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
  • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
  • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
  • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
• • 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
  • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
  • F25B47/02—Defrosting cycles
  • F25B47/022—Defrosting cycles hot gas defrosting
• • 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
  • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
• • 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
  • F25B2309/00—Gas cycle refrigeration machines
  • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
• • 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
  • F25B2347/00—Details for preventing or removing deposits or corrosion
  • F25B2347/02—Details of defrosting cycles
  • F25B2347/023—Set point defrosting
• • 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
  • F25B2400/07—Details of compressors or related parts
  • F25B2400/075—Details of compressors or related parts with parallel compressors
• • 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
  • F25B2400/22—Refrigeration systems for supermarkets
• • 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
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D31/00—Other cooling or freezing apparatus
  • F25D31/001—Plate freezers

Definitions

• the present invention relates to a refrigeration system of the cascade type, comprising an operative refrigerating circuit working with CO 2or another refrigerant and having one or more refrigeration compressors connected so as to suction refrigerant gas from an evaporator equipment and compressing it into a condenser unit, which also acts as an evaporator in a precoupled second refrigerating circuit, and from which condensed refrigerant liquid is conveyed to said evaporator equipment, whereas a defroster circuit is arranged for selectively supplying hot refrigerant to said evaporator equipment for defrosting purposes.
• Defrosting is necessary to remove ice built up on a freezer or a cooler. In most cases it is a question of proper and efficient function of the equipment, but in some cases it is a vital part of the function.
• One of the latter cases is a plate freezer, where the product is frozen between two metal plates wherein refrigerant is circulated. To be able to remove the product it is necessary to defrost the plates.
• Defrosting can be done in several ways, with the most common being:
• Hot gas defrosting where gas is condensed in the cooler/freezer at a temperature above the freezing point. Condensing takes place in the same circuit that is used for cooling/freezing.
• evaporators e.g. plate freezers hot gas defrost is the only possible solution for defrosting
• Hot gas defrosting is very efficient as heat is delivered where the ice has built up and it is very economical since the heat used is present in the system. Electrical and hot liquid defrosting requires an external power source which hot gas defrosting does not. During hot gas defrosting the cooler/freezer acts as a secondary condenser dispersing the heat otherwise dispersed in the cooling media (usually water or air).
• cascade systems are becoming more frequent. Due to the high saturation pressure of CO 2 , it is not possible to keep the pressure within the range normally encountered in refrigeration plants while still condensing it against air or water at ambient temperatures. Thus a cascade system is used, wherein a secondary refrigeration plant cools the CO 2 condenser. The secondary refrigeration plant condenses against the available cooling media. The condensing temperature of the CO 2 is usually in the range of-20°C to -5°C.
• a valve in the outlet controls the defrosting pressure in the evaporator. This valve will close when the pressure is lower than the desired pressure. However, this restricts the liquid condensed during the defrosting from leaving the evaporator, thus resulting in a build up of liquid in the evaporator. The build up of liquid reduces the surface inside the evaporator available for condensing and as such reduces the overall effect of the defrosting.
• CO 2 is considered a safe refrigerant. It is non-flammable, non-explosive and it is considerably safer to the crew than other refrigerants.
• CO 2 is a natural refrigerant with none of the environmental problems associated with older refrigerants such as CFC's and HCFC'S. CO 2 is not harmful to the environment ensuring unrestricted use in the future from the environmental point of view.
• the patent application DK200100310 describes a plant and a process using CO 2 for defrost.
• This system is a unit that delivers both defrosting and standstill cooling, e.g. keeping system pressure down during standstill.
• failure of the defrost system would mean that no standstill cooling is available and it is from some classification societies a demand that the standstill cool- ing is performed by a separate unit as a part of the safety system.
• the above-mentioned system is connected to the "distribution system", defined as a vessel with gas/liquid equilibrium along with the piping to the consumers e.g. the evaporators. From the application and its definitions it appears that the possible con- nection points are: A pump separator, a high-pressure receiver, and the piping to the consumers.
• defrosting compressor Connecting the defrosting compressor to the refrigeration cycle's low-pressure side results in a very large pressure difference, which most industrial refrigeration com- pressors cannot handle. Furthermore a defrosting compressor connected to the low pressure side needs to be about 4 times bigger (by swept volume) than one connected to the high pressure side to deliver the same defrosting capacity. Standard refrigeration equipment can be used when connecting to the high-pressure side, while this is not the case when connecting to the low-pressure side.
• the defrosting compressor If connecting the defrosting compressor to the high-pressure receiver it is very doubtful if sufficient gas is available in the receiver.
• the receiver essentially collects liquid from the condenser and will normally not contain the large amounts of gas necessary for defrosting.
• the suction gas for the compressor is saturated, necessitating a liquid separation. Ensuring that the suction gas contains no liquid is essential for safe compressor operation - especially when using reciprocating compressors.
• the present invention relates to a refrigeration system of the cascade type where said defroster circuit comprises a defrost compressor arranged in a gas pipe connection from the discharge side of said one or more refrigeration compressors to the refrigerant channel system of said evaporator equipment, said defrost compressor being oper- able to supply defrost gas at elevated pressure and temperature governed by preset or presettable discharge pressure/temperature requirements. At +10°C the CO 2 pressure is 45 bara, which calls for a separate dedicated defrost system.
• the system according to the invention limits the high pressure to an absolute mini- mum number of components while employing as many standard components as possible.
• Using a dedicated defrosting compressor another pressure level is created with the sole purpose of defrosting.
• the high pressure can be limited to the defrosting compressor, the defrost pipe, the evaporator to be defrosted and a few valves at the evaporator.
• the cascade cooler, refrigeration compressor and associated equipment can be held at the temperature/pressure yielding the most overall efficient plant and still be standard refrigeration components.
• the defrosting compressor is connected to the refrigeration compressor outlet.
• a system according to the invention has a specially dedicated compressor for defrost- ing.
• This defroster compressor suction gas is the refiigeration compressor discharge gas.
• the gas has been desuperheated before entering the defrost compressor to avoid too high discharge temperature that could create a problem with lubrication of the de- frost compressor.
• the COP (cooling capacity kW per power consumption kW) of the defrost compressor would be lower and oil cooling would be necessary.
• Desuperheating (cooling) of the suction gas to the defrosting compressor has an effect on the overall power consumption of the plant.
• Two methods of cooling are the most likely, the first one being cooling with the same media used in the secondary systems condenser (air or water) and the other method is using the cascade cooler.
• a cascade cooler would desuperheat the gas before condensing, so intro- ducing a nozzle in the appropriate place in the cascade cooler would yield a supply of cooled gas.
• the cooling is performed by the secondary system so power will be required by the secondary system.
• the gas supplied to the defrosting compressor does not contain liquid. A positive superheat is required to avoid liquid hammer (attempting to compress liquid) in the compressor.
• the air/water cooled cooler offers some advantages. As mentioned earlier, it is not practically possible to condense the CO 2 against air/water at normal ambient temperature, but it is possible to use it to cool the gas before entry into the cascade cooler and defrosting compressor. The benefit is that every kW cooled by the cooler does not have to be removed in the cascade cooler. This results in a reduction of both the size and power consumption of the secondary system. In such a cooler the gas can be cooled to a temperature very close to the ambient temperature, but since the saturation (condensing) temperature is much lower the gas is still sufficiently super- heated to avoid liquid hammer. The selection of one of these two systems will be a question of installation costs versus the savings in running costs.
• the defrost compressor capacity regulation regulates after the discharge (defrost) pressure.
• the condensing temperature determines the suction pressure in the cooling cycle. This pressure is kept constant by the "hot" refrigeration cycle.
• a controllable bypass valve is used to bypass hot gas back to the cascade cooler.
• the bypass valve is arranged in a connection from the discharge side of the defrost compressor and the discharge side of the one or more refrigerating compressors. A precise control of the defrost pressure and temperature is thereby enabled and the bypass valve will smoothen the capacity steps and secure that the pressure does not exceed the maximum design pressure. This control method makes it unnecessary to mount control valves on each cooler to control the pressure during defrost. All defrost control is done by the compressor and the bypass valve.
• the defrost pressure/temperature can be set for each evaporator individually by changing the defrost compressor discharge pressure set point. This way the defrost can be optimised for the individual type of evaporator. Some applications can benefit from a more gradual defrost while some need a fast defrost. Considerations when selecting defrost temperature will include heat loss into the surroundings, water/steam contents in the room air and product quality.
• the refrigerant outlet from the evaporator equipment can be connected to the suction side of the one or more refrigeration compressors through a liquid operated liquid draining device.
• thermodynamic liquid drain designed for steam and compressed air application.
• This device allows liquid to pass and stops gas in much the same way as a float valve mechanism.
• Float valve mechanisms employ a floating ball but these have been difficult or expensive to get for the high pres- sure needed.
• the liquid drain used is simple and can accept the pressures. The benefit is that when the compressor controls the pressure completely, the liquid drain only needs to drain the liquid in the freezer and not concern itself with regulating the pressure. The result is an extremely simple system with an efficient operation.
• a system as described, wherein the entire gas conductor system from the defrost com- pressor through the evaporator equipment and to the drain pipe of the evaporator can generally be without pressure regulating means and will preferably be laid out for operating at pressures not exceeding 50 bar.
• the defrost pressure/temperature is controlled by the compressor.
• the compressor will regulate its discharge pressure rather than the traditional suction pressure regulation. It is possible to regulate the compressor either by the normal compressor capacity step supplemented by a bypass valve to achieve a finer regulation or by using a frequency converter on the compressor motor to regulate the compressor RPM. This can be necessary because of the high capacity of a single capacity step on reciprocating compressors.
• thermodynamic liquid drain a commonly available component for compressed air and for steam or by a high-pressure float valve.
• the defrost compressor could be used as a normal refrigeration compressor.
• the compressor used for defrosting can be a dedicated defrost compressor, but can also be anyone of the refrigeration compressors.
• a system according to the invention can be designed with the possibility to use one or more of a plurality of compressors in the system as defrost compressor. In this way an increased safety and reliability of the system is achieved.
• the performance of the compressor in the two running conditions is well matched. That is, when running in the defrost condition the compressor yields 3-5 times as much as when in the refrigeration condition. This ratio is deemed suitable for defrosting in a reasonable time.
• the excess compressor capacity at cooling level matches the need for defrost capacity.
• the gas for defrosting is greatly superheated which, apart from the actual gain in heating capability, secures the system against condensation in pipes and valves before entering the cooler. If liquid enters a low-pressure area from high-pressure it can be "shot” into the low-pressure area and considerable damage can occur from this.
• the compressor is able to start the defrost "gently” while running up the pressure at the start of the defrost. This reduces the risk of pressure surges and liquid hammer.
• the gas will, after compression in the defrosting compressor, be condensed in the evaporator to be defrosted.
• the COP cooling capacity kW per power consumption kW
• the difference is naturally dependent on the type (refrigerant etc) of the secondary system and running conditions, but in general terms a factor of two is realistic. This means that for every 100 kW used by the defrosting compressor, the power consumption of the secondary system drops with 200 kW with a resulting overall drop of 100 kW.
• the defrost compressor employed in this system will deliver approximately 600 kW heating. If electrical defrosting is to be used, all 600 kW is needed in electricity, so the comparison is really an increase of 600 kW compared to a drop of 100 kW. If hot glycol is to be used the heating could be extracted in the system (most likely the secondary systems hot side) so the power con- sumption only increases with the pump power. However, no gain similar to the one described above is achieved.
• the compressors used are mainly large industrial compressors for industrial cooling purposes, but that the invention also can be used in connection with plants comprising commercial compressors capable of handling the given pressure and temperature.
• cooling and freezing plants in butcher shops, in supermarkets or in other retail shops can be mentioned as places to use the system.
• the defrost compressor capacity to supply hot gas to other elements than to a tra- ditional evaporator e.g. to elements consisting of heating/evaporator pipes placed in areas where ice otherwise will built up.
• Freezers that need defrosting is often used onboard fishing vessels and in such plants heating/evaporator pipes can be installed in the floor in the freezing area. In this area there will typically be ice formations, which today is removed or controlled by electrical heating elements. By replacing these elements with heating/evaporator pipes less electrical power is needed and the defrost compressor is used more efficient whereby energy is saved in the second condensing unit.
• CO 2 hot gas from the defrost compressor can be used for traditional defrosting, for heating and for defrosing in all places where the temperature is below 10 °C.
• Fig. 1 shows a system according to the invention and Fig. 2 shows a log(P)-H diagram of defrost according to the invention in cascade systems.
• fig. 1 which shows a system according to the invention, the systems function will be described. Please note that the fig. is simplified to ease understanding.
• the freezing system 2 is executed in the traditional manner.
• the pump separator 4 contains liquid refrigerant at the evaporating temperature.
• the pumps 6 pump refrigerant liquid to the evaporator 8 through the valve station 10.
• the refrigerant liquid is partially or completely evaporated and returned through the valve station 10 to the pump separator 4.
• the gas generated in the evaporator 8 is removed by the refrigeration compressor 12, which compresses the gas to the condensing pressure. From the refrigeration compressor 12 the gas is primarily led to the cascade cooler 14 where the gas is condensed before being led back to the pump separator 4.
• a secondary condensing unit 16 provides cooling for the cascade cooler 14.
• the freezing system 2 as described here, is well known technology and is as such not interesting, but the defrosting system is the essence of the invention described here.
• the defrost compressor 20 takes suction from the discharge of the refrigeration compressor 12 (e.g. at condensing pressure) and compresses it to the desired defrost pressure. Please note that the gas from the refrigeration compressor 12 is significantly superheated. To avoid too high discharge temperature (oil problems) from the defrost compressor 20 it could be necessary to desuperheat (cool) the gas before entry into the defrost compressor 20.
• This cooler has not been included on the sketch because the function is not vital to the principal function of the defrost system.
• the gas cooling could take place in an external heat exchanger or it could take place in the cascade cooler 14. As mentioned this gas cooling is not essential for the principal function of the system 2, but since some energy efficiency issues arise from this it will be discussed later in detail.
• the gas is led to the evaporator 8.
• the gas is led to the liquid/gas "outlet" 22 of the evaporator 8, resulting in a defrosting backward.
• backward defrosting is considered most efficient and thus it is outlined here.
• backward defrosting is safer since the risk of liquid bullets being shot through the system is reduced.
• the defrost gas condenses and it is led out through the liquid "inlet" 24 of the evaporator 8.
• Regulation of the pressure during defrosting is performed by the compressor 20 capacity regulation.
• the compressor 20 capacity regulation will regulate according to the discharge pressure as opposed to the "normal" suction pressure regulation. This method of regulation is common in heat pumps.
• the suction pressure for the defrosting compressor 20 e.g. the condensing pressure in the CO 2 circuit
• the suction pressure for the defrosting compressor 20 is kept constant by the secondary condensing unit 16.
• Regulating the pressure with the compressor 20 while the float valve 28 drains the evaporator 8 has some benefits: • Rather than using a regulating valve for each evaporator 8, the control is at one point only resulting in a more simple control.
• pressure regulators for 50 bars pressure are not standard refrigeration equipment.
• the evaporator 8 is, as mentioned, completely drained and thus offering the maximum surface area for condensing. Once the gas has condensed, e.g. given off its latent heat, it is of little use in the defrosting process. Removing the liquid enables the maximum defrosting capacity to be achieved.
• the defrosting compressor 20 can be put in an idling mode when no defrost is required, thus reducing wear from excessive start-stop situations.
• the defrosting compressor 20 can be stopped or used as a refrigeration compressor 12.
• a controllable bypass 32 valve is arranged in a connection from the discharge side of the defrost compressor and the discharge side of the one or more refrigerating compressors to bypass hot gas back to the cascade cooler 14.
• Fig. 2 is showing a log(P)-H diagram of defrost according to the invention in cascade systems.
• the diagram shows the normal refrigeration cycle (34). From evaporating pressure (36) the refrigerant is compressed (38) up to the condensing pressure (40).
• the system according to the invention connects the defrosting compressor (20) after the refrigeration compressors discharge port (42) and before condensing takes place (44) in the condenser/cascade cooler.
• the defrost compressor is connected at the refrigeration compressors suction side (46) or after the condenser/cascade cooler (48).

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Chemical Kinetics & Catalysis (AREA)
• Defrosting Systems (AREA)
• Fertilizers (AREA)

Priority Applications (3)

Applications Claiming Priority (4)

Publications (1)

Family

ID=26069034

Family Applications (1)

Country Status (5)

Cited By (4)

Citations (7)

• 2002
  • 2002-06-11 DK DK02747250T patent/DK1409936T3/da active
  • 2002-06-11 WO PCT/DK2002/000391 patent/WO2002101305A1/en active IP Right Grant
  • 2002-06-11 AT AT02747250T patent/ATE348301T1/de not_active IP Right Cessation
  • 2002-06-11 DE DE60216764T patent/DE60216764T2/de not_active Expired - Fee Related
  • 2002-06-11 EP EP02747250A patent/EP1409936B1/de not_active Expired - Lifetime

Patent Citations (7)

Non-Patent Citations (1)

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