WO1986000393A1 - Installation de refrigeration - Google Patents

Installation de refrigeration Download PDF

Info

Publication number
WO1986000393A1
WO1986000393A1 PCT/AU1985/000134 AU8500134W WO8600393A1 WO 1986000393 A1 WO1986000393 A1 WO 1986000393A1 AU 8500134 W AU8500134 W AU 8500134W WO 8600393 A1 WO8600393 A1 WO 8600393A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
condenser
inlet
damper
heat exchange
Prior art date
Application number
PCT/AU1985/000134
Other languages
English (en)
Inventor
Klaas Visser
Original Assignee
Klaas Visser
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 Klaas Visser filed Critical Klaas Visser
Publication of WO1986000393A1 publication Critical patent/WO1986000393A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
    • F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/041—Details of condensers of evaporative condensers

Definitions

  • This invention relates to improvements in refrigera ⁇ tion plant and relates particularly to refrigeration plant having an evaporative condenser cooled by an induced or force draught air movement.
  • condensing of the compressed refrigerant gas is effected in an evaporative condenser.
  • the hot, compressed refrigerant gas passes to the evaporative condenser whereby heat and mass transfer occurs and the latent heat of condensation in the refrigerant is removed by heat transfer through the walls of the evaporative condenser.
  • water is caused to pass over the evaporative condenser and air is introduced below the condenser, using either a forced or induced draught arrangement. Some of the water passing over the condenser is evaporated by the latent heat of condensation of the refrigerant and the induced or forced air draught enhances the heat transfer and removes the evaporated water.
  • the heat removed from the refrigerant gas results in an increase in the enthalpy of the air passing over the evaporative condenser.
  • M total weight air supplied to the condenser by the forced or induced draught fans, per hour.
  • h2 enthalpy of air leaving the condenser
  • hi enthalpy of air entering the condenser.
  • the enthalpy of air entering the condenser is largely determined by the wet bulb temperature of the air , which is a measure of its relative humidity. Because heat will only flow from a higher energy level to a lower energy level, it follows, that the higher is the wet bulb temperature of the entry air, the higher the refrigerant condensing temperature has to. be to effect heat exchange. It also follows that the higher is the wet bulb temperature of the entry air, the less heat exchange occurs for a given refrigerant condensing temperature.
  • the total heat is the sum total of the latent heat of evaporation of the refrigerant plus most of the compression energy less the difference in enthalpy between the refrigerant condensing temperature and the evaporating temperature of the water, if no liquid refrigerant subcooling takes place.
  • a system operating under the above conditions normally works well provided that the ambient air temperature is not greatly less than the freezing point of water. However, as the ambient temperature in colder climates frequently falls below -10°C, the ambient air has such a low wet bulb temperature as to freeze some of the water cascading through the evaporative condenser.
  • the refrigerant condensing pressure will tend to be much higher with dry air cooling than with evaporative cooling and, therefore, the compressors in the refrigerant system use substantially more energy than they need to use. It is not uncommon for refirgeration plants in cold climates to use more refrigeration compressor energy in winter than in summer for this reason. For example, in a system used for cooling hot beef, the temperature of the cool room is gnerally not lower than -1°C (+30°F) and frequently the outside temperature in winter in cold climates is -20°C (-4°F) .
  • the condensing temperature is frequently +32°C (+90°F) whilst in spring, summer and autumn, the condensing temperature would be the same with ambient air temperatures as high as +30°C to 35°C (86 to 95°F) .
  • a refrigeration system comprising an evaporative condenser, means for passing water over the condenser, means for passing air over the condenser, air ducting means to enable discharge air to be returned to an air inlet, and control means to control the flow of returned air.
  • the control means includes one or more dampers in the air ducting means, the dampers being operated in conjunction with sensed wet bulb temperature of the air entering the system so as to be able to control the amount of returned air to obtain the desired wet bulb temperature.
  • two sets of dampers are provided, one at the end of the air ducting means adjacent the air discharge from the evaporative condenser and the second in the ambient air inlet.
  • the two sets of dampers may be interconnected so that, as one set opens to allow air to pass into the air ducting means, the other closes thus restricting the entry of ambient air to the system.
  • DESCRIPTION OF THE DRAWING Figure 1 schematically illustrates a heat exchange system foran evaporative condenser of a refrigeration system.
  • the condenser 12 illustrated schematically, generally comprises one or more series or coils of metal tubes through which relatively hot, gaseous refrigerant passes.
  • the gaseous refrigerant enters at 14 and, after condensing, liquid refrigerant flows out at 16 to the evaporator of the refrigeration system (not shown) .
  • Water is caused to cascade ovet the condenser 12 to assist the heat removal from the refrigerant.
  • the water is sprayed onto the top of the condenser 12 through water sprays 17 which are supplied from the pump 18 which draws water from the sump 19.
  • the water may be supplied from a tank (not shown) which enters the water circuit at 21. With this arrangement, the sump 19 drains to the tank through the outlet 22. Make-up water to replace that which is lost through evaporation is supplied through the ball valve 20.
  • Air is caused to flow over the condenser coil 12, preferably in countercurrent to the water flow.
  • the air is forced by a fan 23 which draws in ambient air through the ambient air inlet 28 and forces the air over the condenser 12 to an outlet 24 where the air is discharged to atmosphere at 25.
  • a droplet eliminator 26 is located above the water sprays 17 to remove, or substantially remove, water droplets carried in the air stream.
  • the heat exchange unit is fitted with an air duct 27 extending between the air outlet 24 and the air inlet 28.
  • the upper or inlet end of the air duct 27 i.e. that end adjacent the air outlet 24, is provided with a damper mechanism 29 which enables- the inlet to the air duct 27 to be opened any desired amount, or closed, as required.
  • damper mechanism 31 is provided to control the amount of ambient air entering the air inlet
  • Both damper mechanisms 29 and 31 comprise a plurality of shutters 30 pivotal about their longitudinal axes between substantially horizontal positions, at which the damper mechanisms are fully open, and substantially vertical positions at which longitudinal edges of adjacent shutters
  • damper mechanisms 29 and 31 are controlled by a modulating motor 4 activated by an electrical, electronic or solid state control device 9.
  • the control device 9 receives an input signal from a sensor 32 positioned in the air stream in front of the fan 23, the sensor being able to sense either air wet bulb temperature, total air enthalpy, or both.
  • the modulating motor 4 is connected to the damper mechanisms 29 and 31 by links 5, 6, 8 and 7 so that both dampers 29 and 31 operate together to direct more or less air, as required, from the air discharge 24 to the fan 23.
  • the modulating motor 4 is actuated so as to simultaneously close the damper mechanism 31 a small amount and open the damper mechanism 29 a similar amount whereby some of the air drawn in by the fan 23 is drawn from the air outlet 24.
  • the lowest, desirable value of fan entry air wet bult temperature or enthalpy is set at such a value as to consistently eliminate freezing of water on the fan 23, casing, condenser 12 and condenser sump 19.
  • the sensor 32 and control device 9 are pre-set to maintain a minimum air wet bulb temperature or total air enthalpy, below which the damper mechanisms 29 and 31 are actuated to recirculate air from the air outlet 24 to the fan 23.
  • the embodiment illustrated is a forced draught heat exchange unit
  • the invention is readily adapted for use with an induced draught heat exchange unit.
  • the invention may be incorporated on existing evaporative condenser systems by the provision of external air ducting and appropriate damper mechanisms.
  • the invention may be incorporated into the design of heat exchange units to more easily facilitate the return of discharge air to the fan intake.
  • the control system of the present invention will maintain the desired wet bulb temperature within relatively narrow limits which may be set for maximum efficiency of the heat exchange unit.
  • the use of the present invention avoids the need to disconnect the water supply to the water sprays 17 to prevent freezing of the water in the water circulation system.
  • the heat exchange unit is able . to operate at maximum efficiency irrespective of ambient air temperature.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

Une unité d'échange thermique par évaporation comporte un condensateur de réfrigération (12), de l'eau passant sur le condensateur afin d'en retirer la chaleur. L'air est déplacé par un ventilateur (23) à contre courant de l'écoulement d'eau, l'air étant aspiré à partir d'une admission (28) et évacué par une sortie d'évacuation (24). La sortie d'évacuation (24) communique avec l'admission (28) par un conduit d'air (27). Un registre d'air (29) est placé dans le conduit à proximité de la sortie (24) et un second registre d'air (31) dans l'admission d'air (28). La température mouillée de l'air passant par le ventilateur (23) est captée par le capteur (32). On utilise la lecture du capteur pour réguler les positions relatives des registres d'air (29, 31) afin de forcer une quantité supérieure ou inférieure d'air d'évacuation à passer de la sortie d'évacuation (24) à l'admission d'air (28) en vue de conserver une température mouillée désirée.
PCT/AU1985/000134 1984-06-21 1985-06-21 Installation de refrigeration WO1986000393A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU562484 1984-06-21
AUPG5624 1984-06-21

Publications (1)

Publication Number Publication Date
WO1986000393A1 true WO1986000393A1 (fr) 1986-01-16

Family

ID=3696095

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU1985/000134 WO1986000393A1 (fr) 1984-06-21 1985-06-21 Installation de refrigeration

Country Status (2)

Country Link
EP (1) EP0183808A1 (fr)
WO (1) WO1986000393A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2318180A (en) * 1996-10-08 1998-04-15 Aro Electrical Engineering Co Air-conditioning apparatus
GB2365955A (en) * 1998-09-09 2002-02-27 Liu Fu Chin Evaporative condensing apparatus
WO2004088220A1 (fr) * 2003-03-27 2004-10-14 The Coca-Cola Company Systeme et procede de refrigeration pour distributeur de boisson
US7591140B2 (en) 2003-03-27 2009-09-22 The Coca-Cola Company Beverage dispensing apparatus and method for beverage dispensing
CN101334246B (zh) * 2008-08-07 2010-06-09 北京市京海换热设备制造有限责任公司 一种空气冷却器
WO2015172180A1 (fr) * 2014-05-13 2015-11-19 Klaas Visser Condenseur évaporatif amélioré
CN109990625A (zh) * 2019-04-28 2019-07-09 洛阳鼎瑞节能科技有限公司 一种智控紧凑型干湿联合蒸发式空冷器
GB2622183A (en) * 2022-05-04 2024-03-13 Coopertec Systems Ltd Evaporative condenser operating as either water heater or condenser

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU247330A1 (ru) * Высшее военное инженерно техническое Краснознаменной училиЩй НСГ Испарительный конденсатор
US1861158A (en) * 1930-01-06 1932-05-31 Hilger George Air conditioning system
US3443633A (en) * 1967-03-30 1969-05-13 Gen Electric Temperature compensated air-cooled steam condenser
FR1600281A (fr) * 1968-01-04 1970-07-20
GB1382685A (en) * 1971-04-28 1975-02-05 Jacir J Apparatus for cooling or condensing fluid
GB2052721A (en) * 1979-06-22 1981-01-28 Watson E Hijos Sa Evaporative condensers
US4450899A (en) * 1980-10-27 1984-05-29 Flakt Aktiebolag Method of regulating an outdoor steam condensor and apparatus for performing said method

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU247330A1 (ru) * Высшее военное инженерно техническое Краснознаменной училиЩй НСГ Испарительный конденсатор
US1861158A (en) * 1930-01-06 1932-05-31 Hilger George Air conditioning system
US3443633A (en) * 1967-03-30 1969-05-13 Gen Electric Temperature compensated air-cooled steam condenser
FR1600281A (fr) * 1968-01-04 1970-07-20
GB1382685A (en) * 1971-04-28 1975-02-05 Jacir J Apparatus for cooling or condensing fluid
GB2052721A (en) * 1979-06-22 1981-01-28 Watson E Hijos Sa Evaporative condensers
US4450899A (en) * 1980-10-27 1984-05-29 Flakt Aktiebolag Method of regulating an outdoor steam condensor and apparatus for performing said method

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2318180A (en) * 1996-10-08 1998-04-15 Aro Electrical Engineering Co Air-conditioning apparatus
GB2365955A (en) * 1998-09-09 2002-02-27 Liu Fu Chin Evaporative condensing apparatus
WO2004088220A1 (fr) * 2003-03-27 2004-10-14 The Coca-Cola Company Systeme et procede de refrigeration pour distributeur de boisson
US7591140B2 (en) 2003-03-27 2009-09-22 The Coca-Cola Company Beverage dispensing apparatus and method for beverage dispensing
US7870749B2 (en) 2003-03-27 2011-01-18 The Coca-Cola Company Beverage dispensing apparatus and method for beverage dispensing
CN101334246B (zh) * 2008-08-07 2010-06-09 北京市京海换热设备制造有限责任公司 一种空气冷却器
WO2015172180A1 (fr) * 2014-05-13 2015-11-19 Klaas Visser Condenseur évaporatif amélioré
CN106461297A (zh) * 2014-05-13 2017-02-22 K·维瑟 改进的蒸发冷凝器
CN109990625A (zh) * 2019-04-28 2019-07-09 洛阳鼎瑞节能科技有限公司 一种智控紧凑型干湿联合蒸发式空冷器
CN109990625B (zh) * 2019-04-28 2023-10-27 洛阳鼎瑞节能科技有限公司 一种智控紧凑型干湿联合蒸发式空冷器
GB2622183A (en) * 2022-05-04 2024-03-13 Coopertec Systems Ltd Evaporative condenser operating as either water heater or condenser

Also Published As

Publication number Publication date
EP0183808A1 (fr) 1986-06-11

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