EP0240811A1 - Regelsystem für Anlagen mit einem Kältemittelkreislauf mit Kapillarrohrentspannung - Google Patents

Regelsystem für Anlagen mit einem Kältemittelkreislauf mit Kapillarrohrentspannung Download PDF

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Publication number
EP0240811A1
EP0240811A1 EP87104174A EP87104174A EP0240811A1 EP 0240811 A1 EP0240811 A1 EP 0240811A1 EP 87104174 A EP87104174 A EP 87104174A EP 87104174 A EP87104174 A EP 87104174A EP 0240811 A1 EP0240811 A1 EP 0240811A1
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EP
European Patent Office
Prior art keywords
liquid
container
refrigerant
evaporator
compressor
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.)
Withdrawn
Application number
EP87104174A
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English (en)
French (fr)
Inventor
Claudio Rossi
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.)
Hiross International Corp SA
Original Assignee
Hiross International Corp SA
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 Hiross International Corp SA filed Critical Hiross International Corp SA
Publication of EP0240811A1 publication Critical patent/EP0240811A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle

Definitions

  • the present invention relates to a system for regulating refrigeration circuit installations comprising a capillary expansion, installations in which a refrigerant flows through a thermodynamic cycle which consists of evaporation, compression, condensation and expansion.
  • the objective is to improve the known adjustment systems both from an economic point of view and from a regulation point of view.
  • the fields of application of the invention can be, by way of nonlimiting example: - compressed gas dryers - air conditioning units - heat pumps - liquid refrigerators - more besides.
  • Refrigerant circuits provided with a capillary rolling member.
  • Figures 2 and 3 moreover, show the same type of installation, but being in abnormal operating conditions, namely in the first case with insufficient refrigerant in the evaporator and in the second case, with an excess of refrigerant in the evaporator.
  • the reference 10 designates the evaporator, 11 the refrigerant (at the normal level in Figure 1, in insufficient quantity in Figure 2 and in excess in Figure 3), 12 the compressor, 13 the compressor motor, 14 the condenser, 15 a filter and 16 the expansion capillary.
  • the reference 17 indicates returns of refrigerant in the liquid state to the compressor 12 due to the presence of an excess of said fluid at the level of the evaporator 10.
  • the adjustment system by capillary rolling member is generally used in low-power installations in which it is important to have a low cost and where the drawbacks arising from the imperfect adaptability of the refrigerating installation to variable conditions of use of the capillary 16, which constitutes a regulating member of the static type, are of little importance.
  • This non-adaptability of the capillary 16 can alternatively cause significant overheating of the refrigerant aspirated by the compressor 12 or liquid returns 17, also to the compressor 12.
  • the high overheating can be caused for example by an insufficient charge of refrigerant 11 (see Figure 2) or by an increase in refrigeration charge requested from the evaporator 10 or by a significant decrease in the condensing pressure and can seriously damage the compressor 12 since the cooling of the windings of the electric motor 13, which is almost always supplied by the refrigerant drawn into the compressors 12 used for these applications, may no longer be sufficient.
  • the liquid returns 17 can for example be caused by an excessive charge of refrigerant fluid (see FIG. 3) or by a reduction in the fridge charge. required by the evaporator 10 or by a significant increase in the condensing pressure and can seriously damage the compressor 12 since the possible presence of liquid in the compression phase can lead to rupture of the valves or seizure of the compressor 12.
  • capillary tube installations 16 Another problem with capillary tube installations 16 results from the precision required for the metering of the charge, moreover rather reduced, of refrigerant. In fact, if there is leakage - even very small - of refrigerant, the installation discharges in a short time and gives rise to dangerous operating situations, such as too high overheating at compressor 12 already mentioned. In addition, the refrigerant charge requires a lot of attention and care since, as it is very small, small and large variations can significantly affect the performance and the operational safety of the installation.
  • Refrigerant circuits provided with rolling elements with thermostatic valve.
  • FIG. 5 also relates to this type of installation with a thermostatic valve, showing in detail the function exerted by the valve.
  • the evaporator is designated by the reference 10, the compressor by 12, the compressor motor by 13 and the condenser by 14.
  • the reference 18 marks the presence of a receptacle for receiving condensed fluid at the outlet of the condenser, 19 designates the thermostatic valve, 20 a detector of variation in the flow of refrigerant which will be discussed later.
  • the reference 21 indicates the liquid in evaporation in the evaporator 10 and the reference 22 designates a zone of superheating of the gas leaving the evaporator 10 and going towards the compressor 12.
  • the thermostatic valve 19 controls the flow of the refrigerant 11 which passes through it so as to maintain a constant and moderate superheating of the refrigerant in the vapor state at the outlet of the evaporator 10 (see reference 21 to the 5 to ensure the complete transformation of the refrigerant from liquid to gas and consequently to eliminate the possibility of dangerous returns of liquid to the compressor.
  • a drawback of the thermostatic valve system results from the instability that this dynamic type regulating member introduces. , due to the phase shifts, practically impossible to eliminate, between the effect on the system of the variation in refrigerant flow due to the regulating action of the valve and the signal which controls this regulating action and which comes from the detector 20 placed in downstream of the evaporator 10.
  • This instability of the system consists, for example, of a fluctuation in the evaporation pressure which gives rise to a deterioration in the performance of the installation.
  • the superheating which must be maintained at the outlet of the evaporator 10 must not be excessive but never lower than a minimum value otherwise, because of the variables which have just been described, there may be at certain times dangerous liquid returns to the compressor. This means that in thermostatic valve installations, part 22 of the evaporator exchange surface 10 must be intended for the superheating of the vapor and that, consequently, the exchange capacity of the evaporator is not fully exploited.
  • a regulating member capable of reducing the excess cooling capacity
  • Figures 6 and 7 give the diagram of installations of this type, Figure 6 for capillary tube installations (improvement to the installation of Figures 1 to 3) and Figure 7 for thermostatic valve installations (improvement to the 'installation of Figures 4 and 5).
  • the common members are designated by the same reference numbers as above (10 for the evaporator, 12 for the compressor, 13 for the motor, 14 for the condenser, 15 for the filter, 16 for the capillary, 18 for the container after the condenser, 19 for the thermostatic valve and 20 for the flow variation detector).
  • Reference 23 indicates the pressostatic or other valve for regulating the capacity and 24 the point of injection of the hot gas coming from the evaporator and from the regulating valve.
  • the refrigerant circuits with a capillary tube rolling member and capacity regulator keep the pressure but not the temperature of the refrigerating fluid under control downstream of the capacity regulating valve which injects hot gas and consequently, in the event of drawbacks such as loss of refrigerant or malfunction of the valves, they are exposed to drawbacks to the compressor due to the excessively high overheating which occurs in these cases.
  • the refrigeration circuits with laminating member with thermostatic valve and capacity regulator keep the temperature of the refrigerating fluid drawn in by the compressor under control, provided that the injection of hot gas occurs upstream of the detector of the thermostatic valve, but they can present, at partial loads, that is to say when the capacity regulating valve intervenes, fairly intense evaporation pressure fluctuations determined by the interaction between the two regulating organs. In practice, these interactions are very difficult to eliminate since both the thermostatic valve and the pressostatic valve are controlled by the evaporation pressure and that the intervention of any of their control functions influences this pressure.
  • the present invention consists of a capillary tube adjustment system making it possible to obviate the drawbacks of the existing systems indicated above.
  • thermodynamic cycle which consists of evaporation, compression, condensation and expansion
  • said system being characterized by fact that it comprises, in line, between the evaporator and the compressor, a small container containing refrigerant in the liquid state which simultaneously exercises the function of lung / liquid separator and of device ensuring a return of oil from compressor lubrication.
  • the small lung / liquid separator container has at its lower part a vapor inlet tube coming from the evaporator, at its upper part a suction tube extending into the container by a section of "U" -tube, the second branch of which stops a short distance from the upper part of the container and fitted in the bottom bend with a calibrated passage used to sample of a small quantity of liquid, and a liquid level indicator fixed on the body of the container, at a height located between the two tubes making it possible to ascertain the level of the liquid which is contained in the container and in which the incoming steam should bubble.
  • this level indicator can have any form of construction, even external to the container, provided that it is able to exercise its function.
  • the expansion capillary tube and the capacity of the lung / separator are dimensioned in such a way that whatever the operating condition (i.e. at any evaporation and condensation pressure) the refrigerant to the evaporator outlet is always in the saturated vapor state (never superheated).
  • the level in the container drops due to migration of refrigerant from it to the condenser which, due to the partial flooding of the condenser, causes an increase in subcooling and condensing pressure. In turn, these increases cause an increase in the capacity of the capillary and therefore an increase in the flow rate of the refrigerant.
  • the final situation will therefore be as follows: - increase in evaporation pressure - increase in condensing pressure - increased sub-cooling of the liquid at the capillary inlet - decrease in level in the lung / separator container - always saturated steam at the outlet of the evaporator.
  • the capacity of the container / lung is established in relation to the variations in volume of the coolant as a result of the variation in the operating conditions.
  • This variation in volume must be less than the capacity of said container and the free surface of the liquid refrigerant in the container must always be between the refrigerant outlet section, to prevent liquid from returning to the compressor, and the return device. of oil or the fluid inlet section coming from the evaporator, so that the oil return device is always immersed in the liquid and that there is always a certain amount of liquid above the entrance section.
  • the oil return device necessary for the lubrication of the compressor serves the fact that due to the complete evaporation of the refrigerant in the evaporator there occurs a complete separation between the oil, initially mixed with the refrigerating fluid to liquid state, and vapor.
  • the oil return is ensured by the mechanical drive due to the high speed of the vapor in the suction pipe, in this case, due to the low speed of the vapor in the lung / separator container, which must ensure the separation of the entrained droplets of liquid, it is necessary to withdraw (for example by exploiting the Venturi effect in a U-shaped tube) a small amount of liquid containing the oil not entrained in solution.
  • the level indicator is used to control the amount of refrigerant present and makes the charging phase of the refrigerant in the installation elementary. In fact, as soon as we know the level that the fluid must reach under the preselected charging conditions, it suffices to charge the refrigerant until that it reaches the prefixed level without any type of control.
  • an additional device can be provided for regulating the capacity of the pressostatic valve type.
  • the gas taken from the compressor discharge is mixed with the refrigerant at the outlet of the evaporator before the lung / separator container in order to eliminate the superheating of this gas by bubbling through the liquid contained therein, and therefore always ensure the presence of saturated steam at the compressor intake.
  • the present invention has the following advantages: - adaptability to wide variations in operating conditions, - possibility of application to installations having refrigerant charges which may be significant, thanks to an adequate dimensioning of the volume of the container / separator, without imbalance due to variations in speed, - functionality, even in large cooling capacity installations which generally require relatively large refrigerant charges, - consistency of the suction temperature of the refrigerant to the compressor, which always corresponds to that of the saturated steam.
  • the present invention is characterized by the advantages mentioned below: - reduced cost due to the absence of the thermostatic valve itself, - operating stability due to the absence of dynamic type regulations, - maximum use of the heat exchange surface of the evaporator since, unlike what occurs for the thermostatic valve, it is not necessary to overheat the refrigerant which therefore always works in the saturation state, - minimum torque at the compressor motor thrust, since the capillary quickly balances the suction and discharge pressures of the refrigerant circuit, - absence of instability of the operating conditions, even in the case of using a capacity regulation valve by injection of hot gas, thanks to the functional stability of the capillary, - efficient cooling of the electric motor of the compressor thanks to the small withdrawal of liquid which ensures the return of the oil.
  • reference 10 indicates the evaporator, the number 12 the compressor, 13 the compressor motor, 14 the condenser, 15 the filter 16 the expansion capillary and 23 (figure 11) the capacity regulating valve.
  • the lung / separator container placed at the outlet of the evaporator 10 is designated by the reference 1.
  • it may be of cylindrical shape (see FIGS. 9 and 10) and be provided with a tube d suction 2, of a level indicator 3 (for example a porthole-shaped sight fixed on the body of the container 1) and by an inlet tube 4 of the refrigerating tube coming from the evaporator 10, which tube is arranged preferably in the lower part of the container 1.
  • a level indicator 3 for example a porthole-shaped sight fixed on the body of the container 1
  • an inlet tube 4 of the refrigerating tube coming from the evaporator 10 which tube is arranged preferably in the lower part of the container 1.
  • the suction tube 2 is constituted, for example, by a section of pipe in "U" shape, the end of which inlet 5 is located at the upper part of the container 1 and which is provided with a calibrated passage 6 in the lower part, passage serving (as we have seen) to ensure adequate return of oil to the compressor, the second branch of the U-shaped tube stopping close to the top of the container.
  • the level indicator 3 which here has the shape of a transparent porthole, is placed higher than the inlet tube 4 so that the fluid which enters the container 1 must bubble through the liquid as far as the free surface of the latter is maintained in the visual field of the level 3 indicator.
  • FIG. 11 gives the diagram of an installation according to the invention which can be used more particularly in cases where the refrigerating charge requested from the evaporator can vary within significant limits, or even from 0% to 100%. It is then necessary to provide, in addition, a body for regulating capacity.
  • this member consists of a valve 23, which is here of the pressostatic type, placed in bypass between the discharge of the compressor 12 and the outlet of the evaporator 10 in order, as mentioned above, to always ensure the presence of saturated steam at the suction of the compressor.

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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)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compressor (AREA)
EP87104174A 1986-04-10 1987-03-21 Regelsystem für Anlagen mit einem Kältemittelkreislauf mit Kapillarrohrentspannung Withdrawn EP0240811A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
LU86391A LU86391A1 (fr) 1986-04-10 1986-04-10 Systeme de reglage des installations a circuit frigorifique comportant une detente a capillaire
LU86391 1986-04-10

Publications (1)

Publication Number Publication Date
EP0240811A1 true EP0240811A1 (de) 1987-10-14

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EP87104174A Withdrawn EP0240811A1 (de) 1986-04-10 1987-03-21 Regelsystem für Anlagen mit einem Kältemittelkreislauf mit Kapillarrohrentspannung

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EP (1) EP0240811A1 (de)
IT (1) IT1203467B (de)
LU (1) LU86391A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004053272B3 (de) * 2004-10-26 2006-04-27 Visteon Global Technologies, Inc. Intellectual Property Department, Van Buren Township Baugruppe für Kältemittel-Kreisläufe

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1746406A (en) * 1927-07-01 1930-02-11 Irving L Keith Refrigerating system
US1840954A (en) * 1929-01-04 1932-01-12 Baker Ice Machine Co Inc Refrigerant controlling apparatus
US2512758A (en) * 1946-10-03 1950-06-27 Winkler Morgenthaler Inc Combined refrigerant purifier and control apparatus
FR1067327A (fr) * 1952-12-01 1954-06-15 Réservoir à liquide avec tube indicateur de niveau
DE931048C (de) * 1953-01-03 1955-08-01 Paul Neunert Regeleinrichtung fuer Kompressionskaeltemaschine mit mehreren hintereinander geschalteten Verdampfern
US2770105A (en) * 1954-03-25 1956-11-13 Roland J Colton Automatic refrigerant slug disintegrator
US3651657A (en) * 1970-01-26 1972-03-28 Edward W Bottum Air conditioning system with suction accumulator
DE3105796A1 (de) * 1980-02-18 1981-12-17 Industriventilation Produkte AB, 35004 Vaxjö "waermepumpe"
EP0071062A1 (de) * 1981-07-23 1983-02-09 Giuseppe Tuberoso Behälter mit mehrfacher Funktion für ein thermo-dynamisches Fluidum
BE900218A (fr) * 1984-07-25 1985-01-25 Evzone Holding Appareil de conditionnement de l'air.
EP0143013A2 (de) * 1983-09-16 1985-05-29 Pactole S.A. Verfahren und Vorrichtung zum Überhitzen eines Kühlmittels
US4573327A (en) * 1984-09-21 1986-03-04 Robert Cochran Fluid flow control system

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1746406A (en) * 1927-07-01 1930-02-11 Irving L Keith Refrigerating system
US1840954A (en) * 1929-01-04 1932-01-12 Baker Ice Machine Co Inc Refrigerant controlling apparatus
US2512758A (en) * 1946-10-03 1950-06-27 Winkler Morgenthaler Inc Combined refrigerant purifier and control apparatus
FR1067327A (fr) * 1952-12-01 1954-06-15 Réservoir à liquide avec tube indicateur de niveau
DE931048C (de) * 1953-01-03 1955-08-01 Paul Neunert Regeleinrichtung fuer Kompressionskaeltemaschine mit mehreren hintereinander geschalteten Verdampfern
US2770105A (en) * 1954-03-25 1956-11-13 Roland J Colton Automatic refrigerant slug disintegrator
US3651657A (en) * 1970-01-26 1972-03-28 Edward W Bottum Air conditioning system with suction accumulator
DE3105796A1 (de) * 1980-02-18 1981-12-17 Industriventilation Produkte AB, 35004 Vaxjö "waermepumpe"
EP0071062A1 (de) * 1981-07-23 1983-02-09 Giuseppe Tuberoso Behälter mit mehrfacher Funktion für ein thermo-dynamisches Fluidum
EP0143013A2 (de) * 1983-09-16 1985-05-29 Pactole S.A. Verfahren und Vorrichtung zum Überhitzen eines Kühlmittels
BE900218A (fr) * 1984-07-25 1985-01-25 Evzone Holding Appareil de conditionnement de l'air.
US4573327A (en) * 1984-09-21 1986-03-04 Robert Cochran Fluid flow control system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004053272B3 (de) * 2004-10-26 2006-04-27 Visteon Global Technologies, Inc. Intellectual Property Department, Van Buren Township Baugruppe für Kältemittel-Kreisläufe
US7275391B2 (en) 2004-10-26 2007-10-02 Visteon Global Technologies, Inc. Assembly for refrigerant circuits

Also Published As

Publication number Publication date
IT8720055A0 (it) 1987-04-09
IT1203467B (it) 1989-02-15
LU86391A1 (fr) 1987-12-07

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