EP1775533B1 - Procédé pour faire fonctionner un système frigorifique à compression - Google Patents

Procédé pour faire fonctionner un système frigorifique à compression Download PDF

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Publication number
EP1775533B1
EP1775533B1 EP06021376.6A EP06021376A EP1775533B1 EP 1775533 B1 EP1775533 B1 EP 1775533B1 EP 06021376 A EP06021376 A EP 06021376A EP 1775533 B1 EP1775533 B1 EP 1775533B1
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EP
European Patent Office
Prior art keywords
temperature
pressure
evaporator
refrigerant
condenser
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Application number
EP06021376.6A
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German (de)
English (en)
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EP1775533A2 (fr
EP1775533A3 (fr
Inventor
Martin Herrs
Sebastian Ott
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Stiebel Eltron GmbH and Co KG
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Stiebel Eltron GmbH and Co KG
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Priority claimed from DE102005048967.2A external-priority patent/DE102005048967B4/de
Priority claimed from DE200510054104 external-priority patent/DE102005054104A1/de
Application filed by Stiebel Eltron GmbH and Co KG filed Critical Stiebel Eltron GmbH and Co KG
Publication of EP1775533A2 publication Critical patent/EP1775533A2/fr
Publication of EP1775533A3 publication Critical patent/EP1775533A3/fr
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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
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/002—Defroster control
    • F25D21/006—Defroster control with electronic control circuits
    • 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
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2700/13—Mass flow of refrigerants
    • F25B2700/135—Mass flow of refrigerants through the 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser
    • 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
    • F25B2700/197—Pressures of the 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the invention relates to a method for controlling a refrigeration cycle with a refrigerant, an evaporator, a pressure-increasing unit, a condenser and a throttle body.
  • the refrigerant present in the refrigeration circuit of the compression refrigeration system is in principle evaporated in the evaporator by heat removal of the medium to be cooled.
  • the compressor there is a pressure and thus a temperature increase.
  • the refrigerant is liquefied in the condenser with release of heat through the throttle body, the refrigerant is expanded to the evaporation pressure.
  • Such compression refrigerators are e.g. used for the heating of rooms and the preparation of service water; Both are referred to below as a heat sink.
  • the regulation of the heat sink temperature is usually carried out by switching on and off of the compressor or by modulation of the compressor speed. Such methods are for example from EP 1 355 207 A1 or DE 43 03 533 A1 known. Furthermore, it is an object of the scheme to optimize the efficiency of the evaporator and thus the refrigeration circuit.
  • the efficiency of the evaporator depends inter alia on its degree of filling, that is, which part of the evaporator with wet steam and which part of the evaporator with superheated Refrigerant medium is filled. The higher the wet steam content, the lower the overheating and the better the efficiency.
  • the overheating of the refrigerant at the evaporator outlet is preferably used.
  • This superheating of the refrigerant can preferably be determined from the evaporator pressure p 0 and the temperature T 0h of the superheated refrigerant at the evaporator outlet. Temperature and pressure can be easily measured by suitable sensors. The difference between evaporator outlet temperature T 0h and evaporating temperature T 0 , which is the temperature of the refrigerant during the evaporation without overheating, is calculated and is the actual superheat ⁇ T 0h-ist of the refrigerant.
  • the setpoint for evaporator overheating can be set as a fixed value for the refrigeration system. However, it is advantageous to adapt this to the operating point of the refrigeration system. This can be done via a characteristic field or an automatic adaptation as a function of dynamically variable variables in the cooling circuit. For example, when the tendency to oscillate occurs in the control loop, the superheat setpoint can be increased.
  • An overheating controller determines the difference between overheating actual and setpoint.
  • the manipulated variable here the throttle body, is set.
  • EP 1 275 917 describes a method for controlling a compression refrigeration machine with a refrigerant, an evaporator, a pressure booster unit, a condenser and a throttle body.
  • a first control value of the throttle body is determined as a function of a deviation of an actual overheating of a desired overheating. It is further determined whether the liquefaction temperature exceeds a threshold value. If this threshold has not been exceeded, then it is determined if the evaporator condenser temperature exceeds a threshold. If so, then it is determined if the evaporation temperature is lower than the threshold. If this is not the case, then the setpoint of overheating is increased. If the condenser temperature is less than the threshold, then it is checked if the superheat setpoint is higher than the minimum stable value. If this is the case then the superheat setpoint is returned to the minimum stable value.
  • the invention has for its object to provide a method and a compression refrigeration system of the type mentioned, in which avoided the disadvantages of the above control method and the superheat of the refrigerant optimally controlled at the evaporator output, thus optimizing the efficiency is achieved.
  • the evaporator pressure is a characteristic of the refrigeration cycle size, from which, as well as from the condenser pressure, draw conclusions about the state of the refrigerant circuit.
  • a model is developed according to the invention which generates a second control value for the throttle element. If the first control value, which is determined from direct measured variables of the circuit, linked to the second control value, there is a third control value for controlling the throttle body, which optimally controls the throttle body.
  • the invention is thus based on the assumption that the functions of the components located in the refrigeration circuit evaporator, compressor, condenser and throttle body can be described approximately using simplified physical description formulas.
  • the method according to the invention can comprise an expansion valve, a piston engine or a turbine as throttle element.
  • the second actuating signal reacts immediately. Due to the precalculation of the manipulated variable, the control loop gain is defined and the controller can be adapted accordingly.
  • this second control value according to the invention reacts quickly to changes in ambient conditions, it provides a good indication at the start of the compression refrigeration system and serves as a reference for a refrigerant deficiency detection.
  • the throttle can be set to the second control value.
  • the third control value is formed exclusively from the second control value
  • An offset of the throttling element, a cold circle specific constant and an exponent are included in the modeling as cold circle specific variables. They are predetermined and characteristic for a cycle, which makes integration in the model easy, since they are entered only once.
  • the first control value and the second control value are linked by multiplication.
  • the multiplicative link leads to a simplification of the operating point-dependent evaluation of the refrigerant shortage detection. Furthermore, the multiplicative linkage of the operating point-dependent contributes Line gain calculation and results in an approximately constant gain in the entire control loop.
  • the throttle can be set to a fixed value.
  • An adjustment of the throttle body to predetermined values in the special modes is useful in terms of refrigeration, in order to ensure efficient operation and to condition the refrigerant circuit for the resumption of normal operation.
  • the condenser temperature of the compression refrigeration system is measured and the condenser pressure is calculated therefrom.
  • the further method steps are identical to the steps a) and c) to g).
  • the condenser pressure is measured.
  • the cold-circle-specific constant enters the modeling as a characteristic variable. It can be determined in laboratory tests for the respective plant or type of plant or, preferably, adapted during normal operation.
  • the process steps are always performed when the refrigeration cycle is controlled for optimal overheating. This is preferably done regularly, in particular continuously, during the operation of the compression refrigeration system.
  • a heat pump is used as a compression refrigeration system
  • FIG. 1 A block diagram of a compression refrigeration system is shown in FIG Fig. 1
  • a refrigeration system consists of the components evaporator 11, compressor 12, condenser 13 and throttle body 15, which are connected by a conduit system through which the refrigerant is passed.
  • an expansion valve 15 is used as the throttle body 15.
  • a reciprocating engine or a turbine may be used as the throttle body.
  • a medium with a low boiling point (“refrigerant”, today mostly ozone-harmless CFCs or natural substances) is vaporized in the evaporator 11, the gaseous phase is then compressed in a compressor 12 and heated thereby. Under high pressure, the working fluid releases its heat for use at the condenser 13 (heating water, air flow) and condenses.
  • the condenser 13 heating water, air flow
  • the working fluid enters the partial circuit at low pressure again and is in turn fed to the evaporator 11, at the output of the evaporator pressure is determined by the measuring unit 16.
  • the temperature difference between the heat source and the refrigerant allows a heat flow to the evaporator 11. Subsequently, the refrigerant vapor is sucked by the compressor 12 and compressed. The temperature of the refrigerant is "pumped" through the temperature level of the heat distribution. At the condenser 13 is again a temperature difference, and there is a heat flow, for heat distribution. The high-pressure refrigerant cools again, condenses and is expanded via an expansion valve 15. The entire process takes place again and is thus in a cyclic process.
  • the chiller additionally has a determination unit 21 for determining a first control value W 1 for the expansion valve 15 as a function of the deviation of an actual overheating of the refrigerant from a desired overheating. Further, a unit 14 for determining the condenser pressure and a measuring unit 16 for measuring the evaporator pressure is provided.
  • unit 14 determines condenser pressure and measuring unit 16 measures evaporator pressure at the evaporator outlet. From the evaporation pressure, the evaporation temperature is determined. The formula for calculation is a formula approximation to the dependencies found by measurements on the particular refrigerant used.
  • the instantaneous actual overheating of the refrigerant can be derived: From the comparison of the actual overheating with the target overheating, a first control value W 1 for the expansion valve 15 is determined by means of a regulator, to which the opening angle of the expansion valve 15 is set and thus the refrigerant flow is regulated in the circuit. If the actual overheating is greater than the setpoint overheating, the actuator should start up, ie the first actuating signal will increase. If the actual overheating is less than the setpoint overheating, then the actuator should close, that is, the first control signal is smaller.
  • the controller can be designed as a P, PI, I or PID controller.
  • a second control value W 2 and third control value W 3 are determined in addition to the first control value W 1.
  • a model is formed in the unit 17 which compares the refrigerant mass flow at the evaporator inlet with the refrigerant mass flow at the evaporator outlet a second control value W 2 for the expansion valve 15 is calculated on the basis of the model from the evaporator pressure, the condenser pressure and cold cycle specific variables
  • the determination unit 19 combines the first control value W 1 with the second control value W 2 and in this way determines a third control value W 3 , to the value of which the expansion valve 15 is adjusted by means of the control unit 20.
  • Fig. 2 shows how a control circuit for the evaporator overheating can be operated with the inclusion of the predicted control signal size.
  • the pretreatment and evaluation of the sensor signals from the refrigeration circuit are freed of interference signals (for example 50 Hz hum) by means of low-pass, the sensor time constants are compensated. Furthermore, the actual overheating is calculated from the evaporator outlet temperature and the evaporator pressure and the condenser pressure is calculated from the condenser temperature.
  • the input signals of the block B1 are the evaporator pressure p 0 , the compressor inlet temperature t v1 , the evaporator outlet temperature t 02 and the condenser outlet temperature t c2 .
  • both temperatures compressor inlet temperature t v1 and evaporator outlet temperature t 02 ) are the same because the evaporator outlet is directly connected to the compressor inlet.
  • a recuperator When a recuperator is interposed, it will increase the refrigerant temperature as it passes through heat release, and overheating may occur be controlled before or after the recuperator, depending on the design of the refrigeration circuit control.
  • block B2 a pendulum detection of the signal is performed, and together with block B5 is evaluated by means of the process values from block B1, the operating point of the refrigeration circuit and set a corresponding desired overheating
  • a controller In block B4, a controller, the control deviation of overheating (subtraction of actual overheating ⁇ T actual and set overheating ⁇ T setpoint ) is fed in and in Output signal influenced by the control deviation is output. In this method step, the first control value is calculated
  • the second actuating signal is linked with the aid of the refrigeration-technical model with the control signal influenced by the first control signal to a total control signal.
  • This is advantageously done by multiplication.
  • the factor formed by the controller output 1, insofar as there is no deviation.
  • the factor formed by the control output is not equal to 1, and the precalculated actuating signal is correspondingly corrected with the aid of the refrigeration model.
  • other mathematical combinations such as addition or weighting are also possible.
  • the precalculated actuating signal passes through block B6 for further processing.
  • the third control signal is adapted, for example, to the control range limits of the expansion valve, and there is also a limitation of the control signal rise, so as not to "overwhelm" the time constant of the refrigerant circuit.
  • EMC extremely short-term disturbing influences
  • a very short-term fluctuating control signal are calculated, which would be completely damped away by the time constant of the refrigerant circuit, but charged the actuator.
  • block 6 limits the control signal to the physical control range of the valve.
  • control mode the mathematically linked and limited control signal is forwarded, such as already stated.
  • Further operating modes are the pump-down operation, an existing fault or the defrost operation.
  • Block 8 is an evaluation unit, with the aid of which the first actuating signal is evaluated.
  • a refrigerant deficiency detection it is evaluated whether the first control signal in the operating mode exceeds a parameterized value (here a value >> 1) for a minimum period of time.
  • a refrigerant deficiency is detected, displayed and, if appropriate, a modified processing in block 7 the third actuating signal causes, for example, emergency operation.
  • M is the servomotor of the expansion valve, which is coupled with this.
  • Fig. 3 the flow chart of the method according to the invention is shown schematically as process variables flow into the calculations of the evaporator pressure p 0 , the condenser pressure p c and the associated temperature variables.
  • the model is based on the physical background that the refrigerant mass flow at the evaporator inlet (from the expansion valve to the evaporator inlet) in a steady state refrigeration cycle at constant ambient conditions Evaporator) is equal to the refrigerant mass flow at the evaporator outlet (from the evaporator to the compressor)
  • the two refrigerant mass flows are equated with their respective influencing variables, which are measured in the refrigerant circuit. Furthermore, physical dependencies in the compressor and expansion valve are included in the modeling.
  • the mass flow at the evaporator outlet depends on the delivery behavior of the compressor. This is largely determined by the refrigerant pressures on the high-pressure and low-pressure sides of the refrigeration cycle and the degree of delivery influenced by them.
  • the factor const 1 parameterizes the design-related delivery rate for the refrigerant used in the compressor. This refers to a characteristic operating point, for other operating points deviations are tolerated, which are usually taken from a compressor data sheet or to be determined by laboratory measurements.
  • the mass flow at the evaporator inlet depends on the mass flow rate at the expansion valve. This is determined by the refrigerant pressures on the high pressure and low pressure side as well as by the central opening cross section of the expansion valve certainly.
  • the opening cross-section is controlled by a control or regulation in the case of electronic expansion valves.
  • the factor const 2 parameterizes the mass flow rate of the expansion valve for the refrigerant used. This refers to a characteristic operating point, for other operating points deviations are tolerated.
  • the evaporator pressure and condenser pressure are measured as process variables in the refrigerant circuit.
  • the condenser pressure can be calculated from the condenser temperature by means of refrigerant data.
  • the exponent Exp the offset and the cold-circle-specific constant const
  • these fixed variables are dependent on the respective components of a refrigeration circuit.
  • the offset of the expansion valve which describes the number of steps until the first opening.
  • the exponent maps both the function of the nozzle cross section over the output level and the function of the delivery rate of the compressor.
  • the exponential function formed by the exponent approximates the refrigeration cycle component-specific functions.
  • the parameterization of the model is carried out by a single constant of the refrigeration circuit const.
  • This parameter forms the sum of the parameters in the compressor, condenser, expansion valve and evaporator, which is determined by laboratory measurements or calculation.
  • the cold-zone-specific constant const during operation of the refrigeration circuit be adapted so that the calculation of the expansion valve steps due to the refrigeration cycle model is becoming more accurate.
  • a further advantageous embodiment of the method is to adapt the cold-cycle-specific constant const ascertained for example in laboratory tests in the course of operation so that the control signal obtained with the aid of the refrigeration model including const constant optimally adapts to the refrigeration process by a control deviation necessary corrections of the controller in block B4 minimal, the control is very accurate.
  • control signal (block B3) predefined by the cooling-technical model has to be corrected to a greater extent by the controller (block B4).
  • controller block B4
  • setting the desired overheating requires a much larger actuating signal than predicted, ie. with multiplicative connection of the control signals, the controller output signal is substantially greater than 1 when the control loop is steady.
  • the expansion valve in a preferred embodiment can be adapted to each of the three control values, depending on the operating mode, in order to optimally adapt the mode of operation to the respective operation.
  • the principle of the first embodiment can also be applied to an absorption chiller.
  • FIG Fig. 4 The operation of a compression refrigeration system according to the second embodiment is shown schematically in FIG Fig. 4 shown.
  • the refrigeration system according to the second embodiment can be combined with a refrigeration system according to the first embodiment or it can be operated as a standalone system.
  • a refrigeration system comprises an evaporator 111, a compressor 112, a condenser 113 and a throttle body 115, which are connected by a conduit system through which the coolant is passed.
  • a medium with a low boiling point (“refrigerant", today mostly ozone-harmless CFCs or natural substances) is vaporized in the evaporator 111, the gaseous phase then compressed in a compressor 112 and thereby heated.
  • the working fluid Under high pressure, the working fluid releases its heat for use at the condenser 113 (heating water, air flow) and condenses.
  • a throttle body expansion valve 115
  • the working fluid enters the partial circuit at low pressure again and in turn is fed to the evaporator 111, at whose output the evaporator outlet pressure is determined by the measuring device 16.
  • the temperature difference between the heat source and the refrigerant allows a heat flow to the evaporator 111. Subsequently, the refrigerant vapor is sucked by the compressor 112 and compressed. The temperature of the refrigerant is thereby "pumped" above the temperature level of the heat distribution.
  • the condenser 113 is again a temperature difference and there is a heat flow. for heat distribution.
  • the high-pressure refrigerant cools again, condenses and is via an expansion valve 115 relaxed. The entire process takes place again and is thus in a cyclic process.
  • the refrigerating machine further comprises a measuring unit 116 for measuring the evaporator outlet pressure, a determining unit 117 for calculating a melting temperature from the evaporator outlet pressure, a first determining unit 118 for determining a first difference from the melting temperature and a melting temperature reference value, a second determining unit 119 for determining a second difference from the evaporator outlet pressure and a cut-off pressure, and a defrosting unit 120 for initiating a defrosting operation. if the first difference exceeds a temperature limit, and to terminate the defrost event if the second difference is less than a pressure limit.
  • the measuring device 116 detects at the outlet of the evaporator 111, the pressure of the refrigerant, which is passed from the evaporator to the compressor. From this measured evaporator outlet pressure, the tau temperature is calculated in the determination unit 117, which in turn flows into further arithmetic operations.
  • the arithmetic unit can carry out further computation steps, as described below in the flowchart in FIG Fig. 2 is explained
  • a first difference is determined from the tare temperature calculated in the determination unit 117 and a tau temperature reference value. If this first difference exceeds a temperature limit value, the defrost unit 120 initiates the defrosting operation for the evaporator.
  • the flowchart of Fig. 6 presents this process step in detail.
  • a second difference is formed from the evaporator outlet pressure and a shut-off pressure.
  • the defrost unit 120 stops the defrosting process if the second difference falls below a pressure threshold. This process step is based on Fig. 10 explained.
  • Fig. 5 For example, algorithmic calculation steps for determining an averaged taut temperature of the method according to the invention are shown schematically. Since the evaporator temperature signal can oscillate depending on the operating condition, it must be averaged and filtered. In order to obtain the most stable signal, further signals are generated from the evaporation temperature.
  • the temperatures ⁇ i, n + 1 of the following cycle are calculated from the variables ⁇ i, n of the current cycle, wherein the mean temperature ⁇ middle, n + 1 is the essential quantity to detect a defrost requirement. Furthermore, C Ab as a factor for the decay of the signal and C on as a factor for the sounding of the signal into the calculation.
  • the factors C Ab and C Auf are determined as follows. In general, the factors are to be dimensioned so that in the case of a cyclic fluctuation of the overheating, ie a pendulum, the minimum and the maximum amplitude temperature reflect the periodic maxima and the periodic minima of overheating. If the oscillation stops, the minimum and maximum amplitude temperature should be adapted to the periodically decaying minima and maxima of overheating.
  • the factor C Auf is to be dimensioned so that the minimum and maximum amplitude temperature can follow the gradient of fluctuating overheating so that the maxima and minima can be followed almost unattenuated.
  • the time constant for the fade should be a fraction of the oscillation time constant of commuting, for example a quarter of this.
  • the factor C Ab is to be dimensioned so that the minimum and the maximum amplitude temperature between two maxima or minima is largely retained and does not completely decay, so that an envelope is described with both amplitude temperatures.
  • the time constant for the fade should be a multiple of the swing time constant of the pendulum, for example, twice this.
  • the oscillation time constant of oscillation is approx. 2 to 10 minutes, depending on the cooling circuit. If the time constants are dimensioned for fading up and down, the factors can be calculated after the controller iterative time.
  • T 1 1 - C From ⁇ ⁇ Max _ amp . n + C From ⁇ ⁇ medium . n
  • T 3 1 - C On ⁇ ⁇ Max _ amp . n + C On ⁇ ⁇ 0
  • T 4 1 - C On ⁇ ⁇ min_amp . n + C On ⁇ ⁇ 0
  • T 5 0.5 ⁇ ⁇ min _ amp . n + 1 + ⁇ Max _ amp . n + 1
  • T 5 is the mean temperature ⁇ medium .
  • Fig. 6 By way of example, the sequence of the method according to the invention for defrost detection is shown schematically.
  • the method according to the invention begins with the method step sequence after an initial blocking time t blocking which is between 5 and 30 minutes, preferably between 10 and 15 minutes, which corresponds to the time frame in which the system settles.
  • a defrost requirement is recognized in the method according to the invention in that a first difference between an averaged taut temperature and a taut temperature reference value exceeds a temperature limit value.
  • the taut temperature reference value can be determined from the mean temperature.
  • the maximum averaged taut temperature up to the time t is set as the taut temperature reference value.
  • step 33 is initiated.
  • This method step contains a loop which checks how often the difference from step S32 has exceeded the temperature limit T limit.
  • the defrost process in step S34 is initiated if step S33 is initiated at least once. in a preferred embodiment, five times having received positive information from step S32
  • Fig. 7 shows the course of the calculated values for the amplitude as a function of time. On the x-axis the time course is shown, on the y-axis the Amplitudes. It can clearly be seen from the illustration that the tau temperature ⁇ 0 calculated from the measured evaporator pressure oscillates and is enclosed by the two calculated values for the minimum and the maximum amplitude temperature. The mean value ⁇ mean is between the minimum and maximum amplitude temperature. Above these temperature values lies the temperature reference value ⁇ ref_max , which only changes if the mean temperature exceeds the temperature reference value.
  • Fig. 8 shows the dependencies in the outdoor temperature compensation of the tau temperature ⁇ 0 .
  • the outside temperature ⁇ is measured outside and included in the calculation of the tau temperature.
  • a tare temperature ⁇ corrected by the outside temperature ⁇ outside is calculated by forming the difference of a second tau temperature ⁇ 0 and the outside temperature ⁇ outside .
  • the corrected melting temperature ⁇ corrected enters the method according to the invention as the first melting temperature.
  • Fig. 9 shows a representation of the temperature behavior of water in the range of 0 ° C. On the y-axis is the temperature, on the x-axis the time course is shown. Water has the special property that during the thawing process it remains at the 0 ° C temperature level for a longer time until the temperature finally rises further. This effect is exploited to determine the optimal point at which the entire ice has melted. Only when all the ice has melted on the evaporator surface, the temperature rises from the temperature plateau of 0 ° C, which manifests itself in an increase in the evaporator pressure. Thus, the defrost process is terminated only when the evaporator is free of ice
  • Fig. 10 shows the various pressure ranges that passes through the evaporator outlet pressure p 0 during the defrosting process.
  • the temperature is plotted on the y-axis and the time on the x-axis.
  • zone I the temperature rises to "melt pressure”
  • II the temperature plateau refers to “melt pressure”
  • III the temperature rise after defrosting is shown. If the pressure reaches the switch-off pressure, which is about 2 bar above the evaporator outlet pressure corresponding to the melting temperature of the ice, the defrost is ended.
  • a method of controlling a defrosting operation of an evaporator of a refrigerating machine (such as a refrigerating machine according to the first embodiment).
  • the method according to the second embodiment can be operated independently of the refrigerating machine according to the first embodiment.
  • an evaporator outlet pressure is measured.
  • a teat temperature is determined based on the evaporator outlet pressure.
  • a first difference from the first teat temperature and a tau temperature reference value is determined.
  • a defrost operation is initiated if the first difference exceeds a temperature limit.
  • Defrosting is accomplished by determining a second difference from the evaporator outlet pressure and a shutoff pressure and terminating defrost if the second difference is less than a pressure threshold
  • the evaporator outlet pressure shows a characteristic of the refrigeration cycle over time, from which can be concluded on a non-performance optimized operation.
  • the dew temperature can be calculated from the evaporator outlet pressure. If the surface structure of the evaporator ices up, the efficiency deteriorates, the evaporator pressure drops and thus also the calculated peat temperature. If the difference between the calculated peat temperature and a reference temperature exceeds a temperature limit, a defrost requirement can be detected and a defrost process initiated. During defrost, the evaporator outlet pressure is still monitored and compared to a shutdown pressure. If the difference between these two pressures becomes sufficiently small, the evaporator surface is sufficiently defrosted and the defrosting operation is terminated.
  • the advantages of this method are that a significantly increased detection reliability is given.
  • the calculation is preferably carried out regularly during the operation of the chiller, which also temperature jumps of the outside air can be perceived quickly enough and is responded accordingly.
  • pressure sensors When using pressure sensors, a minimum inertia in the detection process is ensured under a low defrost energy requirement
  • the components in the circuit of the chiller can be reused without having to be exchanged for expensive and sensitive electronic units.
  • the first taut temperature is calculated from a difference between a second tau temperature and an outside temperature, wherein the second tau temperature is calculated from the evaporator outlet pressure and the outside temperature is measured. This evaluates the temporal behavior of the peat temperature relative to the outside temperature
  • the temperature limit, cut-off pressure and pressure limit are fixedly defined for a particular installation. However, they may also be e.g. be adaptable to special external conditions, in particular via manual adjustment or an adaptation device.
  • the tew temperature reference value is determined by the maximum averaged taut temperature to ensure an adaptive method.
  • the evaporator outlet pressure is compared with a shutdown pressure.
  • the switch-off pressure is around 1 to 3 bar, preferably around 2 bar, above the evaporator outlet pressure corresponding to the melting temperature of the ice.

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

Claims (8)

  1. Procédé de réglage d'un réfrigérateur à compression comprenant un fluide frigorigène, un évaporateur (11), une unité d'augmentation de la pression (12), un condenseur (13) et un organe d'étranglement (15) avec pour étapes :
    a)
    mesure de la pression de l'évaporateur et de la température du fluide frigorigène à la sortie de l'évaporateur, calcul de la température d'évaporation à partir de la pression de l'évaporateur et des caractéristiques spécifiques du fluide frigorigène, détermination d'une surchauffe réelle du fluide frigorigène à la sortie de l'évaporateur à partir de la différence de la température du fluide frigorigène et de la température d'évaporation, détermination de la variation entre la surchauffe réelle et une surchauffe de consigne, et détermination d'une première valeur de réglage pour l'organe d'étranglement en fonction de la variation entre surchauffe réelle et la surchauffe de consigne.
    b) calcul de la pression du condenseur
    c) mesure de la pression de l'évaporateur
    d) Élaboration d'un modèle comparant le débit-masse de fluide frigorigène à l'entrée de l'évaporateur et le débit-masse de fluide frigorigène à la sortie de l'évaporateur,
    e) calcul d'une deuxième valeur de réglage pour l'organe d'étranglement (15) à l'aide du modèle selon lequel la pression de l'évaporateur et la pression du condenseur se présentent sous la forme de variables de processus et un offset de l'organe d'étranglement présente une constante spécifique au circuit frigorifique et un exposant sous la forme de valeurs spécifiques au circuit frigorifique,
    f) détermination d'une troisième valeur de réglage pour l'organe d'étranglement (15) en associant la première valeur de réglage à la deuxième valeur de réglage et
    g) réglage de l'organe d'étranglement (15) sur la troisième valeur de réglage.
  2. Procédé selon la revendication 1,
    caractérisé en ce que la température du condenseur est mesurée et en ce que la pression du condenseur est calculée à partir de la température du condenseur.
  3. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que la pression du condenseur est mesurée.
  4. Procédé selon l'une des revendications précédentes selon lequel un processus de dégivrage d'un évaporateur (11) d'un réfrigérateur se produit selon les étapes suivantes :
    a) mesure de la pression à la sortie de l'évaporateur,
    b) détermination d'une première température de dégivrage sur la base de la pression à la sortie de l'évaporateur,
    c) détermination d'une première différence à partir de la première température et d'une valeur de référence de la température de dégivrage,
    d) initiation d'un processus de dégivrage au cas où la première différence dépasse une valeur limite de température, le processus de dégivrage comprenant les étapes suivantes :
    d1) détermination d'une seconde différence à partir de la pression à la sortie de l'évaporateur et d'une pression de disjonction,
    d2) conclusion du processus de dégivrage au cas où la seconde différence est inférieure à une valeur limite de pression.
  5. Procédé selon la revendication 4,
    caractérisé en ce que la première température de dégivrage est calculée à partir d'une différence entre une deuxième température et une température extérieure, la deuxième température étant calculée à partir de la pression à la sortie de l'évaporateur et la température extérieure étant mesurée.
  6. Procédé selon l'une des revendications 4 à 5,
    caractérisé en ce que la première température impliquée dans la constitution de la différence à l'étape c) est une température obtenue à partir d'au moins deux températures calculées à l'étape b).
  7. Procédé selon l'une des revendications 4 à 6,
    caractérisé en ce que les étapes a) à d2) sont réalisées de manière régulière, en particulier en continu.
  8. Procédé selon l'une des revendications 4 à 7,
    caractérisé en ce que la valeur limite de température est définie de manière fixe.
EP06021376.6A 2005-10-13 2006-10-12 Procédé pour faire fonctionner un système frigorifique à compression Active EP1775533B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005048967.2A DE102005048967B4 (de) 2005-10-13 2005-10-13 Verfahren zum Betreiben einer Kompressionskälteanlage
DE200510054104 DE102005054104A1 (de) 2005-11-12 2005-11-12 Verfahren und Vorrichtung zum Regeln eines Abtauvorgangs eines Verdampfers einer Kältemaschine

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EP1775533A2 EP1775533A2 (fr) 2007-04-18
EP1775533A3 EP1775533A3 (fr) 2013-04-03
EP1775533B1 true EP1775533B1 (fr) 2018-03-28

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018125411A1 (de) * 2018-10-15 2020-04-16 Vaillant Gmbh COP-optimale Leistungsregelung

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2894417B1 (fr) * 2014-01-09 2018-03-14 Stiebel Eltron GmbH & Co. KG Système de pompe à chaleur
DE102020115270A1 (de) 2020-06-09 2021-12-09 Stiebel Eltron Gmbh & Co. Kg Verfahren und Vorrichtung zum Regeln eines Kältekreislaufs
DE102020115275A1 (de) 2020-06-09 2021-12-09 Stiebel Eltron Gmbh & Co. Kg Verfahren zum Betreiben einer Kompressionskälteanlage und Kompressionskälteanlage
DE102020115272A1 (de) * 2020-06-09 2021-12-09 Stiebel Eltron Gmbh & Co. Kg Verfahren zum Regeln eines Abtauvorgangs eines Verdampfers einer Kompressionskälteanlage und Kompressionskälteanlage
CN112085367B (zh) * 2020-09-02 2022-08-23 浙江浙能技术研究院有限公司 一种凝汽器脏污系数在线监测方法及系统

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001001052A1 (fr) * 1999-06-30 2001-01-04 Lancer Partnership, Ltd. Ensemble de commande pour groupe frigorifique

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA855945A (en) * 1968-07-26 1970-11-17 K. Foessl John Temperature control unit
US5035119A (en) * 1984-08-08 1991-07-30 Alsenz Richard H Apparatus for monitoring solenoid expansion valve flow rates
ITPD20010173A1 (it) * 2001-07-12 2003-01-12 Carel Srl Dispositivo per limitare la pressione di condensazione di una macchina frigorifera

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001001052A1 (fr) * 1999-06-30 2001-01-04 Lancer Partnership, Ltd. Ensemble de commande pour groupe frigorifique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018125411A1 (de) * 2018-10-15 2020-04-16 Vaillant Gmbh COP-optimale Leistungsregelung

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EP1775533A3 (fr) 2013-04-03

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