EP0142209B1 - Plant, such as cooling plant or heat pump - Google Patents

Plant, such as cooling plant or heat pump Download PDF

Info

Publication number
EP0142209B1
EP0142209B1 EP84201623A EP84201623A EP0142209B1 EP 0142209 B1 EP0142209 B1 EP 0142209B1 EP 84201623 A EP84201623 A EP 84201623A EP 84201623 A EP84201623 A EP 84201623A EP 0142209 B1 EP0142209 B1 EP 0142209B1
Authority
EP
European Patent Office
Prior art keywords
condenser
ejector
liquid
refrigerant
plant
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.)
Expired
Application number
EP84201623A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0142209A2 (en
EP0142209A3 (en
Inventor
Johannes Gerardus Romijn
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.)
Grassos Koniklijke Machinefabrieken NV
Original Assignee
Grassos Koniklijke Machinefabrieken NV
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 Grassos Koniklijke Machinefabrieken NV filed Critical Grassos Koniklijke Machinefabrieken NV
Priority to AT84201623T priority Critical patent/ATE32944T1/de
Publication of EP0142209A2 publication Critical patent/EP0142209A2/en
Publication of EP0142209A3 publication Critical patent/EP0142209A3/en
Application granted granted Critical
Publication of EP0142209B1 publication Critical patent/EP0142209B1/en
Expired legal-status Critical Current

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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
    • F25B41/00—Fluid-circulation 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0015—Ejectors not being used as compression device using two or more ejectors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers

Definitions

  • the invention relates to a plant consisting of a circuit system with one or more compressors, one or more condensors, a separation vessel for separating liquid and gaseous refrigerants, one or more evaporators, and an ejector system coupled to an output line of the condenser(s) to use the high pressure of the liquid refrigerant coming from the condenser(s) for conveyance of the liquid refrigerant from the separation vessel to the evaporator(s).
  • Such plants are known in the literature.
  • NL-A-8105395 shows a cooling plant in which an ejector is used instead of a throttle device and a centrifugal pump or the like.
  • the energy which would otherwise be destroyed in the throttle device during throttling of the liquid refrigerant coming under high pressure from the condenser can be used effectively to convey the low-pressure liquid refrigerant from the separation vessel to the evaporator(s).
  • a plantwith a centrifugal pump or the like can, if necessary, be very simply adjusted by changing the speed of the pump.
  • the pump is, however, generally dimensioned for the maximum capacity of the plant. If a lower capacity is required, the pump continues to run at the same speed, which is a disadvantage from the point of view of energy consumption.
  • An ejector system then has advantages.
  • the disadvantages are that an ejector is geared to a particular capacity of the plant and is difficult or impossible to regulate.
  • Another complication here is that the mass flow of the liquid which is circulated through the ejector depends on the pressure difference over the ejector and increases with increasing pressure difference.
  • the mass flow fed through the compressor also depends on the pressure difference, but this mass flow decreases with increasing pressure difference.
  • the object of the invention is now to produce, in a plant with ejector circulation, regulation which is loss-free as far as possible, and this is achieved according to the invention in that the ejector system has at least two ejectors, connected in parallel and that a valve connecting the second or further ejector with the output line of the condenser(s) is controlled by a pressure difference sensing unit designed to compare the pressure of the gaseous refrigerant in the condenser(s) with the saturation pressure of the refrigerant at the ambient temperature in which the condenser(s) is set up, and to switch on the second and/or a further ejector if a predetermined pressure difference is exceeded.
  • the invention therefore saves on capital outlay and on energy consumption, while good adaption to the required capacity is possible.
  • FR-A-414466 discloses the pressure-controlled switching of parallel ejectors. However, this is not used in a refrigerant circuit system but in a vacuum system in order to rapidly obtain a high vacuum.
  • US-A-3 430 453 discloses the refrigerant pressure control of different condenser outlets, but not in combination with ejectors.
  • Fig. 1 is the diagram of the plant according to the invention with two ejectors.
  • Fig. 2 is a longitudinal section through one of the ejectors.
  • the compressor is indicated by 1, the condensor by 2, the separation vessel by 3, and the evaporators by 4, in this case two of them.
  • the suction line of the compressor 1 is indicated by 5 and debouches in a U-shape into the vapour chamber 6 of the separation vessel 3.
  • the liquid chamber of the vessel 3 is indicated by 7.
  • the line between compressor 1 and condenser 2 is indicated by 8.
  • a conventional oil separator 9 can also be set up in this line 8. The necessity for this depends on the type of compressor 1 used.
  • a line 10 discharges liquid refrigerant under high pressure from the condenser 2.
  • this line 11 there is a circulation device, consisting of two ejectors 12 and 13 connected in parallel and being the same or differing in size.
  • the line 10 coming from the condenser connects with the lefthand inlet of the ejector 12. Through this high-pressure liquid, low-pressure liquid is sucked in from the liquid part 7 via the line 11 and taken to the evaporator(s).
  • the high-pressure liquid from the condenser is first supercooled in the liquid bath 7.
  • a second ejector 13 is switched on in parallel by opening a valve 14.
  • Fig. 1 does show an arrangement, in which another ejector is switched on when the quantity of liquid in the condenser 2 becomes too high.
  • the temperature difference between the condenser and the outside air must remain constant as far as possible, being preferably of the order 11°C ⁇ 1°C.
  • the difference in pressure between the vapour in the condenser and the saturation pressure of the refrigerant at the temperature of the outside air is used as the signal for switching on a second or further ejector.
  • a small quantity of liquid refrigerant is to this end enclosed in a sensor 15, which is exposed to the outside air. Part of the liquid evaporates, and the pressure of the saturated vapour is passed on to an instrument 16, to which the condenser 2 is also connected via a line 8a.
  • the line 10 runs from the condenser 2 into the vapour chamber 6 of the vessel 2 which is in heat exchanging contact with the U-shaped inlet 18 of the suction line 5 of the compressor, as a result of which the inlet 18 is heated.
  • the vapour sucked up by the compressor is in this way considerably preheated by the warm high-pressure liquid from the condenser 2, as a result of which any liquid droplets formed convert to vapour form, so that no liquid is fed to the compressor.
  • the line 10 is conducted further in heat exhang- ing contact, with a capillary line 19, which connects with the line 11 and debouches above the inlet 18.
  • the line 10 then runs in heat exchanging contact through the liquid bath 7 of the vessel 3.
  • This consists of a massive element 21, which is preferably hectagonal in transverse section, and is made of brass or the like, with four connections.
  • the bottom connection is for connection to the ejector 12 set up below it. If the ejector is the lowest one, this connection is closed off with a cap or the like.
  • the line 10 connects with the lefthand connection, and the line part 11 leading to the evaporator(s) connects with the righthand connection.
  • the passage is formed by stepped cylindrial channels 22, 23 and 24 and a wider mixing part 25.
  • a passage made up of cylindrical bores is considerably simpler to produce than a double conical passage.
  • the bores can be made with a conventional drilling device.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Lubricants (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP84201623A 1983-11-11 1984-11-09 Plant, such as cooling plant or heat pump Expired EP0142209B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84201623T ATE32944T1 (de) 1983-11-11 1984-11-09 Anlage, wie kuehlanlage oder waermepumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL8303877 1983-11-11
NL8303877A NL8303877A (nl) 1983-11-11 1983-11-11 Installatie, zoals koelinstallatie of warmtepomp.

Publications (3)

Publication Number Publication Date
EP0142209A2 EP0142209A2 (en) 1985-05-22
EP0142209A3 EP0142209A3 (en) 1985-12-04
EP0142209B1 true EP0142209B1 (en) 1988-03-09

Family

ID=19842700

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84201623A Expired EP0142209B1 (en) 1983-11-11 1984-11-09 Plant, such as cooling plant or heat pump

Country Status (4)

Country Link
EP (1) EP0142209B1 (nl)
AT (1) ATE32944T1 (nl)
DE (1) DE3469799D1 (nl)
NL (1) NL8303877A (nl)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10323863B2 (en) 2015-05-12 2019-06-18 Carrier Kältetechnik Deutschland Gmbh Ejector refrigeration circuit
US10724771B2 (en) 2015-05-12 2020-07-28 Carrier Corporation Ejector refrigeration circuit

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5435149A (en) * 1994-04-28 1995-07-25 Frigoscandia Equipment Aktiebolag Refrigeration system
EP0835680B1 (de) * 1996-10-09 2003-04-02 Sulzer Chemtech AG Destillationsanlage
WO2006091190A1 (en) * 2005-02-18 2006-08-31 Carrier Corporation Refrigeration circuit with improved liquid/vapour receiver

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR414466A (fr) * 1909-10-18 1910-09-03 Bbc Brown Boveri & Cie Procédé et dispositif de fonctionnement des trombes d'eau à jet aspirant
GB125650A (en) * 1916-10-07 1919-05-01 G & J Weir Ltd Improvements in or relating to Steam-jet Air Ejectors.
CH152356A (de) * 1930-11-14 1932-01-31 Sulzer Ag Kälteanlage.
US2016056A (en) * 1935-08-01 1935-10-01 Frick Co Liquid circulating system
US2168438A (en) * 1936-04-08 1939-08-08 Carrier Corp Refrigerant circulation
US2119864A (en) * 1936-10-19 1938-06-07 George M Kleucker Fluid cooling apparatus and method
DE705684C (de) * 1938-01-18 1941-05-07 Ing Karl Krismer Fluessigkeitsstrahlpumpe
US2472729A (en) * 1940-04-11 1949-06-07 Outboard Marine & Mfg Co Refrigeration system
US2595995A (en) * 1947-05-20 1952-05-06 Thorwid Carl Refrigerating plant
US2512869A (en) * 1948-04-24 1950-06-27 James C Mcbroom Method and apparatus for circulating refrigerants
US3315484A (en) * 1965-05-17 1967-04-25 Phillips & Co H A Pressurized refrigeration circulating system
US3369374A (en) * 1966-06-20 1968-02-20 Carrier Corp Capacity control for refrigeration systems
AU421335B2 (en) * 1966-09-05 1972-02-09 Improvements relating to full flooded refrigeration systems
US3430453A (en) * 1967-01-24 1969-03-04 American Air Filter Co Refrigerant condenser arrangement
FR2147510A6 (nl) * 1971-07-29 1973-03-09 Bevengut Pierre Ets
GB1464453A (en) * 1973-09-21 1977-02-16 Daikin Ind Ltd Refrigerating apparatus
NO136427C (no) * 1975-03-11 1977-08-31 Kvaerner Brug Kjoleavdelning Anordning ved anlegg til komprimering og kondensering av gasser.
GB1502607A (en) * 1975-05-19 1978-03-01 Star Refrigeration Low pressure receivers for a refrigerating system
GB1595616A (en) * 1977-01-21 1981-08-12 Hitachi Ltd Air conditioning system
GB1582898A (en) * 1977-07-25 1981-01-14 Kamelmacher E Jet pump or mixer and jet means therefor
US4406134A (en) * 1981-11-23 1983-09-27 General Electric Company Two capillary vapor compression cycle device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10323863B2 (en) 2015-05-12 2019-06-18 Carrier Kältetechnik Deutschland Gmbh Ejector refrigeration circuit
US10724771B2 (en) 2015-05-12 2020-07-28 Carrier Corporation Ejector refrigeration circuit

Also Published As

Publication number Publication date
NL8303877A (nl) 1985-06-03
EP0142209A2 (en) 1985-05-22
EP0142209A3 (en) 1985-12-04
DE3469799D1 (en) 1988-04-14
ATE32944T1 (de) 1988-03-15

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