• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a rotational rheometer having a stator (2) arranged in a rotationally invariable manner, having a rotor (1) rotatable by means of an eddy current drive about the axis of the stator (2), wherein the test medium (6) to be examined is arranged in at least one of surfaces of rotor located opposite one another (1) and stator (2) formed measuring gap (15) can be introduced. According to the invention, the measurement gap (15) filled with the test medium (6) to be examined acts as a hydrodynamic bearing between rotor (1) and stator (2) and is formed exclusively by the rotation of the rotor (1) relative thereto to the stator (2) achieved hydrodynamic bearing effect of the distance and the mutual position of the mutually facing, the measuring gap (15) defining surfaces of the rotor (1) and stator (2) predetermined and adjusted and maintained during the measurement process.
    公开号:AT514549A4
    申请号:T50570/2013
    申请日:2013-09-11
    公开日:2015-02-15
    发明作者:Ronald Dr Henzinger；Josef Gautsch
    申请人:Anton Paar Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a rotational rheometer for determining the viscous and / or theological properties of fluid media according to the preamble of claim 1.
    Rotation rheometers can be used to determine the viscous and theological properties and parameters of fluids, in particular the dynamic viscosity of fluids.
    In rheometers according to the invention, a measuring body designed as a rotor runs around or in or opposite a stator or stator part (s). The measuring gap is between the rotor and the stator. There is an eddy current drive of the rotor. Further, a measurement is made of the rotational speed given by the drive and the actual rotational speed of the rotor during the measurement, and the rotational speed difference serves as a measure of the viscous / rheological properties of the test medium. According to the invention, a hydrodynamic bearing of the rotor relative to the stator is provided.
    From GB 1197476 (A) a rheometer is known in which the cylindrical gap between rotor and stator of a three-phase induction motor provides a passage for the test fluid to be measured; The rotor is supported by a spindle and bearings.
    Measuring systems with cylindrical surfaces having measuring bodies generally comprise a measuring body (inner cylinder) and a measuring cup (outer cylinder). The two cylinders are concentrically arranged in the measuring position, i. the axes of the cylinders coincide. In such cylinder rotation rheometers, the test medium to be measured is located in the annular gap between the inner and outer cylinders. When the inner cylinder rotates, one speaks of a Searle system, in the reverse case it concerns a so-called Couette system.
    There are no fundamental differences in the structure of rotational rheometers and rotational viscometers. In either case, a rotor is relatively moved relative to a stator and the lag angular differences are determined. Only for different purposes and depending on the fluids to be tested, a different construction or different constructions and Meßkörpere used. Frequently, rotational rheometers are used to measure the theological properties of non-Newtonian fluids, while complex rheometers primarily measure the shear rate-dependent behavior of the fluids.
    Searle viscometers comprise a stationary cup in which a coaxial cylinder body in the measuring fluid will rotate by an engine. In this case, either the speed gradient when specifying a defined shear stress or the shear stress when specifying a defined speed gradient (constant rotational speed) is usually measured.
    In general, the measuring body should be stored as friction-free as possible in the case of rotational viscometers in order to measure as much bearing friction as possible when measuring the rotational speeds or the torques that occur. The rotational symmetry axis can thereby run in a horizontal position or inclined, in contrast to the classical, vertical arrangement. The rotor, which is mounted without contact in the outer cylinder by magnets, can be held in its ideal position by a complex control and measuring system and can be driven inductively without contact. However, the structure of such a viscometer and the rotor bearing are extremely complex. Above all, an influence of the rotor by the magnets takes place and a bearing friction or bearing forces can not be completely eliminated.
    The test medium to be examined is located in the measuring gap between rotor and stator. The drive of the rotor acting as a measuring body takes place in the inventive rheometer by an eddy current drive. For this, e.g. around the stator or rotor axis permanent magnets rotates or it is a to the stator or. Rotor axis rotating (rotating) magnetic field created, by at least two, preferably more induction coils, which induce voltages in the conductive measuring body or in the rotor and thus lead to eddy currents. This results in a Lorentz force perpendicular to the magnetic field lines rotating the measuring body.
    An alternative variant of an eddy current drive is achieved by a magnetic or permanent magnet equipped rotor. To the measuring gap or to the rotor rotates externally a concentrically arranged, conductive eddy current body. In this vortex, currents are induced due to its rotation about the permanent magnets, and these currents in turn induce voltages inside the rotor, which in turn generate their own magnetic fields opposite the prevailing magnetic field according to the Lenz rule, which ultimately drive the rotor.
    Considering generally the flow conditions of a fluid in a shear gap between two cylinders, a velocity gradient between the inner and outer cylindrical surfaces is formed, i. there is a shear with a given speed gradient. The torque M transmitted through the gradient to the inner or outer cylinder is directly proportional to the dynamic viscosity. Considering two volume elements, they always experience the same angular acceleration, but the outer volume element experiences higher centrifugal forces, so that Couette arrangements are actually more stable than Searle arrangements wherein in the case of couette arrangements the outer volume elements experience the higher speeds. In the case of a Searle arrangement, the inner cylinder is rotated and there is a velocity profile in which the inner liquid layers rotate at higher speeds while the outer layers rotate more slowly, which can lead to vortexing
    A searle system is always the more unstable variant due to the movement of the inner cylinder and thus the maximum speed on the inner cylinder, since the swirling occurs mainly due to the centrifugal forces acting. This so-called Taylor Couette vortex formation is known. The occurrence of this vortex limits the use of the searle systems. In order to achieve a laminar flow in the measuring gap, the measuring range, which is in principle very wide, is limited, in particular for fluids of low viscosity.
    In general, the advantages of a Searle arrangement are the high possible shear rates, the homogeneous shear rate distribution and the low sensitivity to sedimentation phenomena. Disadvantages are edge effects with necessary correction, the occurrence of vortices, and the need for accurate calibration.
    The bearing of a rotor exclusively with magnets or by means of a magnetic field does not work in a non-contact coupling between the rotor and the drive, as this causes the magnetic forces to decrease quadratically to the distance, an imbalance always arises in the rotor and this arrangement only works at very high revolutions of the rotor (eg 10,000 rpm) ) - otherwise the rotor will rub against the stator. A strong magnetic field also causes a nearly rigid coupling between the rotor and the driving magnetic field and causes the same speed of magnetic field and rotor possibly with a in the
    Testing adjusting, influenced by the magnetic field small angle of rotation between the rotor and stator, which is not or only extremely difficult zudetektieren.
    The aim of the invention is to avoid the disadvantages of the known arrangements or rheometers and to create a rotational rheometer which is simple in construction, provides accurate measured values and can be operated free from bearing forces, in particular mechanical and magnetic bearing forces.
    According to the invention, these objects are achieved in a rotational rheometer of the type mentioned by the features cited in the characterizing part of patent claim 1. It is thus provided that the measuring gap filled with the test medium to be examined acts as a hydrodynamic bearing between the rotor and the stator and the gap and the mutual position of the facing measuring gap are solely due to the hydrodynamic bearing effect achieved by the rotation of the rotor relative to the stator limiting surfaces of rotor and stator predetermined and adjusted and maintained during the measurement process.
    It is only necessary to measure the rotational speed of the rotor and to know the input rotational speed acting on the rotor or its nominal rotational speed, in order to obtain values, uninfluenced by storage influences, which permit a direct inference to the rheological parameters. The only influence on the rotor speed is made by the test medium, which slows down the rotation of the rotor because of its intrinsic properties.
    It is easy for a person skilled in the art to create the gap geometry required for a hydrodynamic bearing effect for different test media. This can be done, in particular, by first determining in advance the parameters to be determined, then setting up the measuring gap or adapting to these parameters and then determining these parameters with a rotational rheometer according to the invention with the highest accuracy. Also, the speed at which the rotor is rotated can be adjusted to the parameters of different test media, as well as taking into account the temperature and pressure of the test medium to achieve a perfect hydrodynamic storage during the measurement process. It is therefore advantageous if the geometry, preferably the distance and the distance profile of the opposing surface sections of the measuring gap, in particular the radial distance of the opposing surfaces of rotor and stator surrounding the rotation axis, for forming the hydrodynamic bearing as a function of the rotational speeds applied by the drive unit, a previously estimated value of viscosity and / or pre-estimated Theological parameters of the test medium are selected. Proper storage is supported if, in the measuring gap, a sufficiently laminar, eddy-free flow is formed when the rotor rotates to form a hydrodynamic bearing. For the stable formation of a hydrodynamic bearing in a rotational meter for measuring operation, it is advantageous if the end regions of the measuring gap communicate with the outer regions adjoining these end regions or the test medium contained in these regions freely, in particular without cross-sectional narrowing of the end region of the measuring gap, or the end regions directly into go over these outdoor areas. In order to obtain exact measured values, it is advantageously provided that the rotor, with the exception of its hydrodynamic bearing in the region of the measuring gap, is mounted on or opposite the stator in the radial direction with respect to its axis of rotation, free of contact and bearing, and in particular free of magnetic bearings.
    A preferred embodiment of the invention results when, for the formation of the eddy current drive rotating the rotor, the rotor is formed, preferably entirely, of nonmagnetic, nonmagnetizable, electrically conductive material and that around or at least partly within the rotor about the stator axis rotatable permanent magnets are mounted or are mounted around the rotor or at least partially within the rotor electromagnetic coils with which a rotatable about the stator axis magnetic field can be generated. Alternatively, it may be provided that the rotor, preferably entirely, is made of non-magnetic, non-magnetizable, electrically conductive material to form the eddy current drive which rotates the rotor, and permanent magnets or coil bearings are mounted at least partially within the stator, the permanent magnets being around the stator axis are rotatable and with the coils a rotating about the stator axis magnetic field can be generated.
    A further embodiment of the invention provides that are arranged to form the rotor in rotation staggering eddy current drive within the rotor permanent magnet fixed fixed or connected to the rotor and that, preferably entirely of non-magnetic, non-magnetizable, electrically conductive material eddy current body, preferably a cage , a pot or a conductor loop, which is rotatable about the rotor.
    An embodiment of the invention that can be used well in practice and provides accurate measured values provides that the rotor is arranged in the interior of a stator having a rotationally symmetrical inner wall and in the form of a rotationally symmetrical container or cup, wherein permanent magnets are arranged so as to be fixed in position within the rotor for forming the eddy current drive rotating the rotor are connected to the rotor and the material of the container, preferably wholly, non-magnetic, non-magnetizable and electrically non-conductive material, and an eddy current body formed of non-magnetic, non-magnetizable, electrically conductive material, preferably a pot, a cage or a conductor loop is provided which is rotatable about the stator.
    It may be advantageous if a rotor having a cylindrical peripheral surface and possibly end faces is provided which is surrounded on all sides by a cylindrical interior wall surface and interior surfaces of the stator which are at least inclined towards end surfaces and inside the interior of the test medium, whereby an eddy current body rotates around the stator is stored, preferably in the form of a pot, a cage or a conductor loop and is formed of non-magnetic or non-magnetizable, electrically conductive material, wherein permanent magnets are mounted in the rotor or connected to this. In practice, it is expedient for the stator to have a closable introduction opening for the test medium. For the bearing of the rotor during the measurement, it is particularly advantageous if the rotor is stabilized with respect to the stator in the longitudinal direction of the stator axis on the rotor and on the stator oppositely interacting permanent magnets and soft iron parts which stabilize the longitudinal position of the rotor relative to the stator axis (B) without contact.
    A precise and well controllable eddy current drive results when the rotor and / or the stator and / or the eddy current body rotated around the rotor have high electrical conductivity and are made, if necessary, from Cu, Pt, Ag or Au.
    The possible use of the rheometer according to the invention is increased if heating and / or cooling units for the test medium are arranged in the stator.
    The geometry of the measuring gap can be chosen differently. It is advantageous if, in a section running through the axis of rotation of the rotor or through the stator axis, the measuring gap or the surfaces of the rotor and stator delimiting the measuring gap have at least one straight, bent, bent and / or curved section inclined to the axis of rotation or to the stator axis or with these forms an acute angle, whose vertex is directed into the interior of the measuring gap and / or that the opposing surfaces of the measuring gap with respect to the axis of rotation are each centrally symmetrical and / or that the measuring gap defining surfaces with respect to a plane perpendicular to the axis of rotation center plane of the measuring gap respectively It is also advantageous for the measuring operation, when the rotor is cylindrical, annular, cup-shaped, conical or frusto-conical or in a plane passing through the axis of rotation plane in section triangular, trapezf is formed as a segment of a conic or Ovoids.
    In general, it is advantageous if the measuring gap is selected as narrow as possible.
    In order to achieve a defined, friction-free mounting of the rotor radially and axially, but without sacrificing the advantages of a hydrodynamic bearing, it can be provided that the rotor is supported on at least one of its surfaces, i. on its inner surface and / or outer surface, and / or on at least one end face, faces each face of the stator or of a stator part or of another stator part, and the rotor rotates through the hydrodynamic bearing action of the test fluid in the radial and optionally also in the radial direction prevailing in the respective measuring gap between the respective surfaces axial direction with respect to the stator axis without contact. For optimum storage it can be provided that the stator is designed in the form of a closed pot or cylinder and that on this stator a rotor having the shape of an open pot with its interior space is formed, forming the measuring gap, optionally additionally on the side of the rotor facing away from the stator at least one stator part and / or another stator part is located at a distance from the rotor, in particular its end wall and / or peripheral wall, and optionally this distance between the rotor and the respective stator part or further stator part is designed as a measurement gap that effects a hydrodynamic bearing.
    In practice, a rotational rheometer, which is simple in design but very precise in measurement, can be immersed in the test medium, characterized in that the stator has on its cylindrically formed outer surface a circumferential groove in which it forms on its inner surface to form the measuring gap The rotor adapted to the cross-sectional shape of the depression is hydrodynamically storable or mounted at a distance from the surface of the depression. In this case, it is advantageous if, at a surface of the rotor mounted in the recess, facing away from the stator, the surface of one stator part lies opposite one another at a distance and forming a further measuring gap in the hydrodynamic bearing.
    This results in a double-gap system, which represents a combination of Couette and Searle principle and ensures excellent hydrodynamic storage.
    To achieve the " cone-plate geometry " advantageous for the measurements of theological parameters. In the case of rotational rheometers according to the invention, it can be provided according to the invention that for the gap width of the respective measuring gap at a distance from the axis of rotation the relation R1 / R2 = S1 / S2 applies, where R1 and R2 are the distances of points on the surfaces bounding the measuring gap from the axis of rotation of the measuring gap And S1 and S2 are the gap thickness formed in these points R1 and R2 during hydrodynamic bearing of the rotor and this thickness of the respective measuring gap increases with increasing distance from the axis of rotation.
    In principle, non-rotationally symmetrical outer surfaces having rotors can be used as long as they allow a hydrodynamic bearing. Such rotors may have the cross section of polygons or ellipses.
    In the following, we will explain the invention with reference to the drawings, for example, in more detail.
    Figures 1 and 2 show a schematic longitudinal and cross-section through an embodiment of a rotational rheometer according to the invention.
    Figures 3 to 7 show schematic sections through further embodiments of the invention according to the rotational rheometer.
    Fig. 8 shows schematically the principle of a cone-plate rotation rheometer.
    A rotational rheometer according to the invention generally has a fixed, outer or inner, acting as a stator 2, preferably rotationally symmetric body, which may also be formed as a closed container, wherein in this container as a rotor 1, preferably rotationally symmetrical trained, measuring body is arranged and concentric with the outer and / or inner stator 2 is located. Between the rotor 1 and stator 2 is the measuring gap 15 and upon rotation of the rotor 1 is formed in the measuring gap 15 between the stator 2 and the rotor 1 is a hydrodynamic storage. Deviations from the concentric position caused by the weight of the rotor 2 can in principle occur in the rheometers according to the invention, but in particular do not play a role in the measurement even if the bearing of the stator axis B deviates from the vertical and can be neglected.
    In principle, the inventively provided, hydrodynamic bearing of the rotor 1 is carried out specifically in the radial direction with respect to its axis of rotation A. The storage in axial direction can either be done by a hydrodynamic bearing on the end faces of the rotor 1 or by placing small guide magnets on the rotor 1 and of soft iron parts 10 on the stator 2, which magnets 9 and soft iron parts 10 opposite each other and restrict the possibility of movement of the rotor 1 in the direction of the rotor axis A. In general, with the eddy current drive, a non-contact drive of the rotor 1 is possible without having to use mechanical or magnetic bearings.
    In general, it depends on the structural design, in particular the radius of the magnetic rotor 1, the width or thickness of the measuring gap 15, the course of the mutual distance of the measuring gap 15 bounding surfaces and the speed, which test media 6 due to their specific density parameters, viscosity parameters and rheological Parameter bring the rotor 1 when starting or Hochlaufen in a stable position with respect to the stator 2 and then maintained in the stationary measurement operation, the mutual position of the rotor 1 and stator 2 and a laminar layering of the test medium 6 in the measuring gap 15. In particular, the viscosity of the test medium 6 is to be considered for the stability.
    The hydrodynamic bearing should be so dimensioned or dimensioned that the rotor 1 is held within the stator 2 in an ideal center position or approximately in the middle position, as may be predetermined by a hydrodynamic bearing. Furthermore, the rotor 1 is to be driven in such a way that it floats sufficiently in the case of a rotor axis A inclined in a horizontal direction and that no vortex is formed in the test medium 6. When the rotor 1 rotates about the stator 2, the rotor 1 is held around the stator 1 by the hydrostatic bearing at an approximately equal distance.
    The hydrodynamic bearing becomes better, the more similar the specific gravity of the rotor 1 is the density of the test fluid to be measured, in particular when the cylindrical peripheral surface and possibly inclined end surfaces having rotor 1 in an adapted, a cylindrical inner wall surface and possibly inclined end surfaces having an interior Stators 2 with the
    Eddy current drive is rotated. To compensate for different, specific densities of the rotor 1 and the test medium 6, the rotor speeds can be increased or adjusted. For the determination of the measured values or the speeds can be at all
    Embodiments Sensors 31, 32, e.g. Hall sensors, optical sensors, capacitive, inductive sensors and other non-contact measuring devices, with which the rotational speed of a rotor 1 can be measured. Also suitable are eddy current sensors.
    In principle, it is also possible to mechanically drive the eddy current body 3 or the permanent magnets 4 to be rotated, e.g. via a belt drive from a drive motor; it is necessary to determine the exact speed of the magnets.
    Since the viscosity of a fluid is usually temperature-dependent, a temperature measurement can also be provided. This is done with a sensor (14) (thermocouple, etc.), the gap at the pot or stator 2 as close as possible to the test medium 6bzw. is flush mounted directly on the stator in contact with the test medium 6, without disturbing the flow, or may be arranged on or in the rotor 1. The sensor then comprises means for non-contact transmission of the measured values to the stator 2 or to the stationary parts of the measuring device.
    Of particular advantage and generally replaceable is the design of the eddy current drive 3 with a magnetic yoke, which leads to the field lines defined, perpendicular to the surfaces of the rotor 1 can be performed. Soft iron or other soft magnetic material is used for this inference, with which stator parts 2 " and further stator parts 2 'may be formed, which parts may also be provided for the formation of an enlarged or of further measuring gaps 15, respectively. With such stator parts 2 ', 2 " On the inner wall surface and on the outer wall surface of the rotor 1, a measuring gap 15, 15 'can be formed.
    More generally, rotating eddy current generating rotors of the present invention may employ either rotating permanent magnets 4 or coils 8 which generate a rotating magnetic field. This is done depending on the constructive design and purpose.
    Fig. 1 shows the basic structure of an embodiment of a rheometer according to the invention in section. A housing 30 carries a rotationally symmetrical stator 2 with respect to a stator axis, the pot-shaped or as a cylinder of the housing 30 goes off. On the stator 2, a pot-shaped, with respect to the rotor axis Arotation symmetrisch formed rotor 1 is placed, which surrounds the stator 2 to form a distance. The rotor 1 is surrounded forming a gap of further stator parts 2 ', 2 " connected to the housing 30. In this way, between the inner and outer cylindrical surfaces of the rotor 1 and the inner and outer end surfaces of the rotor 1 and the outer surfaces of the stator 2 and the inner surfaces of the stator members 2 ', 2 " in each case a measuring gap 15 or 15 'is formed with a hydrodynamic bearing for the rotor 1. Within the stator 2, permanent magnets 4 are distributed around the rotor axis A on a carrier 33, whereby the carrier 33 is rotatable about the stator axis B by a drive 5. Test medium 6 can enter the two measuring gaps 15, 15 'via an opening 16. Via an outlet opening 17, the test medium 6, driven by the rotation of the rotor 1, leave the measuring gaps 15, 15 'again.
    Means 31, 32 for measuring the rotational speed of the permanent magnets 4, e.g. Hall probes whose cooperating measuring parts are arranged on the one hand on the carrier 33 of the permanent magnets 4 and on the other hand on the housing 30. Similarly, measuring units of inductive, optical or capacitive type may be provided to determine the rotational speed of the rotor 1. These measuring units are used by the rotor 1 and the stator 2 and the stator 2 ', 2 " or the housing 30 carried. The rotor 1 is rotated by the rotation of the permanent magnets 4, which induce eddy currents in the soft iron rotor 1, which in turn cause the rotation of the rotor 1 by the electromagnetic forces occurring. The permanent magnets 4 are here, as in all other embodiments of the invention, rotationally symmetrical and axisymmetric with respect to the stator axis B and the axis of rotation A of the rotor 1 is formed. The rotor 1 rotates due to the rotating magnetic field, which is generated in the present case by the permanent magnets 4, wherein the drive speed of the rotor 1 by the speed of the permanent magnets 4 and the rotational speed of the drive motor 5 is predetermined.
    The rotational speed of the permanent magnets 4 can be measured in the same way as the rotational speed of the rotor 1 with non-contact measuring units 31 and 32, e.g. Hall sensors, inductive, optical or capacitive measuring units, are determined. Alternatively, the speed specification of the motor can be used for the further calculation.
    In an axial position on the stator axis B, the rotor 1 is held by the further stator parts 2 ', 2 ", which surround the end wall of the rotor 1. Thus, a hydrodynamic bearing is also formed on both sides of the end wall 1 'of the rotor 1.
    As a result of the hydrodynamic bearing along the rotor 1, the rotor 1 is centered in the radial direction with respect to the stator axis B, and a positional stabilization takes place in the direction of the stator axis B through the further stator parts 2 ".
    In order to be able to measure different test media 6, the geometry of the arrangement or the dimensions of the rotor 1 and optionally of the stator 2 and the further stator parts 2 ', 2 " In particular, the gap thickness of the measuring gap 15, 15 'can be varied, so that a hydrodynamic bearing can always be achieved for the measurement. Thus, any bearing friction or bearing forces caused by mechanical storage or by a magnetic bearing excluded. It is only necessary to overcome fluid friction, which however is an interesting parameter of measurement and can be used as a measure of the characteristics of the test medium. Fig. 2 shows a section along the line C-C in Fig. 1. Manerkennt the carrier 33 for the permanent magnets 4, which are arranged with alternating polarity along the circumference of the carrier 33 within the stator 2. Directly around the stator 2 is the first measuring gap 15, which is limited to the outside of the rotor 1.
    The rotor 1 is surrounded on the outside by the further measuring gap 15 ', which is limited to the outside by the further stator parts 2'.
    In general, the rotational rheometers according to the invention can be used in any position or inclination, since the spatial orientation of the rotor axis A does not play a role due to the hydrodynamic bearing formed on both sides of the rotor 1 and the rotor 1 always interposes measuring gaps 15, 15 'enabling a hydrodynamic bearing the stator 2 and stator parts 2 'and other stator parts 2 " is stored. Occurring unequal weight distributions can be compensated by the hydrodynamic bearing.
    Fig. 3 shows an arrangement in which inside the elongated cylindrical stator 2 with the drive 5 permanent magnets 4, which are arranged successively with alternating polarity, are rotated. The rotor 1 in this case has the formation of a hollow cylinder with an outwardly outgoing collar 35. The inner measuring gap 15 is bounded by the outer surface of the stator 2 and by the inner surface of the rotor 1. The further measuring gap 15 'is bounded by the outer surface of the rotor 1 and by the inner surface of the stator part 2'. With another stator part 2 " the rotor 1 is fixed via the collar 35 in the longitudinal direction of the stator axis B in a substantially fixed position during its rotation. The collar 35 is formed to form a hydrodynamic bearing between the stator parts 2 'and the further stator part 2 " stored and located on both sides of him Messspalte 15 " improve measurement accuracy.
    In general, the axis of rotation of the permanent magnets 4 and the stator axis B are coaxial. Ideally, the axis of rotation A of the rotor 1 coincides with these axes. This is the case in particular when the stator axis B is oriented vertically in the measuring operation. If the stator axis B is arranged horizontally or at an angle to the horizontal, small deviations between the course of the rotor axis A and the stator axis B may occur due to the rotor weight.
    Fig. 3a shows a similar, alternative arrangement. Here, the conductive rotor 1 is driven by a rotating magnetic field generated by coils 8. Inside the stator 2, electromagnetic coils 8 distributed around the stator axis B are arranged. With a supply unit 39, a magnetic field circulating about the stator axis 2 is set up with the coils 8, with which the rotor 1 mounted rotatably about the stator 2 is driven. In order to obtain a constant shear rate over the entire measuring gap, the measuring gaps 15, 15 'and 15 "are designed so that for any distance R1 and R2 from the axis of rotation A of the rotor (or of the rotation axis B of the stator) for the associated Gap widths S1 and S2: R1 / S1 = R2 / S2 = R1 / S1 '= R2 / S2 or R1 / R2 = S1 / S2 = S17S2'
    The fluid 6 to be examined is moved through the measuring gap 15, 15 'by the rotor 1, which is represented by the inlet openings 16 and the outlet 17 in FIG. 3a.
    In this case, the two gaps 15, 15 'extend around the cylindrical surfaces of the rotor 1 with a constant gap width s (R = constant), while the gap widths around the projecting rotor part 35 widen with increasing distance S from the axis of rotation.
    Fig. 5 shows a cylindrical rotor 1, which is completely enclosed by the stator 2. The stator 2 is a container closed on all sides and filled with test fluid 6. Between the outer wall surface of the rotor 1 and the cylindrical inner wall surface of the stator 2, the measuring gap 15 is formed, which simultaneously serves as a hydrodynamic bearing. Permanent magnets 4 are supported by a carrier 43, which is rotatable about the stator 2 by a drive 5. These rotating permanent magnets 4 cause the rotation of the rotor 1 within the stator 2. The rotor 1 serving as the eddy current body is formed of electrically conductive material which is not magnetizable and non-magnetic. The stator 2 is advantageously formed of non-magnetizable and non-magnetic material. For the measurement of the rotational speed of the rotor 1, measuring units 31, 32 are provided. Also, the rotational speed of the rotating permanent magnets 4 is detected by a measuring unit 40. These measured values are evaluated by an evaluation unit 34.
    Instead of the rotating permanent magnets 4, a rotating magnetic field can be used.
    In order to improve the hydrodynamic bearing in the axial direction, the end faces of the cylinder are additionally chamfered in the axial direction. In the illustrated embodiment, the inner wall of the stator 2 is modeled on and extends approximately parallel to the end surfaces of the rotor. In order to achieve defined shear rates, the gap portion 15a may be formed on the end surfaces so that the condition R1 / R1 = S1 / S2 is satisfied again.
    Fig. 6 shows an embodiment which is almost identical in construction to the structure shown in Fig. 5. In this case, however, the at least one permanent magnet 4 is disposed within the rotor 1, and around the stator 2, with the carrier 43 driven by the drive 5, as the eddy current body 3 becomes a cage or a cup-shaped one
    Conductor loop rotates, whereby the rotor 1 is set in rotation about its axis of rotation A. Also, as shown in the drawing by way of example with the magnets 4 ', 4 ", a plurality of permanent magnets may be arranged as symmetrically as possible so that the rotor has a uniform mass distribution along its axis and the magnetic forces are symmetrical to allow the rotor to tumble in the hydrodynamic bearing prevent. The fully cylindrical rotor is stabilized in its position relative to the axis in the longitudinal direction of the stator axis B by means of soft iron parts 10 arranged on the stator 2 and facing at least one of the rotating magnets of the rotor.
    In general, predominantly cylindrical rotors with insufficient axial hydrodynamic bearing in the longitudinal direction of the rotor axis A or stator axis B by the rotor 1 and / or on the stator 2 suitably arranged magnets 9 and the opposite soft iron parts 10 can be stabilized.
    The permanent magnets 4 and the eddy current body 3 according to FIGS. 5 and 6 rotate outside the stator 2, in which the rotor 1 floats freely. The closer the specific density of the rotor 1 is to the density of the test medium 6 to be measured, the better the hydrodynamic bearing becomes. The more different the density of the rotor and the liquid to be measured, the higher the rotor speeds are chosen. In particular, speed ranges from 0.2 to 2000 rpm and even up to 10,000 or 30,000 rpm are considered, since the rotor 1 must float in the middle position, in particular when the rheometer is operated with horizontally oriented stator axis B. In general, a high torque or high speed for the rotor 1 is required, which also depends on the size of the stator 2 and the interior of the stator 2, which surrounds the rotor 1, and the dimensions of the rotor 1 and the parameters of the test medium 6.
    FIG. 7 shows a rotational rheometer in which electromagnetic coils 8 are distributed inside the stator 2 around the stator axis B. With a supply unit 39, a magnetic field rotating around the stator axis 2 is set up with the coils 8, with which the rotor 1 rotatably mounted around the stator 2 is driven. The stator 2 has on its cylindrically shaped outer surface a circumferential groove 20 in which the rotor 1 adapted to its inner surface to form the specific geometry of the measuring gap 15 to the cross-sectional shape of the recess 20 is hydrodynamically storable spaced from the surface of the recess 20 ,
    With the stator 2 ', the rotor 1 on the stator 2 in the direction of the stator axis Blagestabilisiert or amplified the magnetic reflux. Between the stator 2-facing surface of the rotor 1 and the outer surface of the stator 2, the measuring gap 15 is symmetrically extended with respect to the stator axis B and the rotor axis A and with respect to a plane E perpendicular to the axis of rotation A and to the stator axis B through the center of the measuring gap 15 runs, is formed symmetrically ist.Ganz generally be noted that in a through the axis of rotation A of the rotor 1bzw. By the Statorachse B extending section of the measuring gap 15 and the measuring gap 15 bounding surfaces of the rotor 1 and stator 2 at least a straight, kinked, bent and / or curved portion have the rotation axis A and the stator axis B inclined or with these an acute angle includes, whose vertex is directed into the interior of the measuring gap 15 and / or that the opposing surfaces of the measuring gap 15 with respect to the rotational axis A are each formed centrally symmetrical and / or that the measuring gap 15 bounding surfaces with respect to a perpendicular to the axis of rotation A extending center plane E of the measuring gap 15 respectively symmetrical. Such a construction of a measuring gap can be seen in particular from FIGS. 4 and 7.
    In the present case, the surface of the recess 20 in the stator 2 and the surfaces of the rotor 1 as well as the inner surface of the advantageously provided further stator part 2 " curved. The measuring gaps 15, 15 'change their distance; the inner measuring gap 15 becomes larger from the inside to the outside; the thickness of the outer measuring gap 15 'increases towards the outside. Accordingly, the thickness of the measuring gap 15 changes. This change in thickness is chosen so that it does not affect the maintenance of a hydrodynamic bearing.
    With measuring units 31, 32, the rotational speed of the rotor 1 is measured, which is due to the two Meßspalten 15 and 15 'existing test medium 6 is smaller than the rotational speed of the magnetic field generated by the coils 8.
    Fig. 7a shows schematically an embodiment in which the rotor 1 runs on a stator 2 whose shape substantially corresponds to a part of a cone mantle. The axial and radial bearing of the rotor takes place here on the same rotor surface, the proportions in the radial and axial direction correspond to the projections of the lateral surface on the planes through the axis of rotation and the normal thereto.
    The embodiment of the rheometer of FIG. 4, 7 and 7a can be particularly easily inserted into the wall 18 of a pipe or a container and in the Rohrbzw. Container located test medium 6 are measured. For rotational rheometers with a cone-plate measuring system, it is known that constant shear rates are achieved over the entire gap if, as shown in section in Figure 8, for the gap height s at any distance or radius r from the axis of rotation: R1 / R2 = S1 / S2. That is, the gap height s increases as the distance R from the rotation axis A of the rotor 11 increases. This condition can also be realized in rotary rheometers according to the invention, in particular in rheometers according to FIGS. 1 a, 4 and 7.
    4 shows a rotational rheometer in which the rotor 1 has a truncated cone shape and is delimited in a measuring gap 15, which, according to the above condition, has a measuring gap 15 which is sufficient for this condition and which narrows towards the axis of rotation A and the gap center plane E. The rotational rheometer shown in FIG. 7 could also fulfill this condition for measuring gaps 15, 15 'if the rotor 1, the depression 20 and the stator part 2' are appropriately reconfigured. In the illustrated embodiment, only the inside measurement gap satisfies this condition. This condition could then apply to the gap geometry used in FIG. 7, if both measuring gaps 15 and 15 'lying between the inner surface of the rotor 1 and the fixed outer surface of the stator 2 and between the outer surface of the rotor 1 and the inner surface of the stator part 2' are radial and radial to open outwards to the outside and satisfy the above condition. In this case, constant shear rates can be applied to the fluid to be assayed. In particular, non-Newtonian fluids can thus be examined in a simple manner when carrying out a calibration.
    In general, it is advantageous if all opposing measuring gaps 15bzw. 15 'delimiting surfaces are rotationally symmetric or centric symmetrical or concentric. This also applies to the eddy current body 3 and the stator parts 2 'and 2 ". Furthermore, the components used are advantageously constructed homogeneously. For the invention, it is irrelevant whether the rotor 1 rotates within a stator 2 or around the stator 2, since a hydrodynamic bearing can always be formed between the rotor 1 and the stator 2. It is easily possible for the person skilled in the art to match the thickness and geometry of the formed measuring gaps 15, 15 'as well as the dimensions of the rotor 1 and the stator 2, so that always a hydrodynamic bearing can be achieved for testing a specific test medium 6. In particular, by exchanging rotors 1 and choosing different thicknesses, lengths or specific weights of the rotors 1, an adaptation to test media 6 having different densities and / or rheological properties can be made easily. Also by a choice of the drive speeds given by rotating magnetic fields or rotating permanent magnets 4 or rotating eddy current bodies 3, an adjustment is easy to accomplish.
    The provided permanent magnets 4 or coils 8 are arranged centrally symmetrical to the rotor axis A. At least two preferably more than two permanent magnets 4 or coils 8 are provided. Longitudinally adjacent permanent magnets are arranged with opposite polarity and the coils 8 can be reversed accordingly.
    In principle, the rotational speed of the rotating magnetic field and. the drive speed by the rotation of the permanent magnets 4 and the rotational speed of the rotating magnetic field or the rotating eddy current body. These speeds are precisely measurable. To determine the desired rheological parameters, the rotor speed which occurs due to the braking of the rotor by the test medium is measured. It is possible to calibrate a rotor or rheometer with fluids of known viscosity and parameters, respectively, and to create a calibration table relating rotor rotational speeds associated with specific temperatures or pressures to actual viscosity values or rheological parameters.
    In general terms, and for example for FIGS. 1, 3 and 7, the formed hydrodynamic bearings or measurement gaps 15, 15 ', 15 " radial and axial bearing gap sections 15, 15 ', 15 " can own. The hydrodynamic bearing portions extending in the radial direction fix the position of the rotor in the longitudinal direction of the stator axis B. The bearing sections, which extend in the axial direction or in the longitudinal direction of the rotor axis A, determine the radial alignment of the rotor 1. In a rotational rheometer, as shown for example in FIG. 7, the measuring gaps 15, 15 'are not to be separated into axial and radial bearing sections.
    Due to the curvature of the measuring gaps, a radial and an axial portion are present at each point, and thus an overall hydrodynamic bearing is ensured both in the axial and in the radial direction. There are thus also spherical or elliptical or ovoid designed bearing geometries conceivable. Importantly, the projected area in the axial and radial directions is sufficient for hydrodynamic storage.
    Non-Newtonian fluids exhibit a dependency on the shear rate in their parameters, especially viscosities. In order to judge real non-Newtonian fluids, a constant shear rate would have to be applied to the fluid to be measured over the actual measurement gap. To accomplish this, the measuring gap must be carried out especially. By shear rate is meant the slope of the velocity in the gap.
    The ends of the rotors 1 used in the rotary rheometers according to the invention can be rounded or torpedo-shaped to taper to a point. In these areas, the opposing surfaces on the stator 2 and the stator parts 2 'and 2 " have a corresponding inclination or adaptation.
    The diameter of the rotors 1 is selectable; for example, rotors 1 of aluminum or copper with a diameter of 0.5 cm and a length of 3 to 4 cm or a diameter of 1 cm and a length of 15 to 20 cm can be selected; the gaps formed have gap widths of a few tenths of a millimeter, e.g. 0.2 mm or 0.5 to 1 mm, and speed values, e.g. from 500rpm in a speed range from less than 1rpm up to 10,000rpm. However, it is also possible to use rotors 1 having 20cm diameter. It is advantageous, however, if the length of the rotor is about the factor 3 to 6, in particular 4 to 5, greater than the diameter, since this case occurring edge effects are minimized and can be disregarded. The principle arbitrarily long execution of the rotor is characterized by the Handling, production conditions and cleaning limited upwards.
    It is advantageous if during the measurement in the test medium temporally and spatially constant temperature prevails. Thus, it is possible to carry out a temperature control with preferably rotationally rotationally symmetrical Peltier elements or with a liquid-tempered jacket and / or with resistance heaters.
    权利要求:
    Claims (23)
    [1]
    1. Rotational rheometer with a rotationally invariably arranged stator (2), with a by means of an eddy current drive about the axis of the stator (2) around or inside the stator (s) (2) rotatable, rotationally symmetrical and with itsrotation axis (A) coaxial with the stator axis (B) located rotor (1), wherein the test medium to be examined (6) in at least one between opposing surfaces of rotor (1) and stator (2) formed measuring gap (15) can be introduced, with a measuring unit, with the Speed of the rotor (1) which is in contact with the test medium (6) and with an evaluation unit with which the speed difference between the rotational speed applied to the rotor (1) and the rotational speed of the rotor (1) measured during the test procedure is determined determined and used as a measured value for the rheological and / or viscous properties of the test medium (6), characterized gekenn characterized in that the measuring gap (15) filled with the test medium (6) to be examined acts as a hydrodynamic bearing between the rotor (1) and stator (2) and is governed exclusively by the rotation of the rotor (1) relative to the stator (2 ) achieved hydrodynamic bearing effect of the distance and the mutual position of the mutually facing, the measuring gap (15) limiting surfaces of the rotor (1) andStator (2) predetermined and adjusted and maintained during the measurement process.
    [2]
    2. Rotationsrheometer according to claim 1, characterized in that the end regions (17) of the measuring gap with the outer regions (19) adjoining these end regions (17) or the test medium (6) located in these regions, in particular without cross-sectional constriction of the end region of the measuring gap , Communicate or the end regions (17) pass directly into these outer areas (19).
    [3]
    3. Rotationsrheometer according to claim 1 or 2, characterized in that the rotor (1), except its hydrodynamic bearing in the region of the measuring gap, inradialer direction with respect to its axis of rotation (A), free of contact and bearing, in particular free of magnetic bearings on or relative to the stator (2) is mounted.
    [4]
    4. Rotationsrheometer according to one of claims 1 to 3, characterized in that for forming the rotor (1) in rotation eddy current drive of the rotor (1), preferably in its entirety, is formed of non-magnetic, non-magnetizable, electrically conductive material and that rotatable permanent magnets (4) are mounted around the rotor (1) or at least partially within the rotor (1) around the stator axis (B) or are mounted around the rotor (1) or at least partially within the rotor (1) electromagnetic coils (8) are with whichein the rotatable about the stator axis (B) magnetic field can be generated.
    [5]
    5. Rotationsrheometer according to one of claims 1 to 4, characterized in that for forming the rotor (1) in rotation eddy current drive of the rotor (1), preferably entirely, of non-magnetic, non-magnetizable, electrically conductive material is formed and that at least Partially inside the stator (2) permanent magnets (4) or coils (8) are mounted, wherein the permanent magnets (4) about the stator axis (B) are rotatable and with the coils (8) around the stator axis (B) rotating magnetic field generated is.
    [6]
    6. Rotationsrheometer according to one of claims 1 to 5, characterized in that for forming the rotor (1) in rotation eddy current drive within the rotor (1) permanent magnets (4) arranged fixed in position or connected to the rotor (1) and that a , is preferably formed entirely of non-magnetic, non-magnetizable, electrically conductive material eddy current body (3), preferably a cage, a pot or a conductor loop, which is rotatable about the rotor (1).
    [7]
    7. Rotationsrheometer according to one of claims 1 to 6, characterized in that the rotor (1) in the interior of a rotationally symmetrical inner wall and the shape of a rotationally symmetrical container or cup having stator (2) is arranged, wherein for forming the rotor (1) in Rotating Verstellstromantriebs within the rotor (1) permanent magnets (4) arranged fixed in position or. are connected to the rotor (1) and the material of the container or cup, preferably in its entirety, is non-magnetic, non-magnetizable and electrically non-conductive material and a non-magnetic, non-magnetizable, electrically conductive material formed eddy current body (3), preferably a Pot, a cage or a conductor loop is provided, which is rotatable about the stator (2).
    [8]
    8. Rotationsrheometer according to one of claims 1 to 7, characterized in thatin a through the axis of rotation (A) of the rotor (1) or through the stator (B) extending section of the measuring gap (15) or the measuring gap (15). limiting surfaces of the rotor (1) and stator (2) have at least one straight, bent, bent and / or curved portion inclined to the axis of rotation (A) and to the stator axis (B) or with these forms an acute angle, the apex thereof is directed into the interior of the measuring gap (15) and / or that the surfaces of the measuring gap (15) lying opposite each other are centrically symmetrical with respect to the axis of rotation (A) and / or that the surfaces delimiting the measuring gap (15) are perpendicular to the axis of rotation ( A) extending median plane (E) of the measuring gap (15) each symmetrical.
    [9]
    9. rotational rheometer according to one of claims 1 to 8, characterized in that the rotor (1) cylindrical, annular, cup-shaped, conical or frustoconical or in a plane passing through the axis of rotation (A) plane in section triangular, trapezoidal or as a segment of a conic or Ovoids is trained.
    [10]
    A rotational rheometer according to any one of claims 1 to 9, characterized in that the rotor (1) is supported on at least one of its faces, i. on each of its inner surface and / or outer surface, and / or on at least one end surface, faces one face of the stator (2) or one stator part (2 ') or another stator part (2'), and the rotor (1) rotates through each other Measurement gap (15, 15 ') between the respective surfaces prevailing hydrodynamic layer action of the test fluid (6) is mounted without contact inradialer and possibly also in the axial direction with respect to the stator axis (B).
    [11]
    11. Rotationsrheometer according to one of claims 1 to 10, characterized in that the stator (2) is in the form of a closed pot or cylinder and that on this stator (2) has a shape of an open pot exhibiting rotor (1) with its interior with the formation of the measuring gap (15, 15 '), whereupon optionally additionally on the side of the rotor (1) remote from the stator (2) at a distance to the rotor (1), in particular its end and / or peripheral wall, at least one stator part (2 ') and / or another stator part (2') is located and optionally this distance between the rotor (1) and the respective stator (2 ') and further stator (2') as a hydrodynamic storage causing measuring gap (15,15 ' ) is trained.
    [12]
    12. Rotationsrheometer according to one of claims 1 to 11, characterized in that the stator (2) on its cylindrically shaped outer surface a circumferential Nutbzw. A depression (20) in which the rotor (1), which is adapted to the cross-sectional shape of the depression (20) on its inner surface to form the measuring gap (15), is hydrodynamically storable with respect to the surface of the depression (20).
    [13]
    13. A rotational rheometer according to claim 12, characterized in that on a stator (2) averted surface of the recess (20) mounted rotor (1) the surface of a stator (2 ') at a distance and to form a further measuring gap (15') hydrodynamic bearing opposite.
    [14]
    14. rotational rheometer according to one of claims 1 to 13, characterized in that for the gap width (S) of the respective measuring gap (15, 15 ') at a distance (R) from the rotation axis (A) the relationship R1 / R2 = S1 / S2 applies in which R1 and R2 are the distances of points on the surfaces bounding the measuring gap (15, 15 ') from the axis of rotation (A) of the rotor (1) and S1 and S2 in those points R1 and R2 in hydrodynamic mounting of the rotor (1 ) formed gap thickness and this thickness of the respective measuring gap (15, 15 ') with increasing distance from the rotation axis (A) increases.
    [15]
    15. Rotationsrheometer according to one of claims 1 to 14, characterized in that the geometry, preferably the distance and the distance profile of the opposing surface portions of the measuring gap (15), in particular the radial distance of the axis of rotation (A) surrounding, opposing surfaces of rotor (1 ) and stator (2) are selected to form the hydrodynamic bearing in dependence on the rotational speeds applied by the drive unit (5), a pre-estimated value of viscosity and / or pre-estimated rheological parameters of the test medium (6).
    [16]
    16. rotational rheometer according to one of claims 1 to 15, characterized in that a cylindrical peripheral surface and at most inclined endflächenaufweisender rotor (1) is provided, which on all sides by a cylindrical inner wall surface and possibly inclined end surfaces having interior of the stator (2) and within this interior space is completely enclosed by the test medium (6), wherein an eddy current body (3) is rotatably mounted around the stator (2), which preferably has the shape of a pot, a cage or a conductor loop and of non-magnetic or non-magnetizable, electrically conductive material is formed, wherein in the rotor (1) permanent magnets (4) are mounted or connected thereto.
    [17]
    17. Rotationsrheometer according to claim 16, characterized in that the stator (2) has a closable insertion opening for the test medium (6).
    [18]
    18. Rotationsrheometer according to one of claims 1 to 17, characterized in that for stabilizing the position of the rotor (1) with respect to the stator (2) in the longitudinal direction of the stator (B) on the rotor (1) and on the stator (2) oppositely cooperating permanent magnets (4 ) and soft iron parts (10) are arranged, which stabilize the longitudinal position of the rotor (1) relative to the stator axis (B) without contact.
    [19]
    19. Rotationsrheometer according to one of claims 1 to 18, characterized in that in the measuring gap (15) during rotation of the rotor (1) for forming a hydrodynamic bearing sufficiently laminar, eddy current is formed.
    [20]
    20. rotational rheometer according to one of claims 1 to 19, characterized in that the rotor (1) and / or the stator (2) and / or about the rotor (1) rotated Vortex body (3) have high electrical conductivity and optionally of Cu , Pt, Ag or Au are made.
    [21]
    21. Rotationsrheometer according to one of claims 1 to 20, characterized in that in the stator (2) heating and / or cooling units for the test medium (6) are arranged.
    [22]
    22. rotational rheometer according to one of claims 1 to 21, characterized in that on the stator (2) and / or on the rotor (1) and / or within the measuring gap (15, 15 ') non-contact measuring units for measuring the rotational speed of the rotor ( 1) and / or the drive speed given by the eddy current drive and, if appropriate, the temperature and / or the pressure and / or the density are arranged in the measuring gap (15).
    [23]
    23. Rotationsrheometer according to one of claims 1 to 22, characterized in that the axis of rotation (C) of the eddy current body (3), preferably a pot, cage or a conductor loop (3), coaxial with the axis of rotation of the rotor (1).
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    同族专利:
    公开号 | 公开日
    AT514549B1|2015-02-15|
    WO2015035437A1|2015-03-19|
    CN105874315A|2016-08-17|
    DE112014004161A5|2016-05-25|
    US20160223449A1|2016-08-04|
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    法律状态:
    2019-05-15| MM01| Lapse because of not paying annual fees|Effective date: 20180911 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50570/2013A|AT514549B1|2013-09-11|2013-09-11|Rotational|ATA50570/2013A| AT514549B1|2013-09-11|2013-09-11|Rotational|
    US15/021,358| US20160223449A1|2013-09-11|2014-08-25|Rotary rheometer|
    PCT/AT2014/050181| WO2015035437A1|2013-09-11|2014-08-25|Rotary rheometer|
    DE112014004161.0T| DE112014004161A5|2013-09-11|2014-08-25|Rotational|
    CN201480061674.0A| CN105874315A|2013-09-11|2014-08-25|Rotary rheometer|
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