EP1936290A2 - Method and device for detecting the hydraulic state of a heating system - Google Patents

Abstract

The method involves measuring supply temperature for a heating medium in a fluid flow system and a temperature rise, which is derived from a difference of a heat body side temperature and a room air side temperature at different time points. The parameter of a heat requirement of a heating body (2) is determined. The parameter is changed over time or supply temperature. The change of the supply temperature is evaluated. An independent claim is also included for a device for detection of the hydraulic state of a heating appliance.

Description

The invention relates to a method and a system for detecting the hydraulic state of a heating system with a fluid flow system connected to radiators, which are flowed through by a heating medium having a flow temperature.

• zu geringer Differenzdruck über dem Heizkörperventil infolge hydraulisch ungünstiger Lage des Heizkörpers (beispielsweise Bezugszeichen 2f in Fig. 1),
• zu geringer Differenzdruck über dem Heizungsstrang infolge fehlerhafter Einstellung des Strangregulierventiles (Bezugszeichen 8 in Fig. 1),
• fehlerhafte Voreinstellung des Heizkörperventiles (beispielsweise Bezugszeichen 1f in Fig. 1) des unterversorgten Heizkörpers (KVS-Wert zu klein),
• fehlerhafte Voreinstellung der Heizkörperventile (beispielsweise Bezugszeichen 1 a-1 e in Fig. 1) anderer Heizkörper (KVS-Wert dort zu groß),
• Drosselung des Heizkörpermassestromes infolge nicht ausreichend dimensionierter oder nicht bedarfsgerecht eingestellter Drosselungsventile (Bezugszeichen 3a-3f in Fig. 1) beispielsweise im Heizkörperrücklauf und/oder
• zu geringer Pumpendruck der Heizungsumwälzpumpe (Bezugszeichen 4 in Fig. 1).

In such pump hot water heating systems often occurs a hydraulic undersupply of individual radiators with simultaneous oversupply of other radiators. Hydraulic undersupply of a radiator means that despite sufficient flow temperature required for reaching the desired room temperature radiator mass flow can not be achieved even with fully open radiator valve. Causes are typically

• too low differential pressure across the radiator valve due to hydraulically unfavorable position of the radiator (for example, reference numeral 2f in Fig. 1 )
• too low differential pressure across the heating line as a result of incorrect setting of the strand regulating valve (reference numeral 8 in FIG Fig. 1 )
• incorrect presetting of the radiator valve (for example, reference numeral 1f in Fig. 1 ) of the underserved radiator (KVS value too small),
• incorrect presetting of the radiator valves (for example, reference numeral 1 a-1 e in Fig. 1 ) of other radiators (KVS value too high there),
• Throttling of the radiator mass flow due to not sufficiently dimensioned or not adjusted according to demand throttling valves (reference numeral 3a-3f in Fig. 1 ), for example in the radiator return and / or
• too low a pump pressure of the heating circulation pump (reference numeral 4 in FIG Fig. 1 ).

mit

Δp _TV,100%

... Druckabfall über voll geöffnetem Heizkörperventil;

Δp _TV,Zu

... Druckabfall über geschlossenem Heizkörperventil.

To solve the problem described, a hydraulic balancing must be carried out, which includes the correct setting of the balancing, radiator and throttle valves and the circulation pump. The aim of hydraulic balancing is to set the hydraulic resistances of the heating system in such a way that the differential pressures or mass flows required for reaching the design room target temperatures are ensured for all radiators. For example, the strand differential pressure at the strand regulating valve is set at values typically in the range 150-250 mbar. In addition, for hydraulically located radiator radiator hydraulic resistance increases in favor of less favorably located radiator. This is done by reducing the KVS value of the presettable radiator valve. This increases the valve authority a, defined as per VDI 2073 $$a=\frac{{\mathrm{\Delta }p}_{\mathit{TV}.100\%}}{{\mathrm{\Delta }p}_{\mathit{TV}.\mathit{To}}}$$

With

Δp _{TV, 100%}

... pressure drop over fully opened radiator valve;

Δ p _{TV, Z u}

... pressure drop over closed radiator valve.

The relationship between valve authority, stroke position and flow or heat output of the radiator is exemplary in the Fig. 2 and Fig. 3 shown. For optimum room temperature control, values above 0.3 for the valve authority should be aimed for.

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. The main problem is the knowledge of the hydraulic condition of the entire heating system or the individual radiator of the heating system.

As a result, many radiators - not only those far away from the start of the line - are often hydraulically undersupplied. Due to ignorance of the actual cause, the resulting complaints from residents about a lack of heat supply are often countered simply by a drastic increase in the heating curve (ie the flow temperature) or by the increase in the pump pressure (ie the mass flow). This leads to unnecessarily increased heat losses in the distribution and transfer, but also to increased electricity costs of the heating circulation pump.

In the DE 100 03 394 A1 a method for performing the hydraulic balancing a heating system is described. This method is based on a measurement and adjustment of the differential pressure at the radiator. The adjustment takes place via a return valve and is carried out by hand. With regard to the determination of underserved radiators, this method has the disadvantage that the measurement of the differential pressure at each radiator is required. This causes high costs.

From the DE 42 21 725 A1 a method for automatically achieving a hydraulic balancing is known in which the radiator thermostatic valves are initially fully opened and the resulting temperature in each room 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. The method is used to determine hydraulically undersupplied radiators, but has the disadvantage that the thermostatic valves of all radiators must be operated and therefore the apartment must be entered, Furthermore, the stationary state of the plant is waiting to be evaluated before an evaluation. This is particularly disadvantageous because of the manual access. Also, it can lead to misjudgments in the implementation of the method, as one too high room temperature can also set due to incorrectly dimensioned radiator. This would be erroneously attributed to hydraulic balancing by this procedure.

Another procedure is from the 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 the method is that actuators with integrated temperature difference control with additional presettable adapters are needed, which must also be mechanically compatible to the actuator. This is a technically very expensive solution.

Finally, that describes DE 195 06 628 A1 a method for hydraulic adjustment of a heating system with a control device that fully opens all valves on the flow distributor in a commissioning program. After a certain period of operation, temperature changes first occur at those room temperature sensors which are hydraulically best supplied. Then the associated valves are closed slightly. At the end of the first operating program phase, the valves are given maximum opening degrees in accordance with the previous control behavior, taking into account, as a first approximation, the hydraulic system. This procedure is then repeated several times, even during ongoing operation, to obtain a system balance. Here, there is the problem that a temperature rise in a room must not only be causally related to the opening of the valves, but may also be caused by external influences, such as sunlight. In addition, a randomly performed Window ventilation during the adjustment program massively falsify the results of the adjustment.

To circumvent this, the object of the present invention is firstly to gain reliable knowledge of the hydraulic state of the heating system and preferably of the hydraulically poorly supplied radiators, in order to be able to initiate the correct measures in a targeted manner without an inspection of the automatic determination of the hydraulic state the apartments or the building would be necessary.

This object is achieved with the features of claims 1 and 10 by a method and an apparatus arranged for carrying out this method. For carrying out the method proposed according to the invention, provision is made in particular for the flow temperature and for each radiator to measure an excess temperature derived from a difference between a radiator side and room air side temperature at different times and from this at least one characteristic variable indicative of the heat demand of the radiator to be determined at different times and the change in the parameter over time or over the flow temperature and the temporal change in the flow temperature are evaluated.

It could be confirmed experimentally that the heat demand of a radiator during operation indicates characteristic values for a hydraulic undersupply a characteristic behavior that can be differentiated from a hydraulically well supplied condition. Thus measurements according to the invention for the determination of the hydraulic state of the heating system cyclically, ie at predetermined time intervals repeating, made and the trend of the determined parameters over time or the flow temperature can be determined continuously. As a result, for example, by temporary influences (such as simultaneous opening or Closure of a variety of valves or fluctuating room loads) caused changes in the hydraulic state (instead of the hydraulic state is often synonymous with the term "adjustment" used) can be quickly and reliably detected to countermeasures based on this finding, if necessary, such as the automatic execution of a new hydraulic balancing by changing the flow behavior in the heating system to make.

In a simple embodiment of the method proposed according to the invention, the logarithmic radiator overtemperature, the difference between radiator side air and room air side radiator temperature or the difference between the radiator surface temperature and the room air temperature can be used as a parameter. These excess temperatures, which are all characterized by a difference between the radiator side and room air side temperatures, are a measure of how much heat the radiator dissipates to the environment.

In a further embodiment, the radiator operating power ratio determined from the current radiator output and the radiator output at nominal mass flow and actual flow temperature can be used as a parameter, which can be determined particularly simply from the current logarithmic overtemperature and the logarithmic overtemperature at the standard point. As will be explained in detail later, it has been found that the operating power ratio offers a particularly significant possibility for assessing the hydraulic situation of a heating system.

The same applies to another embodiment of the method, in which as a parameter indicating the current heat demand of a radiator Heizköperversorgungszustand used, for example, as in Fig. 4 represented by means of a characteristic from the operating power ratio can be derived. The characteristic curve establishes a relationship between the operating power ratio and a radiator supply state in a heat adaptation control in which a control upstream of the actual heater control is pre-regulated to the one set value of a radiator supply state and an operating duty ratio, respectively. This is for example in the WO 03/052536 A and the DE 10 2007 029 631 A described in principle. Alternatively, the radiator supply state and the radiator operation ratio may also be in accordance with the characteristics of FIG Fig. 5 be taken as a function of the logarithmic overtemperature.

Further, by means of preferably weighted averaging or by applying a fuzzy logic from the radiator operating power ratios (BLV) or the radiator supply states (VZ), it is possible to have a heating circuit or building operating ratio (GBLV) or a heating circuit or building supply state (LV) determine and use as a characteristic.

According to the invention, it may also be advantageous to determine and evaluate several of the above-described parameters in parallel. Thus, for example, the logarithmic excess temperature and the operating power ratio or the radiator supply state can both be evaluated in their time trend in order to allow an even more reliable statement about the hydraulic state of the heating system.

In a preferred embodiment of the method, the change of the characteristic quantities can be generated via gradient formation or ratios of the differences, the latter being the simpler way in practice because the measured values are present in each case and in a simple arithmetic operation even in non-expensive ones Arithmetic units, such as simple microprocessors, can be deducted from each other. Frequently, the analytical formulas for forming the derivatives are not known or a numerical gradient formation is too expensive.

In order not to over-weight random fluctuations in the measured quantities and parameters and not to draw hasty conclusions about the hydraulic condition of the system, the changes of the parameters can be averaged over time, for example.

A particularly simple criterion for the trend evaluation of the parameter is to compare the change in the parameters over time or the flow temperature with specified characteristic or threshold values in order to distinguish a hydraulically adequately supplied state from a hydraulically undersupplied state. Such characteristic or threshold values can be well determined, as will be shown later.

In order to obtain the results of the detection of the hydraulic condition of the plant in a clear form, a state table with the states of the hydraulic supply of the individual radiators and / or the hydraulic supply of the entire heating system can be created. This can be displayed in an information unit, a service center of the heating cost detection system and / or a heat capacity adaptation control. In this case, the service center from the states of the hydraulic supply of the individual radiator can derive the states of the hydraulic supply of the entire heating system by calculation rules.

The invention further relates to a device for detecting the hydraulic state of a heating system with connected via a fluid flow system radiators, which flows through a heating medium with a flow temperature The device is equipped with at least one connection for inputting the flow temperature, at least one connection for inputting a heater-side temperature and at least one connection for inputting a room-air-side temperature and a computing unit, which is set up from the entered temperature values to determine at least one of the heat demand of the radiator indicating characteristic and to evaluate the change in the parameter over time or over the flow temperature and the temporal change of the flow temperature. In particular, the arithmetic unit is set up to carry out the described method according to the invention.

According to a particularly preferred embodiment, a plurality of connections for inputting temperatures are formed in the device as a common connection to a heat cost allocator, with which the or a part of the required temperature values are detected. In this case, it is also possible that the heat cost allocator already transfers an excess temperature or other processed characteristic or intermediate size instead of the individual temperature values. This embodiment of the invention enables a smooth integration of the proposed device into existing heat cost allocation systems, without having to adapt these systems separately.

Also, the device according to the invention may have connections for several heat cost allocators. Then, with the proposed device, the method according to the invention for detecting the hydraulic balancing can be carried out in a central device, which has, for example, only one connection for a centrally measured flow temperature. Of course, it is also possible to provide in such a central device several connections for measured in the flow of a radiator flow temperatures.

In an alternative embodiment, the device according to the invention can be integrated in a heat cost allocator that can be attached, in particular, to a radiator. This allows the hydraulic balancing to be determined decentrally and can be combined, for example, in a service center. Of course, even in the case of a centralized device, it is possible to collect the status data for hydraulic balancing in a service center, which may be separate from the device or integrated therein. The service center can serve the visualization of the respective status data.

In order to output the detected hydraulic states of the individual radiators or the entire heating system and possibly visualize, the device may have a connection for the output of determined hydraulic states of a single radiator or the entire system.

Even if the device proposed according to the invention is not limited thereto, it is particularly advantageous to design some or all of the connections as radio communication connections. Then, the proposed system for detecting the hydraulic state can be particularly easily integrated into radio systems for heating cost distribution, because the radio telegrams emitted by Funkheizkostenverteiler or correspondingly suitable temperature sensors can be easily detected in addition by the inventive device.

Other features, advantages and applications of the present invention will become apparent from the following description of exemplary embodiments and the drawings. All described and / or illustrated features alone or in any combination form the subject matter of the present invention, also independent of their summary in the claims or their back references.

Show it:

Fig. 1

schematically the construction of a designed as a hot water heating system heating system connected via a fluid flow system radiators;

Fig. 2

theoretical characteristics for the dependence of the relative volume flow on the relative valve lift at different valve authorities;

Fig. 3

theoretical characteristics for the relative heater capacity dependence on the relative valve lift at different valve authorities;

Fig. 4

a theoretical curve with the relationship between the power ratio and Heizflächenversorgungszustand;

Fig. 5

theoretical characteristics for the dependence of the heating surface supply condition and the radiator operating duty ratio on the logarithmic overtemperature;

Fig. 6

Characteristic curves of the parameters used for the detection of the hydraulic state of a heating system according to the invention radiator supply state, radiator operating ratio and radiator over temperature depending on the flow temperature at a hydraulically sufficient supply for constant Raumheizlast;

Fig. 7

Characteristic curves of the parameters used for detecting the hydraulic state of a heating system according to the invention radiator supply state, radiator operating ratio and radiator over-temperature depending on the flow temperature at a hydraulic undersupply for constant Raumheizlast;

Fig. 8

Characteristics of the invention used to detect the hydraulic balance of a heating system characteristics radiator supply condition, radiator operating ratio and radiator over temperature depending on the flow temperature at a hydraulic undersupply below a flow temperature of 60 ° C and a hydraulically sufficient supply at a higher flow temperature for constant Raumheizlast;

Fig. 9

a signal flow plan for a system according to the invention for the central determination of hydraulically undersupplied radiator and

Fig. 10

a signal flow plan for a system according to the invention for the decentralized determination of hydraulically undersupplied radiator.

In Fig. 1 schematically a heating layer 9 is shown with a boiler 5 to which a Heizungsumwälzpumpe 4 a Heizungsstrangvorlauf 6 for distributing a heating medium or fluid is connected, which is returned via a Heizungsstrangrücklauf 7 after the heating fluid flows through the radiator 2a to 2f again. In a strand regulating device 8 designed in particular as a valve, the differential pressure between the heating train feed 6 and the heating train return 7 can be set centrally.

The heating line advance 6 and the heating line return 7 forming the fluid flow system supply a plurality of different housing units 10 with the heating fluid, each being heated by two heating elements 2a, 2b; 2c, 2d; 2e, 2f is flowing. At the flow of each radiator 2 is in each case a radiator valve 1 (ie 1a, 1b; 1c, 1d; 1e, 1f), which adjusts the inflow of heating fluid according to the desired heat output of the respective radiator 2. At a desired high heat output, a radiator valve 1 can be opened maximum.

Depending on the particular installation situation of a radiator 2, the hydraulic flow conditions are different, so that even with a maximum open radiator valve 1 does not flow the same mass flow through each radiator 2. However, this is not desirable because then the disadvantaged in the hydraulic system radiator 2 does not reach the required heat output. Therefore, the maximum flow rate through hydraulically-preferred radiators 2 is provided with thermostatic valves 1 (ie, 1a.1b; 1c, 1d; 1e, 1f) with preset (KVS value) and / or throttle valves 3 provided on each radiator return (ie, 3a , 3b, 3c, 3d, 3e, 3f) in favor of the hydraulically disadvantaged radiator 2 limited. This leads to a higher differential pressure in the hydraulically disadvantaged radiators 2 and with optimal setting to the fact that the desired heat output can be delivered to all radiators 2.

This procedure is part of a hydraulic balancing. For this purpose, it is necessary to obtain knowledge beforehand that the entire system is in a hydraulically poorly balanced state and which radiators 2 are hydraulically sufficient or hydraulically undersupplied.

For this purpose, the method described below in detail for the automatic determination of hydraulically undersupplied heating elements is proposed,

By evaluating the time profiles of the heating flow _temperature θ _VL and the parameters, radiator operating ratio (BLV) 'or, radiator supply state (VZ)' or, building supply state (GVZ) 'or 'Heating circuit or building operating ratio (GBLV)', the hydraulic status of the individual radiators 2 (BLV, VZ) or the entire heating system 10 (GVZ) can be determined very well during operation of the system. Alternatively, for each radiator 2, temporal courses of the heating flow temperature θ _VL and the logarithmic radiator overtemperature Δ _log or the radiator side and room air side temperature of the electronic heat cost allocator θ _HKS , θ _RLS or the radiator surface temperatures θ _HK and the room air temperatures θ _air are evaluated.

• die Heizungsvorlauftemperatur ϑ_VL, deren Messung beispielsweise mittels Anlege- oder Tauchfühler entweder zentral im Gebäudeanschluss/ am Heizkreisgebäudeeintritt oder in geeigneter Form dezentral am Heizkörpervorlaufanschluss erfolgen kann und
• die heizkörperseitigen und raumluftseitigen Temperaturen ϑ_HKS, ϑ_RLS der elektronischen Heizkostenverteiler, deren Messung dezentral mittels elektronischer Heizkostenverteiler, insbesondere Funkheizkostenverteiler, erfolgen kann oder
• die Heizkörperoberflächentemperaturen ϑ_HK und die Raumlufttemperaturen ϑ_Luft, deren Messung dezentral mittels Raumtemperaturregler oder mittels anderer geeigneter Messtechnik erfolgen kann.

The input parameters of the process and the required measuring devices are therefore the

• the heating flow _temperature θ _VL , the measurement of which can be done, for example, by means of contact or immersion sensor either centrally in the building / on the heating circuit building entrance or in a decentralized form at the radiator supply connection and
• the radiator side and room air side temperatures θ _HKS , θ _RLS the electronic heat cost allocators, the measurement can be done decentralized by means of electronic heat cost allocators, in particular radio heat cost allocators, or
• the radiator _surface temperatures θ _HK and the room _air temperatures θ _air , the measurement can be done decentralized by means of room temperature controller or by other suitable measurement technology.

From the radiator side and room air side temperatures θ _HKS , θ _RLS or the radiator surface temperatures θ _HK and room _air temperatures θ _air can be calculated as described below each an overtemperature.

According to the various embodiments of the heating cost allocators, there are various possibilities for calculating the radiator overtemperature Δ.

mit

   ... wasserseitiger Korrekturfaktor
K_CW = 1 1-C_RF   ... raumluftseitiger Korrekturfaktor
Δ _HKV = ϑ_HKS-ϑ_RLS   ...Temperaturdifferenz des Heizkostenverteilers
ϑ _HKS   ... heizkörperseitige Temperatur des Heizkostenverteilers
ϑ _RLS   ... raumluftseitige Temperatur des Heizkostenverteilers.In a first variant, a logarithmic radiator overtemperature Δ _log for heat cost allocators according to the 2-sensor principle can be calculated as follows: $${\mathrm{\Delta }}_{\mathit{log}}=\frac{{\mathit{\theta }}_{\mathit{VL}}\mathit{-}{\mathit{\theta }}_{\mathit{RL}}}{\ln \left(\frac{{\mathit{\theta }}_{\mathit{VL}}-{\mathit{\theta }}_{\mathit{L}}}{{\mathit{\theta }}_{\mathit{RL}}-{\mathit{\theta }}_{\mathit{L}}}\right)}={\mathit{K}}_{\mathit{CW}}\mathit{\cdot }{\mathit{K}}_{\mathit{CL}}\cdot {\mathrm{\Delta }}_{\mathit{HKV}}:{\mathrm{\Delta }}_{\mathit{log}}={\mathit{K}}_{\mathit{CW}}\mathit{\cdot }{\mathit{K}}_{\mathit{CL}}\cdot {\mathrm{\Delta }}_{\mathit{HKV}}$$

With

... water-side correction factor
K _CW = 1 1- C _RF ... Room air side correction factor
Δ _HKV = θ _HKS -θ _RLS ... Temperature difference of the heat cost allocator
θ _HKS ... radiator side temperature of the heat cost allocator
θ _RLS ... Room air-side temperature of the heat cost allocator.

The radiator-specific correction factors K _CW and K _CL are calculated from the corresponding radiator-specific C values, which are known anyway for any radiator in the common practice of heating cost recording. In today's practice of heating cost distribution, fixed values are used as C values or as correction factors.

wobei

Δϑ _VL = ϑ _VL - ϑ _Luft

... die Vorlaufübertemperatur des Heizkörpers und

Δϑ _RL = ϑ _RL - ϑ _Luft

... die Rücklaufübertemperatur des Heizkörpers

sind. Ferner gelten folgende Beziehungen:

Δϑ _VL ≈ Δϑ _VL,Heizkreis

... Vorlaufübertemperatur des Heizkreises

Δϑ _VL,Heizkreis = ϑ _VL,Heizkreis - ϑ _VL,Heizkreis - ϑ _{Luft,Heizkreis}

... Vorlaufübertemperatur des Heizkreises (wird zentral gemessen und übertragen).

Alternatively, the calculation of the logarithmic radiator overtemperature Δ _log for heat cost allocators according to the 2-sensor principle in a second variant can also be carried out as follows: $${\mathrm{\Delta }}_{\mathit{log}}=\frac{{\mathit{\theta }}_{\mathit{VL}}\mathit{-}{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\frac{{\mathit{\theta }}_{\mathit{VL}}-{\mathit{\theta }}_{\mathit{L}}}{{\mathit{\theta }}_{\mathit{RL}}-{\mathit{\theta }}_{\mathit{L}}}\right)}=\frac{\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}-\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\frac{{\mathit{\theta }}_{\mathit{VL}}}{{\mathit{\theta }}_{\mathit{RL}}}\right)}=\frac{\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}-\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}\right)-\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}\right)}:{\mathrm{\Delta }}_{\mathit{log}}=\frac{\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}-\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}\right)-\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}\right)}.$$

in which

Δθ _VL = θ _VL - θ _air

... the overflow temperature of the radiator and

Δθ _RL = θ _RL - θ _air

... the return temperature of the radiator

are. The following relationships also apply:

Δθ _VL ≈ Δθ _{VL, heating circuit}

... overflow temperature of the heating circuit

Δθ _{VL , heating circuit} = θ _{VL, heating circuit} - θ _{VL, heating circuit} - θ _{air, heating circuit}

... overflow temperature of the heating circuit (measured and transmitted centrally).

mit

Δ _HKV = ϑ_HKS - ϑ_RLS

... Temperaturdifferenz des Heizkostenverteilers in Montagehöhe h (h=1 entspricht dem Vorlauf, h=0 entspricht dem Rücklauf)

K_Korr

... Korrekturfaktor

ϑ_HKS

... heizkörperseitige Temperatur des Heizkostenverteilers

ϑ _RLS

... raumluftseitige Temperatur des Heizkostenverteilers

Δϑ_VL ≈ Δϑ_VL,Heizkreis

... Vorlaufübertemperatur des Heizkreises

Δϑ_VL,Heizkreis = ϑ_VL,Heizkreis - ϑ_{Luft,Heizkreis}

... Vorlaufübertemperatur des Heizkreises (wird zentral gemessen und übertragen).

The return over-temperature Δθ _RL is determined from the theoretical radiator equation Δθ _h = Δθ ^k _VL · θ ^{(1- h )} _RL : $$\begin{array}{l}\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}=e^{y_{\mathit{RL}}}=\exp \left(y_{\mathit{RL}}\right).\\ y_{\mathit{RL}}=\ln \left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}\right)=\frac{1}{\left(1-H\right)}\cdot \left[\ln \left({\mathit{\Delta }}_{\mathit{FHKV}}\mathit{\cdot }{\mathit{K}}_{\mathit{corr}}\right)-H\cdot \ln \left({\mathrm{\Delta }}_{\mathit{VL}}\right)\right].\end{array}$$

With

Δ _HKV = θ _HKS - θ _RLS

... temperature difference of the heating cost allocator at mounting height h (h = 1 corresponds to the flow, h = 0 corresponds to the return flow)

K _corr

... correction factor

θ _HKS

... radiator side temperature of the heat cost allocator

θ _RLS

... room air-side temperature of the heat cost allocator

Δθ _VL ≈ Δθ _{VL, heating circuit}

... overflow temperature of the heating circuit

Δθ _{VL, heating circuit} = θ _{VL, heating circuit} - θ _{air, heating circuit}

... overflow temperature of the heating circuit (measured and transmitted centrally).

wobei

ϑ_VL

... Vorlauftemperatur des Heizkörpers;

ϑ _RL

... Rücklauftemperatur des Heizkörpers;

ϑ_Luft

... Umgebungslufttemperatur des Heizkörpers

sind.Similarly, the calculation of the logarithmic radiator overtemperature Δ _log for heat cost allocators according to the 3-sensor principle in a first variant: $${\mathrm{\Delta }}_{\mathit{log}}=\frac{{\mathit{\theta }}_{\mathit{VL}}\mathit{-}{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\frac{{\mathit{\theta }}_{\mathit{VL}}-{\mathit{\theta }}_{\mathit{air}}}{{\mathit{\theta }}_{\mathit{RL}}-{\mathit{\theta }}_{\mathit{air}}}\right)}.$$

in which

θ _VL

... flow temperature of the radiator;

θ _RL

... return temperature of the radiator;

θ _air

... ambient air temperature of the radiator

are.

ϑ _VL

...Vorlauftemperatur des Heizkörpers;

ϑ_RL

...Rücklauftemperatur des Heizkörpers;

ϑ _Luft

...Umgebungslufttemperatur des Heizkörpers.

Instead of heat cost allocators, a measuring device can be used which detects the following temperatures:

θ _VL

... flow temperature of the radiator;

θ _RL

... return temperature of the radiator;

θ _air

... ambient air temperature of the radiator.

wobei

Δϑ _VL =ϑ _VL -ϑ _Luft

... Vorlaufübertemperatur des Heizkörpers

ϑ_VL

... Vorlauftemperatur des Heizkörpers

ϑ_Luft

... Raumlufttemperatur am Heizkörper (ersatzweise Messung im Raum)

Δϑ _RL = ϑ _RL - ϑ _Luft

... Rücklaufübertemperatur des Heizkörpers

sind. Optional können anstelle Δϑ _VL

Δϑ _VL ≈ Δϑ _VL,Heizkreis

...Vorlaufübertemperatur des Heizkreises

Δϑ _VL,Heizkreis = ϑ _VL,Heizkreis - ϑ _{Luft,Heizkreis}

... Vorlaufübertemperatur des Heizkreises (wird zentral gemessen und übertragen)

bestimmt werden. Die Rückfaufübertemperatur Δϑ_RL ergibt sich aus der theoretischen Heizkörpergleichung Δϑ _h = Δϑ ^h _VL · ϑ^(1-h) _RL als $$\begin{array}{c}\mathrm{\Delta }{\mathit{\vartheta }}_{\mathit{RL}}=e^{y_{\mathit{RL}}}=\exp \left(y_{\mathit{RL}}\right)\end{array}$$

$$\begin{array}{c}{y}_{\mathit{RL}}=\ln \left(\mathrm{\Delta }{\mathit{\vartheta }}_{\mathit{RL}}\right)=\frac{1}{\left(1-h\right)}\cdot \left[\ln \left({\mathit{\Delta }}_{\mathit{HK}}\left(h\right)\mathit{\cdot }{\mathit{Kʹ}}_{\mathit{Korr}}\right)-h\cdot \ln \left({\mathrm{\Delta }}_{\mathit{VL}}\right)\right]\end{array}$$

mit:

Δ _HK (h) = ϑ _HK (h)-ϑ _Luft

... Temperaturdifferenz am Heizkörper in Höhe h (h=1 entspricht dem Vorlauf, h=0 entspricht dem Rücklauf)

K' _Korr

...Korrekturfaktor

ϑ_HK (h)

... Heizkörper-Oberflächentemperatur in Höhe h (h=1 entspricht dem Vorlauf, h=0 entspricht dem Rücklauf)

ϑ _Luft

... Raumlufttemperatur am Heizkörper (ersatzweise Messung im Raum).

In a second variant of the 3-sensor principle, the radiator overtemperature Δ _log can be calculated as follows; $${\mathrm{\Delta }}_{\mathit{log}}=\frac{{\mathit{\theta }}_{\mathit{VL}}\mathit{-}{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\frac{{\mathit{\theta }}_{\mathit{VL}}-{\mathit{\theta }}_{\mathit{L}}}{{\mathit{\theta }}_{\mathit{RL}}-{\mathit{\theta }}_{\mathit{L}}}\right)}=\frac{\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}-\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\frac{{\mathit{\theta }}_{\mathit{VL}}}{{\mathit{\theta }}_{\mathit{RL}}}\right)}=\frac{\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}-\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}\right)-\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}\right)}:{\mathrm{\Delta }}_{\mathit{log}}=\frac{\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}-\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}}{\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}\right)-\ell n\left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}\right)}.$$

in which

Δθ _VL = θ _VL -θ _air

... overflow temperature of the radiator

θ _VL

... flow temperature of the radiator

θ _air

... room air temperature at the radiator (alternatively measurement in the room)

Δθ _RL = θ _RL - θ _air

... return temperature of the radiator

are. Optionally, instead of Δθ _VL

Δθ _VL ≈ Δθ _{VL, heating circuit}

... overflow temperature of the heating circuit

Δθ _{VL, heating circuit} = θ _{VL, heating circuit} - θ _{air, heating circuit}

... overflow temperature of the heating circuit (is measured and transmitted centrally)

be determined. The Rückfaufübertemperatur Δθ _RL is derived from the theoretical equation radiator Δθ Δθ _h = ^h · θ _VL ^(1-h) as _RL $$\begin{array}{c}\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}=e^{y_{\mathit{RL}}}=\exp \left(y_{\mathit{RL}}\right)\end{array}$$

$$\begin{array}{c}{y}_{\mathit{RL}}=\ln \left(\mathrm{\Delta }{\mathit{\theta }}_{\mathit{RL}}\right)=\frac{1}{\left(1-H\right)}\cdot \left[\ln \left({\mathit{\Delta }}_{\mathit{HK}}\left(H\right)\mathit{\cdot }{\mathit{K\; \text{'}}}_{\mathit{corr}}\right)-H\cdot \ln \left({\mathrm{\Delta }}_{\mathit{VL}}\right)\right]\end{array}$$

With:

Δ _HK ( h ) = θ _HK ( h ) -θ _air

... temperature difference at the radiator at height h (h = 1 corresponds to the flow, h = 0 corresponds to the return flow)

K ' _corr

... correction factor

θ _HK ( h )

... radiator surface temperature at height h (h = 1 corresponds to the flow, h = 0 corresponds to the return flow)

θ _air

... Room air temperature at the radiator (substitute measurement in the room).

The measurement of θ _VL or / and θ _HK ( h ) or / and θ _Luβ can be done with any measurement technique.

wobei:

Δϑ_VL = ϑ_VL - ϑ_Luft

... Vorlaufübertemperatur des Heizkörpers

ϑ_VL ≈ ϑ_VL,Heizkreis

... Vorlauftemperatur des Heizkörpers

ϑ_Luft ≈ ϑ_{Luft,Heizkreis}

... Umgebungslufttemperatur des Heizkörpers

Δϑ_VL ≈ Δϑ_VL,Heizkreis

... Vorlaufübertemperatur des Heizkreises

Δϑ_{VL, Heizkreis} = 9_{VL, Heizkreis} - ϑ_{Luft, Heizkreis}

... Vorlaufübertemperatur des Heizkreises (Die Vorlaufübertemperatur des Heizkreises Δϑ _{VL, Heizkreis} kann somit zentral am Heizkessel oder am Gebäudeeintritt der Heizungsanlage erfasst werden.)

Δϑ _RL.100

... Rücklaufübertemperatur des Heizkörpers bei Nenn- oder Auslegungsmassestrom und aktueller Vorlaufübertemperatur

sind.In addition, a logarithmic radiator _{overtemperature} Δ _log.100 at nominal mass flow (for standard mass flow or design mass flow) is determined as follows: $${\mathrm{\Delta }}_{\mathit{log}}=\frac{{\mathit{\theta }}_{\mathit{VL}}\mathit{-}{\mathit{\theta }}_{\mathit{RL}.100}}{\ell n\left(\frac{{\mathit{\theta }}_{\mathit{VL}}-{\mathit{\theta }}_{\mathit{air}}}{{\mathit{\theta }}_{\mathit{RL}.100}-{\mathit{\theta }}_{\mathit{air}}}\right)}=\frac{{\mathrm{\Delta }}_{\mathit{VL}}-{\mathrm{\Delta }}_{\mathit{RL}.100}}{\ell n\left(\frac{{\mathit{\theta }}_{\mathit{VL}}}{{\mathit{\theta }}_{\mathit{RL}.100}}\right)}\approx \frac{{\mathrm{\Delta }}_{\mathit{VL}.\mathit{heating\; circuit}}-{\mathrm{\Delta }}_{\mathit{RL}.100}}{\ell n\left(\frac{{\mathrm{\Delta }}_{\mathit{VL}.\mathit{heating\; circuit}}}{{\mathrm{\Delta }}_{\mathit{RL}.100}}\right)}:{\mathrm{\Delta }}_{\mathit{log}.100}\approx \frac{{\mathrm{\Delta }}_{\mathit{VL}.\mathit{Heiizkreiis}}-{\mathrm{\Delta }}_{\mathit{RL}.100}}{\ell n\left(\frac{{\mathrm{\Delta }}_{\mathit{VL}.\mathit{heating\; circuit}}}{{\mathrm{\Delta }}_{\mathit{RL}.100}}\right)}.$$

in which:

Δθ _VL = θ _VL - θ _air

... overflow temperature of the radiator

θ _VL ≈ θ _{VL, heating circuit}

... flow temperature of the radiator

θ _air ≈ θ _{air, heating circuit}

... ambient air temperature of the radiator

Δθ _VL ≈ Δθ _{VL, heating circuit}

... overflow temperature of the heating circuit

Δθ _{VL, heating circuit} = 9 _{VL, heating circuit} - θ _{air, heating circuit}

... Excessive overtemperature of the heating circuit (The overflow temperature of the heating circuit Δθ _{VL, heating circuit} can thus be located centrally on the boiler or detected at the building entrance of the heating system.)

Δθ _{RL. 100}

... Return temperature of the radiator at nominal or design mass flow and current overflow temperature

are.

definiert mit:

n:

Heizkörperexponent (aus Herstellerunterlagen)

Δϑ _VL ≈ Δϑ _VL,Herzkreis ...

Vorlaufübertemperatur des Heizkreises

M_zP = (Δ _RL,xP ^1-n - Δ _VL,xP ^1-n ):

fester Parameter für Auslegungspunkt AP

Δ_RL,xP = (ϑ _RL - ϑ _Luft ) _zP :

Heizkörper-Rücklauf Auslegungsübertemperatur

Δ _VL,xP = (ϑ _VL - ϑ _Luft ) _xP :

Heizkörper-Vorlauf-Auslegungsübertemperatur.

The return temperature at standard or design mass flow is calculated as $${\mathrm{\Delta }}_{\mathit{RL}.100}={\mathrm{\Delta }}_{\mathit{RL}}\left(\frac{\stackrel{}{m}}{{\stackrel{}{m}}_{100}}=1\right)=(M_{\mathit{xP}}+{\mathrm{\Delta }{\mathit{\theta }}_{\mathit{VL}}}^{1-n}{)}^{1/\left(1-n\right)}$$

defined with:

n:

Radiator exponent (from manufacturer's documentation)

Δθ _VL ≈ Δθ _{VL, cardiovascular} ...

Flow temperature of the heating circuit

M _{z P} = (Δ _{RL, xP} ^{1- n} - Δ _{VL, xP} ^{1- n):}

fixed parameter for design point AP

_{ΔRL , xP} = (θ _RL -θ _air ) _zP :

Radiator return Excessive overtemperature

Δ _{VL, x P} = (θ _VL - θ _air ) _{x P} :

Radiator-forward design over temperature.

M_NP =(Δ _RL,NP ^1-n -Δ _VL,NP ^1-n )

fester Parameter für Normpunkt NP;

Δ _RL,NP = (ϑ_RL -ϑ _Luft ) _NP

Heizkörper-Rücklaufübertemperatur für Normpunkt;

Δ_{VL, NP} =(ϑ_VL-ϑ_Luft)_NP

Heizkörper-Vorlaufübertemperatur für Normpunkt.

For the design point: xP = AP. The design parameters of the heating system ΔRL _{, AP} , ΔVL _{, AP} are typically known from the planning documents. Alternatively, the radiator parameters of the standard point (xP = AP) (flow / return / air temperature = 90/70/20 ° C) according to DIN EN 442 can be used:

M _NP = (Δ _{RL, NP} ^{1- n} -Δ _{VL, NP} ^{1- n} )

fixed parameter for standard point NP;

Δ _{RL, NP} = ( θ _RL- θ _air ) _NP

Radiator return overtemperature for standard point;

Δ _{VL, NP} = (θ _VL -θ _air ) _NP

Radiator overflow temperature for standard point.

mit

Δ_{log, Nenn}

.. logarithmische Übertemperatur im Heizkörper-Normpunkt, z.B. im Heizkörper-Normpunkt (90,70,20): Δ_{log, 60} =59,44K;

n

... Heizkörperexponent (für jeden Heizkörper bekannt);

Δ _Log

... aktuelle logarithmische Übertemperatur.

With this information, the radiator operating power ratio BLV_HK can be calculated according to the following relationship: $$\mathit{BLV}=\frac{{\stackrel{}{\mathrm{<figure-callout\; id="100"\; label="Q\; act\; Q"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">Q\; </figure-callout>}}}_{\mathit{act}}}{{\stackrel{}{Q}}_{}}=\frac{{\stackrel{}{Q}}_{\mathit{N}}\cdot (\frac{{\mathrm{\Delta }}_{\mathit{log}\mathit{.}\mathit{act}}}{{\mathrm{\Delta }}_{\mathit{log}\mathit{.}\mathit{nominal}}}{)}^n}{{\stackrel{}{Q}}_{\mathit{N}}\cdot (\frac{{\mathrm{\Delta }}_{\mathit{log}\mathit{.}100}}{{\mathrm{\Delta }}_{\mathit{log}\mathit{.}\mathit{nominal}}}{)}^n}=(\frac{{\mathrm{\Delta }}_{\mathit{log}\mathit{.}\mathit{act}}}{{\mathrm{\Delta }}_{\mathit{log}\mathit{.}100}}{)}^n:\mathit{BLV}=(\frac{{\mathrm{\Delta }}_{\mathit{log}}}{{\mathrm{\Delta }}_{\mathit{log}\mathit{.}100}}{)}^n.$$

With

Δ _{log, nominal}

.. logarithmic overtemperature in the radiator standard point, eg in the radiator standard point (90,70,20): Δ _{log, 60} = 59,44 K;

n

... radiator exponent (known for each radiator);

Δ _log

... current logarithmic overtemperature.

The radiator operating power ratio BLV thus results in a simple manner from the ratio of Heizköperübertemperaturen Δ.

The parameter, radiator supply state (VZ) 'can from the previously calculated radiator operating ratio BLV according to Fig. 4 be determined. In addition, the parameters radiator supply state VZ and radiator operating power ratio BLV in knowledge of the logarithmic radiator overtemperature Δ _log also the characteristic according to Fig. 5 be removed. The parameters 'building supply status (GVZ)' or 'building performance ratio (GBLV)' are determined by means of fuzzy logic or weighted Averaging determined from the individual radiator supply states. A concrete example of this is in the WO 03/052536 A described.

• der Gradient oder die erste Ableitung entweder nach der Zeit t oder nach der Vorlauftemperatur ϑ_VL des Heizkörper-Betriebsleistungsverhältnisses BLV: $$\mathit{dt\_BLV}=\frac{\partial }{\partial t}\left(\mathit{BLV}\right)\approx \frac{\mathrm{\Delta }\mathit{BLV}}{\mathrm{\Delta }t},\mathit{dVL\_BLV}=\frac{\partial }{\partial {\vartheta }_{\mathit{VL}}}\left(\mathit{BLV}\right)\approx \frac{\mathrm{\Delta }\mathit{BLV}}{\mathrm{\Delta }{\vartheta }_{\mathit{VL}}}$$
  
• der Gradient oder die erste Ableitung entweder nach der Zeit t oder nach der Vorlauftemperatur ϑ_VL des Weizkörpervensorgungszustandes VZ: $$\mathit{dt\_VZ}=\frac{\partial }{\partial t}\left(\mathit{VZ}\right)\approx \frac{\mathrm{\Delta }\mathit{VZ}}{\mathrm{\Delta }t},\mathit{dVL\_VZ}=\frac{\partial }{\partial {\vartheta }_{\mathit{VL}}}\left(\mathit{VZ}\right)\approx \frac{\mathrm{\Delta }\mathit{VZ}}{\mathrm{\Delta }{\vartheta }_{\mathit{VL}}}$$
  
• der Gradient oder die erste Ableitung entweder nach der Zeit t oder nach der Vorlauftemperatur ϑ_VL des Gebäudeversorgungszustandes GVZ: $$\mathit{dt\_GVZ}=\frac{\partial }{\partial t}\left(\mathit{GVZ}\right)\approx \frac{\mathrm{\Delta }\mathit{GVZ}}{\mathrm{\Delta }t},\mathit{dVL\_GVZ}=\frac{\partial }{\partial {\vartheta }_{\mathit{VL}}}\left(\mathit{GVZ}\right)\approx \frac{\mathrm{\Delta }\mathit{GVZ}}{\mathrm{\Delta }{\vartheta }_{\mathit{VL}}}$$
  
• der Gradient oder die erste Ableitung entweder nach der Zeit t oder nach der Vorlauftemperatur ϑ_VL der logarithmischen Heizkörperübertemperatur Δ_log: $$\mathit{dt\_dt}\log =\frac{\partial }{\partial t}\left({\mathit{\Delta }}_{\log }\right)\approx \frac{\mathrm{\Delta }\left({\mathrm{\Delta }}_{\log }\right)}{\mathrm{\Delta }t},\mathit{dVL\_dt}\log =\frac{\partial }{\partial {\vartheta }_{\mathit{VL}}}\left({\mathrm{\Delta }}_{\log }\right)\approx \frac{\mathrm{\Delta }\left({\mathrm{\Delta }}_{\log }\right)}{\mathrm{\Delta }{\vartheta }_{\mathit{VL}}}$$
  
• der Gradient oder die erste Ableitung entweder nach der Zeit t oder nach der Vorlauftemperatur ϑ_VL der Differenz zwischen heizkörperseitigen und raumluftseitigen Heizkörpertemperatur ϑ_HKS, ϑ_RLS: $$\mathit{dt\_dtfhkv}=\frac{\partial }{\partial t}\left({\mathit{\Delta }}_{\mathit{FHKV}}\right)\approx \frac{\partial }{\partial t}\left({\vartheta }_{\mathit{HKS}}-{\vartheta }_{\mathit{RLS}}\right)\approx \frac{\mathrm{\Delta }\left({\vartheta }_{\mathit{HKS}}-{\vartheta }_{\mathit{RLS}}\right)}{\mathrm{\Delta }t},$$
  
  $$\mathit{dVL\_dtfhkv}=\frac{\partial }{\partial {\vartheta }_{\mathit{VL}}}\left({\vartheta }_{\mathit{HKS}}-{\vartheta }_{\mathit{RLS}}\right)\approx \frac{\mathrm{\Delta }\left({\vartheta }_{\mathit{HKS}}-{\vartheta }_{\mathit{RLS}}\right)}{\mathrm{\Delta }t}$$
  
• der Gradient oder die erste Ableitung entweder nach der Zeit t oder nach der Vorlauftemperatur ϑ_VL der Differenz zwischen Heizkörperoberflächen- und Raumlufttemperatur ϑ_HK, ϑ_Luft: $$\mathit{dt\_dthk}=\frac{\partial }{\partial t}\left({\vartheta }_{\mathit{HK}}-{\vartheta }_{\mathit{Luft}}\right)\approx \frac{\mathrm{\Delta }\left({\vartheta }_{\mathit{HK}}-{\vartheta }_{\mathit{Luft}}\right)}{\mathrm{\Delta }t},$$
  
  $$\mathit{dVL\_dthk}=\frac{\partial }{\partial {\vartheta }_{\mathit{VL}}}\left({\vartheta }_{\mathit{HK}}-{\vartheta }_{\mathit{Luft}}\right)\approx \frac{\mathrm{\Delta }\left({\vartheta }_{\mathit{HK}}-{\vartheta }_{\mathit{Luft}}\right)}{\mathrm{\Delta }{\vartheta }_{\mathit{VL}}}$$
  

For the various parameters mentioned above, the temporal change is determined as follows:

• the gradient or the first derivative either after the time t or after the flow temperature θ _{VL of} the radiator operation ratio BLV: $$\mathit{dt\_BLV}=\frac{\partial }{\partial t}\left(\mathit{BLV}\right)\approx \frac{\mathrm{\Delta }\mathit{BLV}}{\mathrm{\Delta }t}.\mathit{dVL\_BLV}=\frac{\partial }{\partial {\theta }_{\mathit{VL}}}\left(\mathit{BLV}\right)\approx \frac{\mathrm{\Delta }\mathit{BLV}}{\mathrm{\Delta }{\theta }_{\mathit{VL}}}$$
  
• the gradient or the first derivative either after the time t or after the flow temperature θ _{VL of} the Weizkörpervensorgungszustandes VZ: $$\mathit{dt\_VZ}=\frac{\partial }{\partial t}\left(\mathit{VZ}\right)\approx \frac{\mathrm{\Delta }\mathit{VZ}}{\mathrm{\Delta }t}.\mathit{dVL\_VZ}=\frac{\partial }{\partial {\theta }_{\mathit{VL}}}\left(\mathit{VZ}\right)\approx \frac{\mathrm{\Delta }\mathit{VZ}}{\mathrm{\Delta }{\theta }_{\mathit{VL}}}$$
  
• the gradient or the first derivative either after the time t or after the flow temperature θ _{VL of} the building supply state GVZ: $$\mathit{dt\_GVZ}=\frac{\partial }{\partial t}\left(\mathit{GVZ}\right)\approx \frac{\mathrm{\Delta }\mathit{GVZ}}{\mathrm{\Delta }t}.\mathit{dVL\_GVZ}=\frac{\partial }{\partial {\theta }_{\mathit{VL}}}\left(\mathit{GVZ}\right)\approx \frac{\mathrm{\Delta }\mathit{GVZ}}{\mathrm{\Delta }{\theta }_{\mathit{VL}}}$$
  
• the gradient or the first derivative either after the time t or after the flow temperature θ _{VL of} the logarithmic radiator overtemperature Δ _log : $$\mathit{dt\_dt}\log =\frac{\partial }{\partial t}\left({\mathit{\Delta }}_{\log }\right)\approx \frac{\mathrm{\Delta }\left({\mathrm{\Delta }}_{\log }\right)}{\mathrm{\Delta }t}.\mathit{dVL\_dt}\log =\frac{\partial }{\partial {\theta }_{\mathit{VL}}}\left({\mathrm{\Delta }}_{\log }\right)\approx \frac{\mathrm{\Delta }\left({\mathrm{\Delta }}_{\log }\right)}{\mathrm{\Delta }{\theta }_{\mathit{VL}}}$$
  
• the gradient or the first derivative either after the time t or after the flow temperature θ _{VL of} the difference between radiator side and room air side radiator temperature θ _HKS , θ _RLS : $$\mathit{dt\_dtfhkv}=\frac{\partial }{\partial t}\left({\mathit{\Delta }}_{\mathit{FHKV}}\right)\approx \frac{\partial }{\partial t}\left({\theta }_{\mathit{HKS}}-{\theta }_{\mathit{RLS}}\right)\approx \frac{\mathrm{\Delta }\left({\theta }_{\mathit{HKS}}-{\theta }_{\mathit{RLS}}\right)}{\mathrm{\Delta }t}.$$
  
  $$\mathit{dVL\_dtfhkv}=\frac{\partial }{\partial {\theta }_{\mathit{VL}}}\left({\theta }_{\mathit{HKS}}-{\theta }_{\mathit{RLS}}\right)\approx \frac{\mathrm{\Delta }\left({\theta }_{\mathit{HKS}}-{\theta }_{\mathit{RLS}}\right)}{\mathrm{\Delta }t}$$
  
• the gradient or the first derivative either after the time t or after the flow temperature θ _{VL of} the difference between radiator _surface and room air temperature θ _HK , θ _air : $$\mathit{dt\_dthk}=\frac{\partial }{\partial t}\left({\theta }_{\mathit{HK}}-{\theta }_{\mathit{air}}\right)\approx \frac{\mathrm{\Delta }\left({\theta }_{\mathit{HK}}-{\theta }_{\mathit{air}}\right)}{\mathrm{\Delta }t}.$$
  
  $$\mathit{dVL\_dthk}=\frac{\partial }{\partial {\theta }_{\mathit{VL}}}\left({\theta }_{\mathit{HK}}-{\theta }_{\mathit{air}}\right)\approx \frac{\mathrm{\Delta }\left({\theta }_{\mathit{HK}}-{\theta }_{\mathit{air}}\right)}{\mathrm{\Delta }{\theta }_{\mathit{VL}}}$$
  

• Der Heizkörperversorgungszustand VZ fällt,
  d.h. es gilt die Bedingung: d_VZ <-|d _VZ_UVZ,|

wobei d_VZ der Gradient / die Ableitung und d_VZ_UVZ ein einen Schwellenwert angebender Parameter ist.

• Das Heizkörper-Betriebsleistungsverhältnis BLV steigt,
  d.h. es gilt die Bedingung: d_BLV > +|d_BLY_NVZ|,

wobei d_BLV der Gradient / die Ableitung und d_BLV_UVZ ein einen Schwellenwert angebender Parameter ist.

• Die logarithmische Heizkörperübertemperatur Δ_log oder deren Äquivalent, die Differenz zwischen heizkörperseitigen und raumluftseitigen Heizkörpertemperatur, ändert sich nur unwesentlich, d.h. es gelten die folgenden Bedingungen: $$\mathit{d\_dt}\log <=\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{bzw}\mathrm{.}\mathit{d\_dtfhkv}<=\left|\mathit{d\_dtfhkv\_uvz}\right|,$$
  

wobei d_dtlog bzw. d_dtfhkv der Gradient / die Ableitung und d_dtlog_uvz bzw. d_dtfhk_uvz einen Schwellenwert angebende Parameter sind.Like that Fig. 6 and 8th can be taken, the state of a hydraulically sufficiently supplied radiator 2 can then be assumed if the following conditions are observed for the individual parameters in their time trend with decreasing flow temperature θ _VL this radiator 2 and after completion of the control-technical transition process

• The radiator supply state VZ falls,
  ie, we have the condition: d _ VZ <- | d _ VZ _ UVZ , |

where d_VZ is the gradient / derivative and d_VZ_UVZ is a threshold indicating parameter.

• The radiator operating power ratio BLV increases,
  ie the condition applies: d _ BLV > + | d_BLY_NVZ |,

where d_BLV is the gradient / derivative and d_BLV_UVZ is a threshold indicating parameter.

• The logarithmic radiator overtemperature Δ _log or its equivalent, the difference between radiator-side and room-air-side radiator temperature, changes only insignificantly, ie the following conditions apply: $$\mathit{d\_dt}\log <=\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{respectively}\mathrm{,}\mathit{d\_dtfhkv}<=\left|\mathit{d\_dtfhkv\_uvz}\right|.$$
  

where d_dtlog or d_dtfhkv are the gradient / derivative and d_dtlog_uvz and d_dtfhk_uvz, respectively, are threshold indicating parameters.

The aforementioned conditions apply to a mass flow of radiators m> 0 at approximately constant Raumheizlast. Is the radiator mass flow m = 0, ie the radiator 2 is completely throttled by closing the radiator valve 1, the logarithmic radiator overtemperature Δ _log or their equivalent, the difference between radiator side and room air side radiator temperature, approximately 0 and a hydraulic assessment is not possible. This case can be excluded by an appropriate query during the execution of the procedure.

With increasing flow temperature θ _VL apply the above conditions with inverse relations accordingly.

• Es erfolgt keine signifikante Verringerung des Heizkörperversorgungszustandes VZ,
  d.h. es gilt die Bedingung: d_VZ >= -|d_VZ_UVZ|,
  wobei d_VZ der Gradient / die Ableitung und d_VZ_UVZ ein einen Schwellenwert angebender Parameter ist.
• Es erfolgt kein signifikanter Anstieg des Heizkörper-Betriebsleistungsverhältnisses BLV,
  d.h. es gilt die Bedingung: d_BLV <=+|d_BLV_UVZ|,
  wobei d_BLV der Gradient / die Ableitung und d_BLV_UVZ ein einen Schwellenwert angebender Parameter ist.
• Die logarithmische Heizkörperübertemperatur Δ_log oder deren Äquivalent, die Differenz zwischen heizkörperseitigen und raumluftseitigen Heizkörpertemperatur, fällt, d.h. es gelten die folgenden Bedingungen: $$\mathit{d\_dt}\log <-\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{bzw}\mathrm{.}\mathit{d\_dtfhkv}<-\left|\mathit{d\_dtfhkv\_uvz}\right|,$$
  

wobei d_dtlog bzw. d_dtfhkv der Gradient / die Ableitung und d_dtlog_uvz bzw. d_dtfhk_uvz einen Schwellenwert angebende Parameter sind.If a radiator 2 is hydraulically undersupplied, apply to the individual characteristics in their time trend with decreasing flow temperature θ _VL this radiator 2 and after completion of the control-related transition process, the following conditions, such as Fig. 7 and 8th refer to:

• There is no significant reduction in the radiator supply state VZ,
  ie the condition applies: d _ VZ > = - | d _ VZ _ UVZ |,
  where d_VZ is the gradient / derivative and d_VZ_UVZ is a threshold indicating parameter.
• There is no significant increase in the radiator operating power ratio BLV,
  ie the condition applies: d _ BLV <= + | d _ BLV _ UVZ |,
  where d_BLV is the gradient / derivative and d_BLV_UVZ is a threshold indicating parameter.
• The logarithmic radiator overtemperature Δ _log or its equivalent, the difference between radiator-side and room-air-side radiator temperature, falls, ie the following conditions apply: $$\mathit{d\_dt}\log <-\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{respectively}\mathrm{,}\mathit{d\_dtfhkv}<-\left|\mathit{d\_dtfhkv\_uvz}\right|.$$
  

where d_dtlog or d_dtfhkv are the gradient / derivative and d_dtlog_uvz and d_dtfhk_uvz, respectively, are threshold indicating parameters.

The aforementioned conditions apply to a mass flow of radiators m> 0 at approximately constant Raumheizlast. If the radiator mass flow m = 0, ie the radiator is completely throttled by closing the radiator valve, the logarithmic radiator overtemperature Δ _log or their equivalent, the difference between radiator side and room air side radiator temperature, approximately 0 and a hydraulic assessment is not possible. This case can be excluded by an appropriate query during the execution of the procedure.

When evaluating the building supply condition GVZ as a parameter whose temporal tendency is evaluated, regardless of the question of the hydraulic supply individual radiator 2 can make a statement about the hydraulic balance of the entire heating system 9.

• Der Gebäudeversorgungszustand GVZ fällt analog zu der Kennlinie Heizkörperversorgungszustand VZ gemäß Fig. 6,
  d.h. es gilt die Bedingung: d_GVZ < -|d_GVZ_UVZ|,
  wobei d_GVZ der Gradient / die Ableitung und d_GVZ_UVZ ein einen Schwellenwert angebender Parameter ist.
• Die über alle aktiven Heizkörper 2 mittlere logarithmische Heizkörperübertemperatur d_dtlog_av oder deren Äquivalent, die Differenz zwischen heizkörperseitigen und raumluftseitigen Heizkörpertemperatur d_dtfhkv_av, ändert
  sich nur unwesentlich, d.h. es gelten die Bedingungen: $$\mathit{d\_dt}\mathrm{log\_}\mathit{av}<=\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{bzw}\mathrm{.}\mathit{d\_dtfhkv\_av}<=\left|\mathit{d\_dtfhkv\_uvz}\right|,$$
  

wobei d_dtlog_av bzw. d_dtfhkv_av der Gradient / die Ableitung und d_dtlog_uvz bzw. d_dtfhk_uvz einen Schwellenwert angebende Parameter sind.A heating system 9 is hydraulically adequately supplied if and only if with decreasing flow temperature θ _VL after termination of the control-related transition process the following applies:

• The building supply status GVZ is analogous to the characteristic radiator supply state VZ according to Fig. 6 .
  ie the condition applies: d_GVZ <- | d _ _ GVZ UVZ |,
  where d_GVZ is the gradient / derivative and d_GVZ_UVZ is a threshold indicating parameter.
• The mean over all active radiator 2 log heater overtemperature d_dt log_ av, or equivalent d_dtfhkv_av the difference between the radiator side and interior-air-side radiator temperature changes
  only insignificant, ie the conditions apply: $$\mathit{d\_dt}\mathrm{log\_}\mathit{av}<=\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{respectively}\mathrm{,}\mathit{d\_dtfhkv\_av}<=\left|\mathit{d\_dtfhkv\_uvz}\right|.$$
  

where d_dtlog_av and d_dtfhkv_av are the gradient / derivative and d_dtlog_uvz and d_dtfhk_uvz, respectively, are threshold indicating parameters.

• Es erfolgt keine signifikante Verringerung des Gebäudeversorgungszustandes GVZ,
  d.h. es gilt die Bedingung: d_GVZ >= -|d_GVZ_UVZ|,

wobei d_GVZ der Gradient / die Ableitung und d_GVZ_UVZ ein einen Schwellenwert angebender Parameter ist.

• Die über alle aktiven Heizkörper 2 mittlere logarithmische Heizkörperübertemperatur d_dtlog_av oder deren Äquivalent, die Differenz zwischen heizkörperseitigen und raumluftseitigen Heizkörpertemperatur d_dtfhkv_av, fällt signifikant, d.h. es gelten die Bedingungen: $$\mathit{d\_dt}\mathrm{log\_}\mathit{av}<-\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{bzw}\mathrm{.}\mathit{d\_dtfhkv\_av}<-\left|\mathit{d\_dtfhkv\_uvz}\right|,$$
  

wobei d_dtlog_av bzw. d_dtfhkv_av der Gradient / die Ableitung und d_dtlog_uvz bzw, d_dtfhk_uvz einen Schwellenwert angebende Parameter sind.A heating system 9 is then hydraulically undersupplied, if with decreasing flow temperature θ _VL after completion of the control-related transition process analogous to the characteristics according to Fig. 7 and 8th The following applies:

• There is no significant reduction in the building supply state GVZ,
  ie the condition applies: d _ GVZ > = - | d _ _ GVZ UVZ |,

where d_GVZ is the gradient / derivative and d_GVZ_UVZ is a threshold indicating parameter.

• The mean logarithmic radiator overtemperature d_dt_log_av or its equivalent, the difference between radiator-side and room-air-side radiator temperature d_dtfhkv_av , falls significantly over all active radiators 2, ie the conditions apply: $$\mathit{d\_dt}\mathrm{log\_}\mathit{av}<-\left|\mathit{d\_dt}\log \mathit{\_uvz}\right|\mathrm{respectively}\mathrm{,}\mathit{d\_dtfhkv\_av}<-\left|\mathit{d\_dtfhkv\_uvz}\right|.$$
  

where d_dtlog_av or d_dtfhkv_av are the gradient / derivative and d_dtlog_uvz or, d_dtfhk_uvz are parameters indicating a threshold.

The aforementioned conditions apply to a mass flow of radiators m> 0 at approximately constant Raumheizlast. With increasing flow temperature θ _VL apply the above conditions with inverse relations accordingly.

The determination and evaluation of the temporal tendencies of the parameters Δ, BLV, VZ, GVZ for determining the hydraulic state of the radiators 2 and / or the heating system 9 takes place cyclically, i. in certain periods. In order to increase the safety in the hydraulic supply detection, the time characteristics can be subjected to a time averaging.

Thus, for a building or heating system 9, the invention is cyclic, i. a type of hydraulic fingerprint in the form of a state table for all radiators 2 created in predetermined repetitions at intervals. In the state table there are 2 entries for each radiator which indicate the hydraulic state of the radiators 2: UVZ (= hydraulically undersupplied) or NVZ (= hydraulically adequately supplied). For the heating system 9, the individual state values can be compressed to a total value GUVZ (= total system hydraulically undersupplied) or GNVZ (= total system supplied hydraulically sufficient).

An embodiment of a device 11 according to the invention for the detection of the hydraulic state, ie the situation after a hydraulic adjustment, the heating element 2 in a heating system 9, the signal flow plan according to Fig. 9 be removed. The heating system 9 has an outside temperature lead th (T _A ) boiler 5 with a controller (control or control), which possibly also uses other reference variables such as the current building heat demand as input variables, as indicated by the unmarked arrow.

The boiler 5 provides the building heating system 9, a heating fluid or medium with the flow temperature T _VL (also referred to as θ _VL ) and the mass flow m available. In the heating system 9, each radiator 2 (numbered HK_1 to HK_N in the figure) corresponds to one of its hydraulic situation Heating fluid mass flow m ₁ to m _N and the flow temperature T _VL flows through. Every radiator handles a certain heat load Q _Last .

As is customary in the housing industry, a heating cost distributor 12 (numbered HKV_1 to HKV_N in the figure) is provided for heating cost detection, each of which measures radiator side temperatures T _HKS and room air side temperatures T _RLS (also referred to as θ _HKS and θ _RLS ) and from this a logarithmic overtemperature dT _log (also referred to as Δ _log ) characterizing the heat consumption or temperature difference of the heating cost allocator 12 dT _HKV (also referred to as Δ _HKV ) is determined.

The heat cost allocators 12 can basically be 2- or 3-sensor measuring devices which determine the various excess temperatures Δ which are defined as differential temperatures between radiator side and room air side temperatures in the ways explained in detail above. In principle, individual temperature sensors can also be used which deliver their measured values as raw data to the device 11 according to the invention. In this case, the correspondingly calculated arithmetic unit adopts the above-described calculations.

Preferably, the heat cost allocators 12 are radio heat cost allocators, which transmit their measured data and determined results, in particular the excess temperatures Δ, as radio telegrams. These are received by the hydraulic balance detection device 11. Of course, it is also possible for the data of the radio heat cost allocators to be collected in data collectors and transmitted to the device 11 by the data collectors. The device 11 can then for example be integrated into the data collector, for example. Further, preferably also by radio, one in the heating system 9 centrally measured flow temperature T _{VL of} the device 11 fed.

The radio communication can be uni- or bidirectional depending on the requirements. Of course, instead of the wireless communication, a wired or an optical communication are possible.

In the device 11, an arithmetic unit, not shown, is provided, in which then for each radiator 2, the method described above is implemented, which is described again in summary below.

The procedure includes 4 important steps:

First, cyclically, ie at certain time intervals, a calculation of the parameters logarithmic overtemperature Δ _log , Heizkörperbetriebsleistungsver ratio BLV, radiator supply state VZ and / or building supply state GVZ.

• der Gradient oder die erste Ableitung nach der Zeit oder nach der Vorlauftemperatur T_VL der Heizkörperversorgungszustände VZ
• der Gradient oder die erste Ableitung nach der Zeit oder nach der Vorlauftemperatur T_VL des Gebäudeversorgungszustandes GVZ
• der Gradient oder die erste Ableitung nach der Zeit oder nach der Vorlauftemperatur T_VL der Heizkörper-Betriebsteistungsverhältnisse BLV;
• der Gradient oder die erste Ableitung nach der Zeit oder nach der Vorlauftemperatur T_VL der logarithmischen Heizkörperubertemperaturen Δ_log;
• der Gradient oder die erste Ableitung nach der Zeit oder nach der Vorlauftemperatur T_VL der Differenz Δ_HKV zwischen heizkörperseitigen und raumluftseitigen Heizkörpertemperaturen.

Thereafter, the time characteristics for determining the hydraulic radiator / building supply condition are determined. This is especially one of the following sizes:

• the gradient or the first derivative after the time or after the flow temperature T _{VL of} the radiator supply states VZ
• the gradient or the first derivative according to the time or the flow temperature T _{VL of} the building supply state GVZ
• the gradient or the first derivative after the time or after the flow temperature T _{VL of} the radiator operating power ratios BLV;
• the gradient or the first derivative according to the time or the flow temperature T _{VL of} the logarithmic radiator sub-temperatures Δ _log ;
• the gradient or the first derivative after the time or after the flow temperature T _{VL of} the difference Δ _HKV between radiator side and room air side radiator temperatures.

Thereafter, the time characteristics for determining the hydraulic balancing are averaged over time and the mean values corresponding to the aforementioned criteria, which result from the in the Fig. 6 to 8 shown characteristics evaluated.

As a result, a hydraulic building fingerprint is in the form of a state table for all radiators 2 with the hydraulic states for each radiator 2: UVZ (= hydraulically undersupplied) or NVZ (= hydraulically adequately supplied) and the total value (overall hydraulic state) compressed for the heating system 9: GUVZ (= Total system hydraulically undersupplied) or GNVZ (= complete system hydraulically adequately supplied). This table is generated in the device 11 according to the invention. The table entries can be transmitted to a service center 13 for visualization.

The service center 13 can be a home or apartment center of a heating cost detection and / or room temperature control system, in which the device 11 according to the invention can also be integrated in a simple manner.

Fig. 10 FIG. 5 illustrates a second embodiment of a hydraulic balancing detection apparatus 14 according to the invention. The apparatus 14 is in the same Heating system 9 involved, the description can therefore be omitted.

The device 14 is integrated into a heat cost allocator 12 and performs in the manner already described, the detection of the hydraulic adjustment of a radiator 2, wherein the device 14 operates decentralized in this embodiment. Therefore, a corresponding device 14 is provided on each radiator 2. This can be achieved by implementing the device 14 in a microprocessor of the heat cost allocator 12 and carrying out the proposed method for the respective radiator 2. It is also possible to integrate the device 14 in a - usually already connected to the heat cost allocator 12 - room temperature control.

The states UVZ, NVZ the hydraulic supply of each radiator 2 notifies the device 14 to a service center 15, which in addition to the visualization and the determination of the overall hydraulic state GUVZ, GNVZ the heating system 9 takes over. Otherwise, the service centers 13 and 15 may be the same.

The field of application of the proposed method and the application possibilities for the devices 11, 14 set up for carrying out this method are therefore in particular hot water heating systems in which the power adjustment of the central heating supply by changing the flow temperature θ _VL or the mass flow m of the liquid heat carrier (heating medium) heating fluid) or . By combination of the change of flow temperature θ _VL and mass flow m takes place and in which the control of the room temperature by means of variation of the Heizkörpermassestromes m takes place and in which the detection and distribution of the amount of heat for space heating by means of electronic heat cost allocators according to the 2- or 3-feeler principle ,

• die Variation des Massestromes m mittels Heizkörperventilen erfolgt und/oder
• die Regelung der Raumtemperatur mit Thermostatventilen erfolgt und/oder
• die Regelung der Raumtemperatur mit elektronisch gesteuerten Ventilen erfolgt und/oder
• die Variation des Massestromes m mittels elektronisch gesteuerter Pumpen erfolgt und/oder
• die Regelung der Raumtemperatur mit elektronisch gesteuerten Pumpen erfolgt. Ferner sind an den Heizkörpern
• elektronische Heizkostenverteiler nach dem 2-Fühlerprinzip installiert, welche jeweils eine heizkörper- und eine raumluftseitige Temperatur erfassen oder
• elektronische Heizkostenverteiler nach dem 3-Fühlerprinzip oder andere geeignete Geräte installiert sind, welche
  • + die Heizmittelvorlauf-, die Heizmittelrücklauftemperatur und die Raumlufttemperatur oder
  • + die Heizmittelvorlauftemperatur und eine heizkörper- und eine raumluftseitige Temperatur oder
  • + die Heizmittelrücklauftemperatur und eine heizkörper- und eine raumluftseitige Temperatur oder
  • + die Heizkörperoberflächentemperatur und die Raumlufttemperatur
  erfassen.

Included are in particular heating systems, in which at the radiator feeders

• the variation of the mass flow m takes place by means of radiator valves and / or
• the regulation of the room temperature with thermostatic valves takes place and / or
• the control of the room temperature with electronically controlled valves takes place and / or
• the variation of the mass flow m takes place by means of electronically controlled pumps and / or
• the regulation of the room temperature is done with electronically controlled pumps. Further, on the radiators
• electronic heat cost allocators installed according to the 2-sensor principle, which each detect a radiator side and a room air side temperature or
• electronic heat cost allocators are installed according to the 3-sensor principle or other suitable equipment, which
  • + the heating medium flow, the heating medium return temperature and the room air temperature or
  • + the heating medium flow temperature and a radiator and a room air side temperature or
  • + the heating medium return temperature and a radiator and a room air side temperature or
  • + the radiator surface temperature and the room air temperature
  to capture.

The advantages of the invention lie in the retrofittability of existing heating systems that have been equipped with electronic and communication heat exchangers and already transferred the required temperatures. Electronic radio heat cost allocators are the most suitable measuring device, they are state of the art today and therefore very cost-effective.

The standard functions of conventional heat cost allocators are sufficient for carrying out the method according to the invention. Therefore, no installation of the apartments is required for installation of the proposed system, which are already equipped with appropriate heat cost allocators. All that is required is a software update, for example, of the data collector into which the device for detecting the hydraulic state can be easily integrated. These data collectors are often located outside the home, for example, in the hallway. Furthermore, uni- and bidirectional radio heat cost allocators can be used. The invention can also be combined with electronic individual room temperature control systems.

As a result, the invention provides a continuously updated hydraulic building fingerprint. This can be handed over to building owners on a regular basis to motivate them to take action to improve hydraulic balancing. In addition, the invention offers the possibility to check the success of measures to improve the hydraulic balancing, even in Femmonitoring without building access.

LIST OF REFERENCE NUMBERS

1 (a-f)

radiator valve

2 (a-f)

radiator

3 (a-f)

throttle valve

4

heat circulating pump

5

boiler

6

Heating strand lead

7

Heating strand return

8th

Strand regulating device, strand regulating valve

9

heating system

10

apartment

11

Device for detecting hydraulic balancing

12

Heat cost allocators

13

service center

14

Device for detecting hydraulic balancing

15

service center

Claims (16)

Method for detecting the hydraulic state of a heating system (9) with radiators (2) connected via a fluid flow system (6, 7) through which a heating medium flows with a flow temperature (θ _VL ), characterized in that the flow temperature (θ _VL ) and for each radiator (2) a group derived from a difference between a heater side and interior-air-side temperature overtemperature (Δ) measured at different points in time and indicating from a heat demand of the heating body (2) parameter (Δ _log, BLV, VZ, GBLV, LVN) determined is and that the change in the parameter (Δ _log , BLV, VZ, GBLV, GVZ) over time or the flow temperature (θ _VL ) and the temporal change of the flow temperature (θ _VL ) are evaluated. A method according to claim 1, characterized in that as a parameter, the logarithmic radiator overtemperature (Δ _log ), the difference (Δ _HKV ) between radiator side and room air side radiator temperatures or the difference (Δ (θ _HK -θ _air )) between the radiator surface temperature (θ _HK ) and the room air temperature (θ _air ) is used. A method according to claim 1 or 2, characterized in that as a characteristic of the current radiator output and the radiator power at rated mass flow and current flow temperature certain radiator operating power ratio (BLV) is used. Method according to one of the preceding claims, characterized in that a parameter indicating the current heat demand of a radiator Heizköperversorgungszustand (VZ) is used. A method according to claim 3 or 4, characterized in that as a parameter a heating circuit or building operating power ratio (GBLV) or a heating circuit or building supply state (GVZ) is used. Method according to one of the preceding claims, characterized in that the change of the parameters (Δ _{log '} BLV, VZ, GBLV, GVZ) is generated by gradient formation or ratios of the differences. Method according to one of the preceding claims, characterized in that the changes in the parameters (Δ _log , BLV, VZ, GBLV, GVZ) are averaged over time. Method according to one of the preceding claims, characterized in that the change in the parameters (Δ _log , BLV, VZ, GBLV, GVZ) over time or the flow temperature (θ _VL ) are compared with specified characteristic values in order to ensure a hydraulically adequately supplied state ( NVZ, GNVZ) from a hydraulically undersupplied condition (UVZ, GUVZ). Method according to one of the preceding claims, characterized in that a state table with the states of the hydraulic supply (NVZ, UVZ) of the individual radiator (2) and / or the hydraulic supply (GNVZ, GUVZ) of the entire heating system (9) is applied. Device for detecting the hydraulic state of a heating system (9) with radiators (2) connected via a fluid flow system (6), through which a heating medium flows with a flow temperature (θ _VL ), with at least one connection for inputting the flow temperature (θ _VL ), at least one connection for inputting a radiator-side temperature (θ _HKS ) and at least one connection for inputting a room-air-side temperature (θ _RLS ) and a computing unit, characterized in that the arithmetic unit is adapted to determine from the entered temperature values a heat demand of the radiator (2 ) indicative of the characteristic variable (Δ _log, BLV, VZ, GBLV to determine LVN) and the change in the characteristic variable (Δ _log, BLV, VZ, GBLV, LVN) over time or over the flow temperature (θ _VL) and the time variation of the Flow temperature (θ _VL ) evaluate. Apparatus according to claim 10, characterized in that a plurality of terminals for the input of temperatures as a connection to a heat cost allocator (12) are formed. Apparatus according to claim 11, characterized in that the device (11, 14) has connections for a plurality of heat cost allocators (12). Apparatus according to claim 10, characterized in that the device (11, 14) in a heating cost distributor (12) is intergiert. Device according to one of claims 10 to 13, characterized in that the device (11, 14) has a connection for the output of determined hydraulic states (NVZ, UVZ, GNVZ, GUVZ). Apparatus according to claim 14, characterized in that a service center (13, 15) for displaying the hydraulic states (NVZ, UVZ, GNVZ, GUVZ) is provided. Device according to one of claims 10 to 15, characterized in that some or all connections are designed as radio communication connections.

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