Temperature control system with a collector and a pump in the secondary circuit, method for operating a temperature control system or method for manufacturing a temperature control system

Abstract

Temperature control system for temperature-controlling a room, comprising: a primary circuit (11); a secondary circuit; a first heat exchanger (1) with a primary side (10) and a secondary side (12), wherein the first heat exchanger (1) is configured to couple the primary circuit (11) and the secondary circuit, and wherein the primary circuit (11) is configured to extract heat from the secondary side (12) of the first heat exchanger (1) via the primary side (10) of the first heat exchanger, wherein the secondary circuit comprises: the secondary side (12) of the first heat exchanger (1); a manifold (2) which, in operation of the temperature control system, is arranged below (60) the secondary side of the first heat exchanger (1); a pump (3) which is coupled to the manifold (2);and a second heat exchanger (4) which, during operation of the temperature control system, is arranged in thermal interaction with the space (5) to be temperature controlled and is located above the collector (2); and a secondary fluid (50) which, during operation of the temperature control system, is arranged in the secondary circuit and is pressurized such that a phase change from a liquid secondary fluid to a vaporous secondary fluid takes place in the second heat exchanger (4) and a phase change from the vaporous secondary fluid to the liquid secondary fluid takes place in the secondary side (12) of the first heat exchanger (1).

Description

[0001] The present invention relates to a temperature control system that can be used to control the temperature of rooms, wherein these rooms can be stationary or mobile.

[0002] The compression refrigeration machine is the most common type of refrigeration machine. This design utilizes the physical effect of the latent heat of vaporization during the change of state from liquid to gaseous, or from gaseous to liquid. In a compression refrigeration machine, a refrigerant with suitable thermodynamic properties is circulated in a closed loop, as is the case in... Fig. As shown in Figure 2a, the refrigerant undergoes various changes of state sequentially and repeatedly. The gaseous refrigerant is first compressed by a compressor. In the subsequent heat exchanger (condenser or heat sink of the process), it is condensed (liquefied) while releasing heat. The liquefied refrigerant is then expanded to its evaporation pressure via an expansion device, such as an expansion valve or, in the simplest case, an orifice or a capillary tube. This process cools the refrigerant. In the downstream second heat exchanger (evaporator, or heat source of the process), the refrigerant evaporates at a low temperature, absorbing heat (evaporative cooling). The heat absorbed in this process represents the cooling capacity of the refrigeration system. The absorbed heat flow is referred to as the cooling capacity.The evaporator is therefore advantageously located directly within the refrigerated unit, the refrigerated container, or generally within the enclosed space to be cooled, in order to minimize heat transfer losses by bringing the contents into direct contact with the heat source. The cycle can then begin again. The process must be maintained externally by supplying mechanical work (drive power) via the compressor. The refrigerant absorbs heat at a low temperature level and, with the input of mechanical work, releases it at a higher temperature level, usually to the surroundings. The process is referred to as a heat pump process when, instead of a cooling load or energy supplied to the evaporator, the heat released by the condenser of the system is to be utilized.In the present application, this allows for the possibility, with suitable process control and component arrangement, of supplying energy in the form of heat to the described structure, or rather the enclosed interior of the application, for heating purposes. One way to achieve this is to connect the compressor's pressure-side outlet to the heat exchanger located within the enclosed structure in such a way that the heat exchanger heats up during operation. The remaining components then perform their function according to the described application process for generating cold. Furthermore, the heat supply enables efficient defrosting of the heat exchanger within the enclosed space, which can be either time-controlled or demand-based.

[0003] The refrigerant circuit essentially consists of four components: compressor, condenser, expansion vessel, and evaporator. In a single-stage or multi-stage refrigeration system, a distinction is generally made between the high-pressure and low-pressure sides. The high-pressure side extends from the compressor's pressure side to the point where the refrigerant enters the expansion vessel. The low-pressure side comprises the portion of the refrigerant circuit from the refrigerant exit of the expansion vessel to the compressor inlet. This also applies when the refrigerant circuit is operated as a heat pump, meaning that the heat output provided by the condenser is used instead of the evaporator's cooling capacity. This heat output can be used, as described, to heat the application or to defrost the evaporator.

[0004] The refrigerant used in the cycle should, regardless of the application, have the lowest possible environmental impact, be cost-effective, and particularly energy-efficient. A key measure of a refrigerant's environmentally damaging effect is its global warming potential (GWP). This value is given for refrigerants in relation to the GWP of CO2 (carbon dioxide). By definition, CO2 has a GWP of 1. For fluorinated gases (F-gases), which are frequently used as refrigerants, the GWP can reach values ​​of several thousand. This means that one kilogram of F-gas released into the atmosphere during its production, use, or disposal can be equivalent to the greenhouse effect of several tons of CO2.

[0005] The main components of fluorinated gases (F-gases) are carbon, hydrogen, and fluorine. F-gases often decompose very slowly and, once released, can remain in our atmosphere for hundreds or even thousands of years. Regardless of their lifetime and global warming potential, the breakdown of F-gases produces decomposition products. These substances, such as trifluoroacetic acid and hydrogen fluoride, often have long-term negative effects on humans and the environment. For these reasons, the use of F-gases as refrigerants is increasingly restricted or even prohibited by international legislation through regulations and ordinances.The acceptance of F-gases as refrigerants by consumers and users of refrigeration technology, as well as by society, is decreasing, and as a result, the manufacturing industry of refrigeration systems and heat pumps is increasingly demanding alternatives to the existing refrigeration technology based on the use of F-gases.

[0006] International patent application WO 2023052244 A1 discloses a method and a device for temperature-controlling a space to be controlled, with a space boundary that separates the space to be controlled from its environment. The device comprises a primary heat pump circuit with an evaporator, a condenser, a compressor, and an expansion element, wherein the primary heat pump circuit contains a natural primary working fluid, such as a flammable one. The evaporator, the condenser, the compressor, and the expansion element are arranged outside the space to be controlled.Furthermore, the device comprises a secondary circuit that is thermally coupled to the evaporator or condenser via a heat exchanger and fluidically decoupled. This secondary circuit includes a temperature control element located within the space to be temperature controlled. The secondary circuit is connected to the heat exchanger by a piping arrangement containing a secondary fluid different from the primary working fluid, with the piping arrangement penetrating the space boundary. The secondary circuit is designed as a thermosiphon circuit and includes a controllable pump configured to reverse the flow direction in response to a control signal. Normally, in a cooling mode, the thermosiphon circuit is used to cool the space.However, in order to defrost the temperature control element in the room to be tempered, a heat pump cycle reversal is effected in response to a control signal in the primary heat pump circuit, so that in the defrosting mode energy is supplied to the heat exchanger via the primary heat pump circuit, whereby the controllable pump reverses the flow direction in the secondary circuit, so that no thermosiphon cycle is active in the defrosting operation.

[0007] Due to the thermosiphon cycle, the heights of the heat exchanger on the one hand and the temperature control element in the room to be temperature controlled are fixed, and it is necessary that the heat exchanger always contains a relatively small amount of secondary fluid for cooling the room or a large amount of secondary fluid for heating the room.

[0008] Although this functionality delivers good results for various applications, it has become apparent that greater robustness is desirable for some applications.

[0009] The object of the present invention is to create a more robust temperature control concept for temperature-controlling a room to be tempered.

[0010] This problem is solved by a temperature control system for temperature-controlling a room to be temperature-controlled according to claim 1, a method for operating a temperature control system according to claim 27 or a method for manufacturing a temperature control system according to claim 28.

[0011] The temperature control system according to the invention for temperature-controlling a room comprises a primary circuit and a secondary circuit. A first heat exchanger with a primary side and a secondary side is provided, which is designed to couple the primary and secondary circuits. The primary circuit is designed to extract heat from the secondary side of the first heat exchanger via the primary side of the first heat exchanger.

[0012] Furthermore, the secondary circuit comprises the secondary side and, in particular, a manifold located below the secondary side of the first heat exchanger during operation of the temperature control system, a pump coupled to the manifold, and a second heat exchanger located above the manifold and in thermal interaction with the space to be temperature controlled during operation of the temperature control system. Additionally, a secondary fluid is provided, which is located in the secondary circuit during operation of the temperature control system and is pressurized such that a phase change from liquid secondary fluid to vaporous secondary fluid occurs in the second heat exchanger, and a phase change from vaporous secondary fluid to liquid secondary fluid occurs in the secondary circuit of the first heat exchanger.

[0013] The use of a manifold positioned below the first heat exchanger ensures that the first heat exchanger is filled with vaporous secondary fluid, rather than liquid secondary fluid. This allows its entire heat exchanger surface area, or volume, between the primary and secondary sides of the first heat exchanger to condense and cool the secondary side. The circuit is maintained by a dedicated pump. In particular, the pump provides robust and reliable cooling by pumping cold liquid secondary fluid into the second heat exchanger, which cools the space to be cooled. This occurs as the cold liquid secondary fluid evaporates within the second heat exchanger, thereby extracting heat from the space.

[0014] Positioning the second heat exchanger above the manifold ensures that it only cools the room when the pump is circulating liquid secondary fluid into it. When the pump is off, the liquid secondary fluid flows into the manifold by gravity, and the second heat exchanger, filled only with steam, is thermally inactive. This allows for precise temperature control of the room solely through pump operation, ensuring that the room is neither under- nor over-cooled.

[0015] The collector provides a certain supply or tank of cold secondary fluid, which is directly useful for handling even higher cooling loads, even if the primary circuit is not designed for such high cooling capacity. Since typically high cooling loads in the room being cooled are only required for a relatively short time, this required high short-term cooling capacity can be easily supplied by activating the pump, which is connected between the collector and the second heat exchanger. This high cooling capacity is sufficient until the tank or supply in the collector is empty. In contrast, cooling on the primary side can run continuously, as the cooling capacity is constantly absorbed by the collector and therefore not delivered to the secondary side in the room being cooled. This decouples the primary and secondary sides.

[0016] Thus, it is possible to run the primary side continuously, so to speak, in order to constantly ensure a certain supply of "cold" in the collector, i.e., of cold liquid secondary fluid, even if the actual power of the primary circuit is significantly smaller than the power that is required on the secondary side in the short term.

[0017] This approach makes it particularly easy to integrate the temperature control system into a mobile device, such as a van or truck, or another mobile device, such as a boat, or any other vehicle with an internal combustion engine, electric motor, or other type of engine. Typically, in such an application with an internal combustion engine, the system incorporates functionality to charge a battery with a specific capacity via a suitable generator arrangement. This battery powers the primary side for a certain period of time, such as several hours. This ensures continuous operation of the primary side, even when the internal combustion engine is switched off, for example, when a van is making a delivery stop or requiring charging.Even in such a case, where the combustion engine is switched off, a high temperature control output can be delivered in the room to be cooled, thanks to the battery and even with an empty battery, thanks to the cold storage in the preferably well-insulated collector.

[0018] In preferred embodiments of the present invention, several rooms to be temperature-controlled are provided, all of which are supplied by the same manifold. For this purpose, a distributor is provided which has various controllable distributor ports through which controllable flow rates can be achieved. Then, simply by controlling the distributor ports differently, for example by different pumps or by one pump and different valves, the temperature in each room can be set separately, starting from one and the same reservoir of cold secondary fluid, which is continuously generated by condensation in the primary circuit via the first heat exchanger, independent of the demand on the secondary side.

[0019] Furthermore, simple defrosting of the second heat exchanger, which is in thermal interaction with the room to be cooled, can be achieved. For this purpose, energy is supplied to the secondary fluid, causing it to evaporate. This secondary fluid, either stored in the receiver or pumped into the first heat exchanger, then enters the second heat exchanger in the opposite direction to the cooling circuit. Due to the surrounding cold, the vapor in the second heat exchanger condenses, thereby transferring energy into the room to be cooled. This energy is transferred directly to the heat exchanger if it is located within the room, or to the room wall if it is in thermal interaction with the room, for example, in or outside the room wall.This allows ice that has accumulated on, for example, the room wall to be removed quickly and easily, without completely thawing it. Instead, the thawing process, which involves warming the liquid secondary fluid (i.e., evaporating it), causes the "ice layer" to simply detach from the wall and be easily removed, for example, manually from the room being heated.

[0020] This eliminates the need to heat the entire room; instead, only the ice can be loosened and removed without raising the temperature throughout the entire space. This is particularly advantageous when the room contains food items that must be kept within a specific temperature range.

[0021] By using this arrangement, and in particular by evaporating the liquid secondary fluid, selective defrosting can also be carried out in multi-temperature applications, i.e., when several rooms are to be heated or cooled and operated at the same or different temperatures. This is achieved, for example, by filling a heat exchanger located in a room not to be defrosted with cold secondary fluid and maintaining this fill level while defrosting takes place in the other room. This prevents warm steam from entering the fully filled second heat exchanger in the room not to be defrosted, and therefore no defrosting will occur in that room.

[0022] According to the invention, the defrosting process is therefore implemented by means of a thermosiphon circuit, which is initiated by evaporating the liquid secondary fluid in the collector by deactivating the pump, and by designing the pump to allow easy passage of liquid in the deactivated state. Even the use of other pumps that do not allow liquid passage in the deactivated state is possible if a bypass line around the pump is activated by appropriate fluid switches for the defrosting process. However, a pump that allows easy liquid passage in the deactivated state is preferred due to its simpler design.

[0023] According to the invention, the actual standard cooling process is therefore achieved by the tank filled with cold secondary fluid and an activated pump, while the defrosting process is accomplished by a thermosiphon circuit. This achieves a particularly gentle, yet nonetheless very effective defrosting process using the simplest of means.

[0024] Energy can be supplied to the secondary fluid in various ways. One preferred method is to install, for example, a resistance heater in the manifold to generate thermal energy, e.g., through electricity, to evaporate the secondary fluid for defrosting purposes. Another possibility is to supply energy to the first heat exchanger by reversing the primary circuit. However, because the first heat exchanger is not filled with secondary fluid, a pump must be provided to pump the secondary fluid, which is to be evaporated, from the manifold into the first heat exchanger, and specifically into the secondary side of the first heat exchanger, so that the fluid evaporates there.

[0025] The temperature control system according to the invention leads to increased robustness because the cooling, which must be ensured in any case, is reliably supplied from a tank of liquid secondary fluid by a controllable pump. This utilizes the "strong" and "controlled" cooling process to reliably and robustly meet the necessary cooling requirements. In contrast, the "weaker" siphon process is used to achieve defrosting, which is less critical in terms of timing and is also particularly gentle on the overall temperature in the room, i.e., the "cold filling" of the room.

[0026] Further increased robustness is achieved by the fact that, due to the stored supply of cold secondary fluid in the collector, the functionality of the secondary circuit is separated from that of the primary circuit. This allows for very high cooling capacities, which are typically only of short duration, even if the primary circuit does not deliver high capacity. Since the primary circuit can remain active continuously, it has sufficient time between required cooling cycles in the secondary circuit to steadily replenish its supply of secondary fluid, albeit more slowly than in the secondary circuit.

[0027] This functionality is particularly suitable when the temperature control system is housed in a mobile unit with a combustion engine. The combustion engine can then be switched off for a relatively long time if a battery is connected between the combustion engine and the primary circuit, ensuring the operation of the primary circuit for a certain period. Particularly energy-efficient operation of the primary circuit is possible because it can always be operated at its optimal operating point with the same power level, regardless of the cooling demand on the secondary side. This constant operating mode can then be selected as the primary circuit's operating mode, in which it delivers the highest efficiency.This allows for further efficiency gains, which can be used in terms of a small accumulator battery or in terms of an extended maximum running time of the primary circuit with the same accumulator battery and the combustion engine switched off.

[0028] In preferred embodiments, all elements except the second heat exchanger, which is arranged in thermal interaction with the space to be cooled, can be integrated into a complete unit. When used in a delivery van, for example, or in a truck or small van, this unit can be arranged below the loading platform, i.e., below the top of the chassis. Thus, the entire refrigeration system, which is integrated into a specific area of ​​the delivery van, does not interfere with the other loading options or other requirements that the delivery van would also provide without the temperature control system according to the invention.

[0029] Preferred embodiments of the present invention are explained in detail below with reference to the accompanying drawings. These show: Fig. 1 a preferred embodiment of a temperature control system for temperature control of a room to be temperature controlled; Fig. 2 a schematic representation of the temperature control system according to an exemplary embodiment; Fig. 3 a schematic representation of the temperature control system according to an exemplary embodiment during cooling operation; Fig. 4a a preferred embodiment of the temperature control system during heating operation, which is preferably used for defrosting the temperature control system; Fig. 4b another preferred embodiment for implementing heating operation with reversal of the cycle in the primary circuit; Fig. 5 a schematic representation of the temperature control system with the elements in the primary circuit; Fig. 6 a preferred embodiment of the present invention comprising two rooms to be temperature-controlled and a controllable distributor arrangement between the collector and the rooms to be temperature-controlled; Fig. 7a a schematic representation of the temperature control system with several pumps in the controllable distributor arrangement; Fig. 7b another embodiment of the temperature control system with a pump and various controllable valves in the controllable distributor arrangement; Fig. 8 a preferred embodiment for a sequence of steps for implementing a method for selectively defrosting or heating a room; Fig. 9 a representation of the second heat exchanger before interior wall mounting; Fig. 10 a representation of the room to be tempered after the interior wall mounting with a second heat exchanger arranged behind it; Fig. 11a Illustration of a temperature control system with the first heat exchanger, the collector and three pumps for three rooms to be temperature controlled; and Fig. 11b a representation of the primary circuit and the first heat exchanger below the floor of the cargo space.

[0030] Fig. Figure 1 shows a temperature control system for controlling the temperature of a room 5, which has a primary circuit 11 and a secondary circuit. A first heat exchanger 1 is also provided, which has a primary side 10 and a secondary side 12. The first heat exchanger 1 serves to connect the primary circuit 11 and the secondary circuit. The primary circuit 11 is designed to extract heat from the secondary side 12 of the first heat exchanger 1 via the primary side 10 of the first heat exchanger 1. In particular, the secondary circuit comprises the secondary side 12 of the first heat exchanger, the manifold 2 according to the invention, which, in operation of the temperature control system, is arranged below the secondary side 12 of the first heat exchanger 1. A pump 3 is provided, which is coupled to the manifold 2. The second heat exchanger 4 is arranged in thermal interaction with the room 5 and is located above the manifold 2.The secondary circuit contains a secondary fluid which, during operation of the temperature control system, is pressurized to such an extent that a phase change from liquid to vaporous secondary fluid occurs in the second heat exchanger 4 to cool the space 5 being temperature controlled, and that a phase change from vaporous to liquid secondary fluid occurs in the secondary side 12 of the first heat exchanger to extract heat from the secondary side of the first heat exchanger. The heat is then processed in the primary circuit 11, for example, by being released to the environment or used for heating purposes of some kind.

[0031] In preferred embodiments, the second heat exchanger 4 is arranged outside the space 5 to be heated, but in thermal interaction with it. For this purpose, the space to be heated is surrounded by a wall 40, to which the second heat exchanger 4 is attached by means of a thermally conductive material 20. This second heat exchanger is thermally insulated from the outside by thermal insulation material. This means that the thermal conductivity of the material 20 between the second heat exchanger 4 and the wall of the space to be heated is greater than the thermal conductivity in the insulation 30 or in the insulation around the rest of the wall of the space to be heated.

[0032] Although in Fig. Figure 1 shows that the second heat exchanger 4 is arranged only on one wall of the room to be cooled. However, this heat exchanger can also consist of various elements arranged on one or more side walls of the room to be cooled, up to and including all side walls. Furthermore, another part of the second heat exchanger 4 can also be installed in the ceiling of the room to be cooled in order to achieve cooling of the room from all sides.

[0033] A temperature sensor 71 is provided in the room to be cooled. This sensor transmits the current temperature to a pump controller 72, which receives or has internally stored a setpoint temperature for the room. Depending on the comparison between the setpoint and actual temperature, pump 3 is activated. If the actual temperature is above the setpoint temperature, the pump pumps liquid secondary medium from the reservoir 50 in the collector into the second heat exchanger 4. If the actual temperature is below the setpoint temperature, the pump stops pumping to prevent excessive cooling of the room. Pump control 72, based on the actual and setpoint temperatures, can be performed at specific time intervals.

[0034] The primary circuit 11 is controlled by a primary controller 82, which uses a temperature sensor 81 in the collector to measure the actual temperature of the liquid secondary fluid. Depending on a target temperature supplied to the primary controller or stored in the primary controller 82, the primary circuit is controlled. The primary circuit controller will intervene significantly less often than the pump controller 72 for the secondary circuit. This is because the primary controller 82 only ensures that the temperature in the collector, as measured by the sensor 81, does not fall significantly below the temperature intended for the room to be cooled. If several rooms are to be cooled, as is the case, for example, with reference to Fig. As shown in Figure 6, the primary control 82 will ensure that the temperature in the collector is at all times lower than or equal to the temperature that is the lowest setpoint temperature of the various rooms to be cooled.

[0035] However, the requirements for the primary control 82 are not particularly high, because the primary control 82 can set the temperature in the collector 50 below the setpoint temperature of the room to be cooled and also significantly below the setpoint temperature, although a sensible lower limit is given here so that even with a small pump interval of the pump 3, undercooling of the room to be cooled is avoided.

[0036] Typically, the primary circuit 11 will operate almost continuously, powered by a battery 100 which is charged by an internal combustion engine 110, if the temperature control system is housed in a vehicle or mobile device with an internal combustion engine. Depending on the design, the mobile device can be a land vehicle, a watercraft, an aircraft, or a spacecraft.

[0037] The secondary side 12 of the first heat exchanger 1 comprises a secondary inlet 13 and a secondary outlet 14. The manifold 2 comprises a manifold inlet 21 and a manifold outlet 22. Furthermore, the pump comprises a pump inlet 31 and a pump outlet 32. The second heat exchanger 4 has a heat exchanger inlet 41 and a heat exchanger outlet 42. Specifically, the secondary outlet 14 is connected to the manifold inlet 21. Furthermore, the manifold outlet 22 is connected to the pump inlet 31. Additionally, the pump outlet 32 ​​is connected to the heat exchanger inlet 41, and the heat exchanger outlet 42 is connected to the secondary inlet 13.

[0038] The collector 50 is connected to the secondary side of the first heat exchanger 1 via a first pipe on the inlet side, this pipe passing through the elements 14 and 21 in Fig. Figure 1 is shown. Furthermore, the collector 50 is also connected to the pump 3 via a pipeline, this pipeline being connected by elements 22 and 31 of Fig. 1 is shown.

[0039] Furthermore, the collector 50 has a cross-section larger than that of the pipes 14 and 21 at the inlet or the pipes 22 and 31 at the outlet. The collector is clearly separated from the first heat exchanger 1 on the one hand and the pump 3 on the other, which means that no liquid secondary fluid remains in the first heat exchanger 1, which is, for example, a plate heat exchanger. Instead, all the secondary fluid liquefied in the secondary side 12 is discharged directly into the collector, which contains a supply 50 of secondary fluid up to a fill level 2a in the collector 2. This fill level is preferably selected such that the pipe between the first heat exchanger 1 and the collector 2, which is represented by elements 14 and 21, contains no liquid, but only liquid secondary fluid that has been liquefied in the secondary side 12 flows through it.

[0040] The amount of liquid secondary fluid is selected such that, in a state of the temperature control system in which the pump 3 is deactivated, enough liquid secondary fluid is filled in that, in the operating direction of the temperature control system, no liquid secondary fluid is arranged at the bottom of the first heat exchanger 1, and that the collector 2 is completely filled or only up to a defined filling level 2a with the liquid secondary fluid.

[0041] Preferably, the volume held by the collector, i.e., the supply 50 of liquid secondary fluid, is dimensioned such that the total liquid volume 50 is sufficient to supply the second heat exchanger 4 or, in the case of multiple heat exchangers, as further referred to in the Fig. 6, Fig. 7a, Fig. As shown in Figure 7b, all heat exchangers interacting with the spaces to be heated can be partially, i.e., at least up to 50%, but preferably up to 75% of their volume, and in any case up to a volume between 50% and 100% of their volume, filled with liquid. Thus, the volume 50 of the collector is approximately the sum of the volumes of the evaporators and their associated liquid lines located above the system fill level 2a, which is shown in Figure 7b. Fig. 1 or Fig. 2 is shown.

[0042] The collector 2 is therefore dimensioned such that it can hold enough liquid secondary fluid to fill the second heat exchanger at least half and preferably at least 3 / 4 of its volume with the liquid secondary fluid, or, if the temperature control system has more than one second heat exchanger, i.e., for example, a third or fourth heat exchanger, the collector is dimensioned in this case and filled with the liquid secondary fluid during operation of the temperature control system so that all second heat exchangers and volumes of pipes above the collector 2 can be filled at least half or at least 3 / 4 of their volume.

[0043] The following will Fig. Section 2 explains. A pressure-resistant, closed-loop system is described, consisting of a heat transfer unit 1, a collector 2, a pump 3, and another heat transfer unit 4 located in a closed space 5. The heat transfer unit 1, the collector 2, and the pump 3 are located geodesically below the space 5 to be cooled and the heat exchanger 4 located within it. The pump 3 pumps the liquid fluid from the collector 2 into the heat exchanger 4. The fluid is in its liquid phase in the collector 2, while the remaining part of the loop, above the system fill level, is filled with the vapor phase of the fluid. The liquid and vapor phases are always in thermal equilibrium. The pump 3 delivers the volume flow rate corresponding to the mass flow rate required to supply the required cooling capacity to the space 5.Therefore, pump performance control is necessary. This can be achieved, for example, by adjusting the speed or by periodically synchronizing the pump's operation. The pressure in the overall system is determined by the material properties, more precisely by the vapor pressure curve of the fluid used. Good results have been obtained using CO2 as the fluid. However, the use of other fluids is also conceivable and possible.

[0044] The following will Fig. As described in section 3, if a heat flow Q0 is extracted from heat exchanger 1, the vaporous fluid condenses there, and the pressure in the overall system drops. If pump 3 is activated simultaneously, the fluid in its liquid phase is conveyed to heat exchanger 4. There, it evaporates, absorbing the heat flow Q0, thus cooling the closed chamber 5. The vapor produced during the evaporation of the fluid is fed back to heat exchanger 1 in the closed piping system, where the fluid then condenses and, in its liquid phase, is conveyed to collector 2 solely by gravity. The cycle is thus closed, and it is possible to extract the heat flow Q0 from chamber 5, which, in an adiabatic piping system, would also be extracted from heat exchanger 1 at the same level.In this application, the fluid circulates counterclockwise, thus corresponding to the delivery direction of the pump 3 shown.

[0045] Fig. Figure 4a shows an implementation of the temperature control system with defrosting and heating functions, i.e., to supply energy to the room 5 to be heated. For this purpose, a heating control unit 91 is preferably provided, which is configured to control a resistance heater 92 that is in thermal interaction with the collector 2 and, in particular, with the liquid secondary fluid in the collector 2. The heating control unit 91 is connected to the primary control unit 82 of Fig. 1 coupled to the primary circuit 11, which is in Fig. As shown in Figure 1, the heating function for the room is to be deactivated. Furthermore, pump 3 is deactivated, and warm secondary fluid vapor is generated in collector 2 by the heating provided by heater 92.

[0046] Under certain operating conditions, such as defrosting, a heat flow Q is supplied to the heat exchanger 4. H to supply. Ideally, this can be achieved by ensuring that the heat flow Q supplied to the room H The fluid is fed directly into collector 2. In collector 2, the fluid is in its liquid phase. The heat flow Q is introduced. HThe fluid is evaporated, and the vapor increases the system pressure in the closed circuit. The vapor is then routed clockwise through the now thermally inactive heat exchanger 1 and the associated piping system into heat exchanger 4. There, the fluid condenses, releasing its heat of condensation, and in its liquid phase, driven by gravity, flows through pump 3, which in this operating state allows free flow against its intended direction of delivery, into tank 2. There, further heat input Q increases the temperature. H Liquid fluid evaporates again, which then condenses in its vapor phase in heat exchanger 4, thus completing the cycle. This increases the heat flow Q. H, which is supplied to the collector 2 in a simple form, for example directly in the form of electrical energy, is guided through the closed circuit, quasi in fluid-technical natural circulation, which is also called the thermosiphon principle, to the heat exchanger 4.

[0047] Fig. Figure 4b shows an alternative implementation in which a further pump 3a is provided, which is controlled by the heating controller 91, while at the same time a cycle reversal is achieved in the primary circuit 11 in order to generate warm steam from the liquid secondary fluid pumped via the first heat exchanger and, in particular, into the first heat exchanger. In this implementation in Fig. 4b is not a resistance heater 92, as in Fig. 4a, required.

[0048] Besides the in Fig. In the variant shown in 4a, to increase the temperature and thus the saturation pressure in the circuit, it is also conceivable to use a pump 3a, which is then operated instead of pump 3, to pump the fluid into the heat exchanger 1 and then increase the heat flow Q there. H to supply. This heat flow can, for example, be the heat flow of a cold steam process, which is released by its condenser.

[0049] Fig. Figure 5 shows a more detailed representation of the primary circuit 11 with the primary side 10 of the heat exchanger 1, the compressor 11b, the condenser or liquid 11a and the expansion element 11c, wherein the secondary side 10 of the first heat exchanger acts as an evaporator in the primary circuit.

[0050] The heat exchanger 1, which represents the heat sink of the fluid circuit, can in one embodiment be the evaporator of a refrigeration process, in particular a vapor-combustion process, which, as is known, consists of a compressor, a condenser, an expansion valve, and an evaporator, each connected by pipes. This arrangement makes it possible to extract cooling power generated by the refrigeration process from the closed space 5 by means of the fluid circuit described above. This arrangement is always advantageous when it is essential to prevent the working fluid of the refrigeration circuit, especially a flammable refrigerant, from entering the closed space 5 in the event of a leak. In a particular embodiment, the refrigeration process can be combined with the receiver and at least one pump to form a single structural unit. This structurally integrated variant is indicated by the dashed line in Fig. 5 indicated.

[0051] The constructive unit 11a, which comprises the primary circuit 11 as well as the first heat exchanger 1, the collector 2 and the pump 3 of the secondary circuit, is in Fig. 5 shown in dashed lines, and this constructive unit 11a can preferably be conveniently located below the chassis or the loading floor of a delivery vehicle.

[0052] The following refers to Fig. Figure 6 shows an embodiment in which two rooms 5 and 5a are provided, each requiring a specific temperature control. In particular, in addition to the elements described in relation to the Fig. As explained in sections 1-5, a controllable distributor arrangement 100 and a collection arrangement 110 are provided. In particular, the controllable distributor arrangement has a distributor inlet 103, which is connected to a collector outlet 22 of the collector 2, a first distributor outlet 104, which is coupled to a heat exchanger inlet 41 of the second heat exchanger 4, and a second distributor outlet 105, which is connected to a heat exchanger inlet 41a of the third heat exchanger 4a.

[0053] The collection arrangement 110 comprises a first collection inlet 111 and a second collection inlet 112. The first collection inlet is connected to a heat exchanger outlet 42 of the second heat exchanger, and the second collection inlet 112 is connected to a heat exchanger outlet 42a of the third heat exchanger. Furthermore, the collection outlet 113 is coupled to a heat exchanger inlet 13 of the secondary side of the first heat exchanger 1.

[0054] Both the first and second rooms each include a temperature sensor 71, 73 to detect the actual temperatures in the first and second rooms, respectively, and to supply this information to the secondary control unit 70. The secondary control unit 70 includes inputs or memory locations for storing the target temperatures of the first and second rooms. The target temperatures of the two rooms can be the same, but are preferably different, with the first room preferably having a lower target temperature than the second room.

[0055] The secondary control 70 is designed to control the controllable distributor arrangement such that a first flow 101 of the liquid secondary fluid from the distributor inlet 103 to the first distributor outlet 104 is enabled when a first deviation of the first actual temperature from a first setpoint temperature for the room is detected, and that a second flow 102 from the distributor inlet 103 to the second distributor outlet is enabled when a second deviation of the second actual temperature from a second setpoint temperature for the further room 5a is detected.

[0056] For the distributor arrangement 100, there are various implementations, as shown in Fig. 7a and Fig. 7b are shown. Fig. 7a The distribution arrangement includes a branch point 106. In the case of the Fig. In the embodiment shown in Figure 7a, the branch point is coupled to the distributor input 103, and the pump 3 is controllable and coupled between the branch point 106 and the first distributor output 104. A further controllable pump 3a is provided, which is arranged between the branch point 106 and the second distributor output 102.

[0057] In the alternative embodiment, as described in Fig. As shown in Figure 7b, the controllable pump 3 is arranged between the distributor inlet 103 and the branch point 106, and a first controllable throttle arrangement 6 is arranged between the branch point 106 and the first distributor outlet 104. A further controllable throttle arrangement 6a is arranged between the branch point and the second distributor outlet 105.

[0058] For a further third room to be heated, 5b, the following applies: Fig. 7a or Fig. In the embodiment shown in Figure 7b, a heat exchanger 4b is arranged which is in thermal interaction with the third space, i.e., either inside the space or inside the wall of the space, and a third temperature sensor 73 is provided to detect the temperature of the third space and to generate a Fig. to send the control shown in 7a or 7b, in order to do the following at the Fig. In the embodiment shown in 7a, a third pump 3b is to be controlled, or in the case of the embodiment shown in Fig. 7b shows an embodiment in which a third controllable throttle arrangement 6b is to be controlled.

[0059] For more than two rooms to be cooled, all supplied with cooling from the single collector 2, a mixed arrangement of pumps and throttles can also be used, so that, for example, in the Fig. In the embodiment shown in Figure 7b, instead of the throttle 6b, another pump is provided, which is arranged between the distributor input 103 and the third distributor output. Further implementations can be implemented to control three outputs from one output of the distributor arrangement 100 in a controlled manner and selectively.

[0060] Preferably, as it is in Fig. As shown in Figure 7a, the room to be temperature-controlled, room 5, has the coldest target temperature, which is, for example, in the deep-freeze range and is between -30°C and -15°C. The other room to be temperature-controlled, 5a, can, for example, have a cold or freshness temperature slightly above 0°C and below 10°C, and the other room to be temperature-controlled, 5b, can, for example, have a temperature above 15°C and below 20°C. Further temperature ranges for the different rooms can also be implemented, such that the three rooms are assigned different target temperatures.

[0061] The collection arrangement 110 is preferably designed as a simple line connection, as shown in Fig. 7a and Fig. Figure 7b is shown. In alternative embodiments, the collection arrangement 110 can also have control elements and be controlled accordingly by the secondary control 70 to enable or prevent flow into a specific space.

[0062] In general, the controllable distributor arrangement or a controllable collection arrangement is designed to supply the second heat exchanger 4, which is in thermal interaction with the space to be cooled, or the third heat exchanger 4a, which is in thermal interaction with the further space to be cooled 5a, with liquid secondary medium from the collector 2. As shown in Fig. 6 and Fig. 7a and Fig. As shown in Figure 7b, the distributor arrangement can be controlled. Alternatively, control can also be achieved via the collection arrangement.

[0063] If the task is to regulate the temperature of several rooms 5, 5a and possibly other rooms, this can be achieved using several pumps 3, 3a connected in parallel and possibly additional controllable throttles.

[0064] According to the in Fig. In the process described in section 3, the fluid in its liquid phase is fed into the heat exchangers or evaporators 4, 4a, and possibly other heat exchangers. The pumps are controlled so that only the amount of fluid required to reach or maintain the desired temperatures in the rooms is delivered to the heat exchangers. With this arrangement, the system pressure in the closed fluid circuit must always be adjusted so that the lowest achievable temperature can be reached through heat transfer in the heat exchangers. Each pump 3, 3a therefore delivers the volume flow rate corresponding to the mass flow rate required to supply the required cooling capacity to the rooms 5, 5a. Pump capacity control is therefore necessary. This can be achieved, for example, by adjusting the speed or by periodic, time-based cycling.

[0065] If the system is started from, for example, the ambient temperature, the evaporation pressure, and thus the corresponding saturation temperature of the fluid in the circuit, is continuously reduced until the highest achievable temperature in the respective room is reached. The pump for the room with the highest achievable temperature is then switched off, and the temperature in the fluid circuit is further lowered until the lowest required room temperature is also reached. At that point, the pump for that room can also be switched off, and there is no further cooling effect. If no more liquid fluid is supplied to evaporators in rooms with a temperature higher than the saturation temperature, they become thermally inactive as the vapor phase of the fluid reaches the respective room temperature. If cooling is required again in a room, the corresponding pump is switched on or off.switched off, i.e., their quantity delivery is timed or their output is regulated in stages.

[0066] Analogous to the one in Fig. 4a or Fig. In accordance with the method described in section 4b for the purpose of adding heat, e.g., for defrosting the evaporator surfaces 4, 4a, and possibly other evaporator surfaces, the overall circuit can also be reversed in its flow direction. In this case of heat addition, the fluid circulates clockwise. For cooling, i.e., for heat extraction from the chambers 5, 5a, and possibly other chambers, the pumps are reactivated, and the heat exchanger 1 is supplied with heat as described in section 4b. Fig. 3. The heat flow Q0 is extracted, and the fluid now circulates through the respective circuits again in a counterclockwise direction. With this arrangement, it is therefore possible to regulate the temperatures T5, T5a, and any other temperatures in the respective rooms simply by controlling the corresponding pumps.

[0067] The collector 2, with its associated filling volume, is designed such that the total liquid volume is sufficient to supply the evaporators 4, 4a, and any other evaporators at least partially, or preferably to approximately ¾ of their volume, with liquid. The volume of the collector 2 is therefore approximately the sum of the volumes of the evaporators 4, 4a, and any other evaporators, as well as their associated liquid lines located above the [unclear text]. Fig. 2. System fill level shown.

[0068] As it is in Fig. As shown in Figure 5, even in a multi-temperature application with pumped fluid undergoing phase change, the integration of all components, including, if applicable, the refrigeration circuit components for generating a heat flow Q0 to be dissipated, as well as the pumps required for this purpose, into a single structural unit is possible. Alternatively to the one shown in Fig. The given task can also be solved using a single pump 3 and a series of valves, as described in section 7a with several pumps. The opening and thus the flow through the valves depends on the cooling requirements of rooms 5 and 5a.

[0069] In preferred embodiments of the present invention, when a demand for temperature control arises simultaneously from two rooms, the distributor arrangement is controlled such that different passages of the distributor arrangement or the collection arrangement are open at different times. This ensures that only one passage from the distributor inlet to a distributor outlet is open at any given time, while the other passage(s) from the distributor inlet to the second, third, or subsequent distributor outlet(s) are closed. This prevents the tank 50 in the collector from being emptied too quickly, thus eliminating the need for restrictions regarding a minimum pipe diameter. Alternating and preferably clocked operation of, for example, the two pumps in the Fig. 7a, which are shown with 3 and 3a, will nevertheless be sufficient to bring the rooms 5, 5a to the corresponding temperatures, even if at the same time a corresponding cooling requirement is detected via the corresponding temperature sensors and the corresponding required setpoint temperatures are determined by the pump control 72.

[0070] Fig. Figure 8 shows a preferred procedure for dividing a room into two or three rooms. Fig. 7a, Fig. 7b or Fig. 6 to defrost independently of the other room(s). For this purpose, in a first step 201, it is determined that the first room 5 should remain cool and the second room 5a should be defrosted. In a second step 203, the secondary control of Fig. 6 is switched such that the first passage 101 is open and the second passage 102 is closed. Then the pump 3 is operated until the second heat exchanger 4 is completely filled with liquid secondary fluid.

[0071] In step 207, the first passage 101 is closed and the second passage 102 is opened. Then the heating device, i.e., the heater 92, is Fig. 4a or the primary circuit 11 in Fig. 4b is activated via the heating control 91, or it is ensured that warm steam can enter the heat exchanger 4a of the second chamber, since it is empty. In contrast, no hot steam can enter the heat exchanger 4 of the first chamber because it is filled to the top with liquid secondary fluid, despite the fact that the collection arrangement 110 is a passive collection arrangement that does not include any throttles or anything similar.

[0072] As soon as it appears in step 211 in Fig. As shown in Figure 8, once the ice has melted from the wall of the third heat exchanger 4a in the second room 5a (and preferably the ice has been removed from the room), the pump is restarted, and the heating device 92 is switched on. Fig. 4a or the reversal of the primary circuit 11 and the activation of pump 3a from Fig. 4b are deactivated again. This allows cool secondary fluid to be introduced back into the heat exchanger 4a for the second chamber 5a, and the chamber is cooled back to the target temperature, as described in step 213 in Fig. Figure 18 shows that normal operation continues once the second chamber has returned to its normal temperature. Simultaneously, the first passage can be opened either before or in conjunction with step 211 so that, depending on the implementation of the distributor arrangement, the liquid secondary medium previously pumped in heat exchanger 4 flows back out of the heat exchanger and into tank or collector 2. In the Fig. In the embodiment shown in 7a, the pump 3 is deactivated so that the liquid flows back from the heat exchanger 4 due to gravity, while the pump 3a is activated to cool again after the ice has been removed from the further space 5a.

[0073] At the in Fig. In the embodiment shown in Figure 7b, before step 211, i.e., with pump 3 not activated, the throttle valve 6 is first opened so that the second heat exchanger 4 empties. Then, once empty, the throttle valve is closed, pump 3 is activated, and throttle valve 6a is opened so that liquid secondary medium can again enter the third heat exchanger 4a for cooling the further chamber 5a after the ice has been removed. The throttle valve can be designed as a throttle valve with a controllable cross-section to realize more states than the two states "on" and "off". Alternatively, the throttle valve can be implemented as an on-off throttle valve, i.e., for example, as a ball valve with the positions "open" or "closed", without intermediate positions with "throttled" flow.

[0074] It should be noted that all the embodiments described for defrosting can also be used to heat the corresponding chamber or room to be heated. For this purpose, it is typically necessary to operate the heating system for longer than just until the ice moves away from the wall.

[0075] By filling the heat exchanger in the room 5 to be tempered with cold liquid secondary fluid before heating the further room 5a to be tempered, a certain cold buffer is placed in the room 5 to be tempered, so that the cold temperature in the room 5 to be tempered is maintained during the heating situation of the further room 5a.

[0076] This allows a robust multi-temperature application with both heating and cooling operation to be achieved with a minimal number of individual (to be controlled) components using a single collector 2 from which the secondary fluid is pumped for the respective rooms to be temperature controlled.

[0077] Fig. Figure 9 shows a representation of a room 5 to be tempered with a second heat exchanger 4 installed in the room before the wall of the room is fully assembled. In particular, the heat exchanger comprises an upper collection pipe 49a and a lower collection pipe 49b, with corresponding heat exchanger pipes 49c arranged between the collection pipes, so that, pumped from below by the pump 3 via the lower collection pipe 49b into the pipes 49c, and evaporates due to a corresponding temperature in the room 5 to be tempered, so that heat can be carried away from the room 5 to be tempered by the vapor, which is collected at the top via the collection pipe 49a.

[0078] Preferably, the actual wall is a smooth wall 10, as shown in Fig. Figure 10 shows corresponding projections 49d, such that an air space exists between the wall, i.e., between the corresponding projections 49d, even if the goods to be transported or temperature-controlled are loaded directly against the projections 49d. The implementation of the heat exchanger 4 within the wall ensures that simple cooling can be achieved without a cooling fan, and in particular, that defrosting is very easy. Due to the projections 49d extending from bottom to top, when the heat exchanger 4 is... Fig. 9 is heated, so when warm steam from above enters the corresponding heat exchanger 4 via the upper collection pipe 49a, the ice that accumulates on the wall during cooling operation detaches and simply slides down to be collected and transported out by an operator of the room to be tempered.

[0079] The defrosting function is therefore very quick because the ice does not need to be melted, but merely loosened from the wall. Once this has occurred, cooling in the room to be cooled is immediately resumed to ensure that the room does not become too warm during the defrosting process.

[0080] The Fig. 11a and Fig. Figure 11b shows an exemplary implementation of the elements as they appear in Fig. 1 or in Fig. 7a are shown. In particular, it shows Fig. 11a the three pumps 3, 3a, 3b for supplying the respective heat exchangers 4, 4a, 4b in the three rooms to be heated via the in Fig. 11a upwards through the loading floor 70 pipes passing through. In Fig. Figure 11a shows the first heat exchanger 1 with the secondary side and the corresponding connections 13, 14, which is connected to the collector 2, wherein the collector inlet 21 is arranged lower than the lower connection 14 of the secondary side of the first heat exchanger 1, as can be seen from the inclined pipe connection in Fig. 11a is implemented, which connects the heat exchanger outlet 14 with the collector inlet 21.

[0081] Fig. Figure 11b shows a corresponding implementation mainly of the primary circuit with the condenser 11a, which is equipped with a fan to dissipate the heat to the outside, as well as with the expansion device 11c and the compressor 11b, which are connected to the primary side 10 of the first heat exchanger 1.

[0082] Out of Fig. 11a and Fig. As shown in Figure 11b, all elements below the loading floor 70 of a van can be accommodated in a corresponding compartment which can communicate with the outside via a door with passages so that the heat emitted to the outside by the condenser 11a can escape from the inside of the compartment of the van to the outside.

[0083] It is evident that the collector 2 is located below the plate heat exchanger, i.e., the first heat exchanger 1, so that the first heat exchanger 1 is "dry" in the operating state because the liquid secondary medium accumulates in the collector 2 in order to be pumped out from there as a liquid supply by the pumps 3, 3a, and 3b, respectively. It should be noted that in the Fig. 11a and Fig. 11b corresponding isolations are not drawn for illustrative purposes, and that collector 2 typically has a larger volume than in Fig. will have 11a.

[0084] In a method for operating the temperature control system, the pressure in the operation of the temperature control system is maintained in such a way that the secondary fluid is under such pressure that it undergoes a phase change from liquid secondary fluid to vaporous secondary fluid in the second heat exchanger, and that the secondary side of the first heat exchanger undergoes a phase change from vaporous secondary fluid to liquid secondary fluid.

[0085] In a method for manufacturing the temperature control system, the corresponding elements are arranged such that the collector is located below the first heat exchanger, and that the second heat exchanger is located above the collector and preferably also above the first heat exchanger, while preferably the pumps are located below the collector 2 to ensure that the pumps are always supplied with liquid secondary medium on the inlet side to prevent the pumps from running dry.

[0086] Preferred embodiments of the present invention relate to a mobile device with a temperature control system as described above, which is designed as a transport refrigeration arrangement, wherein the mobile device is designed as a passenger car, a truck, a delivery vehicle, a cargo bike with or without an internal combustion or electric motor, a boat or a spacecraft.

[0087] The present invention is particularly preferred for a transport refrigeration system based on natural refrigerants for a vehicle with variably controllable temperature zones in the temperature ranges of ambient, normal cooling, and deep freezing. The secondary circuit is preferably filled with CO2, wherein temperature levels are adjustable at least for normal cooling and deep freezing, and wherein the deep-freeze and normal cooling temperature levels can be controlled and maintained simultaneously at two heat exchangers. Furthermore, propane is preferably used in the primary circuit, in an integrated system designed for underfloor mounting and connected to the secondary circuit, as described in the [reference to the invention]. Fig. 11a and Fig. 11b is shown.

[0088] If the mobile device is equipped with an internal combustion engine, it is preferable to provide a battery which, as described in Fig. As shown in Figure 1, a battery 100 is provided, and the power generation by the combustion engine 110 is decoupled from the power generation in the primary circuit 11. If the mobile device is electrically operated, the compressor 11b, or more generally the primary circuit, can be supplied directly from the vehicle battery without the need for a separate battery.

[0089] A heat pump circuit, such as that used in... can be used as the primary circuit. Fig. 5 and Fig. Figure 11c is shown. Alternatively, however, all other possibilities can be used to extract heat from the secondary side 12 of the heat exchanger 1 via the primary side 10 of the heat exchanger 1.

[0090] Furthermore, it should be noted that the second heat exchanger 4 can be implemented as a heat exchanger integrated into a wall without its own fan. However, the second heat exchanger 4 can also be located in the room and equipped with a fan. Alternatively, the second heat exchanger 4 can be designed as a liquid-to-liquid heat exchanger to cool a medium other than air, which in turn can regulate the temperature of the room.

[0091] Although some aspects have been described in connection with a device, it is understood that these aspects also constitute a description of the corresponding process, so that a block or component of a device is also to be understood as a corresponding process step or as a feature of a process step. Similarly, aspects described in connection with or as a process step also constitute a description of a corresponding block, detail, or feature of a corresponding device.

[0092] The embodiments described above merely illustrate the principles of the present invention. It is understood that modifications and variations of the arrangements and details described herein will be obvious to those skilled in the art. Therefore, it is intended that the invention be limited only by the scope of protection set forth in the following claims and not by the specific details presented herein in the description and explanation of the embodiments. QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] WO 2023052244 A1

[0006]

Claims

[1] Temperature control system for temperature control of a room to be temperature controlled, with the following features: a primary circuit (11); a secondary circuit; a first heat exchanger (1) with a primary side (10) and a secondary side (12), wherein the first heat exchanger (1) is configured to couple the primary circuit (11) and the secondary circuit, and wherein the primary circuit (11) is configured to extract heat from the secondary side (12) of the first heat exchanger (1) via the primary side (10) of the first heat exchanger, the secondary circuit has the following characteristics: the secondary side (12) of the first heat exchanger (1); a collector (2) which is arranged in a unit of the temperature control system below (60) the secondary side of the first heat exchanger (1); a pump (3) coupled to the collector (2); and a second heat exchanger (4) which, in the operation of the temperature control system, is arranged in thermal interaction with the space (5) to be temperature controlled and is located above the collector (2); and a secondary fluid (50) which is arranged in the secondary circuit in the operation of the temperature control system and is under pressure such that a phase change from a liquid secondary fluid to a vaporous secondary fluid takes place in the second heat exchanger (4) and a phase change from the vaporous secondary fluid to the liquid secondary fluid takes place in the secondary side (12) of the first heat exchanger (1). [2] Temperature control system according to claim 1, wherein the secondary side (12) has a secondary inlet (13) and a secondary outlet (14), in which the collector (2) has a collector inlet (21) and a collector outlet (22), where the pump (3) has a pump inlet (22) and a pump outlet (32), in which the second heat exchanger (4) has a heat exchanger inlet (41) and a heat exchanger outlet (42), or in which the collector (2) is connected on the inlet side to the secondary side (12) of the first heat exchanger via a first pipe and on the outlet side to the pump (3) via a second pipe and has a cross-section that is larger than a first cross-section of the first pipe and a second cross-section of the second pipe. [3] Temperature control system according to claim 2, wherein the secondary outlet (14) is connected to the collector inlet (21), where the collector outlet (22) is connected to the pump inlet (31), where the pump outlet (32) is connected to the heat exchanger inlet (41), or where the heat exchanger outlet (42) is connected to the secondary inlet (13). [4] Temperature control system according to one of the preceding claims, in which, in a standstill state of the temperature control system when the pump (3) is deactivated, a quantity of liquid secondary fluid is filled into the temperature control system, such that in one operating direction no liquid secondary fluid is arranged at the bottom of the first heat exchanger (1) and the collector (2) is completely filled or filled to a defined filling level, which is at least half the filling level of the collector, with the liquid secondary fluid. [5] Temperature control system according to one of the preceding claims, wherein the room to be temperature controlled (5) has a floor (70), the second heat exchanger (4) is arranged in the room above the floor (70) and the first heat exchanger (1), the collector (2) and the pump (3) are arranged below the floor and outside the room and a first conduit from the pump (3) to the second heat exchanger (4) and a second conduit from the second heat exchanger (4) to the first heat exchanger (1) penetrate a room wall. [6] Temperature control system according to one of the preceding claims, wherein the secondary fluid is non-flammable or contains CO2, and the primary fluid is flammable or contains propane. [7] Temperature control system according to one of the preceding claims, comprising the following features: a secondary control system with the following features: a temperature detector (71) in the room (5) to record the actual room temperature; a pump control (72) to activate the pump (3) when the actual room temperature deviates from a set room temperature by a predetermined temperature difference, or to deactivate the pump (3) when the actual room temperature deviates from a set room temperature by less than a predefined temperature difference. [8] Temperature control system according to one of the preceding claims, wherein the primary circuit has the following features: a primary fluid; the primary side (10) of the first heat exchanger (1); a compressor (11b) for compressing primary gaseous fluid; a condenser (11a) for condensing compressed primary vapor fluid; an expansion element (11c) connected to the primary side (10) of the first heat exchanger to introduce liquid primary fluid into the primary side of the first heat exchanger (1); and a primary control (82) coupled to a temperature detector (81) for detecting the actual temperature of the liquid secondary medium in the collector (2) and configured to activate the compressor (11b) or the primary circuit (11) when the actual temperature of the liquid secondary fluid in the collector (2) deviates from a setpoint temperature of the liquid secondary fluid (50) in the collector (2) by more than a predetermined temperature difference, or to deactivate the compressor (11b) or the primary circuit (11) when the actual temperature of the liquid secondary fluid (50) in the collector deviates from a setpoint temperature of the liquid secondary fluid (50) in the collector by less than a predetermined temperature difference. [9] Temperature control system according to one of the preceding claims, which is arranged on a mobile device having an internal combustion engine (110), wherein the primary circuit (11) has an accumulator battery (100) which supplies the compressor (11b), and wherein the mobile device has a generator to charge the accumulator battery (100) by means of the internal combustion engine (110). [10] Temperature control system according to one of the preceding claims, wherein the first heat exchanger (1) is designed as a plate heat exchanger, where the secondary circuit has piping to connect elements of the secondary circuit, in which the collector (2) is dimensioned to accommodate enough liquid secondary fluid so that the second heat exchanger (4) can be filled at least half and preferably at least three-quarters of its volume with liquid secondary fluid, or wherein the temperature control system has one or more further heat exchangers (4a, 4b), and wherein the collector (2) is dimensioned and is dimensioned in the operation of the temperature control system to hold enough liquid secondary fluid so that all heat exchangers arranged in the room to be temperature controlled or in one or more further rooms to be temperature controlled, as well as volumes of corresponding pipelines above the collector (2), can be filled at least half and preferably three-quarters full. [11] Temperature control system according to one of the preceding claims, comprising the following features: a heating device (92, 3a) for heating the liquid secondary fluid; and a heating control (91) configured to deactivate the heat extraction from the secondary side of the first heat exchanger (1) in a heating operation in order to activate the heating device, and to deactivate the pump (3) or to reverse its pumping direction, wherein the pump (3) is configured to allow flow in the opposite direction to an operating direction in the activated state when deactivated, or to activate a bypass around the pump (3) which is deactivated when the pump (3) is activated. [12] Temperature control system according to claim 11, wherein the heating device has a heater (92) to heat the liquid secondary fluid in the collector (2), or wherein the heating device has a primary control (82) to effect a reversal of the circuit in the primary circuit (11) to supply heat to the secondary side (12) of the first heat exchanger (1) via the primary side (10), and wherein the heating device has a further pump (3a) to pump liquid secondary fluid from the collector (2) into the secondary side (12) of the heat exchanger (1). [13] Temperature control system according to one of the preceding claims, comprising the following feature: a third heat exchanger (4b) which is arranged in the operation in thermal interaction with another space (5a) which is different from the tempering space (5); and a distributor arrangement (100) or a collection arrangement (110) for selectively supplying the second heat exchanger (4) or the third heat exchanger (4a) with liquid secondary medium. [14] Temperature control system according to claim 13, wherein the distributor arrangement (100) has a distributor inlet (103) connected to a collector outlet (22), a first distributor outlet (104) coupled to a heat exchanger inlet of the second heat exchanger (4), and a second distributor outlet (105) connected to a heat exchanger inlet (41a) of the third heat exchanger (4a), or wherein the collector arrangement (110) has a first collector inlet (111) coupled to a heat exchanger outlet (42) of the second heat exchanger (4), a second collector inlet (112) connected to a heat exchanger outlet (42a) of the third heat exchanger (4a), and a collector outlet (113) connected to a heat exchanger inlet (13) of the secondary side (12) of the first heat exchanger (1). [15] Temperature control system according to claim 13 or 14, wherein the distributor arrangement (100) comprises the pump (3) which is arranged between the distributor inlet and a branch point (106), and wherein a first controllable throttle arrangement (6) is arranged between the branch point (106) and the first distributor outlet (104), and wherein a second controllable throttle (6a) is arranged between the branch point (106) and the second distributor outlet (105), or wherein the distributor arrangement (100) comprises a branch point (106) which is connected to the distributor inlet (103), wherein the pump (2) is controllable and is arranged between the branch point (106) and the first distributor outlet, and wherein a further controllable pump (3a) is arranged between the branch point (106) and the second distributor outlet (105). [16] Temperature control system according to one of claims 13 to 15, comprising the following features: a first temperature sensor (71) to detect the actual temperature in the room (5); a second temperature sensor (72) to detect a second actual temperature in the further room (5a); a secondary control (70) for controlling the distributor arrangement (100), such that a first flow of the liquid secondary fluid from the distributor inlet (103) to the first distributor outlet (104) is enabled when a first deviation of the first actual temperature from a first setpoint temperature for the room (5) is detected, and that a second flow (102) to the second distributor outlet (105) is enabled when a second deviation of the second actual temperature from a second setpoint temperature for the further room (5a) is detected. [17] Temperature control system according to claim 16, in which the secondary control (70) is configured to change the first flow rate and the second flow rate at different time periods when the first deviation and the second deviation are detected simultaneously, so that at one time the first flow rate is not changed and the second flow rate is changed or vice versa. [18] Temperature control system according to one of claims 16 to 17, wherein the first setpoint temperature is lower than the second setpoint temperature, wherein the primary circuit is designed to extract enough heat from the secondary circuit to ensure that the liquid secondary fluid in the collector has a temperature that is lower than or equal to the first setpoint temperature. [19] Temperature control system according to claim 18, in which the secondary control (70) is configured to prevent the first flow after a switch-on state and to allow the second flow until the second target temperature is reached in the further space (5a), and then to prevent the second flow and to allow the first flow until the first target temperature is reached in the space (5). [20] Temperature control system according to one of claims 13 to 19, comprising the following features: a third temperature sensor (73) for recording a third actual temperature in a third room (5b); a fourth heat exchanger (4b) which is arranged in thermal interaction with the third space (5b) in the operation, wherein the distributor arrangement (100) has a third distributor outlet (106), and wherein the distributor arrangement (100) is configured to control a third flow between the distributor inlet (103) and the third distributor outlet (106) depending on the secondary control (70), and wherein the collector arrangement (110) has a third collector inlet which is coupled to a heat exchanger outlet of the fourth heat exchanger and is coupled to the collector outlet. [21] Temperature control system according to claim 20, wherein a first setpoint temperature in the room is lower than a second setpoint temperature in the second room (5a), and wherein a third setpoint temperature in the third room (5b) is higher than the second setpoint temperature in the further room (5a). [22] Temperature control system according to one of claims 13 to 21, comprising the following features: a heating device (92); a heating control (91) for activating the heating device and controlling the distributor arrangement, such that a second passage (102) from the distributor input (103) to the second distributor output (105) is open, and a first passage (101) from the distributor input (103) to the first distributor output (104) is closed in order to heat the third heat exchanger (4a) (207, 209), and to deactivate the pump (3). [23] Temperature control system according to claim 22, wherein the heating control (91) is configured to close the second passage (102) and open the first passage (101) and activate the pump (203, 205) before activating the heating device, so that the second heat exchanger (4) in the space (5) to be tempered is filled with liquid secondary fluid. [24] Temperature control system according to one of the preceding claims, comprising the space to be temperature controlled, which includes a wall, wherein the second heat exchanger (4) is arranged on the outside of the wall and in thermal interaction with the wall and is insulated from an environment of the space outside the wall by an insulating layer (30). [25] Temperature control system according to claim 24, wherein the wall has projecting areas (49d) and recessed areas between two projecting areas with respect to the projecting areas, wherein a material (20) is arranged between the wall and the second heat exchanger which has a thermal conductivity greater than the thermal conductivity of air. [26] Mobile device with a temperature control system according to one of the preceding claims, wherein the temperature control system is designed as a transport refrigeration arrangement, and wherein the mobile device is designed as a passenger car, truck, delivery vehicle, electric or non-motorized cargo bike, boat or spacecraft. [27] Method for operating a temperature control system for temperature control of a room to be temperature controlled, comprising: a primary circuit (11); a secondary circuit; a first heat exchanger (1) with a primary side (10) and a secondary side (12), wherein the first heat exchanger (1) is configured to couple the primary circuit (11) and the secondary circuit, and wherein the primary circuit (11) is configured to extract heat from the secondary side (12) of the first heat exchanger (1) via the primary side (10) of the first heat exchanger, wherein the secondary circuit comprises: the secondary side (12) of the first heat exchanger (1); a manifold (2) which, in operation of the temperature control system, is arranged below (60) the secondary side of the first heat exchanger (1); a pump (3) which is coupled to the manifold (2);and a second heat exchanger (4), which is arranged in thermal interaction with the room to be tempered (5) in the operation of the temperature control system and is arranged above the collector (2), by the following steps: ; Arranging a secondary fluid (50) in the secondary circuit; and Applying the secondary fluid (50) in the secondary circuit to such a pressure that a phase change from a liquid secondary fluid to a vaporous secondary fluid takes place in the second heat exchanger (4), and a phase change from the vaporous secondary fluid to the liquid secondary fluid takes place in the secondary side (12) of the first heat exchanger (1). [28] Method for manufacturing a temperature control system for temperature control of a room to be temperature controlled, comprising the following steps: Coupling a primary circuit (11) and a secondary circuit with a first heat exchanger (1) having a primary side (10) and a secondary side (12), wherein the primary circuit (11) is configured to extract heat from the secondary side (12) of the first heat exchanger (1) via the primary side (10) of the first heat exchanger, wherein the secondary circuit has the following features: the secondary side (12) of the first heat exchanger (1); a manifold (2) which, in operation of the temperature control system, is arranged below (60) the secondary side of the first heat exchanger (1); a pump (3) which is coupled to the manifold (2); and a second heat exchanger (4) which, in operation of the temperature control system, is arranged in thermal interaction with the space (5) to be temperature controlled and is arranged above the manifold (2); and Arranging a secondary fluid (50) in the secondary circuit, wherein the secondary fluid (50) in the secondary circuit is under pressure such that a phase change from a liquid secondary fluid to a vaporous secondary fluid takes place in the second heat exchanger (4) and a phase change from the vaporous secondary fluid to the liquid secondary fluid takes place in the secondary side (12) of the first heat exchanger (1).

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