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EP2558186A1 - Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé - Google Patents

Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé

Info

Publication number
EP2558186A1
EP2558186A1 EP11713805A EP11713805A EP2558186A1 EP 2558186 A1 EP2558186 A1 EP 2558186A1 EP 11713805 A EP11713805 A EP 11713805A EP 11713805 A EP11713805 A EP 11713805A EP 2558186 A1 EP2558186 A1 EP 2558186A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
heat transfer
gas
cold storage
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.)
Withdrawn
Application number
EP11713805A
Other languages
German (de)
English (en)
Inventor
Andreas Foerster
Andreas Fredenhagen
Michael Feisthauer
Andreas Walter
Kristian Dering
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.)
Kaeser Kompressoren AG
Original Assignee
Kaeser Kompressoren AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kaeser Kompressoren AG filed Critical Kaeser Kompressoren AG
Priority to EP11713805A priority Critical patent/EP2558186A1/fr
Publication of EP2558186A1 publication Critical patent/EP2558186A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/265—Drying gases or vapours by refrigeration (condensation)
    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • 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
    • 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the invention relates to a heat exchanger for a refrigeration dryer, in particular for a compressed air refrigerant dryer, according to claim 1 and a refrigerant dryer,
  • compressed air refrigerant dryer according to claim 15.
  • an additional countercurrent heat exchanger is provided in this case, through which the incoming gas to be dried can be cooled by the cold outflowing gas, so that on the one hand the required cooling capacity and on the other hand the relative humidity of the exiting gas can be reduced.
  • the power adjustment can be done by a
  • Refrigerant compressor is switched off at a lower temperature limit and is switched on again at an upper temperature limit and / or after a certain time (on-off control). In such a method, however, there are still relatively large fluctuations in the temperature profile of the cooled air and thus to relatively large fluctuations in the achievable pressure dew point.
  • DE 199 43 109 C1 proposes another solution with regard to the problem of fluctuations in the pressure dew point.
  • a "standard heat exchanger" is proposed in connection with a circulating cooling fluid, which in turn is cooled by a refrigeration circuit
  • the construction cost due to the second required heat exchanger and a pump for pumping the ice-water mixture is not insignificant.Furthermore, the energy efficiency is reduced by the multiple heat transfer and the use of the pump.
  • the pump requires on the one hand electrical drive power and on the other hand increases by the heat input into the Refrigerant fluid, the required cooling capacity and thus the power requirement of the refrigeration compressor.
  • the invention is therefore based on the object, a heat exchanger for a refrigeration dryer, in particular for a compressed air refrigerant dryer to propose, in which an operation with low pressure dew point fluctuations is possible and at the same time the design effort (especially in terms of space taking, of Weight and / or the use of materials) is comparatively low. Furthermore, the heat exchanger should allow a comparatively efficient operation.
  • a heat exchanger for a refrigeration dryer in particular for a compressed air refrigerant dryer, according to claim 1 and a refrigerant dryer, in particular compressed air refrigerant dryer, according to claim 15.
  • the object is achieved by a heat exchanger for a refrigerated dryer, preferably for a compressed air refrigerant dryer, with at least a first inflow element, on which a fluid to be dried, in particular compressed air, can flow during operation of the heat exchanger and with at least one second inflow surface element, on which during operation of the
  • the first and second Anström lakeelement are at least partially coupled to at least one intended cold storage space for filling with a cold storage medium and can be coupled and wherein the first and / or second Anström lakeelement with at least one in the Cold storage space hineinerux, in particular the cold storage space penetrating, heat transfer element is / is connected.
  • An essential idea of the invention is that the heat transfer elements extending into the cold storage space are provided.
  • No. 7,134,483 B2 proposes a stack of profiled metal plates, in which the thermal contact between one plate and the next, and thus from one gap to the next, is comparatively small. In contrast, the thermal contact according to the present invention is increased. Also, especially with respect to US Pat. No. 7,134,483 B2, rapid release of heat, for example heat of solidification, when using
  • latent storage materials such as paraffins
  • the refrigeration dryer according to the invention is particularly advantageous here.
  • the problems that resulted, for example, in DE 102 11 602 AI from the outside attachment of the thermal storage are reduced by the present invention proposed refrigerant dryer.
  • the transfer surfaces are comparatively high and the heat transfer paths are comparatively short, which leads to an overall efficient operation of the refrigeration dryer.
  • Heat transfer element or a further heat transfer device is provided.
  • the transfer of heat from (or to) the cold storage medium takes place in particular via the heat transfer element.
  • a heat transfer for example, from the cold storage medium to be dried air over the
  • Heat transfer element a first plate, a refrigerant heat transfer element, a second plate and an air-heat transfer element take place.
  • the refrigerant may flow.
  • the refrigerant heat transfer member may be formed like the heat transfer member.
  • heat transfer element (without further additives) always means the heat transfer element extending into the cold storage space.
  • the refrigerant heat transfer element and the air-heat transfer element are preferably part of the corresponding inflow elements.
  • the refrigerant heat transfer element and the air-heat transfer element further improve the thermal interface.
  • the cold storage space may preferably be filled with a corresponding cold storage medium, in particular a latent heat storage medium (PCM, "Phase Change Material").
  • a thermal conductivity of the heat transfer element is preferably at least 10 times, more preferably at least 30 times, even more preferably at least 100 times as high
  • the thermal conductivity of the heat transfer element may be, for example, at least 50 W / (mK), preferably at least 100 W / (mK), more preferably at least 130 W / (mK)
  • a specific heat capacity of the cold storage medium may, for example, be at least 1 kJ / (kgK), preferably at least 1.5 kJ / (kg K), even more preferably at least 2 kJ / (kg K).
  • a phase change enthalpy of the cold storage medium may be, for example, at least 50 kJ / kg, preferably at least 100 kJ / kg, more preferably at least 150 kJ / kg.
  • Water and / or paraffin and / or a liquid-crystalline latent heat store and / or a latent heat storage material based on salt or paraffin can preferably be used as the latent heat storage medium.
  • the heat absorption capacity (when using a latent heat accumulator in the region of the phase transition temperature) of the cold storage medium relative to the heat transfer element is comparatively high.
  • the thermal conductivity of the heat transfer element relative to the cold storage medium is relatively high.
  • the cold storage space is at least partially limited by a first and / or second, in particular flat, plate.
  • the first and / or second inflow surface element may be at least partially formed by the first or second, in particular flat, plate.
  • the first and / or second, in particular flat, plate can be formed at least partially by the first or second inflow surface element.
  • the first and / or second inflow surface element may at least partially be formed by a line wall section, in particular a pipe wall section.
  • a pipe wall may preferably be rectangular, in particular square or have a round cross-section.
  • the heat transfer element with the first and / or second Anström vomelement or the first and / or second, in particular flat plate, soldered. This improves the heat transfer and thus the efficiency of the heat exchanger.
  • any point within the cold storage space is closer to a next heat transfer element than a maximum distance, the maximum distance being less than a plate spacing between the plates, with a ratio of plate distance to maximum distance preferably at least 4, more preferably at least 6, more preferably at least 10.
  • the maximum distance may preferably be 0.5 mm to 2.00 mm, in particular about 0.75 mm to 1.25 mm.
  • Heat transfer element are thus preferably designed such that no point within the cold storage space is farther away than a predetermined maximum distance.
  • comparatively short heat conduction paths in the cold storage space or within the cold storage medium are achieved, so that even with a comparatively low thermal conductivity of the cold storage medium, large quantities of heat can be absorbed or released in a short time.
  • a comparatively high efficiency can be achieved with a small footprint.
  • the maximum distance is the largest distance that is available for a point in the
  • Cold storage medium can occur for each next heat transfer element.
  • At least one heat transfer element has at least two sections spaced apart by a heat transfer distance, in particular parallel sections, the sections preferably (substantially) perpendicular to at least one of the, in particular flat, plates, the heat transfer distance preferably being smaller is greater than a plate spacing of the plates, with a ratio of plate distance to heat transfer distance more preferably at least 2, more preferably at least 3, even more preferably at least 5, even more preferably at least 10.
  • the efficiency of the heat exchanger is improved in a structurally simple manner.
  • the plate spacing may preferably be at least 5 mm, more preferably at least 10 mm.
  • the heat transfer distance may preferably be 1 mm to 4 mm, in particular 1.5 mm to 2.5 mm.
  • connection surface in particular solder connection surface, between the first and / or second inflow surface element and / or the first and / or second, in particular flat, plate on the one hand and the at least one heat transfer element on the other hand, at least 10%, preferably
  • connection can also be made, for example, by welding or gluing (in general).
  • the heat exchanger in particular at least one inflow surface element and / or at least one (flat) plate and / or at least one heat transfer element is / are preferably at least partially made of metal, in particular aluminum. This can also improve efficiency.
  • a gas-gas region is formed such that a heat exchange between the fluid to be dried and dried fluid is feasible. This can increase the efficiency of the heat exchanger.
  • a guide for the gas to be dried is at least partially defined by at least one, in particular at least two, in particular flat, plates, the guide still further preferably at least partially through the gas-gas region and a gas-refrigerant region for heat exchange between the fluid to be dried and the refrigerant extends.
  • a meandering curved pipe for guiding the refrigerant is provided, wherein the tube is preferably soldered between the two (flat) plates and further preferably at least one cold storage space is arranged between each two tube passages. This allows a space-saving design.
  • At least one refrigerant guide is designed as a space between at least two (flat) plates, wherein preferably the plates are soldered (generally firmly connected) to at least one heat transfer element.
  • a partition plate between the refrigerant and the storage medium at least partially extends over the gas-gas region.
  • At least two cold storage spaces are fluidly connected to each other by at least one, possibly mounted on an outer side, in particular welded, collecting device.
  • a refrigerant dryer in particular compressed air refrigerant dryer, comprising a heat exchanger according to the above-described type.
  • Figure 1 is a arranged between two plates heat transfer element in a schematic sectional view.
  • FIG. 2 shows a first embodiment of the heat exchanger according to the invention in a schematic side view.
  • FIG. 3 shows the embodiment of FIG. 2 along the section line III-III
  • Fig. 4 shows a second embodiment of the heat exchanger in a schematic
  • FIG. 5 shows a detail of the embodiment according to FIG. 4 in an oblique view
  • Fig. 6 is an enlarged detail of Fig. 5;
  • Fig. 7 is a further schematic sectional view of the between two plates
  • Fig. 8 is a section along the line VIII-VIII of Fig. 7;
  • Fig. 1 shows a heat transfer element 10, which is soldered between a first flat plate 11 and a second flat plate 12.
  • the heat transfer element 10 consists of a sheet which is bent over periodically by 90 degrees. The sheet is preferably provided with slots. Bending points may be partially offset by a predetermined amount.
  • the heat transfer element 10 comprises connecting sections 13, which preferably run parallel to the flat plates 11, 12 and transfer sections 14, which are preferably perpendicular to the connecting sections 13 and the flat plates 11, 12.
  • the sheet-like heat transfer element 10 extends generally (substantially) parallel to the delimiting flat plates 11, 12 (the sections also being perpendicular to the flat plates).
  • the connecting portions 13 of the heat transfer element 10 are soldered to the flat plates 11, 12, but can also be glued or otherwise firmly connected with these.
  • a cooling fluid generally refrigerant
  • the gas to be dried can flow past.
  • the second flat plate 12 serves as a first inflow surface element, on which a fluid to be dried, in particular compressed air, can flow past during operation of the heat exchanger.
  • the first flat plate 11 is used in such a configuration as a second inflow surface element, on which, as needed, the refrigerant can flow past during operation of the heat exchanger.
  • a first embodiment of the heat exchanger can be seen in a schematic side view.
  • the heat exchanger is divided into a first (upper) region, namely a gas-gas region 17 and a second (lower) region, namely a gas-refrigerant region 18.
  • a heat exchange between the gas to be dried and an at least partially dried gas can take place.
  • a heat exchange between the gas to be dried and the refrigerant via a plate between a Refrigerant tube 20 and a first passage 25 for the gas to be dried.
  • the meandering curved refrigerant tube 20 which is a rectangular (preferably square)
  • the refrigerant tube 20 may also have a round or still different cross-section.
  • intermediate spaces 21 between the oppositely parallel longitudinal sections 22 of the refrigerant tube 20 are cold storage subspaces 23 for receiving a cold storage medium.
  • the cold storage part spaces 23 are connected to each other via a collecting device 24 (collecting tank) on an outer side of the heat exchanger and form the cold storage space 19 from.
  • each heat transfer elements 10 which is a comparatively fast storage or
  • the collection device 24 extends over two
  • two complementary collectors 24 may be provided on the outside.
  • the gas to be dried first flows through the first passages 25 through the gas-gas region 17 and then through the gas-refrigerant region 18.
  • the gas to be dried flows both at the meandering Refrigerant tube 20 and past the cold storage compartments 23.
  • the gas to be dried flows through a deflection region 26, in which a precipitated condensate can be separated and discharged through a condensate outlet 27.
  • the gas to be dried continues to flow via an inlet 28 through second passages 29 in the gas-gas region 17 (in countercurrent to the incoming gas) up to an outlet 30.
  • the gas to be dried can be supplied via a feed 31.
  • the heat exchanger of FIG. 2 and 3 is sandwiched, wherein in a first, third and fifth layer between two plates in the gas-gas region 17 of the second passages 29 extends and in the gas-refrigerant region 18 each one of meander-shaped refrigerant tubes 20 is provided with arranged between the longitudinal portions 22 of the refrigerant tube 20 cold storage compartments 23.
  • a second and fourth layer in each case one of the first passages 25 extends for the incoming gas to be dried.
  • the arrangement can in principle also be designed differently, for example, at least three layers of first passages and at least two layers of second passages can be provided. In general, an alternating arrangement of first and second passes is preferred.
  • 4 shows a second embodiment of the heat exchanger in a schematic sectional view.
  • the heat exchanger according to FIG. 4 is likewise subdivided into a gas-gas region 17 and a gas-refrigerant region 18.
  • the gas initially flows through a first passage 25 through the gas-gas region 17 and then the gas-refrigerant region 18 via a feed, not shown.
  • each two flat plates 11, 12 refrigerant lines 32 and cold storage part spaces 23 are provided for a cold storage medium.
  • the cold storage subspaces 23 are separated from the refrigerant pipes 32 by (level) partition plates 33.
  • the flat plates 11, 12 and the partition plate 33 extend (substantially) parallel to the first passages 25.
  • Heat transfer elements 10 are provided in the cold storage compartments 23. Further heat transfer elements may also be located in the first passages 25 and / or the refrigerant lines 32 and / or the second passages 29. Shape and dimension of the respective heat transfer elements may differ from each other.
  • the partition plate 33 extends through both the gas-refrigerant region 18 and the gas-gas region 17. This results in the gas-gas region 17 each two adjacent mutually parallel second passages 29 for the outflowing, partially dried gas. Analogous to FIGS. 2 and 3 (in Fig. 4 can not be seen) with a deflection and separation with
  • Condensate drain be provided.
  • the heat exchanger according to FIG. 4 also has a five-layer structure, with first passages 25 extending in each case in a second and fourth layer.
  • first passages 25 extending in each case in a second and fourth layer.
  • second passages 29 extend within the gas-gas region 17, and one cold-storage chamber 23 and one refrigerant line 32 in the gas-refrigerant region 18, respectively.
  • more than five layers or less, for example only three layers may be provided analogously to the construction shown in the figures.
  • a phase change temperature when using latent heat storage media in a predetermined operating range of the heat exchanger.
  • storage media for example, materials such as paraffins, carboxylic acids, fatty alcohols, esters, amines and / or halogenated hydrocarbons, and
  • FIG. 5 shows a section of the embodiment of FIG. 4 in an oblique view.
  • the embodiment according to FIGS. 5 and 6 can also be regarded as a complete heat exchanger.
  • two second passages 29 are provided between the first and the second planar plates 11, 12 in the gas-gas region 17 and are separated from one another by the separating plate 33.
  • the second passages 29 are opposite to the gas-refrigerant region 18 by one each
  • Separating strip 34 separated or sealed.
  • the second passages 29 periodically bent sheets 35 are arranged, along which the partially dried fluid can flow along.
  • the metal sheets 35 are bent in such a way that approximately trapezoidal recesses are formed in the cross section.
  • the first passage 25 in which the fluid to be dried is carried out.
  • Passage 25 is also a periodically bent sheet, which is designated by the reference numeral 37.
  • the sheet 37 has periodically repetitive recesses, which are formed approximately trapezoidal in cross section.
  • the refrigerant line 32 which comprises a ribbed plate 38.
  • the fin plate 38 has periodically repeating ribs, so that a plurality of individual fluid channels for the refrigerant is formed. Similarly, a plurality of fluid channels is formed by the plate 35 and the plate 37.
  • the fluid channels of the sheets 35, the sheet 37 and the ribbed plate 38 extend in FIGS. 5 and 6 from top to bottom or independently of the
  • a cold storage space 19 or a plurality of cold storage partial spaces 23 are provided between the first flat plate 11 and the separation plate 33.
  • the cold storage space 19 comprises a heat transfer element 10, which is formed as a periodically bent sheet metal.
  • a cold storage medium is introduced in the cold storage space 19 and the recesses of the sheet-like heat transfer element 10.
  • the cold storage medium (this also applies to the other embodiments) is preferably provided stationary within the cold storage space 19 and can further preferably via a filling device 39, which preferably corresponds to the collecting device 24, are introduced.
  • Heat transfer element 10 a plurality of fluid channels are provided which extend horizontally or perpendicular to the fluid channels of the sheets 37 and the rib plate 38. As a result, the heat transfer is improved in a simple manner, which improves the efficiency.
  • the heat exchanger can preferably be soldered after arranging a plurality of, in particular all components (plates, heat transfer elements, strips and / or optionally pipelines) in a continuous furnace with a protective gas atmosphere or in a vacuum furnace or in a flux.
  • the heat transfer elements can be used for example in so-called aluminum block heat exchangers to achieve comparatively high heat transfer performance at a flow.
  • the heat transfer elements are suitable for use with a stationary storage medium.
  • the heat transfer elements may be, for example, folded thin sheets, which optionally contain slots, holes and / or other recesses.
  • the folds can also be executed partially offset in particular slotted sheets.
  • the heat transfer elements may alternatively be formed as extruded or extruded profiles.
  • Storage heat exchanger is preferably provided on the one hand, a comparatively large area in solder connection with the delimiting plates and on the other hand, a large contact area with the storage medium with in particular narrow intervals of sautabitesen.
  • the structure is continuously filled with a storage medium.
  • the heat transfer elements preferably have narrow recesses (for example, 1.5 mm to 2.5 mm wide) which are more preferably (substantially) perpendicular or at an angle of> 60 degrees to the flat plates, so that from any point within of the storage medium a comparatively short heat conduction path to the heat transfer element - at least parallel to the plates - is realized. Due to the comparatively high thermal conductivity of the heat transfer elements, the spacings of the separating plates can be made significantly larger than the width of the recesses of the heat transfer elements (for example 8 mm to 12 mm, in particular 10 mm), so that a comparatively large volume for the storage medium is achieved.
  • the heat transfer elements By manufacturing the heat transfer elements of a material with high thermal conductivity, such as aluminum and / or surface soldering of the heat transfer elements with the flat plates, rapid heat transfer can be achieved at low temperature differences from both the refrigerant to the storage medium and the storage medium to be dried gas.
  • a material with high thermal conductivity such as aluminum and / or surface soldering of the heat transfer elements with the flat plates
  • a comparatively good heat conduction connection is achieved from the cold storage medium to the respective plate and thus to both the first passages 25 on an opposite side of the plate and to the refrigerant tube 20.
  • the refrigerant tube 20 is preferably soldered to at least one of the plates.
  • the heat exchanger is preferably designed as a combined heat exchanger with gas-gas area and gas-refrigerant area (gas-refrigerant storage area), more preferably with a continuous through both heat exchanger areas passage of the incoming gas. But it is also possible, a
  • the partition plate extends between cold storage medium and refrigerant over the entire height (longitudinal extent) of the heat exchanger, so that the passages for the exiting, at least partially dried, gas are subdivided into two adjacent parallel passages.
  • Fig. 7 shows another schematic sectional view of the arranged between two plates heat transfer element.
  • a sum of the cross-sectional areas of the transfer sections 14 is preferably at least 5%, more preferably at least 10%, even more preferably (about) 15% of a disk surface (which is further illustrated by FIG. 8).
  • Heat transfer element 10 is made in one piece from a metal sheet by forming slots and bending the sheet.
  • the heat transfer element 10 comprises a plurality of heat transfer element rows 40, each corresponding to a periodically bent sheet metal strip. Two mutually adjacent heat transfer element rows 40 are each formed the same, but offset in a direction parallel to the preferred direction of the heat transfer element rows by a predetermined amount.
  • the predetermined amount may be, for example, (about) a quarter period of the periodic bends. Overall, this creates a heat transfer element 10 which, on the one hand, is comparatively stable and, on the other hand, permits a comparatively simple filling with a cold storage medium.
  • the materials for the heat transfer elements and / or plates and / or refrigerants in particular aluminum or aluminum alloys can be used, for example AIMg 3 .
  • the materials preferably have a thermal conductivity of more than 100 W / (m 2 K), more preferably more than 130 W / (m 2 K), and are thus significantly above the thermal conductivities of ordinary latent storage materials in which the thermal conductivity is below at least 2 W / (m 2 K) or even 1 W / (m 2 K).
  • a comparatively large specific surface area of the heat transfer elements 10 is provided based on the storage volume of the cold storage space 19 wherein the specific surface area is more preferably at least 500 m 2 / m 3 , more preferably at least 1000 m 2 / m 3 , even more preferably (about) 1200 m 2 / m 3 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé, comportant au moins un premier élément à surface baignée par l'écoulement, sur lequel un fluide à sécher, en particulier de l'air comprimé, peut s'écouler lors du fonctionnement de l'échangeur de chaleur, et comportant au moins un deuxième élément à surface baignée par l'écoulement, sur lequel un fluide cryogénique peut s'écouler en cas de besoin lors du fonctionnement de l'échangeur de chaleur. Le premier et le deuxième élément à surface baignée par l'écoulement sont ou peuvent être accouplés au moins par endroits à au moins un espace d'accumulation de froid prévu, pour le remplissage par un fluide d'accumulation de froid. Le premier et/ou le deuxième élément à surface baignée par l'écoulement sont reliés à au moins un élément de transfert de chaleur s'étendant dans l'espace d'accumulation de froid, et notamment traversant l'espace d'accumulation de froid.
EP11713805A 2010-04-14 2011-04-12 Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé Withdrawn EP2558186A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11713805A EP2558186A1 (fr) 2010-04-14 2011-04-12 Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé

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EP10159958.7A EP2377596B9 (fr) 2010-04-14 2010-04-14 Dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé, ainsi qu'échangeur de chaleur pour un dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé
PCT/EP2011/055672 WO2011128317A1 (fr) 2010-04-14 2011-04-12 Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé
EP11713805A EP2558186A1 (fr) 2010-04-14 2011-04-12 Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé

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EP2558186A1 true EP2558186A1 (fr) 2013-02-20

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EP10159958.7A Active EP2377596B9 (fr) 2010-04-14 2010-04-14 Dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé, ainsi qu'échangeur de chaleur pour un dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé
EP11713805A Withdrawn EP2558186A1 (fr) 2010-04-14 2011-04-12 Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé

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US (1) US10143962B2 (fr)
EP (2) EP2377596B9 (fr)
KR (1) KR101932924B1 (fr)
CN (1) CN102971064B (fr)
BR (1) BR112012026170B1 (fr)
WO (1) WO2011128317A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2377596B9 (fr) 2010-04-14 2016-04-13 Kaeser Kompressoren Se Dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé, ainsi qu'échangeur de chaleur pour un dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé
DE102012110237A1 (de) 2012-07-31 2014-02-06 Thermea. Energiesysteme Gmbh Kältetrockner
FR3014183B1 (fr) * 2013-11-29 2019-05-17 Valeo Systemes Thermiques Echangeur thermique notamment pour vehicule automobile, procede de fabrication correspondant, et utilisation d'un materiau a changement de phase associee
CN103712487A (zh) * 2013-12-16 2014-04-09 吴江华诚复合材料科技有限公司 一种冷却器
US20160377350A1 (en) * 2015-06-29 2016-12-29 Honeywell International Inc. Optimized plate fin heat exchanger for improved compliance to improve thermal life
CN105910478B (zh) * 2016-04-14 2018-05-29 青岛海尔特种电冰箱有限公司 均温容器及具有该均温容器的冰箱
FI20205367A1 (en) * 2020-04-06 2021-10-07 Vahterus Oy PLATE HEAT EXCHANGER ARRANGEMENT

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003076860A1 (fr) * 2002-03-09 2003-09-18 Behr Gmbh & Co. Echangeur de chaleur

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2241411A (en) * 1939-07-03 1941-05-13 Kold Hold Mfg Company Refrigeration
US2416015A (en) * 1943-02-06 1947-02-18 Kold Hold Mfg Company Method of making holdover refrigeration plates
US2814186A (en) * 1955-12-28 1957-11-26 Dole Refrigerating Co Truck plates
DE3428335A1 (de) * 1984-08-01 1986-02-13 Via GmbH, 4000 Düsseldorf Vorrichtung zur kaeltetrocknung von unter druck stehendem gas, insbesondere druckluft
EP0405613B1 (fr) 1989-06-30 1995-06-21 Mta S.R.L Echangeur de chaleur
DE9204952U1 (de) * 1991-06-04 1992-07-16 Autokühler GmbH & Co KG, 3520 Hofgeismar Wärmetauscher, insbesondere für Kondensations-Wäschetrockner
US5275233A (en) * 1993-01-25 1994-01-04 Ingersoll-Rand Company Apparatus for removing moisture from a hot compressed gas
US5816320A (en) * 1997-01-10 1998-10-06 J.I.T. Engineering, Inc. Radiator fin construction
US5845505A (en) * 1997-05-30 1998-12-08 American Precision Industries Inc. Precooler/chiller/reheater heat exchanger for air dryers
IT1310894B1 (it) * 1999-08-31 2002-02-22 O M I Srl Impianto di essiccazione per aria compressa
DE19943109C1 (de) 1999-09-09 2000-12-14 Kta Kaelte Und Drucklufttechni Druckluftkältetrockner
US6393861B1 (en) * 1999-09-17 2002-05-28 Robert Levenduski Thermal storage apparatus and method for air conditioning system
JP4312339B2 (ja) 2000-02-24 2009-08-12 ナブテスコ株式会社 蛇行通路付熱伝達装置
FR2807828B1 (fr) * 2000-04-17 2002-07-12 Nordon Cryogenie Snc Ailette ondulee a decalage partiel pour echangeur de chaleur a plaques et echangeur de chaleur a plaques correspondant
DE10124757A1 (de) * 2000-05-26 2001-11-29 Denso Corp Fahrzeugklimaanlage mit Kältespeicher
DE10030627A1 (de) * 2000-06-28 2002-01-17 Ultrafilter Internat Ag Wärmetauscher für Kältetrockneranlagen
FR2845153B1 (fr) * 2002-10-01 2005-11-18 Nordon Cryogenie Snc Ailette pour echangeur de chaleur a plaques, procedes de fabrication d'une telle ailette, et echangeur de chaleur comportant une telle ailette
DE10311602A1 (de) 2003-03-14 2004-09-23 Agt Thermotechnik Gmbh Vorrichtung, insbesondere Wärmetauscher, und Verfahren
US7134483B2 (en) 2003-09-26 2006-11-14 Flair Corporation Refrigeration-type dryer apparatus and method
DE10347880B4 (de) * 2003-10-10 2007-10-31 Gea Wtt Gmbh Plattenwärmetauscher zum Trocknen eines gasförmigen Mediums
ITMI20040926A1 (it) * 2004-05-07 2004-08-07 Domnick Hunter Hiross S P A Essicatore di gas compresso a refrigerazione
DK1616610T3 (da) * 2004-07-13 2012-10-22 Byeong-Seung Lee Plade-varmeveksler med en adskillelsesfunktion med hensyn til kondenseret fluidum og fremgangsmåde til dens fremstilling
WO2006059005A1 (fr) * 2004-11-30 2006-06-08 Valeo Systemes Thermiques Echangeur de chaleur avec accumulateur thermique
DE202005015627U1 (de) 2005-09-28 2007-02-08 Autokühler GmbH & Co. KG Wärmeaustauschernetz und damit ausgerüsteter Wärmeaustauscher
WO2008155810A1 (fr) * 2007-06-18 2008-12-24 Mitsubishi Electric Corporation Élément d'échange de chaleur, procédé de fabrication de l'élément de chaleur, échangeur de chaleur et dispositif d'échange de chaleur et de ventilation
GB0802445D0 (en) * 2008-02-11 2008-03-19 Penfold William L Low energy cooling device
FR2930020B1 (fr) * 2008-04-10 2014-09-19 Valeo Systemes Thermiques Echangeur interne comportant un moyen de stockage thermique et boucle incorporant un tel echangeur.
EP2377596B9 (fr) 2010-04-14 2016-04-13 Kaeser Kompressoren Se Dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé, ainsi qu'échangeur de chaleur pour un dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé
KR101274241B1 (ko) * 2011-08-23 2013-06-11 현대자동차주식회사 차량용 에어컨 시스템
KR101316859B1 (ko) * 2011-12-08 2013-10-10 현대자동차주식회사 차량용 컨덴서

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003076860A1 (fr) * 2002-03-09 2003-09-18 Behr Gmbh & Co. Echangeur de chaleur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2011128317A1 *

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WO2011128317A1 (fr) 2011-10-20
KR101932924B1 (ko) 2019-03-15
BR112012026170B1 (pt) 2020-05-19
BR112012026170A2 (pt) 2017-10-17
US20130032315A1 (en) 2013-02-07
CN102971064B (zh) 2016-06-22
EP2377596B1 (fr) 2016-01-06
KR20130133119A (ko) 2013-12-06
EP2377596A1 (fr) 2011-10-19
US10143962B2 (en) 2018-12-04
CN102971064A (zh) 2013-03-13
EP2377596B9 (fr) 2016-04-13

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