Cooling compartment with an evaporator and an auxiliary fan

Abstract

A cold storage room with the following features: an evaporator arranged on a wall (970) of the cold storage room (900) and having a fan (700) at one end of a housing (600) of the evaporator, the fan (700) being designed to convey cooled air in a ventilation direction (950) into the cold storage room; and an auxiliary fan (750) arranged in the cold storage room (900) to draw in at least a part (951, 952) of the cooled air conveyed by the fan (700) and convey it further into the cold storage room.

Description

[0001] The present invention relates to the temperature control of a room to be temperature controlled and in particular to cold generation or heat generation and distribution in mobile or stationary refrigeration applications.

[0002] In particular, the present invention relates to methods and devices for the generation and distribution of cold or heat in mobile cold applications or heat applications and can be used in road-bound motor vehicles or trailers or semi-trailers with a refrigerated body or a heated body, a rail- or sea-bound refrigerated or heated body or a container, or generally in rooms to be tempered in air conditioning or air-conditioning applications, which are cooled or heated, for example, by means of a compression refrigeration machine.

[0003] 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. However, from a purely technical perspective, a restriction to these areas is not necessary, as the solutions described here can also be used advantageously in stationary applications.

[0004] The compression refrigeration machine is the most common type of refrigeration machine. This design utilizes the physical effect of the latent heat of vaporization during the change of state from liquid to gaseous, or from gaseous to liquid. In a compression refrigeration machine, a refrigerant with suitable thermodynamic properties is moved in a closed circuit. In the process, it undergoes various changes of state sequentially and repeatedly. The gaseous refrigerant is first compressed by a compressor. In the subsequent heat exchanger (condenser or heat sink of the process), it is condensed (liquefied) while releasing heat. The liquefied refrigerant is then expanded to the evaporation pressure via an expansion device, e.g., an expansion valve or, in the simplest case, an orifice plate or a capillary tube, to reduce the pressure. It cools down in the process.In the downstream second heat exchanger (evaporator, or heat source of the process), the refrigerant evaporates at a low temperature while absorbing heat (evaporative cooling). The heat absorbed in this process represents the utilized cooling power of the refrigeration system. The absorbed heat flow is referred to as the cooling capacity. The evaporator is therefore advantageously located directly in the refrigerated body, in the refrigerated container, or generally in the enclosed space to be cooled in order to keep heat transfer losses to a minimum by bringing the refrigerated goods into direct contact with the heat source as much as possible. The cycle can now begin again. The process must be kept going from the outside by supplying mechanical work (drive power) via the compressor. The refrigerant absorbs heat at a low temperature level and releases it, usually to the environment, at a higher temperature level, by supplying technical work.The identical process described is referred to as a heat pump process if, instead of the cooling capacity or energy supplied to the evaporator, the condensation heat released by the system's condenser is to be used. In the present application, this results in the possibility of supplying energy in the form of heat to the described structure or the closed interior of the application for heating purposes, with suitable process control and arrangement of the system components. One way to achieve this is to connect the pressure-side outlet of the compressor to the heat exchanger, which is located in the closed structure, in such a way that the heat exchanger heats up during system operation. The other components then fulfill their function according to the described application process for generating cold.The heat supply also allows for efficient defrosting or defrosting of the heat exchanger in a closed room, which can be either time-controlled or demand-controlled.

[0005] The refrigerant circuit essentially consists of four components: compressor, condenser, expansion device, and evaporator. In a single-stage refrigeration system, a distinction is generally made between high-pressure and low-pressure sides. The high-pressure side extends from the pressure side of the compressor to the refrigerant inlet into the expansion device. The low-pressure side comprises the part of the refrigerant circuit from the refrigerant outlet from the expansion device to the compressor inlet. This also applies if the refrigerant circuit is operated as a heat pump, i.e., the heating output provided by the condenser is used rather than the cooling capacity of the evaporator. This heating output can be used, as described, to heat up the application or to defrost the evaporator.

[0006] Regardless of the application, the refrigerant used 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 damaging effect of a refrigerant is its greenhouse potential, also known as GWP (Global Warming Potential). This value is given for refrigerants in relation to the GWP value of CO2 (carbon dioxide). CO2 has a GWP value of 1 by definition. For the F-gases frequently used as refrigerants, the greenhouse potential can reach 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 have the equivalent of the greenhouse effect of several tons of CO2.

[0007] The main components of F-gases are carbon, hydrogen, and fluorine. F-gases often decompose very slowly and, once released, can remain in our atmosphere for hundreds or even thousands of years. Regardless of their residence time and their global warming potential, decomposition products are produced during the decomposition of F-gases. These substances, such as trifluoroacetic acid or hydrogen fluoride, often have long-term negative impacts on humans and the environment. For these reasons, the use of F-gases as refrigerants is increasingly being restricted or even prohibited by international legislation through regulations and ordinances.The acceptance of F-gases as refrigerants by consumers, users of refrigeration technology, and also by society as a whole is decreasing, and as a result, the manufacturing industry of refrigeration systems and heat pumps is increasingly demanding alternatives to the current refrigeration technology based on the use of F-gases.

[0008] International patent application PCT / EP2022 / 076419 discloses a device for controlling the temperature of a room to be heated. An evaporator is arranged in the room to be heated. This evaporator is operated during a phase change of the secondary fluid, resulting in a natural circulation process or thermosiphon process. Working fluid, such as CO2, evaporates in the evaporator. This evaporated working fluid, i.e., the CO2 vapor, rises in the evaporator and exits the evaporator via a vapor line. The vapor flows into a heat exchanger of a primary heat pump circuit, where it is reliquefied due to the corresponding control of the primary heat pump circuit, namely by heat being removed from the heat exchanger through the primary heat pump circuit.The liquefied vapor, i.e., the liquid CO2, then flows back through a liquid line and a liquid connection into the evaporator in the cold storage room, thus closing the cycle. From the cold storage room's perspective, comparatively warm air is drawn into the evaporator from below, for example, by a fan. The air then moves from bottom to top and is cooled as the secondary liquid, e.g., CO2, evaporates in the evaporator. The cold air is then blown out of the evaporator at the top and serves to cool the cold storage room, which could be a semitrailer or the loading area of ​​a truck, for example.

[0009] To defrost the evaporator, which will eventually ice over, the primary heat pump circuit is reversed. This is achieved either by reversing the flow direction or rotation direction in the case of a compressor such as a turbo compressor, or by switching the components in the primary heat pump circuit that are connected to the compressor accordingly, so that the heat exchanger, which connects the primary heat pump circuit and the secondary circuit, i.e. the evaporator, no longer functions as a heat source but as a heat sink. As a result, the primary heat pump circuit heats up the heat exchanger. This causes secondary fluid in the heat exchanger to evaporate and flow into the evaporator via the vapor line. This warms the evaporator, and the ice that has formed on the outside of the evaporator thaws. This thawing process, in turn, liquefies the vapor in the evaporator, causing it to flow downwards through the evaporator.Typically, when "normal" cooling operation is achieved by a thermosiphon circuit, a pump is activated to reverse the cycle during defrosting, pumping the liquefied secondary fluid from the evaporator back into the heat exchanger. However, alternative measures such as double-siphon applications also exist to achieve this cycle reversal, as described, for example, in German patent application 102023202885.9.

[0010] In order to achieve efficient cooling in the cold room, it is necessary that the evaporator works efficiently and at the same time can be manufactured inexpensively.

[0011] The object of the present invention is to create an improved cooling concept.

[0012] This object is achieved by a cooling chamber according to patent claim 1.

[0013] An evaporator according to a first aspect of the invention comprises a first header and a second header as well as a plurality of connectors between the first and second headers, wherein the first header and the second header as well as the connectors are designed such that a working fluid can flow through them. Furthermore, a fin stack of spaced-apart fins is provided, which are formed in thermal connection with the connectors and are arranged in a stacking direction, and which are designed such that gas or air can flow in a fin direction between adjacent fins in the fin stack. Furthermore, a housing is provided in which the fin stack is arranged, wherein the housing and the fin stack are designed such that a gas flow in the housing can be directed from a first flow direction in the stacking direction to a second flow direction in the fin direction, e.g.is varied once or multiple times, whereby the lamella direction differs from the stacking direction.

[0014] The evaporator according to the invention makes it possible, with an easily manufactured and readily available fin stack, which actually only allows a gas flow direction in the fin direction for efficient evaporation, to achieve a gas flow in the housing that has both a fin direction and a stack direction component due to the interaction of the housing and the fin stack. In particular, this allows for the manufacture and installation of a very space-saving evaporator, for example on the end wall of a refrigerated compartment of a truck or semi-trailer. There is relatively a lot of space on the end wall in the vertical direction, but relatively little space in the depth and, in this embodiment, also in the width.The limitations regarding depth arise from the fact that in a refrigerated compartment, for example, inside a truck, the loading space should be as large as possible, and therefore the evaporator for cooling the loading space must take up very little depth. On the other hand, the height dimension is rather uncritical.

[0015] At the same time, however, fin stacks typically require a certain depth to achieve good air-liquid coupling with respect to the secondary liquid or vapor in the connectors. Again, the housing should not add a great deal of depth, but at the same time, good circulation should occur within the housing and within the fins. Good circulation is achieved by varying the gas flow within the housing through the design of the housing and / or the fin stack. One implementation is to use a zigzag fin stack shape and to house this zigzag fin stack arrangement in a straight housing. However, it is preferred to design the housing in a zigzag shape and use a straight fin stack due to its ease of manufacture.

[0016] It should be noted that the zigzag flow is merely a preferred embodiment, as it can be easily combined with a finned heat exchanger. However, a flow pattern other than zigzag can also be created as a varied flow pattern through the housing and thermal unit, as long as the air flow is generally perpendicular to the fins in the tube direction. In simple finned heat exchangers, the flow is always parallel to the fins and perpendicular to the tubes, e.g., the connectors. Therefore, alternative geometries that repeatedly push air from left to right and vice versa are also usable.

[0017] According to a second aspect of the present invention, the evaporator comprises a thermal unit and a housing in which the thermal unit is arranged, wherein the housing has a first ventilation opening and a second ventilation opening. Furthermore, the evaporator comprises a controllable fan configured to generate a gas flow through the first ventilation opening of the housing and the second ventilation opening in an active state. Furthermore, the evaporator comprises a closure mechanism configured to throttle or prevent the gas flow when the fan is deactivated and to allow the gas flow to pass when the fan is activated.

[0018] According to this second aspect of the present invention, the evaporator can be designed like the evaporator in the first aspect of the present invention, i.e., with a fin stack and a housing to vary the gas flow in the housing from a first flow direction in the stack direction to a second flow direction in the fin direction. Alternatively, the evaporator in a thermal unit according to the second aspect can also have a different structure, for example a structure as described in German application 102023202885.9. The evaporator used there also comprises a first header and a second header, as well as a plurality of connectors between the two headers. However, convection elements or heat distribution elements are arranged that are not designed as fin stacks, but rather allow gas flow in the direction of the arrangement of the connectors.Still alternative implementations may be formed in the thermal unit for the evaporator according to the second aspect, as long as there is provided a closure mechanism configured to throttle or prevent the gas flow when the fan is deactivated and to allow the gas flow to pass when the fan is activated.

[0019] Preferably, the closure mechanism is a passive closure mechanism in which, for example, one or more closure flaps are opened due to the activity of the fan, i.e. due to the suction effect of the fan, and remain open solely due to the activity of the fan, i.e. the existing airflow. Due to their passive implementation, the fan flaps will then only return to the closed state when the fan is deactivated and the airflow ceases. This ensures that if an evaporator is deactivated, the fan that is supposed to draw air through it is also deactivated and no longer thermally influences the room in which it is located. This is advantageous if, for example, the evaporator needs to be defrosted.The heat supplied to the evaporator, through the reversal of the thermosiphon process and the reversal of the primary heat pump circuit, will then not heat up the space to be cooled, or only minimally. This results in significant energy savings and ensures that the goods being cooled never thaw. Only when the defrosting process is complete will the fan be activated again, and the shutter mechanism open to pump cooled air back into the cold room.

[0020] This implementation is particularly advantageous when a cold storage room contains multiple evaporators located in different compartments, all connected to the same primary heat pump circuit. Even if different target temperatures are required in the different compartments, e.g., a very low target temperature for a freezer compartment (e.g., -30°C), a medium temperature for a fresh food compartment (e.g., 1°C), and a relatively high target temperature for a simple refrigeration compartment (e.g., 10°C), if an actual temperature in one of the three compartments is above a target temperature, the fan of the evaporator located in the corresponding compartment can be activated. The primary heat pump circuit then dissipates heat from this evaporator in the corresponding compartment, while the other two compartments are not affected.This means, for example, that deep freezing can be achieved in the freezer compartment without cooling the other two compartments, simply by controlling the fans so that the fans in the other two compartments are switched off and only the fan in the freezer compartment is activated.

[0021] If, on the other hand, the fresh food compartment is to be cooled, this can also be achieved with one and the same primary heat pump circuit, in which only the fan in the fresh food compartment is activated, but the fans in the other two compartments are deactivated and, due to the locking mechanism, the evaporators in these compartments are thermally inactive.

[0022] According to a third aspect of the present invention, a refrigeration chamber is provided in which an evaporator is arranged on a wall of the refrigeration chamber and has a fan at one end of a housing of the evaporator, wherein the fan is configured to cause cooled air to be conveyed into the refrigeration chamber in a ventilation direction. Furthermore, a support fan is arranged in the refrigeration chamber, positioned such that at least a portion of the cooled air conveyed by the fan is sucked in by the support fan and further conveyed into the refrigeration chamber.

[0023] The use of a backup fan is particularly advantageous when the cold room is relatively long and it must be ensured that, even if the evaporator is located at the front wall of the cold room, a reliable supply is also achieved to the end of the cold room, i.e., where the cold room can be opened. Especially at the cold room door, significant thermal losses can occur due to the door being opened or due to leaks. In such a case, the fan performance in the evaporator may still be too low, and this gap is closed by the backup fan.

[0024] Preferably, a less powerful axial fan can be used as the fan. In preferred embodiments, this fan is arranged at a slight angle above the thermal unit of the evaporator and draws in air from a slightly vertical direction and expels it in a slightly vertical direction. Such an axial fan, on the other hand, has the advantage of being very narrow in depth, so that the evaporator and fan can be installed in a very space-saving manner, e.g., in the cold storage compartment of a truck, thus allowing maximum utilization of the cold storage volume for the chilled goods to be transported. On the other hand, the auxiliary fan ensures that the cooled air is blown reliably throughout the entire refrigeration compartment and, in particular, reliably toward the door of the refrigeration compartment, which requires more thermal protection.

[0025] In preferred embodiments, the primary heat pump circuit is arranged above the evaporator in a niche, outside the refrigeration compartment, but in close proximity to the refrigeration compartment so that the lines penetrating the refrigeration compartment wall can be kept as short as possible. This results in a limited maximum vertical height in the area above the evaporator due to the niche. At the end of the niche, i.e., on the niche side wall, however, the maximum height of the loading space is available. The auxiliary fan is preferably arranged there in order to be optimally positioned with regard to the maximum height of the refrigeration compartment, in that there is almost the same or even more vertical height below the auxiliary fan than below the niche.This ensures that auxiliary ventilation is achieved by the auxiliary fan without the cooling device causing a disadvantage in the vertical direction for the space to be filled, e.g. in the truck or the trailer.

[0026] Preferably, the auxiliary fan is a deflection fan, i.e., a fan that draws in air in a first direction and discharges it in a second direction. Furthermore, an exhaust nozzle is arranged on the auxiliary fan to control the air flow and focus the air expelled by the auxiliary fan in the desired direction. In contrast, the fan in the evaporator is preferably designed as an axial fan to save space.

[0027] In preferred embodiments of a cold storage room with multiple compartments, it is preferable to use the evaporator with a fan and a backup fan in one compartment. In a second compartment, because, for example, a lower target temperature or less airflow is required there, an evaporator is arranged without a backup fan, i.e., with only one fan, which can be an axial fan or a bypass fan depending on the implementation. The fan concepts can be designed differently in the different compartments.

[0028] Furthermore, it is preferred to accommodate the primary housing with the primary heat pump circuit in the niche outside the cold room, wherein the primary circuit has a liquid-air heat exchanger that is arranged at an angle in the primary housing, such that air that can enter the primary housing from the front via air inlet openings flows through the inclined liquid-air heat exchanger and can exit the primary housing via air outlet openings arranged at the top of the primary housing. As a result, heat is released from the primary heat pump circuit into the ambient air. To support convection in the liquid-air heat exchanger, a fan can also be provided below the heat outlet opening and above the inclined liquid-air heat exchanger, for example toto achieve sufficient convection even when the truck is stationary and there is no air flow from the inlet opening to the outlet opening in the primary housing due to the airstream.

[0029] The first aspect of the present invention, with varied gas flow due to the zigzag housing or the zigzag fin stack, can be combined with the second aspect of the present invention, which relates to the closure mechanism in the evaporator. Both aspects, in turn, can be combined with the third aspect of the present invention, in which a support fan is arranged in the cooling chamber, preferably adjacent to the niche in which the primary housing is located. Therefore, according to the invention, all three aspects can be combined with one another.

[0030] Alternatively, however, only two of the three aspects can be combined, or all three aspects can be implemented without any other aspect. Thus, the evaporator can be used in a cold storage room with a zigzag gas flow, with or without a closure mechanism, or with or without a backup fan. Furthermore, the evaporator with a closure mechanism can be used with both a zigzag gas flow and a conventional gas flow, and with or without the assistance of a backup fan. Furthermore, the evaporator combined with the backup fan according to the third aspect of the present invention can be a conventional evaporator without a closure mechanism, an evaporator according to the present invention with a zigzag gas flow, or an evaporator according to the invention with a closure mechanism, which can be passive or active.

[0031] Preferred embodiments of the present invention are explained in detail below with reference to the accompanying drawings. They show: Fig. 1a is a plan view of an evaporator according to the first aspect; Fig. 1b is a side view of the evaporator according to the first aspect; Fig. 1c shows an implementation of the evaporator according to the first aspect with a zigzag housing; Fig. 1d an implementation of the evaporator according to the first aspect with a straight housing and zigzag fins; Fig. 2a a detailed view of the evaporator according to the first aspect and a preferred embodiment; Fig. Figure 2b is a detailed side view of the evaporator according to the first aspect with an air inlet and a baffle fan; Fig. 3a a detailed view of the slat stack with connectors arranged in the slat stack; Fig. 3b shows a further detailed view of a collector with a stack of lamellae arranged on the collector; Fig. 3c another representation of the evaporator with fin stack; Fig. 3d shows an illustration of the evaporator according to a preferred embodiment of the first aspect; Fig. 4a a representation of the evaporator with fin stack and opened housing; Fig. 4b shows a representation of the evaporator according to the first aspect with a closed housing; Fig. 4c shows a representation of the evaporator according to the first aspect with the housing front wall removed; Fig. 4d a preferred embodiment of a deflection fan with discharge nozzle; Fig. 4e a top view of the evaporator with a deflection fan; Fig. 4f a sectional view through the deflection fan with intake from below and a horizontal conveying direction; Fig. 4g a plan view of an evaporator with axial fan; Fig. 4h a detailed view of the axial fan; Fig. 4i a sectional view through the axial fan with intake from diagonally below and discharge diagonally upwards; Fig. 5 is a schematic view of an evaporator with a closure mechanism according to the second aspect of the present invention; Fig. 6a a detailed view of the evaporator with closed closure flaps; Fig. 6b a detailed view of the evaporator with open closure flaps; Fig. 7a a top view of the evaporator with fan seal and closed flaps; Fig. 7b a sectional view into the flow space below the fan seal with closed flaps; Fig. 7c a top view of the evaporator with the sealing ring for the fan seal and opened flaps; Fig. 7d a section through the flow space below the fan seal with the flaps open; Fig. 8a a schematic representation of the primary heat pump circuit and the evaporator with cycle reversal; Fig. 8b an alternative implementation of the cycle reversal of Fig. 8a; Fig. 9a a top view of a cold room with three compartments; Fig. 9b an implementation of a cold room with three compartments and a single primary heat pump circuit; Fig. 10a a view of a cold room with an external primary housing in a niche; Fig. 10b a section through the cooling room of Fig. 10a with a deflection fan; Fig. 10c a schematic representation of a cross section through the cooling chamber of Fig. 10a with an axial fan; Fig. 11 a top view of the front wall with three different fan implementations; Fig. 12 a representation of the section of Fig. 10c with two cooling elements; Fig. 13 is a schematic diagram of a refrigeration chamber having an evaporator and a support fan according to the third aspect of the present invention; and Fig. 14 a detailed view of the third aspect with cut-open primary housing

[0032] Fig. Figure 1a shows an evaporator according to the first aspect of the present invention. The evaporator comprises a first header 100 and a second header 200. Furthermore, a plurality of connectors 300 are provided, which extend between the first header and the second header. In the plan view of Fig. 1a, the connectors 300 are shown as straight tubes. They extend through a fin stack 400 in the direction of the evaporator assembly from bottom to top. Alternatively, the connectors can be arranged as shown in the side view of Fig. 1b, each have an upper slanted section extending away from the first collector 100. In the laminar stack, the connectors then run parallel. At the bottom, near the second collector 200, the connectors are again provided with slanted sections to form the spaced-apart connectors, as shown in the side view of Fig. 1b, back into the single collector pipe. Generally, the first and second collectors and the connectors are designed to allow the flow of a working fluid. This working fluid is preferably a non-flammable working fluid, such as CO2.

[0033] Furthermore, the fin stack 400 is formed with spaced-apart fins that are formed or arranged in thermal connection with the connectors and in a stacking direction, and that are further formed such that gas can flow in a fin direction 404 between adjacent fins 402, 403 in the fin stack 400. Furthermore, the evaporator is provided with a housing 600 that is Fig. 1c or Fig. 1d is shown in cross section, wherein the fin stack 400 is arranged in the housing, and wherein the housing and the fin stack are designed such that a gas flow 500 which is in Fig. 1c and Fig. 1d, in the housing from a first flow direction in the stack direction 401 to a second flow direction in the fin direction 404. This forced variation of the gas flow direction from the stack direction 401 to the fin direction 404 and vice versa due to the structural situation of the fin stack and / or the housing is achieved by the special design and arrangement of the housing 600 and the fin stack 400. In an implementation shown in Fig. As can be seen in Figure 1c, the zigzag flow direction is achieved by a zigzag housing 600, while the fin stack 400 is designed as a straight fin stack.

[0034] It should be noted that the gas or gas flow is typically air or an air flow. However, all concepts can also be operated in any other gaseous atmosphere other than Earth's air. Whenever a gas inlet or gas outlet is mentioned, this always also refers to an air inlet or air outlet, and vice versa.

[0035] On the other hand, the same gas flow 500, as in Fig. 1d, can also be achieved by forming the fin stack in a zigzag shape while the housing has a straight shape. Intermediate solutions with a zigzag housing and a zigzag fin stack can also be used to achieve a gas flow 500 that changes in the housing from a first flow direction in the stack direction to a second flow direction in the fin direction.

[0036] If, on the other hand, a straight fin stack and a straight housing were used, the gas flow would only take place in the stack direction from bottom to top, without the gas actually being drawn between the fins in the fin direction in order to achieve an efficient heat exchange between the gas and the liquid, which undergoes a phase change and flows in the collectors 100, 200 and the connectors 300, via the fins, for example the individual fins 402, 403.

[0037] Preferably, the housing comprises a first ventilation opening, such as an air inlet 603 in Fig. 2b or Fig. 4b, as well as a second ventilation opening, such as at 607 in Fig. 2b. The ventilation opening 607 is, for example, an air outlet from the evaporator and is arranged near the first collector 100. Furthermore, the air inlet opening 603 is formed near the second collector 200, so that air blown by the fan 700 (in Fig. 2b, for example) is drawn from below through the gas or air inlet 603 into the housing 600, from there in the zigzag gas flow direction, which is schematically shown by the individual arrows 505, 506, from bottom to top. Fig. 2b preferred embodiment, the arrows 505 schematically represent the stacking direction 401 of Fig. 1b and the arrows 506 schematically represent the slat direction 404 of Fig. 2b. It should be noted that the gas flow will be continuous, but normally, as shown in Fig. 1c, for example, has a component in the slat direction and a component in the stack direction, wherein the components become larger or smaller depending on the design of the housing or the distance of the housing to the slat stack or will also reverse with regard to the slat direction, as indicated by the alternating direction of the arrows 506 in Fig. 2b is shown.

[0038] Depending on the implementation, the fan 700 can be arranged on top of the evaporator on the air outlet 607. Alternatively, the fan can also be arranged at the bottom of the evaporator to blow air into the air inlet. Furthermore, the air inlet 603 can also be arranged below the fan or, as shown in Fig. 4b, in front of a part of the fan stack passing through the fan opening 603 in Fig. 4b is visible.

[0039] Alternatively, one vent can be a passive vent and the other an active vent. Fig. In the embodiment shown in Figure 2b, the air outlet opening 607 is the active ventilation opening because the fan 700 is arranged at it. However, both openings can also be designed as active ventilation openings. In this case, two fans are provided, namely one fan for blowing into the evaporator and another fan for extracting from the evaporator. However, a single fan 700 is preferred, which is attached to the air outlet opening 607 at the top of the evaporator housing. The fan is attached via a sealing ring as a fan seal or sealing rubber 702, which surrounds the air outlet opening. Alternatively, depending on the embodiment, the fan can also be attached to an air outlet that is not arranged at the top of the housing, but in the upper area, but on the side of the housing, similar to the air inlet.

[0040] Fig. Figure 2a shows in the left part of the image the varying distance between the housing 600, which is designed as a zigzag housing, and the lamination stack 400.

[0041] Furthermore, the cross-section through the lamination stack and the housing in the right-hand part of Fig. 2a a large distance 405 on one side of the lamella stack and a small distance 406 on the opposite side of the lamella stack. The cross section could, for example, be measured at a line 407 in the left part of Fig. 2a, whereby the small distance 406 is then arranged on the right in the left part of the image, while the large distance 405 is arranged on the left with respect to the lamella stack in the left part of the image of Fig. 2a is arranged.

[0042] Thus, the shape of the housing ensures that the distance of the housing on one side changes from a maximum distance 405 to a minimum distance 406 and vice versa. Preferably, the housing is further configured such that when the minimum distance 406 is arranged on one side, the maximum distance 405 is arranged on the other side with respect to the fan stack 400, as shown in Fig. 2a is shown in the left part of the image.

[0043] However, this configuration is merely a preferred embodiment. If the maximum pitch and minimum pitch are offset along the length of the stack 400, a gas flow is also achieved that varies from the fin direction to the stack direction and vice versa. To ensure sufficient flow, it is preferred that a region of the housing with a minimum pitch 406 be opposite a region of the housing with a pitch that is at least half the maximum pitch 405.

[0044] Preferably, the minimum distance is further less than 2 cm and more preferably less than 1 cm, so that a safe flow reversal or a safe forced flow in the slat direction is achieved.

[0045] In preferred embodiments of the present invention, as described in Fig. 2b, there are three locations with minimum distance 406 along the length of the evaporator on the right side and on the left side of the view in Fig. 2b Two locations with a minimum distance, offset from the locations with a minimum distance on the right side. This achieves triple air circulation across the fin stack. In a design with a smaller vertical extension, two areas with a minimum distance on one side of the heat exchanger, offset from a area with a minimum distance on the other side of the heat exchanger, would also be sufficient to achieve a variation in the gas flow from the stack direction to the fin direction and vice versa. In longer evaporators, air or gas circulations of more than three times through the fin stack can also occur.

[0046] In preferred embodiments of the present invention, such as can be easily accommodated in a truck, but are also useful in other applications, the housing is at least 60 cm and more preferably at least 130 cm high, at least 60 cm wide and less than 20 cm and more preferably at least 15 cm deep in order to achieve a slim design, particularly with regard to depth, since depth is of crucial importance for loading the truck.

[0047] Fig. 3a and Fig. 3b show the partial views of the evaporator with the lower collector 200 and the connectors 300, which, as shown in Fig. 1b, extend from the collector 200 over the oblique sections and then penetrate into the lamella stack 400, which, for example, has the individual adjacent lamellae 402, 403. Furthermore, at 406, a lamella holder of the lamella stack is shown, which can be provided either over the entire length or only at fastening sections, as shown at 407 in Fig. 3c and Fig. 3d. The reinforcement sections or fin holders 406 are connected to the fastening sections 407 in order to secure the entire heat exchanger or the thermal unit of the heat exchanger, which is shown in Fig. 3c and Fig. 3d is shown without a housing, to a wall of a cold storage room, such as a front wall in the loading space of a truck or a container. Fig. 3c, the connector 100 is closed on one side 101 and has a connection piece 102 on its other side. In embodiments, both sides can also be open, for example, if one side is the liquid connection or the steam connection and the other side of the corresponding collector, such as the collector 100 in Fig. 3c, is connected to another collector of another evaporator, for example, as will be explained with reference to Fig. 9b is explained.

[0048] Fig. Fig. 4a shows a detailed view of the evaporator with a housing rear wall 601, a fastening section 407 and a screw closure preferably designed as a quick-release mechanism 606 to fasten a front wall 602, which in Fig. 4b, from the rear wall. This ensures that the evaporator can be cleaned easily and safely. By removing the front wall 602 from the rear wall using the quick-release fastener 606, the thermal unit, in particular the fin stack 400, is directly accessible and can be rinsed with water, for example. This enables cleaning, which is particularly important if, for example, the same truck is used to transport fish one day and vegetables another day, although this change occurs rather rarely in practice. However, simple and thorough cleaning is also indispensable if similar goods are always loaded into the same cold storage room. In this case, safe cleaning will be necessary to avoid unpleasant odors.To ensure safe hygiene, it is also particularly important that the vaporizer can be easily cleaned and that steps on the vaporizer to achieve this cleaning can be carried out easily and even by non-specially trained personnel.

[0049] Furthermore, the Fig. The image shown in Figure 4b also shows the arrangement of the air inlet openings 603 in the housing. Furthermore, a fan 700 is shown at the top, which is designed as a deflection fan and has an exhaust nozzle 701. Fig. Figure 4d shows a detailed view of the fan 700 with the exhaust nozzle 701, while Fig. 4e shows a plan view of the fan, further showing a condensate drain 604, which is also shown in Fig. 2b. Furthermore, Fig. 2b shows a cross-section of a condensate drain pan 605, above which the second collector 200 is located. If defrosting of the evaporator is to be achieved, warm steam is brought from a heat exchanger of the primary heat pump circuit via the first collector 100 into the connectors 300, thereby heating the fins of the fin stack 400. This melts ice that has accumulated on the fins, and the defrost water runs along the fins to the end of the fins and then drips downwards. The defrost water can easily pass through the narrow sections of the housing and thus runs from top to bottom into the collecting pan 605, where it is then collected or drained away via the hose 604.

[0050] Fig. 4f shows the deflection fan, which sucks air from below, from the evaporator housing within the sealing ring 702, deflects it in its direction and then blows it out through the exhaust nozzle 701. Fig. Figure 4g shows an alternative fan implementation of the fan 700, namely as an axial fan, which, as particularly shown in Fig. 4i, is arranged slightly obliquely, resulting in a slightly upward blow-out direction 707, which is arranged at right angles to a front side of the fan or to a front side of the housing 708. A corresponding recessed edge, which increases from bottom to top, is provided at 704 in Fig. 4h shown.

[0051] The Fig. 4g, Fig. 4h and Fig. 4i shown axial fan is advantageous if the deflection fan of the Fig. 4d-f cannot be used because the deflection fan is too deep. The axial fan in Fig. 4i has a depth almost half that of the deflection fan from Fig. 4f. However, typically with deflection fans, as used in Fig. 4f, stronger ventilation performance can be achieved than with axial fans, as shown in Fig. 4i. However, if the lower power is sufficient or, as will be explained with reference to the third aspect, a support fan is used, an evaporator according to the invention can be optimally designed with an axial fan 700, which has a very small depth. The slightly inclined installation ensures that, due to the effect of the housing, the air flow 708 is deflected from bottom to top and then by the axial fan into the blow-out direction, wherein the installation direction only needs to have a slight inclination, such as less than 10 degrees upward inclination with respect to the blow-out direction 707, i.e. by an angle α from Fig. 4i, which can be less than 10 degrees to ensure a shallow depth of the fan located on the evaporator.

[0052] Preferred embodiments of the evaporator are characterized in particular by at least one of the following features, which include the following: - a small number of rows of pipes or connectors, - no deflection bends, i.e. no back and forth of the fluid flow, but straight connectors and straight collectors, - a single manifold at the top or a single manifold at the bottom, i.e. vertical connecting pipes, whereby a slight inclination of the entire thermal unit towards the front or back can be used to allow better drainage of condensate, if this is feasible due to space constraints. - Air flow in the connector or pipe direction, realized as a zigzag flow of air in serpentines.

[0053] Fig. Figure 5 shows an evaporator according to a second aspect of the present invention, comprising a thermal unit shown in dashed lines in Fig. 5 and can comprise, for example, the first collector 100, the second collector 200, the connecting lines 300, and the fin stack 400. However, the thermal unit of the evaporator can alternatively be designed in any other known form, as described, for example, in the German application DE 102023202885.9. In general, the thermal unit is designed as a liquid-gas or liquid-air heat exchanger. Furthermore, a housing 600 is provided in which the thermal unit is accommodated, wherein the housing has a first ventilation opening 603 and a second ventilation opening 607. In addition, a controllable fan 700 is provided, which, in an activated state, is designed to generate a gas flow 500 through the first ventilation opening 603 and the second ventilation opening 607.According to the invention, a closure mechanism 800 is further provided, which is designed to throttle or prevent the gas flow 500 when the fan is deactivated and to allow the gas flow 500 to pass when the fan 700 is activated. Merely by way of example, the closure mechanism 800 in the device shown in FIG. Fig. 5 is arranged on top of the housing 600. The closure mechanism could also be formed inside the housing, as shown in Fig. 6a-7d. Alternatively, the closure mechanism 800 can also be arranged below, e.g., in front of or just above the inlet openings 603.

[0054] Preferably, the closure mechanism 800 is designed as a passive closure mechanism in order to release a flow space 801 for the gas flow due to the activity of the fan during the activated state of the fan and to close the flow space 801 when the fan transitions to the deactivated state due to the decreasing gas flow. The flow space 801 is in the Fig. 6a and Fig. 6b and is located below the seal 702, on which the fan is placed. The flow space is located between the fan 700, which is Fig. 6a and Fig. 6b is not shown, and the thermal unit of the evaporator, for example the fin stack 400 with upper collector 100 and the connectors 300. The passive closure mechanism is used in the Fig. 6a to 7d is implemented by two flaps 802, 803, which are each attached to hinges 804, 805 in the flow space 801 and are designed such that when the fan starts the gas flow 500, which is directed upwards, they open upwards and are then in an open state which is shown in Fig. 6b is shown.

[0055] When the fan stops the gas flow 500, the flaps fall back due to gravity and rest on the upper collector 100, as is the case, for example, in Fig. 7a and Fig. 7b is shown. Fig. Figure 7a shows a top view of the housing of the thermal unit with the seal 702 mounted thereon, which is arranged circumferentially. Fig. 7a shows that the fan flaps 802, 803 have an elongated shape over the entire width of the housing in order to effectively throttle or completely stop or prevent the gas flow.

[0056] Fig. 7b shows a section through the housing below the sealing ring 702, i.e. through the flow chamber 801. Fig. 7c again shows a top view of the housing with the fan flaps open, i.e. in the state of Fig. 6b, wherein the lamella stack 400 is visible past the collector 100. Fig. 7d, in turn, shows a cross section through the flow space 801 below the sealing ring 702, so that the edges of the flaps 802, 803 can be seen from above in the open state.

[0057] Preferably, the flaps are on the hinges 804, 805, which are in Fig. 6b, in such a way that the hinges are attached to the rear of the flap, i.e., on the side of the flaps past which the flow does not pass. One hinge piece is attached to the flap and another hinge piece is attached to the housing, and both hinge pieces are engaged to achieve the hinge effect. Furthermore, it is ensured that the hinges themselves do not interfere with the gas flow, or only interfere with it to a very small extent, and that, at the same time, due to the shape of the flaps and the center of gravity of the flaps, they fall back automatically without being spring-loaded. Depending on the implementation, however, a slight spring preload in one direction or the other can also be used. However, it is preferred to allow the flaps to close completely without preload due to gravity alone when the fan 700 is deactivated.

[0058] Depending on the implementation, the present invention can also be implemented with a single flap. This would be the case with the Fig. 6b, the thermal unit has the flap 802, because the gas flow only flows through the side of the flap 802. For reasons of symmetry, and due to the fact that the housing is on the left and right in the top view of Fig. 7a does not have to be 100 percent closed, it is preferred to provide both flaps, i.e. also flap 803, although flap 802 would already achieve the effect of at least throttling the gas flow, whereby it is preferred to completely prevent the flow by completely closing the flow space.

[0059] Alternative structures in which the collector 100 is not arranged centrally in the flow space 801, but at the edge, would also result in a single flap, such as only the flap 802, being required if the collector is arranged at the very right edge, for example in Fig. 6a of the flow chamber. However, the use of two flaps also ensures that the space required in the flow chamber can be kept small, because the flow chamber must accommodate the entire length of the flaps when the flaps are open, as shown in Fig. 6b is shown.

[0060] The automatic flaps 802, 803 are therefore designed to open automatically when the fan is activated by the air flow. When the fan is switched off, they are closed again by gravity alone. When the check flaps or the closure mechanism are closed, the space around the heat exchanger element, i.e., the thermal unit, is closed, sealed off, or insulated, so that regardless of the temperature of the heat exchanger element, i.e., regardless of the temperature of the fin stack, the two collectors, and the connecting lines, no free convection can occur. Thus, the entire evaporator is thermally inactive. This function is particularly advantageous when connecting multiple elements in different cold rooms to achieve different temperatures simply by activating the fan.Furthermore, the elements can be defrosted, i.e. defrosted, with the fan stopped, i.e. with the flaps closed, by supplying warm refrigerant when the cycle in the primary heat pump circuit is reversed, without free convection conducting a heat flow into the cold room.

[0061] To reverse the cycle, a pump 8 is located near the lower or second collector 200 in embodiments, which, for example, Fig. 8a and Fig. 8b is shown.

[0062] Thermal cycle reversal with a lower-lying heat source can also be achieved in ways other than pump 8, as described, for example, in German application 10202302885.9, where a double thermosiphon principle is used, i.e., a thermosiphon principle not only in the normal cooling function, as in the present invention, but also in the defrosting function. However, according to the invention, a double thermosiphon device can also be used, in which pump 8 is not required.

[0063] Defrosting is thus achieved by stopping the fan 700, whereupon the dampers close and render the entire evaporator thermally inactive for the compartment in the cargo space, for example, of the truck. Then, by reversing the circuit in the primary heat pump circuit or primary circuit, the heat exchanger to which the evaporator is connected is heated, so that warm vapor from the heat exchanger enters the first collector 100 and from there into the connectors, thereby heating the fin stack, so that the ice on the fin stack is thawed and flows downward as condensate. The warm vapor supplied via the first collector 100 is condensed in the connectors 300 by this defrosting effect and returned to the heat exchanger by the pump, thus closing the "defrost circuit."Once the fin stack has defrosted, the fan can be activated again, the flaps open, and the gas flow 500 can again enter the room to be cooled.

[0064] Such a temperature control device with a controllable primary heat pump circuit with a compressor, a heat exchanger and a throttle is in Fig. 8a or Fig. 8b. Furthermore, the evaporator is also located at 14 in Fig. 8a, wherein the thermal unit of the evaporator has a vapor connection on the first header 100 and a liquid connection on the second header 200, both of which are coupled to the primary circuit, as shown at 15a and 15b. Furthermore, a controller 30 is provided to control the controllable primary circuit in a cooling mode for the evaporator or in a defrost mode for the evaporator, wherein the controller 30 is configured to activate the evaporator fans in the cooling mode and to deactivate the fans in a defrost mode, so that the closure mechanism 800 throttles or deactivates the gas flow.

[0065] Both lines, the steam connection and the liquid connection, are connected via corresponding lines 15a, 15b, which are Fig. 7a, are coupled to the heat exchanger 7, which acts as an evaporator in normal cooling mode and as a condenser of the primary circuit in heating mode.

[0066] Fig. Figure 8a shows a device for controlling the temperature of a space 5 to be temperature-controlled (e.g., a cold storage room) with a space boundary 20 that separates the space 5 to be temperature-controlled from an environment 21. The device comprises 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 has a natural primary working fluid, the compressor 1, the evaporator 4, the condenser 2, the compressor 1, and the expansion element 3 being arranged outside the space 5 to be temperature-controlled. The device according to the invention further comprises a secondary circuit that is thermally coupled and fluidically decoupled from the evaporator 4 or the condenser 2 via a heat exchanger 7, and has a temperature control element 14. The temperature control element 14 is arranged in the space 5 to be temperature controlled and is connected to the heat exchanger 7 via a line arrangement 15a, 15b.The conduit arrangement contains a secondary fluid that differs from the primary fluid. Furthermore, the conduit arrangement 15a, 15b is designed to penetrate the spatial boundary.

[0067] If the secondary circuit is coupled to the evaporator 4 via the heat exchanger 7, the system is in cooling mode for the room to be tempered. The tempering is then cooling, and the tempering element 14 functions as a cooling element. If, however, the secondary circuit is coupled to the condenser 2 of the primary heat pump circuit via the heat exchanger 7, the tempering device functions as a heating device, and the tempering of the room 5 is heating, with the tempering element 14 functioning as a heating element. The heat exchanger 7 can therefore function as an evaporator or a condenser.

[0068] A controller 30 is provided in the preferred embodiment to switch the compressor 1 of the primary heat pump circuit, e.g., in its flow direction, or generally to effect a circuit reversal, via a control signal 31 to switch the primary heat pump circuit with respect to the flow direction of the primary working fluid. This ensures that, while maintaining the coupling of the secondary circuit, the function of the secondary circuit is also changed, namely that the secondary circuit is in cooling mode or heating mode. If the secondary circuit is normally in cooling mode, the heating mode is used to defrost the temperature control element or evaporator 14.The initiative for outputting the control signal 31 or the control signal 32 from the controller 30 to a pump or fan element possibly arranged in the secondary circuit, such as element 8, can originate from a sensor, a clock generator, or an external signal, as represented by a control input 33. If, however, the controller is designed to be controlled via a sensor input or a clock generator, then the clock generator or the sensor input would be connected to the control input 33, or the control input 33 would not be present, and the initiative for outputting the control signal 31 / 32 would be generated from the controller 30. The controller is further designed to control the fans 700 of evaporators, for example, in the second aspect in which several evaporators are connected to one and the same heat exchanger, to control a fan in a respective compartment when a cooling effect is required in the compartment.

[0069] As it is in Fig. As shown in Figure 8a, the secondary circuit can be provided with a pump 8 to circulate the secondary fluid in the secondary circuit, and in particular in the line arrangement 15a, 15b. The temperature control element 14 operates as a phase-change heat exchanger. Therefore, one part, for example, part 15a of the line arrangement, is the liquid-carrying part, and the other part, such as part 15b, is the steam-carrying part of the line arrangement in the secondary circuit.

[0070] The cold and heat generated by the refrigerant process are then transported indirectly via a suitable heat exchanger, for example, a plate heat exchanger 7, with a non-flammable, safe working fluid, a so-called secondary fluid, to the refrigerated body, refrigerated container, or generally the space to be cooled. The refrigeration system thus consists of a primary circuit for cold generation and a secondary circuit for cold and heat transport.

[0071] The secondary circuit operates through a phase change in the evaporator of the enclosed space, removing heat from it or adding heat. The secondary circuit transports the heat to the refrigerant-filled part of the machine, i.e., the primary circuit. The phase change is advantageously a liquid-to-gas phase change to ensure the pumpability of the secondary fluid.

[0072] Forced-drive secondary circuits, i.e., those using a pump, have the disadvantage that the pump requires energy to overcome the flow resistance of the secondary system. An alternative to this, which does not require the use of a pump, is to design the secondary circuit as a thermosiphon circuit. In this case, the working fluid (the secondary fluid) is liquefied in the evaporator 10 of the refrigeration part of the machine during the phase change of the secondary circuit. It enters the heat exchanger (evaporator of the primary circuit) in vapor form at the upper part 10b and exits the heat exchanger as a liquid 10a at the lower part.The liquid working fluid is then fed through suitable pipes into the enclosed space to be cooled, where it flows into an evaporator, where it enters the lower section in liquid form and exits the upper section of the evaporator / cooler in vapor form. It is then fed back to the heat exchanger 7 of the refrigeration section, where the working fluid is then liquefied again and flows back to the cooler in the cold room solely by gravity, which leads to level compensation. This self-circulation has the advantage of eliminating the need for a pump with its associated energy consumption and risk of failure. Furthermore, only a minimal number of components are required. The secondary circuit must be designed so that, during system operation, a driving pressure difference is created by geodetic differences in height and / or the thermosiphon effect.It is particularly advantageous if the evaporator is flooded during cooling, as this ensures maximum utilization of the cooler's air side. This is the case with the present invention because, for example, the heat exchanger is mounted in the niche at the top of the cooling chamber, and the evaporator is mounted on the front wall of the cooling chamber below the niche.

[0073] In the application case where heat must be supplied to the enclosed space or the evaporator needs to be defrosted, the process is reversed by supplying energy to the heat exchanger 7, and the liquid phase of the secondary fluid evaporates and leaves the heat exchanger as a vapor phase and is fed through a suitable pipe to the heat exchanger 14 in the enclosed space. The refrigerant enters the heat exchanger in the enclosed space as vapor, is liquefied there, releases its heat in the process, and flows in liquid form back from the "evaporator" 14, which now acts as a condenser, back into the heat exchanger 10 of the primary circuit, where the evaporation process then begins again. This cycle reversal can be achieved by the pump 8, which, however, operates in the opposite direction of the arrow with respect to Fig. 8a or Fig. 8b is operated.

[0074] The condenser of the refrigeration part of the machine, as well as the heat exchanger in the enclosed space or container, are generally operated on the air side with forced convection generated by suitable fans. Similar to the refrigeration part of the machine, the primary circuit, care must be taken in the secondary circuit to keep the filling quantities of working fluid to a minimum, thus ensuring that a cooler is used that not only has a small internal volume but also a low thermal mass in order to carry out the defrosting process as quickly and as energy-efficiently as possible. Thus, heat exchangers with a low refrigerant filling and minimal material usage, for example, microchannel technologies for the heat exchanger 14 in the enclosed space, are generally suitable, as they particularly meet the required requirements. Other designs, such as finned heat exchangers, can also be used as alternatives.Both heat exchanger types are ideally operated in a flooded state.

[0075] Due to the elimination of pumps through the use of thermosiphon solutions and the resulting energy advantages, as well as the reduction in the complexity of the systems, such solutions have particular advantages over the state of the art described above in the area of ​​compact systems with spatial distances preferably of up to 10 meters and cooling or heating capacities of less than 50 kW and particularly preferably of up to 2 meters between the two heat exchangers 7 and 14 and with low cooling or heating capacities of less than 10 kW and are therefore to be preferred.

[0076] If, in a considered application, it is not necessary for the refrigeration machine to be able to heat the enclosed space when needed, it is always advantageous to arrange the heat exchanger 14 in the enclosed space 5 geodetically below the heat exchanger 7, where it is flowed through by the refrigerant. It is irrelevant how far below the heat exchanger in the enclosed space 11 is positioned compared to the heat exchanger 7, through which the refrigerant flows. This arrangement of the two heat exchangers in relation to one another ensures that the heat exchanger in the enclosed space is completely filled with the secondary fluid at every operating point, while the heat exchanger 7, through which the refrigerant flows, has its entire surface available for liquefying the vaporous refrigerant that is fed to it from the heat exchanger 14 in the cooling space 5.

[0077] Fig. Figure 8b shows a further embodiment in which two changeover switches 35a, 35b are provided for reconfiguring the primary circuit. In a first state, these switches switch the heat exchanger 4, 7 as the condenser of the primary circuit's refrigeration circuit, i.e., to heat the heat exchanger 2, 7. In the alternative configuration, the changeover switches 35a, 35b are switched such that the heat exchanger is switched as an evaporator, i.e., located on the low-pressure side of the refrigeration circuit. In the first configuration, the connections between the two ports in the control elements 35a, 35b are simply continuous, whereas in the second configuration, they switch the corresponding detours.

[0078] Accordingly, line 15a is split into two individual lines for the two control devices 35a, 35b. Furthermore, control 15 will also control the fans 700 in the various compartments of the refrigeration chamber.

[0079] An alternative implementation can be designed such that the controller 15 only controls the compressor 7a so that it reverses its direction of rotation or conveying direction and, in a sense, conveys from bottom to top. In this case, the two changeover switches 35a, 35b would not be present, the connections of the (then absent) changeover switches would be directly connected, and the controller would simply reverse the direction of rotation of the compressor 7a to switch from heating mode to cooling mode and vice versa. However, for implementation reasons, it is preferred to always run the compressor 7a in the same conveying direction and to perform the switching via fluid switches, such as the fluid switches 35a, 35b.

[0080] Depending on the implementation, the heat exchanger 4 can be integrated with the evaporator or condenser of the refrigeration circuit of the primary circuit. Alternatively, however, the heat exchanger 4 can also be connected into the process, although the refrigeration circuit itself has its own evaporator and condenser. In such a case, for example, to heat the heat exchanger 4, the liquefied warm liquid from its own condenser would be fed into the heat exchanger. Alternatively, the liquid cooled in the evaporator due to 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 refrigeration circuit of the heat transport device via another heat exchanger. The heat exchanger 4 is preferably designed as a plate heat exchanger.

[0081] Fig. Figure 9a shows a plan view of a cargo space with three compartments 901, 902, 903, wherein the compartments are separated from each other by partition walls. Furthermore, in each compartment in the Fig. 9a shown example, an evaporator 14 is arranged, which as in Fig. 1a, or which can also be a conventional evaporator, as is also shown, for example, in Fig. 5 has been presented.

[0082] Fig. Figure 9b shows a top view of the different evaporator units 14, each of which includes fans 700 arranged at the top and intake openings 603 in the lower region. Furthermore, the upper headers and the lower headers are indicated. The upper headers are interconnected by a connecting line 908, and the lower headers are interconnected by a connecting line 906. A single liquid line 905 is arranged between the heat exchanger 2, 7 and the lower header of the evaporator in compartment 903. However, the single liquid line 905 could also be arranged on the lower header of the evaporator in compartment 902 or in compartment 901.

[0083] In addition, a single steam line 904 is connected between the upper collector of the evaporator in the third compartment 903 and a steam connection of the heat exchanger 2, 7, wherein the single steam line 904 may also be connected to the upper collector of the evaporator in the compartment 902 or to the upper collector of the evaporator in the first compartment 901.

[0084] Alternatively, there may be just two different compartments or even four, depending on the design. At least two compartments are connected to a single primary heat pump circuit or a single exchanger, which is used as an evaporator in cooling mode in the primary heat pump circuit.

[0085] The cooling chamber is thus divided into two or more chambers 901, 902, 903, in which preferably different temperatures should be maintained. To achieve this, each compartment contains its own evaporator containing liquid refrigerant. The refrigerant in all evaporators is in a state of equilibrium between the liquid and vapor phases, and the evaporators are connected to each other via communicating tubes, so that the same liquid level is established in each evaporator. The communicating tubes are the liquid connectors 906 in Fig. 9b. Furthermore, the evaporators 14 in the individual compartments are each connected in such a way that in their lower part there is a connecting pipe for the liquid, the connecting pipe 906, and the lower collectors. In the upper part, i.e., above the liquid level, the evaporators are each connected to one another by a pipe 908 through which the vapor, after the evaporation of the refrigerant, can be fed to the heat sink, i.e., the heat exchanger 2, 7 of the evaporator network. The heat sink 2, 7 of the evaporator network serves to reliquefy the refrigerant. This occurs because the primary refrigerant, i.e., preferably the flammable refrigerant, evaporates on the primary side of the heat exchanger 2, 7, thereby liquefying the secondary vapor.

[0086] In the individual compartments 901, 902, and 903, the liquid refrigerant is fed to the evaporators 14 in the cooling rooms. Each evaporator is located in a closed housing, i.e., a closed casing, which has an air intake opening 603 in the lower area and a fan or ventilator 700 in the upper part, which ensures that the air to be cooled flows through the closed housing 600. Evaporation in the respective evaporators 14 only occurs when a respective fan provides an air flow whose temperature is above the saturation temperature of the refrigerant in the respective evaporator. If a fan 700 of an evaporator module is not operated, no cooling effect occurs in the respective room.This allows the cooling effect of a room to be adjusted to the respective target value, i.e., the target temperature in that room, by switching the evaporators and thus the air flow across the evaporator surfaces. If a fan 700 of an evaporator is not operating, the housing ensures that the evaporator package, which is filled with the liquid refrigerant, is not in thermal exchange with its surroundings. Thus, switching the evaporators on and off ensures that each room operates at a different temperature.

[0087] It is also important to ensure that the refrigerant is at the temperature required to bring the coldest room to the desired target temperature. If the lowest temperature is reached in a room, turning off the fan in the room with the lowest temperature and turning on a fan in a room with a higher temperature will reset the saturation pressure in the overall system. This will then result in a refrigerant saturation pressure in the overall system that meets the requirements for achieving the desired air temperature reduction.

[0088] This has the energy advantage that the saturation pressure of the refrigerant in the system does not always have to correspond to the lowest required temperature. In this way, with a saturation pressure of the refrigerant in the evaporators, the corresponding target temperatures can be consistently achieved in the various separate compartments of one and the same cold storage room by switching fans on and off, with only a single primary heat pump circuit being used for two compartments.

[0089] Preferably, the individual evaporators 14 in the various compartments are designed to have a locking mechanism, so that convection through the evaporator is prevented when the corresponding fan of the evaporator is deactivated.

[0090] It should be noted, however, that the closure mechanism need not be present. Then, in each of the at least two compartments, there is only one evaporator with a housing and fan, which are connected to each other by line 906 with respect to the lower collector and by line 908 with respect to the upper collector. These evaporators can be designed like conventional evaporators or like the evaporators according to the invention of the first aspect, and furthermore, with or without closure flaps.

[0091] However, it is preferred to use a locking mechanism as this ensures that in the event of the fan being stopped, no free convection occurs through the case and the top and bottom ventilation openings.

[0092] To determine the actual temperature in the respective compartment, a temperature sensor 911, 912, 913 is arranged in the respective room, as shown in the respective compartment 901, 902, or 903. Furthermore, it is preferred that corresponding target temperatures for the individual compartments 901, 902, 903 are stored in the corresponding controller, such as the controller 15 of Fig. 8b or the control 30 in Fig. 8a, so that a target-actual comparison and a dependent activation of the respective fan can take place. Upon such activation, the control will then only activate the corresponding fan, but will not cause a reversal of the primary heat pump circuit if no defrosting action is to be performed. Furthermore, the control 30 is Fig. 8a or 15 of Fig. 8b Furthermore, the corresponding compressor capacity can be increased if a cooling request arises from the room with the coldest target temperature because the actual temperature has risen above the target temperature. Conversely, the compressor capacity can be reduced if, at a later time, a temperature request arises from the compartment with the highest target temperature because the actual temperature there has risen above the (high) target temperature.

[0093] Fig. 10a shows a side view of a truck with a niche 60 for the primary heat pump circuit. Fig. Figure 10b shows an exemplary dimensioned variant of an arrangement of the evaporator according to the first aspect of the present invention below the niche 60, specifically at a front end thereof. In particular, the primary heat pump circuit is housed in a primary housing 61. Furthermore, in the implementation in Fig. 10b, the fan is designed as a reversible fan or as a fan with a greater depth to achieve high fan performance in the refrigeration chamber. Furthermore, a carriage 62 for transporting refrigerated goods is arranged in the refrigeration chamber. Furthermore, a spacer 63 is provided in the lower area of ​​the refrigeration chamber. This spacer ensures that the carriage has a firm stop. This spacer is arranged in front of the fan housing, so that the carriage 62 does not damage the evaporator when mounted in the refrigeration chamber.

[0094] In Fig. Figure 10c shows an alternative implementation of the fan 700, which is designed here as an axial fan. The axial fan can easily be installed in reverse or operated in reverse with respect to the fan wheel, so that the blowing direction can also be adjusted from top to bottom, in contrast to the normal blowing direction 64, as shown in Fig. 10c is indicated by the arrows.

[0095] Out of Fig. 10a shows that the niche 60 is dimensioned such that all components of the primary heat pump circuit have space in the niche and yet the outer contour of the truck trailer is "undisturbed", i.e. the primary heat pump housing essentially does not protrude beyond the ceiling of the trailer or beyond the front wall of the trailer.

[0096] An advantage of the evaporator according to the invention according to the first or second aspect is that the evaporator is more cost-effective and simple to manufacture using conventional manufacturing methods, which is achieved in particular by the vertical fin stack according to the first aspect. Furthermore, compared to conventional evaporators, less material is used and thus also a lower weight is achieved, which is particularly important for mobile applications, i.e., in trucks. Furthermore, there is a lower air-side pressure drop, thus allowing a higher volume flow to be achieved with the same fan power.

[0097] Furthermore, in particular according to the first aspect of the present invention, a defined and orderly air flow is achieved over the evaporator package, wherein the fan power is guided back and forth through the fin stack in the fin direction up to approximately three times.

[0098] In addition, the locking mechanism in particular ensures that no air flow occurs during defrosting, for example, whereby self-closing flaps in particular ensure such self-closing activity of the flaps due to gravity whenever the fan or blower is stopped.

[0099] In addition, due to the housing having air inlet openings arranged at the front, improved collection and drainage of the condensate is achieved through the collection tray and the connection piece on the collection tray at the preferably lowest point of the housing, below the air inlet opening(s).

[0100] Furthermore, the inventive division of the housing into a front and rear wall, whereby the thermal unit can be exposed by removing the front panel, leads to better cleaning options for the evaporator. Simply removing the front panel provides good access to the thermal unit and also to the front of the rear panel.

[0101] In addition, two different modular blowers or fans can be used for three different configurations with different blower performance. In the fan variant, which is Fig. As shown in Figure 10c, the fan can optionally be mounted with the airflow direction reversed, so that the airflow through the heat exchanger occurs in the direction of natural convection from top to bottom, comparable to displacement ventilation in air conditioning. However, in this case, the "self-closing flaps" are not installed, or no locking mechanism is used.

[0102] Preferably, a typically small-sized CO2 pump is provided at the bottom of the evaporator for reversing the natural circulation for defrosting or for heating the evaporator or the thermal unit of the evaporator.

[0103] Fig. 11 shows a top view of three different fan variants in three different departments, such as the departments of Fig. 9a. Variant 1 includes a fan with a greater depth, as in Fig. 10b, which, however, achieves a higher fan or blower performance. Furthermore, variant 2 shows the use of an axial fan, which has a lower heat output than the deflection fan of variant 1, but has a smaller depth, which can be advantageous, especially when the refrigerated goods wagon 62 is very tall.

[0104] Fig. 11 shows an implementation of a cooling chamber according to a third variant or according to a third aspect of the present invention, which refers to Fig. 13 and Fig. 14 is presented in more detail. Fig. 12 also shows an implementation of variant 2 of Fig. 11 or variant 2 of Fig. 10c with a liquid line 905 and a steam line 904 at a lower and upper connection of a heat exchanger 70, which is arranged in the primary housing 61 in the niche 60 at the top of the cooling chamber 900. Furthermore, in Fig. 12 shows two refrigerated goods trolleys 62, and further shows the gas flow 500 leaving the fan 700, which is mounted on the housing 600.

[0105] Fig. 13 shows a refrigeration chamber 900 according to the third aspect of the present invention, in which an evaporator 14 is mounted on a wall of the refrigeration chamber 900, wherein the wall is preferably the end wall, but may also be any other wall of the refrigeration chamber.

[0106] Furthermore, a fan 700 is mounted at one end, such as the preferably upper end of a housing 600 of the evaporator 14, said fan 700 being designed to blow cooled air in a ventilation direction 950 corresponding to the gas flow 500 of Fig. 12, into the cooling chamber 900. Furthermore, according to the third aspect of the present invention, a support fan 750 is provided, which is arranged in the cooling chamber 900 such that it sucks in at least a portion of the cooled air, i.e., at least a portion of the air conveyed in the ventilation direction 950 by the fan 700, which is indicated by the two different arrows 951 and 952. Furthermore, the support fan 750 causes the air sucked in by the support fan 750 to be conveyed further into the cooling chamber, as shown at 953.

[0107] As a result, a flow is achieved in the cooling chamber which preferably leads to the rear wall, i.e. to the wall which is arranged opposite the evaporator 14, and there sinks downwards due to the limitation of the rear wall and then re-enters the housing 600 of the fan either from the front, as shown by an arrow 955, or from below, as shown by an arrow 956, into the housing 600 of the evaporator 14 due to the suction power of the fan 700.

[0108] This ensures that in a case where the fan 700, which directly ensures the flow through the evaporator, cannot generate a sufficiently large air flow, a ventilation flow sufficient for a large or relatively elongated loading space is nevertheless obtained.

[0109] The support fan 750 is preferably designed to suck in air in a suction direction and to convey it in a blow-out direction that differs from the suction direction, wherein the blow-out direction is substantially the same as the conveying direction of the fan, as is also indicated by the arrows 950, 953 in Fig. 13 is shown.

[0110] Furthermore, in a preferred embodiment of the present invention, as described in Fig. 14, the support fan 750 is arranged next to the ceiling niche 60, wherein in the ceiling niche, as already described with regard to Fig. 12, the primary heat pump circuit is arranged with the primary housing 61. The auxiliary fan in Fig. 14 is designed such that it typically draws in the air flow 950, which leads to a veil of cold air in the area below the auxiliary fan 750, from below, in order to thereby create a reversal of the conveying direction from below into the conveying direction 953, which is again parallel to the conveying direction 950. At the same time, however, the space next to the niche where the auxiliary fan 953 is arranged is optimally utilized and furthermore does not interfere with the clear height of the cold storage room or the maximum permissible height of the refrigerated trolleys 62. By arranging the auxiliary fan 750 next to the ceiling niche 60, the space next to the niche is thus optimally utilized, and it is further ensured that, despite the ceiling niche 60, due to the functionality of the auxiliary fan, the cold air is transported to a maximum in the upper area of ​​the cold storage room 900, typically from the front wall to the rear to the opening flap of the cold storage room.

[0111] The following will refer in more detail to the primary heat pump circuit in the primary housing 61. In particular, the primary heat pump circuit comprises the exchanger 2 or 7, which is preferably designed as a plate heat exchanger and is arranged vertically in the primary housing 61. Furthermore, the steam line 904 is connected to the top of the plate heat exchanger and the liquid line 905 is arranged at the bottom of the vertical heat exchanger. Furthermore, the primary circuit comprises a liquid-air heat exchanger 65, an air inlet 66 at a front end of the housing and an exhaust air inlet 67 at an upper end of the housing. In addition, a compressor 69 and an expansion valve (not explicitly shown) corresponding to the expansion valve 3 of Fig. 8a or Fig. 7b of Fig. 8b. In addition, piping is provided to connect the fluid switches 35a, 35b from Fig. 8b to effect a cycle reversal in the primary heat pump circuit for defrosting purposes. Furthermore, a fan 70 is arranged between the exhaust air opening 67 and the liquid-to-air heat exchanger 65 to effect convection from the inlet opening 66 through the heat exchanger 65 and out of the exhaust air opening 67, even when the truck is stationary.

[0112] It should also be noted that the ventilation opening 67 located at the top does not need to be closed. Should it rain, the water will enter through the ventilation opening and then drain away again without requiring any special measures other than a water drainage opening. Furthermore, the heat exchanger 2, 7 is connected to the compressor and the liquid-air heat exchanger 65 as shown in Fig. 8a or Fig. 8b is shown.

[0113] The outer wall of the cooling chamber comprises an outer skin 970 and an inner skin 971, whereby, depending on the implementation, the lines 904, 905 can run in the insulation of the cooling chamber, i.e. between the outer skin 970 and the inner skin 971. If this is not possible or desired, the lines 904, 905 can preferably be shown in plan view, for example in Fig. 9b run next to the respective housing or next to the housing of the evaporator 14 arranged, for example, on the right or left or centrally on the inner skin 971.

[0114] Furthermore, the ceiling niche 60 comprises a niche floor 980, which is designed to abut a front wall 981 of the cooling chamber, and a niche side wall 982, which adjoins the floor 980 of the niche and runs essentially vertically. Furthermore, the cooling chamber comprises a ceiling 983, which adjoins the side wall 982 of the niche and runs essentially horizontally. In particular, as shown in Fig. 14, the auxiliary fan 750 is mounted on the ceiling in the cooling chamber and arranged at a distance from the side wall 982 of the niche in order to achieve optimal suction. If the lines 904, 905 run in the insulation, i.e., between the outer skin 970 and the inner skin 971, then, contrary to the illustrated implementation, a single opening is preferably provided in the niche side wall 982 through which the two lines are routed through the outer skin 970. If, on the other hand, a line routing is provided on the inner skin 971, then the niche side wall 982 is preferably again completely penetrated with a single opening from the interior of the cooling chamber to the outside in order to route the two lines to the outside, into the primary housing 61.

[0115] Fig.11 shows a preferred implementation of the cooling chamber 900, in which the auxiliary fan 750 is provided in the compartment labeled "Variant 3," but is arranged in front of the niche side wall 982, while the fan 700 is arranged behind it. In the middle compartment, however, ventilation with only the fan 700 is sufficient without a auxiliary fan, while in the left compartment, ventilation with the axial fan 700 is not sufficient, and instead a deflection fan is required, which, although deeper, is nevertheless more powerful in terms of blower performance. The deflection fan is designed, for example, as a drum fan, as found in fans, e.g., in buses or similar vehicles. The deflection fan 750 can preferably also be designed as a radial fan or represents a radial fan.

[0116] Variant 3 in the third compartment will deliver the highest overall fan power, while variant 2 in the middle compartment will deliver the lowest fan power, and variant 1 in the first compartment will deliver a medium fan power. A high fan power is necessary if the compartment is very long, for example, while a lower fan power is sufficient if the compartment is shorter or smaller. This can be achieved, for example, by interior walls in the compartments if all compartments are arranged in one and the same truck trailer. According to the invention, however, the cold storage room can also be a stationary cold storage room in which compartments of different lengths with different required fan powers are arranged.

[0117] Alternatively, a situation may arise where, in addition to the fan power, a corresponding target temperature is also required. In this case, variant 3, for example, would be intended for the coldest room to ensure optimal cold air flow and thus temperature distribution even up to the wall opposite the evaporator. However, it should be noted that the heat output of the auxiliary fan must also be transported out of the compartment by the evaporator. Therefore, fans with very low heat loss and high efficiency are preferred.

[0118] The fan with variant 2 could be intended for a refrigerated compartment, with a temperature, for example, between 6 and 12 degrees, while variant 1 could be intended for a fresh food room that is intended to create temperatures just above or at freezing point, while variant 3 could be a freezer compartment that is intended to maintain temperatures at -30 degrees or similarly low temperatures. However, the assignment to the various target temperatures can also be implemented differently: If the air flow or fan power is sufficient, variant 2 is used for the coldest compartment because the fan generates the lowest power loss, while variant 3 can be intended for the warmest compartment because the power loss of the auxiliary fan is then less significant.

[0119] The cold storage room is preferably designed as a semi-trailer of a truck, as a container, as a stationary cold storage room, as a refrigerated truck, as a refrigerated wagon or as a mobile cold storage room in a land vehicle, aircraft, watercraft or spacecraft.

[0120] Further embodiments of the present invention, for example according to the first aspect, are set forth below, wherein the reference numerals in parentheses are for illustration purposes only and are not to be understood as limiting. 1. Vaporizer with the following features: a first collector (100) and a second collector (200); a plurality of connectors (300) between the first collector (100) and the second collector (200), wherein the first collector (100), the second collector (200) and the connectors (300) are designed such that they can be flowed through by a working fluid; a fin stack (400) of spaced-apart fins (402, 403) arranged in thermal communication with the connectors (300) and in a stacking direction (401), the fins (402, 403) of the fin stack being configured such that gas can flow in a fin direction (404) between adjacent fins in the fin stack (400); a housing (600) in which the lamella stack (400) is arranged, wherein the housing (600) and the lamella stack (400) are designed such that a gas flow (500) in the housing is varied from a first flow direction in the stack direction (401) to a second flow direction in the lamella direction (404). 2. Evaporator according to Example 1, having the following features: a first ventilation opening (607) in a vicinity of the first collector (100); a second ventilation opening (603) in the housing (600) in a vicinity of the second collector (200), wherein the first ventilation opening (607) or the second ventilation opening (603) is connectable to a fan (700), and wherein a gas flow through the respective other ventilation opening is achievable due to the fan (700), or wherein the slat stack (400) is arranged between the ventilation openings (607, 603) or the second ventilation opening (603) is arranged next to a part of the slat stack (400), or wherein the first ventilation opening (607) is arranged on a side of the first collector (100) which is opposite to another side of the first collector (100) on which the fin stack (400) is arranged, or wherein the first ventilation opening (607) or the second ventilation opening (603) is an active ventilation opening at which a fan is arranged, and the other ventilation opening is a passive ventilation opening through which the gas flow occurs, or wherein both ventilation openings (607, 603) are active ventilation openings, each of these ventilation openings having its own fan arranged at it. 3. Evaporator according to example 1 or 2, in which the fin stack (400) is cuboid-shaped and the housing (600) has a front side (602) and a rear side (601), or wherein the front side (602) and the rear side (601) have a variable distance from the fin stack along the stacking direction (401), so that due to a decreasing distance of the front wall (602) or the rear wall, the gas flow (500) is deflected from the first flow direction in the stacking direction (401) into the second flow direction in the fin direction (404), or wherein the slat stack (400) and the back (601) are attachable to an object, and the front (602) is removable from the back via a closure. 4. Evaporator according to example 3, wherein the front side (602) has a minimum distance from the fin stack (400) at its first location along the fin stack (400) and the rear side (601) has a maximum distance or at least a distance greater than half the maximum distance of the rear side (601) from the fin stack (400) at the first location, or wherein the rear side has a minimum distance from the lamella stack (400) at a second location along the lamella stack (400), and the front side has a maximum distance or at least a distance greater than half a maximum distance of the front side (602) from the lamella stack at the second location. 5. Evaporator according to example 4, where the minimum distance is less than 2 cm. 6. Evaporator according to example 3, 4 or 5, in which there are at least two locations along the fin stack (400) at which the front side has a minimum distance from the fin stack (400), and at least two further locations at which the rear side has a minimum distance from the fin stack, wherein the two locations and the two further locations are arranged in a nested manner along the fin stack. 7. Device according to one of the preceding examples, in which the lamella stack is designed such that the lamellae are arranged substantially parallel to one another and to the first collector or the second collector, so that the lamella direction is arranged substantially perpendicular to the stacking direction and substantially perpendicular to the first collector or the second collector, and in which the housing (600) is designed to have different distances from the lamella stack in cross-section along the stacking direction. 8. Evaporator according to example 7, in which the fins (402, 403) are aligned along the stacking direction (401) and the housing (600) has a zigzag shape in cross section along the stacking direction (401). 9. Evaporator according to one of the preceding examples, in which the housing (600) and the fin stack (400) are arranged relative to one another such that, starting from the second collector (200), the gas flow changes from the first flow direction into the second flow direction, then into the first flow direction, then into the reverse second flow direction and then into the first flow direction. 10. Evaporator according to one of the preceding examples, in which the housing (600) is formed from flat areas which are each connected at an angle to one another in order to achieve the varied gas flow (500). 11. Evaporator according to example 2, further comprising a fan (700) arranged at the active ventilation opening (607) for generating the gas flow (500) in the housing (600). 12. Evaporator according to one of the preceding examples, wherein the housing (600) is at least 130 cm high, at least 60 cm wide or less than 15 cm deep. 13. Evaporator according to example 11, wherein the fan (700) is designed to suck gas out of the housing (600) or to blow gas into the housing, or wherein the fan is designed as a deflection fan to suck gas in the first flow direction and to blow it in another direction, optionally the second flow direction or the reversed second flow direction, into a space in which the evaporator is arranged, wherein the deflection fan further comprises a blow-out nozzle (701), or in which the fan (700) is an axial fan which is designed to convey gas from a rear side to a front side, wherein the axial fan is arranged obliquely in the housing (600) in order to convey the gas from the rear side to the front side at least partially in a direction which is directed away from the normal to an extension of the housing from the first collector (100) to the second collector (200) by an angle which is less than 45 degrees. 14. Evaporator according to one of the preceding examples, comprising a controllable fan (700) and a closure mechanism (800), wherein the closure mechanism (800) is designed to throttle or prevent the gas flow when the fan is deactivated and to allow the gas flow to pass when the fan (700) is activated. 15. Evaporator according to one of the preceding examples, further comprising the following features: a condensate drain connection (604) on the housing (600) in the operating direction of the evaporator below the second collector (200), wherein the housing has a collecting tray (605) in or above which the second collector (200) extends, and wherein the condensate drain connection (604) is attached to the collecting tray (605), and / or wherein the ventilation opening (603) is arranged in the vicinity of the second collector (200) above the collecting tray (605). 16. Cold storage room with the following features: an evaporator according to one of the preceding examples in the cooling chamber; and a primary heat pump circuit located outside the cold storage room and coupled to the evaporator.

[0121] Further embodiments of the present invention, for example according to the second aspect, are set forth below, wherein the reference numerals in parentheses are for illustration purposes only and are not to be understood as limiting. 1. Vaporizer with the following features: a thermal unit (100, 200, 300, 400); a housing (600) in which the thermal unit is housed, the housing having a first ventilation opening (603) and a second ventilation opening (607); a controllable fan (700) configured to generate, in an activated state, a gas flow (500) through the first ventilation opening (603) of the housing and the second ventilation opening (607) of the housing; and a closure mechanism (800) configured to throttle or prevent the gas flow (500) when the fan (700) is deactivated and to allow the gas flow (500) to pass when the fan (700) is activated. 2. Evaporator according to example 1, in which the closure mechanism (800) is designed as a passive closure mechanism in order to release a flow space (801) in the housing (600) for the gas flow (500) due to the activity of the fan when the fan is in the activated state, and to close the flow space when the fan (700) transitions to the deactivated state of the fan (700) due to the decreasing gas flow (500). 3. Evaporator according to example 1 or 2, in which, in an operating direction of the evaporator, the controllable fan (700) is attached to an upper end of the housing (600), wherein one or more pivotable flaps (802, 803) are arranged below the fan, which in the deactivated state of the controllable fan (700) closes or closes a gas passage through the housing (600) due to gravity, and which in the activated state of the controllable fan (700) allows or allow the gas passage through the housing (600) by being pivoted upwards. 4. Evaporator according to one of the preceding examples, wherein the thermal unit comprises a first header (100), a second header (200) and a plurality of connectors (300) between the first header (100) and the second header (200), wherein the first header (100) is formed as an elongated tube extending along a width direction of the housing and arranged near the first ventilation opening (607), wherein the connectors (300) extend in a height direction of the housing (600), and wherein the closure mechanism has at least one pivotable flap which extends in a width direction of the housing (600) and is pivotally mounted on the housing, and which rests on the first collector in the deactivated state of the fan (700) and opens in the direction of the first ventilation opening (607) in an activated state of the fan. 5. Evaporator according to example 3 or 4, in which the one or more flaps is / are formed flat with a flap surface, wherein on a first side of the flap surface a first hinge part (804) is arranged, which engages with a second hinge part that is arranged on the housing (600), wherein the first side of the flap surface is directed towards the housing in the open state of the flap, and the second side of the flap surface is directed towards the gas flow. 6. Evaporator according to example 4 or 5, in which an interface for the fan (700) is arranged at the first ventilation opening (607), and a flow space (801) is arranged between the interface and the thermal unit, in which two pivotable flaps (802, 803) are arranged, wherein in the flow space a first flap is attached to a first side of the housing (600) and a second flap is attached to a second opposite side of the housing, wherein the first collector (100) extends through the flow space (801) and both flaps in the flow space are deflectable in the direction of the interface and, when the fan (700) is activated, substantially bear against the housing (600) and, when the fan is deactivated, bear against the first collector (100). 7. Tempering device with the following features: a controllable primary circuit with a compressor (69), a heat exchanger (2, 7) and a throttle (3, 7b); the evaporator according to one of Examples 1 to 6, wherein the thermal unit of the evaporator has a vapor connection and a liquid connection coupled to the controllable primary circuit; and a controller (850) for controlling the controllable primary circuit in a cooling mode for the evaporator or in a defrost mode for the evaporator, wherein the controller is designed to activate the fan of the evaporator in the cooling mode and to deactivate the fan in the defrost mode, so that in the defrost mode the closure mechanism (800) throttles or deactivates the gas flow. 8. Temperature control device according to Example 7, in which the steam connection and the liquid connection are coupled to a heat exchanger (2, 7), to which the primary circuit is also coupled, wherein the heat exchanger (2, 7) in the primary circuit acts as a primary evaporator in the cooling mode, such that due to secondary vapor from the evaporator being supplied to the heat exchanger via the vapor line, the primary liquid is evaporated in the heat exchanger, and the secondary vapor is condensed in the heat exchanger (2, 7) and is conducted from the heat exchanger to the evaporator via the liquid line, and wherein the heat exchanger (2, 7) in the primary circuit acts as a primary condenser in the defrost mode, such that due to the condensation of primary vapor, secondary liquid is evaporated in the heat exchanger and the secondary vapor is conducted via the vapor line into the thermal unit of the evaporator to condense there and heat the thermal unit, thereby defrosting the thermal unit, with condensed secondary vapor being returned to the heat exchanger via the liquid line. 9. Temperature control device according to example 7 or 8, wherein the controller (850) is designed to effect a circuit reversal in the controllable primary circuit in order to change from the cooling mode to the defrosting mode or vice versa. 10. Temperature control device according to one of examples 7 to 9, wherein the evaporator has a pump (8) arranged in the liquid line (905), and wherein the controller (850) is designed to control the pump (8) in the defrost mode so that liquid is conveyed from the evaporator to the heat exchanger (2, 7). 11. Temperature control device according to one of examples 7 to 10, wherein the evaporator is designed in a cooling mode to operate according to the thermosiphon principle without pumping action. 12. Tempering device according to one of examples 7 to 11, which further has the following features: a further evaporator according to one of examples 1 to 7 with a further steam connection and a further liquid connection, wherein the steam connection of the evaporator is connected to the further steam connection of the further evaporator via a line (908), and wherein the liquid connection of the evaporator is connected to the further liquid connection of the further evaporator via a pipe (906), and wherein both steam connections and both liquid connections of the evaporator and the further evaporator are connected to the heat exchanger (2, 7) of the primary circuit. 13. Temperature control device according to example 12, wherein the evaporator is arranged in a first space (901) and the further evaporator is arranged in a second space (902), wherein the first space has a first temperature sensor (911) and the second space has a second temperature sensor (912). 14. Temperature control device according to example 13, in which the controller (850) is designed to activate the fan (700) of the evaporator when the first temperature sensor (911) detects a first temperature that is higher than a first target temperature for the first space (901), and to activate the fan (700) of the second space when the second temperature sensor (912) detects a second temperature that is higher than a second target temperature for the second space (902). 15. The temperature control device according to one of examples 13 or 14, wherein the controller (850) is configured to deactivate the first fan when the first temperature is less than the first target temperature, and to deactivate the second fan when the second temperature is less than the second target temperature. 16. Temperature control device according to example 14 or 15, wherein the first target temperature differs from the second target temperature. 17. Temperature control device according to one of examples 14 to 16, in which the controller (850) is designed to control the primary circuit with regard to its cooling capacity, so that depending on which temperature sensor from which room supplies an actual temperature that is higher than a target temperature for the room, the heat exchanger (2, 7) is cooled such that the target temperature can be reached in the room. 18. Temperature control device according to one of examples 14 to 17, in which the controller (850) is designed to operate the primary circuit in such a way that the heat exchanger is cooled so that the low target temperature can be reached when a temperature sensor from a room with a low target temperature supplies an actual temperature that is too high, and to operate the primary circuit in such a way that the heat exchanger (2, 7) is cooled less when a temperature sensor from another room with a higher target temperature supplies an actual temperature that is too high. 19. Temperature control device according to one of examples 12 to 18, in which the thermal unit of the evaporator has a first collector (100) and a second collector (200), in which the thermal unit of the further evaporator has a third collector and a fourth collector, wherein a first connection of the first collector represents the steam connection and a second connection of the first collector is connected to a first connection of the third collector, wherein a first port of the second collector represents the liquid port and a second port of the second collector is connected to a first port of the fourth collector. 20. Temperature control device according to one of examples 12 to 19, wherein the compressor in the first space has a first fan (700), wherein the further compressor in the second space has a second fan which has a lower fan power than the first fan, wherein a target temperature in the second space is higher than a target temperature in the first space, or wherein a lower fan power is required in the second space than in the first space. 21. The temperature control device according to example 20, wherein the fan is a reversible fan and has an outlet nozzle (701), and wherein the further fan is an axial fan. 22. Cold storage room with the following features: a tempering device according to one of examples 7 to 21; wherein the evaporator is arranged in the cooling chamber, and wherein the controllable primary circuit is arranged outside the cooling chamber. QUOTES CONTAINED IN THE DESCRIPTION

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

[0000] EP 2022 / 076419

[0008] DE 102023202885.9 [0018, 0053] FROM 10202302885.9

[0062]

Claims

[1] Cold storage room with the following features: an evaporator arranged on a wall (970) of the cooling chamber (900) and having a fan (700) at one end of a housing (600) of the evaporator, wherein the fan (700) is designed to convey cooled air in a ventilation direction (950) into the cooling chamber; and a support fan (750) arranged in the cooling chamber (900) to suck in at least a portion (951, 952) of the cooled air conveyed by the fan (700) and convey it further into the cooling chamber. [2] Cooling room according to claim 1, wherein the auxiliary fan (750) is designed to suck in air in a suction direction and to convey it in a blow-out direction (953) which is different from the suction direction, the blow-out direction (953) being substantially the same as or parallel to the conveying direction of the fan (700). [3] A refrigeration chamber according to claim 1 or 2, further comprising a ceiling niche (60), wherein the evaporator is arranged below the ceiling niche on a wall (970) of the refrigeration chamber, and wherein the auxiliary fan (750) is arranged adjacent to the niche (60) away from the evaporator. [4] Cooling chamber according to claim 3, comprising a controllable primary circuit in a primary housing (61), wherein the primary housing (61) is arranged outside the cooling chamber in the niche (60). [5] Cooling chamber according to claim 4, wherein the evaporator comprises a thermal unit in the housing (600), wherein the primary circuit comprises a heat exchanger (2, 7) which is thermally coupled to the evaporator, and wherein the heat exchanger (2, 7) is arranged in the primary housing (61) opposite the auxiliary fan (750). [6] Cooling chamber according to claim 5, wherein the heat exchanger (2, 7) has a primary side with two primary connections for a primary fluid and a secondary side with two secondary connections for a secondary fluid, wherein a first secondary connection is connected to a vapor outlet of the evaporator via a vapor line (904), and a second secondary outlet is connected to a liquid outlet of the evaporator via a liquid line (905), wherein the vapor outlet is arranged at the top of the thermal unit and the liquid outlet is arranged at the bottom of the thermal unit. [7] Cooling chamber according to claim 5 or 6, wherein the heat exchanger (2, 7) is designed as a plate heat exchanger and is arranged upright in the primary housing (61), wherein a first primary connection is arranged at the top of the heat exchanger and is designed to conduct vaporous primary fluid and a second primary connection is arranged at the bottom of the heat exchanger (2, 7) and is designed to conduct liquid primary fluid. [8] Cooling chamber according to claim 6 or 7, wherein the first secondary connection of the heat exchanger (2, 7) is connected to the vapor outlet of the evaporator via a vapor line (904), and the second secondary outlet of the heat exchanger (2, 7) is connected to the liquid outlet of the evaporator via a liquid line (905), wherein the vapor line (904) and the liquid line (905) each have a length, wherein at least one half of the respective length is arranged in a wall of the cooling chamber or within the cooling chamber on the wall of the cooling chamber. [9] A cooling chamber according to any one of claims 6 to 8, comprising a front wall (970), a niche floor (971) of the ceiling niche (60) which extends substantially horizontally and adjoins the front wall (970), a side wall (982) of the ceiling niche (60) which adjoins the floor (961) of the ceiling niche and extends substantially vertically, and a ceiling (983) which adjoins the side wall (982) of the niche and extends substantially horizontally, wherein the support fan (750) is mounted in the cooling chamber on the ceiling (983) and is mounted at a distance from the side wall (982) of the ceiling niche (60). [10] Cooling chamber according to claim 8 or 9, wherein the front wall (970), the niche floor (971), the side wall (982) of the niche and the ceiling (983) have an outer skin (970) and an inner skin (971), wherein the vapor line penetrates the inner skin near the vapor outlet of the evaporator, runs in the front wall, the niche floor and the side wall between the outer skin and the inner skin and penetrates the outer skin in the side wall (982), and wherein the liquid line penetrates the inner skin of the front wall near the liquid connection of the evaporator and runs in the front wall, the niche floor and optionally the niche side wall between the inner skin and the outer skin and penetrates the outer skin of the niche floor or the side wall. [11] Cooling chamber according to one of claims 4 to 10, wherein the primary housing (61) has one or more air inlet openings (66) on a front side arranged above the front wall, in which the primary circuit comprises a liquid-air heat exchanger (65) which is arranged obliquely in the primary housing (61), wherein a front edge of the liquid-air heat exchanger (65) is arranged above the one or more air inlet openings (66) and wherein the heat exchanger (2, 7) is arranged on an opposite wall with respect to the air inlet openings (66) of the primary housing, and wherein the primary housing (61) has one or more air outlet openings on an upper wall. [12] Cooling chamber according to claim 11, in which at least the liquid-air heat exchanger (65) and the heat exchanger as well as a compressor and an expansion valve for the primary circuit are arranged, or in which a fan (70) is arranged below the one or more air outlet openings (67), or in which a control is designed in the primary housing in order to change a conveying direction of the compressor for a circuit reversal of the primary heat pump circuit, or in order to control one or more switching devices (35a, 35b) in order to change connections of the heat exchanger (2, 7) and the liquid-air heat exchanger to the compressor or the expansion element for a circuit reversal. [13] A refrigerating chamber according to any one of claims 1 to 12, comprising two or more compartments (901, 902, 903), wherein two adjacent compartments are separated by a partition wall, wherein the evaporator and the auxiliary fan (750) are arranged in a first compartment, wherein a further evaporator with a further fan is arranged in a second compartment, wherein no auxiliary fan (750) is arranged in the second compartment, wherein a target temperature in the second compartment or a ventilation requirement in the second compartment is different from a target temperature in the first compartment or a ventilation requirement in the first compartment. [14] Cooling chamber according to claim 13, wherein the further fan of the further evaporator is an axial fan or a deflection fan with a blow-out nozzle (701), or the fan of the evaporator is an axial fan, or the fan is a deflection fan with a blow-out nozzle (701). [15] Cooling room according to claim 13 or 14, wherein three compartments are provided, wherein the first compartment comprises the evaporator and the deflection fan (750), wherein the second compartment comprises the further evaporator with the further fan, which is designed as an axial fan, wherein a third compartment has a third evaporator with a third fan, which is designed as a deflection fan with a blow-out nozzle (701), wherein a first target temperature in the first compartment is different from a second target temperature in the second compartment, or a second target temperature in the second compartment is different from a third target temperature in the third compartment, or wherein a ventilation requirement in the first compartment is higher than a ventilation requirement in the second compartment, or wherein a ventilation requirement in the third compartment is higher than a ventilation requirement in the second compartment. [16] A refrigerated chamber according to any one of the preceding claims, which is designed as a semi-trailer of a lorry, as a container, as a stationary refrigerated chamber, as a refrigerated truck, as a refrigerated wagon or as a mobile refrigerated chamber in a land vehicle, aircraft, watercraft or spacecraft.

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