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WO1983002850A1 - Tubes anodiques a rayons x refroidis par un liquide - Google Patents

Tubes anodiques a rayons x refroidis par un liquide Download PDF

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Publication number
WO1983002850A1
WO1983002850A1 PCT/US1983/000204 US8300204W WO8302850A1 WO 1983002850 A1 WO1983002850 A1 WO 1983002850A1 US 8300204 W US8300204 W US 8300204W WO 8302850 A1 WO8302850 A1 WO 8302850A1
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WIPO (PCT)
Prior art keywords
anode
liquid
heat exchange
exchange surface
flow
Prior art date
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Ceased
Application number
PCT/US1983/000204
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English (en)
Inventor
Stephen Whitaker
Arthur H Iversen
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Individual
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Individual
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Publication of WO1983002850A1 publication Critical patent/WO1983002850A1/fr
Anticipated expiration legal-status Critical
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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J35/00—X-ray tubes
    • H01J35/02—Details
    • H01J35/04—Electrodes ; Mutual position thereof; Constructional adaptations therefor
    • H01J35/08—Anodes; Anti cathodes
    • H01J35/10—Rotary anodes; Arrangements for rotating anodes; Cooling rotary anodes
    • H01J35/105—Cooling of rotating anodes, e.g. heat emitting layers or structures
    • H01J35/106—Active cooling, e.g. fluid flow, heat pipes

Definitions

  • the present invention is directed to liquid cooled anode x-ray tubes, and in particular, x-ray tubes having a continuously cooled anode whereby high average power is achieved while still maintaining the high peak powers characteristic of rotating anodes.
  • Such rotating anode x-ray tubes have proven to be less efficient than direct liquid cooled tubes, and sometimes have a tendency to burst or explode when overheated, rendering such tubes unsafe.
  • Liquid cooled rotating anode x-ray tubes are, in general, well known.
  • a hollow anode is disposed so that a rotating portion thereof is irradiated by an energy beam (e.g. electron beam).
  • the irradiated portion of the anode is generally referred to as the electron beam track.
  • Substantially all of the heat generated by irradiation by the energy beam is transmitted to a heat exchange surface, typically the interior wall of the hollow anode underlying the electron beam track and adjacent areas.
  • the heat exchange surface is generally an area of the interior surface of the anode larger than the electron beam track, centered on and underlying the electron beam track.
  • a flow of liquid coolant is passed into contact with the heat exchange surface to remove the heat therefrom, and thus cool the anode.
  • nucleate boiling or other vapor or gas mechanism
  • nucleate boiling bubbles of vaporized fluid are generated on the anode heat exchange surface.
  • the vapor bubbles break away and are replaced by fresh bubbles, much like a pot of boiling water, thus providing efficient cooling by the removal of heat from the exchange surface to vaporize the liquids.
  • the heat flux at the transition from nucleate to film boiling is called the critical heat flux. Should this value be exceeded in electrically heated structures such as a liquid cooled x-ray tube anode, the insulating film blanket would cause a rapid rise in temperature, typically resulting in burn out (i.e., metal down) of the structure. In general, burn out occurs very quickly, and the protective means required are extremely elaborate and expensive. Thus adequate protection has not heretofor been practical.
  • the rotating anode of the Philips device constitutes a hollow cylinder with three radially running tubes through which water flows to a cavity located along the inner surface of the peripheral wall or anode strip of the hollow body. In this device, the water flows back into the hollow drive shaft through three other tubes running radially in the rotary anode.
  • various disadvantages have been attributed to the Philips device. For example, it is reported that only relatively low speeds of rotation can be obtained with the Philips rotary device because the maximum thickness of the peripheral wall provided as the anode target member allowable for proper cooling is not sufficient to withstand the pressures in the cool ing medium that arise due to centrifugal force at higher speeds of revolution.
  • the brazed duct wall peripheries thus also transverse one face of the anode to the other at the prescribed 15° angle. Therefore, the electron beam alternately travels over coolant duct and duct wall as the anode rotates.
  • the anode simulates more closely a solid metal structure, i.e., a conventional solid rotating anode. This creates a hot spot and severely limits the power handling
  • the rate of nucleate bubble removal may be increased by breaking up this viscous or laminar sublayer.
  • such viscous sublayer can be broken up by roughening the anode coolant surface.
  • the height of the roughening projections ranges from 0.3 times the thickness of the viscous sublayer to the sum of the thickness of the viscous sublayer and a transition zone adjacent the viscous sublayer, the sublayer is broken up. Breaking up the viscous sublayer enables the turbulent fluid to reach the base of the nucleate bubble, where it is attached to the anode, thereby providing the energy needed to break it loose.
  • the geometry of nucleate bubbles is a function of the surface roughness geometry; small fissures tend to generate small nucleate bubbles, whereas large
  • nucleate bubble size and generation can be optimized by providing a surface of calculated and preferably uniform roughness and geometry.
  • a regular roughness geometry can be obtained by suitable conventional techniques such as, for example, chemically by means of chemical milling; electronically, by the use of lasers or electron beams; or mechanically, by broaching, hobbing, machining, milling, stamping, engraving, etc.
  • Another method of obtaining a surface with crevices for forming nucleate bubbles is the use of a thin porous metal layer adherent to the anode at the anode heat exchange surface.
  • This porous metal layer may be considered to provide a contoured surface as defined above.
  • Relatively uniform pore size can be obtained by fabricating the porous structure from metal powders with a narrow range of particle sizes. Methods, such as described in U.S. Patent No. 3,433,632, issued to Ebbertotal on March 18, 1969, are well suited to providing the desired porous metal structure.
  • the present invention provides a long life continuous duty liquid cooled rotating anode x-ray tube that possesses high power capabilities while using low pressure pumps and components.
  • Heat flux rate of heat removal
  • critical heat flux burn out
  • Simultaneous and continuous liquid cooling of the entire heat exchange surface of the hollow rotating anode is provided thereby avoiding any power limiting hot spots.
  • High relative velocity of the anode to coolant liquid with low input liquid velocities are provided, while using long lived rotational liquid seals, and low pressure liquid pumps and components.
  • axial flow pump blades are mounted on the inside diameter, i.e. in the liquid conduit, or the hollow rotating shaft, and/or centrifugal pump vanes are mounted on the inside face of the hollow rotating anode to increase liquid flow rate by direct use of the rotational motion of the anode.
  • gear pump elements driven by the rotational motion of the anode can be incorporated in the liquid conduit between the inside face of the rotating anode and the stationary septum. The gear pump elements would be attached, as required, to either the rotating anode or stationary septum to increase flow rate by indirect use of anode rotation.
  • OMPI enabling efficient heat transfer, while the rest of the liquid cooling loop remains at low pressure, thereby eliminating the need for external high pressure rotating liquid seals, pumps and components with their attendant higher costs and shorter life.
  • the flow of liquid is directed to traverse the path of anode rotation along a plurality of independent channels to interact with the anode heat exchange surface in a manner to obtain optimum heat exchange, while simultaneously avoiding or minimizing undesirable liquid flow fields or characteristics such as cavitation, eddies, vortex shedding or inherently stable rotational motion.
  • axial flow pump vanes mounted on the stationary septum contained within the hollow anode and/or radial conduits are constructed substantially in a radial direction through a radial thickness of the stationary septum.
  • the mechanisms for increasing the liquid flow rate combined with the liquid directing means serve to confine a substantial portion of the associated high pressures to the vicinity of the anode heat exchange region thereby enabling the remainder of the liquid loop, including the liquid rotating seals, to operate at low pressure with consequent lower cost, ease of maintenance and longer life.
  • each of the preferred mechanisms for increasing liquid flow rate and for directing the liquid flow substantially eliminates the inherently stabilizing rotational motion of the liquid found in conventional liquid cooled rotating anode x-ray tubes.
  • the axial flow pump vanes, which come into close proximity to the interior anode surface serve to break up the stable liquid flow patterns which cause reduced heat flux and lower critical heat flux i.e. burn out. Also, the
  • SUBSTITUTE SHEET axial flow pump vanes serve to break up the liquid flow across the anode surface into a large number of essentially independent channels. This forces the liquid to move in a direction different from that of the anode. This breakup of the liquid flow across the anode into a large number of segregated channels further interrupts the establishment of the inherently stable flow patterns.
  • use of a number of conduits, which may be circular, substantially radially constructed through a radial thickness of the septum to direct the liquid prevents the establishment of stable flow patterns by virtue of the multitude of high velocity jets of liquid emanating from the periphery of the septum and simultaneously striking the entire anode heat exchange surface.
  • liquid cooled rotating anode x-ray tubes have heat transfer capabilities in the -600 to 1200 watts/cm range. It has been calculated that the present invention will enable heat transfer rates of 12,000 watts/cm to be achieved for systems which are liquid heat transfer limited. Combining a pump and the rotating anode into a single unit enables high liquid flow rates and corresponding pressures to be obtained in the proximity of the anode heat exchange surface thus enabling more efficient heat exchange to be effected.
  • FIG. 1 is a complete cross section of a rotating anode x-ray tube
  • FIG. 2 is a perspective view of the anode- septum assembly illustrating centrifugal pump vanes mounted on the anode to increase the liquid flow rate, axial flow pump vanes mounted on the septum to direct the liquid flow and turbine vanes mounted on the anode discharge face for liquid discharge;
  • FIG. 3 is a partial side cross-sectional view of the anode septum assembly showing centrifugal pump vanes, axial flow pump vanes and turbine vanes;
  • FIG. 4 is a partial vertical view of the septum showing the axial flow pump vanes mounted on the septum;
  • FIG. 5 is a perspective view of the anode- septum assembly illustrating centrifugal pump vanes mounted on the anode for increasing the liquid flow rate and liquid converging means and axial flow vanes mounted on the septum to induce swirl flow at the anode heat exchange surface;
  • FIG. 6 is a partial vertical view of the septum and anode walls illustrating the liquid converging means and axial flow vanes mounted on the septum;
  • FIG. 7 is a partial cross-sectional view of the anode-septum assembly illustrating the centrifugal pump vanes mounted on the anode, the liquid converging members mounted on the septum, swirl flow interacting with the anode, and discharge of the liquid between
  • FIG. 8 is a partial side cross section of the anode septum assembly illustrating centrifugal pump vanes, liquid converging members, swirl flow of liquid, and discharge of liquid;
  • FIG. 9 is a partial cross-sectional view of the anode-septum assembly illustrating centrifugal pump vanes mounted on the input anode face, and radially oriented orifices in the septum to provide jets of liquid to impinge on the anode heat exchange surface;
  • FIG. 10 is a partial side cross-sectional side view of the anode-septum assembly illustrating centrifugal pump vanes for increasing the ⁇ liquid flow rate, radially disposed jets in the septum liquid jets interacting with the anode heat exchange surface, and radially disposed vanes on the discharge face of the septum;
  • FIG. 11 is a partial vertical view of the anode-septum assembly illustrating the radially disposed jets in the septum;
  • FIG. 12 is a perspective view of the anode- septum assembly illustrating axial flow pump blades mounted on the inside diameter of hollow rotating shaft for increasing the liquid flow rate;
  • FIG. 13 is a cross section view illustrating the axial flow pump blades
  • FIG. 14 is an illustration of an x-ray tube assembly
  • FIG. 15 is a partial cross section view of the anode-septum assembly illustrating multiple focal tracks on an angled focal track surface and associated electron g ns, and means for diverting a portion of the heated exhaust liquid to mix with the incoming cold liquid coolant thereby causing a predetermined recirculation of the liquid coolant with the anode;
  • FIG. 16 is a partial cross section view of a septum and a rotating anode with a "V" groove illuminated by the electron beam, each side of the curved liquid cooled “V” groove having liquid flowing inward toward the center of the septum, said liquid being propelled by means attached to the anode; and
  • FIG. 17 is a partial cross section view of surface roughness elements disposed on the anode heat exchange surface in the form of approximate truncated cones containing cavities exposed to the liquid coolant.
  • a hollow anode 20 attaches to a hollow rotating shaft 21.
  • a rotational fluid seal 22 is mounted at the end of hollow shaft 21.
  • a stationary cupped cylindrical attachment 23 with entrance duct 24 is mounted to rotational fluid seal 22.
  • a stationary tube 25 disposed concentrically with, and extends through, stationary hollow cupped cylindrical attachment 23.
  • a hermetic seal is provided between attachment 23 and stationary tube 25.
  • O PI 25 extends longitudinally, and concentrically, within hollow rotatable shaft' 21 into the hollow rotatable anode 20.
  • a stationary septum 26 is mounted on hollow stationary tube 25, and disposed within hollow anode 20.
  • Hollow anode 20 is rotatably coupled to stationary septum 26 by a rotational bearing 27 and a fin shaped radial support and centering structure 28 attached to the inner, stationary segment of bearing 27.
  • a rotatable bearing member 29 including an inner rotating segment 30 and outer stationary segment 31 is utilized to rotatably couple rotatable shaft 21 to a mounting member' 32 and to a vacuum envelope 33.
  • Inner rotating segment 30 of rotatable bearing member 29 is fastened to the outside diameter of hollow rotatable shaft 21.
  • Outer stationary segment 31 of rotatable bearing member 29 is fastened to mounting member 32 and vacuum envelope 33.
  • Suitable rotatable high vacuum sealing means 34 such as ferrofluidic seal, is incorporated in bearing 29 to vacuum seal stationary member 31 to rotatable shaft 21 to facilitate the provision of a vacuum within vacuum envelope 33, surrounding anode 20.
  • Electron gun 36 is mounted within vacuum envelope 33. Electron gun 36 provides an electron beam 37 focused upon electron beam track 38 on the exterior periphery of anode 20. Illumination of anode 20 by beam 37 causes generation of x-rays which exit through a vacuum tight x-ray transparent window 39 in vacuum envelope 33.
  • a pulley 40 or other means, is connected to a suitable motor by a belt (not shown) to provide rotational drive to shaft 21, and thus, anode 20.
  • a port 35 is provided in envelope 33 for attachment to means, not shown, to obtain or maintain the necessary
  • the vacuum may be generated by, for example, barium, titanium or zirconium getters or VAC-Ion, titanium sublimation., cryogenic, turbomolecular, diffusion or other vacuum pumps.
  • FIG. 1 The basic structure of FIG. 1, having been described above, functions as follows. Cooled fluid from an external heat exchanger and pump assembly (not shown) is pumped into the x-ray tube through duct 24. The coolant then travels toward the anode 20 between the outer diameter of stationary inner tube 25, and the inner diameter of rotatable hollow shaft 21. The coolant then passes along inside input face 41 of anode 20, and outside of input face 42 of septum 6, until it reaches the anode heat exchange surface 43.
  • Septum 26 serves to direct the entire coolant flow into close proximity to the anode heat exchange surface by providing a narrow channel between the septum 26 and anode heat exchange surface 43.
  • the width of the septum 45 is typically greater than the width of the electron beam track and is generally centered with the electron beam track.
  • the spacing between the septum and the anode heat exchange surface is designed to maintain optimum flow and heat exchange conditions.
  • the geometry is always such that the entire heat exchange surface of the anode is simul ⁇ taneously and continuously exposed to coolant flow. In this manner, the entire heat exchange surface is continuously cooled and hot spots cannot develop due to interrupted coolant availability. Thus, optimum heat transfer is obtained and maintained.
  • OMPI septum past support fins 28 and out through the inside of stationary tube 25. From there, the coolant proceeds to the external heat exchanger pump (not shown) and back to the x-ray tube. It is desirable that the temperature rise at the rotatable vacuum seal 34 be minimized.
  • the ferro- fluidic vacuum sealing fluids have viscosity and vapor pressure characteristics that are very sensitive to , temperature with the typical maximum operating temperature being 50°. Accordingly, the cooled liquid is passed between the outer diameter of inner tube 25 and the inner diameter of rotatable shaft 21. This passes cooled input liquid against the vacuum seal, to maintain minimum temperatures and thus optimize operating conditions. Reversing the direction of flow would pass-heated liquid next to the vacuum seal, raising the temperature of the seal.
  • the increased seal temperature tends to cause degradation of oper ⁇ ating rpm and degrades the vacuum due to the increased vapor pressure of heated ferrofluids.
  • the coolant flow direction could be reversed which has the advantages with respect to minimizing induced rotational velocity in the liquid flow.
  • the critical heat flux, i.e. burn out, and rate of heat removal are determined by the formation of nucleate bubbles on the anode heat exchange surface 43 and removal of such nucleate bubbles on the heat exchange surface 43 by interaction with the coolant liquid.
  • the laminar nature of the liquid flow, and stable flow patterns caused by the rotation of the anode tend to retard removal of the bubbles, thus decreasing the heat removal capacity of the system.
  • the rate of removal can be increased by creating a pressure gradient in the coolant fluid perpendicular to the anode surface, and/or by breaking up the viscous sublayer of the coolant fluid nearest the heat exchange surface.
  • the rate of removal can also be increased by providing a high shear velocity between the anode heat exchange surface and the liquid.
  • this has entailed use of coolant liquid under high pressure. This has required use of relatively short-lived high pressure fluid seals.
  • the inherently stable flow pattern caused by the anode rotation has tended to limit the power rating of the prior art tubes.
  • FIGS. 2, 3, and 4 a first preferred embodiment of the present invention will be described wherein the liquid flow rate is increased by the provision of a centrifugal pump impeller mounted on the input face of the rotating anode, and axial flow pump vanes are mounted on the stationary septum to prevent inherently stable flow patterns due to the rotating motion of the anode, provides a high shear velocity between the liquid and the anode heat exchange surface.
  • FIG. 2 a cutaway perspective of the anode-septum assembly of the first preferred exemplary embodiment for a general description of the embodiment.
  • a plurality of centrifugal pump vanes 58 are mounted on the interior input surface 41 of anode 20.
  • a plurality of turbine vanes 76 are fixed to the interior outboard face 78 of the rotating anode. The rotation of the anode causes rotation of the attached centrifugal pump and exhaust turbine vanes.
  • SUBSTITUTE SHEET ⁇ plicity of generally S--shaped axial flow pump vanes 66 are mounted on the surface of stationary septum 26 facing the anode heat exchange surface 43.
  • cooled input liquid 50 flows in toward anode 20 between the inside diameter of hollow rotary shaft 21 and the outside diameter of inner stationary tube 25.
  • the cooled input liquid then is engaged by centrifugal pump vane 58, which directly utilizes the rotation of the anode to impart radial and circumferential velocity to the coolant.
  • centrifugal pump vane 58 which directly utilizes the rotation of the anode to impart radial and circumferential velocity to the coolant.
  • the axial flow pump vanes 66 generally of a "S" shape, extend across the peripheral surface of septum 26.
  • Axial pump vanes 66 redirect the liquid into a plurality of independent channels disposed transverse to the direction of rotation (generally parallel to the axis of rotation) ; to prevent formation of stable flow patterns by the rotational motion of the anode.
  • the liquid After passing the anode heat exchange surface 43, the liquid is engaged by exhaust turbine vane 76 which is attached to output anode face 78.
  • the exhaust turbine vane 76 serves to enable the liquid to smoothly make the transition from the axial flow pump vanes 66 to . • the exhaust tube 25 with a minimum of undesirable flow characteristics such as cavitation, eddies and vortex shedding.
  • the curvature of the septum 26 and vanes 66 serve to further assist in the smooth transit of the liquid flow.
  • the exhaust liquid After passing through stationary exhaust tube 25, the exhaust liquid is carried to an external heat exchanger and is then again pumped back to the x- ray tube with a low pressure pump.
  • Centrifugal pump vanes 58 are all suitably connected to a common shroud 98 along the vane peripheries proximate to septum 26.
  • the spacing 96 between the centrifugal pump vane shroud 98 (or vane periphery) and the septum surface 42 is set at a small value to provide a bearing surface for the rotating anode thereby to avoid or minimize vibration.
  • This desired spacing 96 is- a function of liquid viscosity and the surface speed of the rotating shroud 98 and stationary surfaces 42.
  • Entering liquid 50 is engaged, as best shown in FIG. 3, by centrifugal pump vane 58 mounted on anode face 41.
  • the liquid engaged by vanes 58, 94 generally indicated by arrow is accelerated up the anode in the manner of a conventional centrifugal pump.
  • the liquid Upon leaving the end 62 of centrifugal pump vane 58, the liquid (designated by arrow 104) engages the axial flow pump vane 66.
  • the spacing 108 between centrifugal pump vane and edge 64 of axial flow pump vane 66 is designed so as to permit optimum liquid coupling 9.
  • the liquid flows through the axial flow pump vanes 66 past the anode heat exchange surface 43 of width 110, which may have calculated surface roughness thereon as previously described.
  • the anode heat exchange surface 43 is shown as suitably curved, said curve being one of an infinite number of curves lying in the plane containing the axis of rotation of the anode, said plane being rotated about said axis of rotation.
  • the liquid flowing over the curved anode heat exchange surface generates a pressure gradient having a component perpendicular to the anode heat exchange surface, thereby improving heat transfer and minimizing cavitation.
  • the peripheral surfaces of septum 26 and axial flow pump vanes 66 are correspondingly curved thereby minimizing
  • the anode heat exchange surface 43 is shown as suitably curved, said curve being one of an infinite number of curves lying in the plane containing the axis of rotation of the anode and rotated about said axis.
  • the body force generated by the liquid flowing over the anode heat exchange surface has a component perpendicular to the anode heat exchange surface.
  • the peripheral surfaces of septum 26 and axial flow pump vanes 66 are correspondingly curved thereby minimizing undesirable flow characteristics such as cavitation and enabling the proper anode-axial flow pump vane 120 to be maintained.
  • the electron beam track 38 on the anode surface is illuminated by electron beam 37.
  • the spacing 120 between the inner wetted anode surface 122 and the periphery of the axial flow pump vanes 124 is small enough to break up the inherently stable rotational flow that is frequently present in conventional tubes. In addition, the spacing 120 is further optimized so as to provide additional support for anode vibration suppression as will be explained. Leaving the axial flow pump vane, the liquid is engaged by the exhaust turbine vane 76 whence it is directed toward exhaust tube 25. As best seen in FIG. 3 each of the turbine vanes 76 suitably include inwardly curved transition portions 132, and 134 approaching exhaust tube 25 to inhibit undesirable flow characteristics such as cavitation, eddies and vortex shedding. Turbine vanes 76 are also suitably coupled along the peripheries proximate to septum 26 by a shroud 138. Spacing 136 (or vane periphery) is designed to be small enough to serve as a bearing
  • Axial flow pump vanes 66 direct the fluid along a plurality of independent channels disposed transverse to the direction of rotating (generally parallel to the axis of rotation).
  • the plurality of independent channels prevents formation of stable flow patterns due to the rotational motion of the anode and optimized heat transfer.
  • liquid flow, denoted by arrow, 142 from anode mounted centrifugal pump enters the curved section 144 of the axial flow pump vane 66.
  • the curved section 144 of axial flow pump vane 66 serves to provide a smooth change in direction for the liquid thereby eliminating or minimizing undesirable flow characteristics such as cavitation, eddies or vortex shedding.
  • OMPI surface and supplying cool liquid to the anode heat exchange surface as the liquid flow traverses the path of anode rotation.
  • the high shear velocity between the anode and liquid combined with the high pressures generated by centrifugal pump vanes (i.e. over 200 psi) , and the liquid changing direction provides high heat transfer.
  • the liquid After passing the anode heat exchange region, the liquid is again redirected by a further curved portion 152 of axial flow pump vane prior to its smooth transition to the exhaust turbine vanes (not shown) .
  • FIG. 4B A slot 154 of predetermined * ⁇ width and depth is provided in the axial flow pump vanes.
  • the slot width corresponds approximately in dimension and position to the width of the anode heat exchange surface and the depth of the slot corresponds approximately to the diameter of the larger nucleate bubbles.
  • the nucleate bubble is not "scraped off" by the axial flow pump vane with consequent collapse on the vane and possible resultant damage. Instead, the nucleate bubble can pass into the next conduit defined by the next pair of axial flow vanes where it can release into the coolant and thereby pose no potential for damage on the metal surface of the vane.
  • the depth of the slot is.
  • TE SHEET OMPI small enough to permit vanes 66 to significantly reduce any stable rotational patterns induced in the liquid by the rotation of the anode. In some cases, collapse of nucleate bubbles on metal surfaces can also be avoided by the contouring or calculated roughness of the anode heat exchange surface.
  • the anode-septum structure shown in FIGS. 2, 3, and 4 provides, in effect, a centrifugal pump on the liquid inlet side and a turbine on the discharge side to obtain high fluid pressure and flow in the vicinity of the anode heat exchange surface.
  • the provision of axial flow pump vanes on the septum, between the input centrifugal pump and exhaust turbine, serves optimally to redirect the flow rates of the liquid so that it traverses the direction of anode rotation.
  • the design of the various vanes i.e.
  • the liquid accelerating and directing surfaces, the input centrifugal pump mounted on the input side of the anode, the axial flow pump vanes mounted on the septum and the turbine vanes on the discharge side of the anode, are shaped so as to provide for acceleration, change of direction and exhaust of the coolant liquid in such a manner as to avoid undesired flow characteristics such as cavitation, vortex shedding, eddies and inherently stable rotation such as commonly occur in conventional liquid cooled rotating anode x-ray tubes.
  • undesired flow characteristics such as cavitation, vortex shedding, eddies and inherently stable rotation such as commonly occur in conventional liquid cooled rotating anode x-ray tubes.
  • the centrifugal pump impeller is built into the input face of the anode.and serves to accelerate
  • the relative velocity of anode to liquid is the resultant of the anode velocity vector and the liquid flow velocity vector. in general, the resulting relative velocity of anode to fluid will be substantially greater than either velocity alone thereby further improving heat transfer.
  • the anode heat exchange surface is prepared, in accordance with the teachings of the aforementioned copending application SN 250,275 by Iversen with a calculated surface roughness such that the height of the surface roughness elements is not less than 0.3 times the thickness of the viscous sublayer and not more than
  • SUBSTITUTE SHEET OMPI the sum of the thickness of the viscous sublayer and the transition zone.
  • the axial flow pump vanes After passing through the anode heat exchange region, the axial flow pump vanes again redirect the liquid flow such that a smooth transition is made into the exhaust turbine, the turbine impeller design being similar to that of conventional turbine pumps.
  • the exhaust turbine serves to smoothly, and again without unwanted flow characteristics, direct the flow of the heated coolant radially down the face of the anode and into the exhaust tube contained concentrically within the hollow anode shaft for discharge into the external heat exchanger.
  • a further important consideration in the design of liquid cooled rotating anode x-ray tubes is the problem of vibration.
  • vibration is highly undesirable because of the small dimensions and fine tolerances being sought, typically sub-micron.
  • the second source of vibration is improper liquid flow in the system such as cavitation, vortex shedding and eddies.
  • improper liquid flow is caused by liquid flowing through improper conduit geometries such as around or into sharp corners.
  • the third is improper pump element and housing design i.e. improper tolerance between close spaced stationary and moving parts.
  • the dimensions provide a close fit between the anode face and the top of the vane.
  • the vanes also serve as a support to the anode and thereby reduce the vibration caused or amplified by the large gap i.e. the liquid flow passage, between the anode and the septum.
  • the centrifugal pump and turbine similarly provide added structural support to reduce vibration and suppress induced rotational motion in the liquid flow caused.by the rotation of the anode.
  • OMPI Suppression of rotational flow has special importance on the discharge side of the anode where the liquid must travel radially inward toward the anode shaft for discharge inasmuch as the centrifugal force arising from the induced rotational motion of the liquid requires a corresponding increase in pump pressure to overcome it.
  • pump pressure can be reduced with a corresponding increase in the life of the rotating liquid seals, and economy of pump, fittings, etc.
  • the fluid flow path can be configured to maximize swirl flow in the anode heat exchange region. Heat transfer is enhanced by the centrifugal force generated by the swirling motion of the coolant as it traverses the anode heat exchange surface.
  • a pressure gradient with a component perpendicular to the anode heat exchange surface is established that more rapidly breaks ' loose the nucleate bubbles thereby increasing both the heat flux and the critical heat flux i.e. burn out.
  • the swirl flow is maximized by disposing converging elements at the input side of axial flow vanes traversing the top of the septum such that the radial thickness of the rotating liquid is reduced to approximately one-half of the effective diameter of a swirl flow conduit comprising the axial flow vane surface, the anode surface, the opposite axial flow vane surface and the septum surface. Then, the liquid is injected into the anode heat exchange region tangential to a surface of the conduit.
  • the injection angle of the coolant into the swirl flow conduit is such that the tangent of the angle is the ratio of the width of the injected coolant stream to the effective circumference i.e. outer diameter of the swirl flow conduit.
  • the axis of the swirl flow conduits will be at approximately 90°
  • Heat transfer is further enhanced because the preferred orientation of injection of the liquid into the axial flow vane conduit is such that the liquid is flowing substantially in the opposite direction of anode rotation at the anode surface, that is, the vector sum of the two velocities, i.e. liquid and anode, can approach the sum of the scalar values.
  • the large surface of the converging element also serves to further improve anode support i.e. a substantial increase in the bearing surface thereby further inhibiting any vibration.
  • the heated liquid flow After passing the anode heat exchange region, the heated liquid flow leaves the axial flow pump vanes and enters the discharge face of the anode to travel down the face of the anode toward the exhaust tube that is concentric with the hollow anode shaft.
  • the angle i.e. direction of discharge of the swirl flow into the exhaust face of the anode may be selected.
  • the preferred direction of discharge is approximately
  • vanes with peripheral surfaces in close proximity to the anode face are mounted radially on the discharge face of the septum to minimize rotational velocity induced in the liquid by the rotating anode as the liquid travels toward the exhaust exit tube and to assist in the suppression of vibration.
  • Such an anode-septum structure will hereinafter be more fully described in conjunction with FIGS. 5, 6, 7 and 8.
  • liquid is directed through the conduit formed by the inside diameter of the anode rotating shaft 21 and the outside diameter of tube 25, to centrifugal pump vanes 58, which accelerate the ._ liquid toward the anode heat exchange region.
  • each conduit 174 communicates with an associated axial flow channel, formed between successor flow vanes, the anode heat exchange surface and the top of septum 26.
  • Each converging member 170 includes a. first (entry) portion 176 disposed proximate to the periphery 62 of pump vanes 58, complex intermediate surface 180 and a discharge portion 178.
  • the respective entry portions 176 extend outwardly from the side of septum 26 a distance (width) 194.
  • Complex intermediate surface 180 provides a smooth transition curve from outwardly extending portion 176 to a
  • Successive converging members provide an injection orifice (narrow portion) in conduit 174 of width 194 and length 192 (as will be explained) , which cooperates with complex curved surface 180 to achieve the desired swirl flow geometry in the anode heat exchange region.
  • the face of entry portion 176 is suitably disposed at an angle parallel to the velocity vector of the coolant as it leaves the centrifugal pump region.
  • the liquid velocity vector is the resultant of the radial velocity component and the tangential velocity component imparted by the centrifugal pump vane.
  • the converging member entry portion face 176 may make an angle with the coolant velocity vector. A preferred angle would be 7°.
  • the opposite face of conduit 174 i.e. the back surface of the successive converging member
  • FIG. 6 is a top view of the septum containing the converging member 170 and corresponding conduit 174 of width 192 and length 194.
  • the swirl flow conduit 196 which includes the anode heat exchange surface, whose width 198 and length 200 are bounded by axial flow vanes 202 and 204 on-the sides and by the septum surface 26 on the
  • the purpose of 20 the injection angle ⁇ is to ensure that the liquid flow does not interfere with itself as would be caused by a smaller angle and that there are no gaps between the adjacent leading and trailing edges of the flow, as would be caused by a greater angle of injection. 25 The first condition, a smaller angle, would result in reduced heat transfer, whereas the second condition, a larger angle, would result in premature burn out.
  • peripheral surfaces 312 of the converging member 170 are in close proximity at a distance 214 to 30 -the anode surface and thus act as bearing members to suppress vibration.
  • shroud on the centrifugal pump is also disposed in close proximity to the septum, to provide bearing support and suppresses vibration.
  • OMPI Referring now to the lefthand side of FIG. 7, a sectional view of the anode-septum structure taken just on the input side of septum 26 is shown.
  • the coolant liquid (denoted 216) is accelerated up the face of the anode 20 by centrifugal pump vanes 58.
  • the liquid (at point 222) enters converging members 170, and is redirected by converging member face 180 so as to enter the anode heat exchange region in swirl flow 228 in a direction opposite that of anode rotation (denoted by arrow) 230 at the anode heat exchange surface, thereby obtaining a very high shear velocity between the anode and liquid.
  • the calculated surface roughness 112 on the anode heat exchange surface combined with the pressure -gradient perpendicular to the anode surface generated by centrifugal force of the swirl flow combine to further increase the heat transfer and increase the critical hea flux.
  • the radii 234 of the junctures of the axial flow vanes and septum surface are chosen to eliminate any dead spots or eddies.
  • the peripheral portion of the axial flow vanes may also have a radius 236 provided to better conform to the circular nature of the swirl flow.
  • An alternative is to set up a secondary swirl flow 238, 239 hetween the anode heat exchange surface 43, the periphery of the axial flow vane 242 and the main swirl flow 186. What makes this possible is the fact that the anode rotation 150 and the main swirl flow 186 are in opposite directions.
  • the secondary swirl flow 238, 239 is driven in the same direction of rotation alternately by the anode rotation and then the swirl flow rotation.
  • the secondary swirl flow having been derived from the primary flow, will follow along with it through the swirl flow conduit.
  • the relative axial velocity of the secondary swirl flow to the primary flow will vary depending upon relative energy losses i.e. friction, mixing, etc.
  • the peripheral surfaces 242 of the axial flow vanes are in close proximity to the anode heat exchange surface 43 and thus act as bearing members to suppress vibrations as previously discussed.
  • the swirl flow having passed the anode heat exchange region exists through discharge aperture 208, the width ' 252 of the aperture 208 being about 1/2 of the diameter 210 of the swirl flow conduit.
  • the exhaust coolant should traverse the' discharge face of the anode, not shown, such that it enters the exhaust tube 25 with a minimal circumferential component of velocity. This may be achieved by positioning the orifice 208 at the discharge end of the swirl flow conduit such that the velocity vector 258 of the swirl flow is pointing radially inward toward the exhaust tube 25.
  • Stationary vanes 260 are mounted on the exhaust side face of the septum 26 and extend to close proximity to the anode wall to guide the coolant flow into the exhaust tube 25 and to inhibit the circular flow of coolant as induced by anode rotation. The close proximity of the vanes to the anode also serve as a bearing surface thereby further inhibiting vibration.
  • FIG. 8 illustrates a cross section view of the anode and internal components.
  • the coolant 264 is shown entering the centrifugal impeller 58 from the
  • OMPI conduit comprising the inside diameter of the hollow anode shaft 21 and the outside diameter of the discharge tube 25.
  • Pumping means in this case a centrifugal pump impeller 58, propelling the coolant up the face of the anode 41 toward flow converging means 170.
  • the path 276 of the liquid is also changed such that the direction and cross section of the liquid conforms to the predetermined conditions previously described.
  • the conditions that should be met are that the coolant is injected into the swirl flow region 196 tangent to one of the surfaces defining the swirl flow region and is of such cross section that optimum swirl flow conditions are obtained.
  • the swirl flow 186 passes through the anode heat exchange region 43 and exits down the anode discharge face 78 and into exhaust tube 25.
  • the gap 290 between the centrifugal impeller 58 and the septum 26 is small.
  • the gap 296 between the liquid converging 170 means and the anode 20 is also small.
  • the gap 303 between the- axial flow vanes 202, 204 and the anode 20 is also kept small.
  • the gap 308 between the exhaust vanes 260 and the anode exhaust face is kept small.
  • a third preferred embodiment of the present invention includes the centrifugal pump impeller of the embodiment of FIGS. 2-4 as a means to increase the liquid flow rate, and incorporates a septum whose width is at least equal to the anode heat exchange surface and which is provided with a multitude of approximately radially directed conduits which, on the impeller side have their axis in line with the liquid flow and on the anode side have their axis directed somewhat toward the liquid discharge side of the anode.
  • the centrifugal impeller vanes are directly under the apertures in the stationary septum so that the accelerated liquid is directed into the conduits defined by the apertures whence it is directed at the anode heat exchange surface in the prescribed manner.
  • the conduits are preferably curved so as to accept the liquid from the centrifugal- pump impeller and redirect it to the anode heat exchange surface in the desired manner while not inducing undesirable flow patterns such as cavitation, eddies, or vortex shedding which can cause a reduction in power handling and vibration.
  • the discharge side of the anode may have radially aligned vanes attached to the stationary septum such as in the manner of the embodiment of FIGS. 5-8. Such a third embodiment is shown in FIGS. 9, 10, and 11.
  • centrifugal pump vanes 58 are mounted on the input face of the anode, and liquid jet conduits 326 are constructed into the thickness of septum, and radially disposed vanes on the discharge face of the septum.
  • centrifugal pump vanes 58 which are mounted integrally on the coolant wetted input face 41 of the anode 20.
  • centrifugal pump vanes 58 may be shrouded to improve efficiency.
  • the liquid flow which may have energy imparted to it by the centrifugal pump vanes corresponding to pressure in excess of 200 psi, enters the conduits 326, which may be circular, after leaving the tip of the centrifugal pump vane 62.
  • the conduit 326 may be shaped in a curved manner such that the liquid flow exits in a direction 329 opposite that of the direction 150 of anode rotation and angled toward the exhaust side of the anode.
  • the radial thickness 332 of the septum section containing the conduits 36 is such that the conduits, .which are constructed approximately along a radius of the septum create minimal undesirable flow patterns such as cavitation, eddies or vortex shedding.
  • the high velocity jets of liquid 328 from the multitude of conduit exits 330 strike the anode heat exchange surface 43.
  • heat exchange surface 43 may include a calculated surface roughness to further enhance heat transfer.
  • the coolant liquid develops a flow 334 exiting down the discharge face of the anode after passing the anode heat exchange surface 43.
  • stationary septum 26 includes a relatively thin plate 313, mounted on * exhaust tube 25, and a peripheral cylindrical portion 315 disposed underlying anode heat exchange surface 43, extending inwardly from plate 313 towards anode wall 41.
  • O PI septum portion 315 is greater than the width of heat exchange surface 43, and approximately central beneath heat exchange surface 43 liquid enters the centrifugal pump region 314 from the conduit 316 consisting of the inside diameter of the hollow rotating shaft 21 and the outside diameter of the coolant exhaust tube 25.
  • the liquid is accelerated toward the anode heat exchange region by the centrifugal pump vanes 58, which are mounted integrally on the coolant wetted input face 41 of anode 20. Vanes 58 extend to proximity with plate 313 (or the associated shroud is disposed proximate to plate 313) and underlie cylindrical septum portion 315. It is seen that the width 348 of the centrifugal pump vanes is of an extent approximately equal the width of cylindrical septum portion 315.
  • conduits 326 When the anode is rotating, high pressure generated by the centrifugal pump vanes 58, generally. ' in excess of 200 psi for a 4-inch diameter anode rotating at 10,000 RPM, forces the liquid 328 through the conduits 326 at a high velocity.
  • the entrance axis to conduits 326 may be parallel to the velocity vector of the liquid 328 to minimize undesirable flow characteristics due to discontinuities when entering the conduit 326.
  • Conduits 326 are curved in such manner as to direct the exiting liquid jet 329 in a direction opposite that of the anode rotation, and angled towards the exhaust face of the anode.
  • the high velocity liquid jets 329 strike the anode heat exchange surface 43 at a specified angle thereby providing a high shear velocity and a pressure gradient perpendicular to the anode heat exchange surface, combining to provide high heat transfer and breaking up inherently stable flow patterns. After passing the anode heat exchange surface 43, the liquid
  • OMPI 33 discharges down the exhaust face 78 of the anode between radially disposed vanes 364 mounted on the exhaust face of the septum 140 and thence out stationary discharge tube 25.
  • the width 110 of the anode heat exchange surface 43 is generally from one to nine times greater than that of the width of the electron beam track 37.
  • the factor of nine may be greater depending on the anode wall thickness and thermal conductivity of the metal.
  • the number of high velocity jets of liquid 328 is approximately determined by the septum width 352 times the septum circumference (not shown) divided by the center to center conduit spacing 390.
  • the exits of the respective conduits 326 (and the jets 328) are disposed on cylindrical septum portion 315, in staggered rows such that essentially the entire heat exchange surface is sequentially inundated by the liquid coolant jets.
  • the liquid 328 having passed the anode heat exchange surface 43, discharges past the anode exhaust surface 78, being confined by radial vanes 364 to minimize rotational velocity induced by the anode exhaust surface 78. After traversing the anode exhaust face, the liquid 328 discharges through the concentric stationary exhaust tube 25 to an external heat exchanger prior to return to the tube. As previously discussed, the gap 394 between all close spaced rotating and stationary members, such as the periphery 402 of the vanes 364 mounted on the septum discharge surface 140 is maintained small so as to
  • a fourth preferred embodiment of the present invention provides for axial flow pump blades to be mounted on the inside diameter of the hollow rotating shaft and extending to close proximity to the inner stationary exhaust tube.
  • One or more sets of axial flow pump blades may be mounted in series within the hollow rotating shaft so as to increase the liquid flow rate, and radially disposed vanes mounted on the input face of the septum and extending past the anode heat exchange surface and down the discharge face of the septum may be incorporated as the liquid directing means.
  • FIGS. 12 and 13 illustrate the fourth preferred exemplary embodiment of the present invention.
  • FIG. 12 is perspective view of the anode- septum assembly.
  • Liquid is injected 406 into the input liquid conduits at an angle that corresponds to the pitch angle of the helical vane 408 mounted on the outside diameter of the inner stationary exhaust tube 25.
  • a second stationary tube 412 which generally has a thin wall thickness, may be mounted to the periphery 414 of the helical vane 408.
  • the spacing 416 between the outside diameter of the second stationary tube 412 and the inside diameter of the hollow rotating shaft 21 is kept as small as possible.
  • the bulk of the liquid is isolated from rotationally induced motion of the hollow rotating shaft 419.
  • Helical vane 408 produces in the liquid a rotation 410 that is opposite that of the rotation of the anode 150.
  • the liquid, upon leaving the helical vane is almost immediately engaged by axial flow pump blades 414.
  • OMPI blades are mounted to the inside diameter of the hollow rotating shaft 21. Shown is a single set of blades, one stage. To further increase the liquid flow rate, a series of stages of axial flow pump blades may be mounted on the inside diameter of the hollow rotating shaft. The axial flow pump blades tend to also induce rotational motion in the liquid. However, because the liquid has rotational motion 410 induced by the helical vane 408 that is opposite that of the anode 20 the rotation induced by the axial flow pump blades 414 can be partially cancelled. The liquid 421 then travels up the input anode face 41 between approximately radial vanes 422 mounted around the circumference of the input face 424 of the stationary septum 26.
  • a shroud i.e. thin plate
  • the liquid then passes the anode heat exchange surface 43.
  • the shape of the vanes 430 in the vicinity of the anode heat exchange surface may be such as to optimize heat transfer by virtue of a high shear velocity as in the first preferred embodiment, or the vanes may have flow converging members to induce swirl flow as in the second preferred embodiment, or, the septum may have liquid jet conduits constructed into the peripheral thickness of the septum as described in the third preferred embodiment.
  • the liquid 432 After passing the anode heat exchange surface 43, the liquid 432 exhausts down the discharge face 78 of the anode confined by approximately radial vanes 436 mounted on the
  • FIG. 13 is a cross section view of the axial flow pump blades.
  • the blades 414 are mounted to the inside diameter of the hollow rotating shaft 21 which supplies the needed rotational motion 454.
  • the spacing 448 between the outside diameter 450 of a stationary exhaust tube 25 is designed for optimum performance. Shown is one set of blades for a single stage pump. Sets of blades may be seriated on the inside diameter so as to obtain the desired flow rate.
  • the liquid cooled rotating anode x-ray tube is mounted within an x-ray tube assembly.
  • an x-ray tube assembly typically comprises the following elements: an x-ray tube housing 456 which is generally made from an x-ray absorbing material; an x-ray beam limit device 458, commonly called a collimator; a liquid cooled rotating anode x-ray tube 464, as previously described; a motor 466 and a drive belt 468, or other means for rotating the anode at the desired rpm.
  • Collimator 458 may contain movable shutters 460 to permit a variable x- ray field size 462 to be obtained.
  • a vacuum pump 470 is mounted on or within the x-ray tube vacuum envelope to maintain the required vacuum.
  • Vacuum pumping means that may be used include, for example, getters of Vac- Ion, titanium sublimation, cryogenic, diffusion or turbomolecular pumps. These pumps may be used alone or in combination. High 472 and low 474 voltage cables and connectors are utilized as required. A suitable high voltage isolation medium 476 is re ⁇ uired
  • a suitable medium 476 may be a gas such as a freon or sulphur hexafluoride or a liquid such as fluorocarbon, a silicone oil or a transformer oil.
  • a vacuum may also be used as an insulating medium or selected regions may be potted with solid dielectrics such as epoxy or silicone. The above illustrative insulating means may be used alone or in combination.
  • a heat exchanger 478 is required if the coolant system is to be of the closed loop type.
  • the heat exchanger contains a pump 490 for circulating the coolant fluid and heat exchange means 482 to transfer the heat to a secondary medium.
  • the secondary medium is suitable air for air- cooled system and water for a water-cooled system.
  • Suitable couplings and hoses 484 are utilized if the heat exchange is external to the x-ray tube assembly.
  • Mounting elements 486 for the x-ray tube within the x-ray tube housing are also provided. These mounting elements are suitably formed of dielectric materials such as ceramic or plastic " for high voltage isolation.
  • External mounting means 488 are also provided for mounting the x-ray tube assembly in the desired systems configuration.
  • the rotating anode designs of the present invention will accommodate focal spot dimensions ranging from the very large with average powers in the hundreds of kilowatts that are used in x-ray crystallography to circular microfocal spots of a few kilowatts power or less that are used for high resolution imaging. In both instances, the high power densities present require high liquid coolant flow rates in order to achieve high cooling efficiencies.
  • the full liquid flow is probably required to keep the average temperature rise of the liquid coolant within reasonable bounds.
  • the average temperature rise of the liquid coolant is negligible. In these circumstances, the liquid coolant flow rate is excessive from an average power dissipation viewpoint.
  • Electron guns 153 and 155 are disposed radially with respect to
  • SUBSTITUTE SHEET ' O H the anode focal track surface and spaced at an angle apart, in this instance 180°.
  • the generally close spacing 157 between focal tracks 149 and 151 is usually determined by heat transfer considerations i.e. maintaining optimum temperature gradients in order to minimize thermal stressing of the anode surface.
  • the position of the focal spot on the anode focal track surface from each of the electron guns may be positioned arbitrarily on the anode, depending upon the result desired. For example, two micro-focus spots, focused on adjacent tracks, may be spaced apart on the anode the inter-ocular distance in order to achieve stereo or 3-D f, vision w .
  • focal spots may be illuminated continuously, or may be alternately -turned on and off so as to synchronize with TV field rates or other periodic receiving means.
  • Another application of multiple focal spots, also focused on separate focal tracks on the anode is the use of three electron guns disposed about the anode such that they are spaced 120° or other suitable angle apart. In this manner, the three micro-focus spots may be used for precision location measurement and inspection by triangulation.
  • each anode focal track may be coated with different materials to provide different radiation characteristics.
  • each electron gun may be operated at different voltages with respect to the anode in order to .obtain different radiation characteristic i.e. above and below an absorption edge of the material being x- rayed.
  • a further example of the use of multiple focal spots is in the manufacture of semiconductors (VLSI) by x-ray lithography.
  • VLSI semiconductors
  • the output of previously described two focal spots on separate tracks spaced 180°, or other suitable angle, apart is viewed along
  • four x-ray focal spots are projected for lithography use.
  • the system geometry is established such that one wafer alignment mechanism can serve two adjacent focal spots and associated wafer stages.
  • One set of electronics can serve the two sets of wafer alignment mechanisms and four sets of wafer stages.
  • incoming liquid coolant flows towards the anode in the conduit defined by the inside surface of hollow rotating shaft 21 and outside surface of stationary exhaust tube 25.
  • the liquid is then engaged by centrifugal flow pump vanes 58 and propelled up anode input face 41.
  • the liquid is then engaged by axial flow pump vanes 66 and redirected to traverse the path of anode rotation while interacting with the anode heat exchange surface 43 in the same manner as has been described for FIG.
  • the anode heat exchange surface 43 is shown as suitably curved, said being one of an infinite number of curves lying in the plane containing the axis of rotation of the anode, said plane being rotated about said axis of rotation.
  • the liquid flowing over the curved anode heat exchange surface generates a pressure gradient having a component perpendicular to the anode heat exchange surface, thereby improving heat transfer and minimizing cavitation.
  • the peripheral surfaces of septum 26 and axial flow pump vanes 66 are correspondingly curved thereby minimizing undesirable flow characteristics and enabling the proper anode-axial flow pump vane spacing 120 to be maintained.
  • the anode surface containing the electron beam focal track is shown at an angle 6 with the anode surface 41, and the axial flow pump vanes 66 and septum 26 have geometries designed in * accordance with the principles of FIG. 2.
  • the angle ⁇ of the electron beam illuminated anode surface may be the same as for conventional solid anode rotating anode x-ray tubes, which enables an x-ray beam direction 145 which is normal to the axis of anode rotation, to be conveniently utilized. This has special merit when rectangular focal spots of long lengths to widths are utilized and which are projected at the shallow angle ⁇ to obtain an apparent square focal spot.
  • the now heated liquid Upon traversing the anode heat exchange surface 43, the now heated liquid is engaged by exhaust turbine vanes 76 and is exhausted down anode discharge face 78. upon reaching the base region of the exhaust turbine vane 133, the liquid is caused to divide into two flow paths, one path is through conduit 135 whereby a predetermined percentage of the exhaust liquid, as shown by arrow 137, is caused to
  • O PI join the incoming liquid at the anode input face 41.
  • the remainder of exhaust liquid flows into stationary discharge tube 25 and then to an external heat exchanger where it is recycled.
  • the percentage of liquid 139 that is exhausted is determined by the entrance cross section 141 of stationary exhaust tube 25.
  • the slit leaved segments 143 of the exhaust tube 25 may be compressed or expanded to alter input cross section 141 thereby varying in corresponding fashion the percentage of liquid that is exhausted.
  • FIG. 13 of the previously cited copending application by Iversen a "V" groove is provided in the electron beam illuminated surface of the rotating anode in order to provide a more uniform x-ray flux over most of the angle defined by the "V” groove.
  • FIG. 16 illustrates a more efficient liquid cooling means for the "V" groove anode heat exchange surface.
  • Liquid coolant enters the hollow anode structure 20 through the conduit defined by the ID of rotating hollow shaft 21 and the OD of stationary discharge tube 25.
  • Input liquid coolant 159 is caused to divide equally between opposite anode faces 41 and 78 by use of multiple conduits, one being shown as 161.
  • the axial flow pump vanes 165 are shown terminating in the vicinity of the apex 169 of the "V" shaped anode heat exchange surface 171. However, these vanes may be extended approximately radially down 175 into the septum discharge region 173 to connect with stationary discharge tube 25 thereby minimizing any rotational component of velocity of the discharge liquid as well as serving as additional support members.
  • Axial flow pump blades 414 as shown in FIGS. 12 and 13 may also be incorporated in FIG. 16 or may be used instead of the centrifugal pump vanes 58 and 181.
  • Stationary septum 26 has the geometry of the fluid diverter surface 177, in the region of the anode heat exchange surface 171, dimensioned such that either a constant or variable liquid velocity over the anode heat exchange surface 171 is obtained as caused by a constant or variable liquid conduit cross section.
  • the anode heat exchange surface 171 is shown as suitably curved, said curve being one of an infinite number of curves lying in the plane containing the axis of rotation of the anode, said plane being rotated about said axis of rotation.
  • the liquid flowing over the curved anode heat exchange surface generates a pressure gradient having a component perpendicular to the anode heat exchange surface, thereby improving heat transfer and minimizing cavitation.
  • peripheral surfaces of septum 26 and axial flow pump vanes 165 are correspondingly curved thereby minimizing undesirable flow characteristics and enabling the proper anode- axial flow pump vane spacing " to be maintained.
  • the liquid Upon passing the anode heat exchange surface 171, the liquid enters the interior 167 of stationary septum 26 whence it flows toward and into the stationary
  • OMPI discharge tube 25 and from there to an external heat exchanger (not shown) .
  • FIG. 17 A preferred embodiment of surface roughness elements 112 of FIG. 7 is shown enlarged in FIG. 17.
  • the surface roughness 112 is in the approximate form of a truncated cone 259 which contain a cavity 243 which is exposed to the liquid coolant 261.
  • the dimensions of cavities 243 of truncated cone 259 generally range from about ,002mm to .2mm.
  • the ,height of the roughness elements 245 ranges from 0.3 the height of the viscous sublayer to no more than twice the combined height of the viscous sublayer and the transition zone. For example, water at a velocity of 50 ft/sec. has a viscous sublayer thickness of about 5X10 * - * mm and a transition zone thickness of about
  • Spacing 247 between adjacent cavities is determined by maximum nucleate bubble diameter 249 such that at maximum heat flux, adjacent bubbles 251 and 253 do not merge to form the destructive film boiling condition. Spacing 247 generally ranges between .03mm and 3mm. Bubble size is determined by liquid and environment characteristics such as viscosity, surface tension, density, pressure, etc. Suitable methods for fabricating the cavities 243 include the use of laser drilling and mechanical drilling. The inside surface 255 of cavities 243 is further prepared with micro cavities 257, preferably reentrant, with dimensions generally in the range of 10 ⁇ 4 to 10 ""2 mm.
  • Micro cavities 257 serve as permanent vapor traps that remain in equilibrium with the liquid under all conditions, including those of lowest temperature and highest pressure, and serve as the initial nucleate boiling sites until the larger cavities 243 commence nucleate boiling.
  • full scale nucleate boiling becomes a two step affair, with
  • Micro cavities 257 act much like the starting motor in an automobile. Micro cavities 257 may be created by judicious selection of diamond, or other cutting material, particle size which is embedded in the drill bit. With the laser, reactive vapors or gases may be introduced which react with the anode material to create the desired pitting effect. Also, the outer surface of the truncated cone may also possess micro cavities due to the laser melting of material and subsequent deposition action at the edge of the cavity 243. A further preferred embodiment of the present invention incorporates the contoured surface concept described in International Publication No. WO 82/03522 published 14 October 1982.
  • the contoured surface of the above cited FIG. 7 is disposed on the anode heat exchange surface at an angle to the path of anode rotation in such a manner as to generate a component of velocity in the direction of liquid flow, said contoured surface acting basically in the manner of the axial flow pump blades of FIGS. 12 and 13 of the present invention.
  • the contoured surface so placed thus tends to assist in propelling the liquid in the desired direction, that is, towards the anode discharge conduit.
  • Said contoured surface also tends to inhibit any stable liquid flow patterns that might tend to be established in the anode heat exchange region and/or on the anode heat exchange surface.
  • the contoured surface of the above cited FIG. 7 is shown as linearly traversing the anode heat exchange surface at the appropriate angle. To more smoothly engage the liquid, the contoured surface may be curved, for example, in the
  • Another means, alone or in combination with the above, to provide smooth engagement of the liquid by the contoured surface is to vary the height of the contoured surface above the anode heat exchange surface as it traverses said heat exchange surface. In general, said height will be less at each end of the contoured surface and greater in the middle.
  • a preferred embodiment of said contoured surface are the flutes with rounded cusps of FIG. 4 of the above cited application by Iversen.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • X-Ray Techniques (AREA)

Abstract

Un appareil à anode rotative générateur de rayons X comprend un mécanisme qui utilise le mouvement rotatif de l'anode (20) pour augmenter le débit effectif de réfrigérant par rapport à la surfaced'échange thermique (43) de l'anode.
PCT/US1983/000204 1982-02-16 1983-02-16 Tubes anodiques a rayons x refroidis par un liquide Ceased WO1983002850A1 (fr)

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US348,785820216 1982-02-16

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Cited By (8)

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EP0142249A3 (en) * 1983-09-19 1986-02-05 Technicare Corporation High vacuum rotating anode x-ray tube
FR2575329A1 (fr) * 1984-12-21 1986-06-27 Thomson Cgr Gaine equipee a convection forcee pour tube radiogene a anode tournante
EP0212548A3 (en) * 1985-08-12 1988-06-08 Fujitsu Limited A rotary anode assembly for an x-ray source
EP0430367A3 (en) * 1989-11-29 1991-09-11 Philips Patentverwaltung Gmbh X-ray tube
GR910100291A (en) * 1990-07-09 1992-08-26 Gen Electric Engine cooling system by using a water - cooled rotor
EP0872872A1 (fr) * 1997-04-18 1998-10-21 Siemens Medical Systems, Inc. Cible pour production de rayons X
WO2000054308A1 (fr) * 1999-03-09 2000-09-14 Teledyne Technologies Incorporated Refroidissement d'une structure au moyen d'un fluide en ebullition et appareil a cet effet
US9202660B2 (en) 2013-03-13 2015-12-01 Teledyne Wireless, Llc Asymmetrical slow wave structures to eliminate backward wave oscillations in wideband traveling wave tubes

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US4130773A (en) * 1977-03-18 1978-12-19 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung X-ray tube with liquid-cooled rotary anode

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0142249A3 (en) * 1983-09-19 1986-02-05 Technicare Corporation High vacuum rotating anode x-ray tube
US4625324A (en) * 1983-09-19 1986-11-25 Technicare Corporation High vacuum rotating anode x-ray tube
FR2575329A1 (fr) * 1984-12-21 1986-06-27 Thomson Cgr Gaine equipee a convection forcee pour tube radiogene a anode tournante
US4734927A (en) * 1984-12-21 1988-03-29 Thomson-Cgr Equipped force-convection housing unit for a rotating-anode X-ray tube
EP0212548A3 (en) * 1985-08-12 1988-06-08 Fujitsu Limited A rotary anode assembly for an x-ray source
EP0430367A3 (en) * 1989-11-29 1991-09-11 Philips Patentverwaltung Gmbh X-ray tube
GR910100291A (en) * 1990-07-09 1992-08-26 Gen Electric Engine cooling system by using a water - cooled rotor
EP0872872A1 (fr) * 1997-04-18 1998-10-21 Siemens Medical Systems, Inc. Cible pour production de rayons X
WO2000054308A1 (fr) * 1999-03-09 2000-09-14 Teledyne Technologies Incorporated Refroidissement d'une structure au moyen d'un fluide en ebullition et appareil a cet effet
US6252934B1 (en) 1999-03-09 2001-06-26 Teledyne Technologies Incorporated Apparatus and method for cooling a structure using boiling fluid
US9202660B2 (en) 2013-03-13 2015-12-01 Teledyne Wireless, Llc Asymmetrical slow wave structures to eliminate backward wave oscillations in wideband traveling wave tubes

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EP0103616A4 (fr) 1986-06-11

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