DK1936290T3 - A method and device for detecting the hydraulic state for a heating installation - Google Patents

Description

The present invention relates to a method and system for detecting the hydraulic state of a heating system with heaters connected via a fluid flow system which are flowed through a heating medium at a flow temperature. In such pump hot water heating systems, a hydraulic sub-supply of individual heaters frequently occurs, with simultaneous over-supply of other heaters. Hydraulic under-supply of a heater means that despite sufficient supply temperature, the heater mass flow required for the desired room temperature cannot be achieved even with fully opened heater valve. Reasons for this are typical: • too little differential pressure across the heater valve due to hydraulically unfavorable location of the heater (eg reference numeral 2f in Fig. 1), • too little differential pressure across the heating string due to incorrect adjustment of the string control valve (reference number 8 in Fig. 1), • incorrect presetting of the heater valve (e.g., reference numeral 1f in Fig. 1) for the under-supplied heater (KVS value too small); • incorrect presetting of the heater valves (e.g., reference numbers 1a to 1 in Fig. 1) for other heaters (KVS value there too large), • throttle of the heater mass flow due to insufficiently sized or not properly adjusted throttle valves (reference numbers 3a-3f in Fig. 1), for example in the heater return and / or • too low pump pressure for the heat circulation pump (reference number 4 in Fig. 1).

In order to solve the problem described, a hydraulic equalization must be carried out which includes the correct adjustment of the string control, heater and throttle valves as well as the circulation pump. The purpose of the hydraulic equalization is to adjust the hydraulic resistors in the heating system so that, for the purpose of achieving desirable room temperatures, the differential pressure, respectively, is required. Mass flow is ensured for all heaters. Thus, for example, the string differential pressure at the string control valve is set to values typically in the range of 150-250 mbar. In addition, the hydraulic resistance is increased for hydraulically favorably located heaters, for the benefit of disadvantaged heaters. This is done by reducing the KVS value of the preset heater valve. Thereby, the valve authority a, in accordance with VDI 2073 defined as

with Δρτν, · \ οο% ... pressure drop over fully opened heater valve; Δρ τν, ζυ ... pressure drop over closed heater valve.

The relationship between valve authority, opening position and flow, respectively. heat release for the heater is shown, for example, in FIG. 2 and FIG. 3. For optimum room temperature control, values above 0.3 are sought for the valve authority.

In practice, however, the implementation of the hydraulic equalizer is a cumbersome and lengthy process. Consequently, for reasons of time and cost, it is frequently not implemented or only inaccurate. The main problem in this regard is the knowledge of the hydraulic state of the entire heating system, respectively. the individual heaters in the heater. Consequently, many heaters - not just those far from the beginning of the string - are hydraulically under-supplied. The resulting complaints from residents about the lack of heat supply are countered in the predominant number of cases, due to the unknown cause, often simply by a drastic increase in the heat curve (ie the flow temperature) or by increasing the pump pressure (ie the mass flow). This leads to unnecessarily increased heat losses in the distribution and transmission, but also to increased electricity costs for the heat circulation pump. DE 100 03 394 A1 describes a method for carrying out the hydraulic equalization for a heating system. This method relies on a measurement and regulation of the differential pressure at the heaters. The adjustment is done via a return valve and is carried out manually. With regard to the detection of the under-supplied heaters, this method has the disadvantage that the measurement of differential pressure is required at each heater. This causes high costs.

From WO 2004/083733 A1 there is known a method for adjusting several parallel heat exchangers, in which, for each heat exchanger, the heat demand for the heat exchanger specific size is detected for a predetermined period of time, the specific sizes of all heat exchangers are compared with each other and a setting of the heat exchanger having a size indicating the minimum heat demand is changed in the direction of increasing the heat demand. The heat exchanger with the greatest consumption of heat carrier media is, so to speak, penalized as the flow rate of heat carrier media decreases.

From EP 0 189 614 A1 there is known a device for adjusting a heating installation, in which each heating element is provided with a pre-adjustable valve in the flow of the heating medium. In this way, the flow through the individual radiators can be adjusted so that the hydraulic equalization of the various heaters is balanced.

DE 42 21 725 A1 discloses a method for automatically obtaining a hydraulic equalizer, in which the heater thermostat valves are first fully opened and the temperature set in each room is measured. In the rooms with too high a resultant temperature, the thermostat valves are closed so much that the desired temperature is set. The opening degree thus provided for the thermostat valve is used as the maximum opening for all subsequent control activities. The method serves to detect hydraulically-supplied heaters, but has the disadvantage that the thermostatic valves for all heaters must be operated and, consequently, access to the housing. In addition, the stationary state of the plant must be awaited at any time before evaluation can take place. This is especially a disadvantage due to the manual access. Further, in carrying out the method, error judgments can be made, as too high a temperature can adjust due to improperly sized heaters. By this method, this would be wrongly returned to the hydraulic equalizer.

A further method is known from DE 102 43 076 A1. This method uses adjustment drives with integrated temperature differential control, which, for the purpose of adjustment, are mounted on a pre-adjustable heater valve adapter. The volume flow through the heater is varied by means of the preset adapter until a predetermined difference between flow and return temperature is obtained. After the adjustment process is complete, the adjustment drive is again removed and replaced by the thermostat head. The disadvantage of the method is that adjustment drives with integrated temperature difference control with additional preset adapters are required, which must further be mechanically compatible with the adjustment drive. This is a very costly device technology.

Finally, DE 195 06 628 A1 describes a method for hydraulically equalizing a heating system with a control apparatus which, in a commissioning program, opens all valves at the flow distributor completely. After a certain period of operation, temperature changes are first set at the room temperature sensors that are hydraulically best equipped. Then the associated valves are closed somewhat. At the end of the first operating program phase, the valves are assigned maximum opening degrees, which in the first approximation take into account the hydraulic system, in accordance with the previous regulation conditions. This process is then repeated several times, even during the ongoing operation, in order to achieve a system equalization. In this connection, there is a problem that a temperature rise in one room must not only be causally related to the opening of the valve, but can also be caused by foreign influences, for example solar radiation. Furthermore, a randomly executed window vent during the equalization program can massively falsify the results of the equalization.

In order to remedy this, it is the object of the invention, first to provide reliable knowledge of the hydraulic state of the heating system and preferably the hydraulically poorly supplied heaters, in order to be able to initiate the correct measures without the automatic detection of the hydraulic conditions was necessary to access the housing or the building.

This is achieved by the measures according to claims 1 and 8 by a method and a device arranged for carrying out this method. In order to carry out the method proposed according to the invention, it is particularly required that the flow temperature and for each heater one derived from a difference between a heater side and room air side temperature is measured at different times and at least one characteristic size is detected which indicates the heating demand of the heater, at different times, and that the change of characteristic size over time or over the flow temperature and the temporal change of the flow temperature are evaluated.

It could be experimentally confirmed that the characteristic size, which indicates the heating demand of a heater during continuous operation, shows by a hydraulic sub-supply a characteristic which can be safely distinguished from a hydraulically well-supplied state. Thus, in accordance with the invention, measurements for detecting the hydraulic state of the heating system can be cyclically, i.e. with predetermined temporal distances repeating, is carried out and the trend of the detected characteristic sizes is continuously detected over time respectively. flow temperature. Hereby, for example, temporary influences (such as simultaneously opening or closing several valves or oscillating space loads) can induce changes in the hydraulic state (instead of the hydraulic state, the term 'equalization' is often used quickly and reliably to detect). , on the basis of this recognition, to take countermeasures, such as the automatic implementation of a new hydraulic equalizer by changing the flow conditions in the heating system.

In the method proposed according to the invention, the characteristic of the logarithmic heater temperature, the difference measured between a heater side and room air heater temperatures or the difference between the heater surface temperature and room air temperature can be used as characteristic size. These excess temperatures, all of which are distinguished by a difference between heater side and room air side temperatures, is a measure of how much heat is emitted from the heater to the surroundings.

As a characteristic size, based on the actual heater performance and the heater output at nominal mass flow and current flow temperature, the heater operating performance ratio can be determined, which can be determined particularly simply from the current logarithmic overtemperature and the logarithmic overtemperature at the norm point. As explained in further detail later, it has been found that the operating performance ratio provides a particularly significant opportunity for evaluating the hydraulic situation of a heating system.

The same is true of another embodiment of the method in which, as a characteristic size, a heater supply condition is used which indicates the actual heating demand of a heater, such as, as shown in FIG. 4, by means of a characteristic curve can be derived from the operating performance ratio. The characteristic curve indicates a relationship between the operating performance ratio and a heater supply state in a heat fitting control, in which a control placed in front of the actual heat control is pre-regulated to a desired value for a heater supply condition, respectively. an operating performance relationship. This is, for example, basically described in WO 03/052536 A and in DE 10 2007 029 631 A. Alternatively, the heater supply condition and the heater performance ratio could also appear from the characteristic curves in accordance with FIG. 5 depending on the logarithmic overtemperature.

Further, using preferably weighted average value generation or using a Fuzzy logic, from the heater operating performance conditions (BLV) or heater supply conditions (VZ), it is possible to provide a heating circuit or building operating performance (GBLV) or a heating circuit or heat circuit building supply mode (GVZ) and use this as a characteristic size.

According to the invention, it may also be advantageous to detect and evaluate several of the characteristic sizes described above in parallel. Thus, for example, the logarithmic overtemperature and operating performance ratio or heater supply condition can both be evaluated in their temporal tendencies, in order to enable a more reliable statement of the hydraulic state of the preheater.

In a preferred embodiment of the method, the change of characteristic size can be provided by gradient formation or ratio of the differences, the latter being in practice the simpler path, since the target values can be subtracted from each other in a single calculation operation at any one time, e.g. simple microprocessors. Frequently, the analytical formulas for the derivation are not known, respectively. is a numerical gradient formation for cumbersome.

In order not to over-weight random fluctuations in measurement and characteristic sizes, and not to quickly withdraw the hydraulic state of the plant, changes in the characteristic sizes can be temporal, for example sliding, midies.

A particularly simple criterion for the trend evaluation for the characteristic size is to compare the change of the characteristic size over time or the flow temperature with determined characteristics, respectively. limit values, in order to distinguish between a hydraulically adequately supplied condition and a hydraulically supplied condition. Such characteristics, respectively. limit values may well be determined, as will be shown later.

In order to obtain the results of the detection of the hydraulic state of the system in a clear form, a state table can be set up with the states of the hydraulic supply of the respective heaters and / or the hydraulic supply of the total heating system. This can be displayed in an information unit, a service center for the heat cost detection system and / or a heat performance adjustment control. In this connection, the service center, based on the conditions for the hydraulic supply of the respective heaters, can also derive the conditions for the hydraulic supply of the total heating system by means of calculation instructions.

The invention further relates to a device for detecting the hydraulic state of a heating system with heaters connected via a fluid flow system flowing through a heating medium at a flow temperature in accordance with the measures specified in claim 10. The device is provided with at least one connection for introducing the flow temperature, at least one connection for introducing a heater side temperature and at least one connection for administering a room air side temperature and a calculator adapted to, based on the entered temperature values, to provide at least one characteristic size indicating the heat demand of the heater and to evaluate the change of characteristic size over time or above the flow temperature and the temporal change of the flow temperature. In particular, the calculator is adapted to carry out the described method in accordance with the invention. In accordance with a particularly preferred embodiment, several connections for introducing temperatures are provided in the device as a common connection to a heat cost distributor, whereby they or a portion of the required temperature values can be detected. In this case, it is also possible that, instead of the respective temperature values, the heat cost distributor already transmits an over-temperature or an otherwise processed characteristic or intermediate size. This embodiment of the invention enables the frictionless introduction of the proposed device into existing heat-cost distributor systems without having to adapt these systems in particular.

Further, the device may have connections for several heat cost distributors. Then, with the proposed device, the method of detecting the hydraulic equalizer can be carried out in a central device, which, for example, merely has a connection for a centrally measured flow temperature. Of course, it is also possible, in such a central device, to provide several connections for flow temperatures measured in the feed to a heater. In an alternative embodiment, the device may be integrated into one, particularly on a heater, heat cost distributor. Thus, the hydraulic equalization can be determined decentrally and can for example be combined in a service center. Of course, it is also possible in the case of a central device to collect state data for the hydraulic equalization in a service center, which may be designed separately in relation to the device or be designed integral therewith. The service center can serve to visualize the respective state data.

In order to be able to deliver and, where appropriate, visualize the detected hydraulic states of the individual heaters or the entire heater, the device may have a connection for delivering detected hydraulic states for a single heater or the entire system.

Furthermore, when the proposed device is not limited thereto, it is particularly advantageous to design individual or all connections as radio communication connections. Then, the proposed system for detecting the hydraulic state can be particularly easily integrated into radio systems for heat cost distribution, since the radio telegrams transmitted by radio heat cost distributors or corresponding suitable temperature sensors can be easily detected by the device according to the invention.

Further advantages and uses of the present invention will become apparent from the following description of embodiments and the drawings. In the drawing: FIG. 1 shows schematically the construction of a heating system designed as a hot water heating system with heaters connected via a fluid flow system; FIG. 2 theoretical characteristic curves for the dependence between the relative volume flow and the relative valve opening at different valve authorities; FIG. 3 theoretical characteristic curves for the dependence between the relative heater output and the relative valve opening at different valve authorities; FIG. 4 shows a theoretical characteristic curve with the dependence between operating performance conditions and heat supply condition; FIG. 5 theoretical characteristic curves for the dependence between the heating surface supply state and the the heater performance ratio and the logarithmic overtemperature; FIG. 6 characteristic curves of the characteristic sizes of heater supply condition, heater performance ratio and heater over temperature used for the hydraulic state of a heating system in accordance with the invention in dependence on the supply temperature at a hydraulically sufficient supply for constant room heat load; FIG. 7 characteristic curves of the characteristic sizes of heater supply condition, heater performance ratio and heater super temperature used for the detection of the hydraulic state of a heating system in accordance with the invention in dependence on the supply temperature of a hydraulic sub-supply for constant room heat load; FIG. 8 characteristic curves of the characteristic sizes of heater supply condition, heater performance ratio and heater temperature used for detecting the hydraulic equalization of a heating system in accordance with the invention in dependence on the supply temperature at a hydraulic sub-supply at a higher supply temperature at a sufficient temperature of 60 ° C and rumvarmebelastning; FIG. 9 is a signal flow diagram of a system according to the invention for central detection of hydraulically supplied heaters; and FIG. 10 is a signal flow diagram of a system according to the invention for decentralized detection of hydraulically supplied heaters. 1 FIG. 1 is a schematic representation of a heating system 9 with a boiler 5 to which is connected via a heat circulation pump 4 a heat string inlet 6 for distributing a heating medium and a heating medium respectively. fluid, which is returned via a heat string return 7, after flowing the heat fluid through the heaters 2a to 2f. In a special valve-regulating device 8, the differential pressure between the heat-flow inlet 6 and the heat-in-flow return 7 can be set centrally.

The heat-string inlet 6 and the heat-inlet return 7, which form the fluid flow system, provide several different housing units 10 with the heat fluid flowing through two heaters 2a, 2b, respectively; 2c, 2d; 2e, 2f. At the inlet of each heater 2 there is a heater valve 1 (i.e., 1a, 1b; 1c, 1d; 1e, 1f) which adjusts the flow of heat fluid in accordance with the desired heat output for the respective heater 2. At a desired high heat output For example, a heater valve 1 can be opened at maximum.

Depending on the installation situation of a heater 2 in particular, the hydraulic flow conditions are different, so that even at a maximum open heater valve 1, it does not flow together mass flow through any heater 2. However, this is not desirable since the heaters 2 in the hydraulic system are so disadvantaged. cannot achieve the required heat output. Accordingly, the maximum flow rate through hydraulically preferred heaters 2 is limited by thermostat valves 1 (i.e., 1a, 1b; 1c, 1d; 1e, 1f) provided with each heater flow and / or at each heater return flow provided by each heater flow 3 (i.e., 3a, 3b; 3c, 3d; 3e, 3f), for the benefit of the hydraulically disadvantaged heaters 2. This leads to a higher differential pressure at the hydraulically disadvantaged heaters 2 and at an optimum setting that at all heaters 2 can be delivered to the desired heat output.

This method is part of a hydraulic equalization. To this end, it is necessary to know in advance that the entire system is in a hydraulically poorly offset state, and which heaters 2 are hydraulically adequately supplied or not, respectively. hydraulically supplied.

In addition, the method for automatically detecting hydraulically-supplied heaters is described in detail below.

When evaluating the temporal processes for heat flow temperature θνι_ and the characteristic sizes "" heater operating condition (BLV) "or" "heater supply state (GVZ)" or "" building supply state (GVZ) "or" "heating circuit or building operating mode (VV), operation of the system particularly well, the hydraulic state of the individual heaters 2 (BLV, VZ) and the like are detected. the total heating system 10 (GVZ). Alternatively, for each heater, 2 temporal cycles of heat flow temperature θνι_ and the logarithmic heater upper temperature A10 and or heater side and room air side temperature are obtained from the electronic heat cost distributor Ohks, Orls or heat or room air temperature and ambient air temperatures.

The input measurement sizes of the method and the necessary measuring equipment are consequently heat-free running temperature θνι_, the measurement of which can, for example, be done by means of system or dive sensors either centrally in the building connection / on the heating circuit building input or in its own form decentrally on the heater flow-through air connection and heating element connection , Orls from the electronic heat cost distributor, the measurement of which can be decentralized using electronic heat cost distributors, especially radio heat cost distributors, or heater surface temperatures Ohk and room air temperatures θΐυη, the measurement of which can be decentralized using room temperature regulators or other means.

From the heater side and room air side temperatures Ohks, Orls respectively. the heater surface temperatures Ohk and the room air temperatures θΐυη can, as described below, be calculated at any time an overtemperature. In accordance with the different embodiments of heat cost distributors, various options for calculating the heater furnace temperature Δ are provided. In a first variant, a logarithmic heater temperature Δι09 for heat-cost distributors in accordance with the 2-sensor principle can be calculated as follows:

with

water side correction factor

rumluftsidekorrektionsfaktor

temperature difference from heat cost benefits

heater side temperature from heat cost distributor

room air side temperaturefrom heat cost benefits.

Heater-specific correction factors Kcw and Kcl are calculated from the corresponding heater-specific C values known for each heater in the usual practice of heat cost detection per se. In the current practice for the distribution of heat costs, C-values or C-values are obtained. correction factors used fixed values.

Alternatively, the calculation of the logarithmic heater upper temperature A and for heat cost distributors in accordance with the 2-sensor principle in another variant can also be done as follows:

where

is the overflow temperature of the heater and

is the return air temperature of the heater. In addition, the following approximations apply:

flow temperature for the heating circuit

flow temperature for the heating circuit (is centrally measured and transmitted).

The return air temperature A-Qrl is calculated from the theoretical heating equation

with

temperature difference from heat cost distributor at mounting height h (h = 1 corresponds to the flow, h = 0 corresponds to the return flow)

correction factor

heater side temperature from heat cost distributor

room air side temperature from heat cost distributor

flow temperature for the heating circuit

flow over temperature for the heating circuit (is centrally measured and transmitted).

Similarly, the calculation of the logarithmic heater temperature A10 and for heat cost distributors in accordance with the 3-sensor principle in a first variant can be done:

where

... the inlet temperature of the heater;

... is the return temperature of the heater;

... is the ambient temperature of the heater. Instead of heat cost distributors, a measuring device can be used that detects the following temperatures:

... flow temperature of the heater;

... return temperature for the heater;

... ambient temperature of the heater.

In another variant of the 3-sensor principle, the heater furnace temperature Δι09 can be calculated as follows:

where

... the overflow temperature is the preheater body

... is the inlet temperature of the heater

... is the room air temperature at the heater (substitute measurement in the room)

... is the return air temperature of the heater. Alternatively, Δθνι_ can be determined instead

... over-flow temperature for the heating circuit

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

The return air temperature A r rl is obtained from the theoretical heating equation

as

with:

... temperature difference at the heater at height h (h = 1 corresponds to the flow, h = 0 corresponds to the return flow) K'corr ... correction factor

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

... room air temperature at the heater (replacement room measurement). The measurement of dvL and / or j9hp (/?) And / or diuft can be done by any measurement technique.

Further, a logarithmic heater upper temperature Δι09, ιοο at nominal mass flow (at standard mass flow or sizing mass flow) is calculated as follows:

where:

... is the supply air temperature for the heater

... is the supply temperature for the heater

... is the ambient air temperature for the heater

... is the supply air temperature for the heating circuit

... is the overflow temperature of the heating circuit (the overflow temperature of the heating circuit AOvL.Heizkreis can thus be detected centrally at the boiler or at the building entrance of the heating system)

... is the return excess temperature of the heater at nominal or sizing mass flow and current flow excess temperature.

The return flow over temperature at normalized or sizing mass flow is calculated as

defined by: n: heater exponent (from manufacturer's appendix)

flow over temperature for heating circuits

fixed parameter for dimension point AP

heater return circuit sizing over temp.

heater-flow-sizing of temperature.

The dimensioning point applies: XP = AP. Design parameters for the heating system

is typically known from the planning documents. Alternatively, the heater parameters for the norm point (xP = AP) (flow / return / air temperature = 90/70/20 ° C) can also be used in accordance with DIN EN 442:

fixed parameter for norm point NP;

heater return flow over temperature for norm point;

heater flow over temperature for norm point.

With this information, the heat transfer performance ratio BLV_HK can be calculated according to the following approximation:

with

... logarithmic overtemperature in heater norm point, for example in heater norm point (90,70,20): iog, 6o = 59.44K; n ... heater exponent (for each heater known);

... current logarithmic overtemperature.

Thus, the heater operating performance ratio BLV is simply obtained from the ratio of heater furnace temperatures Δ.

The characteristic size "heater supply condition (VZ)" can be provided from the above calculated heater operating ratio BLV according to FIG. 4. Further, the characteristic sizes of heater supply condition VZ and heater operating performance ratio BLV, knowing the logarithmic heater upper temperature A10 and can also be extracted from the characteristic curves according to FIG. 5. The characteristic sizes' 'building supply state (GVZ)' 'or' 'building operating ratio (GBLV)' are provided by Fuzzy logic or weighted mean formation from the individual heater supply modes. A specific example of this is described in WO 03/052536 A.

For the various above-mentioned characteristic sizes, the temporal change is provided as follows: • the gradient or the first derivative either with respect to time t or with respect to the flow temperature θνι_ of the heat performance performance ratio BLV:

• the gradient or the first derivative either with respect to time t or with respect to the flow temperature θνι_ of the heater supply state VZ:

• the gradient or the first derivative either with respect to time t or with respect to the flow temperature θνι_ of the building supply state GVZ:

• the gradient or the first derivative either with respect to time t or with respect to the flow temperature Ov1 for the logarithmic heater over-temperature A10 and:

• the gradient or the first derivative either with respect to time t or with respect to the flow temperature θνι_ for the difference between heater side and air space side heater temperature Ovks, Orls:

• the gradient or the first derivative either with respect to time t or with respect to the flow temperature θνι_ for the difference between heater surface and room air temperature Ohk, dm-

As shown in FIG. 6 and 8, the condition of a hydraulically adequately heated heater 2 can be assumed when the individual characteristic sizes, in their temporal tendency, with decreasing flow temperature θνι_ of this heater 2 and after completion of the regulated conditional transition process, fulfill the following conditions: • Heating supply condition falls, ie that applies to the condition

where d_VZ is the gradient / derivative and d_VZ_UVZ is a parameter that specifies a threshold value. • The heater operating performance ratio BLV increases, ie. that applies to the condition

where d_BLV is the gradient / derivative and d_BLV_UVZ is a parameter that specifies a threshold value. • The logarithmic heater upper temperature ΔιΟ0 or its equivalent, the difference between heater side room and room air side heater temperature, only changes substantially, ie. the following conditions apply:

where d_dtlog respectively. d_dtfhkv is the gradient / derivative and d_dtlog_uvz respectively. d_dtfhk_uvz is a parameter that specifies a threshold value.

The above conditions apply to a heater mass flow m> 0 at approximately constant room heat load. The heater body mass flow m = 0, ie. the heater 2 is completely immersed when the heater valve 1 is closed, the logarithmic heater upper temperature Δι09 or its equivalent, the difference between heater side and room air side heater temperature, approximately 0 and a hydraulic evaluation is not possible. This case may be ruled out by an appropriate inquiry during the practice.

With increasing flow temperature θνι_, the above conditions with inverse relations apply similarly. When a heater 2 is hydraulically supplied, for the respective characteristic sizes in their temporal tendency with decreasing flow temperature θνι_ for this heater 2, and after completion of the control-conditioned conditional process, the following conditions as shown in FIG. 7 and 8: • there is no significant deterioration of the heater supply state VZ, • ie. the condition applies:

• where d_VZ is the gradient / derivative and d_VZ_UVZ is a parameter that specifies a threshold value. • There is no significant increase in the heater operating ratio BLV, ie. the condition applies:

• where d_BLV is the gradient / derivative and d_BLV_UVZ is a parameter that specifies a threshold value. • The logarithmic heater upper temperature A10 and its equivalent, the difference between heater side and room air side heater temperature, decreases, ie. the following conditions apply:

• where d_dtlog respectively. d_dtfhkv is the gradient / derivative and d_dtlog_uvz respectively. d_dtfhk_uvz are parameters that specify a threshold.

The above conditions apply to a heater mass flow m> 0 at approximately constant room heat load. The heater body mass flow m = 0, ie. the heater 2 is completely lowered by closing the heater valve 1, then the logarithmic heater upper temperature Δι09 or its equivalent, the difference between heater side and room air side heater temperature, approximately 0 and a hydraulic evaluation is not possible. This case can be ruled out by an appropriate query during the practice.

When evaluating the GVZ building supply condition as characteristic size, whose temporal tendency is evaluated, an opinion on the hydraulic equalization of the overall heating system 9 may be made, regardless of the hydraulic supply of individual heaters 9.

A heating system 9 is precisely hydraulically equipped when, with decreasing flow temperatureOvL, after the completion of the control-conditioned conditional transition process, the following applies: • The building supply state GVZ decreases corresponding to the characteristic curve heater supply state VZ in accordance with fig. 6, i.e. the condition applies:

where d_GVZ is the gradient / derivative and d_GVZ_UVZ is a parameter that specifies a threshold value. • The median logarithmic heater over temperature d_dtlog_av or its equivalent, over all active heaters 2, the difference between heater side and room air side heater tempature d_dtfhkv_av, only changes substantially, ie. the conditions apply:

where d_dtlog_av respectively. d_dtfhkv_av is the gradient / derivative and d_dtlog_uvz respectively. d_dtfhk_uvz are parameters that specify a threshold.

The heating system 9 is precisely hydraulically under-supplied when, with decreasing flow temperature θνι_, following the control-technically conditioned transition process, corresponding to the characteristic curve according to FIG. 7 and 8, the following applies: • There is no significant reduction in the GVZ building supply condition, ie. the condition applies:

where d_GVZ is the gradient / derivative and d_GVZ_UVZ is a parameter that specifies a threshold value. • The median logarithmic heater upper temperature d_dt \ and_ or its equivalent, over all active heaters 2, the difference between heater side and room air side heater temperature d_dtfhkv_av, decreases significantly, ie. the following conditions apply:

where d_dtlog_av respectively. d_dtfhkv_av is the gradient / derivative and d_dtlog_uvz respectively. d_dtfhk_uvz are parameters that specify a threshold.

The above conditions apply to a heater mass flow m> 0 at approximately constant room heat load. With increasing flow temperature θνι_, the above conditions with inverse relations apply similarly.

The provision and evaluation of the temporal trends of the characteristic magnitudes Δ, BLV, VZ, GVZ for detecting the hydraulic state of the preheater body 2 and / or the heating system 9 takes place cyclically, ie. at specific time intervals. In order to increase the safety of hydraulic supply detection, the temporal characteristic magnitudes can be subjected to a temporal mean formation. Thus, for a building or heating system 9, by means of the present invention, it becomes cyclic, i.e. with predetermined time distances repeated method of providing a kind of hydraulic fingerprint in the form of a state table for all heaters 2.1 The state table contains for each heater 2 entries indicating the hydraulic state of the heater 2: UVZ (= hydraulically supplied) or NVZ (= hydraulically sufficient provided). For the heating system 9, the individual condition values can be compressed to a total value GUVZ (= total system hydraulically supplied) or GNVZ (= total system hydraulically sufficiently supplied).

An embodiment of a device 11 according to the invention for detecting the hydraulic state, i.e. the situation after a hydraulic equalization, for the heaters 2 in a heating system 9 can be seen in the signal flow diagram in fig. 9. The heating system 9 has an exterior temperature-controlled (Ta) heating boiler 5 with a regulator (regulation or control), which, if applicable, also uses additional control sizes such as current building heat requirements as input values, as indicated by the unprinted arrow.

The heating boiler 5 provides a heating fluid respectively. medium, with flow temperature Tvl (also referred to as Ovl) and the mass flow m, available to the building heating system 9.1 the heating system 9, each heating element 2 (in the figure numbered as HK_1 to HK_N) is flowed by a heat fluid mass flow corresponding to its hydraulic situation. to γτιν and the flow temperature Tvl. In this connection, each heater handles a specific heat load GW.

As is customary in real estate companies, for heating cost detection, a heating cost distributor 12 (in the figures numbered as HKV_1 to HKV_N) is provided on each heater 2, each measuring heater side temperatures Thks and room air side temperatures Trls (also designated such as Ohks and Orls), and from there, a heat consumption characterizes logarithmic overtemperature dTiog (also referred to as Aiog) or temperature difference for the heat cost distributor 12 dTm <v (also referred to as Ahkv). In connection with the heat cost distributors 12, these may basically be two or three sensor measuring devices which, in the above-explained ways, determine the various overtemperatures Δ, which are defined as differential temperatures between heater side and room air side temperatures. Basically, individual temperature sensors can also be used which supply their measurement values as raw data to device 11 in accordance with the invention. In this case, the correspondingly arranged calculator takes over the calculations described above.

Preferably, in connection with heat cost distributors 12, these are radio heat cost distributors which transmit their measurement data and obtained results, in particular the overtemperatures Δ, as radio telegrams. These are received by the hydraulic equalizing device 11. Of course, it is also possible that the data from the radio cost distributors are collected in data collectors and transmitted to device 11 via the data collector. In simpler terms, the device 11 may then, for example, be integrated into the data collector. Further, preferably also via radio, a device 11, measured centrally in the heating system 9, is supplied to the device 11.

According to the requirements, the radio communication can be one-way or two-way. Of course, instead of radio communication, a wired or optical communication is also possible. In the device 11 a calculation equipment not shown is provided, in which, for each heater 2, the method described above is implemented, which is described in more detail below in the following.

The process comprises 4 important steps: First, cyclical, ie. with certain temporal distances, a calculation of the characteristic magnitudes logarithmic overtemperature Åiog, heater operating performance ratio BLV, heater supply mode VZ and / or building supply mode GVZ.

Then, the temporal characteristic magnitudes for detecting the hydraulic heater / building supply condition are determined. In particular, this is one of the following sizes: the gradient or first derivative with respect to time or with respect to the flow temperature Tvl for the heater supply state VZ, the gradient or first derivative with respect to time or with respect to the flow temperature Tvl for the building supply state GVZ, the gradient or the first derived with respect to time or with respect to the flow temperature Tv1 for the heater operating performance ratio BLV; the gradient or the first derivative with respect to time or with respect to the flow temperature Tv1 for the logarithmic heater upper temperature Alog; the gradient or first derivative with respect to time or with respect to the flow temperature Tvl for the difference Ahkv between heater side and room air side heater temperatures.

Subsequently, the temporal characteristic magnitudes are averaged over time for the purpose of detecting the hydraulic equalization and the mean values are evaluated in accordance with the above criteria which appear from the ones in FIG. 6 to 8.

As a result, there is a hydraulic building fingerprint in the form of a state table for all heaters 2 with the hydraulic states of each heater 2: UVZ (= hydraulically supplied) or NVZ (= hydraulically adequately supplied) and the total value compressed for the heating system 9 (hydraulic total condition): GUVZ (= total system hydraulically supplied) or GNVZ (= total system hydraulically sufficiently supplied). This table is provided in the device 11 in accordance with the invention. The table results can, for visualization, be transmitted to a service center 13. In connection with the service center 13, it may be a housing or housing center for a heat cost detection and / or room temperature control system, wherein the device 11 in accordance with the invention can also be simply can be integrated.

FIG. 10 shows another embodiment of a device 14 in accordance with the invention for detecting the hydraulic equalizer. The device 14 is incorporated in the same heating system 9, the description of which can consequently be omitted.

The device 14 is integrated with a heat cost distributor 12 and, in the manner already described, performs the detection of the hydraulic equalizer for a heater 2, the device 14 in this embodiment operating decentrally. Accordingly, each heater 2 must thereby be provided with a corresponding device 14. This can be achieved by the device 14 being implemented in a microprocessor in the heat cost distributor 12 and carrying out the proposed method for the respective heater 2. It is also possible to integrate the device 14 into a for the most part without any connection to the heat cost distributor 12 - room temperature control.

The conditions UVZ, NVZ for the hydraulic supply for a respective heater 2 report the device 14 to a service center 15, which, in addition to the visualization, also takes over the calculation of the hydraulic overall condition GUVZ, GNVZ for the heating system 9. Furthermore, the service centers 13 and 15 can be constructed the same.

Thus, the scope of the proposed process and the uses of the devices 11, 14 for carrying out this method are in particular hot water heating systems, in which the performance adjustment in the central heat supply is effected by changing the flow temperature θνι_ or the mass flow heat flow heat (the liquid flow heat flow). . by combining the change of the flow temperature θνι_ and the mass flow m, and wherein the regulation of the room temperature is effected by variation of the heater mass flow m and where the detection and distribution of the amount of heat for the space heating is effected by electronic heat cost distributors in accordance with the 2 or 3 sensor principle.

Particularly included are heating systems where, on the heater supply lines, the variation of the mass flow m is effected by means of heater valves and / or the regulation of room temperature is effected by means of thermostatic valves and / or the regulation of the room temperature is effected by means of electronically controlled valves and / or variation of the mass flow m by means of electronically controlled pumps and / or the regulation of room temperature is done by means of electronically controlled pumps. Further, electronic heat cost distributors are installed on the heaters in accordance with the 2-sensor principle, each of which detects a heater and a room air side temperature, or electronic heat cost distributors in accordance with the 3-sensor principle or other suitable appliances are installed which + detect the heat flow. , the heat return return temperature and the room air temperature or + detects the heat return flow temperature and a heater and a room air side temperature or + detects the heat return return temperature and a heater and a room air side temperature or + detects the heater surface surface temperature and + detects the heater surface temperature and +.

The advantages of the invention lie in the possibility of subsequent installation in connection with existing heating systems, which are equipped with electronic and communication-capable heat cost distributors and already transmit the required temperatures. Electronic radio cost distributors are the particularly suitable measuring equipment. These are today known techniques and consequently very cost-effective.

For carrying out the method according to the invention, the standard functions of the usual cost distributors are sufficient. Consequently, the installation of the proposed system also does not require access to the dwellings, which are already equipped with similar cost distributors. Only a software update is required, for example by the data collector, in which the device for detecting the hydraulic state can be easily integrated. This data collector is frequently located outside the dwelling, for example in the hallway. In addition, one-way and two-way radio cost distributors are useful. The invention can also be combined with systems for the electronic individual room temperature control.

As a result, the invention provides a continuously updated hydraulic structure, respectively. heating circuit fingerprint ". This can be regularly transferred to building property managers to motivate them for measures to improve hydraulic equalization. In addition, the invention provides an opportunity to control the outcome of measures to improve hydraulic equalization, including by remote monitoring without access to the building.

Reference number list 1 (off) heater valve 2 (off) heater 3 (off) choke valve 4 heat circulation pump 5 heat boiler 6 heat string inlet 7 heat string return 8 string control device, string control valve 9 heater 10 housing unit 11 for 12 hydraulic equalization 15 service center

Claims (14)

A method of detecting the hydraulic state of a heating system (9) with heating elements (2) connected via a fluid flow system (6, 7) which is flowed through a heating medium with a heat flow temperature (θνι_), the heat flow temperature (θνι_) and for each heater (2) an excess temperature (Δ) derived from a difference between a heater side and room air temperature is measured at different times and calculated therefrom as a heating demand for the heater (2) indicating characteristic size a logarithmic overtemperature 9 and / or a difference measured between a heater side and a room air side heater temperature by means of a heat cost distributor or temperature measuring device and / or a difference between a heater surface temperature and a room air temperature and / or one, based on the current heater output ( ) and based on a calculated heater output ( ) at nominal mass flow and current heat flow temperature (θνι_) determined heater operating performance ratio and / or a heater supply state (VZ), derived by means of a characteristic curve, the characteristic curve indicating a relationship between the BLV operating performance ratio and a heater supply state (VZ), is the heat flow temperature of the heater, is the heat return temperature of the heater, is the room air temperature at the heater, is the heater side temperature of the heat cost distributor, is the room air side temperature of the heat cost distributor, is the heater surface temperature At the height h of the heater, is the current heater output and is the heater performance at nominal mass flow and current heat flow temperature (Breeding), characterized by the change of one of the characteristic sizes (Δι_09, ΔΗκν, Δηκ, BLV, VZ) or several of the characteristic sizes (Δι09, Ahkv, Δηκ, BLV , VZ) over time or above the heat flow temperature (θνι_) and the temporal change of the heat flow temperature (Avl) are evaluated. Method according to claim 1, characterized in that the heater heater performance ratio (BLV) is calculated from the nth power of the ratio between the logarithmic overtemperature (Δι09) and the logarithmic heater overtemperature at nominal mass flow where $ rl, 100 is a calculated return temperature of the heater at nominal or sizing mass flow and current flow temperature (dvL) and n is the heater exponent. Method according to any one of the preceding claims, characterized in that the change of the characteristic magnitudes (Δι09, Ahkv, Δηκ, BLV, VZ) is provided via gradient formation or relations between the differences. Method according to any one of the preceding claims, characterized in that the change of the characteristic sizes (Δ / 09, Ahkv, Δηκ, BLV, VZ) is temporally averaged. Process according to any one of the preceding claims, characterized in that the changes in the characteristic sizes {Aiog, Ahkv, Ahk, BLV, VZ) over time or above the heat flow temperature (θνι_) are compared with determined characteristic sizes, in order to distinguish between a hydraulically supplied condition (NVZ, GNVZ) and a hydraulically supplied condition (UVZ, GUVZ). Method according to any one of the preceding claims, characterized in that a state table with the states of the hydraulic supply (NVZ, UVZ) for the individual heaters (2) and / or the hydraulic supply (GNVZ, GUVZ) for the total heating system ( 9) set up. Method according to any one of the preceding claims, characterized in that the measurement of the heat flow temperature (θνι_) takes place centrally in the building connection respectively. at the heating circuit building entrance or decentralized at the heater flow connection. Apparatus for detecting the hydraulic state of a heating system (9) with heating elements (2) connected via a fluid flow system (6, 7), which is flowed through a heating medium with a heat flow temperature (θνι_), with at least one connection for introduction of the heat flow temperature (θνι_), at least one connection for introducing a heater side temperature (Ohks) and at least one connection for introducing a room air side temperature (Orls) and a calculating unit, characterized in that the calculating unit is arranged for carrying out the method according to any of claims 1 to 7. Device according to claim 8, characterized in that several connections for introducing temperatures are designed as connection to a heat cost distributor (12). Device according to claim 9, characterized in that the device (11, 14) comprises connections for a plurality of heat cost distributors (12). Device according to claim 8, characterized in that the device (11, 14) is integrated in a heat cost distributor (12). Device according to any one of claims 8 to 11, characterized in that the device (11, 14) has a connection for delivering detected hydraulic states (NVZ, UVZ, GNVZ, GUVZ). Device according to claim 12, characterized in that a service center (13, 15) is provided for displaying the hydraulic states (NVZ, UVZ, GNVZ, GUVZ). Device according to any one of claims 8 to 13, characterized in that some or all connections are designed as radio communication connections.