EP2549007A1 - Wärmepumpenvorrichtung zur Wäschebehandlung - Google Patents

Wärmepumpenvorrichtung zur Wäschebehandlung Download PDF

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Publication number
EP2549007A1
EP2549007A1 EP11174963A EP11174963A EP2549007A1 EP 2549007 A1 EP2549007 A1 EP 2549007A1 EP 11174963 A EP11174963 A EP 11174963A EP 11174963 A EP11174963 A EP 11174963A EP 2549007 A1 EP2549007 A1 EP 2549007A1
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EP
European Patent Office
Prior art keywords
heat exchanger
blower
cooling air
compressor
refrigerant
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
Application number
EP11174963A
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English (en)
French (fr)
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EP2549007B1 (de
Inventor
Alberto Bison
Francesco Cavarretta
Flavio Noviello
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Electrolux Home Products Corp NV
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Electrolux Home Products Corp NV
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Publication date
Application filed by Electrolux Home Products Corp NV filed Critical Electrolux Home Products Corp NV
Priority to EP11174963.6A priority Critical patent/EP2549007B1/de
Publication of EP2549007A1 publication Critical patent/EP2549007A1/de
Application granted granted Critical
Publication of EP2549007B1 publication Critical patent/EP2549007B1/de
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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 invention relates to a laundry treatment apparatus having a heat pump system, in particular a dryer, a washing machine or a washer-dryer.
  • DE 44 09 607 A1 suggests a laundry dryer using a heat pump system with a closed process air loop and a refrigerant loop.
  • a compressor drives the refrigerant through a condenser, an expansion valve, an evaporator and back to the inlet of the compressor.
  • radiator rips are arranged at the refrigerant pipe. Cooling air is blown by a blower to the radiator rips for cooling the refrigerant and removing excess heat from the heat pump system.
  • a laundry treatment apparatus in which the laundry to be treated can be stored in a laundry storing chamber, which is preferably a rotatably supported drum.
  • the laundry is treated by process air, which is preferably completely or at least for the most part of it circulated in a closed processing air loop.
  • the process air loop is formed by the process air flow through the laundry storing chamber and a process air channel that guides the air from the outlet to the inlet of the storing chamber.
  • the process air is conveyed by a process air blower, which for example in the embodiment of the rotatable drum can be driven by a motor for driving the drum.
  • the laundry treatment apparatus has a heat pump system for dehumidifying and heating the process air.
  • Dehumidifying is made by cooling the process air at a first heat exchanger of the heat pump system (e.g. an evaporator or refrigerant gas heater). Heating is made at a second heat exchanger of the laundry treatment apparatus (e.g. a condenser or refrigerant gas cooler).
  • First and second heat exchangers are serially connected in a refrigerant loop in which the refrigerant is driven by a compressor and expanded by a refrigerant expansion device.
  • auxiliary heat exchanger e.g. auxiliary condenser or gas cooler.
  • the auxiliary heat exchanger is connected in the refrigerant loop serially upstream (with respect to the refrigerant flow) or downstream or partially upstream and partially downstream the second heat exchanger. Or the auxiliary heat exchanger is connected in parallel to the second heat exchanger.
  • the auxiliary heat exchanger is adapted to transfer heat from the refrigerant to cooling and/or ambient air ('cooling air' in the following). Additionally depositing the heat in liquid may be provided, for example in water stored in the apparatus (e.g. washing water when the apparatus is a washer-dryer).
  • a cooling air blower is assigned to the auxiliary heat exchanger for blowing or sucking cooling air through the auxiliary heat exchanger.
  • a shielding device is arranged such that the compressor is shielded against the cooling air blown by the blower and/or the compressor is shielded by providing an compressor insulation adapted to prevent heat exchange between the compressor and the compressor's outer ambient. With the insulation heat exchange between the compressor and the air surrounding the compressor and the cooling air moved by the cooling air blower is prevented or essentially prevented.
  • the operation temperature of the compressor is independent from the influence by the cooling air.
  • the compressor's ambient or outer wall temperature is independent from the cooling air being driven by the cooling air blower or not, the cooling air temperature, the spatial cooling effect on the compressor's outer case and/or the cooling air flow rate.
  • the operation temperature of the compressor is independent of the cooling air characteristics and variations which results in an improved uniformity of the compressor operation temperature over time is achieved. This in turn improves its operation efficiency and long-life cycle.
  • the excessive heat amount is removed from the refrigerant without increasing the compressor heat losses. Therefore the temperature level of the refrigerant and of the process air is kept quite constant while the temperature of the compressor is kept under safety level without penalizing the performances of the system.
  • the maximum cooling capacity of the combination auxiliary heat exchanger and cooling air flow rate driven by the blower is in the range of the heating capacity (heat power) deposited by the compressor in the heat pump system.
  • the heating power i.e. at the second heat exchanger
  • the cooling power i.e. at the first heat exchanger
  • P(second heat exchanger) P(first heat exchanger)+ P(power compressor) - P(power loss) where power loss is the amount of power lost and transferred to the environment.
  • the cooling capacity of the auxiliary heat exchanger is in the range of 10 to 100%, 15 to 80%, 20 to 60% of the P(power compressor).
  • the shielding device is arranged between the compressor and the auxiliary heat exchanger and/or the cooling air blower.
  • the blower may be arranged between the shielding device and the auxiliary heat exchanger or the auxiliary heat exchanger is arranged between the shielding device and the blower.
  • the blower blows or sucks the cooling air through the auxiliary heat exchanger.
  • the shielding device may be formed by, may be partially formed by or is a partition wall, a component housing and/or a process air duct section.
  • a section of the process air duct is arranged between blower and auxiliary heat exchanger on the one side and the compressor on the other side of the duct section.
  • a drive motor housing and/or a power electronics housing is arranged to shield the compressor.
  • a separate partition wall is provided to shield the compressor.
  • the shielding device may be formed at a bottom shell of the apparatus, preferably as an integral or monolithic part therewith (e.g.
  • the shielding device additionally has a guiding function for guiding the cooling air from or to a housing opening to exhaust or inhale the cooling air at a predetermined opening in the apparatus housing, in particular a predetermined opening at the bottom wall, a side wall and/or a bottom shell of the apparatus cabinet.
  • the air flow guiding or deflection function of the shielding device is used for example to deflect the air flow direction with respect to the cooling air flow direction which is given by the geometry of the cooling air blower and/or the auxiliary heat exchanger.
  • the shielding device having deflection function gives more freedom in the design and integration of the auxiliary heat exchanger/cooling air blower in the spatial layout of the apparatus.
  • the shielding device In addition to shield the cooling air flow in a potential path to the compressor, it is advantageous to provide the shielding device with one or more side shields each at a respective side of the auxiliary heat exchanger (i.e. on one or more sides thereof).
  • the side shield(s) extend partially or fully along a lateral side of the auxiliary heat exchanger and provide(s) additional channeling of the cooling air flow to improve efficiency in cooling of the auxiliary heat exchanger and shielding the compressor.
  • At least a portion of the cooling air flow is guided to another component of the apparatus, for example to power electronics of the apparatus, like a power converter for the compressor and/or the drum driving motor, and/or to a motor of the apparatus, like the drum drive motor.
  • power electronics of the apparatus like a power converter for the compressor and/or the drum driving motor
  • a motor of the apparatus like the drum drive motor.
  • an auxiliary or branching cooling air guiding channel is used to guide the airflow to such other component(s).
  • the auxiliary or branching cooling air channel has an input or an outlet at the shielding surface of the shielding device.
  • the main components of the heat pump system are arranged in a base section of the apparatus and a section of a process air channel is arranged in a middle region of the base section.
  • this section of the process air channel houses the first and second heat exchanger, wherein this arrangement is sometimes called the 'battery' of the heat pump system.
  • the compressor is arranged at one side of the middle process air channel section and the auxiliary heat exchanger and the cooling air blower are arranged at another side of the middle channel section opposite to the compressor. In this way the middle channel section forms the shielding device shielding cooling air from being blown towards or being sucked from the compressor.
  • the cooling air blower and the auxiliary heat exchanger are arranged at a height level above the first and second heat exchanger, for example above the battery or the cooling air channel in which the first and second heat exchanger are arranged.
  • the cooling air flow path is offset to the compressor location and cooling of the compressor is prevented.
  • the auxiliary heat exchanger has a cooling power in the range from 10 to 500 W, 50 to 450 W or 100 to 450 W, and/or the auxiliary heat exchanger is adapted to reduce the refrigerant temperature by 2 to 18°C, 5 to 15°C, 8 to 13°C or 10 to 15°C.
  • the maximum conveyance capacity of the cooling air blower is in the range of 10 to 180 m 3 /h, 20 to 100 m 3 /h, or 40 to 80 m 3 /h.
  • the operation of the laundry treatment apparatus is controlled by control unit, including the operation and monitoring of the heat pump system.
  • control unit is adapted to activate the cooling air blower after the warm-up phase or when approaching the steady state. End of the warm-up phase or arriving or approaching the steady state is for example detected by a sensor device detecting the temperature and/or pressure of the refrigerant (or being dependent on the refrigerant) at a predefined location of the refrigerant loop, for example at or close to the first heat exchanger inlet or outlet.
  • the control unit is adapted to keep the blower operating during the steady state until the running laundry treatment process is finished.
  • the conveyance or flow rate or rotation speed of the cooling air blower may be varied around a non-zero value without undershooting the zero value so as to keep continuous (positive) operation of the blower.
  • Variation of the conveyance rate of the blower may be required to keep the operation condition of the heat pump system at a predetermined level or within a predetermined target range for optimizing the heat pump system efficiency and/or maintaining the steady state.
  • Adaptation of cooling air flow rate may be required during a treatment cycle, if for example the laundry is to be dried and laundry humidity decreases, or if the cooling air is ambient air having a varying ambient air temperature.
  • Fig. 1 depicts in a schematic representation a home appliance 2 which in this embodiment is a heat pump tumble dryer.
  • the tumble dryer comprises a heat pump system 4, including in a closed refrigerant loop in this order of refrigerant flow B: a first heat exchanger 10 acting as evaporator (gas heater) for evaporating (heating) the refrigerant and cooling process air, a compressor 14, a second heat exchanger 12 acting as condenser (gas cooler) for cooling the refrigerant and heating the process air, an auxiliary heat exchanger 34 acting as additional condenser, and an expansion device 16 from where the refrigerant is returned to the first heat exchanger 10.
  • a first heat exchanger 10 acting as evaporator (gas heater) for evaporating (heating) the refrigerant and cooling process air
  • a compressor 14 a second heat exchanger 12 acting as condenser (gas cooler) for cooling the refrigerant and heating the process air
  • an auxiliary heat exchanger 34 acting as additional condens
  • the heat pump system forms a refrigerant loop 6 through which - in normal operation - the refrigerant is circulated by the compressor 14 as indicated by arrow B.
  • the auxiliary condenser 34 dissipates heat to the ambient of the dryer 2 in the steady state of the heat pump system 4 in which maximum or nearly maximum operation condition is achieved after the warm-up period and the heat deposited by the compressor in the refrigerant loop 6 has to be removed via auxiliary condenser 34 to prevent overheating.
  • the sequence of the components in the refrigerant loop can be modified in the embodiments herein in that the auxiliary condenser 34 is not placed between the condenser 12 and the expansion device 16 with respect to refrigerant flow, but between the compressor 14 and the condenser 12 (not shown). This modification is applicable to all embodiments herein.
  • the expansion device 16 is a controllable valve that operates under the control of a control unit to adapt the flow resistance for the refrigerant in dependency of operating states of the heat pump system.
  • the expansion device 16 can be a capillary tube, a valve with fixed expansion cross-section, a throttle valve with variable cross section that automatically adapts the expansion cross-section in dependency of the refrigerant pressure (e.g. by elastic or spring biasing), a semi-automatic throttle valve in which the expansion cross-section is adapted in dependency of the temperature of the refrigerant (e.g. by actuation of a thermostat and/or where the temperature of the refrigerant is taken between the gas cooler and the gas heater, the gas heater and the compressor, or the compressor and the gas cooler), or the like.
  • the process air flow within the home appliance 2 is guided through a compartment 18 of the home appliance 2, i.e. through a compartment 18 for receiving articles to be treated, e.g. a drum 18.
  • the articles to be treated are textiles, laundry 19, clothes, shoes or the like. In the embodiments here these are preferably textiles, laundry or clothes.
  • the process air flow is indicated by arrows A in Fig. 1 and is driven by a process air blower 8. Outside the drum 18 the process air A is guided through an air channel 20.
  • the air exiting the drum 18 through the drum outlet (which is the loading opening of the drum) is filtered by a first fluff filter 22 arranged close to the drum outlet in or at the channel 20.
  • the first heat exchanger 10 transfers heat from the process air to the refrigerant.
  • humidity from the process air condenses at the first heat exchanger 10 is collected there and the collected condensate is drained to a condensate collector 30.
  • the process air cooled and dehumidified when passing the first heat exchanger passes then through the second heat exchanger 12 where heat is transferred from the refrigerant to the process air.
  • the process air is sucked from exchanger 12 by the blower 8 and driven into the drum 18 where it heats up the laundry 19 and receives the humidity therefrom.
  • the main components of the heat pump system 4 are arranged in a base section 5 or basement of the dryer 2, different embodiments of which are shown in the following figures.
  • the process air channel 20 guides the process air flow A outside the drum 18 and includes different sections, including the section forming the battery channel 20a in which the first and second heat exchangers 10, 12 are arranged.
  • the process air exiting the second heat exchanger 12 flows into a rear channel 20b in which the process air blower 8 is arranged.
  • the air conveyed by blower 8 is guided upward in a rising channel 20c to the backside of the drum 18.
  • E shows the respective time behavior for the dryer 2 according to the invention in which the heat pump system 4 is cooled using only or essentially the auxiliary condenser 34 for removing the excessive heat during the steady state after the warm-up period.
  • a cooling air blower 28 is activated and continuously operated during the steady phase without cooling down the compressor 14.
  • the heat loss factor is the percentage of the power adsorbed by the compressor that is lost as heat losses.
  • the lower this value the better for the system efficiency. From Fig. 12 it is clear that continuous operation of the blower 28 and keeping the compressor at constant temperature is advantageous over the operation mode in prior art heat pump systems.
  • the cooling air blower 28 when reaching or approaching the steady state the cooling air blower 28 is activated and continuously operated.
  • the cooling capacity of the auxiliary condenser 34 is fully used (as compared to the conventional intermittent operation) and the cooling capacity of the auxiliary condenser 34 can be reduced.
  • Fig. 2 shows a top view of the heat pump system 4 of the dryer 2 arranged in the dryer base section 5.
  • the base section is housing the heat pump system and parts of the process air channel 20 in a bottom shell 40 forming the base frame of the dryer and having the dryer foots (compare Fig. 6 ).
  • a cover shell 42 is placed over the bottom shell 40, wherein portions of both shells form the battery channel 20a in which the first and second heat exchanger 10, 12 (which form the battery of the heat pump system) are encased.
  • the rear channel 20b and the blower 8 are also encased by bottom and top shell 40, 42.
  • the reference numerals partially (e.g.
  • blower 8 and the drum 18 have been placed at or over section of the top shell 42 where the component covered by the top shell actually can not be seen, but its location is indicated thereby.
  • the motor 9 for driving blower 8 and the drum 18 is also located under the cover shell 42 and in this embodiment is located between blower 8 and compressor 14.
  • the second fluff filter 24 is placed in a drawer inserted into the lower part of the process air channel 20.
  • the condensate water that is condensing at the first heat exchanger 10 is collected in a tray formed below the exchanger 10 in the bottom shell 40 and is guided in a condensate channel at the side of the second heat exchanger 12 into the condensate collector 30 formed by a rear section of the bottom shell 40.
  • a level sensor and a condensate pump are arranged at the collector 30 to pump the condensate to a condensate reservoir at the top of the dryer.
  • the auxiliary condenser 34 is placed in an upright orientation in the bottom shell 40 such that its slender top side is seen in Fig. 2 .
  • the cooling air blower 28 is arranged which sucks in ambient air through openings in the bottom shell 40 at the basement front side of the dryer 2.
  • the conveyed cooling air passes through the condenser 34 from the lower side as shown in Fig. 2 and exits at the upper side the condenser 34 which is the rear side of the condenser when seen from front of the dryer.
  • the cooling air exiting the condenser 34 is guided downward by a deflector shield 36 placed immediately behind the condenser, facing its rear or exit side.
  • Fig. 3 shows in cross-section an enlarged section of the lower right side of Fig. 2 where the auxiliary condenser 34 is placed.
  • the radiator rips of condenser 34 can be seen arranged around the zigzag or meander-shaped refrigerant pipe.
  • Shield 36 has a side shield 37 that is running at both lateral sides partially over the depth of condenser 34 (the depth direction is the cooling air passing direction) and completely over the top side of the condenser.
  • the partial side shield portions 37 can be seen in cross section in Fig.
  • the shield is enclosing the rear side, partial lateral side and top side of condenser 34 and is open towards the front side (condenser air inlet) and bottom side (air outlet).
  • Fig. 4 is a lateral cross section of a part of the base section 5 in the region of the condenser 34 along a cross section line from the front of the dryer (left side in Fig. 4 ) towards the rear side of the dryer.
  • Dashed arrow C indicates the cooling or ambient air flow conveyed by blower 28 through the auxiliary condenser 34 and deflected at its backside downward by the deflector shield 36.
  • the air flow C exits the base section 5 through openings 38 formed in the bottom shell 40.
  • the openings 38 can be seen in more detail in the view from below in Fig. 6 .
  • Fig. 5 shows a perspective view to the base section 5 with the cover shell 42, second fluff filter 24 (drawer), blower 8 and motor 9 removed.
  • Fig. 7 the lateral side view of the base section 5 is shown completely as compared to Fig. 4 .
  • the cover shell 42 is placed in position and over the motor 9 section of cover shell 42 the power converter 44 for the compressor 14 (and/or other power electronics) is mounted.
  • a branching channel 46 is provided as schematically shown in Fig. 7 .
  • the branching channel 46 has a cooling air inlet at the deflector shield 36 and an outlet to the housing encasing the power electronics 44. As soon as the blower 28 is activated, a portion of the ambient air that passed the auxiliary condenser 34 is guided to the power electronics 4 for cooling it.
  • Figs. 8 to 11 show as schematic view the arrangement of heat pump components in the base section 5 in top view according to other embodiments.
  • the same reference numerals for components of the heat pump system 4 operating the same way as the components in Figs. 1 to 7 are used. For simplicity reference is made to the above and deviating implementations are indicated below.
  • the blower 8, drum and blower motor 9 and compressor 14 are arranged on a first side of the battery channel 20a, and the blower 28, the condenser 34 and the power electronics 44 are arranged on a second side of the battery channel 20a.
  • the battery channel 20a is forming a center or middle section of the base section 5 running from a front region to the back region of the base section 5. It provides a partition wall or deflector shield 36a preventing a cooling or ambient air flow from the cooling air blower 28 to the compressor 14.
  • the power electronics 44 is not arranged in the flow path of the cooling air.
  • the power electronics is arranged above the motor 9 similarly as shown in Fig. 7 .
  • the cooling air flow C is sucked in by blower 28 through openings in the front region of the base section 5, is pushed by the blower 28 through the condenser 34 towards power electronics 44, is deflected by the outer case of the condensate collector to the side and exits the base section 5 through openings at a side wall thereof.
  • the cooling air flow C is reversed and/or the blower 28 is arranged on the rear side of condenser 34 (when seen from the front of dryer 2).
  • the depth of the dryer may be decreased as compared to the 60 cm depth of a conventional dryer.
  • the depth of such dryer type is maximum or less than 55 cm, 50 cm or 45 cm.
  • the volume of the drum is reduced at the same time while the drum diameter is full size adapted to the 60 cm width of conventional dryers.
  • With reduced drum volume the required drying capacity is reduced and the dimension or capacity of the components of the heat pump system 4 can be reduced.
  • narrowing the battery channel 20a width as indicated in Fig. 8 is easily implemented.
  • Such dryer is adapted for small apartment use or single/double household needs.
  • the battery channel 20a is arranged on the left side of the base section 5.
  • a deflector shield 36b is arranged between the compressor 14 at one side and the condenser 34 and blower 28 at the other side to prevent cooling air flow to the compressor.
  • the blower 28 sucks the cooling air flow C through openings on the left side of the base section and through the auxiliary condenser 34 and blows it against the power electronics 44 and the motor 9.
  • Exhaust of the air flow C is through openings on the lateral side and/or in the bottom of base section 5 (bottom shell 40).
  • the flow direction of air flow C is reversed and/or the power electronics and/or the motor 9 are not in the cooling air flow path.
  • the housing of motor 9 is arranged between the cooling air flow C and the compressor 14 thus forming a deflector shield 36c.
  • the blower 28 sucks the cooling air through openings in the bottom shell 40 and pushes it through the auxiliary condenser 34 against shield 36c which deflects the flow C through openings in the lateral side of base section 5.
  • auxiliary condenser 34, blower 28 and power electronics 44 are placed on top and/or above the battery channel 20a (containing evaporator 10 and condenser 12).
  • the power electronics 44 is not in the flow path of cooling air C and instead e.g. placed on the case of motor 9 (compare Fig. 7 ).
  • a deflector shield 36d in the form of a cooling air channel wall is provided to guide the air flow C and prevent flowing it towards compressor 14.
  • the cooling air channel 36d covers the lateral side and the top side of the components 34, 28 and 44.
  • the flow direction of air flow C is inverted and/or the channel 36d has openings not at the lateral side wall of the base section, but on the front side of the base section 5.
  • the cooling air channel 36d preferably is arranged on the outermost left side above the upper level of the battery channel 20a and is preferably small in width as compared to the battery channel 20a. Thereby the lowest point of the drum 18 can be kept close to the upper side of battery channel 20a, while the dead space at the left side within the dryer body is used to arrange the cooling air channel.
  • the cooling air channel is arranged at the outermost right side above the level of the battery channel 20a and/or the case of the motor 9. Compare the position of the power electronics 44 in Fig. 7 - such that the channel 36d takes the position of electronics 44 and preferably does not extend the complete depth of the base section 5, e.g. by providing cooling air inlet or outlet openings at a lateral side or bottom side of the vertically extended base section 5.
  • cooling air blower 28 is depicted and arranged as axial blower (axial fan in which the air flow C enters and exits in the axial direction with respect to the blower rotation axis).
  • axial blower axial fan in which the air flow C enters and exits in the axial direction with respect to the blower rotation axis.
  • a radial blower radial fan or centrifugal fan
  • tangential blower cross-flow fan
  • the backside wall of the radial blower (which is opposite to the inlet opening for the conveyed air) can at the same time represent the deflector shield (shielding device) that prevents air flow to the compressor 14.
  • the cooling air can be sucked through the auxiliary condenser 34 when the radial blower is arranged in the direction of the outlet side of the condenser 34.
  • the cooling air conveyed by the radial blower can then be exhausted into a direction perpendicular to the exit air direction (i.e. preferably the axial inlet direction of the radial blower). For example through openings in the bottom of bottom shell 40.
  • a direction perpendicular to the exit air direction i.e. preferably the axial inlet direction of the radial blower.
  • auxiliary condenser 34 and blower 28 from front to rear can be changed such that the condenser 34 is close to the front opening and the blower is on the backside of condenser 34 and exhausts the cooling air through the outlet openings 38.
  • the radial blower with its housing replaces the axial blower 28 and the deflector shield 36.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
EP11174963.6A 2011-07-22 2011-07-22 Wärmepumpenvorrichtung zur Wäschebehandlung Active EP2549007B1 (de)

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EP2549007A1 true EP2549007A1 (de) 2013-01-23
EP2549007B1 EP2549007B1 (de) 2020-02-26

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2801654A1 (de) * 2013-05-07 2014-11-12 Miele & Cie. KG Wäschetrockner mit einer in einem Gehäuse drehbar gelagerten Trommel
JP2015198872A (ja) * 2014-04-10 2015-11-12 株式会社Tosei 乾燥機
EP2990524A1 (de) * 2014-08-29 2016-03-02 Electrolux Appliances Aktiebolag Wärmepumpenwäschetrockner
WO2018001158A1 (zh) * 2016-06-27 2018-01-04 青岛海尔滚筒洗衣机有限公司 一种根据干衣机出筒空气温度变化调节冷凝介质量的方法
EP2650425B1 (de) * 2012-04-12 2018-11-21 Electrolux Home Products Corporation N.V. Wäschetrocknermaschine
EP3992351A4 (de) * 2019-09-04 2022-08-24 Samsung Electronics Co., Ltd. Wäschetrockner

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4409607A1 (de) 1993-04-21 1994-10-27 Miele & Cie Kondensationswäschetrockner mit einer Wärmepumpe
DE4434205A1 (de) * 1994-08-31 1996-03-07 Joerg Sdrojewski Wäschetrockner
DE202006018205U1 (de) * 2006-11-06 2007-02-15 V-Zug Ag Wäschetrockner mit Zusatzwärmetauscher
EP1811077A1 (de) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Trockner
WO2008073008A1 (en) * 2006-12-11 2008-06-19 Tes Scandinavia Ab Improved drying device
US7458171B1 (en) * 2007-01-29 2008-12-02 Lentz Luke E Dehumidifier clothes dryer apparatus

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4409607A1 (de) 1993-04-21 1994-10-27 Miele & Cie Kondensationswäschetrockner mit einer Wärmepumpe
DE4434205A1 (de) * 1994-08-31 1996-03-07 Joerg Sdrojewski Wäschetrockner
EP1811077A1 (de) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Trockner
DE202006018205U1 (de) * 2006-11-06 2007-02-15 V-Zug Ag Wäschetrockner mit Zusatzwärmetauscher
WO2008073008A1 (en) * 2006-12-11 2008-06-19 Tes Scandinavia Ab Improved drying device
US7458171B1 (en) * 2007-01-29 2008-12-02 Lentz Luke E Dehumidifier clothes dryer apparatus

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2650425B1 (de) * 2012-04-12 2018-11-21 Electrolux Home Products Corporation N.V. Wäschetrocknermaschine
EP2801654A1 (de) * 2013-05-07 2014-11-12 Miele & Cie. KG Wäschetrockner mit einer in einem Gehäuse drehbar gelagerten Trommel
JP2015198872A (ja) * 2014-04-10 2015-11-12 株式会社Tosei 乾燥機
EP2990524A1 (de) * 2014-08-29 2016-03-02 Electrolux Appliances Aktiebolag Wärmepumpenwäschetrockner
WO2016030149A1 (en) * 2014-08-29 2016-03-03 Electrolux Appliances Aktiebolag Heat pump laundry dryer
CN106661815A (zh) * 2014-08-29 2017-05-10 伊莱克斯家用电器股份公司 热泵式衣物干燥机
WO2018001158A1 (zh) * 2016-06-27 2018-01-04 青岛海尔滚筒洗衣机有限公司 一种根据干衣机出筒空气温度变化调节冷凝介质量的方法
US11053634B2 (en) 2016-06-27 2021-07-06 Qingdao Haier Drum Washing Machine Co., Ltd. Method for regulating quantity of condensing medium according to change in air temperature at outlet of barrel of dryer
EP3992351A4 (de) * 2019-09-04 2022-08-24 Samsung Electronics Co., Ltd. Wäschetrockner

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