US2482171A - Flow control device for refrigeration apparatus - Google Patents

Flow control device for refrigeration apparatus Download PDF

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Publication number
US2482171A
US2482171A US62031145A US2482171A US 2482171 A US2482171 A US 2482171A US 62031145 A US62031145 A US 62031145A US 2482171 A US2482171 A US 2482171A
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refrigerant
evaporator
gas
liquid
flow
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Gygax Ernest
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Gen Engineering & Mfg Company
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B40/00Subcoolers, desuperheaters or superheaters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B1/00Compression machines, plant, or systems with non-reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements, e.g. for transferring liquid from evaporator to boiler
    • F25B41/06Flow restrictors, e.g. capillary tubes; Disposition thereof
    • F25B41/067Flow restrictors, e.g. capillary tubes; Disposition thereof capillary tubes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General 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
    • F25B2400/05Compression system with heat exchange between particular parts of the system
    • F25B2400/051Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General 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
    • F25B2400/05Compression system with heat exchange between particular parts of the system
    • F25B2400/052Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle

Description

Sept. 20, 1949. E. GYGAX 2,482,171

FLOW CONTROL DEVICE FOR REFRIGERATION APPARATUS Filed Oct. 4, 1945 9/1? T Fl. ow /4 Patented Sept. 20, 1949 FLOW CONTROL DEVICE FOR REFRIGERA- TION APPARATUS.

Ernest Gygax, St. Louis, Mo., assignor to General Engineering 8; Manufacturing Company, St. Louis, Mo., a corporation of Missouri Application October 4, 1945, Serial No. 620,311

1 Claim. 1

This invention relates to improvements in refrigerating apparatus, and more particularly to a unit adapted to be interposed in the refrigerating cycle for automatically controlling the feed for the refrigerant.

An object of the invention is to provide an eillcient unit in combination with a refrigerating cycle, which may be connected into a refrigerant flow system and whereby the refrigerating effect of the evaporator of such system maybe automatically controlled by controlling the feed to the evaporator in response to the viscosity of the refrigerant mixture in the liquid phase, the temperature of which is controlled by the cooling effect of the evaporator.

In my copending application, Serial No. 618,045, filed September 22, 1945, I have disclosed a method employing this principle of refrigerant flow control, and an apparatus for practicing the method in which the flow conduits for the refrigerant are built into the evaporator structure. The present invention contemplates the provision of an alternate construction of apparatus for performing the method of said copending application which includes a separate unit that may be connected into the standard system without alteration of the evaporator, and by which the control of the flow of the refrigerant is effected in response to the temperature of the expanded gas withdrawn from the evaporator.

Another object of the invention is to provide a unit of the type mentioned, which functions as a heat exchanger between the refrigerant in the gas phase and in theliquid phase, and which also acts as a gas liquid separator whereby the gas in the suction line of the compressor will be freed from a liquid component.

A more specific object of the present invention is to provide a heat exchanger adapted to be connected into the liquid refrigerant feed supply, and the gas discharger whereby the temperature of the gas withdrawn from the evaporator will cause a temperature change of the inflowing stream of refrigerant mixture, and thereby control the flow through the viscosity change in a component in the stream flow to the evaporator.

Additional advantages of the invention will appear from the following detailed description thereof, taken in connection with the accompanying drawing, in which:

Fig. 1 is a diagrammatic illustration of a conventional refrigerating system of the direct expansion type, and with which the control unit of the present invention is cooperatively associated.

Fig. 2 is a vertical section through the heat exchange control unit.

The system is fed from a refrigerant receiver I, and may be charged with any of the known standard refrigerating agents, such, for example, as Freon or methyl chloride or other agents having similar refrigerating characteristics. There is also mixed with the refrigerant an oil component, as fully disclosed in the above mentioned copending application, such as a light oil having an SAE viscosity No. 150, which is specifled only by way of example. A mixture of this character, as I have already disclosed in the copending application, has a viscosity range of approximately from 250 at 0 F. to '75 at approximately F. (Saybolt viscosity numbers). Since petroleum oil of this type is missible with the refrigerant, but due to its viscosity changes is responsive to temperature, it has a varying flow characteristic, which may be utilized in connection with the apparatus herein disclosed as a control for the evaporator feed, as will be more fully hereinafter explained.

The refrigerant oil mixture is withdrawn from the refrigerant oil receiver through a line 2 by which it is carried to the flow conduits of the heat exchanger, under pressure.

The heat exchanger, as disclosed in the drawing, includes a vessel having a cylindrical wall 3, bottom head 4 and a top head 5 fitted over the cylindrical wall 3 of the vessel.

The line 2 discharges into a branch conduit 6, the arms of which are extended into a pair of restricted capillary tube coils l, which coils are formed in an interfitting relationship and with a coil diameter sufliciently less than an inside diameter of the cylindrical wall 3 of the vessel so that they may be mounted therein in the manner clearly illustrated in Fig. 2.

The coils 1 have extensions 8 and 9 that constitute supply lines for the liquid refrigerant to the evaporator. The casing for the heat exchanges comprises the cylindrical walls 3 and the top and bottom walls 4 and 5, and is constructed to provide a gastight vessel with the inlet line 6 entering through the bottom header 4 and outlet lines 8 and 9 extending through the\upper header 5, having a sealed relationship therewith.

The vessel is internally provided in its lower portion with a reticulated member 10 in the form of a truncated cone which forms a screen when mounted, as illustrated in Fig. 2. On the bottom wall 4 of the vessel is a retaining flange II for the member l0, attached to the inner face of said wall 4. The screen member flares at the 3 top and bears against the inner periphery of the walls 3 at a substantial elevation above the bottom thereof, in the manner illustrated in Fig. 2.

The evaporator element of the system includes as illustrated, coils l2 and I3 arranged in vertical parallel planes, which coils extend through a series of plates H of the conventional airflow evaporator.

The conduits 8 and 9 are connected into said coils l2 and I3, respectively, and in which coils the liquid refrigerant is expanded, producing the normal cooling effect, the degree of which is de-, pendent upon the volume Of the liquid refrigerant supply, as will be readily understood, and the degree of cooling effect will be in accordance with the examples given in my copending application above referred to.

Each of the coils l2 and I 3 is connected at its lower end with an arm I and I6, respectively, of a branch fitting which merges into a conduit I1 entering the heat exchange vessel near the top thereof.

It will be understood that the gas is withdrawn? from the heat exchange vessel through a line l8 extending through the wall 3 and elevated some what above the bottom of the vessel. The line l8 extends to the suction inlet of a compressor lil, conventionally illustrated in Fig. 1, and after compression is discharged from the compressor through a line 20 to a condenser 2| where the compressed gas is condensed, and then flows through a line 22 to the refrigerant receiver, completing the refrigerating cycle.

Since the temperature of the gas passing;

through the heat exchange vessel is determined by the volume of the liquid refrigerant supply,

the cooling of the evaporator will be determined 1 by the control of that volume.

The admixture of the oil with the refrigerant 40 vary in viscosity, due to the regulation of the; temperature of the stream as reflected by the causes the streams flowing through the coils 1 to tem erature of the gas leaving the evaporator and If the flow of liquid refrigerant is insufilaent to produce the optimum temperature of the gas in the heat exchanger to maintain the predetermined cooLng capacity of the evaporator, the supply stream of the liquid refrigerant and oil reduces in viscosity and the rate of flow is thereby increased. Similarly, if the supply of liquid refrigerant exceeds the predetermined amount for refrigerating output of the evaporator, the viscosity of the refrigj erantoil stream will increase and the flow will be reduced.

It will, of course, be understood as explained in the above mentioned copending application,

tioned and a refrigerant comprising a. Freon mixture therewith in which the oil is from 5 to 20% by volume, a coil length of approximately thirty feet of restricted tubing of approximately .04

inch will provide an effective control within the normal range of temperature variation of the that the length of the coils i must be properly solid particles from the gas stream by providing the screen ID in the bottom of the heat exchange vessel, which screen extends above the gas outlet.

Since the oil specified is completely missible with the refrigerant, it will not be trapped from the gas stream but only that portion of the refrigerating agent that is liquid when it reaches the lower portion of the heat exchange vessel will be accumulated in the bottom thereof.

A valved withdrawal pipe 23 may be provided in the bottom wall 4 of the heat exchange vessel for withdrawing, any accumulation of liquid from the vessel, if desired.

From the foregoing description, it will be understood that I have provided a construction that fully accomplishes its purposes. It will, likewise, be understood that certain changes in form and dimension of the parts may be made without departing from the spirit and scope of the invention.

What I claim and desire to secure by Letters Patent is:

A refrigerant fiow control attachment for refrigeration apparatus adapted to automatically control the flow of a refrigerant and a missible oil mixture comprising a sealed casing, a plurality of capillary coils disposed in said casing having inlets at one end and outlets at the other end thereof, said inlets being adapted to be connected to a refrigerant receiver, said outlets being adapted to be connected to separate evaporator coils, an inlet in the casing adjacent said coil out-ets adapted to be connected to an evaporator outlet, an outlet in the casing adjacent said coil inlets adapted to be connected to the suction side of a compressor,

said refrigerant gas outlet being disposed above a bottom level of said casing to provide a liquid trap, and means for withdrawing any accumulated liquid from the casing, whereby a heat exchange relationship obtains between a refrigerant and oil liquid mixture in said coils and refrigerant gas in said casing when said attachment is installed.

ERNEST GYGAX.

REFERENCES CITED The following references are of record in the file of this patent: I

Great Britain Oct. 24, 1896

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Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2539908A (en) * 1948-05-19 1951-01-30 Seeger Refrigerator Co Multiple temperature refrigerating system
US2956418A (en) * 1958-07-11 1960-10-18 Mccann Gerry Beverage chiller and dispenser
US2983112A (en) * 1956-07-05 1961-05-09 Joseph R Batteiger Refrigeration apparatus
US3102397A (en) * 1961-03-18 1963-09-03 Trucchi Dante Air-cooling and aeration system for ship's cabins and the like
US3145545A (en) * 1962-10-10 1964-08-25 Wilbert J Jaeger Air conditioning and refrigeration apparatus for motor vehicles
US3283524A (en) * 1964-03-17 1966-11-08 Byron John Thomson Refrigeration system
US4341092A (en) * 1980-11-20 1982-07-27 Liquid Modulators, Inc. Liquid modulator
USRE32092E (en) * 1984-07-27 1986-03-18 Liquid Modulators, Inc. Liquid modulator
US4936113A (en) * 1989-02-03 1990-06-26 Nivens Jerry W Thermal inter-cooler
WO1993006422A1 (en) * 1991-09-19 1993-04-01 Mayer Holdings S.A. Thermal inter-cooler
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
US5289699A (en) * 1991-09-19 1994-03-01 Mayer Holdings S.A. Thermal inter-cooler
US5622055A (en) * 1995-03-22 1997-04-22 Martin Marietta Energy Systems, Inc. Liquid over-feeding refrigeration system and method with integrated accumulator-expander-heat exchanger
WO2001073360A1 (en) * 2000-03-13 2001-10-04 Zimmermann Lars Christian Wulf Regulator with receiver for refrigerators and heatpumps
EP1279911A1 (en) * 2001-07-23 2003-01-29 Zexel Valeo Climate Control Corporation Refrigerant tubing for a vehicle air conditioning system
US6679320B2 (en) * 1998-05-28 2004-01-20 Valeo Climatisation Vehicle air conditioning circuit using a refrigerant fluid in the supercritical state
US20040261449A1 (en) * 2003-06-24 2004-12-30 Memory Stephen B. Refrigeration system
US6848268B1 (en) 2003-11-20 2005-02-01 Modine Manufacturing Company CO2 cooling system
US20050044864A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Apparatus for the storage and controlled delivery of fluids
US20050044865A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Multi-stage vapor compression system with intermediate pressure vessel
US20050109486A1 (en) * 2003-11-20 2005-05-26 Memory Stephen B. Suction line heat exchanger for CO2 cooling system
US20050132729A1 (en) * 2003-12-23 2005-06-23 Manole Dan M. Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
DE102010034112A1 (en) * 2010-08-12 2012-02-16 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Internal heat exchanger for a motor vehicle air conditioning
CN103123230A (en) * 2011-11-17 2013-05-29 通用汽车环球科技运作有限责任公司 Heat exchanger for a motor vehicle air conditioning system
DE102013004600A1 (en) * 2013-02-28 2014-08-28 Liebherr-Hausgeräte Lienz Gmbh Refrigerating and/or freezing apparatus has battery formed as component of heat exchanger located between compressor and evaporator, and capillary for making refrigerant to flow into evaporator

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB189611177A (en) * 1896-01-17 1896-10-24 Alexander Mcvicar An Improvement or Improvements in Refrigerating and Ice-making Machines.
US2393854A (en) * 1942-01-31 1946-01-29 Elizabeth C Carpenter Feed control for liquid refrigerant

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB189611177A (en) * 1896-01-17 1896-10-24 Alexander Mcvicar An Improvement or Improvements in Refrigerating and Ice-making Machines.
US2393854A (en) * 1942-01-31 1946-01-29 Elizabeth C Carpenter Feed control for liquid refrigerant

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2539908A (en) * 1948-05-19 1951-01-30 Seeger Refrigerator Co Multiple temperature refrigerating system
US2983112A (en) * 1956-07-05 1961-05-09 Joseph R Batteiger Refrigeration apparatus
US2956418A (en) * 1958-07-11 1960-10-18 Mccann Gerry Beverage chiller and dispenser
US3102397A (en) * 1961-03-18 1963-09-03 Trucchi Dante Air-cooling and aeration system for ship's cabins and the like
US3145545A (en) * 1962-10-10 1964-08-25 Wilbert J Jaeger Air conditioning and refrigeration apparatus for motor vehicles
US3283524A (en) * 1964-03-17 1966-11-08 Byron John Thomson Refrigeration system
US4341092A (en) * 1980-11-20 1982-07-27 Liquid Modulators, Inc. Liquid modulator
USRE32092E (en) * 1984-07-27 1986-03-18 Liquid Modulators, Inc. Liquid modulator
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
US4936113A (en) * 1989-02-03 1990-06-26 Nivens Jerry W Thermal inter-cooler
WO1990008930A1 (en) * 1989-02-03 1990-08-09 Nivens Jerry W Thermal inter-cooler
WO1993006422A1 (en) * 1991-09-19 1993-04-01 Mayer Holdings S.A. Thermal inter-cooler
US5289699A (en) * 1991-09-19 1994-03-01 Mayer Holdings S.A. Thermal inter-cooler
US5568736A (en) * 1991-09-19 1996-10-29 Apollo Environmental Systems Corp. Thermal inter-cooler
US5622055A (en) * 1995-03-22 1997-04-22 Martin Marietta Energy Systems, Inc. Liquid over-feeding refrigeration system and method with integrated accumulator-expander-heat exchanger
US6679320B2 (en) * 1998-05-28 2004-01-20 Valeo Climatisation Vehicle air conditioning circuit using a refrigerant fluid in the supercritical state
WO2001073360A1 (en) * 2000-03-13 2001-10-04 Zimmermann Lars Christian Wulf Regulator with receiver for refrigerators and heatpumps
EP1701117A2 (en) * 2001-07-23 2006-09-13 Zexel Valeo Climate Control Corporation Refrigerant tubing for a vehicle air conditioning system
EP1701117A3 (en) * 2001-07-23 2006-09-20 Zexel Valeo Climate Control Corporation Refrigerant tubing for a vehicle air conditioning system
EP1279911A1 (en) * 2001-07-23 2003-01-29 Zexel Valeo Climate Control Corporation Refrigerant tubing for a vehicle air conditioning system
US20040261449A1 (en) * 2003-06-24 2004-12-30 Memory Stephen B. Refrigeration system
US20050044864A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Apparatus for the storage and controlled delivery of fluids
US20050044865A1 (en) * 2003-09-02 2005-03-03 Manole Dan M. Multi-stage vapor compression system with intermediate pressure vessel
US6923011B2 (en) 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
US6959557B2 (en) 2003-09-02 2005-11-01 Tecumseh Products Company Apparatus for the storage and controlled delivery of fluids
US20050109486A1 (en) * 2003-11-20 2005-05-26 Memory Stephen B. Suction line heat exchanger for CO2 cooling system
US6848268B1 (en) 2003-11-20 2005-02-01 Modine Manufacturing Company CO2 cooling system
US7261151B2 (en) 2003-11-20 2007-08-28 Modine Manufacturing Company Suction line heat exchanger for CO2 cooling system
US20050132729A1 (en) * 2003-12-23 2005-06-23 Manole Dan M. Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
US7096679B2 (en) 2003-12-23 2006-08-29 Tecumseh Products Company Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
DE102010034112A1 (en) * 2010-08-12 2012-02-16 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Internal heat exchanger for a motor vehicle air conditioning
US9279621B2 (en) 2010-08-12 2016-03-08 GM Global Technology Operations LLC Internal heat exchanger for a motor vehicle air-conditioning system
CN103123230A (en) * 2011-11-17 2013-05-29 通用汽车环球科技运作有限责任公司 Heat exchanger for a motor vehicle air conditioning system
DE102013004600A1 (en) * 2013-02-28 2014-08-28 Liebherr-Hausgeräte Lienz Gmbh Refrigerating and/or freezing apparatus has battery formed as component of heat exchanger located between compressor and evaporator, and capillary for making refrigerant to flow into evaporator

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