軸尾端孔部１Ｅと機枠Ｂ間に介
在させた接触式の第二回転シール継手Ｋ２は、主軸尾端
孔部１Ｅの環体５０に係合させた回転部材６０と、この
後端面に流体シリンダ７０，ピストン７１で加圧力Ｐ２
を付与して接触する加圧部材８０が機枠Ｂに固定した支
持環体９０内に装備している。FIG. 2 shows a schematic structure of the first rotary seal joint K1 and the second rotary seal joint K2. First, the first rotary seal joint K1 for feeding the cooling lubricating liquid C from the center through hole 11B of the piston 11 into the rear end center hole 7A of the drawing bar 7 is a rotary member fitted to the rear end 7C of the drawing bar 7. 20 and a fluid cylinder 30,
The pressurizing member 40, which applies the pressing force P1 with the piston 31 and is in contact with the piston 31, is the expanded diameter portion 11C in the central through hole 11B of the piston 11.
Equipped. Further, the contact type second rotary seal joint K2 interposed between the spindle tail end hole 1E and the machine frame B includes the rotary member 60 engaged with the ring body 50 of the spindle tail end hole 1E, and Pressurization P2 by fluid cylinder 70 and piston 71 on the end surface
The pressing member 80 that applies and contacts is mounted in the support ring 90 fixed to the machine frame B.
【００１８】次に、第一回転シール継手Ｋ１の詳細構成
を、図３により説明する。ドローイングバー７の後端７
Ｃに嵌着したコ字型断面の環体ホルダ２１内に、環状の
回転部材２０が嵌入し、ピン２２で軸方向のみ移動自在
に一体的に支持されている。他方、環状の加圧部材４０
は、ピストン１１の拡径部１１Ｃにピン４３で軸方向の
み移動自在に一体的に備える倒Ｙ字断面の環体ホルダ４
１における凹部４２に設けた流体シリンダ３０と、これ
に嵌合するピストン３１を介して移動可能に嵌合してい
る。上記流体シリンダ３０のピストン３１は、加圧力Ｐ
１を加圧部材４０に付与し、この加圧力Ｐ１を加圧部材
４０の接触輪片４０Ａを介して接触する回転部材２０の
端面に付与している。Next, the detailed structure of the first rotary seal joint K1 will be described with reference to FIG. Rear end 7 of drawing bar 7
An annular rotary member 20 is fitted in a ring-shaped holder 21 having a U-shaped cross section fitted in C, and is integrally supported by a pin 22 so as to be movable only in the axial direction. On the other hand, the annular pressure member 40
Is an annular holder 4 having an inverted Y-shaped cross section, which is integrally provided on the expanded diameter portion 11C of the piston 11 with a pin 43 so as to be movable only in the axial direction.
The fluid cylinder 30 provided in the concave portion 42 of FIG. 1 and the fluid cylinder 30 are movably fitted through the piston 31 fitted therein. The piston 31 of the fluid cylinder 30 has a pressing force P
1 is applied to the pressing member 40, and this pressing force P1 is applied to the end surface of the rotating member 20 that contacts via the contact wheel piece 40A of the pressing member 40.
【００１９】尚、上記回転部材２０の材質は、軽量であ
って耐摩耗性や耐薬品性及び耐熱性，低摩擦係数等に優
れたセラミックス材が採用されている。また、加圧部材
４０の材質は、耐摩耗性及び耐熱性，低摩擦係数等に優
れたカーボン材が採用されている。これら材質の採用に
より、回転部材２０とこれに所定の加圧力Ｐ１を付与す
る加圧部材４０の接触輪片４０Ａとは、冷却潤滑液Ｃを
漏らすこと無く回転シール継手Ｋ１の機能を果たす事が
出来、高速回転でも１０年以上の長寿命を保証する。The rotary member 20 is made of a lightweight ceramic material having excellent wear resistance, chemical resistance, heat resistance and low friction coefficient. Further, as the material of the pressing member 40, a carbon material excellent in wear resistance, heat resistance, low friction coefficient, etc. is adopted. By adopting these materials, the rotary member 20 and the contact wheel piece 40A of the pressurizing member 40 that applies a predetermined pressing force P1 thereto can fulfill the function of the rotary seal joint K1 without leaking the cooling lubricating liquid C. It is possible and guarantees a long life of 10 years or more even at high speed rotation.
【００２０】続いて、第二回転シール継手Ｋ２の詳細構
成を、図３により説明する。主軸尾端孔部１Ｅには、コ
字型断面のホルダ部５１を持つ環体５０がボルト５２に
より締結されている。上記ホルダ部５１には、環状の回
転部材６０が嵌入してピン５３で軸方向のみ移動自在に
一体的に備えられている。他方、環状の加圧部材８０
は、機枠Ｂに固定した支持環体９０のコ字型断面のホル
ダ部９１の内周壁に嵌着したスプライン筒９２の内周面
に軸方向のみ移動自在に一体的に備えている。支持環体
９０の凹部９３に備える流体シリンダ７０と、このピス
トン７１は、加圧力Ｐ２を加圧部材８０に付与し、この
加圧力Ｐ１を加圧部材８０の接触輪片８０Ａを介して接
触する回転部材６０の端面に付与している。上記環体５
０や支持環体９０の内周面と、ドローイングバー７の外
周面との間には隙間Ｘを設け、この隙間Ｘから主軸冷却
した冷却潤滑液Ｃを機枠Ｂの通孔Ｂ１へと導き、第二回
転シール継手Ｋ２にて冷却潤滑液Ｃの漏れを防止する機
能を果たしている。Next, the detailed structure of the second rotary seal joint K2 will be described with reference to FIG. A ring body 50 having a holder portion 51 having a U-shaped cross section is fastened to the spindle tail end hole portion 1E with a bolt 52. An annular rotary member 60 is fitted into the holder portion 51 and integrally provided with a pin 53 so as to be movable only in the axial direction. On the other hand, the annular pressure member 80
Is integrally provided on an inner peripheral surface of a spline cylinder 92 fitted to an inner peripheral wall of a holder portion 91 having a U-shaped cross section of the support ring 90 fixed to the machine frame B so as to be movable only in the axial direction. The fluid cylinder 70 provided in the concave portion 93 of the support ring body 90 and the piston 71 apply a pressing force P2 to the pressing member 80, and the pressing force P1 is contacted via the contact wheel piece 80A of the pressing member 80. It is provided on the end surface of the rotating member 60. The ring 5
0 or the inner peripheral surface of the support ring 90 and the outer peripheral surface of the drawing bar 7 are provided with a gap X from which the cooling liquid C cooled by the spindle is guided to the through hole B1 of the machine frame B. The second rotary seal joint K2 serves to prevent the leakage of the cooling lubricating liquid C.
【００２１】尚、上記回転部材６０の材質も、軽量であ
って耐摩耗性や耐薬品性及び耐熱性，低摩擦係数等に優
れたセラミックス材が採用されている。そして、加圧部
材８０の材質も、耐摩耗性及び耐熱性，低摩擦係数等に
優れたカーボン材が採用されている。これら材質の採用
により、回転部材６０とこれに所定の加圧力Ｐ２を付与
する加圧部材８０の接触輪片８０Ａとは、冷却潤滑液Ｃ
を漏らすこと無く回転シール継手Ｋ２の機能を果たす事
が出来、高速回転でも１０年以上の長寿命を保証する。As the material of the rotating member 60, a ceramic material which is lightweight and is excellent in wear resistance, chemical resistance, heat resistance, low friction coefficient, etc. is adopted. As the material of the pressing member 80, a carbon material having excellent wear resistance, heat resistance, low friction coefficient, etc. is adopted. By adopting these materials, the rotating member 60 and the contact wheel piece 80A of the pressurizing member 80 for applying a predetermined pressing force P2 thereto are cooled by the cooling lubricant C.
The function of the rotary seal joint K2 can be fulfilled without leaking, and a long life of 10 years or more is guaranteed even at high speed rotation.
【００２２】上記第一回転シール継手Ｋ１，第二回転シ
ール継手Ｋ２の各流体シリンダ３０，７０には、冷却潤
滑液Ｃの供給源Ｐからの流体圧が圧力調節器Ｖを介して
供給される。この圧力調節器Ｖは、制御器Ｃｏによって
制御されるように、主軸１の回転計Ｄ１や冷却潤滑液Ｃ
の圧力計Ｄ２や冷却潤滑液Ｃの流量計Ｄ３等からの情報
信号を受け且つ予め動作特性を記憶した記憶素子ＲＯＭ
との照合により、現状の圧力調節を決定し各流体シリン
ダ３０，７０に所定圧の冷却潤滑液Ｃの一部を供給する
ように構成されている。Fluid pressure from a supply source P of the cooling lubricating liquid C is supplied to each of the fluid cylinders 30 and 70 of the first rotary seal joint K1 and the second rotary seal joint K2 via a pressure regulator V. . The pressure adjuster V includes a tachometer D1 of the main shaft 1 and a cooling lubricant C as controlled by a controller Co.
A storage element ROM that receives information signals from the pressure gauge D2 and the flow meter D3 of the cooling lubricant C and stores the operating characteristics in advance.
It is configured to determine the current pressure adjustment by supplying the above-mentioned and to supply a part of the cooling lubricant C having a predetermined pressure to each fluid cylinder 30, 70.
【００２３】本発明の各回転シール継手Ｋ１，Ｋ２は上
記のように構成されており、以下のように作用する。ア
ンクランプ装置１０のピストン１１の尾端孔部１１Ａに
は、主軸１の軸芯冷却と３つの軸受２，３，４のアンダ
ーレース潤滑を行うための冷却潤滑液Ｃが供給源Ｐのポ
ンプから供給される。上記尾端孔部１１Ａに供給された
冷却潤滑液Ｃは、第一回転シール継手Ｋ１を介してピス
トン１１の通孔１１Ｂからドローイングバー７の中心孔
７Ｂ内に送り込まれ、ドローイングバー７の先端に開口
した通孔７Ｃからドローイングバー７の外周に面した主
軸１の内周孔１Ｂに流入する。上記第一回転シール継手
Ｋ１は、アンクランプ装置１０のクランプ，アンクラン
プ動作状態や主軸１の回転及び停止に係わりなく常に安
定したシール作用を発揮する。The rotary seal joints K1 and K2 of the present invention are constructed as described above, and operate as follows. In the tail end hole portion 11A of the piston 11 of the unclamp device 10, the cooling lubricating liquid C for cooling the core of the main shaft 1 and the underrace lubrication of the three bearings 2, 3, 4 is supplied from the pump of the supply source P. Supplied. The cooling lubricating liquid C supplied to the tail end hole portion 11A is sent from the through hole 11B of the piston 11 into the central hole 7B of the drawing bar 7 via the first rotary seal joint K1, and then reaches the tip of the drawing bar 7. From the opened through hole 7C, it flows into the inner peripheral hole 1B of the main shaft 1 facing the outer periphery of the drawing bar 7. The first rotary seal joint K1 always exhibits a stable sealing action irrespective of the clamp and unclamp operation states of the unclamp device 10 and the rotation and stop of the main shaft 1.
【００２４】回転部材２０に圧接する接触輪片４０Ａの
加圧部材４０は、流体シリンダ３０とピストン３１によ
り所定の加圧力Ｐ１を付与することで行う。即ち、制御
器Ｃｏは、主軸１の回転計Ｄ１や冷却潤滑液Ｃの圧力計
Ｄ２や冷却潤滑液Ｃの流量計Ｄ３等からの情報信号を受
け且つ予め動作特性を記憶した記憶素子ＲＯＭとの照合
により、圧力調節器Ｖに対して流体シリンダ３０に付与
する所定の加圧力Ｐ１を決定する。この両者２０，４０
間の接触圧Ｐ１は、図４に示すように、主軸１の停止時
にはＰｏに低下させ、主軸１の回転時に所定の加圧力Ｐ
１となるようにＯＮ，ＯＦＦ制御される。The pressurizing member 40 of the contact wheel piece 40A in pressure contact with the rotating member 20 is provided by applying a predetermined pressurizing force P1 by the fluid cylinder 30 and the piston 31. That is, the controller Co has a storage element ROM that receives information signals from the tachometer D1 of the main shaft 1, the pressure gauge D2 of the cooling lubricating liquid C, the flow meter D3 of the cooling lubricating liquid C, and the like, and stores the operating characteristics in advance. A predetermined pressing force P1 applied to the fluid cylinder 30 with respect to the pressure regulator V is determined by collation. Both of these 20, 40
As shown in FIG. 4, the contact pressure P1 between them is reduced to Po when the main spindle 1 is stopped, and a predetermined pressing force P is generated when the main spindle 1 rotates.
ON / OFF control is performed so that it becomes 1.
【００２５】更に、図５に示すように、冷却潤滑液Ｃの
供給圧Ｐ´や供流給量Ｑに係わらず「点線」のように一
定に制御させ、主軸１の回転及び停止や外部変動の要因
に係わりなく、冷却潤滑液Ｃを漏らすことも無く回転シ
ール継手Ｋ１の機能を果たす。また、図５に「実線」で
示すように、冷却潤滑液Ｃの供給圧Ｐ´や供流給量Ｑと
の関係を予め記憶されている記憶素子ＲＯＭとの照合に
より、比例的に両者２０，４０間の接触圧Ｐ１を増減制
御させられる。特に、回転部材２０とこれに所定の加圧
力Ｐ１を付与する加圧部材４０の接触輪片４０Ａとによ
り、この両者２０，４０間の接触圧が冷却潤滑液Ｃの供
給圧Ｐ´や供流給量Ｑと比例的に制御させると主軸１の
回転及び停止や外部変動の要因にも係わらず、冷却潤滑
液Ｃを漏らすことも無く回転シール継手Ｋ１の機能を果
たす。Further, as shown in FIG. 5, regardless of the supply pressure P'of the cooling lubricating liquid C and the supply flow rate Q, it is controlled to be constant as shown by the "dotted line" to rotate and stop the main spindle 1 or to cause external fluctuations. Irrespective of the above factor, the function of the rotary seal joint K1 is achieved without leaking the cooling lubricating liquid C. Further, as indicated by the “solid line” in FIG. 5, the relationship between the supply pressure P ′ of the cooling lubricant C and the supply flow rate Q is compared with a storage element ROM that is stored in advance, and both are proportionally increased. , 40 can be controlled to increase or decrease the contact pressure P1. In particular, the contact pressure between the rotary member 20 and the contact wheel piece 40A of the pressure member 40 that applies a predetermined pressure P1 to the rotary member 20 causes the contact pressure between the two members 20 and 40 to be the supply pressure P ′ of the cooling lubricant C and the supply flow. When controlled in proportion to the supply amount Q, the function of the rotary seal joint K1 is achieved without leaking the cooling lubricant C regardless of factors such as rotation and stop of the main shaft 1 and external fluctuations.
【００２６】次に、主軸１の内周孔１Ｂに流入した冷却
潤滑液Ｃの大部分は、主軸１の全長にわたって冷却する
と共に、主軸中腹部１Ａで多量に発生するローター５か
らの熱を冷却し、主軸尾端孔部１Ｅと機枠Ｂ間に介在さ
せた接触式の第二回転シール継手Ｋ２の内周隙間Ｘを通
って機枠Ｂの通孔Ｂ１から外部へ軸芯冷却済液として放
出する。上記第二回転シール継手Ｋ２は、主軸１の回転
及び停止に係わりなく常に安定したシール作用を発揮す
る。Next, most of the cooling lubricating liquid C that has flowed into the inner peripheral hole 1B of the main shaft 1 is cooled over the entire length of the main shaft 1, and at the same time, the heat from the rotor 5 that is generated in large amounts in the middle portion 1A of the main shaft is cooled. Then, through the inner peripheral clearance X of the contact-type second rotary seal joint K2 interposed between the spindle tail end hole portion 1E and the machine frame B, from the through hole B1 of the machine frame B to the outside as a shaft core cooled liquid. discharge. The second rotary seal joint K2 always exhibits a stable sealing action regardless of the rotation and stop of the main shaft 1.
【００２７】即ち、回転部材６０に圧接する接触輪片８
０Ａの加圧部材８０は、流体シリンダ７０とピストン７
１により所定の加圧力Ｐ２を付与することで行う。ここ
で、制御器Ｃｏは、主軸１の回転計Ｄ１や冷却潤滑液Ｃ
の圧力計Ｄ２や冷却潤滑液Ｃの流量計Ｄ３等からの情報
信号を受け且つ予め動作特性を記憶した記憶素子ＲＯＭ
との照合により、圧力調節器Ｖに対して流体シリンダ７
０に付与する所定の加圧力Ｐ２を決定する。この両者６
０，８０間の接触圧Ｐ２は、図４に示すように、主軸１
の停止時にはＰｏに低下させ、主軸１の回転時に所定の
加圧力Ｐ２となるようにＯＮ，ＯＦＦ制御される。That is, the contact wheel piece 8 pressed against the rotating member 60.
The pressurizing member 80 of 0 A includes the fluid cylinder 70 and the piston 7.
It is performed by applying a predetermined pressing force P2 with 1. Here, the controller Co includes the tachometer D1 of the main shaft 1 and the cooling lubricant C.
A storage element ROM that receives information signals from the pressure gauge D2 and the flow meter D3 of the cooling lubricant C and stores the operating characteristics in advance.
By comparing with the pressure regulator V, the fluid cylinder 7
A predetermined pressing force P2 applied to 0 is determined. Both 6
The contact pressure P2 between 0 and 80 is, as shown in FIG.
When the main shaft 1 is stopped, it is reduced to Po, and when the main shaft 1 is rotated, ON / OFF control is performed so as to obtain a predetermined pressing force P2.
【００２８】更に、図５に示すように、冷却潤滑液Ｃの
供給圧Ｐ´や供流給量Ｑに係わらず「点線」のように一
定に制御させ、主軸１の回転及び停止や外部変動の要因
に係わりなく、冷却潤滑液Ｃを漏らすことも無く回転シ
ール継手Ｋ２の機能を果たす。また、図５に「実線」で
示すように、冷却潤滑液Ｃの供給圧Ｐ´や供流給量Ｑと
の関係を予め記憶されている記憶素子ＲＯＭとの照合に
より、比例的に両者６０，８０間の接触圧Ｐ２を増減制
御させられる。特に、回転部材６０とこれに所定の加圧
力Ｐ２を付与する加圧部材８０の接触輪片８０Ａとによ
り、この両者６０，８０間の接触圧が冷却潤滑液Ｃの供
給圧Ｐ´や供流給量Ｑと比例的に制御させると主軸１の
回転及び停止や外部変動の要因にも係わらず、冷却潤滑
液Ｃを漏らすことも無く回転シール継手Ｋ２の機能を果
たす。Further, as shown in FIG. 5, regardless of the supply pressure P'of the cooling lubricating liquid C and the supply flow rate Q, it is controlled to be constant as indicated by the "dotted line" to rotate and stop the main shaft 1 or to cause external fluctuations. Irrespective of the above factors, the function of the rotary seal joint K2 is achieved without leaking the cooling lubricating liquid C. Further, as indicated by the "solid line" in FIG. 5, the relationship between the supply pressure P'of the cooling lubricant C and the supply flow rate Q is compared with a storage element ROM stored in advance, and both 60 are proportionally calculated. , 80 to increase / decrease the contact pressure P2. In particular, the contact pressure between the rotating member 60 and the contact wheel piece 80A of the pressurizing member 80 that applies a predetermined pressure P2 to the rotating member 60 causes the contact pressure between the two 60, 80 to be the supply pressure P ′ of the cooling lubricating liquid C or the supply flow. When controlled proportionally to the supply amount Q, the function of the rotary seal joint K2 is achieved without leaking the cooling lubricant C regardless of factors such as rotation and stop of the main shaft 1 and external fluctuations.
【００２９】上記冷却潤滑液Ｃは、図示しない冷却装置
により、冷却後に再び接触式の第一回転シール継手Ｋ１
を介してピストン１１の通孔１１Ｂからドローイングバ
ー７の中心孔７Ｂ内に送り込まれる。他方、主軸１の内
周孔１Ｂに流入した冷却潤滑液Ｃの一部分は、３つの軸
受２，３，４のアンダーレース潤滑を内周孔１Ｂから半
径方向に明けた通孔１Ｆ，１Ｇ，１Ｈから各軸受２，
３，４の内輪２Ａ，３Ａ，４Ａに流れ込み、アンダーレ
ース潤滑をする。主軸１の先端側軸受２，３を潤滑後の
冷却潤滑液Ｃは、主軸固定機枠１２側のドレン通路１２
Ａから放出路１２Ｂに集められ、又、主軸１の後端側軸
受４を潤滑後の冷却潤滑液Ｃは、主軸固定機枠Ｂ側のド
レン通路１２Ｃから放出路１２Ｄに集められ、各々潤滑
済液Ｃ´として放出する。この潤滑済液Ｃ´は再利用さ
れる。The cooling lubricant C is cooled again by a cooling device (not shown) and then contacted again to the first rotary seal joint K1.
Through the through hole 11B of the piston 11 into the central hole 7B of the drawing bar 7. On the other hand, a part of the cooling lubricating liquid C that has flowed into the inner peripheral hole 1B of the main shaft 1 is a through hole 1F, 1G, 1H which is the underrace lubrication of the three bearings 2, 3, 4 which is opened radially from the inner peripheral hole 1B. From each bearing 2,
It flows into the inner rings 2A, 3A, 4A of 3, 4 and under-race lubricates. The cooling lubricating liquid C after lubricating the tip end side bearings 2 and 3 of the main shaft 1 is the drain passage 12 on the main shaft fixing machine frame 12 side.
The cooling lubricating liquid C collected from A to the discharge passage 12B and after lubricating the rear end side bearing 4 of the main shaft 1 is collected from the drain passage 12C on the main shaft fixed machine frame B side to the discharge passage 12D and is lubricated respectively. Discharge as liquid C '. This lubricated liquid C'is reused.
【００３０】本発明は、上記実施例に限定されることな
く発明の要旨内での細部の設計変更が可能である。例え
ば、回転シール継手Ｋ１，Ｋ２は上記構成に限定され
ず、詳細な部分構成を自由に設計変更できる。The present invention is not limited to the above-mentioned embodiments, and it is possible to change the design in details within the scope of the invention. For example, the rotary seal joints K1 and K2 are not limited to the above configuration, and the detailed partial configuration can be freely designed and changed.
【００３１】[0031]
【効果】本発明の請求項１，２，３によると、回転部材
とこれに所定の加圧力を付与する加圧部材の接触輪片と
により、この両者間の接触圧が簡潔な構成手段で主軸回
転や供給流量，供給圧に関係して一定乃至比例的に制御
されるから、ドローイングバーや主軸等の回転体の回転
及び停止や外部変動の要因に係わりなく、冷却潤滑液を
漏らすことも無く回転シール継手の機能を果たす。特
に、主軸等の高速回転時には、これと一体回転する回転
部材に求心作用が働き、液漏れの防止機能が長期間にわ
たり発揮する効果がある。According to the first, second, and third aspects of the present invention, the contact pressure between the rotary member and the contact wheel piece of the pressurizing member for applying a predetermined pressing force to the rotary member is simple. Since it is controlled in a constant or proportional manner in relation to the main shaft rotation, supply flow rate, and supply pressure, it is possible to leak the cooling lubricant regardless of factors such as rotation and stop of the rotating body such as the drawing bar and main shaft, and external fluctuations. Without functioning as a rotary seal joint. In particular, at the time of high-speed rotation of the main shaft or the like, a centripetal effect is exerted on the rotary member that rotates integrally with the main shaft, and the effect of preventing liquid leakage is exerted for a long period of time.
【００３２】本発明の請求項４によると、請求項１，
２，３による効果に加え、回転体の高速回転時でも回転
シール継手に液漏れや発熱，異常摩耗等が見られず、１
０年以上もの長寿命を保証する効果がある。According to Claim 4 of the present invention, Claim 1,
In addition to the effects of 2 and 3, no liquid leakage, heat generation, abnormal wear, etc. were observed in the rotary seal joint even when the rotating body rotated at high speed.
It has the effect of guaranteeing a long life of 0 years or more.
【図１】本発明に係る主軸等の回転シール継手を備えた
主軸装置の全体断面図である。FIG. 1 is an overall cross-sectional view of a spindle device including a rotary seal joint for a spindle or the like according to the present invention.
【図２】本発明に係る主軸等の回転シール継手の拡大断
面図である。FIG. 2 is an enlarged sectional view of a rotary seal joint for a main shaft and the like according to the present invention.
【図３】本発明の各回転シール継手とこの制御系の詳細
構成を示す拡大断面図である。FIG. 3 is an enlarged cross-sectional view showing a detailed configuration of each rotary seal joint of the present invention and this control system.
【図４】本発明の各回転シール継手の動作特性を示す説
明図である。FIG. 4 is an explanatory diagram showing operating characteristics of each rotary seal joint of the present invention.
【図５】本発明の各回転シール継手の動作特性を示す説
明図である。FIG. 5 is an explanatory diagram showing operating characteristics of each rotary seal joint of the present invention.
１ 主軸 １Ｅ 主軸尾端孔部 ２，３，４ 軸受 ２Ａ，３Ａ，４Ａ 内輪 ７ ドローイングバー ７Ｃ 通孔 １０ アンクランプ装置 １１ ピストン ２０，６０ 回転部材 ２１ 環体ホルダ ３０，７０ 流体シリンダ ３１，７１ ピストン ４０，８０ 加圧部材 ４０Ａ，８０Ａ 接触輪片 ４１ 環体ホルダ ５０ 環体 ６０ 回転部材 ９０ 支持環体 Ｂ 機枠 Ｃ 冷却潤滑液 Ｃ１ 外筒冷却液 Ｃｏ 制御器 Ｋ１ 第一回転シール継
手 Ｋ２ 第二回シール転継
手 Ｖ 圧力調節器1 Spindle 1E Spindle tail end hole 2,3,4 Bearing 2A, 3A, 4A Inner ring 7 Drawing bar 7C Through hole 10 Unclamping device 11 Piston 20,60 Rotating member 21 Annular holder 30,70 Fluid cylinder 31,71 Piston 40, 80 Pressurizing member 40A, 80A Contact wheel piece 41 Ring body holder 50 Ring body 60 Rotating member 90 Support ring body B Machine frame C Cooling lubricant C1 Outer cylinder cooling liquid Co Controller K1 1st rotary seal joint K2 2nd Single-sealing rolling joint V Pressure regulator
Claims (4)
液の供給や主軸尾端孔からの冷却潤滑液の排出若しくは
主軸尾端孔への供給を支配する回転シール継手におい
て、ドローイングバーや主軸等の回転体の端部に嵌着さ
せた回転部材と、この回転部材の端面に流体等の加圧力
制御で加圧力を調節付与されて接触する加圧部材を固定
体等に装備させてなることを特徴とする回転シール継
手。1. A rotary seal joint that controls the supply of cooling lubricant to the center hole of the drawing bar, the discharge of cooling lubricant from the spindle tail end hole, or the supply to the spindle tail end hole. The rotating member fitted to the end of the rotating body, and the pressurizing member that is brought into contact with the end face of the rotating member by adjusting the pressing force of the fluid or the like to make contact with the fixed body. A rotary seal joint characterized by.
定の加圧力で接触する加圧部材は、冷却潤滑液の供給流
量や供給圧に比例的又は一定値で加圧力制御する構成と
したことを特徴する回転シール継手。2. The pressurizing member, which comes into contact with the end surface of the rotary member at a predetermined pressurizing force, controls the pressurizing force in proportion to or constant value of the supply flow rate or supply pressure of the cooling lubricating liquid. A rotary seal joint characterized in that
定の加圧力で接触する加圧部材は、主軸の回転・停止に
関連して加圧力制御する構成としたことを特徴する回転
シール継手。3. The rotary seal joint according to claim 1, wherein the pressurizing member contacting the end surface of the rotary member with a predetermined pressurizing force controls the pressurizing force in relation to the rotation / stop of the main shaft. .
ラミックス材にて構成する他、加圧部材はその材質を耐
摩耗性及び耐熱性，低摩擦係数等に優れたカーボン材に
て構成したことを特徴とする回転シール継手。4. The rotating member according to claim 1, wherein the rotating member is made of a ceramic material, and the pressing member is made of a carbon material having excellent wear resistance, heat resistance and low friction coefficient. A rotary seal joint characterized in that
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4242495A JPH08210573A (en) | 1995-02-07 | 1995-02-07 | Rotary sealing joint |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4242495A JPH08210573A (en) | 1995-02-07 | 1995-02-07 | Rotary sealing joint |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08210573A true JPH08210573A (en) | 1996-08-20 |
Family
ID=12635686
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4242495A Pending JPH08210573A (en) | 1995-02-07 | 1995-02-07 | Rotary sealing joint |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08210573A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007085408A (en) * | 2005-09-21 | 2007-04-05 | Rix Corp | Rotary joint |
| JP2008261405A (en) * | 2007-04-11 | 2008-10-30 | Rix Corp | Rotary sealing mechanism in fluid feeding mechanism, and rotary joint |
| JP2014240699A (en) * | 2013-06-11 | 2014-12-25 | クリスティアン マイアー ゲーエムベーハー ウント コンパニ カーゲー マシネンファブリーク | Medium delivering device |
| CN105953000A (en) * | 2016-07-19 | 2016-09-21 | 滕州市天旋旋转接头制造有限公司 | Medium-pressure high-speed rotating connector |
-
1995
- 1995-02-07 JP JP4242495A patent/JPH08210573A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007085408A (en) * | 2005-09-21 | 2007-04-05 | Rix Corp | Rotary joint |
| JP4597017B2 (en) * | 2005-09-21 | 2010-12-15 | リックス株式会社 | Rotary joint |
| JP2008261405A (en) * | 2007-04-11 | 2008-10-30 | Rix Corp | Rotary sealing mechanism in fluid feeding mechanism, and rotary joint |
| JP4542114B2 (en) * | 2007-04-11 | 2010-09-08 | リックス株式会社 | Rotary seal mechanism and rotary joint in fluid feed mechanism |
| JP2014240699A (en) * | 2013-06-11 | 2014-12-25 | クリスティアン マイアー ゲーエムベーハー ウント コンパニ カーゲー マシネンファブリーク | Medium delivering device |
| EP2813740A3 (en) * | 2013-06-11 | 2015-03-25 | Christian Maier GmbH & Co. KG Maschinenfabrik | Device for transporting media |
| CN105953000A (en) * | 2016-07-19 | 2016-09-21 | 滕州市天旋旋转接头制造有限公司 | Medium-pressure high-speed rotating connector |
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