US3430453A - Refrigerant condenser arrangement - Google Patents

Refrigerant condenser arrangement Download PDF

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Publication number
US3430453A
US3430453A US611300A US3430453DA US3430453A US 3430453 A US3430453 A US 3430453A US 611300 A US611300 A US 611300A US 3430453D A US3430453D A US 3430453DA US 3430453 A US3430453 A US 3430453A
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United States
Prior art keywords
refrigerant
condenser
piston
pressure
casing
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Expired - Lifetime
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US611300A
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English (en)
Inventor
John P Norton
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American Air Filter Co Inc
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American Air Filter Co Inc
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Assigned to WOODS KATHLEEN D., AS TRUSTEE, CONNECTICUT NATIONAL BANK THE, A NATIONAL BANKING ASSOCIATION AS TRUSTEE reassignment WOODS KATHLEEN D., AS TRUSTEE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ALLIS-CHALMERS CORPORATION A DE CORP.
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Expired - Lifetime legal-status Critical Current

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    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S62/00—Refrigeration
    • Y10S62/17—Condenser pressure control
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87571—Multiple inlet with single outlet

Definitions

  • the pressure of the refrigerant emitted from the condenser has been related to the temperature of the cooling medium supplied to the condenser so an uncontrolled decrease in temperature of the cooling medium supplied to the condenser results in reduced pressure in the refrigerant emitted from the condenser, and vice versa, regardless of the cooling demands on the system.
  • Previous refrigeration systems have provided various complicated, expensive arrangements to maintain optimum compressor discharge pressure.
  • One such previous arr-angement has included means to control the pressure of the refrigerant emitted from the compressor in response to change in the temperature of the cooling medium supplied to refrigerant condenser while other arrangements have directly controlled compressor discharge pressure regardless of refrigerant pressure at the expansion device.
  • heat is added to the refrigerant to selectively increase the temperature, and pressure, of the refrigerant at the compressor outlet or the temperature or flow rate of the cooling medium supplied to the refrigerant condensing means, for example ambient air, is regulated to control the temperature of the refrigerant within the condenser.
  • means have been provided to flood selected portions of the condenser with refrigerant in accordance with the pressure at the outlet of the compressor to reduce the effective heat transfer area of the condenser and correspondingly decrease the heat loss by the refrigerant to increase refrigerant pressure.
  • Such arrangements provide sluggish control and response to change in conditions is slow because the condense-r must be drained or "ice filled in accordance with changes in refrigerant pressure and the time required for draining or filling the condenser is significant.
  • Another method previously used to control the outlet pressure from the refrigeration compressor has included dividing the refrigerant flow emitted from the compressor between at least two separate condensers in accordance with the pressure at the outlet of the compressor.
  • Such arrangements require cooperative valve and control means at the compressor outlet to control the quantity of compressed refrigerant flowing to the selected condensers.
  • Such refrigerant flow control is not directly and rapidly responsive to change in condenser pressure or temperature at the condenser outlet nor do such systems provide means to cont-r01 the quality or flow rate of refrigerant supplied to the expansion device.
  • the present invention provides a straightforward, inexpensive condenser and condenser control arrangement for use in a closed fluid circuit to efliciently control the condition of vaporizablecondensible Working fluid emitted from a condenser in response to changes in the condition of the working fluid at the condenser outlet.
  • the present invention provides a straightforward refrigerant control arrangement with a minimum number of moving parts to simultaneously sense the condition of the refrigerant at the condenser outlet and control the refrigerant flow rate and effective condensing area without complicated interrelated valve and control apparatus.
  • the present invention provides a valve arrangement which not only improves the operability of the system and uniformly controls the quality of the refrigerant supplied to the expansion device but also simultaneously maintains the refrigerant pressure at the compressor outlet pressure Within selected limits.
  • the present invention provides a condenser arrangement which can be applied in fluid flow circuits of the general type where a vaporizablecondensible Working fluid is condensed and it is desirable to control the pressure within a selected portion of the circuit, the rate of condensation of working fluid and/or the condition of the working fluid at the outlet of the condenser.
  • an advantageous condenser arrangement in accordance with the present invention can be used to control the condition of Working fluid emitted from a condenser in an air heating apparatus where heated vaporizable-condensible working fluid is circulated through a fluid flow circuit and is provided to a condenser to heat a stream of air.
  • the present invention provides an improved condenser arrangement comprising: condenser means having at least two separate flow conduits to conduct working fluid through the condenser, each conduit having an inlet to communicate with means to vaporize said working fluid, and a working fluid outlet; valve means including an elongate casing havin a working fluid outlet and Working fluid inlet ports communicatively connected to outlets of selected flow conduits of said condenser; piston means to move longitudinally through the casing to close selected working fluid inlet ports; and, means to move the piston in the casing to control such selected Working fluid inlets in response to condition of working fluid admitted to the casing from the condensing means.
  • FIGURE 1 is a diagrammatic view of a refrigeration system including one example of a condenser arrangement in accordance with the present invention
  • FIGURE 2 is a diagrammatic view of a fluid heater apparatus including one example of a condenser arrangement in accordance with the present invention
  • FIGURE 3 is a view, in section, showing an example of a pressure-responsive valve which can be used in a condenser arrangement in accordance with the present invention.
  • FIGURE 4 is a view, in section, showing an example of a temperature-responsive valve arrangement which can be used in a condenser arrangement in accordance with the present invention.
  • FIGURE 1 shows a condenser 2 and valve 3, in accordance with the present invention, provided in an example of a flow circuit including a compressor 1, refrigeration expansion valve 4 and an evaporator 5 located in a space to be conditioned.
  • refrigerant is pumped from the outlet of compressor 1 to manifold 8 and the compressed refrigerant fiows through the selectively open conduits of condenser 2 so at least a part of the refrigerant is condensed and the condensed refrigerant is supplied to an expansion device 4.
  • an arrangement is provided to simultaneously regulate the refrigerant flow rate and condensing area so the pressure of the refrigerant supplied to expansion valve 4 is relatively constant and the cooling capacity of the refrigeration system is relatively unaffected by conditions prevailing in the cooling medium supplied to the condenser.
  • Condenser 2 includes an inlet manifold 8 to receive compressed refrigerant from the outlet of the compressor by means of a conduit 7.
  • condenser 2 includes at least two separate flow conduits, and in the example of FIGURE 1 four separate flow conduits 9, 11, 12, and 13 are provided. Each conduit has an inlet communicating with manifold 8 and a separate outlet connected to valve 3 as hereinafter described.
  • a conduit is provided to connect outlet 14 of valve 3 with an expansion device 4 to provide expanded cooled refrigerant to an evaporator coil 5 located in space 6 to be served by the refrigeration system.
  • Refrigerant is returned from evaporator 5 to the inlet of compressor 1 by means of a refrigerant return conduit 17.
  • FIGURE 3 is a view, in section, of one example of a valve 3 which can be used in a condenser arrangement in accordance with the present invention and includes an elongate outer casing 10 having refrigerant inlet ports 9a, 11a, 12a, and 13a, in longitudinally spaced relation in the side of the casing.
  • a piston 21 is cooperatively adapted to move in longitudinal sliding relation within casing 10 to advantageously control the opening and closing of a number of the inlet ports and divide casing 10 into chambers 27 and 28 on either side of the piston in accordance with the position of the piston in casing 10.
  • Chamber 3% can be provided to receive piSton 21 under selected conditions so none of the inlet ports are covered and closed and in response to a selected change in condition of refrigerant piston 21 can move freely out of chamber 28 to cover selected inlet ports.
  • piston 21 can advantageously be long enough to cover only inlet ports 9:1, 11a, 12a and a stop 20 can be disposed as shown, in casing 10 to restrict the movement of piston 21 so inlet 13a is never closed and a minimum refrigerant flow is assured.
  • Piston 21 can be of a straightforward construction using a cylindrical section of selected length dependent on the spacing between inlet ports 9a, 11a, 12a, 13a, and the number of such ports to be open or closed at any one time.
  • piston 21 includes machined or rolled circumferential grooves (not shown) for receiving O-rings 22 of suitable materials, for example Teflon, to restrict leakage of compressed refrigerant past piston 21.
  • Piston 21 advantageously moves freel in casing 10 as hereinbefore described to close or open selected compressed refrigerant ports in accordance with the disposi tion of the inlet ports and the position of piston 21 in casing 10.
  • Means, for example a spring 23, can be provided to maintain selected force on one end of piston 21.
  • spring 23 can be a compression spring where the force exerted by the spring varies with the extent of compression of the spring to provide a variable force on one side of piston 21 and advantageously urge piston 21 through housing 10 toward refrigerant outlet 14 of casing 10.
  • a gas bleed outlet 16 can be provided from chamber 28 for the escape of the compressed refrigerant which leaks past piston 21.
  • a pressure responsive relief valve 16a can be provided at outlet 16 to control the rate at which refrigerant escapes from chamber 28 to provide a relatively constant back pressure within chamber 28 so movement of piston 21 through casing 10 is unaffected by the rate at which refrigerant leaks past piston 21.
  • refrigerant entering chamber 27 exerts a force on the other end of piston 21 to urge the piston in a direction to compress spring 23 and open inlet ports where the force exerted by the spring increases with increased refrigerant pressure so the piston assumes balanced position in casing 10 dependent on the pressure of the refrigerant entering chamber 27.
  • Selection of a mechanical spring means 23 with known loading characteristics provides an arrangement where the piston will move to a prescribed position in casing 10 in response to selected refrigerant pressure in chamber 27 and will respond predictably to change in pressure of the refrigerant to open or close refrigerant inlets 9a, 11a, and 12a.
  • FIGURE 3 the pressure responsive valve as shown in FIGURE 3 in that it includes an elongate outer casing 1011 having longitudinally spaced inlet ports 9b, 11b and 13b where each inlet port communicates with conduits 11, 12, and 13 respectively, of condenser 2.
  • a piston 31 is adapted to move through casing 10a to close or open selected number of inlet ports and divide casing 10 into chambers 37 and 38 where chamber 38 is adapted to receive piston 31 under selected conditions so that none of the inlet ports are closed.
  • Piston 31 can be of selected length to block a selected number of inlet ports and, as in the example of the valve of FIGURE 3, piston 31 is long enough to cover ports 9b, 11b, and 12b. Also, as in the example of the valve of FIGURE 3, a stop 36 can be provided in casing 10 to prevent piston 31 from blocking all of the inlet ports to completely stop the flow of refrigeration through condenser 2.
  • Piston 31 is similar to piston 21 of FIGURE 3 and can be of straightforward construction using a cylindrical section with grooves machined or rolled for receiving 0- rings 32 of a suitable material, for example Teflon.
  • 0- rings 32 are provided to restrict flow of refrigerant past piston 31, but a small amount of leakage is likely to occur so bleed port 16 can be provided and is connected to the inlet of compressor 1 by means of conduit 18. It is desirable to provide gas bleed means such as outlet 16 and conduit 18 even if no refrigerant leaks past piston 31 because movement of piston 31 causes related expansion and contraction of chambers 37 and 38 and the gas flow resulting from change in chamber must be accommodated without affecting the movement of the piston. Since a small amount of refrigerant leakage can be ac commodated and O-ring seals can be used, the relative machine tolerance for piston 31 and valve casing 10 are not restrictive and the piston can be adapted to move freely through casing 10.
  • piston 31 can be moved in casing 14) by a temperature responsive actuator 34, for example a temperature responsive actuator manufactured under the trade name Elac by Standard-Thompson Company, where a change in the temperature of refrigerant entering the valve causes a change in linear dimension of the actuator to move the piston.
  • Actuator 34 is supported in casing 10 by mounting block 37 and piston 31 can be fastened to actuator 34 or, as shown in the example of FIGURE 3, piston 31 can merely rest on actuator 34.
  • the Elac temperature responsive actuator of the example of FIGURE 4 includes a piston 34a which is forced from housing 34b in response to an increase in temperature.
  • the housing can include a substance having a high coeflicient of thermal expansion to obtain a significant movement of piston 34a with relatively little change in temperature.
  • Some temperature responsive actuators for example the actuator where piston 34b is filled with material having high coefficient of thermal expansion, do not provide means to return the piston to the housing in response to decreased temperature, so a spring 33 can be provided to supply the return force necessary to simultaneously reposition both piston 34a in housing 34 and piston 31 in casing 10.
  • spring 33 prevents any movement of piston 31 in casing 10a in response to change in refrigerant pressure in chamber 37.
  • the flow of refrigerant through condenser 2 is controlled by temperature of the refrigerant emitted from condenser 2.
  • temperature of the refrigerant emitted from condenser 2 decreases with a decrease in temperature of cooling medium for example air, supplied to condenser 2 or with a decrease in the temperature of refrigerant emitted from compressor 1.
  • a decrease in refrigerant temperature is sensed by thermal responsive element 34 of valve 3 and the element permits withdrawal of piston 31 in casing 10a to close additional inlet ports in casing 10a.
  • FIGURE 2 is a schematic diagram of an air heating device including a condenser arrangement in accordance with the present invention.
  • the heater illustrated in FIGURE 2 includes a vaporized working fluid generator 41 having an integral heat source and a boiler to provide vaporized working fluid at selected pressure.
  • the air heating device can further include a fluid responsive engine 42 driven by pressurized working fluid emitted from generator 41 as hereinafter described.
  • condenser 40 receives heated working fluid and transfers the heat to the air passed through condenser 40 in heat exchange relation.
  • the heater as shown in the example of FIGURE 2 is self-powered so an auxiliary source of power, other than vaporized fluid generator 41, is not necessary.
  • the selfpowered air heater as shown in FIGURE 2 includes a power transmitting device 43 which receives power from engine 42 to drive several auxiliary elements including a combustion air blower 44, fan device 47, a motive fluid feed pump 53, and a fuel pump 48.
  • auxiliary elements including a combustion air blower 44, fan device 47, a motive fluid feed pump 53, and a fuel pump 48.
  • Each of the elements can be drivingly connected to power transmitting means 43, for example by drive shaft 44a, 47a, 48a, and 53a respectively.
  • Combustion air blower 44 is provided to supply combustion air to the heat source included in vapor generator 41 and fan 47 is provided to move the stream of air to be heated through condenser 40.
  • Pump 53 is provided to return condensed fluid from receiver 54 to vapor generator 41 and fuel to be burned in working fluid generator 41 can be provided by means of a pump 48 where the fuel is delivered to inlet 52 from a storage source (not shown).
  • a fuel control v lve 49 can be provided to control fuel flow to vapor generator 41 in response to selected conditions, for example, the temperature of the air emitted from condenser 40 as measured by thermal element 51 and a condenser arrangement provided by the present invention can be used to control working fluid pressure and temperature.
  • the rate of feed of fuel to working fluid generator 51 determines the rate of vaporization of fluid at selected pressure, and the quantity of heat available to heat fluid passing through condenser 40.
  • engine 42 receives vaporized motive fluid from generator 41 to transform a portion of the pressure energy of the working fluid to rotary motion to drive power transmitting means 43.
  • Reduced pressure motive fluid is exhausted from engine 42 to condenser 40.
  • a portion of the vaporized motive fluid from generator 41 can be by-passed around engine 42 through by-pass 45 to maintain a constant differential pressure across engine 42 to selectively control power output from engine 42 where by-pass 45 includes pressure responsive valve 46 to control the differential pressure across turbine 42 and the pressure at the outlet of generator 41.
  • the fluid which is by-passed around engine 42 and the fluid passed through engine 42 are recombined to flow to condenser 40 to impart heat to air passed through condenser 40 in heat exchange relation.
  • Flow of motive fluid from condenser 40 is controlled by valve 3 and the fluid is returned to receiver 54 to be recycled to generator 41.
  • condenser 40 of the heater of FIGURE 2 can include a number of separate flow conduits, for example 9c, 11c, 12c, and 130 where each separate conduit can be connected to valve 3 through separate inlet ports. If a pressure responsive valve as illustrated in FIGURE 3 is used, an increase in pressure of the fluid in chamber 27 of casing indicates increased fluid pressure in condenser 40 which can, for example, be the result of reduced rate of condensation of working fluid.
  • the reduced rate of condensation of working fluid can result from several factors including an increase in the temperature of the air supplied to the condenser to be heated without a corresponding change in the rate of feed of fuel to generator 41 as hereinbefore described.
  • valve 3 advantageously provides an arrangement to maintain working fluid pressure in such air heating devices to promote stable operations while fuel feed rate corrections are made.
  • piston 21 of valve 3 moves to open additional conduits through condenser 40 to increase effective heat transfer area and the rate of condensation of fluid in condenser 40.
  • decreased fluid pressure resulting from increased rate of condensation which can result from decreased temperature of the air passing over condenser 40, causes valve 3 to close to decrease heat transfer area and increase working fluid pressure.
  • valve 3 can be either pressure or temperature responsive and can advantageously be adjusted to maintain selected refrigerant conditions, for example, complete condensation of motive fluid in condenser 40, or a constant downstream pressure at the outlet of condenser 40.
  • an improved working fluid condenser arrangement comprising: a source of vaporized working fluid; condenser means having at least two separate flow conduits to conduct working fluid through the condenser, each conduit having an inlet to communicate with the source of working fluid and a working fluid outlet; valve means including an elongate casing having working fluid means and Working fluid inlet ports spaced longitudinally along a portion of the length of said casing with each port communicatively connected to the outlet of a selected flow conduit of said condenser; piston means cooperatively disposed within said casing to move longitudinally through said casing to close selected working fluid inlet ports to define first chamber means on one side of said piston means and second chamber means on the other side of said piston means where said inlet ports and said outlet means are in communicative relation with said second chamber means; and, working fluid temperature responsive means disposed in said second chamber to move said
  • said casing includes working fluid escape means communicatively connected with said first chamber to prevent entrapment of working fluid in said first chamber to restrict movement of said piston means.
  • the present invention provides an improved condensing arrangement comprising: condenser means having at least two separate flow conduits to conduct refrigerant to said condenser, each conduit having an inlet to communicate with the high pressure outlet side of said compressor and a working fluid outlet; valve means including an elongate casing having a working fluid outlet adjacent one end of said valve means and working fluid inlet ports spaced longitudinally along said casing; each such inlet communic

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Sorption Type Refrigeration Machines (AREA)
US611300A 1967-01-24 1967-01-24 Refrigerant condenser arrangement Expired - Lifetime US3430453A (en)

Applications Claiming Priority (1)

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US61130067A 1967-01-24 1967-01-24

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US611300A Expired - Lifetime US3430453A (en) 1967-01-24 1967-01-24 Refrigerant condenser arrangement

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US (1) US3430453A (de)
JP (1) JPS5025178B1 (de)
DE (1) DE1601051A1 (de)
FR (1) FR1562071A (de)
GB (1) GB1218063A (de)
SE (1) SE343381B (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5256655U (de) * 1975-10-22 1977-04-23
EP0142209A2 (de) * 1983-11-11 1985-05-22 Grasso's Koninklijke Machinefabrieken N.V. Anlage, wie Kühlanlage oder Wärmepumpe
US4679411A (en) * 1978-08-16 1987-07-14 American Standard Inc. Stepped capacity constant volume building air conditioning system
EP0351204A2 (de) * 1988-07-12 1990-01-17 Sanden Corporation Kraftfahrzeugklimaanlage mit Regelvorrichtung
US5444993A (en) * 1993-05-24 1995-08-29 Nippondenso Co., Ltd. Condenser for refrigerating cycle
US6751965B1 (en) 2002-12-30 2004-06-22 Steven D. Gottlieb Refrigeration machine having sequentially charged condensing conduits
US20090031735A1 (en) * 2007-08-01 2009-02-05 Liebert Corporation System and method of controlling fluid flow through a fluid cooled heat exchanger
US10126027B2 (en) 2013-06-17 2018-11-13 Bayerische Motoren Werke Aktiengesellschaft Method and control device for optimizing cooling of a high voltage accumulator by means of an air-conditioning system

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3323318A (en) * 1965-03-24 1967-06-06 Fisher C Joe Low ambient head pressure stabilizer system

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3323318A (en) * 1965-03-24 1967-06-06 Fisher C Joe Low ambient head pressure stabilizer system

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5256655U (de) * 1975-10-22 1977-04-23
US4679411A (en) * 1978-08-16 1987-07-14 American Standard Inc. Stepped capacity constant volume building air conditioning system
EP0142209A2 (de) * 1983-11-11 1985-05-22 Grasso's Koninklijke Machinefabrieken N.V. Anlage, wie Kühlanlage oder Wärmepumpe
EP0142209A3 (en) * 1983-11-11 1985-12-04 Grasso's Koninklijke Machinefabrieken N.V. Plant, such as cooling plant or heat pump
EP0351204A2 (de) * 1988-07-12 1990-01-17 Sanden Corporation Kraftfahrzeugklimaanlage mit Regelvorrichtung
EP0351204A3 (en) * 1988-07-12 1990-04-25 Sanden Corporation Control device for use in an automotive air conditioning system
US5044169A (en) * 1988-07-12 1991-09-03 Sanden Corporation Control device for use in an automative air conditioning system
US5444993A (en) * 1993-05-24 1995-08-29 Nippondenso Co., Ltd. Condenser for refrigerating cycle
US6751965B1 (en) 2002-12-30 2004-06-22 Steven D. Gottlieb Refrigeration machine having sequentially charged condensing conduits
US20090031735A1 (en) * 2007-08-01 2009-02-05 Liebert Corporation System and method of controlling fluid flow through a fluid cooled heat exchanger
US10126027B2 (en) 2013-06-17 2018-11-13 Bayerische Motoren Werke Aktiengesellschaft Method and control device for optimizing cooling of a high voltage accumulator by means of an air-conditioning system

Also Published As

Publication number Publication date
JPS5025178B1 (de) 1975-08-21
SE343381B (de) 1972-03-06
DE1601051A1 (de) 1970-05-21
GB1218063A (en) 1971-01-06
FR1562071A (de) 1969-04-04

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AS Assignment

Owner name: CONNECTICUT NATIONAL BANK THE, A NATIONAL BANKING

Free format text: SECURITY INTEREST;ASSIGNOR:ALLIS-CHALMERS CORPORATION A DE CORP.;REEL/FRAME:004149/0001

Effective date: 19830329

Owner name: WOODS KATHLEEN D., AS TRUSTEE

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Effective date: 19830329