Patent Application
20130233003
The invention relates to a cooling system for operation with a two-phase refrigerant which is in particular suitable for use on board an aircraft. Further, the invention relates to a method of operating a cooling system of this kind.
Cooling systems for operation with a two-phase refrigerant are known from DE 10 2006 005 035 B3, WO 2007/088012 A1, DE 10 2009 011 797 A1 and US 2010/0251737 A1 and may be used for example to cool food that is stored on board a passenger aircraft and intended to be supplied to the passengers. Typically, the food provided for supplying to the passengers is kept in mobile transport containers. These transport containers are filled and precooled outside the aircraft and after loading into the aircraft are deposited at appropriate locations in the aircraft passenger cabin, for example in the galleys. In order to guarantee that the food remains fresh up to being issued to the passengers, in the region of the transport container locations cooling stations are provided, which are supplied with cooling energy from a central refrigerating device and release this cooling energy to the transport containers, in which the food is stored.
In the cooling systems known from DE 10 2006 005 035 B3, WO 2007/088012 A1, DE 10 2009 011 797 A1 and US 2010/0251737 A1 the phase transitions of the refrigerant flowing through the circuit that occur during operation of the system allow the latent heat consumption that then occurs to be utilized for cooling purposes. The refrigerant mass flow needed to provide a desired cooling capacity is therefore markedly lower than for example in a liquid cooling system, in which a one-phase liquid refrigerant is used. Consequently, the cooling systems described in DE 10 2006 005 035 B3, WO 2007/088012 A1, DE 10 2009 011 797 A1 and US may have lower tubing cross sections than a liquid cooling system with a comparable cooling capacity and hence have the advantages of a lower installation volume and a lower weight. What is more, the reduction of the refrigerant mass flow makes it possible to reduce the conveying capacity needed to convey the refrigerant through the cooling circuit of the cooling system. This leads to an increased efficiency of the system because less energy is needed to operate a corresponding conveying device, such as for example a pump, and moreover less additional heat generated by the conveying device during operation of the conveying device has to be removed from the cooling system.
The invention is directed to the object to provide a cooling system for operation with a two-phase refrigerant which has a high operational reliability and hence is in particular suitable for use on board an aircraft. Further, the invention is directed to the object to provide a method of operating a cooling system of this kind.
These objects are achieved by a cooling system having features of attached claims and a method of operating a cooling system having features of attached claims.
A cooling system, which is in particular suitable for use on board an aircraft for cooling heat generating components or food comprises a first cooling circuit allowing circulation of a two-phase refrigerant therethrough. The two-phase refrigerant circulating in the first cooling circuit is a refrigerant, which upon releasing cooling energy to a cooling energy consumer is converted from the liquid to the gaseous state of aggregation and is then converted back to the liquid state of aggregation. The two-phase refrigerant may for example be CO2 or R134A (CH2F—CF3). Electric or electronic systems, such as avionic systems or fuel cell systems usually have to be cooled at a higher temperature level than food. For cooling these systems, for example Galden® can be used as a two-phase refrigerant. The evaporating temperature of Galden® at a pressure of 1 bar is approximately 60° C.
A first evaporator of the cooling system, which forms an interface between the first cooling circuit and a first cooling energy consumer, is disposed in the first cooling circuit. The first evaporator may, for example, comprise a heat exchanger which provides for a thermal coupling of the refrigerant flowing through the first cooling circuit and a fluid to be cooled, such as for example air to be supplied to mobile transport containers for cooling food stored in the mobile transport containers or any heat generating component on board the aircraft. The two-phase refrigerant is supplied to the first evaporator in its liquid state of aggregation. Upon releasing its cooling energy to the first cooling energy consumer, the refrigerant is evaporated and thus exits the first evaporator in its gaseous state of aggregation.
The cooling system further comprises a first condenser disposed in the first cooling circuit. The refrigerant which is evaporated in the first evaporator, via a portion of the first cooling circuit downstream of the first evaporator and upstream of the first condenser, is supplied to the first condenser in its gaseous state of aggregation. In the first condenser, the refrigerant is condensed and hence exits the first condenser in its liquid state of aggregation. A first heat sink is adapted to provide cooling energy to the first condenser. The first heat sink may be a chiller or any other suitable heat sink. For example, in a cooling system employing Galden® as the two-phase refrigerant flowing through the first cooling circuit the first condenser may be operated without a chiller. The first heat sink then may, for example, be formed as a fin cooler or outer skin heat exchanger which is cooled by ambient air.
The cooling system further comprises a second cooling circuit allowing circulation of a two-phase refrigerant therethrough, a second evaporator disposed in the second cooling circuit, a second condenser disposed in the second cooling circuit and a second heat sink adapted to provide cooling energy to the second condenser. The components of the cooling system which are associated with the second cooling circuit may be designed as described above for the respective components of the cooling system which are associated with the first cooling circuit.
A cooling energy transfer arrangement of the cooling system is adapted to transfer cooling energy provided by the first heat sink and/or the first condenser to the second cooling circuit or to transfer cooling energy provided by the second heat sink and/or the second condenser to the first cooling circuit. Preferably, the cooling energy transfer arrangement is adapted to couple the first heat sink and/or the first condenser to the second cooling circuit or to couple the second heat sink and/or the second condenser to the first cooling circuit in dependence on the operating state of the cooling system. In particular, the cooling energy transfer arrangement preferably is adapted to transfer at least a part of the cooling energy provided by the first heat sink and/or the first condenser to the second cooling circuit, if the amount cooling energy provided by the second heat sink and/or the second condenser is not sufficient to ensure proper operation of the second evaporator. By contrast, in operational states of the cooling system wherein the amount cooling energy provided by the first heat sink and/or the first condenser is not sufficient to ensure proper operation of the first evaporator the cooling energy transfer arrangement preferably is adapted to transfer at least a part of the cooling energy provided by the second heat sink and/or the second condenser to the second cooling circuit. The cooling energy transfer arrangement thus allows to at least partially compensate for a capacity overload, malfunctioning or failure of one or more of the cooling energy generating components in one of the two cooling circuits. The cooling system thus is distinguished by a high operational reliability rendering the cooling system suitable for use on board an aircraft.
In a preferred embodiment of the cooling system a third condenser is disposed in the first cooling circuit. The third condenser may be arranged in the first cooling circuit in parallel to the first condenser such that the refrigerant flowing through the first cooling circuit may be supplied in parallel to the first and the third condenser. Preferably, the first and the third condenser are controllable and operable is independently. Further, the cooling system may be equipped with a third heat sink which is adapted to provide cooling energy to the third condenser. The redundant design of a first cooling circuit comprising two condensers and two heat sinks ensures that the first evaporator can be supplied with a sufficient amount of cooling energy even in case of malfunctioning or failure of one or more of the cooling energy generating components in the first cooling circuit. Further, in case of failure of the second condenser and/or the second heat sink the second evaporator may be provided with cooling energy by the first heat sink, the first condenser, the third heat sink and/or the third condenser, as required. As a result, the operational reliability of the overall system may be enhanced.
The cooling system further may comprise one or more subcooler(s) which serve(s) to subcool refrigerant exiting the condenser(s). Preferably each of the condensers of the cooling system is coupled to a subcooler which provides for an appropriate subcooling of the refrigerant exiting its associated condenser. The condensers and their associated subcoolers may be designed in the form of condenser/subcooler assembly units. Subcooling the refrigerant exiting the condensers ensures that the refrigerant is supplied to a conveying device discharging refrigerant from the condensers in its liquid state of aggregation and sufficiently subcooled such that cavitation in the conveying device due to an unintended evaporation of the refrigerant within the conveying device is prevented. As a result, excess wear of the conveying device due to cavitation can be avoided.
Further, the cooling system may comprise a first accumulator which is disposed in the first cooling circuit and with serves to store refrigerant condensed in the first condenser prior to being supplied to the subcooler associated with the first condenser. The first accumulator may also be used to store refrigerant condensed in the third condenser prior to being supplied to the subcooler associated with the third condenser. If desired, it is, however, also possible to connect the third condenser to a separate accumulator for receiving refrigerant condensed in the third condenser. Similarly, in the second cooling circuit a second accumulator may be provided for receiving refrigerant condensed in the second condenser prior to being supplied to the subcooler associated with the second condenser.
The cooling energy transfer arrangement may comprise a heat exchanger which is adapted to be connected to the first cooling circuit such that refrigerant exiting the first condenser is thermally coupled to the refrigerant flowing through the second cooling circuit. Further, the heat exchanger may be adapted to be connected to the second cooling circuit such that refrigerant exiting the second condenser is thermally coupled to the refrigerant flowing through the first cooling circuit. Preferably, the heat exchanger is adapted to thermally couple the first and the second cooling circuit while maintaining a hermetic separation of the first and the second cooling circuit. This may be achieved by providing the heat exchanger with separate and hermatically sealed flow path fields for the refrigerant flowing through the first cooling circuit and the refrigerant flowing through the second cooling circuit. A hermetic separation of the first and the second cooling circuit enhances the operational reliability of the cooling system, since a leakage in one the two cooling circuits does not affect the operability of the other cooling circuit. Further, if desired, different refrigerants may be employed in the first and the second cooling circuit.
The heat exchanger may comprise a condenser wherein refrigerant flowing through the first cooling circuit may be condensed by means of cooling energy transfer from the refrigerant flowing through the second cooling circuit or wherein refrigerant flowing through the second cooling circuit may be condensed by means of cooling energy transfer from the refrigerant flowing through the first cooling circuit. Further, the heat exchanger may comprise a subcooler which serves to subcool refrigerant exiting the condenser of the heat exchanger. Subcooling the refrigerant exiting the heat exchanger ensures that the refrigerant is supplied to a conveying device discharging refrigerant from the heat exchanger in its liquid state of aggregation and sufficiently subcooled such that cavitation in the conveying device due to an unintended evaporation of the refrigerant within the conveying device is prevented. As a result, excess wear of the conveying device due to cavitation can be avoided.
The heat exchanger may be adapted to be connected to the first cooling circuit such that refrigerant flowing through the first cooling circuit is directed in series first through the condenser and thereafter through the subcooler of the heat exchanger. Further, the coupling between the heat exchanger and the first cooling circuit may be designed such that refrigerant exiting the heat exchanger is recirculated to the first condenser. If a third condenser is provided in the first cooling circuit, the heat exchanger may be adapted to be connected to the first cooling circuit such that the refrigerant exiting the heat exchanger is recirculated in parallel to the first and the third condenser. Further, the heat exchanger may be adapted to be connected to the second cooling circuit such that refrigerant flowing through the second cooling circuit first is directed through the condenser of the heat exchanger and thereafter is discharged to the second accumulator which also serves to store refrigerant condensed in the second condenser. The coupling between the heat exchanger and the first cooling circuit further may be designed such that refrigerant from the second accumulator may be directed in series first through the subcooler associated with the second condenser and thereafter through the subcooler of the heat exchanger. After exiting the subcooler of the heat exchanger the refrigerant flowing through the second cooling circuit may be directed to the second evaporator.
The cooling energy transfer arrangement further may comprise a valve which in its closed state is adapted to disconnect the heat exchanger from the first cooling circuit and which in its open state is adapted to connect the heat exchanger to the first cooling circuit. A further valve may be provided which in its closed state is adapted to disconnect the heat exchanger from the second cooling circuit and which in its open state is adapted to connect the heat exchanger to the second cooling circuit. A thermal coupling between the first and the second cooling circuit thus, by means of the valve(s), may be enabled or disabled, as desired.
Alternatively or additionally to a heat exchanger the cooling energy transfer arrangement of the cooling system may comprises a tubing system which is adapted to connect the first evaporator to the second condenser. This allows the first evaporator to be supplied with liquid refrigerant condensed in the second condenser. Further, the tubing system may be adapted to connect the second evaporator to the first condenser so as to allow the second evaporator to be supplied with liquid refrigerant condensed in the first condenser. Preferably, the tubing system is adapted to maintain a hermetic separation of the first and the second cooling circuit. If a third condenser and a third heat sink is provided in the first cooling circuit, the tubing system of the cooling energy transfer arrangement preferably also is adapted to connect the second evaporator to the third condenser while maintaining a hermetic separation of the first and the second cooling circuit.
Further, the cooling system may comprise a third accumulator which is disposed in the second cooling circuit and which is adapted to store refrigerant condensed in the first condenser prior to being supplied to the subcooler associated with the first condenser. A fourth accumulator may be disposed in the first cooling circuit and be adapted to receive refrigerant condensed in the second condenser. The third accumulator may also be used to store refrigerant condensed in the third condenser prior to being supplied to the subcooler associated with the third condenser. If desired, it is, however, also possible provide the cooling system with a fifth accumulator disposed in the second cooling circuit and being adapted to receive refrigerant condensed in the third condenser and/or a sixth accumulator disposed in the first cooling circuit and being adapted to receive refrigerant condensed in the third condenser.
The cooling system may comprise a first conveying device for conveying refrigerant through the first cooling circuit. The first conveying device may be connected to the first and the fourth accumulator. If also a sixth accumulator is disposed in the first cooling circuit, the first conveying device preferably also is connected to the sixth accumulator. This configuration of the cooling system allows the use of a single conveying device for conveying the refrigerant through the first cooling circuit. Alternatively or additionally thereto, the cooling system may comprise a second conveying device for conveying refrigerant through the second cooling circuit. The second conveying device may be connected to the second and the third accumulator. If also a fifth accumulator is disposed in the second cooling circuit, the second conveying device preferably also is connected to the fifth accumulator. This configuration of the cooling system allows the use of a single conveying device for conveying the refrigerant through the second cooling circuit. The cooling system, however, also may comprise a plurality of conveying devices. For example, a selected number of accumulators or each of the accumulators provided in the cooling system may be connected to a conveying device for discharging refrigerant from the associated accumulator.
The cooling system further may comprise a first interruption device adapted to interrupt a connection between a conveying device, in particular the first conveying device and the first accumulator, if a refrigerant level in the first accumulator falls below a predetermined threshold value, a second interruption device adapted to interrupt a connection between a conveying device, in particular the second conveying device and the second accumulator, if a refrigerant level in the second accumulator falls below a predetermined threshold value, a third interruption device adapted to interrupt a connection between a conveying device, in particular the second conveying device and the third accumulator, if a refrigerant level in the third accumulator falls below a predetermined threshold value, a fourth interruption device adapted to interrupt a connection between a conveying device, in particular the first conveying device and the fourth accumulator, if a refrigerant level in the fourth accumulator falls below a predetermined threshold value, a fifth interruption device adapted to interrupt a connection between a conveying device, in particular the second conveying device and the fifth accumulator, if a refrigerant level in the fifth accumulator falls below a predetermined threshold value, and/or a sixth interruption device adapted to interrupt a connection between a conveying device, in particular the first conveying device and the sixth accumulator, if a refrigerant level in the sixth accumulator falls below a predetermined threshold value.
The interruption devices ensure that the conveying devices do not convey gaseous refrigerant from accumulators which do not contain a sufficient amount of liquid refrigerant. Thereby, excessive wear of the conveying devices due to cavitation can be prevented. The interruption devices may comprise respective controllable valves which may be disposed in the first and/or the second cooling circuit(s) and which may be controlled in dependence of the refrigerant levels in the accumulators measured, for example, by appropriate fill level sensors. Alternatively or additionally thereto, the interruption devices may comprise float valves which are disposed in the accumulators and with close a respective refrigerant outlet of the accumulators, as soon as a refrigerant level in the accumulators falls below a predetermined threshold value.
In a further embodiment of the cooling system the cooling energy transfer arrangement may comprise a tubing and valve system which is adapted to establish a fluid connection between the first and the second cooling circuit. The cooling system then can be of a particularly low-volume and light-weight design while still being operable with the desired redundance and hence reliability.
The cooling system then preferably further comprises a first detection device adapted to detect the amount of refrigerant circulating in the first cooling circuit, and/or a second detection device adapted to detect the amount of refrigerant circulating in the second cooling circuit. A control unit may be adapted to control the tubing and valve system of the cooling energy transfer arrangement in dependence on signals provided to the control unit by the first and/or the second detection device. In particular, the control unit may be adapted to control the tubing and valve system of the cooling energy transfer arrangement such that a fluid connection between the first and the second cooling circuit is only established, if the signals provided to the control unit by the first and/or the second detection device indicate that an amount of refrigerant circulating in the first cooling circuit and/or an amount of refrigerant circulating in the second cooling circuit exceed(s) a predetermined threshold value. This ensures that a fluid connection between the first and the second cooling circuit is not established in case of a leakage in one of the cooling circuits.
Further, the control unit may adapted to control the tubing and valve system of the cooling energy transfer arrangement such that a fluid connection between the first condenser and the first evaporator and/or a fluid connection between the third condenser and the first evaporator is/are interrupted, in case a fluid connection between the first and the second cooling circuit is established in the event of failure of the cooling energy supply to the first evaporator via the first cooling circuit. Alternatively or additionally thereto, the control unit may adapted to control the tubing and valve system of the cooling energy transfer arrangement such that a fluid connection between the second condenser and the second evaporator is interrupted, in case a fluid connection between the first and the second cooling circuit is established in the event of failure of the cooling energy supply to the second evaporator via the second cooling circuit.
Moreover, the control unit may be adapted to interrupt the operation of a first conveying device for conveying refrigerant through the first cooling circuit, in case a fluid connection between the first and the second cooling circuit is established in the event of failure of the cooling energy supply to the first evaporator via the first cooling circuit, and/or to interrupt the operation of a second conveying device for conveying refrigerant through the second cooling circuit, in case a fluid connection between the first and the second cooling circuit is established in the event of failure of the cooling energy supply to the second evaporator via the second cooling circuit.
In a method of operating a cooling system, in particular for use on board an aircraft, a two-phase refrigerant is circulated through a first cooling circuit. The refrigerant circulating through the first cooling circuit is evaporated in a first evaporator disposed in the first cooling circuit. During normal operation of the cooling system the refrigerant circulating through the first cooling circuit is condensed in a first condenser disposed in the first cooling circuit. During normal operation of the cooling system cooling energy is providing to the first condenser from a first heat sink. Further, a two-phase refrigerant is circulated through a second cooling circuit. The refrigerant circulating through the second cooling circuit is evaporated in a second evaporator disposed in the second cooling circuit. During normal operation of the cooling system the refrigerant circulating through the second cooling circuit is condensed in a second condenser disposed in the second cooling circuit. During normal operation of the cooling system cooling energy is providing to the second condenser from a second heat sink. In the event of failure of the cooling energy supply to the second evaporator via the second cooling circuit cooling energy provided by the first heat sink and/or the first condenser is transferred to the second cooling circuit. Alternatively or additionally thereto, in the event of failure of the cooling energy supply to the first evaporator via the first cooling circuit cooling energy provided by the second heat sink and/or the second condenser is transferred to the first cooling circuit.
Preferred embodiments of the invention now are explained in more detail with reference to the enclosed schematic drawings wherein
The cooling system 10 of further comprises a second cooling circuit 12b allowing circulation of a two-phase refrigerant therethrough. The two-phase refrigerant circulating through the second cooling circuit 12a may also for example be CO2 or R134A. Two second evaporators 14b are disposed in the second cooling circuit 12b. Each of the second evaporators 14b comprises a refrigerant inlet and a refrigerant outlet. The refrigerant flowing through the second cooling circuit 12b is supplied to the refrigerant inlets of the second evaporators 14b in its liquid state of aggregation. Upon flowing through the second evaporators 14b the refrigerant releases its cooling energy to a cooling energy consumer which in the embodiment of a cooling system 10 depicted in
The cooling system 10 usually is operated such that a dry evaporation of the refrigerant occurs in the evaporators 14a, 14b. This allows an operation of the cooling system 10 with a limited amount of refrigerant circulating in the cooling circuits 12a, 12b. As a result, the static pressure of the refrigerant prevailing in the cooling circuit 12a, 12b in the non-operating state of the cooling system 10 is low, even at high ambient temperatures. Further, negative effects of a leakage in the cooling system 10 are limited. Occurrence of a dry evaporation in the evaporators 14a, 14b, however, can only be ensured by an appropriate control of the amount of refrigerant supplied to the evaporators 14a, 14b in dependence on the operational state of the evaporators 14a, 14b, i.e. the cooling energy requirement of the cooling energy consumers coupled to the evaporators 14a, 14b.
The supply of refrigerant to the first evaporators 14a is controlled by respective valves 20a, which are disposed in the first cooling circuit 12a upstream of each of the first evaporators 14a. Similarly, the supply of refrigerant to the second evaporators 14b is controlled by respective valves 20b, which are disposed in the second cooling circuit 12b upstream of each of the second evaporators 14b. The valves 20a, 20b may comprise a nozzle for spraying the refrigerant into the evaporators 14a, 14b and to distribute the refrigerant within the evaporators 14a, 14b. The spraying of the refrigerant into the evaporators 14a, 14b may be achieved, for example, by supplying refrigerant vapor from the evaporators 14a, 14b to the nozzles of the valves 20a, 20b and/or by evaporation of the refrigerant due to a pressure decrease of the refrigerant downstream of the valves 20a, 20b.
To ensure occurrence of a dry evaporation in the evaporators 14a, 14b, a predetermined amount of refrigerant is supplied to the evaporators 14a, 14b by appropriately controlling the valves 20a, 20b. Then, a temperature TK1 of the refrigerant at the refrigerant inlets of the evaporators 14a, 14b and a temperature TA2 of the fluid to be cooled by the evaporators 14a, 14b, for example air supplied to the cooling energy consumers, is measured, preferably while a fan conveying the fluid to be cooled to the cooling energy consumers is running. Further, the pressure of the refrigerant in the evaporators 14a, 14b or at the refrigerant outlets of the evaporators 14a, 14b is measured. If a temperature difference between the temperature TA2 of the fluid to be cooled by the evaporators 14a, 14b and the temperature TK1 of the refrigerant at the refrigerant inlets of the evaporators 14a, 14b exceeds a predetermined threshold value, for example 8K, and the pressure of the refrigerant in the evaporators 14a, 14b lies within a predetermined range, the refrigerant supplied to the evaporators 14a, 14b is thoroughly evaporated and possibly also super-heated by the evaporators 14a, 14b. Hence, the valves 20a, 20b again can be controlled so as to supply a further predetermined amount of refrigerant to the evaporators 14a, 14b.
Further, the cooling system 10 comprises a first condenser 22a which is disposed in the first cooling circuit 12a. A second condenser 22b is disposed in the second cooling circuit 12b. Finally, a third condenser 22c is disposed in the first cooling circuit 12a in addition to the first condenser 22a. Each condenser 22a, 22b, 22c has a refrigerant inlet and a refrigerant outlet. The refrigerant which is evaporated in the first evaporators 14a, via a portion of the first cooling circuit 12a downstream of the first evaporators 14a and upstream of the condensers 22a, 22c, is supplied to the refrigerant inlets of the condensers 22a, 22c in its gaseous state of aggregation. The supply of refrigerant from the first evaporators 14a to the condensers 22a, 22c is controlled by means of a valve 28a. The valve 28a is adapted to control the flow of refrigerant through the first cooling circuit 12a such that a defined pressure gradient of the refrigerant in the portion of the first cooling circuit 12a between the refrigerant outlets of the first evaporators 14a and the refrigerant inlets of the condensers 22a, 22c is adjusted. The pressure gradient of the refrigerant in the portion of the first cooling circuit 12a between the refrigerant outlets of the first evaporators 14a and the refrigerant inlets of the condensers 22a, 22c induces a flow of the refrigerant from the first evaporators 14a to the condensers 22a, 22c.
The refrigerant which is evaporated in the second evaporators 14b, via a portion of the second cooling circuit 12b downstream of the second evaporators 14b and upstream of the second condenser 22b, is supplied to the refrigerant inlet of the second condenser 22b in its gaseous state of aggregation. The supply of refrigerant from the second evaporators 14b to the second condenser 22b is controlled by means of a valve 28b. The valve 28b is adapted to control the flow of refrigerant through the second cooling circuit 12b such that a defined pressure gradient of the refrigerant in the portion of the second cooling circuit 12b between the refrigerant outlets of the second evaporators 14b and the refrigerant inlet of the second condenser 22b is adjusted. The pressure gradient of the refrigerant in the portion of the second cooling circuit 12b between the refrigerant outlets of the second evaporators 14b and the refrigerant inlet of the second condenser 22b induces a flow of the refrigerant from the second evaporators 14b to the second condenser 22b.
Each of the condensers 22a, 22b, 22c is thermally coupled to a heat sink 29a, 29b, 29c designed in the form of a chiller. The cooling energy provided by the heat sinks 29a, 29b, 29c in the condensers 22a, 22b, 22c is used to condense the refrigerant. Thus, the refrigerant exits the condensers 22a, 22b, 22c at respective refrigerant outlets in its liquid state of aggregation. Liquid refrigerant from the first and the third condenser 22a, 22c is supplied to a first accumulator 30a. Liquid refrigerant from the second condenser 22b is supplied to a second accumulator 30b. Within the accumulators 30a, 30b the refrigerant is stored in the form of a boiling liquid.
In the cooling circuits 12a, 12b the condensers 22a, 22b, 22c form a “low-temperature location” where the refrigerant, after being converted into its gaseous state of aggregation in the evaporators 14a, 14b, is converted back into its liquid state of aggregation. A particularly energy efficient operation of the cooling system 10 is possible, if the condensers 22a, 22b, 22c are installed at a location where heating of the condensers 22a, 22b, 22c by ambient heat is avoided as far as possible. When the cooling system 10 is employed on board an aircraft, the condensers 22a, 22b, 22c preferably are installed outside of the heated aircraft cabin behind the secondary aircraft structure, for example in the wing fairing, the belly fairing or the tail cone. The same applies to the accumulators 30a, 30b. Further, the condensers 22a, 22b, 22c and/or the accumulators 30a, 30b may be insulated to maintain the heat input from the ambient as low as possible.
The first accumulator 30a may, for example, be an accumulator as it is described in the non-published German patent application DE 10 2011 014 943. Liquid refrigerant from a sump of the first accumulator 30a is directed to a first subcooler 32a. The first subcooler 32a is associated with the first condenser 22a. The second accumulator 30b may, for example, also be an accumulator as it is described in the non-published German patent application DE 10 2011 014 943. Liquid refrigerant from a sump of the second accumulator 30b is directed to a second subcooler 32b. The second subcooler 32b is associated with the second condenser 22b. Refrigerant exiting the first subcooler 32a is directed to a third subcooler 32c associated with the third condenser 22c. The subcoolers 32a, 32b, 32c serve to subcool the liquid refrigerant and to thus prevent an undesired evaporation of the refrigerant. This ensures that the refrigerant is supplied to a first conveying device 34a for conveying refrigerant through the first cooling circuit 12a, which is embodied in the form of a pump, and to a second conveying device 34b for conveying refrigerant through the second cooling circuit 12b, which also is embodied in the form of a pump, in its liquid state of aggregation. Thus, dry operation of the conveying devices 34a, 34b and failure of the conveying devices 34a, 34b can be prevented.
The cooling system 10 further comprises a first storage container 36a which is disposed in the first cooling circuit 12a downstream of the first conveying device 34a, wherein the supply of refrigerant to the first storage container 36a is controlled by means of a valve 40a. A second storage container 36b is disposed in the second cooling circuit 12b downstream of the second conveying device 34b, wherein the supply of refrigerant to the second storage container 36b is controlled by means of a valve 40b. The storage containers 36a, 36b serve as backup reservoir for operational situations of the cooling system 10, wherein the volume of the first and the second accumulator 30a, 30b, respectively, is not sufficient so as to receive the entire amount of liquid refrigerant provided by the condensers 22a, 22b, 22c. Valves 38a, 38b serve to control the supply of refrigerant from the storage containers 36a, 36b to the first and the second accumulator 30a, 30b, respectively.
Finally, the cooling system 10 comprises a cooling energy transfer arrangement 42 which is adapted to transfer cooling energy between the first and the second cooling circuit 12a, 12b. In the cooling system 10 of
Further, the cooling energy transfer arrangement 42 comprises a valve 50 which in its closed state is adapted to disconnect the heat exchanger 44 from the first cooling circuit 12a and which in its open state is adapted to connect the cooling heat exchanger 44 to the first cooling circuit 12a. When the valve 50 opens the connection between the heat exchanger 44 from the first cooling circuit 12a, refrigerant flowing through the first cooling circuit 12a downstream of the first conveying device 34a is directed in series first through the condenser 46 and thereafter through the subcooler 48 of the heat exchanger 44. Further, the coupling between the heat exchanger 44 and the first cooling circuit 12a is designed such that refrigerant exiting the heat exchanger 44 is recirculated in parallel to the first and the third condenser 22a, 22c.
The heat exchanger 44 is adapted to thermally couple the first and the second cooling circuit 12a, 12b while maintaining a hermetic separation of the first and the second cooling circuit 12a, 12b. This is achieved by providing the heat exchanger 44 with separate and hermatically sealed flow path fields for the refrigerant flowing through the first cooling circuit 12a and the refrigerant flowing through the second cooling circuit 12b.
The valve 50, by means of a control device not shown in
The cooling system 10 according to
Further, the cooling system 10 of
The cooling system 10 of
The interruption devices 54a-54f ensure that the conveying devices 34a, 34b do not convey gaseous refrigerant from accumulators 30a-30f which do not contain a sufficient amount of liquid refrigerant. Each of the interruption devices 54a-54f comprises a float valve which is disposed in one of the accumulators 30a-30f and with closes a respective refrigerant outlet of the accumulator 30a-30f, as soon as a refrigerant level in the accumulator 30a-30f falls below a predetermined threshold value. Otherwise the structure and the function of the cooling system 10 according to
The cooling system 10 according to
An accumulator arrangement depicted in
In the cooling system according to
Further, the cooling system 10 comprises a first detection device 72 adapted to detect the amount of refrigerant circulating in the first cooling circuit 12a, and a second detection device 74 adapted to detect the amount of refrigerant circulating in the second cooling circuit 12b. A control unit 76 is adapted to control the tubing and valve system 58 in dependence on signals provided to the control unit 76 by the first and the second detection device 72, 74. In particular, the control unit 76 is adapted to control the tubing and valve system 58 such that a fluid connection between the first and the second cooling circuit 12a, 12b is only established, if the signals provided to the control unit 76 by the first and/or the second detection device 72, 74 indicate that an amount of refrigerant circulating in the first cooling circuit 12a and an amount of refrigerant circulating in the second cooling circuit 12b exceed a predetermined threshold value. This ensures that a fluid connection between the first and the second cooling circuit 12a, 12b is not established in case of a leakage in one of the cooling circuits 12a, 12b.
Further, the control unit 76 is adapted to control the tubing and valve system 58 such that a fluid connection between the first condenser 22a and the first evaporators 14a and a fluid connection between the third condenser 22c and the first evaporators 14a are interrupted, in case a fluid connection between the first and the second cooling circuit 12a, 12b is established in the event of failure of the cooling energy supply to the first evaporators 14a via the first cooling circuit 12a. Additionally thereto, the control unit 76 is adapted to control the tubing and valve system 58 such that a fluid connection between the second condenser 22b and the second evaporators 14b is interrupted, in case a fluid connection between the first and the second cooling circuit 12a, 12b is established in the event of failure of the cooling energy supply to the second evaporators 14b via the second cooling circuit 12b.
Moreover, the control unit 76 is adapted to interrupt the operation of the first conveying device 34a for conveying refrigerant through the first cooling circuit 12a, in case a fluid connection between the first and the second cooling circuit 12a, 14 is established in the event of failure of the cooling energy supply to the first evaporators 14a via the first cooling circuit 12a, and to interrupt the operation of the second conveying device 34b for conveying refrigerant through the second cooling circuit 12b, in case a fluid connection between the first and the second cooling circuit 12a, 12b is established in the event of failure of the cooling energy supply to the second evaporators 14b via the second cooling circuit 12b. Otherwise the structure and the function of the cooling system 10 according to
For controlling the start-up of any one of the cooling systems 10 depicted in
Finally, it is also conceivable to control the supply of cooling energy to the evaporators 14a, 14b upon start-up of the cooling system 10 such that at first all evaporators 14a, 14b are simultaneously supplied with cooling energy until a predetermined intermediate temperature of the evaporators 14a, 14b is reached. Immediately after start-up of the cooling system 10 the temperature difference between the operating temperature of heat sinks 29a, 29b, 29c designed in the form of chillers and the temperature of the cooling energy consumers still is high allowing a quick removal of heat from the cooling energy consumers. After reaching the predetermined intermediate temperature of the evaporators 14a, 14b the operating temperature of the heat sinks 29a, 29b, 29c may be reduced and further cooling energy may be supplied only to selected ones of the evaporators 14a, 14b until a predetermined target temperature of the selected evaporators 14a, 14b supplied with cooling energy is reached. Finally, the remaining evaporators 14a, 14b may be supplied with cooling energy until a predetermined target temperature is reached also for these evaporators 14a, 14b. Again a quick removal of heat from the cooling energy consumers may be achieved due to the large temperature difference between the operating temperature of the heat sinks 29a, 29b, 29c and the temperature of the cooling energy consumers.
In the embodiments of a cooling system 10 described above, the accumulators 30a, 30b and the storage containers 36a 36b fulfill the double function of storing liquid refrigerant exiting the condensers 22a, 22b, 22c, 46 and, in addition thereto, of reducing the system pressure in the cooling circuits 12a, 12b. The pressure reducing effect of the accumulators 30a, 30b and the storage containers 36a, 36b results from the additional volume the accumulators 30a, 30b and the storage containers 36a, 36b add to the volume of the cooling circuits 12a, 12b and becomes more and more significant, as the volume of the accumulators 30a, 30b and the storage containers 36a, 36b increases. The importance of the pressure reduction function of the accumulators 30a, 30b and the storage containers 36a, 36b increases as the operating temperature of the cooling system 10 and hence the pressure in the cooling circuits 12a, 12b increases and is of particular relevance if the cooling system 10 is operated with a refrigerant causing a high system pressure such as, for example, CO2.
Basically the cooling system 10 may comprise both, the accumulators 30a, 30b and the storage containers 36a,36b as described above, and both components may serve to store liquid refrigerant exiting the condensers 22a, 22b, 22c, 46 and to reduce the system pressure in the cooling circuits 12a, 12b. It is, however, also conceivable to equip the cooling system 10 with only the acculumators 30a, 30b or only the storage containers 36a, 36b. The accumulators 30a, 30b or the storage containers 36a, 36b which are provided in such a cooling system 10 then again fulfill the double function of storing liquid refrigerant exiting the condensers 22a, 22b, 22c, 46 and of reducing the system pressure in the cooling circuits 12a, 12b. Finally, a configuration of the cooling system 10 is conceivable, wherein the accumulators 30a, 30b serve to collect and to store liquid refrigerant, whereas the storage containers 36a, 36b, due to their additional volume, serve to reduce the system pressure.
In case the functions “storing liquid refrigerant” and “reducing system pressure” in the cooling system 10 are provided by separate components, these components may be installed at different positions within the cooling circuits 12a, 12b, allowing to more efficiently use the available installation space and to limit the size of the individual components of the cooling system 10. However, the pressure reducing storage containers 36a, 36b then preferably are installed in a high pressure portion of the cooling circuits 12a, 12b in order to reliably prevent the pressure in the high pressure portion of the cooling circuits 12a, 12b from exceeding a predetermined maximum value.
Further, in case the storage containers 36a, 36b merely serve to control the pressure in the cooling system 10, it is no longer necessary to provide for a direct fluid connection between the accumulators 30a, 30b and the storage containers 36a, 36b. Instead, the storage containers 36a, 36b may be connected to the cooling circuits 12a, 12b via only a single line branching off from the cooling circuits 12a, 12b, for example, upstream of one of the condensers 22a, 22b, 22c, 46 and downstream of the evaporators 14a, 14b. The line connecting the storage containers 36a, 36b to the cooling circuits 12a, 12b preferably is connected to the storage containers 36a, 36b at the geodetic lowest point of storage containers 36a, 36b. This configuration ensures that the storage containers 36a, 36b are supplied only with gaseous refrigerant which is discharged from the cooling circuits 12a, 12b due to the pressure in the cooling circuits 12a, 12b exceeding a predetermined value. Of course, if desired, only one storage container may be provided, in the cooling system 10.
| Number | Date | Country | Kind |
|---|---|---|---|
| 12 001 230.7 | Feb 2012 | EP | regional |
This application is entitled to and claims the benefit of European Patent Application No. 12 001 230.7 and U.S. Provisional Application No. 61/602,624, both filed Feb. 24, 2012, the disclosures of which, including the specification, drawings and abstract, are incorporated herein by reference in their entirety.
| Number | Date | Country | |
|---|---|---|---|
| 61602624 | Feb 2012 | US |
