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    • 专利摘要:
    To with a conditioning unit (3) having a base body (20) and a buffer memory (21), wherein a medium is passed through the base body (20) and between the buffer memory (21) and the base body (20) a temperature control unit (23) with a first Heating surface (24) and a second heating surface (25) is arranged and the temperature control unit (23) a temperature difference between the first heating surface (24) and the second heating surface (25) is set, the temperature of a gaseous or liquid medium despite strong flow or to be able to keep constant pressure fluctuations of the medium, it is provided that the conditioning unit (3) is controlled to maintain a predetermined setpoint temperature (Tsoll) of the medium, wherein a manipulated variable (Y) for controlling the conditioning unit (3) from a Model part (A), which calculates the power (Pv) required for the temperature control of the medium in the conditioning unit (3), and a control part (R), which d The power (Pv) calculated with the model part (A) is corrected, whereby a control error (F) from a setpoint temperature (Tsoll) and an actual temperature (Tist) exponentially enters into the control part (R).
    公开号:AT517215A4
    申请号:T50530/2015
    申请日:2015-06-23
    公开日:2016-12-15
    发明作者:Georg Dipl Ing Lichtenegger；Vedran Burazer；Michael Buchner；Ou Jun Zhou
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    Method for controlling a conditioning unit and consumption meter with such a conditioning unit
    The subject invention relates to a method for controlling a Konditioniereinheit with a main body and a buffer memory, wherein a medium is passed through the body and between the buffer memory and the base body a temperature control unit with a first heating surface and a second heating surface is arranged and the temperature control unit with a temperature difference between the the first heating surface and the second heating surface, and the use of this method in a consumption measuring device for measuring the consumption of a gaseous medium. Furthermore, the invention relates to a consumption measuring device for measuring the consumption of gaseous medium, with an input port at which the gaseous medium is supplied to the consumption measuring device, and an output port at which the gaseous medium is provided by the consumption measuring device, wherein between the input port and a gas path is provided in the outlet connection, in which a consumption sensor is arranged and a conditioning unit for tempering the gaseous medium is arranged in front of the consumption sensor and is arranged between the conditioning unit and the consumption sensor of a pressure control unit, in which the gaseous medium is depressurized.
    For accurate measurement of the fuel consumption of an internal combustion engine on a test bench, a precise conditioning of the temperature and the pressure of the fuel supplied to the internal combustion engine is necessary. The measurement of fuel consumption is often done with a known Coriolis flow sensor. In this case, a pre-circulation and a measuring circuit is often formed for liquid fuel, in which liquid fuel is conveyed in a circle. Between pre-circuit and measuring circuit of the flow sensor is arranged. The measuring circuit is closed via the internal combustion engine to be supplied. The usual in liquid fuel supply systems flushing volume is thus returned to the measuring circuit. The pre-charge serves to supply the measuring circuit with the amount of fuel consumed in the internal combustion engine. Thus, the interposed flow sensor measures exactly the amount of liquid fuel consumed. Since liquid fuel has a significant thermal expansion coefficient, the temperature in the measuring circuit must be kept as constant as possible in order to prevent possible measurement errors due to volume changes due to temperature fluctuations of the fuel in the measuring circuit. After the purge amount returned to the measuring circuit is heated by the fuel supply system of the internal combustion engine, a temperature control of the fuel in the inlet to the internal combustion engine is necessary. Also in the pre-price volume changes due to temperature fluctuations are to be avoided for exact consumption measurements. Therefore, the fuel is also tempered in Vorkreis. In addition, the pressure of the liquid fuel, which is supplied to the internal combustion engine, regulated by means of pressure control units as constant as possible. In addition, both the temperature and the pressure of the fuel depend on the current flow. Examples of such measurement of fuel consumption can be found in US 2014/0123742 A1 and EP 1 729 100 A1, which focuses on the conditioning of liquid fuels. Therein, the temperature of the fuel is controlled via a heat exchanger with a cooling liquid. However, such a heat exchanger is sluggish and allows only slow temperature changes, but this is sufficient for liquid fuel, since the temperature is only as constant as possible. Apart from this, such a heat exchanger requires additional components and controls for operating the heat exchanger, which also makes the system more complex.
    The systems for measuring the fuel consumption of an internal combustion engine described above are basically also suitable for gaseous fuel, e.g. for a gas engine, applicable. However, such a system is unfavorable to gaseous fuels, as appropriate compressors or fans would be required to circulate the gaseous fuel in the pre-circuit and measuring circuit, which would make the system considerably more expensive and expensive. Apart from that, a compressor would again massively affect the temperature of the gaseous medium, which is counterproductive to the goal of temperature control.
    For gaseous fuels, such as natural gas or hydrogen, there is the additional problem that the gaseous fuel is usually present under high pressure and consequently for use as fuel in an internal combustion engine (here gas engine) first to a required lower one Pressure must be relaxed. When the gaseous fuel is expanded, however, the fuel can cool down considerably (Joule-Thomson effect), which can be problematic for downstream components of the conditioning system, for example due to condensate formed and icing of the gas lines or other components in the gas line. Therefore, the gaseous fuel is usually heated before relaxing, so that by relaxing a desired temperature of the fuel results. Due to fluctuations in the pressure of the supplied gaseous fuel and also due to the dependence of the temperature after the relaxation of the composition of the gaseous fuel, the temperature can vary greatly after relaxing. However, a system as described in US 2014/0123742 A1 or EP 1 729 100 A1 is not suitable for such strongly varying temperatures at the entrance. The inert heat exchangers described therein are normally unable to compensate for large temperature fluctuations.
    A heat exchanger is sluggish and allows only slow temperature changes. Thus, the conditioning described by means of heat exchanger for heavy load changes is unsuitable.
    This leads to the current state of the art that after such a load change a calming time must be maintained. During this time, the temperature is unstable and high-precision measurement is not possible for flow sensors. For a more independent of the input temperature changes operation, either the power density of the heat exchanger would have to be increased. However, this is not technically feasible and requires, if at all possible, a redesign of the heat exchanger. At constant power density would in turn result in a much larger footprint. Another possibility might be a more aggressive control behavior of the heat exchanger. However, this in turn means greater overshoot and undershoot and concomitantly poorer dynamics with regard to possible setpoint temperature changes. Increasing the heat exchanger would only help with liquids. For gaseous media, a change in flow will directly cause a pressure change and a setpoint temperature change. Thus, the heat exchanger would have to allow extremely fast setpoint temperature changes, but this is not practical feasible for a heat exchanger operated with cooling liquid. For this, the available power would have to be increased even more with constant mass, only to increase the power would have no benefit in this case. Alternatively, the controller of the heat exchanger still has to be set more aggressively, which in turn would result in greater overshoot and undershoot. An accurate and fast temperature control would not be possible.
    In the case of gaseous media, however, a flow change causes a pressure change and a setpoint temperature change directly. Thus, the heat exchanger would have to allow extremely fast setpoint temperature changes, but this is not practical feasible for a heat exchanger operated with cooling liquid. Apart from that, a mere increase in power in terms of dynamics brings little to the point, since only the power density is decisive for a setpoint change and not the absolute power. Accurate and fast temperature control in the event of strong flow fluctuations would thus not be possible with conditioning by means of a heat exchanger. This applies to both gaseous and liquid media to be conditioned.
    It is therefore a first object of the subject invention to provide a method for controlling a conditioning unit of the type mentioned, with which the temperature of a gaseous or liquid medium can be set exactly and kept constant despite strong flow or pressure fluctuations of the medium.
    This object is achieved with a method in which the conditioning unit is controlled to maintain a predetermined setpoint temperature of the gaseous medium, wherein a manipulated variable for controlling the conditioning unit from a model part, which calculates the power required for the preheating of the gaseous medium in the conditioning unit , and a control part which corrects the power calculated with the model part, whereby a control error from the target temperature and the actual temperature exponentially enters into the control part is composed. With the model part, the power required for the temperature control of the gaseous medium can be roughly calculated. For the exact control then ensures the control part that corrects the model part. Due to the exponential consideration of the control error in the control part, the heat propagation in the conditioning unit is approximated, whereby a particularly accurate control of the conditioning unit becomes possible.
    According to the invention, the conditioning unit is preferably provided with a base body in which a media line through which the gaseous medium flows is arranged, and with a buffer memory for storing heat, wherein a temperature control unit is arranged between the base body and the buffer memory. With this conditioning unit, fast control interventions can be realized, which are necessary for the fast, accurate and stable temperature control in the conditioning unit.
    For gas engines, the flow of gaseous fuel may also be heavily dependent on the load of the gas engine. This in turn means that the heat exchangers in US 2014/0123742 A1 or EP 1 729 100 A1 for controlling the temperature of the gaseous fuel in the pre-charge and also in the measuring circuit would have to be able to handle such strongly fluctuating flows. The described, inert heat exchangers are usually not suitable, or would have to be dimensioned accordingly, which in turn would make them more expensive and expensive.
    Apart from that, a temperature control for gaseous fuel with such heat exchangers would also be inaccurate, in particular one would have to expect a significant overheating (overheating or subcooling) after a flow or pressure change.
    Furthermore, the usual systems for liquid fuels are usually only up to 10 bar pressure-resistant. For gaseous fuels but required for preheating up to 300bar compressive strength. This rules out conventional systems for the majority of gaseous fuel applications from the outset.
    The known devices for accurately measuring a consumption of liquid fuel of an internal combustion engine are therefore not suitable for gaseous fuels, or only conditionally suitable. Gaseous fuels therefore require a different approach in order to be able to measure the consumption of gaseous fuel accurately and with reasonable effort.
    Are known gas pressure control systems in natural gas networks to reduce the pressure of high transport pressure to a required consumption pressure, in which a gas flow measurement can be integrated. Such gas pressure control systems usually comprise an input-side natural gas preheater, often in the form of a water heating bath, through which the natural gas is carried in pipes, or a water / natural gas heat exchanger. The natural gas preheater heats the natural gas to the consumption pressure prior to expansion to compensate for cooling due to the Joule-Thomson effect. However, such gas pressure control systems are subject to neither a high requirement for the accuracy of the output pressure, nor specific requirements for the starting temperature. Also, the effects of a slowly changing flow rate are negligible in such gas pressure control systems. Fast, abrupt flow changes do not occur in such gas pressure control systems anyway.
    The required heat output for gas preheating the supplied gaseous fuel to achieve a desired post-expansion temperature can be calculated according to a known formula and is used in such gas pressure control systems to control the natural gas preheater. This formula could also be used in a temperature control of a heat exchanger for controlling the temperature of the gaseous fuel. However, sufficient control accuracy can only be achieved for relatively slow flow changes. For a gas pressure regulator, in which the flow changes little, and then only slowly, you can find the Auslangen. However, in an application in which the flow rate may vary highly dynamically (in the sense of rapid and also large flow changes), such as in the consumption measurement of an internal combustion engine (such as an internal combustion engine or a gas turbine), the achievable accuracy of the temperature control is known with this Approach but inadequate. Similar problems in accurately measuring consumption generally occur wherever a consumer supplies a gaseous medium to a consumer, the gaseous medium being present or delivered at a pressure greater than the consumer's consumption pressure. Other examples besides an internal combustion engine, where similar accuracy requirements are made, is a hydrogen-powered fuel cell, a rocket engine, or a jet engine.
    The regulation of the pressure of the gaseous medium is relatively easy to achieve with conventional regulated pressure control devices. By contrast, the regulation of the temperature of the medium is considerably more difficult to achieve because of the above-mentioned problems.
    It is therefore a further object of the subject invention to provide a method for measuring the consumption of gaseous fuel of a consumer, which provides the gaseous fuel at the output in spite of highly dynamic fluctuating flow rates and / or pressures as constant as possible temperature.
    This object is achieved in that the gaseous medium flows along a gas path through a consumption meter while the consumption is measured with a consumption sensor and the gaseous medium is temperature-controlled before the consumption sensor with the conditioning and pressure-relieved the gaseous medium between the conditioning and the consumption sensor is controlled, and the conditioning unit according to the control method according to the invention.
    Further preferred and advantageous embodiments of the method and the conditioning unit will be apparent from the independent claims and the description of the invention.
    The subject invention will be explained in more detail below with reference to Figures 1 to 5, which show by way of example, schematically and not by way of limitation advantageous embodiments of the invention. It shows
    1 is a flow diagram of a consumption measuring device according to the invention,
    2 shows the consumption measuring device in an alternative embodiment,
    3 a conditioning unit,
    4 shows a conditioning unit with active cooling in the buffer memory and
    5 shows a preferred embodiment of a consumption measuring device.
    The invention is based on the consumption measurement of a similar structure, as known from a gas pressure control system, as shown in Figure 1. The consumption measuring device 1 takes a media supply 2 from a gaseous medium. For example, the media supply 2 may be a gas line or a media container, such as e.g. a gas bottle, his. The gaseous medium is taken from the media supply 2 usually with a non-constant inlet pressure pe and flows through the consumption measuring device 1 along a gas path 17. The inlet pressure pe can assume pressures of up to 300bar and above. The removed gaseous medium is fed to a conditioning unit 3 in the gas path 17, in which the gaseous medium is heated to a certain temperature Ta. Thereafter, the heated gaseous medium is supplied to a pressure control unit 4, in which the gaseous medium is depressurized to a relaxation pressure. By the relaxation in the pressure control unit 4, the temperature of the gaseous medium changes to a relaxation temperature Tred. With natural gas as a gaseous medium, it comes through the Joule-Thomson effect to a cooling of the gaseous medium. In the case of hydrogen, the gaseous medium may even be heated by the relaxation. After expansion in the pressure control unit 4, the gaseous medium is supplied to a consumption sensor 5, e.g. a mass flow sensor or a flow sensor, for example in the form of a known Coriolis sensor. The gaseous medium leaves the consumption meter 1 with an outlet pressure pa and an outlet temperature Ta and is supplied to a consumer 6, e.g. an internal combustion engine, a gas turbine or a fuel cell. The consumption of gaseous medium by the consumer 6 is thus measured by the consumption sensor 5. Accurate measurement requires high temperature stability and pressure stability.
    In the exemplary embodiment according to FIG. 1, the outlet pressure pa and the outlet temperature Ta essentially correspond to the expansion pressure pred and the relaxation temperature Tred after the pressure regulation unit 4. In an alternative embodiment, the pressure expansion can also be carried out in two stages (or else in several stages), as described with reference to FIG. 2 is explained. Here, the gaseous medium before the consumption sensor 5 is brought to a relaxation pressure pred and a relaxation temperature Treci, with which the consumption is measured. In the flow direction after the consumption sensor 5, a second pressure control unit 7 is arranged, which relaxes the gaseous medium to the output pressure pa, which also results in the output temperature Ta. Certain consumption sensors 5, such as e.g. preferably used Coriolis sensors, have at higher pressures and thus at higher densities of the gaseous medium a higher accuracy. Therefore, it may be advantageous to first relax only to a pressure that gives a sufficiently high measurement accuracy and only then relax on the need lower output pressure pa. For accurate consumption measurement of the gaseous medium by the consumer 6, the outlet pressure pa and the outlet temperature Ta should be kept as constant as possible. The outlet pressure pa and the outlet temperature Ta are, however, strongly dependent on the inlet pressure and the inlet temperature Te, on the composition of the withdrawn gaseous medium (due to the Joule-Thomson effect), and on the flow over time, but also in amplitude, can vary greatly. In order to be able to regulate these influences, it is necessary, on the one hand, to regulate the pressure of the outlet pressure pa and, in particular, a high-dynamic temperature control of the conditioning unit 3.
    The pressure control of the output pressure pa can be performed with conventional pressure control units 4, 7, e.g. in the form of adjustable pressure control valves, with sufficient accuracy. The output pressure pa is therefore preferably regulated in a higher-level pressure control loop. For this purpose, a pressure sensor 8 may be provided at the output of the consumption measuring device 1, which detects the output pressure pa and a control unit 10, preferably in digital form, supplies. The control unit 10 controls the first pressure control unit 4 (FIG. 1), or the first and / or the second pressure control unit 4, 7 (FIG. 2), in order to set the desired or predetermined output pressure pa. In the exemplary embodiment according to FIG. 2, the first pressure control unit 4 is set to a constant expansion pressure preci, for example, and the outlet pressure pa is regulated only via the second pressure control unit 7. For regulating the temperature, the output temperature Ta can be detected by a temperature sensor 9 and fed to the control unit 10, preferably in digital form. It should be noted that the invention will be described below with reference to the measurement of the starting temperature Ta, but in principle the temperature could be used at any point of the consumption measuring device 1. In particular, instead of the starting temperature Ta, the relaxation temperature Tred, the temperature Τ · after the conditioning unit 3 or the temperature Ts in the consumption sensor 5 could equally be used. The control unit 10 calculates from the measured temperature, e.g. Output temperature Ta, temperature after the conditioning unit 3, relaxation temperature Tred or temperature Ts in the consumption sensor 5, a manipulated variable Y for the conditioning unit 3, with which the conditioning unit 3 is driven. For this purpose, the control unit 10 also the current flow V, which is measured by the consumption sensor 5, are supplied.
    The desired outlet temperature Ta is thus regulated by regulation of the conditioning unit 3 as a function of the actual flow rate V, and also as a function of the current outlet pressure pa. In order to allow a precise temperature control of the outlet temperature Ta at highly dynamic fluctuating flow V, a special conditioning unit 3 is provided, which is combined with a special control method.
    The conditioning unit 3, as shown in greatly simplified form in FIG. 3, is designed with a basic body 20 through which a media conduit 22 is passed, through which the gaseous medium to be conditioned flows. On the base body 20, a temperature control unit 23 is arranged, on which in turn a buffer memory 21 is arranged for storing heat. The main body 20 is not directly on the buffer memory 21, but is thermally separated by the temperature control unit 23 thereof. The buffer memory 21 is preferably designed as a heat sink with a certain memory mass. Thus, the heat sink is not designed for maximum heat dissipation, as is customary with heat sinks, but the heat sink is to store a certain portion of the dissipated heat at least for a certain period of time. The tempering unit 23 serves to temper the base body 20 and thus the medium flowing through it. For this purpose, the temperature control unit 23 is able to heat the base body 20 and cool it.
    The temperature control unit 23 is advantageously designed as at least one thermoelectric module (Peltier element), preferably a number of thermoelectric modules. A thermoelectric module is known to be a semiconductor element disposed between a first heating surface 24 and a second heating surface 25. Depending on the polarity of the electrical supply voltage supplied to the semiconductor element, either the first heating surface 24 is warmer than the second heating surface 25, or vice versa. Thus, with such a thermoelectric module, depending on the polarity of the supply voltage, the main body 20 can both be heated and cooled. After the structure and function of such thermoelectric modules are well known and such thermoelectric modules are commercially available in different performance classes, will not be discussed in more detail here.
    If an electrical supply voltage is applied to a thermoelectric module, as is known, one of the heating surfaces 24, 25 of the thermoelectric module is cooled, while at the same time the opposite heating surface is heated. The maximum temperature spread between the two heating surfaces 24, 25 depends on the operating temperature (temperature at the warmer heating surface) of the thermoelectric module. The higher the operating temperature, the higher the maximum achievable temperature spread between cold and hot heating surface. As a result, with available thermoelectric modules temperatures of up to 200 ° C can be achieved on the hot heating surface, the cold heating surface does not exceed 100 ° C. By simply reversing the supply voltage, you can quickly switch between cooling and heating. After the gaseous medium flowing through the conditioning unit 3 is to be tempered, heating means that the heating surface 24 applied to the main body 20 is hotter than the opposite heating surface 25. Cooling therefore means that the heating surface 25 is the hotter heating surface and the one resting against the main body Heating surface 24 the cooler. For the temperature control of the gaseous medium but not necessarily the polarity of the supply voltage must be changed if the temperature of the gaseous medium is to be lowered or increased. For this purpose, the temperature spread between the heating surfaces 24, 25 can be used. Smaller control interventions can thus take place via the temperature spread, while large control interventions preferably take place by reversing the polarity of the supply voltage of the thermoelectric module.
    The control over the temperature spread is supported by the buffer memory 21 in the heating mode, so when the medium is to be heated in the media line 22, is used as a heat storage. With a constant power supply of the thermoelectric modules, the thermoelectric modules have a stable temperature spread. As soon as less thermal energy or heat is required for tempering the medium, the supply voltage is reduced at the thermoelectric modules, whereby the temperature spread is lower. Thus, the temperature drops at the voltage applied to the base body 20 heating surface 24 of the thermoelectric module. At the same time, the temperature at the opposite heating surface 25 increases. Thus, a temperature gradient arises between the heating surface 25 and the buffer memory 21 adjacent thereto, whereby heat flows into the buffer memory 21 (indicated by the heat flow Q) and there due to the thermal storage mass not immediately to the Environment is dissipated, but (at least for a limited time) is cached. This cached heat is the temperature control as a support available when more thermal energy is required to temper the medium. In this case, the supply voltage would be raised again, whereby the temperature difference at the thermoelectric modules increases again. Thus, the temperature at the heating surface 25, at which the buffer memory 21 is applied to, from the temperature of the buffer memory 21 decreases. This results in a reverse temperature gradient, which results in the thermal energy stored in the buffer tank 21 flowing into the main body 20 (indicated by the heat flow Q) and thus supporting the thermoelectric modules during the temperature control of the medium. This can be reacted to fast load changes or temperature changes very quickly and accurately and a typical overheating can be largely avoided. For this purpose, it is advantageous to adapt the thermal storage mass of the buffer memory 21 to the thermal storage mass of the base body 2 and the media line 6 arranged therein, in order to make the best possible use of this effect.
    Although the conditioning unit 3 is described above with reference to a thermoelectric module as tempering unit 23, of course, other embodiments of a temperature control unit 23 are conceivable. The temperature control unit 23 only has to be able to change the temperature spread between the heating surfaces 24, 25. From a physical point of view, the operation of a thermoelectric module corresponds to a heat pump, which absorbs thermal energy from a lower temperature range and transfers it to a higher temperature system to be heated. The reversal of the supply voltage corresponds to the provision of two heat pumps, which are operated in opposite directions. Thus comes as temperature control unit 23 in principle any equipment in question, which can be classified under the concept of a heat pump.
    In order to exploit this advantage of the conditioning unit 3 also control technology, which is a prerequisite for a fast and accurate control, the invention provides that the described heat flow Q between the buffer memory 21 and the base body 20 through which the medium flows in the scheme is taken into account. For this purpose, a controller is designed, which determines a manipulated variable Y for the conditioning unit 3 from a setpoint temperature specification Tson. The conditioning unit 3 is controlled with the manipulated variable Y and ensures a stable and constant temperature of the medium.
    The manipulated variable Y is composed of a model part A and a control part R, ie Y = A + R. The model part A models the conditioning unit 3 and serves to optimally the energy or power Pv required for the temperature control of the medium in the conditioning unit 3 calculated and converted for the control in a manipulated variable. The power PG required for the conditioning of a gaseous medium in order to reach a desired temperature Tson after a pressure release can be determined on the basis of the known formulaic relationship
    be calculated. Without the Joule-Thomson effect, the power PG is reduced to the power needed to control the temperature (heating or cooling) of the medium. In this case, the current flow V is measured by the consumption sensor 5 and made available. The specific heat capacity HG of the medium is a constant and known. The input temperature Te may be measured with a suitable temperature sensor 11, e.g. a PT100 sensor. The pressure difference ΔpG indicates the pressure release from the inlet pressure pe to the expansion pressure pred, both of which can be measured by means of suitable pressure sensors 8, 12, ie λpG = (pe - pred). In an embodiment according to FIG. 2, the expansion pressure preci can also be known be. PJT is the well-known Joule-Thomson coefficient of the gaseous medium. For a liquid medium, the Joule-Thomson coefficient should be set to zero.
    Optionally, a power loss PL in the conditioning unit 3 can also be taken into account. For a very accurate and fast control, the power loss PL should be considered. The power loss PL can be modeled, for example, as the heat delivered to the environment with the ambient temperature Tamb of the conditioning unit 3. The ambient temperature Tamb may again be measured by means of a suitable temperature sensor 13, e.g. a PT100 sensor. With an empirical constant kPL obtained from the concrete embodiment of the conditioning unit 3 and assumed to be known, the power loss PL can then be calculated according to the formula
    be calculated.
    The power Pv required for the temperature control in the conditioning unit 3 then results
    , which can be used as model part A. In order to determine therefrom an easy-to-process manipulated variable for the control, the required power Pv can also be set in relation to the maximum available power Pv, max in the conditioning unit 3, that is, the model component
    , The model component A is thus a parameter in the range of [0, 1] or [-1, 1] if it is also possible to switch between heating and cooling in the conditioning unit 3.
    In a specific embodiment of the conditioning unit 3 with a thermoelectric module as a temperature control unit 23, the required power Pv can also be converted into a supply voltage Uv, which is to be applied to the thermoelectric modules. With an ohmic resistance RCu of the thermoelectric modules in the conditioning unit 3, the supply voltage Uv from the known context
    be calculated. Analogous to the above model share A with a maximum possible
    supply voltage
    when
    be calculated.
    The ohmic resistance RCu of a thermoelectric module is usually not known and additionally temperature dependent. In order to be able to determine the ohmic resistance Reu, the empirical connection became the result of experiments
    determined, from which the ohmic resistance RCu with knowledge of the actual temperature Tist (which can be easily measured) of the thermoelectric modules can be calculated. Therein, Rcu2o and Rcuiso are empirical constants indicating the ohmic resistance RCu of the thermoelectric module at a temperature of 20 ° C and 150 °.
    The control component R of the manipulated variable Y is used for highly dynamic, accurate control of the outlet temperature Ta (or another temperature as mentioned above) by utilizing the amount of heat available in the buffer memory 21. After the required power Pv for temperature control in order to reach the target temperature Tson is already roughly controlled with the model part A, the control component R only has to make small corrections of the manipulated variable Y in order to achieve the desired precise control behavior.
    As stated above, in the conditioning unit 3 according to the invention, the heat flow Q between the main body 20 and the buffer reservoir 21 plays a decisive role. To take account of this heat flow Q in the control, the control error F is not linear in the control part R, but exponential, ie R = f (eF). The reason for this lies in the solution of the heat conduction equation, which also contains an exponential component. The control deviation F in the present embodiment is the difference between the setpoint temperature Tson and the actual temperature Tist.
    It should be noted that both the setpoint temperature Tson and the actual temperature Tist refer to the temperature to be controlled, e.g. Output temperature Ta, temperature Τ · after the conditioning unit 3, relaxation temperature Treci or temperature Ts in the consumption sensor 5. It is quite possible, however, to obtain the setpoint temperature TSOii and the actual temperature Tist in the model part A and in the control part R at different temperatures, e.g. the temperature Ts in the consumption sensor 5 in the model part A and the output temperature Ta in the control part R. For the control part R, a classical control engineering approach can be selected in which the control part R for forming a PI controller of a proportional part YP and an integral part Y | is composed, so R = YP + Y |. In the following, a possible concrete embodiment of the control part R, or of the proportional part YP and the integral part Y, will be described.
    A conventional proportional controller consists of a gain factor KP, which weights the control error F, ie KP-F. A conventional integral controller consists of a gain factor Ki which weights the control error F as a function of the time t, that is to say KrF-t, with the gain K | as the reciprocal of the reset time Tn.
    In the proportional part YP and the integral part Y | In the case of the regulator according to the invention, the control error F enters as exponential functions fP (eF) or fI (eF) of the control error F. In the simplest case, the proportional part YP thus yields YP = KP fP (eF) and the integral part Y | in the simplest case to Y | = K | f | (eF) t. For a discrete-time controller with a sampling time Δt (for example, of 10 ms), the integral controller can also be in the form Y | (n) = Yi (n-1) + AY |, with AY | = K | · Fi (eF) At letter. By using the exponential function of the control error F, the heat propagation in the conditioning unit 3 is approximated.
    As described above, the energy supplied to the conditioning unit 3 is used, on the one hand, for heating the gaseous medium and, on the other hand, also for heating the entire conditioning unit 3. With the same supply of energy, increasing the temperature of the gaseous medium is slower than that Lowering the temperature of the gaseous medium. The raising of the temperature is, as described above, supported by the stored heat in the buffer memory 21, so that this effect is already attenuated.
    In order to compensate for this asymmetrical characteristic of the conditioning unit 3, the proportional part YP and the integral part Y | also with a suitable correction function
    be corrected, giving a corrected proportional part
    and a corrected integral part
    results:
    H (x) is the well-known Heaviside function, which maps the real numbers to the set {0, 1}, where H (x) = 0 for x <0 and H (x) = 1 for x> 0. Dh, that by the correction the proportional part YP and the integral part Y | is strengthened, if
    So if the tempera ture of the gaseous medium to be increased. The proportional part Yp and the integral part Yi are attenuated when
    So if the temperature of the gaseous medium is to be lowered. As a correction function
    can, for example
    be used with the model part A described above. Thus, the stronger the correction intervention, ie the larger the model part A is, the stronger the correction. Of course, this characteristic of the correction function YpOWercor presupposes that the model part A is normalized to the range [0,1] or [-1, 1].
    In a preferred embodiment, the proportional part Yp results from the formulaic relationship
    The exponential function f | (eF) in the integral part Yi results in a preferred embodiment from the formulaic relationship
    It should be noted that for the sake of simplicity, the integral part Y | the gain factor KP of the proportional controller is used, which of course is not necessary. Instead, of course, a separate gain factor K | of the integral controller are used. For the discrete-time case, the integral part Y | then again as
    With
    Be written on.
    Where H (x) is again the Heaviside function and sign the Signum function, which maps the real numbers to the set {-1, 0, 1}, with sign (x) = -1 for x <0, sign (x) = 0 for x = 0 and sign (x) = 1 for x> 0. The parameter σ is defined as
    and p = 0.318366. The function f | (eF) for the integral part Yi has been chosen such that it is continuous over the entire range and has an exponential profile. To make this possible, the function has been split into two parts. A first part that has a logarithmic course for large control errors. As well as a second part, which has an exponential course with smaller control errors F. The transition between the first and the second part takes place at the point p at which the slopes of the two parts are identical in order to achieve a continuous function.
    The manipulated variable Y, which is determined by the controller, therefore results
    It should be noted here that the use of proportional part Yp and integral part Yi is preferred but not mandatory. It is also possible to use only the proportional part YP or only the integral part Y. Furthermore, a damping factor YDf can also be taken into account in the manipulated variable Y. The damping factor YDf may be a first damping factor
    Yon (for example, an empirical value) to prevent overheating of the conditioning unit 3. Furthermore, the damping factor YDf may also include a second damping factor YDf2, with which also a set value overshoot can be damped, e.g. according to the principle of maximum value damping. The damping factor YDf then becomes Yof = Ydu · YDf2- Both damping factors are optional and can be used independently of each other. When using a damping factor YDf, the calculated manipulated variable Y is added
    With this controller, in combination with the specially designed conditioning unit 3, the desired temperature can be controlled with high precision and a high temperature stability can be achieved, which is a prerequisite for an accurate determination of the consumption values (mass flow, volume flow) at dynamic flow rates of the medium.
    It should be noted at this point that the regulation described above is independent of a specific application. Although the regulation is described in connection with a consumption measurement of a gaseous medium, the conditioning unit 3 can be regulated in a generally general manner in the manner described and is thus also suitable for other applications in which a medium is to be tempered and in particular also for liquid media. suitable. This is possible above all because it is possible to control the temperature ΤΤ after the conditioning unit 3 at an arbitrary temperature, that is to say also at the temperature.
    With this controller, it is also possible, temperature curves or temperature characteristics of the target temperature Tsoii, also depending on the output pressure pa or inlet pressure pe and also depending on the flow V, nachzufahren. Also, dependencies of the output pressure pa from the flow V could be mimicked, e.g. by means of a corresponding characteristic. If the flow V is dependent on the outlet pressure pa or inlet pressure pe, the regulator could also set a desired flow V via the pressure control. Thus, it is possible with this controller, an original structure, such as he. used in a vehicle, and also to simulate a ride on a vehicle.
    At this point, it should again be pointed out that as desired temperature Tson any temperature in the consumption measuring device 1, but also a temperature outside the consumption measuring device 1 can be used. Preferably, however, the starting temperature Ta is regulated as the setpoint temperature TSOii. Likewise, the output pressure pa can be measured in the consumption measuring device 1, or outside, for example, close to a consumer. 6
    The described control is suitable both for the control by exploiting the temperature spread, as well as for the control with change between heating and cooling. When using thermoelectric modules as tempering unit 23, the supply voltage is reversed when the manipulated variable Y changes the sign. The manipulated variable Y is preferably normalized to the range [-1, 1] as described above.
    In the case of hydrogen as the gaseous medium, the pressure release in the pressure control unit 4 causes heating. In this case, it depends on the input temperature Te, whether it is cooled or heated with the conditioning unit 3. The same applies essentially to liquid media.
    In order to support the cooling, an additional cooling device 26 may also be provided in the buffer memory 21 of the conditioning unit 3, for example in the form of a cooling line 27 through which a cooling medium flows. The control can then be extended by a control of the cooling device 26 with which the active cooling is taken into account by the cooling device 26. This regulation then regulates the cooling device 26 by, for example, varying the flow rate VK (for example via a control valve or via the pressure) and / or the temperature TK of the cooling medium. For this purpose, a control variable Yc is determined in the control, with which the cooling device 26 is driven.
    The regulation of the active cooling should preferably have certain properties. The active cooling by means of cooling device 26 is to take over the base load and the temperature control unit 28 is intended to serve the highly dynamic compensation of disturbances. However, it is desirable that the temperature control unit 28 always carries a portion of the cooling load, in order to avoid that the temperature control unit 28 must be operated around the zero point, which could cause a constant switching between cooling and heating. In Peltier elements as tempering unit 28 that would mean a constant reversal, which can also permanently damage the Peltierelemen te. Apart from that, one would lose the advantage of the buffer memory for the control of the conditioning unit 3 by the operation around the zero point. Last but not least, the regulation of active cooling should also be as far as possible decoupled from the regulation of the conditioning unit 3 so as not to negatively influence this regulation.
    In order to meet these requirements, a regulator is designed in which a temperature difference ΔΤΚ is exponential. The temperature difference .DELTA.Τ, which is controlled, is defined as the difference between a temperature TTe of the temperature control unit 28 (which can be measured), preferably on the side of the buffer memory 21 (heating surface 25), and the actual temperature TK of the cooling medium. In order to avoid the operation of the temperature control unit 28 about the zero point, a predetermined deadband Ttotb can also be defined with which the temperature TTe of the temperature control unit 28 is corrected. This results in a corrected temperature TKh of the temperature control unit 28
    and the temperature difference
    Thus, a P controller can be designed which determines a manipulated variable YCp for the cooling device 26 as follows.
    H here again designates the Heaviside function and Y the manipulated variable from the control of the conditioning unit 3. KCp is a gain factor of the P controller.
    In order to ensure the decoupling between the control of the conditioning unit 3 and the control of the cooling device 26, the reaction time in the control of the cooling device 26 should be slower than the reaction time in the control of the conditioning 3. To the control of the cooling device 26 has a defined delay time to give a filter G can be used. The filter G receives as an input signal the manipulated variable YCp for the cooling device 26 and calculates a filtered manipulated variable YCpf, which is then used as the actual manipulated variable for the cooling device 26, ie
    For this purpose, various known filters G can be used. In this connection, a Gauss filter known from image processing has proved to be advantageous, since such a filter is known to have no overshoot and maximum rise times. It also attenuates all frequencies above a cut-off frequency. Such a Gaussian filter is well known, which is why it will not be discussed further here. It is also known that the calculations underlying a Gaussian filter are complex and computationally expensive, which is disadvantageous for a closed-loop control application. But also to this end solutions from the prior art are known to minimize the computing times. Here, so-called discrete Gaussian kernels or sampled Gaussian kernels come into question.
    The version with the active cooling in the buffer tank is particularly interesting for liquid, but certainly for gaseous, media. This results in a large control range for the conditioning unit 3, with Peltier elements as the temperature control unit 28, for example -40 to 150 ° C. The conditioning unit 3 can bring the required power over the entire control range and still regulate the temperature highly dynamically and always extremely precisely.
    A preferred embodiment of the consumption measuring device 1 for gaseous medium will be described with reference to FIG. The gaseous medium, with an inlet pressure pe, is taken from a media supply 2 and fed via an input line 14 and an input terminal 15 of the consumption measuring device 1. On the input side, either outside or in the consumption measuring device 1, a gas filter 30 may be arranged. The gaseous medium is tempered in a conditioning unit 3 and expanded in a subsequent pressure control unit 4 to a desired expansion pressure pred. The expanded gaseous medium then flows through the consumption sensor 5, in which the consumption (mass flow, volume flow) is measured. After the consumption sensor 5, the second pressure control unit 7 is arranged, with which the desired output pressure pa is set. Via an output port 16, the conditioned gaseous medium can be removed and e.g. a consumer 6 are supplied.
    All functions and components described below are controlled by a control unit 40, in which the control unit 10 is also implemented. The built-in sensors also supply their measured values to the control unit. Due to the clarity necessary control line and measuring lines were not shown in Figure 4.
    As a consumption sensor 5 are here two or more, serially connected Coriolis sensors 31, 32 are provided. The two Coriolis sensors 31, 32 have different measuring ranges. This can be switched to the optimal (in terms of measurement accuracy) Coriolis sensor 31, 32 depending on consumption for measurement. This is done via a bypass switching valve 33 which is arranged in a bypass line 34 to the second Coriolis sensor 32. The switching valve 33 is actuated here by compressed air. For this purpose, a compressed air valve block 35 is provided, which is connected via a compressed air connection 36 with an external compressed air supply. The second Coriolis sensor 32 can thus be switched on or off by actuating the bypass switching valve 33. If both Coriolis sensors 31, 32 flow through, this allows a plausibility of the measurement result in overlapping measuring ranges, which can be used for self-checking.
    In the consumption measuring device 1, an overflow line 37 is further provided, which is connected to an overflow connection 38. The overflow line 37 is connected in the consumption measuring device 1 via pressure relief valves with the gas path for the gaseous medium. Thus, the consumption measuring device 1 can be protected against incorrect overpressing.
    Downstream of the consumption sensor 5, a zeroing valve 39 is arranged. Thus, the zero point of the consumption sensor 5 can be checked. For this purpose, the zero balance valve 39 is closed (again controlled by compressed air) and evaluated the measured value of the consumption sensor 5 at zero flow rate. If the measured value exceeds a certain limit value, an internal sensor calibration can be triggered to set the zero point. In this way, the zero-point drift of the consumption sensor 5 can be counteracted.
    In the consumption measuring device 1, an inert gas purging 41 is also provided in the exemplary embodiment shown. For this purpose, an inert gas pressure accumulator 42 is provided, which can be connected via an inert gas switching valve 43 to the gas path of the gaseous medium through the consumption measuring device 1. About an inert gas 44, the inert gas pressure accumulator 42 can be filled. However, the inert gas (for example, nitrogen) required for purging the consumption metering device 1 may also be supplied directly via the inert gas port 44.
    For flushing the consumption measuring device 1 with inert gas, the input-side shut-off valve 45 is closed and the output-side output switching valve 46 is switched to the overflow line 37. At the same time, the inert gas switching valve 43 is opened. In order for the pressurized, remaining in the metering device 1 gaseous medium can escape via the overflow 37. If the pressure is reduced enough, opens the check valve 47 and the metering device 1 is purged with the inert gas, either until the inert gas pressure accumulator 42 is empty or for a certain period of time. After rinsing, the consumption measuring device 1 is filled with inert gas, preferably with a slight excess pressure, and is in the safe state. The inert gas purging increases the safety of the consumption measuring device 1 and can be activated, for example, when switching off the device or in the event of an emergency stop.
    权利要求:
    Claims (27)
    [1]
    claims
    1. A method for controlling a conditioning unit (3) having a base body (20) and a buffer memory (21), wherein a medium is passed through the base body (20) and between the buffer memory (21) and the base body (20) a temperature control unit (23) is arranged with a first heating surface (24) and a second heating surface (25) and with the tempering unit (23) a temperature spread between the first heating surface (24) and the second heating surface (25) is set, characterized in that the conditioning unit (3 ) is controlled in order to maintain a predetermined target temperature (Tson) of the medium, wherein a manipulated variable (Y) for controlling the conditioning unit (3) from a model part (A), the power required for the temperature of the medium in the conditioning unit (3) (Pv), and a control part (R) which corrects the power (Pv) calculated with the model part (A), wherein a control error (F) is calculated from a target temperature (Tson) and an actual temperature tur (Tist) is exponentially in the control part (R) received, is composed.
    [2]
    2. The method according to claim 1, characterized in that the model part (A) the power required for the temperature control (Pv) based on the formulaic relationship

    calculated.
    [3]
    3. The method according to claim 2, characterized in that in the model part (A) a power loss (PL) of the conditioning unit (3) is taken into account.
    [4]
    4. The method according to claim 1, characterized in that the control part (R) from a proportional part (YP) and / or an integral part (Y |) is composed, wherein the control error (F) as exponential functions (fP (eF), f | (eF)) of the control error (F) is received in the proportional part (YP) and / or the integral part (Y |).
    [5]
    5. The method according to claim 4, characterized in that the proportional part (YP) of a gain factor (KP) and the exponential function fP (eF) is formed.
    [6]
    6. The method according to claim 5, characterized in that the proportional part (YP) from the formulaic relationship

    is calculated.
    [7]
    7. The method according to claim 5 or 6, characterized in that the proportional part (YP) with a correction function

    to a corrected proportional part

    is corrected.
    [8]
    8. The method according to claim 7, characterized in that the corrected proportional part (Ypcor) from the formulaic relationship

    calculated.
    [9]
    9. Method according to claim 4, characterized in that the integral part (Y |) is formed from a gain factor (K |) and the exponential function (fi (eF)) and the time (t).
    [10]
    10. The method according to claim 4, characterized in that the integral part (Y |) for a discrete-time controller having a sampling time (At) of a gain factor (K |) and the exponential function (fi (eF)) and the sampling time (At) is formed.
    [11]
    11. The method according to claim 9 or 10, characterized in that the exponential function (fi (eF)) in the integral part (Y |) from the formulaic relationship

    calculated.
    [12]
    12. The method according to any one of claim 9 to 11, characterized in that the integral part (Y |) with a correction function

    to a corrected integral part

    is corrected. A method according to claim 12, characterized in that the corrected integral part (Yicor) from the formulaic relationship

    calculated.
    [13]
    13. The method according to claim 1, characterized in that in the manipulated variable (Y), a damping factor (YDf) is taken into account.
    [14]
    14. The method according to claim 1, characterized in that in the buffer memory (21) a cooling device (26) is arranged, with the cooling medium through the buffer memory (21) is performed, and the cooling device (26) is controlled by a manipulated variable (Ycp ) is calculated, in which a temperature difference (ΔΤΚ) between a temperature (TTe) of the temperature control unit (23) and an actual temperature (TK) of the cooling medium enters exponentially in the manipulated variable (YCp).
    [15]
    15. The method according to claim 14, characterized in that the temperature (TTe) of the temperature control unit (23) by a deadband (Ttotb) is corrected.
    [16]
    16. The method according to claim 15, characterized in that the manipulated variable (YCp) according to

    is calculated.
    [17]
    17. The method according to any one of claims 14 to 16, characterized in that the calculated manipulated variable (YCp) is filtered and the filtered manipulated variable (Ycpf) is used to control the cooling device (26).
    [18]
    18. The method according to claim 17, characterized in that the filtering is performed with a Gaussian filter (G).
    [19]
    19. Use of the method according to one of claims 1 to 18 for measuring the consumption of gaseous medium, wherein the gaseous medium along a gas path (17) by a consumption meter (1) flows and thereby the consumption with a consumption sensor (5) is measured and the gaseous medium before the consumption sensor (5) with the conditioning unit (3) is tempered and the gaseous medium between the conditioning unit (3) and the consumption sensor (5) is depressurized, and the conditioning unit (3) is regulated according to the control method.
    [20]
    20. The method according to claim 19, characterized in that the pressure of the gaseous medium after the conditioning unit (3) via a pressure control unit (4, 7) is set.
    [21]
    21. Consumption measuring device for measuring the consumption of gaseous medium, with an input port (15) to which the gaseous medium of the Verbrauchsmessein- direction (1) is supplied, and an output port (16) at which the gaseous medium from the consumption measuring device (1 ) is provided, wherein between the input terminal (15) and the output terminal (16) a gas path (17) is provided, in which a consumption sensor (5) is arranged and before the consumption sensor (5) a conditioning unit (3) for temperature control is arranged between the conditioning unit (3) and the consumption sensor (5) of a pressure control unit (4), in which the gaseous medium is depressurized, characterized in that the conditioning unit (3) with a base body (20), in which a gaseous medium flowed through the media line (22) is arranged, and with a buffer memory (21) for storing heat out is, wherein between the base body (20) and buffer memory (21) a temperature control unit (23) is arranged, and a control unit (10) is provided which controls the conditioning unit (3) to maintain a predetermined set temperature (Tsoii) of the gaseous medium ,
    [22]
    22. Consumption measuring device according to claim 21, characterized in that in the buffer memory (21) a cooling device (26) is arranged.
    [23]
    23. Consumption measuring device according to claim 21 or 22, characterized in that after the consumption sensor (5), a further pressure control unit (7) is provided.
    [24]
    24. Consumption measuring device according to claim 21 or 22, characterized in that the consumption sensor (5) is formed of a plurality of Coriolis sensors (31, 32) with different measuring ranges.
    [25]
    25. Consumption measuring device according to claim 21 or 22, characterized in that in the gas path (17) after the consumption sensor (5) a zeroing valve (39) is arranged, with which the gas path (17) can be shut off.
    [26]
    26. Consumption measuring device according to claim 21 or 22, characterized in that in the consumption measuring device (1) an inert gas purging (41) is provided, with which the gas path (17) can be purged with inert gas.
    [27]
    27. Consumption measuring device according to one of claims 21 to 26, characterized in that in the control unit (10) a control according to one of claims 1 to 18 is implemented.
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    同族专利:
    公开号 | 公开日
    US20180275697A1|2018-09-27|
    KR20180020153A|2018-02-27|
    EP3314348A2|2018-05-02|
    AT517215B1|2016-12-15|
    WO2016206983A2|2016-12-29|
    CN108027622A|2018-05-11|
    JP2018520436A|2018-07-26|
    WO2016206983A3|2017-03-02|
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    法律状态:
    2021-02-15| MM01| Lapse because of not paying annual fees|Effective date: 20200623 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50530/2015A|AT517215B1|2015-06-23|2015-06-23|Method for controlling a conditioning unit and consumption meter with such a conditioning unit|ATA50530/2015A| AT517215B1|2015-06-23|2015-06-23|Method for controlling a conditioning unit and consumption meter with such a conditioning unit|
    JP2017566851A| JP2018520436A|2015-06-23|2016-06-09|Control method of temperature control unit and consumption measuring device provided with temperature control unit|
    US15/739,506| US20180275697A1|2015-06-23|2016-06-09|Method For Controlling A Conditioning Unit And Consumption Measuring Device Having Such A Conditioning Unit|
    CN201680037331.XA| CN108027622A|2015-06-23|2016-06-09|For adjusting the method for adjustment unit and there is the consumption measuring device of this adjustment unit|
    EP16729533.6A| EP3314348A2|2015-06-23|2016-06-09|Method for the feed-back control of a conditioning unit and consumption measuring device having such a conditioning unit|
    KR1020177036170A| KR20180020153A|2015-06-23|2016-06-09|METHOD FOR CONTROLLING CONTROL UNIT AND CONSUMPTION MEASURING DEVICE WITH THAT CONTROL UNIT|
    PCT/EP2016/063122| WO2016206983A2|2015-06-23|2016-06-09|Method for the feed-back control of a conditioning unit and consumption measuring device having such a conditioning unit|
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