EP4143439A1 - Détection d'état sur des pompes à vis excentrique - Google Patents

Détection d'état sur des pompes à vis excentrique

Info

Publication number
EP4143439A1
EP4143439A1 EP21722421.1A EP21722421A EP4143439A1 EP 4143439 A1 EP4143439 A1 EP 4143439A1 EP 21722421 A EP21722421 A EP 21722421A EP 4143439 A1 EP4143439 A1 EP 4143439A1
Authority
EP
European Patent Office
Prior art keywords
rotor
sensor
state
eccentric screw
screw pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21722421.1A
Other languages
German (de)
English (en)
Inventor
Michael ROLFES
Nadja Hüdepohl
Peter HARTOGH
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Vogelsang GmbH and Co KG
Original Assignee
Vogelsang GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Vogelsang GmbH and Co KG filed Critical Vogelsang GmbH and Co KG
Publication of EP4143439A1 publication Critical patent/EP4143439A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/022—Stopping, starting, unloading or idling control by means of pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/803—Electric connectors or cables; Fittings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • F04C2250/201—Geometry of the rotor conical shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/16—Wear
    • F04C2270/165—Controlled or regulated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/17—Tolerance; Play; Gap
    • F04C2270/175—Controlled or regulated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/80—Diagnostics

Definitions

  • the invention relates to an eccentric screw pump, with a pump housing with a pump inlet opening and a pump outlet opening, a stator arranged in the pump housing, a rotor of a drive unit arranged in the stator, comprising a drive motor and a drive shaft which connects the drive motor to the rotor for transmitting a torque, wherein the rotor is guided for a rotating movement around a rotating axis in the stator and a state sensor for detecting a state variable of the eccentric screw pump .
  • Eccentric screw pumps are used to convey various media in a variety of applications. Eccentric screw pumps work on the principle of a volume displacement pump and for this purpose have a rotor which is driven in a rotation around its own rotor longitudinal axis in a stator, this rotor longitudinal axis in turn being rotated around a spaced apart, usually parallel, stator longitudinal axis, so that a Rotation of the rotor about the longitudinal axis of the stator and a rotation of the rotor about the longitudinal axis of the rotor as an eccentric rotation results in a superimposed movement of the rotor in the stator.
  • Eccentric screw pumps can be used for defined and plannable volume delivery by executing a certain number of revolutions that are proportional to the desired delivery volume.
  • Eccentric screw pumps are often used in plant construction and are often used to supply a liquid loaded with foreign bodies.
  • a failure of the eccentric screw pump is often synonymous with a longer downtime of the entire plant, which is associated with considerable disadvantages for the user.
  • a failure of an eccentric screw pump can be traced back to many causes.
  • a frequent cause of failure is excessive wear on the stator, which in many types of eccentric screw pumps is made as a jacket construction from a rubber material or other elastomer, and in which there is a rotor made of metal, so that the wear that occurs between the rotor and stator is often essentially Affects stator side.
  • the tumbling form of movement caused by the eccentric movement also requires a corresponding mounting and, on the drive side, a corresponding torque transmission via a wobble shaft, which is often designed with two cardan joints.
  • the wobble shaft is designed as a flexural torsion bar, which means that the two cardan joints in the drive train can be dispensed with and a cause of wear and failure can be avoided.
  • this design is not suitable for pumps with a high throughput volume, because larger eccentricities are advantageous here and is therefore limited to smaller pump designs.
  • An eccentric screw pump type is previously known from EP 2 944 819 B1, which enables a greatly reduced repair time for replacing a rotor or stator of the eccentric screw pump.
  • DE 100 63 953 A1 provides for the monitoring of certain operating parameters of an eccentric screw pump by arranging pressure transducers, temperature sensors and vibration sensors in the area of the joints or bearings or in the area of the rotor or stator.
  • This measuring principle follows an approach which for other types of pumps, namely for example from JP 60-150491 A or DE 19649766 A already known principle of condition monitoring by evaluating temperature or vibration values to gain a statement about the wear condition of the pump.
  • this approach is based on the fact that due to the specific vibration state caused by the eccentric movement in eccentric screw pumps, an arrangement of several different sensors is provided in order to be able to detect an operating state that indicates wear from the normal operating state of the eccentric screw pump with sufficient reliability.
  • this sensor arrangement in the pump outlet also makes it easier to assemble and disassemble than with the previously known solutions.
  • the arrangement of the sensor has the disadvantage that a statement about the operating pressure of the pump, and indirectly derived from this, a statement about the torque should be made by means of a specific evaluation method and by comparison to calibrated comparison values, which to a considerable extent depends on the pumped medium and influences depends in the pipe network at the pump outlet. Conditions of wear and tear, in particular those that require maintenance, or make this necessary at a predictable point in time in the future, cannot be reliably detected with this measured value acquisition and evaluation.
  • an eccentric screw pump with a conical design of rotor and stator which provides an axial adjustment option between rotor and stator and thereby allows adjustment of the gap between rotor and stator.
  • the starting behavior and the stopping behavior of the pump can be designed by controlling the axial infeed by means of an axial infeed from rotor to stator, and if there were knowledge of the wear and operating conditions of the pump, such an axial adjustment between rotor and stator can be more wear-intensive Operating state, if it is recorded, can be avoided in very rapid control, quasi in real time, specifically in the form of a control behavior or a control loop.
  • a state variable is detected directly on the rotor or on the drive shaft.
  • a state variable is to be understood here as a physical variable that is detected by means of a sensor device.
  • This physical variable can be, for example, a temperature, a fluid pressure, a strain, a material tension, an alignment with respect to the direction of gravity, a speed according to absolute height and / or direction, or an acceleration according to absolute height and / or direction.
  • this state variable is detected either by a state sensor which, according to a first alternative, is arranged on the rotor or the drive shaft. In this first alternative, the state sensor is therefore attached directly to the rotor or the drive shaft.
  • the condition sensor can for example be fastened to the outer surface of the rotor or drive shaft, embedded in it, or arranged and fastened in an inner cavity of the rotor or the drive shaft, in particular in such a way that, starting from a cavity of a formed rotor or a hollow shaft as the drive shaft, the condition sensor is arranged on an inner surface of this cavity or, starting from this cavity, in a channel which extends to the outer surface of the rotor or drive shaft and can optionally also penetrate this outer surface, is arranged.
  • the state variable can, according to the invention, take place by means of a state sensor which is connected to the rotor or the drive shaft by means of a signal line and is itself spaced apart from the rotor and drive shaft.
  • the condition sensor is arranged at a distance from the rotor or drive shaft and is connected to the rotor or drive shaft by means of a signal line.
  • an objectively designed signal line i.e. no data transmission by radio waves or the like, is designed to convey a physical state variable via the signal line from a detection point on the rotor or on the drive shaft to the state sensor.
  • a pressure that is detected directly on the surface of the rotor or drive shaft can be diverted away from the detection location and detected elsewhere by the condition sensor.
  • the signal line extends from the condition sensor to an end point that is arranged directly on the rotor or on the drive shaft, as explained above for the condition sensor arranged directly on the rotor or on the drive shaft.
  • a direct measured variable is recorded on the eccentric screw pump, which enables a direct conclusion to be drawn about a measured value relevant to the operating state of the eccentric screw pump.
  • This direct detection makes it possible, on the one hand, to directly record physical quantities that are directly related to the rotation of the rotor or the drive shaft, for example pressure ratios, accelerations or vibration values, such as an amplitude or a frequency of the pressure or an acceleration caused by the rotation capture in real time.
  • a temperature and its possible rise can also be detected in real time at a position at which a temperature peak typically occurs within the entire eccentric screw pump.
  • vibration measurements by means of a sensor arranged, for example, on the outer wall of the housing, the transport and propagation of the vibration waves from the source to the sensor must always be taken into account when evaluating the vibration signal.
  • Material and structural dynamic properties play a role here, such as the The rigidity of the overall structure and the resulting natural frequencies play a decisive role.
  • the damping properties of the conveyed medium and the stator are a decisive disadvantage of this. Due to the many influencing factors, a complex structural analysis of the system and a modal analysis of the measurement signal are necessary.
  • condition sensor Due to the arrangement of the condition sensor on the rotor or the drive shaft, the condition sensor rotates with the rotor or the drive shaft and can thus record a 360 ° profile, whereby a cross-sectional measurement of the condition is achieved.
  • the informative value of such a measurement is much better and more precise than a measurement with a condition sensor arranged in a stationary manner on the eccentric screw pump.
  • the invention is based, inter alia, on the knowledge that an indirect acquisition of physical quantities and a calculation derived therefrom of critical operating parameters that can be derived therefrom on the one hand has the disadvantage that monitoring in real time due to the necessary comparative calculations, the necessary calculation steps per se and the necessity To compare integral time periods in this case is not reliable and sufficiently effective it enables an operating state that would lead to increased wear to be recognized and avoided by appropriate control measures.
  • real-time recording of the state variable on the rotor or the drive shaft is also suitable for controlling control variables of a conically designed rotor-stator arrangement in such a way that predetermined operating states of the eccentric screw pump are targeted by axial adjustment between rotor and stator or by adjusting the eccentricity or predetermined operating state curves of the eccentric screw pump are run through in a closed control loop.
  • the state sensor is arranged within the rotor or within the drive shaft or the signal line ends within the rotor or within the drive shaft.
  • the state variable is detected within the rotor or the drive shaft.
  • the rotor or the drive shaft can be designed with an inner cavity, for example designed as a roll rotor or as a hollow shaft, and the condition sensor or the end of the signal line can then be arranged and fastened in this cavity.
  • condition sensor is connected to an electronic evaluation unit in a wired manner via a sensor cable and the sensor cable or if the signal line runs within a section of the drive shaft and possibly within a section of the rotor.
  • a sensor signal cable runs, which carries the sensor signal electrically or as a light guide or in some other way from the condition sensor attached to the drive shaft or to the rotor leads to an electronic evaluation unit, or in the case of a condition sensor arranged at a distance from the drive shaft or the rotor, the signal line runs through a section of the drive shaft and possibly within a section of the rotor. This course enables a protected placement of the sensor signal cable or the signal line.
  • the sensor cable or the signal line can extend along the entire drive shaft and along the entire drive train to the end point or attachment point of the condition sensor on the rotor or on the drive shaft and in this case run in sections through the drive shaft or the rotor or both. fen. This enables an overall protected course of the sensor cable or the signal line and a routing of the sensor signal by means of corresponding transmission elements from the rotating shaft of the drive train to a stationary transmission unit.
  • the drive shaft is a wobble shaft, which is connected at its end facing the drive motor with the drive motor for rotation about a drive axis, and at its end facing the rotor with the rotor for rotation around a rotor axis and the superimposed Rotation is connected to an eccentric axis spaced from the rotor axis.
  • the eccentric rotational movement of the rotor is transmitted by means of a wobble shaft as the drive shaft.
  • This wobble shaft is rotatably mounted on the connection side to the drive motor and connected to the rotor at the connection point to the rotor and carries out the eccentric rotational movement of the rotor and the rotational movement of the rotor about its longitudinal axis at this point.
  • This wobble wave can basically be designed as a flexible rod in order to transmit a rotation around small eccentricities.
  • the wobble shaft has a wobble shaft center section, a first cardan joint and a second cardan joint, and the first cardan joint is inserted between the wobble shaft center section and the drive motor and the second cardan joint is inserted between the wobble shaft center section and the rotor.
  • Such a configuration provides a wobble shaft that is also suitable for large eccentricities and high torques, in that two spaced-apart universal joints are provided.
  • a universal joint is to be understood as any joint that a rotation with a can transmit angled shaft guide, for example, a pin joint or other designs.
  • the sensor cable or the signal line is led into the first and / or the second cardan joint, or is passed through the first and optionally through the second cardan joint, or around the first and / or the second cardan joint. or the second universal joint is passed around.
  • introduction or passage through the first and / or the second universal joint is advantageous, in particular this can also be combined with passage of the sensor cable or the signal line through the central section of the wobble wave.
  • wobble shafts with universal joints are sealed against the pumped medium by means of a protective hose that is arranged around and seals each universal joint, or a protective hose that extends over both universal joints and the central section of the wobble shaft, sealed against the pumped medium.
  • the sensor cable or the signal line can also be laid between this protective hose and the wobble shaft and is thus also laid so that it is protected from the pump medium.
  • the sensor cable or the signal line can also be incorporated into such a protective tube or placed between two protective tubes arranged as a double sheath or the like in order to protect the sensor cable from mechanical stresses caused by the wobble wave.
  • first universal joint is enclosed by a first sealing sleeve and the second universal joint is enclosed by a second sealing sleeve or the first and second universal joint and the tumbling shaft are enclosed by a sealing sleeve, and that in the first and / or or the second sealing sleeve or a pressure sensor is arranged in the sealing sleeve, or a pressure line is guided into the first and / or the second sealing sleeve or in the sealing sleeve and a pressure sensor is in fluid connection with the pressure line for detecting the pressure in the first and / or second sealing sleeve or in the sealing sleeve, and the pressure sensor are connected for signaling purposes to an evaluation device which is designed to detect the pressure within the first and / or second sealing sleeve or within the sealing sleeve by means of the pressure sensor, the pressure sensor preferably being the Pressure of a pressure line guided into the first and / or the second sealing collar or into the sealing envelope or pressure
  • a pressure sensor is arranged within one of the sealing sleeves or the sealing sleeve or a pressure sensor in each of the sealing sleeves, or a pressure line is used as the signal line, which correspondingly into a first or second sealing sleeve around the first or second universal joint or in a common sealing sleeve of the first or second universal joint is inserted and detects a pressure within these sealing sleeves or the sealing sleeve.
  • a first pressure sensor can also be provided, which is arranged inside the first sealing sleeve or is connected to a pressure line that opens into the first sealing sleeve, and a second pressure sensor, which is arranged inside the second sealing sleeve or is connected to a pressure line, which is in the second sealing sleeve opens.
  • the invention enables the sealing sleeve to be sealed or replaced before such wear has occurred, which then necessitates an expensive repair with replacement of one or both universal joints and possibly further bearing elements. It is particularly advantageous if a pressure medium is fed into the sealing sleeve or sealing sleeve via a pressure line. If a pressure line is provided as a signal line, this can also be done via this signal line. This makes it possible to build up and maintain a pressure within the sealing sleeve.
  • this makes it possible to generate a distance between the sealing sleeve or sealing sleeve and the cardan joints, as a result of which mechanical damage to the sealing sleeve or sealing sleeve by the cardan joint can be avoided.
  • a defined pressure can be generated within the sealing sleeve or sealing envelope, so that a pressure drop can be reliably determined and differentiated from pressure influences that are generated by the conveyed medium itself.
  • the status sensor is connected to an electronic evaluation unit for signal transmission and the electronic evaluation unit is designed to detect a discrepancy between an sensor based on the state sensor data detected ACTUAL state of a predetermined target state to compare this determined deviation with a predetermined permissible deviation and then, if the determined deviation exceeds the permissible deviation, output an alarm signal.
  • the electronic evaluation unit is designed to receive a condition sensor signal as the actual condition, to compare the condition sensor signal with a stored normal condition sensor signal as the TARGET condition and to calculate the determined deviation as the difference between the condition sensor signal and the normal condition sensor signal, as predetermined permissible deviation to use a predetermined permissible deviation value, and to output a value alarm signal as an alarm signal.
  • the detection of a sensor signal from the condition sensor which signals an unfavorable operating condition, that is to say an operating condition that causes or will cause increased wear, is based on a comparison of target and actual data.
  • the target data are stored in electronic form, for example as a data value, data value curve, algorithmic description of a data value curve or as a comparison table with several target values for different operating states of the eccentric screw pump.
  • the setpoint data can be predetermined and stored in advance, that is to say given to the eccentric screw pump ex works, so that they contain characteristic values that are characteristic and constant for the type of eccentric screw pump.
  • the setpoint data can be defined, for example, by the pump's own structural properties such as the eccentricity, constant state values, and load values defined by the drive train.
  • the setpoint data can, however, also be determined as a reference or calibration value when pumping a specific medium, in order then to be stored.
  • This reference or calibration value can, for example, be determined by the user when pumping a certain medium for the first time or when starting up the pump for the first time in a certain installation situation and is then used for comparison during further monitoring, i.e. during subsequent measurements of an actual value, so that critical changes are can be recognized immediately compared to the original reference or calibration value.
  • any deviation of the actual data from the target data can be output as an alarm.
  • the electronic evaluation unit is designed to receive state sensor signals, to determine a state change value as the ACTUAL state from at least two chronologically consecutive state sensor signals, and to compare the state change value with a stored normal state change value as the target state to calculate the detected deviation as the difference of the state change value from the normal state change value, to use a predetermined allowable deviation change value as the predetermined allowable deviation, and to output a change alarm signal as an alarm signal.
  • the electronic evaluation unit is designed to receive state sensor signals, to determine a rate of change of state as the ACTUAL state from at least three successive state sensor signals, and to compare the rate of change of state with a stored rate of normal state change as the target state, the determined deviation - Calculation as the difference of the rate of change of state from the normal rate of change of state, to use a predetermined permissible speed deviation as the predetermined permissible deviation, and to output a rate of change alarm signal as an alarm signal.
  • a status change signal is determined that characterizes the changes of two chronologically successive actual values.
  • This status change signal can be understood as the first time derivative of the status signal and often provides an assessment basis for a critical operating status that has occurred or is imminent, better than the absolute value of a status signal.
  • a rate of change of state can be determined from successive state sensor signals in which the second time derivative of the state signal is to be understood.
  • a large increase in pressure in the eccentric screw pump or a very rapid change in the rise or fall in pressure can indicate a closed state on the pressure side of the pump or a closed state on the suction side of the pump and can be detected at an early stage in order to activate the eccentric screw pump to accomplish.
  • a large rise in temperature or a large rate of change in the rise in temperature that is to say an accelerating rise in temperature, can signal dry running even when the absolute temperature has not yet reached a critical state value.
  • a real-time reaction of the control of the eccentric screw pump can be achieved by monitoring the status, the occurrence of damage and Can prevent wear and tear.
  • the electronic evaluation unit is designed to compare a plurality of chronologically sequential ACTUAL states with a plurality of chronologically sequential TARGET states and to calculate a deviation characteristic value from the comparison as the deviation determined predetermined permissible deviation to use a predetermined permissible deviation parameter.
  • a predetermined deviation is used for the determined changes in the state variables or changes in the rate of change of the state variables in order to enable operation within a tolerance window that is considered to be uncritical and to trigger a corresponding alarm when this tolerance window is exceeded.
  • the eccentric screw pump has a rotor with a conical envelope and a conically tapering stator interior and the rotor and the stator can be adjusted relative to one another in the axial direction by means of an axial actuator, the electronic evaluation unit is connected to the axial actuator for signal transmission and is designed to control the actuator in order to carry out an axial adjustment between the rotor and stator, to detect a plurality of chronologically successive status sensor signals of the status sensor during the axial adjustment process.
  • a conically tapering Rotor and stator enables the radial gap between the rotor and stator to be adjusted, in that an axial adjustment movement takes place between the rotor and stator.
  • the stator can be designed to be stationary and the rotor can be axially adjustable.
  • the axial adjustment device can in particular be designed in such a way that an axial adjustment of the rotor can take place during ongoing operation, for example in that the rotor together with the wobble shaft and drive motor can be adjusted axially.
  • a controllable actuator can be used, for example, which can preferably set a predetermined axial position via a displacement sensor.
  • the drive motor or other parts of the drive train can also be designed to be axially fixed and connected to the rotor by means of a torque-transmitting axial thrust connection.
  • the axial adjustment movement of the rotor typically influences the status signal and can be used to achieve a change in the status signal.
  • At least one status signal is recorded during the adjustment process, preferably several consecutive status signals.
  • the axial adjustment movement can take place as a function of the status signals. This can be done by controlling the axial adjustment or a closed control loop in which the status signal is used as an input or reference variable and the axial adjustment movement is used as an output or control variable.
  • the axial adjustment between rotor and stator allows a spontaneous correction of the operating status of the eccentric screw pump. It can be used to optimize the start-up behavior of the pump, for example to achieve a power-saving run-up with a larger gap and then to reduce the gap after the desired speed has been reached or during run-up.
  • the axial adjustment can be carried out by monitoring a status signal such as the drive power, the torque or the temperature until there is a gap between the rotor and stator that is ideal for pump efficiency and wear.
  • condition sensor is arranged on the drive shaft or the rotor and is further connected to a condition sensor data transmission module for wireless transmission of condition data to a data receiver outside the eccentric screw pump, the condition sensor and the condition sensor data transmission module for receiving electrical energy with an energy converter is connected, which is arranged on the rotor or on the drive shaft and which is designed to convert kinetic or thermal energy acting on it into electrical energy.
  • the status sensor is arranged as an independent module on the rotor or drive shaft and transmits the status data wirelessly to a receiver spaced therefrom.
  • the one for the status data acquisition is provided via an energy converter, which is also arranged on the rotor or the drive shaft and directly connected to the state sensor for energy transmission or designed as a common module with this.
  • the energy converter can be designed, for example, in such a way that it generates electrical energy from the rotational movement, an acceleration or oscillation resulting therefrom, by induction.
  • Other types of converters can also be used, for example thermal converters that generate electrical energy from a temperature of the pumped medium.
  • the energy converter is selected from: a converter based on the electromagnetic induction principle, which converts a relative rotational movement of the rotor or the wobble shaft with respect to a pump housing into electrical energy, a converter based on the electromagnetic induction principle, which converts one of the rotation of the rotor or the wobble shaft around a rotor axis and the rotation of the rotor around an eccentric axis converts the resulting reciprocal acceleration of the rotor or the wobble shaft into electrical energy, or a converter based on a thermoelectric principle that converts a temperature gradient into electrical energy, the converter is arranged in particular in an area that is exposed to a temperature gradient between the conveyed medium and a pump component such as the rotor, the wobble shaft or the stator.
  • two state sensors are arranged on the rotor, which are arranged at two positions spaced apart from one another and the positions have a phase offset of the measured state variable, the phase offset preferably being due to an axial spacing of the state sensors that is greater or smaller than an integral multiple the pitch of the rotor, or is achieved by an angular distance between the two condition sensors that is not equal to an integral multiple of 360 ° divided by the number of thread turns of the rotor.
  • a simultaneous, phase-shifted measurement of two state variables is achieved.
  • phase offset is to be understood as a detection of the two state variables within a periodic curve, which occurs at two points of the periodic course takes place which are not spaced from one another by exactly an integral multiple of the wavelength of the periodic course. If these two state variables are recorded by means of two state sensors on a three-flight eccentric screw rotor, this can be done in different positioning methods.
  • the phase offset can be achieved, for example, in that the two state sensors are not spaced apart from one another in the axial direction - i.e. lie in a cross-sectional plane of the rotor - but have an angular offset in this cross-sectional plane that differs from the quotient 360%, where n is the number corresponds to the threads of the rotor.
  • a phase-shifted measurement could be carried out with a three-speed rotor if the state sensors are offset from one another by an angle that is not equal to 120 ° or 240 °, that is to say, for example, are offset from one another by 90 ° or 180 °.
  • the angular offset would have to be unequal to 180 ° in order to achieve a phase-shifted measurement, with a four-turn rotor unequal to 90 °, 180 ° and 270 °. It must be taken into account that in eccentric screw pumps, the principle of the number of threads on the stator is always one higher than the number of threads on the rotor.
  • a phase-shifted measurement can also be achieved if the status sensors have an angular offset that corresponds to the quotient 360%, in that the status sensors are axially spaced apart by a distance that is not a multiple of the pitch of the thread of the rotor.
  • the division is to be understood as the axial distance between two adjacent thread peaks and corresponds to the pitch for a single thread and to the quotient of pitch / number of thread turns (n) for a multi-start thread.
  • a phase offset can be set in that the state sensors are spaced apart from one another by an axial distance which corresponds to half the division, so that a phase offset of half a wavelength is achieved.
  • the state sensor is a temperature sensor, a pressure sensor, a vibration sensor, or an acceleration sensor.
  • an evaluation by means of a comparison with a previously stored and / or calibrated master curve can provide information about an equilibrium temperature that is being established.
  • a detailed analysis of the course of the curve, taking into account the slope and curvature, allow additional evaluation options.
  • the relaxation time constant correlates with the dynamic properties of the stator's elastomer jacket.
  • a comparison of the area integrals describes the damping performance during the running-in phase.
  • a pressure difference can be determined by a measurement using two or more pressure sensors axially spaced along the rotor axis, which can be used, for example, for a volume flow calculation.
  • Fig. 1 is a longitudinal sectional view of an eccentric screw pump according to the invention
  • FIG. 3 shows a view according to FIG. 2 of a second embodiment of the invention
  • FIG. 4a shows a longitudinal sectional partial view of a third embodiment of the invention
  • FIG. 4b shows a view according to FIG. 4a of a fourth embodiment of the invention
  • FIG. 4c shows a view according to FIG. 4a of a fifth embodiment of the invention
  • FIG. 4d shows a view according to FIG. 4a of a sixth embodiment of the invention
  • FIG. 4e shows a view according to FIG. 4a of a seventh embodiment of the invention
  • FIG. 4f shows a view according to FIG. 4a of an eighth embodiment of the invention
  • FIG. 4g shows a view according to FIG. 4a of a ninth embodiment of the invention
  • FIG. 4h shows a view according to FIG. 4a of a tenth embodiment of the invention
  • FIG. 4i shows a view according to FIG. 4a of an eleventh embodiment of the invention
  • FIG. 4j shows a view according to FIG. 4a of a twelfth embodiment of the invention
  • FIG. 4k a view according to FIG. 4a of a thirteenth embodiment of the invention
  • FIG. 5a shows a schematic representation of the measuring process taking place on the wobble shaft or on the rotor according to a first embodiment
  • FIG. 5b shows a schematic representation of the measuring process taking place on the wobble shaft or on the rotor according to a second embodiment
  • 5c shows a schematic representation of the measuring process taking place on the wobble shaft or on the rotor according to a third embodiment
  • 6a shows a schematic representation of the course of three characteristic ones
  • FIG. 6b shows a typical schematic curve of three temperatures recorded on the rotor over time
  • 6c shows a typical schematic course of the movement of a sensor attached to the rotor in three directions over time in a normal operating state
  • 6d shows a typical schematic course of the movement of a sensor attached to the rotor in three directions over time in an operating state of a pump with advanced wear.
  • the pump has a stator 10, which has a cavity extending along a longitudinal axis A of the stator in the form of a coiled worm flight with two flights.
  • the stator 10 typically comprises a metal tube 11 or some other stable shell construction that encloses an elastomer jacket 12 that forms a cavity with the screw geometry on the inside.
  • a rotor 20 is arranged, which extends along a rotor longitudinal axis B, which runs parallel to the stator longitudinal axis A offset by the so-called “eccentricity”.
  • Eccentric screw pumps can be designed with rotors and stators of different numbers of gears. Basically, the number of turns of the rotor is always one gear higher than the number of turns of the stator for the functional principle.
  • the stator interior and the rotor can taper in the axial direction in the pumping direction (not shown), so that the end of the rotor facing an inlet opening 1 and the stator interior have a larger cross-sectional area than the end facing an outlet opening 2.
  • the rotor and stator are then arranged to be axially displaceable with respect to one another (axial movement Ax).
  • Axial infeed is then preferably possible during the rotational movement Ro of the rotor.
  • a start-up behavior of the pump can be optimized by the axial adjustment, for example by performing the axial adjustment as a function of the pumping behavior on the basis of the state variables. For example, it is possible to react to different viscosities of the pumped medium.
  • the rotor 20 is set in rotation about its longitudinal axis B of the rotor by a wobble shaft 30.
  • the wobble shaft 30 is here between the rotor and a drive input shaft, which is driven by a drive motor 40 via a belt drive 41, and transmits a rotational movement of the drive motor 40 to the rotor 20.
  • the wobble shaft 30 extends from a drive input end 30a, which is rotatably mounted in an inlet housing 50, to a drive output end 30b connected to the rotor.
  • the wobble shaft leads at the drive output end 30b
  • the wobble shaft can be guided by means of an eccentric bearing made by two rotary bearings with eccentrically offset axes, or it can be unguided so that the movement of the drive output end of the wobble shaft is defined by the guidance of the rotor in the stator.
  • the wobble shaft 30 has an input cardan joint at the drive input end 30a
  • the input cardan joint 31 is connected to the drive input shaft and via the belt drive to the output shaft of the drive motor 40.
  • the output cardan joint 32 is connected to the rotor.
  • the entire wobble shaft 30 is arranged in an inlet housing 50 and is bathed by a medium to be pumped which flows into the inlet housing 50 through an inlet opening 51. This represents the suction side of the pump.
  • the wobble shaft is therefore entirely surrounded by a protective sleeve 36 which extends over the input cardan joint 31, the shaft section 33 and the output cardan joint 32.
  • the rotor 20 and the stator 10 extend from an inlet end 10a attached to the inlet housing to an outlet housing 60 attached to an outlet end 20a Pump represents.
  • FIG. 2 shows a detail which shows the wobble shaft with the drive input shaft attached to it and the rotor attached to it.
  • a sensor 101 is inserted into a bore 102 in the rotor that extends in the radial direction relative to the longitudinal axis B of the rotor.
  • the sensor can be, for example, a temperature sensor, an acceleration sensor or a pressure sensor.
  • the rotor 20 also has a longitudinal bore 21 which extends along and coaxially to the longitudinal axis B of the rotor.
  • the sensor 101 is connected by means of a sensor signal line 110 which runs through the longitudinal bore 21 in the rotor, starting from there opens into a flange longitudinal bore 34 running coaxially with the longitudinal bore 21 in the connection flange of the output cardan joint 31. From this flange longitudinal bore 34, the sensor signal line 103 runs through a bore in the connection flange of the output cardan joint 31 that extends in the radial direction to the rotor longitudinal axis B to a position outside of the cardan joint 31.
  • the signal line then runs outside of the cardan joint 31, the shaft section 33 and the cardan joint 32, but within the protective cover 36 up to the input end of the wobble shaft 30.At this input end, the signal line runs analogously to the output end through a radial hole in the shaft section-side connection flange of the input cardan joint to an axial hole in the drive input shaft-side connection flange of the cardan joint, from there in a coaxial longitudinal bore in the drive input shaft.
  • the sensor signal line can then be routed to a rotary sensor signal transmission, which can be implemented, for example, in the form of several slip rings or the like, in order to route the sensor signal from the rotating part of the eccentric screw pump to a stationary part of the eccentric screw pump.
  • FIG. 3 shows a variant of the signal line routing.
  • the figure shows a basically identical structure as in Fig. 2.
  • the signal line is routed exclusively through axial longitudinal bores in the connection flange of the cardan output joint, the shaft section and the connection flange of the cardan input joint, in order to open into the longitudinal bore in the drive shaft .
  • the signal line also runs through corresponding cross bores in the bolts of the two cardan joints. It should be understood that the dimensions of the channels in which the signal line runs are correspondingly large, so that the signal line remains free of shear and therefore damage even with the wobbling movement that occurs during operation and the kinking of the cardan joints.
  • the drive input shaft can be fastened to the input-side universal joint by means of a central bolt which extends through partially or completely through the drive input shaft and is fastened to the universal joint to provide a conical fit between the drive input shaft and the Axial tensioning of the universal joint.
  • a central bolt which extends through partially or completely through the drive input shaft and is fastened to the universal joint to provide a conical fit between the drive input shaft and the Axial tensioning of the universal joint.
  • FIGS. 4a-k Different variants of the sensor arrangement on the rotor are shown in FIGS. 4a-k.
  • the sensors depicted in these figures can be pressure sensors, temperature sensors, acceleration sensors, vibration sensors, or other sensors. It should also be understood that the variants of the sensor arrangement shown in FIGS of these variants can be used, or that several sensors of different types can be arranged at a location shown in these variants.
  • the signal transmission principles and the energy supply of the sensors which are shown in these variants according to FIGS. 4a-k, can be combined with one another.
  • FIGS energy line 306 running for this purpose is to be supplied with energy.
  • an arrangement of the sensor in the outer surface of the rotor that this position on the one hand enables circumferential signal acquisition, i.e. signal acquisition over an angle of rotation of 360 ° around the longitudinal axis of the rotor or the longitudinal axis of the stator and thus enables a type of cross-sectional acquisition of the signal.
  • Another advantage of the arrangement of the sensor on the rotor, and especially when the sensor is arranged in the area of the outer surface of the rotor is the possibility of using this sensor to record signals of a characteristic value on the stator and a characteristic value on the rotor as well as a characteristic value of the conveyed medium during operation. This signal acquisition can take place in particular during one revolution of the rotor over 360 °.
  • This can in particular be a temperature measurement in which, depending on the angle of rotation of the rotor around the longitudinal axis of the rotor, the temperature of the stator is measured in certain angles, angular ranges or over the entire circumference in relation to the longitudinal axis of the stator and also the temperature of the conveyed medium.
  • the temperature of the rotor can also be detected by the sensor.
  • the sensor can also be designed as a sensor unit and can detect several measuring functions of the same or different physical quantities.
  • the sensor position shown in FIG. 4a can also be used for piezoelectric or capacitive vibration sensors in order to detect vibrations or accelerations of the rotor at this installation position of the sensor. These sensors can be single-axis or multi-axis measuring. Eddy current sensors can also be used at this position in order to measure the distance or position of the rotor.
  • FIG. 4b shows schematically a positioning of the sensor 401 that corresponds to FIG. 4a. In this installation variant, however, only the signal line 405 from the sensor to the receiving device is wired.
  • an energy converter 407 is arranged adjacent to the sensor, which converts temperatures or temperature gradients into electrical energy, as can be done, for example, with a Pellier element.
  • FIG. 4c shows a further variant in which the position of the sensor 501 and the signal line 505 corresponds to the sensor position according to FIG. 4a and the sensor is supplied with energy by means of an energy converter.
  • the energy converter is constructed according to the principle of induction, with corresponding magnets 508 in the inlet housing 50 as Fixed magnets or coil magnets are arranged and a coil 507 is located in the region of the output cardan joint or at the inlet end of the rotor, in which a current flow is triggered by induction.
  • the generator / dynamo acting in this way when the rotor rotates then generates the necessary electrical energy to supply the sensor via a short energy line 506.
  • FIG. 4d Another variant of the energy supply is shown in FIG. 4d.
  • a piezo transducer or an electrodynamic transducer 607 is arranged in the rotor, which generates electrical energy from the vibration caused by the eccentric rotational movement of the rotor and supplies the sensor 601 with it. Again, the signal is transmitted in a wired manner via a signal line 605
  • FIG. 4e and 4f show a variant in which two sensors 701a, b and 801a, b are arranged on the rotor in the same angular position with respect to the rotor longitudinal axis B but axially spaced from one another along the rotor longitudinal axis B.
  • the axial distance between the two sensors 701a, b is chosen so that both sensors are arranged in the area of a thread tip of the thread turn of the rotor, the axial distance thus corresponds to the pitch of the rotor thread, whereas in Fig.
  • the axial distance between the two sensors 801a, b is selected so that one sensor is arranged in the area of a thread tip and the other sensor in the area of a thread groove, the axial distance here thus corresponds to half the pitch of the rotor thread.
  • the sensors are supplied via a common power line 706, 806 and derive their signals via separate signal lines 705a, b and 805a, b.
  • FIG. 4g shows a further variant in which two sensors 901a, b are arranged on the rotor at the same axial distance as in FIG. 4e, but in this case not in the same angular position. For the purpose of measuring the phase offset, these sensors are positioned rotated by 180 ° around the longitudinal axis of the rotor.
  • the sensor is arranged centrally in the longitudinal axis of the rotor within the rotor and does not extend to an outer surface of the rotor.
  • the sensor is arranged approximately in the center of the rotor in the axial direction. This arrangement is particularly suitable for arranging a single or multi-axis vibration sensor or a gyroscope or a rotation sensor and thereby determining the movement, speed or acceleration to detect the movement of the sensor, which, due to the eccentric movement, enables a characteristic statement to be made about the operating state of the eccentric screw pump.
  • FIG. 4i shows a variant of the sensor arrangement in which the sensor 1101 is likewise not arranged up to the outer surface of the rotor, but rather remains inside the rotor. In contrast to the sensor position shown in FIG. 4h, however, the sensor is arranged at a radial distance from the longitudinal axis of the rotor and is located near the outer surface of the rotor.
  • FIG. 4j shows an embodiment in which a wired transmission of data or energy to the sensor 1201 is not required.
  • an energy converter 1207 is arranged adjacent to the sensor.
  • a radio transmission module 1209 is also arranged adjacent to the sensor in the rotor. In this way, the sensor signals can be transmitted to a receiver 1210 arranged outside the rotor, in particular outside the stator or the eccentric screw pump.
  • radio transmission module 1309 is also supplied with energy directly from the energy converter 1307 and transmits the signals to an external receiver 1310.
  • the senor is self-sufficient and is arranged on the rotor without the need for a cable-bound signal line or cable-bound power supply and is therefore particularly advantageous in terms of assembly and at the same time robust.
  • FIGS. 5a-5c show the basic principle of generating a measurement signal from a measurement parameter and the energy supply necessary for this to generate the measurement signal and to transmit this measurement signal.
  • 5a shows a sensor 2200 which detects a measurement parameter 2201 and generates and outputs a measurement signal 2204 via a microcontroller 2201.
  • the sensor is connected directly to a power supply 2203.
  • 5b shows a variant of the principle in which a sensor 2300 likewise detects a measurement parameter 2301 and outputs a measurement signal 2304 describing this measurement parameter via a microcontroller 2302.
  • the sensor is not directly connected to an external power supply. Instead, an energy converter 2305 is provided, which converts ambient energy 2303 into electrical energy for supplying sensor 2300 and microcontroller 2302. The energy converter transfers the generated energy to an energy management and storage module 2306, from which the sensor and the microcontroller are supplied with energy.
  • 5c shows a variant based on this, in which, in addition to the sensor 2400, which converts the measurement parameter 2401 into a measurement signal 2404 via a microcontroller 2402, an energy converter 2405, which converts ambient energy 2403 into electrical energy and transfers this to an energy management and storage module 2406 is present.
  • the energy management and storage module supplies the sensor and the microcontroller 2402 with electrical energy.
  • a converter or coupler which operates as a wireless transmission module 2407 and has an antenna 2408, is used to transmit the sensor signal 2404 to an external receiver.
  • FIGS. 6a-d show typical courses of some characteristic sensor signals which reflect measurement parameters that can be detected on the rotor or the wobble shaft.
  • FIG. 6a shows the dynamic rigidity 3001 (curve with triangles), the damping work 3002 (curve with rectangles) and the surface temperature 3003 of the stator (curve with dots) over the entire operating period 3010 in which an eccentric screw pump is operated, applied.
  • the damping work 3002 that is performed in the rubberized stator behaves in terms of its curve shape similar to the surface temperature 3003 of the stator.
  • the dynamic rigidity 3001 is initially high right at the beginning in the run-in phase 3011, then remains almost constant over the normal operating period 3012, and then drops during the fatigue failure phase 3013.
  • the effects that lie behind these curves are dependent on various factors and the cause of the curve cannot therefore be explained in general.
  • the initial fit between rotor and stator plays a role - an initially tight fit can lead to an initially large amount of frictional energy input, which then decreases.
  • the dynamic stiffness of the elastomer (the stator), for example, also plays a role, which describes the ability to propagate vibrations and thus the transport of energy / temperature.
  • 6b shows the temperature profile of the surface temperature 4020 of the stator over the time 4010 during the start-up behavior when an eccentric screw pump is started up once.
  • Three typical temperature profiles T1, T2 and T3 are shown, which could be recorded at three different time points at a measuring point on the stator by means of a sensor embedded in the rotor. All three temperature curves show a steep rise at the beginning, which then flattens out and levels off at a constant temperature level.
  • the temperature curve T2 represents a curve with the comparatively steepest rise, whereas the curve T1 does not rise as steeply, but increases by a difference DT12 to a higher temperature level than T2.
  • This more steeply rising temperature curve T2 correlates, for example, with a more rapidly decreasing dynamic stiffness or other properties of the elastomer of the stator.
  • the comparison of the stationary temperatures DT12 can, for example, signal a pumping situation of a medium with better lubrication properties and a lower temperature.
  • a temperature curve T3 with a flatter course and, in contrast, a constant temperature leveled off by a DT13 lower, can occur, for example, with an identical delivery medium at a lower speed of the pump.
  • FIG. 6c and 6d each show the measured values of a position, speed or acceleration 5020 of a position sensor which is arranged in the outer surface of the rotor or near the outer surface of the rotor and which can be implemented, for example, as a rotation sensor or gyro sensor, in the three Axis directions X, Y and Z over time 5010.
  • FIG. 6c shows a typical curve profile for an eccentric screw pump, which is in the normal operating state without significant wear.
  • FIG. 6d shows a pump operating state with advanced wear.
  • Fig. 6d shows a curve progression which has a significantly larger amplitude of the Z and Y values and also a considerable deviation of the X values from a constant progression with a clear, albeit irregular, oscillation of the rotor in the x direction. All of these three characteristic curves show increased wear on the eccentric screw pump, which can be seen from both radial and axial position fluctuations, accelerations and speeds.
  • the operating state of the pump can be monitored to ensure that unfavorable rotor movements due to, for example, misalignment or a wobbling movement (Fig. 6c and 6d) due to play of the rotor (caused by a decreasing preload of the rotor in the stator) can be detected.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne une pompe à vis excentrique comportant un stator (10) situé dans un carter de pompe ; un rotor (20) situé dans le stator (20) ; une unité d'entraînement comprenant un moteur d'entraînement (40) et un arbre d'entraînement (30) qui relie le moteur d'entraînement au rotor pour transmettre un couple, le rotor étant guidé dans le stator de manière à tourner autour d'un axe de rotation ; et un capteur d'état (101) pour détecter une variable d'état de la pompe à vis excentrique, le capteur d'état étant situé sur le rotor (20) ou sur l'arbre d'entraînement (30), ou étant relié au rotor ou à l'arbre d'entraînement par l'intermédiaire d'une ligne de signaux, et étant situé à une certaine distance du rotor ou de l'arbre d'entraînement, pour détecter une variable d'état sur le rotor ou sur l'arbre d'entraînement.
EP21722421.1A 2020-04-27 2021-04-27 Détection d'état sur des pompes à vis excentrique Pending EP4143439A1 (fr)

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DE102020111386.2A DE102020111386A1 (de) 2020-04-27 2020-04-27 Zustandserfassung an Exzenterschneckenpumpen
PCT/EP2021/060932 WO2021219605A1 (fr) 2020-04-27 2021-04-27 Détection d'état sur des pompes à vis excentrique

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EP (1) EP4143439A1 (fr)
JP (1) JP2023523059A (fr)
CN (1) CN115443379A (fr)
BR (1) BR112022020689A2 (fr)
DE (1) DE102020111386A1 (fr)
WO (1) WO2021219605A1 (fr)

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DE102019130981A1 (de) * 2019-11-15 2021-05-20 Seepex Gmbh Exzenterschneckenpumpe
DE102021121572A1 (de) 2021-08-19 2023-02-23 Hilger U. Kern Gmbh Verfahren zur Bestimmung des Verschleisszustands einer Exzenterschneckenpumpe sowie Exzenterschneckenpumpe zur Durchführung des Verfahrens
DE102021131427A1 (de) 2021-11-30 2023-06-01 Vogelsang Gmbh & Co. Kg Exzenterschneckenpumpe mit Arbeitszustellung und Ruhezustellung sowie Verfahren zum Steuern der Exzenterschneckenpumpe
DE102022110369A1 (de) 2022-04-28 2023-11-02 Audi Aktiengesellschaft Verfahren zum Betreiben eines Fluidkreislaufs für ein Kraftfahrzeug sowie entsprechender Fluidkreislauf
DE102022134734A1 (de) 2022-12-23 2024-07-04 Ruhr-Universität Bochum, Körperschaft des öffentlichen Rechts Verfahren zur Steuerung einer Exzenterschneckenpumpe

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JPS60150491A (ja) 1984-01-18 1985-08-08 Ebara Corp ポンプの異常運転集中予知装置
DE19649766C1 (de) 1996-11-30 1998-04-09 Netzsch Mohnopumpen Gmbh Verfahren und Vorrichtung zum temperaturabhängigen Betreiben von Pumpen mit schneckenförmigen Rotoren
DE10063953A1 (de) 2000-05-19 2002-02-07 Netzsch Mohnopumpen Gmbh Verfahren und Vorrichtung zum Betreiben einer Schneckenpumpe
EP1196693A1 (fr) * 2000-05-19 2002-04-17 Netzsch-Mohnopumpen GmbH Procede et dispositif pour actionner une pompe a vis
DE10157143B4 (de) * 2001-11-21 2007-01-11 Netzsch-Mohnopumpen Gmbh Wartungsintervallanzeige für Pumpen
DE102005019063B3 (de) 2005-04-23 2006-11-09 Netzsch-Mohnopumpen Gmbh Verfahren zum Betreiben einer Exzenterschneckenpumpe
CA2831980C (fr) * 2012-11-01 2016-06-21 National Oilwell Varco, L.P. Rotors legers et flexibles pour dispositifs a deplacement positif
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PT2944819T (pt) 2014-05-12 2017-10-02 Hugo Vogelsang Maschb Gmbh Bomba de parafuso excêntrico
DE102014112552B4 (de) 2014-09-01 2016-06-30 Seepex Gmbh Exzenterschneckenpumpe
DE102015101352A1 (de) 2015-01-29 2016-08-04 Netzsch Pumpen & Systeme Gmbh Stator-Rotor-System und Verfahren zum Einstellen eines Stators in einem Stator-Rotor-System
DE102015112248A1 (de) * 2015-01-29 2016-08-04 Netzsch Pumpen & Systeme Gmbh Exzenterschneckenpumpe und Verfahren zum Anpassen des Betriebszustands einer Exzenterschneckenpumpe
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DE102018113347A1 (de) 2018-06-05 2019-12-05 Seepex Gmbh Verfahren zur Bestimmung oder Überwachung des Zustandes einer Exzenterschneckenpumpe

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WO2021219605A1 (fr) 2021-11-04
DE102020111386A1 (de) 2021-10-28
BR112022020689A2 (pt) 2022-11-29
US20230265846A1 (en) 2023-08-24
CN115443379A (zh) 2022-12-06

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