Cooling sleeve for cooling a component to be cooled of a radiation generating device, and radiation generating device

Abstract

Cooling shell for cooling a component to be cooled of a radiation generating device and radiation generating device. The invention relates to a cooling shell (1) for cooling a component (2) to be cooled of a radiation generating device (37), wherein the cooling shell (1) extends along a longitudinal axis (3) and has inside it a receiving space (4) that is open at least on one side and also extends along the longitudinal axis (3) for receiving the component (2) to be cooled, wherein the cooling shell (1) has several cooling channels (5) provided for guiding a coolant and extending along the longitudinal axis (3), which are arranged radially outside the receiving space (4) and distributed around the receiving space (4).

Description

[0001] The invention relates to a cooling jacket for cooling a component of a radiation generating device. The invention also relates to a radiation generating device.

[0002] In the prior art, so-called target holders or X-ray tubes are known in connection with particle accelerators, especially linear accelerators, which are used to generate X-rays. These generally extend along a longitudinal axis and have a target at their tip or head section, for example a tungsten target, onto which an electron beam is directed to generate X-rays. X-ray tubes can heat up considerably during use and therefore require cooling. The head section of the X-ray tube with the target represents the point of greatest heat generation and therefore requires particularly effective cooling.

[0003] Cooling is typically achieved using a cooling shell consisting of several cooling bowls, in or between which a coolant, such as water or a water-glycol mixture, is circulated. The cooling bowls are arranged around the X-ray tube at varying distances or radii, essentially nested within one another. In other words, a smallest, inner cooling bowl surrounds the X-ray tube and is itself surrounded by one or more larger, outer cooling bowls.

[0004] In addition to cooling, the X-ray tube must also be shielded as effectively as possible to prevent the escape of X-rays in areas where this is not desired. Typically, the X-rays should only be able to escape unhindered at the head section of the X-ray tube, particularly in the longitudinal direction, so the shielding is primarily lateral. For this purpose, shell-like shields, for example made of highly absorbing tungsten, are known in the prior art. These are arranged around the X-ray tube and its cooling shells in such a way as to provide radial or lateral shielding, i.e., shielding in a direction away from the longitudinal axis.

[0005] There is potential for improvement in the known design of cooling shells, as the nested cooling shells occupy a considerable amount of space laterally and radially from the longitudinal axis. This comparatively large space requirement is disadvantageous because components surrounding the cooling shells must also be larger. The resulting increased material requirement is particularly detrimental with regard to the shielding that is mandatory for X-ray tubes and is typically very expensive and heavy.

[0006] The object of the present invention is therefore to provide an improved concept for a cooling shell for cooling a component of a radiation generating device, which in particular enables better cooling of the component to be cooled.

[0007] The aforementioned problem is solved according to the invention in a cooling shell of the type mentioned at the outset by the fact that the cooling shell extends along a longitudinal axis and has in its interior a receiving space open at least on one side and also extending along the longitudinal axis for receiving the component to be cooled, wherein the cooling shell has several cooling channels provided for guiding a coolant and extending along the longitudinal axis, which are arranged radially outside the receiving space and distributed around the receiving space.

[0008] The basic idea of ​​the invention is to guide the coolant through several cooling channels arranged side by side around the receiving space. In other words, the cooling channels are arranged in a cross-sectional area perpendicular to the longitudinal axis, particularly alternately, along a circumferential line, the circumferential line extending parallel and / or equidistant to an outer contour of the receiving space around the longitudinal axis. Depending in particular on the specific cross-sectional shape of the receiving space perpendicular to the longitudinal axis, the circumferential line can be circular, oval, or polygonal, particularly rectangular. In contrast to the nested or concentric arrangement of cooling channels described above, in the cooling jacket according to the invention, at least sections of the cooling channels are arranged at the same distance from the receiving space.The receiving chamber is open, particularly at one axial end, thus allowing the component to be cooled, especially the X-ray tube, to be received.

[0009] Along the outer contour of the receiving space, the cooling channels are arranged sequentially around the receiving space in the cross-sectional area. The previously typical nesting arrangement with respect to a distance direction, particularly radially away from the receiving space, is therefore no longer necessary. Each cooling channel thus does not extend over the entire or nearly the entire outer contour of the receiving space, but only over a respective portion of the outer contour. While in the case of the nested arrangement each cooling channel represents an independent annular space, in the cooling shell according to the invention all cooling channels can be arranged within a common annular space extending around the receiving space.

[0010] This allows for a saving of installation space in the direction radially away from the receiving space. Thus, the cooling shell according to the invention offers the advantage of being particularly thin or narrow around the receiving space. Due to this space saving, especially in the radial direction, less material and installation space are required for a shield that encloses the cooling shell or forms a layer of it. If, for example, a circular cross-section is assumed, a reduction in the radius of the cooling shell has a considerable impact on the material required for the shield, since the cylinder volume increases quadratically with the radius. Particularly given that relatively heavy and expensive tungsten and / or lead are typically used for shielding, this results in savings in both material costs and weight. The durability of the cooling shell is also positively affected.

[0011] A particularly preferred embodiment of the cooling jacket provides that the cooling channels overlap or are identical with respect to their extent along the distance direction to the receiving space. Two adjacent cooling channels thus preferably extend in the distance direction at least along a shared overlapping area, which in turn extends from a smaller inner distance to the receiving space to a larger outer distance. The adjacent cooling channels are then equidistant from the receiving space within the overlapping area. In other words, two adjacent cooling channels each extend in the distance direction from a smaller inner distance to the receiving space to a larger outer distance, wherein the outer distance of the first of the two cooling channels is greater than the inner distance and less than the outer distance of the second of the two cooling channels.The area around the recording space, extending from the inner distance of the second cooling channel to the outer distance of the first cooling channel, can be understood as the overlap area.

[0012] The distance direction can, for example, run along the radial direction if the cross-section of the recording space is circular. Additionally or alternatively, it can run perpendicular to the outer surface of the recording space or perpendicular to the outer contour of the recording space. In particular, if the recording space has a rectangular cross-section, the distance direction can be a surface normal to one of the outer surfaces of the recording space.

[0013] The receiving chamber preferably has the geometric shape of a right circular cylinder or a right prism, particularly with a rectangle or a square as its base. A circular or oval base for the receiving chamber makes the manufacturing of the cooling shell particularly easy. Furthermore, an X-ray tube can then be inserted into the receiving chamber with particular ease during assembly, especially by sliding it in along its longitudinal axis. To ensure simple assembly, it is preferred that the cross-section of the receiving chamber in a plane perpendicular to the longitudinal axis either remains constant along the longitudinal axis or that it tapers with increasing distance from the open end of the receiving chamber. Advantageously, the shape of the outer contour of the component to be cooled corresponds at least approximately, and preferably exactly, to an inner contour of the receiving chamber.In other words, the receiving space and the component to be cooled are preferably opposites.

[0014] The cooling shell itself, and in particular its outer contour, can have the geometric shape of a right circular cylinder or a right prism, at least in a section along the longitudinal axis in which the receiving chamber and the cooling channels also extend, wherein the receiving chamber and the cooling channels can each be cavities. In a particularly preferred embodiment, the cooling shell has the shape of a hollow cylinder, at least in a region along the longitudinal axis, wherein the receiving chamber forms the cavity and the central axis or axis of symmetry of the receiving chamber coincides with that of the cooling shell. In such a configuration, the cooling shell according to the invention can have an outer diameter of less than 30 mm or less than 25 mm. For example, it can have an outer diameter of 23 mm.

[0015] The cooling channels can extend in a straight line parallel to the longitudinal axis. This allows for a particularly simple design of the cooling shell as well as particularly simple manufacturing, for example by extrusion, especially since its cross-section perpendicular to the longitudinal axis can be constant along the longitudinal axis.

[0016] Alternatively, the cooling channels, particularly in a helical shape, can extend around the longitudinal axis. The cooling channels can thus extend helically around the receiving space along the longitudinal axis. The helical or screw shape increases the mechanical strength of the cooling shell, thereby requiring less material to achieve sufficiently high mechanical stability. Furthermore, this shape allows for an increase in the effective length over which the cooling channels extend along the receiving space. Regarding the helical or screw shape, it can be provided that a central axis of the respective cooling channel is formed by the line of motion of a point that moves, particularly at a constant speed, along the circumference of a circle perpendicular to and centered on the longitudinal axis, while the circle itself moves at a constant speed along the longitudinal axis.

[0017] The cooling channels can be integrated radially outside the receiving space into the cooling shell. For this purpose, a radially inwardly projecting wall structure can be provided on the inner side of an outer shell of the cooling shell, forming at least one lateral boundary of at least one of the cooling channels, with the outer shell forming a radially outer boundary of the cooling channels. By means of the wall structure projecting radially from the outer shell toward the receiving space, one or more cooling channels can be laterally bounded, i.e., circumferentially around the receiving space. The wall structure can be designed such that it separates several cooling channels from one another circumferentially or along the perimeter around the receiving space. The wall structure can have at least one rib-, wall-, or rib-like projection projecting inward from the outer shell, which forms the lateral boundary.

[0018] It is conceivable that at least one of the cooling channels is open radially on the inside if the component to be cooled is not located within the receiving space. This cooling channel then effectively extends into the receiving space. A radially inner boundary of one or at least some of the cooling channels can be formed, for example, by the component to be cooled and located within the receiving space. One or more of the cooling channels can then be radially inner bounded by the outer surface of the component to be cooled. For this to occur, the component to be cooled can, at least in some areas, fit snugly against the wall structure. The cooling shell and the component to be cooled can therefore be identical components, with the component to be cooled being positioned, particularly with a precise fit, within the receiving space.This has the advantage that the coolant of the radially open cooling channel(s) can flow directly along the surface of the component to be cooled, enabling particularly effective cooling. At least one sealant can be arranged between the wall structure and the component to be cooled to seal the respective cooling channel. The inwardly open wall structure can have at least one web-, wall-, or rib-like projection extending inwards from the outer shell, which, according to this embodiment, projects in particular perpendicularly from the outer shell.

[0019] The wall structure can form a radially inner boundary of at least one of the cooling channels. In this embodiment, the wall structure forms a structure that is at least partially closed radially inwards. In particular, the web-, wall-, or rib-like projections can converge radially inwards to also close off the respective cooling channel radially on the inside. The inwardly open wall structure can have several inwardly projecting, web-, wall-, or rib-like projections, which, according to this embodiment, are in particular designed to project obliquely from the outer shell or be curved and converge accordingly on the radial inside. The wall structure can run in a meandering or zigzag pattern around the receiving space in a cross-section perpendicular to the longitudinal axis and, together with the outer shell, completely enclose one or more of the cooling channels around the receiving space.In a cross-sectional plane perpendicular to the longitudinal axis, it can, for example, have a star-shaped structure, with the points of the star and the spaces between each pair of points forming the cooling channels. Two adjacent points of the star can then each define a cooling channel radially inwards and circumferentially on both sides. The outermost radial boundary can be formed by the outer shell.

[0020] Alternatively or additionally, it is conceivable that the wall structure extends from the outer shell to an inner shell of the cooling shell, with the inner shell forming the radially inner boundary of at least one of the cooling channels. One or more of the cooling channels are then radially outer bounded by the outer shell and radially inner bounded by the inner shell, and laterally bounded by the wall structure. The cooling shell can thus have at least one first cooling channel and at least one second cooling channel, wherein the at least one first cooling channel, particularly in a cross-section perpendicular to the longitudinal axis, is bounded by the outer shell and the wall structure, and optionally the inner shell, and wherein the at least one second cooling channel, particularly in a cross-section perpendicular to the longitudinal axis, is bounded by the inner shell and the wall structure, and optionally the outer shell.The outer shell, the wall structure, and optionally the inner shell, can each be a component or a section of the cooling shell. They are preferably an integral part of the cooling shell, which is particularly a single piece.

[0021] In a plane perpendicular to the longitudinal axis, all cooling channels can have the same cross-section. For example, the cooling channels could have a cross-section that is at least substantially rectangular or trapezoidal. They could extend, for instance, bounded by two wall elements of the wall structure, around the receiving space in a respective angular increment, particularly from the inner to the outer shell. Alternatively, the cross-sections of the cooling channels could differ. For example, at least one of the cooling channels could have a cross-section that tapers radially outwards, while at least one other cooling channel could have a cross-section that widens radially outwards.

[0022] In a particularly preferred embodiment, at least one supply channel and at least one discharge channel are provided as cooling channels, wherein the coolant can be supplied to the at least one supply channel via a supply interface, and wherein the at least one discharge channel is arranged downstream of the at least one supply channel, and wherein the coolant can be discharged from the at least one discharge channel via a discharge interface. The at least one supply channel allows the supply of cold coolant via the supply interface. Additionally, the at least one discharge channel allows the discharge of the heated coolant via the discharge interface. The coolant flow initially passes through the at least one supply channel and subsequently, i.e., downstream, through the at least one discharge channel.

[0023] Conveniently, the inlet and outlet interfaces can be arranged at a common axial end of the cooling jacket with respect to its longitudinal axis. This simplifies connecting the cooling channels to a coolant supply and outlet, as the integration of the cooling channels into a cooling circuit can occur at only one axial end of the cooling jacket. Preferably, the inlet and outlet interfaces are located at the axial end where the receiving chamber is open. The inlet and / or outlet interface can be or comprise a bore that branches downstream or upstream into one or more cooling channels. It is also conceivable that the inlet and / or outlet interface is or comprises an annular space, i.e., a ring-shaped recess at the axial end of the cooling jacket, that connects several cooling channels.

[0024] At the axial end featuring the inlet and / or outlet interface, the cooling jacket can have a coupling structure, in particular a flange, for non-destructively detachable coupling of the cooling jacket to a support, in particular the radiation generating device. The cooling jacket can be mounted to the support via the flange by means of one or more fasteners, in particular screws. It is also conceivable that the coupling structure has a thread by means of which the cooling jacket can be screwed to the support.

[0025] At the inlet and outlet interfaces, the cooling jacket can each have at least one sealing element, in particular a sealing ring, which is designed to seal the cooling channels at the respective interface to the holder in a liquid-tight manner when the cooling jacket is mounted on the bracket.

[0026] The at least one supply channel preferably opens into a coolant chamber, which, with respect to the longitudinal axis, is arranged at an axial end of the cooling shell, in particular opposite the supply and discharge interfaces, wherein the coolant can be discharged from the coolant chamber via the at least one discharge channel. The coolant chamber thus forms a connecting section between the at least one supply channel and the at least one discharge channel. The at least one supply channel and the at least one discharge channel can be fluidically connected via this chamber, in particular by reversing the flow direction of the coolant. This results in a coolant flow from the supply interface at the first axial end of the cooling shell through the at least one supply channel into the coolant chamber at the second axial end of the cooling shell.There, the coolant flow direction is reversed, and the coolant flows back in the opposite direction through at least one discharge channel to the first axial end of the cooling shell, where it can be discharged from the cooling shell through the discharge interface. Overall, this allows for an advantageous coolant flow that requires a connection to a coolant supply and discharge system at only one axial end.

[0027] The coolant chamber can be axially connected to a head region of the receiving space. With respect to a state in which the component to be cooled is received in the receiving space, a head section of the component to be cooled, in particular a target section, is at least partially arranged in the head region, which forms an axial end of the receiving space. The head region can taper along the longitudinal axis, in particular hemispherically. The at least one feed channel can also taper towards the coolant chamber along its longitudinal axis and / or be curved towards the longitudinal axis in the area opening into the coolant chamber.

[0028] Preferably, the coolant chamber is designed such that the coolant flowing into the cooling chamber through the supply channel(s) flows specifically around or along the head section of the component held in the receiving chamber. This allows the head section to be cooled particularly effectively by the cooling fluid flowing into the cooling chamber.

[0029] The coolant chamber can extend across the entire cross-section of the cooling shell, perpendicular to its longitudinal axis, possibly excluding the outer shell. Along the longitudinal axis, the coolant chamber can extend from the head region of the receiving space to the axial end of the cooling shell where it is closed. Radially, the coolant chamber can be bounded by the outer shell. Radially, the coolant chamber can be bounded, at least partially, by the inner shell. It is also conceivable that the axial end of the cooling shell, which binds the coolant chamber, is plate-shaped, particularly flat, or curved, particularly hemispherical.

[0030] In particular, if the supply channels, as described above, preferably run in a helical shape, winding around the longitudinal axis, then a vortex- or tornado-like flow pattern of the coolant can be generated in the coolant chamber at the head section of the component to be cooled. Thus, a rotating flow pattern can be created, through which the head section of the component, which requires increased cooling, is surrounded and can therefore be cooled particularly effectively.

[0031] In principle, the at least one supply channel and the at least one discharge channel can be arranged around the receiving chamber in any order. Preferably, however, the at least one supply channel and the at least one discharge channel are arranged alternately around the receiving chamber, particularly with regard to the star shape of the wall structure mentioned above. This results in a symmetrical distribution of the supply and discharge channels and consequently symmetrical cooling of the component to be cooled. A uniform distribution of the supply and discharge channels around the receiving chamber is also preferred. This allows for particularly precise adjustment of the ratio of the coolant flows in the supply and discharge channels.

[0032] Preferably, the cooling jacket comprises several inlet channels and several outlet channels arranged alternately around the receiving chamber. The cooling jacket can have an identical number of inlet and outlet channels. For example, it can comprise 6 to 14, preferably 8 to 10, inlet and outlet channels. Their cross-section can remain constant over their entire length or taper downstream.

[0033] In an advantageous embodiment, the at least one supply channel, particularly in the radial direction, is arranged section by section closer to the receiving chamber than the at least one discharge channel. The coolant flowing through the supply channel is thus guided closer to the receiving chamber than the coolant flowing through the discharge channel. This allows for particularly effective cooling.

[0034] Advantageously, the at least one feed channel can taper outwards along the radial direction, while the at least one discharge channel widens outwards along the radial direction, which can be the case, in particular, with the aforementioned star-shaped wall structure. In other words, the at least one feed channel can taper away from the receiving space, while the at least one discharge channel widens away from the receiving space. The feed channels and the discharge channels thus each have at least a substantially triangular or trapezoidal shape, wherein a baseline of the triangular shape or the longer of the two baselines of the trapezoidal shape of the feed channels lies radially further inwards than a baseline of the triangular shape or the longer of the two baselines of the trapezoidal shape of the discharge channels.This offers the advantage that the at least one supply channel to the receiving chamber has a larger contact area than the at least one discharge channel, thus ensuring the most effective possible heat transfer from the receiving chamber to the still-cold coolant flowing through the supply channel. The cooling jacket preferably has several supply channels that extend together in a plane perpendicular to the longitudinal axis, at least approximately around the entire receiving chamber.

[0035] In one specific embodiment, the cooling jacket has several supply channels arranged side by side around the circumference of the receiving chamber, tapering radially outwards. In a cross-section perpendicular to the longitudinal axis, the supply channels form a star shape, with one of the discharge channels located between each pair of adjacent points of the star (i.e., between two supply channels). This discharge channel widens radially outwards. This ensures that the cold coolant in the supply channels is located close to the receiving chamber, while the heated coolant in the discharge channels is carried as far away from the receiving chamber as possible.

[0036] All cooling channels can have the same length and cross-section perpendicular to the longitudinal axis, so that no pressure differences arise between the cooling channels. If the cooling channels differ in length, the longer cooling channel(s) can have a larger cross-sectional area to compensate for the otherwise resulting pressure loss.

[0037] Preferably, the cooling shell is a component manufactured using additive manufacturing, particularly selective laser melting. Additive manufacturing is especially well-suited for realizing complexly shaped, e.g., coiled, cooling channels and, in particular, for their compact integration into the cooling shell. The entire cooling shell can then be manufactured as a single component, thus eliminating the need for joining processes. However, it is also conceivable that the cooling shell is constructed from several joined semi-finished products. For example, a semi-finished product, specifically comprising the receiving space, the cooling channels, and the coolant chamber, can be manufactured using additive manufacturing. Additionally, a flange, specifically comprising the inlet and outlet interfaces as well as the coupling structure, can be manufactured as a further semi-finished product using any other manufacturing process, such as extrusion or machining.The components can be joined together to form the cooling shell using common joining methods such as welding, soldering (especially brazing), or pressing. To achieve the highest possible quality, and especially a smooth, inner surface in the cooling channels, these can be smoothed mechanically, electromechanically, and / or chemically. Methods such as etching, electrical discharge machining (EDM), or passing or pressing a carrier medium containing abrasive particles or a polishing paste through the channel are conceivable for this purpose.

[0038] The cooling jacket is preferably made of metal. Preferably, a metal is used that does not contain any X-ray-activated chemical elements. To shield against X-rays, the cooling jacket can have or be surrounded by a tungsten and / or lead-containing layer on its radial outer surface. The axial end, where the recording chamber is closed, can be recessed with respect to this shielding to allow the unimpeded escape of X-rays from the recording chamber, particularly through the cooling chamber.

[0039] At least one flow control device can be provided in or on at least one of the cooling channels, by means of which the flow direction of the coolant flowing through the respective cooling channel can be varied over time, in particular to generate an oscillating flow pattern. This prevents a steady flow of the coolant in the respective cooling channel, i.e., a flow pattern that does not change over time, with the flow direction instead changing over time, particularly periodically. This has a positive effect on the cooling effect achievable by the cooling jacket. Steady coolant flows, i.e., those that remain constant over time, have the disadvantage that stationary low-pressure areas can form inside the cooling channels and / or in the coolant chamber.These are disadvantageous because the locally reduced pressure results in a lower boiling point of the coolant, causing it to boil faster and evaporate more easily in the low-pressure areas, thus reducing cooling capacity. Furthermore, the additives in the coolant form deposits in stationary low-pressure areas, which reduce heat transfer and impair cooling performance. By using at least one flow control device, it can be advantageously achieved that the flow direction of the coolant changes continuously, so that no or at least significantly fewer low-pressure areas form in the cooling channels or the coolant chamber.

[0040] Preferably, at least one flow control device is provided or arranged in or on several, in particular all, supply channels of the cooling jacket. The flow control device is particularly advantageous in the supply channels, as it allows the coolant flow to be influenced as it is guided along the component to be cooled, especially its head section.

[0041] The at least one flow control device can be arranged within a cooling channel. However, it can also be located outside the cooling channels, for example, upstream of the feed interface, so that one or more cooling channels, particularly feed channels, connect to the flow control device downstream. Furthermore, each flow control device can be provided as a single unit that can be mounted in the cooling jacket, preferably at the feed interface, as required. The at least one flow control device can therefore also be arranged, particularly directly, upstream of the respective cooling channel.

[0042] To keep the design of the cooling jacket as simple as possible, at least one flow control device can be provided at the feed interface. It is also conceivable that at least one flow control device is arranged in at least one of the feed channels between the feed interface and the coolant chamber, in particular directly in front of the coolant chamber.

[0043] The flow control device is particularly advantageous when the cooling channels extend helically around the receiving chamber. The vortex- or tornado-like flow pattern resulting from the helical shape of the cooling channels can be modified over time by one or more flow control devices, so that a precessing, vortex- or tornado-like flow pattern—in other words, a vortex with a moving center—is created at the head section of the component to be cooled. The head section is then particularly well supplied with coolant, thus preventing a stationary coolant flow.

[0044] At least one flow control device is preferably designed such that it has no moving parts, thus reducing the probability of failure and simplifying maintenance. In principle, all common active or passive fluidic oscillators, sometimes also referred to as pendulum nozzles, are suitable as flow control devices, including vortex throttles and vortex valves.

[0045] The flow control device, or at least one of the flow control devices, can preferably be or comprise a Coanda nozzle. The Coanda nozzle is based on the Coanda effect as its physical operating principle. This effect causes a fluid flow near a curved surface to move along or conform to that surface, thereby changing the flow direction. In the Coanda nozzle, the coolant flowing through it is divided. The Coanda nozzle has a suitable internal geometry, in particular at least one curved surface, such that a change in the direction in which the coolant exits is caused over time. Coanda nozzles are also frequently referred to as fluidic oscillators or pendulum nozzles. A self-excited oscillation forms inside the Coanda nozzle without the need for any moving components.Due to the Coanda effect, a jet flowing through a Coanda nozzle alternately adheres to several of its inner walls, with this periodic process causing a periodic oscillation of the flow pattern. Unlike other nozzles, the Coanda nozzle does not need to taper downstream. Instead, its cross-section can remain constant or even increase downstream.

[0046] In an advantageous embodiment, the at least one flow control device comprises an oscillation channel geometrically configured such that the flow direction of the coolant flowing through the oscillation channel is changed over time. The at least one flow control device also includes a bypass channel by means of which a portion of the coolant passing through the flow control device is diverted around the oscillation channel. The oscillation channel is thus configured such that its geometry causes a temporal change in the flow pattern of the coolant, particularly due to the Coanda effect just described. It therefore causes the actual change in flow. Preferably, it is configured to generate an oscillating flow pattern. This means that the flow direction of the coolant moves back and forth over time, particularly uniformly.By means of the bypass channel, which is designed in such a way that it does not change the flow pattern of the coolant flow passing through it, or changes it less than the oscillation channel, a pressure loss occurring at the flow control device can be effectively reduced.

[0047] In the flow control device, the coolant flow passing through it can be divided into the oscillation channel and the bypass channel, so that not the entire coolant flow is directed through the oscillation channel. In principle, the coolant can be divided arbitrarily between the bypass channel and the oscillation channel; however, it is advantageously provided that the smallest possible portion of the coolant flow, which nevertheless causes a sufficiently strong temporal variation in the coolant flow pattern, flows through the oscillation channel. The division of the coolant flow into the bypass channel and the oscillation channel is preferably carried out such that, on the one hand, a sufficiently high variability with respect to the flow pattern is generated, and on the other hand, the pressure drop across the flow control device is minimized.In this embodiment, the coolant flow is split before the oscillation channel and the bypass channel and then recombined after the oscillation channel and the bypass channel.

[0048] Regarding the design of the at least one flow control device, it can comprise an oscillation plate encompassing the oscillation channel and a bypass plate encompassing the bypass channel, with the oscillation plate and the bypass plate arranged one above the other. The at least one flow control device can therefore be simple and compact, in particular in a sandwich-like or stacked configuration. The plates can, in principle, be connected to one another in any way. Preferably, the channels in the respective plates are designed such that they are separated from one another, at least except for one or more local connection points.

[0049] In one conceivable embodiment, the at least one flow control device can have a separating plate arranged between the oscillation plate and the bypass plate, wherein the separating plate laterally delimits the oscillation channel and / or bypass channel. The oscillation channel and / or the bypass channel can then be laterally open, being at least partially delimited or separated from each other by the cover plate sandwiched between the oscillation plate and the bypass plate. This allows for simple fabrication of the channels in the plates, for example by milling. It is conceivable that the separating plate has at least locally isolated openings through which the oscillation channel and the bypass channel are connected to each other, particularly at their respective ends, along the flow direction.

[0050] Preferably, the at least one flow control device comprises a distributor plate with a distributor section for distributing the coolant flowing into the flow control device into the oscillation channel and the bypass channel, wherein the oscillation plate and the bypass plate are arranged on the distributor plate. The distribution of the coolant flow to the oscillation channel and bypass channel can be achieved by means of the distributor plate. The distributor section of the distributor plate can be designed as at least one opening in the distributor plate that fluidically connects the oscillation channel and the bypass channel. The distributor section thus forms a branching point for the coolant flow, so that it is divided into a portion flowing through the oscillation channel and a portion flowing through the bypass channel.The distributor section can be connected to an inlet channel through which the cooling fluid flows into the flow control device. The distributor section then branches into a first channel leading to the oscillation channel and a second channel leading to the bypass channel. The distribution of the coolant flow can be fixed by the geometry of the distributor plate or the distributor section, for example, based on the cross-sections of the first and second channels. Alternatively, the distribution of the coolant flow can be selectively adjusted by means of an actuator, whereby the first and / or the second channel can be opened and closed, particularly continuously, by means of the actuator. The compact and simple, sandwich-like design is retained even when the distributor plate is used.

[0051] The cooling channel, or at least one of the cooling channels with the at least one flow control device, can branch downstream into at least two or more cooling channels. This allows a flow pattern that changes over time to be generated in multiple cooling channels using a single flow control device. In principle, a cooling channel with a flow control device can branch downstream into any number of additional cooling channels. By appropriately selecting the lengths of the cooling channels between their respective flow control devices and the coolant chamber, different flow patterns can be generated within the coolant chamber. Specifically, a phase shift can be set for the coolant flows in the cooling channels, since the time required for the coolant to pass through a cooling channel increases with increasing channel length.Consequently, the wavefront or phase of the coolant flow differs at the end of the cooling channels. If the cooling channels are of different lengths, they can also differ in diameter to avoid pressure differences within the cooling channels.

[0052] Furthermore, the invention relates to a radiation generating device comprising a component to be cooled and a cooling shell, wherein the cooling shell extends along the longitudinal axis and has within it a receiving space, open at least on one side and also extending along the longitudinal axis, in which the component to be cooled is received. The cooling shell has several cooling channels extending along the longitudinal axis for guiding a coolant, which are arranged radially outside and around the receiving space. The radiation generating device according to the invention thus comprises a cooling shell as described above and a component to be cooled received in its receiving space. All features, advantages, and aspects described in connection with the cooling shell according to the invention are equally applicable to the radiation generating device according to the invention, and vice versa.

[0053] In principle, any component that can be accommodated within the cooling chamber of the invention can be cooled using the cooling shell according to the invention. However, the cooling shell according to the invention demonstrates its advantages to a particularly high degree in the context of radiation generation, especially the generation of X-rays. Thanks to the cooling shell according to the invention, the radiation generation device can incorporate a very powerful X-ray tube as the component to be cooled. Therefore, the radiation generation device can, for example, be a medical device for medical examination and / or treatment, particularly for the focused irradiation of a patient's tissue. It is also conceivable that the radiation generation device is a device for examining, especially by fluoroscopy, objects, such as containers.

[0054] In one embodiment, at least one supply channel and at least one discharge channel can be provided as the cooling channels, wherein the coolant can be supplied to the at least one supply channel via a supply interface, wherein the at least one discharge channel is arranged downstream with respect to the at least one supply channel, wherein the coolant can be discharged from the at least one discharge channel via a discharge interface, wherein the at least one supply channel opens into a coolant chamber which, with respect to the longitudinal axis, is arranged at an axial end of the cooling shell, in particular opposite the supply interface and the discharge interface, wherein the coolant can be discharged from the coolant chamber via the at least one discharge channel.It is particularly preferred that the component to be cooled has at one axial end a head section that requires enhanced cooling compared to the remaining area of ​​the component. This head section comprises, in particular, a target of the radiation generation device onto which an electron beam generated by the radiation generation device is directed. The head section requiring enhanced cooling can be cooled at least primarily by the coolant flowing through the coolant chamber of the cooling jacket. The component to be cooled can therefore be an X-ray tube. Its head section, or its tip with the target, can be arranged, at least partially, within the coolant chamber to achieve a flow of coolant, particularly tangential flow. This allows for particularly effective cooling, especially due to the longer residence time of the coolant on the surface of the head section.

[0055] In an advantageous embodiment, the at least one supply channel of the cooling jacket can taper at its end opening into the coolant chamber, and / or a nozzle can be arranged in the end of the supply channel opening into the coolant chamber, such that the coolant flowing from the supply channel into the coolant chamber is directed specifically to a section of the coolant chamber in which the head section requiring enhanced cooling is located. The coolant flowing into the coolant chamber can be directed to or directly onto the head section of the component to be cooled, which is located at least partially within the coolant chamber. Specifically, the coolant flowing into the coolant chamber can be guided along a surface of the head section of the component to be cooled, so that the coolant flows directly around it.

[0056] Further advantages and details of the invention are described below with reference to exemplary embodiments and the figures. The latter are schematic representations of the principle and show: Fig. 1 Perspective, cutaway view of an embodiment of a cooling shell according to the invention, Fig. 2 Sectional view through the cooling shell of the Fig. 1 , where the intersection surface in Fig. 1 indicated by II - II, Fig. 3 Sectional view through the cooling shell of the Fig. 1 , where the intersection surface in Fig. 1 Figure 4, indicated by III - III, is a simplified sectional view of the Fig. 2 with a representation of the coolant flow direction, Fig. 5 perspective, cutaway view of a section of the flow control device of the Fig. 4 , Fig. 6Exploded view of the flow control device of the Figuren 4 und 5 , and Fig. 7 exploded view of an embodiment of a radiation generating device according to the invention comprising the cooling shell according to Fig. 1 .

[0057] Fig. 1 Figure 1 shows an embodiment of a cooling shell 1 according to the invention for cooling a component 2 to be cooled, wherein the cooling shell 1 extends along a longitudinal axis 3. Fig. 1 No component 2 requiring cooling is shown. However, the Fig. 2 and 3 Sectional views of cooling shell 1 of the Fig. 1 , in which a component 2 to be cooled, which in this case is an X-ray tube 12, is indicated by a dashed line. Fig. 2 shows a sectional view of the cooling shell 1 along the longitudinal axis 3 and Fig. 3 shows a sectional view of the cooling shell 1 perpendicular to the longitudinal axis 3.

[0058] The cooling shell 1 has an internal receiving chamber 4, open on one side and extending along the longitudinal axis 3, for receiving the component 2 to be cooled. The component 2 can be inserted into the receiving chamber 4 through an opening 7 at the lower axial end 8 of the cooling shell. To cool the component 2, the cooling shell 1 includes several cooling channels 5 extending radially outside the receiving chamber 4 along the longitudinal axis 3, which are designed to carry a coolant. For easier orientation, a radial direction 6 is introduced, pointing perpendicularly away from the longitudinal axis 3. The design of the cooling shell 1 offers several advantages: One advantage is its compact and space-saving construction.The receiving chamber 4 and the area of ​​the cooling shell 1 around the receiving chamber 4, or a tube 41 of the cooling shell 1, are cylindrical in this case, with the longitudinal axis 3 forming the central axis of the tube 41. As shown in particular . Fig. 3 As shown, all cooling channels 5 are arranged around the intake chamber 4. In other words, all cooling channels 5 are in the Fig. 3 plane shown perpendicular to the longitudinal axis 3 along a circumferential line 9 (in Fig. 3 (shown with dashed lines) are arranged side by side, with the circumferential line 9 running parallel to an outer contour of the receiving space 4 around the longitudinal axis 3. This eliminates the need for the otherwise frequently used "nesting" of the cooling channels 5 in the radial direction 6, where each cooling channel extends over a different radius range. In this case, all cooling channels 5 are arranged within a common annular space 10 surrounding the receiving space 4 (see Fig. 2 and 3). They overlap along a spacing direction, in this case the radial direction 6, and enable a significant saving of installation space in radial direction 6 as well as a compact design of the cooling shell 1.

[0059] If an X-ray tube is used as the component 2 to be cooled, a shield for its X-ray radiation can be provided around the cooling shell 1. Such a shield is usually made of lead or tungsten and is therefore heavy and expensive. The space savings in the radial direction 6 make it possible to reduce the size of such a shield while still achieving sufficient shielding effectiveness, thus saving weight and material costs. In this case, the cooling shell 1 has a comparatively small outer diameter of 23 mm in the area around the imaging chamber 4. In other designs, however, this diameter can also be between 20 mm and 35 mm.

[0060] Another advantage of the cooling shell 1 is the particularly effective cooling of the component 2 contained in the receiving chamber 4 and to be cooled. For this purpose, the cooling shell 1 has several cooling channels 5 in Fig. 1 Flow control devices 11 (not shown in detail) are used to change the flow direction of the coolant flowing through the respective cooling channel 5 over time. This allows flow patterns to be generated in which the flow directions oscillate over time. A steady coolant flow can thus be effectively avoided by means of the flow control devices 11. This is advantageous because a steady flow can result in local low-pressure areas that negatively affect cooling performance, as the coolant boils and evaporates more quickly there due to the reduced pressure. The flow control devices 11 change the coolant flow in the respective cooling channel 5 over time, so that no or significantly fewer low-pressure areas occur. The design and function of the flow control devices 11 will be described later with reference to the Figuren 4 - 6 described in more detail.

[0061] The improved cooling performance of the cooling shell 1 makes it possible to cool four high-performance components in the imaging chamber, which are characterized by high heat generation. The cooling shell 1 is therefore particularly suitable for cooling high-performance X-ray tubes 12, which, in particular, have a target 14 at their tip or head section 13 for radiation generation, which heats up considerably during operation.

[0062] The cooling shell 1 comprises two types of cooling channels 5: supply channels 15 and discharge channels 16. These differ in the direction of their coolant flow along the longitudinal axis 3. While the coolant in the supply channels 15 is guided from the lower axial end 8 to an upper axial end 17 of the cooling shell 1, in the discharge channels 16, which are arranged downstream of the supply channels 15, it is guided back to the lower axial end 8. The flow direction of the coolant is therefore opposite in the supply and discharge channels 15 and 16.

[0063] Coolant can be supplied to the supply channels 15 via a supply interface 18, while the coolant can be discharged from the discharge channels 16 via a discharge interface 19. Both the supply interface 18 and the discharge interface 19 are located at the lower axial end 8 of the cooling shell 1. In this design, they are formed by or integrated into a flange 20, from which the tube 41 extends and by means of which the cooling shell 1 can be mounted on a bracket. This allows both interfaces to be connected to a coolant supply or integrated into a cooling circuit particularly easily.

[0064] All cooling channels 5 are radially bounded on the outside by an outer shell 21 of the cooling shell 1. Furthermore, the cooling shell 1 has a wall structure 22 that projects radially inwards from the outer shell 21, i.e., towards the receiving space 4, and borders all cooling channels 5 laterally, i.e., along the circumferential line 9 (see Fig. 3 ), limited. While the wall structure 22 also radially limits the discharge channels 16 on the inside, so that their cross-section is completely enclosed by the outer shell 21 and the wall structure 22, the supply channels 15 are open radially on the inside, i.e., towards the receiving space 4. A radial inner limitation of the supply channels 15 only exists when the component 2 to be cooled is received in the receiving space 4. The limitation is then formed by an outer surface 23 of the component 2 to be cooled, which abuts the wall structure 22, in particular with a precise fit, and optionally at least one sealing element is provided for sealing the cooling channels 5. Specifically, in the present embodiment, the size of the receiving space 4 is selected such that the component 2 to be cooled can be received precisely in it, so that its outer surface 23 abuts the wall structure 22 exactly.This design allows the coolant, guided in the supply channels 15, to flow directly along the outer surface 23 of the component to be cooled, thus ensuring effective cooling. It is also conceivable that the supply channels 15 are not radially bounded on their inner side by the outer surface 23 of the component 2 to be cooled. For example, the cooling shell 1 can have an inner shell that, on the one hand, bounds the receiving space 4 and, on the other hand, radially bounds the supply channels 15 and / or the discharge channels 16 on their inner side. The wall structure 22 can then extend between the outer shell 21 and the inner shell.

[0065] In particular Fig. 3 Figure 1 shows that the supply channels 15 and the discharge channels 16 are arranged alternately around the receiving chamber 4. This enables symmetrical cooling of the component 2 contained in the receiving chamber 4 and to be cooled. In this design, the supply channels 15 taper outwards along the radial direction 6, while the discharge channels 16 widen outwards along the radial direction 6. The supply channels 15 thus form a kind of star-shaped cross-section perpendicular to the longitudinal axis 3, with one of the return channels 16 arranged between each pair of adjacent points of this star. This geometry offers the advantage that the supply channels 15 have a particularly large contact area with the receiving chamber 4 for heat transfer. As a result, a particularly large portion of the outer surface 23 of the component 2 to be cooled can be directly exposed to the coolant, which is still cold in the supply channels 15.In contrast, the discharge channels 16 are completely separated from the receiving chamber 4 and widen radially outwards, so that the majority of the warm coolant flowing in the discharge channels 16 is as far away as possible from the receiving chamber 4. Overall, this results in a particularly advantageous coolant flow arrangement. It is also conceivable that the supply channels 15 and the discharge channels 16 are not arranged alternately around the receiving chamber 4.

[0066] How Fig. 2 As shown, the cooling shell 1 has a coolant chamber 24. This is located at the upper axial end 17 of the cooling shell 1, i.e., at the axial end opposite the inlet interface 18 and the outlet interface 19. It is bounded radially on the outside by the outer shell 21 and along the longitudinal axis 3 by a thin cover plate 25, which is particularly transparent to X-rays. The inlet channels 15 open into the coolant chamber 24 along the longitudinal axis 3, and the coolant can be discharged from the coolant chamber 24 via the outlet channels 16. The coolant chamber 24 thus connects the inlet channels 15 with the outlet channels 16, whereby the flow direction of the coolant, indicated by the arrows 26, reverses in the coolant chamber 24. During operation, the coolant flows through the feed interface 18 at the lower axial end 8 into the feed channels 15 and through these into the coolant chamber 24 at the upper axial end 17.There it is deflected in the opposite direction and returns via the discharge channels 16 to the lower axial end 8, where it can exit the cooling shell 1 again via the discharge interface 19.

[0067] The wall structure 22 projects further radially inwards in the area of ​​the coolant chamber 24, i.e., at the axial end of the receiving space 4 opposite the opening 7 of the receiving space 4, than in the rest of the area around the receiving space 4. In other words, the receiving space 4 tapers in a head region where the head section 13 of the component 2 to be cooled is located when it is received in the receiving space 4. In the head region, the wall structure 22 follows the surface shape of the head section 13, which is hemispherical in this case, so that the coolant is guided particularly well along the surface of the head section 13. This allows the head section 13 to be cooled very effectively. In the head region, the wall structure 22 is also designed such that the cross-section of the supply channels 15 tapers along the longitudinal axis 3, which increases the velocity of the coolant flow and enhances the cooling effect.

[0068] How Fig. 1 and 2As shown, the cooling channels 5 are helically wound around the longitudinal axis 3, which gives the tube 41 high mechanical stability, allowing the outer shell 21 and the wall structure 22 to have a particularly thin wall thickness. Furthermore, the helical supply channels 15 ensure that a vortex-like or swirling or tornado-like flow pattern of the coolant is created at the head section 13 of the component 2, which is housed in the receiving chamber 4 and is to be cooled, i.e., in the area of ​​the coolant chamber 24. This increases the cooling capacity, particularly due to the associated increase in the flow velocity of the coolant. The flow control devices 11 mentioned above also ensure that a stationary flow does not occur, but rather that the vortex-like flow or swirl moves, and in particular precesses, across the surface of the head section 13 of the component 2 to be cooled.

[0069] It is also conceivable that the cooling channels 5 run in a straight line parallel to the longitudinal axis 3. This ensures that the cross-section of the cooling shell 1, particularly in the area of ​​the receiving space 4, remains constant, making the cooling shell 1 particularly easy and cost-effective to manufacture, for example, by extrusion. In this case, the cooling shell 1 is a single-piece component manufactured from metal using additive manufacturing, specifically selective laser sintering. To ensure a particularly good surface quality in the cooling channels 5 and thus the most friction-free and therefore loss-free coolant flow possible, the cooling channels 5 are post-processed. For this purpose, a liquid carrier medium containing abrasive particles was passed through the cooling channels, reducing surface roughness inside the cooling channels 5. Post-processing by etching or electrical discharge machining (EDM) would also be conceivable.

[0070] The cooling shell 1 can also be assembled from several prefabricated semi-finished products. For example, the tube 41 and the flange 20 can be manufactured separately and joined or connected to each other by pressing, welding, soldering or the like.

[0071] According to the preceding description, the cooling shell 1 includes a flow control device 11 in several cooling channels 5, the operating principle and effect of which can be seen in the simplified sectional view of the Fig. 4 This becomes clear. This shows the cross-sectional view of the Fig. 2 with one of the flow control devices 11 in the form of a Coanda nozzle 27 in one of the cooling channels 5. The Coanda nozzle 27 is designed to effect a temporal change in the coolant flow based on the Coanda effect. Its construction is shown in the schematic diagrams of the Fig. 5 and 6This is shown in more detail below. The Coanda effect causes a flow, in this case the coolant flow, to move not linearly near a curved surface, but along the surface. This results in a change in the flow direction over time. Overall, the Coanda nozzle 27, through its specific geometric design, causes a change in the flow direction of the coolant over time, without requiring any moving, and especially not controlled, components. Fig. 4 The changing flow direction of the coolant, indicated by arrows 28 and 28', is shown by the Coanda nozzle 27. Arrow 28 indicates the flow direction at a first time point, and the dashed arrows 28' at a second time point. The time-changing flow pattern causes the vortex-like coolant flow (indicated by the cone 29) generated by the coiled supply channels 15 in the coolant chamber 24 to move, and in particular precess, on the surface of the head section 13 of the component 2 to be cooled.

[0072] Each of the flow control devices 11 can be integrated into the flange 20 of the cooling jacket 1 or at another location in one of the cooling channels 5. The flow control devices 11 are specifically inserted or mounted in corresponding recesses of the flange 20. If the cooling jacket 1 is additively manufactured as a single component, all flow control devices 11 can be directly integrated into the cooling jacket 1.

[0073] The Figuren 5 and 6 They exemplify the block- and sandwich-like structure of the flow control device 11 of the Fig. 4 in the form of a Coanda nozzle 27, wherein Fig. 5 Figure 11 shows only the lower part of the flow control device 11. The flow control device 11 comprises an oscillation plate 32 with an oscillation channel 31, which is geometrically designed such that the flow direction of the coolant exiting the oscillation channel 31 changes over time. The oscillation channel 32 utilizes the Coanda effect. The flow control device 11 also includes a bypass plate 34 with a bypass channel 33, by means of which a portion of the coolant passing through the flow control device 11 bypasses the oscillation channel 31. Additionally, the flow control device 11 includes a distributor plate 35 with a distributor section 43 for distributing the coolant entering the flow control device 11 via a coolant inlet 30 to the oscillation channel 31 and the bypass channel 33.It is evident that a larger proportion of the coolant entering the flow control device 11 is directed into the bypass channel 33, while only a small proportion, sufficient to generate a time-varying flow pattern, is directed into the oscillation channel 31. This reduces the pressure loss occurring at the flow control device 11 compared to when the entire coolant flow was directed into the oscillation channel 31.

[0074] To at least partially delimit the oscillation channel 31 and the bypass channel 33 laterally, the flow control device 11 also includes a partition plate 44. This plate comprises several openings 36 that connect the oscillation channel 31 and the bypass channel 33 both before and after their respective inlets and outlets. The coolant thus enters the oscillation channel 31 and the bypass channel 33 via the distributor plate 35 through the coolant inlet 30. Within the oscillation channel 31, the flow pattern of the coolant is altered over time, causing the coolant to flow downstream alternately through one of the two openings 36 in the partition plate 44 into the area downstream of the bypass channel 33 and exit the flow control device 11 together with the coolant flow passing through the bypass channel 33. All the panels are arranged on top of each other, forming a compact and simple, sandwich-like or stacked structure.The flow control device 11 is made of metal in this case. In principle, however, it can be made of any material which preferably has high resistance to wear and sufficiently high thermal resistance.

[0075] With regard to the exemplary embodiment of the Fig. 1 The flow control devices 11 are provided at the feed interface 18. However, they can, in principle, be located in the feed channels 15 at any position between the feed interface 18 and the coolant chamber 24, including directly upstream of the coolant chamber 24. It is conceivable that the cooling channel(s) 5 with a flow control device 11 branch(es) downstream into several cooling channels 5, so that the flow direction of the coolant changes over time in several cooling channels 5. By selectively choosing different values ​​for the lengths of the individual cooling channels 5 between the flow control device 11 and the coolant chamber 24, it is possible to adjust the coolant flows of the individual cooling channels 5 so that they exhibit a desired phase shift upon reaching the coolant chamber 24.The flow pattern of the coolant resulting in the coolant chamber 24 can therefore also be specified via the lengths of the individual cooling channels 5.

[0076] Overall, the cooling shell 1 enables particularly effective and space-saving cooling of the component 2 to be cooled, whereby it can be specifically adjusted to the respective component 2 to be cooled by means of several parameters that can be changed during the manufacturing of the cooling shell 1 in order to achieve the best possible cooling.

[0077] Fig. 7 Figure 1 shows an exploded view of a high-performance radiation generating unit 37, for example, for X-ray inspection of containers. It is also conceivable that a comparable radiation generating unit 37 could be used for medical treatment, in particular irradiation, of patients. The radiation generating unit 37 comprises an accelerator structure 42 with a high-performance X-ray tube 12 and the cooling jacket 1 of the exemplary embodiment shown in Figure 1. Fig. 1 The cooling sleeve 1 serves to cool the X-ray tube 12. The cooling sleeve 1 is mounted to a bracket 39 of the accelerator structure 42, which is rigidly connected to the X-ray tube 12, by means of a coupling structure on the flange 20 using several fastening elements 38, in this case screws. In this way, the cooling sleeve 1 can be easily removed for maintenance of the X-ray tube 12, in particular the target 14. In addition, several sealing rings 40 are provided which, in the assembled state, seal the feed interface 18 and the discharge interface 19 between the cooling sleeve 1 and the bracket 39 to the outside.

[0078] As already shown from the Fig. 2 As described, the X-ray tube 12 has a target 14 at its head section 13, onto which an electron beam is directed to generate X-rays. A large amount of heat is released at the head section 13 during this process. In the assembled state, this is also the case in Fig. 7 The head section 13 of the X-ray tube 12 is arranged in the head region of the recording chamber 4 of the cooling shell 1, which forms an axial end of the recording chamber 4. The Fig. 7 The coolant flowing from the supply channels 15 (not shown) into the coolant chamber 24 of the cooling shell 1 (also not shown) is guided along the surface of the head section 13, thus cooling the latter particularly effectively. For this purpose, the supply channels 15 taper at their ends opening into the coolant chamber 24 such that the coolant flowing from the supply channels 15 into the coolant chamber 24 is directed specifically to a section of the coolant chamber 24 in which the head section 13 of the X-ray tube 12 is located. The high-performance X-ray tube 12 can thus be cooled very effectively despite the particularly compact design of the cooling shell 1.

[0079] Regardless of the grammatical gender of a particular term, persons with male, female or other gender identities are included.

Claims

1. Cooling shell (1) for cooling a component (2) of a radiation generating device (37), wherein the cooling shell (1) extends along a longitudinal axis (3) and has inside a receiving space (4) which is open at least on one side and also extends along the longitudinal axis (3) for receiving the component (2) to be cooled, wherein the cooling shell (1) has several cooling channels (5) which are provided for guiding a coolant and extend along the longitudinal axis (3) and are arranged radially outside the receiving space (4) and distributed around the receiving space (4).

2. Cooling cover (1) according to claim 1, characterized by the fact that the cooling channels (5) overlap or are identical with respect to their extent along a distance direction to the receiving space (4).

3. Cooling cover (1) according to claim 1 or 2, characterized by the fact thatthe receiving space (4) has the geometric shape of a right circular cylinder or a right prism, in particular with a rectangle or a square as its base.

4. Cooling shell (1) according to one of the preceding claims, characterized by the fact that the cooling channels (5) extend in a straight line and parallel to the longitudinal axis (3) or, in particular, in a helical shape, wound around the longitudinal axis (3).

5. Cooling shell (1) according to one of the preceding claims, characterized by the fact that a radially inwardly projecting wall structure (22) is provided on the radial inside of an outer shell (21) of the cooling shell (1), which forms at least a lateral boundary and / or at least a radially inner boundary of at least one of the cooling channels (5), wherein the outer shell (21) forms a radially outer boundary of the cooling channels (5).

6. Cooling shell (1) according to one of the preceding claims, characterized by the fact thatat least one supply channel (15) and at least one discharge channel (16) are provided as the cooling channels (5), wherein the coolant can be supplied to the at least one supply channel (15) via a supply interface (18), wherein the at least one discharge channel (16) is arranged downstream of the at least one supply channel (15), wherein the coolant can be discharged from the at least one discharge channel (16) via a discharge interface (19).

7. Cooling cover (1) according to claim 6, characterized by the fact that the feed interface (18) and the discharge interface (19) are arranged at a common axial end (8) of the cooling shell (1) with respect to the longitudinal axis (3).

8. Cooling cover (1) according to one of claims 6 or 7, characterized by the fact thatthe at least one supply channel (15) opens into a coolant chamber (24) which, with respect to the longitudinal axis (3), is arranged at an axial end (17) of the cooling shell (1), in particular opposite the supply interface (18) and the discharge interface (19), wherein the coolant can be discharged from the coolant chamber (24) via the at least one discharge channel (16).

9. Cooling cover (1) according to claims 6 to 8, characterized by the fact that the at least one feed channel (15) and the at least one discharge channel (16) are arranged alternately around the receiving chamber (4).

10. Cooling shell (1) according to one of claims 6 to 9, characterized by the fact that the at least one feed channel (15) tapers outwards along the radial direction (6), while the at least one discharge channel (16) widens outwards along the radial direction.

11. Cooling shell (1) according to one of the preceding claims, characterized by the fact thatThis is a component manufactured using additive manufacturing, in particular selective laser melting.

12. Cooling shell (1) according to one of the preceding claims, characterized by the fact that in or on at least one of the cooling channels (5) at least one flow control device (11) is provided, by means of which the direction of flow of the coolant flowing through the respective cooling channel (5) can be changed over time, in particular to generate an oscillating flow pattern.

13. Radiation generating device (37) with a component (2) to be cooled and a cooling shell (1), wherein the cooling shell (1) extends along the longitudinal axis (3) and has inside it a receiving space (4) which is open at least on one side and also extends along the longitudinal axis (3) and in which the component (2) to be cooled is received, wherein the cooling shell (1) has several cooling channels (5) which are provided for guiding a coolant and extend along the longitudinal axis (3) and are arranged radially outside the receiving space (4) and distributed around the receiving space (4).

14. Radiation generating device (37) according to claim 13, characterized by the fact thatAt least one supply channel (15) and at least one discharge channel (16) are provided as the cooling channels (5), wherein the coolant can be supplied to the at least one supply channel (15) via a supply interface (18), wherein the at least one discharge channel (16) is arranged downstream with respect to the at least one supply channel (15), wherein the coolant can be discharged from the at least one discharge channel (16) via a discharge interface (19), wherein the at least one supply channel (15) opens into a coolant chamber (24) which, with respect to the longitudinal axis (3), is arranged at an axial end (17) of the cooling shell (1), wherein the coolant can be discharged from the coolant chamber (24) via the at least one discharge channel (16), wherein the component (2) to be cooled has at an axial end a head section (13) which is to be cooled more intensively with respect to the remaining area of ​​the component (2) to be cooled, comprising in particular a target (14) of the radiation generation device. (37)upon which an electron beam generated by means of the radiation generation device (37) strikes, wherein the head section (13) which is to be cooled more intensively can be cooled at least mainly by means of the coolant flowing through the coolant chamber (24) of the cooling shell (1).

15. Radiation generating device (37) according to claim 14, characterized by the fact that the at least one supply channel (15) of the cooling jacket (1) tapers at its end opening into the coolant chamber (24) in such a way and / or a nozzle is arranged in the end of the supply channel (15) opening into the coolant chamber (24) in such a way that the cooling fluid flowing from the supply channel (15) into the coolant chamber (24) is directed to a section of the coolant chamber (24) in which the head section (13) to be cooled more intensively is located.

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