WO2021209099A1 - Procédé pour garantir une température prédéfinie dans une chambre de congélation et dans une chambre de refroidissement, et installation de refroidissement, ainsi qu'utilisation d'une installation de refroidissement à bord d'un navire - Google Patents

Procédé pour garantir une température prédéfinie dans une chambre de congélation et dans une chambre de refroidissement, et installation de refroidissement, ainsi qu'utilisation d'une installation de refroidissement à bord d'un navire Download PDF

Info

Publication number
WO2021209099A1
WO2021209099A1 PCT/DK2021/050086 DK2021050086W WO2021209099A1 WO 2021209099 A1 WO2021209099 A1 WO 2021209099A1 DK 2021050086 W DK2021050086 W DK 2021050086W WO 2021209099 A1 WO2021209099 A1 WO 2021209099A1
Authority
WO
WIPO (PCT)
Prior art keywords
working medium
cooling
compressor
evaporator
tank
Prior art date
Application number
PCT/DK2021/050086
Other languages
English (en)
Inventor
Allan Thomsen
Original Assignee
B Cool A/S
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by B Cool A/S filed Critical B Cool A/S
Publication of WO2021209099A1 publication Critical patent/WO2021209099A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J2/00—Arrangements of ventilation, heating, cooling, or air-conditioning
    • B63J2/12—Heating; Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06—Several compression cycles arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction

Definitions

  • US 2017/0122624 A1 discloses a multi-stage system for cooling a refrigerant, which utilises known components such as evaporators, compressors, and gas cooler. However, it does not solve the above- mentioned problems.
  • a method which is adapted for ensuring a predefined temperature in a freezing room with a freezing evaporator and in a cooling room with a cooling evaporator is provided whereby a working medium in gas and/or liquid form is circulated in a circuit and exposed to working conditions in the following units: a) the cooling evaporator, wherein the working medium is evaporated at a cooling evaporator pressure, b) the freezing evaporator, wherein the working medium is evaporated at a freezing evaporator pressure, c) a working medium gas compressor unit, which comprises a first compressor wherein the evaporated working medium gases from the freezing evaporator is pressurized.
  • the compressor unit comprises a second compressor wherein the working medium exiting from the first compressor and the working medium which exits the cooling evaporator are conjointly received and compressed to a final output pressure, and further a working medium cooler is provided wherein the pressurized working medium gas from the second compressor is cooled down whereby the working medium exiting the working medium cooler is received at a working medium receiver tank which is connected to the cooler and freezing evaporators.
  • the working medium cooler inserted after the second compression step is allowed to deliver the working medium in either transcritical condition or in subcritical condition as mainly liquid.
  • C02 it shall depend on the temperature of the cooling medium in the working medium cooler, and the load from the evaporators whether a transcritical or subcritical temperature is reached, and in case seawater is used as the cooling medium, it will be difficult to stay below the transcritical temperature of the C02 when the seawater reaches temperatures of between 26 and 28 degrees Celsius. With the used construction, this poses no problem as the required further cooling is easily provided in the receiver tank.
  • first compression step and in the second compression step one, two or more individual compressors are used, and that there are more compressors assigned to the second compression step than to the first compression step.
  • any condensed cooling medium liquid in the line from either cooling room evaporator or cooling medium exiting the first compressor step shall, by way of the further added heat energy in the receiver circuit tank, be evaporated. This protects the second compression step from receiving any trace of liquid at its input end.
  • the receiver tank is also connected to the working medium stream by way of a receiver vapor exit pipe, which is connected to the output side of the first compression step conjointly with the output from the cooling room evaporator.
  • a motor driven receiver tank bleed off regulation valve is provided in the receiver vapor exit pipe, whereby the regulation valve is adapted to be guided by the temperature of the working medium as sensed by a receiver tank supply line temperature sensor, whereby the temperature of the working medium which exits the high pressure working medium cooler is recorded.
  • working medium may be allowed to escape the receiver tank and expand to a lover temperature in the receiver vapor exit pipe, and be guided into the cooling circuit of the receiver tank and hereby accomplish a further cooling down of the possibly transcritical working medium received here from the working medium cooler.
  • the pressurized gas from the output at the second compressor feeds into the working medium cooler, and enters a high pressure circular cylindrical tank into the spaces between straight cooling pipes arranged in an array in the high pressure tank whereby cooling water is circulated within the cooling pipes and wherein the working medium is supplied to the tank at a pressure PI, and wherein cooling water se supplied to the pipes at a pressure P2, and wherein PI is higher than P2, preferably up to between 30 and 120 bars higher.
  • the high pressure difference between the cooling side and the pressurised working medium side in the cooler is a challenge, but the high pressure tank is preferably a circular cylindrical tank and by ensuring that the cooling water pipes are aligned with the tank cylinder axis, a cooling medium such as water may be circulated through the pipes, while the high-pressure, and hot working medium is allowed to flow past the pipes in spaces provided between the pipes.
  • This design is especially beneficial in order to accommodate the high pressure difference between working medium and cooling water while it, at the same time, facilitates easy cleaning of the cooling water pipes.
  • the method further prescribes that the cooling water enters through a manifold provided at both a first end and a second end of the circular cylindrical tank, such that the inside of the straight cooling pipes between the first and the second end may be cleaned by mechanical means at each end of the cylindrical high pressure tank, and such that cooling water, preferably sea water may be circulated through the pipes.
  • the entrance of the cooling water through a manifold shall ensure, that the pipes between the two manifolds may be cleaned. Also, the manifolds shall ensure, that the high pressure of the working medium gas is maintained inside the cylindrical high-pressure tank. It is preferred, that a closure is provided and placed distally from the cooling pipe manifolds at both ends of the cylindrical tank. The closure is adapted to be removed, such that the cooling water pipes may be accessed at both ends of the circular cylindrical tank. This allows simple mechanical means such as brushes or high-pressure cleaning hoses to be pushed through each pipe.
  • the closure comprise an entrance opening at a lower part thereof and an exit opening at an upper part thereof, whereby the entrance opening connects exclusively to manifold a part, which connects to a range of pipes placed in the lower half of the circular cylindrical tank, and that the exit opening connects exclusively to a manifold part which is in connection with a range of pipes placed in the upper half of the circular cylindrical tank, and further the tank is placed with its longitudinal cylindrical axis in a horizontal direction.
  • the pipes placed in the lower half are allowed fluid flow connection to the pipes placed in the upper half of the tank in the area between the manifold and the closure.
  • An impinge plate may be arranged in the tank below the entrance tube.
  • the gasses shall flow in a generally downward direction while the cooling water in the pipes shall flow firstly inside the lower set of pipes, and then inside the upper set of pipes and thus flow in an overall up ward direction.
  • the first compression step and the second compression step are performed by rotary compressors and at all compressors, lubrication oil bleeds off at a controllable amount at a high pressure such as at the output pressure of the respective compressor is performed.
  • the rotary compressors are both very compact and may also be controlled very precisely and thus are easy to adapt the presented job of ensuring the working medium compression.
  • the bleed off of oil at a high pressure is a measure, whereby oil may be maintained in the compressor and at a well-controlled level, as oil, which has been bled off is piped to the suction or inlet end of the compressors, as is well known in the art.
  • each rotary compressor at the first compressor and at the second compressor the flow of lubrication oil bleeding off from each compressor is regulated by a motor driven valve provided in a bleed oil pipe according to a temperature of the lubrication oil at the high pressure side of the motor driven valve and according to a temperature of the lubrication oil at the low pressure side of the motor driven valve.
  • a motor driven valve is provided in the oil flow from the compressor to the intake end thereof, and the oil temperature is measured in front of the valve and after the valve, and the measured temperatures are used to set or regulate the bleed off rate through the valve.
  • the temperature of the lubrication oil inside the compressor may be regulated, and the lubrication oil flow through the compressor is also kept within acceptable boundaries. This is particularly important in case compressors which regulate the rotation speed are used, such that the oil bleed off amount may be arranged to follow load or temperature conditions at the individual compressor.
  • the cooling room evaporator and freezing room evaporator and the compressors and coolers may be arranged onboard a ship.
  • the ship environment is particularly challenging, as the available space on a ship is very costly, and thus real estate use for secondary items such as cooling shall be kept as low as possible. Also, it is to be observed, that a high reliability is a must onboard a ship, as spare parts and repair is often times not readily available.
  • the method according to the invention will be particularly well suited for use onboard a ship.
  • the invention also provides a cooling plant which is adapted to ensure a predefined temperature in a freezing room by use of a freezing evaporator and in a cooling room by use of a cooling evaporator
  • a working medium compressor unit comprises two compression steps which steps both include the use of rotary compressors and wherein: a) a cooling evaporator is provided, which evaporates the working medium liquid at a cooling evaporator pressure, b) a freezing evaporator is provided, which evaporates the working medium liquid at a freezing evaporator pressure, and c) the working medium gas compressor unit comprises a first compressor wherein the evaporated gases from the freezing evaporator is pressurized.
  • the working medium gas compressor unit comprises a second compressor wherein the working medium exiting from the first compressor and the working medium from the cooling evaporator are conjointly received and compressed to a final output pressure, and that, d) the working medium gas which exits the second compressor is served at the working medium cooler, and that e) the working medium exiting the working medium cooler is received at a working medium receiver tank which is connected to the cooler and freezing evaporators.
  • This cooling plant allows for the plant to work with the working medium in both sub-critical and trans-critical condition, which is most important in case waters, on which a vessel which carries the plant, are used for the cooling of the working medium cooler. Especially the varying temperatures of such waters may be a problem, which usual cooling plants are ill prepared to deal with.
  • a receiver tank evaporator exit pipe is provided between the inside of the receiver tank and the exit pipe of the first compressor, whereby the pipe allows vapours from within the receiver tank to escape and expand to reach a pressure commensurate with the pressure at the exit of the first compression step.
  • This measure may cool down the contents of the receiver tank when needed.
  • the working medium receiver tank includes a cooling circuit adapted to further cool down the working medium received from the high pressure working medium cooler, and that the cooling circuit at an input end is connected to the joint working medium stream in receiver cooling circuit supply pipe, which exits the first compressor and which exits the cooling evaporator and that the cooling circuit at an output end is connected to receiver cooling circuit exit pipe, whereby the working medium which exits the cooling circuit is served at the second compressor.
  • the working medium received in the receiver tank may be safely turned into a liquid, in the cases, where a transcritical temperature is obtained in the working medium which exits the working medium cooler.
  • the work load on the second compression step shall rise, and a higher exit temperature or an increased flow of the working medium exiting the second compression step is to be expected, which again leads to an increase of the energy to be transferred to the cooling water in the high pressure cooler.
  • a receiver tank bleed off regulation valve which is motor driven, is provided in the receiver evaporator exit pipe whereby the valve is guided by the measured temperature of the working medium supplied to the receiver tank by a receiver tank supply line temperature sensor.
  • the advantage of this arrangement is that the temperature of the vapor in the cooling circuit in the receiver tank may be controlled by a bleed off of working medium at high pressure.
  • the working medium exiting the receiver tank through the receiver tank bleed off regulation valve is introduced into the cooling circuit at a lower pressure and thus at a lower temperature.
  • the cooling circuit within the receiver tank comprises a simple spirally wound pipe, in which the working medium of the cooling plant is circulated.
  • the plant may further comprise a working medium cooler which has a circular cylindrical high pressure tank with a first end and a second end and having a multitude of straight cooling pipes arranged parallel to a cylinder axis of the high pressure tank between the first end and a second end whereby further space between the pipes is provided and adapted to receive the pressurized working medium from the working medium compressor unit at a pressure 90 bar or higher, while the pipes are adapted to receive the cooling water at a pressure of no more than 2 bar.
  • a working medium cooler which has a circular cylindrical high pressure tank with a first end and a second end and having a multitude of straight cooling pipes arranged parallel to a cylinder axis of the high pressure tank between the first end and a second end whereby further space between the pipes is provided and adapted to receive the pressurized working medium from the working medium compressor unit at a pressure 90 bar or higher, while the pipes are adapted to receive the cooling water at a pressure of no more than 2 bar.
  • the cylindrical shape of the working medium cooler and the use of pipes with a circular cross section enables the use of a very high pressure difference between the working medium, which is hot, and the cooling medium, which may be water, such as seawater.
  • the cooling water may have a temperature as high as up to 35 degrees Celsius.
  • a manifold is provided at both a first end and a second end, of the high pressure tank such that the straight cooling pipes between the first and the second end may be cleaned by mechanical means at each end of the cylindrical high pressure tank, and that cooling water, preferably sea water may thus be circulated through the pipes.
  • the manifolds are adapted to allow access to the inside of the pipes, which makes their cleaning a lot easier.
  • This arrangement allows for a very simple cleaning action of the pipes, as at both ends, the manifolds are provided which shall allow the pipes to be cleaned. This is especially important whenever un-filtered water is used, and such water is thus applicable as cooling water, and both salt, water and sweet water may be used directly from the sea/lake or river on which a ship is navigating.
  • a closure which has a diameter in accordance with the high-pressure tank diameter is provided at both ends at a low pressure side of the respective manifolds.
  • the pipes are arranged in two layers in the high pressior tank, which is arranged with its cylindrical axis in a vertical direction, such that a lover set of pipes arranged in the lower half of the tank receives cooling water which flows in the pipes from a manifold at a first end of the tank to a manifold at an opposed end. At the manifold of the opposed end, the water flows upward, to gain access to a second set of pipes, which are arranged in the upper half of the cylindrical high pressure tank, whereby the cooling water shall flow in the opposite direction in the upper pipes to reach the manifold at the first end of the tank, to gain access to an outlet opening for cooling water.
  • the outlet is placed above an inlet for the cooling water.
  • the pipes in the cylindrical tank are divided into four sub-groups, such that a first subgroup receives water at the inlet, and at the opposed end the manifold connects this first subgroup of pipes with a second subgroup of pipes, which directs the water back to the inlet end, where the water at the manifolds low pressure side gains connection with a third sub-group of pipes, which once again feeds the water through the cylindrical tank to the opposed end, where the water finally, again at the low pressure side of the manifold is connected to a fourth sub-group of pipes which runs through the length of the cylindrical tank to exit at the manifold and connect to a water outlet from the cylindrical tank heat exchanger.
  • This arrangement is known as a four-way heat exchanger.
  • first compressor and the second compressor each comprises rotary compressors of the type which bleeds a controlled amount of lubricating oil off at a high pressure.
  • Such compressors are commercially available in many variants. And thus, there are many commercially available options for the provision of the first and the second compressor step. It is preferred, that there are always more individual compressors at the second compressor step, such that this step is easy to regulate according to heat spending at the cooling room, which may wary over the day, and also according to the temperature of cooling medium supplied to the high pressure working medium cooler which may vary over time in accordance with water temperatures of the waters on which a vessel carrying the cooling plant is traveling.
  • a first temperature sensor is provided in an oil bleed output line and a second temperature sensor is provided in the oil bleed output line after a bleed off control valve and further the bleed off valve is a motor driven control valve which is adapted to be regulated according to temperature readings of the first and the second temperature sensors.
  • the provisions of the sensors shall ensure, that the bleed off rate of the oil from each compressor is regulated according to the temperatures recorded before and after an oil bleed off valve provided in an oil return pipe, which is adapted to feed the lubrication oil back to a suction manifold. It is noticed, that some working medium vapour may escape with the oil, and that this working medium shall expand according to the lower pressure at the low pressure side of the oil bleed off valve, and thereby a not insignificant temperature difference may be realized over the valve.
  • a suction manifold is provided, which allows oil to be introduced evenly into the working medium stream entering each compression step.
  • an oil separator is provided in the exit of working medium from the second compression step, and the oil which is separated from the high pressure working medium, shall be piped back to the manifolds and distributed to the first and the second compression steps through an oil feed line adapted therefor.
  • the cooling plant may be provided onboard a ship.
  • a ship with such a cooling plant may navigate at any part of the world and use seawater as the cooling medium to transport the excess heat from cooling and/or freezing rooms away.
  • Fig. 1 shows a schematic view of the cooling plant
  • Fig. 2 shows a working medium cooler
  • Fig. 3 is an enlarged sectional vies of a detail of a working medium cooler.
  • a cooling plant 2 of the present invention is illustrated in Fig. 1.
  • the plant 2 comprise the following main components: A freezing evaporator 100 which is adapted for evaporation of a working medium liquid, supplied in a freezing evaporator supply pipe 52, and a cooling evaporator 102, which is adapted to evaporate the liquid working medium supplied in a cooling evaporator supply line 51.
  • a freezing evaporator 100 which is adapted for evaporation of a working medium liquid, supplied in a freezing evaporator supply pipe 52
  • a cooling evaporator 102 which is adapted to evaporate the liquid working medium supplied in a cooling evaporator supply line 51.
  • a fan at the evaporator such that cooled down air, may be supplied inside the cooling room (not shown) and freezing room (not shown) respectively.
  • a freezing evaporator exit pipe 53 is adapted to conduct evaporated working medium to a first step compressor 20.
  • the first step compressor 20 supplies pressurized working medium to a second step compressor 30.
  • the compressors 20, 30 together comprise a working medium compressor unit 10.
  • Each of the first and the second compressor may comprise one, two or more individually driven compressors, and in the disclosed embodiment, the first compressor 20 is a single compressor unit, and the second compressor 30 comprises two individual and identical compressors 30 inserted in parallel between the first compressor 20 and a high pressure working medium cooler 12.
  • the high pressure working medium cooler 12 is adapted to receive the working medium from the second compressor 30 and is working as a heat exchanger, in which the pressurized and thus heated working medium is cooled down using a cooling medium.
  • the cooling medium in the presented embodiment is water, and preferably sea, lake og river water on which a vessel provided with the cooling plant navigates.
  • the receiver tank 16 will usually comprise condensed and liquid working medium at the bottom thereof and above the liquid there will be pressurized working medium vapor.
  • the working medium fraction above the condensed and liquid working medium may be transcritical, which may be the result of a higher temperature of the cooling water circulated in the high pressure working medium cooler 12.
  • additional cooling is carried out by either an expansion and bleed off of vapor through receiver vapor exit pipe 55 and/or through cooling by the circulation of working medium in cooling circuit 16.
  • the bleed off of working medium from the receiver tank 14 is guided by a receiver tank bleed of regulation valve inserted in the receiver vapor exit pipe 55. The valve is regulated according to the temperature of the working medium exiting the high pressure working medium cooler.
  • valves and regulations may be provided by use of a range of further valves possibly regulated and controlled automatically.
  • the valves and possible electronic control system is not disclosed, as this is well known in the art.
  • the receiver vapor exit pipe 55 connects to the receiver tank 14 at an upper part thereof.
  • a pipe is provided, which may guide the liquid from the tank 14 to the cooling evaporator supply line 51 and to the freezing evaporator supply line 52 to ensure, that there is always a supply of liquified working medium at the two evaporators 100, 102.
  • a bleed oil return line 25 shall be arranged, such that the lubrication oil, which exits each compressor is retuned to a manifold of the second compression step 28 and the manifold of the first compression 26 step respectively.
  • an oil bleed off control valve 34 is provided, and in front of each of the valves 34 there is a first temperature sensor 36, which measures the temperature of the oil exiting each compressor unit.
  • a second temperature sensor 38 is inserted after each valve 34 in the oil lines 25, there is inserted a second temperature sensor 38.
  • the signals from the two temperature sensors 36,28 are used in a control module (not shown) in order to regulate the position of each of the oil bleed off control valves 34. This allows the oil bleed off to be regulated according the working conditions of the respective compressors.
  • the working medium which enters the second compressor step shall be piped through the cooling circuit 16 in the receiver tank 16, as the receiver cooling circuit supply pipe 56 collects the working medium which exits each of the first compressor 20, the cooling room evaporator 102 and the working medium in the receiver vapor exit pipe 55.
  • the receiver cooling circuit exit pipe connect to the two second compressor step compressors 30.
  • the working medium cooler 12 is disclosed in Fig. 2. It comprises a circular cylindrical high-pressure tank 4, with a longitudinal centre axis arranged in a vertical position. The tank has a first end 6 and a second end 8, and at the first end 6 a manifold is provided 5 (see Fig. 3) and a similar manifold 5 is provided inside the tank at the second end 8.
  • Each manifold comprises a plate, which is arranged perpendicular to the centre axis of the tank 4.
  • the manifold plates 5 are resistant to the high-pressure conditions, which will reside inside the tank between the plates.
  • straight cooling pipes 7 are arranged to connect the distal surfaces of the manifold plates 5 and extend inside the tank parallel to the centre-axis thereof. Cooling water may be circulated inside the pipes 7 at low pressures, while a very high pressure is maintained in the space between the pipes 7 inside the tank 4.
  • closures 6.1, 8.1 of the tank 4 are arranged and bolted to tank flanges as is known in the art. Theses closures 6.1, 8.1 may be removed, and the pipes 7 may be cleaned by usual means, such as by use of a high pressure hose with a cleaning tip or by brushes arranged on long shafts.
  • the closures 6.1 at the first end 6 of the high-pressure tank 4 comprises an inlet 60 for cooling medium, preferably water, and an outlet 62 for the cooling medium.
  • the inlet 60 connects to a range of pipes 7 through a manifold part, whereby the pipes 7 are provided in the lower half of the tank 4, whereas the outlet connects to a manifold part, which is connected to a range of pipes 7 arranged in the upper half of the tank 4.
  • the pipes at the lower half of the tank gain access to the pipes at the upper half of the tank, in the section between the manifold and the closure 8.1.
  • Cooling water shall thus enter the inlet for cooling medium 60 at the first end 6 and flow through the pipes in the lower part of the tank, then flow upwards at the second end 8, and flow back to the first end in the pipes at the upper half of the tank 4 and exit the tank through the outlet 62 for cooling water.
  • This arrangement of inlet, outlet and manifolds is referred to as a two-way heat exchanger, as the pipes are arranged to transport the cooling water from end to end of the cylindrical tank twice. It is however possible to subdivide the pipes into 4 subgroups and allow the water to travel four times from end to end inside the cylindrical tank. Such an arrangement is referred to as a 4-way heat exchanger.
  • Fig. 3 an example of a pipe 7 and the manifold 5 in which it is inserted is disclosed.
  • the pipe 7 has smooth inner surfaces, and an exterior surface, which has been rolled or machined to comprise parallel furrows and ridges 71 arranged circumferentially around the pipe in the area thereof which shall be exposed to the hot C02.
  • This surface structuring shall give the exterior surface of the pipes an extraordinarily large surface area, and thereby enhance the heat transfer from C02 to water flowing inside the pipe.
  • the manifold 5, which is also partially disclosed in Fig. 3 comprises a layer of corrosive resistant material 72 at the side turned toward the water, but is otherwise made from a stronger material such as a high grade steel.
  • the manifold shall comprise up to 40 holes with pipes 7 mounted therein, and thus a high strength is required of this particular piece considering the high pressure difference between the C02 and the water side of the manifold.
  • the pipes 7 shall also be made of material, which will not corrode when exposed to the seawater on the inside.
  • the working medium of the plant which arrives from the second step compressors 30 at high temperature and at a high pressure is entered into the tank 4 through a vertically arranged entrance tube 64 at an uppermost ridge of the tank 4.
  • An exit tube 66 is provided below at a lowermost part of the tank 4.
  • An impinge plate 68 is provided inside the tank 4 below the entrance tube 64 to ensure, that the working medium which enters the tank 4 shall be spread to the sides and not travel directly down between the horizontally arranged tubes 7.
  • entrance tube 64 shall not be placed directly above the exit tube 66 but the two shall always be shifted sideways with respect to each other.
  • the working medium shall travel generally downward between the pipes 7, as the water shall travel generally upwards from the lower placed inlet 60 to the outlet 62 placed over the inlet.
  • the flow in the heat exchanges is not a real counterflow, but some of the counterflow advantages may be gained by the arrangement of the pipes as explained.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Sustainable Development (AREA)
  • Ocean & Marine Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

La présente invention concerne un procédé de refroidissement, de préférence à bord d'un navire, dans lequel un milieu de travail est mis sous pression dans des compresseurs en deux étapes, refroidi dans un refroidisseur à haute pression de milieu de travail, collecté dans un réservoir de récepteur, davantage exposé à une action de refroidissement dans le réservoir de récepteur, puis acheminé par tuyau vers des évaporateurs dans des chambres de refroidissement et de congélation. Il est préférable que les vapeurs provenant de la chambre de congélation soient comprimées dans la première étape, jointes aux vapeurs provenant de la chambre de refroidissement, puis acheminées conjointement par tuyau vers le circuit de refroidissement à l'intérieur du réservoir de récepteur, avant d'être acheminées par tuyau vers la seconde étape de compression.
PCT/DK2021/050086 2020-04-15 2021-03-22 Procédé pour garantir une température prédéfinie dans une chambre de congélation et dans une chambre de refroidissement, et installation de refroidissement, ainsi qu'utilisation d'une installation de refroidissement à bord d'un navire WO2021209099A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA202000446 2020-04-15
DKPA202000446A DK180741B1 (en) 2020-04-15 2020-04-15 Method for securing a predetermined temperature in a freezer and in a cold room, and refrigeration system as well as the use of a refrigeration system on board a ship

Publications (1)

Publication Number Publication Date
WO2021209099A1 true WO2021209099A1 (fr) 2021-10-21

Family

ID=75477851

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DK2021/050086 WO2021209099A1 (fr) 2020-04-15 2021-03-22 Procédé pour garantir une température prédéfinie dans une chambre de congélation et dans une chambre de refroidissement, et installation de refroidissement, ainsi qu'utilisation d'une installation de refroidissement à bord d'un navire

Country Status (2)

Country Link
DK (1) DK180741B1 (fr)
WO (1) WO2021209099A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006091190A1 (fr) * 2005-02-18 2006-08-31 Carrier Corporation Circuit de refrigeration avec recepteur ameliore de liquide/vapeur
WO2008019689A2 (fr) * 2006-08-18 2008-02-21 Knudsen Køling A/S Système de réfrigération transcritique doté d'un surpresseur
WO2013078088A1 (fr) * 2011-11-21 2013-05-30 Hill Phoenix, Inc. Système de réfrigération au co2 doté d'un dégivrage par gaz chauds
US20130298593A1 (en) * 2012-05-11 2013-11-14 Hill Phoenix, Inc. Co2 refrigeration system with integrated air conditioning module
US20170122624A1 (en) 2012-10-30 2017-05-04 Lennox Industries Inc. Multi-stage system for cooling a refrigerant

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006091190A1 (fr) * 2005-02-18 2006-08-31 Carrier Corporation Circuit de refrigeration avec recepteur ameliore de liquide/vapeur
WO2008019689A2 (fr) * 2006-08-18 2008-02-21 Knudsen Køling A/S Système de réfrigération transcritique doté d'un surpresseur
WO2013078088A1 (fr) * 2011-11-21 2013-05-30 Hill Phoenix, Inc. Système de réfrigération au co2 doté d'un dégivrage par gaz chauds
US20130298593A1 (en) * 2012-05-11 2013-11-14 Hill Phoenix, Inc. Co2 refrigeration system with integrated air conditioning module
US20170122624A1 (en) 2012-10-30 2017-05-04 Lennox Industries Inc. Multi-stage system for cooling a refrigerant

Also Published As

Publication number Publication date
DK180741B1 (en) 2022-02-10
DK202000446A1 (en) 2021-12-07

Similar Documents

Publication Publication Date Title
US11391518B2 (en) Method of operating a heat exchanger
US4184325A (en) Plant and process for recovering waste heat
CN102639923B (zh) 液化天然气的转化
EP2627940B1 (fr) Dispositif de pompage hybride
CN101896777A (zh) 热水贮存式热水供给机和热水贮存式制热热水供给机
US20120118545A1 (en) Thin film evaporator
KR20060121187A (ko) 증발가스의 온도를 제어하기 위한 장치 및 방법
EP0651212A2 (fr) Systèmes d'échange de chaleur
JP2005315558A (ja) ヒートポンプ給湯機
MX2012005506A (es) Una planta para la regasificación de gnl.
US8418487B2 (en) Water chiller economizer system
CN106556191A (zh) 船舶用制冷装置
JP3354750B2 (ja) 天然ガス焚きガスタービン複合サイクル発電所の燃料用ｌｎｇ気化装置
US20100206542A1 (en) Combined multi-stream heat exchanger and conditioner/control unit
US20090183867A1 (en) Varying ambient heat exchanger for a compressor
CN109844423B (zh) 具有在输入侧和输出侧耦联的热泵装置的热泵系统
DK180741B1 (en) Method for securing a predetermined temperature in a freezer and in a cold room, and refrigeration system as well as the use of a refrigeration system on board a ship
JPS5816117B2 (ja) 複数流体間の熱交換方法
CN108351188A (zh) 热交换器及空调
EP0162095B1 (fr) Procede et installation pour l'utilisation de la chaleur de congelation de l'eau en tant que source de chaleur d'une pompe thermique
US11725856B2 (en) Refrigerant processing unit, a method for evaporating a refrigerant and use of a refrigerant processing unit
US10907865B2 (en) Heating and cooling system, and heat exchanger for the same
KR100945185B1 (ko) 증발기 제상 시스템이 구비된 냉각장치
US3734174A (en) Heat exchanger for compressed air
RU2342322C2 (ru) Способ выщелачивания бокситовой пульпы, установка (варианты) и теплообменник для его осуществления

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21718015

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 21718015

Country of ref document: EP

Kind code of ref document: A1