WO2009109355A1 - Passage tournant - Google Patents

Passage tournant Download PDF

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Publication number
WO2009109355A1
WO2009109355A1 PCT/EP2009/001490 EP2009001490W WO2009109355A1 WO 2009109355 A1 WO2009109355 A1 WO 2009109355A1 EP 2009001490 W EP2009001490 W EP 2009001490W WO 2009109355 A1 WO2009109355 A1 WO 2009109355A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotary feedthrough
stator
sealing
rotor
feedthrough according
Prior art date
Application number
PCT/EP2009/001490
Other languages
German (de)
English (en)
Inventor
Daniel Birlinger
Original Assignee
Hunger Maschinen Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hunger Maschinen Gmbh filed Critical Hunger Maschinen Gmbh
Publication of WO2009109355A1 publication Critical patent/WO2009109355A1/fr

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
    • F16L39/00—Joints or fittings for double-walled or multi-channel pipes or pipe assemblies
    • F16L39/06—Joints or fittings for double-walled or multi-channel pipes or pipe assemblies of the multiline swivel type, e.g. comprising a plurality of axially mounted modules
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B21/00—Methods or apparatus for flushing boreholes, e.g. by use of exhaust air from motor
    • E21B21/02—Swivel joints in hose-lines
    • 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
    • F16L27/087—Joints with radial fluid passages

Definitions

  • the invention relates to a rotary feedthrough with a stator and a rotatably mounted in the stator by means of a rotationally symmetrical guide surface, rotatable about an axis rotor, wherein the stator at least a first fluid conduit and the rotor has at least one second fluid conduit, each opening in the guide surface and during rotation the rotor in the stator are in communication with each other, and further wherein axially adjacent to the mouth at least one annular seal is provided, in which an arranged in the stator or the rotor, annular sealing body is pressed with a predetermined contact pressure against the rotor or the stator.
  • the invention further relates to a method for operating a rotary feedthrough.
  • the invention relates to a use of a rotary feedthrough.
  • Rotary unions are well known, for example from DE 40 19 987 C2.
  • boring bars in derricks are successively screwed together in drilling down a borehole to form an increasingly longer drill string.
  • an aggregate is used, which is arranged around the end of a first boring bar to be screwed in and fixed in space.
  • the rotary union serves to supply a working fluid (or more) of, for example, 150 bar pressure and a control fluid (or more) of lower pressure to the boring tool for the boring bars.
  • the screwing in takes place at a relatively low speed in the range between 15 and 25 rpm, depending on the steepness of the respective thread.
  • the pressure is removed and drilling can continue.
  • the device remains on the drill rod, so it rotates with this idle.
  • drilling a much higher speed is set, for example, from 90 to 100 U / min.
  • Rotary feedthroughs are also known, for example from the already mentioned DE 40 19 987 C2, which use a hydrostatic seal, for example a gap seal.
  • a hydrostatic seal for example a gap seal.
  • the invention is based on the object, a rotary feedthrough, a use and a method of the type mentioned in such a way that the above-mentioned disadvantages are avoided.
  • the leakage rate of the rotary feedthrough should be low and in the idle phase, the seal friction low.
  • this object is achieved in that means are provided to selectively press the sealing body with at least two different contact pressures.
  • the object is achieved in that the rotary feedthrough is operated with high contact pressure and small peripheral speed of the guide surface when the fluid lines are subjected to a fluid under working pressure, and with low contact pressure and high peripheral speed is operated when the fluid lines are depressurized.
  • the contact pressure of the seals in the rotary feedthrough is set differently, namely in the working phase high and low in the idling phase.
  • the leak rate is kept low in the working phase and reduced in the idle phase, the seal wear, and the gaskets heat up only slightly.
  • a contact pressure is substantially equal to zero.
  • This measure has the advantage that at idle the wear and thus the heating of the seals are reduced to a minimum.
  • the sealing body arranged in the stator is out of contact with the rotor at a contact pressure or vice versa.
  • This measure has the advantage that during the working phase, the seal is fully biased and fully sealed almost without leakage. In the idle phase, however, the individual pressure rotary seals are not in contact with their respective mating surface.
  • This measure has the advantage that the rotary feedthrough is completely sealed to the outside even if the rotary pressure seals in the idle phase are not in contact with their respective mating surface.
  • the further seals are designed as shaft seals.
  • This measure has the advantage that commercially available components can be used.
  • stator has a relative to the stator movable sealing bush, wherein the sealing body is arranged in the sealing bush and the contact pressure varies depending on the position of the sealing bushing relative to the stator.
  • This measure has the advantage that the contact pressure can be changed by simply moving the sealing bushing.
  • the at least first fluid conduit in the sealing bushing contains a first annular groove, wherein the sealing bush is displaceable in the direction of the axis and the regions are formed as second annular grooves in the guide surface of the rotor adjacent to the first annular grooves.
  • This measure has the advantage that the mechanical adjustment can be performed by a simple axial movement.
  • annular grooves have a rounded cross-sectional shape, and that preferably the sealing body rests with a tapered bearing side on the guide surface.
  • This measure has the advantage that in the process of the sealing bush, the sealing body is continuous, i. without jerky transition, is relaxed from its biased position, in which he then preferably no longer touches its respective mating surface. In this case, the contact pressure can be reduced to virtually zero, when the tapered bearing side dips into the rounded cross-sectional shape.
  • the sealing bush is hydraulically displaceable.
  • This measure has the advantage that the displacement of the sealing bush and thus the change in the contact pressure can be remotely controlled and quickly.
  • the sealing bush is preferably formed at the end as an annular piston, and the annular piston runs in an annular cylinder formed by the stator. This measure has the advantage that a compact size is created.
  • the sealing bush is hydraulically displaceable by means of a fluid tapped from one of the fluid lines.
  • This measure has the advantage that the need for separate fluid lines for moving the sealing bush is eliminated.
  • a channel opens into the guide surface, and the channel is substantially depressurized.
  • This measure has the advantage that changes in shape in the area of the fluid lines and the seals can be kept low, in particular in the area of fluid lines which serve as control lines.
  • the channel leads to a lateral pressure chamber which is bounded on the one hand by a further seal and on the other hand by an annular seal.
  • This measure has the advantage that a possibly accumulating pressure by moving the sealing bushing can not affect the shaft seals, which typically only withstand a pressure of up to 5 bar.
  • the rotor is mounted in the stator by means of two bearings arranged axially on both sides of the sealing bush, wherein in each case a cavity is located between the bearings and the sealing bush, and the cavities are connected to one another via a leakage line.
  • the leakage line runs axially through the sealing bushing.
  • This measure has the advantage that the cable routing is particularly simple and short.
  • the leakage line extends axially through the rotor.
  • This measure has the advantage that more installation space is available. As a result, the leakage line can be dimensioned with a larger diameter. Accordingly, a pressure equalization is possible even with rapid changes in position of the sealing bush with a small time constant.
  • the bearings are preferably sealed on their side facing away from the sealing bushing to the outside via the other seals and preferably designed as shaft sealing rings. Further preferably, the shaft seals are provided with an axially inner sealing lip and with an axially outer dust protection lip.
  • This measure has the advantage that air ingress is avoided in the area of the shaft sealing rings, in particular in the event of a rapid change in position of the sealing bushing.
  • the dust protection lip then has the additional advantage that it rests on the vacuum side and provides protection against air ingress.
  • the small peripheral speed is below 0.5 m / s
  • the high contact pressure is between 100 and 200 bar, preferably about 150 bar, further preferably is the high peripheral speed above 0.5 m / s, and the low contact pressure is in particular less than 0.5 bar.
  • Figure 1 is a side view of an embodiment of an inventive
  • Figure 2 shows a longitudinal section through the rotary feedthrough of Figure 1 along the line II-II;
  • FIG. 3 shows a detail of FIG. 2 in a working phase on a greatly enlarged scale
  • Figure 4 is a view like Figure 3, but for an idle phase
  • Figure 5 in greatly enlarged scale a cross-sectional view of a
  • FIG. 1 and 2 designates a rotary union as a whole.
  • the rotary leadthrough 10 has a stator 12 and a rotor 14 rotatable in the stator 12.
  • the axis of rotation of the rotor 14 is denoted by 16, and the rotation is indicated by an arrow 18.
  • the stator 12 and the rotor 14 both preferably have substantially the shape of a hollow cylinder, as can be seen clearly from FIG.
  • the longitudinal axis of the hollow cylinder coincides with the axis of rotation 18.
  • the rotary feedthrough is about 600 mm long and has a diameter of about 420 mm.
  • this is just one of many possible examples.
  • the rotor 14 has a first sleeve 20.
  • Axial channels extend in the first sleeve 20, one of which is shown at 22 in FIG.
  • From the inner end of the axial channel 22 is a radial channel 24, which opens at an outer surface of the first sleeve 22.
  • the outer end of the axial channel 22 terminates in a port 26 in a left end side 28 of the rotor 14 in FIG.
  • a plurality of such channels 22, 24, 26 or lines over the circumference of the first sleeve 20 and the end face 28 may be distributed, for example, seven or nine such channels.
  • Working channels usually have a larger cross-section and conduct a working fluid, which is needed for example for actuating piston-cylinder units.
  • Control lines usually have a smaller cross-section and conduct a fluid which is needed for actuating control elements, in particular valves.
  • end bearings 32a and 32b are arranged, which rotatably support the rotor 14 in the stator 12.
  • the bearings 32a and 32b are in Figure 2 shown only schematically, because this type of storage is known in the art.
  • the stator 12 has a second sleeve 40, which is arranged coaxially with the first sleeve 20.
  • the second sleeve 40 is provided with a window 42.
  • the sealing bushing 50 is axially displaceably mounted between the sleeves 20 and 40, as indicated by a double arrow 51. In the direction of rotation 18, however, it is connected to the stator 12, so that it forms part of the stator 12.
  • the sealing bushing 50 is provided with a plurality of ports, namely working ports 52 and control ports 54 associated with the above-mentioned working or control ports.
  • the terminals 52 and 54 are accessible through the window 42, wherein the window 42 is dimensioned so that this accessibility over the full displacement (arrow 51) of the sealing bushing 50 is maintained.
  • the fluid lines connected to the ports 52 and 54 from the outside are formed at least over a certain length as flexible hose lines to follow the displacement of the sealing bushing 50 can.
  • the sealing bushing 50 Between the sealing bushing 50 and the bearings 32a and 32b, there are a right pressure chamber 58 and a left pressure chamber 60 in FIG. 2.
  • the sealing bushing 50 By introducing a fluid into one of the two pressure chambers 58 and 60, the sealing bushing 50 can be displaced axially in the direction of the arrow 51 , The required for the displacement fluid pressure in the pressure chambers 58 and 60 can be conveniently provided by the working or the control pressure is tapped in one of the working or control channels (not shown). This can be effected, for example, in that the pressure chambers 58 and 60 are pressurized earlier in time than a tapped annular groove 62 or 64. Then the sealing bushing 50 is already in the desired end position, if the corresponding other connections 52 and 54, respectively Pressure is given.
  • first annular grooves 62 are designed as working channels and second annular grooves 64 as control channels.
  • the first annular grooves 62 are outside the plane of the drawing of Figure 2 with the working ports 62, and the second annular grooves 64 are connected to the control terminals 54 in connection.
  • ring seals 66 may still be located in the inner peripheral surface of the sealing bushing 50, of which only four are shown next to the second annular grooves 64 in FIG. 2 for the sake of clarity.
  • one will provide the ring seals 66 only on both sides of the larger pressure annular grooves 62 and for reasons of space on both sides of the smaller control annular grooves 64 renounce.
  • further seals 68a, 68b are provided on the bearings 32a, 32b, which are preferably formed as shaft seals, as will be explained below with reference to FIG 5.
  • the further seals 68a, 68b are designed for the high rotational speeds of the leevierphase and, for example, for an operating pressure of 5 bar maximum.
  • radial pressure relief lines 70 may be provided in the sealing bushing, which open between the optional ring seals 66 in the inner peripheral surface of the sealing bushing 50.
  • the leftmost pressure relief line 70 in Figure 2 has a left axial branch 72a leading to a left pressure relief cavity 73a.
  • the cavity 73a is located between the left in Figure 2 bearing 32a and the adjacent thereto radial end face of the sealing bushing 50.
  • a right axial branch 72b and a right cavity 73b can be seen, the right Cavity 73b in the operating position shown in Figure 2 has the volume zero.
  • an axial manifold 78 is provided in the sealing bush 50.
  • the optionally provided pressure relief lines 70 are connected to the manifold 78. This is in turn connected to a terminal 80, which is also accessible through the window 42 from the outside.
  • the port 80 is connected to a pressureless fluid tank. Therefore, the line system formed from the lines 70, 72, 78 is depressurized or is at a very low pressure level of less than 0.5 bar.
  • the optional pressure relief lines 70 are arranged in particular between the annular grooves 64 belonging to the control connections 54.
  • the channels 70 ensure that, for example, an increase in pressure in an annular groove 64, the optional annular seal 66 deformed, but this does not affect the adjacent annular groove 64 in such a way that changes by a change in volume, the pressure in the adjacent annular groove 64, because the channel 70th depressurized and connected to a tank.
  • the pressure relief lines are useful in many cases, but they can be omitted in other cases.
  • the branches 72a and 72b, together with the manifold 78 as a leakage line connect the cavities 73a and 73b with each other.
  • an oil volume is moved because the volumes of the cavities 73a and 73b change in opposite directions.
  • an overpressure is created in the left-hand cavity 73a and a negative pressure in the right-hand cavity 73b.
  • the pressure compensation then takes place via the leakage line 72a-78-72b.
  • this pressure equalization depends on how fast the displaced oil volume can flow through the leakage line 72a-78-72b. Even if the cross section of the leakage line 72a-78-72b is made large, the time constant of the pressure compensation remains finite.
  • the leakage line 72a-78-72b passes through the sealing bushing 50.
  • the leakage line in the rotor 14 (not shown), wherein the leakage line then similar to the axial channel 22, so with a larger cross section and the cavities 73a and 73b would connect.
  • the non-pressurized port 80 would continue accordingly radially inward.
  • one has in the dimensioning and arrangement of the annular grooves 62 and 64 more degrees of freedom.
  • one will then place the larger pressure annular grooves 62 on one axial side and the smaller control annular grooves 64 on the other axial side and concentrate all the annular grooves 62, 64 in the axial center to avoid complicated holes near the end surfaces ,
  • the cavity 73a - and correspondingly also the cavity 73b - is bounded by the further seal 68a and in the working phase by the optional ring seal 66. This has the consequence that a possibly accumulating pressure by moving the sealing bushing 50 can not affect the further seal 68a, which, as mentioned, withstands only a lower operating pressure.
  • the ring seals 66 are formed by third, rectangular annular grooves 82, in whose base an elastic O-ring 84 is inserted. On the O-ring 84, an annular, largely inelastic sealing body 86 is placed. The sealing body is provided on its inner circumference with a support side 88, which is preferably designed to be tapered. Such ring seals are known in the art.
  • FIG. 3 shows a working state of the rotary feedthrough in which the working channels are pressurized, for example with an operating pressure of 150 bar, and in which the rotor 14 rotates in the stator 12 with low peripheral speed v of the outer peripheral surface of less than 0.5 m / s. In rotary unions of conventional size, as exemplified above, this corresponds to a speed range of, for example, 15 to 25 U / min.
  • Figure 4 shows an idle state of the rotary feedthrough in which the working channels are substantially unpressurized and in which rotates the rotor 14 in the stator 12 at high circumferential speed v of the outer peripheral surface 30 of more than 0.5 m / s, which in the aforementioned size one Speed range of, for example, 90 to 100 rev / min corresponds.
  • the rotary feedthrough 50 is preferably axially positioned so that the first annular grooves 62 are substantially aligned with the radial channels 24.
  • the working fluid can flow unhindered from the working ports 52 in the stator 12 to the axial channels 22 and the terminals 26 in the rotor 14, as indicated by arrows 92.
  • the bearing sides 88 of the ring seals 66 rest on the cylindrical outer peripheral surface 30 of the rotor 14.
  • the depth and the width of the third annular grooves 82 are dimensioned such that the O-rings 84 are radially compressed in this state, so that a high contact pressure of the bearing sides 88 on the outer peripheral surface 30 is formed and thus a high sealing effect or a low leakage rate in particular between the annular grooves 62 is effected.
  • the pressure relief acts through the pressure relief lines 70 between the annular seals 66.
  • the pressure relief bends, as mentioned, in particular an influence of the control annular grooves 64 with each other by changing the behavior of one ring seal 66 to the next ring seal 66 by deformation of the latter, because the adjacent ring seals 66 are separated from each other by one of the unpressurized pressure relief lines 70.
  • fourth annular grooves 94 are now introduced in the region of the annular seals 66, which preferably have a rounded axial profile at the bottom. These fourth annular grooves are inactive in the working state shown in FIG.
  • the annular grooves 94 are adapted to receive a non-preloaded annular seal 66, wherein the annular seal 66 preferably in a working position, which is determined by an axial end position of the sealing bushing 50 does not touch their mating surface in the outer peripheral surface 30.
  • the sealing bush 50 shifts to the position shown in Figure 4. In this position, the working port 52 and the first annular groove 62 are offset axially by an amount .DELTA.z with respect to the radial channel 24.
  • the sealing bodies 86 can now constantly slide into this 94 due to the rounded shape of the fourth annular grooves.
  • FIG. 5 shows an enlarged view of an embodiment of the further seal 68a, which embodiment can of course also be selected for the further seal 68b.
  • the seal 68a is designed with an annular groove 100 into which a shaft seal 102 is inserted.
  • Shaft seal of this type are known per se, for example from DE 867 189 C.
  • the shaft seal 102 has axially inside a sealing lip 104 which is biased by a sealing spring.
  • a dust protection lip 108 is provided axially on the outside. The lips 104 and 108 ride on a surface 110 of the first sleeve 20.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Sealing Devices (AREA)

Abstract

Un passage tournant comporte un stator (12) et un rotor (14) qui est apte à tourner autour d'un axe (16) et qui est monté au moyen d'une surface de guidage à symétrie de révolution (30). Le stator (12) possède au moins une première conduite de fluide (52, 54, 62, 64, 90) et le rotor (14) possède au moins une deuxième conduite de fluide (22, 24, 26), les conduites de fluide débouchant chacune dans la surface de guidage (30) et étant en liaison l'une avec l'autre lorsque le rotor (14) est en rotation dans le stator (12). De plus, outre l'embouchure, il est prévu axialement au moins un élément d'étanchéité annulaire (66) dans lequel un corps d'étanchéité annulaire (86) disposé dans le stator (12) ou le rotor (14) est pressé contre le rotor (14) ou le stator (12) avec une pression appliquée prescrite. Il est prévu des moyens pour presser le corps d'étanchéité (86) au choix avec au moins deux pressions appliquées différentes.
PCT/EP2009/001490 2008-03-05 2009-03-03 Passage tournant WO2009109355A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008012676.4 2008-03-05
DE200810012676 DE102008012676A1 (de) 2008-03-05 2008-03-05 Drehdurchführung

Publications (1)

Publication Number Publication Date
WO2009109355A1 true WO2009109355A1 (fr) 2009-09-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/001490 WO2009109355A1 (fr) 2008-03-05 2009-03-03 Passage tournant

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DE (1) DE102008012676A1 (fr)
WO (1) WO2009109355A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8336290B2 (en) 2010-09-30 2012-12-25 General Electric Company Pitch change apparatus for counter-rotating propellers
US8371105B2 (en) 2010-09-30 2013-02-12 General Electric Company Hydraulic system for fan pitch change actuation of counter-rotating propellers
CN105782620A (zh) * 2016-04-22 2016-07-20 中国石油天然气集团公司 多液路传输回转装置及抓管器
EP2881535A3 (fr) * 2013-12-06 2016-08-10 Weatherford/Lamb Inc. Outil de manipulation de matériel tubulaire
CN110424898A (zh) * 2019-08-29 2019-11-08 中国石油集团川庆钻探工程有限公司 钻井排砂管线用伸缩式管线长度调整机构
AT16697U1 (de) * 2018-10-24 2020-07-15 Innotool Austria Gmbh Drehverteiler für eine Werkzeugmaschine
EP3754696A4 (fr) * 2018-02-13 2021-11-24 Sealink Corp. Raccord rotatif à mouvement linéaire
CN116838869A (zh) * 2023-09-01 2023-10-03 山东豪迈数控机床有限公司 一种旋转接头及机床主轴

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105221870B (zh) * 2015-09-14 2017-11-10 三一重型能源装备有限公司 一种液压中央回转接头及风力发电机组
CN105114725A (zh) * 2015-09-14 2015-12-02 三一重型能源装备有限公司 一种液压中央回转接头及风力发电机组
AT520464B1 (de) 2017-09-22 2020-03-15 Engel Austria Gmbh Maschinenelement

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DE867189C (de) * 1951-05-24 1953-02-16 Kupfer Asbest Co In ein Gehaeuse eingebaute Wellendichtung mit Staubdichtung
US4729569A (en) * 1984-07-11 1988-03-08 Martin Merkel Gmbh & Co Kg Twist proof seal ring arrangement for shafts
DE3738305A1 (de) * 1987-11-11 1989-05-24 Stromag Maschf Vorrichtung zum radialen zufuehren von druckfluessigkeit und/oder kuehlfluessigkeit zu hydraulisch betaetigten schaltelementen
DE4019987A1 (de) * 1989-03-25 1991-01-03 Brother Ind Ltd Fluessigkeitseinkopplungseinrichtung
DE4203954C1 (en) * 1992-02-11 1993-06-17 Iobb Produktideen Vorausentwicklung Und Problemloesungen Gmbh, 8960 Kempten, De Rotary feed coupling for pressurised gas or liquid - has sealing gap between sealing surfaces adjusted to allow axial displacement of rotor relative to stator
EP0562269A1 (fr) * 1992-03-27 1993-09-29 Heidelberger Druckmaschinen Aktiengesellschaft Jonction rotative
EP0928876A1 (fr) * 1996-03-13 1999-07-14 Wirth Maschinen- und Bohrgeräte-Fabrik GmbH Dispositif de forage d'un trou en terre

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DE19525343C2 (de) * 1995-07-12 2000-11-09 Gat Gmbh Vorrichtung zum Überführen von Fluid zwischen relativ zueinander drehbaren Maschinenteilen

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE867189C (de) * 1951-05-24 1953-02-16 Kupfer Asbest Co In ein Gehaeuse eingebaute Wellendichtung mit Staubdichtung
US4729569A (en) * 1984-07-11 1988-03-08 Martin Merkel Gmbh & Co Kg Twist proof seal ring arrangement for shafts
DE3738305A1 (de) * 1987-11-11 1989-05-24 Stromag Maschf Vorrichtung zum radialen zufuehren von druckfluessigkeit und/oder kuehlfluessigkeit zu hydraulisch betaetigten schaltelementen
DE4019987A1 (de) * 1989-03-25 1991-01-03 Brother Ind Ltd Fluessigkeitseinkopplungseinrichtung
DE4203954C1 (en) * 1992-02-11 1993-06-17 Iobb Produktideen Vorausentwicklung Und Problemloesungen Gmbh, 8960 Kempten, De Rotary feed coupling for pressurised gas or liquid - has sealing gap between sealing surfaces adjusted to allow axial displacement of rotor relative to stator
EP0562269A1 (fr) * 1992-03-27 1993-09-29 Heidelberger Druckmaschinen Aktiengesellschaft Jonction rotative
EP0928876A1 (fr) * 1996-03-13 1999-07-14 Wirth Maschinen- und Bohrgeräte-Fabrik GmbH Dispositif de forage d'un trou en terre

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8336290B2 (en) 2010-09-30 2012-12-25 General Electric Company Pitch change apparatus for counter-rotating propellers
US8371105B2 (en) 2010-09-30 2013-02-12 General Electric Company Hydraulic system for fan pitch change actuation of counter-rotating propellers
EP2881535A3 (fr) * 2013-12-06 2016-08-10 Weatherford/Lamb Inc. Outil de manipulation de matériel tubulaire
US10487597B2 (en) 2013-12-06 2019-11-26 Weatherford Technology Holdings, Llc Tubular handling tool
US10830008B2 (en) 2013-12-06 2020-11-10 Weatherford Technology Holdings, Llc Tubular handling tool
CN105782620A (zh) * 2016-04-22 2016-07-20 中国石油天然气集团公司 多液路传输回转装置及抓管器
EP3754696A4 (fr) * 2018-02-13 2021-11-24 Sealink Corp. Raccord rotatif à mouvement linéaire
US11761518B2 (en) 2018-02-13 2023-09-19 Sealink Corp. Linear motion rotary union
AT16697U1 (de) * 2018-10-24 2020-07-15 Innotool Austria Gmbh Drehverteiler für eine Werkzeugmaschine
CN110424898A (zh) * 2019-08-29 2019-11-08 中国石油集团川庆钻探工程有限公司 钻井排砂管线用伸缩式管线长度调整机构
CN116838869A (zh) * 2023-09-01 2023-10-03 山东豪迈数控机床有限公司 一种旋转接头及机床主轴
CN116838869B (zh) * 2023-09-01 2023-11-10 山东豪迈数控机床有限公司 一种旋转接头及机床主轴

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