Method and device for transferring heat

Abstract

The disclosure relates to a transfer station comprising a primary-side heat input flow, a first and a second secondary-side heat output flow, a secondary-side heat input flow, and a first, second, third, and fourth heat exchanger, wherein the secondary-side heat input flow undergoes a first temperature increase and a second temperature increase before being introduced into the second secondary-side heat output flow, wherein the first temperature increase occurs before the second temperature increase, the second temperature increase is carried out by means of the first heat exchanger, which partially utilizes the primary-side heat input for this purpose, the first temperature increase is carried out by means of the second heat exchanger, which partially utilizes residual heat from the fourth heat exchanger and / or partially residual heat from the first heat exchanger, and a temperature increase of the second secondary-side heat output flow is carried out by means of the third heat exchanger.which partially utilizes the primary-side heat inflow for this purpose; and a temperature increase of the first secondary-side heat discharge flow is carried out by means of the fourth heat exchanger, which partially utilizes the residual heat from the third heat exchanger and / or partially the primary-side heat inflow for this purpose. Furthermore, the disclosure relates to a method for transferring heat in a transfer station comprising a first and a second temperature increase of a secondary-side heat input flow, wherein the first and the second temperature increase of the secondary-side heat input flow occurs before it is introduced into the second secondary-side heat discharge flow, the first temperature increase of the secondary-side heat input flow occurs before the second temperature increase of the secondary-side heat input flow, and the second temperature increase of the secondary-side heat input flow is carried out by means of a first heat exchanger.which partially utilizes a primary-side heat inflow, the initial increase in the temperature of the secondary-side heat supply flow is achieved by means of a second heat exchanger, which partially utilizes residual heat from a fourth heat exchanger and / or partially residual heat from the first heat exchanger.

Description

Field of invention

[0001] This disclosure relates generally to the field of heat transfer technology and in particular to a transfer station for the transfer of (district) heat and a method for transferring heat in a transfer station. Background of the invention

[0002] In general, devices for transferring heat and corresponding methods for transferring heat are known, e.g. in heat supply networks for residential or industrial plants.

[0003] German patent application DE 10 2010 019 727 B4 discloses a method for transferring heat and a heat transfer station. Among other things, it describes a two-stage and a three-stage heat transfer station, in which heat from a primary-side heat supply circuit is transferred to a secondary-side useful heat circuit and a secondary-side domestic hot water circuit. Furthermore, DE 10 2010 019 727 B4 distinguishes between circulation operation and water supply operation, and the operation of the heat transfer station requires a change between circulation operation and water supply operation (and vice versa) over the course of a day.

[0004] DE 10 2008 038 617 A1 concerns methods and devices for heat utilization. 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.

[0005] The article "District heating transfer station with cascade. Stadtwerke Rosenheim expands district heating 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 jet pump.

[0006] Document DE 27 30 406 Al discloses devices and methods for increasing the transport capacity of district heating networks.

[0007] 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

[0008] From a first perspective, a transfer station comprises a primary-side heat input flow, a first and a second secondary-side heat output flow, a secondary-side heat input flow, and a first, second, third, and a fourth heat exchanger.

[0009] The term "may" is used to denote, in particular, optional features of the invention. Accordingly, there is an embodiment of the invention that includes the respective feature or features.

[0010] The secondary-side heat input flow can undergo a first temperature increase and a second temperature increase before it is introduced into the second secondary-side heat output flow.

[0011] The first temperature increase can occur before the second. In other words, the secondary-side heat input flow is successively subjected first to the first temperature increase and then to the second. A heat input or output flow can be characterized by having a predetermined or natural spatial flow direction. The flow direction can be steady in time and / or space. The first temperature increase can occur before the second.

[0012] The temperature of a heat flow, and temperature in general, can be an average temperature over a cross-section of the heat flow, or the maximum or minimum temperature at 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 single point in time.

[0013] The term "introduction" refers to the merging of the previously spatially separated secondary-side heat input flow with the second secondary-side heat output flow. Depending on the media of the secondary-side heat input flow and / or the second secondary-side heat output flow, this can result in a homogeneous or heterogeneous phase after introduction. The secondary-side heat input flow can be a volumetric flow of water in a liquid phase, and the second secondary-side heat output flow can also be a volumetric flow of water in a liquid phase. Both volumetric flows can mix to form a homogeneous phase after introduction.

[0014] The second temperature increase can be achieved using the first heat exchanger. The first heat exchanger can partially utilize the primary-side heat input for this purpose. The first heat exchanger can utilize the primary-side heat input and / or partially residual heat from the first heat exchanger. The first heat exchanger can utilize the primary-side heat input and / or partially residual heat from the first heat exchanger and / or partially residual heat from the third heat exchanger. The first heat exchanger can utilize partially residual heat from the first heat exchanger and / or partially residual heat from the third heat exchanger.

[0015] Residual heat from a heat exchanger can be waste heat from the heat exchanger itself. It can be the heat that the heat exchanger does not utilize for heat transfer. The residual heat from one heat exchanger can be used by another heat exchanger. Residual heat from a heat exchanger can also result from a predetermined limit on the maximum heat flow that can be transferred through the heat exchanger. Finally, residual heat from a heat exchanger can arise from the second law of thermodynamics. In heat transfer via a heat exchanger, the medium with a higher temperature releases heat to a medium with a lower temperature. Therefore, the transferable heat flow is primarily a function of the temperature difference between the two media. The smaller the temperature difference, the lower the transferable heat flow.

[0016] Raising the temperature of a medium using a heat exchanger can occur through mixing or transferring heat from another medium, where the other medium has a higher temperature than the medium being heated. Raising the temperature of a medium using a heat exchanger can occur through the transmission of heat from a higher-temperature medium to the lower-temperature medium. Temperature raising in a heat exchanger can occur through thermal radiation from a higher-temperature medium to a lower-temperature medium. Temperature raising in a heat exchanger can also occur through the transfer of heat from one medium to another via a phase change. Finally, temperature raising in a heat exchanger can occur through the transfer of heat from one medium to another via a phase change, and furthermore, the other medium can also undergo a phase change.This means that one medium releases heat through a phase change, while the other medium absorbs heat through a (different and "reverse") phase change.

[0017] The first temperature increase can be achieved using the second heat exchanger. The second heat exchanger can utilize residual heat from the fourth heat exchanger and / or residual heat from the first heat exchanger for this purpose. Alternatively, the second heat exchanger can utilize residual heat from the fourth heat exchanger, residual heat from the first heat exchanger, and / or residual heat from the third heat exchanger for this purpose.

[0018] The temperature of the second secondary-side heat discharge flow can be increased using the third heat exchanger. The third heat exchanger can partially utilize the primary-side heat input for this purpose. Alternatively, the third heat exchanger can utilize either the primary-side heat input and / or residual heat from the third heat exchanger.

[0019] The temperature of the first secondary-side heat discharge flow can be increased using the fourth heat exchanger. This fourth heat exchanger can utilize either the primary-side heat input or the residual heat from the third heat exchanger.

[0020] The transfer station can include a fifth heat exchanger. The transfer station can include a third secondary-side heat removal flow.

[0021] The temperature of the third secondary-side heat transfer stream can be increased using the fifth heat exchanger. The fifth heat exchanger can utilize residual heat from the fourth heat exchanger and / or residual heat from the third heat exchanger for this purpose.

[0022] The first temperature increase can be achieved using the second heat exchanger, which partially utilizes the residual heat from the first heat exchanger and / or partially the residual heat from the third heat exchanger and / or partially the residual heat from the fourth heat exchanger and / or partially residual heat from the fifth heat exchanger.

[0023] The secondary-side heat input flow can undergo a partial third temperature increase after being introduced into the second secondary-side heat output flow. This third temperature increase can occur simultaneously with the temperature increase of the second secondary-side heat output flow, or it can occur after the second temperature increase.

[0024] The primary-side heat supply flow can be a feed flow of a district heating network or a local heating network.

[0025] The first secondary-side heat dissipation flow can be a first secondary-side useful heat circuit. The first secondary-side useful heat circuit can be a heating circuit.

[0026] The third secondary-side heat dissipation flow can be a second secondary-side useful heat cycle.

[0027] The second secondary-side heat dissipation flow can be a domestic hot water circuit.

[0028] The secondary-side heat supply flow can be water from outside the domestic hot water circuit. This water from outside the domestic hot water circuit can be potable water.

[0029] Domestic water can be circulated within a domestic water circuit using a pump. Circulation of domestic water within a domestic water circuit can be achieved using a pump and by introducing water from outside the domestic water circuit into the domestic water circuit.

[0030] The second temperature increase of the secondary-side heat input flow can occur simultaneously with the temperature increase of the second secondary-side heat output flow. The second temperature increase can occur simultaneously with the temperature increase of the first and / or the third secondary-side heat output flow. The second temperature increase of the secondary-side heat input flow can occur simultaneously with the temperature increase of the first and / or the second and / or the third secondary-side heat output flow.

[0031] The primary-side heat input flow can be used to raise the temperature of the first secondary-side heat output flow via the fourth heat exchanger, and simultaneously, the primary-side heat input flow can be used to raise the temperature of the second secondary-side heat output flow via the third heat exchanger. The primary-side heat input flow can also be used to raise the temperature of the first secondary-side heat output flow via the fourth heat exchanger, and simultaneously, the primary-side heat input flow can be used to raise the temperature of the domestic hot water circuit via the third heat exchanger.The primary-side heat input flow can be used for the second temperature increase of the secondary-side heat input flow by means of the first heat exchanger and / or simultaneously the primary-side heat input flow can be used for the temperature increase of the first secondary-side heat discharge flow by means of the fourth heat exchanger and / or simultaneously the primary-side heat input flow can be used for the temperature increase of the second secondary-side heat discharge flow by means of the third heat exchanger and / or simultaneously the primary-side heat input flow can be used for the temperature increase of the third secondary-side heat discharge flow by means of the fifth heat exchanger.

[0032] The domestic water cycle can be a drinking water cycle.

[0033] The first secondary-side heat recovery circuit can be a primary heating circuit. This primary heating circuit can include a radiator and underfloor heating. It can also include underfloor heating and / or thermally activated building components, or it can include convection heating. The convection heating component can be a radiator.

[0034] The second secondary-side heat recovery circuit can be a second heating circuit. This second secondary-side heat recovery circuit can include underfloor heating and / or thermally activated building components.

[0035] The return temperature of the first secondary-side useful heat circuit can be higher than the return temperature of the second secondary-side useful heat circuit.

[0036] The heat exchangers of the transfer station can each be a heat storage unit and / or a heat exchanger. The heat exchangers of the transfer station can be plate heat exchangers, spiral heat exchangers, or shell and tube heat exchangers. The heat exchangers can be recuperators and / or regenerators (see also DE 10 2010 019 727 B4).

[0037] The heat exchangers of the transfer station can each comprise a primary and a secondary side. The primary side can transfer heat to the secondary side of the heat exchanger. The primary side can store heat. The primary side can store heat before partially transferring it to the secondary side.

[0038] The first heat exchanger can further comprise a temperature difference between its primary and secondary sides. This temperature difference can range from 1 to 10 Kelvin (or higher), preferably 1 Kelvin. The temperature difference can also be a mean temperature difference of the first heat exchanger.

[0039] The second heat exchanger can further comprise a temperature difference between its primary and secondary sides. This temperature difference can range from 1 to 40 Kelvin (or higher), preferably 1 Kelvin. The temperature difference can also be a mean temperature difference of the second heat exchanger.

[0040] The third heat exchanger can further comprise an average temperature difference between its primary and secondary sides. This temperature difference can range from 1 to 30 Kelvin (or higher), preferably 1 Kelvin. The temperature difference can also be an average temperature difference of the third heat exchanger.

[0041] The fourth heat exchanger can further comprise an average temperature difference between its primary and secondary sides. This temperature difference can range from 1 to 40 Kelvin (or higher), preferably 1 Kelvin. The temperature difference can also be an average temperature difference of the fourth heat exchanger.

[0042] The fifth heat exchanger can further comprise an average temperature difference between its primary and secondary sides. This temperature difference can range from 1 to 30 Kelvin (or higher), preferably 1 Kelvin. The temperature difference of the fourth heat exchanger can be its average temperature difference.

[0043] The mean temperature difference can be a time-averaged temperature difference and / or a geometric averaging over the heat transfer surface of a heat exchanger. The time-averaged temperature difference can represent the steady-state heat flows in the heat exchanger.

[0044] The primary side of each heat exchanger at the transfer station can include a primary inlet and a primary outlet.

[0045] The secondary side of each heat exchanger in the transfer station can include a secondary inlet and a secondary outlet.

[0046] The primary inlet of the first heat exchanger can be coupled to the primary-side heat input flow. The primary inlet of the first heat exchanger can be coupled to the primary-side heat input flow and the primary outlet of the first heat exchanger. The primary inlet of the first heat exchanger can be coupled to the primary-side heat input flow and / or the primary outlet of the first heat exchanger and / or the primary outlet of the third heat exchanger.

[0047] The primary inlet of the second heat exchanger can be coupled to the primary outlet of the fourth and / or 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.

[0048] The primary outlet of the second heat exchanger is connected to a primary-side heat removal flow.

[0049] 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 both the primary-side heat supply flow and the primary outlet of the third heat exchanger.

[0050] The primary inlet of the fourth heat exchanger can be coupled to the primary-side heat input 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 input flow and the primary outlet of the third heat exchanger and the primary outlet of the fourth heat exchanger.

[0051] 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.

[0052] The secondary inlet of the first heat exchanger can be coupled to the secondary-side heat supply flow.

[0053] The secondary inlet of the second heat exchanger can be coupled to the secondary outlet of the first heat exchanger.

[0054] The secondary inlet of the third heat exchanger can be connected to the domestic hot water circuit. The secondary inlet of the third heat exchanger can be connected to a return line of the domestic hot water circuit.

[0055] The return flow is determined by the direction of the flowing medium in a circuit, flowing away from the consumer towards the source. The consumer can be an energy sink, heat sink, or extraction point. The source can be an energy source, heat source, or supply point. The supply flow is the opposite direction to the return flow. A return and a supply flow in a circuit can be fluid-connected.

[0056] The secondary inlet of the third heat exchanger can be coupled to the second secondary-side heat discharge flow. The secondary inlet 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 discharge flow, or to a return flow of the domestic hot water circuit.

[0057] The secondary outlet of the first heat exchanger can be connected to a supply and / or return line of the domestic hot water circuit. The secondary outlet of the first heat exchanger can be connected to the second secondary-side heat dissipation flow.

[0058] The secondary outlet of the third heat exchanger can be coupled to the second secondary-side heat dissipation flow. The secondary outlet of the third heat exchanger can be coupled to the supply line of the domestic hot water circuit.

[0059] The couplings can be energy transmission paths or energy transmission paths. These can transfer energy from one coupling point to another and / or vice versa. The energy can manifest 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.

[0060] A fluid can serve as the means of energy transfer (or heat transfer medium). The fluid can be water. The energy transfer path or energy transmission path can be a closed or open pipeline. It can contain a fluid. The fluid can be located in a closed or open pipeline. The fluid can be set in motion by means of a fluid energy machine, thereby transferring heat through forced convection. The fluid energy machine can be a working machine. The fluid energy machine can be a pump, a compressor, a blower, and / or a fan. 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 a mixing valve and a pump.

[0061] 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.

[0062] 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.

[0063] 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.

[0064] The residual heat from the first heat exchanger can be heat supplied at the primary outlet of the first heat exchanger. The residual heat from the second heat exchanger can be heat supplied at the primary outlet of the second heat exchanger. The residual heat from the third heat exchanger can be heat supplied at the primary outlet of the third heat exchanger. The residual heat from the fourth heat exchanger can be heat supplied at the primary outlet of the fourth heat exchanger. The residual heat from the fifth heat exchanger can be heat supplied at the primary outlet of the fifth heat exchanger.

[0065] The transfer station can further include a first and second mixing valve. The first and second mixing valves can each be a controllable three-way valve or two controllable two-way valves.

[0066] 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-side heat supply flow and residual heat from the first heat exchanger. The heat resulting from the mixture can be supplied at the primary inlet of the first heat exchanger. The first mixing valve can be designed to supply 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 from the primary-side heat supply flow can be supplied by element 320a in Figure 3 The residual heat from the first heat exchanger can be transferred to element 302.4. Figure 3 be. the first heat exchanger can be element 302 in Figure 3 The primary inlet of the first heat exchanger can be element 302a.2 in Figure 3be the first mixing valve, element V301 in Figure 3 be.

[0067] 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 mix the heat from the primary-side heat supply flow and the residual heat from the third heat exchanger. The heat resulting from the mixture can be supplied at the primary inlet of the third heat exchanger. The second mixing valve can be designed to supply 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 from the primary-side heat supply flow can be supplied by element 320b in Figure 3 The residual heat from the third heat exchanger can be used by element 306.8 in Figure 3 The third heat exchanger can accommodate element 306 in Figure 3 The primary inlet of the third heat exchanger can be the element 306a.2 in Figure 3 be the second mixing valve can be the element V302 in Figure 3 be.

[0068] 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.

[0069] The transfer station can also include a first and second fluid energy machine.

[0070] The first fluid energy machine can provide a fluid flow at the primary inlet of the first heat exchanger. The second fluid energy machine can provide a fluid flow at the primary inlet of the third heat exchanger.

[0071] The second fluid energy machine can provide a volumetric flow at the primary inlet of the second heat exchanger and / or a volumetric flow at the primary inlet of the fourth heat exchanger and / or a volumetric flow at the primary inlet of the fifth heat exchanger. The volumetric flow can be a heat flux.

[0072] The transfer station can further include a third fluid energy machine. This third fluid energy machine can provide a volumetric flow for the second secondary-side heat removal stream. The third fluid energy machine can also be configured to circulate process water in the process water circuit.

[0073] The transfer station may further include a fourth and fifth fluid energy machine. The fourth fluid energy machine may provide a volumetric flow of the first secondary-side heat removal stream. The fifth fluid energy machine may provide a volumetric flow of the third secondary-side heat removal stream. The transfer station may further include a first, second, fifth, and / or sixth distribution valve. The distribution valve may be a mixing valve. The distribution valve may be a control valve. The distribution valve may be a valve. The valve may be a motorized valve.

[0074] The first distribution valve can be designed to divert at least part of the secondary-side heat input flow into the second secondary-side heat output flow before it is introduced into the second secondary-side heat output flow. The first distribution valve can be connected to the secondary outlet of the first heat exchanger and the secondary inlet and outlet of the third heat exchanger. The first distribution valve can also be connected to the secondary outlet of the first heat exchanger and to the return and supply lines of the domestic hot water circuit.

[0075] The first distribution valve can be designed to supply 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 include element 302 in Figure 3The secondary outlet of the first heat exchanger can be the element 302b.4 in Figure 3 The third heat exchanger can be the element 306 in Figure 3 The secondary inlet of the third heat exchanger can be the element 306b.2 in Figure 3 The secondary outlet of the third heat exchanger can be the element 306b.4 in Figure 3 The first distribution valve can be the element V304 in Figure 3 be.

[0076] The second distribution valve can be designed to supply residual heat from the third heat exchanger partially to the fourth heat exchanger and / or partially 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 supply heat at the primary outlet of the third heat exchanger partially to the primary inlet of the fourth heat exchanger and / or partially to the primary inlet of the second heat exchanger. The third heat exchanger can include element 306 in Figure 3 The fourth heat exchanger can accommodate element 308 in Figure 3 The second heat exchanger can accommodate element 304 in Figure 3 The primary outlet of the third heat exchanger can be the element 306a.4 in Figure 3The primary inlet of the fourth heat exchanger can be the element 308a.2 in Figure 3 The primary inlet of the second heat exchanger can be the element 304a.2 in Figure 3 be. The second distribution valve can be the element V305 in Figure 3 be.

[0077] The fifth distribution valve can be designed to supply residual heat from the fourth and / or fifth heat exchanger, at least partially, 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, as well as to a primary-side heat discharge flow. The fifth distribution valve can be designed to supply heat from the primary outlet of the fourth or fifth heat exchanger partially to the primary inlet of the second heat exchanger. The fifth distribution valve can be designed to supply heat from the primary outlet of the fourth or fifth heat exchanger partially to the primary inlet of the second heat exchanger and / or partially to the primary-side heat discharge flow. The fourth heat exchanger can include element 308 in Figure 3 The fifth heat exchanger can accommodate element 309 in Figure 3The second heat exchanger can accommodate element 304 in Figure 3 be. The primary-side heat dissipation flow can be in element 330. Figure 3 The primary outlet of the fifth heat exchanger can be the element 309a.4 in Figure 3 The primary inlet of the second heat exchanger can be the element 304a.2 in Figure 3 The fifth distribution valve can be the element V308 in Figure 3 be.

[0078] The sixth distribution valve can be designed to partially supply 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 to a primary-side heat removal flow. The sixth distribution valve can be designed to introduce heat at least partially from 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 supply heat from the primary outlet of the first heat exchanger, at least partially, to the primary inlet of the second heat exchanger and / or to partially supply heat to a primary-side heat removal flow. The first heat exchanger can include element 302 in Figure 3 The second heat exchanger can accommodate element 304 in Figure 3 The primary outlet of the first heat exchanger can be the element 302a.4 in Figure 3 The primary inlet of the second heat exchanger can be the element 304a.2 in Figure 3 be. The primary-side heat dissipation flow can be in element 330. Figure 3 The sixth distribution valve can be the element V309 in Figure 3 be.

[0079] The transfer station may also include a distribution valve. The distribution valve may contain the V310 element. Figure 3The distribution valve can be designed to partially transfer residual heat from the third heat exchanger to the first heat exchanger and / or partially transfer residual heat from the third heat exchanger to the fourth heat exchanger. The distribution valve can be coupled to the primary outlet of the third heat exchanger and the primary inlet of the first heat exchanger and / or the primary inlet of the fourth heat exchanger. The distribution valve can be designed to introduce or transfer heat at least partially from the primary outlet of the third heat exchanger to the primary inlet of the first and / or fourth heat exchanger.

[0080] The transfer station may also include a control unit. The control unit may be a regulator. The control unit may be configured to transmit an initial instruction to the first mixing valve. This transmission may be via wired, radio, or optical connection, and may be wired and / or wireless.

[0081] The first instruction to the first mixing valve can cause the first mixing valve to mix the heat from the primary-side heat supply flow and the residual heat from the first heat exchanger. The first instruction to the first mixing valve can also cause the first mixing valve to set or provide a temperature difference between the primary and secondary sides of the first heat exchanger, or a temperature on the secondary side of the first heat exchanger.

[0082] The terms "adjust," "set," or "provide" can refer to the mixing of two volume flows into a single volume flow, depending on a control variable of a valve. The volume flow could be a heat flow. The control variable of the valve could be a rotary valve integrated into the valve. The position of the rotary valve could be controlled by a controller.

[0083] 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 of 0 to 52 Kelvin, preferably 1 Kelvin.

[0084] The control system can be configured to transmit a second instruction to the second mixing valve. This second instruction can cause the second mixing valve to mix the heat from the primary-side heat supply flow and the residual heat from the third heat exchanger. Alternatively, the second instruction can cause the second mixing valve to establish or provide a temperature difference between the primary and secondary sides of the third heat exchanger. This second instruction can also cause the second mixing valve to establish or provide a temperature difference between the primary and secondary sides of the third heat exchanger that represents the exergetically optimal operating point of the transfer station. The temperature difference between the primary and secondary sides of the third heat exchanger can range from 0 to 3 Kelvin, preferably 1 Kelvin.

[0085] The temperature of the second secondary-side heat dissipation flow can reach 60 °C. A temperature of 60 °C can be a common value for hot water temperature supplied to a heat consumer.

[0086] The first and second mixing valves can be controlled in such a way that the residual heat (on the primary side) from the third heat exchanger is made available to the greatest extent possible for raising the temperature of the first and / or third secondary-side heat discharge flow, without directly using heat from the primary-side heat input flow for this purpose. The transfer station can also include a seventh distribution valve. This seventh distribution valve can be designed to make at least some heat from the primary heat input flow available at the primary inlet of the fourth or fifth heat exchanger. The seventh distribution valve can be coupled to the primary-side heat input flow and the primary inlet of the fourth or fifth heat exchanger.The provision of (direct) heat from the primary-side heat input flow for raising the temperature of the first and / or third heat output flow can be achieved by means of the seventh distribution valve. The seventh distribution valve can be designed to mix heat from the primary-side heat input flow and residual heat from the third heat exchanger. The heat resulting from this mixture can be provided at the primary inlet of the fourth or fifth heat exchanger. The fourth heat exchanger can incorporate element 308. Figure 3 The fifth heat exchanger can accommodate element 309 in Figure 3 The third heat exchanger can be the element 306 in Figure 3 be. The primary-side heat input flow can be in element 320. Figure 3 The primary inlet of the fourth heat exchanger can be the element 308a.2 in Figure 3 The seventh distribution valve can be the element V302 in Figure 3 be.

[0087] The control system can find the exergetically optimal operating point for different operating states. These different operating states can result from a time-invariant heat flow of the first and / or second and / or third heat dissipation flow.

[0088] Providing heat from the primary heat input stream can be used if the residual heat from the third heat exchanger is insufficient to raise the temperature of the first and / or third secondary heat output stream.

[0089] The temperature increase of the third secondary heat discharge flow via the fifth heat exchanger can be controlled by means of an eighth and ninth distribution valve. The transfer station also 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 supply heat from the primary outlet of the third heat exchanger to the primary inlet of the fifth heat exchanger. The third heat exchanger can include element 306 in Figure 3 The fifth heat exchanger can accommodate element 309. Figure 3 The primary outlet of the third heat exchanger can be the element 306a.5 in Figure 3 The primary inlet of the fifth heat exchanger can be the element 309a.2 in Figure 3 The eighth distribution valve can be the element V306 in Figure 3 be.

[0090] 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 supply heat from the primary outlet of the fourth heat exchanger to the primary inlet of the fifth heat exchanger. The fourth heat exchanger can incorporate element 308 in Figure 3 The fifth heat exchanger can accommodate element 309 in Figure 3 The primary outlet of the fourth heat exchanger can be the element 308a.4 in Figure 3 The primary inlet of the fifth heat exchanger can be the element 309a.2 in Figure 3 be. The ninth distribution valve can be the element V307 in Figure 3The temperature increase of the third secondary heat discharge flow can be achieved using heat from the primary heat input flow and / or residual heat from the fourth heat exchanger and / or residual heat from the third heat exchanger. Heat supplied at the primary inlet of the fifth heat exchanger can be provided via the seventh and / or eighth and / or ninth distribution valve. The control system can determine the exergetically optimal operating point in conjunction with the temperature increase of the third secondary heat discharge flow.

[0091] 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 will become apparent from the dependent claims, the accompanying drawings, and the description.

[0092] According to 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 a top-down transfer station.

[0093] The advantages of the invention will follow a detailed description.

[0094] It is known that in transfer stations, cold water undergoes a temperature increase before being introduced into the hot water circuit or domestic hot water circuit. According to current hygiene regulations in Germany, the temperature in the return line of the domestic hot water circuit must be at least 55 °C. The temperature of the secondary-side return line of the domestic hot water circuit should therefore not fall below 55 °C. These regulations serve to prevent the spread of germs and pathogens, especially Legionella, in the domestic hot water. Consequently, in some designs, the domestic hot water temperature is greater than or equal to 60 °C. The cold water, or water before it is introduced into the domestic hot water circuit, typically has a temperature of 8 °C to 15 °C. Therefore, a significant temperature increase is required by means of a heat exchanger, which preheats the cold water or the water from outside the domestic hot water circuit.

[0095] It is also known that the aforementioned heat exchanger can utilize residual heat from a heat exchanger used for hot water preparation in a domestic hot water circuit. This allows the district heating operator to utilize the heat supply exergetically.

[0096] In some embodiments of the present invention, preheating takes place successively in two stages using two separate heat exchangers before the chilled water is introduced into the domestic hot water circuit. Additionally, residual heat is partially utilized for the heat exchanger of the first stage and for the heat exchanger used to raise the temperature of the domestic hot water circuit. This combination or cascade of heat exchangers, along with the combination and utilization of residual heat, optimizes the exergetic utilization of the primary heat input flow.

[0097] In some embodiments of the present invention, preheating takes place successively in two stages and additionally in a third stage after the preheated cold water is introduced into the domestic hot water circuit. The third stage of heating the cold water is achieved by raising the temperature of the domestic hot water circuit. This allows for the dual use of heat exchangers, which implies a minimal number of heat exchangers.

[0098] The available primary heat supply flow is used thermally in an optimal manner: The primary heat supply flow undergoes maximum cooling. The return temperature of the primary heat supply flow is minimized. The temperature difference between the supply and return temperatures of the primary heat supply flow is maximized. This temperature difference maximizes the transmission capacity of the connecting pipeline (e.g., district heating / local heating). Upstream supply lines can be reduced in size while maintaining the same transmission capacity.

[0099] Generation processes, i.e., the provision / generation of the primary heat input flow, are optimized: Steam turbines achieve maximum efficiency through the minimum return temperature of the primary heat input flow. 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 improved efficiency and utilization rates.

[0100] It is also known that limescale buildup is primarily a function of water temperature. That is, limescale buildup increases with increasing water temperature. Additionally, the two stages of temperature raising the cold water before it is introduced into the domestic hot water circuit mean that the heat, or rather the temperature, provided to the heat exchangers is lower compared to a single-stage temperature increase before it enters the domestic hot water circuit. In some embodiments of the invention, an additional "final" (third) temperature increase of the domestic hot water is carried out by means of a third heat exchanger. This, in turn, reduces limescale buildup in the heat exchanger, particularly for the two heat exchangers that implement the two stages of temperature raising the cold water.

[0101] It is also known that transfer station procedures and transfer stations comprise two operating modes, namely a water supply operation and a circulation operation.

[0102] In a conventional circulation system, domestic hot water, such as drinking water, circulates in a domestic hot water circuit. Residual heat from a primary-side heat supply circuit, after a secondary-side domestic hot water circuit has been heated, is used to heat a secondary-side utility heat circuit, such as water in a heating circuit. The primary-side heat supply circuit is, for example, a district heating supply line that transfers heat in a heat exchanger on the primary side to the domestic hot water in the secondary-side domestic hot water circuit at a transfer station. This means that the primary side is the heat output side, while the secondary side is the heat input side. To achieve this, at least part of the primary-side heat supply circuit is fed into the utility heat circuit after the domestic hot water circuit has been heated. This means that any residual heat still contained in the primary-side heat supply circuit can be used to heat the utility heat circuit.

[0103] In the conventional water supply system, (cold, fresh) water from outside the domestic hot water circuit is introduced into the domestic hot water circuit, where it is heated, for example, in a heat exchanger. This process utilizes residual heat from the primary-side heat supply circuit after the domestic hot water circuit has been heated. This is achieved by at least partially diverting the primary-side heat supply circuit to the domestic hot water circuit after the domestic hot water circuit has been heated, where it then heats the incoming (cold) water.

[0104] In some embodiments of the present invention, the known circulation operation can take place at least partially or simultaneously with the known water supply operation. This is advantageous because heat losses are associated with the switching process.

[0105] In some 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 domestic hot water circuit (second secondary-side heat removal flow and / or second temperature increase of the secondary-side heat supply flow).

[0106] In some embodiments of the present invention, the advantage is that water from outside the domestic water circuit can also be introduced into the domestic water circuit during the circulation of the domestic water.

[0107] In some embodiments of the present invention, the advantage lies in the fact that the secondary-side heat supply flow can be preheated or heated using residual heat from heat exchangers. The preheating or heating of the secondary-side heat supply flow can be achieved by the first and second temperature increases provided by the first and second heat exchangers. The residual heat from the heat exchangers can be residual heat from the third and / or fourth heat exchanger. This results in exergetically optimal preheating or heating of the secondary-side heat supply flow.

[0108] Exemplary embodiments of the invention are described in more detail below with reference to the figures. Further features and advantages will become apparent from this description. Specific features of these exemplary embodiments may represent general features of the invention. Features of these exemplary embodiments combined with other features may also represent individual features of the invention. Examples of implementation

[0109] Figure 1 : A transfer station. Figure 2 : A transfer station. Figure 3 : A transfer station. Figure 4 : A transfer station. Figure 5 : A method for transferring heat using a heat transfer station.

[0110] In the following description of the exemplary embodiments, identical or similar components may have the same reference numerals.

[0111] In Figure 1Figure 1 shows an embodiment of a heat transfer station 100 for transferring heat according to one aspect of the invention. The heat 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. Furthermore, the heat transfer station 100 comprises a primary-side heat input flow 120, a first secondary-side heat output flow 132, a second secondary-side heat output flow 134, and a secondary-side heat input flow 138. The secondary-side heat input flow 138 undergoes a first temperature increase and a second temperature increase before being introduced into the second secondary-side heat output flow 134.

[0112] The second temperature increase is achieved by means of the first heat exchanger 102, which partially utilizes the primary-side heat inflow 120a for this purpose. This results in at least partial heat transfer from the partial primary-side heat inflow 120a to the secondary-side heat supply flow 138.

[0113] The first temperature increase is achieved by means of the second heat exchanger 104, which utilizes residual heat from the fourth heat exchanger 108.2 and residual heat from the first heat exchanger 102.2. Thus, in the first temperature increase, the second heat exchanger 104 heats the secondary-side heat supply flow 138 partly with the help of residual heat from the fourth heat exchanger 108.2 and the first heat exchanger 102.2.

[0114] Furthermore, the transfer station 100 includes a temperature increase of the second secondary-side heat discharge flow 134 by means of the third heat exchanger 106, which partially uses the primary-side heat inflow 120b for this purpose.

[0115] Furthermore, the transfer station 100 includes a temperature increase of the first secondary-side heat discharge flow 132 by means of the fourth heat exchanger 108, which uses partly the residual heat from the third heat exchanger 106.2 and / or partly the primary-side heat inflow 120c for this purpose. If the residual heat from the third heat exchanger 106.2 is insufficient for raising the temperature of the first secondary-side heat discharge flow 132 by means of the fourth heat exchanger 108, the primary-side heat inflow 120c is used additionally, partly or exclusively, for raising the temperature of the first secondary-side heat discharge flow 132. The temperature of the primary-side heat input flow 120 is greater than or equal to the temperature of the secondary-side heat input flow 138 and the second secondary-side heat output flow 134 and the first secondary-side heat output flow 132.

[0116] The second heat exchanger 104 of the transfer station 100 uses the residual heat from the first heat exchanger 102.2 and the residual heat from the fourth heat exchanger 108.2 for the initial temperature increase of the secondary-side heat supply flow 138. This ensures that the remaining heat initially introduced into transfer station 100 by the primary-side heat supply flow 120 is used in an exergetically optimal manner for the initial temperature increase.

[0117] In one embodiment of the transfer station 100, a temperature of the secondary-side heat supply flow 138 is predetermined before it is introduced into the second secondary-side heat discharge flow 134. This predetermined target temperature is achieved by the first and second temperature increases. In another embodiment of the transfer station 100, the predetermined target temperature is specified at a discrete point in time and further determined by a control system integrated into the transfer station 100. The first temperature increase of the secondary-side heat supply flow 138 is achieved partly by the residual heat from the first heat exchanger 102.2 and partly by the residual heat from the fourth heat exchanger 108.2 via the first heat exchanger 104.The remaining temperature difference of the secondary-side heat supply flow 138 to the specified target temperature is then achieved by the second temperature increase of the secondary-side heat supply flow 138 by means of the first heat exchanger 102. The first heat exchanger 102 utilizes part of the primary-side heat supply flow 120a.

[0118] The secondary-side heat input flow 138, before being introduced into the second secondary-side heat output flow 134, undergoes a first temperature increase and a second temperature increase. This introduction of the secondary-side heat input flow 138 into the secondary-side heat output flow 134 can occur before the temperature increase of the second secondary-side heat output flow 134 by means of the third heat exchanger 106, 138a, and / or after the temperature increase of the second secondary-side heat output flow 134 by means of the third heat exchanger 106, 138b.

[0119] In one embodiment of the transfer station 100, the secondary-side heat supply flow 138 does not reach a target temperature, for example at least 60 °C, after its first and second temperature increases. The secondary-side heat supply flow 138 (after the first and second temperature increases) is therefore introduced upstream of the third heat exchanger, 138a. Thus, the secondary-side heat supply flow 138 undergoes a third temperature increase by means of the third heat exchanger. In another embodiment of the transfer station 100, if the secondary-side heat supply flow 138 reaches a target temperature, for example at least 60 °C, after its first and second temperature increases, the secondary-side heat supply flow 138 can be introduced upstream, 138a, and / or downstream, 138b, of the third heat exchanger.

[0120] In one embodiment, the secondary-side heat supply flow 138 is introduced before and after the temperature increase of the second secondary-side heat discharge flow 134, 138a and 138b, so that the mixed average temperature of the secondary-side heat discharge flow 134 after the temperature increase of the second secondary-side heat discharge flow 134 by means of the third heat exchanger 106 and the secondary-side heat supply flow 138 introduced therein after its first and second temperature increase is equal to or only slightly greater than the said target temperature.

[0121] One advantageous effect of the transfer station 100 is that residual heat from the heat exchangers can still be used to raise the temperature of the secondary-side heat supply flow 138. This ensures exergetically optimal utilization of the provided primary heat flow by means of the transfer station 100.

[0122] In Figure 2A 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. Furthermore, the transfer station 200 comprises a first secondary-side heat discharge flow 232, a second secondary-side heat discharge flow 234, and a secondary-side heat input flow 238.

[0123] In one embodiment, the first heat exchanger 202 is the first heat exchanger 102, the second heat exchanger 204 is the second heat exchanger 104, the third heat exchanger 206 is the second heat exchanger 106, and the fourth heat exchanger 208 is the fourth heat exchanger 108. Furthermore, in this embodiment, the first secondary-side heat discharge flow 232 is the second secondary-side heat discharge flow 132, the second secondary-side heat discharge flow 234 is the second secondary-side heat discharge flow 134, and the secondary-side heat input flow 138 is the second secondary-side heat input flow 138.

[0124] Furthermore, the transfer station 200 includes a fifth heat exchanger 209 and a third secondary-side heat removal flow 236.

[0125] The secondary-side heat input flow 238, before it is introduced into the second secondary-side heat output flow 234, undergoes a first temperature increase and a second temperature increase. The first temperature increase of the secondary-side heat output flow 238 occurs before the second temperature increase of the secondary-side heat output flow 238.

[0126] The second temperature increase is achieved by means of the first heat exchanger 202, which utilizes partly the primary-side heat inflow 220a and / or partly residual heat from the first heat exchanger 202.4 and / or partly residual heat from the third heat exchanger 206.10. This allows the residual heat from the first heat exchanger 202.4, in combination with the primary-side heat inflow 220a, to be used for the second temperature increase. This makes it possible to provide the thermal energy required for the second temperature increase partly from the primary-side heat inflow 220a and / or partly from the residual heat of the first heat exchanger 202.4. In one embodiment, the use of the residual heat from the first heat exchanger 202.4 is prioritized over the use of the primary-side heat supply flow 220 for the second temperature increase.In one embodiment, the residual heat of the third heat exchanger 206.10 is used for the second temperature increase.

[0127] The first temperature increase is achieved by means of the second heat exchanger 204, which utilizes partly the residual heat from the first heat exchanger 202.2 and partly residual heat from the fifth heat exchanger 209.2 and / or partly residual heat from the third heat exchanger 206.4 and / or partly residual heat from the fourth heat exchanger 208.2. The utilization of the partial residual heat from the first heat exchanger 202.2 and partly residual heat from the fifth heat exchanger 209.2 and / or partly residual heat from the third heat exchanger 206.4 and / or partly residual heat from the fourth heat exchanger 208.2 is carried out with exergetically optimal use of the primary-side heat supply flow 220.

[0128] The second heat exchanger 204 therefore utilizes 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 flow 238. The secondary-side heat supply flow 238 has a lower temperature before the first and second temperature increases. Therefore, the first temperature increase also occurs when utilizing residual heat from the first and fourth and / or third and / or fourth heat exchangers, which has a lower temperature than the primary-side heat supply 220, but is sufficient for the first temperature increase. This achieves the advantageous effect of optimal utilization of residual heat. A further advantage arises from the lower temperature of some of the residual heat from the first heat exchanger 202.2 and some of the residual heat from the fifth heat exchanger 209.2 and / or some of the residual heat from the third heat exchanger 206.4 and / or partially 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 the heat transfer. Furthermore, the low temperature reduces scaling.

[0129] In one embodiment, the use of residual heat from 202.2 and 209.2 is prioritized based on their temperatures. In another embodiment, the use of residual heat from 202.2 and 209.2 and / or 106.4 and / or 108.2 is prioritized based on their temperatures.

[0130] In one embodiment, the first and second temperature increase of the secondary-side heat supply flow 238 is achieved using the residual heat 206.10 and / or 206.4 and / or 208.2 and / or 209.2. In other words, the preheating of the secondary-side heat supply flow 238, in particular the second temperature increase, is achieved using return flows from the heat exchangers 206 and / or 208 and / or 209.

[0131] Furthermore, the transfer station 200 includes a temperature increase of the second secondary-side heat discharge flow 234 by means of the third heat exchanger 206, which partially uses the primary-side heat inflow 220b for this purpose.

[0132] Furthermore, the transfer station 200 includes a temperature increase of the first secondary-side heat discharge flow 232 by means of the fourth heat exchanger 208, which partially utilizes the residual heat from the third heat exchanger 206.2. This temperature increase is achieved by means of the fourth heat exchanger 208, which partially utilizes the residual heat from the third heat exchanger 206.2 and / or partially the primary-side heat input 220c and / or partially residual heat from the third heat exchanger 208.6.

[0133] The secondary-side heat input flow 238, before being introduced into the second secondary-side heat output flow 234, undergoes a first temperature increase and a second temperature increase. This introduction of the secondary-side heat input flow 138 into the secondary-side heat output flow 234 can occur before the temperature increase of the second secondary-side heat output flow 234 by means of the third heat exchanger 206, 238a, and / or after the temperature increase of the second secondary-side heat output flow 134 by means of the third heat exchanger 206, 238b. In one embodiment, the introduction of the secondary-side heat input flow 238 into the second secondary-side heat output flow 234 corresponds to that of the transfer station 100.

[0134] Furthermore, the transfer station 200 includes a temperature increase of the third secondary-side heat discharge flow 236 by means of the fifth heat exchanger 209, which partially utilizes the residual heat from the fourth heat exchanger 208.4 for this purpose. In one embodiment, the temperature increase of the third secondary-side heat discharge flow 236 includes the fifth heat exchanger 209, which partially utilizes the residual heat from the fourth heat exchanger 208.4 and / or partially the residual heat from the third heat exchanger 206.6 for this purpose.

[0135] It can be seen that the fifth heat exchanger 209 generally utilizes residual heat to raise the temperature of the third secondary-side heat discharge flow 236. In contrast, the first secondary-side heat discharge flow 232 can partially utilize heat from the primary-side heat input flow 220c. In one embodiment, this is implemented such that the fourth heat exchanger 208 can generally utilize a higher temperature than the fifth heat exchanger 209. This, in turn, generally allows for a higher temperature of the first secondary-side heat discharge flow 232 compared to the third secondary-side heat discharge flow 236. In one embodiment, the first secondary-side heat discharge flow 232 is a high-temperature useful heat flow, and the third secondary-side heat discharge flow 236 is a low-temperature useful heat flow.The high-temperature useful heat flow includes the distribution of heat from the high-temperature useful heat flow via collector radiators. The low-temperature useful heat flow includes the distribution of heat from the low-temperature useful heat flow via underfloor heating and / or component activation.

[0136] In one embodiment, the secondary-side heat input flow 238 is a cold water flow, and the secondary-side heat output flow 234 is a hot water flow.

[0137] Figure 3 Figure 1 shows a transfer station 300 according to a further embodiment. The transfer station 300 comprises 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.

[0138] In one embodiment, the first heat exchanger 302 is the first heat exchanger 202 according to the embodiment shown. Figure 2, the second heat exchanger 304 the second heat exchanger 204, the third heat exchanger 306 the third heat exchanger 206, the fourth heat exchanger 308 the fourth heat exchanger 208 and the fifth heat exchanger 309 fifth heat exchanger 209.

[0139] Furthermore, the transfer station 300 comprises a secondary-side heat supply flow 338 and a second secondary-side heat discharge flow 334. The second secondary-side heat discharge flow 334 is a domestic hot water circuit comprising a domestic hot water return 334a and a domestic hot water supply 334b. The secondary-side heat supply flow 338 is cold water or water outside the domestic hot water circuit 334.

[0140] Furthermore, the transfer station 300 includes a primary-side heat inflow 320. The primary-side heat supply flow 320 is a supply flow of district heating 320.

[0141] The cold water 338, before being introduced into the domestic hot water circuit 334, undergoes a first temperature increase and a second temperature increase. The first temperature increase of the cold water 338 occurs before the second temperature increase of the cold water 338.

[0142] The second temperature increase is achieved using the first heat exchanger 302, which for this purpose partly uses the supply of the district heating 320a and / or partly residual heat from the first heat exchanger 302.4 and / or partly residual heat from the third heat exchanger 306.10.

[0143] The first temperature increase is achieved by means of the second heat exchanger 304, which uses partly the residual heat of the first heat exchanger 302.2 and / or partly residual heat of the fifth heat exchanger 309.2 and / or partly residual heat of the fourth heat exchanger 308.2 and / or partly residual heat of the third heat exchanger 306.4.

[0144] The first heat exchanger 302 comprises a primary side 302a and a secondary side 302b. The primary side 302a and the secondary side 302b are configured 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.

[0145] Furthermore, the primary side 302a comprises a primary inlet 302a.2 and a primary outlet 302a.4, through which 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 district heating supply 320 and to the primary outlet 302a.4. The coupling includes a valve V301. The valve V301 is designed as a three-way valve, thereby providing a resulting heat flow to the primary inlet 302a.2. The resulting heat flow consists of a heat flow from the district heating supply 320 and a heat flow from the residual heat of the first heat exchanger 302.2. Depending on the position of the three-way valve V301, the first heat exchanger 302 partially uses the supply 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.

[0146] 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 from the primary side 302a and partially releases heat at the secondary outlet 302b.4.

[0147] The second heat exchanger 304 comprises a primary side 304a and a secondary side 304b. The primary side 304a and the secondary side 304b are configured 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, through which 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 from the primary side 304a and partially releases heat at the secondary outlet 304b.4.

[0148] The second heat exchanger 304 is preferably designed as a shell-and-tube heat exchanger. The primary side 304a comprises a volume designed to partially store heat at the primary inlet 304a.2 and to partially transfer this heat to the secondary side 304b. This volume typically contains a medium with high heat capacity, for example, a fluid in the liquid phase, particularly water. In one embodiment, the secondary side 304b of the shell-and-tube heat exchanger can further comprise a volume designed to partially store heat at the secondary inlet 304a.2 and to partially transfer this heat to the secondary side 304b.

[0149] In another 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 consists of a material with high thermal conductivity, e.g., 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 efficient heat transfer. At the same time, the larger the surface area of ​​the separating layer, the more heat is transferred. With this principle, an opposing heat flow of the heat media along the separating layer achieves the best heat exchange between the heat media.

[0150] The shell-and-tube heat exchanger has a large heat storage capacity, providing heat on the primary side. This heat can be used to temporarily store a typically continuous heat flow on the primary side 304a. The stored heat can then be transferred to the chilled water 338 that needs to be heated. The chilled water 338 often needs to be heated at high power levels in short intervals. During these periods, the stored heat can be transferred to the chilled water, thus increasing the efficiency of the overall process. It is also recommended to install the shell-and-tube heat exchanger 304 with the hot side facing upwards. This means that the primary inlet 304a.2 is located above the primary outlet 304a.4, while 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.Mixing is counteracted by the lower density of the warmer primary side 304a located on top at the present temperature level.

[0151] The primary inlet 304a.2 is coupled to the primary outlet 302a.4. Thus, the second heat exchanger 304 partially utilizes the residual heat from the first heat exchanger 302.2 for the initial temperature increase of the chilled water 338.

[0152] The primary outlet 304a.4 is connected to a primary-side heat discharge flow 330. The primary-side heat discharge flow 330 includes a return flow of the district heating 330. Thus, the supply flow of the district heating 320 and the return flow of the district heating 330 form a district heating circuit.

[0153] Furthermore, the primary outlet 302a.4 is coupled to the district heating return line 330. The coupling of the primary outlet 302a.4 with the district heating return line 330 and the primary inlet 304a.2 includes a valve V309. The valve V309 is designed as a distribution valve, whereby, depending on the position of the distribution valve V309, the residual heat from the first heat exchanger 302.2 is partially supplied to the primary inlet 304a.2 and / or partially introduced into the district heating return line 330.

[0154] If the residual heat from the first heat exchanger 302.2 is less than the residual heat from the fifth heat exchanger 309.2 and / or the fourth heat exchanger 308.2, the residual heat from the first heat exchanger 302.2 is partially fed into the district heating return line 330 via valve V309. Complete or partial feeding can affect the exergetic performance of the overall system. Therefore, continuous control serves to determine the exergetic optimal operating point.

[0155] The secondary inlet 304b.2 is coupled to the cold water 338. The secondary outlet 304b.4 is coupled to the secondary inlet 302b.2. This means that the first temperature increase of the cold water 338 occurs before the second temperature increase of the cold water 338.

[0156] After the first and second temperature increases of the cold water 338, the cold water 338 is introduced into the domestic hot water circuit 334. The secondary outlet 302b.4 is coupled to the domestic hot water return 334a and the domestic hot water supply 334b. The coupling includes a valve V304. The valve V304 is designed as a distribution valve, whereby the cold water 338 is introduced partially into the domestic hot water return 334a and / or partially into the domestic hot water supply 334b, depending on the position of the distribution valve V304. In one embodiment, if the cold water 338 has a predetermined temperature or exceeds this predetermined temperature before being introduced into the domestic hot water circuit 334, the cold water 338 is introduced into the domestic hot water supply 334b. In one embodiment, if the cold water 338 does not reach the specified temperature, the cold water 338 is introduced into the domestic hot water return 334a and heated in the third heat exchanger.

[0157] Furthermore, the transfer station 300 includes a temperature increase of the domestic hot water circuit 334 by means of the third heat exchanger 306, which for this purpose partly uses the primary-side heat inflow 320b and / or partly residual heat from the third heat exchanger 306.8.

[0158] The third heat exchanger 306 comprises a primary side 306a and a secondary side 306b. The primary side 306a and the secondary side 306b are configured 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, through which 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 comprises 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 from the primary side 306a and partially releases heat at the secondary outlet 306b.4.

[0159] The primary inlet 306a.2 is coupled to the district heating supply 320 and the primary outlet 306a.4. Thus, the third heat exchanger 306 uses partly the primary-side heat inlet 320b and / or partly the residual heat from the third heat exchanger 306.8 to raise the temperature of the domestic hot water circuit 334.

[0160] The coupling includes a valve V302. The valve V302 is designed as a three-way valve, which provides a resulting heat flow to the primary inlet 306a.2. The resulting heat flow consists of a heat flow from the district heating supply 320 and a heat flow from the residual heat of the first heat exchanger 306.8. Depending on the position of the three-way valve V302, the third heat exchanger 306 utilizes either the district heating supply 320b and / or residual heat from the first heat exchanger 306.8. The residual heat flow of 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 for raising the temperature of the domestic hot water circuit 334 by means of the third heat exchanger 306, so that as little limescale precipitation as possible takes place in the third heat exchanger 306.In standard cases, the primary temperature must be above 60 °C to heat the drinking water to 60 °C. This is the usual hot water temperature that ensures no Legionella bacteria can form in the water.

[0161] The secondary inlet 306b.2 is connected to the domestic hot water return 334a. The secondary outlet 306b.4 is connected to the domestic hot water supply 334b. This allows heat transfer from the third heat exchanger 306 to the domestic hot water supply 334. It should be reiterated that the secondary outlet 302b.4 is also connected to the domestic hot water supply 334. This connection occurs either before or concurrently with the connection of the domestic hot water supply 334 at the secondary inlet 306b.2. As a result, the cold water 338, which is introduced into the domestic hot water supply 334, undergoes a third temperature increase. The third temperature increase of the cold water 338 is achieved by increasing the temperature of the domestic hot water circuit 334 by means of the third heat exchanger 306.

[0162] In one embodiment of the transfer station 300, the highest primary-side temperatures often occur at the primary inlet 306a.2. Therefore, in this embodiment of the transfer station 300, the heat is supplied to the heat exchangers 308 and 309 at the primary return 306a.4.

[0163] The domestic hot water circuit 334 is a drinking water circuit containing hot water. According to applicable hygiene regulations, the temperature in the domestic hot water supply line 334b ​​must be at least 60 °C. The temperature of the domestic hot water return line 334a should not fall below 55 °C. These regulations serve to contain the spread of germs and pathogens, especially Legionella, in the drinking water circuit. Consequently, in some embodiments, the drinking water temperature is greater than or equal to 60 °C. To limit germ growth and / or to ensure a uniform temperature distribution in the network, a pump P303 is installed in the drinking water circuit 334, which ensures sufficient circulation of the drinking water. The hygiene regulations prescribe a minimum of 16 hours of drinking water circulation per day, which is maintained in some embodiments.

[0164] If water is taken from the brewing water circuit 334, for example from a tap in the brewing water circuit, the taken water is replaced by the cold water 338.

[0165] Furthermore, the transfer station 300 comprises a first secondary-side heat discharge flow 332 and a third secondary-side heat discharge flow 336. The first secondary-side heat discharge flow 332 is a high-temperature heating circuit, comprising a flow 332b and a return 332a. The third secondary-side heat discharge flow 336 is a low-temperature heating circuit, comprising a flow 336b and a return 336a. The high-temperature heating circuit supplies a radiator heating system with hot water. The typical design is 70 / 50. This means that, under standard design conditions (statistically lowest occurring outside temperature), the flow 332b is 70 °C and the return 332a is 50 °C. Depending on the outside temperature, the temperatures will fluctuate upwards or downwards. 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 an underfloor heating system.For this purpose, a design of 35 / 25 is sufficient, for example – that is, the temperature of the flow pipe 336b is 35 °C and the temperature of the return pipe 336a is 25 °C. In another embodiment, the low-temperature heating circuit is designed for thermal component activation. With thermal component activation, for example, a floor slab, a wall, or a ceiling is heated by means of water-carrying pipes. For this purpose, a design of 23 / 21 is sufficient, for example.

[0166] 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 for this purpose partly uses the primary-side heat inflow 320c and / or partly the residual heat of the third heat exchanger 306.2.

[0167] The fourth heat exchanger 308 comprises a primary side 308a and a secondary side 308b. The primary side 308a and the secondary side 308b are configured 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, through which 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 from the primary side 308a and partially releases heat at the secondary outlet 308b.4.

[0168] The primary inlet 308a.2 is coupled to the district heating supply 320 and the primary outlet 306a.4. Thus, the fourth heat exchanger 308 uses partly the primary-side heat input 320c and / or partly the residual heat from the third heat exchanger 306.2 to raise the temperature of the high-temperature heating circuit 332.

[0169] The coupling between the primary inlet 308a.2 and the district heating supply 320 includes a valve V303. Valve V303 provides heat to the high-temperature heating circuit 332. If the residual heat from the third heat exchanger 306.2 provides sufficient heat to raise the temperature of the high-temperature heating circuit 332, valve V303 can close completely. If the residual heat from the third heat exchanger 306.2 is insufficient to raise the temperature of the high-temperature heating circuit 332, valve V303 can supplement the missing heat by opening.

[0170] Furthermore, the coupling between primary outlet 306a.4 and primary inlet 308a.2 includes a valve V305. If the residual heat from the third heat exchanger 306.2 does not provide sufficient heat for raising the temperature of the high-temperature heating circuit 332, the second heat exchanger 304 also utilizes residual heat from the third heat exchanger 306.4 for the initial temperature increase. Thus, primary outlet 306a.4 is also coupled to primary inlet 304a.2. This coupling is achieved via valve V305.

[0171] In one embodiment of the transfer station 300, the coupling between the primary outlet 306a.4 and the primary inlet 308a.2 can further include a valve V310. The valve V310 is designed as a distribution valve, whereby residual heat from the third heat exchanger 306 is partially supplied to the primary inlet 302a.2 and / or partially supplied to the primary inlet 308a.2, depending on the position of the distribution valve V310. This allows the first and second temperature increases of the chilled water 338, in particular the second temperature increase, to be achieved using residual heat. This represents a further exergetic optimization. The distribution of the still usable residual heat at the primary outlet 306a.4 to the primary inlet 308a.2 (residual heat 306.2) and primary inlet 302a.2 (residual heat 306.10) can be effected via the distribution valve V310. This means that the primary exit 306a.4 is coupled with the primary entry 302a.2 and the primary entry 308a.2.Simply put, this coupling represents a coupling or direct connection between hot water generation, in particular by means of the first heat exchanger 302, and heating, in particular by means of the fourth heat exchanger 308.

[0172] Utilizing the residual heat 306.10 from the third heat exchanger 306 for the second temperature increase via the distribution valve V310 and / or its coupling can offer an advantage, such that only the minimum required temperature level can be achieved at the primary-side supply of the fourth heat exchanger 308, particularly the residual heat 306.2. The transfer station 300 can thus achieve further optimized exergy performance. The minimum required temperature level can be regulated, for example, by means of the second heat exchanger 304.

[0173] Furthermore, the primary outlet 308a.4 is coupled to the primary inlet 304a.2. This allows the second heat exchanger 304 to partially utilize residual heat from the fourth heat exchanger 308.2 for the initial temperature increase of the chilled water 338. The coupling includes a valve V307. Valve V307 is designed as a distribution valve, whereby, depending on the position of the distribution valve V307, the residual heat from the fourth heat exchanger 308.4 is partially supplied to the primary inlet 304a.2 and / or partially supplied to the primary inlet 309a.2. Depending on the temperature and exergy ratio, the primary outlet 308a.4 is either partially or completely discharged into the primary inlet 309a.2 and / or the primary inlet 304a.2. The aim is always to achieve optimal exergetic performance.This means that the heat from the district heating supply line 320 is transferred to the cold water supply line 338, the domestic hot water supply line 334b, the supply line 332b, and the line 336b in a temperature sequence that is as optimal as possible. In other words, the heat from the district heating return line 330 is used in such a way that a minimum volume flow rate is achieved with a maximum temperature difference between the supply and return lines of the district heating system.

[0174] The secondary inlet 308b.2 is coupled to the return line 332a. Furthermore, the secondary outlet 308b.4 is coupled to the supply line 332b.

[0175] 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 residual heat of the third heat exchanger 306.6 for this purpose.

[0176] The fifth heat exchanger 309 comprises a primary side 309a and a secondary side 309b. The primary side 309a and the secondary side 309b are configured 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, through which 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 from the primary side 309a and partially releases heat at the secondary outlet 309b.4.

[0177] The primary inlet 309a.2 is coupled to the primary outlet 308a.4. The primary outlet 309a.4 is coupled to the primary inlet 304a.2. Thus, the second heat exchanger 304 partially utilizes the residual heat from the fifth heat exchanger 309.2 for the initial temperature increase of the chilled water 338.

[0178] Furthermore, the primary inlet 309a.2 is coupled to the primary outlet 306a.4. This allows the fifth heat exchanger 309 to partially utilize the residual heat from the third heat exchanger 306.6 for raising the temperature of the low-temperature heating circuit 336. The coupling includes a valve V306. Valve V306 is designed as a distribution valve, whereby, depending on the position of the distribution valve V306, residual heat from the primary outlet of the third heat exchanger 306 is partially supplied to the primary inlet 308a.2 and / or partially supplied to the primary inlet 309a.2. This supply depends on the temperature and exergy ratio. The aim is always to achieve optimal exergetic performance. This means that the heat from the district heating supply 320 is transferred to the cold water 338, the domestic hot water supply 334b, the supply 332b and the flow 336b as optimally as possible.In other words, the heat of the return flow of the district heating 330 is optimally minimized, see also

[0173] .

[0179] Furthermore, primary outlets 309a.4, 306a.4, and 308a.4 are connected to the district heating return line 330. This allows 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 to be fed into the district heating return line 330. The connection includes a valve V308. Completely or partially bypassing the second heat exchanger 304 using valve V308 may be advantageous if the temperature of the residual heat from the fifth heat exchanger 309.2 and the residual heat from the third heat exchanger 306.4 exceeds 60 °C, thus increasing the risk of scaling in the second heat exchanger 304. Furthermore, bypassing the second heat exchanger 304 completely or partially by means of the valve V308 may be useful if the temperature of the residual heat of the first heat exchanger 302 is low.2 has a higher temperature than the residual heat temperature of the fifth heat exchanger 309.2. In some embodiments, bypassing the second heat exchanger 304 completely or partially by means of the valve V308 may also be advantageous if the residual heat temperature 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. Bypassing the second heat exchanger 304 completely or partially can affect the exergetic performance of the overall system; the continuous control of the valve 308 serves to find the exergetic optimal operating point.

[0180] The secondary inlet 309b.2 is coupled to the return line 336a. The secondary outlet 309b.4 is coupled to the supply line 336b.

[0181] The coupling of heat exchangers 308 and 309, as described above, corresponds to a series connection. The series connection is a temperature series connection.

[0182] The third secondary-side heat discharge flow 236, which is a low-temperature useful heat flow and undergoes temperature elevation by means of the fifth heat exchanger, utilizes the residual heat of the third heat exchanger. In one embodiment, the residual heat has a temperature of 60 °C or higher, since the second secondary-side heat discharge flow 334 is heated to 60 °C by means of the third heat exchanger in this embodiment. Thus, in this embodiment, the residual heat is sufficient for raising the temperature of the third secondary-side heat discharge flow. In another embodiment, the residual heat of the third heat exchanger is insufficient for raising the temperature of the low-temperature useful heat flow 236. Therefore, heat from the primary-side heat supply flow 320c is supplied by means of the distribution valve V303. This heat is supplied to the fifth heat exchanger via the fourth heat exchanger, 308.4.In another embodiment, the residual heat of the third heat exchanger 306.6 is insufficient to raise 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 uses at least some of the heat from the primary-side heat supply flow to raise the temperature of the low-temperature useful heat flow 236 by means of the fifth heat exchanger.

[0183] The transfer station 300 also includes a controller 340 and sensors S301, S302 to S319. Sensor S301 is located at the primary inlet 302a.2. Sensor S302 is located at the primary outlet 302a.4. Sensor S303 is located at the secondary inlet 302b.2. Sensor S304 is located at the primary outlet 302b.4. Sensor S305 is located at the primary inlet 306a.2. Sensor S306 is located at the primary outlet 306a.4. Sensor S307 is located at the secondary inlet 306b.2. Sensor S308 is located at the secondary outlet 306b.4. Sensor S309 is located at the primary inlet 308a.2. Sensor S310 is located at the primary inlet 308a.2 of the fifth heat exchanger. Sensor S311 is located at secondary outlet 308b.4. Sensor S312 is located at primary outlet 309a.4. Sensor S313 is located at secondary outlet 309b.4. Sensor S314 is located at primary inlet 304a.2. Sensor S315 is located at primary outlet 304a.4.Sensor S316 is located at the secondary inlet 304b.2. Sensor S317 is located at the district heating return line 330. Sensor S318 is located at the district heating supply line 320. Sensor S319 is located at the primary outlet 308a.4 of the fourth heat exchanger 308.

[0184] The sensors are temperature sensors. In one embodiment, the sensors are temperature and volume flow sensors and / or pressure sensors for measuring the temperature, heat flow, volume flow, and / or hydrodynamic and / or hydrostatic pressure of the heat transfer medium. In another embodiment, each sensor is a device by which a predetermined temperature, heat flow, volume flow, and / or pressure is set and / or transmitted. "Setting" refers, for example, to the adjustment of a predetermined value, such as by a dial or display. "Transmitting" refers to the transmission of a predetermined value, such as the temperature of the district heating supply line 320 by the district heating operator, or, for example, a predetermined temperature of the supply line 332b by a heating controller or heating system.

[0185] The sensors are communicatively connected to the controller 340. Each valve of the transfer station 300 comprises a machine. The machine of a valve is configured to influence the valve position. The machine is, for example, an electric actuator. The valves of the transfer station 300 are communicatively connected to the controller 340. Furthermore, the control of the machines in the individual valves (and thus the valve position) is carried out by the controller 340. The control of pumps P 301, P 302, and P 303 is carried out by the controller 340. The control of the individual pumps includes the control of the pump speed or flow rate. The speed is proportional to the flow rate and heat flow induced by the pump.

[0186] The exergetically optimal operating point of the transfer station 300 is determined by means of the controller 340. Determining the exergetically optimal operating point constitutes an optimization process. This optimization includes minimizing the temperature of the district heating return flow 330 and / or the heat flow of the district heating return flow 330, as well as a mathematical and / or physical system for the transfer station 300. Furthermore, the optimization can include one or more of the constraints described below, whereby the transfer station according to the invention is not limited to these constraints.

[0187] One requirement is the aforementioned hygiene regulation, according to which the temperature in the supply line of the domestic hot water circuit 334b ​​must be at least 60 °C. The temperature is determined by the S308 sensor.

[0188] Another requirement is the aforementioned hygiene regulation, according to which the temperature in the return line of the domestic hot water circuit 334a must be at least 55 °C. The temperature is determined by the S307 sensor.

[0189] Another requirement is the aforementioned hygiene regulation, which mandates a 16-hour circulation of the service water in service water circuit 334 per day. This 16-hour circulation is ensured by pump P303.

[0190] A further constraint is the minimization of limescale buildup on the first heat exchanger 302. Therefore, the second temperature increase of the cold water 338 should be achieved by a minimum temperature. The temperatures are determined by sensors S301, S302, S303 and / or S304.

[0191] A further constraint is the minimization of limescale buildup on the second heat exchanger 304. Therefore, the initial temperature increase of the cold water 338 should occur at a minimum temperature. The temperatures are determined by sensors S314, S315, S316 and / or S303.

[0192] A further constraint is the minimization of limescale buildup on the third heat exchanger 306. Therefore, the temperature increase of the domestic hot water supply 334a should be achieved by a minimum temperature. The temperatures are determined by sensors S306, S305, S307 and / or S308.

[0193] Another constraint is determined by the temperature of the flow pipe 332b. Accordingly, the temperature increase of the high-temperature heating circuit 332 via the fourth heat exchanger should correspond to the temperature of the flow pipe 332b. The corresponding temperature increase of the high-temperature heating circuit 332 is determined by sensors S309, S319, and / or S311. Alternatively, the temperature of the flow pipe 332b can be predefined.

[0194] Another constraint is determined by the temperature of the flow pipe 336b. Accordingly, the temperature increase of the low-temperature heating circuit 336, via the fifth heat exchanger, should correspond to the temperature of the flow pipe 336b. The corresponding temperature increase of the low-temperature heating circuit 336 is determined by sensors S310, S312, and / or S313. Alternatively, the temperature of the flow pipe 336b can be preset.

[0195] Another constraint is that heat is always transferred from the primary side to the secondary side via the individual heat exchangers.

[0196] A further constraint is provided by specifying the efficiency of the individual heat exchangers of transfer station 300. This allows, for example, the determination of the necessary primary inlet temperature for a given temperature increase using the heat exchanger.

[0197] Another constraint is determined by the temperature and / or heat flow of the district heating supply line 320, which defines the maximum temperature and / or heat flow at the transfer station 300. The temperature and / or heat flow of the district heating supply line 320 is determined by sensor S318.

[0198] The optimization itself is ensured by known optimization algorithms that find the exergetically optimal operating point subject to constraints. For this purpose, the 340 control system comprises a controller and / or a processor unit with a memory unit. The controller and / or processor unit receives sensor signals, processes these signals, solves the optimization problem, and transmits control instructions to the valves and pumps. The memory unit stores the sensor signals and / or predefined temperatures and / or the optimization algorithm and / or its parameters and / or the results of the optimization algorithm and / or controller and / or control variables.

[0199] One 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 domestic hot water supply 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.

[0200] One advantage of the 300 transfer station lies in the functional interaction of the heat exchangers 302, 306, 308, and 309, which together form the five-stage 300 transfer station. For example, this functional interaction results in a two- or three-stage temperature increase of the chilled water before it is introduced into the domestic hot water circuit, thus ensuring optimal exergetic utilization of the heat from the primary-side heat supply flow. Furthermore, this minimizes the risk of limescale buildup in the heat exchangers.

[0201] A further advantage of the transfer station 300 lies in the division of a heating circuit and the grouping of heating circuits according to their flow temperatures. Accordingly, in one embodiment, the transfer station 300 comprises a high-temperature and a low-temperature heating circuit, so that the primary-side heat supply flow is used exergetically in an optimal manner.

[0202] Another advantage of the transfer station 300 lies in the functional interaction of the residual heat from 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 utilizes the residual heat from the first heat exchanger 302.

[0203] A further advantage of the transfer station 300 lies in the functional interaction of the heat exchangers 302, 306, 308, and 309, the functional interaction of the residual heat from the individual heat exchangers 302, 306, 308, and 309, and 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, such as the aforementioned water supply or circulation mode. Instead, simultaneous operation of the water supply and circulation modes is possible.

[0204] A further advantage of the 300-unit heat transfer station lies in its comprehensive control and / or regulation capability for the heat from the primary-side heat supply flow to the primary-side heat supply flow and the first, second, and third secondary-side heat discharge flows. This control and / or regulation capability is achieved by means of the valves and pumps of the 300-unit heat transfer station. This allows the exergetically optimal operating point to be maintained even under changing consumer behavior, such as time-varying heat supply from the primary-side heat supply flow and / or time-varying heat demand from the primary-side heat supply flow and / or time-varying heat demand from the first, second, and / or third secondary-side heat discharge flows.

[0205] Figure 4 This shows a transfer station 400. Transfer station 400 corresponds to transfer station 300 from Figure 3Furthermore, transfer station 400 is shown for a specific time and at an exergetically optimal operating point. This exergetically optimal operating point is defined by temperatures in Figure 4 depicted.

[0206] In this embodiment, the supply line of the district heating system 320 has a temperature of 71°C. The return line of the district heating system has a temperature of 10°C. The cold water 338, before it is introduced into the domestic hot water circuit 334, has a temperature of 9°C.

[0207] The first temperature increase of the cold water 338 is achieved via the second heat exchanger 304 from 9°C to 28°C. The second temperature increase of the cold water 338 is achieved via the first heat exchanger 302 from 28°C to 40°C. After the first and second temperature increases, the cold water 338 does not have the temperature of 60°C required by hygiene regulations for its introduction into the domestic hot water supply 334b. Therefore, the cold water 338 is introduced into the domestic hot water return 334a, which has a temperature of 55°C before this introduction. The position of valve V304 is adjusted accordingly.

[0208] The mixed or averaged temperature of the domestic hot water return 334a and the cold water 338 is 48°C. The temperature of the domestic hot water circuit 334 is raised from 48°C to 60°C by means of the third heat exchanger 306. Simultaneously, the temperature of the cold water 338 is raised from 40°C to 60°C.

[0209] The temperature of the high-temperature heating circuit 332 is increased from 35°C to 48°C by means of the fourth heat exchanger 308. The temperature of the low-temperature heating circuit 336 is increased from 28°C to 32°C by means of the fifth heat exchanger 309.

[0210] For the second temperature increase of the chilled water 338, heat is used partly from the district heating supply 320a and partly from the residual heat of the first heat exchanger 302.4, via valve V301. The position of valve V301 is therefore such that a temperature of 41°C is provided at the primary inlet 302a.2. During the second temperature increase of the chilled water 338, heat is transferred from the primary side 302a to the secondary side 302b, resulting in a temperature of 29°C at the primary outlet. This results in an average temperature difference of 1°C between the primary side 302a and the secondary side 302b.

[0211] To raise the temperature of the domestic hot water circuit 334, heat is drawn partly from the district heating supply 320b and partly from the residual heat of the third heat exchanger 306.8 via valve V302. The position of valve V302 is therefore such that a temperature of 61°C is provided at the primary inlet 306a.2. By raising the temperature of the domestic hot 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 of 1°C between the primary side 302a and the secondary side 302b.

[0212] To raise the temperature of the high-temperature heating circuit 332, the residual heat from the third heat exchanger 306.2 is utilized by means of valves V303, V305, and V306. Valve V303 is therefore closed. Valves V305 and V306 supply the residual heat from the third heat exchanger to the primary inlet 308a.2.

[0213] The temperature increase of the low-temperature heating circuit 336 can be achieved using valves V307 and V306, i.e., with the residual heat from the fourth heat exchanger 306.2. Valves V307 and V306 can be adjusted to supply the residual heat from the fourth heat exchanger to the primary inlet 309a.2.

[0214] For the initial temperature increase of the cold water 338, the residual heat from the fifth heat exchanger 309.2 and the residual heat from the first heat exchanger 302.2 are utilized by means of valves V309 and V308. The position of valve V309 is therefore set such that the residual heat from the first heat exchanger is not directly fed into the return line of the district heating system 330. Similarly, the position of valve V308 is set such that the residual heat from the fifth heat exchanger is not directly fed into the return line of the district heating system 330.

[0215] Figure 5 shows a flowchart of an embodiment of method 600 for the transfer of heat by means of a heat transfer station. Figure 5Figure 1 shows an embodiment of a heat transfer method according to one aspect of the invention, which is implemented, for example, in a transfer station 100, 200, 300, 400. The heat transfer method in a transfer station comprises steps 604, 606, 608, 610, 612 and 614.

[0216] Step 604 involves an initial temperature increase of a secondary-side heat input flow before it is introduced into a second secondary-side heat output flow. This initial temperature increase of the secondary-side heat input flow is achieved using a second heat exchanger, which utilizes residual heat from a fourth heat exchanger and / or residual heat from the first heat exchanger.

[0217] Step 606 involves a second temperature increase of the secondary-side heat input flow before it is introduced into a second secondary-side heat output flow. This second temperature increase of the secondary-side heat input flow occurs after the first temperature increase. The second temperature increase of the secondary-side heat input flow is achieved using a first heat exchanger, which partially utilizes a primary-side heat input flow for this purpose.

[0218] Step 608 involves introducing the secondary-side heat input flow into the second secondary-side heat output flow. This introduction occurs after the first and second temperature increases of the secondary-side heat input flow.

[0219] Step 609 is optional and comprises a third temperature increase of the secondary-side heat supply flow. In one embodiment of method 600, the secondary-side heat supply flow has not reached a target temperature after its first and second temperature increases. Therefore, the secondary-side heat supply flow undergoes a third temperature increase by means of a third heat exchanger. If, in another embodiment of method 600, the secondary-side heat supply flow has reached a target temperature after its first and second temperature increases, then step 609 is not required.

[0220] The step sequence 604, 606 and 608 (and 609) are repeated successively.

[0221] Step 610 involves raising the temperature of a second secondary-side heat removal flow using the third heat exchanger, which partially utilizes the primary-side heat input flow for this purpose.

[0222] Step 612 involves circulating the second secondary-side heat removal flow.

[0223] Steps 610 and 612 are repeated successively and are also independent of the step sequence 604, 606, 608 (and 609).

[0224] Step 614 involves raising the temperature of a first secondary-side heat removal flow by means of a fourth heat exchanger, which uses partly the primary-side heat input and / or partly the residual heat from the third heat exchanger.

[0225] Step 614 is repeated successively. Furthermore, step 614 is independent of the step sequence 604, 606, 608 (and 609) and the step sequence 610, 612.

[0226] 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 described in DE 10 210 019 727 B4. 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. Reference symbol list:

[0227] 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, 206.10, 208.2, 208.4, 208.6, 209.2, 302.2, 302.4, 306.2, 306.4, 306.8, 306.10, 308.2, 308.4, 309.2 residual heat 120, 220, 320 primary-side heat supply flow 120a, 120b, 120c, 220a, 220b, 220c, 320a, 320b, 320c partial primary-side heat supply flow 132, 232, 332 First secondary-side heat dissipation flow 134, 234, 334 Second secondary-side heat dissipation flow 236, 336 Third secondary-side heat dissipation stream 138, 238, 338 secondary-side heat input flow P301, P302, P302 pump S301, S302, ..., S319 sensor V301, V302, ..., V310 Distribution valve 340 steering

Claims

1. A transfer station (100, 200) comprising - a primary-side heat supply stream (120), - a first (132) and a second secondary-side heat removal stream (134), - a secondary-side heat supply stream (138), and - a first (102), second (104), third (106), and fourth heat exchanger (108); wherein a fluid serves as the means for transferring heat, and the heat exchangers are fluidically coupled such that, in operation of the transfer station, - the secondary-side heat supply stream, before it is introduced into the second secondary-side heat removal stream, undergoes a first temperature increase and a second temperature increase, the first temperature increase occurring before the second temperature increase; - the second temperature increase is performed by the first heat exchanger, which for this purpose partially uses the primary-side heat supply; - the first temperature increase is performed by the second heat exchanger, which for this purpose partially uses residual heat of the fourth heat exchanger and / or partially uses residual heat of the first heat exchanger; - a temperature increase of the second secondary-side heat removal stream is performed by the third heat exchanger, which for this purpose partially uses the primary-side heat supply stream; - a temperature increase of the first secondary-side heat removal stream is performed by the fourth heat exchanger, which for this purpose partially uses the residual heat of the third heat exchanger and / or partially uses the primary-side heat supply; - the second secondary-side heat removal stream is a domestic water circuit comprising a domestic water return (334a) and a domestic water supply (334b); - the secondary-side heat supply stream is water from outside the domestic water circuit; - the introduction of the water from outside the domestic water circuit into the domestic water circuit takes place before the temperature increase of the domestic water circuit, by coupling a secondary outlet (302b.4) of the first heat exchanger to the domestic water return (334a); - the primary-side heat supply stream is directly connected to a primary inlet of the third heat exchanger and to a primary inlet of the first heat exchanger.

2. The transfer station according to claim 1, wherein the heat exchangers are further fluidically coupled such that, in operation of the transfer station, - the first temperature increase is performed by the second heat exchanger, which for this purpose partially uses residual heat of the fourth heat exchanger and / or partially uses residual heat of the first heat exchanger and / or partially uses residual heat of the third heat exchanger; and - the second temperature increase is performed by the first heat exchanger, which for this purpose partially uses the primary-side heat supply and / or partially uses residual heat of the first heat exchanger.

3. The transfer station according to any one of the preceding claims, further comprising - a fifth heat exchanger, and - a third secondary-side heat removal stream, wherein the heat exchangers are further fluidically coupled such that, in operation of the transfer station, - a temperature increase of the third secondary-side heat removal stream is performed by the fifth heat exchanger, which for this purpose partially uses residual heat of the fourth heat exchanger and / or partially uses residual heat of the third heat exchanger; and - the first temperature increase is performed by the second heat exchanger, which for this purpose partially uses residual heat of the fourth heat exchanger and / or partially uses residual heat of the first heat exchanger and / or partially uses residual heat of the third heat exchanger and / or residual heat of the fifth heat exchanger.

4. The transfer station according to any one of the preceding claims, wherein - the secondary-side heat supply stream, after introduction into the second secondary-side heat removal stream, undergoes a third temperature increase; wherein the heat exchangers are further fluidically coupled such that, in operation of the transfer station, - the third temperature increase occurs together with the temperature increase of the second secondary-side heat removal stream; and - the third temperature increase occurs after the second temperature increase.

5. The transfer station according to any one of the preceding claims, insofar as dependent on claim 3, wherein - the primary-side heat supply stream is a supply flow of a district heating network or a local heating network; - the first secondary-side heat removal stream is a first secondary-side useful heat circuit; - the third secondary-side heat removal stream is a second secondary-side useful heat circuit.

6. The transfer station according to claim 5, wherein the domestic water circuit has a pump, and, in operation of the transfer station, circulation of the domestic water in the domestic water circuit occurs by means of a pump and with the introduction of water from outside the domestic water circuit into the domestic water circuit.

7. The transfer station according to any one of the preceding claims, wherein the heat exchangers are further fluidically coupled such that, in operation of the transfer station, the primary-side heat supply stream is used for the second temperature increase of the secondary-side heat supply stream by means of the first heat exchanger, and at the same time the primary-side heat supply stream is used for the temperature increase of the second secondary-side heat removal stream by means of the third heat exchanger.

8. The transfer station according to claim 5 or 6, wherein - the domestic water circuit is a drinking water circuit; - the first secondary-side useful heat circuit is a first heating circuit; - the second secondary-side useful heat circuit is a second heating circuit; - wherein, in operation of the transfer station, a return temperature of the first heating circuit is higher than a return temperature of the second heating circuit.

9. The transfer station according to any one of the preceding claims, wherein the second heat exchanger is a heat exchanger and a heat store.

10. The transfer station according to any one of the preceding claims, insofar as dependent on claim 2 or 3, wherein the second heat exchanger is configured to partially store residual heat of the fourth heat exchanger and / or partially store residual heat of the first heat exchanger and / or partially store residual heat of the third heat exchanger and / or store residual heat of the fifth heat exchanger.

11. The transfer station according to any one of the preceding claims, wherein the second heat exchanger is a shell-and-tube heat exchanger.

12. A method for transferring heat in a transfer station comprising a first (102), second (104), third (106), and fourth heat exchanger (108), comprising - a first and a second increase of the temperature of a secondary-side heat supply stream, wherein - the first and the second increase of the temperature of the secondary-side heat supply stream take place before it is introduced into the second secondary-side heat removal stream; - the first increase of the temperature of the secondary-side heat supply stream takes place before the second increase of the temperature of the secondary-side heat supply stream; - the second increase of the temperature of the secondary-side heat supply stream is performed by the first heat exchanger, which for this purpose partially uses a primary-side heat supply; - the first increase of the temperature of the secondary-side heat supply stream is performed by the second heat exchanger, which for this purpose partially uses residual heat of the fourth heat exchanger and / or partially uses residual heat of the first heat exchanger; - an increase of the temperature of a second secondary-side heat removal stream is performed by the third heat exchanger, which for this purpose partially uses the primary-side heat supply; and - an increase of the temperature of a first secondary-side heat removal stream is performed by the fourth heat exchanger, which for this purpose partially uses the primary-side heat supply and / or partially uses the residual heat of the third heat exchanger; - the second secondary-side heat removal stream is a domestic water circuit comprising a domestic water return (334a) and a domestic water supply (334b); - the secondary-side heat supply stream is water from outside the domestic water circuit; - the introduction of the water from outside the domestic water circuit into the domestic water circuit takes place before the temperature increase of the domestic water circuit and / or after the temperature increase of the domestic water circuit by coupling a secondary outlet (302b.4) of the first heat exchanger to the domestic water return (334a) and a domestic water supply (334b); - the primary-side heat supply stream is directly connected to a primary inlet of the third heat exchanger and to a primary inlet (302a.2) of the first heat exchanger.

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