EP3816543B1 - Procédé de régulation d'un détendeur - Google Patents

Procédé de régulation d'un détendeur Download PDF

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Publication number
EP3816543B1
EP3816543B1 EP20200553.4A EP20200553A EP3816543B1 EP 3816543 B1 EP3816543 B1 EP 3816543B1 EP 20200553 A EP20200553 A EP 20200553A EP 3816543 B1 EP3816543 B1 EP 3816543B1
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EP
European Patent Office
Prior art keywords
refrigerant
temperature
heat source
compressor
expansion valve
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EP20200553.4A
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German (de)
English (en)
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EP3816543A1 (fr
Inventor
Florian ENTLEITNER
Florian Fuchs
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Lambda Waermepumpen GmbH
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Lambda Waermepumpen GmbH
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Publication of EP3816543A1 publication Critical patent/EP3816543A1/fr
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—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
    • 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
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • 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
    • F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present invention relates to a method for controlling an expansion valve of a refrigerant circuit with the features of the preamble of claim 1, a refrigerant circuit with the features of the preamble of claim 10 and a device with at least one such refrigerant circuit.
  • WO-A-2019/020952 discloses a method and a refrigerant circuit with the pre-characterizing features of claims 1 and 10.
  • Refrigerant circuits known in the prior art for example for heat pumps, refrigeration systems or air conditioners, include an evaporator, a compressor, a condenser, an expansion valve and a control device connected to the expansion valve in a signal-conducting manner for controlling the expansion valve.
  • the evaporator, compressor, condenser and expansion valve are arranged one behind the other in series in a circulation direction of the refrigerant circuit and have a refrigerant flowing through them that circulates in the closed refrigerant circuit.
  • a heat source acts on the evaporator in a known manner and causes heat to be introduced into the refrigerant in the evaporator and thus leads to an increase in the enthalpy of the refrigerant, so that the refrigerant vaporizes in the evaporator.
  • the heat source can be the area around the evaporator, the ambient air of which surrounds the evaporator or is fed to the evaporator (for example in the case of an air heat pump).
  • heat source is water or another fluid, which is fed to the evaporator in a manner known per se via its own heating medium circuit, which is hydraulically decoupled from the refrigerant circuit and is therefore materially separate from it, in order to heat the refrigerant of the refrigerant circuit in the evaporator .
  • the heat source is thermally connected to the evaporator and in the evaporator the refrigerant is supplied with heat from the heat source thermally connected to the evaporator (or its heat source medium, eg air or water) and the refrigerant evaporates while absorbing heat.
  • the compressor that follows in the direction of circulation (often also known as Compressor) the vaporized (i.e.
  • gaseous refrigerant is compressed, whereby the refrigerant is raised to a higher pressure and temperature level.
  • the gaseous refrigerant is then passed on in the direction of the condenser with a correspondingly increased pressure and temperature.
  • the condenser (often also referred to as the liquefier), the gaseous, superheated refrigerant is cooled to a temperature at which the refrigerant liquefies and is thereby liquefied, with the release of heat.
  • the liquefied refrigerant passes through the expansion valve, which represents a bottleneck in the refrigerant circuit.
  • the refrigerant which was previously brought to a low pressure level by the expansion valve, absorbs heat from the heat source (e.g. the environment).
  • the refrigerant is (usually completely) vaporized and "superheated” by 5 to 15 K (degrees Kelvin).
  • This so-called suction gas overheating i.e. the increase in the gas temperature of the vaporized refrigerant above the saturation temperature
  • the suction gas overheating is therefore the temperature difference between the gas temperature of the vaporized refrigerant when it enters the compressor (so-called suction gas temperature) and the vaporization temperature.
  • the evaporation temperature is the temperature at which the refrigerant can exist both as a liquid and as a gas and depends on the prevailing pressure.
  • the evaporating temperature can be obtained from the pressure at a point between the valve outlet of the expansion valve and the Compressor inlet of the compressor can be calculated, or alternatively measured as a temperature after the expansion valve.
  • the refrigerant is continuously expanded in the expansion valve, causing it to partially evaporate.
  • the liquid-gas mixture then flows through the evaporator, in which heat from the heat source acting on the evaporator (or its heat source medium) is supplied to the refrigerant.
  • the refrigerant initially evaporates essentially completely at constant pressure. After reaching the dew line of the refrigerant, the gaseous refrigerant is further heated approx. 5 to 15 K above the boiling temperature (suction gas overheating, so that the downstream compressor does not suffer any damage from liquid entry).
  • the expansion valve controls the refrigerant mass flow and the pressure, so that the refrigerant at the compressor inlet has a certain suction gas superheat at all times. Insufficient or no suction gas superheat can cause damage to the compressor. In this case, the evaporation pressure must be reduced (ie the expansion valve closed). On the other hand, excessive suction gas superheat has a negative effect on the refrigeration cycle efficiency because the evaporating pressure is lower than necessary.
  • a fixed suction gas overheating eg 5 K
  • the difference between the suction gas temperature (gas temperature of the vaporized refrigerant when it enters the compressor) and the vaporization temperature is used as the controlled variable.
  • Refrigerant circuits with a so-called internal heat exchanger or suction gas heat exchanger are also known, which are also operated with dry evaporation.
  • a first fluid line of the internal heat exchanger is arranged between the condenser and the expansion valve (i.e. connects the condenser outlet with the valve inlet of the expansion valve) and a second fluid line of the internal heat exchanger is arranged between the evaporator and the compressor (i.e. connects the evaporator outlet with the compressor inlet).
  • the refrigerant flowing through the first fluid line gives off heat to the refrigerant flowing through the second fluid line and thus heats the refrigerant before it enters the compressor.
  • the high-temperature liquid refrigerant exiting the condenser is routed through the internal heat exchanger (in its first fluid line) and is thereby cooled by a few Kelvin.
  • This heat is used to further heat the already fully vaporized and slightly superheated refrigerant from the evaporator by passing it through the second fluid line of the internal heat exchanger.
  • the regulation of the expansion valve corresponds to that of the simple dry evaporation described above.
  • the opening width of the expansion valve is controlled in order to maintain a certain suction gas superheat (difference between the suction gas temperature between the evaporator and the internal heat exchanger and the evaporating temperature).
  • a disadvantage of the known concept is that suction gas overheating (even if it is less) is necessary in the evaporator. This means that only small amounts of energy can be transferred in the internal heat exchanger.
  • the suction gas temperature upstream of the compressor cannot be controlled, with excessively high suction gas temperatures at the compressor inlet leading to damage and overheating of the compressor.
  • the temperature changes in the internal heat exchanger are strongly dependent on the operating conditions (e.g. partial load operation and pressure difference). For this reason, internal heat exchangers are usually only used in practice for small increases in the temperature of the refrigerant and the transfer surface is correspondingly small. So-called pipe-in-pipe heat exchangers or pipe spindles in liquid separators as combination devices are typical.
  • a refrigerant circuit can also each include more than one evaporator, internal heat exchanger, compressor or condenser.
  • the term “at least one” in connection with these components means that one instance or several instances of the respective component—arranged in parallel or one behind the other—is or are present. In the interest of easier readability, the components are often referred to in the singular below. In these cases, too, what is meant is that at least one instance of the designated component is present and several instances—arranged in parallel or one after the other—may be present.
  • a refrigerant circuit includes several instances of a component (e.g.
  • a refrigerant circuit with three evaporators and two compressors
  • the instances of the respective component are usually arranged in parallel (the three evaporators arranged in parallel would therefore represent the at least one evaporator and the two compressors arranged in parallel would represent the at least one compressor).
  • the instances of the respective component are arranged in series or mixed (some instances in parallel and some instances in series).
  • a refrigerant circuit includes more than one expansion valve. Provision can thus be made for two or more expansion valves to be present, which are arranged in parallel, with at least one of them being regulated. It is also possible that all expansion valves are controlled or that they are controlled in a staggered manner depending on the desired refrigerant mass flow.
  • the object of the invention is to avoid the disadvantages described above and to specify a method for controlling an expansion valve of a refrigerant circuit that is improved compared to the prior art and a refrigerant circuit that is improved compared to the prior art.
  • the method according to the invention provides that the expansion valve is controlled as a function of a temperature difference between a heat source temperature of the heat source and the evaporation temperature of the refrigerant, which prevails in the area between the valve outlet of the expansion valve and the compressor inlet of the at least one compressor.
  • the suction gas overheating is not used as the controlled variable for controlling the expansion valve, but the temperature difference between a heat source temperature of the heat source and the evaporation temperature of the refrigerant, which prevails in the area between the valve outlet of the expansion valve and the compressor inlet of the at least one compressor, is used as the controlled variable. used. This ensures that the control system can react much more quickly.
  • the heat source temperature of the heat source can be the temperature of a heat source medium (eg air or water) of the heat source.
  • the heat source temperature can also be a temperature that is dependent on a temperature of the heat source (or its heat source medium).
  • it can be a Act surface temperature of at least one evaporator, which changes depending on the temperature of the heat source or the heat source medium (eg ambient air that is fed to the evaporator or water of a heat medium circuit that is fed to the evaporator).
  • the heat source temperature is a value that reflects the temperature of the heat source at the evaporator.
  • the heat source temperature can be, for example, the inlet or outlet temperatures (e.g. if the heat source is water that is fed to the evaporator via a separate circuit) or surface temperatures on the evaporator (e.g. if the heat source is ambient air) as well as averaged or weighted values from these.
  • the refrigerant In the area between the valve outlet and the compressor inlet, the refrigerant has essentially a constant pressure, as a result of which the evaporation temperature of the refrigerant, which is directly related to the pressure, is also essentially constant in this area.
  • the evaporation temperature of the refrigerant can be measured after the refrigerant has exited the valve outlet of the expansion valve or can be calculated from a pressure of the refrigerant at a point between the valve outlet and the compressor inlet with the help of the vapor pressure curve (also called boiling curve).
  • compressors can have different power levels or variable-power control.
  • the proposed control concept is independent of the heat source used (which acts on the evaporator) or heat sink (which refrigerant in or on the condenser extracts heat) and the refrigerant circuit can also contain other parts and components that have no significant influence on the functioning of the control strategy. Examples of this are sight glasses, collectors, filters, non-return valves, additional expansion valves, additional subcoolers, intermediate vapor injection systems or components that enable switching to reversible operation.
  • the refrigerant can exit the at least one evaporator partially evaporated, saturated or superheated.
  • the refrigerant circuit includes at least one internal heat exchanger.
  • This heat exchanger is often also referred to as a suction gas heat exchanger.
  • a condenser outlet of the at least one condenser is connected to a first internal heat exchanger inlet of the at least one internal heat exchanger and a first internal heat exchanger outlet of the at least one internal heat exchanger is connected to a valve inlet of the expansion valve.
  • the first fluid line runs between the first internal heat exchanger inlet and the first internal heat exchanger outlet.
  • An evaporator outlet of the at least one evaporator is connected to a second internal heat exchanger inlet of the at least one internal heat exchanger and a second internal heat exchanger outlet of the at least one internal heat exchanger is connected to a compressor inlet of the at least one compressor.
  • the second fluid line runs between the second internal heat exchanger inlet and the second internal heat exchanger outlet.
  • the second fluid line is materially separate from the first fluid line, but thermally coupled or connected to the first fluid line, so that heat can be released from the refrigerant flowing through the first fluid line to the refrigerant flowing through the second fluid line in a manner known per se.
  • the at least one internal heat exchanger can be designed as a tube-in-tube heat exchanger, as a plate heat exchanger, as a tube bundle heat exchanger or the like.
  • the refrigerant flows through the refrigerant circuit as follows: starting from the valve outlet of the expansion valve, the refrigerant is introduced into the evaporator, in which it evaporates completely or partially due to the effect of heat from the heat source that is thermally connected to the evaporator or acts on the evaporator becomes. After exiting the evaporator, the refrigerant flows through the second fluid line of the internal heat exchanger, in which the refrigerant is further completely evaporated and heated. After exiting the internal heat exchanger or its second fluid line, the refrigerant flows into the compressor, in which it is compressed and further heated.
  • the refrigerant flows through the condenser, in which it liquefies while releasing heat. After exiting the condenser, the refrigerant flows completely or partially through the first fluid line of the internal heat exchanger and ensures that the refrigerant flowing through the second fluid line is heated in the internal heat exchanger. After leaving the internal heat exchanger or its first fluid line, the refrigerant flows to a valve inlet of the expansion valve and after the refrigerant has left the valve outlet of the expansion valve, the cycle begins again.
  • the evaporation of the refrigerant in a tube goes through several phases, with the tube wall temperature being indirectly proportional to the heat transfer coefficient.
  • a completely liquid refrigerant so-called nucleate boiling occurs first and then film evaporation.
  • the heat transfer coefficient is generally very high high.
  • the refrigerant flow heats up, which also reduces the driving force of the heat transport (the temperature difference).
  • the position of the dryout point depends on the flow speed, geometry/orientation and heat flow density, but is usually between approx. 70% and 90% gas mass fraction.
  • the heat transfer coefficient reduces by one to two orders of magnitude compared to film evaporation.
  • the limitation of the heat transfer coefficient means that a large part of the evaporator's heat exchanger surface is required for complete evaporation after the dryout point and, above all, for superheating of the refrigerant.
  • these two process steps only contribute to a fraction of the total energy input.
  • About 80% to 90% of the heat is transferred to the refrigerant in the nucleate boiling and film evaporation region.
  • only about 5% to 15% of the heat is transferred during aerosol vaporization and less than 5% of the heat is transferred by suction gas superheat.
  • the proposed method for controlling the expansion valve enables optimal utilization of the internal heat exchanger, while at the same time the control system can be kept stable. It is possible to increase the liquid content of the refrigerant in the evaporator and move the dry-out point from the evaporator to the internal heat exchanger. The overheating process is completely relocated and parts of the evaporation process are relocated to the internal heat exchanger. As a result, the entire heat exchanger surface of the evaporator can be used for the evaporation process, which leads to an increase in the evaporation temperature (and thus to an increase in efficiency).
  • the internal heat exchanger can not only increase the temperature of the suction gas (the gaseous refrigerant when it enters the compressor), but also enable the wet vapor to be evaporated after the actual evaporator. Thus, the heat transfer in the evaporator is improved, which greatly increases the efficiency of the system.
  • the first temperature sensor can be arranged, for example, on at least one evaporator and can measure the temperature of the ambient air as the heat source medium. It is also conceivable that the first temperature sensor measures a surface temperature of the at least one evaporator, which is dependent on the temperature of the heat source medium.
  • the first temperature sensor can also be arranged in a circulation line of a heat medium circuit, via which, for example, water or an antifreeze mixture is fed into the evaporator as a heat source medium.
  • the refrigerant circuit comprises a second temperature sensor, which measures a refrigerant temperature of the refrigerant after the refrigerant has exited the valve outlet of the expansion valve and before the refrigerant has entered the at least one evaporator and reports it to the control device, with the temperature from the second Refrigerant temperature measured by the temperature sensor corresponds to the evaporation temperature.
  • the refrigerant In the area between the valve outlet and the compressor inlet, the refrigerant has essentially a constant pressure, as a result of which the evaporation temperature of the refrigerant, which is directly related to the pressure, is also essentially constant in this area.
  • the temperature of the refrigerant at the valve outlet of the expansion valve therefore reflects the evaporating temperature of the refrigerant.
  • the refrigerant has the evaporation temperature in the entire area between the valve outlet and the entry into the evaporator. Only in the evaporator and the subsequent internal heat exchanger does the temperature of the refrigerant rise above its evaporation temperature. If the second temperature sensor is arranged between the valve outlet and the at least one evaporator, then it can measure the evaporation temperature of the refrigerant directly. In other words, the refrigerant temperature measured in the area between the valve outlet and the entry into the evaporator corresponds to the evaporation temperature of the refrigerant at the pressure conditions in this area.
  • the refrigerant circuit includes a pressure sensor, with the pressure sensor measuring a refrigerant pressure of the refrigerant at a point between the valve outlet and the compressor inlet and reporting it to the control device, with the control device preferably determining the evaporation temperature from the refrigerant pressure.
  • the evaporation temperature is the temperature at which the refrigerant changes from the liquid phase to the gaseous phase.
  • the evaporation temperature depends on the pressure and can be calculated from the refrigerant pressure using the vapor pressure curve (also known as the boiling curve). be determined.
  • the proposed control is significantly faster than the conventional suction gas overheating control, since measuring the pressure, in contrast to measuring the suction gas temperature before the compressor, has no significant dead time.
  • the heat source temperature of the heat source acting on the at least one evaporator and the evaporation temperature of the refrigerant in the area between the valve outlet and the compressor inlet are determined, with an actual heat source rating being determined from the temperature difference between the heat source temperature and the evaporation temperature, the actual heat source rating being determined by Regulation of an opening width of the expansion valve of a predetermined or specifiable target heat source degree is tracked. Provision can also be made for two or more expansion valves to be present which are arranged in parallel, at least one of which is regulated. It is also possible that all expansion valves are controlled or that they are controlled in a staggered manner depending on the desired refrigerant mass flow.
  • only one of the expansion valves can be regulated up to a first predetermined or predeterminable refrigerant mass flow, with the other expansion valves initially remaining closed.
  • a further expansion valve can be regulated in order to be able to further increase the throughput of refrigerant.
  • further threshold values for the refrigerant mass flow can be predetermined or can be predetermined in order to achieve a desired staggering of the refrigerant mass flow by including further regulated expansion valves.
  • the so-called heat source gradient between the heat source temperature of the heat source and the evaporation temperature (e.g. the evaporator inlet temperature of the refrigerant after the refrigerant has exited the valve outlet of the expansion valve or determination via evaporation pressure) is used as a controlled variable.
  • the respective current actual value of the heat source rating (actual heat source rating) is determined and tracked to a specified or specifiable setpoint (target heat source rating).
  • the heat source temperature can be measured in the heat source medium or on the evaporator (e.g. a surface temperature of the evaporator, an air temperature of the ambient air in the area of the evaporator or the water temperature of water supplied to the evaporator in a heat medium circuit when it enters the evaporator or when it leaves the evaporator).
  • the evaporation temperature of the refrigerant can be measured, for example, at the evaporator inlet or can be calculated from a measured refrigerant pressure of the refrigerant before the refrigerant enters the at least one compressor.
  • the opening width of the expansion valve is changed continuously (time-continuously or time-discretely) in such a way that the actual degree of heat source matches the desired degree of heat source.
  • the opening width of the expansion valve is regulated in order to achieve and/or maintain a predefinable or predefinable desired degree of heat source.
  • the expansion valve can be a thermal valve or an electric or electronic valve, for example in the form of a stepping motor valve that changes the opening width with the help of an electromagnet.
  • the first controller can be a PID, PI, PD controller or the like.
  • the new control value for the expansion valve is generated from the comparison between the target value (target heat source rating) and the actual value (actual heat source rating).
  • the opening width of the expansion valve controls the amount of refrigerant injected into the evaporator and thus has a direct influence on the evaporation pressure.
  • the target heat source grade will be continuously adjusted.
  • the target heat source degree can be adjusted or set or specified continuously (time-continuously or time-discretely) so that on the one hand the compressor does not suffer any liquid hammer and on the other hand high suction gas temperatures upstream of the compressor are prevented.
  • control device comprises a further control device for preventing liquid refrigerant from entering the at least one compressor, with at least one measured or determined temperature of the refrigerant in the refrigerant circuit and/or at least one measured or determined pressure of the refrigerant in the refrigerant circuit being used the overheating state of the refrigerant is determined before or after the at least one compressor characterizing control actual value and the actual control value is tracked by controlling the desired heat source degree to a predetermined or predeterminable control setpoint.
  • the target heat source rating can be adjusted, for example, by determining the actual suction gas overheating of the refrigerant after the internal heat exchanger and before it enters the at least one compressor, with the target heat source rating being adjusted or set or changed depending on the actual suction gas overheating .
  • the refrigerant circuit includes a third temperature sensor, which measures the suction gas temperature of the refrigerant after the internal heat exchanger and before entry into the at least one compressor and reports it to the control device, the control device including a second control device, the control device for determining the Actual suction gas superheat calculates the difference between the suction gas temperature and the evaporation temperature, with the second control device specifying the target heat source degree on the basis of a second control deviation between target suction gas superheat and actual suction gas superheat.
  • the second control device can in turn be a PID, PI, PD controller or the like.
  • the actual suction gas superheat is therefore the difference between the suction gas temperature and the evaporation temperature.
  • the target suction gas superheat can be a fixed stored value (e.g. 5 K) or can be dynamically specified as a variable depending on the operating conditions (e.g. 5 K at low evaporation temperatures and 10 K at high evaporation temperatures).
  • the second control device determines the desired degree of heat source and reports this to the first control device. For the first controller is thus the target heat source grade reported by the second control device is the target value for the control.
  • the second control device can ensure that the difference between the suction gas temperature and the evaporation temperature (evaporator inlet temperature) is regulated to the target value for superheating (target suction gas superheating) and thereby the target value for heat source grading (target heat source grading) continuously or discontinuously is adjusted.
  • the first control device can also be referred to as an inner cascade and the second control device can be referred to as an outer cascade.
  • the basic principle of this control cascading is the division of the control system into an inner, very fast and precise control circuit (first control device) and an outer, more sluggish control circuit (second control device).
  • the internal control loop regulates the expansion valve by comparing the heat source rating (comparison of the actual heat source rating with the target heat source rating).
  • the outer control circuit adapts the target value of the heat source degree (target heat source degree) to the prevailing operating conditions by adjusting the overheating condition of the refrigerant upstream of the compressor.
  • target suction gas overheating It regulates to the desired overheating state of the gas upstream of the compressor (target suction gas overheating) and dynamically specifies the target value in the form of the target heat source degree to the inner control loop. In principle, this results in an "approach” to the optimal operating conditions and at the same time a stable control for the inner control loop, which reacts quickly to short-term changes in operation.
  • suction gas superheat control instead of or in addition to suction gas superheat control as an external cascade, other concepts that fulfill the same task (preventing liquid refrigerant from entering the compressor) can alternatively be used as actual values, e.g additional control device for controlling the hot gas overheating.
  • the hot gas overheating results from the temperature difference between the hot gas temperature (temperature at the compressor outlet) and the condensation temperature (condensing temperature of the refrigerant, which is calculated, among other things, via the pressure, measured at a point between the compressor outlet and the expansion valve inlet, using the vapor pressure curve of the refrigerant can be).
  • a high discharge gas superheat is synonymous with a high suction gas superheat.
  • the controller attempts to adjust a fixed or variable target hot gas superheat by adjusting the actual hot gas superheat.
  • the desired hot gas overheating can be made dependent on the pressure difference (condensation pressure - evaporation pressure) and the compressor speed, for example.
  • Another concept that can be used as an alternative to the suction gas overheating control is the control of the "minimum most stable signal". Only the suction gas temperature (temperature before the compressor inlet) is measured. As soon as this can no longer be kept stable, the minimum stable signal is reached. Any further increase in refrigerant flow through the expansion valve would cause liquid hammer in the compressor.
  • the outer cascade which is used to determine the target heat source rating, does not necessarily have to consist of a classic control system.
  • values for the overheating state of the refrigerant upstream of the compressor ie the actual suction gas overheating
  • the target heat source rating can be adjusted from the deviation.
  • further measured variables can optionally be implemented in the overall system (by adding further controller modules to the control device), for example to take into account the influence of various disturbance variables, such as compressor speed or capacity or subcooling temperature through a pre-control regulation.
  • various disturbance variables such as compressor speed or capacity or subcooling temperature through a pre-control regulation.
  • the supercooling temperature temperature of the refrigerant in front of the expansion valve
  • the compressor speed / compressor output or the fan speed in the form of a pilot control system (feed-forward) or a pilot control (feed-forward control) or another standard control method can also be implemented.
  • the compressor speed when the compressor speed is reduced, the refrigerant mass flow and thus the opening width of the expansion valve can be reduced.
  • this operational change is noticeable with a delay in an increase in the suction gas temperature in the outer cascade.
  • a change in the compressor speed can directly affect the setpoint of the brine grading (target brine grading).
  • target brine grading target brine grading
  • the heat source motor is the device that transports the heat source medium of the heat source and brings it into thermal contact with the refrigerant in the evaporator (e.g. a fan for air as the heat source medium or a pump for water as the heat source medium).
  • the heat source engine can generally be a turbomachine for the heat source medium of the heat source.
  • the heat source motor can be a fan that supplies the evaporator with ambient air as the heat source medium.
  • the brine motor can also be a pump that supplies water or an antifreeze mixture as the brine to the evaporator.
  • the refrigerant is only partially evaporated in the at least one evaporator, with the refrigerant being completely evaporated in the internal heat exchanger.
  • the refrigerant which is only partially evaporated in the evaporator, flows after exiting the evaporator through the second fluid line of the internal heat exchanger, in which the refrigerant is further fully evaporated and heated. This enables optimal utilization of the internal heat exchanger, while at the same time keeping the control system stable.
  • the liquid content of the refrigerant in the evaporator is increased and the dryout point is moved from the evaporator to the internal heat exchanger. Parts of the evaporation process and the overheating process are therefore completely relocated to the internal heat exchanger.
  • the internal heat exchanger should not only increase the temperature of the suction gas, but also enable evaporation of the wet steam after the actual evaporator. Thus, the heat transfer in the evaporator is improved, which greatly increases the efficiency of the system.
  • the described refrigeration circuit design with an internal heat exchanger is required, with the internal heat exchanger being designed for a comparatively high transmission capacity, in contrast to the internal heat exchangers or suction gas heat exchangers that are customary in practice should be.
  • a plate heat exchanger is preferably used for this.
  • the described control strategy is required, which ensures a stable overheating condition directly before or (alternatively) directly after the compressor. The lower the superheated state of the refrigerant, the higher the liquid fraction of the refrigerant at the evaporator outlet.
  • the refrigerant circuit comprises at least one evaporator, at least one internal heat exchanger, at least one compressor, at least one condenser, an expansion valve and a control device connected to the expansion valve in a signal-conducting manner for controlling the expansion valve, in particular according to a method according to one of claims 1 to 9, wherein a first Fluid line of the at least one internal heat exchanger is arranged between the at least one condenser and the expansion valve and a second fluid line of the at least one internal heat exchanger is arranged between the at least one evaporator and the at least one compressor, the at least one evaporator, the second fluid line, the at least a compressor, the at least one condenser, the first fluid line and the expansion valve being arranged one behind the other in series in a circulation direction of the refrigerant circuit and through which a refrigerant can flow .
  • the refrigerant circuit comprises a first temperature sensor connected to the control device in a signal-conducting manner, with a heat source temperature of a heat source acting on the at least one evaporator being able to be measured by the first temperature sensor and reported to the control device, wherein the first temperature sensor is preferably arranged in a heat source medium of the heat source or on the at least one evaporator, wherein the refrigerant circuit has a temperature determination device connected to the control device in a signal-conducting manner for determining the evaporation temperature of the refrigerant, which prevails in the area between the valve outlet of the expansion valve and the compressor inlet of the at least one compressor , Includes, wherein the control device controls an opening width of the expansion valve depending on a temperature difference between the heat source temperature and the evaporation temperature of the refrigerant in the area between the valve outlet and the compressor inlet.
  • the evaporation temperature can either be calculated using the evaporation pressure at
  • the heat source acting on the at least one evaporator can be the environment surrounding the evaporator or the air from which is supplied to the evaporator (e.g. in the case of an air heat pump).
  • a heat source is water or another fluid, which is fed to the evaporator in a manner known per se via its own heating medium circuit, which is hydraulically decoupled from the refrigerant circuit and is therefore materially separate from it, in order to heat the refrigerant of the refrigerant circuit in the evaporator .
  • the heat source is thermally connected to the evaporator, and in the evaporator, heat is supplied to the refrigerant from the heat source thermally connected to the evaporator, and the refrigerant evaporates while absorbing heat.
  • the refrigerant circuit comprises at least one internal heat exchanger, wherein heat is transferred from the refrigerant flowing through the first fluid line of the at least one internal heat exchanger to the refrigerant through the second Fluid line of at least one internal heat exchanger flowing refrigerant can be released.
  • the at least one internal heat exchanger - also referred to as a suction gas heat exchanger - can not only increase the temperature of the suction gas (the gaseous refrigerant when it enters the compressor), but also enable evaporation of the wet vapor after the actual evaporator.
  • the heat transfer in the evaporator is improved, which greatly increases the efficiency of the system.
  • the temperature determination device comprises a second temperature sensor arranged between the valve outlet and the at least one evaporator, with the second temperature sensor being able to measure the evaporation temperature and report it to the control device.
  • the second temperature sensor thus measures a refrigerant temperature of the refrigerant after the refrigerant has exited the valve outlet of the expansion valve and before the refrigerant has entered the at least one evaporator. In this range, the measured refrigerant temperature corresponds to the evaporation temperature of the refrigerant.
  • the temperature determination device comprises a pressure sensor arranged between the valve outlet and the compressor inlet, the pressure sensor being able to measure a refrigerant pressure of the refrigerant and to report it to the control device, the control device being able to determine the evaporation temperature from the refrigerant pressure.
  • control device from the temperature difference between heat source temperature and evaporation temperature determines an actual heat source degree and the actual heat source degree by controlling the opening width of the expansion valve of a predetermined or specifiable target heat source degree tracked. It is also envisaged that the control device continuously adjusts the desired heat source degree.
  • control device comprises a further control device for preventing liquid refrigerant from entering the at least one compressor, the control device being based on at least one measured or determined temperature of the refrigerant in the refrigerant circuit and/or at least one measured or determined pressure of the refrigerant in the refrigerant circuit, an actual control value characterizing the overheating state of the refrigerant before or after the at least one compressor is determined, and the actual control value is tracked by controlling the target heat source grade to a predetermined or predeterminable control setpoint.
  • control device includes a first control device that determines a valve control value in relation to the opening width on the basis of a first control deviation between the target heat source degree and the actual heat source degree and reports it to the expansion valve.
  • the expansion valve sets the opening width depending on the valve control value.
  • the expansion valve can be a thermal valve or an electric or electronic valve, e.g. in the form of a stepper motor valve that changes the opening width with the help of an electromagnet.
  • the first controller can be a PID, PI, PD controller or the like.
  • the refrigerant circuit includes a third temperature sensor, with a suction gas temperature of the refrigerant being measured by the third temperature sensor can be measured after the internal heat exchanger and before entering the at least one compressor and can be reported to the control device, the control device determining an actual suction gas overheating from a temperature difference between the suction gas temperature and the evaporation temperature, and the actual suction gas overheating by controlling the desired heat source grade to a predetermined or specifiable target -Suction gas overheating tracks.
  • control device calculates the difference between the suction gas temperature and the evaporation temperature.
  • control device includes a second control device which determines the target heat source degree on the basis of a second control deviation between the target suction gas superheat and the actual suction gas superheat and reports it to the first control device.
  • the second controller can be a PID, PI, PD controller or the like.
  • the proposed device can be, for example, a heat pump, a refrigeration system or an air conditioner.
  • figure 1 shows a schematic representation of a device 19 with a refrigerant circuit 2 according to the prior art and figure 2 shows a cycle process carried out in the refrigerant circuit 2 in a pressure-enthalpy diagram or log-ph diagram.
  • the device 19 can be, for example, a heat pump, a refrigeration system or an air conditioner.
  • the refrigerant circuit 2 comprises an evaporator 3, a compressor 4, a condenser 5, an expansion valve 1 and a control device 6, which is connected to the expansion valve 1 via a signal line 20 in a signal-conducting manner, for controlling the expansion valve 1.
  • the evaporator 3, the compressor 4, the condenser 5 and the expansion valve 1 are arranged in series in a circulation direction Z of the refrigerant circuit 2 and have a refrigerant K flowing through them, which circulates in the closed refrigerant circuit 2 in the circulation direction Z.
  • a heat source 8 acts on the evaporator 3 in a known manner and leads to an increase in the enthalpy of the refrigerant K in the evaporator 3 , so that the refrigerant K is at least partially evaporated in the evaporator 3 .
  • the heat source 8 can be ambient air that surrounds the evaporator 3 or is supplied to the evaporator 3 (for example in the case of a device in the form of an air heat pump).
  • a heat source 8 is water or another fluid, which is fed to the evaporator 3 in a manner known per se via its own heat medium circuit, which is hydraulically decoupled from the refrigerant circuit 2 and is therefore materially separate from it, in order to cool the refrigerant K of the refrigerant circuit 2 to heat in the evaporator 3.
  • the heat source 8 is thermally connected to the evaporator 3, and in the evaporator 3, heat is supplied to the refrigerant K from the heat source 8 thermally connected to the evaporator 3, and the refrigerant K evaporates while absorbing heat.
  • the heated and at least partially evaporated (i.e. gaseous) refrigerant K is compressed, whereby the refrigerant K is raised to a higher pressure and temperature level.
  • the gaseous refrigerant K is then forwarded in the direction of the condenser 5 with a correspondingly increased pressure and correspondingly increased temperature.
  • the condenser 5 (often also referred to as the condenser), the gaseous, overheated refrigerant K is cooled to a temperature at which the refrigerant K liquefies, and heat is thereby given off to a heat sink (not shown in detail) (e.g.
  • the liquefied refrigerant K passes through the expansion valve 1, which has a constriction in the Refrigerant circuit 2 represents.
  • this constriction in the form of the expansion valve 1 is passed, there is a rapid drop in pressure in the refrigerant K, since the refrigerant K can relax after passing through the expansion valve 1 .
  • the drop in pressure is also accompanied by a cooling of the refrigerant K, which is fed back to the evaporator 3 after the expansion valve 1 and the cycle described starts again with at least partial evaporation of the refrigerant K in the evaporator 3 .
  • the refrigerant K is continuously expanded in the expansion valve 1, as a result of which it partially evaporates.
  • the refrigerant K in the form of a liquid-gas mixture then flows through the evaporator 3, whereby the remaining liquid is first completely evaporated and finally overheated by 5 to 15 K (so-called suction gas overheating) before the gaseous refrigerant K reaches the compressor 4.
  • the compressor 4 increases the pressure of the gaseous refrigerant K.
  • the refrigerant K is liquefied by dissipating heat.
  • FIG figure 2 shows an example of a cycle process C in the refrigerant circuit 2 according to FIG figure 1 in the well-known log-ph diagram.
  • the specific enthalpy E energy content of the refrigerant K
  • P logarithmically scaled pressure
  • the refrigerant K is liquid, to the right of it (i.e. to the right of the dew line T) it is completely gaseous. In between, the gas content increases continuously from left to right.
  • the cycle process C is indicated by dashed lines and includes the process steps C1, C2, C3 and C4.
  • the refrigerant K initially evaporates completely at constant pressure in the evaporator 3 (process step C1). After reaching the dew line T, the then completely gaseous refrigerant K is further heated by approx. 5 to 15 K above the boiling point. This so-called suction gas overheating is necessary so that the compressor 4 does not suffers liquid shocks.
  • the pressure and temperature of the refrigerant K are increased (process step C2).
  • the refrigerant K condenses at a constant pressure while releasing heat (process step C3).
  • the pressure of the refrigerant K drops (process step C4) and the cycle process C begins again with the process step C1.
  • the expansion valve 1 is controlled in order to achieve a specified desired value for the suction gas overheating.
  • a second temperature sensor 13 and a third temperature sensor 16 are provided to determine the actual value of the suction gas overheating and are connected to the control device 6 in a signal-conducting manner.
  • the second temperature sensor 13 records the temperature of the refrigerant K before it enters the evaporator 3 and reports this temperature to the control device 6 via a second sensor line 22.
  • the third temperature sensor 16 records the temperature of the refrigerant K at the evaporator outlet before it enters the compressor 4 and reports this temperature to the control device 6 via a third sensor line 23.
  • the control device 6 determines the actual value of the suction gas overheating by measuring the temperature difference between the temperature of the refrigerant K before it enters the compressor 4 (suction gas temperature) and the evaporation temperature (e.g. measured by the temperature of the Refrigerant K before entering the evaporator 3) is calculated.
  • the expansion valve 1 is controlled via the signal line 20 in such a way that an opening width of the expansion valve 1 is adjusted so that the actual value of the suction gas overheating is regulated to the target value of the suction gas overheating.
  • a (eg electronic or thermal) expansion valve 1 can thus be used to regulate to a fixed suction gas overheating (eg 5 K).
  • the difference between the suction gas temperature and the evaporation temperature is used as the controlled variable.
  • the expansion valve 1 regulates the refrigerant mass flow and the pressure, so that the refrigerant K has a specific suction gas overheating at the compressor inlet. Too small or no suction superheat can cause compressor 4 damage. In this case, the evaporation pressure must be reduced (ie the expansion valve 1 closed). On the other hand, excessive suction gas superheat has a negative effect on the refrigeration cycle efficiency because the evaporating pressure is lower than necessary.
  • FIG figure 3 shows a device 19 according to FIG figure 1 , wherein the refrigerant circuit 2 additionally includes a heat exchanger 9 in the form of a so-called internal heat exchanger or suction gas heat exchanger and the third temperature sensor 16 is arranged between the evaporator 3 and the internal heat exchanger 9 and thus measures the suction gas temperature of the refrigerant K at the evaporator outlet.
  • a first fluid line 10 of the internal heat exchanger 9 is arranged between the condenser 5 and the expansion valve 1 and a second fluid line 11 of the internal heat exchanger 9 is arranged between the evaporator 3 and the compressor 4, with heat from the refrigerant K flowing through the first fluid line 10 can be delivered to the coolant K flowing through the second fluid line 11 .
  • a condenser outlet 24 of the condenser 5 is connected to a first internal heat exchanger inlet 25 of the internal heat exchanger 9 and a first internal heat exchanger outlet 26 of the internal heat exchanger 9 is connected to a valve inlet 27 of the expansion valve 1 .
  • the first fluid line 10 runs between the first internal heat exchanger inlet 25 and the first internal heat exchanger outlet 26.
  • An evaporator outlet 28 of the evaporator 3 is connected to a second internal heat exchanger inlet 29 of the internal heat exchanger 9 and a second internal heat exchanger outlet 30 of the internal heat exchanger 9 is connected to a compressor inlet 31 of the Compressor 4 connected.
  • the second fluid line 11 runs between the second internal heat exchanger inlet 29 and the second internal heat exchanger outlet 30.
  • the second fluid line 11 is materially separate from the first fluid line 10, however thermally coupled or connected to the first fluid line 10 so that heat can be released from the refrigerant K flowing through the first fluid line 10 to the refrigerant K flowing through the second fluid line 11 in a manner known per se.
  • the liquid refrigerant K emerging from the condenser 5 at a high temperature level is routed through the internal heat exchanger 9 and is thereby cooled by a few Kelvin. This heat is used to further heat the already fully evaporated and slightly overheated refrigerant K from the evaporator 3 .
  • the evaporation process can thus be operated with less overheating ( ⁇ 5 K) without the compressor 4 being damaged.
  • the suction gas temperature of the refrigerant K is measured with the third temperature sensor 16 between the evaporator 3 and the internal heat exchanger 9 .
  • the evaporation temperature of the refrigerant K can be measured at the inlet of the evaporator 3 using the second temperature sensor 13 .
  • the regulation of the expansion valve 1 corresponds to that of simple dry evaporation (see figure 1 ).
  • the opening width of the expansion valve 1 is therefore in turn regulated in order to maintain a specific suction gas superheat (temperature difference between the suction gas temperature and the evaporation temperature).
  • figure 4 shows an example of a cycle process C in the refrigerant circuit 2 according to FIG figure 3 in the log ph diagram.
  • process step C1 the overheating of the completely gaseous refrigerant K takes place after reaching the dew line T in the internal heat exchanger 9 (in its second fluid line 11) and accordingly in process step C3 the last cooling of the refrigerant K before the subsequent entry into the expansion valve 1 also takes place in the internal heat exchanger 9 (in its first fluid line 10).
  • FIG figure 5 shows a device 19 with an exemplary embodiment of a proposed refrigerant circuit 2.
  • the structure and connection of the expansion valve 1, evaporator 3, internal heat exchanger 9, compressor 4 and condenser 5 correspond to that in FIG figure 3 refrigerant circuit 2 shown.
  • the refrigerant circuit 2 comprises a temperature determination device 18, which is connected to the control device 6 in a signal-conducting manner, for determining an evaporator inlet temperature of the refrigerant K after the refrigerant K has exited from a valve outlet 7 of the expansion valve 1.
  • the temperature determination device 18 comprises a second temperature sensor 13 , wherein the evaporation temperature (corresponds to the evaporator inlet temperature) can be measured by the second temperature sensor 13 and can be reported to the control device 6 via a second sensor line 22 .
  • the proposed refrigerant circuit 2 also includes a first temperature sensor 12, which is connected to the control device 6 in a signal-conducting manner and is arranged in a heat source medium of the heat source 8 or on the at least one evaporator 3, with the first temperature sensor 12 receiving a heat source temperature of a heat source 8 acting on the at least one evaporator 3 can be measured and reported to the control device 6 via a first sensor line 21 .
  • the control device 6 is configured to control an opening of the expansion valve 1 depending on a temperature difference between the heat source temperature and the evaporation temperature.
  • the control device 6 determines an actual heat source degree IW from the temperature difference between the heat source temperature and the evaporation temperature and tracks the actual heat source degree IW by controlling the opening width of the expansion valve 1 to a predetermined or specifiable target heat source degree SW.
  • the control device 6 includes a first control device 15, not shown in detail here, which is configured to determine a valve control value in relation to the opening width on the basis of a first control deviation between the target heat source degree SW and the actual heat source degree IW and the expansion valve 1 via a signal line 20 to report.
  • figure 6 shows schematically the control scheme for the control of the expansion valve 1 of the refrigerant circuit 2 according to figure 5 .
  • the heat source gradient difference between the heat source temperature and the evaporation temperature
  • the first control device 15 determines a valve control value V in relation to the opening width of the expansion valve 1 and reports this via the signal line 20 to the expansion valve 1, which represents the controlled system in the control scheme.
  • a new actual heat source degree IW results from a changed opening width of the expansion valve 1, which is fed back in the control scheme to determine the first control deviation.
  • the target heat source grade SW can be specified as a fixed value (fixed stored value).
  • the actual heat source degree IW is determined by the control device 6 by calculating the temperature difference between the heat source temperature reported by the first temperature sensor 12 and the evaporator inlet temperature reported by the second temperature sensor 13 (corresponds to the evaporation temperature).
  • the target heat source degree SW should have a value of 5 K
  • the evaporation temperature should be -5 °C
  • the heat source temperature e.g. air temperature
  • the actual value of the opening width of expansion valve 1 should be 40% at the beginning of the control .
  • the actual heat source rating IW has a value of 6 K (heat source temperature minus evaporation temperature), ie the evaporation temperature could be raised by 1 K, which increases the refrigeration circuit efficiency.
  • the deviation between the setpoint heat source degree SW and the actual heat source degree IW is processed, for example in a PID controller, and a new valve control value V for the expansion valve 1 is generated therefrom.
  • the expansion valve 1 opens to 42%, for example, so that more refrigerant K flows into the evaporator 3 and the pressure and thus the evaporation temperature rise. This reduces the actual heat source rating IW to 5.8 K and a new control cycle begins.
  • figure 7 shows an example of a cycle process C in the refrigerant circuit 2 according to FIG figure 5 in the log ph diagram.
  • the internal heat exchanger 9 Since the dryout point in the proposed refrigerant circuit 2 is strongly shifted in the direction of the internal heat exchanger 9, the internal heat exchanger 9 not only increases the temperature of the suction gas, but also enables the wet vapor to be evaporated after the actual evaporator 3. Overall, this allows the refrigerant circuit to be 2 operate much more efficiently.
  • FIG figure 8 shows a device 19 with a further exemplary embodiment of a proposed refrigerant circuit 2.
  • temperature determination device 18 includes a pressure sensor 14, with pressure sensor 14 being able to measure a refrigerant pressure of refrigerant K at a point between valve outlet 7 and compressor inlet 31 and reporting this to control device 6 via a pressure sensor line 32, with control device 6 being able to determine the evaporation temperature from the refrigerant pressure is.
  • the expansion valve 1 is controlled in the same way as in the exemplary embodiment according to FIG Figures 5 and 6 .
  • FIG 9 shows a device 19 with a further embodiment of a proposed refrigerant circuit 2.
  • the refrigerant circuit 2 corresponds to the refrigerant circuit 2 of FIG figure 8 , supplemented by additional sensors and controller modules.
  • the refrigerant circuit 2 shown also includes a third temperature sensor 16, which is located between the internal heat exchanger 9 and the compressor 4 and thus measures the suction gas temperature of the refrigerant K after the internal heat exchanger 9 and before it enters the compressor 4 and reports it to the control device 6 via a third sensor line 23 .
  • the temperature determination device 18 can also include a second temperature sensor 13 for directly determining the evaporation temperature from the evaporator inlet temperature (see figure 5 ).
  • the control device 6 includes a second control device 17, not shown in detail here. To determine the actual suction gas overheating IS, the control device 6 calculates the difference between the suction gas temperature reported by the third temperature sensor 16 and the evaporation temperature determined by the temperature determination device 18, and the second control device 17 gives the basis a second control deviation between a predefined or predefinable target suction gas superheat SS and the actual suction gas superheat IS, the target heat source degree SW, which is fed to the first control device 15 as a reference variable. In other words, the actual suction gas overheating IS is tracked by controlling the setpoint heat source degree SW to a predetermined or predeterminable setpoint suction gas overheating SS.
  • figure 10 shows schematically the control scheme for the control of the expansion valve 1 of the refrigerant circuit 2 according to figure 9 .
  • the control scheme shows a 2-stage control cascade, in which the first control device 15 represents the inner cascade (inner control circuit) and the second control device 17 represents the outer cascade (outer control circuit).
  • the inner cascade corresponds to the control scheme of figure 6 .
  • the second control device 17 specifies the target heat source degree SW, which is fed to the first control device 15 as a reference variable.
  • the first control device 15 determines a valve control value V in relation to the opening width of the Expansion valve 1 and reports this via the signal line 20 to the expansion valve 1, which represents the controlled system in the inner cascade.
  • a changed opening width of the expansion valve 1 results in a new actual heat source degree IW, which is fed back in the inner cascade to determine the first control deviation.
  • a change in the opening width of the expansion valve 1 causes a changed refrigerant mass flow and thus a changed pressure and a changed temperature of the refrigerant K upon entry into the evaporator 3, which represents the controlled system of the outer cascade with the subsequent internal heat exchanger 9. After the refrigerant K has exited the internal heat exchanger 9, it has a new actual suction gas overheating IS, which is fed back in the outer cascade to determine the second control deviation.
  • the basic principle of this control cascading is the division of the control system into an inner, very fast and precise control circuit (first control device 15) and an outer, more sluggish control circuit (second control device 17).
  • the inner control loop regulates the expansion valve 1 by comparing the heat source rating (comparison of the actual heat source rating IW with the target heat source rating SW).
  • the outer control loop adjusts the target value of the heat source degree (target heat source degree SW) to the prevailing operating conditions by adjusting the overheating state of the refrigerant K upstream of the compressor 4 . It regulates to the desired superheating state of the gas upstream of the compressor 4 (target suction gas superheat SS) and dynamically specifies the target value in the form of the target heat source degree SW for the inner control loop.
  • the input setpoint value for the outer cascade in the form of the setpoint suction gas superheat SS is intended to ensure on the one hand that the compressor 4 does not suffer any liquid hammer and on the other hand high suction gas temperatures prevent before the compressor 4.
  • the setpoint suction gas superheat SS can be a permanently stored value or can be specified dynamically as a variable depending on the operating conditions.
  • FIG 11 shows a device 19 with a further embodiment of a proposed refrigerant circuit 2.
  • the refrigerant circuit 2 corresponds to the refrigerant circuit 2 of FIG figure 9 , but here the temperature determination device 18 includes a second temperature sensor 13 for direct measurement of the evaporation temperature and wherein the refrigerant circuit includes 2 additional sensors.
  • a second pressure sensor 33 for determining the pressure of the refrigerant K after it exits the compressor 4 and before it enters the expansion valve 1
  • a fourth temperature sensor 34 for determining the temperature of the refrigerant K after it exits the compressor 4 and before it enters the condenser 5 provided.
  • the signals of the second pressure sensor 33 are supplied to the control device 6 via a second pressure sensor line 35 and the signals of the fourth temperature sensor 34 are supplied via a fourth sensor line 36 .
  • the hot gas overheating can be controlled on the basis of the hot gas temperature (determined by the fourth temperature sensor 34) compared to the condensation temperature (determined from the vapor pressure curve by measuring the pressure from the second pressure sensor 33) to specify the target heat source degree.
  • the hot gas superheat control behaves similarly to the suction gas superheat control. A slight hot gas superheat leads to Liquid slugging in the compressor 3, excessive hot gas overheating to loss of efficiency.
  • the hot gas overheating is adjusted to a fixed or changeable target hot gas overheating. A changeable desired hot gas overheating can be dependent on the evaporation pressure, the condensation pressure and the compressor speed, for example.
  • figure 12 shows a device 19 according to FIG figure 11 , supplemented by an additional valuation method and additional controller modules.
  • a further sensor 37 is specifically provided for determining the output and/or speed of the compressor 4 .
  • the signals of the sensor 37 are supplied to the control device 6 via a further sensor line 38 .
  • the compared to the control scheme of figure 10 other controller blocks are in the schematic control scheme of figure 13 shown.
  • the added controller modules are a first pre-control 39 and a second pre-control 40.
  • the first pre-control 39 can take into account the temperature of the refrigerant K at the inlet to the expansion valve 1, and the second pre-control 40 can set a compressor speed and/or Compressor performance of the compressor 4 (determined by the other sensor 37) are taken into account.
  • a proposed refrigerant circuit was each shown with an evaporator, internal heat exchanger, compressor and condenser.
  • a proposed refrigerant circuit can also include more than one evaporator, internal heat exchanger, compressor or condenser.
  • a proposed refrigeration cycle includes multiple instances of a component (e.g., a refrigeration cycle with three evaporators and two compressors)
  • the instances of the respective component are typically arranged in parallel.

Claims (13)

  1. Procédé de régulation d'une soupape de détente (1) d'un circuit frigorifique (2) comprenant au moins un évaporateur (3), au moins un échangeur de chaleur interne (9), au moins un compresseur (4), au moins un condensateur (5), la soupape de détente (1) et un dispositif de régulation (6) relié par acheminement de signaux à la soupape de détente (1) pour réguler la soupape de détente (1), dans lequel une première conduite de fluide (10) de l'au moins un échangeur de chaleur interne (9) est disposée entre l'au moins un condensateur (5) et la soupape de détente (1) et une deuxième conduite de fluide (11) de l'au moins un échangeur de chaleur interne (9) est disposée entre l'au moins un évaporateur (3) et l'au moins un compresseur (4), dans lequel un agent réfrigérant (K) circule dans le circuit frigorifique (2), dans lequel l'agent réfrigérant (K) traverse, dans une direction de circulation (Z) du circuit frigorifique (2), en partant d'une sortie de soupape (7) de la soupape de détente (1), l'au moins un évaporateur (3), la deuxième conduite de fluide (11) de l'au moins un échangeur de chaleur interne (9), l'au moins un compresseur (4), l'au moins un condensateur (5), la première conduite de fluide (10) de l'au moins un échangeur de chaleur interne (9) et la soupape de détente (1), dans lequel l'agent réfrigérant (K) est évaporé au moins en partie dans l'au moins un évaporateur (3) par apport de chaleur à l'agent réfrigérant (K) par une source de chaleur (8) agissant sur l'au moins un évaporateur (3), dans lequel l'agent réfrigérant (K) circulant dans la première conduite de fluide (10) distribue de la chaleur à l'agent réfrigérant (K) circulant à travers la deuxième conduite de fluide (11) et ainsi l'enthalpie de l'agent réfrigérant (K) est augmentée avant l'entrée dans l'au moins un compresseur (4), caractérisé en ce que la soupape de détente (1) est régulée en fonction d'une différence de température entre une température de source de chaleur de la source de chaleur (8) et la température d'évaporation de l'agent réfrigérant (K), laquelle prédomine dans la zone entre la sortie de soupape (7) de la soupape de détente (1) et l'entrée de compresseur (31) de l'au moins un compresseur (4), dans lequel la température de source de chaleur, agissant sur l'au moins un évaporateur (3), de la source de chaleur (8) et la température d'évaporation de l'agent réfrigérant (K) sont déterminées dans la zone entre la sortie de soupape (7) et l'entrée de compresseur (31), dans lequel une graduation de source de chaleur réelle (IW) est déterminée à partir de la différence de température entre la température de source de chaleur et la température d'évaporation, dans lequel la graduation de source de chaleur réelle (IW) est pilotée conformément à une graduation de source de chaleur théorique (SW) spécifiée ou pouvant être spécifiée par régulation d'une largeur d'ouverture de la soupape de détente (1), dans lequel la graduation de source de chaleur théorique (SW) est adaptée en continu, dans lequel le dispositif de régulation (6) comprend un autre système de régulation pour empêcher l'entrée de réfrigérant liquide (K) dans l'au moins un compresseur (4), dans lequel une valeur réelle de régulation caractérisant l'état de surchauffe de l'agent réfrigérant (K) avant ou après l'au moins un compresseur (4) est déterminée à partir d'au moins une température mesurée ou déterminée de l'agent réfrigérant (K) dans le circuit frigorifique (2) et/ou à partir d'au moins une pression mesurée ou déterminée de l'agent réfrigérant (K) dans le circuit frigorifique (2) et la valeur réelle de régulation est pilotée conformément à une valeur théorique de régulation spécifiée ou pouvant être spécifiée par régulation de la graduation de source de chaleur théorique (SW).
  2. Procédé selon la revendication 1, caractérisé en ce que le circuit frigorifique (2) comprend un premier capteur de température (12), dans lequel le premier capteur de température (12) est disposé de préférence dans un milieu de source de chaleur de la source de chaleur (8) ou sur l'au moins un évaporateur (3), dans lequel le premier capteur de température (12) mesure la température de source de chaleur et la communique au dispositif de régulation (6).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que le circuit frigorifique (2) comprend un deuxième capteur de température (13), qui mesure une température d'agent réfrigérant de l'agent réfrigérant (K) après la sortie de l'agent réfrigérant (K) de la sortie de soupape (7) de la soupape de détente (1) et avant l'entrée de l'agent réfrigérant (K) dans l'au moins un évaporateur (3) et la communique au dispositif de régulation (6), dans lequel la température d'agent réfrigérant mesurée par le deuxième capteur de température (13) correspond à la température d'évaporation.
  4. Procédé selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le circuit frigorifique (2) comprend un capteur de pression (14), dans lequel le capteur de pression (14) mesure une pression d'agent réfrigérant de l'agent réfrigérant (K) sur un point entre la sortie de soupape (7) et l'entrée de compresseur (31) et la communique au dispositif de régulation (6), dans lequel de préférence le dispositif de régulation (6) détermine la température d'évaporation à partir de la pression d'agent réfrigérant.
  5. Procédé selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le dispositif de régulation (6) comprend un premier système de régulation (15), dans lequel le premier système de régulation (15) détermine, sur la base d'un premier écart de régulation entre la graduation de source de chaleur théorique (SW) et la graduation de source de chaleur réelle (IW), une valeur de réglage de soupape (V) et la communique à la soupape de détente (1), dans lequel la soupape de détente (1) règle la largeur d'ouverture en fonction de la valeur de réglage de soupape (V).
  6. Procédé selon l'une quelconque des revendications 1 à 5, caractérisé en ce qu'une température de gaz d'aspiration de l'agent réfrigérant (K) est déterminée après l'échangeur de chaleur interne (9) et avant l'entrée dans l'au moins un compresseur (4), dans lequel une surchauffe de gaz d'aspiration réelle (IS) est déterminée à partir d'une différence de température entre la température de gaz d'aspiration et la température d'évaporation, dans lequel la surchauffe de gaz d'aspiration réelle (IS) est pilotée conformément à une surchauffe de gaz d'aspiration théorique (SS) spécifiée ou pouvant être spécifiée par régulation de la graduation de source de chaleur théorique (SW).
  7. Procédé selon la revendication 6, caractérisé en ce que le circuit frigorifique (2) comprend un troisième capteur de température (16), qui mesure la température de gaz d'aspiration de l'agent réfrigérant (K) après l'échangeur de chaleur interne (9) et avant l'entrée dans l'au moins un compresseur (4) et la communique au dispositif de régulation (6), dans lequel le dispositif de régulation (6) comprend un deuxième système de régulation (17), dans lequel le dispositif de régulation (6) calcule, pour déterminer la surchauffe de gaz d'aspiration réelle (IS), la différence entre la température de gaz d'aspiration et la température d'évaporation, dans lequel le deuxième système de régulation (17) spécifie la graduation de source de chaleur théorique (SW) sur la base d'un deuxième écart de régulation entre la surchauffe de gaz d'aspiration théorique (SS) et la surchauffe de gaz d'aspiration réelle (IS).
  8. Procédé selon l'une quelconque des revendications 1 à 7, caractérisé en ce que la graduation de source de chaleur théorique (SW) spécifiée ou pouvant être spécifiée est modifiée d'au moins une valeur de modification, dans lequel l'au moins une valeur de modification est déterminée en fonction d'une température de l'agent réfrigérant (K) avant la soupape de détente (1) et/ou d'une vitesse de rotation de compresseur de l'au moins un compresseur (4) et/ou d'une puissance de compresseur de l'au moins un compresseur (4) et/ou d'une vitesse de rotation de moteur de source de chaleur d'un moteur de source de chaleur.
  9. Procédé selon l'une quelconque des revendications 1 à 8, caractérisé en ce que l'agent réfrigérant (K) est évaporé seulement en partie dans l'au moins un évaporateur (3), dans lequel l'agent réfrigérant (K) est évaporé en totalité dans l'échangeur de chaleur interne (9).
  10. Circuit frigorifique (2) comprenant au moins un évaporateur (3), au moins un échangeur de chaleur interne (9), au moins un compresseur (4), au moins un condensateur (5), une soupape de détente (1) et un dispositif de régulation (6) relié par acheminement de signaux à la soupape de détente (1) pour réguler la soupape de détente (1), en particulier selon un procédé selon l'une quelconque des revendications 1 à 9, dans lequel une première conduite de fluide (10) de l'au moins un échangeur de chaleur interne (9) est disposée entre l'au moins un condensateur (5) et la soupape de détente (1) et une deuxième conduite de fluide (11) de l'au moins un échangeur de chaleur interne (9) est disposée entre l'au moins un évaporateur (3) et l'au moins un compresseur (4), dans lequel l'au moins un évaporateur (3), la deuxième conduite de fluide (11), l'au moins un compresseur (4), l'au moins un condensateur (5), la première conduite de fluide (10) et la soupape de détente (1) sont disposés en série les uns derrière les autres dans une direction de circulation (Z) du circuit frigorifique (2) et peuvent être traversés par un agent réfrigérant (K), caractérisé en ce que le circuit frigorifique (2) comprend un premier capteur de température (12) relié par acheminement de signaux au dispositif de régulation (6), dans lequel une température de source de chaleur d'une source de chaleur (8) agissant sur l'au moins un évaporateur (3) peut être mesurée par le premier capteur de température (12) et peut être communiquée au dispositif de régulation (6), dans lequel le premier capteur de température (12) est disposé de préférence dans un milieu de source de chaleur de la source de chaleur (8) ou sur l'au moins un évaporateur (3), dans lequel le circuit frigorifique (2) comprend un dispositif de détermination de température (18) relié par acheminement de signaux au dispositif de régulation (6) pour déterminer la température d'évaporation de l'agent réfrigérant (K), laquelle prédomine dans la zone entre la sortie de soupape (7) de la soupape de détente (1) et l'entrée de compresseur (31) de l'au moins un compresseur (4), dans lequel le dispositif de détermination de température (18) comprend un deuxième capteur de température (13) disposé entre la sortie de soupape (7) et l'au moins un évaporateur (3), dans lequel la température d'évaporation peut être mesurée par la deuxième capteur de température (13) et peut être communiquée au dispositif de régulation (6), et/ou le dispositif de détermination de température (18) comprend un capteur de pression (14) disposé entre la sortie de soupape (7) et l'entrée de compresseur (31), dans lequel une pression d'agent réfrigérant de l'agent réfrigérant (K) peut être mesurée par le capteur de pression (14) et peut être communiquée au dispositif de régulation (6), dans lequel la température d'évaporation peut être déterminée à partir de la pression d'agent réfrigérant par le dispositif de régulation (6), dans lequel le dispositif de régulation (6) régule une largeur d'ouverture de la soupape de détente (1) en fonction d'une différence de température entre la température de source de chaleur et la température d'évaporation de l'agent réfrigérant (K) dans la zone entre la sortie de soupape (7) et l'entrée de compresseur (31), dans lequel le dispositif de régulation (6) détermine une graduation de source de chaleur réelle (IW) à partir de la différence de température entre la température de source de chaleur et la température d'évaporation et la graduation de source de chaleur réelle (IW) est pilotée conformément à une graduation de source de chaleur théorique (SW) spécifiée ou pouvant être spécifiée par régulation de la largeur d'ouverture de la soupape de détente (1), dans lequel le dispositif de régulation (6) comprend un premier système de régulation (15), qui détermine une valeur de réglage de soupape (V) par rapport à la largeur d'ouverture sur la base d'un premier écart de régulation entre la graduation de source de chaleur théorique (SW) et la graduation de source de chaleur réelle (IW) et la communique à la soupape de détente (1), dans lequel le dispositif de régulation (6) adapte en continu la graduation de source de chaleur théorique (SW), dans lequel le dispositif de régulation (6) comprend un autre système de régulation pour empêcher l'entrée d'un agent réfrigérant liquide (K) dans l'au moins un compresseur (4), dans lequel le dispositif de régulation (6) détermine, à partir d'au moins une température mesurée ou déterminée de l'agent réfrigérant (K) dans le circuit frigorifique (2) et/ou à partir d'au moins une pression mesurée ou déterminée de l'agent réfrigérant (K) dans le circuit réfrigérant (2), une valeur réelle de régulation caractérisant l'état de surchauffe de l'agent réfrigérant (K) avant ou après l'au moins un compresseur (4) et pilote la valeur réelle de régulation par régulation de la graduation de source de chaleur théorique (SW) conformément à une valeur de régulation spécifiée ou pouvant être spécifiée.
  11. Circuit frigorifique selon la revendication 10, caractérisé en ce que le circuit frigorifique (2) comprend un troisième capteur de température (16), dans lequel une température de gaz d'aspiration de l'agent réfrigérant (K) peut être mesurée après l'échangeur de chaleur interne (9) et avant l'entrée dans l'au moins un compresseur (4) par le troisième capteur de température (16) et peut être communiquée au dispositif de régulation (6), dans lequel le dispositif de régulation (6) détermine, à partir d'une différence de température entre la température de gaz d'aspiration et la température d'évaporation, une surchauffe de gaz d'aspiration réelle (IS) et pilote la surchauffe de gaz d'aspiration réelle (IS) par régulation de la graduation de source de chaleur théorique (SW) conformément à une surchauffe de gaz d'aspiration théorique (SS) spécifiée ou pouvant être spécifiée.
  12. Circuit frigorifique selon la revendication 11, caractérisé en ce que le dispositif de régulation (6) comprend un deuxième système de régulation (17), qui détermine, sur la base d'un deuxième écart de régulation entre la surchauffe de gaz d'aspiration théorique (SS) et la surchauffe de gaz d'aspiration réelle (IS), la graduation de source de chaleur théorique (SW) et la communique au premier système de régulation (15).
  13. Dispositif (19), en particulier pompe à chaleur ou installation de refroidissement ou appareil de climatisation, avec au moins un circuit frigorifique (2) selon l'une quelconque des revendications 10 à 12.
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IT202100018296A1 (it) * 2021-07-12 2023-01-12 Irinox S P A Macchina frigorifera per prodotti alimentari
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