EP1936288B1 - Method and system for detecting the hydraulic balance of a heating system - Google Patents

Description

The present invention relates to a method and a system for detecting and optionally carrying out a hydraulic balancing of a heating system with a fluid flow system connected radiators, in particular a hot water heating system according to the preamble of claim 1. For the implementation of the hydraulic balancing can after detection of an over- or undersupply of a radiator, the fluid flow can be regulated by individual radiators.

In pump hot water heaters with connected via a pipe system radiators often occurs the problem of undersupply of individual, hydraulically unfavorable located radiator with simultaneous oversupply of other, hydraulically located radiator conveniently. This problem is due to different differential pressures at the different radiators. To compensate for this, a hydraulic adjustment of the heating system must be carried out. The aim of the hydraulic balancing is to adjust the hydraulic resistances in the fluid flow system so that an adequate supply of all radiators is ensured. For this purpose, a sufficiently large differential pressure must be applied to the hydraulically most unfavorable radiator.

definierte Ventilautorität, wobei Δp_TV,100% der Druckabfall am Ventil bei voll geöffnetem Ventil und Δp_TV,Zu der Druckabfall bei geschlossenem Ventil ist. Durch die Erhöhung des hydraulischen Widerstandes steigt der Druckabfall Δp_TV,100% bei einem voll geöffneten Heizkörperventil und somit die Ventilautorität. Der Zusammenhang zwischen der Ventilautorität, der Hubstellung des Heizkörperventils und dem Durchfluss bzw. der Wärmeabgabe des Heizkörpers ist in Fig. 5 dargestellt, wobei Werte von a ≥ 0,3 anzustreben sind, um eine gute Regelbarkeit zu erreichen.For this example, radiator valves can be used with a corresponding default. For hydraulically located radiators, the hydraulic resistance is increased by selecting the default setting. This increases according to VDI 2073 as $$a=\frac{\mathrm{\Delta }{p}_{TV.100\%}}{\mathrm{\Delta }{p}_{TV.Zu}}$$

defined valve authority, where Δp _{TV, 100% is} the pressure drop across the valve when the valve is fully open and Δp _{TV, to} the pressure drop when the valve is closed. By increasing the hydraulic resistance, the pressure drop Δp _{TV increases, 100%} with a fully opened radiator valve and thus the valve authority. The relationship between the valve authority, the stroke position of the radiator valve and the flow or the heat output of the radiator is in Fig. 5 with values of a ≥ 0.3 are desirable in order to achieve a good controllability.

The hydraulic balancing by increasing the hydraulic resistance of individual radiators leads in a parallel connection of the radiator, which is commonly used today, to a reduction of the mass flow through this radiator and thus to a higher differential pressure at the hydraulics less well located radiators. The implementation of hydraulic balancing is in practice a time-consuming and lengthy process. It is therefore often not or only inaccurately carried out for time and cost reasons. Often, instead, the pump is set to a higher speed level, which can lead to unnecessarily high power consumption and flow noise.

In the DE 100 03 394 A1 a method for hydraulic balancing a heating system is described. This procedure is based on a measurement and regulation of the differential pressure on the radiator itself. The adjustment is made by adjusting the return valve is done by hand and thus has the disadvantage that the process is tedious and cumbersome and high costs.

From the DE 42 21 725 a method for automatically achieving a hydraulic balancing is known in which the radiator thermostatic valves initially fully opened and the thus adjusting in each room temperature is measured. In rooms where the resulting temperature is too high, the thermostatic valves are closed until the desired temperature is reached. The degree of opening of the thermostatic valves determined in this way is used as the maximum opening for all other control activities. However, the method has the disadvantage that first the stationary state of the system must be awaited before an adjustment can take place.

Another procedure is over DE 102 43 076 A1 known. This method uses actuators with integrated temperature differential control, which are mounted on a pre-settable radiator valve adapter for adjustment purposes. The volume flow through the radiator is varied by the presettable adapter until a predetermined difference between the flow and return temperatures is reached. After completion of the adjustment process, the actuators are removed again and replaced by thermostatic heads. The disadvantage of this method is that additionally presettable adapters are needed, which must be mechanically compatible with the actuator. In addition, this method also requires manual implementation and is therefore cumbersome and expensive.

From the WO 2004/083733 A1 a method for adjusting a plurality of parallel-connected heat exchanger is known in which for each heat exchanger from the current operation, the heat demand of the heat exchanger specific size is determined in a predetermined period of time, the specific sizes of all heat exchangers are compared and the setting of the heat exchanger with the The smallest heat demand indicating size is changed in the sense to increase the heat demand. The heat exchanger with the largest consumption of heat transfer medium is penalized so to speak, by the flow rate of heat transfer medium is reduced.

From the EP 0 189 614 A1 a device for adjusting a heating installation is known in which each radiator is provided with a presettable valve in the inlet of the heating medium. This allows the flow through the individual radiators to be adjusted so that the hydraulic balancing of the various radiators is balanced.

The WO 03/052536 A2 describes a method for adapting the heat output in heating systems by specifying a flow temperature, which is derived from a building supply state. The building supply state is determined from supply states of the individual radiators, which indicate their current heat demand, which is derived, for example, from the valve positions of the individual radiator valves.

The object of the invention is to provide a simple way for the detection and possibly carrying out a hydraulic balancing a heating system, with which it can be automatically detected which radiators are undersupplied. For this purpose, it is preferable to use devices already present on radiators, such as room temperature controls and / or consumption cost recording devices such as heat cost allocators.

This object is achieved in a method of the type mentioned above with the features of claim 1. It is particularly provided that for each radiator, the thermal dynamics of a through the radiator and the characteristic values of several radiators, in particular all radiators of a heating circuit of the heating system, and / or several (eg at least two) temporally successive characteristic values of a radiator, in particular after a flow temperature change in the heating circuit or the heating system, to detect a hydraulic over- or undersupply of a radiator are compared. A possibly necessary after the detection of hydraulic balancing can be done automatically by adjusting or limiting the radiator valve positions, which in a simple way, a regulation of the fluid flow is effected.

A particular advantage of the invention is that the thermal dynamics is performed in a room by measuring thermal or heating dynamic variables that can be detected in the current heating operation. The evaluation of the hydraulic conditions is carried out in a simple manner by comparing the characteristics of the thermal space dynamics, unfavorable hydraulic conditions are present when the space or heating dynamics of different radiator significantly different values or the characteristics of a radiator for a purposeful change carried out, for example The flow temperature does not behave as with radiators with optimum hydraulic balancing. According to the invention, the evaluation of the characteristic values of several radiators can also be combined with the evaluation of the particular time profile of the characteristic value of a radiator after a defined change, for example, the flow temperature. These two ways of detecting hydraulic balancing complement each other and, in combination, can provide a particularly reliable estimate of the given hydraulic balancing. However, they can also be used individually and will be explained in more detail below. With the present invention, therefore, an analysis of the hydraulic Adjustment and possibly a correction by intervention in the hydraulic adjustment of the heating system automatically without manual intervention.

For this, the dynamic characteristic is a heating dynamics for a room, i. the speed with which an externally specified increase in temperature is carried out. From the rate of a temperature rise in a room, a heating dynamics or constant for the radiator assigned to the room is determined in each case. For hydraulic balancing, all values of the heating dynamics are then adjusted to each other by regulating the respective radiator valve positions. The heating dynamics are determined by specifying a room temperature increase and a measurement of the time required for heating. The proposed method is thus based on the evaluation of heating dynamics for each radiator. The heating dynamics or constant indicates how quickly the space heats up after the heating fluid flow through the heating element increases, wherein the increase in the heating fluid flow can be caused, in particular, by a valve opening initiated, for example, by a radiator room temperature control. The hydraulic conditions are evaluated by comparing the values of the heating dynamics for different rooms or radiators, unfavorable hydraulic conditions being present when the heating dynamics show very different values.

The heating-up constant can be determined particularly simply by specifying a set room temperature increase and by measuring the time required for heating. This can be done, for example, by means of an already existing electronic radiator room temperature control.

In particular, in addition to the heating dynamics, but possibly also as an exclusively detected size, is a parameter for the thermal dynamics of a the space heated by the radiator also uses the dead time between a preset for increasing the room temperature and the beginning of a heating process. In this case, according to the specification of such a desired room temperature increase, the time until the start of the heating process is determined, ie, until a first temperature change in the room after a changed setpoint specification by appropriate sensors, usually temperature sensor is detected. In particular, first the dead time and then the heating dynamics for the temperature increase following the dead time can be determined. This is particularly advantageous if it comes only after a certain delay to a temperature increase in the room. A large dead time means a poor supply of the radiator. This information can be used in addition to the value of the heating dynamics for conclusions on the hydraulic system of the heating system.

Radiator temperatures and / or radiator supply states, in particular their temporal change or discharge, which are detected for different radiators and / or over time for a radiator, for example after a deliberately made flow temperature change, are also considered as additional or alternatively used parameters become. As Heizkörpertemperaturen Heizköpervorlauf-, Heizkörperrücklauf- and / or radiator surface temperatures and their particular related to the room air temperature overtemperatures can be detected. Embodiments with alternatively used characteristics do not fall under the scope of the claims. The radiator supply state is derived from the aforementioned temperatures and / or from the valve position of the radiator size, which indicates the heat demand of the radiator or the heating surface. The measured values required for determining the radiator temperatures or radiator supply states can, for example, be determined by existing electronic heat cost allocators. Also from the comparison of such characteristic values for a radiator, in particular in the course of time, can be determined whether a radiator or other heating surface such as a floor heating, for which the Invention is also used in the heating system is hydraulically balanced properly.

The following basic idea can be used: If the hydraulic supply to a heating surface in the heating system is acceptable, a small change in the flow temperature compared to the absolute height of the optimum flow temperature can be compensated by a changed mass flow of the heating fluid through the radiator or the heating surface become. In a deliberately carried out, small reduction of the flow temperature in the entire heating system, there is an increase in the stroke position of the radiator valve and consequently to an increase in mass flow, provided that the heating system and the radiator are adjusted hydraulically meaningful and the heat load remains constant during this time. In this case, therefore, a slightly reduced flow temperature can be compensated by increasing the mass flow and it is expected that after a sufficiently sized transitional time measured by a heat cost allocator or corrected with correction factors mean over-temperature of the radiator undergoes only a slight change. The supply state of the radiator is derived from the radiator mass flow, this indirectly proportional size and will decrease (see also the in Fig. 6 shown relationship), wherein the heat output of the radiator remains approximately constant assuming the same heating load. If this expected behavior does not occur on the radiator, the hydraulic balancing of the heating system is not optimal and should be repeated.

In an advantageous embodiment of the proposed method, a characteristic value can be represented by a transmission element of first or higher, for example. Second, order or a differential equation whose parameters are determined or estimated. Such mathematically representable functions allow the dynamics of the system to be taken into account particularly well and quickly. In this case, unfavorable hydraulic conditions exist if the determined or estimated parameters for the individual radiators deviate greatly from each other.

In order to avoid too rapid a change in the values of the heating dynamics, the dead time and / or other parameters of the transmission elements or differential functions and to suppress the influence of temporary disturbances, for example an external heat influence due to direct solar radiation during a monitored heating phase, the new one can be provided Values not to be taken over directly, but to be weighted with old values, for example by averaging.

A particularly favorable constellation for determining the characteristic values is when all radiators simultaneously initiate a heating phase. Then the heating dynamics or other characteristics can be determined simultaneously for all radiators. This can be realized that a radiator room temperature control for all rooms specifies a particular same increase in temperature as the setpoint. In an optimally hydraulically balanced system, the room temperature would then have to increase in the different rooms in approximately equal periods. In the case of different characteristic values, it is thus possible to conclude a not completely balanced hydraulic state in a particularly reliable manner.

However, it is also possible to determine automatically the heating dynamics or other characteristic values additionally in each room, for example by a temperature control individual room temperature control in a room, even if in this case the overall hydraulic situation of the heating system, detected for example. By determining different Aufheizkonstanten different can be. Embodiments with the use of other characteristic values do not fall under the scope of the claims. By accepting this disadvantage, however, hydraulic balancing can be adapted quickly and flexibly to changes in the system and constantly updated during normal operation. Especially when updating already existing characteristic values with new values for the heating dynamics, the dead time and / or other parameters of the transfer elements or differential equations, the new values can be weighted with old values.

According to a preferred embodiment of the method, the matching of the characteristic values takes place iteratively, i. After a change in the stroke of the valve position on a hydraulically over- or underserved radiator, the corresponding characteristic values are determined again at a next predetermined temperature change, adjusted and set the resulting valve position limits accordingly. In this way, the best possible hydraulic balance is achieved over time, which also adapts automatically to a changed hydraulic situation, for example. A permanent shutdown of a particular radiator in an unused space, adapts.

The heating-up constant can be determined particularly simply by specifying a set room temperature increase and by measuring the time required for heating. This can be done in particular by means of an already existing electronic radiator room temperature control. The characteristic values can be determined decentrally by a radiator room temperature controller equipped with room temperature sensors and transmitted to a control center or determined in a control room connected to room temperature sensors for the respective rooms and the radiator room temperature controllers.

Thus, by evaluating the different radiators associated characteristics, eg. Aufheizdynamiken, determined by unfavorable hydraulic conditions under or over supply of a radiator. If, for example, the heating constant for a radiator indicates an oversupply, the maximum valve lift used can be reduced. Thus, the hydraulic conditions of the radiators of the heating system are automatically adapted to each other and the values of the heating dynamics are approximately equal to each other. A manual intervention is not necessary. The values of the heating dynamics are therefore also a particularly suitable determinant for the hydraulic properties of the heating system because they take into account the dynamic heating situation and not only an absolutely achievable room temperature.

The regulation of the radiator valve position can preferably be effected by the stroke of the radiator valve used in particular by a radiator control. If the maximum valve lift used for an overheated radiator is limited, this means that even with a desired heating process less heating fluid gets into the radiator. This limitation automatically increases the differential pressure on hydraulically less favorably located radiators in the closed heating system. This leads to an optimized hydraulic balancing of the heating system, which significantly improves the heating behavior.

Accordingly, the invention relates to a system for detecting a hydraulic balancing a heating system with fluid-flow radiators. The system is constituted by a device adapted to carry out the method described above and comprises a detection device for detecting the room temperature of a space heated by a radiator, a radiator temperature and / or a valve position of a radiator valve, a computing unit for determining the thermal dynamics of the radiator Heated room indicating characteristic value from the detected room temperature, radiator temperature and / or valve position and a comparison device for comparing a characteristic with the characteristics of other rooms or radiators and / or more temporally successive following characteristic values of a radiator. The arithmetic unit and / or the comparison unit, which, for example, can be accommodated in a common or different microprocessor (s), are set up to carry out the method described above. In the case of a common microprocessor, the system may have a central unit with a computing unit, which is set up to carry out the method. In this case, the center may be a room temperature control, a consumption value detection device and / or a central apartment for temperature control or detection.

It is particularly advantageous when the detection device is integrated into a heat cost allocator and / or a single room temperature control, for example in the form of a radiator room temperature controller, since such systems are present in a variety of homes anyway, so that the inventive hydraulic balancing example Programs can be implemented in existing systems. In this sense, the arithmetic unit in an individual room control and / or a Verbrauchswert- or heating cost detection device and / or a central control units and / or data collector can be integrated.

If, for example, several apartments are supplied by a common heating circuit, ie a coherent hydraulic system, it makes sense that several individual room regulations, consumption value or heating cost detection devices and / or the central control unit in particular of the heating circuit or the heating system communicate with each other, so that the individual Characteristics can be compared. The characteristic values can be determined centrally in the common control unit or decentrally in the respective computing units of the individual room controls and / or consumption value or heating cost detection devices.

Finally, the system preferably has a control device for adjusting the valve lift of the radiator valves so that the hydraulic balancing can take place immediately. The hydraulic balancing can be done in particular by adjusting the valve lift of a radiator.

Further developments, advantages and applications of the present invention will become apparent from the following description of exemplary embodiments and the drawings.

Fig. 1

einen Signalflussplan für die Ermittlung von Kennwerten zur Durchführung eines hydraulischen Abgleichs;

Fig. 2

Kenngrößen zur Bestimmung der Aufheizdynamik;

Fig. 3

eine schematische Darstellung einer Zweirohr-Heizungsanlage mit einem erfindungsgemäßen System zur Detektion und ggf. Durchführung eines hydraulischen Abgleichs;

Fig. 4

eine schematische Darstellung der Kommunikationsverbindungen des erfindungsgemäßen Systems gemäß Fig. 3;

Fig. 5

den Zusammenhang zwischen dem relativen Ventilhub und dem Durchfluss (relativer Volumenstrom) bzw. dem relativen Ventilhub und der Wärmeabgabe (relative Heizkörperleistung) eines Heizkörpers (Radiator) bei verschiedenen Ventilautoritäten zwischen a = 1 und a = 0,1 und

Fig. 6

den Zusammenhang zwischen dem relativen Heizflächen-Massenstromverhältnis und dem Heizflächenversorgungszustand.

Show it:

Fig. 1

a signal flow chart for the determination of characteristics for performing a hydraulic balancing;

Fig. 2

Parameters for determining the heating dynamics;

Fig. 3

a schematic representation of a two-pipe heating system with a system according to the invention for the detection and possibly carrying out a hydraulic balancing;

Fig. 4

a schematic representation of the communication connections of the system according to the invention Fig. 3 ;

Fig. 5

the relationship between the relative valve lift and the flow (relative volume flow) or the relative valve lift and the heat output (relative heater power) of a radiator (Radiator) at different valve authorities between a = 1 and a = 0,1 and

Fig. 6

the relationship between the relative heating surface mass flow ratio and the Heizflächenversorgungszustand.

In Fig. 1 schematically a signal flow diagram of the invention is shown, after which a characteristic value can be determined for each heated by a radiator room, which indicates the thermal dynamics of this heated by the radiator space.

For this purpose, the temperature θ is measured in a space heated by the radiator and / or on the radiator itself by means of a temperature sensor and fed to a computing unit 1, in which the method for determining the dynamic characteristic value is implemented, which is used for carrying out the hydraulic balancing , The measured temperature θ may be a radiator _temperature θ _HKV1 , θ _HKV2 measured at a room temperature θ _room or, for example, with a consumption value _detector (heat cost allocator). In addition, the relative stroke position h of a radiator valve, ie its relative opening degree, can be detected.

This information is used on the basis of a transfer element or a differential equation D (θ) in the arithmetic unit 1 to determine a dynamic characteristic for each radiator. This parameter may be the heating dynamics k _therm , the dead time t _T , a time constant T, a gain K or a radiator supply state VZ, a (corrected or uncorrected) radiator overtemperature Δ _log or their time derivative.

For the determination of the heating dynamics k _therm , the time t _start and the actual temperature θ _start are stored at the beginning of a heating phase defined from the outside. As soon as the setpoint temperature θ _{target has been} reached, the heating-up time dynamics k _{therm are} calculated.

gilt. Die Aufheizdynamik k_therm gibt also an, wie schnell die Temperatur in dem Raum ansteigt, und stellt somit eine wesentliche dynamische Kenngröße dar.This results from the temperature increase Δθ = θ _setpoint - θ _start during the heating phase and the time required for this Δt = t _end - t _start , so that $k_{\mathit{therm}}={}^{\mathrm{\Delta }\theta }{/}_{\mathrm{\Delta }t}$

applies. The heating dynamics k _therm thus indicates how fast the temperature in the room increases, and thus represents a significant dynamic characteristic.

A variant consists of first determining a dead time t _T and then the heating dynamics k _therm for the following temperature increase, wherein the dead time t _{T is} the time interval between the time at which a heating phase is predetermined and the detection of a temperature rise. This is particularly advantageous when it comes only after a certain delay to a temperature increase. A large dead time t _T means a poor supply of the radiator and can thus serve as a dynamic characteristic.

An overview of the meaning of the above quantities can be the temperature-time diagram of Fig. 2 be removed.

der Zusammenhang $${\bar{k}}_{\mathit{therm}}=\frac{K\cdot h}{\mathrm{\Delta }t}\cdot {1-\exp \left[-\left(t-t_0\right)/T\right]}_{\mathrm{\Delta t}>4T}\approx \frac{K\cdot h}{\mathrm{\Delta t}}=\frac{\mathrm{\Delta }{\vartheta }_{\mathit{Raum}}}{\mathrm{\Delta t}}$$

zwischen der Aufheizdynamik k_therm und den Kenngrößen Verstärkung K, Zeitkonstante T, relativer Ventilhub h, und Aufheizdauer Δt = t_Ende - t_Start der Differentialgleichung D(ϑ).Furthermore, it is possible to represent the heating process by a differential equation D (θ) or by a dynamic transfer element first, second or higher order and estimate the parameters of the differential equation D (θ) or the transfer member with known identification method and from there the heating time or the start time t _start the heating phase before the setpoint step and finally calculate the heating dynamics k _therm . This leads to an accelerated convergence in an iterative calculation of the heating dynamics k _therm . For example, the differential equation D (θ) for the room air behavior or a radiator temperature follows $$\dot{\theta }\left(t\right)+\frac{1}{T}\cdot \left[\theta \left(t\right)-\mathrm{<figure-callout\; id="0"\; label="\theta \; t"\; filenames="imgf0004.png"\; state="\{\{state\}\}">\theta \; </figure-callout>}\left(t_{}\right)\left({}_0\right)\right]=\frac{K\cdot H}{T}$$

the relationship $${\tilde{k}}_{\mathit{therm}}=\frac{K\cdot H}{\mathrm{\Delta }t}\cdot {1-\exp \left[-\left(t-{\mathrm{<figure-callout\; id="0"\; label="t"\; filenames="imgf0004.png"\; state="\{\{state\}\}">t</figure-callout>}}_0\right)/T\right]}_{\mathrm{.delta.t}>4T}\approx \frac{K\cdot H}{\mathrm{.delta.t}}=\frac{\mathrm{\Delta }{\theta }_{\mathit{room}}}{\mathrm{.delta.t}}$$

between the heating dynamics k _therm and the parameters gain K, time constant T, relative valve lift h, and heating time Δt = t _end -t _{start of} the differential equation D (θ).

If the valve lift h is not known, the time-variable product K * h must be estimated instead of the gain K. This leads to a reduction in the convergence speed of the process. Therefore, the knowledge of Ventilstellhubes h is advantageous, but not condition for the feasibility of the method according to the invention.

The calculation of the heating dynamics k _therm and the dead time t _T is typically iterative. The new values of the heating time constants k _therm , dead times t _T or the other parameters do not have to be taken over directly, but can be weighted with the old values. This prevents the values from changing too fast. The influence of disturbances (eg external heat influence during the heating phase) is thus reduced.

In Fig. 3 a system for carrying out a hydraulic balancing of a heating system 2 with fluid radiators 3 is shown, which are connected via a two-pipe system 4 with a flow line 5 and a return line 6 to a central heat generator 7. The two-pipe system 4 extends through several apartments 8 and provides a variety of radiators 3. Therefore, 3 different hydraulic conditions prevail on the radiators, which should be suitably balanced.

For this purpose, a radiator-room temperature controller 9 is provided with a detection device 10 to each radiator 3, which detects the room temperature θ of a heated by a radiator 3 space and the valve position h of a radiator valve 11 to which the radiator temperature control 9 acts. Alternatively or additionally, 3 consumption value detecting means 13 for measuring radiator temperatures θ, such as a Heizköperoberflächen-, Heizkörpervorlauf- and / or Heizkörperrücklauftemperatur provided on the individual radiators. Furthermore, a temperature sensor 14 for detecting the flow temperature in the heating system 2 for determining variables derived from the detected temperatures, such as, for example, a radiator supply state VZ, may be provided.

For example. the room temperature θ and the valve position h sends the radiator room temperature controller 9, for example. By means of radio communication to one of the respective apartment 8 associated central control unit 12 (control center), which also communicate with each other. The same applies to the consumption value detection devices 13 and the temperature sensor 14. Each or a control center 12 is provided with a computing unit, not shown, which determines for each heater 3 a thermal dynamics of a heated by the radiator 3 space characteristic value. In a control center 12, a comparison device, also not shown, is also provided, which compares all determined characteristic values in order to draw a conclusion on the hydraulic behavior of the heating system 2. Then, starting from this control unit 12, possibly via other control panels 12, the radiator room temperature controller 9 is addressed to by regulations for the valve Stel-lungen the radiator valves 11, for example, to limit the maximum stroke and thus to provide a hydraulic compensation.

The corresponding communication paths between the individual radiator room temperature controllers 9 and the control centers 12 are in Fig. 4 illustrated again in an explanatory manner, wherein the double arrows indicate a bidirectional communication. The system has a plurality of decentralized control units 12, to each of which a plurality of radiator room temperature controllers 9 and / or consumption detection devices 13 are assigned. Between radiator room temperature controllers 9 and associated control unit 12, there is a bidirectional communication link. There is a unidirectional or bidirectional communication connection between consumption recording devices 13 and assigned control unit 12. There are also bidirectional communication links between the remote control units 12. Thus, a correspondingly configured control unit 12 can take over the evaluation of the heating dynamics k _therm for the entire system and, for example, from the evaluation resulting Maximalhubwerte h _max for the radiator valves 11 individual radiator 3 via the corresponding decentralized control units 12 again to the Heizköperregler 9 transmit then take these values into account when controlling the temperature.

However, the invention is not to those in the Fig. 3 and 4 illustrated embodiment limited. For example, it is possible to choose another type of communication instead of radio communication. In addition, the detection device, arithmetic unit and comparison unit required according to the invention can be located in devices other than those described above. The system described is only particularly advantageous because radiator-room temperature controller 9 with temperature sensors or consumption value detection devices 13 and control panels 12, for example. In the context of a room temperature control and / or heating cost detection anyway, so that the invention can be implemented with little or no additional hardware.

The implementation of the method according to the invention will be described again concretely on the example of the heating dynamics k _therm . The method is based on the calculation and evaluation of the heating dynamics k _therm for each radiator 3. The heating dynamics k _therm indicates how fast the space surrounding the radiator 3 heats up. If the heating dynamics k _{therm of} a radiator 3 always comparatively small, can be closed to a hydraulically unfavorable adjustment of this radiator 3 compared to the other radiators 3 of the heating system 2. The method can be realized according to the other specified characteristic values.

The heating dynamics k _therm is calculated for each radiator 3 by an electronic radiator room temperature controller 9, a consumption value detection device 13 or by a decentralized or central control unit 12. The attached to the radiator valves 11 radiator room temperature controller 9 record for the room air actual temperature θ _Ist or possibly also the Ventilstellhub h and send these values to at least one control unit 12. Likewise, the required actual temperature θ _Is also from other suitable devices such about room temperature sensors or electronic heat cost allocators as consumption value detection devices 13, are transmitted to the control units 12 or to the radiator room temperature controller 9. The radiator-room temperature controller 9 or the control units 12 calculate from the received measured values cyclically the characteristics of the thermal space dynamics including the heating dynamics k _therm for each radiator 3. Advantageously, the calculation of these parameters from measured values during the heating phase before or after a set temperature jump. If the characteristic values of the thermal room dynamics including the heating dynamics k _therm of the Radiator room temperature controllers 9 or determined by another (electronic) device, they transmit the results to a decentralized or to a central control unit 12. All calculation results are preferably transmitted to an excellent central control unit 12. This generates a list of all dynamic parameters including the heating dynamics k _{therm of} all radiators 3 and performs a rating including a comparison of these characteristics. From the evaluation of the dynamic characteristics and in particular the heating dynamics k _therm is closed to the hydraulic adjustment of the radiator 3. In particular, the hydraulically unfavorably located heating elements 3 can be determined on the basis of the heating dynamics k _therm .

For the sake of simplicity, the following statements relate only to the heating dynamics k _therm . They also apply analogously to dead times or to parameters of the differential equations or transfer elements.

In the central control unit 12, a comparison of the heating dynamics k _{therm of} all radiators 3. From this comparison follows the information about the hydraulic adjustment of the radiator valves 11. If all values of the heating dynamics k _therm in the same order of magnitude, this indicates a uniform heating of all rooms , This means that all rooms are supplied with heat evenly and the hydraulic balancing of the heating system 2 is correct.

If there is a large, absolute or relative difference between the values of the heating dynamics k _therm , this means uneven heating. The cause of this need not necessarily be in a poor hydraulic balance. There may also be other causes, such as disturbances such as an open window or poor adaptation of the radiator output to the heat demand of the room. For example, one for the To be heated space to small sized radiator 3 have a long heat up, while a too large sized radiator 3 has a rapid heating result.

It is therefore advantageous to average the values of the heating dynamics k _therm over a certain period of time, for example by arithmetic or sliding mean value formation, in order to minimize disturbing influences. If the mean values of the heating dynamics k _{therm are} too far apart, this indicates a poor hydraulic balance or incorrectly dimensioned radiator 3.

In order to distinguish between poor hydraulic balancing and incorrect dimensioning of the radiator 3 can still according to the invention in Fig. 2 use defined dead time t _T. Thus, in the case of poor hydraulic balancing, it is more likely that a dead time t _{T will have} to be determined first before the room temperature rises. With a wrong sized but well balanced radiators 3, a temperature increase without long dead time t _{T will be} noted.

Alternatively, instead of the heating dynamics k _therm , the parameters K (gain) and T (time constant) or the ratio K / T can also be evaluated. This embodiment does not fall within the scope of the claims. Thus, from comparatively small amplification and a large time constant, ie from a small ratio K / T, to poor hydraulic balancing and comparatively large amplification and small time constant, ie from a high ratio K / T, good hydraulic balancing of the corresponding radiator 3 can be concluded. Furthermore, the particular temporal behavior of radiator temperatures 9 or radiator supply states VZ can be considered.

Fig. 6 shows the relationship between the relative heating surface mass flow ratio, which, as in Fig. 5 shown with the relative valve lift is correlated, and a Heizflächenversorgungszustand. The setpoint mass flow ratio in this example is chosen so that at 40% of the relative mass flow ratio (based on the nominal mass flow), the heating surface supply state is zero, ie an optimal heat supply is present. A thermal oversupply on the heating surface, ie a Heizflächenversorgungszustand. > 0, corresponds to a lower heating surface mass flow ratio and a thermal undersupply on the heating surface, ie a Heizflächenversorgungszustand <0, corresponds to a higher Heizflächenge mass flow ratio than 40%. According to the in Fig. 6 illustrated, linearized dependence can therefore be concluded by evaluating the Heizflächenversorgungszustandstendenz on the state of the current hydraulic balancing of the individual heating surfaces. In the case of a hydraulically correctly balanced heating surface, an increase in the flow surface mass flow ratio and thus a decreasing heating surface supply state follow from a flow temperature reduction. By observing this relationship, it is possible to infer the hydraulic condition of the various heating surfaces. This is particularly useful when the supply state of the individual heating surfaces is determined anyway within the scope of a heat capacity adaptation control.

An advantage in particular for the starting behavior of the method is when all radiator room temperature controller 9 at the same time a heating phase, caused by a set temperature jump in the positive direction begin. If this state is not possible by the setting of radiator-room temperature controller time profiles, a corresponding command can be triggered in the central control unit 12. The execution of this command causes all radiator room temperature controllers 9 to perform a heating-up phase almost simultaneously.

Prerequisite for the implementation of the method is that the heating system 2 is turned on and provides sufficient heat to heat the rooms available.

If the system detects that a poorly balanced hydraulic pipe system 4 of the heating system 2 is present, the reaction consists of the stroke h of the radiator valves 11 of radiators 3 with larger values of the heating dynamics k _therm (corresponds to a rapid heating of the room and thus a good heat supply ) For example, in the radiator room temperature controller 9 limit. The limitation takes place in an iterative process until the heating dynamics k _{therm of} all radiators 3 are approximately the same. A parameterisable minimum stroke h _min must not be undercut.

Due to the limitation of the stroke h of the flow of the heat carrier is thus limited by a radiator 3 with a larger value of the heating k _therm . As a result, the poorly balanced radiators 3 is a larger amount of the heat carrier available. To limit the stroke h the corresponding radiator room temperature controller 9 is transmitted a maximum value h _max for the hub. In normal control mode, the radiator room temperature controller 9 will not exceed this maximum value h _max .

In the presence of an oversized radiator 3 and the stroke h of the radiator room temperature controller 9 can be limited, whereby the maximum heat output of this radiator 3 is also limited.

The information obtained by the system on the hydraulic balancing of the heating system 2 can be prepared in a suitable form the user made available. This can be done, for example, by a display on a central control unit 12. The user can feel so about the Inform the current status of the system and, if necessary, carry out readjustments manually, such as changing the valve presetting.

By constantly monitoring the heating dynamics, the process allows automatic adaptation to changing hydraulic conditions. Therefore, an easily manageable possibility for automatic adjustment of a heating system is created by the inventive method and the system according to the implementation of this method, which can in particular be automatically kept up to date, without a manual adjustment is required.

LIST OF REFERENCE NUMBERS

1

computer unit

2

heating system

3

radiator

4

Two-pipe system, fluid flow system

5

supply line

6

Return line

7

heat generator

8th

Apartments

9

Radiator Room temperature controller

10

detector

11

radiator valve

12

Control center, control unit

13

Consumption value detection device, heat cost allocator

14

Flow temperature sensor

θ

Room or radiator temperature

θ _start

Temperature at the start of the heating phase

θ _end

Temperature at the end of the heating phase (desired setpoint temperature)

θ _target

set temperature

θ _is

Actual temperature

t _start

Time at the start of the heating phase

t _end

Time at the end of the heating phase

θ (t)

Differential equation, transfer element

k _therm

Aufheizdynamik

t _T

dead

H

Valve position, stroke of a radiator valve

VZ

Heating area supply state

Δ _log

Radiators overtemperature

Claims (12)

1. A method for detecting the hydraulic balancing of a heating system (2) having radiators (3) connected via a fluid flow system (4), wherein a characteristic value indicating the thermal dynamic of a room heated by the radiator (3) is determined for each radiator (3), and the characteristic values of a plurality of radiators (3) and/or a plurality of chronologically successive characteristic values of a radiator (3) are compared with one another for detecting a hydraulic oversupply or undersupply of a radiator (3), characterized in that a room temperature increase is set and that a heating dynamic (k_therm ), which is determined by the setting of a room temperature increase and a measurement of the time needed for heating, is used as a characteristic value, and/or the dead time (t_T) between the setting for increasing the room temperature (ϑ) and the start of a heating process is used as a characteristic value.
2. The method according to claim 1, characterized in that the temporal change in radiator temperatures (ϑ, Δ_log) and/or radiator supply states (VZ) are/is used as an additional characteristic value, wherein the radiator supply state (VZ) is a variable derived from the radiator temperature (ϑ, Δ_log) and/or the valve position of the radiator (3), which variable indicates the heat requirement of the radiator (3).
3. The method according to any one of the preceding claims, characterized in that the heating process is represented by a dynamic transfer element and/or a differential equation D(ϑ) of first, second or higher order, and the parameter of the transfer element and/or the differential equation D(ϑ) are estimated using identification methods, and therefrom, the heating duration and/or the start time of the heating phase prior to the setpoint jump and the heating dynamic (k _therm,) are calculated.
4. The method according to any one of the preceding claims, characterized in that the characteristic values are determined simultaneously for all radiators (3).
5. The method according to any one of the preceding claims, characterized in that the characteristic values are determined upon each temperature change at a radiator (3).
6. The method according to any one of the preceding claims, characterized in that detecting the hydraulic balancing is performed iteratively.
7. The method according to any one of the preceding claims, characterized in that after detection of the hydraulic balancing or state, a hydraulic balancing is performed in particular by means of regulating the fluid flow through individual radiators (3) after detecting a hydraulic oversupply or undersupply of the radiator (3).
8. A system for detecting a hydraulic balancing of a heating system (2) having radiators (3) through which a fluid flows, comprising a recording device (10, 13) for recording the room temperature (ϑ) of a room heated by a radiator (3), a radiator temperature (ϑ) and/or a valve position (h) of a radiator valve, a computing unit (1) for determining a characteristic value indicating the thermal dynamic of a room heated by the radiator (3) from the recorded room temperature (ϑ), radiator temperature (ϑ) and/or valve position (h), and a comparing device for comparing a characteristic value with the characteristic values of other radiators (3) and/or a plurality of chronologically successive characteristic values of a radiator (3), characterized in that the computing unit (1) and the comparing device are configured for carrying out the method according to any one of claims 1 to 7.
9. The system according to claim 8, characterized in that the recording device is integrated in a heat cost allocator (13) and/or a single room temperature controller (10).
10. The system according to claim 8 or 9, characterized in that the computing unit (1) is integrated in a single room controller and/or a heat cost allocating device and/or a central control unit (12).
11. The system according to claim 10, characterized in that a plurality of single room temperature controllers (10), consumption recording devices (13) and/or the central control unit (12) of a heating circuit communicate with one another.
12. The system according to any one of the claims 8 to 11, characterized in that a control device for carrying out a hydraulic balancing is provided in particular by adjusting the valve stroke (h) of a radiator valve (11).

Images