Method and apparatus for temperature control of a temperature-controlled space

Abstract

The present invention provides a device for controlling the temperature of a space that is to be temperature-controlled, while a spatial limiting element separates the temperature-controlled space from the surrounding area. [Solution] The apparatus comprises a primary heat pump circuit having an evaporator, a condenser, a compressor, and an expansion element, wherein the primary heat pump circuit contains a natural primary working fluid such as flammable fluid, and the evaporator, liquefaction device, compressor, and expansion element are located outside a temperature-controlled space; and a secondary circuit comprising a temperature-controlled element that is thermally coupled to the evaporator or condenser via a heat exchanger, is fluidically separated from the evaporator or condenser, is located in a temperature-controlled space, and is connected to the heat exchanger via a piping configuration containing a secondary fluid different from the primary working fluid, the piping configuration passing through a space limiter.

Description

Technical Field

[0001] The present invention relates to controlling the temperature of a temperature-controlled space, and more particularly to the generation and distribution of refrigeration or heat in mobile or stationary refrigeration applications.

[0002] More particularly, the present invention relates to methods and apparatus for the generation or distribution of refrigeration or heat in mobile refrigeration or heating applications, for example, for road vehicles, trailers, or semi-trailers with refrigeration or heating structures that are refrigerated or heated using a compression refrigeration machine, for railway or marine refrigeration or heating structures or containers, or generally for temperature-controlled spaces in ventilation or air conditioning applications.

[0003] Furthermore, the present invention can also be used in the field of comfortable air conditioning in mobile applications such as buses or railway passenger cars in railway transportation. However, in principle, from a purely technical perspective, the solutions described herein can be advantageously used in fixed applications, so there is no need to restrict the present invention to these fields.

Background Art

[0004] Compression refrigeration machines are the most common design of refrigeration machines. This design utilizes the physical effect of heat of vaporization when the aggregate state changes from liquid to gas or from gas to liquid. In a compression refrigeration machine, a refrigerant with appropriate thermodynamic properties is moved in a closed cycle as shown in Figure 2A. In this case, the refrigerant undergoes a series of changes in aggregate state. The gaseous refrigerant is first compressed by compressor 1. In the subsequent heat exchanger (or heat transferr) 2 (the condenser or heat sink of the process), the refrigerant is condensed (liquefied) while releasing heat. Subsequently, the condensed refrigerant is expanded to the evaporation pressure via an expansion element 3, or in the simplest case, via a diaphragm or capillary tube, to reduce the pressure. In this process, the refrigerant becomes cold. In the downstream second heat exchanger (or heat transferr) 4 (the evaporator or heat source of the process), the refrigerant evaporates (evaporative cooling) while absorbing heat at a low temperature. The heat absorbed in this process represents the coldness used by the refrigeration system. The absorbed heat flow rate is referred to as the refrigeration capacity. Therefore, the evaporator is directly advantageously positioned in a refrigeration structure, in a refrigerated container, or generally in the cooled closed space of the application, to minimize heat exchange losses by bringing the items being refrigerated into as direct contact as possible with the heat source. Here, the cycle begins again. The process must be kept moving from the outside by supplying mechanical work (driving force) through the compressor. The refrigerant typically dissipates its heat output into the surrounding area by absorbing heat at lower temperature levels and supplying technical work at higher temperature levels. The same process described is referred to as a heat pump process when, as shown in Figure 2B, condenser heat released by the system's condenser is used instead of refrigeration capacity or energy supplied to the evaporator. In this application, this results in the ability, through proper process control and configuration of the system's components, to supply energy in the form of heat for heating purposes to the described structure or closed internal space of the application.One way to achieve this is to connect the pressure-side outlet of a compressor to a heat exchanger located in a closed structure such that the heat exchanger heats up during the operation of the structure. To this end, the remaining components perform their functions according to the process of the described application for refrigeration. Heat supply can also be used to achieve efficient defrosting of the heat exchanger in a closed space, which can be done by either time control or demand control.

[0005] The refrigerant cycle essentially consists of the following four components: compressor 1, condenser 2, expansion element 3, and evaporator 4. In single-stage or multi-stage refrigeration systems, the distinction is generally between the high-pressure and low-pressure sides. The high-pressure side extends from the pressure side of the compressor to the refrigerant inlet to the expansion element. The low-pressure side includes the portion of the refrigerant cycle from the refrigerant outlet leaving the expansion element to the compressor inlet. This is also true when the refrigerant cycle is operated as a heat pump, meaning the heat output provided by the condenser is used in place of the refrigeration capacity of the evaporator. As described, the heat output can be used to heat the application or to defrost the evaporator.

[0006] Regardless of its application, refrigerants used in the cyclical process should have as little environmental impact as possible, be cost-effective, and specifically be energy-efficient. An important criterion for evaluating the harmful environmental impact of a refrigerant is its global warming potential (GWP). This value is given for refrigerants in relation to the GWP value of CO2 (carbon dioxide). By definition, CO2 has a GWP value of 1. For F gas (or fluorine gas), which is often used as a refrigerant, the global warming potential can be several thousand. This further means that one kilogram of F gas released into the atmosphere during its production, use, or exhaust may have the same greenhouse effect as several tons of CO2.

[0007] The most important components of F gas are carbon, hydrogen, and fluorine. F gas often decomposes very slowly and, once released, can remain in the atmosphere for hundreds or even thousands of years. Regardless of its residence time and global warming potential, decomposition products are formed when F gas decomposes. These substances, such as trifluoroacetic acid or hydrogen fluoride, often have long-term adverse effects on people or the environment. For these reasons, international legislation is increasingly restricting, or even prohibiting, the use of F gas as a refrigerant through regulations and ordinances. Acceptance of F gas as a refrigerant is declining not only among consumers and users of refrigeration technology but also within society as a whole, and as a result, the refrigerant and heat pump manufacturing industries are increasingly seeking alternatives to existing refrigeration technologies that rely on the use of F gas.

[0008] Patent Document 1 describes a heat pump system comprising a heat pump, a consumer-side circuit, and a buffer tank configured as a gas separator in the consumer-side circuit. Propane is used in the heat pump, and the heat pump is located in a safe area outside the building.

[0009] Patent Document 2 describes a configuration for vehicle air conditioning, in which a first cycle can be switched between a refrigeration mode and a heating mode. CO2 circulates as a heat exchange fluid in the first supercritically operable cycle. A coolant for driving the vehicle's motor circulates in the second cycle. [Prior art documents] [Patent Documents]

[0010] [Patent Document 1] German Utility Model Application No. 202022100810 Specification [Patent Document 2] German Patent Application No. 102007039195 Specification [Overview of the project] [Problems that the invention aims to solve]

[0011] The objective of this invention is to provide an improved concept for temperature control in a temperature-controlled space. [Means for solving the problem]

[0012] This objective is achieved by the apparatus described in claim 1, the temperature-controlled space described in claim 24, the method for operating the apparatus for temperature-controlling the temperature of the temperature-controlled space described in claim 27, or the method for manufacturing the apparatus for temperature-controlling the temperature of the temperature-controlled space described in claim 28.

[0013] With a space limiter separating the space to be temperature-controlled from the surrounding area, the apparatus for temperature-controlling the space includes a primary heat pump circuit comprising an evaporator, a condenser, a compressor, and an expansion element, the primary heat pump circuit comprising a natural primary working fluid, and the evaporator, condenser, compressor, and expansion element being located outside the space to be temperature-controlled. The apparatus further includes a circuit comprising one or more temperature-control elements, which are thermally coupled to the evaporator and condenser via a heat exchanger and fluidically separated from the evaporator and condenser, and which are located in the space to be temperature-controlled and connected to the heat exchanger via a piping configuration comprising a secondary fluid different from the primary fluid, the piping configuration passing through the space limiter.

[0014] This invention is based on the discovery that in a primary heat pump circuit located outside a temperature-controlled space, i.e., in the area surrounding the temperature-controlled space, a natural primary working fluid is used that may have properties undesirable for a closed space when inhaled by living organisms, such as flammability. On the other hand, a different secondary fluid, which is typically harmless or non-flammable and therefore less hazardous to living organisms, is used in the secondary circuit. Thus, according to this invention, a primary working fluid and a secondary fluid that have properties favorable for compression and primary heat pump circuits, and on the other hand, properties favorable for temperature control in a temperature-controlled (closed) space, can be combined with each other.

[0015] Specifically, the use of flammable primary working fluids as examples of natural refrigerants enables high environmental compatibility and good energy efficiency characteristics in compression refrigeration / heating cycles. On the other hand, such refrigerants / heaters can generally only be used in enclosed spaces with considerable additional effort due to their flammability. Such refrigerants are hydrocarbons (HC) such as propane (R290) or propene (R1270). Other primary working fluids besides F gases include NH3 or NH3 / DME (R723), which are slightly flammable but toxic to humans in enclosed spaces and therefore undesirable. Fluorinated hydrocarbons are also found in this group of working fluids for refrigeration, and are flammable due to their molecular structure.

[0016] On the other hand, a non-flammable and therefore low-risk refrigerant / heat transfer medium can be used in the secondary circuit, which is not used for refrigeration or heat generation, but only for the distribution of cold and heat, and ideally undergoes a phase change when transporting cold or heat. Preferably, a secondary fluid is used that changes its aggregate state during heat transport. Heat is absorbed or released at a constant temperature, and the principle of a thermal siphon is driven by the density difference between the vapor and the liquid.

[0017] A piping configuration penetrating a space limiter and elements of a primary heat pump circuit, including at least a portion of a heat exchanger, located outside the space, prevent natural working fluids, such as flammable fluids, from entering the enclosed space. Only a noncritical heat transfer medium with the heat / cold to be transported enters the enclosed space, releasing the transported heat / cold into the space via a temperature control element. The temperature control element is typically a secondary fluid-air heat exchanger, while the heat exchanger is a primary working fluid-secondary fluid heat exchanger. Thus, the heat exchanger is coupled to the condenser of the primary heat pump circuit when heating is achieved as temperature control. However, when cooling is used as temperature control, the heat exchanger is thermally coupled to the evaporator of the primary heat pump circuit. In a preferred embodiment, the evaporator and condenser are configured such that the corresponding elements of the primary heat pump circuit can perform both functions depending on the direction of operation of the compressor.

[0018] Furthermore, the implementation of the heat exchanger can be configured such that the actual evaporator or condenser of the primary heat pump circuit is connected in series with the primary working fluid-secondary fluid heat exchanger. Alternatively, the functions can be integrated into a single element, which on the one hand achieves evaporation / condensation in the primary heat pump circuit, and on the other hand transfers heat or cold from the primary heat pump circuit to the secondary circuit. When the primary working fluid-secondary fluid heat exchanger is connected in series with the actual condenser or evaporator of the primary heat pump circuit, the arrangement of the two elements, i.e., the actual condenser or evaporator of the primary heat pump circuit, can be freely selected according to the actual conditions to be positioned before or after the primary working fluid-secondary fluid heat exchanger in the direction of the primary working fluid flow. When the two functions of a primary heat pump circuit—evaporation or condensation—and the function of heat transfer from one fluid to the other, while the two fluids are strictly separated from each other, are integrated into a single element, this element is also located outside the temperature-controlled space, that is, in a surrounding region separated from the temperature-controlled space by a spatial limiter.

[0019] In a preferred embodiment, the temperature control element is an air-secondary fluid heat exchanger with a phase transition. In this case, the piping configuration of the secondary circuit comprises a first section through which a liquid secondary fluid flows and a second section through which a steam secondary fluid flows. Depending on the embodiment, the secondary circuit can be implemented without a drive unit, i.e., according to the concept of a thermal siphon only, such that the secondary fluid is transported in the secondary circuit solely by gravity and the difference in density between the gaseous and liquid phases of the secondary fluid. However, depending on the embodiment, a pump may also be placed in the liquid transport section of the piping configuration to assist in the circulation of the secondary fluid, or a fan may be placed in the steam transport section of the piping configuration.

[0020] In particular, when using such support in a secondary circuit, it is preferable to provide a control device that causes defrosting to occur at specific times during normal refrigeration use in a temperature-controlled space, depending on the direction of pumping or blowing in the secondary circuit, in order to avoid freezing of temperature-controlled elements and, consequently, loss of efficiency. The pump or fan controlled by the control device can also be used to switch to refrigeration mode at a selected time when the temperature-controlled space is actually heated, for example, when a certain temperature is achieved, or when air conditions are achieved over a wide temperature range.

[0021] Preferably, the control device is also configured to reverse the cycle in the primary heat pump circuit, which is equivalent to reversing the compressor's transport direction so that the primary heat pump circuit operates in a way that the evaporator becomes a condenser, for example, when the primary heat pump circuit operates in a way that the evaporator is coupled to a heat exchanger, i.e., in a way that is used for cooling purposes. This means that heat is supplied to the heat exchanger, which in turn means that heat is also supplied to a temperature-controlled space. Reversing the transport direction can be achieved by the compressor, either by reversing the direction of rotation of the compressor wheel or by switching the four-way valves coupled to the pressure and suction sides of the evaporator and condenser of the primary heat pump circuit.

[0022] If the secondary circuit does not have a pump or fan, that is, if it simply operates according to the principle of a thermal siphon by reversing the refrigeration cycle, such as by switching the direction of transport of the compressor or by using a valve in the primary heat pump circuit, then it can be achieved that the switching occurs from refrigeration mode to heating mode during short periods of defrosting, or from "normal" heating mode to refrigeration mode for purposes such as temperature control, while also supplying cold or heat to temperature-controlled elements.

[0023] An alternative to the use of F gas as a refrigerant is the use of so-called natural refrigerants. The use of hydrocarbons (HCs) is particularly advantageous here because, in contrast to F gas, these substances have a very small and negligible global warming potential, and enable high energy efficiency in the refrigerant process, thus requiring only very small driving energy per unit of refrigeration or heating capacity. The disadvantage of hydrocarbons is their high flammability, which limits their use, or substantially eliminates their safe use, not only in small, enclosed spaces such as the refrigeration structures and refrigerated containers considered herein, but also in other enclosed spaces that are cooled or air-conditioned.

[0024] To minimize risk, and therefore the objective, is to use as little refrigerant as possible and to prevent the refrigerant from entering closed refrigeration structures and refrigerated containers, as well as other closed spaces being conditioned. This results in the use of refrigeration components with the smallest possible refrigerant volume to keep the refrigerant fill level as low as possible. Microchannel technology and plate heat exchangers are particularly suitable technologies for heat exchangers. The compactness of the overall system and the avoidance of storage volumes, such as those often used in refrigerant collectors, must also be considered. Compressors should have a small refrigerant volume and a low oil fill level to further reduce the refrigerant mass required for the process. This technique of refrigerant reduction or minimization also applies to all other components used in the process and should ideally be considered when selecting and positioning those components.

[0025] Preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings.

Brief Description of the Drawings

[0026] [Figure 1] FIG. is a diagram of an apparatus for controlling the temperature of a temperature-controlled space according to a preferred embodiment of the present invention. [Figure 2A] FIG. is a diagram of a simple primary heat pump circuit for cooling a space. [Figure 2B] FIG. is a diagram of a simple primary heat pump circuit for heating a space. [Figure 3] FIG. is a diagram of an apparatus for temperature control involving a heat exchanger coupled to an evaporator or condenser of a primary heat pump circuit. [Figure 4] FIG. is a diagram of an apparatus for temperature control according to a preferred embodiment involving the concept of a heat siphon. [Figure 5] FIG. is a diagram of a preferred embodiment of the present invention according to the concept of a heat siphon for refrigeration. [Figure 6] FIG. is a diagram of a further embodiment of an apparatus for temperature control according to the concept of a heat siphon for heating. [Figure 7] FIG. is a diagram of an implementation of a pump-assisted heat siphon for refrigeration or heating depending on the pump direction. [Figure 8A] FIG. is a schematic diagram of a pump with an inner stator. [Figure 8B] FIG. is a schematic diagram of a pump with an outer stator. [Figure 9] FIG. is a diagram of a preferred embodiment of an apparatus for temperature control according to the concept of a pump-assisted heat siphon for heating. [Figure 10] FIG. is a diagram of the concept of a pump-assisted heat siphon for refrigeration. [Figure 11] FIG. is a diagram of the concept of a pump-assisted heat siphon for heating. [Figure 12]This figure shows an implementation of a temperature control device according to the present invention, which includes a blower in the steam transport section of a piping configuration for refrigeration. [Figure 13] This is a schematic diagram of a heat exchanger that is fluidly separated and thermally coupled. [Figure 14] This is a schematic diagram of a heat exchanger separated from an actual evaporator or condenser, with a (variable) liquid level of a liquid secondary fluid. [Figure 15] This is a schematic diagram of an obliquely positioned temperature control element, through which a passage for a secondary fluid is connected via fins through which air driven by a blower can flow. [Figure 16A] This figure shows an implementation of a device for temperature control according to the present invention for refrigeration, comprising a plate heat exchanger as an integrated element and a vertically positioned air register. [Figure 16B] This figure shows an embodiment of a temperature control apparatus according to the present invention for heating, comprising an integrated element, a temperature control element positioned vertically at the same height, and a pump. [Figure 16C] This figure shows an embodiment of a temperature control apparatus according to the present invention for cooling, comprising an integrated element, a temperature control element vertically positioned at the same height, and a pump. [Figure 17A] This figure shows an implementation of a device for temperature control according to the present invention for refrigeration, comprising a plate heat exchanger as an integrated element and air registers arranged vertically and configured in an alternating manner. [Figure 17B] This is a diagram illustrating an integrated element configured as a plate heat exchanger. [Figure 17C] Figure 17B shows an embodiment of a device for temperature control according to the present invention for refrigeration, comprising a plate heat exchanger as an integrated element and air registers arranged vertically and configured in an alternating manner. [Modes for carrying out the invention]

[0027] Figure 1 shows a device for temperature-controlled space 5, with a space limiter 20 separating the space 5 from the surrounding area. The device includes a primary heat pump circuit 6 with an evaporator 4, a condenser 2, a compressor 1, and an expansion element 3, the primary heat pump circuit having a natural primary working fluid, and the evaporator 4, condenser 2, compressor 1, and expansion element 3 being located outside the space 5. The device according to the present invention further includes a secondary circuit thermally coupled to the evaporator 4 and condenser 2 via a heat exchanger 7, fluidically separated from the evaporator 4 and condenser 2, and comprising a temperature control element 14. The temperature control element 14 is located in the space 5 and connected to the heat exchanger 7 via piping configurations 15a and 15b. The piping configurations have a secondary fluid different from the primary fluid. Furthermore, the piping configurations 15a and 15b are configured to penetrate the space limiter.

[0028] When the secondary circuit is coupled to the evaporator 4 via the heat exchanger 7, the configuration is in a refrigeration (or cooling) mode for the temperature-controlled space. Therefore, the temperature control is refrigeration, and the temperature control element 14 functions as a refrigeration element. In contrast, when the secondary circuit is coupled to the condenser 2 of the primary heat pump circuit via the heat exchanger 7, the device for temperature control is used as a heating device, the temperature-controlled space 5 is heated, and the temperature control element 14 functions as a heating element.

[0029] Therefore, the heat exchanger 7 may include not only an evaporator or liquefaction device, but also a heat exchanger 10 as shown in various drawings. The temperature control element 14 may consist of a heat exchanger 11 as shown in various drawings, or may include one or more additional elements, such as a sensor or blower as shown in Figure 15.

[0030] In a preferred embodiment, the control device 30 is configured to switch the compressor 1 of the primary heat pump circuit in its transport direction, that is, to switch the primary heat pump circuit with respect to the flow direction of the primary working fluid via a control signal 31. If the secondary circuit is the same coupling, this results in the function of the secondary circuit also being changed, that is, the secondary circuit being in a refrigeration mode or a heating mode. When the secondary circuit is normally in refrigeration mode, the heating mode is used to achieve defrosting of the temperature control element 14. However, when the secondary circuit is primarily in heating mode, intermittent refrigeration may be used to maintain a specific set temperature range. The initiative for outputting the control signal 31 or control signal 32 from the control device 30 to pump or blower elements such as element 8 which are as far as possible located in the secondary circuit may arise from an external signal such as a sensor, clock oscillator, or control input 33. However, if the control device is configured to be controlled via a sensor input or clock oscillator, the clock oscillator or sensor input is connected to the control input 33, or if the control input 33 does not exist, the initiative for outputting the control signals 31 / 32 arises from the control device 30.

[0031] Switching the conveying direction of a compressor can be achieved in several ways. In one embodiment, the compressor 1 has conveyor wheels. In this case, the compressor is configured to reverse the rotation direction of the conveyor wheels in response to a control signal 31 in order to reverse the conveying direction.

[0032] In other embodiments, the compressor includes a four-way valve. In this case, to reverse the transport direction, the compressor is configured to, in response to a control signal 31, for example based on the refrigeration mode, to fluidly separate the suction side of the compressor from the evaporator 4 and fluidly connect the suction side of the compressor to the condenser 2, or to fluidly separate the pressure side of the compressor from the condenser 2 and fluidly connect the pressure side of the compressor to the evaporator 4. In this case, the elements that were in the refrigeration mode take over the function of the condenser in the heating mode or defrosting mode.

[0033] Based on the defrosting mode, in order to reverse the conveying direction, the suction side of the compressor is fluidically separated from the condenser (which was the evaporator in defrosting mode) and fluidly connected to evaporator 4 (which was the condenser in defrosting mode), and the pressure side of the compressor is fluidically separated from evaporator 4 (which was the condenser in defrosting mode) and fluidly connected to condenser 2 (which was the evaporator in defrosting mode).

[0034] As shown in Figure 1, the secondary circuit may be provided with a pump 8 to circulate the secondary fluid in the secondary circuit, specifically in the piping configurations 15a and 15b. The secondary fluid may be a secondary liquid when the temperature control element 14 functions as a heat exchanger without phase change. However, when the temperature control element 14 functions as a heat exchanger with phase change, as shown in Figures 4 to 12 and 15, for example, a portion of the piping configuration such as part 15a is a liquid transport section, and another portion such as part 15b is a steam transport section of the piping configuration in the secondary circuit.

[0035] The refrigeration process 6 shown in Figure 3 is carried out according to the same principles as described earlier, when using the components and refrigerants described, the only difference being that the amount of filling is considerably reduced here, the refrigerant cannot reach the inside of the structure or container, and the flammable refrigerant can be used for refrigeration and heat generation with a considerably reduced risk.

[0036] The cold and heat generated in the refrigerant process are subsequently transported indirectly to a refrigeration structure, refrigerated container, or generally the space to be cooled, via a suitable heat exchanger such as a plate heat exchanger 7, using a non-flammable, safe working fluid known as a secondary fluid. Thus, a refrigeration system consists of a primary cycle for refrigeration and a secondary cycle for transporting cold or heat.

[0037] The secondary cycle for distributing the generated cold and heat can be carried out in different ways. It is possible to use brine, which is transported from a suitable pump 8, thereby removing heat from the space to be cooled or introducing heat into the space to be heated, and transporting heat to the refrigerant transport section of the machine, i.e., to the primary cycle, without a phase change in the secondary cycle 9.

[0038] Further variations involve a phase change, also using pumps to transport the fluid through a closed-space heat exchanger, in which case a substance is used to remove or introduce heat from the closed space. In this case, the secondary cycle transports heat to the refrigerant-filled portion of the machine, i.e., the primary cycle. Advantageously, the phase change is a liquid-gas change of phase to ensure the ability to pump the secondary fluid. Phase changes from solid to liquid in the form of a slurry, i.e., a mixture of watery ice and glycol, are generally not ruled out.

[0039] A forced-drive secondary cycle, i.e., one involving the use of a pump, has the disadvantage that the pump will inevitably require energy to overcome the flow resistance of the secondary system. An alternative that does not require the use of a pump is the design of the secondary cycle as a thermal siphon cycle, shown in Figure 4. In this case, the working fluid is introduced in the form of vapor into the upper part 10b of the heat exchanger (evaporator of the primary cycle), and is condensed in the evaporator 10 of the refrigeration section of the machine by a phase change of the secondary cycle (secondary fluid) by the secondary cycle (secondary fluid) present in the lower region 10a as a liquid. Here, using appropriate piping, the liquid working fluid is guided into a closed space to be cooled, in which case it flows into the cooler 11, entering the lower part in liquid form 11a and exiting the upper part in gaseous form 11b, and is then guided again to the heat exchanger 10 of the refrigeration section of the machine 7, where the working fluid is condensed again and flows back to the cooler in the refrigeration space only by gravity, which brings it to a horizontal position. This self-circulating system has the advantage of not requiring a pump, which comes with corresponding energy consumption and the risk of failure, and requires only the minimum number of components used. The secondary cycle needs to be designed so that when the system is operating, the driving pressure difference is created by the difference in geodetic height and / or by the thermal siphon effect. In this case, it is particularly preferable when the cooler is filled to capacity in the case of refrigeration, as this ensures maximum use of the air side of the cooler.

[0040] In applications where heat needs to be transported into a closed space, or where the evaporator is defrosted, the process is reversed by supplying energy to the heat exchanger 10, evaporating the liquid phase 10a of the secondary fluid, which then exits the heat exchanger as the gas phase 10b and is supplied to the heat exchanger 11 in a closed space via appropriate piping. The refrigerant enters the heat exchanger 11 in the closed space as vapor 11b, is condensed, dissipates its heat, exits the heat exchanger in its liquid form 11a, and flows back to the heat exchanger 10 of the machine's refrigeration, where the evaporation process restarts. When transporting heat into a closed space, this process is also carried out solely on the geodetic height difference of the liquid phase in the two heat exchangers, with gravity always providing leveling in both components.

[0041] When designed in this way, each of the methods described also allows for the reversal of the cycle, so that the heat exchanger 11 in Figure 4 in the closed space 5 can perform both defrosting and heating. Depending on the use of the space to be cooled, this process can be performed several times a day, and there are requirements to ensure that defrosting can be performed quickly and reliably. The defrosting process is carried out by the refrigeration part of the machine, which is the primary cycle, and which is no longer operating as a refrigeration system, as shown in Figure 5, and has switched to heat pump mode or heated gas mode. Thus, as described, in heat pump mode the condenser becomes an evaporator and the evaporator becomes a condenser. In heated gas mode the condenser of the refrigerant cycle no longer generates flow through the condenser, and heat is instead dissipated in the evaporator. Thus, the refrigeration unit of the machine can transport heat to the secondary cycle, and the secondary cycle can transport heat to the refrigerated container, so that the cooler 11 in the refrigerated container is also heated, enabling quick and efficient defrosting of the cooler in the container. The same applies to the continuous heating operation of a container when the external temperature falls below the target temperature inside the container.

[0042] Heat exchangers in enclosed spaces or containers, as well as condensers in the refrigeration section of machinery, are typically operated by forced convection generated by a suitable blower on the air side. Similar to the refrigeration section of machinery, the primary cycle should also consider minimizing the amount of working fluid used compared to the secondary cycle, and using coolers with small internal volume and low thermal mass to perform the defrosting process as quickly as possible, and therefore as energy-efficiently as possible. Thus, all heat exchangers with small refrigerant charges and minimal material usage, such as microchannel technology, which specifically address the requirements, can be used for heat exchangers in enclosed spaces 11. Other structures, such as finned heat exchangers, can also be used as alternatives. Both types of heat exchangers are ideally operated by the full-fluid method.

[0043] Due to the elimination of pumps through the use of a thermal siphon solution and the resulting energy advantages, as well as the reduction in system complexity, such a solution has specific advantages compared to the prior art described above. For this reason, it is preferred in the field of compact systems with a spatial distance of preferably up to 10 meters and a cooling and heating capacity of less than 50 kW, and particularly preferably up to 2 meters between the two heat exchangers 10 and 11, and with a small cooling and heating capacity of less than 10 kW.

[0044] In the use under consideration, it is not necessary for the refrigeration machine to also be used to heat a closed space, and if necessary, it is advantageous in any case to geodesically position the heat exchanger 11 below the heat exchanger 10 in the closed space 5 through which the refrigerant flows, as shown in Figure 5. In this case, it is irrelevant how far below the heat exchanger 10 through which the refrigerant flows the heat exchanger 11 in the closed space is positioned. Positioning the heat exchangers relative to each other ensures that the heat exchanger 11 in the closed space is completely filled with secondary fluid 11a at each operating point, while the heat exchanger 10 through which the refrigerant flows has its entire surface area available for condensation of the vapor refrigerant 10a as it is transported from the heat exchanger 11 to the heat exchanger 10 in the enclosed space 5.

[0045] As shown in Figure 6, when only heat needs to be introduced into a closed space, it is advantageous for the heat exchanger 11 located in space 5 to be geodesically above the heat exchanger 10 through which the refrigerant flows. Here, how the difference in geodetic height is actually selected in the application is relevant. In either case, the energy supplied to the heat exchanger 10 evaporates the secondary fluid, and the vapor 11b then flows into the heat exchanger 11 in the closed space 5, where its previously captured heat is ensured to dissipate into space during condensation. After heat dissipation, driven by gravity, the condensed secondary fluid 11a flows back through the heat exchanger 10, and the refrigerant flows through the heat exchanger 10, where it can be evaporated again by the heat supply.

[0046] In the specific installation and operating conditions of the component arrangement shown in Figure 4, failure of the transmitted output into the closed space 5 is possible. For example, this may be due to structural limitations on the possible horizontal arrangement of the heat exchangers 10 and / or 11, the maximum possible installation height, or overall structural limitations such as the fact that the connecting piping between the two heat exchangers 10 and 11 cannot be made large enough to ensure flow with the least possible pressure loss.

[0047] In these cases, the solution shown in Figure 7 is used, where pump 8 is a remedy for the aforementioned shortcomings. In this case, this pump does not need to have a specific transport stroke in the sense of a large transport height, in contrast to conventionally used pumps, but in any case it is essential that it merely assists in the self-correction of the liquid level in heat exchangers 10 and 11, which is given by the thermal siphon effect described. Preferably, the assistance of self-sustaining flow is achieved, for example, or specifically, by reversing the direction of rotation of the rotor 13 by switching the polarity of the stator 120 in both directions of secondary fluid flow, so that the heat exchanger 11, which is located in a closed space, can be cooled and heated for the reasons mentioned above.

[0048] Figure 8 shows two possible conceptual structures for such a pump 8. Figure 8A shows a variation of the pump in which the rotor 13 and stator 120 of the motor that drives the propeller 140 are positioned in the piping and thus in the secondary fluid. In this configuration, the electrical energy that drives the motor can be guided through the pipe that carries the secondary fluid, which can be ensured by a component 150 that simultaneously positions the motor in the pipe.

[0049] Figure 8b shows a variation of the pump in which the stator 120 of the pump motor is positioned in the atmosphere outside the tube through which the secondary fluid flows, while the rotor 13 that drives the propeller 140 via a shaft is positioned in the fluid flow inside the tube. In this structure, it is not necessary to guide electrical energy to generate a magnetic field through the stator 120. This structure also allows for reversing the direction of secondary fluid flow by reversing the direction of rotation of the propeller 140, thereby reversing the polarity in the stator, or by other appropriate measures such as negative polarity.

[0050] Figure 7 shows the resulting height difference of the secondary fluid liquid levels 10a and 11a in the two heat exchangers 10 and 11 when such a pump is used in the arrangement of heat exchangers 10 and 11 shown in Figure 4. It can be seen that heat exchanger 11 in the closed space 5 has a higher liquid level 11a than heat exchanger 10 connected to the refrigerant. This allows the refrigerant to be utilized over the larger surface area of ​​heat exchanger 11 in the closed space 5, while at the same time making available a larger surface area 10b for condensing the secondary fluid in heat exchanger 10, thereby increasing the energy transferred between the two heat exchangers.

[0051] The ability to reverse the pump's transport direction by changing the polarity of the pump's motor results in a usage scenario where the heat exchanger 11 is heated to heat the closed space 5 shown in Figure 9, or to defrost the heat exchanger 11 if it is frozen. In this scenario, the pump draws the liquid secondary fluid 11a from the heat exchanger 11 in the closed space 5 and transports the secondary fluid 11a to the refrigerant-carrying heat exchanger 11, which is why the liquid phase 10a of the secondary fluid in the heat exchanger is higher than the liquid level in the heat exchanger 11. Thus, there is a larger available surface area in the heat exchanger 10 for evaporation of the secondary fluid, while there is a larger surface area 11b in the heat exchanger 11 for condensation, increasing the capacity of the two heat exchangers.

[0052] Finally, Figures 10 and 11 show a case of use that results from a situation where the orientation of the two heat exchangers 10 and 11 at the same geodetic height is not possible due to structural circumstances. Figure 10 shows the case where the refrigerant-carrying heat exchanger 10 is positioned below the heat exchanger 11, which is located in a closed space 5. The pump can raise the liquid level of the secondary fluid 11a to such an extent that the liquid level of the secondary fluid 11a is above the liquid level 10a in the refrigerant-carrying heat exchanger. Thus, the function of heat exchange is maintained despite the possibility of it being impaired by continuous conditions.

[0053] Figure 11 shows the case where the refrigerant transport heat exchanger 10 is geodesically positioned above the heat exchanger 11 in the closed space 5. In this use, the pump is responsible for ensuring that the liquid level 10a of the secondary fluid in the refrigerant transport heat exchanger 10 is above the liquid level 11a of the heat exchanger 11 in the closed space 5.

[0054] As an alternative to the cases shown in Figures 7-11 where a pump is used to assist the flow of a secondary fluid, it is also possible to introduce a conveying device 12 into the piping that exclusively carries the gas phase of the secondary fluid. The configuration of the components that assist the gas phase of the secondary fluid in the natural flow direction of the secondary fluid corresponds in principle to the configuration of the pump 8 shown in Figures 7-11, the difference being that the conveying means 12 can be optimized for the flow of gaseous fluids by having conveying elements with shapes particularly suitable for conveying steam.

[0055] In the case shown in Figure 12, the transport means 12 transports the gas phase 11b from the heat exchanger 11 in the closed space 5 to the heat exchanger 10 in which the secondary fluid in the form of vapor 10b replaces the liquid phase 10a, and thus is responsible for the geodetic height difference between the fluid in the heat exchanger 10 and the fluid in the heat exchanger 11 as shown in Figure 12. The application of the illustrated transport means 12 shown in Figure 12 corresponds to the case shown in Figure 7, but it can also be fully utilized in the cases shown in Figures 9 to 11 by replacing the pump 8 with the transport unit 12 and assisting the circulation of the secondary fluid in the respective illustrated directions.

[0056] Figure 13 shows a schematic arrangement of a heat exchanger for connecting the secondary circuit and the primary heat pump circuit. Specifically, a passage indicated by reference numeral 14a for the primary working fluid arriving from the expansion element 3 and a passage indicated by reference numeral 14b for the primary heat pump fluid leaving the heat exchanger 7, which is connected to the compressor 1, enter the heat exchanger.

[0057] Simultaneously, the first portion 15a of the piping configuration is shown as entering the heat exchanger 7, and the second portion 15b of the piping configuration entering the heat exchanger 7 is also shown. In Figure 13, reference numeral 22 indicates the effective band in which heat transfer occurs from the primary heat pump circuit to the secondary heat pump circuit. Specifically, the two cycles are thermally coupled but fluidly separated so that a highly effective natural refrigerant, such as one made from hydrocarbons, can be used in the primary heat pump circuit, while a secondary fluid that does not pose a flammability risk can be used within the space limiter 20.

[0058] Figure 1 illustrates a configuration where the heat exchanger is located entirely outside the space 5, and the actual piping of the secondary circuit penetrates the space limiter 20 outside the heat exchanger. However, the placement of the heat exchanger 7 may be configured such that the supply or discharge to the effective area 22, already located within the outer limit of the heat exchanger 7, is “embedded” in the space limiter 20, so that it functions as a piping configuration penetrating the space limiter. This is indicated in Figure 13 by dotted lines 20a or 20b located within the outer limit of the heat exchanger 7 and penetrated by piping configurations 15a and 15b within the heat exchanger 7.

[0059] Figure 14 shows a preferred embodiment of a device for temperature control, specifically relating to a special implementation of a heat exchanger. Specifically, the heat exchanger 7, which can be configured as a plate heat exchanger or a brazed plate heat exchanger, is indicated by reference numeral 10 and consists of interconnected elements that combine the function of the heat exchanger with that of the condenser 2 or evaporator 4. In an alternative implementation to that shown in Figure 14, the heat exchanger 10 may be connected before the evaporator or condenser, i.e., it may be implemented as two separate elements. Alternatively, the order of the two elements of the heat exchanger 10 and the evaporator / condenser 4 or 2 may be reversed so that the liquid output from the evaporator is fed into the heat exchanger.

[0060] However, it is preferable to integrate both functions into a single element 10. The primary working fluid flows through the passage 40 shown in Figure 14, is fed in by the expander 41, and is collected by the collector 42 to return to the piping 14b, while the second fluid flows through the connectors 15a and 15b. In the case of a heat exchanger functioning as an evaporator 4, high-temperature steam is fed from the temperature-controlled space through the piping 15b to the heat exchanger 10. This results in the primary working fluid being evaporated after entering the passage 40, the steam being collected by the collector 42, and the steam being drawn in by the compressor 1. The secondary steam supplied by the connector 15b condenses outside the passage 40 for the evaporator and drips into a region with a variable liquid level. The cooled liquid is then carried through the connector 15a to the temperature-controlled element in Figure 15, either by the principle of a siphon or by a pump, to cool the temperature-controlled space.

[0061] Conversely, when the temperature-controlled room is heated, the exchanger acts as a condenser for the primary working fluid. In this case, the warm, compressed primary working fluid flows into passage 40, which is positioned as far away as possible from the cold liquid secondary fluid via element 42, which acts here as an expander. Through this, the primary working fluid condenses inside passage 40 and leaves the heat exchanger 10 as a liquid via element 41, which acts here as a collector. Through this, the secondary fluid evaporates in the heat exchanger 10, and the vapor flows through connection 15b to the temperature-controlled elements 11 and 14 so that it heats the space. Through this, the secondary fluid condenses in the temperature-controlled elements and returns to the heat exchanger as a liquid, either by the principle of a siphon or via a pump, so that it can be evaporated again.

[0062] Figure 14 shows a heat exchanger 10, which includes a variable liquid level, where this level covers a portion of the effective heat exchanger volume, leaving the other portion empty in the embodiment shown in Figure 14. This corresponds to the case in Figures 4, 5, 7, 9, 10, 11, and 12 where the heat exchanger 10 is not completely filled with liquid. Specifically, the heat exchanger is configured such that, apart from the liquid level, the lower region 10a is filled with secondary liquid, while the upper region 10b is a steam space where the secondary fluid of steam is located. At the same time, the first part 15a of the piping configuration is the liquid transport section, while the second part 15b of the piping configuration is the steam transport section. Therefore, it is preferable that the diameter of the second piping configuration be considerably larger than the diameter of the first part so that steam can flow out as efficiently as possible and has sufficient space.

[0063] Furthermore, although the heat exchanger 10 is shown as a positive displacement microchannel heat exchanger in which an expansion or collection element 41 connects the piping 14a to the individual passages of the microchannel heat exchanger, the collection or expansion element 42 collects or distributes the primary fluid, which is liquid (in the case of two separate elements) or vapor (in the case of an integrated element and refrigeration operation) on the external force side, and in separate implementations, simply supplies that liquid or vapor to an evaporator or condenser. Although not shown in Figure 14, fins may be positioned between the micropassages to provide better heat exchange, and the fins are preferably porous so that bubbles can rise in the element 10 or droplets can fall from top to bottom in the element 10.

[0064] In the apparatus according to the embodiment, the evaporator 4 or liquefaction device 2 of the primary heat pump circuit is configured to be integrated with the heat exchanger 10. For example, with respect to Figure 14, the heat exchanger 10 includes a first connection portion such as a collector or expander 41 for the primary working fluid, a second connection portion such as a collector or expander 42 for the primary working fluid, a third connection portion 15a for the secondary fluid, a fourth connection portion 15b for the secondary fluid, and a passage portion 40 extending between the first connection portion 41 for the primary working fluid and the second connection portion 42 for the primary working fluid.

[0065] Furthermore, an interaction region 43 is provided extending between a third connection portion 15a for the secondary fluid and a fourth connection portion 15b for the secondary fluid. The passage portion 40 is positioned in the interaction region 43, and the passage portion 40 is thermally coupled to the interaction region 43 and fluidly separated from the interaction region 43.

[0066] Condensation and evaporation of the primary circuit occur in the passage portion within the interaction space. Furthermore, due to condensation or evaporation in the primary circuit within the interaction region, there is evaporation or condensation of the primary fluid outside the passage portion. Preferably, the interaction region is a volume confined by walls and having a variable liquid level.

[0067] Figure 15 shows a preferred implementation of a temperature control element configured as a secondary fluid-air heat exchanger, which is again configured as a schematic microchannel heat exchanger. A passage for the secondary fluid connected by fins is also shown. Furthermore, a blower 35, positioned in space and blowing air present in space through the temperature control element 14, is shown above the temperature control element. Furthermore, Figure 15 shows an optional oblique arrangement, i.e., an arrangement with an angle α with respect to the horizontal line, as shown in the thermal siphon and pump applications in Figures 3 to 12. This results in the fact that, if the temperature control element is not completely filled with liquid, as illustrated in Figure 9, only the lower left region of the passage in the temperature control element is filled with secondary fluid, while the upper part of the passage is filled with steam secondary fluid. However, as shown in Figure 5, when the temperature control element is completely filled with liquid, the secondary fluid in the passage reaches the connection point of the steam pipe 15b, i.e., the top, so that there is only a small steam space 11b that can be dissipated through the connection point of the second part 15b of the piping configuration so that the steam is fed through the pipe 15b to the heat exchanger 10 in Figure 14. Also, the liquid pipe 15a of the temperature control element in Figure 15 is connected to the connection point 15a at the bottom of the heat exchanger 10.

[0068] Figure 14 shows the functions of a heat exchanger and an evaporator or condenser in an integrated element as a further embodiment, such that the function of heat exchange from the primary working fluid to the secondary fluid occurs in the evaporator, and at the same time, the function of evaporation or condensation occurs in the primary heat pump circuit.

[0069] Figure 16A shows an implementation of a device for temperature control according to the present invention for refrigeration, comprising a plate heat exchanger as an integrated element and a vertically positioned air register. Furthermore, a pump 8 is provided that pumps the cooled secondary fluid to the vertically positioned temperature control element 11 via the air register. The temperature control element does not need to be positioned at an angle or perfectly vertically. The temperature control element can have any arrangement and configuration as long as the secondary fluid can be evaporated by heat in the temperature-controlled space and the evaporated secondary fluid can reach the steam space of the heat exchanger 10 via the connecting portion 15b.

[0070] Figure 16B shows an implementation of the apparatus for temperature control according to the present invention for heating, comprising an integrated element, a temperature control element positioned vertically at the same height, and a pump. Pump 8 is also positioned here to achieve different liquid levels in elements 10 and 11. If pump 8 is absent, or if pump 8 is in standby mode, the two levels will be at the same height due to the siphon principle. Pump 8, which pumps the liquid to the heat exchanger 10 and primary circuit, is operated so that the integrated heat exchanger also functions as a condenser 2. As a result, the secondary fluid in the heat exchanger is evaporated in the warm passage region of the condenser and pushed into the temperature control element. There, the warm vapor of the secondary fluid dissipates its heat into the temperature-controlled space, thereby causing the secondary fluid to condense in the air register and be returned to the exchanger 10 through the pump.

[0071] Figure 16C shows an implementation of the apparatus for temperature control according to the present invention for refrigeration, comprising an integrated element, a temperature control element positioned vertically at a similar height, and a pump. Pump 8 is also positioned here to achieve different liquid levels in elements 10 and 11. If pump 8 is not present, or if pump 8 is in standby mode, the two levels will be at the same height due to the principle of connecting pipes. Pump 8, which pumps the liquid to the heat exchanger 10 and primary circuit, is operated so that the integrated heat exchanger also functions as the evaporator 2. Therefore, the evaporated secondary fluid is condensed in the heat exchanger, in the cold passage region of the evaporator, and pushed through the pump as a cooled liquid to the temperature control element. There, the cold liquid secondary fluid absorbs heat from the temperature-controlled space by the same evaporation in the temperature control element. This vapor returns to element 10 to condense again.

[0072] Figure 17A shows an implementation of the apparatus for temperature control according to the present invention for refrigeration, comprising a plate heat exchanger as an integrated element and air registers arranged vertically and configured in an alternating manner. Pump 8 merely assists fluid circulation, as elements 10 and 11 have the same pressure over the secondary fluid.

[0073] Figure 17B shows an implementation of an integrated element configured as a plate heat exchanger. This element includes four connection sections 41, 42, 15a, and 15b for the primary working fluid and secondary fluid, which extend through a cover plate and are separated by a sealing plate. This passage region 40 and interaction region 43 for the primary fluid are realized by the passage plate. Thus, the primary fluid is fluidically separated from the secondary fluid but thermally coupled to it.

[0074] Figure 17C shows an implementation of the apparatus for temperature control according to the present invention for refrigeration, comprising a plate heat exchanger as an integrated element of Figure 17B, and air registers arranged vertically and configured in an alternating manner. A pump achieves different liquid levels in the plate heat exchanger and air registers. In the case of a standby pump, the liquid levels will be at the same height.

[0075] Next, preferred embodiments of the present invention are summarized as examples.

[0076] 1. A refrigeration system for temperature control, preferably for a closed space, preferably for a moving or stationary application, on a road, rail, water, or land, i.e., for freezing or heating as required, Preferably, the refrigeration part of the machine does not have direct contact with a closed, temperature-controlled space, and / or The secondary circuit prevents the refrigerant from the refrigeration section of the system from reaching the preferred enclosed internal space of the application, and / or The separation between refrigeration and cooling distribution involves a flammable refrigerant or working fluid in the refrigeration section, and / or Preferably, in a thermal distribution section of a system arranged in or in communication with space, a non-combustible fluid is used that undergoes a phase change between a liquid aggregate state and a gas aggregate state, and / or A refrigeration system in which the required electric drive force for distributing cold or heat through a secondary fluid is preferably less than 10 percent of the total required drive force of the machine for refrigeration or heating.

[0077] 2. The machine described in Example 1, wherein the operating pressure of the secondary cycle fluid for cooling distribution exceeds the operating pressure of the fluid in the system part for refrigeration.

[0078] 3. The secondary cycle is configured purely as a solution for the thermal siphon, as described in Example 1 or 2, so that no electric drive is required.

[0079] 4. The machine according to any one of Examples 1 to 3, comprising a pumping means for a secondary fluid that is effective in both flow directions, supporting natural circulation using the principle of a thermal siphon and thus also supporting refrigeration or heating operations.

[0080] 5. The machine according to any one of Examples 1 to 4, wherein the machine is used solely for cooling the internal space, and the heat exchanger in the internal space is geodetically positioned lower than the heat exchanger between the refrigeration section and the refrigeration distribution system section.

[0081] 6. The machine according to any one of Examples 1 to 5, wherein the machine is used solely for heating an internal space, and the heat exchanger in the internal space is geodetically positioned higher than the heat exchanger between the refrigeration section and the refrigeration distribution system section.

[0082] 7. A pumping means capable of pumping a secondary fluid in a liquid or gas phase in both conveying directions in a flow-direction manner, either alone or in combination with a machine described in any of Examples 1 to 6, to assist in cooling and heating operations of an internal space, by changing the rotation direction of a drive motor and a corresponding appropriate shape of a conveying unit.

[0083] 8. A conveying means for assisting the circulation of a secondary fluid introduced into a cycle, either alone or in combination with a machine described in any of Examples 1 to 6, so as to assist circulation in the cycle, exclusively by generating a pressure difference in the gas phase of the secondary fluid.

[0084] 9. The pumping means according to Example 7, wherein the current passage region of the motor is located outside the pipe through which the secondary fluid flows.

[0085] 10. The pumping means according to Example 7, wherein the current passage region of the motor is located inside a pipe through which a secondary fluid flows.

[0086] While several embodiments have been described in the context of a device, it is understood that these embodiments also represent descriptions of the corresponding method, such that elements of a block or structure of the device are also understood as corresponding method steps or features of method steps. Similarly, embodiments described in the context of a method step, or as a method step, also represent descriptions of corresponding blocks, details, or features of the corresponding device. Some or all of the method steps may be performed while using a hardware device such as a microprocessor, a programmable computer, or an electronic circuit. In some embodiments, some or all of the most important method steps may be performed by such a device.

[0087] The embodiments described above are merely illustrative of the principles of the present invention. It will be understood that those skilled in the art will be able to comprehend improvements and modifications of the configurations and details described herein. This is because the present invention is intended to be limited only to the scope of the following claims, and not to the specific details presented herein by the description and discussion of embodiments. [Explanation of Symbols]

[0088] 1. Compressor 2. Heat exchangers, heat transfer devices, condensers, heat sinks, liquefaction devices 3. Expansion elements 4. Second heat exchanger, heat transferr, evaporator 5. Temperature-controlled space 6 Cooling process 7. Heat exchangers, plate heat exchangers 8 elements, pump 10 Heat exchanger, mutual element 10a Lower region, liquid phase, liquid level 10b Upper region, gas phase, surface area 11. Heat exchangers and coolers in enclosed spaces 11a Liquid form, secondary fluid, liquid level 11b Gaseous form, vapor, surface area, gas phase, vapor space 12. Conveying device, conveying means, conveying unit 13 rotor 14 Temperature control elements 14a, 14b Passageways, piping 15 components 15a First part of the piping configuration, liquid transport section, connection section 15b Second part of the piping configuration, steam transport section, connection section 15a Third connection section 15b Fourth connection section 20, 20a, 20b Spatial limiting bodies 22 Effective bandwidth 30 Control device 31, 32 Control signals 33 Control Inputs 35 Blower 40 Passage section 41, 42 Expander, collector, expansion element, collecting element, connection part, interaction region 43 Interaction area 120 Stator 140 propellers

Claims

[Claim 1] A device for controlling the temperature of a temperature-controlled space, wherein the space limiting body (20) separates the temperature-controlled space (5) from the surrounding region (21), A primary heat pump circuit comprising an evaporator (4), a condenser (2), a compressor (1), and an expansion element (3), wherein the primary heat pump circuit contains a natural primary working fluid, and the evaporator (4), the liquefaction device (2), the compressor (1), and the expansion element (3) are located outside the temperature-controlled space. A secondary circuit comprising a temperature control element (11, 14) that is thermally coupled to the evaporator (4) or the condenser (2) via heat exchangers (7, 10), fluidly separated from the evaporator (4) or the condenser (2), and located in the temperature-controlled space (5), and connected to the heat exchangers (7, 10) via a piping configuration (15a, 15b) containing a secondary fluid different from the primary working fluid, wherein the piping configuration (15a, 15b) penetrates the space limiter (20), and In response to control signals (31, 32), the primary heat pump circuit is configured in freezing mode to dissipate energy from the heat exchangers (7, 10), and the device is configured to cool the space (5) in freezing mode via the temperature control elements (11, 14), while a control device (30) controls the primary heat pump circuit in defrost mode so that energy is supplied to the heat exchangers (7, 10). A device equipped with the following features.

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