EP4688472A1

EP4688472A1 - Apparatus for temperature-controlling a space with two pumps, and truck or container

Info

Publication number: EP4688472A1
Application number: EP24716141.7A
Authority: EP
Inventors: Jürgen Süss
Original assignee: Ecooltec Grosskopf GmbH
Current assignee: Ecooltec Grosskopf GmbH
Priority date: 2023-03-29
Filing date: 2024-03-27
Publication date: 2026-02-11
Also published as: WO2024200602A1; DE102023202882A1

Abstract

Apparatus for temperature-controlling, comprising: a gas-liquid heat exchanger (2) with a liquid side (2a) with two ports; a heat exchanger (4) with a primary side (4a) and secondary side (4b), wherein the secondary side (4b) comprises two secondary ports; a heat transport apparatus (10) configured to supply heat to the primary side (4a) of the heat exchanger (4) for heating the gas-liquid heat exchanger (2), or to dissipate heat from the primary side (4a) of the heat exchanger for cooling the gas-liquid heat exchanger (2); a first pump (6) comprising a first suction side and being connected at the suction side to a port of the gas-liquid heat exchanger (2); a second pump (8) comprising a second suction side and being connected at the second suction side to a secondary port of the heat exchanger (4); and a controller (15) for activating the first pump (6) and for controlling the heat transport apparatus to supply heat to the primary side (4a) of the heat exchanger for heating the gas-liquid heat exchanger, or for activating the second pump and for controlling the heat transport apparatus to withdraw heat from the primary side (4a) of the heat exchanger (4) for cooling the gas-liquid heat exchanger (2).

Description

Apparatus for Temperature-Controlling a Space with Two Pumps, and Truck or Container

Description

The present invention concerns temperature-controlling a space to be temperature- controlled and, in particular, refrigeration or heat generation and distribution in mobile or stationary refrigeration applications.

In particular, the present invention relates to methods and apparatuses for refrigeration or heat generation or distribution in mobile refrigeration applications or heating applications and can be used for road-bound motor vehicles or trailers or semi-trailers with a refrigeration structure or a heating structure, a rail-bound or sea-bound refrigerated or heated structure or container, or generally for spaces to be temperature-controlled in ventilation or air- conditioning applications, which are refrigerated or heated by means of a compression refrigeration machine, for example.

Furthermore, this invention can also be used in the field of comfort air conditioning in mobile applications such as buses or rail-bound passenger cars in rail transport. In principle, however, from a purely technical point of view is not necessary to restrict the invention to these fields, as the solutions described here can also be used to advantage in stationary applications.

The compression refrigeration machine is the most common design of refrigeration machines. This design uses the physical effect of evaporation heat when the aggregate state changes from liquid to gaseous or from gaseous to liquid. In a compression refrigeration machine, a refrigerant with suitable thermal dynamic properties is moved in a closed cycle. In this case, it undergoes the various changes of the aggregate state one after the other. The gaseous refrigerant is first compressed by a compressor. In the following heat exchanger (or heat exchanger) (condenser or heat sink of the process), it is condensed (liquefied) while releasing heat. Subsequently, the condensed refrigerant is expanded to the evaporation pressure via an expansion element, or, in the simplest case, a diaphragm, or a capillary tube, so as to reduce the pressure. In this process, it cools down. In the downstream second heat exchanger (or heat exchanger) (evaporator or heat source of the process), the refrigerant evaporates while absorbing heat at a low temperature (evaporation cooling). The heat absorbed in this process represents the coldness used by the refrigeration system. The heat flow absorbed is referred to as refrigerating capacity. The evaporator is therefore advantageously located directly in the refrigeration structure, in the refrigeration container or generally in the closed space to be cooled of the application so as to keep heat exchange losses to a minimum by bringing the refrigerated goods into direct contact with the heat source as much as possible. The cycle can now start again. The process must be kept going from the outside by supplying mechanical work (drive power) via the compressor. The refrigerant absorbs a heat output at a low temperature level and usually dissipates it to the surrounding area by suppling technical work at a higher temperature level. The identical process described is referred to as a heat pump process if the condensation heat emitted by the condenser of the system is to be used instead of the refrigerating capacity or energy supplied to the evaporator. In the present application, this results in the possibility of supplying energy in the form of heat for heating purposes to the described structure, or the closed interior space, of the application with a suitable process control and an arrangement of the components of the system. One of the ways to achieve this is to connect the pressure-side outlet of the compressor to the heat exchanger located in the closed structure in such a way that it heats up during operation of the structure. The remaining components then fulfill their function according to the described application process for refrigeration. The heat supply can also be used to achieve efficient defrosting of the heat exchanger in the closed space, which can be either time-controlled or demand- controlled.

The refrigerant cycle essentially consists of the following four components: compressor, condenser, expansion element, and evaporator. In a single-stage or multi-stage refrigeration system, a distinction is generally made between the high-pressure and the low- pressure side. The high-pressure side extends from the pressure side of the compressor to the inlet of the refrigerant into the expansion element. The low-pressure side comprises the part of the refrigerant cycle from the outlet of the refrigerant out of the expansion element to the compressor inlet. This also applies if the refrigerant cycle is operated as a heat pump, i.e. the heat output provided by the condenser is used instead of the refrigerating capacity of the evaporator. As described, the heat output can be used to heat up the application or to defrost the evaporator.

Regardless of the application, the refrigerant used in the circular process in the cycle should have as little impact on the environment as possible, be cost-effective and particularly energy-efficient. A key measure of the environmentally harmful effect 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 the F-gases (or fluorinates gases) frequently used as refrigerants, the global warming potential can have values of several thousand. This in turn 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.

The most important components of F-gases are carbon, hydrogen, and fluorine. F-gases often decompose very slowly and, once released, sometimes remain in our atmosphere for hundreds or several thousand years. Regardless of their residence time and the level of global warming potential, decomposition products are formed when F-gases decompose. These substances, such as trifluoroacetic acid or hydrogen fluoride, often have long-term negative effects on humans and the environment. For these reasons, international legislation is increasingly restricting or even prohibiting the use of F-gases as refrigerants by means regulations and ordinances. The acceptance of the F-gases as refrigerants by consumers and users of refrigeration technology, but also by society as a whole, is decreasing, and as a result, the refrigeration and heat pump manufacturing industry is increasingly demanding alternatives to the existing refrigeration technology based on the use of F-gases.

Fig. 7a shows an embodiment for heating a space 160 with a heat exchanger 100 and a gas-liquid heat exchanger 120 and a single pump 140. Furthermore, it illustrates an arrangement of the heat exchanger 100 and the gas-liquid heat exchanger 120 with respect to a certain geodetic height indicated with the symbol 180. If the pump is used for heating the space such that the circulation takes place in a clockwise direction in the cycle shown in Fig. 7a, the level of the liquid in the heat exchanger 100 is lifted above a middle line 200. By supplying heat into the heat exchanger 100, liquid in the heat exchanger 100 evaporates and flows into the gas-liquid heat exchanger 120 in order to be condensed there. The condensation process in the space 160 due to the cold air present in this space leads to the air in the space 160 being heated up. Then, the vapor converted by the condensation liquid flows back down out of the gas-liquid heat exchanger and into the heat exchanger 100 as a liquid.

Fig. 7b shows the reverse conveying direction of the pump 140. This pump effect leads to the liquid being pumped out of the heat exchanger 100 and into the gas-liquid heat exchanger 120. This liquid is a cool liquid and leads to the air in the space 160 being cooled down. This occurs because the liquid evaporates in the gas-liquid heat exchanger 120 and this vapor escapes upwards out of the gas-liquid heat exchanger and into the pipeline and is guided into the heat exchanger 100 where it condenses again. This condensation of the vapor in the heat exchanger 100 takes place due to the fact that cold liquid is supplied via the primary side and heat energy is withdrawn from the heat exchanger 100.

Temperature-controlling apparatus for cooling or heating have a problem in that, in the cycle including a gas-liquid heat exchanger and a heat exchanger, depending on the operation mode, the circulation direction of the fluid, which is present in this cycle in its liquid for or in its liquid and gaseous form, has to be reversed. For cooling the gas-liquid heat exchanger, which ultimately temperature-controls the space, there has to be a different flow direction in this cycle than for heating the same. To this end, as illustrated in the non-published International Patent Application PCT/EP2022/076419, a single pump in combination with with a thermosiphon cycle may be used so that one circulation direction is created by a thermosiphon cycle while the other circulation direction is created by the pump.

However, this approach is problematic if, e.g., the implementation of a thermosiphon cycle is not possible, since, under certain operational conditions and in particular due to the type of the application, it cannot be ensured or achieved that corresponding heights of the heat exchanger for temperature-controlling the space on the one hand and the heat exchanger for heating or cooling the heat exchanger on the other hand and in particular the height difference required for the thermosiphon cycle will be maintained under all operational conditions, such as inclinations during operation, e.g., of trucks, trailers for trucks, containers when loading, or other activities, or they are not possible for constructional reasons.

The object of the present invention is to improve a concept for temperature-controlling.

This objection is solved by an apparatus for temperature-controlling according to claim 1 or a truck, trailer, towed vehicle, or container according to claim 14 or a method for manufacturing an apparatus according to claim 17.

According to the invention, for temperature-controlling, a gas-liquid heat exchanger is coupled to a heat exchanger comprising a primary side and a secondary side. In addition, a heat transport apparatus configured to supply heat to the primary side of the heat exchanger for heating the heat exchanger or to dissipate heat from the primary side of the heat exchanger for cooling the heat exchanger is provided. In addition, a first pump comprising a first suction side and being preferably fluidically connected at the first suction side to a port of the heat exchanger is used. In addition, a second pump comprising a second suction side and being preferably fluidically connected at the second suction side to the secondary exit of the heat exchanger is provided.

Thus, not just one single pump with a reversible rotational direction, but two different pumps that both have a single pump direction, i.e. a specified suction side, are used. Thus, by selectively operating or controlling or regulating the two pumps so that the first pump or the second pump is active, temperature-controlling of the space can be achieved for heating or for cooling.

This approach has the advantage of preventing a pump from running dry. It has been shown that when using a single pump with two different conveying directions, i.e. a pump with switchable conveying directions, this pump has typically run dry, since, in particular, the suction-side conveying paths were too long. This situation is exacerbated if a gas-liquid heat exchanger based on a change of phase is used in the secondary circuit. Here, relatively small pressure differences, as achieved by a pump, are enough for the liquid to already evaporate due to the negative pressure of the pump action itself, e.g. at the pump wheel.

According to the invention, this "dry-run" of the pump, which is further promoted by the pressure conditions in this cycle, may be avoided by providing two different pumps.

The two separate pumps are advantageous in that they can be assembled easily, as they only have to convey in one direction. Thus, even though two pumps are now required, these pumps are overall not much more elaborate compared to the case in which a single pump would be used.

In addition, it is preferred that the pumps comprise little or approximately no flow resistance when they are not active, which is also readily possible for pumps that have to convey in one direction. In addition, it is preferred that the pumps are placed as close as possible to the corresponding heat exchanger ports and preferably to the lower heat exchanger ports in which liquid is to be expected, so as to reliably avoid a dry-run of the individual pumps. This ensures that no pump runs dry even if, in the cycle between the gas-liquid heat exchanger and the heat exchanger, there are pressure ratios based on a change of phase taking place for cooling or heating at the gas-liquid heat exchanger. In particular, the main cooling effect in the space is achieved due to the fact that liquid being conveyed by a pump arrives at the gas-liquid heat exchanger, that the liquid in the gas-liquid heat exchanger is evaporated and therefore cooled due to the air or the gas being led to the gas-liquid heat exchanger. The vapor flows into the heat exchanger, where it is condensed again due to the heat energy heat dissipated via the primary side.

However, the gas-liquid heat exchanger is to be heated, liquid is pumped out of the gasliquid heat exchanger into the heat exchanger, where the same evaporates due to the heat energy supplied to the heat exchanger via the primary side. Thus, the vapor enters the gasliquid heat exchanger and is condensed due to the cold air flowing through the gas-liquid heat exchanger, resulting in the cold air being heated. The condensed vapor is then pumped as a liquid from the gas-liquid heat exchanger into the heat exchanger, where it is evaporated again by the heat supply.

As a heat exchanger with a primary side and a secondary side, a plate heat exchanger is preferably used, which is a liquid-liquid heat exchanger and is perfectly suitable for a change of phase at least on the secondary side.

As a gas-liquid heat exchanger, a typical liquid-air heat exchanger may also be used, which is suitable for a change of phase of the liquid and which comprises any type of air register. Depending on the implementation, however, a gas-liquid heat exchanger having a vertical extension and therefore an upper area in which vapor is typically contained and a lower area in which liquid is typically contained may be used.

However, alternatively, as described, a heat exchanger that operates without a change of phase and has a liquid flow through its entire area, e.g. because it is arranged at a ceiling or has a low vertical extension only, may be used as well, with said liquid either being supplied by the heat exchanger coupled to the heat transport apparatus as a warm liquid or as a cold liquid.

Preferred embodiments of the present invention are subsequently described in more detail on the basis of the accompanying drawings, in which:

Fig. 1 shows a schematic embodiment of the present invention with two pumps and a controller; Fig. 2a shows a configuration of the heat transport apparatus for cooling the heat exchanger;

Fig. 2b shows a configuration of the heat transport apparatus for heating the heat exchanger;

Fig. 3a shows a section through a preferably usable pump with one conveying direction;

Fig. 3b shows a cross-sectional view as well an isometric view of the pump;

Fig. 3c shows an isometric view of the sectional view of Fig. 3a;

Fig. 4 shows a further embodiment of the heat transport apparatus with switchable compressor input/output ports;

Fig. 5 shows an exemplary arrangement of the gas-liquid heat exchanger in a truck;

Fig. 6 shows a schematic illustration of the outer housing for receiving the heat transport apparatus and the heat exchanger outside of the cargo space; and

Fig. 7a shows a schematic illustration of the use of one pump with two conveying directions for heating or cooling.

Fig. 1 shows an apparatus for temperature-controlling, particularly comprising a gas-liquid heat exchanger 2 with a liquid side and two ports 2a. Furthermore, a heat exchanger 4 having a primary side 4a and a secondary side 4b is provided, wherein the secondary side 4b comprises two secondary ports, i.e. a secondary port directed towards the gas-liquid heat exchanger 2a and a further secondary port located in Fig. 1 at the bottom of the heat exchanger 4 and directed towards a second pump 8. Furthermore, a heat transport apparatus 10 is provided and configured to supply heat energy to the primary side 4a of the heat exchanger 4 for heating the gas-liquid heat exchanger 2 or configured to dissipate heat from the primary side 4a of the heat exchanger 4 for cooling the gas-liquid heat exchanger.

In addition, a first pump 6 comprising a first suction side and being preferably fluidically connected at its suction side to a port 2a of the gas-liquid heat exchanger is provided. Furthermore, a second pump 8 comprising a second suction side and being preferably fluidically connected at the second suction side to a secondary port of the heat exchanger 4 is provided. In addition, a controller 15 is provided to activate the first pump 6 and to drive the heat transport apparatus 10 so as to supply heat to the primary side 4a of the heat exchanger 4 for heating the gas-liquid heat exchanger 2 or to activate the second pump 8 and to drive the heat transport apparatus 10 so that heat is withdrawn from the primary side 4a of the heat exchanger 4 for cooling the gas-liquid heat exchanger. In addition, the controller includes control lines 15a for the heat transport apparatus 10 and end lines 15b and 15c for the two pumps 6, 8. Preferably, as shown in Fig. 1 , the first suction side of the first pump 6 is connected to the port 2a of the gas-liquid heat exchanger that is the lower port of the two ports 2a of the liquid side of the gas-liquid heat exchanger 2 in the operation direction of the apparatus. In addition or alternatively, the second suction side of the second pump is connected to the port of the heat exchanger 4 that is the lower port of the two ports of the heat exchanger 4 in the operation direction of the apparatus. This ensures that the suction sides of the two pumps are always supplied with liquid due to gravity so that there is no dry run of a pump.

Preferably, with respect to their suction sides, the first pump 6 and the second pump 8 are arranged as closely as possible to the gas-liquid heat exchanger 2 and the heat exchanger 4, respectively. This closest possible connection may be a direct connection of the suction side of the pump to the corresponding port of the gas-liquid heat exchanger. However, if such direct connections are not possible, e.g. for constructive reasons, a line is provided between the corresponding suction side and the corresponding port of the element 2 and 4, respectively, that is preferably smaller than 1 m and particularly preferably smaller than 50 cm and most preferably smaller than 30 cm.

The gas-liquid heat exchanger 2 is preferably arranged in a space so that the apparatus for temperature-controlling is configured to temperature-control the space. In this case, the gas-liquid heat exchanger 2 and the first pump 6 are arranged in this space. Furthermore, the heat exchanger 4 and the second pump 8 are arranged outside of this space. If this space is a cargo space of a truck, for example, as is shown in Fig. 6 from the outside and as shown in Fig. 5 from the inside, the gas-liquid heat exchanger 2, also shown in Fig. 5, as well as the first pump 6 are arranged within the space, while the second pump 8, the heat exchanger 4, and the heat transport apparatus 10 are arranged in a housing 41 outside of the space. Preferably, the housing 41 is arranged as a refrigerating unit in a recess 40 in a structure at the front end of the structure, i.e. typically flush with the other dimensions of the structure, so that the housing 41 fits well both aerodynamically and aesthetically into the outer appearance of the truck schematically shown in Fig. 6.

Thus, the gas-liquid heat exchanger 2 and the first pump 6 may both be arranged at a ceiling of a cargo space of the truck, as shown in Fig. 5, while the heat exchanger 4 and the second pump are arranged on the outside of the structure of the truck, i.e. preferably in close proximity to the “interior unit”, i.e. with respect to Figs. 5 and 6, directly below the housing 41 but in the cargo space.

This strict separation into elements within and outside of the cargo space ensures that refrigerants ideally adapted to the corresponding applications may be used for both cycles, i.e. the cycle of the heat transport apparatus 41 and the cycle of the gas-liquid heat exchanger. In particular, the refrigerant entering into the interior of the truck structure should be preferably non-toxic and non-flammable, while the refrigerant arranged outside at the truck and essentially circulating in the housing 41 may be adapted ideally with respect to the efficiency of the refrigerant cycle, so that certain requirements with respect to nontoxicity or flammability, as are essential in the interior of the structure, are not required.

For example, the gas-liquid heat exchanger 2 includes a heat exchanger in a cuboid shape with an air register, as shown in Fig. 2, having guided therethrough one or several liquid- guided lines, wherein a first port of the two ports is preferably fl uidically connected to a port of the heat exchanger, and a second port is preferably fluidically connected to the pump side of the first pump 6. Such an arrangement is schematically shown in Fig 5, additionally showing a blower 23 that typically draws in air from the bottom side and blows the same upwards through the front of the air register from the end wall of the truck structure towards the back into the cargo space.

Figs. 2a and 2b show different implementations or configurations of the heat transport apparatus 10, as may be adjusted by means of the controller 15 via the control port 15a. In particular, the heat transport apparatus preferably includes a refrigerating cycle with a compressor 7a, an expansion element 7b and its own condenser 30 or its own evaporator 31 . In the use case of the configuration of the heat transport apparatus 10 shown in Fig. 2, the heat exchanger 4 operates as the evaporator of the refrigerating cycle in the heat transport apparatus 10 so that the separate condenser 30 is connected between the compressor 7a and the expansion element 7b. However, if the heat transport apparatus 10 is switched into the heating mode, the heat exchanger 4 serves as a condenser of the refrigerating circuit, and a separate evaporator 31 is arranged between the expansion element 7b and the compressor 7. While cold is supplied to the heat exchanger via the primary side 4a of the heat exchanger 4 in the embodiment shown in Fig. 2a, i.e. a condensed refrigerant, in the embodiment shown in Fig. 2b, heat, i.e. hot vapor, is supplied to the primary side 4a of the heat transmitter 4 after the compression by means of the compressor 7a.

Fig. 4 shows a further embodiment, wherein, to reconfigure the heat transport apparatus 10, two switches 35a, 35b that switch, in a first state, the heat transmitter 4 to be a condenser of the refrigerating cycle of the heat transport apparatus 10, i.e. same as in Fig. 2b, so as to heat the heat exchanger 2, are provided. In the alternative configuration, the switches 35a, 35b are switched so that the heat exchanger is switched to be an evaporator, i.e. the same as on the low-pressure side of the refrigerating cycle, as indicated by Fig. 4. In the first configuration, the connections between the two ports in the control elements 35a, 35b are simply continuous, while they switch the corresponding circumventions in the second configuration.

Accordingly, the line 15a is divided into two single lines for the two control apparatuses 35a, 35b. Furthermore, the controller 15 will drive the two pumps 6 and 8 accordingly via the lines 15b, 15c.

Another alternative implementation may be configured such that the controller 15 drives only the compressor 7 so that it reverses its rotational direction and conveys from bottom to top, so to speak. In this case, the two switches 35a, 35b would not be present, the ports of the (here non-existing) switches would be directly connected and the controller would only reverse the rotational direction of the compressor 7a for switching from the heating mode to the refrigeration mode and vice versa. However, for reasons of the implementation, it is preferred that the compressor 7a always runs in the same conveying direction and that the switch is carried out via fluid switches, such as the fluid switches 35a, 35b.

Depending on the implementation, as is the case in Figs. 2a, 2b, and Fig. 4, the heat exchanger 4 could be configured so as to be integrated with the evaporator or the condenser of the refrigerating cycle of the heat transport apparatus. Alternatively, however, the heat exchanger 4 could also be connected into the process, however, wherein the refrigerating cycle itself comprises a separate evaporator and a separate condenser. In such a case, for heating the heat exchanger 4, e.g. the condensed warm liquid would be fed into the heat exchanger from the separate condenser. Alternatively, the liquid in the evaporator that is cooled due to the evaporation could be fed into the heat exchanger 4 for cooling purposes, or the primary side 4a of the heat exchanger 4 could also be connected to a condenser or evaporator of the refrigerating cycle of the heat transport apparatus via a further heat exchanger. Preferably, the heat exchanger 4 is configured as a plate heat exchanger.

The first pump 6 and the second pump 8 are preferably configured such that they move liquid from the respective suction side to an output side in an active state and such that liquid will flow through them in a non-activated state and they comprise as low a flow resistance as possible.

Alternatively, a pump that cannot experience flow-through in a non-activated state, but that has in an non-activated state a bypass or a circumvention line through which the liquid can flow past the non-activate pump, so to speak, may be used. The bypass line may be actively opened or closed via switches, or may be passively controlled via check valves so that the bypass line at the pump is blocked if a pump is active or such that the bypass line at the pump is open when the pump is inactive. Depending on the implementation, a bypass line may be provided at both pumps, or at just one of the two pumps. Furthermore, it is preferred that only one pump is always active and the other pump is always inactive so that one pump always experiences flow-through or its bypass line is opened, while the other pump is active or the bypass line of the other pump is blocked.

Such a pump is exemplary shown in Figs. 3a to 3c. For example, such a pump includes a pump chamber, a suction-side port 42 leading into the pump chamber, and a pump-side port 44 also leading into the pump chamber. Furthermore, a motor 46 driving a pump wheel 48 may be provided, wherein said pump wheel may be driven by the motor 46 in a rotational direction and pushes liquid out of the pump chamber 40 into the pump-side port 44 in a driven state. In the sectional view in Fig. 3b, this pump-side port 44 is shown to be eccentric with respect to a rotational axis of the pump wheel 48. Both the suction port and the pressure-side port include corresponding port pipes also shown at 42, 44 in Fig. 3b and Fig. 3c. Furthermore, the pump pipes of preferably both pumps are arranged in an angle of between 60° and 120° (preferably essentially 90°) with respect to the suction pipes. Furthermore, as shown in Figs. 3a to Fig. 3c, has overall a cylindrical shape, wherein the suction pipe shown at 42 extends in or in parallel to an axis of the cylindrical shape of the pump and wherein the pump pipe shown at 44 in Fig. 3c extends essentially perpendicular to the respective suction pipe.

Furthermore, the pump chamber 40, as shown in Fig. 3c, includes a longitudinal entry arranged essentially in the center of a wall of the pump chamber. Furthermore, a cross exit for the pump-side port arranged laterally with respect to the pump chamber and eccentrically with respect to the pump chamber 40, as shown at 44 in Fig. 3b, is formed. Furthermore, the liquid side of the gas-liquid heat exchanger, as shown in Fig. 2, includes areas with a vertical extension in the operational direction that extend from a lower end to an upper end. In addition, the heat exchanger 4 also includes corresponding areas with a vertical extension in the operation direction that extend from a lower end to an upper end. Furthermore, the gas-liquid heat exchanger 2 and the heat exchanger 4 are arranged with respect to each other such that a lower end of the gas-liquid heat exchanger or of the heat exchanger are each aligned with an upper end of the respectively other element with respect to a height in an operation direction, or such that the corresponding upper end is higher than a lower end of the respectively other element, and such that the same is at most as high as the corresponding upper end so that, as exemplary shown on the basis of Fig. 7a and 7b, there is a certain overlap of the vertical extension of the gas-liquid heat exchanger and the heat exchanger 4 so that the pump capacities may be kept as low as possible. However, this arrangement is not required for certain embodiments that may not necessarily achieve this arrangement, since the pump capacities of the pumps at the bottom of the heat exchanger and at the bottom of the gas-liquid heat exchanger can be increased correspondingly.

Preferably, the apparatus for temperature-controlling is housed in a truck, as previously described on the basis of Figs. 5 and 6.

Preferably, the refrigerating cycle and the primary heat pump cycle arranged outside of the space to be temperature-controlled, i.e. in the surrounding area of the space to be temperature-controlled, are configured to use a natural primary working fluid having properties that are unfavorable for a closed space, such as flammability. However, a different secondary fluid that is typically not harmful for an organism or has little risk since it is not flammable, for example, is used in a secondary circuit. Thus, primary working fluids and secondary fluids comprising suitable properties for a compression cycle or primary heat pump cycle on the one hand and for temperature-controlling a closed space to be temperature-controlled on the other hand may be combined.

In particular, the use of flammable primary working fluids as an example of a natural refrigerant enables high environmental compatibility and energy-efficient properties in a compression refrigeration/heat cycle. On the other hand, such refrigerants may be used in closed spaces usually only with significant additional effort due to their flammability. For example, such refrigerants are hydrocarbons (HC) such as propane (R290) or propene (R1270). Other fluorinated gas-free primary working fluids include NH₃ or NH₃/DME (R723) that are only slightly flammable but are toxic in closed spaces for the human organism and are therefore not desired. This group of substances for refrigeration also includes fluorinated hydrocarbons that are flammable due to their molecular composition.

On the other hand, non-flammable and therefore risk-free ref rig erat ion/h eat carrier media that ideally undergo a change of phase in the transport of cold and heat can be used in the secondary circuit, which is not used for refrigeration or heat generation but only for cold/heat distribution. A secondary fluid that changes its aggregate state in the transport of heat is preferably used is. In this case, heat is absorbed, or is dissipated, at a constant temperature, and the thermosiphon principle or natural circulation principle is driven in both directions, i.e. when refrigerating and when heating, due to the difference in density between vapor and liquid.

Even though some aspects have been described within the context of a device, it is understood that said aspects also represent a description of the corresponding method, so that a block or a structural component of a device is also to be understood as a corresponding method step or as a feature of a method step. By analogy therewith, aspects that have been described within the context of or as a method step also represent a description of a corresponding block or detail or feature of a corresponding device. Some or all of the method steps may be performed by a hardware device (or while using a hardware device), such as a microprocessor, a programmable computer or an electronic circuit. In some embodiments, some or several of the most important method steps m ay be performed by such a device.

The above-described embodiments merely represent an illustration of the principles of the present invention. It is understood that other persons skilled in the art will appreciate modifications and variations of the arrangements and details described herein. This is why it is intended that the invention be limited only by the scope of the following claims rather than by the specific details that have been presented herein by means of the description and the discussion of the embodiments.

Claims

1 . Apparatus for temperature-controlling, comprising: a gas-liquid heat exchanger (2) with a liquid side (2a) with two ports; a heat exchanger (4) with a primary side (4a) and secondary side (4b), wherein the secondary side (4b) comprises two secondary ports; a heat transport apparatus (10) configured to supply heat to the primary side (4a) of the heat exchanger (4) for heating the gas-liquid heat exchanger (2), or to dissipate heat from the primary side (4a) of the heat exchanger for cooling the gas-liquid heat exchanger (2); a first pump (6) comprising a first suction side and being fluidically connected at the suction side to a port of the gas-liquid heat exchanger (2); a second pump (8) comprising a second suction side and being fluidically connected at the second suction side to a secondary port of the heat exchanger (4); and a controller (15) for activating the first pump (6) and for controlling the heat transport apparatus to supply heat to the primary side (4a) of the heat exchanger for heating the gas-liquid heat exchanger, or for activating the second pump and for controlling the heat transport apparatus to withdraw heat from the primary side (4a) of the heat exchanger (4) for cooling the gas-liquid heat exchanger (2).

2. Apparatus according to claim 1 , wherein the first suction side of the first pump (6) is fluidically connected to the port of the gas-liquid heat exchanger that is the lower port of the two ports of the liquid side of the gas-liquid heat exchanger in the operation direction of the apparatus, or wherein the second suction side of the second pump (8) is fluidically connected to the port of the heat exchanger (4) that is the lower port of the two ports of the secondary side (4b) of the heat exchanger (4) in the operation direction of the apparatus.

3. Apparatus according to claim 1 or claim 2, wherein the first suction side or the second suction side are directly fluidically connected to the respective port, or are fluidically connected via a line that is shorter than 50 cm.

4. Apparatus according to any of the preceding claims, wherein the gas-liquid heat exchanger (2) and the first pump (6) are arranged in a space, wherein the heat exchanger (4) and the second pump (8) are arranged outside of the space, and wherein the apparatus is configured to temperature-control the space.

5. Apparatus according to any of the preceding claims, wherein the gas-liquid heat exchanger (2) and the first pump (6) are arranged at a ceiling of a cargo space of truck, and wherein the heat exchanger (4) and the second pump (8) are mounted outside of the cargo space at a structure of the truck in which the cargo space is arranged.

6. Apparatus according to any of the preceding claims, wherein the gas-liquid heat exchanger (2) comprises a heat exchanger in a cuboid shape with an air register through which the one or the several liquid-carrying lines are guided, wherein a first port of the two ports is fluidically connected to a port of the secondary side (4b) of the heat exchanger (4), and a second port of the gas-liquid heat exchanger (2) is fluidically connected to the pump side of the first pump (6).

7. Apparatus according to any of the preceding claims, wherein the heat transport apparatus (10) comprises an evaporator (31 ), a condenser (32), a com pressor (7a), and an expansion valve (7b), wherein the evaporator or the condenser are formed through the primary side (4a) of the heat exchanger (4), or wherein the evaporator or the condenser are configured so as to be separate from the heat exchanger (4) and are fluidically connected to the primary side (4a) of the heat exchanger via a line or a further heat exchanger.

8. Apparatus according to claim 7, wherein the controller (15) is configured to activate the first pump (6) for heating the gas-liquid heat exchanger (2) and to operate the primary side (4a) of the heat exchanger as the condenser or to connect the same to the condenser, or to activate second pump (8) for cooling the gas-liquid heat exchanger (2) and to operate the primary side (4a) of the heat exchanger as the evaporator or to connect the same to the evaporator.

9. Apparatus according to any of the preceding claims, wherein the first pump (6) and the second pump (8) are configured to move liquid from the respective suction side to the respective pump side in an activated state and to have liquid flow through them in a non-activated state, or wherein at least one pump of the first pump (6) and the second pump (8) comprises a controllable bypass line, wherein the controller bypass line is blocked when the pump is active or is open when the pump is inactive.

10. Apparatus according to any of the preceding claims, wherein the first pump (6) or the second pump (8) comprises: a pump chamber (40); a suction-side port (42) leading into the pump chamber (40); a pump-side port (44) leading into the pump chamber (40); a motor (46); and a pump wheel (48) that can be driven by the motor (46) in a rotational direction and that pushes liquid out of the pump chamber (40) to the pump-side port (44) in a driven state.

1 1. Apparatus according to claim 10, wherein the suction-side port (42) comprises a suction pipe, wherein the pump-side port (44) comprises a pump pipe, wherein the pump pipe extends in an angle of between 60° and 120° with respect to the suction pipe, and wherein the pump comprises a cylindrical shape, wherein the suction pipe extends in or in parallel to an axis of the cylindrical shape, and the pump pipe extends essentially perpendicular to the suction pipe.

12. Apparatus according to claim 10 or 11 , wherein the pump chamber (40) comprises a longitudinal entry and a cross exit, wherein the longitudinal entry is formed essentially in the center of wall of a pump chamber, and wherein the cross exit (44) is arranged laterally with respect to the pump chamber and eccentrically with respect to the pump chamber (40).

13. Apparatus according to any of claims 1 to 12, wherein the liquid side of the gasliquid heat exchanger comprises an area having a vertical extension in an operation direction, with said area extending from a lower end to an upper end, wherein the heat exchanger (4) comprises an area having a vertical extension in an operation direction, with said area extending from a lower end to an upper end, wherein the gas-liquid heat exchanger (2) and the heat exchanger (4) are arranged with respect to each other such that a lower end of the gas-liquid heat exchanger or of the heat exchanger and an upper end of the respectively other element of the gas-liquid heat exchanger and the heat exchanger are aligned with respect to a height in the operation direction, or such that an upper end of the gas-liquid heat exchanger or of the heat exchanger is arranged higher with respect to a height in the operation direction than a lower end of the respectively other element, but at most as high as the upper end of the respectively other element.

14. Truck, trailer, towed vehicle, or container, comprising: an apparatus according to any of claims 1 -13, wherein the gas-liquid heat exchanger (2) is arranged in a cargo space of the truck, trailer, towed vehicle, or container, and wherein the heat exchanger (4) and the heat transport apparatus (10) are arranged outside of the cargo space of the truck, trailer, towed vehicle, or container.

15. Truck, trailer, towed vehicle, or container according to claim 14, wherein the cargo space is arranged in a structure, wherein the structure comprises at a front end arranged in proximity to the driver’s cab of the truck a recess (40) in which the heat exchanger (4) and the heat transport apparatus (10) are arranged in a housing (41 ), wherein the housing (41 ) is configured and arranged so that housing walls and adjacent walls of the structure are essentially flush with respect to each other.

16. Truck, trailer, towed vehicle, or container according to claim 14 or 15, wherein the gas-liquid heat exchanger is arranged at a ceiling of the cargo space, wherein a collection tray (24) for defrosting water is arranged below the gas-liquid heat exchanger, and wherein the first pump is arranged above the collection tray (24).

17. Method for manufacturing an apparatus for temperature-controlling comprising a gas-liquid heat exchanger (2) with a liquid side (2a) with two ports; a heat exchanger (4) with a primary side (4a) and secondary side (4b), wherein the secondary side (4b) comprises two secondary ports; and a heat transport apparatus (10) configured to supply heat to the primary side (4a) of the heat exchanger (4) for heating the gasliquid heat exchanger (2), or to dissipate heat from the primary side (4a) of the heat exchanger for cooling the gas-liquid heat exchanger (2), the method comprising: connecting a first suction side of a first pump (6) to a port of the gas-liquid heat exchanger (2); connecting a second suction side of a second pump (8) to a secondary port of the heat exchanger (4); and mounting a controller (15) for activating the first pump (6) and for controlling the heat transport apparatus to supply heat to the primary side (4a) of the heat exchanger for heating the gas-liquid heat exchanger, or for activating the second pump and for controlling the heat transport apparatus to withdraw heat from the primary side (4a) of the heat exchanger (4) for cooling the gas-liquid heat exchanger (2).