RU2789441C2 - Method for operation of the circulation system and the circulation system - Google Patents

Abstract

FIELD: water supply systems.

SUBSTANCE: group of inventions relates to water supply systems. The outlet port water temperature is set to T_a by the cooling device. Set the volume flow at the inlet port to the value V_z. The change in water temperature between the start area and the end area is determined, in particular calculated, according to the axial temperature change model for the first individual section connected to the outlet port, starting from the initial temperature value T_MA*<T_soll and the initial value of the volume flow V_z*. The change in water temperature between the initial area and the end area for each additional specified individual section is determined, in particular calculated, according to the model of temperature change under the boundary condition that the water temperature in the initial area of ​​the specified individual section is equal to the water temperature in the end area of ​​the individual section to which the specified separate lot attached. The water temperature value Ta and the volume flow rate V_z at the outlet port are then selected so that at the end region of each individual section the water temperature is T_ME<T_soll and at the inlet port the water temperature is set to T_b<T_soll with T_soll-T_b<θ, where θ>0 is the set value.

EFFECT: invention increases the energy efficiency of the system.

27 cl, 8 dwg, 1 tbl

Description

The invention relates to the method of operation of the circulation system, as well as the circulation system, each time according to the features of the preambles of the independent claims.

In order to prevent the growth of microbes in cold water networks, DIN EN 806 as well as VDI 6023 directive require for drinking water installations in buildings to permanently limit the cold drinking water temperature (PWC) in all installation lines to a maximum of +25°C. According to DIN EN 806-2,3,6, the water temperature in cold water supply points must not exceed +25°C for 30 seconds after the complete opening of the tapping point. In addition, in order to avoid water stagnation, the cold water installation must be designed so that, under normal operating conditions, potable water is regularly replenished in all lines of the installation. Similarly, VDI Directive 6023 also contains a recommendation to keep drinking water temperatures as low as +25°C as possible. Naturally, limiting the water temperature is often seen as necessary for other water supply installations, such as industrial service water installations.

The occurrence of high temperatures PWC contributes to the single or combined occurrence of various circumstances, including:

- high PWC temperatures already in the domestic branch,

- thermal effects on installation areas, e.g. due to the position and orientation of the building or installation areas inside the building,

- insufficient insulation of PWC pipelines to protect against heat,

- installation of PWC piping in rooms and spaces of equipment with heat sources, in common areas of the installation, such as shafts, channels, false ceilings and walls of the installation with heat transfer media (for example, piping of the heating system, drinking hot water (PWH) and circulating drinking water system (PWH-C), air intakes and exhaust ducts, lamps),

- phases of stagnation in the indicated areas of the installation,

- highly branched PWC plants with attendant large plant volumes,

- Extra-large PWC pipelines.

The method of preference in efforts to comply with the prescribed rules in the stagnation phases has so far been the forced flushing of installations to simulate the desired operation in these phases.

To provide cold drinking water, various refrigerated circulation systems for the cold water supply network have already been proposed.

A refrigerated circulation system is already known from EP 1 626 034 A1, which proposes the controlled addition of a disinfectant to water.

From patent DE 10 2014 013 464 A1, a method for operating a circulation system with a heat accumulator, a circulation pump, a control unit and at least two branches, and having an otherwise unknown structure of a pipeline network, is known. The branches, each with a valve controlled by a drive motor, are matched to temperature sensors that are located before each mixing point between the branches. The drive motors and/or the circulation pump are connected wirelessly or by wire for communication with the control unit. The control unit is designed to perform thermal and hydraulic balancing and thermal disinfection by limiting the range of measured temperatures and / or adapting the pump power depending on the difference between the actual temperature value and the set temperature value.

From patent DE 20 2015 007 277 U1, a device for supplying drinking water and industrial water to a building is known, which has a domestic branch for cold water, which is connected to a public distribution network. The feed device contains at least one circulation pipeline, equipped with a pump, and which leads to at least one consumer. A heat exchanger is provided in the circulation pipeline, which removes heat from the water.

In addition, patent EP 3 159 457 A1 describes a device for supplying drinking water and industrial water, known from patent DE 20 2015 007 277 U1, in which the heat exchanger is formed by a latent heat accumulator and contains an electrically driven flushing valve provided in the circulation pipeline, connected to control device for control purposes. The flush valve is located between the latent heat store and the entry point of the household branch in the circulation pipe, located downstream of the latent heat store in the direction of flow.

Known water-cooled circulating systems do not guarantee or effectively ensure that the water temperature remains below the desired temperature for all individual sections and during the entire operation of the circulating system.

The problems that the present invention proposes to solve are therefore ensured in an efficient manner that the water temperature remains below the desired temperature for all individual sections and during the entire operation of the circulating system.

The problem is solved according to the invention with features of independent claims.

The method according to the invention relates to a circulation system having a cooling device with an inlet port and an outlet port for cooling water, and having a piping system with a plurality of branches, containing one or more separate sections with a given thermal interaction with the environment and connected by means of nodes, while one or several lines of the pipeline system are configured as a supply pipeline, at least one as one supply line connected to a branch point, and at least one line is configured as a circulation pipeline connected to the supply pipeline or pipelines.

The method of operation of the circulation system according to the invention is characterized in that the change in water temperature between the start area and the end area is determined according to the axial temperature change model for the first separate section connected to the outlet port, starting from the initial temperature value T _MA *<T _soll and the initial value of the volume flow V _z *, while the change in water temperature between the initial area and the end area is determined for each additional specified individual section connected to the first individual section, according to the temperature change model, under the boundary condition that the water temperature in the initial area of the specified individual section is equal to the temperature water in the end area of the individual section, with which the specified individual section is connected in the direction of water flow, and the temperature value T _{a of} the water and the value of the volume flow V _z at the outlet port are selected so that in the end area of each individual section qi circulation system, the water temperature was T _ME <T _soll , and at the inlet port the water temperature was set to T _b <T _soll with T _soll -T _b <θ, where θ>0 is the set value.

Preferably, the determination consists in calculating, according to the model, the axial change in water temperature between the start area and the end area of the individual section, ie the corresponding part of the pipeline, based on the absorption of heat from the environment of the individual section. Thus, starting from the first individual section connected to the cooling device, moving sequentially through the entire system of individual sections and thus calculates the temperature in the entire system.

According to the invention, the value T _{a of} the water temperature and the value V _z of the volume flow at the outlet port, for which the water temperature T _ME <T _soll in the end region of each individual section of the circulation system and the water temperature T _b <T _soll at the inlet port is T _soll - T _b <θ, where θ>0 is a predetermined value, are determined in the method by simulating the temperature and volumetric flow rates of the circulating water in the piping system, preferably by calculation. This is preferably done for a state with constant V _z .

The cooling device and possibly the circulation pump of the circulation system are then adjusted so that the water temperature and the volumetric flow take on the set values T _a and V _z .

According to the invention, it is proposed to set the temperature at the outlet port, and calculate the temperature changes based on it and use it for modeling according to the characteristic of paragraph 1 of the claims.

The advantage of computing is that you don't need a sensor to measure anything, and you can evaluate and change influencers, and possibly make predictions.

The calculation has the advantage over point-to-point control and/or cascade or branch control in that fewer measurement points are required and the system as a whole is less prone to fluctuations.

Thus, the regulation according to the invention, in contrast to the prior art, is carried out by the operation of setting the outlet port, although the design of the regulator is based on a common plumbing system with distributed parameters and the calculation of several temperatures T _ME . Therefore, basically only one controller and only one temperature setting is required to provide the temperature T _a .

A problem similar to that of the cold water network exists in the case of the hot water network. Only the operating temperatures change, and a heater or reservoir is used instead of a cooling device. The temperature in the hot water supply network ranges from 60°C at the tank outlet to 55°C at the tank inlet. In contrast to the cold water supply network, where the temperature rise occurs due to heat from the environment, heat losses lead to a temperature drop in the hot water supply network.

The following formula is true for both a temperature drop in a hot water network and an increase in temperature in a cold water network.

= удельный тепловой поток в Вт/м

= specific heat flux in W/m

Δϑ = ϑ initial medium - ϑ final medium, hot water

Δϑ = ϑ final medium - ϑ initial medium, cold water

Thus, the invention also includes a similar example of a hot water network in which a tank or heater is used instead of a cooling device.

In addition, the above formulas are also valid in a cold water supply network if the water temperature is higher than the ambient temperature.

Thus, in general, the invention covers, with appropriate adaptations of the formulas used for calculation according to the models, the case of using a heat exchanger instead of a cooling device that can heat or cool water.

The term branch means a line consisting of a single section or several separate sections between two nodes, with no additional nodes lying between them. Branches are interconnected by nodes.

Preferably, the boundary condition that the temperature of the water in the start area of the predetermined individual section is equal to the temperature of the water in the end area of the individual section to which the predetermined individual section is connected applies only to the individual sections of the corresponding branch.

The temperature and amount of volume flow leaving one node to an adjacent individual section depend on the temperature and amount of incoming volume flow. The invention preferably assumes that this is due to the design of the piping system.

The distribution of the volume flow rates leaving the node between the various outgoing lines or individual sections is preferably assumed by the invention as given by the design of the pipeline system.

Preferably, the mixing temperature when the branches are joined together and the temperatures when the branches are separated are calculated based on the percentage distribution of the volume flow.

In the method according to the invention, the piping system is assumed to be predetermined, it being understood that the piping system is designed in accordance with DIN 1988-300 rules for the design of piping networks, specifying, in particular, the defined nominal dimensions of the PWC (cold drinking water) line and the value of the thermal connection (thermal interaction) of circulating water with the environment. It is understood that piping network designs specified or recommended in other countries or regions may also be taken into account.

Preferably, the highest allowable value according to the design of the piping system is selected as the initial value of the volume flow V _z *. This value decreases until the temperature of the circulating water is close to T _soll , because as the volume flow decreases, the temperature of the circulating water increases and hence the temperature at the inlet port increases.

Preferably, the value of T _MA * is varied and a maximum water temperature value T _a is selected for which the water temperature at the inlet port is T _b <T _soll with T _soll -T _b <θ, where θ>0 is the set value.

Considering T _soll -T _b <θ, it is guaranteed that the temperature of the water in the circulating system will not be too low and the system will not be operated with low power consumption. Usually θ is in the range from 1°C to 5°C, but it can also lie in a different range.

The determination of the change in water temperature between the start and end area of each individual section can be carried out according to models which are known per se, for example by simulation calculations or also by corresponding known formulas.

When implementing the method according to the invention, the circulating system is preferably operated in a state in which there is no water removal and water absorption, because in this state more heating of the water can be expected than in the state in which water is removed, and therefore, a margin of safety from a state of undesirably high water temperature is provided by using the parameters T _a and V _z determined in this way.

The parameters T _a and V _z , determined in this way, are used primarily to model a given circulation system in which the piping system is designed in accordance with legal specifications regarding the nominal width and thermal interaction of the circulating water with the environment, and to operate in such a way that the mandatory rules regarding the temperature of drinking water in the circulation system.

Applicant's simulations for already existing systems have shown that by using the parameters set in accordance with the invention: a) the mentioned legal requirements are met, and b) a higher energy efficiency of the system operation is achieved.

The parameters T _a and V _z , determined by the method, are preferably used to determine the design of the cooling device in terms of its cooling capacity in a given circulating system, in which the piping system is designed in accordance with legal specifications regarding the nominal width and thermal interaction of the circulating water with the environment. environment. In addition, the design of the circulation pump can be determined in terms of its pumping power.

The following terms are to be used in this text with a defined meaning, the definition being based on DIN EN 806.

The circulating piping of a circulating system means a piping downstream of a branch point in a circulation through which water flows from the outlet port of the cooling unit back to the inlet port of the cooling unit, unless an additional branch point of that piping is connected to it.

The term node is used for the piping element to which piping is connected. Either at least two volume flows can enter the node and exactly one volume flow can leave it, or exactly one volume flow can enter and at least two volume flows can leave it. A node corresponds to a branch point.

Preferably, exactly two volumetric flows enter and one volumetric flow leaves from it, or exactly one volumetric flow enters and exactly two volumetric flows leave it, for example, in the form of a tee.

Kirchhoff's first law applies to the nodes of a circulating system, similarly to electrical circuits, according to which the sum of the incoming volumetric flows is equal to the sum of the outgoing volumetric flows.

Preferably, the outgoing volume charges at each node are distributed among the outgoing volume charges of equal magnitude. It should be understood that other distributions are also possible.

For an assembly with exactly one outgoing volume flow with different temperatures and exactly one incoming volume flow, it is preferably assumed that the temperature t _m and the mass flow m _{m of} the mixed water of the outgoing volume flow are related by the following equation to the temperature t _k and mass flow m _k of the cooler flow or temperature t _w and mass flow m _w of the warmer flow:

Where:

t _m = mixed water temperature (°C)

t _k =cold water temperature (°C)

t _w = warm water temperature (°C)

m _m = mass/volume (flow rate) of mixed water (kg; m³; kg/h; m³/h or %)

m _k = mass/volume (flow rate) of cold water (kg; m³; kg/h; m³/h or %)

m _w = mass/volume (flow rate) of warm water (kg; m³; kg/h; m³/h or %)

The following parameters can preferably be used along with the length of the individual section to determine the change in water temperature between the start and end area of a particular section.

T _Luft = ambient air temperature (°C)

K _r = pipeline heat transfer coefficient (W/(m*K))

m _M = mass flow of water in a separate section (kg / s)

C _pm = specific heat capacity of water (J/(kg*K))

V _M = volumetric flow of water in a separate section (m ³ / s)

P _M =density of water (kg/m ³ )

Preferably, the change in water temperature between the start area and the end area can be determined for each individual section of the circulating system during a stationary volume flow, while the water temperature in the end area of the specified individual section is chosen to be equal to the water temperature in the initial area of the individual section to which the specified individual the section is connected in the direction of the flow of circulating water. Therefore, for each individual section of the circulation system, it is possible to determine the temperature of the water in the end region of the corresponding individual section, based on the temperature in the initial region.

Preferably, starting from the temperature at the outlet port at the time of stationary volume flow, it is possible to determine the temperature of the circulating water for each individual section, i.e. it is also possible to determine the temperature value T _{a of} the water temperature at the outlet port as the initial temperature of the individual section adjacent to the outlet port, so, that the water temperature is T _ME <T _soll for the end regions of all individual sections.

In a further embodiment of the invention, it is proposed that the values of T _a and V _z are determined in an iterative approximation procedure, wherein the temperature T _ME of the water in the final region is calculated for each given individual section, starting from the initial temperature value T _MA *<T _soll and the initial value volume flow V _z * for the first separate section connected to the outlet port, and the water temperature T _MA ' in the start area of the next connected separate section is chosen equal to the water temperature T _ME in the end area of a given separate section.

In another embodiment of the invention, it is proposed that the individual sections be designed uniformly in the axial direction, taking into account their thermal interaction with the environment along the length between their start region and their end region, i.e. they do not change in the axial direction. This simplifies the calculations.

In another embodiment of the invention, it is proposed that the water temperature T _ME of the end region of at least one separate section of length L is determined by the formula:

=

*

=

*

=

=

=

=

Where:

L= length (m) of a uniform individual section (T _S1 )

T _MA = water temperature in the initial area (°C)

T _ME = water temperature in end area (°C)

T _Luft = ambient air temperature (°C)

k _R = pipeline heat transfer coefficient (W/(v*K))

m _M = mass flow of water in a separate section (kg / s)

C _pm = specific heat capacity of water (J/(kg*K))

V _M = volumetric flow of water in a separate section (m ³ / s)

P _M =density of water (kg/m ³ )

This formula allows a good approximation of the temperature change for uniform individual sections.

In another embodiment of the invention, it is proposed that the heat transfer coefficient of individual sections is determined by the formula:

Where:

= сопротивление теплопередачи трубопровода (м*K/Вт)

= heat transfer resistance of pipeline (m*K/W)

= коэффициент теплопередачи внутрь (Вт/(м²*K))

= heat transfer coefficient inside (W/(m²*K))

= тепловое сопротивление (м*K/Вт)

= thermal resistance (m*K/W)

= коэффициент теплопередачи наружу (Вт/(м²*K))

= heat transfer coefficient to the outside (W/(m²*K))

= внешний диаметр (м)

= outside diameter (m)

= внутренний диаметр (м)

= inside diameter (m)

And

Equations 1-4 should then be used to determine the temperature changes and heat gain in the water due to the temperature difference compared to the environment.

To do this, equation 1 for thermal resistance is inserted into equation 2 and thus the heat transfer resistance is determined. The heat transfer coefficient (Equation 3) is calculated using the reciprocal of Equation 2.

трубопровода, включая изоляциюThermal resistance

pipeline, including insulation

=

·

Уравнение 1, см. VDI 2055, 2008

=

·

Equation 1, see VDI 2055, 2008

изолированного трубопроводаThermal transition resistance

insulated pipeline

Уравнение 2, см. VDI 2055, 2008

Equation 2, see VDI 2055, 2008

·

·

Heat transfer coefficient UR of insulated pipeline

Уравнение 3U _R=

Equation 3

The heat transfer coefficient is the central component of Equation 4 for calculating the temperature at the end of an individual section.

Using Equation 4, the corresponding cold water start and end temperatures are found for all relevant individual sections. The derivation of the formula for axial heating of water in a pipeline begins with Equation 5:

Уравнение 4

Equation 4

Уравнение 5, см. VDI 2055, 2008

Equation 5, see VDI 2055, 2008

и затем объединить.insert

and then merge.

In an iterative calculation with a gradual/step increase in volume flow, the volume flow is searched for, which ensures the operation of the cold water plant with the desired/given spread, for example 5 K (15°C/20°C).

With this solution, it is possible to determine not only the volume flow of the circulation system, which is the main factor, but also the temperature of the water at any given point in a particular pipeline network.

Preferably, the iterative approximation method was a known Excel target value search; see Excel and VBA: An Introduction to Practical Applications in the Life Sciences, Franz Josef Mehr, Maria Therese Mehr, Wiesbaden 2015, section 8.1.

According to the invention, the key data of the pipeline system, including the above parameters of the individual sections, are entered into the program, and the search for the target value is used to determine the volume flow V _z at which the target temperature T _{b of} drinking water is reached; for example, as follows:

3.1.1. Material values, water

No. Designation Value/ MT Units MT1 Drinking water temperature at the inlet after the outlet port 15.0°C MT2 Target drinking water temperature 20.0°C MT3 Density of water at 17.5°C 998.8 kg/m³ MT4 Volume flow _Vz 0.022 m³/h MT5 Specific heat 1.163 Wh/(kg*K)

3.1.2 Heat transfer coefficients

No. Designation W (W/(m²*K)) Wi Heat transfer coefficients to the outside α _a 5 Wa Heat transfer coefficients inside a _i 0

3.1.3 Ambient temperature

No. Designation Temperature UT t _Luft in °C UT1 Boiler room UT2 Walk in the basement UT3 Mine UT4 Suspended ceiling hallway UT5 Bathroom front wall UT6 Reverse mine

3.1.4 Insulation

No. Material thermal conductivity coefficient DA λ _DA in W/(m*K) DA1 Rockwool with pvc Boiler room 0.035 DA2 Rockwool lined with aluminum Walk in the basement 0.035 DA3 Rockwool lined with aluminum Riser 0.035 DA4 Rockwool lined with aluminum hallway ceiling 0.035 DA5 Flex EL-Conel 24×18 Bathroom front wall 0.032 DA6 with 9 mm floor insulation Bathroom floor 0.04

3.1.5 Piping materials

No. Designation Nominal thickness wall thickness Coefficient of thermal conductivity DA mm mm λ _R in W/(m*K) R1 Viega Raxofix 16×2.2 2.2 0.4 R2 Viega Raxofix 20×2.8 2.8 0.4 R3 Viega Raxofix 25×2.7 2.7 0.4 R4 Viega Raxofix 32×3.2 3.2 0.4 R5 Viega Raxofix with insulation 16×2.2 2.2 0.35 R6 Viega Raxofix with insulation 20×2.8 2.8 0.35 R7 Viega Raxofix with insulation 25×2.7 2.7 0.35 R8 Viega Raxofix with insulation 32×3.2 3.2 0.35 R9 Viega Sanpress 15×1.0 1 23 R10 Viega Sanpress 18×1.0 1 23 R11 Viega Sanpress 22×1.2 1.2 23 R12 Viega Sanpress 28×1.2 1.2 23 R13 Viega Sanpress 35×1.5 1.5 23 R14 Viega Sanpress 42×1.5 1.5 23 R15 Viega Sanpress 54×1.5 1.5 23 R16 Viega Sanpress 64×2 2 23

In this example, the calculated volume flow V _z for which the target temperature T _b of 20°C is achieved for an inlet temperature T _a of 15°C is indicated on line MT4.

In a further embodiment of the invention, it is assumed that the circulation pump is integrated into the circulation system so that the desired volume flow can be set.

Of course, several cooling devices and/or circulation pumps can also be provided.

Next, embodiments with piping structures that are commonly used for drinking water installations in buildings will be described.

The connection line is the line between the supply line and the drinking water installation or circulation system.

The consumer line is the line that takes water from the main shutoff valve to the branch point assemblies and possibly appliances. The collective supply line is a horizontal consumption line between the main shutoff valve and the riser. A riser (outlet riser) leads from one floor to another, and from it depart the floor lines of the building or individual supply lines. The building floor line is a line extending from the riser (outlet riser) inside the building floor, and separate supply lines radiate from it. A separate supply line is a line leading to a branch point.

In one embodiment of the invention, it is assumed that at least one supply pipeline is connected to at least one bypass line.

In another embodiment of the invention, it is assumed that at least one branch of the circulation pipeline departs from at least one supply pipeline.

In another embodiment of the invention, it is assumed that at least one branch of at least one circulation pipeline departs from at least one bypass line.

In a further embodiment of the invention, it is contemplated that the at least one supply conduit comprises at least one riser line and/or a building floor line.

In a further embodiment of the invention, it is assumed that at least one supply pipeline contains a common supply line, which is connected by a branching point to the water supply network.

In a further embodiment of the invention, it is assumed that the junction point is connected to at least one connecting line and/or at least one consumer line.

In a further embodiment of the invention, it is assumed that at least one static or dynamic flow divider is located in at least one supply line and/or in at least one bypass line, through which one point is preferably connected branches for water. Preferably, a percentage allocation of volume flow rates of 95% on exit and 5% on through is performed.

In a further embodiment of the invention, it is contemplated that a cooling device is used to cool the circulating water to transfer thermal energy from the circulating water to another material stream, preferably by heat transfer, which can optimize the cooling process by appropriate selection of the other material stream, such as propane, and reducing the energy required to operate the cooling device.

In a further embodiment of the invention, it is contemplated that the cooling device is thermally coupled to a refrigeration generator, preferably a heat pump, water cooler or refrigeration supply network, which can likewise reduce the energy required for the refrigeration process.

In another embodiment of the invention, it is proposed to determine the duty cycle of the circulating pump depending on the supplied volume flow of the circulating pump, and to determine the duty cycle of the cooling device depending on the temperature of the water at the outlet port, and adjust the volume flow V _z and the water temperature T _a at the outlet port so so that the power consumption of the circulation pump and the cooling device takes a relative or absolute minimum value, thereby increasing the energy efficiency of the method.

In a further embodiment of the invention, it is intentionally assumed that a value of 20°C +/- 5°C is chosen for the temperature T _soll and a value of 15°C +/- 5°C is chosen for the _water temperature Ta at the outlet port.

In a further embodiment of the invention, it is assumed that at least one separate section of the pipeline system is designed as an external circulation pipeline, since external circulation pipelines are usually installed, in particular, in already existing circulation systems.

In an additional embodiment of the invention, it is assumed that at least one separate section is designed as an internal circulation pipeline, since they are often installed in newer or newer circulation systems.

Additional advantages will be apparent from the following description of the drawings.

The drawings show exemplary embodiments in the specification. The drawing, specification, and claims contain many features in combination. The skilled person will also consider the features individually and combine them into additional meaningful combinations.

Shown as an example:

1: schematic representation of the circulation system according to the invention;

Fig. 2: an additional embodiment of the circulation system according to the invention;

3: a further embodiment of the circulation system according to the invention, in which an additional heat exchanger is provided;

4: additional embodiment of the circulation system according to the invention;

5: an additional embodiment of the circulation system according to the invention;

Fig. 6: an additional embodiment of the circulation system according to the invention;

7: additional embodiment of the circulation system according to the invention;

Fig. 8: An additional embodiment of the circulation system according to the invention.

The circulation systems shown in Figures 1-8 are merely examples, the invention is not limited to these systems. In all systems shown, exactly two volume flows enter and one volume flow leaves the assembly, or exactly one volume flow enters and exactly two volume flows leave it, such as a tee. However, the invention is not limited to systems with such nodes. As such, all lines present between nodes, and between nodes and an input port, as well as nodes and an output port, may consist of one or more separate sections, as defined above.

Like components have like reference numerals.

In the circulation system shown in Fig. 1, one unit K1 is connected via a supply line 4a to the outlet port 12b of a cooling device 12. The cooling device 12 has connections on the cooling side and a cooling pump 13.

At node K1 there is a branching point to the collective line 4, a connecting line to branching 1 in the water supply network, and to a consumer line 3, the latter and the connecting line being not part of the circulation system. Therefore, there is no proportional distribution of the volume flow in the K1 node.

The common supply line 4 is connected to the riser 5, which is included in the node K2. Node K2 branches into line 6 of the building floor and riser 5, which enters node K3, and in which a branch occurs to line 6 of the building floor and riser 5, which is connected to line 6 of the building floor, which enters node K4. Node K2 is connected by a line on the 6th floor of the building with node K6. Node K3 is connected by a line on the 6th floor of the building with node K5.

Two separate sections TS1 and TS2, clearly different as such, are connected via node K4, with TS1 representing a separate section of the line 6 of the floor of the building and TS2 representing the circulation pipe.

In addition, at node K4 there is a branching through a single supply line 7 to a branch point 9 . To simplify the subject, the individual supply lines and branch points connected to nodes K2 and K3 do not have reference numbers. Since the circulation system according to the invention is used to carry out the method according to the invention in a state in which there is no water removal, the nodes that are matched to the branch points are not discussed below and, accordingly, are not indicated in the drawings by reference numbers, with the exception of the K4 node.

A separate section TS2 is connected to a vertical circulation pipe 10a, which is included in the node K5. The node K5 is connected to the circulation pipe 10a, which is included in the node K6. The node K6 is connected to a vertical circulation pipe 10a, which is connected to a horizontal circulation pipe 10a, which in turn is connected via a vertical circulation pipe to a circulation pump 10b.

The circulation system shown in Fig. 2 has a structure similar to that in Fig. 1, but the bypass lines are provided in the floor lines 6 of the building, and for the sake of simplicity, the reference number 8 is used only for the uppermost bypass line shown in Fig. 2. The bypass line 8 is matched with a possible flow divider 8a. Bypass lines are coordinated with nodes K21-K32. It is understood that such systems in which there is only one bypass line are also covered by the invention.

3 shows another system with nodes K31-K34, but here the circulation pipes 10a entering nodes K34 and K35 run parallel to the lines of the 6th floor of the building extending from nodes K32 and K33.

In addition, an exemplary decentralized cooling device 14 with an inlet port 14a and an outlet port 14b is located on the line 6 of the highest floor of the building, while for ease of presentation the existing branching points of the cold side circuit and the corresponding pump are not shown.

Similarly, additional decentralized cooling units can be placed on other floors of the building.

In another embodiment, similar to that shown in FIG. 3, heat exchanger 12 may be omitted; in this case, one cooling device 14 or several cooling devices 14 are needed.

Similar to the embodiment in FIG. 3, cooling devices may be provided in risers 5 and the floor line of the building in the embodiments in FIGS. 1, 2, and 4-8.

Fig. 4 shows a system with nodes K41-K51 as in Fig. 3, but bypass lines 8 are provided in the floor lines of the building.

5 shows a system with nodes K51-K55, in which the circulation pipes 10 run parallel to risers 5 connected to nodes K52, K53.

6 shows a system with nodes K61-K69b, where bypass lines are provided between nodes K63, K64, K66, K67 and K68, K69.

Fig.7 shows a system with nodes K71-K75, where risers 5 are connected to nodes K72 and K73.

Fig. 8 shows a system with nodes K81-K89b similar to Fig. 7, but with bypass lines located between nodes K89a, K89b, K88, K89 and K84 and K85.

The embodiments shown in the drawings without reference under figures 1, 3, 5, 7 can also circulate only certain areas. In this way, individual areas can also represent installations, for example in residential areas, which are not allowed to circulate together due to different requirements (water consumption accounting). Here it is possible to exchange water to maintain the desired temperature by means of automatic rinsing.

The method according to the invention is implemented in the systems in figures 1-8 in the manner described above: starting from the initial temperature value T _MA *<T _soll and the initial value of the volume flow V _z * for the first separate section connected to the outlet port (12b), while changing The water temperature between the start area and the end area is determined according to the temperature change model.

In addition, the change in water temperature between the initial area and the end area for each subsequent given individual section is determined in accordance with the model of temperature change under the boundary condition that the water temperature in the initial area of the specified individual section is equal to the water temperature in the end area of the individual section to which the given separate lot attached.

Preferably, the axial temperature change model described above is used, according to which the temperature T _ME of water in the end region of a separate section of length L is calculated by the formula:

=

*

=

*

=

=

=

=

The value T _a of the water temperature and the value V _z of the volume flow at the outlet port 12b are chosen so that in the end region of each individual section of the circulation system the water temperature is T _ME <T _soll , and at the inlet port 12a the water temperature is T _b <T _soll with T _soll -T _b <θ, where θ>0 is the set value.

It is clear that the circulation pump 10b does not always operate at a constant volume flow, that is, regardless of whether the temperature at the inlet port 12a has a precisely set value or even below it.

If the temperature at the inlet port 12a for various reasons should be 17°C, for example, at a maximum of 20°C, the volume flow of the circulation pump 10b can be reduced. This can be done automatically, for example in temperature control. As a result, energy savings will be achieved.

Likewise, in such a case, the volume flow of the pump 13 can be reduced by temperature control.

If the port inlet temperature for various reasons must be eg 17°C (with a maximum of 20°C, for example), the supply temperature in the refrigeration circuit can be adjusted in the same way. As a result, energy savings will be achieved.

List of reference positions

1 Connection to the water supply network

2 Connecting line

3 of the consumer line

4 Collective feed line

5 Riser (drain pipe)

6th line of the building

7 separate feed line

8 Obvodnaya line

8a Static or dynamic flow separation

9th of the branch

10 circulation system

10a Circulation pipeline

10B circulation pump

12 cooling device

12a entrance port

12b output port

14 heat exchanger

14a entrance port

14b output port

Claims (49)

1. The method of operation of the circulation system (10) having a cooling device (12, 14) with an inlet port (12a, 14a) and an outlet port (12b, 14b) for cooling water and having a piping system with multiple branches, containing one or more separate sections with a given thermal interaction with the environment and connected by nodes, while one or more lines of the pipeline system are configured as a supply pipeline (4, 5, 6), at least one as a single supply line (7) connected to a point ( 9) branches, and at least one line is configured as a circulation pipeline (10a) connected to the supply pipeline or pipelines (4, 5, 6), with the steps in which: set the temperature of the water at the outlet port (12b, 14b) to the value of T _a by means of the cooling device (12, 14), set the volume flow in the inlet port (12a) to the value of V _z , characterized by the following steps, in which: determine, in particular, the change in water temperature between the start area and the end area is calculated according to the axial temperature change model for the first separate section connected to the outlet port (12b, 14b), starting from the initial temperature value T _MA *<T _soll and the initial value of the volume flow V _z *, determine, in particular calculate, the change in water temperature between the initial area and the end area for each additional specified individual section according to the temperature change model with the boundary condition that the water temperature in the initial area of the specified individual section is equal to the water temperature in the final area of \u200b\u200bthe individual section, to which the specified individual section is connected, and the value T _{a of} the water temperature and the value V _z of the volume flow in the outlet port (12b, 14b) are selected so that in the end region of each individual section the water temperature is T _ME <T _soll , and in the inlet port (12a, 14a) the water temperature was set is given on T _b <T _soll with T _soll -T _b <ϴ, where ϴ>0 is the given value. 2. The method according to claim 1, characterized in that the values of T _a and V _z are determined in an iterative approximation procedure, while the change in water temperature between the initial region and the final region is calculated from the initial temperature value T _MA *<T _soll and the initial value volume flow V _z * for the first individual section connected to the outlet port (12b, 14b), for each additional specified individual section, with the boundary condition that the water temperature in the initial region of the specified individual section is equal to the water temperature in the final region of the individual section, to which the specified separate section is connected. 3. The method according to claim. 1 or 2, characterized in that the individual sections are designed uniformly in relation to their thermal interaction with the environment along the length between their start area and their end area. 4. The method according to claim 3, characterized in that the temperature T _ME of the water in the end region of at least one individual section of length L is determined by the formula

=

*

=

=

Where

= length of a uniform individual section (T _S1 ) (m)

= water temperature in the initial area (°C)

= water temperature in end area (°C)

= ambient temperature (°C)

= pipeline heat transfer coefficient (W/(m*K))

= mass flow of water in a separate section (kg/s)

= specific heat capacity of water (J/(kg*K))

= volumetric flow of water in a separate area (m ³ / s)

\u003d density of water (kg / m ³ ). 5. The method according to claim 4, characterized in that the heat transfer coefficient of individual sections is determined by the formula

Where

= heat transfer resistance of pipeline (m*K/W)

= internal heat transfer coefficient (W/(m²*K))

= thermal resistance (m*K/W)

= external heat transfer coefficient (W/(m²*K))

= outside diameter (m)

= inside diameter (m) And

. 6. Method according to one of the preceding claims, characterized in that the circulation pump (10b) is integrated into the circulation system (10). 7. Method according to one of the preceding claims, characterized in that the cooling device (12, 14) is used to cool the circulating water by transferring thermal energy from the circulating water to another material flow, preferably via a heat transfer medium. 8. Method according to claim 7, characterized in that the cooling device (12, 14) is thermally connected to a cold generator, preferably a heat pump, water cooler or refrigeration network. 9. The method according to one of paragraphs. 6-8, characterized by stages, in which: determine the consumer characteristics of the circulation pump (10B), depending on the supplied volumetric flow rate of the circulation pump (10B); determine the consumer characteristics of the cooling device (12, 14) depending on the temperature of the water in the output port (12b, 14b); The volume consumption of V _Z and the temperature T _A water in the output port (12B, 14B) are installed so that the power of the circulation pump (10B) and the cooling device (12, 14) took the relative or absolute minimum value. 10. The method according to one of the previous points, characterized in that for the temperature T _Soll , the value of 20 ° C +/- 5 ° C is selected, and for the temperature t _A , the value of 15 ° C +/- 5 ° C is selected in the output port ( 12b, 14b). 11. The circulation system with a cooling device (12, 14) with the input port (12a, 14a) and the output port (12b, 14b) for cooling water and having a pipeline system with many branches containing one or more separate areas with a given thermal interaction with the environment and connected by means of nodes, while for a given distribution of volumetric costs emerging from the nodes, the temperature of mixed water is determined from volumetric expenses that go out of the nodes depending on the volumetric costs included in the nodes, one or more lines of the pipeline system are configured as one or more The supply pipeline (4, 5, 6), at least one line as a single feed line (7) connected to a point (9) of the branch, and at least one line is configured as a circulation pipeline (10A) connected to the supply pipeline or pipelines (4, 5, 6), having a means for installing water temperature in the output port (12b, 14b) on the value of T _A by means of a cooling device (12, 14), a means for installing a stationary volumetric flow rate of circulating water in the input port (12A, 14A) by the value of V _Z , which is characterized by a tool for determining the change in water temperature between the initial area and the final region each individual section under the boundary condition that the temperature of the water in the final region of a given individual section is selected equal to the temperature of the water in the initial area of the individual section connected to the specified separate section in the direction of the circulating water flow, and the device of the value of the value of t _a water temperature and the water temperature and The values of V _Z volumetric flow rate in the output port (12b, 14b) so that in the final region of each individual area the temperature of the water is T _Me <T _Soll , and in the entrance port (12a, 14a) the water temperature was set on t _b <t <t <t <t <t <t <t <t <t <t <t _soll with T _soll -T _b <ϴ, where ϴ>0 is the set value. 12. The circulation system according to paragraph 11, characterized in that the device is provided for determining the values of T _A and V _Z in the iteration procedure of approximation, in which the temperature T _ME of the water is calculated for each specified individual section in its final area, starting from the initial value Temperates T _Ma * <T _Soll and the initial value of the volumetric flow rate V _Z * for the first separate section connected to the output port (12B), while the temperature T _MA 'of the water in the initial area of the next attached separate section is selected equal to the temperature t _{Me of} water in the final area of a given individual section. 13. The circulation system according to paragraphs. 11, 12, characterized in that the individual sections are designed uniformly in relation to their thermal interaction with the environment along the length between their initial region and their final region. 14. The circulation system according to paragraphs. 11-13, characterized in that the circulation pump (10b) is integrated into the circulation system (10). 15. The circulation system according to one of paragraphs. 11-14, characterized in that at least one supply pipeline (4, 5, 6) is connected to at least one bypass line (8). 16. The circulation system according to one of paragraphs. 11-15, characterized in that at least one line of the circulation pipeline (10a) departs from at least one supply pipeline (4, 5, 6). 17. The circulation system according to one of paragraphs. 11-16, characterized in that at least one line of at least one circulation pipeline (10a) departs from at least one bypass line (8). 18. The circulation system according to one of paragraphs. 11-17, characterized in that at least one supply pipeline (4, 5, 6) contains at least one riser (5) and/or line (6) of the building floor. 19. The circulation system according to one of paragraphs. 11-18, characterized in that at least one supply pipeline (4, 5, 6) contains a common supply line (4), which is connected by a branching point (1) to the water supply network. 20. The circulation system according to one of paragraphs. 11-19, characterized in that the branching point (1) is connected to at least one connection line (2) and/or at least one consumer line (3). 21. The circulation system according to one of paragraphs. 11-20, characterized in that at least one supply pipeline (4, 5, 6) and/or at least one bypass line (8) has at least one static or dynamic flow divider (8a). 22. The circulation system according to one of paragraphs. 11-21, characterized in that the cooling device (12, 14) is used to transfer thermal energy from the circulating water to another material flow, preferably by means of a heat transfer agent. 23. Circulation system according to claim 22, characterized in that the cooling device (12, 14) is thermally connected to a cold generator, preferably a heat pump, water cooler or refrigeration network. 24. The circulation system according to claim. 23, characterized in that at least one separate section of the pipeline system is designed as an external circulation pipeline. 25. The circulation system according to claim 24, characterized in that at least one separate section is designed as an integrated circulation pipeline. 26. The circulation system according to one of paragraphs. 11-25, characterized in that the cooling device (12) is connected by its outlet port (12b) to the supply pipeline (4a) and its inlet port (12a) to the vertical circulation pipeline. 27. The circulation system according to one of paragraphs. 11-26, characterized in that the cooling device (14) is integrated into the riser line (5) and/or the building floor line (6).

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