EP4050269A1 - Heating device, heating system and method - Google Patents

Abstract

The invention relates to a heating device (15), a heating system (10) and a method for de-icing the heating device (10), the heating device (15) having a heat pump (30) with a first heat exchanger (90) and a thermal fluid transport device (35). a primary circuit pump (125), at least one first heating circuit connection (150) and a second heating circuit connection (155), wherein the thermal fluid transport device (35) can be filled with a thermal fluid (170) and is designed to transport and distribute the thermal fluid (170). , wherein a first secondary side (120) of the first heat exchanger (90) is fluidically connected to the first and/or second heating circuit connection (150, 155), the thermal fluid transport device (35) having a small reservoir (135) for temporarily storing the thermal fluid (170). , The small reservoir (135) being fluidically connected to the first heating circuit connection (150) and/or to the first secondary side (120) of the first heat exchanger (90). Is nden, wherein the primary circuit pump (125) is designed to promote the thermal fluid (170) between the first secondary side (120) and the small storage (135).

Description

The invention relates to a heating device according to patent claim 1, a heating system according to patent claim 11 and a method according to patent claim 12.

State of the art

From the EP 2 853 844 A1 a method for de-icing a heat pump, which has a refrigerant circuit with a compressor, a condenser and an evaporator, is known. A controllable, variable-speed fan is assigned to the evaporator.

Disclosure of Invention

It is an object of the invention to provide an improved heater, an improved heating system and an improved method for de-icing a heater.

This object is achieved by means of a heating device according to patent claim 1, a heating system according to patent claim 11 and a method according to patent claim 12.

Advantageous embodiments are specified in the dependent claims.

It was recognized that an improved heating device for heating a building can be provided in that the heating device has a heat pump with a first heat exchanger. Furthermore, the heating device a thermal fluid transport device with a primary circuit pump, at least one first heating circuit connection and a second heating circuit connection. The thermal fluid transport device can be filled with a thermal fluid. The thermal fluid transport device is designed to transport and distribute the thermal fluid. A first secondary side of the first heat exchanger is fluidically connected to the first and/or second heating circuit connection. Furthermore, the thermal fluid transport device has a small reservoir for temporarily storing the thermal fluid. The small storage tank is fluidically connected to the first heating circuit connection and/or to the first secondary side of the first heat exchanger. The primary circuit pump is designed to convey the thermal fluid between the first secondary side and the small storage tank.

The small storage tank has the advantage that, in addition to a first heating circuit that can be connected to the first heating circuit connection, a second heat can be temporarily stored in the small storage tank by means of the thermal fluid, so that even with a closed first heating circuit or with a slightly open first heating circuit there is sufficient second heat to defrost a first heat exchanger can be provided in the heat pump.

It is of particular advantage if the small storage tank is arranged parallel to the first heating circuit and the second heating circuit connection. This ensures that warm thermal fluid flows safely through the small accumulator even when the first heating circuit is closed and/or the first heating circuit is slightly open.

In a further embodiment, the small storage tank is arranged in series between the first heating circuit connection and the first secondary side of the first heat exchanger. The small accumulator can be connected upstream of the first heating circuit connection in relation to a conveying direction of the thermal fluid. This configuration has the advantage that the thermal fluid must flow through the small storage tank on the way to the first heating circuit connection and the small storage tank is therefore filled with warm thermal fluid at an early stage. This configuration has the advantage that when the second heat exchanger is de-iced, sufficient second heat can also be made available very early by the small storage tank, in order to prevent the building from cooling down on the one hand, but at the same time to ensure reliable de-icing of the second heat exchanger.

In a further embodiment, at least one first secondary circuit pump is arranged between the small storage tank and the first heating circuit connection. The first secondary circuit pump is designed to convey the thermal fluid between the small storage tank and the first heating circuit connection. This configuration has the advantage that sufficient pressure can be provided for the thermal fluid at the first heating circuit connection. This ensures a sufficiently high mass flow through the first heating circuit with the heating fluid when the heating device is installed in the building to the heating system.

In a further embodiment, the thermal fluid transport device has an overflow valve, the overflow valve having a closed position and an open position. The overflow valve is switched to the closed position when the pressure at the overflow valve falls below a predefined opening pressure. The overflow valve is switched to the open position when the predefined opening pressure at the overflow valve is exceeded. The overflow valve is arranged parallel to the first heating circuit connection and the second heating circuit connection. This configuration ensures that a sufficient flow of thermal fluid is ensured even when the first heating circuit is closed or the first heating circuit is only slightly open within the thermal fluid transport device, so that the small reservoir is reliably filled with warm thermal fluid. This configuration is particularly suitable if the small storage tank is connected in series with the first heating circuit connection and the overflow valve.

In a further embodiment, the heating device has a hot water storage tank with a storage tank and a hot water heat exchanger arranged in the storage tank. The storage tank is designed to store hot water. The thermal fluid transport device has a three-way valve, with a first valve connection of the three-way valve being fluidically connected to the second heating circuit connection and a second valve connection of the three-way valve being fluidically connected to the primary circuit pump. A first page of the hot water heat exchanger is fluidically connected to a first branch arranged between the first secondary side and the small accumulator. A second side of the hot water heat exchanger is fluidly connected to a third valve port of the three-way valve. The three-way valve has a first valve position and at least one second valve position that differs from the first valve position. In the first valve position, the three-way valve fluidically connects the second heating circuit connection to the primary circuit pump. In the second valve position, the three-way valve fluidly connects the second side of the hot water heat exchanger to the primary circuit pump. This configuration has the advantage that, if sufficient heat cannot be provided by the small storage tank and the first heating circuit for de-icing the second heat exchanger of the heat pump, a second proportion can also be provided by adjusting the three-way valve from the first valve position to the second valve position the second heat can be taken from the hot water tank to defrost the second heat exchanger.

In a further embodiment, the small storage tank has a first storage connection and a second storage connection, the first storage connection being connected between the first branch and the first heating circuit connection. The second storage connection is connected between the second heating circuit connection and the three-way valve. This configuration has the advantage that a circulating volume of the thermal fluid is particularly large in the first valve position and as a result a particularly large amount of second heat can be provided for de-icing the second heat exchanger.

In a further embodiment, the small storage tank has a first storage connection and a second storage connection, the first storage connection being fluidically connected to the first branch and the second storage connection being fluidically connected to the first heating circuit connection, the small storage tank being fluidically connected to the first branching with the first heating circuit connection. This ensures early heating of the small storage tank, so that if unfavorable environmental conditions require early de-icing, for example after heating the water in the hot water storage tank, sufficient second heat can be drawn from the small storage tank, even if the first heating circuit is not yet essentially fully heated, for example.

In a further embodiment, the heating device has an outdoor unit and an indoor unit, the heat pump being arranged in the outdoor unit and having at least one second heat exchanger, the second heat exchanger being fluidically connected to the first heat exchanger for heat exchange. The thermal fluid transport device and the small storage tank are arranged in the indoor unit. This configuration ensures that the outdoor unit can be designed to be particularly compact and at the same time that reliable de-icing is ensured.

In a further embodiment, the heating device has a fluid line for guiding the thermal fluid, the fluid line having at least one curved section. The curved section encloses at least one angle of at least 45°, preferably at least 90°. The fluid line has at least one plastic and is preformed. The fluid line is preferably arranged stress-free or low-stress. As a result, the fluid line can be routed at a particularly small distance. Furthermore, geometries that cannot be produced with conventional copper tubing to form the fluid line are possible using the preformed plastic fluid line.

It was recognized that an improved heating system can be provided in that the heating system has a heating device and at least a first heating circuit. The heating device is designed as described above. The first heating circuit is connected to the first heating circuit connection and to the second heating circuit connection and is filled with the thermal fluid. The primary circuit pump is designed to conduct the thermal fluid between the small storage tank and the first secondary side of the first heat exchanger.

A particularly advantageous method for de-icing a heating device with a heat pump, a hot water storage tank and a thermal fluid transport device can be provided in that the heat pump has a compressor integrated into a refrigerant circuit, a first heat exchanger and a second heat exchanger. A heating mode and a de-icing mode can be provided for operating the heating device. In the heating mode, the refrigerant circuit is operated in a normal direction, with a first heat being absorbed by the second heat exchanger and being at least partially given off to the refrigerant. From the first heat exchanger, the first heat is absorbed by the refrigerant and transferred to the thermal fluid for heating the thermal fluid. In a de-icing mode, the heat pump is operated in the opposite direction to the normal direction for targeted heating of the second heat exchanger. A primary circuit pump of the thermal fluid transport device is activated and the heated thermal fluid is conveyed to the first heat exchanger. The second heat is transferred from the thermal fluid to the refrigerant, the refrigerant circulating in the refrigerant circuit in a direction opposite to its normal direction, and the refrigerant transferring the second heat to the second heat exchanger. The second heat exchanger is defrosted with the second heat. When a predefined operating parameter of the heating device is reached, in particular a temperature of the thermal fluid, the thermal fluid is conducted through the hot water tank and the second heat is at least partially removed from the hot water tank for de-icing the second heat exchanger. This configuration has the advantage that reliable de-icing is ensured even under unfavorable weather conditions.

In a further embodiment, the thermal fluid is conveyed from a small reservoir of the thermal fluid transport device to the first heat exchanger in the de-icing mode before the predefined operating parameter is reached. The second heat for defrosting the second heat exchanger is transferred from the thermal fluid stored in the small storage unit to the first heat exchanger. This configuration has the advantage that the heating system can be operated particularly conveniently.

In a further embodiment, the primary circuit pump is controlled in the heating mode in such a way that the thermal fluid has a pressure that is greater than an opening pressure of an overflow valve of the thermal fluid transport device.

Fig. 1

eine schematische Darstellung eines Heizsystems gemäß einer ersten Ausführungsform;

Fig. 2

ein Ablaufdiagramm eines Verfahrens zum Betrieb des in Fig. 1 gezeigten Heizsystems;

Fig. 3

eine schematische Darstellung eines Heizsystems gemäß einer zweiten Ausführungsform;

Fig. 4

eine schematische Darstellung eines Heizsystems gemäß einer dritten Ausführungsform;

Fig. 5

eine schematische Darstellung eines Heizsystems gemäß einer vierten Ausführungsform;

Fig. 6

eine perspektivische Darstellung einer Heizeinrichtung eines Heizsystems gemäß einer fünften Ausführungsform;

Fig. 7

einen in Fig. 6 markierten Ausschnitt A des in Fig. 6 gezeigten Heizsystems; und

The invention is explained below with reference to figures. show:

1

a schematic representation of a heating system according to a first embodiment;

2

a flowchart of a method for operating the in 1 heating system shown;

3

a schematic representation of a heating system according to a second embodiment;

4

a schematic representation of a heating system according to a third embodiment;

figure 5

a schematic representation of a heating system according to a fourth embodiment;

6

a perspective view of a heating device of a heating system according to a fifth embodiment;

7

one in 6 marked section A of the in 6 heating system shown; and

8 and 9 Plan views of an in 6 marked section B.

1 shows a schematic representation of a heating system 10 according to a first embodiment.

The heating system 10 has a heating device 15 , at least one first heating circuit 20 and a water supply device 25 . The first heating circuit 20 can have one or more radiators, for example. The water supply device 25 can have, for example, one or more water lines for supplying the heating device 15 and the building with water, in particular with drinking water.

In the embodiment, the heating device 15 is designed as an air-water heat pump, for example. The heating device 15 has a heat pump 30 , a thermal fluid transport device 35 and preferably a hot water tank 40 . In the embodiment, for example, the heater 15 is divided into an outdoor unit 45 and an indoor unit 50 . In this case, for example, the outdoor unit 45 can be arranged outside the building. For example, the outdoor unit 45 can be designed as an outdoor installation device. The outdoor unit 45 can also be arranged in the building and be fluidically connected to an environment 405 of the building via a fresh air duct, for example.

The indoor unit 50 can, for example, be in the form of an indoor set-up device and is arranged in the building. A multi-part configuration of the internal unit 50 can also be provided. In particular, the integration of the hot water tank 40 in the internal unit 50 can be dispensed with and, for example, the hot water tank 40 can be set up next to the internal unit 50 .

The hot water tank 40 has, for example, a fresh water connection 55 and a hot water connection 60 . Furthermore, the hot water storage tank 40 has a storage tank 65 and a hot water heat exchanger 70 arranged in the storage tank 65 . In addition, the hot water tank 40 can have a circulation connection 75 . The circulation connection 75 can also be omitted. The fresh water connection 55 can be fluidically connected, for example, to a fresh water network, in particular a drinking water network. Furthermore, the fresh water connection 55 is connected to the storage tank 65 by means of a fresh water line 80 . The storage tank 65 is thermally insulated and stores 10 hot water during operation of the heating system. The hot water connection 60 is in turn fluidly connected to the storage tank 65 by means of a hot water line 85 . The water supply device 25 is connected to the fresh water connection 55 and the hot water connection 60 in order to fluidly connect an extraction point 76 to the hot water tank 40 .

The heat pump 30 has a first heat exchanger 90, a second heat exchanger 95, a refrigerant circuit 100 and a compressor 105 and an expansion valve 110 on. The refrigerant circuit 100 is filled with a refrigerant 115 . The refrigerant 115 can be R410 or R290, for example.

The first heat exchanger 90 has a first primary side and a first secondary side 120, the first primary side of the first heat exchanger 90, the expansion valve 110, a second secondary side of the second heat exchanger 95 and the compressor 105 being integrated into the refrigerant circuit 100.

The thermal fluid transport device 35 has at least one primary circuit pump 125, preferably an electric auxiliary heater 130, a small reservoir 135, preferably a first secondary circuit pump 140, a three-way valve 145, a first heating circuit connection 150 and at least one second heating circuit connection 155. In addition, the thermal fluid transport device 35 can have an expansion vessel 160 and/or optionally a safety valve 165 .

The thermal fluid transport device 35 is filled with a thermal fluid 170 . The thermal fluid 170 can, for example, contain water and optionally an additional additive, in particular an antifreeze. The thermal fluid 170 is preferably present in the liquid state in the thermal fluid transport device 35 .

The primary circuit pump 125 has a first input side and a first output side. The first output side of the primary circuit pump 125 is fluidically connected to the first secondary side 120 of the first heat exchanger 90 by means of a first fluid line 175 . On the outlet side of the first heat exchanger 90 , the first secondary side 120 is connected to the electric auxiliary heater 130 via a second fluid line 180 , for example. Electrical auxiliary heater 130 is connected to a first branch 190 via a third fluid line 185 on a side facing away from second fluid line 180 . A fourth fluid line 195 is connected to the first branch 190 and connects a first side 200 of the hot water heat exchanger 70 to the first branch 190 . A fifth fluid line 205 fluidly connects the first branch 190 to a second branch 210. Both the first branch 190 and the second branch 210 can be designed as a T-branch, for example.

The small memory 135 has a first memory connection 215 and a second memory connection 220 . The second storage port 220 is arranged opposite to the first storage port 215 . A storage container 225 of the small storage device 135 extends between the first storage connection 215 and the second storage connection 220. The storage container 225 is thermally insulated and has a significantly smaller capacity for temporarily storing the thermal fluid 170 than the storage tank 65. For example, the storage tank 65 can have a volume from 150 to 300 liters, while for example the storage tank 225 has a volume of 15 to 25 liters, preferably 15 to 20 liters. The small storage tank 135 can, for example, be in the form of a solar upstream vessel. The storage container 225 connects the first storage connection 215 to the second storage connection 220. The storage container 225 is designed in such a way that a quasi-short circuit between the first storage connection 215 and the second storage connection 220 is avoided. In particular, the storage tank 225 can, for example, be of tubular design, with the storage connection 215 , 220 being arranged at one end of the storage tank 225 in each case.

The first storage port 215 is connected to the second branch 210 by means of a sixth fluid line 230 . Furthermore, the second branch 210 is connected to a second input side of the first secondary circuit pump 140 on a side opposite the fifth fluid line 205 by means of a seventh fluid line 235 . Thus, the second branch 210 is arranged directly upstream of the first secondary circuit pump 140 and the first branch 190 is arranged upstream of the second branch 210 . Downstream of the first secondary circuit pump 140 , the first secondary circuit pump 140 is connected to the first heating circuit connection 150 on its second outlet side by means of an eighth fluid line 240 . The first heating circuit 20 is connected, for example, to the first heating circuit connection 150 on one side and to the second heating circuit connection 155 on the other side. In this case, for example, the first heating circuit connection 150 can form a flow connection for the first heating circuit 20 and the second heating circuit connection 155 can form a return connection for the first heating circuit 20 .

The second heating circuit connection 155 is connected to a first junction 250 by means of a ninth fluid line 245 . The first junction 250 can be T-shaped, for example. A tenth fluid line 255 is connected to the first junction 250 and fluidly connects the first junction 250 to the second storage port 220 .

The three-way valve 145 has a first valve port 260 , a second valve port 265 and a third valve port 270 . The first valve port 260 is fluidically connected to the first junction 250 by means of an eleventh fluid line 275 . A twelfth fluid line 280 fluidly connects the first input side of the primary circuit pump 125 to the second valve port 265 of the three-way valve 145. A thirteenth fluid line 285 is also connected to the third valve port 270, which connects a second side 290 of the hot water heat exchanger 70 to the third valve port 270 fluidly connects.

Optionally, for example, the safety valve 165 can be connected to the twelfth fluid line 280 downstream of the second valve connection 265 . Furthermore, for example, the expansion vessel 160 can be connected fluidically to the twelfth fluid line 280 between the safety valve 165 and the first input side of the primary circuit pump 125 .

The control system 39 has, for example, a control unit 300, an outside temperature sensor 305, a first temperature sensor 310, preferably a second temperature sensor 315, a pressure sensor 320 and/or a storage temperature sensor 330.

Control device 300 has a data memory 335 , a control device 340 and an interface 345 . The data memory 335 is connected to the control device 340 by means of a first connection 346 . Furthermore, the control device 340 is connected to the interface 345 by means of a second connection 347 .

At least one predefined operating parameter is stored in the data memory 335, for example. Furthermore, a predefined control algorithm, which is embodied as a computer program, for example, can be stored in the data memory 335 . Furthermore, a first to third predefined temperature threshold value S1, S2, S3, a predefined heating curve and a predefined maximum permissible icing state are stored in the data memory. The predefined second temperature threshold S2 can be the predefined operating parameter.

The outside temperature sensor 305 measures an outside temperature TA. The first temperature sensor 310 is arranged, for example, on the seventh fluid line 235 and measures a first temperature T1 of the thermal fluid 170 upstream of the second input side of the first secondary circuit pump 140. The second temperature sensor 315 is arranged on the output side of the first heat exchanger 90 and measures a second temperature T2 of the thermal fluid 170 in the third fluid line 185. The pressure sensor 320 is arranged in the refrigerant circuit 100 and measures a pressure of the refrigerant 115.

The interface 345 is connected to the outside temperature sensor 305 by means of a third connection 350 . Furthermore, the interface 345 is connected to the compressor 105 via a fourth connection 355 . A fifth connection 360 connects the three-way valve 145 to the interface 345. A sixth connection 365 connects the interface 345 to the primary circuit pump 125 and a seventh connection 370 connects the first secondary circuit pump 140 to the interface 345. An eighth to eleventh connection 375 to 395 connects the first temperature sensor 310 and the second temperature sensor 315 as well as the storage tank temperature sensor 330 to the interface 345.

The connection 346, 347, 350, 355, 360, 365, 370, 375, 380, 385, 395 can be both wireless and wired. Furthermore, the first to eleventh connection 346, 347, 350, 355, 360, 365, 370, 375, 380, 385, 395 can be part of a bus system, in particular a Modbus system, for example. A different configuration of the first to eleventh connection would also be possible.

Furthermore, it is pointed out that the number of temperature sensors 310, 315, 330 and the connections 346, 347, 350, 355, 360, 365, 370, 375, 380, 385, 395 is exemplary. A different configuration of the control system 39 would also be possible.

In 1 the connection 346, 347, 350, 355, 360, 365, 370, 375, 380, 385, 395 is an example for easier differentiation from the fluid lines 175, 180, 185, 195, 205, 230, 235, 240, 245, 255 , 275, 280, 285, 435, 445, 455 are represented by dashed lines. By means of the connection 346, 347, 350, 355, 360, 365, 370, 375, 380, 385, 395, a data/control signal with information can be transmitted, for example. The data/control signal can be transmitted digitally or analogously.

The three-way valve 145 has a first valve position and a second valve position that differs from the first valve position. In the first valve position, the three-way valve 145 connects the eleventh fluid line 275 to the twelfth fluid line 280, so that the second storage port 220 is connected via the tenth fluid line 255 and the first junction 250 to the first input side of the primary circuit pump 125. Likewise, in the first valve position, the second heating circuit connection 155 is fluidically connected via the ninth fluid line 245 , the first junction 250 and the eleventh fluid line 275 by means of the twelfth fluid line 280 to the first input side of the primary circuit pump 125 .

In the second valve position of the three-way valve 145, the eleventh fluid line 275 is fluidically decoupled from the twelfth fluid line 280, so that both the second heating circuit connection 155 and the second accumulator connection 220 are fluidically isolated from the twelfth fluid line 280 and thus from the first input side of the primary circuit pump 125 are separated. In the second valve position, the thirteenth fluid line 285, which fluidly connects the second side 290 of the hot water heat exchanger 70 to the third valve port 270, is fluidly connected to the twelfth fluid line 280, so that the second side 290 of the hot water heat exchanger 70 via the three-way valve 145 is connected fluidically continuously to the first input side of the primary circuit pump 125 .

In the embodiment, the three-way valve 145 is switched such that the three-way valve 145 accommodates either the first valve position or the second valve position. The first valve position thus forms the alternative to the second valve position. In a further development, the three-way valve 145 can also be designed as a mixing valve which, in a mixing position, assumes both the first valve position and the second valve position, thereby fluidically connecting both the second side 290 of the hot water heat exchanger 70 to the first input side of the primary circuit pump 125 and also connects the second heating circuit connection 155 and the second storage connection 220 to the first input side of the primary circuit pump 125 .

2 shows a flowchart of a method for operating the in 1 shown heating system 10.

The heating system 10 has at least two, preferably three operating states, as described below in the embodiment.

In a first operating state, which can also be referred to as the first heating mode, the heating system 10 heats the heating circuit 20 in order to heat a room in a building. In a second operating state, which can also be referred to as a second heating mode, fresh water introduced into the storage tank 65 is heated and made available in a heated state via the water supply device 25, for example at the extraction point 76 as hot water.

In a third operating mode, the second heat exchanger 95 is de-iced in a de-icing mode in order to ensure the functionality of the heat pump 30 for heating the thermal fluid 170 . The icing of the second heat exchanger 95 occurs above all in the case of high humidity in connection with an outside temperature around the freezing point.

Before the method described below is carried out, the first temperature sensor 310 measures the first temperature T1 of the thermal fluid 170 on the inlet side of the first secondary circuit pump 140. The outside temperature sensor 305 also measures the outside temperature TA. The controller 340 takes into account the first temperature T1 and the outside temperature when controlling the compressor 105 and the primary circuit pump 125 as well as the first secondary circuit pump 140.

Based on the outside temperature TA and the heating curve, which can be set by the customer on the device, there is a target value for the first temperature T1. If the measured value of the first temperature T1 is less than the setpoint, control device 340 recognizes a heat requirement for the first heating circuit 20.

In a first method step 505, the heating device 15 is switched to the first heating mode. The control device 340 activates the compressor 105 and the compressor 105 conveys the refrigerant 115 in the refrigerant circuit 100 in a normal direction. In this case, a first heat Q - ₁ is taken from the environment 405 by a source medium, for example by fresh air conveyed to the second heat exchanger 95 . The first heat Q - ₁ is transferred from the second heat exchanger 95 via the refrigerant circuit 100 to the first primary side of the first heat exchanger 90 . In the first heat exchanger 90, the first heat Q - ₁ is at least partially transferred from the refrigerant 115 to the thermal fluid 170 and the thermal fluid 170 is heated. Furthermore, the primary circuit pump 125 is activated in the first operating state, so that the primary circuit pump 125 delivers the thermal fluid 170 . The thermal fluid 170 is conveyed from the first secondary side 120 of the first heat exchanger 90 via the second fluid line 180 to the electric auxiliary heater 130 . In the first operating state, the electric auxiliary heater 130 is deactivated, for example. The thermal fluid 170 flows through the electric auxiliary heater 130 and the third fluid line 185 to the first branch 190. In the first operating state, the three-way valve 145 is switched to the first valve position by the control device 340, so that the thermal fluid 170 essentially flows into the fifth fluid line 205 . The thermal fluid 170 flows towards the second branch 210. In the first operating state, the first heating circuit 20 is open, for example. The control device 340 preferably controls the first secondary circuit pump 140 in such a way that a delivery rate of the first secondary circuit pump 140 is lower than a delivery rate of the primary circuit pump 125. This has the consequence that at the second branch 210 a mass flow of the thermal fluid 170 to the sixth fluid line 230 and the seventh fluid line 235 divides. It is of particular advantage here if the delivery rate of the primary circuit pump 125 is approximately 5 to 10% greater than the delivery rate of the first secondary circuit pump 140.

A first portion of the thermal fluid 170 flows via the seventh fluid line 235 to the first secondary circuit pump 140, which conveys the first portion via the first heating circuit connection 150 into the first heating circuit 20. After the building has been heated, the first part exits the first heating circuit 20 via the second heating circuit connection 155 and re-enters the thermal fluid transport device 35 after it has cooled and flows via the ninth fluid line 245 to the first junction 250.

A second portion of the thermal fluid 170 flows into the sixth fluid line 230 and enters the storage tank 225 at the first storage port 215 . The storage container 225 can, for example, be of tubular design. The incoming heated thermal fluid 170 flows through the storage container 225, and a thermal fluid 170 that has already been cooled is routed from the storage container 225 of the small storage device 135 via the second storage connection 220. During the conveyance of the thermal fluid 170 of the primary circuit pump 125, the thermal fluid 170 stored in the storage tank 225 is successively exchanged, so that the storage tank 225 of the small storage tank 135 is filled with warm thermal fluid 170 after a predefined first time interval. As long as the primary circuit pump 125 is activated, the warm thermal fluid 170 continues to be guided with the second part through the storage tank 225 and flows continuously through the storage tank. The warm thermal fluid 170 flows via the second storage connection 220 towards the first junction 250.

The arrangement of the small accumulator 135 fluidically between the first heating circuit connection 150 and the second heating circuit connection 155 means that the small accumulator 135 is connected hydraulically in parallel with the first heating circuit connection 150 and the second heating circuit connection 155 and the first heating circuit 20 .

At the first junction 250, the first portion of thermal fluid 170 and the second portion of thermal fluid 170 are combined and via the eleventh Fluid line 275 out to the three-way valve 145. By switching the three-way valve 145 to the first valve position, the thermal fluid 170 flows via the first fluid line 175 to the twelfth fluid line 280 and back to the first input side of the primary circuit pump 125. The primary circuit pump 125 again delivers the thermal fluid 170 from the twelfth Fluid line 280 in the circuit towards the first fluid line 175, which leads the thermal fluid 170 in the first secondary side 120 of the first heat exchanger 90.

In summary, in the first valve position, preferably only the first heating circuit 20 is supplied with the first heat Q ₁ . The first heat Q _-1 can then be transferred to the building in the first heating circuit 20 in order to heat the building.

In a second method step 510 , storage temperature sensor 330 measures water temperature TW of the hot water stored in storage tank 65 . The second method step 510 can take place in parallel with the first method step 505 .

In a third method step 515 following the second method step 510, the control device 340 compares the detected water temperature TW with the predefined first temperature threshold value S1. If the determined hot water temperature TW falls below the predefined first temperature threshold value S1, then the process continues with a fourth method step 520. If the hot water temperature TW exceeds the predefined first temperature threshold value S1, the process continues with a fifth method step 525.

It is pointed out that the second and third method step 510, 515 can also be carried out before the first method step 505, in particular if prioritization of the hot water tank 40 is desired.

In the fourth method step 520, the control device 340 uses a control signal to switch the three-way valve 145 to the fifth connection 360 second valve position. Furthermore, the control device 340 can deactivate the first secondary circuit pump 140 . The control device 340 can also continue to activate the first secondary circuit pump 140 .

At the first branch 190, the warm thermal fluid 170 flows into the fourth fluid line 195 to the first side 200 of the hot water heat exchanger 70. The warm thermal fluid 170 flows through the hot water heat exchanger 70 from the first side 200 to the second side 290. With the first heat Q̇ ₁ , the warm thermal fluid 170 heats the (cold) fresh water/warm water present in the storage tank 65 to warm water.

In addition, a running time of the compressor 105 can be determined in the first method step 505 and/or in the fourth method step 520 . The running time determined can be compared with a predefined minimum running time of the compressor 105, with the first method step 505 or the fourth method step 520 being continued if the minimum running time is not reached until the minimum running time is reached.

In a fifth method step 525, the control device 340 switches the three-way valve 145 to the first valve position or the three-way valve 145 remains in the first valve position.

During the first to fifth method steps 505 to 525, when the outside temperature is low, moisture can condense on the second heat exchanger 95 and the condensate can ice the second heat exchanger 95.

In a sixth method step 530 following the fourth and fifth method step 520, 525, the pressure sensor 320 determines an evaporation pressure p. Furthermore, a current evaporation temperature TVD is calculated in the control device 340 on the basis of this measurement and the thermophysical material data of the refrigerant 115 . On the basis of the outside temperature TA and the pressure p or the temperature TVD, the control device 340 determines an icing condition on the primary side of the second heat exchanger 95. Additionally On the air side of the second heat exchanger 95, another temperature sensor (not in 1 shown) can be arranged in order to determine the icing condition particularly well.

In a seventh method step 535 following the sixth method step, the control device 340 checks, by comparing the determined referral state with a predefined maximum permissible icing state, whether the second heat exchanger 95 is excessively icy on the primary side or whether the icing is within a permissible range. If the control device 340 recognizes that the second heat exchanger 95 is iced to a greater extent than the predefined maximum permissible icing state, then the control device 340 continues with an eighth method step 540 . If the icing of the second heat exchanger 95 is below the predefined maximum permissible icing state, the control device 340 continues with the first method step 505 if the water temperature TW is greater than the first predefined temperature threshold value S1 (cf. fifth method step 525), or with the fourth Method step 520 if the water temperature TW is lower than the first predefined temperature threshold value S1.

In the eighth method step 540, the conveyance of the refrigerant 115 is reversed with respect to the normal direction in the refrigerant circuit 100 by a corresponding switching of the refrigerant circuit 100 and the refrigerant circuit 100 is switched in the cooling direction. As a result, the refrigerant 115 in the first heat exchanger 90 absorbs a second heat Q - ₂ from the thermal fluid 170 and transfers it to the second heat exchanger 95. The thermal fluid 170 is thereby cooled in the first heat exchanger 90 . The second heat exchanger 95 is de-iced on the primary side with the second heat Q ₂ .

In order to provide a sufficiently large quantity of second heat Q - ₂ , in the eighth method step 540 the three-way valve 145 is set to the first valve position by the control device 340 . Furthermore, the control device 340 activates the primary circuit pump 125 and the first secondary circuit pump 140 in order to convey both the thermal fluid 170 from the first heating circuit 20 and from the small reservoir 135 to the first secondary side 120 of the first heat exchanger 90 .

The cooled thermal fluid 170 is introduced into the second fluid line 180 in a cold state. The thermal fluid 170 circulates between the small reservoir 135 and the first heating circuit 20 and the first heat exchanger 90. In a ninth method step 545, the second temperature sensor 315 measures the second temperature T2 of the thermal fluid 170 on the outlet side of the first heat exchanger 90.

In a tenth method step 550 following the ninth method step 545, the control device 340 compares the second temperature T2 with the predefined second temperature threshold value S2. If the second temperature T2 falls below the predefined second temperature threshold value S2, then the control device 340 continues with an eleventh method step 555. If the second temperature T2 exceeds the predefined second temperature threshold value S2, then the control device 340 continues with the eighth method step 540.

The control device 340 continuously carries out the sixth and seventh method step 530, 535 parallel to the ninth method step 545 to check whether the second heat exchanger 95 has now been defrosted far enough. If the control device 340 recognizes that the second heat exchanger 95 has been defrosted, the control device ends the defrosting mode. Depending on the current requirement (heating or hot water or no requirement), the control device 340 switches the heat pump 30 to the first or second heating mode or to a standby mode.

In the eleventh method step 555, the control device 340 controls the three-way valve 145 in such a way that the three-way valve 145 is switched from the first valve position to the second valve position. Furthermore, the control device 340 can deactivate the first secondary circuit pump 140 in order to avoid charging the first heating circuit 20 with cold thermal fluid 170 . However, the first secondary circuit pump 140 can also remain in operation. The primary circuit pump 125 remains activated. By activating the primary circuit pump 125, the thermal fluid 170 is now in the cooled state on the first side 200 in the Storage tank 65 introduced with hot water. The hot water from the storage tank 65 heats the thermal fluid 170 with the second heat Q̇ ₂ , so that the thermal fluid 170 is routed in a warm state via the second side 290 and the thirteenth fluid line 285 to the three-way valve 145 . The primary circuit pump 125 conveys the thermal fluid 170 via the first fluid line 175 into the first heat exchanger 90. In the first heat exchanger 90, the second heat Q - ₂ is transferred from the thermal fluid 170 to the refrigerant 115. The refrigerant 115 circulating in the reverse direction transfers the second heat Q̇ ₂ to the second heat exchanger 95. The second heat Q̇ ₂ is then further used to defrost the second heat exchanger 95.

The control device 340 continuously carries out the sixth and seventh method step 530, 535 parallel to the eleventh method step 555 to check whether the second heat exchanger 95 has now been defrosted far enough.

Furthermore, in the ninth and eleventh method step 545, 555, a minimum running time of the compressor 105 is recorded by the control device 340. If the minimum runtime is not reached, the ninth or eleventh method step 545, 555 is carried out until the minimum runtime is reached.

If the control device 340 recognizes that the second heat exchanger 95 has been defrosted, the control device 340 ends the defrosting mode. Depending on the current requirement (heating or hot water or no requirement), the control device 340 switches the heating device 15 to the first or second heating mode or to a standby mode.

Parallel to the eleventh method step 555, the storage tank temperature sensor 330 determines the water temperature TW of the hot water in the storage tank 65 in a twelfth method step 560.

In a thirteenth method step 565, which follows the twelfth method step 560, the control device 340 compares the hot water temperature TW with the predefined third temperature threshold value S3. The third temperature threshold S3 may be lower than the first temperature threshold S1 and greater than the second temperature threshold S2. If the water temperature TW falls below the third predefined temperature threshold value S3, then the control device 340 continues with the fourteenth method step 570. If the hot water temperature TW exceeds the predefined temperature threshold value S3, then the control device 340 continues with the eleventh method step 555.

In the fourteenth method step 570, the control device 340 activates the electric auxiliary heater 130, wherein the control device 340 can use the first temperature threshold value S1 as a target value for the hot water in the storage tank 65 as a reference variable for controlling the electric auxiliary heater 130.

The control device 340 continuously carries out the sixth and seventh method step 530, 535 parallel to the fourteenth method step 570 to check whether the second heat exchanger 95 has now been defrosted far enough. If the control device 340 recognizes that the second heat exchanger 95 has been defrosted, the control device ends the defrosting mode. Depending on the current requirement (heating or hot water or no requirement), the control device 340 switches the heating device to the first or second heating mode or to a standby mode.

The method described above and the heating system 10 have the advantage that the parallel arrangement of the small accumulator 135 ensures a minimum volume flow in the first method step 505, regardless of whether the first heating circuit 20 is open or closed. By controlling the primary circuit pump 125, the first secondary circuit pump 140 and the heat pump 30, a predefined setpoint flow temperature of the thermal fluid 170 is reliably ensured at the first temperature sensor 310, so that the small reservoir 135 is particularly filled with warm thermal fluid.

The volume of the small reservoir 135 is selected such that the compressor 105 can be operated at least for the minimum running time in the first method step 505 even when the first heating circuit 20 is closed. As a result, a long service life of the compressor 105 can be guaranteed.

Furthermore, the small reservoir 135 ensures that the second heat exchanger 95 can be defrosted in the eighth method step 540 in most cases and the eleventh to fourteenth method step 555, 560, 565, 570 are only carried out in exceptional cases.

3 shows a schematic representation of a heating system 10 according to a second embodiment.

The heating system 10 is essentially identical to that in FIG 1 shown heating system 10 is formed. In the following, only the differences of the in 3 shown heating system 10 compared to that in FIGS figures 1 and 2 shown heating system 10 received.

In addition to the first heating circuit 20 , the heating system 10 has a second heating circuit 410 . In addition, the thermal fluid transport device 35 has a third heating circuit connection 415 and a fourth heating circuit connection 420 in addition to the first heating circuit connection 150 and the second heating circuit connection 155 . The third heating circuit connection 415 and the fourth heating circuit connection 420 are connected to the second heating circuit 410 in such a way that the second heating circuit 410 is connected to the third heating circuit connection 415 on the flow side and to the fourth heating circuit connection 420 on the return side.

In addition, the thermal fluid transport device 35 can have a mixing valve 425 and a second secondary circuit pump 430 to control the second heating circuit 410 , which can be designed, for example, as underfloor heating in the building. The mixing valve 425 is connected on the inlet side via a fourteenth fluid line 435 to a third branch 440 , the third branch 440 being built into the seventh fluid line 235 . On the output side, the mixing valve 425 is connected to a third input side of the second secondary circuit pump 430 via a fifteenth fluid line 445 . Furthermore, the mixing valve 425 is connected to a bypass 450, which runs parallel to the third and fourth heating circuit connection 415, 420. The bypass 450 and the fourth heating circuit connection 420 are connected to the ninth fluid line 245 via a sixteenth fluid line 455 at a second junction 460 . The second heating circuit 410 is due to this configuration of the thermal fluid transport device 35 designed as a mixed heating circuit, while the first heating circuit 20 is unmixed.

The method for operating the heating system 10 can be essentially identical to that in 2 explained procedures are carried out. In the following, only the differences will be discussed. During de-icing, in the eighth method step 540, in addition to the first secondary circuit pump 140, the second secondary circuit pump 430 is also activated and the mixing valve 425 is set by the control device 340 in such a way that a backflow from the fifteenth fluid line 445 via the bypass 450 to the mixing valve 425 is avoided. The thermal fluid 170 thus flows not only through the first heating circuit 20, but also through the second heating circuit 410 and is introduced from the first and second heating circuit 20, 410 via the second junction 460 into the ninth fluid line 245 and from there in the direction of the first and second heat exchanger 90, 95 for de-icing the second heat exchanger 95.

In the eleventh method step 555, in addition to first secondary circuit pump 140, second secondary circuit pump 430 is also deactivated.

4 shows a schematic representation of a heating system 10 according to a third embodiment.

The heating system 10 is essentially identical to that in FIG figure 1 explained heating system 10 formed. In the following, only the differences of the in 4 shown heating system 10 compared to that in FIGS figure 1 shown heating system 10 received. In 4 will opposite 3 the second heating circuit 410 and the corresponding expansion of the thermal fluid transport device 35 are dispensed with.

Furthermore, the small reservoir 135 is made particularly thin in the embodiment and can be made, for example, as a tube. In contrast to the parallel connection of the small memory 135, the small memory 135 is in figures 1 and 3 arranged in parallel to the first and second heating circuit connection 150, 155 in series between the first branch 190 and the first heating circuit connection 150.

In 4 the first secondary circuit pump 140 is dispensed with. In this case, the primary circuit pump 125 also serves to supply the first heating circuit 20 with thermal fluid 170 . This configuration has the advantage that the first heating circuit 20 is fluidically coupled directly to the first heat exchanger 90 . As a result, the heating system 10 is particularly simple and inexpensive.

The small reservoir 135 is arranged fluidly in series between the first branch 190 and the second branch 210 . An overflow valve 465 is arranged on the second branch 210 parallel to the first heating circuit connection 150 and the second heating circuit connection 155 . The spill valve 465 may be adjustable or non-adjustable. The overflow valve 465 has a closed position and an open position, with the overflow valve 465 fluidically connecting the second branch 210 to the first junction 250 in an open position. In the closed position, the overflow valve 465 fluidly separates the second branch 210 from the first junction 250. The overflow valve 465 is below a predefined opening pressure on the input side of the overflow valve 465 in the closed position. If the pressure of the thermal fluid 170 on the inlet side adjacent to the overflow valve 465 exceeds the opening pressure, the overflow valve 465 is switched to the open position, so that the thermal fluid 170 overflows from the second branch 210 via the overflow valve 465 to the first junction 250.

The overflow valve 465 can be designed in various ways. For example, it can be controlled to open electronically by the control device 340 . It would also be possible for the overflow valve 465 to be spring-loaded. The overflow valve 465 can be adjustable or designed with a fixed opening pressure.

It is of particular advantage if the defined opening pressure is fixed, since this avoids a source of error when installing the heating system 10 . The opening pressure is greater than a residual delivery head for the connected first heating circuit 20.

The integration of the overflow valve 465 and the small reservoir 135 reduces the installation effort when installing the heating system 10 in the building.

The method for defrosting the second heat exchanger 95 is essentially identical to that in FIG 2 explained operating procedures. In the following, only the differences between the operation of the in 4 shown heating system 10 compared to that in 2 procedures explained.

In the first method step 505, the thermal fluid 170 flows through the small reservoir 135 on the way from the first branch 190 to the first heating circuit connection 150. As a result, the small reservoir 135 is filled with particularly warm thermal fluid 170 when the primary circuit pump 125 is activated.

If the first heating circuit 20 is closed, for example because the control valves of the first heating circuit 20 are closed or the thermostats are turned off, the flow through the small reservoir 135 is ensured in such a way that the control device 340 controls the primary circuit pump 125 in such a way that the primary circuit pump 125, although the first heating circuit 20 is closed, the thermal fluid 170 continues to be conveyed in the direction of the first heat exchanger 90 at least with a small volume flow. Furthermore, the heat pump 30 is activated, so that the first heat Q - ₁ is transferred to the thermal fluid 170 in the first heat exchanger 90 and the thermal fluid 170 is heated. Despite the first heating circuit 20 being switched off or closed, the primary circuit pump 125 delivers the thermal fluid 170 via the first branch 190 through the small reservoir 135. Due to the closed first heating circuit 20 and the delivery of the thermal fluid 170, the pressure of the thermal fluid 170 on the inlet side of the overflow valve 465 increases. The control device 340 controls the primary circuit pump 125 in such a way that the pressure on the inlet side of the overflow valve 465 is greater than the opening pressure and the overflow valve 465 changes from the closed position to the open position and the thermal fluid 170 in the circuit via the overflow valve 465 and the three-way Valve 145 to the primary circuit pump 125 flows. It can thereby be ensured that the small reservoir 135 is filled with warm thermal fluid 170 .

In the eighth method step 540, as explained in the first method step 505, the control device 340 can control the primary circuit pump 125 in such a way that the pressure of the thermal fluid 170 on the inlet side of the overflow valve 465 is greater than the opening pressure of the overflow valve 465. This ensures that the thermal fluid 170 stored in the small reservoir 135 can be conveyed in the direction of the three-way valve 145 via the overflow valve 465 . Furthermore, the primary circuit pump 125 conveys the warm thermal fluid 170 originating from the small accumulator 135 in the direction of the first heat exchanger 90, in which the second heat Q̇ ₂ is removed from the warm thermal fluid 170 in de-icing mode and via the refrigerant circuit 100 to the second heat exchanger 95 for de-icing the second Heat exchanger 95 is transferred.

This configuration has the advantage that sufficient second heat Q ₂ can be made available for de-icing, even if the first heating circuit 20 is closed. In particular, a loss of comfort as a result of the additional removal of second heat Q ₂ from the hot water tank 40 that may be necessary in the eleventh method step 555 can be kept low.

figure 5 shows a schematic representation of a heating system 10 according to a fourth embodiment.

The heating system 10 is essentially identical to that in FIG 4 shown heating system 10 is formed. Deviating from this is in figure 5 the small reservoir 135 is designed with a significantly larger volume than the one in 4 shown small memory 135. The in figure 5 The small storage tank 135 shown can be designed, for example, as a solar ballast vessel.

In the figure 5 Serial arrangement shown with a small memory 135 with a significantly larger volume than in 4 shown has the advantage that even a large second heat exchanger 95 can be reliably de-iced without having to resort to the removal of second heat Q̇ ₂ from the hot water tank 40 with the first heating circuit 20 closed as a rule.

6 shows a perspective view of the heating device 15 of a heating system 10 according to a fifth embodiment.

The heating device 15 is essentially identical to that in 1 shown heater 15 is formed. In the following, only the differences of the in 6 shown heating system 10 compared to in 1 shown heating system 10 received.

In the embodiment, the fourth fluid line 195 has a first section 600 and a second section 605 by way of example. The second section 605 is formed from a bent copper tube, for example.

The first section 600 has a plastic as the material, for example, and is preformed. For example, the first sub-section 600 can be designed as an arcuate section that encloses at least an angle of at least 45°, preferably of at least 90°. The configuration of the first partial section 600 from a preformed plastic line has the advantage that the fourth fluid line 195 is mounted essentially free of stress or at least with little stress. Furthermore, a tolerance compensation between the second section 605 and a storage tank 65 can be achieved in a substantially stress-free or low-stress manner.

The configuration of the first subsection 600 with a preformed plastic line has the advantage that a few millimeters of tolerance can be compensated for by the preformed plastic line of the first subsection 600 compared to a fixed copper pipe connection.

The thirteenth fluid line 285 can be designed analogously to the fourth fluid line 195 . Deviating from this, the thirteenth fluid line 285 is made entirely of plastic and is preformed.

7 shows an in 6 marked section A of the in 6 shown heating system 10.

The design of the thirteenth fluid line 285 from a preformed plastic allows the thirteenth fluid line 285 to be routed past the fourth fluid line 195 in the area of the second subsection 605 at a spatially narrow distance. As a result, the space required for the heating system 10 is particularly small.

8 and 9 show plan views of an in 6 marked section B.

In order to connect the second section 605 to the first section 600, a clamping means 610 is provided in the embodiment. The clamping means 610 can be embodied, for example, as a spring clip that encompasses the first subsection 600 on the peripheral side and fixes the first subsection 600 to the second subsection 605 . The first subsection 600 is slipped onto the second subsection 605 and fixed in a positive and non-positive manner by the clamping means 610 .

This configuration has the advantage that the fourth and thirteenth fluid line 195, 285 can be mounted in a fluid-tight manner in a particularly simple and cost-effective manner. Furthermore, the clamping means 610 can be released reversibly without being destroyed.

Compared to the second section 605, the first section 600 offers the advantage that bends in space can be guided particularly tightly and cost-effectively. Furthermore, the first subsection 600 and the thirteenth fluid line 285 can be produced in a particularly simple and cost-effective manner, for example by thermal deformation to preform the first subsection 600 and the thirteenth fluid line 285 . Furthermore, geometries can be produced that cannot be produced using a copper tube.

It is pointed out that in the example the preformed plastic line is provided in the first section 600 and in the thirteenth fluid line 285 by way of example. Of course, at least one of the other fluid lines 175, 180, 185, 195, 205, 230, 235, 240, 245, 255, 275, 280, 435, 445, 455 can be formed at least in sections by a preformed plastic line.

Claims (14)

Heating device (15) for heating a building,
having a heat pump (30) with a first heat exchanger (90) and a thermal fluid transport device (35) with a primary circuit pump (125), at least one first heating circuit connection (150) and a second heating circuit connection (155), the thermal fluid transport device (35) with a thermal fluid (170) can be filled and is designed to transport and distribute the thermal fluid (170), a first secondary side (120) of the first heat exchanger (90) being fluidically connected to the first and/or second heating circuit connection (150, 155), characterized in that the thermal fluid transport device (35) has a small reservoir (135) for temporarily storing the thermal fluid (170), the small reservoir (135) being fluidically connected to the first heating circuit connection (150) and/or to the first secondary side (120) of the first heat exchanger (90) is connected, wherein the primary circuit pump (125) is formed, the thermal fluid (170) between the first secondary side (120) and the dress to promote n memory (135). Heating device (15) according to claim 1,
wherein the small memory (135) is arranged parallel to the first heating circuit connection (150) and the second heating circuit connection (155). Heating device (15) according to claim 1,
wherein the small storage tank (135) is arranged in series between the first heating circuit connection (150) and the first secondary side (120) of the first heat exchanger (90). Heating device (15) according to one of the preceding claims,
at least one first secondary circuit pump (140) being arranged between the small reservoir (135) and the first heating circuit connection (150), the first secondary circuit pump (140) being designed to convey the thermal fluid (170) between the small reservoir (135) and the first heating circuit connection ( 150) to promote. Heating device (15) according to one of the preceding claims,
wherein the thermal fluid transport device (35) has an overflow valve (465), the overflow valve (465) having a closed position and an open position, the overflow valve (465) being switched to the closed position when the pressure at the overflow valve (465) falls below a predefined opening pressure, wherein the overflow valve (465) is switched to the open position when the predefined opening pressure at the overflow valve (465) is exceeded, the overflow valve (465) being arranged parallel to the first heating circuit connection (150) and the second heating circuit connection (155). Heating device (15) according to one of the preceding claims, having a hot water storage tank (40) with a storage tank (65) and a hot water heat exchanger (70) arranged in the storage tank (65), the storage tank (65) being designed to store hot water, the Heat fluid transport device (35) has a three-way valve (145), wherein a first valve connection (260) of the three-way valve (145) with the second heating circuit connection (155) and a second valve connection (265) of the three-way valve (145) is fluidically connected to the primary circuit pump (125), a first side (200) of the hot water heat exchanger (70) being fluidically connected to a first branch (190) arranged between the first secondary side (120) and the small reservoir (135). , wherein a second side (290) of the hot water heat exchanger (70) with a third valve port (270) of the three-way valve (145) is fluidly connected, the three-way valve (145) having a first valve position and at least one second valve position that differs from the first valve position, with the three-way valve (145) fluidically connecting the second heating circuit connection (155) with the primary circuit pump (125) in the first valve position, with the three-way -Valve (145) fluidically connects the second side of the hot water heat exchanger (70) to the primary circuit pump (125). Heating device (15) according to claim 6 and claim 2,
wherein the small storage tank (135) has a first storage connection (215) and a second storage connection (220), the first storage connection (215) being connected between the first branch (190) and the first heating circuit connection (150), the second storage connection ( 220) is connected between the second heating circuit connection (155) and the three-way valve (145), Heating device according to claim 6 and claim 3,
wherein the small reservoir (135) has a first reservoir connection (215) and a second reservoir connection (220), the first reservoir connection (215) being fluidic with the first branch (190) and the second reservoir connection (220) with the first heating circuit connection (150). are connected, wherein the small memory (135) fluidly connects the first branch (190) to the first heating circuit connection (150). Heating device according to one of the preceding claims, having an outdoor unit (45) and an indoor unit (50), the heat pump (30) being arranged in the outdoor unit (45) and having at least one second heat exchanger (95), the second heat exchanger (95 ) is fluidly connected to the first heat exchanger (90) for heat exchange, wherein the thermal fluid transport device (35) and the small memory (135) are arranged in the internal unit (50). Heating device (15) according to one of the preceding claims, having a fluid line (175, 180, 185, 195, 205, 230, 235, 240, 245, 255, 275, 280, 285, 435, 445, 455) for conducting the heating fluid (170), wherein the fluid line (175, 180, 185, 195, 205, 230, 235, 240, 245, 255, 275, 280, 285, 435, 445, 455) has at least one curved section, the curved section having at least one angle of at least 45°, preferably at least 90°, wherein the fluid line (175, 180, 185, 195, 205, 230, 235, 240, 245, 255, 275, 280, 285, 435, 445, 455) has at least one plastic and is preformed, the fluid line (175, 180, 185, 195, 205, 230, 235 , 240, 245, 255, 275, 280, 285, 435, 445, 455) is arranged stress-free or low-stress. heating system (10),
having a heating device (15) according to one of the preceding claims and a first heating circuit (20), wherein the first heating circuit (20) is connected to the first heating circuit connection (150) and to the second heating circuit connection (155) and is connected to the heating fluid (170) is filled, wherein the primary circuit pump (125) is designed to promote the thermal fluid between the small storage (135) and the first secondary side (120) of the first heat exchanger (90). Method for de-icing a heating device (15) with a heat pump (30), a hot water tank (40) and a thermal fluid transport device (35),
wherein the heat pump (30) has a refrigerant circuit (100) with a refrigerant (115) and in each case a compressor (105) integrated into the refrigerant circuit (100), a first heat exchanger (90), and a second heat exchanger (95), the Heat pump (30) for operating the heating device (15) has at least one de-icing mode, in which the heat pump (30) is operated for targeted heating of the second heat exchanger (95), a primary circuit pump (125) of the thermal fluid transport device (35) being activated and the heated thermal fluid (170) is conveyed to the first heat exchanger (90), a second heat (Q̇ ₂ ) being transferred from the thermal fluid (170) to the refrigerant (115), the refrigerant (115) in the refrigerant circuit (100) circulates and the refrigerant (115) transfers the second heat (Q̇ ₂ ) to the second heat exchanger (95), with the second heat (Q̇ ₂ ) of the second heat exchanger (95) being deiced, with a s predefined operating parameters of the heating device (15), in particular a temperature (T2) of the thermal fluid (170), the thermal fluid (170) is passed through the hot water tank (40) and the second heat (Q̇ ₂ ) for de-icing the second heat exchanger (95) is at least partially removed from the hot water tank (40). Method according to claim 12,
wherein in the de-icing mode, before the predefined operating parameters are reached, the thermal fluid (170) is conveyed from a small reservoir (135) of the thermal fluid transport device (35) to the first heat exchanger (90), the second heat (Q̇ ₂ ) for de-icing the second heat exchanger (95) is transferred from the thermal fluid (170) stored in the small reservoir (135) to the first heat exchanger (90). Method according to claim 12 or 13,
wherein in the heating mode the primary circuit pump (125) is controlled such that the thermal fluid (170) has a pressure that is greater than an opening pressure of an overflow valve (465) of the thermal fluid transport device (35).

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