US2363273A - Refrigeration - Google Patents

Refrigeration Download PDF

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Publication number
US2363273A
US2363273A US48936843A US2363273A US 2363273 A US2363273 A US 2363273A US 48936843 A US48936843 A US 48936843A US 2363273 A US2363273 A US 2363273A
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Prior art keywords
evaporator
compressor
vapor
valve
refrigerant
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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.)
Expired - Lifetime
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Inventor
Robert W Waterfill
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BUENSOD STACEY Inc
BUENSOD-STACEY Inc
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BUENSOD STACEY Inc
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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
    • F25B41/00Fluid-circulation arrangements, e.g. for transferring liquid from evaporator to boiler
    • F25B41/04Disposition of valves

Description

Nov. 21, 1944. R. w. WATERFlLL 2,363,273

REFRIGERATION Filed June 2, 1945 IN V EN TOR. 30 bar! W. Wafer/1'1! Patented Nov. 21, 1944 REFRIGERATION Robert W. Waterfill, Montclalr, N. 3., assignor to Buensod- Stacey, Incorporated, New York, N. Y., a corporation of Delaware Applicgtion June 2, 1943, Serial No. 489,368

Claims.

This invention relates to refrigerating systems, and, more particularly, to improvements in the arrangements for controlling the operation of such systems.

The principal object of the invention is to provide a refrigerating system which may be operated continuously to maintain a substantially constant temperature at the evaporator, regardless of whether the heat load upon that element is almost zero or is approaching the maximum for which the system was designed.

It is a further object of the invention to provide a refrigerating system in which the supply of refrigerant to the evaporator may be varied in precise accordance with the heat load imposed on that element, and in which the suction pressure of the compressor may be maintained at or above some predetermined minimum, wherefore the system as a whole may be operated continuously with its capacity modulated at any point between zero and full load conditions.

It is a more specific object of the invention to provide a refrigerating system with a bypass through which refrigerant vapor may be circulated to maintain a minimum load on the compressor of the system whenever the load on the evaporator falls below some predetermined value, and a second by-pass through which liquid refrigerant may be bled from the condenser of the system into the suction side of the compressor, whereby to maintain the temperature of vapor which is circulated through the first-mentioned by-pass, at or below some predetermined temperature.

The foregoing and other objects of the invention will be better understood from a consideration of the following description in the light of the accompanying drawing, which illustrates diagrammatically a refrigerating system in which the features of the invention have been incorporated.

Referring to the drawing, the evaporator I0 may be of any suitable design, and may of course be employed to coolany appropriate medium to a desired final temperature. It will be assumed, for purposes of description, however, that the medium in question is air, that it passes over the surfaces of the evaporator at such widely varying temperatures as at times to impose a maximum heat load on that element, and at other times a load which is so light as to be almost negligible, and that the evaporator must function to cool that air to a substantially constant final temperature. ployed to control the operation of-the evaporator in such a way as to meet this last-mentioned re- Any suitable means may be emquirement. As here shown, the control takes the form of a liquid feed valve I I which is located in liquid line I2, and serves to regulate the quantity of liquid refrigerant admitted to the evaporator from the condenser I3 of the system in response to variations in heat load as reflected by changes in the superheat temperature of vapor leaving the evaporator.

The operation of the liquid valve is entirely conventional and need be little more than mentioned. Thus, upon an increase in the superheat of vapor leaving the evaporator, a condition which reflects an increased load on the latter element, the thermo-sensitive bulb I4 acts through control line I5 to open valve I I and permit an increased flow of liquid refrigerant such as will meet the new load condition. Conversely, a decrease'iin load will be reflected by a decrease in superheat, and the bulb I4 will react to close the valve and reduce the flow of refrigerant to the evaporator.

In those cases in which a finer, more precise, control of the evaporator temperature is required, a back-pressure control may be added to the system. The control which performs this service in the illustrated system is a conventional back-pressure valve I6 located in the suction line at a point adjacent the evaporator, and having its control line I1 connected to the suction line substantially as shown. Accordingly, when the pressure in the evaporator rises above a predetermined value, this increased pressure acting upon the valve will open that element and permit an increased flow of vapor through the suction line to the compressor I8, In the event, however, that the evaporator pressure tends to fall below the set value, the valve will close to whatever extent is required to hold the back pressure, and hence the evaporator temperature, at the desired point.

It will be apparent to those familiar with the art that either one of the valves II and I6 will, alone, regulate the operation of the evaporator to meet variations in heat load. Either one may be dispensed with, and the system operated on the one which is retained, or both may be employed, as the needs of the particular case seem to require. It will also be evident that various other forms of control may be substituted for those which have been illustrated and described;

' and that all that is required by this invention is some means which will regulate the flow of refrigerant through the evaporator in accordance with variations in load on that element.

The illustrated compressor I8 is of the conventional positive displacement type in which a piston (not shown) is continuously reciprocated whereby continuously to withdraw refrigerant vapor from evaporator I through suction line 2|, and to compress that vapor, and simultaneously raise its temperature, so that it may flow through discharge line 22 to the condenser l3 of the system. While any other suitable form of, compressor may be employed, the one shown is widely used, and serves particularly well to illustrate the utility of the invention.

It will be evident that if the evaporator is to operate continuously, the compressor must likewise operate uninterruptedly. It will also be recognized, however, that when the flow of refrigerant to the evaporator is greatly reduced, and perhaps interrupted on occasion, by the operation of valves II and I6, continued operation of the compressor would, in the system as so far described, serve to reduce the pressure in the suction line 2| to an undesirably low value. In order to prevent the suction pressure from falling unduly, and thus to avoid the concomitant problems of compressor shaft sealing, bearing lubrication and others with which those skilled in the art are familiar, a by-pass line 23 is connected across the suction and discharge lines 2| and 22, thus providing a path through which a controlled flow of vapor may be established whenever the normal flow from evaporator I is severely restricted. The control of this line is simply effected by a conventional pressure-actuated valve 24 located in the by-pass and having its control line 25 connected to the by-pass on the suction side thereof. Accordingly, when the suction pressure drops below a desired point, this low pressure acting upon the diaphragm or bellows (not shown) of the valve 24, allows that valve to open and permit a recirculation of vapor from the discharge line 22 back to the intake of the compressor. Conversely, when the suction pressure rises above the set point, it acts to hold the valve 24 closed and thus to allow operation of the system in the normal way.

It will be evident that continued recirculation of vapor through by-pass 23 will produce a cumulative heating effect which, if not offset, will result in the raising of the temperature of the vapor to a dangerously high value. In order to balance-out this heating effect, a second bypass line 26 is connected from the liquid line l2 on the condenser side of the system to some point in the suction side of the compressor, and means are provided which will permit a controlled bleeding or injection of liquid refrigerant into the hot recirculating vapor whereby to cool that vapor to a desired degree. As here shown, this means comprises a thermo-operated liquid feed valve 21, which may be of any conventional construction, installed in the by-pass line 26 with its thermo-responsive bulb 28 secured to the suction side of by-pass line 23.

The operation of valve 21 is entirely conventional. Thus, when the superheat temperature of vapor recirculated through the first by-pass rises above a predetermined value, thermo-bulb 28 will react, through control line 28, to open valve 21 and establish a flow of liquid refrigerant into the suction side of the compressor. The liquid thus injected will immediately evaporate,

thereby abstracting heat from the vapor, and

cooling it to a desired degree. At that point, of course, the thermo-bulb 28 again reacts, this time tending to close valve 21, thus reducing the fiow of liquid until it is just sufficient in quantity within cylinder l9 by an associated motor 20,

to offset the superheating of recirculated vapor above a desired temperature.

It will be noted that in the illustrated system, the liquid by-pass line 26 joins the vapor bypass line at a point well back from the junction of the latter line with suction line 2|. While this precise arrangement is not essential, it is desirable that the liquid be injected into the suction side of the compressor at such a point as to allow for its complete vaporization by the recirculated vapor whereby to avoid the passage of liquid refrigerant directly into the compressor. In this connection it will also be recognized by those familiar with the art that the thermo-responsive bulb 28 need not be located precisely as shown, but may be placed on suction line 2i or at some other appropriate point.

Those familiar with the art will recognize that the vapor and liquid by-pass lines and their associated controls, serve to establish a minimum artificial load upon the compressor whenever the normal load supplied by the evaporator is unduly low; and that this artificial loading of the compressor permits the continued operation of the system as a whole with its refrigerating effect modulated precisely in accordance with the demand upon the evaporator. They will also recognize that the various structural elements of the system, the evaporator, compressor, condenser, connecting lines, and control valves, may be of any appropriate design, and that the illustrated arrangements of these elements are entirely diagrammatic and may be varied in accordance with good engineering practice.

What I claim is:

1. A refrigerating system comprising an evaporator, a compressor, a condenser, and lines permitting a circulation of refrigerant between said elements; means for regulating the flow of liquid refrigerant from said condenser to said evaporator in response to variations in the heat load affecting the latter element; means for by-passing refrigerant vapor from the discharge side of said compressor to the inlet side thereof whereby to maintain the pressure at the inlet side above a predetermined minimum; and means for by-passing refrigerant liquid from said condenser to the inlet side of said compressor whereby to cool vapor by-passed from the discharge side of said compressor.

2. A refrigerating system comprising an evaporator, a compressor, a condenser, and refrigerant circulating lines between said elements; means for governing the flow of refrigerant through said evaporator in response to variations in heat load affecting that element; means for admitting refrigerant vapor directly from the outlet side of said compressor to the inlet side thereof responsive to the existence of a predetermined low pressure at such inlet side; and means for admitting refrigerant from said condenser directly to the inlet side of said. compressor responsive to the existence of a predetermined high temperature at such inlet side.

3. A refrigerating system comprising an evaporator, a compressor, a condenser, and refrigerant circulating lines connecting said several elements; means for regulating the flow of refrigerant through said evaporator to said compressor in accordance with variations in heat load upon said evaporator; a connection between the inlet and discharge sides of said compressor, and means responding to the existence of a predetermined low pressure at such inlet side for regulating the flow of refrigerant vapor through said connection; a connection from the condenser side of the system directly to the inlet side of said compressor, and means for regulating the flow of liquid refrigerant through said last-mentioned connection in response to the existence of a predetermined high temperature at the inlet side of said compressor.

4. A refrigerating system comprising an evape orator, a compressor, a condenser, and refrigerant circulating lines between said several elements; means for regulating the flow of liquid refrigerant from said condenser through said evaporator in response to variations in heat load upon the latter element; a conduit directly connecting the inlet and discharge sides of said compressor, a valve in said conduit, and means for actuating said valve in response to the existence of a predetermined low pressure at such inlet side; a second conduit connecting the discharge side of said condenser with the inlet side of said compressor, a second valve located in said second conduit, and means for actuating said second valve in response to the existence of a predetermined high temperature at the inlet side of said compressor.

5. A refrigerating system comprising an evaporator, a compressor, a condenser, and refrigerant circulating lines between said several elements; means for regulating the flow of liquid refrigerant from said condenser through said evaporator in response to variations in heat load upon the latter element; a conduit directly connecting the inlet and discharge sides of said compressor, a valve in said conduit, and means for actuating said valve in response to the existence of a predetermined low pressure at such inlet side; a second conduit directly connecting the condenser side of said system with said firstmentioned conduit, a valve in said second-mentioned conduit, and means for actuating said lastmentioned valve to admit liquid refrigerant from the condenser side of said system to said firstmentioned conduit responsive to the existence of a predetermined high temperature-in said second conduit.

ROBERT W. WA'IERFIIL.

US2363273A 1943-06-02 1943-06-02 Refrigeration Expired - Lifetime US2363273A (en)

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Cited By (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2418853A (en) * 1944-11-29 1947-04-15 Philco Corp Refrigerating apparatus in which the pressure in the crankcase of the compressor is controlled
US2423382A (en) * 1943-11-20 1947-07-01 Gen Motors Corp Control for air conditioning systems
US2446156A (en) * 1946-05-13 1948-07-27 Frank F Kolz Automatic freezer control and refrigerating system
US2456386A (en) * 1946-05-07 1948-12-14 Howell C Cooper Cascade refrigeration unit with controls therefor
US2470655A (en) * 1944-06-12 1949-05-17 Allis Chalmers Mfg Co Cooling and lubrication of compressors
US2506757A (en) * 1946-07-16 1950-05-09 Carrier Corp Refrigeration system
US2513361A (en) * 1944-11-01 1950-07-04 Specialties Dev Corp Method and system for producing low-temperature refrigeration
US2564310A (en) * 1950-10-05 1951-08-14 Kramer Trenton Co Means for controlling the head pressure in refrigerating systems
US2577107A (en) * 1947-05-09 1951-12-04 Gen Electric Compressor head cooling system for refrigerator machines
US2675683A (en) * 1954-04-20 Control means fob refrigeration
US2739451A (en) * 1952-09-30 1956-03-27 Carrier Corp Refrigeration system provided with compressor unloading mechanism
US2765629A (en) * 1946-02-02 1956-10-09 Carrier Corp Refrigerant expansion control
US2774219A (en) * 1954-10-27 1956-12-18 Gen Motors Corp Automobile refrigerating apparatus
US2957318A (en) * 1956-06-13 1960-10-25 Liquefreeze Company Inc Control for refrigerating system
US2963878A (en) * 1959-06-19 1960-12-13 United Aircraft Corp Compressor surge prevention and drive motor cooling system
US3064447A (en) * 1959-11-16 1962-11-20 Gen Motors Corp Control for refrigerating apparatus
US3142969A (en) * 1962-11-13 1964-08-04 Phillips Petroleum Co Refrigeration control system
US3201950A (en) * 1963-09-26 1965-08-24 Larkin Coils Inc Refrigeration apparatus including liquid injection desuperheater
US3349570A (en) * 1964-02-04 1967-10-31 Dryvent Ltd Adsorptive removal of contaminants from compressed gas mixture
US3390540A (en) * 1966-08-16 1968-07-02 Carrier Corp Multiple evaporator refrigeration systems
US3477240A (en) * 1968-03-25 1969-11-11 Refrigeration System Ab Refrigerating method and system for maintaining substantially constant temperature
US3736074A (en) * 1972-04-20 1973-05-29 Worthington Cei Inlet, filter and noise suppressor enclosure for compressing apparatus
US3911693A (en) * 1974-05-06 1975-10-14 Friedrich Refrigerators Inc Hazardous duty room air conditioner
US3948060A (en) * 1972-05-24 1976-04-06 Andre Jean Gaspard Air conditioning system particularly for producing refrigerated air
US4017286A (en) * 1975-12-22 1977-04-12 Westinghouse Electric Corporation Heat pump suction line vent
DE3002165A1 (en) * 1979-02-05 1980-08-14 Carrier Corp Vapor compression-Cooling and operational procedures for such
US4326868A (en) * 1978-12-20 1982-04-27 Tokyo Shibaura Denki Kabushiki Kaisha Refrigeration system utilizing a gaseous refrigerant bypass
US4487034A (en) * 1981-03-27 1984-12-11 Lockheed Corporation Energy-efficient all-electric ECS for aircraft
EP0247236A2 (en) * 1986-05-27 1987-12-02 Tecumseh Products Company Refrigeration system including capacity modulation
US4870834A (en) * 1987-05-29 1989-10-03 Nippondenso Co., Ltd. Vapor pressure-adjusting valve and refrigeration system using same
EP0348333A1 (en) * 1988-06-20 1989-12-27 Carrier Corporation Quench expansion valve refrigeration circuit
US4920757A (en) * 1988-08-18 1990-05-01 Jimmy Gazes Geothermal heating and air conditioning system
US5052189A (en) * 1987-10-29 1991-10-01 Sanden Corporation Heat pump refrigeration system for a motor vehicle
US5201189A (en) * 1990-09-13 1993-04-13 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerant compressor with an initial seizure prevention means
US5207072A (en) * 1990-03-08 1993-05-04 Rayco Enterprises, Inc. Unloading structure for compressor of refrigeration system
US5657637A (en) * 1994-11-25 1997-08-19 Technotrans Gmbh Assembly for temperature control of a fountain fluid and/or selected rolls of a printing press
US5937658A (en) * 1998-02-24 1999-08-17 Scotsman Group Apparatus and method for head pressure control valve disabling for an icemaker
EP1000787A3 (en) * 1998-11-09 2002-06-19 Denso Corporation Vehicle refrigerating cycle apparatus and method for inhibiting cycle corrosion and for facilitating rapid passenger compartment warm-up during low temperature conditions
US20040040459A1 (en) * 2000-03-16 2004-03-04 Hans-Heinrich Henning Method and device for utilising the waste heat that has accumulated during the supply of forced draught/compressed air to a printing press
WO2005022053A1 (en) * 2003-09-02 2005-03-10 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Compressor or air-conditioning system
WO2007068336A1 (en) * 2005-12-17 2007-06-21 Ixetic Mac Gmbh Air-conditioning compressor
DE102015016377A1 (en) * 2015-12-17 2017-06-22 Man Diesel & Turbo Se Refrigeration plant-Umblaseventil and refrigeration plant

Cited By (48)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2675683A (en) * 1954-04-20 Control means fob refrigeration
US2423382A (en) * 1943-11-20 1947-07-01 Gen Motors Corp Control for air conditioning systems
US2470655A (en) * 1944-06-12 1949-05-17 Allis Chalmers Mfg Co Cooling and lubrication of compressors
US2513361A (en) * 1944-11-01 1950-07-04 Specialties Dev Corp Method and system for producing low-temperature refrigeration
US2418853A (en) * 1944-11-29 1947-04-15 Philco Corp Refrigerating apparatus in which the pressure in the crankcase of the compressor is controlled
US2765629A (en) * 1946-02-02 1956-10-09 Carrier Corp Refrigerant expansion control
US2456386A (en) * 1946-05-07 1948-12-14 Howell C Cooper Cascade refrigeration unit with controls therefor
US2446156A (en) * 1946-05-13 1948-07-27 Frank F Kolz Automatic freezer control and refrigerating system
US2506757A (en) * 1946-07-16 1950-05-09 Carrier Corp Refrigeration system
US2577107A (en) * 1947-05-09 1951-12-04 Gen Electric Compressor head cooling system for refrigerator machines
US2564310A (en) * 1950-10-05 1951-08-14 Kramer Trenton Co Means for controlling the head pressure in refrigerating systems
US2739451A (en) * 1952-09-30 1956-03-27 Carrier Corp Refrigeration system provided with compressor unloading mechanism
DE951815C (en) * 1952-09-30 1956-11-08 Carrier Corp Method and apparatus for controlling a compression Kaelteanlage
US2774219A (en) * 1954-10-27 1956-12-18 Gen Motors Corp Automobile refrigerating apparatus
US2957318A (en) * 1956-06-13 1960-10-25 Liquefreeze Company Inc Control for refrigerating system
US2963878A (en) * 1959-06-19 1960-12-13 United Aircraft Corp Compressor surge prevention and drive motor cooling system
US3064447A (en) * 1959-11-16 1962-11-20 Gen Motors Corp Control for refrigerating apparatus
US3142969A (en) * 1962-11-13 1964-08-04 Phillips Petroleum Co Refrigeration control system
US3201950A (en) * 1963-09-26 1965-08-24 Larkin Coils Inc Refrigeration apparatus including liquid injection desuperheater
US3349570A (en) * 1964-02-04 1967-10-31 Dryvent Ltd Adsorptive removal of contaminants from compressed gas mixture
US3390540A (en) * 1966-08-16 1968-07-02 Carrier Corp Multiple evaporator refrigeration systems
US3477240A (en) * 1968-03-25 1969-11-11 Refrigeration System Ab Refrigerating method and system for maintaining substantially constant temperature
US3736074A (en) * 1972-04-20 1973-05-29 Worthington Cei Inlet, filter and noise suppressor enclosure for compressing apparatus
US3948060A (en) * 1972-05-24 1976-04-06 Andre Jean Gaspard Air conditioning system particularly for producing refrigerated air
US3911693A (en) * 1974-05-06 1975-10-14 Friedrich Refrigerators Inc Hazardous duty room air conditioner
US4017286A (en) * 1975-12-22 1977-04-12 Westinghouse Electric Corporation Heat pump suction line vent
US4326868A (en) * 1978-12-20 1982-04-27 Tokyo Shibaura Denki Kabushiki Kaisha Refrigeration system utilizing a gaseous refrigerant bypass
DE3002165A1 (en) * 1979-02-05 1980-08-14 Carrier Corp Vapor compression-Cooling and operational procedures for such
FR2448115A1 (en) * 1979-02-05 1980-08-29 Carrier Corp refrigeration installation with cold vapor compression refrigerant reinjection into the fluid refrigerant evaporates, and its method of operation
US4258553A (en) * 1979-02-05 1981-03-31 Carrier Corporation Vapor compression refrigeration system and a method of operation therefor
US4487034A (en) * 1981-03-27 1984-12-11 Lockheed Corporation Energy-efficient all-electric ECS for aircraft
EP0247236A2 (en) * 1986-05-27 1987-12-02 Tecumseh Products Company Refrigeration system including capacity modulation
EP0247236A3 (en) * 1986-05-27 1990-05-16 Tecumseh Products Company Refrigeration system including capacity modulation
US4870834A (en) * 1987-05-29 1989-10-03 Nippondenso Co., Ltd. Vapor pressure-adjusting valve and refrigeration system using same
US5052189A (en) * 1987-10-29 1991-10-01 Sanden Corporation Heat pump refrigeration system for a motor vehicle
EP0348333A1 (en) * 1988-06-20 1989-12-27 Carrier Corporation Quench expansion valve refrigeration circuit
US4920757A (en) * 1988-08-18 1990-05-01 Jimmy Gazes Geothermal heating and air conditioning system
US5207072A (en) * 1990-03-08 1993-05-04 Rayco Enterprises, Inc. Unloading structure for compressor of refrigeration system
US5201189A (en) * 1990-09-13 1993-04-13 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerant compressor with an initial seizure prevention means
US5657637A (en) * 1994-11-25 1997-08-19 Technotrans Gmbh Assembly for temperature control of a fountain fluid and/or selected rolls of a printing press
DE4442072B4 (en) * 1994-11-25 2005-11-10 Technotrans Ag An arrangement for temperature control of a fountain solution and a cooling fluid to selected rollers of a printing machine
US5937658A (en) * 1998-02-24 1999-08-17 Scotsman Group Apparatus and method for head pressure control valve disabling for an icemaker
EP1000787A3 (en) * 1998-11-09 2002-06-19 Denso Corporation Vehicle refrigerating cycle apparatus and method for inhibiting cycle corrosion and for facilitating rapid passenger compartment warm-up during low temperature conditions
US6868788B2 (en) * 2000-03-16 2005-03-22 Gebr. Becker Gmbh & Co. Method and device for utilizing the waste heat that has accumulated during the supply of forced draught/compressed air to a printing press
US20040040459A1 (en) * 2000-03-16 2004-03-04 Hans-Heinrich Henning Method and device for utilising the waste heat that has accumulated during the supply of forced draught/compressed air to a printing press
WO2005022053A1 (en) * 2003-09-02 2005-03-10 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Compressor or air-conditioning system
WO2007068336A1 (en) * 2005-12-17 2007-06-21 Ixetic Mac Gmbh Air-conditioning compressor
DE102015016377A1 (en) * 2015-12-17 2017-06-22 Man Diesel & Turbo Se Refrigeration plant-Umblaseventil and refrigeration plant

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