EP0521298B1 - Dispositif d'échange de chaleur pour séchoir par réfrigération dans les installations d'air comprimé - Google Patents

Dispositif d'échange de chaleur pour séchoir par réfrigération dans les installations d'air comprimé Download PDF

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Publication number
EP0521298B1
EP0521298B1 EP92108919A EP92108919A EP0521298B1 EP 0521298 B1 EP0521298 B1 EP 0521298B1 EP 92108919 A EP92108919 A EP 92108919A EP 92108919 A EP92108919 A EP 92108919A EP 0521298 B1 EP0521298 B1 EP 0521298B1
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EP
European Patent Office
Prior art keywords
heat exchanger
air
passages
passage
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92108919A
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German (de)
English (en)
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EP0521298A3 (en
EP0521298A2 (fr
Inventor
Werner Brüggemann
Josef Gievers
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Autokuehler GmbH and Co KG
Original Assignee
Autokuehler GmbH and Co KG
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 DE4118289A external-priority patent/DE4118289A1/de
Application filed by Autokuehler GmbH and Co KG filed Critical Autokuehler GmbH and Co KG
Publication of EP0521298A2 publication Critical patent/EP0521298A2/fr
Publication of EP0521298A3 publication Critical patent/EP0521298A3/de
Application granted granted Critical
Publication of EP0521298B1 publication Critical patent/EP0521298B1/fr
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Classifications

    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/206—Heat pump arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B21/00—Arrangements or duct systems, e.g. in combination with pallet boxes, for supplying and controlling air or gases for drying solid materials or objects
    • F26B21/06—Controlling, e.g. regulating, parameters of gas supply
    • F26B21/08—Humidity
    • F26B21/086—Humidity by condensing the moisture in the drying medium, which may be recycled, e.g. using a heat pump cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0041—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having parts touching each other or tubes assembled in panel form
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • F28D7/085—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions
    • F28D7/087—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions assembled in arrays, each array being arranged in the same plane
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0038—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for drying or dehumidifying gases or vapours
    • 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
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

Definitions

  • the invention relates to a heat exchanger device for refrigeration dryers in compressed air systems according to the preamble of claim 1.
  • Compressed air systems of the type of interest here serve to be generated by means of a compressor and under a pressure of e.g. to provide compressed air up to 25 bar.
  • This compressed air however, like the atmospheric air, has a high one at least in European areas Moisture content corresponding to a relative humidity of up to 80% and more.
  • Moisture content corresponding to a relative humidity of up to 80% and more.
  • absolutely dry air is needed. It is therefore known from the compressor to discharge compressed air through a refrigeration dryer before it can be used is fed, and completely remove the moisture in this refrigeration dryer.
  • Air is usually dried in such a way that the air coming from the compressor heated air first in an aftercooler to a temperature of e.g. 35 - 55 ° C cooled becomes. After that, the air is passed through a heat exchanger device, which is an air / air heat exchanger and has a refrigerant-air heat exchanger.
  • the air / air heat exchanger serves the purpose of the compressed air at approx. 35 - 55 ° C on the one hand on e.g. 20 ° C to cool and on the other hand, the counterflow, from a strongly cooled compressed air coming to a water separator at about room temperature heat up to avoid that on the outer sides of the pipes leading to cold air or Apparatus a cold bridge arises.
  • the refrigerant / air heat exchanger serves the purpose that of the air / air heat exchanger Coming compressed air, cooled to approx. 20 ° C, using a refrigerant, e.g. Freeze on cool down their dew point, which is usually 2 - 3 ° C.
  • a refrigerant e.g. Freeze on cool down their dew point, which is usually 2 - 3 ° C.
  • the refrigerant is in liquefied in a known manner by means of a compressor and a condenser, then by the Refrigerant / air heat exchanger relaxed and thereby to a temperature of e.g. - brought 2 ° C at its entrance and + 4 ° C at its exit, and then again at the Compressor fed.
  • the air cooled down to its dew point becomes after her Passage through the refrigerant / air heat exchanger to a water separator, in from which the moisture is completely removed, and then again through the air / air heat exchanger passed by while cooling the still warm, from the Compressed air system coming compressed air is warmed to about room temperature.
  • the refrigerant / air heat exchanger contains a serpentine or meandering shape laid pipes to be flowed through by air on the baffles or fins are plugged in, and laid between the baffles, to form passages for a Refrigerant specific plates.
  • the pipes are perpendicular to the baffles and plates arranged. This results in a comparatively low heat transfer overall, and A comparatively large construction volume is required to achieve a specified performance.
  • the two heat exchangers also have open passages at their ends and are housed with these in a common housing that has the required redirections for the air or refrigerant flows. This results in a comparative complicated manufacturing method and the disadvantage that the mutual sealing of the different Passages is problematic and high flow resistance can occur, resulting in cross-sectional reductions that reduce efficiency.
  • heat exchangers are known (US-A-4 966 230), which are parallel to one another arranged plates alternately by these limited passages for a first medium and have further passages intended for the flow of a second medium, which pass through pipes lying parallel to the plates, laid in a serpentine or meandering shape are.
  • Such heat exchangers have so far not been used to manufacture heat exchanger devices the genus described at the outset.
  • the invention has for its object the heat exchanger device of the beginning designate the designated genus so that it has a comparatively small volume, is inexpensive to manufacture and has little tendency to become contaminated.
  • the invention has the advantage that a heat exchanger device in a compact design was created, which makes it possible for the entire refrigeration dryer Reduce construction volume to about a third of the previously required volume. Since the Heat exchanger of the heat exchanger device according to the invention also preferably are made of aluminum, the invention also leads to a considerable weight reduction. Finally, the heat exchanger device according to the invention is inexpensive producible, which can significantly reduce the total cost of the refrigeration dryer. Of the Pipe / plate heat exchanger of the heat exchanger device according to the invention is also very compact design and enables a small construction volume. On the other hand, he can be designed on the process air side so that the Risk of serious contamination, especially those that are too noticeable Lead cross-sectional reductions is small. Finally, the heat exchanger points to the Refrigerant side closed pipes so that it is in contrast to in plate construction manufactured heat exchangers has a high compressive strength.
  • 1 and 2 contains an air / air heat exchanger 1 and a refrigerant / air heat exchanger 2. Both heat exchangers 1 and 2 are arranged one above the other according to FIG. 1, the refrigerant / air heat exchanger 2 is below the air / air heat exchanger 1, although it may also be the other way around could.
  • the air / air heat exchanger 1 (Fig. 1) consists of a plate heat exchanger and contains a heat exchanger block 3 (Fig. 5-7) with a plate construction Passages 4 and 5, each in the direction of the arrows, i.e. mostly in counterflow, through which air flows. The air comes out, as shown in FIGS. 6 and 7, each at one end of the passages 4 and 5 laterally into this and at the opposite End in the longitudinal direction again. Passages 4 and 5 are also 4 and 5 alternately arranged one above the other.
  • Each passage 4 is made up of two parallel to the longitudinal direction of the heat exchanger block 3, to the left in Fig. 6 end of the heat exchanger block 3 bordering strips 6 and 7 with in essentially square or rectangular cross-section and two above or arranged below the same, over the entire length and width of the heat exchanger block 3 extended plates 8 formed.
  • the passages 4 are at the right end in FIGS. 5 and 6 through the Width of the heat exchanger block 3 extended strips 9 completed while at the same time the strips 6 are shorter than the strips 7 so that the passages 4 accordingly Fig. 6 are not open to the right end, but to the side and the air in Direction of the drawn arrow can flow in from the side.
  • conventional slats 10 only partially in Fig. 5 are shown and their passages according to FIG. 6 along a line 11 by 90 ° are redirected.
  • the passageways 5 are open.
  • the passages 5 are in Fig. 5 and 7 left end by strips 16 extending over the width of the heat exchanger block 3 completed, while at the same time the strips 14 are shorter than the strips 15 are so that the passages 5 according to FIG.
  • the strips 6, 7, 9 and 16, the plates 8 arranged between them and the between two plates 8 arranged slats 10 and 17 are stacked one above the other, as is known per se from plate heat exchangers, and arranged in such a way that a passage 4 or 5 alternates and the heat exchanger block 3 is completed up and down by a plate 8 each.
  • Plate 8 and possibly also the strips 6, 7, 9 and 16 preferably consist of plated with a solder Aluminum and are first stacked in a known manner and then in an air or vacuum oven or soldered together in a flux bath.
  • the strips 6 and 14, the strips 7 and 15 and the strips 9 and 16 are useful identically formed, so that there is a symmetrical and training of the heat exchanger block 3 results in a particularly cost-effective manner.
  • the Number of runs 4 and 5 depends on the required output of the heat exchanger block 3rd
  • the refrigerant / air heat exchanger 2 (Fig. 1) consists of a combined tube / plate heat exchanger and contains a heat exchanger block 20 (Figs. 8-10) with passages 21 for a refrigerant and passages 22 for the compressed air, the passages 21 and 22 each in the direction of the arrows drawn in Fig. 9, i.e. predominantly in Direct current, through which the refrigerant or compressed air flows.
  • the passages 21 for the refrigerant consist of tubes with a round or preferably rectangular or square cross section, each between two over the length and Width of the heat exchanger block 20 extending plates 23 are arranged. Every run 21 is serpentine or meandering and has a plurality of straight sections 24, which in the exemplary embodiment are parallel to one another and perpendicular are arranged to the longitudinal axis and at a close distance. Two adjacent straight Sections 24 are corresponding to FIG. 9 by sections 25 bent by 180 ° connected that an uninterrupted flow path from an entrance 26 to a Output 27 results. As particularly shown in FIGS.
  • the passages 22 are therefore in FIG. 8 and 9 open at the right and left ends, respectively.
  • the arrangement is such that The passages 21 and 22 alternate in the heat exchanger block 20, i.e. that the pipes (Passages 21) covered on both sides with plates 23 and these to form the passages 21 are kept at a distance by the spacers 28. According to this scheme, in Fig.
  • one passage 21 each can form a unit with the two adjoining plates 23.
  • the various parts of the heat exchanger block 20 consist of those of the heat exchanger block 3 preferably made of aluminum, especially plated with a solder Aluminum, and are first stacked in a manner known per se and then together soldered.
  • the heat exchanger blocks 3 and 20 are arranged one above the other and firmly connected, e.g. soldered.
  • the passages 5 are where the air in it occurs (Fig. 7), with a side and over the height of the heat exchanger block 3 extended collection box 33 connected liquid-tight, the one with a Inlet flange having inlet opening 34 is provided.
  • the passages are 5 at their open ends in FIGS. 1 and 2 by a width and height both the heat exchanger block 3 and the heat exchanger block 20 extended Collection or deflection box 35 with the likewise open right ends of the passages 22 (Fig. 10) of the heat exchanger block 20 connected liquid-tight.
  • the inputs and outputs 26, 27 of the passages shown only schematically in FIGS. 2 and 10 21 are corresponding to FIGS. 3 and 4 each by a tubular construction summarized. Since a total of three passages 21 are provided according to FIGS. 8 to 10 , the three resulting outputs 27 are shown in FIGS. 3 and 4 Way through curved intermediate sections 43 to a flange 44 with a common Exit opening guided, the liquid-tight with a via a curved tube 45 Connection nipple 46 is provided.
  • the inputs 26 are corresponding to a connection nipple 47 (Fig. 1) connected, which is not visible in Fig. 3, because this arrangement the Parts 43 to 46 corresponding part includes.
  • the heat exchangers 1 and 2 described which are firmly connected to one another existing heat exchanger device forms a compact, space-saving unit that as a whole can be assigned to a refrigeration dryer with which conventional Compressed air systems can be equipped, as briefly explained below. It follows the particular advantage that the two heat exchangers 1 and 2 are essentially the same Have width and length and are combined into a common block can.
  • Compressed air is supplied from a compressor, which is preferably provided with an aftercooler delivered, e.g. is at a temperature of approx. 35 - 55 ° C.
  • This compressed air will first fed to the collecting box 33 by means of the inlet flange 34 and flows from there in the direction of an arrow line 49 (FIGS. 2 and 7) through the passages 5 of the air / air heat exchanger 1 in the collection and deflection box 35. From there the compressed air enters the refrigerant / air heat exchanger 2 (Fig. 1) and then flows in the opposite Direction of its passages 22 (Fig. 10 and arrow line 50 in Fig. 9). At the same time it will Refrigerant in the direction of the arrows shown in FIG.
  • the compressed air cooled to the dew point flows after the passage through the passages 22 in the collecting box 40 (Fig. 1), is deflected laterally in this and passes over the side extension 41 (Fig. 2) and the outlet flange 42nd out again. Thereafter, the compressed air, as shown schematically in Fig. 2, one Water separator 51 supplied. The one that comes out of it, completely dried Compressed air is finally via the inlet flange 37 (FIG. 2) and the header box 36 fed back to the air / air heat exchanger 1 so that they passages 4 in Direction of an arrow line 52 in FIGS. 2 and 6 can happen.
  • the compressed air is in Interaction with the warm compressed air passing through the passages 5 up to approximately Warmed up to room temperature before reaching the collection box 38 (Fig. 2) and over the outlet flange 39 of the tap for the compressed air is supplied.
  • the number of their passages 4 and 5 or In principle, 21 and 22 can be enlarged arbitrarily by a corresponding number other plates or pipes are stacked on top of each other without the Change dimensions in the height and width of the heat exchanger device.
  • FIG. 11 to 17 An even more compact and less space consuming heat exchanger device, which is particularly suitable for smaller outputs, results from Fig. 11 to 17. It contains an air / air heat exchanger 56 and a refrigerant / air heat exchanger 57.
  • the two heat exchangers 56, 57 are not one above the other, but arranged side by side and into an integral unit with each other connected.
  • both heat exchangers 56 and 57 are made from a coherent Heat exchanger block 58 is produced, which in its in Fig. 15, 16 and 18th right part a section 59 responsible for the air / air heat exchange and in its left part in Fig. 15, 16 and 18 one for the heat exchange refrigerant / air responsible section 60.
  • Both sections 59, 60 are covered by plates 61 formed, which extend over the entire width and length of the heat exchanger block 58.
  • a part of the plates 61 is on the one hand by perpendicular to the longitudinal direction, at the right end of Fig. 15 of the heat exchanger block 58 arranged strips 62 and on the other hand by extending in the longitudinal direction and up to the left in Fig. 15, 16 and 18 End extending strips 63 and 64 arranged on the side edges of the plates 61 Kept clear. This results in passages 65 between the plates 61, which in 18 left end of the heat exchanger block 58 are open. At the right end in Fig.
  • the lower ledges 64 are somewhat shorter, so that between their right ends and the Last 62 creates a space 66 through which air in the direction of the drawn Arrow can enter laterally.
  • the passages 65 there are usual lamellae 67 (Fig. 15 and 17) arranged, which are designed according to Fig. 18 so that the side entering air is deflected along a line 68 (FIG. 18).
  • the other part of the plates 61 is as shown in FIGS. 15 and 16 in the section 59 forming Part by running parallel to the longitudinal direction on the side edges of the plates 61 15 and 16 to the right end of the heat exchanger block 58 extended ledges 69 and 70 and a transverse to the left end of the Section 59 forming end bar 71 completed.
  • the deflection is preferably also corresponding trained slats 74 causes.
  • the arrangement is such that in a central part of the heat exchanger block 58 the passages 72 and 76 are arranged, each of which is up and down Passage 65 (Fig. 15) connects.
  • FIGS. 11 to 14 An input 81 and an output 82 (FIG. 16) of the passage 76 are shown in FIGS. 11 to 14 and analogous to FIGS. 1 to 4 via curved pipe sections 83, each with a connecting nipple 84, 85 provided, of which only the connection nipple 85 is visible in Fig. 13. Furthermore, the 15, 16 and 18 right ends of the passages 65 with a header box 86 and an inlet flange or inlet nipple 87 which has an inlet opening and is liquid-tight 15, 16 and 18 left ends of the passages 65 with a collection box 88 are connected liquid-tight, similar to the collection box 40 according to FIGS.
  • the coming from the compressed air system is on e.g. approx. 35 - 55 ° C heated compressed air via the inlet flange 87 to the collecting tank 86 fed so that they the passages 65 in the direction of an arrow line 96 (Fig. 18) flows through.
  • the compressed air is first in the heat exchanger 56 by the in Countercurrent through the inlet flange 93 or the header 92 supplied by one not shown water separator coming cold compressed air to a temperature of cooled down to approx. 20 ° C.
  • the compressed air On its way through the passages 65, the compressed air then gradually cooled in the heat exchanger 57 to the dew point, since here with the Refrigerant interacts, which flows through the passage 76 in the direction of the arrows (FIG. 16).
  • the compressed air is then the collector box 88 and the outlet flange 91 Water separator and fed from there to the inlet flange 93 so that they are on the outlet nipple 95, which serves as a tap for the compressed air, again approximately to room temperature is heated.
  • the performance of the heat exchanger device be changed in that the length and width of the Heat exchanger blocks 58, the number of passages 65, 72 and 76 changed accordingly becomes.
  • the refrigerant / air heat exchanger described with reference to FIGS. 8 to 10 and 15 to 18 can also be composed by a plurality of the units 140 shown in FIGS. 19 and 20 9, which is formed according to FIG. 9 and meanders Contains pipe coil 141, on the two broad sides of which a plate 142 or 143 is attached is.
  • the pipe coil 141 can be e.g. either through Solder or bond to plates 142, 143 as in Fig. 20 is indicated by the reference symbol.
  • the entire heat exchanger block expediently consists of a plurality of one above the other stacked units 140 (Fig. 21) which are spaced by spacers 145, e.g. Last, at a distance are held. 22, all coils 141 are made of a single, continuous tube formed.
  • the units 140 can accordingly 22 in a row, but also next to each other, star-shaped, triangular, circular or the like. After that, the individual units 140 become the series laid one on top of the other, the tube sections 146 simply corresponding to FIG. 21 be folded over and therefore outside the front or rear end of the actual one Heat exchanger blocks come to rest.
  • the refrigerant flows through the various units 140 not in parallel, but one after the other.
  • the connections for the compressed air and the refrigerant take place analogously to FIGS. 1 to 18.
  • the straight sections of the pipe coil 141 run as in the embodiment 8 to 10 preferably perpendicular to the strips 145, so that the compressed air or Refrigerant flows are mainly directed perpendicular to each other.
  • the invention is not restricted to the exemplary embodiments described, which are based on can be modified in many ways.
  • the spacers 28 and the adjacent ones Plates 23 or the spacers 145 and the two adjacent plates 142 and 143 as e.g. folded pipes 150 (FIG. 23) with a flat oval or rectangular cross section form and the pipe coil 21 and 141 respectively between two such pipes fasten, the axes of these pipes expediently perpendicular to the straight sections the coil are arranged.
  • passages 21, 76 and 141 continuous Pipe but from several parallel pipes or from the usual plate construction to assemble pipe sections produced, the straight Sections corresponding sections through transverse to the longitudinal direction of the heat exchanger block 20 or 58 running strips and the corresponding to the curved sections Sections also formed by straight, but longitudinally extending sections be, for example, by alternating the above bars in front of one or end of the other longitudinal edge of the respective heat exchanger block and thereby the refrigerant Leave the deflection sections deflected by 180 °.
  • the invention Heat exchangers are readily designed such that e.g. the passages 22 according to FIGS. 8 to 10 of inwardly projecting projections, edges or the like, in particular also from the otherwise usual slats or the like, are completely free. Because in this If there were only large, smooth surfaces on the air side, there would be a risk of Contaminations, especially those that cause noticeable reductions in cross-section over time lead, comparatively low. Nevertheless, such a heat exchanger could trained on the refrigerant side with high pressure resistance and overall with small dimensions can be produced. Furthermore, the individual elements of the described heat exchanger used in other than the combinations shown will.
  • grooved plates or the like could. be provided, which extend over the entire height and depth of the heat exchanger blocks 20th or 140 extend and receive the plates 23, 142 and 143 with their grooves.
  • This Grooved plates could also have holes through which the pipe sections 146 or the ends 147 are guided to the outside.
  • the currents of the refrigerant and the air also differently than in cross flow, in particular also in the or countercurrent or in any other, depending on the individual case Flow direction, for which the strips, coils or the like.
  • Just a different orientation need in the respective heat exchanger block 20 or 140 received. So is without further ado it can be seen that the strip-shaped spacers 145 in FIG. 21 also on the free ones there Sides of plates 142 and 143, i.e. parallel to the straight sections of the coil 141, could be arranged.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Textile Engineering (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Drying Of Gases (AREA)
  • Drying Of Solid Materials (AREA)

Claims (8)

  1. Dispositif d'échangeurs de chaleur pour séchoirs à froid d'installations d'air comprimé, constitué d'un échangeur de chaleur air/air configuré comme échangeur de chaleur à plaques, qui présente des premiers passages (4, 65) et des deuxièmes passages (5, 72) séparés des premiers, et d'un échangeur de chaleur air/fluide de refroidissement configuré comme échangeur de chaleur à tubes/plaques combinés (2, 57) qui présente au moins un troisième passage (22, 65) formé par des plaques (8, 61) et au moins un quatrième passage (21, 76) séparé du précédent, en forme de serpentin ou en méandres, les deux échangeurs de chaleur (1, 56 et 2, 57) étant reliés l'un l'autre pour former un module, et les sorties des premiers passages (4, 65) étant raccordées à l'entrée du troisième passage (22, 65), la sortie du troisième passage (4, 65) étant raccordée aux entrées des deuxièmes passages (5, 72), caractérisé en ce que le troisième passage (22, 65) est prévu pour être traversé par l'air et est formé de plaques (23, 61) et de pièces d'écartement (28, 62-64) disposées entre ces dernières, tandis que le quatrième passage (21, 76) est prévu pour être traversé par le fluide de refroidissement et est également disposé entre les plaques (23, 61), et en ce que le module possède soit deux blocs d'échangeur de chaleur (3, 20) reliés l'un à l'autre par un caisson commun de collecte et de renvoi (35) et formant chacun l'un des échangeurs de chaleur (1, 2), soit un seul bloc d'échangeurs de chaleur (58) qui présente deux tronçons (59, 60) d'échangeur de chaleur formant chacun l'un des échangeurs de chaleur (56, 57).
  2. Dispositif d'échangeurs de chaleur selon la revendication 1, caractérisé en ce qu'il présente deux blocs d'échangeur de chaleur (3, 4) disposés l'un au-dessus de l'autre, reliés par le caisson (35) de collecte et de renvoi.
  3. Dispositif d'échangeurs de chaleur selon la revendication 1, caractérisé en ce qu'il présente deux tronçons (59, 60) disposés l'un au-dessus de l'autre, configurés en un bloc intégré (58) d'échangeur de chaleur.
  4. Dispositif d'échangeurs de chaleur selon l'une des revendications 1 à 3, caractérisé en ce que le troisième passage (22, 65) prévu pour l'air est doté de lamelles (29, 67).
  5. Dispositif d'échangeurs de chaleur selon l'une des revendications 1 à 4, caractérisé en ce que le quatrième passage (21, 76) prévu pour le fluide de refroidissement est constitué d'un tube continu posé en méandres, présentant des tronçons rectilignes (24, 77) disposés parallèlement les uns aux autres et des tronçons (25, 78) reliant les premiers et courbés à 180°.
  6. Dispositif d'échangeurs de chaleur selon la revendication 5, caractérisé en ce que les tronçons en ligne droite (24, 77) sont disposés perpendiculairement à la direction d'écoulement dans les passages (22, 65) présentant les lamelles (29, 67).
  7. Dispositif d'échangeurs de chaleur selon l'une des revendications 3 à 6, caractérisé en ce que le bloc (58) d'échangeur de chaleur est formé de plaques (61) superposées les unes sur les autres et de lamelles (62, 63, 64, 69, 70, 71, 79) maintenant ces dernières à distance, et entre les plaques (61) sont disposés les deuxièmes passages (72) formant les composants de l'échangeur de chaleur air/air (56), et en dessous de ces plaques, dans le sens de la longueur, est disposé le quatrième passage (76) formant un composant de l'échangeur de chaleur fluide de refroidissement/air (57).
  8. Dispositif d'échangeurs de chaleur selon l'une revendications 1 à 7, caractérisé en ce que les deux échangeurs de chaleur (1, 2 et 56, 57) sont réalisés en aluminium.
EP92108919A 1991-06-04 1992-05-27 Dispositif d'échange de chaleur pour séchoir par réfrigération dans les installations d'air comprimé Expired - Lifetime EP0521298B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4118289 1991-06-04
DE4118289A DE4118289A1 (de) 1991-06-04 1991-06-04 Waermetauscher-vorrichtung fuer kaeltetrockner an druckluftanlagen
DE9204952U 1992-04-09
DE9204952U DE9204952U1 (de) 1991-06-04 1992-04-09 Wärmetauscher, insbesondere für Kondensations-Wäschetrockner

Publications (3)

Publication Number Publication Date
EP0521298A2 EP0521298A2 (fr) 1993-01-07
EP0521298A3 EP0521298A3 (en) 1993-04-14
EP0521298B1 true EP0521298B1 (fr) 1999-12-08

Family

ID=25904241

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Application Number Title Priority Date Filing Date
EP92108919A Expired - Lifetime EP0521298B1 (fr) 1991-06-04 1992-05-27 Dispositif d'échange de chaleur pour séchoir par réfrigération dans les installations d'air comprimé

Country Status (7)

Country Link
US (1) US5299633A (fr)
EP (1) EP0521298B1 (fr)
JP (1) JP3273633B2 (fr)
AT (1) ATE187547T1 (fr)
DE (2) DE9204952U1 (fr)
DK (1) DK0521298T3 (fr)
ES (1) ES2142310T3 (fr)

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DE19754405A1 (de) * 1997-12-09 1999-06-10 Manfred H Langner Verfahren und Vorrichtung zum Entfeuchten von Abluft
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SI2407587T1 (sl) 2010-07-16 2013-01-31 Miele & Cie. Kg Sušilni stroj s toplotno črpalko
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DE102011081572A1 (de) * 2011-08-25 2013-02-28 BSH Bosch und Siemens Hausgeräte GmbH Haushaltsgerät mit einem Wärmerückgewinnungsaggregat
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CN103820984B (zh) * 2014-03-18 2016-02-03 杨卫星 一种家用空气内循环式除湿烘衣机
US9682782B2 (en) * 2014-12-04 2017-06-20 Honeywell International Inc. Plate-fin tubular hybrid heat exchanger design for an air and fuel cooled air cooler
JP6190352B2 (ja) * 2014-12-19 2017-08-30 株式会社神戸製鋼所 流体流通装置及びその運転方法
EP3168561A1 (fr) * 2015-11-11 2017-05-17 Air To Air Sweden AB Dispositif d'échange de chaleur et/ou de transfert de masse entre des débits de fluide
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CN110195985A (zh) * 2019-06-11 2019-09-03 哈尔滨汽轮机厂辅机工程有限公司 一种可实现穿管发货的凝汽器水室管板结构
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Also Published As

Publication number Publication date
JP3273633B2 (ja) 2002-04-08
ATE187547T1 (de) 1999-12-15
JPH05223474A (ja) 1993-08-31
DE9204952U1 (de) 1992-07-16
DE59209774D1 (de) 2000-01-13
EP0521298A3 (en) 1993-04-14
DK0521298T3 (da) 2000-05-29
EP0521298A2 (fr) 1993-01-07
ES2142310T3 (es) 2000-04-16
US5299633A (en) 1994-04-05

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