• 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:
    Arrangement for calibrating a torque-measuring device (1) of a motor vehicle test bench or engine test stand (2) comprising: - a reference torque generating device (3) for generating a reference to an effective axis (4) acting reference torque, - a reference torque measuring device (5) for measuring the order of the (4) acting reference torque, - and a connecting device (6) for connecting or rotational connection of the arrangement with the torque measuring device (1) and for transmitting the reference torque to the torque-Messejnrichtung (1), wherein the reference torque generating device ( 3) has at least one actuator friction-free operable actuator (8) with a drive frictionless actuated drive member (7) for generating a reference force.
    公开号:AT517537A1
    申请号:T535/2015
    申请日:2015-08-13
    公开日:2017-02-15
    发明作者:Christian Schabiner Bsc；Manfred Hofer Ing；Dipl Ing Schochlow Andreas；Pätschke Klaus；Ing Dipl (Fh) Bernhard Aumüller；Thomas Abraham Ing；Joachim Schmidt Ing
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    Arrangement for calibrating a torque measuring device
    The invention relates to an arrangement according to the preamble of the independent claim.
    In particular, the invention relates to an arrangement that can be used in the calibration of a torque-measuring device, wherein the torque-measuring device is preferably a torque-measuring device of a motor vehicle dynamometer or an engine test bench.
    Engine test stands are known devices which typically include an input shaft, a torque measuring device coupled to the input shaft and a loading machine. In a conventional engine test bed construction coupled via a clutch with the input shaft of the test rig driving machine is driven and thereby loaded by the loading machine of the test bench. The torque acting between the loading machine and the drive machine is measured via the torque measuring device of the test bench and, if necessary, taken into account in the evaluation of acquired measured data.
    Due to ever higher demands on the measuring accuracy and the reproducibility of the test bench measurements, it is necessary to increase the measuring accuracy of the torque measuring device or the test stand. An important factor in increasing the measuring accuracy is the calibration of the torque measuring device of the test bench,
    According to the prior art, there are different possibilities for calibrating the torque measuring device. For example, a roughly horizontally projecting lifting thrust of a predefined length can be attached to the input world of the test stand. As a result, it is possible to apply weights to this lever, which bring about a defined torque on the torque measuring device via the known lever length. However, in practice this method is cumbersome and, in particular, inaccurate due to the transverse forces that occur.
    To improve this system, it is proposed according to the prior art to transfer the necessary reference force for generating the reference torque via compressed air cylinders to the lever. Furthermore, it is known for improving the calibration accuracy that the calibration device itself comprises a torque sensor whose measurement data can be used to calibrate the torque measuring device of the test bench. A disadvantage of these known constructions that only relatively small forces can be generated by compressed air cylinder. Thus, to produce sufficient torque for the test bench, the lever coupled to the input shaft must therefore be relatively long, thereby degrading the compactness of the calibration equipment.
    In addition, in conventional pneumatic cylinders, but also in conventional hydraulic cylinders, the so-called "stick-sfip effect" occurs. This effect relates to the known technical problem that for the movement of the actuating element of an actuator from the rest position, the static friction, in particular the "starting friction" occurring when starting the actuator from a rest position must be overcome.As is known, the static friction forces are greater than the sliding friction forces after overcoming the static friction to a jerky movement, which often leads to an undesirable excessive motion sequence of the actuator.
    Thus, in torque calibrator calibration arrangements there is a trade-off between * the accuracy of the reference torque that can be generated, the size of the maximum torque that can be generated, and the practicality of the application, particularly the compactness and ease of use of the assembly.
    The object of the invention is now to solve this conflict of goals.
    The object of the invention is achieved in particular by the feature combination of the independent claim.
    Optionally, the invention relates to an arrangement for calibrating a torque-measuring device of a motor vehicle dynamometer or engine dynamometer comprising a reference torque generating device for generating a reference axis acting about a reaction axis reference torque, a reference torque measuring device for measuring the effective axis acting around the axis of action reference torque, and a connecting device for connection or rotary connection the arrangement with the torque measuring device and for transmitting the reference torque to the torque measuring device.
    Optionally, it is provided that the reference torque generating device has at least one actuator which can be operated without starting friction, with a drive element which can be operated without starting friction to generate a reference force.
    Optionally, it is provided that the actuator of the
    Reference torque generating means comprises a base body, an actuating element and at least one driving friction-free operable drive member for moving the actuating element relative to the base body and for generating the reference force by elastically deforming the drive member;
    Optionally, it is provided that the actuator comprises a pressure chamber acting on the drive member, and that in the pressure chamber, a fluid, in particular a hydraulic fluid, is provided with controllable or controllable fluid pressure for elastic deformation of the drive member and for actuating the actuator.
    Optionally, it is provided that the actuator or the drive member has the functional structure of a diaphragm drive, a diaphragm cylinder, a simple bellows cylinder, a Doppelbalgzylinders, a flour bellows or bellows, wherein the functional structure of the membrane (s) or the bellows corresponding components of a elastically deformable but firm and form-stable material such as metal or steel is or are formed.
    Optionally, it is provided that the drive member comprises at least one elastically deformable first plate, wherein the first plate at least partially limits the pressure chamber and wherein the shape of the first plate and the pressure chamber for actuating the actuator by changing the fluid pressure in the pressure chamber is variable.
    Optionally, it is provided that the drive member comprises an elastically deformable first plate and an elastically deformable second plate, wherein the two plates together form a pair of plates, that the first plate and the second plate are sealed together along a closed contour that the first plate and the second plate defining the pressure chamber such that the pressure chamber extends between the first plate and the second plate, and that the shape of the first plate, the second plate and the pressure chamber for actuating the actuator by changing the fluid pressure in the pressure chamber is variable ,
    Optionally, it is provided that the arranged between the first plate and the second plate portion of the pressure chamber is flat and along the course of the plates has a larger dimension than transverse or normal to the course of the plates, and thereby characterized the functional structure of a bellows cylinder, in particular the functional structure of a simple bellows cylinder or a simple bellows cylinder is formed,
    Optionally, it is provided that the actuator comprises two or more pairs of plates, each surrounding a portion of the pressure chamber, that the pairs of plates are serially aligned transversely to the course of the plates, and thereby characterized the functional structure of a bellows cylinder, in particular the functional structure of a double bellows, a Multiple bellows or a bellows cylinder is formed.
    Optionally, it is provided that a control loop for controlling the reference torque is provided, wherein the reference variable or the desired value is a selectable or predetermined by a calibration curve torque value, wherein the feedback in the control loop actual value measured by the reference torque measuring device value, and in particular the is measured torque, and wherein the manipulated variable or the control variable is a signal for changing the pressure in or in the pressure chamber.
    Optionally, it is provided that for controlling or regulating the fluid pressure of the pressure chamber a DruGkaufbauvorrichtung, in particular a fluid pump and a shut-off element, is provided.
    If appropriate, it is provided that the shut-off element is designed as a pulse-width modulation driven digital valve.
    Optionally, it is provided that the arrangement and the actuator have a first state, in which a first reference torque is transmitted to the torque-measuring device, that the arrangement and the actuator have a second state in which a second reference torque to the Torque measuring device is transmitted, and that the reference torque at the transition between the first state to the second state at any time between the first reference torque and the second reference torque is transmitted.
    Optionally, it is provided that a reference drive train is provided, and that the reference torque generating device, the reference torque measuring device and the connecting device successively, in particular in this order sequentially, along the outgoing force from the actuator to the reference drive train are arranged.
    Optionally, it is provided that the reference torque generating device comprises at least one extension acting as a crank or cam about the effective axis, and that the reference force of the actuator for generating the reference torque acts on the extension spaced from the effective axis.
    Optionally, it is provided that the reference torque generating device comprises two actuators which can be actuated without friction, the reference forces of which act selectively or simultaneously spaced from the effective axis on opposite sides of the extension for selecting the effective direction of the reference torque.
    Optionally, it is provided that the reference torque generating device comprises two extensions acting around the effective axis as cranks or cams, wherein the extensions are arranged rotated about 180 ° to each other about the axis of action that the Referenzmomenterzeugungseinriohtung four actuators frictionless operable actuators includes, whose reference forces for selecting the Wirkriehtung the reference -Trehmoments each pairwise spaced from the axis of action on the two extensions act.
    Optionally, it is provided that the arrangement is designed as a couplable with the torque-measuring device of the motor vehicle dynamometer or the engine test module, with a base for stationary determination or fixing is provided on a component of the Kraftfährzeugprüfstandes or engine test
    Optionally, it is provided that the connecting device is designed as a coaxial and essentially torque-free and force-free coupling device with the torque-measuring device, in particular as a clutch or multi-plate clutch with radial and / or axial adjustment.
    The arrangement is suitable and / or set up in particular for the semi-automatic and / or fully automatic calibration of a torque measuring device on a motor vehicle test bench or on an engine test bench. However, if appropriate, the arrangement can also be used for calibrating a torque-measuring device in a test arrangement, that is to say independently of a test stand.
    The arrangement is characterized in particular by the fact that the reference torque generating device comprises at least one actuator, which can be actuated essentially without friction friction, with a drive member which can be actuated essentially in an arresting manner.
    An actuator which can be actuated without friction is, in particular, an actuator in which substantially no stick-slip effect occurs. In principle, the term "start-up friction-free" in all embodiments of the term "free of friction", which is defined to improve clarity by the term "startup friction" that the actuator used is largely free of the static friction that normally when starting, so when a change in position an actuating element from a rest position occurs.
    Preferably, it is provided that the actuator comprises an actuating element which can be moved by elastic deformation of a drive member relative to a base body, in this movement by elastic deformation occurs in contrast to the movement of conventional pneumatic cylinder no friction between two bodies, which also no start-up friction occurs.
    Elastic deformation in the sense of the invention corresponds to a deformation which can be reversibly reversed in particular. If necessary, slight creep effects or plastic deformations occur in the elastic deformation, but remain to such a small extent that the actuator can be moved back into its original shape several times or as often as desired by actuation of the drive member.
    Optionally, the actuator and / or the drive member, the functional structure of a diaphragm drive, a diaphragm cylinder, a simple bellows cylinder, a double bellows, a Mehrfachbalgzylinders or bellows, preferably wherein the functional structure of the membranes or the bellows corresponding components of an elastically deformable but solid and dimensionally stable material, such as made of metal or steel.
    In conventional membrane or Balgantrieben the drive member is formed of a substantially pliable membrane, such as an elastomeric membrane., However, such materials may not be suitable for solving the problem of the invention. The actuator of the present arrangement, however, comprises a drive member, which is preferably formed of a solid and dimensionally stable material or of a plurality of solid and dimensionally stable materials. The actuator of the actuator thus acts in its functional structure, i. in its basic kinematic structure, as a conventional diaphragm or Balganordnungen. However, the specific structure of the actuator according to the invention differs in principle from conventional membrane or Balganordnungen.
    In particular, the drive member comprises at least a first plate. This plate may for example be disc-shaped or plate-shaped and made of a solid and dimensionally stable material. In addition, the first plate defines a pressure chamber filled with a fluid. If the pressure of the fluid in the pressure chamber is changed, this pressure acts on the first plate. Thereby, the first plate can be deformed, whereby a movement of an actuating element is effected.
    Optionally, the drive member comprises a second plate. These second plate may be plate-shaped or disc-shaped and made of a solid and dimensionally stable material.
    The first plate is preferably sealingly connected to the second plate along a closed contour such that the pressure chamber extends between the two plates. For example, two plate-shaped plates are aligned with their concave sides to each other and along a closed contour, for example along its edge, screwed together or clamped and sealed. Preferably, the pressure chamber is formed flat and has along the course of the plates a larger dimension than transverse to the course of the plates or as along the direction of action of the actuator. In particular, the ratio of the dimensions of the flat section of the pressure chamber, ie the ratio of the dimension "along the path of the plates" to the dimension "across the path of the plates or along the effective direction of the actuator" may be about 5-10, 10-20, 20 By increasing the fluid pressure in the pressure chamber, the curvature of the plate or plates can be changed, whereby the actuator is moved relative to the main body by elastic deformation of the drive member.
    The two plates preferably form a pair of plates, wherein the pressure chamber preferably extends between the two plates. Optionally, an actuator or a drive member comprises a plurality, for example two, three, four or more pairs of plates, which are serially lined up along the effective direction of the actuator. As a series strung together in this context, a juxtaposition is referred to, in which, for example, a first pair of plates is provided on a second plate pair, so that upon actuation of the first pair of plates, the entire second plate pair is moved. By changing the fluid pressure in the pressure chamber or in the pressure chambers of an actuator, therefore, the movements of the plate pairs add up.
    To change the fluid pressure of the pressure chamber, a Druckaufbauvorriehtung is preferably provided. This includes, for example, a fluid pump and a shut-off element. The fluid pressure can be increased via the fluid pump.
    By controlling and / or regulating a shut-off element, the increased fluid pressure can be delivered to the pressure chamber or removed from the pressure chamber.
    Preferably, a control circuit for controlling the fluid pressure in the pressure chamber and / or for controlling the torque exerted by the arrangement on the torque-measuring device is provided. Preferably, the control loop is configured such that, at a transition from a first torque to a second torque, the torque is at any point in time between the first and the second torque. This means in particular that the transition from a first torque to a second torque no overshoot of the torque occurs. As a result, the accuracy of the arrangement is further improved.
    The present arrangement is particularly adapted to be used in a calibration of a torque measuring device for up to fökNm. For such large torques, it may be advantageous to keep the lever arm, so the extension as short as possible. As a result, however, high forces must be applied in order to produce the desired reference torque despite the short lever arm. In order to be able to select the reference torque exactly, the reference force emanating from the actuator should be able to be controlled or regulated in very fine steps or essentially steplessly. This is done in the present arrangement, in particular by a control and / or regulation of the fluid pressure in the pressure chamber of the starting friction-actuated actuator. For this purpose, the fluid pressure can be controlled or regulated via rapidly switchable digital valves, wherein the digital valves are preferably controlled via a pulse width modulation. As a result, the fluid pressure can be exactly metered, which allows a micro-adjustment and a realization of the smallest defined movements of the actuating element can be achieved.
    In pulse width modulation (PWM) digital valves are controlled by a PWM signal, which has a substantially constant frequency, but a variable and especially modulated pulse length. This, in contrast to other digital controls, such as e.g. For a PCM control system, only one digital valve per control edge is required. By reducing the number of valves, the complexity of the arrangement can be reduced.
    Also, the disadvantages associated with control via proportional valves or servovalves, such as high hydraulic fluid demand, high hydraulic fluid flow, hydraulic fluid loss, frictional heating of the hydraulic fluid, or elongation of the relatively long communication lines, can be overcome by the pulse width modulation controlled valves, thereby further improving efficiency ,
    The largest excitation of the hydraulic system occurs at a pulse width of about 50%. At low pulse widths of about 0% to 10% or at higher pulse widths of about 90% to 100%, the excitation of the pulsations is correspondingly lower. The range of low pulse widths is particularly suitable for high-precision control, but in which no high speed is needed. For high speeds with high accuracy, a proportional valve may additionally be provided.
    According to a preferred embodiment, conventional, fast switching valves, in particular Umsehaltventile or digital valves, can be used with a switching time of about 10ms. In contrast to conventional proportional or servo valves can be kept unchanged by using the controlled by pulse width modulation digital valves, the pressure in the pressure chamber and thus possibly the position of the actuator or the applied torque without having to spend energy. Also, the efficiency of the arrangement can be improved. As exemplary valves, standard switching valves may be used, having, for example, a switching time of about 5 ms to 15 ms, preferably about 7 ms to 12 ms or 7 ms to 10 ms. Preferably, the valves have a relatively low nominal flow rate of, for example, less than 10 l / min.
    The present arrangement in particular also has the advantage that a relatively small fluid volume is sufficient to generate the necessary forces.
    Optionally, in all embodiments, the actuators may comprise a plurality of drive members, which are serially connected in series or parallel to effect a relative movement of the actuating element relative to the main body. Optionally, a lever may be employed to effect translation of the reference force from the actuator to the reference force acting on the extension.
    Furthermore, by enlarging the pressure chamber transversely to the direction of action of the actuator, ie by increasing the effective area of the fluid pressure, the ratio between the pressure acting in the pressure chamber and the force generated by the actuator can be changed according to known physical relationships.
    Optionally, the arrangement comprises one or two substantially horizontally projecting from the axis of action lever, which may act similar to the extension as a crank or as a cam. Adjusting weights can be arranged on this lever to zero the arrangement or the entire measuring setup.
    Preferably, in all embodiments, the fluid is a hydraulic fluid, such as a hydraulic oil,
    The torque-measuring device of a test stand is often exposed to their intended use high dynamic forces, since the torque-measuring device is optionally designed as a co-rotating torque-measuring device. For example, as a torque-measuring device, a so-called torque measuring flange is used, which comprises two by the applied torque to a small extent twisted body, wherein the rotation of the two bodies with respect to each other by sensors, for example by strain gauges, detected and converted into a Drebmomentmesswert. In the calibration, however, preferably only a static torque is applied and measured, with which no high rotational or inertial forces act. For this reason, the reference torque measuring device can be made more sensitive and can thereby have a higher measuring accuracy than the torque measuring device of an engine test stand.
    The projection which acts as a crank or as a cam preferably projects substantially radially from the effective axis of the arrangement. In particular, the extension is pivotally or rotatably arranged. The actuator or actuators act on the extension to convert its reference force into a reference torque. The reference force of the actuator along the effective direction of the actuator acts. This is preferably in all embodiments a linear direction of action, the actuator and its effective direction are in particular arranged such that they act tangentially to the axis of action of the arrangement on the extension. In particular, the effective direction runs in a normal plane of the effective axis and spaced from the axis of action.
    The actuator comprises an actuating element which can be moved relative to a base body. This movement occurs in particular along the effective direction of the actuator. The actuating element may, for example, be arranged on that region of the actuator which is in operative contact with the extension. The main body is in particular that part of the actuator which is connected to the Grundgesfell the arrangement. The reference force thus acts between the extension and the basic GestuU, wherein the base frame is supported against the forces via a fixed or a fixed connection with the machine part of the test stand.
    The extension is, for example, a web projecting from an intermediate shaft. Optionally eliminates the intermediate shaft, whereby the extension is arranged directly on an element of the torque-measuring device of the arrangement.
    Preferably, the main body of the actuator is the only element of the actuator which is rigidly connected to the base frame of the arrangement. In particular, the actuator or the drive member of the actuator can be arranged at a distance from other components of the arrangement, so that there are no frictional forces during the actuation of the actuator by the relative movement. In particular, it may be advantageous to guide the supply line for the fluid into the pressure chamber through the main body, whereby flexible lines can be dispensed with. For example, the supply line runs through the main body essentially in the effective direction of the actuator,
    The invention will be further described with reference to concrete, non-limiting embodiments and with reference to the figures, wherein Fig. 1 is a schematic side view of an arrangement and a test stand, Fig. 2 shows a section of the arrangement along the axis of action, Fig. 3 is a section of the arrangement normal 4 shows a detail from FIG. 3 and FIG. 5 shows a schematic view with a control loop for regulating the arrangement.
    Unless otherwise indicated, the reference numerals correspond to the following components: torque measuring device 1, engine test bench or test bench 2, reference torque generating device 3, effective axis 4, reference torque measuring device 5, connecting device 6, drive element 7,
    Actuator 8, base body 9, actuating element 10, pressure chamber 11, fluid 12, first plate 13, second plate 14, plate pair 15, control circuit 16, automation system or data processing device 17, interface 18, control panel 19, pressure build-up device 20, fluid pump 21, shut-off element 22,
    Reference drive train 23, extension 24, base frame 25, contour 26, drive machine 27, input shaft (of the test stand) 28, loading machine 29, power supply 30, hydraulic components 31, control device 32.
    Fig. 1 shows a schematic side view of the arrangement with a Mötorenprüfstand 2, wherein instead of a drive machine 27, an inventive arrangement is coupled to the engine test stand 2. The engine test bench 2 comprises an input shaft 28, a loading machine 29, and a torque measuring device 1. The arrangement according to FIG. 1 comprises a reference torque generating device 3, a reference torque measuring device 5, and a connecting device 6. The connecting device 6 is suitable and / or adapted for this purpose. to couple the assembly with the torque measuring device 1. Preferably, the connecting device 6 is suitable and / or set up, a coaxial alignment of the axis of action 4 of the arrangement with the
    To allow rotation of the torque measuring device 1. In particular, it is advantageous if the connecting device 6 can produce a torque-free or force-free connection between the arrangement and the torque-measuring device. For this purpose, the connecting device 6 may have a radial and / or axial adjustment. Exemplary connecting devices are multi-plate clutches, which are specially designed for connection to test benches.
    The arrangement is designed in particular as a module dockable to a test stand. The arrangement preferably comprises a base frame 25, via which the arrangement can be fixed or fixed on the machine part of a test rig. Thus, the drive machine 27 can be separated from the test stand 2 at a desired time in order to couple the arrangement according to the invention with the test stand. After calibration or after the recording of the data necessary for the calibration, the arrangement can be removed again in order subsequently to connect the same or another drive machine 27 to the test stand 2.
    2 shows a schematic sectional illustration of an arrangement according to the invention comprising a reference torque generating direction 3, a reference torque measuring device 5, and a connecting device 6. The reference torque generating device 3 comprises an extension 24 and an actuator 8 which optionally acts on the extension 24. The extension 24 preferably acts as a crank or Nock and extends to at least partially radially outward from the axis of action 4 of the arrangement. By orders of a force acting tangentially to the active axis 4 on the extension 24, the linear acting reference force of the actuator 8 can be converted into a force acting around the active axis 4 reference torque. Starting from the actuator 8 thus the force flow runs on the extension 24, from the extension 24 optionally via an intermediate shaft to the reference torque measuring device 5 and on to the connecting device 6, these components together form a reference drive train 23. The extension 24, the optionally provided intermediate shaft, the Reference torque measuring device 5 and the connecting device 6 are preferably pivotally or rotatably arranged in all embodiments relative to the base frame or opposite the test stand 2 in order to transmit a torque to the torque-measuring device 1 can. In practice, a torque measurement by a conventional torque measuring device 1 and / or by the conventional reference torque measuring device 5 is often only possible if there is an at least slight relative rotation of two components against each other, since the torque measurement takes place via a detection of a rotation second body against each other , By way of example, twists of up to 0.2 ° can occur at a reference torque of about 5 kNm to about TOkNm.
    The schematically illustrated connection device 6 is preferably suitable or arranged in all embodiments for the coaxial, torque-free and / or force-free arrangement of the effective axis 4 relative to the axis of rotation of the test bench, in particular to the axis of rotation of the input shaft 28 or the torque measuring device 1.
    FIG. 3 shows a further schematic sectional illustration, wherein the sectional plane is essentially a normal plane of the effective axis 4 of the arrangement, with which the effective axis 4 in the present representation runs essentially projecting.
    The arrangement comprises a reference torque generating device 3 for generating a reference torque. The reference torque generating device 3 comprises an extension 24. The extension 24 acts in particular as a crank or as a cam. The arrangement comprises at least one actuator 8, which acts on the extension 24 in order to generate a torque about the effective axis 4. In the present embodiment, two actuators 8 are provided, which can selectively or simultaneously act on opposite sides of the extension 24 in order to make a choice of the effective direction and the magnitude of the torque can.
    For example, in the present view, a clockwise torque may be caused by the right side actuator 8 and a counterclockwise torque by the left side actuator 8. Optionally, both actuators can also be constantly in operative contact with the extension 24, so that the force acting on the extension 24 resulting reference force by vector addition of the two forces exerted by the two actuators 8 forces. Alternatively, in each case only one actuator 8 is in operative contact with the extension 24, so that the reference force acting on the extension 24 corresponds to the force of the respectively active actuator 8. The arrangement according to FIG. 3 again comprises a base frame 25, which in the present embodiment is fixedly fixed to the floor.
    4 shows a detail of the reference torque generating device 3 of FIG. 3. The reference torque generating device 3 comprises an extension 24 and at least one actuator 8. The actuator S comprises a base body 9, an actuating element 10, and a drive member 7 for moving the actuating element 10 relative to the Base body 9. According to the present embodiment, a pressure chamber 11 is provided, which is filled with a fluid 12. The fluid 12 is preferably a hydraulic fluid in all embodiments. By changing the fluid pressure in the pressure chamber 11, the drive member 7 can be deformed. For this purpose, the drive member 7 may have the functional structure of a diaphragm cylinder, a bellows cylinder or a bellows cylinder.
    In the present embodiment, the shape of the drive member 7 substantially corresponds to the functional structure of a double bellows cylinder and a double bellows cylinder. Thus, the actuator 8 or the drive member 7 has a first plate 13. By increasing the fluid pressure in the pressure chamber 11, for example, a curvature of this first plate 13 take place, whereby the actuating element 10 is moved relative to the base body 9 and exerts a reference force on the extension 24. Optionally, a second plate 14 may be provided. Preferably, the second plate 14 is elastically deformed when the pressure in the pressure chamber 11 changes. Thus, for example, by increasing the pressure, the second plate 14 can be arched, whereby a displacement of the entire first plate and thereby an additional movement of the actuating element 11 relative to the base body ö is effected.
    Preferably, the first plate 13 and the second plate 14 are sealed together along a closed contour 26, so that a pressure chamber 11 is formed. This pressure chamber 11 has a flat shape, in particular in the region between the first plate 13 and the second plate 14. Due to this flat shape, the areal extent of the pressure chamber 11 is increased normal to the direction of action of the actuator, thus positively affecting the relationship between pressure prevailing in the chamber and applied force of the actuator. The two plates 13, 14 together form a pair of plates 15. In the present embodiment, the actuator 8 or the drive member 7 has two plate pairs 15, which are serially connected and in particular serially aligned along the effective direction of the actuator. Preferably, however, the pressure chamber 11 extends between the plates 13, 14 of both plate pairs 15. If necessary, however, a separately controllable pressure chamber 11 is provided per plate pair 15 in all embodiments.
    In the present embodiment, the reference torque generating device 3 has two actuators 8, wherein the two actuators 8 are optionally configured the same. By selectively or simultaneously actuating the actuators 8, the direction and magnitude of the reference torque generated by the extension 24 can be selected.
    5 shows a schematic view of components of the arrangement and a control circuit 16 for regulating the arrangement and in particular for regulating the reference torque. The arrangement is preferably modular and optionally comprises all components which are arranged within the dashed rectangle of FIG. 5. In particular, the arrangement comprises a reference torque generating device 3, a reference torque measuring device 5 and a connecting device 6. The connecting device 6 is set up to establish a connection or a coupling to the torque measuring device 1 to be calibrated.
    The arrangement preferably comprises in all embodiments hydraulic components 31, such as a pressure build-up device 20 with a fluid pump 21 and a shut-off element 22 for establishing the fluid pressure in the pressure chamber. The arrangement preferably also includes a power supply 30.
    Preferably, a data processing device 17, an interface 18 and a control panel 19 are provided.
    Upon actuation of the reference torque generator 3, a reference torque is generated. This reference torque is measured on the one hand by the reference torque measuring device 5 and on the other hand transmitted by the connecting device 6 to the torque measuring device 1. In order to transmit a desired torque to the torque measuring device 1 for calibration, a control circuit 16 is preferably provided in all embodiments. The control circuit 16 includes a control device 32. The desired reference torque preferably forms the command variable or the setpoint value of the control loop. As a manipulated variable or control variable is preferably a signal for changing the pressure in one or in the pressure chamber or in a plurality of pressure chambers. In particular, a shut-off element 22 is provided, through the control or regulation of which the fluid pressure of the fluid 12 in the pressure chamber 11 can be controlled or regulated. The reference torque which is modified by the pressure in the pressure chamber 11 is measured by the reference torque measuring device 5, a signal of the reference torque measuring device 5 preferably being fed back as the actual value in the control loop 16 in order to bring about a regulation of the torque measured by the reference torque measuring device 5 to the desired torque ,
    In a data processing device 17, which may in particular be part of the test stand 2 or part of the present arrangement, the measurement data of the torque measuring device 1 are optionally stored and / or compared with the torque measurement data of the reference torque measuring device 5 to the desired calibration of the torque To be able to make measuring device 1.
    According to a further embodiment, the
    Reference torque generating means 3 comprise a further extension 24 and one or more further actuators 8, wherein the second extension 24 is arranged rotated substantially 180 ° about the Wirkaehse, By orders of two forces on opposite extensions 24 lateral forces can be reduced and the Katibriergenauigkeit be improved. This embodiment can optionally be provided and is shown in broken lines in FIG. 3.
    In general, it is noted that the invention is determined in particular by the features of the claims and is in no way limited to the stated embodiments. Optionally, the embodiments of Figures 1 to 5 are different embodiments. Optionally, the embodiments of Figs. 1 to 5 all show the same embodiment.
    权利要求:
    Claims (18)
    [1]
    claims
    1. A device for calibrating a torque-measuring device (1) of a motor vehicle test bench or engine test stand (2) comprising: - a reference torque generating device (3) for generating a reference axis (4) acting reference torque, - a reference torque measuring device (5) for measuring the 4) acting reference axis, and a connecting device (6) for connection or rotational connection of the arrangement with the torque-measuring device (1) and for transmitting the reference torque to the torque-measuring device (1), characterized in that the reference torque generating device (3) has at least one actuator (8) which can be actuated without friction against friction and with a driving member (7) which can be actuated without causing any friction to generate a reference force.
    [2]
    2. Arrangement according to claim 1, characterized in that the actuator (8) of the reference torque generating device (3) has a base body (9), an actuating element (10) and at least one drive frictionless operable drive member (7) for movement of the actuating element (10) relative to the Grand body (9) and for generating the reference force by elastically deforming the drive member (7).
    [3]
    3. Arrangement according to claim 1 or 2, characterized in that the actuator (8) on the drive member (7) acting pressure chamber (11), and in that the pressure chamber (11) a fluid (12), in particular a hydraulic fluid, with controllable or controllable fluid pressure for elastic deformation of the drive member (: 7.) And for actuating the actuator (8) is provided.
    [4]
    4. Arrangement according to one of claims 1 to 3, characterized in that the actuator (8) or the drive member (7) has the functional structure of a diaphragm actuator, a diaphragm cylinder, a simple bellows cylinder, a double bellows cylinder, a Mehrfachbalgzyfinders or a bellows cylinder, wherein the components corresponding to the functional structure of the membrane (s) or of the bellows are or are formed from an elastically deformable but firm and dimensionally stable material such as metal or steel.
    [5]
    5. Arrangement according to one of claims 3 and 4, characterized in that the drive member (7) comprises at least one elastically deformable first plate (13), wherein the first plate (13) the pressure chamber (11) at least partially limited and wherein the shape the first plate (13) and the pressure chamber (11) for actuating the actuator (8) by changing the fluid pressure in the pressure chamber (11) is variable
    [6]
    6, arrangement according to one of claims 3 to 5, characterized in that the drive member comprises an elastically deformable first plate (13) and an elastically deformable second plate (14), wherein the two plates together form a pair of plates (15) that the the first plate (13) and the second plate (14) are sealed together along a closed contour (26) such that the first plate (13) and the second plate (14) define the pressure chamber (11) such that the Pressure chamber (11) between the first plate (13) and the second plate (14) extends, and that the shape of the first plate (13), the second plate (14) and the pressure chamber (11) for actuating the actuator (8) by changing the fluid pressure in the pressure chamber (11) is variable.
    [7]
    7, arrangement according to one of claims 3 to 5, characterized in that the drive member comprises an elastically deformable first plate (13) and an elastically deformable second plate (14), wherein the two plates together form a pair of plates (15) that the the first plate (13) and the second plate (14) are sealed together along a closed contour (16) such that the first plate (13) and the second plate (14) define the pressure chamber (11) such that the Pressure chamber (11) between the first plate (13) and the second plate (14) that the shape of the first plate (13), the second plate (14) and the pressure chamber (11) for actuating the actuator (8) by Variation of the fluid pressure in the pressure chamber (11) is variable, that between the first plate (13) and the second plate (14) arranged portion of the pressure chamber (11) is formed flat and along the course of the plates (13,14) a larger dimension than transverse or normal to the course of the plates (13,14), and that thereby the functional structure of a bellows cylinder, in particular the functional structure of a simple bellows cylinder or a simple bellows is formed.
    [8]
    8, arrangement according to one of claims 1 to 7, characterized in that the drive member comprises an elastically deformable first plate (13) and an elastically deformable second plate (14), wherein the two plates together form a pair of plates (15) that the the first plate (13) and the second plate (14) are sealed together along a closed contour (16) such that the first plate (13) and the second plate (14) define the pressure chamber (11) such that the pressure chamber (11) between the first plate (13) and the second plate (14), that the shape of the first plate (13), the second plate (14) and the pressure chamber (11) for actuating the actuator (8) by changing of the fluid pressure in the pressure chamber (11) is variable, that the actuator comprises two or more pairs of plates (15) each surrounding a portion of the pressure chamber (11) that the plate pairs (15) transverse to the course of the plates (13, 14) serially strung together, u nd that thereby the functional structure of a bellows cylinder, in particular the functional structure of a double bellows cylinder, a Mehrfachbalgzylinders or a Faltenbalgzylinders is formed.
    [9]
    9. Arrangement according to one of claims 3 to 8, characterized in that a control circuit (16) is provided for regulating the reference torque, - wherein the reference variable or the desired value is a selectable or predetermined by a calibration curve torque value, - wherein the in Control loop (16) is a value measured by the Referenzmomentmesseinriehtung (5), and in particular the measured torque is - and wherein the manipulated variable or the control variable is a signal for changing the pressure in or in the pressure chamber (11).
    [10]
    10. Arrangement according to one of claims 3 to 9, characterized in that for controlling or regulating the fluid pressure of the pressure chamber (11) DruekaufbauvorriGhtung (20), in particular a fluid pump (21) and a shut-off element (22) is provided.
    [11]
    11. Arrangement according to one of claims 3 to 10, characterized in that for controlling or regulating the fluid pressure of the pressure chamber (11) a pressure build-up device (20), in particular a fluid pump (21) and a shut-off element (22) is provided, and the shut-off element (22) is designed as a digital valve actuated by pulse width modulation.
    [12]
    12. Arrangement according to one of claims 3 to 11, characterized in that a control circuit (16) is provided for regulating the reference torque, -wobei the reference variable (17) or the desired value (17) a selectable or predetermined by a calibration curve torque value wherein the actual value (18) returned in the control circuit (16) is a value measured by the reference torque measuring device (5), and in particular the measured torque, and wherein the manipulated variable (19) or the control variable (19) is a signal for varying the pressure in or in the pressure chamber (11) is that the arrangement and the actuator (8) have a first state in which a first reference torque is transmitted to the torque-measuring device (1) that the arrangement and the actuator have a second state in which a second reference torque is transmitted to the torque-measuring device (1), and that the reference torque at the transition between the first State is at the second state at any time between the first reference torque and the second reference torque,
    [13]
    13. Arrangement according to one of claims 1 to 12, characterized in that a reference drive train (23) is provided, and that the reference torque generating means (3), the reference torque measuring device (5) and the connecting device (6) successively along the from the actuator (8) outgoing Kraftfius on the reference drive train (23) are arranged.
    [14]
    14. Arrangement according to one of claims 1 to 13, characterized in that the reference torque generating means (3) at least one about the active axis (4) acting as a crank or cam extension (24), and that the reference force of the actuator (8) for generating the reference torque at a distance from the axis of action (4) acts on the extension (24).
    [15]
    15. Arrangement according to one of claims 1 to 14, characterized in that the reference torque generating means (3) at least one about the active axis (4) acting as a crank or cam extension (24), and that the reference torque generating means (3) two frictionless operable actuators (8) whose reference forces for selecting the effective direction of the reference torque optionally or simultaneously spaced from the effective axis (4) act on opposite sides of the extension (24).
    [16]
    16. Arrangement according to one of claims 1 to 15, characterized in that the reference moment generating means (3) comprises two about the active axis (4) acting as cranks or cam extensions (24), wherein the projections (24) about 180 ° about the axis of action (4) are arranged twisted relative to one another such that the reference moment generating device (3) comprises four actuators (8) which can be actuated without friction and whose reference forces act to couple the direction of action of the reference torque in pairs spaced from the effective axis (4) to the two extensions (24) ,
    [17]
    17. Arrangement according to one of claims 1 to 16, characterized in that the arrangement as with the torque-measuring device (1) of the motor vehicle test stand or the engine test stand (2) couplable module is formed, wherein a base frame (25) for stationary fixing or for Determination is provided on a component of the vehicle dynamometer or engine test stand (2).
    [18]
    18. Arrangement according to one of claims 1 to 17, characterized in that the connecting device (6) as a coaxial and substantially torque-free and force-free with the torque-measuring device (1) coupleable connecting device (6), in particular as a clutch or multi-plate clutch with radial and / or axial adjustment is formed,
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    同族专利:
    公开号 | 公开日
    AT517537B1|2021-03-15|
    EP3335022B1|2019-08-07|
    WO2017025623A1|2017-02-16|
    EP3335022A1|2018-06-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    AT523168B1|2020-03-18|2021-06-15|Avl List Gmbh|Method for adjusting a piezoelectric torque sensor|DE2952024C2|1979-12-22|1983-04-28|Carl Schenck Ag, 6100 Darmstadt|Load device for generating and transmitting forces, in particular for calibrating force measuring devices|
    FR2677449B1|1991-06-07|1993-10-15|Technomesure|METHOD AND DEVICE FOR CALIBRATION OF COUPLEMETERS AND COMPACT COUPLEMETER ADAPTED TO THE DEVICE.|
    DE102006055614A1|2006-11-24|2008-05-29|Horiba Automotive Test Systems Gmbh|Apparatus and method for calibrating torque measuring devices|
    DE102007040106B4|2007-08-24|2017-12-07|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|Calibration device and method for calibration|
    AT11331U3|2010-01-14|2011-01-15|Avl List Gmbh|METHOD AND DEVICE FOR CALIBRATING A TORQUE MEASUREMENT DEVICE|
    EP2397832A3|2010-06-21|2016-12-21|Horiba, Ltd.|Automatic torque calibration device|
    CH705262B1|2011-07-08|2015-09-30|Markus Lindegger|Torque Tester.|
    CN103969043A|2013-02-05|2014-08-06|中机生产力促进中心|Hydraulic-servo dynamic torque loading system|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA535/2015A|AT517537B1|2015-08-13|2015-08-13|Arrangement for calibrating a torque measuring device|ATA535/2015A| AT517537B1|2015-08-13|2015-08-13|Arrangement for calibrating a torque measuring device|
    EP16750451.3A| EP3335022B1|2015-08-13|2016-08-12|Arrangement for calibrating a torque-measuring device|
    PCT/EP2016/069225| WO2017025623A1|2015-08-13|2016-08-12|Arrangement for calibrating a torque-measuring device|
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