EP2468944B1 - Haushaltswäschetrockner mit Wärmepumpe - Google Patents

Haushaltswäschetrockner mit Wärmepumpe Download PDF

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Publication number
EP2468944B1
EP2468944B1 EP10197041.6A EP10197041A EP2468944B1 EP 2468944 B1 EP2468944 B1 EP 2468944B1 EP 10197041 A EP10197041 A EP 10197041A EP 2468944 B1 EP2468944 B1 EP 2468944B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
temperature
pressure
outlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10197041.6A
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English (en)
French (fr)
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EP2468944A1 (de
Inventor
Alberto Bison
Francesco Cavarretta
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Electrolux Home Products Corp NV
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Electrolux Home Products Corp NV
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Filing date
Publication date
Priority to EP10197041.6A priority Critical patent/EP2468944B1/de
Application filed by Electrolux Home Products Corp NV filed Critical Electrolux Home Products Corp NV
Priority to US13/997,907 priority patent/US20140082960A1/en
Priority to BR112013016443A priority patent/BR112013016443A2/pt
Priority to PCT/EP2011/073604 priority patent/WO2012089585A1/en
Priority to RU2013135232/12A priority patent/RU2013135232A/ru
Priority to AU2011351627A priority patent/AU2011351627A1/en
Priority to CN2011800665546A priority patent/CN103348056A/zh
Publication of EP2468944A1 publication Critical patent/EP2468944A1/de
Application granted granted Critical
Publication of EP2468944B1 publication Critical patent/EP2468944B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/206—Heat pump arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • 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
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/2103—Temperatures near a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet 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
    • F25B2700/21—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
    • 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

Definitions

  • the present invention relates to a home laundry dryer.
  • the present invention relates to a rotary-drum, heat-pump type, home laundry dryer, to which the following description refers purely by way of example without implying any loss of generality.
  • today's rotary-drum home laundry dryers comprise: a substantially parallelepiped-shaped outer boxlike casing structured for resting on the floor; a substantially cylindrical, hollow revolving drum structured for internally housing the laundry to be dried, and which is housed in axially rotating manner inside the casing to rotate about its horizontally-oriented longitudinal axis, directly facing a laundry loading/unloading through opening realized in the front wall of the casing; a door hinged to the front wall of the casing to rotate to and from a closing position in which the door rests completely against the front wall of the casing to close the laundry loading/unloading opening and airtight seal the revolving drum; and an electrically-powered motor assembly structured for driving into rotation the revolving drum about its longitudinal axis inside the casing.
  • Rotary-drum home laundry dryers of the above type are also provided with a closed-circuit, hot-air generator which is designed to circulate inside the revolving drum a stream of hot air having a low moisture content, and which flows through the revolving drum and over the laundry inside the drum to rapidly dry said laundry; and with an electronic central control unit which controls both the motor assembly and the hot-air generator to perform one of the user-selectable drying cycles stored in the same central control unit.
  • the closed-circuit, hot-air generator comprises an air recirculating conduit having its two ends connected to the revolving drum, on opposite sides of the latter; an electric centrifugal fan located along the air recirculating conduit to produce, inside the latter, an airflow which flows through the revolving drum; and finally a heat-pump assembly having its two heat exchangers located one after the other, along the air recirculating conduit.
  • the heat-pump assembly comprises a first air/refrigerant heat exchanger which provides for rapidly cooling the airflow arriving from the revolving drum to condense and restrain the surplus moisture in the airflow; a second air/refrigerant heat exchanger which provides for rapidly heating the airflow arriving from the first heat exchanger and directed back to the revolving drum, so that the airflow re-entering into the revolving drum is heated rapidly to a temperature higher than or equal to that of the airflow coming out of the drum; and an electrically-powered refrigerant compressing device which is interposed between the refrigerant-outlet of the first air/refrigerant heat exchanger and the refrigerant-inlet of the second air/refrigerant heat exchanger, and it is structured to continuously compress the gaseous-state refrigerant directed towards the second heat exchanger so that refrigerant pressure and temperature are much higher at the refrigerant-inlet of the second heat exchanger than at the refrigerant-out
  • the first air/refrigerant heat exchanger is traditionally called “evaporator”, and it is structured so that the airflow arriving from the revolving drum and the low-pressure and low-temperature refrigerant directed to the suction of the refrigerant compressing device can flow through it simultaneously, allowing the refrigerant having a temperature lower than that of the airflow, to absorb heat from the airflow, thus causing condensation of the surplus moisture in the airflow arriving from the revolving drum;
  • the second air/refrigerant heat exchanger is traditionally called “condenser”, and it is structured so that the airflow directed back into the revolving drum and the high-pressure and high-temperature refrigerant arriving from the delivery of the refrigerant compressing device can flow through it simultaneously, allowing the refrigerant having a temperature greater than that of the airflow to release heat to the airflow, thus rapidly heating the airflow directed back into the drum.
  • the heat-pump assembly is provided with a refrigerant expansion device which is interposed between the refrigerant-outlet of the condenser and the refrigerant-inlet of the evaporator, and it is structured so as to cause a rapid expansion of the refrigerant directed towards the evaporator so that refrigerant pressure and temperature are much higher at the refrigerant-outlet of the condenser than at the refrigerant-inlet of the evaporator.
  • US 2005/198852 discloses a drying machine provided with a housing chamber which houses the matter to be dried, and executing a drying operation of the matter to be dried in the housing chamber comprises: a gas cooler; an evaporator; a blower fan; an air circulation path for discharging air heated by the gas cooler into the housing chamber by the blower fan, sending the air passed through the housing chamber into the evaporator, and circulating the air in the gas cooler; and a closable outside air introduction port for mixing outside air with the air circulating in the air circulation path.
  • EP 1 983 095 discloses a dryer with a controller, and a drum for accommodating clothes to be dried.
  • a process circuit conducts heated process air through the drum for cooling the process air for dewatering and for reheating the process air.
  • a heat pump circuit conducts a medium e.g. liquid medium, through a condenser, a throttle, an evaporator and a compressor. The process air is heatable by the condenser and coolable by the evaporator.
  • a heater is arranged in the heat pump circuit between the evaporator and the compressor.
  • the air dehumidification is very low at beginning of the drying cycle (low moist quantity extracted from the air) and it increases as the drying cycle proceeds, thus it takes a lot of time to the heat-pump assembly to reach the steady-state full-power working condition in which the temperature of the airflow circulating into the revolving drum reaches the highest value and remains substantially constant to said highest value.
  • a second problem correlated to the use of a heat-pump type hot-air generators is the intrinsically unbalanced energy balance between the heat absorbed from the airflow in the evaporator, i.e. in the first air/ refrigerant heat exchanger, and the heat supplied to the airflow in the condenser, i.e. in the second air/ refrigerant heat exchanger, when the hot-air generator is in the steady-state full-power working condition.
  • the air flowing along the air recirculating conduit of the hot-air generator should give off and absorb approximately the same quantity of heat to return at the same temperature as when coming out of revolving drum.
  • the air/refrigerant heat exchange in the condenser i.e. in the second heat exchanger
  • the refrigerant circulates in close loop also in the evaporator, i.e. in the first heat exchanger
  • the reduced air/refrigerant heat exchange capacity leads to a consequent limitation of the air cooling capacity of the refrigerant in the evaporator, where much more energy could be exchanged due to the dehumidification process.
  • the latent condensation heat of the water, i.e. of the moisture in fact is very high.
  • Another applicant solution envisages the use of a third air/refrigerant heat exchanger in series to the second air/refrigerant heat exchanger, i.e. to the condenser, immediately downstream the latter.
  • This third air/refrigerant heat exchanger is cooled by a cold airflow that an auxiliary electric fan draws from the outside of the laundry dryer, so as to slightly cool down the high-temperature and high-pressure refrigerant directed towards the refrigerant expansion device.
  • This second solution significantly increases the air/refrigerant heat exchange capacity at high-pressure side of heat-pump assembly and, as a consequence, significantly increases the available air cooling capacity of the refrigerant in the first heat exchanger, i.e. in the evaporator.
  • the main drawback of this second solution is that the air cooling capacity of the refrigerant in the evaporator, i.e. in the first air/refrigerant heat exchanger, is strictly limited by the fact that the refrigerant must be completely vaporized, i.e. completely in gaseous state, at suction of refrigerant compressing device, and the use of the third air/refrigerant heat exchanger may cause the refrigerant to be still partially in liquid state when coming out of the evaporator, i.e. of the first air/refrigerant heat exchanger, directed to the suction of the refrigerant compressing device, with all problems concerned.
  • the heat absorbed from the airflow arriving from the revolving drum is not enough to completely vaporize the refrigerant flowing along the evaporator.
  • an excessive cooling of the refrigerant at the high-pressure side of the heat-pump assembly can deteriorate the refrigerant "vapor quality" at suction of the refrigerant compressing device, up to irreparably damage the structural integrity of the refrigerant compressing device.
  • a third air/refrigerant heat exchanger that cools down the refrigerant too much, may cause the refrigerant "vapor quality" at suction of the refrigerant compressing device to be below 1.
  • the refrigerant "vapor quality" at suction of the refrigerant compressing device in fact, is the ratio, determined at suction of the refrigerant compressing device, between the amount of refrigerant in gaseous state and the total amount of refrigerant (i.e. both in liquid and gaseous state).
  • a "vapor quality” equal to 1 means that all refrigerant is in gaseous state (saturated vapor refrigerant or superheated refrigerant), whereas a "vapor quality” equal to 0 means that all refrigerant is in liquid state (saturated liquid refrigerant or sub-cooled refrigerant).
  • Aim of the present invention is to improve efficiency and performances of the heat-pump type, hot-air generator of today's rotary-drum home laundry dryers, and to eliminate the drawbacks referred above.
  • a home laundry dryer comprising an outer boxlike casing structured for resting on the floor and, inside the casing, a laundry container structured for housing the laundry to be dried, and a closed-circuit, hot-air generator structured to circulate, through the laundry container, a stream of hot air;
  • the hot-air generator in turn comprising: an air recirculating conduit having its two ends connected to the laundry container; air circulating means structured to produce, inside the air recirculating conduit, an airflow which flows through said laundry container; and a heat-pump assembly structured to cool the airflow coming out from the laundry container for condensing the moisture in said airflow, and then to heat the airflow returning back into the laundry container;
  • said heat-pump assembly comprising: a first air/refrigerant heat exchanger which is located along the air recirculating conduit, and it is structured for transferring heat from the airflow arriving from the laundry container to the refrigerant so as to condense the moisture in the airflow;
  • the said at least one physical quantity is the temperature and/or pressure of the refrigerant at refrigerant-inlet or at refrigerant-outlet of said first air/refrigerant heat exchanger; and/or the temperature rise or drop of the refrigerant flowing through said first air/refrigerant heat exchanger.
  • said at least one physical quantity is the temperature and/or pressure of the refrigerant at low-pressure refrigerant inlet or at low-pressure refrigerant outlet of the low-pressure side of said refrigerant/ refrigerant heat exchanger; and/or the temperature and/or pressure of the refrigerant at high-pressure refrigerant inlet or at high-pressure refrigerant outlet of the high-pressure side of said refrigerant/refrigerant heat exchanger; and/or the temperature rise of the refrigerant flowing through the low-pressure side of said refrigerant/refrigerant heat exchanger; and/or the temperature drop of the refrigerant flowing through the high-pressure side of said refrigerant/refrigerant heat exchanger.
  • said at least one physical quantity is the temperature and/or pressure of the refrigerant at suction and/or at delivery of said refrigerant compressing device.
  • said at least one physical quantity is the temperature and/or pressure of the refrigerant at refrigerant inlet or at refrigerant outlet of said second air/refrigerant heat exchanger.
  • said at least one physical quantity is the temperature and/or moisture degree of the airflow entering into, or coming out of, said laundry container.
  • the central control unit is structured for controlling said refrigerant vapor-quality adjusting means so as to selectively keep said ratio below or equal to 1.
  • the central control unit is structured for controlling said refrigerant vapor-quality adjusting means so as to maintain between 0,80 and 0,99 the ratio, at refrigerant-outlet of said first heat exchanger, between the amount of refrigerant in gaseous state and the whole amount of refrigerant.
  • the refrigerant vapor-quality adjusting means comprise high-pressure refrigerant cooling means which are structured for selectively cooling down the high-pressure refrigerant flowing from the second heat exchanger to the refrigerant expansion device.
  • said high-pressure refrigerant cooling means comprise a third air/refrigerant heat exchanger which is connected in series to the second air/ refrigerant heat exchanger.
  • said high-pressure refrigerant cooling means additionally comprise an auxiliary ventilation device which is structured for channeling a stream of cooling air towards the body of said third air/refrigerant heat exchanger.
  • the refrigerant vapor-quality adjusting means comprise refrigerant flow-rate adjusting means which are structured for varying the flow-rate of the low-pressure refrigerant flowing through the first air/refrigerant heat exchanger.
  • said refrigerant flow-rate adjusting means comprise a variable speed refrigerant compressing device, or an electrically-operated refrigerant expansion valve, or an electrically-operated multiple capillary-tube expansion system.
  • said detecting means comprise sensor means structured for detecting the temperature and/or pressure of the refrigerant at low-pressure refrigerant inlet of said refrigerant/refrigerant heat exchanger, and/or at low-pressure refrigerant outlet of said refrigerant/ refrigerant heat exchanger, and/or at high-pressure refrigerant inlet of said refrigerant/refrigerant heat exchanger, and/or at high-pressure refrigerant outlet of said refrigerant/refrigerant heat exchanger.
  • an operating method of a laundry dryer that comprises an outer boxlike casing structured for resting on the floor and, inside the casing, a laundry container structured for housing the laundry to be dried, and a closed-circuit, hot-air generator structured to circulate through the laundry container a stream of hot air; the hot-air generator being provided with a heat-pump assembly structured to cool the airflow coming out from the laundry container for condensing the moisture in said airflow, and then to heat the airflow returning back into the laundry container; said heat-pump assembly comprising: a first air/refrigerant heat exchanger which is structured for transferring heat from the airflow arriving from the laundry container to a low-pressure refrigerant so as to condense the moisture in the airflow; a second air/refrigerant heat exchanger which is structured for transferring heat from a high-pressure refrigerant to the airflow directed back into the laundry container so as to heat said airflow; wherein the operating method comprises the steps of
  • said refrigerant vapor-quality adjusting means are controlled so as to selectively maintain below or equal to 1 the ratio between the amount of refrigerant in gaseous state and the whole amount of refrigerant.
  • said refrigerant vapor-quality adjusting means are controlled so as to selectively maintain between 0,80 and 0,99 the ratio, at refrigerant-outlet of said first heat exchanger, between the amount of refrigerant in gaseous state and the whole amount of refrigerant.
  • At least one physical quantity is the temperature and/or pressure of the refrigerant at refrigerant-inlet or at refrigerant-outlet of said first air/refrigerant heat exchanger; and/or the temperature rise or drop of the refrigerant flowing through said first air/refrigerant heat exchanger.
  • said at least one physical quantity is the temperature and/or pressure of the refrigerant at low-pressure refrigerant inlet or at low-pressure refrigerant outlet of the low-pressure side of said refrigerant/refrigerant heat exchanger; and/or the temperature and/or pressure of the refrigerant at high-pressure refrigerant inlet or at high-pressure refrigerant outlet of the high-pressure side of said refrigerant/refrigerant heat exchanger; and/or the temperature rise of the refrigerant flowing through the low-pressure side of said refrigerant/refrigerant heat exchanger; and/or the temperature drop of the refrigerant flowing through the high-pressure side of said refrigerant/refrigerant heat exchanger.
  • said at least one physical quantity is the temperature and/or pressure of the refrigerant at suction and/or at delivery of said refrigerant compressing device.
  • said at least one physical quantity is the temperature and/or pressure of the refrigerant at refrigerant inlet or at refrigerant outlet of said second air/refrigerant heat exchanger.
  • said at least one physical quantity is the temperature and/or moisture degree of the airflow entering into, or coming out of, said laundry container.
  • the step of measuring the current value of said at least one physical quantity comprises the steps of measuring the current pressure and temperature of the refrigerant at refrigerant-outlet of the first heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of calculating the saturation temperature of the refrigerant on the basis of the current refrigerant pressure, and the step of driving said refrigerant vapor-quality adjusting means so as to keep the temperature of the refrigerant at refrigerant-outlet of said first heat exchanger within a predetermined first temperature range located beneath said refrigerant saturation temperature.
  • the step of driving said refrigerant vapor-quality adjusting means comprises the step of either
  • the step of measuring the current value of said at least one physical quantity comprises the steps of measuring the current pressure and temperature of the refrigerant at low-pressure refrigerant outlet of the auxiliary refrigerant/ refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of calculating the saturation temperature of the refrigerant on the basis of the current refrigerant pressure, and the step of driving said refrigerant vapor-quality adjusting means so as to keep the temperature of the refrigerant at low-pressure refrigerant outlet of the auxiliary refrigerant/ refrigerant heat exchanger within a predetermined second temperature range located above said refrigerant saturation temperature.
  • the step of driving said refrigerant vapor-quality adjusting means comprises the step of either
  • the step of measuring the current value of said at least one physical quantity comprises the steps of measuring the temperature rise of the refrigerant flowing through the low-pressure side of said refrigerant/refrigerant heat exchanger, and of measuring the temperature drop of the refrigerant flowing through the high-pressure side of said refrigerant/ refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the difference between the temperature rise of the refrigerant flowing in the low-pressure side of the refrigerant/refrigerant heat exchanger and the temperature drop of the refrigerant flowing in the high-pressure side of the refrigerant/refrigerant heat exchanger, within a predetermined third temperature range.
  • the step of driving said refrigerant vapor-quality adjusting means comprises the step of either
  • the step of driving said refrigerant vapor-quality adjusting means also comprises the step of increasing the ratio between the amount of refrigerant in gaseous state and the whole amount of refrigerant, when the temperature rise of the refrigerant in the low-pressure side of said refrigerant/ refrigerant heat exchanger goes below a predetermined third tolerance value greater than zero.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the temperature rise or drop of the refrigerant flowing through the first air/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the temperature rise or drop of the refrigerant flowing through said first air/refrigerant heat exchanger within a predetermined narrow fourth temperature range immediately above 0°C.
  • said fourth temperature range is included among 0°C and 5°C.
  • the step of driving said refrigerant vapor-quality adjusting means comprises the step of either
  • the step of measuring the current value of said at least one physical quantity comprises also the step of measuring the temperature drop of the refrigerant flowing through the high-pressure side of said refrigerant/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to also keep the temperature drop of the refrigerant flowing through the high-pressure side of the refrigerant/refrigerant heat exchanger within a fifth temperature range whose upper and lower ends are both higher than 0°C.
  • the step of driving said refrigerant vapor-quality adjusting means comprises the step of either
  • the step of measuring the current value of said at least one physical quantity comprises also the step of measuring the temperature rise of the refrigerant flowing through the low-pressure side of said refrigerant/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to also keep the temperature rise of the refrigerant flowing through the low-pressure side of the refrigerant/refrigerant heat exchanger within a sixth temperature range whose upper and lower ends are located above that of said fourth temperature range.
  • the step of driving said refrigerant vapor-quality adjusting means comprises the step of either
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the temperature drop of the refrigerant flowing through the high-pressure side of said refrigerant/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the temperature drop of the refrigerant flowing through the high-pressure side of the refrigerant/refrigerant heat exchanger within a seventh temperature range whose upper and lower ends are both higher than 0°C.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the temperature rise of the refrigerant flowing through the low-pressure side of said refrigerant/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the temperature rise of the refrigerant flowing through the low-pressure side of the refrigerant/refrigerant heat exchanger within a eighth temperature range whose upper and lower ends are both higher than 0°C.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the refrigerant temperature at low-pressure refrigerant outlet of the refrigerant/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the refrigerant temperature at low-pressure refrigerant outlet of said refrigerant/refrigerant heat exchanger within a predetermined ninth temperature range.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the refrigerant temperature at refrigerant inlet of the second air/ refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the refrigerant temperature at refrigerant inlet of said second air/ refrigerant heat exchanger within a predetermined tenth temperature range.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the refrigerant temperature at delivery of the refrigerant compressing device; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the refrigerant temperature at delivery of said refrigerant compressing device within a predetermined tenth temperature range.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the refrigerant temperature at high-pressure refrigerant inlet of the refrigerant/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the refrigerant temperature at high-pressure refrigerant inlet of said refrigerant/ refrigerant heat exchanger within a predetermined eleventh temperature range.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the refrigerant temperature at high-pressure refrigerant outlet of the refrigerant/refrigerant heat exchanger; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the refrigerant temperature at high-pressure refrigerant outlet of said refrigerant/ refrigerant heat exchanger within a predetermined twelfth temperature range.
  • the step of measuring the current value of said at least one physical quantity comprises the step of measuring the temperature of the airflow entering into the laundry container; and in that the step of controlling said refrigerant vapor-quality adjusting means comprises the step of driving said refrigerant vapor-quality adjusting means so as to keep the temperature of said airflow within a predetermined thirteenth temperature range.
  • number 1 indicates as a whole a heat-pump type, home laundry dryer which comprises:
  • heat-pump type, closed-circuit hot-air generator 5 provides for gradually drawing air from laundry container 3; extracting and retaining the surplus moisture from the hot air drawn from laundry container 3; heating the dehumidified air to a predetermined temperature, normally higher than or equal to the temperature of the air arriving from laundry container 3; and feeding the heated, dehumidified air back into laundry container 3, where it flows over, to rapidly dry, the laundry inside the container.
  • Hot-air generator 5 therefore, provides for continuously dehumidifying and heating the air circulating inside laundry container 3 to rapidly dry the laundry inside the container.
  • laundry dryer 1 is preferably a rotary-drum, heat-pump type, home laundry dryer, therefore laundry container 3 consists in a substantially cylindrical, hollow revolving drum 3 which is structured for internally housing the laundry to be dried, and which is fixed in axially rotating manner inside the outer casing 2, directly facing the laundry loading/unloading through opening 2a formed in the front wall of casing 2.
  • the rotary-drum home laundry dryer 1 additionally comprises an electrically-powered motor assembly 6 which is structured for driving into rotation the revolving drum 3 about its longitudinal axis; and an electronic central control unit 7 which controls both the electrically-powered motor assembly 6 and the hot-air generator 5 to perform one of the user-selectable drying cycles preferably, though not necessarily, stored in the same central control unit.
  • the revolving drum 3 preferably, thought not necessarily, extends inside casing 2 coaxial to a substantially horizontally-oriented longitudinal axis L, and preferably, thought not necessarily, consists of a substantially cylindrical, rigid tubular body 3 which rests substantially horizontally inside the casing 2 on a number of substantially horizontally-oriented supporting rollers 8 which are located at both axial ends of tubular body 3, and are fixed to the casing 2 in free revolving manner so as to allow the tubular body 3 to freely rotate inside the casing about its horizontally-oriented longitudinal axis L.
  • Front rim of tubular body 3 is coupled in substantially airtight manner and in axially rotating manner to the front wall of the outer casing 2, so as to surround the laundry loading/unloading opening 2a present on that wall; whereas rear rim of tubular body 3 is preferably, thought not necessarily, coupled in substantially airtight manner and in axially rotating manner to an inner bulkhead parallel and spaced to the rear wall of the outer casing 2.
  • closed-circuit hot-air generator 5 comprises:
  • the bulkhead portion aligned to the rear rim of tubular body 3 is perforated, or at any rate permeable to air, so to permit air entry into the rear rim of tubular body 3, and a first end of the air recirculating conduit 9 is coupled in airtight manner directly to the perforated portion of the inner bulkhead.
  • the second end of air recirculating conduit 9, instead, is integrated into porthole door 4, and is faced to the front rim of tubular body 3 when door 4 is placed in the closing position.
  • Centrifugal fan 10 is designed to produce an airflow f which flows, along air recirculating conduit 9, from the door 4 to the perforated portion of the inner bulkhead of casing 2.
  • hot-air generator 5 is also provided with a manually-removable filtering device 12 which is located along air recirculating conduit 9, upstream of the heat-pump assembly 11 and preferably also of centrifugal fan 10, and which is structured to stop fluff and/or lint particles upstream of heat-pump assembly 11 or even centrifugal fan 10.
  • the heat-pump assembly 11 instead comprises:
  • the air/refrigerant heat exchanger 13 is conventionally referred to as the "evaporator” or the “gas heater” (the latter in case the refrigerant operates at supercritical pressure) of the heat-pump assembly, and it is structured so that the airflow f arriving from revolving drum 3 and the low-pressure and low-temperature refrigerant directed to the suction of the refrigerant compressing device 15 can flow through it simultaneously, allowing the refrigerant having a temperature lower than that of the airflow f, to absorb heat from the airflow f, thus causing condensation of the surplus moisture in the airflow f arriving from revolving drum 3.
  • the air/refrigerant heat exchanger 14 is conventionally referred to as the "condenser” or “gas cooler” (the latter in case the refrigerant operates at supercritical pressure) of the heat-pump assembly, and it is structured so that the airflow f directed back into revolving drum 3 and the high-pressure and high-temperature refrigerant arriving from the delivery of the refrigerant compressing device 15 can flow through it simultaneously, allowing the refrigerant having a temperature greater than that of the airflow f to release heat to the airflow f, thus rapidly heating the airflow f directed back into the revolving drum 3.
  • the heat-pump assembly 11 moreover comprises:
  • internal heat exchanger 18 is preferably crossed, at the same time, by the high-pressure and high-temperature refrigerant directed towards the refrigerant expansion valve 16, and by the low-pressure and low-temperature refrigerant coming out of the refrigerant-outlet of heat exchanger 13 directed to the suction of refrigerant compressing device 15, and it is structured for transferring heat from the high-pressure and high-temperature refrigerant to the low-pressure and low-temperature refrigerant, so to heat up the low-pressure and low-temperature refrigerant before the latter reaches the suction of refrigerant compressing device 15.
  • Internal heat exchanger 18 is structured for transferring heat from the high-pressure side of the heat-pump assembly 11, to the low-pressure side of the same heat-pump assembly 11.
  • the internal heat exchanger 18 is preferably structured so that the refrigerant flowing in the high-pressure side and the refrigerant flowing in the low-pressure side flow in counter-current configuration.
  • Central control unit 7 of laundry dryer 1 is structured/programmed for additionally controlling the refrigerant vapor-quality adjusting means 17 according to the time-progression of at least one physical quantity measured within the laundry dyer 1, so to continuously adjust/vary the current "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, i.e. at refrigerant-outlet of first air/refrigerant heat exchanger 13.
  • central control unit 7 of laundry dryer 1 is preferably structured/programmed for controlling the refrigerant vapor-quality adjusting means 17, so to selectively maintain the "vapor quality" of the refrigerant coming out of evaporator 13 at an average value below 1 and preferably, though not necessarily, also ranging between 0,80 and 0,99.
  • internal heat exchanger 18 is dimensioned so to finalize the evaporation of the low-pressure refrigerant coming out of evaporator 13, so that the refrigerant coming out of the low-pressure refrigerant outlet of internal heat exchanger 18 and directed towards the suction of refrigerant compressing device 15 is always completely in gaseous state, i.e. it is located on the right side of the refrigerant Saturated Vapor Curve F" on the Pressure-Enthalpy chart.
  • the refrigerant vapor-quality adjusting means 17 preferably, though not necessarily, comprise a refrigerant cooling device 17 which is connected in series to the condenser 14, i.e. to the air/refrigerant heat exchanger 14, so to be crossed by the high-pressure and high-temperature refrigerant arriving from the condenser 14, and which is structured for selectively cooling down the high-pressure refrigerant in addition to the condenser 14.
  • the refrigerant vapor-quality adjusting means 17 preferably, though not necessarily, comprise:
  • auxiliary air/refrigerant heat exchanger 19 may be interposed between the high-pressure refrigerant outlet of internal heat exchanger 18 and the refrigerant expansion valve 16.
  • Central control unit 7 of laundry dryer 1 controls refrigerant cooling device 17, i.e. controls activation and deactivation of cooling fan 20, so to selectively maximize or minimize the cooling of the refrigerant directed towards the refrigerant expansion valve 16, so to continuously adjust/vary the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, i.e. at refrigerant-outlet of the air/refrigerant heat exchanger 13.
  • auxiliary air/refrigerant heat exchanger 19 is preferably located downstream of condenser 14, i.e. between the refrigerant outlet of air/refrigerant heat exchanger 14 and the high-pressure side of refrigerant/refrigerant heat exchanger 18.
  • the central control unit 7 of laundry dyer 1 controls the activation and/or the current revolving speed of cooling fan 20 so as to selectively maintain, when hot-air generator 5 is preferably in the steady-state working conditions, the evaporator 13 in a flooded condition.
  • central control unit 7 controls the activation and/or the current revolving speed of cooling fan 20 so as to keep the low-pressure refrigerant that flows along evaporator 13 at least partly in liquid state up to the refrigerant-outlet of the same evaporator 13, i.e. with a refrigerant "vapor quality" below 1 up to the refrigerant-outlet of evaporator 13.
  • the "vapor quality" of the low-pressure refrigerant could also be equal to 1.
  • the refrigerant/refrigerant heat exchanger 18 is structured for sequentially heating up the partially-liquid, low-pressure and low-temperature refrigerant coming out of refrigerant-outlet of the evaporator 13, i.e. of the air/refrigerant heat exchanger 13, so as to perform, when hot-air generator 5 is in the steady-state working phase, the complete evaporation and the subsequent superheating of the refrigerant directed towards the suction of refrigerant compressing device 15.
  • central control unit 7 of laundry dryer 1 is preferably structured/programmed to firstly determine whether the hot-air generator 5 is either in warm-up phase or in steady-state working phase.
  • This operation can be performed, for example, via a continuous control of the temperature of the airflow f entering into revolving drum 3, i.e. on exit from the condenser 14, or via a control of the time-progression of the refrigerant temperature and/or of the refrigerant pressure at refrigerant-outlet of the condenser 14.
  • the moisture degree of the airflow f entering into or coming out of the revolving drum 3 could be used for determining whether the hot-air generator 5 is either in warm-up phase or in steady-state working phase.
  • the temperature of the airflow f flowing through revolving drum 3 reaches the highest value and remains roughly constant to said highest value for several minutes, up to the end of the drying cycle.
  • the central control unit 7 of laundry dryer 1 assumes that hot-air generator 5 is in the warm-up phase and keeps the cooling fan 20 switched-off, or at minimum revolving speed, to perform an intensive superheating of the refrigerant both in the evaporator 13, i.e. in the air/refrigerant heat exchanger 13, and in the auxiliary internal refrigerant/refrigerant heat exchanger 18, so as to rapidly increase the refrigerant temperature at suction of the refrigerant compressing device 15.
  • a given first threshold value for example below 50°C
  • a given second threshold value for example below 40°C
  • central control unit 7 of laundry dryer 1 assumes that hot-air generator 5 is in the steady-state working phase and controls activation and deactivation of cooling fan 20, or varies the revolving speed of cooling fan 20, so to preferably maintain the evaporator 13 in a flooded condition, i.e. so to keep the low-pressure refrigerant that flows along evaporator 13 partly in liquid state up to the refrigerant-outlet of the same evaporator 13.
  • central control unit 7 controls the activation and/or the current revolving speed of cooling fan 20, so as to selectively maintain the "vapor quality" of the low-pressure refrigerant coming out of evaporator 13 at an average value below 1 up to the refrigerant-outlet of the evaporator 13.
  • the central control unit 7 preferably continuously switches the cooling fan 20 on and off, or varies the revolving speed of cooling fan 20, so that the refrigerant coming out of refrigerant-outlet of heat exchanger 13 has a refrigerant "vapor quality" ranging between 0,40 and 1, and in particular preferably, though not necessarily, between 0,80 and 0,99.
  • the refrigerant/refrigerant heat exchanger 18 is instead structured for heating up the low-pressure and low-temperature refrigerant coming out of refrigerant-outlet of the evaporator 13, so as to rise at 1 the refrigerant "vapor quality" and afterward to superheat the gaseous-state refrigerant directed towards the suction of refrigerant compressing device 15.
  • FIG. 3 shows the closed thermodynamic cycle performed by the heat-pump assembly 11 when cooling fan 20 is switched off.
  • the high-pressure and high-temperature refrigerant when coming out of the delivery of refrigerant compressing device 15, the high-pressure and high-temperature refrigerant enters into the condenser 14, i.e. into the air/refrigerant heat exchanger 14, wherein it gives off heat to the airflow f entering into revolving drum 3. Afterwards the high-pressure and high-temperature refrigerant enters into the auxiliary air/refrigerant heat exchanger 19, but, being the cooling fan 20 switched-off, the air/refrigerant heat exchanger 19 has substantially no cooling effects on the refrigerant flowing from the refrigerant-outlet of condenser 14 to the refrigerant expansion valve 16.
  • the high-pressure and high-temperature refrigerant flows inside the refrigerant/refrigerant heat exchanger 18 with substantially no pressure drop, wherein it gives off heat to the low-pressure and low-temperature refrigerant flowing towards the suction of refrigerant compressing device 15, thus moving from point c (high-pressure refrigerant inlet of heat exchanger 18) to point d of the Pressure-Enthalpy chart (high-pressure refrigerant outlet of heat exchanger 18 and inlet of refrigerant expansion valve 16) again along a constant-pressure line.
  • the refrigerant When coming out of air/refrigerant heat exchanger 19 or out of refrigerant/refrigerant heat exchanger 18, the refrigerant is completely in liquid state and therefore it is located on the left side of the refrigerant Saturated Liquid Curve F' on the Pressure-Enthalpy chart.
  • the high-pressure and high-temperature refrigerant flows through the refrigerant expansion valve 16 which subjects the refrigerant to a substantially adiabatic rapid expansion, so as to cause a rapid drop of both refrigerant pressure and refrigerant temperature, and also the evaporation of part of the refrigerant.
  • the refrigerant moves from point d (high-pressure refrigerant outlet of heat exchanger 18 and inlet of refrigerant expansion valve 16) to point e of the Pressure-Enthalpy chart (outlet of refrigerant expansion valve 16 and refrigerant-inlet of evaporator 13) along a substantially constant-Enthalpy line that crosses the refrigerant Saturated Liquid Curve F'.
  • the low-pressure and low-temperature refrigerant flows inside the evaporator 13, i.e. the air/refrigerant heat exchanger 13, wherein it absorbs heat from the airflow f coming out of revolving drum 3 with substantially no pressure drop.
  • the low-pressure and low-temperature refrigerant is allowed to absorb, from the airflow f arriving from revolving drum 3, a heat amount which suffices to perform a complete evaporation and a slight superheating of the refrigerant directed towards the suction of refrigerant compressing device 15.
  • a refrigerant In thermodynamic, a refrigerant is defined as being in a superheated condition when the temperature of the refrigerant is greater than the refrigerant saturation temperature at the current refrigerant pressure. This implies that a refrigerant in superheated condition is a refrigerant completely in gaseous state and it is located on the right side of the refrigerant Saturated Vapor Curve F" on the Pressure-Enthalpy chart.
  • the refrigerant moves from point e (refrigerant-inlet of heat exchanger 13) to point f of the Pressure-Enthalpy chart (low-pressure refrigerant-inlet of refrigerant/ refrigerant heat exchanger 18) along a substantially constant-Pressure line, and point f of the Pressure-Enthalpy chart (low-pressure refrigerant-inlet of internal refrigerant/refrigerant heat exchanger 18) is located on the right side of the refrigerant Saturated Vapor Curve F".
  • the gaseous-state low-pressure and low-temperature refrigerant flows again inside the refrigerant/refrigerant heat exchanger 18 with substantially no pressure drops, wherein it absorbers heat from the high-pressure and high-temperature refrigerant flowing towards the inlet of refrigerant expansion vale 16, thus continuing its superheating process.
  • the gaseous-state refrigerant moves from point f (low-pressure refrigerant-inlet of internal refrigerant/refrigerant heat exchanger 18) to point g of the Pressure-Enthalpy chart (suction of the refrigerant compressing device 15) again along a constant-Pressure line.
  • the gaseous-state, low-pressure and low-temperature refrigerant enters in the refrigerant compressing device 15 wherein it is compressed so as to close the thermodynamic cycle, and moves from point g (suction of the refrigerant compressing device 15) back to point a the Pressure-Enthalpy chart (delivery of refrigerant compressing device 15) along an inclined Pressure-, and Enthalpy- increasing line.
  • Figure 4 instead shows the closed thermodynamic cycle performed by the heat-pump assembly 11 when cooling fan 20 is switched on, i.e. when the refrigerant cooling device 17 cools down the refrigerant flowing from the condenser 14 to the refrigerant expansion device 16.
  • the high-pressure and high-temperature refrigerant enters into the auxiliary air/refrigerant heat exchanger 19, wherein, being the cooling fan 20 switched on, the refrigerant is cooled by a stream w of cooling air arriving from the outside of casing 2.
  • the refrigerant therefore, moves from point b (refrigerant inlet of heat exchanger 19) to point c of the Pressure-Enthalpy chart (high-pressure refrigerant inlet of heat exchanger 18) along the same constant-pressure line.
  • the high-pressure and high-temperature refrigerant flows inside the refrigerant/refrigerant heat exchanger 18 with substantially no pressure drop, wherein it gives off heat to the low-pressure and low-temperature refrigerant flowing towards the suction of refrigerant compressing device 15, thus moving from point c (high-pressure refrigerant inlet of heat exchanger 18) to point d of the Pressure-Enthalpy chart (high-pressure refrigerant outlet of heat exchanger 18 and inlet of refrigerant expansion valve 16) again along a constant-pressure line.
  • the liquid-state, high-pressure and high-temperature refrigerant flows through the refrigerant expansion valve 16 which subjects the refrigerant to a substantially adiabatic rapid expansion, so as to cause a rapid drop of both refrigerant pressure and refrigerant temperature, and also the evaporation of part of the refrigerant.
  • the refrigerant therefore, moves from point d (high-pressure refrigerant outlet of heat exchanger 18 and inlet of refrigerant expansion valve 16) to point e of the Pressure-Enthalpy chart (outlet of refrigerant expansion valve 16 and refrigerant-inlet of evaporator 13) along a substantially constant-Enthalpy line that crosses the refrigerant Saturated Liquid Curve F'.
  • the low-pressure and low-temperature refrigerant flows inside the evaporator 13, i.e. the air/refrigerant heat exchanger 13, wherein it absorbs heat from the airflow f coming out of revolving drum 3 with substantially no pressure drop.
  • the low-pressure and low-temperature refrigerant flowing along the evaporator 13 is able to absorb, from the airflow f arriving from revolving drum 3, an increased heat amount which is however insufficient to perform a complete evaporation of the refrigerant directed towards the suction of refrigerant compressing device 15.
  • the low-pressure and low-temperature is still partly in liquid state, i.e. it has a refrigerant "vapor quality" lower than 1, and it is located on the left side of the refrigerant Saturated Vapor Curve F" on the Pressure-Enthalpy chart.
  • the refrigerant moves from point e (refrigerant-inlet of heat exchanger 13) to point f of the Pressure-Enthalpy chart (low-pressure refrigerant-inlet of internal refrigerant/ refrigerant heat exchanger 18) along a substantially constant-Pressure line, but point f is located on the left side of the refrigerant Saturated Vapor Curve F" on the Pressure-Enthalpy chart.
  • the liquid-gaseous double-phase, low-pressure and low-temperature refrigerant flows again inside the internal refrigerant/ refrigerant heat exchanger 18 with substantially no pressure drop, wherein it absorbers, from the high-pressure and high-temperature refrigerant flowing towards the inlet of refrigerant expansion vale 16, a heat amount which suffices to complete evaporation of the refrigerant and afterwards to perform the superheating of the refrigerant directed towards the suction of refrigerant compressing device 15.
  • the refrigerant while flowing inside the heat exchanger 18, the refrigerant therefore moves from point f (low-pressure refrigerant-inlet of internal heat exchanger 18) to point g of the Pressure-Enthalpy chart (suction of the refrigerant compressing device 15) along a constant-Pressure line that, in this case, crosses the refrigerant Saturated Vapor Curve F" on the Pressure-Enthalpy chart.
  • the gaseous-state, low-pressure and low-temperature refrigerant enters in the refrigerant compressing device 15, wherein it is compressed so as to close the thermodynamic cycle, and moves from point g (suction of refrigerant compressing device 15) back to point a the Pressure-Enthalpy chart (delivery of refrigerant compressing device 15) along an inclined Pressure-, and Enthalpy-increasing line.
  • the central control unit 7 of laundry dryer 1 is structured/ programmed to drive the refrigerant cooling device 17, i.e. to switch the cooling fan 20 on and off, so as to force the heat-pump assembly 11 to selectively and alternatively perform either the Figure 3 closed thermodynamic cycle which produces, at refrigerant-outlet of evaporator 13, a refrigerant having a "vapor quality" equal to 1, or the Figure 4 closed thermodynamic cycle which produces, at refrigerant-outlet of evaporator 13, a refrigerant having a "vapor quality" considerably below 1.
  • thermodynamic cycle The switching between the Figure 3 thermodynamic cycle and the Figure 4 thermodynamic cycle is purposely controlled so as to maintain the evaporator 13 in a flooded condition, i.e. so as to keep the low-pressure refrigerant that flows along the evaporator 13 partly in liquid state up to the refrigerant-outlet of the same evaporator 13.
  • central control unit 7 purposely controls the activation and/or the revolving speed of cooling fan 20, so as to maintain the "vapor quality" of the low-pressure refrigerant coming out of evaporator 13 at an average value below 1 up to the refrigerant-outlet of evaporator 13.
  • central control unit 7 is structured/programmed to switch the cooling fan 20 on and off, or to vary the revolving speed of cooling fan 20, so as to maintain the "vapor quality" of the refrigerant coming out of evaporator 13 at an average value ranging between 0,40 and 1 , and preferably, though not necessarily, also ranging between 0,80 and 0,99.
  • central control unit 7 of laundry dryer 1 preferably implements a control strategy which maintains, when hot-air generator 5 is in the steady-state working phase, the temperature of the refrigerant at refrigerant-outlet of evaporator 13 below the corresponding refrigerant saturation temperature, so that part of the low-pressure refrigerant coming out of heat exchanger 13 is surely still in liquid state.
  • central control unit 7 could maintain the temperature of the refrigerant at refrigerant-outlet of evaporator 13 roughly equal to the corresponding refrigerant saturation temperature, so that the low-pressure refrigerant remains at least partly in liquid state up to the refrigerant-outlet of heat exchanger 13.
  • the refrigerant saturation temperature is the refrigerant temperature at which, for a given pressure of the refrigerant, the liquid-to-gaseous phase-change of the refrigerant is completed.
  • the refrigerant temperature measured at refrigerant-outlet of evaporator 13 is lower than the refrigerant saturation temperature at the same refrigerant pressure, this implies that the refrigerant liquid-to-gaseous phase-change is not finalized in the evaporator 13 and that, consequently, part of the refrigerant is still in liquid state at refrigerant-outlet of the evaporator 13.
  • the central control unit 7 of laundry dryer 1 maintains, when hot-air generator 5 is preferably in the steady-state working phase, the heat exchanger 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the refrigerant temperature and refrigerant pressure measured at refrigerant-outlet of the evaporator 13, i.e. of the air/refrigerant heat exchanger 13.
  • central control unit 7 of laundry dryer 1 firstly measures the current pressure and temperature of the refrigerant at refrigerant-outlet of heat exchanger 13, then calculates the exact refrigerant saturation temperature on the basis of the measured current refrigerant pressure, and finally compares the measured refrigerant temperature with the calculated refrigerant saturation temperature so as to determine whether the calculated refrigerant saturation temperature is greater than the measured refrigerant temperature.
  • central control unit 7 of laundry dryer 1 is structured/programmed to switch on and off the cooling fan 20, so as to maintain the average temperature of the refrigerant at refrigerant-outlet of the evaporator 13, i.e. of the air/refrigerant heat exchanger 13, within a given temperature range located immediately beneath the calculated refrigerant saturation temperature.
  • the upper and lower ends of this temperature range are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13, i.e. of the evaporator 13, ranges between 0,40 and 1 , and in particular ranges preferably, though not necessarily, between 0,80 and 0,99.
  • the temperature of the refrigerant at refrigerant-outlet of the evaporator 13 is preferably, though not necessarily, maintained from 0,1°C to 4°C beneath the calculated refrigerant saturation temperature. This implies that the difference between the calculated refrigerant saturation temperature and the measured refrigerant temperature at refrigerant-outlet of heat exchanger 13 ranges preferably, though not necessarily, between roughly 0,1°C and 4°C.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed
  • the central control unit 7 of laundry dyer 1 deactivates the cooling fan 20 for increasing the current "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the refrigerant temperature at refrigerant-outlet of the evaporator 13 exceeds a predetermined first threshold value (in the example shown equal to 4°C); and activates the cooling fan 20 for reducing the current "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13, whenever the refrigerant temperature at refrigerant-outlet of heat evaporator 13 goes below a predetermined second threshold value (in the example shown 0,1°C) which is lower than said first threshold value.
  • a predetermined first threshold value in the example shown equal to 4°C
  • the first and the second threshold value are conveniently selected to assure that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is below 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • central control unit 7 deactivates the cooling fan 20 for increasing the current "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13, whenever the refrigerant temperature at refrigerant-outlet of evaporator 13 goes too far below the corresponding calculated refrigerant saturation temperature; and activates the cooling fan 20 for reducing the current "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13, whenever the refrigerant temperature at refrigerant-outlet of evaporator 13 goes too close to the corresponding refrigerant saturation temperature.
  • the central control unit 7 of laundry dryer 1 activates the cooling fan 20 to maximize the cooling of the refrigerant inside heat exchanger 19 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13, only if hot-air generator 5 is in the steady-state working phase.
  • variable-speed cooling fan 20 allows a much more accurate control of the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, i.e. at refrigerant-outlet of air/ refrigerant heat exchanger 13.
  • the laundry dryer 1 is obviously provided with at least one pressure sensor (not shown) and with at least one temperature sensor (not shown), both located at refrigerant-outlet of evaporator 13, i.e. of the air/ refrigerant heat exchanger 13, for continuously measuring the refrigerant local pressure and temperature.
  • refrigerant pressure at outlet of evaporator 13 is substantially equal to the refrigerant pressure at suction of refrigerant compressing device 15 or at low-pressure refrigerant outlet of internal heat exchanger 18, the pressure sensor could also be located at low-pressure refrigerant outlet of internal heat exchanger 18 or at suction of refrigerant compressing device 15.
  • central control unit 7 of laundry dryer 1 can determine whether the evaporator 13, i.e. the air/refrigerant heat exchanger 13, is in a flooded condition, via a direct measurement of the current pressure and temperature of the refrigerant at low-pressure refrigerant outlet of refrigerant/refrigerant heat exchanger 18.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the refrigerant temperature and refrigerant pressure measured at refrigerant-outlet of heat exchanger 18.
  • the measurement of the current pressure of the refrigerant at low-pressure refrigerant outlet of internal heat exchanger 18 may be replaced by the measurement of the current pressure of the refrigerant at refrigerant-outlet of evaporator 13 because substantially no pressure drops occurs while the refrigerant flows along the low pressure side of internal heat exchanger 18, or by the measurement of the current pressure of the refrigerant at suction of refrigerant compressing device 15.
  • the refrigerant saturation temperature is a scalar physical quantity which depends strictly on the type of refrigerant and on its pressure, therefore central control unit 7 firstly measures the current pressure of the refrigerant at low-pressure refrigerant outlet of internal heat exchanger 18, or at suction of refrigerant compressing device 15, or at refrigerant-outlet of heat exchanger 13; then calculates the exact refrigerant saturation temperature on the basis of the measured current refrigerant pressure; and finally compares the refrigerant temperature measured at low-pressure refrigerant outlet of heat exchanger 18 with the calculated refrigerant saturation temperature, so as to determine whether the refrigerant coming out of the low-pressure refrigerant outlet of internal heat exchanger 18 is superheated and so as to determine the current amount of such superheating.
  • the difference between the refrigerant temperature measured at low-pressure refrigerant outlet of heat exchanger 18 and the calculated refrigerant saturation temperature is very high (for example greater than 12°C), it means that the low-pressure refrigerant is deeply superheated and that, therefore, the low-pressure refrigerant comes out of evaporator 13 when refrigerant evaporation is already finalized. Thus evaporator 13 is in a non-flooded condition.
  • the difference between the refrigerant temperature measured at low-pressure refrigerant outlet of heat exchanger 18 and the calculated refrigerant saturation temperature is very low (for example lower than 1°C), it means that the low-pressure refrigerant is only slightly superheated and that, therefore, the low-pressure refrigerant comes out of the evaporator 13 still partly in liquid state. Thus evaporator 13 is working in a flooded condition.
  • central control unit 7 of laundry dryer 1 may be structured/programmed to switch the cooling fan 20 on and off, so as to keep the difference between the current temperature of the refrigerant at low-pressure refrigerant outlet of internal heat exchanger 18 and the calculated refrigerant saturation temperature, i.e. the current refrigerant superheating, within a predetermined temperature range which is located above the calculated refrigerant saturation temperature and which depends on the structure of internal heat exchanger 18.
  • this temperature range are conveniently selected so that the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13 is below 1, and ranges between 0,40 and 1 .
  • the upper and lower ends of this temperature range are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 ranges preferably, though not necessarily, between 0,80 and 0,99.
  • the central control unit 7 of laundry dryer 1 may be structured/ programmed so to keep the difference between the current temperature of the refrigerant at low-pressure refrigerant outlet of internal heat exchanger 18 and the calculated refrigerant saturation temperature within a given temperature range preferably, though not necessarily, extending from 1°C to 20°C.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed
  • the central control unit 7 of laundry dyer 1 deactivates the cooling fan 20 for increasing the current "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the refrigerant temperature at low-pressure refrigerant outlet of internal heat exchanger 18 goes below a predetermined first threshold value (in the example shown 1°C); and activates the cooling fan 20 for reducing the current "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the refrigerant temperature at low-pressure refrigerant outlet of internal heat exchanger 18 exceeds a predetermined second threshold value (in the example shown 20°C) which is greater than said first threshold value.
  • a predetermined first threshold value in the example shown 1°C
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13; whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13.
  • the first and the second threshold value are conveniently selected to assure that the "vapor quality" of the refrigerant coming out of evaporator 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • central control unit 7 keeps the cooling fan 20 switched off for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, if the refrigerant temperature at low-pressure refrigerant outlet of internal heat exchanger 18 arrives too close to the corresponding refrigerant saturation temperature; and keeps the cooling fan 20 switched on for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, if the refrigerant temperature at low-pressure refrigerant outlet of internal heat exchanger 18 goes too high with respect to the corresponding calculated refrigerant saturation temperature.
  • variable-speed cooling fan 20 allows a much more accurate control of the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, i.e. of evaporator 13.
  • the laundry dryer 1 is obviously provided with at least one pressure sensor (not shown) and with at least one temperature sensor (not shown), both located at low-pressure refrigerant outlet of internal heat exchanger 18 for continuously measuring the refrigerant local pressure and temperature.
  • refrigerant pressure at low-pressure refrigerant outlet of internal heat exchanger 18 is substantially equal to the refrigerant pressure at suction of refrigerant compressing device 15 or at outlet of evaporator 13, the pressure sensor could also be located at outlet of evaporator 13 or at suction of refrigerant compressing device 15.
  • thermodynamic approach considering refrigerant zeotropic blends, if the refrigerant temperature at refrigerant-outlet of evaporator 13 is lower that the refrigerant saturation temperature at the same refrigerant pressure, it means that a negative refrigerant superheating is taking place inside the evaporator 13. Similarly to the previous approach, this condition is necessary and sufficient to ensure that part of the refrigerant is in liquid state at refrigerant-outlet of evaporator 13 and that, therefore, heat exchanger 13 is in the flooded condition.
  • central control unit 7 can alternatively check whether the evaporator 13 is in a flooded condition, via a direct measurement and comparison between the temperature drop of the refrigerant flowing in the high-pressure side of internal heat exchanger 18, and the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18.
  • the refrigerant flowing in the low-pressure side of heat exchanger 18 is merely superheated, and the increase of the refrigerant temperature measured at the low-pressure side of heat exchanger 18 is significantly higher than the drop of refrigerant temperature measured at the high-pressure side of heat exchanger 18.
  • a refrigerant almost completely in liquid state i.e. the refrigerant flowing in the high-pressure side of heat exchanger 18
  • has a thermal capacity, i.e. a specific heat considerably higher than that of a whole gaseous-state refrigerant (i.e. the refrigerant flowing in the low-pressure side of heat exchanger 18).
  • the refrigerant flowing in the low-pressure side of heat exchanger 18 must be firstly completely vaporized and then superheated, thus the difference between the increase of the refrigerant temperature measured at the low-pressure side of heat exchanger 18 and the drop of the refrigerant temperature measured at the high-pressure side of heat exchanger 18 is small. This is due to the fact that the average thermal capacity of the refrigerant flowing in the low-pressure side of heat exchanger 18 becomes close to the thermal capacity of the liquid-state refrigerant flowing in the high-pressure side of heat exchanger 18.
  • central control unit 7 of laundry dryer 1 may be structured/programmed
  • the first tolerance value is significantly greater than zero (for example 10°C), whereas the second tolerance value is preferably, though not necessarily, lower than the first tolerance value.
  • central control unit 7 of laundry dryer 1 may be structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the current "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, if the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 exceeds of a predetermined first tolerance value the temperature drop of the refrigerant flowing in the high-pressure side of heat exchanger 18 (for example the temperature rise of the low-pressure refrigerant is more than 10°C higher than the temperature drop of the high-pressure refrigerant).
  • central control unit 7 of laundry dryer 1 deactivates the cooling fan 20 for increasing the current "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, if the temperature drop of the refrigerant flowing in the high-pressure side of heat exchanger 18 exceeds of a predetermined second tolerance value the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 (for example the temperature drop of the low-pressure refrigerant is more than 3°C higher than the temperature rise of the low-pressure refrigerant), or if the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 goes below a predetermined third threshold value (for example it goes below 5°C).
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed to measure the temperature drop of the refrigerant flowing in the high-pressure side of internal heat exchanger 18, and the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18; and to drive the refrigerant cooling device 17, i.e.
  • the refrigerant vapor-quality adjusting means so as to keep the difference between the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 and the temperature drop of the refrigerant flowing in the high-pressure side of heat exchanger 18, within a predetermined tolerance range whose upper and lower ends are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is below 1 and preferably ranges between 0,40 and 1 .
  • central control unit 7 is structured/programmed to switch the cooling fan 20 on and off, so as to keep the difference between the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 and the temperature drop of the refrigerant flowing in the high-pressure side of heat exchanger 18, within a tolerance range preferably, though not necessarily, extending from -3°C to 15°C.
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the difference between the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 and the temperature drop of the refrigerant flowing in the high-pressure side of heat exchanger 18 exceeds the upper limit of said tolerance range (for example the upper limit is equal to 15°C).
  • central control unit 7 deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the difference between the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 and the temperature drop of the refrigerant flowing in the high-pressure side of heat exchanger 18 goes below the lower limit of said tolerance (for example the lower limit is equal to -3°C); or whenever the temperature rise of the refrigerant flowing in the low-pressure side of heat exchanger 18 goes below a predetermined threshold value (for example it goes below 5°C).
  • this threshold value is greater than zero so as to ensure that the low-pressure and low-temperature refrigerant flowing in the low-pressure side of internal heat exchanger 18 is at least a little bit superheated before reaching the suction of refrigerant compressing device 15.
  • the laundry dryer 1 is obviously provided with four temperature sensors (not shown), each located at a respective inlet or outlet of heat exchanger 18 to measure the corresponding refrigerant temperatures.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the temperature difference of the refrigerant flowing in the evaporator 13, i.e. in the air/refrigerant heat exchanger 13.
  • central control unit 7 of laundry dryer 1 can measure the temperature drop of the refrigerant flowing in evaporator 13 and, when the hot-air generator is in the steady-state working phase, it can continuously switch the cooling fan 20 on and off so as to keep the temperature drop of the refrigerant flowing through the evaporator 13 as constant as possible within a given narrow temperature range located immediately above 0°C.
  • the upper and lower ends of this narrow temperature range are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is below 1 and ranges between 0,40 and 1 , and in particular ranges preferably, though not necessarily, between 0,80 and 0,99.
  • central control unit 7 is structured/programmed to continuously switch the cooling fan 20 on and off, so as to keep the temperature drop of the refrigerant flowing through the evaporator 13 within a given narrow temperature range extending from approximately 0°C to 3°C, or event from 0°C to 5°C, and preferably, though not necessarily, extending from 0,2°C to 0,8°C.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13 and that deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, the central control unit 7 of laundry dryer 1, when hot-air generator 5 is in the steady-state working phase, activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature drop of the refrigerant flowing through the evaporator 13 exceeds a first threshold value (for example 0,8°C).
  • a first threshold value for example 0,8°C
  • central control unit 7 of laundry dryer 1 deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the temperature drop of the refrigerant flowing through the evaporator 13 goes below a second threshold value (for example 0,2°C) which is lower than said upper threshold value.
  • a second threshold value for example 0,2°C
  • the laundry dryer 1 is provided with two temperature sensors located, respectively, at refrigerant-inlet and at refrigerant-outlet of evaporator 13 to measure the corresponding refrigerant temperatures.
  • central control unit 7 may improve precision of the fourth control-strategy referred above via an additional control of the temperature drop of the refrigerant that flows in the high-pressure side of internal heat exchanger 18. If the temperature drop of the refrigerant flowing through the evaporator 13 is slightly greater than 0°C and, at the same time, the temperature drop of the refrigerant flowing in the high-pressure side of refrigerant/refrigerant heat exchanger 18 is significantly high, this means that internal heat exchanger 18 is finalizing the evaporation of the low-pressure refrigerant and that, therefore, the evaporator 13 is in a flooded condition.
  • This combined control-strategy is particularly helpful when the behaviour of the refrigerant flowing in the heat-pump assembly 11 is that of a pure/ideal fluid.
  • the central control unit 7 of laundry dryer 1 maintains, when hot-air generator 5 is in the steady-state working phase, the evaporator 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the temperature drop of the refrigerant flowing in the evaporator 13, i.e. flowing in the air/ refrigerant heat exchanger 13, and of the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18.
  • the temperature drop of the refrigerant flowing through the evaporator 13 is very close to zero when the evaporator 13 is in a flooded condition, because the refrigerant liquid-to-gaseous phase-change takes place at a constant temperature and it is not finalized at refrigerant-outlet of heat exchanger 13.
  • the drop of the refrigerant temperature at the high-pressure side of internal heat exchanger 18 is considerably high when the evaporator 13 is in the flooded condition, because the high-temperature and high-pressure refrigerant flowing through internal heat exchanger 18 has to transfer to the low-pressure refrigerant flowing through the same heat exchanger enough heat to finalize both the evaporation and the superheating.
  • the latent evaporation heat transfer coefficient of the refrigerant in fact, is considerably higher than the sensible heat transfer coefficient of the same refrigerant.
  • central control unit 7 of laundry dryer 1 can measure both the temperature drop of the refrigerant flowing in evaporator 13 and the temperature drop of the refrigerant that flows in the high-pressure side of internal heat exchanger 18, and, when the hot-air generator is in the steady-state working phase, it can continuously switch on and off the cooling fan 20 so as to keep the temperature rise of the refrigerant flowing through the evaporator 13 as constant as possible within a first narrow temperature range located immediately above 0°C, and which extends preferably, though not necessarily, from 0°C and 5°C; and, at the same time, so as to keep the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18 within a second temperature range whose upper and lower ends are both significantly higher than 0°C.
  • the first temperature range extends preferably, though not necessarily, from 0,2°C to 0,8°C; whereas the second temperature range extends preferably, though not necessarily, from 10°C to 20°C, thus assuring that the complete vaporization of the refrigerant and subsequent superheating of the refrigerant take place inside internal heat exchanger 18.
  • Central control unit 7 is therefore preferably, though not necessarily, structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature drop of the refrigerant flowing through the evaporator 13 exceeds a first threshold value (for example 0,8°C), and whenever, at the same time, the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18 goes below a second threshold value (for example 10°C); and deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature drop of the refrigerant flowing through the evaporator 13 goes below a third threshold value (for example 0,2°C) which is lower than said first threshold value, and whenever, at the same time, the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18 exceeds a fourth threshold value (for example 20°
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13; whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13.
  • the laundry dryer 1 is provided with four temperature sensors located, respectively, at refrigerant-inlet of evaporator 13, at refrigerant-outlet of evaporator 13, at high-pressure refrigerant inlet of heat exchanger 18 and finally at high-pressure refrigerant outlet of heat exchanger 18 to measure the corresponding refrigerant temperatures.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the evaporator 13, i.e. the air/refrigerant heat exchanger 13, in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the temperature drop of the refrigerant flowing in the evaporator 13, i.e. flowing in heat exchanger 13, and of the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18.
  • this combined control-strategy is particularly helpful when the behaviour of the refrigerant flowing in the heat-pump assembly 11 is a pure/ideal fluid.
  • the temperature drop of the refrigerant flowing through the evaporator 13 is very close to zero when the evaporator 13 is in a flooded condition, because the refrigerant liquid-to-gaseous phase-change takes place at a constant temperature and it is not finalized at refrigerant-outlet of heat exchanger 13.
  • the temperature rise of the refrigerant flowing through the low-pressure side of internal heat exchanger 18 is significantly high, i.e. significantly greater than zero, because the refrigerant flowing in the low-pressure side of internal heat exchanger 18 is to be only superheated.
  • central control unit 7 of laundry dryer 1 can measure both the temperature drop of the refrigerant flowing in the evaporator 13 and the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18, and, when hot-air generator is in the steady-state working phase, it can switch the cooling fan 20 on and off (i.e.
  • central control unit 7 is preferably, though not necessarily, structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature drop of the refrigerant flowing through the evaporator 13 exceeds a first threshold value (for example 0,8°C), and whenever the temperature rise of the refrigerant flowing through the low-pressure side of internal heat exchanger 18 exceeds a second threshold value (for example 20°C); and deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature drop of the refrigerant flowing through the evaporator 13 goes below a third threshold value (for example 0,2°C) which is lower than said first threshold value, and the temperature rise of the refrigerant flowing through the low-pressure side of internal heat exchanger 18 goes below a fourth threshold value (for example 3°C) which is lower than said second threshold value.
  • a first threshold value for example 0,8°C
  • second threshold value for example
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13; whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13.
  • the fourth threshold value is always greater than the second threshold value.
  • the heat exchanger 18 finalizes only the superheating of the refrigerant.
  • the liquid state portion of the refrigerant coming out from the evaporator 13 is excessive, and the internal heat exchanger 18 is not able to finalize the evaporation of low-pressure refrigerant and afterwards superheat the refrigerant directed towards the suction of refrigerant compressing device 15.
  • the laundry dryer 1 is provided with three temperature sensors located, respectively, at refrigerant-inlet of the evaporator 13, at refrigerant-outlet of the evaporator 13, and finally at low-pressure refrigerant outlet of heat exchanger 18 to measure the corresponding refrigerant temperatures.
  • the refrigerant temperature at low-pressure refrigerant inlet of heat exchanger 18, in fact, is to be considered equal to the refrigerant temperature at refrigerant-outlet of heat exchanger 13.
  • control-strategy can be also adapted to deal with refrigerant zeotropic blends, taking into consideration that the complete liquid-to-gaseous phase-change of a refrigerant zeotropic blend takes place at increasing temperature. This implies that, when the evaporator 13 is in flooded condition, the refrigerant flowing through the evaporator 13 is subjected to a temperature rise greater than zero, even if the liquid-to-gaseous phase-change is not finalized at refrigerant-outlet of evaporator 13.
  • central control unit 7 of laundry dryer 1 can measure the temperature rise of the refrigerant flowing in evaporator 13 and, when the hot-air generator is in the steady-state working phase, it can continuously switch the cooling fan 20 on and off so as to keep the temperature rise of the refrigerant flowing through the evaporator 13 as constant as possible within a given narrow temperature range slightly above 0°C.
  • the upper and lower ends of this narrow temperature range are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is below 1 and ranges between 0,40 and 1 (upper limit not included), and in particular ranges preferably, though not necessarily, between 0,80 and 0,99.
  • central control unit 7 is structured/programmed to continuously switch the cooling fan 20 on and off, so as to keep the temperature rise of the refrigerant flowing through the evaporator 13 within a given narrow temperature range extending from approximately 1°C to 5°C, or even from 0°C to 5°C, and preferably, though not necessarily, extending from 2°C to 4°C.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13 and that deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, central control unit 7 of laundry dryer 1, when hot-air generator 5 is in the steady-state working phase, activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature rise of the refrigerant flowing through the evaporator 13 exceeds a first threshold value (for example 4°C).
  • a first threshold value for example 4°C
  • central control unit 7 deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the temperature rise of the refrigerant flowing through the evaporator 13 goes below a second threshold value (for example 2°C) which is lower than said upper threshold value.
  • a second threshold value for example 2°C
  • the laundry dryer 1 is again provided with two temperature sensors located, respectively, at refrigerant-inlet and at refrigerant-outlet of evaporator 13 to measure the corresponding refrigerant temperatures.
  • central control unit 7 may optionally improve precision of this last control-strategy, via an additional control of the temperature drop of the refrigerant that flows in the high-pressure side of internal heat exchanger 18. If the temperature rise of the refrigerant flowing through the evaporator 13 is slightly above 0°C and, at the same time, the temperature drop of the refrigerant flowing in the high-pressure side of refrigerant/refrigerant heat exchanger 18 is significantly high, this means that internal heat exchanger 18 is finalizing the evaporation of the low-pressure refrigerant and that, therefore, the evaporator 13 is in a flooded condition.
  • the central control unit 7 of laundry dryer 1 maintains, when hot-air generator 5 is in the steady-state working phase, the evaporator 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the temperature rise of the refrigerant flowing in the evaporator 13, i.e. flowing in the air/ refrigerant heat exchanger 13, and of the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18.
  • the temperature rise of the refrigerant flowing through the evaporator 13 is slightly above zero when the evaporator 13 is in a flooded condition.
  • the drop of the refrigerant temperature at the high-pressure side of internal heat exchanger 18 is considerably high when the evaporator 13 is in the flooded condition, because the high-temperature and high-pressure refrigerant flowing through the internal heat exchanger 18 has to transfer to the low-pressure refrigerant flowing through the same heat exchanger enough heat to finalize both the evaporation and the superheating.
  • the latent evaporation heat transfer coefficient of the refrigerant in fact, is considerably higher than the sensible heat transfer coefficient of the same refrigerant.
  • central control unit 7 of laundry dryer 1 can measure both the temperature rise of the refrigerant flowing in evaporator 13 and the temperature drop of the refrigerant that flows in the high-pressure side of internal heat exchanger 18, and, when the hot-air generator is in the steady-state working phase, it can continuously switch on and off the cooling fan 20 so as to keep the temperature rise of the refrigerant flowing through the evaporator 13 as constant as possible within a first narrow temperature range located above 0°C, and which extends preferably, though not necessarily, from 1°C and 5°C; and, at the same time, so as to keep the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18 within a second temperature range whose upper and lower ends are both significantly higher than 0°C.
  • the first temperature range extends preferably, though not necessarily, from 2°C to 8°C; whereas the second temperature range extends preferably, though not necessarily, from 10°C to 20°C, thus assuring that the complete vaporization of the refrigerant and subsequent superheating of the refrigerant take place inside internal heat exchanger 18.
  • Central control unit 7 is therefore preferably, though not necessarily, structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature rise of the refrigerant flowing through the evaporator 13 exceeds a first threshold value (for example 4°C), and whenever, at the same time, the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18 goes below a second threshold value (for example 10°C); and deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature rise of the refrigerant flowing through the evaporator 13 goes below a third threshold value (for example 2°C) which is lower than said first threshold value, and whenever, at the same time, the temperature drop of the refrigerant flowing through the high-pressure side of internal heat exchanger 18 exceeds a fourth threshold value (for example 20°C)
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13; whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13.
  • the laundry dryer 1 is again provided with four temperature sensors located, respectively, at refrigerant-inlet of evaporator 13, at refrigerant-outlet of evaporator 13, at high-pressure refrigerant inlet of heat exchanger 18 and finally at high-pressure refrigerant outlet of heat exchanger 18 to measure the corresponding refrigerant temperatures.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the evaporator 13, i.e. the air/refrigerant heat exchanger 13, in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the temperature rise of the refrigerant flowing in the evaporator 13, i.e. flowing in heat exchanger 13, and of the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18.
  • the temperature rise of the refrigerant flowing through the evaporator 13 is slightly higher than zero when the evaporator 13 is in a flooded condition.
  • the temperature rise of the refrigerant flowing through the low-pressure side of internal heat exchanger 18 is significantly high, i.e. significantly greater than zero, because the refrigerant flowing in the low-pressure side of internal heat exchanger 18 must be only superheated.
  • central control unit 7 of laundry dryer 1 can measure both the temperature rise of the refrigerant flowing in the evaporator 13 and the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18, and, when hot-air generator is in the steady-state working phase, it can switch the cooling fan 20 on and off (i.e.
  • central control unit 7 is preferably, though not necessarily, structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature rise of the refrigerant flowing through the evaporator 13 exceeds a first threshold value (for example 4°C), and whenever the temperature rise of the refrigerant flowing through the low-pressure side of internal heat exchanger 18 exceeds a second threshold value (for example 20°C); and deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature rise of the refrigerant flowing through the evaporator 13 goes below a third threshold value (for example 2°C) which is lower than said first threshold value, and the temperature rise of the refrigerant flowing through the low-pressure side of internal heat exchanger 18 goes below a fourth threshold value (for example 3°C) which is lower than said second threshold value.
  • a first threshold value for example 4°C
  • second threshold value for example 20°C
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13; whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13.
  • the fourth threshold value is always greater than the second threshold value.
  • the heat exchanger 18 finalizes only the superheating of the refrigerant.
  • the liquid state portion of the refrigerant coming out from the evaporator 13 is excessive, and the internal heat exchanger 18 is not able to finalize the evaporation of low-pressure refrigerant and afterwards superheat the refrigerant directed towards the suction of refrigerant compressing device 15.
  • the laundry dryer 1 is again provided with three temperature sensors located, respectively, at refrigerant-inlet of the evaporator 13, at refrigerant-outlet of the evaporator 13, and finally at low-pressure refrigerant outlet of heat exchanger 18 to measure the corresponding refrigerant temperatures.
  • the refrigerant temperature at low-pressure refrigerant inlet of heat exchanger 18, in fact, is to be considered equal to the refrigerant temperature at refrigerant-outlet of heat exchanger 13.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the temperature drop of the refrigerant flowing in the high-pressure side of internal heat exchanger 18.
  • the drop of the refrigerant temperature at the high-pressure side of internal heat exchanger 18 is very high when the evaporator 13 is in a flooded condition, because the high-temperature and high-pressure refrigerant flowing through internal heat exchanger 18 must transfer to the low-pressure refrigerant flowing through the same heat exchanger enough heat to finalize both the evaporation and the superheating of the refrigerant.
  • the drop of the refrigerant temperature at the high-pressure side of internal heat exchanger 18 is much higher when the evaporator 13 does not finalize the evaporation of the refrigerant within itself, i.e. when heat exchanger 13 is in a flooded condition, than when the evaporator 13 finalizes evaporation of the refrigerant within itself.
  • central control unit 7 of laundry dryer 1 can measure the temperature drop of the refrigerant flowing in the high-pressure side of internal heat exchanger 18, and, when the hot-air generator is in the steady-state working phase, it can switch the cooling fan 20 on and off (i.e. adjusts the "vapor quality" of the refrigerant coming out of heat exchanger 13), so as to keep the temperature drop of the refrigerant flowing in the high-pressure side of internal heat exchanger 18 within a predetermined temperature range whose upper and lower ends are both higher than 0°C.
  • This temperature range assures that the complete vaporization and superheating of the refrigerant takes place inside internal heat exchanger 18, and that the "vapor quality" of the refrigerant coming out of the evaporator 13 is lower than 1 and ranges between 0,40 and 1 .
  • this temperature range are conveniently selected so as to assure the "vapor quality" of the refrigerant coming out of heat exchanger 13 preferably, though not necessarily, ranges between 0,80 and 0,99. In the example shown, in particular, this temperature range extends preferably, though not necessarily, from 3°C to 20°C.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13, whenever the temperature drop of the refrigerant flowing in the high-pressure side of internal heat exchanger 18 goes below a first threshold value (for example 3°C); and deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13, whenever the temperature drop of the refrigerant flowing in the high-pressure side of internal heat exchanger 18 exceeds a second threshold value (for example 20°C) which is higher than said first threshold value.
  • a first threshold value for example 3°C
  • the laundry dryer 1 is provided with two temperature sensors located, respectively, at high-pressure refrigerant inlet and at high-pressure refrigerant outlet of internal heat exchanger 18 to measure the corresponding refrigerant temperatures.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18.
  • the increase of the refrigerant temperature flowing in the low-pressure side of the internal heat exchanger 18 is much higher when the evaporator 13 finalizes the refrigerant evaporation, than when the evaporator 13 does not finalize the refrigerant evaporation and, therefore, operates in a flooded condition.
  • the refrigerant flowing in the low-pressure side of internal heat exchanger 18 is merely subjected to superheating.
  • the refrigerant flowing in the low-pressure side of internal heat exchanger 18 is firstly subjected to a complete evaporation and afterwards is subjected to superheating.
  • central control unit 7 of laundry dryer 1 can measure the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18, and, when the hot-air generator is in the steady-state working phase, it can continuously switch on and off the cooling fan 20 so as to keep the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18 within a given temperature range whose ends are both higher than 0°C.
  • the upper and lower ends of this temperature range are properly selected to assure that the vaporization of the refrigerant is finalized in internal heat exchanger 18, and that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • the temperature range extends preferably, though not necessarily, from 3°C to 20°C.
  • central control unit 7 may be preferably, though not necessarily, structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18 goes above a first threshold value (for example 20°C); and deactivates the cooling fan 20 for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the temperature rise of the refrigerant flowing in the low-pressure side of internal heat exchanger 18 goes below a second threshold value (for example 3°C) which is lower than said first threshold value.
  • a first threshold value for example 20°C
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13.
  • the first and the second threshold value are conveniently selected so to assure that the "vapor quality" of the refrigerant coming out of the evaporator 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • the laundry dryer 1 is provided with two temperature sensors located, respectively, at high-pressure refrigerant inlet and at high-pressure refrigerant outlet of internal heat exchanger 18 to measure the corresponding refrigerant temperatures.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in a flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the refrigerant temperature measured at low-pressure refrigerant outlet of internal heat exchanger 18, or at suction of refrigerant compressing device 15.
  • the refrigerant temperature in fact, is roughly the same in both places.
  • a too low temperature of the refrigerant coming out of the low-pressure refrigerant outlet of internal heat exchanger 18 implies that the internal heat exchanger 18 is not able to sufficiently superheat the refrigerant arriving from the evaporator 13. This, in turn, implies that an excessive amount of the heat arriving from the high-pressure refrigerant is used for finalizing the evaporation of the low-pressure refrigerant, thus too much liquid-state refrigerant is coming out of evaporator 13.
  • central control unit 7 of laundry dryer 1 may be preferably, though not necessarily, structured/programmed to measure the refrigerant temperature at low-pressure refrigerant outlet of internal heat exchanger 18, and to continuously switch the cooling fan 20 on and off so as to keep the temperature of the refrigerant at suction of refrigerant compressing device 15, or at low-pressure refrigerant outlet of internal heat exchanger 18, within a given temperature range whose upper and lower ends are experimentally determined to assure that refrigerant vaporization is finalized inside internal heat exchanger 18, and that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is lower than 1 and ranges between 0,40 and 1 .
  • This temperature range strictly depend on the structure of heat-pump assembly 11, namely of heat exchangers 13 and 18, and are conveniently selected so that the "vapor quality" of the refrigerant coming out of the evaporator 13 ranges preferably, though not necessarily, between 0,80 and 0,99.
  • the temperature range extends preferably, though not necessarily, between 20°C and 40°C.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the refrigerant temperature at suction of refrigerant compressing device 15 goes above a predetermined first threshold value (for example 35°C); and deactivates the cooling fan 20, or minimizes the revolving speed of cooling fan 20, for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the refrigerant temperature at suction of refrigerant compressing device 15 goes below a given predetermined second threshold value (for example 30°C) which is lower that said first threshold value.
  • a predetermined first threshold value for example 35°C
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13; whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13.
  • first and second threshold values are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • central control unit 7 of laundry dryer 1 is structured/programmed to keep the cooling fan 20 switched on when the refrigerant temperature at suction of refrigerant compressing device 15 gets too warm (for example it moves above 35°C); and to keep the cooling fan 20 switched off when the refrigerant temperature at suction of refrigerant compressing device 15 gets too cold (for example it moves below 30°C).
  • the laundry dryer 1 is provided with a temperature sensor (not shown) located at suction of refrigerant compressing device 15.
  • central control unit 7 maintains, when hot-air generator 5 is in the steady-state working phase, the evaporator 13 in flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the refrigerant temperature measured at refrigerant-inlet of condenser 14, i.e. of the air/refrigerant heat exchanger 14, or at delivery of refrigerant compressing device 15.
  • the refrigerant temperature in fact, is the same in both places.
  • thermodynamic compression in turn, depends on some mechanical features of the refrigerant compressing device 15, namely the compression ratio, thus the refrigerant temperature measured at refrigerant-inlet of condenser 14, or at delivery of refrigerant compressing device 15, depends on the temperature of the refrigerant at suction of the refrigerant compressing device 15.
  • a too low temperature of the refrigerant coming out of the refrigerant compressing device 15 implies that internal heat exchanger 18 is not able to sufficiently superheat the refrigerant arriving from the evaporator 13, and that therefore too much liquid-state refrigerant is coming out of the evaporator 13; whereas a too high temperature of the refrigerant coming out of the refrigerant compressing device 15 implies that an excessive superheating of the low-pressure refrigerant is taking place inside internal heat exchanger 18, and that therefore too few liquid-state refrigerant is coming out of the evaporator 13.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed to measure the temperature of the refrigerant at refrigerant-inlet of condenser 14, and to continuously switch on and off the cooling fan 20 so as to keep the temperature of the refrigerant at refrigerant-inlet of condenser 14, or at delivery of refrigerant compressing device 15, within a given temperature range whose upper and lower ends are experimentally determined to assure that refrigerant vaporization is finalized inside internal heat exchanger 18, and that the "vapor quality" of the refrigerant coming out of the evaporator 13 is lower than 1 and ranges between 0,40 and 1 .
  • the upper and lower ends of this temperature range strictly depend on the structure of heat-pump assembly 11, namely of the heat exchangers 13 and 18 and of the refrigerant compressing device 15, and are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 ranges preferably, though not necessarily, between 0,80 and 0,99.
  • the temperature range extends preferably, though not necessarily, between 60°C and 120°C.
  • central control unit 7 of laundry dryer 1 is structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the refrigerant temperature at delivery of refrigerant compressing device 15 moves above a predetermined first threshold value (for example 95°C); and deactivates the cooling fan 20, or minimizes the revolving speed of cooling fan 20, for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the refrigerant temperature at delivery of refrigerant compressing device 15 moves below a given predetermined second threshold value (for example 90°C) which is lower that said first threshold value.
  • a predetermined first threshold value for example 95°C
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13.
  • first and second threshold values are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • central control unit 7 of laundry dryer 1 is structured/programmed to keep the cooling fan 20 switch on when the refrigerant temperature at delivery of refrigerant compressing device 15, or at refrigerant-inlet of condenser 14, gets too warm (for example it moves above 95°C); and to keep the cooling fan 20 switch off when the refrigerant temperature at delivery of refrigerant compressing device 15, or at refrigerant-inlet of condenser 14, gets too cold (for example it moves below 90°C).
  • the laundry dryer 1 is provided with a temperature sensor (not shown) located at delivery of refrigerant compressing device 15 or at refrigerant-inlet of condenser 14.
  • the central control unit 7 of laundry dryer 1 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the refrigerant temperature measured at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18.
  • the temperature of the refrigerant coming out of refrigerant outlet of auxiliary heat exchanger 19 is strictly correlated to the temperature of the refrigerant coming out of the evaporator 13.
  • a too low temperature of the refrigerant coming out of the refrigerant outlet of auxiliary heat exchanger 19 implies that internal heat exchanger 18 is not able to sufficiently superheat the refrigerant arriving from the evaporator 13, and that too much liquid-state refrigerant is coming out of the evaporator 13; whereas a too high temperature of the refrigerant coming out of the refrigerant outlet of auxiliary heat exchanger 19 implies that an excessive superheating of the low-pressure refrigerant is taking place inside internal heat exchanger 18, and that too few liquid-state refrigerant is coming out of the evaporator 13.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed to measure the refrigerant temperature at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18, and to continuously switch the cooling fan 20 on and off so as to keep the temperature of the refrigerant at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18, within a given temperature range whose upper and lower ends are experimentally determined to assure that refrigerant vaporization is finalized inside internal heat exchanger 18, and that the "vapor quality" of the refrigerant coming out of the evaporator 13 is lower than 1 and ranges between 0,40 and 1 .
  • the upper and lower ends of this temperature range strictly depend on the structure of heat-pump assembly 11, are both considerably above 0°C, and are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 ranges preferably, though not necessarily, between 0,80 and 0,99.
  • the temperature range extends preferably, though not necessarily, between 40°C and 70°C.
  • central control unit 7 of laundry dryer 1 is structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the refrigerant temperature at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18, moves above a predetermined first threshold value (for example 60°C); and deactivates the cooling fan 20, or minimizes the revolving speed of cooling fan 20, for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the refrigerant at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18, moves below a given predetermined second threshold value (for example 55°C) which is lower that said first threshold value.
  • a predetermined first threshold value for example 60°C
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13.
  • First and second threshold values are conveniently selected so that the "vapor quality" of the refrigerant coming out of the evaporator 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • central control unit 7 of laundry dryer 1 is structured/programmed to keep the cooling fan 20 switch on when the refrigerant temperature at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18, gets too warm (for example it moves above 60°C); and to keep the cooling fan 20 switch off when the refrigerant temperature at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18, gets too cold (for example it moves below 55°C).
  • the laundry dryer 1 is provided with a temperature sensor (not shown) located at refrigerant outlet of auxiliary heat exchanger 19, or at high-pressure refrigerant inlet of heat exchanger 18.
  • the central control unit 7 of laundry dryer 1 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the refrigerant temperature measured at high-pressure refrigerant outlet of internal heat exchanger 18.
  • the temperature of the refrigerant coming out of the high-pressure refrigerant outlet of internal heat exchanger 18 is strictly correlated to the temperature of the refrigerant coming out of the evaporator 13.
  • a too low temperature of the refrigerant coming out of the high-pressure refrigerant outlet of internal heat exchanger 18 implies that internal heat exchanger 18 is not able to sufficiently superheat the low-pressure refrigerant arriving from the evaporator 13, and that therefore a too much liquid-state refrigerant is coming out of the evaporator 13;
  • a too high temperature of the refrigerant coming out of the high-pressure refrigerant outlet of internal heat exchanger 18 implies that an excessive superheating of the low-pressure refrigerant is taking place inside internal heat exchanger 18, and that therefore a too few liquid-state refrigerant is coming out of the evaporator 13.
  • central control unit 7 of laundry dryer 1 may be preferably, though not necessarily, structured/programmed to measure the refrigerant temperature at high-pressure refrigerant outlet of internal heat exchanger 18, and to continuously switch the cooling fan 20 on and off so as to keep the temperature of the refrigerant at high-pressure refrigerant outlet of internal heat exchanger 18 within a given temperature range, whose upper and lower ends are experimentally determined to assure that refrigerant vaporization is finalized inside internal heat exchanger 18, and that the "vapor quality" of the refrigerant coming out of the evaporator 13, i.e. of the air/refrigerant heat exchanger 13, is lower than 1 and ranges between 0,40 and 1 .
  • the upper and lower ends of this temperature range strictly depend on the structure of heat-pump assembly 11, are both considerably above 0°C, and are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 ranges preferably, though not necessarily, between 0,80 and 0,99.
  • the temperature range extends preferably, though not necessarily, between 25°C and 65°C.
  • central control unit 7 of laundry dryer 1 is structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the refrigerant temperature at high-pressure refrigerant outlet of internal heat exchanger 18 moves above a predetermined first threshold value (for example 40°C); and deactivates the cooling fan 20, or minimizes the revolving speed of cooling fan 20, for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of evaporator 13, whenever the refrigerant temperature at high-pressure refrigerant outlet of internal heat exchanger 18 moves below a given predetermined second threshold value (for example 35°C) which is lower that said first threshold value.
  • a predetermined first threshold value for example 40°C
  • cooling fan 20 drives below 1, i.e. reduces, the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13; whereas deactivation of cooling fan 20 brings back to 1, i.e. increases, the "vapor quality" of the refrigerant at refrigerant-outlet of the evaporator 13.
  • First and second threshold values are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • central control unit 7 of laundry dryer 1 is structured/programmed to keep the cooling fan 20 switch on when the refrigerant temperature at high-pressure refrigerant outlet of internal heat exchanger 18 gets too warm (for example it moves above 40°C); and to keep the cooling fan 20 switch off when the refrigerant temperature at high-pressure refrigerant outlet of internal heat exchanger 18 gets too cold (for example it moves below 35°C).
  • the laundry dryer 1 is provided with a temperature sensor (not shown) located at high-pressure refrigerant outlet of heat exchanger 18.
  • the central control unit 7 of laundry dryer 1 maintains, when hot-air generator 5 is in the steady-state working phase, the heat exchanger 13 in flooded condition via a selected activation and deactivation of cooling fan 20 on the basis of the current temperature of the airflow f coming out of condenser 14, i.e. of the air/refrigerant heat exchanger 14, directed back into revolving drum 3.
  • the temperature of the airflow f entering into revolving drum 3 is strictly correlated to the temperature of the high-pressure refrigerant entering into the condenser 14 of heat-pump assembly 11.
  • an excessive reduction of the temperature of the airflow f entering into revolving drum 3 implies that internal heat exchanger 18 is not able to sufficiently superheat the low-pressure refrigerant arriving from the evaporator 13, and that, therefore, too much liquid-state refrigerant is coming out of the evaporator 13.
  • an excessive increase of the temperature of the airflow f entering into revolving drum 3 implies that an excessive superheating of the low-pressure refrigerant is taking place inside internal heat exchanger 18, and that, therefore, too few liquid-state refrigerant is coming out of the evaporator 13.
  • central control unit 7 of laundry dryer 1 is preferably, though not necessarily, structured/programmed to switch on and off the cooling fan 20, so as to keep the temperature of the airflow f coming out of the air-outlet of the condenser 14, within a given temperature range whose upper and lower ends are experimentally determined to assure that refrigerant vaporization is finalized inside internal heat exchanger 18, and that the "vapor quality" of the refrigerant coming out of the condenser 13 is lower than 1 and ranges between 0,40 and 1 .
  • the upper and lower ends of this temperature range strictly depend on the structure of heat-pump assembly 11, are both considerably above 0°C, and are conveniently selected so that the "vapor quality" of the refrigerant coming out of heat exchanger 13 ranges preferably, though not necessarily, between 0,80 and 0,99.
  • the temperature range of the airflow f coming out of condenser 14 extends preferably, though not necessarily, between 50°C and 80°C.
  • central control unit 7 of laundry dryer 1 is structured/programmed
  • central control unit 7 of laundry dryer 1 activates the cooling fan 20 for reducing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the air temperature of the airflow F coming out of condenser 14 moves above a predetermined first threshold value (for example 70°C); and deactivates the cooling fan 20, or minimizes the revolving speed of cooling fan 20, for increasing the "vapor quality" of the refrigerant at refrigerant-outlet of heat exchanger 13, whenever the air temperature of the airflow F coming out of condenser 14 moves below a given predetermined second threshold value (for example 65°C) which is lower that said first threshold value.
  • a predetermined first threshold value for example 70°C
  • first and second threshold values are conveniently selected so that the "vapor quality" of the refrigerant coming out of the evaporator 13 is lower than 1 and preferably, though not necessarily, ranges between 0,80 and 0,99.
  • central control unit 7 of laundry dryer 1 is structured/programmed to keep the cooling fan 20 switch on when the air temperature of the airflow F coming out of condenser 14 gets too warm (for example it moves above 70°C); and to keep the cooling fan 20 switch off when the air temperature of the airflow F coming out of condenser 14 gets too cold (for example it moves below 65°C).
  • the laundry dryer 1 is provided with a temperature sensor (not shown) located at air-outlet of condenser 14, i.e. of air/refrigerant heat exchanger 14.
  • the central control unit 7 could use other physical quantities to determine whether the evaporator 13 is in a flooded or a non-flooded condition, such as, for example, the current temperature of the refrigerant at refrigerant inlet of the evaporator 13, or the current temperature of the refrigerant at refrigerant outlet of the evaporator 13 or the current temperature of the refrigerant at refrigerant outlet of the condenser 14 or at refrigerant inlet of auxiliary heat exchanger 19.
  • central control unit 7 controls the refrigerant vapor-quality adjusting means 17 (namely the auxiliary heat exchanger 19 and the auxiliary cooling fan 20) so to continuously adjusting/varying the refrigerant "vapor quality" at refrigerant-outlet of the evaporator 13 so as to maintain said "vapor quality" below 1, and preferably, though not necessarily, also between 0,80 and 0,99, when hot-air generator 5 is preferably in the steady-state working phase.
  • the refrigerant/refrigerant internal heat exchanger 18 is dimensioned so to finalize the evaporation of the low-pressure refrigerant and ensure that the refrigerant entering into the refrigerant compressing device 15 is in gaseous state, i.e. it is on the right side of the refrigerant vapor saturated curve F", and has a temperature higher than the corresponding refrigerant saturation temperature, i.e. it is superheated.
  • the bi-phase state refrigerant has a thermal capacity which is higher than that of a gaseous-state refrigerant, keeping the air/refrigerant heat exchanger 13 in a flooded condition allows to maximize the air cooling capacity of heat exchanger 13 and, consequently, to improve dehumidification process.
  • the potential drawback of the internal refrigerant/ refrigerant heat exchanger 18 as such is that in the steady state phase the refrigerant temperature at suction of refrigerant compressing device 15 could be higher than that of a traditional heat-pump assembly for laundry dryers, thus more power is required to the refrigerant compressing device 15 to compress the refrigerant and complete the closed thermodynamic cycle.
  • the air cooling capacity in the evaporator 13 increases more than the power required by the refrigerant compressing device 15, thus significantly improving the overall energy efficiency of heat-pump assembly 11.
  • air/refrigerant heat exchanger 19 and refrigerant/refrigerant heat exchanger 18 are "passive" components which have a very simplified structured, thus they are very cheap to produce and their incorporation into the heat-pump assembly does not significantly increase the overall production costs of the rotary-drum, heat-pump type, home laundry dryer.
  • air/refrigerant heat exchangers 13 and 14 can now be dimensioned so to have optimal performances when the hot-air generator 5 operates both in the steady state working conditions, and in the warm up working condition. Possibility barred to the traditional heat-pump type, closed-circuit, hot-air generators.
  • heat-pump assembly 11 may control the refrigerant "vapor quality" (i.e. the "gaseous-liquid ratio") at refrigerant-outlet of the evaporator 13, i.e. of the air/refrigerant heat exchanger 13, via means structured for selectively varying the flow-rate of the refrigerant flowing through evaporator 13 and internal heat exchanger 18, i.e. along the heat-pump assembly 11.
  • refrigerant "vapor quality" i.e. the "gaseous-liquid ratio”
  • These means for varying the flow-rate of the low-pressure refrigerant flowing through the evaporator 13 may comprise, for example:
  • the central control unit 7 of laundry dryer 1 controls said refrigerant flow-rate varying means so as to increase the flow-rate of the refrigerant flowing into the evaporator 13, i.e. into the heat exchanger 13, in all working conditions in which activation of cooling fan 20 was previously requested; and so as to reduce the flow-rate of the refrigerant flowing into the evaporator 13 in all working conditions in which deactivation of cooling fan 20 was previously requested.
  • the central control unit 7 of laundry dryer 1 may be structured/programmed for varying the target "vapor quality” value during the drying cycle.
  • the central control unit 7 could, for example, initially maintain the target "vapor quality” at 0,8, then rise the target "vapor quality” at 0,90, and finally rise the target "vapor quality” at 0,99 or 1, so to maximize step-by-step the performance of the drying cycle.

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Claims (42)

  1. Wäschetrockner (1), umfassend ein äußeres kastenartiges Gehäuse (2) das dazu gestaltet ist, auf dem Boden aufzuliegen, innerhalb des Gehäuses (2) einen Wäschebehälter (3), der dazu gestaltet ist, die zu trocknende Wäsche aufzunehmen, und einen Heißlufterzeuger (5) mit geschlossenem Kreislauf, der dazu gestaltet ist, einen Heißluftdampf durch den Wäschebehälter (3) zirkulieren zu lassen;
    wobei der Heißlufterzeuger (5) seinerseits Folgendes umfasst: eine Luftumwälzleitung (9) deren beide Enden mit dem Wäschebehälter (3) verbunden sind; Luftumwälzmittel (10), die dazu gestaltet sind, innerhalb der Luftumwälzleitung (9) einen Luftstrom (f) zu erzeugen, der durch den Wäschebehälter (3) strömt; und eine Wärmepumpenanordnung (11), die dazu gestaltet ist, den aus dem Wäschebehälter (3) austretenden Luftstrom (f) zu kühlen, um die Feuchtigkeit im Luftstrom (f) kondensieren zu lassen, und dann den in den Wäschebehälter (3) zurückkehrenden Luftstrom (f) zu erhitzen;
    wobei die Wärmepumpenanordnung (11) Folgendes umfasst:
    - einen ersten Luft-/Kältemittel-Wärmetauscher (13), der sich entlang der Luftumwälzleitung (9) befindet und dazu gestaltet ist, Wärme aus dem Luftstrom (f), der aus dem Wäschebehälter (3) austritt, auf das Kältemittel zu übertragen, um die Feuchtigkeit im Luftstrom (f) kondensieren zu lassen;
    - einen zweiten Luft-/Kältemittel-Wärmetauscher (14), der sich entlang der Luftumwälzleitung (9), stromabwärts des ersten Wärmetauschers (13) befindet und dazu gestaltet ist, Wärme aus dem Kältemittel auf den in den Wäschebehälter (3) zurückgerichteten Luftstrom (f) zu übertragen, um den Luftstrom (f) zu erhitzen;
    - eine Kältemittelverdichtungsvorrichtung (15), die zwischen dem Kältemittelauslass des ersten Wärmetauschers (13) und dem Kältemitteleinlass des zweiten Wärmetauschers (14) angeordnet ist und dazu gestaltet ist, das zum zweiten Wärmetauscher (14) gerichtete Kältemittel zu verdichten, sodass Kältemitteldruck und -temperatur am Kältemitteleinlass des zweiten Wärmetauschers (14) viel höher als am Kältemittelauslass des ersten Wärmetauschers (13) sind;
    - eine Kältemittelentspannungsvorrichtung (16), die zwischen dem Kältemittelauslass des zweiten Wärmetauschers (14) und dem Kältemitteleinlass des ersten Wärmetauschers (13) angeordnet ist und dazu gestaltet ist, eine Entspannung des Kältemittels zu erzeugen; und
    - einen zusätzlichen Kältemittel-/Kältemittel-Wärmetauscher (18), umfassend eine Hochdruckseite, durch die das zur Kältemittelentspannungsvorrichtung (16) gerichtete Hochdruckkältemittel strömt, und eine Niederdruckseite, durch die das aus dem ersten Wärmetauscher (13) austretende Niederdruckkältemittel strömt, und der so gestaltet ist, dass die Hochdruck- und die Niederdruckseite terminal miteinander gekoppelt sind, um eine Wärmeübertragung vom Hochdruck- und Hochtemperaturkältemittel auf das Niederdruck- und Niedertemperaturkältemittel zu ermöglichen; wobei der Wäschetrockner (1) dadurch gekennzeichnet ist, dass die Wärmepumpenanordnung (11) zusätzlich Folgendes umfasst:
    - Kältemitteldampfqualitätseinstellmittel (17), die dazu gestaltet sind, das am Kältemittelauslass des ersten Wärmetauschers (13) bestehende Verhältnis zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge durch selektives Maximieren oder Minimieren des Kühlens des zur Kältemittelentspannungsvorrichtung (16) gerichteten Kältemittels einzustellen;
    - Detektionsmittel, die dazu in der Lage sind, den aktuellen Wert zumindest einer dem Kältemittel und/oder dem Luftstrom (f) zugeordneten physikalischen Größe zu messen;
    - eine zentrale Steuereinheit (7), die dazu gestaltet ist, die Kältemitteldampfqualitätseinstellmittel (17) gemäß dem zeitlichen Verlauf der zumindest einen physikalischen Größe zu steuern;
    - wobei die zentrale Steuereinheit (7) dazu gestaltet ist, die Kältemitteldampfqualitätseinstellmittel (17) so zu steuern, dass das Verhältnis selektiv unter oder gleich 1 gehalten wird.
  2. Wäschetrockner nach Anspruch 1, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels am Kältemitteleinlass oder am Kältemittelauslass des ersten Luft-/Kältemittel-Wärmetauschers (13) und/oder der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels ist.
  3. Wäschetrockner nach Anspruch 1, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels am Niederdruckkältemitteleinlass oder am Niederdruckkältemittelauslass der Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) und/oder die Temperatur und/oder der Druck des Kältemittels am Hochdruckkältemitteleinlass oder am Hochdruckkältemittelauslass der Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) und/oder der Temperaturanstieg des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels und/oder der Temperaturabfall des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels ist.
  4. Wäschetrockner nach Anspruch 1, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels auf der Saugseite und/oder auf der Druckseite der Kältemittelverdichtungsvorrichtung (15) ist.
  5. Wäschetrockner nach Anspruch 1, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels am Kältemitteleinlass oder am Kältemittelauslass des zweiten Luft-/Kältemittel-Wärmetauschers (14) ist.
  6. Wäschetrockner nach Anspruch 1, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Feuchtigkeitsgrad des in den Wäschebehälter (3) eintretenden oder aus selbigem austretenden Luftstroms (f) ist.
  7. Wäschetrockner nach Anspruch 1, dadurch gekennzeichnet, dass die zentrale Steuereinheit (7) dazu gestaltet ist, die Kältemitteldampfqualitätseinstellmittel (17) so zu steuern, dass das am Kältemittelauslass des ersten Wärmetauschers (13) bestehende Verhältnis zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge zwischen 0,80 und 0,99 gehalten wird.
  8. Wäschetrockner nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Kältemitteldampfqualitätseinstellmittel (17) Hochdruckkältemittel-Kühlmittel (19, 20) umfassen, die dazu gestaltet sind, das vom zweiten Wärmetauscher (14) zur Kältemittelentspannungsvorrichtung (16) strömende Hochdruckkältemittel selektiv abzukühlen.
  9. Wäschetrockner nach Anspruch 8, dadurch gekennzeichnet, dass die Hochdruckkältemittel-Kühlmittel (19, 20) einen dritten Luft-/Kältemittel-Wärmetauscher (19) umfassen, der mit dem zweiten Luft-/Kältemittel-Wärmetauscher (14) in Reihe geschaltet ist.
  10. Wäschetrockner nach Anspruch 9, dadurch gekennzeichnet, dass die Hochdruckkältemittel-Kühlmittel (17) außerdem eine zusätzliche Kältemittel-/Kältemittel-Wärmetauscher Lüftungsvorrichtung (20) umfassen, die dazu gestaltet ist, einen Kühlluftstrom (w) zum Körper des dritten Luft-/Kältemittel-Wärmetauschers (19) zu kanalisieren.
  11. Wäschetrockner nach einem der Ansprüche 1 - 7, dadurch gekennzeichnet, dass die Kältemitteldampfqualitätseinstellmittel (17) Kältemitteldurchflussrateneinstellmittel umfassen, die dazu gestaltet sind, die Durchflussrate des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Niederdruckkältemittels zu variieren.
  12. Wäschetrockner nach Anspruch 11, dadurch gekennzeichnet, dass die Kältemitteldurchflussrateneinstellmittel eine Kältemittelverdichtungsvorrichtung mit variabler Geschwindigkeit oder ein elektrisch betriebenes Kältemittelentspannungsventil oder ein elektrisch betriebenes Entspannungssystem mit mehreren Kapillarrohren umfassen.
  13. Wäschetrockner nach Anspruch 3, dadurch gekennzeichnet, dass die Detektionsmittel Sensormittel umfassen, die dazu gestaltet sind, die Temperatur und/oder den Druck des Kältemittels am Niederdruckkältemitteleinlass des Kältemittel-/Kältemittel-Wärmetauschers (18) und/oder am Niederdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) und/oder am Hochdruckkältemitteleinlass des Kältemittel-/Kältemittel-Wärmetauschers (18) und/oder am Hochdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) zu detektieren.
  14. Verfahren zum Betreiben eines Wäschetrockners (1), umfassend ein äußeres kastenartiges Gehäuse (2), das dazu gestaltet ist, auf dem Boden aufzuliegen, und innerhalb des Gehäuses (2) einen Wäschebehälter (3), der dazu gestaltet ist, die zu trocknende Wäsche aufzunehmen, und einen Heißlufterzeuger (5) mit geschlossenem Kreislauf, der dazu gestaltet ist, einen Heißluftdampf durch den Wäschebehälter (3) zirkulieren zu lassen; wobei der Heißlufterzeuger (5) mit einer Wärmepumpenanordnung (11) bereitgestellt ist, die dazu gestaltet ist, den aus dem Wäschebehälter (3) austretenden Luftstrom (f) zu kühlen, um die Feuchtigkeit im Luftstrom (f) kondensieren zu lassen, und dann den in den Wäschebehälter (3) zurückkehrenden Luftstrom (f) zu erhitzen; wobei die Wärmepumpenanordnung (11) Folgendes umfasst:
    einen ersten Luft-/Kältemittel-Wärmetauscher (13), der dazu gestaltet ist, Wärme aus dem Luftstrom (f), der aus dem Wäschebehälter (3) austritt, auf ein Niederdruckkältemittel zu übertragen, um die Feuchtigkeit im Luftstrom (f) kondensieren zu lassen;
    einen zweiten Luft-/Kältemittel-Wärmetauscher (14), der dazu gestaltet ist, Wärme aus einem Hochdruckkältemittel auf den in den Wäschebehälter (3) zurückgeleiteten Luftstrom (f) zu übertragen, um den Luftstrom (f) zu erhitzen; eine Kältemittelverdichtungsvorrichtung (15), die zwischen dem Kältemittelauslass des ersten Wärmetauschers (13) und dem Kältemitteleinlass des zweiten Wärmetauschers (14) angeordnet ist und dazu gestaltet ist, das zum zweiten Wärmetauscher (14) gerichtete Kältemittel zu verdichten, sodass Kältemitteldruck und -temperatur am Kältemitteleinlass des zweiten Wärmetauschers (14) viel höher als am Kältemittelauslass des ersten Wärmetauschers (13) sind;
    eine Kältemittelentspannungsvorrichtung (16), die zwischen dem Kältemittelauslass des zweiten Wärmetauschers (14) und dem Kältemitteleinlass des ersten Wärmetauschers (13) angeordnet ist und dazu gestaltet ist, eine Entspannung des Kältemittels zu erzeugen; und einen zusätzlichen Kältemittel-/Kältemittel-Wärmetauscher (18), umfassend eine Hochdruckseite, durch die das zur Kältemittelentspannungsvorrichtung (16) gerichtete Hochdruckkältemittel strömt, und eine Niederdruckseite, durch die das aus dem ersten Wärmetauscher (13) austretende Niederdruckkältemittel strömt, und das so gestaltet ist, dass die Hochdruck- und die Niederdruckseite terminal miteinander gekoppelt sind, um eine Wärmeübertragung vom Hochdruck- und Hochtemperaturkältemittel auf das Niederdruck- und Niedertemperaturkältemittel zu ermöglichen;
    wobei das Betriebsverfahren dadurch gekennzeichnet ist, dass es die folgenden Schritte umfasst:
    - Messen des aktuellen Werts zumindest einer dem Kältemittel und/oder dem Luftstrom (f) zugeordneten physikalischen Größe,
    - basierend auf dem zeitlichen Verlauf der zumindest einen physikalischen Größe, Steuern der Kältemitteldampfqualitätseinstellmittel (17), die dazu gestaltet sind, am Kältemittelauslass des ersten Wärmetauschers (13) das Verhältnis zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge durch selektives Maximieren oder Minimieren des Kühlens des zur Kältemittelentspannungsvorrichtung (16) gerichteten Kältemittels einzustellen,
    Zuführen des Kältemittels zur Hochdruckseite und zur Niederdruckseite des zusätzlichen Kältemittel-/Kältemittel-Wärmetauschers (18), um Wärme von dem durch die Hochdruckseite strömenden Hochdruck- und Hochtemperaturkältemittel auf das durch die Niederdruckseite strömende Niederdruck- und Niedertemperaturkältemittel zu übertragen,
    - wobei die Kältemitteldampfqualitätseinstellmittel (17) so gesteuert werden, dass das Verhältnis zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge selektiv unter oder gleich 1 gehalten wird.
  15. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 14, dadurch gekennzeichnet, dass die Kältemitteldampfqualitätseinstellmittel (17) so gesteuert werden, dass das am Kältemittelauslass des ersten Wärmetauschers (13) bestehende Verhältnis zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge selektiv zwischen 0,80 und 0,99 gehalten wird.
  16. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 14 oder 15, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels am Kältemitteleinlass oder am Kältemittelauslass des ersten Luft-/Kältemittel-Wärmetauschers (13) und/oder der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels ist.
  17. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 14 oder 15, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels am Niederdruckkältemitteleinlass oder am Niederdruckkältemittelauslass der Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) und/oder die Temperatur und/oder der Druck des Kältemittels am Hochdruckkältemitteleinlass oder am Hochdruckkältemittelauslass der Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) und/oder der Temperaturanstieg des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels und/oder der Temperaturabfall des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels ist.
  18. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 14 oder 15, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels auf der Saugseite und/oder auf der Druckseite der Kältemittelverdichtungsvorrichtung (15) ist.
  19. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 14 oder 15, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Druck des Kältemittels am Kältemitteleinlass oder am Kältemittelauslass des zweiten Luft-/Kältemittel-Wärmetauschers (14) ist.
  20. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 14 oder 15, dadurch gekennzeichnet, dass die zumindest eine physikalische Größe die Temperatur und/oder der Feuchtigkeitsgrad des in den Wäschebehälter (3) eintretenden oder aus selbigem austretenden Luftstroms (f) ist.
  21. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 16, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe die Schritte des Messens des aktuellen Drucks und der aktuellen Temperatur des Kältemittels am Kältemittelauslass des ersten Wärmetauschers (13) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Berechnens der Sättigungstemperatur des Kältemittels basierend auf dem aktuellen Kältemitteldruck und den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Temperatur des Kältemittels am Kältemittelauslass des ersten Wärmetauschers (13) innerhalb eines vorbestimmten ersten Temperaturbereichs, der sich unterhalb der Kältemittelsättigungstemperatur befindet, gehalten wird.
  22. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 21, dadurch gekennzeichnet, dass der Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) entweder den Schritt
    - des Erhöhens des Verhältnisses zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge umfasst, wenn die Differenz zwischen der berechneten Kältemittelsättigungstemperatur und der am Kältemittelauslass des ersten Wärmetauschers (13) gemessenen Kältemitteltemperatur die Obergrenze des ersten Temperaturbereichs überschreitet, oder
    - des Verringerns des Verhältnisses umfasst, wenn die Differenz zwischen der berechneten Kältemittelsättigungstemperatur und der gemessenen Kältemitteltemperatur die Untergrenze des ersten Temperaturbereichs unterschreitet.
  23. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe die Schritte des Messens des aktuellen Drucks und der aktuellen Temperatur des Kältemittels am Niederdruckkältemittelauslass des zusätzlichen Kältemittel-/Kältemittel-Wärmetauschers (18) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Berechnens der Sättigungstemperatur des Kältemittels basierend auf dem aktuellen Kältemitteldruck und den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Temperatur des Kältemittels am Niederdruckkältemittelauslass des zusätzlichen Kältemittel-/Kältemittel-Wärmetauschers (18) innerhalb eines vorbestimmten zweiten Temperaturbereichs, der sich über der Kältemittelsättigungstemperatur befindet, gehalten wird.
  24. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 23, dadurch gekennzeichnet, dass der Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) entweder den Schritt
    - des Erhöhens des Verhältnisses zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge umfasst, wenn die Differenz zwischen der am Niederdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) gemessenen Kältemitteltemperatur und der berechneten Kältemittelsättigungstemperatur die Untergrenze des zweiten Temperaturbereichs unterschreitet, oder
    - des Verringerns des Verhältnisses umfasst, wenn die Differenz zwischen der am Niederdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) gemessenen Kältemitteltemperatur und der berechneten Kältemittelsättigungstemperatur die Obergrenze des zweiten Temperaturbereichs überschreitet.
  25. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe die Schritte des Messens des Temperaturanstiegs des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels und des Messens des Temperaturabfalls des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Differenz zwischen dem Temperaturanstieg des in der Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels und dem Temperaturabfall des in der Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18)strömenden Kältemittels innerhalb eines vorbestimmten dritten Temperaturbereichs gehalten wird.
  26. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 25, dadurch gekennzeichnet, dass der Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) entweder den Schritt
    - des Verringerns des Verhältnisses zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge umfasst, wenn der Temperaturabfall des in der Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels den Temperaturanstieg des in der Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18)strömenden Kältemittels um einen vorbestimmten ersten Toleranzwert überschreitet, oder
    - des Erhöhens des Verhältnisses umfasst, wenn der Temperaturabfall des in der Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels den Temperaturanstieg des in der Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels um einen vorbestimmten zweiten Toleranzwert überschreitet.
  27. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 25 oder 26, dadurch gekennzeichnet, dass der Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) ferner den Schritt des Erhöhens des Verhältnisses zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge umfasst, wenn der Temperaturanstieg des Kältemittels in der Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) einen vorbestimmten dritten Toleranzwert, der größer als Null ist, unterschreitet.
  28. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 16, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens des Temperaturanstiegs oder -abfalls des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels innerhalb eines vorbestimmten engen vierten Temperaturbereichs, der unmittelbar über 0°C liegt, gehalten wird.
  29. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 28, dadurch gekennzeichnet, dass der vierte Temperaturbereich innerhalb von 0°C und 5°C eingeschlossen ist.
  30. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 28 oder 29, dadurch gekennzeichnet, dass der Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) entweder den Schritt
    - des Erhöhens des Verhältnisses zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge umfasst, wenn der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels die Untergrenze des vierten Temperaturbereichs unterschreitet, oder
    - des Verringerns des Verhältnisses umfasst, wenn der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels die Obergrenze des vierten Temperaturbereichs überschreitet.
  31. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 18 und einem jeglichen der Ansprüche 29 - 31, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe ferner den Schritt des Messens des Temperaturabfalls des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass der Temperaturabfall des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauscher (18) strömenden Kältemittels innerhalb eines fünften Temperaturbereichs, dessen oberes und unteres Ende beide höher als 0°C sind, gehalten wird.
  32. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 31, dadurch gekennzeichnet, dass der Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) entweder den Schritt
    - des Verringerns des Verhältnisses zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge umfasst, wenn der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels die Obergrenze des vierten Temperaturbereichs überschreitet und der Temperaturabfall des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18)strömenden Kältemittels die Untergrenze des fünften Grenzwerts unterschreitet; oder
    - des Erhöhens des Verhältnisses umfasst, wenn der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels die Untergrenze des vierten Temperaturbereichs unterschreitet und der Temperaturabfall des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels die Obergrenze des fünften Grenzwerts überschreitet.
  33. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17 und einem jeglichen der Ansprüche 29-31, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe ferner den Schritt des Messens des Temperaturanstiegs des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass ferner der Temperaturanstieg des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels innerhalb eines sechsten Temperaturbereichs, dessen obere und untere Enden sich über denen des vierten Temperaturbereichs befinden, gehalten wird.
  34. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 33, dadurch gekennzeichnet, dass der Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) entweder den Schritt
    - des Verringerns des Verhältnisses zwischen der Kältemittelmenge in gasförmigem Zustand und der Kältemittelgesamtmenge umfasst, wenn der Temperaturanstieg oder -abfall des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels die Obergrenze des vierten Temperaturbereichs überschreitet und der Temperaturanstieg des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels die Obergrenze des sechsten Grenzwerts überschreitet; oder
    - des Erhöhens des Verhältnisses, wenn der Temperaturanstieg des durch den ersten Luft-/Kältemittel-Wärmetauscher (13) strömenden Kältemittels die Untergrenze des vierten Temperaturbereichs unterschreitet und der Temperaturanstieg des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels die Untergrenze des sechsten Grenzwerts unterschreitet.
  35. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens des Temperaturabfalls des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass der Temperaturabfall des durch die Hochdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels innerhalb eines siebenten Temperaturbereichs, dessen oberes und unteres Ende beide höher als 0°C sind, gehalten wird.
  36. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens des Temperaturanstiegs des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass der Temperaturanstieg des durch die Niederdruckseite des Kältemittel-/Kältemittel-Wärmetauschers (18) strömenden Kältemittels innerhalb eines achten Temperaturbereichs, dessen oberes und unteres Ende beide höher als 0°C sind, gehalten wird.
  37. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens der Kältemitteltemperatur am Niederdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Kältemitteltemperatur am Niederdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) innerhalb eines vorbestimmten neunten Temperaturbereichs gehalten wird.
  38. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 19, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens der Kältemitteltemperatur am Kältemitteleinlass des zweiten Luft-/Kältemittel-Wärmetauschers (14) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Kältemitteltemperatur am Kältemitteleinlass des zweiten Luft-/Kältemittel-Wärmetauschers (14) innerhalb eines vorbestimmten zehnten Temperaturbereichs gehalten wird.
  39. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 18, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens der Kältemitteltemperatur auf der Druckseite der Kältemittelverdichtungsvorrichtung (15) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Kältemitteltemperatur auf der Druckseite der Kältemittelverdichtungsvorrichtung (15) innerhalb eines vorbestimmten zehnten Temperaturbereichs gehalten wird.
  40. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens der Kältemitteltemperatur am Hochdruckkältemitteleinlass des Kältemittel-/Kältemittel-Wärmetauschers (18) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Kältemitteltemperatur am Hochdruckkältemitteleinlass des Kältemittel-/Kältemittel-Wärmetauschers (18) innerhalb eines vorbestimmten elften Temperaturbereichs gehalten wird.
  41. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 17, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens der Kältemitteltemperatur am Hochdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Kältemitteltemperatur am Hochdruckkältemittelauslass des Kältemittel-/Kältemittel-Wärmetauschers (18) innerhalb eines vorbestimmten zwölften Temperaturbereichs gehalten wird.
  42. Verfahren zum Betreiben eines Wäschetrockners nach Anspruch 20, dadurch gekennzeichnet, dass der Schritt des Messens des aktuellen Werts der zumindest einen physikalischen Größe den Schritt des Messens der Temperatur des in den Wäschebehälter (3) eintretenden Luftstroms (f) umfasst; und dadurch, dass der Schritt des Steuerns der Kältemitteldampfqualitätseinstellmittel (17) den Schritt des Antreibens der Kältemitteldampfqualitätseinstellmittel (17) umfasst, so, dass die Temperatur des Luftstroms (f) innerhalb eines vorbestimmten dreizehnten Temperaturbereichs gehalten wird.
EP10197041.6A 2010-12-27 2010-12-27 Haushaltswäschetrockner mit Wärmepumpe Not-in-force EP2468944B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP10197041.6A EP2468944B1 (de) 2010-12-27 2010-12-27 Haushaltswäschetrockner mit Wärmepumpe
BR112013016443A BR112013016443A2 (pt) 2010-12-27 2011-12-21 secadora de roupas e método de operação de uma secadora de roupas
PCT/EP2011/073604 WO2012089585A1 (en) 2010-12-27 2011-12-21 Home laundry dryer
RU2013135232/12A RU2013135232A (ru) 2010-12-27 2011-12-21 Бытовое сушильное устройство для белья
US13/997,907 US20140082960A1 (en) 2010-12-27 2011-12-21 Home laundry dryer
AU2011351627A AU2011351627A1 (en) 2010-12-27 2011-12-21 Home laundry dryer
CN2011800665546A CN103348056A (zh) 2010-12-27 2011-12-21 家用干衣机

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Families Citing this family (7)

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Publication number Priority date Publication date Assignee Title
US9140396B2 (en) 2013-03-15 2015-09-22 Water-Gen Ltd. Dehumidification apparatus
WO2014146704A1 (en) * 2013-03-20 2014-09-25 Electrolux Appliances Aktiebolag Appliance for drying laundry
CN105324529B (zh) * 2013-06-24 2017-12-26 伊莱克斯家用电器股份公司 热泵式衣物干燥机
JP2016104111A (ja) * 2014-11-19 2016-06-09 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 乾燥機
JP6616594B2 (ja) * 2015-06-11 2019-12-04 東芝ライフスタイル株式会社 衣類乾燥機
CN113891642B (zh) * 2021-12-08 2022-03-04 浙江飞旋科技有限公司 散热装置及冷板散热系统
CN114892371B (zh) * 2022-06-15 2023-08-25 惠而浦（中国）股份有限公司 一种洗衣机蒸汽发生器的控制方法

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3022150B2 (ja) * 1994-04-27 2000-03-15 三洋電機株式会社 衣類乾燥機
DE4434205A1 (de) * 1994-08-31 1996-03-07 Joerg Sdrojewski Wäschetrockner
JP3557002B2 (ja) * 1995-07-14 2004-08-25 三洋電機株式会社 電気機器
JP2001120898A (ja) * 1999-10-27 2001-05-08 Matsushita Electric Ind Co Ltd ガス衣類乾燥機
JP2003075065A (ja) * 2001-09-04 2003-03-12 Matsushita Electric Ind Co Ltd ヒートポンプ式乾燥機
JP2004313765A (ja) * 2003-04-02 2004-11-11 Matsushita Electric Ind Co Ltd 乾燥装置及びその運転方法
WO2005031231A1 (en) * 2003-09-25 2005-04-07 Matsushita Electric Industrial Co. Ltd. Heat pump type drying apparatus drying apparatus and drying method
JP2005253588A (ja) * 2004-03-10 2005-09-22 Sanyo Electric Co Ltd 乾燥機
US7698911B2 (en) * 2005-11-30 2010-04-20 General Electric Company Methods and systems for detecting dryness of clothes in an appliance
DE102005062939A1 (de) * 2005-12-29 2007-07-05 BSH Bosch und Siemens Hausgeräte GmbH Hausgerät zur Pflege von Wäschestücken
JP5473922B2 (ja) * 2007-10-09 2014-04-16 ビーイー・エアロスペース・インコーポレーテッド 熱制御システム
EP1983095B1 (de) * 2008-08-08 2012-09-05 V-Zug AG Wäschetrockner mit Heizung im Wärmepumpenkreislauf
EP2284310B1 (de) * 2009-08-12 2014-07-09 Electrolux Home Products Corporation N.V. Trommeltrockner mit einer Wärmepumpe und Verfahren zur Kontrolle einer Wärmepumpe für einen Trommeltrockner

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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BR112013016443A2 (pt) 2016-09-20
CN103348056A (zh) 2013-10-09
RU2013135232A (ru) 2015-02-10
WO2012089585A1 (en) 2012-07-05
US20140082960A1 (en) 2014-03-27
EP2468944A1 (de) 2012-06-27
AU2011351627A1 (en) 2013-04-11

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