EP2122272A2 - Installation frigorifique - Google Patents

Installation frigorifique

Info

Publication number
EP2122272A2
EP2122272A2 EP07859138A EP07859138A EP2122272A2 EP 2122272 A2 EP2122272 A2 EP 2122272A2 EP 07859138 A EP07859138 A EP 07859138A EP 07859138 A EP07859138 A EP 07859138A EP 2122272 A2 EP2122272 A2 EP 2122272A2
Authority
EP
European Patent Office
Prior art keywords
receptacle
plant according
coolant fluid
outlet
conduit
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.)
Ceased
Application number
EP07859138A
Other languages
German (de)
English (en)
Inventor
Mauro Barbieri
Ezio Fornasieri
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.)
Teklab Sas Di Barbieri Mauro E C
Original Assignee
Teklab Sas Di Barbieri Mauro E C
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 Teklab Sas Di Barbieri Mauro E C filed Critical Teklab Sas Di Barbieri Mauro E C
Publication of EP2122272A2 publication Critical patent/EP2122272A2/fr
Ceased legal-status Critical Current

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
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/001—Compression machines, plants or systems with reversible cycle not otherwise provided for with two or more 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/02—Centrifugal separation of gas, liquid or oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention relates to a refrigerating plant, in particular a plant in which the heat exchange in the evaporator is optimised and the quantity of coolant required by the plant per refrigerating power unit is optimised.
  • dry-expansion refrigeration plants consist of a compressor / a first heat exchanger acting as a condenser of the refrigerating fluid and a second heat exchanger acting as an evaporator o£ the coolant fluid.
  • the coolant fluid in overheated steam state, is compressed at high pressure by the compressor and sent to the condenser, where it surrenders heat to the external environment, condensing in the form of high-pressure liquid.
  • an expansion valve through which the coolant liquid passing through coming from the condenser, expands adiabatically, cooling before entering the evaporator.
  • the low-pressure coolant absorbs heat from the environment and is transformed into steam that is returned, via the suction line, to the inlet of the compressor.
  • thermostatic expansion valve In many traditional refrigerating plants, the expansion valve is represented by a so-called thermostatic expansion valve. Different types of thermostatic expansion valves are in use; the most common ones are the mechanical and the electronic valves and the operating principle is common to both.
  • a common mechanical thermostatic expansion valve has inside an expansion chamber with a limiting orifice and a shutter for regulating the flow of the coolant through said orifice, A spring pushes the shutter inside the orifice to the closing position thereof.
  • the valve is also provided with an actuating diaphragm, A face of the diaphragm is in direct communication with the coolant fluid delivered into the valve, whilst the other face is in communication, through a capillary pipe, with a thermostatic bulb that detects through contact .the temperature of the fluid in overheated steam state at the outlet of the evaporator.
  • the bulb is loaded with a suitable volatile fluid (for example the same coolant fluid that circulates in the refrigerating plant or another suitable fluid) and is thus able to exert pressure on the shutter of the valve by means of the actuating diaphragm, contrasting both the force of the spring and the pressure of the coolant fluid inside the valve.
  • the thermostatic valve detects an increase in the outlet temperature of the coolant at the outlet of the evaporator, the force exerted on the actuating diaphragm increases proportionally, determining a greater opening of the valve and a consequent increase in the flow of coolant through the evaporator and this causes a decrease in the temperature of the coolant at the outlet of the evaporator. If, on the other hand, the thermostatic bulb detects a decrease in the coolant temperature the force exerted on the actuating diaphragm decreases proportionally, enabling the spring to close partially and thus reducing the flow of coolant through the evaporator and this produces an increase in the temperature of the coolant fluid leaving the evaporator.
  • the expansion valve adjusts overheating of the coolant fluid at the outlet of the evaporator, i.e. the difference between the temperature of the coolant fluid and a saturated fluid of the coolant fluid at the same pressure .
  • electronically controlled expansion valves are used that are piloted by an electronic drive by means of an electronic control unit that is connected, for example, to temperature and pressure sensors located at the outlet of the evaporator.
  • the degree of opening of the valve and, therefore, the flow of coolant fluid sent to the evaporator are adjusted in function of the overheating of the coolant, which is calculated on the basis of pressure and temperature values read by the sensors located at the outlet of the evaporator.
  • the electronically controlled valves generally permit more precise adjustment of the flow of the coolant sent to the evaporator, but above all eliminate the proportional behaviour, which, is the main drawback in mechanical thermostatic valves.
  • the refrigerating coolant fluid leaving the evaporator and delivered to said collecting receptacle is in a saturated condition (liquid and steam balanced) .
  • a saturated condition liquid and steam balanced
  • the liquid phase and the gas phase of the saturated fluid separate, with the liquid phase remaining inside the collecting receptacle and being pumped or recirculated in the evaporator, whilst the gas phase is sucked by the compressor, through said second outlet,
  • the potential of the evaporator is fully exploited because the coolant fluid leaves the evaporator in humid saturated steam state and so all the exchange surface, being wet by the liquid, is active for evaporation purposes.
  • the level of liquid in the separator is kept constant, increasing the degree of opening of the valve if the level decreases and decreasing the degree of opening of the valve if the level increases.
  • the level of liquid in the collecting receptacle is detected by a level sensor.
  • the level is kept constant at the bottom of the condenser or on a capacity located on the outlet thereof.
  • the level is kept constant by opening the valve if the level rises and closing the valve if the level falls. Also in this case, the level of the liquid is detected by a level sensor.
  • a refrigerating plant comprising a coolant fluid, a compressor, a condenser, an expansion valve, an evaporator, a collecting receptacle for collecting said coolant fluid, and means for piloting said expansion valve, characterised in that said collecting receptacle is interposed between an outlet of said evaporator and an inlet of said compressor.
  • the liquid, fraction of the saturated steam leaving the evaporator can be minimised compared with a system with a flooded evaporator, but maintaining the advantage of exploiting to the full the potential of the evaporator, to which the advantage of substantially reducing the quantity of coolant fluid loaded in the system is added.
  • the liquid that is collected in the collecting receptacle is not used to supply the evaporator, but is used to provide a reference for the level sensor, for adjusting the degree of opening of the expansion valve.
  • the quantity of liquid in the collecting receptacle can thus be reduced to the minimum indispensable for ensuring correct operation of the level sensor, As a result, the titre of the humid saturated steam leaving the evaporator can be very near to 1 , for example can be equal to about 0.9.
  • Figure 1 is a general diagram of a refrigerating plant according to the invention.
  • Figure 2 is a detail of the refrigerating plant of Figure 1;
  • Figure 3 is a first version of the detail in Figure 2;
  • Figure 4 is a second version of the detail in Figure 2;
  • FIG. 5 is a further version that can be applied to the drawings of Figure 2, Figure 3 and Figure 4;
  • FIG. 6 is a general diagram of a plant with heat pump according to the invention.
  • a refrigerating plant according to the invention comprises a compressor 1 that comprises a coolant fluid entering the compressor 1 in overheated steam state and sends the coolant fluid, via a first conduit 2, to a condenser 3 in which the coolant fluid condenses, yielding heat to the external environment.
  • the coolant fluid, exiting the condenser 3, passes into a second conduit 4 in which there is placed an expansion valve 5, passing through, which the coolant fluid reduces pressure and cools.
  • the second conduit 4 delivers the coolant fluid to an evaporator 6, in which the coolant fluid evaporates, removing heat from an environment to be cooled.
  • the coolant fluid which leaves the evaporator 6 in humid saturated steam state, with titre just below 1, for example with titre equal to 0.9, is sent, through a third conduit 7, to a collecting receptacle S in which the liquid fraction of the coolant fluid is separated from the gas fraction, gathering on the bottom of the collecting receptacle 8, whilst the gas fraction gathers in the upper part of the collecting receptacle 8.
  • the collecting receptacle S communicates, above, with a first outlet conduit 9, through which the gas phase of the coolant fluid exits, and, below, with a second outlet conduit 10 through which the liquid phase of the coolant fluid exits.
  • the first outlet conduit 9 and the second outlet conduit 10 flow together into a fourth conduit 11 in which the gas phase and the liquid phase of the coolant fluid are mixed together.
  • the fourth conduit 11 sends the coolant fluid to a heat exchanger 12 in which the liquid fraction of the coolant fluid is evaporated so that the coolant fluid leaves the exchanger 12 in the form of overheated steam.
  • the coolant fluid exiting the heat exchanger 12 is sent through a fifth conduit 2.3 to the compressor 1, to restart the refrigerating cycle.
  • the heat for evaporating the liquid fraction of the coolant fluid in the heat exchanger 12 is supplied by the coolant fluid coming from the condenser 3 via the second conduit 4, which passes through the heat exchanger 12.
  • the flow of coolant fluid in the evaporator 6 is regulated by the expansion valve 5, the degree of opening of which determines the flow of coolant fluid that is sent to the evaporator 6.
  • the degree of opening of the expansion valve 5 is adjusted by an electronic control device 14 in function of the level of liquid in the collecting receptacle 8 ,
  • the level L of liquid in. the collecting receptacle 8 is detected by a level sensor 15, preferably an infrared-ray sensor associated with the collecting- receptacle 8.
  • the signal generated by the level sensor 15 is sent to the control device 14 which, in response to said signal, adjusts the degree of opening of the expansion valve 5, increasing the degree of opening if the level L of liquid in the collecting receptacle S decreases and decreasing the degree of opening if the level L of liquid increases,
  • the control device 14 which, in response to said signal, adjusts the degree of opening of the expansion valve 5, increasing the degree of opening if the level L of liquid in the collecting receptacle S decreases and decreasing the degree of opening if the level L of liquid increases.
  • the collecting receptacle 8 has a substantially cylindrical shape, with an inlet 16 into which the third conduit 7 coming from the evaporator 6 leads .
  • the inlet 16 is preferably arranged so that the coolant fluid coming from the evaporator 16 enters the collecting receptacle 8 in a noticeably tangential direction, &o that a turbulent motion of the coolant fluid in .the collecting receptacle 8 is generated, so as to promote the separation of the liquid phase from the gas phase.
  • first separating means 17 and second separating means 18 are arranged, arranged respectively in the upper part and in the lower part of the receptacle.
  • Said separating means has the following functions: the means 17 promotes the separation of the liquid phase of the coolant fluid from the gas phase, ensuring in the conduit 9 a sole flow of steam / the means 18 prevents the underlying level of liquid being disturbed by the turbulence of the steam.
  • Said separating means 17, 18 can be constituted, for example, by net means, or by radial protrusions of the internal wall of the receptacle.
  • the collecting receptacle 8 is provided, above, with a first outlet 19, through which the gas fraction of the coolant fluid enters the first outlet conduit 9, and, below, with a second outlet 20 through which the liquid fraction of the coolant fluid, which has collected on the bottom of the collecting receptacle 8, enters the second outlet conduit 10.
  • the first and the second outlet conduit 10 flow, as said, into the fourth conduit 11 that conveys the coolant fluid to the heat exchanger 12.
  • flow adjusting means 10a is provided, for example a diaphragm with a calibrated hole / for adjusting the flow of liquid that is supplied to the fourth conduit 11, in function of the potential of the heat exchanger 12, so as to guarantee that all the liquid delivered to the fourth conduit 11 evaporates in the evaporator 12 before then reaching the compressor 1.
  • a valve can if necessary be used that modulates the fluid in function of the overheating of the steam measured at the outlet of the exchanger 12, so as to ensure, together with the safety of the computer against the shocks from liquid, an effective use of the exchange surface of the exchanger 12.
  • the level sensor 15 is arranged, preferably an infrared-ray sensor, which detects if the level L of the liquid is lower or higher than a preset level, sending a corresponding signal to the control device 14, which adjusts the expansion valve 5,
  • FIG 3 there is illustrated a second embodiment of the collecting receptacle Sa, In this second embodiment, about half way up the height of the second embodiment there is a narrowing 21, the object of which is to reduce the influence of the free surface of the liquid of the turbulences generated by the coolant fluid, which enters the collecting receptacle S. Said turbulences, may in fact cause oscillations of the free surface of the liquid that may negatively influence the readings of the level sensor 15 , In Figure 4 there is illustrated a third embodiment of a collecting receptacle Sb.
  • the collecting receptacle 8b has a first further opening 22, located in the upper part of the receptacle and a second further opening 23 , located in the lower part of the receptacle at the zone in which the coolant fluid is collected in liquid state.
  • the first further opening 22 and the second further opening 23 make the collecting receptacle 8b communicate with an auxiliary receptacle 24, so that in the auxiliary receptacle 24 there is, through the effect of the communicating vessels principle, a level L of liquid equal to that of the receptacle Sa, without the free surface of the liquid in the auxiliary receptacle 24 being disturbed by the turbulences that are generated in the collecting receptacle Sb at the inlet of the coolant fluid coming from the evaporator 6.
  • the level sensor 15 is associated with the auxiliary receptacle 24.
  • the auxiliary receptacle can also have the shape of a level pipe.
  • FIG 5 there is illustrated a further version of the system in Figure 3, that is applicable also to the diagrams of Figure 2 and of Figure 4, that differs by the methods with which the liquid collected in the receptacle 8a is evaporated: in this case, in addition to, or instead of the exchanger 12, an exchanger 25 is used inside which a coil 27 is located that is condensed fluid coming from the condenser 3, located below the level of liquid fixed in the receptacle 8a.
  • the plant comprises a compressor 101 in which the coolant fluid is compressed that, via a first conduit 102, is sent to a v inversion valve, for example a four-way valve, that reverses the flow direction of the coolant fluid in the plant, when switching from operation as a refrigerator to operation as a heat pump.
  • the V valve is connected, via a second conduit 103 with a first heat exchanger 104 that, in the operation as a refrigerator, acts as a condenser, whilst, in operation as a heat pump, it acts as an evaporator.
  • the first heat exchanger 104 is associated with a first receptacle 108 that, when the exchanger acts as an evaporator, performs the same function as the collecting receptacle 8, 8a, 8b disclosed previously and which is provided with a respective level sensor (which is not shown) .
  • the coolant fluid exiting the first heat exchanger 104 is sent to a third conduit 105 in which a two- directional expansion valve 106 is arranged.
  • the third conduit 105 leads into a second heat exchanger 107 that in operation as a refrigerator acts as an evaporator, whilst in operation as a heat pump acts as a condenser.
  • the second heat exchanger 107 is associated with a second receptacle 108a that is completely similar to the first receptacle 108 associated with the first heat exchanger 104. Also the second receptacle 108a is provided with a respective level sensor (which is not shown) .
  • the level sensors associated with the collecting receptacles 108 and 108a are operationally associated with a control device 109, for example an electronic control device that pilots the expansion valve 106, increasing the degree of opening thereof when the level of liquid in the collecting receptacle 108, or 108a, associated with the heat exchanger 104, or 107, that acts as an evaporator, decreases and the level of opening of the expansion valve 106 decreases when the level of liquid in the collecting receptacle 108, or 108a, increases.
  • a control device 109 for example an electronic control device that pilots the expansion valve 106, increasing the degree of opening thereof when the level of liquid in the collecting receptacle 108, or 108a, associated with the heat exchanger 104, or 107, that acts as an evaporator, decreases and the level of opening of the expansion valve 106 decreases when the level of liquid in the collecting receptacle 108, or 108a, increases.
  • a fourth conduit 110 connects the second heat exchanger 107 to the inversion valve V and a fifth conduit 111 connects the inversion valve V to the suction of the compressor 101, possibly through a suction accumulator 112.
  • the receptacles 108 and 108a are any way connected to an exchanger, which is not shown in Figure 6, having the function of evaporating the liquid contained in the bottom of the aforesaid receptacles for cooling the liquid condensate directed to the lamination valve.
  • Said exchanger is shown as a component 12 in Figure l r or 25 in Figure 5.
  • the coolant fluid compressed by the compressor 101 is sent, for example, by the valve v to the first heat exchanger 104 in which it condenses, releasing heat to the exterior.
  • the coolant fluid before entering the first heat exchanger 104, passes through the first receptacle 108, which, in this case, does not perform any function, the level sensor associated thereto being disabled.
  • the coolant fluid that has condensed in the first heat exchanger 104 is sent, passing through the expansion valve 106, to the second exchanger 107 in which it evaporates, absorbing heat from the exterior, passing to saturate steam state, with titre near 1,
  • the coolant fluid passes through the second receptacle 108a in which the liquid phase separates from the steam phase, becoming deposited at the bottom of the receptacle 108a, as already disclosed with reference to the refrigerating plant illustrated in Figures l to 5.
  • the level sensor associated with the second receptacle 108a is active and sends to the control device 109 a signal indicating the level of the liquid in the receptacle 108a, on the basis of , which the control device adjusts the degree of opening of the expansion valve 106.
  • the liquid phase and the gas phase of the coolant fluid separated in the second receptacle 108a are mixed together, as already disclosed, at the outlet of the receptacle and the coolant fluid is sent to the compressor to restart the cycle .
  • the direction of. the flow of the coolant fluid into the exchangers 104 and 107 is reversed by the inversion valve V, so that the second heat exchanger 107 acts as a condenser and the first exchanger 104 acts as an evaporator.
  • the second receptacle 108a associated with the second exchanger 107 does not perform any function and the level sensor associated therewith is disabled, whilst the first receptacle 108 acts as a collecting receptacle, in which the gas phase and the liquid phase of the coolant fluid exiting the first exchanger 104 separate.
  • the level sensor associated with the first receptacle 108 is, in this case, active.
  • each evaporator will be associated with a respective collecting receptacle 8.
  • the material, dimensions and constructional details may be different from those indicated but be technically equivalent thereto without thereby falling outside the legal domain of the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne une installation frigorifique qui comporte un fluide de refroidissement, un compresseur (1), un condenseur (3), une soupape de détente (5), un évaporateur (6), un réceptacle collecteur (8) pour recueillir ledit fluide de refroidissement, et un moyen de commande (14, 15) pour piloter ladite soupape de détente (5), ledit réceptacle collecteur (8) étant interposé entre une sortie dudit évaporateur (6) et une entrée dudit compresseur (1).
EP07859138A 2006-12-21 2007-12-21 Installation frigorifique Ceased EP2122272A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000418A ITMO20060418A1 (it) 2006-12-21 2006-12-21 Impianto di refrigerazione
PCT/IB2007/004029 WO2008081273A2 (fr) 2006-12-21 2007-12-21 Installation frigorifique

Publications (1)

Publication Number Publication Date
EP2122272A2 true EP2122272A2 (fr) 2009-11-25

Family

ID=39381990

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07859138A Ceased EP2122272A2 (fr) 2006-12-21 2007-12-21 Installation frigorifique

Country Status (4)

Country Link
US (1) US20100132395A1 (fr)
EP (1) EP2122272A2 (fr)
IT (1) ITMO20060418A1 (fr)
WO (1) WO2008081273A2 (fr)

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JP5845590B2 (ja) * 2011-02-14 2016-01-20 富士電機株式会社 ヒートポンプ式蒸気生成装置
DE102014203578A1 (de) * 2014-02-27 2015-08-27 Siemens Aktiengesellschaft Wärmepumpe mit Vorratsbehälter
GB2539911A (en) * 2015-06-30 2017-01-04 Arctic Circle Ltd Refrigeration apparatus
DE102017117565A1 (de) * 2017-08-02 2019-02-07 Wurm Gmbh & Co. Kg Elektronische Systeme Kälteanlage und verfahren zur regelung einer kälteanlage
US11536498B2 (en) 2020-05-11 2022-12-27 Hill Phoenix, Inc. Refrigeration system with efficient expansion device control, liquid refrigerant return, oil return, and evaporator defrost

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WO1998039605A1 (fr) * 1997-03-04 1998-09-11 Frigoscandia Equipment Ab Systeme frigorifique et separateur destine a ce systeme
WO1998057104A1 (fr) * 1997-06-11 1998-12-17 American Standard Inc. Procede et appareil de demarrage pour refroidisseurs

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US20100132395A1 (en) 2010-06-03
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