EP2718642A1 - A multi-evaporator refrigeration circuit - Google Patents

A multi-evaporator refrigeration circuit

Info

Publication number
EP2718642A1
EP2718642A1 EP12796452.6A EP12796452A EP2718642A1 EP 2718642 A1 EP2718642 A1 EP 2718642A1 EP 12796452 A EP12796452 A EP 12796452A EP 2718642 A1 EP2718642 A1 EP 2718642A1
Authority
EP
European Patent Office
Prior art keywords
liquid
refrigeration circuit
evaporator
suction
receiver
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP12796452.6A
Other languages
German (de)
French (fr)
Other versions
EP2718642A4 (en
EP2718642B1 (en
Inventor
Sergio Girotto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Huurre Group Oy
ENEX Srl
Original Assignee
Huurre Group Oy
ENEX Srl
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
Priority claimed from IT000077A external-priority patent/ITTV20110077A1/en
Priority claimed from IT000141A external-priority patent/ITTV20110141A1/en
Priority claimed from IT000010A external-priority patent/ITTV20120010A1/en
Application filed by Huurre Group Oy, ENEX Srl filed Critical Huurre Group Oy
Priority to PL12796452T priority Critical patent/PL2718642T3/en
Publication of EP2718642A1 publication Critical patent/EP2718642A1/en
Publication of EP2718642A4 publication Critical patent/EP2718642A4/en
Application granted granted Critical
Publication of EP2718642B1 publication Critical patent/EP2718642B1/en
Priority to HRP20161607TT priority patent/HRP20161607T1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2600/2521—On-off valves controlled by pulse signals
    • 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
    • F25B2700/04—Refrigerant level
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit

Definitions

  • the present invention relates to a multi-evaporator refrigeration circuit, deployed both in low pressure and intermediate pressure receiver versions, adapted to use carbon dioxide as a refrigerant.
  • the refrigeration circuit comprises at least a compressor; a condenser/gas cooler; a first throttling valve; a liquid/vapour separator; a pressure limiting valve; a liquid level sensing device; at least one evaporator; and a suction receiver, wherein the refrigeration circuit is adapted to feed the liquid refrigerant to the at least one evaporator from said separator through a second throttling device.
  • the present invention also relates to the extension of the above circuit to a booster concept, where two different evaporation levels are made available, comprising the booster concept, beside the above components, at least a low temperature compressor; at least one evaporator; and a regenerative heat exchanger; wherein the method comprises feeding the liquid refrigerant to the at least one evaporator from said separator through the regenerative heat exchanger and a second throttling device.
  • TV201 1 A000141 present a mode of embodiment of a refrigeration system of this type that is characterized by a degree of overfeeding of the evaporators, but without the use of a circulation pump and without direct control of the superheating, that is the difference between refrigerant temperature at evaporator outlet and saturated temperature at evaporating pressure. It can thus obtain a greater efficiency of heat transfer in the evaporators without the complication of using a circulation pump, as well as a higher saturated suction temperature for a given temperature of fluid or body to be cooled, and consequently a higher efficiency of the whole system.
  • One of the key points of the invention as described in the aforementioned patent applications is a circuit arrangement such as to allow the transfer of excess of liquid, i.e. the flow rate circulated in evaporators, but not evaporated, from the low pressure receiver into the liquid / vapour separator at medium pressure.
  • the refrigeration system described in the two patent applications mentioned above provides for use of a single cold temperature.
  • usage of both medium temperatures MT, i.e. temperatures in the neighborhood of 0 ° C, and low temperatures BT, i.e. temperatures in the neighborhood of -30 ° C are present. It is therefore appropriate to extend the scope of the previously described refrigeration system also to the case where two temperature levels are present, possibly with the most economical and efficient way available when using CO 2 as a refrigerant, i.e. the configuration called "booster".
  • This configuration using the two levels of evaporation temperatures is made with two different compressors or groups of compressors.
  • a refrigeration circuit adapted to use carbon dioxide as a liquid refrigerant.
  • the refrigeration circuit is primarily characterized in that the refrigeration circuit further comprises at least one ejector comprising a suction port, in parallel to the first throttling valve; and that the refrigeration circuit is adapted to drive cold liquid from the suction receiver to the suction port of said at least one ejector, being activated for direct charge transfer, for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of a first control valve in the line from the suction receiver to the suction port of the at least one ejector, based on a maximum level signal generated by the liquid level sensing device, whenever the level of liquid refrigerant in said suction receiver is above a set maximum level.
  • a method in a multi-evaporator refrigeration circuit adapted to use carbon dioxide as a liquid refrigerant.
  • the method is primarily characterized in that the refrigeration circuit further comprises at least one ejector comprising a suction port included in parallel to the first throttling valve; wherein the method further comprises direct driving of cold liquid from the suction receiver to the suction port of said at least one ejector for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of one valve in the line from the low pressure receiver to the suction port of the ejector, based on a maximum level signal generated by the liquid level sensing device, whenever the level of liquid in said suction receiver is above a set maximum level.
  • a refrigeration circuit of low pressure receiver type primarily characterized in that the refrigeration circuit further comprises at least one ejector, comprising a suction port, in parallel to the first throttling valve; and that the refrigeration circuit is adapted to drive cold liquid from the suction receiver to the suction port of said at least one ejector, being activated for the charge transfer for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of a first control valve in the line from the suction receiver to the suction port of the at least one ejector, based on a minimum level signal generated by the liquid level sensing device, whenever the level of liquid refrigerant in said liquid vapour separator is below a set minimum level.
  • the refrigeration circuit further comprises at least one ejector comprising a suction port included in parallel to the first throttling valve; wherein the method further comprises direct driving of cold liquid from the suction receiver to the suction port of said at least one ejector for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of a first control valve in the line from the low pressure receiver to the suction port of the at least one ejector, based on a minimum level signal generated by the liquid level sensing device, whenever the level of liquid refrigerant in said liquid vapour separator is below a set minimum level.
  • a further mean of a charge transfer between the suction receiver and the liquid/vapour separator, of indirect type, is considered.
  • FIG. 1 illustrates a diagram of a refrigeration system for medium temperature with recirculation flow according to an example embodiment using an indirect charge transfer method
  • Fig. 2 illustrates a diagram of a refrigeration system for medium temperature with recirculation flow according to an example embodiment using a direct charge transfer method
  • Fig. 3 illustrates another example embodiment of a refrigeration system for medium temperature with recirculation flow comprising a charge transfer device
  • Fig. 4 illustrates another example embodiment of a refrigeration system for medium temperature with recirculation flow comprising a charge transfer device
  • Fig. 5 shows a diagram of a system booster type according to an example embodiment
  • Fig. 6 illustrates an example of connection and control means of an evaporator with relative supply valve and its control device
  • Fig. 7 is an example of a control algorithm of a feeding valve to the evaporator referred to in Fig. 6;
  • Fig. 8a illustrates an example of the algorithm for adjusting the valve to control the pressure difference with a level switch as a level detection device on the suction receiver
  • Fig. 8b illustrates an example of the algorithm for adjusting the valve to control the pressure difference with a level detection device on the suction receiver comprising a continuous level measurement and analog output
  • Fig. 8c illustrates an example of the algorithm for adjusting the valve to control the pressure difference with a level detection device on the liquid/vapour separator comprising a continuous level measurement and analog output.
  • - 19 a low temperature compressor or compressors
  • a liquid / vapour separator 5 Downstream of the valve 4 is present a liquid / vapour separator 5 having the function of separating the flash vapour, produced by the first expansion through the valve 4, from the liquid intended to supply the evaporators.
  • the refrigerant leaving the condenser / gas cooler 2 is entered, prior to entry to the valve 4, in a regenerative exchanger 3 in which the refrigerant is cooled by heat exchange with the fluid contained in the suction receiver 8.
  • a certain flow rate of refrigerant liquid contained in said receiver 8 will circulate due to the density difference in the primary heat exchanger 3, connected for thermosiphon-like circulation, and return to the form of vapour at the top of the suction receiver 8 itself.
  • the resulting cooling of the fluid in one circuit of heat exchanger 3 will produce a reduction of the amount of injected vapour in the liquid / vapour separator 5 and, at the same flow rate ml output from the liquid / vapour separator 5 will result in an increase of the liquid fraction in the separator 5 itself.
  • a virtual transfer of charge from the receiver 8 to the liquid/vapour separator 5 is obtained in this way.
  • a pressure-regulating valve 9 will limit the absolute or differential pressure in the separator 5 by draining a vapour flow rate in the suction receiver 8, and the difference in pressure between the liquid/vapour separator 5 and the suction receiver 8 will be adjusted so as to have a pressure differential sufficient to circulate the refrigerant in the evaporators.
  • the refrigerant leaving the condenser / gas cooler 2 is entered to the valve 4 and to at least one ejector 14, these components being installed in parallel. Downstream of the valve 4 and ejector 14 is present the liquid / vapour separator 5 having the function of separating the flash vapour, produced by the first expansion through the valve 4, from the liquid intended to feed the evaporators.
  • the pressure-regulating valve 9 will limit the absolute or differential pressure in the liquid/vapour separator 5 by draining a vapour flow rate in the suction receiver 8, and the difference in pressure between the liquid/vapour separator 5 and the suction receiver 8 will be adjusted so as to have a pressure differential sufficient to circulate the refrigerant in the evaporators.
  • a certain flow rate of liquid contained in said suction receiver 8 will return into the liquid/vapour separator 5 through a port 15 of an ejector 14. A direct transfer of charge from the suction receiver 8 to the liquid/vapour separator 5 is obtained in this way.
  • the interface of the regulating and charge transfer device of X can be traced to a single module of a block diagram with three inputs and two outputs, as shown in fig. 3.
  • the three input pipes are identified as inlet pipe of the fluid coming from the heat exchanger 2 and indicated with a), the inlet pipe of the flash vapour from the liquid/vapour separator 5 and indicated with b), the inlet pipe of the liquid from the suction receiver 8 and denoted by c) while the outlet pipes are those of release of the fluid to the separator 5 and the input of the flash vapour to the suction receiver 8, respectively indicated with d) and e).
  • FIG. 5 A possible configuration of the booster according to an embodiment of the invention is shown in Figure 5.
  • the medium temperature compressor (compressors) 1 sucks refrigerant vapour from the suction receiver 8 and compress it to the high pressure of the cycle in the heat exchanger condenser / gas cooler 2, in which the refrigerant is cooled with the external air or other fluid.
  • the pressure in this heat exchanger 2 is either directly or indirectly controlled by both the flow rate and the temperature of the cooling fluid and via a regulating valve 4 located on the pipe downstream of the heat exchanger 2 and included in the regulating and charge transfer device X.
  • Said device X also performs the fine adjustment of the high pressure, the control of pressure in the liquid/vapour separator 5 and the transfer of the flow rate of refrigerant not evaporated from the suction receiver 8 into the liquid/vapour separator 5 according to the technique described above.
  • a low temperature regenerative heat exchanger 16 Downstream of the liquid/vapour separator 5 is installed a low temperature regenerative heat exchanger 16, one circuit of which, defined as the primary circuit, is configured for the circulation of the entire liquid flow ml , intended to supply both the medium temperature evaporators 7, m1_MT, and the low temperature evaporators 18, m1_BT.
  • the adjustment of the flow rate through the evaporators will be made, for example but not exclusively with a controller Rp that regulates the opening of valves 6 and 17 according to the temperature TA of air or fluid to be cooled, always as an example, as shown in Fig. 5 and 6, relating to a generic group feeding valve / evaporator MT indicated with 6n and 7n.
  • the controller Rp adjust the ratio Time ON/Time cycle D to maintain it proportional to the offset of T compared to set SO of the medium.
  • a larger deviation of the value T-SO, provided T>S0, will give a higher ratio Time ON/Time cycle D.
  • feeding valves 6 and 17 can simply be adjusted in ON / OFF and a balancing valve located downstream of said valves 6 and 17 can be used to limit the maximum flow rate.
  • the refrigerant leaving the primary circuit of the low temperature regenerative heat exchanger 16 is partially directed in the liquid line of supply of the medium temperature evaporators 7 through the valves 6, and indicated with m1_MT, and in part is placed in the liquid line of the evaporators 18 through the BT supply valves of the low temperature evaporators 17, and indicated with m1_BT.
  • Both in the medium temperature evaporators 7 and in the low temperature evaporators 18 a fraction of the fluid, if not all, will evaporate extracting heat from substance or fluid to be cooled.
  • the fluid flow which may not have been evaporated in the medium temperature evaporators, ml__MT, will be drained together with the vapour flow rate mV_MT in the receiver 8 through the suction pipe.
  • m1_MT ml__MT + mV_MT.
  • the fluid flow which may not have been evaporated in the low temperature evaporators 18, ml__BT, will be drained together with the vapour flow rate mV_BT in the secondary circuit of the heat exchanger 16 toward the suction of the low temperature compressor or compressors 19.
  • m1_BT ml__BT + mV_BT.
  • the ability to evaporate the amount ml__BT would be at any event sufficient due to the high temperature difference, of the order of 30K, between the liquid in the primary circuit of the exchanger 16 and the mixture liquid / vapour in the secondary circuit of the same and said temperature difference makes it possible, without risk of suction of liquid into the low temperature compressor 19, a circulation ratio RC in the evaporators of BT section of about 1 .25.
  • the low temperature compressor 19 will send the flow of refrigerant compressed in the suction receiver 8.
  • a further problem to be solved with the present invention is to define a method of protection to prevent an excessive amount of liquid to flow through the medium temperature evaporators 7 in the case where the flow rate regulation in these medium temperature evaporators 7 is not optimized due to inaccurate setting of the control system of the valves 6, or due to other unforeseen situations.
  • suction receiver 8 or liquid/vapour separator 5 is used for containment of liquid charge not active in the refrigeration circuit.
  • a level switch 22 or other device is installed on the suction receiver 8 which allows to detect an excessive accumulation of liquid refrigerant. If the refrigerant level detection device 22, e.g. a switch detects an excess of refrigerant in said suction receiver 8, an indication of an unsuitable flow regulation in the evaporators 7 is provided, wherein the pressure regulating valve 9, as shown in fig. 4, said pressure regulating valve 9 being included in the charge transfer device X and shown in both fig. 8a and fig. 8b, limits the differential pressure between the liquid/vapour separator 5 and the suction receiver 8 to a value lower than that normally regulated.
  • valve 9 when the switch or the signal level 22 on the suction receiver 8 detects the presence of excess liquid the valve 9 will act directly or indirectly on the relevant signal.
  • the pressure regulating valve 9 may either be mechanically or electrically operated.
  • the pressure regulating valve 9, through a proper control system, shown schematically in Fig.
  • an increase in liquid level in the suction receiver 8 is detected by the refrigerant level detection device 22 and via a regulator RL will control the opening degree of the valve 9 to decrease the pressure difference between the suction receiver 8 and the liquid/vapour separator 5 from the value ⁇ 1 to the value ⁇ 2.
  • Fig. 8b which refers to an alternative to the previous embodiment
  • an increase in the level of liquid in the suction receiver 8 is detected by the refrigerant level detection device 22, which will send a signal proportional to the level to the controller RL which will control the opening degree of the valve 9 so as to vary the pressure difference between the suction receiver 8 and the liquid/vapour separator 5, for example but not exclusively, according to the function represented in fig. 8b which graphically shows a proportional correspondence of differential pressure between upstream and downstream of the valve 9 with liquid level in the suction receiver 8, the upper limit of differential pressure ⁇ 1 obtained with liquid level less than or equal to L M IN, and with the lower limit of differential pressure ⁇ 2, obtained with a level equal to or greater than L M AX-
  • the pressure in the liquid/vapour separator 5 is adjusted approximately to approximately 34 bar while the suction pressure, and then the pressure existing in the suction receiver 8 is of about 29 bar.
  • the pressure difference between the liquid/vapour separator 5 and the suction receiver 8, ⁇ 1 is therefore of 5 bar, and on the basis of this design value are calculated by the valve 6 is selected to provide 100% of the maximum required flow.
  • a level switch 23 or other device will be on the liquid/vapour separator 5 which allows to detect a too low level of liquid refrigerant which may bring to starving of the system. If the refrigerant level detection device 23, e.g. a switch detects a shortage of refrigerant in said liquid/vapour separator 5, which is an indication of excess of mass flow through evaporators 7, the valve 9 will reduce the pressure difference using a control logic reversed to that previously described, in the sense that a lower level will bring to a lower pressure difference between the liquid/vapour separator 5 and the suction receiver 8. The above logic is shown in fig. 8c.
  • One valve 10 can be used to stop the charge transfer in case both ⁇ and liquid level in the liquid/vapour separator 5 are at their maximum, and a valve 13 can be arranged to open as a further protection means.
  • An example embodiment comprising valve 13 is shown in fig. 1 .
  • the present invention is not limited solely to the above described embodiments but it can be varied within the scope of the appended claims.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

The invention relates to a multi-evaporator refrigeration circuit of low pressure receiver type adapted to use carbon dioxide as a refrigerant, comprising at least a compressor (1); a condenser/gas cooler (2); a first throttling valve (4); a liquid/vapour separator (5); a pressure limiting valve (9); a liquid level sensing device (22); at least one evaporator (7); and a suction receiver (8). The refrigeration circuit is adapted to feed the liquid refrigerant to the at least one evaporator (7) from said separator (5) through a second throttling device (6). In the refrigeration circuit at least one ejector (14) comprising a suction port (15) is included in parallel to the first throttling valve (4). The refrigeration circuit is adapted to drive cold liquid from the suction receiver (8) to the suction port (15) of said at least one ejector (14), being the charge transfer activated by the flow transfer, for maintaining a sufficient liquid level in the separator (5) even if the mass flow circulating in evaporators (7) is higher than the mass flow evaporated, through an opening of one valve (10) in the line from the suction receiver (8) to the suction port (15) of the ejector (14), based on a maximum level signal generated by the liquid level sensing device (22), whenever the level of liquid in said suction receiver (8) is above a maximum set level. The present invention also relates to a method in a booster refrigeration circuit including a low temperature circuit, where the liquid mass flow exiting evaporator(s) 18 is evaporated in one circuit of one heat exchanger 16, which other circuit is arranged for circulation of the whole liquid mass flow feeding both MT and LT evaporators.

Description

A multi-evaporator refrigeration circuit
Field of the Invention
The present invention relates to a multi-evaporator refrigeration circuit, deployed both in low pressure and intermediate pressure receiver versions, adapted to use carbon dioxide as a refrigerant. The refrigeration circuit comprises at least a compressor; a condenser/gas cooler; a first throttling valve; a liquid/vapour separator; a pressure limiting valve; a liquid level sensing device; at least one evaporator; and a suction receiver, wherein the refrigeration circuit is adapted to feed the liquid refrigerant to the at least one evaporator from said separator through a second throttling device. The present invention also relates to the extension of the above circuit to a booster concept, where two different evaporation levels are made available, comprising the booster concept, beside the above components, at least a low temperature compressor; at least one evaporator; and a regenerative heat exchanger; wherein the method comprises feeding the liquid refrigerant to the at least one evaporator from said separator through the regenerative heat exchanger and a second throttling device.
Background of the Invention
In many refrigeration systems of direct expansion, even among those using carbon dioxide (R744) as refrigerant, it is desirable to control the flow of refrigerant through the evaporator(s) in order to obtain a circulation ratio RC, i.e. the ratio between the flow rate through evaporators and the amount evaporated, slightly higher than the unit value. In this way it may be possible to obtain both the maximum use of the heat transfer surface and a smaller difference in temperature between the refrigerant and the fluid or object to be cooled and therefore a higher overall efficiency of the system. The above is possible, for example with forced circulation by a pump. The method is however expensive and complex. Italian patent applications no. TV201 1 A000077 and no. TV201 1 A000141 present a mode of embodiment of a refrigeration system of this type that is characterized by a degree of overfeeding of the evaporators, but without the use of a circulation pump and without direct control of the superheating, that is the difference between refrigerant temperature at evaporator outlet and saturated temperature at evaporating pressure. It can thus obtain a greater efficiency of heat transfer in the evaporators without the complication of using a circulation pump, as well as a higher saturated suction temperature for a given temperature of fluid or body to be cooled, and consequently a higher efficiency of the whole system.
One of the key points of the invention as described in the aforementioned patent applications is a circuit arrangement such as to allow the transfer of excess of liquid, i.e. the flow rate circulated in evaporators, but not evaporated, from the low pressure receiver into the liquid / vapour separator at medium pressure.
The refrigeration system described in the two patent applications mentioned above provides for use of a single cold temperature. In many applications, for example in supermarkets, usage of both medium temperatures MT, i.e. temperatures in the neighborhood of 0 ° C, and low temperatures BT, i.e. temperatures in the neighborhood of -30 ° C, are present. It is therefore appropriate to extend the scope of the previously described refrigeration system also to the case where two temperature levels are present, possibly with the most economical and efficient way available when using CO2 as a refrigerant, i.e. the configuration called "booster". This configuration using the two levels of evaporation temperatures is made with two different compressors or groups of compressors. The suction from the lower pressure compressor or group of compressors compress(es) the vapour to the suction pressure of the compressor or the group compressor to the upper level which coincides with the evaporation temperature of the medium temperature. Said compressor at a higher level of pressure then will provide both the removal of the vapour produced in evaporators for medium temperature and also compression to the higher pressure of the cycle of the fluid evaporated at the lower temperature level and compressed by the low pressure stage compressors. Such embodiment is the object of the Italian patent application TV2012A000010. Summary of the Invention
In the following there is described a system-type refrigeration booster, which allows operation with excess of mass flow in the evaporators of both of low temperature and of medium-temperature, describing in detail some embodiments of a safe and simple refrigerator circuit and a method in a refrigerator circuit.
According to a first aspect of the present invention there is provided a refrigeration circuit adapted to use carbon dioxide as a liquid refrigerant. The refrigeration circuit is primarily characterized in that the refrigeration circuit further comprises at least one ejector comprising a suction port, in parallel to the first throttling valve; and that the refrigeration circuit is adapted to drive cold liquid from the suction receiver to the suction port of said at least one ejector, being activated for direct charge transfer, for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of a first control valve in the line from the suction receiver to the suction port of the at least one ejector, based on a maximum level signal generated by the liquid level sensing device, whenever the level of liquid refrigerant in said suction receiver is above a set maximum level.
According to a second aspect of the present invention there is provided a method in a multi-evaporator refrigeration circuit adapted to use carbon dioxide as a liquid refrigerant. The method is primarily characterized in that the refrigeration circuit further comprises at least one ejector comprising a suction port included in parallel to the first throttling valve; wherein the method further comprises direct driving of cold liquid from the suction receiver to the suction port of said at least one ejector for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of one valve in the line from the low pressure receiver to the suction port of the ejector, based on a maximum level signal generated by the liquid level sensing device, whenever the level of liquid in said suction receiver is above a set maximum level. According to a third aspect of the present invention there is provided a refrigeration circuit of low pressure receiver type primarily characterized in that the refrigeration circuit further comprises at least one ejector, comprising a suction port, in parallel to the first throttling valve; and that the refrigeration circuit is adapted to drive cold liquid from the suction receiver to the suction port of said at least one ejector, being activated for the charge transfer for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of a first control valve in the line from the suction receiver to the suction port of the at least one ejector, based on a minimum level signal generated by the liquid level sensing device, whenever the level of liquid refrigerant in said liquid vapour separator is below a set minimum level. According to a fourth aspect of the present invention there is provided a method primarily characterized in that the refrigeration circuit further comprises at least one ejector comprising a suction port included in parallel to the first throttling valve; wherein the method further comprises direct driving of cold liquid from the suction receiver to the suction port of said at least one ejector for maintaining a sufficient liquid level in the liquid/vapour separator even if the mass flow circulating in the at least one evaporator is higher than the mass flow evaporated, through an opening of a first control valve in the line from the low pressure receiver to the suction port of the at least one ejector, based on a minimum level signal generated by the liquid level sensing device, whenever the level of liquid refrigerant in said liquid vapour separator is below a set minimum level.
A further mean of a charge transfer between the suction receiver and the liquid/vapour separator, of indirect type, is considered.
Description of the Drawings
In the following the present invention will be described in more detail with reference to the appended drawings, in which Fig. 1 illustrates a diagram of a refrigeration system for medium temperature with recirculation flow according to an example embodiment using an indirect charge transfer method; Fig. 2 illustrates a diagram of a refrigeration system for medium temperature with recirculation flow according to an example embodiment using a direct charge transfer method;
Fig. 3 illustrates another example embodiment of a refrigeration system for medium temperature with recirculation flow comprising a charge transfer device;
Fig. 4 illustrates another example embodiment of a refrigeration system for medium temperature with recirculation flow comprising a charge transfer device;
Fig. 5 shows a diagram of a system booster type according to an example embodiment; Fig. 6 illustrates an example of connection and control means of an evaporator with relative supply valve and its control device;
Fig. 7 is an example of a control algorithm of a feeding valve to the evaporator referred to in Fig. 6;
Fig. 8a illustrates an example of the algorithm for adjusting the valve to control the pressure difference with a level switch as a level detection device on the suction receiver; Fig. 8b illustrates an example of the algorithm for adjusting the valve to control the pressure difference with a level detection device on the suction receiver comprising a continuous level measurement and analog output; and Fig. 8c illustrates an example of the algorithm for adjusting the valve to control the pressure difference with a level detection device on the liquid/vapour separator comprising a continuous level measurement and analog output.
Nomenclature and abbreviations
The numbering used in this patent application is as follows:
- MT: medium temperature
- BT: low temperature
- RC: circulation ratio (actual mass flow through evaporators / mass flow evaporated)
- X: a regulating and charge transfer device
- 1 : a medium temperature compressor or compressors
- 2: a condenser / gas cooler
- 3: a medium temperature regenerative exchanger
- 4: a high pressure regulating valve / 1 st stage throttling valve
- 5: a liquid / vapour separator
- 6: a medium temperature throttling valves to evaporators
- 7: a medium temperature evaporators
- 8: a suction receiver
- 9: a pressure-regulating valve in the separator 5
- 10: a first control valve for starting of charge transfer
- 13: a second control valve for liquid discharge from the liquid/vapour separator 5
- 16: a low temperature regenerative heat exchanger
- 17: a low temperature throttling valves to evaporators
- 18: a low temperature evaporators
- 19: a low temperature compressor or compressors
- 22: a refrigerant level detection device on suction receiver 8
- 23: a refrigerant level detection device on liquid / vapour separator 5
Detailed Description of the Invention The above mentioned Italian patent applications TV201 1 A000077 and TV201 1 A000141 describe some circuit solutions that allow to obtain a degree of recirculation RC in the evaporators and one of these solutions is shown, by way of example, in fig. 1 . With reference to fig. 1 , the compressor (compressors) 1 suck(s) refrigerant vapour from the suction receiver 8 and compresses it to the higher pressure of the cycle in the heat exchanger condenser / gas cooler 2, in which the refrigerant is cooled with the external air or other fluid used for cooling said condenser / gas cooler 2. The pressure in condenser / gas cooler 2 is controlled indirectly by both flow rate and temperature of the cooling fluid either directly through a high pressure- regulating valve 4 located on the pipe downstream of the heat exchanger 2, according to a known technique.
Downstream of the valve 4 is present a liquid / vapour separator 5 having the function of separating the flash vapour, produced by the first expansion through the valve 4, from the liquid intended to supply the evaporators. The refrigerant leaving the condenser / gas cooler 2 is entered, prior to entry to the valve 4, in a regenerative exchanger 3 in which the refrigerant is cooled by heat exchange with the fluid contained in the suction receiver 8. A certain flow rate of refrigerant liquid contained in said receiver 8 will circulate due to the density difference in the primary heat exchanger 3, connected for thermosiphon-like circulation, and return to the form of vapour at the top of the suction receiver 8 itself. The resulting cooling of the fluid in one circuit of heat exchanger 3 will produce a reduction of the amount of injected vapour in the liquid / vapour separator 5 and, at the same flow rate ml output from the liquid / vapour separator 5 will result in an increase of the liquid fraction in the separator 5 itself. A virtual transfer of charge from the receiver 8 to the liquid/vapour separator 5 is obtained in this way. A pressure-regulating valve 9 will limit the absolute or differential pressure in the separator 5 by draining a vapour flow rate in the suction receiver 8, and the difference in pressure between the liquid/vapour separator 5 and the suction receiver 8 will be adjusted so as to have a pressure differential sufficient to circulate the refrigerant in the evaporators.
In a further embodiment shown in fig.2 the refrigerant leaving the condenser / gas cooler 2 is entered to the valve 4 and to at least one ejector 14, these components being installed in parallel. Downstream of the valve 4 and ejector 14 is present the liquid / vapour separator 5 having the function of separating the flash vapour, produced by the first expansion through the valve 4, from the liquid intended to feed the evaporators.
The pressure-regulating valve 9 will limit the absolute or differential pressure in the liquid/vapour separator 5 by draining a vapour flow rate in the suction receiver 8, and the difference in pressure between the liquid/vapour separator 5 and the suction receiver 8 will be adjusted so as to have a pressure differential sufficient to circulate the refrigerant in the evaporators. A certain flow rate of liquid contained in said suction receiver 8 will return into the liquid/vapour separator 5 through a port 15 of an ejector 14. A direct transfer of charge from the suction receiver 8 to the liquid/vapour separator 5 is obtained in this way.
Similarly, other configurations may be used functionally equivalent, as described in Italian patent applications no. TV201 1 A000077 and no. TV201 1 A000141 .
All the circuit solutions described in the patent applications mentioned above are due to regulating and charge transfer device indicated by X in fig. 3 and fig. 4, imagining to delimit the object of the invention described in the applications mentioned with the control surface indicated by dashed lines in figs. 3 and 4.
The interface of the regulating and charge transfer device of X, for all the configurations described, can be traced to a single module of a block diagram with three inputs and two outputs, as shown in fig. 3. With reference to the regulating and charge transfer device X of fig. 3 and Fig. 4, the three input pipes are identified as inlet pipe of the fluid coming from the heat exchanger 2 and indicated with a), the inlet pipe of the flash vapour from the liquid/vapour separator 5 and indicated with b), the inlet pipe of the liquid from the suction receiver 8 and denoted by c) while the outlet pipes are those of release of the fluid to the separator 5 and the input of the flash vapour to the suction receiver 8, respectively indicated with d) and e). A possible configuration of the booster according to an embodiment of the invention is shown in Figure 5. With reference to Fig. 5, the medium temperature compressor (compressors) 1 sucks refrigerant vapour from the suction receiver 8 and compress it to the high pressure of the cycle in the heat exchanger condenser / gas cooler 2, in which the refrigerant is cooled with the external air or other fluid. The pressure in this heat exchanger 2 is either directly or indirectly controlled by both the flow rate and the temperature of the cooling fluid and via a regulating valve 4 located on the pipe downstream of the heat exchanger 2 and included in the regulating and charge transfer device X. Said device X also performs the fine adjustment of the high pressure, the control of pressure in the liquid/vapour separator 5 and the transfer of the flow rate of refrigerant not evaporated from the suction receiver 8 into the liquid/vapour separator 5 according to the technique described above.
Downstream of the liquid/vapour separator 5 is installed a low temperature regenerative heat exchanger 16, one circuit of which, defined as the primary circuit, is configured for the circulation of the entire liquid flow ml , intended to supply both the medium temperature evaporators 7, m1_MT, and the low temperature evaporators 18, m1_BT. The adjustment of the flow rate through the evaporators will be made, for example but not exclusively with a controller Rp that regulates the opening of valves 6 and 17 according to the temperature TA of air or fluid to be cooled, always as an example, as shown in Fig. 5 and 6, relating to a generic group feeding valve / evaporator MT indicated with 6n and 7n. The flow of fluid in the liquid phase at the entrance is indicated by m1 n, and the flow rate at the exit, obviously the same, will be partly liquid, ml_n, and partly in the vapour phase, mVn. In the graph of Figure 7 are reported respectively in abscissa and in ordinate the time τ and the air temperature T of the medium to be cooled. According to this method a probe for measuring the temperature T is connected to a suitable controller Rp, which adjusts the time of ON / OFF, on a time cycle D, of the valve 6n feeding refrigerant to the evaporator 7n, according to a technique PWM - Pulse Width Modulation. The controller Rp adjust the ratio Time ON/Time cycle D to maintain it proportional to the offset of T compared to set SO of the medium. A larger deviation of the value T-SO, provided T>S0, will give a higher ratio Time ON/Time cycle D. The generic valve 6 will be sized according to the flow coefficient kv, for example according to the formula m = kv * V Δρ, in which m is the mass flow rate, kv is the coefficient of discharge of the valve 6 and Δρ is the difference in pressure between upstream and downstream of the same, so that it is possible to achieve a required flow rate of the flow through the valve 6 under conditions of maximum thermal load and the conditions of pressure difference regulated by the regulating and charge transfer device X. This technique is mentioned for the sole purpose of allowing a complete understanding of the principle of operation of the system described herein. Other adjustment techniques may be employed, such as feeding valves 6 and 17 can simply be adjusted in ON / OFF and a balancing valve located downstream of said valves 6 and 17 can be used to limit the maximum flow rate.
The refrigerant leaving the primary circuit of the low temperature regenerative heat exchanger 16 is partially directed in the liquid line of supply of the medium temperature evaporators 7 through the valves 6, and indicated with m1_MT, and in part is placed in the liquid line of the evaporators 18 through the BT supply valves of the low temperature evaporators 17, and indicated with m1_BT. Both in the medium temperature evaporators 7 and in the low temperature evaporators 18 a fraction of the fluid, if not all, will evaporate extracting heat from substance or fluid to be cooled. The fluid flow which may not have been evaporated in the medium temperature evaporators, ml__MT, will be drained together with the vapour flow rate mV_MT in the receiver 8 through the suction pipe. With reference to fig. 5, m1_MT = ml__MT + mV_MT. The fluid flow which may not have been evaporated in the low temperature evaporators 18, ml__BT, will be drained together with the vapour flow rate mV_BT in the secondary circuit of the heat exchanger 16 toward the suction of the low temperature compressor or compressors 19. With reference to fig. 5, m1_BT = ml__BT + mV_BT. Since in a system of the booster type the ratio between the flow rate m1_BT circulating in the low temperature evaporators 18 and the total flow of liquid leaving the liquid/vapour separator 5, ml = m1_MT + m1_BT, is generally of the order of 0.3 or lower the ability of the said low temperature heat exchanger 16 to evaporate the scope ml__BT is high. If also the total flow rate of liquid circulating in the primary side of the low temperature heat exchanger 16 was equal to the flow rate of liquid intended to circulate in the low temperature evaporators 18, or m1_BT, the ability to evaporate the amount ml__BT would be at any event sufficient due to the high temperature difference, of the order of 30K, between the liquid in the primary circuit of the exchanger 16 and the mixture liquid / vapour in the secondary circuit of the same and said temperature difference makes it possible, without risk of suction of liquid into the low temperature compressor 19, a circulation ratio RC in the evaporators of BT section of about 1 .25. The low temperature compressor 19 will send the flow of refrigerant compressed in the suction receiver 8.
A further problem to be solved with the present invention is to define a method of protection to prevent an excessive amount of liquid to flow through the medium temperature evaporators 7 in the case where the flow rate regulation in these medium temperature evaporators 7 is not optimized due to inaccurate setting of the control system of the valves 6, or due to other unforeseen situations.
There may be two options for doing that, depending on the concept used for system design, that is depending on which vessel, suction receiver 8 or liquid/vapour separator 5, is used for containment of liquid charge not active in the refrigeration circuit.
In case the refrigerating circuit is designed for containment of the liquid charge in the liquid/vapour separator 5, a level switch 22 or other device is installed on the suction receiver 8 which allows to detect an excessive accumulation of liquid refrigerant. If the refrigerant level detection device 22, e.g. a switch detects an excess of refrigerant in said suction receiver 8, an indication of an unsuitable flow regulation in the evaporators 7 is provided, wherein the pressure regulating valve 9, as shown in fig. 4, said pressure regulating valve 9 being included in the charge transfer device X and shown in both fig. 8a and fig. 8b, limits the differential pressure between the liquid/vapour separator 5 and the suction receiver 8 to a value lower than that normally regulated. The flow rate through the valves 6 and the medium temperature evaporators 7 depends on the degree of opening of the valves 6, but also on the pressure difference between upstream and downstream of the same, being such difference in pressure, disregarding the pressure drop in pipes, equal to the difference in pressure between the liquid/vapour separator 5 and the suction receiver 8. According to the ideal relationship already introduced m = kv * V Dp decreasing the pressure difference between upstream and downstream of the valve 6 reduces the flow rate through all evaporators 7, and therefore, given the same thermal load, a lower flow rate of fluid ml__MT not evaporated at the exit is achieved. At the limit, equalizing the pressure in the separator 5 to that in the suction receiver 8 will stop the flow of refrigerant to the evaporators 7. With reference to Fig. 4, fig. 8a and fig. 8b, when the switch or the signal level 22 on the suction receiver 8 detects the presence of excess liquid the valve 9 will act directly or indirectly on the relevant signal. The pressure regulating valve 9 may either be mechanically or electrically operated. The pressure regulating valve 9, through a proper control system, shown schematically in Fig. 8a and 8b, reduces to a predetermined value the pressure difference between the pipes b) and e) of the regulating and charge transfer device X for adjusting pressure and charge transfer, and then between the liquid/vapour separator 5 and the suction receiver 8, thereby causing, for a given heat load, both reduction of flow rate m1_MT and a reduction in the fraction of liquid ml__MT and then allowing a proportional increase in the fraction of the vapour mass flow mV_MT at the exit of the medium temperature evaporators 7. With reference to fig. 8a an increase in liquid level in the suction receiver 8 is detected by the refrigerant level detection device 22 and via a regulator RL will control the opening degree of the valve 9 to decrease the pressure difference between the suction receiver 8 and the liquid/vapour separator 5 from the value ΔΡ1 to the value ΔΡ2.
With reference to Fig. 8b, which refers to an alternative to the previous embodiment, an increase in the level of liquid in the suction receiver 8 is detected by the refrigerant level detection device 22, which will send a signal proportional to the level to the controller RL which will control the opening degree of the valve 9 so as to vary the pressure difference between the suction receiver 8 and the liquid/vapour separator 5, for example but not exclusively, according to the function represented in fig. 8b which graphically shows a proportional correspondence of differential pressure between upstream and downstream of the valve 9 with liquid level in the suction receiver 8, the upper limit of differential pressure ΔΡ1 obtained with liquid level less than or equal to LMIN, and with the lower limit of differential pressure ΔΡ2, obtained with a level equal to or greater than LMAX-
Merely by way of example, in normal operating conditions in a refrigerator system for use at 0°C, the pressure in the liquid/vapour separator 5 is adjusted approximately to approximately 34 bar while the suction pressure, and then the pressure existing in the suction receiver 8 is of about 29 bar. The pressure difference between the liquid/vapour separator 5 and the suction receiver 8, ΔΡ1 , is therefore of 5 bar, and on the basis of this design value are calculated by the valve 6 is selected to provide 100% of the maximum required flow.
Reducing said pressure differential to a value ΔΡ2 = 2.5 bar the valve 6 will be able to drain, when it is fully to (100%) open, a flow rate 30% less than the previous one. In the example in question it is possible to estimate the percentage change of flow rate to be approximately as Am = (V 5 - V 2.5) / V 5 x100.
As another example, reducing the pressure differential to the value ΔΡ2 = 1 bar the valve 6 will be able to flow out, always with opening degree of 100%, approximately 45% of flow, and consequently a flow rate 55% less than the original condition with ΔΡ=5 bar. The reduction of flow rate can be estimated as Am = ( 5 - l ) / V 5 x100.
In case the refrigerating circuit is designed for containment of the liquid charge in the suction receiver 8, a level switch 23 or other device will be on the liquid/vapour separator 5 which allows to detect a too low level of liquid refrigerant which may bring to starving of the system. If the refrigerant level detection device 23, e.g. a switch detects a shortage of refrigerant in said liquid/vapour separator 5, which is an indication of excess of mass flow through evaporators 7, the valve 9 will reduce the pressure difference using a control logic reversed to that previously described, in the sense that a lower level will bring to a lower pressure difference between the liquid/vapour separator 5 and the suction receiver 8. The above logic is shown in fig. 8c.
As for economic reasons it might be desirable to reduce the size of the liquid/vapour separator 5 to a minimum. One valve 10 can be used to stop the charge transfer in case both Δρ and liquid level in the liquid/vapour separator 5 are at their maximum, and a valve 13 can be arranged to open as a further protection means. An example embodiment comprising valve 13 is shown in fig. 1 . The present invention is not limited solely to the above described embodiments but it can be varied within the scope of the appended claims.

Claims

Claims:
1 . A multi-evaporator refrigeration circuit adapted to use carbon dioxide as a liquid refrigerant, comprising at least:
- a compressor (1 );
- a condenser/gas cooler (2);
- a first throttling valve (4);
- a liquid/vapour separator (5);
- a valve (9) controlling pressure in the liquid/vapour separator (5);
- a liquid level sensing device (22, 23);
- at least one evaporator (7, 18); and
- a suction receiver (8);
wherein the refrigeration circuit is adapted to feed the liquid refrigerant to the at least one evaporator (7) from said liquid/vapour separator (5) through a second throttling device (6),
characterized in that the refrigeration circuit further comprises at least one ejector (14) comprising a suction port (15) in parallel to the first throttling valve (4); and that the refrigeration circuit is adapted to drive cold liquid from the suction receiver (8) to the suction port (15) of said at least one ejector (14), being activated for direct charge, for maintaining a sufficient liquid level in the liquid/vapour separator (5) even if the mass flow circulating in the at least one evaporator (7) is higher than the mass flow evaporated, through an opening of a first control valve (10) in the line from the suction receiver (8) to the suction port (15) of the at least one ejector (14), based on a maximum level signal generated by the liquid level sensing device (22), whenever the level of liquid refrigerant in said suction receiver (8) is above a set maximum level.
2. The refrigeration circuit according to claim 1 , characterized in that the refrigeration circuit further comprises a first heat exchanger (3) having at least a primary circuit and a secondary circuit, wherein one circuit of the first heat exchanger (3) is adapted to circulate cold liquid from the suction receiver (8) by gravity to exchange heat with the high pressure fluid from the condenser/gas cooler (2) adapted to circulate in another circuit of the heat exchanger (3).
3. The refrigeration circuit according to claim 2, characterized in that the at least one ejector (14) is installed in a separate piping line between an exit of the condenser/gas cooler (2) and the liquid/vapour separator (5), said piping line being connected in parallel with the piping line connecting the exit of the condenser/gas cooler (2) through the heat exchanger (3) with an inlet of the first throttling valve (4).
4. The refrigeration circuit according to claim 1 , 2 or 3 characterized in that the refrigeration circuit further comprises at least one low temperature compressor (19) and a second heat exchanger (16), and the refrigeration circuit is further configured for supplying the at least one evaporator (18) having an exit configured for entering one circuit of the second heat exchanger (16) exchanging heat with the main liquid line exiting the liquid/vapour separator (5) circulating in the other side of said second heat exchanger (16).
5. The refrigeration circuit according to any of the claims 1 to 4, characterized in that the liquid level sensing device (22) is installed in the suction receiver (8).
6. The refrigeration circuit according to any of the claims 1 to 4, characterized in that the liquid level sensing device (23) is installed in the liquid/vapour separator (5).
7. The refrigeration circuit according to any of the claims 1 to 6, characterized in that the liquid level sensing device (22) or (23) is a level switch.
8. The refrigeration circuit according to any of the claims 1 to 7, characterized in that the suction receiver (8) is a low pressure suction receiver.
9. A refrigeration system using the arrangement refrigeration circuit according to any of the claims 1 to 8.
10. A method in a multi-evaporator refrigeration circuit of low pressure receiver type adapted to use carbon dioxide as a liquid refrigerant, the multi- evaporator refrigeration circuit comprising at least:
- a compressor (1 );
- a condenser/gas cooler (2);
- a first throttling valve (4);
- a liquid/vapour separator (5);
- a pressure limiting valve (9);
- a liquid level sensing device (22, 23);
- at least one evaporator (7); and
- a suction receiver (8);
wherein the method comprises feeding the liquid refrigerant to the at least one evaporator (7) from said liquid/vapour separator (5) through a second throttling device (6),
characterized in that the refrigeration circuit further comprises at least one ejector (14) comprising a suction port (15) included in parallel to the first throttling valve (4); wherein the method further comprises direct driving of cold liquid from the suction receiver (8) to the suction port (15) of said at least one ejector (14) for maintaining a sufficient liquid level in the liquid/vapour separator (5) even if the mass flow circulating in the at least one evaporator (7) is higher than the mass flow evaporated, through an opening of a first control valve (10) in the line from the low pressure receiver (8) to the suction port (15) of the at least one ejector (14), based on a maximum level signal generated by the liquid level sensing device (22), whenever the level of liquid in said suction receiver (8) is above a set maximum level.
1 1 . A multi-evaporator refrigeration circuit adapted to use carbon dioxide as a liquid refrigerant, comprising at least:
- a compressor (1 );
- a condenser/gas cooler (2);
- a first throttling valve (4);
- a liquid/vapour separator (5);
- a valve (9) controlling pressure in the liquid/vapour separator (5);
- a liquid level sensing device (22, 23);
- at least one evaporator (7, 18); and
- a suction receiver (8); wherein the refrigeration circuit is adapted to feed the liquid refrigerant to the at least one evaporator (7) from said liquid/vapour separator (5) through a second throttling device (6),
characterized in that the refrigeration circuit further comprises at least one ejector (14) comprising a suction port (15) in parallel to the first throttling valve (4); and that the refrigeration circuit is adapted to drive cold liquid from the suction receiver (8) to the suction port (15) of said at least one ejector (14), being activated for the charge transfer for maintaining a sufficient liquid level in the liquid/vapour separator (5) even if the mass flow circulating in the at least one evaporator (7) is higher than the mass flow evaporated, through an opening of a first control valve (10) in the line from the suction receiver (8) to the suction port (15) of the at least one ejector (14), based on a minimum level signal generated by the liquid level sensing device (23), whenever the level of liquid refrigerant in said liquid/vapour separator (5) is below a set minimum level.
12. The refrigeration circuit according to claim 1 1 , characterized in that the refrigeration circuit further comprises a first heat exchanger (3) having at least a primary circuit and a secondary circuit, wherein one circuit of the first heat exchanger (3) is adapted to circulate cold liquid from the suction receiver (8) by gravity to exchange heat with the high pressure fluid from the condenser/gas cooler (2) adapted to circulate in another circuit of the heat exchanger (3).
13. The refrigeration circuit according to claim 12, characterized in that the at least one ejector (14) is installed in a separate piping line between an exit of the condenser/gas cooler (2) and the liquid/vapour separator (5), said piping line being connected in parallel with the piping line connecting the exit of the condenser/gas cooler (2) through the heat exchanger (3) with an inlet of the first throttling valve (4).
14. The refrigeration circuit according to claim 1 1 , 12 or 13 characterized in that the refrigeration circuit further comprises at least one low temperature compressor (19) and a second heat exchanger (16), and the refrigeration circuit is further configured for supplying the at least one evaporator (18) having an exit configured for entering one circuit of the second heat exchanger (16) exchanging heat with the main liquid line exiting the liquid/vapour separator (5) circulating in the other side of said second heat exchanger (16).
15. The refrigeration circuit according to any of the claims 1 1 to 14, characterized in that the liquid level sensing device (22) is installed in the suction receiver (8).
16. The refrigeration circuit according to any of the claims 1 1 to 14, characterized in that the liquid level sensing device (23) is installed in the liquid/vapour separator (5).
17. The refrigeration circuit according to any of the claims 1 1 to 16, characterized in that the liquid level sensing device (22) or (23) is a level switch.
18. The refrigeration circuit according to any of the claims 1 1 to 17, characterized in that the suction receiver (8) is a low pressure suction receiver.
19. A refrigeration system using the arrangement refrigeration circuit according to any of the claims 1 1 to 18.
20. A method in a multi-evaporator refrigeration circuit of low pressure receiver type adapted to use carbon dioxide as a liquid refrigerant, the multi- evaporator refrigeration circuit comprising at least:
- a compressor (1 );
- a condenser/gas cooler (2);
- a first throttling valve (4);
- a liquid/vapour separator (5);
- a pressure limiting valve (9);
- a liquid level sensing device (22, 23);
- at least one evaporator (7); and
- a suction receiver (8);
wherein the method comprises feeding the liquid refrigerant to the at least one evaporator (7) from said liquid/vapour separator (5) through a second throttling device (6), characterized in that the refrigeration circuit further comprises at least one ejector (14) comprising a suction port (15) included in parallel to the first throttling valve (4); wherein the method further comprises direct driving of cold liquid from the suction receiver (8) to the suction port (15) of said at least one ejector (14) for maintaining a sufficient liquid level in the liquid/vapour separator (5) even if the mass flow circulating in the at least one evaporator (7) is higher than the mass flow evaporated, through an opening of a first control valve (10) in the line from the low pressure receiver (8) to the suction port (15) of the at least one ejector (14), based on a minimum level signal generated by the liquid level sensing device (23), whenever the level of liquid refrigerant in said liquid/vapour separator (5) is below a set minimum level.
EP12796452.6A 2011-06-06 2012-05-28 A multi-evaporator refrigeration circuit Not-in-force EP2718642B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL12796452T PL2718642T3 (en) 2011-06-06 2012-05-28 A multi-evaporator refrigeration circuit
HRP20161607TT HRP20161607T1 (en) 2011-06-06 2016-12-01 A multi-evaporator refrigeration circuit

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IT000077A ITTV20110077A1 (en) 2011-06-06 2011-06-06 REFRIGERATOR SYSTEM WITH STEAM COMPRESSION AND DIRECT EXPANSION WITH HIGH CIRCULATION RATIO IN EVAPORATORS.
IT000141A ITTV20110141A1 (en) 2011-10-14 2011-10-14 REFRIGERANT SYSTEM WITH REFRIGERANT R744 WITH HIGH CIRCULATION REPORT IN EVAPORATORS.
IT000010A ITTV20120010A1 (en) 2012-01-19 2012-01-19 BOOSTER REFRIGERANT SYSTEM WITH REFRIGERANT R744.
PCT/FI2012/050513 WO2012168544A1 (en) 2011-06-06 2012-05-28 A multi-evaporator refrigeration circuit

Publications (3)

Publication Number Publication Date
EP2718642A1 true EP2718642A1 (en) 2014-04-16
EP2718642A4 EP2718642A4 (en) 2015-04-01
EP2718642B1 EP2718642B1 (en) 2016-09-14

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Application Number Title Priority Date Filing Date
EP12796452.6A Not-in-force EP2718642B1 (en) 2011-06-06 2012-05-28 A multi-evaporator refrigeration circuit

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EP (1) EP2718642B1 (en)
AU (1) AU2012266219B2 (en)
CA (1) CA2868441C (en)
DK (1) DK2718642T3 (en)
ES (1) ES2602169T3 (en)
HR (1) HRP20161607T1 (en)
HU (1) HUE032488T2 (en)
LT (1) LT2718642T (en)
PL (1) PL2718642T3 (en)
PT (1) PT2718642T (en)
WO (1) WO2012168544A1 (en)

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RU2659679C2 (en) * 2013-09-19 2018-07-03 Кэррие Корпорейшн Refrigerating circuit with heat regeneration module
CN103791651B (en) * 2013-12-23 2016-01-20 滁州安兴环保彩纤有限公司 Directly spin steam composite more than short silk and utilize device
WO2015144627A1 (en) * 2014-03-27 2015-10-01 Carrier Corporation Device and method for determining the filling height of liquid in a container
US9897363B2 (en) 2014-11-17 2018-02-20 Heatcraft Refrigeration Products Llc Transcritical carbon dioxide refrigeration system with multiple ejectors
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CN108139132B (en) 2015-10-20 2020-08-25 丹佛斯有限公司 Method for controlling a vapor compression system with variable receiver pressure set point
JP6788007B2 (en) * 2015-10-20 2020-11-18 ダンフォス アクチ−セルスカブ How to control the vapor compression system in long-time ejector mode
ITUA20163465A1 (en) * 2016-05-16 2017-11-16 Epta Spa REFRIGERATOR SYSTEM WITH MORE LEVELS OF EVAPORATION AND METHOD OF MANAGEMENT OF SUCH A SYSTEM
RU2705696C2 (en) * 2017-01-26 2019-11-11 федеральное государственное автономное образовательное учреждение высшего образования "Российский университет дружбы народов" (РУДН) Multi-stage heat pump plant
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US11221163B2 (en) 2019-08-02 2022-01-11 Randy Lefor Evaporator having integrated pulse wave atomizer expansion device
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US20220178602A1 (en) * 2020-12-04 2022-06-09 Honeywell International Inc. Surge control subcooling circuit
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Also Published As

Publication number Publication date
HRP20161607T1 (en) 2017-01-13
CA2868441A1 (en) 2012-12-13
PL2718642T3 (en) 2017-07-31
CA2868441C (en) 2018-07-10
DK2718642T3 (en) 2016-12-19
AU2012266219B2 (en) 2016-09-08
EP2718642A4 (en) 2015-04-01
WO2012168544A1 (en) 2012-12-13
ES2602169T3 (en) 2017-02-17
PT2718642T (en) 2016-12-20
EP2718642B1 (en) 2016-09-14
LT2718642T (en) 2016-11-25
AU2012266219A1 (en) 2015-06-11
HUE032488T2 (en) 2017-09-28

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