WO2014146704A1 - Appareil pour sécher le linge - Google Patents

Appareil pour sécher le linge Download PDF

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Publication number
WO2014146704A1
WO2014146704A1 PCT/EP2013/055783 EP2013055783W WO2014146704A1 WO 2014146704 A1 WO2014146704 A1 WO 2014146704A1 EP 2013055783 W EP2013055783 W EP 2013055783W WO 2014146704 A1 WO2014146704 A1 WO 2014146704A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
compressor
appliance
cooling
Prior art date
Application number
PCT/EP2013/055783
Other languages
English (en)
Inventor
Francesco Cavarretta
Alberto Bison
Original Assignee
Electrolux Appliances Aktiebolag
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.)
Filing date
Publication date
Application filed by Electrolux Appliances Aktiebolag filed Critical Electrolux Appliances Aktiebolag
Priority to PCT/EP2013/055783 priority Critical patent/WO2014146704A1/fr
Priority to CN201380075793.7A priority patent/CN105121730A/zh
Priority to EP13713781.6A priority patent/EP2976454A1/fr
Publication of WO2014146704A1 publication Critical patent/WO2014146704A1/fr

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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 appliances for drying laundry, like laundry dryers and laundry washer s/dryers.
  • Appliances for drying laundry like laundry dryers (tumble dryers) and laundry washers/dryers, generally comprise a drying chamber for accommodating therein the laundry to be dried.
  • a heated and dehumidified drying medium typically air
  • the heated and dehumidified drying medium takes up humidity and at the same time cools down.
  • the drying medium then exits the drying chamber, thereby discharging humidity from the drying chamber and the laundry.
  • Heat pump technology is, at present, the most energy efficient way to dry laundry.
  • Heat pumps generally operate with refrigerants as working fluids.
  • the drying medium i.e. drying air (i.e. process air)
  • the drying air impelled by a fan, passes through the drying chamber (drum) removing water from wet clothes, then it is cooled down and dehumidified in a heat pump evaporator (main evaporator - a heat exchanger wherein the process air releases heat to the refrigerant), and heated up in a heat pump condenser (main condenser - a heat exchanger wherein the refrigerant releases heat to the process air), to be re-introduced into the drum.
  • a heat pump evaporator main evaporator - a heat exchanger wherein the process air releases heat to the refrigerant
  • a heat pump condenser main condenser - a heat exchanger wherein the refrigerant releases heat to the process air
  • the refrigerant instead is compressed by a compressor, condensed in the main condenser, expanded in an expansion device (e.g. an expansion valve or a capillary tube) and then vaporised in the evaporator.
  • an expansion device e.g. an expansion valve or a capillary tube
  • the Applicant has tackled the problem of improving the operation of the heat pump in a heat pump dryer.
  • the Applicant has found that a certain amount of sub-cooling at the inlet of the expansion device improves the performances of the heat pump dryer, because the expansion device is fed up with refrigerant in complete liquid state and then it works properly, otherwise the expansion process is not regular.
  • a high level of sub-cooling allows the evaporator to be fed up with the refrigerant in more favorable conditions, and thus the evaporator cooling power can increase.
  • the Applicant has found that if the sub-cooling is achieved or increased by the use of an auxiliary condenser placed downstream the main condenser before the expansion device, and that exchanges heat with a medium different from the drying air (for example ambient air or condensed water), the temperature of the drying air could happen to be decreased, penalizing the efficiency of the drying process.
  • a medium different from the drying air for example ambient air or condensed water
  • an operating cycle of a heat pump dryer can be divided into two main phases: a first, transitory phase, followed by a second, operative phase.
  • first phase the drying air and the refrigerant fluid temperatures (that usually are at ambient temperature when the tumble dryer starts operating) are increased up to reach respective desired operating levels, suitable to dry the laundry; the laundry are mainly dried during the second phase (although also during the first phase the laundry is dried to a certain, limited extent).
  • the Applicant has found that, for increasing the efficiency of the heat pump system in terms of cooling power of the drying air (for efficiently removing the moisture therefrom), it is advantageous to keep the refrigerant sub-cooling level at the expansion device inlet in a certain range at least for a portion of the drying cycle, preferably after the above-mentioned first, transitory phase.
  • the drying cycle portion can for example correspond to the above-mentioned second phase.
  • the refrigerant sub-cooling level is defined in terms of the degrees, in a temperature scale like °C, at which the refrigerant in saturated liquid state is sub- cooled, measured at the inlet of the expansion device.
  • Said portion of the drying cycle can be a percentage of the above-mentioned second phase of the drying cycle (e.g. 100 %, or at least 70 %, or at least 50 % of the second phase).
  • the Applicant has observed that a high efficiency of the heat pump system is attained if the heat pump system elements (e.g., the heat exchangers, and/or the expansion device, and/or the compressor) are designed and/or operated so that the refrigerant sub-cooling level measured at the inlet of the expansion device is between 5 °C to 15 °C, preferably between 5 °C to 10 °C, more preferably between 6 °C to 9 °C during a relevant part of the drying cycle (e.g. 100 %, or at least 70 %, or at least 50 %).
  • the heat pump system elements e.g., the heat exchangers, and/or the expansion device, and/or the compressor
  • the Applicant has also found that a certain degree of super-heating of the refrigerant is useful to avoid that refrigerant fluid in liquid phase enters the compressor.
  • the super-heating of the refrigerant can be achieved by properly dimensioning the main evaporator of the heat pump system. However, in order not to penalize the performance, it may be preferable to relief the main evaporator from this task, and provide auxiliary means (like for example one or more auxiliary evaporators) for accomplishing the super-heating.
  • the refrigerant super-heating level is defined in terms of the degrees, in a temperature scale like °C, at which the refrigerant in saturated vapour state is superheated, measured at the input of the heat pump compressor.
  • the Applicant has found that a level of super-heating of the refrigerant (at the input of the compressor) between 6 °C and 22 °C, preferably between 6 °C and 15 °C, more preferably between 6 °C and 10 °C, during the above-mentioned portion of the drying cycle is suitable.
  • an appliance for drying laundry has a heat pump system having a refrigerant circuit.
  • the appliance comprises:
  • a first heat exchanger for heating a refrigerant and cooling the drying medium
  • a second heat exchanger for cooling the refrigerant and heating the drying medium
  • a refrigerant expansion device arranged in the refrigerant circuit between the second heat exchanger and the first heat exchanger and
  • a compressor arranged in the refrigerant circuit between the first heat exchanger and the second heat exchanger.
  • the heat pump system is advantageously designed to operate so that a level of sub-cooling of the refrigerant in the heat pump system is between 5 °C and 15 °C measured at the inlet of the refrigerant expansion device.
  • the heat pump system is designed to operate so that the level of sub-cooling of the refrigerant in the heat pump system is between 5 °C and 15 °C measured at the inlet of the refrigerant expansion device for a part of the drying cycle following an initial transitory part of the drying cycle during which the medium temperature and the refrigerant temperature are increased up to respective operating levels suitable to remove moisture from the laundry being dried.
  • the heat pump system is designed to operate so that the level of sub-cooling of the refrigerant in the heat pump system is between 5 °C and 15 °C measured at the inlet of the refrigerant expansion device for at least a percentage, particularly 100 %, or 70 %, or 50 %, of said part of the drying cycle following the initial transitory part.
  • the appliance may comprise a compressor cooling fan provided for cooling the compressor by means of ambient air, and the activation/de-activation of the compressor cooling fan or the speed of the compressor cooling fan is controlled based on the detection of the refrigerant temperature in at least one location along the refrigerant circuit portion, preferably at the inlet of the refrigerant expansion device and/or at the output of the compressor, whereby the compressor cooling fan is controlled so as to attain said level of sub-cooling of the refrigerant.
  • a compressor cooling fan provided for cooling the compressor by means of ambient air
  • the activation/de-activation of the compressor cooling fan or the speed of the compressor cooling fan is controlled based on the detection of the refrigerant temperature in at least one location along the refrigerant circuit portion, preferably at the inlet of the refrigerant expansion device and/or at the output of the compressor, whereby the compressor cooling fan is controlled so as to attain said level of sub-cooling of the refrigerant.
  • the compressor is a variable speed or variable power compressor, and the compressor action is controlled based on the detection of the refrigerant temperature in at least one location along the refrigerant circuit portion, preferably at the inlet of the refrigerant expansion device and/or at the output of the compressor, whereby the compressor is controlled so as to attain said level of sub-cooling.
  • the heat pump system comprises only said first heat exchanger for the exchange of heat between the refrigerant and the drying medium, and only said second heat exchanger for the exchange of heat between the refrigerant and the drying medium, without auxiliary heat exchangers for the exchange of heat between the refrigerant and a medium different from the drying medium.
  • the heat pump system comprises at least one internal, refrigerant-refrigerant heat-exchanger arranged to cause transfer of heat by the refrigerant in a high-pressure portion of the refrigerant circuit to the refrigerant in a low-pressure portion of the refrigerant circuit.
  • the heat pump system may further comprises at least one first auxiliary, refrigerant-air heat exchanger arranged in a high-pressure portion of the refrigerant circuit, for causing a transfer of heat by the refrigerant to ambient air taken in from outside the appliance, and an associated first auxiliary heat exchanger fan, whereby the first auxiliary heat exchanger fan is controlled so as to attain said level of sub- cooling of the refrigerant.
  • the first auxiliary heat exchanger may be is arranged downstream the second heat exchanger.
  • the first auxiliary heat exchanger is arranged upstream a high-pressure side of the internal refrigerant-refrigerant heat exchanger.
  • the first auxiliary heat exchanger is arranged downstream a high-pressure side of the internal refrigerant-refrigerant heat exchanger.
  • said first auxiliary heat exchanger fan may be the compressor cooling fan.
  • the heat pump system can be operated so that a level of super-heating of the refrigerant in the heat pump system is between 6 °C and 22 °C, preferably between 6 °C and 15 °C, more preferably between 6 °C and 10 °C, measured at the input of the compressor.
  • the heat pump system may comprises at least one second auxiliary, refrigerant-air heat exchanger arranged in a low-pressure portion of the refrigerant circuit, for causing a transfer of heat by ambient air taken in from outside the appliance to the refrigerant, and an associated second auxiliary heat exchanger fan operatively associated with said at least one second auxiliary heat exchanger, whereby the second auxiliary heat exchanger fan is controlled so as to attain said level of superheating of the refrigerant.
  • the second auxiliary heat exchanger may be is arranged downstream the first heat exchanger.
  • the second auxiliary heat exchanger may be arranged upstream a low- pressure side of the internal refrigerant-refrigerant heat exchanger.
  • the second auxiliary heat exchanger may be arranged downstream a low- pressure side of the internal refrigerant-refrigerant heat exchanger.
  • said second auxiliary heat exchanger fan may be the compressor cooling fan.
  • Figure 1 schematically shows a heat pump laundry dryer according to an embodiment of the present invention
  • Figure 2 is a pressure versus enthalpy diagram of the fluid R407C
  • FIGS. 3 - 14 schematically show several different embodiments of heat pump laundry dryer according to the present invention.
  • Figure 15 is an isometric view of the heat pump laundry dryer, with one lateral wall of an appliance cabinet removed;
  • Figure 16 shows in exploded view a basement of the laundry dryer of Figure 15 configured for accommodating the heat pump
  • Figure 17 shows a lower part of the basement of Figure 16 from another side, in an embodiment of the present invention.
  • Figure 18 shows the lower part of the basement in another embodiment of the present invention
  • Figure 19 is a time chart exemplifying the variations of temperature of the refrigerant fluid at some points of the refrigerant fluid circuit during an exemplary drying cycle.
  • FIG. 1 schematically shows a heat pump laundry dryer 1 according to an embodiment of the present invention. It is pointed out that although in the following description a heat pump laundry dryer is considered, this choice is merely exemplary, because the present invention applies also to laundry washing machines having also a laundry drying functionality.
  • the heat pump laundry dryer 1 comprises a drying chamber 2, preferably a rotatable drum (drying drum), however the present invention also applies to laundry dryers without a rotatable drum (cabinet dryer).
  • the drying drum 2 accommodates wet laundry 3 to be dried.
  • a drying medium 4 such as air (process air)
  • a drying medium circuit which preferably forms a closed-loop circuit (however, the present invention also applies to dryers with an open-loop drying medium circuit, in which the drying air is taken in from the external environment, and exhausted into the environment after having been de-hydrated).
  • the drying medium 4 heated to a temperature for example of about 70°C at the most and thereby having a comparatively low relative humidity, is fed into the drying drum 2 and impinges the wet laundry 3. As a consequence, humidity of the wet laundry 3 is absorbed by the drying medium 4 thereby drying the laundry 3. As the laundry 3 in the drying drum 2 receives heat from the drying medium, the drying medium 4 also cools down when passing through the drying drum 2, for example to temperatures of about 30°C.
  • the drying medium 4 After having passed through the drying drum 2, the drying medium 4, having now a comparatively high relative humidity, exits the drying drum 2 and is further cooled down to condense humidity therefrom. After that, the drying medium 4 is recirculated through the drying drum 2. Before re-entering the drying drum 2, the drying medium 4 is heated up again, thereby reducing its relative humidity once again.
  • the heat pump tumble dryer 1 For dehumidifying and (re)heating the drying medium 4, the heat pump tumble dryer 1 comprises a heat pump system or unit 5.
  • the heat pump unit 5 exemplarily comprises a refrigerant evaporator 6 and a refrigerant liquefier 7.
  • the heat pump unit 5 further comprises a compressor 8 interconnected between the refrigerant evaporator 6 and the refrigerant liquefier 7.
  • a refrigerant evaporator outlet 9 is connected to a compressor inlet 10 and a compressor outlet 11 is connected to a refrigerant liquefier inlet 12.
  • a refrigerant liquefier outlet 13 is connected via an expansion device 14, for example a throttling element, an expansion valve, a capillary tube, to a refrigerant evaporator inlet 15.
  • an expansion device 14 for example a throttling element, an expansion valve, a capillary tube
  • the drying air i.e. process air
  • the drying air passes through the drying chamber (drum) removing water from wet clothes, then it is cooled down and dehumidified in the refrigerant evaporator, and heated up in the refrigerant liquefier, to be re- introduced into the drum.
  • the refrigerant instead is compressed by the compressor 8, condensed in the liquefier 7, expanded in the expansion device 14 and then vaporised in the evaporator 6. In this way, residual heat from the drying medium exiting the drying chamber can be extracted therefrom and transferred again to the drying medium before it re-enters the drying chamber.
  • the refrigerant, coming from the compressor 8, is de-superheated (i.e. it is cooled down to the saturation temperature corresponding to the current operating pressure of the refrigerant, then it is condensed and sub-cooled (i.e. it is cooled down below saturation temperature corresponding to the current operating pressure of the refrigerant in the liquefier 7.
  • the refrigerant corning from the expansion device 14 is vaporized and superheated (i.e. it is warmed up to a temperature level higher than the saturation temperature corresponding to the current operating pressure of the refrigerant in the evaporator 6).
  • the relatively low temperature at the refrigerant evaporator 6 is used to cool the drying medium 4 down so as to condensate humidity, i.e. to dehumidify the drying medium 4 exiting the drying drum 2.
  • the elevated temperature at the refrigerant liquefier 7 is used to re-heat the drying medium 4 which in turn is then fed to the drying drum 2 for drying the laundry 3.
  • auxiliary heat exchanger is intended to be a heat exchanger for the exchange of heat between the ref4rigerant fluid and a medium different from the process (i.e. , drying) air.
  • auxiliary liquefiers and/or one or more auxiliary evaporators
  • the heat pump unit 5 may further comprise auxiliary heat exchangers for further optimizing energy efficiency.
  • an auxiliary refrigerant evaporator and/or an auxiliary refrigerant liquefier may be provided.
  • An auxiliary refrigerant evaporator may be used to speed up the heat-up phase of the heat pump dryer; an auxiliary refrigerant liquefier may be used to balance the excess of energy of the heat pump dryer.
  • the Applicant has found that it is beneficial to properly choose the level of sub-cooling of the refrigerant fluid.
  • An operating cycle of a heat pump tumble dryer can be divided into two main phases: a first, transitory phase, followed by a second, operative phase.
  • first phase the drying air temperature and the refrigerant fluid temperature (that usually are at ambient temperature when the tumble dryer starts operating) are increased up to reach respective desired operating levels, suitable to dry the laundry.
  • the drying of the laundry mainly takes place during the second phase (although also during the first phase the laundry is dried to a certain, limited extent).
  • Figure 19 is a time chart exemplifying the variations of temperature of the refrigerant fluid at some points of the refrigerant fluid circuit (curve A: at the compressor outlet; curve B: at the main liquefier outlet; curve C: at the compressor inlet; curve D: at the main evaporator inlet) during an exemplary drying cycle. It can be seen that during the first phase (approximately 40 minutes in the shown example) the temperatures essentially rise, to reach the operating temperature values, and then during the second phase the temperatures remain more or less constant.
  • the refrigerant sub- cooling level at the expansion device 14 inlet is kept in a certain range at least for a portion of the drying cycle, for increasing the efficiency of the heat pump system in terms of cooling power of the drying air.
  • the drying cycle portion can for example correspond to the above-mentioned second phase of the drying cycle.
  • the portion of the drying cycle can be a percentage of the second phase of the drying cycle (e.g., 100%, or at least 70%>, or at least 50%).
  • the heat pump elements e.g. the heat exchangers, the expansion device, the compressor
  • the heat pump elements are designed and/or operated so that the refrigerant sub-cooling level at the inlet of the expansion device 14 is between 5 °C and 15 °C, or between 5 °C and 10 °C, or between 6 °C and 9 °C, during a relevant part of the drying cycle. This allows achieving the highest efficiency of the heat pump system.
  • a certain amount of refrigerant super-heating is provided in the heat pump unit 5.
  • a certain degree of super-heating of the refrigerant is useful to avoid that refrigerant fluid in liquid phase enters the compressor.
  • the refrigerant superheating level is between 6 °C and 22 °C, preferably between 6 °C and 15 °C, more preferably between 6 °C and 10 °C, measured at the input of the compressor 8.
  • the diagram shows the pressure over enthalpy of a possible fluid that can be used as a refrigerant in the heat pump system, i.e. the fluid R407C (a known HydroFluoroCarbon - HFC - fluid).
  • the saturated liquid curve SLC and the saturated vapor curve SVC distinguish three different zones (corresponding to three refrigerant status) that are typical for all refrigerants (indeed, the shape and the values of the curves are peculiar for each specific refrigerant fluid).
  • the points that belong to the saturated liquid curve SLC represent the saturated liquid condition: the refrigerant is all in liquid phase at the saturation temperature related to the actual pressure.
  • the saturation temperature of the liquid state is also called “bubble point temperature” or, shortly, “bubble temperature”.
  • the points that belong to the saturated vapor curve SVC represent the saturated vapor condition: the refrigerant is all in vapor phase at the saturation temperature related to the actual pressure.
  • the saturation temperature of the vapor state is also called “dew point temperature” or, shortly, “dew temperature”.
  • the area at the left of the saturated liquid curve SLC is the sub-cooled liquid zone: the refrigerant is in liquid phase at a temperature lower than saturation temperature (at the actual pressure).
  • the zone between the saturated liquid curve SLC and the saturated vapor curve SVC is the two -phase zone: in this zone liquid phase and vapor phase coexist at the same time.
  • the relative amount between liquid and vapor phases changes according to the position in the two -phase zone.
  • the area at the right of the saturated vapor curve SVC is the superheated vapor zone: the refrigerant is in vapor phase at a temperature higher than saturation temperature (at the actual pressure).
  • the saturated condition (liquid and vapor) can be seen as a limit condition for the maintenance of the complete liquid and vapor condition respectively.
  • thermodynamic cycle of the refrigerant with levels of sub- cooling and super-heating is also depicted (points 1 -> 2 -> 3 -> 4).
  • FIGS 3 - 14 schematically show several exemplary and non-limitative embodiments of a heat pump laundry dryer according to embodiments of the present invention. Like in Figure 1, the direction of refrigerant flow is indicated by small arrows, whilst the flow of the drying medium 4 is indicated by larger and broader arrows.
  • the refrigerant fluid circuit essentially corresponds to that depicted in Figure 1, with only the main liquefier 7 and the main evaporator 6 (no auxiliary heat-exchangers), with the addition of a compressor cooling fan 305, arranged for cooling the compressor 8 by directing towards it a flow of air (distinct from the drying air) taken in from the external environment, and a dryer control unit 310, provided and configured for controlling the operation of the laundry dryer.
  • the control unit 310 may control the activation speed of the compressor cooling fan 305.
  • the control of the activation of the compressor cooling fan 305 by the control unit 310 may be based on the detection of the temperature of the refrigerant in one or more locations along the refrigerant fluid circuit, for example at the inlet of the expansion device 14 (a temperature sensor 315 positioned at the inlet of the expansion device 14 reads the temperature of the refrigerant), or/and at the outlet of the compressor 8, or in other locations, e.g. at the outlet of the main liquefier 7 or/and at the outlet of the main evaporator 6 (in fact, it is possible to find a relationship between the refrigerant temperature measured at a certain location along the refrigerant circuit and the refrigerant temperature at the inlet of the expansion device 14).
  • the control unit 310 determines whether the compressor cooling fan 305 is a variable-speed fan. If the compressor cooling fan 305 is a variable-speed fan, the control unit 310 may control the compressor cooling fan 305 in order to adjust the speed thereof.
  • the compressor 8 may be a variable-output or variable-speed or variable-power compressor, controlled by the control unit 310.
  • the control unit 310 can control the output or speed or power of the compressor 8, based on the detected temperature of the refrigerant as described above, to keep the level of sub-cooling of the refrigerant at the inlet of the expansion device 14 in the desired range.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • Figure 4 shows the provision of an additional, internal refrigerant-refrigerant heat exchanger 405, comprising at least a low-pressure side portion 405a in the low pressure portion of the refrigerant fluid circuit and a high-pressure side portion 405b in the high pressure portion of the refrigerant fluid circuit.
  • the internal heat exchanger 405 causes an exchange of heat between the refrigerant fluid after exiting the liquefier 7 (i.e., along the high-pressure portion of the refrigerant fluid circuit) and the refrigerant fluid after exiting the evaporator 6 and before entering the compressor 8 (i.e., along the low-pressure portion of the refrigerant fluid circuit).
  • the internal heat exchanger 405 can for example be implemented by making a portion of the refrigerant circuit pipe that connects the liquefier outlet 13 to the expansion device 14 inlet run in thermal contact (in direct or indirect physical contact) with a portion of the refrigerant circuit pipe that connects the evaporator outlet 9 to the compressor inlet 10; the two pipe portions should be sufficiently close so that there is a transfer of heat from the refrigerant (at a higher temperature) exiting the liquefier 7 and the refrigerant (at a lower temperature) exiting the evaporator 6. Such a transfer of heat aids the sub-cooling of the refrigerant before it enters the expansion device 14, and at the same time contributes to the super-heating of the refrigerant before it enters the compressor 8.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the internal heat exchanger 405, and possibly also the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • FIG. 5 shows the provision of a high-pressure auxiliary heat exchanger 505, e.g. an auxiliary liquefier, arranged in the high pressure portion of the refrigerant fluid circuit, e.g. downstream the main liquefier 7.
  • the high-pressure auxiliary heat exchanger 505 essentially comprises a refrigerant-air heat exchanger for the exchange of heat between the refrigerant fluid and ambient air (air taken in from the outside ambient of the appliance, distinct from the process air), taken in from the outside environment by a fan 510.
  • the exchange of heat with ambient air aids the sub-cooling of the refrigerant exiting the liquefier 7; the sub-cooling amount depends on the design of the high-pressure auxiliary heat exchanger 505, as well as on the activation/deactivation or speed control of the fan 510 by the control unit 310.
  • the control of the activation of the fan 510 by the control unit 310 may be based on the detection of the temperature of the refrigerant in one or more locations along the refrigerant fluid circuit, for example at the inlet of the expansion device 14 (a temperature sensor 315 positioned at the inlet of the expansion device 14 reads the temperature of the refrigerant), or/and at the outlet of the compressor 8, or in other locations, e.g. at the outlet of the main liquefier 7 or/and at the outlet of the main evaporator 6.
  • a similar control of the compressor cooling fan 305 or/and of the (output or speed or power of the) compressor 8 by the control unit 310 as in the embodiment of Figure 3 can be implemented, to achieve the desired refrigerant sub-cooling.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the high-pressure auxiliary heat exchanger 505 and the associated fan 510, and possibly also the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • Figure 6 shows an arrangement similar to that of Figure 5, but with the high- pressure auxiliary heat exchanger 505 arranged along the refrigerant fluid circuit in such a way that it exploits the same flow of ambient air impelled by the compressor cooling fan 305 for cooling the compressor 8, so that the provision of a separate fan 510 as in the embodiment of Figure 5 can be omitted. Also in this case, a similar control of the compressor cooling fan 305 or/and of the compressor 8 by the control unit 310 as in the embodiment of Figure 3 can be additionally implemented, to achieve the desired refrigerant sub-cooling.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the high-pressure auxiliary heat exchanger 505 and the compressor cooling fan 305, and possibly also the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • FIG. 7 shows the provision of a low-pressure auxiliary heat exchanger 705, e.g. an auxiliary evaporator, arranged in the low pressure portion of the refrigerant fluid circuit, e.g. downstream the main evaporator 6.
  • the low-pressure auxiliary heat exchanger essentially comprises a refrigerant-air heat exchanger for the exchange of heat between the refrigerant fluid and ambient air (air taken in from the outside ambient of the appliance, distinct from the process air), taken in from the outside environment by a fan 710.
  • the exchange of heat with ambient air aids the superheating of the refrigerant exiting the evaporator 7; the super-heating amount depends on the design of the low-pressure auxiliary heat exchanger 705, as well as on the speed of the fan 710 (which may be controlled by the control unit 310, based on the detection of the temperature of the refrigerant in one or more locations along the refrigerant fluid circuit, as described in connection to the previously described embodiments).
  • the low-pressure auxiliary heat exchanger 705 can be positioned proximate to the compressor 8, in such a way that the flow of air impelled by the compressor cooling fan 305 also hits the auxiliary evaporator, in a manner conceptually similar to the embodiment of Figure 6.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the compressor cooling fan 305, and/or also the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • the heat pump system is designed and operated to achieve the desired level of super-heating; particularly, the low-pressure auxiliary heat exchanger 705 and associated fan 710 contribute to maintain the desired level of super-heating.
  • Figure 8 shows a combination of the embodiments of Figures 4 and 5, with both the high-pressure side 405b of the internal heat exchanger 405 and the high- pressure auxiliary heat exchanger 505 arranged downstream the main liquefier 7, and with the fan 510.
  • the auxiliary liquefier 505 is positioned upstream the high- pressure side 405b of the internal heat exchanger 405.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the high-pressure auxiliary heat exchanger 505 and associated fan 510, the internal heat-exchanger 405, and possibly also the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • the (low-pressure side 405a of the) internal heat exchanger 405 contributes to achieve and maintain the above-mentioned level of super-heating of the refrigerant.
  • Figure 9 shows an arrangement similar to that of Figure 8, but with a high- pressure auxiliary heat exchanger 905 (and associated fan 910 for taking in ambient air distinct from the drying air) arranged downstream the high-pressure side 405b of the internal heat exchanger 405.
  • the fan 901 can be controlled by the control unit 310 to achieve the desired level of refrigerant sub-cooling, based on the detection of the temperature of the refrigerant in one or more locations along the refrigerant fluid circuit, as described in connection to the previously described embodiments.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly the high-pressure auxiliary heat exchanger 905 and associated fan 910, the internal heat- exchanger 405, and possibly also the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • the (low-pressure side 405a of the) internal heat exchanger 405 contributes to achieve and maintain the above- mentioned level of super-heating of the refrigerant.
  • Figure 10 shows a combination of the embodiments of Figures 4 and 7, with both the internal heat exchanger 405 and the low-pressure auxiliary heat exchanger 705.
  • the low-pressure auxiliary heat exchanger 705 is arranged downstream the low-pressure side 405a of the internal heat exchanger 405 and upstream the compressor 8.
  • a similar control of the compressor cooling fan 305 or/and of the (output or speed or power of the) compressor 8 by the control unit 310 as in the embodiment of Figure 3 can be additionally implemented, to achieve the desired refrigerant sub-cooling.
  • the embodiment of Figure 11 is similar to that of Figure 10, but with the low-pressure auxiliary heat exchanger 705 arranged upstream the low-pressure side 405a of the internal heat exchanger 405.
  • a similar control of the compressor cooling fan 305 or/and of the (output or speed or power of the) compressor 8 by the control unit 310 as in the embodiment of Figure 3 can be additionally implemented, to achieve the desired refrigerant sub-cooling.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the internal heat- exchanger 405, and possibly also the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • the heat pump system is designed and operated to achieve the desired level of super-heating; particularly, the low-pressure auxiliary heat exchanger 705 and associated fan 710, and the (low- pressure side 405a of the) internal heat exchanger 405 contribute to achieve and maintain the above-mentioned level of super-heating of the refrigerant.
  • Figure 12 shows an arrangement being a combination of the embodiments of Figures 5 and 7, with both the high-pressure auxiliary heat exchanger 505 and the low-pressure auxiliary heat exchanger 705 (each one with the associated fan 510, 710). Also in this case, a similar control of the compressor cooling fan 305 or/and of the compressor 8 by the control unit 310 as in the embodiment of Figure 3 can be additionally implemented, to achieve the desired refrigerant sub-cooling.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the high-pressure auxiliary heat exchanger 505 and associated fan 510, and possibly also the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • the heat pump system is designed and operated to achieve the desired level of super-heating; particularly, the low-pressure auxiliary heat exchanger 705 and associated fan 710 contribute to achieve and maintain the above-mentioned level of super-heating of the refrigerant.
  • FIG. 13 The embodiment of Figure 13 is similar to that of Figure 12, but with the pipes of the refrigerant fluid circuit routed in such a way that the high-pressure auxiliary heat exchanger 505 and the low-pressure auxiliary heat exchanger 705 are arranged in proximity to the compressor, in such a way that the flow of air impelled by the compressor cooling fan 305 also hits the high-pressure auxiliary heat exchanger 505 and the low-pressure auxiliary heat exchanger 705, so that no fans 510 and 710 are necessary.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the high-pressure auxiliary heat exchanger 505 and the fan 305, and possibly also the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • the heat pump system is designed and operated to achieve the desired level of super-heating; particularly, the auxiliary evaporator 705 and the fan 305 contribute to achieve the desired level of super-heating.
  • Figure 14 shows an arrangement being a combination of the embodiments of Figures 4, 5 and 7, with the internal heat exchanger 405, the high-pressure auxiliary heat exchanger 505 and the low-pressure auxiliary heat exchanger 705 (each one with the associated fan 510, 710). Also in this case, a similar control of the compressor cooling fan 305 or/and of the compressor 8 by the control unit 310 as in the embodiment of Figure 3 can be additionally implemented, to achieve the desired refrigerant sub-cooling.
  • the heat pump system is designed and operated so that the refrigerant sub-cooling level at the inlet of the expansion device is in the above mentioned range; particularly, the high-pressure auxiliary heat exchanger 505 and associated fan 510, the (high-pressure side 405b of the) internal heat exchanger 405, and possibly also the compressor cooling fan 305, and/or the compressor 8 contribute to maintain the refrigerant sub-cooling level at the inlet of the expansion device in the above mentioned range.
  • the heat pump system is designed and operated to achieve the desired level of super-heating; particularly, the low-pressure auxiliary heat exchanger 705 and associated fan 710 and the (low- pressure side 405a of the) internal heat exchanger 405 contribute to achieve and maintain the above-mentioned level of super-heating of the refrigerant.
  • FIG 15 is an isometric view of an exemplary laundry dryer.
  • the laundry dryer comprises a cabinet 1500, having lateral walls (one of which has been removed in the drawing) and housing the drying drum 2 and the heat pump unit 5.
  • the heat pump unit 5 is for example housed in an appliance basement 1505, which is shown per se in Figure 16.
  • the basement 1505 is for example a shell composed of two half-shells 1605 and 1610 designed to match each other so that, when matched, they define inside them a space for accommodating the heat pump unit parts, like the evaporator 6, the liquefier 7, the compressor 8, and passageways for the drying air.
  • the bottom half-shell 1605 of the basement 1505 is also depicted in Figure 17, in which the compressor cooling fan 305 is also visible, and in Figure 18, showing both the compressor cooling fan 305 and the auxiliary liquefier 505, arranged proximate to the compressor 8 so as to exploit the ambient air flow impelled by the compressor cooling fan 305, as in the embodiment of Figure 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
  • Drying Of Solid Materials (AREA)

Abstract

L'invention concerne un appareil pour sécher le linge (1), qui comprend un système de pompe à chaleur (5), le système de pompe à chaleur ayant un circuit de réfrigérant, l'appareil comprenant : une chambre de séchage d'articles (2) pour sécher les articles à l'aide d'un milieu de séchage; un premier échangeur de chaleur (6) pour chauffer un réfrigérant et refroidir le milieu de séchage; un second échangeur de chaleur (7) pour refroidir le réfrigérant et chauffer le milieu de séchage; un dispositif de dilatation de réfrigérant (14) disposé dans le circuit de réfrigérant entre le second échangeur de chaleur (7) et le premier échangeur de chaleur (6), et un compresseur (8) disposé dans le circuit de réfrigérant entre le premier échangeur de chaleur (6) et le second échangeur de chaleur (7). Le système de pompe à chaleur est conçu pour fonctionner de telle sorte qu'un niveau de sous-refroidissement du réfrigérant dans le système de pompe à chaleur est compris entre 5 °C et 15 °C mesuré à l'entrée du dispositif de dilatation de réfrigérant.
PCT/EP2013/055783 2013-03-20 2013-03-20 Appareil pour sécher le linge WO2014146704A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/EP2013/055783 WO2014146704A1 (fr) 2013-03-20 2013-03-20 Appareil pour sécher le linge
CN201380075793.7A CN105121730A (zh) 2013-03-20 2013-03-20 用于干燥衣物的器具
EP13713781.6A EP2976454A1 (fr) 2013-03-20 2013-03-20 Appareil pour sécher le linge

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2013/055783 WO2014146704A1 (fr) 2013-03-20 2013-03-20 Appareil pour sécher le linge

Publications (1)

Publication Number Publication Date
WO2014146704A1 true WO2014146704A1 (fr) 2014-09-25

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PCT/EP2013/055783 WO2014146704A1 (fr) 2013-03-20 2013-03-20 Appareil pour sécher le linge

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Country Link
EP (1) EP2976454A1 (fr)
CN (1) CN105121730A (fr)
WO (1) WO2014146704A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
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EP3517680A1 (fr) * 2018-01-29 2019-07-31 BSH Hausgeräte GmbH Dispositif pour sécher de linge et procédé pour l'opération d'une pompe à chaleur pour un tel dispositif
EP3617390A1 (fr) * 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3895594A1 (fr) * 2020-04-17 2021-10-20 BSH Hausgeräte GmbH Appareil ménager comportant une pompe à chaleur et procédé de fonctionnement d'un tel appareil ménager
EP4086538A1 (fr) * 2021-05-03 2022-11-09 BSH Hausgeräte GmbH Module de compresseur comportant un moyen de refroidissement et appareil ménager le comprenant

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WO2011080045A1 (fr) * 2009-12-22 2011-07-07 BSH Bosch und Siemens Hausgeräte GmbH Appareil domestique doté d'un circuit de pompe à chaleur
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EP2489774A1 (fr) * 2011-02-18 2012-08-22 Electrolux Home Products Corporation N.V. Sèche-linge à pompe à chaleur

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EP2460928B1 (fr) * 2010-12-02 2014-02-26 Electrolux Home Products Corporation N.V. Procédé de fonctionnement d'un séchoir à pompe à chaleur et séchoir à pompe à chaleur
EP2468944B1 (fr) * 2010-12-27 2019-02-20 Electrolux Home Products Corporation N.V. Séchoir à linge avec pompe de chaleur pour usage domestique

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WO2004076948A1 (fr) * 2003-02-28 2004-09-10 Delta S Technologies Limited Séchoir déshumidificateur a efficacité améliorée et a écoulement d'air réversible, et commande améliorée
US20050066538A1 (en) * 2003-09-29 2005-03-31 Michael Goldberg Heat pump clothes dryer
EP1580314A1 (fr) * 2004-03-26 2005-09-28 Whirlpool Corporation Trajet d'air avec sorties multiples pour sèche-linge
DE102005041145A1 (de) * 2005-08-29 2007-03-01 Alpha-Innotec Gmbh Wäschetrockner
WO2011080045A1 (fr) * 2009-12-22 2011-07-07 BSH Bosch und Siemens Hausgeräte GmbH Appareil domestique doté d'un circuit de pompe à chaleur
US20110203300A1 (en) * 2010-02-19 2011-08-25 Rafalovich Alexander P Refrigeration system with consecutive expansions and method
US20120017466A1 (en) * 2010-07-26 2012-01-26 Beers David G Apparatus and method for refrigeration cycle capacity enhancement
EP2455526A1 (fr) * 2010-11-17 2012-05-23 BSH Bosch und Siemens Hausgeräte GmbH Machine comportant une pompe à chaleur et ensemble de procédés correspondant
EP2468947A1 (fr) * 2010-12-27 2012-06-27 Electrolux Home Products Corporation N.V. Système de pompe à chaleur pour sèche-linge et procédé de fonctionnement d'un système de pompe à chaleur de sèche-linge
EP2489774A1 (fr) * 2011-02-18 2012-08-22 Electrolux Home Products Corporation N.V. Sèche-linge à pompe à chaleur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3517680A1 (fr) * 2018-01-29 2019-07-31 BSH Hausgeräte GmbH Dispositif pour sécher de linge et procédé pour l'opération d'une pompe à chaleur pour un tel dispositif
EP3617390A1 (fr) * 2018-08-30 2020-03-04 Electrolux Appliances Aktiebolag Sèche-linge comprenant un système de pompe à chaleur
EP3895594A1 (fr) * 2020-04-17 2021-10-20 BSH Hausgeräte GmbH Appareil ménager comportant une pompe à chaleur et procédé de fonctionnement d'un tel appareil ménager
EP4086538A1 (fr) * 2021-05-03 2022-11-09 BSH Hausgeräte GmbH Module de compresseur comportant un moyen de refroidissement et appareil ménager le comprenant

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EP2976454A1 (fr) 2016-01-27
CN105121730A (zh) 2015-12-02

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