GB2229295A - Air conditioning system - Google Patents

Air conditioning system Download PDF

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Publication number
GB2229295A
GB2229295A GB9000358A GB9000358A GB2229295A GB 2229295 A GB2229295 A GB 2229295A GB 9000358 A GB9000358 A GB 9000358A GB 9000358 A GB9000358 A GB 9000358A GB 2229295 A GB2229295 A GB 2229295A
Authority
GB
United Kingdom
Prior art keywords
compressor
refrigerant
evaporator
air conditioning
conditioning system
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Withdrawn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
GB9000358A
Other versions
GB9000358D0 (en
Inventor
Peter Keith Jackson
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.)
JACKSON JULIE
Original Assignee
JACKSON JULIE
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 JACKSON JULIE filed Critical JACKSON JULIE
Publication of GB9000358D0 publication Critical patent/GB9000358D0/en
Publication of GB2229295A publication Critical patent/GB2229295A/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/1405—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B49/025—Motor 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Peptides Or Proteins (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

An air conditioning system comprises a variable displacement compressor 14 driven by an electric motor 13. A refrigerant hot gas pipe 16 extends to a condenser 3, having a condenser pressure control system, from which refrigerant liquid pipe 17 extends to a liquid distributor having a plurality of refrigerant liquid output pipes each with liquid flow control valves 5 leading to a multiple circuit evaporator 7 having a temperature sensor 8 and a humidity sensor 9 in the air stream entering the evaporator 7. A refrigerant suction pipe 21 from the evaporator has a suction pressure sensor 10. Refrigerant is then led back to the compressor 14. Control system 11 receives data from the temperature sensor 8, humidity sensor 9 and suction pressure sensor 10, and outputs data to the refrigerant flow control valves 5 and to a variable frequency inverter 12 to control the rotational speed of the electric motor 13 and hence the displacement of the compressor 14. <IMAGE>

Description

AIR CONDrTIONING SYSTEM AND OPERATING METHOD This invention relates to an air conditioning system and to a method of operating an air conditioning system.
In selecting an air conditioning system for a given volume of air the conventionally provided evaporator coil of the system is sized to give a cooling duty greater than, or equal to, the heat load imposed on the conditioned volume.
Sections of this coil may be switched on and off, for control of temperature. When control of humidity is required, the cooling coil must be capable of removing water vapour from the air in the form of condensation on the conventionally provided fins of the cooling coil, when it is necessary for it to do so, and a humidifier must be included in the system to add water vapour to the air, when required.
It is usual practice for the cooling coil to dehumidify the air as a by-product of the cooling function when the room is at its design conditions (e.g. 2oc 5% RH), and the humidifier is used to offset the moisture removal of the cooling coil.
It should be noted that the sensible heat ratio of any standard evaporator coil is a function of the coil depth in the direcion of airflow (number of rows of refrigerant tubes), the fin spacing, the volume of air flowing through the coil, the evaporating temperature of the refrigerant within the the coil, and the temperature and relative humidity of the air passing through the coil.
The evaporating temperature in turn depends on the displacement duty of the compressor, which until very recently, was fixed at a discrete value, and was not adjustable.
Dehumidification is presently achieved by one of the following methods: 1. Switch on a special section of the cooling coil with a lower sensible heat ratio. This means that a section of cooling coil must be provided that will be redundant for long periods of time, taked up space in the air conditioning unit, and is costly to produce.
2. Switch on additional cooling stages, and switch on heating stages to balance the sensible cooling, so that the nett result is latent cooling only. This is very wasteful of energy, since heating and cooling are in conflict to achieve dehumidification.
3. Reduce the airflow through the evaporator coil so that the sensible heat ratio of the coil is reduced and dehumidification increases. This can upset the air distribution within the conditioned space, leading to irregulatiries in temperature across the space.
From points 1 - 3 above it is clear that humidity control requires a penalty, either in manufacturing, energy input, or uniformity of control. The air conditioning system and its operating method overcomes all of these problems in a manner which has the benefits of reduced running costs.
The effect will be: 1. The airflow rate will be constant.
2. Dehumidification (and hence the need for rehumidif ication) will not occur unless specifically called for by the control system.
3. No special sections of evaporator coil are necessary.
4. Independent stepless control of both total coding duty and sensible heat ratio is achieved.
5. Very close control of both temperature and RH is possible.
6. Running costs will be some 75% of equivalent traditional systems.
According to a first aspect of the invention, there is provided an air conditioning system comprising a variable displacement compressor drivable by an electric motor, a refrigerant hot gas pipe extending to a condenser, having a condenser pressure control system, then via a refrigerant liquid pipe to a liquid distributor havinga plurality of refrigerant liquid output pipes each with liquid flow control valves leading to a multiple circuit evaporator having a temperature sensor and a humidity sensor in the air stream entering the evaporator, with a refrigerant suction pipe from the evaporator having a suction pressure sensor, and then led back to the compressor, and a control system to receive input data from the temperature sensor, the humidity sensor and the suction pressure sensor, and to emit output data to the refrigerant flow control valves and to a variable frequency inverter to control the rotational speed of the electric motor and hence the displacement of the compressor.
The use of a rotary compressor e.g. of the multivane type, with a variable speed drive enables the displacement of the compressor to be varied from approximately 2% to 150% of its rated duty, in stepless control.
The refrigerant flow control valves may be constituted by solenoid valves, with downstream expansion devices, or alternatively may be constituted by electrically operable, thermostatic expansion valves capable of shutting off completely the flow of refrigerant.
If the compressor is of a type requiring oil separation, then preferably an oil separator is interposed in the refrigerant circuit between the compressor and the conderisor, with a primary oil circuit to the compressor, from the oil separator, and a secondary oil circuit from the oil separator to the refrigerant suction pipe ahead of the return into the compressor.
According to a second aspect of.the invention, there is provided an operating method for an air conditioning system wherein evaporating temperature is used as a stepless control variable.
According to a third aspect of the invention, there is provided a method of operating an air conditioning system having an evaporator coil, comprising variably controlling, in a stepless manner, the sensible heat ratio of the evaporator coil as a function of the relative humidity of air entering the coil, independently of the total cooling duty of the coil.
According to another aspect of the invention there is provided an air conditioning system having control over the rotational speed of the compressor such that prescribed limits of compressor discharge temperature, compressor suction pressure, compressor discharge pressure and compressor motor running current, are never exceeded.
This aspect advantageously obviates the need for conventional over-load switches e.g. for high pressure, low pressure or high temperature with the system being controlled e.g., by reducing the compressor duty, as any prescribed threshold limit is closely approached.
In detail, suitable sensors or transducers appropriate for the parameter to be monitored, are placed at suitable locations within the system, with outputs to a control system e.g. incorporating a microprocessor, with the control system storing threshold values and comparing stored threshold values with actual values received from the transducers, and simply controlling the motor speed e.g. via a variable frequency inverter powering an electric motor driving a compressor, to ensure that no stored threshold value is exceeded. Clearly, it is desirable for the stored threshold values to be changeable e.g. by keying alternative values into a memory of the control system, to suit a change in operation or components of an established air conditioning system, or to give flexibility for installation of identical components in different air conditioning systems.
Method of Operation of a Preferred Svstem The refrigeration components generally operate as in a standard air conditioning system.
The compressor speed controls the evaporating pressure of the system, and is directly related to the output frequency of the inverter.
The control system senses the condition of the air entering the evaporator, both as to temperature and relative humidity. It also senses the pressure within the conventionally provided suction header of the evaporator.
The control system is adjusted such that the evaporating pressure is varied as a function of the relative humidity of the entering air: as RH rises, the evaporating pressure set point is reduced. A control output is produced proportional to the difference between the suction pressure set point selected by the control system and the suction pressure sensed at the suction header on the evaporator, and is fed directly to the inverter.
This control signal varies the output frequency of the inverter, thus correcting any error in the evaporating pressure, and hence controls the sensible heat ratio of all the evaporator coil sections in operation.
The control system also produces outputs to open and close the solenoid valves, thus switching sections of evaporator coil on and off, and controlling the total cooling duty of the evaporator.
In this manner both the total cooling duty and the sensible heat ratio of the evaporator coil may be controlled accurately so that the minimum cooling duty at the correct sensible heat ratio may be applied to any imposed cooling load, thus minimising the electrical input to the air conditioning system as a whole under all opeating conditions.
One example of the various aspects of the invention is shown in the accompanying drawings, which the following reference numerals have been applied to the following components: 1. Variable duty compressor package 2. Oil separator 3. Condenser 4. Condenser pressure controller 5. Solenoid valves 6. Expansion device 7. Multiple circuit evaporator 8. Temperature sensor 9. Humidity sensor 1PI. Suction pressure sensor 11. Control system 12. Variable frequency inverter 13. Electric motor 14. Compressor 15. Shut-off valve 16. Refrigerant hot gas pipe 17. Refrigerant liquid pipe 18. Lead control 19. Lead control 2. Suction header pipes 21. Refrigerant suction pipe 22. Control lead 23. Control lead 24. Control lead 25. Power lead 26.Power lead In the drawing, the air conditioning system can be seen to comprise a variable displacement compressor package 1, comprising an electric motor 13, a multivane compressor 14.
A shut-off valve 15 allows flow of a refrigerant hot gas along pipe 16 to an oil separator 2, from which oil separator 2, beyond which the pipe 16 leads to a condenser 3 from which a refrigerant liquid pipe 17 having a compressor pressure controller 4, extends to a multiple circuit evaporator 7, the supply splitting into four solenoid valves 5 and four downstream expansion devices 6. Associated with the evaporator 7 are a temperature sensor 8 connected by lead 18 to a control system 11, and a humidity sensor connected by lead 19 to the control system 11. Four suction header pipes 2 lead to a common refrigerant suction pipe 21 to the compressor 14, with a suction pressure sensor 1 associated with the suction pipe 21 and connected by a control lead 22 to the control system 11. The latter can also be seen to have control leads 23 to the four solenoid valves 5 and a control lead 24 to a variable frequency inverter 12 connectable to mains power via a power lead 25 and connected to the electric motor 13 via a power lead 26. Hence the control system 11 receives input data from the temperature sensor 8, the humidity sensor 9, and the suction pressure sensor 18 on the basis of which data, output control signals are fed via the control leads 23 to the solenoid valves 5, and via control lead 24 to the inverter 12, the latter controlling the speed of the motor 13 and hence the displacement of the compressor 14.

Claims (9)

1. An air conditioning system comprising a variable displacement compressor drivable by an electric motor, a refrigerant hot gas pipe extending to a condenser, having a condenser pressure control system, then via a refrigerant liquid pipe to a liquid distributor having a plurality of refrigerant liquid output pipes each with liquid flow control valves leading to a multiple circuit evaporator having a temperature sensor and a humidity sensor in the air stream entering the evaporator, with a refrigerant suction pipe from the evaporator having a suction pressure sensor, and then led back to the compressor, and a control system to receive input data from the temperature sensor, the humidity sensor and the suction pressure sensor, and to emit output data to the refrigerant flow control valves and to a variable frequency inverter to control the rotational speed of the electric motor and hence the displacement of the compressor.
2. A system as claimed in Claim l, wherein the compressor is of the multivane type.
3. A system as claimed in Claim 1 or Claim 2, wherein the refrigerant flow control valves are solenoid valves, with downstream expansion devices.
4. A system as claimed in Claim 1 or Claim 2, wherein the refrigerant flow control valves are electrically operable, thermostatic expansion valves capable of shutting off completely the flow of refrigerant.
5. A system as claimed in any preceding Claim, comprising an oil separator interposed in the refrigerant circuit between the compressor and the condensor, with a primary oil circuit to the compressor, from the oil separator, and a secondary oil circuit from the oil separator to the refrigerant suction pipe ahead of the return into the compressor.
6. An operating method for an air conditioning system, wherein evaporating temperature is used as a stepless control variable.
7. A method of operating an air conditioning system having an evaporator coil, comprising variably controlling, in a stepless manner, the sensible heat ratio of the evaporator coil as a function of the relative humidity of air entering the coil, independently of the total cooling duty of the coil.
8. An air conditioning system substantially hereinbefore described with reference to the accompanying drawing.
9. An air conditioning system having control over the rotational speed of the compressor such that prescribed limits of compressor discharge temperature, compressor suction pressure, compressor discharge pressure and compressor motor running current, are never exceeded.
GB9000358A 1989-01-06 1990-01-08 Air conditioning system Withdrawn GB2229295A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB898900251A GB8900251D0 (en) 1989-01-06 1989-01-06 Air conditioning system and operating method

Publications (2)

Publication Number Publication Date
GB9000358D0 GB9000358D0 (en) 1990-03-07
GB2229295A true GB2229295A (en) 1990-09-19

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GB898900251A Pending GB8900251D0 (en) 1989-01-06 1989-01-06 Air conditioning system and operating method
GB9000358A Withdrawn GB2229295A (en) 1989-01-06 1990-01-08 Air conditioning system

Family Applications Before (1)

Application Number Title Priority Date Filing Date
GB898900251A Pending GB8900251D0 (en) 1989-01-06 1989-01-06 Air conditioning system and operating method

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CA (1) CA2024103A1 (en)
GB (2) GB8900251D0 (en)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0490089A2 (en) * 1990-12-11 1992-06-17 Zanussi Elettromeccanica S.p.A. Improvement in refrigeration compressors with electronic control arrangement
WO1997050022A1 (en) * 1996-06-27 1997-12-31 York International Corporation Variable speed control of a centrifugal chiller using fuzzy logic
EP1035644A1 (en) * 1999-03-09 2000-09-13 Samsung Electronics Co., Ltd. Variable frequency inverter for electromotor
WO2004097308A1 (en) * 2003-04-30 2004-11-11 Lg Electronics, Inc. Apparatus for controlling operation of outdoor unit and its method
EP1400765A3 (en) * 2002-09-17 2005-09-28 Kabushiki Kaisha Kobe Seiko Sho Screw refrigerating apparatus
WO2006011789A1 (en) * 2004-07-26 2006-02-02 Antonie Bonte Improvements in transcritical cooling systems
CN1329695C (en) * 2003-05-15 2007-08-01 乐金电子(天津)电器有限公司 Apparatus and method for safety operation of outdoor unit
WO2009077355A1 (en) * 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Control unit for a refrigerating machine and domestic refrigerator using this control unit
CN103471215A (en) * 2013-09-24 2013-12-25 江苏春兰空调设备有限公司 Variable-frequency multi-connected air conditioning unit self-adaptive control device and variable-frequency multiple machine unit self-adaptive control method
US8974573B2 (en) 2004-08-11 2015-03-10 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US9140728B2 (en) 2007-11-02 2015-09-22 Emerson Climate Technologies, Inc. Compressor sensor module
US9285802B2 (en) 2011-02-28 2016-03-15 Emerson Electric Co. Residential solutions HVAC monitoring and diagnosis
US9310094B2 (en) 2007-07-30 2016-04-12 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
US9551504B2 (en) 2013-03-15 2017-01-24 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9638436B2 (en) 2013-03-15 2017-05-02 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9762168B2 (en) 2012-09-25 2017-09-12 Emerson Climate Technologies, Inc. Compressor having a control and diagnostic module
US9765979B2 (en) 2013-04-05 2017-09-19 Emerson Climate Technologies, Inc. Heat-pump system with refrigerant charge diagnostics
US9803902B2 (en) 2013-03-15 2017-10-31 Emerson Climate Technologies, Inc. System for refrigerant charge verification using two condenser coil temperatures
US9823632B2 (en) 2006-09-07 2017-11-21 Emerson Climate Technologies, Inc. Compressor data module
US9885507B2 (en) 2006-07-19 2018-02-06 Emerson Climate Technologies, Inc. Protection and diagnostic module for a refrigeration system
US9903624B2 (en) 2012-06-14 2018-02-27 Alfa Laval Corporate Ab System and method for dynamic control of an evaporator

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EP0104872A2 (en) * 1982-09-22 1984-04-04 Dunham-Bush Inc. Air conditioning and compressor control system
WO1989012269A1 (en) * 1988-06-10 1989-12-14 Honeywell Inc. A method for the optimal comfort and efficiency control of variable speed heat pumps and air conditioners

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EP0104872A2 (en) * 1982-09-22 1984-04-04 Dunham-Bush Inc. Air conditioning and compressor control system
WO1989012269A1 (en) * 1988-06-10 1989-12-14 Honeywell Inc. A method for the optimal comfort and efficiency control of variable speed heat pumps and air conditioners

Cited By (47)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0490089A3 (en) * 1990-12-11 1994-03-23 Zanussi Elettromecc
EP0490089A2 (en) * 1990-12-11 1992-06-17 Zanussi Elettromeccanica S.p.A. Improvement in refrigeration compressors with electronic control arrangement
WO1997050022A1 (en) * 1996-06-27 1997-12-31 York International Corporation Variable speed control of a centrifugal chiller using fuzzy logic
EP1035644A1 (en) * 1999-03-09 2000-09-13 Samsung Electronics Co., Ltd. Variable frequency inverter for electromotor
CN100380052C (en) * 1999-03-09 2008-04-09 三星电子株式会社 Wall-installed microwave oven and method for controlling motor of exhausting hood thereof
EP1400765A3 (en) * 2002-09-17 2005-09-28 Kabushiki Kaisha Kobe Seiko Sho Screw refrigerating apparatus
US6948326B2 (en) 2003-04-30 2005-09-27 Lg Electronics Inc. Apparatus for controlling operation of outdoor unit and its method
CN1311205C (en) * 2003-04-30 2007-04-18 Lg电子株式会社 Apparatus and method for controlling operation of outdoor unit
WO2004097308A1 (en) * 2003-04-30 2004-11-11 Lg Electronics, Inc. Apparatus for controlling operation of outdoor unit and its method
CN1329695C (en) * 2003-05-15 2007-08-01 乐金电子(天津)电器有限公司 Apparatus and method for safety operation of outdoor unit
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US9669498B2 (en) 2004-04-27 2017-06-06 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US10335906B2 (en) 2004-04-27 2019-07-02 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
WO2006011789A1 (en) * 2004-07-26 2006-02-02 Antonie Bonte Improvements in transcritical cooling systems
US8974573B2 (en) 2004-08-11 2015-03-10 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US9023136B2 (en) 2004-08-11 2015-05-05 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US9086704B2 (en) 2004-08-11 2015-07-21 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US9017461B2 (en) 2004-08-11 2015-04-28 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US10558229B2 (en) 2004-08-11 2020-02-11 Emerson Climate Technologies Inc. Method and apparatus for monitoring refrigeration-cycle systems
US9690307B2 (en) 2004-08-11 2017-06-27 Emerson Climate Technologies, Inc. Method and apparatus for monitoring refrigeration-cycle systems
US9304521B2 (en) 2004-08-11 2016-04-05 Emerson Climate Technologies, Inc. Air filter monitoring system
US9885507B2 (en) 2006-07-19 2018-02-06 Emerson Climate Technologies, Inc. Protection and diagnostic module for a refrigeration system
US9823632B2 (en) 2006-09-07 2017-11-21 Emerson Climate Technologies, Inc. Compressor data module
US9310094B2 (en) 2007-07-30 2016-04-12 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
US10352602B2 (en) 2007-07-30 2019-07-16 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
US10458404B2 (en) 2007-11-02 2019-10-29 Emerson Climate Technologies, Inc. Compressor sensor module
US9194894B2 (en) 2007-11-02 2015-11-24 Emerson Climate Technologies, Inc. Compressor sensor module
US9140728B2 (en) 2007-11-02 2015-09-22 Emerson Climate Technologies, Inc. Compressor sensor module
WO2009077355A1 (en) * 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Control unit for a refrigerating machine and domestic refrigerator using this control unit
US9703287B2 (en) 2011-02-28 2017-07-11 Emerson Electric Co. Remote HVAC monitoring and diagnosis
US10884403B2 (en) 2011-02-28 2021-01-05 Emerson Electric Co. Remote HVAC monitoring and diagnosis
US9285802B2 (en) 2011-02-28 2016-03-15 Emerson Electric Co. Residential solutions HVAC monitoring and diagnosis
US10234854B2 (en) 2011-02-28 2019-03-19 Emerson Electric Co. Remote HVAC monitoring and diagnosis
EP2674697B1 (en) * 2012-06-14 2018-09-12 Alfa Laval Corporate AB A plate heat exchanger
US9903624B2 (en) 2012-06-14 2018-02-27 Alfa Laval Corporate Ab System and method for dynamic control of an evaporator
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CA2024103A1 (en) 1990-07-12
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