WO1996020378A1 - Systeme de compression de vapeur - Google Patents

Systeme de compression de vapeur Download PDF

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Publication number
WO1996020378A1
WO1996020378A1 PCT/GB1995/002982 GB9502982W WO9620378A1 WO 1996020378 A1 WO1996020378 A1 WO 1996020378A1 GB 9502982 W GB9502982 W GB 9502982W WO 9620378 A1 WO9620378 A1 WO 9620378A1
Authority
WO
WIPO (PCT)
Prior art keywords
vapour
refrigerant
liquid
reservoir
withdrawal conduit
Prior art date
Application number
PCT/GB1995/002982
Other languages
English (en)
Inventor
Geoffrey Gordon Haselden
Original Assignee
British Technology Group Usa Inc.
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 British Technology Group Usa Inc. filed Critical British Technology Group Usa Inc.
Priority to AU42691/96A priority Critical patent/AU692023B2/en
Priority to BR9510409A priority patent/BR9510409A/pt
Priority to JP8520282A priority patent/JPH11503814A/ja
Priority to DE69508787T priority patent/DE69508787T2/de
Priority to DK95941207T priority patent/DK0795110T3/da
Priority to EP95941207A priority patent/EP0795110B1/fr
Publication of WO1996020378A1 publication Critical patent/WO1996020378A1/fr
Priority to MXPA/A/1997/004716A priority patent/MXPA97004716A/xx
Priority to US09/245,910 priority patent/US6038875A/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
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/315—Expansion valves actuated by floats
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure

Definitions

  • the present invention relates to vapour compression systems such as might be used in, for example, air conditioners, refrigerators and heat pumps, and to components of vapour compression systems such as condensers, evaporators and expansion devices.
  • the invention addresses issues of control of such systems and components.
  • the systems of the invention are suitable for use with mixtures of mutually soluble refrigerant substances with different boiling points (such that the mixture boils or condenses through a temperature range) , and can enable power savings identified through the use of such mixtures to be achieved.
  • Conventional vapour compression systems comprise an evaporator, a condenser, and a compressor for raising the pressure of refrigerant vapour from that which prevails in the evaporator (where the refrigerant takes in heat) to that which prevails in the condenser (where the refrigerant loses heat) .
  • Condensed liquid refrigerant is supplied from the condenser to the evaporator through an expansion device which maintains the pressure difference between the condenser and the evaporator and regulates the flow of refrigerant through the system.
  • the components of such systems are assembled together into integrated sealed units.
  • the efficiency of the system can be increased by using a refrigerant which consists of two or more mutually soluble substances which do not form an azeotrope, and can therefore condense or boil over a range of temperatures.
  • the normal boiling points of the two substances are separated by about 15 to 60°C.
  • the changing boiling point of the mixed refrigerant as it condenses can be arranged to follow closely the temperature of the fluid being heated in the condenser throughout the length of the condenser with the refrigerant and heat trans er fluid flowing in countercurrent relationship with each other. Similar considerations apply to the evaporator. As a result, less power is required in order to drive the compressor because the pressure ratio required of the compressor is reduced.
  • the two phases of the refrigerant flow cocurrently at least through the evaporator and the condenser, so that the separate phases are each well mixed and there is effective mixing between the phases.
  • This condition can be referred to as equilibrium evaporation or condensation. It can arise for example when liquid and vapour flow cocurrently with vapour flowing down the bore of the channel, and liquid flowing along the walls of the evaporator or the condenser, effectively as a varying thickness film around the flowing vapour.
  • the equilibrium conditions of evaporation or condensation are sustained throughout substantially the entire length of the evaporator or condenser (as the case may be) .
  • This can be difficult to achieve because the change in phase is accompanied by a large change in volume, which affects the flow condition of the two phases.
  • a vapour compression system is disclosed in WO-A-92/06339 which incorporates a two-section evaporator which discharges refrigerant into a low pressure receiver.
  • the first (or major) section of the evaporator receives liquid from the condenser through an expansion device, and discharges refrigerant vapour together with a small quantity of liquid into the low pressure receiver, from which vapour is supplied to the compressor.
  • Liquid from the receiver is supplied to the second section of the evaporator and ensures that, under steady state operating conditions of the system, the discharge from the first section of the evaporator remains wet.
  • the system includes a modulating float valve as the expansion device, which opens when the quantity of liquid within or behind it exceeds a pre-determined level, the force required to open the valve being substantially independent of the pressure drop across it.
  • the valve ensures that liquid does not accumulate in the condenser and is supplied steadily to the evaporator.
  • a two-section evaporator such as is incorporated in the system disclosed in O-A-92/06339 can be complicated, especially when liquid refrigerant must be distributed amongst an array of separate tubes fed from the receiver, to maintain an appropriate flow rate of refrigerant through the second section of the evaporator.
  • the distribution should be such that each tube in the array is maintained active, even when the load on the system is light.
  • the invention provides a method of operating a vapour compression system in which a quantity of a refrigerant circulates between at least two pressure levels in a condenser and an evaporator respectively, comprising:
  • vapour withdrawal conduit through which refrigerant vapour is supplied from the receiver to the compressor
  • the method comprising controlling the rate of removal of liquid refrigerant from the receiver in proportion to the amount of refrigerant that is removed from the receiver as vapour, so as to control the wetness of the refrigerant discharged into the receiver from the evaporator to ensure that it is wet under normal operating conditions of the system.
  • the rate of removal of liquid from the receiver is such that the wetness of the refrigerant discharged from the evaporator is not more than about 5% by weight, more preferably not more than about 3.5% by weight, especially not more than about 2.5%, for example between about 1 and 2% by weight.
  • the invention can also ensure that the liquid content in the refrigerant that is supplied to the compressor is controlled so that the amount of liquid is kept steady without significant fluctuations.
  • the wetness of the refrigerant supplied to the compressor can be similar to the wetness of the refrigerant that is discharged from the evaporator to the receiver. However, in many circumstances, the two wetnesses will be different. The differences between the two wetnesses can be accounted for by, for example, evaporation of some of the liquid refrigerant that is removed from the receiver. The differences can also be balanced by the receiver.
  • the invention provides a vapour compression system in which a quantity of a refrigerant circulates between at least two pressure levels in a condenser and an evaporator respectively, comprising: (a) a compressor for increasing the pressure of refrigerant vapour;
  • a receiver into which refrigerant is discharged from the evaporator, with a vapour withdrawal conduit through which vapour is withdrawn from the receiver for supply to the compressor, the receiver including a reservoir into which liquid refrigerant discharged from the evaporator collects, to control supply of liquid refrigerant to the compressor;
  • (g) means for controlling the rate of removal of liquid refrigerant from the reservoir in proportion to the amount of refrigerant that is removed from the receiver as vapour
  • the receiver is arranged so that liquid refrigerant contained in the reservoir is retained in the reservoir at shut-down of the system.
  • the control of the flow of liquid refrigerant from the receiver can be achieved using a liquid withdrawal conduit through which liquid is supplied to the conduit for vapour feed from the receiver to the compressor, due to a pressure drop along the vapour withdrawal conduit downstream of the reservoir.
  • the control can be achieved through use of a receiver into which refrigerant is discharged from the evaporator, which includes:
  • vapour withdrawal conduit through which refrigerant vapour is supplied from the receiver to the compressor
  • the vapour withdrawal conduit being arranged so that the pressure of vapour flowing in it is reduced at a point downstream of the reservoir relative to the pressure in the reservoir, so that liquid refrigerant in the reservoir is drawn into the vapour withdrawal conduit through the liquid withdrawal conduit.
  • a system which includes such a receiver with means for removing a controlled quantity of liquid refrigerant has the advantage that appropriate control of the wetness of the refrigerant supply to the receiver can be achieved without having to include a two-section evaporator.
  • This enables the power consumptions available from use of mixed refrigerants to be obtained, while also minimising equipment costs by avoiding the use of certain complicated multi-tube heat exchanger constructions.
  • By appropriate design of the flow resistance of the vapour and liquid withdrawal conduits including their disposition relative to the reservoir it is possible to ensure that, at steady state operation of the system, the liquid supplied from the receiver to the vapour withdrawal conduit (for supply to the compressor) is such that the refrigerant discharged from the evaporator to the receiver has an appropriate low degree of wetness.
  • Such operation of the system involves optimum use of the heat exchange surfaces of the evaporator, and can allow the advantages of reduced power consumption from the use of mixed refrigerants to be realised.
  • a further advantage that arises from the use of the receiver referred to above is that the optimised use of the heat exchange surfaces of the evaporator is achieved without deterioration of the control due to accumulation of compressor oil.
  • compressor oil can tend to accumulate excessively in the second evaporator section, especially if the velocity of the refrigerant in the second section drops too low as can happen if the tubes in the second section are not appropriately manifolded.
  • Such accumulation of oil can give rise to operational instability, especially when the duty required of the system is reduced or when the system is restarted after a temporary shut-down.
  • the quantity of liquid refrigerant that is removed from the reservoir is controlled so that it is removed at a substan ⁇ tially steady rate.
  • the rate at which liquid refrigerant is removed from the reservoir is preferably determined in relation to the quantity of refrigerant that is removed as vapour; this can be achieved by means of so-called proportionating devices. Details of such devices are set out below.
  • the receiver is arranged such that not more than about 4% by weight of the compressor throughput of refrigerant passes through the liquid withdrawal conduit, the remainder passing through the vapour withdrawal conduit. More pref ⁇ erably, the liquid withdrawal conduit carries not more than about 3% by weight of the compressor throughput. Preferably, the liquid withdrawal conduit carries at least about 0.5% of the compressor throughput, more preferably at least about 1%. For example, the receiver can be arranged so that about 2% by weight of the compressor throughput of refrigerant passes through the liquid withdrawal conduit.
  • the junction between the vapour and liquid withdrawal conduits is at a level that is about or slightly above the level of liquid refrigerant in the reservoir when the system is at steady state operation.
  • This has the advantage that the tendency of liquid refrigerant to drain into the vapour withdrawal conduit during temporary shut down of the system is reduced.
  • the level of the said junction should preferably be only slightly above the steady state liquid level so that the system provides about the same proportion of liquid injected into the liquid withdrawal conduit over a range of duties.
  • the opening for vapour to enter the vapour withdrawal conduit for supply to the compressor is located above the level of the refrigerant liquid in the reservoir, and is preferably at or towards the top of the reservoir.
  • This arrangement has the advantage that it reduces the tendency for liquid refrigerant to be drawn with refrigerant vapour from the reservoir or the discharge from the evaporator or both, and transferred to the compressor suction.
  • the vapour withdrawal conduit will include a section which extends downwardly to a level below the level of liquid in the reservoir when the system is in operation.
  • the opening for liquid to enter the liquid withdrawal conduit to flow to the vapour feed line is located close to the bottom of the reservoir, more preferably in the base of the reservoir, so that liquid will continue to be drawn from the reservoir, even when the level of liquid in the reservoir is low.
  • the opening from the liquid withdrawal conduit into the vapour withdrawal conduit discharges liquid refrigerant into the vapour withdrawal conduit at a point at least about one quarter of the distance across the vapour withdrawal conduit, more preferably at least about one third of that distance.
  • This has the advantage that it encourages the dispersion of the liquid refrigerant into the vapour in droplet form.
  • the cross-sectional area of the vapour withdrawal conduit can be greater at a point downstream of the junction with the liquid withdrawal conduit than at a point upstream of that junction, so that the overall pressure drop in the compressor suction is minimised.
  • the change in cross-sectional area of the vapour withdrawal conduit can be associated with a constriction in the conduit.
  • the constriction can be such that a venturi is provided in the vapour withdrawal conduit.
  • the venturi is mounted horizontally, with its centre-line at about the normal level of liquid in the reservoir when the system is operating in a steady state condition. It has been found that injection of a small quantity of liquid refrigerant into the stream of refrigerant vapour at the throat of a venturi constriction does not significantly affect pressure recovery adversely. Consequently, the pressure drop in the vapour conduit between -li ⁇ the receiver and the compressor suction remains low, providing energy efficient performance.
  • An arrangement using a venturi can lead to liquid refrigerant being removed from the reservoir in proportion to the amount of refrigerant removed as vapour.
  • the liquid withdrawal conduit can include an n-shaped portion with two limbs and a connecting portion extending between them, in which liquid is drawn from the reservoir and made to flow initially upwardly from the reservoir along a first one of the limbs, and downwardly to the junction with the vapour flow conduit along the other of the limbs, thus acting as a syphon.
  • the height of the n-shaped portion of the liquid withdrawal conduit above the normal level of liquid refrigerant in the reservoir will be selected so that the n-shaped portion is at least as high as the highest anticipated level of liquid that will be contained in the reservoir at any time during operation of the system, to ensure that liquid refrigerant will not drain from the reservoir to the compressor, particularly at shut down.
  • the second down-flow limb will preferably include the capillary flow resistance conduit.
  • the reservoir into which refrigerant is discharged from the first evaporator section, will generally be arranged so that refrigerant collected within it has a large surface area.
  • the surface area of liquid refrigerant may be at least about twice the square of the height of the reservoir, preferably, at least about three times the square of that height. This has the advantage that variation in the amount of liquid refrigerant contained in the reservoir does not affect significantly the depth of the liquid and frothing of the refrigerant in the reservoir is less likely to lead to liquid refrigerant being supplied to the compressor. This allows a significant gap to be maintained between the upper surface of collected liquid refrigerant, and the outlet through which vapour is supplied to the compressor, thus minimising and preferably avoiding the possibility of liquid refrigerant being supplied in bulk to the compressor under any possible operating conditions.
  • vapour withdrawal conduit with a venturi provided in it by a constriction, together with a liquid withdrawal conduit which includes an n-shaped portion as described above.
  • the venturi can give rise to a significant pressure difference between the reservoir and the exit from the vapour withdrawal conduit at the junction with the liquid withdrawal conduit.
  • the pressure difference can be arranged such that liquid refrigerant is drawn up the first limb of the n-shaped portion of the liquid withdrawal conduit, at a rate appropriate to maintain the discharge from the evaporator wet as discussed above.
  • This arrangement has the advantage of reduced power loss due to frictional effects in the vapour withdrawal conduit can be reduced, because the pressure loss involved in accelerating the vapour through the throat of the venturi is largely recovered in the divergent diffuser section.
  • the liquid withdrawal conduit is designed to have an overall pressure drop, when supplying liquid refrigerant at the desired flow rate, which equals the overall pressure drop in the exit vapour conduit between the receiver and the point of liquid injection into the liquid conduit.
  • This can be achieved by selection of the configurations of the vapour and liquid withdrawal conduits such that the pressure drop in the vapour withdrawal conduit between the reservoir and the junction with the liquid withdrawal conduit provides a controlled flow of liquid along the liquid withdrawal conduit from the reservoir to the said junction in proportion with the suction flow rate of vapour to the compressor.
  • the selection involves parameters such as cross-sectional areas and of lengths the conduits between the junction between them and the reservoir.
  • the conduit may be in the form of a capillary tube having a small cross-section, along at least a part of its length.
  • the cross-sectional configuration of the vapour withdrawal conduit can differ between the portions upstream and downstream respectively of the junction with the liquid withdrawal conduit.
  • the vapour withdrawal conduit can include a U-shaped portion with two limbs and a connecting portion extending between them.
  • the upstream limb of the U-shaped portion can then provide a downwardly extending section of the vapour withdrawal conduit, from the opening for vapour to enter the vapour feed line for supply to the compressor, above the level of the refrigerant liquid.
  • the junction between the vapour withdrawal conduit and the liquid withdrawal conduit is located in the downstream limb of the U-shaped portion of the vapour withdrawal conduit.
  • the drop in pressure in the vapour withdrawal conduit between the reservoir and the junction with the liquid withdrawal conduit preferably corresponds to a head of liquid refrigerant of between 45 and 200 mm, more preferably between 65 and 160 mm, especially between 80 and 130 mm.
  • the liquid withdrawal conduit may be configured so that liquid contained in it is placed in heat exchange relationship with liquid refrigerant discharged from the condenser so that it is heated by the said liquid refrigerant, between discharge into the conduit from the reservoir and discharge from the conduit into the vapour withdrawal conduit.
  • the liquid withdrawal conduit includes a constriction in it, by which flow of refrigerant along the conduit is controlled. It will be preferred for this refrigerant stream to flow generally upwardly while in heat exchange relationship with the condensate.
  • Examples of materials which are suitable for use as refrigerants in a single refrigerant system include those designated by the marks R22 and R134a.
  • a particular advantage of the system of the invention is that it is well suited to the use of wide boiling non-azeotropic mixed refrigerants in which it is particularly desirable that, at all places within the condenser and the evaporator, liquid and vapour refrigerant flow together co-currently and are in equilibrium, whilst the refrigerant mixture flows essentially counter-currently with the fluid with which it is exchanging heat.
  • This objective can be achieved by the system of the invention, particularly when it includes both an expansion valve where the force required to open it is substantially independent of the pressure drop across it.
  • the vapour compression system of the invention therefore makes possible the power saving which is available from the use of wide boiling mixed refrigerants.
  • further power saving can be achieved because of the ability of the system of the invention to adapt to varying duty, start-up conditions, varying ambient conditions and so on, while operating at optimum efficiency.
  • suitable mixed refrigerants include those designated by the marks R23/R134a and R32/R227.
  • Suitable mixtures of refrigerant substances can have boiling points separated by at least about 10°C, for example at least about 20°C. The difference in boiling points will often be less than about 70°C, preferably less than about 60°C, for example less than about 50°C.
  • the duty performed by the vapour compression system is determined by appropriate adjustment of the flow rate of the refrigerant vapour through the system. This can be achieved in a number of ways: for example, the throughput of the compressor can be adjusted, for example by adjustment of its speed or by unloading one or more cylinders, or more than one compressor may be provided of which some or all may be used according to the quantity of refrigerant required to be circulated. Alternatively, the desired duty may be obtained by selectively switching the compressor on and off as necessary.
  • the control of the compressor through-put may be in response to a detected change in temperature in the medium required to be heated or cooled by the system.
  • a temperature sensor may be used to cause the through-put of a compressor to increase on detecting an increase in temperature of a cold chamber.
  • variable output fans may be used to modulate air flow and to conserve power.
  • FIG. 1 is a schematic illustration of a vapour compression system in accordance with the present invention
  • FIG 2 is a schematic illustration of a receiver suitable for use in the vapour compression system shown in Figure 1;
  • FIG. 3 is a schematic illustration of another embodiment of receiver,-
  • FIG. 4 is a schematic illustration of another vapour compression system in accordance with the present invention.
  • FIG 5 is a schematic illustration of a vapour compression system in which condensed refrigerant is split into two streams which are split between two evaporators.
  • Figure l shows a vapour compression system which comprises a compressor 1 for increasing the pressure of refrigerant vapour, and for forcing the vapour through a first conduit 3 to a condenser 5.
  • the condenser 5 comprises an array of condenser tubes 7, connected both in series and in parallel, which are attached to a plurality of fins which facilitate heat transfer between a cooling medium which flows over the fins and the refrigerant contained within the condenser tube.
  • the medium might be for example air when the system forms part of an air conditioning unit or a refrigerator.
  • the flow directions of the two fluids are essentially countercurrent so this design is suitable for mixed refrigerants as well as pure refrigerants.
  • Refrigerant is discharged from the condenser 5 into a second conduit 11 through a valve 13.
  • a vapour return tube 14 is provided to ensure that the inlet to the valve 13 does not become vapour locked.
  • the valve is arranged to open when the quantity of the condensed liquid refrigerant behind or within it exceeds a pre-determined level.
  • An appropriate valve will be one in which the force required to open it is substantially independent of the pressure drop across it.
  • the refrigerant from the condenser passes to an evaporator 15 through the valve 13 and the second conduit 11.
  • the evaporator 15 comprises an array of tubes connected both in series and in parallel. It further comprises evaporator fins over which a fluid flows so as to transfer heat and to cause the refrigerant to evaporate.
  • the fluid is cooled as a result.
  • the fluid might be, for example, air when the refrigeration system forms part of an air conditioning unit or a refrigerator.
  • the refrigerant is discharged from the evaporator 15 into a receiver 21.
  • Liquid refrigerant discharged from the evaporator collects in the reservoir 23 of the receiver which can provide buffer storage of the liquid refrigerant.
  • a vapour withdrawal conduit 25 extends from the top of the reservoir 23, to convey the major part of the refrigerant as vapour (that is, essentially liquid-free vapour) from the reservoir to the compressor. It will therefore be understood that refrigerant can be separated in the receiver, into liquid and vapour phases.
  • the receiver includes a liquid withdrawal conduit 27 through which liquid refrigerant is supplied from the reservoir into the vapour withdrawal conduit 25.
  • the vapour withdrawal conduit is arranged so that the pressure of vapour flowing in is reduced at a point downstream of the reservoir related to the pressure in the reservoir, so that liquid refrigerant in the reservoir is drawn into the vapour withdrawal conduit 25 through the liquid withdrawal conduit 27 at a rate proportional to the vapour flow.
  • the pressure drop corresponds approximately to a head of liquid refrigerant of about 100 mm.
  • the evaporator, receiver and flow proportioning means in combination ensure that all of the evaporator surface is employed for heat transfer, irrespective of the duty required of the system.
  • the arrangement of vapour and liquid withdrawal conduits in the receiver will ensure that liquid is drawn from the reservoir at a controlled rate. Consequently, the level of liquid in the reservoir will tend to go down.
  • the use of an expansion device which opens when the quantity of condensed liquid refrigerant within or behind it reaches a pre-determined level ensures that liquid cannot accumulate anywhere in the system other than in the reservoir, because the expansion device ensures that liquid does not accumulate in the condenser. Liquid is admitted to the evaporator from the condenser at the rate at which it is produced in the condenser.
  • the system will therefore tend towards a steady state condition in which the liquid refrigerant removed from the reservoir by means of the liquid withdrawal conduit is exactly compensated by the liquid component of the two phase refrigerant discharged into the reservoir from the evaporator.
  • the pressure in the evaporator will adjust itself automatically to achieve this balance. This means that all of the evaporator surface must be wet during such steady state operation.
  • Figures 2 and 3 show constructions of receivers in more detail.
  • the disclosed construction comprises a reservoir 31, into which refrigerant is discharged from the evaporator through a discharge conduit 33.
  • the outlet from the discharge conduit is located towards the top of the reservoir 31.
  • the vapour withdrawal conduit 25 from which the refrigerant vapour is supplied from the reservoir 31 to the compressor is located towards the top of the reservoir.
  • the vapour withdrawal conduit 25 has a U-shaped portion 35 immediately downstream of the reservoir 31.
  • the U-shaped portion comprises first and second limbs 37, 39 and a connecting base portion.
  • the base portion is located at a level well below the normal level 41 of liquid refrigerant contained in the reservoir 31 when the system is running in a steady state condition.
  • the second limb 39 of the U-shaped portion of the vapour withdrawal conduit is flared.
  • a liquid withdrawal conduit 43 extends from the base of the reservoir 31 (well below the normal liquid level 41) and joins the second limb 39 of the U-shaped portion of the vapour withdrawal conduit.
  • the junction between the liquid and vapour withdrawal conduits 25, 43 is at a point just upstream of the flare in the vapour withdrawal conduit.
  • the opening from the liquid withdrawal conduit into the vapour withdrawal conduit discharges liquid refrigerant into the vapour withdrawal conduit at a point about one third of the distance across the vapour withdrawal conduit, so that the liquid refrigerant discharged into the vapour will tend to atomise as it is discharged.
  • the liquid withdrawal conduit 43 is provided by a capillary tube.
  • the diameter and length of the capillary tube are selected so that, for a rate of liquid injection into the vapour withdrawal conduit 25 at the desired ratio (for example about 2% by weight of the throughput of refrigerant through the compressor) , the pressure drop across the liquid withdrawal conduit is equal to the pressure drop in the vapour withdrawal conduit 25.
  • the junction between the vapour and liquid withdrawal conduits is at a level that is about or slightly above the level of liquid refrigerant in the reservoir when the system is at a steady stage operation.
  • FIG. 3 shows an alternative construction of receiver 51. It comprises a reservoir 53 into which refrigerant is discharged from the evaporator through a conduit 55.
  • a vapour withdrawal conduit 57 has an opening towards the top of the reservoir for entry of vapour for supply to the compressor.
  • the vapour withdrawal conduit includes a downwardly extending portion and a portion which extends approximately parallel to the surface of liquid refrigerant contained in the reservoir, at about the level of liquid when the system is running in a steady state condition.
  • a constriction in the vapour withdrawal conduit provides a venturi 59, by which the pressure of the vapour in the vapour withdrawal conduit is decreased and then increased.
  • a liquid withdrawal conduit 61 is provided in the form of an n-shaped tube, with its opening 63 for entry of liquid located towards the base of the reservoir 53.
  • the opening 65 for discharge of liquid refrigerant into the vapour withdrawal conduit 57 is located relative to the venturi 59 such that liquid refrigerant is drawn from the reservoir 53 into the vapour withdrawal conduit through the liquid withdrawal conduit as a result of the pressure changes imposed on vapour in the vapour withdrawal conduit by the venturi.
  • the quantity of liquid that is drawn into the vapour withdrawal conduit is controlled at least partially by the dimensions of the venturi.
  • Figure 4 shows a vapour compression system which comprises a compressor 81 for increasing the pressure of refrigerant vapour, and for forcing the vapour through a first conduit 83 to a condenser 85.
  • Refrigerant is discharged from the condenser into a second conduit 91 through a valve 93.
  • a vapour return tube can be provided to ensure that the inlet to the valve does not become vapour locked.
  • the valve is arranged to open when the quantity of the condensed liquid refrigerant behind or within it exceeds a pre-determined level.
  • the refrigerant from the condenser passes through an evaporator 95 through the valve 93 and the second conduit 91.
  • the refrigerant is discharged from the evaporator 95 into a receiver 101.
  • Liquid refrigerant discharged from the evaporator collects in the reservoir 103 of the receiver.
  • a vapour withdrawal conduit 105 extends from the top of the reservoir, and to convey the major part of the refrigerant as vapour from the reservoir to the compressor.
  • the receiver includes a liquid withdrawal conduit 107 through which liquid refrigerant is supplied from the reservoir into the vapour withdrawal conduit.
  • the liquid conduit includes a constriction 108 which provides a resistance to flow.
  • Liquid refrigerant in the conduit 107 is exposed to heat imparted by liquid refrigerant that is discharged from the condenser as it flows generally upwardly through a heat exchanger 109 (such that the point of entry to the heat exchanger is lower than the point of exit) so that the liquid refrigerant is evaporated, at least partially.
  • the refrigerant from the heat exchanger is then injected into the vapour withdrawal conduit 105 for supply to the compressor.
  • the valve 93 comprises a float 111 which is exposed to saturated liquid refrigerant from the condenser, and valve orifices 113 which are exposed to liquid refrigerant that has been sub-cooled by passage through the heat exchanger 109.
  • the float 111 and the needles by which the valve orifices are closed are connected by an elongate rod 115 in a close fitting tube which are such that the flow of liquid that is permitted between the float chamber and the valve orifices through the resulting annular passage is negligible. Accordingly, saturated refrigerant condensate is caused to flow from the base of the float chamber, through the heat exchanger, into the valve body, where it expands through the orifices of the valve.
  • the evaporator, receiver and flow proportioning means in combination ensure that all of the evaporator surface is effectively employed for heat transfer, irrespective of the duty required of the system.
  • the arrangement of vapour and liquid withdrawal conduits in the receiver will ensure that liquid is drawn from the reservoir at a controlled rate. Consequently, the level of liquid in the reservoir will tend to go down.
  • the use of an expansion device which opens when the quantity of condensed liquid refrigerant within or behind it reaches a pre-determined level ensures that liquid cannot accumulate anywhere in the system other than in the reservoir, because the expansion device ensures that liquid does not accumulate in the condenser.
  • the system will therefore tend towards a steady state condition in which the liquid refrigerant removed from the reservoir by means of the liquid withdrawal conduit is exactly compensated by the liquid component of two phase refrigerant discharged into the reservoir from the evaporator.
  • the pressure in the evaporator will adjust itself automatically to achieve this balance. This means that all of the evaporator surface must be wet during such steady state operation.
  • Figure 5 shows a system which can accommodate a temperature change in the evaporator which is significantly greater than that in the condenser, for example by as much as a factor of two or more.
  • the temperature change across the condenser might be about 10°C (between say 19 and 29°C)
  • the temperature change across the evaporator might be about 22°C (in two stages from say 27 to 16°C and 16 to 5°C) .
  • the system includes a receiver 120 into which liquid is discharged from the condenser 122. Liquid from the reservoir is split between two streams, each of which supplies refrigerant into first and second evaporators 124, 126. Flow of refrigerant into the evaporators is controlled by means of valves 128, 130.
  • Refrigerant is discharged from the evaporators into respective reservoirs 132, 134, in liquid and vapour phases, from which refrigerant vapour is withdrawn for supply to the compressor assembly 136.
  • the reservoirs also supply liquid refrigerant in small controlled quantities to the compressor through liquid withdrawal conduits 138, 140 which join the vapour withdrawal conduits, in the manner described above with reference to Figure 2 or Figure 3.
  • the valves 128, 130 are controlled by level sensors for liquid in the reservoirs.
  • the compressor assembly 136 comprises two separate compressors, which operate at high and low pressures respectively.
  • the use of two compressors in this way facilitates operation of the two evaporators of the system over different temperature profiles.
  • the components are arranged so that the receiver can hold all of the free refrigerant in the system when the reservoirs do not hold any.
  • the reservoirs are sufficiently large that they can hold liquid refrigerant without frothing into the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Magnetic Resonance Imaging Apparatus (AREA)
  • Steroid Compounds (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Compressor (AREA)

Abstract

Un système de compression de vapeur dans lequel une certaine quantité de réfrigérant circule entre au moins deux niveaux de pression, c'est-à-dire dans un condensateur et un évaporateur, comprend un compresseur (1) conçu pour augmenter la pression de la vapeur de réfrigérant; un condensateur (5) pour la vapeur de réfrigérant à haute pression arrivant du compresseur; un dispositif d'expansion (13) tel qu'une vanne maintenant un différentiel de pression entre le condensateur et l'évaporateur, pour réguler l'évacuation du réfrigérant liquide hors du condensateur en fonction du volume du réfrigérant liquide qui est à l'intérieur ou derrière celui-ci; un évaporateur (15) pour le réfrigérant liquide arrivant du condensateur; un collecteur (21) dans lequel est évacué le réfrigérant de l'évaporateur, avec une conduite (25) d'évacuation de la vapeur par laquelle la vapeur est évacuée hors du collecteur pour alimenter le compresseur, le collecteur comprenant un réservoir (23) pour recueillir le réfrigérant liquide évacué de l'évaporateur, afin de réguler l'alimentation en réfrigérant liquide du compresseur; une conduite (27) d'évacuation de liquide par laquelle le réfrigérant liquide est amené du réservoir dans la conduite d'évacuation de la vapeur; et un moyen (35) pour réguler la vitesse d'évacuation du réfrigérant liquide hors du réservoir proportionnellement à la quantité de réfrigérant évacuée du collecteur sous forme de vapeur. Le système permet d'ajuster l'humidité du réfrigérant évacué dans le collecteur depuis l'évaporateur pour que ce réfrigérant soit humide dans des conditions opératoires normales du système, afin d'optimiser l'utilisation des surfaces d'échange thermique du condensateur et de l'évaporateur.
PCT/GB1995/002982 1994-12-23 1995-12-20 Systeme de compression de vapeur WO1996020378A1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
AU42691/96A AU692023B2 (en) 1994-12-23 1995-12-20 Vapour compression system
BR9510409A BR9510409A (pt) 1994-12-23 1995-12-20 Sistema de compressÆo de vapor
JP8520282A JPH11503814A (ja) 1994-12-23 1995-12-20 蒸気圧縮システム
DE69508787T DE69508787T2 (de) 1994-12-23 1995-12-20 Dampfkompressionssystem und verfahren zum betreiben desselben
DK95941207T DK0795110T3 (da) 1994-12-23 1995-12-20 Dampkompressionssystem
EP95941207A EP0795110B1 (fr) 1994-12-23 1995-12-20 Systeme de compression de vapeur et methode d'utilisation de celui-ci
MXPA/A/1997/004716A MXPA97004716A (en) 1994-12-23 1997-06-23 Va compression system
US09/245,910 US6038875A (en) 1994-12-23 1999-02-08 Vapor compression system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB9426207.8A GB9426207D0 (en) 1994-12-23 1994-12-23 Vapour compression system
GB9426207.8 1994-12-23

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US87855697A Continuation 1994-12-23 1997-06-19

Publications (1)

Publication Number Publication Date
WO1996020378A1 true WO1996020378A1 (fr) 1996-07-04

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1995/002982 WO1996020378A1 (fr) 1994-12-23 1995-12-20 Systeme de compression de vapeur

Country Status (13)

Country Link
EP (1) EP0795110B1 (fr)
JP (1) JPH11503814A (fr)
CN (1) CN1175304A (fr)
AT (1) ATE178398T1 (fr)
AU (1) AU692023B2 (fr)
BR (1) BR9510409A (fr)
CA (1) CA2208536A1 (fr)
DE (1) DE69508787T2 (fr)
DK (1) DK0795110T3 (fr)
ES (1) ES2130687T3 (fr)
GB (1) GB9426207D0 (fr)
IL (1) IL116497A (fr)
WO (1) WO1996020378A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1705437A1 (fr) * 2005-03-23 2006-09-27 Luk Fahrzeug-Hydraulik GmbH & Co. KG Procédé de lubrification pour le compresseur d'un climatiseur
WO2008124637A2 (fr) * 2007-04-05 2008-10-16 Johnson Controls Technology Company Echangeur de chaleur
ES2318941A1 (es) * 2006-02-21 2009-05-01 Aproalia, S.L. Sistema combinado de refrigeracion y climatizacion.
EP2428750A3 (fr) * 2010-07-28 2014-05-28 LG Electronics Inc. Réfrigérateur et son procédé de commande
EP2772705A1 (fr) * 2013-02-28 2014-09-03 LG Electronics Inc. Accumulateur pour un système de climatisation

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3582185B2 (ja) * 1995-10-24 2004-10-27 ダイキン工業株式会社 熱搬送装置
DE102008011255A1 (de) * 2008-02-27 2009-09-03 Valeo Klimasysteme Gmbh Ejektorzyklus mit einphasigem Strahl
CN102032728B (zh) * 2010-12-09 2012-03-14 东南大学 一种自动调节制冷工质流量的装置
DE102013101721A1 (de) * 2013-02-21 2014-09-18 Halla Visteon Climate Control Corporation Vorrichtung zur Aufteilung eines Kältemittelmassenstromes
JP7038300B2 (ja) * 2017-07-27 2022-03-18 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置
DE102020120400A1 (de) 2020-08-03 2022-02-03 Audi Aktiengesellschaft Kältemittelspeicher für ein Kältemittel mit steuerbarem Auslass; Kältekreis; Kraftfahrzeug sowie Verfahren

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US2432859A (en) * 1944-04-10 1947-12-16 Detroit Lubricator Co Refrigerant flow controlling means
US2953906A (en) * 1955-05-09 1960-09-27 Lester K Quick Refrigerant flow control apparatus
US3111819A (en) * 1961-11-03 1963-11-26 Bell & Gossett Co Evaporator with oil return means
US3370440A (en) * 1966-01-06 1968-02-27 Ac & R Components Inc Suction accumulator
US3600904A (en) * 1969-05-27 1971-08-24 Emerson Electric Co Control for refrigeration system
US3735603A (en) * 1971-08-12 1973-05-29 Dunham Bush Inc Liquid refrigerant feed control
DE2602582A1 (de) * 1976-01-21 1977-10-13 Schultze Erich Kg Fluessigkeitsabscheider mit absaugduese
GB1502607A (en) * 1975-05-19 1978-03-01 Star Refrigeration Low pressure receivers for a refrigerating system
EP0104750A2 (fr) * 1982-09-23 1984-04-04 Richard John Avery, Jr. Accumulateur de réfrigérant et dispositif et procédé d'introduction de réfrigérant dans un système de réfrigération à compression
GB2164736A (en) * 1984-09-17 1986-03-26 Tyler Refrigeration Gmbh Means for protecting compressors of refrigeration plants and heat pumps
DE3545013A1 (de) * 1985-12-19 1986-12-18 Audi AG, 8070 Ingolstadt Kaelteanlage, insbesondere klimaanlage fuer personenfahrzeuge
US5027602A (en) * 1989-08-18 1991-07-02 Atomic Energy Of Canada, Ltd. Heat engine, refrigeration and heat pump cycles approximating the Carnot cycle and apparatus therefor
WO1992006339A1 (fr) * 1990-10-04 1992-04-16 The University Of Leeds Systeme de compression de vapeur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1884186A (en) * 1926-12-06 1932-10-25 Servel Inc Refrigeration
US2432859A (en) * 1944-04-10 1947-12-16 Detroit Lubricator Co Refrigerant flow controlling means
US2953906A (en) * 1955-05-09 1960-09-27 Lester K Quick Refrigerant flow control apparatus
US3111819A (en) * 1961-11-03 1963-11-26 Bell & Gossett Co Evaporator with oil return means
US3370440A (en) * 1966-01-06 1968-02-27 Ac & R Components Inc Suction accumulator
US3600904A (en) * 1969-05-27 1971-08-24 Emerson Electric Co Control for refrigeration system
US3735603A (en) * 1971-08-12 1973-05-29 Dunham Bush Inc Liquid refrigerant feed control
GB1502607A (en) * 1975-05-19 1978-03-01 Star Refrigeration Low pressure receivers for a refrigerating system
DE2602582A1 (de) * 1976-01-21 1977-10-13 Schultze Erich Kg Fluessigkeitsabscheider mit absaugduese
EP0104750A2 (fr) * 1982-09-23 1984-04-04 Richard John Avery, Jr. Accumulateur de réfrigérant et dispositif et procédé d'introduction de réfrigérant dans un système de réfrigération à compression
GB2164736A (en) * 1984-09-17 1986-03-26 Tyler Refrigeration Gmbh Means for protecting compressors of refrigeration plants and heat pumps
DE3545013A1 (de) * 1985-12-19 1986-12-18 Audi AG, 8070 Ingolstadt Kaelteanlage, insbesondere klimaanlage fuer personenfahrzeuge
US5027602A (en) * 1989-08-18 1991-07-02 Atomic Energy Of Canada, Ltd. Heat engine, refrigeration and heat pump cycles approximating the Carnot cycle and apparatus therefor
WO1992006339A1 (fr) * 1990-10-04 1992-04-16 The University Of Leeds Systeme de compression de vapeur

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1705437A1 (fr) * 2005-03-23 2006-09-27 Luk Fahrzeug-Hydraulik GmbH & Co. KG Procédé de lubrification pour le compresseur d'un climatiseur
ES2318941A1 (es) * 2006-02-21 2009-05-01 Aproalia, S.L. Sistema combinado de refrigeracion y climatizacion.
WO2008124637A2 (fr) * 2007-04-05 2008-10-16 Johnson Controls Technology Company Echangeur de chaleur
WO2008124637A3 (fr) * 2007-04-05 2008-12-18 Johnson Controls Tech Co Echangeur de chaleur
US9410709B2 (en) 2007-04-05 2016-08-09 Johnson Controls Technology Company Multichannel condenser coil with refrigerant storage receiver
EP2428750A3 (fr) * 2010-07-28 2014-05-28 LG Electronics Inc. Réfrigérateur et son procédé de commande
US9146046B2 (en) 2010-07-28 2015-09-29 Lg Electronics Inc. Refrigerator and driving method thereof
EP3998438A1 (fr) * 2010-07-28 2022-05-18 LG Electronics Inc. Réfrigérateur et son procédé de commande
EP2772705A1 (fr) * 2013-02-28 2014-09-03 LG Electronics Inc. Accumulateur pour un système de climatisation
US9377248B2 (en) 2013-02-28 2016-06-28 Lg Electronics Inc. Integrated accumulator and receiver having a vibration damping guide tube

Also Published As

Publication number Publication date
DK0795110T3 (da) 1999-10-18
IL116497A (en) 2000-07-26
ES2130687T3 (es) 1999-07-01
MX9704716A (es) 1997-10-31
DE69508787T2 (de) 1999-08-05
EP0795110A1 (fr) 1997-09-17
AU4269196A (en) 1996-07-19
AU692023B2 (en) 1998-05-28
IL116497A0 (en) 1996-03-31
BR9510409A (pt) 1999-08-24
ATE178398T1 (de) 1999-04-15
GB9426207D0 (en) 1995-02-22
JPH11503814A (ja) 1999-03-30
EP0795110B1 (fr) 1999-03-31
CN1175304A (zh) 1998-03-04
DE69508787D1 (de) 1999-05-06
CA2208536A1 (fr) 1996-07-04

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