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
  • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
• • 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
  • F25B40/00—Subcoolers, desuperheaters or superheaters
• • 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
  • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
  • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
• • 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
  • F25B2600/25—Control of valves
  • F25B2600/2513—Expansion valves
• • 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
  • F25B2700/21—Temperatures
  • F25B2700/2103—Temperatures near a heat exchanger
• • 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
  • F25B2700/21—Temperatures
  • F25B2700/2115—Temperatures of a compressor or the drive means therefor
  • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

• Refrigeration systems in cooling and freezing systems refrigeration technology, refrigeration machine for cooling and heating operation, refrigeration systems, refrigeration units, heat pumps, air conditioning systems and others.
• thermosiphon mode in which the refrigerant is fed to the evaporator via a compensating and separating vessel, either by gravity or with the help of a pump, and where the evaporator outlet may still contain liquid components in the vapor, and so in the There is usually no overheating of the refrigerant at the evaporator outlet.
• Dry expansion systems have the advantage of simple construction and small refrigerant contents.
• the evaporator efficiency is essentially influenced by the smallest possible evaporator overheating.
• Our innovation relates firstly to the dry expansion system (6) (1), to the dry expansion system (6) (1) with a downstream IWT (2) (internal heat exchanger, i.e. with a heat exchange between the refrigerant liquid line upstream of the expansion valve on the one hand and the suction steam after the evaporator on the other hand), to the two-stage evaporation system (6) (1 + 2) (a combination of dry expansion system and thermosiphon system, evaporator with IWT) and other refrigeration systems built on this basis.
• IWT internal heat exchanger, i.e. with a heat exchange between the refrigerant liquid line upstream of the expansion valve on the one hand and the suction steam after the evaporator on the other hand
• x-value is the value that indicates the proportion of the refrigerant that has already evaporated at the beginning of the evaporation process) of the refrigerant state in the injection valve (6 ) and at the beginning of the evaporator (1), which affects the injection valve (6) and evaporator output (1) as well as the control behavior of the injection valve (6) and its output, respectively the promoted refrigerant mass flow and, on the other hand, with suction steam at the inlet to the compressor (5 ), where the changed temperature (B), because of the specific volume assigned to the respective temperature (and pressure), has an influence on the delivery volume of the compressor (5), that is, again on the delivered mass flow.
• the aim of the invention is to achieve the following in cooling / freezing systems, refrigeration machines for cooling and heating operation, refrigeration systems, refrigeration units, heat pumps and all systems using refrigerants and coolants:
• This temperature difference can in any case be smaller than if the refrigerant leaves the evaporator (1) "overheated" (P8 / T22) during dry expansion operation.
• This constant can be achieved by various measures. For the sake of simplicity, we describe keeping it constant by means of a heat exchanger (4) in the refrigerant liquid line upstream of the injection valve, which uses a second medium to keep the outlet temperature of the liquid refrigerant constant.
• the medium used to keep the refrigerant liquid temperature constant can be of any type (gaseous, liquid, etc.).
• One way of keeping the refrigerant liquid temperature upstream of the injection valve (A) constant is for the flow (D) of the medium to be cooled, for example water, brine, etc., to be passed through a heat exchanger (4), on the second side of the heat exchanger the refrigerant is led either in cocurrent, cross or countercurrent, etc.
• the refrigerant liquid temperature upstream of the injection valve (A) can also be regulated by means of mass flow control of the refrigerant liquid (9) by the IWT (2) or the suction steam (12) by the IWT (2) (depending on the conditions, only partial mass flows sometimes flow through) the IWT (2)).
• a new feature of the invention is that the refrigerant liquid temperature upstream of the injection valve (6) (A) is kept constant.
• a new feature of the invention is that the refrigerant liquid temperature, especially in the two-stage evaporation process (1 + 2) upstream of the injection valve (6) (A), is at a very low value, close to or on the left limit curve of the log (p), h diagram for Refrigerant, (the refrigerant enters liquid like in a thermosiphon system or with a minimal vapor content in the evaporator (1)) is kept constant.
• a new feature of the invention is that the refrigerant suction steam at the inlet to the compressor (5) (B) is kept constant.
• Measures for this can be appropriate, such as keeping the refrigerant liquid upstream of the injection valve (6) (A) :.
• IWTs (2) two-stage evaporators, semi-flooded systems
• IWTs (2) two-stage evaporators, semi-flooded systems
• the suction steam temperature can also be maintained by means of measures such as external subcoolers (3), which regulate the refrigerant liquid inlet temperature in the IWT (2) (8) and in this way the suction steam outlet temperature from the IWT (2) (B).
• measures such as external subcoolers (3), which regulate the refrigerant liquid inlet temperature in the IWT (2) (8) and in this way the suction steam outlet temperature from the IWT (2) (B).
• the constant maintenance of the suction steam temperature can also be controlled by means of mass flow control of the refrigerant liquid (9) by the IWT (2) or the suction steam (12) by the IWT (2).
• the constant maintenance of the suction steam temperature can also be achieved by more or less "flooding" the IWT (2) (only in the two-stage evaporation process).
• the "flooding" of the IWT's (2) can be done by means of temperature control of the suction steam at the inlet of the compressor (two-stage evaporator control) (T23), level control (7) directly via the evaporator (1), IWT (2) individually or together or a reference size such as for example, the collector or another or a pressure difference control (7) directly via the evaporator (1), IWT (2) individually or together.
• the invention is essentially based on the fact that, through suitable measures, the refrigerant liquid temperature upstream of the injection valve (A) and the suction steam temperature upstream of the compressor (B) are at an arbitrary value (within the physically possible but, if necessary, reaching the physical limits) is held.
• the constant temperature of the refrigerant at these two points in the refrigeration system ensures stable operation and, if desired, the smallest temperature differences between the media to be cooled (inlet / outlet temperature ( C / D) on the one hand and inlet and / or outlet temperature to the evaporation temperature (C / D to to) on the other) reached.
• the invention is based on the fact that by means of suitable measures a stable operation of cooling systems with small temperature differences of the media to be cooled and thus higher efficiencies (and thereby highly efficient evaporation in cooling systems) is achieved.
• the process of refrigeration is supplemented or changed in such a way that in addition to the controlled suction and high pressures in refrigeration systems, the temperature of the liquid refrigerant upstream of the injection valve (A) and the suction steam upstream of the compressor inlet (B) is now controlled, regulated and kept constant.
• the innovation is the control of the two refrigerant states described (A + B), regardless of which method is used, whereby depending on the application, only one or the other measure (A or B or 7) has to be taken. It is therefore possible only with the temperature control of the liquid refrigerant upstream of the injection valve (A) or the temperature control of the suction steam upstream of the compressor (B) or with the control of the liquid refrigerant upstream of the injection valve and the temperature control of the suction steam (A + B) desired result to come.
• Suitable measures for controlling the temperature of the refrigerant upstream of the injection valve are:
• a controlled fill level of the refrigerant to be liquefied in the evaporator or. in the IWT resp. in the second stage of the two-stage evaporator for example by means of level control (7) or pressure difference measurement (7) or suction steam temperature control (T23) in front of the compressor, with level control via the evaporator, the IWT or the second stage of the two-stage evaporator individually and / or the evaporator alone or in combination with the IWT or the second stage of the two-stage evaporator or a reference object, e.g. B. collector.
• control and integration can be carried out as follows (combinations and variants thereof are also possible): Injector control by detecting the temperature of the refrigerant upstream of the injection valve (T20) and pressure / temperature after the injection valve (T21 / P7), between the first and the second evaporator stage P8 / T22) or after the second evaporator stage (P9 / T23) or combinations thereof.
• the temperature / pressure difference (T20 / P7, P8, P9) serves as the controlled variable for the injection valve (6).
• a level or pressure difference control (7) can be used for the injection valve.
• the temperature upstream of the injection valve is kept constant by means of suitable measures (as described above).
• This constant temperature of the liquid refrigerant upstream of the injection valve can be achieved, for example, with a heat exchanger (4) installed between the liquid line and the medium flow.
• Part or all of the mass flow of the cooled medium is passed through the heat exchanger (4) in cocurrent, countercurrent or crossflow, etc. to the refrigerant liquid (10/11).
• the medium can be fed through the exchanger at a regulated or unregulated temperature.
• the refrigerant liquid is subcooled or kept constant in front of the injection valve (A) at any but, if desired, also at a very low temperature level, which means that the evaporator (1) has a liquid or only a small amount Share of already evaporated refrigerant is fed.
• the proportion of refrigerant that has already evaporated in the evaporator can be optimized and adjusted to the evaporator type (1) with a corresponding temperature of the liquid refrigerant upstream of the injection valve (A) and thus the efficiency for starting the evaporation process.
• the refrigerant liquid inlet temperature can be entered into the second evaporator stage (IWT) (2) (F), for example using an ex- internal subcooler (3) can be limited at high condensation temperatures.
• part of the refrigerant liquid mass flow (E), depending on the suction steam temperature (B), can be directed past the second compressor stage (IWT) (2).

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Devices That Are Associated With Refrigeration Equipment (AREA)
• Air Conditioning Control Device (AREA)
• Greenhouses (AREA)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

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• 2004
  • 2004-01-28 AT AT04705750T patent/ATE426785T1/de active
  • 2004-01-28 ES ES04705750T patent/ES2322152T3/es not_active Expired - Lifetime
  • 2004-01-28 DE DE502004009247T patent/DE502004009247D1/de not_active Expired - Lifetime
  • 2004-01-28 EP EP09003503A patent/EP2063201B1/fr not_active Expired - Lifetime
  • 2004-01-28 US US10/587,741 patent/US9010136B2/en active Active
  • 2004-01-28 EP EP04705750A patent/EP1709372B1/fr not_active Expired - Lifetime
  • 2004-01-28 WO PCT/CH2004/000046 patent/WO2005073645A1/fr not_active Application Discontinuation
  • 2004-01-28 ES ES09003503T patent/ES2401946T3/es not_active Expired - Lifetime

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