Abstract:
A coaxial valve for regulating and blocking a fluid medium having a valve housing having at least one inlet opening, at least one outlet opening and a flow duct connecting the inlet opening to the outlet opening; a tubular valve sleeve disposed in an axially movable manner in a portion of the flow duct and having an inflow and an outflow opening for the medium, wherein the inflow and outflow openings open into the flow duct; a closure member disposed in the valve housing and arranged coaxially with the valve sleeve and configured to close the inflow opening; and a drive configured to axially move the valve sleeve and having an electric servomotor and a transmission part coupled between the servomotor and the valve sleeve, the transmission part configured to transmit an axial movement to the valve sleeve.

Description:
This application is a U.S. National Phase Application under 35 U.S.C. §371 of International Application No. PCT/DE2008/001304, filed on Aug. 7, 2008 and claims benefit to German Patent Application No. DE 10 2007 037 995.3, filed on Aug. 10, 2007. The International Application was published on Feb. 19, 2009 as WO 2009/021492 under PCT Article 21 (2). 
     The invention relates to a coaxial valve for regulating and blocking a liquid or gaseous medium, in particular a coaxial valve for cryogenic fluid. The coaxial valve comprises a valve housing, which has at least one inlet opening and one outlet opening and also a flow duct which connects said openings to one another. A tubular valve sleeve is provided, which is provided in an axially movable manner in a portion of the flow duct and which has an inflow opening and an outflow opening for the medium, both of these openings opening out into the flow duct. A closure member provided in the valve housing is arranged coaxially with respect to the valve sleeve and is configured to close off the outflow opening of the valve sleeve. A drive is provided for axially moving the valve sleeve, the drive being formed by an electric servomotor and by a transmission part which is coupled between the servomotor and the valve sleeve for transmitting an axial movement to the valve sleeve. 
     BACKGROUND 
     Specific requirements are set for valves which are used for regulating and blocking a liquid or gaseous medium under extreme conditions, such as chemical aggression, very high or very low temperatures or under very high pressures. One application for valves which are used for blocking a liquid or gaseous medium under extreme conditions is that of drives in the aerospace field. In this case, the valves are subjected, on the one hand, to extreme temperatures and extreme temperature changes. In the case of valves for liquid and gaseous rocket fuels, there are further parameters such as high mass flow rates, high pressures and short switching times for opening and closing as well as the adoption a predetermined position. 
     In the aerospace field, a coaxial valve is used for blocking a liquid or gaseous medium, which contains a valve housing comprising an inlet and an outlet for the medium to be blocked, a valve sleeve mounted in the valve housing so as to be longitudinally displaceable in the axial direction between an open position and a closed position and in a sealed relationship with the valve housing, through which the medium to be blocked flows when the valve is open in the longitudinal direction and a closure member arranged coaxial with the valve sleeve at one end of said valve sleeve, against which closure member the valve sleeve bears sealingly in the closed position and from which closure member the valve sleeve is distanced in the open position, opening up a valve opening cross section, and a servo for opening and closing the valve. 
     A generic coaxial valve of this type is disclosed in DE 199 60 330 A1. In this known valve, the valve sleeve is axially moved relative to the closure member, which is fixed in the flow duct, by means of a lever mechanism which is actuated by an electric or pneumatic servo provided outside the valve housing. In said valve, actuation via the lever mechanism is complex and thus increases the risk of malfunction in a manner which is unacceptable for aerospace applications. 
     A further coaxial valve is disclosed in DE 10 2005 028 584 A1. In said valve, the valve sleeve is provided on its outer periphery, at least over portions, with a channel-shaped outer helical groove and is surrounded in the portion of the channel-shaped outer helical groove by a drive sleeve which is coaxial with the valve sleeve. The drive sleeve is provided on its inner periphery with at least one channel-shaped inner helical groove which is adapted to the outer helical groove in such a way that the inner and outer helical grooves engage with one another via balls which run in them, and thus form a recirculating-ball gearing of a recirculating-ball spindle drive. The drive sleeve is rotatable in the valve housing, but axially rigidly mounted and subjected to rotational action by a drive motor provided inside the valve housing. The drive motor and the drive sleeve form the drive for the valve sleeve by incorporating the portion integrated in the valve sleeve with the channel-shaped outer helical groove and the balls. The valve sleeve is thus identical to the spindle of the recirculating-ball spindle drive thus formed. 
     An electro-mechanical coaxial valve is further disclosed in U.S. Pat. No. 6,802,488 B1. Said coaxial valve is unsuitable, however, for the operation of liquid or gaseous media under high pressure and, in particular, unsuitable for cryogenic fluids. A reason for this is that at temperature differences and/or higher pressures the spindle drive may seize up and/or become stiff due to radial pipe expansion. To compensate for this drawback, a powerful servo is therefore required which has a correspondingly high energy requirement. 
     SUMMARY OF THE INVENTION 
     An aspect of the present invention is to provide a coaxial valve which with a compact construction, permits reliable operation and only consumes minimal energy. 
     By means of the invention, a coaxial valve is provided for regulating and blocking a liquid or gaseous medium, in particular a cryogenic fuel. Said coaxial valve comprises a valve housing which has at least one inlet opening and one outlet opening and also a flow duct which connects said openings to one another. A tubular valve sleeve is provided in an axially movable manner in a portion of the flow duct and has an inflow opening and an outflow opening for the medium, both of these openings and opening out into the flow duct. A closure member provided in the valve housing is arranged coaxially with the valve sleeve and is configured to close off the inflow opening of the valve sleeve. A drive for axially moving the valve sleeve is provided, the drive being formed by an electric servomotor and a transmission part which is coupled between the servomotor and the valve sleeve for transmitting an axial movement to the valve sleeve. In this case, the transmission part is formed by a drive sleeve and a spring pack. The drive sleeve which is coaxial with the valve sleeve comprises a driver which is arranged on said drive sleeve and can be placed in engagement with the valve sleeve in order to move the valve sleeve in a first direction. The spring assembly, which is coaxial with the valve sleeve, acts in the axial direction and is supported on the drive sleeve and on the valve sleeve, makes it possible to move the valve sleeve in a second direction which is opposite to the first direction. 
     The first direction thus corresponds to an opening of the valve. The movement in the second direction corresponds to a closure of the valve. 
     The coaxial valve according to the invention is characterised by its high level of reliability even under extreme conditions. Said coaxial valve may thus be produced in a compact, rigid coaxial arrangement, whereby it may be easily incorporated in installation spaces. The coaxial valve can be adjusted directly between the open position and the closed position in a highly accurate manner. In this regard, the high adjusting speeds may be implemented with low energy consumption. A further advantage is that the actuating time between the open position and the closed position and/or from a predetermined position to a further predetermined position may be freely selected. The valve thus remains sealed in the closed position by means of the spring-loaded device, without the application of current. Due to fewer mobile parts, the valve is robust and unlikely to fail; in particular it is also unsusceptible to engine vibrations. The coaxial valve is provided with a dual sealing system (preliminary seal and dual main seal) having, in each case, a leakage line arranged therebetween, whereby substantial protection against explosion is achieved. By enclosing the drive and optionally rinsing the inner chamber with inert gas, the protection against explosion may be further improved. Even in a standard embodiment, without enclosure and rinsing of the engine compartment, said valve may be operated immersed in gases and liquids. Moreover, it may be electrically controlled in a simple manner. 
     According to any one embodiment, the spring assembly is arranged between a spindle, which is arranged on the drive sleeve on the inner peripheral side, and a ball and socket segment which is arranged on the valve sleeve on the outer peripheral side. In order to seal the valve without the application of current, according to a further embodiment it may be provided to bias the spring assembly when the valve sleeve bears against the closure member. 
     In a further embodiment, it is provided for the spindle to be an integral component of the drive sleeve. It may also be provided that the ball portion of the ball and socket segment is an integral component of the valve sleeve. These variants promote simple and cost-effective manufacture of the coaxial valve. 
     A further embodiment provides for the spring assembly to bear against a first, radially-extending bearing portion of the ball and socket segment. As a result, a defined bearing surface is provided for the spring assembly, the reliability of the valve thus being increased. 
     The force introduction via the ball and socket segment for opening the valve sleeve and the biased spring assembly for closing the valve sleeve prevents constraining forces, as a result of angular alignment errors, between the valve axis and drive axis and provides a clamping force for which no additional energy is required in the closed state. 
     In a further embodiment, the driver is configured as an adjusting ring which is arranged on the drive sleeve on the inner peripheral side and introduces a force on a second bearing portion of the ball and socket segment opposing the first portion. As a result, the ball and socket segment is arranged on the valve sleeve between the spindle and the driver. The separate configuration of the driver from the drive sleeve permits simple assembly of the coaxial valve. 
     According to a development, the contact surface between the ball portion and socket portion of the ball and socket segment has an incline extending outwardly away from the valve sleeve and facing the first bearing portion. This development promotes a smooth-running axial displaceability of the valve sleeve. 
     According to a further embodiment, the drive sleeve is radially and non-rotationally mounted on the valve housing. The load path therefore has to be closed. This is necessary in order to convert the rotation into an axial movement. As a result, it is ensured that the drive sleeve carries out a co-linear movement relative to the direction of movement of the valve sleeve. In addition to improved reliability, precision is thus also improved when adjusting the valve sleeve. 
     In a further embodiment, the drive sleeve is surrounded by a rotor of the drive motor and axially movably mounted relative thereto. The coaxial arrangement of the motor relative to the valve sleeve ensures a particularly compact construction of the coaxial valve. Thus, the rotor is advantageously surrounded by a stator of the drive motor, said stator being mounted non-rotationally in the valve housing. 
     It is also expedient if the drive sleeve is provided on its outer periphery, at least over portions, with at least one channel-shaped outer helical groove, and if the rotor of the drive motor is provided on its inner periphery with at least one channel-shaped inner helical groove, which is adapted to the outer helical groove in such a way that the inner and outer helical grooves engage with one another via balls which run in them and thus form a recirculating-ball gearing of a recirculating-ball spindle drive. The drive sleeve is thus identical to the spindle of the recirculating-ball spindle drive thus formed. An advantage is the compact construction achieved, in particular, by integration of the drive sleeve in the recirculating-ball spindle drive and the resulting low weight and resistance to vibration. Moreover, according to the invention, as an alternative to the recirculating-ball spindle, a planetary roll spindle (possibly of differential configuration) may also be used; this results in the same advantages. 
     In a further embodiment, the valve sleeve has a smooth outer surface. Expediently, the valve sleeve is of thin-walled configuration in order to keep the hydraulic forces low. Moreover, the valve sleeve is radially uncoupled from the spindle and/or the drive sleeve. 
     In one embodiment, the valve sleeve is mounted in the valve housing with at least two plain bearings arranged remotely from one another. In this case, the at least two plain bearings may have different diameters, whereby a force equalisation is produced on the sealing seats. 
     In a further embodiment of the coaxial valve, the at least two plain bearings have, on their end faces, sealing lips which are remote from one another and are manufactured as an integral component, in order to minimise tolerance chains and secondary leakage paths. 
     In a further embodiment of the coaxial valve, in order to seal the valve sleeve a preliminary seal and a main seal are used for each bearing point so as to reduce the pressure difference in a gradual manner. 
     In a further embodiment of the coaxial valve, ventilation lines (vent lines) are arranged between every two sealing lips in order to produce the pressure difference and to discharge leaks in a controlled manner. 
     In a further embodiment of the coaxial valve, the secondary leakage paths on the plain bearing are sealed by auxiliary seals in order to compensate for thermal expansion and thus minimise leaks. 
     In the coaxial valve according to the invention, between the two bearing points an inner chamber is produced, isolated from the pressure of the medium to be sealed. Moreover, as a result of the sealing lips of the main seal facing said inner chamber, the inner chamber is free from leakage gas and able to be conditioned with inert gas. Moreover, the outer housing may be welded by peripheral seams at the separation points in order to increase the external seal. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention is described in more detail hereinafter with reference to an embodiment. 
       The only FIGURE shows a longitudinal section through a coaxial valve according to the invention. 
     
    
    
     DETAILED DESCRIPTION 
     In a valve housing  1  a flow duct  25  is provided which has a fluid inlet opening E and a fluid outlet opening A. The fluid inlet opening E and the fluid outlet opening A are thus configured at ends of the valve housing  1  remote from one another so that the flow duct  25  extends straight from the fluid inlet opening E to the fluid outlet opening A. The flow duct  25 , the fluid inlet opening E and the fluid outlet opening A are configured to be circular in cross section and arranged coaxially relative to one another, comprising a common central axis X. 
     The first end-face cover part  27  has a cylindrical housing projection  30  protruding outwardly in the direction of the X-axis, which at its free end is provided with the fluid inlet opening E. In the region of the fluid inlet opening E the flow duct  25  is formed by a first cylindrical bore portion  26 . In the interior of the cylindrical housing projection  30  a second bore portion  31  of the flow duct  25  is formed, said bore portion having a diameter which is greater than that of the first cylindrical bore portion  26 . Between the second cylindrical bore portion  31  and the third bore portion  18  of the flow duct  25  in the region of the cylindrical central portion  29  of the valve housing  1 , a cylindrical inner chamber is formed, the diameter thereof being markedly greater than that of the second bore portion  31 . 
     The fluid outlet opening A is provided in a second end-face cover part  28  on the side of the valve housing  1  remote from the first end-face cover part. Between the first end-face cover part  27  and the second end-face cover part  28  extends a cylindrical central portion  29  of the valve housing  1 . The two cover parts  27 ,  28  are, for example, screwed to the cylindrical central portion  29 . 
     In the flow duct  25  a tubular valve sleeve  2  is arranged coaxially with the flow duct  25  between the second bore portion  31  and the fluid outlet opening A. The valve sleeve  2  is configured to be of annular cross section and may be moved along its axis which is configured to the central axis X. The valve sleeve  2  is configured as a straight tube, and surrounds an inner channel  32  which is provided with an inflow opening  33  on the end face adjacent to the fluid inlet opening E and an outflow opening  34  on the end face facing the fluid outlet opening A. The inner channel  32  thus forms a central portion of the flow duct  25  between the first cylindrical bore portion  26  and the fluid outlet opening A. 
     In the first end-face cover part  27 , in the inside of the cylindrical housing projection  30 , i.e. in the bore portion  31  of the flow duct  25 , a closure member  3  is provided which is connected to the inflow opening  33  of the valve sleeve  2  to open and close the valve. The closure member  3  comprises an annular, conical base portion  36 , which is arranged coaxially with the central axis X in the region of the fluid inlet opening E. An annular extension  37  is connected to the annular base portion  36 , which extension is also arranged coaxially with the central axis X and extends in the axial direction towards the inner channel  32 . The ends of the annular extension  37  facing the inner channel  32  have a convex outer surface. Said surface faces an annular and substantially cylindrical shoulder portion  38  of the conical base portion  36 . Between the annular extension  37  and the annular, substantially cylindrical shoulder portion  38  an annular groove-shaped support  39  is formed which represents a sealing seat. The support  39  is annular in cross section, the diameter being adapted to the diameter of the valve sleeve  2 . In the closed state of the valve, the valve sleeve  2  bears sealingly against the support  39 . 
     The closure member  3  and the first end-face cover part  27  may, as shown in the figure, be configured in one piece. 
     The valve sleeve  2  is mounted without anti-twist protection by two plain bearings  23 ,  24  in the valve housing  1 . The plain bearings  23 ,  24  are in each case arranged in a bearing housing  40  and/or  41  and have at their end faces sealing lips oriented in opposing directions. The bearing housing  40  is thus adjacent to the first end-face cover part  27 . The bearing housing  41  is adjacent to the second end-face cover part  28 . Portions of the bearing housing  40 ,  41  may protrude beyond the cylindrical central portion  29  and be fastened thereto, for example, by screws. For force equalisation, different diameters may be provided on the two sealing seats formed by the plain bearings  23 ,  24 . 
     The valve sleeve  2  is sealed at the bearing points  23  and  24  (main seal) and by the preliminary seal  45  which is configured to be robust. The leakage of the preliminary seal  45  is fed back by the vent line  43 , for example, into the fuel tank. Between the preliminary seal and the first lip of the main seal facing said preliminary seal, a space is produced at a reduced pressure level, whereby the main seal experiences low leakage, as it only operates against a small pressure difference. This small amount of leakage is discharged via the vent line  42  against ambient pressure or a vacuum. The sealing lip of the main seal  23 ,  24  facing the inner chamber (engine compartment) prevents infiltration of leakage gas or humidity from the vent line  42 . If the engine compartment is pressurised with inert gas, it is sealed against the vent line  42  in order to minimise the rinsing gas losses. Advantageously, the main seal  23 ,  24  with a plain bearing function is manufactured as an integral component from high performance plastics materials. With fuels at very low temperatures, all secondary leakage paths on the seal have to be additionally sealed by means of metallic C-rings  46  due to the high degree of shrinkage of the sealing material relative to the metal housing. 
     In an inner chamber  35  of the valve housing  1  a drive  4  is provided which acts on the valve sleeve  2  for movement in the axial direction along the central axis X and is disclosed hereinafter. 
     The drive  4  comprises a servomotor  5  which is arranged inside the inner chamber  35 , configured as an electric motor and surrounds the valve housing  2 . A stator  6  of the servomotor  5  is arranged non-rotationally on the cylindrical central portion  29  of the valve housing  1 . The stator  6  surrounds a rotor  7  which, in turn, surrounds a drive sleeve  9 . The drive sleeve  9  is provided on the outer peripheral side, at least over portions, with a channel-shaped outer helical groove  19 . Similarly, the rotor  7  of the servomotor  5  on its inner periphery has a channel-shaped inner helical groove  20 . Said helical groove may, for example, be incorporated in a nut  44  connected to the rotor, which nut is rotationally engaged with the rotor. The inner helical groove  20  is adapted to the outer helical groove  19  so that said helical grooves are in engaged with one another via balls  21  running in them, and thus a recirculating-ball gearing of a recirculating-ball spindle drive is formed. Alternatively, instead of the recirculating-ball spindle drive, a planetary roll spindle may be driven. As a result, by rotation of the rotor  7 , the drive sleeve  9  is moved coaxially with the valve sleeve  2 . 
     The drive sleeve  9  has low-friction anti-twist protection  17 , which may be implemented by a lever extending in the direction of the cylindrical central portion  29 . Said lever is adjacent to the cylindrical central portion  29  with its end remote from the drive sleeve  9  and is brought into engagement there with a housing portion  18 . The housing portion  18  may, for example, be an integral component of the cylindrical central portion  29 . 
     On the inner periphery on the drive sleeve  9 , an annular spindle  13  is provided. The annular spindle  13  is an integral component of the drive sleeve  9 . Between the annular spindle  13  and a ball and socket segment  14 ,  11  arranged on the valve sleeve  2  on the outer peripheral side, a spring assembly  12  is provided. The spring assembly  12  extends in an annular manner about the valve sleeve  2  and bears against a radially extending first bearing portion  15  of the ball portion of the ball and socket segment  14 . 
     If the valve sleeve  2 , as shown in the figure, is in its closed position, the spring assembly  12  is preferably biased. The closed position is present when the valve sleeve  2  bears with its inflow opening  33  against the support  39  of the closure member  3 . 
     The ball portion of the ball and socket segment  14  is an integral component of the valve sleeve  2  and has a second bearing portion  16  which opposes the first bearing portion  15  and has an incline extending outwardly away from the valve sleeve  2  and facing the first bearing portion  15 . On the inner periphery of the drive sleeve  9 , an adjusting ring  10  is fastened which serves as a driver and via the socket portion of the ball and socket segment  11  introduces a force for opening the valve sleeve  2 . By the rigid connection of the adjusting ring  10  with the drive sleeve  9 , with a corresponding rotational direction of the servomotor  5 , the axial movement of the drive sleeve  9  is transmitted via the ball and socket segment  14 ,  11  to the valve sleeve  2 , whereby said valve sleeve is moved away from the closure member  3  and a connection between the inflow opening  33  and the bore portion  3  and the fluid outlet opening A is produced. The closure of the valve sleeve  2 , which is introduced by a reverse rotational direction of the servomotor  5 , is undertaken by a movement of the drive sleeve  9  extending in the direction of the fluid inlet opening E. As soon as the valve sleeve  2  comes to bear on its valve seat, i.e. the support  39 , the spring assembly  12  is subjected to greater bias and the servomotor may be operated without the application of current, since a clamping force is present as a result of the spring-biased spring assembly  12 . In this case, the spring assembly  12  is supported on the spindle  13  of the drive sleeve  9 . 
     In the invention, force is introduced onto the valve sleeve  2  via a ball and socket segment  14 ,  11  whereby the valve  2  is opened. The valve is closed with the assistance of a biased spring assembly  12  which prevents constraining forces, as a result of angular alignment errors, between the valve axis and the drive axis, and moreover provides a clamping force in the closed state, without the need to apply current to a servomotor. 
     The vent lines (leakage lines)  42 ,  43  are guided in the component as radial bores to intermediate spaces of seals, in order to divert leaks. They are the primary structural measures used to counter the uncontrolled formation of explosive mixtures in greater quantities. The vent line  43  returns the leakage of the preliminary seal  45  into the fuel tank and thus reduces the pressure level on the mutually opposed sealing lips of the plain bearings  23 ,  24 , whereby the sealing action thereof is improved. The remaining small leakage of the dynamic main seal at the engine compartment is discharged by the vent line  42  against ambient pressure, a vacuum or gettering material. The sealing lips of the plain bearings  23 ,  24  facing the engine compartment prevent the infiltration of leaked gases and/or moisture into the engine compartment. In the reverse direction, they prevent the discharge of inert gas into the vent line, if the engine compartment is pressurised as a protective measure, for example, against hydrogen embrittlement. In order to improve the external leakage in the explosion-protective embodiment, and/or in order to prevent the penetration of water into the valve, for example in deep sea applications, the housing may be hermetically sealed at the periphery by weld seams, which are subjected to low mechanical loads, at the separation points. Further explosion-protective measures are enclosure of the engine and diversion of electrostatic charge to the bearing points. 
     LIST OF REFERENCE NUMERALS 
     
         
         A Fluid outlet opening 
         E Fluid inlet opening 
         X Central axis 
           1  Valve housing 
           2  Valve sleeve 
           3  Closure member 
           4  Drive 
           5  Servomotor 
           6  Stator 
           7  Rotor 
           8  Transmission part 
           9  Drive sleeve 
           10  Driver (adjusting ring) 
           11  Socket portion of ball and socket segment 
           12  Spring assembly 
           13  Spindle (spring abutment) 
           14  Ball portion of ball and socket segment 
           15  First bearing portion of the ball and socket segment 
           16  Second bearing portion of the ball and socket segment 
           17  Anti-twist lock of the drive sleeve 
           18  Housing portion of the valve housing for engagement of the anti-twist lock 
           19  Outer helical groove of the drive sleeve 
           20  Inner helical groove of the rotor 
           21  Balls 
           22  Recirculating-ball gearing 
           23  Plain bearing (with sealing lip) 
           24  Plain bearing (with sealing lip) 
           25  Flow duct 
           26  First cylindrical bore portion 
           27  First end-face cover part 
           28  Second end-face cover part 
           29  Tie rod (cylindrical central portion) 
           30  Housing projection 
           31  Second bore portion 
           32  Inner channel 
           33  Inflow opening 
           34  Outflow opening 
           35  Inner chamber (engine compartment) 
           36  Conical base portion 
           37  Annular extension 
           38  Shoulder portion 
           39  Support (valve seat) 
           40  Bearing housing 
           41  Bearing housing 
           42  Vent line leakage line 
           43  Vent line leakage line 
           44  Nut 
           45  Preliminary seal 
           46  Auxiliary seal (metal C-ring)