EP2565321A1 - Dryer with a cross-flow heat exchanger and method for operating same - Google Patents
Dryer with a cross-flow heat exchanger and method for operating same Download PDFInfo
- Publication number
- EP2565321A1 EP2565321A1 EP12182350A EP12182350A EP2565321A1 EP 2565321 A1 EP2565321 A1 EP 2565321A1 EP 12182350 A EP12182350 A EP 12182350A EP 12182350 A EP12182350 A EP 12182350A EP 2565321 A1 EP2565321 A1 EP 2565321A1
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- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- flow
- cross
- dryer
- process air
- 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.)
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- 238000000034 method Methods 0.000 title claims abstract description 146
- 238000001816 cooling Methods 0.000 claims abstract description 74
- 238000001035 drying Methods 0.000 claims abstract description 35
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- 239000000463 material Substances 0.000 description 8
- 238000009833 condensation Methods 0.000 description 5
- 230000005494 condensation Effects 0.000 description 5
- 238000000926 separation method Methods 0.000 description 5
- 239000002826 coolant Substances 0.000 description 4
- 238000007791 dehumidification Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 238000011068 loading method Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 229920001169 thermoplastic Polymers 0.000 description 2
- 239000004416 thermosoftening plastic Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 239000002041 carbon nanotube Substances 0.000 description 1
- 229910021393 carbon nanotube Inorganic materials 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 238000011049 filling Methods 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000009972 noncorrosive effect Effects 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
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Images
Classifications
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- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
- F28D9/0068—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
-
- 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
- D06F2103/00—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
- D06F2103/28—Air properties
- D06F2103/36—Flow or velocity
-
- 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
- D06F2105/00—Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
- D06F2105/16—Air properties
- D06F2105/24—Flow or velocity
-
- 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
- D06F58/30—Drying processes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/106—Particular pattern of flow of the heat exchange media with cross flow
Definitions
- the invention relates to a dryer, comprising a control device, a process air duct, in which a heater, a drying chamber for objects to be dried, a fan and a cross-flow heat exchanger are arranged, wherein the process air duct comprises a supply air duct in front of the drying chamber and an exhaust duct between the drying chamber and crossflow heat exchanger, and a preferred method of operating this dryer.
- Under dryer in the present case is a pure dryer, which is used only for drying certain items, but also a washer dryer, which is intended for drying certain items, usually laundry.
- the dryer is thus a tumble dryer or a washer-dryer, ie a combination of a washing machine and a tumble dryer.
- process air Usually in a dryer air (so-called "process air") by means of a blower through a drying chamber, which contains the objects to be dried, passed.
- the process air absorbs moisture from the objects to be dried. Since warm air is able to absorb more moisture, the process air is heated before it enters the drying chamber.
- the warm moist process air is cooled in a heat exchanger, wherein the heat exchanger, a filter, in particular a lint filter, may be upstream.
- the cooling of the process air in the heat exchanger generally condenses the moisture contained in the process air and can be removed as condensate.
- the dehumidified process air is then usually reheated and fed again to the objects to be dried (circulating air dryer) or the storage room of the dryer supplied (exhaust air dryer).
- the EP 1 050 618 B1 describes a staggered arrangement of heat exchanger plates, whereby the flow losses of the gas stream is reduced and the heat exchange performance is increased.
- the DE 30 27 900 C2 an air-cooled heat exchanger for a domestic laundry dryer, wherein in the cooling air area air guide body are provided to improve the heat transfer and design-related improved sealing is achieved.
- the EP 1 729 078 A2 describes a heat exchanger for a condensation clothes dryer, which has a plurality of lamellar structures in the cooling air area, whereby a larger surface for the heat transfer is achieved and the cooling air is introduced as a turbulent flow in the heat exchanger. This leads to an improved heat transfer and thus a higher efficiency of the heat exchanger.
- the font EP 0 982 427 B1 discloses a crossflow heat exchanger for a condensation clothes dryer with plates of a highly conductive metal or thermoplastic.
- the DE 10 2009 046 680 A1 discloses a heat exchanger constructed of a composite material including thermoplastic and carbon nanotubes.
- the efficiency of the heat exchanger is increased mainly in terms of improved cooling performance, whereby an improved separation efficiency of the moisture in the moist, warm process air from the drying chamber (dehumidification) can be achieved.
- Dryers with a heat pump are for example from the DE 10 2008 044 277 A1 and the DE 10 2008 043 920 A1 known.
- a heat pump is generally associated with a comparatively high construction-related outlay, which can have an unfavorable economic effect (costs, maintenance).
- the invention thus relates to a dryer, comprising a control device, a process air duct, in which a heater, a drying chamber for drying Objects, a fan and a cross-flow heat exchanger are arranged, wherein the process air duct comprises a supply air duct in front of the drying chamber and an exhaust duct between the drying chamber and crossflow heat exchanger, and wherein the exhaust duct and / or cross-flow heat exchanger is / are such that a larger proportion p * M a process air amount M passing through the exhaust duct into the crossflow heat exchanger, where p> 0.5, being directed to a cooling flow entrance side of the cross flow heat exchanger.
- p * M a process air amount M passing through the exhaust duct into the crossflow heat exchanger
- p> 0.5 being directed to a cooling flow entrance side of the cross flow heat exchanger.
- Extraction duct in the sense of the invention means the part of the process air duct between the drying chamber and cross-flow heat exchanger, ie the part in which generally the moist, warm process air flows from the drying chamber to the crossflow heat exchanger.
- an exhaust duct can be present both in a circulating air and in an exhaust air dryer.
- a heat exchanger In a heat exchanger, thermal energy is generally transferred from one material stream to another.
- a heat exchanger In this case, a heat exchanger is usually well sealed to the outside and between the streams.
- the material flows In the case of a cross-flow heat exchanger, the material flows are guided in such a way that their directions intersect, essentially at right angles. Thus, the warmer material flow is cooled and the cooler stream, hereinafter also called cooling stream, heated.
- the warmer material flow In a cross-flow heat exchanger in a dryer, the warmer material flow is usually the process air flow. Since the directions of the process air flow and the cooling flow intersect, the greatest temperature differences are thus found in the process air area of the heat exchanger at the side facing the cooling flow inlet, i. the cooling flow inlet side.
- the exhaust duct and / or cross-flow heat exchanger are designed such that a larger proportion of the process air is passed to the cooling flow inlet side of the crossflow heat exchanger, at which the cooling flow occurs.
- a larger volume fraction of the process air flows through the region of the greater temperature difference in the heat exchanger.
- a larger proportion of the process air here usually means more than 50% by volume of the process air.
- the reference volume (100%) is that volume of the process air which flows through the entire process air inlet surface of the heat exchanger in the same time unit (for example 1 s).
- the volume flow can be determined, for example, by flow sensors.
- cooling flow inlet side of the crossflow heat exchanger generally refers to a volume fraction of the heat exchanger.
- the heat exchanger can be divided, for example, in a volume half, which faces the cooling flow inlet and in another volume half, which faces away from the cooling flow inlet.
- Cooling flow inlet side thus refers to the volume half of the heat exchanger facing the cooling flow inlet. At least 60% by volume is preferred the process air passed to the side of the cross-flow heat exchanger, where the cooling flow occurs.
- the attachment of at least one flow guide in the relevant process air stream i. in the exhaust air part channel and / or in the cross-flow heat exchanger, preferably.
- a larger proportion of the process air is thus brought to the cooling flow inlet side.
- the respective number, design and arrangement of the flow guide body depends on the geometry of the exhaust air duct and the geometry of the crossflow heat exchanger itself, on the type of flow and on the distribution of the flow velocities over the cross section.
- At least one flow guide body is arranged in the exhaust air duct and / or cross flow heat exchanger, wherein the position of the flow guide is fixed or changeable.
- the flow guide body e.g. a baffle, a first baffle surface and a second baffle surface, which differ in their location with respect to the cooling flow inlet side.
- the flow guide body can generally be flowed around by the process air from the drying chamber.
- a flow guide according to the invention may generally be any type of body that is capable of directing the process air flow according to the invention.
- the at least one flow guide body is a guide plate.
- "baffle” generally means a relatively thin body, the generally uniform thickness of which is relatively small compared to its length.
- preference is given to those materials whose properties are not impaired by the contact with the moist, warm process air.
- This material is preferably a non-corrosive metal, such as aluminum, or a plastic.
- the flow guide body, in particular the guide plate can have a correspondingly structured surface such as a guide profile, which is then preferably located on the upstream side of the guide plate.
- the at least one flow guide is arranged in the exhaust duct.
- the at least one flow guide body is preferably arranged in the exhaust air duct in the inflow region of the crossflow heat exchanger.
- inflow region generally means the section of the exhaust air duct through which the process air stream flows immediately before entry into the crossflow heat exchanger.
- At least one flow guide body is arranged in the crossflow heat exchanger.
- the at least one flow guide body preferably divides a process air area in the crossflow heat exchanger into at least two separate process air portions, of which a first process air portion faces the cooling flow inlet side and a second process air portion of the cooling flow inlet side faces away from the side of the cooling flow outlet.
- the at least one flow guide body is arranged largely in the flow direction of the process air flow in the process air region of the heat exchanger.
- a baffle divides the process air area in the cross-flow heat exchanger into two separate process air subregions, of which a first process air portion faces the cooling flow inlet side and a second process air part region faces away from the cooling flow inlet side.
- the area of the process stream inlet is preferably smaller than the area of the process stream outlet in the first process air partial area, whereas in the second process air partial area the corresponding area ratio is preferably reversed.
- the volume fractions of the two process air subregions are preferably not greatly different, ie the volume fraction of one of the two process air subregions at the corresponding total process air range does not exceed 70%, more preferably not 60%, particularly preferably not 55%.
- the corresponding proportions, based on the total process air range, depending on the design of the cross-flow heat exchanger are determined differently, for example in a plate heat exchanger based on the respective plate gap. This is important in that, in the case of a plate heat exchanger, the arrangement of the at least one flow guide body can be configured differently in different plate interspaces of the process air area.
- the heat exchange in the cross-flow heat exchanger and in particular the heat exchange accompanied by condensation of the heat exchange accompanied by the moist, warm process air in the heat exchanger can be made efficient.
- the heat exchange via the position of the flow guide be optimally adjusted.
- a position of the flow guide in the exhaust duct and / or in the crossflow heat exchanger can be adjusted by means of the control device. This makes it possible in particular for the temperature and moisture content of the moist warm process air originating from the drying chamber to be taken into account.
- the position of the flow guide can be adjusted depending on parameters of a drying process.
- a wall of the exhaust air duct can be designed such that a larger proportion p * M of the process air quantity M, where p> 0.5, is conducted to a cooling flow inlet side of the crossflow heat exchanger in the process air flowing in the exhaust air duct .
- the wall of the exhaust duct for example, contain correspondingly shaped ribs, which direct the flow of process air in the direction of the cooling flow inlet side of the crossflow heat exchanger, or the wall itself may have a suitable slope or other shape. This is in particular possible by means of curvatures in the exhaust air duct, which can cause, for example, different flow velocities over the duct cross section.
- the exhaust air duct may comprise a plurality of partial exhaust air ducts, which differ with respect to the flow of the cooling flow inlet side of the crossflow heat exchanger.
- these may be separate pipes, each of which represents a partial exhaust air duct.
- the at least one flow guide body divides the exhaust air duct upstream of the crossflow heat exchanger in at least two separate exhaust air ducts.
- the at least one flow guide body is generally arranged substantially in the flow direction of the process air flow in the exhaust duct upstream of the heat exchanger, ie, generally along the exhaust passage, whereby at least two separate exhaust air ducts are formed.
- one of the cooling flow inlet side of the heat exchanger faces and the other facing away from this.
- the number of exhaust air partial ducts thus formed is thus determined as a rule from the number of flow guide.
- a baffle can be introduced along the flow direction into the exhaust air duct, so that now two separate Ablufteilkanäle arise through which the cross-flow heat exchanger is flown, with an exhaust air duct facing the cooling flow inlet side and the other side facing the cooling flow outlet.
- the entire surface of the heat exchanger which is flowed through by the process air is subdivided in such a way that a maximum of one third of the total area of the crossflow heat exchanger which is flown by the process air is occupied by the exhaust air part channel facing the cooling flow inlet side.
- the crossflow heat exchanger is not limited by its type and design. So it may be an air-gas or air-liquid heat exchanger. For example, it may be the heat sink of a heat pump or an air-to-air heat exchanger. As a cooling medium can thus serve, for example, a refrigerant of a heat pump. Likewise, can serve as a cooling medium cold air of an air-to-air heat exchanger. According to the invention, a dryer is preferred in which the cross-flow heat exchanger is an air-air heat exchanger.
- the heat exchanger has a suitable shape and / or surface structure to assist the heat exchange.
- the shape and / or surface structure are suitably selected so that the heat exchange between an optionally loaded with lint moist warm process air and a coolant or refrigerant optimally.
- a plate heat exchanger is advantageous in this case.
- a plate heat exchanger consists of several plates, which are composed so that in each successive spaces alternately once the heat-emitting and once the cooling stream flows. Thus, the areas through which the process air flows alternate with the areas of the cooling flow.
- the at least one flow guide body is arranged in the heat exchanger, its arrangement can take place in all process air intermediate spaces ("process air areas") in an identical manner or vary.
- a variation of the arrangement of the at least one flow guide body over the different process air intermediate spaces is preferred in particular for different admission of the different interspaces with process air, but also with different loading of the various spaces with coolant such as cooling air.
- a larger proportion of the process air is conducted to the side of the crossflow heat exchanger, at which the cooling flow occurs.
- the invention also relates to a method for operating a dryer, comprising a control device, a process air duct, in which a heater, a drying chamber for objects to be dried, a fan and a cross-flow heat exchanger are arranged, wherein the process air duct a supply air duct in front of the drying chamber and an exhaust duct between drying chamber and cross-flow heat exchanger, and wherein the exhaust duct and / or cross-flow heat exchanger is / are such that a larger proportion p * M of a process air amount M flowing through the exhaust duct into the cross-flow heat exchanger, where p> 0.5, to a cooling flow inlet side the cross-flow heat exchanger is passed, wherein in the method, the moist, warm process air from the drying chamber in the exhaust duct is divided and divided so that a larger proportion p * M of a process air amount M, which flows through the exhaust duct in the cross-flow heat exchanger where p> 0.5, is passed to a cooling flow inlet side of the cross-
- the invention has the advantage that a dryer is provided with an efficient heat exchanger, thereby enabling energy saving. This is the case in particular because, with a dryer according to the invention, the separation efficiency for the moisture from the moist, warm process air is improved, whereas an increase in the cooling capacity is unnecessary. Thus, despite more efficient heat exchanger no amplified power supply is needed to supply lost thermal energy in the heat exchanger process air.
- the cross-flow heat dryer is an air-to-air heat exchanger, there is the advantage that it costs less and less maintenance compared to dryers with heat pump by fewer components.
- a rib 30 In the wall 29 of the exhaust duct 2 is a rib 30, which ensures that the air flowing in the exhaust duct 2 process air flows mainly in the direction of a cooling flow inlet side 24 in the cross-flow heat exchanger 14 and there contributes to an efficient heat exchange.
- the part of the process air channel 2, 12 from the heat exchanger 14 to the drum 3 is thus also referred to as the supply air duct 12 and the part of the process air duct 2, 12 from the drum 3 to the heat exchanger 14 as the exhaust air duct 2.
- the drum 3 is in the in Fig. 1 shown embodiment at the rear bottom by means of a pivot bearing and front mounted by means of a bearing plate 7, wherein the drum 3 rests with a brim on a sliding strip 8 on the bearing plate 7 and is held at the front end.
- control of the dryer 1 via a control device 11 (also denoted by program control), which regulated by the user via an operating unit 9 can be.
- a display device 10 By means of a display device 10 different states of the dryer 1 can be displayed visually or acoustically.
- Fig. 2 shows a three-dimensional view of a relevant section of a second embodiment of a dryer 1 according to the invention, in which an air-air heat exchanger as a cross-flow heat exchanger 14 and adjacent process air ducts 2,12, supply air and exhaust duct, are visible.
- a baffle is arranged as a flow guide 22 in the inflow region 23 of the cross-flow heat exchanger 14.
- the cross-flow heat exchanger 14 is formed as an air-to-air heat exchanger with heat exchanger plates 19.
- the hot, moist process air supplied via the supply air channel 2 to the crossflow heat exchanger 14 is guided through the intermediate spaces of the heat exchanger plates 19, which are designed as process air regions 20.
- the process air regions 20 are arranged alternately in the cross-flow heat exchanger 14 with separate cooling air regions 21, through which cooling air flows, which is passed from the cooling air inlet 17 to the cross-flow heat exchanger 14 and from there via the cooling air outlet 18 from the dryer 1 passes.
- a baffle 22 is arranged as a flow guide 22 in the inflow region 23 of the crossflow heat exchanger 14 such that a larger proportion of the process air is passed to the cooling flow inlet side 24 of the crossflow heat exchanger 14.
- the guide plate 22 of the exhaust duct 2 is divided into two separate process air duct areas 25 and 26 respectively.
- Fig. 3 shows a three-dimensional view of a relevant section of a third embodiment of a dryer 1 according to the invention, in which an air-air heat exchanger 14 as a cross-flow heat exchanger and adjacent process air ducts, supply air duct 12 and exhaust duct 2, are visible.
- a baffle 22 is arranged in the process air region of the cross-flow heat exchanger 14.
- the cross-flow heat exchanger 14 is also formed as an air-to-air heat exchanger with heat exchanger plates 19.
- a baffle 22 is arranged as a flow guide 22 in the process air area 20 of the cross-flow heat exchanger 14, so that a larger proportion of the process air to the cooling flow inlet side 24 of the cross-flow heat exchanger 14 is passed.
- the baffle 22 of the crossflow heat exchanger 14 is divided into two separate process air sections 27,28. In this case, a first process air part region 27 faces the cooling flow entry point 24 and a second process air part region 28 faces away from the cooling flow entry point 24.
- Fig. 2 shown second embodiment of a dryer 1 according to the invention
- Fig. 3 shown third embodiment of a dryer according to the invention therefore consists in the different arrangement of the baffle 22.
- Fig. 2 is the baffle 22 in the exhaust duct 2 in the upstream region 23 of the cross-flow heat exchanger 14, whereas in Fig. 3 the guide plate 22 is arranged in the crossflow heat exchanger 14 itself.
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- Physics & Mathematics (AREA)
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- General Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Detail Structures Of Washing Machines And Dryers (AREA)
Abstract
Description
Die Erfindung betrifft einen Trockner, umfassend eine Steuereinrichtung, einen Prozessluftkanal, in welchem eine Heizung, eine Trocknungskammer für zu trocknende Gegenstände, ein Gebläse und ein Kreuzstromwärmetauscher angeordnet sind, wobei der Prozessluftkanal einen Zuluftkanal vor der Trocknungskammer und einen Abluftkanal zwischen Trocknungskammer und Kreuzstromwärmetauscher umfasst, sowie ein bevorzugtes Verfahren zum Betrieb dieses Trockners.The invention relates to a dryer, comprising a control device, a process air duct, in which a heater, a drying chamber for objects to be dried, a fan and a cross-flow heat exchanger are arranged, wherein the process air duct comprises a supply air duct in front of the drying chamber and an exhaust duct between the drying chamber and crossflow heat exchanger, and a preferred method of operating this dryer.
Unter Trockner wird vorliegend ein reiner Trockner, welcher nur zum Trocknen bestimmter Gegenstände dient, aber auch ein Waschtrockner verstanden, welcher zum Trocknen bestimmter Gegenstände, in der Regel Wäschestücke, bestimmt ist. Insbesondere ist der Trockner somit ein Wäschetrockner oder ein Waschtrockner, also eine Kombination aus einer Waschmaschine und einem Wäschetrockner.Under dryer in the present case is a pure dryer, which is used only for drying certain items, but also a washer dryer, which is intended for drying certain items, usually laundry. In particular, the dryer is thus a tumble dryer or a washer-dryer, ie a combination of a washing machine and a tumble dryer.
Üblicherweise wird in einem Trockner Luft (sogenannte "Prozessluft") mittels eines Gebläses durch eine Trocknungskammer, welche die zu trocknenden Gegenstände enthält, geleitet. Dabei nimmt die Prozessluft Feuchtigkeit aus den zu trocknenden Gegenständen auf. Da warme Luft mehr Feuchtigkeit aufzunehmen vermag, wird die Prozessluft vor Eintritt in die Trocknungskammer erwärmt. Nach Austritt aus der Trocknungskammer wird die warme feuchte Prozessluft in einem Wärmetauscher abgekühlt, wobei dem Wärmetauscher ein Filter, insbesondere ein Flusenfilter, vorgeschaltet sein kann. Durch die Abkühlung der Prozessluft im Wärmetauscher kondensiert im Allgemeinen die in der Prozessluft enthaltene Feuchtigkeit und kann als Kondensat abgeführt werden. Die entfeuchtete Prozessluft wird danach in der Regel wieder erwärmt und erneut den zu trocknenden Gegenständen zugeführt (Umlufttrockner) oder aber dem Abstellraum des Trockners zugeführt (Ablufttrockner).Usually in a dryer air (so-called "process air") by means of a blower through a drying chamber, which contains the objects to be dried, passed. The process air absorbs moisture from the objects to be dried. Since warm air is able to absorb more moisture, the process air is heated before it enters the drying chamber. After exiting the drying chamber, the warm moist process air is cooled in a heat exchanger, wherein the heat exchanger, a filter, in particular a lint filter, may be upstream. The cooling of the process air in the heat exchanger generally condenses the moisture contained in the process air and can be removed as condensate. The dehumidified process air is then usually reheated and fed again to the objects to be dried (circulating air dryer) or the storage room of the dryer supplied (exhaust air dryer).
Da der Trocknungsvorgang sehr energieintensiv ist, ist es aus Umwelt- und ökonomischen Gründen erstrebenswert, den Energieverbrauch des Trockners zu senken. Dies kann durch eine gesteigerte Effizienz des Wärmetauschers erreicht werden.Since the drying process is very energy intensive, it is desirable for environmental and economic reasons to reduce the energy consumption of the dryer. This can be achieved by increasing the efficiency of the heat exchanger.
Es ist bekannt, die Effizienz eines Wärmetauschers in einem Trockner dadurch zu steigern, dass eine möglichst gleichmäßige Verteilung des Prozessluftstroms über die Fläche des Wärmetauschers gewährleistet wird. Dies spielt insbesondere deshalb eine Rolle, weil Prozessluftkanäle in Trocknern bauartbedingt häufig Krümmungen aufweisen, wodurch der Prozessluftstrom ungleichmäßig in den Wärmetauscher eintritt.It is known to increase the efficiency of a heat exchanger in a dryer in that the most uniform possible distribution of the process air flow over the surface of the heat exchanger is ensured. This plays a role in particular because process air ducts in dryers often have bends due to the design, as a result of which the process air flow enters the heat exchanger unevenly.
So offenbart die
Die
Weiterhin ist es ist bekannt, die Effizienz eines Luft-Luft-Wärmetauschers durch Verbesserung der Wärmeabfuhr auf der Kühlluftseite zu steigern. Auf der Kühlluftseite liegt durch die dort vorhandene trockene Luft ein deutlich schlechterer Wärmeübergang als auf der Prozessluftseite vor, da auf der Prozessluftseite ein sehr guter Wärmeübergang durch die dort stattfindende Kondensation begünstigt wird. Aus diesem Grund wirken sich Maßnahmen auf der Kühlluftseite stark auf die Effizienz des Wärmetauschers aus.Furthermore, it is known to increase the efficiency of an air-air heat exchanger by improving the heat dissipation on the cooling air side. On the cooling air side is due to the existing dry air there is a significantly poorer heat transfer than on the process air side, as on the process air side a very good heat transfer is favored by the condensation taking place there. For this reason, measures on the cooling air side have a strong effect on the efficiency of the heat exchanger.
In diesem Zusammenhang offenbart die
Die
Um durch eine verbesserte Wärmeabfuhr die Effizienz des Wärmetauschers zu erhöhen, ist weiterhin der Einsatz von Materialien mit verbesserter Leitfähigkeit bekannt. Die Schrift
Durch solche Maßnahmen wird die Effizienz des Wärmetauschers hauptsächlich hinsichtlich einer verbesserten Kühlleistung gesteigert, wodurch auch eine verbesserte Abscheideleistung der Feuchte in der feuchtwarmen Prozessluft aus der Trocknungskammer (Entfeuchtung) erreicht werden kann.By such measures, the efficiency of the heat exchanger is increased mainly in terms of improved cooling performance, whereby an improved separation efficiency of the moisture in the moist, warm process air from the drying chamber (dehumidification) can be achieved.
Es ist überdies bekannt, die in einem Trockner eingesetzte Energie durch Verwendung einer Wärmepumpe effizient zu nutzen. Trockner mit einer Wärmepumpe sind beispielsweise aus der
Es ist vor diesem Hintergrund Aufgabe der vorliegenden Erfindung, einen Trockner mit einem effizienten Wärmetauscher bereitzustellen, wobei insbesondere die Abscheideleistung bezüglich Feuchtigkeit aus feuchtwarmer Prozessluft aus der Trocknungskammer verbessert ist, eine Verstärkung der Kühlleistung hingegen vermieden werden kann.It is against this background object of the present invention to provide a dryer with an efficient heat exchanger, in particular, the separation efficiency is improved with respect to moisture from moist warm process air from the drying chamber, an increase in cooling capacity can be avoided.
Die Lösung der Aufgabe wird nach dieser Erfindung erreicht durch einen Trockner mit den Merkmalen des entsprechenden unabhängigen Patentanspruchs sowie das Verfahren des entsprechenden unabhängigen Patentanspruchs. Bevorzugte Ausführungsformen des erfindungsgemäßen Trockners sind in entsprechenden abhängigen Patentansprüchen aufgeführt. Bevorzugten Ausführungsformen des erfindungsgemäßen Trockners entsprechen bevorzugte Ausführungsformen des erfindungsgemäßen Verfahrens und umgekehrt, auch wenn dies hierin nicht explizit festgestellt ist.The object is achieved according to this invention by a dryer with the features of the corresponding independent claim and the method of the corresponding independent claim. Preferred embodiments of the dryer according to the invention are listed in corresponding dependent claims. Preferred embodiments of the dryer according to the invention correspond to preferred embodiments of the method according to the invention and vice versa, although this is not explicitly stated herein.
Gegenstand der Erfindung ist somit ein Trockner, umfassend eine Steuereinrichtung, einen Prozessluftkanal, in welchem eine Heizung, eine Trocknungskammer für zu trocknende Gegenstände, ein Gebläse und ein Kreuzstromwärmetauscher angeordnet sind, wobei der Prozessluftkanal einen Zuluftkanal vor der Trocknungskammer und einen Abluftkanal zwischen Trocknungskammer und Kreuzstromwärmetauscher umfasst, und wobei Abluftkanal und/oder Kreuzstromwärmetauscher derart ausgebildet ist/sind, dass ein größerer Anteil p*M einer Prozessluftmenge M, die durch den Abluftkanal in den Kreuzstromwärmetauscher fließt, wobei p > 0,5 gilt, zu einer Kühlstromeintrittsseite des Kreuzstromwärmetauschers geleitet wird. Hierbei gilt vorzugsweise p ≥ 0,6 und besonders bevorzugt p ≥ 0,7.The invention thus relates to a dryer, comprising a control device, a process air duct, in which a heater, a drying chamber for drying Objects, a fan and a cross-flow heat exchanger are arranged, wherein the process air duct comprises a supply air duct in front of the drying chamber and an exhaust duct between the drying chamber and crossflow heat exchanger, and wherein the exhaust duct and / or cross-flow heat exchanger is / are such that a larger proportion p * M a process air amount M passing through the exhaust duct into the crossflow heat exchanger, where p> 0.5, being directed to a cooling flow entrance side of the cross flow heat exchanger. In this case, preferably p ≥ 0.6, and more preferably p ≥ 0.7.
"Abluftkanal" im Sinne der Erfindung bedeutet den Teil des Prozessluftkanals zwischen Trocknungskammer und Kreuzstromwärmetauscher, also den Teil, in dem im Allgemeinen die feuchtwarme Prozessluft von der Trocknungskammer zum Kreuzstromwärmetauscher fließt. In diesem Sinne kann ein Abluftkanal sowohl in einem Umluft- als auch in einem Ablufttrockner vorhanden sein."Extraction duct" in the sense of the invention means the part of the process air duct between the drying chamber and cross-flow heat exchanger, ie the part in which generally the moist, warm process air flows from the drying chamber to the crossflow heat exchanger. In this sense, an exhaust duct can be present both in a circulating air and in an exhaust air dryer.
Bei einem Wärmetauscher wird thermische Energie im Allgemeinen von einem Stoffstrom auf einen anderen übertragen. Dabei ist ein Wärmetauscher in der Regel nach außen und zwischen den Stoffströmen gut abgedichtet. Bei einem Kreuzstromwärmetauscher werden dabei die Stoffströme so geführt, dass sich ihre Richtungen kreuzen, im Wesentlichen im rechten Winkel. So wird der wärmere Stoffstrom abgekühlt und der kühlere Stoffstrom, im Folgenden auch Kühlstrom genannt, erwärmt. Bei einem Kreuzstromwärmetauscher in einem Trockner ist der wärmere Stoffstrom in der Regel der Prozessluftstrom. Da sich die Richtungen des Prozessluftstroms und des Kühlstroms kreuzen, finden sich im Prozessluftbereich des Wärmetauschers die größten Temperaturunterschiede somit an der dem Kühlstromeintritt zugewandten Seite, d.h. der Kühlstromeintrittsseite.In a heat exchanger, thermal energy is generally transferred from one material stream to another. In this case, a heat exchanger is usually well sealed to the outside and between the streams. In the case of a cross-flow heat exchanger, the material flows are guided in such a way that their directions intersect, essentially at right angles. Thus, the warmer material flow is cooled and the cooler stream, hereinafter also called cooling stream, heated. In a cross-flow heat exchanger in a dryer, the warmer material flow is usually the process air flow. Since the directions of the process air flow and the cooling flow intersect, the greatest temperature differences are thus found in the process air area of the heat exchanger at the side facing the cooling flow inlet, i. the cooling flow inlet side.
Erfindungsgemäß sind Abluftkanal und/oder Kreuzstromwärmetauscher derart ausgebildet, dass ein größerer Anteil der Prozessluft zu der Kühlstromeintrittsseite des Kreuzstromwärmetauschers geleitet wird, an der der Kühlstrom eintritt. Dadurch durchströmt ein größerer Volumenanteil der Prozessluft den Bereich der größeren Temperaturdifferenz im Wärmetauscher. Überraschend wurde gefunden, dass dies vor allem zu einer höheren Abscheidung der Feuchtigkeit aus der feuchtwarmen Prozessluft und somit zu einer verstärkten Entfeuchtung der Prozessluft führt, ohne dass eine verstärkte Abkühlung der Prozessluft erfolgt. Somit hat die Prozessluft daraufhin die gewünschte geringere Wasserbeladung, ohne dass durch gleichzeitig gesteigerte Abkühlung im Folgenden die Prozessluft stärker erwärmt werden müsste. Ein erfindungsgemäßer Trockner, bei dem im Prozessluftbereich des Kreuzstromwärmetauschers die Kühlluftseite stärker angeströmt wird, ist somit aufgrund seiner höheren Abscheideleistung effizienter.According to the exhaust duct and / or cross-flow heat exchanger are designed such that a larger proportion of the process air is passed to the cooling flow inlet side of the crossflow heat exchanger, at which the cooling flow occurs. As a result, a larger volume fraction of the process air flows through the region of the greater temperature difference in the heat exchanger. Surprisingly, it has been found that this leads above all to a higher separation of the moisture from the moist, warm process air and thus to an increased dehumidification of the process air, without an increased cooling of the process air takes place. Thus, the process air has the desired lower water loading, without the process air should be heated more by simultaneously increased cooling below. A dryer according to the invention, in which the cooling air side is more strongly flown in the process air area of the cross-flow heat exchanger, is thus more efficient due to its higher separation efficiency.
Ein größerer Anteil der Prozessluft bedeutet hierin in der Regel mehr als 50 Volumen-% der Prozessluft. Dabei ist das Referenz-Volumen (100%) dasjenige Volumen der Prozessluft, das in der gleichen Zeiteinheit (beispielsweise 1s) die gesamte Prozesslufteintrittsfläche des Wärmetauschers durchströmt. Im Allgemeinen wird das Volumen eines Mediums, das sich in einer Zeiteinheit durch einen Querschnitt bewegt, als Volumenstrom bezeichnet mit:
wobei Q den Volumenstrom [m3/s], V das Volumen [m3] und t die Zeit [s] darstellt. Der Volumenstrom lässt sich beispielsweise durch Durchflusssensoren bestimmen. Weiterhin gilt für den Volumenstrom:
wobei c die mittlere Strömungsgeschwindigkeit [m/s] und A die durchströmte Fläche [m2] darstellt. Folglich kann ein größerer Anteil der Prozessluft, der erfindungsgemäß zur Kühlstromeintrittsseite des Wärmetauschers geleitet wird, beispielsweise durch eine vergrö-βerte Eintrittsfläche des zur Kühlstromeintrittsseite zu leitenden Prozessluftanteils in den Wärmetauscher (mehr als 50 % der Prozesslufteintrittsfläche) oder durch Erhöhung der Strömungsgeschwindigkeit in dem zur Kühlstromeintrittsseite zu leitenden Prozessluftanteil erreicht werden.A larger proportion of the process air here usually means more than 50% by volume of the process air. In this case, the reference volume (100%) is that volume of the process air which flows through the entire process air inlet surface of the heat exchanger in the same time unit (for example 1 s). In general, the volume of a medium moving through a cross-section in a unit of time is referred to as a volumetric flow with:
where Q represents the volume flow [m 3 / s], V the volume [m 3 ] and t the time [s]. The volume flow can be determined, for example, by flow sensors. Furthermore, the following applies to the volume flow:
where c represents the average flow velocity [m / s] and A represents the area [m 2 ] which is traversed. Consequently, a greater proportion of the process air, which is passed according to the invention to the cooling flow inlet side of the heat exchanger, for example, by an enlarged entrance surface of the cooling air inlet side to be conductive process air fraction in the heat exchanger (more than 50% of the process air inlet surface) or by increasing the flow velocity in the cooling flow inlet side to conductive process air content can be achieved.
"Kühlstromeintrittsseite" des Kreuzstromwärmetauschers bezieht sich dementsprechend in der Regel auf einen Volumenanteil des Wärmetauschers. Der Wärmetauscher kann beispielsweise in eine Volumenhälfte eingeteilt werden, die dem Kühlstromeintritt zugewandt ist und in eine andere Volumenhälfte, die dem Kühlstromeintritt abgewandt ist. "Kühlstromeintrittsseite" bezieht sich somit auf die Volumenhälfte des Wärmetauschers, die dem Kühlstromeintritt zugewandt ist. Bevorzugt werden mindestens 60 Volumen-% der Prozessluft zu der Seite des Kreuzstromwärmetauschers geleitet, an der der Kühlstrom eintritt.Accordingly, "cooling flow inlet side" of the crossflow heat exchanger generally refers to a volume fraction of the heat exchanger. The heat exchanger can be divided, for example, in a volume half, which faces the cooling flow inlet and in another volume half, which faces away from the cooling flow inlet. "Cooling flow inlet side" thus refers to the volume half of the heat exchanger facing the cooling flow inlet. At least 60% by volume is preferred the process air passed to the side of the cross-flow heat exchanger, where the cooling flow occurs.
Da es in einem Trockner aufgrund der baulichen Gegebenheiten in der Regel nur wenig Spielraum für eine Veränderung der Geometrie der Prozessluftkanäle gibt, ist das Anbringen von mindestens einem Strömungsleitkörper im relevanten Prozessluftstrom, d.h. im Abluftteilkanal und/oder im Kreuzstromwärmetauscher, bevorzugt. Durch das Einbringen von einem oder mehreren Strömungsleitkörpern wird somit ein größerer Anteil der Prozessluft zu der Kühlstromeintrittsseite gebracht. Die jeweilige Anzahl, Ausbildung und Anordnung der Strömungsleitkörper hängt von der Geometrie des Abluftkanals und der Geometrie des Kreuzstromwärmetauschers selbst, von der Art der Strömung sowie von der Verteilung der Strömungsgeschwindigkeiten über den Querschnitt ab.Since there is usually little room for a change in the geometry of the process air channels in a dryer due to the structural conditions, the attachment of at least one flow guide in the relevant process air stream, i. in the exhaust air part channel and / or in the cross-flow heat exchanger, preferably. By introducing one or more flow guide bodies, a larger proportion of the process air is thus brought to the cooling flow inlet side. The respective number, design and arrangement of the flow guide body depends on the geometry of the exhaust air duct and the geometry of the crossflow heat exchanger itself, on the type of flow and on the distribution of the flow velocities over the cross section.
In einer bevorzugten Ausführungsform des Trockners ist im Abluftkanal und/oder Kreuzstromwärmetauscher mindestens ein Strömungsleitkörper angeordnet, wobei die Position des Strömungsleitkörpers fest oder veränderbar ist. Im Allgemeinen weist der Strömungsleitkörper, z.B. ein Leitblech, eine erste Leitkörperoberfläche und eine zweite Leitkörperoberfläche auf, die sich in ihrer Lage hinsichtlich der Kühlstromeintrittsseite unterscheiden. Hierbei kann der Strömungsleitkörper in der Regel von der Prozessluft aus der Trocknungskammer umströmt werden.In a preferred embodiment of the dryer, at least one flow guide body is arranged in the exhaust air duct and / or cross flow heat exchanger, wherein the position of the flow guide is fixed or changeable. In general, the flow guide body, e.g. a baffle, a first baffle surface and a second baffle surface, which differ in their location with respect to the cooling flow inlet side. In this case, the flow guide body can generally be flowed around by the process air from the drying chamber.
Ein Strömungsleitkörper im Sinne der Erfindung kann im Allgemeinen jede Art von Körper sein, der in der Lage ist, den Prozessluftstrom erfindungsgemäß zu lenken. In einer bevorzugten Ausführungsform des erfindungsgemäßen Trockners ist der mindestens eine Strömungsleitkörper ein Leitblech. Hierbei bedeutet "Leitblech" im Allgemeinen einen relativ dünnen Körper, dessen im Allgemeinen einheitliche Dicke relativ klein verglichen mit seiner Länge ist. Hinsichtlich des Materials sind solche Materialien bevorzugt, deren Eigenschaften nicht durch den Kontakt mit der feuchten, warmen Prozessluft beeinträchtigt werden. Dieses Material ist vorzugsweise ein nicht korrodierendes Metall, wie beispielsweise Aluminium, oder ein Kunststoff. Zur verbesserten Strömungsleitung kann der Strömungsleitkörper, insbesondere das Leitblech, eine entsprechend strukturierte Oberfläche wie ein Leitprofil aufweisen, die sich dann vorzugsweise auf der angeströmten Seite des Leitbleches befindet.A flow guide according to the invention may generally be any type of body that is capable of directing the process air flow according to the invention. In a preferred embodiment of the dryer according to the invention, the at least one flow guide body is a guide plate. Here, "baffle" generally means a relatively thin body, the generally uniform thickness of which is relatively small compared to its length. With regard to the material, preference is given to those materials whose properties are not impaired by the contact with the moist, warm process air. This material is preferably a non-corrosive metal, such as aluminum, or a plastic. For improved flow conduction, the flow guide body, in particular the guide plate, can have a correspondingly structured surface such as a guide profile, which is then preferably located on the upstream side of the guide plate.
Es ist erfindungsgemäß bevorzugt, dass der mindestens eine Strömungsleitkörper im Abluftkanal angeordnet ist. Hierbei ist der mindestens eine Strömungsleitkörper vorzugsweise im Abluftkanal im Anströmbereich des Kreuzstromwärmetauschers angeordnet. Hierbei bedeutet Anströmbereich im Allgemeinen den Abschnitt des Abluftkanals, den der Prozessluftstrom unmittelbar vor Eintritt in den Kreuzstromwärmetauscher durchströmt.It is inventively preferred that the at least one flow guide is arranged in the exhaust duct. In this case, the at least one flow guide body is preferably arranged in the exhaust air duct in the inflow region of the crossflow heat exchanger. In this case, inflow region generally means the section of the exhaust air duct through which the process air stream flows immediately before entry into the crossflow heat exchanger.
In einer weiteren bevorzugten Ausführungsform des erfindungsgemäßen Trockners ist mindestens ein Strömungsleitkörper im Kreuzstromwärmetauscher angeordnet. Vorzugsweise unterteilt hierbei der mindestens eine Strömungsleitkörper einen Prozessluftbereich im Kreuzstromwärmetauscher in mindestens zwei getrennte Prozessluftteilbereiche, von denen ein erster Prozesslufteilbereich der Kühlstromeintrittseite zugewandt ist und ein zweiter Prozessluftteilbereich der Kühlstromeintrittseite der Seite des Kühlstromaustritts abgewandt ist. Dabei ist der mindestens eine Strömungsleitkörper weitgehend in der Strömungsrichtung des Prozessluftstroms im Prozessluftbereich des Wärmetauschers angeordnet.In a further preferred embodiment of the dryer according to the invention, at least one flow guide body is arranged in the crossflow heat exchanger. In this case, the at least one flow guide body preferably divides a process air area in the crossflow heat exchanger into at least two separate process air portions, of which a first process air portion faces the cooling flow inlet side and a second process air portion of the cooling flow inlet side faces away from the side of the cooling flow outlet. In this case, the at least one flow guide body is arranged largely in the flow direction of the process air flow in the process air region of the heat exchanger.
Besonders bevorzugt ist dabei, dass ein Leitblech den Prozessluftbereich im Kreuzstromwärmetauscher in zwei getrennte Prozessluftteilbereiche unterteilt, von denen ein erster Prozessluftteilbereich der Kühlstromeintrittsseite zugewandt und ein zweiter Prozessluftteilbereich der Kühlstromeintrittsseite abgewandt ist. Dabei ist vorzugsweise beim ersten Prozessluftteilbereich die Fläche des Prozessstromeintritts kleiner als die Fläche des Prozessstromaustritts, wohingegen beim zweiten Prozessluftteilbereich das entsprechende Flächenverhältnis vorzugsweise umgekehrt ist. Die Volumenanteile der beiden Prozessluftteilbereiche sind vorzugsweise nicht stark unterschiedlich, d.h. der Volumenanteil einer der beiden Prozessluftteilbereiche am entsprechenden gesamten Prozessluftbereich überschreitet nicht 70 %, mehr bevorzugt nicht 60 %, besonders bevorzugt nicht 55 %. Dabei werden die entsprechenden Anteile, bezogen auf den gesamten Prozessluftbereich, je nach Bauart des Kreuzstromwärmetauschers unterschiedlich bestimmt, beispielsweise bei einem Plattenwärmetauscher bezogen auf den jeweiligen Plattenzwischenraum. Dies ist insofern von Bedeutung, da bei einem Plattenwärmetauscher die Anordnung des mindestens einen Strömungsleitkörpers in verschiedenen Plattenzwischenräumen des Prozessluftbereichs unterschiedlich ausgestaltet sein kann.It is particularly preferred that a baffle divides the process air area in the cross-flow heat exchanger into two separate process air subregions, of which a first process air portion faces the cooling flow inlet side and a second process air part region faces away from the cooling flow inlet side. In this case, the area of the process stream inlet is preferably smaller than the area of the process stream outlet in the first process air partial area, whereas in the second process air partial area the corresponding area ratio is preferably reversed. The volume fractions of the two process air subregions are preferably not greatly different, ie the volume fraction of one of the two process air subregions at the corresponding total process air range does not exceed 70%, more preferably not 60%, particularly preferably not 55%. The corresponding proportions, based on the total process air range, depending on the design of the cross-flow heat exchanger are determined differently, for example in a plate heat exchanger based on the respective plate gap. This is important in that, in the case of a plate heat exchanger, the arrangement of the at least one flow guide body can be configured differently in different plate interspaces of the process air area.
Mit der vorliegenden Erfindung kann der Wärmeaustausch im Kreuzstromwärmetauscher und insbesondere der von einer Kondensation der in der feuchtwarmen Prozessluft im Wärmetauscher begleitete Wärmetausch effizient gestaltet werden. Vorzugsweise kann hierbei der Wärmeaustausch über die Position des Strömungsleitkörpers optimal eingestellt werden.With the present invention, the heat exchange in the cross-flow heat exchanger and in particular the heat exchange accompanied by condensation of the heat exchange accompanied by the moist, warm process air in the heat exchanger can be made efficient. Preferably, in this case, the heat exchange via the position of the flow guide be optimally adjusted.
Vorzugsweise kann im erfindungsgemäßen Trockner daher eine Position des Strömungsleitkörpers im Abluftkanal und/oder im Kreuzstromwärmetauscher mittels der Steuereinrichtung eingestellt werden. Hierdurch ist es insbesondere möglich, dass Temperatur und Feuchtigkeitsgehalt der aus der Trocknungskammer herrührenden feuchtwarmen Prozessluft berücksichtigt werden.Preferably, therefore, in the dryer according to the invention a position of the flow guide in the exhaust duct and / or in the crossflow heat exchanger can be adjusted by means of the control device. This makes it possible in particular for the temperature and moisture content of the moist warm process air originating from the drying chamber to be taken into account.
Beispielsweise kann vorzugsweise die Position des Strömungsleitkörpers in Abhängigkeit von Parametern eines Trocknungsprozesses eingestellt werden.For example, preferably, the position of the flow guide can be adjusted depending on parameters of a drying process.
Alternativ oder in Ergänzung hierzu kann bei einem erfindungsgemäßen Trockner eine Wand des Abluftkanals so ausgestaltet sein, dass bei der im Abluftkanal fließenden Prozessluft ein größerer Anteil p*M der Prozessluftmenge M, wobei p > 0,5 gilt, zu einer Kühlstromeintrittsseite des Kreuzstromwärmetauschers geleitet wird. Hierzu kann die Wand des Abluftkanals beispielsweise entsprechend ausgeformte Rippen enthalten, welche die Strömung der Prozessluft in Richtung der Kühlstromeintrittsseite des Kreuzstromwärmetauschers leiten, oder die Wand selbst kann eine hierzu geeignete Schräge oder sonstige Form aufweisen. Dies ist insbesondere durch Krümmungen im Abluftkanal, die beispielweise unterschiedliche Strömungsgeschwindigkeiten über den Kanalquerschnitt verursachen können, möglich.Alternatively or in addition to this, in a dryer according to the invention, a wall of the exhaust air duct can be designed such that a larger proportion p * M of the process air quantity M, where p> 0.5, is conducted to a cooling flow inlet side of the crossflow heat exchanger in the process air flowing in the exhaust air duct , For this purpose, the wall of the exhaust duct, for example, contain correspondingly shaped ribs, which direct the flow of process air in the direction of the cooling flow inlet side of the crossflow heat exchanger, or the wall itself may have a suitable slope or other shape. This is in particular possible by means of curvatures in the exhaust air duct, which can cause, for example, different flow velocities over the duct cross section.
In einer weiteren bevorzugten Ausführungsform der Erfindung kann der Abluftkanal mehrere Abluftteilkanäle umfassen, die sich in Hinblick auf die Anströmung der Kühlstromeintrittsseite des Kreuzstromwärmetauschers unterscheiden. Beispielsweise kann es sich hierbei um getrennte Rohre handeln, die jeweils einen Abluftteilkanal darstellen.In a further preferred embodiment of the invention, the exhaust air duct may comprise a plurality of partial exhaust air ducts, which differ with respect to the flow of the cooling flow inlet side of the crossflow heat exchanger. For example, these may be separate pipes, each of which represents a partial exhaust air duct.
In einer bevorzugten Ausführungsform des erfindungsgemäßen Trockners unterteilt der mindestens eine Strömungsleitkörper den Abluftkanal vor dem Kreuzstromwärmetauscher in mindestens zwei getrennte Abluftteilkanäle. Dabei ist der mindestens eine Strömungsleitkörper im Allgemeinen weitgehend in der Strömungsrichtung des Prozessluftstroms im Abluftkanal vor dem Wärmetauscher angeordnet, d.h. in der Regel längs des Abluftkanals, wodurch mindestens zwei getrennte Abluftteilkanäle gebildet werden. Von diesen ist einer der Kühlstromeintrittsseite des Wärmetauschers zugewandt und der andere dieser abgewandt. Die Anzahl der entstehenden Abluftteilkanäle bestimmt sich somit in der Regel aus der Anzahl der Strömungsleitkörper. Beispielsweise kann ein Leitblech längs der Strömungsrichtung in den Abluftkanal eingebracht werden, sodass nunmehr zwei getrennte Ablufteilkanäle entstehen, durch welche der Kreuzstromwärmetauscher angeströmt wird, wobei ein Abluftteilkanal der Kühlstromeintrittsseite zugewandt und der andere der Seite des Kühlstromaustritts zugewandt ist. Dabei ist vorzugsweise die gesamte von der Prozessluft angeströmte Fläche des Wärmetauschers derart unterteilt, dass maximal ein Drittel der gesamten von der Prozessluft angeströmten Fläche des Kreuzstromwärmetauschers von dem der Kühlstromeintrittsseite zugewandten Abluftteilkanal eingenommen wird.In a preferred embodiment of the dryer according to the invention, the at least one flow guide body divides the exhaust air duct upstream of the crossflow heat exchanger in at least two separate exhaust air ducts. In this case, the at least one flow guide body is generally arranged substantially in the flow direction of the process air flow in the exhaust duct upstream of the heat exchanger, ie, generally along the exhaust passage, whereby at least two separate exhaust air ducts are formed. Of these, one of the cooling flow inlet side of the heat exchanger faces and the other facing away from this. The number of exhaust air partial ducts thus formed is thus determined as a rule from the number of flow guide. For example, a baffle can be introduced along the flow direction into the exhaust air duct, so that now two separate Ablufteilkanäle arise through which the cross-flow heat exchanger is flown, with an exhaust air duct facing the cooling flow inlet side and the other side facing the cooling flow outlet. In this case, preferably, the entire surface of the heat exchanger which is flowed through by the process air is subdivided in such a way that a maximum of one third of the total area of the crossflow heat exchanger which is flown by the process air is occupied by the exhaust air part channel facing the cooling flow inlet side.
Der Kreuzstromwärmetauscher ist von seiner Art und Ausgestaltung her nicht eingeschränkt. So kann es sich um einen Luft-Gas- oder Luft-Flüssigkeit-Wärmetauscher handeln. Beispielsweise kann es sich um die Wärmesenke einer Wärmepumpe oder einen Luft-Luft-Wärmetauscher handeln. Als Kühlmedium kann somit beispielsweise ein Kältemittel einer Wärmepumpe dienen. Ebenso kann als Kühlmedium kalte Luft eines Luft-Luft-Wärmetauschers dienen. Erfindungsgemäß bevorzugt ist ein Trockner, bei dem der Kreuzstromwärmetauscher ein Luft-Luft-Wärmetauscher ist.The crossflow heat exchanger is not limited by its type and design. So it may be an air-gas or air-liquid heat exchanger. For example, it may be the heat sink of a heat pump or an air-to-air heat exchanger. As a cooling medium can thus serve, for example, a refrigerant of a heat pump. Likewise, can serve as a cooling medium cold air of an air-to-air heat exchanger. According to the invention, a dryer is preferred in which the cross-flow heat exchanger is an air-air heat exchanger.
Weiterhin können verschiedene Bauarten des Kreuzstromwärmetauschers eingesetzt werden, beispielsweise Rohrbündelwärmetauscher und Plattenwärmetauscher. Vorzugsweise hat der Wärmetauscher eine geeignete Form und/oder Oberflächenstruktur, um den Wärmetausch zu unterstützen. Hierbei werden Form und/oder Oberflächenstruktur geeignet ausgewählt, damit der Wärmetausch zwischen einer ggf. mit Flusen beladenen feuchtwarmen Prozessluft und einem Kühl- oder Kältemittel optimal erfolgt.Furthermore, various types of cross-flow heat exchanger can be used, for example, tube bundle heat exchanger and plate heat exchanger. Preferably, the heat exchanger has a suitable shape and / or surface structure to assist the heat exchange. In this case, the shape and / or surface structure are suitably selected so that the heat exchange between an optionally loaded with lint moist warm process air and a coolant or refrigerant optimally.
Erfindungsgemäß ist hierbei ein Plattenwärmetauscher vorteilhaft. Ein Plattenwärmetauscher besteht aus mehreren Platten, die so zusammengesetzt sind, dass jeweils in den aufeinanderfolgenden Zwischenräumen abwechselnd einmal der wärmeabgebende und einmal der kühlende Stoffstrom fließt. Somit wechseln sich die von Prozessluft durchströmten Bereiche mit den Bereichen des Kühlstroms ab. Wenn bei einem Plattenwärmetauscher der mindestens eine Strömungsleitkörper im Wärmetauscher angeordnet ist, kann dessen Anordnung in allen Prozessluftzwischenräumen ("Prozessluftbereichen") auf identische Weise erfolgen oder variieren. Eine Variation der Anordnung des mindestens einen Strömungsleitkörpers über die verschiedenen Prozessluftzwischenräume ist insbesondere bei unterschiedlicher Beaufschlagung der verschiedenen Zwischenräume mit Prozessluft, aber auch bei unterschiedlicher Beaufschlagung der verschiedenen Zwischenräume mit Kühlmittel wie Kühlluft bevorzugt.According to the invention, a plate heat exchanger is advantageous in this case. A plate heat exchanger consists of several plates, which are composed so that in each successive spaces alternately once the heat-emitting and once the cooling stream flows. Thus, the areas through which the process air flows alternate with the areas of the cooling flow. If, in a plate heat exchanger, the at least one flow guide body is arranged in the heat exchanger, its arrangement can take place in all process air intermediate spaces ("process air areas") in an identical manner or vary. A variation of the arrangement of the at least one flow guide body over the different process air intermediate spaces is preferred in particular for different admission of the different interspaces with process air, but also with different loading of the various spaces with coolant such as cooling air.
Erfindungsgemäß wird ein größerer Anteil der Prozessluft zu der Seite des Kreuzstromwärmetauschers geleitet, an der der Kühlstrom eintritt. Dies bedeutet beispielsweise bei einem Plattenwärmetauscher, dass hinsichtlich der "Seite des Kreuzstromwärmetauschers, an der der Kühlstrom eintritt" das Volumen über alle Prozessluftzwischenräume insgesamt betrachtet wird. Es kann bei einem Plattenwärmetauscher somit genügen, dass in einem einzigen Prozessluftzwischenraum mehr als 50 Volumen-% der Prozessluft dieses Zwischenraums zu der Seite des Kreuzstromwärmetauschers geleitet werden, an der der Kühlstrom eintritt.According to the invention, a larger proportion of the process air is conducted to the side of the crossflow heat exchanger, at which the cooling flow occurs. In the case of a plate heat exchanger, for example, this means that the volume over all process air gaps is considered as a whole with regard to the "side of the crossflow heat exchanger at which the cooling flow occurs". Thus, in a plate heat exchanger, it may be sufficient that in a single process air gap more than 50% by volume of the process air of this gap is directed to the side of the crossflow heat exchanger where the cooling flow occurs.
Gegenstand der Erfindung ist außerdem ein Verfahren zum Betrieb eines Trockners, umfassend eine Steuereinrichtung, einen Prozessluftkanal, in welchem eine Heizung, eine Trocknungskammer für zu trocknende Gegenstände, ein Gebläse und ein Kreuzstromwärmetauscher angeordnet sind, wobei der Prozessluftkanal einen Zuluftkanal vor der Trocknungskammer und einen Abluftkanal zwischen Trocknungskammer und Kreuzstromwärmetauscher umfasst, und wobei Abluftkanal und/oder Kreuzstromwärmetauscher derart ausgebildet ist/sind, dass ein größerer Anteil p*M einer Prozessluftmenge M, die durch den Abluftkanal in den Kreuzstromwärmetauscher fließt, wobei p > 0,5 gilt, zu einer Kühlstromeintrittsseite des Kreuzstromwärmetauschers geleitet wird, wobei bei dem Verfahren die feuchtwarme Prozessluft aus der Trocknungskammer in den Abluftkanal geleitet und so aufgeteilt wird, dass ein größerer Anteil p*M einer Prozessluftmenge M, die durch den Abluftkanal in den Kreuzstromwärmetauscher fließt, wobei p > 0,5 gilt, zu einer Kühlstromeintrittsseite des Kreuzstromwärmetauschers geleitet wird.The invention also relates to a method for operating a dryer, comprising a control device, a process air duct, in which a heater, a drying chamber for objects to be dried, a fan and a cross-flow heat exchanger are arranged, wherein the process air duct a supply air duct in front of the drying chamber and an exhaust duct between drying chamber and cross-flow heat exchanger, and wherein the exhaust duct and / or cross-flow heat exchanger is / are such that a larger proportion p * M of a process air amount M flowing through the exhaust duct into the cross-flow heat exchanger, where p> 0.5, to a cooling flow inlet side the cross-flow heat exchanger is passed, wherein in the method, the moist, warm process air from the drying chamber in the exhaust duct is divided and divided so that a larger proportion p * M of a process air amount M, which flows through the exhaust duct in the cross-flow heat exchanger where p> 0.5, is passed to a cooling flow inlet side of the cross-flow heat exchanger.
Die Erfindung hat den Vorteil, dass ein Trockner mit einem effizienten Wärmetauscher bereitgestellt wird und dadurch eine Energieeinsparung ermöglicht wird. Dies ist insbesondere deshalb der Fall, da bei einem erfindungsgemäßen Trockner die Abscheideleistung für die Feuchtigkeit aus der feuchtwarmen Prozessluft verbessert ist, wohingegen eine Verstärkung der Kühlleistung unnötig ist. Somit ist trotz effizienterem Wärmetauscher keine verstärkte Energiezufuhr nötig, um im Wärmetauscher verlorene thermische Energie der Prozessluft wieder zuzuführen. In Ausführungsformen des erfindungsgemäßen Trockners, in denen der Kreuzstromwärmetrockner ein Luft-Luft-Wärmetauscher ist, besteht der Vorteil, dass er gegenüber Trocknern mit Wärmepumpe durch weniger Bauteile kosten- und wartungsärmer ist.The invention has the advantage that a dryer is provided with an efficient heat exchanger, thereby enabling energy saving. This is the case in particular because, with a dryer according to the invention, the separation efficiency for the moisture from the moist, warm process air is improved, whereas an increase in the cooling capacity is unnecessary. Thus, despite more efficient heat exchanger no amplified power supply is needed to supply lost thermal energy in the heat exchanger process air. In embodiments of the dryer according to the invention, in which the cross-flow heat dryer is an air-to-air heat exchanger, there is the advantage that it costs less and less maintenance compared to dryers with heat pump by fewer components.
Weitere Einzelheiten, Merkmale und Vorteile der Erfindung ergeben sich aus der nachfolgenden Beschreibung von nicht einschränkenden Ausführungsbeispielen eines erfindungsgemäßen Trockners unter Bezugnahme auf die
-
Fig. 1 zeigt einen vertikalen Schnitt durch einen Trockner gemäß einer ersten Ausführungsform, bei welcher der Trockner als Umlufttrockner ausgestaltet ist. -
Fig. 2 zeigt eine dreidimensionale Ansicht eines relevanten Ausschnitts aus einer zweiten Ausführungsform eines erfindungsgemäßen Trockners, bei dem ein Luft-Luft-Wärmetauscher als Kreuzstromwärmetauscher und angrenzende Prozessluftkanäle, Zuluft- und Abluftkanal, sichtbar sind. -
Fig. 3 zeigt eine dreidimensionale Ansicht eines relevanten Ausschnitts aus einer dritten Ausführungsform eines erfindungsgemäßen Trockners, bei dem ein Luft-Luft-Wärmetauscher als Kreuzstromwärmetauscher und angrenzende Prozessluftkanäle, Zuluft- und Abluftkanal, sichtbar sind. Dabei ist ein Leitblech im Prozessluftbereich des Kreuzstromwärmetauschers angeordnet. -
Fig. 1 zeigt insbesondere einen senkrecht geschnittenen Trockner 1 gemäß einer ersten Ausführungsform, bei welcher der Trockner 1 als Umlufttrockner ausgestaltet ist, dermit einem Kreuzstromwärmetauscher 14 ausgestattet ist.Der Kreuzstromwärmetauscher 14 ist hierbei als Luft-Luft-Wärmetauscher ausgestaltet.Der Trockner 1 weist eine um eine horizontale Achse drehbare Trommel 3als Trocknungskammer 3 auf, innerhalb welcher Mitnehmer 4 zur Bewegung von Wäsche während einer Trommeldrehung befestigt sind. Prozessluft wird mittels eines Gebläses 15 durch einenZuluftkanal 12 als Teil des Prozessluftkanals und eine Heizung 16 indie Trommel 3 sowie durch einen Ausgang 13 ineinen Abluftkanal 2 und durch einen Kreuzstromwärmetauscher 14 in einem geschlossenen Kreis geführt (Prozessluftkreislauf 2, 12). Nach dem Durchgangdurch die Trommel 3 gelangt hierbei die feuchte, warme Prozessluft inden Kreuzstromwärmetauscher 14, wo sie abgekühlt und entfeuchtet wird und anschließend durch dieHeizung 16 wieder erwärmt wird. Die erwärmte Prozessluft wird von hinten, d.h. von der einer Tür 5 gegenüberliegenden Seite derTrommel 3, durch deren gelochten Boden indie Trommel 3 geleitet, kommt dort mit der zu trocknenden Wäsche (hier nicht gezeigt) in Berührung und strömt durch dieBefüllöffnung der Trommel 3 zu einem Flusensieb 6 innerhalb einer die Befüllöffnung verschließenden Tür 5. Anschließend wird der Prozessluftstrom in der Tür 5 nach unten umgelenkt undim Abluftkanal 2zum Kreuzstromwärmetauscher 14 geführt, wo sie abgekühlt und entfeuchtet. Inden Kreuzstromwärmetauscher 14 gelangt hierzu amKühllufteingang 17 ein Kühlluftstrom inden Trockner 1, der diesenam Kühlluftausgang 18 wieder verlässt.
-
Fig. 1 shows a vertical section through a dryer according to a first embodiment, in which the dryer is designed as a circulating air dryer. -
Fig. 2 shows a three-dimensional view of a relevant section of a second embodiment of a dryer according to the invention, in which an air-air heat exchanger as a cross-flow heat exchanger and adjacent process air ducts, supply air and exhaust air duct, are visible. -
Fig. 3 shows a three-dimensional view of a relevant section of a third embodiment of a dryer according to the invention, in which an air-air heat exchanger as a cross-flow heat exchanger and adjacent process air ducts, supply air and exhaust duct, are visible. In this case, a baffle is arranged in the process air area of the crossflow heat exchanger. -
Fig. 1 shows in particular a vertically cutdryer 1 according to a first embodiment, in which thedryer 1 is designed as a circulating air dryer, which is equipped with across-flow heat exchanger 14. Thecross-flow heat exchanger 14 is designed here as an air-to-air heat exchanger. Thedryer 1 has adrum 3 rotatable about a horizontal axis as a dryingchamber 3, within which Carrier 4 are attached to the movement of laundry during a drum rotation. Process air is conducted by means of ablower 15 through asupply air duct 12 as part of the process air duct and aheater 16 in thedrum 3 and through anoutlet 13 in anexhaust duct 2 and through across-flow heat exchanger 14 in a closed circuit (process air circuit 2, 12). After passing through thedrum 3 in this case passes the moist, warm process air in thecross-flow heat exchanger 14, where it is cooled and dehumidified and then heated by theheater 16 again. The heated process air is from the rear, ie from the door 5 opposite side of thedrum 3, passed through the perforated bottom in thedrum 3, comes there with the laundry to be dried (not shown) into contact and flows through the filling opening of thedrum 3, the process air flow in the door 5 is deflected downward and guided in theexhaust duct 2 to thecross-flow heat exchanger 14, where it is cooled and dehumidified. For this purpose, a cooling air flow into thedryer 1, which leaves it at the coolingair outlet 18, enters thecrossflow heat exchanger 14 at the coolingair inlet 17.
In der Wand 29 des Abluftkanals 2 befindet sich eine Rippe 30, die dafür sorgt, dass die im Abluftkanal 2 strömende Prozessluft vor allem in Richtung einer Kühlstromeintrittsseite 24 im Kreuzstromwärmetauscher 14 fließt und dort zu einem effizienten Wärmeaustausch beiträgt.In the
Der Teil des Prozessluftkanals 2,12 vom Wärmetauscher 14 bis zur Trommel 3 wird somit auch als Zuluftkanal 12 bezeichnet und der Teil des Prozessluftkanals 2,12 von der Trommel 3 bis zum Wärmetauscher 14 als Abluftkanal 2.The part of the
Die Trommel 3 wird in der in
Die Steuerung des Trockners 1 erfolgt über eine Steuereinrichtung 11 (auch als Programmsteuerung bezeichenbar), die vom Benutzer über eine Bedieneinheit 9 geregelt werden kann. Mittels einer Anzeigevorrichtung 10 können verschiedene Zustände des Trockners 1 optisch oder akustisch dargestellt werden.The control of the
In dieser Ausführungsform ist der Kreuzstromwärmetauscher 14 als Luft-Luft-Wärmetauscher mit Wärmetauscherplatten 19 ausgebildet. Die über den Zuluftkanal 2 dem Kreuzstromwärmetauscher 14 zugeführte warme, feuchte Prozessluft wird durch die als Prozessluftbereiche 20 ausgebildeten Zwischenräume der Wärmetauscherplatten 19 geführt. Die Prozessluftbereiche 20 sind im Kreuzstromwärmetauscher 14 wechselweise mit davon getrennten Kühlluftbereichen 21 angeordnet, durch welche Kühlluft strömt, die vom Kühlluftzugang 17 zum Kreuzstromwärmetauscher 14 geleitet wird und von dort über den Kühlluftausgang 18 aus dem Trockner 1 gelangt.In this embodiment, the
Im Abluftkanal 2 ist ein Leitblech 22 als Strömungsleitkörper 22 im Anströmbereich 23 des Kreuzstromwärmetauschers 14 derart angeordnet, dass ein größerer Anteil der Prozessluft zu der Kühlstromeintrittsseite 24 des Kreuzstromwärmetauschers 14 geleitet wird. Durch das Leitblech 22 wird der Abluftkanal 2 in zwei getrennte Prozessluftkanalbereiche 25 bzw. 26 unterteilt.In the
In dieser Ausführungsform ist der Kreuzstromwärmetauscher 14 ebenfalls als Luft-Luft-Wärmetauscher mit Wärmetauscherplatten 19 ausgebildet. Jedoch ist hierin ein Leitblech 22 als Strömungsleitkörper 22 im Prozessluftbereich 20 des Kreuzstromwärmetauschers 14 angeordnet, so dass ein größerer Anteil der Prozessluft zu der Kühlstromeintrittsseite 24 des Kreuzstromwärmetauschers 14 geleitet wird. Durch das Leitblech 22 wird der Kreuzstromwärmetauscher 14 in zwei getrennte Prozessluftteilbereiche 27,28 unterteilt. Dabei ist ein erster Prozessluftteilbereich 27 der Kühlstromeintrittstelle 24 zugewandt und ein zweiter Prozessluftteilbereich 28 der Kühlstromeintrittstelle 24 abgewandt.In this embodiment, the
Der Unterschied zwischen der in
- 11
- Trockner, KondensationstrocknerDryer, condensation dryer
- 22
- Prozessluftkanal, AbluftkanalProcess air duct, exhaust duct
- 33
- Trocknungskammer, TrommelDrying chamber, drum
- 44
- Mitnehmertakeaway
- 55
- Türdoor
- 66
- Flusensieblint
- 77
- Lagerschildend shield
- 88th
- Gleitstreifenlubricating strip
- 99
- Bedieneinheitoperating unit
- 1010
- Anzeigevorrichtungdisplay device
- 1111
- Steuereinrichtung, ProgrammsteuerungControl device, program control
- 1212
- Prozessluftkanal, ZuluftkanalProcess air duct, supply air duct
- 1313
- Trommelausgangdrum exit
- 1414
- KreuzstromwärmetauscherCross-flow heat exchanger
- 1515
- Gebläsefan
- 1616
- Heizungheater
- 1717
- KühllufteingangCooling air inlet
- 1818
- KühlluftausgangCooling air outlet
- 1919
- Wärmetauscherplattenheat exchanger plates
- 2020
- ProzessluftbereichProcess air area
- 2121
- KühlluftbereichThe cooling air
- 2222
- Leitblech, StrömungsleitkörperGuide plate, flow guide
- 2323
- Anströmbereich des KreuzstromwärmetauschersFlow area of the cross-flow heat exchanger
- 2424
- KühlstromeintrittsseiteCooling flow inlet side
- 2525
- Erster AbluftteilkanalFirst exhaust air duct
- 2626
- Zweiter AbluftteilkanalSecond partial exhaust air duct
- 2727
- Erster Prozessluftteilbereich im KreuzstromwärmetauscherFirst process air section in cross flow heat exchanger
- 2828
- Zweiter Prozessluftteilbereich im KreuzstromwärmetauscherSecond process air section in the crossflow heat exchanger
- 2929
- Wand des AbluftkanalsWall of the exhaust duct
- 3030
- Rippe in Wand des AbluftkanalsRib in wall of the exhaust duct
Claims (15)
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DE102011081940A DE102011081940A1 (en) | 2011-09-01 | 2011-09-01 | Dryers with a cross-flow heat exchanger and method of its operation |
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2980306A1 (en) * | 2014-07-31 | 2016-02-03 | Indesit Company S.p.A. | Household drying appliance with improved inlet section of the drying fluid in the condenser |
EP3633307A1 (en) * | 2018-10-04 | 2020-04-08 | Hamilton Sundstrand Corporation | Plate fin heat exchanger flexible manifold |
US10801790B2 (en) | 2018-03-16 | 2020-10-13 | Hamilton Sundstrand Corporation | Plate fin heat exchanger flexible manifold structure |
EP3819423A1 (en) * | 2019-11-07 | 2021-05-12 | Whirlpool Corporation | Method of removing heat from a clothes tumbling system on the outside of the cabinet |
US11686530B2 (en) | 2018-03-16 | 2023-06-27 | Hamilton Sundstrand Corporation | Plate fin heat exchanger flexible manifold |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015200237A1 (en) | 2015-01-12 | 2016-07-14 | BSH Hausgeräte GmbH | Condensation dryer with improved drying and process for its operation |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3027900C2 (en) | 1980-07-23 | 1986-11-06 | Bosch-Siemens Hausgeräte GmbH, 7000 Stuttgart | Air-cooled heat exchanger for household tumble dryers |
DE19644710A1 (en) * | 1996-10-28 | 1998-04-30 | Aeg Hausgeraete Gmbh | Laundry drying appliance |
DE19644711A1 (en) | 1996-10-28 | 1998-04-30 | Aeg Hausgeraete Gmbh | Laundry dryer |
DE19644709A1 (en) * | 1996-10-28 | 1998-04-30 | Aeg Hausgeraete Gmbh | Laundry dryer |
EP0982427B1 (en) | 1998-08-25 | 2003-03-05 | Joma-Polytec Kunststofftechnik GmbH | Cross flow heat exchanger for laundry drier with condenser |
EP1050618B1 (en) | 1999-04-08 | 2003-10-15 | BSH Bosch und Siemens Hausgeräte GmbH | Heat exchanger for laundry drier |
US6845813B1 (en) * | 2003-10-13 | 2005-01-25 | Knighthawk Engineering | Intra-body flow distributor for heat exchanger |
EP1729078A2 (en) | 2005-05-26 | 2006-12-06 | LG Electronics Inc. | Heat exchanger for dryer and condensing type dryer using the same |
DE102008043920A1 (en) | 2008-11-20 | 2010-05-27 | BSH Bosch und Siemens Hausgeräte GmbH | Condensation dryer with a heat pump and method for its operation |
DE102008044277A1 (en) | 2008-12-02 | 2010-06-10 | BSH Bosch und Siemens Hausgeräte GmbH | Dryer with a heat pump and an electric heater and method of operation |
DE102009046680A1 (en) | 2009-11-13 | 2011-05-19 | BSH Bosch und Siemens Hausgeräte GmbH | Domestic appliance with heat exchanger made of thermoplastic material containing, as well as such a heat exchanger |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3446468A1 (en) * | 1984-12-20 | 1986-07-03 | Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt | Process and apparatus for the drying of laundry |
DE4211011C2 (en) * | 1992-04-02 | 1996-08-22 | Bosch Siemens Hausgeraete | Household clothes dryer with a process air duct and a heat exchanger |
JP2006336874A (en) * | 2003-10-15 | 2006-12-14 | Matsushita Electric Ind Co Ltd | Heat pump type drier |
DE102007042969B4 (en) * | 2007-09-10 | 2021-05-27 | BSH Hausgeräte GmbH | Dryer with heat recovery and circulating air |
CN102918198B (en) * | 2010-06-07 | 2015-12-16 | 阿塞里克股份有限公司 | Thermoelectric heatpump clothesdrier |
-
2011
- 2011-09-01 DE DE102011081940A patent/DE102011081940A1/en not_active Withdrawn
-
2012
- 2012-08-30 EP EP12182350.4A patent/EP2565321B1/en active Active
- 2012-08-30 PL PL12182350T patent/PL2565321T3/en unknown
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3027900C2 (en) | 1980-07-23 | 1986-11-06 | Bosch-Siemens Hausgeräte GmbH, 7000 Stuttgart | Air-cooled heat exchanger for household tumble dryers |
DE19644710A1 (en) * | 1996-10-28 | 1998-04-30 | Aeg Hausgeraete Gmbh | Laundry drying appliance |
DE19644711A1 (en) | 1996-10-28 | 1998-04-30 | Aeg Hausgeraete Gmbh | Laundry dryer |
DE19644709A1 (en) * | 1996-10-28 | 1998-04-30 | Aeg Hausgeraete Gmbh | Laundry dryer |
EP0982427B1 (en) | 1998-08-25 | 2003-03-05 | Joma-Polytec Kunststofftechnik GmbH | Cross flow heat exchanger for laundry drier with condenser |
EP1050618B1 (en) | 1999-04-08 | 2003-10-15 | BSH Bosch und Siemens Hausgeräte GmbH | Heat exchanger for laundry drier |
US6845813B1 (en) * | 2003-10-13 | 2005-01-25 | Knighthawk Engineering | Intra-body flow distributor for heat exchanger |
EP1729078A2 (en) | 2005-05-26 | 2006-12-06 | LG Electronics Inc. | Heat exchanger for dryer and condensing type dryer using the same |
DE102008043920A1 (en) | 2008-11-20 | 2010-05-27 | BSH Bosch und Siemens Hausgeräte GmbH | Condensation dryer with a heat pump and method for its operation |
DE102008044277A1 (en) | 2008-12-02 | 2010-06-10 | BSH Bosch und Siemens Hausgeräte GmbH | Dryer with a heat pump and an electric heater and method of operation |
DE102009046680A1 (en) | 2009-11-13 | 2011-05-19 | BSH Bosch und Siemens Hausgeräte GmbH | Domestic appliance with heat exchanger made of thermoplastic material containing, as well as such a heat exchanger |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2980306A1 (en) * | 2014-07-31 | 2016-02-03 | Indesit Company S.p.A. | Household drying appliance with improved inlet section of the drying fluid in the condenser |
US10801790B2 (en) | 2018-03-16 | 2020-10-13 | Hamilton Sundstrand Corporation | Plate fin heat exchanger flexible manifold structure |
US11686530B2 (en) | 2018-03-16 | 2023-06-27 | Hamilton Sundstrand Corporation | Plate fin heat exchanger flexible manifold |
EP3633307A1 (en) * | 2018-10-04 | 2020-04-08 | Hamilton Sundstrand Corporation | Plate fin heat exchanger flexible manifold |
EP3819423A1 (en) * | 2019-11-07 | 2021-05-12 | Whirlpool Corporation | Method of removing heat from a clothes tumbling system on the outside of the cabinet |
Also Published As
Publication number | Publication date |
---|---|
EP2565321B1 (en) | 2015-01-14 |
DE102011081940A1 (en) | 2013-03-07 |
PL2565321T3 (en) | 2015-06-30 |
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