EP2540905A1 - A laundry dryer with heat pump system - Google Patents
A laundry dryer with heat pump system Download PDFInfo
- Publication number
- EP2540905A1 EP2540905A1 EP11171923A EP11171923A EP2540905A1 EP 2540905 A1 EP2540905 A1 EP 2540905A1 EP 11171923 A EP11171923 A EP 11171923A EP 11171923 A EP11171923 A EP 11171923A EP 2540905 A1 EP2540905 A1 EP 2540905A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- refrigerant
- pump system
- inlet
- temperature
- 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.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 146
- 238000001035 drying Methods 0.000 claims abstract description 29
- 238000001816 cooling Methods 0.000 claims abstract description 16
- 238000010438 heat treatment Methods 0.000 claims abstract description 7
- 239000012080 ambient air Substances 0.000 claims description 60
- 239000003570 air Substances 0.000 claims description 45
- 239000000498 cooling water Substances 0.000 claims description 29
- 239000012071 phase Substances 0.000 description 19
- 238000010586 diagram Methods 0.000 description 9
- 229910052799 carbon Inorganic materials 0.000 description 7
- 239000007791 liquid phase Substances 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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. Further, the present invention relates to a controller for a laundry dryer.
- the operation of the laundry dryer with the heat pump system includes two working phases, namely a transitory phase and a steady state phase.
- the transitory phase is the initial phase after the heat pump system has been switched on.
- the temperatures of the air and the refrigerant are at ambient temperature.
- the temperatures of the air and the refrigerant increase up to a desired level.
- the temperatures of the drying air and the refrigerant are kept quiet constant. For example, said temperatures are kept constant by means of an compressor cooling fan or an auxiliary condenser until the laundry becomes dry.
- the heat pump is in unbalanced, because the same drying air stream is cooled in the evaporator and heated in the condenser, where more heating capacity is available on the side of the refrigerant circuit.
- the compressor cooling fan blows ambient air onto the compressor case.
- the auxiliary condenser is an additional heat exchanger between the refrigerant and an auxiliary cold source.
- the auxiliary condenser is arranged downstream the condenser.
- the refrigerant is further cooled down, wherein heat is transferred to a source, which may be water or ambient air.
- a source which may be water or ambient air.
- the cooling capacity is increased. Also the balancing between the cooling and heating capacity is increased.
- the condenser is a heat exchanger at the high pressure side of the refrigerant circuit.
- the evaporator is a heat exchanger at the low pressure side of the refrigerant circuit.
- the low pressure side of the refrigerant circuit extends from the outlet of the expansion means, e.g. a capillary tube or an adjustable valve, to the inlet of the compressor.
- the high pressure side of the refrigerant circuit extends from the outlet of the compressor to the inlet of the expansion means.
- An internal heat exchanger can be used to cool down the refrigerant between the condenser and expansion means and to heat up the refrigerant at the outlet of the evaporator.
- the internal heat exchanger allows the refrigerant to enter the evaporator in more favourable conditions.
- the vapour quality is lower and a part of the refrigerant is in the liquid phase, wherein the cooling capacity of the evaporator is increased. Otherwise the temperature of the refrigerant at the outlet of the low pressure side of the internal heat exchanger, which enters the inlet of the compressor, is higher, and the power required to the compressor increases as well. If cooling capacity increases more than the power required by the compressor, then the internal heat exchanger improves heat pump efficiency.
- the internal heat exchanger in a heat pump system of a tumble dryer allows a shorter transitory phase on the one hand and an improved heat pump performance during the steady state phase on the other hand.
- the internal heat exchanger can additionally improve the heat pump performance more than usual, if said internal heat exchanger is used to flood the evaporator, so that a part of the refrigerant flowing through the evaporator is maintained in the liquid phase. This occurs, if the superheating phase in the evaporator is provided at the low pressure side of the internal heat exchanger.
- Condensed refrigerant is cooled down as usual in the high pressure side of the internal heat exchanger, while in the low pressure side of the internal heat exchanger the vaporization of the refrigerant is completed and the superheating is performed. Therefore the evaporator improves its cooling performance, because the flooding allows a big heat exchange coefficient of the refrigerant in the liquid phase and the internal heat exchanger can improve the refrigerant sub-cooling at the high pressure side, since at the low pressure side of the internal heat exchanger the refrigerant can exchange both latent and sensible heat, so that more energy is available.
- EP 999 302 B1 discloses a laundry dryer with a closed process air cycle and a refrigerant circuit.
- a heat flow correction element is incorporated into the refrigerant circuit between the evaporator and the compressor.
- the heat flow correction element allows a heat exchange between the refrigerant on the one hand and the process air and/or the ambient air on the other hand.
- the object of the present invention is achieved by the laundry dryer with the heat pump system according to claim 1.
- the additional heat exchanger is connected between the outlet of second heat exchanger and the inlet of the compressor and is controlled or controllable by the temperature of the refrigerant in at least one position of the refrigerant circuit and/or by the temperature of the drying air.
- the present invention is based on the additional heat exchanger cooling down the refrigerant before compressor suction, wherein said additional heat exchanger is controlled by the temperature of the refrigerant and/or by the temperature of the drying air.
- the required power of the compressor decreases by the reduced temperature of the refrigerant after passing the additional heat exchanger.
- the additional heat exchanger is provided for a heat exchange between the refrigerant on the one hand and ambient air and/or cooling water on the other hand.
- the additional heat exchanger corresponds with at least one ambient air fan.
- the additional heat exchanger, the ambient air fan and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an inlet and/or at an outlet of the compressor.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched on, if the temperature of the refrigerant at the inlet of the compressor becomes higher than a predetermined value.
- Said predetermined value may be within a range between 20 °C and 45 °C, especially between 25 °C and 40 °C, in particular between 30 °C and 36 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C. Further, the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the temperature of the refrigerant at the outlet of the compressor becomes higher than a predetermined value. Said predetermined value may be within a range between 50 °C and 110 °C, especially between 60 °C and 100 °C, in particular between 70 °C and 90 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an inlet and/or at an outlet of the second heat exchanger.
- the temperature of the refrigerant at the outlet of the second heat exchanger and at the inlet of the additional heat exchanger are identical, if not any further component is arranged between them.
- the temperature of the refrigerant at the outlet of the second heat exchanger and at the inlet of the compressor are identical, if the additional heat exchanger is switched off and no further component is arranged between them.
- the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the temperature of the refrigerant at an inlet of the additional heat exchanger.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched on, if the temperature of the refrigerant at the inlet of the additional heat exchanger becomes higher than a predetermined value.
- Said predetermined value may be within a range between 20 °C and 60 °C, especially between 25 °C and 50 °C, in particular between 30 °C and 36 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched off, if the temperature at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the temperature of the refrigerant at an outlet of the first heat exchanger.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched on, if the temperature of the refrigerant at the outlet of the first heat exchanger becomes higher than a predetermined value.
- Said predetermined value may be within a range between 40 °C and 65 °C, in particular between 50 °C and 55 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the temperature of the air stream at an inlet of the laundry treatment chamber.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched on, if the temperature of the air stream at the inlet of the laundry drum becomes higher than a predetermined value.
- Said predetermined value may be within a range between 50 °C and 75 °C, in particular between 55 °C and 65 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the difference between the temperatures of the refrigerant at the inlet of the compressor and an inlet of the second heat exchanger.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched on, if the difference between the temperatures of the refrigerant at the inlet of the additional heat exchanger and at the inlet of the second heat exchanger becomes higher than a predetermined value.
- Said predetermined value may be within a range between 5 °C and 60 °C, in particular between 10 °C and 50 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if said difference becomes lower than the previous value minus between 0 °C and 5 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively may be switched on, if the difference between the temperatures of the refrigerant at the inlet and the outlet of the second heat exchanger becomes higher than a predetermined value.
- Said predetermined value may be within a range between 0 °C and 25 °C, in particular between 10 °C and 15 °C.
- the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if said difference becomes lower than the previous value minus between 0 °C and 5 °C.
- a low pressure portion and a high pressure portion of the refrigerant circuit are thermally coupled by at least one internal heat exchanger.
- the low pressure portion may extend between the outlet of the expansion means and the inlet of the compressor
- the high pressure portion may extend between the outlet of the compressor and the inlet of the expansion means
- a high pressure side of the internal heat exchanger is interconnected between an outlet of the first heat exchanger and the inlet of the expansion means.
- a low pressure side of the internal heat exchanger may be interconnected between an outlet of the second heat exchanger and an inlet of the additional heat exchanger.
- the at least one ambient air fan may be switched or switchable in an on-off mode depending on at least one temperature of the refrigerant.
- the speed of the at least one ambient air fan is continuously variable depending on at least one temperature of the refrigerant.
- the present invention relates to a controller for a laundry dryer or a spinner-washer with a heat pump system mentioned above, wherein the controller is provided for controlling the additional heat exchanger in response to the temperature of the refrigerant in at least one position of the refrigerant circuit.
- FIG 1 illustrates a schematic diagram of a heat pump system for a laundry dryer according to a first embodiment of the present invention.
- the heat pump system includes a closed refrigerant circuit 10 and a, preferably, closed drying air circuit 12.
- the refrigerant circuit 10 includes a compressor 14, a condenser 16, expansion means 18, an evaporator 20 and an additional heat exchanger 22.
- the compressor 14, the condenser 16, the expansion means 18, the evaporator 20 and the additional heat exchanger 22 are switched in series and form a closed loop of the refrigerant circuit 10.
- the additional heat exchanger 22 corresponds with an ambient air fan 24.
- 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 condenser 16 to the inlet of the expansion means 18.
- the low pressure portion extends from the outlet of the expansion means 18 via the evaporator 20 and the additional heat exchanger 22 to the inlet of the compressor 14.
- the refrigerant for example carbon dioxide
- the refrigerant can operates at a supercritical mode in the high pressure portion of the refrigerant circuit 10.
- the refrigerant In the high pressure portion the refrigerant is at least at the critical pressure and always in gas phase so that the condenser is better indicated as a gas cooler.
- the refrigerant In the low pressure portion of the refrigerant circuit 10 the refrigerant can also operate at the supercritical mode so that the evaporator is better indicated as a gas heater.
- the during air circuit 12 includes the compressor 14, a drying air stream fan 26, a laundry treatment chamber for accommodating the clothes 28, preferably a rotatable drum 28, the condenser 16 and the evaporator 20.
- the condenser 16 and the evaporator 20 are heat exchangers and form the thermal interconnections between the refrigerant circuit 10 and the drying air circuit 12.
- the evaporator 20 cools down and dehumidifies the drying air, after said drying air has passed the laundry drum 28. Then the condenser 16 heats up the air stream, before the drying air is re-inserted into the laundry drum 28.
- the drying air is driven by the drying air stream fan 26.
- a refrigerant is compressed by the compressor 14, condensed in the condenser 16, laminated in the expansion means 18, vaporised in the evaporator 20 and cooled down in the additional heat exchanger 22.
- the additional heat exchanger 22 cools down the refrigerant by ambient air before the suction by the compressor 14.
- the ambient air may be driven by the ambient air fan 24.
- the required power of the compressor 14 decreases by the reduced temperature of the refrigerant after passing the additional heat exchanger 22. Considering the pressures in the high pressure portion and the low pressure portion of the refrigerant circuit 10 as constant, the lower the temperature of the refrigerant at the inlet of the compressor 14, the lower the power for compressing the refrigerant by the compressor 14.
- the temperature at the inlet of the compressor 14 is kept within a predetermined range.
- the temperature of the refrigerant at the inlet of compressor 14 should not be too low, since refrigerant superheating is required to prevent liquid refrigerant from entering the compressor 14, thereby avoiding damages.
- the temperature at the outlet of the compressor 14 could be too low, so that the refrigerant cannot heat up the drying air to the desired temperature via the condenser 16.
- the temperature at the inlet of the compressor 14 is controlled by the ambient air fan 24.
- An upper limit of the predetermined range for the temperature at the inlet of the compressor 14 depends on the properties of said compressor 14. Usually, the upper limit for the temperature at the inlet of the compressor 14 is about 40°C.
- a lower limit of the predetermined range for the temperature at the inlet of the compressor 14 depends on several thermodynamic parameters, in particular on the pressure in the low pressure portion of the refrigerant circuit 10 and on the temperature at the inlet of the compressor 14. Said pressure and temperature determine whether the refrigerant is completely vaporized or not at the inlet of the compressor 14.
- the operation cycle of the heat pump system is subdivided into a transitory phase and a steady state phase.
- the transitory phase is the initial phase after the heat pump system has been switched on. Before the heat pump system starts, the temperatures of the air stream and of the refrigerant are at ambient temperature. During the transitory phase, the temperatures of the air stream and the refrigerant increase up to a desired level.
- the ambient air fan 24 of the additional heat exchanger 22 can work in an on-off mode or can be driven at a variable speed to maintain the temperature range at the compressor within predetermined value.
- the upper limit for the temperature range at the inlet of the compressor 14 is between 25°C and 40°C.
- the lower limit for the temperature range at the inlet of the compressor 14 is between 20°C and 35°C during the steady state phase of the operation cycle.
- the ambient air fan 24 of the additional heat exchanger 22 may be switched off, if the temperature of the refrigerant at the outlet of the compressor 14 becomes too low, for example below 70°C.
- a further control strategy for the ambient air fan 24 of the additional heat exchanger 22 may be the maintaining of a minimum difference between the temperature of the refrigerant at the inlet of the compressor 14 and the temperature of the refrigerant at the inlet of the evaporator 20.
- Said minimum temperature difference is between 0°C and 10°C, preferably greater than 5°C. This minimum temperature difference assures a certain margin of superheating of the refrigerant before entering the compressor 14. If the actual temperature difference is less than said minimum difference temperature value, then the ambient air fan 24 of the additional heat exchanger 22 is switched off.
- the heat pump system comprises a set of temperature sensors within the refrigerant circuit 10 in order to detect the temperature of the refrigerant.
- the temperature sensors are arranged at the inlet of the compressor 14, at the inlet of the evaporator 20 and/or at the outlet of the compressor 14.
- FIG 2 illustrates a schematic pressure-enthalpy-diagram of the refrigerant in the heat pump system according to the first embodiment of the present invention.
- the diagram shows the pressure p of the refrigerant as a function of the specific enthalpy h.
- a curve 32 marks the limit between the portions of the sub-critical conditions and the over-critical conditions of the refrigerant.
- the sub-critical conditions of the refrigerant occur within the portion inside the curve 32.
- the over-critical conditions occur in the portion outside the curve 32.
- a first state a and a modified first state a' correspond with the refrigerant at the inlet of the condenser 16.
- a second state b corresponds with the refrigerant at the outlet of the condenser 16.
- a third state c corresponds with the refrigerant at the inlet of the evaporator 20.
- a fourth state d and a modified fourth state d' corresponds with the refrigerant at the inlet of the compressor 14. The modified first state a' and the modified fourth state d' occur, when the ambient air fan 24 of the additional heat exchanger 22 is switched on.
- the refrigerant follows the cycle with the states a, b, c, d and a again.
- the ambient air fan 24 of the additional heat exchanger 22 is switched on, then the refrigerant follows the cycle with the states a', b, c, d, d' and a' again.
- the power absorbed by the compressor 14 is reduced, when the ambient air fan 24 of the additional heat exchanger 22 is switched on.
- the compressor 14 transfers the refrigerant from a modified fourth state d' to the modified first state a', instead of a transfer from the fourth state d to the first state a.
- FIG 3 illustrates a schematic diagram of a heat pump system for a laundry dryer according to a second embodiment of the present invention.
- the heat pump system includes the closed refrigerant circuit 10 and the, preferably closed drying air circuit 12.
- the second embodiment includes additionally an internal heat exchanger 30.
- the refrigerant circuit 10 includes the compressor 14, the condenser 16, the expansion means 18, the evaporator 20, the additional heat exchanger 22 and the internal heat exchanger 30.
- the compressor 14, the condenser 16, a high pressure side of the internal heat exchanger 30, the expansion means 18, the evaporator 20, a low pressure side of the internal heat exchanger 30, and the additional heat exchanger 22 are switched in series and form the closed loop of the refrigerant circuit 10.
- the additional heat exchanger 22 corresponds with the ambient air fan 24.
- the drying air circuit 12 includes the compressor 14, an air stream fan 26, a laundry drum 28, the compressor 14 and the evaporator 20.
- the condenser 16 and the evaporator 20 are heat exchangers and form the thermal interconnections between the refrigerant circuit 10 and the drying air circuit 12.
- the evaporator 20 cools down and dehumidifies an air stream, after said air stream has passed the laundry drum 28. Then the condenser 16 heats up the air stream, before the air stream is re-inserted into the laundry drum 28.
- the air stream is driven by the air stream fan 26.
- the refrigerant is compressed by the compressor 14, condensed in the condenser 16, cooled down in the high pressure side of the internal heat exchanger 30, laminated in the expansion means 18, vaporised in the evaporator 20, heated up in the low pressure side of the internal heat exchanger 30 and cooled down in the additional heat exchanger 22.
- the additional heat exchanger 22 cools down the refrigerant by ambient air before the suction by the compressor 14.
- the ambient air may be driven by the ambient air fan 24.
- the internal heat exchanger 30 allows a heat exchange between the high pressure portion and the low pressure portion of the refrigerant circuit 10.
- the high pressure portion of the second embodiment extends from the outlet of the compressor 14 via the condenser 16 and the high pressure side of the internal heat exchanger 30 to the inlet of the expansion means 18.
- the low pressure portion of the second embodiment extends from the outlet of the expansion means 18 via the evaporator 20, the low pressure side of the internal heat exchanger 30 and the additional heat exchanger 22 to the inlet of the compressor 14.
- the ambient air fan 24 of the additional heat exchanger 22 is controlled in the same way as in the first embodiment as described above.
- the internal heat exchanger 30 cools down the refrigerant in the low pressure portion additionally by the refrigerant in the high pressure portion.
Landscapes
- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Detail Structures Of Washing Machines And Dryers (AREA)
Abstract
Description
- The present invention relates to a laundry dryer with a heat pump system according to the preamble of claim 1. Further, the present invention relates to a controller for a laundry dryer.
- In a laundry dryer, the heat pump technology is the most efficient way to save energy. The operation of the laundry dryer with the heat pump system includes two working phases, namely a transitory phase and a steady state phase. The transitory phase is the initial phase after the heat pump system has been switched on. Before the heat pump system starts, the temperatures of the air and the refrigerant are at ambient temperature. During the transitory phase, the temperatures of the air and the refrigerant increase up to a desired level. During the steady state phase, the temperatures of the drying air and the refrigerant are kept quiet constant. For example, said temperatures are kept constant by means of an compressor cooling fan or an auxiliary condenser until the laundry becomes dry.
- The heat pump is in unbalanced, because the same drying air stream is cooled in the evaporator and heated in the condenser, where more heating capacity is available on the side of the refrigerant circuit. The heating power at the condenser is in fact higher than the cooling power at the evaporator, since Pcondenser = Pcooling + Pcompressor
- This results in a continuous increasing of the temperature and pressure of the refrigerant of the heat pump system. The compressor cooling fan, the auxiliary condenser and/or other means stabilize the temperature and pressure of the heat pump during steady state phase
- The compressor cooling fan blows ambient air onto the compressor case. Thus, the power given from the compressor itself to the refrigerant is reduced, since a part of the power absorbed by the compressor is wasted by convection. The auxiliary condenser is an additional heat exchanger between the refrigerant and an auxiliary cold source. The auxiliary condenser is arranged downstream the condenser. In the auxiliary condenser the refrigerant is further cooled down, wherein heat is transferred to a source, which may be water or ambient air. Thus, the refrigerant enters the evaporator in more favourable conditions. The cooling capacity is increased. Also the balancing between the cooling and heating capacity is increased.
- The condenser is a heat exchanger at the high pressure side of the refrigerant circuit. The evaporator is a heat exchanger at the low pressure side of the refrigerant circuit.
- The low pressure side of the refrigerant circuit extends from the outlet of the expansion means, e.g. a capillary tube or an adjustable valve, to the inlet of the compressor. The high pressure side of the refrigerant circuit extends from the outlet of the compressor to the inlet of the expansion means.
- An internal heat exchanger can be used to cool down the refrigerant between the condenser and expansion means and to heat up the refrigerant at the outlet of the evaporator.
- The internal heat exchanger allows the refrigerant to enter the evaporator in more favourable conditions. The vapour quality is lower and a part of the refrigerant is in the liquid phase, wherein the cooling capacity of the evaporator is increased. Otherwise the temperature of the refrigerant at the outlet of the low pressure side of the internal heat exchanger, which enters the inlet of the compressor, is higher, and the power required to the compressor increases as well. If cooling capacity increases more than the power required by the compressor, then the internal heat exchanger improves heat pump efficiency.
- The internal heat exchanger in a heat pump system of a tumble dryer allows a shorter transitory phase on the one hand and an improved heat pump performance during the steady state phase on the other hand. The internal heat exchanger can additionally improve the heat pump performance more than usual, if said internal heat exchanger is used to flood the evaporator, so that a part of the refrigerant flowing through the evaporator is maintained in the liquid phase. This occurs, if the superheating phase in the evaporator is provided at the low pressure side of the internal heat exchanger.
- Condensed refrigerant is cooled down as usual in the high pressure side of the internal heat exchanger, while in the low pressure side of the internal heat exchanger the vaporization of the refrigerant is completed and the superheating is performed. Therefore the evaporator improves its cooling performance, because the flooding allows a big heat exchange coefficient of the refrigerant in the liquid phase and the internal heat exchanger can improve the refrigerant sub-cooling at the high pressure side, since at the low pressure side of the internal heat exchanger the refrigerant can exchange both latent and sensible heat, so that more energy is available.
-
EP 999 302 B1 - It is an object of the present invention to provide a laundry dryer with a heat pump system, wherein the heat pump performance is improved by low complexity.
- The object of the present invention is achieved by the laundry dryer with the heat pump system according to claim 1.
- According to the present invention the additional heat exchanger is connected between the outlet of second heat exchanger and the inlet of the compressor and is controlled or controllable by the temperature of the refrigerant in at least one position of the refrigerant circuit and/or by the temperature of the drying air.
- The present invention is based on the additional heat exchanger cooling down the refrigerant before compressor suction, wherein said additional heat exchanger is controlled by the temperature of the refrigerant and/or by the temperature of the drying air. The required power of the compressor decreases by the reduced temperature of the refrigerant after passing the additional heat exchanger.
- Preferably, the additional heat exchanger is provided for a heat exchange between the refrigerant on the one hand and ambient air and/or cooling water on the other hand.
- In particular, the additional heat exchanger corresponds with at least one ambient air fan.
- For example, the additional heat exchanger, the ambient air fan and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an inlet and/or at an outlet of the compressor. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the temperature of the refrigerant at the inlet of the compressor becomes higher than a predetermined value. Said predetermined value may be within a range between 20 °C and 45 °C, especially between 25 °C and 40 °C, in particular between 30 °C and 36 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C. Further, the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the temperature of the refrigerant at the outlet of the compressor becomes higher than a predetermined value. Said predetermined value may be within a range between 50 °C and 110 °C, especially between 60 °C and 100 °C, in particular between 70 °C and 90 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- According to another example, the additional heat exchanger, the ambient air fan and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an inlet and/or at an outlet of the second heat exchanger. The temperature of the refrigerant at the outlet of the second heat exchanger and at the inlet of the additional heat exchanger are identical, if not any further component is arranged between them. In a similar way, the temperature of the refrigerant at the outlet of the second heat exchanger and at the inlet of the compressor are identical, if the additional heat exchanger is switched off and no further component is arranged between them.
- Further, the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the temperature of the refrigerant at an inlet of the additional heat exchanger. In this case, the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the temperature of the refrigerant at the inlet of the additional heat exchanger becomes higher than a predetermined value. Said predetermined value may be within a range between 20 °C and 60 °C, especially between 25 °C and 50 °C, in particular between 30 °C and 36 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if the temperature at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- Moreover, the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the temperature of the refrigerant at an outlet of the first heat exchanger. In this case, the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the temperature of the refrigerant at the outlet of the first heat exchanger becomes higher than a predetermined value. Said predetermined value may be within a range between 40 °C and 65 °C, in particular between 50 °C and 55 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- Further, the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the temperature of the air stream at an inlet of the laundry treatment chamber. In this case, the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the temperature of the air stream at the inlet of the laundry drum becomes higher than a predetermined value. Said predetermined value may be within a range between 50 °C and 75 °C, in particular between 55 °C and 65 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if the temperature of the refrigerant at the inlet of the compressor becomes lower than the previous value minus between 0 °C and 5 °C.
- Additionally or alternatively, the additional heat exchanger, the ambient air fan and/or the cooling water may be controlled or controllable by the difference between the temperatures of the refrigerant at the inlet of the compressor and an inlet of the second heat exchanger.
- Further, the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the difference between the temperatures of the refrigerant at the inlet of the additional heat exchanger and at the inlet of the second heat exchanger becomes higher than a predetermined value. Said predetermined value may be within a range between 5 °C and 60 °C, in particular between 10 °C and 50 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if said difference becomes lower than the previous value minus between 0 °C and 5 °C.
- In a similar way, the additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched on, if the difference between the temperatures of the refrigerant at the inlet and the outlet of the second heat exchanger becomes higher than a predetermined value.
- Said predetermined value may be within a range between 0 °C and 25 °C, in particular between 10 °C and 15 °C. The additional heat exchanger, the ambient air fan and/or the cooling water, respectively, may be switched off, if said difference becomes lower than the previous value minus between 0 °C and 5 °C.
- In particular, a low pressure portion and a high pressure portion of the refrigerant circuit are thermally coupled by at least one internal heat exchanger.
- Thereby, the low pressure portion may extend between the outlet of the expansion means and the inlet of the compressor, and the high pressure portion may extend between the outlet of the compressor and the inlet of the expansion means.
- For example, a high pressure side of the internal heat exchanger is interconnected between an outlet of the first heat exchanger and the inlet of the expansion means.
- Further, a low pressure side of the internal heat exchanger may be interconnected between an outlet of the second heat exchanger and an inlet of the additional heat exchanger.
- The at least one ambient air fan may be switched or switchable in an on-off mode depending on at least one temperature of the refrigerant.
- Alternatively or additionally, the speed of the at least one ambient air fan is continuously variable depending on at least one temperature of the refrigerant.
- Further, the present invention relates to a controller for a laundry dryer or a spinner-washer with a heat pump system mentioned above, wherein the controller is provided for controlling the additional heat exchanger in response to the temperature of the refrigerant in at least one position of the refrigerant circuit.
- The novel and inventive features believed to be the characteristic of the present invention are set forth in the appended claims.
- The invention will be described in further detail with reference to the drawings, in which
- FIG 1
- shows a schematic diagram of a heat pump system for a laundry dryer according to a first embodiment of the present invention,
- FIG 2
- shows a schematic pressure-enthalpy-diagram of a refrigerant in the heat pump system according to the first embodiment of the present invention, and
- FIG 3
- shows a schematic diagram of the heat pump system for the laundry dryer according to a second embodi-ment of the present invention.
-
FIG 1 illustrates a schematic diagram of a heat pump system for a laundry dryer according to a first embodiment of the present invention. The heat pump system includes a closedrefrigerant circuit 10 and a, preferably, closed dryingair circuit 12. - The
refrigerant circuit 10 includes acompressor 14, acondenser 16, expansion means 18, anevaporator 20 and anadditional heat exchanger 22. Thecompressor 14, thecondenser 16, the expansion means 18, theevaporator 20 and theadditional heat exchanger 22 are switched in series and form a closed loop of therefrigerant circuit 10. Theadditional heat exchanger 22 corresponds with anambient air fan 24. - 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 thecompressor 14 via thecondenser 16 to the inlet of the expansion means 18. The low pressure portion extends from the outlet of the expansion means 18 via theevaporator 20 and theadditional heat exchanger 22 to the inlet of thecompressor 14. - The refrigerant, for example carbon dioxide, can operates at a supercritical mode in the high pressure portion of the
refrigerant circuit 10. In the high pressure portion the refrigerant is at least at the critical pressure and always in gas phase so that the condenser is better indicated as a gas cooler. In the low pressure portion of therefrigerant circuit 10 the refrigerant can also operate at the supercritical mode so that the evaporator is better indicated as a gas heater. - The during
air circuit 12 includes thecompressor 14, a dryingair stream fan 26, a laundry treatment chamber for accommodating theclothes 28, preferably arotatable drum 28, thecondenser 16 and theevaporator 20. Thecondenser 16 and theevaporator 20 are heat exchangers and form the thermal interconnections between therefrigerant circuit 10 and the dryingair circuit 12. Theevaporator 20 cools down and dehumidifies the drying air, after said drying air has passed thelaundry drum 28. Then thecondenser 16 heats up the air stream, before the drying air is re-inserted into thelaundry drum 28. The drying air is driven by the dryingair stream fan 26. - In the refrigerant circuit 10 a refrigerant is compressed by the
compressor 14, condensed in thecondenser 16, laminated in the expansion means 18, vaporised in theevaporator 20 and cooled down in theadditional heat exchanger 22. Theadditional heat exchanger 22 cools down the refrigerant by ambient air before the suction by thecompressor 14. The ambient air may be driven by theambient air fan 24. - The required power of the
compressor 14 decreases by the reduced temperature of the refrigerant after passing theadditional heat exchanger 22. Considering the pressures in the high pressure portion and the low pressure portion of therefrigerant circuit 10 as constant, the lower the temperature of the refrigerant at the inlet of thecompressor 14, the lower the power for compressing the refrigerant by thecompressor 14. - Further, the temperature at the inlet of the
compressor 14 is kept within a predetermined range. On the one hand, the temperature of the refrigerant at the inlet ofcompressor 14 should not be too low, since refrigerant superheating is required to prevent liquid refrigerant from entering thecompressor 14, thereby avoiding damages. - On the other hand, the temperature at the outlet of the
compressor 14 could be too low, so that the refrigerant cannot heat up the drying air to the desired temperature via thecondenser 16. - The temperature at the inlet of the
compressor 14 is controlled by theambient air fan 24. An upper limit of the predetermined range for the temperature at the inlet of thecompressor 14 depends on the properties of saidcompressor 14. Usually, the upper limit for the temperature at the inlet of thecompressor 14 is about 40°C. A lower limit of the predetermined range for the temperature at the inlet of thecompressor 14 depends on several thermodynamic parameters, in particular on the pressure in the low pressure portion of therefrigerant circuit 10 and on the temperature at the inlet of thecompressor 14. Said pressure and temperature determine whether the refrigerant is completely vaporized or not at the inlet of thecompressor 14. - The operation cycle of the heat pump system is subdivided into a transitory phase and a steady state phase. The transitory phase is the initial phase after the heat pump system has been switched on. Before the heat pump system starts, the temperatures of the air stream and of the refrigerant are at ambient temperature. During the transitory phase, the temperatures of the air stream and the refrigerant increase up to a desired level.
- The
ambient air fan 24 of theadditional heat exchanger 22 can work in an on-off mode or can be driven at a variable speed to maintain the temperature range at the compressor within predetermined value. During the steady state phase of the operation cycle the upper limit for the temperature range at the inlet of thecompressor 14 is between 25°C and 40°C. The lower limit for the temperature range at the inlet of thecompressor 14 is between 20°C and 35°C during the steady state phase of the operation cycle. - Additionally, the
ambient air fan 24 of theadditional heat exchanger 22 may be switched off, if the temperature of the refrigerant at the outlet of thecompressor 14 becomes too low, for example below 70°C. - A further control strategy for the
ambient air fan 24 of theadditional heat exchanger 22 may be the maintaining of a minimum difference between the temperature of the refrigerant at the inlet of thecompressor 14 and the temperature of the refrigerant at the inlet of theevaporator 20. Said minimum temperature difference is between 0°C and 10°C, preferably greater than 5°C. This minimum temperature difference assures a certain margin of superheating of the refrigerant before entering thecompressor 14. If the actual temperature difference is less than said minimum difference temperature value, then theambient air fan 24 of theadditional heat exchanger 22 is switched off. - The heat pump system comprises a set of temperature sensors within the
refrigerant circuit 10 in order to detect the temperature of the refrigerant. In particular, the temperature sensors are arranged at the inlet of thecompressor 14, at the inlet of theevaporator 20 and/or at the outlet of thecompressor 14. -
FIG 2 illustrates a schematic pressure-enthalpy-diagram of the refrigerant in the heat pump system according to the first embodiment of the present invention. The diagram shows the pressure p of the refrigerant as a function of the specific enthalpy h. - A
curve 32 marks the limit between the portions of the sub-critical conditions and the over-critical conditions of the refrigerant. The sub-critical conditions of the refrigerant occur within the portion inside thecurve 32. The over-critical conditions occur in the portion outside thecurve 32. - A first state a and a modified first state a', respectively, correspond with the refrigerant at the inlet of the
condenser 16. A second state b corresponds with the refrigerant at the outlet of thecondenser 16. A third state c corresponds with the refrigerant at the inlet of theevaporator 20. A fourth state d and a modified fourth state d', respectively, corresponds with the refrigerant at the inlet of thecompressor 14. The modified first state a' and the modified fourth state d' occur, when theambient air fan 24 of theadditional heat exchanger 22 is switched on. - When the
ambient air fan 24 of theadditional heat exchanger 22 is switched off, then the refrigerant follows the cycle with the states a, b, c, d and a again. When theambient air fan 24 of theadditional heat exchanger 22 is switched on, then the refrigerant follows the cycle with the states a', b, c, d, d' and a' again. - When the
ambient air fan 24 of theadditional heat exchanger 22 is switched off, then an unbalancing of the heat pump system is proportional to the difference between the segments a-b and c-d of the diagram inFIG 2 . When theambient air fan 24 of theadditional heat exchanger 22 is switched on, then the unbalancing of the heat pump system is proportional to the difference between the segments a'-b and c-d in the diagram ofFIG 2 . Thus, when theambient air fan 24 of theadditional heat exchanger 22 is switched on, then the unbalancing of the heat pump system is reduced. - Further, the power absorbed by the
compressor 14 is reduced, when theambient air fan 24 of theadditional heat exchanger 22 is switched on. In this case, thecompressor 14 transfers the refrigerant from a modified fourth state d' to the modified first state a', instead of a transfer from the fourth state d to the first state a. -
FIG 3 illustrates a schematic diagram of a heat pump system for a laundry dryer according to a second embodiment of the present invention. The heat pump system includes the closedrefrigerant circuit 10 and the, preferably closed dryingair circuit 12. Unlike the first embodiment of the present invention, the second embodiment includes additionally aninternal heat exchanger 30. - The
refrigerant circuit 10 includes thecompressor 14, thecondenser 16, the expansion means 18, theevaporator 20, theadditional heat exchanger 22 and theinternal heat exchanger 30. Thecompressor 14, thecondenser 16, a high pressure side of theinternal heat exchanger 30, the expansion means 18, theevaporator 20, a low pressure side of theinternal heat exchanger 30, and theadditional heat exchanger 22 are switched in series and form the closed loop of therefrigerant circuit 10. Theadditional heat exchanger 22 corresponds with theambient air fan 24. - The drying
air circuit 12 includes thecompressor 14, anair stream fan 26, alaundry drum 28, thecompressor 14 and theevaporator 20. Thecondenser 16 and theevaporator 20 are heat exchangers and form the thermal interconnections between therefrigerant circuit 10 and the dryingair circuit 12. Theevaporator 20 cools down and dehumidifies an air stream, after said air stream has passed thelaundry drum 28. Then thecondenser 16 heats up the air stream, before the air stream is re-inserted into thelaundry drum 28. The air stream is driven by theair stream fan 26. - In the
refrigerant circuit 10 the refrigerant is compressed by thecompressor 14, condensed in thecondenser 16, cooled down in the high pressure side of theinternal heat exchanger 30, laminated in the expansion means 18, vaporised in theevaporator 20, heated up in the low pressure side of theinternal heat exchanger 30 and cooled down in theadditional heat exchanger 22. Theadditional heat exchanger 22 cools down the refrigerant by ambient air before the suction by thecompressor 14. The ambient air may be driven by theambient air fan 24. - The
internal heat exchanger 30 allows a heat exchange between the high pressure portion and the low pressure portion of therefrigerant circuit 10. The high pressure portion of the second embodiment extends from the outlet of thecompressor 14 via thecondenser 16 and the high pressure side of theinternal heat exchanger 30 to the inlet of the expansion means 18. The low pressure portion of the second embodiment extends from the outlet of the expansion means 18 via theevaporator 20, the low pressure side of theinternal heat exchanger 30 and theadditional heat exchanger 22 to the inlet of thecompressor 14. - The
ambient air fan 24 of theadditional heat exchanger 22 is controlled in the same way as in the first embodiment as described above. Theinternal heat exchanger 30 cools down the refrigerant in the low pressure portion additionally by the refrigerant in the high pressure portion. - Although illustrative embodiments of the present invention have been described herein with reference to the accompanying drawings, it is to be understood that the present invention is not limited to those precise embodiments, and that various other changes and modifications may be affected therein by one skilled in the art without departing from the scope or spirit of the invention. All such changes and modifications are intended to be included within the scope of the invention as defined by the appended claims.
-
- 10
- refrigerant circuit
- 12
- drying air circuit
- 14
- compressor
- 16
- condenser, first heat exchanger
- 18
- expansion means
- 20
- evaporator, second heat exchanger
- 22
- additional heat exchanger
- 24
- ambient air fan
- 26
- air stream fan
- 28
- laundry drum
- 30
- internal heat exchanger
- 32
- curve between sub- and over-critical conditions
- a
- first state of the refrigerant
- a'
- modified first state of the refrigerant
- b
- second state of the refrigerant
- c
- third state of the refrigerant
- d
- fourth state of the refrigerant
- d'
- modified fourth state of the refrigerant
- h
- specific enthalpy of the refrigerant
- p
- pressure of the refrigerant
Claims (13)
- A laundry dryer with a heat pump system, said heat pump system comprises a refrigerant circuit (10) for a refrigerant and an drying air circuit (12) for drying air, wherein- the refrigerant circuit (10) includes a compressor (14), a first heat exchanger (16), expansion means (18) and a second heat exchanger (20) connected in series and forming a closed loop,- the drying air circuit (12) includes the first heat exchanger (16), at least one air stream fan (30), a laundry treatment chamber (28) and the second heat exchanger (20) connected in series and forming a closed loop,- the refrigerant circuit (10) and the drying air circuit (12) are thermally coupled by the first heat exchanger (16) and the second heat exchanger (20),- the first heat exchanger (16) is provided for heating up the air stream and cooling down the refrigerant,- the second heat exchanger (20) is provided for cooling down the drying air and heating up the refrigerant, and- the refrigerant circuit (10) includes at least one additional heat exchanger (22),characterized in, that
the additional heat exchanger (22) is connected between the outlet of second heat exchanger (20) and the inlet of the compressor (14) and is controlled or controllable by the temperature of the refrigerant in at least one position of the refrigerant circuit (10) and/or by the temperature of the drying air. - The heat pump system according to claim 1, characterized in, that
the additional heat exchanger (22) is provided for a heat exchange between the refrigerant on the one hand and ambient air and/or cooling water on the other hand. - The heat pump system according to claim 1 or 2, characterized in, that
the additional heat exchanger (22) corresponds with at least one ambient air fan (26). - The heat pump system according to any one of the preceding claims,
characterized in, that
the additional heat exchanger (22), the ambient air fan (26) and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an inlet and/or at an outlet of the compressor (14). - The heat pump system according to any one of the preceding claims,
characterized in, that
the additional heat exchanger (22), the ambient air fan (26) and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an inlet and/or at an outlet of the second heat exchanger (20) . - The heat pump system according to any one of the preceding claims,
characterized in, that
the additional heat exchanger (22), the ambient air fan (26) and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an inlet of the additional heat exchanger (22). - The heat pump system according to any one of the preceding claims,
characterized in, that
the additional heat exchanger (22), the ambient air fan (26) and/or the cooling water are controlled or controllable by the temperature of the refrigerant at an outlet of the first heat exchanger (16). - The heat pump system according to any one of the preceding claims,
characterized in, that
the additional heat exchanger (22), the ambient air fan (26) and/or the cooling water are controlled or controllable by the temperature of the drying air at an inlet of the laundry treatment chamber (28). - The heat pump system according to any one of the preceding claims,
characterized in, that
the additional heat exchanger (22), the ambient air fan (26) and/or the cooling water are controlled or controllable by the difference between the temperatures of the refrigerant at the inlet of the additional heat exchanger (22)and at the inlet of the second heat exchanger (20). - The heat pump system according to any one of the preceding claims,
characterized in, that
the additional heat exchanger (22), the ambient air fan (26) and/or the cooling water are controlled or controllable by the difference between the temperatures of the refrigerant at the inlet of the additional heat exchanger (22) and at the inlet of the second heat exchanger (20). - The heat pump system according to any one of the preceding claims,
characterized in, that
a low pressure portion and a high pressure portion of the refrigerant circuit (10) are thermally coupled by at least one internal heat exchanger (30) having a high pressure side interconnected between an outlet of the first heat exchanger (16) and the inlet of the expansion means (18) and a low pressure side interconnected between an outlet of the second heat exchanger (20) and an inlet of the additional heat exchanger (22). - The heat pump system according to any one of the claims 3 to 11,
characterized in, that
the at least one ambient air fan (26) is switched or switchable in an on-off mode and/or the speed of said ambient air fan (26) is continuously variable depending on at least one temperature of the refrigerant and/or drying air. - A controller for a laundry dryer or a spinner-washer with a heat pump system according to any one of the claims 1 to 14,
characterized in, that
the controller is provided for controlling the additional heat exchanger (22) in response to the temperature of the refrigerant in at least one position of the refrigerant circuit (10).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11171923.3A EP2540905B1 (en) | 2011-06-29 | 2011-06-29 | A laundry dryer with heat pump system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11171923.3A EP2540905B1 (en) | 2011-06-29 | 2011-06-29 | A laundry dryer with heat pump system |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2540905A1 true EP2540905A1 (en) | 2013-01-02 |
EP2540905B1 EP2540905B1 (en) | 2015-02-25 |
Family
ID=44512598
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11171923.3A Active EP2540905B1 (en) | 2011-06-29 | 2011-06-29 | A laundry dryer with heat pump system |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP2540905B1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111945401A (en) * | 2019-05-17 | 2020-11-17 | Bsh家用电器有限公司 | Appliance for drying laundry and method for operating a heat pump of such an appliance |
WO2022030815A1 (en) * | 2020-08-06 | 2022-02-10 | 엘지전자 주식회사 | Heat pump and control method therefor |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108951047B (en) * | 2017-05-17 | 2021-10-01 | 青岛海尔洗涤电器有限公司 | Heat pump system capable of adjusting system load, clothes dryer and control method |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19638865A1 (en) * | 1995-09-23 | 1997-03-27 | Miele & Cie | Condensation laundry dryer |
EP0999302B1 (en) | 1998-10-21 | 2003-08-20 | Whirlpool Corporation | Tumble dryer with a heat pump |
US20050066538A1 (en) * | 2003-09-29 | 2005-03-31 | Michael Goldberg | Heat pump clothes dryer |
US20050198852A1 (en) * | 2004-03-10 | 2005-09-15 | Sanyo Electric Co., Ltd. | Drying machine |
EP1811076A1 (en) * | 2006-01-20 | 2007-07-25 | SANYO ELECTRIC Co., Ltd. | Drying machine |
-
2011
- 2011-06-29 EP EP11171923.3A patent/EP2540905B1/en active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19638865A1 (en) * | 1995-09-23 | 1997-03-27 | Miele & Cie | Condensation laundry dryer |
EP0999302B1 (en) | 1998-10-21 | 2003-08-20 | Whirlpool Corporation | Tumble dryer with a heat pump |
US20050066538A1 (en) * | 2003-09-29 | 2005-03-31 | Michael Goldberg | Heat pump clothes dryer |
US20050198852A1 (en) * | 2004-03-10 | 2005-09-15 | Sanyo Electric Co., Ltd. | Drying machine |
EP1811076A1 (en) * | 2006-01-20 | 2007-07-25 | SANYO ELECTRIC Co., Ltd. | Drying machine |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111945401A (en) * | 2019-05-17 | 2020-11-17 | Bsh家用电器有限公司 | Appliance for drying laundry and method for operating a heat pump of such an appliance |
CN111945401B (en) * | 2019-05-17 | 2024-04-26 | Bsh家用电器有限公司 | Appliance for drying laundry and method for operating a heat pump of the appliance |
WO2022030815A1 (en) * | 2020-08-06 | 2022-02-10 | 엘지전자 주식회사 | Heat pump and control method therefor |
Also Published As
Publication number | Publication date |
---|---|
EP2540905B1 (en) | 2015-02-25 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2489774B1 (en) | A heat pump laundry dryer | |
EP2468946B1 (en) | A heat pump system for a laundry dryer and a method for operating a heat pump laundry dryer | |
KR100755160B1 (en) | Control of refrigeration system | |
EP2594687B1 (en) | A laundry dryer with a heat pump system | |
EP2468947B1 (en) | A heat pump system for a laundry dryer and a method for operating a heat pump system of a laundry dryer | |
US10662575B2 (en) | Clothes dryer and method for controlling same | |
TW200937001A (en) | Test chamber with temperature and humidity control | |
CN105316920B (en) | Dryer and dryer heat pump system and its control method | |
EP2551401A1 (en) | A heat pump system for a laundry dryer | |
EP2540905B1 (en) | A laundry dryer with heat pump system | |
JP2004313765A (en) | Drier and method of operating the same | |
EP2594688B1 (en) | A laundry dryer with a heat pump system | |
EP2527522B1 (en) | A heat pump laundry dryer | |
KR101718041B1 (en) | Clothes dryer and method for controlling the same | |
EP2586905B1 (en) | A laundry dryer with a heat pump system | |
EP2527521A1 (en) | A heat pump laundry dryer | |
KR102348960B1 (en) | A Laundry treating apparatus comprising a heat pump and control method of the same. | |
EP2586907B1 (en) | A laundry dryer with a heat pump system and air recirculation | |
KR200405714Y1 (en) | Heat-pump type heating apparatus | |
KR200405760Y1 (en) | hEAT-EXCHANGING APPARATUS RAISING THE HEATING CAPACITY | |
JP2013122333A (en) | Container refrigeration apparatus | |
JP3721963B2 (en) | Refrigeration equipment | |
KR20070043553A (en) | Heat-pump type heating apparatus |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
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 |
|
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 |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
17P | Request for examination filed |
Effective date: 20130702 |
|
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 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20140924 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
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 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602011013904 Country of ref document: DE Effective date: 20150409 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 712113 Country of ref document: AT Kind code of ref document: T Effective date: 20150415 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20150225 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 712113 Country of ref document: AT Kind code of ref document: T Effective date: 20150225 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
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: 20150225 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: 20150225 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: 20150225 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: 20150225 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: 20150525 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: 20150225 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20150625 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: 20150225 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: 20150225 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: 20150526 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: 20150225 |
|
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: 20150225 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20150225 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: 20150225 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: 20150225 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: 20150225 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: 20150225 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602011013904 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20150225 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20150225 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
26N | No opposition filed |
Effective date: 20151126 |
|
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: 20150629 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: 20150225 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
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: 20150630 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150629 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150630 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20150225 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 6 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20160621 Year of fee payment: 6 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20160627 Year of fee payment: 6 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20150225 |
|
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: 20110629 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: 20150225 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: 20150225 |
|
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: 20150225 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20150225 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170629 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180228 |
|
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: 20170629 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170630 |
|
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: 20150225 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: 20150225 |
|
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: 20150225 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230625 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20230620 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240627 Year of fee payment: 14 |