DE102022114949A1 - Method and device for transferring heat - Google Patents

Abstract

The disclosure relates to a transfer station comprising a primary-side heat supply stream, a first and a second secondary-side heat removal stream, a secondary-side heat supply stream and a first, second, third and fourth heat exchanger, wherein the secondary-side heat supply stream, before it is introduced into the second secondary-side heat removal stream, undergoes a first temperature increase and experiences a second temperature increase, the first temperature increase taking place before the second temperature increase, the second temperature increase taking place by means of the first heat exchanger, which partially uses the heat inflow on the primary side, the first temperature increase taking place by means of the second heat exchanger, which partially uses residual heat from the fourth heat exchanger and/or partially uses residual heat from the first heat exchanger, a temperature increase of the second secondary-side heat dissipation flow takes place by means of the third heat exchanger, which partially uses the primary-side heat inflow for this purpose; and the temperature of the first secondary-side heat dissipation flow is increased by means of the fourth heat exchanger, which partially uses the residual heat of the third heat exchanger and/or partially uses the primary-side heat inflow.

Description

Field of invention

This disclosure relates generally to the field of heat transfer technology and in particular to a transfer station for transferring (district) heat and a method for transferring heat in a transfer station.

Background of the invention

Devices for transferring heat and corresponding methods for transferring heat, for example in heat supply networks for residential or industrial facilities, are generally known.

Out of DE 10 2010 019 727 B4 a method for transferring heat and a transfer station for transferring heat are known. Among other things, it describes a 2- and a 3-stage transfer station, with heat from a primary-side heat supply circuit being transferred to a secondary-side useful heat circuit and a secondary-side service water circuit. Furthermore, in DE 10 2010 019 727 B4 A distinction is made between a circulation operation and a water supply operation and the operation of the transfer station requires a change over the course of a day between the circulation operation and the water supply operation (and vice versa).

DE 10 2008 038 617 A1 relates to methods and devices for using heat. It describes 2-, 3- and 4-stage transfer stations for heat transfer from a primary flow to a heating circuit and a hot water circuit.

The article “District heating transfer station with cascade. Stadtwerke Rosenheim expands FW capacity through low return temperatures” by Götz Brühl, Reinhard Bielmeier, Horst Neugebauer and Edwin Weinmann in EuroHeat & Power, 41st year (2012), issue 12, pages 45 to 51 describes a three-stage cascaded district heating transfer station with a jet pump.

The object of the invention is to provide an improved method for transferring heat in a transfer station and an improved transfer station for transferring heat compared to the prior art.

Summary of the invention

According to a first aspect, a transfer station comprises a primary-side heat supply stream, a first and a second secondary-side heat removal stream, a secondary-side heat supply stream and a first, second, third and a fourth heat exchanger.

“May” refers in particular to optional features of the invention. Accordingly, there is one embodiment of the invention that has the respective feature or features.

The secondary-side heat supply stream can experience a first temperature increase and a second temperature increase before it is introduced into the second secondary-side heat removal stream.

The first temperature increase can occur before the second temperature increase. In other words, the heat supply flow on the secondary side is successively first subjected to the first temperature increase and then to the second temperature increase. A heat supply or removal flow can be characterized by the fact that it has a predetermined or natural spatial flow direction or current direction. The flow direction can be stationary in time and/or space. The first temperature increase can take place before the second temperature increase.

The temperature of a heat flow and the temperature in general may be an averaged over a cross section of the heat flow, maximum or minimum temperature in a cross section of the heat flow. The temperature of a heat flow and temperature in general can be a temperature averaged over a time interval or a temperature at a point in time.

Initiation can be understood as merging the previously spatially separated secondary-side heat supply stream with the second secondary-side heat removal stream. Depending on the media of the secondary-side heat supply stream and/or the second secondary-side heat removal stream, a homogeneous phase or a heterogeneous phase can occur after the introduction. The secondary-side heat supply flow can be a volume flow with the medium water in a liquid phase and the second secondary-side heat removal flow can be a volume flow with a medium water in a liquid phase and both volume flows after introduction can mix to form a homogeneous phase.

The second temperature increase can be carried out using the first heat exchanger. The first heat exchanger can partially use the heat inflow on the primary side. For this purpose, the first heat exchanger can use the heat inflow on the primary side and/or partially a residual heat from the first heat exchanger.

Residual heat from a heat exchanger can be waste heat from the heat exchanger. The residual heat or waste heat of a heat exchanger can be the heat that the heat exchanger does not use for heat transfer. The residual heat from one heat exchanger can be used by another heat exchanger. Residual heat or waste heat from a heat exchanger can be determined by a predetermined limit value of a maximum heat flow to be transferred by means of the heat exchanger. Residual heat or waste heat from a heat exchanger can arise due to the second law of thermodynamics. When heat is transferred using a heat exchanger, the medium with a higher temperature gives off heat to a medium with a lower temperature. As a result, the transferable heat flow is in particular a function of a temperature difference between the two media. The lower the temperature difference, the lower the transferable heat flow.

The temperature of a medium can be raised using a heat exchanger by mixing or transferring heat from another medium, with the other medium having a higher temperature than the medium. The temperature of a medium can be raised using a heat exchanger by transmitting the heat from another medium with a higher temperature to the medium with a lower temperature. The temperature increase in a heat exchanger can be achieved by thermal radiation from a medium with a higher temperature to another medium with a lower temperature. Raising the temperature using a heat exchanger can transfer heat to another medium by changing the phase of one medium. The temperature increase in a heat exchanger can transfer heat by means of a phase change of one medium to another medium and the other medium (also) carries out a phase change. This means that the medium releases heat by means of the phase change, the other medium absorbs heat by means of the (different and “reverse”) phase change.

The first temperature increase can be done using the second heat exchanger. For this purpose, the second heat exchanger can partially use residual heat from the fourth heat exchanger and/or partially use the residual heat from the first heat exchanger. For this purpose, the second heat exchanger can partially use residual heat from the fourth heat exchanger and/or partially use residual heat from the first heat exchanger and/or partially use residual heat from the third heat exchanger.

The temperature of the second secondary-side heat dissipation stream can be increased using the third heat exchanger. The third heat exchanger can partially use the heat inflow on the primary side. For this purpose, the third heat exchanger can partially use the heat inflow on the primary side and/or partially use residual heat from the third heat exchanger.

The temperature of the first secondary-side heat dissipation stream can be increased using the fourth heat exchanger. For this purpose, the fourth heat exchanger can partially use the heat inflow on the primary side and/or partially use the residual heat from the third heat exchanger.

The transfer station can include a fifth heat exchanger. The transfer station can include a third secondary-side heat dissipation stream.

The temperature of the third secondary-side heat dissipation stream can be increased using the fifth heat exchanger. For this purpose, the fifth heat exchanger can partially use residual heat from the fourth heat exchanger and/or partially use the residual heat from the third heat exchanger.

The first temperature increase can be carried out by means of the second heat exchanger, which partially uses the residual heat of the first heat exchanger and/or partially the residual heat of the third heat exchanger and/or partially uses the residual heat of the fourth heat exchanger and/or partially uses residual heat of the fifth heat exchanger.

The secondary-side heat supply stream can sometimes experience a third temperature increase after being introduced into the second secondary-side heat removal stream. The third temperature increase can occur with the temperature increase of the second secondary-side heat dissipation stream. The third temperature increase can occur after the second temperature increase.

The primary-side heat supply flow can be a flow flow from a district heating network or a local heating network.

The first secondary-side heat dissipation stream can be a first secondary-side useful heat circuit. The first secondary-side useful heat circuit can be a heating circuit.

The third secondary-side heat dissipation stream can be a second secondary-side useful heat circuit.

The second secondary-side heat dissipation stream can be a service water circuit.

The secondary-side heat supply stream can be water from outside the process water circuit. The water from outside the service water circuit can be drinking water.

A process water in the process water circuit can be circulated using a pump. The process water can be circulated in the service water circuit by means of a pump and by introducing water from outside the service water circuit into the service water circuit.

The second temperature increase of the secondary-side heat supply stream can take place simultaneously with the temperature increase of the second secondary-side heat removal stream. The second temperature increase can take place simultaneously with the temperature increase of the first and/or the third secondary-side heat dissipation stream. The second temperature increase of the secondary-side heat supply stream can take place simultaneously with the temperature increase of the first and/or the second and/or the third secondary-side heat removal stream.

The primary-side heat supply stream can be used to increase the temperature of the first secondary-side heat dissipation stream by means of the fourth heat exchanger and at the same time the primary-side heat supply stream can be used to increase the temperature of the second secondary-side heat dissipation stream by means of the third heat exchanger. The primary-side heat supply flow can be used to increase the temperature of the first secondary-side heat removal flow by means of the fourth heat exchanger and at the same time the primary-side heat supply flow can be used to increase the temperature of the process water circuit by means of the third heat exchanger. The primary-side heat supply flow can be used for the second temperature increase of the secondary-side heat supply flow by means of the first heat exchanger and/or at the same time the primary-side heat supply flow can be used for the temperature increase of the first secondary-side heat removal flow by means of the fourth heat exchanger and/or at the same time the primary-side heat supply flow can be used for the temperature increase of the second secondary-side heat dissipation stream can be used by means of the third heat exchanger and/or at the same time the primary-side heat supply stream can be used to increase the temperature of the third secondary-side heat dissipation stream by means of the fifth heat exchanger.

The process water circuit can be a drinking water circuit.

The first secondary-side useful heat circuit can be a first heating circuit. The first heating circuit can include a radiator and underfloor heating. The first heating circuit can include underfloor heating and/or include component activation or include convection heating. The convection heater can be a radiator.

The second secondary-side useful heat circuit can be a second heating circuit. The second secondary-side useful heat circuit can include underfloor heating and/or component activation.

A return temperature of the first secondary-side useful heat circuit can be higher than a return temperature of the second secondary-side useful heat circuit.

The heat exchangers of the transfer station can each be a heat storage and/or heat exchanger. The heat exchangers of the transfer station can be plate heat exchangers, spiral heat exchangers or tube bundle heat exchangers. The heat exchangers can be recuperators and/or regenerators (see also DE 10 2010 019 727 B4 ).

The heat exchangers of the transfer station can each include a primary and a secondary side. The primary side can transfer heat to the secondary side of the heat exchanger of the transfer station. The primary side can store heat. The primary side can store heat before it is partially transferred to the secondary side.

The first heat exchanger can further include a temperature difference between the primary side and the secondary side of the first heat exchanger. The temperature difference of the first heat exchanger can cover a range from 1 to 10 Kelvin (or even higher), preferably 1 Kelvin. The temperature difference of the first heat exchanger can be an average temperature difference of the first heat exchanger.

The second heat exchanger can further include a temperature difference between the primary side and the secondary side of the second heat exchanger. The temperature difference of the second heat exchanger can cover a range from 1 to 40 Kelvin (or even higher), preferably 1 Kelvin sen. The temperature difference of the second heat exchanger can be an average temperature difference of the second heat exchanger.

The third heat exchanger can further include an average temperature difference between the primary side and the secondary side of the third heat exchanger. The temperature difference of the third heat exchanger can cover a range from 1 to 30 (or even higher) Kelvin, preferably 1 Kelvin. The temperature difference of the third heat exchanger can be an average temperature difference of the third heat exchanger.

The fourth heat exchanger can further include an average temperature difference between the primary side and the secondary side of the fourth heat exchanger. The temperature difference of the fourth heat exchanger can cover a range from 1 to 40 Kelvin (or even higher), preferably 1 Kelvin. The temperature difference of the fourth heat exchanger can be an average temperature difference of the fourth heat exchanger.

The fifth heat exchanger can further include an average temperature difference between the primary side and the secondary side of the fifth heat exchanger. The temperature difference of the fifth heat exchanger can cover a range from 1 to 30 Kelvin (or even higher), preferably 1 Kelvin. The temperature difference of the fourth heat exchanger can be an average temperature difference of the fourth heat exchanger.

The average temperature difference can be a temporal averaging of a temperature difference and/or a geometric averaging over a heat transfer surface of a heat exchanger. The time averaging can be the stationary state of the heat flows in the heat exchanger.

The primary side of each heat exchanger of the transfer station may include a primary inlet and a primary outlet.

The secondary side of each heat exchanger of the transfer station may include a secondary inlet and a secondary outlet.

The primary inlet of the first heat exchanger can be coupled to the primary-side heat supply flow. The primary inlet of the first heat exchanger can be coupled to the primary-side heat supply flow and the primary outlet of the first heat exchanger.

The primary inlet of the second heat exchanger can be coupled to the primary outlet of the fourth and/or the fifth heat exchanger and the primary outlet of the first heat exchanger. The primary inlet of the second heat exchanger can be coupled to the primary outlet of the fourth and/or fifth and/or third and/or first heat exchanger.

The primary outlet of the second heat exchanger is connected to a heat dissipation flow on the primary side.

The primary inlet of the third heat exchanger can be coupled to the primary-side heat supply flow. The primary inlet of the third heat exchanger can be coupled to the primary-side heat supply flow and the primary outlet of the third heat exchanger.

The primary inlet of the fourth heat exchanger can be coupled to the primary-side heat supply flow and the primary outlet of the third heat exchanger. The primary inlet of the fourth heat exchanger can be coupled to the primary-side heat supply flow and the primary outlet of the third heat exchanger and the primary outlet of the fourth heat exchanger.

The primary inlet of the fifth heat exchanger can be coupled to the primary outlet of the fourth heat exchanger. The primary inlet of the fifth heat exchanger can be coupled to the primary outlets of the fourth and third heat exchangers.

The secondary inlet of the first heat exchanger can be coupled to the secondary-side heat supply flow.

The secondary inlet of the second heat exchanger can be coupled to the secondary outlet of the first heat exchanger.

The secondary inlet of the third heat exchanger can be coupled to the process water circuit. The secondary inlet of the third heat exchanger can be coupled with a return of the service water circuit.

The return flow is determined by the direction of the flowing medium in a circuit, which flows away from the consumer towards the producer. The consumer can be an energy sink, heat sink or a withdrawal point. The generator can be an energy source, heat source or supply point. The forward direction is the reverse of the return direction. A return and a forward flow of a circuit can be in fluid communication.

The secondary inlet of the third heat exchanger can be coupled to the second secondary-side heat dissipation stream. The secondary entry of the third heat exchanger can be coupled to the secondary outlet of the first heat exchanger. The secondary inlet of the third heat exchanger can be coupled to the secondary outlet of the first heat exchanger and the second secondary-side heat dissipation flow or to a return of the process water circuit.

The secondary outlet of the first heat exchanger can be coupled to a flow and/or a return of the process water circuit. The secondary outlet of the first heat exchanger can be coupled to the second secondary-side heat dissipation stream.

The secondary outlet of the third heat exchanger can be coupled to the second secondary-side heat dissipation stream. The secondary outlet of the third heat exchanger can be coupled to the flow of the service water circuit.

The couplings can be energy transmission routes or energy supply routes. These can transfer energy from one coupling point to another coupling point and/or vice versa. The energy can manifest itself as thermal energy in the form of heat. Heat can be transferred by transmission, diffusion, dispersion, free and/or forced convection (in combination with a carrier medium, for example a fluid) and/or radiation.

A fluid can serve as a means of transmitting energy (or heat transfer medium). The fluid can be water. The energy transmission route or energy supply route can be a closed or open pipeline. A fluid may be contained therein. The fluid can be in a closed or open pipeline. The fluid can be caused to flow/move using a fluid energy machine and thereby heat can be transferred by forced convection. The fluid energy machine can be a work machine. The fluid energy machine may be a pump, compressor, blower and/or ventilator. The fluid energy machine can be a (water) jet pump. The fluid in a closed pipeline can be under hydrostatic pressure. A jet pump can replace the combination of mixing valve and pump.

The first temperature increase can be a temperature difference between a temperature at the secondary outlet of the second heat exchanger and a temperature at the secondary inlet of the second heat exchanger.

The second temperature increase can be a temperature difference between a temperature at the secondary outlet of the first heat exchanger and a temperature at the secondary inlet of the first heat exchanger.

The third temperature increase can be a temperature difference between a temperature at the secondary outlet of the third heat exchanger and a temperature at the secondary inlet of the third heat exchanger.

The residual heat of the first heat exchanger can be heat that is provided at the primary outlet of the first heat exchanger. The residual heat of the second heat exchanger can be heat that is provided at the primary outlet of the second heat exchanger. The residual heat of the third heat exchanger can be heat that is provided at the primary outlet of the third heat exchanger. The residual heat of the fourth heat exchanger can be heat that is provided at the primary outlet of the fourth heat exchanger. The residual heat of the fifth heat exchanger can be heat that is provided at the primary outlet of the fifth heat exchanger.

The transfer station may further include first and second mixing valves. The first and second mixing valves can each be a controllable three-way valve or two controllable two-way valves.

The coupling of the primary inlet of the first heat exchanger with the primary-side heat supply flow and the primary outlet of the first heat exchanger can include the first mixing valve. The first mixing valve can be designed to mix heat from the primary heat supply flow and residual heat from the first heat exchanger. The heat resulting from the mixture can be provided at the primary inlet of the first heat exchanger. The first mixing valve can be designed to provide heat from the primary-side heat supply flow and/or residual heat from the first heat exchanger at the primary inlet of the first heat exchanger. The heat of the primary-side heat supply flow can be the element 320a in 3 be. The residual heat from the first heat exchanger can be used by element 302.4 in 3 be. the first heat exchanger can be element 302 in 3 be. The primary inlet of the first heat exchanger can be the element 302a.2 in 3 be. The first mixing valve can contain element V301 3 be.

The coupling of the primary inlet of the third heat exchanger with the primary-side heat supply flow and the primary outlet of the third heat exchanger can include the second mixing valve. The second mixing valve can be designed to transfer the heat from the primary side heat supply roms and the residual heat from the third heat exchanger. The heat resulting from the mixture can be provided at the primary inlet of the third heat exchanger. The second mixing valve can be designed to provide heat from the primary-side heat supply flow and/or residual heat from the third heat exchanger at the primary inlet of the third heat exchanger. The heat of the primary-side heat supply flow can be the element 320b in 3 be. The residual heat from the third heat exchanger can be used by the element 306.8 in 3 be. The third heat exchanger can be the element 306 in 3 be. The primary inlet of the third heat exchanger can be the element 306a.2 in 3 be. the second mixing valve can put element V302 in 3 be.

The first mixing valve can directly or indirectly determine or influence the first temperature increase and/or the second temperature increase. The second mixing valve can directly or indirectly determine or influence the second temperature increase and/or the third temperature increase.

The transfer station may further include first and second fluid energy machines.

The first fluid energy machine may provide fluid flow at the primary inlet of the first heat exchanger. The second fluid energy machine may provide fluid flow at the primary inlet of the third heat exchanger.

The second fluid energy machine can provide a volume flow at the primary inlet of the second heat exchanger and/or a volume flow at the primary inlet of the fourth heat exchanger and/or a volume flow at the primary inlet of the fifth heat exchanger. The volume flow can be a heat flow.

The transfer station may further comprise a third fluid energy machine. The third fluid energy machine can provide a volume flow of the second secondary-side heat dissipation stream. The third fluid energy machine can be set up to circulate process water in the process water circuit.

Transfer station may further include fourth and fifth fluid energy machines. The fourth fluid energy machine can provide a volume flow of the first secondary-side heat removal stream. The fifth fluid energy machine can provide a volume flow of the third secondary-side heat removal stream. The transfer station may further comprise a first, second, fifth and/or sixth distribution valve. The distribution valve can be a mixing valve. The distribution valve can be a control valve. The distribution valve can be a valve. The valve can be an engine valve.

The first distribution valve can be designed to at least partially introduce the secondary-side heat supply flow into the second secondary-side heat removal flow before it is introduced into the second secondary-side heat removal flow. The first distribution valve can be coupled to the secondary outlet of the first heat exchanger and the secondary inlet of the third heat exchanger and the secondary outlet of the third heat exchanger. The first distribution valve can be coupled to the secondary outlet of the first heat exchanger and to the return of the domestic water circuit and to the flow of the domestic water circuit.

The first distribution valve can be designed to provide heat at the secondary outlet of the first heat exchanger, partially at the secondary inlet of the third heat exchanger or partially at the secondary outlet of the third heat exchanger. The first heat exchanger can be the element 302 in 3 be. The secondary outlet of the first heat exchanger can be the element 302b.4 in 3 be. The third heat exchanger can be the element 306 in 3 be. The secondary inlet of the third heat exchanger can be element 306b.2 in 3 be. The secondary outlet of the third heat exchanger can be element 306b.4 in 3 be. The first distribution valve can contain element V304 3 be.

The second distribution valve can be designed to provide residual heat from the third heat exchanger partly to the fourth heat exchanger and/or partly to the second heat exchanger. The second distribution valve can be coupled to the primary outlet of the third heat exchanger and the primary inlet of the fourth heat exchanger and/or the primary inlet of the second heat exchanger. The second distribution valve can be designed to provide heat at the primary outlet of the third heat exchanger, partially at the primary inlet of the fourth heat exchanger and/or partially at the primary inlet of the second heat exchanger. The third heat exchanger can be the element 306 in 3 be. The fourth heat exchanger can be the element 308 in 3 be. The second heat exchanger can be the element 304 in 3 be. The primary outlet of the third heat exchanger can be the element 306a.4 in 3 be. The primary inlet of the fourth heat exchanger can be the element 308a.2 in 3 be. The primary inlet of the second heat exchanger can be the element 304a.2 in 3 be. The second distribution valve can include element V305 3 be.

The fifth distribution valve can be designed to at least partially provide residual heat on the fourth and/or fifth heat exchanger to the second heat exchanger. The fifth distribution valve can be coupled to the primary outlet of the fourth or fifth heat exchanger and the primary inlet of the second heat exchanger and a primary-side heat dissipation flow. The fifth distribution valve can be designed to partially provide heat from the primary outlet of the fourth or fifth heat exchanger to the primary inlet of the second heat exchanger. The fifth distribution valve can be designed to partially provide heat from the primary outlet of the fourth or fifth heat exchanger to the primary inlet of the second heat exchanger and/or partially to provide it to the primary-side heat removal stream. The fourth heat exchanger can be the element 308 in 3 be. The fifth heat exchanger can be element 309 in 3 be. The second heat exchanger can be the element 304 in 3 be. The primary side heat dissipation flow can be the element 330 in 3 be. The primary outlet of the fifth heat exchanger can be element 309a.4 in 3 be. The primary inlet of the second heat exchanger can be the element 304a.2 in 3 be. The fifth distribution valve can contain element V308 3 be.

The sixth distribution valve can be designed to partially provide residual heat from the first heat exchanger to the second heat exchanger. The sixth distribution valve can be coupled to the primary outlet of the first heat exchanger and the primary inlet of the second heat exchanger and a primary-side heat dissipation flow. The sixth distribution valve can be designed to at least partially introduce heat at the primary outlet of the first heat exchanger to the primary inlet of the second heat exchanger. The sixth distribution valve can be designed to at least partially provide heat from the primary outlet of the first heat exchanger to the primary inlet of the second heat exchanger and/or partially provide heat to a primary-side heat dissipation flow. The first heat exchanger can be the element 302 in 3 be. The second heat exchanger can be the element 304 in 3 be. The primary outlet of the first heat exchanger can be the element 302a.4 in 3 be. The primary inlet of the second heat exchanger can be the element 304a.2 in 3 be. The primary side heat dissipation flow can be the element 330 in 3 be. The sixth distribution valve can contain element V309 3 be.

The transfer station can also include a controller. The control can be a regulator. The control can be set up to transmit a first instruction to the first mixing valve. The transmission can take place via wire path, radio path, light path, wired and/or wireless.

The first instruction to the first mixing valve can cause the first mixing valve to mix the heat of the primary-side heat supply stream and the residual heat of the first heat exchanger. The first instruction to the first mixing valve can cause the first mixing valve to set or provide a temperature difference between the primary side and the secondary side of the first heat exchanger or a temperature on the secondary side of the first heat exchanger.

By adjusting or adjusting or providing can be understood as meaning a mixing of two volume flows to form a common volume flow depending on a manipulated variable of a valve. The volume flow can be a heat flow. The manipulated variable of the valve can be a rotary valve built into the valve. The position of the rotary valve is done using a control.

The first instruction to the first mixing valve can cause the first mixing valve to set or provide a temperature difference that represents the exergetically optimal operating point of the transfer station. The first instruction to the first mixing valve can cause the first mixing valve to set a temperature difference between the primary inlet and the secondary outlet of the first heat exchanger in a range from 0 to 52 Kelvin, preferably 1 Kelvin.

The controller can be set up to transmit a second instruction to the second mixing valve. The second instruction to the second mixing valve can cause the second mixing valve to mix the heat of the primary-side heat supply flow and the residual heat of the third heat exchanger. The second instruction to the second mixing valve can cause the second mixing valve to set or provide a temperature difference between the primary side and the secondary side of the third heat exchanger. The second instruction to the second mixing valve can cause the second mixing valve to set or provide a temperature difference between the primary side and the secondary side of the third heat exchanger, which represents the energetically optimal operating point of the transfer station. The temperature difference between the primary side and the secondary side of the third heat exchanger can cover a range from 0 to 3 Kelvin, preferably 1 Kelvin.

The temperature of the second secondary-side heat dissipation stream may be 60°C. The temperature of 60 °C can be a common value a hot water temperature that is provided to a heat consumer.

The first and second mixing valves can be controlled in such a way that a (primary-side) residual heat from the third heat exchanger is made available to the greatest possible extent for the temperature increase of the first and/or third secondary-side heat dissipation flow, without direct heat from the primary-side heat supply flow being used for the temperature increase of the first and/or third heat supply stream is provided. The transfer station can further comprise a seventh distribution valve. The seventh distribution valve can be designed so that heat from the primary heat supply flow is at least partially provided at the primary inlet of the fourth or fifth heat exchanger. The seventh distribution valve can be coupled to the primary heat supply flow and the primary inlet of the fourth or fifth heat exchanger. The (direct) heat of the primary-side heat supply stream for raising the temperature of the first and/or third heat supply stream can be provided by means of the seventh distribution valve. The seventh distribution valve can be designed to mix heat from the primary heat supply flow and residual heat from the third heat exchanger. The heat resulting from the mixture can be provided at the primary inlet of the fourth or fifth heat exchanger. The fourth heat exchanger can be the element 308 in 3 be. The fifth heat exchanger can be element 309 in 3 be. The third heat exchanger can be the element 306 in 3 be. The primary side heat supply flow can be the element 320 in 3 be. The primary inlet of the fourth heat exchanger can be the element 308a.2 in 3 be. The seventh distribution valve can contain element V302 3 be.

The control can find the exergetically optimal operating point for different operating states. The different operating states can result from a time-invariant heat flow of the first and/or second and/or third heat dissipation flow.

The provision of heat from the primary heat supply stream can be used if the residual heat from the third heat exchanger is not sufficient to increase the temperature of the first and/or third secondary heat removal stream.

The control of the temperature increase of the third secondary heat dissipation stream by means of the fifth heat exchanger can be carried out by means of an eighth and ninth distribution valve. The transfer station further includes the eighth and ninth distribution valves. The eighth distribution valve can be coupled to the primary outlet of the third heat exchanger and the primary inlet of the fifth heat exchanger. The eighth distribution valve can be designed to provide heat from the primary outlet of the third heat exchanger to the primary inlet of the fifth heat exchanger. The third heat exchanger can be the element 306 in 3 be. The fifth heat exchanger can be element 309 in 3 be. The primary outlet of the third heat exchanger can be element 306a.5 in 3 be. The primary inlet of the fifth heat exchanger can be element 309a.2 in 3 be. The eighth distribution valve can contain element V306 3 be.

The ninth distribution valve can be coupled to the primary outlet of the fourth heat exchanger and the primary inlet of the fifth heat exchanger. The ninth distribution valve can be designed to provide heat from the primary outlet of the fourth heat exchanger to the primary inlet of the fifth heat exchanger. The fourth heat exchanger can be the element 308 in 3 be. The fifth heat exchanger can be element 309 in 3 be. The primary outlet of the fourth heat exchanger can be the element 308a.4 in 3 be. The primary inlet of the fifth heat exchanger can be element 309a.2 in 3 be. The ninth distribution valve can contain element V307 3 be. The temperature increase of the third secondary heat removal stream can be done by means of heat from the primary heat supply stream and/or residual heat from the fourth heat exchanger and/or residual heat from the third heat exchanger. Heat that is provided at the primary inlet of the fifth heat exchanger can be provided by means of the seventh and/or eighth and/or ninth distribution valve. The control can find the exergetically optimal operating point in conjunction with the temperature increase of the third secondary heat dissipation stream.

According to the first aspect, the present invention provides a transfer station in accordance with claim 1. Further embodiments and features of the present invention emerge from the dependent claims, the accompanying drawings and the description.

In a second aspect, the present invention provides a method for transferring heat in a transfer station in accordance with claim 12. The transfer station can be the transfer station from above.

Before a detailed description of the invention follows its advantages.

It is known that in transfer stations cold water experiences a temperature increase before it is introduced into the hot water circuit or water before it is introduced into the service water circuit. According to current hygiene regulations in Germany, the temperature in the return of the service water circuit must be at least 55 °C. The temperature of the secondary return of the domestic water circuit should therefore not fall below 55 °C. These regulations serve to contain the spread of germs and pathogens, especially legionella, in industrial water. Consequently, in some embodiments the service water temperature is greater than or equal to 60 °C. The cold water or water before it is introduced into the domestic water circuit usually has a temperature of 8°C to 15°C. This requires a high temperature increase using the heat exchanger, which preheats the cold water or the water from outside the service water circuit.

It is also known that the said heat exchanger can use residual heat from a heat exchanger for hot water preparation in a domestic water circuit. This means that the heat provided by the district heating operator is used for energy purposes.

In some exemplary embodiments of the present invention, however, the preheating takes place successively in two stages by two separate heat exchangers before the cold water is introduced into the process water circuit. In addition, residual heat is partially used for the heat exchanger of the first stage and residual heat for the heat exchanger for increasing the temperature of the useful water circuit. This combination or cascade of heat exchangers and the combination and use of residual heat optimizes the exergetic use of the primary heat supply stream.

In some exemplary embodiments of the present invention, however, the preheating takes place successively in two stages and additionally in a third stage after the preheated cold water has been introduced into the process water circuit. The third stage of heating the cold water occurs by increasing the temperature of the domestic water circuit. This creates a dual use of heat exchangers, which implies a minimum number of heat exchangers.

The available primary heat supply flow is used thermally in an optimal way: The primary heat supply flow experiences maximum cooling. The return temperature of the primary heat supply stream is minimized. The (temperature) spread between the flow and return temperatures of the primary heat supply stream is maximized. The spread means maximizing the transmission capacity of the connecting line (e.g. district/local heating). Upstream supply lines can be minimized in size while maintaining the same transmission power.

Generation processes, i.e. the provision/generation of the primary heat supply stream, are optimized: Steam turbines achieve maximum efficiencies due to the minimum return temperature of the primary heat supply stream. Low-temperature heat sources such as waste heat from industrial processes can be used more efficiently as generation processes. Furthermore, condensing boilers can be used as generation processes and experience better efficiency and utilization.

It is also known that calcification is particularly a function of the water temperature. This means that calcification increases as the water temperature increases. In addition, the two stages of increasing the temperature of the cold water before it is introduced into the domestic water circuit means that the heat provided for the heat exchangers, or rather the temperature, is lower compared to a single-stage temperature increase before it is introduced into the domestic water circuit. In some exemplary embodiments of the invention, an additional “final” (third) increase in the temperature of the process water takes place using the third heat exchanger. This in turn reduces the calcification of the heat exchanger, especially for the two heat exchangers that implement the two stages of increasing the temperature of the cold water.

Furthermore, it is known that methods of a transfer station and transfer stations include two operating modes, namely a water supply operation and a circulation operation.

In the known circulation operation, process water, for example drinking water, circulates in a process water circuit. Residual heat from a primary-side heat supply circuit is used after heating a secondary-side service water circuit to heat a secondary-side useful heat circuit, such as water in a heating circuit. The primary-side heat supply circuit is, for example, a district heating inlet that transfers heat in a heat exchanger on the primary side to service water of the service water circuit on the secondary side in a transfer station. That is, the primary side is the heat release side, while the secondary side is the heat absorption side. For this purpose, the primary-side heat circuit is at least partially led to the useful heat circuit after the process water circuit has been heated. This means that (residual) heat that is then still contained in the primary-side heat circuit can be used to heat the useful heat circuit.

In the known water supply mode, (cold, fresh) water is introduced into the process water circuit from outside the service water circuit, which is heated, for example, in a heat exchanger. For this purpose, the method uses residual heat from the primary-side heat supply circuit after heating the useful heat circuit, in that the primary-side heat circuit is at least partially led to the process water circuit after heating the useful heat circuit and heats the supplied (cold) water there.

In some embodiments of the present invention, the known circulation operation may occur at least partially or simultaneously with the known water supply operation. This is advantageous because heat losses are associated with the switching process.

In some exemplary embodiments of the present invention, the advantage lies in the simultaneous use of the primary-side heat supply flow for a useful heat flow (first and/or third secondary-side heat removal flow) and the process water circuit (second secondary-side heat removal flow and/or second temperature increase of the secondary-side heat supply flow).

In some exemplary embodiments of the present invention, there is the advantage that water from outside the process water circuit can be introduced therein even during the circulation of the service water in the process water circuit.

Exemplary embodiments of the invention are described in more detail below with reference to figures. Further features and advantages arise from this description. Specific features of these exemplary embodiments can represent general features of the invention. Features of these exemplary embodiments associated with other features can also represent individual features of the invention.

Examples of embodiments

• 1 : A transfer station.
• 2 : A transfer station.
• 3 : A transfer station.
• 4 : A transfer station.
• 5 : A method of transferring heat using a transfer station.

In the following description of the exemplary embodiments, the same or similar components may have the same reference numerals.

In 1 An exemplary embodiment of a transfer station 100 for transferring heat according to one aspect of the invention is shown. The transfer station 100 comprises a first heat exchanger 102, a second heat exchanger 104, a third heat exchanger 106 and a fourth heat exchanger 108. The transfer station 100 further comprises a primary-side heat supply stream 120, a first secondary-side heat removal stream 132, a second secondary-side heat removal stream 134 and a secondary-side heat supply stream 13 8 The secondary-side heat supply stream 138, before it is introduced into the second secondary-side heat removal stream 134, experiences a first temperature increase and a second temperature increase.

The second temperature increase occurs by means of the first heat exchanger 102, which partially uses the primary-side heat inflow 120a for this purpose. This means that at least partial heat transfer takes place from the partial heat supply flow 120a on the primary side to the heat supply flow 138 on the secondary side.

The first temperature increase is carried out by means of the second heat exchanger 104, which partially uses residual heat from the fourth heat exchanger 108.2 and partially uses residual heat from the first heat exchanger 102.2. The second heat exchanger 104 thus heats the secondary-side heat supply stream 138 in the first temperature increase partially with the help of the residual heat from the fourth heat exchanger 108.2 and the first heat exchanger 102.2.

Furthermore, the transfer station 100 includes a temperature increase of the second secondary-side heat removal stream 134 by means of the third heat exchanger 106, which partially uses the primary-side heat inflow 120b for this purpose.

Furthermore, the transfer station 100 includes a temperature increase of the first secondary-side heat dissipation stream 132 by means of the fourth heat exchanger 108, which partially uses the residual heat of the third heat exchanger 106.2 and/or partially uses the primary-side heat inflow 120c. If the residual heat of the third heat exchanger 106.2 is not sufficient to raise the temperature of the first secondary-side heat dissipation stream 132 by means of the fourth heat exchanger 108, the primary-side heat inflow 120c is additionally used partially or exclusively for raising the temperature of the first secondary-side heat dissipation stream 132. The temperature of the primary side heat supply stream 120 is greater than or equal to a temperature of the secondary side heat supply stream 138 and the second secondary side Heat dissipation stream 134 and the first secondary-side heat dissipation stream 132.

The second heat exchanger 104 of the transfer station 100 uses the residual heat of the first heat exchanger 102.2 and the residual heat of the fourth heat exchanger 108.2 for the first temperature increase of the secondary-side heat supply stream 138. This means that the remaining heat, which is initially introduced into the transfer station 100 by the primary-side heat supply stream 120, becomes exergetic optimally used for the first temperature increase.

In an exemplary embodiment of the transfer station 100, a temperature of the secondary-side heat supply stream 138 is predetermined before it is introduced into the second secondary-side heat removal stream 134. This specified target temperature is achieved by the first and second temperature increases. In an exemplary embodiment of the transfer station 100, the predetermined target temperature is specified at a discrete point in time and is further determined by a control system comprehensive in the transfer station 100. The first temperature increase of the secondary-side heat supply stream 138 is partly caused by the residual heat of the first heat exchanger 102.2 and partly by the residual heat of the fourth heat exchanger 108.2. realized by means of the first heat exchanger 104. The still missing temperature difference of the secondary-side heat supply stream 138 to the predetermined target temperature is then realized by the second temperature increase of the secondary-side heat supply stream 138 by means of the first heat exchanger 102. The first heat exchanger 102 uses the partial heat supply flow 120a on the primary side.

The secondary-side heat supply stream 138, before it is introduced into the second secondary-side heat removal stream 134, experiences a first temperature increase and a second temperature increase. The said introduction of the secondary-side heat supply stream 138 into the secondary-side heat dissipation stream 134 can take place before the temperature increase of the second secondary-side heat dissipation stream 134 by means of the third heat exchanger 106, 138a, and/or after the temperature increase of the second secondary-side heat dissipation stream 134 by means of the third heat exchanger 106, 13 8b.

In an exemplary embodiment of the transfer station 100, the secondary-side heat supply stream 138 has not reached a target temperature, for example at least 60 ° C, after its first and second temperature increase. The secondary-side heat supply flow 138 (after the first and second temperature increase) is thus introduced before the third heat exchanger, 138a. The secondary-side heat supply stream 138 thus experiences a third temperature increase by means of the third heat exchanger. In another exemplary embodiment of the transfer station 100, if the secondary-side heat supply stream 138 has reached a target temperature, for example at least 60 ° C, after its first and second temperature increase, the secondary-side heat supply stream 138, after its first and second temperature increase, can be before, 138a, and/or or after, 138b, the third heat exchanger.

In one embodiment, the secondary-side heat supply stream 138 is initiated before and after the temperature increase of the second secondary-side heat removal stream 134, 138a and 138b, so that the mixed average temperature of the secondary-side heat removal stream 134 after the temperature increase of the second secondary-side heat removal stream 134 by means of the third heat exchanger 106 and therein initiated secondary-side heat supply flow 138 after its first and second temperature increase is equal to or only slightly greater than the said target temperature.

An advantageous effect of the transfer station 100 is that residual heat from the heat exchanger can still be used to increase the temperature of the secondary-side heat supply flow 138. In this way, an energetically optimal use of the primary heat flow provided is realized by means of the transfer station 100.

In 2 a transfer station 200 is shown. The transfer station 200 comprises a first heat exchanger 202, a second heat exchanger 204, a third heat exchanger 206 and a fourth heat exchanger 208. The transfer station 200 further comprises a first secondary-side heat removal stream 232, a second secondary-side heat removal stream 234 and a secondary-side heat supply stream 238.

In one exemplary embodiment, the first heat exchanger 202 is the first heat exchanger 102, the second heat exchanger 204 is the wide heat exchanger 104, the third heat exchanger 206 is the wide heat exchanger 106 and the fourth heat exchanger 208 is the fourth heat exchanger 108. Furthermore, in the exemplary embodiment, the first secondary-side heat removal stream is 232 the secondary-side heat removal stream 132, the second secondary-side heat removal stream 234, the second secondary-side heat removal stream 134 and the secondary-side heat supply stream 138.

Furthermore, the transfer station 200 includes a fifth heat exchanger 209 and a third secondary-side heat dissipation stream 236.

The secondary-side heat supply stream 238, before it is introduced into the second secondary-side heat removal stream 234, experiences a first temperature increase and a second temperature increase. The first temperature increase of the secondary-side heat dissipation stream 238 occurs before the second temperature increase of the secondary-side heat dissipation stream 238.

The second temperature increase occurs by means of the first heat exchanger 202, which partially uses the primary-side heat inflow 220a and/or partially uses residual heat from the first heat exchanger 202.4. This means that the residual heat from the first heat exchanger 202.4 can be used in combination with the primary-side heat inflow 220a to carry out the second temperature increase. This makes it possible to provide the thermal energy required for the second temperature increase partly through the primary-side heat inflow 220a and/or partly through the residual heat of the first heat exchanger 202.4. In one exemplary embodiment, for the second temperature increase, the use of the residual heat of the first heat exchanger 202.4 is prioritized over the use of the primary-side heat supply flow 220.

The first temperature increase is carried out by means of the second heat exchanger 204, which partly uses the residual heat of the first heat exchanger 202.2 and partly a residual heat of the fifth heat exchanger 209.2 and/or partly a residual heat of the third heat exchanger 206.4 and/or partly a residual heat of the fourth heat exchanger 208.2. The use of the partial residual heat of the first heat exchanger 202.2 and partially of the residual heat of the fifth heat exchanger 209.2 and/or partially of the residual heat of the third heat exchanger 206.4 and/or partially of the residual heat of the fourth heat exchanger 208.2 takes place with an exergetically optimal use of the primary-side heat supply flow 220.

The second heat exchanger 204 therefore uses residual heat from the first and fourth and/or third and/or fourth heat exchangers. The first temperature increase thus preheats the secondary-side heat supply stream 238. The secondary-side heat supply stream 238 has a lower temperature before the first and second temperature increases. This means that the first temperature increase also takes place when using the residual heat of the first and fourth and/or third and/or fourth heat exchanger, which has a lower temperature than the primary-side heat inflow 220, but is sufficient for the first temperature increase. An advantageous effect of optimal utilization of residual heat is thus achieved. A further advantage implies the lower temperature of the partial residual heat of the first heat exchanger 202.2 and partially of the residual heat of the fifth heat exchanger 209.2 and/or partially of the residual heat of the third heat exchanger 206.4 and/or partially of the residual heat of the fourth heat exchanger 208.2 compared to the temperature of the primary-side heat supply flow 220. This increases the efficiency of heat transfer. Furthermore, the said low temperature reduces calcification.

In one exemplary embodiment, the use of the residual heat 202.2 and 209.2 is prioritized based on their temperatures. In one exemplary embodiment, the use of the residual heat 202.2 and 209.2 and/or 106.4 and/or 108.2 is prioritized based on their temperatures.

Furthermore, the transfer station 200 includes a temperature increase of the second secondary-side heat removal stream 234 by means of the third heat exchanger 206, which partially uses the primary-side heat inflow 220b for this purpose.

Furthermore, the transfer station 200 includes a temperature increase of the first secondary-side heat dissipation stream 232 by means of the fourth heat exchanger 208, which partially uses the residual heat of the third heat exchanger 206.2 for this purpose. A temperature increase of the first secondary-side heat dissipation stream 232 by means of the fourth heat exchanger 208, which partially uses the residual heat of the third heat exchanger 206.2 and/or partially uses the primary-side heat inflow 220c and/or partially uses residual heat from the third heat exchanger 208.6.

The secondary-side heat supply stream 238, before it is introduced into the second secondary-side heat removal stream 234, experiences a first temperature increase and a second temperature increase. The said introduction of the secondary-side heat supply stream 138 into the secondary-side heat dissipation stream 234 can take place before the temperature increase of the second secondary-side heat dissipation stream 234 by means of the third heat exchanger 206, 238a, and/or after the temperature increase of the second secondary-side heat dissipation stream 134 by means of the third heat exchanger 206, 23 8b. In one embodiment, the introduction of the secondary-side heat supply stream 238 into the second secondary-side heat removal stream 234 corresponds to that of the transfer station 100.

Furthermore, the transfer station 200 includes a temperature increase of the third secondary-side heat dissipation stream 236 by means of the fifth heat exchanger 209, which partially uses the residual heat of the fourth heat exchanger 208.4 for this purpose. In one exemplary embodiment, the temperature of the third secondary-side heat dissipation stream 236 is raised by means of the fifth heat exchanger 209, which partially uses the residual heat of the fourth heat exchanger 208.4 and/or partially uses the residual heat of the third heat exchanger 206.6.

It can be seen that the fifth heat exchanger 209 basically uses residual heat to increase the temperature of the third secondary-side heat dissipation stream 236. In comparison, the first secondary-side heat removal stream 232 may partially utilize heat from the primary-side heat supply stream 220c. In one exemplary embodiment, this circumstance is realized in such a way that the fourth heat exchanger 208 can fundamentally use a higher temperature than the fifth heat exchanger 209. This in turn fundamentally enables a higher temperature of the first secondary-side heat dissipation stream 232 compared to the third secondary-side heat dissipation stream 236. In one exemplary embodiment the first secondary-side heat removal stream 232 is a high-temperature useful heat flow and the third secondary-side heat removal stream 236 is a low-temperature useful heat flow. The high-temperature useful heat flow includes a release of heat from the high-temperature useful heat flow by means of collector radiators. The low-temperature useful heat flow includes the release of heat from the low-temperature useful heat flow by means of underfloor heating and/or the release of component activation.

In one exemplary embodiment, the secondary-side heat supply stream 238 is a cold water stream, the secondary-side heat removal stream 234 is a hot water stream.

3 shows a transfer station 300 according to a further embodiment. The transfer station 300 includes a first heat exchanger 302, a second heat exchanger 304, a third heat exchanger 306, a fourth heat exchanger 308 and a fifth heat exchanger 309.

In one exemplary embodiment, the first heat exchanger 302 is the first heat exchanger 202 according to the embodiment 2 , the second heat exchanger 304 is the second heat exchanger 204, the third heat exchanger 306 is the third heat exchanger 206, the fourth heat exchanger 308 is the fourth heat exchanger 208 and the fifth heat exchanger 309 is the fifth heat exchanger 209.

Furthermore, the transfer station 300 includes a secondary-side heat supply stream 338 and a second secondary-side heat removal stream 334. The second secondary-side heat removal stream 334 is a process water circuit comprising a process water return 334a and a service water flow 334b. The secondary-side heat supply stream 338 is cold water or water outside the service water circuit 334.

Furthermore, the transfer station 300 includes a primary-side heat supply flow 320. The primary-side heat supply flow 320 is a flow of a district heating 320.

The cold water 338, before it is introduced into the service water circuit 334, experiences a first temperature increase and a second temperature increase. The first temperature increase of the cold water 338 takes place before the second temperature increase of the cold water 338.

The second temperature increase is carried out by means of the first heat exchanger 302, which partially uses the flow of the district heating 320a and/or partially uses residual heat from the first heat exchanger 302.4.

The first temperature increase is carried out by means of the second heat exchanger 304, which partly uses the residual heat of the first heat exchanger 302.2 and/or partly a residual heat of the fifth heat exchanger 309.2 and/or partly a residual heat of the fourth heat exchanger 308.2 and/or partly a residual heat of the third heat exchanger 306.4 .

The first heat exchanger 302 includes a primary side 302a and a secondary side 302b. The primary side 302a and the secondary side 302b are set up to transfer heat from the primary side 302a to the secondary side 302b. In one embodiment, the heat exchanger 302 is a plate heat exchanger/plate heat exchanger.

Furthermore, the primary side 302a includes a primary inlet 302a.2 and a primary outlet 302a.4, whereby heat flows into the primary inlet 302a.2, then partially releases the heat to the primary side 302a and residual heat from the first heat exchanger 302.4 flows out at the primary outlet 302a.4 . The primary inlet 302a.2 is coupled to the flow of the district heating 320 and to the primary outlet 302a.4. The coupling includes a valve V301. The valve V301 is designed as a three-way valve, resulting in a Heat flow is provided to the primary inlet 302a.2. The resulting heat flow is composed of a heat flow from the flow of the district heating 320 and a heat flow from the residual heat from the first heat exchanger 302.2. Depending on the position of the three-way valve V301, the first heat exchanger 302 partially uses the flow of the district heating 320a and/or partially uses residual heat from the first heat exchanger 302.4. The residual heat flow of the first heat exchanger 302.2 is generated by a pump P301, which is coupled between the valve V301 and the primary inlet 302a.2.

Furthermore, the secondary side 302a includes a secondary inlet 302b.2 and a secondary outlet 302b.4, whereby heat flows into the secondary inlet 304b.2, then partially absorbs the heat of the primary side 302a and partially flows out heat at the secondary outlet 302b.4.

The second heat exchanger 304 includes a primary side 304a and a secondary side 304b. The primary side 304a and the secondary side 304b are set up to transfer heat from the primary side 304a to the secondary side 304b. Furthermore, the primary side 304a includes a primary inlet 304a.2 and a primary outlet 304a.4, whereby heat flows into the primary inlet 304a.2, then partially releases the heat to the primary side 304a and residual heat from the second heat exchanger flows out at the primary outlet 304a.4. Furthermore, the secondary side 304a includes a secondary inlet 304b.2 and a secondary outlet 302b.4, whereby heat flows into the secondary inlet 304b.2, then partially absorbs the heat of the primary side 304a and partially flows out heat at the secondary outlet 304b.4.

The second heat exchanger 304 is preferably designed as a tube bundle heat exchanger. The primary side 304a includes a volume that is designed to partially store heat at the primary inlet 304a.2 and partially release this heat to the secondary side 304b. The volume typically has a medium with a high heat capacity, for example a fluid in the liquid phase, in particular water. In one embodiment, the secondary side 304b of the tube bundle heat exchanger may further comprise a volume that is designed to partially store heat at the secondary inlet 304a.2 and partially release this heat to the secondary side 304b.

In another exemplary embodiment, the second heat exchanger 304 is designed as a plate heat exchanger. In both embodiments, the primary side 304a and the secondary side 304b are materially separated. This means that heat transfer takes place through and across a separating layer. The separating layer typically has a material with high thermal conductivity, for example metal such as copper or stainless steel, enamel, plastic, glass or silicon carbide. In some embodiments, the separating layer has a small thickness for the most effective heat transfer possible. At the same time, the larger the surface of the separating layer, the more heat is transferred. With this principle, an opposite heat flow of the thermal media along the interface achieves the best heat exchange among the thermal media.

The tube bundle heat exchanger has a large heat storage capacity, providing heat on the primary side. This heat can be used to temporarily store a continuously occurring heat flow on the primary side 304a. The temporarily stored heat can be transferred to the cold water 338 to be heated. The cold water 338 often has to be heated at high outputs in short time intervals. The temporarily stored heat can be transferred to the cold water during these times. This increases the effectiveness of the overall process. It is also recommended to install the tube bundle heat exchanger 304 with the warm side facing up. This means that the primary inlet 304a.2 is located above the primary outlet 304a.4, whereas the secondary outlet 304b.4 is located above the secondary inlet 304b.2. This counteracts the exergetically unfavorable mixing of the primary side 304a and the secondary side 304b. The mixing is counteracted by the lower density of the warmer primary side 304a located at the top at the current temperature level.

The primary entry 304a.2 is coupled to the primary exit 302a.4. The second heat exchanger 304 thus partially uses the residual heat of the first heat exchanger 302.2 for the first temperature increase of the cold water 338.

The primary outlet 304a.4 is connected to a heat dissipation stream 330 on the primary side. The primary-side heat dissipation stream 330 includes a return flow of the district heating 330. The flow of the district heating 320 and the return flow of the district heating 330 thus form a district heating circuit.

Furthermore, the primary outlet 302a.4 is coupled to the return of the district heating 330. The coupling of the primary outlet 302a.4 with the return of the district heating 330 and the primary inlet 304a.2 includes a valve V309. The valve V309 is designed as a distribution valve, whereby the residual heat of the first heat exchanger 302.2 depending on the position of the distribution valve V309 is partially provided at the primary inlet 304a.2 and/or is partially introduced into the return of the district heating 330.

If the residual heat of the first heat exchanger 302.2 is less than that of a residual heat of the fifth heat exchanger 309.2 and/or a residual heat of the fourth heat exchanger 308.2, the residual heat of the first heat exchanger 302.2 is partially introduced into the return of the district heating 330 by means of the valve V309. Complete or partial initiation can influence the exergetic performance of the entire system. Accordingly, the continuous control serves to find the exergetically optimal working point.

The secondary inlet 304b.2 is coupled to the cold water 338. The secondary exit 304b.4 is coupled to the secondary entry 302b.2. This means that the first temperature increase of the cold water 338 takes place before the second temperature increase of the cold water 338.

After the first and second temperature increase of the cold water 338, the cold water 338 is introduced into the service water circuit 334. The secondary outlet 302b.4 is coupled to the service water return 334a and the service water flow 334b. The coupling includes a valve V304. The valve V304 is designed as a distribution valve, whereby the cold water 338 is partially introduced into the service water return 334a and/or partly into the service water flow 334b, depending on the position of the distribution valve V304. In the event that the cold water 338 has a predetermined temperature or exceeds this predetermined temperature before it is introduced into the service water circuit 334, in one exemplary embodiment the cold water 338 is introduced into the service water flow 334b. If, in one exemplary embodiment, the cold water 338 has not reached the assigned temperature, the cold water 338 is introduced into the service water return 334a and heated in the third heat exchanger.

Furthermore, the transfer station 300 includes a temperature increase of the process water circuit 334 by means of the third heat exchanger 306, which partially uses the primary-side heat inflow 320b and/or partially uses residual heat from the third heat exchanger 306.8.

The third heat exchanger 306 includes a primary side 306a and a secondary side 306b. The primary side 306a and the secondary side 306b are designed to transfer heat from the primary side 306a to the secondary side 306b. Furthermore, the primary side 306a includes a primary inlet 306a.2 and a primary outlet 306a.4, whereby heat flows into the primary inlet 306a.2, then partially releases the heat to the primary side 306a and residual heat from the third heat exchanger flows out at the primary outlet 306a.4. Furthermore, the secondary side 306b includes a secondary inlet 306b.2 and a secondary outlet 306b.4, whereby heat flows into the secondary inlet 306b.2, then partially absorbs the heat of the primary side 306a and partially flows out heat at the secondary outlet 306b.4.

The primary inlet 306a.2 is coupled to the flow of the district heating 320 and the primary outlet 306a.4. The third heat exchanger 306 thus partially uses the primary-side heat inflow 320b and/or partially the residual heat of the third heat exchanger 306.8 to increase the temperature of the service water circuit 334.

The coupling includes a valve V302. The valve V302 is designed as a three-way valve, whereby a resulting heat flow is provided to the primary inlet 306a.2. The resulting heat flow is composed of a heat flow from the flow of the district heating 320 and a heat flow from the residual heat from the first heat exchanger 306.8. Depending on the position of the three-way valve V302, the third heat exchanger 306 partially uses the flow of the district heating 320b and/or partially uses residual heat from the first heat exchanger 306.8. The residual heat flow from the third heat exchanger 306.2 is generated by a pump P302, which is coupled between the valve V302 and the primary inlet 306a.2. The resulting heat flow is regulated to a minimum required temperature level by means of the third heat exchanger 306 in order to increase the temperature of the process water circuit 334, so that the least possible limescale loss takes place in the third heat exchanger 306. In the standard case, the temperature on the primary side must be above 60 °C so that the drinking water is heated to 60 °C. This is the usual hot water temperature, which ensures that legionella bacteria do not form in the water.

The secondary inlet 306b.2 is coupled to the service water return 334a. The secondary outlet 306b.4 is coupled to the service water flow 334b. This means that the heat is transferred from the third heat exchanger 306 to the service water flow 334. It should be noted again that the secondary outlet 302b.4 is coupled to the process water flow 334. The coupling of the secondary outlet 302b.4 with the service water flow 334 takes place in such a way that this coupling takes place before or with the coupling of the service water flow 334 at the secondary inlet 306b.2. This means that the cold water 338, which is introduced into the service water flow 334, experiences a third temperature increase. The third temperature increase of the cold water 338 is done with the tempera Raising the temperature of the process water circuit 334 by means of the third heat exchanger 306.

In one embodiment of the transfer station 300, the highest temperatures on the primary side often occur at the primary inlet 306a.2. Therefore, in the exemplary embodiment of the transfer station 300, the heat at the primary return 306a.4 is made available to the heat exchangers 308 and 309.

The domestic water circuit 334 is a drinking water circuit with hot water. According to applicable hygiene regulations, the temperature in the service water flow 334b must be at least 60 °C. The temperature of the service water return 334a should not fall below 55 °C. These regulations serve to contain the spread of germs and pathogens, especially legionella, in the drinking water cycle. Consequently, in some embodiments the drinking water temperature is greater than or equal to 60 °C. To limit the proliferation of germs and/or to evenly distribute the temperature in the network, a pump P303 is arranged in the drinking water circuit 334, which ensures sufficient movement of the drinking water. The hygiene regulations prescribe at least 16 hours of drinking water circulation per day, which is adhered to in some embodiments.

If water is taken from the brewing water circuit 334, for example from a withdrawal point in the brewing water circuit, the water withdrawn is substituted by the cold water 338.

Furthermore, the transfer station 300 includes a first 332 and a third secondary-side heat removal stream 336. The first secondary-side heat removal stream 332 is a high-temperature heating circuit comprising a flow 332b and a return 332a. The third secondary-side heat removal stream 336 is a low-temperature heating circuit, comprising a flow 336b and a return 336a. The high-temperature heating circuit supplies hot water to a radiator heater. Typical design is 70/50. This means that with the standard design (statistically coldest outside temperature that occurs), the flow 332b is 70 °C, the return 332a is 50 °C. If the outside temperature is appropriate, the temperatures slide down or up. In other embodiments, the high temperature heating circuit is designed and operated at lower temperatures such as 60/40, 50/30, etc. The low-temperature heating circuit supplies hot water to underfloor heating. For example, a design of 35/25 is sufficient for this - that is, the temperature of the flow 336b is 35 °C and the temperature of the return 336a is 25 °C. In another exemplary embodiment, the low-temperature heating circuit is designed for thermal component activation. During thermal component activation, for example, a floor slab, a wall, or a ceiling is tempered using water-carrying pipes. A design 23/21, for example, is sufficient for this.

Furthermore, the transfer station 300 includes a temperature increase of the high-temperature heating circuit 332 by means of the fourth heat exchanger 308, which partially uses the primary-side heat inflow 320c and/or partially uses the residual heat of the third heat exchanger 306.2.

The fourth heat exchanger 308 includes a primary side 308a and a secondary side 308b. The primary side 308a and the secondary side 308b are set up to transfer heat from the primary side 308a to the secondary side 308b. Furthermore, the primary side 308a includes a primary inlet 308a.2 and a primary outlet 308a.4, whereby heat flows into the primary inlet 308a.2, then partially releases the heat to the primary side 308a and residual heat from the fourth heat exchanger flows out at the primary outlet 308a.4. Furthermore, the secondary side 308a includes a secondary inlet 308b.2 and a secondary outlet 308b.4, whereby heat flows into the secondary inlet 308b.2, then partially absorbs the heat of the primary side 308a and partially flows out heat at the secondary outlet 308b.4.

The primary inlet 308a.2 is coupled to the flow of the district heating 320 and the primary outlet 306a.4. The fourth heat exchanger 308 thus partially uses the primary-side heat inflow 320c and/or partially the residual heat of the third heat exchanger 306.2 to increase the temperature of the high-temperature heating circuit 332.

The coupling between the primary inlet 308a.2 and the flow of the district heating 320 includes a valve V303. The valve V303 provides a heat supply for the high-temperature heating circuit 332. If the residual heat from the third heat exchanger 306.2 provides sufficient heat to increase the temperature of the high-temperature heating circuit 332, the valve V303 can close completely. If the residual heat of the third heat exchanger 306.2 is not sufficient to increase the temperature of the high-temperature heating circuit 332, the valve V303 can supplement the heat missing for increasing the temperature of the high-temperature heating circuit 332 by opening the valve V303.

Furthermore, the coupling between the primary outlet 306a.4 and the primary inlet 308a.2 includes a valve V305. In the event that the residual heat of the third heat exchanger 306.2 does not provide sufficient heat for the temperature increase of the high-temperature heating circuit 332, the second heat exchanger 304 also uses residual heat from the third heat exchanger 306.4 for the first temperature increase. The primary outlet 306a.4 is thus further coupled to the primary inlet 304a.2. The coupling takes place using the valve V305.

Furthermore, the primary outlet 308a.4 is coupled to the primary inlet 304a.2. The second heat exchanger 304 thus partially uses residual heat from the fourth heat exchanger 308.2 for the first temperature increase of the cold water 338. The coupling includes a valve V307. The valve V307 is designed as a distribution valve, whereby the residual heat of the fourth heat exchanger 308.4 is partially provided at the primary inlet 304a.2 and/or partially provided at the primary inlet 309a.2, depending on the position of the distribution valve V307. Depending on the temperature and exergy ratio, the primary outlet 308a.4 is introduced either in part or completely into the primary inlet 309a.2 and/or into the primary inlet 304a.2. The goal is always to achieve optimal exergetic performance. This means that the heat from the flow of the district heating 320 is transferred as optimally as possible to the cold water 338, the service water flow 334b, the flow 332b and the course 336b in a temperature sequence. In other words, the heat of the return flow of the district heating 330 is used in such a way that a minimum volume flow results with a maximum temperature spread between the flow and return flow of the district heating.

The secondary entry 308b.2 is coupled to the return 332a. Furthermore, the secondary outlet 308b.4 is coupled to the flow 332b.

Furthermore, the transfer station 300 includes a temperature increase of the low-temperature heating circuit 336 by means of the fifth heat exchanger 309, which partially uses the residual heat of the fourth heat exchanger 308.4 and/or a residual heat of the third heat exchanger 306.6.

The fifth heat exchanger 309 includes a primary side 309a and a secondary side 309b. The primary side 309a and the secondary side 309b are set up to transfer heat from the primary side 309a to the secondary side 309b. Furthermore, the primary side 309a includes a primary inlet 309a.2 and a primary outlet 309a.4, whereby heat flows into the primary inlet 309a.2, then partially releases the heat to the primary side 309a and residual heat from the fifth heat exchanger flows out at the primary outlet 309a.4. Furthermore, the secondary side 309a includes a secondary inlet 309b.2 and a secondary outlet 309b.4, whereby heat flows into the secondary inlet 309b.2, then partially absorbs the heat of the primary side 309a and partially flows out heat at the secondary outlet 309b.4.

The primary entry 309a.2 is coupled to the primary exit 308a.4. The primary exit 309a.4 is coupled to the primary entry 304a.2. The second heat exchanger 304 thus partially uses the residual heat of the fifth heat exchanger 309.2 for the first temperature increase of the cold water 338.

Furthermore, the primary inlet 309a.2 is coupled to the primary outlet 306a.4. The fifth heat exchanger 309 thus partially uses the residual heat of the third heat exchanger 306.6 to increase the temperature of the low-temperature heating circuit 336. The coupling includes a valve V306. The valve V306 is designed as a distribution valve, whereby residual heat from the primary outlet of the third heat exchanger 306, depending on the position of the distribution valve V306, partially provides the residual heat of the third heat exchanger 306.2 at the primary inlet 308a.2 and/or partially provides the residual heat of the third heat exchanger 306.6 at the primary inlet 309a .2 provides. The provision takes place depending on the temperature and exergy ratio. The goal is always to achieve optimal exergetic performance. This means that the heat from the flow of the district heating 320 is transferred as optimally as possible to the cold water 338, the service water flow 334b, the flow 332b and the course 336b. In other words, the heat of the return of the district heating 330 is optimally minimized, see also [0173].

Furthermore, the primary outlet 309a.4, the primary outlet 306a.4 and the primary outlet 308a.4 are coupled to the return of the district heating 330. This means that some of the residual heat from the fifth heat exchanger 309.2 and/or some of the residual heat from the third heat exchanger 306.4 and/or some of the residual heat from the fourth heat exchanger 308.2 is introduced into the return flow of the district heating 330. The coupling includes a valve V308. Completely or partially bypassing the second heat exchanger 304 using the valve V308 can make sense if the temperature of the residual heat of the fifth heat exchanger 309.2 and that of the residual heat of the third heat exchanger 306.4 is above 60 ° C and there is therefore a risk of calcification of the second heat exchanger 304 . Furthermore, completely or partially bypassing the second heat exchanger 304 using the valve V308 can make sense if the temperature of the residual heat of the first heat exchanger 302.2 has a higher temperature than the temperature of the residual heat of the fifth heat exchanger 309.2. In some embodiments Furthermore, completely or partially bypassing the second heat exchanger 304 by means of the valve V308 can make sense if the temperature of the residual heat of the first heat exchanger 302.2 has a higher temperature than a mixed or averaged temperature of the residual heat of the first heat exchanger 302.2 and/or the residual heat of the third heat exchanger 306.4 and/or the residual heat of the fourth heat exchanger 308.2 and/or the residual heat of the fifth heat exchanger 309.2. A complete or partial redirection of the second heat exchanger 304 can affect the exergetic performance of the entire system; the continuous control of the valve 308 serves to find the exergetic optimal working point.

The secondary entry 309b.2 is coupled to the return 336a. The secondary outlet 309b.4 is coupled to the flow 336b.

The coupling of the heat exchanger 308 and 309, as described above, corresponds to a series connection. The series connection is a temperature series connection.

The third secondary-side heat removal stream 236, which is a low-temperature useful heat stream and experiences the temperature increase by means of the fifth heat exchanger, uses the residual heat of the third heat exchanger, wherein in one exemplary embodiment the residual heat has a temperature of 60 ° C or higher, since by means of the third heat exchanger in the exemplary embodiment the second secondary-side heat dissipation stream 334 is heated to 60 ° C. The residual heat in the exemplary embodiment is therefore sufficient to increase the temperature of the third secondary-side heat dissipation stream. In another exemplary embodiment, residual heat from the third heat exchanger is not sufficient to increase the temperature of the low-temperature useful heat flow 236, so that heat from the primary-side heat supply flow 320c is provided by means of the distribution valve V303, which is provided to the fifth heat exchanger via the fourth heat exchanger, 308.4. In another exemplary embodiment, residual heat from the third heat exchanger 306.6 is not sufficient for raising the temperature of the low-temperature useful heat flow 236, so that the fifth heat exchanger is further (directly) coupled to the primary-side heat supply flow (not shown) and thus for raising the temperature of the low-temperature useful heat flow 236 by means of of the fifth heat exchanger at least partially uses heat from the primary-side heat supply flow.

The transfer station 300 further includes a controller 340 and sensors S301, S302 to S319. The sensor S301 is placed at the primary inlet 302a.2. The sensor S302 is placed at the primary outlet 302a.4. The sensor S303 is placed at the secondary inlet 302b.2. The sensor S304 is placed at the primary outlet 302b.4. The sensor S305 is placed at the primary inlet 306a.2. The sensor S306 is placed at the primary outlet 306a.4. The sensor S307 is placed at the secondary inlet 306b.2. The sensor S308 is placed at the secondary outlet 306b.4. The sensor S309 is placed at the primary inlet 308a.2. The sensor S310 is placed at the primary inlet 308a.2 of the fifth heat exchanger. The sensor S311 is placed at the secondary outlet 308b.4. The sensor S312 is placed at the primary outlet 309a.4. The sensor S313 is placed at the secondary outlet 309b.4. The sensor S314 is placed at the primary inlet 304a.2. The sensor S315 is placed at the primary outlet 304a.4. The sensor S316 is placed at the secondary inlet 304b.2. The sensor S317 is placed on the return line of the district heating 330. The sensor S318 is placed at the flow of the district heating 320. The sensor S319 is placed at the primary outlet 308a.4 of the fourth heat exchanger 308.

The sensors are temperature sensors. In one embodiment, the sensors are temperature and volume flow sensors and/or pressure sensors for measuring temperature and heat flow and volume flow and/or the hydrodynamic and/or hydrostatic pressure of the heat transfer medium. In one exemplary embodiment, the sensors are each a device whereby a predetermined temperature and/or heat flow and/or volume flow and/or pressure is set and/or transmitted. Setting means, for example, a setting of a predetermined value, for example using an adjusting wheel or display. By transfer is meant a transmission of a predetermined value, for example the temperature of the flow of the district heating 320 by the district heating operator or, for example, a predetermined temperature of the flow 332b by a heating controller or a heating control.

The sensors are communicatively connected to the controller 340. The individual valves of the transfer station 300 each comprise a machine. The machine of a valve is set up to influence the valve position of the valve. The machine is, for example, an electric actuator. The valves of the transfer station 300 are communicatively connected to the controller 340. Furthermore, the machines in the individual valves (and thus the valve position) are controlled by means of the control 340. The pumps P 301, P302 and P303 are controlled by means of the control 340. The control of the individual pumps includes the control of the speed or volume flow of the Pump. The speed is proportional to the volume flow and heat flow induced by the pump.

A determination of the exergetically optimal operating point of the transfer station 300 is achieved by means of the controller 340. Finding the exergetically optimal working point represents an optimization. The optimization includes a temperature of the district heating return 330 to be minimized and/or a heat flow of the district heating return 330 to be minimized and a mathematical and/or physical system of the transfer station 300. Furthermore, the Optimization includes one or more of the secondary conditions described below, wherein the transfer station according to the invention is not limited to the following secondary conditions.

A secondary condition is the said hygiene regulations, according to which the temperature in the flow of the service water circuit 334b should be at least 60 °C. The temperature is determined by the sensor S308.

Another additional condition is the said hygiene regulation, according to which the temperature in the return of the service water circuit 334a should be at least 55 °C. The temperature is determined by the sensor S307.

Another additional condition is the said hygiene regulation, according to which a 16-hour circulation of the service water in the service water circuit 334 per day is required. The 16-hour circulation is ensured by the P303 pump.

Another additional condition is the minimization of calcification of the first heat exchanger 302. Accordingly, the second temperature increase of the cold water 338 should take place at a minimum temperature. The temperatures are determined by the sensors S301, S302, S303 and/or S304.

Another additional condition is the minimization of calcification of the second heat exchanger 304. Accordingly, the first temperature increase of the cold water 338 should take place at a minimum temperature. The temperatures are determined by the sensors S314, S315, S316 and/or S303.

Another additional condition is the minimization of calcification of the third heat exchanger 306. As a result, the temperature increase of the service water flow 334a should take place at a minimum temperature. The temperatures are determined by the sensors S306, S305, S307 and/or S308.

Another additional condition is the temperature of the flow 332b. As a result, the temperature increase of the high-temperature heating circuit 332 by means of the fourth heat exchanger should be corresponding to the temperature of the flow 332b. The corresponding temperature increase of the high-temperature heating circuit 332 is determined by the sensors S309, S319 and/or S311. Alternatively, the temperature of the flow 332b can be predetermined.

Another additional condition is the temperature of the flow 336b. As a result, the temperature increase of the low-temperature heating circuit 336 by means of the fifth heat exchanger should be corresponding to the temperature of the flow 336b. The corresponding temperature increase of the low-temperature heating circuit 336 is determined by the sensors S310, S312 and/or S313. Alternatively, the temperature of the flow 336b can be predetermined.

Another additional condition is that heat is always transferred from the primary side to the secondary side using the individual heat exchangers.

Another additional condition is the specification of the efficiency of the individual heat exchangers of the transfer station 300. This means that, for example, with a given temperature increase, the necessary temperature at the primary inlet can be determined using the heat exchanger.

A further secondary condition is the temperature and/or a heat flow of the flow of the district heating 320, which determines the maximum temperature and/or a maximum heat flow in the transfer station 300. The temperature and/or the heat flow of the flow of the district heating 320 is determined by sensor S318.

The optimization itself is ensured by well-known optimization algorithms, which find the exergetically optimal working point with the additional conditions. For this purpose, the controller 340 includes a controller and/or a processor unit with a memory unit. The controller and/or the processor unit includes receiving sensor signals from the sensors, processing the sensor signals, solving the optimization problem and transmitting control instructions to the valves and pumps. The storage unit includes storage of the sensor signals and/or predetermined temperatures and/or the optimization algorithm and/or parameters of the optimization algorithm and/or a result of the optimization algorithm and/or controller and/or control variables.

A result of the optimization includes the first temperature increase of the cold water 338 by means of the second heat exchanger 304, the second temperature increase of the cold water 338 by means of the first heat exchanger 302, the temperature increase of the service water flow 334 by means of the third heat exchanger, the temperature increase of the high-temperature heating circuit 332 by means of the fourth heat exchanger, the Temperature increase of the low-temperature heating circuit 336 by means of the fifth heat exchanger, a position of the distribution valves V301, V302, V303, V304, V305, V306, V307, V308 and V309 and a volume flow of the pumps P301, P302, P303.

An advantage of the transfer station 300 is the functional interaction of the heat exchangers 302, 306, 308 and 309, which together realize the five-stage transfer station 300. For example, the functional interaction results in a two- or three-stage increase in the temperature of the cold water before it is introduced into the process water circuit, whereby the heat from the primary-side heat supply flow is used optimally in terms of energy. Furthermore, this minimizes the risk of calcification of the heat exchangers.

Another advantage of the transfer station 300 is the division of a heating circuit and a grouping of heating circuits according to their flow temperatures. Accordingly, in one exemplary embodiment, the transfer station 300 includes a high- and a low-temperature heating circuit, so that the heat supply flow on the primary side is used optimally in terms of energy.

Another advantage of the transfer station 300 is the functional interaction of the residual heat of the individual heat exchangers 302, 306, 308 and 309, so that residual heat from one heat exchanger can be used by another or several other heat exchangers. For example, the second heat exchanger 304 partially uses the residual heat of the first heat exchanger 302.

A further advantage of the transfer station 300 consists in the functional interaction of the heat exchangers 302, 306, 308 and 309, in the functional interaction of the residual heat of the individual heat exchangers 302, 306, 308 and 309 and in the functional interaction of the sensors and pumps of the transfer station 300. This eliminates the need for a classification of operating states of the transfer station 300, for example in the said water supply operation or circulation operation. Rather, simultaneous operation of the water supply operation and the circulation operation is possible.

A further advantage of the transfer station 300 is the comprehensive control and/or regulation option of the heat from the primary-side heat supply flow to the primary-side heat supply flow, the first, second and third secondary-side heat removal flow. The said control and/or regulation option is implemented using the valves and pumps of the transfer station 300. This means that the exergetically optimal working point can also be achieved under changing consumer behavior, such as time-variant heat provision of the primary-side heat supply stream and/or time-variant heat demand of the primary-side heat supply stream and/or time-variant heat demand of the first, second and/or third secondary-side heat removal stream.

4 shows a transfer station 400. The transfer station 400 corresponds to the transfer station 300 3 . Furthermore, the transfer station 400 is shown for a point in time and at an exergetically optimal working point. This exergetically optimal working point is indicated by temperatures in 4 shown.

In this exemplary embodiment, the flow of the district heating 320 has a temperature of 71 ° C. The district heating return has a temperature of 10°C. The cold water 338, before it is introduced into the service water circuit 334, has a temperature of 9 ° C.

The first temperature increase of the cold water 338 takes place from 9 ° C to 28 ° C by means of the second heat exchanger 304. The second temperature increase of the cold water 338 takes place from 28 ° C to 40 ° C by means of the first heat exchanger 302. The cold water 338 after the first and second temperature increase does not have the temperature of 60 ° C from the hygiene regulations for introduction into the service water flow 334b. The cold water 338 is thus introduced into the service water return 334a, which has a temperature of 55 ° C before this introduction. The position of valve V304 is accordingly.

The mixed or average temperature of the domestic hot water return 334a and the cold water 338 is 48°C. The temperature of the process water circuit 334 is raised from 48°C to 60°C by means of the third heat exchanger 306. This is accompanied by a third increase in the temperature of the cold water 338 from 40°C to 60°C.

The temperature of the high-temperature heating circuit 332 is raised from 35 ° C to 48 ° C by means of the fourth heat exchanger 308. The temperature of the low-temperature heating circuit 336 is raised from 28 ° C to 32 ° C by means of the fifth heat exchanger 309.

For the second temperature increase of the cold water 338, heat is partly used from the flow of the district heating 320a and partly the residual heat from the first heat exchanger 302.4 by means of valve V301. The position of the valve V301 is therefore such that a temperature of 41 ° C is provided at the primary inlet 302a.2. The second temperature increase of the cold water 338 transfers heat from the primary side 302a to the secondary side 302b in such a way that a temperature at the primary outlet of 29 ° C results. This results in an average temperature difference with respect to the primary side 302a and the secondary side 302b of 1°C.

To raise the temperature of the domestic water circuit 334, heat is partly used from the flow of the district heating 320b and partly the residual heat from the third heat exchanger 306.8 by means of valve V302. The position of the valve V302 is therefore that a temperature of 61 ° C is provided at the primary inlet 306a.2. By increasing the temperature of the service water circuit 334, heat is transferred from the primary side 306a to the secondary side 306b in such a way that a temperature of 49 ° C is present at the primary outlet. This results in an average temperature difference with respect to the primary side 302a and the secondary side 302b of 1°C.

To increase the temperature of the high-temperature heating circuit 332, the residual heat from the third heat exchanger 306.2 is used by means of valve V303, valve 305 and valve V306. The position of valve V303 is therefore closed. The position of the valves V305 and V306 provides the residual heat from the third heat exchanger to the primary inlet 308a.2.

The temperature increase of the low-temperature heating circuit 336 can be realized by means of the valves V307 and V306, i.e. with the residual heat from the fourth heat exchanger 306.2. The valves V307 and V306 can be set so that they provide the residual heat from the fourth heat exchanger to the primary inlet 309a.2.

For the first temperature increase of the cold water 338, the residual heat of the fifth heat exchanger 309.2 and the residual heat of the first heat exchanger 302.2 are used by means of the valves V309 and V308. The position of the valve V309 is therefore set such that the residual heat from the first heat exchanger is not introduced directly into the return of the district heating 330. The position of the valve V308 is therefore set such that the residual heat from the fifth heat exchanger is not introduced directly into the return of the district heating 330.

5 shows a flowchart of an exemplary embodiment of a method 600 for transferring heat using a transfer station. In 5 An exemplary embodiment of a method for transferring heat according to one aspect of the invention is shown, which is carried out, for example, in a transfer station 100, 200, 300, 400. The method for transferring heat in a transfer station includes steps 604, 606, 608, 610, 612 and 614.

Step 604 includes first raising a temperature of a secondary-side heat supply stream before it is introduced into a second secondary-side heat removal stream. The first increase in the temperature of the secondary-side heat supply flow takes place by means of a second heat exchanger, which partially uses residual heat from a fourth heat exchanger and/or partially uses residual heat from the first heat exchanger.

Step 606 includes a second increase in the temperature of the secondary-side heat supply stream before it is introduced into a second secondary-side heat removal stream. The second increase in the temperature of the secondary-side heat supply stream occurs after the first increase in the temperature of the secondary-side heat supply stream. The second increase in the temperature of the secondary-side heat supply flow takes place by means of a first heat exchanger, which partially uses a primary-side heat supply flow for this purpose.

Step 608 includes introducing the secondary-side heat supply stream into the second secondary-side heat removal stream. The introduction takes place after the first and second temperature increase of the secondary-side heat supply flow.

Step 609 is optional and includes a third increase in the temperature of the secondary heat supply stream. In one embodiment of the method 600, the secondary-side heat supply stream has not reached a target temperature after its first and second temperature increase. The secondary-side heat supply flow thus experiences the third temperature increase by means of a third heat exchanger. If, in another exemplary embodiment of method 600, the secondary-side heat supply flow has reached a target temperature after its first and second temperature increase, step 609 is not necessary.

The step sequence 604, 606 and 608 (and 609) are repeated successively.

Step 610 includes increasing a temperature of a second secondary side heat source supply current by means of the third heat exchanger, which partially uses the heat supply flow on the primary side.

Step 612 includes circulating the second secondary side heat removal stream.

Steps 610 and 612 are repeated successively and are also independent of the step sequence 604, 606, 608 (and 609).

Step 614 includes raising a temperature of a first secondary-side heat dissipation stream by means of a fourth heat exchanger, which partially uses the primary-side heat inflow and/or partially uses the residual heat of the third heat exchanger.

Step 614 is repeated successively. Furthermore, step 614 is independent of step sequence 604, 606, 608 (and 609) and step sequence 610,612.

Due to the independence of the step sequence 604, 606, 608 (and 609) and the step sequence 610,612 and step 614, there is no need to distinguish between the known circulation operation and the known water supply operation, as in DE 10 210 019 727 B4 is described. The method 600 has the advantageous effect that the circulation operation and the water supply operation can run in parallel. This eliminates the need to switch between these two operating modes. Furthermore, the heat losses associated with each individual switchover are eliminated.

List of reference symbols:

100, 200, 300, 400

transfer station

102, 104, 106, 108, 202, 204, 206, 208, 209, 302, 304, 306, 308, 309

Heat exchanger

102.2, 106.2, 108.2, 202.2, 202.4, 206.2, 206.4, 206.8, 208.2, 208.4, 208.6, 209.2, 302.2, 302.4, 306.2, 306.4, 306.8, 30 8.2, 308.4, 309.2

residual heat

120, 220, 320

primary side heat supply flow

120a, 120b, 120c, 220a, 220b, 220c, 320a, 320b, 320c

partial heat supply flow on the primary side

132, 232, 332

First secondary-side heat dissipation stream

134, 234, 334

Second secondary-side heat dissipation stream

236, 336

Third secondary heat dissipation stream

138, 238, 338

secondary side heat supply flow

P301, P302, P302

pump

S301, S302, ..., S319

sensor

V301, V302, ..., V309

distribution valve

340

steering

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102010019727 B4 [0003, 0035]
• DE 102008038617 A1 [0004]
• DE 10210019727 B4 [0219]

Claims (12)

Comprising a transfer station - a heat supply flow on the primary side, - a first and a second secondary-side heat dissipation stream, - a secondary heat supply flow and - a first, second, third and fourth heat exchanger; where - the secondary-side heat supply stream, before it is introduced into the second secondary-side heat removal stream, experiences a first temperature increase and a second temperature increase, the first temperature increase occurring before the second temperature increase; - the second temperature increase is carried out by means of the first heat exchanger, which partially uses the heat inflow on the primary side; - the first temperature increase is carried out by means of the second heat exchanger, which partially uses residual heat from the fourth heat exchanger and/or partially uses residual heat from the first heat exchanger; - a temperature increase of the second secondary-side heat dissipation flow takes place by means of the third heat exchanger, which partially uses the primary-side heat inflow for this purpose; and - a temperature increase of the first secondary-side heat dissipation flow takes place by means of the fourth heat exchanger, which partially uses the residual heat of the third heat exchanger and/or partially uses the primary-side heat inflow. The transfer station after Claim 1 , wherein - the first temperature increase is carried out by means of the second heat exchanger, which partially uses the residual heat of the fourth heat exchanger and/or partially uses the residual heat of the first heat exchanger and/or partially uses the residual heat of the third heat exchanger; and - the second temperature increase takes place by means of the first heat exchanger, which partially uses the heat inflow on the primary side and/or partially uses the residual heat of the first heat exchanger. The transfer station according to one of the preceding claims, further comprising - a fifth heat exchanger, and - a third secondary-side heat dissipation stream, where - the temperature of the third secondary-side heat dissipation stream is increased by means of the fifth heat exchanger, which partially uses the residual heat of the fourth heat exchanger and/or partially uses the residual heat of the third heat exchanger; - the first temperature increase is carried out by means of the second heat exchanger, which partly uses the residual heat of the fourth heat exchanger and/or partly the residual heat of the first heat exchanger and/or partly the residual heat of the third heat exchanger and/or a residual heat of the fifth heat exchanger. The transfer station according to one of the preceding claims, wherein - the secondary-side heat supply stream experiences a third temperature increase after being introduced into the second secondary-side heat removal stream; where - the third temperature increase occurs with the temperature increase of the second secondary-side heat dissipation stream; and - the third temperature increase occurs after the second temperature increase. The transfer station according to one of the previous patent claims, if dependent on Claim 3 , whereby - the primary-side heat supply stream is a flow stream of a district heating network or a local heating network; - the first secondary-side heat dissipation stream is a first secondary-side useful heat circuit; - the third secondary-side heat dissipation stream is a second secondary-side useful heat circuit; - the second secondary-side heat dissipation stream is a service water circuit; - The secondary heat supply flow is water from outside the process water circuit. The transfer station after Claim 5 , whereby the process water is circulated in the service water circuit by means of a pump and with the introduction of water from outside the service water circuit into the service water circuit. The transfer station according to one of the preceding claims, wherein the primary-side heat supply flow is used for the second temperature increase of the secondary-side heat supply flow by means of the first heat exchanger and at the same time the primary-side heat supply flow is used for the temperature increase of the second secondary-side heat removal flow by means of the third heat exchanger. The transfer station after Claim 5 or 6 , where - the domestic water cycle is a drinking water cycle; - the first secondary-side useful heat circuit is a first heating circuit; - the second secondary-side useful heat circuit is a second heating circuit; whereby - a return temperature of the first heating circuit is higher than a return temperature of the second heating circuit. The transfer station according to one of the preceding claims, wherein the second heat exchanger is a heat exchanger and a heat storage. The transfer station according to one of the previous patent claims as far as dependent on one of the Claims 2 or 3 , wherein the second heat exchanger is designed to store partially the residual heat of the fourth heat exchanger and/or partially the residual heat of the first heat exchanger and/or partially the residual heat of the third heat exchanger and/or the residual heat of the fifth heat exchanger. The transfer station according to one of the preceding claims, wherein the second heat exchanger is a tube bundle heat exchanger. A method for transferring heat in a transfer station comprising - a first and a second increase in the temperature of a secondary-side heat supply stream, wherein - the first and second raising of the temperature of the secondary-side heat supply stream before it is introduced into the second secondary-side heat removal stream; - the first increase in the temperature of the secondary-side heat supply stream takes place before the second increase in the temperature of the secondary-side heat supply stream; - the second increase in the temperature of the secondary-side heat supply flow takes place by means of a first heat exchanger, which partially uses a primary-side heat supply for this purpose; - the temperature of the secondary-side heat supply stream is first raised by means of a second heat exchanger, which partially uses residual heat from a fourth heat exchanger and/or partially uses residual heat from the first heat exchanger; - the temperature of a second secondary-side heat dissipation stream is raised by means of the third heat exchanger, which partially uses the primary-side heat inflow for this purpose; and - The temperature of a first secondary-side heat dissipation stream is raised by means of the fourth heat exchanger, which partially uses the primary-side heat inflow and/or partially uses the residual heat of the third heat exchanger.

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