EP2594687A1 - Sèche-linge avec système de pompe à chaleur - Google Patents

Sèche-linge avec système de pompe à chaleur Download PDF

Info

Publication number: EP2594687A1
Authority: EP; European Patent Office
Prior art keywords: refrigerant; temperature; heat exchanger; inlet; delivery device
Prior art date: 2011-11-21
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.): Granted

Application number

EP11189866.4A

Other languages

German (de)

English (en)

Other versions

EP2594687B1 (fr

Inventor

Francesco Cavarretta

Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Electrolux Home Products Corp NV

Original Assignee

Electrolux Home Products Corp NV

Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)

2011-11-21

Filing date

2011-11-21

Publication date

2013-05-22

2011-11-21 Application filed by Electrolux Home Products Corp NV filed Critical Electrolux Home Products Corp NV

2011-11-21 Priority to EP11189866.4A priority Critical patent/EP2594687B1/fr

2013-05-22 Publication of EP2594687A1 publication Critical patent/EP2594687A1/fr

2014-09-10 Application granted granted Critical

2014-09-10 Publication of EP2594687B1 publication Critical patent/EP2594687B1/fr

Status Not-in-force legal-status Critical Current

2031-11-21 Anticipated expiration legal-status Critical

Images

Classifications

- 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

Definitions

the present invention relates to a laundry dryer with a heat pump system according to the preamble of claim 1.
the heat pump technology is at present the most efficient way to dry clothes in view of energy consumption.
a typical heat pump laundry dryer an air stream flows in a closed air stream circuit.
the air stream is moved by a fan, passes through a laundry chamber, which is preferably formed as a rotatable laundry drum.
the air stream removes water from wet clothes, is then cooled down and dehumidified in an evaporator or gas heater, heated up in a condenser or gas cooler and at last re-inserted into the laundry drum again.
the refrigerant is compressed by a compressor, condensed in the condenser or gas cooler, laminated in an expansion device and then vaporized in the evaporator or gas heater.
the temperatures of the air stream and the refrigerant are strictly connected to each other.
the evaporator or gas heater and the condenser or gas cooler are heat exchangers between the air stream circuit and the refrigerant circuit. If the refrigerant changes its phase, then the heat exchangers act as evaporator and condenser, respectively. If the refrigerant remains in the gas phase, then the heat exchangers act as gas heater and gas cooler, respectively.
the cycle of the heat pump laundry dryer is characterized by two phases: a transitory phase and a steady state phase.
the temperatures of the air stream and the refrigerant which are usually at an ambient temperature when the system begins to operate, increase up to a desired level.
the temperatures of the air stream and the refrigerant are kept almost constant.
a cooling fan cools down the compressor, which removes excess heat from the heat pump system, in order to keep the temperatures of the air stream and the refrigerant constant until the laundry is dried.
the traditional condenser in which the refrigerant is coming from the outlet of the compressor condensates while the air stream is heated up, is substituted by a gas cooler, in which the carbon dioxide is cooled down while the air stream is heated up.
a gas cooler At the outlet of the gas cooler there is no refrigerant in liquid state, but a gas with an increased density. After an expansion, the carbon dioxide is partially liquid and evaporates in the evaporator like the traditional refrigerants.
the heat pump system can be forced working in a totally-supercritical cycle.
the refrigerant is kept always in a gaseous phase, also in a low pressure portion of the heat pump circuit.
the evaporator acts as a gas heater, since the carbon dioxide is heated up without change of phase.
the terms evaporator and gas heater are hereinafter used as synonymous.
the heat pump system passes through a trans-critical cycle.
FIG 2 shows a temperature-entropy diagram of carbon dioxide in the trans-critical cycle.
FIG 4 shows the temperature-entropy diagram of carbon dioxide in the totally-supercritical cycle.
the temperature-entropy diagrams comprise a high pressure isobaric line 30, a low pressure isobaric line 32, a saturation curve 34 of carbon dioxide, a compression phase 36 and a lamination phase 38.
a state GH-OUT of the refrigerant at the outlet of the gas heater, a state GC-IN of the refrigerant at the inlet of the gas cooler, a state GC-OUT of the refrigerant at the outlet of the gas cooler and a state GH-IN of the refrigerant at the inlet of the gas heater are indicated in the temperature-entropy diagrams.
a state EV-OUT of the refrigerant at the outlet of the evaporator and a state EV-IN of the refrigerant at the inlet of the evaporator are also indicated in the temperature-entropy diagrams.
a gas cooling phase occurs from the state GC-IN to the state GC-OUT along the high pressure isobaric line 30.
a gas lamination phase occurs from the state GC-OUT to the state GH-IN or EV-IN, respectively, along the lamination phase 38.
a gas heating phase occurs from the state GH-IN to the state GH-OUT along the low pressure isobaric line 32.
An evaporation and superheating phase occurs from the state EV-IN to the state EV-OUT along the low pressure isobaric line 32.
a gas compression phase occurs from the state GH-OUT or EV-OUT to the state GC-IN along the compression phase 36.
the pressure of the low pressure isobaric line 32 is higher than about 71 bar (refrigerant critical pressure in case of carbon dioxide refrigerant), then the whole cycle is always in the gas phase zone, i.e. the portion of the chart is outside the saturation curve 34.
the refrigerant is heated up without phase change in the gas heater from the state GH-IN to the state GH-OUT.
the evaporation phase in which the pressure and the temperature remain constant, is avoided.
the temperature difference between the refrigerant and the air stream, which has to be cooled down for dehumidifying the moisture air stream, is reduced.
the performance of the gas heater is improved.
the increase of the pressure level in the low pressure portion of the refrigerant circuit has the advantages of the higher refrigerant flow rate and the lower difference between the pressures assuming that the pressure in the high pressure portion remains constant.
the higher refrigerant flow rate results in an increased cooling and heating capacity of the heat pump system.
the lower difference between the pressures allows a reduced power required by the compressor.
the pressure in the low pressure portion becomes higher than the critical level, i.e. the totally-supercritical cycle, then a better matching between the refrigerant and the air stream through the gas heater is achieved.
the temperature of the refrigerant at the evaporator or gas heater increases with the pressure in the low pressure portion.
the relative high temperature of the refrigerant at the evaporator or gas heater can reduce the ability of dehumidifying the air steam, which means a disadvantage for the performance of the heat pump system.
the object of the present invention is achieved by the laundry dryer according to claim 1.
the present invention allows that the refrigerant works in the low pressure portion of the refrigerant circuit at a pressure lower than the critical pressure and that the temperature of the refrigerant at the inlet of the evaporator is lower than the evaporation temperature.
the present invention allows that the refrigerant works in the low pressure portion of the refrigerant circuit at a pressure equal to or higher than the critical pressure and that the temperature of the refrigerant at the inlet of the gas heater is lower than the critical temperature of the refrigerant.
the auxiliary gas cooler is arranged outside the drying air circuit so that no heat exchange occurs between the auxiliary gas cooler and the drying air.
auxiliary fan or the water delivery device is controlled or controllable in dependence of the temperature of the refrigerant and/or the drying air.
the auxiliary fan is activated, if the temperature of the drying air at the inlet of the laundry drum exceeds a predetermined set-point temperature.
the auxiliary fan is activated, if the temperature of the refrigerant at the inlet of the gas cooler exceeds a predetermined set-point temperature.
auxiliary fan may be activated, if the temperature of the refrigerant at the inlet of the evaporator or at the inlet of the gas heater exceeds a predetermined set-point temperature.
auxiliary fan or the water delivery device is controlled or controllable in dependence of the pressure of the refrigerant.
the auxiliary fan works in an on-off mode.
the refrigerant is carbon dioxide.
the auxiliary gas cooler is a heat exchanger between the refrigerant and condensate water of the heat pump system.
the laundry dryer comprises an auxiliary fan controller or a water delivery device controller adapted to activate or deactivate the auxiliary fan and the water delivery device in response to the temperature and/or pressure of the refrigerant and/or in response to the temperature of the drying air.
the laundry dryer comprises at least one sensor for detecting the temperature of the drying air and/or the temperature refrigerant and/or the pressure of the refrigerant.
the auxiliary fan or the water delivery device is activated, if the temperature of the drying air at the inlet of the laundry treatment chamber exceeds a predetermined set-point temperature, wherein the predetermined set-point temperature is preferably in a range between 50°C and 75°C, preferably in a range between 55°C and 70°C, preferably in a range between 57°C and 65°C.
the auxiliary fan or the water delivery device is deactivated, if the temperature of the drying air at the inlet of the laundry treatment chamber becomes lower than said predetermined set-point temperature minus preferably 0°C to 5°C, minus preferably 1°C to 4°C, minus preferably 2°C to 3°C.
the auxiliary fan or the water delivery device is activated, if the temperature of the refrigerant at the outlet of the first heat exchanger exceeds a predetermined set-point temperature, wherein the predetermined set-point temperature is preferably in a range between 35°C and 60°C, preferably, in a range between 40°C and 55°C.
the auxiliary fan or the water delivery device is deactivated, if the temperature of the refrigerant at the outlet of the first heat exchanger becomes lower than said predetermined set-point temperature minus preferably 0°C to 5°C, minus preferably 1°C to 4°C, minus preferably 2°C to 3°C.
the auxiliary fan or the water delivery device is activated, if the temperature of the refrigerant at the inlet of the second heat exchanger exceeds a predetermined set-point temperature, wherein the predetermined set-point temperature is in a range preferably between 20°C and 31°C, preferably in a range between 25°C and 31°C, preferably in a range between 28°C and 31°C, and the refrigerant operates below the critical pressure in the low pressure portion of the refrigerant circuit.
the auxiliary fan or the water delivery device is deactivated, if the temperature of the refrigerant at the inlet of the second heat exchanger becomes lower than said predetermined set-point temperature minus 0°C to 5°C, preferably minus 1°C to 4°C, preferably minus 2°C to 3°C.
the auxiliary fan or the water delivery device is activated, if the temperature of the refrigerant at the inlet of the second heat exchanger exceeds a predetermined set-point temperature, wherein the predetermined set-point temperature is in a range preferably between 31°C and 40°C, preferably between 33°C and 36°C, and the refrigerant operates at least at critical pressure in the low pressure portion of the refrigerant circuit.
the auxiliary fan or the water delivery device of the auxiliary heat exchanger is deactivated, if the temperature of the refrigerant at the inlet of the second heat exchanger becomes lower than said predetermined set-point temperature minus preferably 0°C to 5°C, minus preferably 1°C to 4°C, minus preferably 2°C to 3°C.
the auxiliary fan or the water delivery device is activated, if a first condition is met and a second condition is met, wherein the first condition is met when the temperature of the refrigerant at the inlet of the second heat exchanger reaches or exceeds a predetermined temperature value and the second condition includes at least one of the following:
the second condition includes a set-point temperature range having an upper limit and a lower limit
the auxiliary fan or the water delivery device is activated when temperature of the refrigerant at the inlet of the second heat exchanger reaches or exceeds the upper limit and deactivated when the temperature of the refrigerant at the inlet of the second heat exchanger reaches or goes below the lower limit
both the upper limit and a lower limit of the second condition are lower than said predetermined temperature value of the first condition and at least the lower limit of the set-point temperature range is lower than the evaporation temperature of the refrigerant and the refrigerant operates below the critical pressure in the low pressure portion of the refrigerant circuit.
the second condition includes a set-point temperature range having an upper limit and a lower limit
the auxiliary fan or the water delivery device is activated when temperature of the refrigerant at the inlet of the second heat exchanger reaches or exceeds the upper limit and deactivated when the temperature of the refrigerant at the inlet of the second heat exchanger reaches or goes below the lower limit
the lower limit of the second condition is lower than said predetermined temperature value and lower than the critical temperature of the refrigerant and the refrigerant operates at least at critical pressure in the low pressure portion of the refrigerant circuit.
the auxiliary fan or the water delivery device is controlled or controllable so that either
FIG 1 illustrates a schematic diagram of a heat pump system for a laundry dryer according to a preferred embodiment of the present invention.
the heat pump system includes a closed refrigerant circuit 10 and a drying air circuit 12.
the refrigerant circuit 10 includes a compressor 14, a gas cooler 16, an auxiliary gas cooler 18, lamination means 20 and an evaporator 22 or gas heater 22.
the compressor 14, the gas cooler 16, the auxiliary gas cooler 18, the lamination means 20 and the evaporator 22 or gas heater 22 are switched in series and form a closed loop.
the drying air circuit 12 includes the gas heater 22 or evaporator 22, the gas cooler 16, a laundry treatment chamber 48, preferably a rotatable drum, and a drying air fan 50.
the evaporator 22 or gas heater 22 is one single physical device, which acts as evaporator 22, if the refrigerant changes its phase, and acts as gas heater 22, if the refrigerant remains in the gas phase.
the use of the denotation "evaporator” or “gas heater” depends on the aggregate states of the refrigerant.
the gas cooler 16 and the evaporator 22 or gas heater 22 are heat exchangers and form the thermal interconnections between the refrigerant circuit 10 and the drying air circuit 12.
the auxiliary gas cooler 18 is also a heat exchanger and forms the thermal interconnection between the refrigerant circuit 10 and ambient air or water.
the auxiliary gas cooler 18 corresponds with an auxiliary fan 24 for driving the ambient air towards/over/through the auxiliary gas cooler 18 or with a water delivery device, such as sprinkling head or spray nozzle or a water conveyor, for supplying water to the auxiliary gas cooler.
the water is condensate water collected at the evaporator or gas heater 22 during the dehumidification of the drying air.
the evaporator 22 or gas heater 22 cools down and dehumidify the drying air, after said drying air has passed the laundry drum 48. Then the gas cooler 16 heats up the drying air, before the drying air is re-inserted into the laundry drum 48.
the drying air is driven by the drying air fan 50.
the drying air circuit 12 is preferably a closed loop in which the process air is continuously circulated through the laundry storing chamber. However it may also be provided that a (preferably smaller) portion of the process air is exhausted from the process air loop and fresh air (e.g. ambient air) is taken into the process air loop to replace the exhausted process air. And/or the process air loop is temporally opened (preferably only a short section of the total processing time) to have an open loop discharge.
the refrigerant circuit 10 is subdivided into a high pressure portion and a low pressure portion.
the high pressure portion extends from the outlet of the compressor 14 via the gas cooler 16 and the auxiliary gas cooler 18 to the inlet of the lamination means 20.
the low pressure portion extends from the outlet of the lamination means 20 via the evaporator 22 or gas heater 22 to the inlet of the compressor 14.
the refrigerant is compressed and heated up by the compressor 14.
the gas cooler 16 cools down the refrigerant and heats up the drying air.
the refrigerant is further cooled down in the auxiliary gas cooler 18 by ambient air or by water.
the ambient air is driven by the auxiliary fan 24, the water is supplied by the water delivery device.
the refrigerant is expanded in the lamination means 20. Therein the pressure of the refrigerant is decreased down to the pressure of the low pressure portion of the refrigerant circuit.
the refrigerant enters the evaporator 22 or gas heater 22. In the evaporator 22 or gas heater 22 the refrigerant is vaporised and superheated or heated up, respectively. At last, the refrigerant is sucked by the inlet of the compressor 14.
the auxiliary gas cooler 18 increases the cooling capacity of the evaporator 22 or gas heater 22. Thus, the performance of the heat pump system and the laundry dryer is improved.
the heat removed from the refrigerant circuit 10 by the auxiliary gas cooler 18 allows a balance between the refrigerant and the drying air, so that a steady state phase can be kept.
the heat pump system may use carbon dioxide as refrigerant. Since no condensation of carbon dioxide occurs, the auxiliary gas cooler 18 acts as gas cooler.
auxiliary gas cooler 18 allows that the temperature at the inlet of the evaporator 22 can be lower than the evaporation temperature, when the refrigerant works in the trans-critical cycle. Further, the use of an auxiliary gas cooler 18 allows that the temperature at the inlet of the gas heater 22 can be lower than the critical temperature of the refrigerant, when the refrigerant works in the totally-supercritical cycle. In this way, the heat pump system can work at a higher pressure level in the low pressure portion of the refrigerant circuit 10 and keep an average temperature of the evaporator 22 or gas heater 22 lower.
FIG 2 shows a temperature-entropy diagram of a trans-critical cycle in the heat pump system for a laundry dryer according to the invention.
Said temperature-entropy diagram relates to the heat pump system in FIG 1 , wherein the auxiliary gas cooler 18 and the auxiliary fan 24 or the water delivery device are switched off, i.e. no heat exchange occurs between the auxiliary heat exchanger and the ambient air or the water.
the temperature-entropy diagrams comprise a high pressure isobaric line 30, a low pressure isobaric line 32, a saturation curve 34 of carbon dioxide, a compression phase 36 and a lamination phase 38.
a state EV-OUT of the refrigerant at the outlet of the evaporator 22 a state GC-IN of the refrigerant at the inlet of the gas cooler 16, a state GC-OUT of the refrigerant at the outlet of the gas cooler 16 and a state EV-IN of the refrigerant at the inlet of the evaporator 22 are indicated in the temperature-entropy diagrams.
the state EV-IN is inside the saturation curve 34 of carbon dioxide, so that the state EV-IN belongs to a two-phase zone.
FIG 3 shows a detailed temperature-entropy diagram of the trans-critical cycle in the heat pump system for the laundry dryer according to the present invention.
FIG 3 clarifies the effect of the auxiliary gas cooler 18 and the auxiliary fan 24 or the water delivery device.
auxiliary fan 24 of the auxiliary gas cooler 18 or the water delivery device When the auxiliary fan 24 of the auxiliary gas cooler 18 or the water delivery device is switched on, then the refrigerant coming from the gas cooler 16 is additionally cooled down.
the auxiliary gas cooler 18 and the auxiliary fan 24 cause the transfer in the diagram from the state GC-OUT to a state AUX-GC-OUT representing the state of the refrigerant at the outlet of the auxiliary gas cooler 18.
the three states AUX-GC-OUT', AUX-GC-OUT" and AUX-GC-OUT''' at the outlet of the auxiliary gas cooler 18 correspond with the states EV-IN', EV-IN” and EV-IN”', respectively, at the inlet of the evaporator 22.
the state EV-IN' still belongs to the two-phase zone.
the temperature at the outlet of the auxiliary gas cooler 18 becomes lower, as in the states AUX-GC-OUT" and AUX-GC-OUT'', so that the states EV-IN" and EV-IN'' start belonging to the liquid zone.
the applicant has found that when the temperature of the refrigerant at the inlet of the evaporator 22 goes below the evaporation temperature, the cooling and dehumidifying capacity of the evaporator 22 increases.
FIG 4 shows a temperature-entropy diagram of a totally-supercritical cycle in the heat pump system for the laundry dryer according to present invention.
Said temperature-entropy diagram relates to the heat pump system in FIG 1 , wherein the auxiliary gas cooler 18 and the auxiliary fan 24 or the water delivery device are switched off, i.e. no heat exchange occurs between the auxiliary heat exchanger and the ambient air or the water.
the temperature-entropy diagrams comprise the high pressure isobaric line 30, the low pressure isobaric line 32, the saturation curve 34 of carbon dioxide, the compression phase 36 and the lamination phase 38.
the state GH-OUT of the refrigerant at the outlet of the gas heater 22 is indicated in the temperature-entropy diagrams. All the states of the refrigerant are outside the saturation curve 34 of carbon dioxide, so that the refrigerant belongs to the gas phase zone during the whole cycle.
FIG 5 shows a detailed temperature-entropy diagram of the totally-supercritical cycle in the heat pump system for the laundry dryer according to the preferred embodiment of the present invention.
FIG 5 clarifies the effect of the auxiliary gas cooler 18 and the auxiliary fan 24 or the water delivery device.
FIG 5 clarifies that the lower the temperature at the outlet of the auxiliary gas cooler 18, the lower is the temperature at the inlet of the gas heater 22.
the states AUX-GC-OUT', AUX-GC-OUT" and AUX-GC-OUT'' at the outlet of the auxiliary gas cooler 18 correspond with the states GH-IN', GH-IN” and GH-IN”', respectively, at the inlet of the gas heater 22.
auxiliary fan 24 of the auxiliary gas cooler 18 is switched off in the beginning of the cycle, so that the temperatures of the refrigerant and the drying air increase up to desired levels.
the end of the transitory phase can be determined by detecting the temperature of the drying air in the laundry drum 48, preferably at the drum inlet, the temperature and/or pressure of the refrigerant at the outlet of the gas cooler 16 or the temperature and/or pressure of the refrigerant at the inlet of the evaporator/gas heater 22.
the auxiliary gas cooler 18 and the auxiliary fan 24 start working, then the temperatures of the drying air and the refrigerant are kept constant. However, if the cooling capacity of the auxiliary gas cooler 18 is higher than necessary in order to balance the heat pump system, then the temperatures of the drying air and the refrigerant start decreasing. If the temperatures of the drying air and the refrigerant remain constant, then the auxiliary gas cooler 18 and the auxiliary fan 24 can work continuously. If the temperatures of the drying air and the refrigerant decrease, then the auxiliary gas cooler 18 and the auxiliary fan 24 work in an on-off mode.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched on, if the temperature of the drying air at the inlet of the laundry drum 48 becomes higher than a predetermined set-point temperature.
Said predetermined set-point temperature is in a range between 50°C and 75°C.
said predetermined set-point temperature is in a range between 55°C and 70°C.
said predetermined set-point temperature is in a range between 57°C and 65°C.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched off, if the temperature of the drying air at the inlet of the laundry drum 48 becomes lower than said predetermined set-point temperature minus 0°C to 5°C, preferably minus 1°C to 4°C, preferably minus 2°C to 3°C.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched on, if the temperature of the refrigerant at the outlet of the gas cooler 16 becomes higher than a further predetermined set-point temperature.
Said predetermined set-point temperature is in a range between 35°C and 60°C.
said predetermined set-point temperature is in a range between 40°C and 55°C.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched off, if the temperature of the refrigerant at the outlet of the gas cooler 16 becomes lower than said predetermined set-point temperature minus preferably 0°C to 5°C, preferably minus 1°C to 4°C, preferably minus 2°C to 3°C.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched on, if the temperature of the refrigerant at the inlet of the evaporator 22 becomes higher than a further predetermined set-point temperature.
Said predetermined set-point temperature is in a range between 20°C and 31°C.
said predetermined set-point temperature is in a range between 25°C and 31°C.
said predetermined set-point temperature is in a range between 28°C and 31°C.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched off, if the temperature of the refrigerant at the inlet of the evaporator 22 becomes lower than said predetermined set-point temperature minus preferably 0°C to 5°C, preferably minus 1°C to 4°C, preferably minus 2°C to 3°C.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched on, if the temperature of the refrigerant at the inlet of the gas heater 22 becomes higher than a predetermined set-point temperature, which is in a range between 31°C and 40°C, in particular between 33°C and 36°C.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 is switched off, if the temperature of the refrigerant at the inlet of the gas heater 22 becomes lower than said predetermined set-point temperature minus preferably 0°C to 5°C, preferably minus 1°C to 4°C, preferably minus 2°C to 3°C.
FIG 6 shows a schematic flow chart diagram of a method for controlling the auxiliary fan 24 of the heat pump system for the laundry dryer according to a first embodiment of the present invention.
Said first embodiment relates to the above three examples.
a switch on-off condition 40 is checked in order to switch on and to switch off the auxiliary fan 24 or the water delivery device when predetermined conditions are met.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 are activated or deactivated in response to the detection of predetermined values of quantities associated to the drying air or to the refrigerant.
the switch on-off condition 40 may depend on the temperature of the drying air at the inlet of the laundry drum 48 according to the first example. Further, the switch on-off condition 40 may depend on the temperature of the refrigerant at the outlet of the gas cooler 16 according to the second example. Moreover, the switch on-off condition 40 may depend on the temperature of the refrigerant at the inlet of the evaporator 22 or gas heater 22 according to the third example.
An auxiliary fan controller or a water delivery device controller is provided to drive the auxiliary fan 24 or the water delivery device in response to the detected temperature values of the drying air or in response to the detected temperature values of the refrigerant.
FIG 7 shows a schematic flow chart diagram of the method for controlling the auxiliary fan 24 or the water delivery device of the heat pump system for the laundry dryer according to a second embodiment of the present invention wherein the refrigerant operates below the critical temperatures in the low pressure side of the refrigerant circuit 10.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 remains switched off. Then, a first condition 44 is checked whether it is met.
the first condition 44 relates to the temperature of the refrigerant at the inlet of the evaporator 22.
the auxiliary fan 24 or the water delivery device is kept OFF until the temperature at the evaporator inlet reaches or exceeds a value corresponding to a desired relatively high pressure level at the low pressure portion of the refrigerant circuit 10 and then the auxiliary fan 24 or the water delivery device starts working. In this way the heat pump works in trans-critical conditions with a relatively high pressure level at the low pressure portion of the refrigerant circuit 10.
the auxiliary fan 24 or the water delivery device is kept OFF until the temperature at the evaporator inlet reaches a value comprises in a range between 20°C and 31°C or, preferably, between 25°C and 31°C or, preferably, between 28°C and 31°C.
a predetermined set-point temperature of the refrigerant at the inlet of the evaporator 22 is set at 28°C. If the first condition 44 is met, i.e. when the temperature reaches at least 28°C, then a second condition 46 is checked whether satisfied or not.
the second condition 46 preferably, relates to a predetermined set-point temperature range of the refrigerant at the inlet of the evaporator 22.
Said predetermined set-point temperature comprises and an upper limit (for example 25°C) for switching on the auxiliary fan 24 or the water delivery device and a lower limit (for example 22°C) for switching off the auxiliary fan 24 or the water delivery device.
an upper limit for example 25°C
a lower limit for example 22°C
the auxiliary fan 24 or the water delivery device is activated, while when the temperature of refrigerant detected at the inlet of the evaporator 22 is equal to or lower than the upper limit, the auxiliary fan 24 or the water delivery device is deactivated.
the upper limit (for example 25°C) and the lower limit (for example 22°C) of the set-point temperature range are both lower than the temperature value of the first condition (for example 28°C) and preferably at least the lower limit of the set-point temperature range is lower than the evaporation temperature of the refrigerant.
the auxiliary fan 24 or the water delivery are activated (switched on, energized), while if the temperature of the refrigerant at the inlet of the evaporator 22 first meets the first condition and then the set-point temperature range lower limit of second condition 46, the auxiliary fan 24 or the water delivery are deactivated (switched off, de-energized).
the second condition 46 relates to the predetermined set-point temperature of the during air at the inlet of the laundry drum 48 or of the refrigerant at the outlet of the gas cooler 16.
the auxiliary fan 24 or the water delivery are activated when the temperature of the refrigerant at the outlet of the gas cooler 16 reaches or exceeds a predetermined temperature, or when temperature of the drying air at the inlet of laundry treatment chamber 48 reaches or exceeds a predetermined temperature.
a cycle end condition 42 is satisfied, then the cycle is stopped.
An auxiliary fan controller or a water delivery device controller are provided to drive the auxiliary fan 24 or the water delivery device according to the first and second condition 44, 46.
FIG 8 shows a schematic flow chart diagram of the method for controlling the auxiliary fan 24 of the heat pump system for the laundry dryer according to a third embodiment of the present invention wherein the refrigerant operates at least at the critical temperatures in the low pressure side of the refrigerant circuit 10.
the auxiliary fan 24 or the water delivery device of the auxiliary gas cooler 18 remains switched off. Then, a first condition 44 is checked whether it is met.
the first condition 44 relates to the temperature of the refrigerant at the inlet of the gas heater 22.
the auxiliary fan 24 or the water delivery device is kept OFF until the temperature at the gas heater inlet reaches or exceeds a value (at least equal to the refrigerant critical temperature) corresponding to a desired relatively high pressure level at the low pressure portion of the refrigerant circuit 10 and then the auxiliary fan 24 or the water delivery device starts working. In this way the heat pump works in totally-supercritical conditions with a relatively high pressure level at the low pressure portion.
the auxiliary fan 24 or the water delivery device is kept OFF until the temperature at the gas cooler inlet reaches a value comprises in a range between 31°C and 40°C or, preferably, between 33°C and 36°C.
the predetermined set-point temperature of the refrigerant at the inlet of the gas heater 22 is set at 35°C.
a second condition 46 is checked whether satisfied or not.
the second condition 46 preferably, relates to a predetermined set-point temperature range of the refrigerant at the inlet of the gas heater 22.
Said predetermined set-point temperature comprises an upper limit (for example 30°C) for switching on the auxiliary fan 24 or the water delivery device and a lower limit (for example 26°C) for switching off the auxiliary fan 24 or the water delivery device.
an upper limit for example 30°C
a lower limit for example 26°C
the auxiliary fan 24 or the water delivery device is activated, while when the temperature of refrigerant detected at the inlet of the evaporator 22 is equal to or lower than the upper limit, the auxiliary fan 24 or the water delivery device is deactivated.
the lower limit (for example 26°C) of the set-point temperature range is lower than the temperature value of the first condition (for example 35°C) and preferably the lower limit of the set-point temperature range is lower than the critical temperature of the refrigerant (31°C in case of carbon dioxide).
the upper limit (for example 30°C) is preferably lower than the temperature value of the first condition (for example 35°C) but it can also be higher (for example 38°C) and preferably the upper limit (for example 30°C) of the set-point temperature range is lower than the critical temperature of the refrigerant.
the auxiliary fan 24 or the water delivery are activated (switched on, energized), while if the temperature of the refrigerant at the inlet of the gas heater 22 first meets the first condition and then the set-point temperature range lower limit of second condition 46, the auxiliary fan 24 or the water delivery are deactivated (switched off, de-energized).
the second condition 46 relates to the predetermined set-point temperature of the drying air at the inlet of the laundry drum 48 or of the refrigerant at the outlet of the gas cooler 16.
the auxiliary fan 24 or the water delivery are activated when the temperature of the refrigerant at the outlet of the gas cooler 16 reaches or exceeds a predetermined temperature, or when temperature of the drying air at the inlet of laundry treatment chamber (48) reaches or exceeds a predetermined temperature.
An auxiliary fan controller or a water delivery device controller are provided to drive the auxiliary fan 24 or the water delivery device according to the first and second condition 44, 46.

Landscapes

Engineering & Computer Science (AREA)
Textile Engineering (AREA)
Detail Structures Of Washing Machines And Dryers (AREA)

EP11189866.4A 2011-11-21 2011-11-21 Sèche-linge avec système de pompe à chaleur Not-in-force EP2594687B1 (fr)

Priority Applications (1)

Application Number	Priority Date	Filing Date	Title
EP11189866.4A EP2594687B1 (fr)	2011-11-21	2011-11-21	Sèche-linge avec système de pompe à chaleur

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
EP11189866.4A EP2594687B1 (fr)	2011-11-21	2011-11-21	Sèche-linge avec système de pompe à chaleur

Publications (2)

Publication Number	Publication Date
EP2594687A1 true EP2594687A1 (fr)	2013-05-22
EP2594687B1 EP2594687B1 (fr)	2014-09-10

Family

ID=45375170

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP11189866.4A Not-in-force EP2594687B1 (fr)	2011-11-21	2011-11-21	Sèche-linge avec système de pompe à chaleur

Country Status (1)

Country	Link
EP (1)	EP2594687B1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN104566973A (zh) *	2015-01-14	2015-04-29	郑运婷	空气能节能干衣热水器
CN104562600A (zh) *	2015-01-14	2015-04-29	郑运婷	节能空气能干衣热水器
KR20160149851A (ko)	2015-06-19	2016-12-28	엘지전자 주식회사	의류건조기 및 이의 제어방법
KR20160149852A (ko)	2015-06-19	2016-12-28	엘지전자 주식회사	의류건조기
CN107089696A (zh) *	2017-06-01	2017-08-25	东莞理工学院	一种喷雾蒸发海水淡化装置
CN107270696A (zh) *	2017-06-23	2017-10-20	中国科学院理化技术研究所	一种基于co2跨临界热泵循环的干燥系统
EP3323933A4 (fr) *	2015-06-19	2019-05-15	LG Electronics Inc.	Sèche-linge et son procédé de commande
US10519591B2 (en)	2016-10-14	2019-12-31	Whirlpool Corporation	Combination washing/drying laundry appliance having a heat pump system with reversible condensing and evaporating heat exchangers
US10633785B2 (en)	2016-08-10	2020-04-28	Whirlpool Corporation	Maintenance free dryer having multiple self-cleaning lint filters
KR102137574B1 (ko)	2019-02-22	2020-07-24	주식회사 하이낸드	히트펌프 건조기
US10738411B2 (en)	2016-10-14	2020-08-11	Whirlpool Corporation	Filterless air-handling system for a heat pump laundry appliance
CN111750658A (zh) *	2020-07-29	2020-10-09	青岛达能环保设备股份有限公司	基于跨临界二氧化碳热泵的物料干燥系统
CN115478419A (zh) *	2021-05-31	2022-12-16	重庆海尔滚筒洗衣机有限公司	一种热泵干衣机的温度控制方法及温度控制装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US10502478B2 (en)	2016-12-20	2019-12-10	Whirlpool Corporation	Heat rejection system for a condenser of a refrigerant loop within an appliance
US10514194B2 (en)	2017-06-01	2019-12-24	Whirlpool Corporation	Multi-evaporator appliance having a multi-directional valve for delivering refrigerant to the evaporators
US10718082B2 (en)	2017-08-11	2020-07-21	Whirlpool Corporation	Acoustic heat exchanger treatment for a laundry appliance having a heat pump system
CN108716090B (zh) *	2018-09-13	2020-06-30	惠而浦（中国）股份有限公司	一种用于洗干一体机的直排结构及其烘干控制方法

Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP1884586A2 (fr) *	2006-11-06	2008-02-06	V-Zug AG	Sèche-linge avec échangeur de chaleur supplémentaire
WO2008086933A1 (fr) *	2007-01-15	2008-07-24	BSH Bosch und Siemens Hausgeräte GmbH	Sèche-linge à condensation équipé d'une pompe à chaleur et procédé pour faire fonctionner ce sèche-linge

2011
- 2011-11-21 EP EP11189866.4A patent/EP2594687B1/fr not_active Not-in-force

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP1884586A2 (fr) *	2006-11-06	2008-02-06	V-Zug AG	Sèche-linge avec échangeur de chaleur supplémentaire
WO2008086933A1 (fr) *	2007-01-15	2008-07-24	BSH Bosch und Siemens Hausgeräte GmbH	Sèche-linge à condensation équipé d'une pompe à chaleur et procédé pour faire fonctionner ce sèche-linge

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN104566973A (zh) *	2015-01-14	2015-04-29	郑运婷	空气能节能干衣热水器
CN104562600A (zh) *	2015-01-14	2015-04-29	郑运婷	节能空气能干衣热水器
KR20160149851A (ko)	2015-06-19	2016-12-28	엘지전자 주식회사	의류건조기 및 이의 제어방법
KR20160149852A (ko)	2015-06-19	2016-12-28	엘지전자 주식회사	의류건조기
EP3712322A1 (fr)	2015-06-19	2020-09-23	LG Electronics Inc.	Sèche-linge
US10662575B2 (en)	2015-06-19	2020-05-26	Lg Electronics Inc.	Clothes dryer and method for controlling same
EP3323933A4 (fr) *	2015-06-19	2019-05-15	LG Electronics Inc.	Sèche-linge et son procédé de commande
US10633785B2 (en)	2016-08-10	2020-04-28	Whirlpool Corporation	Maintenance free dryer having multiple self-cleaning lint filters
US10519591B2 (en)	2016-10-14	2019-12-31	Whirlpool Corporation	Combination washing/drying laundry appliance having a heat pump system with reversible condensing and evaporating heat exchangers
US10738411B2 (en)	2016-10-14	2020-08-11	Whirlpool Corporation	Filterless air-handling system for a heat pump laundry appliance
US11299834B2 (en)	2016-10-14	2022-04-12	Whirlpool Corporation	Combination washing/drying laundry appliance having a heat pump system with reversible condensing and evaporating heat exchangers
US11542653B2 (en)	2016-10-14	2023-01-03	Whirlpool Corporation	Filterless air-handling system for a heat pump laundry appliance
US12188164B2 (en)	2016-10-14	2025-01-07	Whirlpool Corporation	Combination washing/drying laundry appliance having a heat pump system with reversible condensing and evaporating heat exchangers
CN107089696A (zh) *	2017-06-01	2017-08-25	东莞理工学院	一种喷雾蒸发海水淡化装置
CN107270696A (zh) *	2017-06-23	2017-10-20	中国科学院理化技术研究所	一种基于co2跨临界热泵循环的干燥系统
KR102137574B1 (ko)	2019-02-22	2020-07-24	주식회사 하이낸드	히트펌프 건조기
CN111750658A (zh) *	2020-07-29	2020-10-09	青岛达能环保设备股份有限公司	基于跨临界二氧化碳热泵的物料干燥系统
CN115478419A (zh) *	2021-05-31	2022-12-16	重庆海尔滚筒洗衣机有限公司	一种热泵干衣机的温度控制方法及温度控制装置

Also Published As

Publication number	Publication date
EP2594687B1 (fr)	2014-09-10

Publication	Publication Date	Title
EP2594687B1 (fr)	2014-09-10	Sèche-linge avec système de pompe à chaleur
JP4126322B2 (ja)	2008-07-30	乾燥装置
KR101613966B1 (ko)	2016-04-20	의류처리장치
KR100755160B1 (ko)	2007-09-04	냉각 시스템의 제어
US8910394B2 (en)	2014-12-16	Tumble dryer comprising a heat pump and heating system and method for operating the same
KR101409854B1 (ko)	2014-06-19	히트 펌프식 냉열풍 건조기
KR101355689B1 (ko)	2014-01-27	공기 조화 장치 및 그 어큐뮬레이터
DK2006437T3 (en)	2016-08-22	Dryer with heater in the heat pump circuit
KR101409855B1 (ko)	2014-06-19	히트 펌프식 열풍 건조기
US10662575B2 (en)	2020-05-26	Clothes dryer and method for controlling same
CN105316920B (zh)	2019-01-25	干衣机和干衣机热泵系统及其控制方法
JP5416375B2 (ja)	2014-02-12	乾燥方法及び乾燥装置
WO2012110353A2 (fr)	2012-08-23	Sèche-linge à pompe à chaleur
WO2014079934A1 (fr)	2014-05-30	Procédé permettant de commander un sèche-linge qui présente une vitesse de rotation de tambour variable ainsi qu'une vitesse de rotation de ventilateur variable
EP2551401A1 (fr)	2013-01-30	Système de pompe à chaleur pour sèche-linge
KR101756090B1 (ko)	2017-07-19	냉방제공 히트펌프 열풍건조기 및 그의 운전제어방법
EP1716375A1 (fr)	2006-11-02	Appareil de pompe chaleur et m thode d exploitation pour celui-ci
KR101718041B1 (ko)	2017-03-20	의류건조기 및 이의 제어방법
JP2005279257A (ja)	2005-10-13	乾燥装置及びその運転方法
JP2004313765A (ja)	2004-11-11	乾燥装置及びその運転方法
KR101756099B1 (ko)	2017-07-10	지열원 열펌프열풍건조기
EP2540905B1 (fr)	2015-02-25	Sèche-linge avec système de pompe à chaleur
EP2527522B1 (fr)	2013-12-25	Sèche-linge à pompe à chaleur
WO2013075997A1 (fr)	2013-05-30	Sèche-linge équipé d'un système de pompe à chaleur
EP2527521A1 (fr)	2012-11-28	Sèche-linge à pompe à chaleur

Legal Events

Date	Code	Title	Description
2013-05-21	PUAI	Public reference made under article 153(3) epc to a published international application that has entered the european phase	Free format text: ORIGINAL CODE: 0009012
2013-05-22	AK	Designated contracting states	Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR
2013-05-22	AX	Request for extension of the european patent	Extension state: BA ME
2014-01-01	17P	Request for examination filed	Effective date: 20131122
2014-01-01	RBV	Designated contracting states (corrected)	Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR
2014-04-16	GRAP	Despatch of communication of intention to grant a patent	Free format text: ORIGINAL CODE: EPIDOSNIGR1
2014-04-30	RIC1	Information provided on ipc code assigned before grant	Ipc: D06F 58/20 20060101AFI20140326BHEP
2014-05-14	INTG	Intention to grant announced	Effective date: 20140417
2014-08-01	GRAS	Grant fee paid	Free format text: ORIGINAL CODE: EPIDOSNIGR3
2014-08-08	GRAA	(expected) grant	Free format text: ORIGINAL CODE: 0009210
2014-09-10	AK	Designated contracting states	Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR
2014-09-10	REG	Reference to a national code	Ref country code: GB Ref legal event code: FG4D
2014-09-15	REG	Reference to a national code	Ref country code: CH Ref legal event code: EP
2014-10-08	REG	Reference to a national code	Ref country code: IE Ref legal event code: FG4D
2014-10-15	REG	Reference to a national code	Ref country code: AT Ref legal event code: REF Ref document number: 686762 Country of ref document: AT Kind code of ref document: T Effective date: 20141015
2014-10-23	REG	Reference to a national code	Ref country code: DE Ref legal event code: R096 Ref document number: 602011009768 Country of ref document: DE Effective date: 20141023
2015-01-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141210 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141211 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2015-02-11	REG	Reference to a national code	Ref country code: NL Ref legal event code: VDEP Effective date: 20140910
2015-02-25	REG	Reference to a national code	Ref country code: LT Ref legal event code: MG4D
2015-02-27	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2015-03-15	REG	Reference to a national code	Ref country code: AT Ref legal event code: MK05 Ref document number: 686762 Country of ref document: AT Kind code of ref document: T Effective date: 20140910
2015-03-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2015-04-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150112 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150110 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2015-05-29	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2015-06-11	REG	Reference to a national code	Ref country code: DE Ref legal event code: R097 Ref document number: 602011009768 Country of ref document: DE
2015-06-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141121 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20141130
2015-06-30	REG	Reference to a national code	Ref country code: CH Ref legal event code: PL
2015-07-17	PLBE	No opposition filed within time limit	Free format text: ORIGINAL CODE: 0009261
2015-07-17	STAA	Information on the status of an ep patent application or granted ep patent	Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT
2015-07-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20141130 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20141130 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2015-08-19	26N	No opposition filed	Effective date: 20150611
2015-08-26	REG	Reference to a national code	Ref country code: IE Ref legal event code: MM4A
2015-10-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20141121
2015-11-19	REG	Reference to a national code	Ref country code: FR Ref legal event code: PLFP Year of fee payment: 5
2015-11-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2016-04-29	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2016-06-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2016-07-29	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20111121 Ref country code: BE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2016-11-18	REG	Reference to a national code	Ref country code: FR Ref legal event code: PLFP Year of fee payment: 6
2017-01-31	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: GB Payment date: 20161122 Year of fee payment: 6 Ref country code: FR Payment date: 20161118 Year of fee payment: 6
2018-06-29	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910
2018-07-25	GBPC	Gb: european patent ceased through non-payment of renewal fee	Effective date: 20171121
2018-08-31	REG	Reference to a national code	Ref country code: FR Ref legal event code: ST Effective date: 20180731
2018-10-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140910 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171130
2018-11-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171121
2023-01-31	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: IT Payment date: 20221124 Year of fee payment: 12 Ref country code: DE Payment date: 20221123 Year of fee payment: 12
2023-08-02	P01	Opt-out of the competence of the unified patent court (upc) registered	Effective date: 20230625
2024-06-01	REG	Reference to a national code	Ref country code: DE Ref legal event code: R119 Ref document number: 602011009768 Country of ref document: DE
2024-10-10	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20240601
2024-10-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20240601
2024-12-03	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20231121
2024-12-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20231121