WO2005024314A2 - Ameliorations a ou liees a la refrigeration - Google Patents

Ameliorations a ou liees a la refrigeration Download PDF

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Publication number
WO2005024314A2
WO2005024314A2 PCT/GB2004/003796 GB2004003796W WO2005024314A2 WO 2005024314 A2 WO2005024314 A2 WO 2005024314A2 GB 2004003796 W GB2004003796 W GB 2004003796W WO 2005024314 A2 WO2005024314 A2 WO 2005024314A2
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WO
WIPO (PCT)
Prior art keywords
refrigerator
evaporator
refrigerant
hot gas
condenser
Prior art date
Application number
PCT/GB2004/003796
Other languages
English (en)
Other versions
WO2005024314A3 (fr
Inventor
Ian David Wood
Original Assignee
Applied Design And Engineering Ltd
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 Applied Design And Engineering Ltd filed Critical Applied Design And Engineering Ltd
Publication of WO2005024314A2 publication Critical patent/WO2005024314A2/fr
Publication of WO2005024314A3 publication Critical patent/WO2005024314A3/fr
Priority to GB0517807A priority Critical patent/GB2415490A/en

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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
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/051—Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • 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
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • This invention relates to the art of refrigeration.
  • the invention relates to ref igerators, freezers, combined refrigerator/freezers, cold storage compartments configurable as both refrigerators and freezers, coolers and air conditioners, all for domestic or commercial applications including fixed and mobile appliances and installations.
  • ref igerators freezers
  • combined refrigerator/freezers cold storage compartments configurable as both refrigerators and freezers
  • coolers and air conditioners all for domestic or commercial applications including fixed and mobile appliances and installations.
  • refrigerators for brevity, all such appliances and installations will be referred to herein collectively as refrigerators unless the context demands otherwise.
  • the invention primarily relates to appliances and installations for cold storage and cooling, it does not exclude such appliances or installations that have the additional ability to heat to above-ambient temperatures, for example in defrosting.
  • the invention finds particular benefit in the context of the Applicant's multi-compartment cold storage appliances disclosed in its co-pending patent applications WO 01/20237, WO 02/073104, WO 02/073105 and WO 02/073107.
  • the compartments of those appliances are drawers sealed from one another to minimise cross-contamination, waste of energy and icing.
  • the basic elements of a typical refrigerator are a compressor, a condenser, a metering or expansion device and an evaporator, connected in that order in a circuit through which refrigerant cycles in use.
  • the compressor compresses gaseous refrigerant that enters the compressor at low pressure via a suction or return line.
  • the high-pressure hot gaseous refrigerant emanating from the compressor via a hot gas line flows through the condenser where it cools to a liquid also at high pressure, the condenser most commonly rejecting heat to atmosphere.
  • the cool high-pressure liquid refrigerant emanating from the condenser via a liquid line is forced through the metering or expansion device to reduce its pressure so that its boiling point drops to a level suitable for cooling.
  • the effect of the metering or expansion device is to maintain the necessary pressure difference between the condenser and evaporator.
  • the cool low-pressure liquid refrigerant emanating from the metering or expansion device flows through the evaporator where it evaporates in a low- pressure environment to draw heat from a storage compartment cooled by the evaporator.
  • the low-pressure gaseous refrigerant emanating from the evaporator is drawn back into the compressor via the suction line to start the cycle again.
  • Appendix 1 hereto is a sheet of symbols used in the diagrams of this specification, accompanied by notes where appropriate. Among other information, these notes explain that there are many variations of the basic elements described above, such as plate-type evaporators and forced air fan-coil type evaporators.
  • FIGS. 1 and 2 of the drawings show that capillary tubes 1 (although there is no capillary effect in the true sense) or other fixed orifices are commonly employed as metering or expansion devices in unitary appliances that have a single cold storage compartment, albeit a compartment that may be partitioned by shelves, drawers or the like.
  • the theory behind the operation of metering or expansion devices is well known, essentially causing the required pressure drop due to the restrictive effect of the narrow aperture and/or the frictional effect of the length of narrow tube which may be coiled as shown for compactness.
  • a capillary tube passes liquid much more readily than vapour due to the increased friction with the vapour; as a result, it is a practical metering device.
  • a capillary tube is sized to permit the desired flow of refrigerant, the liquid seals its inlet. If the system becomes unbalanced, some vapour (uncondensed refrigerant) enters the capillary tube. This vapour reduces the mass flow of refrigerant considerably, which increases condenser pressure and causes sub-cooling at the condenser exit and capillary tube inlet. The result is an increase of the mass flow of refrigerant through the capillary tube. If properly sized for the application, the capillary tube compensates automatically for load and system variations and gives acceptable performance over a range of operating conditions.
  • a common flow condition is to have sub-cooled liquid at the entrance to the capillary tube (see Figure 2).
  • the capillary tube controls the refrigeration system by allowing either liquid refrigerant, in case of high evaporator duty, or gaseous refrigerant, in case of low evaporator duty, to enter the inlet to the tube.
  • capillary tubes 1 Most simple domestic refrigerators, freezers and small air conditioning units employ a single capillary tube 1 as shown in Figures 1 and 2. These systems are 'charge sensitive' to the amount of refrigerant in the system and operate within a narrow band of evaporating and condensing temperatures, at small flow rates. Consequently, a system configured for a refrigerator cannot easily be turned into a freezer without components and the refrigerant charge being modified. In other words, capillary systems do not naturally lend themselves to multi-compartment cold storage involving widely-variable temperature (refrigerator-to- freezer) under a wide range of load and ambient operating conditions.
  • Figure 2 has the added refinement of heat transfer from the liquid line at the capillary tube 1 to the suction line 2 leaving the evaporator 3 en route to the compressor 4.
  • This suction liquid heat exchanger increases the capacity of the refrigeration system by transferring heat from the liquid in the capillary tube 1 to the suction vapour in the suction line 2 returning to the compressor 4. Consequently, the enthalpy of the refrigerant entering the evaporator 3 is reduced, increasing its refrigerant effect. Ignoring some small losses, the enthalpy increase in the vapour refrigerant in the suction line 2 is equal to the enthalpy decrease of the liquid refrigerant entering the evaporator 3.
  • the suction liquid heat exchanger shown in Figure 2 has a major effect on the operation of the capillary tube 1. If the heat exchange takes place before vapour starts to form, it sub- cools the liquid refrigerant. This greatly increases the mass flow of refrigerant through the capillary tube 1. If the heat exchange takes place after vapour has started to form, the liquid temperature will have decreased. The temperature difference between the liquid refrigerant and the refrigerant vapour in the suction line 2 will therefore be less and less heat will be transferred. Generally, the liquid is sub-cooled to prevent bubbles forming when it is expanding (thus increasing flow rate) and vapour in the suction line 2 is heated or even superheated, with the effect that the overall system capacity is increased.
  • FIG 3 introduces a thermostatic expansion valve 5 (TEV) as a metering device in place of the capillary tube of Figures 1 and 2.
  • TEV 5 provides a variable orifice that regulates refrigerant flow based upon the degree of superheat in vapour leaving the evaporator 3.
  • the degree of superheat is the extent to which vapour temperature is above the saturation temperature determined by pressure in the evaporator 3, and is detected via a phial or bulb sensor 6 associated with the TEV 5 that is located on the suction line return to the compressor to feed back actuating pressure to the TEV 5 via a pipe 7.
  • a TEV 5 ensures that liquid refrigerant does not return to the compressor 4, which liquid could otherwise cause hydraulic damage to the compressor 4.
  • the TEV 5 also allows for greater fluctuations in demand than would a capillary tube 1, provided that those fluctuations are not too rapid.
  • systems employing TEVs are not as charge-sensitive (i.e. to the amount of refrigerant in the system) as capillary systems.
  • the present invention resides in the concept of a refrigerator as herein defined, comprising a refrigerant circuit having a compressor means for receiving refrigerant via a suction line, a condenser means for receiving refrigerant from the compressor via a hot gas line, an expansion means for receiving refrigerant from the condenser via a liquid line and an evaporator means for receiving refrigerant from the expansion means and sending refrigerant after evaporation to the compressor means via the suction line, wherein the circuit includes a branched portion comprising a plurality of parallel branches each having a respective evaporator of the evaporator means.
  • the expansion means comprises a thermostatic expansion valve in each branch situated upstream of the evaporator of that branch, a superheat sensor associated with the thermostatic expansion valve being situated downstream of that evaporator.
  • the superheat sensor is also on the branch associated with the associated thermostatic expansion valve.
  • the invention also contemplates arrangements in which the expansion means comprises a thermostatic expansion valve situated upstream of the branched portion, a superheat sensor associated with the thermostatic expansion valve being situated downstream of the branch portion. That thermostatic expansion valve may be substantially solely responsible for expansion of the refrigerant before the refrigerant encounters the evaporator means.
  • the expansion means comprises a capillary in each branch upstream of the evaporator of that branch and there may also be means for heat exchange between the capillary and the suction line.
  • the refrigerator of the invention preferably comprises a cooling control valve in each branch situated upstream of the evaporator of that branch.
  • That cooling control valve may be an on/off valve that is cycled in use to control cooling by the evaporator of that branch. It is also, or alternatively, possible to control evaporator cooling by a cooling control fan means that acts upon the evaporators.
  • the cooling control fan may be varied in speed and/or cycled to control evaporator cooling in use.
  • the refrigerator of the invention may further include an accumulator downstream of the evaporator means to receive refrigerant from the evaporator means and from which the compressor draws refrigerant vapour.
  • That accumulator preferably includes means for heat exchange with the liquid line downstream of the condenser.
  • the superheat sensor associated with the optional thermostatic expansion valve may be situated downstream of the accumulator.
  • a liquid receiver may be situated downstream of the condenser means to receive refrigerant from the condenser means in a reservoir from which refrigerant passes to the evaporator means.
  • the optional thermostatic expansion valve may be situated downstream of the condenser means and the liquid receiver. It is also possible for the suction line to include the liquid receiver, refrigerant being drawn by the compressor means in use from a vapour cavity above liquid in the liquid receiver.
  • the refrigerator of the invention further comprises head pressure control means associated with the condenser.
  • That head pressure control means may comprise one or more fans acting on the condenser, in which case the or each fan operates cyclically or at variable speed to control head pressure.
  • the head pressure control means may comprise a pressure regulating means in the liquid line.
  • the pressure regulating means may, for example, be an automatic valve or a means for switching between differently- sized fixed orifices in the liquid line.
  • the refrigerator of the invention may also include a circulation pump to impel refrigerant through the evaporator means.
  • Suction pressure control means may be provided, responsive to suction pressure control logic.
  • the suction pressure control means advantageously selects an evaporating pressure/temperature appropriate for the evaporator with the lowest set temperature among the evaporators.
  • the suction pressure control logic suitably takes input from a look-up table recording absolute pressure, evaporator temperature and bar gauge pressure appropriate to refrigeration temperature levels to be achieved by an evaporator.
  • any of the embodiments of the invention may further comprise a hot gas feed taken from the hot gas line downstream of the compressor means to supply hot gas to the evaporator means.
  • the hot gas feed preferably joins the refrigerant circuit at a junction upstream of the evaporator means, and there may be a hot gas control valve upstream of the junction.
  • the hot gas feed suitably branches to join each of the branches of the branched portion at a respective junction, in which case each branch of the hot gas feed preferably has a respective hot gas control valve upstream of the junction.
  • FIG 4 shows a way of adapting the abovementioned prior art to suit the Applicant's preferred multiple-compartment variable-temperature storage system.
  • Like numerals are used for like parts.
  • a four-compartment arrangement is illustrated but any practical number of compartments is possible.
  • Each compartment is cooled by a respective evaporator 3 on respective parallel branches 8 of the circuit.
  • any compartment can be used as a refrigerator or as a freezer by virtue of mass control achieved by cycling a respective solenoid shut-off valve 9 serving each evaporator 3.
  • Each branch 8 of the circuit is served by a respective TEV 5 whose superheat sensor 6 is downstream of the evaporator 3 of that branch 8.
  • the circuit is much the same as the basic circuits illustrated in Figures 1 to 3, apart from the routine additions of a high- pressure liquid receiver 10 as a reservoir in the liquid line 11 downstream of the condenser 12 .
  • a filter drier 13 in the liquid line downstream of the liquid receiver 10 to maintain refrigerant quality
  • a sight glass 14 in the liquid line downstream of the filter drier 13 to monitor the refrigerant condition.
  • the compressor 4 and condenser 12 are referred to in the singular for brevity but, in all embodiments, they can be plural and/or variable speed to meet variable load and duty requirements in use.
  • TEVs are expensive, meaning that in a four-compartment appliance the overall cost of TEVs alone would be in excess of GBP 200 (about US$320 or €290).
  • the system shown in Figure 5 introduces a low-pressure accumulator 15 in the suction line 2 between the evaporators 3 and the compressor 4 but is otherwise identical to that shown in Figure 4.
  • the low-pressure suction line accumulator 15 traps any slugs of liquid emanating from the evaporators 3 that might otherwise be returned to the compressor 4.
  • the accumulator 15 holds any such liquid at the bottom of a pressure vessel and allows the compressor 4 only to draw off vapour above the liquid within the vessel. That vapour is drawn into the compressor 4 via a U-shaped compressor return line 16 that is partially immersed in the liquid within the pressure vessel and has an orifice 17 in the lowest part of the U to allow a metered flow of oil back to the compressor.
  • This oil typically emanates from within the compressor casing and is entrained in use as liquid or vapour by the refrigerant passing through the compressor.
  • TEVs 5 Whilst the low-pressure suction line accumulator 15 of Figure 5 ensures that liquid is not returned to the compressor 4, TEVs 5 are still needed for control under most circumstances. This involves substantial expense as outlined above, and the Applicant is aware of only one commercially-available TEV that is suitable for its needs.
  • the arrangement of Figure 7 is essentially a hybrid of the arrangements of Figures 5 and 6, in that a low-pressure accumulator 15 is placed in the suction line 2 between the evaporators 3 and the compressor 4, downstream of the superheat sensor 6 associated with the TEV 5. Again, this solves the problem of liquid returning to the compressor 4. However, the distribution of liquid refrigerant is still poor, involving oversupply of refrigerant to some evaporators 3 while starving others. Low temperature distribution problems also arise as aforesaid.
  • the arrangement shown in Figure 8 replaces the TEVs 5 of the Figure 4 arrangement with capillary tubes 1 to provide individual expansion to each evaporator 3 at a fraction of the cost of the same number of individual TEVs 5. As shown, the system in Figure 8 is completely uncontrolled and risks poor refrigeration conditions and the passage of liquid slugs to the compressor 4.
  • Figure 8a shows a modification of Figure 8 providing for heat transfer from the liquid line at each capillary tube 1 to the suction line 2 leaving the evaporator 3 en route to the compressor 4. This improves efficiency and adds heat to the refrigerant in the suction line 2 returning to the compressor 4.
  • FIG. 9 replaces the high-pressure liquid receiver 10 upstream of the evaporators 3 of Figure 8 with a low-pressure suction line accumulator 15 downstream of the evaporators, akin to that shown in Figures 5 and 7 above.
  • the capillary tubes 1 are sized such that the evaporator 3 provides some superheat to the refrigerant under most operating conditions for the evaporator 3.
  • Figure 9a shows a hybrid of the arrangements of Figure 8a and Figure 9.
  • Figure 8a there is provision for heat transfer from the liquid line at each capillary tube 1 to the suction line 2.
  • suction line 2 As in Figure 9, there is a low-pressure suction line accumulator 15 downstream of the evaporators 3.
  • FIGs 10 and 11 show preferred embodiments of the invention that provide inexpensive expansion devices for a multiple-compartment cold storage appliance in which each of the compartments may be set at temperatures in the range between ambient and substantially below zero Celsius.
  • Both embodiments are similar to Figure 9, Figure 11 the more so because, like Figure 9, it has solenoid shut-off valves 9 for each evaporator 3 to provide capacity control, whereby temperature within each compartment is maintained by cyclically opening and closing the appropriate solenoid.
  • Figure 10 omits the solenoid shut-off valves 9 in favour of cycling a fan (not shown) associated with each evaporator 3 to maintain temperature within each compartment.
  • FIG. 10 and 11 both employ a modified low-pressure accumulator 18 in the suction line 2 downstream of the evaporators 3.
  • the accumulator 18 is modified by the provision of a liquid/suction heat exchanger 19 in which the high pressure liquid line 11 from the condenser 12 passes through the vessel to boil the accumulated refrigerant liquid and to provide superheat to the gaseous refrigerant returned to the compressor 4 via the suction line 2.
  • This allows each evaporator 3 to be fully flooded with liquid refrigerant (i.e. liquid in and liquid out) giving greater cooling efficiency.
  • the capillary tube 1 would be sized so that the refrigerant would boil off completely by the time it reaches the downstream end of the evaporator 3, the evaporator 3 often also adding superheat before the vapour leaves the evaporator 3 and enters the suction line 2 leading to the compressor 4. This protects the compressor 4 from slugs of liquid refrigerant.
  • this precaution is not necessary in the systems of Figures 10 and 11 because any excess liquid flows harmlessly to the suction accumulator 18, where it is boiled off by heat exchange from the liquid line 11.
  • the evaporators 3 can be run fully flooded and so at optimum efficiency.
  • a capillary tube 1 has further practical advantages in addition to its low cost in comparison with a TEV 5.
  • the small-bore capillary tube 1 can be run to the evaporator 3 by hand without the need for skilled pipe fabrication. Also, very low temperatures are first encountered only at the downstream end portion of the capillary tube 1 adjacent to the evaporator 3, representing perhaps 10% to 20% of the capillary length, which makes insulation requirements less onerous. A TEV 5 and its associated phial/bulb superheat sensor 6 are much more difficult to insulate.
  • head pressure control 20 associated with the condenser 12. This is because the condensing temperature/pressure normally varies with ambient temperature due to the ⁇ t over the heat rejection exchanger. Specifically, low ambient temperature implies low head pressure and high ambient temperature implies high head pressure.
  • the capillary tube 1 requires a more constant ⁇ P so that it regulates the same flow of refrigerant to the evaporator 3 under all ambient conditions. Consequently, head pressure control 20 is preferably employed to stabilise the ⁇ P over the capillary tube 1. This may be via multiple fans cycling in combination on the condenser 12 or with variable-speed fans on the condenser 12. Alternatively, a pressure regulating valve may be employed in the liquid line 11 or means may be provided for switching between a series of differently-sized fixed orifices in the liquid line 11.
  • Figures 12 and 13 show arrangements akin to those of Figures 10 and 11, in that a low- pressure accumulator 18 in the suction line 2 downstream of the evaporators 3 includes a liquid/suction heat exchanger 19 in which heat from the high pressure liquid line 11 boils accumulated refrigerant liquid and superheats the gaseous refrigerant returned to the compressor 4 via the suction line 2. It is expected that in the arrangements of Figures 12 and 13, head pressure control 20 would not be required as the automatically operated TEV 5 should compensate for variations in temperature.
  • Figure 13 is identical to Figure 11 save for the provision of a single TEV 5 upstream of the evaporators 3 whose feedback line 7 extends from a superheat sensor 6 on the suction line 2 downstream of the low-pressure suction line accumulator 18.
  • superheat is measured by the TEV 5 on the suction line 2 to the compressor 4 having picked up heat from the liquid/suction heat exchanger 18.
  • Figure 13 therefore introduces the concept of two-stage expansion where some of the expansion is carried out by the fixed capillary tubes 1, but the TEV 5 provides automatic (even if crude) control of refrigerant expansion. This arrangement is proposed to improve liquid distribution and overcome variations in ambient temperature, negating head control.
  • the arrangement of Figure 12 has the same TEV arrangement as shown in Figure 13 but in this instance, the capillary tubes 1 are omitted entirely so that the TEV 5 is fully responsible for the pressure drop from high-pressure liquid leaving the condenser 12 to low pressure liquid entering each evaporator 3.
  • the arrangement of Figure 12 replaces the capillary tubes 1 with a common TEV 5.
  • the system still allows for the evaporators 3 to be flooded with refrigerant, even where only one evaporator 3 is being used for cooling: the oversized TEV 5 can still provide crude control without liquid returning to the compressor 4 and compensate for variations in ambient temperature.
  • the arrangement in Figure 14 is as for Figure 13 apart from omission of the TEV 5 and provision of a hot gas feed 21 from the hot gas line 22 immediately downstream of the compressor 4.
  • the hot gas feed 21 branches via a hot gas solenoid valve 23 on each branch to supply hot gas to a junction 24 with the main circuit immediately upstream of the evaporators 3.
  • the hot gas solenoid valve 23 to each evaporator 3 in Figure 14 is normally closed. On defrost, that valve 23 is opened and the corresponding liquid refrigerant solenoid valve 9 is closed to introduce hot gas to the associated evaporator 3 and melt accumulated ice.
  • Each evaporator 3 can be defrosted separately by virtue of independently controllable valves 23 on each branch. However, it is not essential to have an individual hot gas solenoid valve 23 on each branch of the hot gas feed 21. As Figure 15 shows, it is possible to have a common hot gas solenoid valve 23 upstream of the branch in the hot gas feed 21. In this case, each branch of the main circuit has a liquid refrigerant solenoid valve 9 downstream of its junction 24 with the associated branch of the hot gas feed 21.
  • liquid refrigerant solenoid valve(s) 9 associated with the evaporator(s) 3 to be defrosted must be open and the other liquid refrigerant solenoid valves 9 must be closed.
  • a low-pressure receiver 25 receives cold liquid refrigerant from the liquid line 11 downstream of the condenser 12 and outputs that liquid refrigerant to the evaporators 3 via a filter drier 13, a circulation pump 26 and a sight glass 14. Vapour refrigerant flowing from the evaporators 3 is returned to the receiver 25 above the liquid level therein and is drawn off from above the liquid level into the suction line 2 that feeds the compressor 4.
  • the refrigerant being drawn off from the receiver 25 through the suction line 2 has been exposed to the cold liquid refrigerant beneath and so will be somewhat colder than the vapour entering the receiver from the evaporators 3.
  • the liquid refrigerant leaving the receiver 25 en route to the evaporators 3 will be somewhat warmer than the liquid refrigerant flowing in to the receiver 25 from the condenser 12 via the liquid line 11. This is by virtue of heat exchange with the warmer vapour within the receiver 25 above the body of liquid refrigerant.
  • a TEV 5 is situated in the liquid line 11 between the condenser 12 and the low-pressure receiver 25 and its superheat sensor 6 is situated on the suction line 2 upstream of the compressor 4.
  • the TEV 5 operates in a simple circuit with the compressor 4, condenser 12 and receiver 25.
  • the low-pressure receiver 25 acts as a reservoir to damp out sudden fluctuations in refrigerant flow, thus enabling more stable operation of the TEV 5.
  • the circulation pump 26 simply impels cold liquid refrigerant through any evaporator 3 whose associated solenoid valve 9 is open.
  • hot gas may only need to be pulsed periodically into the appropriate evaporator. Meanwhile, evaporator air circulation fans can run continuously in all compartments. It would therefore be possible to close all of the liquid refrigerant solenoid valves for the pulse duration of hot gas solenoid valve opening without greatly affecting the product storage temperatures experienced in the chilled and frozen compartments.
  • Solenoid valve switching could be reduced by fitting non-return valves to the downstream exit of each evaporator before the branches converge into the common suction line.
  • Another possibility is a blast chill facility, in which case alternative evaporator air- circulation fans would be required in order to obtain the increased air flow-rate required. Either multi-speed or supplementary fans could be used to provide the increased air flow- rate as and when it was required.
  • the low-pressure accumulator system suggested for certain arrangements above allows the evaporator coils to run not only fully-flooded, but actually to be overfed with liquid under normal operation without fear of liquid returning to the compressor. This over-capacity should accommodate a blast chill facility by maintaining the evaporating temperature despite the large heat load made possible by higher air flow-rates over the evaporator coil.
  • this table shows how suction pressure control logic selects an evaporating pressure/temperature appropriate for the compartment with the lowest set point. That is, the control logic will maintain a higher suction pressure/temperature if all drawers are set above zero than if they are all set below zero.
  • the table in Figure 17 shows the relationship between absolute pressure, temperature and bar gauge.
  • the table shows typical temperature/pressure settings that are provided in a look-up table in the control logic.
  • Figure 18 shows a refrigeration circuit diagram for a unitary cold-storage system, serving a single compartment such as a drawer.
  • An alternative would be to supply each compartment of a multi-compartment system from a central refrigerator engine via an umbilical service connection.
  • the evaporator 3 discharges into a low-pressure accumulator 15 in the suction line 2 between the evaporator 3 and the compressor 4. Unlike previous embodiments, the evaporator 3 discharges into the liquid refrigerant at the bottom of the accumulator 15. Moreover, the surface of that liquid is maintained above the level of the evaporator 3, ensuring that the evaporator 3 is kept flooded for efficiency.
  • a capillary tube 1 upstream of the evaporator 3 is placed adjacent the accumulator 15 for the purpose of heat exchange.
  • the tube 1, can, for example be wrapped around the accumulator 15 in a circular or spiral arrangement. It is also possible for refrigerant to pass through a heat exchanger within the accumulator 15 before passing through the tube 1.
  • a pump down solenoid valve 27 is situated downstream of the condenser 12. When closed, the pump down solenoid valve 27 isolates the high pressure side and low pressure side of the refrigeration system. This stops refrigerant expanding into the evaporator 3 and allows the compressor 4 to pump the refrigerant from the low pressure side into the high pressure side thereby maintaining the pressure differential when the compressor 4 is stopped. Without the pump down solenoid valve 27, the pressures will equalise.
  • the pump down solenoid valve 27 is used in conjunction with a temperature switch (storage temp) and a LP switch that stops the compressor.
  • Appliance not calling for cooling compressor 4 stopped, and system pumped down (high and low pressure sides).
  • Appliance calls for cooling opens pump down solenoid valve 27, LP switch is satisfied and starts compressor 4.
  • Appliance cooling is satisfied, pump down solenoid valve 27 closes, system pumps down to LP switch point, and stops compressor 4.
  • a suction pressure sensor and a look-up table akin to that shown in Figure 17 may provide multi-point switching of the compressor 4.
  • Condenser head control could be provided by variable-speed heat-exchanger fans, a series expansion valve and/or the number or surface area of the condenser(s) used, in the manner of the arrangements in Figures 12 and 13.
  • Evaporator fans may cycle on/off or be variable-speed to maintain the temperature of the storage compartment.
  • a hot gas defrost solenoid valve 23 is switchable to direct hot refrigerant from upstream of the compressor 4 through the evaporator 3 when defrosting is required. Water dripping from the evaporator 3 during defrosting discharges to a heating plate 28 associated with the condenser 12, from where it is evaporated to the surrounding atmosphere.
  • FIGs 19 and 20 show a prior art warm cabinet condenser unit, Figure 19 being a plan view and Figure 20 being a partial section on line X of Figure 19.
  • condenser pipe coils 29 are attached to the casing of a refrigerator cabinet 30 and PU foam 31 is injected to form an insulated structure defining a cold-storage volume.
  • the coils 29 are sandwiched between the foam insulation 31 and the casing of the cabinet 30.
  • Such an arrangement can commonly be provided on three vertical walls of the cabinet 30, namely two side walls and a back wall, and in theory could be employed on other walls too e.g. top and bottom.
  • FIGS 21 and 22 show a cold-storage appliance modified in accordance with the present invention.
  • Figure 21 is a plan view and Figure 22 is a detail plan view of region Y marked in Figure 21.
  • an insulated container 32 such as a drawer can be moved in and out of a cabinet 33 defined by condenser casing walls 34.
  • a condenser pipe coil 35 visible in Figure 22 is located to the outboard side of a condenser casing wall 34 and so faces away from the container 32. This arrangement, if used with a flat sheet condenser casing, provides for separation of the pipe coil 35 from an air gap 36 between the container 32 and the condenser casing wall 34.
  • the internal flat condenser casing provides a smooth wipe-clean surface without dirt traps.
  • Separate air passages can be created on respective sides of the condenser casing to the benefit of airflow, and each air passage can be designed for specific requirements.
  • the internal air passage can be designed to supply only the minimum amount of heat required for anti-condensation requirements, without adding unnecessary cooling load to the refrigeration system, and the external air passage can be designed to reject the remaining portion of the unwanted heat.
  • the or each air passage may be ventilated, for heat exchange, by natural convection or by forced air flow (e.g. by fans).
  • Air pressure and airflow directions can be optimised between the internal and external air passages.
  • the internal air passage could receive filtered air that positively pressurises the cubicle to prevent unclean air ingress, keeping internal surfaces clean and hot condenser air out.
  • the external air passage can be at a lower pressure (negative) relative to the internal air passage. Unfiltered ambient and/or air discharged from the internal air passage can be directed though the external air passage.
  • Vacuum storage can also be useful for dehydration.
  • the condenser is to be used to evaporate water emanating from the use of defrost or condenser means
  • a choice can be made as to which air passage or surface should be used to reject that water. For example, it may be desirable to maintain a higher humidity around the external surfaces of the drawer, in which case the water can be discharged to the internal air passage. More likely, however, it will be preferable to discharge the water outside the inner air passage and hence into the external air passage.
  • Heat rejection could be wholly to either the internal or external side of the condenser casing. Heat can also be rejected by conduction to structural or heat exchanging attachments to the condenser casing.
  • the casing defined by the condenser casing walls 34 may or may not be structural: it can be self-supporting and structurally independent, or it may take support from adjacent units such as kitchen cabinets to which it is attached.
  • the casing could be a self-contained module including other components such as drawer lids or drawer runners.
  • the condenser casing warms the surrounding air and adjacent surfaces by radiation and convection, which prevents condensation by using a portion of the rejected heat from the condenser. Where the casing is fixed to an adjacent structure, heat rejection from the condenser may also be by conduction.
  • defrost water and condensation from a cooling fan coil may be drained to the condenser plate and evaporated locally to the unit.
  • This arrangement saves the complexity of running a pipe to a convenient drain point, which is particularly useful for unitary installations.
  • a further variant envisages a fan or the like forcing air to circulate through the condenser heat exchange and around the external surfaces of the insulated cold-storage container and evaporator fan coil.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

La présente invention a trait à un réfrigérateur comportant un circuit frigorifique comprenant un moyen compresseur pour la réception de réfrigérant via un conduit d'aspiration, un moyen condenseur pour la réception de réfrigérant via un conduit de gaz chauds, un moyen de détente pour la réception de réfrigérant en provenance du condenseur via un conduit de liquide et un moyen évaporateur pour la réception de réfrigérant en provenance du moyen de détente et le transport de réfrigérant après évaporation vers le moyen compresseur via le conduit d'aspiration, le circuit comportant une portion ramifiée comprenant une pluralité de branches parallèles dont chacune présente un évaporateur respectif du moyen d'évaporation.
PCT/GB2004/003796 2003-09-05 2004-09-06 Ameliorations a ou liees a la refrigeration WO2005024314A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB0517807A GB2415490A (en) 2004-09-06 2005-09-01 Cold-storage appliance

Applications Claiming Priority (2)

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GB0320856.8 2003-09-05
GB0320856A GB2405688A (en) 2003-09-05 2003-09-05 Refrigerator

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WO2005024314A2 true WO2005024314A2 (fr) 2005-03-17
WO2005024314A3 WO2005024314A3 (fr) 2005-06-23

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US7748228B2 (en) 2006-01-13 2010-07-06 The Delfield Company, Llc Refrigeration system capable of multi-faceted operation
CN102121774A (zh) * 2011-03-30 2011-07-13 合肥美的荣事达电冰箱有限公司 制冷系统及具有该制冷系统的冰箱
CN104315798A (zh) * 2014-10-30 2015-01-28 六安索伊电器制造有限公司 一种用于电控冰箱的单毛细管的电控制冷系统
EP3076109A1 (fr) * 2015-03-30 2016-10-05 Viessmann Werke GmbH & Co. KG Système de refroidissement et procédé de fonctionnement du système de refroidissement
CN106164609A (zh) * 2013-09-13 2016-11-23 斯科茨曼制冰系统有限公司 制冰设备
WO2019167909A1 (fr) * 2018-03-02 2019-09-06 パナソニックＩｐマネジメント株式会社 Unité d'échangeur de chaleur et climatiseur l'utilisant

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CN105333653A (zh) * 2007-05-11 2016-02-17 纳幕尔杜邦公司 蒸汽压缩热传递系统
US8769976B2 (en) 2007-06-12 2014-07-08 Danfoss A/S Method for controlling a refrigerant distribution
GB0717908D0 (en) * 2007-09-14 2007-10-24 Univ Exeter The An ice making system
JP5210626B2 (ja) * 2007-12-27 2013-06-12 三菱重工業株式会社 陸上輸送用冷凍装置及び陸上輸送用冷凍装置の運転制御方法
WO2009128097A1 (fr) * 2008-04-14 2009-10-22 Giuseppe Floris Unité de réfrigération fonctionnant à différentes pressions
CN201281484Y (zh) * 2008-09-09 2009-07-29 李亮 多功能变频空调冷气循环系统
US10429111B2 (en) 2015-02-25 2019-10-01 Heatcraft Refrigeration Products Llc Integrated suction header assembly
DE102015117850A1 (de) * 2015-03-30 2016-10-06 Viessmann Werke Gmbh & Co Kg Kühleinrichtung und Verfahren zum Betreiben einer Kühleinrichtung
KR20180118615A (ko) 2015-12-29 2018-10-31 쥬타-코어 엘티디. 진공 기반 열관리 시스템
ITUA20163465A1 (it) * 2016-05-16 2017-11-16 Epta Spa Impianto frigorifero a più livelli di evaporazione e metodo di gestione di un tale impianto
CN110770522B (zh) * 2017-03-12 2022-05-24 祖达科尔有限公司 冷却系统和方法
US11365906B2 (en) * 2017-07-23 2022-06-21 Zuta-Core Ltd. Systems and methods for heat exchange
CN111512110A (zh) * 2017-11-06 2020-08-07 祖达科尔有限公司 热交换的系统及方法

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US7748228B2 (en) 2006-01-13 2010-07-06 The Delfield Company, Llc Refrigeration system capable of multi-faceted operation
CN102121774A (zh) * 2011-03-30 2011-07-13 合肥美的荣事达电冰箱有限公司 制冷系统及具有该制冷系统的冰箱
CN106164609A (zh) * 2013-09-13 2016-11-23 斯科茨曼制冰系统有限公司 制冰设备
CN106164609B (zh) * 2013-09-13 2019-05-17 斯科茨曼制冰系统有限公司 制冰设备
CN104315798A (zh) * 2014-10-30 2015-01-28 六安索伊电器制造有限公司 一种用于电控冰箱的单毛细管的电控制冷系统
EP3076109A1 (fr) * 2015-03-30 2016-10-05 Viessmann Werke GmbH & Co. KG Système de refroidissement et procédé de fonctionnement du système de refroidissement
WO2019167909A1 (fr) * 2018-03-02 2019-09-06 パナソニックＩｐマネジメント株式会社 Unité d'échangeur de chaleur et climatiseur l'utilisant

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