Valve with axial angle compensation

Abstract

A valve (500) is described, preferably in a high-performance chromatography system (10), for separating components of a sample liquid introduced in a mobile phase. The valve (500) has a first valve element (210) and a second valve element (220), wherein by a relative movement of the first valve element (210) relative to the second valve element (220) an active surface of the first valve element (210) is connected with an active surface (605) of the second valve element (220) and a flow path (1030A, 1050A, 1070A, 1030B) can be established or interrupted. The second valve element (220) has a resilient region (1110) to compensate an axial angle between the first valve element (210) and the second valve element (220) so that the first and second active surfaces (605) can be parallel to each other. This allows to compensate an axial angle between the first and second valve elements, i.e. for example between a rotor and a stator, whereby the fluid tightness and / or the long-term service life of the valve can be positively influenced.

Description

Technical Field

[0001] This invention relates to a valve, particularly a valve for HPLC. Background Technology

[0002] In high-performance liquid chromatography (HPLC), liquids must be delivered at typically very tightly controlled flow rates (e.g., in the nanoliter to milliliter range per minute) and at high pressures (typically 20–100 MPa, 200–1000 bar, and even higher up to, for example, 200 MPa, 2000 bar) where the compressibility of the liquid is perceptible. Regarding liquid separation in an HPLC system, during operation, a mobile phase containing the sample liquid, including the components to be separated, is driven through a stationary phase (such as a chromatographic column) to separate the different components of the sample. The composition of the mobile phase can here remain constant over time (isocratic mode) or can change over time (e.g., in so-called gradient mode).

[0003] A problem in many HPLC applications can be the fluid sealing of the flow path, especially under high pressure in the mobile phase. This is particularly relevant where the flow path can be separated at least temporarily, such as in valves or so-called fittings used for mechanical connections between different fluid elements.

[0004] Valves are commonly used in HPLC applications to establish or interrupt one or more flow paths. Rotary valves are often suitable for this purpose, where the relative movement of the rotor relative to the stator affects the corresponding flow path. In particular, the sealing performance and service life of such shear valves are critical, especially regarding axial misalignment between the rotor and stator. Summary of the Invention

[0005] The object of this invention is to improve the valve in terms of possible angular misalignment of the interacting elements, particularly for HPLC applications. This object is achieved by the features of the independent claims. Advantageous embodiments are mentioned in the dependent claims.

[0006] One embodiment relates to a valve, preferably for separating components of a sample liquid introduced in a mobile phase in a high performance chromatography system. The valve has a first valve element and a second valve element, wherein by a relative movement of the first valve element with respect to the second valve element an active surface of the first valve element is connected with an active surface of the second valve element and a flow path can be established or interrupted. The second valve element has a resilient region to compensate an axial angle between the first valve element and the second valve element so that the first active surface and the second active surface can be parallel to each other. This allows to compensate an axial angle between the first and the second valve element, i.e. for example between a rotor and a stator, whereby the fluid tightness and / or the long-term service life of the valve can be positively influenced. A parallel orientation of the opposing active surfaces of the valve elements enables a uniform or at least more uniform force distribution along the active surfaces, so that an increased mechanical load and in particular a higher wear between the valve elements can be avoided or at least reduced.

[0007] In one embodiment the second valve element has an outer region and an inner region. The inner region has the second active surface and the outer region is connected with the inner region via a resilient region, by which the inner region is resiliently moved with respect to the outer region. This structure allows a resilient relative movement between the inner region and the outer region and can in particular react to an axial misalignment between the first and the second valve element by this resilient relative movement.

[0008] In one embodiment the outer region is fixedly arranged with respect to the first valve element and the inner region is resiliently alignable with respect to the first valve element.

[0009] In one embodiment the resilient region has one or more connecting pieces, which are respectively connected on one side with the outer region and on the opposite side with the inner region, so that the inner region can be tilted with respect to the outer region.

[0010] In one embodiment the first valve element is a rotor and the second valve element is a stator, wherein the rotor is rotatable with respect to the stator.

[0011] One embodiment of the valve has a sealing structure, which is configured so that under the influence of a pressure of a fluid at least partially increases a volume of the sealing structure, whereby for fluid-tightly sealing the flow path the first valve element and the second valve element are pressed against each other.

[0012] In one embodiment the sealing structure has a region which is resiliently deformable like a hydraulic cushion, so that upon the first active surface and the second active surface being parallel to each other and being pressed against each other an axial angle between the first valve element and the second valve element causes a change in the thickness of the sealing structure.

[0013] In one embodiment, the valve has a flow element. The flow element has a flow path for transporting a flow phase. A sealing structure, which can preferably be a pressure structure, is connected or connectable with the flow phase in order to cause a fluidic seal of the flow path under the influence of the pressure of the flow phase. The sealing structure is configured such that, under the influence of the pressure of the flow phase, the volume of the sealing structure, preferably within the flow path of the sealing structure, is at least partially increased, and the at least partial volume increase causes a fluidic seal of the flow path.

[0014] The flow element preferably has an inlet port and an outlet port, wherein the flow path is fluidically connected or connectable with the inlet port and the outlet port.

[0015] The flow element according to the application allows a dynamic and / or adaptive fluidic seal of the flow path in that the flow phase to be fluidically sealed itself serves for the fluidic seal and enables or at least enhances the fluidic seal. A low pressure of the flow phase, which requires correspondingly low forces for fluidically sealing the flow phase, can cause a low sealing force for the fluidic seal. Conversely, a high pressure of the flow phase, which requires a high force of the flow phase for fluidically sealing, causes a high sealing force for the fluidic seal.

[0016] The flow element according to the application can adaptively and dynamically match the respective requirements in the sealing force required for ensuring a sufficient fluidic seal. This can avoid excessively high sealing forces, in particular when no sealing force at all is required for a sufficient fluidic seal, thus reducing the wear of the components to be sealed and / or prolonging the service life.

[0017] The flow element according to the application furthermore allows a static loading of the connection to be fluidically sealed only slightly, i.e. only with a small force, for example to mechanically secure the connection to be sealed (but for example without a fluidic seal here). The force required for the fluidic seal is then dynamically and adaptively supported by the flow element. This can be advantageous in particular in fluid connections in which, for example, two fluid components, such as a capillary and a device to which the capillary is to be connected, are mechanically coupled to one another and are to be fluidically connected. The flow element according to the application allows here that the connection is mechanically coupled first "hand-tight" (i.e. with a small force, such as a coupling or closure that can be achieved by hand, for example), i.e. for example screwed, whereby there is only a slight fluidic seal or even no fluidic seal at all. In operation, i.e. when the flow phase is applied, the pressure of the flow phase dynamically causes an increase in the sealing force and thus can adaptively cause a fluidic seal of the connection. By reducing the static force on the "hand-tight" connection, the static force can be kept low, thus prolonging the service life of the components involved. A "tool-free" establishment of a high-pressure secure connection is likewise achieved thereby.

[0018] In one embodiment the sealing structure is configured such that under the influence of the pressure of the flow phase at least a part of the volume of the sealing structure is increased (e.g. bulges), which volume increase causes a fluidic sealing of the flow path, preferably by pressing the opposing faces together. This volume increase can technically correspond to the function of a sponge, i.e. a body whose volume at least partially expands under the pressure of a medium flowing through the body. If the sealing structure is pressed against another face, the increase in volume of the sealing structure can exert a force onto the other face, which in turn causes a pressing force of the sealing structure against the other face if the other face cannot escape this pressing force. By a suitable shaping of the sealing structure, the volume increase is only locally defined to a partial area of the opposing faces, and the sealing effect of the opposing faces can be further increased.

[0019] In one embodiment the flow element has a first surface and the sealing structure has a second surface, wherein the first surface opposes the second surface. The at least partial increase in volume of the sealing structure takes place in the first surface, preferably by at least partially bulging the first surface, such that the volume increase causes a pressing of the first surface against the second surface, preferably by the bulge pressing and pressing against the second surface, thereby causing a fluidic sealing of the flow path.

[0020] In one embodiment the sealing structure has a sealing channel, which is connected or connectable with the flow phase, in order to cause a fluidic sealing of the flow path under the influence of the pressure of the flow phase. Instead of the flow phase, the sealing channel can also be traversed by another fluid under pressure, but this would require a separate pump. In this case the sealing channel is separate from the flow channel and fluidically separated therefrom.

[0021] In one embodiment the first valve element has a sealing structure, wherein at least for the fluidic sealing of the flow path the sealing structure of the first valve element presses against the second valve element.

[0022] In one embodiment the second valve element has a sealing structure, wherein at least for the fluidic sealing of the flow path the sealing structure of the second valve element presses against the first valve element.

[0023] In one embodiment the sealing structure is separate from the first valve element and the second valve element, wherein at least for the fluidic sealing of the flow path the sealing structure presses the first valve element and the second valve element against each other.

[0024] In one embodiment the valve is a rotary valve, wherein the first (preferably movable) valve element is a rotor and the second (preferably stationary) valve element is a stator, and the flow path (e.g. between the inlet opening and the outlet opening) is fluidically established or interrupted by rotating the rotor relative to the stator.

[0025] In one embodiment the valve is a translational valve, wherein by translational movement of the first valve element relative to the second valve element a fluidic establishment or disconnection of a flow path (e.g. between an inlet port and an outlet port) is possible.

[0026] In one embodiment of the valve the sealing structure is arranged to or acts on the first valve element and / or the second valve element such that an axial angular misalignment between the first valve element and the second valve element is compensated or at least reduced. Preferably, the first valve element is arranged axially fixed in the valve and the second valve element or at least a region thereof is elastically alignable relative to the axial arrangement of the first valve element, wherein the sealing structure is arranged to or acts on the second valve element such that the second valve element matches the axial arrangement of the first valve element.

[0027] In one embodiment of the valve the sealing structure also allows a dynamic matching of the switching process and / or switching behavior of the valve. For example, a pressing force between interacting valve elements, such as a rotor and a stator, can be controlled in relation to the switching process, such that the pressing force is reduced, for example, before and / or during the relative movement of the interacting valve elements, in order to thereby simplify the switching process or to reduce, even avoid, wear and / or abrasion. Alternatively or additionally, the pressing force can also be increased after the relative movement of the interacting valve elements, in order to thereby improve the fluidic sealing of the valve. Of course, the pressing force can also be dynamically matched or controlled in other ways, especially suitable for the application of the valve.

[0028] In one embodiment the flow element has a plurality of layers with at least one microfluidic channel formed by one or more recesses in at least one of the plurality of layers. The plurality of layers is preferably connectable to each other by a bonding process, such as diffusion bonding. Other connection methods, such as conventional soldering, for example at the edges, can also be applied. Alternatively or additionally, additive manufacturing methods, such as 3D printing, micro-pressing structures, etc. can also be used. Preferably, at least one of the layers has or is formed from a material from the group of metals, especially stainless steel, preferably high-quality stainless steel (e.g. 316L, MP35N, 304), ceramics, especially aluminum oxide, magnesium oxide, zirconium oxide, aluminum titanate, polymers, especially PEEK, ULTEM, PEAK, PEKK, PEI, etc.

[0029] In one embodiment the sealing structure has a plurality of structures.

[0030] In one embodiment the sealing structure has a plurality of structures, wherein the sealing structure is configured such that, under the influence of the pressure of the flow phase, the at least one microfluidic channel can expand at least in partial regions to cause a fluidic sealing of the flow path.

[0031] In one embodiment the at least one microfluidic channel forms at least a part of the flow path.

[0032] In one embodiment the sealing structure is spatially separated from the flow path at least in the region of the flow path which needs to be sealed by the sealing structure.

[0033] In one embodiment the sealing structure is not part of the flow path which needs to be sealed by the sealing structure.

[0034] In one embodiment the flow path, at least the part of the flow path which needs to be sealed by the sealing structure, has an outer wall in which the flow phase can flow. Preferably the sealing structure is spatially separated from the outer wall and the sealing structure is located outside the flow path and its outer wall.

[0035] In one embodiment the sealing structure is part of the flow path and is traversed by the flow phase flowing through the flow path. The sealing of the flow path can be achieved by a bulging of the region of the flow path caused by the pressure of the flow phase and the bulging abutting and pressing against the other face. Preferably the other face remains spatially constant or can move at least in the direction of the bulging less than the bulging itself, whereby the bulging can press against the face.

[0036] Preferred embodiments relate to a high performance chromatography system having a pump for moving the flow phase and the stationary phase to separate components of a sample liquid introduced in the flow phase. The high performance chromatography system also has a valve, as described previously, preferably for controlling, establishing and / or interrupting the flow path for transporting the flow phase.

[0037] In one embodiment the flow element is configured such that the pressure can be suitably adjusted and / or controlled depending on the flow phase acting on the sealing structure, preferably independently of the sample liquid using the flow phase. For example a part of the flow element can be branched off the flow phase, wherein another part of the flow phase is used for separating the sample liquid. Preferably the pressure can be varied depending on the flow phase acting on the sealing structure, for example independently of the flow phase pressure used for separating the sample liquid. The pressure variation of the flow phase acting on the sealing structure can preferably be achieved by a suitable pump, which in the case of a high performance chromatography system can be one or more pumps of the system. Instead of a pump other known pressure generating mechanisms can also be used accordingly. By suitable coupling, for example by means of a valve, and control the pressure of the flow phase can be controlled differently at different locations.

[0038] In one embodiment the flow element can be preconfigured such that for example a given pressure value is set for the flow phase acting on the sealing structure. The flow phase acting on the sealing structure can preferably be fluidically separated from the flow phase used for separating the sample liquid at least during the analysis phase for separating the introduced sample liquid. For example if the flow element is or has a valve or a fitting, the valve and / or fitting can be pre-tensioned and set with the desired pressure of the flow phase acting on the sealing structure accordingly.

[0039] In one embodiment of the high-performance chromatography system, the flow element is configured such that a delay volume of the high-performance chromatography system can be matched. The delay volume here is the volume between the mixing point of the mobile phase and the stationary phase. Preferably, the flow element allows to increase a given delay volume of the high-performance chromatography system, for example by means of adding a volume which is traversed by the mobile phase. The volume which is traversed by the mobile phase of the flow element can suitably be set or preselected by a suitable spatial design. For example, the traversed volume can be selectively or settable varied. Alternatively, a suitable flow element for a respective application can be found and used from a plurality of given flow elements each having a given traversed volume, for example by a suitable coupling, for example by means of a valve or other coupling element, or by fluidically connecting the flow element into the system accordingly. By such setting or adjustment of the delay volume of the entire high-performance chromatography system, for example, a dynamic behavior of another target high-performance chromatography system can be emulated, such that the used high-performance chromatography system behaves at least substantially the same as the target high-performance chromatography system by adjusting the delay volume.

[0040] The high-performance chromatography system according to the application has a pump for moving a mobile phase, a stationary phase for separating components of a sample liquid introduced into the mobile phase, and a valve in the flow path of the mobile phase as described above. The high-performance chromatography system can also have a sample injector for introducing the sample liquid into the mobile phase, a detector for detecting separated components of the sample liquid, and / or a fractionation device for outputting separated components of the sample liquid.

[0041] Embodiments of the application can be implemented on the basis of various known HPLC systems, for example the Agilent Infinity Series 1290, 1260, 1220 and 1200 of the applicant Agilent Technologies, see www.agilent.com.

[0042] As mobile phase (eluent) pure solvents or mixtures of different solvents can be used. The mobile phase can be selected such that the retention of the components of interest and / or the amount of mobile phase used for running the chromatography is minimized. The mobile phase can be selected to effectively separate specific components. The mobile phase can have an organic solvent, methanol or acetonitrile, which is usually diluted with water. For gradient runs, the mixing ratio of water and organic solvent (or other solvents common in HPLC) is usually changed over time.

[0043] The aforementioned methods can be wholly or partially controlled, assisted or implemented by software when the software is run on a data processing system, such as a computer or workstation. The software can be stored on a data carrier here. BRIEF DESCRIPTION OF DRAWINGS

[0044] The application is described further below with reference to the drawings, in which identical reference signs refer to identical or functionally identical or similar features.

[0045] Figure 1 A liquid separation system 10 according to an embodiment of the application is shown, for example, for use in an HPLC.

[0046] Figure 2 An example of a valve 200 is shown, for example, for use in a sample injector 40.

[0047] Figure 3 An embodiment according to the different aspects of the application to achieve a dynamic fluid seal between the rotor 210 and the stator 220 is shown. Figure 2

[0048] Figure 4A and Figure 4B An embodiment 400 for sealing one or more of the sealing structures 280, 285, 290 is shown exemplarily and in a cross-sectional view.

[0049] Figure 5 An embodiment of a valve 500 is shown schematically and in a cross-sectional view.

[0050] Figure 6 A preferred embodiment of the stator 220 is shown in a top view.

[0051] Figure 7 A preferred embodiment of the sealing structure 280 shown and used, for example, in Figure 5

[0052] Fig. 8 shows a preferred embodiment for an adaptive fitting 800.

[0053] Figure 9 Another embodiment of the fitting 800 according to the application is shown.

[0054] Fig. 10 shows another embodiment of the valve 500 schematically.

[0055] Figure 11-1 4 A further embodiment of the valve 500 is shown again schematically and in a cross-sectional view.

[0056] Figures 15-17 A three-dimensional view of a further embodiment of the stator 200 is shown schematically and independently from the valve 500. DETAILED DESCRIPTION

[0057] Figure 1 ​​A general schematic of a liquid separation system 10 is shown in detail. A pump 20 obtains a mobile phase from a solvent supply 25, typically via a degasser 27, which degasses the mobile phase and in this way reduces the amount of dissolved gas in the mobile phase. The pump 20 drives the mobile phase through a separation device 30, such as a chromatographic column, which has a stationary phase. A sample device (or sample injector) 40 can be provided between the pump 20 and the separation device 30 to introduce a sample fluid into the mobile phase. The fluid line between the pump 20 and the sample injector 40 can be indicated with reference 41 and the fluid line between the sample injector 40 and the separation device 30 can be indicated with reference 42. The stationary phase of the separation device 30 is matched to separate components of the sample fluid. A detector 50 detects the separated components of the sample fluid and a fraction device 60 can be used to output the separated components.

[0058] The mobile phase can consist of only one solvent or of a mixture of different solvents. The mixing can be done at low pressure and before the pump 20, so that the pump 20 already delivers the mixed solvents as mobile phase. Alternatively, the pump can consist of individual pump units, where each pump unit delivers one solvent or one solvent mixture, respectively, so that the mobile phase is mixed at high pressure and after the pump 20 (as seen by the separation device 30 at this time). The components (mixtures) of the mobile phase can remain constant over time (isocratic mode) or change over time in a so-called gradient mode.

[0059] A data processing unit 70, which can be a conventional PC or workstation, can be coupled to one or more of the devices in the liquid separation system 10, as indicated by the dashed arrows, to obtain information and / or to control the operation of the system or of individual components thereof.

[0060] Figure 2 An example of a valve 200 is shown, which can be applied, for example, in a sample injector 40, for example for injecting a sample fluid into the mobile phase. Such injectors comprising switchable valves are well known in the art, for example from WO2010139359A1, US20160334031A1 or US2017343520A1, all from the same applicant. The first two documents show injectors in a so-called flow-through configuration, where a sample loop in which the sample fluid resides during injection is coupled between the pump and the separation device. While the third document describes an injector in a so-called feed injection configuration, where the sample fluid is pressed into the mobile phase between the pump and the separation device by means of a T-shaped coupling, so that the sample flow containing the sample fluid is added to the flow of the mobile phase.

[0061] Figure 2The valve 200, which is shown by way of example, is a so-called rotary valve, wherein the rotor 210 and the stator 220 are in relative rotational motion to one another, wherein typically the rotor rotates relative to the stator. Herein in the rotor and in the stator there can be so-called ports, which represent the open end of a respective flow path, which can be connected to the valve 200 via a respective connection 230A, 230B, etc. The stator 210 and the rotor 22 can also have respective connection elements, for example recesses, such as grooves, channels, etc., which by the relative motion of the rotor and the stator can fluidically connect one or more ports to one another. This is shown in Figure 2 schematically and is known in the prior art, for example from the aforementioned documents. It is also known that instead of a rotary valve a so-called translational valve can also be used, wherein instead of a rotational motion a translational motion is implemented.

[0062] In the embodiment of Figure 2 The valve 200 also shows a drive 240 for moving the rotor 210, for example a rotatable shaft, which can be driven by a motor, for example. The drive 240 can be fixedly connected to the rotor 210, even be an integral part thereof. The drive 240 is pressed, preferably elastically / spring- elastically, to the stator 220, for example by means of a spring pack 250. The rotor 210, the drive 240 and the spring pack 250 can be arranged in a housing 260. The stator 220, together with the connections 230, can preferably be arranged in a valve head 270, which can be connected to the housing 260, for example by means of a screw connection 270.

[0063] The valve 200 can be coupled, for example, such that the flow path 41 is coupled to the connection 230A and the fluid line 42 is coupled to the connection 230B. By suitably disconnecting the rotor 210 and the stator 220, in particular by implementing suitable connection elements, the desired functionality can be shut off in the fluidic coupling between the flow paths 41 and 42, for example as is known in the prior art.

[0064] In order to achieve fluid tightness in the fluidic path between the flow paths 41 and 42, in the liquid path between the rotor 210 and the stator 220, in the prior art it is mostly proposed that the respective geometry of the spring pack 250 or another static pre-tensioning mechanism is such that the rotor 210 is pressed to the stator 220 in the axial direction, i.e. in the direction of the sealing force F, with the desired sealing force F. Herein a too low sealing force F can lead to a lack of tightness, in particular between the rotor 210 and the stator 220, while a too high sealing force F can cause an increased wear, in particular at the frictional parts between the rotor 210 and the stator 220.

[0065] Figure 3 According to Figure 2The embodiments shown in Fig. 2 illustrate different approaches to achieve a dynamic and adaptive fluid seal between the rotor 210 and the stator 220. The dynamic sealing approaches shown here can be applied alternatively or in any combination with each other. In general, each of the approaches shown (for dynamic sealing) results in a dynamic axial force FD, which can be superimposed on a static axial force FS. The dynamic axial force FD is here numerically related to the respective pressure of the flow phase, i.e. a low pressure of the flow phase results in a low dynamic axial force FD and a high pressure of the flow phase results in a higher dynamic axial force FD. The static axial force FS can be implemented and dimensioned, for example, by the spring set 250 or other measures known in the prior art.

[0066] Figure 3 The first approach to dynamic sealing shown in Fig. 2 is a first sealing structure 280, the second approach is a second sealing structure 285 and the third approach is a third sealing structure 290. The sealing structures 280, 285, 290 are also referred to as sealing structures (or pressure structures) and shall be described in detail below and demonstrated by exemplary embodiments. In general, each of these sealing structures 280, 285, 290 is connected or connectable with the flow phase, for example via a suitable fluid switch, such as a valve, in order to be influenced by the (respective) pressure of the flow phase under the influence of the flow paths 41 and 42. Figure 3 The dynamic fluid seal is established in the flow path exemplarily shown in Fig. 2, in which the flow phase also flows or can flow.

[0067] The first sealing structure 280 is connected with or in the stator 220. The second sealing structure 285 is fixed on the drive 240 and the third sealing structure 290 is axially located between the housing 260 and the drive 240. The sealing structures 280, 285, 290 can be flowed through by the flow phase respectively and can be applied individually or in any combination with each other as described. Correspondingly, respective further sealing structures can be applied alternatively or in combination at suitable locations.

[0068] In other embodiments not shown here, the sealing structure that generates or can generate an axial force by expansion has no self-connection to the flow phase, for example a connection parallel to the flow paths 41 and 42, but is in series with the normal function of the injection valve of the syringe 40, for example, so that it always looks at the highest pressure in the system in addition to in the case of obstruction. Here the sealing structure is preferably in series with the flow path to be sealed.

[0069] The sealing structures 280, 285, 290 are preferably implemented by a microfluidic structure, preferably based on a plurality of metal layers which are connected to each other by diffusion bonding, as described in detail for example in WO2017025857A1 of the same applicant. The microfluidic structure here has at least one microfluidic channel which is or can be flowed through by the flow phase. The microfluidic structure is configured in such a way that it at least partially expands or can expand in the axial direction, i.e. in the direction of the sealing force F or FS, under the influence of the pressure of the flow phase. Such a microfluidic structure based on metal layers connected to each other is also referred to as a metal microfluidic or MMF structure.

[0070] Figure 4A and Figure 4B An embodiment 400 for one or more of the sealing structures 280, 285, 290 is shown exemplarily and in a sectional view. It is understood here that this figure is purely schematic in order to explain the mode of action of the sealing structure 280, 285, 290. The sealing structure 400 consists of three metal layers 410, 415 and 420 which are fixedly connected to each other, preferably by diffusion bonding. A channel 430 is produced by a recess in the metal layer 415, which is visible in the sectional view chosen here in the flow direction. The channel 430 has an (not shown in Figure 4) inlet and an (also not shown in Figure 4) outlet and can be flowed through by the flow phase, wherein the pump 20 is preferably fluidically coupled with the inlet and the separation device 30 is fluidically coupled with the outlet. The flow phase (in the schematic view according to Figure 1 has essentially the same pressure between the pump 20 and the separation device 30, which is also correspondingly essentially applied in the channel 430 at this point in time.

[0071] In Figure 4A the sealing structure 400 is shown in a state in which the flow phase does not flow through the channel 430. In Figure 4B the sealing structure 400 is shown how it expands under the pressure of the flow phase flowing through the channel 430 in the direction of the arrow shown. The expansion shown here is intentionally shown exaggerated in order to better see the effect. In reality the sealing structure 400 expands in the embodiment according to Figure 4 only very slightly, for example by a few micrometers, for example 50 to 200 pm, in the direction of the arrow, depending on the material selection and the pressure ratio. The expansion in the direction of the arrow can be correspondingly increased and thickened, for example by using a plurality of layers with a plurality of channels.

[0072] Figure 5 An embodiment of a valve 500 is shown schematically and in a sectional view, which essentially corresponds to Figure 2 and Figure 3The valve 200 is shown in the figure and is therefore referred to accordingly by reference numerals. The rotor 210 is located in the housing 260, abutting against the stator 220, and can be driven to rotate by the driver 240. An axial pressure bearing 510 supports the driver 240 in the axial direction.

[0073] First sealing structure 280 (according to) Figure 3 (The schematic diagram in Figure 4) is connected to or acts on the stator 220 in the axial direction. The first sealing structure 280 is also shown schematically and in exaggerated size as in embodiment 400 shown in Figure 4. The first sealing structure 280 preferably consists of multiple layers, wherein, according to... Figure 5 The schematic diagram shows only two layers 520 and 525, and the channel 530 surrounded by layers 520 and 525. Preferably, the first sealing structure 240 is also presented as an MMF structure.

[0074] As the pressurized fluid phase flows through, the channel 530 expands in the direction of the arrow and acts on the stator 220 in the axial direction with a dynamic sealing force FD, while the stator presses against the rotor 210 in the axial direction, so that the stator 220 and the rotor 210 are fluidly sealed relative to each other when the magnitude of the dynamic sealing force FD is appropriate.

[0075] According to Figure 5 In the schematically illustrated embodiment, the stator 220 is implemented and arranged or fixed in the valve 500 such that the axial angular misalignment relative to the rotor 210 can be compensated for at least a certain degree, thereby ensuring that the working surfaces of the stator 220 and the rotor 210 are relatively parallel or planar. For this purpose, the stator 220 is fixedly connected to the housing 260, for example by means of appropriate mechanical fasteners (e.g., in…). Figure 6 (See mounting holes 630 and 635 shown). Furthermore, the stator 220 is implemented as resilient, so that although the stator is rigidly connected to the housing 260, it can be resiliently aligned axially with respect to the rotor 210. For this purpose... Figure 5 In the illustrated embodiment, the rotor 210 is configured to have an elastic region 550 located between the fixed region 555 and the contact region 560. The fixed region 550 is the region where the stator 220 is fixed relative to the housing 260. The contact region 560 is the region where the stator 260 is in contact with the rotor 210, i.e., the area where the valve function of the stator 220 is required is located.

[0076] The elastic region 550 is implemented such that the sealing structure 280 can planarly press the contact region 560 onto the corresponding contact surface of the rotor 210, thereby compensating for possible axial angular misalignment between the contact region 560 and the rotor 210. According to... Figure 5 In the schematic diagram, this is exaggeratedly shown by the (elastic) deformation or shaping of the elastic region 550.

[0077] In an embodiment according to Figure 5 The sealing structure 280 is in this embodiment implemented and arranged such that, in case of an axial angular misalignment of the rotor 210 relative to the housing 260, the abutment region 560 of the stator 220 is aligned relative to the rotor 210 in axial direction such that the abutment region 560 lies plane against the abutment face of the rotor 210 and can be pressed (fluid-tightly) against each other. The sealing structure 280 is enabled to be laterally deformed by the passage 530 and can be elastically aligned abuttable between the housing 530 and the abutment region 560 of the stator 220 such that the abutment region 560 is aligned in axial direction with the stator 210 and pressed thereon.

[0078] It can be seen from the foregoing embodiments that the respective sealing structure 280, 285, 290 dynamically presses the stator 220 and the rotor 210 against each other with a dynamic sealing force FD. This sealing force FD is in this case related to the respective pressure of the flow phase, i.e. a higher pressure of the flow phase leads to a higher sealing force FD. But on the other hand the pressure of the flow phase also exactly acts onto the area to be sealed, in this case the contact area between the stator 220 and the rotor 210, since between the flow paths 41 and 42, where the flow phase is conveyed, is guided. Therefore the contact area between the stator 220 and the rotor 210 has to be sealed to a greater extent when the pressure of the flow phase is higher (than when the pressure of the flow phase is lower). Therefore the sealing structure 280, 285, 290 dynamically acts onto the contact area between the stator 220 and the rotor 210 such that a higher dynamic sealing force FD is provided by the sealing structure 280, 285, 290 when the flow phase pressure, which requires a higher sealing force in the contact area, is higher. In contrast, the sealing structure 280, 285, 290 reduces the dynamic sealing force FD on the contact area when the flow phase pressure, which requires a lower sealing force in the contact area, is lower. This leads to the fact that the dynamic sealing force of the sealing structure 280, 285, 290 basically follows the pressure of the flow phase such that the dynamic sealing force FD is low when the pressure of the flow phase is low and the dynamic sealing force FD is high when the pressure of the flow phase is high. Therefore the contact area between the stator 220 and the rotor 210 is not unnecessarily heavily loaded when the pressure of the flow phase is low, which can lead to less wear and a longer service life.

[0079] Figure 6 A preferred embodiment of a stator 220, which can for example be used in an embodiment according to Figure 5 The stator 220 is preferably implemented in MMF technology. A plurality of interfaces 600 is centrally implemented in a middle region 605 of the stator 220. The interfaces 600 are respectively an open end of a respective flow path and jointly act with a respective connection element (for example a slot) of the stator 210 to connect the respective flow paths to each other.

[0080] The intermediate region 605 (with the interface 600) is implemented as a flexible region, which in embodiments according to Figure 6 is achieved by two recesses 610 and 615. The two recesses 610 and 615 allow the intermediate region 606 to be twisted (in particular flipped) through an angle such that the intermediate region 605 lies as flat as possible on the rotor 210 even if the stator 220 is twisted or tilted relative to the rotor 210.

[0081] The stator 220 also has external connections 620, which in embodiments according to Figure 6 are exemplarily shown in three connections 620 in the side regions to the right and to the left of the stator 220, which can correspond, for example, to the connections 230 in Figure 2 for external fluidic contact with the stator 220.

[0082] The stator 220 in embodiments according to Figure 6 also has two mounting holes 630 and 635 for mechanically coupling and / or fastening the stator 220, for example, relative to the housing 260. Naturally, more or fewer than two mounting holes 630, 635 or a different solution for mechanical coupling and / or fastening than is known from the prior art can also be used accordingly.

[0083] The intermediate region 605 shown in Figure 6 corresponds to the contact region 550 shown in Figure 5 , while the region between the recesses 610 and 615 and the mounting holes 630, 635, which is not represented in detail here, corresponds to the elastic region 550 shown in Figure 5 .

[0084] Figure 7 A preferred embodiment of the sealing structure 280, for example, shown and used in Figure 5 is shown in a sectional view (upper part) and a plan view (lower part). The sealing structure 280 is likewise preferably implemented in MMF technology. According to the embodiment shown in Fig. 4, Figure 7 the sealing structure 280 is constructed from a plurality of metal layers 700, in the shown embodiment four metal layers 700A-700D, which are fixedly connected to one another, preferably by diffusion bonding. The channel 710 (corresponding to the channel 430 of Fig. 4) is formed by suitable recesses in the metal layers 700B and 700C and can be traversed by a fluid, for example, a mobile phase. In embodiments according to Figure 7 the channel 710 is at least partially surrounded by a ceramic inlay 720, which can be added as a bonding aid during the bonding process, for example. The ceramic inlay 720 serves the manufacturing process and can prevent or reduce sagging of the geometry.

[0085] In Figure 7In the top view of the sealing structure 280 shown in the lower middle section, two external connectors 730A and 730B can also be seen. The external connectors can be used for external fluid contact of the sealing structure 280, such that, for example, a mobile phase enters the sealing structure 280 through connector 730A, moves through channel 710, and can exit again through connector 730B.

[0086] In the sectional view ( Figure 7 In the upper middle section, the (axial) expansion (in the direction of the arrow) of channel 710 under the influence of the pressure of the flowing phase is again exaggerated to illustrate the principle function of the sealing structure 280. By accordingly guiding and / or designing channel 710 and / or by arranging channels in multiple planes, the deflection caused by the pressure of the flowing phase can be designed and preferably enhanced accordingly.

[0087] Figure 8 illustrates a preferred embodiment of the adaptive fitting 800. The fitting 800 shown here fluidly connects a tubular capillary 810 (e.g., made of glass or metal) to a (preferably disc-shaped) planar sealing structure 820 and is configured as a high-pressure connection for pressures from 200 bar, and preferably between 1000 and 2000 bar. Figure 8A A cross-sectional view of accessory 800 is shown. Figure 8B A view of accessory 800 is shown below. Figure 8C and Figure 8D It shows Figure 8A The area enclosed by the dashed line at the edge. Figure 8E The channel structure of accessory 800 is shown in a three-dimensional view.

[0088] Figure 8A A capillary 810, which is fluidly coupled and mechanically connected to a planar sealing structure 820 via fitting 800, is shown in detail. The capillary 810 is encapsulated in a stabilizing tube (e.g., a base) 830, which is preferably connected to the planar sealing structure 820 by means of laser welding (see weld 835).

[0089] The planar sealing structure 820 is exemplarily shown as consisting of four separate layers 840A-840D, wherein the number of layers may be varied according to the implementation and the design of the planar sealing structure 820. An annular channel 850 is formed within the planar sealing structure 820 through corresponding recesses in the layers 840, and the annular channel can be traversed by a liquid medium such as a mobile phase.

[0090] The planar seal structure 820 also has an inlet 855 and an outlet 857, with an annular channel 850 extending between the inlet and the outlet or the annular channel 850 being fluidly coupled to the inlet and outlet, such that the mobile phase enters the planar seal structure 820 through the inlet 855, is transported through the annular channel 850, and can exit again through the outlet 857.

[0091] Figure 8A middle and lower parts Figure 8B The second surface 860 of the planar sealing structure 820 shown in the top view is preferably additionally coated with a sealing material, such as polytetrafluoroethylene, to compensate for surface defects if necessary.

[0092] The wall thickness of layer 840 in the planar sealing structure 820 is designed such that the wall of the annular channel 850 bulges outward under pressure loading, as in... Figure 8C and 8D The enlarged portion is shown as X in the schematic diagram. Here, X represents the annular channel 850 relative to... Figure 8C The image shows a bulge without pressure applied through the flowing phase.

[0093] exist Figure 8E The image exemplarily illustrates the possible shape of an annular channel 850 through which a capillary tube 810 is fed and a possible connector 870 is exiting from the planar structure.

[0094] The profile of the planar seal structure 820 can be implemented, for example, as a circle or an ellipse of uniform thickness, to additionally prevent the planar seal structure 820 from twisting, for example, during tension. This ellipse shape can be predetermined during diffusion bonding or produced afterward by machining steps, thereby potentially achieving higher profile accuracy.

[0095] if Figure 8A The fitting 800 shown in Figure 8 abuts against another surface (not shown) with its second surface 860. Under pressure loading through the annular channel 850 (through the flowing phase), the raised portion X is loaded onto the surface it abuts, where the larger the raised portion X, the greater the pressure of the flowing phase. Accordingly, the planar sealing structure 820 itself, and adaptively by means of the raised portion X, seals or enhances the existing static seal relative to the abutting surface.

[0096] replace Figure 8A The single connection shown is used to establish only one fluid connection, but a corresponding multi-connector with multiple channels can also be provided, with each channel individually sealed and fed by only one pressure channel if necessary.

[0097] Figures 3-7 In the illustrated embodiments, the sealing structures (hereinafter also referred to as pressure structures) 280, 285, 290, and 400 are spatially separated from the flow paths 41 and 42, respectively, at least in the regions of the flow paths 41 and 42 of the flow elements 200 and 400 that require sealing by the pressure structures 280, 285, 290, and 400. Therefore, in these embodiments, at least in the regions of the flow paths that require sealing by the pressure structures, the pressure structures are not part of the flow paths.

[0098] Figures 3-7 The flow paths 41, 42, which are only shown schematically, generally have an outer wall, within which the flow phase can flow. The pressure structures 280, 285, 290, 400 are then spatially separated from the outer wall and located outside the flow path and its outer wall. Typical flow paths can be capillaries or microfluidic structures. In a capillary, the wall is presented by the capillary itself, i.e. the capillary is the wall within which the flow phase can flow. In a microfluidic structure, this transition is generally presented by a corresponding channel within a substrate, which is composed of a plurality of layers connected to one another if necessary.

[0099] Figure 9 Another embodiment of the fitting 800 is shown. Figure 9 In this case, the upper region shows a tubular capillary 810, which corresponds to the embodiment according to Figure 8, which is fixedly connected to the planar carrier 900, for example by means of laser welding (shown by the weld seam 835), enclosed into a stabilization cannula 830.

[0100] The planar sealing structure 820 should be pressed against the first surface 905 of the planar carrier 900 with its second surface 860, which end side is in Figure 9 In this case, the upper side of the planar sealing structure 820 is shown) in order to thereby connect the inlet 855 (for the channel structure of the planar sealing structure 820) fluidically sealingly to the capillary 810. Figure 9 The annular channel 850 of the planar sealing structure 820 in this case is configured such that, in the region of the inlet 855, a Figure 9 The bulge 920, which is shown schematically in this case, acts dynamically fluidically. The outlet 857 is in Figure 9 The outlet 857 is shown only schematically as a lateral outlet in this case.

[0101] The planar sealing structure 820 according to the embodiment of Figures 8 and Figure 9 may be, for example, part of a rotary valve or a mixer (for example a stator or a rotor).

[0102] Figure 10 shows another embodiment of the valve 500, which is similar to the embodiment according to Figure 2 and Figure 3 and in particular according to Figure 5 , so that the reference signs are used accordingly. Figures 10A-10D The embodiment of the valve 500 is shown schematically and in a sectional view, while Figure 10E The stator 220 is shown in a sectional view and in a bottom view. Figures 10A-10D The different operating states of the valve 500 are shown in deliberately exaggerated schematic illustrations, as described in detail below.

[0103] In all the attached Figures 10A-10DThe central valve 500 has a housing 260, which in the embodiment chosen here is two-part and has a stator element 1000 and a rotor element 1010, which are connected to one another in a known manner, for example by screw connections, but are preferably settable / selectable for loose fixing. By dividing the housing 260 into two or more elements, simple manufacture is achieved, but it can be seen that one-piece variants of the housing 260 can also be provided accordingly.

[0104] In the embodiment of Figure 10, the stator element 1000 accommodates the stator 220 and a first sealing structure 280, which is also referred to below as an element for hydraulic pressure generation or pressure element 280. Between the stator element 1000 and the pressure element 280, a transmission element 1020 can also be provided, which takes over the force transmission between the elements 280 and 220 and at the same time homogenizes the pressure via the bearing surfaces. Likewise, a flat bearing surface for the element 220 can be provided by the element 1020. The transmission element 1020 is preferably embodied rigidly, in particular in relation to the "hydraulic pad" of the sealing structure 280. The transmission element 1200 can also be embodied elastically in the case of the use of adjusting screws.

[0105] In the stator element 1000, corresponding fluid channels are (schematically) shown, in order to fluidically connect the first sealing structure 280 and the stator 220 in the sense of an input line and an output line, wherein according to the embodiment a plurality of input lines and output lines can also be provided, in particular for the stator 220, as is known from the prior art. It is also to be considered here that the terms input line and output line are to be understood in the respective operating state, i.e. fluid is introduced into the respective element by the input line and fluid is removed from the respective element by the output line. Fluid connections which were previously used as input lines can thus be used as output lines in different operating states. In the schematic diagram of Figure 10, the stator 220 is fluidically coupled with an input line 1030A and an output line 1030B and the first sealing structure 280 is fluidically coupled with an input line 1040A and an output line 1040B.

[0106] The stator 220 is fluidically coupled in its fluid coupling (preferably for fluid introduction of the flow phase) here only schematically with a first line 1050A and a second line 1070A, the first channel being fluidically coupled with the input line 1030A and having an interface 1060 opposite the rotor 210, the second channel being fluidically coupled with the output line 1030B and having an interface 1080 opposite the rotor 210.

[0107] The rotor element 1010 accommodates the rotor 210, wherein the rotor is according to Figure 5The implementation in this manner can be rotated by a drive 240 and is preferably supported by an axial pressure bearing 510. As described above, the rotor 210 may have suitable connecting elements, such as slots, to allow interfaces 1060 and 1080 to be fluidly connected or not connected to each other, depending on the rotational position (of the rotor 210 relative to the stator 220).

[0108] The rotor 210, which is not shown in the schematic diagram, may have an anti-rotation part relative to the driver 240. The anti-rotation part may be implemented according to known prior art as, for example, a pin connection (e.g., a rotor-rotor shaft connection via three or more pins) or other geometrically engaged connection.

[0109] Apart from Figure 10A In addition to the cross-sectional view shown in -D Figure 10E The stator 220, separate from valve 500, is also shown in the top view, thus illustrating interfaces 1060 and 1080 (according to...). Figure 6 (The implementation method) and piping 1050A and 1070A. Preferably, stator 220 can be implemented using MMF technology. The plurality of interfaces 600 schematically shown in the intermediate region include exemplary interfaces 1060 and 1080 and are respectively presented to the open ends of the fluid flow path.

[0110] Stator 220 includes the intermediate region 605 of interface 600 (according to...) Figure 6 In addition to the intermediate region 605, it also has an outer annular region 1100 and two connecting pieces 1110A and 1110B, which extend between and connect to the intermediate region 605 and the outer annular region 1100, respectively. Only one connecting piece or more than the two connecting pieces 1110 shown here may be implemented, and the connecting pieces 1110 can naturally have different shapes than those shown here. The connecting pieces guide the fluid connection between the interface 600 and the interface in the outer annular region.

[0111] Similar to Figure 6 The implementation method, by means of Figure 10E In the embodiment of the connecting piece 1110, the intermediate region 605 is elastically movable relative to the outer annular region 1100, thus serving as a flexible region, allowing the intermediate region 605 to move relative to the outer annular region 1100, particularly in the axial direction (of the valve 500). This flexible structure also allows the intermediate region 605 to twist / flip relative to the outer annular region 1100, i.e., the surface of the intermediate region 605 that abuts against the rotor 210 can be bent at an angle / inclined relative to the surface containing the outer annular region 1100. This is further described below.

[0112] Figure 10AThe valve 500 is shown in a state where the first sealing structure 280 is not circulated by fluid (such as a preferred flowing phase) or the fluid is not under pressure or is only slightly under pressure, thereby the first sealing structure 280 does not expand or only expands very slightly in the axial direction of the valve 500. In this state, the stator 220 is not connected to the rotor 220 or is only slightly connected to it, that is, the stator 220 is not (as in...) Figure 10A (The distance shown is too large) or it is only against the rotor 210 with a small axial force. This state is shown here only to illustrate the mode of operation.

[0113] Figure 10B The diagram illustrates a state where the fluid loading pressure element 280 causes a bulge in passage 530 in the axial direction of valve 500, thus causing an axial increase in pressure element 280. By increasing pressure element 280, the stator 220 is pressed against the rotor 210 via transmission element 1020, or more specifically, the intermediate region 605 of the stator 220 is pressed against the corresponding contact surface of the rotor 210. As can also be seen from the intentionally exaggerated schematic diagram chosen for better explanation, the intermediate region 605 is axially deflected (towards the rotor 210) relative to the outer annular region 1110 of the stator, which is fixedly connected to the stator element 1000. The pressure loading of pressure element 280 allows for influencing or controlling its axial increase and the clamping force relative to rotor 210. Therefore, the sealing force of stator 220 relative to rotor 210 can be controlled by controlling the fluid pressure in passage 530 of pressure element 280.

[0114] Figure 10C The diagram, deliberately exaggerated for clarity, illustrates how axial angular misalignment between rotor 210 and stator 220 occurs, or how this is compensated in the embodiment according to FIG. 10. Rotor 210 is slightly tilted relative to the axis of valve 500, for example due to tolerances, wear, misadjustment, etc. The intermediate region 605 is elastically movable and / or torsional relative to the outer annular region 1100 via the elastically implemented stator 220. Furthermore, pressure element 280 is implemented such that channel 530 can be extended or bulged differently along the axial direction, similar to a "hydraulic cushion" that can be aligned between opposing but not parallel surfaces with a certain angular misalignment.

[0115] exist Figure 10C In the example shown, the axial angular misalignment of the rotor 210 (relative to the axis of valve 500) is applied to the pressure element 280 via the stator 220 (and optional abutment element 1020), such that the pressure element 280 has a different radial thickness (in the axial direction), as... Figure 10C As shown in the diagram, the working surfaces of the rotor 210 and stator 220 are thus fixedly and fluid-tightly pressed together.

[0116] Figure 10D Exemplarily and intentionally exaggerated, it is shown how an axial angular misalignment between the rotor 210 and the stator 220 can be compensated, wherein in the embodiment according to Figure 10D the stator element 1000 is bent in axial direction with respect to the rotor element 1010, for example again due to tolerances, wear, incorrect adjustment, etc. According to Figure 10C the elastically embodied stator 220 can compensate for this axial angular misalignment, so that the intermediate region 605 can be (further) flatly abutted against the abutment face of the rotor 210. This angular misalignment is here embodied in a change in the radial thickness of the pressure element 280, and the channel 530 of the pressure element 280 serves as a hydraulic cushion and compensates for the axial angular misalignment.

[0117] The hydraulic seal explained and shown in the preceding embodiments is preferably achieved by the carrier medium to be sealed, i.e. the flow phase of the liquid separation system 10 itself. Alternatively, a further flow medium can naturally also be used to achieve the volume increase of the respective sealing structure according to the application. This generally, however, requires a separate pump mechanism and, if necessary, a corresponding pressure control to achieve the desired dynamic sealing.

[0118] Instead of or in addition to the pump 20, a further (not shown in the drawings) auxiliary pump can be used to deliver the fluid (in particular the flow phase) that causes the volume increase of the respective sealing structure.

[0119] The embodiments shown in the preceding for sealing a flow path with a sealing structure can be partly equivalent to mechanical arrangements, for example toggle levers or the mechanism described in US 10428960 for changing the valve pressure force. Such toggle levers can for example statically and / or dynamically press the rotor onto the stator in a valve, for example according to Figure 2 However, the embodiments according to the application allow an automatic, self-adapting and dynamic matching of the respective pressure ratio in the flow path to be sealed, i.e. a higher pressure in the flow path to be sealed automatically causes a higher sealing force through the sealing structure, as long as the medium flowing through the flow path to be sealed is also used to generate the sealing force in the sealing structure, for example the flow phase of the high-performance chromatography system 10 is used in the respective sealing structure, for example the sealing structures 280, 285, 290, to generate the self-adapting and dynamic sealing force.

[0120] In the embodiments shown in Figures 8-9, the sealing structure or pressure structure, respectively, is part of the flow path at least in the region of the flow path of the flow element that needs to be sealed by the sealing structure / pressure structure. The flow path is sealed by a bulge of the part region of the flow path caused by the pressure of the flow phase and the abutment and pressing of this bulge on the other face that is preferably spatially fixed or at least only deflectable in the direction of the bulge with a smaller movement than the bulge itself, whereby the bulge presses against this face.

[0121] Figure 11-1 4Also shown schematically and in a sectional view is a further embodiment of the valve 500, which is similar to the embodiment shown in particular according to Fig. 10, whereby the aforementioned can be used accordingly here. In order to simplify and make clearer the illustration, the differences are shown and explained first below.

[0122] Correspondingly to the embodiment of Fig. 10, in the embodiment according to Figure 11-1 4the stator 210 is embodied to be respectively elastically movable, whereby the intermediate region 605 can be moved and / or twisted to a certain extent elastically relative to the outer annular region 1100. As shown and described in Fig. 10, this allows in particular to compensate for axial angular misalignments between axially arranged elements of the valve 500, for example between the housing 260 and / or the rotor 210 relative to the stator 220.

[0123] In contrast to the embodiment according to Fig. 10, in the embodiment according to Figure 11-1 4the pressing of the intermediate region 605 of the stator 220 against the opposite active surface of the rotor 210 is not effected by the (hydraulic) pressure element 280, but respectively by a preferably further mechanical mechanism, which is shown below.

[0124] In Figure 11 between the stator 220 and the housing 260 an at least partially elastic rod 1200 is arranged. An axial pressing mechanism 1210, which can be provided preferably in connection with the housing 260, for example a corresponding screw mechanism, as shown exemplarily, can be provided, such that the rod 1200 is positioned relative to the stator 220 in the axial direction and for example presses the stator 220 firmly against the rotor 210 in the axial direction.

[0125] The rod 1200 has an upper side 1220, a lower side 1230 and between them an elastic region 1240. The upper side 1220 serves to abut the rod 1200 against the housing 260 or the axial pressing mechanism 1210, while the lower side 1230 serves to abut against the stator 220. The elastic region 1240 is configured here such that it can at least be elastically bent to a certain extent, such that by the bending an axial angular misalignment can be compensated for, for example as shown in Figure 11 by the axial angular misalignment between the rotor 210 and the housing 260. By the elastic embodiment of the stator 220, the intermediate region 605 can follow and compensate for the axial angular misalignment together with the elastic bending of the elastic region 1240, such that the active surfaces of the stator 220 and the rotor 210 can be pressed parallel to each other. The rod 1200 is preferably made of an elastic material with sufficient pressure resistance, for example steel, alternatively a suitable metal alloy, a composite material, a plastic, an elastomer or a ceramic. In principle all materials which are elastic by material properties or are made elastic by a corresponding geometric embodiment can be used.

[0126] InFigure 12 China Replacement Figure 11 The elastic rod 1200 shown illustrates a compensation assembly 1250, which, in conjunction with the elastic rod 1200, allows for compensation of axial angular misalignment. The compensation assembly 1250 is here made of an elastic and, as far as possible, incompressible pad 1260, which is held, for example, within the frame 1270. A clamping element 1280 is provided between the pad 1260 and the stator 220. The elastic pad 1260 allows for angular compensation by having a different thickness in the radial direction while maintaining an approximately constant overall volume, thereby allowing for the setting of angular misalignment extending forward via the clamping element 1280 onto the compensation assembly 1250. The elastic pad 1260 is preferably made of a durable, but incompressible plastic (e.g., polyurethane), but may also be made of a slightly plastically deformable material (e.g., PTFE). A liquid with high viscosity and surface stress is also conceivable. The clamping element 1280 performs the same function as the transmission element 1020 in FIG. 10, in addition to sealing.

[0127] according to Figure 11 In another embodiment, the compensation component 1250 can also be positioned in the axial direction by a corresponding axial clamping mechanism 1210 and pre-tightened relative to the stator 220 if necessary.

[0128] Figure 13A Another embodiment of the compensation assembly 1250 is shown. The compensation assembly is composed of a clamping element 1280, which abuts against the stator 220 during operation and presses it against the rotor 210. The compensation assembly 1250 also has an upper abutment element 1300 and a spring element 1310, which is located between the clamping element 1280 and the upper abutment element 1300. Figure 13B An axial view of one embodiment of spring element 1310, for example, a cloverleaf coil spring, is shown. The shape of spring element 1310 is essentially free, as long as it allows elastic axial bending between the clamping element 1280 and the upper abutment element 1300, as in Figure 13A It is shown schematically in the diagram.

[0129] Figure 14A Another embodiment of the compensation assembly 1250 is shown. Similar to the embodiment according to FIG. 13, the compensation assembly 1250 consists of a clamping element 1280 that abuts against the stator 220 during operation and presses it against the rotor 210. The compensation assembly also has an upper abutment element 1300 and a spring structure 1400 located between the clamping element 1280 and the upper abutment element 1300. Figure 14BAn axial view of an embodiment of a spring structure 1400, here for example a ring-shaped arrangement of a coil spring, is shown. The spring structure 1400 here has for example three spring elements 1410A-C in this embodiment, but the number and the design are basically free, as long as this allows an elastic axial bending between the compression element 1280 and the upper abutment element 1300, as is schematically shown in Figure 14A

[0130] Figures 15-17 A three-dimensional view of further embodiments of the stator 220 is shown schematically and separately from the valve 500. With this embodiment it should be exemplarily shown that the design of the elastic stator 220 is almost not limited, which in this regard enables an elastic movement of the intermediate region 605 relative to the outer annular region 1100. The precise design can be derived from the respective application and the used materials and manufacturing processes. It is particularly advantageous here that the already mentioned MMF technology is used for manufacturing this elastic stator 220.

[0131] The embodiment according to Figure 15 has four connection tabs 1110A-D, which connect the intermediate region 605 with the outer region 1100 respectively and symmetrically to each other in an arc shape and thereby allow an elastic movement of the intermediate region 605 relative to the outer region 1100.

[0132] The embodiment according to Figure 16 has two connection tabs 1110A-B, which likewise connect the intermediate region 605 with the outer region 1100 in an arc shape and symmetrically to each other.

[0133] In the embodiment according to Figure 17 the connection tabs 1100 are complex and intertwined with each other and are implemented to act together. This also leads to an elastic connection between the intermediate region 605 and the outer region 1100.​

Claims

1. A valve (500) for separating components of a sample liquid introduced into a mobile phase in a high-performance chromatography system (10), said valve being a rotary valve having: A first valve element (210) and a second valve element (220), wherein the action surface of the first valve element (210) is fluidly connected to the action surface of the second valve element (220) by the relative rotation of the first valve element (210) with respect to the second valve element (220), and the pipeline (1030A, 1050A, 1070A, 1030B) can be controlled, established or disconnected. in, The second valve element (220) has an elastic region (1110) to compensate for the axial angle between the first valve element (210) and the second valve element (220) under the influence of fluid pressure, so that the first action surface and the second action surface can be parallel to each other.

2. The valve (500) according to claim 1, wherein, The second valve element has an outer region (1100) and an intermediate region (605). The intermediate region (605) has a second working surface, and The outer region (1100) is connected to the middle region (605) via an elastic region (1110), through which the middle region (605) moves elastically relative to the outer region (1100).

3. The valve (500) according to claim 2, wherein, The outer region (1100) is fixedly arranged relative to the first valve element (210) and the middle region (605) can be elastically aligned relative to the first valve element (210).

4. The valve (500) according to claim 2, wherein the elastic region (1110) has one or more connecting pieces (1110A, 1110B) connected to the outer region (1100) on one side and to the intermediate region (605) on the opposite side, such that the intermediate region (605) can tilt relative to the outer region (1100).

5. The valve (500) according to claim 1 or 2, wherein, The first valve element (210) is a rotor and the second valve element (220) is a stator, wherein the rotor is rotatable relative to the stator.

6. The valve (500) according to claim 1 or 2, comprising: A sealing structure (280) is configured such that the volume of the sealing structure (280) is at least partially increased under the influence of fluid pressure, thereby pressing the first valve element (210) and the second valve element (220) together relative to each other for fluid sealing of the pipelines (1030A, 1050A, 1070A, 1030B).

7. The valve (500) according to claim 6, wherein, The sealing structure (280) has a region (530) that is elastically deformable like a hydraulic cushion, such that when the first and second working surfaces are parallel to each other and pressed against each other, the axial angle between the first valve element (210) and the second valve element (220) causes a change in the thickness of the sealing structure (280).

8. The valve (500) according to claim 1, comprising: - Flow element (200; 500; 800), said flow element having: Flow paths (41, 42) used for transporting the mobile phase. Sealing structures (280, 285, 290, 400, 820), which are connected to or can be connected to the flowing phase, so as to cause a fluid seal in the flow path (41, 42) under the influence of the pressure of the flowing phase. in, The sealing structures (280, 285, 290, 400, 820) are configured such that, under the influence of the pressure of the flowing phase, the volume of the sealing structures (280, 285, 290, 400, 820) is at least partially increased, and the at least partial increase in volume causes a fluid seal on the flow paths (41, 42).

9. The valve (500) according to claim 8, characterized in that, The fluid seal for the flow paths (41, 42) has a first surface (905) and a second surface (860) that are pressed against each other.

10. The valve (500) according to claim 8, characterized in that, The flow element (200; 500; 800) has a first surface (905) and the sealing structure (280, 285, 290, 400, 820) has a second surface (860), wherein the first surface is opposite to the second surface and the volume of the sealing structure (280, 285, 290, 400, 820) is increased at least partially on the first surface.

11. The valve (500) according to claim 10, characterized in that, By bulging the first surface at least partially, the increased volume causes the first surface to press against the second surface, thereby causing a fluid seal on the flow paths (41, 42) by bringing the bulge against and pressing against the second surface.

12. The valve (500) according to any one of claims 8-10, characterized in that, The sealing structures (280, 285, 290, 400, 820) have a sealing channel (850) that is connected to or can be connected to the flowing phase, so as to cause a fluid seal on the flow paths (41, 42) under the influence of the pressure of the flowing phase. The sealed channel is separate from the flow path (41, 42) and separate from its fluid.

13. The valve (500) according to any one of claims 8-10, having at least one of the following features: The first valve element (210) has sealing structures (280, 285, 290), wherein at least for fluid sealing of the flow paths (41, 42), the sealing structures (280, 285, 290) of the first valve element (210) are pressed against the second valve element (220); The second valve element (220) has sealing structures (280, 285, 290), wherein at least for fluid sealing of the flow paths (41, 42), the sealing structures (280, 285, 290) of the second valve element (220) are pressed against the first valve element (210); The sealing structures (280, 285, 290) are separated from the first valve element (210) and the second valve element (220), wherein at least in order to fluid seal the flow paths (41, 42), the sealing structures (280, 285, 290) are pressed together with the first valve element (210) and the second valve element (220).

14. The valve (500) according to any one of claims 8-10, having at least one of the following features: The valve (500) is a rotary valve, wherein the first valve element (210) is a rotor and the second valve element (220) is a stator, and by rotating the rotor relative to the stator, flow paths (41, 42) can be fluidly established or disconnected.

15. The valve (500) according to any one of claims 8-10, characterized in that, The sealing structures (280, 285, 290, 400) are arranged or act on the first valve element (210) and / or the second valve element (220) to compensate for or at least reduce the axial angular misalignment between the first valve element (210) and the second valve element (220).

16. The valve (500) according to claim 15, characterized in that, The first valve element (210) is axially fixedly arranged in the valve and the second valve element (220) is elastically aligned with the axial arrangement of the first valve element (210), wherein the sealing structures (280, 285, 290) are arranged relative to and act on the second valve element (220) such that the second valve element (220) matches the axial arrangement of the first valve element (210).

17. The valve (500) according to claim 1 or 2, characterized in that, It has multiple layers connected to each other by a bonding process, and has at least one microfluidic channel formed through one or more recesses in at least one of the multiple layers, wherein at least one layer has a material from or is formed of the group consisting of: metals, ceramics, alumina, magnesium oxide, zirconium oxide, aluminum titanate, and polymers.

18. The valve (500) according to claim 17, characterized in that, The multiple layers are connected to each other by diffusion bonding, the metal includes stainless steel, and the polymer includes PEEK, ULTEM, PEAK, PEKK, and PEI.

19. The valve (500) according to claim 8, characterized in that: One or more features: The sealing structure (280, 285, 290, 400, 820) has multiple structures; The sealing structures (280, 285, 290, 400, 820) have multiple structures, wherein the sealing structures (280, 285, 290, 400, 820) are configured such that at least one microfluidic channel can expand at least in a partial region under the influence of the pressure of the mobile phase to cause a fluid seal on the flow path (41, 42). The at least one microfluidic channel forms at least a portion of the flow path (41, 42).

20. The valve (500) according to claim 8, having at least one of the following features: At least in the areas of the flow path of the flow element that need to be sealed by the sealing structure, the sealing structure (280, 285, 290, 400) is spatially separated from the flow path (41, 42); The sealing structures (280, 285, 290, 400, 820) are not the parts of the flow paths (41, 42) that need to be sealed by the sealing structures; The flow paths (41, 42), and at least the portions of the flow paths that need to be sealed by the sealing structures (280, 285, 290, 400), have an outer wall in which the flow phase can flow; The flow paths (41, 42), and at least the portions of the flow paths that need to be sealed by the sealing structures (280, 285, 290, 400), have outer walls in which the flow phase can flow, wherein, The sealing structures (280, 285, 290, 400) are separated from the outer wall space and the sealing structures (280, 285, 290, 400) are located outside the flow paths (41, 42) and their outer walls; The sealing structure (820) is part of the flow path (41, 42) and is permeated by the flow phase flowing through the flow path.

21. A high-performance chromatography system (10) comprising: Pumps (20) used to move the mobile phase. The stationary phase (30) used to separate the components of the sample liquid introduced into the mobile phase, and The valve (500) according to any one of claims 1-18.

22. The high-performance chromatography system (10) according to claim 21, wherein: The valve (500) is used to control, establish and / or disconnect the flow path (41, 42) for transporting the mobile phase.

23. The high-performance chromatography system (10) according to claim 21 or 22, wherein: The valve (500) has a sealing structure (280) having a region (530) that is elastically deformable like a hydraulic cushion, such that when the first and second action surfaces are parallel to each other and pressed against each other, the axial angle between the first valve element (210) and the second valve element (220) causes a change in the thickness of the sealing structure (280).

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