WO2016128849A1 - Sèche-linge et procédé de fonctionnement d'un sèche-linge - Google Patents

Sèche-linge et procédé de fonctionnement d'un sèche-linge Download PDF

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Publication number
WO2016128849A1
WO2016128849A1 PCT/IB2016/050267 IB2016050267W WO2016128849A1 WO 2016128849 A1 WO2016128849 A1 WO 2016128849A1 IB 2016050267 W IB2016050267 W IB 2016050267W WO 2016128849 A1 WO2016128849 A1 WO 2016128849A1
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WO
WIPO (PCT)
Prior art keywords
air
heat exchanger
channel
clothes dryer
air inlet
Prior art date
Application number
PCT/IB2016/050267
Other languages
English (en)
Inventor
Jose Antonio Ruiz Bermejo
Roberto San Martin Sancho
Original Assignee
BSH Hausgeräte GmbH
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
Priority claimed from EP15382052.7A external-priority patent/EP3056603A1/fr
Application filed by BSH Hausgeräte GmbH filed Critical BSH Hausgeräte GmbH
Priority to CN201680009283.3A priority Critical patent/CN107208349B/zh
Priority to EP16702005.6A priority patent/EP3256635B1/fr
Priority to PL16702005T priority patent/PL3256635T3/pl
Publication of WO2016128849A1 publication Critical patent/WO2016128849A1/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 
    • 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
    • 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 
    • D06F58/24—Condensing arrangements

Definitions

  • the invention relates to a clothes dryer, comprising a closed loop for process air, the closed loop comprising a drum for storing clothes, a first heat exchanger, a second heat exchanger, and a third heat exchanger, wherein the first heat exchanger is an air-air heat exchanger having a first air channel and a second air channel for transferring heat between these air channels, an air inlet of the first air channel is connected to an air outlet of the drum, an air outlet of the first air channel is connected to an air inlet of the second heat exchanger, and an air outlet of the third heat exchanger is connected to an air inlet of the drum.
  • the first heat exchanger is an air-air heat exchanger having a first air channel and a second air channel for transferring heat between these air channels
  • an air inlet of the first air channel is connected to an air outlet of the drum
  • an air outlet of the first air channel is connected to an air inlet of the second heat exchanger
  • an air outlet of the third heat exchanger is connected to an air inlet of the drum.
  • the invention also relates to a method for operating a clothes dryer, wherein process air flows from a drum through a first channel of a first heat exchanger where it is cooled down, then through a second heat exchanger where it is cooled down further, then through a third heat exchanger where it is warmed up, and then back into the drum.
  • the invention is particularly useful for a closed-loop heat pump clothes dryer.
  • a known heat pump clothes dryer 1 comprises a closed cycle or closed loop L for circulating process air P.
  • One component of this closed loop L is a drum 2 for receiving wet clothes or laundry that is to be dried.
  • the process air P is circulated using a fan 3.
  • the process air P is discharged from an air outlet 2b (working point p1) of the drum 2.
  • the process air P has an intermediate temperature T1 of about 40 °C, a high absolute humidity, and a relative humidity rh1 of about 85% or 0.85.
  • the process air P then enters an air inlet 4a of a heat exchanger that is also an evaporator 4 of a compressor-type heat pump H.
  • the process air P is cooled down below its dew point such that condensate C is generated, in particular by getting the process air P in contact with surfaces of the evaporator 4.
  • the process air P discharged by an air outlet 4b of the evaporator 4 (at working point p3) thus has a relatively low temperature level T3 of about 32 °C, has a significant lower absolute humidity, and a relative humidity rh3 close to its saturation point or being saturated, i.e. having a rh3 of about 100% or 1.
  • the process air P then enters an air inlet 5a of a further heat exchanger that is also a condenser 5 of the heat pump H.
  • adjacent air outlets 2b, 4b, 5b and air inlets 4a, 5a, and 2a are close together and/or if air ducts between adjacent air inlets and air outlets have a negligible effect on the process air P, the condition of the process air P and the working points, resp., are the same for these air inlets and air outlets.
  • Operation of the heat pump clothes dryer 1 may be controlled by a control means, e.g. a central control circuitry 13.
  • a control means e.g. a central control circuitry 13.
  • a temperature difference between the heat exchangers is generated due to the compressor-type heat pump H in which a fluid (or refrigerant R) is compressed by a compressor 6 from a superheated gas status at a low pressure/low temperature regime to a superheated gas status at high pressure/high temperature regime.
  • a fluid or refrigerant R
  • the refrigerant is condensed to a sub-cooled liquid in the condenser 5 (which thus acts as a refrigerant-air heat exchanger) at a temperature equal or close to a saturation temperature at a bubble point of the refrigerant R for that pressure.
  • the refrigerant R expands to a low pres- sure level reaching a bi-phase state at a temperature equal or close to the saturation temperature at a dew point of the refrigerant R for that pressure and then evaporates in the evaporator 4 (which thus acts as an air-refrigerant heat exchanger) to reach the superheated gas status again.
  • h denotes an enthalpy at working point pi, m a i r; i a mass flow rate of the dry air component of the process air P, m wa ter;i a mass flow rate of the water contained in the process air P, v, a volume flow rate of the wet air / process air P, and w, a ratio ("humidity ratio") of the mass of water (in kg) per mass of dry air (in kg) of the process air P.
  • the clothes dryer 1 achieves a dehumidification rate or condensate C generation rate at the evaporator 4 of 2.22 kg/h of water.
  • a separate fan 12 may be used.
  • WO 2013/124163 A2 discloses a household appliance, more particularly a tumble dryer, comprising a working chamber and at least one latent heat store having a respective storage medium, wherein the respective storage medium is thermally coupled via a respective associated heat exchanger to a working medium circulating through the working chamber, wherein the working medium first moves from the working chamber to a heat sink, from said heat sink to the heat exchanger, from said heat exchanger to a heat source, and from said heat source back to the working chamber, and wherein the respective storage medium forms a substance mixture together with a respective carrier fluid, wherein said substance mixture can be conducted in a respective closed circuit through the associated heat exchanger for an exchange of heat with the working medium.
  • the respective substance mixture circulates between the associated heat exchanger and at least one reservoir in the respective closed circuit, and the reservoir can be refilled layer-by-layer with the substance mixture conducted through the respective associated heat exchanger.
  • Document WO 2013/124163 A2 further relates to a method for operating such a household appliance.
  • WO 2012/123914 A1 discloses a treatment device for treating hot and humid air from at least one drying installation, notably a dryer (I 0), comprising: an inlet to receive the air for treating coming from the outlet of the drying installation, an air/air exchanger through which the air for treating circulates - at least one air/fluid exchanger for dehumidifying the air for treating, the air/air exchanger and said at least one air/fluid exchanger being placed in series in such a way as to allow air from said at least one air/fluid exchanger and/or air from outside to be heated up using the air for treating, at least one outlet for air after treatment connected to the inlet of the drying installation, at least one bypass bypassing said at least one air/fluid exchanger.
  • WO 2008/155263 A1 discloses a condensation tumble dryer having a drying chamber for the objects to be dried, a process air channel, in which a heater is located for heating the process air and by means of which the heated process air can be guided to the objects to be dried via a fan, an air-to-air heat exchanger, a heat pump circuit having an evaporator, a compressor, and a condenser, at least one condensate collection vessel, a condensate pump, a condensate drain, and a first line leading from the condensate pump to the condensate drain, wherein a second line branches off the first line, the second line opening in the process air channel between the drying chamber and the air-to-air heat exchanger.
  • WO 2008/155263 A1 further relates to a method for the operation of the said condensation tumble dryer.
  • the placement of the additional air/air heat exchanger according to the prior art causes a considerably higher construction effort (including a significantly higher construction volume) and considerably higher costs.
  • DE 43 06 215 A1 discloses a program-controlled laundry drier with a laundry drum, in which process air is conveyed through the laundry drum in a closed process-air channel by means of a blower, and with a heat-pump circuit which is designed for precipitating the moisture carried out of the laundry drum in the process air and which consists of an evaporator, compressor and condenser.
  • a preheat exchanger which in terms of flow precedes both the evaporator and the condenser. It is the object of the present invention to at least partially overcome the disadvantages of the prior art and in particular to provide a clothes dryer that has a significantly increased efficiency while showing an only moderately increased complexity.
  • a clothes dryer comprising a closed loop or air channel for process air, the closed loop comprising a drum for storing clothes, a first heat exchanger, a second heat exchanger, and a third heat exchanger
  • the first heat exchanger is an air-air heat exchanger having a first air channel and a second air channel for transferring heat between these air channels
  • an air inlet of the first air channel is connected to an air outlet of the drum
  • an air outlet of the first air channel is connected to an air inlet of the second heat exchanger
  • an air outlet of the second heat exchanger is connected to an air inlet of the second air channel of the first heat exchanger
  • an air outlet of the second air channel of the first heat exchanger is connected to an air inlet of the third heat exchanger
  • an air outlet of the third heat exchanger is connected to an air inlet of the drum.
  • This clothes dryer gives the advantage that, with the same energy input, a considerable increase of the dehumidification rate of over 10 % can be achieved. Also, with the same energy input, an increase of the temperature of the process air at the air outlet of the condenser and thus at the air inlet of the drum of over 5 °C can be achieved. Therefore, by the improved ability to condense the process air and to generate higher temperatures of the process air at the drum inlet, a considerably faster drying cycle (over 10% faster) with consequent energy savings can be provided as compared to the prior art.
  • This clothes dryer takes advantage of the lower process air temperature at the outlet of the evaporator to saturate the wet process air coming from the drum and to pre-heat it before entering the condenser.
  • the clothes dryer may be a household appliance.
  • the clothes dryer may be a tumble dryer having a rotatable drum.
  • the drum may be rotatable around a horizontal or a vertical axis.
  • the clothes dryer may be a stand-alone dryer or a washing/drying appliance.
  • the first heat exchanger may also be called a "cross flow air-to-air heat exchanger".
  • the second heat exchanger is provided to cool down the process air, in particular below its dew point to generate condensate and thus to reduce the absolute humidity of the process air.
  • the third heat exchanger is provided to heat up the dried process air, in particular before it enters the drum. This decreases a relative humidity of the process air.
  • the process air within the process air loop therefore flows from the drum through the first channel of the first heat exchanger where it is cooled down, then through the second heat exchanger where it is cooled down further, then at least partially through the second channel of the first heat exchanger where it is warmed up, then through the third heat exchanger where it is warmed up further, and then back into the drum.
  • the air outlet of the second heat exchanger is only connected to the air inlet of the second channel of the first heat exchanger.
  • a flow of the process air by-passing the second air channel is prevented.
  • the air outlet of the second heat exchanger is connected to the air inlet of the second air channel of the first heat exchanger and to the air inlet of the third heat exchanger.
  • process air being discharged from the air outlet of the second heat exchanger may partially flow to the air inlet of the second air channel of the first heat exchanger (representing a first branch of the process air loop) and partially directly to the air inlet of the third heat exchanger (representing a second branch or by pass branch of the process air loop).
  • This at least partial diversion or by-passing of the second air channel of the first heat exchanger allows an adaptation to operating conditions of the heat exchangers and therefore a particularly flexible adaption to varying drying conditions.
  • a controllable air guidance device is connected to the air outlet of the second heat exchanger to control a relative flow volume of the process air to the air inlet of the second air channel of the first heat exchanger (i.e., the first branch) and directly to the air inlet of the third heat exchanger (i.e., the second branch), resp.
  • the controllable air guidance device may be driven by a motor. It may comprise one or more flaps, valves, shutters etc. to widen or narrow a flow cross- section of one path or of both paths.
  • the air guidance device may also be called an "air path splitter".
  • the controllable air guidance device may be controlled such that it may be set to two or more pre-defined positions (e.g. flap positions) corresponding to respective flow volume ratios. Alternatively or additionally, the controllable air guidance device may set the flow volume ratio in a continuous or quasi-continuous manner. The controllable air guidance device may completely block or shut off the air path from the air outlet of the second heat exchanger to the air inlet of the second air channel of the first heat exchanger and/or to the air inlet of the third heat exchanger. It is an alternative embodiment that the air guidance device is a non-controllable or fixed device splitting the process air loop L and process air paths, resp., in a fixed manner, esp. in a fixed ratio of flow volumes.
  • the second heat exchanger and the third heat exchanger are components of a heat pump of the clothes dryer.
  • a clothes dryer can be operated in a particularly efficient manner.
  • Such a clothes dryer may also be called a "closed cycle heat pump clothes dryer”.
  • the any suitable type of heat pump may be used, e.g. a Stirling-type heat pump or a Vuilleumier-type heat pump. It is a particularly advantageous embodiment that the second heat exchanger is an evaporator and the third heat exchanger is a condenser of a compressor-type heat pump.
  • a compressor-type heat pump additionally comprises a compressor and an expansion valve in generally well-known manner.
  • the clothes dryer is operable such that the process air that is discharged from the first air channel of the first heat exchanger is nearly or just saturated. Thus, a precipitation of condensate from the first heat exchanger can be avoided.
  • the first heat exchanger can be used to cool down the incoming process air below its dew point and to thus create the conditions for condensation.
  • the clothes dryer is operable such that (in particular including the first heat exchanger being designed such that) it can cause precipitation of condensate at the first heat exchanger during a drying cycle.
  • a mass flow rate of the dry air component of the process air m a i r may be between 0.02 and 0.10 kg/s, in particular between 0.05 and 0.06 kg/s, in particular for the case in which the process air in the evaporator inlet has a relative humidity of about 0.85 and a temperature of about 40 °C.
  • a mass flow rate of the water contained in the process air m wa ter before the second heat exchanger may in particular be between 2.5 and 18.62 kg/h, in particular between 5 and 15 kg/h, in particular between 8 and 9 kg/h, in particular between 8.2 and 8.5 kg/h, in particular between 8.35 and 8.45 kg/h, in particular at about 8.4 kg/h, in particular for the case in which the process air in the evaporator inlet has a relative humidity of about 0.85 and a temperature of about 40 °C.
  • a mass flow rate of the water contained in the process air m wa t e r after the second heat exchanger may be between 0,8 and 16 kg/h, in particular between 2 and 10 kg/h, in particular between 5.5 and 6.5 kg/h, in particular between 5.7 and 6.1 kg/h, in particular between 5.8 and 6.0 kg/h, in particular between 5.9 and 6.0 kg/h, in particular for the case in which the process air in the evaporator inlet has a relative humidity of about 0.85 and a temperature of about 40 °C
  • a relative humidity rh of the process air may be in the range between 0.75 and 0.95, in particular between 0.8 and 0.9, in particular about 0.85, after the drum and before the first air channel of the first heat exchanger (i.e., at working point 1).
  • the relative humidity rh may in particular be approx. 1 after the first air channel of the first heat exchanger and before the second heat exchanger (i.e., working point 2) and also after the second heat exchanger and before the second air channel of the first heat exchanger (i.e., working point 3).
  • the relative humidity rh may be in the range from 0.70 to 0.95, in particular between 0.8 and 0.9, in particular about 0.85, after second air channel of the first heat exchanger and before the third heat exchanger (i.e., at working point 4).
  • the relative humidity rh may be in the range between 0.04 and 0.26 (in particular in the range between 0.08 between 0.15, especially at about 0.1 1 , after the third heat exchanger and before the drum (i.e., at working point 5).
  • a temperature T of the process air may e.g. be in the range from 25 °C to 45 °C (in particular about 40 °C) at working point 1.
  • the temperature T may e.g. be in the range from 35 °C to 40 °C (in particular about 37 °C) at working point 2, but lower than the temperature T at working point 1 , in particular between 2 °C and 5 °c lower, in particular 3 °C to 4 °C lower.
  • the temperature T may be e.g. in the range from 3,9 °C to 41 ,4 °C, in particular in the range from 25 °C to 35 °C, in particular, in the range from 29 °C to 33 °C, in particular at about 31 °C, at working point 3.
  • the temperature T may be in the range from 8,8 °C to 43 °C, in particular in the range from 32 °C to 36 °C, but higher then working point 3 (in particular approx. 34 °C) at working point 4 and in the range from 59 to 80 °C (in particular approx. 75 °C) at working point 5.
  • a volume flow rate v of the process air may e.g. be in the range from 0.865 to 0,991 m 3 /kg (in particular in the range from 0.94 to 0.95 m 3 /kg) at working point 1 , in the range from 0.8514 to 0.9875 m 3 /kg (in particular in the range from 0.93 to 0.94 m 3 /kg) at working point 2, and in the range from 0.807 to 0.956 (in the range from 0.88 to 0.92, in particular at about 0.90) m 3 /kg at working point 3.
  • the volume flow rate v may be in the range from 0.821 to 0.959 (in particular in the range from 0.90 to 0.93, in particular at about 0.91) m 3 /kg at working point 4 and in the range from 0.934 to 1.087 (in particular in the range from 1.00 to 1.05, in particular at about 1.03 or 1.04) m 3 /kg at working point 5.
  • a humidity ratio w of the process air may e.g.
  • the object is also achieved by a method for operating a clothes dryer, wherein process airflows from a drum through a first channel of a first heat exchanger where it is cooled down, then through a second heat exchanger where it is cooled down further, then at least partially through a second channel of the first heat exchanger where it is warmed up, then through a third heat exchanger where it is warmed up further, and then back into the drum.
  • the method may be implemented in analogy to the clothes dryer as described above and achieves the same advantages.
  • none of the process air directly flows from the second heat exchanger to the third heat exchanger.
  • This is equivalent to a design in which the second channel of the first heat exchanger is not bypassed and practically all of the process air flows from the second heat exchanger to the second channel of the first heat exchanger.
  • part of the process air discharged from the second heat exchanger flows directly to the third heat exchanger and the other part flows to the second channel of the first heat exchanger and only then to the third heat exchanger.
  • Fig.1 shows a sketch of a clothes dryer according to the prior art
  • Fig.2 shows a w-T-diagram for the clothes dryer according to the prior art
  • Fig.3 shows a sketch of a first novel clothes dryer
  • Fig.4 shows a w-T-diagram for the first novel clothes dryer
  • Fig.5 shows a sketch of a second novel clothes dryer.
  • Fig.3 shows a sketch of a first novel closed loop heat pump clothes dryer 21.
  • the clothes dryer 21 differs from the clothes dryer 1 according of the art in that the second air channel 11 of the first heat exchanger 8 is not connected to the ambience or the outside of the process air loop L but to the process air loop L itself. In other words, process air P flows through both air channels 9 and 1 1.
  • the first air channel 9 and the second air channel 1 1 are functionally separated by the evaporator 4.
  • the process air P flows from the drum 2 through the first channel 9 of the first heat exchanger 8 where it is cooled down, then through the evaporator 4 where it is cooled down further, then through the second channel 1 1 of the first heat exchanger 8 where it is warmed up, then through the condenser 5 where it is warmed up further, and then back into the drum 2.
  • a section of the process air loop L between and including the air outlet 9b of the first air channel 9 and the air inlet 4a of the evaporator 4 defines a working point p2 for the process air P.
  • the working point p3 corresponds to a section of the process air loop L between and including the air outlet 4b of the evaporator 4 and the air inlet 1 1a of the second air channel 11 of the first heat exchanger 8.
  • a working point p4 corresponds to a section of the process air loop L between and including the air outlet 11 b of the second air channel 1 1 and the air inlet 5a of the condenser 5.
  • the calculations have been carried out assuming an atmospheric pressure at all the points of 1 ,013 bar.
  • Fig.5 shows a sketch of a second novel clothes dryer 31. That clothes dryer 31 is similar to the clothes dryer 1 but additionally comprises a controllable air guidance device 32 that is connected to the air outlet 4b of the evaporator 4 to control a relative flow of a volume of the process air P through a first branch b1 to the air inlet 11 a of the second air channel 1 1 of the first heat exchanger 8 and through a second branch b2 to the air inlet 5a of the condenser 5.
  • controllable air guidance device 32 introduces a bypass or branch line from the air outlet 4b of the evaporator 4 directly to the air inlet 5a of the condenser 5. It is controllable e.g. by an electrical motor or an actor (not shown), e.g. by the central control circuitry 13.
  • the relative flow volume can e.g. be controlled by setting a flow cross-section of one or both branches b1 and b2.
  • the air guidance device 32 may also be set such that the process air P flows through the first branch b1 (thus completely passing the second channel 11 of the first heat exchanger 8) and/or only through the second branch b2.
  • the clothes dryer may comprise a non-controllable or fixed air guidance device to give a fixed flow ratio through both branches.

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

Abstract

Ce sèche-linge 31 comprend une boucle fermée L pour l'air de procédé P, cette boucle L comprenant un tambour 2, un premier échangeur de chaleur 8, un second échangeur de chaleur 4, et un troisième échangeur de chaleur 5, et il est caractérisé en ce que le premier échangeur de chaleur 8 comprend un premier canal d'air 9 et un second canal d'air 11 pour le transfert de la chaleur entre eux, une sortie d'air 9b du premier canal d'air 9 étant raccordée à une entrée d'air 4a du deuxième échangeur de chaleur 4, une sortie d'air 4b du second échangeur de chaleur 4 étant raccordée à une entrée d'air 11a du second canal 11 du premier échangeur de chaleur 8, et une sortie d'air 11b du second canal 11 étant raccordée à une entrée d'air 5a du troisième échangeur de chaleur 5. L'invention concerne également un procédé de fonctionnement d'un sèche-linge 21; 31. L'invention est particulièrement utile pour des sèche-linge à pompe à chaleur en boucle fermée.
PCT/IB2016/050267 2015-02-11 2016-01-20 Sèche-linge et procédé de fonctionnement d'un sèche-linge WO2016128849A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201680009283.3A CN107208349B (zh) 2015-02-11 2016-01-20 干衣机及用于操作的干衣机方法
EP16702005.6A EP3256635B1 (fr) 2015-02-11 2016-01-20 Sèche-linge et procédé de fonctionnement d'un sèche-linge
PL16702005T PL3256635T3 (pl) 2015-02-11 2016-01-20 Suszarka do ubrań i sposób obsługi suszarki do ubrań

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP15382052.7 2015-02-11
ES201530167 2015-02-11
EP15382052.7A EP3056603A1 (fr) 2015-02-11 2015-02-11 Sèche-linge et procédé de fonctionnement d'un sèche-linge
ESP201530167 2015-02-11

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WO2016128849A1 true WO2016128849A1 (fr) 2016-08-18

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EP (1) EP3256635B1 (fr)
CN (1) CN107208349B (fr)
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US10753684B2 (en) 2016-02-19 2020-08-25 Float Biopro As System and process for drying loose bulk material
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EP3256635A1 (fr) 2017-12-20

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