Mobile chilled-transport device, motor vehicle or vehicle trailer therewith and use thereof

Abstract

The invention relates to a mobile chilled-transport device (1) having a cooling chamber (10), a refrigerating machine (21) and a power generator (30), wherein the cooling chamber (10) is temperature-controlled by the refrigerating machine (21), wherein the power generator (30) is connected to the refrigerating machine (21) to supply it with power, wherein the refrigerating machine (21) has a heat pump circuit (23) with a low-pressure side (23A) and a pressure side (23B), and wherein the cooling chamber (10) is part of the low-pressure side (23A) of the heat pump circuit (23). The invention also relates to a motor vehicle or a vehicle trailer (100) having such a mobile chilled-transport device (1) and to the use of a mobile chilled-transport device (1) or of such a motor vehicle or vehicle trailer (100) for transporting goods or medicaments.

Description

[0001] Mobile refrigerated transport device, motor vehicle or vehicle trailer herewith and their use

[0002] The invention relates to a refrigerated transport device according to claim 1, a motor vehicle or a vehicle trailer therewith according to claim 30 and the use thereof according to claim 31.

[0003] State-of-the-art refrigerated transport vehicles, particularly trucks, trailers, and semi-trailers, feature refrigerated compartments equipped with air conditioning systems. These systems achieve minimum temperatures of down to -25°C. Goods requiring colder storage cannot be transported in these vehicles, at least not without additional measures such as the use of liquid nitrogen or dry ice.

[0004] Goods requiring lower temperatures are therefore cooled and transported using dry ice or liquid nitrogen in special containers. The disadvantage of this is the small transport volume, although dry ice can provide temperatures down to -78.5 °C, and liquid nitrogen (LN2) down to -196 °C. A further disadvantage is the limited transport time, which depends, for example, on the outside temperature and the number of transfers. Other disadvantages of the cooling media used are the potential for freezer burn of deeper tissue upon physical contact, the risk of suffocation due to the formation of carbon dioxide with dry ice, or the loss of oxygen with liquid nitrogen. With liquid nitrogen, there is also a risk of overpressure or explosion, and material damage, e.g. due to embrittlement and thermal stress. In practice, therefore, only special vehicles are considered suitable for transporting dry ice and liquid nitrogen.In air and sea transport, dry ice must also be labeled as dangerous goods.

[0005] The object of the invention is to overcome the disadvantages of the prior art and to provide solutions with which very deep-frozen goods can be transported and stored in large quantities in a convenient, safe, environmentally friendly manner and, if possible, without classification as hazardous substances.

[0006] Main features of the invention are defined in claims 1, 30, and 31. Embodiments are the subject of claims 2 to 29.

[0007] The invention relates to a mobile refrigerated transport device with a cooling chamber, a refrigeration machine and a power generator, wherein the cooling chamber is temperature-controlled or temperature-adjustable by the refrigeration machine (in particular freely), wherein the power generator is connected to the refrigeration machine for power supply, wherein the refrigeration machine has a heat pump circuit with a low-pressure side and a pressure side, and wherein the cooling chamber is part of the low-pressure side of the heat pump circuit.

[0008] This provides a highly flexible storage space with a wide cooling temperature range that operates without refrigerants, particularly both as a direct coolant such as dry ice and nitrogen, and without refrigerants in the heat pump circuit. A heat pump circuit that operates with the air in the cooling chamber itself is particularly suitable for achieving very low temperatures in the cooling chamber. Depending on the operating concept and control circuits, very precise temperatures and / or freely adjustable temperatures within the cooling machine's performance range can also be achieved in the cooling chamber.

[0009] The pharmaceutical industry in particular can benefit from this solution, as the invention enables additional storage space to be provided at short notice and larger product quantities, such as mRNA vaccines, enzymes, and other medical products, to be stored and transported. This is particularly safe for users and the environment, as the low-temperature storage space requires only the storage room air (refrigerant), electricity, and ambient air (cooling the heat sink), for example to achieve temperatures as low as -100°C. The solution also offers advantages for fish and seafood processing, as, for example, exclusive fish can be transported at approximately -60°C. According to the invention, neither dry ice nor liquid nitrogen is required, improving the carbon footprint. Furthermore, larger transport quantities and longer transport routes are possible.

[0010] The refrigerated transport device can even be used as a temporary storage space.

[0011] The low-pressure side and the pressure side of the heat pump circuit are typically separated from each other by a compressor, in particular a turbo-compressor, and an expansion device, in particular a turbo-expander.

[0012] The pressure on the low-pressure side should exactly match, or at least essentially match, the pressure inside the cooling chamber. Ambient pressure is ideal inside the cooling chamber. This eliminates the need for the cooling chamber to accommodate a pressure gradient, and access points can be opened easily.

[0013] According to a special design, the refrigeration machine for controlling the temperature of the cooling chamber is designed according to the open Joule cycle or the reverse Brayton cycle. These processes enable very low temperatures using air as the refrigerant.

[0014] Furthermore, the refrigeration unit, especially the pressure side of the heat pump circuit, should have a heat exchanger as a temperature sink that communicates with the ambient air outside the cooling chamber. This allows energy to be released into the environment.

[0015] A suitable design involves blowing the ambient air past the heat exchanger. This allows for a high volume flow. The heat exchanger is preferably located within a housing of the refrigeration unit. This protects it. The ambient air can then be directed to the heat exchanger via supply and exhaust air ducts.

[0016] In particular, and especially because the cooling chamber is part of the low-pressure side of the heat pump circuit, the cooling chamber air from the cooling chamber forms the compression medium, or refrigerant, in the heat pump circuit. This is environmentally friendly and offers a high level of occupational safety.

[0017] In a more detailed embodiment, the refrigeration machine is provided with an electric drive that drives a turbo-expander and a turbo-compressor. This allows a high pressure on the pressure side to be achieved while simultaneously maintaining the low-pressure side essentially at ambient pressure. The turbo-expander and turbo-compressor each comprise a turbo-turbine. The turbo-turbines simultaneously enable a high volume flow, so that the entire volume of the cooling chamber is circulated sufficiently for cooling and temperature homogenization. The turbo-expander forms the expansion device, and the turbo-compressor the compressor. A piston compressor as

[0018] Compressors and / or an expansion valve as an expansion device are not required.

[0019] Preferably, a turbo expander wheel of the turbo expander and a turbo compressor wheel of the turbo compressor are mounted on or on a continuous shaft. The drive, particularly an electric motor, can drive the shaft between them. Preferably, the entire shaft, including the turbo compressor wheel and turbo expander wheel, is mounted on air bearings. This eliminates contact points with the housing, thus minimizing vibrations and noise. This also allows compliance with noise emission regulations during transport. Furthermore, the air bearings keep the refrigeration machine free of oil.

[0020] The electric drive is preferably air-cooled. This can be achieved with low weight. This can be achieved by direct air cooling of the electric drive. Optionally, a cooling circuit with a heat exchanger can also be used to dissipate heat into the environment. Such a cooling circuit should, in particular, be able to operate independently, i.e., without external connections, and, in particular, require only the power of the generator.

[0021] Furthermore, there is the option of having a recuperator in the chiller, with which the cooling chamber air exiting the cooling chamber absorbs energy from the cold air returned to the cooling chamber, particularly before the cold air is expanded, i.e. still on the pressure side of the heat pump circuit. This increases the efficiency of the chiller, because the outlet air from the cooling chamber is preheated before compression, while the returned air releases energy and thus cools down. The recuperator should be located on the pressure side behind the heat exchanger (especially a gas cooler), especially so that the temperature gradient in the recuperator is reduced by the energy release in the heat exchanger. The recuperator is, in a sense, an air-

[0022] An air heat exchanger between two pipe sections of the heat pump circuit, a so-called internal heat exchanger. The heat exchanger or gas cooler is different: This acts between the pressure side of the heat pump circuit and the ambient air.

[0023] The air heat pump circuit preferably comprises the following stations in the order listed: Air is drawn in from the cooling chamber via the recuperator to the turbo compressor. The turbo compressor then compresses the drawn-in air, e.g., to 1 bar above ambient pressure, which heats the air. The thus heated air is passed to the heat sink, specifically the heat exchanger or gas cooler, where the heated air releases energy to the ambient air. From here, the air is passed through the recuperator again, where, after cooling in the heat sink, it releases further energy, which is transferred to the drawn-in air in the recuperator. The cold drawn-in air from the cooling chamber is thereby heated, and the still-compressed air on the pressure side becomes colder.After the compressed air has been cooled twice (first cooling in the heat sink against the environment; second cooling in the recuperator against the cold air sucked in from the cooling chamber), expansion follows via the turbo expander, from where the relaxed, deep-cold air is fed back into the cooling chamber.

[0024] This process is therefore continuous; the refrigerant is the air from the cooling chamber itself, and the heat sink is the environment. Therefore, it is preferable for the refrigeration machine to be designed without refrigerant (except for the air from the cooling chamber).

[0025] For transport or storage of goods with corresponding requirements, the refrigeration machine is preferably designed or configured to achieve a temperature in the cooling chamber of at least -30 °C, and preferably down to at least -60 °C, and particularly preferably down to at least -100 °C.

[0026] Furthermore, it is advantageous if the mobile refrigerated transport device has a dehumidification unit (also referred to as a snowcatcher unit) for the cooling chamber air, which is designed in particular to reduce the humidity in the cooling chamber and / or prevent icing of the refrigeration unit. This prevents icing in the cooling chamber, as well as frostbite of tissue upon entering the cooling chamber. The dehumidification unit can be part of the refrigeration unit.

[0027] Expansion: Cryogenic air is preferably introduced into the cooling chamber via a ceiling duct, and the air flowing in the opposite direction to the compressor is drawn in via the filter candles of the dehumidification unit. Humidity can accumulate on the filter candles in the form of snow, ice, dirt particles, and CO2 crystals. Once the filter candles are loaded with snow, etc. (e.g., measured by a pressure differential sensor on the filter candles), the agglomerated snow, etc., can be released, for example, by applying a pressure surge to the filter candles.

[0028] The fallen snow, etc., then preferably falls into a discharge device, where it is transported out of the cooling chamber. There it can then melt, preferably while still in the mobile refrigerated transport device. This prevents snow and ice from being spread, for example, onto roads.

[0029] The chiller should be located at least substantially or entirely outside the cooling chamber. This minimizes heat input into the cooling chamber. The chiller should be located in a machine chamber of the mobile refrigerated transport device, with the machine chamber temperature controlled by an air conditioning system. This keeps critical environmental parameters, such as excessive heat from sunlight, away from the chiller and any control units in the machine chamber. This prevents overheating of electrical components, motors, fans, lighting, etc. Furthermore, dirt can be kept away from these components and the chiller.

[0030] The air conditioning system preferably operates as a heat pump based on the heat pump principle. A heat exchanger of this heat pump communicates directly with the interior of the machine room for heat exchange. In particular, this heat exchanger should be located on the inside of the machine room. Depending on the outside temperature, the temperature in the machine room can be adjusted by the ambient temperature or with the assistance of the air conditioning system's heat pump.

[0031] In a specific embodiment, the air conditioning device is designed to maintain the machine chamber within a specific temperature range, and the refrigeration machine is designed to cool the cooling chamber to a temperature lower than the temperature range in the machine chamber. Thus, air conditioning is provided for the refrigeration machine and any other technical components in the machine chamber, which are thereby protected from external influences such as heat, humidity, and dirt.

[0032] It proves to be advantageous if the air conditioning device is designed or configured to achieve a target temperature in the temperature range in the machine chamber between 5 °C and 60 °C, preferably between 10 °C and 40 °C, more preferably between 10 °C and 30 °C and particularly preferably between 15 °C and 25 °C, in particular as soon as the temperature exceeds a threshold value, for example 25 °C.

[0033] Furthermore, it is preferable if the air conditioning system is powered by the generator. This provides greater autonomy for the mobile refrigerated transport device. In particular, a tractor unit can be separated from a trailer carrying the refrigerated transport device, as its on-board power is not required to operate the air conditioning system.

[0034] In general, the mobile refrigerated transport device should have one or more independent power grids for its autonomous operation. The air conditioning system is preferably located at least substantially (e.g., with the exception of a heat exchanger) or entirely outside the machine chamber and outside the cooling chamber (preferably with all heat-emitting components outside). This allows its waste heat to be easily dissipated into the environment.

[0035] In practical terms, it makes sense to locate the engine compartment between the air conditioning unit and the cooling compartment. This creates a gradual temperature gradient. In a motor vehicle or trailer, the first air conditioning unit should be located at the front. The front area is exposed to airflow and typically contains vehicle-side connections. The engine compartment follows at the front of the vehicle. This allows loading and unloading of the cooling compartment from the rear of the vehicle, for example, at unloading ramps.

[0036] For efficient temperature control of the machine chamber, the outer walls of the machine chamber should be thermally insulated with insulation material.

[0037] Due to the high cost of the refrigeration unit, it should be mounted in the machine chamber, isolated from the outside, especially the exterior walls. This protects it from damage in the event of an accident.

[0038] Optionally, the cold storage chamber features an access lock, which provides a gap between two individual doors. This defines how much warm ambient air and moisture is exchanged with the deep-cold cold storage air when entering the cold storage chamber. This has a significant impact on energy efficiency. It also reduces temporary temperature increases in the cold storage chamber upon entry.

[0039] The access lock can also optionally be equipped with a defrosting device. In particular, the door to the cooling chamber can be equipped with a door frame or door seal heater. This prevents the door from freezing.

[0040] For efficient operation, the outer walls of the access lock should be thermally insulated. This creates a gradual thermal gradient between the ambient air and the cooling chamber, preventing very warm ambient air from entering the cooling chamber.

[0041] To achieve and maintain very low temperatures in the cooling chamber, the outer walls of the cooling chamber should be thermally insulated with insulating material. The thermal transmittance of the cooling chamber walls should be lower (better) than that of the machine chamber, and preferably also than that of the access lock walls. The insulating material preferably has a thermal transmittance of less than 22 W / (m 2 K). The insulation material is preferably made of polyurethane (e.g., CORAFOAM® HPT 50 from DU NA CORRADINI SpA). The insulation material should be at least 20 cm thick.

[0042] The generator preferably has a first and a second generator unit, with the power supply being provided redundantly by the first and second generator units by means of a safety circuit. This increases operational reliability because the power supply is ensured even if one of the generator units fails. The generator units can be diesel generators, for example. Fueling a diesel generator during operation is generally not permitted. During fueling, the other of the two generator units can then ensure the power supply. Separate tanks are preferably provided for the generator units for this purpose.

[0043] The generator should be located outside the cooling chamber and, preferably, outside the engine room as well. This keeps waste heat and exhaust gases away from both chambers.

[0044] In practice, it is advantageous to position the generator lower than the cooling chamber and, preferably, also lower than the engine compartment. This could be, for example, below the loading area of ​​a motor vehicle or trailer. There, the generator is easily accessible for the operator and for service work, and does not reduce the available cargo space.

[0045] Optionally, the mobile refrigerated transport device can be equipped with a power connection for supplying electricity from the ground, with the ground power supply preferably being protected by the generator via a safety circuit. This allows the mobile refrigerated transport device to be set up in a location where the generator cannot or may not be used without prior notice, for example, because it generates exhaust fumes or noise. Nevertheless, the generator can maintain the temperature in the cold storage room even in the event of a power failure.

[0046] The invention achieves particular advantages when the refrigerated transport device is a vehicle body and / or is at least partially integrated into a vehicle body. This enables mobile and flexible use. A vehicle body also includes containers such as those used in combined air, sea, rail and road transport. In particular, the cooling chamber should be arranged in the vehicle body. The cooling chamber, including its walls, preferably takes up at least 50% of the floor space of the vehicle body. This provides a relatively large cargo space for extremely low-temperature goods. The vehicle body can, in particular, be essentially divided into the cooling chamber and the machine chamber. The power generator can, but does not have to, be part of the vehicle body. For example, it can also be located underneath the vehicle body.

[0047] Due to the sensitivity of the goods being transported, an optional addition is available: the refrigerated transport device can be equipped with a monitoring device that outputs at least one operating status to a receiver, e.g., the location, the temperature in the machine compartment, the temperature in the cooling chamber, the operating status of the air conditioning system, the operating status of the refrigeration machine, the operating status of the generator, the fill level of energy sources such as batteries or tanks, the open status of access points to the refrigerated transport device, and the status of the dehumidification unit. This allows for automated monitoring of the cargo, for example, even remotely.

[0048] The monitoring device can be part of a control unit for controlling the mobile refrigerated transport device. The receiver can be, for example, a driver or a control center. The monitoring device is preferably designed to output a transport log. This can be used to verify the unbroken cold chain. More preferably, the monitoring device has a wireless data interface, e.g., a mobile communications interface. This enables remote monitoring. Furthermore, the monitoring device can output an alarm signal in the event of deviations from target conditions. This can be done, for example, by warning tones, service calls, and the like. Thus, the monitoring device can also, in particular, include an anti-theft alarm system. Finally, it is advisable to certify the refrigerated transport device according to GDP (=Good Distribution Practices).

[0049] The invention also relates to a motor vehicle or trailer with a mobile refrigerated transport device as described above and below. This device allows for the convenient, safe, environmentally friendly transport and storage of very deep-frozen goods in large quantities, without the need for hazardous substances classification. The motor vehicle or trailer should have vehicle wheels.

[0050] Finally, the invention also relates to the use of a mobile refrigerated transport device as described above and below, or of a motor vehicle or vehicle trailer as described above and below, for transporting goods or medications. This provides the advantage of a self-sufficient transport device for large quantities of goods and with a highly flexible temperature in the cooling chamber, which is environmentally friendly, offers a high level of occupational safety, and can also temporarily store goods over extended periods.

[0051] Further features, details, and advantages of the invention will become apparent from the wording of the claims and from the following description of exemplary embodiments with reference to the drawings. They show:

[0052] Fig. 1 is a schematic horizontal section of a refrigerated transport device;

[0053] Fig. 2 is a perspective side view of a refrigerated transport device; and Fig. 3 is a functional diagram of the refrigerated transport device.

[0054] Fig. 1 shows a schematic horizontal section through a mobile refrigerated transport device 1, which is partially integrated into a vehicle body 107. The vehicle body 107 is part of a vehicle trailer 100, in particular a semi-trailer. This has vehicle wheels 101, here in particular six wheels, and a trailer coupling 102, in particular a kingpin. A loading area door 103 is formed at the rear end of the vehicle body 107. Fig. 2 shows a perspective view of such a refrigerated transport device 1, wherein a tractor 106 is connected to the vehicle trailer 100 via the trailer coupling 102. The same reference numerals therefore refer to the same components in Figs. 1 and 2, which are therefore described together.

[0055] The refrigerated transport device 1 according to FIGS. 1 and 2 has a cooling chamber 10 and a machine chamber 20 in the vehicle body 107. These two chambers 10, 20 occupy a large part of the floor space of the vehicle trailer 100. The machine chamber 20 is temperature-controlled by an air conditioning device 11. This air conditioning device 11 is located at the front of the vehicle trailer 100 and operates according to the heat pump principle. A heat exchanger of this heat pump is connected to the interior of the machine chamber 20 for heat exchange. In particular, this heat exchanger is arranged on the inside of the machine chamber 20 or at least with direct access thereto. In addition, the air conditioning device 11 can direct ambient air LU into the machine chamber 20 for temperature control.Thus, the air conditioning device 11 is located at least substantially, namely with the maximum exception of the one heat exchanger, outside the machine chamber 20 and completely outside the cooling chamber 10. The air conditioning device 11 is designed such that it caps or maintains a temperature T1 in the machine chamber 20 (+ / -5 degrees), wherein the temperature T1 can be defined, for example, to a value between 15 °C and 25 °C. The temperature T1 is below the critical temperature for the operation of a refrigeration machine 21, which is arranged in the machine chamber 20 for tempering the actual cooling chamber 10.

[0056] The refrigeration machine 21 is designed to cool the cooling chamber 10 to a temperature T2 which is lower than the first temperature T1. The temperature T2 to be achieved with the refrigeration machine 21 is at least -30 °C, preferably up to -100 °C.

[0057] The refrigeration machine 21 is designed as an air-circulation refrigeration machine, which regulates the temperature of the cooling chamber 10. This refrigeration machine 21 is located as a plug-and-play unit within the machine chamber 20. Furthermore, the refrigeration machine 21 has a dehumidification or snow catcher unit, which can be located within the plug-and-play unit, outside this unit, or within the cooling chamber 10.

[0058] The refrigeration machine 21, designed as an air-circuit refrigeration machine, operates with the cooling chamber air LW as the compression medium or refrigerant. For this purpose, the refrigeration machine 21 has a heat pump circuit 23 according to the schematic diagram in Fig. 3, which has a low-pressure side 23A and a pressure side 23B. The cooling chamber 10 is part of the low-pressure side 23A of the heat pump circuit 23. The refrigeration machine 21 is designed to control the temperature of the cooling chamber 10 according to the open Joule cycle or the reverse Brayton cycle. The pressure on the low-pressure side 23A corresponds at least substantially to the ambient pressure outside the cooling chamber 10 or the entire refrigerated transport device 1.

[0059] According to Fig. 3, the refrigeration machine 21, namely the pressure side 23B of the heat pump circuit 23, has a heat exchanger 22 as a temperature sink, which communicates with ambient air LU outside the cooling chamber 10. The heat exchanger 22 is located within the refrigeration machine 21. The ambient air LU is blown past the heat exchanger 22 by a fan. The airflow of the ambient air LU can also be assisted by airflow, if appropriately designed.

[0060] Furthermore, the low-pressure side 23A and the pressure side 23B of the heat pump circuit 23 are separated from each other by a compressor and an expansion device. For this purpose, the refrigeration machine 21 has an air-cooled, electric drive 28, which drives a turbo expander 28A as an expansion device and a turbo compressor 28B as a compressor. The turbo expander 28A and the turbo compressor 28B each constitute a turbo turbine. At one end of a continuous shaft 28C, a turbo expander wheel of the turbo expander 28A is located, and at the other end, a turbo compressor wheel of the turbo compressor 28B is located. The drive 28, in particular an electric motor, is located between them and drives the shaft 28C, including the turbo expander wheel and the turbo compressor wheel.The entire shaft 28c with turbo compressor wheel and turbo expander wheel should be designed with air bearings and therefore have no contact points with the housing during operation, at least in the circumferential direction, and preferably also in the longitudinal direction of the shaft 28C.

[0061] In addition, the refrigeration machine 20 has a recuperator 29. The recuperator 29 is located in the heat pump circuit 23, on the one hand in the pressure side 23B between the heat exchanger 22 and the turbo expander 28A, and on the other hand in the low-pressure side 23B between the cooling chamber 10 and the turbo compressor 28B. As a result, the recuperator 29 transfers energy from the cold air LK returned to the cooling chamber 10 to the cooling chamber air LW exiting the cooling chamber 10. This occurs in particular in the elevated temperature range of the returning cold air LK before expansion in the turbo expander 28A. The recuperator 29 is therefore an air-to-air heat exchanger between two line sections of the heat pump circuit 23, namely between the low-pressure side 23A and the pressure side 23B. The heat exchanger 22, on the other hand, is an air-to-air heat exchanger that acts between the pressure side 23B of the heat pump circuit 23 and the ambient air LU.

[0062] The heat pump circuit 23 of the cooling chamber air LW comprises the following stations:

[0063] - Suction of cooling chamber air LW from the cooling chamber 10 via the recuperator 29 to the turbo compressor 28B, including preheating of the cooling chamber air LW in the recuperator;

[0064] Compressing the cooling chamber air LW sucked in and preheated in the recuperator 29 with the turbo compressor 28B, whereby the cooling chamber air LW is heated on the pressure side 23B in front of the heat exchanger 22;

[0065] Directing the thus heated cooling chamber air LW to the heat exchanger 22 as a heat sink; First cooling of the heated cooling chamber air LW in the heat exchanger 22 by transferring energy to the ambient air LU;

[0066] Directing the cooled cooling chamber air LW to the recuperator 29;

[0067] Second cooling of the heated cooling chamber air LW in the recuperator 29 by transferring energy to the cooling chamber air LW on the low-pressure side 23A, thereby preheating it;

[0068] Directing the twice-cooled cooling chamber air LW to the turbo expander 28A; expanding the twice-cooled cooling chamber air LW with the turbo expander 28A to cold air LK;

[0069] Directing the cold air LK from the turbo-expander 28A into the cooling chamber 10. This process is therefore continuous, the compressor medium or refrigerant is the cooling chamber air LW from the cooling chamber 10 as such, and the heat sink is formed by the environment or ambient air LU.

[0070] The mobile refrigerated transport device according to Fig. 1 has a dehumidification unit 24 (also referred to as a snowcatcher unit) for the cooling chamber air LW, which reduces the humidity in the cooling chamber 10. The dehumidification unit 24 can be part of the refrigeration machine 10, or located in the wall between the machine chamber 20 and the cooling chamber 20, or placed separately in the cooling chamber 20. The cooling chamber air LW flowing to the turbo compressor 28B can be drawn in, in particular, via filter candles of the dehumidification unit 24. A sensor device measures the pressure difference across the filter candles. Humidity collects on the filter candles in the form of snow, ice, dirt particles, and CO2 crystals. As soon as a threshold pressure difference is exceeded, the agglomerated snow, etc., is released by a pressure surge acting on the filter candles. The fallen snow, etc.falls into a discharge device so that it is transported out of the cooling chamber 10 and also out of the heat pump circuit 23.

[0071] The dehumidification unit 24 according to Fig. 1 can be arranged in Fig. 3 in a section of the exhaust air duct 25 between the cooling chamber 10 and the recuperator 29. The return of the cold air LK to the cooling chamber 10 can in turn be implemented using a ceiling duct as the supply air duct 26. The cold air LK is thus distributed over the floor area of ​​the cooling chamber 10 and, due to its higher density, sinks towards the bottom of the cooling chamber 10. This achieves a homogeneous temperature distribution. The cooling chamber air LW is preferably extracted from the cooling chamber 10 in the geodetically upper half, preferably in the upper third, of the cooling chamber 10. This is where the slightly warmer air is stratified, which is consequently extracted and can be cooled more efficiently.

[0072] For transport or storage of goods with corresponding requirements, the refrigeration machine 21 is designed or configured to achieve a temperature in the cooling chamber of at least -30 °C, and preferably down to at least -60 °C, and particularly preferably down to at least -100 °C.

[0073] Fig. 1 shows that the refrigeration machine 21 is arranged entirely outside the cooling chamber, namely in the machine chamber 20. There, the refrigeration machine 21 is positioned at a distance from the outside. Access to the machine chamber 20 is via a laterally oriented access door 104 (see Figs. 1 and 2). A ventilation grille 105 is located next to the access door 104. Ambient air LU for the heat exchanger 22 and the cooling of its electric drive 28 is supplied to the refrigeration machine 21 via this air grille 105. Also located in the machine chamber 20 is a monitoring device 40, which is part of a control unit for controlling the refrigerated transport device 1.

[0074] Furthermore, the cooling chamber 10 has an access lock 12 on the side of the loading compartment door 103. Behind the loading compartment door 103, an access gap 13 is formed between two individual doors 14, 15. This prevents direct air exchange between the environment and the cooling chamber 10. Optionally, the loading compartment door 103 and the first door 13 of the access lock 12 could also be formed as a single component.

[0075] The outer walls 16 of the cooling chamber 10, the outer walls 17 of the access lock 12, and the outer walls 27 of the machine chamber 20 are each thermally insulated with insulating material. The thermal insulation of the outer walls 16, including the floor and ceiling of the cooling chamber 10, is significantly thicker than that of the machine chamber 20 and the access lock 12. This leaves more space in the machine chamber 20 for the refrigeration machine 21 and other components, as well as in the access lock 12, for example, as a changing area and temporary storage space during loading and unloading. This maximizes the storage capacity of the cooling chamber 10.

[0076] Furthermore, the refrigerated transport device 1 comprises a power generator 30, which is connected to the air conditioning device 11 and the refrigeration machine 21 for the power supply. The power generator 30 has a first and a second power generator unit 31, 32, wherein the power supply is provided redundantly by the first and second power generator units 31, 32 by means of a safety circuit. The power generator 30 is arranged outside the machine chamber 20 and the cooling chamber 10. According to Fig. 2, the power generator 30 is visibly arranged lower than the machine chamber 20 and the cooling chamber 10. In particular, it hangs between the vehicle wheels 101 and the trailer coupling 102 below the cooling chamber 10.

[0077] The monitoring device 40 in the machine chamber 20 outputs various operating states or parameters to a receiver, in particular the location (e.g., via a GPS module), the temperature T1 of the machine chamber 20 (e.g., via a temperature sensor), the temperature T2 in the cooling chamber 10 (e.g., via a temperature sensor), the operating state of the air conditioning device 11 (e.g., via a data signal), the operating state of the refrigeration machine 21 (e.g., via a data signal), the operating state of the power generator 30 (e.g., via a data signal or current measuring unit), the fill level of energy sources such as accumulators (e.g., via a current measuring unit) or tanks (e.g., via a fill level sensor), the opening state of the accesses to the refrigerated transport device 1 (e.g., via door contacts), and the state of the dehumidification unit 24 (e.g., via a data signal). The recipient of this data preferably includes the driver, as they can resolve problems most quickly.The recipient group preferably also includes a central office that can receive the data, for example, via a mobile phone interface.

[0078] The invention is not limited to one of the embodiments described above, but can be modified in many ways.

[0079] In the exemplary embodiment, the machine chamber 20 is arranged between the air conditioning device 11 and the cooling chamber 10, and the power generator 30 is located below the cooling chamber 10. Alternatively, however, the power generator 30 and / or the air conditioning device 11 can also be arranged within an at least substantially cubic housing, such as a sea freight container (ISO container). For this purpose, additional chambers for the air conditioning device 11 and / or the power generator 30 can be formed therein.

[0080] All features and advantages arising from the claims, the description and the drawings, including design details, spatial arrangements and method steps, can be essential to the invention both individually and in a wide variety of combinations.

[0081] Reference symbol list

[0082] Refrigerated transport device 28C shaft

[0083] 29 Recuperator

[0084] Cooling chamber

[0085] Air conditioning device 30 Generator

[0086] Access lock 31 first generator unit

[0087] Access space 32 second generator unit

[0088] door

[0089] Door 40 monitoring device and

[0090] Outer walls of the cooling chamber additional control electronics

[0091] Exterior walls of the

[0092] Access gate 100 vehicle trailers

[0093] 101 vehicle wheels

[0094] Machine room 102 trailer coupling

[0095] Refrigeration machine 103 cargo door

[0096] Heat exchanger 104 access door

[0097] Heat pump circuit 105 Ventilation grille A Low pressure side 106 Tractor B Pressure side 107 Vehicle body

[0098] Dehumidifier or snow catcher

[0099] Unit LK cold air

[0100] Exhaust air duct LW cooling chamber air

[0101] Supply air line LU ambient air

[0102] Outer walls of the T1 temperature in the

[0103] Machine chamber Machine chamber electric drive T2 Temperature in the cooling chamber A Turbo- Expander B Turbo-Compressor

Claims

Mobile refrigerated transport device (1) with a cooling chamber (10), a refrigeration machine (21), and a power generator (30), wherein the cooling chamber (10) is temperature-controlled by the refrigeration machine (21), wherein the power generator (30) is connected to the refrigeration machine (21) for power supply, wherein the refrigeration machine (21) has a heat pump circuit (23) with a low-pressure side (23A) and a pressure side (23B), and wherein the cooling chamber (10) is part of the low-pressure side (23A) of the heat pump circuit (23). Mobile refrigerated transport device (1) according to claim 1, characterized in that the refrigeration machine (21) is designed to temperature-control the cooling chamber (10) according to the open Joule cycle or the reverse Brayton cycle.Mobile refrigerated transport device (1) according to one of claims 1 or 2, characterized in that the refrigeration machine (21) has a heat exchanger (22) as a temperature sink, which is connected to ambient air outside the cooling chamber (10). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the cooling chamber air (LW) from the cooling chamber (10) is the compression medium in the heat pump circuit (23). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the refrigeration machine (21) has an electric drive (28) with which a turbo-expander (28A) and a turbo-compressor (28B) are driven. Mobile refrigerated transport device (1) according to claim 5, characterized in that the electric drive (28) is air-cooled.Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the refrigeration machine (21) has a recuperator (29) with which the cooling chamber air (LW) exiting the cooling chamber (10) absorbs energy from the cold air (LK) returned to the cooling chamber (10). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the refrigeration machine (21) is designed to achieve a temperature (T2) in the cooling chamber (10) of at least -30°C, and preferably up to at least. -60 °C, and particularly preferably down to at least -100 °C. Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that it has a dehumidification unit (24) for the cooling chamber air (LW). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the refrigeration machine (21) is designed to be refrigerant-free. Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the refrigeration machine (21) is arranged at least substantially or completely outside the cooling chamber (10). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the refrigeration machine (21) is arranged in a machine chamber (20) of the mobile refrigerated transport device (1), wherein the machine chamber (20) is temperature-controlled by an air conditioning device (11).Mobile refrigerated transport device (1) according to claim 12, characterized in that the air conditioning device (11) is designed to maintain the machine chamber (20) within a temperature range (T1), and the refrigeration machine (21) is designed to cool the cooling chamber (10) to a temperature (T2) that is lower than the temperature range (T1) in the machine chamber (20). Mobile refrigerated transport device (1) according to one of claims 12 or 13, characterized in that the air conditioning device (11) is designed or configured to achieve a target temperature in the temperature range (T1) in the machine chamber (20) between 5°C and 60°C, preferably between 10°C and 40°C, more preferably between 10°C and 30°C, and particularly preferably between 15°C and 25°C.Mobile refrigerated transport device (1) according to one of claims 12 to 14, characterized in that the power supply to the air conditioning device (11) is provided by the power unit (30). Mobile refrigerated transport device (1) according to one of claims 12 to 15, characterized in that the air conditioning device (11) is arranged at least substantially or entirely outside the machine chamber (20) and outside the cooling chamber (10). Mobile refrigerated transport device (1) according to one of claims 12 to 16, characterized in that the machine chamber (20) is arranged between the air conditioning device (11) and the cooling chamber (10). Mobile refrigerated transport device (1) according to one of claims 12 to 17, characterized in that the outer walls (27) of the machine chamber (20) are thermally insulated with insulating material. Mobile refrigerated transport device (1) according to one of claims 12 to 18, characterized in that the refrigeration machine (21) is mounted in the machine chamber (20) decoupled from the outside. Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the cooling chamber (10) has an access lock (12) which has an access gap (13) between two individual doors (14, 15). Mobile refrigerated transport device (1) according to claim 20, characterized in that the access lock (12) has a de-icing device.Mobile refrigerated transport device (1) according to one of claims 20 or 21, characterized in that the outer walls (17) of the access lock (12) are thermally insulated with insulating material. Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the outer walls (16) of the cooling chamber (10) are thermally insulated with insulating material. Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the power generator (30) has a first and a second power generator unit (31, 32), wherein the power supply is provided redundantly by means of a safety circuit through the first and second power generator units (31, 32). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the power generator (30) is arranged outside the cooling chamber (10) and preferably also outside the machine chamber (20). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that the power generator (30) is arranged lower than the cooling chamber (10) and preferably also lower than the machine chamber (20). Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that it has a power connection for supplying power with terrestrial power, wherein the terrestrial power supply is preferably protected by the power generator (30) by means of a safety circuit. Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that it is a vehicle body (107) and / or is at least partially integrated into a vehicle body (107).Mobile refrigerated transport device (1) according to one of the preceding claims, characterized in that it has a monitoring device (40) which outputs at least one operating state to a receiver, e.g., the location, the temperature (T1) in the machine chamber (20), the temperature (T2) in the cooling chamber (10), the operating state of the air conditioning device (11), the operating state of the refrigeration machine (21), the operating state of the power generator (30), the fill level of energy sources such as accumulators or tanks, the opening state of access points to the refrigerated transport device (1), and the state of the dehumidification unit (24). A motor vehicle or vehicle trailer (100) with a mobile refrigerated transport device (1) according to one of the preceding claims 1 to 29.Use of a mobile refrigerated transport device (1) according to one of claims 1 to 29 or a motor vehicle or vehicle trailer (100) according to claim 30 for transporting goods or medicines.

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